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 ' / . ; *. SJ-WWV'Y'.- American Society of Heating and Ventilating Engineers Heating ventilating air conditioning guide. VOL 2A 19 St 628.8 AMERICAN 21718 77910 Ml i ' Sr. Louis Public Library Heating Ventilating Air Conditioning Guide 1946 >vC/,e-T: v* , Heating Ventilating " Air Conditioning GUIDE 1946 `' ' . An Instrument of Service prepared for the Profession--Containing a Technical Data Section OP REFERENCE MATERIAL ON THE DESIGN AND SPECIFICATION OF HEATING, VENTILATING AND AIR CONDITIONING SYSTEMS BASED ON----THE TrANS- ACTIONS--THE INVESTIGATIONS OF THE RESEARCH LABORATORY AND CO OPERATING Institutions--and the Practice of the Members and ". . Friends of the Society .. TOCETHER WITH A . Manufacturers' Catalog Data Section ' Containing Essential and Reliable Information Concerning Modern Equipment . ALSO . Th& Roll of Membership of the Society ., WITH . Complete Indexes to Technical and Catalog. Data Sections . . ' . Vol. 24 . $6.00 per Copy _ . . ' f' PuBlisiHED AhNUALI.y;BY-' ' - ' American Society of Heating And Ventilating Engineers , 51 Madison Avenue 'New York to, N. Y. A55410 Amei Vei I coi :- ..4 <? *zy.r- Copyright, i946 ' by' the American Society of Heating and Ventilating Engineers AND BY IT - ... . . . ; `C Dedicated \ To the. Advancement of . ' . - n * /. f / '. The Profession ' ' ' AND ' . .. ' , ' ' ' ` ' :` Its Allied Industries ' . ' text and illustrations are fully pro TECTED ' BY COPYRIGHT . AND NOTHING^ THAT APPEARS MAY BE REPRINTED EITHER WHOLLY OR IN PART WITHOUT SPEGIAL PERMISSION. Printed and Bound by ' * The Horn-Shafer-Company BALTIMORE MARYLAND D. S. A. 1 V- Y'. ' ' '' i M /t? PREFACE TO THE 24th EDITION ^ - -- '- rr^HE twenty-fourth edition of The Heating, Ventilating, Air Conditioning $ J[ Guide contains an enlarged technical data section and a new grouping of subjects 3 to provide a more logical progression from fundamental principles to special application. The Guide serves a dual function as both textbook and handbook. As text, it repre sents a condensation'of the pertinent experimental data in this field. The desire for accuracy precludes the use of many of the approximate but convenient tables of the ordinary handbook. - Terminology, Chapter one, covering engineering terms used in heating, ventilating, and air conditioning, has been revised to obtain better conformance with the terms of basic science rather than the less accurate forms which are frequently adopted by engi neers in a specific field. Progress in standardization of letter symbols has been con tinued; leading to uniformity of symbols used throughout the text as far.as possible. Separate lists of symbols have been placed at the end of those chapters in which large numbers of symbols are used. . . The most accurate information obtainable on properties of moist air and of water in the range --160 to +212 F has been obtained from the cooperative research work of the A.S.H.V.E. and the Towne Scientific School of the University of Pennsylvania and is incorporated in Chapter 3, Thermodynamics. The new Mollier Diagram for Moist Air, prepared by John A. Goff, corresponds With the revised tables of Properties of Moist Air arid of Water in Chapter 3, and, in its larger size, is improved in readability. Chapter 4, Fluid Flow, is a new and very useful addition to the text as it presents the basic theory of fluid flow through pipes, nozzles, and orifices and gives recommendations for location of pressure taps for orifice and venturi meter applications.. The explanation of the method of using the data in Chapter 6, Heat Transmission Coefficients of Building Materials, has been simplified and certain suggestions regarding the use of the tabulated data have been added. Chapter 10, Air Contaminants, contains most of the material previously given in the former chapter, on Air Pollution as well as the latest acceptable limits for toxic gases and dusts in.working spaces. The rewritten chapter gives the viewpoint of the industrial hygiene engineer. Much useful information regarding the use of testing equipment is . given in Chapter 11, Instruments and Measurements. In Chapter 12, Physiological Principles and Chapter 13, Air Conditioning in the Prevention and Treatment of Disease it has been possible to add interesting information obtained from tests conducted in cooperation with the military services during the war. Chapter 15, Cooling Load, has been improved by the addition of new data on solar heat transmission through glass obtained from a recent study made at the A.S.H.V.E. Research Laboratory. Revision has been made in the method of computing the cooling load in order to reflect present knowledge of the subject. . A new section on furnaces has been included in Chapter 18, Heating Boilers and Fur naces. This chapter now includes information on the characteristics, performance, and . latest rating methods for these appliaftces. Chapter 21, Gravity Warm Air Systems, and Chapter 22, Mechanical Warm Air Systems show the progress made during the past year in the methods of designing and installing warm air systems. To the pipe capacity tables in Chapter 23, Steam Heating Systems and Piping, have ' been added the capacities expressed in pounds of steam so that these capacities are now available in both EDR and pounds. Similarly.a chart has been added to Chapter 24, Hot Water Heating Systems and Piping) showing pipe capacities in pounds of water per . hour corresponding to various friction losses. This chart is supplied in addition to the familiar chart showing the capacities based on 20 deg temperature drop. Methods (with illustrative examples) of computing heat loss through pipe covering consisting of layers of different kinds of insulation have been added to Chapter 28, Pipe Insulation. Chapter 38, Dehumidification by Sorbent Materials, has been amplified to include the latest accepted practice in use of sorbents. Chapter 39, Refrigeration, has been enlarged to permit-a simple presentation of the different refrigeration cycles in addition to a brief treatment of the most commonly used refrigeration equipment arrangements. New material from Society sponsored research on air flow in outlets has been added ) to Chapter 40, Air Distribution, to provide additional useful design information. As a ' .result of studies of the best available data on air flow, made at the A.S.H.V.E. Research Laboratory, a new air friction chart has been prepared and this chart is now included in Chapter 41, Air Duct Design. . . - The economics of air conditioning are given in a new Chapter 44, Owning and Operat ing Costs, which shows the method of determining the actual cost of air conditioning to the owner. .v rrvr*. In Chapter.5I, Codes'and Standards,''the list, of various codes'affecting installation of air conditioning and heating'equipment has been .brought'up-to-date through inform ation obtained from the various state departments concerned. The chapter also contains a list of more than 75 codes and. standards, relating to performance, rating, testing, . selecting and installing equipment used in heating, ventilating, and air conditioning work, adopted by various societies and organizations. . All chapters not specifically mentioned in the foregoing have been carefully reviewed so that they conform to current engineering practice. .. A complete cross-index of the technical section provides ready reference to any . desired information in the text. . '' - As in the past the Guide Publication Committee has had the cooperation and enthu siastic support of a great many Society members and interested organizations, as well as other authorities on the subjects treated in The Guide. To those who have contributed to the success of the previous editions great credit is due for the present high standing of The Guide throughout the world. In the preparation of the 1946 edition the following . members and others have served faithfully and capably and therefore the Guide Publi cation Committee takes great pleasure in expressing its sincere appreciation of their services: '- -. P, R. Achenbach J. C. Albright C. M. Ashley A. R. Behnke C. B. Bradley A. D. Brandt R. C. Cross A. G. Dixon C. W. Drake F. C. Fennell John A. Goff F. G. Hechler R. H. Heilman C. M. Humphreys L. N. Hunter F. W. Hutchinson E. F. Hyde S. Konzo F. J. Kurth J. N. Livermore D. W. Loucks R. D. Madison W: L. McGrath D. W. Nelson H. B: Nottage F. J. NunlisT, Jr. J. S. Parkinson G. V. Parmelee E. R. Queer H. E. Rex K. M. Ritchie C. G. Segeler L. G. Seigel E. T. Smith J. P. Stewart Ernest Szekely G. L. Tuve L. M. Van der Pyl W. J. Warren W. N. Witheridge D. K. Wright, Jr. C. P. Yaglou An enlarged Catalog Data Section contains condensed information from 233 manu facturers of modern equipment and constitutes a valuable reference section for the engi neer, architect, contractor, or student interested in all types of heating, ventilating, and : air conditioning installations. A cross index is included 'so that information on any product can be located quickly by the user. '. This 24th edition of The Guide, like its predecessors,- provides the latest available ' comPhcd from authoritative sources for the use of the practicing engineer and . ' reflects the progress of engineering in the Heating, Ventilating, and Air Conditioning . Field. . . . GUIDE PUBLICATION COMMITTEE ! C. S. Leopold, Chairman C. F. Kayan T. F. Rockwell W. C. Bevington P. F. McDermott ' G. H. Tuttle R- S. Dill A. B. Newton W. L. Yerkes . Cyril Tasker, ex-ojficio . Carl H. Flink, Technical Secretary t vi CONTENTS Title. Page.................................................... .......................................................-........ ................................... m Preface^........... -..................................-......... -........................-..... .........................:.... .Y. Code of Ethics for Engineers--.................................................... -........................................... vin Index to Technical Data...........-.................................... -..........................-----............................ Section I. Principles * . .' Chapter 1. Terminology.................................... ..................................................................... 2*. Abbreviations and Symbols......... .......................-.......................-............. 3: Thermodynamics................ -............................................................................. 4. Fluid Flow...... ............. ;.................................................................. 5. Fundamentals of Heat Transfer.--.............................................. 6. Heat Transmission Coefficients of Building Materials............... 7. Heat Transfer Surface Coils.......... .--........................................ 8. Air Leakage..............................-..................................................... 9. Natural Ventilation...................................................................--- 10. Air Contaminants...... ......... .......................................... -.............. .11. Instruments and Measurements--................................................. Section II. Human Reaction to Atmospheric Environment 1 H 24 74 99 113. 143 107 175 184 199 * Chapter 12. Physiological Principles--............-- ----........... :............. 215 13. Air Conditioning in the Prevention and Treatment of Disease.... 241 Section III. Heating and Cooling Loads Chapter 14. Heating Load....... ........ :......... -.........................-...... ;................... 257 15. Cooling Load--...........'......-....................................................-...... 275 Section IV. Combustion and Consumption of Fuels Chapter 16. Fuels and Combustion--......................................... . 17. Automatic Fuel Burning Equipment.__ :.................. 18. Heating Boilers and Furnaces.----........................................... 19. Chimneys and Draft Calculations...................... :........... 20. Estimating Fuel Consumption for Space Heating--................... . 297 317 339 359 375 Section V. Heating Systems and Equipment . ** Chapter 21. Gravity Warm Air Systems....................................... ...... -.......... 389 22. Mechanical Warm Air Systems.............. :.................................... 399 23. Steam Heating Systems and Piping..... ......................................... 409 24. Hot Water Heating Systems and Piping....................................... 449 . . 25. Radiators and Convectors..... ....... .......... ........... ......................... 46S ` 26. Unit Heaters, Unit Vehtiiators, Unit Humidifiers......................... 477 27. Pipe, Fittings; Welding:.... ............................................ ............. 494 . 28. Pipe Insulation........................ -.............................................. ....... 513 . 29. District Heating....................................................... ........................ 529 ` ' 30. Electric Heating,............................................... ............................ 541 ' 31. Panel Heating and Radiant Heating.......... t............... ..... :...... 551' 32. Fans.......-.......... -.................................................... :....................... 567 . 33. Air Cleaning Devices.................................................................... - 581 34. Automatic Control................. ............. -................ :........................ 593 35. Motors and Motor. Controls...... ...................................1............... 607 ' 36. Unit Air Conditioners, Unit Air Coolers, AtticFans.................... 627 37. Spray Apparatus.--..........................:..................... ......................... 641 Section VI. Air Conditioning ; Chapter 38. Dehumidification by Sorbent Materials............ ....................... 663 39. Refrigeration.......... ............................................. v 40. Air Distribution..................... ............ -................... ...................... 717 N 41. Air Duct Design.--.......................................................... 739 . 42. Sound Control.................................................... * 43. Central Systems for Comfort Air Conditioning--......................... 781 44. Owning and Operating Costs...................... -............................... 812 Section VII. Special Applications . Chapter 45. Industrial Air Conditioning....... ............... ................ ................... . 46. Exhausting and Conveying Systems ..... ........ ................... 47. Drying Systems................... ............. .................. ........................... . 48. Transportation Air Conditioning.--.................I...::....:....;............. 49. Marine Heating and Ventilation... ............ ;....................... ........ 50. Hot Water Supply........................................-........ ........ --I...;..!... 823 835 850 867' 875 887 Section VIII. Installation and Testing Codes . Chapter 51. Codes and Standards..--...... ................................. :..... >............... 899 Catalog Data Section..................................................... :................. .. ..... ............... 905 Roll of Membership ' - vn 679 761 CODE of ETHICS for ENGINEERS RiP NGINEERING work has become an increasingly important factor E in the progress of civilization and in the welfare of the community. The engineering profession is held responsible for the planning, construc tion and operation of such work and is entitled to the position and authority which will enable it to discharge this responsibility and -to render effective service to humanity. rmv That the dignity of their chosen profession may be. maintained, it is the duty of all engineers to conduct themselves according to the principles of the following Code of Ethics: 1--The engineer will cany on his professional work in a spirit of fairness to employees and contractors, fidelity to clients and employers, loyalty to his country and devotion to high ideals of courtesy and personal honor. , 2--He will refrain from associating himself with or allowing the use of his name by an enterprise of questionable character. 3--He will advertise only in a dignified manner, being careful to avoid misleading statements. 4--He will regard as confidential any information obtained' by him as to the business affairs and technical methods or processes of a client or . employer. . 5--He will inform a client or employer of any business connections, in terests or affiliations which might influence his judgment or impair the disinterested quality of his services. 6--He will refrain from using any improper or questionable methods of soliciting professional work and will decline to pay or to accept com missions for securing such work. 7--He will accept compensation, financial or otherwise/ for a particular service, from one source only, except with the full knowledge and consent of all interested parties. . .. 8--He will not use unfair means to win professional advancement or to injure the chances of another engineer to secure and hold employment. 9--He will cooperate in upbuilding the engineering profession by exchang ing general information and experience with his fellow engineers and students of engineering and also by contributing to work of engineering societies, schools of applied science and the technical press' . 1()--He will interest himself in the public welfare in behalf of which he will be ready to apply his special knowledge, skill and training for the use and benefit of mankind. . ' ` ir-/ vm INDEX Heating Ventilating Air Conditioning GUIDE 1946 TECHNICAL DATA SECTION CHAPTERS 1-51 and PAGES 1-904 Cross Reference to Subjects in Chapters 1-51 Alphabetically Listed 24th EDITION v:^v.'r'-T" v .;^i V' T '- S'' '. >' .'. ' ' Heating Ventilating Air. Conditioning' Guide 19.46 INDEX HEATING VENTILATING AIR CONDITIONING GUIDE 1946 .. Technical Data Section Chapters 1-51 and Pages 1-904 - Air {continued) ' - ' : 'Abatement air pollution. 284 ' smoke, 188 ' -, , currents. 207 ' dehumidification, 663 distribution. 389, 399. 736. 868 air entrainment, 718, 722 ' . Abbreviations, ll . . . application of methods. 736 - Absolute : ., balancing system, 401, 737 . ' humidity. 5 - ' ' ' '! definitions, 717 ^ pressure, 6 " . duct approaches to outlets. 729 . temperature, 8 flow patterns, 729, 730 . zero. 1 ' , . furnace systems. 389. 399 Absorbents. 663. 666 process, 666 . temperature, pressure; concentration, 665. 667 668 induction 718,728 . mechanics, 718 . ' ' momentum theory. 718 operation of ceiling outlets. 724 outlet location. 727 . . . '' Absorbers , . outlet performance, 724, 729. 730. . . duct sound, 767 outlets, 726 ' ' outlet, 770 - railway car. 867 - plate cells. 770 - recommended velocity, 399. 400. 403. 731. 749 plenum. 769 -` * ' . return and exhaust intakes, 731 . Absorption systems, 666 room air motion, 723 -' Acceleration, 1 Acclimatization, 225 Activated-alumina,'664 . , - ' - - spread, 721 . .` standards for, 717 `-throw, 719 vanes, 720 -\ -- , '. ' ' Activated carbon, 590 '. . . ' * vertical drop and rise. 721 .' ` . Adiabatic, 1 mixing . . .. ' , . duct design, 401, 739. 748, 750 duct friction loss. 740.742 . '' -. - injected water, 58 - *` ' dust concentrations, 188. 192 - . two air streams, 57 ' . excess, 301,314 * '- - ' -saturation, 58 , ' . filter, 581 - . \ . Adsorbents, 663 ' ` process. 665 - - ,' ; temperature, pressure',concentration, 667, 668 , - Adsorption, odor, vapor,'590 ' -. ' Aerosol, 1 . flow resistance of coils, 152. 752 \ impurities, 184, 186; 582 infiltration, 167 .. causes of. 167 . ' due to wind'pressure, 167. . through walls. 168 - ' . ` ' ~' - Agitated dryer, 851; 853 - '- ' leakage; 167, 267 s': " Air ' moist, 24.26 .. - motion, 221. 723 . ' .' .- . change measurements. 209 - movement, influence of, 221 . / - . chemical vitiation of. 215 . movement, measurement of. 205 - ' . ' circulation in drying, 856 outdoor, 184,787 . classification of impurities. 184, 581 physical impurities in, 184, 218 dust. 185. 582 . > pollution, 187, 835 ' -; . . lint, 582 abatement. 188 . cleaner, 581,868 . quantity, 182, 216, 796 ' * : viscous impingement type. 583. 585 - room motion, 400, 723 . - cleaning devices, 581 , - -" . saturated, 1 ' ' classification of, 583 - - secondary, 302,334 .* - _ , ' ` ` maintenance, 588, 589 .. space conductance. 116 - "-' - performance'. 587 - ' ' standard, 1- - safety requirements, 589 ' . .. ... sterilization of, 241. 248 ' selection, 588 :1 ' . ' , ' supply and return openings, 726 r ' testing,.587 ' ` " ' ' supply opening noise, 725, 773 l vapor.adsorption,'590 ,1,- * - - combustion^ 297-; .. -1 - ' temperature, 225. 243, 261 ' - - ;V '.theoretical requirements, 216, 300 ' ", - . : conditionihg.'process, 55 , vthermodynamics of, 24 - - contaminants.'184,218 ' r unit cleaning devices. 581 . . -> l cooled;/' - ", " . condensers; 707 - 1-'.v-iU.nitconditioning, 627,-631`y ' ` . washers, 1. 641 / s . ''-i ,*v ' . : Air change method' . - ; computing infiltration, 172 ' ,,* * ^'index to Technical Data Section 1 - 1 ' 'l conditioning,. 1 &*>..^c^airplane; 872 ` automobiles in summer, ote central.systems.- 781 - ^h0^Ot3k22;2f6.2.251 ` ' ' . , , -:;._ humidity table, 826 -^industrial, 823 .__ : i . "' .atmospheric conditions required. 823 $ calculations, 832 : ,.. classification of problems, 825 general requirements, 825 r." 'owning and operating cost^8L .passenger bus in summer, 871 ;railway passenger car. 869 . v,./.relationto metabohsm. 236 ship. 875 . ^ state codes. 899 . -stoker-fired units. 318 " storage systems. 703 temperature, table. 827 .-transportation, 867 . Kf ^%v-r 'treatment of disease, 241 ?-i; *:.i'iV'unit,'627-*'-- - '^Air cooler, 627 , ' -^V.^A'./cbst * maintenance. 639 'X'-.7"- 'operation, 639 , 'units, 627. 630 ' control, 602 ^ , udeofiruoasutiungs,. v636 tFtU;J&" -.design, 636 ^ performance, 636 f:- ratings,,636 ' - .% t-f'i -: types of, 636 w-.t 'vAir requirements, 216 . Air supply, opening noises, 725, 773 k~V; ; t*Air washer, 1, 641 Airfoil fan, 567 . ' `^Airplane air conditioning, 872 . '. - rAllergic disorders, 251 S apparatus. 251 ' -.asthma symptoms, 251 hay fever symptoms, 251 - ' a&S&'.i.'limitations of air conditioning methods. 252 ^vtAlUtude. pressure and temperature, 70, 71 ^- Aluminum oxide.'664 v^-.- ,/Ainmonia, 684 ' ^/Anemometer, 1, 208 jr'-jh'1''. "deflecting vane, 208 hot wire, 208 ^/propeller, 208. - '4; '.i;.^revolving vane,-208 , . -' ''^-Anesthetics, 244 . . '^Anthracite coal, 305. 306, 307, 308 firing methods, 309 '^Apparatus dew-point, 63. 295, 790 Aspect.ratio, 722, 746 r^^AstHma'symptoms, 251 ," ^Atmosphere, standard. 70 ' . . ^Atmospheric ' ^ 'conditions for industrial processes, 826 S-SprraSure; 1. 71 . . . 3v.water coolihg equipment, 646 ' make-up water, 662 ' - sizes, 649 -. winter freezing,'662 . 'Atommng humidifiers, 644'- . -- ' .^. -'Atomizirig oil burner/ 326 ' . i'>Attenuatioh, 763, 766 . . dticts, 766 * ^-.- elbows; 766 . -f * liV-grilles to room'; 766 . ^Attic . - ' |Sfahs,'r639 -- '^CS^Iocaiion, 639' - *%4r-types. 639 ' temperature, 263 . . ... .. . .- ' . . Automatic " controls {see Controls), 401, 593 ' purpose of, 593 ' types of, 595 - - --fuel buming.eauipment, 317 ..^viscous.filter, 583 , . , ^Automobile air conditioning, 872 ' 'Axial flow fans, 567 ` . ` ' Baffle, 1. 333 ' Bare pipe beat loss, 513 . Barometer, 203 - Basement - coefficients of transmission. 139 heat loss, 139, 265 temperatures, 265 - ^ Bernoulli equation, 75 * Bin-feed stoker. 318, 320, 321 Biochemical reactions control of rate of. 831 ' . Bituminous coal, 305, 306 firing methods, 309 . Blast heater, 1 Blow 1, 718. 720 ' . Body ._ adaptation to hot conditions, 220. 222, 225 heat loss. 219. 234. 237 . odor. 217 : thermal interchanges, 219 - ;, v Boiler, boilers, 339 capacity for unit heaters, 487 -' care, 351 . . cast-iron, 339 ' cleaning steam, 350 - combustion rates, 348. ' connections, 348, 436, 437 - ' Hartford return, 436 . return, 436 '' sizing, 437 . ' steam, 436 '. . efficiency, 341, 342, 344 electric, 544 t 'erection, 349 - fittings, 348 furnace design, 341 r - gas-fired, 332 - "' selection of, 347 . u ' gas-fired units. 333, 478 :/ conversions, 332 ' ' selection of, 335 .- heating, 339 . heating surface, 2, 341 . -heat transfer rates. 341 . horsepower, 2 ' hot water supply, 340, 891, 893' ' ,, maintenance, 349 - oil-fired units, 329 - operation. 349 . ' . output. 345- ' rating codes, 341 ' selection, of. 345 . - based on heating surface and grate area, 347 . cast-iron, 346 ' estimated design load. 345 . estimated maximum load, 345 ' . . , gas-fired, 347 ' hot water supply load, .345; 888 * .' - piping tax, 345.513 ' s radiation load, 345 \ - - - steel, 346 wanning up allowance, 346 * . ' . soot, 314 , ' ... space limitations, 348 . . - -` ' ' special heating, 340 . . . '' . steel, 340 . . . ' . ` -stoker-fired units; 318 % - . ! testing codes, 341 . troubles, 350 .' - British thermal unit, 2 Bucket trap. 44 T ' Building, buildings 1 .- condensation, 139 . heat transfer through surfaces, 113 . infiltration, 167. 172, 266 ' -' intermittently heated, 271 . ' materials heat transfer through, 113, 123, 12o. 210 ^ multi-story, air leakage, 172, 173 . , ' Burner, oil, 325 Bus air conditioning,' 871, 874 ' By-pass, 2,797 . \ - '' '>~V-v'iV '-,'j''75"v-r_ '-T.- -'*- 1 *. : - _ ::'Heating ^Ventilkting-S-.Air^ Conditioning Guide 1946 iKi'^Intlex to Technical Data Section ~- ' c ;* Calcium.chloride, 663, 666. 668. Calculated heat-loss method, 375 Calone.2 . Calorific value, 297 ' ' - Carbon . . activated. 590 dioxide. 211, 300. 302. 330. 335 monoxide. 191, 194. 212, 302 Cast-iron boilers, 339 Ceiling ` . cooling unit. 636, 637 high. 262 outlets, 727 perforated. -726 unit heater. 477, 480 ' . Central air conditioning systems, 781 air quantity, 796 apparatus dew-point, 790 by-pass, 797 , classification, 781 . control, 593 cooling load. 275 ` corrosion, 510 . . design. 781 . design procedu|&, 810 equipment arrangement, 808 equipment selection, 806 evaporative cooling, 803 fan system,' 2 heating load. 790 - induction units, 802, 803 high pressure type, 803 low pressure type, 802 modifications, 783 outdoor air; 787 . pre-cooling, 804 . reheating, 798 % relation to building, 805 run-around. 804 - selection, 783 . . sensible cooling, 804 - ' use.-783 - zoning, 783, 800 . . ' . . Centrifugal compressors, 705, 706, 707 ' condensing unit, 706 fan, 567 . Chart air flow and loudness, 773 ,' ` area and'weight of rectangular ducts. 756 - - comfort. 230 computed static draft for short chimneys, 368 economical thickness.pipe insulation, 527 * - effective temperature, 229 * friction air pipes, 742' . ,. ' friction heads in black iron pipes, 451, 454 . heat emission by . ' convection from panels, 559 ' 'radiation from panels, 559, 561 heat loss ' coefficients insulated ducts, 758 from body, 235 insulated pipe, 517, 518, 519 humidity, 857 '1 - loss of pressure in elbows, 747 . Mollier diagram, 50 . *' ' permissible relative humidities for various ' transmission coefficients, 140 - . psychrometric chart, persons at rest, 228 - . rectangular equivalents of round ducts, 746 . solar intensity, 278 /* sound attenuation. 771 ." surface conductances, 122 ' ... - temperature zone map, 260! - - - thickness pipe insulation prevent sweating.- 523 ...well-water temperatures, 648 ' " Chemical laboratory hoods, 843 - reactions, 830 control of rate of, 830 vitiation of air, 215 _ Chimney, chimneys, 359 . characteristics of, 362 construction details, 370 determining sizes, 362, 373 domestic, 365 effect, 2 gas heating, 369 general considerations for. 373 performance, 365 static draft, 368 .' . . n '* . Cinders. 187. 188, 189 Circular equivalents of rectangular ducts. 741 Circulators, 450 ' Classification coals, 305, 306 cokes, 307 gas, 313 , oils, 312 ' . stokers, 317 1 " * . .. Cleaning boilers, 350 Climatic conditions, 259 ' ' Closed expansion tank. 456, 457 ' * . ' . Coal, coals - . '` . . anthracite, 305, 306, 307 . '. bituminous, 305, 306 - classification of. 305, 306 dustless treatment. 315 estimating consumption. 384 firing methods, 308, 309. 310 lignite, 305, 307 . Codes, 899 . .' . installation, 902 rating, 902 state, 899 ` testing, 902 - . , ' .' '" Coefficients of transmission, 5, 113. 125 . basement. 139 ' floor. 133. 139 wall. 139 .. . doors, 138 floors and ceilings, 132. 133 frame construction. 127, 128 ' glass block walls, 138 - '. _ masonry partitions, 131 ' masonry walls, 129. 130 -" over-all 113, 153, 755 formulas for calculating. 114 roofs, 134, 135, 136, 137 - ' skylights, 138 ' windows, 138 '' Coil, coils- . air flow resistance, 152 applications, 150 . arrangement,. 144 - construction, 144 . . direct-expansion, 147 dry cooling, 804 .. flow arrangement, 149 heat transfer surface, 143 . performance, 153, 158 ` cooling, 153 . dehumidification, 154 .graphical analysis, 158.. heating, 153 selection, 159 cooling, 160 \ . dehumidifying. 161 ' -heating. 160 ' . steam, 146 ' . - , . water, 146 .' ' '- . . '- \ * ' ;* '~ ' '#- , , .: '- .. . : '- . Coke '' . . classification of, 307 ' - -- - estimating consumption, 384 . ' "firing methods, 310 ' .. Cold therapy, 250 ' - - Color, piping systems, 22' . ^ Column dryer, 853 * , _ /JV . Xll T,.,,.. -Combustion; 297, 319 y V.C- .j o-' -analysis, 211 _ ."chamber, 331 . . - 1 / gas, 298.^300, 314, 334, 335 ' - 'heat of, 297 ' ; ' oil. 312. 329. 330 f.r .- .principles of, 297 " ' smokeless, 188,303 -y-'- Comfort . * air conditioning. I. /-j_ air conditioning systems, 781 -- chart. 230 line, 2 . '.`S . . zone, 2 . -; Commercial oil burners, 325 Compartment dryer. 853 "-Compressor, compressors, 704 ' : centrifugal. 705, 706 x reciprocating, 705 '. y refrigeration, performance of, 158 . t. steam jet, 706, 707 . .'^'.^Condensation - v;~ t V. buildings, 139 : interstitial. 139 return heating systems, 409 .* 'return pumps. 437 . -i- 'v-'J'- . , surface. 139 ' ? -Condensers; 707 ; air.cooled, 707 v'S/V' '' - design data, 650 'evaporative, 709, 710 : i r '"V- .water cooled, 708 - Condition line, 61, 295, 790 . - SU-i1 C - Conduetanee, 2. 113 air'space, 121. 116, 124 j .--building materials, 117 . -i - insulators; 117 Couductlon, 2, 99, 113 '' .drying methods, 850 . . electric heaters, 542 equation, 100 . . - steady-state solutions, 109 Conductivity, 2, 101, 113 T bat type insulation. 119, 124 jAV building boards, 119. 124 vi;,rv.buildihg construction, 127 --building materials, 117, 118, 124 homogeneous materials. 115 "insulating materials, 119,`124, 514 a.- insulation'blankets, 119 ansulators, 119, 124 loose-fill insulation, 120, 124 ^ masonry materials, 117, 124 vpiastering materials, 118, 124 - reflective insulation, 116, 124 rigid insulation, 119, 124 '''^'.^irbofing'construction, 118, 125 ^.Ui/woods, 118, 125 ` ^.Conductor, 3 . - Conduits.for piping, 531 y'Gontrol, controls airbome infection, 241 - -y'`,.ail year conditioning, 593, 783 ^ ^ application, 606 ^'.--automatic, 401. 593 ' -'fuel appliances. 325, 599 temperature, 597 basic types, 693 "'^central fan system, 593, 807 /T-- ^ all year system. 598, 599, 606 H"v*.' heating cycle, 606 ,^. coal fired, plant, 599 - ^.cooling units. 602 dehumidification, 673 r-'dehydrating equipment, 663, 850 - designation, 593 . x draft. 304' * electric heating, 547 ^electric systems, 593 ' " equipraent-for motors, 607, 611- Controls, controls (continued) fan. 578 gas burner, 600 - -gas-fired appliances. 401, 600 _ hot water supply, 599 . - humidity, railway cars, 870 _ ' individual room, 603 modulating. 604 motor, 607 ` oil burners, 599 pilot, 597 . pneumatic systems, 594 positive acting, 604 - rate of biochemical reactions,.831 . rate of chemical reactions. 830 rate of crystallization, 831 refrigeration equipment, 603 compressor type, 603 - ice cooling, 604 - vacuum refrigeration, 604 well water, 605 regain, 828 ' residential systems', 598 self-contained systems. 593 service water temperature, 894, 895 single phase motor, 622, 624 - small buildings, 601 - sound. 761 squirrel-cage motor, 620, 621 stoker, 199. 325, 600 terminology, 597 . two-position control, 593 unit heaters, 601 unit systems, 601 unit ventilators, 602 valves, 448 ' ventilator, 180 zone, 600 * - Controllers, 595functions, 595 types, 595 . Convection, 3. 99. 103 equation, 100 unit conductances. 105 . Convector, convectors, 3, 468, 470 correction factor, 472 heat emission, 468 heating effect. 473 . heating-up, 474 ratings, 471 - Converging vanes, 721 Conversion burners, 325, 333 equations, 15 ' ' - Coolers, 673, 712 Cooling, 275, 627. 663 air conditioning units, 627 atmospheric water, 646 - coil selection, 159, 163 > - , evaporative, 803 ' load. 55, 275, 788 methods, 403 performance of coils, 153, 154 ponds, 652 residential, 403 ' sensible, 804 ' spray. 646, 667, 702 ' design wet-bulb, 651 effect of wind, 654 ' - make-up water. 662 size of equipment, 650 - winter freezing. 662 systems, 403, 663, 781 tower design, 655 tower performance, 661 - units, 637 control, 602 defrosting, 638 design, 636 performance. 636 '' - ratings, 635, 638 types of, 637 Copper elbow equivalents, 453 Core area, 718 ' XIII ' Heating- Ventilating -vAir Conditioning Guide. 19 . ' Corrosion, 370, 510 ' ' 'air washers, 512 ' industrial exhaust systems, 848 pipe. 510 - ' Cost of air conditioning, 812 amortization, 812 - condenser water. 821 . first, 813 ` fixed charges, 812 heating. 822 . installed, 813 insurance. 817 maintenance. 818, 819 owning and operating, 812 . rent, 817 ' service, 818. Crack length used for computations, 169, 267 Crystallization control rate of, 831 Cylinder dryer, 853 ' *>' .. ' . ' ; . '. \ /D ' ' 'Dalton's rule,'24,65 . 'Damper, dampers, 400, 730, 738 ' Darcy formula; 76 . - Decibel. 761 * ,' Definitions, i * Defrosting, 638 - ' '' . Degree-day, 3. 375 . *' for cities, 380 '" -formula for, method, 378, 379 `.-operating unit, 385 unit fuel consumption, 382 Degree of saturation. 8, 37 Dehumidification, 643, 663 - - air conditioning units, 628 ' *. air washers, 647 ` ' . coil selection, 161 comparison of methods, 676 control, 673 definitions and methods, 663 equipment, 673 . auxiliaries, 673 ' - performance. 674 ` estimating loads, 650. 670 liquid methods, 666, 672, 673 solid methods. 671 Dehumidifying agents. 671 sorbents, 663. absorbents, 666 adsorbents, 663 Density of.air, 3, 26 ' Dew-point apparatus temperature, 54. 790 temperature, 8, 54 . Dichlorodifluororaethane, 681 . . ' ' ' ' ' Direct - . expansion coils, 147 . -fired unit heater,478, 481 indirect heating unit, 3 . - radiator, 7 ' return system, 3. 467 ' - Disc fan, 567 . _ - " Distribution of air (see Air distribution), 717 District heating, 529 . automatic control, 540 glossary of rate terms. 537 - meters, 535 . piping, 529 . conduits for, 530 ` inside, 533 , -' overhead distribution, 533 - sizes, 531' - ; tunnels, 532 - . ' types of, 531 - rates. 537 " -. . steam requirement;'384, 537 ' utilization. 539. Diverging vanes, 721*/ . . ,,. ' ' Domestic oil burners, 325 - Door, doors * v./ ` . 'coefficients of transmission,'138 - ' leakage. 171' --- - . natural ventilation, 179.. * , . - ' Down-feed ' one-pipe riser, 6 . . steam heating, 6. 42], 425, 427 , system, 3 - ... ' Draft, drafts, 3, 304 available, 360 . calculations, 359 ' ' control. 304 . .. factors, 364 . general equation. 360 . head, 3 ' natural. 176, 362 . - regulation, 304 requirements, 365, 369 . theoretical. 359 Drawing-symbols. 17 ' - Drip, drips, 3, 442 Drum dryer, 853 ' . . ' . Dry air, 1, 24 . composition, 24 - density. 24 , ' . filters, 585 . specific enthalpy, 25, 26 specific volume, 24. 26 ' velocity head. 739 volume. 26 `' Dry-bulb temperature, 8 Dry cooling coils, 804 Dry return. 7 , Dryer, dryers agitated, 853 compartment, 853 ^ cylinder, 853 drum. 853 ' festoon, 853 ' high temperature. 862 induction, 853 ' rotary, 853 spray. 853 tower. 853 tunnel, 853 - vacuum, 853 - Dryer calculations. 856 . . ' '- . . ' - Drying, 830. 850 ' calculations. 856 control. .830 . ` - biochemical reaction, 831 _ chemical reaction, 830 ' - crystallization, 831 static electricity, 832 design. 859 estimating methods, 864 factors influencing, 855 - general rules for, 855 - air circulation, 856 . humidity, 855 . temperature. 855 -humidity,-855 \ mechanism of, 852 - ' methods. 850 r - conduction, 851\ - ` - ' convection, 851 < .-estimating,-864 .. radiant heat, 850 . omissions in the cycle, 854 .- radiant. 850' ' - systems, 850 ventilation phase, 861 D^ial duct, 801 Duct, ducts, 392, 739 - ' air- velocities in, 400, 749, 838, 844 approaches to outlets, 729 attenuation, 766 . construction,' 845 - construction details. 753 . design, 748 ..' - ' - - details. 753 - dual, 801 `' < elbow friction losses,. 741 . friction-losses. 740, 742 heat loss coefficients, 757 .. ' heat losses, 755 . _ lining. 771 . measurement of velocities,' 208 - - - noise transmitted, 763 . XIV rypTiP&'rr: :;-V ' -to ~Technical Data Section ducta (continued) y --.'proportioning the losses, 747 ` ' `v, recirculating. 392, 397, 403 rectangular equivalents of round. 746 ' '. resistance. 846 - i ' side outlets, 730 - 5 fsound absorbers. 767 . ' symbols for drawing. 18, 19 < system design, 844 ' Duct sixes, 739, 747 - air velocities, 749, 838. 844 ' equal friction, 750 general rules, 747, 748 main trunk, 750 velocity method, 750 . Dust, 3.184, 582 * . ^collectors, 847 . combustible, 193 s concentrations, 188 . - r -f- determination. 210 ' ' .filters. 681. 847 * ' -nature's catcher, 184 . s- \ precipitators, 585, 586 Dynamic head, 5 US EDR (Equivalent direct radiation) 344. 346, 416. . 418; 488. 489 defined, 346. 418 ..Effective temperature (see Temperature) 8. 226 .; -.chart, 229 . . . -i ..difference, 796 - '-index, 229 ; ' -Ejector nozzles, 726 . . Elbow . - -attenuation, 766, 767 ; - copper equivalents, 453 - /-friction losses, 453, 747, 846 /.iron equivalents, 453 * Excess air, 301, 329. 334 . Exhaust opening, 731 measurement of velocities, 209 Exhaust systems, 835 .. air flow measurement, 837 classification of, 835 - collectors. 847 duct construction, 845 duct design. 844 duct velocity, 844 ducts for, 844 air velocities in, 844 - - construction, 845 design. 844 - - resistance. 846 dust filters, 847 efficiency of; 848 hoods, 836 air flow, 837 . - - - air velocities, 837, 839 axial velocity formula for, 840. chemical laboratories, 843 design principles. 836 .' - kitchen, 843 ' large open, 841 lateral exhaust, 842 low velocity systems, 841 spray booths, 842 velocity contours, 840, 841 rate of flow, 838 resistance of. 847 . suction requirements, 837 * .types of fans, 849 ' velocity requirements, 837 Expansion - factor, gases, 88, 89 of pipe, 498 ' orifice plates, 90, 91 tanks. 456 valves, 695, 710, 711 . . Electric, electrical /' tellers. 544 , ' control systems, 593 . heaters,' 542 ' - *- conduction, 542 - '* /gravity convection. 542 ' - - -radiant. 542 - . heating, 541 - . -. auxiliary, 547 - - calculating capacities. 548 ' central fan, 543' ' . control. 547 ' definitions, 541' - domestic water, 546 - > ' elements, 541 `power, problems. 549 -c./ T resistors, 541 V hot water heating. '545, 546 - '- panel heating, 551. precipitators. 585 ^.../ radiant heating,' 547. 551 resistors, 541. . heaters, 477, 481, 543 /^'Electricity, static, 832 %-fSElectronic heating, 548 Emissivity. 122, 554, 561 / ' ^factors, 104 ' .. Enclosed radiator, 475 - ^/'Enthalpy, 3, 61, 69 -jL^/Jree; 4 ' -. specific, 4, 25 ////Entrance loss, 747 //Entropy, 4, 25- ^/Equipment ^'"'arrangement. 808 *?/ '^selection,.806 - ^-^/.vibration; 776 . . ^Equivalent evaporation, 4 . '''Estimating fuel'consumption. 375 ^Eiipatheoscope,' 211, 564 ^Evaporative . /'^condensers, 709 . Ir.xooled. unit conditioners,' 629> . ./cooling, 663, 803 - - /-Evaporators, 712 ' , Mfzr.'. '. .. V' - /' ' . ' ' . - '. ' - ' - '' -F Fan, fans, 401. 567 ' arrangement of drives, 577 attic. 627, 639 location. 639, 640' types, 639 ' axial flow. 567 booster, 389 . .... centrifugal, 567 ` ' characteristic curves, 570 control, 579. ' designations. 576 efficiency, 569 - furnace system, 399, 402 motive power. 579 ' noise generated, 576, 765 performance. 567 radial flow, 567 . selection of. 575 _ - air,conditioning systems, 576 industrial exhaust systems. 848' speed, 568, 569, 575, 576 system characteristics. 573 volume control,. 578 - - Fanning formula, 76 ' .. Festoon dryer, 853 t . . Fever therapy. 248 .' ' equipment for production of, 249 Film conductance, 113 coefficient, 156, 157 '. ` Filter, filters, 399, 581 air conditioning units, 399. 639 dry air. 585 . ' . dust, 581. 847 . performance 587 ' testing 587 . , - viscous automatic, 585 - viscous impingement type, 583 .. Fittings, 494 ; pipe allowance, 411, 453 - types of, 501 . . ' FIame,299 _ Flexible mountings, 776 ^ - ... ' XV '  ~7:'-~ V>/- -I.1' ' ~'.'T'\''vV':` ^ J *CvT :-k! ''-; ' Heating1 Ventildting Air. Coiufitiorirng Guide 1946 ''Float trap,-441 / .. Floor ' ' cooling unit, 636, 637 heat transfer coefficients, 139 : unit heater, 480 ' Flow ' coefficients, orifices. 85 . compressible fluids, 79 critical. 83 . measurement orifices. 91 Pitot tube, 94 steam, 88 ,, . Flow meters, 535 Fluid flow, 74 theory, 74 . Fluid meters, 535 '' Fog, 185 Force, 4 Forced air heating system, 399, 402 circulation pipe sizes, 450 convection, 102 Free - convection, 102 ' ` - enthalpy, 4 . Friction loss ' air ducts, 739. 740 circular pipes, 76 - elbows, 746 -- ' non-circular pipes, 78 water heating. 451 water piping, 898 ' Fuel, fuels, 297 . burning equipment, 317. ' . classification, 305, 306, 307, 312, 313 consumption, 375, 379, 383, 384 load factor, 386 - maximum demands. 386 seasonal efficiency, 387 . unit consumptions, 379, 382 . Fuel oil .carbon residue. 311 classification of, 312 ' combustion of, 312 ' `grade of. 311 . maximum carbon dioxide values, 301 . theoretical air requirements, 300 ^ viscosity, 311. -' Fumes, 4, 184 ' Fundamentals heat transfer, 99 Furnace, furnaces, 4. 351, 389 ' capacity, 353, 354, 395 casings, 401 -* design, 323,355 . - efficiency, 356 fan, 4, 402 . ' - gas-fired' units, 332 . gravity systems. 389 heating surface. 355- ' heavy duty, 353 . ' mechanical warm air systems, 399 cooling methods, 403 - - cooling system, 408 - dampers, 400, 401 ducts, 401 fans, 399, 401 filters. 352. 399 - . method of designing, 402 ' motors, 352, 399 - oil-fired units, 329 . rating, 354 steel, 354 ' stoker-fired units, 318 . volume, 4, 305 - G Gage, gages . . draft, 204 - . pressure, 6, 204 Garage.ventilation, 182 Gas, gases, 185 - . ` burner controls. 600 chimneys for heating, 369 classification of. 313 combustion of, 314 estimating consumption. 383 expansion factor. 88 specific heat, 23 . . . .. ' Gaseous fuels classification of. 313 , combustion of. 314 flame temperature, 313 . maximum carbon dioxide values, 301, 313 products of combustion. 313 properties of, 313 specific gravity. 313 ' theoretical air requirements, 300, 313 . ' Gas-fired appliances, 332 boilers, 332, 339, 347 combustion process, 334 controls, 600 . ' ` conversion burners, 332. 333 furnaces, 332 ` . measurement of efficiency of combustion.'335 ratings for. 335 sizing beating plants, 335 space heaters, 333 .- Glass . - coefficient of transmission. 140 ' - solar heat transmitted. 282 ` Glass block walls - coefficient of transmission, 140 solar heat gain. 287 ' Globe thermometer. 473,.565 ` Graphical symbols for drawings, 17 duct work, 18, 19 heating, 20 , . piping, 17 ' refrigerating. 21 ' ventilating, 20 Grate area, 4 ' Gravity. - circulation pipe sizes, 454 furnace systems, 5, 389 capacity. 394 design procedure. 392; 394 typical design. 390, 392 warm air, 5, 389 steam system, 409 ' . Greek alphabet, 15 ' . _ '` .. . . '- ' ' Grille, grilles (see Registers), 391, 393, 400, 717 air supply noises, 773 . .. . attenuation, 766 ' . .. exhaust. 394, 731 locations, 727 ` -- door, 736 .... . . floor. 736 . ;- wall, 736 " ^- mechanical furnace systems. 399 ., . noises, 734. 773 railway car, 868 - *. recirculating, 391, 731 . return, 394, 731 .. selection, 774 . velocity. 731,839,840 -- Ground temperatures. 266 ' - Guarded hot plate, 210,211 Gun type oil burners, 326 - . .. .. Hangers, pipe, 500 Hay fever symptoms, 251 Heat, 5 area transmitting surface. 893 . auxiliary sources, 269 , combustion. 297 ' emission of appliances, 290 occupants, 237. 288. 552 ' . exchange measurements, 211 extended surface. 8 . XV! &&Index: to Technical Data Section. (continued) ` - 'flow resistance, 107 . flow through.roofs, 278. 279 . . -flow through walls, 279, 280, 281, 282 -- . generated by motors, 290 ' humid, 5 ' - infiltration equivalent, 266 introduced by outside air, 288 - latent,' 5, 267, 792 V: liquid, 5 ' mechanical equivalent of. 6, 15 ' methods of, transfer,114 ?- ' ` removal, natural ventilation. 177 * sensible. 5, 266, 792 * ' factor, 792. . V specific, 23 5 transfer. 99. 143. 152. 153 . - boiler rates, 341 over-all coefficients, 114, 153 .surface coils, 143, 153 ; `symbols, 113 ; ' ' through building materials, 113, 211 Heat gain, 275 ' - - appliances, 269. 289, 290 ` > components of, 275 TV .electrical heating equipment, 289 > - gas burning equipment, 289 -'glass, 286 glass blocks, 287 \-.U '-`latent. 275 i-i '-light,'290 -/'-occupants. 288 - -outside air, 288 people, 288 >V. -roof, 278 - T;,'sensible, 275 - shaded windows, 286 ..solar, 276 . `/ . -'steam heated equipment, 289 - -various sources, 289 wall, 279, 281 '' * Heat loss . bare pipe. 513 ; basement, 139 ;'-duct,'755 . ^--..".infiltration, 266 sw r c '--insulated pipe, 514 .* '.latent, 267, 792 > pipe, 513 'V residence problems, 271 . sensible, 266. 792 through ceilings and roofs,.266 /'.'-/transmission. 266, 275, 276 ` . . /Heater, heaters . / direct-fired unit. 477 /V: 'electric.-541 - .. V. solar water, 895, 896 - unit, 477 . -7 '--vertical blow unit, 479 ., m-Heating ' . ; air conditioning units, 627 . ' boilers, 339 " - .surface, 2, 341 /.coil selection, 159 / :district,.529 ' . /'domestic water by electricity, 546 .-/effect,' radiator. 473 . . /electric.541 '. /-' 'Hot'water, 545 .- %/load.-,63. 257, 728. 790 ;perfonnance of coils, 153 //radiant (see Radiant Heating), 551. 563 "/State codes, 899 j.^team systems, 409 `' /surface, 2 - ^square foot of. 8 . symbols for drawing, 20 . /systems, 781 Tup the'radiator, 474 - -.vacuum' systems, 9, 427 '- - :vapor, 9/423 . 'warm air system, 10, 389, 399 * . ` ^ water. 887 - - - [Heavy duty fan furnace, 353 1S&'" - ' - High duty humiclifiers. 645 - Hood, hoods, 836 Horsepower, boiler. 2 * - Hospital, hospitals , air conditioning in. 254 - operating rooms, 244 air conditions, 245, 247 . . reducing explosion hazard, 244 sterilization of air, 242, 248 ' ventilation'requirements, 246 Hot water boiler supply load. 345, 888 demand per fixture, 890 person. 889 - electric heating. 545 heating surface. 893 . methods of heating, 890 panel heating, 551 radiant heating, 551 solar heaters, 895 storage tank, 888 supply boilers, 340, 890 ' piping. 887 temperature control, 894, 895 . . Hot water heating systems, 5. 449 direct return system, 450 ' ` elbow equivalents. 453 . expansion tank. 456 forced circulation, 449, 465 . friction heads; 454, 455 . gravity. 454 circulation, 461 pressure heads, 456 ' installation details. 458 ' - mechanical circulators. 450 - one-pipe forced circulation, 465 - gravity circulation, 463 . - orifice friction heads, 455 ' pipe sizes, 452, 453 ` forced circulation, 450 ` gravity circulation, 454 pressure bead. 456 - reversed return system, 449, 467 systems of piping, 449 two-pipe forced 463 . T gravity 459 Human body . - adaptation, 222 .. cold conditions, 222 hot conditions. 221 '` ' heat emission, 235, 237, 552, 554 odors, 217 - temperature. 219 zone of evaporative regulation, 222 . - Humid.heat, 5 . Humidification, 404, 643. . control, 401, 596 mechanical furnace systems, 358, 404 residence requirements, 405 Humidifier, humidifiers air washer, 641, 643 atomizing, 645 high duty, 645 spray, 628, 644, 645 unit, 492 . - Humidify, 5 air conditioning units, 628 Humidistat, 5, 596 - *' . Humidity, 5 . absolute, 5 * '. drying, 855 - . influence of, 227 - - . measurement of. 209, 855 . nurseries for premature infants, 247 , permissible relative. 140 ' ' - ratio, 5,25 - - ' relative. 5, 24 ' Hydraulic radius, 104 . - Hygrostat, 5, 596 - XVli . '- , ' Healing VentilatingAir Conditioning Guide 1946 ';\v . ./ i .. . Ice systems, 703- Impulse trap, <442 . - Inch of water, 5 Induction dryer, 853 . Induction units, 802 high pressure types, 803 low pressure types, 802 ' - Industrial ' - air conditioning, 823 exhaust systems (see Exhaust sysietns), 835 , humidities. 826 ' process, 826 . temperatures, 826 Infiltration causes, 167 - due to wind pressure, 167 ` heat equivalent, 267 heat losses, 266 latent, 267 sensible, 266 temperature difference, 172 throughoutside doors. 171, 172 through walls, 168 through windows, 168, 169, 170. 171 Inflammability. 194 Inside temperature, 261 Instruments, 199 Insulation, 5, 513 ^ duct, 755. 885 " economical pipe thickness, 525, 526 gravity furnace duct, 390. 391 . low temperature pipe, 523 pipes to prevent freezing, 524. 525 ship, 884 - - underground pipe, 526 Intermittently heated buildings, 271 Interstitial condensation, 139, 140' Ionization, 218 . . .' Iron elbow equivaJents. 453 Isobaric, 5 Isothermal. 5 . J-K-L Johits, duct, 740, 753, 754, 755 Kata-thermometer, 207. 473 -Latent heat, 267, 793 loss, 267 .- Laws'of thermodynamics, 9 Leaders, 389 ' Leakage'of air, 167 door. 171, 172 : .window, 168, 169, 170, 171 `- Light beat gain, 290' . . Lignite. 300, 305, 306, 307 . Lint, 582^ . ' Liquid. ` ' absorbents, 666 heat of. ,5 ' '. Lithium chloride. 666, 667, 669, 670 Load cooling, 60, 275. 788 . design. 5. 345. heating 32,257. 728,790 . maximum, 5, 345' - .. refrigeration, 275 . - . - . -> - ` ' ; ' M Machine vibration, 776 . Manometer, 6,204 ` .. . Marine heating and ventilation, 875 7 factors affecting design, 877 i general considerations, 875 - - insulation' of hull. 884 . -- ' ducts.'885 . : Marine heating and ventilation (continued) requirements for space, 880 - ' . bakery. 883 ` -- bath, 883 cargo, 884 food handling, 883 galley. 883 laundry, 883 - living, 882 shower. 883 - storeroom. 884 toilets, 883 . washroom, 883 Mass, 6 Mb, 459 Mbh. 459 ' Mean radiant temperature. 551, 559: - Mechanical circulators, 450 draft, 359 towers, 654 equivalent of beat. 6 furnace systems. 399 air distribution, 399 control, 401 - cooling methods, 403 dampers, 400 design, 402 .ducts, 401 - fans, 352 ' filters, 352 heavy duty, 353 humidification. 353 . methods of design, 402 motors, 352 -. registers, 399 refrigeration. 679 return heating system, 409 - stokers, 318 . . Meter, meters, 535 condensation. 535 differential, 535 flow, 535 fluid. 535 Nicholls' heat. 211 : orifice, 535 plug, 535 . velocity, 535 ' venturi. 207 . . Metering liquids. 91 Metering steam. 88 Methyl chloride, 680, 683 Micromanometers. 205 Micron, 6 \ Mist, 185 Moist air. 24 '* ' 8aturation.25.-37 volume, 25 .. -' .' . -. .. . . Moisture, 828, 850 * content, 828 - Iqss per person, 223, 233, 237 ' ` permeability. 291 . - regain, 825, 829 Mol, 6 Moilier diagram. 50 . Monofluorotrichioromethane, 686 Motor,' motors, 352, 607 ' adjustable speed, 612- .. - alternating current. 614 . capacitor type. 619 ' classification, 608 ' compound wound, 610 . constant' speed, 611 - ' control,.611. 621, 623, 624 control-equipment for, 607, 611. 621 ; direct current, 610 . ` . electric, 607 . - .^enclosures, 625 - ''.gear, 625 :. ' ' .' ` . glossary, 625 . heat generated by. 290 ' polyphase; 614. ' ; rating; 607 '- : K^Iniiex to Technical Data Section . Motor, mown'(continued) f fv-;*.* repulsion induction. 619 V- .series wound, 611 m ' shunt wound. 610 " single phase, 619. 620 ' &v:r ' specifications, 613, 616, 620, 622 speed characteristics. 612, 614. 617 split phase, 620 .. squirrel cage induction. 621. 623 ' synchronous, 615 wound rotor, 615. 622 u Multiblade fans, 573 N - Natural draft, 359 towers. 653 .^Natural ventilation, 175 general rules. 181 heat, removal, 177 -'~-Nolse, noises - ` f-; air conditioning system, 761 V: . air supply opening. 773 - . .t;.` apparatus for measuring, 762 ^*v-- % v|A } " controlling vibration, 776 ' `-'.cross transmission between rooms, 775 ' ' design room level. 764 duct sound absorbers, 767 ir -7 ' duct system attenuation. 766 jr- [ generated by fans, 765 - kinds of, 763 ' Ievels,-764 ' - - through building construction. 776 1 transmitted through ducts, 763 7; c - , unit of measurement, 761 > ; Nozzle flow, 81, 84 Nozzle installation, 96 ' _7Nuraerles for premature infants, 247 ^ air conditioning equipment. 248 air conditioning requirements, 247 n* - O. ' M' '. r"-Occlusion of solar radiation, 189 Odors., 189. 215, 217 ' human body. 216 .-Oil, oils .- . classification of, 312 ' combustion of. 312 - rr.estimating consumption, 375 . . '-Oil burners, 325 ' - . boiler settings. 331 ''v - combustion adjustments. 330 . ~ ' combustion process, 329 Af.'-'y .controls, 332. 599. .' - -r--.* 'domestic. 325 ` - furnace design, 331 ^-^7 ^ measurement of efficiency of combustion, 331 " :mechanical draft. 325 . .jjoperating requirements. 329 . s-T^rOne-pipe system, 419 gravity air-vent. 419 .. .sy^ir'hot,water, 6,`449 ' steam. 6.419 . ``WV-i^.iPPly riser. 6 -.- ''-\"SrT ..unit heater connection, 444, 485 vapor, 423 - ' ' . openings air.supply noises. 773 'stacks,181 ... - types of, 179 - " s'_> doors, 179 ' . . ''roof ventilators, 179, 180 , yiVt'skylights, 179 ' ^-windows, 179 -- . ' m'Opaating rooms, 244 ' '`0^-conditions,-246 ' . : " V reducing explosion hazard,I244 .- ^sterilization of air in. 246. 248 ^Operative temperature. 221, 551 Orifice-.... ' '^discharge; 88 ` :i;flow. 81. 84 . ^Keating systems, 430 ' .' . .Orsat'apparatus,-211 ` . .. .Outdoor' air, 787 ` `. . Outlet, outlets .air supply noises,-773 "ceiling. 727 . . duct approaches, 729 sound absorbers, 767 . Outlet locations. 727 heating load, 728 Outside temperature, 257, 258 Overhead distribution. 6. 533, 887 Overhead system, 533 . Oxygen chambers, 253 . tents, 252 therapy, 252 Ozone, 218 p Panel heating, 551 calculation principles, 556, 563 electric, 556 , hot water, 555 ` steam, 556 . warm air, 554 . . Panel radiator, 6 . Particle size chart, 186 Per cent of saturation, 37 Perforated ceilings, 727 Perforated outlets, 726 Phon,`761 Physical impurities in air, 218 . ' ! ' .' ` - . , `' ', Physiological principles, 215, 553 Pilot controls, 597 ' Pipe coils. 469 .. heat emission, 469 '. wall, 469 ` `Pipe, piping, 424, 494 . -* capacity. 412. 414, 415, 432 - coil connections! 446 '- ` commercial dimensions, 495. 496, 497 ` conduits for. 531 . .1 connection to heating units, 444 `. .' corrosion, 510 design, hot water system. 459 v direct return, 467 , v` forded circulation, 460 . gravity, 459 . . .' one-pipe forced circulation, 465 one-pipe gravity circulation. 463 * . reversed return, 467 - two-pipe forced circulation, 463 ' - two-pipe gravity circulation, 461 ' . economical thickness insulation 525, -526 expansion. 498 ' ' .. fittings, 495 ' ' fitting equivalent, 414 .- - flexibility, 498 - . - hangers, 500 . heat losses, 513 . . ' hot water heating systems, 449 ` inside, 533 insulation prevent freezing, 524, 525 . leader sizes. 392, 393 . ' ' low temperature insulation. 523 . materials, 494 `- overhead distribution, 425, 427, 533 -. ' proportioning wall stacks, 393, 402 . . recirculating grilles, 394, 397 . . ` - refrigerant sizes. 695, 696, 697, 698 ' register selections, 390, 393 , return connection, cold air, 392 ' return ducts, 394, 397 . sizes, 411 '` high pressure steam. 433 . . hot water forced circulation, 450 ' hot water gravity circulation, 454 indirect heating units. 418 - -. maximum velocity, 413 . one pipe riser, 415 ' - orifice systems, 430 :` pressure drop, 411 . ` ' sub-atmospheric systems 429 . ` tables for. 412, 413, 415, 416, 417, 423, 432 - . two-pipe riser. 415 two-pipe vapor systems,' 424 _ . ' vacuum systems, 427 .r - water supply systems, 887, 897, 898 ` ' 'Heatings Ventilating. Air Conditioning Guide 1946' Tnkex to Technical Data Section r Pipe, piping Ccontinued) * steam distribution. 529 ' -. steam heating systems. .409 . supports. 500 . . symbols for drawing. 17 - tax. 345 . thread connections. 500. 503 threads. 500 - tunnels. 532 underground insulation. 526. 531 unit heater connections. 485. 486 water supply. 887, 897. 898 Pitot tubes. 94, 206 ' Plate cell. 770 Plenum absorbers. 769 Plenum chamber, 6 Pneumatic control systems. 594 Pollution of air, 184 Polyphase motors, 614' Ponds, 652 Potentiometer, 6 Power. 6 ' Precipitators. 585 Pre-cooling, 804 . Premature infant nurseries. 247 --Pressure. absolute, 6 ' - atmospheric, 1 - gages, 204 .. loss, water supply piping. 898 measurement, 203 ' barometer. 203 . regulators, 435, 533 static. 7 taps, 87 total. 7 - ' vapor. 7 . velocity. 7 - . Prime surface (see Healing surface). 8 , Propeller fan, 567 '. Psychrometer, 7 ' ' Psychrometric chart, 228 Pump, pumps ` ' ' - condensation return, 437 -' mechanical circulators, 450 vacuum heating, 438, 439 . controls, 440 piston displacement, 440 Pyrometer. 7. 203 - optical. 203 radiation, 203 . - Q-R Radial flow fan, 567, 572 'Radiant drying, 548 ' ' Radiant heating, 551 . application methods, 554 ' calculation principles, 563 - ' control. 565 ' ' - detailed computation method, 556 r electric, 548 - hot water, 555, 562 '* mean radiant temperature, 551, 559 measurement of, 564 objective. 553 . operative temperature. 551, 565 steam, 556 . warm air, 555 Radiation, 7 ' angle factor. 103 equation, 103 * -load, 345 . .' . .. Radiator, radiators, 7, 468 '` . codes, 471, 903 . " concealed. 470 - . ' - connections, 444, 445 - correction factor. 472" -.-.direct,'7 . :- . effect of paint, 473 - . Radiator, radiators (continued) enclosed, 475. gas-fired. 334 heat emission of. 468 heating effect, 473 v heating up, 474 ' output of, 468 panel, 6 ratings, 468, 471 recessed. 7, 475 , tube. 468 types of. 468 warm air, 334 , _ ". ' Railway air conditioning, 867 air distribution, 867 humidity control, 870 summer systems, 869 temperature control, 870 ventilation, 867 winter systems, 869 ' Reciprocating compressors, 705 . Recooling, 784, 800 Rectangular, duct equivalents, 741, 744 Reducing valves, 434, 435, 532 . Reflective insulation, 116, 123 - Refrigerant, refrigerants, 7, 679, 681 ammonia. 684 carbon dioxide. 685 dichlorodifluoromethane, 681 feeds, 147, 148 . methyl chloride, 683 . monochlorodifluoromethane. 682 - monofluorotrichloromethane. 686 pipe sizes, 695 - water, 686 _ ' ` ' Refrigeration, 679 . - absorption systems, 700 - compression systems, 706 ' condensers (see Condensers). 707 control, 603 equipment selection. 713 expansion valves, 695. 710 ice systems, 702 . load, 295 mechanical. 679 reverse cycle, 547, 703 storage systems, 703 symbols for drawing, 17 ton of, 7 day of. 7 - types of compressors (see Compressors). 704 Regain, 825, 828 control of, 825 *' hygroscopic materials. 829 .. . Register, registers, (see Grilles). 391, 393,400,717 air supply noises. 773 -- - mechanical furnace systems. 399 noises, 725, 734, 774 ' railway car, 868 selection. 390,397,399 . - Reheat, 800 '' Reheating, 798 Relative humidity, 5, 67 - measurement of, 209 - Repulsion induction motors, 619 - ' - Residence ' . control systems, 598 air conditioning. 599 ' . coal-fired heating plant, 599 - .. domestichot water supply, 599 cooling methods. 405 '` : gravity furnace systems, 389 heat loss problems, 271 hot water heating system, 449 ; - * - . mechanical.furnace system, 399 ' , steam heating system, 409 .' Resistance thermometers, 202 - '' . Resistors, 541 ' ' Return - -. '- . grille, 391 - mains. 8 . - . '. ' ' - , openings, 392,400.731 . - '' - Reverse cycle refrigeration, 547, 703 ' , Reversed return system. 8,450 " '. . Roof, roofs - ; -heat flow through, 279 . time lag of solar radiation, 280 ventilators, 180 -Room ' air motion, 723 * ` ' control, 595, 601 ' cross transmission, noise. 775 latent heat, 792, 793 - noise level. 764 - operating, 241___ sensible heat. 792, 793 Rotary diyer, 853 'Rotary oil burner. 327 Run-around system, 804 ' . - - . . ,, .. - S -Saturated air, 1,37 Saturation,. 8 degree of. 8,37 - pressure, 6 ' . . Secondary air, 302, 303, 314 Sectional boiler, 339 Self-contained ` ' control systems, 593 _ : -humidifiers, 645 . unit conditioner, 627 .'Sensible cooling, 804 Sensible heat, 792, 793 ' - factor, 792, 793 . gain, 288, 289. 290, 295 ,loss.'266 ` v.Sheet metal gages. 754, 755 ' . . - ' . . VShip air conditioning (see Marine). 875 . rheating, 877 ` ventilation, 877 " Shunt wound motors, 610 ' Silica gel, 664, 665 Silicon dioxide, 664 .Single phase motors, 619 ' Slotted outlets, 726 ' -Smoke. 8, 185.1 - 'abatement,-188 - . density measurements, 212 ' ? Smokeless arch, 8 -y Smokeless combustion, 188; 303 _ . /-Solar heat . ,,_' through shaded windows, 286 V. ' time .lag, 280 - transmission of, 276 ' -J.< transmitted through glass, 282 ... transmitted through walls, 280 ^`' Solar radiation ;. absorption of, 189 against walls, 279 Solar water heater, 895 %SooV, 314 ` % '.Sorbents, 663 - absorbents, 666 - '.adsorbents, 663 . . . . _:Sound (see Noise) % - absorbers, 767 ' IV.* attenuation, 766, 767 .< S control, 761 . . " . cross transmission between-rooms, 775 general problem. 762 , duct absorbers, 767 .' . levels, 764 -. - outlet absorbers, 770 '* ' Space heaters, 333 Specific enthalpy, 4, 24, 25,-68 ^ ' ~ -dry air, 25, 52 '> -/ water vapor, 25 --' gravity, 4 -y.:- heat, 5 ' . ' ' /gases,' 23 liquids, 23 ' ' -T -/solids, 23 Tg_.` 'vapors,-23 ..--.volume, 10 , . air.25,26 y. < water vapor, 38 . Split system, 8 Splitter dampers, 401 - . Spray , . booths, 842 . ' cooling, 647 cooling ponds, 652 cooling towers, 653 distribution, 645 dryer, 853 equipment, 644 generation, 644 humidifiers, 645 type unit, 644 unit air conditioner, 628 - -' Spread, air distribution, 721 Square foot of heating surface, 8 Squeeze dampers, 401 Squirrel-cage induction motor, 619 Stack, stacks, 181 height, 8 wall, 389 . Standard, standards, 899 " air distribution, 770 atmosphere, 70 State codes ` air conditioning, 899 ` -heating, 899 ventilating, 899 - Standard air, 1 Static .- electricity elimination, 832 pressure, 7 ' control. 596 . Steady flow, energy equation. 68 enthalpy. 69 gravitational energy, 69 heat and shaft work. 69 kinetic energy, 68 Steam, 8 ' coils, 146 .. distribution piping, 529 ' estimating consumption, 384 flow, 411..435 heated equipment, 289 heating systems. 409 condensation return, 409 ' corrosion, 510 - down-feed two-pipe vapor, 425 gravity one-pipe air-vent. 419 gravity return, 409. . high pressure steam, 433 mechanical return, 409 one-pipe vapor, 423 - orifice, 431 piping for.-409 sub-atmospheric, 429 " two-pipe vapor, 424 - vacuum, 427 jet type of compressor, 696, 714 panel heating, 551 pipe capacities, 412-417, 432 ` radiant heating, 551 requirements, 537 ' , runout, 421 ' superheated, 8 traps, 440 ' Steel boilers, 340 Sterilization of.air, 242 Stoker, stokers, 317 classification of, 317 - combustion adjustments, 323 combustion process, 319 . ' controls, 325, 600 ' furnace design, 323 mechanical, 317 - . overfeed flat grate, 319 overfeed inclined grate, 319, 322 sizing and ratings, 324 ' . underfeed, 318 rear cleaning, 319 , side cleaning. 319 Storage refrigeration system, 703 - ^ -___ t___ _ '_______,, 400 XX U "`'Heating Ventilating.- Air- . Conditioning Guide 1946 `^''Summer air conditioning system. 399 Tables (continued) ' . '. ,. r.s 'Summer comfort. 230 * . .- Superheated steam, 8 y-;"" Supply mains, 8 - 'heat transmission, 127, 514, 516, 522, 893 - ' coefficients, 127 ~~ hot water demand, 889.890 - ' hot water pipe sizes, 452, 453 " Supply openings, 399, 726 humidities, industrial air conditioning. 826 -v ; measurement of velocities. 208 infiltration through outside doors. 171 * ` * .types of. 726 infiltration through .walls, 168 'V Supports, pipe. 500 infiltration through windows, 170 - inflammability, gases, 194 `' .' Surface -' inside temperatures, 261 ' condensation. 139 . insulation factors, 520 ' conductance, 2, 113. 120 iron elbow equivalents, 453 -' . coefficients, 121 maximum allowable concentrations external pipe, 515 ' dusts, fumes, mists, 192 ' - _ . ' heating, 8 .. dusts. 192 ' ' . extended. 8 metabolic rate, 237 . ` temperature.- 202. 357 . minimum outdoor air requirements to remove Suspended unit heater, 480 . odors,-217 * - - moisture content for materials, 826, 829 . Symbols, 11. 12 noise levels, 764 ' ' ' / . ductwork, 18, 19 particulate matter, size, 186 - v ' for drawings, 17 . permeability to vapor, 291 '- ' .heat transfer, 113 physiological response . -- - - heating. 20 to gases and vapors, 191 piping. 17 to heat, 223 ' * . refrigerating. 21 pipe dimensions, 495. 496, 497 - . ventilating, 20 pressure loss ' refrigerant line. 697 /-V T - return intake, 731 properties of ' Tables/ . ammonia. 684 _ . : ' air changes, 172 - carbon dioxide, 685 * ,. air conditioning temperatures and humidities, 82G dichlorodifluoromethane, 681 - ' \ air requirements, 217. ` ' fueloil, 311 .. , - air. volume of, 26 - gaseous fuels. 313 .- > ' altitude, pressure and temperature. 71 . lithium chloride, 669 . : anthracite, size. 307 ' methyl chloride, 683 area flanged fittings, 516 -_ moist air, 26 - ._ . - t attenuation between grille and room, 767 - monofluorotrichloromethane. 686 - ' . . formula, lining board, 770 ` - water. 38.686 ' .. .. in straight .ducts, 765, .< . of elbows, 766 ' radiation; black body, 107 radiation factors, 106 - -' _ ; average maximum water main temperatures, 646 radiator sizes, 469 .. / , boiler ratings, 342. 343 regain of hygroscopic materials. 829 . - - . capacity constants relation between metabolic rate and activity, 237 . - - blow-throUgh unit heaters. 482 . requirements for fuel oil, 311 '- . ' draw-through unit heaters, 483 return pipe capacities, 416.-417, 433 - ' . . carbon dioxide maximum, 302 screen mesh, 187 '- - /; ' ceiling temperature, 262 '- sheet metal gages for ducts, 755, 757 . ' circular equivalents of rectangular ducts, 743 ship practice, 881 - - ' classification of coals, 305 smoke chart numbers, 212 ' - solar radiation, 280. 283, 284. 285, 286 . motors. 608 ' specific heat of .compressible fluids. 80 . climatic conditions, 258, 276, 277.. *' . ' coal.classification, 305 - !y - > ' combustible elements and compounds, 298 specific heat of solids, liquids, gases. 23 State codes, standards or laws air conditioning. 899 . ' - ' ,, <' -. . combustion air requirements, 300 -' heating. 899 . . . . . ..combustion rates, 348 . ventilating. 899 . - . ' . ' ' conductivity materials. 101. 117, 516 . steady-state conduction problems. 109 :y > cooling coil arrangements, 161 . - steam consumption of buildings, 386 copper elbow equivalents, 453 ` . steam pipe capacities, 412, 413, 415,-432 ' - . .corrosion resistance, 848 . r temperatures, industrial air. conditioning. S26 ) > >degree-days for cities. 380 - . . theoretical air'requirements, 300 . ' --'".design dry- and wet-bulb temperatures. 270. 277 thermal conductivity, 101,109 . '- ' _ -; _ ' draft requirements of appliances, 369 thermal convection conductance, 105 ' ` . .. dryers for evaporation of water, 853 thermodynamic properties -' V .duct attenuation, 765- - moist air, 26 . ' ' ;'1 dust concentration, 188, 192 ' . water, 38 ``. ' .- . elbow attenuation, 766 unit fuel consumption, 382 - '. - emissivity factors. 106 ' velocity.' return intake, 731 . , end reflection, 769 `' .water; properties^ .' ' ' environmental conditions, limits, 225 weight of air, 26 . ' .' 1 exhaust pipes for machines. 838 - . factors influencing drying. 855. ' Tank/ tanks *, * ' . v - ' fitting dimensions, 502-508 . expansion, 456 ' ._ flame temperature data.-299 . " /, flammability of gases and vapors. 194 Tax, pipe, 344 - . . " 1 .. ' - free convectlon, 102 ' factors, 103 ; - fuel oil properties, 311 . . ` ' ' fumes, concentration, 192 : - - gaseous fuel properties, 313 heat gain - : ' , appliances, 289 '` - : glass blocks, 287 _ insulated cold pipes, 522 - '' :i ' heat, loss . *. .bare copper pipe.-514 bare steel pipe. 514 ' --- Temperature, temperatures absolute. 8 - . `. . attic, 263 ' . automatic control, 593 . basement, 265 . - .' heated,'265 .. unheated, 265 ... . " control for railway passenger cars. .870 - control service water, 894 ` - ' design wet-bulb, 651 _ ' . - design zone map.' 260 ' " ' . .. 'dew-point, 54 - ' ' ' . ' ... r ` VlnAex to Technical Data Section ... .. ^-Temperature, temperatures (continued) drtmlb,8 .' - tfieSfve8^. 226, 261. 551 ' ' ground, 265 - J',- -hazards, 222 'fii industrial. 823 - '*' inside. 261 - ceilings, high. 262 fr* - oroper level. 261 . mea0 radiant, 231, 551, 559 measurement, 199 thermocouple. 201 - - thermometers, 199 , -A.. - operative. 551 - -outside, 257 ^sutrhfearcmeo,d2y0n2a.m3i5c7wet-.b.u.lb. 53 V -'unheated spaces. 264 j water main, 646 . _ wet-bulb, 8 - ' 1 -'' Terminology. 1 /Test methods, 901 . s-fl' Therapy cold, 250 . fever, 248 _ " oxygen, 252 , .. fe AThermal . conductance. 113 ` conduction equation, 1W - conductivity, 113 - '."convection, 101 .' h `-convectionequaUon. 101 . 'Jr. expansion of pipe, 498 . .v*/. interchanges' of body.- 219 ..radiation equation, 103 ' resistance, 7. 113 . ^^Sy^tate conduction problems. 109 -- . transmittance. 266 : unit conductances for convection, 10j _>/'Thermocouples, 201 ' .-?- ThermPdynamic9. 24 air and water mixture, 24 ~ laws of, 9 wet-bulb temperature. 53, 643. ^' Thermometers, 199 . I'.i .alcohol,-199 ' . - 'jidry-bulb, 227 globe. 211, 565 . Kata. 207, 211 .mercurial. 199 - . --'resistance. 202 .* vstem correction, 199 , _ . wet-bulb. 210, 227 -. . ^/'Thermostat, 9, 595 VV- '',ro0ra. 595 - . r -wThermostatic trap, 441 . - ?Y*-Tilting trap, 442 -' d^Time' lag through walls and roofs. 280 ^vTon ofrefrigeration, 7 , - Total heat, 5 ' /'^'Total'pressure, 7 .. r;/'Tower, towers . X^y'oooling.' design, 655 cooling, performance, 661 mechanical draft. 654 -^k^'^iiatural draft, 653 ''K'C- spray cooling, 653 -.--Tower dryer, 851 ' ^T>Trari8missioa ' , `/L'*'1?''coefficient, 107, 114 V\- * Heat losses. 266 ' - ``.normal heat, 275, 276 ., . -solar heat, 276 . . . ^. Transmittance, thermal; 9 - ^Trahsportation air conditioning, 867 /`Trap, traps, 440. ^automatic retum,-.442 v . bucket. 441 . ::>float,'441 * ->-impulse..442 2stun, 8,'.' _ ' . . __ '"thermostatic, 441 ' L^' ^tilUng, 442 - ' " . ' . Traveling-grate stoker, 321 Treatment of disease, 241 Tube radiator, 7 Tunnel dryer. 853 Tunnels, pipe. 532 Turning vane,- 730 ' Two-pipe system, 9 u Ultra-violet right, 189, 218. 243 Underfeed stoker, 318 Underground pipe insulation, 526 Unheated space temperatures, 264 Unit, unira, 9 air cleaners, 581 air conditioners. 627 application, 633 cooling, 628 dehumidifying, 628 filtering, 628 - heating, 627 humidifying, 628 - ratings, 635 types of. 629 ventilating, 629 air coolers, 636 defrosting. 638 design. 636 performance, 636 ratings. 638 types of, 637.. air filters, 581 / British thermal; 2 direct-indirect heating, 9 . fuel consumption, 382 heaters, 477 .' application. 478 ` boiler capacity. 487 capacity factors. 482. 483 control. 601 . direct-fired, 477 electric, 477, 478. 481. 543 piping connections, 485 ratings. 479 suspended. 480 temperatures, 481 . types of. `477 humidifiers, 492 - . - types of. 492 induction. 802 - noise measurement, 762 systems, 627 , . economics, 639 - ventilators, 487 ' air exhaust vents. 491 applications. 490 capacity, 489 ' _ control, 602 . ratings, 487 window, 492 . ' v Vacuum cooling unit. 700 . heating pumps, 438 control. 440 piston'displacement. 440 heating systems. 9, 427 down-feed, 427 unit beater connection, 485, 486 Vacuum dryer, 853 Valve, valves, 508 . angle. 448 automatic, 509 - check. 509 control, 448 ` expansion,'*695,'710 gate, 508 ' . .. 'XX1U ; treating ' Ventilating Air Conditionin'! C.^ 1946 -. --Vane, vanes,- 721 Varied outlets; 726 -Vapor,'vapors, 185 heating system, 9 - - unit heater connection 485 pressure, 7 Vaporizing oil burner, 328 ' Velocity, 9 ' exhaust intakes. 731, 840 hood, 840 method duct design, 748 pressure. 7 return grilles, 400, 731 warm air duct, 400 ventilation, 10 air conditioning units 627 ' dairy barn. 182 garage. 182 hospitals, 246, 254 ' natural, 175 . general rules. 181 passenger bus in summer, 871 railway passenger car, 867 ' ship. 877, 881 State codes, 899 ' symbols for drawings, 17 systems, 781 wind forces, 175 - Ventilator, ventilators control, 180 roof. 179. 180 unit, 487 . , control, 602 . - -window, 492 Vertical blow unit heater, 477 Vertical openings, 173 sealing of. 173 Vibration machine, 776 Viscous filters. 583 - -automatic. 585 impingement, 583 Vitiation of air,`215 Volume control. 801 furnace, 312 specific. 10 ' w Wall, walls . heat flow' through, 281. 282 fen tl^3frucoefficients. 113. 127r13I. 'infiltration through. 168 time lag of solar radiation, 280 ` Warm Air . , gravity heating system. 389 . combination carrying capacity, 393 design procedure, 392, 394 furnace capacity. 354. 397 installation practice, 389. 398 standardized combinations, 392 mechanical heating system, 399 . automatic control, 401 cooling methods, 403 ' cooling system design, 408 dampers, 400 design procedure, 402, 748 duct velocities, 749 ducts, 739 fans. 352, 399, 401. 402. 408 filters, 352, 399. 402 . Warm Air (continued) furnace; 351, 399 heavy duty, 353 selection, 355 humidification, 358 motors, 352 panel heating, 555 radiant heating, 555 radiators, 334 Washer, washers, 641 air. 1, 641 Water cooUng equipment. 647 control temperature service, 894 cooled condenser, 708 . unit conditioning, 631 corrosion treatment, 510 heater coal-fired, 894 solar, 895 heating, 887 make-up. 662 maximum, main'temperature 646 properties of, 686 supply piping, 887 ' ' arrangement. 888 - thermodynamic properties of, 37 well, temperatures, 648 Water vapor, 24. 66 - saturation pressure, 25 . specific enthalpy, 4 specific volume, 10, 25' - Welding, 494, 505, 506 Wet-bulb temperature (see Temperature), 8, 651 Wet return, 7. 416, 422 -. Win'd, winds forces, 175 ' ' due to stack effect. 176 natural draft equipment, 654 selection of, velocity, 268 Window, windows confidents of transmission, 138 leakage, 167 - solar radiation through, 282 283 ventilators. 492 ' Winter '- - air conditioning system. 781 comfort zone, 227. 228, 230 ' freezing, equipment, 662 - Wound rotor motor, 615 Wrought-iron pipe, 494 . Wrought-steel pipe, 494 X-Y-Z . Y 781 rOUnd alr conditioning system, 604, 605.'. Zone"control, 600 Zone of evaporative regulation, 222 Zoning, 800 ' ' . control^ 600 .' dual duct, 801 multiple fans, 801 ' recooling, 800 ' reheat, 800 . separate equipment, 800 ` volume control. 801. '. - -* ' - - * -. ' " .. ' . ' Glossary of Physical and Heating, Ventilating, Refrig& and Air Conditioning Terms Used in the Text Absolute Zero: The zero from which absolute temperature is reckoned. Ap proximately -- 273.2 C or --459.8 F. . Absorbent: A material which has the ability to take up water vapor but which changes physically, chemically, or both, during the cycle. . Absorption: A process in which a fluid, liquid or gaseous, passes into the inter stices of a porous substance and is held there by absorption or capillarity (G.P.) a Acceleration: The time rate of change of velocity i.e:, the derivative of velocity with respect to time.- In the cgs system the unit of acceleration is the centimeter per j(second) (second), in the fps system the unit is the foot per (second) (second) o = Acceleration Due to Gravity: The rate of gain in velocity of a freely falling body, the value of which varies with latitude and elevation. The international gravity standard has the value of 980.665 cm per (second) (second) or 32.174 ft per (second) (second) which is the actual value of this acceleration at sea level and about 45 deg latitude. Adiabatic: An adjective descriptive of a process in which no heat is added to or . extracted from the system executing the process. . Adsorbent: A material which has the ability to hold water or other vapors on its internal surfaces without itself being permanently changed physically or chemically. Adsorption: A term applied to the .phenomena connected with the adherence of molecules of a foreign substance to the surface of a solid or a liquid (G.P.). Aerosol: An assemblage of small particles, solid or liquid, suspended in air. The diameters- of the particles may vary from 100 microns down to 0.01 micron or less . e.g. dust, fog, smoke. . `, . Air Cleaner: A device designed for the purpose of removing air-borne impurities such as dusts,, gases, vapors, fumes and smokes. (Air cleaners, include air washers, air. filters, electrostatic precipitators and charcoal filters.) ' Air Conditioning: The simultaneous control of all or at least the first three of those factors affecting-both the physical and chemical conditions of the atmosphere, within any structure. These factors include temperature, humidity, motion, distribution, dust, bacteria, odors and toxic gases, most of which affect in greater or lesser degree human health or comfort. (See Comfort Air Conditioning.)- - Air, Dry: In psychrometry, air unmixed with, or containing no, water vapor. Air, Saturated: A mixture of dry air and saturated water vapor, all at the same dry-bulb temperature. . Air, Standard; Air weighing 0.075 lb percubic foot. . This is the density at standard atmospheric pressure (29.921 in. Hg) of dry air at 69.41 F and of saturated air at 60.12 F` Air Washer: An enclosure in which air is drawn or forced through a spray of water in order to cleanse, humidify, or dehumidify the air. - Anemometer: An instrument for measuring the velocity of a fluid. Aspect Ratio: In air distribution outlets the ratio of the length of the core of a grille, face or register to the width. In rectangular ducts the ratio of the width to the depth. Atmospheric Pressure: The pressure due to the weight of the atmosphere: It is the pressure indicated by a barometer. Standard Atmospheric Pressure or Standard Atmosphere is the pressure of 76 cm of mercury having a density of 13.5951 grams per cubic centimeter, under,standard gravity of 980.665 cm per (second) (second). It is equivalent to 14.696 lb per square inch or 29.921 in. of mercury at 32 F. Baffle: A surface for deflecting gases or fluids, usually in the form of a plate or wall. Blast Heater: A set of heat transfer coils or sections used to heat air which is drawn ' or forced through it by a fan. '. Blow (throw): In air distribution, the distance an air stream travels from an outlet to a position at which air motion along the axis reduces to a velocity'of 50 fpm. , , "From Glossary of Physics, by LeRoy Dougherty Weld (McGraw-Hill, 1937). 1 2 CHAPTER 1 1946 Guide For unit heaters, the distance an air stream travels from a heater without a perceptible rise due to temperature difference and loss of velocity. . Boiler Heating Surface: That portion of the surface of the heat-transfer apparatus in contact with the fluid being heated on one side and the gas or refractory being cooled on the other, in which the fluid being heated forms part of the circulating system; this surface shall be measured on the side receiving heat. This includes the boiler, water , walls, water screens, and water floor. (A.S.M.E. Power Test Codes, Series 1929.) Boiler Horsepower: The equivalent evaporation of 34.5 lb of water per hour from and at 212 F. This is equal to a heat output of 970.3 X 34.5 = 33,475 Btu per hour. British Thermal Unit: Classically the Btu is defined as the quantity of heat required to raise the temperature of 1 lb of water 1 Fahrenheit degree. By this definition , the exact value depends upon the initial temperature of the water. Several values of the Btu are in more or less common use, each differing from the others by a slight amount. One of the more common of these is the mean Btu which is defined as 1/180 of the heat . required to raise the temperature of 1 lb of water from 32 F to 212 F at a constant atmospheric pressure of 14.696 lb per square inch absolute. . For most accurate work the International Table (I.T.) Btu is usually used. This is defined by the relation: 1 (I.T.) Btu per (pound) (Fahrenheit degree) = 1 (I.T.)- calorie per (gram) (Centigrade degree). This value corresponds to the amount of heat required to raise the temperature of 1 lb of water 1 Fahrenheit.degree at 58 F and also at 149 F. The mean Btu corresponds to 1.0008 (I.T.) Btu. - ByPass: A pipe or duct, usually controlled by valve dr damper, for conveying a fluid around an element of a system. Calorie (Gram Calorie): Classically the calorie is defined as the quantity of heat required to raise the temperature of 1 gram of water 1 Centigrade degree. By this definition the exact value depends upon the initial temperature of the water. Several values of the calorie are in more or less common use, each differing from the others by a slight amount. Among these are the 15 C calorie and the 17^ C calorie. The mean calorie, i.e. 1/100 the quantity of heat required to raise the temperature of' 1 gram of water from 0 C to 100 C, is also extensively used. - For the most accurate work the International Table (I.T.) calorie, defined in. terms of the international electrical units, is usually used: 1 (I.T.) calorie = 1/860 inter national watt-hour = 3,600/860 international watt-seconds or international joules. The kilocalorie =1,000 cal. . Central Fan System: A mechanical indirect system of heating, ventilating, or air conditioning, in which the air is treated or handled by equipment located outside the rooms served, usually at a central location, and is conveyed to and from the rooms by means of a fan and a system of distributing ducts. (See Chapter 43.) Chimney Effect: The tendency of air or gas in a duct or other vertical passage to rise when heated due to its lower density compared with that of the surrounding air or gas. In buildings, the tendency toward displacement (caused by the difference in tem perature) of internal heated air by unheated outside air due to the difference in density of outside and inside air. . ' Comfort Air Conditioning: The process by which simultaneously the temperature, moisture content, movement and quality of the air in enclosed spaces intended for human occupancy may be maintained within required limits. (See Air Conditioning.) Comfort Line: The effective temperature at which the largest percentage of adults feels comfortable. ' . Comfort Zone (Average): The range of effective temperatures over which, the majority (50 per cent or more) of adults teel comfortable. (See Chapter 12.) Conductance, Surface (Unit): The amount of heat transferred by radiation, con duction, and convection from unit area of a surface to the air or other fluid in contact with it, or vice versa, in unit time for a unit difference in temperature between the surface and the fluid. The common unit is: Btu per (hour) (square foot) (Fahrenheit degree). Symbol/. The temperature of the fluid should be taken in a plane sufficiently far from the surface that it will not be affected by the temperature of the surface. Conductance, Thermal: The time rate of heat flow through unit area of a body, of given size and shape, per unit temperature difference. Common unit is: Btu per (hour) (square foot) (Fahrenheit degree). Symbol C. .' Conduction, Thermal: The process of heat transfer through a material medium in which kinetic energy is transmitted by the particles of the material from particle to- particle without gross displacement of the particles. . . Conductivity, Thermal: The time rate of heat flow through unit area of a homo geneous substance under the influence of a unit temperature gradient. Common units are: Btu per (hour) (square foot) (Fahrenheit degree per inch). Symbol k. .Terminology 3 Conductor, Thermal: A material which readily transmits heat by means of conduction. - Convection: The motion resulting ina fluid from the differences in density and the action of gravity. In heat transmission this meaning has been extended to include both forced and natural motion or circulation. Convective Heat Transfer; The transmission of heat by either natural or forced motion of a fluid (liquid or gas). . Convector: An agency of convection. In heat transfer, a surface designed to transfer its heat to a surrounding fluid largely or wholly by convection. The heated fluid may be removed mechanically or by gravity (Gravity Convector). Such a surface may or may not be enclosed or concealed. When concealed and enclosed the resulting device is sometimes referred to as a concealed radiator. (See also definition of Radiator.) (See also Chapter 25.) Decibel: 'A unit used to express the relation between two amounts of power. By definition the difference in decibels between two powers Pi and P*, P* being the larger, is ,, jrrr________ ____ in I--_ In acoustics the threshold of hearing at 1,000 cycles per second has been standardized at 10"16 watts per square centimeter. If Pj is the power in watts per square centimeter of a measured sound, then 10 logjo is the db difference above the threshold and is known as theintensitylevel. This is a definite recognized way of describing the intensity of a sound. . . ' Degree-Day: A unit, based upon temperature difference and time, used in estimating fuel consumption and specifying nominal heating load of a building in winter. For any one day, when the mean temperature is less than 65 F, there exists as many degree-days as there are Fahrenheit degrees difference in temperature between the mean temperature for the day and 65 F. .. ' Dehumidify: To reduce, by any process, the quantity of water vapor within a given space. . Dehydrate: To remove water in all forms from matter. Liquid water, hygroscopic water, and water of crystallization.or water of hydration are included. Density: The ratio of the mass of a specimen of a substance to the volume of the specimen. The mass of a unit volume of a substance. When weight can be used without confusion, as synonymous with mass, density is the weight of a unit volume of a sub stance. ': _ Dew Point: See Temperature, Dew Point. .. . Direct-Indirect Heating' Unit: A heating unit located in the room or space to be heated and partially enclosed, the enclosed portion being used to heat air.which enters from outside the room. " Direct-Return System (Hot Water): A hot water system in which the water, after it has passed through a heating unit, is returned to.the boiler along a direct path so that the total distance traveled by the water is the shortest feasible, and so that there are considerable differences in the lengths of the several circuits composing the system. Down-Feed One-Pipe Riser (Steam): A pipe which carries steam downward to the heating units and into which the condensation from the heating units drains. Down-Feed System (Steam): A steam heating system in which the supply mains are above the level of the heating units which they serve. Draft: A current of air. Usually refers to the pressure difference which causes a current of air or gases to flow through a flue, chimney, heater or space. Draft Head (Side Outlet Enclosure): The height of a gravity convector between the , bottom of the heating unit and the bottom of the air outlet opening. . (Top Outlet En-_ ' closure); The height of a gravity convector between the bottom of the heating unit and the top of the enclosure. .. . .- Drip: A pipe, or a steam trap and a pipe considered as a unit, which conducts con densation from the steam side of a piping system (o the water or return side of the system; 'Dry: To separate or remove a liquid or vapor from another substance. The liquid . may be water but* the term is also used for the removal of liquid or vapor forms of other substances. . . . ' -; ' ` Dust: An aif suspension (aerosol) of solid particles of any material. (See`also Chapter 10, p. 184.) , . . Enthalpy: A term applied to the Gibbs function, h -- u -f pv and superseding total heat, heal content, and heat of formation. The increase of enthalpy of a system is equal 4 CHAPTER 1 1946 Guide to the heat absorbed by the system during a process occurring at constant pressure when the only work done is that of compression or expansion (See also Chapter 3.) Enthalpy* Free: A thermodynamic property which serves as a measure of the available energy of a system with respect to surroundings at the same temperature and same pressure as that of the system. No process involving an increase in available energy can occur spontaneously. . Enthalpy* Specific: A term sometimes applied to enthalpy per unit weight, the English unit being Btu per pound. Entropy: Entropy is the ratio of the heat added to a substance to the absolute * temperature at which it is added. The entropy associated with an isolated physical system has the characteristic property that, as the system spontaneously settles into a final, steady state, the entropy approaches a maximum. It may be regarded as a measure of the degree in which the energy of the system is unavailable. If a system absorbs an infinitesimal amount of heat dQ during a reversible'process, the entropy change of the system is equal to dS = -- where T is the absolute temperature of the system. Two of the functions of entropy may be mentioned to clarify this somewhat abstruse property: (1) During a reversible adiabatic change of state, entropy is constant; (2) during a reversible isothermal change of state, the heat absorbed is equal to the absolute temperature times the change in entropy. " The term Specific Entropy is sorrfetimes applied to entropy per unit weight, the English-unit being Btu per (Fahrenheit degree) (pound). " Equivalent Evaporation: The amount of water a boiler would evaporate, in pounds per hour, if it received feed water at 212 F and vaporized it at the same temperature and atmospheric pressure. ' '* Fan Furnace System: See Warm Air Heating System. Fog: Suspended liquid droplets generated by condensation from the gaseous to the liquid state or by. breaking up a liquid into a dispersed state, such as by splashing, foaming, and atomizing. (See also Chapter 10, p. 186.) Force: The action on a body which tends to change its relative condition as to ` rest or motion. Fumes: Smoke; aromatic smoke; odor emitted, as of flowers; a smoky or vaporous ' exhalation, usually odorous, as that from concentrated nitric acid. The word fumes is so broad and inclusive that its usefulness as a technical term is very limited. Its principal definitive characteristic is that it implies an odor. The terms vapor, smoke, fog, etc., which can be more strictly defined, should be used whenever possible. . Also defined as solid particles generated by condensation from the gaseous state, generally after volatilization from molten metals, etc., and often accompanied by a chemical reaction such as oxidation. Fumes flocculate and sometimes coalesce. (See also Chapter 10, p. 184.) Furnace: That part of a boiler or warm air heating plant in which combustion takes * place. Also a complete heating unit for transferring heat from fuel being burned to the . air supplied to a heating system. ' Furnace Volume (Total): The total furnace volume for horizontal-return tubular boilers and water-tube boilers is the cubical contents of the furnace between the grate and the first plane of entry into or between tubes. It therefore includes the volume behind the bridge wall as in ordinary horizontal-return tubular boiler settings, unless manifestly ineffective (t.e., no gas flow taking place through it), as in the case of waste-, heat boilers with auxiliary coal furnaces,, where one part of the furnace is. out of action when the other is being used. For Scotch or other internally fired boilers it is the cubical contents of the furnace, flues and combustion chamber, up to the plane of first entry into , the tubes. (A.S.M.E. Power Test Codes, Series 1929.) . Grate Area: The area of the grate surface, measured in square feet, to be used in estimating the rate of burning fuel. This area is construed to mean the area measured in the plane of the top surface of the grate, except that with special furnaces, such as ,, those having magazine feed, or special shapes, the grate area shall be the mean area of . the active part of the fuel bed taken perpendicular to the path of the gases through it. For furnaces having a secondary grate, such as those in double-grate down draft boilers,' the effective area shall be taken as the area of the upper grate plus one-eighth of the area of the lower grate, both areas being estimated as previously defined. . Gravity, Specific: The ratio of the mass of a unit volume of a substance to the. mass of the same volume of a standard substance at a standard temperature. Water at Terminology __________________________________________________ _____ H 39.2 F is the standard substance usually referred to. For gases, dry air, at the same temperature and pressure as the gas, is often taken as the standard substance.1 * Gravity Warm Air Heating System: See Warm Air Heating System.'' -' Head, Dynamic: Same as Total Pressure expressed in height of liquid. Heat: Thermal energy. Heat is a mode of motion. When a change in the quantity of heat in a body results in a change of temperature without change of state the heat is called Sensible Heat. When a change in the quantity of heat in a substance results in a change of state, e.g. from liquid to vapor, solid to liquid, etc., without change in tem perature, the heat is called Latent Heat. Heat, Humid: Ratio of increase of enthalpy pier pound of dry air to rise of tem perature under conditions of constant pressure and constant humidity ratio. . . Heat of the Liquid: The increase in enthalpy per unit weight of a saturated liquid as its temperature increases from a chosen base temperature. For water the base tem perature is usually taken as 32 F. n . ., \ Heat, Specific: The heat absorbed (or given up) by a unit mass of a substance when its temperature is increased (or decreased) by 1 deg. Common Units: Btu per (pound) (Fahrenheit degree), calories.per (gram) (Centigrade degree). For gases, both specific heat at.constant pressure (Cp) and specific heat at constant volume (CV) are frequently used-. In air-conditioning, Cp is usually used. ' ` Heat, Total: See Enthalpy. . . . Heat Transmission, Coefficient: Any one of a number of coefficients used in the .. calculation of heat transmission by conduction, convection, and ^radiation, through various materials and structures. (See thermal conductance,, thermal conductivity, thermal resistance, thermal resistivity, thermal transmittance, etc;). =. . Hot Water Heating System: A heating systefii in which water is used as the medium by which heat is carried from the boiler tp the heating units. Humidify: To increase, by any process, the density of water vapor within a given space. Humidistat; A regulatory device, actuated by changes in humidity, used.for the . automatic control of relative humidity. .. . Humidity: Water vapor within a given space. . . Humidity, Absolute: The weight of water vapor per unit volume, pounds per cubic foot or grams per cubic centimeter. : Humidity, Relative: The ratio of-the actual partial pressure of the water vapor in a space to the saturation pressure of pure water at the same temperature. (See dis cussion in Chapter 3.) .. . . Humidity, Constant Relative Line: Any line on the psychrometric chart repre senting a series of conditions which may be. evaluated by one percentage of relative humidity; there are also constant dry-bulb lines, wet-bulb lines, effective temperature lines, vapor pressure lines, and lines showing other physical properties of air mixed with water vapor. - Humidity Ratip: In a mixture of water vapor and air, the weight of water vapor per pound of dry air. Also called Specific Humidity. ' . . Humidity, Specific: See Humidity Ratio. , . Hygrostat: Same as Humidistat. . ` , Inch of Water: A unit of pressure equal to the pressure exerted by a column of liquid water 1 in. high at a standard temperature. The standard temperature is some times taken as 0 C and sometimes as 62 F. One inch of water at 62 F = 5.197 lb per . square foot. ' -. Insulation (Thermal): A material having a relatively high resistance to heat flow, | . and used principally to retard the flow of heat. . Isobaric: An adjective used to indicate a change taking place at constant pressure. Isothermal: An adjective used to indicate a change taking place at constant, temperature. . "Load, Estimated Design: In a heating or cooling system, the sum of the useful heat transfer plus heat transfer from or to the connected piping plus heat transfer . occurring in any auxiliary apj)aratus connected to the system.. The units are Btu per hour or, in heating, equivalent direct`radiation (EDR). The unit EDR is becoming obsolete . . -. ' Load, Estimated Maximum: In a heating or cooling system, the calculated maxi mum heat transfer that the system will be called, upon to provide. '-' s' 6 , CHAPTER 1 1946 Guide - Manometer: An instrument for measuring pressures; essentially a U-tube partially filled with a liquid, usually water, mercury, or a light oil, so constructed that the amount. . of displacement of the liquid indicates the pressure being exerted on the instrument.. - Mass: A measure of the inertia of a body. It also measures the quantity of matter in a body. Since the only general property of a given portion of matter that cannot be changed is its inertia, it is this property by which quantities of matter are defined. Two bodies which have equal inertias are said to have equal masses or to contain equal quantities of matter. (This definition fails at velocities approaching the velocity of light.) The mass of a body is numerically equal to the ratio of the force required to give the body a given acceleration to the acceleration, m =---- . The common units of mass are the gram and the pound. a _ Mechanical Equivalent of Heat: The quantity of mechanical energy equal to. one unit of heat. J = 778.3 ft-lb per Btu = 4.187 X 107 ergs per gram-calorie. Medium, Heating: A substance such as water, steam, air or furnace gas used to convey heat from the boiler, furnace or other souce of heat or energy to the heating unit from which the heat is dissipated. . Micron: A unit of length, the thousandth part of 1 mm or the millionth of a meter. Millimeter of Mercury: A unit of pressure equal to the pressure exerted by a column of mercury 1 mm high at a temperature of 0 C. One millimeter of mercury at 0 C = 1.934 X 10"* lb per square inch. ' Mol: A weight of a substance numerically equal to its molecular weight. If the weight is in pounds the unit is a Pound Mol, in grams the unit is a Gram Mol. For. .perfect gases the volume of 1 mol is constant for all gases at the same temperature and pressure. For real gases this is approximately true at moderate pressures. At 32 F and zero-pressure the value of the product, pressure times specific volume, is 359.045 0.006 atmosphere cubic feet (atm ft*), for 1 mol of any gas. For dry air at 32 F and standard atmospheric pressure, the specific volume is.358.83 cu ft per mol.(ft* per mol). One-Pipe Supply Riser--(Steam): A pipe which carries steam vertically to a heat ing unit and which also carries the condensation from the heating unit. In an upfeed system steam and condensation flow in opposite directions; in an overhead or down-feed system they flow in the same direction. One-Pipe System--(Steam): A steam heating system in which a single main serves the dual purpose of supplying steam to the heating unit and conveying condensation from it. Ordinarily to each heating unit there is but one connection which must serve as both the supply and the return, although separate supply and return connections may be used. (Hot Water)--A hot water system in which the cooled water from the heating units is returned to the supply main. Consequently, the heating units farthest from the boiler are supplied with cooler water than those near the boiler in the same circuit. Overhead System: Any steam or hot water system in which the supply main is above the heating unit. In a steam system the return must be below the heating units; in a water system the return may be above or below the heating units. Panel Heating: A heating system in which heat is transmitted by both radiation and convection from panel surfaces to both air and surrounding surfaces. Panel Radiator: A heating unit placed on or flush with a flat wall surface and in tended to function essentially as a radiator. Plenum Chamber: An air compartment maintained under pressure and connected to one or more distributing ducts. ' Potentiometer: An instrument for comparing small electromotive forces .or for measuring small electromotive forces by comparison with a known electromotive force. Its principal advantage is that during the measurement no current flows through the source of electromotive force. Power: The rate of performing work. Common units are horsepower, Btu per hour, and watts. .. Pressure: Force per unit area. Common units are pounds per square inch, gram per square centimeter, inch of water, millimeter of mercury. . Pressure, Absolute: The sum of the gage pressure and the barometric pressure. Pressure, Gage: Pressure measured from atmospheric pressure as a base. Gage pressure may be indicated by a manometer which has one leg connected to the pressure source and the other exposed to atmospheric pressure. - v . ; Pressure, Dynamic: Same as Total Pressure. Pressure, Saturation: The saturation pressure for a pure substance for any given temperature is that pressure at which vapor and liquid or`vapor and solid can co-exist - in stable equilibrium. .. * .. 1' Terminology_________ 7. Pressure, Static: The normal force per unit area that would be exerted by a moving fluid on a small body immersed in it if the body were carried along with the fluid. Practi cally it is the normal force per unit area at a small hole in a wall of the duct through which the fluid flows (piezometer) or on .the surface of a stationary tube at.a point where the disturbances created by inserting the tube cancel. It is supposed that the thermo dynamic properties of a moving fluid depend on static pressure in exactly the same, manner as those of the same fluid at rest depend upon its uniform hydrostatic pressure. _ . Pressure Total: In the theory of the flow of fluids; the sum of the static pressure and the velocity pressure at the point of measurement. . Pressure, Vapor: The pressure exerted by a vapor. .If a vapor is kept in confine- ment over its liquid so that the vapor can accumulate above the liquid, the temperature . ' being held constant, the vapor pressure approaches a fixed limit called the maximum, or saturated, vapor pressure, dependent only on the temperature and the liquid. - The term vapor pressure is sometimes used as synonymous with saturated vapor pressure. .. Pressure, Velocity: In a moving fluid, the difference, due to velocity, between total pressure and static pressure." . Psychrometer: An instrument for ascertaining the humidity or hygrometric state of the atmosphere. . Psychrometric: Pertaining to psychrometry or'the state of the atmosphere with reference to moisture. ' Psychrometry: The branch of physics relating to the measurement or determination of atmospheric conditions, particularly regarding the moisture mixed with the air. Pyrometer: An instrument for measuring high temperatures. Radiant Heating: A heating system in which only the heat radiated from panels is effective in providing the heating requirements. The term Radiant Heating is frequently used to include both Panel and Radiant Heating. ! ' Radiation: The transmission of energy by means of electromagnetic waves. Radiation, Thermal (Heat) Radiation: The transmission of energy by means of electromagnetic waves of very long wave length. Radiant energy of any wave length may, when absorbed, become thermal energy and result in an increase in the temperature of the absorbing body. ." Radiation, Equivalent Direct (EDR, Steam): That amount of heating surface, expressed in square feet, which will deliver 240 Btu per hour, under the design operating conditions. (EDR Hot Water): That amount of heating surface, expressed in square feet, which will deliver 150 Btu per hour, under the design operating conditions. Thus, 1 sq ft of EDR does not imply 144 sq in. of heater surface, but means a heat delivery of . . 240 (or 150) Btu per hour for each EDR of a given radiator or convector. , Radiator: A heating unit exposed to view within the room or space to be heated. A radiator transfers heat by radiation to objects within visible range and by conduction" to the surrounding air which in turn is circulated by natural convection; a so-called radiator is also a convector but the single term radiator has been established by long usage. ' '. . . Radiator, Concealed: A heating device located within, adjacent to, or exterior to ' . the room being heated but so covered or enclosed, or concealed that the heat transfersurface of the device, which may be either a radiator or a convector, is not visible from " the room. Such a device transfers its heat to the room largely by convection air currents, -- ` Radiator, Direct: Same as Radiator. . - Radiator, Recessed: A heating unit set back into a wall recess but not enclosed. Radiator, Tube or Tubular: A heating unit used as a radiator in which the heat transfer surfaces are principally tubes. ' ' Refrigerant: A substance which produces a refrigerating effect by its absorption . of heat while expanding or vaporizing. " - . . Refrigeration, Ton of: The removal of heat at a rate of 200 Btu per minute, 12,000 Btu per hour, or 288,000 Btu per 24 hours. . /' > Resistance, Thermal: The reciprocal of thermal conductance. Symbol R. . Resistivity, Thermal: The reciprocal of thermal conductivity. Symbol r. . Return, Dry: A return pipe in a steam heating system which carries both water of condensation and air. The dry return is above the level of the water line in the boiler . *n a gravity system. (See Return, Wet.) .. . Return, Wet: That part of a return main of a. steam heating system which is filled . ' with water of condensation. The wet return usually is below the level of the water line . m the boiler, although not necessarily so. (See Return, Dry.) . - y 8 CHAPTER 1 1946 Guide . Return Mains: Pipes or conduits which return the heating or cooling medium from the heat transfer .unit to the source of heat or refrigeration. . Reversed-Return System: A system in which the heating or cooling medium from several heat transfer units is returned along paths arranged so that all circuits com posing the system or composing a major sub-division of the system are'of practically equal length. Saturation: The condition for co-existence in stable equilibrium of a vapor and liquid or a vapor and solid phase of the same substance. Example: Steam over the water from which it is being generated. Saturation, Degree of, or Per Cent: The ratio of the weight of a given volume of. water vapor to the weight of an equal volume of saturated water vapor at the same temperature. Smoke: An air suspension (aerosol) of particles, usually but not necessarily solid, often originating in a solid nucleus, formed from combustion or sublimation. Also defined as carbon or soot particles less than 0.1 micron in size which- result .from the incomplete combustion of carbonaceous materials such as coal, oil, tar, and tobacco. Smokeless Arch: An inverted baffle placed in an up-draft furnace toward the rear to aid in mixing the gases of combustion and thereby to reduce the smoke produced. ` Sorbent: Material which has the property of dehumidifying gases without the help of refrigeration. The term generally refers to materials which have a large capacity for moisture compared to their bulk or weight. .. Sorption: Adsorption or absorption. - Split System: A system in which the heating is accomplished by means of radiators or- convectors supplemented by mechanical circulation of air (heated or unheated) from a central point. Ventilation may be provided by the same system.' Square Foot of Heating Surface {Equivalent): This term is synonymous with Equivalent Direct Radiation (EDR). Stack Height: The height of a gravity convector between the bottom of the heating unit and the top of the outlet opening. Steam: Water in the vapor phase. Dry Saturated Steam is steam at the saturation temperature corresponding to the pressure, and containing no water in suspension. Wet Saturated Steam is steam at the saturation temperature corresponding to the pressure, and containing water particles in suspension. Superheated Steam is steam at a tem perature higher than the saturation temperature corresponding to the pressure. Steam Heating System: A heating system in which heat is transferred from the boiler or other source of heat to the heating units by means of steam at, above, or below atmospheric pressure. . ' Steam Trap: A device for allowing the passage of condensate, or of air and con densate and preventing the passage of steam. : Supply Mains: The pipes through which the heating medium flows'from the boiler or source of supply to the run-outs and risers leading to the heating units. Surface, Heating: The exterior surface of a heating unit. Extended heating surface {or extended surface):, Heating surface consisting of fins, pins or ribs which receive heat by conduction from the prime surface. Prime Surface: Heating surface having.the heating medium on one side and air (or extended surface) on the other. (See also Boiler Heating Surface.) . *. Temperature: The thermal state of matter with reference to its tendency to com- municate heat to matter in contact with it. If no heat flows upon contact, there is?no difference in temperature. Temperature, Absolute: Temperature expressed in degrees above absolute zero. Temperature, Dry-Bulb: The temperature of a gas or mixture of gases indicated > by an accurate thermometer after correction for radiation. . Temperature, Dew-Point: The temperature at which the condensation of water vapor in a space begins for a given state of humidity and pressure as the temperature of the vapor is reduced. The temperature corresponding to saturation (100 per centrelative humidity) for a given absolute humidity at constant pressure. Temperature, Effective: An arbitrary index which combines into a single value the effect of temperature, humidity, and air movement on the sensation of warmth or cold felt by the human body. The numerical value is that of the temperature of still, saturated air which would induce an identical sensation. ' Temperature, Wet-Bulb: Thermodynamic wet-bulb temperature is the tem perature at which liquid or solid water, by evaporating into air, can bring the.air to saturation adiabatically at the same temperature. Wet-bulb'temperature (without qualification) is the temperature indicated by a wet-bulb psychrometer constructed and Terminology 9 used according to specifications. {A.S.M.E. Power Test Codes,.Series 1932, Instru ments and Apparatus, Part 18.) - - * ' '. Thermodynamics, Laws of: Two laws upon, which rest the classical theory of thermodynamics. These laws have been stated in many different,, but equivalent ways. The First Law: (1) When work is expended in generating.heat, the quantity of heat nroduced is proportional to the work expended and, conversely; when heat is employed in the performance of work, the quantity of heat which disappears is proportional to the work done. (Joule)b (G.P.); (2) If a system is caused to change from an initial state to a final state by adiabatic means only, the work done is the same for all adiabatic paths connecting the two states. (Zemansky); (3) In any power cycle or refrigeration-cycle the net heat absorbed bv the working substance is exactly equal to the net work done. The Second Law: (1) It is impossible for a self acting machine, unaided by anv external atrency to convey heat from a body of lower to one of higher temperature. (Clausius) (G P V (2) It is impossible to derive mechanical work from heat taken from a body unless there is available a body of lower temperature into which the residue not so used- mav be discharged (Kelvin) (G.P.); (3) It is impossible to construct an engine that, operating in a cycle, wilf produce no effect other than the extraction of heat from a reservoir and the performance of an equivalent amount of work (Zemansky). Thermostat: An instrument which responds to changes in temperature and which directly or indirectly controls temperature. Transmittance, Thermal: The time rate of heat flow, from the fluid on the warm side to the fluid on the cold side, per (square foot) (degree temperature difference be tween the two fluids). Sometimes called Over-all Coefficient of Heat Transfer. Common unit is Btu per (hour) (square foot) (Fahrenheit degree). Symbol U. Two-Pipe System {Steam or Water):. A heating system in which one pipe is used for the supply of the heating medium to the heating unit and another for the return of the heating medium to the source of heat supply. The essential feature of a two-pipe system is that each heating unit receives a direct supply of the heating medium which medium cannot have.served a preceding heating unit. Unit: As applied to heating, ventilating and air conditioning equipment this word means factory-built and assembled equipment with apparatus for accomplishing some specified function or combination of functions. (See Chapters 26 and 36.) It is loosely applied to a great variety of equipment. Usually the function is included in the name, and hence come terms like Unit Heater, Unit Ventilator, Humidifying Unit; and Air Conditioning Unit. ' Units are said to be direct or room, when intended for location, or located.in, the treated space; indirect or remote, when outside or adjacent to the treated space. They are ceiling units when suspended from above, and floor when supported from below. Other descriptive words includefree delivery when the unit is not intended to be attached to ducts or similar resistance-producing devices, and pressure when for use with such ducts. Complete description requires the use of several of these qualifying words or phases. (See Chapters 26 and 36.) ` ' , Up-Feed System: A heating system in which the supply mains are below the level of the heating units which they serve. . Vacuum Heating System: A two-pipe,steam heating system equipped with the necessary accessory apparatus which will permit operating the system below atmospheric pressure when desired. ` . Vane Ratio: In air distributing devices the ratio of depth of vane to shortest opening width between two adjacent grille barsT ` Vapor: The gaseous form of substances which are normally in the solid or liquid state and which can be changed to these states either by increasing the pressure or decreasing the temperature. Vapors diffuse. (i4.5.A. definition.) - Vapor Heating System: A steam'heating system which operates under pressures at or near atmospheric and which returns the condensation to the boiler or receiver by gravity. Vapor systems have thermostatic traps or other means of resistance on the return ends of the heating units for preventing steamfrom entering the return mains; they also have a pressure-equalizing and air-eliminating device at the end of the dry return. Velocity: A vector quantity which denotes at once the time rate and the direction of a linear motion. V = at-. Fo- r uniform linear motion V = --t~ . Common units are: feet per second. . ' bNames of authors who first stated law are given in parentheses). 10 CHAPTER 1 . . 1946 Guide - Ventilation: The process of supplying or removing air, by natural or. mechanical . means, to or from any space. Such air may or may not have been conditioned. (See Air Conditioning.) .*' .. .. Volume, Specific: The volume of a substance per unit niass; the reciprocal of density. Units:. cubic feet per pound, cubic centimeters per gram, etc. . Warm Air Heating System: A warm air heating plant consists of a heating unit (fuel-burning furnace) enclosed in a casing, from which the heated air is distributed to the various rooms of the building through ducts. ' . Warm Air Heating System, Gravity: A warm air heating system in which the motive head producing flow depends on the difference in weight between the heated-air leaving the casing and the cooler air entering the bottom of the casing. Warm Air Heating System, Mechanical: A warm.air heating system in which ..circulation of air is effected by a fan. Such a system may include air cleaning devices. ` CHAPTER 2 - _^bbreutation6 anJSfm u Standard Abbreviations; Standard Symbols; Greek Alphabet; Conversion Equations; Graphical Symbols for Piping, Ductwork, Heating and Ventilating, Refrigerating; Identification of Piping by Color; Specific Heat Table THIS chapter contains information regarding abbreviations, symbols, and conversion equations, which are of particular interest to the engineer engaged in heating, ventilating, and air conditioning. ABBREVIATIONS Abbreviations are shortened forms of names and expressions employed in texts and tabulations and should not generally be used as symbols in equations. Most of the following abbreviations have been compiled from a list of approved standards l. In general the period has been omitted in all abbreviations except where the omission results in the formation of an English word. Additional abbreviations applying to individual chapters will be found at the end of Chapters 3, 4, 5, 7, 39, 41, and 43. Absolute..:--------------------- -............................... -......................................... -................. ..^abs Air horsepower.... ................................................ --t........ -................................-........... air hp Alternating-current (as adjective)...................... .....................1....................................... a-c Ampere........ .................................................. ;.... -............. -........... -........ -........... --..... .-amp Ampere-hour..^.......................... -............. 1.......... ..................................-....... -.......... amp-hr Atmosphere....... ........................ Average... ........ ........... -........... Avoirdupois.......... ........ ........... Barometer......... ..... .................. , Boiling point--........................... .......atm ..... .avg .... avdp ...... bar. .... -bp Brake horsepower................:.... Brake horsepower-hour............ British thermal unit................. British thermal units per hour. Calorie........................................ .... ,,bhp ,,bhp-hr ...... Btu .....Btuh ........ cal Centigram........... .................................... .... ..:....................................=..................:.....--leg Centimeter......................... .............. ................................................................ ............... .cm. Ceritimeter-gram-second (system)................................ ....................................................cgs Cubic.......... ........... ................. ....................................... ......... 1........ ................ ;................ cu Cubic centimeter__ ................................................................-.......... .................cu. cm or cc Cubic foot... Cubic feet per minute. Cubic feet per second.. Decibel________ _____ Degree*--..________ ..... cu ft ..cfm ....cfs ....db .deg or Degree, Centigrade............................:__`..................... ;............... -......... --..................... C Degree, Fahrenheit.........................................-..................................................................... F Degree, Kelvin!........... ........................... ....... ...................................:... ................. ..... ...... K Degree, Reaumur!................... ............. !..... .............. I.......--..............._:!.... .............. R Diameter................. ......... 1........................... ....................... ,.......... !..............;....T........ diam `Abbreviations for Scientific and Engineering Terms, 210.1-1941 {American Standards Association). . *It is recommended that the abbreviation for the temperature scale. F, C, K. be included in expressions tor numerical temperatures but, wherever feasible,- the abbreviations for degree be omitted; as 68 F.- . 12 CHAPTER 2 1946 Guide Direct-current (as adjective).................................................... .......................................d-c Electromotive Force....'............. .......... .......................................... ............................. .... emf Feet per minute.___.:_________ ......... ...... .... ............. ,,... ;............... ................fpm Feet per second....... ....... .......................... .... ..............."........... .......................................fps Foot... ............ ... ..... ..... ...... ............................. ........................................... ........ _............ ft Foot-pound.................... ....................... '..................................1......................................ft-lb Foot-pound-second (system)............':.............. .... ............ _____:.................... ..... .......... fps Freezing point___________ __ ___________..;;.____ ___ ________________________ _fp Gallon........ ................................................................................. ... ......... ..... ..................gal Gallons per minute............... ;..... J:.... ;.....................................-............. ,,..... _............. -gpm Gallons persecond'...........................-............ ............ -....... .'........ -............................ ... gps Gram.......................... ............................. ....................................... ... 1.............................. g Gram-calorie......... ....... ...............................................,,........................'....... ...... ........ g-cal Horsepower.............................................. ........................................._................................. hp Horsepower-hour.--..................... .......... .............. ............... ......................................._hp-hr Hour....................... --.......................... ................ ............ :..................................... ... ;....... hr Inch................. ........... -............... ..... ........................................ ...... ........... ............ ,... ,,....in. Inch-pound .......... .--............................................... :.........................1................ ........ in.-lb Indicated horsepower........................................ ;............ ..................................................ihp Indicated horsepower-hour.--............................ ....................:.......................... .... ..... ihp-hr Kilogram.......... ,,........................:................ .............. ;...... ................................. ;...... .. ..... kg Kilowatt................:....... ,........................................................ ............................................kw Kilowatthour.................................................................................................................... kwhr Mass.--..................................................................... ,............................................... . mass Melting point..... ......... _mp Meter....... ........................................... m Micron....... ........... ...... .................................................. ;............................................. ^ (mu) Miles per hour.--................................... ...................... :........ .... :........ :..................... imph Millimeter.-.................................. ........................................... ;..................................... ... mm Minute.--......................................T.................................................. ;...................... ..... .... min Molecular weight............................................................................................. ;_____ mol. wt Mol.--................................................................................................................ ;.... ........ jjnol Ounce.............!.......................................................................................................... I.....___oz Pound................................ `........ t........ ........ ;.................................... ................................. lb Pounds pr square inch............................. ;...................................... ........... r........... ___ psi Pounds per square inch, gage...... Pounds per square inch, absolute. Revolutions per minute................ Revolutions per second................ Second..^............._......................... -PS`g ..psia .jpm ....rps Specific gravity.............................................................................................................. sp gr Specific heat............................... ....................................... ;...... ............................... ...... sp ht Square foot:........................................................... .....................................................-.....sq ft Square inch........... ;.......................................... ..... :.......................................... ...... ...... sq in. Watt................................................................. .......................................... :.......... ........ _,,w Watthour....... ............................................................................................. :..................... whr - SYMBOLS ,A letter symbol is a single character, with subscript or superscript if required, used to designate a physical magnitude in mathematical equa tions and expressions. Two or more symbols together always represent a product. The following have been compiled from a selected list of approved standards 3. Additional symbols and variations in the standard `Letter Symbols, for Mechanics of Solid -Bodies. ZtO.3-1942, and-Letter Symbols for Heat and Thermo dynamics, Z10.4-1943 {American Standards Association). - . Abbreviations and Symbols - :.------------------------------------------------------------------=---------11 symbols found necessary in the individual chapters will be found in a list at the end of Chapters 3, 4, 5, 7, .39, 41, and 43. ' Acceleration, due to gravity............................................................................................................ ------------ Acceleration, linear:---------------------->..............1................................. -*............. :........................ ......... r------a Area................................................ --: -..................... .................................................... A Change in specific volume during vaporization ...... ..................................... ------ *fg Density, Weight per unit volume* Specific weight.......................................... .d or p (rho) Distance, linear....... ..........................-.............................................-..................................... s Dry saturated vapor, Dry saturated gas at saturation pressure and temperature, vapor in contact with liquid...... .......... ........................................-.............. Subscript g Efficiency..........- -.......... -......................................-.......................... ---...........................*3 Elevation above some datum...................J.............................................................z, Z Emissivity......... .....................................-.....-.......................................... -........... -..............e, Energy in general; work, total; work, molal.... .................................................... ........... E Entropy. (The capital should be used for any weight, and the small letter for unit weight)------------ -- ....... .................r-- ...........................-.................................. S or s Force, total load--!..................... -................... *......................................................................F Gas Constant, in equation pV -- nRT..................................................... -.... ................... R Head__ 1......... .................... 1................ .................... -- ................. -.............-...... H or * Heat content, Total heat, Enthalpy. (The capital should be used for any weight and the small letter for unit weight)..J............ ............. ..........................or h Heat content of saturated liquid, Total heat of saturated liquid, Enthalpy of saturated liquid, sometimes called heat of the liquid....................................... --M Heat content of dry saturated vapor, Total heat of dry saturated vapor, Enthalpy of dry saturated vapor..................................................................................................hg Heat of vaporization at constant pressure.:_____________________ ______ ___^...L or h(g Hydraulic radius................................. ..... ....................................-................. ............ '..:...Ra Internal energy, Intrinsic energy. (The capital should be used for any weight and the small letter for unit weight)________ ________ :............. .............................V or u Length of path of heat flow, .thickness............................. ....... ..... ......................:----- :----- L r .*'*' - '. Load, totalJ.........--....... ......... ....... .............................................................~~W Mechanical efficiency.________ ___:.......... ...... ............. J.................... .-......... -............ :-----Cm Mechanical equivalent of heat....... ................... ............................................ ........ ...... Power, Horsepower, Work per unit time________ _____ ______ .....................i--..... .---P Pressure, Absolute pressure, Gage pressure, Force per unit'area__ ' --.----...p Quantity (total) of fluid, water, gas, heat; Quantity by volume; Total quantity' of heat transferred________ _____ _____________________________ ____ .................. Q Quality of steam, Pounds of dry steam per pound of mixture.................;.... .... ............. x Reynolds Number.......................... ........................ ......... ...............................................iVRe Saturated liquid at saturation* pressure and temperature, Liquid in -contact with vapor__ ::_______ ___________ _____ ____ Subscript f Specific heat__________________^...__________ j....... .......................... '.....______ ^...c. Specific heat at constant pressure.............. ....... ......... ........ .................. ...... ................... ^p. . Specific heat at constant volume....___ ________ ____________________________:.......cv ' Specific volume, Volume per unit weight, Volume per unit mass.__________________ Temperature (ordinary) F or C. (Theta is used preferably only when t is used for. . Time in the same discussion)_____________ ^_______ ________ ^t or 0 (theta) ' Temperature (absolute) F abs or K. (CapitaU/ns/a is used preferably, only when . small theta is used for ordinary, temperature)--.!__ _i~:...T or (capital theta) . 14_________ , CHAPTER 2 , t- ,1946 Guide Thermal conductance4: heat transferred per (unit time) (degree)..........;...... -..... :.......:C ' r = J_ = M = q RLh-tt .. Thermal conductance per unit area/ Unit conductance: heat, transferred per . . (unit time) (unit area) (degree)_______ _______________ -.............-........... ........ :Ca rC 1_ g _k - ' Ca " A RA A(h -h) L - Thermal conductivity: heat transferred per (unit time) (unit area) (degree per unit length)-------------- ---------------------------------------- :------------- ---- ---------------- k -' . ` . g k= A____ - <) L .. Surface coefficient of heat transfer,-Film coefficient of heat transfer, Individual coefficient of heat transfer: heat transferred per (unit time) (unit area) . (degree).......... .............. ;............................ ...................,,... ............................... -/ A / - ti - tt (In general/ is not equal to k/L, where L is the actual thickness of the fluid film.) Over-all coefficient of heat transfer. Thermal transmittance per unit area: heat transferred per (unit time) (unit area) (degree over-all).......................................... U V= Thermal transmission (heat transferred per unit time)_____ --q Thermal resistance (degree per unit of heat transferred per unit time):.. .R' Thermal resistivity____ _.._________________________________ __ ______ ___________ 1/k Vaporization values at constant pressure, Differences between values for saturated.. .. vapor and saturated liquid at the same pressure...: 1...Subscript fg Velocity._________ ___________ _L...................................... ................. ........ ........................V Viscosity, absolute....................;.................. ................................. '........................................ [L Viscosity, kinematic-............... ............ .......... ............. .................................... ........ ...... p./p Volume (total)______ ,:_________ ____ _______ _____ ________ ...... . V Volume per unit time, Rate at which quantity of material passes through a , machine, Quantity of heat per unit time, Quantity of heat per unit weight......;.__q Weight of a major item, Total weight.__________ ____ ____;'I_______________________W Weight rate. Weight per unit of power, Weight per unit of time_____ ________ ;_____w Work (total)....___ ............ ...... ........... ............ :.................. ........ .......................'......._.W _ 4Terms endlug iviiy deaignate properties independent of sue or shape, sometimes called specific proper ties. Examples: conductivity, resistivity. Terms ^wHing ance designate quantities.depending not only on the material, but also upon size and shape,'sometimes called total quantities. Examples: conductance, transmittance. . Terms 'ending ion designate rate of heat transfer. Examples: conduction, transmission.' and Symbols ^ ' .r.-' . /j - L1:'............. : THE GREEK ALPHABET AlphaBeta Gamma Delta Epsilon Zeta Eta Theta . I t Iota K k Kappa A X Lambda M p. Mu N * Nu S5 Xi . O o Omicron II.it Pi is' P p Rho Eos Sigma T t Tau T u Upsilon p Phi X x ,Chi ^ Psi Q a) Omega . CONVERSION EQUATIONS5 Heat Power and Work 1 ton Refrigeration Latent heat of ice ' 1 Btu 1 Int. watthour ' 1 In't. kilowatthour ' 1 Int. kilowatt (1000 watts) 1000 I.T. calories 1 1 I.T. Kilocalorie / 1 horsepower 1 boiler horsepower / 12,000 Btu per hour \ 200 Btu per minute 143.4 Btu per pound : 778.3 ft-lb 0.2930 Int. whr , 252.0 I.T. calorie '. ' . 2656 ft-lb ' 3.413 Btu . 3600 Int. joules , 860 I.T. calories . 3.413 Btu 3.517 lb water evaporated from and at 212 F. 1.341 hp . 56.88 Btu per minute 44,267 ft-lb per minute 3.968 Btu 3088 ft-lb 1.1628 Int. whr 0.7455 Int. kw . 42.40 Btu per minute. 33.000 ft-lb per minute 550 ft-lb per second ' / 33,475 Btu per hour \ 9.809 Int. kw - Weight and Volume . 1 gal (U..S.) , 1 British or Imperial gallon . , ii 4 cu ^ . ' 1 cu ft water at 60 F( in vacua) 1 cu ft water at 212 F ( " " ) , 1 gal water at 60 F - (; "1) .. 1 ' 1 gal water at 212 F ( " ) UbTavdp) '' 1 bushel 1 short ton ` - . = \ 0.1337 cu ft = 277.42 cu in. _ / 7.481 gal t 1728 cu in. = 62.37 lb = 59.83 lb -- 8.338 lb = 7.998 lb "{'TOW grains =. 1.244 cu ft ' , = 2000 lb ` ' *Checked in 1944 by National. Bureau of Standards.' Abbreviations /nh and I.T. refer to International ' y and International CSteam) Table respectively. S 16 CHAPTER 2 1946 Guide Pressure , 1 lb per square inch 1 oz per square inch 1 atmosphere 1 in. water at 62 F (in vacuo) 1 ft water at 62 F (in vacuo) 1 in. mercury at 62 F (in vacuo) 1 in-, mercury at 32 F (in vacuo) 144 lb per square foot . {2.0360 in. mercury at 32 F 2.0422 in. mercury at 62 F 2.309 ft water at 62 F [ 27.71 in. water at 62 F / 0.1276 in. mercury at 62 F \ 1.732 in. water at 62 F 14.696 lb per square inch 2116 lb per square foot 33.94 ft water at 62 F 30.01 in. mercury at 62 F 29.921 in. mercury at 32 F 0.03609 lb per square inch 0.5774 oz per square inch 5.197,1b per square foot -{ 0.4330 lb per square inch 62.37 lb per square foot 0.4897 lb per square inch 7.835 oz per square inch 1.131 ft water at 62'F 13.57 in. water at 62 F . = 0.49115 lb per square inch Metric Units 1 cm . . = 0:3937 in. = 0.0328 ft - 1 in. . ' = 2.540 cm 1 m - = 3.281 ft lft 1 sq cm `. * .. . . = 0.3048 m , = 0.1550 sq in. - , 1 sq in. ; 1 sq m 'a . = 6.452 sq cm - .` , = 10.76 sq ft 1 sq ft . = 0.09290 sq m 1 cu cm ` . = 0.06102 cu in. -- 1 cu in. 1 cu m * *' . = 16.39 cu cm = 35.31 cu ft . ` . 1 cu ft 1 liter . '. .. . = 0.02832 cu m = 1000 cu cm = 0.2642"ga! . .. 1 kg ' ' ' '' , ' = 2.205 lb (avdp) 1 lb r\ . . . = 0.4536 kg .- 1 metric ton = 2205 lb (avdp) ' 1 gram = 0.002205 lb. (avdp) ,- 1 kilometer per hour ' = 0.6214. mph - - 1 gram per square centimeter. . _ f 0.02905 in. mercury at 62 F \ 0.3942 in. water at 62 F . 1 kg per sq cm (metric atmosphere) = 14.22 lb per square inch *i \ 1 gram per cubic centimeter. ' _ f 0.03613 lb per cubic inch. . \ 62.43 lb per cubic foot 1 dyne : = 0.00007233 poundals - 1 absolutejoule ... _ / 10,000,000 ergs . ~ \ 0.7376 ft-lb .. . ` 1 Int. joule ", = 0.7378 ft-lb 1 metric horsepower ^ f 75 kg-m per second . ~ \ 0.986 hp (U. S.) ._ 1 I. T. kilocalorie per kilogram . = 1.8 Btu per pound 1 I.T. calorie per square centimeter - = 3.687 Btu per square foot 1 I.T. calorie per (second) (square centimeter) for , f2903 Btu per (hour) (square.foot) a temperature gradient of 1 .C. deg per'centi:. = -J for a temperature gradient of1 F meter' **"."'* ' " ; ' 1' ' (deg per inch.of thickness: : , Jktirvtjiations and Symbols_ 17 GRAPHICAL SYMBOLS FOR DRAWINGS6 Graphical Symbols for Drawings (, Piping Heating 1. High Pressure Steam . 2. Medium Pressure Steam 3. Low Pressure Steam , 4. High Pressure Return 5. Medium Pressure Return . 6. .Low Pressure Return . 7. Boiler Blow'Off 8. Condensate or Vacuum Pump Discharge 9. Feedwater Pump Discharge 10. Make Up Water 11. Air Relief Line . 12. Fuel Oil Flow . ' 13. Fuel Oil Return 14. Fuel Oil Tank Vent . 15. Compressed Air . * 16. Hot Water Heating Supply . --00-- --00-- --00-- --------- FOR----------------- FOV--------- Air Conditioning . . 18. Refrigerant Discharge ' 19. Refrigerant Suction . 20. Condenser Water Flow 21. Condenser Water Return 22. Circulating Chilled or Hot Water Flow 23. Circulating Chilled or Hot Water Return 24. Make Up Water ' 25. Humidification Line 26. Drain 27. Brine Supply . ; 28. Brine Return -------------------;-----RD ....................... -------------- C------------------ ---------CR--------- ---------------- CM------------- - ------------------ p ---------- 8--------------- Plumbing . 29. Soil, Waste or Leader (Above Grade) 30. Soil, Waste or Leader (Below Grade) 31. Vent 32. Cold Water 33. Hot Water * . 34. Hot Water Return - 35. Fire Line 36. Gas 37. Acid Waste 38. Drinking Water Flow 39. Drinking Water Return 40. Vacuum Cleaning . 41. Compressed Air `. ACIO --A- Sprinklers . 42. Main Supplies . 43. Branch and Head 44. Drain . . ,' - ' ** ' 1 s* --o-- ------- s_______ 'Graphical Symbols for Use on Drawings in Mechanical Engineering. Z32.2-1941 (American Standards Association). .^ , 18 CHAPTER 2 - . ____________ 1946 Guide Graphical Symbols for Drawings Ductwork 45. Duct (1st Figure, Width; 2nd, Depth) 46. Direction of Flow . 47. Inclined Drop in Respect to Air Flow . 48. Inclined Rise in Respect to Air Flow 49. Supply Duct Section 50. Exhaust Duct Section 51. Recirculation Duct Section 52. Fresh Air Duct Section 53.- Other Duct Sections 54. Register 55. Grille 56. Supply Outlet . ' . ----- 12*20 ------- 12*20 ----- --12*20 GEU- __ (Label) Kitchen Exh. ,.R .G I 57. Exhaust Inlet . 58. Top Roister or Grille 59.* Center Register or Grille 60. Bottom Register or Grille . 61. Top and Bottom Register or Grille 62. Ceiling Register or Grille . 63. Louver Opening ' . 64. Adjustable Plaque H-- TR] 20*!2- 700cfm TS 20*12-- 700 cfm CR^ 20*12- 700cfm . Cg"20*12-- 700cfm BR) 20 *12- 700cfm BCT20*12- 700cfm Te.BR 20*12- eat. 700 cfm Te.BG 20 *12-ea. 700 cfm \ p'. ,.n CR 20 *12 - 700 cfm 20*12-- 700Cfm I L 20 * 12 - 700 c fm P-20*l2~700cfm ' --i . , - 1L__ --i '' <tr = P-20"<p-700cfm' dKKrr.vidtibhs.afid Symbols _ 19 Graphical Symbols for Drawings '65. Volume Damper i: 5' r , 66. Deflecting Damper Ductwork 1 I '--Plan X . E/ev. ` ' - 67. Deflecting Damper, Up 68. Deflecting Damper, Down 69. Adjustable Blank Off 70. Turning Vanes r I- ] -p-------- TR 20*12 71. Automatic Dampers 72. Canvas Connections 73. Fan and Motor With Guard 74. Intake Louvers and Screen. * 1 ^------------y- 20 . . CHAPTER 2 ___________. -1946 Guide Graphical Symbols for Drawings 75. Heat Transfer Surface, Plan 76. Wall Radiator, Plan 77. .Wall Radiator on Ceiling, Plan 78. Unit Heater (Propeller), Plan 79. Unit Heater (Centrifugal Fan), Plan 80. Unit Ventilator, Plan Traps ' 81. Thermostatic 82. Blast Thermostatic 83. Float and Thermostatic 84. Float 85. Boiler Return . Valves 86. , Reducing Pressure 87. Air Line ; 88. Lock and Shield 89. Diaphragm .' . 90. Air Eliminator 91. Strainer . 92: Thermometer . 93. .Thermostat . Heating and Ventilating I T~1 o> Qp- <&=> A- e JL Abbreviations and Symbols 21 Graphical Symbols for Drawings l Thermostat ' (Self Contained) ; /C\ Qj/ HO. Low Side Float i. Thermostat (Remote Bulb) JCT1 1 => 0, m. Gage Refrigerating ,96. Pressurestat :-dU ,112. Finned Type Cool . ing Unit, Natural Convection 97. Hand Expansion Valve 98. Automatic . Expansion Valve 99- Thermostatic Expansion Valve 113. Pipe Coil 114. Forced Convection Cooling Unit' 10b. Evaporator Press. Regu lating Valve, Throttling Type .' . 101. Evaporator Press. Regu lating Valve, Thermo static-Throttling Type 102. Evaporator Press. Regu lating Valve, Snap-Ac- J tion Valve .. 115.. Immersion Cooling Unit . .116. Ice Making Unit -(-*- 117. Heat Interchanger 118. Condensing Unit, Air Cooled . 103. Compressor'Suction -R>-Pressure Limiting Valve, ' Throttling Type t 119. Condensing Unit, : Water Cooled 104. Hand Shut Off.Valve 105. Thermal Bulb .Tf."i20;: Compressor i 6 6- = - m 6_ . I ^ ' "H 106.1 Scale Trap i21. Cooling Tower 107/Dryer 108. Strainer 109. High Side Float 122. Evaporative Condenser 123. . Solenoid Valve 124. Pressurestat With -rFh-- High Pressure Cut Out 22 CHAPTER 2 1946 Guide IDENTIFICATION OF PIPING SYSTEMS BY COLOR The color scheme for identification of piping systems listed in the following table and shown in Fig. I is reprinted from Part V, Fourth -Edition, of the Engineering Standards of the Heating, Piping and. Air Conditioning Contractors National Association, All piping systems are classified according'to the material carried in the pipes and colors are assigned as follows: Class . F--Fire-protection D--Dangerous materials S--Safe Materials ' ' and, when required P--Protective materials V--Extra valuable materials Color Red Yellow or Orange '. Green (or the achromatic colors, white, black,' gray or aluminum). Bright blue Deep purple .. i *From Scheme for Identification 'of Piping.Systems, Beating. Piping and Air Conditioning Contractors ' National Association,.P*it V, Fourth Edition, p. 17. Used by permission. '- 23 SPECIFIC HEAT Table 1. Specific Heat of. Solids*. Alloys Materials . Cued-- Glass . Rocks^ Zinc. ................... ....... -- Temperature F Specific Heat Authority 32 32 .57-208 68-2370 80-212 68-208 104-1637 . 64-212 77-1832 0.0899 0.0883 0.0862 0.127 0.212 0.195 0.195 0.314 0.278 0.201 0.270 0.0928 0.258 S S. s s s s H I H . H. .H s .I 50-122 - . 50-122 . 0.161 0.117 S' . s 64 0.0312 s 0.259 H 32 0.487 s -40 . 0.434 s- 32 0.1043 ' .s 32-600 0.127 M 68-212 ' 0.1189 H 59-212 " 0.1152 H 32 . 0.0297 s 32 . 0.1032 s . 0.2159 H 58-212 ' 0.2 0.0319 /H . .S _ , ------- . 63-210 54-212 59-212 32-212 .32 240-320 77-1832 77 68 32 0.196 0.192 0.216 - 0.21 0.22 . 0.0536 0.1175 0.220 0.263 ' 0.0548 ' 0.327 . 0.0913 . , . S S S s s s H s.. . . . s s s Table 2. Specific Heat of Liquids Liquid 7 .end fMnltenl Sea Water Sn Gt 1.0043 Sn Gr 1.0463 S Temperature F Specific Heat 32 59-68 ' , 59-122 360 68 70-136 . 0.548 0.601 0.576 0.041 0.03325 0.511 64 0.980 - -64 ' 0.903 59 1.000 .. Authority .- . .. . S s. s H S:-' s ' - . ` s' * ' s1 s Table 3. Specific Heat of Gases and Vapors Substance Air. .. ........ Ammonia ' Carbon Dioxide Carbon Monoxide Coal Gas..... . Hydrogen Nitroven Oxveen Water Vanor Water Vanor ' . . Temperature F 32-392 80-392 52-417 79-388 68-1900 . 70-212 32-392 . 55-404 212 356 Specific Heat at Constant Pressure Ratio of ' Specific Heat Cp/Cr Specific Heat at Constant Volume (Computed). Authority 0.2375 0.5356 . . 0.2169 0.2426 0.3145 . 0.24 (Approx.) 3.41 0.2438 - 0.2175 0.421 0.51 - 1.405 1.277 1.3003 . 1.395 --------. 1.419 l.il 1.3977 1.305 .-------- . 0.169 . 0.419 0.1668 0.1736 -------- 2.402 0.1729 0.155 0.322 -- S .. -s S s .s H >s - S. 'S S S . ' ' .. "See also The Specific Heat of Thermal Insulating Materials, by Gordon B. Wilkes and Carl O. Wood ` (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 493). . . . .' Notes: When one temperature is giventhe true specific heat is given, otherwise the value is the mean specific heat between the given limits. ` ., , . ,. , .J * Authorities: S--Smithsonian Physical Tables. 1933: I--International Critical Tables;;H--Heating. ventilation and Air Conditioning^ by L. A. Harding and A. C. Willard;'M--Engineers' Handbook, byr' S Lionel S. Marks. '- ' *. CHAPTER 3 Dkermodi erm.oclifna.micA Degree of Saturation; Mollier Diagram; Derived Properties; Typical Air Conditioning Processes, Heating, Cooling, Adiabatic Mixing; Wet-Bulb Temperatures Below 32 F; Dalton's Rule; Steady Flow Energy Equation, U. S. Standard Atmosphere THE working substance of the air conditioning engineer is called moist air. In order to be able to apply the laws of conservation of energy and mass to the analysis of typical air conditioning processes, it is necessary to know the thermodynamic properties of moist air, particu larly its enthalpy and volume. When the limitations imposed by the Second Law of Thermodynamics have to be considered, it is also necessary to know its entropy. - , For the purpose of analysis, moist air may be regarded as a mixture of only two constituents, namely, dry air and water vapor. It has long been customary to predict the thermodynamic properties of the mixture from a knowledge of those of dry air and water vapor separately by means of Dalton's Rule. According to this rule: each constituent of a gas -mixture occupies the whole volume of the mixture just as if no other constituent were present; it therefore exerts a partial pressure equal to the pressure it would exert if alone in the whole volume at the temperature of the mixture; the observed pressure of the mixture is the sum of these so-called partial.pressures; the enthalpy of the mixture is the sum of separate contributions from the individual constituents as determined by their partial pressures, their weights, and the temperature of the mixture; and the entropy of the mixture is obtained in a similar manner. . Dalton's Rule has long been regarded erroneously as a fundamental law of nature. Actually it is not, and in many cases its predictions are quite unreliable. In the case of moist air at atmospheric pressure, it happens to give a close approximation to the truth; but as progress is made the need for greater accuracy than the rule can afford is felt even .. in this case. Fortunately most of the complications involved in following ' a correct procedure based on the predictions of statistical mechanics are met in preparing suitable tables of thermodynamic properties; and, once these tables have been prepared, their use in the analysis of typical air conditioning processes is actually simplified by abandonment of the rule . together with its fictitious concepts of partial pressure, relative humidity, etc. , .' Thermodynamic Properties oi Moist Air . Table I, Thermodynamic Properties of Moist Air' (Standard Atmospherie Pressure, 29.921 In. Hg), contains results of a cooperative investi gation between the American Society of Heating and Ventilating . Engineers and the.Towne Scientific School, University of Pennsylvania. These results are to be considered by an International Joint Committee on Psychrometric Data as a possible starting point'from which to reach agreement on standard properties of moist air, A detailed explanation of the data and methods used in constructing Table 1 is given in a paper 1 recently presented before the ASHVE upon the; recommendation-of its . 24 Thvrniodvnamics . 25 Technical Advisory Committee on Psychrometry as a final report of the. cooperative investigation. . In Table 1 there are 15 columns of figures, each column being headed by a suitable symbol. In the following sub-paragraphs are given brief explanations of the data in Table 1 under the appropriate column headings. i(F) = Fahrenheit temperature defined in terms of absolute temperature T by the relation, T = t + 459.69 (1) This particular Fahrenheit scale differs slightly from that derived from the Inter national Centigrade Scale 1(C) by the definition, - ((F) = 1.81(C) 4- 32 ' ' (2) However, the maximum difference between the two Fahrenheit scales appears not to exceed 0.01 Fahrenheit deg in the range 32 to 212 F. Ws - humidity ratio at saturation. By humidity ratio is meant the ratio, by weight, of water vapor to dry air, pounds of water vapor per pound of dry air. By saturation is meant the point where coexistence of the vapor phase (moist air) with a condensed phase (liquid or solid) is possible at the given temperature and pressure (standard atmos-. pherie pressure in the case of Table 1). At given values of temperature and pressure the humidity ratio W can have any value from zero to Ws. t>a = specific volume of dry air, cubic feet per pound. ,,as = vs tia, the difference between the volume of moist air at saturation, per pound of dry air, and the specific volume of the dry air itself, cubic feet per pound of dry air. Vs = volume of moist air at saturation per pound of dry air, cubic feet per pound of dry air. /,a = specific enthalpy of dry air, Btu per pound. It will be noticed that the specific enthalpy of dry air has been assigned the value zero at 0 F, standard atmospheric pres sure. The energy unit Btu is related to the foot-pound, though not exactly by definition, as follows: 1 Btu = 778.18 ft-lb. ' ". has = hs -- Aa, the difference between the enthalpy of moist air at saturation, per pound of dry air, and the specific enthalpy of the dry air itself, Btu per pound of dry air. As = enthalpy of moist air at saturation per pound of dry air, Btu per pound of dry air. Ja = specific entropy of dry air, Btu per (pound) (F). It will be noticed that the specific entropy of dry air has been assigned the value zero at 0 F and standard atmos pheric pressure. . ' jas = Js -- 5a, the difference between the entropy of moist air at saturation, per pound of dry air, and the specific entropy of the dry air itself, Btu per (pound of dry air) (F). 5s = entropy of moist air at saturation per pound of dry air, Btu per (pound of dry air) (F). ' ' ' Aw = specific enthalpy of condensed water (liquid or solid) at standard atmospheric pressure, Btu per pound of water. The specific enthalpy of liquid water has been as signed the value zero at 32 F, saturation pressure. It will be noticed that, under this assignment, the specific enthalpy of liquid water at 32 F,`standard atmospheric pressure, assumes the value 0.04 Btu/lbw 5W = specific entropy of condensed water (liquid or solid) at standard atmospheric pressure. Btu per (pound'of water) (F). The specific entropy of liquid water has been , assigned the value zero at 32 F, saturation pressure. It will be noticed that, under this assignment, the specific entropy of liquid water at 32 F, standard atmospheric pressure, is also zero, though not exactly. `. ps - saturation pressure of pure water vapor, pounds per square inch or inches of Hg. Moist air can be saturated at any given values of temperature and pressure, though this requires that it have a definite humidity ratio Ws and that the coexisting condensed phase contain a definite, but very small quantity- of dissolved air. On the other hand, pure water vapor (steam) cannot be saturated at any given values of temperature and pressure because its composition is invariable. It can, however, be saturated at any T a b l e 1.' h e r m o d y n a m ic .P r o p e r t ie s o f M o is t A ir * (St a n d a r d A t m o s p h e r ic P r e s s u r e , 29.921 i n . H g)T T a b l e 1. h e r m o d y n a m icT P r o p e r t ie s o f M o is t A ir " (St a n d a r d A t m o s p h e r ic P r e s s u r e , 29.921 i n . H g) (Continued) Compiled by John A. Goff and S.` Gratch. 26 CHAPTER 3 __________________ 1946 Guide az oSf-c_u !x<. S_-- "0# OOt-OO eoteOo-e^oeeOo c0o9c- i f m 111r 7777 7777 Mil. 1 1 II 7777 71 1-5 dc . 5* .e OwUT * d 5 3 J6 Cm Ww . oCaOoCOoO CkO)^m<t~eOn. 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IOQOOOOON 0O0O0)--0'0--9 - 80--9 0n090oc--39o0oo9* C_9'_<0_ p__o o* --aooeso Tfi*coiopd *O0O0v) . 3-0*T0j<' . MM. MM IMI: I 1.1 I . OfflK5S2 oOeOoc--oeeoo '3e9oe--oeOocO9 771 1, 7777 7777- Thermodynamics  - ifc 0CD010s*)C0O N00--)O0 O00 CHAPTER 3 o00o0n0oooiooo *r me* 00 00 00 00 MM MM IIM II II MII II II Mil MM .MM II II Mil II II 1 II 1 Mil mm* M 1 l: T a b l e 1. T h e r m o d y n a m ic P r o p e r t ie s o f M o is t -A ir * (S t a n d a r d A t m o s p h e r ic P r e s s u r e , 29.921 i n . H g) (Continued) .os < gg2 - j / u3 . ' ; oNOeMoIO<oNitOO-l os uH S S lzaa/l o U sisss TTTT 3b H * ii g. s? e - H u m id ity /E nthalpy u l b dry 3. . CQ *0s a < > Oi ii s' . SF et a. S m E n th a lp y B tu/Lb h-w E n tro p y B tu /^ L b ) Sw nhmcONoMOIoOCnOO * O) IN C4 MM * 08iQ)0-f6M1 . 00h0C5 S00. 00WOO00 JKNH 00 00 CO 00 1.369 , 1.489 1.617 1.756 9.147 9.173 9.198 9.224 0.000 0.000 0.000 0.000 NVNNiAOMOWnfl t--ON--ONCD OO o o. 0)0 05 0) ' 1.906 2.068 2.242 2.430 0.000 0.000 0.000 0.000 2.034' 2.852 3.089 3.342 | 0.000 0.000 0.000 0.000 3.015 3.909 4.225 4.564 i 9.451 9.477 9.502 9.527 0.000 .0.000 0.000 0.000 nOjCCnSOvONsWiHi N* IQ IQ CO 9.553. 0.000 1 9.578 0.000 9.604 0.000 1 9.629 0.000 6.677 7.196 7.753 8.349 9.654 9.680 9.705 9.730 0.000 0.000 0.000 0.000 oooooooooooo dodo 8.990 9.675 10.40 11.19 9.756 9.781 9.806 9.831 4000 0)0)0) 12.03 12.92 13.88 14.91 O0OJ0Ot0~O"0OIN0) 0.000 0.000 0.000 0.000 9.147 9.173 , 9.198 9.224 -2 3 .0 7 5 -22.835 -22,694 -22.353 0.001 0.002 0.002 0.002 -23.074 -22.833 -22.692 -22.341 -0.05631 -0.05565 -0.05500 -0.05434 IoNooIoN oIoNooCD oooo 9.249 9.275 9.300 9.325 9.351 9.370 9.401 9.426 -22.113 -21.872 -21.631 , -21.391 j -2 1 .1 5 0 1 0.003 -2 0 .9 0 9 0.003 -2 0 .6 6 9 0.003 -2 0 .4 2 8 0.003 : 9.451 -2 0 .1 8 8 9.477 i -1 9 .9 4 7 0.502 1 ! -19.706 9.527 -1 9 .4 6 6 0.004 0.004 0.004 0.005 -0.05369 -0.05303 -0.05237 -0.05172 -21.147 -0.05107 -20.900 -0.05042 -20.666 -0.04978 -20.425 j -0.04913 -20.184 1 -1 9 .9 4 3 -1 9 .7 0 2 -19.461 -0.04849 -0.04785 -0.04721 -0.04658 9.553 9.578 9.604 9.029 -19.225 -18.984 -18.744 -18.503 0.005 0.005 0.006 0.006 -19.220 -0.04595. -18.979 I -0.04532 -18.738 -0.04469 -18.497 -0.04400 1 9.654 9:680 9.705 9.730 -18.263 -18.022 -17.782 -17.541 0.007 0.007 0.008 0.008 -18.256 -18.015 -17.774 -17.533 -0.04343 -0.04280 -0.04218 -0.04155 110*0 110*0 010*0 6000 rClo-OtscI--HooCooOo-noH 00)0)0) -17.301 -17.060 - r 16.820 -1 6 .5 7 9 ' -17.292 -17.050 -16.809 -10.568 -0.04093 -0.04031 -0.03969 -0.03908 eCOoOOoOO)OCOoOtNC-D* CO *Q IQ .MM 9.850 9.882 9.907 0.932 0.012 0.013 0.014 0.015 -10.327 -10.085 -15.844 -15.602 -0.03840 -0.03785 -0.03724 -0.03063 S)sj*sj< oooooooooooooooo o o" do CooooOCooooO ooooCO oooorf oooo .oooooooooooooooo oooo 0.00000 0.00000 0.00000 0.00000 0.00001 0.00001 0.00001 0.00001 0.00001 0.00001 0.00001 i 0.00001 0.00001 0.00002 1 0.00002 0.00002 0.00002 0.00002 0.00003 0.00003 -0.05631 -0.05565 -0.05500 -0.05434 -0.05368 -0.05302 -0.05230 -0.05171 -0.05106 -0.05041 -0.04977 -0.04912 -0.04848 -0.04784 -0.04720 -0.04057 -0.04594 1 -0.04530 -0.04467 -0.04404 -0.04341 -0.04278 -0.04215 -0.04152 -0.04090 -0.04028 -0.03900 -0.03904 -0.03842 -0.03781 -0.03720 -0.03658 -1 9 9 .7 3 -199.35 -198.97 -198.59 -0.4235 -0.4225 -0.4214 -0.4204 -198.21 -197.83 -197.44 I -197.00 -0.4193 -0.4183 -0.4173 -0.4162 -196.67 -0.4152 -196.29 -0.4142 -195.90 -0.4131 -195.51 ! -0.4121 -195.12 -194.73 -194.34 -193.95 -0 .4 1 1 0 -0.4100 -0.4090 -0.4079 -193.55 -0.4009 -193.16 -0.4059 1 -192.76 -0.4048 -192.37 -0.4038 '-0 .4 0 2 7 -0.4017 -0.4007 -0.3990 -190.37 -189.97 -189.56 -189.16 -0 .3 9 8 6 -0.3975 -0.3905 -0.3954 -188.75 -188.35 -187.94 -187.53 -0.3944 -0.3934 -0.3924 -0.3913 0.6542 0.7111 0.7725 0.8388 0.9105 0.9879 1.071 1.101 1 1.728 1.868 2.019 2.181 2.356 2.543 2.744 2.960. 3.192 3.441 3.707 3.092 4.298 4.625 4.976 6.351 5.752 ' 6.181 6.640 7.130 WODNONIIN-* fIr-t*. CO NNrMtOsO) OCD0CtsD.COCOO^ `Compiled by John A .'G off and S. Gratch. T a b l e 1. T h e r m o d y n a m ic P r o p e r t ie s o f M o is t A ir * (S t a n d a r d A t m o s p h e r ic P r e s s u r e , 29.921 i n . H g) (Continued) oooot^ot-or*r-. SNSN - itNS.t--S-tON.OC3) .1946 Guide 0CD0 tC-Ds CCOO ICQO Thermodynamics `Compiled by John A. Goff and S.'Gratch. '( a Io 30 . fu V a ca c O U a ' OS fc,-* toH'* 2? o a ^CQ , XQ O z, o e< os* s td 06 D cinn U a, y 2 a si X ? sp04 CO O os H 0. < Qat < Q Z H(/) a *' at < as in O S S **S t,' CO . a H os fcl 04 ,o . aS cu . yi 2 < >' 2- OS ti X U w a-< . 'CQ a `< IV WHO WPS CON 1 1 II cor-o'us WWWW MM CHAPTER 3 WWW*-* WWWW 1M 0#N W^ Mil H cq s .`Shu jj*- ' . ' sgto /V o lum e ft lb dry /E nthalpy u lb dry -kSa f ! s . . 'nNWW *0 0*0 0 uspsoco NNNO 11 11 i oocew.w . n>wiq - 00f-WUS WWWW MM. Mil www-* * 0005S NNNP) If II 1 1 1 1 -HMM OOOO WWW PS PS PS PS wpswus 1 .0 4 9 1.750. 1.856 1 .9 6 9 2 .0 8 7 2 .2 1 2 2 .3 4 4 2 .4 8 3 2 .6 3 0 2 .7 8 5 2 .9 4 8 3 .1 2 0 4 .1 2 5 4 .3 5 9 4 .6 0 6 4 .8 6 5 5 .1 3 7 5 .4 2 3 5 .7 2 4 6 .0 4 0 0 .3 7 1 6 .7 2 0 7 .0 8 5 7 .4 0 9 1 0 .7 0 9 10.794 1 0 .8 2 0 1 0 .8 4 5 00 ..00 00 22 0 .0 0 2 0 .0 0 3 10.771 ! 10.796 10.822 ; 10.848 1 0 .8 7 0 10.896 10.921 10.040 0.003 0 .0 0 3 0 .0 0 3 0 .0 0 4 '1 0 .8 7 3 10.899 : 10.924 10.950 10.972 10.997 11.022 . 11.048 0 .0 0 4 0 .0 0 4 0 .0 0 4 0 .0 0 4 10.970 11.001 11.026 11.052 ooog oooo dodo' 11.073 1 1 .0 9 8 11.124 1 1 .1 4 9 11.078 11.103 11.129 11.155 11.174 11.200 11.225 11.250 0 .0 0 0 6 0 .0 0 0 0 .0 0 7 0 .0 0 7 11.180 1 1 .2 0 6 . 11.232 11.257- os ao do oo S8SS' dodo 11.275 11.301 11.320 U -351 11.376 I 11.401 11.427 11.452 1 0.009 0 .0 1 0 0 .0 1 0 0 .0 1 1 11.283 11.309 11.334 11.369 11.385 11.411 1 1 .4 3 7 11.403 ! 11.477 11.502 11.528 11.553 0.012 11.489 0:013 11.515 0 .0 1 3 . 11.541 0.014 11.567 WWOOW NWW 'do MM WWWW OONCO oouspso Wi'i' MM -7 .0 8 7 -7 .4 4 7 -7 .2 0 7 -0 .9 0 6 -0 .7 2 0 -0 .4 8 0 -0 .2 4 0 -6 .0 0 5 -5 .7 0 5 -5 .5 2 5 -5 .2 8 5 -6 .0 4 4 0 .1 3 6 0 .1 4 5 ' 0.154 0 .1 0 3 0 .1 7 3 0 .1 8 4 0 .1 9 6 0 .2 0 7 0 .2 1 9 0 .2 3 2 0 .2 4 6 0 .2 0 1 -3 .8 4 3 0.348 -3 .0 0 3 0.368 -3 .3 0 3 i 0.389 -3 .1 2 3 0.412 --22 ..08 48 22 0 .4 3 6 0.461 -2 .4 0 2 -2 .1 6 2 : ' 0 .4 8 7 0 .5 1 4 -1 .9 2 2 0.543 -1 .6 8 1 1 0.674 -1 .4 4 1 0.006 -1 .2 0 1 0.639 0 .0 7 5 . 0.712 0 .7 5 1 0 .7 9 2 snoco t- -- w .wwww dodo -0 .0 1 7 3 3 -0 .0 1 0 7 7 -0 .0 1 6 2 1 -0 .0 1 5 0 5 WWOOO *00*00) iflcoos w w w us MM -0 .0 1 5 0 9 -0 .0 1 4 5 3 -0 .0 1 3 9 8 -0 .0 1 3 4 2 -5 .5 4 0 1 -0.01287 -5 .2 9 3 -0.01232 -5 .0 3 9 . -0.01177 -4 .7 8 3 | -0.01122 -4 ,5 2 7 -4 .2 7 1 -4 .0 1 4 -3 .7 6 5 -0 .0 1 0 0 7 -0 .0 1 0 1 2 -0 .0 0 9 5 8 -0 .0 0 9 0 4 -3 .4 9 5 -0.00850 -3 .2 3 5 -0.00796 j -2 .9 7 4 -0 .0 0 7 4 3 -2 .7 1 1 -0.00689 W -H US 00 W --3>S pi pi-* J 1. 1 1 .1. -0 .0 0 6 3 0 -0 .0 0 5 8 2 -0 .0 0 5 2 9 -0 *0 0 4 7 5 -1 .3 7 9 ! --01 ..81 30 57 -0 .5 6 2 -0 .0 0 4 2 2 -0 .0 0 3 6 9 -0 .0 0 3 1 6 -0 .0 0 2 0 3 . -0 .2 8 6 -0 .0 0 9 0 .2 7 1 0 .5 5 2 -0 .0 0 2 1 0 -0 .0 0 1 5 7 -0 .0 0 1 0 5 -0 .0 0 0 5 2 w-- * cer-ous. W PSP* -- 7771 II 11 1111 `Compiled by John A. Goff and S. G ra tc h .. 0.00034 0 .0 0 0 3 0 0 .0 0 0 3 8 0 .0 0 0 4 0 0 .0 0 0 4 3 0 .0 0 0 4 5 0 .0 0 0 4 8 0 .0 0 0 5 1 - 0 .0 0 0 5 4 0 .0 0 0 5 7 0 .0 0 0 6 1 0 .0 0 0 6 4 ' 0 .0 0 0 6 8 0 .0 0 0 7 2 0 .0 0 0 7 0 0 .0 0 0 8 0 0 .0 0 0 8 4 0.00089 0.00094 0 .0 0 0 9 0 0.00104 0 .0 0 1 0 9 0 .0 0 1 1 6 0.00121 0 .0 0 1 2 8 0 .0 0 1 3 5 0.00142 0.00149 0 .0 0 1 5 7 0 .0 0 1 6 5 0.00174 0.00183 > OS ' 25' E n th a lp y B tu /L b Aw ? -0 .0 1 0 0 9 -0 .0 1 0 4 1 -0 .0 1 5 8 3 -0 .0 1 5 2 5 -1 7 3 .5 2 -1 7 3 .0 8 -1 7 2 .0 4 -1 7 2 .2 0 0.3573 -0 .3 5 0 3 -0 .3 5 5 2 -0 .3 5 4 2 0 .6 2 0 9 3 0.65979 0 .7 0 0 4 0 0.74305 -0 .0 1 4 0 0 -0 .0 1 4 0 8 -0 .0 1 3 5 0 -0 .0 1 2 9 1 -1 7 1 .7 5 -0.3531 -171.31 -0.3521 -1 7 0 .8 6 1 -0.3511 -1 7 0 .4 2 -0 .3 5 0 0 0 .7 8 9 2 8 0 .8 3 7 4 8 0 .8 8 8 3 8 0 .9 4 2 1 2 -0 .0 1 2 3 3 -0 .0 1 1 7 5 -0 .0 1 1 1 6 -0 .0 1 0 5 8 -1 0 9 .9 7 -1 6 9 .5 2 -1 6 9 .0 7 -1 6 8 .6 2 -0 .3 4 9 0 -0 .3 4 8 0 -0 .3 4 6 9 -0 .3 4 5 9 0 .0 9 8 8 5 1.0587. 1.1219 1 .1 8 8 6 -0 .0 0 9 9 9 -0 .0 0 9 4 0 -0 .0 0 8 8 2 -0 .0 0 8 2 4 -1 0 8 .1 7 -1 0 7 .7 2 -1 6 7 .2 6 -1 6 6 .8 1 , -0 .3 4 4 9 -0 .3 4 3 9 -0 .3 4 2 8 -0 .3 4 1 8 1.2587 1.3327 1.4107 1.4029 -0 .0 0 7 6 6 -0 .0 0 7 0 7 -0 .0 0 0 4 9 -0 .0 0 5 9 0 -1 6 0 .3 5 -1 6 5 .9 0 -1 0 5 .4 4 -1 0 4 .9 8 -0 .3 4 0 8 1.5795 -0 .3 3 9 8 I 1.6700 -0 .3 3 8 7 1.7660 -0 .3 3 7 7 ! 1.8677 -0 .0 0 5 3 2 -0 .0 0 4 7 3 -0 .0 0 4 1 4 -0.00354 . WiQWOOOWh W WWW wwww 7777 -0 .3 3 6 7 -0 .3 3 5 7 -0 .3 3 4 0 1 -0 .3 3 3 6 1.9740 2.0859 2.2035 2:3272 -0 .0 0 2 9 4 -0 .0 0 2 3 4 -0 .0 0 1 7 4 -0 .0 0 1 1 4 -1 0 2 .6 7 -1 6 2 .2 1 -1 0 1 .7 4 -1 0 1 .2 8 -0 .3 3 2 0 -0 .3 3 1 0 -0 .3 3 0 5 -0 .3 2 9 5 2.4573 2 .5 0 4 0 2.7377 2 .8 8 8 6 -0 .0 0 0 5 3 0 .0 0 0 0 8 0 .0 0 0 6 9 0.00131 -1 0 0 .8 1 -1 6 0 .3 4 -1 5 9 .8 7 -1 6 9 .4 0 -0 .3 2 8 5 -0 .3 2 7 5 -0 .3 2 0 4 -0 .3 2 5 4 3.0472 3.2137 3 .3 8 8 5 3.5720 - X as Is* T7Te*oTw 7777WDWW 7w 77'--o oop- w us II II .1946 Guide WWW-M MM Thermodynamics '_ os al_ tot- toH - w ps w uswr-oo o-*pww uswr^oo POIW'-*CW4PW4CW4 uNsNwNt^NooPi 0w w--wwwwwwww 'T a b l e 1. T h e r m o d y n a m ic P r o p e r t ie s of M o is t A ir 3 (St a n d a r d A t m o s p h e r ic P r e s s u r e , 29.921 i n . H g) (Continued) oas 5 5 V) z sa z0 a `g > 0 otsd^&- S OS -c . H CQ a O000Pw0IoWo-1wN--w dodo s es> W00OO0OO0OC4ONNCOOO , UCOSOPW4 PPO1)PWWJPww4 dodo- u P00S *ooo P00S00 N0* Ww a3< BSixw, H u m id ity R atio W x JO* V o lum e >O0S nj < u /E n t h a l p y u lb dry t dddod dddod dddod O -H PI PS W tOiflCNClO OOOOO 0.7872 0.8295 0.8739 0.9204 0.9692 1.020 -1.074 1.130 1.189 1.261 11.578 11.604 11.029 11.654 11.079 11.705 11.730 11.756 11.781. 11.806 OHNoO-PO*pIONMOw wON.NoU>StpN->woOqWoo 11.593 11.619 11.645 11.071 11.097 : . 1.201 1.441 1.681 1.022 2.102 0.835 1.120 1.408 1.698 1.991 OWN; 00 O -- PWW UJ W N- 00 ci pi pi pi pi pi P PS PS PS 1.315 1.383 1.454 1.528 I 1.600 nWW-UWoSoOWoNW---Nw. wW 0uINs0WPSI0WO0 PUJS -- N0W0 hN- HW00*Q rIQt J 1.958 11.983 12.009 12.034 12.059 . 0.032 0.034 0.035 0.038 0.040 12.084 12.110 12.135 12*160 12.186 0.042 0.044 0.040 0.049 0.051 12.211 12.236 12.262 12.287 12.312 uOC4sOPw4OPo4oOPo)OWo 11.850 11.883 11.910 . , 11.936 11.963 2.402 2.642 2:882 3.123 3.363 11.990 12.017 12.044 12.072 12.099 3.003 3.843 4.083 4.324 4.504 OwOWOwOOwONP*I0JPwuNs TP US US US L.d 12.126 12.154 12.181 12.209 12.237 1 ; 12.265 0.005 12.293 i 6.245 12.321 6.485 1 12.349 6.720 12.377 0.900 1.401 3.803 1.474 4.116 1.550 1 4.432 1.030 I 4.753 1.713 5.076 OO00P4CG0COOO0OO0P--4 -i J r- pi ci 5.403 6.735 6.071 0.412 0.756 ' 2.302 7.106 2.416 7.460 < 2.530 7.820 2.661 8.186 1 2.792 8.657 8.934 9.317 9.700 10.103 10.506 OP1P--4Pw4Pw4Pw4 POJSNPI^NN-cNPtS^WOMS' OONNWoONoNoNNoWwCwO-- pi ps ps ps ps PS PS w w w" w" oWPwiWWcWWoWcWoNw-Nw--NNNNNCO wUOSrOU~SOUpSOWuOWs cCOoNO--NOusNOusNO0Ow0 dddod . dddddo CwPOS PwPSSow0o0 0cwe0 P--wS owwc pi pi pi w' w' pi uWs wWPr-) gWo P4 OWW--WPJWwWwPwS 3.454 12.400 3.617 ' 12.434 3.788 ' 12.463 3.788 .12.463 3.944 12.492 4.107 12.520 - "Compiled by John'A. Goff and S. Gratch. . , Extrapolated to represent metastable equilibrium w ith undercooled liquid. U--SWWwNuQsO-NuOs-OW--OOUUOSS O -- -- -- w" pi 0Ww0 P0u0SsoOWo0 C0--O0 ww pi pi pi ps ps tad. H CQ g OO--OOoIOWN.OOW*P-OWwOrtWOWOw oddo'd 0.00000 0.00052 ! 0.00104 0.00156 i 0.00208 0.00260 0.00312 .0.00364 0.00415 . 0.00467 0.00192 : 0.00254 1 0.00310 0.00379 0.00442 0.00246 0.00258 0.00271 0.00285 0.00299 0.00500 0.00570 0.00035 0.00700 0.00760 0.00518 0.00569 0.00020 0.00071 0.00721 . 0.00314 0.00330 ; .0.00346 0.00363 0.00380 0.00832 0.00899 ; 0.00966 0.01034 0.01101 0.00772 0.00822 0.00873 0.00923 0.00973 0.00399 0.00418 0.00438 0.00459 0.00481 0.01171 0.01240 . 0.01311 0.01382 ' 0.01454 0:01023 0.01073 0.01123 0.01173 0.01223 0.00504 0.00528 0.00553 0.00579 0.00607 0.01627 0.01601 0.01670 0.01752 0.01830 0.01273 0.01322 0.01372 0.01421 0.01470 0.00035 0.00605 0.00690 0.00728 0.00761 ' 0.01908 0.01987 0.02068 0.02149 0.02231 0.01519 0.01568 . 0.01017 0.01017 0.01666' 0.01715 0.00790 0.00832 0.00870 0.00870 0.00904 0.00940 0.02315 0.02400 0.02487 0.02487 0.02570 0.02655 * 1 Eg*-" tdeo Enthalpy B tu /L b Aw i' - 158.93 -158.40 -157.99 -157.52 -157.04 Vap. Press In. Hg Pa X 10* -0.3244 -0.3234 -0.3223 -0.3213 -0.3203 3.7045 3.9666 ' 4.1785 4.4007 4.0337 -150.57 -156.09 -156.01 -155.13 -154.05* -0.3193 -0.3182 -0.3172 -0.3102 -0.3152 ' 4.8779 5.1339 5.4022 5.6832 5.9776 1 -154.17 -0.3141 -153.69 -0.3131 -153.21 -0.3121 ! -152.73 -0.3111 -152.24 -0.3100 ! 6.2858 6.6085 6.9462 7.2997 7.6690 -151.76 -0.3090 -151.27 -0.3080 1 -160.78 -0.3070 . -150.29 1 -0.3059 -149.80 -0.3049 , 8.0565 8.4612 8.8843 9.3267 9.7889 -149.31 -148.82 148.33 -147.84 -147.34 -0.3039 -0.3029 -0.3018 -0.3008 -0.2998 10.272 10.777 11.305 11.850 12.431 -146.85 -140.35 -145.85 -145.36 -144.86 -0.2988 -0.2977 -0.2967 -0.2957 -0.2947 13.032 13.659 14.313 14.996 15.709 0UW4S fWW-- UPOSS fP-S NCPO-- wUrPS W N-' 00 00 ao' -144.30 -143.86 -143.30 0.04 1.05 2.06 -0.2936 -0.2920 -0.2916 0.0000 0.0020 0.0041 8S 'Si 0.03106 0.03213 0.03323 0.00977 0.01016 0.01056 0.01097 0.01139 0.01183 0.01228 00(275 0.01323 I 0.01373 ! :8il8l? 0.01534 0.01591 0.01650 T able 1. T hermodynamic Properties of M oist.A ir3 (Standard Atmospheric Pressure, 29.921 in . H g) (Continued) 32' -- ` ~" ....... - CHAP-T-E-.R...3. ' 1946 Guide .. ............ .-- 11? 88S88 S333S SSS3S SSSSS SSSSg- 8S83S 8S5 1Kr mil ii! mi in in hi in 1Is III. Ill III III 111 III III! s JI- assss isiii'iiiis mu mm m 1 Ii mi ns mi li mi mi s: "g $ ini in in inn ms in ill E nthalpy/ Bto lb dry air III 111 II! Ill Si ill 111 i- |!!i III ii! Hill mu m 4- ill 'i!|| ||| III HI HI III V olume '/ cu ft lb dry air by John A. Goff and S .i s 111 1111111BI HI ill 111 1 mi uni m mis isi m isa S 111 III ill ill ill Hi Hi l!il ill ill ill! ill m mi 11?- SSSfeSS 3SSSS S3SS33 SSSSSS SSS3S 8S63S H umidity R a tio W* x 10* 34 1946 Guide > ' 1 is" . 12 x a Sb. S2S 23233 23322 ggsgg g|Sg| ggggS ggggg ' 5 mi 11111111 mi 1111.1111 in t > *! mI -cs sin iiai S X H M> J! # j CD < III ill II! Ill IS 85ill! *2 Sis. . fc.H~ II222 22235 22222 2225 22sS SSBSS H u m id ity R atio Wh x 10 by John. A. Goff and S,' 3 aa 1111 Illl'llllllllli 1111111111`lilH m m. mmm m <SS HI Hi ill in mi mi in c III! HI ill ilf 111 IIS III ? HI! HU III! Sill III! lill SHI *a? 111 11! ill III III 111 III >s ' /E n t h a l p y Btu lb dry a ir . . E ntropy . B t u p e r (F) ( l b d r y a ir ) 81.34 ! 0.04943 I 83.42 I 0.04985 85.56 1 0.05028 ! 87.76 0.05070 90.03 0.05)13 &' 3J=0J^" & a Enthalpy , B tu /L b hw * 0.1385 0.1403 0.1421 0.1438 0.1456 2.2439 1 2.3109 2.3707 2.4502 j 2.5225 * g 1111? mi mu mi iSfcS 1- 110.55 -113.46 1 116.46 \llji 1? i 136.4 iSi. 111:1 s8 : 0 .0 5 5 7 -3 0.05615 0.05739 1 I IK! 3.9558 4.0640 4.1765 4.2907 4.4076 !H.I m s ' 189.0 111:1 m ! 0.1902 i.T able T hermodynamic Properties of M oist A ir* (Standard Atmospheric Pressure, 29.921 in . H g) (Continued) by John A. Goff and S. Gratch. 36 CHAPTER 3 1946 Guide Thermodynamics . 37 given temperature (below the critical temperature), though this requires that it have a definite pressure ps and that the coexisting condensed phase have the same temperature and pressure. The yalues of saturation pressure listed in Table 1 have been computed from the formulae of Goff and Gratch *. - Thermodynamic Properties of Water at Saturation Table 2 offers revisions to existing steam table data 3 with extension downward to --160 F. These revisions and extension were a necessary preliminary to the construction of Table 1. A detailed explanation of the methods employed in constructing Table-2 is given in a paper * by John A. Goff and S. Gratch. As in Table 1 the temperature scale used as argument in Table 2 is the Fahrenheit scale defined in terms of absolute temperature T by Equation 1 whereas the Fahrenheit scale used as argument in exist ing steam tables is that derived from the International Centigrade scale by means of Equation 2. The symbols used as column headings in Table 2 . are the same as those used in the steam tables and have the same mean ings; therefore, a detailed explanation seems unnecessary. . : DEGREE OF SATURATION At given values of temperature and pressure the humidity ratio W of moist air can have any value between zero (dry air) and We (moist air at saturation). For convenience a parameter p. called alternatively degree of saturation or percent saturation is introduced through the definition, .. W = (ills . (3) Obviously the degree of saturation p. can "have any value from zero (dry air) to unity (moist air at saturation). To a degree of approximation within the estimated uncertainty of the data in Table 1 at temperatures below about 150 F, the volume v of moist air per pound of dry air at any degree of saturation p. may be computed from the simple relation, , V = a + iVis (4) To obtain comparable accuracy at temperatures above about 150 F it is necessary to add a correction term v as follows, . n(l - p)A 1 F aWe n (4a) where a denotes the ratio of the apparent molecular weight of dry air (28.966) to the molecular weight of water (18.016), namely, 1.6078. In Table 3 are given, for each of several higher temperatures, the correspond ing value of the coefficient A, the value of |i at which the correction term v attains its maximum value, and the maximum value of the correction term there attained. . At temperatures below about 150 F. the enthalpy h of moist air per pound of dry air at any degree of saturation p. may be computed from the simple relation, , . - - : / h = fia "h pfias. (5) ` To obtain comparable accuracy at temperatures above, about 150 F it is , by John A. Goff and S. Cratch. 38 li U.H a J' `o COhOUdtOtQ . OlQClOChO- omubd CHAPTER 3 OMU--5IO0 001- CDm ^ 7777 7777 177 i 7777 711 i 7777 7777 7777 TT able 2. hermodynamic Properties of Water at Saturation11 hoa rt >4b 'S' d a aa - 3H m > oa H Za m a cu D H a > " a-* 1 B Ha. - H ' =L>> . q|> a >H j a .u u ao. CO a a 3. w. u,, tf cl- 5 j S . -a < OIO mm ^QwW, d -- OOt^COlQ w 777 i 1777 i-i 7 i 7777 . 7^777 7777 7171 7777 1o* - ' 6 >M ` a 5* . CO . In. H g Sat. Solid tt Sat. S olid Ai Sat. V apor hg Sat. S olid | - Si , > a Fahr. T bmp. ', 0.4949 0.5592 0.6312 0.7121 0.8026 0.9040 1.017 1.144 '1 .2 8 8 1.444 1.620 1.816 2.035 2.278 2.549 2.850 3.184 . 3.556 3.967 4.423 4.928 5.487 6.106 6.790 7.546 8.380 9.301 10.32. . 11.44 12.67 14.03 15.52 ' . CojoNaiOoOo mdad -- cionn NSNN oooo dodo OdOwOoOotQmOo-^wv 36.07 32.03 28.47 . 25.32 1 36.07 32.03 28.47 . 25.32 ^0 O 00 O CO **- e4ci 1 0.01723 < 0.01723 0.01723 0.01723 22.54. 20.08 -1 17.90 i 15.97 22.54 20.08 - j 17.90 1 15.07 2.618 2.939 3.298 3.698 . 0.01723 0.01723 0.01723 . 0.01723 14.26 14.26 12.74 . 12.74 .11.39 11.39 10.19 10.19 nvos. . dt^wr* -- -- mm cot^d 4.143 . 0.01724 4 .6 3 9 ' '- I 0.01724 6.190 i 0.01724 5.803 0.01724 9,123 8.174 7.330 . 6.577 6.483 7.240 8.076 9.005 0.01724 0.01724' ,0.01724 0.01724 5.905 5.305 4.770 . .4.292 5.905 5.305 4.770 ' 4.292 10.03 11.17 12.43 13.82 ' 0.01724 0.01724 0.01724' 0.01724 . 3.864 3.864 ' 3.481 - 3.481 3.138 3.138 2.831 2.831. tQOOCDCD >m0m00o0c0o0 . d'dd -- MOOD Ol'V6O-$C<Od 15.36 17.06, 18.64 21.01 0.01725 0.01725 0.01726 0.01725 .2.555 2.308 2.086 - .1.886 0.01725 0.01725 0.01725 0.01725 1.707. . 1.545 1.400 1.269 n00olOo--eooo dddm NNNN Mil 2SgS NMNN till -2 2 2 .0 5 -2 2 1 .7 3 -2 2 1 .4 1 .-221.09 -2 2 0 .7 8 -2 2 0 .4 4 -2 2 0 .1 2 -219.79 -2 1 9 .4 7 -2 1 9 .1 4 -2 1 8 .8 2 -2 1 8 .4 9 -2 1 5 .4 9 -2 1 5 .1 6 -214.82 , -2 1 4 .4 8 -2 1 4 .1 4 -2 1 3 .8 0 -2 1 3 .4 6 -2 1 3 .1 1 ' -212.77 -2 1 2 .4 3 -2 1 2 .0 8 -2 1 1 .7 3 1212.43 1212.55 1212.67 1212.79 990.38 990.82 - 991.26 991.70 1212.90 1213.02 1213.15 1213.26 , 992.14 992.58 993.03 993A7 1213.38 1213.49 1213.62 1213.73 993.01. 994.35 994.80 995.24 1213.84 1213.95 1214.06 1214.17, 995.68 996.12 996.50 997.00 1214.28 1214.39 1214.40 1214.60 . 997.45 997.89 998.33 998.77 1214.70 1214.82 1214.92 1215.02 999.21 909.66 1000.10 1000.54 1215.12 1215.22 1216.32 1215.42 1000.98 1001.42 1001.86 1002.31 1215.52 1215.62 1215.71 1215.80 1002.75 1003.19 1003.63 1004.07 -0.4907 -0 .4 8 9 6 -0 .4 8 8 8 -0 .4 8 7 5 -0 .4 6 9 5 -0 .4 6 8 5 -0 .4 6 7 4 -0 .4 6 6 4 -0 .4 6 6 3 -0 .4 6 4 3 -0 .4 6 3 2 -0 .4 6 2 2 -0 .4 6 1 1 , -0.4601 -0 .4 5 0 0 -0 .4 5 8 0 SSOO MNNNSHNO dodo 1111 oOo0NioNo0aS'*o` dodo 1111 CdS ----1 --Oroa aTJoI "oSo' coTt-f dodo 1 II 1 g'COd C00O00Q0g*0> W0v0 dodo I i II . 4.0456 4.0325 . 4.0196 4.0067 3.5549 3.5429 3.5310 ' 3.5192. 3.9939 3.9812 ' 3.9685 3.9559 . 3.5075 3.4958' 3.4842 3.4727 3.9435 3.9311 3.9188 3.9065 3.8944 3.8823 3.87023.8583 3.4613' 3.4600 i 3.4387 3.4275 ' 1 3.4164 3.4054 - 3.3944 3.3835 3.8464 3.8346 3.8229 3.8112 3.3727 3.3619 3.3513 3.3406 3.7996 3.7881 3.7766 3.7653 3.3301 3.3198 3.3092 3.2989 3.7540 3.7428 3.7315 , 3.7205 3.2887 3.2785 3.2683 3.2583 3.7093 < 3.2482 3.6984 3.2383 3.6874 3.2284 3.6766 ' 3.2186 1 OClCWCWN COW-*W rowmm co co co 6* ^<m>r sd* --< Q0t'S*WW m --W CO CO cow .1946 Guide WdW--WCaM> d. a' O ' go c' .-too. O e` JS , o , >. " S -* o U . i ' . ' - Thermodynamics a z o H 2 D H C/3 H < as 03 H < > b> 'o cn a H ec ' Id a. 0 as CL, y 1 < >* QO s as B H M*WC* C4C4004 1777 ' 7777- 7777 1 II 1 7777, ora we ll .11 T a b le 2. (C o n tin u e d ' -its 'S' d te aa. 3 H m > oHa . z B CD a a. O H a >Q. < H Z B >^s B a j ec .K ac. H D u . di a. . >X a o- s >. o a u a0. cn a a i ak S4 J -- s a < * Lb/S q In. Sat. S olid I n . H g , t/j a CO cp5 o 2- ao, J,,t S a t. V a p o r S a t. S'o lid 1 > H Sat. V apor Sg 7T7? -1 1 2 --1n1 o1 -1 0 9 Cm<NC4N W CN -- graoof- concern OOOON QOr'cOtQ IN IN (N CM 1.716 1.897 2.095 2.312 2.551 2.812 3.099 3.413 3.757 4.133 4.544 4.993 5.484 6.019 6.604 7.241 7.030 ' 8.693 0.517 10.41 11.39 12.45 13.60 14.86 : ooraw 04 <D d O cc> c~` ra -- 22.91 24.04 27.15 29.54 dom'd , 3.494 3.862 4.265 .4.708 5.194 5.726 6.310 ,6.949 7,649 8.414 9.251 10.17 11.10 ' 12.20 13.44 14.74 . 16.16 17.70 10.38 21.20 23.19 25.35 27.70 30.25 ' 33;01 36.02 39.28 42.81 j 0.01726, ' 0.01726 0.01726 0.01726 0.01720 1 0.01728 ! 0.01726 1 ! 0.01720 .0.01720 0.01720 0.01727 0.01727 0 .0 1 7 2 7 0.01727 0.01727 , 0.01727 0.01727 0.01727 0.01728 - 0.01728 0.01728 ^ 0.01728 . 0.01728 0.01728 0.01728 0.01728 0.01728 0.01729 0.01729 0.01720 0.01720 0.01720 11.61 10.45 9.489 8.622. 11.51 10.45 0.489 8.622 7.839 7.131 0.491 . , . 5.911 ] 7.839 7.131 0.401 5.911 5.386 4.011 4.480 4.088 5.386 4.611 4.480 4.088 3.733 3.411 3.118 2.852 | | 3.733 3.411 3.118 2.852 2.610 2.389 2.189 2.006 1.839 1.687 1.549 1.422 2.610 2.389 2.189 2.006 1.839 1.687 1.540 1.422 1.307 1.201 1.104 1.016 1.307 1.201 1.104 1.016 0.9352 0.8613 0.7936 0.7314 . 0.9352 0.8613 . 0.7936 0:7314 o) com--i WWW oCICo4Co4Co4 MM -2 1 1 .3 9 1 1 -211.04 | -2 1 0 .0 9 -2 1 0 .3 4 -2 0 9 .9 9 -2 0 9 .0 4 -2 0 9 .2 8 -2 0 8 .9 3 1 -2 0 8 .5 8 , i --22 00 87 ..28 20 1 1 -2 0 7 .5 1 -j -2 0 7 .1 6 ; -2 0 6 .7 9 -2 0 6 .4 3 | -2 0 0 .0 7 | -2 0 5 .7 0 -2 0 5 .3 4 -2 0 4 .0 8 -2 0 4 .0 1 . ! 1 j -2 0 2 .7 7 -2 0 2 .4 0 -2 0 2 .0 3 -2 0 1 .6 5 -2 0 1 .2 8 -2 0 0 .9 0 -2 0 0 .6 3 -2 0 0 .1 5 1215.91 1216.00 1216.09 1216.18 1004.52 1004.96 1005.40 1005.84 -0 .4 5 6 9 -0 .4 5 5 9 -0 .4 5 4 8 ! -0 .4 5 3 8 3.6658 3.6551 3.6444 3.6338 3.2089 , 3.1992 3.1896 . 3.1800 1216.27 1000.28 -0 .4 5 2 7 1216.37 1006.73 -0 .4 6 1 7 1216.45 1007.17 -0 .4 5 0 6 1216.54 1007.01 -0 .4 4 9 6 3.6232 3.6127 3.6022 3.5919 3.1705 3.1610 3.1516 3.1423 , oo t-com <* mC* -J< "* odd MM 1216.63 1210.71 1216.80 1216.89 1008.05 1008.40 1008.04 1009.38 3.5815 3.5713 3.5611 3.5510 3.1330 3.1238 3.1147 3.1056 1210.97 1009.82 -0 .4 4 4 4 3.5409 1217.05 1010.26 -0 .4 4 3 3 3.5308 1 1217.13 1010.70 -0 .4 4 2 3 3.5209 ! 1217.21 | 1011.14 | - 0 . 4 4 1 2 | 3.5109 1217.29 1217.37 1217.45 1217.52 1011.59 1012.03 1012.47 1012.91 -0 .4 4 0 2 ' -0 .4 3 9 1 -0 .4 3 8 1 -0 .4 3 7 0 3.5011 3.4012 3.4815 3.4718 3.0965 3.0875 3.0786 . 3.0697 ! 3.0609 3.0521. 3.0434 . 3.0348 1 1217.60 1013.36 -0 .4 3 6 0 3.4621 3.0261 1217.68 1 1013.80 -0 .4 3 5 0 3.4526 3.0170 1217.75 | 1014.24 | - 0 . 4 3 3 0 . | 3.4430 ! 3.0091 1 1217.02 1014.68 1 - 0 .4 3 2 9 3.4335 : 3.0006 .1217.89 1217.90 1218.04 1218.10 1015.12 1 1015.56 1 1010.01 1016.45 -0 .4 3 1 8 -0 .4 3 0 8 -0 .4 2 9 8 -0 .4 2 8 7 3.4240 3.4140 3.4053 . 3.3960 2.9922 1 2.9838 ; 2.9765 2.9673 1218.17 1218:23 1218.30 1218.37 1016.89 j 1017.33 , 1017.77 1018.22 -0 .4 2 7 7 -0 .4 2 6 0 , -0 ,4 2 5 0 -0 .4 2 4 0 3.3868 3.3775 , 3.3684 3.3593 - 2.9591 2.9509 2.9428 2.9347 1 7 m7 7777 7111 -1 2 8 -1 2 7 -1 2 6 -1 2 5 -1 1 2 -1 1 1 -1 1 0 -1 0 9 Compiled by John A. Goff-and S. Gratch.' corner w 7777 oooot-coomo' 7777 g-wn --< oooo OOOO 7777 OCSOOC~ 00)0) 39 lide 41 I I I I IMi MM III WNOK5 ocs co r- o in tp co ip Tp t* tp vcoeoeo 09090909 IMI II II I II.I -II II C5 04 COO . 0c4&0o0o5r-0r-9. COCO CO CO oioioi'oi CCOD 0ID> CIDO tt--P cO OCO cO -4 04 04 64 09 -- CO h0404010 OV0DN - oooiro-iro- cCOoOcoTcPc0v0 OD leOi otoi 1o0i c*0i -- -- OOm r-OOO IN CO 0*0 0C59*C0O 0t--0 6--4 'jcoeoo*. 01*0 0004 COOCO-H >o09*0 0-0 00 r- CD CO MOtphco-cOo oooo OOOO 09 CO CO CO 09 09 09 CO 09 09 CO 09 Ocoos OocooOcro-Or0o5io05ic0i5o0*5 IN cs IN IN OOOWl0O5O0O5 -0H5 05 006--4 6t4p-Ocp- 009 0-0 09 04 04 1-1 00 0- CO CO 09 05 05 05 CO 00 00 00 0*04 04 04 . 04 0404 O* 04 -- -- -4. oo28 09 09 09 09- ddo dodo dodo II II. II II II M 05 05 00 00 0-<0tf9^< nnnn 09 09 09 09- dodo Mil r-r-r-r09 09 69 09oddd MII 05 CO t-- CO * *0^09 64 CD CD CO CO 0d9 o09 d09o09 II II 04 09 09 -cp 0O9 O09 O09O09 01tP000D40C*O^O Oi0O- .^0C509f9--06V940tCOOOOO09 09 09 09 - 09 09""" oooo------ aO CD as OJ OOOO 0300- OOOO ,0060 C4SO'f -^OOCOt09 09 r" ` OO ss 05 09 0- W --o0iod0c*0d >0 TO -CO * O -- tP CO 95000 dod HC4C4C4 N 04 04 04 o 09 ID 00 ------ -- dodo 04 04 04 04 -04010401 CQ9f 04 64 04 64 dodo 04 04 04 04 04040404 C3 -- *6 CO 04090909 dddo 04 04 C4 C4 04 04 04 04 SCOOO 09 PC TP TP dodo 04 0404 04 04040104 05 Tp ID rTP Tp Tp tP dodo 04 0404 04 040*0404 00 05 05 O Tj TO ID dodo 01 04 04 04 0404040) -- -- 64 64 *D ID ID tt5 dodo 01 0404 04 04 04 0104 I* MM D -- CO C4 OO^'O MM IMI OOCD 04 --oiC--O-0--9 05 . CO 00 00 00 MM IMI IMI 8S2 NNSN Nt-NN IMi MM 04 05 COO P04-*000 6T-f0--4I 00 05 04*0 00 0-001 r-Tp --as ^i 69 tID- CO Tp C00O44004 O O CD 09 69 CO 05-W 00 CO 09 O O -- T}* OcOtPiN Cc4io0i0--5 C--D O 04OO- - 69tP --64 -- -- -- 04 TfOOOJ h> CO 05 >D *D 05 09 00 005 0 00 > -- -- t*. ao 040COO 00T99p C0^O4 01--5-10--044I .2os 00 05 0410 PCS- ClOOPT--p T--I- 000-05 74 NV-D- CO >0 to ID -V^I^ICO *0 09 CO Tp CO OCO 09 NVC4 04- 69 CO 05 "P O tj> (NO coco-vcc 09090909 04 0104 04 CD --tp O co Tp 04 C4005 00 0404 -- -- ----- P-CO 05*0 *D 05 COCO u X H C009-,TJI TjlTJlTjlTf 09090909 . 09 09 09-09 NNSN-SNSN p-p-p-poooo f*0D-9t*0--D9*0rD9-*r0D-9 . C0t-O9.0r9-C00O-9f0Cs9O. oooo oooo p-t-p- NNNN OOOO NNSN < OOOO OOOO- OOOO' OOOO - 04 -- 00 TP ID -- O tji 04 *D 64tP 0CO-060400000T5p.- --OOOO-CTONtji 04 CO ID--I 0099 0T4f *0D4 09 09 09 O CO o*6-aCOo0a5j 0--4 ' 004 ID 0 004-0T4P C*O01I--D -- -- -- 04 0404 0404 0109 09 09 O ID >DO 05 09 05 p-- 0-004 ID 09 Tp Tp tj 04 Of-09 oCOr--- oTP^oqi. TO d id' *d 54 0909 0 05.040000 0) OOOO OOOO oooo T4p<C095 *--6Ij-9TJ0I C--O 0604--0UT9fi viocor- 00 05 -- 04 o0090oTidOoor--otCo--O. 1C4C4 04 04 0404. ID ID *o ID- 005UOC-- iOt-co coioio.io. 04 --*0 0*D0T5p . CtOp lt-ptpIDTp T>*p cTPooTp* --tP oTpo6s9o6o5 6r-9 MM MM Ml) MM I M I II M MM ftCompilejl by John A. Goff and S. Gratch. 42 CHAPTER 3 1946 Guide 43. T a b l e 2. T h e r m o d y n a m ic P r o p e r t ie s o f W a t e r a t Sa t u r a t io n 3 (Continued) " Compiled by John A. Goff and S, Cratch. T a b l e 2. h e r m o d y n a m i c P r o p f r t i e s. o f W a t e r a t S a t u r a t i o n 3 (Continued)T " Compiled by John-A. Goff and S. Gratch. - * <"v .i &.H- fiOOtN . 00 05*- ,, a<8 -_ NHJ *J<TO NN CO COCO CO -" OCNO 0--0H0<05 CO CO CON C->O tc-ot-o--o CD CO 001-- C4NNM CO LO O t-0 ' i . >oet TOTO^ NNM TOOt-- -*t- N-iO MCtCtN etONN NNCtet ** CO t-- matTOO OC9OOC0 -*-* --t* NOONP -**<tcoo tot- o05^>00 TO *? ^ TO- CO<-*~* p .COCO `` ` CO CO totototo dodo odd I hi I Mil -o*OTOO-* 4040 '' t- -* v : teoo-o*o-t--* COCOt-- 1040^4 40 r--***-* oMONO> VTOTO -* . ' TOTO ' TO TO TO ' oooo TOToOToOTO . root-*oo oo CO TO CO dodo odd Mil IIM -oanNxOncMo GO1-- W*1 V p " ' NNNNO TO TO TO 00 JD>TTOOtC--S--*f T00OOttf--O-O* -!-*-*" TO TO D- 500 OO S o OO t-t- oo ooCD OSoNN-o* N--NNN' 1-t-t-t-t- O OO CONN 4 (? ** ** TOTO 00 00 00 C-*O40NOTCO O 00 00 00 00 oo 40 O to MM O-a* oo'o -a . to to 40 to 7MM M I TOTOO-* 7777 TOT0O0 T^O<4000 -TO*TdOoTOcs* MM TTOOC0NO0. 0T0O00fO0--0O ' IIII II II ooo *t; -o; *p. to ^ to To1 4 *t< *t< * 77777 N- to-OOTO oiwo TOoOo*00;'-J** J< TO -*-* o'oo .cdt-r-'t-- N- --< CP I--*40 -T*Oo- - I _ t-OO t-- TOO j-< tTOo oO o*o< rO-OoOcoOto .C-O*to -* << *PTO --< -- . OOOO CQNNN . to t-o -* TO "t OO TO to -*-* N TO TO -* TO TOTOrt TO '*t-*t*-"t'-* tTf-<f*J-<t*I-<t-< ooo O OO OOO.oo NNNN t-t-t-tOO O . OOO dodo odd tt*O-r tt*}o-<tt*o-r*ta4->0 Tr**-Or-Tc-Ot*-ft*-P - NNNN oooo oo ONNNN' N--Nr- t--fl' f-- t-- So dodd c*}oOo (TOO CTONOONX .r-of--o-ToO*-0*0 TOTOrt TO TO CD t-- CO , odd OOO.OO OO.OO CO O -* TO rf TO -* `- t-- TO CO O TOTO p-* o--op-pop odd dodo --t-` TOt-t- TO-*00 TO CO *T -* 00 CD TO- TO CD CO O N- O TO t-- _ -- TO TO OO poToOTO oTOoTOoTOTO pop odd odd odd i to co tO--oOSoOctToOo TCTOOD Tt~--O 0O0 --C*D- TC3OO0 ooooN t-- r-- on co oo odd } TO f-- 00 -* TO ^ TO Oi e. _ S< WSlzw, CHAPTER 3 04 05-*ii<5 1946 Guide oooot--p*p-N h(Dho *4p-o4oo^ 05 04 10 04 001 (DOOlQlO 04 04 04 04 04 04 04 04 04 04 ONCOON MOO >0 04 00 * wvco 04 04 04 04 04 04 04 04 04 04 *4p-<<ji *4**040*440 04 04 04 04 04 N>rilOO> OhOO'I oooot-ot'.'C 0404040404 aoo0en0vc0c^o00ii4-5. 04 04 0404 04 .0404 04 04 04 0U54P*P-00*4P OOOOOOO hOOOO 04 04 04 04 04 0404040104 Uco3ao*t<*^< o qq^.PoSoW 04 04 04 04 04 04 o-<-- 004 *P 00 ODONM'O *P ->*1 CO 4 O -4 04 04 4 OC4VCCO 04 0044 0*P4 040004 04 04 04 04 04 .OOOOO oodo 00 {*5 0 0 O NiJ-OW-- C*5 CO CO CO CO OOOOO ddddo O40-O4P-** <000*4050 00500000 SOlO>f 0-*IQh. - *C>SI-. *P *t< *J< *p OOOOO OOOOO ddddo ddddo* dd*o*0d0-045 N*-!oiqoio*cin;oo NNNN N OO^MH 05 CO 4 CO *4 p- c-cd 06 d ost- r-p-coocao voonocj 05 oo oo oo oo oo CO *p -p in <o 00 oO 00 00 00 OOOOO OOOOO OOOOO OOOOO >***05 04 NOSOSONONO tU.N4HNHNONO OOOOO' OOOOO 00*4 10 0 04OhioOv oonoo cocot^*; 6(Olfl>si^. ototo 0505 04 04**4, OOOOO OOOOO OOOOO i*j*oo *prop*40 0 000 OOOOO OOOOO *-> 04 CO *} 000-000 0*4C4C*5V 000-000 q*J<iqt*-*ct-o^ 0s0 OOOO^CO 05*40000 05 05 CO 4 4 *p '00 05 05 4. p- 05 *fj 01 doi p- 0-0*4 coo OC4OO40 4*4*400 00 OO!-. 0-0 04 04 04 04-H 00 TJ* *4 *4 05 0005 00 05 00 ^> CO U5 0-0*4 C4 (0O5 0m5O^O*0N0N COC4 C4C4 *4 HOOO^OJ o 05 o-- d d OCQCO^I -I0 4>M >4 04 04 04 04 00 CO 04 04'd 04 r-' ` P-- *H CO 04*4*4 04 04 04 04*4 in P- 05 *3* doiidgd 0400 -o oo co o-o-o P- C*5 *H - U5 0-0*4 04 00*0*4*4 05 d*4cdf-f- 00 05 CO 05 00 *}< rP 05 '0O55C4C*4P04 *04 04 05 05 0505 05 05 05 05 OOOOO OOOOO OOOOO O O O O O ' 00-1005*4 CO 0000*4 *4 *4 *4 C4 C4 ododd OQOOP-PC4C405'#U5 04 04 04 04 04 ddddo 05 05 05 0 t-- C0O*4 04 04 04 CO 05 dodo'd 0-0050*4 C405**0t>05 0 05 0505 ododd 004 05*00 OCOOON 0C?40<OOOHt- CfO n>0c0o5 *4^Oi O 4 05*A ododd .ododd ____________ in 04 *< *h *p g oo tP op*0 O *0 *4 *40*40-05 05 05 40*0 0. *4 *4 *4 *4 *4 ododd t-- t-- co 05 O ** *PP- C) in --IP- *p IOONNOO *4*4*4*4*4 ododd coot- oo 00005000 *400005*4 00)0*404 *4 *4 4 04 C4 ddddo o o oo in O 4tl >4 *4 4J1 OaOP-O 05 05^*0 0 .0104 04 04 04 ododd 04 05 *p m ` Thermodynamics Compiled by John A. Goff and S. Gratch. . Extrapolated to represent metastable equilibrium w ith undercooled liquid. Compiled by John A'. Goff and S. Gratch. ' 45, : / 46 ,. Il - |.|.g. . CHAPTER 3 SSSSo "8o |SS 22 22222 222 1IiJ'`- 8i8iSl8lS'1881l8813. 18.1-g'1S!..Si8'lS.gl3 is mu si ms in in P ill 111 111 HU Hill 111 ini in ini in in ini dodo ocodd do odd doddd dodo'd dodo'd ls, wu. ill ill 111! Ill 111111 ill 11111 lli lill-llil Hill- ill ill 111 111111111 mu33333- mu33333 milgslss mslsSS s IIS IIS II! 111! ill 111 T able 2. T hermodynamic Properties,of Water at Saturation3 (Continued) ! A bsolute Pressure i is, ' Lb/Sq In. Sp e c ific V o lu m e , cu f t per lb Enthalpy, Btu per lb Sat. Liquid Evap. . 1 t 'f Sat. Vapor Sat. Liquid H ht . E ntropy, Dtu per (lb) (F ) ' Sat. Liquid st Sat. Vapor Sg 441.12 428.40 416.09 1161.30 1101.73 1102.16 !! 330.98 ,S?iS 1104.31 1104.74 1105.17 1105.50 1106.02 m m3=m3=m1 m-llg- 251.27 1 219.85 S' 214.12 llOtul WToil 1110.71 1111.14 1111.56 1111.98 1112.41 1112.83 :iti T able 2. T hermodynamic Properties of Water at Saturation3 (Continued) III *22222 1946 Guide mi . -. 222s- r " Compiled by John A. Goff and S. Gratch. X47 Thermodynamics T a b l e 2. T h e r m o d y n a m ic Pr o per ties of W a t e r a t Sa t u r a t io n 11 (C oncluded) " Compiled by John A. Goff and S. Gratch. I 50 CHAPTER 3 1946 Guide necessary to add a correction term h as follows, r n(l.-- n)B 1 + aWe n (5a) In Table 3 are listed values of the coefficient B and maximum values of the correction term h, the latter occurring at the same values of [i as do those of the correction term v. . . Unfortunately, values of the entropy s of moist air per pound of dry air computed from the simple relation, i = ia + ILJas (6 ' do not approximate the true values as closely as.might be desired except at temperatures considerably lower than 150 F. Only a relatively small, portion of the error is contributed by the correction term . ' * " f+~awC 1 + eWs n `" <6a) Table 3 lists values of the coefficient C and maximum values of the correction term s, the latter occurring at the same values of (J. as do those of the correction terms ti and h. The larger portion of the error is con tributed by the so-called mixing entropy. It can be expressed as an additional correction term 5 as follows, -' ' 5 = 0.1579 [(1 + HO wy logic (1 + \toWs) -- W'H'b login (pi) .s . - ti(l + oWyiogmU + aWs)). ' (0D> Maximum values of s and the values of (i at which they occur are given in Table 3. In Equation 6b logio denotes logarithm to the base 10. F ig . 1. A b r id g e m e n t of M o l l ie r D ia g r a m for M o ist A ir ' MOLLIES DIAGRAM It is a fundamental proposition of thermodynamics that when a fluid flows across a section fixed in space it connects with it an amount of energy equal to its enthalpy as determined by the pressure, temperature, and com position of thefluid at that section. This fundamental proposition provides the correct procedure for applying the law of conservation of energy' to the processes occurring most frequently, in air conditioning practiced Thus if moist air is flowing through a duct it carries across any section of the duct energy of amount mh Btu per minute and water of amount mW : pounds per minute, if m denotes the weight of dry air crossing the section per minute. . . The above considerations suggest the importance of having accurate knowledge regarding the enthalpy of the fluid in question arid the desir ability of using enthalpy as one of the coordinates in graphical repre sentation. The use of enthalpy h and humidity ratio W as coordinates in the case of moist air is due to Mollier4. A convenient modification of the Mollier diagram introduced by Goff is obtained by taking humidity ratio W as ordinate and reduced enthalpy (h-lOOOW) as abscissa. . A Mollier Diagram modified in this way is enclosed in the envelope attached, to- the inside back cover and an abridgement of the Diagram is shown in Fig. 1. . The Mollier Diagram is a constant-pressure chart, the one provided with this book being drawn for standard atmospheric pressure from the data in Table 1. Along the axis of abscissae (W 0, p. = 0) are plotted 52 CHAPTER 3 ` ' 1946' Guide Table 3. Coefficients A, B, C appearing in Equations 4a, 5a, 6a, Maximum Values of Corrections defined by Equations 4a, 5a, 6a. Degree of Satu ration AT WHICH THESE MAXIMA OCCUR, - pLiri- MAXIMUM VALUE OF CORRECTION DE FINED by Equation 6b. Degree of Saturation at which this maximum occurs, Jm- . (Standard Atmospheric Pressure) .t (F) A B (ft*/lba) (Btu/lba) c (Btu/F/ lba) /imax (ftVlba) (Btu/lba) Smax (Btu/F/ lba) *coax BO (Btu/F/ . lba) '. 96 112 128 ' 144 160 176 192 0.0018 0.0042 0.0096 0.0215 0.0487 0.1169 0.3363 0.0286 0.0650 0.1439 0.3149 0.6969 1.636 4.608 0.00004 0.00009 0.00020 0.00042 0.00091 0.00207 0.00567 0.0004 0.0010 0.0022 0.0047 0.0099 0.0207 0.0451 0.0069 0.0155 0.0332 0.0693 0.1418 0.2903 0.6180 0.00001 0.00002 0.00005 0.00009 0.00019 0.00037 0.00076 0.4925 0.4878 0.4805 0.4691 0.4511 0.4213 0.3662 0.0015 0.0025 0.0040 0.0065 0.0106 0.0179 0.0333 0.3650 0.3632 0.3602 0:3557 0.3485 0.3363 0.3129 values of the specific enthalpy of dry air ha at qpe-degree intervals of tem perature. Values of humidity ratio at saturation Ws plotted against values of reduced enthalpy at saturation (feTOOOfTs) determine the satu ration curve (p. = 100 per cent). Lines of constant temperature connect points on the saturation curve with corresponding points on the dry-air axis and are inclined upward to the right. They are drawn straight in ac cordance with Equations 3 and.5 because the curvature contributed by the -correction term 5a is inappreciable at all temperatures within the range of the chart. The portion of each isotherm lying between the dry-air axis and the saturation curve is divided into 10 equal parts by curves of - constant per cent saturation. The per cent saturation of any point below the saturation curve is readily determined by linear interpolation along . the isotherm through that point.. ' ' Each isotherm breaks at the saturation curve to incline upward to the left into the two-phase region above the saturation curve. The ordinate- . of a point in this region is the total weight of water in both the vapor phase (moist air) and the condensed, phase (liquid or solid) per.pound of dry air in both phases. Neglecting the very small amount of dissolved air in the condensed phase, it is the weight of water in both phases per pound of dry air in the vapor phase. The ordinate at the break in .the . isotherm through the point in question is the weight of water per pound of dry air in the vapor phase. Consequently, the difference between the , two ordinates is the weight of condensed phase per pound of dry air in : the vapor phase. . It has been stated that the region above the saturation curve is the two-phase region. This is so except in the wedge with apex on the satu ration curve at 32 F where three distinct phases, namely, solid, liquid, and vapor coexist. In fact, this. wedge separates the liquid-vapor region above the wedge from the solid-vapor region below it. A point inside the wedge divides the horizontal line extending through it from one, boundary to the other into two segments which are in the same ratio as are the weights of solid and liquid. The temperature is 32 F throughout the wedge. ' The isotherms in the two-phase regions above the saturation curve have been extended downward to the right into the vapor-phase region Thermodynamics 53 below the saturation curve as lines of constant thermodynamic, wet-bulb temperature. The definition of thermodynamic wet-bulb Temperature will be given later. . . - ._, On the Mollier Diagram provided with The 1946 Guide there has been drawn a protractor from which can be determined the direction in which the state point of a mixture of water and dry air will be moved by simul taneous addition of energy and water without addition of dry air. A par ticular direction is specified by the numerical value of the ratio of energy to water added which ratio is designated as q and called the specific enthalpy of water added, Btu per pound. The protractor is especially useful in locating the condition line of a cooling load or heating load problem. - ' '- : DERIVED PROPERTIES Thermodynamic Wet-bulb.Temperature. For any state of moist air there exists a temperature t* at which liquid (or solid) water may be evaporated into the air to bring it to saturation at exactly this same temperature. The humidity ratio of the air is increased from a given initial value W to the value WB* corresponding to saturation at the temperature t*; the enthalpy of the air is increased from a given initial value h to the value hs* corresponding to saturation at the temperature t*; the weight of water added per pound of dry air is Ws* -- IT and this adds energy of amount (Wa* -- W) h?,*, where hw* denotes the specific enthalpy of the . water as added at the temperature t*; therefore, if the process is strictly adiabatic, h + (Ts*W)h,,* = As* ' . (7) The solution of Equation 7 for given values of Ti"and. W is called thermo- dynamic wet-bulb temperature. .- . Example 1. Find the thermodynamic wet-bulb temperature of moist air at 80 F, 50 per cent saturation, atmospheric pressure. . .- . ' Solution. The answer is obtained directly from the Mollier Diagram. From the data of Table 1, the enthalpy of the air is h = 19.221 + 0.50 X 24.47 = 31.46 Btu/lba (Equation 5). To a first approximation this is the.enthalpy at saturation at the thermodynamic wet-bulb temperature which is therefore approximately 67 F.' . At 67 F the humidity ratio at saturation is O.01424 lbw/lba and the specific enthalpy of liquid water is 35.11 Btu/lbw. The humidity ratio of the air is PF = 0.50 X 0.02233 = 0.01117 lbw/lba (Equation 3). Therefore, to a second'approximation, the enthalpy at saturation at the thermodynamic wet-bulb temperature is hs* = 31.46 + (0.01424 -- 0.01.117) X 35.11 = 31.57 Btu/lba, Equation 7. Interpolation in Table 1 gives as final'' answer, ' . .'' 1 ' '" . - - ' ' t* -- 66.94 F "' . ' ' The psychrometer is an instrument consisting of two thermometers one of which has the bulb covered with a suitable wick that; has been dipped in liquid-water and thoroughly wetted by it. On placing the wet-bulb of the instrument in an air stream, the liquid begins to evaporate from the wick and it is usually assumed that such evaporation brings the air immediately adjacent to the wick to saturation. At first this air may ' . reach saturation at a higher or lower temperature than that of the liquid . on the wick; but in a relatively short time the temperature of the liquid * . will have changed to approach equality with that of the air touching; the wick, even if this requires the iiquid- to freeze on the wick. Then .the liquid (or solid) will continue for a time to evaporate .into the air stream .. at such temperature as will bring a portion of the air stream to saturation 54 CHAPTER 3 1946 Guide ' at this same temperature.. 'This equilibrium temperature is called wet- bulb temperature. ' It is clear that the readings of an actual wet-bulb thermometer cannot be regarded as values of a thermodynamic property of moist air; for these readings are importantly affected by a number of non-thermodynamic factors including design, construction, installation, and technique of using the instrument. Thus, unless the wet-bulb is effectively shielded against radiation from relatively warm surfaces the process will not be strictly adiabatic as tacitly assumed in writing Equation 7. - Also, partial . drying of the wick will prevent the air immediately adjacent to it from reaching complete saturation as assumed in Equation 7. A working theory developed by Arnold 6.enables the calculation of corrections to be applied to the readings of the actual instrument in order to make them agree with the values of temperature calculated from Equation 7. For tunately, and indeed fortuitously, these corrections can be made small, but to emphasize the necessity of making them in accurate experimen- . tation, the temperature defined by Equation 7 is called thermodynamic wet-bulb temperature. ' Example 2. Find the degree of saturation of moist air at 90 F dry-bulb, 63 F thermo dynamic wet-bulb, atmospheric pressure. ' . - . ' Solution. The answer is read directly from the Mollier Diagram. Inserting numerical data from Table 1 into Equation 7 gives (21.625 + 34.31 p) + (0.01235 - 0.03118p) X .31.12 = 28.57 The solution of this equation is direct and the final answer is ' ' , . p = 19.67 per cent ,' Example 3. Find the temperature to which moist air initially saturated at 40 F and at standard atmospheric pressure must be heated in order to have a thermodynamic wet-bulb temperature of 60 F. ' . . Solution. On the Mollier Diagram follow a horizontal line from the saturation curve at 40 F to its intersection with the 60 F thermodynamic wet-bulb line and read the corre: sponding temperature directly. * Inserting numerical data from Table 1 into Equation 7, this becomes . : fta + O.0b5213*as/1F8 = 26.46 - (0.01108 - 0.005213) . X .28.12 = 26.295 . At 85 F the letthand member of this equation has the value 26.147; at 86, F itsvajue is 26.389; by linear interpolation the answer is. . . . .. 1 _ . . t = 85.61 F ' ' Dew-Point Temperature. Corresponding to any given state of. moist air there exists another state on the saturation curve having the same humidity ratio W and same pressure p as the given state. , The tempera ture at. this other state on the saturation curve is called the dew-point , ;temperature of the given state. Obviously, if moist air is cooled at con stant pressure and constant humidity ratio it will reach saturation when its temperature.falls to.a value equal to its dew-point temperature. . This 'will usually be marked by the first appearance of a coexisting condensed phase. In one type of dew-point apparatus a continuous sample .of air is passed over a mirror which can be cooled by external refrigeration and ;whose temperature can be.accurately measured. The measured ,ternperature at which the intensity of light reflected from the mirror is ab ruptly diminished by condensation is taken to be the dew-point tempera ture' of the air sample/ Examples 4 and.5 illustrate the relation between' ' the dew-point, degree of saturation and dry-bulb temperature. Thermodynamics " 'V,' - - " 55' . Example h- . Find the dew-point temperature of moist air at 80 F, 50 per cent satu ration, atmospheric pressure, , ,. Solution. On the -Mollier Diagram follow a horizontal line from a given state point . * (80 F, 50 per cent) to the saturation curve and read the temperature at the intersection. From the data in Table 1, the humidity ratio of the air is W = 0.50 X 0.02233 -- 0.01117 lbw/lba- By interpolation this is found to be the humidity ratio at saturation at 60.22 F which is therefore the required answer. ` '. Example 5. Find the degree of saturation of moist air at 90 F dry-bulb, 40 F (dew point), atmospheric pressure. ' Solution. On the Mollier Diagram follow a horizontal line from 40 F on the saturation curve to. the 90 F isotherm (dry-bulb) and read the degree of saturation directly. From the data in Table 1, the humidity ratio of the air must be W = 0.005213. But the humidity ratio at saturation at 90 F is 0.03118; hence the degree of saturation is p = 0.005213/0.03118 = 16.72 per cent . TYPICAL AIR CONDITIONING PROCESSES The use of Table 1 and the Mollier Diagram in analyzing typical air conditioning processes is best explained by means of illustrative ex amples. In-each of the following, it is to be understood that the process in question takes place at a constant pressure of 29.921 in. Hg, of standard atmospheric pressure. - ' Heating ' , ' . The process of adding heat to moist air is represented by a horizontal line on the Mollier Diagram. The length of the line between the initial and finalstate points is the increase of reduced enthalpy; but, since the humidity ratio is constant, it is also the increase of enthalpy itself,and therefore'the quantity of heat added per pound of dry air. . Example 6. Air initially at 20 F, 80 per ce'nt saturation is heated to 120 F. Find the quantity of heat required to process 20,000 dm of heated air. Solution. From the data in Table 1: the initial humidity ratio is 0.80 X 0.002152 = 0.001722 lbw/lba; the initial enthalpy is 4.804 + 0.80 X 2.302 = 6.646 Btu/lba; the final degree of saturation is 0.001722/0.08149 = 2.113 per cent; the final enthalpy is 28.841 + 0.02113 X 90.70 = 30.757 Btu/lba. -. ' - ^ may be supposed that the air is heated between two sections of a duct. The quantities of energy convected across the two sections per pound of dry air crossing them are the two enthalpies calculated. Conservation of energy requires that the differ-, ence between-these two enthalpies be the quantity of heat added; thus,- ' ` aQb = 30.757 - 6.646 = 24,111 Btu/lba. The final volume is 14.611 + 0.02113 X 1.905 = 14.651 cu ft/lba. Since 20,000 cfm- of heated air is to be processed,+he total quantity of heat required is ' '' , ` aQb ~ 24.111 X 20,000/14.651 = 32,914 Btu per minute. , On the Mollier Diagram the process is represented by the horizontal' line AB, Fig. 2,. whose length is the quantity of heat added per pound of dry air. The reduced enthalpy at A,is 4.92 while that at B is 29.03, both being read directly from the chart. Since humidity ratio is constant the difference between these reduced enthalpies is also the difference between the enthalpies themselves, namely, 24.11 Btu/lba. . Cooling -, ' Theproccss of cooling moist air is,also represented by a horizontal line " on the Mollier Diagram. The line may extend.across the saturation curve into the two-phase region, nevertheless, the. length of. the line between Fig. 2. Illustration of Use of Mollier Diagram in Solution of Example 6 the initial and final states is the quantity of heat removed, or refrigeration supplied, per pound of dry air. By following the final isotherm downward to the right to the saturation curve and reading the ordinate there, the weight of water vapor per pound of dry air in the vapor phase is deter-. mined. The difference between the initial humidity ratio and this ordi- . nate is the weight of condensed phase per pound of dry air in the final state. . , Example 7. Air at 95 F and 50 per cent saturation is cooled to 70 F. Find the refrigeration required to process 20,000 cfm of uncooled air. . Solution. From the data iii Table 1: the initial humidity ratio is 0.50 X 0.03673 = 0.01837 lbw/lba; the initial enthalpy is 22.827 + 0.50 X 40.49 .= 43.072 Btu/lba; the humidity ratio at saturation at the final temperature is 0.01582 lbw/lba; the quantity of liquid formed is 0.01837 -- 0.01582 = 0.00255 lbw/lba; the enthalpy of the final two-phase mixture is 34.09 -f- 0.00255 X 38.11 = 34.187 Btu/lba- , . It may be supposed that the air is cooled between two sections of a duct. The; quantities of energy convected across the two sections per pound of dry air crossing them. . 15.82 24.70 Fig; 3. Illustration of Use of Mollier Diagram in Solution of Example 7 Thermodynamics -__:----------------------------------- ------------- :------------------------------------- the two enthalpies calculated above. Conservation of energy requires that the difference between these two enthalpies be the quantity of heat removed, or refrigeration supplied, between the two sections. Therefore, . . . -Age = 43,072 - 34.187 = 8.885 Btu/lba ,. The initial volume is 13.980 -4- 0.50 X 0.822 = 14.391 cu ft/lba. Since 20,000 cfm of air is to be processed, the total refrigeration required is -a(?b = 8.885 X 20,000 h- 14.391 = 12,348 Btu per minute On the Mollier Diagram the process is represented by the horizontal line AB, Fig. 3, whose length is the quantity of refrigeration required per pound of dry air. . Adiabatic Mixing of Two Air Streams A typical air conditioning process requiring special, analysis is the adiabatic mixing of two air streams. Referring to Fig. 4, let mlt mi, m3 denote the weights of dry air convected across sections Fi, F2, Fj, respect ively, per minute. Then miWu m?Wi, m3W3 and mihlt m^i3, m3h3 will Fig. 4. Adiabatic Mixing of 2 Air Streams denote the weights of water and the quantities of energy similarly con vected. If the mixing is adiabatic, it must be governed by the. three equations, . . mi 4- ftti = mi . ' '. . miWi + mtWt -- riiiWi (8) . mihi .+ viih-i = mju . Elimination of m3 'gives, ' , hi -- h3 . Wi -- Wz _ mi . . h, - h! W, - Wi m, ' 1' according to which: on the Mollier Diagram the state point of the resulting mixture lies on the straight line connecting the state points of the two streams being mixed and divides the line into two segments which are in the same ratio as are the weights of dry air in the two streams. ' .. . Examples. Outside Air at 0 F and 80 per cent saturation is to be mixed adiabatically with recirculated Inside Air at 70 F and 20 per cent saturation in the ratio of one pound of dry air in the former to seven in the latter. Find the temperature and degree of saturation of the resulting mixture., ... . . Solution. The humidity iutio Wi and the enthalpy hi of the resulting mixture must satisfy Equations 9, namely, . ' ' 0.003164 Wi f 20.270 -- hi _ 1 .. IFj - 0.000630 hi - 0.668 7 - '' ' i- . - ' : 58 CHAPTER 3 ,1946 Guide. from which: Wi = 0.002847, hj = 17.820. At the temperature of the resulting mixture, therefore, .: .' . Aa + 0.003847 h^s/Ws = 17.820 '. At 61 F the Iefthand member of this equation has the value 17.750; at 62 F its. value is. 17.991; by interpolation the temperature of the resulting mixture is 61.29 F where the . humidity ratio at saturation, also by interpolation, is 0.01161; hence the'degree of saturation of the resulting mixture is . tt = 0.002847 ^ 0.01161 = 24.52 per cent . On the Mollier Diagram, Fig. 5, a straight line is drawn between point 1 (0 F, 80 per cent) and point 2 (70 F, 20 per cent); then point 3 is located on the line one-eighth of the distance from point 2 to point 1. The temperature and degree of saturation at point 3 are read directly. .. Adiabatic Mixing with Injected Water Another typical air conditioning.process is that of injecting water into. . an air stream to mix with it adiabatically.. Let W2 -- Wlt denote the increase in humidity ratio of the air; this is obviously.the quantity of water injected per pound of dry air; it follows that the quantity of energy injected per pound of dry air is (W2 -- where h,, denotes the' specific enthalpy of the water as injected; if the process is adiabatic this produces an equal increase in the enthalpy of the air, namely, h2 -- hi; therefore, . .. - ' . hi ~ h\ = hw(Ws ~ PFi) * (10) according to which: the process of injecting water into an air stream to mix adiabatically with it is represented by a straight line on the Mollier Chart whose direction is fixed by the specific enthalpy of the water as injected. The protractor drawn, on the. Mollier Diagram provided with this book 1 provides a*convenient means for determining this direction. Example 9. It is desired to increase the humidity ratio of air at 70 F dry-bulb, without changing its temperature. Under what conditions may water be injected in. order to accomplish the desired result: , ', Solution. .At 70 F the increase of enthalpy'per unit increase of humidity ratio is has/WB = 17.27 -* 0.01582 = 1092 Btu per pound of water. This must be the specific enthalpy of the water added if the state point of the air is to be moved along the 70 F isotherm. Saturated steam at 668 F has this specific enthalpy (see Keenan-Keyes, Thermodynamic Properties of Steam). ' On the Mollier Diagram, Fig. 6, it is seen that the 70 F isotherm is parallel to the line on the protractor for a specific enthalpy of 1092 Btu per pound. * Adiabatic Saturation ' * Any process by which the state point of moist air is moved to the saturation curve adiabatically may properly be called adiabatic satu ration. ' .. Example 10. Liquid water chilled to 35 F is evaporated Into an air stream initially at 90 F and 50 per cent saturation. How much water must be evaporated to bring the air to saturation at what temperature. > *. Solution. The initial enthalpy of the air is 21.625 + 0.50 X 34.31 = 38.780 Btu/lba; the initial humidity ratio is 0.50 X 0.03118 = 0.01559 lbw/lba; the specific enthalpy of the chilled water is 3.06 Btu/lbw; therefore, the temperature at which the air reaches ' the saturation curve must be such that the enthalpy As and humidity ratio W$ at satu ration satisfy the equation, .' '; . As. - (We-- 0.01559) X 3.06 = 38.780 ' ^The'solution is.75.19 F where the humidity, ratio aFsaturation is 0.01894; consequently, Fig. 6. Illustration of Use of Mollier Diagram in Solution of Example 9 60 CHAPTER 3 1946 Guide the weight of water evaporated is 0.01894 -- 0.01559 = 0.00335 lb per pound of dry air. On the Mollier Diagram, Fig. 7, a line is drawn through the initial state point (90 F, 50 per cent saturation) in the direction given by the protractor for a specific enthalpy of 3.06 Btu/lbw. If air is saturated adiabatically with spray water which is recirculated, the water. will ultimately assume a temperature such. that the air is brought to saturation at exactly the same temperature; that is, the water will assume the thermodynamic wet-bulb temperature of the air. Example 11.1 Air at 75 F and 60 per cent saturation is saturated adiabatically with recirculated spray- water. Find the resulting temperature and the weight of water added-per pound of dry air. * .' Solution. In view of the above remarks the solution of this example reduces to the determination-of the thermodynamic wet-bulb temperature of the air. Its humidity Fig. 8. Illustration of Use of Mollier Diagram in Solution of Example 11 - ratio is 0.60 X 0.01882 = 0.01129; its enthalpy is 18.018 + 0.60 X . 20.59 = 30.372; Equation 7 defining thermodynamic wet-bulb temperature becomes . As* - (Wf - 0.01129) Aw* = 30.372 . At 65 F the value of the lefthand member is 29.995; at 66 F its value is 30.746; by inter polation the thermodynamic wet-bulb temperature is 65.51 F where the humidity ratio at saturation is 0.01350; consequently the weight of water added is 0.01350 -- 0.01129 = 0.00221 lb per pound of dry air. . -. On the Mollier Diagram, Fig. 8, the process is represented by the line AB which is a segment of the 65.51 F thermodynamic wet-bulb line. The difference between the ordi nates at B and at A is the weight of water added per pound of dry air. - Cooling Load ' The problem of calculating the cooling load for an air conditioned space usually reduces to the determination of the quantity of inside air that must be withdrawn .and the condition to which it must- be brought by suitable processing so that its return to the conditioned space-will have the net effect of removing given amounts of energy and water from the space. Let M denote the weight of dry'air withdrawn with inside air per hour. With it will be withdrawn energy of amount Mhi and water of.amount ' , Thermodynamics 61 MWi per hour, where hi and Wi denote the enthalpy and humidity ratio of the inside air, respectively.. The weight of dry air returned with the conditioned air will necessarily be the same as that withdrawn with the inside air but with it must be returned a smaller quantity of energy Mh and a smaller quantity of water MW.. LetAQ and A W denote the given amounts of energy and water to be removed from the conditioned space . per hour; then Mh = Mhi - AQ MW= MW, - AW . Eliminating M and letting q denote the ratio of energy removed to water removed, that is, q = AQ/AIT, : according to which; all possible states for the Conditioned Air lie on astraight line on the Mollier Diagram passing through the state point of the inside air in the direction specified by the numerical value of the ratio q. This line is called the condition line for the given problem. If the condition line crosses the saturation curve, the point of intersection is called the appa ratus dew-point for the given problem. The protractor on the Mollier Diagram facilitates the drawing of the condition line and the locating of the apparatus dew-point. For this purpose the numerical value of the ratio q is to be regarded as a value of the specific'enthalpy of water added, Btu per pound. , Example 12. A condition of 80 F dry-bulb, and 67 F thermodynamic wet-bulb, is to be maintained in a clothing store, outside conditions being 95 F dry-bulb, and 75 F thermodynamic wet-bulb. The energy gain from normal heat transmission is estimated at 16,000 Btu per hour, that from solar radiation at 48,000 Btu per hour. The energy generated by lights, fans, etc. is estimated at 13,900 Btu per hour. The ventilation requirement is 30,000 cu ft per hour. The number of occupants is 50. Find the ap paratus dew-point. . Solution. The properties of inside air arid outside air are readily calculated from the data in Table 1, see especially Example 2. -. ' Inside Air n = . 0.5024 . A = 31.514 W = . 0.01122 . ,v = ............. Outside Air 0.3848 38.408 0.01413 14.296 The weight of dry air entering with the ventilating air is 30,000/14.296 = 2098.5 lb per hour which brings with it energy of amount 2098.5 X 38.408 = 80.595 Btu per hour and water of amount 2098:5 X 0.01413 = 29.659 lb per hour. The weight of.dry air displaced from the store by the ventilating air is.2098.5 lb per hour which takes with it energy-of amount 2098.5 X,31.514 = 66,132 Btu per hour-and water of amount 2098.5 X 0.01122 = 23.541 lb per hour. . . Each occupant may be regarded as a normal person standing at rest and therefore evaporating 0.198 lb of water per hour at about 79 F (Table 4, Chapter 12).' From this source there is water of amount 50 X 0.198 == 9.90 lb per hour and energy of amount 9.90 X 1095.7 -- 10.847 Btu per hour added to the conditioned space. In addition each occupant loses 225 Btu per hour by conduction, convectiori, and radiation, making - a total for 50 persons of 11,300 Btu per hour. ., - The net energy gain is 16,000 4- 48,000 4- 13,900 + 80,595 -- 66,132 -f- 10,847 4 11,300 = 114,510 Btu per hour. The net water gain is 29.659 -- 23.541 4- 9.90 = 16.018 lb per hour. ' Accordingly the direction of the condition line is fixed by the. ratio, q = 114,510 -i- 16.018 = 7148.8 Btu per pound of water., , ................ - On the Mollier Diagram, Fig. 9, the direction of the' condition line is given.by the pro tractor for a specific enthalpy of water added of 71-18.8 Btu per- pound.-' The line itself l 62 CHAPTER 3 i!946i Guide, { passes through the state point of the Inside Air and intersects the saturation curve at the apparatus dew-point. .. . -' .' According to. Equation 11 tlie enthalpy he and humidity ratio Ws at the. apparatus . dew-point must satisfy the equation -' , ' . - 7l48.8^a - hs = 7148:8 X 0.01122 - 31.514 = 48.681 . . - At 58 F the left-hand member has the value 48.513; at 59 F its value is 50.641; by inter polation the apparatus dew-point is 58.08 F. It would be a mistake to assume that the refrigeration to be supplied . is equal to the net energy to be removed; for in general water is to.be removed simultaneously and unless this is removed as liquid at 32 F. it will automatically take some energy with it. Thus, unless the water, is reftioved as solid (ice) the refrigeration to be supplied will be somewhat less than the net energy to be removed. . . Example IS. Referring to the cooling load problem of Example 12, suppose that the conditioning process consists of cooling a portion of the inside axr to the apparatus dew point temperature, separating out the liquid thus formed; and returning the resulting saturated mixture to the conditioned space. Find the quantity of inside air that must be processed in this manner and the corresponding quantity of refrigeration required. , 'ThermodYnaniics ,-: `----------------------------------------------------------------------- ;63 formed-in the.cooling.operation .is represented by line BC whose projection on.the ordinate axis is the quantity of liquid so separated per pound of dry air. Point C is the apparatus dew-point and lies on.the condition line as required. . ' / In. practice it may not .be feasible to choose the apparatus .dew-pointas the point on the condition line to which to condition the inside air because to do so would require an excessive number of air changes in the given space. Or it may be that the condition/ line does not cross the saturation curve at all so that the apparatus dew-point as defined does not exist. Finally, it is rarely possible to obtain complete saturation in conventional air conditioning apparatus. Nevertheless the requirements of the cooling load problem can be exactly .met if the conditioned air is brought to any point on the condition line of the problem. Heating Load \ The condition line is also useful in the analysis of heating load problems as may best be illustrated by means of an illustrative example. Fig. 9; Illustration of Use of Mollier Diagram in Solution of Example 12 Solution. During the cooling operation the enthalpy of the Inside Air is reduced to the value, , * . .. '* ; . A. =* 25.17..-}- (0^01122 --.0^01033)' >/26.20 = 25.193 V where 25.17 and 0.01033 are the values of enthalpy and humidity ratio at saturation at the apparatus dew-point temperature and 26.20 is the specific'enthalpy of liquid . water at that temperature.. It follows that the quantity of.refrigeration reQuired is 31.514 -- 25.193 = 6.321 Btu per pound of dry air. ' '' . . , The inside air being processedleaves % the store with an enthalpy of 31.514 arid is returned with an enthalpy of 25.17;'it therefore removes energy of axhount 6.344*Btu. per pound of dry air; This means that the weight of dry air involved in the-process is 114,510/6.344. = 18,050 lb"per hour and that the total refrigeration to'be suDolied' is 18,050 X 6.321 = 114,090 Btu per hour, dr 9.508 tons. . ; . ' ' The quantity of liquid separated out. during the conditioning process is 18,050 X .. (0.01122 -- 0.01033) .= 16.018.1b per hour as required. . In leaving;.the apparatus it takes with it energy of amount 16.018 X 26.20 = 420 Btu per'hour/ This plus, the refrigeration accounts for the total energy .removal of 114,510 Btu per Hour as required. . On'.the'Mollier'Diagrain, Fig: 40, the'cooling operation is represented by line AB whoser length?is thVquantity bf refrigeration per pound of dry air; the separation of the liquid Fig. 10. Illustration of Use of Mollier Diagram in Solution of Example 13 Example 14* A certain space is to be maintained at 70 F and 50. per cent saturation with outside conditions at 0 F and 80 per cent saturation. The normal heat trans mission through walls, partitions, floor, roof, glass and doors is estimated at 75,000 Btu per hour. Energy gained from lights and appliances is estimated at 15,000 Btu per hour. Energy and water gains from occupants are to be disregarded in the calculations. Double * doors-and windows are used, so that infiltration is negligible! The ventilation require- ment is -30,000 cu ft per hour of outside, air. . ** ' The requirements of the problem are to be met in the following manner; preheat the. ventilating air; mix it adiabatically with recirculated inside air; saturate the mixture adiabatically with recirculated spray water; heat the resulting mixture to 105 F and return it to the conditioned space as supply dir. * , - * Analysis., Every pound of dry,air admitted to the system (air conditioned space plus air-conditioning apparatus) with the ventilating air displaces a* pound of dry'air /rom the systeiri with inside air. ` Since the ventilating air is not admitted, directly to. the space, then for every pound of dry air withdrawn with inside air there is a pound of dry air returned with supply air. This has to have, the net effect of adding energy of amount 60,000 Btu per hour and water of amount zero pounds per hour. Thus the ratio.q deter mining the direction of the condition line is infinite, which means that the condition line is horizontal as indicated by*the protractor on* the Mollier'Diagram. '.* ` / " . . ' . The properties of inside air are: h = 25.451, W = 0.007910. Since the state'point of the supply air must be on the condition line at 105 F, its properties'are:: h = 33.986, /^, 64 CHAPTER 3 1946 Guide W -- 0.007910: Therefore the weight of dry air withdrawn with inside air.arid returned with supply air is 60,000 4-' (33.986 - 25:451) = 7029.9 lb per hour. . The properties of outside air are: A = 0.668, W = 0:0006298, v = 11.590. Therefore the .weight of dry air introduced into the system with the venlilaling air is 30,000 4 11.590 - 2588.4 lb per hour. This ventilating air is to be mixed adiabatically with inside air containing 7029.9 - 2588.4 = 4441.5 lb of dry air per hour; therefore, the humidity ratio of`he mixture must be (2588.4 X 0.0006298 + 4441.5 X 0.007910) = 7029.9 0.005229. The condition line crosses the saturation curve at 50.86 F where the enthalpy is 20.782 and the humidity ratio is 0.007910. This is the state point to be reached by adiabatic saturation of the mixture of ventilating air and inside air with recirculated spray water:' l y' t*ie state point of the mixture must lie on the 50.86 F thermodynamic wet-; bulb line so that its enthalpy must have the value, . h = 20.782 - (0.007910 - 0.005229) X 18.97 = 20.731 ' ' This requires that the enthalpy of the preheated ventilating air have the value, h = (7029.9 X 20.731 - 4441.5 X 25.451) 2588.4 = 12.632 ' Since the humidity ratio of the preheated ventilating air is known to be 0.0006298. its temperature is readily found to be 49.75 F. . n Boof quantity of heat required for preheating the ventilating air is 2588.4 X (12.632 -- 0.668) =< 30,968;Btu per hour; that to be added to the supply air is 7029.9 X (33.986 - Fig. 11. Illustration of Use of Mollier Diagram in Solution of Example 14 -. .\ - . hour; the energy added with the spray water is 7029.9 X 18.97 X (0.007910 -- 0.005229) = 357 Btu per hour; that introduced into the system with the ventilating air is 2588.4 X 0.668 = 1729 Btu per hour; that carried out of the system with the inside air displaced by the venlilaling air is 2588.4 X 25.451 = 65,877 Btu per hour; therefore, the net energy added to the system is 30,968 4- 92.823 + 357 4 1729 65,877 = 60,000 Btu per hour as required. - On the Mollier Diagram, Fig. 11, point A is the state point of the inside air. The con dition line is horizontal so that point D is the state point of the supply air. The condition line crosses the saturation curve at point C so that the state.point of the mixture of preheated ventilating air and inside air before adiabatic saturation with recirculated spray water, must lie somewhere on the thermodynamic wet-bulb line through C.. The state point of the ventilating air is point B, hence that of the. preheated ventilating air must he somewhere on the horizontal line through B. Its exact location is determined' graphically by finding the straight line AF which is cut by the thermodynamic wet-bulb line through C into two segments, such that AE; AF = 253S.4 : 7029.9. The length of the line BF is the quantity of heat required for preheating the ventilating air per pound of dry air; the length of the line CD is the quantity of heat to be added to the supply aw, per pound of dry.air. . . ' . . .Thermodynamics ___________________ ;;i_------------------------------------------------- 1:!----------------------------------------------- -- -: WET-BULB TEMPERATURES BELOW 32F A condition in which the water evaporating from the wick of a wet-bulb thermometer remains liquid at 32 F or lower is one of metastable equi librium and should therefore not be expected to occur in practice: The evidence that it does.sometime occur appears to be indirect and incon clusive- Stable, equilibrium requires that the water freeze at 32 F or lower and is the condition to be expected in practice. On the Mollier Diagram the lines of constant thermodynamic Wet-bulb temperature have been 'drawn for stable equilibrium only. In other words it has been assumed that the water evaporating from the wick of the wet-bulb thermometer freezes when its temperature falls'to 32 F or lower. Example 15. Find the temperature at which dry air has a thermodynamic wet-bulb temperature of 32 F. ' - , ... Solution. If it is assumed that the water evaporating from the wick of the wet'bulb thermometer remains liquid, the specific enthalpy of the dry air must have the value, Aa = 11-758 - 0.04 X 0.003788 = 11,758 ' corresponding to which the temperature is 48.95 F. On the other hand if it is assumed that the water freezes, the specific enthalpy of the dry air must have the value, ; Aa = 11.758 + 143.36 X 0.003788 = 12.301 . .. corresponding to which the temperature is 51.21 F.' The second assumption is the as sumption of stable equilibrium arid should be expected to represent the actual situation. The corresponding answer, namely, 51.21 F is the one given by the Mollier Diagram. ` DALTON'S RULE As stated in the introduction the thermodynamic properties of moist air have hitherto been obtained from those of dry air and water vapor separately by application of Dalton's Rule. Actual departures from the rule are- due principally, but not entirely, to intermolecular forces; therefore, in order to apply the rule with any measure of consistency it - is necessary to idealize the situation by assuming that the effects of such intermolecular forces are negligible and that both the dry air and the water vapor behave like perfect gases. Making this assumption, the volume occupied by a mols of dry air at'temperature T and pressure pa is t = naRT/pa while that occupied by nw mols of water vapor at the same temperature but at pressure is t = th,RTJp,,. According to Dalton's Rule, if the dry air and water vapor are mixed, each occupies the whole volume .of the mixture at'the temperature of the mixture and the pressure of the mixture' is the sum of the individual pressures. Mathe matically, ' ' . .' UaRT nwRT '(a +nw)RT rir = ----- -- .--r Pa pw ------------'' p., ., -. .' 1 ... . - VMI ' It follows: from these equations that the so-called "partial" pressure of each constituent is its mol-fraction times the observed pressure of the mixture; thus, for water vapor, W Pw ' a + nw t (13) and similarly for dry air. Equation 13 may be regarded as the Dalton Rule definition of partial pressure in terms of the observable terms Wa, Ww, P` ' . 66 CHAPTER 3' `1946 Guide The humidity ratio W is the mol ratio Ww/na iimes the ratio of molecula'r weights, namely, 18.016/28.966 = 0.6220; hence (13) can be written ' . W = 0.6220 --P ---- --Pw- (14) ... . Now, even if it is assumed that both the dry air and the water vapor.' behave like perfect gases, it does not follow that at saturation the "partial" pressure of the water vapor can be put equal to the saturation pressure of pure water at the temperature of the mixture because; (1) the coexisting liquid (or solid) phase is not pure water but contains a small amount of dissolved air, and (2) the coexisting liquid (or solid) phase has to support ' the observed pressure p and not just the saturation pressure p, of pure water. These effects are calculable but are in general smaller than the effects of intermolecular forces which have already been ignored. Be . sides, the only legitimate reason for retaining Dalton's Rule is to gain simplicity; hence these effects should be disregarded also, and the humi dity ratio at saturation estimated as follows, - . Wa = 0.6220 --5-- . P ~ Ps . (15) . In this chapter the ratio W/We has been called degree of saturation and denoted by the greek letter p.. The ratio pa,/Pa has long been called relative humidity and will be denoted by the' Greek letter 9. Equations 14 and 15 can be combined to give '- = 9 1 - Ps/P 1 - tPs/P which can be inverted to give (16) 1* 1 - (1 - v-)ps/p (17) Example 16. Find the relative humidity of moist air at 180 F, 20 per cent saturation. Solution. Inserting numerical data from Table 1 into (17), the answer is ' '= 0-20 . =n : -(p 1 -.0.80 X 15.294/29.921 . .. . Example 17. Find the degree of saturation of moist air at 70 F, .50 per cent relative humidity. ' . - ' '' ' ' ` . Solution. Inserting numerical data from Table 1 into Equation ,16. the answer, is 1 - 0.73915/29.921' % p = 0.50 = 0.4937: 1 - 0.50 X 0.73915/29.921 . The foregoing examples show that there is . a substantial difference . between degree of saturation and. relative humidity, particularly at higher temperatures. Of course, they both have the value zero for dry I. air and 'the value unity for saturated moist air regardless of the tem perature. - . - - .' A- Dalton Rule expression for the volume' of moist air per pound of dry air obtainable directly from Equation 12 is '` :: . . .' . : (R*T\ , fWaRv,T\ ' / = {--) +(--p~)................., (I8) . where ;: ' ' : : ' i?a = gas constant for dry air = 1545.31 28.966 = 53.349 (ft/Fj. -j '. ' Thermodynamics 67, = gas constant for water vapor = 1545.31 18.016 = 85.774-(ft/F).' This expression is of the form of Equation 4. ' According to Dalton's Rule the enthalpy of moist air is the sum of separate contributions from the dry air and the water vapor; thus,. . " h = ha. 4- p(IFsiw) ' (19) where, to be consistent, the specific enthalpies ha and K, should be ' allowed to vary with`temperature only, riot with pressure or compo sition. This expression is of the form of Equation 5. '; '' Within the accuracy of Dalton's Rule the following empirical equations give suitable values of ha and h,,: ' . .. . ' ' - , ha -- 0.2401 . '. . ha, = 0.4441 + 1061 (20) Equation 7 defining thermodynamic wet-bulb temperature may be written in the form, h -V + tWs* - W)K* = ha* -- V If the quantify h! that has been subtracted from both sides is understood to be the enthalpy at the thermodynamic wet-bulb ternperature t* but at the humidity ratio W, then within the accuracy of Dalton's Rule ' h -- h' -- (0.240 + 0.444 IF) (1 - 1*) As* - A1 = (1061 + 0.4441*) (IFs* - HO . A,,* = 1* - 32 ' - With these approximations Equation 7 becomes Wa* -W = 0.240 + 0.444 IF 1093 - 0.5561* . ,. 1 (21) Carrier 6 has modified Equation 21 by introducing further approxh mations as, follows, . . .. . . ... ' ' Wa* = 0.6220ps*/(p - pa*) . : .W = 0.6220pw/(p -- pa*) , 0.444 W -- 0 ' .. , .. the first of which is.part of Dalton's Rule. The result is Pw -- ps* 2830 - 1.441* (1 - 1*) (22) except that the numerical values of the constants in the denominator of the rightmost term are somewhat different than Carrier's; ':' '. Equation 22 permits direct calculation of the partial pressure pw from observed values of pressure p, temperature t, arid wet-bulb temperature t*, assuming that information is available regarding the . saturation pressure ps. . The ratio pa,/pa is the sorcalled relative humidity. . .. - _ , Example 18. Kind the relative humidity of moist air at 90 F dry-bulb; arid -63 F- ' (thermodynamic wet-bulb).. . . ' -r ' ' - ' Solution. At 63 F the value of the saturation pressure is 0.58002 in. Hgi Therefore, . at atmospheric pressure (29.921 in. Hg), pa, = 0.58002 - 29.341 X 27/2739 = 0.2908 in. Hg . 68 CHAP TER 3 1946. Guide The relative humidity is . 9 = 0.2908/1.4219 = 0.2045 . . the denominator being the value of saturation pressure at 90 F. * From Equation 16 may be computed the corresponding degree of saturation, the result being - p. = 19.67 per cent in remarkably close agreement with the answer to Example 2. . STEADY FLOW ENERGY EQUATION In steady flow, the energy convected by the fluid at any section is the sum of (a) kinetic energy due to velocity; (b) gravitational energy due to elevation; (c) enthalpy due to the condition of pressure, temperature and composition of the fluid. Kinetic Energy There are reasons to believe that the so-called velocity pressure hv read by a Pitot tube is simply the kinetic energy per unit volume of the. fluid immediately upstream from the tube, as application of Bernoulli's' Equation suggests. Thus ../ -' F = 1097.3 ' -- (23) where V -- velocity, feet per minute. . hv = velocity pressure, inches of water at 60 F. p = density of fluid, pounds per cubic foot. - In the case of flow through a duct, the velocity pressure is found to vary considerably over the section and a traverse has to be made. The cross sectional area of the duct is divided into a number of equal concentric areas, and measuring stations are located at centroidal points in each area along two perpendicular diameters. Usually the ultimate object is to determine an average velocity V from which the weight of fluid crossing ;the section per unit time can be obtained on multiplying by the cross sectional area of the duct and by the density of the fluid. This is obtained by simply averaging the square roots of all measured velocity pressures as follows: . 1097.3 V= VT (24) where ; F = average velocity, feet per minute. ' - (A^)av = arithmetic average of the square roots of all measured velocity pressures, , ` inches of water at 60 F. .. But the item of-present importance is the average kinetic energy, con verted, with each pound of fluid. Consistently with the previous discus sion, this can be shown to be .: . KE = 0.006678 v (25) 4 Thermodynamics 69,. where .. ^ . KE = average kinetic energy, Btu per pound. . v =* specific volume, cubic feet per pound. . .. . * . Qta)w ~ arithmetic average of the 3/2-powers of all measured velocity pressures, inches of water at 60 F. ,. .. If the velocity pressure were uniform over the section, Equations 24 and 25 could be combined to give But, it is interesting to note that if the velocity varies pardbolically from zero at the walls to maximum at the center as it doesin the case of purely viscous flow in a circular duct, then the average kinetic energy is twice that given by Equation 26. . Example 19. If 2000 cfm of air flows through an 8 in. diameter circular duct, find the average kinetic energy per pound of air. Solution. The cross-sectional area of the duct is 0,349 sq ft; hence the average flow velocity is 5730 fpm. If the.velocity were uniform over the section, the average kinetic ' energy would be (5730 -s- 13,430)* = 0.182 Btu per pound. But it is more likely that the actual distribution of velocity would approximate that characteristic of viscous flow; hence the average kinetic energy would be more nearly 2 X ,0.182 = 0.364 Btu per pound. _. '* Gravitational Energy The potential energy due to elevation Z (feet) above any convenient datum is simply Z -5- 778.3 Btu per pound of fluid. In the case of moist air. TM Z (\ + W) PE--------- 7781$ where PE = average potential energy, Btu per pound dry air. Z = average elevation, feet.-' ' ' W = humidity ratio, pound water per pound dry air. (27) Enthalpy , . No further discussion of enthalpy is required. It may be well to emphasize, however, that enthalpies have been figured on the basis of' one pound of dry air. ' . . Heat and Shalt Work Between any two sections 1 and 2 in an apparatus through which steady flow occurs, there may be heat absorbed from outside, iQt, Btu 'per pound of dry air, and shaft work removed to outside, ih, Btu per pound of dry air. If heat is actually rejected to outside, 152 is intrinsically negative; and if shaft work is actually put in from outside ilt, is intrinsi cally negative. " ' Steady-flow Energy Equation '. A complete energy accounting takes the form of Equation 28 which is usually referred to as'the steadyrflow'energy equation. ' . ` . iff* = (A* + KEt + PEi) -- {hi KEi PP.i) T ill - . ' (28) - ^ . TO CHAPTER 3 1946 Guide where . - = heat added from outside between sections 1 and 2, Btu per pound dry air. _lh = enthalpy of the mixture at section 2, 'Btu per pound dry air. KE, = average kinetic energy at section-2, Btu per pound dry air. PE, =.average potential energy at section 2, Btu per pound dry-air. _*i = enthalpy at section 1, Btu per pound dry air. KE, = average kinetic energy at section 1, Btu per pound dry air. PE, = average potential energy at section 1, Btu per pound dry air. ' . ,k = shaft work withdrawn between sections 1 and 2, Btu per pound dry air. . . In Equation 28 all quantities are per pound of dry air. If Equation 25 is used in computing average kinetic energy, the result will be in Btu per pound of dry air if v is taken as volume per pound of dry air. If Equation 26 is used,-multiplication by (1 + W)- a.s in Equation .27 is required though this is a refinement seldom justified; ' . - Thermodynamic properties of water at saturation are given in Table 2 for the range --160 to +212 F. U. S. STANDARD ATMOSPHERE The so-called U. S. Standard Atmosphere is an essential standard of reference in aeronautics and as such has become important to the air conditioning engineer who frequently has to simulate atmospheric con ditions at high altitudes in connection with aeronautical research. In defining this standard it is first assumed that temperature T varies linearly with altitude Z above sea level, at any rate up to the lower limit of the isothermal layer at 35,332 ft. Thus, . . T = T0 - 0.0019812 Z or . (29) -- = --0.0019812 (degree Centigrade per foot) . (30) oZ . The second assumption is the validity of the perfect gas laws, namely, . Pv = RT . . (31) . A horizontal disc of air having unit cross-sectional area (1 sq ft) and ' vertical thickness dZ (ft) weighs dZ/v (lb); This accounts for the dif ference of pressure dP {\b per sq.ft) between:the upper and lower faces of the disc; -hence, using Equation 31. % , RT dP dZ = P (32) Equations 30 and 32 ;can be combined to eliminate Z and then in tegrated to obtain the relation between pressure and temperature, namely, p / p \o.woa To \ Po / (33) The values T0 = 288 K and P0 = 29.921 in..Hg are parts of the definition of. the standard atmosphere. . , , Values of pressure and temperature are listed in Table 4 for altitudes in the standard atmosphere from --1,000 to 50,000 ft above sea level. Values for altitudes below the lower limit of the isothermal layer conform Thermodynamics v71 to Equations 29 and 33. For further explanation, reference (7) should be consulted. Table 4. Pressure and Temperature for Altitudes in U. S. Standard Atmosphere .. . Altitude Feet Z - 1,000 - 500 0 + 500 +1,000 . + 5,000 10,000 15,000 20,000 25,000 30,000 35,000 40,000 . 45,000 50,000 Pressure In; of Hg P 31.02 30.47 29.921 29.38 28.86 . . . Temp F ` *' +62.6 +60.8 +59.0 +57.2 +55.4 . 24.89 . +41.2 20.58 . . +23.4 16.88 ' +5.5 13.75 -12.3 - . n.io. ~ .. -30.1 . 8.88 ' 7.04 5.54 . 4.36 ... , 3.436 --47.9 -65.8 -67.0 -67.0 -67.0 ' LETTER SYMBOLS USED IN CHAPTER 3 ja = degree of saturation or per cent saturation, p = density of fluid, pounds per cubic foot. <? = relative humidity (decimal). /, a = ratio of apparent molecular weight of dry air (28.966) to the molecular weight of water (18.016) = 1.6078. . ; . . A -- coefficient from Table 3'for use in Equation 4a (obtained from Table 3). . B = Coefficient to be used in Equation 5a (obtained from Table 3). C = coefficient for usein Equation 6a (obtained from Table 3). h = enthalpy of moist air, Btu per pound of dry air. ` - A -- enthalpy correction term to bemadded above 150 F, to enthalpy. . Aa = specific enthalpy of dry air, Btu per pound. . AasAs ~ Aa = the difference between the enthalpy of moist air at saturation per pound of dry air, and the specific enthalpy of-the dryair itself, . Btu per pound of dry air. . ; . . ' hs* = enthalpy of moist air at saturation thermodynamic wet-bulbtempera ture, Btu per pound of dry air. : " ' *. As = enthalpy of moist air at saturation per pound of dry air, Btu per pound of dry air. . hv ^ velocity pressure, inches of water'at 60 F.: ' ; \ ` Aw =* specific enthalpy of condensed water (liquid or solid) at standard pres sure, Btu per pound water. ' Aw* = specific enthalpy of water as added-at * the thermodynamic wet-bulb temperature}*,.Btu per pound of dry air.,.. . , .' K Kelvin degrees. . . KE = kinetic energy, Btu.per pound. , .- f . KE = average;kinetic energy, Btu per pound. , ............... l -- shaft work withdrawn, Btu per pound of air: 1 . ilt = shaft work withdrawn between sections 1 and 2, Btu per pound of air.. 72 CHAPTER 3 1946' Guide Thermodynamics . . .__________ ______________ - 73 . LETTER SYMBOLS (Continued) , '- ' . m = weight of dry air crossing any duct section, pounds per minute. . m\, ms. = weights of dry air convected across sectiohs F\, Ft, - Ft respectively, . pounds per minute: ' M = weight of dry air withdrawn with inside air, pounds per hour. a = mols of dry air. Hw = mols of water vapor., .. . p = total pressure of a mixture of air and water vapor, pounds per square ; inch or inches Hg. . pa. = partial pressure of air, pounds per square inch or inches Hg. ^ p$ = saturation pressure of pure water vapor, pounds per square inch or inches Hg. ' * = partial pressure of water vapor in mixture of air arid water vapor, ^ pounds per square inch or inches Hg. . P = atmospheric pressure, inches Hg. pQ = standard atmospheric pressure by definition 29.921 in. Hg. PE = potential energy, Btu.per pound dry air. . PE == average potential energy,- Btu per pound dry air. i .1 > ! : . ! ' j 1 / * LETTER SYMBOLS (Continued) fas =-fs -- fa the difference between volume of moist-air at'saturation/^ pound of dry air, and the volume of the dry air itself, cubic feet per pound of dry air. .. rs = volume of moist air at saturation per pound of dry auv cubic feet per pound of dry air.. . '. . .- , ; t^r = total volume, cubic feet. . ' `\ V -- velocity, feet per minute. . V = average velocity, feet per minute. -- .- . . W = humidity ratio, of moist air, pounds of water.per pound of dry air. / APF = water to be removed from (or added to) conditioned space, pounds per hour, r . -`' : ', ; Ws -- humidity ratio, at saturation, weight of water vapor per pound of dry '. air, pound per pound. .. - W3* = humidity ratio corresponding to thermodynamic'wet-bulb temperature t*, pounds of water per pound of.dry air. ; ... Z = elevation above any datum,, feet. . . Z = average elevation, feet. '. ' ! q = ratio of energy added (or removed) to water added (or removed), Btu per pound. Also called specific enthalpy of water added. REFERENCES . .. iqt = heat added between sections 1 and 2, Btu per pound dry air.- AqB = heat added between sections A' arid B per pourid of dry air, Btu per pound. ,. aQb = total heat added between sections A and B, Btu per minute. &Q = energy to be removed from or added to conditioned space, Btu per hour. . . R = universal gas constant. .. Ra = gas constant for dry air. -- gas constant for water vapor. :: ' - . i-Thermodynamlc Properties of Moist Air, by J. A. Goff and S. Gratch (A.S.H.V.E. Journal Section, Heating. Piping and Air Conditioning, June 1945, p. 334). .. 2--Low Pressure Properties of Water in the Range. --160 to 212 F. by J. A. Goff and S. Gratch (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning, February 1946). . 2--Thermodynamic Properties of Steam, by J. H. Keenan and F. G. Keyes (John Wiley and Sons. Inc.. New York. 1936). . *--Das i. x-Diagramm fur Dampfluftgemische, by R. Mollier (ZVDI, 1929). * 5_The Theory of the Psychrometer, by' J. H. Arnold (Physics, Vol. 4. 1933). -* 6-Rational Psychrometric Formulae, by W. H. Carrier (A.S.M.F.. Transactions, Vol. 33, 1911, p. 1005). j == entropy of moist air per pound of dry air, Btu per (pound) (Fahrenheit , degree). , . . > i--National Advisory Committee for Aeronautics.'Technical Report No. 538. 1935. . 5 -- correction to be added to entropy of moist air obtained from Equation 6. I = additional correction to be, added to entropy because of "mixing : ' entropy" (obtained'from Table 3). Correction to be added to value of. s obtained from Equation 6, . . , . ' --$a =* specific entropy of dry air, Btu per-(pound) (Fahrenheit degree, ab .. - . solute). f ' / jas = the difference between the entropy of,moist air at saturation per pound of dry air, and the specific entropy of the'dry.air itself, Btu.per (pound of dry air) (Fahrenheit degree, absolute). . , .; ; Jg = entropy of moist air at saturation per..pound of dry air, Btu per (pound of dry air) (Fahrenheit degree, absolute). ... . .' sw- -- specific entropy of condensed water (liquid or solid) at standard atmos pheric pressure, Btu per (pound of water) (Fahrenheit degree, absolute). t* = thermodynamic wet-bulb temperature, Fahrenheit degrees. .> . *(F) = temperature, Fahrenheit degrees. . ... T = absolute temperature, Fahrenheit degrees. . r T0 = standard atmospheric temperature, by definition. 288 Kelvin degrees. . . . ' v = volume of moist air per pound of dry air, cubic feet per pound. v = correction to be added to volume of moist air per pound of dry air, ( above 150 F., . . :. .* . . na =. specific volume,of dry air, cubic feet per pound. CHAPTER 4 3Lid 3(ow Theory; Pressure Loss in Circular and Non-Circular Pipes; Compressible Fluids; Nozzles and Orifices; Steam Flow Meas urement; Metering Liquids; Nozzle Coefficients and Expansion Factors; Pitot Tube; Installation of Nozzles and Orifices. THE flow of fluids is part of the branch of engineering science known as fluid mechanics, which will be discussed here insofar as it applies to the work of engineers in the fields of heating, ventilating, and air conditioning. Probably air is the most frequently handled fluid, but . other gases and liquids are often involved. Compressible fluids (gases) and incompressible fluids (liquids) vary somewhat in behavior, though in cases where pressure and density changes are small, the gases may be treated as incompressible fluids. .. THEORY OF FLUID FLOW The following head equation based on energy considerations for steady flow processes will serve as a basis for the theory of the flow of fluids. This equation is presented in several ways in various texts, but a suitable form is: . . where '-qr--1- Jui -f- piVi + E + Jq + zi = + Jut + pivt + Sj 2g *g ' '. V = velocity in feet per second. . g -- acceleration due to gravity = 32.17 ft per (second) (second). J -- mechanical equivalent of heat = 778 foot pounds per Btu. . u = internal energy, in Btu'per pound of fluid. p = pressure in pounds per square foot. v = specific volume, in cubic feet per pound: - E = mechanical work, in foot pounds per pound of fluid flowing. q = heat transferred to the fluid, in Btu per pound of fluid flowing, and z = elevation above some arbitraty datum, in feet. Subscript 1 refers to the entrance, subscript 2 to the exit. (1) - Introducing the enthalpy h, which by definition is u + , expressed.iri Btu per pound of fluid, Equation 1 becomes .. \ + Jhi + E + Jq + Zi = + Jht + Zj (2) The steady flow energy equation is.. applicable to a wide range of problems in.the flow of fluids. Obviously it applies to flow through pipes," orifices, and nozzles, and to the flow through turbines and centrifugal pumps. Reciprocating engines and pumps are essentially intermittent, but the flow tends to become steady as the number of cylinders increases, and becomes practically uniform at the entrance, and exit if the system . includes receivers and pipes of sufficient size. ' ' By substituting -- (where p is density in pounds per cubic foot) for . ' P. 74 Fluid FUno 75 Fig. 1. Relation of Various Factors in Bernoulli Equation its equivalent po in'Equation 1, the result, after rearranging, will be: ^- + -^-+zi=^- + -^- + ^+ [/(, - ui) -- E -- Jq] (3) In the case of flow through a pipe, no outside work is performed and, if the process is considered adiabatic, and if the change due to turbulence and friction is considered to be negligible, the bracketed expression in Equation 3 will disappear, leaving: . . T.' , Pi , z _ JV , P, , , -qj ~ + * t + -- + zs *g . Pi ig Pi (4) which is commonly called the Bernoulli equation, named after the Swiss mathematician and physician who first propounded the theory. V! . 2g Fig. 2. Relation of Kinematic Viscosity to Temperature of Air Fig. 3. Relation of Kinematic f Viscosity to Temperature of Water 76 CHAPTER 4 1946 Guide . known as the velocity head, --is the pressure head, and z is the elevation . p. head, all in feet of the fluid; the total head, ht is the sum of the other , three heads. Fig. 1 shows diagrammatically the relation of the various factors. The pressure head at point 2 is lower than at point 1 because of . the elevation of point 2 over point 1, and the velocity at point 2.is lower than at point 1 because of the larger pipe diameter at point 2. If the pipe diameter were the same throughout, the velocity, and consequently the velocity head, would be the same at both points, but tlje higher elevation at point 2 would still be responsible for a loss in pressure head. The utility of the equation is evident, though it should be remembered ' that in it the effects offriction and turbulence are neglected, and that Fig. 1 represents ideal conditions. It should also be noted that the Bernoulli equation applies only to incompressible fluids. Pressure Loss in Circular Pipes The pressure loss in circular pipes is customarily expressed by the formula: ' where ft V1 hi = 2gd (5) . hi = the loss in head of the fluid under conditions of flow, in feet. I = the length of the pipe, in feet. V - the velocity, in feet per second. g = the acceleration due to gravity = 32.17 ft per (second) (second). d = the internal diameter, of the pipe, in feet, and, - 1 / = a dimensionless friction coefficient. . The formula is generally known by the name'of Darcy-of Fanning, . though it seems to have been originated by d'Aubisson de Voisins in 1834. The factor / is a function of the Reynolds number ' ' . , where . N*e = ^ I* - ` (6) .. A7Re = Reynolds number. p = the density in pounds per cubic foot. l = the absolute viscosity in pounds per foot-second. . Both / and the Reynolds number are dimensionless. To aid in com puting the Reynolds number, values of * the kinematic viscosity, are shown as a function of temperature for air in Fig. 2 and for water in Fig. 3. Fig. 4 shows the relation between/and the Reynolds number, adapted from a review by Moody1. The straight line sloping downward at the left of the chart supplies the values of / for laminar flow; it represents the formula . 64 f = Nr (7) With laminar flow, the velocity profile is a parabola, having the formula. r_ ' . ' 1 Superior numbers refer to the references at the.end of the chapter. ' i } J Fluid Flow 77 where r = the radius of the pipe in feet. L = distance perpendicularly from the axis of the pipe, in feet. Accordingly, the maximum velocity occurs at the center of the pipe and is twice the average velocity; the average.velocity is found when L = 0.707 r. It is worth noting that roughness of the pipe wall has no effect on the loss in head for laminar flow. ' Between values of the Reynolds number of 2000 and 4000, there is an Fig. 4. Relation Between Friction Factor and Reynolds Number Note: The straight line at left shows values of Friction Factor for laminar flow. , Reprinted by permission from A.S.M.E. Transactions. unstable region where the flow changes from laminar to turbulent, or vice versa. The actual value, is impossible of prediction for any condi tions of flow, though in general it may be said that the prevailing type of flow persists into the unstable region; however, once the change starts, it proceeds very rapidly. .- When the flow is turbulent, the velocity profile is essentially parabolic ' over four fifths of the pipe diameter, but near the pipe walls, the effect of friction becomes evident, and in the boundary layer at the pipe wall the flow is laminar. Fig. 5 compares the velocity profiles'for > three different Reynolds numbers, but for the same average velocity. ` ` The lower curve in the turbulent region in Fig. 4 represents the relation of/ to the Reynolds number for smooth pipe, such as drawn brass tubing or glass tubing. The effect of roughness on/, which is a considerable 78 CHAPTER 4 1946 Guide Fig. 5. Comparison of Velocity Profiles for 3 Different Reynolds Numbers but for Same Average Velocity factor in turbulent flow, is open to some conjecture; artificially roughened pipes, for instance, give results at. variance with actual tests. The curves above the smooth pipe curve of Fig. 4 represent a summary of tests on rough pipe, each of them, identified by a value of e/d, with e signifying the absolute roughness in feet. Values of e/d for different . pipes are given in Table 1. ' To find the friction loss for any. pipe, follow the curve with the proper value of e/d, to the pertinent value of Nrc; and from this point proceed horizontally, to left margin, to find the value of / to use in Equation 5. . Equation 5 is applicable to all liquids, and to gases when the pressure loss is less than. 10 per cent of the initial pressure. When the loss in head is high, the formula to be used for gases is ; , Pi1 - Pi' flVi my ' . pf Fi* . . .. which may be rearranged to give the loss in> pressure V : \ Pressure Loss In Non-Circular Pipes The formulas for flow in pipes are based upon the use of pipes of circular cross-section. The formulas may be used with conduits of other shapes, and in conduits riot flowing full, when the flow is turbulent, by using the hydraulic radius, I?h, which is really a' ratio: . ^ ________ area of cross-section ' wetted perimeter of cross-section ' * (11) Table 1. Values of ejd for Different Kinds of Pipe . Type of pipe Smooth drawn tubing Commercial steel or. wrought iron.___ Asphalted cast-iron.____________ ________ _____________ Galvanized iron..'.......................................... :..............:........ Cast-iron,,...,,.;_.J..................................... ...... 1......... Wood stave........................................................................... Concrete.......... ...................................................... .---- -------Piveted steel...................... ..........................................:.......... . *14 0.000005 0.00015 . 0.0004 ' 0.0005 0.00085 . 0.0006 to 0.003 0:001 to 0.01 - 0.003 to 0i03 Fluid Flout 79 For instance, in a square duct, I ft on a side, handling air, the hydraulic radius is or 0.25. If the same duct is handling water, flowing 9 in. deep, the hydraulic radius is 0.75/2.5 or 0.30. Note in this latter case that the wetted perimeter does not include the distance across the free surface. In the case of a round pipe Ra = :E^ir=`~Tmd = *** (12) Substituting Equation 12 in Equation 6, NRe = ' P and in the flow Equation 5, fiv . hi SgRji and finally in the compressible fluid flow Equation 10, pi -- pi = pi flVi' ] ig'Rll flFlJ (13) . (14) (15) Equations 13, 14, and 15^ may be used to compute the flow in pipes arid ducts of non-circular section and in any type of conduit not flowing full. They should not be used when the flow is laminar. FLOW OF COMPRESSIBLE FLUIDS The energy equation for the flow of compressible fluids, as represented by the gases, is derived from Equation 1. Assuming that no heat is transferred to the fluid, that no work is done, and that there is no differ ence in elevation, Equation 1 becomes . VV IV "2j + Jui + Pill = + Jui + ptVi . (16) or, after rearrangement, ... . IV -- W ------2^------ = pay-- ptVt + /(!-- Ki) ' . (17) Since internal energy, is dependent only on temperature, where u\ -- ut cv{Ti -- 7i) (18) Cv =_the specific Keat of the gas at constant volume. . Ti and I\ -- the temperatures in Fahrenheit degrees at points 1 and 2, respectively. Substituting Equation 18 in Equation 17, ' ,v - IV -- poll -- pii/2 4" Jcv(Ti -- Ti) 2g Now -R J(k -1) (19)' (20) 80 CHAPTER 4 1946 Guide where . , .. R = the gas constant in the expression. . pv.~ RT . ' ' . . ' (21) k = the ratio of the specific heat at constant pressure to the specific heat at constant volume. This ratio, k, is used extensively in fluid dynamics; values of k for various gases are given in Table 2. Table 2. Ratio of. Specific Heat at Constant Pressure to Specific Heat at . Constant Volume for Compressible Fluids . Compressible Fluid Carbon dioxide, methane, natural gas, superheated steam, Ratio k = cp/cy 1.66 1.40 . 1.34 1.28 to 1.32 . , 1.24 to 1.26 Substituting Equations 20 and 21 in'Equation 19, the energy equation becomes . ... v* __ V,2 h 2g = r^i(pm ~ to1** . (22) While this is a convenient form of equation, it does not include all the necessary specifications. If the steady flow process is frictionless and reversible, .. . . -(*)*-.(*)* (23) By introducing this relation in Equation 22 it is possible to reduce that ;equation to: . vs - VS 2g . (24) This form of the.equation is applicable not only to flow in pipes, but also. to flow through orifices and nozzles. . A significant factor in the flow of compressible fluids is the velocity of sound, Eso, which for present. purposes will be 'considered as that velocity under the conditions at the entrance to the steady flow system. The velocity of sound is expressed as . Vt (25) This formula may be developed rationally and agrees perfectly with experimental results. Substituting Equation 25 in Equation 24: 2 Fluid Flout or, by rearrangement, 81 (27) which permits the calculation of the ratio of pressures at entrance and exit of the steady flow device,--pipe, orifice, or nozzle. FLOW THROUGH NOZZLE OR ORIFICE Another useful expression, covering the energy change in an orifice or nozzle, may be derived from Equation 2. As with the flow .through pipes, no outside work is done. Then, assuming that there is no difference in elevation, and since practically no heat is evolved or absorbed, i.e., the process is adiabatic, E, z, and q of Equation 2 may be eliminated, and, by rearranging, the equation becomes Yl vs -- J(hi -- ht) foot pounds per second 2g 2g (28) In any flow device, Mi = or, Vl = -Fl Vt AiVt (29) in which A i or A 2 is the cross-sectional area of the flow at a particular point, expressed in square feet. With, this substituted in Equation 28, and solving for Vi: VrV, = 2gJ(hi - ht) {At/A.Y (vi/vtY (30) Using this expression, it is possible to determine the velocity at any point in the flow through an orifice or nozzle. If the area at the point of entry is very large with respect to that at point 2, the denominator on the right side of Equation 30 will approach unity, and the equation will reduce to ' . V, = V' 2gj(ht - ht) (31) -J-For this reason, the expression ------ -- .. 11- (Az/Atf.ivS/vS) correction factor for the velocity of approach. is called the' ' The velocity of approach factor may be further simplified if the dif ference -in volume between points 1 and 2 is negligible. Under this condition, the velocity of approach factor becomes -J----------------. If . . M 1 - {Ai/AxY At_ = DS At DS (S2 (32) . the velocity of approach factor is in which form it is generally used in flow formulas. The quantity g is the ratio of the throat or.orifice ;diameter to -the pipe diameter. .. .' 82 CHAPTER 4 1946 'Guide The connection of the velocity of sound with the flow of fluids has already been noted. Its most important application is to the. flow of gases through a converging tube or nozzle. If it is assumed that the inlet velocity of the fluid, Vi, is negligible, Equation 24 will reduce to Let W represent the weight of gas flowing through the converging tube in a unit of time, and At the area at the throat; then, . ' W = AiVJih or V, = Wvt/At (34) Substituting this, as well as the relation piVik = ptVtk, in Equation 33 gives, (3s> If this is computed and the figures are plotted, the curved line (partly solid and partly broken) of Fig. 6 is found. The maximum value of may be computed by differentiating W with respect to pt and equating the result to zero. This operation produces the formula: PL = ( 2 Pi \k + 1 / k . . (36) . For air, with k -- 1.40, 0.53. pi Critical Pressure and Critical Flow . Actually, the broken part of the curve is not attained for the flow in the nozzle. If the ratio of pt to pi is decreased from unity, the weight Fig. 6. Relation of Flow of Gas to Pressure Drop in a Converging Tube: Fluid Flout . _., . ' '' . , .. '83 rate of discharge, as well as the volume, increases from zero to a maximum, as shown by the solid section of the curve in Fig. 6; thereafter, as pt/pi is. decreased further, the discharge is constant, as indicated by the horizontal line. The value.of pt at the maximum point is called the critical pressure, or pc, and from Equation 27 it is seen that pc is approximately 53 per cent of pi when air is flowing. ; To find the velocity at the critical pressure, let us assume- that the upstream velocity Vi in Equation 22 is so small as to be negligible. Using the subscript c to indicate conditions at the critical point, we have ' = (i~j) (P`r` ~ /wt) or< . . (k A (flVl- " Kc " y - ) ~ p*'c) . (37) Substituting Equations-23 and 36, and rearranging, Equation 37 becomes and . ' '* - ** . ' . : (38>. . `. Comparing Equation 39 with Equation 25, it will be seen that the velocity at the. throat is equal to the velocity of sound at the critical pressure. , Critical flow is attained only in. converging tubes, in nozzles, and in ' orifices with a well-rounded approach. It does not occur in sharp-edged orifices or in nozzles having an expanding-outlet section. The so-called critical flow prover uses this property of constant rate of flow above `the critical pressure, and finds application as a flow regulator and a quantity- rate meter; in; either case, the theoretical rate of flow may be computed from Equation 38, multiplying Vc by the area of the constriction to obtain the volume rate of flow. , .' In developing the working equations' for orifices and nozzles, it is . customary to start with . .' -Vi1 -- V,* = 2gh, (40) This may be derived from the Bernoulli equation or from the relations of falling bodies. Now, since , . . . AiVi = AtVi = Q3 (41) in which Qsds the discharge rate in cubic feet per second, " - - .- . ' Qi A, 21 Ai' 2ghi Transposing, A,A, QSi V 2ghi Vil,* - A,1 ' i, (42) (43) 84 CHAPTER 4 ' __________ ^_________ 1946 Guide '(44) y the central term on the right hand side of Equation 44 will be recognized as the velocity of approach factor, so that , 1 0s -- At Vl - p* (45) Actual Flow Through Orifices and Nozzles - The actual rate of flow through an orifice, nozzle, or Venturi tube is rarely equal to the theoretical, and generally the actual rate is less than the theoretical. In the case of the nozzle and Venturi tube, this is due to losses from wall roughness, fluid friction, and turbulence during the expansion in the section following the throat. While wall roughness is not a factor in a sharp-edged orifice, fluid friction and turbulence are important, as is the fact that the discharge contracts to a degree variable with the ratio of outlet to inlet pressure after leaving the orifice, so that the limiting area is somewhat less than the opening in the orifice plate. Accordingly, Equation 45 must be modified by a correction factor, C. Usually, the velocity of approach factor is included with this correction factor, and, if . . K=C 1 Vi - e4' (46) 0s = KA, (47) Multiplying by 3600 to convert from cubic feet per second to cubic feet ` per hour and converting area in square feet to diameter in inches, gives . Qi - 3000A'4^4 , . .. or - . ' ' '. ' Qi = 19.635 KD1W2gki. .. .' (48) where .. Qf = -rate-of flow in cubic feet per -hour. Ds = the diameter of the orifice or nozzle throat in inches. ` . 1 . Equation 48 is a general equation, expressing the flow of any fluid through an orifice or nozzle. Further use of it will be made as other types of flow are discussed. .; The differential loss, hi, is in terms-of feet of the fluid flowing through the orifice or nozzle. In the case of a gas flowing, where it is customary to read the differentia! pressure in inches of water, feet of gas must be converted to inches of water. Since dry air at 32 F and 14.7 psi absolute pressure weighs 0.0807 lb per cubic foot, the weight of a cubic foot of any other kind of gas under the same conditions is 0.0807 G, where G is the specific gravity of the gas referred to air. Water weighs 62.37 lb per cubic foot at 60 Fi Using also the relation of 12 in. in i ft,- few 62.37 k 12 - 0.0807G in which Aw .is the differential pressure in inches of water. '. . '` (49) . i j Fluid Flow 85 Fig.'7. Flow Coefficients, K, for Square-edged Orifice Plates and Flange Taps in Smooth pipe Note: From Table 6, Bibliography [HJ. Also, since the gas flowing is'not necessarily at 32 F and 14.7 psi, it is necessary to apply Charles' and Boyle's laws to the density of the gas ` / and therefore: . - few' 62.37 xiilvil f 12 * 0.0807G Pi 492 (50) in which Pi and Ti are the absolute pressure and temperature of the- _ flowing gas. Substituting this in Equation 48, and combining the constants, $Qi = 218.44ifZV Ti PiG (51) Then, to correct the value of Qt to any. other standard conditions of pressure and temperature, using the gas laws, Equation 51 becomes . 0b = 0f X Pb 0b = 218A4XD,' Tt VPjfew TtG (52) (53) Finally, since gases expand under the. conditions of reduced pressure downstream from the orifice or nozzle, an .expansion factor, Y, must be added. The final formula, then, is 0b = 218.44-fiC YD* 4Pjfew TtG (54) In Equatiqn 54, all the data must be observed at the time of measure ment except.A and .Y. These must be obtained from charts, tables, or formulas, derived from or based on the results of a great many experi- . ments, the results of which have been collected by a joint committee of. the American Gas Association and the American Society of .Mechanical - Engineers2'*: The report of the two associations gives orifice coefficients . as a function of the Reynolds number and of the ratio of orifice to pipe - , diameter, for pipes.from 2 to . 12 and 14'in. in diameter, and for four. ^ , '-Fluid Flow 87 - different types'of pressure taps in use in the United States. The coeffici ents are higher for the smaller pipe sizes. .This is an effect of the turbu lence produced by the roughness of the pipe surface, a given roughness being relatively greater with a small pipe than with a large one. ` Space does not permit presenting all the coefficient data that are avail- ., able. However, if the pipe is smooth drawn tubing, the effect of roughness is negligible, and the coefficients for the largest size of pipe apply also to smaller pipes. Figs. 7, 8, 9, and 10 show these coefficients, Nkc, being the Reynolds number referred to the diameter of the orifice or throat of the nozzle, in feet. . Pressure Taps-Location and Types _ ' . The different sets of pressure taps are called flange taps, radius taps, Fig. 11. Relative Location of Flange, Radios and Vena Contracta Taps . vena contracta taps, and pipe or full-flow; taps. The relative locations of the'first'three of these are shown in Fig. 11, and the need for different coefficients for the different taps is indicated by the course of the change in pressure of the flowing fluid shown in the lower part of the figure. Pipe taps are located 2J/ pipe diameters upstream and 8 pipe diameters downstream, both measured from the upstream face of the orifice plate, or in other words, before the orifice plate has had any effect on the flow and after the recovery in pressure has been completed. . Still another type of pressure tap is used in European practice,-- corner taps. Pressures are taken from recesses in the flange connected to annular slits in the comers formed by the pipe wall and the orifice plate. Coefficients for these taps have been adopted by the International Standards Association, but are not used commercially in America. \ It will be noted that the location of the downstream pressure tap of the vena contracta arrangement is variable. Vena contracta is the term ' - applied to the minimum cross-section of the jet from the orifice, where. / 88 ______________________ CHAPTER 4' '1946 Guide , '' 'I ` _, the static pressure is at a minimum. Its location, and the location of'" the downstream vena contracts tap, varies with the ratio of orifice to pipe diameter, and with /ate of flow, as shown in Fig. 12; the tap is generally located<in accordance with the mean curve in the figure. Expansion Factor for Gases . The expansion factor, F, for gases (for liquids, Y =;1) is found from the empirical formula Y = 1 -- (0.41 + 0.35fr) ~ fr/fe) . (55) This is applicable to flange, radius, and vena contracta taps. For pipe - .taps, the formula is ., . Y = 1 -- 0.333 + 1.145 (P + 0.7fl + 12fl`) J ~ *"/*] (56) Values of F for air, computed from these equations, are given in Fig. 13 and Fig. 14. Computing Orifice Discharge - With this information it is possible to compute the discharge from an orifice if the Reynolds number is known. Here an odd complication is . encountered--when the value of 7VRe is computed, the rate of flow, which is the unknown quantity, must be used in the computation. How ' ever, it will be noted in Figs. 7, 8, 9, and 10 that the orifice coefficient does not change greatly as IVRe changes. If, then, an estimate is made of . the velocity, using this in computing IVrc and if the corresponding coef ficient is used in Equation 54, a value for the rate of flow will be found. Using this velocity to compute a corrected value of 7VRe and repeating . the process, a more nearly correct value of Qt is found. This cut-and-try method may be continued for several more cycles, but generally the first or second correction will be found sufficient. . ' Another method, would be to use the value of AT, corresponding to lVRe = cd , modifying this with a factor involving the rate of flow, deter? mined from the temperature, and the differential and static pressures. This method is used by the American Gas Association3.. . ! STEAM FLOW MEASUREMENT . While steam may be considered as a gas, its measurement differs from . that of the usual gases because of a number of factors. Equation 48 serves as the starting point.1 Since it is usual to measure the differential pressure in inches of wafer, it is necessary -to convert fe, the head in feet in terms of the flowing fluid, to few, the actual head in inches of water, ' using the equation' ' . ;' ; ' .(5U where '. Pw -- the density of.water at 60 F (62.37 lb per cubic foot).. , p = the density of the flowing fluid. . Substituting Equation 57 in Equation 48 gives ' ' Qi = 359.15 (58) Fig. 13. Expansion Factor for Air and Other Diatomic Gases Applicable to Flange, Radios and Vena Con- tracta Taps 89 Fig. 12. Location of Vena Contracta in Relation to Ratio of Orifice to Pipe Di ameter and to Rate of Flow ' CHAPTER 4 1946- Guide In steam measurement, a constant head of water is maintained, over each, leg of the manometer by means of condensing chambers, in order to keep the heat of the steam away from the meter. ' As the mercury level fluctuates, the difference in head as recorded on the chart, therefore, is not that due to mercury alone, but to mercury minus an equivalent head of water. To correct for this, the equation . *aw - *w (59) . is applied to Equation 58. The denominator in Equation 59 is the specific gravity of mercury; and the numerator is the difference in specific gravity between mercury and water. Equation 58, hence, becomes Qt = 345.155 KDf (60) Fluid Flow 91. METERING LIQUIDS Orifices are also used for metering'liquids, and Equation 48 serves again as a starting point for, developing the working -formula. Again, too, it is necessary to convert h( to Zkw.'the actual head in inches of water, by substituting Equation 57. It is a|so necessary to correct for the weight of the fluid above the manometer, and since this may be other than water, it is better to use an equation of more general form than Equation .59: p13.557 - - Aaw -- Aw 13.557 (64) where Pf = the density of the fluid over the mercury in the manometer. ,PW -- the density of water at 60 F. ' Fic. 15. Variation of Orifice Plate Expansion Factor, P, with Temperature and Material : Steam is commonly measured in terms of weight, and since '' W = fQ( - , ' (61) where ; - . W = the rate of flow in pounds per hour. ' ' ._ : W = 345.65 KDSVh^p (62) , The expansion factor Y, and the factor P, correcting for the expansion of the orifice plate with the temperature must then be applied, so that W = 345.65 K YPDi VfcTp (63) which is the final form of the equation for the flow of steam through orifices. Values of K may be obtained from Figs. 7, 8, 9, and'10, according to the pressure taps used. Y may be computed from Equations 55 or 56. Fig. 15 gives values of the correction factor P, according to the temperature and the material of the orifice plate. Values of the density, p, may he' . obtained from steam tables, such as Keenanand Keyes4, which are widely used. -' Fig. 16.' Shape of ASME Long Radius Nozzle When Ratio of Throat to Pipe Diameter is 0.53 or Less . . Fig. 17.' Shape of ASME Long Radius . Nozzle When Ratio of Throat to Pipe Diameter is 0.4 to 0.7 ' Substituting Equations 57 and 64 in Equation 48 gives '. ; Qi = 44.764 K.D' - 0.00118). _ ; (65) . Then, since liquids are generally measured in gallons instead of cubic feet, and since there are 7.4805 gal in. l cu ft, . ' ', ' . Qw = 334.86 KDt (-L - 0.00118). - - (66) ' . $ in which Qv is the discharge or rate-of flow, in gallons per hour. ' |] .'Since liquids,,for practical purposes, are incompressible, no expansion ' factor is .necessary. If circumstances demand, the 'factor P for the . expansion of . the orifice may be applied. Also; if it is necessary to correct ', the volumetric discharge to a base temperature,-application'of the known: . . expansion.characteristics of the liquid will enable the conversion. Values- `s' ' 92^V CHAPTER 4 ' ' 1946 Guide of K again are obtainable from Figs. 7, 8, 9, and-10, according to the type of pressure tap. ' ' NOZZLE COEFFICIENTS AND EXPANSION FACTORS Nozzles differ from orifices in that the flow is guided to the throat in such a way that contraction of the jet is suppressed, or, in other words, there is no vena contracta. Because of this fact, the coefficients are different from those of orifices, and very close to unity before the velocity of approach factor is added. Also, the expansion factor may be deduced rationally, rather than empirically, as with orifices. . Two shapes of nozzles that have been under investigation by the . A.S.M.E. for some time are shown in Figs. 16 and 17. They are referred 0.2 Fig. 19. 0.3 0.4 as 0.6 0.7 08 09 DIAMETER RATIO p Relation of Nozzle Discharge Coefficient, C, for 6-Inch Pipe, To Diameter Ratio and Reynolds Number coefficient for a given nozzle shape is higher if the finish of the surface is smoother. , ` Discharge coefficients, C, for pipes 2, 6, and 10 in. in diameter are given in Figs. 18, 19, and 20, as correlated by Bean, Beitler and Sprenkle6, . as functions of the diameter ratio $ and the Reynolds number referred ' to the diameter of the throat in feet. to as long-radius nozzles. Their contour is that of a semi-ellipse, and the ` contracting portion is followed by a cylindrical section of the same area as the throat. The shape shown in Fig. 16 is designed for use with ratios of throat to pipe diameter of 0.53 or less, that of Fig. 17 for ratios of 0.4 to 0.7. The most usual location of pressure taps is 1 pipe diameter up stream and ]/2 diameter downstream, both measured from the plane of the nozzle inlet. In addition, the International Standards Association has adopted still another shape of nozzle, which has a rather sharper approach-than the A.S.M.E. nozzles, and which uses corner taps. Very little use of this nozzle has been made in this country. ' . The formulas already given for orifices apply equally to nozzles except for discharge coefficients, and for the expansion factor, .when it is applied. Discharge coefficients for nozzles, as for orifices, vary with pipe size; they may either increase,r decrease with decreasing sizeof pipes depend- . .' ing on the sharpness of the approach curvature of the nozzle.. For the A.S.M.E. nozzles, they tend to decrease. Generally speaking, too, the. 94 CHAPTER 4 ' 1946 Guide - \ *- ' Coefficients from these curves must be multiplied by '--^===, the velocity of approach factor, in accordance with Equation 46, to obtain the value of K to use in the various equations. . The expansion factor for nozzles, designated by q>, is obtained from a rational formula, as already noted. , J(lA2/* ( k Vi-(ft/*)*- l/k\( 1-e4 \ f A i - p* to/p.)2/* / (68) This formula is plotted for k = 1.40 (air and other diatomic gases) and & = 1.30. (steam, carbon dioxide, natural gas) in Figs. 21 and 22, respect ively. . ' Fluid Flow___________' ,;;__________________________________________, 95 pressure, which is the sum'of the static and kinetic pressures, while' the tube directed crosswise receives only the static pressure; the difference between the two, as read on the separate tubes or on the U-tube is, of ' course, the kinetic pressure. The velocity is expressed as , V = VWi ' (69) Application of Equation 57 serves to make the. formula general, assuming that water is used in the manometer connecting the two tubes. Using tins equation, and mutiplying by 60 to convert feet per second to feet per minute, . Fm = 1096.5 ^*25 , (70) in which Vm is the rate of flow in feet per minute. Fig.' 21. Relation of Expansion Factor, <p, for Nozzles to Diameter Ratio and Pressure Loss for Air and Other Diatomic Gases FLOW MEASUREMENT BY PITOT TUBE There remains one other head type meter useful in ventilating work, the Pitpt tube, named for the Frenchman who discovered the principle. The Pitot tube is essentially a bent tube with its open end pointed upstream, combined with another tube with its end pointed crosswise to the flow or downstream,, or connected to openings crosswise to the flow. Used with flowing liquid, the liquid will rise in each tube, but higher in the one pointed upstream. Used with a flowing gas, and the two tubes : connected by a U-tube containing.water,.the liquid level in the U-tube will be displaced, with the lower level on the side connected, to the tube pointed upstream.- The tube'directed hpstream receives the impact . Fig. 22. Relation of Expansion Factor, 9, for Nozzles to Diameter Ratio and Pressure Loss for Steam, Carbon Dioxide and Natural Gas It is often difficult to obtain the exact static pressure. In the usual construction of Pitot tubes, the static pressure openings are downstream from the impact pressure opening, and turbulence induced by the nose may affect the static pressure reading. If the static pressure openings point downstream in anj? degree, a suction effect is' produced to falsify the reading. In instruments having the static pressure opening pointed downstream, the coefficient may be as low as 0.86. Consequently, for _ accurate work, Pitot tubes should be calibrated, and the pertinent coefficient should be applied to-Equation 69. In a sense,, this coefficient is advantageous, since it results in a higher differential reading, which, in turn, enables more accurate readings at low flows. . . In.using Pitot tubes, it is generally necessary to make a traverse'of the pipe or duct to. determine the course of the velocity pattern. In a pipe, for instance, one of the profiles, shown in Fig. 5 would be obtained. Near a valve or fitting, however, the profile might be quite distorted, a ^ 96 CHAPTER. 4 1946 Guide fact which would be revealed, by the traverse. If the pipe or duct is divided into equal areas, and a determination of-AaW is made for each, the average velocity would be obtained by using the average of the square roots of /iw in Equation 70. ' INSTALLATION OF NOZZLES AND ORIFICES . A final note should be made of the installation of orifices and nozzles. Generally speaking, the orifice or nozzle, together with a holding arrange ment, including pressure taps, is available from the manufacturer. In making the installation, the user should make certain that the flow Fig. 23. Minimum Conditions to be Observed When Installing Orifices and Nozzles Between Fittings and Valves approaching the nozzle or orifice is-steady and evenly distributed, .i.e.t with velocity profiles similar to those shown in Fig. 5. Fittings and valves, which tend to direct the flow to one side, and which in some cases cause, it to rotate as it advances, must be far enough upstream from the orifice of.nozzle to permit the disturbed stream to straighten out to the even form before reaching the meter. Minimum conditions in the installation for, avoiding, trouble from fittings and valves.are. shown in Fig. 23. If* necessary,-straightening vanes may be used upstream from the orifice or nozzle at a distance of not less than 8 pipe diameters. '. ` -The. information given in this chapter is of necessity an abridgment. It is strongly recommended that anyone contemplating accurate measure-, ment should refer to the references and bibliography given at the end of thischapter. . ` . Fluid Flow 97 LETTER SYMBOLS USED, IN CHAPTER 4 (5 = ratio, throat or orifice diameter to pipe diameter. .; ' ' . y. -- absolute viscosity in pounds per foot second. . * jjl/p = kinematic viscosity in square feet per second. ' , p = density of flowing fluid in pounds per cubic foot. .. ' pw = density of water at 60 F, (62.37 lb per cubic foot). Pf -- density of fluid over mercury in a manometer. 9 = expansion factor for nozzles. . . ` . A = cross-sectional area of flow, in square feet. . ' C = correction factor (coefficient of discharge) for flow through orifice, nozzle " or Venturi. . . cp -- specific heat of gas at constant pressure. - Cv -- specific heat of gas at constant volume. .. D = diameter of fluid stream in feet. d' = internal diameter of pipe in feet. `' E = mechanical work in foot pounds per pound of fluid flowing. e = absolute roughness of pipe surface, in feet. . /. = dimensionless friction coefficient. '` g -- acceleration due to gravity = 32.17 ft per (second) (second). G = specific gravity of gas referred to air. .. h = enthalpy, Btu per pound of fluid. . .. /taW = loss of head in inches of water. ` hi = loss of head in feet of fluid. . ht = total head in feet-of fluid. , ' hw ~ differential pressure in inches of water. . . J -- mechanical equivalent of heat = 778 foot-pounds per Btu. K -- flow coefficient (correction factor), including velocity of approach, for flow ' through orifice, nozzle or Venturi. ` k ~ ratio of specific heat at constant pressure to specific heat at constant volume. L =. perpendicular distance .from axis of. pipe in feet. . ;. l = length of pipe in feet. . N*e -- Reynolds number. - , .. - P = correction factor for expansion of orifice piate with temperature. . y P -- pressure in pounds per square foot. . Pc = critical pressure. . - Pb ,= standard pressure to which correction is to be made, pounds per square inch, . absolute. Pf = pressure of gas flowing, pounds per square inch,.absolute. . Qb =.rate of flow in cubic feet per hour under standard conditions of pressure and temperature. ' @f = rate of flow in cubic feet per hour. . @s = discharge rate in cubic feet per second. Qw = rate of flow in gallons per hour. q = heat transferred to the fluid per pound of fluid flowing. ` R = gas constant. . . ' ,* Rr = hydraulic radius = ratio of area of cross-section to wetted perimeter of cross section. . r = radius of pipe in feet. . . T ~ temperature, Fahrenheit degrees, absolute. Tb ~ standard temperature to which correction is to be made, Fahrenheit degrees ' absolute. .. '- 7f = temperature of gas flowing, Fahrenheit degrees,-absolute. , = internal energy,.Btu per pound of fluid. . V. = velocity in feet per second. . .i Vc = critical velocity, feet per second. .' . Fso = velocity of sound, feet per second. 98 CHAPTER 4 1946 Guide Vm = velocity in feet per minute. v -- specific volume, cubic feet per pound. . W = weight of gas flowing,' pounds per hour. * Y = expansion factor--correcting for expansion of gas under reduced downstream pressure. ''' z -- elevation above some arbitrary datum, in feet. REFERENCES *--Friction Factors for Pipe Flow, by Lewis F. Moody (A-S.M.E. Transactions, 66, 1944, 671-678; Dis cussion, idem. 66, 1944.678-684). ' ' History of Orifice Meters and the Calibration. Construction, and Operation of Orifices for Metering. Report of the Joint A.C.A.--A.S.M.E. Committee on Orifice Coefficients (American Society of Mechanical Engineers, 1935). '. *--Gas Measurement Committee Report No. 2. Natural Gas Department (American Gas Association, 1935). . . .. Thermodynamic Properties of Steam, by Joseph H. Keenan and Frederick G. Keyes Uohn Wiley & Sons. Inc.. 1936). . - s--Discharge Coefficients of Long Radius Flow Nozzles When Used with Pipe Wall Pressure Taps, by H. S. Bean, S. R. Beitler, and R. E. Sprenkle (A.S.M.E. Transactions, 63, 1941, 439-442; Discussion, idem. 63, 1941, 442-445). - BIBLIOGRAPHY [A] Principles of Thermodynamics, by G. A. Goodenough (Henry Holt & Co.). [BJ Principles of Engineering Thermodynamics, by Paul J. Kiefer and Milton C. Stuart (John Wiley & Sons, Inc., 1944). . . [CJ Fluid Mechanics, by Russell A. Dodge and Milton J. Thompson (McGraw-Hill Book Co., 1937). [D] Fluid Mechanics, by R. C. Binder (Prentice-Hall, Inc., 1943). , fE] The Physics of Solids and Fluids, by P. P. Ewald, H. Poschl and L. Prandtl (Blackie, 1936). . . [FJ A Study of the Data on the Flow of Fluids in Pipes, by Emory Kemler, Hydraulic Paper HYD-55-2 (A.5.M.E. Transactions 55, No. 10, 7-22, 1933; Discussion, idem., 55, No. 10,23-32, 1933). ., , '_ ' . [G] The Flow of Fluids in Closed Conduits, by R. J. S. Pigott (Mechanical Engi neering 65, 1933, 497-501, 515). /' [H] Fluid Meters, Their Theory'and Application (American Society of. Mechanical Engineers, 4th edition, 1937). - ' '/l [II Fluid Meters, Their Selection and Installation (American Society of Mechanical' '. Engineers, 1933). ` . [J] The Orifice Meter for Measurement of Flow of Gases and`Liquids, by . Allen D. MacLean (Pittsburgh Equitable Meter Co., 1938). ,. , [KJ Flow Measurement (American Society of Mechanical Engineers, 1940). ^ ` [LJ Pitot Tube Practice, by Edward S. Cole {A.S.M.E. Transactions 57,1935,281-294; Discussion, idem. 68,1936, 146-156). . \ .. ,, [M] Pitot Tubes in Large Pipes, by Edward S. Cole and .E. Shaw Cole {A.S.M.E. Transactions, 61, 1939, 465-473; Discussion, idem. 61, 1939, 473-475). ' [N] Investigation of Errors of Pitot Tubes, by C. W. Hubbard {A.S.M.E. Trans actions, 61, 477-497; Discussion, idem. 61, 1939, 497-506). ' [O] Piping Arrangements for Acceptable Flowmeter Accuracy, by R. E/ Sprenkle {A.S.M.E. Transactions, 67, 345-357, 1945; Discussion, idem. 67, 357-360, 1945). CHAPTER 5 Jundamentaii of Jdeat nJransfer Conduction, Convection, Radiation, Combined Convection and Radiation, Heat-Flow Resistance, Electrical Analogies, Practical Heat Transfer Problems, Unit Conductances for Convection Flow Systems, Radiation Factors or Emissivities, ' Solutions for Steady-State Conduction Problems . HEAT is that form of energy which is transferred from place to place by virtue of an existing temperature difference. The temperature difference is the potential which causes the transfer, the latter in turn being resisted by the thermal properties of the material combined in a simple term and known as the resistance. Energy exchange associated with mass transfer from place to place (evaporation, condensation, etc.) due to concentration differences is treated elsewhere such as in the section on cooling tower design in Chapter 37. The objectives of this chapter are to: 1. . Describe the mechanisms and present the rate equations for the different modes of heat transfer. . 2. Illustrate the application of the basic concepts to steady-state problems (tempera ture independent of time or a cyclic variable thereof) by means of several typical solutions of heat transfer systems. , . Further-applications to specific systems will be found throughout The Guide. ' CONDUCTION. CONVECTION AND RADIATION Thermal conduction in fluids is the term applied to the mechanism of heat transfer whereby the molecules of higher random kinetic energies transmit by direct molecular collision part of their energy to adjacent. 'molecules of lower random kinetic energy. Since the .temperature is proportional to the random kinetic energy of the molecules, thermal transfer will occur in the. direction of decreasing temperature. The molecules oscillate about a mean position at fairly high velocities and frequencies, but there is no net material -flow associated with the con duction mechanism. In the case' of fluids, thermal conduction is signi- . ficant in the region very close to a solid boundary or wall, for in this region the flow is laminar, parallel with the wall surface, and there are. practically no cross currents in the direction of the heat transfer across the solid fluid boundary. In solid bodies the significant mechanism of heat transport is always thermal conduction and is ascribed to an energy transfer mechanism associated with the free electrons l. . Contrasted to the thermal conduction mechanism, thermal convention involves energy transfer by eddy mixing and diffusion 1 in addition to conduction. This condition is pictured schematically-in Fig. 1 which exhibits transfer from a pipe wall at surface temperature t, to a colder fluid at a bulk temperature k- (Bulk temperature is that which would be attained if the fluid stream were drawn off at a certain section and mixed. It is therefore slightly higher than the lowest temperature in the stream). In the laminar sublayer, immediately adjacent to the wall; the heat transfer occurs by thermal conduction; in the transition region, which is called the buffer layer, eddy mixing as well as conduction effects are significant; in the eddy or turbulent region the major fraction of the transfer occurs by eddy mixing. 99 100 ,CHAPTER 5 1946-Guide In most commercial equipment the main body of the fluid is in turbu lent flow, and the laminar film exists at the solid wails only, as shown in Fig. 1. But in cases of low-velocity flow in small tubes, or with viscous liquids such as heavy oil (low Reynolds numbers), the entire flow may be . laminar. In these latter cases there is no transition or eddy region. When the fluid currents are induced by sources external to the heat transfer region, as for example a pump, the described solid to fluid heat transfer is termed forced convection. In contrast, if the fluid currents are internally generated, as a result of non-homogeneous densities arising from the temperature variations, the heat transfer is termedfree convection. In the conduction and convection mechanisms heat is transferred as internal energy, i.e., the random molecular kinetic energy associated with the material temperature. For radiant heat transfer, however, a change in energy form takes place from internal energy at the source to electro magnetic energy for transmission, then back to internal energy at the receiver. Since radiant energy exhibits characteristic wave lengths, the Fig. 1. Thermal Convection Conditions Fig. 2. Thermal Conduction in a Flat Slab solution of thermal radiation problems is in many respects similar to the solution of problems in the field of illumination. ` .. ' The rate, of thermal current flow (i.e., rate of heat transfer), corre sponding to the three transfer mechanisms previously described, may be expressed by three rate equations. These are similar to Ohm's Law for ' electrical flow, the current flow through a resistance being proportional to the potential difference. Thermal Conduction Equation , Equation 1 states symbolically that the thermal conduction current per unit transfer area normal to the flow, (dq)/(dA), Btu per (hour) (square foot), is proportional to the temperature gradient (dt)/(dL), degrees Fahrenheit per foot. The proportionality factor is termed the thermal conductivity, k, Btu per (hour) (square foot) (degrees Fahrenheit per foot of thickness). Al___kJL dA dL (1). The minus sign on the right side of the equation is introduced to indicate positive current flow in the direction of decreasing temperature. Fig. 2 shows the physical significance of indicated quantities. .- It should be emphasized that the thermal conductivity used should be expressed in consistent units; either using the inch or foot throughout. ' Fundamentals of Heat Transfer 101 Expressions of conductivity used in the heating field are usually inconsistent in this sense, in that it is customary to refer to the con ductivity per square foot but for one inch of thickness. This custom has been adopted for the reason that wall thicknesses are usually expressed in inches, whereas if expressed in feet, decimal or fractional thicknesses would result. When, dealing with flat walls no complication is involved in using the inconsistent expression of conductivity. However, when curved or spherical walls are considered, considerable complication is involved. Therefore, in this discussion the consistent units of con ductivity expressed in Btu per (hour) (square foot) (degrees Fahrenheit per one foot thickness) are used throughout. Conductivity values obtained from Chapter 6 or Table 1 in this chapter, which are expressed in inconsistent units, must therefore be converted for use in the calculations of this chapter by dividing by 12. As an example, the conductivity of brick, expressed in inconsistent units as 5.0 in Table 2 of Chapter 6, becomes 0.42 when Table 1. Approximate Unit Thermal Conductivities.3 Conductivity, k = Btu per (hr) (sq ft) (deg F per in.) ` Material Air. ` Aluminum...'............ . .. Brass (70 -- 30) ......... Cast-Iron.........-............ Copper......................... .. Glass.--..... :....................... 'k 0.168 1416.0. ' 720.0 336.0 2640.0. 3.6--7.32 Material Nickel............ j......... ..... Soil................................... Steel, mild.............. :..... Water,.liquid................ k 240.0 408.0 2.4--12.0 312.0 ! 4.08 . . &Thern?pl conductivities depend to some extent on temperature. The above magnitudes are approxi mate only. Refer to Heat Transmission, by W. H. McAdams (McGraw-Hill Co., 1942) for additional values. .. used in the calculations of this chapter. Also, it should be emphasized that in order to make the calculations and applications consistent in this chapter, all dimensions of thickness must be expressed in feet. , Thermal Convection Equation . ! '- ' . = he ((.. - tt) ' '" (2) This rate equation states that the thermal convection current per unit transfer area (dq)/(dA), Btu per (hour) (square foot) is proportional to the temperature difference, (ts -- k) which is the temperature of the surface less that of the fluid. The particular fluid temperature to use for a given system will be noted under the discussion of that system. The proportionality factor is termed the unit convection conductance (some times called the film coefficient for convection), hc, Btu per (hour) (square foot) (degree' Fahrenheit). These convection conditions are illustrated in Fig.,1. .' . The heat transmission by free or natural convection for objects sur rounded by air can be conveniently expressed as in Equation 2a: ' f where ^ . (- ) U )1 \ O.f / 1 \ 0.1B1 ft . ..... : (2a) ,. <7c " heat transmission by convection, Btu per (square foot) (hour). 1 C -- a constant depending upon the surface shape. . 102 CHAPTER 5 ' 1946 Guide D = diameter of pipe or circular duct or height of vertical wall, inches. (Effect of diameter or height becomes constant at 24 in.) . # lav = average of wall surface and surrounding air temperature, degrees Fahrenheit absolute. ' ts -- tt ~ temperature excess between wall, surface and surrounding air, degrees Fahrenheit. . For horizontal cylinders, the value of C = 1.016 has been well estab lished by various investigations. For vertical plates, the value of C = 1.394 has been fairly well established. Suggested values * of C for hori zontal plates warmer than the surrounding air, are 1.79 when facing upward and 0.89 when facing downward. Table 2. Heat Transmission by Free Convection for Large Vertical Surfaces Expressed in Btu per square foot per hour . Dbg F 0 1 2 3 4 5 6 7 8 9 Temperature Difference between Body and Surrounding Still Air at 80 F 0 10 20 30 40 50 60 70 80 90 100 110 120 130 0 4.4 0.3 4.9 0.6 S.S 1.0. 6.0 1.4 6.6 1.8 7.3 2.3 7.9 2.8 -8.5 3.3 9.1 3.8 9.7 10.4 11.1 11.8 12.5 13.2 13.9 14.6 .15.3 16.0 16.7 17.4 18.1 18.9 19.7 20.5 21.2 22.0 22.7 23.5 24.3 25.0 25.8 26.7 27.5 28.3 29.2 30.0 30.8 31.6 32.4 33.2 34.1 34.9 35.7 36.6 37.4 38.3 39.1 40.0 40.9 4i.8 42.6 43.5 44.3 45.2 46.1 47.0 47.8 48.7 49.7 50.6 59.9 51.5 60.8 52.4 61.8 53.4 62.7 54.3 .63.7 55.2 64.6 56.1 65.6 57.1 66.5 58.0 67.5 59.0 68.4 69.4 79.4 89.2 70.3 80.4 90.2 71.3 81.4 91.2 72.3 82.4 92.2 73.3 83.3 93.3 74.3 84.2 94.3 75.3 85.2 95.-8 76.3 86.2 96.3 77.4 87.2 97.4 78.4 88.2 98.4 99.4 100.4 101.5 102.6 103.6 104.7 105.7 106.7 107.8 108.8 109.8 110.9 112.0 113.0 114.1 115.2 116.3 117.3 118.4 119.5 The heat transmission by free convection from vertical walls j24 in. or more in height is given in Table 2 as calculated from Equation 2a for ' an ambient air temperature of 80 F. The values in Table 2 are not changed appreciably by a considerable change in air temperature for a given temperature excess. For instance, a change in air temperature < from 80 to 40 F will increase the heat transmission given in Table 2 by only 1.3 per cent. . ,' . Table 2 can also be used for calculating the free convection rate of transmission for various commercial shapes such as pipes and ducts. These calculations are simplified by the use of the factors in Tables 3 and 4. Table 3 gives factors by which the values in Table 2 must be. multiplied to obtain the-free-convective transfer from various shapes whose characteristic dimensions are 24 in. or over, and Table 4 gives the factors to be used in conjunction with the factors in Table 3 for obtaining the free convection from Table 2 for pipes and ducts whose characteristic dimensions are less than 24 in. . - ' For example, the free convection transfer from a 3 in. O.D. horizontal cylinder .for a temperature difference of 40 F = 25.0 X 0.73 X 1.52 = 27.7 Btu per (square foot) (hour). .. ' Problems in either forced convection or natural convection may be solved by the simple first-power equation if the convection coefficient is expressed as a unit conductance: -. . Qc -- he A (/i --. Ij) . . (2b) Fundamentals of Heat Transfer , . _ J03 where .. qc = heat transmission by convection, Btu per hour. A = surface area, square feet. t, -- tt = temperature difference between the surfaceand the fluid degrees Fahrenheit. ' he = unit conductance, from Table 5, Btu per (square foot) (hour) (degree Fahrenheit temperature difference.) Table 3. Free Convection Factors-for Various Shafes Shapes Factor 0.73 0.88 1.00 1.28 0.64 0.64 1.28 Table 4. Free Convection Factors for Various Diameter Pipes . or Various Height Plates Actual O.D., or height, in.____ 1 Factor. -- - - 1.88 Actual O.D., or height, in...____ 9 Factor .. 1.22 2 1.64 10 1.19 3 1.52 12 1.15 4 1.43 14 1.11 5 1.37 16 1.09 67 1.32 1.28 18 , 20 1.06 1.04 8 1.25 22 . 1.02 Thermal Radiation Equation ... - The relation shown in Equation 3 is usually applicable to systems in which radiant exchange takes place between the surfaces of solids, as sche- ' . ?r = c-4,FaFe (TV - TV) . ' (3) matically shown in Fig. 3. Gaseous and luminous radiation are not consid ered in this discussion. Equation 3 states that the net radiation current per unit transfer area of surface 1, qT/A Btu per (hour) (square foot), which seer surface 2 through a non-absorbing medium, is proportional to .the difference of the fourth powers of the absolute surface temperatures (7V -- TV). The proportionality factor-(u FaFe) may be conveniently separated into three parts: . o = the Stefan-Boltzmann radiation constant. = 1730 X 10-" Btu per (hour) (square foot) (degree Fahrenheit absolute temperature to the fourth power). . Fi = the configuration factor is dimensionless and < 1. This factor accounts for the shape and relative position of the two surfaces. The value of Fa = 1 may be used in the cases of large parallel planes, long concentric cylinders or smaller - . bodies in large enclosures. ' . ' .. ,FS = the emissivity factor is also dimensionless and 1. This factor accounts for the absorption and emission characteristics of the surfaces for the radiation which exists. Individual emissivities (e) should be taken from Table 6 and applied, for either radiation or absorption, as follows: ,, ' ` . . a. For a small body in a large enclosure, use the emissivity of the small body only: FB = ii. ' 104 CHAPTER 5 ' 1946 Guide b. For rectangles or disks,' either parallel or perpendicular and with a common side, use the product of the emissivities: Fb = e* X e. c. For large parallel planes, long concentric cylinders or large enclosed bodies, use. both emissivities in the equation: . Fe ei 6j The radiation under black-body conditions, or for an emissivity of 1.0; is given in Table 74 for cold surfaces as low as -- 39 F to warmer surfaces as high as 139 F. The emissivities of a number of surfaces ordinarily encountered in engineering practice are shown in Table 6. For radiation table at higher temperatures,, and further discussion of radiation calcu lations,'see Chapter 31. Surfaces Insulated Cold Water Line , NOMENCLATURE AND DIMENSIONS FOR TABLE $ cp = fluid unit heat capacity at constant pressure, Btu per (pound) (degree Fahrenheit) .. D = cylinder diameter, feet. '" . ; . G = 3600 Yep -- fluid mass velocity, pounds per (hour) (square foot of flow cross-section). .. p = density, pounds per cubic foot. \ . he -- unit conductance for thermal convection,. Btu per (hour) (square foot) - (degree Fahrenheit). ' . k = `unit thermal conductivity of the fluid, Btu per (hour) (square foot) (degree . -Fahrenheit per one foot thickness). ; . . ` Rm = hydraulic radius of the. flow cross-section = flow cross-section area per wetted perimeter, feet. ` ' ' - $ = fin spacing, feet. t = average fluid film temperature, degree Fahrenheit. it--ti ~ temperature difference surface to main fluid, degree Fahrenheit. * V8 = fluid velocity, feet per second. . (a = fluid viscosity, pounds per (hour) (foot) = viscosity in centipoises X 2.42. Combined Convection and Radiation . , It should be noted that the previous equations and tables give the heat transfer by convection and by radiation computed separately. In many Fundamentals of Heat Transfer 105 Table 5. Approximate Unit Conductances for Thermal Convection for Several Flow Systems3 ' Expressed in Convenient Empirical Form ' Case System Unit Conductance Equation!* Forced Convection ' Longitudinal flow in cylinders, turbulent 1. region. Fluid being heatedo. - For > 3000 . he " ,0.0036 G*/&* 2. For longitudinal air flow in cylinders case 1 reduces toe. For (-^-) > 3000 ^ftc = 0.00486 (1 + 0.010 ' 3. For longitudinal water flow in cylinders case 1 reduces toe. For (-pp~) > 3000 4. Air flow normal to a single right circular fc> = 0.45 (-5- ) + 0.178 C (-5-)' " cylinder. ' 5. Air flow over staggered pipe banks. / fr \*41 A* = 0.061 6. Air flow over single spheres. 7. Air flow over plane surfaces. ' G,* < Ac 0 040 oTa 0 < t < 250 F he - 1 + 0.22 VB For V% < 16 fps or Ac - 0.53 V.* * 16 fps < Ve < 100 fps . . . 8. Air flow normal to finned cylinders. 0 < t < 250 F ' Free Convection^ 0. Single horizontal right circular cylinder in air. " '23 Vo--) 10. Vertical surfaces in air. he = 0.3 . 11. Top surface of horizontal plates to air.' Ac = 0.4 (i--/*> * . . 12. Bottom surface of horizontal plates to air. he = 0.2 </i-*)- ' Heat Transmission, by W. H. McAdams.- bFluid properties should be evaluated at the arithmetic mean fluid temperature. It (^surface *1" *fluid) divided by 2. s -- . Thee expressions are applicable to longitudinal flow in other than right circular cylinders provided the hydraulic radius is employed as the conduit dimension parameter. For non-circular cross-sections D * 4 Rq. dFor low rates of heat transfer by free convection the exponent decreases towards zero, and for higher rates increases towards 0.33. The following equations employing an exponent equal'to 0.25 are applicable in the intermediate range. . '' - . . ` .' 106 ' :" : 1 ' CHAPTER 5 " t ... 1946 Guide 1: 1 ` ' practical cases it is desirable to treat convection and radiation as a single combined process, using a first-power equation: - ffrc = Arc 'A (ii -- it) ' . (4) where ?rc is the total heat flow due to radiation and convection, in Btu per hour. Values of hm the surface or film conductance for combined Table 6. Radiation Factors or Emissivities, e. For the determination offactor FK in Equation 3 Class N ' Surfaces ' - Fraction of Black-Body Radiation" At 50-100 F At 1000 F Solar - Radiation i A small hole in a large box. sphere, furnace, or enclosure 0.97 to 0.99 0.97 to 0.99 0.97 to 0.99 ' 2 Black non-metallic surfaces such , as asphalt, carbon, slate, paint, paper............................ .... 0.90 to 0.98 0.90 to 0.98 0.85 to 0.98 3 Red brick and tile, concrete and stone, rusty steel and iron, dark paints (red, brown, green, etc.)..................................... 0.85 to 0.95 0.75 to 0.90 0.65 to,0.80 4 Yellow and buff brick and stone, firebrick, fire clay........... ,.......... 0.85 to 0.95. 0.70 to 0.85 0.50 to 0.70 5 White or light-cream brick, tile, paint or paper, plaster, white wash........... ..................................... 0-85 to 0.95 0.60 to 0.75 0.3 to 0.5 6 Window glass.... ................................ 0.90 to 0.95 .................. - Transparent 7 Bright aluminum paint; gilt or bronze paint. ............................... 0.4 to 0.6 ..................... . 0.3 to 0.5 . - 8. : Dull brass, copper,-or alumi num; galvanized steel; pol ished iron......... ;....... ................... 0.2 to 0.3 0.3 to 0.5 0.4 to 0.65 9 Polished brass, copper,, monel metal. ............................................ 0.02 to 0.05 0.05 to 0.15 0.3 to 0.5' 10 Highly polished aluminum, tin plate, nickel, chromium.............. 0.02 to 0.04 0.05 to 0.10. O'. 10 to 0.40 radiation and convection, are given in Chapter 6, Table 1 and Fig. 3. ' Complete tables for the combined heat transfer of steam arid hot water ' radiators, pipes, coverings, etc., will be found in the appropriate chapters. When dealing with the effect of operating temperatures upon the com -! bined heat transfer of a given piece of equipment (as for instance a steam radiator), another form of equation is frequently used: ' 5rc = B A ((, - <,)" . (5) Values of n in this equation usually range from 1.3 to 1.5 (see Chapter 25). The-chief advantage.of this equation is .the convenience.^ representing _' .heat transfer performance on logarithmic coordinates, and the factor B \ should be regarded as a simple constant of proportionality. . ~ .. Fundamentals of Heat .Transfer __________ . ' ______ 'j107. HEAT-FLOW RESISTANCE . ' In most of the steady-state heat transfer problems encountered in air. conditioning applications, more than one of the heat transfer mechanisms are effective, and the thermal current flows through several resistances in' . Series or in parallel. In using the resistance concept the calculations in volved are analogous to the application of Ohm's Law in electricity, viz., the heat flow or thermal current is directly proportional to the thermal Table 7. Heat Transmission by Radiation for Black-Body Conditions3 , Expressed in.Btu per {square foot) {hour) - . Temp Deg F -30 -^20 -10 0 0 ^i 59:3 65.2 71.4 78.0 58.7 64.7 70.8 77.4 -2 58.2 64.1 70.1 76.7 -3 57.7 63.5 69.5 76.0 -4 57.2 62.9 68.9 . 75.4 --5- 56.7 . 62.3 68.3 74.7 -6, 56.2 61.7 67.7 74.0 -7. -8 55.7' 61.1 67.1 73.4 55.2 60.5 66.4 72.7 -9 54.7 59.9 65.8 72.1 0 +i; +2 +3 . '+* :+5 ' +6. 0 10 20 30 40 ' 50 -60 70 80 90 100 110 120 130 78.0 85.0 92.4 100 109 118 127 137 148 159 170 183 196 211 78.7 85.7 93.3 101 110 119 128 138 149 160 171 . 184 197 212 '79.4 . 86.5 94.0 102 111 120 129 139 150 161 173 185 199 214 80.1 97.2 94.8 103 112 121 130 140 151 162 174 187 200 215 ' 80.8 88.0 95.6 104 112 122 131 142 152 163 175 188 201 217 . 81.5 1 82.2 . 88.7 . 89.4 96.4 97.2 105 105 113 il4 123 123 132 133 143 144 153 - 154 164 166 176 178 189 191 203 204 218 220 +J +8 82.9 90.4 98.0 106 115 124 134 145 155 167 179 192 206 221 83.6 90.9 98.8 107 116 . 125 135 146 156 168 180 193 207 222 +9 84.3 91.7 99.6 108 117 .126 136 147 157 169 182 195 209 '224 Example: Radiation from walls of room at 32 F to surface at -- 25 F for effective emissivity of 0.95 =' (102 -- 62.3).0.95 = 37.7.Btu per (square foot) (hour).' . - . ,, potential or temperature difference, and inversely proportional to the therrhal resistance: " ' ' 9rc = --^----tt \ (6) ' Following the electrical analogy, when there is a thermal current flowing . . . through several resistances in series, the resistances are additive: . . Rr = Rl + R,- R,+ +Rn ' (7) . Similarly, conductance is the reciprocal of resistance, arid for heat flow . . . through several resistances in parallel, the conductances are additive: ' - Practical Heat Transfer Problems . .. .. , . The use of these simple relations for resistance and conductance simpli- ' . fies rriany practical'heat transfer problems. - As discussed in Chapters 6/ . 7 and 28, the practical analyses of heat transfer in building walls, in . fin-tube coils and in pipe coverings, are usually computed by this method. , 108 __________ ;CHAPTER 5_______________________________ __ _________1946 Guide The same resistance analysis may be applied to complicated steady- ' state conduction problems. Table Vindicates the solutions in six common cases of steady-state conduction. . A complete analysis by the resistance method is well illustrated by considering the heat transfer from the air outside to the cold water inside of an insulated pipe. The temperature gradients and the nature of the resistance analysis are indicated by the two sketches of Fig. 4. Since air is sensibly transparent to radiation, there will be some heat transfer by both radiation and convection to the outer insulation surface. The mechanisms act in parallel on the air side. The total current, by radiation and convection then passes through the insulating layer and the pipe wall by thermal conduction, and thence by convection into main cold water streams. Radiation is not significant on the water side as liquids are sensibly opaque to radiation, although water transmits energy ' in the visible region. The contact resistance between the insulation and . the pipe wall is presumed to be equal to zero. Referring to Fig. 4, the thermal current for a given length N of pipe, 5re, Btu per hour, may be thought of as flowing through the parallel resistances Rt and 2?c, associated with the insulation surface radiation and convection transfer. Then the flow is through the resistance offered, to thermal conduction by the insulation, R3, through the pipe wall resistance, Rt, and into the water stream through the convection resistance, Ri. Note the analogy to the direct current electrical circuit problem. A temperature (potential) drop is required to overcome these resistances to the flow of thermal current. The total resistance to heat transfer, J?t, hour degrees Fahrenheit per Btu, is the summation of the individual resistances: ,- Rt = Ri + Rt + Rt + R, (9) where the resultant parallel resistance Ri is obtained from: -L = _L + _L ' R, Rr ^ Rc . Provided the individual resistances may be evaluated, the total resistance can be obtained from this relation. Then the heat transfer current for the length of pipe (N, ft) can be established by the relation: . ' Src (Btu per hour) -- ^-=--!f . Rt For a unit length of the pipe the heat transfer rate is: (10) . ^ (Btu per hour foot) = (11) ' The temperature drop, A t, through an individual resistance may then be calculated from the relation: \ . At ~ R Qrc where R is the resistance in question. , The problem is now reduced to one of evaluating the individual resist ances of the system. This entails suitable integration of the rate- Equa tions 1, 2 and 3 to produce expressions of the form: Fundamentals of Heat Transfer 109 Table 8. Solutions'for Some Steady-State Thermal Conduction Problems3^ Expressions for the resistance R entering Into' No. . the equation: ., g = At/R (Btu per hour) . i. Flat wail or curved wall if curvature is small (wall thickness less than 0.1 of inside dia meter). . L kA Surface area A Radial flow through a right circular cylinder. ,Ot R 2rkN (See footnote c). The buried cylinder. ^A^AW k .At:tp-ts `-Id . Long cylinder of length. N Radial flow in a hollow sphere. jJSI- 2-wkN ' far --r > 3 (See footnote c). 2ftAT The straight fin or rod heated at one end. Conduction k cross-section y ______ area, A Finned surface of area HB. R - htp tanh m L. (see footnotes d and ) For ml > 2.3, tanh m L * 1 ' m = \/kgP/kA . A -- conduction cross-section area. P = .perimeter of cross-section A. ,. . ht = unit conductance to the surroundings from the fin surface. . k thermal conductivity fin material. Af wall temperature--ambient temperature (* + *) h% (-2- tanh ml + s') HB A/ deflned.as in Case 5 above. "The dimensions to be employed in these solutions are: length of dimension p, L, r = feet; units of ft = Btu per (hour) (square foot) (degree Fahrenheit for one foot thickness); units of ft, Btu per (hour) (square foot) (degree Fahrenheit); units of area, A = square feet. /- *The thermal conductivity, ft, in these solutions should be taken at the average material temperature (see Table 5). ... . ' *Log x 2.303 iog x. . - '. - . ' ` dThis expression can also be employed as an approximation for tapered fins or of annular fins by employ ing average magnitudes of A and p. . .` Tanh is the hyperbolic tangent. ' _ - *, no. CHAPTER 5 . -1946. Guide'. where q is the.heat transfer rate, arid At is the potential drop or tempera ture difference through the resistance R. .Table 8 lists such solutions for six different conduction systems. Table 2 in Chapter 6 and Table 1 of this chapter indicate the magnitudes of the thermal conductivities, k, to be employed in the expressions of Table 8, after dividing k by 12. The solution applicable to the problem depicted in Fig. 4, for the calculation of R2 and Rj, is case 2 in Table 8. Thus for a 1 ft length of 2 in: nominal size, pipe (I. D. = 2.067 in., O. D. = 2.375 in.) insulated with 1 in. of material having a conductivity of 0.025: . 1.188 log. 1.033 Ri = 8.5 'X 10:* hr degree Fahrenheit per Btu. 2% X 26 X 1 2.188 log, 1.188 R, = 2x X 0.025 X 1 = 3.9 hr degree Fahrenheit per Btu. The convection resistances to beat transfer from the pipe wall to the cold water, Ri, and from the air to the surface of the insulating material, Rc, are dependent on the flow conditions prevailing at these surfaces, and on the thermal properties of the fluids.' The unit conductances for . thermal convection, Ac, Btu per (hour) (square foot) (degree Fahrenheit), have been determined by test for many flow systems. These data may be employed to predict the conductances for similarflow systems. Table 5 summarizes some empirical equations expressing such test results. For the problem under consideration (Fig. 4) case 3 of Table 5 is applicable for the calculation of the cold water side convection resistance Ri. Corresponding to the water velocity of 5 fps, the mass velocity is: G = 5 (ft per sec) X 62.4 (lb per cu ft) X 3600 (sec per hr) = 11.2 X 10s lb per (hour) (square fopt). ' . The inside diameterof the pipe D is ?I067 = 0.1725 ft. . .. 12 . '; . The average water film temperature will be estimated as 36 F (mixed mean fluid temperature of 34 F). Then case 3, Table 5 yields: . .. Ac = 0.00486 (1 + 0.36) ,. ' Fahrenheit). = 650 Btu per (hour) (square foot) (degree \ . ,mj . The transfer area on which this conductance is based is the inside tube area. Associated with 1 ft length of pipe there are: . . ' . x X2 X 1 = 0.542 sq ft. - Thus the resistance for 1 ft of tube length is: '. . . - AcxP Xl. " 650 >?0.542 = 2 8 X hr de?ree Fahrenheit P" Btu- ' Case 9, Table 5 is applicable for calculating the free thermal convection resistance,-Rc, existing between the surrounding air and: the-insulation. -The air temperature is given as 120 F. As an approximation a 20 deg Fundamentals of Heat Transfer ' ' ill temperature difference between the air and the pipe surface will be assumed.- Then case 9 yields: ' . ' D=if-S = 0.364 ft. = 0.63 Btu per (hour) (square foot) (degree Fahrenheit). (13) This result may not be deemed conservative inasmuch as the expression is for still air. If, however, the air is not still, but flows at approximately 5 mph or 7 fps the.mass velocity corresponds to: G = 7 X 0.07 X 3600 = 1770 lb air per (hour) (square foot). A magnitude of k = 0.014 Btu per (hour) (square foot) (degree Fahren heit) per one foot thickness applied to case 4 yields: '- = 0.017.+ 2.8 = 2.8 Btu per (hour) (square foot) (degree Fahrenheit). This conductance is based on 1 sq ft of outside lagging area. Thus, since 4.375 . ' ... ... there are x X = 1.14 sq ft of outside lagging area associated with 1 ft length of pipe: ' Rc = 2 8 X 1 14 = hr degree Fahrenheit per Btu. The radiation resistance, Rr, which acts in parallel with the convection resistance, -Rc', for the transfer of heat to the surface of the insulation, may be calculated. For the purposes of this illustrative problem it will be assumed that the insulated pipe is exposed to (sees)1 surroundings, which exist at 120 F. Then the angle factor, EA, is unity and for an estimated surface emissivity of 0.9 (see Table 6), Ee = 0.9. As a first approximation the insulation surface temperature will be estimated as 20 deg below the surroundings at 120 F. Then the radiation per degree of temperature difference, by Equation .3 (or more conveniently by Table 8) divided by the temperature difference will be: - . . Ar (196 - 170) 0.95 20 1.17 Btu per (hour) (square, foot) (degree Fahrenheit). The outside surface area of the insulation associated' with 1 ft of pipe length was previously calculated as 1.14'sq ft. Thus: Rr = ~f ~17 X 1 14 = kr degree Fahrenheit per Btu. The resultant resistance of Rc and i?r acting in parallel (see Fig.'4) can now be evaluated as: . = Q-^J2 + 7)^5 = 4.54 Btu per (hour) (degree Fahrenheit). ' R< = 0.22 hr degree Fahrenheit per Btu. The over-all resistance, Rt, surroundings to cold water, is the sum of -Ri + Rj + Rz + Rt = 4.1 hr degree Fahrenheit per Btu for 1 ft length- 112 \_________-_____________ CHAPTER 5 1946 Guide of pipe. Note that the controlling resistances are Rz and R, and that neglect of both Ri and Rt would not significantly influence the total re sistance, Ri. , . On the basis of this resistance calculation the heat transfer from the surroundings to the cold water may be evaluated as: . -Jj- = ^----- = 21 Btu per (hour) (foot) or about 0.175 tons of refrigeration per 100 ft of pipe. Since the calculation is based on a 1 ft pipe length: . 3rc = 21 Btu per hour. The temperature drops through the various resistances are now readily evaluated by Equation 12 as: ` <o--<sj 1st--ht kt--tsi tm--If air to insulation surface = Ri grc = 0.22 X 21 = 4.6 F. through the insulation = Ri Qrc -- 3.9 X 21 = 82 F. through the pipe wall = Rt grc = 8.5 X 10"* X 21 = 0.02 F. pipe wall to cold water = Ri grc = 2.8 X 10"* X 21 = 0.06 F. :. The-solution was obtained on the assumption that the air temperature and the outside temperature differed by 20 F. In order to obtain a slightly better estimate of the rate of heat transfer the numerical solution should be repeated using the temperatures calculated from the previous listed temperature.differences. The foregoing problem serves to illustrate a general method of solving ` steady-state heat transfer problems. There are many problems which cannot be approximated by steady-state solutions. For instance, the problem of pipe line insulation in transient service; the behavior.of auto matically controlled thermoflow circuits; or the periodic absorption.of solar energy by roof and wall structures during the day and nocturnal . radiation to the cold sky at night. The transient heat transfer problem differs from the steady-state in that energy storage rates need to be considered. Thus thermal capacity in addition to resistance effects is significant. The vector sum of the thermal capacitance and resistance is ` the thermal impedance. It is not within the scope of this chapter to deal with many .of these problems. There are, however, solutions available in graphical form for certain special cases. Also a general approximate method may be employed which is analogous to the treatment of capacity- resistance lumped parameter electrical circuits. ; - REFERENCES , I--The Metallic State, by H. Hume-Rothery (Oxford Press, 1931). ' ' Absorption and Extraction, by T. K. Sherwood (McGraw-Hill Co., 1937)., '' *--The Transmission of Heat by Radiation and Convection, by Griffith and Davis (.Special Report No. 9, . 1922, Department of Scientific and Industrial Research, His Majesty's Stationery Office, London, England). 4--Heat Insulation in Air Conditioning, by R. H. Heilman (Industrial and Engineering Chemistry, Vol. - 28, July, 1936, p. 782). , CHAPTER 6 ^JrandmiiSion Coefficients of (Cuilclincj. Wuteria is v; Heat Transfer Symbols; Calculating Over-all Coefficients; Conductivity of Homogeneous Materials; Surface Conduct ance; Air Space Conductance; Practical Coefficients and Their Use; Computed Heat Transmission Coefficients; Roof Co efficients; Combined Ceiling arid Roof Coefficients; Basement Floor, Basement Wall, and Concrete Slab Floor Coefficients, Condensation in Buildings ' THE design of conditioning or heating systems for buildings requires a knowledge of the thermal properties of the walls enclosing the space. The rate of heat flow through the walls under steady-state conditions at design temperatures is usually the basis for calculating the heat required. For a given wall under standard conditions the rate as a specific value designated as U, the over-all coefficient of heat transmission. It may be determined by test in a guarded hot box apparatus or it may be computed from known values of the thermal conductance of the various components. Because testing of all combinations of building materials is impracticable, the procedure and necessary data for calcu lation of the value of U are .given in this chapter, together with tables of computed values for the more common constructions. HEAT TRANSFER SYMBOLS U = over-all coefficient of heat transmission (air to air); the time rate of heat flow expressed in Btu per (hour) (square foot) (Fahrenheit degree temperature difference between air on the inside and air on the outside of a wall, floor, roof or ceiling). The term is applied to the usual combinations of materials in construction and also to single materials, such as window glass, and includes the surface conductance on both sides. k -- thermal conductivity; the time rate of heat flow through a homogeneous material under steady conditions through unit area per unit temperature gradient in the direction perpendicular to the area. Its value is expressed in Btu pet (hour) (square foot) (Fahren heit degree per inch). Materials are considered homogeneous when the valueNof k is not affected by-variation in thickness or size of sample within the range normally used in'construction. C -- thermal conductance; the time rate of heat flow through a material from one of its surfaces to the other per unit temperature difference between the two surfaces. Its value is expressed in Btu per (hour) (square foot) (Fahrenheit degree). The term is applied to specific materials as used which may be either homogeneous or heterogeneous. / = film or surface conductance; the time rate of heat flow between a surface and the surrounding air. Its value is expressed in Btu per (hour) (square foot of surface) (Fahrenheit degree temperature difference). Subscripts i and o are used to differentiate between inside and outside surface conductances respectively. a thermal conductance of an air space; the time rate of heat flow.through an air space per unit temperature difference between the boundary surfaces. Its value is ex pressed in Btu per (hour)(square foot of area)(Fahrenheit degree). The conductance of an air space is dependent on the temperature difference, the height, the depth, the position and the character of the boundary surfaces. The relationships are not linear and accu rate values must be obtained by test and not by computation. R = thermal resistance. Its value is expressed in Fahrenheit degrees per (Btu) (hour) (square foot). It may represent any of the following and must therefore be properly described: 's 1 ,,. . .. --jj = over-all or air-to-air resistance . . -i- = resistance per unit thickness (resistivity) .. . 113 ^14 CHAPTER 6 1946 Guide = resistance of a material (surface-to-surface) . * = film or surface resistance * f . i: . -- = air space resistance . CALCULATING OVER ALL COEFFICIENTS Prom Chapter 5, Equation 7, the total resistance to heat flow through a wall is equal numerically to the sum of the resistances in series. Then by definition, .. . ' where ' . V= = Rt Ri + Ri + Ri -F * * + Ra ' Ri, Ri, etc. are the individual resistances of the wall components.. -f?t r - total resistance. - (1) ' ' For a wall of a single homogeneous material of conductivity k and thick ness x, with surface coefficients /i and f0 . . U= 7i k + /o (2): For a compound wall of. three homogeneous materials in series, having conductivities k\, k2 and k3 and thicknesses xu x2 and x3 respectively, and laid together without air spaces, . U1 Rt _1___ , h li x ,___ Xt_ + it (3)' For a wall with air space construction and consisting of two homo geneous, materials of conductivitiesA and k3,. thicknesses and *2, and separated by an air space of conductance a x, + kv -.+ (4) . In the case of types' of building materials, having non-uniform'or irregular sections such as hollow clay tile or concrete blocks, it is necessary to use the conductance C of the section unit as manufactured instead of a.conductivity k. The resistance of.the section ~ is therefore substi tuted for in Equations 2, 3 and 4. . :. ` . CONDUCTIVITIES AND CONDUCTANCES The method of calculating the over-all coefficient of heat transmission for a given construction is comparatively simple, but accurate values of conductivities and conductances must be used to obtain satisfactory results. In addition there are sometimes parallel' heat flow paths of different resistances in the same wall,, which require modification of the Heat Transmission Coefficients of Building Materials _____________ . '. '115 formula. In such cases calculated result's should'be checked by test measurements. ' . V ' '' \: ' ` The determination 'of the fundamental' conductivities and conduc tances requires considerable skill and experience. to obtain accurate results. It is recommended that thermal conductivities of homogeneous ' materials be determined by means of the Guarded Hot Plate l. For deter mination of conductances, a Guarded Hot Box method s is generally used. Tables 1 and 2 give conductivities and conductances which' are quite generally used in calculation and which have been selected.from various sources. Wherever possible the properties, of the material and test conditions are given. In selecting arid applying heat transmission values to any construction, caution is necessary, because coefficients for the same material may differ because of variations which occur, in test methods, in the materials themselves, or in. the temperature of the mater- ial when tested. !. ' ' . Conductivity of Homogeneous Materials. ' .' . . Thermal conductivity is a property of a homogeneous material and of types of building materials such as lumber, brick and stone which may be considered homogeneous. Most insulating riiaterials,. except air spaces and reflective types, are of a porous nature arid consist of combinations of solid matter with small air cells. The thermal conductivity of these . materials will vary with density, mean temperature, size of fibers or particles, degree and extent of bond between particles, moisture present, and the arrangement of fibers or particles within the material. . The effect of density upon conductivity (at constant mean temperature) is illustrated'for two fibrous materials in Fig. 1. It will be,noted that for each there is an optimum density for lowest conductivity: Typical variation of conductivity with mean temperature is shown in Fig. 2. Fig. 1. Typical ' Variation of Thermal Conductivity with . , Density--for Fibrous ,.. - Material '0 1 2 '3 4 56 DENSITY POUNDS PER CUBIC FOOT Fig: 2. Typical Variation of _ Thermal Conductivity with', ' Mean Temperature - ' ' 116 CHAPTER 6 1946 Guide Table l. Conductances (C) for Surfaces and Air Spaces All conductance values expressed in Btu per (hour) (square foot) (Fahrenheit detree temperature difference), ' Section A. Surface Conductances for Still Air* Position of Surface ' Direction of Heat Flow ' Surface Emissivity e 0.83 e - 0.05 Upward Downward 1.21 . 1.52* 0.74 Section B. Conductance of Vertical Spaces at Various Mean Temperaturesb Mean Temp Fahr Deg Conductances of Air Spaces for Various Widths in Inches 0.128 0.250 0.364 0.493 0.713 1.00 1.500 20 2.300 1.370 1.180 1.100 1.040 1.030 1.022 30 2.385 1.425 1.234 1.148 1.080 1.070 1.065 40 2.470 1.480 1.288 1.193 1.125 1.112 11105 50 2.560 1.535 1.340 1.242 1.168 1.152 1.149 60 2.650 1.590 1.390 1.295 1.210 1.195 1.188 70 2.730 1.648 1.440 1.340 1.250 1.240 1.228 80 2.819 1.702 1.492 .1.390 1.295 1.280 1.270 90 2.908 1.757 1.547 1.433 1.340* 1.320 1.310 100 2.990 1.813 1.600 1.486 . 1.380 1.362 1.350 110 * 3.078 1.870 1.650 1.534 . 1.425 1.402 1.392 120 3.167 1.928 1.700 . 1.580 1.467 1.445 1.435 130 3.250 1.980 1.750 1.630 1.510 1.485 1.475 140 3.340 2.035 - 1.800 1.680 1.550 1.530 1.519 150 3.425 2.090 1.852 1.728 1.592 1.569 1.559 Section C. Conductances and Resistances of Air Spaces Faced on One Surface with Reflective Insulation^ ' Location and Position of Air Space Direction of Heat Flow Temp Diff Fahr Deg Winter Summer Conductance* (C) No. of Air Spaces 1 23 Resistance* () - ` No. of Air Spaces - 1 2 3* Rafter Space (8 in.) Horizontal Horizontal. Down Up 45 45 0.10 0.27 0.07 0.17 10.00 14.29 3.70 5.88 Horizontal Horizontal Down Up 25 - * 25 0.09 0.24 0.06 0.16 11.11 16.67 4.17 6.25 30 deg slope 30 deg slope Down Up 45 45 0.15 0.25 0.10 0.17 6.67 10.00 4.00 5.88 30 deg slope 30 deg slope -. Down Up 25 0.13 0.09 ' 7.69 11.11 . 25 0.23 0.14 4.35 7.14 Stud Space (Z*A in-) Vertical/ Vertical . ' 30 0.34 2.94 40 0.23 0.13 . 4.35 7.69 Vertical/ Vertical 15 05^ 3.13 20 0.18. 0.11 5.56 9.09 Vertical - 30 0.46 2.17 "Radiation and Convection from Surfaces in Various Positions, by G. B. Wilkes and C. M. F. Peterson (A.S.H.V.E. Transactions, Vol. 44, 1938, p. 513). . ' 6A.S.H.V.E. Research Report No. 825--Thermal Resistance of Air Spaces, by F. B. Rowley and A. B. Algren (A.S.H.V.E. Transactions, Vol 35, 1929, p. 165). ' - "Thermal Test Coefficients of Aluminum Insulation for Buildings, by G. B. Wilkes, F. G. Hechler and E. R. Queer (A.S.H.V.E. Transactions. Vol. 46. 1940). .-* ^Temperature difference is based on total space between plaster base and sheathing, flooring or- roofing. "These air space conductance and resistance values are based on one reflective surface (aluminum)' having an emissivity of 0.05 facing each space and are based on total space between plaster base and sheath* ' . ing, flooring or roofing. .The rafter and stud spaces are divided into equal spaces. /Stud space is lined on plaster base side with loose paper with aluminum on surface facing air space. The resistance of the small air space between the plaster base and paper was 0.43. ' "Radiation and Convection Across Air Spaces in Frame Construction, by G. B. Wilkes and C. M. F. Peterson (A.S.H.V.E. Transactions, Vol. 43. 1937, p. 351). ' *The recommended surface conductance for calculating heat losses for still air for non-reflective surfaces la 1.65 Btu. For a 15 mph wind velocity, the recommended value is 6.0 Btu. . These' coefficients were derived from Fig. 3 which was based on tests conducted at the .University of Minnesota, and apply to vertical surfaces. . " .` ' Heat Transmission Coefficients of Building Materials 117 Table 2. Conductivities (k) and Conductances (C) of Building and Insulating Materials - These constants are expressed in Btu per (hour) (square foot) (Fahrenheit degree temperature difference). Conductivities (k) are per inch thickness and conductances (C) are for thickness or- construction stated, not per inch thickness. . `' Material Description - Conduct! v itt ' __ Resistance ^ Dbnbitt (Lb pub Mean Temp Co Ft) Deo) OR Conductance > (O Per Inch Thickness For Thickness Listed 0 U) (*) 1 < BUILDING BOARDS (NoN-lKSULATINa)----- Compressed cement and asbestos sbeeta_ 123 86 2.70 057 Corrugated aabestoB board___ --___,,___ 20.4 110 0.48 _ 2.08 Pressed asbestos mill board....... 60.5 86 054 -1.19 Gypsum board--gypsum between layers of heavy paper___ ______________ __--- 62.8 70 1.41 0.71 H in. gypemaboard..--__ ________ ______ . 3.73 H in- gypsum board__ _________ __ 252 H in- gypsum board__ ___________ , 535 90 -- 2.60 -- (1) 2) -- (3) (3) 0.27 055 0.38 (1) FRAME CONSTRUCTION 1 in. firsheathing and building paper.... .... ____ 30 -- 056 -- . 1.16 (4) COMBINATIONS------------ 1 in. fir sheathing, building paper and yellow pine Upsiding............. .......... ...... ____ 20 -- 050 ----- 2.00 (4) 1 in. fir sheathing, building paper and stucco........... ............................._______ ____` 20 ____ 052 ----- - 152 C4) Pine lap siding and building paper, Biding 4 in. wide.__......___ ____________ ____ 16 055 Ycllow pine lapriding,........--............ ....... -- - -- 1.28 1.18 0.78 S41' (4) MASONRY MATERIALS Brick.--...........-------------- -- Damp or wet____ _______________ _____ 5.0* 0.20 Common yellow day brick_--_________ -- 45 - ,, 051 One her yellow common day brick, one tier face brick, approx. 8 in. thick,.....,, -- -- -- 0.77 (2) -- (4) 150 (4) Clat Tub, Hollow---------------- 2 in. Tile, H in. plaster both rides._______ 4 in. Tile, H in. plaster both sides...... ....... 6 in. Tile, Yi in.- plaster both sides--___--. 8 in. Tile, average of 8 types (Walls No. 59,63,64,66.67.90,91,92) 12 in. Clay tile wall: 8in.x5in.xl2in. and 4 in. x 6 in. x 12 in..... -........... _...... 120.0 127.0 1245 ____ ____ 110 100 105 -- -- ' Concrete. Sand and gravel aggregate, various ages and miTM <__________________ Sand and gravel aggregate.--__ ______ limestone aggregate___________________ Cinder aggregate!_________ _________ __ Steam treated limestone slag aggregate.,. Pumice (Mined in California) aggregate. Expanded burned day aggregate___ ___ Burned clay aggregate. Blast furnace slag aggregate!........ '........... Expanded vennkuliteaggregate--___ _ Expanded vermiculite aggregate,____ __ . __ 142 75 132 - 75 97 75 74.6 . 75 65.0 75 59.9 75 67.1 75 76.0 70 20 90 26.7 90 1.00 0.60 -- 0.47 -- 052 -- -- 056 -- 1155 to ,, 1656 12.6 105 ,4.9 257 2.42- __ 258 256 __ 1.6 0.68 ` 0.76 0.09 to 0.06 0.08 . 0.09 052 0.44 0.41 0.44 055 0.63 1.47 152 ' 150 1.67 2.13 (2) (2) (2) 1.92 (4) 3.84 * ___ (4) (5) ,,__ ...... ___ ___ ___ __ _ -- (4) (4) (4) 4) (4) (4) (4) (3) 3 (3) Authorities: ' '' lU. S. Bureau of Standards, tests based on samples submitted by manufacturers. . *A. C. Willard, L. C. Lichty and L. A. Harding, tests conducted at' the University of Illinois. *J. C. Peebles, tests conducted at Armour Institute of Technology, based on samples submitted by- - manufacturers. -* *F. B. Rowley, et al. tests conducted at the University of Minnesota. A.S.H.V.E. Research Laboratory. ' .` . *E. A. AUcut, tests conducted at the University of Toronto. - .. . See Thermal Conductivity of Building Materials, by F. B. Rowley and A. B. Algren (University of . ' Minnesota Engineering Experiment Station Bulletin No. 12). ' 6Heat Transmission Through Insulation as Affected by Orientation of Wall, by F. B. Rowley and ' '' C. E. Lund (A.S.H.V.E. Transactions, Vol. .49, 1943, p. 331). . . ' .: .s ; The Effect of Convection in Celling Insulation, by G`. B. Wilkes and L. R. Vianey (A.S.H.V.E. Trans actions, Vol. 49, 1943. p. 196). - -. ' *See A.S.H.V.E. Research Report No. 915--Conductivity of Concrete, by F. C. Houghten and Carl Gutberlet (A.S.H.V.E. Transactions, VoL 38, 1932. p. 47). : - - . See Heating, Ventilating and Air Conditioning, by Harding and .Willard, revised edition, 1932. .- /See BMS13, U. S. Department of Commerce, National Bureau of Standards, Washington. D. C. "Roofing, 0.15 in. thick (1.34 lb per square foot), covered with gravel (0.83 lb per square foot), combined------- thickness assumed 0.25. ' . ... / 118 CHAPTER 6 -r_______________ 1946 Guide v . Table 2: Conductivities (A) and Conductances (C) of'Building and Insulating Materials--Continued These constants are expressed, in Blu per (hour) (square foot) (Fahrenheit degree temperature difference). ' Conductivities (k) are per inch thickness and conductances (Q are for thickness or construction stated, not per inch thickness. Heat Transmission Coefficients of Building Materials 119 Table 2. Conductivities (k) and Conductances (C) of Building and Insulating Materials--Continued . These constants are expressed in Btu per (hour) (square foot) (Fahrenheit degree temperature difference). Conductivities (k) are per inch thickness and conductances (C) ore for thickness or construction stated, not per inch thickness. .. Materia) WOODS--(Continued) Description Density (Lb peb Mean Temp Co Ft) (Fahb Deg) Conductivity OB Conductance (t) (O Resistance 1Per Inch Thickness For. Thickness listed (t) (i)' n n .< Hard maple, 0 per cent moisture*................ Maple Made, ftcrcwi mtin ... Norway pine, 0 per cent moisture*___ ^___ Red cypress, 0 per cent moisture*_________ Red oak, 0 per cent moisture*. Short leaf yellow pine, 0 per cent moisture* Soft elm, 0 per cent moisture*....................... Soft maple, 0 per cent moisture*.................. Sugar pine, 0 per cent moisture* Virginia pine West coast hemlock, 0 per cent moisture* White pine.______________________________ . Sawdust, various Shavings, various from dnf>PT................. Shavings, from maple beech and birch 46.0 44.3 40.0 32.0 32.0 48.0 36.0 34.0 42.0 28.0 34.3 * 30.0 31.2 12.0 8.8 13.2 75 86 75 75 75 75 75 75 75 75 86 75 86 90 90 .90 1.05 1.10 '1.20 0.74 0.79 1.18 0.91 .0.88 0.95 0.64 0.96 . 0.79 0.78 0.41 0.41 . 0.36 **.* 0.95 0.91 033 135 1.27 035 1.10 1.14 1.05 136 1.04 137 1.23 2.44 2.44 2.78 ------- (4) (1) (3) (4) (4)' (4) (4) (4) (4) (4) (1) 4) Id (l) <1) (1) INSULATING MATERIALS Blanket and Bat Insulations_______ __ ______ , Chemically treated wood fibers -held between layers of strong naner ........ Ed grass between strong paper.....^..-____ Ed grass between strong paper . Flax fibers between strong paper__________ Chemically treated hog hair between kraft paper ,,. Chemically treated hog hair between kraft paper and asbestos paper____ ___ _ Hair fdt between layers of paper Kapok between burlap or paper. _______ Stitched and creped expanding fibrous blanket....................... ............... ................. .. ... Paper and asbestos fiber with' emulsified annhalt hinder Cotton insulating bat... __ _ Cotton fibers . Short Staple Lintera, Fireproofed............ Short Staple Lintcrs, Fireproofed............ Short Staple Iinters, Fireproofed............ Short Staple lintera, Fireproofed............ Short Staple Linters, Fireproofed............ Short Staple Iinters, Fireproofed............ Fdted cattle hair....... .......................................... Fdted cattle hair Felted hair and *he*tnA ` Ground paper between two layers, each H in- thick made up of two layers of kraft paper (sample % in. thick)............. 3.62 4.60 3.40 4.90 70 90 90 90 5.76 71 7.70 11.00 1.00 71 75 90 1.50 70 4.2 0.875 94 72 6.25 90 4.50 90 2.45 90 ' 1:60 90 0.85 -90 0.65 90 13.00 11.00 90 90 7.80 . 90 12.1 75 0.25 0.26 0.25 0.28 0.26 . - 0J28 0.25 0.24 0.27 0.28 0.24 0.25 0.24 0.24 0.26 0.29 0.30 0.26 0.26 0.28 4.00 335 4.00 337 335 - 337 . 4.00 4.17 3.70 337 4.17- 4.00 4.17 4.17 335 3.45 333 334 . 334 -337 0.40. -- 230 (3) (1) (1) (1) (3) (3) (3). (1) (3) (1) (3) (1) (1) (1) (1>(1) 0) (1) (1) (1> (4) Reflective^ ............ See Table 1, Section C_______________ _____ ...... - - --- Insulating Board . . s notes on Page 117. Made from stnr u>* fiber . .... 13.5- 70 Made from corn atalfa 15.00 71 Made from exploded wood fibers........^____ 17.90 78- Made from hard wnnd fihm* 15.20 70. Made from wood fiber..........,,................ j___ 15.90 72 Made from wood fiber.............. . 15.00- 70 Made from wnnd fiber 52 Made from wnnd fiber .830 ' 72 Made from wodd fiber.... .......... .. 15.20 Made from wood fiber ... ................. ' 16.90' 90 0.33 0.33 0.32 .032 '0.33 033 033 0.29 033 : 03i; *3.03 3.03 3.12 3.12 3.03 :-3.033.03 3.45 3.03 2.94 (3V (3) (4) 13) (3)(3) (6) (3) (3) (D 120 CHAPTER. 6 1946 Guide Table 2. Conductivities (k) and Conductances (C) of Building and Insulating Materials--Concluded These constants are expressed in Btu per (hour) (square foot) (Fahrenheit degree temperature difference). Conductivities (k) are per inch thickness and conductances (C) are for thickness or construction stated, not per inch thickness. ' 1A u t b o b it t J . Material - Description CorrooenvOT Density (Lbpeb Cc Ft) Mean Temp (Fahe Deg) OB Conductance (t) . (O Resistance Per Inch Thickness For Thickness Listed a> (*) INSULATING MATERIALS H in. insulating boards without special finish/ (eleven samples)------........-- 1 in. insulating board*--------- 16.1 16.5 to 2L8. 13.2 81 90 0.34 0.33 to 0.40 0.34 , ' 1.90 75 0.23 Made from cribs fibers------ - -------------- 1.60 75 0.24 Fibrous material made from dolomite 1.50 75 0.27 Fibrous material made from Blag.------ -- 9.40 103 0.27 3.00 90 0.31 Redwood bark.... ....... .............------------- 5.00 75 0.26 Glass wool fibers 0.0003 in. to 0.006 in. 1.50 75 0.27 - Granular insulation made from combined 4.20 72 0.24 Expanded vermiculite...... ................. -- .. ___ 0.48 Expanded vermiculite, particle sue-- -3 + 14 _______ 6.2 Regranulated cork about */& in. particles 8.10 90 0.31 Hand applied fT*nnlar mineral wool 2 in. 6.05 0.30 to. 6 in. thick; horizontal position*. to to 7.13 0.33 A in maehina hlnwn irrannlar mineral wool, horizontal position*. No covering 5.74 030 Rock wool ..... ... ........................... --- 10.0 90 0.27 Corkboard, no added binder..................... Corkboard, no added binder --................ Corkboard, no added binder. Corkboard, asphaltic binder.................... Chemically treated hog hair with turn oi Sugar cane fiber Insulation blocks en=_ cased in asphalt membrane.......... ..-- Made from 85 per cent magnesia and 15 ner cent asbestos ------------- ---- Made from shredded wood and cement... Made from shredded wood and cement*.. 14.0 10.6 7.0 5.4 8.7 14.5 10.0 13.8 . 19.3 24.2 29.8 90 034 90. r 030 90 037 _90 035 0.29 90 032 75 0.28 70 030 86 031 72 0.46 0.77 2.94 ' (3) _. 3.03. ___ (1) to ...... 230 - 2.94 - -- (4) 435 __ 4.17 (3) ...... 13) .... 3.70 .... 3.70 332 3.84 !3! ___ ___ (3) 3.70 __ (3) 4.17 __ 2.08 ___ (3) ___ Cl) 332 __ 333 to 333 (3) (1) (4) ___ 333 ""' ---- -- S(1I)! 2.94 ' ---- ` tt> _3.70 ---- (l) (1) ...4.00 (1) 3.45 f! 3.12 -- (1) 3.5/ 3.33 1.96 1.30 (3) * (3) _ < --_ >5! (4) See notes on Page 117. Surface Conductance . The surface conductance of a wall is the combined heat, transfer to or . from the wall by radiation, convection and conduction. Each of the three portions making up the total may vary independently of the others, thus affecting the total conductance. The heat transfer by radiation ' ' ' between two surfaces is controlled by the character of the surfaces . (emissivity), the temperature difference between them, and the solid . angle through which they see each other. The heat transfer by convection . and conduction is controlled by the roughness of the surface, by . air movement and temperature difference between the air and the surface. ` The importance of .the effect of temperature of surrounding surfaces .' on the surface conductance due to the effect on radiation is illustrated in Heat Transmission Coefficients of Building Materials 121 Table 3, which applies to a vertical surface at 80 F, with ambient air at 70 F and effective emissivity equal to 0.83 *. In many cases, because the heat resistance of the internal parts of the wall is high compared with the surface resistance, the surface factors are of minor importance. In other cases, e.g. single glass windows, the surface resistances constitute almost the entire resistance and are there fore very important. In a building heated by convection there is only a slight difference between the temperatures of the interior wall surface and the surroundings, but if the building is heated by radiant panels there may be a considerable difference 4. (See also Chapter 31.) The convection part of the surface conductance coefficient-is affected markedly by air movement. This is illustrated by Fig. 3, which shows the surface conductances for different materials at a mean temperature of 20 F and for wind velocities up to 40 mph. These include the radiation portion of the coefficient, which for ordinary building materials under these conditions would be constant at about 0.7 Btu. Table 3. Variation in Surface Conductance Coefficient with Different Temperatures of Surrounding Surface , Surrounding Surface Temperature Convection--Btu per (hr) (sq ft)___ Radiation--Btu per (hr) (sq ft)........ Total--Btu per (hr) (sq ft)................. Surface Coefficient--surface and air temperature only--Btu per (hr) (sq ft) (F deg difference of surface and air)................................... 75 F 6.6 ~ 4.4 11.0 70 F 6.6 8.6 ' 15.2 1.10 1.52 69 F 6.6 9.6 16.2 1.62 60 F 6.6 17.0 23.6 2.36 50 F 6.6 24.9 31.5 . 3.15 Due to these variations for different conditions the selection of surface conductance coefficients for a practical building becomes a matter of . judgment. In calculating the over-all heat transmission coefficients for the walls, etc. of Tables 5 to 18, 1.65 hag been selected as an average inside surface conductance and 6.0 as an average outside surface-conductance for a 15-mile wind. These values apply only to ordinary building ma terials and should not be used for bright metal surfaces having a low emissivity. ' . In special cases, where surface conductance coefficients become important factors in the over-all rates of heat transfer, more selective coefficients may be required. The surface conductance values given in Table 1, Section A are based on recent tests and are for still air conditions and surface emissivities of 0.83 and 0.05 respectively, and may be used where it is desirable to differentiate between horizontal and vertical surfaces or where coefficients applicable to low-emissivity surfaces are required. . Air Space Conductance . .' The transfer of heat across an air space involves the boundary surfaces aswell as the intervening air, consequently the factors influencing surface conductance play an important part in determining the conductance of the air space. The coefficients given for air space conductance represent the total conductance from surface to surface. - The radiation portion of the coefficient is affected by the difference . in temperature between the boundary surfaces and by their respective . '. 122 CHAPTER 6 ' : >' -1946-Guide emissivities aiid is practically independent of depth. The convection and . conduction transfer is controlled by depth arid shape of the air space, . the roughness of the boundary surfaces, the mean temperature and the direction of heat flow. For air spaces usually employed in building construction, the radiation and convection factors vary independently of each other. ` . 1 . Table 1, Section B gives experimentally-determined conductances of vertical air spaces bounded by such materials as paper, wood, plaster, etc., having emissivity coefficients of 0.8 or higher, and haying extended parallel surfaces perpendicular to the direction of heat flow.- The con ductances decrease as the depth is increased, but change only slightly c. Fig. 3. Curves Showing. Relation Between Surface Conductances for : ' Different Surfaces at 20 F Mean Temperature. for spaces greater than % in. Air space tests reported by Wilkes and Peterson gave conductance values for air spaces of 3^4 in.'- depth having boundary surfaces with emissivity values of 0.83 as follows 5.. . . Vertical................................... ...............l,,1.17 ' ", Horizontal (heat flow upward)....... ..... 1.32 ^ . ; .' * Horizontal (heat flow downward)____ 0.94 , . -Since, in buildings, the same constructions may be'used for conditions . where the direction of heat flow may be in one direction or its opposite', and since.much of the construction involves vertical air spaces, an average ' value of 1.10 Btu per (hour) (square foot) (Fahrenheit degree temperature - . difference) was-chosen. for use in calculating .the over-all coefficients in Tables 5 to 18 wherever air spaces % in. or more in depth were iriVolved. -. r. '-H. eat Transmission Coefficients oif Bu ildin. .g_ M. at erials 123 If one or both boundary surfaces of. an air space are faced with metals which have low emissivity surfaces, the radiant heat transfer will be . greatly reduced in comparison with that occurring from surfaces of ordinary building materials. Table 1, Section C gives conductances and resistances of air spaces bounded by one reflective surface with an emissivity of 0.05. These values include heat transferred both by radi ation and convection, but the' radiation component is relatively small for the test conditions. , When reflective materials are installed with single or multiple air spaces, the position (vertical, horizontal or inclined) of the material and . the direction of heat flow must be taken into consideration. For example, the resistance to upward heat flow is about one-third the resistance to downward heat flow in a horizontal position-.(Table 1, Section G). The- difference between the conductance through vertical air spaces and that, through horizontal and sloping air spaces with upward heat flow is considerably less. For upward heat flow it is recommended that a value - of 0.46 be used for the conductance of horizontal or sloping air spaces bounded on one side by reflective materials having an emissivity of approximately 0.05. The same conductance value is also recommended. for similar vertical air spaces. , ., When considering heat transfer to and from reflective surfaces in building construction, the emissivity should be known. This can be determined directly for the long wave length radiation corresponding to average room and'wall temperatures. The possibility of change in emissivity with time of exposure due to surface coatings, chemical action, deposition of dust, etc. must be considered in selecting a material. for use s. . - PRACTICAL COEFFICIENTS AND THEIR USE For practical purposes it is necessary to have average coefficients that may be applied to various materials and types of construction with out the necessity of making actual tests. In Table 2 coefficients are given for a group of materials which have been selected from tests by various authorities. Since there is some variation in the resulting values due to variations in materials and in test conditions; average values for the usual conditions encountered in building practice have been selected and ' listed in Table 4. These coefficients were used in the calculation of over all coefficients given in.Tables 5 to 18. These tables constitute typical examples of combinations frequently used, but any special Constructions not given can be computed by the use of the conductivity values in Table 4 and the fundamental heat transfer formulae. - Caution ' The user should realize that the average.conductivity and conductance values given in Tables 2 or 4 do not necessarily apply to all products of the same gerieral description. In using these values judgment should be. exercised with regard to the extent to which the product (either as received or as applied) will comply with the tabulated values. Exact conductivities or conductances for specific materials should be obtained from the manufacturer. . ' ' _ Insulating Materials ', ., In order to determine the benefit derived from the addition of. insulat- ing materials to a given construction, the over-all coefficient of'heat . " 124 CHAPTER 6 1946 Guide Table 4. Conductivities (k) and Conductances (O Used in Calculating 1 Heat Transmission Coefficients (U) in Tables 5 to 18 , These constants are expressed in Btu per (hour) (square foot) (Fahrenheit degree temperature difference). ' Conducticities (k) are per inch thickness and conductances (C) are for thickness or construction stated. . not per. inch thickness. . MATERIAL DESCRIPTION CONDUCTIVtTT Conductance ( (O Resistance Per Inch '(t) For Thickness listed (c) AIR SPACES v Vertical4, ^ in. or more in-width...--------- --. 1.10 0.46 0.91 2.17 EXTERIOR FINISHES (Frame Walls) 1230 2.27 138 138 0.08 0.44 0.78 0.78 INSULATING MATERIALS Made Rom mineral or vegetable fiber or animal hair, enclosed or open_____________ Insulating Board.,--:........... .................... Mineral Wool.--------- --------- ~...-- Fiber made born rock, slag or glass_______ __ 0.27 030 033 037 0.48 -- 3.70 333 3.03 330 2.08 ____ - '-- ' INTERIOR FINISHES Composition Wallboaed___ , Gtpsum Board (M in.)-- -------------_ Gtpsuh Lath (H in.) and Plaster..:. Insulating Board (Vi in.)-- Insulating Board Lath (Vi in.) and Insulating Board Lath (1 in.) and P1aster thickness assumed H -- Plaster thickness assumed Vi iiu.____ __ _-- 030 330 Wood Lath and Plabteb---------- '------- 3.70 ~ 2.4 0.66 0.60- .0.31 4.40 2.12 t 230 2.00 030 -- . 037 0.42 132 1.67 * . 3.18 0.23 0.47 0.40 MASONRY MATERIAIH Por/TV * \Mr\ rS ' - Adobe, assumed 4 in. thick.__ _____________ 12.Q0 \- rk Hollow,1 cinder aggregate^-------------------- 230 12.00 8 in. Concrete blocks.......... Hollow, gravel aggregate_____________ ________ -- Hollow, gravel aggregate------------ .;------- ----------- " 12 in. Concrete blocks.......................... Hollow, cinder aggregate--------------------------------8 in. Concrete blocks___ ________ ,,. ---. . Gtpsum fiber concrete-- --------....... ,87H per cent gypsum and 12)4 per cent 1.66 1230 1230 12.50, .0.89 1.25 ' 230 138 1.00 0.64 0.60 ^ . 038 0.40 031 1.28 1.00 LOO 0.80 0.60 033 030 0.47 ____ . _0.08 , , ___ . 0.40 0.08 -- ....... -- , ,. 0.61 0.46 .. 0.60 _______ ____ . 0.08 0.08 0.08 1.12 . 0.43 --. 0.78 . 1.00 - 137 . 1.67 1.72 230 3.23 ____ ____ 0.78 1.00 1.00 1.25 1.66 138 2.00 2.13 1.64 2.18 . , ,, ______ Conductance values for horizontal air spaces depend on whether the heat flow is upward or downward, but in most cases it is sufficiently accurate to use the same values for horizontal as for vertical air spaces. `Expanded slag, burned clay or pumice. ' Heat Transmission Coefficients of Building Materials 125 Table 4. Conductivities (&) and Conductances (C) Used in Calculating Heat Transmission Coefficients (U) in Tables 5 to 18--Concluded These constants are expressed in Btu Per (hour) (square foot) (Fahrenheit degree temperature difference). Conductivities (&) are Per inch thickness and conductances (O ore for thickness or construction stated, not per inch thickness.' " MATERIAL ' DESCRIPTION - CONDUCTIVITT OR Conductance (W (C) Resistance Per loch For Thickness Thickness lasted (t) ar ROOFING MATERIALS Built-up Roofing__ SHEATHING Fir or Yellow Pine (1 in.)________ SURFACES . ' . Ordinary nou-reflective materials, vertical.... Ordinary nou-reflective materials, vertical.. WOODS ,. Fib sheathing (1 in.) building papeb - '. Maple or Oak ... Yellow Pine or Fir ____ ,, io'.bo E: ...... *1.15 030 - 6.00 630 3.53 6.50 20.00 138 232 0.42 2.56 1.02 036 1.65 6.00 ' 030 030 E -- 037 1.25 0.17 0.1S 038 0.15 0.05 0.78 035 237 039 0.98 1.16 0.61 0.17 2.00 transmission JJ\ of the insulated construction may be compared with the corresponding coefficient U without insulation. Attention is called to the necessity of applying the insulating material in accordance with the manufacturer's specification. The engineer must carefully evaluate . the economic considerations involved in the selection of an insulating material as adapted to various building constructions. Lack of proper evaluation, or improper installation may lead to unsatisfactory results. Computed Heat Transmission Coefficients - Computed over-all heat transmission coefficients of many common types of building construction are-given in Tables 5 to 18, inclusive, each coefficient being identified by a serial number except in Table 18. For example, the coefficient V of a brick-veneer, frame wall with wood sheathing and Y2 in. of. plaster on gypsum lath is 0.27, (Wall No. 28-C in Table 5) and with 2 in. of blanket or bat insulation .the coefficient would be 0.097 (No. 49-B in Table 6). . Example /. Calculate/the coefficient of heat transmission U of a brick-veneer, frame wall with wood sheathing, building paper, arid 34 in. plaster on % in. gypsum lath,_ based .on a wind exposure of 15 mph. Also calculate the coefficient when 2 in. of bat insulation is added, leaving an" air space in the wall, and correcting for framing amounting to 15 per cent of the. wall area. Solution: Starting from the exterior, the resistances making." up the total heat resistance are (1) exterior surface," (2) brick-veneer, (3) wood sheathing in. thick and building paper,- (4) air space 3% in.- wide, (5) % in. gypsum lath and plaster, (6) interior surface. Then using the values from Table 4 in Equation 4: . x I t. 1 -- 1 1 1 6.0 T 2.27 'r 0.86 T 1.10 T2.4 _r 1.65 - . 126 CHAPTER 6 1946 Guide T 0.17 + 0.44.+ 1.16 + 0.91 + 0.42 + 0.61 1 3.71 0.27 ' When 2 in. of bat insulation is added in the air space in the wall, an air space will still be left since it was originally 3% in. wide. Then, . _ V= 3.71 + 0.27 1 11.11 = 0.090 This coefficient (0.090) applies only to the wall where no studding or framing is present and is assumed to constitute 85 per cent of the whole wall. Then for 1 sq ft of wall the heat transfer through the insulated portion is 0.85 X 0.090 or 0.0765 Btu. In the portion of wall where framing is present, the air space'will be replaced with an equivalent thickness of wood framing. Then, -' If (through framing) U = 0.136 J_. , _J_ , _J_ , 3.625 6.0 2.27 ^ 0.86 ^ 0.80 1.1 2.4 T 1.65 . Then for 1 sq' ft of wall the heat transfer through the framing is 15 per cent of 0.136 or 0.0204 Btu. The total heat transfer through 1 sq ft of wall (with 3% in. framing. _ covering -15 per cent of area) equals , ' V (corrected) = 0.0765 + 0.0204 = 0.097 Btu . This is the value shown for No. 49-B in Table 6, which is1 included to eliminate the need for the calculation of framing corrections when insulation is used in frame con struction. - In making the calculations for values of U shown in Tables 5 to 18, the following conditions have been assumed: ' ' Equilibrium or steady-state heat transfer, eliminating, effects of heat capacity. . Surrounding surfaces at ambient air temperatures. - Exterior wind velocity-of 15 mph. .' - Surface emissivity of ordinary building materials = 0.83. ' :- No, correction for position or direction of heat flow. (Average coefficients used). . Air spaces are % in. or more in width. .- .. Variation of conductivity with mean temperature-neglected. ' Corrections for framing made on basis of parallel heat flow through 2` X 4 in. (nominal) studs, 16 in. on centers, the framing covering 15 per cent of wall area. ' .. . . - Actual thicknesses of lumber assumed to be as follows: , , . ` '. Nominal Actual 1 in. (S-2-S).................................'................ ..... "^32 in. 1}4 in. (S-2-S)............................................ ...........1^6 in. ` 2 in. (S-2-S)............................................ ......... 1%. in. 2Yi in. (S-2-S)............. ................ .........................2% in. 3 in. (S-2-S)................................................ -1.:.2% in. 4 in. . (S-2-S).:........... .................................... :..3% in. Finish flooring, (maple or oak) ------ 1JK f> 'n- . . , . . Coefficients for frame construction are corrected for the effect of framing where such correction would increase the coefficients, blit not where the correction, would decrease the coefficients7. - It should be noted that the effects of poor workmanship in construction and installation have an increasingly greater percentage effect on heat transmission as the coefficient becomes numerically smaller. ' Failure to meet design estimates may be caused by lack of proper attention to Heat Transmission Coefficients of. Building-Materials: ' ,' . . 127 W all N umber Table 5. Coefficients of Transmission (U) of^Frame Walls Coefficients ore expressed in Btu per (hour)' (squarefoot) {Fahrenheit degree difference in temperature between the air on the two sides), and are based on an outside wind velocity of 16 mph. No Insulation Between Studs* (See Table 6) TYPE OF SHEATHING exterior FINISH ` INTERIOR FINISH Gtpsum (H THICK) I*LT' WOOD (its m. thick) Wood/ (H6m. thick) Bldg. Papeb Insul ating Board (H6w. thick) ,A' B C D Wood Siding (Clapboard) veop Metal Lath and Haste**-- ...... ......... ........ 0.33 0^2 036- 0.20 1 Gypsum Board (H in.) Dwviraterf 032 032 0.26 030 2 Efi Gypsum Lath (H in.) Plastered*. 031 0.31 0.30 0.25 0.19 A Plywood (M in.) Plain or Decorated-- .. . 030 030 0.24 0.19 S Insulating Board (H in.) Plain or Decorated-:. ' 0.23 033 0.19 0.16 6 US'/j'*- Insulating Board Lath (M in.) Plastered*..__-- 0.22 032 . 0.19 Insulating Board Lath (1 in.) Plastered*.... ...... 0.17 . 0.17 0.15 0.15 0.12 7 8 jnttx Wood- Shingles STTWA WOOP '`"'See ' .THEfCI MHff) Metal Lath and Piaster* ' .... ................. Gypsum Board (H in.) Decorated Wood Lath and Plaster- Gypsum Lath (K in.) Plastered* Plywood (H in.) Plain or Decorated - - Insulating Board (H in.) Plain or Decorated.... Insulating Board Ith (H in.) Plastered*_____ Insulating Board Lath (1 in.) Pfastoed*........... 035 035 034 034 0.24 0.19 0.19 .0.14 0.25 035 034 034 034 0.19 0.18 0.14 036 0.17 9 036 0.17 10 035 0.16 11 035 0.16 12 0.24 0.16' 13 0.19 0.14 14 0.19 0.13 15 0.15 . 0.11 . 18 Stucco JTVPSk jtvcco. U, \ Metal pnd PUqfpr* Gypsum Board in.) Decorated..................... Wood TaUi and Planter Gypsum Lath (H in.) Plastered*....................... Plywood (H in.) Plain or Deoorated - ' ,,. Insulating Board ()-$ in.) Plain or Decorated.-. Insulating Board lath (H in.) Plastered*-___ Insulating Board Lath (1 in.) Plastered*........... /HEAT SING*) ' 0.43 0.42 0.40 0.39 0.39 037 036 - 0.19 0.42 0.41 039 039 038 037 036 0.19 . 032 031 0.30 030 0.29 0.22 0.22 0.16 033 17 033 18 032 19 032 . 20 032 . 21 0.18 - 22 0.17 23 0.14 24 Bates Veneer* /TDFA MUCKi /; /HtM _. - Metal I-Ath and Pl*t*....-. - 037 Gypsum Board in.) Decorated-.--. .... .... 036 Wood Lath and Plaster _______ _ _______ 0.35 Gypsum Lath (% in.) Plastered*. 034 Plywood in.) Plain or Decorated...--L-____ 034 Insulating Board (M in.) Plain or Decorated.... 035 Insulating Board Lath (M in.) Plastered*-'. `... 0.24' Insulating Board Lath (1 in.) Plastered*____ . 0.18 ,. 036 , 038 036 038, 034 037 034 037 033 037 0.25 031 0.24 f 030 0.18. 0:15 031 25 031 26 0.20 ' 27 0.20 28 030. -29 0.17 30 0.16 ' 31 .0.13 32 "Coefficients not weighted; effect of 6tudding'neglected. ^Piaster assumed % in. thick.' ` ` ' ~ V* ' Plaster assumed K in. thick. ' '* ^_ ^Furring strips (1 in. nominal thickness) between wood shingles and all sheathings except wood. ' Small air space and mortar between building paper and brick veneer neglected. . .. /Nominal thickness, 1 in. _ .' . . - .. 128. CHAPTER 6 1946 Guide Table 6. Coefficients of Transmission (U) of Frame Walls with , Insulation Between Framing^ b Coefficients ore expressed in Btu per (.hour) (square foot) (Fahrenheit .degree difference in temperature between the air on the two sides), and are based on an outside wind velocity of 15 mpk. COEFFICIENT WITH NO INSULATION BETWEEN FRAMING COEFFICIENT WITH INSULATION BETWEEN FRAMING Mineral Wool ob Vegetable Fibers in Blanket or Bat Fork0 (Thickness below) 1 IN. 2 IN. 3 in. - 3% IN. Mineral Wool A B C' D O.II 0.12 0.13 0.14 0.15 0.078 0.083 0.088 ' 0.092 0.097 0.063 0.067 0.070 0.072 0.075 0.054 0.056 0.058 0.061 0.062 0.051 0.053 0.055 0.057 0.059 33 34 35 36 37 0.16 ' 0.17 0.18 0.19 0.20 0.10 . 0.10 0.11 0.11 0.12 0.078 0.080 0.082 0.084 0.086 0.064 0.066 0.067 0.069 0.070 0.060 38 0.062 39 0.063 40 0.065 " 41 0.066 ; 42 ' 0.21 0.22 0.23 0.24 0.25 0.12 0.088 0.12 . 0.089 0.12 0.091 0.12 0.093 0.13 0.094 0.072 0.073 0.074 0.075 0.076 - 0.067 - 0.068 0.069 0.070 . -0.073 43 44 45 46 .47 0.20 0.13 0.096 0.27 0.14 0.097 0.28 . 0.14 0.098 0.29 0.14 0.10 0.30 0.14 0.10 0.077 0.078 0.079 0.080 0.080 ' - 0.072 0.073 0.073 0.075 0.075 48 49 50 51 52 0.31 0.14 0.10 0.081 ^ 0.076 . .53 0.32 0.15 0.10 - , 0.082 - ' 0.077 54 0.33 0.15 0.10 0.083 ' 0.077 55 ' 0.34 0.15 - 0.10 0.083 0.078 56 0.35 0.15 . 0.11 .. 0.084 0.078 57 0M 0.15 0.37 0.16. 0.38 0.16 0.39 0.16 0.40 0.16 0.11 0.085 0.079 58 0.11 0.085 0.080 59 0.11 \ 0.086 0.080 60 0.11 0.086 0.081 61 0.11 0.087- - 0.082 62 . 0.41 0.42 0.43 0.44 0.16 0.16 . 0.17 0.17 0.11 . 0.11 0.11 0.11 0.087 0.088 0.088 0.089 _ - 0.082 0.082 0.082 0.083 ' 63 64 65 66 . This table may be used for determining the coefficients of transmission of frame constructions with the types and thicknesses of insulation indicated in Columns A to D inclusive between framing. Columns A, B and C may be used for walls, ceilings or roofs with only one air space between framing but are not. applicable to ceilings with no flooring above.- (See Table 11.) Column D is applicable to walls only. Example: Find the coefficient of transmission of a frame wall consisting of wood siding, in. insulating board sheathing, studs, gypsum lath and plaster, with 2 in. blanket insulation between studs.' -According to Table 5. a^wall of this construction with no insulation between studs has a coefficient of 0.19 (Wall No. 4D). Referring to Column B above, it will be found that a wall of this value with 2 in. blanket insulation between the studs has a coefficient of 0.034; ... . ` `Coefficients corrected for 2x4 framing, 16 in. on centers--15 per cent of surface area. . `Based on one air space between framing. . .' . '. *No air space. ' ." . rr**it Transmission Coefficients of Building Materials 129 . Table 7. Coefficients of Transmission (U) of Masonry Walls Coefficients are expressed in Btu per (hour) (square foot) (Fahrenheit degree difference in temperature between the air on the two sides), and are based on an outside wind velocity of 16 mph. Based on 4 in. hard brick and remainder common brick. . `The 8 in. and 10 in. tile figures are based on two cells in the direction of heat flow. The 12 in. tile is based on three cells in the direction of heat flow. -The 16 in. tile consists of one 10 in. and one 6 in. tile each having two cells in the direction of heat flow. . -. Limestone or sandstone. .. ` *These figures may be used with sufficient accuracy for concrete walls with stucco exterior finish. Expanded slag, burned clay or pumice. ' - - /Thickness of plaster assumed % in. . Thickness of plaster assumed in. ' ' '' `Based on 2 in. furring strips; one air space. ' . ' 130 vCHAPTER 6 1946 Guide Table 8. Coefficients of Transmission.(CO of Brice and Stone Veneer Masonry Walls Coefficients are expressed in Btu per, {hour) {square foot)^(Fakrenheit detree difference in temperature . between the air on the two sides), and are based on an,outside wind velocity of 16 mpk. "Calculations based on M In. cement mortar between, backing and facing except in the case of-the * concrete backing which is assumed to be poured in place. > ` . - .' The hollow tfie figures are based on two air cells in the direction of-heat flow. ' . eHoUow concrete blocks.'- -. ' - ^Expanded slag, burned clay or pumice. , '. .' ' '. Thickness of plaster assumed H in. . . .- .. /Thickness of-plaster assumed in. ' . #Based on 2 in. furring strips; one air space. ' .. ; , ,,. `. . Hont. Transmission Coefficients of.Building Materials 131 Table 9. Coefficients of Transmission (U) of Frame Partitions or Interior Walls3 . - Coefficients are expressed in Btu per {hour) (square foot) (Fahrenheit degree difference in temperature between the air on the two sides), and are based on stUl air (no wind) conditions on both sides. INTERIOR FINISH Metal Loth and Plaster*-------- ... Gypsum Board (M in*) Decorated. Wood Lath and Plaster-----------Gypsum Lath (H in ) Plastered*-- Plywood (M in.) Plain or Decorated.................. Insulating Board (H in.) Ram or Decorated..Insulating Board Lath (M in.) Plastered*----Insulating Board Lath (1 in.) Plastered*........ SINGLE PARTITION (Finish on one side only of studs) DOUBLE PARTITION (finish on both sides of studs) NO INSOLATION BJSTWKJ5N STUDS 1 in. Blanket*1 BETWEEN STUDS. One aoi space. -zo zo ABC 0.69' 0.67 . 0.62 0.61 039 036 035 0.23 0.39 0.37 034 0.34 033 0.19 0.18 0.12 0.16 0.16 " 0.15 0.15 0.15 0.11 0.11 0.082 12 3 "Coefficients not weighted; effect of studding neglected. .. Plaster assumed % in. thick. Plaster assumed H in. thick. . ; . ` ' . apor partitions with other insulations between studs refer to Table 6. using values in Column B of above table in St hand column of Table 6. Example: What is the coefficient of transmission (U) of a partition consisting of gypsum lath and-plaster on both sides of studs with 2 in. blanket between stud.9? Solution: According to above table, this partition with no insulation between studs (No. 4B) has a coefficient of 0.34.. ' -Referring to Table 6, it will be found that a wall having a coefficient of 0.34 with no insulation between studs, yill have a coefficient of 0.10 with 2 in. of blanket insulation between studs (No. 56B). Table 10. Coefficients of Transmission (U) of Masonry Partitions ' Coefficients are expressed in Btu per (hour) (square foot) (Fahrenheit degree difference in temperature between the air on the two sides), and arc based on still air (no totnd) conditions on both sides. . 0U TYPE OF PARTITION 1 zs - fl s E5- * TYPE OF FINISH No ; Finish (Plain walls) Plasteb One Side .A ' . .B ,. ' Plaster Both ' Sides* . C. tae a p .z zo E iCl. ' 3 030 4 0.45 0.47 .0.42 0.43 - . 9 0.40 . 10 3 . 035 4 039 0.33 . - 038 032 11 037 12 Hollow Concrete Tils'ob Blocks ' 3. Light Weight Aggregate6___ 3 4, 030 0.45 0.41 035 . ` 0.47. 0.42 039 034 0.43 0.40 i 037 .032 13 14 15 16 4 "2 in. solid plaster partition. If = 0.53. Expanded'slag. burned clay or pumice. 030 . ' 0.46 0.43 17 T a b l e 11. C o e f f ic ie n t s o f r a n s m is s io nT '( /) o f F r a m e C o n s t r u c t io n C e il in g s a n d F l o o r s Coefficients ore expressed in B lu per (hour) (square foot) (Fahrenheit degree difference in temperature between the a ir on the two sides) and are based on stiU a ir (no w ind) conditions on both sides. ' . ooo feScs ooo -- iS- 132 CHAPTER 6 1946 Guide ' 2' e E 5"3 O i 5z5eo 5o3o 111. S c 22 ..CO JS hi i.'Jo2 ao jkS ,, J3-S Oo 3 "3 % 5q cc gj **o "S _V V ge S=53 s. 41 5 u o a m rS 3 t) H !SS ; ^3 !!'i j s 2 I "' s 8-4 S-J M m 55 cc *5 3 8 8 5 8^ c3 gJ *eoJ*3j Jj* *3 8 "8 *2 *53 s6 "e sg 2 30c)*3CV 3*1*e *S s a a c S-* ~--c5Eo lBcS Jc _C.8 sn 1 n*nt Transmission Coefficients of Building Materials 133 Table 12. Coefficients of Transmission (CO of Concrete Construction , . Floors* and Ceilings Coefficients are expressed in Btu per, (hour) (square foot) (Fahrenheit degree difference in temperature between the air on the two sides), and are based on sttU air (no wind) conditions on both sides. , type of ceiling . TYPE OF FLOORING Thickness 07 Concrete# (Inches) No Flooring (Concrete Bare) Tile or Terrauo Flooring on Concrete M In. Battleship* Linoleum Directly on Concrete Parquet* Flooring In Mastic on Concrete Double Wood Floor' on Sleepers* UK 2 AB CDE 3 0.68. 0.65 0.45 0.45 035 1 6 0.59 036 0.41 0.41 033 2 10 030 . 0.4S 036 036 032 3 OOO yfc in. Plaster Applied to Underside of 3 6 10 ,, 0.43. 039 034 0.43 039 034 034 032 0.21 4 5 6 Metal Lath and Plaster*--Suspended or 3 6 10 035 035 032 030 030 0.19 7 0.28 038 0.18 8 036 036 0.17 9 Gypsum Board (% in.) and Plaster/-- Suspended or Furred,,..^.,, ____ __ 3 6 10 036` 033 030 035 032 039 038 037` 034 0.28 037 0.24 0.19 0.18 0.17' 10 11 12 ooo 1 Insulating Board Lath (M in.) and Plaster/ Suspended or Furred............... ................. 3 .6 10 0.24 031 031 0.15 13 0.23 030 0.20 0.15 14 031 0.19 0.19 0.14 15 ` ^Thickness of tile assumed to be 1 in. ,- ^Conductance of linoleum in. thick is 1.36. Values in Column C may be used with sufficient accuracy for concrete floors covered with carpet. . Thickness of wood assumed to be ,J,4 in.; thickness of mastic. H in- (& 93 4.5). *Based on H4 in. yellow pine or fir sub-flooring and % in. hardwood finish flooring with an air space between sub-floor and concrete. Thickness of plaster assumed to be % in. /Thickness of plaster assumed to be H in. For other thicknesses of concrete, interpolate. Table 13. Coefficients of Transmission (CO of Concrete Floors on Ground with Various Types of Finish Flooring U = 0.10a Btu per (hour) (square foot) (Fahrenheit degree temperature difference between the ground and the air over the floor). ^ * Until more complete data are available, it is recommended that a coefficient of 0.10 be used for all ' types of concrete floors on the ground, with or without insulation. For basement wall below grade, use the same average coefficient (0.10). A lower ground temperature should, however, be used for walls than' floors as explained in Chapter 14. For further data see A.S.H.V.E. Research Report No. 1213--Heat Loss Through Basement Walls and Floors, by F. C. Houghten, S. I, Taimuty, Carl Gutberlet and C. J. Brown (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 369). ` . exact compliance with specifications, and a factor of safety may be employed as a precaution when it is judged desirable. Roof Coefficients . . ,/ Computations for wood'shingle roofs applied over wood stripping are based on 1 by 4 in. wood strips, spaced 2 in. apart. Values for roofs containing Spanish and French clay roofing tile are assumed the same'as for slate roofs. Values for'pitched roofs in Table 16 apply where the' roof is oyer a heated'attic or top floor so that the heat passes directly through the roof structure,.including any interior finish material. 134 ' , , CHAPTER 6 . , 1946 Guide. (If)Table 14. Coefficients of Transmission of Flat Roofs Covered with Built- - - Nup Roofing. o Ceiling--Under Side of Roof Exposed ' - - (See Table 15 for Flat Roofs with Ceilings) . ' These coefficients ore expressed in Btu per (hour) (square foot) (Fahrenheit degree difference in temperature between the air on the two sides), and are based on an outside wind velocity of 16 mph. TYPE OF ROOF DECK Thickness OP Roof Deck (Inches) No Insula tion INSULATION ON TOP OF. DECK (Covered with Built-Up Roofing) - , Insulating Board - (Thickness Below) COHKBOARD (Thickness Below) . X Id. , 1 In. IX In. 2 In.. 1 In. 1H In. 2 In. cuEs0 oa z A B C D E F G .H Flat Metal Roof Deck* ' iNraunw/ . yccK~ 1.06 . 039 . 034 . 0.18 0.14 0.23 0.17 0.13 1 Precast Cement Tfle /CAST EocriKC; /tut SpshlEp *jvpeoe.r/Jr` IMin. 0.84 037 034 0.17 0.14 032 0.16 0.13 2 . Concrete ' ROOHNGj COIfCkRTE.'' "jf 2 in. ' 4 in. 6 in. 0.82 036 034 0.17 0.14 032 046 0.13 3 0.72 034 033 0.17 0.13 031 0.16 0.12 4 0.65 033 032 0.16 0.13 031 0.15 0.12 5 Gypsum Fiber Con- crete* on.K in. Gypsum Board - iruoLATion/ itdfptnci / etr/vny. &0AAP' '2K in- 3K in. \ 0.38 031 -' 034 0.18 031 0.16. 0.14 0.13 ,0.12 ` 0.11 0.17 . 0.13 0.11 0.15 0.12 . 0.10 6 7 Wood* , ' 1 in. * 0.49. 038 - 030 0.15 0.12 0.19, 0.14 T 0.12 8 IK in. , 037 034 0.17 0.14 0.11- 0.17 . 0.13'.: 0.11 9- umi.iufiiuiiii.Vi 2inl 032 1 032 0.16 0.13 0.11 0.16 0.12 0.10 10 1S222222222223 3 in. . utops . 033 . 0.17 0.14 0.11 0.096- 0.13 0.11 0.091 11 "Coefficient of transmission of bare corrugated'iron (no roofing) is 1.50 Btu per (hour)(square foot of ' projected area)(Fahrenheit degree dinerence in temperature) based on an outside wind velocity of 15 mph. per cent gypsum', 12H per cent wood fiber. Thickness indicated includes H'in. gypsum board. Nominal thicknesses specified---actual thicknesses used in calculations. . ` Heat Transmission Coefficients of Building Materials ; 135 Table 15. Coefficients of Transmission (V) ofJ<lat Roofs Covered with Built-up Roofing. With Lath'and Plaster Ceilings3 . ... . (See Table 14 for Flat Roofs with No Ceilings) ` These coefficients are expressed in Btu per (hour) (square foot) (Fahrenheit degree difference in temperature between the air on the two sides), and are based on an outside wind velocity of 15 mph. TYPE OF ROOF DECK Root; Deck (Inches) No ' Insula tion INSULATION ON TOP OF DECK (COTEBXD WITH BUILT-Up ROOFING) ' Insulating Board (Thickness Below) CORKBOARD (Thickness Belcrw) Kin- IK In- IK In. Flat Metal Roof Deck ' IMIOUTMII/ ppOFIKtfi Precast Cement Tile IK in. `T/UrfOKT^jr* ` f\AH^ ' nois RflOFINC 2 2 in. 4 in. 0.42 '0.26 0.19 0.14 0.12 0.18 0.14 0.11 0.40y1 <0.25 0.18 0.14 0.12 0.17 0.13 0.11 037 034. 0.18 0.14 0.11 0.17 0.13 0.11 Gypsum Fiber Con crete* on K in. Gypsum Board' itdariltMiG/xU. LAftfin/ f\uJsrtrfTrrjJ;ys.m i 2K in. ,3M in- 037 033 0.19 0.15 0.12 0.17 .0.14 . 0.11 0.10 0.097 0.14 0.13 00..1112 0.097 0.091 Wood* UKimoAtFTinifffiTs/ti W090-' IK in 2 in. 3 in. 0.31 '0.21 0.16 0.13 0.11 0.15 0.12 0.10 036 0.19 0.15 0.12 0.10 0.14 0.11 0.095 0.120341 0.17 0.14 0.11 0.097 0.13 0.11. 0.092 0.18 0.14 0.10 0.087 0.11 04)95 0.082 Calculations based on nietal lath and-plaster ceilings, but coefficients may be used with sufficient accuracy for gypsum lath or wood lath and plaster ceilings. It is assumed that there is an air space between the under side of the roof deck and the upper side of the ceiling. , *' *87>$ per cent gypsum. 12K per cent wood fiber. Thickness indicated includes K in. gypsum board Nominal thicknesses'specified--^actual thicknesses used in calculations. > ' .t ' [feat Transmission Coefficients of Building:Materials 137 Table 17. Combined Coefficients of Transmission (U) of Pitched Roofs and Horizontal Ceilings-^Based on Ceiling Area*1 - Coefficients are expressed.in Btu per (hour) (square fool of ceiling area) (Fahrenheit degree difference in' ' temperature between the air on the two sides), and are based on an outside wind velocity of 16 mph. ' CEILING COEFFICIENT/ (From 0.10 0.11 0.12 0.13 0.14 TYPE OP ROOFING AND ROOF SHEATHING \ Wood Sbingi^s on Wood Strips1* Insulation (Rafters ` Exposed) (17, - 0.48) 14 In. Insulating Board on Under Side of Rafters ' (Ut - 0.22) 1 In. Insu* lating Board on Under Side of Rafters (U, = 0.16) Asphalt SbINOLES* OB Roll ROOTINO No Roof Insulation (Rafters Exposed) ' (U, 023) \4 In. Insulating Board on Under Side of Rafters (U, - 0.23) 1 In. Insu- lating Board on Under Side of Rafters (Hr =0.17) as} I 2 A B. C D 'E F 0.085 0.092 0.099 0.11 0.11 0.073 0.078 0.082 0.087 0.091 0.066 0.07 0.074 0.078 0.081 0.087 0.094. 0.10 0.11 0.11 0.074 0.079 0.083 0.088 0.093 0.067 0.071 0.075 0.079 0.083 19 20 21 .22 23 0.15 0.12 0.096 - 0.084 0.12 0.097 0.086 ' 24 0.16 0.13 0.10 0.087 0.13 0.10 0.089 25 0.17 0.13 0.10 ' . 0.090 0.13 0.10 0.092 28 0.18 0.14 0.11 . 0.093 0.14 0.11 0.095 27 - 0.19 0.14 0.11 0.095 0.15 0.11 0.098 28 0.20 0.15 0.11 0.098 0.15' 0.12 0.10 29 021 0.15 0.12 0.10 0.16 0.12 0.10 . 30 . 022 0.16 0.12 . o.io- . 0.17 0.12 .0.11 31 0.23 0.16 0.12 0.10 0.17 0.12 0.11 32 024 0.17 0.13 0.11 * 0.18 0.12 ` 0.11 33 025 0.17 0.13 0.11 0.18 0.13 0.11 34 026 0.18 0.13 0.11 0.19 0.13 0.1! 35 0.27 0.18 0.13 0.11 . 0.19 0.13 0.12 38 0.28 0.19 0.14 0.12 * 0.19 0.14 0.12 - 37 029 . 0.19 0.14 0.12 020 0.14 0.12 38 020 024 . 025 . 026 027 0.45 0.59 0.61 ' 0.62 0.67 0.69 , 020 021 0.22 022 023 025 0.29 . 029 020 021 021 0.14 0.15 0.15 0.15 0.15 0.17 0.18 0.18 0.19 0.19 0.19 0.12 0.12 0.13 0.13 0.13 -' 0.20 0.22 0.22 023 023 ` 0.14 0.15 0.15 0.15 0.16 * 0.12 0.13 0.13 - 0.13 0.13 39 40 41 42 43 0.13 0.26 0.17 0.14 ^ . 44 0.14 . 020 *. 0.19 0.15 45 0.15 4.31 0.19 ' 0.15 48 0.15 0.31 : 0.19 . . 0.15 . 47 0.15 0.33 1 . 0.20 0.16 48 0.15 023 , - 020 0.16 49 Calculations based on H pitch roof (n = 1.2) using the following formula: Ut X Uco U y Ut H------- 'n U = combined coefficient to be used with ceiling area. ' Ut = coefficient of transmission of the roof. Uc -- coefficient of transmission of the ceiling. ' *=. the ratio of the area of the roof to the area of the ceiling. Use ceiling area (not roof area) with these coefficients.. . Coefficients in Columns D, E and F may be used with sufficient accuracy for tile, slate and rigid asbestos shingles on wood sheathing. . ' ^Based on-1 z 4 in. strips spaced 2 in. apart. ; - Sheathing assumed H6 in. thick. - ' ' ^Values of to be used in this column may be selected from Table 11. 138 CHAPTER 6 1946 Guide Table 18. Coefficients of Transmission (U) of Doors, Windows, Skylights . . .. .. and Glass Block Walls .' Coefficients are expressed in Btu per (hour) (square foot) (Fahrenheit degree difference in thetemperaturebetween the air inside and outside of the door, window, skylight or wall) and are based on an outside wind velocity of - 16 mph. -s' - Section A. . Windows and ' Skylights Section B. Solid Wood . Doorsbc u Nominal Thickness Inches 1 IK m 2 3 Single v Double 1.13" 0.45" Actual Thickness Inches ' . / u Exposed Door h* -m m m m 2 yt . 0.69 0.59 0.52 0.51 0.46 0.38 0.33 . Triple 0.281" u* With Glass Storm Door 0.42 0.38 0.35 0.35 0.32 0.28 . 0.25 . Description u Still Air Both Sides u Still Air Inside 15 mph Outside Section C. Smooth surface glass blocks 7% x 7% x 'Sj/% in. thick.... _r. 0.40 0.49 Ribbed surface glass blocks 7% x7&x 3% in. thick.-- 0.38 . 0.46 . See Heating. Ventilating and Air Conditioning, by Harding and Willard, revised edition. 1932. ` ^Computed using C = 1.15 for wood;/> =? 1.65 and fo * 6.0. ' . 'It is sufficiently accurate to use the same coefficient of transmission for doors containing thin wood panels as that of single panes of glass, namely. 1.13 Btu per (hour) (square foot) (degree difference between inside and outside air temperatures). : . _ _ ' '/These values may also be used with sufficient accuracy for wood storm doors. Neglect storm doors if loose and use values for exposed doors. -' . .. . 'Air spaces assumed to be H in. or more In width. - Combined Ceiling and Roof Coefficients If the attic space between ceiling and roof is unheated, the combined coefficient from room air below the ceiling to exterior air can be calculated from the following formula. " .: ' - ` - .. __ Ur X Uce Ur+ff*. . n , ` ' . where .: U = combined coefficient to be used with ceiling area. Ut = coefficient of transmission of roof. . . f/ce = coefficient of transmission of ceiling. . n = ratio of roof area to ceiling.area. . ' '. : '. . '1 . . It should be,noted that the over-all coefficient Z7 should be multiplied. by the ceiling area to determine ' heat loss and. not by the roof area. Values of UT and '/ should'be calculated using a , value of 2.2 (the reciprocal ef- one-half the air space resistance) rather than 1.65 for the conductances of surfaces facing the attic, since the attic js equivalent to an air space. ...... . . .... . . . If the attic contains windows, dormers and vertical wall spaces and if their area is small compared to that of the. roof, they may be considered. Rent`Transmission Coefficients of Building Materials - , ` 139 part of the roof area... For accuracy, the sum of the coefficients of each individual section multiplied by its percentage of,the total area'should be used as UT. Where large vertical wall areas in. the. attic are involved, it is preferable to estimate the attic temperature as illustrated in Chapter 14 and calculate the heat loss through the ceiling by 'multiplying the value of Uce for the ceiling by the difference in temperature above and below the ceiling. ' ' * . 1 *, '. ' Jr1'' Basement Floor, Basement Wall and Concrete Slab Floor Coefficients:: The heat transfer through basement walls and floors to the ground is; dependent on the temperature difference between the air within and that of the ground, on the material constituting the wall or floor, and on the conductivity of the surrounding earth. The conductivity of the . earth will vary with local conditions and is usually unknown. Tests 8 at the A.S.H.V.E. Research Laboratory indicate a heat flow of approximately 2.0 Btu per (hour) (square foot) through an uninsulated concrete base ment floor with a. temperature difference of 20 F between ground tem perature and the air temperature 6 in. above the floor. Based on this result,'a coefficient of 0.10 Btu per (hour) (square foot) (Fahrenheit degree'temperature difference),is recommended for calculation where it' is desirable to allow for the small basement floor heat loss, e.g. for Heated" basements. " , For basement walls the same coefficient may be used, but due to closer proximity to the surface of the ground, the temperature difference for winter design conditions will be greater than for' the floor. The test results indicate a unit area heat loss, at, mid-height of the basement wall, approximately twice that of the same floor area. , ' For concrete slab floors laid in contact with the ground at grade level, recent tests "indicate that for small .floor areas (equal to that of a house 25 ft square) the heat loss may be calculated as proportional to the length of exposed edge rather than total area. This amounts to 0.81 Btu-per (hour) (lineal foot of exposed edge) (Fahrenheit degree difference between the inside air temperature and the average outside air tempera ture). It should be noted that this may be appreciably reduced by insu- lating the edges of the floor from the abutting wall. CONDENSATION IN BUILDINGS Water vapor in the. air within a building condenses if it comes in contact with surfaces at or below its dew-point temperature. It also will be transmitted into or through a wall, floor or ceiling; if a vapor pressure, difference exists between the opposite sides, at a rate determined by the permeability of the materials encountered.10 (see Table 14 Chapter 15). Building practice must take account of these facts in avoiding (1) surface , condensation on interior building surfaces (walls, ceilings, roofs or glass) and (2) interstitial condensation or accumulation of condensation in-the voids within the structure. The conditions under which surface con densation will take place are directly dependent on surface temperature and upon the relative humidity of the air in contact. Limiting maximum relative humidities for walls, roofs or glass having transmission coefficients' up to 1.2 Btu for outside temperatures from --30 F .to 40 F and for 70 F inside temperature may be obtained from Fig. 4 ". . Surface condensation may be controlled by. air conditioning, ventila tion for the purpose of removing water vapor, particularly from laundries 140 CHAPTER 6 1946 Guide and from kitchens during lengthy periods of cooking, elimination of .sources of vapor such as urivented gas stoves, or by local application of heat or insulation to raise surface temperatures. -. . . Interstitial condensation results from vapor transmission which is dependent on vapor pressure differential and the ratio of the rate at which vapor may enter the materials of the structure to that at which it passes out of the structure. The proper installation of a vapor barrier on the warm side of the structure, where the higher vapor pressure ' usually exists, will reduce greatly the amount of vapor entering the building construction and will minimize the possibility of objectionable condensation. Such a barrier may consist of a coated paper applied Fig. 4. Permissible Relative Humidities for Various Transmission Coefficients under the plaster, a coated plaster base, or a.vaporTresistant finish applied to the interior wall surface 12. A vapor barrier is tentatively defined as a material having a water vapor permeability .no exceeding 1.25 grains per (hour) (square foot) (inch, of Hg vapor pressure differential). To prevent condensation on the under side of roofs above attic spaces over insulated ceilings, ventilation with outside air may be provided through suitable louvers or other roof ventilators. : . REFERENCES . '--Standard Method of Test for Thermal.Conductivity by Means of the Guarded Hot Plate, sponsored by A.S.H.V.E., A.S.T.M., A.S.R.E.,-and N.R.C. and approved as a Tentative Code by A.S.H:V.E. and AS.TM. in 1942 (AS.T.M. designation C-177-42T).. . . . . . 2--Keat Transmission Through Building Materials, by F..B. Rowley and A; B. Algren (University of Minnesota, Engineering Experiment Station Bulletin No. 8, p. 11). . . Radiation and Convection from Surfaces in Various Positions, by G. B. Wilkes and C. M. F. Peterson ' (A;S.H.V.E. Transactions, Vol. 44, 1938, p. 513). `' Heat' Transmission Coefficients of Building Materials 141 4--`Radiation Corrections for Basic Constanta Used in the Design of A!1 Types of Heating Systems, by B. F. Raber and F. W. Hutchinson (A.S.H.V.E. Journal Section, Healing.-Pipingond Air Conditioning. December 1944, p. 705). - . . *, s--Radiation and Convectidn Across Air Spaces in Frame Construction, by G. B. Wilkes and C. M. F. Peterson (A.S.H.V.E. Transactions, Vol. 43, 1937, p. 351). ,` : a--Thermal Test Coefficients of Aluminum Insulation for Buildings, by G. B. Wilkes, F. G. Hechler and E.R. Queer (A.S.H.V.E. Transactions, Vol. 46, 1940, p. 109). . . 7-- Effect of Studs and Joists on Heat Flow Through Frame Walls and Ceilings, by Paul D. Close (Head ing, Piping and Air Conditioning, October, 1943, p. 529). '' 8-- A.S.H.V.E. Research Report No. 1213--Heat Loss Through Basement Walls and Floort,-by F. C. Houghten, S. I. Taimuty. Carl Gutberlet and C. j. Brown (A.S.H.V.E. Transactions, Vol. 48. 1942. p. 369). 9--Measurements of Heat Losses from Slab Floors, by R. S. Dill, Wm, C. Robinson and H. E. Robinson (National Bureau of Standards, Building Materials and Structures Report BMS 103). - '. i a-Methods of Moisture Control and Their Application to Building Construction, by F. B. Rowley, ` A. B. Algren and C. E. Lund (University of Minnesota Engineering Experiment .Station Bulletin No.-17>. , Moisture Migration: A Survey of Theory and Existing Knowledge, by P. F. McDermott {Refrigerat ing Engineering, August 1941,.p. 103). . * . .1 it--Permissible'Relative Humidities in Humidified Buildings, by Paul D. Close (A.S.H.V.E. Journal Section. Heating, Piping and Air Conditioning, December. 1939, p. 766). - . ' is--Condensation Within Walls, by F. B. Rowley, A. B. Algren and C. E. Lund (A.S.H.V.E. Trans actions, Vol. 44, 1938, p. 95). ` BIBLIOGRAPHY fA;S.H.V.E. Research Reports: No. 852--Effects of Air Velocities'on Surface Coefficients, by F, B. Rowley, A. B. Algren and J. L. Blackshaw (A.S.H.V.E. Transactions, Vol. 36, 1930, p. 123). . .; ^ No. 895--Wind Velocity Gradients Near a Surface and Their Effect on Filn? Con-. * ductance, by F. C. Houghten and Paul McDermott (A.S.H.V.E. Trans , actions, Vol. 37, 1931, p. 301). No. 914--Surface Coefficients as Affected by Direction of Wind, by F. B. Rowley . and W. A. Eckley (A.S.H.V.E. Transactions, Vol. 38, 1932, p. 33). No. 915--Conductivity of Concrete, by F. C. Houghten and Carl Gutberlet (A.S.H.V.E. Transactions, Vol. 38, 1932, p. 47). No. 964--The Heat Conductivity of Wood at Climatic Temperature Differences, by F. B. Rowley (A.S.H.V.E. Transactions, Vol. 39, 1933; p. 329). No. 996--Insulating Value of Bright Metallic Surfaces, by F. B. Rowley (A.S.H.V.E; Transactions, Vol. 40, 1934, p. 413). No. 1026--Thermal Properties of Concrete Construction, by F. B. Rowley, A. B. Algren and Clifford Carlson (A.S.H.V.E. Transactions, Vol. 42, 1936, p. 33). No. 1048--Thermal Properties of Concrete Construction, by F. B. Rowley, A. B. Algren and Robert Lander (A.S.H.V.E. Transactions, Vol. 43, 1937, ; P- 33). . ' Insulating Effect of Successive Air Spaces Bounded by Bright Metallic Surfaces, by L. W. Schad (A.S.H.V.E. Transactions, Vol. 37, 1931, p. 285). -- . Condensation of Moisture and Its Relation to Building Construction and Operation, by F. B. Rowley, A. B. Algren and C. E. Lund (A.S.H.V.E. Transactions, Vol. 45, 1939, p. 231). -. A Theory Covering the Transfer of Vapor Through Materials, by F. B. Rowley (A.S.H.V.E. Transactions, Vol. 45, 1939, p. 545). Thermal Conductivity of Wood, by J. D. MacLean (A.S.H.V.E. Transactions, ;Voi. 47, 1941, p.323). '. ' . The Specific Heat of Thermal Insulating Materials, by G. B. Wilkes and C. O. Wood (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 493). * '. : i I 142 - CHAPTER 6 - 1946 Guide Heat-Loss Studies in Four Identical Buildings to Determine the Effect of Insulation, ` by D. B. Anderson (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 471). ` Simultaneous-Heat and Vapor Transfer Characteristics of an Insulating Material, by F. G. Hechler, E. R. McLaughlin and E. R. Queer (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 505). , . ... . : . . Comparative Resistance to Vapor Transmission of Various Building Materials, by L. V. Teesdale (A.S.H.V.E. Transactions, VoL 49, 1943, p. 124). The Diffusion of: Water Vapor Through Various Building Materials, by J. D. . Babbitt {Canadian Journal of Research, Vol. 17, February, 1939,p. T5).. . . ' Effect of Ceiling Insulation upon Summer Comfort, by T. D. Phillips (National Bureau of Standards, Report.BMS52, July; 1; 1940). - : - Moisture Condensation in Building Walls, by H; W. Wooley {National Bureau of Standards, Report BMS63, December 14, 1940). -. ' Heat Transmission Through Building Materials, by F. B. Rowley and A. B. Algren, (University of Minnesota Engineering Experiment Station Bulletin No. 8). Building Insulation, by P. D. Close (American Technical Society,-Chicago, 1945). \ CHAPTER 7 Construction and Arrangement, Steam Coils, Water Coils, . Direct-Expansion Coils, Flow Arrangement, Applications, ' Heat Transfer and Air Flow .Resistance, Performance of Heating, Dry Cooling and Dehumidifying Coils, Coil Selection THE coils' described in this chapter are for heating or cooling ah air stream under forced convection. Surface coil equipment may be made up of a number of banks assembled in the field, or the entire as-, sembly may be factory constructed. The applications of each type of coil are limited to the field within which it is rated. Other limitations are imposed by code regulations, by proper choice of materials for the fluids used and the condition of the air handled, or by an economic analysis of the possible alternates on each installation. For heating service, coils are used as preheaters, reheaters or booster . heaters. ' The function of the coils is air heating only, but the apparatus . assembly may include means for humidification and air cleaning. Steam or hot water are the usual heating media, although others are used in . special cases, such as reheating by means of discharge gas from a refriger- .. ating system. _ . Coils are used for air cooling with or without accompanying dehumidi fication. Examples of cooling applications without dehumidification are precooling coils using well water or other relatively high temperature water to reduce the load on the refrigerating machinery, or water cooled . coils to remove sensible heat in connection with chemical moisture- absorption apparatus. By proper coil selection it is1 possible to handle both sensible cooling and'dehumidification together as explained later. ' The assembly usually includes an air cleaning means to protect the coil . from accumulation of dirt and to keep dust and foreign matter out of the conditioned space. Although cooling and dehumidification are the usual functions; there are cases of cooling coils purposely wetted to aid in air - cleaning and odor absorption. ' The usual cooling media used in surface coils are cold water or Group I (ASA Classification) refrigerants, but others are used in special cases. Brines are seldom required for the range of applications covered by this chapter, although there, are cases where low entering air temperatures . with large latent heat loads require'a refrigerant temperature so low that . water becomes impractical. Sometimes, also, brine from an industrial system already installed is the only convenient source of refrigeration. , For combined cooling and dehumidifying, surface coils present an alter nate, to spray dehumidifiers. , For many applications it is possible, by proper selection of apparatus, choice' of air velocities, refrigerant tem peratures, etc., to perform the same duty with either. In a few-cases both sprays and coils are used. The coils may then be installed within the spray chamber, either in series with the sprays or below them. In making the selection between spray and-surface dehumidifiers, certain . advantages of each should be considered. The fact that a spray dehumi difier is usually designed to deliver nearly saturated air tends to simplify, the control problem. In this case the dry-bulb temperature is-also the , dew-point, and hence a dew-point, control can be arranged by using a 143 . 144 CHAPTER 7 1946 'Guide simple duct thermostat. Spray dehumidifiers have an advantage over unwetted coils of a certain degree of air cleaning and odor absorption. On the other hand, coils make possible a closed and balanced cooling water circuit, obviating the unbalanced pumping head, the complication of water level control, and danger from possible floods incidental to multiple spray dehumidifiers, especially if located on different levels. The use of coils often makes it possible for the same surface to serve for summer cooling and winter heating by circulating cold water in the one season and hot water in the other, with consequent saving in apparatus and ~ piping. Another advantage is that where the surface coil system can be used with direct expansion of refrigerant, it is comparatively low in initial and operating costs. The safety of the occupant must be kept in mind in comfort conditioning applications. Some localities have refrigeration codes which restrict the use of direct-expansion coils in the air stream, and hence local codes should be consulted by the engineer before a system employing direct expansion methods is designed. The choice between spray dehumidifiers and coils depends upon the necessities and the economic aspects of each case and no general rule can be given. There are many installations in which either may be used. COIL CONSTRUCTION AND ARRANGEMENT Coils are basically of-two types, those consisting of plain tubes or pipe and those having extended surfaces. The former are little used for the applications covered by this chapter, but are often employed where condi tions cause frost accumulation, and for cooling within spray dehumidifiers. The heat , transmission from air passing over a tube to a fluid flowing . within it is impeded by three resistances. The first resistance is from the , air to the surface of the tube, usually called the outside surface resistance or air-film resistance. Second is the resistance to the flow of heat by ' conduction through the metal itself. Finally there is another surface or film resistance to the flow of heat between the inside surface of the metal and the fluid in the tube. For the applications under consideration both . ' the resistance of the metal wall to heat conduction, and the inside surface ' or film resistance are usually low as compared with the air-side surface resistance. Economy in space, weight and cost makes it advantageous to decrease the external surface resistance, where it is proportionately large, to approach that of the tube wall, and that from tube to refrigerant. This may be accomplished by increasing the external surface by means of fins. Sometimes water spray is applied to the same type surface as would have been used without it. The over-all heat transfer is not necessarily increased much by such an arrangement, but the water spray may serve other purposes than to increase the flow of heat, such as air and coil cleaning. . .. - In fin or extended surface coils the external surface of the tubes is known as primary and the fin surface is called secondary. The primary surface consists generally of round tubes or pipes. In some cases these are staggered and in others in line with respect to the air flow. The' staggered arrangement gives a somewhat higher heat transfer value but also a higher resistance to air flow and in some cases makes the header and return bend arrangement more complicated, i Numerous types of fin arrangement are used, the most common of which.are spiral, flat and flat-crinkled or corrugated, all as shown in Fig. 1. While the spiral fin surrounds each tube individually in all cases, the flat types may be con- Heat Transfer Surface Coils 145 tinuous'(including several rows of tubes), or they may be round or square, with individual fins for each tube. All. of these, as well as other less common types, are in use, the selection for a particular installation being based on economic considerations, space requirements and resistances of individual designs of coils. A most important factor in the performance of extended surface coils is the bond between the fin and the tube. An intimate contact is assured in a number of ways. The assembled coil may be coated with tin, zinc, etc., after fabrication. The spiral type fin may be knurled into a shallow, groove on the exterior of the tube. The tube ' may be expanded after the fins are assembled, or the tube hole flanges of a flat or corrugated fin may be made to override those in the preceding fin and so compress them upon the tube. There are also types, of con struction where the fin is formed out of the material of the tube itself. . For heatinglcoils the materials most generally used are copper, steel and aluminum. Sometimes aluminum or brass fins are used on copper tubes. Some types of heating coils are made of east-iron. For equal performance brass and aluminum fins must be of greater thickness than copper fins on account of their lower thermal conductivities. Copper coils are Spiral fins OO oo Flat continuous fins O' O s Z OO z 4- Flat corrugated fins 13 o Q 3 oO Fig. 1. Types of Fin Coil Arrangement frequently tin-dipped and steel coils galvanized to protect them from corrosion and to assure a bond between fin and tube. : Cooling coils for water or for volatile refrigerants most frequently have copper fins and tubes, although aluminum fins on copper tubes are also used. For brines such as sodium or calcium chloride,and for ammonia, steel fins and tubes are common. , -. Although there are many variations for special cases, tube and fin sizes and spacings for air conditioning coils, both heating and cooling, fall within fairly narrow limits. The tubes are usually J/, j/g, or in. OD, and the fins spaced from 4 to 8 per inch, 7. per inch being a common design. The tube spacing generally varies from about l]/g to 2 in. on centers. Small tube size and close fin spacing give large capacity with small space demand, but the resistance, both over the surface and through the tubes, is higher than with larger tubes and more-widely spaced fins. Moreover, too close a fin spacing may. result in trouble from dirt accumu lation, especially on dehumidifying coils, and may also cause trouble from water held between the fins, particularly with air flow vertically, . upward. This condition increases the air resistance and decreases the capacity of the coil. Water hold-up sometimes causes flooding trouble in . vertical air flow units by accumulating too much, water for the drain to handle all at once when the fan is stopped. .. . 146 CHAPTER 7 1946 Guide Steam Coils . For proper performance of steam heating coils, condensate'and air must be continuously, eliminated and the steam must be evenly distributed to the individual tubes. This distribution is usually accomplished by ' individual orifices in the tubes, by distributing plates and orifices in the steam header, or by perforated internal steam-distributing pipes extend^ ing into the individual tubes. The latter arrangement has the advantage of distributing the steam throughout the length of each tube, and is con ducive to uniform temperature of delivered air. The tendency of conden sate to freeze at the bottom of the coil with cold entering air and light Heat-Transfer Surface Coils . .- __________ . 147 provision for cleaning of individual tubes is of advantage. It is important to arrange water coils for complete drainage if located where they will be exposed to freezing. Fig. 2 shows such construction. The drains may be provided in the water piping -although they are often arranged in the coil headers. - - ' . Direct-Expansion Coils . '. Coils for volatile refrigerants present more complex problems of fluid distribution than do water, brine or steam. It is desirable that the coil be effectively and uniformly cooled throughout, and necessary that the compressor be protected from entrained, unevaporated refrigerant. There are two types; namely, flooded systems, and thermal expansion valve systems, as shown in Figs. 3 and 4. In a flooded coil, the circulation is similar to that in a water tube boiler. The liquid is maintained at the proper level by the action of a float regulator as. shown in Fig. 3. The thermal expansion valve system depends upon the thermal valve auto- heating loads is also minimized- This is'especially valuable for outside , air preheaters. Methods of air and condensate elimination are discussed ' in Chapters 23 and 26. .' Water Coils . . ' ' . - The performance of water coils, for heating or cooling, depends on. the elimination of air from the. system and proper distribution of water. Air elimination is taken care of in the system piping as' described in Chapter .24. To assure a pressure drop sufficient for adequate distribution but at ' the same time to provide against excessive pumping head where'large' water quantities are handled, water coils.are provided with various water circuit arrangements. For. instance; a typical coil 18 tubes high and 6 tubes deep in the direction of air flow can be arranged for'6, 9, 18 or 36 parallel water circuits as conditions may require. Orifices in individual, . tubes are occasionally employed^ but- are usually unnecessary as the .. resistance qf individual water circuits, is generally sufficient to effect a; ..satisfactory distribution. .. In precooling, coils using well water, where there may be considerable sand and other foreign matter in the water,' Fig. 3. Direct-Expansion Coil with. Flooded System. Fig. 4. Direct-Expansion Coil with. Thermal Valve System matically feeding just as much liquid to the coils as is required to main tain the superheat at the coil suction outlet within predetermined limits which vary from about 6 to 10 deg. The thermal valve arrangement is in common use for the type of coils covered by this chapter, while the flooded system is comparatively rare. . With the flooded system the refrigerant distribution through the tubes depends on. properly selecting: the length of the feeds and the head of liquid imposed upon the liquid inlets. No auxiliary distributing devices are required. With the thermal valve system there are two factors to consider. There must be, generally, more than one refrigerant feed through the coil per thermal valve to keep the pressure drop through the refrigerant circuit within practical limits' and to reduce the corresponding penalty in increased evaporating temperature. At the same time the coil'must be so arranged that the required suction superheat -can be attained with a minimum sacrifice in the performance of the coil as a whole. It is general practice to attain this superheat within the coil itself and not . by the use of external heat exchangers or other auxiliary devices. ., '. With thermal expansion valves it is advantageous to keep the pressure drop through the refrigerant feeds as low as possible. The feeds are'laid out to expose each to the same mean temperature difference so that it 148 CHAPTER 7 1946 Guide y . jr^nt Transfer Surface Coils 149 connections are led as shown. In type C the refrigerant enters at high velocity from the thermal.valve and is discharged against the. end plug in which the individual liquid feeds are closely arranged. These distribu tors can be used in either vertical or horizontal position. Although there ' are other forms of distributors those mentioned are typical examples. The individual liquid connections from the distributor to the coil inlet are ' commonly made of small diameter tubing and are all of the same length t and diameter in order to impose the same friction between the distributor and the coil. Since the thermal valves act in response to the superheat at the coil outlet, this superheat should be produced with the least pos sible sacrifice of active evaporating surface. Sometimes a single thermal valve is used per coil. In other cases multiple valves are used, with the' coil divided across the air flow or parallel to the air flow as shown in Fig. 6. Fig. 5. Types of Refrigerant Feed Distributing Heads handles the same refrigerating load. A distributing means is imposed between valve and coil liquid inlets to divide' the refrigerant equally among the feeds. Such a distributor must be effective for distributing both liquid and vapor, because the entering refrigerant is a mixture of the two. Fig. 5 shows three typical types of distributors. In distributor A the liquid and gas mixture from the thermal valve is led tangentially into a chamber. The coil feed connections extend outward radially at the top of.this chamber. Iri distributor B the refrigerant is discharged at a high velocity through a central jet against the end . plate, forming a uniform mixture of gas and liquid within the distributor, from which individual i ' Fig. 8. Flow of MUdia in Tubes in Relation to Air Flow The arrangement of Fig. 7 should be avoided since it offers the disad vantage of unequal load on the two parallel circuits. . Flow Arrangement The relative direction of flow of the air outside the- tubes and the' medium within them influence the performance of the surface. "There ' . are three types of relative flow in common use.'. Fig. 8A shows parallelflow in which the air and the medium in the tube's`proceed through the' coil in the same direction. Fig. 8B shows counter-flow in which the medium in the tubes proceeds in a direction opposite to the flow of aif.;' ' Fig. 8C shows cross-flow in which the air and the medium in the tubes pass at right angles to each other. The counter-flow arrangement is almost universally used in brine or water coils to take advantage of the highest possible mean temperature difference for.given entering water ' and air temperatures. It is also commonly used in coils fed with volatile' refrigerant to take advantage of the. higher air temperature for super- , heating the leaving gas. In deep.coils, however, it is sometimes advan tageous to use parallel flow from second-row to last row and then tocomplete the circuit by passing through the first row to take advantage of the higher air temperature for superheating. : Complete evaporation . and superheating of the refrigerant are essential to proper operation of the thermal expansion valve. Cross-flow is common in steam heating y ISO ________ . CHAPTER 7 1946 Guide coils, the temperature within the tubes being substantially uniform,and the mean temperature difference the same whatever the direction'of flow, relative to the air. Cross-flow is to be avoided in coils-with volatile refrigerants-on account of unequal loading of parallel-circuits and the danger of short, circuiting of liquid refrigerant which disturbs proper functioning'of the thermal expansion valve. Applications .- Heating coils in field assembled banks are. used for a . number of pur . poses as described in Chapter 43. They may be arranged with the air , flow vertical or horizontal, although the latter is more common. For steam heating, the coils may be set with the tubes vertical or horizontal. In .the latter case the coil should.be sloped to provide for condensate drainage. Because of the multi-circuit feed arrangement and the neces- Heat Transfer Surface Coils 151 exposed to freezing temperatures: in winter if the-apparatus, is used on winter humidifying duty. Access doors should be provided for servicing filters, humidifying nozzles; and fan bearings andfor.cleaning the coils. With certain designs of coils when used for dehumidifying,-eliminators must be used beyond the coil to catch any water which may be blown into the air stream. It is customary to include these eliminators when the air velocity exceeds about 450 fpm with the individual fins and about 600 fpm for the continuous flat fin type. Where a number of coil sections are stacked one upon another, and where the velocities are low, so that eliminators need not be used,-occasional trouble results when water splashes down from one coil to the next and blows out into the air stream. In such cases drip troughs as shown in Fig. 19 are used to collect this ' water and conduct it to the condensate pan. ' Sometimes finned surface coils on summer cooling and dehumidifying ' Fig. 9. Typical Arrangement of Cooling: Coils ina Central'System ' sity for avoiding air and water pockets, water heating coils are generally arranged with the tubes horizontal. Certain precautions must' be taken against freezing. Where steam coils are used with entering air below freezing temperature, throttling the steam supply may result in freezing the condensate in the bottom of the coil if the tubes are of the variety not provided with internal distributing pipes, or an equivalent arrangement. If these are used, there is little danger of freezing the condensate as long as the leaving, air. temperature is not allowed to fall below about 40 F.. As an added precaution with both steam and water coils the outside air inlet dampers are often closed automatically when the. fan is stopped to avoid trouble caused by very cold outside air drifting in during off periods. , A typical arrangement of cooling coils is shown in Fig. 9: Some means . should be:provided, to filter all. the entering air to keep dirt, and foreign. ' matter from accumulating on the coils. The assembly is provided with a; ' . drip-pan to catch the condensate during summer, dehumidifying duty and '. to collect the non-eyaporated water from the humidifying sprays in : winter.. The drip connection should:be made ample in size and liberally, provided with plugged tees and crosses for cleaning. It.should:not.be- ' Fig. 10. Coil Arranged with Drip Trough . .. ! , Fig. 11. Recirculating Spray System . for Cleaning Coils . duty are provided with water sprays. These' sprays, are of two types.In the first type a set of spray nozzles is arranged for intermittent cleaning. These sprays are not operative when the system is in use and no recircu lating pump, is provided.- The second arrangement requires a collecting tank and a recirculating, pump. The water is in circulation whenever the apparatus is in operation, and assists in keeping the coil clean and in absorbing odors. -Fig. 11, illustrates such an arrangement.-. Wherever air by-passes are used around a coil on summer duty for. control purposes, it is advantageous to direct only return air through the by-pass.rather than a mixture of return and outside air. The casing should be arranged accordingly. To maintain the air quantity handled by the fan reasonably constant, and to assure the required design quantity of by-passed air. when the by-pass damper is open, cooling coil banks are frequently. . furnished with both face-and- by-pass dampers as shown in Fig. 9. Although both heating and cooling coils are made of sufficient strength to take up expansion and- contraction arising within themselves, care should be taken to avoid imposing strains from the piping on to the coil; connections. (See Chapter 23.) ................. 152 ,___________________________ CHAPTER 7 ' 1946 Guide HEAT TRANSFER AND AIR FLOW RESISTANCE : The transfer of heat between the heating or cooling medium and the air stream is influenced by several variables: . 1. The temperature difference. 2. The design and surface arrangement of the coil. 3. The velocity and character of the air stream. 4. The velocity and character of the medium in the tubes. ' The driving force is usually taken as the logarithmic mean temperature, difference for heating or cooling without dehumidification. For combined cooling and dehumidification, the logarithmic difference does not apply strictly and such problems should be handled as described later. With volatile refrigerants there is often an appreciable pressure drop and corresponding change in evaporating temperature through the refrigerant circuit. The problem is further complicated by the fact that the refriger ant is evaporating in part of the circuit and superheating in the remain der. In spite of this, heat transfer and ratings for coils using volatile refrigerants are usually based on a refrigerant temperature corresponding to the average pressure in the coil. The design and surface arrangement of the coil includes such items as' materials, type, thickness, height and spacing of the fins, and the ratio of this surface to that of the tube, the use of the staggered or in-line tube arrangement, and provisions to increase the air turbulence such as the use of corrugated as against flat fins. Staggered tubes increase the total' heat transfer as against the in-line arrangement and corrugated fins may be more effective than flat. It is this design and surface arrangement that determines the air film heat transfer resistance. , The velocity of the air usually considered is the coil face velocity. , This bears a varied relation to the actual velocity over the surface, depending upon the individual coil design. As long as a fixed design of coil is under consideration face velocities may be used, but they may be unsatisfactory in comparing different designs, as, it is the actual surface velocity that is significant: :The air volume is often based on standard air at 70 F.and. a barometric pressure of 29.92 in. Hg. The use of air volume in coil rating information may be misleading. The significant value is mass velocity in pounds per (minute) {square foot offace area) and not cubic feet per minute, because for a fixed volume the corresponding weight may vary widely, depending upon the temperature and barometric pressure. At the same mass air velocity, varying performance can be obtained depending upon the turbulence of the air flow into the coil and upon the uniformity of distribution of air over the coil face. The latter is very im portant in obtaining reliable test ratings and in realizing rated perform ance in practical installations. The resistance through the coils will assist in distributing the air properly,'but where the inlet duct connections are' brought in at sharp angles to the coil face, the effect is frequently bad and there may even be reverse air currents through the coils. This reduces the capacity, but can be avoided by proper layout or by the use of, directing baffles. , Heat transfer depends also, upon the velocity of the medium in the tubes and upon its character, whether flowing water, condensing steam or' evaporating volatile refrigerant. Heat transfer rates expressed as Btuper' (square, foot of internal surface) (degree logarithmic mean, effective temperature difference between the fluid and tube wall) are, for example:. Heat Transfer Surface Coils 153 ' about 150 to 300 for evaporating dichlorodifluoromethane, about 350 to 1200 for water at 2 and 6 fps and about 1200 for condensing steam. The influence of the medium in the tubes on the over-all heat transfer rate is, therefore, apparent. ' Because of these variables, reliable rating and performance information for any design of coil must be based on actual tests on that coil under the expected conditions of operation. A comparison between the perfor mance of two designs, unless based on such tests on each, may lead to entirely erroneous conclusions. PERFORMANCE OF HEATING AND DRY COOLING COILS Heating and dry cooling, coils are heat exchangers and as such their performance depends in general upon: . 1. The over-all coefficient of heat transfer from the fluid within the coil to the air it heats or cools. . 2. The mean temperature difference between the fluid within the coil and the air flowing over the coil. - 3. The physical dimensions of the coil. . Thus, for any one definite operating condition, the heating or cooling capacity of a given coil is expressed by the following basic formula: ,. 9t =V X {MTD) X A X N (1) where ~' .. qt = total heat transferred by the coil, Btu per (hour) (square foot of coil face area). - U = over-all coefficient of heat transfer, Btu per (hour) (square foot of external coil surface) (Fahrenheit degree temperature difference between the fluid within the coil and the air flowing over the coil). UTD -- mean temperature difference, Fahrenheit degrees between the fluid within the coil and the air passing over it. (This is commonly taken as the loga rithmic mean temperature difference.) A = external surface area of the given coil, square feet per square foot of coil ' face area, per row of coil depth. N -- number of rows of coil depth. Over-all Coefficient of Heat Transfer . - Of all factors affecting the performance of heating or dry cooling coils,' the over-all coefficient of heat transfer is the most difficult to determine as it is influenced by. several factors which depend upon coil design, and conditions of operation. . .' Considering any coil, whether of bare pipe or of finned type, the over-all heat transfer coefficient- for a given size and design of coil can always be considered as a combined effect of three individual heat transfer coef- ' ficients, namely: 1. The film coefficient of heat transfer- between air and the external surface of the coil, usually given in Btu per (horn) (square foot external surface) (Fahrenheit degree, mean temperature difference). . . ., 2. The coefficient of heat transfer through the coil material--tube wall, fins, ribs, etc. 3. The film coefficient of heat transfer between the internal surface of the coil and' the fluid flowing within the coil, usually given in Btu per (hour) (square foot internal surface) (Fahrenheit degree-mean temperature difference). , . These three individual coefficients acting in scries result in an over-all coefficient of heat transfer in accordance with the basic laws. For a harepipe coil the over-all coefficient of heat transfer, whether for heating or for 154 CHAPTER 7 * 1946 Guide cooling (dry), can be expressed by a simplified basic formula as follows: . Jl + _L hr ^ k A* , ,(2) . where .. . . *, ' . U = over-all coefficient of heat transfer, Btu per (hour) (square foot external surface) .. (Fahrenheit degree mean temperature difference between air and fluid within the coil). . " . ht -- film coefficient of heat transfer between the internal surface of the coil and the fluid flowing within the coil, Btu per (hour) (square foot internal surface) . (Fahrenheit degree mean temperature difference between that surface arid the average fluid temperature). Aa = film coefficient of heat transfer between air and the external surface of the coil, ' Btu per (hour) (square foot external surface) (Fahrenheit degree mean tem perature difference between the mass of air and the external surface). . ` k = conductivity of material from which the bare pipe is constructed, Btu per (hour) (square foot) (Fahrenheit degree per inch thickness). * . L-= thickness of tube-wall, inches. ' . R = ratio between external and internal surface of the bare tube, usually varying from 1.03 to 1.15 for the tube used in typical heating' or cooling coils. * This ratio R is inserted in the formula in order to place internal fluid coefficient of `' heat transfer on the basis of external surface. - ; Frequently, when pipe or tube walls are thin and of material having high conductivity (as is the case in construction of typical heating and cooling coils) the term L/k in Equa tion 2 becomes negligible and is generally disregarded. (The effect of the term L/k in, typical bare pipe heating or cooling coils seldom exceeds 1 to 2 per cent of the over-all coeffident). Thus, in its simplest form, for bare pipe: . .. ` u - ------------ -- ` JL , _L : hr - A* ' '. (3) . For finned coils the formula1 for the over-all coefficient of heat transfer can be conveniently written: . \ . u =------------ A + ...l - Ar ^JfAa . ' > in which the term Vi, called the fin efficiency, is introduced to allow, for the resistance to heat flow encountered in the fins. -. . The term R, in this case, is the ratio of total, external surface to internal surface. For typical designs of finned coils for heating or cooling, this ratio varies from 10 to 30. Term R is again introduced to place'the internal surface coefficient of heat transfer on a basis of external surface. In the .discussions which follow, coefficients hT and will be considered separately, and also various ways of combining them will be outlined. The performances of all heating and dry cooling coils are influenced by the same factors. But, when cooling coils operate wet or act as dehumidifying coils, the performance cannot be predicted on the basis of over-all coefficients and an analysis must be made on the basis of individual film coefficients.as will be explained. PERFORMANCE OF DEHUMIDIFYING COILS - .When a'cooling coil operates with a surface temperature which is' below the dew-point of the air entering the coil, moisture is condensed .and the air leaves the coil with a humidity ratio lower, than it had when ; ' Heat Transfer Surface Coils it entered the.coil: To understand the performance of surface coils under such conditions, assume that air/ enters a cooling coil at conditions corresponding to point 1 in Fig: 12. As long as-the surface temperature .of the coil is above'the dew-point; the air is cooled without dehumidifi cation, and its condition leaving the coil will be somewhere on line l-A." Its exact position on this line depends on the air velocity and the external film coefficient as well as upon the surface temperature. When the surface temperature just equals the dew-point, the air leayes with conditions represented by point A. If the surface temperature is below the dew point, condensation takes place, and the air has a final condition some where along the line A-2-3 which is a line at a constant horizontal distance from, the saturation curve. It should be understood that the line l-A-2-3 is not intended to represent the path of the condition of the air'as it ! passes through the coil from row to row. It is simply the path traced Fig. 12. Performance of Dehumidifying Coil . by the exit air conditions as the surface temperature is gradually reduced with other conditions remaining constantJ. .. In the process of dehumidification, since heat is being transferred to the coil surface by two different mechanisms, (convection and cbhden-. satiori), it is evident that ail over-all coefficient of'heat transfer cannot be determined by the. same method used for heating, and for dry cooling , coils. However, if it is assumed that the sensible "heat transfer 'of a, . dehumidifying coil is unaffected by the presence of . moisture, on its surface, Equation 5 may be obtained to express-this part of the heat ' transfer in terms of the external film coefficient and the surface tern-'' perature.. ' . 5s = fta X A X N X (krZJa) 7 , . . - ' (5)` . where -' / ' y '" - ' qs = sensible heat transferred, Btu per . (hour) (square foot of coil face area), h = dry-bulb temperature of air entering coil, Fahrenheit degrees, . ti = dry-bulb temperature of air leaving coil, Fahrenheit degrees. ' ts = average temperature of coil external surface, Fahrenheit degrees. MTD& = logarithmic mean temperature difference between air and coil surface =,- 156 CHAPTER 7 ' 1946 Guide If this equation is combined with another equation expressing sensible heat transfer in terms of mass-velocity and temperature difference, the variables may be arranged in the following form (which is useful for the sqlution of dehumidification problems and for the determination of Aa from test data): . " or, where . 0.243 G ha A N (h - t,) = 0.243 G {h -- h) ft Is tog< h -- is KAN ft -- ts 0.243G = logt it -- ts specific heat of humid air, Btu per (pound) (Fahrenheit degree), air mass velocity, pounds per (hour) (square foot of coil face area). (6) An examination of Fig. 12 will reveal that when ts is at thedew-point of the entering air: - ti -- ts __ t\ --/dpi /a " /s /a -- /dpi . and when ts is below the dew-point: . tl -- tg tl -- /dpi ' ti is t% ^dp2 . Therefore, Equation 6 may be written in its most useful form as: AN , /, fdpi , ii -- is 0.243G = toge T~ ~ `0ge T^ts (7) where /a /dpi Alps : minimum dry-bulb possible-without dehumidification, Fahrenheit degrees. : dew-point of air entering coil, Fahrenheit degrees. " : dew-point of air leaving coil, Fahrenheit degrees. j .This.equation may be used to establish a line as A-2-3 for a given coil if Aa is known for the coil, or it may be used to determine.ha from test data for the purpose of rating coils. The use of this equation for coil selection is illustrated in Example 1 at the end of the chapter. Equation 7 is also important as a means of determining the external film coefficient. External Film Coefficient ' . While formulae'have been developed expressing the film coefficient Aa for air passing parallel to a plane surface, they cannot be used directly: for fins on tubes because of air turbulence and because of the temperature gradient prevalent from the edge of a fin to its center. It is therefore necessary to make tests to evaluate the combined term fi(Aa. The term,. "hiha, will be written merely Aa in this discussi'on as there is no necessity for separately evaluating -q and because values of Aa are-usually applied .only to the particular.coils for which tests are made. The air side coefficient, Aa, of a coil of particular dimensions is an exponential function of the mass velocity of the air: . where ha = ZGn ' - : (8) . - ha = film coefficient of heat transfer, Btu per (hour) (square foot external . surface) (Fahrenheit degree mean temperature difference between air . and average surface temperature). ' Ifmt Transfer Surface Coils 157 - G -- air mass velocity, pounds per (hour) (square foot of coil face,area). Z and n = constants which depend upon both air turbulence and surface arrange - ' ment. Evaluation of constants Z and n may be accomplished through the use of test data in Equation 7 which gives values of ha directly from the results of any wet coil test. If ha, calculated in this manner, is plotted against values of G which prevailed during the tests a straight line should . result on logarithmic coordinates. The slope of this fine is the value of n. The value of Z may then be determined by direct substitution in Equa tion 8. Internal Film Coefficient .. The internal film coefficient, Ar which appears in Equation 3, is evalu ated in various ways, depending upon the nature of the fluid, and whether the fluid is changing state. ". When evaporating refrigerants are used in tubes, the temperature of the fluid is fairly constant, being affected principally by pressure drop ' through the tubes, by superheat of the evaporated refrigerant, and by the presence of oil in solution. To obtain maximum coil capacity it iS necessary to keep the pressure drop through the tubes at a minimum (,/4 lb per square inch), to keep the superheat as low as possible without carrying liquid back to the compressor, and to arrange for good separation and return of oil to the compressor. Another important factor is-the removal of gas to keep the tube surface' flooded with liquid as much as possible. The internal film coefficient is markedly increased by heavy heat loads, because. the increased turbulence and gas velocity cause good contact of the liquid with the tubes. Values of Ar usually lie between 150 and 450. For rating of dehumidifying coils, satisfactory results are obtainable by first determining the average external surface temperature from. Equation 7, and then using the difference between, the external film temperature and the refrigerant for evaluating hr in Equation 9. where .- K <=> internal film coefficient of heat transfer, Btu per (hour) (Square foot of internal tube surface) (Fahrenheit degree), tr = average refrigerant temperature, Fahrenheit degrees. . The term (ts -- tr) is commonly written At. To evaluate' h, by this method the same tests that were required to determine ha may be used. When water is the cooling medium in tubes, the rate of heat transfer is a function of its velocity, which influences the number of contacts of the water molecules with the tube surface, per unit of time. Increased water velocity and reduced tube diameter cause increased heat transfer. Heat transfer is also greater at higher temperatures of the water. The basic formula for the film coefficient of heat transfer for flow of water is as follows: . . ftr= i.5 {t + ioor-^i . (10) where . V =. water, velocity, feet per second. D. -- internal diameter of tube, inches. , t a* average water temperature, Fahrenheit degrees. '' , . - .' 158 _________CHAPTER 7 . > .1946 Guide Heat Transfer Surface Coils 159 -In the case of finned tubes, values of hi may be "lower than those obtained by use of Equation 10 and .actual testResults are preferred if available. . '' ' When saturated steam is condensed in . the tubes of coils, the film coefficient hi varies from 1000 to 2000, depending on freedom from air in the steam, and upon good drainage of the tubes. The coefficient is fairly' constant for a particular coil, giving values of-Al that are directly propor tional to qt. - Performance of Coils and Refrigeration Compressor .. Practically all data published by various makers of. direct expansion .. cooling coils are based upon maintaining a predetermined refrigerant' temperature within the coils. While it is often possible to maintain a 2. The performance curve of a given compressor with a definite condenser (com bination usually called a condensing unit) is. plotted as a function of suction temperature^ corresponding to the saturation suction pressure at the compressor suction service valve for a given inlet water temperature and quantity supplied to the condenser. ' .. 3. The performance curve.of the given cooling coil is'next plotted as a function of- mean suction temperature within the coil, and the wet-bulb temperature of air entering the coil, for a given mass air velocity over the coil. .' ' 4. The refrigerant pressure drop between the center of the cooling coil and the com pressor suction service valve is computed and converted into the terms of temperature difference. This temperature difference is then fitted in horizontally between the performance curves of the cooling coil and the compressor, as shown, and the total capacity of the coil-compressor combination is read along the horizontal line upon which the above mentioned temperature-difference segment falls. . ^ COIL SELECTION In the selection of a coil it is necessary to consider several factors: 1. The duty required--heating, cooling, dehumidifying. . .. 2. Temperature of entering air--dry-bulb only if there is no dehumidification, dry- and wet-bulb if moisture is to be removed. -` 3. Available heating and cooling media. - 4. Space and dimensional-limitations. .- - - . . 5. Air quantity limitations.' . ' " ,. ' . 6. Allowable resistances in air circuit and through tubes. 7. Peculiarities of individual designs of coils. . 8. Individual installation requirements, such, for example, as type of automatic con trol to be used. . ' . . , .... part it'is either impossible or impractical. 'This is due to' the fact that the capacity, of standard refrigeration compressors, is usually fixed and in matching a given cooling coil and a standard.compressor the capacityof the latter is often somewhat smaller or greater than that of the.former. Consequently, the refrigerant temperature resulting within.a cooling coil and correspondingly the capacity- of the coil-compressor combination are very often hot what they were originally.calculated to be.. .. In order to determine the actual performance of a given coil-compressor combination under varying conditions of operation, a graphical solution. . of. the balance point is highly desirable. A typical procedure for graphical analysis of a coil-compressor combination performance is shown in Fig. 13, which is constructed as follows: . ' . . 1. The equipment capacity scale, total Btu per hour, is laid'out along the' vertical ' axis while the refrigerant suction temperature scale-is laid out-along the horizontal ' . axis using rectangular coordinates. - . ... .- The duties required may be determined from information in Chapters 6, 8, 14 and 15. There may or may not be a choice of cooling and heating media, as well as temperatures available, depending upon whether the installation is new or is in combination with present sources of heating or cooling. Space limitations are dictated by the requirements of individual -cases. The air quantity is influenced by a number of considerations. The air quantity through heating coils is often made the same as that necessary to handle the summer cooling load. The air handled may be fixed by the use of old ventilating' ducts as an air distribution system for new air conditioning apparatus, or may. be dictated by requirements of satisfac tory air distribution or, ventilation. The resistance through the air circuit influences the fan horsepower and speed. This resistance may be limited to allow the use of a given size of fan motor, or to keep the opera ting' expense low, or it may be limited by the maximum fan peripheral velocity which requirements of quietness may permit. The friction. . through the water or brine circuit may be dictated by the head available from a given size of pump and pump motor. As the fan and pump motor ' inputs represent a refrigerating load on cooling installations, it is eco- , nomical to keep them low. ,. .. . Proper performance of a surface heating or cooling coil depends upon correct choice of the original equipment and upon certain other factors. The usual coil ratings are based on a uniform face velocity of air. If the' air is brought in at odd angles or if the fan is-located so as to block part .of ' the air flow, the performance as given in the manufacturer's ratings cannot usually be: obtained. To obtain this performance it is necessary ' also that the air quantity be adjusted on the job to that used in deter-': mining the.coil selection, and must also be kept at this value. The most -. !l 160 CHAPTER 7 1946 Guide '. common causes for a reduction of air quantity are the fouling of the filters and collection of dirt in the coils. These difficulties can be avoided by proper design and proper servicing1. There are a number of ways in which coils may be cleaned.' A common method is to wash them off with water. They can sometimes be brushed and cleaned with a vacuum cleaner. In bad cases of neglect, especially on restaurant jobs where grease and dirt have accumulated, it is sometimes necessary to remove the coils and wash off the accumulation with steam, compressed air and water, or hot water. The most satisfactory, solution, however, is to keep the filters serviced,. and thus make the cleaning of the coils unnecessary. The proper selection of coils requires an understanding of the necessities of each case and should be based on ah economic analysis of the plant design as a whole. No general rule can, therefore, be laid down for the selection of heating or cooling coils. It is possible* however, to point out the limits of usual practice and to indicate the influence of the variables involved in the coil selection. . Heating Coils . ' Steam, and hot water heating coils are usually rated within these limits: Air Face Velocity--200 to 1200 fpm, sometimes up to 1500 fpm. 1 Steam Pressure--2 to 200 lb, sometimes up to 350 lb per square inch. Hot Water Temperature--150 to 225 F. . Water Velocity--2 to 6 fps. . - . Individual cases may deviate widely, but the tabulation given-herewith will serve as a guide to usual heating installation practice: Air Face Velocity--500 to 800 fpm face, 500 being a common figure. .. Delivered Air Temperature--varies from about 72 F .for ventilation, only to about 150 F for complete heating. .. . Steam Pressure--2 to 10 lb, 5 lb being common. Hot Water Temperature--150 to 225 F. ... Water Velocity--2 to 6 fps. . .Water Quantity--Based on about 20 F temperature drop through a hot-water coil. Air, Resistance--The total resistance through heating coils is usually limited to from 54s to 54s in. of water gage for public buildings, to about 1 in. for factories. . The selection of heating coils is relatively'simple as it involves"dry-bulb temperatures and sensible heat only, without the complication of simul taneous latent heat loads, as in cooling coils. For a given ditty, entering air temperature, and steam pressure, it is possible to select several arrange ments of the same design of coil depending upon the relative importance of space, cross-sectional area, and air resistance. . Cooling Coils Cooling and dehumidifying coils are usually rated within these limits: Entering Air Dry-Bulb--60 to 100 F.' - Entering Air Wet-Bulb--50 to 80 F. - , , Air Face Velocities--300 to 800 fpm, (sometimes as low as 200 and as high as 1200). Volatile Refrigerant Temperatures--25 to 55 F, at coil suction outlet. -. Water Temperatures--40 to 65 F. , ' Water Quantities--2 to 6 gpm per ton, dr-equivalent to a water temperature rise of from 4 to 12 deg. . .- Water Velocity--2 to 6 fps. . Heat Transfer Surface Coils 161 The ratio of total to. sensible heat removed varies in practice from 1.00 to about 1.65, i.e., sensible heat is from 60' to 100 per cent of total, depending on the application. (See Chapter .43.) Since required-ratios may demand wide variations in air velocities, refrigerant temperatures, and coil depth, general rules as to their values may be misleading.' On usual comfort installations, air face velocities between 400 and 600 fpm are frequent, 500 being, a common value. Refrigerant temperatures ordinarily vary between 40 and 50 F where cooling is accompanied by dehumidification. Water velocities range from 2 to about 6 fps. When no dehumidification is desired, for which condition the dew-point of the entering air is equal to or lower than the cooling coil surface tern- perature, the coil selection is made on the basis of dry-bulb temperatures and sensible heat transfer only, the same as with heating coils. It is possible also to choose various arrangements of face area, depth, air velocity, etc., for the same duty. ' Dehumidifying Coils The selection of coils for combined cooling and dehumidifying duty is more involved than for heating or sensible cooling and requires con- Table 1. Various Cooling Coil Arrangements Selection 1 Total cooling capacity, tons...'.-- 100 Sensible cooling capacity, tons... 69 Latent cooling capacity, tons.. 31 Ratio total to sensible heat.____ 1.45 Air quantity, cfm - ........... 47,800 Cfm per total ton..... ......... ^______ 478 Face velocity, fpm.______________ 325 Resistance, m. water 0.11, Coil face area, sq ft.._ ........ .......... 147 Coil rows'deep.__l.......................... 4 Coil evaporator temp. F deg...... 45 2. 100 69 31 1.45 41,700 417 423 0.27 99.0 6 45 3 100 69 31 1.45 37,100 371 500 0.51 74.2 8 45 4 100 . 69 31 1.45 46,800 468 600 0.37 78.1 '4 38 sideration of both dry- and wet-bulb air temperatures. It is further complicated by the fact that the proportional amount of dehumidification required is also highly variable. The methods outlined previously under Heat Transfer and Resistance may be used to determine whether it is possible for a coil to perform the duty required. If entering and leaving air conditions are arbitrarily specified* the corresponding duty'sometimes . cannot be obtained at all without the use of reheat. As with heating and sensible cooling coils, there are combinations of face areas, depth, air velocity and refrigerant temperatures which will give the required per formance. This is illustrated in Table 1. . It is possible as shown in Table 1 to perform approximately the same duty at a given refrigerant temperature with small face area and large ~ thickness or vice versa. The large face area coil gives low air velocity and resistance but high air quantities per ton. The coil of small face area and 1 great depth requires small air quantities per ton of refrigeration, high resistance and high air velocities: As shown also in Table 1 the same , sensible, latent and total cooling capacity may be obtained with.various refrigerant temperatures by proper choice of coil. This makes it possible . to keep the evaporating, temperature high enough to carry the load with a chosen size of condensing unit. High evaporating temperatures with 162 CHAPTER 7 1946 Guide correspondingly small compressor operating expense can be attained but - at the expense of coil surface, air quantity or both. The choice will be determined by the necessities of. individual installations. ' For a given quantity and condition of entering air the evaporating temperature of a volatile refrigerant coil is determined by a balance'' between the condensing unit and the coil. The total, sensible and latent cooling capacity can then be determined from the coil rating information. . If the condensing unit and cooling coil have been properly balanced for the required load and, due to miscalculated duct resistance or improper choice of fan speed,' the air quantity is reduced, the total cooling capacity will also be reduced. The decrease is generally in the sensible capacity. This is the effect also when the air by-pass or volume control is used. It is necessary that not only the total capacity but also the sensible and latent cooling requirements both be-met. The installation of an excess of coil results in an increase in total capacity, but not a proportional gainin latent heat capacity. On installations controlled from dry-bulb tem- Table 2. Capacity Balances for Maximum and Minimum Load Conditions Conditions . '' ' . Required at peak load conditions___ ________ Required at minimum load conditions............. Peak load equipment balance. .................. Same equipment balanced at minimum load conditions..._... _____ ___ ___ Same equipment balanced at maximum load conditions with 40 per cent by-pass._______ Same equipment balanced at minimum load conditions with 38,800 Btu per hour reheat Capacity in Tons Total . Sensible 10.90 6.62 10.90 7.90 3.36 7.90 Latent 3.00 3.26 3.00 9.85 ,6.58 3.26 8.38 ..5.05, 3.33 6.62 3.36 3.26 _Ratio T=S-eo--nt--sa-i-lb--l--e- 1.38 1.98 > 1.38 1.50 1.66 1.98 . . ' perature the operating time is shortened because of the added sensible cooling capacity. This results in less moisture pick-up and higher relative humidity than calculated. If an oversize condensing unit is installed, the opposite situation occurs. Generally, this is not a disad vantage except that it results in a load from outside air greater than; calculated, as well as in.increased power consumption: If oversize equip ment is furnished,, a balance should be made to assure that, the ratio of total to sensible capacity is the same as in the estimated load. .. Sometimes arbitrary air quantities are specified for ventilation' or other reasons independent of the selection of the cooling coil. As shown in Table 1, the coil selection can be altered to take care of various air quantities for the same duty. . ' Where coil and condensing unit are selected for the peak load condition, and the sensible load partially disappears due to fall of outside tempera ' ture or other cause, the condensing unit and coil 'rebalance: This may result in more sensible and less latent capacity than required at the light - . , load condition, with an increased relative humidity in the conditioned . , space. Such a condition is shown in Table 2. If approximately 40 per cent of the total air is by-passed, the condition is improved as indicated. The situation may be entirely avoided by using reheat; where it is possible to handle any.ratio of sensible and latent loads and maintain the design, temperature and humidity *. ' ; Care should be taken to avoid freezing at light loads. In-general; ' Heat'Transfer Surface Coils ' ______ ., ' ' ' * , 163 freezing occurs, when the. coil surface temperature falls , to-32 F. With usual coils for comfort installations, this does not occur unless the evapo rating temperature at the coil outlet is about 20 to 25'F. The exact value depends on the design of the coil and the amount of loading. Although it is not customary to .choose coil and condensing units to balance at low temperatures at peak loads, there is danger of this occurring when the load decreases. This is further aggravated if a: by-pass is used so that less air is passed through the coil at light loads. It may be even worse if the control is arranged for decrease of inside temperature with fall of that outside. Freezing can be avoided by making the full load balance a high evaporating temperature and checking the balance at the minimum load. Care should be exercised in the design of humidity control to minimize the cycling of the refrigerating compressor because of re-evaporation of moisture from the fins.. It is sometimes necessary to by-pass air around a coil when the compressor is not operating. . Determining Size of Cooling Coil ' The procedure for selecting the proper size of coil for cooiing and'for determining exit air condition, coil surface temperature, total coil load and refrigerant temperature is illustrated in Example, 1/ . Example 1. An industrial application requires the cooling of a certain quantity of air from a condition, of 102 F dry-bulb and 85 F wet-bulb to a final condition of 80.5 F dry-bulb and 73 F wet-bulb. The air velocity across the coil is to be 400 fpm and coil data are as follows: 5a = 10.7 at 400 fpm, Ar -- 325, external surface area^ = 15 sq ft per (square foot of face) (row of coil depth), ratio of external surface area to internal surface area = 15. ' Solution. (1) Lay out the problem psychrometry as indicated in Fig. 14 and note that the minimum horizontal distance'between the load ratio line and the saturation- curve is 1.8 F dry-bulb at point A Fig. 14.- This means that k -- <dns in Equation" 7 must not be less than 1.8. . Therefore, Equation 7 should be solved for N to'determine the proper number of rows to be used for the coil. . '' ' - 164 i CHAPTER 7 . 1946 Guide Aa A, N. 0.243 Gi - hpt 102-80 = loge 12.22 = 2.5 . 1.8 Then substituting values for ha, A\, and Gu N may be found as follows: 10.7 X .15N = 2.5 from which, N -- 6.58 0.243 X 1740 (2) This establishes the maximum whole number of coil rows that can be used as 6 and it is now possible to determine the actual location of the exit air conditions from Equation 7 by solving for the actual value of tt -- /dpa for a 6 row coil. 10.7. X 15 X 6 , _ . 102 - 80 0.243 X 1740 -loge h - hpi 2.275 This establishes values of 9.78 for j------= R and 2.25 for U -- /dp2** " <dpa (3) Next, the exit air condition at 57.3 F dry-bulb and 56 F wet-bulb as shown at B, is found by locating a point on the load ratio line at a horizontal distance of 2.25 dry-bulb degrees from the saturation curve. ' (4) The surface temperature may now be found from Equation 7 which may also be written as: '. - , . Bit - tr -ta~ TT^T where ... ti ~ /dpi h fdps k - 9.78 X 57.3 8.78 - 102 52.3 (5) The total coil load may be calculated from the enthalpy difference across the coil and the air quantity using the weight of dry'air instead of the weight of the mixture. $t = Ga (hi -- ht) = 1700 (49.24 -- 23.77) -- 43,200 Btu per (hour) (square foot of face area) where . Ga = Weight of dry air per (hour) (square foot of coil face area). hi ~ enthalpy of air vapor mixture entering coil, Btu per pound of dry air. fh = enthalpy of air vapor mixture leaving coil, Btu per pound of dry air. (6) The refrigerant temperature may be found from Equation 9 43,200 325 = Os - tT) = 22.1 15 X 6 X 15. Therefore, h = (52.3 - 22.1) = 30.2. Thus a coil 6. rows deep operating at a refrigerant temperature of 30.2 F and a face velocity of 400 fpm is required and it will carry a total load of 43,200 Btu per (hour) (square foot of face area). The air conditions leaving the coil are too low for the con ditions of the problem and therefore it is necessary to by-pass air at the entering condition to obtain the desired, result of 80.5 F dry-bulb and 73 F wet-bulb. . ., ' ' Although the preceding solution is satisfactory, it may be more desirable in some cases to use a higher refrigerant temperature-and employ reheat to obtain the desired load ratio. Such a solution is shown in Fig. 15. In this case the coil load ratio line intersects the saturation curve and therefore a coil of any depth may be selected. . ` If a coil depth of 6 rows is maintained, the exit air conditions for the coil are indicated at point B Fig. 15 as 72i3 F dry-bulb and 70.8 F wet-bulb and the surface temperature . will be: '` `" 4 9.78 X 72.3 -102.. ,, h =-------- "887788--------- - = 690 Heat Transfer Surface Coils ' 165 Fig. 15.. Psychrometric Layout for Coil Selection The coil load will be:, gt = 1700 (49.24 -- 34.66) = 24,800 Btu per (hour) (square foot of face area) and the refrigerant temperature will be found from Equation 9: 24,800 325 15 X'6 X 15 (ts - tx) = 12.7 Therefore, tr = 69.0 - 12.7 = 56.3. . Thus, for the case where, reheat is used, a coil 6 rows deep operating at a refrigerant temperature of 56.3 F is required. The total coil load will be 24,800 Btu per (hour) (square foot of face area) but the actual effective load will be less by the amount of reheat required. Therefore, for a given load, a larger coil and more refrigerating capacity are required when reheat is used. ', '*; LETTER SYMBOLS USED IN CHAPTER t) = fin efficiency. ' . . A = external area of coil^ square feet per (square foot of coil face area) (row of-coil depth). ' . B = ~ *dpl ti -- tdpt . , . , D -- internal diameter of tube, inches. . G '= air mass velocity, pounds per (hour) (square foot of coil face area). Ga dry &ir mass velocity, pounds dry air per (hour) (square foot of coil face area). '. hi = enthalpy of air-vapor mixture entering coil, Btu per pound of dry air. ' hi -- enthalpy of air-vapor mixture leaving coil, Btu per pound, of dry air. , . fca = film coefficient of heat transfer between air and external coil .surface, Btu per (hour) (square foot external surface) (Fahrenheit degree mean tem perature difference between air and coil). . _, 166 CHAPTER'7 ^ 1946y Guide hr = film coefficient of heat transfer between; fluid and internal coil surface, ' Btu per (hour) (square foot internal surface) (Fahrenheit' degree mean . temperature between fluid and surface). '' k =~ conductivity of pipe or tube material, Btu (square foot) (hour) (Fahrenheit * degree per inch thickness). ` L = thickness of tube wall, inches. MTD = abbreviation--mean temperature difference between fluid in coil and air passing over coil, Fahrenheit degrees. ` Note: MTD--usually logarithmic mean. - . MTDa -- logarithmic mean temperature difference between air and coil'surface. ' N = number of rows of coil, depth. ' n - a constant, exponent of G in Equation 8, obtained by plotting,, on loga rithmic coordinates, G against values of h&. The value of h is the slope of the line. ' 2s --. sensible heat transferred Btu per (hour) (square foot of coil face area). qt = total heat transferred by coil, Btu per (hour) (square foot of face area). R. = ratio between external and internal surface of tube. t = average water temperature, Fahrenheit degrees. t% -- dry-bulb temperature of air entering coil, Fahrenheit degrees. . it = dry-bulb temperature of air leaving coil, Fahrenheit degrees. /a -- minimum dry-bulb temperature possible without dehumidification, Fahren heit degrees. .. . . Mpi = dew-point of air entering coil, Fahrenheit degrees. *dpj = dew-point of air leaving coil, Fahrenheit degrees. . .tt ~ average refrigerant temperature, Fahrenheit degrees. /s = average temperature of external surface of coil, Fahrenheit degrees. At = is - fr. . ',, '. U = over-all coefficient of heat transfer, Btu per (hour) (square foot of external . coil surface) (Fahrenheit degrees temperature difference between fluid in coil and air flowing over coil). . - . ,. V = water velocity, feet per second. . . . Z = a constant for use in Equation 8 obtained by plotting on logarithmic i coordinates G against values of h^. . Note: Numerical subscripts refer to condition entering and leaving respectively. , . . REFERENCES `" *--Rational Development and Rating of Extended Air Cooling Surface, by HT B. Pownall (Refrigerating Engineering; October, 1935. p. 211). -v *--Performance of Surface-Coil Dehumidifiers for Comfor lAir Conditioning. by.G. L. Tuve and L. G. Srigel (A.S.H.V.E. Transactions, Vol. 44. 1938. p. 523). .. --Reheating by Means of Refrigerant Compressor Discharge Gas, by S. F. Nicoll (A.S.H.V.E. Trans actions, VoL 47, 1941, p. 239). .^ . - CHAPTER 8 oCeah a9e Causes of Infiltration., Infiltration Due to Wind Pressure, Infiltration Through Walls, Window and Door Leakage, Crack Method, Air Change Method, Infiltration Due to Temperature Difference, Sealing of Vertical Openings - THE air leakage which takes place through various apertures in buildings must be considered in heating and cooling calculations; and properly evaluated. This infiltration as it is sometimes designated takes place through cracks around doors and windows, through solid walls and through fireplaces and chimneys. Although the latter sources of leakage may be considerable, they are often neglected on the assumpr tion that dampers would be closed during periods of extreme cold weather: or else that the fireplace will be in use at such times and will therefore contribute to the heat supplied and lessen the heating load'. CAUSES OF INFILTRATION The displacement of heated air in buildings by unheated outside air is due to two causes, namely, (1) the pressure exerted by the wind and (2) the difference in density of outside and inside air because of differences in temperature. The former is generally referred to as infiltration and die latter as stack or chimney effect. In either case an exact estimate of the amount of infiltration under, design conditions is difficult to make. The complicating factors include (1) variations in building construction particularly as to width of crack or size of openings through which air leakage takes place, (2) the varia tions in wind velocity and direction, (3) the exposure of the building with respect to air leakage openings and with respect to adjoining buildings, (4) the variations in outside temperatures which influence the chimney effect, (5). the relative area and resistance of openings on the windward and leeward sides and on the lower floors and on the upper floors, and (6) the influence of a planned air supply and the related outlet vents. Tight' construction is essential for preventing large heat loss due to infiltration. INFILTRATION DUE TO WIND PRESSURE The wind causes a pressure to be exerted on one or two sides of a building. As a result, air comes into the building on. the windward side through cracks or porous construction, and a similar quantity of air leaves on the leeward side through like openings. In general the resist tance to air movement is similar on the windward to that on the leeward side. This causes a building up of pressure within the building and a. lesser air leakage than that experienced in'single wall tests as determined, in the laboratory. It is assumed that actual building leakages owing to this building up of pressure will be 80 per cent of laboratory test values: While there are cases where this is not true, tests in actual buildings substantiate the factor for the general case. Mechanical ventilating systems are frequently designed to produce positive or negative pressures in an enclosure which are greater or lower than-prevalent wind pressures. In such.designs, if the rate at which air is specified to be introduced to or removed' from the enclosure by positive means exceeds the infiltration rate, it is common practice to use the greater value in determining the heating capacity to warm the outside air. ' - . 167 .. 168 CHAPTER 8 ' 1946 Guide Infiltration Through Walls . Data on infiltration through.brick and frame walls are given in Table 1 *. The brick walls listed in this table are walls which show poor workman ship and which are constructed of porous brick and- lime mortar. For good workmanship, the leakage through hard brick walls with cementlime mortar does not exceed one-third the values given. These tests . indicate that plastering reduces the leakage by about 96 per cent; a heavy coat of cold water paint, 50 per cent; and 3 coats of oil paint carefully applied, 28 per cent. The infiltration through walls ranges from 6 to 25 percent of that through windows and doors in a 10-story office building, with imperfect sealing of plaster at the baseboards of the rooms, With perfect sealing the range is from 0.5 to 2.7 per cent or a practically negligible quantity, which indicates the importance of good workmanship in proper sealing at the baseboard. It will be noted from Table. 1, that the infiltration through properly plastered walls can be neglected.' The value of building paper when applied between sheathing and Table X, Infiltration Through Walls3 Expressed in cubic feet per squarefoot Per hour Ttps or Wall Wind Tzlocot, Miles fob Houb 5 10 15 20 25 30 Brick WalL--{BSsSlI 2 -4 8 0.02 0.04 , 0.07 12 0.11 19 0.16 23 0.24 id in. brick WalL--------{plastered.... 1 0.01 ,4 0.01 7 12 16 21 0.03 0.04 0.07 0.10, Frame Wall, with lath and plaster1* 0.03 0.07 0.13 0.18 0.23 0.26 . * *The values given in this table are 20 per cent less than test values, to allow for building up of pressure in rooms and are based on test data reported In the papers listed in chapter footnotes. . ' bWall construction: Bevel siding painted or cedar shingles, sheathing, building paper, wood lath and 3 coats gypsum plaster. > . shingles is indicated by Fig. 1, which represents the effect on outside construction only, without lath and plaster. The effectiveness of plaster properly applied is no justification for the use of low grade building paper or of the poor construction of.the wall containing it! Not only is it difficult to secure and maintain the full effectiveness of, the plaster but also it is highly desirable to have two points of high resistance to air flow with an air space between them. The infiltration indicated in Fig. 1 is that determined in the laboratory and should be multiplied by the factor 0.80 to give proper working values. , .. . Window and Door Leakage , . . . There are two methods of estimating air leakage through window and door cracks, namely; (1) the crack method and (2) the air change method. The crack method is generally regarded as being more accurate-than the purely arbitrary'air change method, provided the variables entering into the crack method, such as crack width and clearance, can be properly- evaluated. . -- ^ Air Leakage 169 Crack Method The crack method is based on known air leakage factors for various types of windows and widths of crack and clearance. The wind velocity and length of crack are also considered when the crack method is employed. . The amount of infiltration for various types of windows is given in Table 22. The fit of double-hung wood windows is determined by crack and clearance. Crack thickness is equivalent to one-half the difference between the inside window frame dimension and the outside sash width. The difference between the width of the window frame guide and the sash thickness is considered as the clearance. The length of the perimeter opening or crack for a double-hung window is equal to three times the width plus two times the height, or in other words, it is the outer sash perimeter length plus the meeting rail length. Not all the window crack in any given room is necessarily used in estimating the infiltration heat Fig. X. Infiltration Through Various Types of Shingle Construction loss by the crack method. The length of crack to be selected in any given case depends on the number of exposed sides as explained in Chapter 14. Values of leakage shown in Table 2 for the average double-hung wood window were determined by using, on nine windows tested in the labo ratory, the average measured crack and clearance of a large number of windows found in a field survey. In addition, the table gives figures for a poorly fitted window. All of the figures for double-hung wood windows are for the unlocked condition. Just how a window is closed, or fits when it is closed, has considerable influence on the leakage. The leakage will be high if the sash are short, if the meeting rail members are warped, or if the frame and sash are not fitted squarely to each other. It is possible to have a window with approximately the average crack and clearance that will have a leakage at least double that of the figures shown. Values for the average double-hung wood window in Table 2 are considered to be .. easily obtainable figures provided the workmanship on the window is good. Should it be known that the windows under consideration are poorly fitted, the larger leakage values should be used. Locking a window ' 170 CHAPTER 8 1946 Guide Table 2. Infiltration Through Windows Expressed in Cubic Feet per Foot of Crock per Hour* Ttpe o Window Remarks Worn Vslocitt, Miles peb Hour 5 10 IS ' 20 25 30 Around frame in masonry wall--not calked** 3 8 14 Around frame in masonry wall--calkedb____ 1 ' 2 3 Around frame in wood frame construction^_ Double-Hung Total for average window, non-weatherWood Sash stripped, J6-in. crack and 36*in. clearance.c Windows Includes wood frame leakage^ ' (Unlocked) Ditto, weatheratrippedd 2 7 4 6 21 13 11 39 24 Total for poorly fitted window, non-weather- stripped, $-m. crack and %rin. clearance.* Includes wood frame leakage^- Ditto, weatheratrippedd . 27 6 69 . Ill 19 34 Double-Hung Noo-weatheratripped, lockedMetal _ Non-weatheratripped, unlocked........ ..... Windows^ Weatherstripped, unlocked______ . 20 45 20 47 6 19 70 74 32 Industrial pivoted, 36-in. cracks ' 52 108 176 Rolled Architectural projected, kr-in. crackh_:____ 15 36 . Section Architectural projected, 36-in. crackh______ 20 52 Steel Residential casement, 16-io. crack! 6 ,18 Sash Residential casement, 16-in. crack* 14 32 Windows^. Heavy^casement.section, projected, 16-in. 3 10 62 88 33 52 18 Heavy casement section, projected l-in. cracki .- 8 24 38 Hollow Metal, vertically pivoted window^._____ 30 88 145 20 27 35 4 56 .17 23 30 59 80 104'36 49 63 154 199 249 51 71 92 96 125 ' 154 104 137. 170, 46 60 76 244 86 116 47 76 26 54' 304 - 112 152 60 100 36 72 372 139 182; : 74 . 128 48 92 . 186 221 242 . `The values given in this table, with the exception of those for double-hung and' hollow metal windows, are 20 per cent less than test values to allow for building up of pressure in rooms, and are based on test data reported in the papers listed in chapter footnotes. . bThe values given for frame leakage are per foot of sash perimeter as determined for double-hung wood windows.- Some of the frame leakage in masonry walls originates in the brick wall itself and cannot be prevented by calking. For the additional reason that calking is not done perfectly and deteriorates with time, it is considered advisable to choose the masonry frame leakage values for calked frames as the average determined by the calked and non-calked tests. . ' The fit of the average double-hung wood window was determined as )-in. crack and $6-in. clearance by measurements on approximately GOO windows under heating season conditions.- dThe values given are the totals for the window opening tier foot of sash perimeter and include frame leakage and so-called elsewhere leakage. The frame leakage values included are for wood frame construction 'but apply as well to masonry construction assuming a 50 per cent efficiency of frame calking. ' *A $-in. crack and clearance represent a poorly fitted window, much poorer than average. -' - ` fWindows tested in place in building. . - ` .. , ^Industrial pivoted window generally used in industrial buildings. Ventilators horizontally pivoted at center or slightly above, lower part swinging out. '. hArchitecturally projected made of same sections as industrial pivoted except that outside framing member is heavier, and it has refinements in weathering and hardware. Used in semi-monumental buildings such as schools. Ventilators swing in or out and are balanced on side arms. J6-in. crack is obtainable in the best practice of manufacture and installation, 36-in- crack considered to represent average practice. - - ' >Of same design and section shapes as so-called heavy section casement but of lighter weight. !-in. crack .is obtainable in the best practice of manufacture and installation, &-tn. crack considered to represent average, practice. - ". . ' ' J Made of heavy sections. Ventilators swing in or out and stay set at any degree of opening. J^-in. crack is obtainable in the best practice of manufacture and installation, J6-in. crack considered to represent average practice. -. .. kvvith reasonable care in installation, leakage at contacts where windows are attached to steel-frame work and at mullions is negligible. With 36-in. crack, representing poor installation, leakage'at contact with steel framework is about one-third, and at mullions about one-sixth of that given for industrial pivoted Endows in' the table.' ' ' Air Leakage 171 generally decreases its leakage,, but in some cases may push the meeting, rail members apart and increase, the leakage. On windows with large clearances, locking will usually reduce the leakage. '. Wood casement windows may be assumed to have the same unit leakage as for the average double-hung wood window when properly fitted. Locking, a normal operation in the closing of this type of window, maintains the crack at a low value. For metal pivoted sash, the length of crack is the total perimeter of the movable or ventilating sections. Frame leakage on steel windows may be neglected when they are properly grouted with cement mortar into brick work or concrete. When they are not properly sealed, the linear feet of sash section in contact with steel work at mullions should be figured at 25 per cent of the values for industrial pivoted windows as given in Table 2. .. . . , When storm sash are applied to well fitted windows, very' little re duction in infiltration is secured, but the application of the sash does give an air space which reduces the heat transmission and helps prevent the. frosting of the windows3. By applying storm sash to poorly fitted windows, a reduction in leakage of 50 per cent may be obtained, the effect so far as air leakage is concerned being roughly equivalent to that obtained by the installation of weatherstrips. . Door Leakage . ' . Doors vary greatly in fit because of their large size and tendency to warp. For a well fitted door, the leakage values for a poorly fitted double- hung wood window may be used. If poorly fitted, twice this figure should be used. If weatherstripped, the values may be reduced one-half. A single door which is frequently opened, such as might be found in a store, should have a value applied which is three times that for a well fitted door. This extra allowance is for opening and closing losses and is kept from being greater, by the fact that doors are not used ;as much in the coldest and windiest weather. , .. ` The infiltration rate through swinging and revolving doors is generally a matter of judgment by the engineer making cooling load determinations and in the absence of adequate research data the values given in Table 3 represent current engineering practice4. These values are based on the average number of persons in a room at a specified time, which may alsol Table 3. Infiltration Through Outside Doors for Cooling Loads3 Expressed in Cubic Feet per Minute per Person Entering Room ' Application 1 Pair 36 in. Swinging Doors, Single Entrance1* Application Pair 36 in. Swinging Doors, Single Entrance!* Bank Barber Shop____ :_________ Broker's Office____________ Candy and Soda__ _____ Department Store..... .......... Dress Shop Drug Store Furrier 7.5 4.5 7.0 6.0 8.0 , 2.5 7.0 2.5 Lunch Room. ............... Men's Shop........ ................... ' Office............______ ............... Office Building_________ ..... 35 5.0 3.5 3.0 2.0 2.5 25 ' 35 For doors located in only one wall or where doors, in other walls are of revolving type. . bVestibules with -double pair swinging doors; infiltration may be assumed 75 per cent of swinging door values. , . Infiltration for 72 in. revolving doors may be assumed 60 per cent of swinging door values. *- 172 CHAPTER 8 1946 Guide be the same occupancy assumed for determining the outside ventilation requirements outlined in Chapters 12 and 15. Air Change Method . The amount of air leakage is sometimes roughly estimated by assuming a certain number of air changes per hour for each room, the number of changes assumed being dependent upon the type, use and location of the room, as indicated in Table 4. This method may be used to advantage as a check on the calculations made in the more exact manner. On the other hand, where it is not possible' to determine or pre-determine with accuracy the width of crack or clearance of windows, or where other sources of air leakage cannot readily be evaluated, as is often the case, the use of the air change method may be justified. The values in Table 4 may be used with reasonable accuracy for resi dences and are the requirements for each room. The total infiltration allowance for the entire building should be one-half the sum of the infiltration allowances of the individual rooms, since whatever air enters on the windward side generally leaves the building on the leeward side and the infiltration'requirements therefore do not exist simultaneously on all sides or in all rooms. An allowance of one air change per hour for all sources of air leakage for the entire volume may be considered average for a well constructed residence. The air leakage for vestibules due to opening and closing of doors is sometimes based on the air change method, even though the air leakage estimates for other rooms are based on the crack method. Except for vestibules and reception halls, it is not advisable to attempt to apply the air change method to factories and industrial and commercial buildings because of wide variations in the type and percentage of fenestration which is the principal source of air leakage in such buildings. . INFILTRATION DUE TO TEMPERATURE DIFFERENCE The air exchange due to temperature difference, inside to outside, is a chimney effect, causing air to enter through openings at lower levels and to leave at higher levels 5. Although it is not appreciable in low buildings, this loss should be considered in tall, single story buildings with openings near the ground level and near the ceiling. Also in tall, multi-story buildings it may be a considerable item unless the sealing between various floors and rooms is quite perfect. In tall buildings, temperature difference or chimney effect will produce a head that will add to the effect of the wind at lower levels and subtract from it at higher levels. On the other hand, the wind velocity at lower Table 4.' Air Changes Taking Place under Average Conditions Exclusive of Air Provided for Ventilation3 Kind of Room or Building Number of Air Changes taking Place per Hour Kind of Room or Building Number of Air Changes taking Place per Hour Rooms, 1 side exposed____ i Rooms with no windows Rooms, 2 sides exposed...... l'A or outside doors_________ M toH Rooms, 3 sides exposed...... 2 Entrance Halls......... ............ 2 to 3 Rooms, 4 sides exnosed...... 2 Reception Halls................... 2 . 2. Stores. ............................... 1 to 3 "For rooms with weatherstripped windows or storm sash, use H these values, where applicable. Air Leakage 173 levels may be somewhat abated by surrounding obstructions, Further more, the chimney effect is reduced in multi-story buildings by the partial isolation of floors, the'reby preventing free upward movement, so that wind and temperature difference may seldom cooperate to the fullest extent. Making the rough assumption that the neutral zone8 is located at mid-height of a building, and that the temperature difference is 70 F, Equations 1 and 2 may be used to determine an equivalent wind velocity to be used in connection with Tables 1 and 2 that will allow for both wind velocity and temperature difference: . Ve = VV5 - 1.75o (1) where Ke =. VV5 + 1.75 b . (2) Ve = equivalent wind velocity to be used in conjunction with Tables 1 and 2. V = wind velocity upon which infiltration would be determined if tern* perature difference were disregarded. . .. a -- distance of windows under consideration from mid-height of building if above mid-height, feet. b = distance if below mid-height, feet. , The coefficient 1.75 allows for about one-half the temperature difference head. For buildings of unusual height, Equation 1 would indicate negative infiltration at the highest stories, which'condition may, at times, actually exist. . Sealing of Vertical Openings In tall, multi-story buildings, every effort should be made to seal off vertical openings such as stair-wells and elevator' shafts from the re- . mainder of the building. Stair-wells shou|d be equipped with self-closing doors, and, in exceptionally high buildings, should be closed off into sections of not over 10 floors each. Plaster cracks should be filled. Elevator enclosures should be tight and solid doors should be used. If the sealing of the vertical openings-is made effective, no allowance, need be made for the chimney effect. Instead, the greater wind move ment at the greater heights makes it advisable to install additional heating surface on the upper floors above the level of neighboring buildings, this additional surface being increased as the height is increased. One arbitrary rule is to increase the heating surface on floors above neighboring buildings by an amount ranging from 5 per cent to 20 per cent. This extra heating surface is required only on the windward side and on windy days, and hence automatic temperature control is especially desirable with such installations. In stair-wells that are open through many floor levels although closed off from the remainder of each floor by doors and partitions; the strati.fication of air makes it advisable to increase the amount of heating surface at the lower levels and to decrease the amount at higher levels. One rule is to calculate the heating surface of the entire stair-well in the usual way' and' to place 50 per cent of this in the bottom third, the normal amount in the middle third and the balance in the top third. Infiltration and Air for Combustion . Infiltration in residences normally supplies the air required for com bustion by fuel burning appliances, but in some residences weather- 17.4 CHAPTER 8 -1946 .Guide stripping, sealing and caulking may reduce infiltration to the point that special openings must be provided to supply, adequate air to the heating appliances. - ' REFERENCES *--A.S.H.V.E. Research Reports No. 786--Infiltration Through Plastered and Unplastered Brick Walls, by F.C. Hougbten and Margaret.Ingels (A.S.H.V.E. Transactions, Vol. 33. 1927. p. 377). No. 826--Air Infiltration Through Various Types of' Brick Wall Construction, by G. L. Larson, D. W. Nelson and C. Braatz (A.S.H.V.E. Transactions, Vol. 35, 1929. p. 183). No. 851--Air Infiltration Through Various Types of Wood Frame Construction, by G. L. Larson. D. W. Nelson and C. Braatz (A.S.H.V.E. Transactions, Vol. 36, 1930, p. 99). ' . . ' A.S.H.V.E. Research Reports No. 686--Air Leakage, by F. C. Houghten and C. C. Schrader (A.S.H.V.E. Transactions/Vol. 30, 1924, p. 105). No. 704--Air Leakage Around Window Openings, by. C. C. Schrader (A.S.H.V.E. Transactions, Vol. 30.' 1924, p. 313). No. 803--Air Leakage on Metal Win . dows in a Modern Office Building, by F. C. Houghten and M.' E. O'Connell (A.S.H.V.E. Transactions. Vol. 34, 1928. p. 321). No. 815---Air Leakage Through a Pivoted Metal Window, by F. C. Houghten and M. E". O'Connell (A.S.H.V.E. Transactions, Vol. 34,1928, p. 519). No. 817--Effect of Frame Calking and Storm Sash on Infiltration Around and ThroughWindows, by W. M. Richtmann and C. Braatz (A.S.H.V.E. Transactions, Vol. 34, 1938, p. 547). No. 909--Air Infiltration Through Double-Hung Wood Windows, by G. L. Larson. D. W. Nelson and R. W. Kubasta (A.S.H.V.E. Transactions. Vol. 37, 1931,-p. 571). The Weathertightness of Rolled Section Steel Windows, by J. E. Emswiler and W. C. Randall (A.S.H.V.E. Transactions, Vol. 34, 1928, p. 527). Pressure Differences Across Windows in Relation to Wind Velocity, by J. E. Emswiler and W. C. Randall (A.S.H.V.E. Transactions,-Vol. 36,1930, p. 83). Air Infiltration Through Steel Framed Windows, by D. O. Rusk, V. H. Cherry and L. Boelter (A.S.H.V.E. Transactions. Vol. 39, 1933, p. 169). . ., , s--Fuel Saving Resulting from the Use of Storm Windows and Doors, by A. P. Kratz and S. Konzo (A.S.H.V.E. Transactions, VoL 42. 1936, p. 87).` The Infiltration Problem of Multiple Entrances, by A. M. Simpson'and K. B. Atkinson (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning, June. 1936. p. 345). Infiltration Characteristics of Entrance Doors, by A. M. Simpson {Refrigerating Engineering, June, 1936). '% *--A.S.H.V.E. Research Reports No. 994--Wind Velocities Near a Building and Their Effect on Heat Loss, by F. C. Houghten, J. L. Blacksha'w and'Carl Gutberlet (A.S.H.V.E. Transactions, Vol. 40, 1934, p. 387). No. 1069--Heating Requirements of an Office Building as Influenced by the Stack Effect, by F. C. Houghten and Carl Gutberlet (A.S.H.V.E.-Transactions, VoL 43, 1937, p.437). Flue Action in High Buildings, by H. L. Alt (A.S.H.V.E. Journal Section. Healing. Piping and Air Conditioning, May, 1932. p. 376). Influence of Stack Effect on the Heat Loss In Tall Buildings, by Axel Marin (A.S.H.V.E. Transactions, VoL 40,1934, p. 377). - '/ ' '. ' * ^"Neutral Zone In Ventilation, by J. E. Emswiler (A.S.H.V.E. Transactions, VoL 32, 1926, p. 59). ". [ CHAPTER 9 Ifjaturai `Uentiia.tion Wind Forces, Temperature Different Forces, Heat Removal, Openings, Windows,. Doors, Skylights, Roof Ventilators, Stacks, Principles of Control, General Rules, Dairy Barn Ventilation, Garage Ventilation - VENTILATION by natural forces finds application in industrial plants, public buildings, schools, dwellings, garages, and in farm buildings. . The natural forces available for moving air into,, through and out of buildings are: (a) wind forces, and (b) the difference in temperature between the air inside and outside a building. The air movement may be caused by either of these forces acting alone or by a combination of the two, depending upon atmospheric conditions, building design and loca tion. The ventilating results obtained will vary, from time to time, due to variation in the velocity and direction of the wind and the temperature difference. The arrangement, location, and control of the ventilating openings should be' such that the two forces act cooperatively rather . than in opposition. , .. ' WIND FORCES In considering the use of natural wind forces'.for producing ventilation, account must be taken of:.(l) average wind velocity, (2) prevailing wind direction, (3) seasonal and daily variations in velocity and direction, and (4) local wind interference by nearby buildings, hills or other obstructions of similar nature. Values are given in Table 2, Chapter 15 for the average summer wind velocities and the prevailing wind directions in various localities through out the United States, while Table 1, Chapter 14, lists similar values for the winter. . In almost all localities the summer wind velocities are lower than those in the winter, and in about two-thirds-of the localities the prevailing direction is different during the summer and winter. While the tables give no. average velocities below 5 mph, there will be times when the velocity is lower, even in localities where the seasonal average is con siderably above 5 mph. There are relatively few places where the velocity . faffs .below one half of the average for :many hours per month. Con^ sequently, if the natural ventilating system is designed for wind velocities of one-half of the average seasonal velocity, it should prove satisfactory in almost every case. .. . Equation 1 may be used for calculating the quantity of air forced through ventilation openings by the wind, or for determining the proper size of such openings to produce given results: where Q = EAV .. . (1) Q = air flow, cubic feet per minute. .. A -- free area of inlet openings, square feet. . ' - . . V = wind velocity, feet per minute, miles per hour X 88. - E = effectiveness of openings. {E should be taken at 0.50 to 0.60 for.perpendicular winds and 0.25 to 0.35 for diagonal winds1.) The accuracy of the results obtained by the use of .Equation 1 depends upon the placing of the openings, as the formula assumes that ventilating ' t 175 '' 176 CHAPTER 9 1946 Guide openings have a flow coefficient slightly greater than that of a squareedged orifice. If the openings are not advantageously placed with respect to the wind, the flow per unit area of the openings will be less and, if unusually well placed, the flow will be slightly more than that given by the formula. Inlets should be placed to face directly into' the prevailing wind, while outlets should be placed in one of the five places listed: 1. On the side of the building directly opposite the direction of the prevailing wind. 2. On the roof in the low pressure area caused by the jump of the wind (see Fig. 1). Natural Ventilation 177 where ;, - Q = air flow, cubic feet per minute. A = free area of inlets or outlets (assumed equal), square feet. . h = height from inlets to outlets, feet. , ' t = average temperature of indoor air in height h, Fahrenheit degrees. to = temperature of outdoor air, Fahrenheit degrees. 9.4 = constant of proportionality, including a value of 65 per cent for effectiveness of openings. This should be reduced to 50 per cent (constant = 7.2) if conditions are not favorable. ` HEAT REMOVAL . . In problems of heat removal, knowing the amount of heat to be re moved and having selected a desirable temperature difference, the amount Fig. 1. The Jump of Wind from Windward Face of Building. (A--Length of Suction Area; B--Point of Maximum Intensity of Suction; ' C--Point of Maximum Pressure) . 3. On the sides adjacent to the windward face where low pressure areas occur. 4. In a monitor on the side opposite from the wind. . 5. In roof ventilators or stacks. . " .. TEMPERATURE DIFFERENCE FORCES* The stack effect produced within a building when the outdoor tempera ture is lower than the indoor temperature is due-to the difference in weight . of the warm column of air within the building and cooler air outside. . The flow due to stack effect is proportional to the square root of'the - draft head, or approximately: " < ;. Q = 9.4 A y h (l - to) (2) Fig. 2. Increase in Flow Caused by Excess of One Opening Over Another of air to be passed through the building per minute to maintain this tem perature difference can be determined by means of Equation 3. where !? .= 0.0175 0 ((-lo) , . H = heat removed, Btu per minute. ' Q -- air flow, cubic feet per minute. . l--to= inside-outside temperature difference, Fahrenheit degrees. (3) . EFFECT OF UNEQUAL OPENINGS The largest flow per unit area of openings is obtained when inlets and outlets are equal, and the equations given previously are based on this condition. Increasing outlets over inlets, or. vice-versa, will increase the air flow, but not in proportion to the added area. When solving problems having an unequal distribution of openings, use' the smaller area, either inlet or outlet, in the equations and add the increase as determined' from Fig. 2. . .. . COMBINED FORCES OF WIND AND TEMPEM.TURE ,, . . . Equations for determining-the. air flow due to temperature; difference and wind have already been given. It must be remembered that when 178 CHAPTER 9 ; 1946.Gu.idc both forces are acting together, even without interference, the resulting air flow is not equal to the sum of the . two estimated quantities. The flow through any opening is proportional to the square root of-, the sum . of the heads acting on that opening. - - . ' . When the. two heads are about equal in value and the ventilating openings are operated so as to coordinate them, the total air flow through . 'the building is about 10 per cent greater than that produced by either head acting independently under conditions ideal to it. This percentage . decreases rapidly , as one head increases over the other and the larger will predominate. . The wind velocity and , direction, the outdoor temperature, or the indoor distribution, cannot be predicted with certainty, and refinehient in calculations is not justified ^consequently, a simplified method can be used. This may be done by using the equations and calculating the-flows . produced by each force separately under \conditions of openings best suited for coordination of the forces. Then, by-determining, as a ,per- centage, the ratio of the flow produced by temperature difference to the sum of the two flows,' the actual'flow'due to the combined forces can be approximated.from Fig. 3. . . . ; .. - Example-1. .Assume a drop forge shop, 200 ft long,-100 ft wide,.and,30 [thigh. The cubical content is 600,000 cu ft, and the height of the air outlet _oyer;that of the inlet is 30 ft.: Oil fuel of 18,000 Btu per, pound is used in this shop at the rate of, 15 gal per:Hour (7.75 lb'per "gal). , Desired summer temperature difference is 10 deg and the prevailing wind1 is 8 mph perpendicular to the'long'dimension'. '-What is the necessary area for the inlets'and outiets, and what is the rate of'air flow, through the building? ; i''v.i. Join- Solution for Temperature Difference Only, ' 34,;875 Btu per minute. ' = 15 X 7.75 X 13,000"" The heat II V ` - .V!^ ' "'5By Equation 3, the air flow required to remove this heat with!an'av<irage'temperature ' difference of lO deg is: - : t-rr;;.'!..': ncrv, bn/J Natural Ventilation. 179 ,,_ H V 0.0175 (1 - h) 34,875 0.0175 X 10 199,286 cfm. This is equal to about 20 air changes per hour. From Equation 2 the inlet (or outlet) opening area should be: '- ' 9.4 ^ A (t - to) 199,286 9.4 ^30 X 10 1224 sq ft. The flow per square foot of inlet or outlet would be 199,286 -5- 1224 = 163 cfm with all windows open. . Solution for Wind Only. With 1,224 sq ft. of inlet openings distributed around the sidewalls, there would be about 410 sq ft m each long side and 202 sq ft in each end. The outlet area will be equally distributed-on the two sfdes of the monitor, or 612 sq ft on each side. With the wind perpendicular to the long side, there will be 410 sq ft of opening in its path for inflow and 612 in the lee side of the monitor for outflow with the windward side closed. The air flow, as calculated by Equation 1', will be: Q = 0.60 X 410 X 704 = 173,200 cfm. . This gives 17.3 air changes per, hour, which should be more than ample when there is no heat to be removed. Solution for Combined Heads. Since the windward side of the monitor is closed when the wind is blowing, the flow due to temperature difference must be calculated for this condition, using Fig. 2. This chart shows that when inlets are twice the size of the outlets, in this case 1,224 sq ft in the sidewalls and 612 sq ft in the monitor, the flow will be increased 26.5 per cent over that produced by equal openings. Using the smaller opening and the flow per square foot obtained previously, the calculated amount for this condition will be: ' ^ . 612 X 163 X 1.265 =. 126,200 cfm. / . Adding the two computed flows: . . Temperature Difference = 126,200 = 42 per cent. . Wind ' . = 173,200 = 58 per cent. - Total - 299,400 = 100 per cent. From Fig. 3, it is determined that when the flow, due to temperature difference, is 42 per cent of the total, the actual flow, dire.to the combined forces, will be about 1.6 times that calculated for temperature difference alone, or 201,920 cfm. , The original flow, due to temperature difference alone, was 199,286 cfm with all openings in use. The effect of the wind is to increase this to 201,920 cfm even though half of the outlets are closed. V . A factor of judgment is. necessary in the location of the openings in a' building, especially those in the roof, where heat, smoke and fumes are to be removed. Usually windward monitor openings, should be closed, but if the wind is low enough for the temperature head to overcome it, all windows may be opened. ' . TYPES OF OPENINGS Types of openings may be classified as: (1) windows, doors, monitor openings and skylights, (2) roof, ventilators, (3) stacks connecting to registers, and (4) specially designed inlet or outlet openings: . Windows, Doors and Skylights . Windows have the advantage of transmitting light, as well as providing . Ventilating area when open. Their movable parts are arranged'to open ' in various^ ways; they may open by sliding either vertically or horizon- ' tally, by tilting on horizontal pivots at or near the center, or by swinging on pivots at the top, bottom or side. Regardless of their design, the air flow per square foot of opening-may be considered to be the same under the same conditions. The type of pivoting should receive consideration 180 CHAPTER 9 1946 Guide from the standpoint of weather protection, and certain types may be advantageous in controlling the distribution of incoming air. Deflectors are sometimes used for the same purpose, and these devices should be considered a part of the ventilation system. . Roof Ventilators The function of a roof ventilator is to provide a storm and weather proof air outlet. These are actuated by the same forces of wind and temperature head, which create flow through other types of openings. The capacity of a ventilator depends upon four things: (1) its location on the roof, (2) the resistance it and the duct work offers to air flow, (3) the height of draft, and (4) the efficiency of the ventilator in utilizing the kinetic energy of the wind for inducing flow by centrifugal or ejector . action. For maximum flow induction, a ventilator should be located on that part of the roof where it will receive the full wind without interference. If ventilators are installed within the suction region created by the wind passing over the building, or in a light court, or on a low building between two high buildings, their performance will be seriously influenced. Their normal ejector action, if any, may be completely lost. The base of the ventilator should be-of a taper-cone design to produce, the effect of a bell-mouth nozzle whose coefficient of flow is considerably higher than that of a square-entrance orifice. If a grille is provided at the base or if the base or structural members present obstructions, additional resistance is introduced, and the base opening should be increased in size accordingly. Air inlet openings located at lower levels in the building should be at least equal to, and preferably larger than the combined throat areas of all roof ventilators. The air discharged by a roof ventilator depends on wind velocity and temperature difference, and, in general, their per formance will be the same as any monitor opening located in the same place, but due to the four capacity factors already mentioned, no simple formula can be devised for expressing ventilator capacity. . Roof ventilators may be classified as stationary, pivoting or oscillating, and rotating. Generally, these have a found throat, but the continuousridge ventilator, or so-called heat valve, would fall in. the stationary classification, When selecting roof ventilators, some attention should be given to ruggedness of construction, storm proofing features, dampers and damper operating mechanisms, possibility of noise, original' cost and maintenance. \ '. Natural ventilation units may be used to supplement power-driven supply fans, and under favorable weather conditions it may be possible to stop the power-driven units. Units are not subject to code tests for ratings. Generally they must be selected from manufacturers' tables. It is, therefore, very important to consider the reliability of the ratings used. Controls , Gravity ventilators may have dampers controlled.by hand, thermostat, or wind velocity, in combination with a fan. The thermostat station may be located anywhere in the building, or it may be located within the ventilator itself. The purpose of wind velocity control is to obtain a definite volume of exhaust regardless of the natural forces, the fan motor being: energized when the natural exhaust capacity falls below a certain minimum, and again shut off when the wind velocity rises to the point where this minimum, volume can be supplied by natural forces. Natural Ventilation 181 Stacks Stacks or vertical flues are really chimneys which function through the effects, of the wind and temperature difference. Like the roof venti lator, the stack outlet should be located so that the wind may act upon it from any direction. With little, or no wind, the chimney effect de pends entirely on temperature difference to produce a removal of air from the rooms where the inlet openings are located. GENERAL RULES A few of the important requirements in addition to those already outlined are: ' 1. Inlet openings in the building should be well distributed, and should be located on the windward side near the bottom, while outlet openings are located on the leeward side near the top. Outside air will then be supplied to the zone to be ventilated. 2. Inlet openings should not be obstructed by buildings, trees, sign boards, etc.-, outside nor by partitions inside. 3. Greatest flow per square foot of total opening is obtained by using inlet and outlet openings of nearly equal areas. 4. In the design of window ventilated buildings, where the direction of the wind is quite constant and dependable, the orientation of the building together with amount and grouping of ventilation openings can be readily arranged to take full advantage of the force of the wind. Where the wind's direction is quite variable, the openings should be arranged in sidewalls and monitors so that, as far as possible, there will be approxi mately equal areas on all sides. Thus, no matter what the wind's direction, there will always be some openings directly exposed to the pressure force and others to a suction force, and effective movement through the building will be assured. 5. Direct short circuits between openings on two sides at a high level may clear the air at that level without producing any appreciable ventilation at the level of occupancy. 6. In order that temperature difference may produce a motive force, there must be vertical.distance between openings. That is, if there are a number of openings available in a building, but all are at the same level, there will be no motive head produced by temperature difference, no matter how great that difference might be. 7. In order .that the force of temperature difference may operate to maximum ad vantage, the vertical distance between inlet and outlet openings should be as great as possible. Openings in the vicinity of the neutral zone are less effective for ventilation. 8. In the use of monitors, windows on the windward side should usually be kept closed, since, if they are open, the inflow tendency of the wind counteracts the outflow tendency of temperature difference. Openings on the leeward side of the monitor result in cooperation of wind and temperature difference. 9. In an industrial building where furnaces that give off heat and fumes are to be installed, it is better to locate them in the end of the building exposed to the prevailing wind. The strong suction effect of the wind at the roof near the windward end will then cooperate with temperature difference, to provide for the most active and satisfactory removal of the heat and gas laden air. 10. In case it is impossible to locate furnaces in the windward end, that part of the building in which they are to be located should be built higher than the rest, so that the wind, in splashing therefrom will create a suction. The additional height also increases the effect of temperature difference to cooperate with the wind. 11. The intensity of suction or the vacuum produced by the jump of the wind is greatest just back of the building face. The area of suction does not vary with the wind velocity, but the flow due to suction is directly proportional to wind velocity. 12. Openings much larger than the calculated areas are sometimes desirable, especially when changes in occupancy-are possible, or to provide for extremely hot days. In the former case, free openings should be located at the level of occupancy for psychological reasons. 13. In single story industrial buildings, particularly those covering large areas, natural ventilation must be accomplished by taking air in and out of the roof openings. Openings in the pressure zones can be used for inflow and openings in the suction zone, or openings in zones of less pressure, can be used for outflow. The ventilation is accomplished by the ;manipulation of openings to get air flow through the zones to be ventilated. 182 CHAPTER 9 1946 Guide DAIRY BARN VENTILATION8 A successful barn ventilating system is one which continuously supplies the proper amount of air required by the stock, with proper distribution . and without drafts, and one which removes the excessive heat, moisture, and odors, and maintains the air at a proper temperature, relative humidity, and degree of cleanliness. Bam temperatures below freezing and above 80 F affect milk produc tion. Milk producing stock should be kept in a bam temperature be tween 45 and 50 F. Dry stock, at reduced feeding, may be kept in a bam . 5 to' 10 deg higher. Calf bams are generally kept at 60 F, while hospital and maternity bams usually have a temperature of 60 F or somewhat higher. The heat produced, by a cow of an average weight of 1000 lb may be taken as 3000 Btu per hour. The. average rate of moisture production by a cow giving 20 lb of milk per day is 15 lb of water per day, or 4375 grains per hour. To set a standard of permissible relative humidity for cow barns is difficult. For 45 F an average relative humidity of 80 per cent is satisfactory, with 85 per cent as a fimit. : Where the barn volume and construction permit adequate heating by the stabled animals, the air supply need not be heated. The air should be supplied through or near the ceiling. It is better to have-the exhaust * openings near the floor as larger volumes of warm air are then held in the bam and there is better temperature control with less likelihood of sudden, change in bam temperature. . If a cow weighs 1000 lb and produces 3000 Btu of heat per hour, and if a bam for the cow has' 600 cu ft of air space with 130 sq ft of building exposure, one cow will require 2600 to 3550 cu ft per hour of ventilation, depending on the temperature zone in which the barn is located. The permissible heat losses through the structure, based on one cow and depending on the temperature zone, vary between 0.043 and. 0.066 Btu. per (hour) (cubic foot of barn space), and 0.197 to 0.305 Btu per (hour) (square foot of barn exposure). .. GARAGE VENTILATION On account of the hazards resulting from carbon monoxide and other - physiologically harmful or combustible gases or vapors in garages, the' importance of proper' ventilation of these buildings cannot be over emphasized: During the warm months of the year,, garages are usually ventilated adequately because the doors and windows are kept open. As cold weather sets in, more and more of the ventilation openings are closed , and consequently on extremely cold days the carbon monoxide concentra tion runs high. . ' Many garages can be satisfactorily ventilated by natural means par ticularly during the mild weather when doors, and windows.can be kept . open. However, the A.S.H.V.E. Code of Minimum Requirements for Heating and Ventilating Garages, adopted in 1935, states that natural ventilation may be employed for the ventilation of storage sections where ' it is practical to maintain open windows or other openings at all times. . The code specifies that such openings shall be distributed as uniformly as possible in at least two outside walls, and that.the total area of such, '.openings shall be equivalent to at least 5 per cent of the floor area. The . code further states that where it is impractical to operate such a system of natural ventilation, a mechanical system shall be used which shall Natural Ventilation_________ '_________ /_______ ______ - '. 8. provide for either the supply of 1 cu ft of air per minute from out-of-doors for each square foot of floor area, or for removing the same amount and discharging it to the outside as a means of flushing-the garage4:- . Research .. Research on garage ventilation, undertaken by the A.S.H.V.E. Com mittee on Research at Washington University, St. Louis, Mo., and at the University of Kansas, Lawrence, Kans., in cooperation with, the A.S.H.V.E. Research Laboratory, and at the A.S.H.V.E. Research Laboratory, has resulted in authoritative papers on the subject. Some of the conclusions from work at the Laboratory are listed in the following statements: . , 1. Upward ventilation results in a lower concentration of carbon monoxide at the breathing line and a lower temperature above the breathing line than does downward ventilation, for the same rate of carbon monoxide production; air change and the same' temperature at the 30-in. level. , .. 2. A lower rate of air change and a smaller heating load are required with upward' than with downward ventilation. ; .` . . ... 3. In the average case upward ventilation results in a lower concentration of carbon monoxide in the occupied portion of a garage than is had with complete mixing of the exhaust gases and the air supplied. However, the variations in concentration from point to point, together with the possible failure of the advantages of upward ventilation to accrue, suggest the basing of garage ventilation on complete mixing arid an air change sufficient to dilute the exhaust gases to the allowable concentration of carbon monoxide. 4. The rate of carbon monoxide production by an idling car is shown to vary from 25 to 50 cu ft per hour, with an average rate of 35 cu ft per hour. 5. An air change of 350,000 cu ft per hour per idling car is required to keep the carbon monoxide concentration down to one part in 10,000 parts of air. -' . REFERENCES . 1--Predetermining Airation of Industrial Buildings, by W. C. Randall and E. W.' Conover (A.S.H.V^E.' Transactions, VoL 37, 1931, p. 605). '' . .. . 2--Neutral Zone in Ventilation, by J. E. Emswiler (A.S.H.V.E. Transactions, VoL 32,1926, p. 59). ' 3--Dairy Barn Ventilation, by F. L. Fairbanks (A.S.H.V.E. Transactions. Vol. 34.1928, p. 181). Cow: Bam Ventilation, by Alfred J. Offner (A.S.H.V.E. Transactions, Vol. 39, 1933, p. 149). For additional information on this subject refer to Technical Bulletin, U. 'S. Department of Agriculture (1930), by M. A.` R.'Kelley: Also see Air Conditioning of Farm Buildings, by F; L. Fairbanks (Agricultural Engineering* November, 1937, p. 485). `_ t. ^ 4_Code of Minimum Requirements for Heating and .Ventilating Garages (A.S.H-.V.E.' Transactions," Vol. 41, 1935, p. 30). Airation Study of Garages by W. C. Randall and L. W. Leonhard (A.S.H.V.E. Transactions. Vol. 36. 1930, p. 233). .... , .... A.S.H.V.E. Research Report No. 874^--Carbon Monoxide Concentration'in Garages, by A. S. Langs-- dorf and R. R. Tucker (A.S.H.V.E. Transactions, Vol. 36, 1930, p. 511). ' A.S.H.V.E. Research.Report No. 935--Carbon Monoxide Distribution in Relation to the Ventilation of an Underground Ramp Garage, by F. C. Houghten and Paul McDermott (A.S.H.V.E. Transactions, Vol. 38, 1932. p. 439). * .- , A.S.H.V.E. Research Report No. 934--Carbon Monoxide Distribution in Relation to the Ventilation of a One-Floor Garage, by F. C. Houghten and Paul McDermott (A.S.H.V.E. Transactions, Vol. 38.1932. p. 424).. ... , . A.S.H.V.E. Research Report No. 967--Carbon Monoxide Distribution in Relation to the-Heating, and Ventilation of a One-Floor Garage,- by F. C. Houghten and Paul McDermott (A.S.H.V.E. Trans-' actions, Vol. 39, 1933, p. 395). : ' Carbon Monoxide Surveys of Two Garages, by A. H. Sluss, E. K. Campbell and Louis M. Farber (A.S.H.V.E. Transactions, Vol. 40, 1934, p. 263). . CHAPTER 10 _y^tV (Contaminants Classification of Air Contaminants; Sizes of Airborne Particles; Air Pollution by S/noice, Ash and Cinders; Smoke Abatement; Odor Nuisance; Maximum Allowable Concentrations of Indus trial Air Contaminants; Flammable Gases and Vapors; Com bustible Dusts; Atmospheric Pollen; Airborne Bacteria THE . normal constituents of the. earth's atmosphere are oxygen, nitrogen, carbon dioxide, water vapor, argon, small or negligible amounts of other inert gases, hydrogen, variable traces of ozone, and small quantities of microscopic and submicroscopic solid matter, sometimes caljed permanent atmospheric impurities. From the viewpoint of the air conditioning engineer, all other airborne substances may be termed con taminants. This term is applied preferably, however, to undesirable or chance impurities, since the occasion may arise for adding to the air controlled amounts of. substances such as: solid or gaseous diluents for the prevention of explosions; germicidal mists or aerosols for bacteria control; masking substances for odor control; or a substitute for one of the normal gases, as is the case when helium is used to replace nitrogen in atmospheres for compressed air workers or divers. . The control of air quality is one of the functions of complete air con ditioning, and some knowledge of the composition, concentration and properties of air contaminants under various circumstances is therefore essential. Air contaminants arise from the normal processes of wear, erosion, windstorm, sea-spray evaporation, thermal disintegration, earthquake, volcanic eruption, combustion, manufacturing, transportation, agricul ture, and the biochemical or biological processes of life. They are classi fied at various times as organic and inorganic, visible or invisible, micro scopic or macroscopic, particulate or gaseous, toxic or harmless, beneficial or destructive. The following classification is based chiefly upon the origin or method of formation of air contaminants, using distinctions that are necessarily arbitrary iii some cases. CXASSIFICATION OF AIR CONTAMINANTS Dusts, Fumes, and Smokes are known as solid particulate air contami nants. ' . Dusts are solid particles projected into the air by natural forces, such as wind, volcanic eruption or earthquake, and by mechanical or man-made processes, such as crushing, grinding, milling, drilling, demolition, shovelling, conveying, screening, bagging and sweeping. Some of these forces produce dust from iarger masses, while the others simply . disperse materials that are already in dust or pulverized form. Generally particles are not called dust unless they are smaller than about 100 microns in size. Dusts may be of' mineral type, such as rock, ore, metal, sand; vegetable, such as grain, flour, wood, cotton, pollen; or animal, such as wool, hair, silk, feathers, leather. . Fumes are solid particles commonly formed by the condensation of vapors of solid materials and may usually be found above molten metals in industrial environments. Metallic fumes generally occur as the oxides in air because of the highly reactive nature of finely divided matter. Fumes may also be formed by sublimation, distillation, calcination, or chemical reaction, whenever such processes create airborne particles predominately below the 1 micron size. Fumes permitted to age tend to flocculate into clumps or. aggregates of much larger size and this tendency may facilitate their removal * 'from air under controlled conditions. . J 84 Air Contaminants 185 Smokes are the extremely small solid particles produced by incomplete combustion of organic substances such as tobacco, wood, coal, oil, tar and other carbonaceous materials. The term smoke is commonly applied to the mixture of solid, liquid and gaseous products of combustion, although the technical literature prefers to distinguish between such component's as soot or carbon particles, fly-ash, cinders, tarry matter, unburned gases, and gaseous combustion products. The finest particulate constituents are characteristically much less than 1 micron in size, often in the range of 0.1 to 0.3 micron. Mists and Fogs are known as liquid particulate air contaminants. Mists are very small airborne droplets of materials that are ordinarily liquid at normal temperatures and pressures. They may be formed by atomizing, spraying, splashing, mixing, violent chemical reaction, electrolytic evolution of gas from a liquid, or escape of a dissolved gas upon release of pressure. The very small droplets expelled or atomized into the air by sneezing constitute mists containing microorganisms thdt become air' contaminants. ' Fogs are limited by some classifications to airborne droplets formed by condensation from the vapor state. This arbitrary distinction between mist and fog is of' minor importance, as both terms are used to indicate the particulate state of airborne liquids (occasionally termed aerosols). Fog nozzles are so named because of their ability to produce extra fine droplets as compared to the mist from ordinary spray devices. The highly volatile nature of some liquids quickly reduces their airborne droplets from the mist to the fog range, and eventually to the vapor phase until the air becomes saturated, with that liquid. Many droplets in fogs or clouds are microscopic and submicroscopic in size, and may be conceived as the transition state between the larger mists and the vapors. . Vapors and Gases are known as gaseous non-particulate air contami nants. ' Vapors are the gaseous phase of substances that are either liquid or solid in their commonly known state, examples being gasoline, kerosene, benzene, carbon tetrachloride,; mercury, iodine, camphor. Vapors may be changed to the solid or liquid form by in creasing the pressure, decreasing the temperature or applying both processes simultan eously. They are removed from the air by condensation with less difficulty than are the gases. . ` ' . Gases are normally formless fluids which tend to occupy a space or enclosure completely and uniformly at ordinary temperatures and pressures. The following substances, there fore, qualify as gases: oxygen, nitrogen, carbon dioxide, carbon monoxide, hydrogen, ammonia, sulfur dioxide. Gases, likewise, may be solidified or liquefied by the proper control of temperature and pressure. The preceding classification is not suitable for the airborne living organisms, which themselves range in size from the submicroscopic viruses to the largest pollen grains, not considering the smallest insect life. Bacteria range from about 0.2 to 5 microns in size, fungus spores from 1 to 10 microns, and pollen from 5 to 150 microns. . SIZES OF AIRBORNE PARTICLES Fig. 1 is a graphic tabulation of the properties of airborne solids and, liquids arranged according to size on the micron scale. There are 25,400. microns in 1 inch. , Particles larger than 10 microns are unlikely , to remain suspended in air currents of moderate strength, but settle out by gravity at speeds dependent upon the shape, the size and specific gravity of the particle, the wind velocity, the orientation of the collecting surface, and the topography. These.larger particles are of major interest to the engineer in the solution of nuisance problems, but it is usually the smaller particles, or those below 10 microns, that remain in the air long enough.to be of hygienic as well as.economic significance. . The great bulk of industrial dust particles are of the order of 1 micron ' 186 CHAPTER 10 , 1946 Quidt< <Air Contaminants 187 reveal particles in. the 0.1 micron vicinity may-account in part for this observed statistical average of 0.5 micron. .. . The lower limit of particle size visible to the naked eye cannot be stated definitely. It depends not only upon the individual eye, but,also upon the shape and color of the particle, the intensity and quality of the light, and the nature of the background or the opportunity for contrast. Under ideal conditions a particle of 10-micron size may be recognized, while under less favorable conditions it may be impossible to distinguish a particle smaller than 50 microns. The lower limit of visibility should, therefore, be considered as a physiological range, probably 10 to 50 microns. .' Dusts, powders and granular materials are frequently classified by reference to the size of screens used for separation. Particles above 40 microns are said to be the screen sizes and those below, the sub-screen or microscopic sizes. The approximate or theoretical sizes of particles corresponding to the mesh scale of the U. S. Standard Sieve Series are given in Table 1. . Table 1. Relation of Screen Mesh to Particle Size U. S. Standard Sieve Mesh. . 400 325. 200 140 100 60 35 18 Nominal Sieve Opening in Microns________ 37 44 74 105 149 250 500. 1000 Microscopic examination of screened dust indicates, that the average diameter of a sample of irregular particles may be substantially larger than the openings of the screen through which it has passed, if the particle shapes deviate considerably from the spherical form2. The smallest dimension of many such particles will correspond with the maximum permissible distance between the wires of commercial screens made to ASTM Standard specifications. . . Screening does not give sharp separation into size groups, and accord ingly such a classification is statistical rather than absolute. Mineral particles, such as grains of sand, bits of rock, volcanic ash, or fly-ash, can be transported long distances under unusual circumstances. Thus, the dust storms' of 1935 in the Kansas district resulted' in vast amounts of fine top soil being thrown high into the air. Solar illumination as far east as Boston was affected noticeably and particles as large as 40 to 50 microns were actually carried half way across the continent before they settled out. In similar manner volcanic ash has been carried even farther. It is not surprising, therefore, that fly1ash from furnace gases, cement dust and the like, can be carried for considerable distances and that, occasionally, the engineer is confronted with the problem- of remov ing such material before the air in question is suitable for use in building ventilation.- , AIR POLLUTION BY SMOKE, ASH AND CINDERS The total airborne solids settling in urban areas are usually reported as soot fall in tons per (square mile) (month). Such data published- for the cities in this country range-from 20 to 200 tons per (square mile) 188 CHAPTER 10 1946 ,Guide (month). To the air conditioning engineer this information may indicate the effectiveness of smoke abatement or fuel combustion control methods in his locality, but it does not provide a suitable index of the suspended dust that air cleaners in a ventilating system are expected to capture3i 4-6. Gravimetric or weight data of the type given in Table 2 are preferable. In some cases airborne particle counts may be necessary, as for pollen, bacteria, spores, and dusts causing illness or lung disease. Dust concentrations by weight cannot be converted directly to con centrations by particle count because of the variability of particle size, shape and specific gravity, and the inherent characteristics of dust counting and weighing procedures. One milligram of dust per cubic meter of air may represent dust counts from 1 million to 100 million particles per cubic foot of air (lightfield microscope technic) according to the size distribution of the airborne dust sample. Information of this type for a specified application is best obtained by simultaneous sampling for both counting and weighing and noting carefully at the time all factors that might affect the reproducibility of the count-weight ratio. Table 2. Dust Concentration Ranges ' Location Rural and suburban districts Metropolitan districts Industrial districts... Ordinary factories or workrooms Excessively dusty factories or mines Minimum explosive concentrations ............ Grains per 1000 Cu Ft 0.02-0.2 0.04-0.4 0.1 -2.0 0.2 -4.0 4-400 4000-200,000 1 grain per 1000 cu ft =* 2.3 milligrams per cubic meter. l'oz per cubic foot - l gram per liter = 1000 grams per cubic meter. Milligrams per Cubic Meter 0.05-0.5 0.1 -1.0 0.2 -5.0 0.5 -10 10-1000 10,000-500,000 Smoke Abatement' ' Successful abatement of atmospheric pollution caused by smoke requires the combined efforts of the combustion engineer, industrial executive, public health officer, city planning commission and the com munity at large. Electrification of industry and railroads, increase in the use of domestic oil and gas furnaces, and segregation: of industrial districts is gradually providing effective aid in the solution of this problem. In the large cities where nuisance from smoke, fly-ash and cinders is more serious, limited areas obtain some relief by-the use of district heating. Boilers in these plants are of large size, designed and operated to burn the fuel without wasteful smoke, and equipped in some cases with dust collecting devices. The gases of combustion are usually discharged at a much higher level than is possible in the case of scattered buildings equipped with separate boiler plants. . 1 Time, temperature and turbulence are fundamental requirements for smokeless combustion. Increase of any one of these factors will reduce the quantity of smoke discharged, although excessive turbulence in fur naces may. increase the output of ash and cinders. Special care must be taken in hand firing the bituminous coals. . (See Chapters 16, 17 and 18 for further discussion on fuel burning technic). - Legislative measures at the present time are ..largely concerned with .reduction of the visible smoke discharged from chimneys of boiler plants. Practically all ordinances limit the number of minutes in any one hour Air Contaminants 189 that smoke of a specified density may be-discharged, as measured by comparison With a Ringelmann -Chart (Chapter- 11, Instruments and Measurements).' Ordinances generally do not make specific provision for control of the corrosive and irritant gases, such as sulfur dioxide and trioxide, which are discharged with the gases of combustion. Where high sulfur coals are burned, these sulfur gases present a serious hazard to property, health and vegetation. In foggy weather the accumulation of these gases in the lower strata of the atmosphere may be such as to cause irritation of the eyes, nose and respiratory passages, and possibly even more dangerous consequences. The Meuse Valley (Belgium) fog disaster has become a classic example in the history of gaseous air pollution. Released in a rare combination of atmospheric calm and dense fog, it is believed that sulfur dioxide and other toxic gases from the industrial region of the valley caused 63 sudden deaths, and injuries to several hundred persons. Dusts and cinders in flue gas may be'caught by various available devices, such as settling chambers, centrifugal separators, electric precipi tators, and gas scrubbers. The difficulty of retaining the dust and cinder . particles is principally a function of their size, specific gravity, and re sistance to wetting if a washer is used. Descriptions of dust collecting devices are given in Chapter 33. Absorption of Solar Radiation . The loss of light, particularly the absorption of solar ultraviolet light by smoke and soot, is recognized as a health problem in many industrial cities. Measurements of solar radiation in Baltimore 6.by actinic methods demonstrated that ultraviolet light in the country was 50 per cent greater than in the city. In New York City 7 a loss as great as 50 per cent in visible light was found by the photo-electric cell method. ODOR NUISANCE - A problem companionate with smoke abatement is the control of odor nuisance in the neighborhood of industrial plants discharging noxious or offensive air contaminants. Community planning and zoning will avoid much of the difficulty in the future, but meanwhile many industrial cities must resort to corrective'measures by requiring the installation of air cleaning devices, the alteration of manufacturing processes, or by legal termination of the offensive operation in residential or commercial districts. The development and manufacture of more effective and economical air cleaning devices for application to industrial plants will make it possible for many industries to continue operation in their original locations if desired, even though the community standards of air purity become more rigid. To a limited extent such developments already are benefiting the manufacturer, his employees, and his neighbors, when cleaning of the air from ventilated dusty processes makes it possible to return the reclaimed or recovered air to the workroom atmosphere instead of discharging it to the outside with its full load of contamination (Chapter 33). . The control of outdoor odor nuisance is especially, troublesome because of the extremely minute quantities of contaminant that are capable of offending, through a wide area. New industrial chemicals with strange 190 CHAPTER 10 1946 Guide ' or unfamiliar odors tend to receive-much-more attention from the neigh borhood than the customary odors generated by well known processes and raw materials. Methods of odor control currently in use include charcoal adsorption, scrubbing towers and air washers, chlorination, condensation, masking, passage of the odorous air through combustion chambers, and best of all, substitution of less offensive materials whenever possible *10- The control of air quality within buildings ventilated for human occupancy is discussed in -Chapter 12. Tobacco smoke odors, cooking odors and body odors are air contaminants of the nuisance type which now command a decisive position in the standards of air quality for indoor comfort. However, the engineer will find, at times, that odors originating outside buildings in industrial or business districts may have an even greater bearing than indoor contamination on the kind and capacity of equipment he must provide for a, high quality air supply installation. INDUSTRIAL AIR CONTAMINANTS Many industrial processes are sources of contaminants. Their unde sirable effects are known to the public and their control is an important function of the ventilating or air conditioning engineer, because the atmosphere within buildings is the medium whereby such finely divided matter is dispersed and transported from the source to remote locations where it may cause property damage, nuisance, fire, explosion, disease- and even death. . Tables 3,- 4 and 5 give the maximum allowable concentrations for industrial air contaminants as currently accepted in most sections of the country. They apply to exposures of 8 hours per day, and refer to the quantities of contaminant permissible in the workers'. breathing zone. . Some of these figures may be altered as the result of continuous research, and some may differ from those in force in a few cities, or states. The prudent engineer will design equipment using these values as the upper limits of air contamination, and will incorporate a reasonable margin of safely in his estimates of ventilation capacity. Information on the properties and effects, with respect to health, of -specific industrial air contaminants has developed rapidly within the past decade into an extensive literature. Some of the more readily available publications are listed at the end of this chapter. ; FLAMMABLE GASES AND VAPORS Adequate ventilation is a primary requirement for eliminating or .minimizing.the hazard of fire or explosion due to gases and vapors. The need for good ventilation is not removed by the use of other precautions,. such as the elimination of known ignition sources, segregation of hazard ous operations,' adoption of safe building construction, and installation of automatic alarms. Some safety engineers regard overventilation of an operation employing flammable liquids as a legitimate <operating charge for the privilege or necessity of using a dangerous process. However, it is ' not possible to apply a reasonable safety factor to the ventilation estimate without consideration of the concentrations of gases or vapors that ap proach the danger point. Safety engineers prefer to limit the concen tration to M or H of the lower explosive limit, and this fact should be given full weight'in determining the capacity and design of ventilating equipment. Rarely- should consideration be given to operation' above # Air Contaminants 191 Table 3. Physiological Response to. Gases and VAPORSa . Concentrations in Parts of Substance per Million Parts of Air (ppm) Acrolein---------- ----------------Ammonia----------- -------------- Amyl acetate.------------------Aniline--------------- --------Arsine.-------------------- ---------- Benzene (benzol)-. BromineButyl acetate.. Carbon dioxide.. Carbon disulfide--------------- Carbon monoxide.-------Carbon tetrachloride.-- Chlorine.. DichlorobenzeneDichloroethyl ether-- Ether (diethyl)--------Ethyl acetate..... -...... Ethylene dichloride.. Formaldehyde--------- , Gasoline------------- ------ Hydrogen chloride.. Hydrogen cyanide. Hydrogen fluoride. Hydrogen sulfide... Methyl alcohol------- Methyl bromide.Methyl chloride. Methylene chloride... Monochlorobenzene. Nitrobenzene._______ Nitrogen oxides. Phosgene. Phosphine-------Styrene.-----------Sulfur dioxide.. Tetrachloroethane...... Tetrachloroethylene.. Toluene (toluol)--------Trichloroethylene.----Turpentine...-----------Xylene (xylol)----------- Rapidly Fatal 2,000 5,000 250 20,000 500 165660 2,000 4,000 50,000 . 1,000.. 40,000 1,000 200 '"600 20,000 150,000 300 50 1,000 ""466' 7,000 '2a000 "2o'666 Dangerous to Life in >4 to 1 Hr 100 2,500 """266' 10 Maximum Allow able Concentration for Daily Exposures 1 100 400 5 1 5.000 40 10,000 50,000 1.000 100b 1 400 5,000 20b' 1,000 10. 500 100b 100c 1 75 15 35.000 10.000 . 4,000 400 400 100 10b 1,000 10 100 20 50 3. 200 ' 20b 200b '2,000 .20,000 50 . 100 500 75 5 100 -5 ' 4Q0.; "wo 5,000 5,000 25b 1 1 400b . 10 10.. 200 200 200 200 200b Adapted from: Manual of Industrial Hyglenel-by W."M.Gafafer et al. U. S. Public Health Service (W. B. Saunders Co.. 1943); Analytical Chemistry of Industrial Poisons. Hazards and Solvents, by M. B. Jacobs (Intersdence Publishers, 1941); Noxious Gases, by Henderson and Haggard (Reinhold Publishing Co., N. Y., 1943); and other authoritaUve sources., ........ , . , t .- bAdopted by the American Standards Association (American Standard Z-37). ' . . "HI . i \ ! the upper explosive limit in the open areas of buildings or rooms--even though unoccupied--because the-;,-..danger-; of: temporary drop of,1 gas concentration to,a.point within the,explosive range is top great. ... ... The ability of-av.flammable liquid;.to form explosive-mixtures is. de termined largely by its vapor pressure,- volatility, or rate of'evaporation. ^ 192 CHAPTER 10 _________ 1946 Guide Table 4. Maximum Allowable Concentrations of Dusts, Fumes and Mists'* ' Substance . ' ' Arsenic; arsenic trioxide Cadmium, and compounds-- Chlorodiphenvls. Chromic acid mist... Lead; lead carbonate; lead oxides; lead sulfate. Manganese, and compounds. Mercury, and compounds Pentachloronaphthalene..... I richloronaphthalene Zinc oxide fume chloride; -. lead nitrate; lead Milligrams per Cubic ' Meter, Daily Exposures* . 0.1c oil 0.15c o'.l . 15.0 *1 milligram per cubic meter = 0.44 grain per 1000 cu ft. m,b'odaJted./rnk Manual of Industrial Hygiene, by W. M. Gafafer, et al US Public Health Service (W. B. Saunders Company, 1943); and other authoritative sources. Service 'Adopted by the American Standards Association (American Standard Z-37). Table 5. Maximum Allowable Concentrations of Dusts2 Substance Aluminum oxide abrasive. Asbestos.__' ....... Carborundum (silicon carbide) Cement (Portland) Coal (less than 5 per cent quartz) . Dusts containing less than 10 per cent free silica. Granite (Barre)... Gypsum (hydrated calcium sulfate) Limestone (calcium carbonate). . Marble (calcium carbonate) ............ Mica_____________ Nuisance dusts (non-toxic, non-silica) Quartz (silicon dioxide). band (silica, silicon dioxide).. Sandstone........... Silica (free or uncombined silicon dioxide) Silicates (combined silicon dioxide) Slate......................... : - Talc....................... ...... ................................. lotal (maximum concentration for mixed dusts) * Million Particles per Cubic Foot of Air, Daily Exposures1* 5 15- 50 50-100 50-100 15-100 50-100 50-100 50-100 10- 50 50-100 5 '5 15-100 15-50 . 50-100 ` . `Adapted from: Study of Asbestosis in Asbestos Textile Industry, U. S. Public Health Service Bulletin No; 241, 1938; Industrial Dust, by.Drinker and Hatch (McGraw Hill Book'Co;, 1936); Industrial Code Bulletin No. 35, New York State Department of Labor- recommendations of state and local industrial hygiene agencies compiled by-the National Conference of Governmental Industrial Hygienists; and other authoritative sources. -' wgSJSHrimtaBtf ^dn,,CI,oTmenfrThha2" mldlCrtinm,(SiseC^^I'n'Kduhstftireialdl cDouusmt- Cahfoarpttheer sVaIrIn. ebysaDmripnfkeear aaon?dorHdiangtcahtoCMthcc- Flash point is a convenient method of expressing this property in terms of the temperature scale. It may be defined as the temperature to which . a. combustible liquid must be heated to produce a flash of flame when a small, flame is passed across the surface of the liquid. The higher the Air Contaminants 193 flash point, the more safely can the liquid be handled. Liquids with flash points under 70 F should be regarded as highly flammable. The upper and lower limits of flammability of gases and vapors, and the flash points of the corresponding liquids are given in Table 6. - Methods for estimating the flammable limits of mixtures of gases or vapors must be applied with caution; the reader is referred to other publications for this information 12,13. - Design of equipment for the control of combustible anesthetics is outlined in Chapter 13. Construction of equipment for handling air containing flammable substances, or operating in atmospheres so con taminated, is discussed in Chapter 46. It is customary to report the concentrations of flammable gases or vapors in per cent by volume, or volume per cent. Comparison with concentrations on the part per million scale used in chemical, medical or industrial hygiene literature is readily made by the conversion: 1 per cent = 10,000 ppm (parts, of contaminant per million parts of air, or in other words, cubic feet of contaminant per million cubic feet of air). It will1 be noted in Table 6 that nearly all of the substances listed have lower explosive limits above 1.0 per cent, while the maximum allowable, concentrations for gases and vapors in Table 3 are below 1000 ppm or 0.1 per cent in most cases. Therefore, control of toxic or injurious vapors in workrooms to levels below their maximum allowable concen trations for health, usually requires much more effective ventilation than for the prevention of a fire hazard. COMBUSTIBLE DUSTS A dust explosion is essentially a sudden pressure rise caused by the very rapid burning of airborne dust. The primary explosion often originates from a small amount of dust in suspension exposed to a source of ignition and the pressure and vibration it creates may be sufficient to dislodge large accumulations of dust on horizontal ledges or surfaces of the building and equipment, thereby creating a secondary explosion of great force. Thus the air conditioning engineer is involved for two reasons; (1) to obtain a movement of dust-laden air into exhaust hoods or openings, and through ventilating or pneumatic conveying ducts in a manner that will prevent accumulation of highly flammable dust at points where it , could ignite inside the equipment; and (2) to so design process ventilation as to prevent the escape of dust which might settle on horizontal surfaces and become a potential source of disaster at some distance from the . dusty operations. (See Chapter 46). The intensity of a dust explosion depends upon: the chemical and thermal properties of the dust; the particle size and shape; the concen tration in air; the proportion of inert dust in the air; the moisture content and composition of the air; the size and temperature of the ignition source; and the degree of dispersion of the dust cloud. Investigations on the explosibility of dusts require a determination of the maximum pressure " developed during an explosion of a known air concentration, as well as determination of the rate of pressure rise. Investigators frequently experience difficulty in obtaining dust suspensions of uniform dispersion; and this fact must be weighed when comparing results from several sourcesM. ... - - The minimum explosive concentrations of airborne dusts already tested range from 0.01 to 0.5 oz pier cubic foot, or 10 to 500 grams per cubic 194 CHAPTER 10 '___________ -. 1946 Guide Table 6. Approximate Limits of Flammability of Single Gases and Vapors In Air at Ordinary Temperatures and Pressures11 . Gas or Vapor Acetaldehyde__________________ Acetone___________ --__ ____ Acetylene*5-- ____ ____ ______ AUyl alcohol___ _______________ Ammonia_______________________ Lower Limit Per cent by . Volume ' 4.0 2.1 2.5 2.4- 16.0 ' . "1 Upper Limit Per cent by Volume .57 13.0 ' 80 . 27.0. Closed Cup : Flash Point F Deg. ' -17 0 70 Amyl alcohol. _______ Amyl chloride .. Amylene.__ ,,_______ _______ Benzene (benzol).--__________ Benzyl chloride_______________ ' 1.2 1.4 1.6 1.4 T.r 8.0 91 12 140 Butane . ` ' Butyl acetate_________________ Butvl alcohol . Butylene________ _______________ Carbon disulfide.______ ___ . . Carbon monoxide Crotonaldehyde______________ ' . Cyclohexane Cyclopropane____________ 1____ Decane . . 1.6 . 1.7 1.7 1-7 , 1.0 12.5 2.1 1.3 ' 2.4 . 0.67 . . 8.5 15.0 9.0 50 74 ' ' , 15.5 8.4' . 10.3 . 2.6 ' ' -76 72 . 84 ' . '-22-. 55 '1 . 115 Dichloroethylene (1, 2)_____ Diethyl selenide. .. Diovan ' ... Ethane.__________________ ___ ___ Ether (diethyl)............................. 9.7 . 2.5 : 2.0 , ............ 3.1 1.7 . -. ., 12.8 22.2 < 15.0. 48.0 .... , ' 43 65 . -20 Ethyl acetate...______ ___ Ethyl alcohol.____ ____________ Ethyl bromide -........................ Ethyl cellosolve______________ Ethyl chloride 2.2 ! ' 11.5 . 24 -3.3 19.0 - .; . 55.. 6.7. . ; . 11.3 . - 2.6 . : - 15.7. 104 3.6 ' ,14.8"' ' - - ' --58 ' , Ethylene....-___________ :_________ . Ethylene dichloride._________ Ethyl formate-________________ ' Ethyl nitrite. .. ....___ Ethylene oxide. __ _ . ... . . . 3.0. 6.2 2.7 3.0' 3.0 ' : " : 34.0 , 15.9, 16.5 ' . - :: 80 , ' ,, ` , .. . 56 . -4 : -31 . Furfural (125 C)________ ____ Heptane.________________ ________ Hexane. ................. ............ Hydrogen cyanide___________ . 2.1 ; v1.3 ` ' 1.0 s 1.2 5.6: . , ' ' , 65 6.0 6.9 40.0 ' *' " ' 140, . 50 '25 ,- 1 ' -7 ' 0. Hydrogen____________!__________ Hydrogen sulfide....:_________ Illuminating gas._____________ Iso-butyl alcohol___________ _ Iso-pentane.___________________ Iso-propyl acetate_______ ...... Iso-propyl alcohol__________ : Methane15....... ............................... , 4.r- ' ` ' ' 74 4.3 -. 5.3 `y . 45.5 31.0 1.7 . i.3 ... . -------- ,. " :. .: - 1.8' : . 2.5 . 5.0 - - 7:8 . . .. 150 , 82 . 43 : 53 Adapted from: Limits of Inflammability of Gases and Vapors, by H. F. Coward and G. W..Jones (U. S. Bureau of Mines. Bulletin No. 279. 1939); Properties-of Flammable Liquids, Gases anH Solids (As sociated Factory Mutual Fire Ins. Cos.; January. 1940); and National Fire Codes for Flammable Liquids, Gases, Chemicals and Explosives--1945' {.Naiioridl'Fire Protection Association). ` " ' ' bTorbulent mixture. . - - , ' '`* ' - . ^Closed cup refers to the equipment used in flash point determinations! . ' Air Contaminants 195 > Table 6. Approximate Limits of Flammability of Single Gases and Vapors In Air at Ordinary Temperatures and Pressures (Continued) ' Gas or Vapor Methyl acetate____ J__________ Methyl alcohol. . ... Methyl bromide.:_____________ Methyl butyl ketone. _____ Methyl chloride............. ............. Methyl cyclohexane. ___ Methyl ethyl ether.__________ Methyl ethyl ketone................ Methyl formate_______________ Methyl propyl ketone--_____ Naptha (benzine)________ ___ Naphthalene___________________ Nonane_________________________ Octane__________________________ Lower Limit Per cent by Volume 3.1 6.0 13.5 . 1.2 8.0 . 1.1 2.0 1.8 5.0 . 1.5 ' ` 4.8 ` ' 1.1 0.9 0.74 0.84' Upper Limi* ' Per cent by Volume 15.5 36.5 14.5 8.0 19.7 , " 10.1 11.5 ' 22.7 8.2 13.5 6.0 ` 2.9 3.2 , Paraldehyde___ ___________ Pentane...................................... Propyl acetate..............J............. . Propyl alcohol.............. .. ... 1.3 1.4 2.4 1.8 2.5 Propylene.................... --..... ......... Propylene dichloride____ -- Propylene oxide______________ Pyridine (70 C)________ ____ Toluene (toluol)______ ;_______ . 2.0 .3.4 2.1 1.8 1.3 ' . 8.0 . 9.5 8.0 11.1 14.5 21.5 12.4 7.0 Turpentine......... ............................ Vinyl ether____ __________ _____ Vinyl chloride-________________ Water gas (variable)________ Xylene (xylol).............................. 0.8 . 1-7 : 4.0 6.0 . 1.0 -- 27.0 22.0 70 6.0 Closed Cup Flash Point -F Dbg. 15 54 - .......... ' 25 --35 30 : -2 . -- ' 20-45 174 88 56 ` --i-. 58 59 59 - 68 .40 - 95 ........ 63 ` meter of air. Maximum pressures generated have been reported as high as 500 psi, although they are more likely to be of the order of 50 psi: ' Investigations on the flammable.characteristics.of dusts are currently made at 0.1 and 0.5 oz per cubic foot15_!1. . . ATMOSPHERIC POLLEN The properties of pollen grains discharged by weeds, grasses and trees and responsible for hay fever are- of, special interest to engineers who . , design equipment for their removal from indoor air (see Allergic Dis- orders in Chapter 13, and Air Cleaning Devices, .Chapter 33). Whole. . grains and fragments transported by the.air range chiefly between 10 and , 50 microns in size, but some have been .measured as small as 5 microns and others over 100 microns in diameter. Ragweed pollen grains are ' . fairly uniform in size within the range pf 15 to 25 microns. Pollen grains can be removed from the air more readily than the parti- cles of dust prevalent in outdoor air and found near dusty industrial processes, since the latter predominate in ;the range of 0.1 to 10 microns . in size. . ' ,. . Most grains are quite hygroscopic and therefore vary in weight with the Z _' ;; . . , ; ' ' I i ' 196 CHAPTER 10 1946 Guide humidity. The specific gravity of air-dried pollen is reported to vary from 0.4 to 1.2, and accordingly their weight will either increase or decrease with the addition of moisture". Their shapes and surface designs " are marvelously complex, though they tend to be spherical, especially when fully distended with moisture. Illustrations and data on individual pollen grains are available in the botanical literature52'2S> 24. The geographical distribution of plaints known to produce hay fever is ' also recorded 25, 26. The quantity of pollen grains in the air is generally estimated by exposing an adhesive-coated glass plate outdoors for 24 hr and then counting calibrated areas under the microscope. Methods ate available for determining the number of grains in a measured volume of air 26, 27, 28 but their greater accuracy has not caused them to replace the more simple gravity slide method used for most pollen counts. Counting technics vary somewhat, but the daily pollen counts reported in local newspapers during the hay fever season usually represent the number of grains found on 1.8 sq cm of a 24-hr gravity slide. .. Hay fever sufferers may notice the first symptoms when the pollen count' is 10 to 25, and in some localities the maximum figures for the seasonal peak may approach 1000 for a 24-hr period, depending upon the sampling . and reporting methods of the laboratory. Translation of gravity counts by special formulas to a volumetric basis, or the number of grains per cubic yard or per cubic foot of air, is still uncertain because of the com plexity of the modifying factors. When such information is important, it is best obtained directly by a volumetric instrument. The number of pollen grains per cubic yard of air evidently varies from 2 to 20 times . the number found on 1 sq cm of a 24-hr gravity slide, depending on grain diameter, shape, specific gravity, wind velocity, humidity and physical placement of the collecting plate29,30,8l. *' ` ' AIRBORNE BACTERIA Study of the occurence and significance of micro-organisms in the " atmospheres of the indoor world is currently absorbing the energies of a substantial number of physicians, bacteriologists, aerobiologists, physicists, public health workers, engineers and hospital personnel. Some data are available' on the types, and quantities of bacteria found in a variety of occupied and unoccupied spaces, but it is not possible at present to use this information as a conclusive index of the potential health hazard of a given environment. The number of airborne organisms may vary from 1 to 1000 per cubic foot of air, depending on the method of testing 32. Many are attached to the dust particles which also inhabit the air. . Where it seems advisable or desirable to control the bacterial content of rooms, public conveyances or buildings; highly effective methods are available (see Chapter 13), and their extended use may do much to,assist the workers jn this field in accumulating the necessary mass of evidence that will decide the practical value of air sterilization for the control of communicable disease. It is now well established that ultraviolet radia tion is commercially feasible for the protection or preservation of phar maceuticals, cosmetics, and food products. . ., REFERENCES '--Atmospheric Pollution of American Cities for the Years 1931 to 1933, J. E. Ives et al (U. S. Public Health Service Bulletin No. 224, March, 1936). - . Air Contaminants 197 z--Micromeritics, The Technology of Fine Particles, by J. M. DallaValle (Pitman Publishing Cor poration. 1943). ' .' , 3--Atmospheric Pollution Due to Smoke, by A. C. Stern (Healing and Ventilating. May, 1945). Atmospheric Pollution Due to Dust and Cinders, by A. C. Stern (Heating and Ventilating. July. 1945). 4--Sootfall Studies for New York City, by J. Siegel and B. Feiner (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning, p. 495, September, 1945). ' 5--The Use of Fuel Consumption and Equipment Data in the Abatement of Atmospheric Pollution, by A C. Stern (A.SJI.V.E. Journal Section, Heating, Piping and Air Conditioning, p. 447-454, August, 1945). . .* 6-- Effects of Atmospheric Pollution Upon Incidence of Solar Ultra-Violet Light, by J. H. Shrader, M. H. Coblentz and F. A. Korff (American Journal of Public Health, Vol. 19, 1929, p. 7). ^-Studies in Illumination--III: A Study of the Loss of Light Due to Smoke on Manhattan Island, by J. E. Ives (U. S. Public Health Service Bulletin No. 197, June, 1930). *--Study and Control of Industrial Atmospheric Pollution Nuisances, by F. M. Stead (American Journal of Public Health. Vol. 35. p. 491-498. May, 1945). --Evaluation of Odor Nuisance in. the Manufacture of Kraft Paper, by J. M. DallaValle and H. C.. Dudley (U. 5. Public Health Service Reprint No. 2022. Public Health Reports, Vol. 54, p. 35-43, January 13, 1939). ' '' . . io--Disposal of Refinery Wastes. Section II: Waste Gases, Vapors, Sludges and Dusts (American Petroleum Institute, New York City, 1938). > i--Offensive Trades, by David Ronald (William Hodge and Co., London). 12--Limits of Inflammability of Gases and Vapors,.by H. F. Coward and G. W. Jones (U. S. Bureau of Mines. Bulletin No. 279, 1939). .. 13--Inflammation Limits and Their Practical Application in Hazardous Industrial Operations, by G. W. Jones (Chemical Reviews, Vol. 22, February, 1938). 14--private Communication, by Hylton R. Brown (Bureau of Mines, College Park, Maryland). i--Explosibility of Agricultural-and other Dusts as Indicated hy Maximum Pressure and Rates of Pressure Rise, by P. W. Edwards and L. R. Leinbach (U. S. Department of Apiculture Technical Bulletin No. 490, October, 1935). i--Dust Explosion Hazards in Plants Producing or Handling Aluminum, Magnesium, or Zinc Powder, by H. R. Brown (U. S. Bureau of Mines Information Circular No. 7148, March. 1941). , 17--Inflammability and Explosibility of Metal Powders, by I. Hartman, J. Nagy and H. R. Brown (U-. S. Bureau of Mines Report of Investigation No. 3722, October, 1943). . I--Inflammability and Explosibility of Powders Used in the Plastics Industry, by I. Hartman and J. Nagy (U. S. Bureau of Mines Report of Investigation No. 3751, May, 1944). 19--Industrial Dust Explosions, by H, R. Brown (U. S. Bureau of Mines. Information Circular No. 7309, January, 1945). ', zo--proposed Code for the Prevention of Dust.Explosions in the Plastics Industry (Notional Fire Protection Association, Boston, May, 1945). . . * i--National Fire Codes for the Prevention of Dust Explosions (National Fire Protection Association, Boston, 1944). Contains codes for aluminum, magnesium, coal, pulverized fuel, flour, spice, starch,- sugar, cocoa, sulfur and wood. - 22--An introduction to Pollen Analysis, by G. Erdtman (Chronica Botanica Co., Waltham, Mass, 1943). 23--Pollen Grains, by R. P. Wodehouse (McGraw Hill Book Co., New York, 1935). 24-- Atmospheric Pollen, by R. P. Wodehouse (Aerobiology, p. 8-31, Publication No. 17, American Association for the Advancement of Science, Washington, D.C., 1942). 2S--Hayfever Plants, by R. P. Wodehouse (Chronica Botanica Co., Waltham, Mass., 1945). *2--Hay Fever: A Geographical and Botanical Survey, by E. R. Squibb and Sons, New York, 1937. *7--Techniques for Appraising Air-Borne Populations of Microorganisms, Pollen and Insects (Phyto pathology. Vol. 31, p. 201-225, March. 1941). 2*--Apparatus for Determining the Pollen Concentration of the Atmosphere, by B. J. Cody, VV. F. Kinney and N. A. Kerstein (Research Department, the Detroit Edison Company, Detroit). 29--The Volumetric Incidence of Atmospheric Allergens, by O. C. Durham (Journal of AUergy, Vol. 14, p. 455-461, September, 1943). ' 3--The Volumetric Incidence of Atmospheric Allergens, II: Simultaneous Measurements by Volumetric and Gravity Slide Methods, by O. C. Durham (Journal of Allergy, Vol. 15, p.'226-235, May, 1944). v 3t--Air-Borne Fungus Spores as Allergens, O. C. Durham (Aerobiology, p. 32-47, Publication No. 17, American Association for the Advancement of Science, Washington, D. C., 1942). 32--Sampling Devices, by H. G. DuBuy and A. Hollaender (American Journal of Medical Science', Vol. 209, p. 172-177, February, 1945). 198 CHAPTER 10 . 1946 Guide ; BffiUQGRAPHY , Abstracts and Bulletins (monthly, annual and special) Industrial Hygiene Founda tion, Inc., Pittsburgh, Pa. ' Aerobiology, Publication No. 17 {American Association for the Advancement of Sci ence, Washington, D! C., 1942). \ . Air Sanitation and Industrial Ventilation, by W. N. Witheridge (Detroit Department of Health, 1945). . Analytical Chemistry of Industrial Poisons, Hazards and Solvents, by M. B. Jacobs (Interscience Publishers, New York, 1941). .. Bibliography of Industrial Hygiene, 1900-1943 (U. 5. Public Health Service Bul letin No. 289, 1945). . Clouds and Smokes, by W. E. Gibbs (P. Blakiston's Son & Co., Philadelphia, Pa., 1924). . .... . . Determination and Control of Industrial Dust, by Bloomfield and DallaValle ( U. S. Public Health Service Bulletin No. 217, 1935). . . Dust, by S. C. Blacktin (The Sherwood Press, Cleveland, 1934). ' ; .(The) Environment and Its Effect upon Man (Harvard School of Public Health, , Boston, 1937). ' Health Practices Pamphlets;' Industrial Data Sheets {National Safety Council, Chicago): ' ' . Industrial Dust, by Drinker and Hatch (McGraw Hill Book Co., New York, 1936). - . Industrial Hygiene Bulletin (monthly) (New York State Department of Labor). . Industrial Medicine (monthly) (Industrial Medicine Publishing Co., Chicago, 111.). Journal of Industrial Hygiene and Toxicology (monthly) (Harvard School of Public Health, Boston, Mass.): See cumulative abstract and subject indexes. Manual of Industrial Hygiene, by W. M. Gafafer et al (U.S. Public.Health Service, W.B. Saunders Co., Philadelphia, 1943). , Noxious Gases and the Principles of Respiration Influencing their Action, by Hender son and Haggard {American Chemical Society Monograph Sertes No. 35, Reinhold, New York, 1943). . ... . Occupation and Health, two volumes {International Labor Office, Washington, D. C.). Occupation Hazards and Diagnostic Signs, by Dublin and Vane (17. S. Dept, of Labor, Division of Labor Standards Bulletin No. 41, 1942). .. Toxicology and Hygiene of Industrial Solvents, by Lehmann and Flury, translated by Eleanor King and H. F. Smyth, Jr. (Williams and Wilkins, Baltimore, 1943). War Gases, by M. B. Jacobs (Interscience Publishers, New York, 1942). Yearbooks {American Public Health Association). * .. CHAPTER 1 1 trumenti and *ffl\ea&urement& Temperature Measurement, Pressure Measurement, Measurement of Air Movement, Air Change Measurements, Measurement of - Relative Humidity, Dust Determination, Heat Transfer Through Building Materials, Measurement of Heat Exchange for Comfort Conditions, Combustion Analysis, Smoke Density Measurements THIS chapter presents a description of many test instruments used for heating, ventilating and air conditioning tests and presents a discussion of their use. TEMPERATURE MEASUREMENT Changes in the intensity of heat may be determined by several methods1 such as measuring the change in volume of a liquid, the change in internal pressure of a confined gas, the current set up between dissimilar metals joined in a circuit, or the change in resistance of an electrical circuit. Thermometers . ' .' The most common method used is the change in volume of a liquid such as mercury or alcohol enclosed in glass. Mercurial thermometers may be used for measuring temperatures from -- 40 F to approximately 1000 F. The lower limit is set by the freezing point of mercury. Since the boiling point of mercury is only about 675 F, the space above the mercury in thermometers designed for higher temperatures must be filled with an inert gas under pressure. Alcohol thermometers may be used for temperatures from -- 94 F to +248 F. . The more accurate thermometers have divisions etched on the stem and are preferred for test purposes due to their low heat capacity.. During their manufacture, the freezing aiid boiling points of water are first marked while the thermometer is immersed in a test bath. The required divisions between these points, whether Centigrade or Fahrenheit, are then marked and etched' on the stem. In spite of these precautions the probable error in etched stem thermometers plus or minus one scale division, which makes calibration after manufacture necessary for most test work. Such thermometers are usually calibrated for complete stem immersion. .' , When incompletely immersed, a stem .correction should be made. At ordinary atmospheric temperatures the correction is negligibly.small,, but it usually is important when measuring high temperatures such as those of steam and flue gas. The emergent stem, correction may be calculated by the equation: i ' . K = 0.00009 D{h -t,) (1). , where - . . ' '' K = correction to be added, Fahrenheit degrees. ` ` 1 d =: number of degrees on the thermometer scale which are not immersed. .b = temperature indicated on the thermometer, Fahrenheit degrees, temperature of the non-immersed mercury column, Fahrenheit degrees, 0.00009 = difference in the coefficient-of expansion of the mercury.and glass. ' 1 . 199 ' 200 CHAPTER 11 . 1946 Guide Since the bulb has considerable area, radiant energy may affect tem perature readings2. In measuring room temperatures, care must be taken to locate thermometers away from hot surfaces, such'as radiators, or cold surfaces, such as walls or windows. Where this is impracticable, bright, polished shields should be used to screen the bulb from the radiant energy. ' Errors may also be avoided: (a) by allowing the thermometer time to reach equilibrium, (b) by-providing sufficient circulation to give a true average temperature of the medium observed, and (c) by reading with the eye at the same level as the top of the liquid, i.e., avoiding parallax. ' Two types of industrial thermometers for permanent installation in ducts or pipes are shown in Fig. 1, and consist of a glass thermometer protected by a metal case. The better grades have metal scales made specially for each instrument. These are ruled in the same manner as -Instruments and Measurements' 201 Thermocouples .. / . When two dissimilar metals are joined at two points and a temperature difference exists between these junctions, an electromotive force is developed. By maintaining the cold junction at a constant temperature (or providing equivalent electrical compensation), the magnitude of the electromotive force developed is a direct measure of the temperature of the warm junction. By proper selection of metals, any temperature up to 2900 F may be measured. Readings are obtained by means of a potentiometer or sensitive galvanometer which may be calibrated in degrees; If a potentiometer is used, there is no current flowing through the thermocouple wires at the time of measurement and therefore the resistance of the thermocouple circuit does not affect the accuracy of the reading. If a. galvanometer is used instead of a potentiometer, the instrument is usually built with a high internal resistance to minimize the effect of the resistance of the thermocouple circuit and also, special' described for etched stem thermometers. Due to the heat capacity and heat conductance of the jacket, it is more difficult to obtain the true temperature at a point with these than with the exposed etched stem type. The latter is usually preferred for test purposes. ' 't. '' .\ `' . Thermometer Wells .. . Where temperatures of fluids or gases in vessels or conduits are to be measured, it is often necessary to resort to thermometer wells. These are especially designed to contain thermometers and thermocouples. Since they separate the temperature sensitive element from the medium to be observed, large errors may result from their improper use *. These errors may be due both to poor heat transfer from the wall of the well to the sensitive element, and also to the tendency of heat to travel along the length of the well itself. To improve heat transfer in the case of ther- . mometers, the void should be filled with a liquid of minimum practical viscosity. At the well mouth, the stem should be packed to check evapor ation and heat transfer to the atmosphere. To reduce the temperature gradient over the length of the well, the wall of the conduit should be carefully insulatednn the area surrounding the observation point. ~ Fig. 2. Basic Circuit and Connections for Thermocouple and Potentiometer . lead wires of known resistance are used to connect the galvanometer to the thermocouples. The basic potentiometer circuits are shown in-Fig. 2. The thermocouple leads A-B are so connected that their polarity opposes that of battery C. If the position of E on the graduated slide wire rheo stat DF is adjusted until galvanometer G shows no current flowing, resistance DE will indicate directly the voltage generated by the thermo couple. In order to correct for variations in voltage from battery C, switch S is momentarily thrown over to the standard cell circuit and rheostat R is then adjusted so that the galvanometer shows zero current. Battery C then exerts the known voltage of the standard.cell at DH. -Calibration of thermocouples for high temperatures may be made against known melting points of metals. Radiation effects may be minimized by using the smallest size of wires consistent with mechanical strength. The use of small wires also makes the thermocouple sensitive to minute fluctuations in temperature. Wires of No. 33 B & S gage are small enough to be sensitive and to minimize radiation effects while still rugged enough for many purposes. By the use of thermocouples,, temperatures at remote points may. be indicated or recorded on con veniently located instruments; average'temperature .may be . readily obtained by connecting several couples in parallel or in'series'; and tern- 202 \ CHAPTER 11 ; r ; 1 1946 Guide peratures may be obtained within thin materials, narrow1 spaces,' or * otherwise inaccessible locations.. ", ' . Thermocouples in series with every alternate junction, maintained at a common temperature will give an emf which, divided by the number of couples to give the average emf 4 per couple, may be used to find the average temperature. . Thermocouples in parallel having the similar metals of a number of couples connected together and run to a common cold junction will cause an indication on a potentiometer which is the true emf only if the electrical resistances of the parallel junctions are the same *5. _ ' The temperature of the surface is at best difficult to obtain accurately6. The thermocouple is most readily adaptable for this purpose. In a metal surface, a common method is to peen the'.couple into a small drilled hole, bearing in mind that the temperature indicated is that existing at the last point of junction in the couple. Other methods involve .Fig. 3. Typical Resistance Thermometer Circuit and Connections fastening the couple to'the surface with adhesive cellophane, dr cementing, the.couple with litharge in a surface scratch, and grinding it flush with the surface. Wires may also be fastened to the surface by brazing, care being taken to add as little extra metal as possible. This is a useful method'for obtaining the temperature of cast-iron heating surfaces; . In any of these methods the.leads should be of.as fine wire as practicable, since conductance along the' leads to the couple may''be a source of considerable error. . Resistance thermometers depend for their operation upon the change of resistance. of metal with change in temperature.' Their use largely parallels that of thermocouples, although readings tend to be unstable above 950 F. Two-lead temperature elements are not recommended, since they do not permit correction for lead resistance. Three leads to each resistor are necessary.to obtain consistent readings. .. 1 A -typical circuit used, by several manufacturers is shown in Fig. .3. In this design a differential galvanometer is used, in which coils L and H exert'opposing forces on the indicating needle. ' Coil L is'in series with . the thermometer, resistance AB, and coil H is in series'with-the constant resistance' Rv' As the temperature falls, the resistance of AB decreases allowing more current to flow' through coil L than through coil H. This.' 'U* 'V X_ Instruments and Measurements 203 causes an increase in the force exerted by coil L, pulling the.needle.down to a lower reading. Likewise, as, the temperature rises the resistance of- .; AB increases,. causing less current to flow through coil, L than through coil H. This.forces the. indicating needle to a. higher reading.. Rheostat S must be adjusted occasionally to maintain a constant flow of current. . Instruments of this type are frequently connected through a,selector, switch to a number of thermal resistor elements and used to indicate temperatures in Eemote locations in large buildings. ,.The direct reading -. feature is advantageous in this case.' . . . . -' Pyrometers .. . ' . .. ' For measuring high temperatures, such as in furnaces, pyrometers are often used. Radiation pyrometers concentrate the radiant energy on a ' thermopile, and the reading is obtained on a galvanometer or potentio meter. Optical pyrometers require visual- matching of a narrow spectral band, usually-red, emitted by the object'with that from-a standard electric lamp. ' Barometer PRESSURE MEASUREMENT . The most accurate barometer for determining the atmospheric pressure is the mercurial type, consisting of a tube over 30. in., long closed at the top and standing in a mercury well. The barometric pressure is expressed as the height of the mercury column above the level of the mercury in the well. Such barometers are equipped with an adjustment to compensate 1 for change in level of mercury in the. well. The reading should be taken at the top of the meniscus and is obtained on a Vernier scale. Correction for variation of the density; of the mercury column and for expansion of the brass scale, which are usually calibrated for 32 F mercury " and 62 F scale temperature,'should be made by subtracting from the . observed height in inches the value of C determined by Equation 2. . ., h{t - 28.630) (1.11231 - 10978) . where . ., ' . C ~ correction to be subtracted, inches of mercury. . -, h = observed height, inches of mercury. . t = observed temperature of the barometer; Fahrenheit degrees: . . . K' ' - .' . . . Standard atmospheric pressure at sea level is 29.921- in. Hg. Since . normal atmospheric pressure.decreases about O.Ol in. Hg-.for each 10 ft increasem elevation, it is important to make a correction if the elevation of the barometer is not that of the test apparatus. In, many cases the barometric reading may be obtained from a nearby .Weather-Bureau Station, in which.case inquiry should be made as to whether the value is as observed or corrected to sea level. . . .. ' - Atmospheric pressure may also be measured by an aneroid barometer, . -. which is easijy portable. In this type, variations in atmospheric pressure ' bend the thin surface of a sealed box or tube. The 'aneroid type is not ; ' as accurate as the mercurial and needs frequent calibration: Most of-the pressure gages used in-engineering work indicate the difference between . the pressure being measured and the atmospheric-pressurer-^Such pres- sures-are called gage pressures. Absolute pressure, may :be obtained by-' '. ', - adding barometric pressure and gage pressure algebraically. 204 CHAPTER II ' 1946 Guide Pressure Gages ' . '. The Bourdon type gage is a widely used device for measuring pressures. The Bourdon tube is elliptical in cross-section and circular in form, and is connected by suitable linkage to a pointer which moves over a dial. An increase in pressure tends to straighten the tube and a decrease has the opposite effect. When used with'high temperature steam, the tube . must be protected by a water seal. When used with ammonia it must be made of steel or other material not attacked by this substance. When ' used for sub-atmospheric pressure, the gage is known as a vacuum gage, and is usually graduated in inches of mercury. For pressures above atmospheric, it is termed a pressure gage and is graduated in pounds per square inch. Some are made to read in both directions and are termed compound gages. Calibration is usually made by means of a dead weight . tester, consisting of a platform and weights resting on a piston floating on oil. The pressure at all points in the fluid is determined from the area of the piston and the total weight resting on the oil. Adjustments Instruments and Measurements 205 For measuring low pressure differences to within 0.001 in. of water very sensitive micromanometers are available, such as the Illinois or Wahlen, the Askania, and the Emswiler 3| . ..Calibration of these is impossible,, and readings are converted to pressure units by fundamental calculations involving the specific gravity of the fluids used and the design principles involved. ........ . . Static Holes and Tubes . . In the case of low pressure air flow, the type of pressure opening used and its location are quite as important as the accuracy, of the gage to Fig. 4. Inclined Draft Gage are provided in the gage linkage to make necessary corrections. A cor rection chart may be used for accurate work. Manometers For comparatively low gage pressures or differences in pressure between two points in a duct system, the vertical U tube is a simple and accurate gage and is often used for test work with various fluids such as mercury, water, kerosene, or alcohol. Readings may be in inches of any of these fluids. . For measuring pressure differences of a few inches of water, or less, U gages are often set at an angle for scale amplification. In commercial ' gages of this type, commonly termed draft gages, only one tube of small bore is used and. the other leg is replaced by a reservoir. Although the scale is calibrated to read in inches of water, a fluid'having the density and characteristics of kerosene is often used. It is necessary, in such a gage, to use a fluid having the same gravity as that for which the gage was originally calibrated, or to apply a correction if another fluid is used. Such, gages may be checked one against another to detect errors in gravity of fluid.' For more accurate calibration the gage may be checked . against a micromanometer or a calibrating device known as a hook gage 7. The accuracy of a draft gage is dependent on the slope of the tubes and consequently the base of the gage must be leveled carefully. It is not desirable to use a slope of less than -1 in 10. -, . ' The better grades'of inclined draft gages are . equipped as shown in Fig.: 4; This includes a built-in level and leveling adjustment, a means of adjusting the scale to zero, and three-way vent cock-connectors lor . checking purposes. . ,. which it is connected. Where velocities are low, as in certain plenum chambers, or where flow is free of large eddies and parallel to the wallsof the conduit, a carefully drilled, opening cleared of burrs and at right angles to the stream will give accurate readings10. The drilled depth of this hole through the wall should be at least two diameters. A second method less likely to involve error is the use of the static pressure element of a Pitot tube shown in Fig. 5. A static tube of the same general design as the Pitot may also be used, omitting the center tube. In using this instrument it should be pointed upstream, avoiding impact or eddies. MEASUREMENT OF AIR MOVEMENT The problem of measuring air movement may be divided into three main parts: air confined.in ducts, air circulating in free spaces, and air entering or leaving such space through openings such as. grilles. Other 206 CHAPTER 11 -.'1946 Guide gases may be measured by the same, methods,'butemphasis here is on. air "measurementsu. . ' . ' : For determining the velocity; and therefore the volume of air flowing in a duct, the Standard1 Pitot Tube 7 shown in Fig. 5 .is probably most often' used. When connected as illustrated; this instrument will give readings'of both static and velocity pressure directly; From the latter .the air velocity may be found from tables, or calculated .from.the fob lowing relation: ....... ............................ VV = 1096.5 where V -- velocity, feet per minute. .,. hv = velocity pressure, inches of water. d -- density of air, pounds per cubic foot. . ' (3)' Air flow in'a duct is seldom uniform. In general the velocity is lowest Fig. 6. Pitot Tube Traverse for Round and Rectangular Ducts near the edges or corners, and greatest at or near, the center. ' For this ' reason a large number of readings should'be taken in-the manner shown in; Fig. 6. In die case of round ducts not less than 20 should be taken along' two. diameters at centers of equal annular areas. In rectangular ducts the readings should be taken in the, center, of equal areas over the crossT section of the duct. The number of spaces should not be lessthan 16 and ' need not be more than 64. . .When less than 64 are .taken the, number, of equal spaces should be such that the centers, of the areas are;.not more -than 6 in. apart. - : . r- . -' In determining the :average velocity in the duct from the readings given, the calculated individual-velocities or the, square, roots of. the velocity heads must be averaged. It is incorrect To use, the average. velocity head for this purpose. .. ' ` '. For small pipes it is sometimes necessary, to,construct a Pitot tube ' smaller than the standard size. Such a small Pitot tube should be geo- ' ; metrically similar to the standard tube. . Pulsating.or disturbed-flow will . give erroneous results and every effort should: be made to remove- dis1 " turbances in the Pitot tube section.- i -n i - Instruments and Measurements'- ' ________ ______ '' ,207 The velocities used in many ducts are too low for measurement by. means of pressure gages and it therefore becomes necessary to resort to other types of instruments. .. : . . . - Many forms of Pitot tubes other than the one described have been used : and calibrated A double-ended tube u, one end pointing down-stream, . and one up-stream, is sometimes used for low velocities, but It should be carefully calibrated for accurate results. A special form of this .tube design consists of two straight }/& in. tubes soldered together, closed at the end, and with a 0.04 in. hole in each tube opposite the line of contact. This tube is useful in exploring velocities on exhaust inlets, such as on hoods placed around grinding wheels. . ' The rounded approach orifice or nozzle of the general type described in the A.S.H.V.E. Unit Heater14 and Unit Ventilator u Codes is an accurate . air measuring device. When it is well made, the coefficient closely ap proaches unity. The discharge from such a nozzle is uniform16 and provides a good location for calibration of air velocity instruments17. The Venturi meter is like the nozzle except for the addition of a down- stream transition section that reduces the pressure drop through the measuring apparatus. . .. . The thin-plate square-edged orifice has a coefficient of approximately 0.60. The exact value depends on .the location of . the connections, the pressure drop, the diameter ratio of orifice to pipe, and the sharpness of the edge18. _ ,. Another method of air measurement uses the thermal electric principle where, -by means of a measured amount of current, heat is put into the air stream. The weight of air flowing is calculated from the heat equiva- ' lent of the electrical input and. the temperature rise of the air. Heat should be applied uniformly to the mass of air passing, and the small . . temperature rise must be determined accurately. In certain.applications the air velocity through a duct, heater coil, or ' heating unit may be most conveniently obtained by computation from -. , the heat given up by the coil'and-the temperature rise (hieasured by , thermocouples) of the air passing through. It is essential to have a uniform flow over the entire inlet and outlet of the heater at the plane of temperature measurement. . . Air Currents in Free Spaces .. . One of the instruments useful in determining the velocity of air cur - rents in free spaces is the Kata-thermometer. It is essentially an alcohol thermometer with a .large bulb. The stem has two marks, one corre sponding to 95 F, and the other 100 F. The instrument is heated above . 100 F and then the time in seconds required for it to cool from 100 to 95 , when located in the air current gives a measure of the non-directional . velocity. It is important to have the Kata-thermometer dry before taking the reading. Each Kata has its own factor, etched on the stem, and this factor must be used with its codling formula or chart for obtain . ' ing the velocity. The Kata-thermometer is useful in exploring ventilated spaces to determine whether the proper air movement and distribution ' are being maintained; It is also used in determining the cooling power ... of the atmosphere, since it loses heat by radiation and convection-when dry, and by radiation; convection, and' evaporation when the bulb is . equipped with a wetted cloth covering 19. . Another. instrument for measuring: low velocity air currents is the 208 CHAPTER 11 1946 Guide heated thermometer anemometer 2o. This consists of a mercurial glass thermometer with a resistance winding on the bulb. Current is supplied from an external source in a measured amount. The difference between the temperature of this heated thermometer and that of an ordinary thermometer at the same location, together with the current supplied, makes it possible to calculate the non-directional velocity of the air stream. The heated thermocouple anemometer, employs a thermocouple instead of a thermometer21. . ' Another instrument is the hot wire anemometer which has been made in several patterns. In general, a measured current is supplied to raise the temperature of a fine bare wire above the temperature of the surrounding air. With the use of a very fine wire, minute fluctuations in velocity may be measured, and the area exposed to radiant exchange with heated or cooled surfaces is at a minimum. This instrument is easily adapted to remote reading or recording. A group of them may be connected together to give the average velocity in a space, or the velocity at individual points within a test space, by suitable switching arrangements 23. . Deflecting Vane Anemometer . The deflecting vane anemometer consists of a pivoted vane enclosed in a case, against which air exerts a pressure as it passes through the instrument from an up-stream to a down-stream opening; The move ment of the vane is resisted by a hair spring and a damping magnet. The instrument gives instantaneous readings of directional, velocities on an indicating scale. When used in fluctuating velocities, it is necessary to average visually the swings of the needle to obtain average velocities. N This instrument is very useful for studying mixing of air in a room24 and in locating and measuring peak velocities that may be objectionable. Various attachments are available, such as the double tube arrangement for obtaining velocities in ducts, and a device for measuring static pres sures. Each instrument and the attachments for it must receive individual calibration. , Propeller or Revolving Vane Anemometer . The propeller or revolving vane anemometer consists of a light re volving wheel connected through a gear train to a set of recording dials that read the linear feet of air passing in a measured length of time. It is made in various sizes, 3 in., 4 in., and 6 in. being most common. Each instrument requires individual calibration. At. low velocities the friction drag, of the mechanism is considerable. In order to compensate for this, a gear train that overspeeds is commonly used. For this reason the correction is often additive at the lower range and subtractive at the upper range with the least correction in the middle range of velocities, Most of these are not sensitive enough for use below 200 fpm. Measurement of Velocities at Inlets and Outlets of Ducts ' . In the field it is often desirable to make volume measurements at the face of the supply openings. It is rare to have access to the interior of duct sections where the flow is sufficiently uniform for measurement. For accuracy the instrument and. its application should be checked on a similar approach and grille'in the laboratory before use in the field. Tests have shown that the propeller type anemometer-can be used; successfully on most of the common, types of supply grilles a: ". The core Instruments and Measurements 209 area is divided into equal squares, and the anemometer is held against the, face of the grille for the same length of time in each. To get the air volume in cubic feet per minute, the average corrected velocity in feet per minute thus obtained is multiplied by the average of the gross and net free area of the grille (core) in square feet. . On exhaust openings, the anemometer traverse is made as described previously. The air volume may be determined by multiplying the corrected velocity in feet per minute by the gross core area of the grille in square feet and by a coefficient for average conditions of 0.85 27. When a propeller type anemometer is held in a stream of varying velocities, it tends to indicate higher than the true average, that is, the speed of the propeller is nearer to the top velocity in its area than it is to the minimum velocity. This is the main reason for the large difference, in ratings of unit ventilators by the anemometer method and by air volume measurements in a duct approach to the inlet. Any of the other anemometers described can be used within their range at the face of supply grilles when properly applied. In principle it is a case of finding the velocity at many points and. using the average thus found with the correct discharge area at that cross-section. The deflecting vane anemometer equipped with a jet on the end of a rubber tube has been found especially convenient and accurate on supply grilles29. On modern air conditioning grilles the core area is used without a cor rection coefficient when the jet is held one inch away from the face of the grille. At this distance the constriction due to the thin bars has disappeared since the small air jets have reunited, and the air stream has not yet spread beyond the core dimensions. With deflecting grilles the exploring jet should be turned to the angle giving a maximum reading. With suitable traversing tips and calibration, this instrument may also be used on exhaust grilles if proper grille factors are applied50. - While hardly a quantitative instrument, smoke is very useful in studying air streams and currents. The application of a more accurate instrument is often made more exact by a preliminary exploration with smoke. A mixture of potassium chlorate and powdered sugar in equal portions gives a very satisfactory non-irritating smoke. It is fired by a. match, and since considerable heat is evolved, it should be placed in a pan away from, inflammable objects. AIR CHANGE MEASUREMENTS Atmospheric air contains a certain amount of carbon dioxide. Its concentration is increased within enclosures by the-carbon dioxide given off by occupants. The total air change through open windows, infiltra tion, and mechanical ventilation, may be measured by the carbon dioxide concentration but absorption of COj by walls and. other materials may -introduce errors 51 and consequently some investigators prefer hydrogen to CO2 for such tests. Since occupants also give off moisture, the increase in humidity may also be used as an index of ventilation within a space. Usually,more direct methods of measuring air supply and air distribution are in favor; . ... ... . . MEASUREMENT OF RELATIVE HUMIDITY Wet- and dry-bulb mercurial thermometers are usually-used to deter mine relative humidity. The.sling psychrometer is a common mounting of the thermometers to permit swinging. The wet-bulb wick and water 210 CHAPTER 11 1946 Guide ' for wetting' it must be dean, and the temperature of the water should preferably be slightly above the wet-bulb temperature. An air stream . velodty of 900 fpm is recommended, although higher velocities will result in greater .accuracy 32. This velocity is obtained with the sling psychrometer by whirling it rapidly, followed by reading the wet-bulb" thermometer quickly before its indication changes. Owing to the human element involved in this method, more accurate results are obtained with types of psychrometers in which air is drawn over the. thermometers by a fan, or by a bulb operated aspirator. In ducts, the air flow itself gives the proper evaporating conditions. Several observations should be made until the minimum temperature is reached. Relative humidity may be obtained from tables or psychrometric charts 33. Although it is common practice to use the charts which are based on a barometric pressure of 29.92 in. Hg, a correction for barometric pressure is necessary for extreme accuracy. This correction is.made by multiplying the relative humidity as determined from the chart by the ratio of the observed barometric pressure and the standard barometric pressure. - For temperatures below 32 F, the water on the wick is allowed to freeze, during which time the temperature will drop below the true wet- ' bulb. A thin film of ice is more desirable than a thick one, and it is ' satisfactory to remove the wick and freeze a. thin film directly on the bulb. Care must be taken to read the temperatures accurately due to the slight wet-bulb depressions. Tables for ice conditions must .be used M. Dew-point apparatus for humidity measurements consists of a polished plated container cooled by the evaporation of a volatile liquid within: -The temperature at which the first slight water vapor forms on the polished surface is the dew-point. If the temperature is below-32 F, the deposit will appear as frost. Another method of determining humidity is by chemical means in which the water vapor is removed by a drying agent and weighed on a chemical balance. A thermal conductivity method is available for temperatures above 212 F or for extremely low humidities 3S. DUST DETERMINATION . The measurement of dust is complicated by. the many kinds involved. Some of the collecting methods are impingement on viscous surfaces, impingement at high velocity under water, collection on porous crucibles or filter paper through which air passes, and electric precipitation. Deter mination may be by direct weighing of samples Or by microscopic count- mg. A commonly used method employs the Smith-Greenburg impinger which collects samples in water or alcohol and in which particles are counted under a microscope in various cells such as the Hatch or Dunn cells. Another method employs the Lewis " sampling tube with the analytical determination of the increase in weight of a porous crucible. All reports should state the method of sampling and counting. The A.S.H.V.E. Code for Testing and Rating Air. Cleaning Devices Used in General .Ventilation Work specifies the porous crucible method 37. , . HEAT TRANSFER THROUGH BUILDING MATERIALS The A.S.H.V.E. Standard Test Code for HeatTransmission Through Walls 38 describes the construction and use of the guarded hot box for -determining over-all heat transmission coefficients of buiit-up sections including surface resistances. This apparatus consists of inner and outer insulated boxes, each having one open side which is sealed tightly against. Instruments and Measurements.. the wall specimen to-be tested. ` The outer box. serves as a guard-and a . zero temperature difference is maintained-between ,the inner-box;and-. . the air space: separating it from-the! outer box.- Electric heaters are .. provided: to. maintain'any desired-.temperature within the boxes while : at the same, time the outer surface, of the wall specimen is subjected to a low temperature:. A common method of applying this low tempera^ ture is to fit the specimen into an opening in the wall of a refrigerated room. The air temperature: difference - between the two sides of the specimen, and the. rate of heat input to the guarded hot box are measured, from which data an over-all heat flow coefficient can be calculated. The Nicholls heat meter is very useful for determining the heat flow ' through walls of buildings This apparatus consists of a guarded plate . on both sides of which are mounted a series of thermocouples. `The plate - is calibrated so fhat the rate of heat flow through it can be determined by observing the temperature difference between the two surfaces. In use, the meter is clamped tightly against the surface of the wall in question, and readings of heat flow of accuracy sufficient for. many test purposes may be obtained. ; >, ; : . In June 1942, the A.S.H.V.E. adopted a standard test procedure for determining the conductivity of materials' by iise. of the guarded hot . plate40. This method is adapted to homogeneous materials, arid-con ductivities obtained do. not include surface coefficients. The method involved, is one in which-two identical samples are arranged one on each side of a heated plate having a guard and a central test section. The re- . suiting sandwich.is placed between cold plates. In operation the same temperature is maintained in the guard section and test section of the heated plate .and a lower temperature is maintained in each of. the cold plates from a common source of cold water. Thermal conductivity is ' determined by measuring the amount of heat supplied to the center or guarded portion of the hot plate, the temperatures at the hot and cold surfaces and the thickness of the specimen. The apparatus requires careful, precise construction and its operation requires care and skill.. ,. The actual design of basic types of hot plates is described in an A.S.T.M. publication41. ... . - . .--- . MEASUREMENT OF HEAT EXCHANGE FOR COMFORT CONDITIONS Several instruments have been devised to measure the effect of various. factors as they relate to the coirifort of the body43. The principal ones are the Kata-thermometer, Dufton's eupatheoscope, Vernon's globe ther mometer, Winslow and Greenburg's thermo-integrator, and Yaglou's heated globe431 44. These instruments were designed to obtairi a quariti- - , tative measurement1 of the thermal exchange between' the human body - , and its environment. . - '' '' '; ' COMBUSTION ANALYSIS : The. analysis of flue gases to determine completeness and efficiency of combustion is usually made chemically-with an Orsat apparatus. This consists of a measuring burette, a leveling bottle, and three pipettes. Carbon dioxide is absorbed in the first pipette by potassium hydroxide, oxygen in the second by potassium pyrogallate, and,carbon monoxide in: the third by cuprous chloride. A known volume of gas is drawn in, and 212 . CHAPTER 11 ' '1946 Guide after each of the three absorptions the reduced volume is again measured in the burette. Pressure and temperature of the gas sample are kept constant while measuring. Several passes are made through each pipette which contains tubes or glass beads to increase the wetted surface. _ It js essential that each reaction be completed before the next reaction is started. Since the life of the reagents is limited, it is well to keep a record , of the number of samples tested. Care is needed in operation to prevent the pulling of reagents out of the pipettes into the capillary tubing and burette. Many types of recording gas analyzers are available and are usually found in the larger boiler plants. Carbon Monoxide Measurement . ,' A method of analyzing for low carbon monoxide concentrations com pletes the oxidation of the carbon monoxide in a known volume of sample, in the presence of a catalyst. The heat resulting is measured by a thermocouple calibrated in parts per 10,000 of carbon monoxide45. SMOKE DENSITY MEASUREMENTS Smoke density may be judged by assigning to it the number of the Ringelmann Smoke Chart which appears to -have the same color when Number of Caro i 2 3 4 Table 1. Ringelmann Smoke Chart Spacings Thickness of Lines, mm 1.0 2.3 3.7 5.5 , - , Distance in Clear7 Between Lines, mm ' Y ; 9.6 7.7 6.3 4.5 observed at a distance of 50 ft. The charts are numbered 1 to 4 and are made of black lines cross-ruled on white as given in Table 1. Apparatus using the photo-electric cell has been devised for recording smoke densities in large plants. ' ,. - . ' REFERENCES \ - l--For a comprehensive treatment of temperature measurement the reader is referred to Temperature, Its Measurement and Control in Science and Industry, a symposium sponsored by the American Institute of Physics and published by Reinhold'Publishing Corp. 2*~Errors in the Measurement of the Temperature of Flue Gases, by P. Nicholls and W. E. Rice (A.S.H.V.E. Transactions, Vol. 35. 1929, p. 473). 1. 3--Temperature Measurement (A.S.M.B. Power Test Code, Part 3). 4--Measuring Heat Transmission in Building Structures and a Heat Transmission Meter, by P. Nicholls (A.S.H.V.E. Transactions, Vol. 30, 1924, p. 94). .s --Parallel-Connected Thermocouples for the Testing of Gas Appliances, by Walter B. Kerband George J. Pacanovsky (Cos, September, 1939, p. 51). - '. ' Measurement of Surface Temperatures, by F. C. Houghten and H. T. Olson, Temperature, Its - Measurement and Control in Science and Industry (Reinhold Publishing Corp.). , . standard Test Code for. Centrifugal and Axial Fans, Edition of 1938. See also Standard Code for the Testing of Centrifugal and Disc Fans (A.S.H.V.E. Transactions, Vol. 29, 1923, p. 407; Vol. 37, 1931, p. 363), ' - '' Instruments and Measurements 21$ *--Illinois Micromanometer (University of Illinois, Engineering Experiment Station Bulletin No. 120. P.91). . *, ' ' _ --The Weathertightness of Rolled Steel Windows, by J. E. Emswiler and W. C. Randalh(A.S.H.V.E. Transactions, Vol. 34,1928, p. 527). * _ *--Pressure Measurement (A .S.M.E. Power Test Code 1936, Part 2, Chapter 2). . 11--For technical data refer to Fluid Meter Reports, Parts 1--1937, 2--1931, and 3--1933 (American Society of Mechanical Engineers). . .- 12--Technical Notes No. 546 (National Advisory Committee for Aeronautics, November, 1935). ` 1 *--The Characteristics of Double Pitot Tubes, by F. R. Ingram, E. Diez-Canseco and L. Silverman (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning, November, 1942, p. 708). * 1--Standard Code for Testing and Rating Steam Unit'Heaters (A.S.H.ViE. Transactions, Vol. 36, 1930, p. 165), adapted January. 1930 by A.S.H.V.E. . A.S.H.V.E. Standard Code for Testing and Rating Steam Unit Ventilators (A.S.H.V.E. Transac tions, Vol. 38, 1932, p. 25), adopted June, 1932. , i*--Discharge Coefficients of Square Edged Orifices for Measuring the Flow of Air, by H. S. Bean, E. Buckingham and P. S. Murphy (Bureau of Standards Journal of Research, Vol. 2, 1929, p. 561). ,7~A.S.H.V.E. Research Report No. 1140--The Use of Air Velocity Meters, by G. L. Tuve, B. K. Wright. Jr. and L. J. Seigel (A.S.H.V.E. Transactions, Vol. 45, 1939, p. 645). . . >*--Flow Measurement by Nozzles and Orifice Plates (A.S.M.E. Power Test Codes, Chapter 4 of Part 5. 1940). . -v - . is--Temperature. Humidity and Air Motion'Effects in Ventilation, by O. W. Armspach and Margaret Ingels (A.S.H.V.E. Transactions, Vol. 28. 1922, p. 103). ' . ' 2--The Heated Thermometer Anemometer, by C. P. Yaglou (Journal Industrial Hygiene and Toxi cology, Vol. 20, October, 1938, No. 8). ` 2,_A.S.H.V.E. Research Report No. 1165--Development of Instruments for the Study of Air Dis-' tribution in Rooms, by A. P. JCratz, A. E. Hershey and R. B. Engdahl (A.S.H.V.E. Transactions, Vol. 46. 1940. p.351). 22--Development of Testing Apparatus for Thermostats, by D. D. Wile (A.S.H.V.E. Transactions. Vol. 42. 1936. p. 349). . 2*--Linear Hot Wire Anemometer, Its Application to Technical Physics, by L. V. King (Journal Franklin Institute, 1916). . .. " 24~A.S.H.V.E. Research Report No. 1204--Entrainment and Jet-Pump Action of Air'Streams, by G. L. Tuve, G. B. Priester and D. K. Wright. Jr. (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 241). 2S_A.S.H.V.E. Research Reports Nos. 857, 911 and 966--Measurement of the Flow of Air Through Registers and Grilles, by L. E. Davies (A.S.H.V.E. Transactions, Vol. 36, 1930, p. 201, Vol. 37, 1931, p. 619, and Vol. 39. 1933, p. 373). .. 2--A.S.H.V.E. Research Report No. 1162---Air Flow Measurements at Intake and Discharge Open ings and Grilles, by G..L. Tuve and D. K. Wright, Jr. (A.S.H.V.E. Transactions, Vol. 46,1940, p. 313). - 27-- A.S.H.V.E. Research Report No. 1092--The Flow of Air Through Exhaust Grilles, by A. M. Greene, Jr. and M. H. Dean (A.S.H.V.E. Transactions, Vol. 44, .1938, p. 387). 28-- A.S.H.V.E. Research Report No. 936--Investigation of Air Outlets in Class Room Ventilation, by G. L. Larson, D. W. Nelson and R. W. Kubasta (A.S.H.V.E. Transactions, Vol. 38, 1932, p. 463). . 2*--A.S.H.V.E. Research Report No. 1076--Air Distribution From Side Wall Outlets, by D. W. Nelson and D. J. Stewart (A.S.H.V.E. Transactions; Vol. 44,1938, p. 77). . 30 Measuring Air Flow, by G. L. Tuve (Healing, Piping and Air Conditioning, December, 1941). , 31 A.S.H.V.E. Research Report. No. 959--Indices of Air Change and Air Distribution, by F. C. Houghten and J. L. Blackshaw (A.S.H.V.E. Transactions, Vol. 39, 1933. p. 261). 33--The Temperature of Evaporation, by Wiliis H. Carrier (A.S.H.V.E. Transactions, Vol: 24, 1918, P- 25). -. 33 Psychrometric Tables for Vapor Pressure. Relative Humidity and Temperatures of the Dew-Point \U. S. Department of Agriculture, Weather Bureau, Washington. D. C.). . ' 34--A Review of Existing Psychrometric Data in Relation to Practical Engineering Problems, by W. H. Carrier an O. Mackey (A.S.M.ti. Transactions, -January, 1937, p. 33; Discussion A .S.M.E. Trans- actions, August, 1937, p. 528). ' '. - . 35--Gas Analysis by Measurement of Thermal Conductivity, by/H. A. Daynes (Cambridge Press, 1933). 214 :, . CHAPTER 11'- 1946 Guide * ^Testing and Rating of Air Cleaning Devices Used for General Ventilation Work, by S. R. Lewis (A.S.H.V.E. Transactions. Vol. 39.1933, p. 277). '. '. **--A.S.H.V:E. Cod^ for Testing and Rating Air Cleaning Devices Used in. General Ventilation Work, adopted January, .1934 (A.S.H.V.E; Transactions. Vol. 39, 1933, p. 225). **--A.S.H.V.E. Standard Test Code for Heat Transmission Through Walls (A.S.H.V.E. Transactions, Vol. 34. 1928. p. 253), adopted 1928. . .' . A.S.H.V.E. Research Report No. 685--Measuring Heat Transmission in'Building Structures and a Heat Transmission Meter,.by P. Nicholls (A.S.H.V.E. Transactions, Vol. 30, 1924, p. 65). 40--Standard Method of Test for Thermal Conductivity of Materials by Means of the Guarded Hot Plate (Tentative), adopted July, 1942,`by A.S.H.V.E.; (A+S.T.M. Designation C177-42T). . .. 41-- Guarded Hot Plate Apparatus Complying With the Requirements of Section 4 of AJi.T.M. Tenta- .. tiye Method of Test for Thermal Conductivity of Materials by Means of the Guarded Hot Plate, AS.T.M. Measurement of the Physical .Properties of the Thermal Environment, by D. W. Nelson. F. R- Bichowsky, L. M. K.' Boelter^R. S. Dill. A. P. Gagge. John A. Goff. A. E. Hershey. F. C. McIntosh, F. W. Reichelderfer, G. L. Tuve and C. P. Yaglou (A.S.H.V.E. Journal Section, Heating, Piping and Atr Conditioning, June, 1942, p. 382). , '' . -. ' 4*--Instruments and Methods for Recording Thermal 'Factors Affecting Human Comfort, by C. P. Yaglou. A. P. Kratz and C.-E. A. Winslow (Year Book. American Journal Public Health, 36-37). *4--The Thermo-Integrator--A New Instrument for the Observation of Thermal Interchanges, by C.-E. A. Winslow and Leonard Greenburg (A.S.H.V.E. Transaction^ Vol. 41, 1935, p. 149). 4--a Carbon Monoxide Recorder, by S. H. Katz, D. A. Reynolds. H. W. Frevert and J. J. Bloomfield (17. S. Bureau of Mines, Technical Paper No. 355, 1926). . /' 4 v CHAPTER 12 Pliy-iiolofyiciii principfeA Chemical Vitiation of Air, Physical Impurities in Air, Thermal Interchanges Between the Body and Its Environment, Adap tation to Environmental Conditions, High Temperature Hazards, Acclimatization, Effective Temperature Index, Relation of Air Conditioning Needs to Metabolism VENTILATION is defined in part as the process of supplying air to, or removing air from, any space by natural or mechanical means. The word in itself implies quantity but not necessarily quality. From the standpoint of. comfort and health, however, the problem is now considered to be one of securing air of the proper quality rather than of supplying only a given quantity. The term air conditioning in its broadest sense implies control of any or all of the physical or chemical qualities of the air. When applied to ' " comfort air conditioning, however, the A.S.H.V.E. Code of Minimum Requirements for Comfort Air Conditioning1 defines it "as the process by which simultaneously the temperature, moisture content, movement and quality of the air in enclosed spaces intended for human occupancy may be maintained within required limits. If ah installation cannot perform all of these functions, ifshall be designated by a name that describes only the function or functions performed." CHEMICAL VITIATION OF AIR , Under the artificial conditions of indoor life, the air undergoes certain physical and chemical changes which are brought about by the occupants . themselves. The oxygen content is somewhat reduced, and the carbon dioxide slightly increased by the respiratory processes. Organic matter, which is usually perceived as odors,.comes from the nose, mouth, skin and clothing. The temperature of the air is increased by the metabolic processes, and the humidity raised by the moisture emitted from the skin and lungs. ' Contrary to old. theories, the usual changes in oxygen and carbon dioxide are of no physiological concern because they are too small to produce appreciable effects even under the worst conditions of, normal . human occupancy. Only in such unusually air-tight enclosures as sub marines and some air raid shelters need the increase in carbon dioxide and the reduction in oxygen be considered.. The amount of carbon dioxide in air is often used as an index of odors of human origin, but the information it affords rarely justifies the labor involved in making .the observation2> *. Little is known of the identity and physiological effects of the organic matter given off in the process of respiration. The former belief that the discomfort experienced in confined spaces was due to some toxic volatile , matter in the expired air is now limited, in . the light of numerous re searches, to the much less dogmatic view that the presence of such, a substance has not been demonstrated. The only certain fact is'that expired air may be odorous, offensive, and capable of producing loss of. _ appetite and a'disinclination for physical activity. Objectionable body ,. dors have the: same effects. These,reasons, whether esthetic or physio logical, usually make it desirable in the design of air conditioning systems, . '" 2/5 " ' '. . 216 CHAPTER 12 11946 Guide to provide for the elimination or control of odors arising from occupancy, cooking, or other sources. This may be accomplished by introducing odor-free air in sufficient quantities to reduce odor concentrations by dilution to a level which is not objectionable. Odor-free air may be outdoor air or air which has been cleared of odors by sorption, washing, or other appropriate means. In the case of vitiation by a few hazardous gases such as carbon mon oxide from heating, cooking, and certain industrial processes, no satis factory chemical treatment for the elimination of the impurity has been found. The only really satisfactory solution is elimination at the source by local exhaust ventilation; or, if this is impossible, reduction to a safe concentration by dilution. (See Chapter 10.) In the case of contami nation by other matter, including volatile vapors and gases, chemical treatment for the removal or reduction of the impurities has been made available through air cleaning methods, which are discussed in Chapter 33 on Air Cleaning Devices. ' When the only source of contamination is the human occupant, the minimum quantity of outdoor air needed appears to be that required' to remove objectionable body odors, or tobacco smoke. The concen tration of body odor in a room, in turn, depends upon a number of factors, including the dietary and Hygienic habits of the occupants (frequently reflecting their socio-economic status), the outdoor air supply, air space allowed per person, odor adsorbing capacity of air conditioning processes, and temperature and relative humidity. Perception of odor has been found to vary as the logarithmic function of the odor intensity, or inversely with the logarithmic function of the amount of outdoor air supplied, and the air space per person. ' The relation between air supply and occupancy has been reported by, the Harvard School of Public Health 3 and the A.S.H.V.E. Research Laboratory 2. The findings from the Harvard study are given in Table 1. Outdoor air requirements for removal'of objectionable tobacco smoke odors are not accurately known but available information and current practice indicate the need of 15 cfm per person or more. ' . The total quantity of outside air to be circulated through an enclosure is governed by both chemical and physical considerations. The physical requirements for controlling temperature, air distribution and air velocity usually predominate. Other factors which must be taken into consideration include the type and usage of the building, locality, climate, height of rooms, floor area, window area, extent of occupancy, and the operation of the system distributing the air supply. Frequently, some of these factors, particularly the need for air movement and good distribu tion, may be satisfied by recirculation of inside rather than by outside air. It will be noted that, with adequate air space, the rate of air change indicated in Table 1 is from 10 to 30 cfm per person. In rooms occupied by only a few persons such a rate of air change will be automatically attained in cold weather by normal leakage around doors and windows, while it can easily be secured in warm weather by the opening of windows. With a space allotment of 400 cu ft per person, only V/i air changes per hour are necessary to provide an air change of 10 cfm per person. . Therefore, in the ordinary dwelling with adequate cubic space allot ment, no special provision for controlling chemical purity of the air is necessary (aside from removal of fumes from heating appliances). For Physiological Principles 217 Table 1. Minimum Outdoor Air Requirements to Remove Objectionable Body Odors 4 Tips or Occupiers Am Space pee ^ Ootdooh Am Supply ' Peeson Cu Ft ` CFM pee Pebsoe Heating season with or without recirculation. Air not conditioned. Sedentary adults of average socio-economic status___ Sedentary adultsof average socio-economic status.__ Sedentary adults of average socio-economic status.__ Sedentary adults of average socio-economic status___ 100 200 300 500 ' 25 16 12 7. Laborers... ,, _ ... ------- ;. -------- ------------- 200 23 Grade school children of average class................ ............ Grade school children of average class___________ ;___ Grade school children of average class....... _______ Grade school children of average class 100 200 300 500 29 21 17 11 Grade school children of poor class__________ _______ 200 . 38 Grade school children of better class...... ......................... 200 18 Grade school, children of best class________________ ___ 100 22 - Heating season. Air humidified by means of centrifugal humidifier. Water atomization rate 8 to 10 gph. Total air circulation SO cfm per person. Sedentary Adults... 200 12 Summer season. Air cooled and dehumidified by means of a spray dehumidifier. Spray water changed daily. Total air circulation SO cfm per person. Sedentary Adults___________ 200 <4 such conditions, the control of air temperature is the major factor to be considered. . . In more crowded rooms (large offices, large workrooms, auditoriums), the whole picture changes. Cubic space per person is less and it is usually impossible to admit untempered outside air without creating drafts. Here, mechanical .ventilation is essential, but as will be noted in . a later paragraph, it is even more essential for thermal than for chemical reasons. It is control of the thermal properties of the air in order to effect the removal of the heat produced by human bodies, rather than* control of chemical properties, which must govern practice. The present data regarding the effect of cubic space on ventilation requirements are not universally accepted. It is anticipated that studies now in progress under the auspices of the armed forces may yield addi tional information on the subject. . " The Code of Minimum Requirements-for Comfort Air Conditioning ! prescribes definite minimum requirements which should be familiar to the designing engineer. It should be emphasized, however, that the pro visions of the code aim to provide minimum, rather than adequate, requirements. ' .. ' Notwithstanding the rapid advance in the field of air conditioning during the past few years; there still remain those who believe in a superior, stimulating quality of outdoor air (particularly country, moun tain and .seashore air) under ideal, weather conditions, as compared with 218 CHAPTER 12 1946 Guide '. properly conditioned air. While this point of view is usually held by , persons not intimately acquainted with the complicated factors involved, r" they nevertheless carry some weight. It is apparent, however, to anyone i acquainted with the factors involved and the conditions effecting comfort, that in modern air conditioning, as in most other branches of engineering, < modern science makes it possible to control the phenomena of nature for ` the service and comfort of man beyond any possibilities found in nature itself. When the requirements for optimum'comfort as determined by the atmospheric environment are known (and the comprehensive studies to date indicate that they are known at least to a high degree), the air conditioning engineer can supply these requirements indoors to the same perfection as may accidentally be found at times outdoors, and keep them . under control. The freedom of movement, action and thought, together with the variability of stimulae experienced by persons under ideal ' conditions in the country, mountains or seashore, and the psychological effect of these wide open spaces undoubtedly have some stimulating effect, which when compared with the monotony of confinement indoors, even in the most favorable atmospheric environment, account for the contrast-. Various experimenters have attempted to duplicate the invigorating qualities of outdoor air by the use of ozone, ionization, or ultra-violet ' light, but results to date have been inconclusive dr negative 6. Ozone has been used with success for the destruction of micro-organisms . (molds) in meat packing establishments and the like; and where con siderable amounts of organic effluvia are present it may be useful as a deodorant. For ordinary ventilation practice! however, neither of these purposes can be attained, since the concentration of ozone necessary for effectiveness would be likely to transcend the limit of comfort in ordinary occupied rooms. While ozone has been used in the treatment of certain diseases, there is no evidence that it has a tendency to increase comfort or - to benefit health under conditions of normal human occupancy. The - allowable concentrations in the breathing zone are very small, between 0.01 to 0.05 ppm parts of air. These, are much too small to influence; ' bacteria.' Higher concentrations are associated with a pungent unpleasant , .odor and considerable, discomfort to the occupants. One part per million causes respiratory discomfort, headaches, depression,' and a lowering of the metabolic rate, and may even lead to coma 6. v , ;' : r ' PHYSICAL IMPURITIES IN AIR ' Dust particles of various types, when present in- considerable con centrations, produce an irritating effect .upon the mucous membranes of nose and throat and may be associated with high prevalence of acute respiratory diseases such as bronchitis and pneumonia. Dust which -contains free silica has special harmful effects, causing a primary disease of the'liings (silicosis) and predisposing the victim'in a high degree, to tuberculosis. These, however, are special problems of industrial hygiene which will not be discussed in detail in this chapter. (See Chapter 10:) ' A certain part of the dissemination of disease in confined spaces is caused by'the emission of pathogenic organisms from infected persons. Droplets sprayed into the air in talking, coughing, sneezing, etc.; do'not all fall immediately to the ground within a few feet from the source, as was . formerly believed. The large droplets fall, but minute droplets less than 0.1 mm in diameter evaporate to dryness before they fall the height, of a.man. Nuclear residues from such sources, which, may contain infective organisms drift long distances with the air currents and the Physiological Principles. '' ' . -;_________________ 219 virus may remain-alive long enough to: be transmitted to other persons in the same room or building. Droplet nuclei have been recovered from cultures of resistant micro-organisms-a week after introduction into a tight chamber of 3000 cu ft capacity, although' the majority of .disease germs died out within a few hours7. Practical epidemiological-evidence indicates that the danger of such atmospheric transmission is slight with the bacterial diseases but may be appreciable with the diseases caused by . the much smaller viruses. Avoidance of overcrowding is a major factor in avoiding such dangers. The microbic concentration in the atmosphere may be reduced by air. change, but. since the rate'of contamination, may be great at local points over short periods of time the hazardous concentra tion may not be eliminated quickly enough and may even be spread.1 over; larger areas by local drafts. The possibility of sterilizing the air supply at the source, or destroying the micro-organisms at their-point of admis sion to the air by the use of ultra-violet light8 or glycol vapors9 is being' studied and'offers considerable promise. . .... .. While in some instances it may be possible to reduce the physical impurities of the air by dilution from a non-contaminated. source, such non-contaminated sources are rarely available. Frequently the outside air contains a higher concentration of physical impurities than that within an enclosure. Therefore, it is usually desirable to reduce the concentra tion of physical impurities by air cleaning methods (see Chapter 33). THERMAL INTERCHANGES BETWEEN THE BODY AND ITS ENVIRONMENT . . . The importance of the thermal factors arises from-the profound in fluence which they exert upon body temperature, comfort and health: Body temperature depends upon the balance between heat production and heat loss. The heat resulting from the oxidation which occurs within the body (metabolism) maintains the body temperature well above that of .the surrounding air in a cool or cold'environment. At the same time, heat is constantly lost from the body by radiation, convection and. evaporation. Since, under ordinary conditions, th,e body temperature is maintained at its normal level of about 98.6 F, the heat production must' be balanced by the.heat loss. . . -. ..In.conditioning air for comfort and health it is necessary to know the rate of. sensible and latent heat liberation from the human body, which in conjunction with other heat loads-(see Chapters 6,. 14 and 15) determines the capacity required for proper conditioning. The data in common: use are those of the A.S.H.V.E. Research Laboratory10. : ,, The fundamental thermodynamic processes concerned in . heat inter changes between the body and its environment may be described by the equation: `" . M= S+E R C (1) where '. ' ' - M = rate of metabolism. 5 = rate of storage. -' : E = fate of evaporative heat loss. R = rate of radiative'heat loss or gain. C = rate of convective heat loss Or gain.' ' ,. '' .... .. . *' Factor M, the rate of metabolism, is always positive. The storage, S, may be either positive or negative, depending upon whether heat is being 220 CHAPTER 12 1946 Guide stored or given off, accompanied by a rise or fall in body temperature. Under ordinary circumstances (when the dew-point of the air is below the body surface temperature) the evaporation loss, E, is always positive;, that is, heat from metabolism supplies this loss, R and C are positive when the surface temperature of the body is above that of the walls and air, and negative when it is cooler. The human body possesses remarkable powers of adaptation to a narrow range of atmospheric conditions around an ideal optimum where storage is zero, and metabolism and skin and tissue temperature are at optimum values. Under these conditions, the body experiences a sensa tion of comfort. As skin temperature and body-tissue temperature rise or fall above or below an optimum, complex adaptive mechanisms come into play, chiefly associated with redistribution of blood supply between the skin and deeper tissues (in a cold environment) and with sweat secretion (in a hot environment). These reactions are governed by nervous or chemical stimuli from both skin arid internal tissues. Nerves from the skin, for example, carry the sense impressions to the brain and the response comes back over another set of nerves, the motor nerves, to the musculature and to all the .active tissues in the body, including the endocrine glands. In this way, a two-sided mechanism controls the body temperature by (1) regulation of internal heat production (chemical regulation), and (2) regulation of heat loss by means of automatic varia tion in the rate of cutaneous circulation and the operation of the sweat glands (physical regulation). The reactions involved in cold and in hot environments are on the whole radically different in nature. The mech anisms of adjustment involved are extremely complex and, while they are receiving considerable study, a complete understanding of their operation is still lacking. '. . -. Some of the phenomena of body temperature control are shown graphically in Fig. 1. The dotted curves, from a study at the John B. Pierce Laboratory of Hygiene11, are for subjects lightly clothed in a semi- reclining position and give the relation between the dry-bulb temperature of the environment (with about 45 per cent relative humidity) and the metabolic rate, the rate of heat dissipation by radiation and convection combined, and the latent heat loss due to evaporation of perspiration and moisture from the respiratory tract. The smooth line curves from the work of the A.S.H.V.E. Research Laboratory 10 give the same relationships for healthy, male subjects (18 to 24 years of age), seated at rest and normally clothed for winter-heated and air conditioned occu pancy. The data for the semi-reclining subjects also include the rate of heat storage (either positive or negative) due to a rise or fall in body temperature. For the normally clothed subjects, a curve gives the total heat loss (that is, the sum of the radiation, convection and evaporative losses). Here, storage is given by the difference between the metabolism and total heat loss. - The small difference between the metabolic or heat production rates for the two types of subjects may be accounted for by the difference in activity. Heat exchange between the body and the environment by radiation and convection is greater for the lightly clothed subject, both for cool con ditions where there is considerable heat loss, and for very warm conditions where there is sensible transfer from the atmosphere to the body. The two curves for evaporative loss serve to show how physiological control uses evaporation of perspiration to maintain equilibrium, particularly at high temperatures. Below about 75 F for the normally clothed subject, Physiological Principles 221 and below about 85 F for the lightly clothed subject, evaporation loss is minimal and probably due to uncontrolled evaporation from the relatively dry skin and from the respiratory tract. Above these temperatures con trol is obtained by the availability of perspiration for evaporation. The difference in the curves above 75 F is probably largely determined by the difference in clothing and activity. Above temperatures from 95 to 100 F (the probable average outside surface temperature of the clothed body) the combined effect of radiation and convection causes a change from positive to negative. Slightly above this temperature even the greatly increased latent heat loss ceases to take care of the rate of heat production plus the negative radiation and convection loss, and heat storage occurs with a consequent rise in body. temperature. Above this range, even Fig. 1. Relation Between Metabolism, Storage, Evaporation, Radiation Plus Convection, and Operative Temperature for the Clothed Subject though there is inability to dissipate heat rapidly enough, metabolism actually increases. This may be accounted for by the predominance of the purely chemical laws of increased chemical reaction with rise in' temperature, over physiological control, and indicates the point where a breakdown in thermal equilibrium begins. For'higher, temperatures life can only, survive to the point where these accelerated processes will result in a rise in body temperature to the limiting level of from 106 to 108 F. Air movement is an important factor in increasing heat loss by either convection or evaporation. The result is accomplished through removal of hot humid air from near the body surface and replacing it with cooler and relatively drier air. This-is an important factor in maintaining thermal equilibrium either for persons at rest or at work in hot, humid conditions. For conditions in the comfort zone and'below, excessive velocities (particularly localized drafts) should be avoided since differ ential cooling of one area of the body may produce surprisingly unpleasant, reactions in quite different parts of the body. In one experiment12 it was shown that the application of an ice pack to an area of 60 sq cm.'on the back of the neck for 15 min caused a drop of 17 F in the skin temperature 222 CHAPTER 12 1946 Guide .. of the fingers and that this low temperature of the fingers-persisted for. one hour after the ice pack was removed: ' . ADAPTATION TO ENVIRONMENTAL CONDITIONS As stated previously, the optimum environmental conditions for com fort are those under which the body can maintain complete thermal equilibrium with only minor adjustments in blood, distribution. As . conditions depart from the optimum, more drastic adjustments are made by the body in its attempt to maintain equilibrium, and the sensation of comfort gives way to one of.increasing discomfort. If conditions.are too severe, adequate adjustments may be impossible, and prolonged exposure may result in serious injury or death. In a cold environment the blood vessels leading, to the surface are constricted, thus decreasing the flow of blood and heat to the skin, and reducing the radiation and convection losses from it. If this adjustment is insufficient, an involuntary muscular activity (shivering) takes place which increases the metabolism. The range over which these physiologi cal controls are effective is rather narrow, and .man's existence in cold climates is dependent upon his-ability to provide himself with heated ' living quarters and warm clothes. During the last few years extensive research has been carried on by and for the armed services of the United Nations to determine the proper types and amounts of clothing for a wide range of conditions. The results of these studies are now being released and should add greatly to our knowledge on the subject. As man's environment changes from cool or comfortable to warm, the ' body first attempts to adjust to the new conditions-by a redistribution of the blood circulation. Blood capillaries near the surface become dilated, . allowing more blood to flow to the skin, thus raising the skin temperature - and increasing the radiation and convection losses from the body. If this correction proves inadequate, the stimulus is extended to the sweat glands which cause progressively greater portions of the body area to become moist or wet as conditions become more severe. The evaporation of this . moisture from the body surface provides the body with its most effective method of cooling, but even this fails when the dew-point temperature of the air becomes so high that rapid evaporation is no longer possible. Although -the body is able, by evaporative cooling, to maintain complete thermal balance under conditions of moderate excess, it does so only at the cost of considerable discomfort. - \- . Studies at the John B. Pierce laboratory of Hygiene 13 have indicated the relation!between discomfort and the degree of wetting of the body surface by perspiration for lightly clothed subjects in a semi-reclining position, and the investigators there have designated this as the zone of evaporative regulation. The relation between sensible perspiration and the atmospheric environment for normal persons at rest and at work- has-been determined at the A.S.H.V.E. Research Laboratory 10. ' . HIGH TEMPERATURE HAZARDS Studies at the A.S.H.V.E. Research Laboratory 14 and elsewhere15 during the past two decades have made available a mass of information dealing.with the physiological effects of, hot atmospheres on workers.and . means of alleviating the distress and hazards associated-therewith. This Physiological Principles- 223 interest has been termed air conditioning in industry, or the effects of hot atmospheres in industrial hygiene, and is a growing factor in air conditioning applications. Table 2 gives some of the,physiological responses of men at rest and at work, to hot environments. Physiological studies 16 indicated that frequent and continued exposure of workers to hot environments results in physiological derangement affecting the leucocyte count of the blood, and other factors dealing with man's mechanism of defense against infection. . In hot environments the blood is diverted from the internal'organs to the surface capillaries, in order to serve in the process of cooling. This affects the stomach, heart, lungs and other.vital organs, and it is suggested that the feeling of lassitude and discomfort experienced is due in part to the anaemic condition of the brain. The stomach loses some of its power Table 2. Physiological Responses to Heat of,Men at Rest and at Work3 Effective Trap 60 70 80 85 90 . 95 too 105 110 Actual Cheek Trap (PtRR Deo) . 96.1 96.6 97.0 97.6 99.6 104.7 ---- Men at Rest i Men at Wore . 90.000 ft-lb or Wore per Hour . Rise in Rectal Temp . (Fahr Deg per Hr) Increase io Pulse Rate . (Beats pa Min pa Approximate Loss is Body Weigbtby ' Perspiration (Lb per Hr) . Hr) Total Work Accomplished j (Ft-Lb) Rise in Body Temp (Fahr Deg . pa Hr) Increase io Pulse Rate (Beats pa Min pa Hr) Approximate Loss in Body. Wt by Pa* spiration (Lb pa Hr) - 0.0 0.0 0.1 0.3 0.9 2.2 4.0 5!9l> -6 0 1 4 15 40 83 137*> o'! 0.3 0.4 0.5 0.9 1.7 2.7 4.o> '225.000- 225.000 209.000 - 190.000 153.000 102.000 67.000 49.000 - 37.000 0.0 . 0.1 0.3 - 0.6 1.2 2.3 4.0b 6.0b 8.5b 6' .7 11 17 31 61 103b 158b 237b 0.5 0.6 0.8 1.1 1.5 .2.0. 2.7b 3.5b 4.4b Data by A.S.H.V.E. Research Laboratory. - . ^Computed value from exposures lasting-less than one hour. to act upon the food, owing to a diminished secretion.of gastric juice, and there is a corresponding'loss in'the antiseptic and antifermentive , action which'favors, the growth'of bacteria in the'intestinal tract17. These are considered to be the potent factors in: the increased suscepti- , bility to gastro-intestinal disorders in hot summer weather. . . In warm atmospheres, particularly during physical,work, a considerable amount of chloride is'lost fromthe system through:sweating. . The loss of this substance may cause excessive fatigue,ror.may lead to attacks of cramps, unless the salts are replaced.. 'In order to.'relieve both cramps and fatigue, it is recommended that salt tablets be taken, or that sufficient salt be added, to the drinking water to provide a'*/i* of 1 per cent saline solution18. ' , .. ........ . " . , ; . . - -. . ; ' The deleterious physiologic effects of high temperatures exert a power-' ful influence upon physical .activity,, accidents; .sickness and mortality. Both-laboratory and field data show that physical work in warm atmos- . . pheres is a great effort, and that production falls progressively as the tem perature rises. The incidence of industrial accidents reaches a minimum at about 68 F, increasing above and below that temperature. Sickness and mortality rates increase progressively as ithe temperature rises. . Diseases due to heat are now classified as heat exhaustion, heat cramps, S 224 HEAT CHAPTER 12 1946'Guide Increased Metabolism Failure to Sweat Derangement of Heat Regulatory Center HEAT STROKE .( BODY--------- INCREASED BODY TEMPERATURE Vasodilation . .y ` AfcCLIMATIZATION -<--------- SWEATING ' Increased Ability to Sweat Salt Economy Increased Circulation to Skin Increased Pulse Rate Temporary Loss of Blood Volume Circulatory Insufficiency ' . --------------------------------------------*- HEAT EXHAUSTION Decreased Metabolic Rate Maintenance of Normal Body Temperature Excess Water Loss ' -----------------------------------------SUPER DEHYDRATION Excess Salt Loss HEAT CRAMPS Fig. 2. Physical Effects of Overheating and Acclimatization and heat strokes 10. Heat exhaustion is due to circulatory failure; heat cramps to excessive loss of body chlorides and heat stroke to dn inade- . quacy of the heat dissipating mechanism which results in hyperthermia (high fever) (See Fig. 2). If the hyperthermia becomes excessive, the liver and the central nervous system may be seriously injured and this damage may prove fatal. The hazards of jiigh temperature are not understood. It is difficult to say whether short exposures at high tem peratures are more harmful than longer exposures at lower temperatures. A new concept is evident from the observation of an increase in leucocytes ' (white cells) of the blood in workers subjected to high temperatures.. These leucocytes are defensive factors which are increased when infection invades the body. A rise in temperature and leucocyte count indicates a mobilization of the body defenses. Since both' temperature and cell count are increased20, the question arises as to whether long exposures to very high-temperatures might not cause exhaustion of these defense mechanisms. . A study was made recently at the: Armored Medical Research Laboratory21 to determine the upper limits of environmental conditions under' which a man can perform certain work. Thirteen enlisted men, . who were first thoroughly acclimatized to the hot conditions, served as Physiological Principles~ '______________________ ';225 Table 3. Upper Limits of Environmental Conditions for Acclimatized, - Healthy, Young Men in Military Service ' Environment Reactions at the end of 4 hr Rectal Temp F Pulse rate. Relatively Easy................................... Below 101 Difficult................................................... 101 to 102 Impossible.---------- ---- :..............,------- ' Above 102 Below 130 130 to 145 Over 145 . subjects. During each test, the subjects were required to march for 4 hr at the rate of 3 mph, carrying 20 lb packs. Tests were made under a wide range' of environmental conditions, and these environments were rated in 3. zones as relatively easy, difficult, and impossible, on the basis of the physiological reactions of the subjects at the end of the 4 hr period as shown in Table 3. Fig. 3 shows the limits of the three environ mental zones. ' . Recognition of the need of air conditioning for workers in hot indus tries is growing rapidly and this should become an important field for the air conditioning, engineer. The hot conditions may be remedied by any of the recognized comfort cooling applications. The choice of the type Of system and cycle to be used in a given instance must be determined by the air conditioning engineer.after a study of surrounding conditions. ` In some hot industries where a small number of workers are engaged in spaces of large volumetric capacity the worker himself, rather than the Fig. 3. The Endurance of Environmental Conditions by Acclimatized . Subjects Working at a Specific Rate From The Upper Limits of Environmental Heat and Humidity Tolerated by Acclimatized Men Work ing in' Hot Environments (Journal of Industrial Hygiene and Toxicology, March, 145, p. 70). Used by> permission. . ' ' ' ` ' ' .. . 226 CHAPTER 12 1946 Guide entire environment, can be cpoled by placing him in a small cooled and ventilated booth, by blowing cooled air over him, or by circulating cooled air through a loose-fitting suit22. ACCLIMATIZATION Acclimatization and the factor of psychology are two important influences in air conditioning which cannot be ignored. The first is man's ability to adapt himself to changes in air conditions; the second is an intangible matter of habit and suggestion. ' . Some persons regard the unnecessary endurance of cold as a virtue. They believe that the human organism can adapt itself to a wide range of air conditions with no apparent discomfort or injury to health. In the light of present knowledge of air conditioning these views are not justified. Acclimatization to extreme conditions involves a' strain upon the heat regulating system and interferes with the normal physiologic functions of the human body. Thousands of years in the heat of Africa do not seem to have acclimatized the Negro to a temperature exceeding 80 F. The same holds true of northern races with respect to cold, although the effects are. mitigated by artificial control. An environment averaging 64 F for the 24-hour period has been indicated as associated with minimal mortality23. . Within limits, however, there dpes occur a definite adaptation to ex ternal temperature level. People and anifnals raised under conditions of. tropical moist heat stand chilling poorly as they,are unable quickly to increase internal combustion to keep up the body temperature. For this reason they have trouble standing the cold, stormy weather of the tem perate zones, and when exposed to it are very susceptible to respiratory infections. Likewise, people living in icool climates suffer greatly in the moist heat of the tropics until their adaptive mechanism has been adj usted. Within a few years, however, they find themselves reacting as natives . to the new environment. . The. adaptive level changes tomewhat with the season 24. There are also marked differences between the sexes. In the cold zone the thickness of thermal insulating tissues of women is almost double that of men, although the. sensory responses to cold are similar. In the hot zone, the threshold of sweating'and skin temperature levels are higher for women. The thickness and insulating value of the clothing worn is also an import ant factor in the determination of the- comfort level. . In recent tests made at the A.S.H.V.E. Research Laboratory a, sub jects were required to perform .light work under very hot conditions for a four hour period each day. It was found that the ability of a new subject , to endure these conditions showed daily improvement for a period of at least two weeks. However, after acclimatization wais completed, a recess of several days had no effect on the endurance of the subject. EFFECTIVE TEMPERATURE INDEX The primary purpose, of comfort air conditioning is to provide an environment in which the body can easily maintain, its thermal equili-' brium, and thereby experience a: feeling of-comfort. It is important, Physiological Principles' *____________________ _________ ' 227, . therefore, that the designing engineer know what conditions are necessary for comfort. ' .. Sensations of warmth or cold depend, not only on the temperature of. the surrounding air as registered by a dfy-bulb thermometer, but also upon the temperature indicated by a wet-biilb thermometer., upon air movement and upon radiation effects. - Dry air at a relatively high temperature may feel cooler than air of considerably lower temperature with a high moisture'content. Air motion makes any moderate condition feel cooler. Radiation to cold or from warm surfaces is another important factor- under certain conditions. ... Combinations of temperature, humidity, and air movement which induce the same feeling of warmth are called thermo-equivalen t condi- lions. A series of studies 26 at the A.S.H.V.E. Research Laboratory established the equivalent conditions met with in general air conditioning, work. This scale of thermo-equivalent conditions not only indicates the sensation of warmth, but also to a considerable degree determines the physiological effects on the body induced by heat or cold. For this reason, it is called the effective temperature scale or index, and it denotes sensory heat level. .. ' Effective temperature is an empirically determined index of the degree of warmth perceived on-exposure to different combinations of temperature, humidity, and air movement.; It was determined by trained subjects who compared the relative warmth of various air conditions in two adjoining conditioned rooms by passing back and forth from one room to the other. The numerical value of the index for any given air conditions is fixed by the temperature of slowly moving (15 to 25 fpm air movement) saturated air which induces a like sensation.of warmth or cold. Thus, any air condition has an effective temperature of .6.0 deg, when it induces a sensation of warmth like that experienced in slowly moving air at 60 deg saturated with moisture. The effective temperature index cannot be measured directly but is determined from dry- and wet-bulb temperature and air motion observations by reference to an Effective Temperature Chart (see Figs. 4, 5.and 6) or tables. , Fig. 4 gives the effective temperature for any combination of dry- and wet-bulb temperatures for still air (15 to 25 fpm) conditions. Charts similar to Fig. 4 for air velocities of 300 and 500 fpm have been presented in some of the earlier editions of the Guide. Fig. 5 is another form of effective temperature chart embodying all three variables; dry-bulb and wet-bulb temperatures, and air velocity. ' As stated previously, effective temperature is an index of the degree of warmth experienced by the.body. An effective temperature line is, there fore, a. line defining the various combinations of conditions which will induce like sensations of warmth.. It does not necessarily follow that like . sensations of comfort will also be experienced along the entire length of an effective temperature line. Some degree of discomfort is likely to be' experienced at very high or very low relative humidities, regardless of the effective temperature. It has also been found that the optimum effective temperature varies with the season, and is lower in winter than in summer. Fig. 6, commonly referred to as the Comfort Chart27, is an effective temperature chart on which the summer and winter comfort zones have been indicated. These zones indicate the various combinations of con ditions under which 50 per cent or more of the people are comfortable. Curves showing the percentage of subjects comfortable at each effective 228 CHAPTER 12 1946 Guide temperature in summer'and winter have been added to the chart. The;, summer comfort zone is indicated as extending from 66 ET to 75 ET with a maximum of 98 per cent comfortable at 71 ET. The winter comfort zone extends from 63 ET to 71 ET with a maximum of 97 per cent comfortable at 66 ET. The 71 ET and 66 ET lines are referred to, .respectively, as the summer and winter comfort lines. The comfort zones and lines as shown in Fig. 6 are based on research prior to 1932. Later studies 28 by the A.S.H.V.E. Research Laboratory Physiological Principles 229 GRAINS OF MOISTURE PER POUND OF DRY AIR indicate a desirable winter effective temperature of 67 deg, and this finding is confirmed by current practice. The shape of the curve showing the per cent of subjects comfortable in winter also justifies this conclusion, since a drop of only one degree from the 66 ET line seriously reduced the percentage of subjects comfortable. The comfort zones in Fig. 6 are located between the 30 per cent and 70 per cent relative humidity lines. There is some evidence that the zones could be extended somewhat beyond these, limitations. . It should be emphasized that a satisfactory system will not necessarily result by designing for just any combination of conditions within the .boundaries of the comfort zone. As pointed out, the comfort zone.covers all conditions under which 50 per cent or more of the subjects were com- ' fortable. An air conditioning system which leaves 50 per cent of the Fig. 5. Effective Temperature Chart Showing Normal Scale of. Effective Temperature. Applicable to Inhabitants of the United States Under ' Following Conditions: ... A. Clothing: Customary indoor clothing. B. Activity: Sedentary or light muscular work. C. Heating Methods: Convection type, ijt., warm air, direct steam or hot water radiators, plenum systems, ' . 230 CHAPTER 12 ' \ 1916 Guide ' Physiological Principles 231 rooni itself and objects within the room, including windows, heating and cooling equipment, and other occupants, has an important bearing, on the feeling of warmth and may alter to some measurable degree the optimum conditions for comfort previously indicated. Fig. 7 29 shows the elevation in the dry-bulb temperature of the air necessary to compensate for the lower temperature ofcthree of four side-wall surfaces, and indicates that for this condition each degree reduction in the average of the three wail surface temperatures requires an elevation of 0.3 deg in the dry-bulb temperature of the air. Studies by the A.S.H.V.E. Research Laboratory 28 .on the effect of radiation within an enclosure, including the effect of panel heatingT indicate that each degree elevation or depression of the mean ' Fig. 6. A.S.H.V.E. Comfort Chart for Still Air Note.---Both summer and winter comfort zones apply to inhabitants of the United States only. Applica tion of winter comfort line is further limited to rooms heated by central station systems of the convection type. The line does not apply to rooms heated by radiant methods. Application of summer comfort line is limited to homes, offices and the like, where the occupants become fully adapted to the artificial air con-' ditionsT The line does not apply to theaters, department stores, and the like where the exposure is less than 3 hours. The optimum summer comfort line shown pertains to Pitmburgh and to other cities in the northern -portion of the United Stated and Southern Canada, and at elevations not in excess of 1000 ft above sea level. An increase of one deg ET should be made approximately per 5 deg reduction in north latitude. ' people uncomfortable would not be acceptable. Systems should be designed to assure comfort for the maximum possible number. The results of recent tests 25 made at the A.S.H.V.E. Research Labora tory in very hot conditions with subjects doing light work.were'in very close agreement with the effective temperature chart. Other recent work21 under similar environmental conditions, but with subjects walking 3. mph and carrying 20 lb packs indicated that the effective temperature lines should be more nearly, horizontal. It therefore appears that the slope of the ET lines may vary depending upon the rate of work being per formed. " Radiation between the occupant of an enclosure and the surfaces.of the Fig. 7. Cooling Effect of Three Cold Walls in a Small Experimental Room, as Determined by Comparison with Sensations in a Room of Uniform , Wall and Air Temperature radiant temperature above or below the air temperature requires about 0.5 deg counterchange in effective temperature of the air. Since the mean radiant temperature of a space is affected by cold walls and win dows, as well as by the warm surfaces of heating units placed within the ' room or imbedded in the walls, these factors' must. be compensated. Likewise, in densely occupied spaces, such as classrooms, theaters'and auditoriums, temperatures somewhat lower than, those indicated 'by. the comfort line may be desirable because of counter-radiation between the bodies of occupants in close proximity to each other. Such radiation will also elevate the mean radiant temperature of the room. ''More recent tests25 made at the A.S.H.V.E. Research Laboratory indicate that for high effective temperatures the correction in ET neces sary per degree rise in mean radiant temperature is'not a constant, but varies with the values of effective temperature and mean radiant tem perature. At effective temperatures near the upper limit of human endurance, the' effect of radiant heat is very small. Additional studies on the physiological effects of radiant heating are contemplated. ' - 232 CHAPTER 12 1946 Guide A long series of studies have been made to determine the optimum effective temperature for comfort of normal persons in both winter and . summer- air conditioned space, in different geographical regions and for different age groups of men and women. A group of these studies30 was made between 1935 and 1940 by the A.S.H.V.E. Research Laboratory in Pittsburgh, and in several metropolitan districts of^he United States andCanada in cooperation with the managements.of offices employing large numbers of workers. Some of the results are shown in Fig. 8. Taking all of these studies together, women of all age groups studied indicate an ' average effective temperature for comfort 1.1 deg higher than for men. All men and women, beyond the age of 40 years, show an average desire Fig. 8. Relation Between Effective Temperature and Percentage Observations Indicating Comfort for ,0.9 deg ET. higher than, those below this age, while the men and women,-respectively, beyond 40 desired effective temperatures of 0-8 and 1.2 deg higher than those below 40. The persons serving in all of these studies were representative of office workers clothed for air conditioned space in the summer season and engaged in the customary sedentary activity of office workers. . ' '. On the basis of present knowledge, for different geographical regions and age groups, the total spread in optimum comfort conditions ranges from a low of 66 deg ET for winter heating and air conditioning, to a high of 73 deg ET for summer cooling and air conditioning. The spread for summer cooling and air conditioning for optimum com fort is confined entirely to an effective temperature range of from '69 to ' 73 deg; and it may be presumed that for winter conditioning a like spread wouid exist; while for inter-seasonal conditions there will be a fluctuation, between these two ranges. . .. Physiological Principles 233 . Laboratory studies 28 indicate that for the average individual a tem perature change of about 3 deg ET is required to change a: person's sensation from ideally comfortable to cool or warm. From this it may be observed that necessary variations in the effective temperature of air conditioned space for optimum comfort for most persons need little differ entiation for either the winter season or the summer season, and not more than about 4 deg on the average between seasons. - Acclimatization and habits of clothing and diet account for these variations. An analysis 31 of most of the material published up to 1942, made by the A.S.H.V.E. Technical Advisory Committee on Sensations of Comfort, indicates a spread of approximately 3 deg in the optimum effective temperature for summer cooling and air conditioning due to geographical location. However, it should be recognized that variations in sensation of. comfort among individuals may be greater for any given location, as shown in Fig. 8, than variations due to a difference in geo graphical location. The available information indicates rather clearly that changes in weather conditions over a period of a few days do not acclimate people to a desire for different indoor conditions, but in general, people experiencing low temperatures over an extended period of time become acclimated to desiring lower indoor temperatures, while those experiencing higher temperatures become acclimated to a desire for higher indoor temperatures. It is obvious that a person spending a considerable portion of his time in space conditioned to his comfort will become acclimated to his indoor, environment. While few people spend more, than a small percentage of the total time within an air conditioned enclosure, there is some evidence that persons experiencing summer comfort air conditioning a large part of the time tend to become acclimated to about 70 or 71 deg ET. _ The sudden sensation of coldness felt by persons entering a cooled and air conditioned space during the summer months, and often referred to as shock, may at times be important. It is due to the rapid evapora tion of perspiration which accumulated on the skin during previous subjection to hot and humid, outside conditions. While studies32 have shown that for healthy individuals this shock is usually a pleasant ex perience, it is plausible, but not proven, that under some conditions it may result in unpleasant or even'harmful cooling. Where a large number of occupants may enter for only a short'time, 15 min or less, such occu pants may-be satisfied with less cooling. For -long occupancy very little deviation from the optimum effective temperature is desirable. : An exit shock when leaving air. conditioned space and entering, a warm- atmosphere is equally plausible. Experiments at the A.S.H.VIE."Research! Laboratory 83 indicated no demonstrable harm to a healthy individual: Complete acclimatization occurred as soon as normal perspiration was established, in 5 to 15 min and mild exercise shortened the time required. Satisfactory comfort conditions for persons at work 34 are found to vary depending upon the rate of work and the amount of clothing worn. Iri general, the greater the degree of activity, the lower the effective tempera ture necessary for optimum comfort. However; work by the A.S.H.V.E: Research Laboratory 35 indicates that under certain conditions moderate' activity on the part of a person standing up and moving about may result in a slightly higher optimum effective temperature than for a person seated at rest, because of the larger body surface area exposed for heat elimination and the increase in 'effective air movement over, his body.' Where few workers occupy a large space in hot industries,-work by -the 234 CHAPTER 12_______________ . 1. . .1946 Guide A.S.H.V.E. Research Laboratory 27 shows that they may be made reason ably comfortable by blowing relatively small volumes of slightly cooled air over them or .through their clothing. .. For prematurely born infants, the optimum temperature varies from 100 to 75 F, depending upon the stage of development. The optimum relative humidity for these infants is placed at 65 per cent **. No data are yet available on the optimum air conditions for full term infants and 9. Loss- Fig, Relation Between Total Heat from the Human Body and -.... , Effective Temperature for Still Air . . .... , , * . . aCurve idv--Persons worklng so as to have a metabolic rate.of 1310 Btu. per hour. :Curve B-^-Persons working so as to have a metabolic,rate of 850 Btu per'hour. Curve C--Persona working so.as to.have a metabolic rate of 860 Btu per hour.Curve Persons seated at rest, or with a metabolic rate of 400'Btu' per hour. Curves B and D based on test data covering a wide,temperatore range. Curves A and C based * on. testrdata at;an' Effective Temperature of 70 deg and extrapolation'of Curves-'B and All curved are averages ofrvalues for hi^h and low relative humidities which apply with satisfactory accuracy for most considerations.. For special problems requiring a higher degree of accuracy see more detailed A.S.H.V.E, - Research, Laboratory .reports.. . . `' young children upi to school age. Satisfactory air conditions for-these age groups.are assumed to vary from 75 to 68F with natural indoor humidities. For children (haying, high, metabolism) at school, in winter clothes, 70-E has. been; considered correct, while in a gymnasium 55 F has been recom mended.- A great number of persons seem to be fairly content in.summer with a .higher plane of, indoor, temperature;,particularly when the matter of .first.,cost and operating cost of a cooling plant is given due considera tion...,,Studies, by the. University of Illinois 57 in cooperation with;the A.S.H.V.E, .Committee on; Research indicate that effective temperatures i as: high;as 74.5 deg, are acceptable in the living quarters of a. residence,. mid while, this condition, is not representative of optimum comfort it 236 CHAPTER 12 1946 Guide provides sufficient relief in hot weather to be acceptable to the majority of users, ft should 'be emphasized, however, that these are borderline cases that may be acceptable largely in the interest of economy. Com prehensive studies by the A.S.H.V.E. Research Laboratory 30 in coopera tion with office staffs in widely distributed regions, including San Antonio, Minneapolis, Washington, D. C., and New York City (see Fig. 7), show conclusively that lower effective temperatures are required for optimum comfort. - The sensation of comfort, insofar as the physical environment is con cerned, is not absolute but varies considerably among certain individuals. Therefore, in applying,the air conditions indicated, it should not be, expected that all the occupants of a room will feel perfectly comfortable. Fig. 12. . Chart for Determining Surface Area of Individuals for Height and Weight Given However, when optimum comfort temperatures are applied in accordance with foregoing recommendations, the majority of the occupants should be comfortable, and it should be expected that there, will be a few too warm and a few too cold. These individual differences among the min ority should be counteracted by suitable clothing. ' RELATION OF AIR CONDITIONING NEEDS TO METABOLISM To maintain optimum conditions in summertime requires the removal, of heat from the conditioned space. In calculating the cooling load it is always necessary to consider the heat given up'by the occupants. In theaters or similarly densely populated spaces, the occupants may con-. tribute the greater part of the total load. . The metabolic rate varies with the size of the individual, with the rate of work being performed, and at extreme conditions, with the environ ment. The relative proportions of sensible and latent heat given off also yary widely. The curves in Fig. 9 show the total heat loss (sensible plus.latent) from the average man for four different rates of work. Heatloss iii this figure is plotted against effective temperature. . Figs, lOand 11 give the sensible and latent losses for the same four work rates,, plotted against dry-bulb temperature. By proper interpolation, it is possible Physiological Principles 237 4.Table Relation Between Metabolic Rate and Activity a- Hourlt Metabolic Bats for Avg Person or Total Heat . Dissipated, Btu per hour Hourlt Hourly Sensible Latent Heat Did* HEAT DIS SXPATED, at 79 F, Btu per Hour SIPATED, Btu perHour Moisture . Dissipated pee Hour per Person Grains Pounds Basal.:-- Seated at RestReading Aloud (Seated)- Standing at RestHand Sewing (Seated)--------Knitting 23 stitches per minute on Sweater 291 384 420 431 441 462 Dressing and Undressing.-------------------------------- Tailor.------------------------- ------------------------------------Singing.-- Office Worker Moderately ActiveLight Work Standing---------------------- 468 482 486 490 549 Typewriting Rapidly.---------------------- 558 Ironing with 5 lb iron-- Dishwashing--Plates, Bowls, Cups and Saucers 570 .600 Clerk Moderately Active Standing at Counter. 600 Book Binder.---------------------------------------------- ------Shoemaker. Sweeping Bare Floor 38 Strokes per Minute.... 626 661 672 Pool Player. 680 Walking 2 mph, Light Dancing.----------------------- 761 Light Metal Worker (at Bench)----------------------- 862. Painter of Furniture (at Bench).,-------------- ---. 876 Carpenter. 954 Restaurant Serving : 1000 Pulling Weight-------Walking 3 mph------- - 1041 1050 1390 Walking Down Stairs.. 1444 Stone Mason--:----------- BowlingMan Sawing Wood-- 1490 1500 1800 Swimming.------------------ 1986 Running 5.3 mph-------- 2268 Walking 5 mph.. 2330 Walking Very Fast 5.3 mph 2580 Walking Upstairs- 4365 Maximum Exertion Different People.----- --------. 3000-4800 145 225 225 225 225 225 225 225 225 225 225 225 225 225 225 225 225 229 230 250 277 280 307 325 335 339 452 467 485 490 5_9_0 ... 145 978 159. 1072 195 1315 206 1389 216 1457 237 1598 243 1639 257 1733 261 1760 265 1787 324 2185 333 2246 345 2326 375 2529 375 2529 401 2704 , 436 2940 443 2987 450 3055 511 3446 585 3945 596 4019 647. 4363 . 675 4552 708 4774 711 4795 938 6325 977 6588 1005 67.77 1010 6811 _12_10 . 8160 0.140 0.153 0.188 0.198 0.208 0.228 0.234 0.248 0.251 0.255 0.312 0.321 0.332 0.361 0.361 0.386 0.420 0.427 0.434 0.492 0.564 0.574 0.623 0.650 0.682 0.685 0.904 0.941 .0.968 0.973 1.166 .......... "These metabolic rates were compiled by the A.S.H.V.E. Research Laboratory from actual tests, from other authoritative sources, and from estimates based upon various considerations. ^ Division of .the total heat dissipation into latent and sensible rates is based on actual test data and on various considerations for metabolic rates up to 1250 Btu per hour, and extrapolated for. higher rates. Values for total beat dissipa tion for a person at rest apply for a dry-bulb temperature range from approximately 60 to 90 F;-for other than rest conditions the values apply for a similar but lower temperature range. Below these temperature ranges metabolic rates and total rates of heat dissipation increase, while above these ranges metabolic rates increase slightly and total heat dissipation rates decrease rapidly.- Division of total dissipation rates into sensible and latent heat holds only for a dry-bulb temperature of 79 F. For lower temperatures, sensible heat dissipation increases and latent heat decreases, while for higher temperatures the reverse is true. - from Figs. 9, 10 and 11, to determine the sensible and latent heat dissi pation for any work rate and any environmental condition, provided the metabolic rate is known at one elective temperature. For example, if it is found that a certain type of work results in a metabolic rate of approximately 760 Btu per hour for an average person working in an atmosphere of 70 ET, then this total rate of heat dissipation to atmos pheres of various temperatures will be approximately as given by the broken-line curve in Fig. 9. The broken line curves in Figs. 10 and 11 give-. the rate of sensible and latent heat dissipation of the person for different, dry-bulb temperatures. The metabolic rates for a number of types of: 238 CHAPTER 12 1946 Guide work are given in Table 4, and may be plotted in this manner on the figures. ; ' . -............" - . It should be noted that metabolic rates are proportioned to the body surface areas of the persons considered, and that the data given in Table 4 and Figs. Q.10 and 11 are for persons having an average surface area of 19 5 sq ft, or that of the average American male 5 ft 8 in. high and weigh ing 150 lb. | Therefore, these data will not apply to many audiences made. up largely of women or younger persons. Fig. 12, taken from the work of DuBois ", gives the relation of body surface area to height and weight, and may serve .to correct the data for groups of various types. .' REFERENCES _ ^"Cdeof Minimum Requirements for Comfort Air Conditioning (A.S.H.V.E. Transactions, VoI. 44. ' 1938,.p. 27). : : . * _ *tA.S.H,V.E. Research Report No. 959--Indices of Air Change and Air Distribution, by R C. Houghten ahd J. L. Blackshaw (A.S.H.V.E. Transactions, Vol. 39, 1933, p. 261). . ' , *^A.S.H.V.E. Research Report No. 1031--Ventilation Requirements, by C. P. Yaglou. E. C. Riley' and D. J. Coggins (A.S.H.V.E. Transactions, Vol. 42, 1936, p. 133). .. '/ 4~Loc. Cit. Note 3, p. 156. _ .? ' btA.S.H.V.E. Research Report No. 921--Changes in Ionic Content in Occupied Rooms, Ventilated by Natural and1 Mechanical Methods, by C. P. Yaglou. L. C. Benjamin and S. P. Choate (A.S.H.V.E. - Transactions, -Vol. 38, 1932, ,p. 191). A.S.H.V.E. Research Report No. 965--Physiologic'Changes During-Exposure to Ionized Air, by C. P. Yaglou. A. D. Brandt and L. C. Benjamin (A.S.H.V.E. Trans^ actions, Vol. 39,1933, p. 357). A.S.H.V.E. Research Report No. 985--^Diurnal and Seasonal Variations in the Small-Ion Content of Outdoor and Indoor Air, by C. P. Yaglou and L/C. Benjamin (A.S.H.V.E. . Transactions, Vol. 40, 1934, p. 271). The Nature of Ions in Air and Their Possible Physiological Effects, ' by L. B. Loeb (A.S.H.V.E. Transactions, VoL 41, 1935, p. 101). The Influence of Ionized Air upon ' Normal Subjects, by L. P. Herrington {Journal Clinical Investigation, 14, January, 1935). The Effect of ': HlCfll I nnrpnfra tlnno nf 1 i irhf M nn i A Tnn .M . ,L____, , 1.; f, AIL! ! Ti _ . ' Herringtop (A.S.H.V.E. Transactions, Vol. 42. 1936, p. 119). . *~Thc br-tiish Medical Journal, Editorial. June 25, 1932, p. 1182. See also Loc. Cit. Note 8. '-Air-Borne Infection and Sanitary Air Control, by W. F. Wells (Journal Industrial Hygiene, November, 1935). ... , -Sanitary Ventilation in Wards, by W. F. Wells {Heating and Ventilating. April. 1939, p. 26). Measure- r ment of Sanitary Ventilation, by W. F. Wells {American Journal of Public Health; Vol. 28, 1938, p. 343). ' Air Disinfection in Ventilation, by W. F. Wells (A.S.H.V.E. Transactions, Vol. 50. 1944, p: 361) Principles of Ultraviolet Disinfection of Enclosed Spaces, by L. J. Buttolph (A.S.H.V.E. Journal . Section, Heaitng, Piping and Air Conditioning, May, 1945, p. 282). '. % . _ Ultraviolet as.a Protective Agent in Preparation of Pharmaceuticals, by A. R. Dennington (A.S.H.V.E. Journal Section, Heating, Piptng and Air Conditioning, July, 1945, p. 398). ,, *7The Use of Glycol Vapors for Air Sterilization and the Control of Air Borne Infection, by B. H. Jennings, Edward-Bigg, M.D., and F. C. W. Olson (A.S.H.V.E. Transactions, VoL 50, 1944, p. 343). ` ' Research'Report No. 830--Heat and Moisture Losses from the Human Body and Their Relation to Air Conditioning Problems, by F. C. Houghten. W. W. Teague, W. E. Miller and W. P. Yant (A.S.H.V.E. Transactions,'Vol. 35, 1929, p. 245). Thermal Exchanges Between the Human Body . and Its. Atmospheric Environment, by F. C. Houghten, W. W. Teague. W. E, Miller and W. P. Yant: {American Journal of Physiology, Vol. 88. 1929. p. 386). A.S.H.V.E. Research Report No. 908--Heat Mature Lossesfrom Men at Work and Application to Air Conditioning Problems, by F. C. Houghten. W. W. Teague, W. E. Miller and W. P. Yant (A.S.H.V.B. Transactions. Vol. 37,1931, p. 541). Thermal Exchanges Between the Bodies of Men Working and the Atmospheric Environment, by F. C. Houghten. W. W. Teague, W. E. Miller and W. P. Yant {American Journal ofHygiene", Vol. XIII, 1931, No. 2, p. 415). A.S.H.V.E. Research Report No. 1106--Air Conditioning in Industry, by W. L. Fleisher, A. E. Stacey, .Jr., F. C. Houghten and M. B. Ferderber (A.S.H.V.E. Transactions,' Vol. 45, 1939,'p. 59). . . A.S.H.V.E. Research Report No. 1107--Recent Advances in Physiological Knowledge and Their' Baring on Ventilation Practice, by C.-E. A. Winslow, T. Bedford, E. F. DuBois, R. W. Keeton, A. Missen- ard, R. R. Sayers and C. Tasker. (A.S.H.V.E. Transactions, VoL 45, 1939, p. 111). . . ""The Relative Influence of Ra&ation ahd Convection Upon: the Temperature Regulation of the VoLIM'October ^938! ns^ow* Herrington and A. P. Gagge {American Journal of Physiology, . - "-Relations Between Atmospheric Conditions, Physiological Reactions, and Sensations of Pleasantness, - XTE- A. Winslow, L. P. Herrington add A. P. Gagge {American Journal of Hygiene, Vol; 26, July/1937/ p. 102). ; The Reactions of the Clothed Human Body to Variations in Atmospheric Humidity, by C.-E.'A. Winslow, L. P. Herrington and A. P. Gagge {American Journal of Physiology, Vol. 124, December, -1938. p.' p92). : - - * . Physiological Principles 239 li-A S H V E. Research Report No'. 654--Some Physiological Reactions to High Temperatures and Hnmidities. by W. J. McConnell and F. Cl Houghten (A.S.H.V.E. Transactions, Vol. 29, 1923. p. 129). ash V E Research Report No. 672--Further Study of Physiological Reactions, by W. J. McConnell. PC 'Houghten and F. M. Phillips (A.S.H.V.E. Transactions, Vol. 29. 1923, p. 353). A.S.H.V.E. r'ksrarch Report No. 690--Air Motion, High Temperatures and.Various Humidities--Reactions on Human Beings, by W. J. McConnell, F. C. Houghten and C. P. Yaglou (A'.S-H.V.E. Transactions. Vol. SJ 1924 d/167). A.S.H.V.E. Research Report No. 718--Work Tests Conducted in Atmospheres of Hiffh Temperatures and Various Humidities in Still and Moving Air, by W. J. McConnell and C. P. Yaglou. IASH V.eTTransactions, Vol. 31, 1925, p. 101). A.S.H.V.E. Research Report No. 719--Basal Metabolism Before and After Exposure to High Temperatures and Various Humidities, by W. J. McConrififC P Yaglou and W. B. Fulton (A.S.H.V.E. Transactions, Vol. 31, 1925, p. 123). A.S.H.V.E. Rrsrarch Report No. 908--Heat and Moisture Losses from Men at Work and Application to Air Con ditioning Problems, by F. C. Houghten. W. W. Teague, W. E. Miller and W. P. Yant (A.S.H.V.E. Trans- , actions. Vol. 37.1931, p. 541). A.S.H.V.E. Research Report No. 1106--Air Conditioning in Industry-- Physiological Reactions of Individual Workers to High Effective Temperatures, by W. L. Fleisher, A. E. sEcev. Jr- F. C. Houghten and M. B. Ferderber (A.S.H.V.E. Transactions. VoL 45. 1939. P-59). * c h V E Research Report No. 1153--Seasonal Variation in Reactions to Hot Atmospheres, by F. C. Hnurfiten.'A. A. Rosenberg and M. B. Ferderber (A.S.H.V.E. Transactions, VoL 46. 1940, P-185). Physiologic Effects of Hot Atmospheres, by F. C. Houghten, M. B. Ferderber and A. A. Rosenberg (indus trial Medicine, January, 1940, p. 7). is--a S.H.V.E. Research Report No. 1151--The Peripheral Type of Circulatory Failure in Experi mental Hat Exhaustion, by R. W. Keeton. F. K. Hick. Nathaniel- Glickman and M. M: Montgomery (A.S.H.VJS. Transactions, VoL 46, 1940, p. 157). ... ' , -' . is--a S H V.E. Research Report No. 1153--Seasonal Variation in Reactions to Hot Atmospheres, by F. C. Houghten, A. A. Rosenberg and M. B. Ferderber (A.S.H.V.E. Transactions, VoL 46. 1940, p. 185). * 7--influence of Effective Temperature upon Bacterial Action of Gastro-Intestinal Tract, by Arnold and Brody {Proceedings Society Exp. Biol. Med., Vol. 24, 1927, p. 823). l *--Manual of Industrial Hygiene. 1943 (Prepared by U. S. Public Health Service, p. 328). Introduction to Industrial Medicine, 1944 (University of Pittsburgh, p. 167). i s--Heat Tli<a>gftp- Pliniml nnri Laboratory Studies, bv M. W. Heilman and E. S. Montgomery {Journal of Industrial Disease and Toxicology, 18:651, 1936). ' so--A.S.H.V.E. Research Report No. 1106--Air Conditioning in Industry, by W. L. Fleisher, A. E. Stacey. Jr., F. C. Houghten and M. B. Ferderber (A.S.H.V.E. Transactions, Vol. 45.1939, p. 59). si--The Upper limits of Environmental Heat and Humidity Tolerated by Acclimatized Men Working in Hot Environments, by'Ludwig W. Eichna, William F. Ashe, William B. Bean,'and Walter B. Shelley. {The Journal of Industrial Hygiene and Toxicology, VoL 27, March, 1945, p. 59). . **"A.S.H.V.E. Research Report No.- 1188--Local Cooling of Workers in Hot Industry, by F. C. Houghten. M. B. Ferderber and Carl Gutberlet (A.S.H.V.E. Transactions, VoL 47, 1941, p. 403). is--Civilization and Climate, by Ellsworth Huntington, Yale University Press, 1928. 24--The Reactions of the Clothed Human Body to Variations in Atmospheric Humidity, by C.-E. A. Winslow, L. P. Herrington and A. P. Gagge {American Journal of Pkysiology, VoL 124, December, 1938, p. 692). i'-Physiological Response of Subjects Exposed to High Effective Temperatures and Elevated Mean Radiant Temperatures, a Report to the Air Conditioning Section, Design Division, Bureau of Ships, U. S. Navy. (A paper on the work will be presented early in 1946). * i4--A.S.H.V.E. Research Report- No. 673--Determination of the Comfort Zone, by F. C. Houghten and C. P. Yaglou (A.S.H.V.E. Transactions, Vol: 29, 1923, p. 361). A.S.H.V.E. Reskarch Report No. 691--Cooling Effect on Human Beings Produced by Various Air Velocities, by F. C. Houghten and C. P. Yaglou (A.S.H.V.E. Transactions, Vol. 30, 1924, p. 193). A.S.H.V.E. Research Report No. 717- Effective Temperature with Clothing, by C. P. Yaglou and W. E. Miller (A.S.H.V.E. Transactions, Vol. 31. 1925, p. 89). A.S.H.V.E. Research Report No. 755--Effective Temperature for Persons Lightly Clothed and< Working in Still Air, by F. C. Houghten. W. W. Teague and W. E. Miller (A.S.H.V.E. Trans actions. Vol. 32. 1926. p. 315). . How to Use the Effective Temperature Index and Comfort Charts, by C. P. Yaglou, W, H. Carrier, Dr. E. V. Hill, F. C. Houghten and J. H. Walker (A.S.H.V.E. Transactions. VoL 38. 1932, p. 410). . . **--A.S.H.V.E. Research Report No. 117l2--Radiation as a Factor in the Sensation of Warmth, by . F. C. Houghten. S. B. Gunst and J. Sucio, Jr. (A.S.H.V.E. Transactions, Vol. 47, 1941, p. 93). A.S.H.V.E. Research Report No. 946--Cold Walls and Their Relation to Feeling of Warmth, by F. C. Houghten and Paul McDermott (A.S.H.V.E. Transactions, VoL 39, 1933, p. 83). >0--A.S.H.V.E. Research Report No. 1035--Comfort Standards for Summer Air Conditioning, by F. C. Houghten and Carl Gutberlet (A.S.H.V.E. Transactions, VoL 42. 1936, p. 215). A.S.H.V.E. Research Report No. 1055--Cooling Requirements for Summer Comfort Air Conditioning, by F. C. Houghten, F. E. Giesecke, C. Tasker and Carl Gutberlet (A^.H.V.E. Transactions, Vol. 43,1937,* P-145). A.S.H.V.E. Research Report No. 1088--Summer Cooling Requirements of 275 Workers in an Air Con ditioned Office, by A. B. Newton, F. C. Houghten, Carl Gutberlet and R. W. Quailey (A.S.H.V.E, Transactions, Vol. 44.1938. p. 337). Cooling Requirements for Sommer Comfort Air Conditioning in Toronto, by C. Tasker (A^.H.V.E. Transactions. Vol. 44. 1938, p. 549). A.S.H.V.E. Research Report No. 1127--Reactions of Office Workers to Air Conditioning in South Texas, by A. J. Rummel, F. E. Giesecke. W. H. Badgett and A. T. Moses (A.S.H.V.B. Transactions. VoL 45.1939, p. 459). A.S.H.V.E. Research Report No. 1136--Summer Cooling Requirements in Washington, D.C., and Other Metropolitan Districts,. by' F. C. Houghten, Carl Gutberlet and Albert A. Rosenberg (A.S.H.V.E. Transactions, Vol. 46, 1939, p.677). A.S.H.V.E. Research Report No.'1160--Reactions of 745 Clerks to Summer Air Conditioning, by W. J. McConnell and M. Spiegelman (A.S.H.V.E. Transactions, Vol. 46,1940, p. 291); - . * s .240 CHAPTER 12 , ' ; 1946 Guide al ^-S-H.V.E. Research Paper--Comfort with Summer Air Conditioning, by Thomas Chester, N. D. Adama C. R. Bellamy, G. D Fife E P. Heckel, Dr. W. J. McConnell. F. C. McIntosh, A. B. Newton, B,. F. Raber and C. Tasker. (A.S.H.V.E. Transactions, Vol. 4S, 1942, y. 107). -A.S.H.V.E. Research Report No. 1102--Shock Experiences of 275 Workers After Entering and Leaving Copied and Air Conditioned Offices, by A. B. Newton. F. C. Honghten, Carl Gutberlet, R. W. Qualley and M. C. W. Tomlinson (A.S.H.V.E. Transactions, Vol. 44. 1938, p. 571>. . .. .**"rA^tH.y.E. Research Report No. 1055--Cooling Reauirements for Summer Comfort Air Coaditimng;7iy F. a Houghten, F. E. Giesecke. C. Tasker and-Carl Gutberlet (A.S.H.V:E. Transactions, ... "rA S-H-Y-E. Research Report No. 755-Effective Temperatiire for Peisons Lightly Clothed and 'yettmE.mSUIl Air by F. C. Houghten. W. W. Teague and Wl E; Miller (A.S.H.V.E. Transactions, VoL 32, 1926, p. olo). ' " ' ,, ,J5-A.S.H:V.E. Research Report No. 1106--Air Conditioning in industry; by W. L' Fleisher. A. E. Stacey. Jr., F. C. Houghten and M. B. Ferderber (A.S.H.V.E. Transactions, Vol. 45. 1939, p. 59). ,3?rA?piicatio,n of Air Conditioning to Premature Nurseries in Hospitals, by C. P. Yaglou, Philip Drinker and K. D. Blackfan (A.S.H.V.E. Transactions, VoL 36, 1930, p. 383). ' .... . . *7~A.S.H.V.E. Research Report No. 1012--Study of Summer Cooling in the Research Residence for the Summer of 1934, by A. P. Kratz, S. Konzo, M. K. Fahnestock and E. U Broderick (A.S.H.V.E. Trans actions, Vol. 41. 1935. p. 207). DuBois, D. and E. F. (Archives of Internal Medicine, 1916, Vol. 18, p.865). -1 k sdl-ss CHAPTER; 13___ (Conditioning in the prevention and dreatment o^ d^iieaie Control of Airborne Infection, Value of-Air Cooling-Under , Tropical Conditions, Treatment of Disease, Operating Rooms, Nurseries for Premature Infants, Fever Therapy, Cold Therapy, Allergic Disorders, Oxygen Therapy, Evacuation of Sick and Wounded, General Hospital Air Conditioning . ; THE late war has caused an increase of interest in the preventive . aspects of air conditioning. It has re-emphasized the importance of , the control of airborne infection and has demonstrated the value of air cooling under tropical conditions for the prevention of heat rash, for proper rest and sleep, and in the convalescence of patients. . CONTROL OF AIRBORNE INFECTION Any program of air sanitation is influenced by a number of factors '3' *. In the winter months, the closing of doors, windows and other means of access to the outside air to.conserve warmth and further the crowding of persons indoors provides conditions conducive to a high incidence of contagion. This seasonal phenomenon, illustrated in Fig. 1 which represents a study made by the U. S. Public Health Service, will concern the ventilating engineer in so far as air quality, determined by tempera ture, humidity, air replenishment and type of air movement and by. freedom from contamination, is a major intrinsic factor. : Apart from the seasonal picture of airborne contagion are such extrinsic factors as rate of turnover of personnel and the marked, susceptibility of the recruit in comparison with permanent personnel6 as shown by studies of military personnel housed in" barracks, Fig. 2. These extraneous variables and the factor of contact infection (direct spray) tend to complicate any evaluation of the effectiveness of air sanitation for eliimnation'of micro organisms in droplet:nuclei and droplet-dust.. Thus, .control, measures - may eliminate consistently 90 per cent of airborne organisms in laboratory tests, but cannot effect a decrease in actual incidence of infection ex- ' > ceeding 30 per cent. Thirty per cent may be the maximal reduction in infection possible by air treatment methods. The distinction should be clearly drawn,, therefore,- between the effectiveness of a procedure in laboratory tests and its effectiveness and applicability in'actually reducing the incidence .of airborne disease. . . .- - The following sequence of events has been postulated as occurring in. - a large proportion of intra-ward infections: ' (a) ejection of relatively large protected infective particles from patients, (b) rapid venting or . settling of these particles' so that .those remaining airborne - are in low concentration, (c) survival of infective particles to permit the accumu lation of high concentrations-on surfaces, (d) repeated reintroduction of infective particles.into the air under the stimulus of ward activities or by air currents of the order of 50 fpm over the floor, and' (e) extension of infective areas bV air turbulence throughout the ward or. hospital. The most important link in this probable infection, chain has been demon strated to be the reintroduction of particles into the air 6. ` 242 . CHAPTER 13- : . 1946 Guide .Intensive studies on air disinfection have indicated two distinct control measures, (a) suppression of dust and lint, and. (6) disinfection of droplet- nuclei. ' ' ' ' V Well controlled,'large scale tests of the various methods of air sterili- . zation conducted in barracks V 8 have confirmed the importance of dust control in minimizing the spread of airborne disease, a consideration which has guided the practices of ventilating engineers for a number of years. The importance of the dust factor has been emphasized by many .engineers and has been, convincingly; demonstrated by subsequent bacteriologic studies aboard.ships. . / ; , " i ; Treatment of floors and bedclothes' with oil emulsions has proved effective in reducing bacterial dispersion by as much as 90 per cent in JU-l AUC iSCPIlOCt (MOV >DCC.iJAM. rCS.iMAR.iAPa..MAY .JUN. ' 100 -100 M 00Soo- AU. RCSPIRATOThf / \ -so' . -oo. $ 70 - 70 S o- - u< 30- . k 40- - -. / INIXOCNZA / AMO V / s. \ 1/ \\ !\\ - y\ ' 1 -o . -SO -4 !_Z J !- *103-~ ' / `OISEASO1 \ -30 . ` ..// y'TpM.AoHYrMX-. \ . ,\- -,*o . AMO TONSILS - 10 -U-- .. BRONCHITIS-- - s. 3- PNEUMONIA ` - ^ ' 4 ; - i:. - s Jtfc- AU6.SCPX OCT MWfc 0CC. JAM PCS- MAR. APR.8MAY JUN. . MONTH IN WMKM DISABILITY 'OCCAM _ Occurrence, of diseases causing disability for. 8 consecutive days or longer in a etoud of, 100 000 waee ' earners`(10 per. cent women) in different industries. ' \'1' ' - 1' ; ` "Graph obtained from Dean K. Brundage. U. S.Public Health Service. ;' ' * 11 : ` - ; Fig.; 1./: Study of Average Monthly Frequency (1921;-1926 inclusive) of , ... ; . Specified Respiratory'Diseases3 , .. . , Armjr barrciks and station hospitals18.' * This incidence of acute respiratory infections was from 10 to 30 per cent lower in barracks with oiled floors and bedclothes than it was in control barracks'which received no special treatment.. : '- ;/ No simple method for disinfecting drqplet-huclei has yet been' devised: Under favorable laboratory conditions, propylene glycol in concentrations 6f 0.07 to 0.14 milligrams per liter, and' trieth'ylerie-glycol in a concen- tration of 0.0.045 milligrams per liter Were highly getiniddal for most airborne'Jbacteria in clean air when the relative humidity was: between 40 and 60 per cent ". Under practical conditions, however, particular!^ in the pretence of dust in the air, glycol effectiveness is much reduced:. The use of other chemical aerosols that have been tried-is limited by their toxicity, odor, or destructiveness to-fabrics and metals..' ' " Ultraviolet radiation of floors and upper air has proved more effective Air Conditioning in the Prevention'and Treatment of Disease__________ 243, than glycol aerosols-in >reducing respiratory illness. In barracks housing naval recruits,.-hospital admissions- for respiratory infections (mostly catarrhal fever) were 25 per cent lower in a group of men exposed to ultra violet radiation--(2537 Angstrom Units, 1 to 7 ergs per (cm1) (sec) at . bed level)--than they were in adjacent control barracks without :ultra-. violet radiationa. . A combination of ultraviolet radiation and ; dust ' control measures is believed to be more effective than when either one of the two is used alone, but the proof for this has yet to come, . VALUE OF AIB COOLING UNDER TROPICAL CONDITIONS The commissioning of a class of naval hospital ships with all,.wards, laboratories and living spaces air. cooled is a notable achievement to provide better treatment of patients, especially those, suffering from, extensive burns, by control of environmental factors. Although statistics ( are not at hand to indicate the deaths or retarded recoveries of patients due'to lack of air cooling in ships*operating in"tropical."waters, it' is generally agreed among competent observers that high temperature and humidity aremajorfaetbrs in prblonging disability and 'increasing, mortality of the sick and injured: Physiologic data obtained on healthy men, mbreover.' show the large loss of-body fluids', and the stress, on' the . cardiovascular system in terms of increased bulse rate when these men are> continuously subjected to high temperatures. Even at rest'about 50 cc of fluid per hour are lost as sweat18 through intact skin.In burn patients the difficulty, encountered in temperate climates, of maintaining fluid and electrolyte:balance-is tremendously augmented by the .addi- tionalevaporative.fluid loss in hot environments. . Frequently from150 to 75 per cent of personnel aboard naval vessels operating in-tropical waters'are afflicted with heat rash to a degree that interferes, with rest and sleep. In carefully controlled experiments 18 it was possible to produce a fulminating ' type of rash in all men living continuously at an effective temperature of' 85 (90 F dry-bulb and 83 F - wet-bulb). In the control gtoup, 12 out of 24 hr were spent in a relatively cool- atmosphere of 75 ET. (80.F dry-bulb, and.70. F wet-bulb).. These ' ' y 244 , CHAPTER 13 .1946 Guide men either remained free from heat rash or occasionally developed a mild form. Thus, intermittent cooling'to a degree which prevented sweating in men at rest eliminated a serious, handicap to good performance of duty. In both laboratory tests and aboard hospital ships a relatively cool living environment of 76 to 78 ET provided an atmosphere conducive . to rest and sleep without sweating. Berthing spaces tended to have extremely low: odor levels. Motivation, initiative and alertness in con trast to the usual irritability and lack of incentive incident to residence in tropical climate were maintained 14> ls-16. Little has been done, however, to obtain practical methods for appli cation of air conditioning under heavy heat loads and on the enormous scale that would be needed to modify life in the tropics. It is not im . probable that cooled houses in a tropical climate, if used consistently for one generation, might modify the whole character of a population17. , The obvious advantages of part time cooling oil personnel to promote rest and sleep in tropical areas would provide a prophylactic measure of great potential importance. TREATMENT OF DISEASE In the past few years considerable progress has been made in using air conditioning as an adjunct in the treatment of various diseases. Among the important applications are those in operating rooms, nurseries for premature infants, maternity and delivery rooms, children's wards, ' clinics for arthritic patients, heat therapy, cold therapy, oxygen therapy, X-ray rooms, the control of allergic disorders, and for the physiological . effects in industry. . OPERATING ROOMS . The widest application of air conditioning in hospitals' is in operating rooms:- Complete air-conditioning of-operating .wards is important, because winter humidification helps reduce the danger of anesthetic . gases; summer cooling with some dehumidification is needed to eliminate excessive fatigue and to protect the patient arid operating personnel; and finally, filtering for the removal of allergens from the operating room air. Reducing Explosion'Hazard . -: - :: Explosion hazards in operating ftoms began with. the. introduction of modern anesthetic gases and apparatus. Ether, administered by the old drop method gives rise to an explosive, mixture, but jja- practice this method is still-regarded as comparatively safe.- When ether, is mixed with pure oxygen, or nitrous oxide in certain concentrations, the explosion hazard may be as great as with ethylene-oxygen, or cyclopropaneoxygen mixturesu. Of the anesthetic gases nitrous oxide alone does not explode but sup ports combustion. Ether,- vinyl ether, ethylene, and cyclopropane are as potentially dangerous as gasoline or illuminating, gas in the . home19. Chloroform does not explode violently in contact with flame but decom poses to liberate phosgene.. All of the anesthetic gases and vapors.except ethylene are heavier than air. Although the Incidence of injury or death- -from explosion is'negligible compared with other hazards in the operating .room, the..dramatic features-surrounding an explosion justify continued investigation to eliminate the hazard. During the course of ethylene anesthesia, the mixture, usually 80 /lir Conditioning in the Prevention and Treatment of Disease 245 per cent ethylene and 20 per cent oxygen, is: so rich that the danger of explosion is slight in the immediate vicinity of the face mask, but leakage of ethylene into the air may accumulate to any lower concentration, and thus introduce a serious hazard. The most dangerous period is at theend of the operation when the patient's lungs and the anesthesia apparatus are customarily washed out with oxygen with or without the'addition of carbon dioxide. Even when this procedure is omitted,'it is difficult in practice to avoid dilution of the anesthetic gas with air during the normal course of breathing following the administration. In either case the mixture would pass through the explosion range and extraordinary precaution1 is necessary for the safety of the patierit arid operating personnel. ' '. In a study 20 of 230 anesthetic explosions and fires,,70 per cent of. the explosions and ,60 per cent of the deaths were caused by igniting agents other then static sparks. In 1941 the National Fire Protection Associa tion 21 made certain recommendations for safe practice based on available information. Some of these recommendations are: '. Windows should be kept-closed so that the air conditioning system can prevent pooling of explosive anesthetic gases. Twelve air changes per hour and a humidity of 55 per cent are advised. If a higher humidity were compatible with the well being of the. patient and personnel, it shouldbe maintained. All electrical.installations should comply with the , standards set by the National Electrical Code for use in explosive situations. Cautery equipment should not be used in hazardous locations. To prevent static sparks, all bodies in an operating-room should be conduc tive or coupled. It is essential that adequate grounding be-provided for the floor and every object in the operating room. Conductive rubber should be used on shoes, leg tips, operating table coverings and ail rubber parts of the anesthesia equipment. All furniture,in contact with the floor should be metal: In the absence of complete grounding facilities, the Simple method of intercoupling patient, operating .table,-anesthetist and gas machine at ground potential may be used. '' ' ' : . Experience has shown that neither high humidity.nor intercouplirig devices have eliminated the danger from static.electric discharge... .The removal of gas concentrations from the operating table area by means of specially devised exhaust ventilation should be thoroughly tested'. Port? able duct systerris as installed aboard ship should be acceptable. Serious explosions can occur in" a closed, system but proper precautions wilj reduce this hazard to a minimum. . -. . . . '. .. . It should be realized that when a room and the occupants have been completely grounded there is always the possibility that the.patient or the operator might receive a dangerous shock if a short circuit developed- in any of the electrical equipment., ... . .. -. ; A comprehensive study of the explosion problem and: :of the general causes and- prevention of operating room hazards by the University, of Pittsburgh, the A.S.H.V.E.- Research.Laboratory,land -the' U. 5. Bureau of. Mines has led to a fruitful attempt to eliminate the explosive range of cyclopropane, one of the best but most difficult gases to handle.; The use of helium as a diluent in the total gaseous mixture controls the oxygen, concentration by replacement and, because of its flame quenching proper-. ties, it is. the ideal gas for this purpose. ' In addition, a gaseous mixture containing helium, is more difficult to ignite by electric discharges,and this quality also iricreases the. safety factor of anesthetic adriiinistratlon. 246 CHAPTER 13 1946 Guide Operating Room Conditions - . Little is known about optimum air conditions for maintaining normal . body temperatures during anesthesia and the immediate post-operative period. An anesthetized patient displays dilation of blood vessels in . the skin resulting in profuse sweating and (it has been believed) inability to regulate body temperature. From this it was concluded that all anesthetized patients suffered considerable heat loss, although there may be little more than 0.8 F variation in the rectal temperature during the course of the operation22. The severe physiological effects, such as excessive sweating and rapid pulse, of high operating room temperatures on attendants and patients during the hot months signify the need for proper cooling. A comparison of'surgeons^ statements who operate in both air conditioned and non-air conditioned rooms strongly indicates that the recuperative power of the patient is greater when operated upon ' in air conditioned rooms22. .. Although the comfortable air conditions for the operators are not identical with those for the patient, it is usually not difficult to coiriprm mise within a range of 55 to 60 per cent relative humidity, and 72 to.80 F temperature. The work just cited , reported that 68 to 70 F, effective temperature not only furnished comfort for the operating room workers, but apparently prevented exhaustion of the patient as evidenced by rapid convalescence in the recovery ward. Additional heat may be furnished to the patient locally or by suitable covering according to body-tempera ture in individual cases, i : _ ... . . In the control of airborne infection in the operating room the prevention of dispersal of infectious materials into the air, control of dust and proper ventilation supersede attempts to remove or kill pathogenic organisms. ' , In atLinvestigatipn recently conducted at the University of Pittsburgh, . , in,a cpoperative research,program with the Society, comparative sthdies were". made on bacterial'con|em.of conditioned and n'on'-conditioned operating rooms. From these studies23 it was concluded that' the bac terial content of conditioned operating rooms was' considerably less than that of non-conditioned rooms. ' . . . . .. . Bacterial bounts aboard an air conditioned submarine were found to be exceptionally low and not cumulative.with time'although all: of the air' was recirculated for more than 12 hours2* without replenishment. The removal of bacteria by the process of air cooling'and condensation of moisture out of air' merits further study ". ' '! . _ The degree of air contamination can be reduced by proper ventilation if-velocity of air over the'floor does'not exceed 50 fpm. Research is in progress on the use of-filtered air flowing through a system of mechanical cleaners which protect the patient against infection from'attendants and ' from bacteria-containing air in the corridor of ward - Operations may be-postponed on allergic patients during asthmatic manifestations :through fear. of'complications.' The removal of air-borne allergens, therefore,.is.in some cases an important function of the air conditioning.system.in preparing, patients for-operation.' . Central system air conditioning plants and unit air conditioners prove satisfactory in operatitig rooms when .producing between 8 and 12 air .-changes per hour of filtered and properly conditioned air without redrculatioh during ihe course' of anesthesia. A separate exhaust fan system is usually-necessary to confine and remove the gases and odors. Double . windriws are desirable arid often necessary to prevent-condensation and i i i ! 1 ' . .= ' ^ :lj j A ) 'S ' '1 .1 .r Air Conditioning in the Prevention and Treatment of Disease 247 frosting on the glass in cold weather arid to minimize drafts. The air flow of 8 to 12 air changes in operating rooms should: (1) reduce the concern tration of the anesthetic to well below the pharmacologic threshold in the vicinity of the operating personnel, (2) remove the great amounts of heat'and sometimes moisture, from sterilizing equipment if inside the operating room, from the powerful surgical lights, from solar heat, and from: the bodies of the operatives, and (3) provide extra capacity for quickly preparing , the room for emergency1 operations. Much can be gained by thermal insulation of sterilizirig equipment and by thorough exhaust ventilation of sterilizing rooms adjoining the operating rooms. Too great a difference in temperature between the operating room and the final hospital destination of the patient, including corridors and elevators, is conducive to infections of the upper part of the respiratory tract and .post-operative pneumonia.' A suggested remedy, is a recovery ward in which conditions closely approximate those of the operating room and in which the patients remain from one to four days.' Satis factory conditions in the recovery ward not only hasten convalescence, but dispel the fear frequently found in patients who must undergo operations during the hot seasons27........... - Experience has shown that aifew hours after the operation the tem perature of the post-operative room can be decreased a few degrees below that of an overheated operating room to stimulate recovery.- . , * NURSERIES FOR PREMATURE INFANTS One. of the most important requirements.in. the. care of premature' infants is the stabilization of body temperature. , This is necessary, because their heat regulating systems are not fully developed; the . metabolism is low and the infants generally, exhibit-marked inability to maintain normal body temperatures. The resistance to infectionjs low and mortality rate high. . . ., .. .. Air Conditioning Reqiurements ' . . .' . ' : . . The optimum air conditions for. the. growth and development of these in fants were determined by extensive research2? at the Children's Hospital, Boston, Mass., using four valid criteria; namely,- stability of.body tem perature, gain in weight, incidence of digestive syndromes, and mortality. Individual temperature requirements varied>,widely;(frorir72 .to TOO F) according to the constitutional state of the infants .and body.. .weights. The optimum relative humidity, was about 65 per cent, . and ..the air mpvemeht'less. than 20 fpm.' T- .- : ; ' A single-nursery conditioned to 77. F arid 65 per,cerit felatiye humidity ' was found to fulfill satisfactorily the.,requirements, of the' inajority.-of premature infants. Additional .heat , for weak (or debilita.ted) -infants may be furnished in the cribs or by means of electric incubators placed inside the conditioned nursery, and the.temperature adjusted according to individual requirements. "In' this way multiplicity of chambers and. of air conditioning apparatus is obviated;.the infants in the heated beds derive the benefit of breathing cool humid air, and :the nurses and .doctors need not expose themselves to extreme-conditions.-- Importance of Humidity: I Although external , heat : is: an ..-important factor in the maintenarice of.normal body teiriperature, humidity appears to be of equal or greater importance. When the premature.nurseries at ' the Children's Hospital were kept at relative humidity between"-25 and 50 248 CHAPTER 13 1946 Guide per cent for two weeks or-longer, the body temperature became unstable; gain in weight diminished, the incidence of gastro-intestinal disturbances increased, and the mortality rose. On the other. hand, continuous exposure to air conditions with 55 to 65 per cent relative humidity gave satisfactory results over a period of years.. The initial physiologic loss of body weight (loss-occurring within first four days of life) was found to vary inversely with the humidity. In the old-nurseries with natural humidity it averaged 12.4 per cent of the birth weight; in the conditioned nurseries it was 8.9 per cent with:25 to 49 per cent relative humidity, and 6.0 per cent, with 50 to 7,5 per cent relative humidity. The number of days required to regain the birth weight was correspondingly maximum in the old nursery and minimum in the conditioned nurseries under high humidity. . .. -.. . .: ' .. Maximum gains in body, weight occurred in the conditioned nurseries under high humidity (55 to. 65 per .cent) in infants weighing less than 5 lb. The gains were less under low humidity (25 to 50 per cent), in the same nurseries,-and in the old nurseries prior to the installation of air conditioning, apparatus. ; . - -.. The incidence and severity of digestive syndromes, with diarrhea, persistent vomiting, diminishing gain or loss of body weight, and other symptoms, were generally from two to three times as high under low than under high humidity. . . . : . ......... , Summarizing, the best chances for life in premature infants are created by maintaining a relative humidity of 65 per cent in the nursery and by providing a uniform environmental temperature just sufficiently high to keep the body temperature within normal limits. Medical and nursing care are, of course, factors of equal and sometimes of greater importance. Air Conditioning Equipment - . '. Many of the installations now in use are of the central system type providing for filtration, for humidification and heating in cold weather, and for cooling and dehumidification in hot weather. A ventilation rate, between 8 and 12 air changes, is desirable to remove odors and maintain uniformity of temperatures in extremes of weather. Recirculation should not be used in these wards owing to odors and the possibility of infection. There should be a frequent change in spray water. r. Control of Airborne Infection' . . . - ' The protection of the premature and older infant against infection is of the utmost importance.' It was found in one installation equippedwith air conditioning, germicidal lights and mechanical barriers that air conditioning alone did not prevent the spread of respiratory cross infections.":: Bactericidal ultraviolet light barriers and air conditioning or mechanicarbamers and air conditioning were efficient29.. ; ; ; ' FEVER THERAPY ' ' .' ' - Artificial production of fever in man is an imitation of nature's way of overcoming invading pathogenic organisms. The action may be direct and specific by destruction of the invading organism within the safe limitcof human Temperatures, or indirect in the case of heat resistant organisms,: by general mobilization .Of. the defensive mechanisms, of the body,-,which-retard >or;neutralize the activity, of pathogenic bacteria and their toxins. : : ' '.. ' ".......: : Air Conditioning in the Prevention and Treatment of Disease Although the action may. be direct and specific by: destruction of the invading-organisms within the safe limits of-human tolerance,, fever therapy exerts much of its benefit through the improvement of the mechanism of bodily defense. A serious challenge to the theory on which feyer. therapy is based comes from the demonstration that high fever causes, a reduction in the concentration of circulating antibodies in experimental: animals. Clinically, it has been shown that there is no change in the per cent of phagocytes which engulf -bacteria in patients during fever therapy, although the action of the complement fixing antibodies may be temporarily, diminished. - . - . '. Patients, for fever therapy should be. carefully selected. The most serious complications which may arise are heat stroke, heat exhaustion and circulatory collapse. The - chief minor complications are spasm, heat cramps, fever blisters and mild dehydration. . The limits of induced systemic fever are usually between 104 and 107 F (rectal), and the duration from 3 to 8 hours at a time. The total period of fever treatment varies with the type of the organism involved from a few hours to 50 or more. .. The diseases which respond favorably to artificial fever therapy are gonorrhea and its complications (which,include arthritis, pelvic infections in women, and involvement'of the eye),^syphilis, chorea, infectious arthritis (non-gonorrheal), encephalitis, and. some forms of asthma. There are other conditions which show promise under this treatment; but: the most striking results are seen in gonorrhea and syphilis, since the causative organisms can be destroyed at temperatures compatible with human life. . ...... . . Equipment for Production of Fever ` Artificial fever can be induced by injections of various crystalloid or colloid substances, bacterial products of typhoid and malarial organisms, or by physical methods using hot baths, radiant heat cabinets, hot humidified air cabinets, or by- short wave diathermy in combination with a cabinet. . , ' - . .. The relative advantages of various methods have been evaluated clinically30- Among the devices for the production of fever by physical means, the one most widely used is the hot humid air or air conditioned cabinet. This apparatus was'developed at the Kettering Institute for Medical Research at Miami Valley Hospital in Dayton, Ohio. . In the earlier studies of the Society32, temperatures were elevated more easily using saturated atmospheres. A feyer therapy apparatus,3 using these same principles has proved efficient as a', means of inducing and maintaining fever in a body with small likelihood of burns because of the comparatively low dry-bulb temperatures. -. .' . When heat is necessary in treating legs or arms, such media as short or -long wave diathermy, .infrared, water baths, etc. have been used extensively, A recent development, a saturated atmosphere heating unit, similar to one previously described has-proven satisfactory, because heat may be administered over longer periods which render deep heating possible without fear of burns or shocks. Local heating has been some what satisfactory in relieving the painful symptoms'of peripheral vascular disease. . . .. - - Some investigators employ- short wave: diathermy within the cabinet during the induction phase. When the optimum body temperature has ; 250 _____________ CHAPTER 13 1946 Guide been reached by electrical induction, the atmosphere of the enclosure is kept at saturation to prevent heat loss, thus maintaining the patient's temperature at the. desired point. The two underlying principles' in 'the production of fever by the hot, humid air cabinet are: (l).the transfer of heat by conduction from the. circulating hot air to the body and (2) prevention of heat loss. The latter is more important. In an atmosphere of high humidity, the mechanism of heat loss-by- evaporation is markedly decreased.' ., The chief physiologic effects exhibited during fever therapy are: (a) the cardio-vascular system is stimulated to increase the amount of blood to various parts of the body, (b) a mobilization of blood elements by the blood forming system, (c) general metabolism is increased, (d) only ' slight changes in blood chemistry except that the chlorides may . be de pleted if dehydration occurs. ': . ' The therapeutic value of fever therapy for certain1 diseases has been : definitely proved.. The combination of chemo-therapy and fever has proved to be more effective than when either is employed separately. This is especially true in regard to gonorrhea and early syphilis. - ` ` COLD THERAPY \ In contrast to fever therapy the use of .cold as a means of anesthesia and treatment is of established importance. Refrigeration anesthesia is being more widely used and the advantages of the method claimed by Allen have been completely confirmedM. - :; It has been demonstrated that the cooling of limbs and other parts with ice-water or ice, cracked or pulverized, down to near, the freezing point (5 C or 40 F) is harmless. Freezihg must'be avoided.' There is a . temporary retardation or suspension of life, with resumption of cellular activity as the temperature returns, to normal., A human limb can remain bloodless and anesthetic below a tourniquet for at least. 8 hr and perhaps up to 48 hr without injury, while .the rest of, the body, remains warm. Where amputation is indicated it can thus be done without pain, loss of blood or strength and also without shock. There is no apparent interference with the subsequent, healing of the stump. Refrigeration- anesthesia is of importance not only in amputation but also in the control of hemorrhage, pain, infection and shoclf1 during'the transportation of patients with .traumatized-limbs. . . . y' ' , '....' Apart from the advantages of cold in.amputations, cryotherapy has .been beneficial in the treatment pf-burns and'arterial obstruction, and essential in the treatment of frostbite and immersion foot. -It has been used successfully for.dental anesthesia'. The principle of hibernation in which the body as a whole is cooled for as much as .five days in air. tem peratures between 50 to 60 F and applied to such conditions as morphine addiction, leukemia, and schizophrenia continues to "be experimental. Prolonged cold therapy which keeps the body-temperature below 95 F . depresses the vital processes and' is fraught with danger:. . The methods used for refrigeration depending upon available facilities . are as follows54: ' '. 1 ' 1. (1) Cracked or shaved ice whieh is. simple and - has the advantage of not freezing tissues. However, it is cumbersome and sloppy to handle and is unsuited to prolonged treatments. . (2) Use of ice in a pail for immersion of local parts. - . * " .< (3) Special boxes for holding ice with padded or curtained openings for the' limb:! (- . Air Conditioning in the Prevention and Treatment of Disease 251 - (4) Bare ice bags and cloth bags for.iced wet dressings for prolonged.treatments and convenience. - . ,. . -- - - . (5) A double chambered cabinet using dry ice has been constructed. (6) Electrical refrigerating apparatus, consisting of a compact noiseless unit that, - pumps fluid to various types of applications, is available. The applicators may be in 1 . the form of blankets containing rubber tubes suitable for covering the entire body or all or part of a limb. Special applicators are available for insertion into various body- . cavities and for inducing dental anesthesia.. . (7) An air chamber at regulated temperature for treatments of frostbite and immersion - foot, and amputation stumps. ' . The electrical apparatus is costly but has the advantages of thermo static regulation, light weight, freedom of movement, and permits prolonged treatments with heat as well as cold over the range of tem peratures therapeutically, desirable. ' . .... , ALLERGIC DISORDERS Although there is some division of opinion over, the -ultimate, cause of allergy, the prevailing belief is.that it is due to an inherited or acquired hypersensitiveness to pollen or other foreign, proteins in certain indivi duals who react abnormally to the offending substance. The reaction may be induced by inhalation, eating, or absorption (through the skin) of the allergens. Some of the clinical manifestations are hay fever, ' asthma, eczema, and contact dermatitis., . ' , ;; , . Symptoms of Hay Fever and Asthma . ' The respiratory tract is; the usual site of allergic manifestations, e.g. hay fever and asthma. In hay fever, the nose and eyes are red and itchy, - arid there is corisiderable1 discharged Nasal obstruction- is the most common and distressing symptom. The severity of the symptoms varies widely from day to day depending chiefly on the amount of pollen in the air. . - : . - -; .. . ;. -. . -' . Seasonal asthma comes in attacks. The most popular theory concern- . irig the mechanism of action is that the offending substance irritates the nerve endings in mucous membranes of the respiratory tract, causing spasmodic contraction of the small bronchioles of' the lungs,'which interferes with'breathing,- particularly with1 expiration.1 Noniseasonal allergic-disturbances are srirnetiriies attributed to house''or street, dusts, fungi,:odorsi animal dander,'irritatirig gases;-and heritor arid,'-particu larly sudden temperature changes. It is often stated in the literature that heat regulation in asthmatic individuals tends to be unstable, with a tendency, toward the subnorriial.- Many allergic cases who are apparently well develop their attacks when cold weather appears, or upon changing - from.warm to cool outdoor air. - ; . ' . -, Air Conditioning Apparatus :- -, .. ' In recent years considerable effort has-been directed toward, the elimi- - nation of the principal criuse of allergy'from the air of enclosures by . filtration or other air conditioning processes capable of removing pollens* '. in the hope of providing relief to individuals who fail to respond to medical treatment (desensitization or immunization). ........... ' ' Papier or cloth filters, mounted in inexpensive window or floor units, prove quite satisfactory-in many cases, but since dust and smoke fre quently cause asthmatic attacks, it is desirable that an air filter; to be of full value in the treatment of asthma, .should:remove all possible'dusts ; 252 CHAPTER 13 . 1946 Guide and pollens regardless of size or amount. Electrostatic air cleaners are more efficient than most commonly used types for capturing very fine dust M. _ Although the chief remedial factor in the treatment by conditioned air is the filtration of pollen, a certain amount of cooling and dehumidification appears to be desirable. A comfortable temperature between 70 and 75 F ' and a relative humidity well below 50 per cent proved satisfactoryM. Direct drafts, overcooling or overheating are apt to initiate or aggravate the symptoms. Limitations of Air Conditioning Methods ' The results obtained with air filtration or other air conditioning pro cesses in the control of allergic conditions are fairly comparable to those obtained by desensitization treatment so long as the patients remain in the pollen free atmosphere. But while specific desensitization is preven tive and in a few instances curative, for all practical purposes filtration gives only, temporary relief. In mild cases sleeping in an air conditioned space may make it possible for the individual to pass more comfortable days. _With rare exceptions, the symptoms recur on exposure-to pollen laden air. Moreover the usefulness of air conditioning methods is limited because all cases are not caused by air-borne substances. Cases of bacterial asthma do not respond to treatment with filtered air. Despite these limitations air conditioning methods possess definite advantages in the simplicity of treatment, convenience, and under certain conditions almost immediate relief ". Pollen cases are usually relieved of jnost of their symptoms within 1 to 3 hr.after exposure to properly filtered air. A pollen-free atmosphere is especially .valuable when desensitization has given little or no relief, and when desensitization is not. advisable owing to intercurrent illness. . .. OXYGEN THERAPY Oxygen, therapy is the principal measure employed for preventing and relieving the distressing symptoms of anoxemia, which is a deficiency in the oxygen content of the blood. Some of the more important conditions in which oxygen treatment is believed to .be beneficial are pneumonias, anemia, heart affections, post-operative pulmonary disturbances, certain mental. disturbances, asphyxia, asthma and atelectasis in new-born infants. .. ... .. The effectiveness of oxygen therapy depends upon the'manner of ad ministration. Three common methods, catheter, face mask, or tent"8:39 , are employed. . ., ... .. . The necessity of air conditioning in oxygen therapy arises from the fact that oxygen is too expensive a gas to waste in the ventilation of oxygen tents arid oxygen chambers. The oxygen rich atmosphere in these enclosures- is therefore reconditioned in a, closed circuit by removal, of excess heat, moisture, and carbon dioxide given off from the occupants being treated.. .... , . .' . . Oxygen Tents - .. In oxygen tents .the air enriched with oxygen is usually circulated by means of a small motor blower which sends the air over soda lime to remove carbon dioxide and then over ice to remove excess heat and moisture. The concentration of oxygen in the tent is regulated by means Air Conditioning in the Prevention and Treatment of Disease 253 of a pressure reducing valve and flow' meter. In an inadequately cooled tent, high temperatures and humidities are inevitable, increasing the discomfort of the patient and imposing an added strain on an already overburdened heart. Oxygen therapy under such conditions may do more harm than good. An ice melting rate of approximately 10 lb per. hour gives satisfactory results in patients with fever in a medium size oxygen tent. ' Oxygen tents are confining to the patient. They may terrify the. rest less and delirious patient. Medical and nursing care is complicated, as the tent must be opened or. removed with attendant loss of oxygen. Oxygen concentrations of 50 per. cent or more are difficult to maintain, and it is a problem to keep the temperature and humidity low enough in hot weather. However, with attention to details, the patient can be made quite comfortable., . . Oxygen Chambers . . . The conventional oxygen chamber is an air-tight sheet metal enclosure of fire-proof construction, large enough to accommodate one or two patients. Trap doors or curtains are provided for the personnel, food and service, to avoid loss of oxygen, Glass windows in the ceiling and walls admit light from outside the chamber. The air conditioning system may be of. the gravity type, or of the fan type using mechanical refrig eration or air drying agents. , .. The temperature and humidity requirement in oxygen therapy depends primarily upon the physical condition of the patient, and secondarily upon the type of disease. In pneumonias40 prescribed conditions should be an effective temperature of 66 to 68 F, humidity of 50 per cent, air movement of not less than 50 linear feet per minute, oxygen concentra tion of 50 per cent, arid carbon dioxide of less than one per cent. / .Oxygen in Aviation . ... . . : . An important application`of`the principle of oxygen therapy is in aviation. At the present tinie ajl high, altitude military airplanes in this country are'provided with gaseous oxygen equipment and military personnel are required to utilize oxygen at all times while in flight above 15,000 ft, or-between 12,000 to 15,000 ft for longer than two hours, or between 10,000 to 12,000 ft for longer than six hours. The use of oxygen in commercial aviation .will .depend-on .the height and duration of the flights as well as the! state of health of the passengers. The necessity for portable, comfortable equipment, the possible fire hazards due to smoking, and the use of oxygen on sleeper planes are some of the difficulties facing civil airline operators. The pressure cabin airplane is a solution to the problem. ' : AIR EVACUATION OF THE SICK AND WOUNDED ; Between November 1942 and June 1945, some 510,000 wounded orsick 1 soldiers were transported by air. So efficient was the service that in the Normandy campaign men wounded in France in the morning could be given operative treatment- iri English hospitals the same evening. . A major problem encountered in this type of service is the removal of odors in the hospital space. The ideal deodorant method for use in aircraft, should effect complete removal of unpleasant odors without vitiating cabin air with other odors or irritants in the form of vapor sprays or ^ 2S4 CHAPTER 13 ._________________ 1946 Guide perfumes. It should not only be light weight and portable but capable of utilization in pressure type, cabins, without imposing an additional burden upon the limited ventilation facilities. GENERAL HOSPITAL AIR CONDITIONING Complete conditioning of a large hospital involves a capital investment and running expenses which may not be justified. Air conditioning has important applications in certain hospital wards such, as nurseries for premature infants, oxygen therapy chaimbers, heat therapy' rooms or cabinets, allergy wards 37, operating rpoms and recovery wards. In clean arid quiet districts, the requirements of almost all general and private wards during the cool season of the year can be satisfactorily fulfilled by the use of conventional heating equipment' in conjunction with window air supply and gravity or mechanical exhaust. . Insulation against heat and sound is much more important than humidification in winter;.it wilTalso l]elp in keeping the building cool in warm weather. Excessive outside noise and dust, may require the use of. silencers and air filters int the window openings. . .. . _. . Cooling and dehumidification in warm weather are important. In new hospitals particularly, the desirability of cooling certain sections of the building should be given serious consideration. Financial reasons may preclude the cooling of the entire building, but the needs of the average hospital can be met by the use of built-in room coolers and a few portable units which can be wheeled from ward to ward when needed. In the North and certain sections of the Pacific Coast, cooling is needed tyit a few; days during summer, while in the South, it can be used to advantage from, May to October, and in tropical climates almost con tinuously throughout the year. - . ... Aside from comfort and recuperative power of the-patients,> cooling is of great assistance in the treatment of fevers in the new-born.and. in post-operative cases, in enteric disorders, fevers, heat stroke, heart . failure, and in a variety of other ailmentswhich often accompany summer heatwaves.' ' . " ' 1' '. . . '' Considerable research is in progress on the influence of air conditioning - upon, a -wide variety of diseases' such as'pneumonia, upper respiratory diseases, tuberculosis, arthritis, nervous, instability, hyper-thyroidism, essential hypertension, skin diseases, and vascqlar disorders. ' ' .' Problem of Odors ,. The evacuation of battle casualties in aircraft and their subsequent hospitalization have stimulated efforts to minimize odors arising from draining wounds, old odorous, casts, ancFgangrenous wounds. For air craft, chemical sprays and vapors! perfumes, oxidizing gases and venti lation methods are unsatisfactory. An ideal deodorant would purify the air by means of odor adsorption so that subsequently the air can be recirculated; . Based upon the effectiveness of. activated carbon com-: merdally and industrially .to adsorb odors,-individual adsorption units . have.been.used successfully. In hospital wards the question of super iority of adsorption methods for elimination of odors over other methods' remains to be answered. The.present status of the problem is that the. commercial aspect is highly controversial. . -- Air. Conditioning in the Prevention arid`Treatment of Disease 255 REFERENCES i-Confined Air as a Vehicle of Infection; Current Progress in Air' Sanitation, by Stuart Mudd.(Medical Clinics of Norik America. 28:1293, 1944). ... . *--The Sea*3TM3! Patterns of Measles and Chicken Pox, by Mildred W. Wells (American Journal of Hygiene, 40:279, 1944). .. ., . ., -Aerobiology (Publication No. 17 of the American Association for the Advancement of Science, 1942).. 4--Scarlet Fever as an Air-Borne Infection, by H. L. Hodes, F.\F. Schwentker, B. M. Chenowith,- Jr., and J. L. Peck {American Journal of Medical Sciences, 209:64,1945). .. . 5--Factors in the Control of the Spread of Acute Respiratory Infections with Reference to Streptococcal Illness and Acute Rheumatic Fever, by S. M. Wheeler and T. D. Jones {American Journal of the Medical Sciences, 209:58. 1945). . ... ..... -Laboratory and Reid Studies of Glycols and Floor-Oiling in the Control of Air-Borne Bacteria,, by A. P. Krueger et al {U. S. Naval Medical Bulletin, 42:1288, 1944). , - . 7-Bacteria! Content of Air in Army Barracks, by A. M. Lemon, H. Wise and M. Hamburger {War Medicine, 6:92, 1944). -.. --A Study of the Nature and Control of Air-Borne Infection in Army Camps, by O. H. Robertson, M. Hamburger, C. G. Loosli. T. T. Puck, and H. M. Lemon {Journal of the American Medical Association,. 126:993, 1944). . .. 9--Lethal Effects of Triethylene Glycol Vapor on Air Borne Bacteria and Influenza Virus, by O. H. Robertson et al {Science 97:142, 1943). - .. to--The Present Status of Glycol Vapors in Air Sterilization, by M. Hamburger, Jr., O. H. Robertsoa, and t. T. Puck {American Journal of the Medical Sciences, 209:162, 1945). ' 11--Summary of a 3-Year Study of the Clinical Applications of the Disinfection of Air by Glycol Vapors, by T. N. Harris and J. Stokes. Jr. {American Journal of the Medical Sciences, 209:152, 1945). l x--Ultra-Violet Light Control of Air-Borne Infections in a Naval Training Center, by S. M. Wheeler, H S Ingraham. A. Hollaender. N. D. Lill, J. Gershon-Cohen. and E. W. Brown {American Journal of Public Health, 35:457, 1945). .. i s--A Comparative Study of the Effect on Men of Continuous. Versus Intermittent Exposure to a Tropical Environment, by N. Pace. M. B. Fisher. J. E. Birren. G. C. Pitts, W. A. White, Jr., W. V. Conso- lazio, and L. J. Pecora (Research Project X-205, Report No. 2, Naval Medical Research Institute, Bethesda. Md.. May. 1945). f 14--physiological Observations Made on Men Aboard Ship During a Shakedown Cruise in Tropical Waters, by N. Pace, W. V. Consolazio, and A. R. Behnke (Research Project X-205, Report No. 3. Naval Medical Research Institute, Bethesda, Md,, August, 1945). - . i s--Environmental and Physiologic Studies Aboard an Air-Cooled Hospital Ship Enroute from Norfolk. Virginia to Canal Zone (U. S. S. Tranquility (AH-14), 6-13 June 1945). by A. R. Behnke (Research Project X-205, Report No. 4, Naval Medical Research Institute, Bethesda, Md., September 1945). i --Environmental and Physiologic Studies aboard an Air-Cooled Hospital Ship En Route from Norfolk. Virginia to Can?! Zone (U. S. S. Consolation (AH-15), 14-20 July 1945), by G. J. Duffner and M. Ross (Research Project X-205, Report No. 5, Naval Medical Research Institute, Bethesda, Md., September 1945). * '-Book Review by H. C. Bazett {Science, 102:74, 1945) of Climate and the Energy of Nations, by S. F. Markham (Oxford University Press, 1944). . i --Safeguarding the Operating Room Against Explosions, by Victor B. Phillips {Modern Hospital, 46, April and May, 1936). . See also Explosion Hazards of Combustible Anesthetics, by G. W. Jones, R. E. Kennedy and G. J.- Thomas (/. 5. Bureau of Mines, Technical Paper No. 653. 1943). ` * --Fundamentals of Anesthesia (American Medical Association Press, Chicago, III., 2nd Edition, 1944. p. 204). . --The Hazard of Fire and Explosion in Anesthesia, by B. A. Green {Anesthesiology 2:144, 1941): *i--Control of Physical Hazards of Anesthesia, by R. M. Tobell and A. W. Friend'(Canadian Medical Association Journal 46:560. 1942). - ' . **--A.S.H.V.E. Research Report No. 1111--Air Conditioning Requirements of an Operating Room and Recovery Ward, by F. C. Houghten and W. Leigh Cook, Jr. (A.S.H.V.E. Transactions, Vol. 45, 1939, p. 161). . **--Report'on Air Conditioning in Surgery, by W. Leigh Cook, Jr. {Department of Industrial Hygiene, School of Medicine, University of Pittsburgh, 1940). - --Unpublished Naval Studies by A. R. Behnke and O. Schneider (1940). --Disinfection of Air by Air Conditioning Processes, by C.` P. Yaglou and Ursula Wilson {American Association for the Advancement of Science, Publication No. 17, p. 129). '' -The Control of Cross-Contamination by the Use of Mechanical Barriers, by J. A. Reyniers {Aero biology, American Association for the Advancement of Science, Symposium,l7:254, 1942). *7_Report of the Committee on Air Conditioning {The American Hospital Association, p. 2, 1937). . -The Premature InfantrA Study of the Effect of Atmospheric Conditions on Growth and on Develop ment. by K. D. Blackfan, C. P. Yaglou and K. McKenzie {American Journal Diseases of Children. 46: 1175, 1933). : --Observations on the Control of Respiratory Contagion in the Cradle, by I. Rosenstern {Aerobiology, American Association for the Advancement of Science, Symposium 17:242,1942). * . jo--Fever Therapy by Physical Means, by Frank H. Kruscn and E. C. Elkins {Journal American Medtcal Association, 112:1689, 1939)t -. ^Physical Medicine, by F. H. Krusen (W.B. Saunders Co., Philadelphia and London, 1941). 256 CHAPTER 13 1946 Guide Vw RPO --Some Physiological Reactions of High Temperatures and Humidities, by W. J. McConnell and F. C. Houghten (A.S.H.V.E. Transactions. Voi. 29. 1923, p. 129). _ A.S.H.V.E, Rkbakch Rkpo&t No. 1054--Fever Therapy Induced by Conditioned Air. by F. M. B. Ferderber and Carl Gutberlet (A.S.H.V.E. Transactions, Vol. 43. 1937. p. 131). c;ir^`K2E't^r?S^RCnu^EPORj N.1161--FeverTherapy Locally Induced by Conditioned Air. by M. B. Ferderber, F. G. Houghten and Carl Gutberlet (A.&H.V.E. Transactions. Vol. 46, 1940, p. 307)f * //oj3^^64Sram5)fr Anesthesia Therapy, by L. W. Crossman and S. K. Safford (the Modern 35-AirCleaning as an Aid in the Treatment of. Hay Fever and Bronchial Asthma, by Leo H. Criep and M. A. Green (Journal of Allergy, 7:120, 1936). .. .. .* ___ 1S^T^ ,Effect Humidityand Constant Temperature on Pollen Asthma, by B. Z. Rappa- port, T. Nelson and W. H. Welker (Journal of Allergy, 6:11C 1935). . . : :; SctooTZfPMfc P- Xuslou (The Environment and Its. Effect Upon Man. Huraoed I943)1_ManUal f XyEen Therapy Techniques; by A. H. Andrews. Jr. (Tie Year Book Publishers. Inc., , , ""Prindples and Practices of Inhalational Therapy, by A. L. Barach (J. B. Llppincbtt Co:, Phila~The Management of Pneumonia, by j. G. M. Bullowai. (Oxford University Press, p. 260. 1937). CHAPTER 14 General Procedure, Outside Temperatures, Inside Tempera- ` tures, Attic Temperatures, Temperatures in XJnheated Spaces, Ground Temperatures, Basement Temperatures and Heat ' Loss, Transmission Heat Loss, Heat Loss Through Ceilings . and Roofs, Infiltration Loss, Selection of Wind Velocities, Auxiliary Heat Sources, Intermittently Heated Buildings, Residence Heat Loss Problems - IN the design of a heating system, an estimate must be made of the maximum probable heat loss of each room or space to be heated, based on maintaining a specified inside air temperature during periods of minimum selected design weather conditions. The heat losses may be divided into two groups, namely (1) the transmission losses or heat losses through the confining walls, floor, ceiling, glass or other surfaces and (2) the infiltration losses or heat losses due to air leakage through cracks and crevices, around doors and windows, opening of doors and other sources of interchange of air between the inside and outside. GENERAL PROCEDURE The general procedure for calculating heat losses of a structure is: 1. Select the outside design temperature. The data on climatic conditions given in Table 1 and the Design Temperature Zone Map, Fig. 1, will be.useful but should be applied with judgment as suggested in the section Outside Design Temperatures. 2. Select the inside air temperature, at the 60-in. breathing line or the 30-in. line, which is to be maintained in the building during the coldest weather. (See Table 2). 3. Estimate temperatures in adjacent unheated spaces and the attic. The attic temperature need not be estimated if the combined roof and ceiling coefficient is used. 4. Select or compute the heat transmission coefficients for outside walls and glass; also for inside walls, floors, or top-floor ceilings, if these are next to. unheated space; include roof if next to heated space. (See Chapter 6). : 5. Measure amount of net outside wall, glass and roof next to heated spaces, as well as any cold walls, floors or ceilings next to unheated space. Such measurements are made from building plans, or from the actual building, using inside dimensions. 6. Compute the heat transmission losses, for each kind of wall, glass, floor, ceiling and.'roof in the building by multiplying the heat transmission coefficient in each case by the area of the surface in square* feet and the temperature difference between the inside and outside air. (See Items 1, 2, and 3). 7. Select unit values and compute the heat equivalent pf the infiltration of cold air taking.place around outside doors and windows. These unit values'depend on the kind or width of crack and wind velocity, and when multiplied by the length of crack and the temperature difference between the inside and outside air, the result expresses the heat required to warm up the cold air leaking into the building per hour. (See Chapter 8). 8. The sum of the heat losses by transmission (Item 6) through the outside wall and glass, as well as through any cold floors, ceilings or roof, plus the heat.equivalent (Item 7) of the cold air entering by infiltration, or required to replace mechanical exhaust, represents the total heat loss equivalent for any building. OUTSIDE DESIGN TEMPERATURES ' There are no hard.and fast.rules for selecting the outside: design tem perature to be used for a given locality or type of building or heating system, and the problem is to some extent a matter of judgement, and experience. The outside design temperature is seldom, taken as the lowest temperature, or even the lowest daily mean temperature ever recorded in a given locality. Such temperatures are rarely repeated in successive years. A temperature somewhat higher than the minimum or the lowest daily mean on record may properly be assumed in making the heat los$ ' .... 257 -- *.................................. -- - 258 , CHAPTER: 14) .'> '__ 1946 Guide' Table 1. ' Climatic Conditions Compiled from Weather Bureau Records3 Col. A Col. B . Col. C . Col. D Col. E Col. P - Col- G State ' - Normal City Temperature, Oct. 1- May 1 . AAvnenraugael . Minimum ' Tempera* tureb ; Ayerage Wiod ' - Velocity.' ' Dec.. Jan.-, Feb.. MUee Hour Direction of Prevailing Wind, Dec, Jan_ Feb. Alabama..,.____ _ Birmingham:___ 53.8 . . -10 12 8.0 N 58.9: -1. . 22 10.2 N Phoenix as 8 59.5 -30 16 -15 26 7.8 ..'5.3 SW E. 5ft A. -15 ` 6 8.1 E .. Little Rock 51.6 ,--12 - id 8:3 NW ' California.-.:.....__ Los Angeles..:.__ . 58.5 ! ; 28 , 37 6.3 : NE Colorado San Francisco. 54.2. aa-ft .* Grand Junction.'. : 38.9 27 -29 -21. 37 -11 -2 7.5 . 7.5 4.3 N sNW' V ,1 Connecticut --. New Haven.. :... - 38.4 ' ' -15 9.5 N District of Col.__ : - 43 4 i. I " -15 - -1 7.9 NW-- Florida___...._____ Jacksonville____ . 62.0. . 10 .. 29 9.1 NE Georgia. --............ Atlanta_________ 51.5 -8,. 12 11.4 . NW Savannah........... - 58.5 8 22 9.5 ' NW 1 ` Idaho__;................. Lewiston ....... . 42.3-. . -23 . > 1 5.3 E Pocatello.j;_.'. 35.7 - -28 - -12 9.3 SE Illinois___ - 36 4 ..-23 ,. -8 12.5 . W Springfield..-___ . 39.8 ' -24" ' -7 12.1 NW Indiana____ u___ Evansville 45.1 --16: 9.8 ;. . S Iowa........ - I ndianapolis-.--- . 40.3; \ -25 . . .. --6;: .11.5 , s . .. 33 9-' -32 . -17 .. 7.1 1 NW Sioux City______: 32.6 .->35 , - 20 . .. 11.6 . NW Kansas..-__ _____ Concordia______ V 39.8;. ,-25,: ,-13 7.7, . N : , N- . ` 41.4 -26 -10 10.3 NW. Kentucky.__l..:... Louisville -___ 45.3 Louisiana New Orleans. . 61.6 -20 ` '. -5; ; 9.9 . ' SW' '' 7 ' .26- ' 8.7 NE ' Shreveport---:-. ' 56.2 , =16"' 8.1 SE ' Maine.---....- . Eastport..Portland____ s. 31.5 > 33.8 -23 --15` '--21=" . V 12.6 - 9.2 ! NW '=: NW = .... 43 :-7 ;. n .8 -8.1, .. SW Massachusetts___ .Boston . > : 38.1 : -is:: . : .--3, ; 11.2 : Michigan Alpena . >-..> > 29.6.!/ j c-28-. : --.12-:.. ;..11.0 W ... W' Detroit__.___ ... 35.8 ... i -24;. , r^ll. . . -12.7... SW. Marquette-- . - 28.3,i; .i!--27;,. -13, ; , 1018 NW- , Minnesota..-- " ;,:'24.3 ` 1 -41; ... ,,^28, . 13.5 SW Minneapolis-___ 29.4 ...-.34;.; . -23 ' ,11.3.;, `.NW Mississippi____ ___ Vicksburg- . ,, 56.8 Missourii...,,:._^.;__ St. Joseph-:'.'---- ''>39.5':: `-1 .;. is . 8.3 ; . SE - -24"' r]2.;'' ?' 9:3 ' w.. St. Louis-l----. ; 43.6 ; '.-22''; ' "-2 '11.7. "S ' Montana. _ Springfield-- '44.3'' ''. -29 ." "10.9" SE ` ' Billings----^.--. '34:3- ` ; .--3o. 11.9 : sw ' Havre___ '27.6" ` '-57"' ' --36 ' ' " 1 915' ' sw =-" Nebraska:.....:^-- Lincoln----^. ; 37.0 -29 '--13-' 10.7.- s ' Nevada1 North Platte.^ "35.4"; -35 "'-171 ' " 8.3 - W " n 3Q7 -15 . ' -2 ' 10.0 1 SE Winnemurra f - 37.9 " !n--36 10' 8.2'- NET New Hampshire.. Concord 33.3 ..-35 6.6 NW New Jersey...____ Atlantic City//.I :4i.6,- -9 New.York.............. Albany_________ 35.2 : -24 6./ -11 15.6 8.4 sNW.. B uffalo..:. = 34.8 < -20 ' 17.2" w V : New York-- .40.7/0 ;^14; ; 3 = 16.7/ NW-1: New Mexico.-- Santa Fe_. t 38.3- -13.; :,= 0 : (7:8, (1; i-NE.'.: Noith Carolina.-- Raleigh . . .. ' Wilmington ' 50.0;" 0.-2.,; ' ' .''54.3'', ' ' ' 5': . .,1183-. , :r;7.9 ' '8.1 ' !.SW. : w' North Dakota!.-./. Bismarck" '. "24.6 . " 1 "--45 1 :'.'* ': r>: . Devils Lake--:. 20.3 : -46.: Ohio........;;.;.....__ _ Cleveland-- -- . 37.2 . : = -17 !i --31.: 1 ' 9.01:1 -NW'5- . -33 , if >10.4 0 -W.; -2. , ,15.0 SW , ; Columbus____ ___ -1- 39.- 9. ' .1. v -2: . - 11.6,.. SW Heating- Load 259 Table l. Climatic Conditions Compiled from Weather Bureau Records3--' ' . (Concluded) ,' -- Col. A . State ' or Province Col. B City Col. C Col. D Col. E Normal ,, Lowest Temperature, Temperature Oct 1* Ever May 1 Reported Average Annoai Minimum Tempera ' tureb . Col. F .. Col. G Average - Wind Velocity Dec., Jan., Pelk, Miles per Hour Direction of Revailiog Wind, Dec^ Jam, ' Feb. Oklahoma City.. . 47.9 -17 '2 11.8 NW 35.2 -25 -17 . 6.8 SE Portland-............. 46.1 -2 18 . 7.4 s Pennsylvania_-- Philadelphia____ Pittsburgh'........... 42.7 41.0 -11 -20 6 11.0 . -2 11.7 NW W Rhode Island____ Providence------- - 37.2 = -17 1 12.6 NW South Carolina.... Charleston--------- 57.4 7 22 10.6 sw Columbia------------ 54.0 -2. 19 8.1 NE 28.2 -43 -26 10.5' NW Rapid City.,,____ 33:4 -34 -21 7.9 W Tennessee..... Knoxville.............. 47.9 . Memphis------------ 51.1 -16 -9 . 2 7.1. SW 9 9.4 s Texas........... ----- El Paso--------------- 53.5 Ft. Worth----- ... 55.2 -5 -8 16 9.0 . NW 12 10.3 NW San Antonio.____ 60.6 4 21 8.3 NE Utah........................ Modena-------------- 36.3 Salt Lake City-- 40.0' -32 -20 -15 2 .9.3 6.7 w. SE . Vermont______ ..... Burlington.-,__1. 31:5 Virginia------------- ... Lynchburg....:..'... ,, .46.8 : 49.3 -29'. -17 -7 . 8 2 15 11.7 .. v S : ` 8.1 . NW 12.4 N Richmond_______ / 47.0 -3 10 8.0 . SW Washington___ _ Seattle--..*--------- . 46.3 3 20 10:1 ' SE Spokane.....*.:........ 37.7 -30 -5 6.3 SW "West Virginia____ Elkins___________ 39.4 ' -28 -8 5.8 , w Parkersburg____ .42.6. -27 -1 7.3 SW ' Wisconsin__ Green Bay...:...... 30.0 -36 -18 10.6 SW - LaCrosse. ..L____ 31.7 -43 -21 5.6 . S Milwaukee___ .. 33.4 -25 -12 12.0 w. Wyoming___ ;____ Lander____:--------- 30.0 -40 -12 3.9 sw Sheridan.. .... 31.0 -41 -26 5.1 NW Alta-----------............ Edmonton.. ___ 22.8 -57 -41.3 7.5 sw .: B. C- .... _____ Vancouver.__ . 42.6 2 13.1 . 4.5 ,.E ' Victoria--------- ----- 44.0 -2 19.4 12.6 N Man._______ ___ Winnipeg--___ _ 17.2 -54 -37.7 10.1 ' NW N. B____ .,________ Fredericton, __ 27.5 -35 -25.0 9.1 NW N. S.._,,T.. ___ Yarmouth---------- 34.8 -12- -0.1 14.3 . NW Ont. _______ .____ London...-11_____ 32.6 -27 -13.7 10.3. . `W > Ottawa_____ 26.4: . -35 --24:1 . 8.4 -W *' : Port Arthur.......:. 22.0 Toronto-- .. .. .32.6 --40 -26 -29.5 8.0. -11.2. 13.6 NW SW P. E. I.. _________ Charlottetown--. v- 29.4 -27 ^13:2 9.8, NW ; ,, Que.__--......... 28.1 -29 -18.4. 11.3 SW Quebec--..:__ 24.5 -34 -2312 13.3 SW Sask--------------------- Prince Albert...-- 16.0 -70 . -47.3 5.1 .w. 1.9 -68". .-54.3 3.7 s . Newfoundland___ St. Johns_______ . 31.4 . -21 = . -5.3 12 sw "United States data from U. S. Weather Bureau, and Canadian data from Meteorological Service! of Canada, corrected to 1943. ` ... ": hObtaihed by averaging the lowest temperatures (one for each year) recorded for the period of years the local Weather Bureau has been in operation. . -. ' computations. Column D,Table l.lists the lowest dry-bulb temperatures ever reported'in the plaices listed.'. Column E, Table 1, shows the average of the lowest "annual dry-bulb temperatures for the 'same localities. Temperatures for other cities may. be obtairied from local weather bureau records`. '-The design.temperatures shown in Fig:, 1 are generally reprer sentative of the practice in various sections of the United States, although' 260 CHAPTER 14 -- 1946 Guide in spme instances, due to local conditions of altitude or exposure, the design temperatures may vary somewhat from those indicated. ' ' ' The A.S.H.V.E. Technical Advisory Committee on Weather, Design Conditions has recommended the adoption for heating of an. outside design temperature which is equalled or exceeded during 97J^ per cent Heating Load 261 of the hours in December, January, February, and March, but the work of compiling the various local temperatures is not yet completed. INSIDE TEMPERATURES The inside air temperature which must be maintained within a building is understood to be the dry-bulb temperature at the breathing line, 5 ft above the floor, or the 30-in. line, and not less than 3 ft from the outside walls. Inside air, temperatures, usually specified, vary in accordance with the use to which the building is to be put and Table 2 presents values which conform to good practice. Table 2. Winter Inside Dry-Bulb Temperatures Usually Specified3 Type of Building Dbg F Type of Building Dbg F Schools-- Class rooms._________ ____ ____ Gymnasiums............... --__________ Toilets and baths_~. .. .. Wardrobe and locker rooms.... 70-72 68-72 55-65 70 65-68 Playrooms-- . .- -- -- 65-70 60-65 75 Hospitals-- Private rooms (surgical)_______ Operating,rooms._____________ .... Wards__________ ______ _____________ Toilets___ __ _ _ _______ Bathrooms..................... ............... ... 70-72 70-80 70-95 68 66 68 70-80 Theaters^- ^ Seating space. ..................... ...... Toilets. ------------------------ .. 68-72 68-72 68 , Hotels-- Kitchens and laundries__ ______ Toilets and service rooms........... 70 70 66 65-68 68 - Homf.r ............................... Stores____ 1.................................. ...... Public buildings!.................. Warm air baths.___________________ Factories and machine shops. Foundries and boiler shops__ Paint shops._________________________ 70-72 65-68 68-72 120 .110... 60-65 50-60 80 The most comfortable dry-bulb.temperature to be maintained depends on the relative humidity and air motion. These three factors considered together constitute what is termed the effective temperature. (See Chapter 12.) When relative humidity is not controlled separately, optimum dry-bulb temperature for comfort will be slightly higher than shown in Table 2. - ' - - The proper dry-bulb temperature to be maintained depends upon the ' relative humidity and air motion, as explained in Chapter 12. In other words, a person may feel warm or cool at the same dry-bulb temperature, depending on the relative humidity and air motion. The optimum winter effective temperature for sedentary persons, as determined at the A.S.H. V.E. Research-Laboratory, is 66 deg. .- . As explained in Chapter 12 for-so-called still air conditions, a relative, humidity of approximately 50 per cent is required to produce, an effective temperature of 66 deg when the dry-bulb temperature is 70 F. However, even where provision is made for artificial humidification, the. relative humidity is seldom maintained higher than 40 per cent during the ex tremely cold weather, and where no provision is made for humidification, the relative humidity may be 20 per cent or less. Consequently, in using the figures listed in Table 2, consideration should be given to whether provision is to be made for humidification and, if so,, the actual-relative humidity to:be maintained,. .... . ., ..: : Temperature at Proper Level: - la. making the actual heat loss compu- . tations, however, for the various rooms in a building it is often necessary 262 CHARTER 14 - ._____________ 1946 CUide to modify the temperatures given in Table 2 so that the air temperature at the proper level will be used. By air temperature at the proper level is meant, in the case of walls, the air temperature at the mean height be tween floor and ceiling; in the case of glass, the air temperature at the mean height of the glass; in the case of roof or ceiling, the air temperature at the mean height of the roof or ceiling above the floor of the heated room; and in the case of floors, the air temperature at the floor level. ; . Temperature at Ceiling: The air temperature at the ceiling is generally higher than at the breathing level due to stratification of air resulting from the tendency of the warmer or less dense air to rise. An allowance for this fact should be .made in calculating ceiling heat losses, particularly in the case of high ceilings. However, the exact allowance to be, made may be Table 3. Approximate Temperature Differentials Between Breathing Level and Ceiling, Applicable to Certain Types of Heating Systems Ceiling Height (Ft) 60 Breathing Level Temperature .(5 ft Above Floor) 65 70 72 74 76 78 80 85 90 10 3.0 3.3 3.5 3.6 3.7 3.8 3.9 4:0 4.3 4.5 11 3.6 3.9 4.2 4.3 4.4 4.6 f4.7 4.8 5.1 5:4 12 4.2 4.6 4.9 5.0 5.2 5.3 5.5 5.6 6.0 6:3 13 4.8 5.2 5.6 5.8 5.9 6.1 6.2 6.4 6.8 7:2 14 5.4- 5.9 6.3 6.5 6.7 6.8 7.0 7.2 7.7 8.1 15 6.0 6.5 7.0 7.2 .7.4 7.6 7.8 8.0 8.5 910 16 6.1 6.6 7.1 7.3 7.5 7.7 7.9 8.1 8:6 9.1 i 17 6.2 6.7 7.2 7.4. 7.6 7.8 8.0 8.2 8.7 9.2 18 6.3 6.8 7.3 7.5 7.7 7.9 8:1 8.3 8.8 93 19 6.4 6.9 7.4 7.6 7.8 8.0 8.2 8.4 8.9 9.4 20 6.5 7.0 7-5. 7.7 7.9 8.1 8.3 8.5 9.0 9.5 25 7.0 7.5 8.0 8.2 8.4 8.6 8.8 9.0 9.5 10.0 30 7.5 8.0 8.5- 8.7 8.9 9.1 9.3 9.5 10.0 10:5 35 8.0 8.5 9.0 9.2 9.4 9.6 9.8 10.0 10.5 1110 40 8.5 9.0 9.5 .9.7 9.9 10.1 10.3 10.5 11.0 11.5 . 45 . 9.0 9.5 10.0 10.2 10.4 10.6 10.8 11.0 11.5 12.0 50 , 9.5 10.0 10.5 10.7 10.9 11.1 11.3 11.5 12.0 12.5 ' , The figures in this table are based on an Increase of 1 per cent per foot of height above the breathing wd (5.ft) up to 15ft and 1/10 of one degree for each foot above. 15 ft. This table is generally applicable-, to forced air types of heating systems. For direct radiation or gravity warm air, increase values SO per cent to 100 per cent. ' . * ., t . . ., > , somewhat difficult to determine as it depends,on many factors, including (1-) the. type of heating system, (2) ceiling height,: and (3) the insideoutside temperature differential. The type of heating system is par; ticularly important as the temperature gradient from floor to breathinglevel to ceUing.may depend to a large extent on'whether direct radiation; unit heaters or warm air is used, and in the latter case, whether the circu lation is by gravity, auxiliary fan or forced air. Although with properly, adjusted air flow, the temperature differential with unit heaters can be reduced to a minimum, it is possible with improper adjustment that it ' may be increased over that which.would- normally result without me: chanical circulation of the-air if the air flow is not properly, adjusted. . It would `be difficult from, present available information' to establish rules for determining the temperature difference-'to-use in all cases; However,-.for residences and other structures having ceiling.heights under . 10. ft,-ther comparatively.. small temperature. differential between . the . j Heating-Load 263 breathing level and ceiling, may generally be neglected without serious error.: For higher ceilings.where spedfic:test data are not available; an allowance of approximately 1 per cent per foot of height above the breathing level may be made for ceiling heights up to 15 ft and approxi mately 1/10 of 1 deg per foot of height above this level. The values in Table 3 are calculated on this basis. For direct radiation and. gravity warm air systems, the allowance should be increased from 50 per cent to 100 per cent over those given in Table 3. These rules should, however, be used with considerable discretion. ' Temperature at Floor Level: According to the. University of Illinois Research Residence tests *, the temperature at the floor level ranged from about 2J4 to 6 deg below that at the breathing level, or somewhat, greater than the difference between the breathing level and ceiling temperatures. Tests at the University of Wisconsin* indicated a some what smaller differential between the floor and breathing level tempera-. tures. As a general rule, if the breathing level to ceiling temperature differential is neglected (as with ceiling heights under 10 ft), the breathing level-floor differential may also be neglected as the two are somewhat compensating,'especially where both floor and ceiling^ heat losses are. calculated for the same space. In other cases, the 10 ft temperature differentials in Table 3 may be used in arriving at the floor heat loss, these differentials to be subtracted from the breathing level; temperature. . ; ATTIC TEMPERATURES ;: ; Frequently' it is necessary to estimate the attic.temperature, and *n such cases Equation 1 can be used for'this purpose. ' ' AcUcti ~F to (AtUt *4* AwUmt 4- AgUg) AtUt + Ay/Uyr -h-AgCl, -f- AcUc- (1) where /a = attic temperature, Fahrenheit degrees:- - : = inside temperature near top,floor ceiling,.Fahrenheit.degrees. i0 : outside temperature, Fahrenheit degrees. .. . . : ... Ac. area of .ceiling,.square feet. .. .. ' Ai =. area.of roof, square feet. ^ 'Aw 1 area of net vertical attic wali surface, square feet................... , As = area of attic glass, square feet. ............................ *' * .................. . . .' ...Uc- coefficient of transmission of ceiling, based, on. surface conductance of. -2.20 . (upper surface, see Chapter. 6). . 2.M = reciprocal ofohe`rhatf the/airspace resistance.'7. . V ..VV. :-*./ *. `Ut = . coefficient of - transmission of roof, based on- surface, conductance of .2.20 ; (lower surface, see Chapter 6). ' ; , :.: 5 l Uw coefficient .of transmission of vertical wall surface. . ' ^ U* coefficient of transmission of glass. ... ............... , . . Example 1. Calculate the temperature in.an unheated attic, assuming the following conditions: t\ -- 70; to -- 10;Ac -- 1000;i4r a12d0; 100; Aj 10; Ur = 0.50; Uc 0.40; Uw - 0:30; Ug - 1.13. . - `! - Solution: Substituting these values in Equation 1: * . . . (1000 X 0.40 X 70) + IQ K1200 X 0.50) + (100 X 0.30) + (10 1.13)1 ; ^ ^ =' (1200 X 0.50) +.(10o x 0.30) + (10. x M3) ;-r (iooo x 0.40).. ; 34,413 ' 33.1 F. 1041 .S 264 CHAPTER 14 1946 Guide Equation 1 neglects-the effect of any interchange of air such as would take place through attic vents or louvers intended to preclude attic com densation. However, according to tests *, such venting of attics by means of louvers or other small openings does not appreciably reduce the attic temperature and may be neglected without serious error. The attic temperature may be calculated in the usual manner by means of Equa tion 1, allowing the full value of the roof. The error resulting from this assumption will generally be considerably less than if the roof , were neglected (as is sometimes the practice) and the attic temperature as^ sumed to be. the same as the outside temperature. . TEMPERATURES IN UNHEATED SPACES The heat loss from heated rooms into unheated rooms or spaces must -be based on the estimated or assumed temperature.in such unheated spaces. This temperature will generally range between the inside and outside temperatures, depending on the relative areas of the: surfaces adjacent to the heated room and exposed to the outside. If the respective surface areas adjacent to the heated room and exposed to the outside are approximately the same, and if the coefficients, of transmission are approximately equal, the temperature in the unheated space may be assumed to be the mean of the inside and outside design temperatures. If, however, the surface areas and coefficients are unequal, the tempera ture in the unheated space should be estimated by means of Equation.2. , _ t(A,U, -|- AjUt + AtU, + etc.) + to (Aa.Ua + AbUb 4- AcUc + etc.) AiUi + AtUx + AiUi + etc. + AaVa + AbUb + ACUC + etc. . . , where .. . ' *u = temperature in unheated space, Fahrenheit degrees. / -- inside design temperature of heated room, Fahrenheit degrees.' . to = outside design temperature, Fahrenheit degrees. . . -. Ai, At, At, etc. = areas of surface of unheated' space adjacent to heated space, square feet. . , Aa, A b, Ac, etc. = areas of surface of unheated space exposed to outside, square feet. Ui, U,, Ui, etc. = coefficients of transmission of surfaces of A,, At, Ai, etc. Vo, Ub. Uc, etc. = coefficients of transmission of surfaces Aa, Ab, Ac, etc. . Example S. Calculate the temperature in an unheated space adjacent to a heated room having surface areas (j4r. At, and A,) in contact therewith of 100, 120 and 140 sq ft and coefficients (Vi, XJt, and Ui) of 0.15, 0.20 and 0.25 respectively. The surface areas of the unheated space exposed to the outside (A,, and ,4b) are respectively 100 and 140 sq ft and the corresponding coefficients are 0.10 and 0.30. The sixth surface is on the ground and is neglected .in this example. Assume ! = 70 and to = --10. : . Solution. Substituting in Equation 2: . = 70[(i00X0.15)+(l20X0.20) 4;(140 X0.25)]4- -- I0[(l()0 x0.10)+(140 X0.30)1 " (100 X 0.15) + (120X 0.20) + (140 X 0:25) +(100 X 0.10) + (140 X 0.30) The temperature-in unheated spaces having large glass areas and with two or more surfaces exposed to the outside (such as sleeping porches and sun parlors), are generally assumed to be the same as .the: outside tem perature. . . - " : ;. - Heating Load 265 ... GROUND TEMPERATURES . Ground temperatures to be assumed, for estimating basement heat' losses will usually differ in the case of basement walls and floors, ;the temperatures under the floors being generally higher than those adjacent to walls. ...... Temperatures Adjacent to Basement Walls . Ground temperatures near the surface and under open spaces vary with the climate, the season of the year and the depth below the surface. The nearer the surface (during the cold weather) the lower the tem: perature. Frost will penetrate to a depth of over 4 ft in some localities if not protected by snow. A thick blanket of snow will result in a higher ground temperature near , the surface. Consequently ground tempera tures near die surface may be higher in cold climates where the snow remains on the ground for a greater length of time than in more moderate climates where the snow melts away periodically during the winter. Complete data for various localities are not as yet available but in estimating heat losses through vertical walls below grade* it is advisable not to assume average ground temperatures above 32 F in northern climates when estimating heat losses from heated basements. This is for the mean height of the basement wall. Since the recommended wall coefficient for basement walls in contact with the soil is only 0:10, any small variation in the-assumed ground temperature will.not materially, affect the calculated heat loss. - : Temperatures Under Basement Floors . The temperature under, basement floors6 is influenced by the.heat from the basement or protected from die influence of atmospheric conditions' by the basement. In computing losses through basement floors the ground temperatures may be assumed the same as the approximate water, temperature at depths of 30 to -60 ft given in Fig. 3, Chapter 37.. . Test results indicate that the heat losses through basement flobrs are frequently over estimated6. . BASEMENT TEMPERATURES AND HEAT LOSS The allowance to be made for basement heat loss depends on whether the basement is to be heated or not. If a basement is completely below .grade and is not heated, the tem perature in the basement will normally range between that in the rooms above and the ground temperature. Basement windows will of course lower the basement temperature when it is colder outside arid any heat given off by the heating plant will increase the basement temperature. In any case, the exact basement' temperature is likely to be a somewhat indeterminate.quantity, if the-basement is. not heated. /Since the base ment temperature will generally be lower than that of the rooms above, an allowance should theoretically be made for the loss from the rooms above through the floor over the basernent. If the basement is heated and a specified temperature is id Be main tained, the heat, loss, should be estimated in the usual manner, basedfon' the proper wall and floor, coefficierits (see Chapter 6) and the outside air. and the ground temperatures. Heat loss through windows and Walls 266 ' CHAPTER 14 1946 Guide above grade should be based on outside temperatures and the proper air- to-air coefficients. Heat loss through basement walls below grade should be based on the floor and wall coefficients for surfaces in contact with the soil and on the proper ground temperature. . TRANSMISSION HEAT LOSS The basic formula for the loss of heat by transmission through any -surface is given in Equation 3. . . . .. where Ht - A U (t - <o) /J (3) Ht : heat loss transmitted through the wail, roof, ceiling, floor or glass, Btu' per hour. ., A = area of wall, glass, roof, ceiling, floor or other.exposed surfaces, square feet. U = coefficient of transmission, air to air, Btu per (hour) (square foot) (Fahrenheit degree temperature difference) (Chapter 6). t = inside temperature near surface involved* which may not .necessarily be the . so-called breathing line temperature,. Fahrenheit degrees. to =r outside temperature, or temperature of adjacent unheated space or of the ground,- Fahrenheit degrees. . * .. Example 8. Calculate the transmission loss through an 8 in., brick wall having an . area of 150 sq ft if the inside teinperature (/) fa 70 F and the outside temperature (to) fa --10 F. Solution. The coefficient of transmission ( U) of a plain 8 in. brick wall fa 0.50 (Chapter 6, Table 7). The area (A) is 150 sq ft. Substituting in Equation 3: :. , Ht = 150 X 0.50 X 170 -- ( -- 10)1 = 6000 Btu per hour. Transmission Loss, Through Ceilings and Roofs . The transmission heat loss through top floor ceilings, attics and roofs may be estimated by either of two methods: "* 1. By substituting in Equation 3 the ceiling area (4), the inside-outside temperature difference, (/ -- to) and the proper value of (U): a. Flat roofs. - Select the coefficient of transmission of the ceiling and roof from' 1 Tables 14 or"15, Chapter 6, or use appropriate coefficients in Equation 1 if side walls extend appreciably above the ceiling of the floor below. . b. Pitched roofs. Select the combined roof and ceiling coefficient from Table 17, Chapter 6 or calculate the combined roof and ceiling coefficient by means of Equation 5, Chapter 6, where this formula fa applicable as explained in Chapter 6. 2. By estimating the attic temperature (based on the inside and outside design tem perature) by means of Equation 1, and substituting for to in Equation 3, the value of to thus obtained, together with the ceiling area (A) and the ceiling coefficient (U). This applies to pitched roofs. In the case of flat roofs it fa not necessary to calculate the attic temperatures as the ceiling-roof heat loss can be determined as per paragraph la. ' INFILTRATION HEAT LOSS The infiltration heat loss includes-(1). the sensible heat loss or the heat required to warm the outside air entering by infiltration and (2) the latent heat loss or the heat equivalent of any moisture which must be added. Sensible Heat Loss . "- - .-. - The formula, for the heat- required to warm the outside air which ' enters- a room by infiltration to the temperature of. the room,, is given in Equation 4. Heating Load 267 .' Ht = 0.24 Qd (t - to) -. *, (4) where . *-. - . . . '. - Ha = heat required to raise temperature of air leaking into building from to to t, Btu per hour, 0.24 = specific heat of air. Q = volume of outside air entering building, cubic feet per hour (see Chapter 8). d = density of air at temperature to, pounds per cubic foot. It is sufficiently accurate to use d = 0.075 in which case Equation 4 reduces to . " . H, - 0.018 Q (t - to) (4a) The volume of outside air entering per hour ( depends on the wind velocity and direction, the width of crack or size of openings, the type of openings and other factors, as explained in Chapter 8. Where the crack method is used for estimating leakage, it is more convenient to express the air leakage heat loss in terms of the crack length: Ha = 0.018 QL(t -- to) = B L (t -- to) (4b) where * ..' . B = air leakage per (hour) (foot of crack) (Chapter 8) for the wind velocity and type of windows or door crack involved multiplied by 0.018. . L = length of window or door crack to be taken into consideration, feet. Example 4. What fa the infiltration heat loss per hour through the crack of a 3 x 5 ft average, double-hung, non-weatherstripped, wobd window, based on a wind velocity of 15 mph? Assume inside and outside temperatures to be 70 F and zero respectively. . Solution. According to Table 2, Chapter 8, the air leakage through a window of this type (based on VjJ in. crack and %-t in. clearance) fa 39 cu ft per foot of crack per hour. Therefore, B = 39 X 0.018 = 0.70. The length of crack (L) is (2X5) + (3 X 3), or 19 ft; t = 70 and to -- 0. Substituting in Equation 4b, Hs = 0.70 X 19 X (70 - 0) = 931 Btu per hour. Crack Length to be Used for Computations . ' .' ' . The amount of crack' used for computing the infiltration heat loss should not be less than half of the total crack in the outside walls of the room. For a building having ho partitions, whatever wind enters through the cracks on the windward side must leave- through the cracks on the leeward side. Therefore, take one-half the total crack for1 computing each side and end of the building. In a room with one exposed wall, take all the crack; with two exposed walls, take the wall having the most crack; and with three or four exposed walls, take the wall having the most crack; but in nb case, take less than half the total crack." " The total infiltration loss of a building having partitions will not be equal to the sum of the infiltration losses of the various rooms, since at- any given time infiltration will take place, only, on the windward side or sides and not on the leeward side. Therefore, if a building has more than one room which is divided by interior walls or partitions, it is sufficiently accurate to use half of the total infiltration losses for determining the total heat requirements. , .. . . .' . , Latent Heat Loss ................... j r , .. When it is intended to add moisture to air leaking into a room for .the maintenance, of proper winter comfort conditions, it is .necessary to 268 CHAPTER 14 1946. Guide determine the heat equivalent to evaporate the required amount of water vapor, which may be calculated by the equation: * '" where . - Hi = heat required to increase moisture content of air leaking into building from >o to mi, Btu per hour. Q = volume of outside air entering building, cubic feet per hour, d = density of air at temperature ti, pounds per cubic foot, mi = vapor density of inside air, grains per pound of dry air. m0 = vapor density of outside air, grains per pound of dry air. Afg -- latent heat of vapor at mi, Btu per pound. , If the latent heat of vapor (Afg) is assumed to be 1060. Btu per pound, Equation 5 reduces to . . . . Hi = 0.0114 Q (mi - m0) (5a) Equations 4a, 4b and 5a may also be used for determining the sensible and latent heat gains due to infiltration in cooling load computations. SELECTION OF WIND VELOCITIES The effect of wind on the heating requirements of any building should be given consideration under two heads: 1. Wind movement increases the heat transmission of walls, glass, and roof, affecting poor walls to a much greater extent than good walls. 2. Wind movement materially increases the infiltration (inleakage) ofcold air through the cracks around doors and windows, and even through the building materials them selves, if such materials are at all porous. Theoretically as a basis.for design, the most unfavorable combination of temperature and wind velocity should be chosen. It is entirely possible that a building might require more heat on a windy day with a moderately low outside temperature than on a quiet day with a much lower outside temperature. However, the combination of wind and temperature which is: the worst would differ with different buildings, because wind velocity has a greater effect on . buildings which have .'relatively high infiltration losses.. It would be possible to work.out the heating load for a building for several different combinations of temperature and wind velocity which records show to have occurred and to select^the worst combination; but designers generally do not feel that such a degree of refinement is justified. It has- been the practice for many years in estimating air leakage by the crack method to use the average wind velocity during the. months of December, January and February. This average wind velocity may not necessarily correspond with that occurring during periods when the outside design temperature prevails, the latter being not an average but rather a near extreme, that is,, a specified number of degrees above the lowest temperature recorded in the locality involved.. Therefore instead qf .using the aforementioned average wind velocity, it is the practice of some designers to use in all cases a wind velocity of 15 mph together with the proper design temperature. Although a 15 mph wind velocity is. higher than the general average wind velocity-during December, -January ; and'February.in various United States cities, this and higher wind veloci ties frequently-occur during periods of outside temperature corresponding to the design temperature. - It should be added that this wind velocity Heating Load 269 also corresponds with that on which the heat loss coefficients in Chapter 6 are based, although the effect of variations in wind velocity on the in filtration losses is generally much greater than, the effect of wind velocity on the heat loss by transmission through walls. Therefore, pending further investigation of this subject, either the average during December, . January and February or a 15 mph wind velocity may be used at the discretion of the designer. Where the air change method is used for estimating infiltration losses, the wind velocity is not. considered. Exposure Factors: Many designers use empirical exposure factors to increase the calculated heat loss of rooms dr spaces on the side or sides of the building exposed to the prevailing winds. However, according to a . survey made in 1943, many Guide users have found that the use of exposure factors is not necessary as the Guide method of calculating heat losses provides an ample heat loss allowance. Therefore exposure factors may be regarded as factors of safety for the rooms or spaces exposed to the prevailing winds, to allow for additional capacity for these rooms or spaces, or to balance the radiation, particularly in the case of multi story buildings. Although the exposure allowance is frequently assumed to be 15 per cent, the actual allowance to be made, if any, must to a large extent be a matter of experience and judgment of the designer, since there are at present no authentic test data available from which rules could be developed for the many conditions encountered in practice. As stated previously, the value of U in the tables of Chapter 6 is based on a wind velocity of 15 mph and the surface resistance for this wind velocity (0.17) is sufficiently low that higher wind velocities will decrease the surface resistance to a negligible degree and therefore have only a slight effect on the average over-all coefficient. On the other hand, in filtration losses vary almost directly as the wind velocity, as will be apparent from the factors in Table 2 of Chapter 8. The more exact method therefore would be to differentiate among the various exposures more accurately by. calculating the infiltration and transmission losses separately for the different sides of the building, using different assumed wind velocities for the infiltration losses on the various sides of the building. . .. AUXILIARY HEAT SOURCES The heat supplied by persons, lights, motors and machinery should, always be ascertained in the case of theaters, assembly halls, and in dustrial plants, but allowances for such heat sources must be made only after careful consideration of all local conditions. In many cases, these heat sources should not be allowed to affect the size of the installation at all, although they may have a marked effect on the operation and con trol of the system. In general, it is safe to say that where audiences are involved, the heating installation must have sufficient capacity to bring the building up to the stipulated inside temperature before the -audience arrives. In industrial.plants, quite a different condition exists, and heat sources, if they are always available during the period of human occu pancy, may be substituted for a portion of the heating installation. In no case should the actual heating- installation (exclusive of heat sources) be reduced below that required to maintain at least 40 F in the building. Electric Motors and Machinery Motors and the machinery which they drive, if both are located in the room, convert all of the electrical energy supplied into heat, which is 270 CHAPTER 14 1946 Guide Heating Load 271 retained in the room if the product being manufactured is not removed until its temperature is die same.as the room temperature. If power is transmitted to the machinery from the outside,-then only the heat equivalent of the brake horsepower supplied is used. In the first case the Btu supplied per hour = g^^'oTm^r X 2546' and in the second case Btu per hour = bhp X 2546, in which 2546 is the Btu equivalent of 1 hp-hr. In some mills this is the chief source of heating and it is frequently sufficient to overheat the building even in zero weather, thus requiring cooling by ventilation the year round.. The heat (in Btu per hour) from electric lamps is obtained by multi plying the watts pier lamp by the number of lamps and by 3.413. One cubic foot of producer gas gives off about 150 Btu; one cubic foot of manufactured gas about 535 Btu; and one cubic foot of natural gas about 1000 Btu. A Welsbach burner averages 3 cu ft of gas per hour arid a fish-tail burner, 5 cu ft per hour. For information concerning the heat supplied by persons, refer to data given in Chapter 12. ' INTERMITTENTLY HEATED BUILDINGS In the case of intermittently heated buildings additional heat is required for raising the temperature of the air, the building, materials and the material contents of the building to the specified inside temperature. The rate at which this additional heat must be supplied depends upon the heat capacity of the structure and its material contents and upon the time in which these are to be heated7. This additional heat may be figured aind allowed for as conditions re quire,, but inasmuch as the heating system proportioned for taking care of the heat losses will usually have a capacity about 100 per cent greater than that required for average winter weather, and inasmuch as most buildings may either be continuously heated or have more time allowed for heating-up during the few minimum temperature days,- no allowance is usually made except in the size of boilers or furnaces. For churches, auditoriums and other intermittently, heated buildings, additional capacity should be provided. RESIDENCE HEAT LOSS PROBLEMS Example 6. Calculate the heat loss of residence shown in Fig. 2 located in the vicinity of Chicago. Assume inside and outside design temperatures to be 70;F and --10 F respectively. The attic is unheated: Assume ground temperature to be 50. F under basement'and garage floors, and 32 F adjoining basement walls. Estimate in filtration by crack method, assuming average wind velocity to be 12.5 mph during December, January and February, No Wall, ceiling or roof insulation is tip be figured in this problem, but all first and second floor windows are to have storm sash. The building ' is constructed as follows (transmission coefficients (U) in parentheses): ' Walls: Brick veneer, building paper, wood sheathing, studding, metal lath and plaster (0.28). Walls of dormer over garage, same except wood siding in place of brick veneer (0.26). .' .. - AUic Walls: Brick veneer, building paper, wood sheathing on studding'(0.42), Basement Walls::. 10 in.concrete.(0.10)." ...: Roof: Asphalt shingles on wood sheathing on rafters (0.53). .; Ceiling {Second floor): Metal lath and plaster (0.69). " ' - _ Windows: Double-hung wood windows with storm sash (0.45).. Steel casement sash in basement (1.13). .... :. Floor {Bedroom D): Maple finish flooring on yellow pine sub-flooring;-metal lath and.plaster ceiling below (0.25). .' , 272. CHAPTER 14 1946 Guide Table 4. Heat Loss Calculation Sheet for Uninsulated Residence . 7 ': (Fig. 2) ` " - . . J B ; -- \ .7. c .. D E . F ^- G Room ob Spacb Pabt or Structure ' , Net Abba ob COEFFI Temp. Heat Loss . Totals - Crack Length CIENT Dipf. (Btu per hour) (Btu per boor Walls ' ' ' ' " - ' 238 sq ft 0.28 80 5330 Bedroom A Glass * infiltration 1 . * 40 sq ft 0.45 80 36 lin ftb 0.35c .80 1440 1010 Ceiling4 r . 242 sq ft 0.69 39.8 6660 14,440 Walls' . Bedroom B Glass '' - and Closet Infiltration . 156 sq ft * ' - 40 sq'ft' r ; 36 lin fte 0.28 0.45 0.35 80 80 80 3490' 1440 1010 . *` Ceiling4 . , ` ' . . 160 sq ft 0.69 39.8 . . 4400 10,340 Walls . 114 sq ft 0.28 80 . 2560 Bedroom C Glass ' ' , ` Infiltration 27 sq ft 0.45 80 18 lin ftf 0.35 80 970 500 Ceiling4 .. 120 sq ft 0.69 39.8 3300 . 7,330 Walls . 118 sq ft 0.28 80 2650 Bedroom D Glass 20 sq ft 0.45 80 ' 720 and Closet Infiltration 18 lin ft 0.35 80 500 Ceiling4. -'.:7. ;... ' . 120 sq ft . 0.69 ; 39:8 ,. 3300 h loor over Garage 110 sq ft 0.25 35s 960m 8,130 .Walls . 30 sq ft 0.28 . 80 670 Bathrooml Glass ; . Infiltration 14 sq ft 18 lin ft 0.45 80 . 500 0.35 80 500 Ceiling4 ' - ' 55 sq ft 0.69 39.8 .1510 3,180 Walls ` ' 79-sq ft 0.26 80 ' 1770 Bathroom 2 Glass :. Infiltration . 9 sq ft 0.45 80 .320 15 lin ft 0.35 80 . 420 . Ceiling4 . , . . 35 sq ft 0.69 39.8 960 ' Living Room h loor over Garage ` . Walls Walls (adjoining garage) Glass - 35 sq ft , 267 sq ft . 94 sq ft 50.sq ft . 0.250.28 0.39h 0.45 35 80 ' 35 80 310m 5980- . ,, \ 3,7. 80. . 1280" 1800 Infiltration' * 40 lin ft 0.35 80 1120 `10,180 Dining . Room . Walls Glass .(doors) . . Glass (window) 166 sq ft 35 sq ft 20 sq ft 0.28 1.13 0.45 80 80 80 3720 3160 - 720 . Infiltration1 * 31 lin ft 0.35 80 870 ..... 8,470 Kitchen and Entrance - to Garage ' Walls (Outside)' - 96 sq ft " 0.28 Walls (adjoining garage) 51 sq ft 0.39h Infiltration 27 lin ft 0.35 Glass - - .- 18 sq ft . 0.45 , 80 35 80 80 2150 700" 760 650 Door to garage , 17 sq ft : * 0.51 35 300" 4,560 Walls (outside) . . 82 sq ft 0.28 80 1840. Lavette and Vestibule Walls (adjoining garage) 85 sq ft Door . .. . 19 sq.ft Glass . . ,, ' . : 9,sq ft 0.39h 35 ,0.51 80 0.45 . '80 1160" 780 320 >' Infiltration . 119 lin ft 0.35 80 . 530 . 4,630. Entrance Hall Walls , . Door . Infiltration. . \ . 7 39 sq ft . 21 sq ft 20 lin ft 0.28 0.38 0.35 80 80 V 80 870 . '640 ' 560 Ceiling4* p 87 sq ft 0.69 39.8 2490 ' 4,560 Walls - - , 167 sq ft .0.28 45 . 2110 Glass : . #- 53 sq ft .1.13 45 . ,,2700; . Garage Doors *x 44 sq ft 0.51 45 1010 Infiltration , . . 37 lin ft .1.62) 45 . - 2700 ' Floor (heat gain) 185 sq ft 0.10k -15^ -280. Heat gain -4710" 3,530 Floor * . ' : 287' sq ft ' 0.10 20 ' - 570 Recreation Walls .220 sqift . 0.10 ,38.. :V 840- . Roomn Glass, . . 8 sq ft 1.13 80 .. : 720 ' Infiltration 8 lin ft 0.76' 80 ` .490 . 2,620.. . - U - . < .Total. ' 85,750 i Notes for Table 4. \ The inside-outside temperature difference is 70 -? ( --10) or 80 F, except where otherwise not bOnly the south windows are used for arriving at the window crack-for this room, on the assn that whatever air enters through the south window cracks .will- leave through the west window or elsewhere. . . - cDouble-hung wood windows with storm sash are assumed to have the same leakage per foot of c. , as weatherstripped windows. The air leakage per foot of crack is about 19.5 cu ft per foot of crack ft wind velocity of 12.5 mph. fSee Table 2. Chapter 8.) The heat equivalent of the air leakage per (hoi , (degree temperature difference per foot of crack) is obtained by multiplying this value by 0.018. or 19.5 X 0.018 = 0.35. . .. din problem the ceiling heat losses are calculated by estimating the attic-temperature and then calculating the loss through the ceiling using the proper temperature difference. This unheated attic is not ventilated during the winter months. The attic temperature is estimated from Equation 4 to be 30.2 F when the outside temperature is --10 F and the room temperature is 70 F. The temperature difference b therefore 70 - 30.2 or 39.8 F. The window crack in the west wall having two windows is used... `. ' ` ` COne-half the total crack is used in these rooms. . ... - .. (Temperature in garage assumed to be 35 F. ' ' hCoefficient for wall adjoining garage calculated on basis of metal lath and plaster on both sides of studs. (U " 0.39.) IThe door crack is used for estimating the infiltration in this room and as the French doors are weatherstripped the infiltration coefficient b assumed to be the same as in Note h. jThe leakage for the garage doors b assumed to be twice that for.poorly-fitted double-hung wood windows or about 90 cu ft per foot of crack for a wind velocity of 12.5 mph. The infiltration coefficient b therefore 0.018 X 90 or 1.62. , - - i kThe ground temperature b assumed to be 50 F and. as the garage temperature b 35 F. the heat transfer will be from the ground to the garage, and this heat gain should therefore be subtracted from the heat loss. mThe heat losses from various rooms into the garage are heat gains for the garage. nHeat is to be provided for the recreation room and this space b therefore figured onthebasb ofa70 F temperature. Heat loss into the basement from recreation room.is neglected, the calculations being based only on losses through the outside walls, glass and floor. '. pThe upstairs ball ceiling b included with the downstairs entrance hall because these are connected by means of the stairway. The heat should be provided downstairs.. Example 5 {continued) Floor {Basement and Garage): = .. 4 in. stone concrete on 3. in. cinder concrete (0J0). Solution: The calculations for this problem are given in.Table .4, and a summary of the results in Table 5. The values in column F of Table 4 were obtained by multiplying together the figures in columns C, D and E. The heat losses are calculated to the nearest 10 Btu. See reference notes for Table 4 for further explanation of data. . Attention is called to the summary of heat losses (Table 5) of the uninsulated residence (Fig. 2). As storm windows are used in this instance the glass and door trans- Table 5. Summary .of Heat Losses of Uninsulated Residence Heat losses given in. Btu per hour .. Room ob Spacb Bedroom A Bedroom B Bedroom C Bedroom D Bathroom 1 . Bathroom 2 Living Room Dining Room Kitchen Lavette Entrance Hall Garage Recreation Totals ., Percentages ' Walls Ceiling and Root Floob Glass and Doob Infiltration Totals 5330 3490 2560 2650' 670 1770 .7260 3720 2850 3000 870 -1030s 840 \ 6660 4400 , 3300 3300 1510. 960 .. 960 310 . 2490 . -1550b ----- 570 1440 1440 970 . 720 . '500. , 320 . 1800 3880 950 1100 . 640 3410 720. 1010 1010 500 . 500500 , 420 . .. 1120 870 760 530 560 . 2700 490 . 14^440 10,340 7,330 8,130 . 3,180 : 3,780 . 10,180 .8,470 4,560 . 4,630 4,560 , 3,530 ; 2,620 33,980 . 22,620 39.6 26.4 .290 . 03 .17,890 '' ' 2olO 10,970 12.8 85,750 lOOO' "Wall heat loss of 2110 Btu minus wail heat gain of'3140 Btu. bHeat gains; 960, 310 and 280 Btu. 274 . *____ CHAPTER 14 _________ 1946 Guide CHAPTER 15 mission heat losses of 20.9 per cent are-relatively small. The infiltration losses (12.8 per cent) are also comparatively small in this case because the storm windows serve substantially the same purpose as weatherstripping. In this problem, the wall, ceiling and Boor transmission losses comprise 66.3 per cent of the total. * Example 6. Calculate the heat loss of residence shown in Fig. 2 based on the same conditions as in Example 5 but having construction improved or insulated to obtain coefficients as follows: Walls, 0.13; Walls of Dormer over Garage,-0.12; Attic Walls, 0.28; Walls Adjoining Garage, 0.18; Basement Walls (Recreation Room), 0.10. . Roof, 0.53. . . Ceiling {Second Floor), 0.15. .. * . - Windows (Same as in Example 5). y- Floor {Bedroom D), 0.18. ` Solution: The procedure for calculating the heat losses is similar to that" for. Example ' 6. A summary of the results is given in Table 6. . Table 6. Summary of Heat Losses of Insulated Residence ` Heat losses given in Btu per hour * - Room or Space Walls -CsoiNO and-Roof Floor Glass and Door Infiltration tTotals Bedroom A Bedroom B Bedroom C Bedroom D Bathroom 1 Bathroom 2 - Living Room .Dining Room Kitchen Lavette Entrance Hall Garage Recreation 2670 1750 1280 1320 340 ` 820 3580 .1860 . 1400 1460 440 --400s 840 2370 1570 1170 1170 540 . 340 __ __ ' 850 -- ... ' 690 * - _2_20 .__ ___. .... - -1190b 570 1440 1440 970 720 *500 320 1800 3880 950 1100 640 3410 720 1010 1010 500 500 500 . ' 420 1120 870 760 - 530 ' 560 2700 490 7,490 5,770 3,920 4,400 1,880 2,120 6,500 6,610 3,110. 3,090 2,490 4,520 2,620 Totals 17,360 .8,010 290 17,890 10,970 54,520 Percentages 31.9 14.7 0.5 _ . 32.8 i 20.1 100.0 - Wall loss of 1050 Btu'minus gains of 590.-320 and 540 Btu. - bHeat gains; 690, 220 and 280 Btu. , REFERENCES > . ; 1--An Analysis of Winter Temperatures for,One Hundred and Twenty Cities, by Clark M. Humphreys. (Carnegie Institute of Technology Bulletin). ' " *--Investigation of Oil-Fired Forced Air Furnace Systems' in the Research Residence, by A. P. Kratz . and-S.-Konzo (University of Illinois Engineering Experiment Station Bulletin No. 318). , v ' *--A.S.H.V.E. Research Report No. 1011--Tests of Three Heating Systems in an Industrial Type of Building, by G. L. Larson. D. W. Nelson, and John James (A.S.H.V.E. Transactions. Vol. 41.1935. p. 185): 4--Methods of Moisture Control and Their Application to Building Construction, by F. B. Rowley. A. B. Algren and C. E. Lund. University of Minnesota, Engineering Experiment Station Bulletin, Np. 17).' . --A.S.H.V.E Research Report No. 1213-1:-Heat Loss Through Basement Walls and Floors, by F. C: Houghten. & I. Taimuty. Carl Gutberlet and C. J. Brown (A.S.H.V.E. Transactions, Vol. 48. 1942, p. 369). . '` .- . ; --Measurements of Heat Losses from Slab Floor, by R.-S. Dill, W. C. Robinson and H. E. Robinson (U. S. Department of Commerce, National Bureau of Standards, Building Materials and Structures Report BMS 103). *\ 7--Heat Requirement Tables for Intermittently Heated Buildings, (Engineering Experiment Station Bulletin, No. 60. A. and M. College of 7Yxos.'College Station. Texas), contains a set of tables applicable to either intermittent heating or cooling. Further information may be found in a paper, A Method of Coni- ..' piling Tables for Intermittent Heating, by Elmer G. Smith (A.S.H.V.E. Journal Section, Seating, Piping and Air Conditioning, June, 1942, p.-386). ' - , ' Design Outside Temperatures, Components of Heat Gain, Normal Heat Transmission, Solar Heat Transmission, Solar Radiation Through Glass, Heat Introduced by Outside Air, Heat Emission of Appliances, Moisture Through Walls ' . . , . :' . LOAD calculations for summer air conditioning are more complicated than heating load calculations. Due to the variable nature of some of the contributing load components and the fact that they do not necessarily impose their- maximum effect simultaneously, considerable care must be used in determining their phase relationship. The conditions to be maintained in an enclosure depend upon several factors, especially the outside design conditions, duration of occupancy, and relationship between air motion, dry-bulb and wet-bulb temperatures: Information concerning the proper indoor effective temperature to be maintained is given in Chapter 12, for different geographical locations' and for various age groups of individuals. Typical commercial design room conditions for the summer average peak load are shown in Table 1. Summer dry-bulb and wet-bulb temperatures of various cities are given in Table 2. The temperatures are not the maximums but the design tem peratures which should be Used in air conditioning calculations. The maximum outside wet-bulb temperatures as given in Weather Bureau reports usually occur only from 1 to 4 per cent of the time, and because they are. of such short duration it is not practicable to design a cooling system for them. The temperatures shown in Table 2 are based on available design conditions known to be applied successfully.. . COMPONENTS OF HEAT GAIN . c A cooling load determination is composed of five components which are classified in the following manner: , . , ...... , ' "i ] :: ; -- ' 1. Normal heat transfer through windows, walls, partitions, doors, floors, ceilings, etc. ' 2. Transfer of solar radiation through windows, walls, doors, skylights, and roof 3. Heat emission of occupants within enclosures. 4. Heat introduced by infiltration of outside air and controlled ventilation. . 5. Heat emission of mechanical,. chemical,. gas, steam, hot water, and electrical ' appliances located within enclosures. . The components of heat gain; classified by source, are further classified , as sensible and latent heat gain. .` * - The first two components fall into the classification of sensible heat ' gain, that is, they tend to raise the temperature of the air within the . structure. The last three components not only produce.sensible heat gain but they may also tend to increase the moisture content of the air- i- within-.the structure. ' Normal Heat Transmission ' . ,' By normal heat transmission; as distinguished from solar heat trans mission, is meant the transmission- of heat through' windows, walls; , ^partitions,.etc. from without to interior of enclosure by. virtue of difference 'i between outside and inside air temperatures. Since the daily range of 276 , CHAPTER IS \ 1946 Guide Table 1. Typical Commercial Design Room Conditions for Summer Average, Peak Load* Type of Installation Dry-Bulb Temp Deluxe Application_______ _ Normal Application............... 15 to 40 min Occupancy...... 78 ' 80 82 Wet-Bulb Temp Relative Humidity Per Cent 65.25; 67 68 1 50 51 49 Grains Per Lb ' 72.7 ' 78.5 ' 80.0 Effective Temp ' 72.2 . 74.0 75.3 ' `Values in Tablet are'for peak load-conditions. It is general practice to operate a system' at-approxi mately 76 F and 50 per cent relative humidity at other than i>eak load. , . . i. outside air temperature is usually in. excess of 20 .F, the effective outside temperature for normal heat transmission through walls and floors having substantial heat capacity is usually taken 5. to 10 deg below the design maximum outside temperature. For windows, however, the instantaneous value of outside temperature is used. This load is calculated in a manner similar to that described ini Chapter 14 (except that flow of heat is reversed) by means of the formula: .. Ht -- ATJ (fe - t) . ' (l) where ' .. ' ?. Ut heat transmitted through the material of wall, glass, floor, etc., Btu per hour. , A ~ 'net inside area of wall, glass, floor, etc., square feet. .' i t = inside temperature, Fahrenheit degrees. . te = effective outside temperature, Fahrenheit degrees. U = coefficient of transmission of wall, glass, floor, etc,, from Tables 4 to 18, Chapter 6, Btu per (hour) (square foot) (Fahrenheit degree difference in temperature). Solar Heat Transmission - - Calculations of the solar heat transmitted^through walls and roofs are difficult because of periodic character of heat flow and time lag due to heat capacity of construction.- f : '' - An illustration of the variation in radiation intensity on differently oriented surfaces is given in Fig., 1... The greater part of the radiation .intensity is always direct radiation from the sun.,., However, during the time when the sun is shining, any surface receives radiation of a lower . Table 2. ' Design Dry- and Wet-Bulb Temperatures, Wind Velocities, and ' -Wind Directions For June. July, August, and September - 1 1 SfcATl` - ' 1 - Cot * - Design Del-Bulb c Design , Wet-Bui* 8DmcEB Wind Velocot . MPH PbETAILINO SuiaoB Wind Dxhectiqn Ala.. _ Birmingham.-:____:___ :__:__-- 95 78 ' 5.2 s .' ' Mobile- ---; ~ ----- :-- - 95 - :80 . 8.6- sw . 105.. 76 ... 6.0- w Ark_________ Little Rock............. 95- 78 7.0 , NE Calif;________ Los Angeles- ____ .. . 90 70 6.0 SW ' 90 65 1L0 sw 95 '64-' : - 6.8 - '-s' ' ' 95 .75 7.3 s iW D.-'C........ 95 " '78' Washington-TM.___---_____ ' '95 - ' 78 9.7 ' ' 6.2 sw ; s. Fla : . 95 i 78 . . 8.7 SW V ,Tampa.... _____ -- 94 . : 79 7.0 ... E ... Cooling-Load 277 Table 2. Design Dry- and Wet-Bulb Temperatures, Wind Velocities, and Wind Directions for June, July, August, and September (Concluded) Stats ^ . Cot Design Dbt-Bulb Design Wet-Bulb Suvhbb Wind Prevailing : Velocot Summsb Wind. MPH DlBBCnON Ga--................. Atlanta___ _________ ____ _________ Savannah.__ _______ .1: 95 95 76 78 7.3 NW 7.8 SW 111......____ -- Chicago... ___ _ .. . Peoria__________________________ - Ind---------------- I ndianapolis.____ _________ _ --. Des Moines................... .................. . Wichita.-!______________ ;______ 95 95 95 95 95 100 95 65 75 76 76 .. 77' 75 76 5.8 NW. 10.2 ' NE 8.2 S 9.0 SW 6.6 SW 11.0 S 8.0 ' SW . La.............. : New Orleans___________________ Shreveport-^_____________ ______ 95 100 79 78 .7.0 . sw . 6.2 s' Maine___-- Portland. -- __________ 90. . 73 .' 7.3 . s Mr! 95 78 6.9 sw Mass.________ Boston______ _________ __________ 92 75 9.2 sw 95 - 75 10.3 . SW Minn._____ _-- Minneapolis......____________ .. Miss__________ . Vicksburg.____ 1................ ...... --. Mo____________ Kansas City. ~ ____ _ 95 : .95 100 75 78 76 8.4 SE 6.2 SW 9.5 s St. Louis._______________________ 95 78 9.4 , sw Mont;___ _____ Helena__________________________ Nebr______-- Lincoln.--__________ ___________ 95 .95 67 75 . 7.3 9.3 . sw - s. Matt n.'h................. Manchester____________________ N. J------- :-- > Trenton--___ !,,___________ -- N. Y.......... ... Alhany ' ' 95 90 .95 .'92 65 73 78 75 7.4 5.6 10.0 7.1 W : i NW ' SW . : S Buffalo... -------- ---------- 93 75 12.2 : SW ! New York -. . 95 75 12.9 SW N. M_______ ' Santa Fe __________ _____ __ 90 65 6.5 se : . N.C.......... .... Asheville.- ............ ,, 90 75 5.6 . SE i Wilmington___ ;.____ 95 79 7.8 SW : N. Dak..:.:__ Bismarck...... --__;___________ OUa...-- Ore--------- ----Pa. . Cleveland--!...:............. .........Oklahoma City.____________ Portland.-^............................... 95 95 95 101 90 ' 95 - / 73 : 78 , 75 76 65 78 8.8 6.6 . 9.9 . 10.1' .. NW . sw s ' . s . 6.6 9.7-1 NW, sw r Pittsburgh______ ;__ _______ 95 75 9.0 NW R. I...______ Providence-- : ....................... .93 S. C.._______ Charleston-. __1. ................ 95 75 . 80 10.0 9.9 : NW SW ' Greenville. S. Dak.,^_ ___ _ . 95 . -95 ` 76 6.8 75 . . 7.6 . NE S - Tenn-............ Chattanooga______ ___ _____ 95 77 " 6.5 . SW ' Memphis___ - ' 95 . 78 7.5 100 78 1 9.4 SW s El Paso._____ __ ____:..... . 100 69 6.9 E Galveston_____________ :____ 95 , 80 - 9.7 S' .. Houston____________;__ _-- 95 78 7.7' S ; San Antonio.;....... ____ r..... 100 - 78 - 7.4 SE Utah Salt Lake City--____ Vt________ ;... Burlington________ ______--... 92 90 63 73 8.2 SE 8.9 S . Va...,,l___..._. 95 . ' 78 10.9 S, Richmond. _____ :!...........- ,95 78 6.2 ' SW " Wash............. -- W. Va . - iWis_____ ____ Wyo________ Seattle.__________ ............ ....... 85 Spokane______ ................. ......... . 90 Parkersburg.__ 1_____ --______ 95 Madison__________ ___----- 95 Milwaukee.____ :...................... . .95 Cheyenne........................... --__ ,95 65 . 65 75 . 75 . 75 65 7.9 6.5 5.3 8.1 10.4 . . 9.2 1 S' SW SE SW s s . 278 CHAPTER IS 1946. Guide Cnoline Load 279 HEAT FL0W -&T.U PER SO.FT. P/_R HOUR 1. - Fig. 1. Solar Intensity Normal to Sun on Horizontal Surface and on Walls - . for August 1 at 40 Deg North Latitude .. Fig. 2. Heat Flow-Time Relationship for Horizontal Roofs . Fig. 3. Heat Flow-Time Relationship for Horizontal Roofs intensity coming from all parts of the sky due to reflection and refraction. This scattered radiation intensity has been found to vary from a very low . value to values as high as 20 per cent of the total radiation observed on certain days in Pittsburgh. The values shown on the curves in Fig. 1 are . for combined direct solar and scattered sky radiation, and are given to , represent expected design radiation intensity for August 1 for Pittsburgh. They were prepared by the A.S.H.V.E. Laboratory from data 1 obtained by pyrheliometer observations. ' - A study of the curves discloses the periodic relationship and wide vari ation in solar intensity on various surfaces. It will be observed that both the roof (horizontal surface) and south wall radiation curves are in exact phase relationship with each other, while those for the east and west walls: overlap each other due to scattered sky radiation on the west wall during the forenoon and on the east wall during the afternoon.. This phase . relationship has an important bearing on the cooling load. Failure to . . consider the periodic character of heat flow resulting from diurnal move ment of the sun and the lag due to heat capacity of the structure, which determine the timing and magnitude of the heat wave flowing through the wall, may result in a large error in load calculations.' [ The values of solar intensity appearing in Fig. 1 must not be confused with the actual heat transmission through the wall, for much of the solar- radiation impinging against the outer surface fails to pass through the- . wall. Instead it is delivered to the outside air by reflection, radiation,. . ' and convection. A mathematical solution for the determination of solar heat transmission has been developed but the equations involved are too complex , for practical application '. A simpler method embodying an, approximate determination of the maximum contribution, to the cooling load due to heat transfer from the inside surface of a wall exposed to solar radiation has been developed s. ' - ' - The heat flow in summer through various types of roofs and walls has been measured 4-6 by the A.S.H.V.E.- Laboratory. The curves in Figs. 2' / MGTU 1V3H 280 CHAPTER 15 1946 Guide . 110 -100 -3 90 ui a. - 80 ________________ Tot^J--J--------------I i' i i i i i i i 1 6A.M. 8 10 12 2P.M. 4 6 8 10 12 SUN TIME. AUGUST 1 . >: ' .' - Fig. 4. Outside Design Temperature Basis for Figs. 2 and 3 and 3 give the heat flow through the inside surface of roofs 6 with details of . the construction of the roofs tested. The conditions for which these' results are given are: solar radiation for 40 deg north latitude on August 1 as given in Fig. 1, outdoor design temperature reaching a maximum .of 95 F as shown in Fig. 4, and an indoor temperature of 75 F. Due to devi ations in the tests from design temperature, solar conditions, and typical construction it is believed that the values from Figs. 2 and 3, as well as from Figs. 5, 6, 7, and 8 for walls, may be as much as 20 to 30 per cent below normal design expectations. . . Curves in Figs. 5, .6, .7 and 8 were prepared by the A.S.H.V.E. Lab- oratory from tests made there and show the heat flow through the inside surface of three types of walls for various orientations 5.. The results are given for the following conditions: 90 per cent of the solar radiation given in Fig. 1 for 40 deg north latitude on August 1; outdoor design tempera ture reaching a maximum of 95 F, as shown in Fig. 4, and an indoor tem perature of. 78 F and 50 per cent relative humidity. ... . The heat flow shown in Figs; 2, 3, 5, 6, 7 and 8 is a combination of normal transmission and solar radiation-transmission and is the -total heat -flow through the w'all-or roof. Due to. the heat capacity of walls and roofs there is a time lag 2 in the transmission of heat through them as shown by the curves. For the types of construction covered, in these ljgures arid for the conditions indicated, the heat flow through, the inside surface at any given, time can be read directly. ,For other types of con struction, the curves may be used as a guide in estimating the heat flow. Table 3. Time Lag in Transmission of Solar Radiation Through Walls and Roofs . .: .:, . - .. Type and Thickness op Wau, or Roof \ .. Time Lag, Hours 1-in. yellow pine horizontal roof, water proofing, smooth blackiinish______ 2-in. yellow pine horizontal roof, water proofing, smooth black finish ,, 4-inl reinforced clay tile horizontal roof, water proofing, slag finish__ 2-in. gypsum horizontal roof, water proofing, slag finish Slate and slaters felt on 2J in. tongue and grooved yellow pine, sloped roof 4-im gypsum horizontal roof, waterproofing, slag finish __' ,, . .. 6-in. concrete horizontal roof, water proofing, slag finish '' : 1 1H 2J4 2K 2H m' 5 1-in. concrete, 4-in. cinders, lM-in. concrete, water proofing, smooth black v finish- ......... , ................ Wood siding. 1-in. sheathing. 2x4 studs, lath and piaster. ........ 8 -2 - Wood siding, 1-in. sheathing, 2x4 studs (studding' space filled with insula- 4-in. brick; 1-in. sheathing, 2x 4studs, lath and plaster. 5: ' .7 4-in. brick, 8-in. tile and plaster................. ........ " 13-in. brick, plastered ............................ u................. . ____ . 1014 12 : 9-ini brick, 3%-in. tile, 5^-in. air space; 3^-in. tile and lj^-in. plaster.... . 16 ' CnolinsLoad 281 Fig. 5. Heat Flow-Time Relationship for Northern Exposed Walls . HEAT PLOW - B.T.U. PER SOFT. PER HOUR Fig. 7. : Heat Flow-Time Relationship for Southern Exposed Walls' 282 CHAPTER IS 1946' Guide Fig. 8. Heat Flow-Time .Relationship foe Western Exposed Walls The heat gain through southeast and southwest walls can be considered approximately the same as that through east and west walls respectively. The gain through northeast and northwest walls is less than , half that through east and west walls respectively. The time lag for other types of construction is included in Table 3 which was prepared by the A.S.H.V.E. Laboratory from data collected by it and by other authorities. . ' Solar Radiation Transmitted Through Glass : Windows present a problem'somewhat different from that of opaque walls, because they permit a large percentage of the solar energy to pass through. A small portion is reflected and an additional portion is ab sorbed by the glass. The reflected portion increases with the index of refraction and with the decrease of the angle of the sun with the' glass. The absorbed portion increases with the glass thickness and with decreas ing angle of the sun with the glass. It also depends on the character of glass; some heat.absorbing glass having a very high absorptive value. The absorbed heat warms the glass, causing an increase in the inward flow of heat due to temperature difference. In effect, therefore, a portion of the absorbed heat passes inward and can be considered as a part of the room load due to solar radiation. Particularly where heat: absorbent glass or glass block is used, without shades; the increase in temperature of the inner surface may be sufficiently great to cause serious added discomfort due to direct radiation of heat. 1. ' The amount of heat delivered to a room due to solar radiation may be obtained from'Tables 4 to 9. -These.values should be used only for the net glass area on which the sun shines. In addition, to obtain the total heat gain, computation should be made of the heat transmission due to temperature difference according to Equation 1. The solar radiation data . Cooling Load 283 Table 4. Solar Radiation Transmitted By Single Unshaded Glass for , Variously Oriented Vertical Surfaces and a Horizontal Surface ' For 6 Deg North Latitude on August /a. b, c Sun Time Altitude 8 A.M. 7 8 9 10 11 12 1 P.M. 2 3 4 5 6 . 7.5' 20.5 34.0 47.5 61.5 74.5 83.0 74.5 61.5 47.5 34.0 20.5 7.5 Solar Radiation Transmitted. Btu per (Hour) (Square FooT) North east ` East 77 145 148 123 67 28 16 16 16 15 13 10 3 84 173 193 -174 129 60 16 16 16 15 13 10 3 South east 41 98 121 i23 98 60 25 16 16 15 13 10 3 South 3 10 13 15 23 31 31 31 23 16 ` 13 10 `3 South west 3 10 13 15 16 16 25 60 98 123 121 98 41 West 3 10 13 15 16 16 16 60 129 174 193 173 - 84 North west Hori zontal 3 20 10 90 13 155 . 15 230 . 16 279 16 312 16 324 28 312 67 - 279 123 230 148 155 145 90 77 20 The values of solar radiation are for a relatively dear,atmosphere. In heavily industrialized and hazy atmosphere it may be necessary to reduce values as much as 10 per cent. '` `` . ^Values are for sea level. Approximate correction for altitude can be made by increasing the values. - 1 per cent per thousand feet of altitude. . - - Values in the tables may be used approximately for times of the year other, than August 1 by choosing 9 taht* for a latitude differing from the geographical latitude by the difference of declination of the sun at Table 5 Solar Radiation Transmitted By Single Unshaded Glass for Variously Oriented Vertical Surfaces and a Horizontal Surface For SO Deg North Latitude on August la- >c Sun Tims. 7 8 9 10 ii 12` 2 3 4^ 5 6 Solar Altitude Solar Radiation Transmitted, Btu per (Hour) (Square Foot) North east East South east - South . South west West North west Hori- \ zontai 9.0 21.5 34.5 47.5 60.0 72.0 78.0 72.0 60 47.5 34.5 21.5 9.0 89 146 142 106 53 20 16 . 16 16 15 14 .11 4 98 T78 .194' 174 129 59 16 . 16 : 16 . 15 14 11 '4 48 107 133 133 112 80 36 1 16 ' 16 15 .14 ' 11 '4 4:n 14 ' 23 .36 45 45 45 `36 23 ; 14 ii 4 4 11 14 - 15 16 16 36 80 112 133 133 107. 48 ' 4 11 -14 i IS ' 16 . 16 .16 ' 59 T29 174 .194 178 98 .4 u 14 15 16 . 16 16 20 53 106 142' 146 89 25 95 152 227 ... 277. . 307 :. 318 307 ' 277 227 ` , 152 ` 95 25 The values of solar radiation are for a relatively clear atmosphere. In heavily industrialized and hazy atmosphere it may be necessary to reduce values as much as 10 per cent. - . -<>Values a" for. sea level. Approzimatecdrrection for altitude can be made by increasing the values 1 per cent per thousand feet of altitude. ..` '" '' ' Values in the tables may be used approximately for.times of the year-other than'Augustl.by choosing a table for a latitude differing from the geographical latitude by the difference of declination of the sirn at the desired date and at August 1 (17.5 deg). 1 284 CHAPTER 15 1946 Guide Table 6. Solar Radiation Transmitted By Single Unshaded Glass for Variously Oriented Vertical Surfaces and a Horizontal Surface , For 35 Deg North Latitude on August . Sun Time Solar Altitude Solas Radiation Transmitted, Btu per (Hour) (Square Foot) North east East South east South South west West : North ' west Hori' zontai 6 A.M. 7 8 9 10 11 12 1 P.M. 2* 3 4, 5 6 10.0 98 . 109 22.5 .143 179 34.5 133 194 46.5 93 173 58.5 41 128 68.5 16 . 59 73.0 . 16 16 68.5 16 16 58.5 16 16 46.5 . 15 15 34.5 14 14 22.5 11- u 10.0 4 . 4 54 110 140 144 .131 94 45 45 16 15 : 14 . 11 4 4 11 . 39 . 31 50 62 68 62 . 50 31 39 . 11 4 4 11 . 14 . 15 16 .45 45 . 94. 131 144 140 .110 ' 54 . 4 11 14 15 16 16 16 59 .128 : 173 194 179 . 109 4 31 : . u - 100. 14 167 15 225. 16 270 16 299 16 309 ' 16 : 299 41 270 93 225 . 133 167 143 . 100., 98 31 . `The.vaJira of solar radiation are for a relatively dear atmosphere. In heavily industrialized and hazy atmosphere it may be necessary to reduce values as much as 10 per cent. ` - ` ^Values are for sea level. Approximate correction for altitude can be made by increasing the values 1 per cent per thousand feet of altitude. . ` ' . /Values in the tables may be used approximately for times of the year other than August 1 by choosing * **?"JO* a latitude differing from the geographical latitude by the difference of declination of the sun at the desired date and at August 1 (17.5 deg). ' Table 7. Solar Radiation Transmitted By Single Unshaded Glass for - Variously Oriented Vertical Surfaces and a Horizontal Surface . For 40 Deg North Latitude on August 1a. b, c `f ` Sun Time Solar Altitude Solar Radiation Transmitted, Btu per (Hour) (Square Foot) North- east East South east South South west West North ' west .Hori-' zontai 5 A.M. 6 7 8 ; 9 10 11 ' 12 . . 1 P.M. 2. 3 4, 5. 67 . 1.5 11.5 23.0 34.5 45.5 56.0 64.5 68.0 $4.5 56.0 45.5 34.5 23.0 11.5 1.5 18 : 106 141 122 '76 . 30 16 16 16 . 16' 15 . 14 . 11 .5 1 17 6. .1 . 1. .121 62 . 5 5 .181 118 11 11 194 147 19' . 14 170. 156 42 ' 15 125 144 66 : 16 53' . 110 87 25 16 .. 59 "94 '59 - 16 . .25 ' , 87 110 16 16 66 144 15 .15 ' ' 42 .156 14 14 18 147 . 11 ' . 11 11 118 . 5 - 5 . ' 5 . 62 1 1 16 :i : . r .5 5 11 n 14 . 14 15 : 15 .16 : 16 .16 , 16 16 . 16 53 16 125 30 170 76 193 122 181 141 121 106 17 18 7 38 `, 102 ' 167 220 262 290 . 298 290 - 262 . 220 167 102 38 7 *Tbe values of solar radiation are for a relatively dear atmosphere, atmosphere it may be necessary to reduce values as much as 10 per cent. In heavily industrialized and hazy bvalues are for sea level. . Approximate correction' illLILUUC \ 1 per cent per thousand feet of altitude. * tables may be used approximately for .times of the year other than August 1 by choosing aat the desired date.and^lfaf5t rAlnuggufrsotn1? (17.5gedoeggr)a. phical latitude by .the diffe,rence of declination of the sun. Cooling' Load 285 Table 8. Solar RadiationJtiUNSJ0TtED,,BY.-$iNC^E Unshaded Glass, for Variously Oriented Vertical Surfaces and a Horizontal Surface , For 45 Deg North Latitude on, August b*c Sun Time Solar Altitude Solar Radiation Transmitted, Btu per (Hour) (Square Foot) ` North east .East' South east ` South South west : West . North Horiwest ' zontai 2.0 23 23 17 i i 1 i n 6 12.5 111 129 68 6 6 6 6 ' 44 7 ' 23.0 135 182 144 11 11 11 11 103 ' g 33:5 115 190 151 24 14 14 14 163 Q 44.0 63 . 168 163 55 15 15 15 .214 10 53.0 24 123 154 88 16 16 16 251 11 60.0 16 56 127 113 30 16 16 277 12 63.0 16 16 76 , 119 76 16 16 285 60.0 16 16 .30 . 113 . 127 56 16 . 277 2 3 53.0 44.0 16 16' 16 88 154 123 24 251 15 15 15 55 163 168 63 214 4 33.5 14 14 14 24 151 190 115 163 5 23.0 11 , 11 11 . 11 . 144 : 182 . 135 103 6 12.5 ,. 6 6.6 6 68 129 111 44 7. 2.0 1' 1 1 1` 17 23 23 11 The values of solar radiation are for a relatively dear atmosphere. In heavily industrialized and hazy atmosphere it may be necessary to reduce values as much as. 10 per cent. ^Values are for sea level. Approximate correction for altitude cain be made by increasing the values 1 per cent per thousand feet of altitude. . ` . . .. ' , Values in the tables may be used approximately.for times of the year other than August I by choosing a table for a latitude differing from the geographical latitude by the difference of declination of the sun at the desired date and at August 1 (17."5 deg). \ . .> 7 . Table 9. Solar Radiation.Transmitted By Single Unshaded Glass for Variously Oriented Vertical Surfaces and a Horizontal Surface . . . For 50 Deg Norik Latitude on August /a.-b.c. ..... Sun Time Solar Altitude '< Solar Radiation Transmitted, Btu per (Hour) (Square, Foot) .. North east .East South east South South west West North west . Horizontai ' 5 A.M. 67 8 9 10 11 12 1 P.M. 2' 3 4 5 6 7 4:5 13.5 23.5 33.0 42.0 50.0 56.0 58 56 50 ... 42 33 23.5 13.5 4.5 ' 48 ^ ' 48 ' 119 139 ' 131 183 . 105 190 52 168 19 125 16 58 16 16 16 16 16 ; 16 14 14 13 13 11 11 '6 6 2 2 is: ' " 2 78 6 127 . . 11 161 '32 173 .71 166 ` 109 144 136! 92 140 41 136 16 109 14 71 13 32 11 11 66 2 '2 2 6 11 . 13 14 16 41 92 144' 166173 161 127 78 18 " 2''' 6 ' . 11 13 14 16 16 16 58 : 125 168 190 183 139 48' 2 6 11 13 -14. 16 16 ' 16 16 19 52 105 131 119 48 .8 49 ' 104 159 204 240 261 - 269 261 240 204 159 104 49 8- The values of solar radiation are for a relatively clear atmosphere. In heavily industrialized and hazy atmosphere it may be necessary to reduce values as much a? 10 percent. , *>Values are for sea level. Approximate correction for altitude can be made by increasing the values 1 per cent per thousand feet of altitude. ' Values in the tables may be used approximately for times of the year other than August ! by choosing a table for a latitude differing from the geographical latitude by the difference of declination of the sun at the desired date and at August 1 (17.5 deg). ' ' 286 CHAPTER 15 1946:- Guide. Table 10.. Solar Radiation Transmitted Through Shaded Windows Type of Shading Canvas awning._,,.;________________________________________ Inside Venetian blind, slats at 45 deg! fully cover ing window............................ .......................................... Inside roller shade, half drawn.............................. ....... Outside Venetian blind, slats at 45 deg, extended as an awning without sides to cover approximately % of window.... ............................................................... Inside roller-shade, fully drawn. .Inside roller shade, half drawn..!.................................. ____ Outside Venetian blind, slats at 45 deg, fully covering window. -- --:-- Finish Dark Aluminum Dark Light . Aluminum Buff Aluminum Portion of That Transmitted By Unshaded Window . 0.25-0.35 0:65-0.80 0.90-0.95 0.35-0.50 Approx. 0.45 Approx. 0.70 Approx. 0.60 , in Tables 4 to 9 were prepared from solar radiation transmission data developed by the A.S.H.ViE- Research Laboratory 6 and direct-radiation- intensity values of Moon7. Included in these values are also an allowance for sky radiation and a reduction factor to take account of the radiation which is prevented from entering the room due to the glass; The notes accompanying the table give suggested factors of(modification due to haze, elevation, time of year, etc. Table 10.gives the portion of.the solar radiation transmitted .to a room by ah unshaded window for different , indoor and outdoor shading-fixtures according to tests8 at the A;S.H.V:E. Research Laboratory. 11 is obvious that there are a numberof factors which influence the magnitude of the values, including color, fit, elevation and angle of the sun to the wall and so forth. These Values-, therefore, can be considered approximate only, and will have to be used with considerable judgment. .' Table 11 gives factors by which the' solar.radiation: through unshaded - glass should be multiplied to take into account the effect'of difference from the- usual transmissivity of glass (1 minus absorptivity minus reflectivity) for perpendicularly incident radiation. These tables are for use primarily with heat absorbent glass.- The values given- are only approximate, being based upon radiation perpendicular to the glass; and arefor use with single glass only. 7 . -- -: .. . 5 The total heat transmission through sunlit windows may be expressed ` by the equation: . . . : ------ .. where - . i/g = Aslfl + i/go - 6)1 ; . . . < .. Hs = heat, transmitted through a window, Btu per hour. A g = net area of glass, square feet.,; . ' . (2) Table 11. Multiplying Factors for Glasses. Having Various Total. Energy Transmissivities : . Transmissivity _ ' . . .- - , .' 0.900 . 0.875 0.800 ' 0.700.......... .. ' 0.600 0.500 ;' 0.400'..................................... .... _ f . '/ . 0.300 0.200 .. . -V ..... 7;- Factor . 1.02 1.00 0.93 s' 0.85 0.76, . '" - ' \ . 0.68 '-.................. - . ' . .0.60 ; - " . - . '. 0.52 : 0.45 v .. v- -; , Cnnline Load 287 . j = factor (from Table, .10)" for adjustment of. radiation transmitted through bare windows due to shading or heat absorbent glass (bare window = 1.0). " I = solar heat gain to room through bare glass, Btu per (hour) (square foot) - . (Tables 5-9). . Ug -- coefficient of transmission of glass, Btu per (hour) (square foot) (Fahrenheit degree). . ' to = outside temperature, Fahrenheit degrees. ti = inside temperature, Fahrenheit degrees. The maximum solar intensity on any surface is of limited duration as shown in Fig. 1. In the case of windows the total energy impinging on the glass before and after the time of maximum intensity is further reduced Table 12. Heat Gain Through Glass Blocks3 SoI-ak Radiation -Heat Gain (Direct plus Sky) Btu per (Sq Ft) (Hour) Sms East West ' N. Latitude Degrees 40 - 40 - 30 SoulfH 35 . 40 Total Heat GainB (Solar Radiation \ plus Normal Transmission) . Btu per (Sq Ft) (Hour) Easto West South ` 45 40 40 30 35 ! 40 45 Sun Outside Time TempF 7:00 74 65.0 8:00 76 63.0- 0.0 9:00 79 40.0 5.0 10:00 83 24.0 . 6.0 11:00 121:O000 87 15.5 90 10.0 93 - 7.0 7.0 10.0 15.5 2:00 300 4:00 94 95 95 6.0 24.0 5.0 40.0 4.5 65.0 5:00 000 700 93 : 91 89 4.0 63.0 2.5 23.5 .1.5 0.0 1.0 3.0 5.5 8.5 12.0 14.0 12.0 8.5 5.5 3.0 1.0 0.0 2J8 4.4 7.1 11.3. 3.0 6.5 10.2 14.7 5.0 11.0 13.4 17.1 15.2 18.7 17.4 . 21.0 15J2 18.7 21.8 24.8 21^ 11.3 14.7 7.1. 10.2 4.4 6.5 17.1 13.4 n.o 2.8 3.0 5.0 0.7 0.7 ' 3.0 0.0 0.7 61.0 77.5 73.5 57.5 5.0 . 6.5 45.0' ' 7.5 36.5 10.5 30.0 22.0 24.0 19.5 15.5 35.6 55.0 77.0 12.5 10.5 8.0 85.5 55.0 18.5 -4.5 0.0 5.0 11.0 -2.0 2.0 7.0 15.0 16.5 21.5 25.0 22.0 28.0 31.8 26.0 24.0 20:0 32.0 29-S 25.5 15.0- 20'b 9.5 13.5 3.5 7.0 -0.5 4.0 10.0 18.0 25.5 33.8 38.5 39.0 36.5 31.5 25.2 18.0 11.0 1.0 5.0 12.0 20.8 32.0 40^ 46.0 47.0 45.0 40.5 33.5 25.5 18.0 For August 1. . blnaide temperature, 78 F, .. -- ' cFor east and west walls these values can be applied to all latitudes between 30 and 45 deg N without excessive errors. - - ,. ; .' . ... by increased shading of the glass from the frame, or wall. Another point which should be noted is that the maximum solar radiation load on the east wall occurs early in the mbrning when the outside temperature is low. Tests9 have shown that where sunlight from bare windows impinges upon floors and walls of high heat capacity, the effect of the radiation is not immediately felt in the room. On the other hand,- where shades or blinds are used, the heat may go directly into the air or it may rise to . the top of the.room and not be immediately, reflected in the room load. For these reasons it is customary, to assume a load somewhat below the maximum value; the amount of this reduction being largely a matter of. individual judgment depending upon,the particular problem in hand, but possibly being of the order of 10 to 20 per cent reduction from the maxi mum. .. . The direct solar and' scattered sky radiation penetration through glass block panels is given in Table 12 for various times'of the day for south,east and west exposures for different latitudes on August 1. This table CHAPTER 15 - 1946 Guide also gives the total heat gain intb an air conditioned space when 78 F is maintained indoors, resulting from the effect of both radiation and air to air transmission. These values result from A.S.H.V.E. Laboratory data 1 and apply for expected design radiation intensity, and for a design day having a maximum temperature of 95 F. The resulting heat gains are averages for four typical glass block designs, two having smooth exterior faces, and the other two having exterior ribbed faces. Heat Emission of Occupants The heat and moisture given off by human beings under, different states of activity are shown in various tables and figures of Chapter 12 which covers the physical and physiological principles of air conditioning. It will be observed, from these data that the rate of sensible and latent heat emission by human beings varies greatly depending upon state of activity. In many applications this component becomes- a large per.- centage'of total load. Metabolic rates are markedly variable for some extreme environmental conditions and this is another important factor which must be considered in cooling load computations.. Consideration should be given to the typical age and sex of the occupants (whether men, women, or children) and the duration of-the occupancy (since for short occupancy applications the extra heat and moisture -brought in by people may be an important factor in the toad). : Heat Introduced by Outside Air Heat and, moisture are added by the outside air introduced for venti lation purposes and also by infiltration air entering the building through cracks, openings, and doors. ' . The volume of air entering due to infiltration may be estimated from data given in Chapters 8 and 14. Information on the amount of outride air required for ventilation 'will be found in Chapter 12. In general, ventilation air is supplied on a per person basis at a rate between 5 and 30 cfm per person (10 to 20 cfm being normal good practice), its specific . amount depending upon the amount of contamination by smoke, food- odors, etc. .. > As outside air is introduced through the air conditioning apparatus it tends to decrease infiltration by building up the pressure within the building. Usually, however, some infiltration still occurs unless the amount of outside air is very large. .- For instance, it is necessary to supply between 2,000 and 3,000 cfm of outside air through the apparatus to prevent infiltration through a single swinging door.. As no demonstrated factors are generally available for the effect (on infiltration) of outside air introduced through the apparatus, it is necessary to use judgment in assigning an effect. . .. ' ... In .determining the amount of outside air which must be drawn through the apparatus the amount of air needed for ventilation is established and ' it is normally possible to subtract from this the assumed amount of infiltration: The division between the ventilation provided by infiltration and by outside air is important to the designer, since the infiltration adds directly to the room sensible and moisture toads, whereas the outside air brought through the apparatus affects only the refrigeration load and the dehumidifier performance (except where shallow coils are used,, in which case a portion of the outside air ineffectively "by-passed" through the coil): ' . Cnolintt Load_ Table 13.. Heat Gain from.Various Sources3 289 ------------------------------- Source ' ' Per Cent Name-' PLATE Rating Percentage or Btu per Hour - Sensible [ Latent Total Electrically Heated Equipment Electric Oven-Bating- . BBaker''s Ouvveenn.---------------------------- -- . Coffee Urn--per Gallon Capacity-- . Glass Coffee Maker--per Section-- . Warming Receptacle.......... ............. . . Plate Warmer----------- --.... .............. . Hot Plates--------------------------- --. . Steam Table--Water Bath Type-- . Frying Griddles.--------------------------- Fry Kettle--- ------------------ -__--... . Waffle Baker Toaster--'Intermittent or Timed Control.. 4.! Toaster--Continnuoouuss...' ...... 5. Hair Dryer in Beauty Parlor--600 w- 70 20 30 50 80100 75 70 40.. 60 : 50 100 80% 80% 1025 181 100% 65% 90% "75% ' 90% 881 2050 2050 20% 20% 1025 2ol ' 0% 100% 100% 2050 100% 100% 100% ____ 35% 10% . 100% 100% "25% - 10% 10% 10% ____ -- 100%. ' 100% 100% 100% 2050 2050 Gas Burning Equipmentb n vent connection . gravity vent connection 18. Open Top Burner per Hole -- - no vent connection gravity vent connection 20. Coffee Urn--Large 18 in. Diam.- 21. Coffee uro-omau ---------...... to. rijriusv __no vent connection gravity vent connection no vent connection gravity vent connection vent connection _____ gravity vent connection ;........ no vent connection gravity vent connection 70 72% ' . 35... 50 100 . 45% ' 55% : .55% 70 , 50% 50% 5000 5000 - ' 3000 V 500 3000 . 500 60- . 90% 10% 100% 60 . 55% 45% 42 50% 50% 75 . : 81% 52 . W7o 181 j?' 49 72% 80% 2500 28% 20% 2500 2250 250 _.. - . 2250 _ 180 250 20 . Steam Healed Equipment? 31. Steam Heated Surface Not Polished--per Square Foot of. ` Surface__ '___--,.... ......................... ...................................... 32. Steam Heated Surface Polished--per Square Foot of Surface . -- 33. Insulated Surface--per Square Foot.__________________ 34. Bare Pipea.Not Polished--per Square Foot of Surface-- 35. Bare Pipes. Polished--per Square Foot of Surface______ 36. Insulated Pipes--per Square Foot,,,,___________ 37. Coffee Urn--Large. 18 in. Diam.--Single Dnim_ .A 38. Coffee Urn--Small. 12 In. Diam.--Single Drum39. Egg Boiler--per Egg Compartment____________ 40. Steam Table--per Square Foot of Top Surface- '_ 330 : 130 80 400 . 220 110 2000 1200 2500 ' 300 ' 0 .0 0 0 0 o 2000 1200 2500 800 '330 130 80' 400 220 110 4000 2400 5000 1100 .. Miscellaneous . 42! Heat Liberated from Hot Water used direct and on towels per hour--Barber Shops__ ---------------------- --:--;------------- - 30 ` 100 30 200 60' 300 *Heat gain from electric or gas residential ranges or cooking stoves.depends on size of the family,'socio economic status of the individual, time of day for principal meal, and whether the equipment is manually or automatically controlled. Total heat gain will probably not exceed'40 per cent name-plate rating. Per cent sensible and latent heat will depend upon use of equipment; dry beat; baking or boiling. bName-plate ratings of gas burning equipment'can' be obtained from a' Directory of Approved Gas Appliances and.listed Accessories, obtainable from American CosAssociation. \ '. `; Steam Requirements of Process Equipment, Report oi the CommerdalRelations Committee, National District-Heating Association (Heating, Piping'and Air-Conditioning, November, 1942,-p. 675). : ` : 290 CHAPTER 15 1946 Guide The total heat gain resulting from outside air introduced may be. deter mined by Equation 3: . where H lk ~ . . <3) H -- heat to be removed from outside air entering the building above inside con ditions, Btu per hour. Q = volume of outside air entering building, cubic feet per hour. v = cubic feet of outside air per pound of dry air. . . .ho = enthalpy of outside air, Btu per pound of dry air. ' hi = enthalpy of inside air, Btu per pound of dry air: '. . "' . ' The moisture gain resulting from outside air and infiltration may .be determined, by Equation 4: Qw = ~,{Wo - Wi) (4) where =. ' Qw = weight of water to be removed from outside air ..above inside conditions, pounds per hour. ' , Wo = humidity ratio of outside air, pounds water per pound dry air. Wi -- humidity ratio of inside air, pounds water per pound dry air. . . Heat Emission of Appliances .. Heat generating appliances which give off either sensible heat or both sensible and latent heat in an air conditioned enclosure may be divided into three general, classes of equipment or devices: (1) electrical ap pliances, (2) gas appliances, and (3). steam heating appliances. . In the first group may be found such devices as lights10, fans, motors, toasters, waffle irons, etc. -The heat load caused by such devices may normally be obtained by multiplying the nameplate rating in watts by an appropriate load factor and'by 3.4 (Btu per watt hour). In some cases it may also be possible to remove some of the heat.of such appliances as lights and motors with exhaust air without involving it in the room load. . Electric motors aire usually rated in'units of horsepower output. ,To determine' the conesponding- input, which is the rate' at which heat is added to the conditioned space by full-load, operation of such motors, some idea of motor efficiency is necessary. The aggregate input in horse power should then be multiplied by 2546 (Btu per horsepower hour)! .' ' Motor efficiencies can be assumed about as follows: Motor efficiencies vary from 50 to 60 per cent a.t the hp level to 80 per cent at 1 hp and ' 88 per cent at 10 hp and above. Where the motor is outside of the conditioned space the heat equivalent of'the motor output only is used, but where the motor is inside of the. space the heat equivalent of the output divided by the efficiency is used. "" In the second group belong such appliances as coffee urns, gas ranges, steam tables;'broilers, .hot plates, etc. For heat generating capacities of such appliance's refer to Table-13, - '. ,' ... : ? Judgment must be used. in. the application of data given in. Table 13. Consideration-must be'given to-the. heat> contributed by appliances ..which are in use at the time.pf . peak load. The quantity of heat will. :Cooling Load 291 depend upon whether products of combustion are.vented to a flue, whether . they escape into the space to be conditioned,-or. whether appliances are' hooded allowing part of the heat to escape through a stack. There me no generally accepted data available on the effects of venting and shield ing heating appliances but it, is believed that,, when they, are properly hooded with a positive fan exhaust system, through the hood, 50 per' cent of the heat will be carried away and 50 per cent dissipated in the space to be conditioned. The same effectiveness of the hood should be figured for both latent and sensible heat. : . ' . Table 14. -Permeability of Various Materials to Water Vapor ' Material . Permeability ' . Grains per (So Ft) (Hr) (Inch He) . Group 1 . 14.7 2.9 49.1 4.9 3.4 12.5 11 Group 2* 0.08 to 0.13 0.13 to 0.17 1.37 to 2.58 11.00 3.68 to 3,84. 1.15 19.73 to 20.57/ 2.67 to 2.74 25.68 to 34.27 3.03 to 4.36 ' 6.19 29.07. , Calculating Vapor and Heat Transfer Through-Walls,-by. L.lG.MiUer,'{Healing and Ventilating 35, No. 11,'56 November, 1938). ' .- . bHow to Overcome!Condensation in Building Walls and Attics, by, L..V. Teesdale (Beating and Venti lating, Vol. 36. No. 4,'April. 1939). ' . .. ' eLight weight slaters felt used to keep rain from drifting through. Not used as a vapor barrier. Moisture Through Walls . ' - . In some applications walls of the conditioned space may- be in contact with other spaces which have in .them a, higher water vapor pressure.than that in the conditioned space. It is known that water, vapor will flow' through the building materials in proportion`to. the'vapor pressure dif- ference on the two sides of the materia).,,.'The, total.amount of water . vapor transmitted is dependent on the permeability which isJ usually expressed in grains of moisture per (square foot) (hour) (inch of-mercury vapor pressure difference). The values,for permeability in Table 14 are quoted from a publication :6i Hie Natumal'-Bureau of: Standards11. The water vapor entering the .conditioned space must be added.to the latent cooling load. ' ' . Vapor barriers, to be effective in reducing entrance of moisture,'must seal completely the walls, ceilings, and floors .that are exposed to space 292 CHAPTER IS 1946^ Guide having excessive vapor pressure arid all doors >must have gaskets applied to them to make the barrier, effective; ; . ILLUSTRATION From the foregoing discussion it is .obvious that the determination of the maximum cooling load is rather complicated by reason of the variable nature of contributing load components.. An illustrative example will explain the method presented in the foregoing text. . Example 1. Determine cooling load requirements for a clothing store illustrated in Fig. 9 and located in Pittsburgh, Pa.; Latitude 40 deg. This is a one-story building located on a corner and it faces south and west. Assume building on east and north sides^conditioned. - . . . ^ ........... . Wall construction, 8 in. concrete block, 4 in. brick veneer,' plaster on walls, V = 0.33 (Table 8, Chapter 6, No. 93 B). , Roof construction, 2 in.- concrete, \4 in. insulating-board, metal lath-and plaster ceiling, U = 0.26 (Table 15, .Chapter 6, No. 14 B). . ' - .. ' Floor, maple flooring on yellow pine, no ceiling below, U = 0.34 (Table 11, Chapter 6, No. l'-N). . , ` .. ^` ` Partition, wood lath and plaster on both sides of studding, U = 0.34 (Table 9. Chapter 6, No. 3 B). . - x ; .. . . . Windows, provided with awnings., ... .. . ' Front doors, 2 ft 6 in. x 7 ft (glass paneled). * : -. Side door, 3 ft x 7 ft (glass paneled), U ,= 1.13-(Table 18 A* Chapter 6). Occupancy, 10 clerks, 40 patrons. ' ;_ - ' ' Lights, 4200 w. ' . ' f . - . -. * ' : -. . - Outside design conditions, dry-bulb 95 jpi.wet-bulb 75 F.. . Inside des^h conditionsj dry-biilb 80 F; wet-bulb 67 F: ` ' ' - Basement temperature, 85 F. ... t .. .4, : .. . . , Store room temperature; 88'F. ':)l r: ^ v. .... -Cooling'Load ______________________ . <. ;__j:________________________________________________ .^ Solution. It is obvious from the shape and exposure of this store and the large glass area on the west side that the maximum cooling load will1 occur during the afternoon when the sun is shining on the west wall. -From-Fig. 1, the peak load may be expected at 4:00 p.m. The combined normal transmission and solar radiation transmission through the roof at 4:00 p.m. is obtained from Fig. 2. While none of the roofs in Fig. 2 is exactly like this one, roof 4 is similar. A heat flow of 8)4 Btu per (square foot) (hour) was assumed, 20 per cent more than for roof 4. The combined normal transmission and solar radiation transmission through the south and west walls at 4:00 p.m. is obtained from curves in Figs. 7 and 8. Note that the curve values for combined wall transmission have been increased by a judgment factor of 20 per cent. Also, that the values are still only about half what would be obtained due to normal transmission taking the instantaneous tem perature difference. ' The normal heat transmission through the south and west glass, floor and partition is determined by application of Equation !. The solar radiation effect passing through bare south and west glass is determined from Table 7 as being 18 and 193 Btu per (square foot) (hour) respectively. This is multiplied by'a haze factor of 0.9 (10 per cent reduc tion) and by a factor of 0.25 to take account of the awning (Table 10). It will be seen that the sun effect on the south glass might well have been neglected. To determine the load imposed by occupants, it will be found from Chapter 12 that the average person standing at rest will dissipate 431 Btu per hour, and that the moisture dissipated is 0.198 lb per hour. .. . The amount of infiltration through a swinging door is determined from Table 3, Chapter 8 as being 3)4 cfm per person for 40 patrons or 140 cfni total. Since the windows are sealed it can be assumed that this is the- only infiltration which will occur. The infiltration affects both the sensible and latent load of the room and, therefore, must be' considered separately from the outside air passed through the apparatus for ventilation purposes which affects the room conditions little or none. (See Chapter 7 and 43 for treatment of "by-passed" outside air as a part of the room load.) The ventilation requirements as given in Table 1, Chapter 12 would indicate the need of about 9 cfm per person based on a volume of the store of 21,600 cu ft and 50 persons making a total volume of' 450 cu ft. ..However, the ventilation requirements in the summer are somewhat greater than those in the winter and, therefore; 10 cfm per person or 500 cfm total will be chosen. From this should be subtracted the estimated infiltration of 140 cfm, making a net amount of outside air to be drawn through the apparatus of 360 cfm. .. The total heat addition due. to the infiltration and outside air is determined from Equation 3, and the moisture addition is determined from Equation 4. '' .' The room tptal load is then made up of normal transmission,.combined normal.and sun radiation transmission, solar radiation through glass, heat from occupants, total heat addition due to infiltrations, and heat from lights. ' It is necessary to determine only the amount of water condensed from the air (not the latent heat). In considering the room load this consists of the water evaporated from the people plus the excess water in the infiltration air. - . . .. The excess heat and moisture load due to the outside air tends to raise the return air temperature and moisture content, but if the dehdmidifier is 100 per cent effective and fully saturates the leaving air, the outside air load has no direct effect upon the.room. It, therefore, should be determined separately and added only in connection with the determination of the refrigeration requirements. . . Normal Transmission: Surface S Glass...... W Glass........ Floor.__......... N Partition.. Dimensions 2 (2 ft 6 in. x 7 ft)+ 2 (10 ft x . 6 ft) 3 (14 ft x 6 ft) + (8 ft x 6 ft) + (3 ft x 7 ft) 26 ft x 54 ft 30 ft x 12 ft Area Sq Ft u- 155- 1.13 .321 1.13. 1404 0.34 .360 0.34 Temp Diff FDeg 15 . 15' 5. ' 8 ' Btu per Hour 2,627 5,445 2,387 979 . Total_______ " 11,438 '!  ! / 294 CHAPTER 15 1946 Guide Combined Normal and Solar Radiation Transmission: Surface S Wall........... W Wall Roof....... ....... Total: ..... Dimensions (30 ft x 12 ft) - 155 (60 ft x 12 ft) - 321 60 ft x 30 ft Area Sq Ft 205.. 399 1800 Btu per (Hour) (Sq Ft) 2 x 1.2 2 x 1.2 m Btu per Hour . 490 960 15,300 16,750 Solar Radiation Through Glass: South Hs = 155 ,X (18 X 0.9) X 0.25 = 625 ` . . ' West Hz = 321 X (193 X 0.9) X 0.25 = 13,930 .t"iuat,on 2) Occupants: 50 X 431 = 21,550 Btu per hour. 50 X 0.198 = 9.90 lb water evaporated per hour. Infiltration and Outside Air: * H= (ho -- Ap (Equation 3) _ _ . .. ` . v = 13.33 cu ft per pound dry air (infiltration, and outside air required for ventir ' * lation may be considered in terms of Standard. Air). . . . `" .. H = per cent saturation at 95 F dry-bulb and 75F wet-bulb * 38.4 per cent (by . calculation, Chapter 3). : ho = hi + yhas (Equation 5, Chapter 3). .. h* '= specific enthalpy of dry air at .95 F = 22.827 Btu per pound (Table 1, Chapter 3). . . ;haa =. difference between enthalpy of saturated mixture and specific, enthalpy.of dry air at'95 F = 40.49 Btu per. pound .(Table 1, Chapter 3).. ' . ho -- 22.80 -f (0.384 X 40.49) = 38.26 Btu per pound dry air. . * . : . (i at 80 Fdry-bulb and 67 F wet-bulb -- 50.2 per cent (by calculation, Chapter 3). hi = ha + tAas = 19.221 + (0.502:X 2447) = 31.50 Btu per pound dry.air (Table . 1, Chapter 3). - . ' . . > * . . .. 14A v fin ' ,* . H (infiltration) =--13 33--(38.26 -- 31.50) = 4,270'Btu per hour.' ; : B (outside) = (^17^>)6 (38.26 - 31.50) = 10,950 Btu per hour. Wo =.humidity ratio of outside air at 95 F dry-bulb and 75 F wet-bulb = 0.384 X . . 0.03673 = 0.01410 lb water per pound dry air. (Equation 3, Chapter 3.) Wi = humidity ratio of inside air at 80 F dry-bulb and 67 F wet-bulbi = 0.502 X. - 0.02233 = 0.01121 lb water per pound dry air. (Equation 3, Chapter 3.) ' Weight of water.to be removed from infiltration air = ~(W0 -- Wi) (Equation.4) v; (0.01410 - 0.01121) - .1.82 lb per hour/ .. ,\ Lights:! 14200 X 3.413 = 14,335 Btu per hour. Cnoling -Load 29S, Summary: * ` Components of Load* .... ' Combined Normal and Solar Radiation Transmission...:.----------------- Liehts plus Heat Equivalent of that Proportion of the Power Load Used in Air Conditioning System Which Adds Heat to the Air.... Total Room Load (Sensible and Latent Heat Gain)------------:.............. Btu per Hour . 11,438 16,750 - 14,555 21,550 4,270 -' 14,335 82,898 10,950 . 93,848 Determination of Apparatus Dew-Point: . First, determine the water added as a part of the room load as follows: Occupants.__1.......-..9.9 lb water per hour Infiltration............... 1.82 lb water per hour . . 11.72 lb water per hour . . > The condition line for this application may be determined' from Equation 11 in' Chapter 3 by taking the ratio of room total load to pounds water per hour released in the room = 82,898 -s- 11.72 .= 7075 Btu per pound of water. In this case, it crosses the saturation curve at.a temperature for which the enthalpy kg and the humidity ratio. Ws satisfy the equation, **- 31.50 - hs = 7075 0.01121 - WB The required apparatus dew-point may be determined graphically from the Mollier, chart or by cut and try from Table 1, Chapter 3, as 57.9 F. , Air Quantity and Refrigeration Load: Assuming 100 per cent saturation efficiency for the air conditioning apparatus, the air will leave the dehumidifier saturated. The thermodynamic properties involved in cal culating the air quantity are: .. - Inside Air After Cooling . ' t 80.0 57.9 k 31.50 ' 25.06 W 0.01121 (0.01030 Vapor -f 0.00091 Liquid) The cooling effect is 31.50 - 25.06 = 6.372 Btu per pound dry air. The total outside and recirculated dry air through the air conditioning apparatus is: .. . - 6.44 X 60 = 2860 cfm (Standard Air) The refrigeration may be assumed equal to the grand total load; that is. 93,848 12,000 7.82 tons REFERENCES 1 ' . ` -! . A.S.H.V.E. Research Report No. 1147--Heat Gain Through Glass Blocks by Solar Radiation and ' Transmittance, by F. C. Houghten, David Shore, H. T. Olson and Bait Guast (A.S.H.V.E. Transactions, Vol. 46. 1940. p. 83). - . . v. l~A,S.H,V.E. Research Report No. 923--Heat Transmission as Influenced by Heat Capacity and, Solar Radiation, by F. C. Houghten, J. L. Blackshaw, E. M. Pugh and Paul McDermott (A.S.H.V.E.. Transactions. Vol. 38, 1932, p. 231). Effect of Heat Storage and Variation in Outdoor Temperature.and Solar Intensity on Heat Transfer Through Walls, by J. S. Alford, J. E. Ryan and F. O. Urban (A.S.H.V.E. Transactions, VoL 45, 1939. p. 369).' Periodic Heat Flow in Building Walls Determined by Electrical Analogy Method, by Victor Paschkis (A.S.H.V.E. Transactions, VoL 48, 1942, p. 75). 'Summer Comfort Factors as Influenced by the Thermal Properties of Building Materials, by C. O. Mackey and L. T. Wright, ' Jr. (A.S.H.V.E. Transactions, Vol. 49, 1943, p. 148). . 296 CHAPTER 15 ..J946.Guide ,, * If??i2?lic Heat FIow--Homogeneous Walls or Roofs, by - C. O.. Mackey and L. T. Wright Jr (A.S.H.V.E. Transactions, Vol. 50, 1944, p. 293). , . J 4-A.S.H.V.E. Research Report No, 1157--Summer Cooling Load as Affected by Heat Gain Through Transactions 'V 1 45'Y940 V*'r 23 L*' by F' C' Ho"ght'n' H' T- Olson and Carl Gutberiet (A.S.H.V.E. _ frAS-H-V-E-RESEARCH Report No. 1195--Heat Gain -Through -Walls and Roofs as Affected by Solar Radrarion by F. C. Houghten, E. C. Hach, S. I, Taimuty and Carl Gutberiet (A.S.H.V.E. Transactions, Vol. 48,1942, p. 91). .. - e-The Trannisaon of Solar Radiation Through Flat Glass Under Summer Conditions, by G. V. Fa-jroelec (A.S.H.V.E. Journal Section. Heating, Piping and Air Conditioning, October-November. 1945, p. 562). -. , ' ; - r J.yProPpsedStandardSolar Radiation Curves for Engineering Use. by P. Moon (Journal of the Franklin Institute, November, 1940, Vol. 230, No. 5,;p..583-617). . . .. ,,f. *7a 's-H.V.E Research Report No. 975--Studies of Solar Radiation-Through Bare and Shaded Wrndows, by F. C- Houghten. Carl Gutberiet, and J. L. Blackshaw (A.S.H.V.E. Transactions. Vol. 40. A.S.H.V.E. Research Report No. 1180--Heat Gain Through Western Windows With and Without Shading, by F. C. Houghten. and David Shore (A.S.H.V.E. Transactions, Vol. 47. 1941, p. 251). "A.S;H;V.E. Research Report No. 1002--Cooling Requirements of Single Rooms in a Modern Office Budding, by F. C. Houghten. Carl Gutberiet, and. Albert J. Wahl (A.S.H.V.E. Transactions. Vol. 41, 1985, p. 53). .. . , `Cooler Footcandles for Air Conditioning, by W. G.- Darley (A.S.H.V.E: Transactions, Vol. 46, 1940, p. 367). Lighting and Air Conditioning Design Factors, Report of I.E.S.--A.S.H.V.E. Joint Com mittee on Lighting in Air Conditioning (A.S.H.V.E: Journal Section, Heating, Piping and Air Con- dtitoning, September, 1941, p. 605). Lighting and Air Conditioning, by. Howard M. Sharp (Heating and Venltlattng, November. 1942. p. 35). .. XT V-Moisture Condensation in Building Walls, by Harold W. Woolley {U. S. Department of Commerce, National Bureau of Standards, Building Materials and Structures Report BMS63). CHAPTER T 6 and C^ombuition Combustion Principles, Heat and Flames; Air Required, Excess Air and Secondary Air; Draft Requirements, Classic beation of Coal and Coke, Firing Methods, Classification and Combustion of Oil and Gas; Dustless Treatment of Coal THE data given in the first part of this chapter are of general appli cation to the various fuels used in domestic heating which are coal, coke, oil and gas. The choice of fuel is a question of dependability, cleanliness, fuel availability, economy, operating requirements and control. FUNDAMENTAL PRINCIPLES OF COMBUSTION Combustion may be defined as the chemical combination of a substance with oxygen with a resultant evolution of heat. The rate of combustion depends partly upon the specific rate of reaction of. the combustible substance with oxygen, partly upon the rate at which oxygen is supplied, and upon the temperature obtained due to surrounding conditions. Complete combustion is obtained when all of the combustible elements in the fuel are oxidized with all of the oxygen with which they can combine. All of the oxygen supplied may not be utilized. Perfect combustion is -defined as the result of supplying the required amount of oxygen for combination with all of the combustible elements of the fuel and utilizing all of the oxygen so supplied. The oxygen required for the process of combustion is obtained from air which is a mechanical mixture of oxygen, nitrogen and small amounts of carbon dioxide, water vapor and inert gases. These inert gases are generally included with the nitrogen, and for engineering purposes the values given herewith may be used. .- . Br Volume, Per Cent 20.9 Nitrogen, Nj._.............. .......... ---..... -- ' 79.1 Bt Weight, Pee Cent . 23.15 76.85 The combination of oxygen with the combustible elements and com-, pounds of a fuel is in accordance with fixed laws. In the case of perfect combustion the reactions and resultant combinations are shown in Table 1. The most important condition governing the process of combustion, is temperature. It is necessary to bring a combustible substance to its ignition temperature before it will unite in chemical combination with. oxygen to produce combustion. The ignition temperatures for several of the combustible constituents of fuels are presented in Table 1. ; HEAT OF COMBUSTION As previously stated, the process of combustion results in the evolution of heat. The heat generated by the complete combustion of a unit of fuel is. constant for a given combination of combustible elements and com- . pounds, and is known as the heat of combustion, calorific value, or heating value of the fuel. . 297 .. : and Combustion , . ' > 299 . The heat of combustion of the several fuel elements and compounds in their pure state is given in Table 1: ' The reaction of the carbon in the'fuel with oxygen may result in the' formation of carbon monoxide or carbon dioxide. In burning-to carbon monoxide, the carbon is not completely oxidized and, as shown by the data, the heat produced is considerably less than if it were completely oxidized. This fact is of greatest importance in considering the efficiency , of combustion. , The calorific value of a fuel is determined by direct measurement of the heat evolved during combustion in a calorimeter. Although the ash and moisture content of coal from a given mine or locality may vary widely, the heating value of the coal, on a moisture and ash free basis, remains relatively constant. ' It is therefore possible to approximate the heating value of a shipment of coal as received if its moisture and ash content are determined, and if the heating value of similar coal on a moisture and ash free basis is known. This may be calculated by Equation 1. Heating value, as received = Heating value, moisture and ashfree X [100 -- (Moisture + Ash)] 100 ,,, UJ where, moisture and ash are expressed in per cent. . Typical analyses.of the coals of the United States are given in U. S. Bureau of Mines Bulletin HQ. ' As practically all fuels, including coal, oil,, and gas, contain hydrogen, water vapor is one of the products of combustion. The amount of water vapor produced is proportional to the hydrogen content of the fuel. When the heating value of a fuel is determined in a.calorimeter the water vapor is condensed and the latent heat of vaporization is included in the heating value of the fuel. The heating value so determined is termed the gross or higher heating value and this is what is ordinarily meant when the heating value of a fuel is specified. In burning the fuel,' however, the products of-combustion are not cooled to the dew-point and the higher heating value cannot be. obtained. oValue fro m N ational Bureau o f Standards. FLAME The appearance of the flame or products of combustion may serve as an approximate measure of the temperatures developed in the combustion process. The luminosity of a flame is caused by the heating to incan descence of unconsumed particles of combustible matter in the gases, and the higher the temperature of these particles the whiter the flame. Table 2 gives some approximate flame temperature data. ' Table 2. Approximate Flame Temperature Data Red, visible in Orange-yellow. Appearance of Flame' ' Temperature F Dbg 1000 . 1800 2000 2200 2400 2600 .. 300 CHAPTER 16 1946 Guide . AIR REQUIRED FOR COMBUSTION The weight of air required for the perfect combustion of a pound of fuel may be determined by use of the ultimate analysis of the fuel as applied to Equations 2 to 4. The various elements are expressed in percentages by weight. ' Solid and Liquid Fuels: Pounds air required per pound fuel = 34.56 f- Gaseous Fuels: ,, + (-IH Pounds air required per pound fuel = 2.46 CO + 34.56 Hi + 17.28 CH4 + 13.29 CiHt + 14.81 CtHi + 16.13 CM* + 6.10 HiS - 4.32 O, When the analysis is given on a volumetric basis the equation is ex pressed as follows: Cubic feet air required per cubic foot gas = 2.39 (CO + Hi) 9.56 CH, + 11.98 C,H, + 14.35 C,H, + 16.74 C,H, - 4.78 0, ... w Equations 5 and 6 may be used as approximate methods of determining the theoretical air requirement for any fuel. , Pounds air required per pound fuel -- 0.755 X Seating-value^IBtii Ptr pound) ^ Cubic feet'air required per unit fuel = Per unh) (6) Approximate values for the theoretical air required for different fuels are given in Table 3. . It is customary to make use of the analysis of the products of com bustion to determine the amount of flue gas produced and the actual Table 3. Approximate Theoretical Air Requirements Solid Fuel ' .. Fuel Ou. Commercial Standard No. 1...... ...... ........ Commercial Standard No. 2........................... Commercial Standard No. 3.... ................. Commercial Standard No. 5..... ..................... Commercial Standard No. 6............. ...... * Pounds Am Per Pound Furl ' 9.6 11.2 10.3 6.2 11.2 ' Pounds Am Per Gallon Fuel 102.6 104.5 106.5 112.0 114.2 Natural gan Gassoub Fueu Carbureted water gas .... , Cubic Febt Am P&b Cubic Foot Gab 10.0 ' 4.4 4.4 2.1 - ' 5.2 . Fiiels and Combustion 301 amount of air supplied for combustion. The analysis of flue gases has been well described in various publications of the Bureau of Mines and in the literature and the details of Orsat manipulation need not be considered in this discussion. (See Chapter 11.) The weight of dry flue gas per pound of fuel burned is used in com- bustion loss calculations and may be determined by Equation 7. _ .. ,, _ , , 11 CO, + 8 0, + 7 (CO + Ni) ,, ,, Pounds dry flue gas per pound fuel =---------------3 (CO, + CO) --------- x c (7) Values for CO,, Ot, CO and Nt are percentages by volume from the flue gas analysis and C is the weight of carbon burned per pound of fuel corrected for carbon in the ash. . -o 20 40 60 80 100 I20. MO EXCESS AIR, PER CENT 160 . Fig. 1. Relation Between COi and Excess Air in Gases of Combustion EXCESS AIR Since one measure of the efficiency of combustion is the relation existing between the amount of air theoretically required for perfect combustion and the amount of air actually supplied, a method of determining the latter factor is of value. Equation 8 will give reasonably accurate results, . for most solid and liquid fuels, for determining the amount of air supplied per pound of fuel. Pounds dry air supplied per pound of fuel 3.04 N, (CO, + CO) (8) Values for CO,, CO and N are percentages by volume from the flue gas analysis and C is the weight of carbon burned per pound of fuel corrected for carbon in the ash. ' 302 CHAPTER 16 -19.46 Guide The. difference between the air. actually supplied for combustion and the. theoretical air required is known as excess air. . Per cent excess air Air supplied --.Theoretical air Theoretical air . (9) Since the calculation is usually made from Orsat readings, Equation 10 will be found to be a convenient statement of this relationship. ' 100 ( O, - ^ ) Per cent excess air = --------------- ------------------L---------- - ` ' (10) ' N, X 0.264 - (o, - . In this formula the symbols represent volumetric percentages of the flue gas constituents as determined by analysis. The amount of excess air in its relation to the percentage of CO% is shown by the curves in Fig. 1 for several fuels. These are approximate^ values. It should be noted that in hand-fired furnaces with long periods' Table 4. Representative Maximum COj Value Fuel - No. 6 Fuel OIL ............................. ........................ Theoretical CO* Usually Attained COj . In Practice 21.00 20.20 18.20 15.00 16.50 12.00 11.00 12-14 12-14 13 10 5 13.5 9.7 . . 8.5 : between firings the combustion goes through a cycle in each period and the quantity of excess air present varies. Due to the different carbon-hydrogen ratios of the different fuels the maximum COy attainable varies. Representative values for perfect com bustion of several fuels are given in Table-4. In considering the factor of excess air it should be noted that a deficien cy of air supply will result in combustible products passing to the stack , unbumed. An excess of air.absorbs heat from the products of combustion and results in a greater loss of sensible heat'to the stack. An excess of air is always required, however, to eliminate combustible losses occasioned' by poor mixing of the fuel and air.: It is considered good practice, under usual operating conditions, to supply from 25 to 50 per cent excess air,- dependent upon the fuel utilized. ; ' -. SECONDARY AIR When bituminous coal is hand-fired in a furnace the volatile matter in the fuel distills off leaving coke on the grate. The product of combustion .of the coke is COy and under certain conditions some CO may arise from the bed. The combustion of the volatile matter and the CO may amount to the. liberation of from 40 to 60 per cent of the heat in the fuel in the combustion space over the fuel bed. ... - The air that passes through the fuel bed is called primary air and the - Fuels and' Combustion, ';. 303 air that is admitted over the fuel bed in order to burn the volatile matter and CO is called secondary air. i This process of combustion is illustrated in Fig. 2 *. The free oxygen of the air passes through the grate and the ash above it and burns the carbon in the lower 3 or 4 in. of the fuel bed forming carbon dioxide. This layer noted as the oxidizing zone is indicated' by the symbols COy and Ot. Some.of the.carbon dioxide of. the oxidizing zone is reduced to carbon monoxide in the upper layer of the fuel bed noted as the reducing zone and indicated by the symbols. COy and CO. The gases leaving the- fuel bed are mainly carbon monoxide, carbon dioxide, nitrogen ,and a small amount of free oxygen. Free oxygen is admitted through the firing door in an attempt to burn carbon monoxide and the volatile combustible . distilled from the freshly fired fuel: The division of the total into primary and secondary air necessary to produce the same rate of burning and the same excess air depends on a Fig 2. Combustion of Fuel in a Hand-Fired Furnace number of factors which include size and type of fuel, depth of fuel bed, and size of fire-pot. '~ . Size of the fuel is a very important factor in fixing the quantity of secondary air required for non-caking coals. With caking coals it is not so important bemuse small pieces fuse together and form large lumps. Fortunately a smaller size fuel gives more resistance to air flow through the fuel bed and thus'automatically causes a larger draft above the fuel bed, which draws in more secondary air through the same slot openings, " but, nevertheless, the smallest size of fuel will require the largest second ary air openings. For. certain sizes of fuel no secondary air openings sire ' required, and for large sizes, too much excess air may pass through the fuel bed. It is impossible to establish a single rule for the correct slot opening for all types and sizes of fuels and for all rates of burning. Furthermore,.the effect of slot opening is dependent on whether the ashpit damper is open or closed. Bituminous coals require a large amount of secondary air during the period after firing in order to burn the gases and to reduce the smoke. The smoke produced is a good indicator, and that opening is best which reduces the smoke to a minimum. Too much secondary air will cool the gases below the ignition point, and prove harmful instead.of beneficial. . Secondary' air that-enters the combustion, chamber too far removed from the zone of combustion will also be harmful, for the oxygen in the 304 CHAPTER 16 1946 Guide secondary air will not react with any unburned gases unless the mixture is subjected to high temperatures. ' The air requirements of oil and gas burners are discussed in Chapter 17, Automatic Fuel Burning Equipment. DRAFT REQUIREMENTS The draft required to effect a given rate of burning the fuel is dependent on the following factors: .1. Kind and size of fuel. . 2. Grate area. 3. Thickness of fuel bed. . 4. Type and amount of ash and clinker accumulation. 5. Amount of excess air present in the gases. ' 6. Resistance offered by the boiler passes to the flow of the gases. 7. Accumulation of soot in the passes. , Insufficient draft will necessitate additional manipulation of the fuel bed and more frequent cleanings to keep its resistance down. Insufficient draft also restricts the control that can be accomplished by adjustment of the dampers. / The quantity of excess air present has a marked effect on the draft required to produce a given rate of burning.. If the excess is caused by holes in the fuel bed, or an extremely thin fuel bed, it is often possible to produce a higher rate of burning by increasing the thickness of the bed. The thickness of the fuel bed should not, however, be increased too much because the increased draft resistance will reduce the rate of primary air supply and the rate of burning. For amount of draft required see Chapter 19, Chimneys and Draft Calculations. . DRAFT REGULATION Because of the varying heating load demands present in most instal lations it is necessary to vary the rate of fuel burning. The maintenance. of the proper air supply for the various rates of burning is accomplished by regulation of the drafts. Correct and incorrect methods of draft regulation are shown in Fig. 3. The air enters through the ashpit draft door, firing door and by leaks in the setting, whereas the gases leave only through the uptake. By throttling the gases with the damper in the, Fig. 3. Correct'and Incorrect Methods of Draft Regulation . in a Hand-Fired Furnace .. fuels and Combustion 305 uptake all the air entering by each of the three intakes is reduced in the same proportion. If the ashpit draft door is closed, the air admitted through.the ashpit is reduced, while it is increased through the other two intake openings. Methods of control of draft conditions when burning oil or gas are noted in Chapter 17, Automatic Fuel Burning Equipment. ' CLASSIFICATION OF COALS The complex composition of coal makes it difficult to classify it into clear-cut types. Its chemical composition is some indication but coals having the same chemical analysis may have distinctly different burning characteristics. Users are mainly interested in the available heat per .Table 5. Classification of Coals by Rank* Legend: F.C. = Fixed Carbon. V.M. = Volatile Matter. Btu = British thermal units. II. Bituminous*-- III. Sub-bituminous, IV. Lignitic.,, Gaou? Limits or Fixed Cabbon or Btu Mineral-Matter-Free Basis Requisite Physical Properties . 1. Meta-anthracite-- Dry F.C., 98 per cent or more (Dry V.M., 2 per cent or less) Dry F.C., 92 per cent or more and laaa than 98 per cent (Dry V.M., 8 per Non-agglomerating* centor lessand more than 2 percent) 3. Semi-anthracitc_. Dry F.C., 86 per cent or more and less than 92 per cent (Dry V.M., 14 per centor less and morethan 8 per cent) 1. Low volatile bituminous coal___ Dry F.C., 78 per cent or more and less than 86 per cent (Dry V.M., 22 per . cent or less and more than 14 per cent) 2. Medium volatile bituminous coal Dry F.C., 69 per cent or more and less than 78 per cent (Dry V.M., 31 per cent or less and more than 22 per cent) Either agglomerating* or non-weathering^ 3'. High volatile A bituminous coaL Dry F.C., less than 69 per cent (Dry V.M., more than 31 per cent); and moist4 Btu, 14,000* or more . 4. High volatile B bituminous coaL Moist* Btu, 13,000 or more and less than 14,000* 5. High volatile C bituminous CoaL Moist Btu, 11,000 or more and less than 13,000* l. Sub-bituminous A coal 2. Sub-bituminous B coaL. Moist Btu, 11,000 or more and less than 13,000* Moist Btu, 9500 or more and less than 11,000* Both weathering and non-agglomerating* 3. Sub-bituminous C wwl 1. T.ignit* Moist Btu, 8300 or more and less than 9500* Moist Btu less than 8300 Consolidated Moist Btu less than 8300 Unconsolidated This classification does not include a few coals which have unusual physical and chemical properties and which come within the limits of fixed carbon or Btu of the high-volatile bituminous and sub-bituminous ranks. All of these coals either contain less than 48 per cent dry, mineral-matter-free fixed carbon or have more than 15,500 moist, mineral-matter-free Btu. '> *If agglomerating, classify-in low-volatile group of the bituminous class. '- Moist Btu refers to coal containing its natural bed moisture but not including visible water on the surface of the coaL - *It is recognized that there may be non-caking varieties in each group of the bituminous class. . Coals having 69 per cent or more fixed carbon on the dry. mineral-matter-free basis shall be classified"1 according to fixed carbon, regardless of Btu. ' '' (There are three varieties of .coal in the high-volatile C bituminous coal group, namely. Variety 1, * agglomerating and non-weathering; Variety 2, agglomerating and weathering; Variety 3. non-agglomerating and non-weathering. ` * .. Adapted from AS.T.M. Standards, 1937, Supplement, p. 145. American Society for Testing Materials Philadelphia. .. '. 306 CHAPTER 16 1946 Guide pound of coal, in the handling and storing properties, and in the burning characteristics. A description of the relationship between the qualities of coals and these characteristics requires considerable space: a treatment applicable to heating boilers is given in a Bureau of Mines Bulletin2. . Coal composition may be expressed by either an ultimate or proximate analysis. In the ultimate analysis the proportions of carbon, hydrogen, oxygen, nitrogen, sulphur, and ash are determined. This form of analysis is difficult to make and is used only for extremely, close* studies. The proximate analysis is more easily made and is satisfactory for most purposes. In this analysis, the proportions of moisture, volatile matter, fixed carbon, and ash are determined. Moisture is obtained by noting the loss of weight of a sample of coal when dried at about 220 F. To determine volatile matter, the dried sample is heated to about 1750 F, 1 in a closed crucible, and the loss of weight is noted. The sample is then burned in an open crucible, and the accompanying loss of weight repre sents the fixed carbon. The unburned residue is ash. Although deter mined separately, the sulphur content is frequently reported with a proximate analysis. Other important qualities of coals are the screen sizes, ash fusion temperature, friability; caking tendency, and the qualities of the volatile matter. In considering these factors the following points are of interest. The volatile products given off by coals when they are heated differ 1 materially in the ratios by weight of the gases to the oils and tars. No . heavy oils or tars are given off by anthracite, and very small quantities are given off by semi-anthracite. ` As the volatile matter in the coal . increases to as much as 40 per cent of ash and moisture-free coal, in creasing amounts of oils and tars are released. For coals of higher volatile content, the relative quantity of oils and tars decreases, so it is low in the' sub-bituminous coals and in lignite. The percentage of ash and its fusion temperature do not indicate the composition or distribu- tion of its constituents. ^ A classification of coals is given in Table 5, and a brief description of the kinds of fuel is given in the following paragraphs, but it should be - recognized that there are no distinct lines of demarcation between the kinds, and that they graduate into each other. _ ' Anthracite is a clean, dense, hard coal which creates little dust in handling. It is com paratively hard to ignite but it burns freely when well started. It is non-caking, it burns uniformly and smokelessly with a short flame, and it requires no attention to the fuel bed * between firings. It is capable of giving a high efficiency in the common types of hand fired furnaces. A tabulation of the quality of the various anthracite sizes will be found in a Bureau of Mines Report *. Standard anthracite sizing specifications are shown in Table 6. .. Semi-anthracite has a higher volatile content than anthracite. It is not so hard and. ignites somewhat more easily; otherwise its properties are similar to those of anthracite. Semi-bituminous coal is soft and friable, and fines and dust are created by handling it. It ignites somewhat slowly and burns with a medium length of flame. Its caking prop * erties increase as the volatile matter increases, but the coke formed is relatively weak.' . Having only half the volatile matter content of the more abundant bituminous coals it : can be burned with less production of smoke,- and it is sometimes called smokeless'coal. The term bituminous coal covers a large range of coals and includes many types having distinctly different composition, properties, and burning characteristics. The coals range . from the high-grade bituminous coals of the East to the poorer coals of the West. Their caking properties range from coals which completely melt, to those from which the volatiles and tars are distilled without change of form, so that they are classed as non-, caking or free-burning. Most bituminous coals are strong and non-friable enough to permit of the screened sizes being delivered free from fines. In general, they ignite* Fuels and Combustion 307 easily and burn freely; the length of flame varies with different coals, but it is long. Much smoke and soot are possible, if improperly fired, especially at low rates of burning. . Sub-bituminous' coals~occur in the western states; they are high in moisture when mined and tend to break up as they dry or when exposed to the weather; they are.liable to ignite spontaneously when piled or stored. They ignite easily and quickly and have a. medium length flame, are non-caking and free-burning; the lumps tend to break into small pieces if poked; very little smoke and soot are formed. Lignite is of woody structure, very high in moisture as mined, and of low heating * value; it is clean to handle. It has a greater tendency than the sub-bituminous coals to disintegrate as it dries, and it also is more liable to spontaneous ignition. Freshly mined lignite, because of its high moisture, ignites slowly. It is non-caking. The char left after the moisture and volatile matter are driven off burns very easily, like charcoal. The lumps tend to break up in the fuel bed and pieces of char falling into the ashpit continue to burn. Very little smoke or soot is formed. /t CLASSIFICATION OF COKES Coke is produced by the distillation of the volatile matter from coal. The type of coke depends on the coal or mixture of coals used, the temperatures and time of distil lation and, to some extent, on the type of retort or oven; coke is also produced as a residue from the destructive distillation of oil. High-temperature cokes. Coke as usually available is of the high-temperature type, and contains between 1 and 2 per cent volatile matter. High-temperature cokes are sub divided into beehive coke of which comparatively little is now sold for domestic use, by product coke, which covers the greater part of the coke sold, and gas-house coke. The differences among these three cokes are relatively small; their denseness and hardness decrease and friability increases in the order named. In general, the lighter and more friable cokes ignite and burn the more easily. . Low-temperature cokes are produced at low coking temperatures, and only a portion of the volatile.matter is distilled off. Cokes as made by various processes under develop ment have contained from 10 to 15 per cent volatile matter. In general, these cokes ignite and burn .more readily than high-temperature cokes. The properties of various low-temperature cokes may differ more than those of the various high-temperature cokes because of the differences_in the quantities of volatile matter and because some may be light and others briquetted. ^ . Petroleum cokes, which.are obtained by coking the residue left from the distillation of petroleum, vary in the amount of volatile matter they contain, but all have the common property of a very low ash content, which necessitates the use of refractory pieces to protect the grates from being burned. . Table 6. Standard Anthracite Sizing Specifications3 Size Test Mesh, In. * Through Over Round Mesh Oversize Max. Per Cent .Undersize * Max; Min. Per Cent Per Cent Maximum Impurities. Per Cent Slateb Bone , Broken....... ......... 4% Egg----------------- ~ 3K to 3 2% Stove.................... 2% m Nut_______:_____ m % Pea,,................ ..... % Buckwheat._____ % Hi Hi He Barley.- ___ .. % % 5 7^ 7K 10 . 10 10 10 15 15 12H 10 15 15 15 20 .m m .m 5 m m. 7% 10 m2 m2 23 34 45 12 Ash 13 Ash . -------- ' ' . Approved and adopted by Anthracite Committee. State Street Building, Harrisburg, Pa. bWhen slate content on Broken to Pea inclusive is lessthan above standards, bone content may be cor respondingly increased, but slate content specified above shall not be exceeded in any event and the total maximum impurities shall not exceed those above specified. ' *' ^ . 308 CHAPTER 16 1946 Cuide FIRING METHODS FOB ANTHRACITE An anthracite fire should never be poked or disturbed, as this serves to bring ash to the surface of the fuel bed where it may melt into clinker. Egg size is suitable for large fire-pots (grates 24 in. and over) if the fuel can be fired at least 16 in. deep. For best results this coal should be fired deeply. Stove size coal is the proper size of anthracite for many boilers and furnaces used for heating buildings. It burns well on grates at least 16 in. in diameter and 12 in. deep. The fuel should be fired deeply and uniformly. Chestnut size coal is in demand for fire-pots up to 20 in. in diameter, with a depth of from 10 to 15 in. Pea size coal is often an economical fuel to burn. When fired carefully, pea coal can be burned on standard grates. Care should be taken to shake the grates only until the first bright coals begin to fall through the grates. The fuel bed, after a new fire has been built, should be increased in thickness by the addition of small charges until it is at least level with the sill of the fire-door. A satisfactory method of firing pea coal consists of drawing the red coals toward the front end and piling fresh fuel toward . the back of the fire-box. . Pea size coal requires a strong draft and therefore the best results generally will, be obtained by keeping the choke damper open and regu lating solely by means of the cold air check and the air inlet damper. Buckwheat size coal for'best results requires more attention than pea size coal, and in addition the smaller size of the fuel makes it more difficult to burn on ordinary grates. Greater care must be taken in shaking the grates than with the pea coal on account of the danger of the fuel filing through the grate.- In house heating furnaces the coal should be fired lightly and more frequently than pea coal. When banking a buckwheat coal fire it is advisable after coaling to expose a small spot of hot fire by putting a straight poker down through the bed of fresh coal. This will serve to ignite the gas that will be distilled from the fresh coal and prevent delayed ignition within the fire-pot, which in some cases, depending upon the thickness of the bed of fresh coal, is severe enough to blow open the doors and dampers of the furnace. Where frequent attention can be given and care exercised in manipulation of the grates this fuel can be burned satisfactorily without the aid of any special equipment. In general it will bq found more satisfactory with buckwheat coal to . maintain a uniform heat output and consequently to keep the system warm all the time, rather than to allow the system to cool off at times and then to attempt to burn the fuel at a high rate while warming up. A uni form low fire will minimize the clinker formation and keep the clinker in an easily broken up condition so that it readily can be shaken through the grate. ' ,. Forced draft and small mesh grates are frequently used for burning buckwheat anthracite. For greater convenience, domestic stokers are used. '' Buckwheat anthracite No. 2, or rice size, is used principally in stokers of the domestic, commercial and industrial type. No. 3 buckwheat anthracite, or barley, has no application-in domestic heating. - Fuels and Combustion 309 FIRING METHODS FOR BITUMINOUS GOAL A commonly recommended procedure for firing domestic heating units, called the side-bank method, requires the movement of live coals to one side or the back of the grate, and placing the fresh fuel charge on the opposite side. The results are a more uniform release of volatile gases, and the subjection of these gases to the high temperature of the red coals. If the fresh charge is covered with a layer of fine coal, still better results may be obtained because of slower release of volatile matter. Bituminous coal should never be fired over the entire fuel bed at one time. A portion of the glowing fuel should always be left exposed to ignite the gases leaving the fresh charge. The importance of firing bituminous coal in small quantities at short intervals is discussed.in a U. S. Bureau of Mines technical paper1. Better combustion is obtained by this method in that the fuel supply is main tained more nearly proportional to the air supply. If the coal is of the caking kind the fresh charge will fuse into one solid mass which can be broken up with the stoking bar and leveled from 20 min to one hour after firing, depending on the temperature of the fire-box. Care should be exercised when stoking not to bring the bar up to the surface of the fuel as this will tend to bring ash into the high temperature zone at the top of the fire, where it will melt and form clinker. The stoking bar should be kept as near the grate as possible and should be raised only enough to break up the fuel. With fuels requiring stoking it may not be necessary to shake the grates, as the ash is usually dislodged during stoking. ' . It is acknowledged that it may be difficult to apply the outlined methods to domestic heating boilers of small size, especially when frequent attendance is impractical. The adherence to these methods insofar as practical, however, will result in better combustion. The output obtained from any heater with bituminous coal will usually exceed that obtained with anthracite, since bituminous coal burns more. rapidly than anthracite and with less draft. Bituminous coal, however, will usually require frequent attention to the fuel bed. Preventing Smoke ' In general, time, temperature and turbulence are the essential require ments for smokeless combustion. Anything that can be done to increase . any one of these factors will reduce the quantity of smoke discharged. Especial care must be taken in hand-firing bituminous coals. . Checker or alternate firing, in which the fuel is fired alternately on separate parts of the grate, maintains a higher furnace temperature and thereby decreases the amount of smoke. ' . Coking and firing, in which the fuel is first fired close to the firing door and the coke pushed back into the furnace just before firing again, pro.duces the same effect. The volatiles as they are distilled thus have to pass over the hot fuel bed where they will be burned if they are mixed with sufficient air and are not cooled too quickly by the heat-absorbing surfaces of the boiler. Steam or compressed air jets, admitted over the fire, create turbulencein the furnace and bring the volatiles of the fuel more quickly into contact with the air required for combustion. These jets are especially helpful for the first few minutes after each firing. Frequent firings of small charges shorten the smoking period and reduce the density.. Thinner 310 CHAPTER 16 1946 Guide fuel beds on the grate increase the effective combustion space in the . furnace, supply more air for combustion, and are sometimes effective in reducing the smoke emitted, but care should be taken that holes are not formed in the fire. A lower volatile coal or a higher A.P.I. gravity oil always produces less smoke than a high volatile coal or low A.P.I. gravity oil used in the same furnace and fired in the same manner. The installation of more modern or better designed fuel burning equip ment, or a change in the construction of the furnace, will often reduce . smoke. The installation of a Dutch oven which will increase the furnace volume and raise the furnace temperature often produces satisfactory results. , In the case of new installations, the problem of smoke abatement can be solved by the selection of the. proper fuel-burning equipment and furnace design for the particular fuel to be burned and by the proper operation of that equipment. Constant vigilance is necessary to make certain that the equipment is properly operated. In old installations the solution of the problem presents many difficulties, and a considerable investment in special apparatus is often necessary. Lower rates of combustion per square foot of grate area will reduce the quantity of solid matter discharged from the chimney with the gases of combustion. The burning of coke, coking coal, and sized coal from which the extremely fine coal has been removed will not as a general rule produce as much dust and cinders as will result from the burning of non-cokirig coals and slack coals when they are burned on a grate. , . Modem boiler installations are usually designed for high capacity per square foot of ground area because such designs give the lowest cost of construction per unit of capacity. Designs of this type discharge a large quantity of dust and cinders with the gases of combustion, and if pollution of the atmosphere is to be prevented, some type of catcher must be installed. ' FIRING METHODS FOR SEMI-BITUMINOUS COAL The Pocahontas Operators' Association recommends the central cone method of firing, in which the coal is heaped on to the center of the bed forming a cone, the top of which should be level with the middle of the firing door. This allows the larger lumps to fall to the sides, and the fines to remain in the center and be coked. The poking should be limited to breaking down the coke without stirring, and to gently rocking the grates. ' It is recommended that the slides in the firing door be kept closed, as the thinner fuel bed around the sides allows enough air to get through. FIRING METHODS FOR COKE Coke ignites less readily than bituminous coal and more readily than anthracite and burns rapidly with little draft. In order to control the air admitted to the fuel it is very important that all openings or leaks into the ashpit be closed tightly. A coke fire.responds rapidly to the opening of the dampers. This is an advantage in warming up the system, but it also makes it necessary to watch the dampers more closely in order to prevent the fire from burning too rapidly. In order to obtain the same interval of attention as with other fuels a deep fuel bed always should.be maintained when burning coke. The grates should be shaken only. slightly in mild weather and should be shaken only until the first red particles drop from the grates in cold weather. The best size of coke for T a b l e 7. D e t a il e d R e q u ir e m e n ts for F u e l O il s 0 ' Fuels and Combustion \ 311 ssg L-isssf5gSsS|sis: i | c J c S D.I | e*.*S v3 g e -:g-D sa Ml8 Hi1 Stilt -:rHT?TiSi .a4>s-r c , 03 a IP m t> g'e . BS 54J gJJ3 3g :9,q S s iig g 5* II1 I 1-5 11 ! e 4-1! S ,,g Se8 an O v ..o a a i il C3C I:S8 '* s IlSi M O 4f ! S r "I S3 O* CsCou3 2c3 c vc ow cSats. /Ba 'N1!lM!O.!O.l! Oooooo hZZZZZ fill* g ,s 2jg3j-scaJ--"S. 2a-t g aH OJjSc-' 312 ' CHAPTER 16 1946 Guide Table 8. Approximate Gravity and. Calorific Value of Standard Grades of Fuel Oil Commercial Standard No. 1 2 3 5 6 Approximate Gravity Range A. P. I. 38-40 34-36 28-32 18-22 14-16 Calorific Value Btu Per Gallon 136,000 138,500 141,000 148,500 152,000 general use, for small fire-pots where the fuel depth is not over 20 in., is that which passes over a 1 in. screen and through a \x/i in. screen. For large fire-pots where the fuel can be fired over 20 in. deep, coke which passes over a 1 in. screen.and through a 3 in. screen can be used, but a coke of uniform size is always more satisfactory. Large sizes of coke should be either mixed with fine sizes or broken up before using. FURNACE VOLUME . The principal requirements for a hand-fired, furnaceiaie that it shall have enough grate area and correctly proportioned combustion space. The. amount of grate area required is dependent upon-the desired combustion rate. The furnace volume is influenced by the kind of coal used. Bituminous coals, on account of their long-flaming characteristic, require more space in which to burn the gases of combustion completely than do the coals low in volatile matter. For burning high volatile coals provision should be made for mixing the combustible gases thoroughly; so that combustion is complete before the gases come in contact with the relatively cool heating surfaces.- An abrupt change in the direction of flow tends to mix the gases of combustion more thoroughly. Anthracite requires com-' paratively little combustion space. . CLASSIFICATION OF OILS The Commercial Standard Specifications for Fuel Oils (CS 12-40) of the U. S. Department of Commerce are given in Table 7. These speci fications conform with American Society for Testing Materials Tentative .Specifications for Fuel Oils D396-38T. The A.P.I. gravity of oil is of interest in it& relationship to the calorific " value and these data are given in Table 8. - COMBUSTION OF OIL , With oil, as with any kind of fuel, efficient heat production requires that all combustible matter in the fuel shall be completely consumed and that it shall be done with a minimum of excess air. The combustion of oil is a rather rapid chemical reaction. Excess air provides an over supply of oxygen so that all of the oil will be completely oxidized and thus produce all the heat possible. The use of unreasonable quantities of air in excess of theoretical combustion requirements results in lowered efficiencies due to increased stack losses. Such losses, if not accompanied by unbumed products of combustion, may be offset somewhat by in creasing the secondary heating surfaces of the heat absorbing medium. , boiler or furnace. Oil is a highly concentrated fuel composed mainly of Filp.Is and Combustion Table 9. Representative Properties of Gaseous Fuels. . Based on Gas at 60 F and 30 in. Hg. 313 Ga3 Btu per Cu Ft (Gross) Low (Net) Specific Grayitt, Am = 1.00 for Combus tion, (CuFt) Products of Combustion Cubic Feet Total COi HsO with tfi Ulti mate COi Dry Basis Flame Tem perature, (F DEO) Natural gas-- California 1200 1085 0.67 11.26 1.24 2.24 12.4 12.2 3610 Natural gas-- Mid-Conti nental 970 870 0.57 9.17 0.97 1.92 10.2 11.7 3580 Natural gas-- Ohio 1130 1025 0.65 10.70 1.17 2.16 11.8 12.1 3600 . Natural gas-- Pennsylvania Retort coal gas Coke oven gas 1130 1025 0.71 570 510 0.42 590 520 0.42 11.70 5.00 5.19 1.30 0.50 0.51 2.29 1.21 1.25 12.9 5.7 5.9 12.3 11.2 11.0 3620 3665. 3660 Carbureted water gas Blue water gas 540 495 0.65 300' 280 0.53 4.37 2.26 0.74 0.75 0.46 0.51 5.0 17.2 2.8 22.3 3815 3800 Anthracite pro ducer gas .135 125 0.85 1.05 0.33 0.19 1.9 19.0 3000 Bituminous producer gas Oil gas .. 150 140 0.86 575 510 0.35 1.24 4.91 0.35 0.19 0.47 1.21 2.0 19.0 5.6 10.7 3160 3725 hydrogen and carbon. In its liquid form oil cannot burn. It must be converted into -a- gas of vapor by some means. If the excess air is to be kept within efficient limits, air must be supplied in carefully regulated quantities. The air and oil vapor must be thoroughly mixed to get a rapid and complete chemical reaction. The better the mixing, the less excess air will be needed. The combustion must take place in a space that maintains the temperatures high so the reaction will be completed. - CLASSIFICATION OF GAS Gas is broadly classified as being either natural or manufactured:' Natural gas is a mechanical mixture of several combustible and inert gases rather than a chemical compound. Manufactured gas as dis tributed is usually a combination of.certain proportions^ gases produced . by two or more processes. Representative properties of gaseous fuels commonly used in domestic heating are presented in Table 9. Natural gas is the richest of the gases and contains from 80 to 95 per cent methane, with small percentages of the other combustible hydrocarbons. In addition, it contains from 0.5 to 5.0 per cent of COt, and from 1 to 12 or 14 per cent of nitrogen. The heat value varies from 1000 to 1200 Btu per cubic foot, th.e majority of natural gases averaging about 1000 Btu per cubic foot. Table 9 shows typical values for thefour main oil fields, although values from any one field vary materially. ' , : . ' 314CHAPTER 16^^-1946 Guide Table 9 also gives the calorific values of the more common types of . manufactured gas. Most states have legislation which controls the distri-. . button of gas and fixes a minimum limit to its heat content. The gross or higher calorific value usually ranges between 520 and 545 Btu per cubic foot, with an average of 535. A given heat value may be maintained and yet leave considerable latitude in the composition of the gas so that as distributed the composition is not necessarily the same in different dis tricts, nor at successive times in the same district. However, in any community the variations in gas composition are held within suitable limits so that the performance of approved gas appliances will not be adversely affected. ' .. _ COMBUSTION OF GAS The majority of gas burners utilized in central domestic heating plants are of the Bunsen type and operate with a non-luminous flame. In this type of burner part of the air required for combustion is mixed with the gas as primary air, the air and gas mixture being fed to the burner ports. Additional secondary air is introduced around the flame by draft inspi' ration. In the luminous flame burner, which is sometimes used, all of die , . air for combustion is brought in contact with the flame as secondary air. This secondary air should be brought into intimate contact with the' gas. , . Some makes of burners use radiants or refractories to convert some of tbe energy in the gets to radiant heat. The radiants also serve as baffles in directing the flow of the products of combustion. , The quantity of air given in Table 9 is that required for theoretical combustion, but with a properly designed and installed burner the excess - air can be kept low. In Order to insure freedom from carbon monoxide .. under conditions which may obtain in installations, it is customary to design gas burning appliances for a supply of 30 to 35 per cent of excess air. In individual installations in which flue gas analyses are made, the . excess air is sometimes reduced to approximately 20 per cent. The division of the air into primary and secondary is a matter of burner ' design, the pressure of gas available, and the type of flame desired. _ , The air gas ratio has a decided effect upon flame propagation. It is - ' necessary that the gas will flow out of the burner ports fast enough so that the flame cannot travel back into the burner head. i.e. flash back, but the ' velocity must not be so high that it blows the flame away from the port. The maximum and minimum flow speeds from burner ports which may . . be permitted, are known to be very close together when air-gas mixtures ' ` in theoretical proportions are being supplied to the burner. As the air-gas ratio is lowered, and the mixture becomes more gas rich, the limiting speeds become farther apart, until with 100 per cent gas, in an all-yellow . flame, flash back cannot occur and a much higher velocity is needed to , blow off the flames. . SOOT The deposit of soot on the flue surfaces of a boiler or heater acts as an. .. insulating layer over the surface and reduces the heat transmission to the water or. air. The Bureau of Mines Report of Investigations No. 3272 4 shows that the loss of seasonal efficiency is not so great as has been . believed and usually is not over 6 per cent because the greater part of the , heat is transmitted through the combustion chamber surfaces. The' ~Bureau of Standards Report BMS 546 points out that, although the F,lets and Combustion- ' '_________ ___________. . '315 decrease in efficiency of an oil fired boiler due to soot deposits is relatively small the attendant increase in stack temperature may be considerable. ' The soot accumulation clogs the flues, reduces the' draft, and may prevent proper combustion, ' CONDENSATION AND CORROSION Sulphur dioxide or trioxide formed by the combustion of fuels is the corroding element in flue gases and becomes active whenever moisture is available for the formation of sulphurous or sulphuric acid. It is there fore necessary to maintain a flue'gas temperature above 175 F in all parts of appliances, and consequently it is not practicable to recover the latent heat in flue gases. Since some unpreventable condensation occurs during the warming-up period, it is important to design appliances so that all surfaces reach quickly a temperature above the dew-point of the flue gases or have corrosion resistant properties enabling them to with stand the corrosive effect: . .' DUSTLESS TREATMENT OF COAL The practice of treating the more friable coals to allay the dust they create is increasing. The coal is sprayed with various petroleum products, a solution of calcium chloride or a mixture of calcium and magnesium chlorides. -. , The coal is usually treated at the mine, but sometimes by the local distributor just before delivery. The salt solutions are sprayed under high pressure, using from 2 to 4 gal or from 5 to 10 lb of the salt per ton of coal, depending on its friability and size. Oil for the dustless treatment of coal is also applied under high, pressure, in concentrations of 1 to 8 qt per ton of coal, depending upon the characteristics of the coal and oil. Dustless treatments which are of such a corrosive nature that they may damage coal handling or burning equipment should not be used. REFERENCES . -Hand Firing Soft Coal Under Power Plant Boilera (U. S. Bureau of Mines Technical Paper No. 80). 2-Five Hundred Tests'of Various Coals in Househeating Boilers (U. S. Bureau of Mines Bulletin No. 276). . ' . 3_Quality of Anthracite as Prepared at Breakers, 1935 (17. S. Bureau of Mines Report of Investigations, R. I. 3283). --Effect of Soot on Heat Transmission in Boilers (U. S. Bureau of Mines Report of Investigation No. 3272). ' . 5_Effect of Soot on the Rating of an Oil-Fired Heating Boiler (National Bureau of Standards Report BMS 54). .. BIBLIOGRAPHY Fuels and Their Combustion, by Haslam and Russell (McGraw-Hill Co., 1926). Principles of Combustion in the Steam Boiler Furnace, by Arthur D. Pratt (Babcock and Wilcox Co.). ` '' Smoke-Producing Tendencies in Coals of Various Ranks, by H. J. Rose and F. P. Lasseter (A.S.H.V.E. Transactions, Vol. 45, 1939, p. 329). Fundamentals of Combustion in Small Stokers, by C. A. Barnes (Bituminous Coal Research, Inc., Technical Report No. IV). Combustion Efficiencies as Related to Performance of Domestic Heating Plants, by A. P. Kratz, S. Konzo, and D. W. Thomson {Illinois Engineering Experiment Station Circular No. 44). . ' ` Hand-Firing of Bituminous Coal in the Home, by A. P. Kratz, J. R. Fellows, and J. C.. Miles {Illinois Engineering Experiment Station Circular No. 46). Classification and Selection of Illinois Coals, by G. H. Cady {Illinois State Geologtcal Survey Bulletin No. 62). ' 316 CHAPTER 16 -'1946 Guide Bituminous Coal Research, Inc.: . . Technical Report VI, The Treatment of Coal with Oil and Other Petroleum Products, by J. M. Pilcher and R. A. Sherman. _ Information Bulletin No. 4, Dustless Treatment of Coals with Materials Other than Oil, by R. A. Sherman and G. W. Land. Information Bulletin No. 6, Questions and Answers on the Use of Fuel Oil for Dustless Treatment. . Technical Report VII--Application of Overfire Air Jets, by R. B. Engdahl. Bureau of Mines Publications: - Bulletin No. 97, Sampling and Analyzing Flue Gases, by Henry Kreisinger and F. K. Ovitz. r. Report of Investigations (R. I. 2980), Coke as a Domestic Heating Fuel, by P. Nicholls and B. A. Landry. . , Technical Paper No. 303, Value of Coke, Anthracite, and Bituminous Coal for Generating Steam in a Low-pressure Cast-Iron Boiler, by John Blizard, Tames Neil, and F. C. Houghten. Bulletin 378, Effect of Preheat, and Distribution of Ash in Fuel Beds, by P. Nicholls. Bulletin 360, Removal of Soot from Furnaces and Flues by the Use of Salts and Compounds, by P. Nicholls. . v Handbook, Questions and Answers for the Home Fireman (Revised), by J. F. Barkley. Anthracite Industries Laboratories, Publications: " < Report 2015, Comparison of Sizes, Egg, Stove and Chestnut Anthracite. Report 2018t Domestic Survey. .. Report 2062, Utilization of Anthracite for Domestic Heating. Report 2204, The Crater Method of Firing. ' Report 2403, Anthracite Industries Manual. . 0*7 and Gas Publications: ' Oil Fuels and Burners, by James A. Moyer (McGraw-Hill Co., 1937). ' Handbook of Oil Burning, by Harry F. Tapp {American OH Burner Association). . Industrial Gas Series, Combustion {American Gas Association). Comfort Heating {American Gas Association). .. CHAPTER 17 ^Automatic ^ue( (burning. Equipment Classification of Stokers, Combustion Process and Adjustments, Furnace Design, Classification of Oil Burners, Combus tion Chamber Design, Classification of Gas-Fired Appliances, Combustion Process, Ratings, Fuel Burning Rates AUTOMATIC mechanical equipment for the combustion of solid, liquid, and gaseous fuels is considered in this chapter. MECHANICAL STOKERS A mechanical stoker is a device that feeds a solid fuel into a combustion chamber, provides a supply of air for burning the fuel under automatic control and, in some cases, incorporates a means of removing the ash and refuse of combustion automatically. Coal can be burned more efficiently by a mechanical stoker than by hand firing because the stoker provides a uniform rate of fuel feed, better distribution in the fuel bed and positive control of the air supplied for combustion. CLASSIFICATION OF STOKERS ACCORDING TO CAPACITY Stokers may be-classified according to their coal feeding rates. The following classification has been made by the U. S. Department of Com merce, in cooperation with the Stoker Manufacturers Association. Class 1. Capacity, under 61 lb of coal per hour. Class2. Capacity 61 to 100 lb of coal per hour. Class 3. Capacity 101 to 300 lb of coal per hour. Class 4.- Capacity 300 to 1200 lb of coal per hour. Class 5. Capacity 1200 lb of coal per hour and over. . . Class 1 Stokers These stokers are used primarily for home heating and are designed for quiet, automatic operation. Simple, trouble-free construction and. attractive appearance are desirable characteristics of these small units. A common stoker in this class (Fig. 1) consists essentially of a coal hopper, 'a screw for conveying the coal from the hopper to the retort, a fan which supplies the air for combustion, a transmission for driving the coal feed worm, and an electric motor for supplying power for coal feed and air supply. Air for combustion is admitted to the fuel through tuyeres at the. top of the retort which may be either round or rectangular. Stokers in this class are made for burning anthracite, bituminous, semi-bituminous, and lignite coals, and coke. The U. S. Department of Commerce has issued commercial standards for household anthracite stokers *. Units are available in either the hopper type, as shown in.Fig. 1 or in . the bin-feed type as shown .in Figs. 2 and 3. Some stokers, particularly those designed for use with anthracite, automatically remove ash from the ash pit and-deposit it in an ash receptacle as shown in Fig. 3. Most of the bituminous models, however, require removal of the ash from the fuel bed after it is fused into a clinker. Stokers in this class feed coal to the furnace intermittently in accor dance with temperature or pressure demands; A special control is used 317 y 318 i CHAPTER'17 1946 Guide to insure sufficient stoker operation to maintain a fire during periods when no heat.is required. ... . , ' -. - Stoker-Fired Boiler and Furnace Units - ' . Boilers, air conditioners, and space, heaters especially designed for stokers are available having design, features closely coordinating the heat . absorber and the stoker. Although efficient and satisfactory performance . can be obtained from the application of stokers to existing boilers and furnaces, some of the combination stoker-fired units (Fig. 4) are more 1 compact and attractive in appearance. ' Class 2 and 3 Stokers Stokers in this class are usually of the screw feed type without auxiliary plungers or other means of distributing the coal. They are used exten sively for heating plants in apartments and hotels, also, for industrial Fig. 1. Underfeed Stoker, Hopper Type, Class 1 Fig. 2. Underfeed Stoker, Bin Feed Type, Class 1. plants. They are of the underfeed type and are available in both the hop per type, as illustrated in Fig: 5, and the bin feed type, shown in Fig. 6. These units also are built in plunger feed type with an electric motor; or a steam or hydraulic cylinder coal feed drive. . Stokers in this class are available for burning all types of anthracite, bituminous and lignite coals. The tuyere and retort design varies ac cording to the fuel and load conditions. Stationary typie grates.are used on bituminous models and the `clinkers formed from the ash accumulate on the grates surrounding the retort. .' Anthracite stokers in this class are equipped with moving grates which discharge the ash into a pit below the grate. This ash pit may be' located on one or both sides of the.grate and on some installations is of sufficient capacity to hold the ash for several weeks' operation. \ '.. ' ' Automatic Fuel Burning Equipment 319 Class 4 Stokers . Stokers in this group- vary widely in details of design and several- methods of feeding coal are employed. The underfeed stoker is widely used, although a number of the overfeed types are used in the larger sizes. Bin-feed, as well as hopper models, are available in both under feed and overfeed types. . Class 5 Stokers ' The prevalent stokers in this field are: (1) underfeed side cleaning, (2) underfeed rear cleaning, (3) overfeed flat grate, and. (4) overfeed inclined grate. ' Underfeed side cleaning stokers are made in sizes up to approximately 500 boiler horsepower. They are not so varied in design as those in the. smaller classes, although the principle of operation is similar. A stoker of this type is illustrated in Fig. 7. The rear cleaning underfeed stoker is usually of the multiple retort design and is used in some of the largest industrial plants and central power stations. Zoned air control has been applied to these stokers, both longitudinally and transversely of the grate surface. The overfeed flat grate stoker is represented by the various chain--or traveling-grate stokers. A typical traveling-grate stoker is illustrated in Fig. 8. Another distinct-type of overfeed flat-grate stoker is the spreader (Figs. 9 and' 10) type in which coal is distributed either by rotating paddles or by air over, the entire grate surface. . This type of stoker is adapted to a wide range of fuels and has a wide application on small sized fuels, and on fuels such as lignites; high-ash coals, and coke breeze. The overfeed inclined-grate stoker operates on the same general com bustion principle as the flat-grate stoker, the main difference being that rocking grates, set on an' incline, are provided in the former to advance the fuel during combustion. Combustion Process .. , In anthracite stokers of the Class 1 underfeed type, burning takes place entirely within the stoker retort. The refuse of- combustion spills over the edge of-the retort into an ash pit or receptacle from which it may be removed'either manually or automatically. , - Larger underfeed anthracite stokers operate on the same principle, ` except that the retort is rectangular and the refuse spills over only one or two sides, of the grate. Anthracite for stoker firing is usually the No. 1 buckwheat or No. 2 buckwheat size. Because the majority of the smaller bituminous coal stokers operate on the underfeed principle, a general description of their operation is.given. When the coal is fed into the retort, it moves upward toward the zone of combustion and is heated by conduction and radiation from the burning fuel in the combustion zone. As the temperature of the cqal rises, it gives off moisture and occluded gases, which are largely non-combustible. When the temperature increases to around 700 or 800 F the coal particles become plastic,- the degree of plasticity varying with the type of coal. A rapid evolution of the combustible volatile matter.occurs during and directly after the plastic stage. The distillation of volatile matter con- tinues'above the plastic zone where the coal is coked.' The strength and porosity of the coke formed will vary according to the size and character1 istics of the coal. While some of the ash fuses into particles on the surface 320 CHAPTER 17 1946 Guide Automatic Fuel Burning Equipment 321 Fig. 6. Underfeed Screw Stoker, Bin Type, Class 2, 3 or 4 n COAL COAL HOPPER AGITATOR COAL PLUNGER Fig. 7. Underfeed Side Cleaning Stoker 322 ____________ CHAPTER 17 __________ 1946 Guide of the coke as it is released, most of it remains on the hearth or grates and, as this ash layer becomes thicker with time, that portion exposed to the higher temperatures surrounding the retort fuses into a clinker. The temperature in the fuel bed, the chemical composition and homogeneity of the ash, and the time of heating govern the degree of fusion. , Most bituminous coal stokers of Classes 1, 2, 3 and 4 require manual' removal of the ash in clinker form. ' In the. underfeed'side-cleaning stokers the fuel is introduced at the front of the furnace to one or more retorts, and is advanced away from the retort as combustion progresses, while finally the ash is disposed of at the sides. This type of stoker is suitable for all bituminous coals while in the smaller sizes it is suitable for small sizes of anthracite. In this type of stoker the fuel is delivered to a retort beneath the fire and is raised into the fire. During this process the volatile gases are released, are mixed with air, and pass through the fire where they are burned. The ash may be continuously or periodically discharged at the sides." Automatic Fuel Burning Equipment 323 coking fuels but preferably for those, of low volatile content. Its grate action keeps the fuel bed broken up. thereby allowing for, free passage of air. Because of its agitating effect on the fuel it is not desirable for badly . dickering coals. It usually should be provided with a.front arch to ignite the volatile gases. ' Combustion Adjustments .' The coal feeding rate and air supply to the stoker should be regulated so as to maintain a balance between the load demand and the heat liberated by the fuel. Under such conditions no manual attention to the fuel bed should be required, other than the removal of clinker in stokers which operate on this, prindple of ash removal. As in all combustion processes, the maintenance of the correct pro portions of air and fuel is essential. It is desirable to supply the minimum amount of air required to properly burn the fuel at the rate of feed. While there may be only slight variations in the rate at which the coal is being fed due to variations in the size or density of the coal, there may The underfeed rear-cleaning stoker accomplishes combustion in much the same manner as the side-cleaning type, but consists of several retorts placed side by side and filling up the furnace width, while the ash disposal is at the rear. In principle, its operation is the same as the side cleaning underfeed type. % . Overfeed flat-grate stokers receive fuel at the front of the grate in a layer of uniform thickness and move it horizontally to the rear of the furnace. Air is supplied under the moving grate to carry on combustion at a sufficient rate to complete the burning of the coal near the rear of the furnace. The ash is carried over the back end of the stoker into an ash pit beneath. This type of stoker is suitable for small sizes of anthra cite or coke breeze, and also for bituminous coals, the characteristics of which make it desirable to burn the fuel without disturbing it. This type of 'stoker requires an arch over the front of the fuel bed to maintain ignition of the incoming fuel. Frequently, a rear combustion arch is also required. .' . In addition to the use of rocking grates, the overfeed inclined-grate stoker is provided with an ash plate on which ash is accumulated and dumped'periodically. This type of stoker is suitable for all types of Fig. 10. Overfeed Spreader Stoker.(Pneumatic Type) be wide variations in the rate of air flow as the result of changes in fuel bed resistance. - These changes in resistance may be caused by changes in the porosity of the fuel bed due to variations in size or friability of the coal, ash and clinker accumulation, and variations in depth of the fuel bed. Because of this variable fuel bed resistance, many bituminous stokers, even in the smaller domestic sizes, incorporate air controls which. automatically, compensate for these changes in resistance and maintain a constant air fuel ratio. . It is desirable on most stoker installations to provide automatic draft regulation in order to reduce air infiltration and provide better control during the banking, or off, periods of the stoker. The efficiency of com bustion. may be determined by analyzing the flue gases as explained in Chapter 16. . Furnace Design Although there is considerable variation in stoker, boiler, and furnace design, the stoker , industry, from long-time experience,-has established certain rules for- the-proportioning of furnaces for domestic, and com mercial stokers. The stoker installer and designer of stoker-fired equip ment should give careful consideration to these factors. ' 324 CHAPTER 17 '1946 Guide The Stoker Manufacturers Association has published standard recom mendations on setting heights for stokers having capacities up to 1200 lb of coal per hour1. . The empirical formulas for determining these setting heights are: For burning rates up to 100 lb coal per hour ' H = 0.1125 B + 15.75 (1) . For burning rates from 100 to 1200 lb coal per hour H = 0.03 5+24 (2) where H = minimum setting height, inches, for steel boilers. For cast-iron boilers height may be % H. B -- burning rate coal per hour, pounds. - Standards for minimum firebox dimensions and base heights have been formulated by the Stoker Manufacturers Association as shown in Fig. 112. ic Fuel Burning Equipment '- ____________________________________ 325 The Association also has adopted a uniform method of. selecting stokers that is published in convenient tables and charts8. The required capacity of the stoker is calculated as follows: ' Load (Btu per hour) Stoker burning rate ---------------------------------------------------------------------------------------------- = required (pounds of Heating value of coal (Btu per pound) X over-all efficiency of coal per hour) - stoker and boiler or furnace - In determining the total load placed on a stoker-fired boiler by a steam or hot water heating system, a piping and pick-up factor of 1.33 is com monly used in sizing the stoker, but this factor should be increased at times due to unusual conditions. Controls The heat delivery from the stoker of the smallest household type to the largest industrial unit can be regulated accurately with fully automatic controls. The smaller heating applications are controlled normally by a Fig. 11. Suggested Minimum Firebox Dimensions and Base Heights? For reference in selecting or designing boilers and furnaces for stoker firing. Dimensions shown are for , net Inside clearance at grate level using coal with heating value of not less tlian 12,000 Btu per pound. Under certain conditions smaller fireboxes will permit satisfactory performance but these dimensions are preferred normal minimums. ' In considering these recommendations, it should be understood that they show the average recommended minimum. There are many factors affecting the proper application of stokers to various types of boilers and furnaces, and, in.certain instances, setting height or firebox dimensions shown in the standards may be modified without impairing performance. Such modification rests with the experience of the installer, or designer, with a particular stoker, the type of fuel used, and the construction of the boiler or furnace. . Bating and Sizing Stokers The capacity or rating of small underfeed stokers is usually stated as the burning rate in pounds of coal per hour. Codes for establishing uni form methods of rating anthracite, and bituminous coal stokers have been adopted by the Stoker Manufacturers Association3. . thermostat placed in the building to be heated. Limit controls are supplied to prevent excessive temperature or pressure being developed in the furnace or boiler and refueling controls are used to maintain ignition during periods of low heat demand. Automatic low water cut-outs are recommended for use with all automatically-fired steam boilers. (See Chapter 34.) DOMESTIC OIL BURNERS An oil burner is a mechanical device for producing heat automatically from liquid fuels. Two methods are employed for the preparation of the oil for the combustion process; atomization, and vaporization. The simpler types of burners depend upon the natural chimney draff forsupplying the air for combustion. Other burners provide mechanical air supply or a combination of atmospheric, and mechanical. Ignition is accomplished by. an electrical spark or hot wire, or by an oil or gas pilot. ' Some burners utilize a combination of these methods. Continuously operating burners may use manual ignition. Burners of different types- y^ 326. CHAPTER 17 1946 .Guide operate with luminous or non-luminous flame. Operation may be inter- mittent, continuous with high-low flame, or continuous with graduated flame. CLASSIFICATION OFBURNERS Domestic oil burners may be classified by type of design or operation into the following groups: pressure atomizing or gun, rotary, and vapor izing or pot. These are further classified as mechanical draft, and natural draft. . Pressure Atomizing (Gun Type) - Gun type burners may be divided into two classes, low-pressure, and high-pressure atomization. In the first group, a mixture of oil and primary air is pumped as a spray through the nozzle at a pressure of 2 to 7 lb per square inch. Secondary air is supplied by a fan. Ignition is obtained by means of a high-voltage electric spark used alone, or as primary ignition for a gas pilot. Various features of a low pressure atomizing burner are shown in Fig. 12. -Automatic Fuel Burning Equipment 327 Rotary Type . This class of burners may be divided into two groups: vertical, and horizontal. Most of the smaller rotary burners are of the vertical type, and use the lighter distillate oils, No. 1 or 2 grade. . The most distinguishing feature of vertical rotary burners is, the principle of .flame application. ' These burners are of two general types: the center flame and wall flame. In the former type (Fig. 14), the oil is atomized by being thrown from the rim of a revolving disc or cup and the ' flame burns in suspension with a characteristic yellow color. Combustion is supported by means of a bowl-shaped chamber or hearth. The wall flame burner (Fig. 15) differs in that combustion takes place in a ring of stainless steel or refractory material, which is placed around the hearth. Dependent upon combustion adjustment, these burners may operate with either a semi-luminous or non-luminous flame. . Both types of vertical rotary burners are further characterized by their installation within the ash pit of the boiler or furnace. Various types of Fig. 13. High-Pressure Atomizing Oil Burner The high-pressure atomizing type, illustrated in Fig. 13, is characterized by an air tube, usually horizontal, with oil supply pipe centrally located in the tube and arranged so that a spray of atomized oil is introduced, ' at about 100 lb per square inch, and mixed in the combustion chamber with the air stream emerging from the air tube. A variety of patented shapes is employed at the end of the air tube to influence the direction and speed of the air and thus the effectiveness of the mixing process. This type of burner utilizes a fan to supply the air for combustion, and ignition, is established by a high-voltage electric spark that may be operative continuously while the burner is running, or just at the beginning of the running period. Gun type burners operate on the intermittent on-off principle, and with a luminous flame. , . The combustion process is completed in a chamber constructed .of refraictoiy material, or stainless steel, this being a part of the installation. Pressure-atomizing burners generally use the distillate oils,' No. 1) 2 or 3 grade. '(See Chapter 16.) ' .' '" Fig. 14. Center Flame Vertical Rotary Burner Fig. 15. Wall Flame Vertical Rotary Burner ignition are utilized, gas and electric, either spark or hot wire. The air for combustion is supplied partially by natural draft, and partially by fan effect of the central spinner element. . Horizontal rotary burners are used principally to burn the heavier oils, Nos. 5-and 6 grades, principally ip larger commercial and industrial installations, although domestic sizes are available. Such burners are of the mechanical atomizing type, using rotating cups which throw the oil from, the edge of the cup at high velocity into the surrounding stream. . of air delivered by the blower (Fig. 16). Horizontal rotary burners commonly use a combination electric-gas ignition system, or are lighted manually. Primary air for combustion is . supplied by a blower, and secondary air, often introduced through a checkerwork in the combustion chamber, is controlled by chimney draft. These burners operate with a luminous flame,, usually on high-low or continuous setting. ' . In larger installations, burners may be installed in multiple in a common combustion chamber. Because of the high viscosity oils used in these Automatic Fuel Burning Equipment.\329 Vaporizing burners of the natural draft type are used ,a's the firing device in integral space heaters, water heaters, or furnace units. Only those with full mechanical draft are suitable for conversion installation. . Oil-Fired Boiler and Furnace Units . A number of types of specially designed oil-fired boiler-burner and furnace-burner units are available. A typical boiler-burner unit is shown in Fig. 18. The coordinated-design of boiler (or furnace) and burner elements insures the optimum in operating characteristics, and the main ' tenance of balanced performance. This type of equipment usually has more heating surface, better flue proportions and gas travel than con- Fig. 16. Horizontal Rotating Cup Oil Burner burners, it is customary to preheat the oil between the tank and the burner. Preheating when delivering from tank' car, or truck is often required in cold weather. As with pressure atomizing burners, a refrac tory combustion chamber, built within the boiler furnace, is a part of the installation. . Vaporizing Burners * '' This type burner transforms the oil into a combustible vapor by the application of heat from a plate, or cracking chamber. The class may be subdivided into burners supplying combustion air mechanically, and those utilizing the natural chimney draft. Vaporizing pot-type burners are restricted to the use of the lighter distillates. ' These burners are designed for continuous or intermittent operation, with manual ignition, and the rate of burning is controlled by a metering valve. Flame may be luminous or non-luminous, dependent upon adjustment. A burner of this type is illustrated in Fig. 17. , Fig. 17. Vaporizing Pot-Type Burner . - Fig. 18. Typical Boiler-Burner Unit . ventional boilers or furnaces. Some of the better conversion installations, however, may equal the unit type in performance." . Operating Requirements for Mechanical Draft Oil Burners '- The U. S. Department of Commerce in conjunction with the oil burner industry has established commercial standards for automatic mechanical draft oil burners for domestic installations which cover. installation requirements and performance tests4. - Combustion Process , /. Efficient combustion must produce a clean flame and use a relatively -small excess of'air, t.e., -between 25 and 50 per cent. This can be done only by vaporizing the oil quickly and completely, and mixing it vigorously with air in a combustion chamber hot enough to support the combustion. A vaporizing burner prepares the oil, for combustion, by transforming the liquid fuel to. the gaseous state by the application of heat. .This is accom plished before the oil vapor-mixes with air . to any extent and if the air and oil vapor temperatures are high and the fire pot hot, a clear blue flame is produced. , ., In an atomizing burner the oil is mechanically separated into very fine particles so that the surface exposure of the liquid to the radiant heat of the combustion chamber is vastly increased and vaporization proceeds quickly. The result is the ability to burn more and heavier oil within a given Combustion space. Because the air enters the combustion chamber 330 CHAPTER 17 1946 Guide with the liquid fuel particles, mixing, vaporization and burning occur all at once in the same space. This produces a luminous flame. A deficient amount of air is indicated by a dull red or dark orange flame with smoky tips. An excessive supply of air may produce a brilliant white flame or a short ragged flame with incandescent sparks flashing through the com bustion space. While extreme cases may be detected, it is not possible to distinguish, by eye, the effect of the finer adjustment which competent installation requires. Combustion Adjustments . The present-day oil burner with mechanical oil and air supply, properly installed and equipped with an automatic draft regulator, is capable' of maintaining efficient combustion for an appreciable period following .the initial adjustments of oil and air. Eventually certain changes may occur, however, that will cause the per cent of excess air to decrease below allowable limits. A decrease in air supply while the oil delivery remains constant or an increase in oil delivery while the air supply . remains constant will make the mixture of oil and air too rich for clean combustion. The more efficient the adjustment the more critical it will be. The oil and air supply rates must remain constant. The following factors may influence the oil delivery rate: (1) changes in oil viscosity due to temperature change or variations in grade of oil delivered, (2) erosion of atomizing nozzle, (3) fluctuations in by-pass relief pressures, and (4) possible variations in methods of atomization. Any change due to partial stoppage of oil delivery wijl increase the proportion of excess air. This will result-in less heat, reduced economy and possibly a complete interruption of service. . The following factors may.influence the air supply: (1) changes in combustion draft due to a variety of causes (i.e., changes in chimney draft because of weather changes, seasonal changes, back drafts, failure or inadequacy of automatic draft regulator, use of chimney for other purposes, possible stoppage of the chimney and changes in draft resis tance of boiler due to partial stoppage of the flues), and (2) changes in air inlet adjustments at the fan. Air leakage into the boiler or furnace setting should be reduced to a minimum. The amount of air leakage will be determined by the draft in the combustion chamber. It is important that this draft should be reduced as low as is consistent with the proper disposal of the gases of combustion. When using mechanical draft burners with average con ditions, the combustion chamber draft should not be allowed to exceed 0.02-0.05 in. water. An automatic draft regulator, is very helpful in maintaining such values. -. _ Even though a fan is generally used to supply the air for combustion, in most oil burners, the importance of a- proper chimney should not be , overlooked. The chimney should have sufficient height and size to insure ` that the draft will be uniform within the limits given above if maximum efficiency throughout the heating season is to be maintained. Measurement of the Efficiency of Combustion .. . Since efficient combustion is based upon a clean flame and definite proportions of oil and air employed, it is possible to determine the results by analyzing the combustion gases. It is usually sufficient to analyze only for carbon dioxide (C02). A showing of 10 to 12 per cent, indicates Automatic Fuel Burning Equipment 331 the best adjustment if the flame is clean. Most of the good installations show from 8 to. 10 per cent C02. Taking into account the potential hazard of low excess air (high COi), a setting to give 10 per cent C02 constitutes a reasonable standard for most oil burners. ' ` Combustion Chamber Design . With burners requiring a refractory combustion chamber the size and shape should be in accordance with the manufacturer's instructions. It is important that the chamber shall be as nearly air tight as is possible, except when the particular burner requires a secondary supply of air for combustion. ., , The atomizing burner is dependent upon the surrounding heated refractory or firebrick surfaces to vaporize the oil and support combustion. ' Unsatisfactory combustion may be due to inadequate atomization and miring. A combustion chamber can only compensate for these things to a limited extent. If liquid fuel continually reaches some part of the fire brick surface, a carbon deposit will result. The combustion chamber should enclose a space having a shape similar to the flame but large enough to avoid flame contact. The nearest approach in practice is to have the bottom of the combustion chamber flat, but far enough below the nozzle to avoid flame contact, the sides tapering from the air tube at the same angle as the nozzle spray and the back wall rounded. A plan view of the combustion chamber resembles in shape the outline of the flame. In this wayas much.firebrick as possible is close to the flame so it may be kept hot. This insures quick vaporization, rapid combustion and better mixing by eliminating dead spaces in the combustion Chamber. An overhanging arch at the back of the fire pot is sometimes used to increase the flame travel and give more time for mixing and burning, and sometimes to prevent the gases from going too directly into the boiler flues. When good atomization and vigorous mixing are achieved by the burner, combustion chamber design becomes a less critical matter. .Where secondary air is used; combustion chamber design is quite important. When installing some of the vertical rotary burners the manufacturer's instructions must be followed carefully when installing the hearth, as in this class successful performance depends upon this factor. . Boiler Settings . - As the volume of space available for combustion is a determining factor in oil consumption, it is general practice to remove grates and extend the combustion chamber downward to include or even exceed the ash pit volume; in new installations the boiler may be raised to make added volume available. Approximately 1 cu ft of combustion volume . should be provided for every developed boiler horsepower, and in this volume from 1.5 to 2.5 lb of oil per hour can properly be burned. This corresponds to an average liberation of about 38,000 Btu per. cubic foot per hour. At times much higher fuel rates may be satisfactory. For best results, care should be taken to keep the gas velocity below 40 fps. Where checkerwork of brick is used to provide secondary air, good practice calls for about 1 sq in. of opening for each pound of oil fired per hour. Such . checkerwork is best adapted to flat flames, or to conical flames that can be spread over the floor of the combustion chamber. The proper bricking of a large or even medium sized boiler for oil firing is important and frequently it is advisaJble to consult an authority on this subject. The essential in combustion chamber design is to provide against flame . impingement upon either metallic or firebrick surfaces. Manufacturers of 332 CHAPTER 17 1946 Guide oil burners usually have available detailed plans for adapting their burners to various types of boilers, and such information should be utilized. Controls . Controls for oil burner operation, including devices for the safety and protection of a boiler or furnace, are fully described in Chapter 34. GAS-FIRED HEATING EQUIPMENT A gas burner is defined by the American Gas Association as "a device for the final conveyance of the gas, or a mixture of gas and air, to the combustion zone." Burners used for domestic heating are of the atmos pheric injection, yellow flame, or power burner types. The use of gas has resulted in the production of a number of types of . domestic gas heating appliances, and systems. These may be classified Automatic Fuel Burning Equipment 233 are of circular or rectangular shape in order to fit in space available. The control equipment is generally the same as for gas boilers and furnaces. Various baffles made of clay'radiants or metal are used for the purpose of guiding the products of combustion along the heating surface in the firebox or flues. Automatic air dampers are supplied on many models, to prevent flow of air into the firebox^ when the burner is- not operating.- A typical gas conversion burner is shown in Fig. 20, Burners of this type are available in sizes ranging from 80,000 to 500,000 Btu per hour capacity. Burners of even larger capacity, for use with natural gas in large steel boilers are usually engineered by the local utility or contractor. . They are available in an infinite number of sizes because the burner may be an assembly of multiple burner heads filling the entire firebox. . . Domestic sizes of conversion burners should be installed with due attention to the method of venting. Draft hoods, conforming to Ameri in. types designed for central heating plants^ and those for unit applica-' tion. Gas-designed units and- conversion burners are available for the several kinds of central systems. Unit heaters, space heaters and circu lators may be had for installation in the space being heated. Central Heating Systems , Boilers and furnaces specially designed for gas-firing incorporate design features for obtaining maximum efficiency and performance. Small flue passes to secure good heat transfer, the use of materials resistant to the corrosive effects of products of combustion, and draft hoods are notable features. Control equipment includes gas pressure regulators, thermostatic pilots and limit controls designed to protect the appliance and to insure safety of operation. A boiler designed for gas-burning is illustrated in Fig. 19. ' , Conversion burners are usually complete burner and control units designed for installation in existing boilers and furnaces. Burner.heads can Standard .Requirements, should be installed in place of the dampers- used with a solid fuel. , .: . . . One form of central heating system is the warm air floor furnace5. The use of these furnaces is adaptable to mild climates. They are used for' heating first floors, or where heat is required in only, one or two rooms. A number may be used to provide heat for the entire building where all rooms are on the ground floor, thus giving the heating system flexibility.- With the usual type the register is installed in the floor, the heating element and gas piping being suspended below. . . .. Unit Type Heaters Space heaters may be used for auxiliary heating, but in many cases are installed for furnishing heat to entire buildings. With the exception of wall heaters, they are semi-portable. '' Parlor Heaters or circulators are usually of the cabinet type. They heat" the room entirely by convection, i.e., die cold air of the room is drawn in near the base, passes up inside the jacket around a heating section, and, out of the heater at, or near, the top. These heaters cause a continuous circulation of- the air in the room during the time they are in operation. 334 CHAPTER 17. . . 1946 Guide The burners are located in the base, at the bottom of an enclosed coim - bustion chamber.. The products of combustion pass around baffles within the heating element,-and out the flue at the back near the top. They are' well adapted for residence room heating, and also for stores and offices. Radiant heaters give off a considerable portion of their heat in the form of radiant energy emitted by an incandescent refractory that is heated by . a Bunsen flame. They are made in numerous shapes and designs and in sizes ranging from two to fourteen or more radiants. . An atmospheric burner is supported near the center of the base. Others have a group of . small atmospheric burners supported on a manifold attached to the base. Most radiant heaters are portable; however, there are also types, which are encased in a jacket that fits into the wall with a grilled front. ' Gas-fired steam and hot water radiators are other types of room heating appliances. They are made in a large variety of shapes and sizes and are similar in appearance to the ordinary steam or hot water radiator. A separate combustion chamber is provided in the base of each radiator and is usually fitted with a one-piece burner. They may be secured in either the vented or unvented types, and with steam pressure, thermostatic or room temperature controls. . Warm air radiators are similar in appearance to steam or hot water radiators. They are usually constructed of sheet metal hollow sections. The products of combustion circulate through the sections and are discharged from a flue or into the room, depending upon whether the radiator is of the vented or unvented type. ' Unit heaters are used extensively for heating large spaces such as stores, garages, and factories. .These heaters consist of a burner, heat exchanger, fan for distributing the air, draft hood, thermostatic pilot and controls for burners and fan. They are usually mounted in an elevated position from which the heated air is directed downward by louvres. Some unit heaters are suspended from the ceiling, and others are free-standing floor units of the heat tower type. Unit heaters are available in two types, classified according to their use, with, or without ducts. Only those types of unit heaters tested and approved as warm air furnaces can be connected safely to ducts, as they have sufficient blower capacity to deliver an adequate air supply against duct resistance and are equipped, with limit controls. Combustion Process and Adjustments - Most domestic gas burners are of the atmospheric injection (Bunsen) type in which primary air is introduced, and mixed with the gas in the throat of the mixing tube. A ratio of about 3 parts primary air to 1 part gas for manufactured gas, and a 5J^ to 1 ratio for natural gas, are generally used as theoretical values. The amount of excess air required in practice depends upon several factors, notably; uniformity of air distribution and .. mixing, direction of gas travel from burner, and the height and tem perature of. combustion chamber. _- Secondary air is drawn into gas appliances by natural draft: As with other fuels, excess secondary air constitutes a loss, and should be reduced to a proper minimum, which usually cannot be less than 25 to 35 per cent if the appliance is to meet A.S.A. approval. Yellow flame burners depend upon secondary air, alone, for combustion. .. The flame produced by atmospheric injection burners is non-luminous.: . Air shutter adjustments for manufactured gas should be made by closing; - ,Automatic Fuel Burning Equipment 335 the air shutter until yellow flame tips appear and then by opening the air shutter to a final position at which the yellow tips just disappear.. This' type of flame obtains ready ignition from port to port and also favors ' quiet flame extinction. When burning natural gas the.air adjustment is generally made to secure as blue a flame as obtainable. Little difficulty should be had in maintaining efficient combustion when burning gas. The fuel supply is normally held to close limits of variation in pressure and calorific value and the rate of heat supply is nominally constant. Because the force necessary to introduce the fuel into the combustion chamber is an inherent factor of the fuel, no draft by. the chimney is required for this purpose. The use. of a draft hood'insures the maintenance of constant low draft condition in the combustion chamber with a resultant stability of air supply. A draft hood is also helpful in controlling the amount of excess air and. preventing back drafts that might extinguish the flame. (See Chapter 16.) Due to the use of draft hoods and gas pressure regulators both the input and combustion conditions of gas appliances are maintained quite uniform until deposits of dirt, corrosion, or scale accumulate in the air inlet openings, burner ports or on the heating surface. Periodic cleaning is necessary to keep any gas appliance in proper operating condition. Measurement oi the Efficiency of Combustion The efficiency of combustion may be judged from the percentage of carbon dioxide (COt), oxygen (Oi) and carbon monoxide (CO) in the flue gases. The COt and Ot may be obtained ,by means of an Orsat apparatus but the CO must be determined by more accurate equipment. It is customary to use simple indicators to determine whether CO is present and to make adjustments of the appliances to reduce the CO below 4/100 of one per cent before continuing tests in which the COt and Ot can.then be found by use of the Orsat apparatus. Since the ultimate COt for any gas depends on the total hydrogen content the quality of the combustion should not be judged from the value of the COt in the flue gas without reference to the ultimate COt obtainable. Practical values of COt will usually be from 8 to 14 per cent depending on the gas used. Ratings for Gas-Appliances Input rating for a gas appliance'is established by demonstrating that the appliance can meet the Approval Requirements of the A.S.A. The tests are conducted at the A.G.A.. Testing Laboratories. Output rating is determined from the approved input and an average efficiency stated in the Approval Requirements and is the heat available at the outlet. Sizing Gas-Fired Heating Plants .' Although gas-burning equipment usually is completely automatic, maintaining the temperature of rooms at a predetermined figure, there are some manually controlled installations. In order to overcome effectively the starting load and losses in piping, a manually-controlled gas boiler should have an output as much as 100 per cent greater than the equivalent standard radiation'which it is expected to serve. . Boilers under thermostatic control, however, are not subject to such severe pick-up loads and consequently, it is possible to use a lower selec tion factor. . For a gas-fired boiler or furnace under thermostatic control a factor of 20 to 25 per cent is usually 'sufficient for pick-up allowance. 336 . CHAPTER 17' 1946 Guide Automatic Fuel Burning Equipment 337 In those installations, in mild climates where 100 per cent outside air . is used, furnaces should be of larger size in' order to provide adequate ,-capacity and quick pick-up under intermittent heating conditions; . The factor to be allowed for loss of heat from piping will vary some what, the proportionate amount of piping installed being greater for small installations than for large ones. For selection factors to be added to installed radiation under thermostatic control see Chapter 18. - Appliances used for heating with, gas should bear the approval seal of the A.G.A. Testing Laboratories on the manufacturer's nameplate, ) P together with the official input and output ratings. It is not permissible to operate a gas heating unit above its stated rating. It may be necessary to operate below this rating at elevations above 3,000 ft. Installations should be made in accordance with recommendations shown in. the publications of the American Gas Association. Controls .. Temperature controls for gas burners are described in Chapter 34. Some central heating plants are equipped with push-button or other manual control. The main gas valve may be of either the snap action or throttling type. Automatic electric ignition is available. FUEL BURNING RATES The burning rate for automatic fuel burning devices is determined by the gross heat output required of the boiler, or furnace,- to carry the net ` heating load plus allowances for system losses, and pick-up. General values for these allowances previously have been noted. Detailed infor mation for piping and pick-up allowances for steam; and hot water systems 'is given in Chapter 18 and for warm air systems'in Chapters 21 and 22. ' ' When the gross output, operating efficiency, and heat value of the fuel -1------- 1--------- 1-------1--------- 1------- 1--------- 1------- 1--------- 1-------1---------- 1-------1----------1------- 1 r 0 g 4 6 8 10 12 14 16 - GROSS OUTPUT-HUNDRE0 FEET STEAM.RADIATION 1 , 1--1--1-- i 111 i 1 i--i 1--1 1 1 1 1 l .1--r--1 0 5 10 15. 20 25 CROSS OUTPUT- HUNORED FEET WATER RA0IAT10N :--1 21 0 30 Fig. 22. Oil Fuel Burning Rate Chart3 This chart is based upon No. 3 oil having a heat content of 143.400 Btu per gallon. If other grades pf; oil are used multiply the value obtained from this chart by the following factors: No. 1 oiT(l39;000`Btu ner gallon) 1.032; No. 2 oil (141,000 Btu per gallon) 1.017: No. 4 oil (144.500 Btu per gallon) 0.992; No. 5 oil (146.000 Btu per gallon) 0.982; and No. 6 oil (150.000 Btu per gallon) 0.956. ' , \ nonce r*i rtmrtr i/ai i ip ' GROSS OUTPUT; HUNDRED FEET STEAM RA0IATI0N . ' * . < i i i -i i -i--i" i --t--i- i "i 1 r i--i--i--i i i i i i 'i i i i--1 T-1 O 5 - 10 6 20 25 "30 '. GROSS OUTPUT-HUNORED FEET WATER RAOIATION % Fig. 23.. Gas Fuel Burning Rate Chart As the rate of fuel burning is directly proportional to the load for a. given efficiency, these charts can be extended by moving the decimal points the same number of digits in both vertical and.horizontal scales.' ' ^ 338________ __________ .CHAPTER 17 ,, - r ,. . . 1946 Guide ' The correct fuel burning rate can be determined directly -from the several charts for oil or gas burning installations, as these customarily operate on a strictly intermittent basis. These fuel burning devices usually introduce the fuel at a single fixed rate during the on periods and this rate should be sufficient to carry the gross load. In the case of coal stokers, which are usually capable of variable rates of firing, it is desirable to operate at as low a rate as weather conditions will permit, but the maxi mum firing rate of the stoker should be sufficient to carry the gross load. This rate may be determined by the same method as used for oil or gas. REFERENCES 1--Domestic Burners for Pennsylvania Anthracite (Underfeed Type), (U. S. Department of Commerce, Notional Bureau of Standards. Commercial Standard No. CS48-40). *--Stoker Manufacturers Association Manual: Industry Standards. Recommended Practices, Technical Information. Published by Stoker Manufacturers Association, 307 N. Michigan Ave., Chicago 1, III. Code for Determination of Rated Capacities of Anthracite Underfeed Stokers, adopted June 1,1944, and a Code for Determination of Rated Capacities of Bituminous Underfeed Stokers, adopted May 3, 1944. See Stoker Manufacturers Association Manual. - *--Automatic Mechanical Draft Oil Burners Designed for Domestic Installations (17. S. Department of , Commerce. National Bureau ofStandards. Commercial Standard No. CS75-42). Flue Connected Oil Burning Space Heaters Equipped with Vaporizing Pot Type'Burners (U. S. Department of Commerce, National Bureau ofStandards, Commercial Standard No. CS101-43). Warm-Air Furnaces Equipped with Vaporizing Pot-Type Oil Burners {U. S. Department of Commerce, National Bureau of Standards, Commercial Standard . No. CS(E) 104-43). . 8--Gas Floor Furnaces. Gravity Circulating Type (U. S. Department of Commerce, National Bureau of Standards, Commercial Standard No. CS99-42). f BIBLIOGRAPHY . Performance Expectancy of Domestic Underfeed Stokers for Anthracite, by Allen J. Johnson (Transactions, A.I.M.E., Coal Division, Vol'. 119, 1936). The Relation of the Size of Bituminous Coals to Their Performance on Small Under feed Stokers--Burning Tests on Four Typical Coals, by R. A. Sherman, E. R. Kaiser and H. R. Limbacher, Technical Report No. 1, Bituminous Coal Research, Inc. (July, 1937) . Part II. . Oil Fuels and Burners, by James A. Moyer (McGraw-Hill). Handbook of Oil Burning, by Harry F. Tapp. ` A Study of the Oil Burner as Applied to Domestic Heating, by Arthur H. Senner (Technical Bulletin 109, U. S. Department of Agriculture). ' . Progress in Domestic Oil Heating, by Rene J. Bender (Mechanical Engineering, October, 1942). . . * A.S.H.V.E. Research Report No. 907--Study of Performance Characteristics of Oil Burners and Low Pressure Heating Boilers, by L. E. Seeley and E. J. Tavanlar (A.S.H.V.E. Transactions, Vol. 37, 1931, p. 517). , A.S.H.V.E. Research Report No. 925--A Study of Intermittent Operation, of Oil . Burners, by.L. E. Seeley, and J. H. Powers (A.S.H.V.E. Transactions, Vol. 38, 1932,.'. p. 317). , ... Air Supply and Its Effect on Performance of Oil Burners and Heating Boilers, by L. E. Seeley, J. H. Powers and E. J. Tavanlar (A.S.H.V.E. Transactions, Vol. 39,1933, p. 75). . Study of Fuel Burning Rates and Power Requirements of Oil Burners in Relation to Excess Air, by L. E. Seeley and E. J. Tavanlar (A.S.H.V.E. Transactions, Vol. 40, 1934, p. 319). . Oil Burning in Residences, by D. W. Nelson (A.S.H.V.E. Transactions, Vol. 41, 1935, p.355). . A Study of Oil-Fired Heating Boilers, by R. C. Cross and W. R. Lyman (Heating and Ventilating, October, 1931). Combustion, American Gas Association. - - Comfort Heating, American Gas Association. ' . .. Approval Requirements of Central House Heating Gas Appliances, American Standards Association. . A Method for Determining Fuel Burning Rates in Heating Boilers Fired by Auto matic Devices, by R. C. Cross (Heating and Ventilating, January, 1932). . Heat Losses and Efficiencies of Fuels in Residential Heating, by R. A. Sh'erman and R. C. Cross.(A.S.H.V.E: Transactions, Vol. 43, 1937, p. 185).' ." CHAPTER 18 lf (fjoilerS an13,urnacei BOILERS: Construction, Types, Design Considerations,. Testing and Rating Codes, Efficiency, Rating, Selection, Space Limitations, Connections and Fittings, Erection, Operation and Maintenance. FURNACES:- Types, Materials and Con struction, Ratings, Testing and Rating Codes, Efficiency, . Design Considerations, Humidification Equipment - IN presenting the subject of Boilers and Furnaces this chapter is; divided into two parts; the first dealing with boilers and the second- treating warm air furnaces. . HEATING BOILERS Steam and hot water boilers for low pressure heating are built in a wide variety of types and sizes, many of which are illustrated in the Catalog Data Section. They are made of steel or cast-iron. CONSTRUCTION The only code governing the construction of low-pressure heating steel and cast-iron boilers that has gained recognition on a national basis is the ASME Boiler Construction Code for Low Pressure Heating Boilers. Some states and municipalities have their own codes which apply, locally but these are usually patterned after the ASME Code. The maximum allowable working pressures are limited by the ASME , Code to 15 psi for steam and 30 psi for hot water heating boilers. Hot water boilers may be used for higher, working pressures for heating purposes or for hot water supply when designed and tested for the higher, pressure. ' - TYPES OF HEATING BOILERS Heating boilers are classified in a number of different ways, such as: (n) According to materials of construction. These are steel and cast-iron. Very few non-ferrous boilers are.made. .. . ' (b) According to the fuels for which the boilers are designed. These are coal, hand fired or stoker fired; oil; gas; or wood. Some boilers are designed specifically for one fuel but many boilers are designed for more than one fuel. ' - (,c) According to the specific purpose or application for which the boiler is'used, such as space heating or domestic hot water supply. , (d) According to the design or construction of the boiler such as, sectional, round, fire-tube, water-tube, magazine feed, Scotch, etc. * . - Cast-Iron Boilers , . Cast-iron boilers are generally classified as: (a) Square or rectangular boilers with vertical sections and rectangular grates commonly known as sectional boilers! (b) Round boilers with horizontal pancake sections and circular grates. ` Cast-iron boilers are usually shipped in sections and assembled at . the place of installation. In the majority of boilers the sections are assembled . with push nipples and tie rods.. Many sectional boilers are provided with 339 . 340 CHAPTER 18 1946 Guide large push nipples at top to permit'the circulation of water between adjacent sections at both the water line and bottom of the boiler, which is necessary to enable the use of an'indirect water heater with the boiler for summer-winter hot water supply. Round and sectional boilers may be increased in size by the addition of sections and corresponding plate work. .- Capacities of cast-iron boilers range generally from capacities required for small residences up to about 12,000 sq ft of steam radiation. There are a few boilers made with'capacities-up to 18,000 sq ft of steam radia tion. For larger loads, boilers must be installed in multiple. .Steel Soflers. . - '. Steel boilers may be of the fire-tube type, in which the gases of com bustion pass through the tubes and the boiler water circulates around them, or of the water-tube type, in which the gases circulate around the .tubes and the water passes through them. ' Either the fire-tube or water-tube type may be designed with integral water jacketed furnaces or arranged for refractory lined brick.or refractory lined jacketed furnaces. Those with integral water jacketed furnaces are called portable firebox boilers and are the most commonly used type. They are usually shipped in one piece, ready for piping. Refractory furnaces are usually installed in refractory lined furnace boilers after they are set in place. .' . _: Capacities of steelboilers range from those required for small residences up to about 35,000 sq ft of steam radiation. J Boilers for Special Applications . . '= One of these is known as the magazine feed boiler developed for the bupiing of small .sizes of anthracite and coke and has a large fuel carrying capacity which results in longer firing periods than would be the case with the standard types burning coal of buckwheat size. Special atten tion must be given to proper chimney" sizes and connections when in stalling in order to insure adequate draft. . -" Boilers for hot water supply are classified as direct, if the water heated passes "through the boiler, and asindirect.if the "water heated does hot come in contact with the water or steam in the boiler: - : ; Direct healers are built to operate at the pressures found in city supply mains and are tested at pressures from 200 to "300 lb per square inch. The .life of direct heaters depends almost entirely on the scale-forming properties of the water supplied and the temperatures maintained. If low water temperatures are maintained the life of the heater will be much longer due to decreased scale formation and minimized corrosion. . Direct water heaters in some cases are designed to burn refuse and garbage. Indirect heaters generally consist of steam boilers in connection with heat exchangers of the coil or tube types which transmit the heat from the steam to the water. This type of installation has the following advantages: 1. The boiler operates at low pressure. ` 2. The boiler is protected from scale and corrosion. -- _ 3.- The scale is formed in the heat exchanger in which the parts to which the scale is attached can be cleaned or replaced. The accumulation of scale does not affect efficiency although it will affect the capacity of the heat exchanger. 4. Discoloration of water may be prevented if the water supply comes in contact with only non-ferrous metal. " Heatine Boilers and Furnaces_________ - ';341 Where a steam or a forced circulation hot water heating system is installed, the domestic hot water may be heated by ah indirect heater attached to the boiler. For most satisfactory performance in the steam system, this heater is placed just below-the water line of the boiler. In a forced circulation hot water system, it should .be located as high as possible with respect to the boiler. ; BOILER DESIGN CONSIDERATIONS Furnace Design . ... Good efficiency and proper boiler performance are dependent bn correct furnace design. There must be sufficient volume for burning the particular fuel which is used, and means to obtain a thorough mixing of air and gases at a high temperature and. at a velocity low enough to permit complete combustion of all the volatiles. For hand fired boilers, the furnace volume should be large enough to hold sufficient fuel for reasonably long firing periods.. (See Chapters 16 and 17.) . . Heating Surface .. " Boiler heating surface is that portion of the surface.of the heat transfer apparatus in contact with the fluid being heated on one side and the gas or refractory being cooled on.the other side. Heating surface on which the fire shines is known as direct or radiant surface and that in contact with hot gases only, as indirect or convection surface., The amount of heating surface, its distribution, and the temperatures on. either side thereof influence the capacity of any boiler.. . "; . .- ", Direct heating surface is more valuable, than indirect per square foot because it is subjected to a higher temperature and. also, in the case of solid fuel, because it is in position to receive the full radiant energy of the fuel bed. The effectiveness of the heating surface depends on its cleanliness, its location in the boiler, and the shape of the gas passages. The area of the gas passages must not be so small as to cause excessive resistance to the flow of gases where natural draft is employed. Inserting baffles so that the heating surface is arranged in series with respect to the gas flow increases' boiler efficiency and reduces stack temperature, but increases the draft loss through the boiler....................... Heat Transfer Rate ...................... . Practical-heat transfer rates in heating boilers expressed in Btu absorbed per square foot of surface per hour will average about 3300 for hand fired boilers and 4000 for mechanically fired boilers when operating at design load. ' When mechanically fired boilers are operating at maximum load as defined in this chapter under heading Selection of Boilers, these values will run between 5000 and 6000." Boilers operating under favorable conditions at'these heat transfer rates will-give exit gas temperatures that are considered consistent with good practice, although there are boilers which have high efficiencies and. also operate at higher trans mission rates. " - TESTING AND RATING CODES The Society has adopted four "solid fuel testing codes, a solid fuel rating code and an oil fuel testing code. ASHVE Standard and Short Form Heat Balance Codes for Testing Low-Pressure Steam Heating Solid Fuel Boilers--Codes T and 2-- / 342 CHAPTER IS .1946'Guide (Revision of June, 1929) \ are intended to provide a method for con: ducting and reporting tests to determine heat efficiency and performance characteristics. ' ASHVE Performance Test Code for Steam Heating Solid Fuel Boilers --Code No. 3--(Edition of 1929)1 is intended for use with ASHVE Code for Rating Steam Heating Solid Fuel Hand-Fired Boilers *. The object of this test code, is to specify the tests to be conducted and to provide a method for conducting and reporting tests to determine the efficiencies and performance of the boiler. The ASHVE Standard Code for Testing Steam Heating Boilers Burn ing Oil Fuel *, (Adopted June, 1932), is intended to provide a standard method for conducting and reporting tests to determine the heating efficiency and performance characteristics when oil fuel is used with steam heating boilers. , In 1938 the Society adopted a Standard Code for Testing Stoker-Fired Steam Heating Boilers4, (Adopted June, 1938), which is intended to provide a test method for determining the efficiency and performance characteristics of any stoker and boiler combination burning any type of solid fuel such as anthracite or bituminous coal. The Steel Boiler Institute, Inc. has adopted (June J2, 1945) a Rating Code for Commercial Steel Boilers and Residential Steel Boilers and for -Testing' Oil-Fired Residential Steel Boilers. The commercial boilers (defined as those having 129 to 2500 sq ft of heating surface) are rated in square feet (steam) on the basis, of heating surface with limitations set for grate area, furnace volume and furnace height. The residential boilers (defined as those having not more than 177 sq ft of heating surface) are rated on tests for oil-fired boilers, with limitations in relation to heat . ing surface and testing conditions. Stoker-fired and gas-fired residential boilers are rated (SBI Net Rating) not in excess of the oil-fired rating. Hand-fired residential boilers are rated (SBI Net Rating) not greater than 14 times the heating surface. .' Tables 1 and 2 show the SBI ratings of residential and commercial steel boilers respectively. . ' ' '. , Table 1. SBI Net Rating Data for Residential Steel Boilers--Oil Fired* SBI Net Rating . Sq Ft Steam 275 . . 320 400 550 ' 700 900 . 1100 1300 1500 1800 2200 2600 3000 Sq Ft Water 440 510 640 880 1120 1440 . 1760 2080' 2400 2880 3520 4160 4800 . Btu 66000 77000 .96000 132000. 168000 216000 264000 312000360000 432000 528000 624000 .720000 Minimum Furnace ' Volume Cu Ft Heating Surface Sq Ft X 2.5 2.9 . 3.6 5.0 6.4 ,, 8.2 10.0 . 11.8 13.6 16.4 20.0 . 23.6 . 27.3 16 ' 19 24 32 41 53 65 77 88 106 129 153 177 ' 1 StoIter-fired and Gas-fired SBI Net Rating not greater than Oil-fired. Hand-fired, SBI Net, Rating (Steam) not greater than 14 times the square feet of heating surface. - Heating Boilers and Furnaces ,343 , iMin* rSrGAmqutaetFaem .ItS.O.tuelnP8.atem8.itRte..onP.uraSnmI I ' 1 ffl 1 ' COrOtO co co id4 ^ t*4 t#4 id4-"d4 id* tCCOO 'O'O' COC ''00 oOOOOO OOoOoO COOOO t-^COO* io-^-h 1-H 1-H Ce1-MsH ro 1-4 iid-H4 'O 1-4 o-hOiOdilNd ' IOoo Ono-d* o 1--1 CM 04 CN CN CO feON^N-cnMHr--i . fO CO TT 4.000. 000 5.000. 000 6.000. 000 7,000,000 16,700 2.500.000 20,000 3,000,000 23.330 3.500.000 9.330 1.400.000 11.330 1.700.000 13.330 2,000,000 6.000 900,000 6.670 1,000,000 8,000 1,200,000 600.000 700.000 800.000 360.000 439.000 521.000 26.670 33.330 40,000 46.670 9 -m 3 *s- 4.000 4.670 5.330 2,400 2,930 3,470 Sq tF tWaer 5 e eo 1 Si ' 0QO(^ON Th oi-T- " . OOCON (OO' oTcvTco" rOI--O--ON< QO crT^wf ' COoOoOOoO wOCO ineCco - --(OTNjIicO-iOHon'iWtOi-d*t4' fOv--4tOCoONo`QcOwmfONe--shT ' w p9a 11,200 1.680.000 13,600 2.040.000 16,000 2.400.000 7,200 1,080,000 8,000 1,200,000 9.600 1.440.000 720.000 840.000 960.000 432.000 528.000 624.000 1 4,800 5.600 6,400 2,880 3,520 4,160 Sq tF tWaer w (2 5 to 4.800.000 6.000. 000 7.200.000 8.400.000 32.000 40.000 48.000 56.000 12.500 20,000 3.000. 000 15.000 24.000 3.600.000 17.500 28.000 4.200.000 20.000 25.000 30.000 35.000 7,000 8.500 10,000 4.500 5.000 6.000 3.000 3.500 4.000 1,800 2,200' 2,600 Sq tF tSeam T a b l e 2. S B I R a t in g s f Or C o m m e r c ia l St e e l B o ile r s 4.800.000 6.000. 000 7.200.000 8.400.000 Hetaing iMin ' iMin Sruface mum mum 8q tF Furnace Furnace Vloume Hiegth* jCu tF I .n C1-S454-0400 o1-4o0 *ICoHM ICOM5MC0N rCsM tooo OCSv 400'o0Oor----o1 wOO5cti---nTICo-OM4"_. aCMoOOwId" o' < i-Tcm"cm- 4CM0 COMO xOCM' xOCMlCOOOxCO -x.C1-O4x1C--OxCCOM TCOt" 4x00 CC-Oxx^<04"<d- xOOxIldO"vxOO5O -t11--^0> cO1-vs4 \CCqMM .CM15-04COtJ" 00 C^O CO5 CidO4 4CM0 o"OootC--Ooo>OqQ0 O1-oO4cCO1Os-41o4-~o404 iCt1o--O-4c"4COv-NMc0COoM4CCOO 7,200 1,080,000 8,000 1,200,000 9.600 1.440.000 4,800 ' 720,000 5.600 , 840,000 6,400 , 960,000 432.000 528.000 624.000 2,880 3,520 4,160 4,500. 5.000, 6.000. ' 8q tF 1 tWaer E6 :3c el a0 'z 5j. <C5Q , 1 su 1 OO1CQ m- 32.000 40.000 48.000 56.000 20.000 25.000 30.000 35.000 3.643.000 12.500 20,000 3.000. 000 4.373.000 15.000 24.000 3.600.000 5.100.000 17.500 28.000 4.200.000 2.040.000 7.000 .11,200. .1,680,000 2.479.000 8.500 13,600 2.040.000 2.916.000 10,000 16,000 2.400.000 `Bituminous Stoker Fired. 5.830.000 7.286.000 8.743.000 10,200,000 1.313.000 1.459.000 1.750.000 876.000 ' 3,000 1,020,000 3.500 1,166,000 4.000 3,500. 526.000 1,800 4,280 643^000 2,200 5,050 . 758,000 I 2,600 38,860 48,570 ,58,280 68.000 24,280 29,150 34.000 13,600 16,520 19,440 8,750 9,720 11,660 ' 5,840 6,800 7,770 Sq tF ; tWaer SBI Rtaing |- 1c-n^\ ONeOs 1c-oH.-I"OOCMIOCO>0- Tjt"-- CCO^CM\ ^' I0O0^C1OCO-1O^ci1i-m-hoH"^ - OC1-O^CCMM CtoM 0C\N0COcIqd5" 10' `i-Hcf0i-1 CM0C^MCO'COeids"'1 - .344 CHAPTER IS ' 1946 Guide The Institute of Boiler. and. Radiator Manufacturers has adopted a method of rating cast-iron, heating boilers based upon performance obtained under tests. This code6 now applies to sectional boilers having a grate width of 41 in- or less. Eventually the Institute intends to include all sizes of cast-iron boilers in this program of testing and rating. ' The American Gas Association has adopted a method of rating gas designed boilers based upon performance under tests. This is described in Approval Requirements for Central Heating Gas Appliances. The Heating, Piping and Air Conditioning Contractors National Aj- sociation has adopted' a method of rating boilers based on their physical characteristics for those boilers that are not rated in accordance with the SBI or I=B=R Codes. Ratings are expressed on a Net Load .basis in square feet-of steam radiation. > '; BOILER EFFICIENCY . : | The term efficiency as used for guarantees of boiler performance is usually construed as follows: ' 1. Solid Fuels. The efficiency of the boiler alone is the ratio of the heat absorbed by the water and steam in the boiler per pound of combustible burned on the grate to the " calorific value of 1 lb of combustible as fired. The combined efficiency of boiler, furnace and grate is the ratio of the heat absorbed by the water and steam in the boiler per, pound of fuel as fired to the calorific value of 1 lb of fuel as fired. ` 2. Liquid and Gaseous Fuels. The combined efficiency of boiler, furnace and burner is the ratio of the heat absorbed by the water and steam in the boiler per pound of cubic foot of fuel to the calorific value of 1 lb or cubic foot of fuel respectively. ! The following efficiencies apply to current designs of boilers operated under favorable conditions at their gross output ratings. Some older boilers designed primarily for hand firing may. have lower efficiencies when automatically fired. . :' ' ii Anthracite, hand fired_...... Bituminous Coal, hand fired Stoker fifed...... ......................... Oil and Gas fired------- ----------- 60 to 75 per cent 50 to 65 per cent 60 to 75 per cent 70 to 80 per cent ` Higher efficiencies for hand fired bituminous coal may be obtained by careful firing of either a regular or a smokeless boiler.; * ` ; RATING OF BOILERS --! : i I In deferring to boiler rating it is necessary to know; the basis on jwhich the rating has been established in order to understand the exacjt meaning of the term. The following example will illustrate the 'meaning, ofj three ratings which might be established for the same boiler. j .: \ ` Assume that an installation has the.following loads determined, in accordance with the section Selection of Boilers: 11! Net Load..................... .................................. -............ Piping Tax.______........................ :........................... -1 Design Load...... ............................. ................. -....... Pickup Allowance............... ............... :...................... Maximum or Gross Load.........................-...... -- 1000 sq ft of steam radiation 200 sq ft of steam radiation 1200 sq ft of steam radiation 240 sq ft of steam radiation 1440 sq ft of steam radiation A boiler that is just large enough to carry this system might be said to have a net load rating of 1000 sq ft, a design load rating of 1200. sq ft, or a gross load fating of 1440 sq ft, depending on the basis on which the boiler is rated. : HeatinS Boilers and Furnaces 345 On a neiload basis the above boiler wouid'be rated 1000 sq ft of steam radiation and would have sufficient excess'capacity to supply'the normal piping and pickup load. Net I = B = R Ratings, SBI Net Ratings, and Net Load Ratings of the Heating, Piping and Air Conditioning Con tractors National Association are established on this basis-,. .. On a design load basis the boiler would be rated 1200 sq ft of steam radiation and would have sufficient excess capacity to supply the pickup loadx It would be of adequate size for a system in which the sum of the net load and the piping heat loss did not exceed 1200 sq ft of steam radi-: ation. The SBI Ratings shown in columns 1, 2, 3, 10; 11 and 12 of Table 2 (not to be confused with SBI Net Rating) are established on a design load basis. . '' On a gross output basis of rating the boiler would be rated 1440 sq ft of steam radiation and would be of adequate size for a system in which the sum of the net load, piping load, and pick-up load did not exceed 1440 sq ft of steam radiation. Gross I=B=R Output and A.G.A. Ratings are established on a gross output basis: . In the determination of boiler ratings, the Gross Output is the quantity of heat available at the boiler nozzle with the boiler normally insulated: and when operating under limitations stipulated in the code or method by which the boiler is rated. The boiler may. be capable of producing a- greater nozzle output but in doing so would exceed some of these limitations. . SELECTION OF BOILERS Factors Involved in Boiler Selection The Maximum Load or Gross Load on the boiler is the sum of the four following items. The Design Load is the sum of items 1, 2 and 3. The Net Load is the sum of items 1 and 2. 1. Radiation Load. The estimated heat emission in Btu per hour of the connected radiation (direct, indirect, or forced convection coils) to be installed, . The connected radiation is determined by calculating the heat losses for each room in accordance with data given in Chapters 6, 8. and 14. The sum of the calculated heat losses for all the rooms represents the total required, heat emission of the connected radia tion expressed in Btu per hour. As practically all boilers are now rated on a Btu basis, it is unnecessary to convert the radiation load to equivalent square feet of equivalent radiation. -- ' . 2. Hot Water Supply Load. The estimated maximum heat in Btu per hour required ' to heat water for domestic use. When the hot water supply is heated by the building heating boiler, this load must be.taken into consideration in.sizing the boiler. A common practice is to add 240 Btq per hour to the radiation load for each gallon of storage tank capacity. For more specific information see Chapter 50. 3. Piping Tax. The estimated heat emission in Btu per hour of the piping con necting the radiation and other apparatus to the boiler. As the heating industry as a whole is not entirely agreed upon piping tax allowances for different sizes of installations it is better to compute the heat emission from both bare and covered pipe surface in accordance with data in Chapter 28. In average house heating systems, it is common practice to consider the piping tax to be equal to 25 per cent of the Net Load. In determining Net I=B=R Ratings from Gross I--B--R Output, the piping factor allowed varies from 30 per cent for small boilers to 12 per cent for larger boilers. '` 4. Warming-Up or Fick-Up Allowance. The estimated increase in the normal load in Btu per hour caused by the heating up of the cold system. The warming-up allowance represents the load due to heating the boiler and contents 346 CHAPTER 18 1946 Guide ' to operating temperature, and heating up cold radiation and piping.. The factors to be used for determining the allowance to be made should be selected from Table 3. Other items to be considered in boiler selection are: (a) Efficiency with hard or'soft coal, gas, or oil firing, as the case may be. . (6) Grate area-with hand-fired coal, or fuel burning rate with stokers, oil, or gas. ' (c) Combustion space in the furnace. '1 (d) Type of heat liberation, whether continuous or intermittent, or a combination of both. - (e) Convenience in firing and cleaning. -' (/) Adaptability to changes in fuel and kind of attention. (g) Height of water line. (A) Miscellaneous items such as draft available, possibility of future extension, pos sibility of break-down, and head room in the boiler room. (i)The most economical size of boiler is usually one that is just the right size for the load. Either larger or smaller boilers may be less economical. * Selection of Cast-Iron Boilers - Net load ratings of cast-iron boilers are usually available from manu facturers' catalogs. They may also be obtained conveniently from published tables of I=B = R ratings6, or from recommendations of the Heating, Piping and Air Conditioning Contractors National Association7 and can be used in selection of boilers, unless the heating system contains an unusual amount of bare pipe, or the nature of the connected load is such that the normal allowances for pipe loss and pick-up do not apply. In such a case, the selection must be based on the gross output. Selection of Steel Heating Boilers ' SBI catalog ratings in accordance with the previously mentioned Steel Boiler Institute, Inc. code are intended to correspond with the estimated design load. When the heat emission of the piping is not known, tjie net load to be considered for the boiler may be determined from Tables 1 and. 2.The difference between design load and net load represents an amount which is considered normal for piping loss of the ordinary heating system. Boilers with less than 177 sq ft of heating surface and having SBI net ratings .'(steam) of not more than 3,000 sq ft if mechanically fired and Table 3. Warming-up Allowances for Hand-Fired Low-Pressure Steam . and Hot Water Heating Boilers a-b-c i.Design Load (Representing Summation or Items 2. and 3) Bto per Hour Equivalent Square Feet of Radistiond - Percentage Capacity to Aod roB Warming-Up Up to 100,000 100,000 to 200,000 200,000 to 600,000 600,000 to 1,200,000 1,200,000 to 1,800,000 ' Above 1,800,000 Up to 420 420 to 840 840 to 2500 2500 to 5000 5000 to 7500 Above 7500 . 65 60 55 50 45 40 "This table is taken from the A.S.H.V.E. Code of Minimum Requirements for, the. Heating and Venti lation of Buildings, except that the second column has been added for convenience in interpreting the design load in terms of equivalent square feet of radiation. * ,* bSee also Time Analysis in Starting Heating Apparatus, by Ralph C. Taggart (A.S.H.V.E. Transac tions. Vol. 19.1913, p. 292); Report of A.S.H.V.E. Continuing Committee on Codes for Testing and RatingSteam Heating Solid Fuel Boilers (A.S.H.V.E. Transactions. Vol. 36. 1930, p. 35); Selecting the Right Size Heating Boiler, by Sabin Crocker (Heating, Piping and Air Conditioning, March. 1932). Tliis table refers to hand-fired, solid fuel boilers. A factor of 20 per cent over design load is adequate when automatically-bred fuels are used. ' - - .... ` d240 Btu per square foot. ', Tfmtine Boilers and Furnaces________ ________ .' : '_______ 347 2 480 sq ft if hand fired, are classified as residence size. An insulated residence boiler for oil, gas or stoker firing may carry a net load expressed in square feet of steam radiation of not more, than 17 times the square- feet of heating surface in the boiler, provided the boiler has been tested in accordance with the SBI Code for Testing Oil-Fired Steel Boilers at output rates of 125, 150 and 175 per cent of the SBI Net Rating. The SBI Net Rating (square feet steam) for hand-fired residence boilers is not greater than 14 times the heating surface. If the heat loss from the piping system exceeds 20 per cent of the installed radiation, the excess is to be considered sis a part of the net load. ' Selection Based on Heating Surface and Grate Area. - Where neither the net load nor gross output ratings based upon per formance tests are available, a good general. rule' for conventionally designed boilers is to provide 1 sq.ft of boiler heating surface for each 14 sq ft of equivalent radiation (240 Btu per square foot) represen ted by the design load. This is equivalent to allowing 10 sq ft of boiler heating surface, per boiler horsepower. In this case it is assumed that the maxi-, mum load including the warming-up allowance will be provided for by operating the boiler in excess of the design load, that is, in excess of the 100 per cent rating on a boiler-horsepower basis. SBI ratings for hand firing are based on 10 sq ft of heating surface per boiler horsepower. Due to the wide variation which may be encountered in manufacturers' ratings for boilers of approximately the same capacity, it is advisable to check the grate area required for heating boilers burning solid fuel by means of the following formula: ' ' f _____ H- . - - CX FXE . ... v' where G = grate area, square feet. '. H -- required gross output of the boiler, Btu per hour (see Selection of Boilers). C = desirable combustion rate for fuel selected, pounds of dry coal per square foot - of grate per hour (see Table 4). .' F = calorific value of fuel, Btu per pound. 1 .. E = efficiency of boiler, usually taken as 0.60. Example 1. Determine the grate, area for a required gross output of the boiler of 500,000 Btu per hour, a combustion rate of.6 lb per hour, a calorific value of 13,000 Btu per pound, and an efficiency of 60 per cent. '' . ;' 500,000 6 X 13,000 X 0.60 10.7 sq ft The boiler selected should have a grate area not less than that deter mined by Equation 1. With small boilers, where it is desired to provide sufficient coal capacity for approximately an eight-hour firing period plus a 20 per cent reserve for igniting a new charge,' more grate area may be required depending upon the depth of the fuel pot. . . Selection of Gas-Fired Boilers . After determining the net load for the installation, gas designed boilers can usually be selected from manufacturers' tables of net load ratings which are based on piping and pickup allowances varying from 56 per cent for boilers of 200 sq ft and less to 35 per cent for boilers of 4000 sq ft and larger. If the '.piping and pickup load or other factors create an unusual load, a boiler should be selected which has an A.G.A. 348 CHAPTER 18 . 1946 Guide output rating equal to the maximum output required. Detailed'recom mendations for selection of gas designed boilers are given in the A.G.A. publication, Comfort Heating. . SPACE LIMITATIONS Boiler rooms should, if possible, be situated at a central point with respect to the building and should be designed for a maximum of natural light. The space in front of the boilers should be sufficient for firing, stoking, ash removal and cleaning or renewal of flue tubes, and should be at least 3 ft greater than the length of the tubes. A space of at least 3 ft should be allowed on at least one side of every boiler for convenience of erection and for accessibility to the various dampers, cleanouts and trimmings. The space at the rear of the boiler should be ample for the chimney connection and for cleanouts. With large boilers the rear clearance should be at least 3 ft in width. The boiler room height should be sufficient, for the location of boiler accessories and for proper installation of piping. In general the ceiling height for small steam boilers should be at least 3 ft above the normal boiler water line. With vapor heating, especially, the height above the boiler water line is of vital importance. . When steel boilers are used, space should be provided for the removal and replacement of tubes.. , CONNECTIONS AND FITTINGS Steam outlet connections should be the full size of the manufacturers' tappings in order to keep the velocity of flow through the outlet reasonably Table 4. Practical Combustion Rates for Coal-Fired Heating Boilers Oper ating at Maximum Load on Natural Draft of from J's iN. to pi in. Water Kind of Coal No. 1 Buckwheat Anthracite Anthracite Pea - Sq Ft Grate Lb op Coal per Sq Ft : . Grate per Hour ' . Up to 4 5 to 9 10 to 14 15 to 19 20 to 25 :i. 3J4 4 4H 5- \ Up to 9' . 10 to 19 20 to 25 5 6 Anthracite Nut and Larger . ' Up to 4 5 to 9 10 to 14 15 to 19 20 to 25 '* 8 9 10 11 13 . :. Bituminous... - Up to 4 , 5 to 14 ' 15 and above 9.5 12 15.5 . . . "Steel boilers usually have higher combustion rates for grate areas exceeding 15 sq ft than those indicated in this' table. ... '` Heating Boilers and Furnaces 349 low and to avoid fluctuation of the water line aind undue entrainment of moisture, and should extend vertically to the maximum height available above the boiler. A steam velocity in boiler outlets not exceeding 25 to 30 fps at maximum load is recommended unless data are available to show that a higher velocity is satisfactory. Particular attention should be given to fitting connections to secure con formity with the ASME Boiler Construction Code for Low Pressure Heating Boilers. Attention is called in particular to pressure gage piping, water gage connections and safety valve capacity. . Where a return header is used on a cast-iron sectional boiler to distribute the returns to both rear tappings, it is advisable to provide full size plugged-tees instead of elbows, where the branch connections enter the return tappings. This facilitates cleaning sludge from the bottom of the boiler, sections through the large, plugged openings. An equivalent clean out plug should be provided in the case of a single return connection. Blow-off or drain connections should be made near the boiler and so arranged that the entire system may be drained of water by opening the drain cock. In the case of two or more boilers separate blow-off connec tions must be provided for each boiler on the boiler side of the stop valve on the main return connection. '- Water service-connections must be provided for both steam and water boilers, for refilling and for the addition of make-up water to boilers. This connection is usually of-galvanized steel pipe, and is made to the return main near the boiler or boilers. ,. For further data on pipe connections, for steam and hot water heating systems, see.Ohapter 23 and 24 and the ASME Boiler Construction Code for Low Pressure Heating Boilers. '- . . Smoke Breeching and Chimney. Connections.- The-breeching or smoke pipe from the boiler outlet to the chimney should be air-tight and as short and direct as possible, preference being given to long radius and 45-deg instead of 90-deg Lends. The breeching entering a brick chimney should not project beyond the flue lining and where practicable it should be grouted from the inside of the chimney. - A. thimble, or sleeve usually is provided where the-breeching enters a bHck chimney.. . Where a .battery of boilers is connected into a breeching each boiler should be provided with a tight damper. The breeching for a battery of boilers should not be reduced in size, as it goes to the more remote boilers. Good connections made to. a good chimney will usually result in a rapid response by the boilers to demands for heat. ERECTION. OPERATION. AND MAINTENANCE The directions of the boiler manufacturer should always be read before the assembly or installation of any 'boiler is started, even though the contractor may be familiar with the boiler.' . All joints requiring boiler putty or cement which cannot be reached after assembly is complete must be finished as the assembly progresses." " ' " Five precautions that should be taken in all installations to prevent damage to the boiler are: .. . 1.-There should be provided proper and convenient drainage connections-for use if the boiler is not in operation during freezing weather.! ' ' 2. Strains on the boiler due to movement of piping during expansion should be 350 CHAPTER 18 1946 Guide . ' prevented by suitable anchoring of piping and by proper provision for pipe expansion and contraction. .* * 3. Direct impingement of too intense local heat upon any part of the boiler surface, as with oil burners, should be avoided by protecting the surface with firebrick or other refractory material. 4. Condensation in steam systems must flow back to the boiler as rapidly and uni formly as possible. Return connections should prevent the water from backing out of the boiler. . 5. Automatic boiler feeders and low water cut-off devices which shut off the source of heat if the water in the boiler falls below a safe level are recommended for mechanically fired boilers. . Boiler Troubles A complaint regarding boiler operation generally will be found to be due to one of the following: ' 1. The boilerfails to deliver enough heat. The cause of this condition may be: (o) poor draft; (b) poor fuel; (c) inferior attention or firing; (d) boiler too small; (e) improper piping; (f) improper arrangement of sections; (g) heating surfaces covered with soot; (&) insufficient radiation installed; and (*) with mechanical firing, fuel burning equip ment too small. # 2. The water line is unsteady. The cause of this condition may be: (a) grease and dirt in boiler: (6) water column connected to a very active section and, therefore, not showing actual water level in boiler; and (c) boiler operating at excessive output. 3. Water disappears from gage glass. This may be caused by: (a) priming due to grease and dirt in boiler; (&) too great'pressure difference between supply and return piping preventing return of condensation; (c) valve closed in return line; {d) connection of bottom of water column into a very active section or thin waterway; and (e) improper .connections between boilers in battery permitting boiler with excess pressure to push returning condensation into boiler with lower pressure. , 4. Water is carried over into steam main. This, may be caused by: (a) grease and dirt * . in boiler; (6) insufficient steam dome or too small steam liberating area; (c) outlet con-, sections of too small area; (d) excessive rate of output; and (e) water level carried higher than specified. . 5. Boiler is slow in response to operation of dampers. This may be due to: (a) poor draft resulting from air leaks, into chimney or breeching; (6) inferior fuel; (c) inferior attention; (d) accumulation of clinker on grate; and (e) boiler too small for the load. 6. Boiler requires too frequent cleaning of flues. This may be due to: (a) poor draft; (6) smoky combustion; (c) too low a rate of combustion; and (d) too much excess air in firebox causing chilling of gases. .. - 7. Boiler smokes through fire door. This may be due to: (a) defective draft in chimney . or incorrect setting of dampers; (6) air leaks into boiler or breeching; (c) gas outlet from firebox plugged with fuel; (d) dirty or clogged flues; and (e) improper reduction in ' breeching size. ` -. 8. Low carbon dioxide. This may be due on oil burning boilers to: (a) improper ad- i'ustment of the burner; (b) leakage through the boiler setting; (c) improper fire caused. iy a fouled nozzle; or (d) to an insufficient quantity of oil being burned. Cleaning Boilers All boilers are provided with flue dean-out openings through which the . heating surface can be reached by means of brushes or scrapers. Flues of solid fuel boilers should be cleaned often to keep the surfaces free of soot or ash. Gas boiler flues and burners should be cleaned at least once a year. Oil burning boiler flues should be examined periodically to deter . mine when cleaning is necessary. The grease used to lubricate the cutting tools during erection of new piping systems serves as a carrier for sand and dirt, with the result that a scum of fine particles and grease accumulates on the surface of the water in all new boilers, while heavier partides may settle to the bottom of the boiler and form sludge. These impurities tend to cause foaming, preventing the generation of steam and causing an unsteady waterline. Heating Boilers and Furnaces 351 This unavoidable accumulation of oil and grease'should be removed by blowing off the boiler as follows: If not already provided, install a surface blow connection of at least \]/i in. nominal pipe size with outlet extended-to within 18 in. of the floor or to sewer, inserting a valve in line close to boiler. Bring the water line to center of outlet, raise steaim pres sure and while fire is burning briskly open valve in blow-off line. When pressure recedes, close.valve and repeat process adding water at intervals to maintain proper level. As a final operation bring the pressure in the boiler to about 10 lb', close blow-off, draw the fire or stop burner, and open drain valve. After boiler has cooled partly, fill and flush out several times before filling it to proper water level for normal service. The use of soda, or any alkali, vinegar or any acid is not recommended for cleaning heating boilers because of the difficulty, of complete removal and the possibility of subsequent injury, after the cleaning process has been completed. Insoluble compounds have been developed which are effective,, but special instructions on the proper cleaning compound and directions for its use in a boiler, as given by the boiler manufacturer, should be carefully followed. Care of Idle Heating Boilers . Heating boilers are often seriously damaged during summer months due chiefly to corrosion resulting from the combination of sulphur from the fuel with the moisture in the cellar air. At the end of the heating season the following precautions should be taken: - 1. All heating surfaces should be cleaned thoroughly of soot, ash and residue, and the. heating surfaces of steel boilers should be given a coating of lubricating oil on the fire side. 2. All machined surfaces should be coated with oil or grease. 3. Connections to the chimney should be cleaned and in case of small boilers the pipe should be placed in a dry.place after cleaning. . 4. If there is much moisture in the boiler room, it is desirable to drain the boiler to prevent atmospheric condensation on the heating surfaces of the' boiler when they are below the dew-point temperature. Due to the hazard that some one may inadvertently build a fire in a dry boiler, however, it is safer to keep the boiler filled with water, par ticularly in residential installations. Air caii be excluded from a steam boiler by raising the water level into the steam outlets. A hot water system usually is left filled to the expansion tank. ... ' -- , ' 6. The grates and ashpit should be cleaned. ' .' - 6. Clean and repack the gage glass if necessary. 7. Remove any rust or other deposit from exposed surfaces by scraping with a wire brush or sandpaper. After boiler is thoroughly cleaned, apply a coat of preservative paint where required to external parts normally painted. ' 8. Inspect all accessories of the boiler carefully to see that they are in good working order. In this connection, oil all door hinges, damper bearings and regulator parts. WARM AIR FURNACES , Warm air heating: furnaces of a number of types and a wide range of sizes are listed and illustrated in the Catalog Data Section. TYPES OF FURNACES Warm air furnaces may be classified in several different ways: a. According to method of heat distribution--these are either gravity or mechanical . (blower) furnaces. '' 352 CHAPTER 18 ' 1946- Guide b. According to fuels for which the furnaces are designed - these are coal hand-fired or stoker-fired, oil, gas, or wood. . . '. c. According to .materials of construction--they are cast-iron, low carbon steel, and occasionally high temperature steel alloys. ' .. . d. According to design or construction, such as drum and radiator, tubular, hori zontal, etc. ' Gravity Warm Air Furnaces A gravity furnace is one in which the motive head producing air flow' depends upon the difference in density between the heated air leaving the top of the casing and the cooled air entering the bottom of the casing. Since this gravity head is relatively low, the furnace must have low in ternal resistance to the flow of air and relatively large areas must be available for free circulation within the furnace casing. It is common practice to provide approximately 50 per cent free air area through gravity type furnaces. . Furnaces for gravity type systems are available in designs suitable for. central heating, pipeless furnace, or unit floor furnace installations. Booster fans are sometimes used in conjunction with gravity design systems, to increase air circulation. Where a fan is to be used with a furnace casing sized for gravity air flow, some form of baffling must be employed to restrict the free area within the casing and to force impinge ment of the air against the heating surfaces. Where square casings are used, the corners must be baffled. -. Mechanical Warm Air Furnaces Mechanical or forced warm air furnaces include fans or blowers as ' integfal parts for the purpose of circulating the air and usually includeair filters. .. ,. Fans and Motors ;. Centrifugal fans with either backward or forward curved .blades are the type most commonly used. Motors may be mounted on the' fan- shaft or connected to the fan by a belt-drive. Adjustable pulleys aiej desirable to provide means of regulating the quantity of air distributed! to the heated spaces. Either the, motor load or the noise, may limit the- maximum operating fan speed. Two-speed motors have given successful operating results and are recommended.-. Motors and mountings must be carefully selected for quiet operation. Electrical conduit and water piping must not be fastened to, nor make contact with' the fan housing. . . -- . - . \ ' .- Filters . , Several types of filters, are. available for mechanical warm air furnace applications and are.discussed in Chapter 33. 'For maximum efficiency^ and life under operating conditions, filters should not be subjected to a temperature in excess of 150 F. Filters should have at least 80 per cent average efficiency on an 8-hr test at a maximum resistance of 0.25 in. of water. Filter resistance rises rapidly with the accumulation of dirt, and may reduce the air circulation over heating surfaces. In domestic furnaces, the maximum velocity, based on nominal filter area, should not exceed 300 fpm. .- . Fuel Utilization . '. ,A combustion rate of from 5 to 8 lb of coal per (square foot of grate) (hour) is recommended for residential furnaces* A higher combustion / Heating Boilers and Furnaces' 353 rate is!permissible with larger furnaces for buildings other than residences,. depending upon the.ratio of grate surface to heating surface, firing period, and available draft. . In residential furnaces for coal burning, the ratio of heating surface to grate area will average about 20 to 1; in commercial sizes the ratio may be as high as 50 to l-, .depending on fuel and draft. Furnaces may be installed singly, each furnace with its own fan, or in batteries of a number of furnaces, using one or more fans. . Where oil fuel is used, care must be exercised in selecting the proper size and type of burner for the particular size and type of furnace used. . Furnaces for burning oil fuel are usually designed for blow-through installations so that the pressure in the,air space is higher than that in the combustion chamber or flues. The National Warm Air Heating and - Air Conditioning Association has prepared a Tentative Code for Testing and Rating of Oil-Fired Furnaces. Compact fan-furnace-burner units are available, suitable for basement, closet, or even attic installations. ; Gas fired forced air furnaces should conform in construction and performance to A.G.A. Approval Requirements. Heavy Duly Fan Furnaces " Fan furnaces for large commercial and industrial buildings, churches, schools, etc., are available in sizes ranging from 300,000 to 3,000,000 Btu per (hour) (unit).' Heavy duty furnace heaters may be arranged in battery combinations of one or more units. " Most manufacturers of heavy duty furnaces rate their furnaces in Btu per hour and also in the number of square feet of heating surface. Con servative practice indicates that at no time in the heating-up period should the furnace surface be required to emit more than an average of 3500 Btu per square foot. A higher rate of heat emission tends to increase . the heat loss, up the chimney, and raise fuel consumption, to shorten the life of the furnace, and to overheat the air. The ratio of heating surface to grate area of furnaces for this type of work should never be less than 30 to 1 and as indicated previously may run as high as 50 to 1. - Control of temperature is secured through (1) controlling the quantity of. heated, air entering the room, (2) using mixing dampers, or (3) regulafing the, fuel'supply. The design of heavy duty fan furnace heating systems is in many respects similar to that of .the central fan heating systems described in* Chapter 43. Ducts are designed by the method outlined in Chapter 4L - MATERIALS AND CONSTRUCTION ;: Cast-Iron Furnaces . - Cast-iron furnaces are made in a multiplicity of designs or shapes. For solid fuels they are generally of round sectional construction, the sections being cemented or bolted together. Various types of radiators for.second- ary convection heat transfer are employed. Such radiators are of the circular, doughnut type, or tubular type. ,' Cast-iron is frequently used in the construction of gas or oil-fired, furnaces, designs varying considerably with two general types in common use: multi-sectional type and those with single combustion chambers having auxiliary secondary surface. . '- . Cast-iron furnaces are made in capacities ranging from those for small 354 CHAPTER 18 1946 Guide .insulated residence application with inputs of -40,000 Btu per hour.or less, to capacities as large as 600,000 Btu per hour. Cast-iron furnaces are usually constructed with a minimum sectional thickness of J4 in. and effectively resist high.temperatures and corrosion. They usually have a fairly large heat capacity because of their mass, which provides a distinct fly wheel or carry-over heating effect. Steel Furnaces Formed sheet steel construction is frequently used in furnace design. Welding, riveting or both, are used to join the formed metal. The use of steel castings, however, is rare, because of the cost, and because high stresses are not encountered in normal furnace construction. Types of design employed vary greatly, although perhaps the most common type consists of a drum and circumferential or rear radiator. Steel gas fur naces may also be sectional in design or may be combinations of common combustion chambers and sectional or tubular radiation surfaces con nected to a flue gas collector. . `. Steel furnaces are made in capacities ranging from those for small insulated residence application with inputs of 40,000 Btu per hour to capacities as large as 600,000 Btu. / Steel furnaces have low heat capacities as a result pf their relatively low mass and, therefore, deliver heat rapidly on demand. ' RATING OF FURNACES--TESTING AND RATING CODES Warm air furnaces are generally rated in Btu per hour output at the bonnet (point of heat generation) or at the register (point of heat delivery).' . ' Rating Equations for Gravity Warm Air Furnaces9 .- ' Until a method of testing and rating gravity warm air furnaces has. been developed, the' following empirical rating equations are recom mended by. the National Warm Air Heating and. Air Conditioning Asso ciation. ' ' ". ' . Gravity warm-air furnaces of conventional design, having ratios (of heating surface to grate area) of 15 to Tor greater, arid having a ratio of casing area to face area not less than 0.4, are rated by the following equatioris:- .' . ' a. Hand-fired furnaces Converted to Stoker, Gas, or (JiL Firing. Bonnet Capacity in Btu per hour = 1785 xSx 1.333 (2) b. Hand-fired furnaces, with ratios of heating surface to grate area greater than 15 to 1 and less than 25 io 1. , Bonnet Capacity in Btu per hour = 1785 x S x 1.333 (3) ' c. Hand-fired furnaces with ratios of heating surface to grate area in excess of 25'to 1: ` where Bonnet Capacity in Btu per hour = 1785 x 25xGx 1.333 . 5 = heating surface, in square feet. . G = actual grate area, in square feet. - . ' (4) * . The- -Register Delivery Rating is equal to 0:75 x (Bonnet Capacity). The Leader Pipe Rating in square inches, formerly used as a rating unit, -may be found by dividing the Register Delivery Rating by 136. - . Heating Boilers and Furnaces 355 Heating Surface of Furnace ! Prime heating surface is defined as surface above the top of the grate having hot gases or livefuel on one side and circulating air over the other,and in all cases is measured on the exterior or air side. The areas of the outer casing, the inner liner, and any radiation shields shall not be con sidered as heating surface. . '. ' In determining the amount of heatirig surface, extended surfaces are considered to be prime heating surface subject to the following limitations: a. Extended heating surface may consist of fins, ribs, websj lugs, or other projections from the prime heating surface. Projections less than Y m. thick at the base and extending more than 1 in. from the prime surface are classified as fins. ' .- . b. Integral fins are continuously welded, to, or cast as a part of, the prime heating surface. Both sides are included as heating surface, subject to the following allowances: 1st inch ' 2nd inch Ratio of Effective Area to Total Area___ 0.40 0.30 3rd inch Over 3 in. 0.20 None c. Non-integral fins are spot welded .to, or otherwise held in line.contact with the prime heating surface. Both sides are included as heating surface, subject to the fol lowing allowances: " '. - 1st inch 2nd inch Ratio of Effective Area to TotalArea',,.. . 0.30. . 0.20 . 3rd inch Over 3 in. 0.15 None d. In the case of ribs, webs, or lugs more than Y in. thick at the base and extending less than 1 in. from the prime surface, the entire surface in contact with circulating air is included as heating surface. e. In the case of ribs, webs, or lugs more than Y .in. thick at the base and extending more than 1 in. from the prime heating surface the areas of both sides of the first inch are included as prime heating surface. The portions projecting beyond. 1 in. are treated as integral fins. . ' ! ' Grate Area , 1 Grate area is defined arid 'treated'.fori purpose of rating as follows: a. The nominal grate area is:defined as..the total cross-sectional area of the-bottom of the firepot. In steel furnaces the nominal grate-area is the cross-sectional area inside the firebrick lining. '' '` ' b: The actual grate area, used for calculating the ratios of heating surface to grate area, is the nominal grate area minus certain areas that cannot be considered as part of the grate itself. The following rules govern.these deductions: (1) If a solid, con tinuous ledge extends'around the grate and inside the firepot, any area of this ledge extending' inside of a circle^ the diameter of which is 1 in. less than the diameter of the bottom of the firepot, shall be deducted. (2) If separate, solid projections extend from the firepot towards the grate, the areas of any portions of these projections extending inside of a circle, the-diameter of which is 3 in. less than the diameter of the.bottom of the firepot, shall be deducted. (3) In the case of grates which are inclined, or are conical, the projected area is the same as the nominal grate area. The latter should, therefore, be used after making any necessary deductions. - .' Ratings for Forced Air . Furnaces ... . For solid fuel burning,' forced air furnaces having, bonnet capacities between 80,000 and 250,000 Btu per hour, no standard method.of test has been accepted, although eventually such codes will be developed. 356 CHAPTER 18 1946 Guide The National Warm Air Heating and Air Conditioning Association recommends empirical equations similar to Equations 2, 3. and 4 for gravity furnaces, except that a constant of 2265 is used in place of the 1785. _ ' The following testing and rating codes have been generally accepted, in the industry: / . .. Commercial Standards CS-109-44 for rating solid fuel-burning, forced-air furnaces having bonnet outputs of 80,000 Btu per hour or less. This provides a method of rating small coal-fired forced-air furnaces by test. . A Tentative Code for Testing Oil-Fired Furnaces. This code has been adopted by the National Warm Air Heating and Air Conditioning Association for rating oil-fired fur naces by test. '.! The American Gas Association method of rating gas-fired furnaces based upon per formance under tests. This is described in the Approval Requirements for Central Heating Gas Appliances. . Commercial Standards 118-44 is a method of rating oil-burning floor furnaces by test. Commercial Standard CS 104-43 is a method of rating warm air furnaces equipped' with pot-type oil burners by test. Various codes covering the construction and performance of appliances as related to fire hazards'have been developed by Underwriter Laboratories, Inc. In addition, there are many municipal codes 10 which regulate construction and installation of furnace equipment. . The Yardstick of the National Warm Air Heating and Air Conditioning Association provides criteria for evaluating a furnace design and installation against, industry accepted standards. . FURNACE EFFICIENCY *. \ Rating formulae of the National Warm AirHeating and Air Conditioning Association are based on 55 per cent efficiency for gravity coal furnaces arid 65 per cent efficiency for forced air coal furnaces. In the tentative- Oil Testing Code the contemplated minimum efficiency is 70 per cent for oil fired forced air-furnaces. Gravity gas furnaces approved by the. American Gas Association are assigned a rating based on `75 per cent: efficiency. Ali forced air gas-fired furnaces approved by American. Gas. .Association are assigned a rating based on 80 per cent efficiency. DESIGN CONSIDERATIONS Considerations of prime importance in the design of warm air fur naces and some general suggestions to be observed in connection with1 each are as follows: ' 1. Adequate heat transfer surface. . . . a. Heat transfer rates of 2,000 to 4,500 Btu per (hour) (square foot) of heating surface may be obtained without unduly high metal temperatures. . . b. Fins, pins and bosses are frequently used to add surface and to break down - superficial gas films, both on gas-to-metal and metal-to-air surfaces. . c. Surface and stack (flue gas) temperatures are good indications of the amount . and effectiveness of the heating surfaces. . 2. Safe and efficient combustion offuel. . a. Proper mixture of fuel and air is'necessary for efficient combustion. This necessitates careful attention to the design of grates, nozzles, burners, air inlet- areas and location, and combustion chamber baffling. * . b. Regulation of the quantity and the distribution of the air for combustion should be provided by use of check dampers, draft regulators, draft hoods, air . shutters and air orifices. ` . . - ; Heating Boilers and Furnaces 357 c. Total draft loss through appliances should not exceed that available from ` chimneys which would normally be obtainable in the size of building which the appliance will supply with heat. . ' d. The use of ignition safety devices such as safety pilots, hold-fire controls, and the like is recommended. . 3. Fuel Capacity of Appliance. ' a. With solid fuels adequate coal capacity should be provided for at least 5 hr of operation at the maximum rated combustion rate. . 4. Adequate circulation of air over heating surface. a. In gravity furnaces, free air space between casing and heat exchanger should be great enough to permit free flow over all surfaces. b. Forced air furnace design must include fans having proper capacity and having performance characteristics. Internal static pressures must be minimized without losing the advantages of high velocity circulation over the heat exchanger surfaces. c. The air flow -over the heating surface must be directed to obtain maximum efficiency and. to eliminate hot spots and air noises. . d. Air velocities at bonnet should not be much in excess of 1,000 fpm and air temperature distribution at the furnace outlet should be uniform within approxi- mately 30 deg. ,, . 5. Durability. , . .. a. A minimum metal weight for gas-fired heat exchangers is established at No. 20 U. S. Gage for plain carbon steel by the A .G.A . Approval Requirements for Central Heating Gas Appliances with some municipal codes specifying 18 gage. Cast-iron sectional thicknesses of in. to % in. are recommended. . b. Added strength and reinforced designs may be required to preclude damage in shipment, burning out from overfiring, or corrosion from condensation. c. Maximum heat exchanger surface temperatures which, may be used vary with the metal. The American Gas Association Approval Requirements for Central - Heating Gas Appliances specify a maximum of 875 F for cast-iron or steel gas furnaces, and the Bureau of Standards CS 109-44 Code for-Forced Air Solid Fuel-Burning Furnaces specifies 1000 F-as a maximum surface temperature. These temperatures define the range in which oxidation of non-alloy ferrous metal begins. The use of proper alloy additions increases the temperature resistance properties of metals. '. ,,- d. Casing temperatures should be controlled so that they do not become hazards to bum those who touch them, or to create fires. 6. Serviceability. . . ` a. Those parts of the furnace which may be subject to soot, fly-ash, or conden sation deposits, should be accessible for cleaning. ' b. Parts which may require adjustments or replacements, such as grates, baffles, liners, controls, should be removable. . ' c. Furnaces should be so designed that they can be installed with a minimum of difficulty. 7. Control. . - a. Thermostatic controls of various types should be used to correlate space tem peratures with unit operation. , ' b. Controls should be provided wherever possible, to prevent the occurrence of excessive temperatures or other conditions in any part of the unit which might cause unsafe operation. . 8. General design considerations. . .. a. Furnace casings are normally constructed of formed and painted sheet steel or of galvanized iron. The casing should be protection from.excessive radiation losses and temperatures by use of insulation or sheet steel air space liners. Liners should extend from the grate level to the top of the furnace and should be spaced from 1 in. to in. from the outer casing. . 358 CHAPTER 18 , 1946 Guide . b. The hood or bonnet of the casing' above the furnace should be as high as base . ment conditions will allow, to'form a plenum chamber over the top of the furnace. This tends to equalize the pressure and temperature' of the air leaving the bonnet through the various openings. It is generally considered advisable to take off . the" warm air pipes from the'side of the bonnet near the top, as this method of take-off allows the use of a higher bonnet and thus provides a larger plenum chamber. . c. Warm air outlet and return air connections should be designed so that the ductwork may be easily attached. A % in. flange is normally used for this purpose. d. Suitable provision shall be made in appliances so that the controls and humidi fiers may be installed in the proper location. When these auxiliary units are installed in the ductwork, detailed instructions should be provided to insure - their proper location. '' '. e. The flue connection should be of integral flue pipe size and provision should be made to attach the flue pipe to the flue outlet of the furnace. HUMIDIFICATION EQUIPMENT FOR FURNACES Water evaporating pans are usually located in air which has been heated by contact with the heating surfaces'. To change water into vapor capable of being carried in an air stream as part of the mixture, about 1000 Btu per pound are required. There is a trend in present practice toward heating the water in addition to heating the air. Equipment for doing this, may make use of sprays, or it may . take' the form of water' circulating coils placed within the combustion chamber and connected by pipes to the humidifier pans where a constant water level is maintained by some separate float device. Sprays are usually controlled by solenoid valves wired in parallel with the fan motor. The water supply may, in torn, be controlled by a humidity-controlling device located in one of the living rooms, so that the washer will operate at all times when the fan is in operation, unless the relative humidity should rise beyond a desirable percentage. Sprays used in connection with commercial or heavy duty plants should be a regulation type of commercial spray. In all cases provision must be made to flush out accumulation of lime and dirt. . REFERENCES . '--See A.S.H.V.E. Transactions, Vol. 35. 1929, pp. 322 and 332. . 1 *--See A.S.H.V.E. Transactions, Vo!. 36. 1930. p. 42. ' *--See A&H.V.E. Transactions, Vol. 37, 1931. p. 23.' . ' ' <--See A1S.H.V.E. Transactions, Vol. 44. 1938, p. 366. ' 5_/ = B = R Testing and Rating Code for Low Pressure Heating Boilers (Institute of Boiler and Radiator Manufacturers). -. . . ---- R Ratings for Cast-Iron Boilers (Institute of Boiler and Radiator Manufacturers). 7~Engineering Standards. Part II. Net Square Feet Radiation Loads in.70 Deg Fahr., Recommended for 1 Low Pressure Heating Boilers, 1943 (Heating, Piping and Air Conditioning Contractors National Association). *--Comfort Heating, 1938, pp. 35 to 39 (American Gas Association). . --For definition of Heating Surfaces.and Ratings of Wood-Burning Furnaces see Gravity. Code and Manual for the Design and Installation of Gravity Warm Air Heating Systems. (National WarmAir Heating and Air Conditioning Association).- * ;' ' - l o--Recommended forms for municipal installation and fire codes are included in Volume 7--Code and Manual for the Design and Installation of Warm Air Winter Air Conditioning Systems (National Warm Air Heating and Air Conditioning Association). ' CHAPTER ,19 (dhimneys and obraj^t (daiculationA Theoretical and Available Draft, Determining Chimney Sizes, Factors Affecting Required Draft,. Domestic Chimneys, Ob served Test Performance, Draft Requirements of Domestic ' Appliances, Construction Details, General Considerations ADRAFT, in the older sense, is a current of air and the draft of a furnace or boiler is that air current which flows through the fire-box and furnishes the oxygen for combustion. In engineering, however, the. word draft has come to mean, that pressure difference which causes this air current to flow and the word will be used in this sense in this chapter. . Draft is usually measured in inches of water and it is proper to speak of the draft in the fire-box or in the smoke breeching, etc., meaning the difference in pressure between the gases within and the air without those parts of a system. Draft is called positive when the pressure within such a part is less than that outside.1 . . Draft is classified as natural, and mechanical, depending on whether it is produced by a chimney or by a blower, and mechanical draft is further classified as induced or forced, depending on whether the air is drawn through or forced through the combustion chamber. ' Chimneys can serve both to create a draft and to dispose of combustion products at a desirable height. For the latter purpose, chimneys, stacks, or, in the case of ships, funnels, are used in conjunction with mechanical- draft systems. . THEORETICAL DRAFT . If the air in one of two equal chimneys is heated while that in the other is not, the air in the heated chimney will be less heavy, than that in the other chimney and a manometer or other pressure gage connecting the two at the bottom will indicate a pressure difference, called natural draft. The pressure of the air at the tops of the'two chimneys will be equal, so that the pressure difference between them at the bottom will depend only on their height and the difference in density of the air they contain. The density of the air-in either chimney is inversely proportional to its absolute temperature, so that the difference in pressure between them at the bottom will be proportional to their height and to the difference between the reciprocals of the absolute temperatures within them. The pressure-at the bottom of an unheated (and'uncooled) chimney will be the same as that of the air outside, so that the unheated chimney can be dropped from the foregoing illustration.. The manometer reading will be the same if its free connection is left open to the atmosphere. These considerations in conjunction with those of barometric pressure and the difference in density of flue gases from that of- air lead to the following formula: ' . Dt = 2.96 IIBo . . (1) where '. ` . H = height of chimney, feet. `* > Bo = existing barometric pressure, inches of mercury. Wo = density of air at 0 F and l atmosphere pressure, pounds per cubic foot. Wc density of flue gas at 0 F and 1 atmosphere pressure, pounds per cubic foot. . 359 360 CHAPTER 19 1946 Guide Tq = temperature of air surrounding the chimney, Fahrenheit degrees absolute. Tc = average or effective temperature of the.gases in the chimney, Fahrenheit de grees absolute. The quantity Dt, yielded by the formula, is the pressure difference between the gas inside and air outside of the chimney, in inches of water, when no flow occurs in the chimney. The quantity is variously known as the theoretical draft, the static draft or the computed draft. It'is very . useful in predicting and analyzing chimney performance, but it is seldom if ever attained in an actual chimney on account of the friction incident to gas flow, wind effects, etc. , AVAILABLE DRAFT The available draft, D*,for large chimneys and stacks has been estimated with apparent satisfaction in the past by means of formulas which in effect deduct an estimated friction loss from a theoretical draft deter mined as in Equation 1. The friction loss can be estimated by means of one of the formulae available for ducts, such as the Fanning equation. This procedure results in formulas for the available draft as follows:. ' For a cylindrical stack: . D3 = 2.96 HB0 (j? W7N 0.00126 Tc) D*B0Wc (2) and for a rectangular stack: where Dc = 2.96 HB,, - --000388 W* TcfL (x + y) xy> Bo Wc . (3) >a ** .available draft, inches, water gage. H = height of chimney above grate, feet. - B0 -- existing barometric pressure, inches of mercury. Wo -- density of air at 0 F, 1 atmosphere pressure. . Wc = density of flue gas at 0 F, 1 atmosphere pressure. To = temperature of atmosphere, degrees Fahrenheit absolute. Tc = temperature of flue gas, degrees Fahrenheit absolute. W =sflue gas flow rate, pounds, per second.. / = coefficient of friction. ` . L = length of friction duct.( = H approximately), feet. . D = minimum diameter of round chimney, feet. x and y = length and width of cross-section of rectangular chimney, feet. The following notes facilitate the use of Equations 2 and 3. ... 1. The barometric pressure, represented by BQ, is the actual pressure at the site of the chimney and not the pressure reduced to sea level datum. In general, the barometric pressure decreases approximately 0.1 in. HgJ>er 100, ft increase in elevation. ... ` 2. The unit weight of a cubic foot of chimney gases at 0 F and sea level barometric pressure is given by the equation: ./ . Wc=.0.131COt + 0.0950, + 0.083iV, . (4) In this equation CO,, 0, and N* represent the percentages of the parts by volume of the carbon dioxide, oxygen and nitrogen content, respectively, of the gas analysis. For ordinary operating conditions, the value'of Wc may be assumed at 0.09. . The density effect on the chimney gases due to superheated water vapor resulting from moisture and hydrogen in the fuel, or due to any air infiltrations in the chimney proper is disregarded.. Though water vapor content is hot disclosed by Orsat analysis, its presence tends, to reduce the actual weight per cubic foot of chimney gases. 3. The atmospheric temperature is the actual observed temperature of the outside air Chimneys and Draft Calculations 361 at the time the analysis of the operating chimney is made. The mean atmospheric temperature in the temperate zone is approximately 62 F. 4. The chimney gas temperature decreases from' the breeching connection to the top of the stack. This drop in temperature depends upon the material and construction of the' stack, its tightness or freedom from leaks, its area, its height, and the velocity of. the gases through it. The same chimney will suffer different temperature losses depending upon the capacity under which it is working and the variable atmospheric conditions. No general equation covering all these variables has been suggested, but from observa tions on chimneys varying in diameter from 3 to 16 ft and in height from 100 to 250 ft Equation 5 was deduced l: . 3.13 r,[(f)"-! ffb-3 where . T*i = absolute temperature at the center of the connection from the breeching, Fahrenheit degrees. Hb = the height of the stack above center line connection to breeching, feet. 5. The coefficient offriction between the chimney gases and a sooted surface has been taken by many workers in this field as a constant value of 0.016 for the conditions in volved; This value, of course, would be less for a new unlined steel stack than for a brick or brick-lined chimney, but in time the inside surface of all chimneys regardless of the materials of construction becomes covered with a layer of soot, and thus the coef ficient of. friction has been taken the same for all types of chimneys and in general constant for all conditions of operation. For reasons of simplicity and convenience to the reader,, this constant value of 0.016 has been employed in the development of the various special equations and charts shown in this chapter. In important chimney design, especially when the construction or the materials are unusual, it is recommended that use be made of the Reynolds number 4 in determining the friction factor, /. ` The following problem illustrates the use of Equation 2: Example 1. Determine the available draft of a natural draft chimney 200 ft in height and 10 ft in diameter operating under the following conditions: atmospheric tempera ture, 62 F; chimney gas temperature, 500 F; sea level.atmospheric pressure, B0 = 29.92 in.' Hg; atmospheric and chimney gas density, 0.0863 and 0.09, respectively; coefficient of friction, 0.016; length of friction duct, 200 ft. The chimney discharges 100 lb of gases per second. ' Substituting these values in Equation 2 and reducing: . A, = 2.96 X 200 X 29.92 X (^3 0.09 \ 0.00126 X 100* X 960 X 0.016 X 200 960 / 10s X 29.92 X 0.09 = 1.27 -0.14 = 1.13 in. Fig. 1 shows the variation in the available draft of a typical 200 ft by 10 ft chimney operating under the general conditions noted in Example 1. When the chimney is under static conditions and no gases are flowing, the available draft is equal to 1.27 in. of water, the theoretical intensity. As the amount of gases flowing increases, the available draft decreases until it becomes zero at a gas flow of 297 lb per second, at which point the draft loss due to friction is equal to the theoretical intensity. The point of maximum draft and zero capacity is called shut-off draft, or point of impending delivery, and corresponds to the point of shut-off head of a centrifugal pump. The point of zero draft and maximum capacity is called the wide open point and corresponds to the wide open point of a centrifugal pump. A set of operating characteristics may be developed for any size chimney operating under any set of conditions by substituting the proper values in Equation 2 and then plotting the results in the manner shown in Fig. 1. . 362 CHAPTER 19 1946 `Guide Chimneys and Draft Calculations 363 Fig. 2. Chimney Performance Chart Fig. 1. Typical Set of Operating Characteristics of a Natural Draft Chimney i. Fig. 2 is a typical chimney performance chart giving the available draft for various gas flow rates and sizes of chimney. This chart is based oh an atmospheric temperature of 62 F, a chimney gas temperature of 600 F, a unit chimney gas weight of 0.09 lb per cubic foot, sea level atmospheric pressure, a coefficient of friction of 0.016, and a friction duct length equal to the height of the chimney above the grate level. These curves may be used for general operating conditions. For specific conditions, a new chart may be prepared from Equation 2 or 3. - DETERMINING CHIMNEY SIZES If the required performance for a proposed chimney is known and if a chimney-gas velocity is assumed, Equation 2 can be transposed to yield the necessary height and an equation can be developed'for the required diameter. These operations result in the following equations: H= . 0.184/1^50 V* ' TcD The weight of gas per second, W = 12.075 D*. from which (6) . where D = 0.288 s B0WCV ' H = required height of chimney above grate, feet. D = required minimum diameter of chimney, feet. ' V = chimney gas velocity, feet per second. . Dr = total required draft, inches of water. . , - (7) For large chimneys, it is usual to assume that total construction cost is least when the product HD (height X diameter) is minimum. On this assumption, the product of Equations 6 and 7 can be differentiatedand To solve a typical example: Pro ceed horizontally from a Weight Flow Rate point to intersection with diameter line; from this inter section follow vertically to chimney height line; from this intersection follow horizontally to the right to Available Draft scale. Starting from a point of Available Draft, take steps in reverse order. the differential. set equal to zero to find the minimum. Solution for velocity then yields the following equation: where Ke = economical chimney gas velocity, feet pet second. ' Equations 6,-7 and 8 can of course be simplified if values are assumed for some of the factors in it. Some typical figures for boiler plants are : Average chimney gas temperature 500 F ................ ............ Tc = 960 F absolute Average atmospheric temperature 62 F__________.................. To = 522 F absolute ' Average coefficient of friction 0.016.___ ./ = 0.016 Average chimney, gas density, 0 F, 1 Atmosphere__ _____ Wc = 0.09 lb per cubic foot Barometer reading, sea level___ _____ __ _Bo = 29.92 in. Hg When these values are substituted in Equations 8, 7 and 6 respectively, the results are: - Vo = 1Z.7WU* (9) D = 1.5W" (10) H = 190Z3r (11) ' , Fig. 3 gives the economical chimney sizes for various amounts of gases flowing and for required draft intensities computed from Equations 9, 10 and 11. They are based on the operating factors used in-reducing Equations 6, 7 and 8 to their simpler form. The sizes shown by the curves in the chart-should be used for general operating conditions only, 364 CHAPTER 19 1946 Guide or where the required data necessary for an exact determination are difficult or impossible to secure. Whenever it is possible to secure accurate data, or the anticipated operating conditions are fairly well known, the required size should be determined from Equations 6, 7 and 8. FACTORS AFFECTING REQUIRED DRAFT The foregoing considerations deal with chimney size selection when the required draft and flue gas volume and temperature are known. The Height of Chimney, ft. Chimneys and Draft Calculations 365 hour per square foot for each Fahrenheit degree temperature difference between the gases and surrounding air. DOMESTIC CHIMNEYS The height of a chimney for a residence or apartment is generally limited by the height of the building since it is desirable to have the chimney architecturally congruous with the building. . The height desir able from an architectural viewpoint and the location of the chimney may be disadvantageous to the operation of the boiler or furnace and it is therefore important that the manufacturer of the fuel burning appliance to be installed be consulted in regard to the adequacy of the chimney. Diameter values also for gas temperatures of 400, 500 and 600 F. Fig. 3. Economical Chimney Sizes required draft is, of course, equal to the sum of all the resistances to gas flow from the ash pit door to and including the chimney connection. Fig. 4 presents information on the fuel-bed draft loss for various kinds of coal burned at different rates and rough generalizations can be given for the losses in the flue passages of boiler or furnace, but, on account of the great differences in such devices, more reliable data on their flue gas volume temperature and flue resistance should be obtained for design purposes from their respective manufacturers. Flue gases encounter resistance to flow in breechings or smoke pipes and this can probably be treated with sufficient accuracy by means of the method used for air ducts. (See Chapter 41.) The friction in straight ducts can be estimated by means of the last terms of Equations 2 and 3.. Also, the temperature of flue gases falls during passage through breech ings or flue pipes. For uninsulated surfaces this probably can be ade quately estimated by assuming a loss of heat from the flue gas of 3 Btu per POUNDS OF COAL BURNED PER SQ FT OF GRATE SURFACE PER HOUR Fig. 4. Draft Required at Different Rates of Combustion for Various Kinds of Coal A chimney in order to provide a satisfactory performance must have adequate height and area, be of permanently tight construction and should be as smooth internally as practicable. It should be remembered that mechanically fired devices, oil burners and stokers, are equipped with blowers so that, with these devices, the chimney is not required to overcome the resistance of a fuel bed. Never theless, a draft in the fire box, of about 0.03 in. of water is considered desirable so that any small openings in the fire box or flue passages will result in leakage of air in, and not leakage of combustion products out, of such parts. This is not to be taken to condone leaks in fire boxes. Such leaks adversely affect plant efficiency. ' OBSERVED TEST PERFORMANCE The observed performances of some brick chimneys3 are given in Tables 1 and 2. The tests on which these data are based were made at various outside temperatures as shown and, to make them comparable among themselves, the observed drafts were corrected to 32 F, 1 atmosphere pressure, bv the formula: T a b l e 1. e m p e r a t u r e a n d D r a f t i n 9 i n . b y 9 i n . M a s o n r y C h i m n e y 8T 366 CHAPTER 19 1946 Guide gal per h o u r o f fuel o il burned w ith 10 per cent C O t produces 18.4 cfm or 1.38 lb per m inute o f flue gases (corrected to 70 F . 1 atm osphere pressure); gal per n d ic a t e dI F r ic t io n Loss Inch W ater . In ' ' ' ' ^Corrected fo r outside tem perature 32 F. Barom eter 29.92 in. H g. . co*<toooto 'ww eon co*h-3>toto oooooS SSqqoq qqqqqq pppppppS SSSSSSSS ddddod dddodd dodddd dddddddo dddodddd ++.++++ i ++++<- ++++++ ++++++++ +1++++11 Computed Static Inch Water i OOJO0C0B-4aJ---M TOfrt--Ot SO*4M*C4,9h-Q-00 NoNoTOhOChC44h9tm0 P3O 00 > *4 oppp*4*4*4-< HdHooTOoCaDoC4*.q00ptt0oCSO dodddd dodddd dodddd dddodddd dddodddd UawHuueeOit h-WpMo--oC--OOo-H r*tO-0iH',T-4Ot*+h^0 tOrqOt**M4coT'NOH*t> OTOoOTOOCrOQ*TCOO0OhSmh**ThO h00M00(od0e0Nio04*|40o oododd dooodd dddodd dodddddo dddodddd Observed Inch 1 Water qOToOOoTSHOHbH-O*4C^H<) 5O<TPC-PfO'o1Oo'o1eC'o1l otpCOpfC-Op0*4T-HOo 0o*qq04Oq*4op-O4wOHoH* o(9oToONToOHot'Oot>No*Oo dodddd dodddd dodddd dodddddo dddodddd Computed St a t ic D r a f tI nch W ater 02o^p0*o45O00H0* q5ToOqTNqO>^4*^>040 oT*}<Op*TJ<oOOpTeOHp4e}<tHOCD* 00>T0*O4T00pO0>00000*-<4<*40*4 ',oToTOoOMoTOooOdot^o^'o dddodd ddddod dodddd dddodddd dddodddd O bserved D raft Inch W ater O u t s id e T emp. F COo*o4rf-*>Ocott*^h00. - CaOoa-oo'0c0o0tw4 c^O0t4* OrOtO.Ot>OcOo o a> ao to TO TO ra rcoco0c4oT^O*coo0'c0o4uip5 A verage 1 C h im n e y Gas T emp. F 0*C44CT*OO4'CCSO*-00*00tO*4 Q0*4T^O0*W440C(4SD-O^0O*0O .*h*44-**N44O*4Q^r t*4*O0*40O1-O Ch4-TOOTOIOO*5p TT*O4O0*O04TOOpTOCOO*fC>TOf*Or*TO^ gag OTC4OCO4OO-OWOOOOOOOO OTOOT^OO<OO^O*OO0OO0 O0O4OO(NOO4jOOi4OOfOOOO O<C4O0P0O40OW0OO0OO0OO0TOO4 oTC4OCo4Oo4Olo'fQoOoOoO0oO0 CO Per Cent F u e l O il Eq u iv a l e n t of C h im n e y G ases OTOOTOOTO O TO O 00 OTO' OTOOTOOTO OTOOTOOTOOTO OTOOTOOTOOTO '' %. .. ToOT-OITdO*T4OdTO<T-O* ToO*T4OdTO*T4OdTO*T4O TO TO TO TO TO TO ohohoh TO-T*OTO*<TO'TOT*-O<ToOT*O4' TOTOTOTOTOTOTOTO ohohohoh ` Fuel Oil Gal/Hr Height Above Thimble H Us TOTOTOTOTOTO .TOTOTOTOTOTO CO 05 CO CO H3o5 TOTOTOTOTOTO 0404 04 0404 04 004400440044 0044 0044 0044 ^hhhh hhh 5 X > Nominal S T0O3TCOOTCOOTTOOT0O3TCOO TOOOTOOTOTOOOTOOTO TCO4 T0O4T0O4T0O4T0O4T0O4 O04 O04 O04 O04O04 O04 O04O04 ThOThOThOThOTOHTOThOThO ' x .u A c tu a l inside dimensions o f flue lin in g 7 \ i X In'- hour of fuel oil burned w ith 8 per cent CO t produces 67.5 cfm or 5.06 lb per m inute o f flue gas (corrected to 70 F, 1 atmosphere pressure). Chimneys and Draft Calculations 367 T a b l e 2. T e m p e r a tu r e a n d D r a ft in 9 in . b y 13 in . M aso nry C h im n e y 8 n d ic a t e dI W ater Inch W ater i Computed ' I n c h Loss , F r ic t io n 0O--0OT0OO**44O*TO4O*O044 dodddd i +++++ TO *-< Tf -^< C4 O C*4 * 4 C4 SSoooo S0888S oododd + l-H-++/ dodddd I-H-++ 0.002- -+0 .0.000130 +0.004 +0.013 +0.005 *45>00*4 888888 ddddod 1ll1+l X S ta tic JH5 tOO--<T-04O00*4440t4 3 oododd Q 0.086 0.088 0.144 0.176 0.191 0.227 0coCr04*C0*C44V-C*-TD40O0 O00TCOO0*4T--O4*40004*0*44** dddodd dodddd m UtOMGA c000v0TOO*To4O^0T04OoT4Ot0(oO4 4'H 0*4,2-* 4 OTO Oh8#-CeH44H*<2rTOt!HC2O! dodddd oododd dodddd 0.062 0.069 0.089 0.111 0.115 1 0.140 .0.041 0.040 0.073 0.082 0.082 0.101 ! 0.040 0.038 0.070 0.078 0.091 0.100 HU Observed , Inch W ater 0.046 0.047 ! 0.103 0.144 0.148 0.168 0.034 0.052 0.141 0.117 0.178 0.201 St a t ic D r a f tI nch W ater C04O>0CNO0OO*4O*4*N404C-T49O oododd 0.028 0.041 0.079 Q.094 0.107 0.127 O*4OOTOOhOajO00 ddddod 3 If S3 i 0.034 0.039 0.086 0.106 0.120 0.151 0.030 0.044 0.069 0.080 0.094 0.122 0.035 0.047 0.140 0.104 0.163 0.189 W ater t f h a c Observed r n OOOOOTOCO 2>o222 dodddd OOTOTOOOOOCO ddddod 'o"8 S3 DI < NMttH4<NOSOONOY. coooaeoocoot*--co CCOOCCOO0C0O0C0O0T0O0'O0' **4^1 ^ia O0aToOqo ^d>o00TqOo C omputed O u t s id e T emp. F A verage C h im n e y Gas T emp. F T0*H4OTT^OO-TTTOOO00O44-T0^O00T4O TT*OO4 TOoCO4* ate*oo> aC4#OOcOo ONNNS *4 * COCOAS Tt**O4-4eo*40^T^O ,Ht*HWT*4O410108 258 200 600 592 1007 1007 280 250 598 . 604 1016 1000 270 200 . 604 599 1000 . 1000 F lu b G as T e m p , a tI nlet, F P. Zm |3 4 d| gs u. S o S X >ta z s X .u Nom inal H e ig h t Above Thim ble Fuel OU G al/H r COi . Per Cent 204 206 600 600 1000 1000 OSCC4oC4q4TO0oTTqOOfo-0TO) \v oao oooooo O OOOOOOOO OOOOcOOOO aoocoooq oooooooo , TOTOTOTOTOTO TOTOTOTOTOTO TOTOTOTOTOTO TOTOTOTOTOTO TOTOTOTOTOTO OnHOOH di-*d*4d-J d**d--d-- d+d*4d*4 d*-`d*4'*4 % TOTOTOTOTOTO TOTOTOTOTOTO C*3 C3 CO CO 03 CO eqcqeqcq oqeq 04 04 04 04 04 Nh-SSh-hCO CO CO CO CO CO C4C4C4C4C4C4 04 04 04 04 TOTOTOTOTOTO CO 03 CO CO C3 CO Oco Oco Oco OcoOeoOco TOTOTOTOTOTO OOOOOO TOTOTOTOTOTO 368 CHAPTER 19 1946 Guide 0, = 0, + 5, - Si where . (12) Si = computed static (theoretical) draft, experimental conditions. Si = computed static (theoretical) draft, standard conditions. Oi = observed draft, experimental conditions. Oi = observed draft corrected to standard conditions. ' It will be noted that the observed draft exceeded the computed static draft during some observations on the shorter chimneys. This is mainly attributed to the draft producing effect of the hot gases immediately above the chimney. By means of a manom eter it was found that a measurable draft ex isted in this gas column for some distance above the chimney top. How ever, the temperatures in the chimney were measured with un shielded thermocouples and the actual gas tem peratures may have been higher for this rea son than the observed temperatures on which the computations of draft were based. The tests were made in calm weather. Tests were made at the National Bureau of Standards to find the draft produced by round, metal smoke pipe set in a vertical position to act as chim Effective Chimney Temperature-Degrees F neys, Curves are pre sented in Fig. 5 show Fig. 5. Computed Static Draft for Short Chimneys ing the computed static \ or theoretical draft for short chimneys for various heights and tem peratures. For this purpose, the density of chimney gases was assumed to be the same as that of air at the same condition, since the error thus introduced was not considered important in this case. The results of the tests showed that the following procedures would yield the available draft for 6-in. flue pipe used as a chimney within 10 per cent for the range shown and for fuel burning rates from about one-quarter to three- quarters of a gallon of oil per hour. ' Using the temperature at the smoke collar of the heater, find the static draft corresponding to the available chimney height. Then:1 2 3 1. If the chimney is bare, multiply the static draft by 0.76 to find the available draft. 2. If the chimney is insulated with 1 in. of air-cell material with a )^-in. air space, multiply the static draft by 0.85 to find the available draft. 3. If the chimney is insulated with 1 in. of air-cell material with a 1-in. air space, open ' Chimneys and Draft Calculations 369 at top and bottom for ventilation, multiply the static draft by 0.81 to find the available draft. 4. If the chimney is insulated with 1 in. of air-cell material and has a 1-in. air space closed at top and bottom to prevent ventilation, multiply the static draft by 0.85 to find the available draft. The use of the 1-in. air-cell asbestos insulation in the tests discussed is not to be construed as an approval of such insulation in all cases in regard to fire resistance. Several laboratories are working on the fire resistance aspects of the problem but definite rules are not yet available. For coalor oil-burning devices, a bare smoke pipe'is probably safe if kept 2 ft or more from any woodwork and the better the pipe is insulated, or the lower its temperature, the nearer it can be placed to combustible materials. DRAFT REQUIREMENTS OF DOMESTIC APPLIANCES Typical flue-gas temperatures and drafts required at rated output for several kinds of domestic heating appliances4 are contained in Table 3. Table 3. Drafts Required by Typical Domestic Heating Devices or Appliances Device Floor Furnace, Oil Burning, Pot Burner............................... Mechanical Oil Burner, More than 5 gph________________ Space Heater, Coal Burning........ :......... ............... ,,................ ' Draft, Inches Water 0.06 to 0.08 0.06 0.06b 0.06 0.03a 0.05a or less 0.04b 0.06b Stack Temperature F Deg 1000 860 900 860 400 900 Draft in fire-box. *>For chestnut sized anthracite. CHIMNEYS FOR GAS HEATING Heating appliances designed to burn gas as well as appliances converted to gas burning, except those equipped with power type burners and excepting conversion burner installations in excess of 400,000 Btu per hour input in large steel boilers, are always equipped with a draft hood attached to the flue outlet of the appliance. This draft hood is required if the appliance is to meet the approval requirements of the American Gas Association and the American Standards Association and is essential for safe operation. It is designed to prevent excessive chimney draft which would lower appliance efficiency, to prevent a blocked flue or a down draft in the chimney from impairing combustion, to provide a relief opening for the products of combustion during down draft or blocked flue conditions, and to prevent spillage of the products of combustion to the space surrounding the appliance if there is a chimney draft equivalent to that provided by a 3-ft chimney. As the draft hood is designed without moving parts, the relief opening is always open and consequently some air is drawn into the chimney. While the air drawn in lowers the gas- temperature in the chimney, it also lowers the dew-point of the gases and tends to prevent condensation. . The installation of conversion burner equipment in large boilers is usually made in accordance with regulations of the local gas company. In such installations a definite chimney draft may be required for proper 370 CHAPTER 19 - 1946 Guide combustion and consequently the foregoing reference to the use of draft hoods would not apply. The products of complete combustion of gas are water vapor (H^O) and carbon dioxide (COj). In the case of manufactured gas, the presence of organic sulphur compounds, generally between 3 and 15 grains per hundred cubic feet, gives rise to minute percentages of sulphur dioxide and sulphur tri-oxide. The volume of water vapor in the flue products from natural or coke oven gas is about twice the volume of carbon dioxide. It is extremely important that the chimney be tight and resistant to corrosion not only of moisture, but also of dilute sulphur trioxide. Vitreous tile linings with joints which prevent retention of moisture and linings made of non-corrosive materials are advantageous. The protection of unlined chimneys has been investigated and the results indicate that after the loose material has been removed, the spraying with a water emulsion of asphalt chromate will provide excellent protection. Advice regarding recommended practice and materials for flue con nections and chimney linings can usually be obtained from the local gas company and should be given careful consideration. Since a gas designed appliance must be able to operate at rated input (plus 10 or 15 per cent) without chimney connection,' and without pro ducing carbon monoxide, the only function of the chimney is to .remove the products of combustion from the room. The chimney provides draft to overcome the friction in the flue pipe and chimney, but does not draw air into the appliance. Chimneys for venting appliances designed for bhrning gas can there fore be low in height, but must have adequate area. The height is usually established by the building height. Chimney sizes are usually selected on the basis of Btu input to the appliance. One chart6 designed to facilitate selection is shown in Fig. 6. The assumptions made in preparing the chart as well as its limitations should be noted carefully. Since Fig. 6 has been prepared for circular flues, relative capacities for rectangular and semi-elliptical flues6 are shown in Fig. 7. When a flue is connected to several appliances, the number of hori zontal funs of various sizes which may be substituted for the single run having a diameter equal to that of the flue may be obtained from Table 4. CONSTRUCTION DETAILS For general data on the construction of chimneys reference should be made to the Building Code recommended by the National Board of Fire Underwriters, Article XI, Sections 1101 to 1105, in which the following are some of the important provisions listed in the 1943 edition: () Chimneys erected within or attached to a structure shall be constructed of brick, of solid block masonry, or of reinforced concrete. () Chimneys shall extend at least 3 ft above the highest point where they pass through the roof of' the building and at least 2 ft higher than any ridge within 10 ft of such chimney. . .(c) Every such chimney shall be properly capped with brick, terra cotta, stone, cast-iron, concrete or other approved non-combustible, weatherproof material. . (<f) Chimneys shall be wholly supported on approved masonry or self-supporting fireproof construction. . (e) No such chimney shall be corbeled from a wall more than 6 in.; nor shall such chimney be corbeled from a wall which is less than 12 in. in thickness unless it projects equally on each side of the wall; provided that in the second story of two-story dwellings Chimneys and Draft Calculations 371 corbeling of chimneys on the exterior of the enclosing walls may equal the wall thickness. In every case the corbeling shall not exceed 1 in. projection for each-course of brick projected. . ' (f) No change in the size or shape of a chimney, where the chimney passes through the roof, shall be made within a distance of 6 in. above or below the roof joists or rafters. (g) Smoke flues for warm air, hot water and low pressure steam heating furnaces shall have walls not less than 8 in. thick; the walls may be of solid masonry using brick, stone or concrete, or of solid moulded or solid cast chimney units of concrete, or of burned clay, or of suitably reinforced solid concrete cast in place; provided that for stone masonry other than sawed or dressed stone in courses, the thickness shall be not less Fig. 6. Allowable Btu Input to Circular Flues for Domestic Gas Appliances with Draft Hoods Notes: 1. Chart is based on: average flue temperature of 150 F, outside temperature of 60 F, barometric pressure of 30 in. Hg, 100 per cent excess air and 100 per cent dilution at draft hood. 2. Based on terra-cotta lined flues. With rough.brick flues, capacities are 15 per cent less. 3. Based on condition that horizontal run is not greater than 20 ft except for a flue height less than 20 ft, in which case the horizontal run is not to have greater length than the height of the flue. . 4. Two long radius elbows are included in the horizontal run. the diameter of which is equal to that of the flue. . . 5. Each additional elbow reduces the allowable horizontal run by a length In feet equal to the diameter tn inches. .- . 6. When the horizontal run has an effective length in excess of that given (or additional elbows) the next larger size of flue should be chosen. It is desirable that long horizontal runs be insulated to reduce beat loss of flue products and to conserve draft. ' . ,,' 7. Capacities should be reduced 3.5 per cent for each 1000 ft above sea level- . 372 CHAPTER 19 1946 Guide than 12 in. The walls shall be properly bonded, or tied with non-corrosive metal anchors. . In dwellings and buildings of like heating requirements the thickness of-the chimney walls may be reduced to not less than 3^ in. when lined with a flue lining con forming to the Code requirements. . (h) Required flue linings shall be made of fire clay or other refractory clay to with stand the action of flue gases and to resist, without softening or cracking, the tempera tures to which they will be subjected, but not less than 2,000 F, or of cast-iron'of ap proved quality, form and construction. Approved corrosion resistant linings may be used in flues for gas appliances. (t) Required clay flue linings shall be not less than % in. thick for the smaller flues and increasing in thickness for the larger flues. (j) Flue linings shall be built ahead of the construction of the chimney as it is carried up, carefully bedded one on the other in mortar as hereinafter specified with.close fitting joints left smooth on the inside. (k) Flue linings shall start from a point not less than 8 in. below the intake. They Fig. 7. Capacity, of a Rectangular Flue or a Semi-Elliptical Flue, with Semi Circular Ends Having Its Minimum Width Equal to the Diameter of a Circular Flue, Compared with the Capacity of the Circular Flue shall extend, as nearly vertically as possible, for the entire height of the chimney. It is recommended that flue linings be extended 4 in. above the top or cap of the chimney. (I) Only Portland cement mortar, cement lime mortar or fire clay mortar shall be used in setting flue linings. For gas appliances the Building Code specifies lined chimneys and metal smoke stacks for all appliances which may be converted readily to the use of solid or liquid fuel and also for all boilers and furnaces except those having a flue gas temperature, not exceeding 550 F at the outlet of the draft hood when burning gas at the manufacturer's rating and which may therefore be connected to Type B vent piping. Approved Type B vent piping is non-combustible, corrosion resistant piping of adequate strength and heat insulating value, and having bell and spigot or other acceptable joints. Fig. 6 may be used for selection of vent pipe size. . . Important points to be considered in the use of Type B vent piping are: 1. Type B flues must be plainly and permanently marked, at the point where the vent connection enters the flue: For use of gas appliances only.- . _ 2. Type B vent material should not be used for external chimney flues and external runs of it should not exceed 3`ft outside the building roof. When this requirement makes it necessary to cross over through attic space, the piping should be pitched not less than 45 deg. . ... . - - 3. Because of the small size and low temperature. Type B vents should be provided with a vent cap with wire screening to prevent building of buds' nests.. .. Chimneys and Draft Calculations 373 4. Each appliance should have the equivalent of a 4 in. diameter Type B vent, even though the appliance may have a 3 in. flue collar. A typical minimum vertical flue size for a frame dwelling is 6 in. in diameter ` or equivalent. ' 5. When several floor furnaces are to be vented, it. is acceptable practice to connect each of these by means of 4 in. vents to a common 6 in. vertical vent. Lateral piping must have adequate pitch, in. per foot, and should not exceed 20 ft in horizontal length. ' - 6. An alternate method of connecting several appliances is to run separate Type B vents to the attic and then to connect them by means of cross-over piping and Y fittings to a common vertical vent pacing ' through the roof. This reduces the number of boles in the roof. All flue mortar for flues or vent pipes from gas burning appliances shall be acid resisting. GENERAL CONSIDERATIONS FOR CHIMNEYS The draft of domestic chimneys may be subject to a variety of influences not usually encountered in power chimneys7. Horizontal winds have an aspirating effect as they cross the chimney and are an aid to draft. However, surrounding objects, such as trees or other buildings, may Table 4. Equivalent Flue Pipe Sizes3 Diameter Size of Flue of Horizontal Runs 3 4 5 6 8 10 12 3 4 5 6 . 8. i 2 3 5' 9 12 22 1 2 3 5 7 11. 1 2 347 1235 i 23 `Comfort Heating (American Gas Association). affect the direction of the wind at the chimney top and may even direct it down the chimney, tending to reduce the draft or even to cause it to be negative. Although the chimney should extend well above the highest part of the roof, it is impracticable to carry it much beyond this point. It is also important to consider the source of the air supply for proper combustion. Usually the boiler or furnace is located in the basement. When the furnace room has windows or doors opening to the outside on two or more sides of the house, the leakage of air will be sufficient for combustion, even though the windows and doors may be shut. If, however, the leakage is not sufficient to prevent an appreciable drop of pressure in the furnace room below that of the air outside, the chimney draft will be reduced by the difference between the atmospheric pressure outside and that inside the boiler room. In case the boiler room is fairly tight and is open to the outside on only one side of. the house, then the draft will be affected in windy weather even with windows or doors open. If the wind is blowing toward the boiler room the draft will be increased, but if blowing in the opposite direction the draft may be decreased. It is not to be assumed that increasing the cross-section area of a chimney will always effect a cure for poor draft. The opposite result may be experienced because of the cooling effect of the larger area. This reduces the theoretical draft and the velocity of. the gases, and affords a greater opportunity for counter currents in the chimney. Sometimes the only practical remedy for a chimney with bad draft, when the chimney is of the proper size and is affected by conditions beyond control, is to resort to mechanical draft. This can often be done at small expense and the arrangement can be such that the fan or blower need be operated only when conditions are bad. ' / 374 CHAPTER 19 1946 Guide Two or more chimneys, either large or small, should never be connected together especially near the bottom. Hot gases in an inverted U-tube thus formed will be in unstable equilibrium. Cold air will descend through one such chimney, from the top, and drive the hot gases out of the other and thus annul the draft. . More than one device can be served by one chimney. Batteries of boilers are commonly connected to a single chimney in power plants. However, if two or more chimneys are used, each chimney should be used separately for part of the boilers, and not connected in manifold with another chimney, in order to avoid the difficulty described previously. In domestic installations it is sometimes necessary to serve a space heater or cooking stove and a water heater with the same chimney flue. This is not desirable; especially for low chimneys, since doors left open on one device while it is un-fired will tend to annul the draft on another device. Gas burning devices, with their draft hoods and lack of draft dampers, are especially bad in this respect. The traditional method of avoiding this with brick chimneys has been to construct multiple-flue chimneys, so that each fuel-burning device could be served by a separate opening. If two devices must be served by one flue-opening in a chimney, their connections to the chimneys should not be located opposite each other. The connection from the larger device should be reasonably low down and that from the smaller, up near the ceiling, so that each device can be serviced as well as possible, regardless of the treatment of the other. Excessive height in a chimney does no harm but means for controlling the draft are more than ordinarily essential if the chimney is too large in capacity. Coal-burning devices often have air leaks around the fire-box and the draft doors sometimes, fit poorly so that the fire cannot be con trolled at a low rate. Perhaps the simplest remedy for such cases is the barometric damper which admits air into the flue pipe and thus reduces the draft. . ' Directions for building chimneys for fireplaces are contained in Depart ment of. Agriculture Farmers' Bulletin No. 1230. It is considered bad practice,to connect any heating device to a fireplace flue unless the fireplace is effectively sealed. '. REFERENCES l--Notes on Power Plant Design, by E. F. Miller and James Holt (Massachusetts Institute of Technology, 1930). , *--A.S.H.V.E. Research Report No. 1105--Frictional Resistance to the Flow of Air in Straight Ducts, by F. C. Houghten. J. B. Schmider, J. A. Zalovdk and N. Ivanovic (A.S.H.V.E. Transactions. Vol. 45,1939, p. 35) and for more complete discussion see Flow of Fluids in:Closed Conduits, by R. J. S. Pigott (Mechanical Engineering, August, 1933). . '* *--Observed Performance of Some Experimental Chimneys, by R. S. -DU1. P. R. Achenbach and J. T. Duck (A.S.H.V.E. Transactions, Vol. 48. 1942, p. 351). .- *--National Bureau of Standards Commercial Standards: CS101-43 Oil-Burning Space Heaters Equipped With Vaporizing Pot-Type Burners, CS75-42 Automatic Mechanical Oil Burners Designed for Domestic Installations CS(E)104-43 Warm Air Furnaces Equipped With Vaporizing Pot-Type Burners; and Trade Standards: TS3536a Solid-Fuel Burning Forced Air Furnaces, TS3518 Oil-Burning Floor Furnaces Equip ped With Vaporizing Pot-Type Burners. _ ^ 5--Comfort Heating. 1938. p. 71 (American Gas Association). ' Comfort Heating, 1938, p. 74 (American Gas Association). 7~Chimneys and Draft (Chapter 32 in Winter Air Conditioning, by S. Konzo. published by National Warm Air Heating and Air Conditioning Association, 1939). ' CHAPTER 20 Cdtimatina Alltel Coniumption Dor Space Sweating. Fuel Consumption Records, Calculated Heat Loss Estimation Method, Degree-Day Method, Unit Fuel Consumption per Degree-Day, Degree-Day as an Operating Unit, Maximum Demands and Load Factors . MANY methods are in use for estimating in advance of actual oper ation the anticipated heat or fuel consumption of heating plants over long or short periods. With suitable modification in procedure these same general methods are frequently useful in checking the degree of effectiveness with which heat or fuel is utilized during plant operation. In applying any of these estimating methods to the consumption of a particular building plant it should be noted that (a) reliable records of past heat or fuel consumptions of the building under consideration will ' usually produce more trustworthy estimates of future consumptions than will any data obtained by averages or from other similar buildings; (b) where no past records exist useful data can sometimes be obtained from records of similar buildings with similar plants in the same locality; (c) records of consumption, .which are averages from many types of plants in many types of buildings in various localities, can produce no better than an average estimate which may be far from accurate; (d) estimates based on computed heat losses without the benefit of operating data are wholly dependent on how well the computation represents the actual facts. Estimates based on computed heat losses alone are frequently the only ones possible to obtain, especially where new equipment is put into unusual buildings and there is a scarcity of records and an absence of experience data. Such estimates also have to be made where direct information is not obtainable as, for example, if a survey is being made without the assistance or knowledge of the building operator and thus ' without information as to the actual consumption. Estimates of this kind are also useful in some cases where a relative standard of performance is desired to serve as a base of comparisons in a campaign of fuel utili zation. " In interpreting and evaluating heat or fuel consumption estimates as well as in their preparation, it is well to realize that any estimating method used will produce a more reliable result over a long period operation than over a short period. Nearly all of the methods in common use will give trustworthy results over a full annual heating season, and in some cases such estimates will prove consistent within themselves for monthly periods. As the period of the estimate is shortened there is more chance that some factor not allowed for in the estimating method will become controlling and thus give discrepant and even ridiculous results. Of the various estimating methods in use attention is directed in this, discussion to but two as they are illustrative of all, viz: (1) calculated heat loss method, and (2) degree-day method. CALCULATED HEAT LOSS METHOD This method is theoretical and assumes constant temperatures for very definite hours each day throughout the entire heating season. It does not 375 376 CHAPTER 20 1946 Guide take into account factors which are difficult to evaluate such as opening of windows, abnormal heating of the building, poor heating systems, winter heat gains, such as sun effect, and many others. In order to apply this method the hourly heat loss from the building under maximum load, or design condition, is computed following the principles discussed in Chapters 6 and 8 and the method described and illustrated in Chapter 14. In some cases, however, depending on the presence of interior par titions, the computed heat loss is modified when used for estimating the heat or fuel consumption. If the building has no interior walls or par titions then, by the method of Chapters 8 and 14, the infiltration losses are calculated by using only half the total window crack. In such a building the calculated loss need not be modified in order to prepare heat or fuel estimates by this method. Where the building does contain interior walls or partitions instead of using as the calculated heat loss (H) which is equal to the sum of the transmission losses (Ht) and the infiltration losses (Hi), it is more desirable to let H = Ht + t~' In predicting fuel consumption for heating a building by the Calculated Heat Loss Method, the general'equation is: , where H{t - t*) N E (td -- to) C (1) F = quantity of fuel or energy required (in the units in which C is expressed). H = calculated heat loss, Btu per hour, during the design hour, based on to and /d ^generally H -- Ht + Hi but may on occasion equal Ht + t -- average inside temperature maintained during heating period, Fahrenheit degrees, /a ~ average outside temperature through estimate period, Fahrenheit degrees (for cities with an Oct. 1-May 1 heating season, see Table 1, Chapter 14). <d ~ inside design temperature, Fahrenheit degrees (usually 70 F). . to = outside design temperature, Fahrenheit degrees (see Table 1 in Chapter 14). > N = number of heating hours in estimate period (for an Oct. 1--May 1 heating season, 212 days X 24 hr = 5088). E -- efficiency of utilization of the fuel over the period, expressed as a decimal; not the efficiency at peak or rated load condition. C *= heating value of one unit of fuel or energy. Although the assumption of an Oct. 1-May 1 heating season is reason ably accurate in the well-populated New York-Chicago zone, it is not valid as far north as Minneapolis nor farther sbuth than Washington, D. C. and St. Louis. Consequently, it is suggested that allowance be made for this variation, especially in the far north or southern cities. Example 1. A residence in Chicago is to be heated to 70 F from 6 a.m. to 10 p.m. and 55 F from 10 p.m. to 6 a.m. The calculated hourly heat loss is 120,000 Btu per hour based on 70 F inside at --10 F outside. If the building is to be heated by metered steam, how many pounds would be required during an average heating season? Solution. The heating value of steam may be taken as 1000 Btu per pound, and since it is purchased steam, the efficiency can be assumed as 100 per cent. From Table 1, Chapter 14, /a = 36.4 F. The average inside temperature is: ` (16 X 70) + (8 X 55) _ 65 F Substituting in Equation 1: 120,000 (65 - 36.4) 5088 1.00 [70 - (-10)] 1000 218,275 lb. Estimating Fuel Consumption for Space Heating 377- Example 2. How much would the fuel cost to heat the building in Example 1 during an average heating season with coal at $8 per ton and with a calorific value of 11,000 Btu per pound, assuming that the seasonal efficiency of the plant was 55 per cent? . ,, 120,000 (65 - 36.4) 5088 ,,,, ,,,,,, ,L Solution. Substituting in Equation 1: F= 0 55 [70' -- (--10)1 11 000 = 36,079 lb = 18 tons, which, at $8 per ton, costs $144. Example S. What will be the estimated fuel cost per year of heating a building with gas,.assuming that the calculated hourly heat loss is 92,000 Btu based on 0 F, which includes 26,000 Btu for infiltration? The design temperatures are 0 F and 72 F. The normal heating season is 210 days, and the average outside temperature during the ' heating season is 36.4 F. The seasonal efficiency will be 75 per cent. The heating plant will be thermostatically controlled, and a temperature of 55 F will be maintained from 11 p.m. to 7 a.m. Assume that the price of gas is 7 cents per 100,000 Btu of fuel con sumption, and disregard the' loss of heat through open windows and doors. Solution. The average hourly temperature is: = (72 X 16) + (55 X 8) = g6 g p The maximum hourly heat loss will be: on non H = 92,000 - TSiEES = 79,000 Btu. M = 79,000 (66.3 - 36.4) 100,000 X 0.75 X X 24 X 210 = (72 - 0) 2204.6 hundred thousand Btu. 2204.6 X $0.07 = $154.32 = estimated fuel cost per year of heating building. Several time-saving procedures have been devised for quickly esti mating the heat consumption of one and two-story residences in order that fuel estimates can be predicted more quickly from Equation 1. . A graphical method of calculating heat losses has beep developed1 which makes possible a quick solution if the gross wall, ceiling, or floor areas,and respective transmission coefficients are known. . The Federal Housing Administration has originated a short-cut formula for residential heat loss determinations which makes use of the floor area and three selected transmission coefficients. Equation 2 is for a one-story residence and Equation 3 is intended for two-story structures. H, = A (0.45 + U,,+Vc + Ut) (ld- to) (2) .H,"= A (0.45 + 1.2 l/,, + 0.5 Uc + 0.5 Ut) (td - to) (3) where . Hi = heat loss from one-story residence, Btu per hour. Hi = heat loss from two-story residence, Btu per hour. A -- floor area, square feet. f/w = coefficient-of transmission for outside wall. ' Uc = coefficient transmission for ceiling, from air in rooms to air in attic space (for 1 ventilated attics). Ut -- coefficient of transmission for floor from air in rooms to air in basement. /d = inside design temperature, Fahrenheit degrees. <0 = outside design temperature, Fahfenheit degrees. ' Both the graphical method and short-cut formula have been found to give accurate and consistent results for the average residence, but if precise estimates are required, the procedure outlined in Chapter 14 should be used. In the case of gravity warm air heating installations, the load was formerly expressed in square inches of leader pipe which can be converted 378 CHAPTER 20 1946 Guide into Btu per hour by multiplying the square inches of leader area by 111. 167 and 200 for first, second and third floor respectively. . Example 4 What would be the total gas consumption over a full heating season of a gas-fired gravity warm air furnace designed according to the Code*, and with four 12 in. and two 8 in. round leaders to the first floor and six 10 in. leaders to the second floor, if the gas has a heating value of 500 Btu per cubic foot, the plant operates at a 70 per cent seasonal efficiency and is designed to maintain an average inside temperature of 65 F when it' is 10 F outside in a city where the average outside temperature is 45 F and the heating season is 5088 hr long? ' Solution. The area of the round leaders is: 12 in., 113 sq in.; 10 in., 79 sq in.; and 8 in., 50 sq in. The total Btu transmitted is: First Floor: [(4 X 113) + (2 X 50)1 X 111 = 61,272 Btu per hour. Second Floor: (6 X 79) X 167 = 79,158 Btu per hour. Total 140,430 Btu per hour. Substituting this total heat loss value as H in Equation 1 gives: 140,430 (65 - 45) 5088 F 0.70 (70 - 10) 500 = 680,483 cu ft gas. DEGREE-DAY METHOD This method is based on consumption data which have been taken from buildings in operation, and the results computed on a degree-day basis. While this method may not be as theoretically correct as the Calculated Heat Loss Method, it is considered by many to be of more value for practical use. ,. . The amount of heat required by a building depends upon the outdoor temperature, if other variables are eliminated. Theoretically it is pro portional to the difference between the outdoor and indoor temperatures. The American Gas Association * determined from experiment in the heating of residences that the gas consumption varied directly as the dif ference between 65 F and the mean outside temperature. In other words, on a day when the temperature was 20 deg below 65 F, twice as much gas was consumed as on a day when the temperature was 10 deg below 65 F. For any one day, when the mean temperature is less than 65 F, there are as many degree-days as there are degrees difference in temperature between the mean temperature for the day and 65 F. Degree-days may be calculated on other than the 65 F base but are seldom used and are of little value except where the inside'temperature to be maintained as, for example, in warehouses, differs greatly from the usual inside temperature range of 68 F to 72 F. . The normal or average number of degree-days, on a 65 F basis, which have occurred over a long period of years, by months, oh a 65 F basis are given for various United States and Canadian and Newfoundland cities in Table 1. .The United States values were computed from daily mean temperatures recorded by the Weather Bureau over a 43-year period 4 from 1899 to 1941. The number of degree-days for a calendar day of a given year was obtained by taking the difference between 65 F and the mean temperature determined from a reading of the maximum and minimum thermometers for a particular locality. The daily normal was established by taking an average of the 43 daily degree-day figures. These daily values were then added to obtain a monthly normal, and the yearly or seasonal degree-day figure was established by taking a summation of the monthly values. In general, attempts to apply the degree-day Estimating Fuel Consumptionfor Space'Heating 379 method to fuel consumption over a period of less than a month are of questionable value. 1 If the degree-days occurring each day are totaled for a reasonably long period, the fuel consumption during that period as compared with another period will be in direct proportion to the number of degree-days in the two periods. Consequently, for a given installation, the fuel consumption can be calculated in terms of fuel used per degree-day for any sufficiently long, period and compared with similar ratios for other periods to deter mine the relative operating efficiencies with the outside temperature variable eliminated. Studies made by the National District Heating Association5 of the metered steam consumption of 163 buildings located in 22 different cities and served with steam from a district heating company substantiate the fact that the 65 F base originally chosen by the gas industry is approxi mately correct. . Formula for Degree-Day Method The general equation for calculating the probable fuel consumption by the degree-day method is: . . F= UX NXD (4) where ' F -- fuel consumption for the estimate period. U = unit fuel consumption, or quantity of fuel used per (degree-day) {building ' load unit). - N = number of building load units (when available use calculated heat loss instead of actual amount of radiation installed). D = number of degree-days for the estimate period. , . Values of N depend on the particular building for which the estimate is being prepared and must be found by surveying plans, by observation, or by measurement of the building. Values of U for use in this equation are the unit fuel consumptions per degree-day and are obtained as a result of the collection of operating information. Certain of this information is presented later but before referring to these data attention is directed to the nature of the unit. Unit Fuel Consumptions per Degree-Day The quantity of fuel used per degree-day in a given heating plant can be reduced to a unit basis in terms of quantity of fuel or steam per degree- day per square foot of radiation, per cubic foot of heated building space, or per thousand Btu hourly heat loss at design conditions. A less fre quently used basis is quantity of fuel per (degree-day) (square foot of floor area).. In fact any convenient unit can be used to relate the consumption to the degree-day and to the building. . . The choice of these units requires explanation and some discrimination and judgment. If the volume basis is used, the net heated space is pref erable to the gross building cubage since gross cubage includes outer walls and certain portions of attic arid basement space which are usually unheated: In the absence of data on net heated volume a figure of 80 per cent of the gross volume may be used to obtain the estimated net heated volume: Regardless of which volume figure is used, this unit basis is not considered accurate-for estimating fuel consumption due to differences in types of construction, exposure and ratio of exposed area to cubic contents. 380 CHAPTER 20 1946 Guide Table 1. Normal Degree-Days for Cities in the United Stater, Canada and Newfoundland3 State Crrr Jam. Feb. Mar. Apr. Mat June Jolt Aug. Sept. Ocr. Nov. Dec. Total Ala___ Birmingham___ 586 502 318 133 23 i 0 i 10 in 351 582 2618 Mobile.......... .. 392 317 178 54 a c c 0 1 45 203 374 1567 Ariz.__ Phoenix.____ __ 404 261 152 47 7 0 0 0 0 18 168 389 1446 Ark..... b ort Smith____ 761 623 398 159 34 1 t 0 12 130 409 708 3230 Little Rock.___ 700 584 37C 148 3C 1 c 0 1C 121 382 659 3005 Calif... Los Angeles...... 276 232 201 158 104 27 1 0 5 43 110 225 1390 San Francisco.. 464 340 314 269 252 196 198 180 122 140 242 426 3143 Colo... Denver__ .'.____ 1026 900 792 523 271 62 9 8 124 415 721 1012 5863 Grand Junction 1230 887 667 381 152 22 1 1 60 352 745 1149 5647 Conn... New Haven...... 1103 1024 848 521 222 46 D. C__ Washington...... 929 842 637 345 104 14 a 12 89 341 660 1010 5879 0 2 43 254 558 870 4598 Fla___ Jacksonville. ... 295 241 131 39 3 0 0 0 0 24 142 286 1161 Ga....... Atlanta. ........... 662 568 389 173 32 2 0 1 12 130 393 640 3002 Savannah______ 395 335 206 68 6 1 0 0 1 46 209 386 1647 Idaho.. Boise.... ......... ..... 1065 840 686 441 248 87 10 17 135 394 717 1025 5659 in____ Chicago_______ 1219 1084 871 536 260 67 7 8 84 334 709 1108 6287 Springfield......... 1145 988 732 382 130 15 1 3 64 290 666 1047 5463 Ind___ Evansville-____ 942 826 588 289 82 5 0 1 32 207 540 875 4387 Indianapolis___ 1104 982 751 414 155 22 2 4 65 299 663 1026 5487 Iowa__ Des Moines....... 1326 1143 849 449 165 27 2 6 , 99 357 768 1200 6391 Sioux City........ 1410 1216 913 488 194 37 3 10 124 405 841 1268 6909 Kan.__ Dodge City....... 1050 878 669 354 134 16 1 3 ' 58 276 644 994 5077 Topeka............... 1104 932 666 331 112 11 0 2 54 258 623 1008 5101 Ky....... Lexington_____ 964 862 650 353 123 14 1 3 47 258 600 916 4791 Louisville--____ 931 824 595 302 92 7 0 1 34 218 549 875 4428 La........ New Orleans.... 319 251 130 32 1 0 0 0 0 23 147 305 1208 Shreveport...__ 522 421 243 83 10 0 0 0 4 71 274 499 2127 Me___ Eastport_______ 1353 1242 1090 778 532 297 159 148 274 528 831 1219 8451 Portland............ 1296 1184 1003 668 375 135 29 46 179 459 792 1172 7338 Md___ Baltimore.... ..... 922 844 650 347 98 12 0 2 34 230 531 852 4522 Mass... Boston................ 1101 1027 852 538 248 66 8 16 98 338 651 1000 5943 Mich... Detroitb............. 1228 1141 943 569 252 56 7 15 109 387 753 1120 6580 Marquette____ 1471 1358 1208 801 493 220 87 102 257 556 927 1306 8786 Minn... Duluth....... ...... 1726 1504 1267 809 514 232 82 100 289 636 1066 1541 9766 Minneapolis.__ 1597 1379 1082 580 255 59 . 8 24 163 484 943 1415 7989 Miss... Vicksburg._____ 498 413 239 85 9 0 0 0 , 5 77 268 479 2073 Mo.___ Kansas City.__ 1083 921 657 327 106 11 0 2 .50 242 599 986 4984 St. Louis.-.:____ 999 865 616 305 88 7 0 1 36 218 558 917 4610 Springfield____ 971 835 599 306 105 11 1 2 45 232 560 900 4567 Mont.. Havre .............. 1548 1374 1109 623 338 129 28 56 275 604 1010 1380 8474 Neb__ Lincoln________ 1254 1070 798 411 161 23 1 6 84 328 732 1142 6010 Omaha________ 1285 1098 813 414 152 "21 1 4 84 326 741 1163 6102 Nev__ Winnemucca__ 1126 887 763 539 320 109 11 23 190 502 802 1099 6371 N. H... Concord.... --. 1339 1212 1005 633 310 98 19 46 189 492 827 1221 7391 N. J_ Atlantic City.-- 944 893 762 489 215 37 4 2 40 250 552 864 5049 N. M._ Santa Fe.______ 1094 892 786 544 297 62 10 . 15 129 451 772 1072 6124 N. Y.,, Albany..... .......... 1276 1174 955 549 221 44 4 14 116 410 756 1139 6658 Buffalob____ -- 1220 1168 1010 672 352 90 15 24 125 410 747 1102 6935 New York......... 1025 958 785 467 176 29 .1 4 51 276 600 934 5306 N. C._ Raleigh__ ______ 699 618 436 213 47 5 0 1 17 155 417 673 3281 Wilmington___ 528 481 328 147 25 2 0 0 5 92 310 514 2432 N. D... Bismarck........... 1720 1478 1187 650 335 104 20 44 240 605 1059 1527 8969 Ohio__ Cincinnati......... 1009 905 681 374 132 16 . 1 3 52 274 613 953 5013 Cleveland.......... 1141 1074 891 558 255 56 8 14 92 354 688 1040 6171 Columbus. ____ 1082 982 762 436 167 26 2 6 68 318 674 1013 5536 Okla... Oklahoma City 850 696 459 204 56 3 0 0 22 156 461 791 3698 Ore,___ Baker.... 1221 994 839 600 411 210 56 73 261 540 849 1165 7219 Portland_______ 776 622 530 370 241 106 29 29 109 298 540 729 4379 Pa........ Philadelphia___ 957 885 696 379 117 16 0 2 36 236 548 877 4749 Pittsburgh b___ 1043 971 767 448 170 29 3 7 69 324 656 979 5466 S. C__ Charleston^___ 450 386 245 84 7 1 0 0 1 48 227 421 1870 Columbia______ 568 488 312 129 18 1 0 0 6 98 330 554 2504 Estimating Fuel Consumption for Space Heating 381 Table 1. Normal Degree-Days for Cities in the United States, Canada and Newfoundland3 (Concluded) State Province CrrT . Jan. Feb. Mar. Ape. Mat June Tult Aug. Sept. Ocr. Nov. Dec. Total S. D.. . Huron. ------------ 1586 1366 1044 579 264 66 9 Rapid City------ 1288 1152 980 607 333 104 15 Knoxville.......... .774 669 478 229 55 3 0 Memphis..--..... 709 605 389 159 32 1 0 Nashville......... 785 681 476 222 54 2 0 Tex..... El Paso._______ 611 433 288 107 15 1 0 Fort Worth...... 582 470 269 100 16 1 0 Houston............. 366 279 144 31 3 0 0 San Antonio___ 382 290 148 38 4 0 0 Modena............. 1191 944 811 569 336 93 7 Salt Lake City.. 1084 868 708 450 232 62 4 Vt____ Burlington____ 1444 1327 1117 679 330 98 22 Va..... Lynchburg____ 829 735 545 290 82 12 1 Norfolk.----------- 709 654 492 257 65 6 0 812 727 548 281 74 g o Seattle................ 765 644 595 440 304 162 71 Spokane............. 1136 935 748 488 282 113 21 W. Va. Elkins................. 103C 95C 774 492 233 59 15 Parkersburg___ 975 888 671 371 129 170 1 Wis..... Green Bay____ 1498 1337 1099 663 325 89 17 LaCrosse........... 150C 1291 1001 533 222 50 7 Milwaukee........ 132S 1)81 969 621 34C 10C 13 Wyo. Cheyenne.......... 1188 107C 994 726 455 160 42 Lander............... 1423 1198 1000 674 406 150 28 21 174 507 966 1415 7997 29 188 503 843 1183 7225 0 20 189 497 751 3665 0 13 127 383 660 3078 0 19 170 470 741 3620 0 6 90 369 618 2538 0 5 76 288 549 2356 0 1 29 164 343 1360 0 0 32 169 361 1424 11 156 503 833 1151 6605 5 95 377 712 1040 5637 47 196 510 866 1294 7930 2 37 232 524 793 v4082 0 9 132 397 664 . 3385 1 27 19 491 775 3944 71 174 372 558 708 4864 37 185 482 816 1061 6305 23 114 40S 724 997 5814 3 55 287 619 922 5091 3 176 495 891 1327 7956 22 154 459 865 1338 7442 18 120 409 782 1198 7086 48 247 592 880 1147 7549 44 263 630 1020 1401 8237 Alta.. Calgary.............. 1674 1428 1240 750 496 270 124 186 450 744 1170 1395 9,927 Edmonton......... 1829 1512 1302 720 434 270 124 186 450 713 1230 151E 10,289 B.C.. Vancouver____ 899 756 713 510 341 180 62 31 270 496 660 837 5,755 Man... Winnipeg...... .... 2139 1820 1581 810 465 90 62 270 744 1320 1829 11,130 NR 1519 1428 1178 810 465 210 93 300 620 930 1333 8,886 N.S 1302 1176 1085 780 496 210 210 496 780 1147 7,682 1674 1484 1271 690 279 30 210 589 990 1457 8,674 Port Arthur. ... 1829 1624 1426 900 558 240 62 86 360 713 1140 1550 10,488 1333 1204 1209 720 372 60 180 558 870 1201 7,715 P F. T 1178 1120 1209 870 529 210 600 558 870 1240 8,384 Que..... Montreal........... 1581 1428 1209 720 310 180 558 960 1395 8,341 Quebec________ 1705 1484 1333 870 434 120 31 270 651 1050 1519 9,467 Sask... Saskatoon. . 2108 1820 1581 810 465 210 62 155 450 806 1290 1736 11,493 Newf... St.John's........ 1286 1215 1153 900 680 412 202 175 339 613 834 1110 8,919 Computed from daily mean temperatures recorded by U. S. Weather Bureau over a 43-year period from 1899 to 1941. Data for Canadian cities abstracted from Heating 6* Ventilating, October. 1939. The National Joint Committee on Weather Statistics, in cooperation with the U. S. Weather Bureau, is pre paring revised Degree-Day Normals which will be available in 1946. - bData for these cities and possibly other localities are based on readings taken at more than one official Weather Station during the 43-year period of analysis and are subject to local verification, as these figures are being examined for possible revision by the U. S. Weather Bureau. The calculated heat loss or its equivalent square feet of calculated radiator surface may be used as the unit. The use of the unit equivalent direct radiation is of questionable value when referring to heat transfer surfaces used in warm air furnace or central air conditioning systems. Where steam or hot water radiation is already installed, care should be exercised in using the unit equivalent direct radiation basis for estimating since actual installed radiation may differ considerably from the exact radiation requirements. In view of all these considerations it is believed that the unit based on thousands of Btu of hourly calculated heat loss for the design hour is probably the most desirable, although the one most widely used seems to be units of fuel per degree-day per square foot of 382 CHAPTER 20 1946 Guide Table 2. Unit Fuel Consumption Constants (/) foe Gas3 Based on OF Outside Temperature, 70 F Inside Temperature, and 8-Hour Reduction to 60 F. Heating Value or Ga& Btu peb Cu Ft 500 535 800 1000 ' Hot Water .Cu Ft Gas per Degree-Day per Sq Ft Radiator Up to 500 Sq Ft 500 to 1200 Sq Ft Over 1200 8q Ft 0.142 0.132 0.089 0.071 0.135 0.126 0.085 0.068 0.128 0.120 0.081 0.065 Steam . ' Warm Aih Cu Ft Gas per Degree-Day . per Sq Ft Hamator Up to 500 8q Ft . 300 to 700 Sq Ft Over 700 Sq Ft Cu Ft Gas per Degree-Day per 1000 Btu Hourly Design Heat Loss Gravity Fail Systems 0.242 0.226 0.151 0.121 0.231 0.215 0.144 0.115 0.220 0.206 0.137 0.110 0.855 ' 0.800 0.534 0.428 0.820 0.766 0.513 0.410 1 Therm 100.000 Btu Gas Consumption in Therms per Degree-Day 0.000708 0.000675 0.000642 0.00121 0.00115 0.00110 0.00428 0.00109 Abstracted from Comfort Heating, American Cos Association. 1938. Table 3. Unit Fuel Consumption3 Constants (/) foe OiLb Based onO F Outside Temperature, 70 F Inside Temperature, and 8-Hour Reduction to 55 F.' - Unit ` EmcoKCT w Pee Cent 40 . 50 60 70. 80 Gal Oil per Sq Ft Steam Radiator.. 0.00172 0.00137 0.00114 0.00098 0.00086 Gal Oil per Sq Ft Hot Water Radiator......... ............... 0.00108 0.00086 0.00072 0.00062 0.00054 Gal Oil per 1000 Btu per Hour Heat Loss. .... ....... 0.00715 0.00571 0.00476 0.00409 0.00358 Baaed on a heating value of 140,000 Bin per gallop. ' ^Abstracted by permission from Degree-Day Handbook (Second Edition. 1037), by C. Strock and C. H. B. Hotchkiss. \ Table 4. Unit Fuel Consumption3 Constants (U) for Coal1* Based on 0 F Outside Temperature, 70 F Inside Temperature, and 8-Hour Reduction to 55 F. Unit 40 Lb Coal per Sq Ft Steam Radiator.. 0.0200 Lb Coal per Sq Ft Hot Water Radiator. _ . .................. 0.0125 Lb Coal per 1000 Btu per Hour Heat Loss. . ......... 0.0825 EmcBNcr m Per Cent 50 0.0160 60 0.0133 70 0.0114 80 0.0100 0.0100 0.0084 0.0072 0.0063 0.0666 0.0550 . 0.0471 .0.0412 Based on a heating value of 12.000 Btu per pound. -. _ ^Abstracted by permission from Detree-Day Handbook, (Second Edition, 1937), by C. Strock and C. H. B. Hotchkiss. ' Estimating Fuel Consumption for Space Heating 383 equivalent direct radiator surface. The equivalent heating load for the hot water supply is not included in the latter unit, but it generally includes- the piping load. _ Since this unit is the one most widely used at present the unit fuel con sumptions given in succeeding paragraphs of this chapter make use of this unit to a considerable extent, although it should be understood that most of these units of consumption can be transposed as desired. . Estimating Gas Consumption Values of the Unit Fuel Consumption Constant (/) for gas are given in Table 2 for various gas heating values, and different types and sizes of heating plants. They are based on an inside design temperature of 70 F and an outside design temperature of 0 F and apply only to these con ditions. For other outside design conditions corrections must be made as given in Table 5. The factors in Table 2, as corrected if necessary, are satisfactory for regions having 3500 to 6500 degrfee-days per heating season.- In regions with less than 3500 degree-days the unit gas consumption is higher than given; where over 6500, the unit is less than given. Ten per cent addition Table 5. Coeeection Factoes foe Outside Design Tempeeatuees3 Outside Design Temp. F Deg__ -20 Correction Factor.--------------- , 0.778 -10 0.875 0 1.000 + 10 1.167 20 1.400 The multipliers in Table 5. which are high for mild climates and low for cold regions are not in error as might appear. The unit figures in Tables 2,3. and 4 are per square foot of radiator or thousand Btu heat loss per degree-day. For equivalent buildings and heating seasons, those in warm climates have-lower design heat losses and smaller radiator quantities than those in cold cities. Consequently, the unit figure, in quantity of fuel per square foot of radiator per degree-day, is larger for warm localities than for colder regions. Since the northern cities have more radiator surface per given building and a higher seasonal degree-day total than cities in the south, the total fuel per season will be larger for the northern dty. or deduction in these cases is recommended by A .G.A. publications. Esti mates for industrial buildings where low inside temperatures are main tained cannot be made from this table. For gas heating values other than those given in Table 2, simply inter polate or extrapolate. It will also be noted that Table 2 applies only to small installations. In general the larger the installation the smaller the unit gas consumption becomes and the values in the table should be used with care, if at all, in large gas-buming installations. Example 6. Estimate the gas required to heat a building located in Chicago, III., which has 6287 degree-days and a gas heating value of 800 Btu per cubic foot. The calculated heating surface requirements are 1000 sq ft of hot . water radiation based on design temperature of --10 F and 70 F. ` Solution. From Table 2, the fuel consumption for a design temperature of 0 F with 800 Btu gas is found to be 0.085 cu ft of gas per degree-day per square foot of hot water radiation. From Table 5, the correction factor is 0.875 for --10 F outside design tem perature, hence 0.875 X 0.085 = 0.07438. By Equation 4, F = 0.07438 X 1000 X 6287 = 467,000 cu ft. Estimating Oil Consumption ' . Unit fuel consumption factors for oil, similar to those for gas in Table 2, are given in Table 3. The factors in Table 3 apply only to an inside design temperature of 70 F and an outside design temperature of OF. For other outside design temperatures, the constants in Table 3 must be multiplied by the values in Table 5 as explained under Estimating Gas Consumption. 384 CHAPTER 20 1946 Guide Values given in Table 3 assume the use of oil with a heating value of 140,000 Btu per gallon. For other heating values, multiply the values in Table 3 by the ratio of 140,000 divided by the heating value per gallon of fuel being used. Example 6. Estimate the seasonal oil consumption of an oil-fired boiler in a building located in Minneapolis having a calculated heat loss of 192,000 Btu per hour, burning 144,000 Btu per gallon oil and operating at a seasonal efficiency of 60 per cent. The out side design temperature for Minneapolis is --20 F, and the inside design temperature is 70 F. Solution. From Table 3, under 60 per cent efficiency and opposite the bottom column, the value of U is found to be 0.00476 gal per 1000 Btu hourly heat loss for 0 F outside temperature. The correction factor for --20.F outside design temperature from Table 5 is 0.778. Solving, 0.778 X 0.00476 = 0.00370. Making a further correction for the heating value: 0.0037 X |44 qoq = 0.0036 gal per 1000 Btu per hour calculated heat loss per degree- day. From Table 1, the normal degree-days for Minneapolis is 7989. Since U is expressed in 1000 Btu, N is equal to 192. Substituting in Equation 4: F = 0.0036 X 7989 X 192 = 5525 gal. Estimating Coal or Coke Consumption / Coal or coke consumption estimates are made in exactly the same procedure as for oil. Values of U are given in Table 4 which only apply to inside design temperatures of 70 F and an outside design temperature of 0 F. A correction must be made for other conditions by use of the multi plying factors in Table 5. Data in Table 4 are based on 12,000 Btu per pound coal and for other heating values of coal they must be multiplied by the ratio of 12,000 divided by the heating value of fuel used. _ Example 7. A building in Marquette, Mich., has an hourly heat loss at design con ditions of 240,000 Btu per hour. Based on an inside design temperature of 70 F and an outside design temperature of --20 F, what will be the estimated norpial seasonal coal consumption for heating if 12,000 Btu per pound fuel is burned at a 50 per cent seasonal efficiency, and what part of the total will be used during November, December, and January? . Solution. From Table 4, U is 0.0666 lb of coal per 1000 Btu per hour heat loss. Cor recting for the outside design temperature of -- 20. F from Table 5, the value of V is 0.778 X 0.0666 - 0.0518. From Table 1, D is 8786 and from the problem, :Y is 240. Substituting in Equation 4: . F = 0.0518 X 240 X 8786 = 109,200 lb. Fuel used over any period is, according to the theory of the degree-day, proportional to the number of degree-days during the period. From Table 1, the average numbers of degree-days for November, December, and January in Marquette are 927, 1306, and 1471, a total of 3704. The yearly total is 8786, so that during these three months the estimated consumption is: 3|^7g0g4 X 109,200 = 46,200 lb. Estimating Steam Consumption . In estimating steam consumption the efficiency is generally assumed at 100 per cent. If for low pressure steam an average heating value of 1000 Btu per pound of steam is used no correction is necessary. In com paring values from different cities, correction should be made for design temperature (see Table 5) when the unit figures are in terms of square feet of radiation but not when the values are in terms of building volume or floor space. Estimating Fuel Consumption for Space Heating 385 Where the heat loss is calculated in Btu per (hour) (degree difference in temperature) the simple Equation 5 may be used: . ^ H X 24 X D . 1000 (5) where - F = pounds of steam required for estimate period. H = calculated heat loss, Btu per (hour) (degree difference). D -- number of degree days for the period of estimation. 1000 = Btu delivered per pound of steam condensed. In this method the number of degree-days automatically takes care of average inside and outside temperature difference. When degree days are taken from Table 1, an average inside temperature of approximately 65 F is assumed throughout the period. If an average inside temperature other than approximately 65 F is to be used, the number of degree-days should be obtained for the new base. Example 8. An eight story building in Pittsburgh maintains daytime temperatures of 70 F but allows night temperature to drop to not lower than 60 F. Its calculated heat loss is 10,500 Btu per (hour) (degree temperature difference). .What is the estimated average yearly steam consumption for building heating? Solution. Since the average inside temperature is approximately 65 F, the degreedays from Table 1,-.based on 65 F may be used. Therefore, from Table 1, Pittsburgh has 5,466 degree-days per normal season. Inserting in Equation 5 10,509 X 24 X 5466 1,000 1,377,432 lb of steam. Consideration has been given to the difference in steam utilization of different types of buildings and Table 6 shows actual average units for these various types. These figures were obtained from operating results in 896 buildings located in all sections of. the United States. Being averages, and for small groups in each type, the figures may need con siderable modification to allow for local variations. It should be especially noted that the steam used for heating hot water is not included in the values given in Table 6. Example 9. A store in Philadelphia with a heating system designed to maintain 70 F inside in 0 F weather has 250,000 cu ft of heated space. What would be the estimated . average yearly stcam consumption of purchased steam for heating? Solution. According to Table 6, a store-would use 0.624 lb of steam per degree-day per 1000 cu ft heated space. From Table 1, Philadelphia has 4749 degree-days per normal year. Inserting in Equation 4: F = 0.624 X 250 X 4749 = 740,000 lb of steam. Degree-Day as an Operating Unit . The degree day is also widely used as a means of comparing the efficiency of the fuel consumption of one period with another for the same building..- Since, the fuel, consumption is proportional to the weather (degree-days) and since the periods to be compared may not have the same weather conditions, the comparison can be made only after the fuel consumptions have been computed on a comparable weather basis, that is, upon the actual number of degree days occurring for a given month and year in the city under consideration. Since fuel consumption is proportional to the number of degree-days, plant operators frequently compute each month the fuel burned per degree-day by the heating plant. The resulting unit figure, by eliminating the outside temperature 386 CHAPTER 20 1946 Guide Table 6. Steam Consumption of Buildings with Various Types of Occupancy Type op Building No. Bldgs. Average Volume Heated Space 1000 Cu Ft Office. ... - Office and Bank.............................. . ... Office and Printing.......... _................ Office and Theater Office and Stores or Shops Bank...................... Department Store Sfnrfx: ____________ .. . Loft__________________________________ Warehouse___________________________ Hotel and Club Apartment or Residence Theater. ... . Garage. _................... .................. ............. Manufacturing.______________________ Church. .......... ..................... _ _ Hospital... School____ Municipal or Federal.... Lodge, Gym, Hall or Auditorium____ Miscellaneous. 334 2160 49 3000 8 1895 7 4950 26 1615 16 806 63 3400 . 73 310 63 865 24 2230 73 1795 51 1425 22 1240 13 1540 19 1350 9. 656 .4 3306 8 1115 15 3215 12 880 7 1387 Total or Average . 896 1890 Steam for Heating Lb per DD per 1000 Cu Ft Average Hours op Occupancy 0.685 0.577 1.230 0.412 0.617 0.786 0.385 0.624 0.588 0.459 0.990 0.962 0.482 0.202 0.808 0.532 1.194 0.592 0.587 0.390 0.479 12.1 13.1 17.7 12.9 13.2 11.7 11.1 10.4 10.0 9,4 22.3 21.8 12.9 21.4 ; 9.5 7.9 22.0 11.5 15.6 12.4 21.4 0.651 13.4 Principles of Economical Heating, National Association of Building Owners and Managers. variable, indicates whether the operating efficiency of the plant is above or below the previous month or year. The figures in Table 7 illustrate a typical example of a method of using the degree-day for making heating comparisons for one building for - two consecutive heating seasons. The heat quantity figures inserted are pounds of steam, but a similar comparison could be made using pounds of coal, gallons of oil, or cubic feet of gas. For such a comparison, a two-year record is often used, as shown in Table 7. The year under consideration may then be compared, month by month, with the previous year; Column 3, Consumption for Heating, would be used if the same fuel is used for heating and process steam. Some reasonable figure must be assumed for the'process requirement and should be deducted from the amount shown in column 2. This would leave in column 3 only the fuel chargeable to heating. The degree-day values in column 5 are obtainable from the local Weather Bureau. Figures in column 6 are obtained by dividing corresponding values in column 3 by the degree days in column 5. The heating index in column 6 is, then, a figure of heat consumption, corrected for outdoor temperature, and should be relatively constant month by month. Column 7 in Table 7 may be used if the heat consumption is to be compared on a building volume basis with average values shown in Table 6. MAXIMUM DEMANDS AND LOAD FACTORS ' In one form of district heating rates, a portion of the charge is based upon the maximum demand of the building. The maximum demand may Estimating Fuel Consumptionfor Space Heating ' 387 Table 7. Heat Consumption Record for Comparison Col. 1 Col. 2 Col. 3 Consumption For Heating N z (A CM/3 p X Sept- ........ Oct.._ ___ Nov............. Dec............. Jan_ ___ Feb............. Mar............. Apr- _ ... May............ June............ July------- .... Aug........ -- 337,500 834,200 1,446,600 2,176,400 2,332,200 2,131,100 2,021,900 1,241,500 672,500 258,600 188,400 180,100 13,821,000 Sept.______ 330,200 Oct.. . 887,100 * Nov........ ..... 1,525,200 Dec..... : 2,045,500 a Jan............... 1,933,400 Feb............... 1,990,200 Mar 1,984,100 170,500 667,200 1,279,600 2,009,400 2,165,200 1,964,100 1,854,900 1,074,500 505,500 ...9..1.,6..00. ..... .... 146,200 703,100 1,341,200 1,861,500 1,749,400 1,806,200 1,800,100 Col. 4 Avc. Mean Temp. 65 53 44 25 22 28 31 43 55 61 52 39 28 30 30 31 Col. 5 Dec Days 65 F Base 146 339 641 1,233 1,297 1,106 1,032 647 303 50 Col. 6 Lb/Deg Day 1,170 1,966 1,990 1,630 1,670 1,775 1,799 1,660 1,670 1,830 Col. 7 Lb/Deg Day/ M Cu Ft 0.575 0.970 0.982 0.804 .0.822 0.888 0.885 0.818 0.822 0.905 167 410 812 1,120 1,044 1,111 1,021 875 1,718 1,653 1,660 1,670 1,624 1,760 0.431 0.845 0.815 0.817 0.825 0.800 0.868 If. for example, the heat-consumption in March, 1943, is compared with that in March, 1944, it will be found that in the latter the steam consumption is 1799 -- 176Q = 39 lb less which is a decrease of 2.2 per cent. `' be measured in several different ways. It may be taken as the instan taneous peak or as the rate of use during any specified interval. One method is to take the average of the three highest hours during the winter. These figures are available for a number of buildings in Detroit, as shown in Table 86. These maximum demands were measured by an attachment on the condensation meter and therefore represent the. amounts of condensation passed through the meter in the highest hours, rather than the true rate at which steam is supplied. There might be slight differences in these two quantities due to time lag and to storage of condensate in the system, but wherever this has been investigated it has been found to be negligible. The load factor of a building is the ratio of the average load to the maximum load and is an index of the utilization. Thus, in Table 8, the theaters, operating for short hours, have a load factor of 0.126 as compared with the figure of 0.318 for clubs and lodges. SEASONAL EFFICIENCY The task of predicting fuel consumption within reasonably accurate limits is a simple one where sufficient experience data are available for the fuel in question. Such data can be analyzed to the point where average unit factors can be determined and expressed in such terms as, for example, average gallons of oil actually burned per square , foot of calculated steam radiator surface per degree-day. The unit U can be inserted directly in Equation .2 without reference to efficiency. Such experience factors are available for gas (see Table 2). and for district steam (Table 6), but not for coal or oil. Since values of U are not available for oil or coal; an assumed seasonal efficiency E must be used. Selection of a value for this E must be made ' / 388 CHAPTER 20 .1946 Guide Table 8. Building Load Factors and Demands of Some Detroit Buildings Building Classification Clubs and Lodges............. Hotels____ Printing......... ...... ................................. Apartments Retail Stores...... ........ ............... Auto Sales and ServiceBanks... . . Churches._____________________ _ Department Stores__________ _______ Theaters . Load Factor 0.318 0.316 0.287 0.263 0.255 0.238 0.223 0.203 0.158 0.138 0.126 Lb of Demand per Hour per Sq Ft op Equivalent Installed Radiator Surface 0.184 0 207 0.217 0 200 0.225 0.182' 0.248 0.158 0.152 0.145 0.151 with caution, for its.use implies a meaning not commonly associated with the word efficiency and consequently is frequently misleading. The input of heat to a building consists not only of the energy in the fuel but that from occupants, the sun, appliances, processes, and all other sources. In many cases these make up, over a period, an important percentage of the total heat required, and if they are not taken into account a calculation of efficiency can show a figure over 100 per cent. For this and other reasons the actual seasonal efficiency is a difficult thing to determine. Published data are widely scattered and insufficient. From the available published material it is found that the seasonal effi ciency varies over a wide range, depending on the fuel used, and it varies widely even for a given fuel. For example, in a recent survey of 30 houses in one locality there was found a variation of from 45 to 75 per cent in the utilization efficiency depending on the fuel7. REFERENCES 1 Graphical Method of Calculating Heat Losses, by Paul D. Close (A.S.H.V.E. Transactions, VoI. 49, 1943, p. 345). ^""Standard Gravity Code for the Design and Installation of Gravity Warm Air Heating Systems (llth edition), and the Technical Code for the Design and Installation of Mechanical Warm Air Heating Systems (National Warm Air Heating and Air. Conditioning Association). 3--See Industrial Gas Series. House Heating (third edition), published by the American Gas Association. 4""Received from U. S. Weather Bureau.September, 1943. . .' s~Report of Commercial Relations Committee, Proceedings, National District Heating Association, 1932. *~The Heat Requirements of Buildings, by J. H. Walker and G. H.-Tuttle (A.S.H.V.E. Transactions. Vol. f1. 1935. p.. 171). v 7--Heat Losses and Efficiencies of Fuels in Residential Heating, by R. A. Sherman and R. C. Cross (A.S.H.V.E. Transactions, Vol. 43. 1937, p. 185). CHAPTER 21 Warm Air Leaders, Stacks, and Registers; Return Air Ducts, Grilles, and Shoe Connections; Outline of Design Procedure WARM air heating systems of the gravity type are described in this chapter l. In these systems the motive head producing flow depends upon the difference in weight between the heated air leaving the top of the casing and the cooled air entering the bottom of the casing, while in the mechanical type a fan may supply all or part of the motive head. ' In general, a warm-air furnace heating plant consists of a fuel-burning furnace or heater, enclosed in a casing of sheet metal, which is placed in the basement of the building. The heated air, taken from the top or sides near the top of the furnace casing, is distributed to the various rooms of the building through sheet metal warm-air pipes. The warm-air pipes in the basement are known as leaders, and the vertical warm-air pipes which ' are run in the inside partitions of the building are called stacks. The heated air is finally discharged into the rooms through registers which are set in register boxes placed either in the floor or in the side wall, usually at or near the baseboard. A sectional view of a typical plant showing good installation practice is given in Fig. 1. The air supply to the furnace is usually taken entirely from inside the building through one or more recirculating ducts, although in some cases an outside air supply duct is provided. WARM AIR LEADERS. STACKS, AND REGISTERS ' In a gravity circulating warm-air furnace system, the size of the leader pipe to a given room depends upon the length of the leader and the tem perature of the warm air entering the room at the register. For . most successful operation, the furnace should be centrally located with respect to register and stack positions so that the leaders will be of uniform length and as short as possible, in which case the frictional resistance to air flow and the temperature loss from the ducts will be about the same for all runs. In the Standard Code for Installation of Gravity Warm Air Heating Systems, the design was originally based on the heat carrying capacities per square inch of leader pipe area with register air temperatures of 175 F. In a recent revision of the.entire design procedure, as shown in the section entitled Outline of Design Procedure, the carrying capacities of leader pipes have been expressed directly in terms of Btu per hour. In general it is advisable to use two or more leader pipes to rooms requiring more than the capacity of a 12 in. round pipe. The tops of all sizes of leader pipes should be cut into the furnace bonnet at the same elevation, and from this point there should be a uniform upgrade of at least 1 in. per foot of run. Leaders over 12 ft in length, or having a large number of elbow fittings should be avoided if possible. In cases where such leaders are necessary, it is recommended that smooth transition fittings be used, and that duct insulation be applied. Asbestos paper, unless of the corrugated type, should not be considered as insulation. To assist in balancing the air distribution of the system, a damper should be placed in each leader pipe except one, this latter leader preferably . being connected to a room heated at all times, such as a living room. 389 / 390 CHAPTER 21 1946 Guide In a gravity circulating system, the ratio of stack to leader area is . quite important, although little is gained by providing wall stacks with areas in excess of 75 per cent of their connected leader pipe area. In most cases a 3J4 in- X 12 in. stack is the largest which can be installed in normal wall construction. Hence, any room having a heat loss much in excess of 9000 Btu per hour, will require two or more stacks, or one oversized stack built into a 6 in. studding space, providing the design register temperature is to be retained at the value of 175 F as recommended. Y-* ' - Gravity Warm Air Systems 391 First story registers may be of the baseboard or floor type, with the former location preferred. High sidewall registers in gravity systems deliver more warm air into the room than do baseboard registers, but most of the additional air merely results in high temperatures at the ceiling. return air ducts, grilles, and shoe connections The ducts through which air is returned to the furnace should be designed to minimize resistance to air flow. They should be of ample area, in excess of the total area of warm-air pipes, and should be stream lined. Horizontal ducts should pitch at least in. per foot downward toward the furnace, avoiding fittings which would require lifting of the return air after the duct has passed under some obstacle. The return air grilles should have free areas at least equal to the ducts to which they connect and should be installed in the floor, or in the base- Fig. 1. A Sectional View of a Typical Plant Showing Good Installation Practice3 . A. House chimney, no bends nor offsets, - B. Top of chimney at least 2 feet above ridge of roof. C. Flue lining, fireclay. D. All joints air tight. E. At least 8 in. brick. F. No other connection beside that to furnace. G. Cleanout frame and door, airtight. ' H. Smoke pipe, end flush with inner surface of flue. I. Draft door. J. Use flue thimble. L. Casing hood or bonnet, top of alfleader collars on same level. - K. Casing body. - M. Round leader, pitch 1 in. per foot. NJ Sleeve with air space around leader where nagging through wall. O.- Dampers in all leaders. P. Transition fittings. - - Q. Rectangular wall stack. R. Baseboard register. S. Distribute pipes equally around bonnet. T. Floor register. U. Return air face. V. Panning under joist. W. Transition collar. X. Round return pipe. * Y. Transition shoe. - Z. Top of shoe at casing not above grate level. From N.W.A.H.&A.C. Assn. Standard Code Application Manual. Registers used for discharging warm air into rooms should have a net area not less than the area of the leader pipe to which the register is attached., First story registers should be connected through boot and register box extensions having areas at least equal to leader areas. Upper story registers should be of the same width as the wall stack, and should be placed either in the baseboard or sidewall, preferably without offsets. Stcnr^ ujf Register jgj* FG HI Fig. 2. Typical Warm Air Boots board with the top edge of the grille not more than about 14 in. above the floor line. Frictional resistance in the return air system is as detrimental as is resistance in the warm-air system, so that care should be exercised in locating return air grilles which require long return ducts. The placement and number of return grilles will depend upon the size, details, and exposure of the house. Small compactly built houses may be adequately served by a single return grille effectively placed in the central hall. It is usually desirable to have two or more returns, provided that in two-story residences one return is placed to effectively receive the return air at the foot of the stairs. A return air connection must be carried to any room whose floor level is below that of adjacent rooms. "Where a divided system of two or more returns is used, the grilles must be placed- to serve the maximum area of cold wall or windows. Thus, in rooms having only small windows the grille can be brought as close to the furnace as possible, but if the room has large window exposure the grille should be located near the exposure. The frictional resistance of the . long ducts used in parallel with short return ducts must be reduced to compensate for the length. Return ducts from upstairs rooms may be. 392 CHAPTER 21 1946 Guide necessary in spaces which are closed off from the rest of the house or which have much outdoor exposure. Return grilles on different floor levels should not be connected to the same vertical return duct. Ducts returning air to the furnace should avoid heat sources which tend to reheat the return air. If the duct must be run over the top of the furnace, or above the vent pipe from the furnace, insulation should be interposed between the heat source and the duct. Circulation of air is facilitated if the air can slide down a pipe inclined at approximately 45 deg and into a furnace shoe connection having a cross-sectional area equal to that of the pipe. The top of the return shoe should enter the casing below the level of the grate in the case of a coal Up to 20' - Same as Type E except that col* !ar and shoe are same as for Type A. Ty(* F Note: For Types C, D, E, and F return-air duct systems, reduce the carrying capacities shown in Table 8 by 1 per cent for each 4 ft additional length in the horizontal run. Fig. 3. Typical Arrangements of Return-Air Duct Systems furnace, and not more than 14 in. above the floor in the case of oil or gas furnaces. In order to accomplish this the shoe is made wide. OUTLINE OF DESIGN PROCEDURE - The data underlying the design procedure are given in detail in a circular2 issued by the University of Illinois. In this procedure the design of the warm-air duct system is considered as an entire unit, so that for a given heat loss the sizes of leaders, stacks, boots, stackheads, and registers are all correlated. Similarly in the case of return ducts, the selection specifies a complete unit consisting of return grille, return duct, and shoe connection. Recommended Standard Sizes . For the purpose of simplification and standardization, selected com binations of commercial sizes of warm air pipes, return air pipes, ducts, grilles, fittings, and registers arc designated as Combination Numbers. The numbers assigned and the combinations selected as standard are listed in the following tables 3. Gravity Warm Air Systems 393 Table 1--Combination Numbers 1 to 5--First Story Warm Air Ducts and Registers. Table 2--Combination Numbers 11 to 16--Second Story Warm Air Ducts, Single Wall Stacks, Fittings, and Registers. . Table 3--Combination Numbers 21 to 24--Second Story Warm Air Ducts, Double Wall Stacks, Fittings, and Registers. - Table 4--Combination Numbers 31 to 38--Return Air Ducts, Fittings, and Grilles. The selected types of boots are shown in Fig. 2 and their resistances expressed in equivalent elbows are shown in Table 5. It is essential that free areas be maintained throughout fittings. The selected types of return air ducts and fittings are shown in Fig. 3. Table 1. First Story Warm-Air Ducrsa , Combination No. . Leader Pipe Diameter, In. 18 29 3 10 4 12 5 14 Floor . 8 x 10 9x 12 10 x 12 12 x 14 14 x 16 Register Size. In. Baseboard Size 10 x 8 12 x 8 12 x 9 13 x 11 ---------- - Extension 2K 2^ . 5H `When the calculations indicate a requirement for a given room greater than Combination No. 4, two or more smaller units totalling the required capacity are recommended. " - Table 2. Second Story Warm-Air Ducts--Single Wall Stacks and Fittings Combi nation No.. Leader Pipe Diameter, . In. . * Stack1* Size In. ' Floor Register Size, In. - Baseboard Size - Extension Sidewall n8 10 x 3Ji 8x 10 10 x 8 2J4 12 9 12 x 3 9 x 12 12 x 8 2J4 14 10 . 14 x 3J 10 x 12 12 x 8 2K 15 12 12 x 5M 12 x 9 3)i 16 12 14 x -- 13 x 11 5K 10x8 12 x 8 12 x 8 bRecommended stack sizes. Tables may also be applied to 3 in. and 3)4 In. stack depths. Table 3. Second Story Warm-Air Ducts--Double Wall Stacks and Fittings Combi nation No. " Leader Pipe Diameter, In. Sta^k Size, In. Internal. External . Floor Register Size, In. . Baseboard * Size Extension Sidewall 21 8 2HC * 10 3 x 10% 8x 10 22 8 3 x 10 3% x 10% 8 x 10 23 9 2W- x 12 3%c x 12%s 9 x 12 24 9 3 x 12 3% X12% 9 x 12 `Commercial sizes vary )4 in. from values, shown. 10 x 8 10x8 12x8 12x8 . 2M 2M 2M 2H 10-x 8 10 x 8 12 x 8 12 x 8 1 .'/ / ; 394 CHAPTER 21 1946 Guide Carrying Capacity ... .' . The. Btu carrying capacities'of the selected warm air and return air combinations are shown in Tables 6, 7 and 8: - . Table 6--Combination Numbers 1 to 5--Warm Air Carrying Capacities to first story registers with 1 to 5 elbows and with leaders 4 to 24 ft long. , Table 7--Combination Numbers 11 to 16 and 21 to 24--Warm Air Carrying Capaci ties to second story registers with 1 to 5 elbows with leaders 4 to 24 ft long. Table 8--Combination Numbers 31 to 38--Return Air Carrying Capacities for types Ay B, Cy D, E, and F return combinations. Table 4. Return Air Ducts . Combi , Duct nation Dia. No. In. Area at Shoe Con nection, Sq In. Metal Grille Sizes Choose One A Bc When Joist Lining When Duct is , is Used* Used No. of Minimum* Joists Depth. - Lined In. Choose One 31 .10 32 12 33 14 34 16 35 18 36 20 37 22 38 24 8x14 10x12 i 6x30 8x24 12x14 1. 170 8x30 10x24 14 x 16 1 220 10x30 12x24 2 280 12x30 14x24 -'2 340 14x30 18x24 2 420 18x30 2 500 20x30 2 7 9 12. 8 10 12.5 15.0 18.0 14 x 6 22 x 6 28 x 6 28 x 8 36 x 8 36x10 42x10 42 x 12 12 x 8 16 x 8 22 x 8 .22x10 28x10 30x12 36x12 36x14 d Based on 14 in. space between joists. . be Use used. full depth ' of . joist . except when joist depth is less than minimum depth required, . xo hen .pan must, Table 5. Resistances of Warm Air Boot Combinations Expressed in Elbow Equivalents , ' Warm Air Boot - A .B C D E F G H I: ' . Name of Combination . .Equivalent No. of 90-Deg Elbows ' `45-.Deg Angle Boot and 45-Deg Elbow 90-Deg Angle Boot . Universal Boot and 90-Deg Elbow ' End Boot ' Offset Boot ' .: . 45-Deg Angle . . / . Floor Register--Second Story . Offset * ' ' . ` - Offset : . ` i '1 i 2 2H > Vi '3 .3 2 ' . Design Procedure , . . The steps to be taken in designing a gravity warm air duct system are: 1. Calculate the heat loss from each room as explained in. Chapters 6, 8 and 14. . 2. Prepare a layout showing (a) furnace, (6) chimney connection, (c) warm air 'registers (whether floor, baseboard or wall), (d) return air grilles.- . 3. .Indicate on each warm air run (using symbols shown in Fig. 4): (a) whether the room to be heated is on the. first or second story, (6) the approximate length of leader ' pipe in the basement, (c) the number of right angle elbows required-, including the elbow at the boot connection (see Pig. 2), .(d) whether the register is to be located in the floor, in the-baseboard, or in the wall. . '_, > _ . . . . ' ._ 4r Show the number and proposed -locations of -return air grilles and the type of- return air system (see. Fig. 3). ... 1 . .. Combination No.. - Gravity Warm Air Systems. 395 T a b le 6 . W arm A ir Carrying Capacity, B tu D eliver ed , F irst Story R egisters5 . Length o f Leader P ip e -- in Feet' o04 oCD o^ oCDoCO 0rHo0 0CoN5 01o10 o0tt5*otrHo oCoO oOi--< oOcoot0o2oru-o o02 OrH Or-- 0>--!.l0-H 00 05OC0C0 oCr-OroI-OoCooOcCooNoo.Hs* CJ ' id go Oi cn Tf4 tO CD 02 CrHN Tt4 to CO .00 --4 CO TJ4 CO 00 rH CO to 00 o l-H LHh o0^50o000o--0eoI5Do0CO. oCtjO* ooocootoOooCxOo o0r-l)oC0O1oto5oC0OoC0N OOTJ4 OrrHHOCrHOOt<3o5Orto-. r0oH5 T0o5flOroHCcooOoCrO- Cl cMON OCO to CO C2 r!NH to co.05 CN N4 toco 00 -H co "h?4 co oo -h- OCcoO Oc0o5 Ofc-n OCcoN OCioO' ooooo U5N005- oCtOO oOtooO00otCOOoCcoO o0rH5oC0OXotO5'0CoN 0oCN tOoocroHo CCoOO 00o55o000 . Cl- ^UJNOCO to 02 co tjTioco'ocn--( ^ toco C5 CN hj4 to co co ---I OC0O0O1--^1 OTt5<ONOOto .NocoHo05Cocn5ocNooOco oHIOoONo^OOoOMoH otcoo ootoocro-occoooctoo' oOCN oCCON oCtoOcoCoNoCCNO tJI GO T- O ^ ^lON. OrCH rOH cf4 tor- o eo to co 05 cn re toco 05 CN tHb . OOO OCNO O0h0OCOOOUlOJ QOt}4OOr--HOtIoCOC02DOOOO oNCO0o<305oC2NUoCO5oC0O' otoo oCoOs ocOn or<3-2oo'-H OCtoO OOtoOO00OHCJO4 OtCoO ' mcoNfr-H'T*-*h COT- O T* to t- o*--1 Cl-HO 4* tor- 02 co H* toco 05 CN . toH- IohOJ4 orO-ot^oOotO OOO OCCNOO0O0OCOOttOo occoo oip--H octoooor-ooo oCtoO o0CO5oCCONorCHOoHto* OotooOC5OcOOorO-0<53Oo5 to CO CO rH to to CO -H T*4 T^cor-O'cr e4 tor- o co nf to r- 02 co Otc}o4 OCrO- OctJo4 OCoOoOttOo OC--O1 OCtoN OCOOCNO1OO'N4 O0055 OcrHoOoro-OotoO-t-oH oOCO o0O0oOtootCoOo0022 - oCX?O4 oC0O0oCCNOooCOoCtoN tO CO 00 rH to to CO OO i-h to . tji co r- i-h tj4 Ncor-co tor-oeo toH. OHtONO05OOCOHOCNTOofl. oCcOo'Cr-OcOCoN OoOo OOto oUH5toOHoCOOo^OOoN) oc<3o5 oCr-NoN.r4-o0055oC^N o0r-5 oCoO o0-x5j4 oCcoNot0o5 . ID CO 00 CN CO to CO 00 i-h to to CO 00 ii--Hh N^H4 N4 co r- o CONOCO O0CO0 OT0-0< OrCO-O0lO5OClOO o0h*54 o0T5t4 oOtoOo1t-4-o0055 oc-oH or-h- oocnoorto-o^t#* olr-HH oCNO4 o0002oCCOOo0CO0 O0t*54OctonOCrN-Ot0o5cOcoo GO tO t- 00CrH4 CrHO to CO 00 CN to ' ID CO 00 -H to to co r- ^H rH rJ4 CD r- -IHt. -- ,,ioono^Oh^NooNoo oCcoO oto oorJo4otooto oco o--054 otcoooo--1oo05 CocNooCcOoCooNr'C-oCO oCNO - o0O5 oTrt*44 ot0o5oC0N5o000 CO ` . tO T- 02 CN t- tOr-OOCNCO to CO 00 CN to. to CO 00 rrHH tro-- d cor- h CHx. oNocNooO^oeWoooNo. o0to0 oCcoO oCO5o<0--2!o0-c2 oCcoN oCi-HN or0-0ot-oroCcoO oCTpNo0C0OorCt4Ooo-Horr-- oCTNt4.oCCOOo0-H0ocrHooCtoN N* CO '05 CrHO trH-- to 02 cn co to r- co cn co toco CO CN to to CO 00 rH to cn si 65 H CN CO e4 ' to . za rH CN CO t*i to 1--< CN CO N4 to -H CN CO ^ to ^H CN CO to -h cn co -e4 to * if Additional values for`0 arid 7 elbows are given in original Mjanual. Combination No.b.o. 396 CHAPTER 21 ' 1946 Guide Length of Leader Pipe-- in Feet T a b l e 7 .' W a r m A ir C a r r y in g C a p a c it y , B t u D e l iv e r e d , Seco nd Sto r y R e g is te r s * 16 F t 24 F t 6,000 7,200 8,400 11,640 131570 22 F t OO O00O0005Ot0-0O005 ooTb*o--^c1oo0oo-^o0o--4* oO-H oC.-MH oF-^o00oCO Oo(50 bo-obCM.oe-hpooo ~t^---1--H o^Hf idco*bT--oHo--4 idcdb-^05 -h ^jTidcdoTo oC^MOoTOfi otM--ofO--ioOW oCCO5oh^Ho0C5Moooo* O04bOc^oOOcOoOO0O5Ob0- oOCO oCO oCM oOCMOoG0O5 o05^o05^oo0o5ocCoOoCoop - edb-*odc4 8* idb^oo^HHc-o4 *ddbTcMfH" idcdtCo idcdoTi--T bO- Obb--OoOOeo oI-QH oC0O0 oOIoC0O5o0-5< cdb^cTcM^ edb^ooi-red ooOobo-o^f oOHOCoCMM oCMoTO* o--N< "`r-`o`cM" `b-"` 1-H 5,830 6,990 8,160 11,300 13,180 20 Ft 18 F t -oNHOoinCodDooOooH) cobo-ocoCooMsocoCoM OOrt< OOfhO 004CO oot>-Oo^Ooo0o5oICOoO5 Neop'VoT*HoOooV CO 00 o> co edb^coedtjT cdb^odi-Tcd cdb^-H1--C1 M^H* ""b-*"cM~ oon oCeOo oCt--M oot--i< oOcoCoQ45C_oCOM oOooCo0O0 oCM oob-Co-MHohI-*H oo05 ooooCMot^*CoO oibop-OboONobW-obedcdcTcHdf-H cdb^05C--4< T-H cdt^odoi"-^* db^odi-Tcd `CO b^fH C.-MH* 6,110 7,330 8,550 11,830 13,810 5,750 6,900 8,050 11,140 13,000 oOHCNoOoCOOoCdMoNt* -Oc0o0Oo^n.1OI00Oc4oOet*o obT* ob-_o0CoO_Co4 b^oo cded edodosed cdb^oTc1M-H Tl-H* oco oooa ocoiorooooto>o o0-1o*0ob0-ob0-o05 oocOo_o-h_CoOo05_o----H<_ o--< o oCOoCMo CO 00 CM o035*eo--oi oHc*5OoCoMT* tCooo b-"oo" cd1 t-H odcS'cM* cdtCoocfMH ti--*I ~b-"oo" --fHTcfHd ocbo-oo-nhcoMooooct-o4 ooo oco oooooo Oo05No04U^oC5ONoCO0oI0O oCMoh00ohi-Hhobho OC--OiCOpiOp00oOOb*OOO o'o t-" `tsToo T*cd cocooned corses cm"h* cdb^odi-Tcd oO05 oNoomoCoOoGoO oO oO oOoCOoC0O5 o1fH-HoCM0o-r^JHofoOob-^ oCNMOoWo05Oo^obH OCcMpiO0p0OOOO-CHM*_O0CM0^ t-Ton -Tidb^ b^oT*r* CO b^odcTcded cdodoscdid edb^odCfMH*,id-H oocOoCOotOo05 boN^CoNMOoHOoNOSob^* oo on idoo b-ToTo ^b oCMCoMboC-DCoC5OCoM o^o10-(-oHoob.cdoooTcd "b-~05*CM~ t}h* 12 F t j' 10 Ft 7,320 8,780 10,240 14,180 16,550 8,370 10,040 11,710 16,200 18,920 7,940 9,540 11,120 16,400 17,980 oCO oCOoCOo00oo^ oCi-M^oCiOpooso0b0-oCoO bo0-^oO*boC-Obo0-5-or^H bToni-oH -fdHb?--^( 1 b^odosefHdei-Hd cdodorcMi--*H"fH . - CM eo CN4 Nt* hT* hh C0M4 0r4* tH* HH CCM4CTM*T>--*1iOi--Ci tO--' CCMM CTM* T--f(_i-H 1-H CCMM TCM* T-* rH V-t 1---H4 Ci-HN if--Hi 0fH4 iH-hCHM fh CM 8 Ft *W h e n floor registers are used, see F ig. 2. bN o. 21 fo r B tu values m u ltip ly 11-22 values b y 0.S3. *N o. 23 fo r B tu values m u ltip ly 12-24 values by 0.83. 6 Ft ." No. op Elbows Gravity Warm Air Systems 397 5. From Table 6, for first story, or from Table 7 for second story, select the combi-' nation number for the warm air system which will supply the heat required to each room, with the number of elbows and length of leader pipe previously determined. Then, using the combination number as found, read directly in Tables 1, 2, or 3 the leader, stack, and register sizes required. 6. From Table 8 select the combination number for the return air system to correspond:. with the Btu serviced and the type of return air system. Then from Table 4 select the duct and grille sizes, etc., corresponding to the same combination number. 7. Select a furnace having a register delivery, in Btu per hour, equal to the total heat loss from the structure. . ` Table 8. Return Air--Carrying Capacity--Btu Serviced. Return Air Com bination No. Duct Dia In. Type ABtu per Hr Types B and C Btu per Hr Type D Btu per Hr Type E Btu per . Hr Type F Btu per Hr Return Air Com bination No. 31 10 11,300 9,500 7,800 5,000 7,800 31 32 12 16,300 13,700 11,300 7,200 11,300 32 33 14 22,200 18,700 15,300 9,800 15,300 33 34 16 29,000 24,400 . 20,000 12,800 20,000 34 35 18 36,700 30,800 25,300 16,200 25,300 35 36 20 45,300 38,000 31,300 20,000 31,300 36 37 22 54,800 - ^ 46,000 37,800 24,100 37,800 37 / 38 24 65,200 54,800 45,000 28,700 45,000 38 Examples 1 and.2 will illustrate the use of the tables in selecting warm air and return system sizes. Example 1. For a room which has a heat loss of 22,500 Btu per hour select the size of first story warm air system. There are three elbows and the leader is approximately. 10 ft long. Solution: Since 22,500 Btu is beyond the capacities shown in Table 6, it is necessary to select two units of 11,250 each. From Table 6 in 10 ft leader column and in section for three elbows find 11,400 as nearest capacity which corresponds to Combination Num ber 4 in first column. Refer to Combination Number 4 in Table 1 and find that the leader should be 12,in. in diame ter and should-be used with a 12 x 14 in. floor register or a 13 x 11 in. baseboard register with a 5% in. extension. Example 2. What is the size of a return system of Type D which is to service 35,000 Btu. per hour? Solution: From Table 8 find Combination,Number 37 which will service 37,800 Btu per hour. Refer to Table 4 to find that Combination Number 37 will require a 22-in. diameter duct, a shoe area of 420 sq in., a metal grille 18 x 30 in., a duct 42 x 10 in. or 36 x 12 in. If joist lining is used the minimum depth x should be 15 in. for two 2-joist spaces 14 in. wide, or 10 in. for three joist spaces. Fig. 4. Typical Basement Line Drawing 398 CHAPTER 21 . :' ....................... : .. 1946 Guide ir space- open'- Insulated with airspace or cov ered with magnc' 3ks. asbestos, or sand. , Inner finer-from ~top casing ring to grate level - ffetof cosing Fig. 5. Details of Furnace Bonnet, Casing, and Foundation (From Gravity Code and Manual) Supporttojoist or ce/I/r- ` " Masonry wall. W6 . /fetal thimb/e. fair space all around pipe.. . asbestos paper' K'P/Tpfhght collar Insulated with 3 layers of air cellasbestos paper whenpipe passes thru unheaTed space. Fig. 6. Details of Bonnet and Leader of Gravity Warm-Air Furnace . (From Gravity Code and Manual) . .' Figs. 5 and 6 show recommended practice as given in the N.W.A.H. &A.C.` Assn. Gravity Code and Manual. For construction,, design features, and ratings of gravity furnaces see Chapter 18. . REFERENCES The engineering data were obtained from University of Illinois, Engineering Experiment Station Bulletins Nos. HI, 188, 189 and 246; Warm Air Furnaces and Heating Systems, by A. C. Willard, A. P. Kratz, V. S: Day. and S. Konzo. See also Gravity Code and Manual for Gravity Warm Air Heating Systems, published by the National Warm Air Heating and Air Conditioning Association.. . ^ . 2--Simplified Procedure for Selecting Capacities of Duct Systems for Gravity Warm-Air Heating Plants, by'A. P. Kratz and S. Konzo (University of Illinois, Engineering Experiment Station Circular 45, Dec., ' 1942). ... - . .. .. / *--Gravity Code and Manual for Gravity Warm Air Heating Systems. Second Edition. 1945; National Warm Air Heating and Air Conditioning Association. ` .. , .- CHAPTER 22 eenumea l *\AJarm Systems Air Distribution, Standard Combinations of Parts, Automatic Controls, Simplified Design of Heating System, Cooling Methods, Cooling System* Design IN mechanical warm air or fan. furnace heating systemsthe air circu lation is effected by motor-driven fans instead of by the difference in weight between the heated air leaving the top of the casing and the cooled air entering the bottom, as in gravity systems described in Chapter 21. The advantages of mechanical systems, as compared with gravity systems, are: . . 1. The furnace need not be centrally located but may be placed in any part of the . basement. . '- . 2. Basement distribution piping can be made smaller and can be so installed as to give full head room in all parts of the. average basement, or be completely concealed From view .where desired. ' -- 1 3. Circulation of air is positive, and in a properly designed system can be balanced in. such a way as to give a greater uniformity of temperature distribution. . 4. Humidity control is more readily attained. ' 5. The air may be cleaned by sprays or filters, or both. " . 6. The fan and duct equipment may be utilized for a complete cooling and dehumidi- fying system for summer, using either ice, mechanical refrigeration, or low temperature water for cooling and dehumidifying, or adsorbers for dehumidifying. ' 7. The use of the fan increases the volume of air which can be handled, thereby , increasing the rate of heat extraction from a given amount of heating..surface and insuring sufficient air volume to obtain proper distribution in a large room. 8. Ventilation air may be positively introduced and heated. The construction features of mechanical warm air furnace, units and discussions of the function and selection of the various parts, such as the furnace, casings, motors, filters and controls are included in.Chapter 18. AIR DISTRIBUTION The conditions of comfort obtained in a room are' greatly influenced by the type of register used and the locations of the supply registers and return grilles. In general it has been found that changes in the type, air velocity, and location of the supply register affect the room conditions much more than the changes in the location of the return grilles.' One method is to locate the supply register near the floor so that the warm air from the register blankets a cold wall, and mixes with the cold air dropping off from the exposed walls and glass.- Another method is to locate the supply openings near the floor on the inside wall and the return openings near the greatest, outside exposure. In any case-the warm air registers should be located so that the air stream never discharges directly into space that will normally be occupied by people at rest. Tests in the Warm Air Research Residence *. have' indicated that continuous fan operation provided better results than intermittent fan operation. Register and Grille - Openings . Supply registers located in the floor require attention to keep them clean and are-usually avoided. Tests, conducted in the Warm Air Research ' 399 400 . CHAPTER 22 1946 Guide Residence have indicated that comparable results are obtainable with either high side wall or baseboard registers, if proper registers and air velocities are selected. Baseboard registers should be of a deflectingdiffuser type which throw the air downward toward the floor and diffuse it at the same time. For baseboard registers air temperatures under 125 F and air velocities over 500 fpm should be avoided as they may cause drafts. High side wall registers must be of such type that the air is delivered horizontally or in a slightly downward direction, and must be so located as to avoid impingement of air on ceiling or wall. Directional flow diffusing type should be used to insure best results. Register air velocities Fig. 1. Recommended Type of BaseBOARD AND Low SlDEWALL' REGISTERS3 Fig. 2. Recommended Type of High SlDEWALL REGISTERS6 Vertical bars with adjustable deflection, or fixed vertical bars with deflections to right and left not exceeding about 22 deg. For low sidewall location; the deflection for horizontal, multiple'valve, registers should not exceed 22 deg. For baseboard locations, the deflection for horizontal,' multiple valve, registers should not exceed about 10 deg. . ^Horizontal valves, in back or front, to give downward deflections not to exceed from 15 to 32 deg;~ should be such that the air stream carries to the opposite exposure. Velocities under 500 fpm are not recommended. Basic rules for the location and selection of registers are given in Section C of the Code and Manual (Textbook Section 7) of the National Warm Air Heating and Air Conditioning Association. Registers should be well proportioned and decorated to harmonize with, the trim. Air supply registers'should be equipped with dampers and all registers should be sealed against leakage around edges. The register types shown in Figs. 1 and 2 have been recommended as standard by the National Warm Air Heating and Air Conditioning Association. Velocities through registers may be reduced by the use of registers larger than the connecting ducts. Diffusers should be used to spread the air uniformly over the register face. - '. - Return air grilles may be located in hallways, near entrance doors, ' under windows, in exposed corners, or inside walls, depending on location of supply registers. Baseboard returns are preferable to floor grilles. --Dampers - Suitable dampers for air direction or volume control are essential to any trunk or individual duct system. Special care must be used in the design . Mechanical Warm Air Systems 401 of any system to avoid turbulence and to minimize resistance. Sharp elbows, angles, and offsets should be avoided. Three types of dampers are commonly used. Volume dampers are used to completely cut off or reduce the flow through pipes. Splitter dampers are used where a branch is taken off from a main trunk. Squeeze dampers are Used for adjusting the volume of air flow and resistance through a given duct. It is essential that a damper with positive locking device be provided for each main or duct branch. Labels placed on ducts should indicate the room being served. Damper positions should be marked for summer and winter operation, and to avoid tampering. Ducts The ducts may be either round or rectangular in cross section. The radii of elbows should preferably be not less than one and one-half times the pipe diameter for round pipes, or the equivalent round pipe size in the case of rectangular ducts. Warm air ducts'passing through cold spaces, or where located in exposed walls, should have to 2 in. of insulation. Special attention should be given to the problem of noise elimination. The metal duct connection to and from the furnace casing and fan housing should be broken by strips of canvas. Motors and mountings must be carefully selected for quiet operation. Electrical conduit and water piping must not be fastened to, nor make contact with fan housing. Installation of a fan directly under a cold air grille is usually not recommended. STANDARD COMBINATIONS OF PARTS The combinations of parts selected as a standard by the National Warm Air Heating and Air Conditioning Association are shown in Tables 1 and 2. A method for selecting these combinations is indicated in the section entitled Simplified Method of Designing Domestic Forced-Air Systems. AUTOMATIC CONTROLS Air stratification, high bonnet temperatures, excessive flue gas tem peratures, and. heat overrun or lag in a properly designed system can be largely eliminated through proper care in the planning and installation of the control system8. Controls which are considered desirable for this system are: 1. A thermostat located in a living room where maximum fluctuation in temperature can be expected, in order to secure frequent operation of fans, drafts, and burners. The thermostat location should not be on an outside wall, in a bed room, bath room or sun room, or in a location where it will be affected by direct radiant heat from the sun or from a fireplace, or by direct heat from any warm air duct, register or chimney. 2. A fan switch control located in the bonnet to start blower operations at tempera tures between 110 and 130 F, and to stop the blower at about 25 to 30 F below the cut-in point. The lower settings are used for high side wall register installations, and the higher settings for baseboard register installations. For most satisfactory results these settings should be as low as is feasible., 3. A protective high limit switch located in the bonnet to stop the system independently of the thermostat if the bonnet-temperature exceeds 175 F. 7 4. On oil and gas burner installations, a protective control should be included which will stop the system if the fire is extinguished or if there is a failure of the ignition system. 5. On automatic stoker installations, a control is usually included which will start the operation regardless of thermostat settings whenever the bonnet temperature indicates that the fire is dying, or a time interval contactor is used that will start the stoker to run a few minutes out of each hour. . ... 6. A humidistal to regulate the moisture supplied to the rooms, located either in one of the rooms or in the main return duct near the furnace. . 402 ,________________ . CHAPTER 22 . . .. . 1946 Guide Table 1. . Warm Air Duct System Combinations of Parts Selected as Standard Combi Stack nation Size No. In. Branch Pipe Size. In. Register Size. In. ' (See Figs. 1 and 2) Round Rec tangular Base board, or Low Sidewall High Sidewall For throws For throws less than more than 13 ft 13 ft : -1 , . 2 .3 ' 4 5 6 .7 41 10x3Id 6 4x8 10 x 6 10x6 10 x 4 , Floor Regis- " TBRS*. Required Increase in Width of Trunk Duct. In. 8' 8 x 10 9. 1 42 10x3K 6 4x8 10 x 6 10x6 10 x 4 8 x 103 2 43 12 x 3K 7 5x8 12 x 6 12 x 6 12 x 4 9 x 12a 3 44 14 x 3K 8 __ 6x8 14 x 6 14 x 6 14 x 4 .9 x 12a or longer 4 45 10x3% (2-Stacks) 9 8x8. (2) 10 x 6 (2) 10x6 (2) 10x4 10 X 12a or ' or or (1)24x6 (1)24x6 (1)24x4 6 46 12x3^ (2-Stacks) 10 10 x 8 (2) 12 x 6 (2) 12 x 6 (2) 12 x 4 12 x 14a or or or (1)30x6 (1)30x6 (1)30x4 7 *Use these items only when the building construction or capacity requirements necessitate the use of floor registers. The sizes listed for floor registers correspond to the standard sizes for gravity warm-air systems, except for the sizes of the floor box collars. The use of standard blind boxes is suggested. SIMPLIFIED METHOD OF DESIGNING DOMESTIC FORCED-AIR SYSTEMS A simplified method for selecting, the combinations of branches, boots, stacks, and registers, is given in the Code and Manual (Textbook.section No., 7) of the National Warm Air Heating and. Air Conditioning Associa tion. In this method the sizes of the branch ducts are obtained from two tables giving their Btu-capacities. The proper combination of parts for each branch can be determined if the following information is available. a. Location of room, that is, whether on first or second story.' _" , b. Actual length of basement duct from bonnet to boot>in feet. c. Btu loss from room to.be heated. . . =. . d. Equivalent lengths in feet Of all fittings and of the register. Fig. 3 shows the values of equivalent lengths of fittings ^commonly, used for domestic systems. This simplified method is applicable to structures having heat losses not in excess of approximately 150,000 Btu per hour. The capacities shown in Tables 3 and 4 are based upon the most reliable, data'pertaining ' to friction losses and temperature drops in ducts. They are also-based upon a 100 deg temperature rise of the air, and a static pressure available for overcoming friction losses in the external duct system alone of 0:20 in. water gage.' The Use of this method assumes that the fan in the fan- furnace assembly will be capable not only of overcoming the resistance of' the external duct system alone, but also the resistances imposed, by the . blower inlet, the filter, and the furnace casing. . . . Mechanical Warm Air Systems 403 Table 2. Return-Air Duct. System Combinations of Parts Selected as Standard ' Combi nation . No. Return-Air Intake Size, In. Base board Floor* -1 . 51 2 10 x 6 3 6x 10 or 4 x 14 Riser Size. In. Where Stack is. Used in Stud Space Branch Pipe Size, In. Round Rec- TANGULAR When Joist Lining ' IS USEDb Number of Joist Spaces Lined and Minimum Depth of ' Space Required Required Increase in Width of Trunk, Duct (for ; 3 In. Depth of duct). In. 4 5 6. 7 8 10 x3Kc 6 4x8 1 space of 3 in. depth 1 52 10x6 6x 10 10 x 3KC 6 4x8 1 space of 3 in. .2 or depth 4 x 14 53 12 x 6 6x 12 12 x 3Md 7 5x8 1 space of 4 in. or depth 6 x 14 3 54 14x6 6 x 14 14 x 3>d 8 6x8 1 space of 5 in. *4 depth 55 24x6 6 x 30 . Two 9 8x8' 1 space of 6 in. 6, or stacks depth or 2 spaces 30x6 each of 3 in. depth 10 x 3 Yf 56 30 x 6 6 x 30 Two 10 10 x 8 1 space of 7 in. 7 stacks depth or 2 spaces 12 x of 4 in. depth 57 8 x 30 12 15 x 8 1 space of 9 in., 11 depth or 2 spaces of 5 in. depth Use these items only when building construction, or capacities, requires the use of floor intakes. The sizes listed correspond to standard sizes for gravity installations, except floor box collars. The use' of . standard blind boxes is suggested. - ' . bBased on 14 in. space between joists. Use full depth of joist, except when joist depth is less than mini mum depth required, in which case a drop pan must be used. This may occur when two or more return ducts are connected to the same joist space. , ' . ' elf it is desired to use 14 in. x 3% in. stud space, it makes no difference whether this space has pro- ' trading keys or not. -1 '. dlf it is desired tqoise 14 in. x 3H in. stud space, the plaster base must be smooth, without any pro truding piaster,keys to interfere with the flow of air. , The combination numbers shown in the right hand column of Tables 3 and 4 correspond to those given in Tables 1 and 2. ' Tables 3 and 4 are also applicable for the selection of the return air branches. A depth of 8 in. has been adopted .as the standard for the trunk ducts. The width of a trunk duct serving two. branches is deter mined by adding to the width of the remote branch the value shown in column 9 of Table 1, or column 8 of Table 2. .' ' For buildings having.a heat loss in excess of 150,000 Btu per hour the design procedure may be that given in the Technical Code, Fourth Edition, of the National Warm Air Heating and Air Conditioning Association. Air ' duct sizes and air distribution may also be calculated in accordance .with . data given in Chapters 40 and 41. ! .' . COOLING METHODS , A slight cooling effect may be obtained under certain conditions by the use of the cooler basement air. A more positive cooling effect may be 404 CHAPTER 22 1946 -Guide Mechanical Warm Air Systems Croup 5 Ft 5. Branch Ang/es and E/bows (not including boots) - to Fq.Ft. 30 Eg. Ft 5 EgFt. p Fp. Ft e 40 Eg. Ft. Sharp Sharp GROUP b. Boot from Branch to Stack.. 405 obtained by the use of an air washer where the temperature of the city or well, water is sufficiently low (55 F or lower), and where a sufficient volume of water can be provided. Unless the temperature of the leaving water is below the dew-point temperature of the indoor air at the time the washer is started, both the relative and absolute humidities will be somewhat increased. ' Coils of copper finned tubing through which-cold water is pumped are available for cooling. They require less space than air washers and have the advantage that no moisture is added to the air when the temperature ' of the water rises above the dew-point. Ample coil surface and fan capacity are necessary with'this type of cooling. . . ' It is thoroughly feasible to use ice or mechanical- refrigeration in con nection with a warm air system and to cool the building by this method; Ouct tefow joist- 30 {Includes Return Intake) 50 {Includes Return,, Intake) Croup 7. Registers (.Including tosses in stackhead and velocity pressure) ` TABLE 7. Equivalent Length for Registers. (See diagrams at right) Deflec Baseboard High Sidewall Register tion or Low For throw of air of Angle Sidewall less than over 7. Register 13 feet 13 feet O'. 35 Eg. Ft 35Egft. 70 Eg. Ft. 15' 40 - - 40 - - 80 - - ZZ' 45- - 45 - ' 40 - ' 30' 60 - - 60 - - II5 ~ - 45'. U5 U5 - - Z30- - Notes for Table 7. a) When turning vanes are used <n stack- head use 0.7 of values tn columns 2 to4. b) Values shown in 2nd and 3rd columns in Table are for bin height registers (Standard height), and those in 4th column are for 4in. height registers. . For 5in. height registers, multiply values in Col. 2 and 3 by 13 For 0in. height registers, multiply values in Col. 2 and 3 bif 0.8_________ For 2-way deflection registers, add the vertical and horizontal deflection angles - together and multiply by 0.7. 5elect closest angle 'am in Col. I of Table 7 Fig. 3. Equivalent Length of Fittings (Continued) provided the building is reasonably, well constructed and insulated. Windows and doors should be tight, and awnings should be supplied on the sunny side of the building. (See also Chapters 38, 39 and 43.) Conclusions drawn from studies4 conducted in the University of Illinois Research Residence, subject to the limitations of the test are: ,1. An uninsulated building of ordinary residential type may require the equivalent of three tons of ice in 24 hr on days when the maximum outdoor temperature-reaches 100 F if an effective temperature of approximately 72 deg is maintained indoors. 2. The use of awnings at all windows in east, south, and west exposures may result in savings of from 20 to 30 per cent in the required cooling load. . . 3. The cooling load per degree difference in temperature is not constant but increases as the outdoor temperature increases. 1406 CHAPTER 22 1946 Guide Table 3. ' Capacity Tables for Warm-Air and Return-Air Branches*1* ' FIRST STORY For UNINSULATED Metal Ducts ACTUAL LENGTH from bonnet to boot) or. FROM RETURN PLENUM TO BOOT) IN FEET 1 TO 7 FT 8 TO 13 TO 18 TO 25 to 35 to 45 to 55 to 12 FT 17 FT 24 FT 34 FT 44 FT 54 FT 64 FT . 1 Col. a Col. b Col. c Col. D Col. e Col. f Col. c Col. h Warm Air Combi nation No. Re turn Air .Combi nation No. Section' A. 40 to 69 . Equivalent 7200 6700 6100 5600 4800 4100 3500 12500 11700 10800 9900 8500 7400 6400 16000 15000 14000 13000 11300 9900 8700 19100 18000 17000 16000 14200 12500 11000 3000 5500 7700 9600 41 42 43 44 51 52 53 54 Fittings and Register 25000 23400 21600 19800 17000 14800 12800 11000 - 45' 32000 30000 28000 26000 22600 19800 17400 15400 46c 80000 75000 70000 65000 56500 49500 43500 38500 55 56 57c Section B. 70 to 99 Equivalent Ft 5500 5100 4800 4500 3900 3400 9900 9200 8600 8100 7100 6200 13100 12300 11600 10900 9700 8500 16300 15400 14500 13700 12200 10800 3000 2600 5400 4600' 7500 6500 9500 .8300 r 19800 18400 17200 16200 14200 12400 10800 9200 26200 24600 23200 21800 19400 17000 15000 13000 65500 61500 58000 54500 48500 42500 37500 42500 41 42 43 44 45c 46c 51 52 53 54 55 ' 56 57c Section C. 100 to 139 Equivalent . 4400 4200 3900 3700 3200 8100 7600 .7100 6600 5800 10800 10100 9600 9000 8000 13700 12900 12100 11300 10000 2900 5100 7100 8900 2600 4500 6200 7900 2300 4000 5400 7000 41 42 43 44 51 52 53 . 54 16200 15200 14200 13200 11600 10200 9000 8000 21600 20200 19200 18000 16000 14200 12400 10800 54000 50500 48000 45000 40000 35500 31000 27000 45c 46c 55 56 57c Section D. 140 to 189 Equivalent '' Ft 3900 6900 9300 11600 3700 6500 8700 11000 3500 6100 8100 10400 3300 5700 7600 9800 2900 5100 6800 8700 2500 4500 6000 7700 2200 4000 5300 6800 2000 3600 4700 6000 13800 13000 12200 11400 10200 9000 8000 7200 18600 17400 16200 15200 13600 12000 10600 9400 . 46500 43500 40500 38000 34000 30000 26500 23500 Section E. 190 to 250 Equivalent' 3300 5700 7800 9700 3100 5400 7300 9100 2900 5100 6900 8600 2700 4800 6500 8100 2500 4300 5700 7300 2200 1900 380ft 3400 5000' 4400 6500 5800 1700 3000 3900 5100 41 42 43 44 , 51 52 53 54 . 45c 55 46? 56 57c 41 51 42 52 43 53 44. 54- 11400 10800 10200 9600 8600 7600 6800 6000 15600 14600 13800 13000 11400 10000. 8800 7800 39000 36500 34500 32500 28500 25000 22000 19500 45c 46c 55 56 57c Col. a Col. b Col. c Col. d Col. e Col. f For ducts that are COM- For : . PLETELY INSULATED INSULATED i TO 10 TO 18 TO 25 to 35 to 55 to WITH V4 IN. THICK .INSULA- Ducts . 9 FT 17 FT 24 FT 34 Ft 54 FT ' 74 FT tion from Bonnet to Boot. use these column headings. - "These tables are for use in sizing both the warm air and the return air branches. ^Frictional resistances and temperature drops in ducts have both been accounted for in these tables. . "Use these items only when the building construction, or capacity requirements, necessitates the use of two adjoining stacks or floor registers. . ' ' _ - 1 Mechanical Warm Air Systems 407 Table 4. .Capacity Tables for Warm-Air and Return Air Branches^ SECOND STORY For UNINSULATED Metal Ducts a/"*tTTAT I FNirTIT (FROM BONNET TO BOOT) OR. A ^ n (FROM RETURN PLENUM TO BOOT) IN FEET 1 TO 8 TO 13 TO 18 TO 25 to 35 to 45 TO 55 to 7 FT 12 FT 17 FT 24 FT 34 FT 44 FT 54 FT 54 FT Warm Air Combi nation No. Re- v TURN Air Combi nation No. COL. A Col. b Col. c Col. d Col. e Col. f- Col. g Col. h Section A. 6300 5700 5200 4800 4100 3500 3100 2800 41 10900 10000 9200 8500 7300 6400 5600 5000 42 40 to 69 14000 13000 12100 11400 10000 8800 7800 6800. 43 , Equivalent 17000 15900 14900 13900 12400 11100 9900 9000 44 Ft for Fittings ` 21800 20000 18400 17000 14600 12800 11200 10000 ,45c and 28000 26000 24200 22400 20000 17600 15600 13600 46c Register ' 70000 65000 60500 57000 50000 44000 39000 34000 51 52 53 .54 55 56' 57c Section B. 70 to 99 Equivalent Ft . 5000 4600 4300 4000 3400 9000 8200 7600 7100 6200 11900 11000 10300 9600 8400 14800 13900 13000 12200 10800 3000 5400 7500 9600 2700 4700 6700 8500 2300 4200 6000 7500 41 -.42 . . 43" 44 18000 16400 15200 14200 12400 10800 9400 8400 23900 22000 20600 19200 16800 15000 13400 12000 59500. 55000 51500 48000 42000 37500 33500 30000 45c 46c 51 52 53 54 55 . 56 57c Section C. 4100 3800 3600 3400 7400 6900 6400 6000 100 to 139 . 10000 9300 8700 8100 Equivalent 12500 11600 10800 10100 2900 5200 7100 9000 2600' 4600 6200 8000 2300 4000 5500 7200 2000 3600 .4800 6500 . Ft 14800 13800 12800 12000 10400 9200 8000 7200 20000 18600 17400 16200 14200 12400 11000 9600 50000 46500 43500 40500 35500 31000 27500 24000 41 42 43 V 44; 45c 46c 51 52 53 54 55 56 57c Section D. 140. to 189 Equivalent Ft . . .. 3700 3400 6500 6000 8600 8000 10900 10100 3100 5600 7500 9400 2900 5300 .7000 8800 2600 4700 6100 7800 2200 4100 5400 6900 2000 3700 4800 6100 1800 41 3300 42 4300 43 5400 ' 44. 51 52 53 54 13000 12000 11200 i0600 9400 8200 7400 6600 17200 16000 15000 14000 12200 10800 9600 8600 43000 40000 37500 35000 30500 27000 24000 21500 45c . 55 46c 56 ' 57c Section El 190 to 250 Equivalent Ft 3200 5500 7300 9100 2900 5200 6800 8500 2700 4800 6300 7900 2500 4400 5900 7500 2200 1900 3900"1 3400 5100 4500 6600 5900 1700 3100 3900 5200 1500 2800 3500 4700 41 42' - 43 44 51 52 53 54 11000 10400 9600 880b 7800 6800 6200 5600 14600 13600 12600 11800 10200 .9000 7800 7000 36500 34000 31500 29500 25500 22500 19500 17500 45c ' 55 46c 56 57c For . INSULATED Ducts Col. a I TO 8ft Col. b 9 TO 14 FT ; Col. c Col. d Col. e 15 TO 21 to 28 to 20 ft- 27 FT 42 FT. For ducts that are Col. f Col. g COMPLETELY IN SULATED with 43 to 55 to . IN. THICK INSULATION 54 FT 70 FT from Bonnet to Boot use these column headings. These tables are to use in sizing both the warm air and the return air branches. . ' ` ^Frictional resistance and temperature drops in ducts have both been accounted for in these tables. "Use these items only when the building construction, or capacity requirements, necessitates the use . of two adjoining stacks or floor registers. 408 CHAPTER 22 1946 Guide ' 4. The heat lag of the building complicates the estimation of the cooling load under any specified conditions and makes such estimates, based on the usual methods of computation, of doubtful value. . 5. The seasonal cooling requirements are extremely variable from year to year, and the ratio between the degree-hours of any two seasons occurring within a 10-year period may be as high as 7.5 to 1. Hence an average value of the degree-hours cooling per season is comparatively meaningless. . 6. The duct system in a forced-air heating installation can be successfully converted to a system for conveying cool air for the purpose of cooling the structure. 'No conden sation of moisture was observed when the duct temperatures were not less than 65 F. 7. Cooling by means of water at a temperature of 60 F is not satisfactory unless an indoor temperature of less than 80 F is maintained. 8. In the selection of cooling coils, the additional frictional resistance of the coil to flow of air must be given consideration. _ . 9* Cooling the structure by introducing large quantities of air from outdoors at night tended to reduce the amount of cooling required on the following day and was a practical means of providing more comfortable conditions in those homes where cooling systems were not available. ' .' METHOD OF DESIGNING COOLING SYSTEM The general procedure which may be used for the design of a summer cpoling system in a forced-air installation is: ' ' -/ . 1. Calculate heat gain for each room or space to be conditioned. (See Chapters 6 and 15.) Allowance for addition of outside air must be included in this calculation. 2. Select a temperature of air leaving supply inlets. In Research Residence tests a value of from 65 to 70 F was found satisfactory. 3. Determine indoor conditions to be maintained. In Research Residence 80 F drybulb and 45 per cent relative humidity were found satisfactory. 4. Determine the quantity of air to be introduced into each room. (See Chapter 43.) 5. Estimate heat loss in duct system between cooling unit and supply registers. 6. Calculate the sensible and latent heat to be removed by the cooling unit. 7. Determine size of ducts in duct system and size of registers, as explained in Chap ters'40 and 41. 8. Determine pressure loss in duct system and select fan as also explained in the same section. . 9. Select cooling unit from manufacturer's data. Specify temperature and pressure, of available cooling water, voltage and characteristics of electrical supply, and method of control of apparatus. . . - ' 10. Select cooling coils from manufacturer's data to take care of latent heat load and . to give required drop in air temperature with the weight of air flowing. (See Chapter 7.) II. If system is to be used for both winter heating and summer cooling, duct sizes must be checked to insure that velocities and friction losses are reasonable for both conditions of operation.. Adjustable dampers will be necessary to make changes in air - distribution for the two seasons. Provision must also be made for changing fan speeds for summer and winter operation. '. , REFERENCES ^Specifications for the furnace unit and the installed duct system are shown in The Yardstick (Text-' book Section 8) and the Code and Manual (Textbook Section 7) published by National Warm Air Heating and Air Conditioning Association. - *--Performance of a Forced Warm-Air Heating System as Affected by Changes in Volume and Tern-- perature of Air Recirculated, by A. P. Kratz and S. Konzo (A.S.H.V.E. Transactions, Vol. 48. 1942, p. 393). : / Automatic Controls for Forced-Air Heating Systems, by S. Konzo and A. F. Hubbard (A.S.H.V.E. Transactions, Vol. 40, 1934, p. 37). . -. s ' *--Summer Cooling in the Research Residence, by A. P. Kratz, S. Konzo, M. K. Fahnestock and E. L. .'Broderick (University of Illinois Engineering Experiment Station Bulletins Nos. 290,305 and 321). A.S.H.V.E '.Research Report No. 1177--Summer Cooling in the Research Residence with a Gas-Fired Dehydration 'Cooling Unit, by A. P. Kratz, S. Konzo and E. L. Broderick (A.S.H.V.E. Transactions. Vol. 47. 1941. j>. 203). ' CHAPTER 23 ^team ^JJeatincj. ^Systems and piping. Classification, Piping for Steam Heating Systems, Steam Flow, Pipe Sizes, Indirect Heating Units, Types of Heating Systems, High Pressure Steam Systems, Boiler Connections, Condensa tion Return Pumps, Vacuum Pumps, Traps, Control Valves, Connections to Heating Units STEAM heating systems may be classified according to any one of or combination of the.following features: (1) the piping arrangement, (2) the method of returning the condensation to the boiler, (3) the acces sories used, (4) the method of expelling or removing the air from the system, (5) the type of control used, and (6) the pressure or vacuum conditions obtained in operation. In all heating systems, the condensation is returned to the boiler either , by gravity or by mechanical means. In gravity systems the condensate is returned by gravity due to the static head of water in the return pipes or mains. The elevation of the boiler water line must be sufficiently below the lowest heating unit, steam pipe or dry return pipe to permit the return by gravity. The water line difference forming the static head must be sufficient to overcome the maximum pressure drop in the system, including the pressure drop due to the condensing effect of the radiation. When radiator and drip traps are used, as in two-pipe vapor systems, the static head must also exceed the operating pressure of the boiler. The pressure drop caused by condensing rate of the radiation is especially important during those portions of the operating periods, when changing pressure conditions prevail, as for example, when the system is being initially filled with steam. In systems where the condensate is wasted, to the sewer, no water line difference is required. However, the waste of condensate may introduce conditions which warrant the use of an appropriate mechanical return system. Whenever the conditions of a heating system are such that the condensate cannot gravitate to the boiler, it must be returned by some mechanical means. In mechanical systems the condensate flows to a receiver by gravity and is then forced into the boiler against its pressure. In all instances the preferable practice is to provide for gravity flow even when .a vacuum pump is used. The lowest parts of the supply side of the system must be kept sufficiently above the water line of the receiver to insure adequate drainage of water from the system. ._ There are three general types of mechanical return devices in common use, namely, (1) the mechanical return trap, (2) the condensation return ' pump, and (3) the vacuum return line pump. PIPING FOR STEAM HEATING SYSTEMS , The functions of the piping system are the distribution of the steam, the return of the condensate and, in systems where no local air vents are provided, the removal of the air. The distribution of the steam should be rapid, uniform and without noise, and the release of air should be facili tated as much as possible, as an air bound system will not heat readily nor properly. In designing the piping arrangement it is desirable to. maintain equivalent resistances in the supply and return piping to and 409 ' 410 CHAPTER 23 1946 Guide from a radiator. Arranging the piping so the total distance from the boiler to the radiation is the same as the return piping distance from theheating unit back to the boiler tends to obtain such a result. The condensation which occurs in steam piping as well as in radiators must be drained to prevent impeding the ready flow of the steam and air. The effect of back pressure in the returns and excessive revaporization, such as occurs where condensation is released from pressures considerably higher than the vacuum or pressure in the return, must be avoided. It is important that steam piping systems distribute steam not only at full design load but during excess and partial loads. Usually the average winter steam demand is less than half of the demand at the design outside temperature. Moreover, in rapidly warming up a system even in moder ate weather, the load on the steam main and returns may exceed the maximum operating load for severe weather due to the necessity of raising the temperature of the metal in the system to the steam temperature and the building to the design indoor temperature. Investigations of the return of condensation have revealed that as high as .143 per cent of the design condensation rate may exist under conditions of actual operation. . The piping design of a heating system is greatly, influenced by its operating characteristics. Heating systems do not operate under constant conditions as they are'continually changing due t(^ variation in load. As the system is being filled with steam the pressures'existing in various -locations may be different from those which exist for appreciable periods ' at other locations although at equilibrium conditions the pressures are approximately the same. In designing piping it is of especial importance , . to arrange the system to preclude trouble caused by such pressure' dif ferences. The systems which readily release the air permit uniform pressures to be attained in;much shorter time intervals than those which are sluggish. Results are given in Fig. 1 from investigations1 to deter mine the rate Of condensate and air return from a two-pipe gravity heating system. Variations'in the steam pressure during the warming-up period . when the rate of air elimination and condensation is high are clearly' indicated in these curves. ' ' - It is evident that the condensation flow during the initial warming-up - period reaches a peak' which1 is greater than the-constant condensation . - rate eventually reached when the pressure becomes uniformr Moreover,. Steam- Heating Systems and Piping 411 the peak condensation rate is obtained when the system steam pressure is' lower than that existing'during a period of constant condensing rate. It will also be noted that .the peak rate of air elimination does not coincide with the higher condensing rate. - STEAM FLOW ^ The rate of flow of dry steam or steam with a small amount of water flowing in the same direction is in accordance with the general laws of gas flow and is a function of the length and diameter of the pipe, the density of the steam, and the .pressure drop through the pipe. This relationship has been established by Babcock in the formula given at the top of Table 1. In Columns 1, 2, 3, and 4 of this table, the numerical values of the factors for different pressure losses, pipe diameters, steam-densities and lengths of pipe have been worked out in convenient form so that the steam flowing in any pipe may be calculated by multiplying together the proper factors in each column as shown in the example at the bottom of the table. PIPE SIZES The determination of pipe sizes for a given load in steam heating depends on the following principal factors: 1. Theinitial pressure and the total pressure drop which may be allowed between the source of supply and the end of the return system. 2. The maximum velocity of steam allowable for quiet and dependable operation of the system, taking into consideration the direction of condensate flow. * 3. The equivalent length of the run from the boiler or source of steam supply, to the farthest heating unit. . . - 4. The direction of flow of the condensate, whether against or with the steam. Initial Pressure and Pressure Drop - Theoretically there are several factors to be considered,.such as initial pressure and pressure required at the end of the line, but it is most import ant that: (1) the total pressure drop does,not exceed the initial gage pressure of the system and in actual practice it should never exceed one- half of the initial gage pressure'; (2) the pressure drop is not so great as to cause excessive velocities; (3)-there is a constant initial pressure, except on systems specially designed for varying initial pressures, such as the sub-atmospheric, which normally operate under controlled partial vacua, and orifice and vapor systems which at times operate under such partial vacua as may be obtained due to the condition of the.fire; and (4) the equivalent head due to pressure drop does not exceed the difference in level, for gravity return systems; between the lowest point on the steam main, the heating units, or the dry return, and the boiler water line. All systems should be designed for a low initial pressure and a reason ably small pressure drop for two reasons: first, the. present tendency in steam heating unmistakably points toward a constant lowering of pres sures even to those below atmospheric; second, a system designed in this manner will operate, under higher pressures without difficulty. When a system designed for a relatively high initial pressure, and a relatively high pressure drop is operated at a lower pressure, it is likely to be noisy and have poor circulation. ' ... The total pressure drop should never exceed one-half of the initial gage pressure when condensate is flowing in the same direction' as the steam. Where the condensate must flow counter to the steam, the governing 412 CHAPTER 23 _________ ' 1946 Guide Table 1. Flqw of Steam jn Pipes P ! loss in pressure in pounds per square inch. D : inside diameter of pipe in inches. L = length of pipe in feet. d 8 weight of 1 cu ft of steam. W : pounds of steam per hour. VoW = 5220 PdD` (*)P = 0.0000000367 W'L dD6 Pn*aTn> Loss IN Ounces Col. 1 Fife Size / p Actual 5220\-4/--1-0-0- Nominal Internal Diameter Internal Area or Pipe Sq Inches Col. 2 V'+T Steam Press. psig Col. 3 {7 Length op Pipe IN Feet Col. 4 /loo v-- 0.25 0.50 1.00 2 3. 4 5 6 7 8 10 12 14 16 20 65.28 92.28 130.5 184.6 226.0 261.0 291.8 319.7 345.3 369.1 412.7 452.0 488.3 522.0 583.6 1 IX m 2 2X 3 3X 4 iX 5 6 7 8 9 10 1.049 1.380 1.610 2.067 2.469 3.068 3.548 4.026 4^506 5.047 . 6.065 7.0237.981 8.941 10! 020 0.864 0.536 -1.03 0.187 1.496 1.178 --0.5a 0.190 2.036 1.828 0.0 0.193 3.356 4.788 3.710 6.109 0.3 0.195 1.3 6.201 7.393 11.183 2.3 0.207 9.887 16.705 5.3 0.223 12.730 23.631 10/3 0.248 15.947 32.134 15.3 0.270 20.006 43.719 20.3 0.290 28.886 71.762 30.3 0.326 38.743 106.278 40.3 0.358 50.027 149.382 50.3 0.388 62.786 201.833 60.3 0.415 78.854 272.592 75.3 0.452 20 40 60 80 100 120 140 160 180 `200 250 300 350 400 450 2.240 1.580 1.290 1.120 1.000 0.912 0.841 0.793 0.741 0.710 0.632 0.578 0.538 0.500 0.477 - 24 . 28 - 32 ' 639.3 690.5 738.2 12 14 16 12.000 13.250 15.250 113.098 437.503 100.3 0.507- 500 137.880 566.693 125.3 0.557 600 182.655 816.872 150.3 0:603 , 700 40 825.4 Column 1 X 2 X 3 X 4 ' lb of steam 175.3 0.645 `800 per hour that will flow through a straight .48 904.1 pipe for a given condition. 200,3 0.685 900 Example 1: 1. oz drop -- 2 in. pipe 80 1167.2 ' -- 1.3 lb press. -- 100 ft equivalent length: 1000 160 1650.7 130.5 X 3.710 X 0.201 X 1 = 97.2 lb per hour. 97.2 X 4b = 388.8 sq ft equivalent radiation. 1200 320 2334.5 ` .Table 1 does not allow for entrained water in low-pressure steam, condensation in covered pipe and roughness in com 1500 mercial pipe as found in practice. .480 2859.1 2000 0.447 0.407 0.378 .0.354 0.333 0.316 0.289 0.258 0.224 Pounds per square inch gage = 2.Q4 in. Vacuum, Mercury Column. ' bThe factor 4 is the approximate equivalent in square feet of steam radiation of 1 lb of steam per hour. Steam Heating Systems and Piping 413 factor is the velocity permissible without interfering with the condensate flow. A.S.H.V.E. Research Laboratory experiments limit this to the capacities given in. Table 2 for horizontal pipes at varying grades. . Maximum Velocity . The capacity of a steam pipe in any part of a steam system depends upon the quantity of condensation present, the direction in which the condensate is flowing, and the pressure drop in the pipe. Where the quantity of condensate is limited and is flowing in the same direction as the steam,, only the pressure drop need be considered. When the con densate must flow against the steam, even in limited quantity, the ve locity of the steam must not exceed limits above which the disturbance between the steam and the counter-flowing water may produce object-' ionable sounds, such as water hammer, or may. result in the retention of Table 2. Comparative Capacity of Steam Lines at Various Pitches for Steam and Condensate Flowing in Opposite Directions3 Pitch of Pipe in Inches per 10 Ft. Velocity in Ft per Sec. Pitch of Pipe H IN. M IN. 1 IN. IK in. 2 IN. 3 IN. 4 IN. 5 IN. ' CapRcity C a p a c ity M ax. Vel. C a p a c ity M ax. Vel. | C a p a c ity M ax. Vel. | C a p a c ity M ax. Vel. C a p a c ity ' Capacity M ax. Vel. Capacity Pipe Size Inches V > .$ 2 "3 > > wa s 22 Capacity Expressed in Square Feet E D R *i . 25.0 12 30.3 14 37.3 18 40.4 19 42.5 20 46.1 21 47.*5 22 49.3 23 1 .45.8 12 52.6 15 63.0 17 70.0 20 75.2 22 83.0 23 87.9 25 90.2 26 llA IK 2 104.9 18 117.2 20 133.0 23 144.5 25 154.0 27 165.0 28 172.6 29 178.2 31 142.6 18 159.0 21 181.0 23 196.5 25 209.3 27 224.0 28 234.8 30 242.6 31, 236.0 19 263.5 20 299.5 23 325.5 25 346.5 27 371.5 28 388.4 29 401.1 30 Capacity Expressed in Pounds per Hour ' H l 1H 1H 2* 6.3 11.5 26.2 35.7 59.0 12 12 18 18 19 7.6 13.2 29.3 39.8 65.9 14 15 20 21 20 9.3 15.8 33.3 45.3 74.9 18 17 23 23 23 10.1 17.5 36.1 49.1 81.4 19 20 25 25 25 10.6 18.8 38.5 52.3 86.6 20 22 27 27 27 11.5 20.8 41.3 56.0 92.4 21 23 28 28 28 11.9 22 12.3 23 22.0 25 22.6 26 43.2 29 44.6 31 58:7 30 60.7 31 97.1 29 100.3 30 Data from American Society of Heating and Ventilating Engineers Research' Laboratory. water in certain parts of the system until the steam flow is reduced sufficiently to permit the water to pass. The velocity at which such disturbances take place is a function of (1) the pipe size, whether the pipe runs horizontally or vertically, (2) the pitch of the pipe if it runs hori zontally, (3) the quantity of condensate flowing against the steam, and (4) freedom of the piping from water pockets which under certain con ditions acLas a restriction in pipe size. , Reaming Important Three factors of uncertainty always exist in determining the capacity of any steam pipe. The first is.variation in manufacture, which appar ently cannot be avoided. The second is the .care used in reaming the ends of the pipe after cutting.' The effect of both of these factors increases as the pipe size decreases. According to A.S.H.V.E. Research Laboratory tests, either of these-factors may affect the capacity of a 1-in. pipe as much as ' 20 per cent. The third factor is the uniformity in grading the pipe line. 414 ' ________ . .________CHAPTER 23 . . .1946 Guide All of the capacity tables given in' this chapter include a-factor of safety. However, the factor of safety referred to does not cover abnormal'defects or constrictions nor does it cover pipe not properly reamed. ' Equivalent Length of Run .. All tables for the flow of steam in pipes, based on pressure drop, must allow for the friction offered by the pipe as well as for the additional resistance of the fittings and valves. These resistances generally are stated in terms of straight pipe; in other words, a certain fitting will produce a drop in pressure equivalent to so.many feet of straight run of Table 3/ Length in Feet of Pipe to be Added to Actual Length of Run-- Owing to Fittings--to Obtain Equivalent Length - Size of Pipe Inches ` . Length in Feet to be Added to Run Standard Elbow Side Outlet Tee Gate Valve" Globe Valve Angle Valve .^ x. i IX m 2 2X 3 3X 4 5 6 8 10 12 .14 1.3 1.8 2.2 3.0 3.5 4.3 5.0 6.5 8 .9 11 13 17 21 27 30 3 4 5 6 -7 8 11 13 15 18 22 27 35 45 - 53 63 . ' 0.3 0.4 0.5 0.6 0.8 1.0 1.1 1.4. 1.6 1.9 2.2 2.8 3.7 4.6 5.5 6.4 14 18 . 23 ' 29 34 46 54 66 80 92 . . 112 136 180 230 270 310 7 10 12 15 18 22 27 34 40 45 56 67 92 112 132 152 ; "Valve in full open position. ' Example of length in feet of pipe to be added to actual length of run. I*~ - Measured Length = 132.0 ft 4 in. Gate Valve = ` 1.9 ft UZ-Q----- 4- --4. in. Elbows =____3_6_.0__f_t _ -------1 ; Equivalent Length .= 169.9 ft --1.......... H the same size of pipe. Table'3 gives the number of feet of straight pipe usually allowed for the more common types of fittings and valves. In all pipe sizing tables in this chapter the length of run refers to the equivalent length of run as distinguished from the actual length of pipe in -feet. The length of fun is not usually known at the outset;" hence it may be necessary to assume some pipe size at the start. Such an assumption frequently is considerably in error and a more common and practical method is to assume the length of run and to check this assumption after the pipes are' sized. For this purpose the length of run usually is taken as double the actual'length qf pipe. . .. ' TABLES FOR PIPE SIZING FOR LOW PRESSURE SYSTEMS2 Tables 4, 5, and 6 are based on the. actual inside diameters, of .the pipe . and .the condensation of lb (4 oz) of steam per square foot of equivalent direct radiation {abbreviated EDR) per hour. The drops indicated are Steam Heating Systems and Piping 415 Table 4. Steam Pipe Capacities for Low Pressure Systems (Reference to this table will be by column letter A through L) This table is based on pipe size data developed through the research investiga tions of the American Society of Heating and Ventilating Engineers. CAPACITIES OF STEAM MAINS AND .RISERS Direction op Condensation Flow in Pipe Line Special Capacities for One-Pipe Systems Only With the Steam in One-Pipe and Two-Pipe Systems Against the Steam Radiator In. *4psi . `/fePei . . .or or or or HOa HO* 1 Os 20a Drop Drop Drop Drop .. . .. . Two-Fipe Only Supply Valves Radiator Risers and Up- OS5 4 Os Drop . 8 0s Drop Vertical Hori zontal Feed Corn . nections AB C D B` F G I* Jb K Capacity Expressed in Square Feet E D R X 30 30 25 1 39 46 56 79 111 157 56 34 45 ix 87 100 122 173 245 346 122 75 98 m 134 155 190 269 2 273 315 386 546 380 ' 538 190 . 108 152 771 1,091 386 195. 288. 2X 449 518 635 898 1,270 1,800 635 395 464 3 822 948 1,160 1,650 2,330 3,290 1,130 700 800 1,230 1,420 1,740 -2,460 . 3,470 4,910 1,550 1,150 1,140 4 1,740 2,010 2,460 3,480 4,910 6,950 2,040 1,700 1,520 5 3,210 3,710 4,550 6,430 9,090 12,900 3,150 6 5,280 6,100 7,460 10,550 14,900 21,100 8 11,000 12,700 15,500 21;970 31,070 .43,900 10 20,000 23,100 28,300 40,100 56,700 80,200 12 32,000 37,100 45,500 64,300 91,000 129,000 16 61,000 69,700 84,800 121,000 i7o;ooo 242,000 .28 28 62 62 93 93 169 169 260 475 745 1,110 2,180 . Capacity Expressed in Pounds per Hour . % '8 1 10 12 14 20 IX '. 22 . -25 ; 31 43 IX . 34 . 39 48 67 2 68 - 79 97 137 2X 112 130 .159 225 3 i 206 237 291 411 3X 307 .355 _ 434 614 4 ; 435 503 614 869 5 806 92S 1,140 1,610 6 1,32C 1,52C 1,871 2,640 8 ' 2.75C 3,17C 3,881 5,490 10 5,01C 5,79C 7,091 10,000 12 8,040 9.29C 11,400 16,100 16 15,100 17,400 21,200 30,300 8 -28 40 ` 14 61 . ,''87. . 31 . -95 . 135 48 193 - 273 97 318 449, 159 581 822 . 282 . 869 1,230 387 1,230 1,740 511 - 2,270 3,210 3,730 5,280 7,770 11,000 14,200 20,000 22,700 32,200 42,400 60,500 .9 19 27 49 99 175 -288 425 788 6 11 20 38 : 72 116 200 286 380 ___ 7 71 7 16 i6 23 . -23 42 42 65 . 119 186 -278. 545 All Horizontal Mains and Down-Feed Risers Mains Up- and UnFeed dripped Risers, Run outs UpFeed Risen Radiator RunCon- nections Dripped . Noie.--All drops shown are in psi per 100 ft of equivalent run--based on pipeproperly reamed. "Do not use Column- H for drops of 1/24 os; 1/32 psi; substitute Column C or Column B ns required. . *>Do not use Column J for drop of 1/32 psi except on sizes 3 in. and over; below 3 in. substitute Column B. On radiator runouts over 8 ft long increase one pipe size over that shown in Table 4. T a b l e 5. R e t u r n P ip e .C a p a c it ie s fo r L o w P ressure S ystem s 416 CHAPTER 23 1946 Guide Steam Heating Systems and Piping 417 OTfoi'to'SO-OroO^O'OOO0O.O0 Oo oo fO oo r-- cd io rD oo oo c^--o(i Nooft-m~O LNoO -HNcuor OrfO> CD CO L--O LOO -- CS CD t". NLhOOONr}^Oi O0O5 0*O0DOOQOO00O'O0Oort T! ! i I I I i 00 CO oo r-o Olo HNDN OO CD CO LO O &.:scr s: ^ 418 ; CHAPTER 23 . , - 1946 Guide drops in pressure per 100 ft of equivalent length of run. The pipe is assumed to be well reamed and without unusual or noticeable defects. Table 4 may be used for sizing piping for steam heating systems by ' pre-determining the allowable or desired pressure drop per 100 equivalent ; feet of run and reading from the column for that particular pressure drop. This applies to all steam mains on both one-pipe and two-pipe systems, vapor systems, and vacuum systems. Columns B to G, inclusive, are used where the steam and condensation flow in the same direction, while Columns H and I are for cases where the steam and condensation flow in opposite directions, as in risers and runouts that are not dripped. Columns J, K, and L are for one-pipe systems and cover riser, radiator valve and vertical connection sizes, and radiator and runout sizes, all of which are , based on the critical velocities of the steam to permit the counter flow of condensation without noise. . . Return piping may be sized with the aid of Tables 5 and 6 where pipe capacities for wet, dry, and vacuum return lines are shown for the pres sure drops per 100 ft corresponding to the drops in Table 4. It is cus tomary to use the same pressure drop on both the steam and return sides of .a system, . Example 2. What pressure drop should be used for- the steam piping of a system if the measured length of the longest run is 500 ft and the initial pressure is not to -be over 2-psi gage? . ., . Solution.; It will be assumed, if the measured length of the longest run is 500 ft, that -when the allowance for fittings is added the equivalent length of run will not exceed 1,000 ft. Then, with the pressure drop, not oyer one half of the initial pressure, the drop could be 1 psi or less. With a pressure drop of 1 psi and a length of run of 1,000 ft, the* drop per 100 ft would be Ho psi, while if the total drop were 2 psi, the drop per 100 ft . would be Ho psi. In the first instance the pipe could be sized according to Column D for ^6 psi per 100 ft, and in the second case, the pipe could be sized according to Column C for H4 psi- 0 completion of the sizing, the drop could be checked by taking the longest line and actually calculating the equivalent length of run from the pipe sizes determined. If the calculated drop is less than that assumed, the pipe size is all right; if it is more, it is -probable that there are an unusual number of fittings involved, and either the lines must be straightened or the column for the next lower drop must be used and the lines resized. Ordinarily resizing will be unnecessary. . . '- . PIPE SIZING FOR INDIRECT HEATING UNITS Pipe connections and mains for indirect heating units are sized in a manner similar to radiators, but the equivalent direct radiation must be ascertained for each row of heating unit stacks and then must be divided into the number of stacks constituting that row and into the number of connections to each stack. ' . c r t> _ Q x 60 X (tl -- <e) 55.2 X 240 Q X (f| - t*) 220.8 0) where * _ . ' . . . EDR = equivalent direct radiation, square feet. , Q volume of air, cubic feet per minute. ` te -- the temperature of the air entering the* row of heating units under con sideration, Fahrenheit degrees. . \ t\ = the temperature of the air leaving the row of heating units under considera tion, Fahrenheit degrees. ' . . 60 = the number of minutes in one hour. * 55.2 = the number of cubic feet of air heated 1 Fahrenheit degree by 1 Btu. . 240 = Btu equivalent of 1 sq ft of EDR. Steam Heating Systems and Piping 419 . Example 8. Assume that a. 3-row heating unit shown in this chapter in Fig. 3$ is handling 50,000 cfm of air and that the rise.in the first row-is from 0 to 40 F, in the second row from 40 to 65 F, and in the third row from 65 to 80 F. What is the load in.EDR on each supply and return connection? ' . . Solution. For row 1, 50,000 X (40 - 0) R= 220.8 - = 9058 sq ft. For row 2, 50,000 X (65 - 40) / 220.8 5661 sq ft. For row 3, 50,000 X (80 - 65) = 3397 sq ft. 220.8 Each row of heating units consists of four stacks and.each stack has two connections so that the load on each stack and each connection of the stack is as follows: Row i 2 3 Total Load (EDR) Stack Load* (EDR) 9058 - 2265 5661' 1415 " 3397 . 849 Connection LoAob . (EDR) 2265 or 1132 .. 1415 or 708 849 or 425 "One quarter of total row load. bOne half of stack load if two steam connections are made: otherwise, same as stack load. The pipe sizes would then be based on the length of the run and the pressure drop desired, as in the case of radiators. It generally is considered desirable to place the in direct heating units on a separate system and not on supply or return lines connected to the general heating system. . Most manufacturers of heating coils how publish condensing capacities of their coils for all common operating conditions in pounds of steam per hour per square foot of face, area (or free area for some designs). These rates may be used in connection with Tables 4 and 6 to size the piping. - GRAVITY ONE-PIPE AIR-VENT SYSTEM . This system is the most common of all methods of steam heating, . especially for small size installations, due largely to its low cost and simplicity. The downward pitch of a one-pipe air-vent system is indicated in Fig. 2. ' Low points and ends of steam mains pitched down from the boiler should be dripped. All drips should be sealed below water line before connecting together^ In the risers and radiator connections, steam and condensation flow in opposite directions. In long steam mains it flows in the same direction as the steam arid is removed from the main through the drip. Short mains may'be arranged for the condensate to flow in a direction opposite the steam by sizing them so the critical velocity is not . exceeded. It is customary to drip the heel of each riser in buildings of several stories to avoid counter-flow of the steam and condensate in the ' riser, runout. In buildings of one or two stories the condensate is returned to the steam main instead of being dripped. Both types of risers are shown in Fig. 2, and riser connections are shown in Figs. 3 and 4. A . typical overhead down-feed system' is illustrated in Fig. 5. While wet- 420 _________________ -CHAPTER 23 ,1946 Guide return mains need not be pitched toward the boiler to maintain steam circulation, they should be pitched for drainage. . To improve steam circulation in one-pipe systems quick vent air valves should be provided at the ends and at intermediate points where the steam main is brought to a higher elevation. It is desirable to install the air-vent valves about a foot ahead of the drips, as indicated in Fig. 2, to prevent possible damage to their mechanisms by water. The radiator valves may be the angle-globe, offset-corner pattern or gate type. Straight-globe and straight-comer types should not be used ' since the raised valve seat would interfere with the flow of condensation through the valve. Graduated valves cannot be used since the steam valves on this system must be fully open or fully closed to prevent the radiators filling with water and creating a dangerous water line condition. With a one-pipe system the heat cannot be modulated at the radiator, the steam being either all on or all off. Systems and devices are available which make it possible to obtain a partial modulating effect from one-pipe heating systems. ,. , It is important to keep the lowest points of the steam mains and heating units sufficiently above the water line of the boiler to prevent flooding; The minimum water line difference depends on the initial steam pressure and piping pressure drop plus a safety factor for heating up. . Referring to Fig. 6 it will be noted that the boiler, and wet return form a U-shaped container, with the boiler steam-pressure on the top of the water at one end and the steam main pressure on the top of the water at the other end. .The difference between these'two pressures is the pressure drop in the system,'i.e., the friction and resistance to the flow of steam in passing from the boiler to the far end of the main and the pressure re duction in consequence of the condensation occurring in the system.- Steam Heating Systems and Piping 421 The water in the far end will rise sufficiently to overcome this difference in order to balance the pressures, and it will rise far enough to produce a ' flow through the return pipe and overcome the.resistance of check valves if installed. If a one-pipe steam system is designed, for example, for a total pressure drop of )4 psi, and utilizes a Hartford return connection instead of a', check valve on the return, the rise in the water level at the far end of the return due to the difference in steam pressure would be )4 of 28 in. (28 in. Fig. 3. Typical Steam Runout where Risers are Not Dripped Fig. 4. Typical Steam Runout where Risers are Dripped Supply riser- ^Supply main -Drop riser 4s= Air valve- 4= Air vent "Air valve. -Air valve mi J- Hartford return connection" 3- EL ,__________ h_________ j___ vWet return h--'' Fig. 5. Typical Down-Feed Gravity One-Pipe Air-Vent System- head being equal to one pound per square inch)', or 3)4 in. Adding 3 in. to overcome the resistance of the return main and 6 in. as a factor of safety for heating up gives 12)4 in. as the distance the bottom of the lowest ' part of the steam main and all heating units must be above the boiler water line. The same system, however, installed and sized for a total pressure drop of )4 psi, and with a check in the return, would require 34 of 28'in., or 14 in: for the difference in steam pressure, 3 in. for the ' flow through the return, 4 in. to operate the check, and 6 in. for a factor of safety, making a total of. 27 in. as the required distance. Higher . pressure drops would increase the distance accordingly. . 422 - ' ____________________ CHAPTER 23 v , 1946 Guide . Gravity one-pipe air-vent systems in which the equivalent length of run does not exceed 200 ft should be sized by means of Tables 4, 5 and 6 as follows: .. 1. For the steam main and dripped runouts to risers where the steam and condensate flow in the same direction, use HVpsi drop (Column D). . 2. Where the riser runouts are not dripped and the steam and condensation flow in opposite directions, and also in the radiator runouts where the same condition occurs, use Column L. ' -_ . 3. For up-feed steam risers carryingcondensation back from the radiators, use Column J. 4. For down-feed systems the main risers of which do not carry any radiator con- densation, use Column H. . 5. For the radiator valve size and the stub connection, use Column K. 6. For the dry return main, use' Column U. 7. For the wet return main use Column T. On systems exceeding an equivalent length of 200 ft, it is suggested th^t / the total drop be not over Hi psi. The return piping sizes should corres- ' Steam pressure at Boiler steam pressure end of main / Return water Water line of boiler - ` fine - f Rise*water fine difference -- Level-- ^Vet return Fig. 6. Difference in Steam Pressure on Water in Boiler and at End of Steam Main . pond with the drop used on the steam side of the system.- Thus, where Hi-psi drop is being used, the steam main and dripped runouts would be sized from Column C; radiator runouts and undripped riser runouts from Column L; up-feed risers from Column /; the main riser on a down-feed system from Column C (it will be noted that if Column H is used the drop would exceed the limit of Ha psi); the dry return from Column R; and the wet return from Column Q. ` With a K2-psi drop the sizing would be the same as for Ha psi except . that the steam main and dripped runouts would-be sized from Column B, the main riser on a down-feed system from Column B, the dry return from * Column O, and the wet return from Column N.. ' '- ` ' \ . ' Notes on Gravity One-Pipe Air-Vent Systems . 1. Pitch of mains should not be less than ^ in. in 10 ft. - 2. Pitch of horizontal runouts to risers and radiators should not be less than H in. in 10 ft. Where this pitch cannot be obtained runouts over 8 ft in length should be one size larger than called for in the table. . 3. In general, it is not desirable to have a main less than 2 in. The diameter of the far end of the supply main should not be less than half its diameter at its largest part. 4. Supply mains, runouts to risers, or risers, should be dripped where necessary. 5. Where supply mains are decreased in size they should be dripped, or be provided with eccentric couplings, flush on bottom. v . .... Example 4- Size the one-pipe gravity steam system shown in Fig. 7 assuming tiiat this is all there is to the system or that the riser and run shown involve the longest run on the system. . . Solution. The total length of run actually shown is 215 ft. If the equivalent length .of run is taken at double this, it will amount to 430 ft,.and with a total drop of H psi Steam Heating Systems and Piping Table 7. Pipe Sizes for One-Pipe Up-Feed System Shown c ` in Fig." 7 .. .. Past or Ststem Section or Pips Branches to radiators.. Branches to radiators.. Riser............................ a to b Riser------ --------- ----------- btoc Riser............................-- ctod Riser........................ -- -. d to e Runout to riser._______ Supply main...........--1 Branch to supply, main Dry return main........... Wet return main........... Wet return main______ Wet return main........... / tog g to h h to j f to k fe to m to to n n to p Radiation Shpplxed EDR Sq Ft Thbobbtical - Practical Pipe sms Pep* size ' (Inches) ' (Inches) 100 50. 200 ' 300 400 . 500 600 600 600 600 600 600 600 600 2 m .2 2K 3 3 3 yi 3 2H IK' 1 1 1 2 VA 2. 2K 2H . 3 3 m 3 3 2 2 2 2 ..423 Fig. 7. Riser, Supply Main and Return Main . of One-Pipe System s'" * the drop per 100 ft will be slightly less than He psi- It would be well in this case to use Ha psi, and this would result in the theoretical sizes indicated in Table 7. These theo retical sizes, however, should be modified by not using a wet return less than 2 in. while the main supply, g-h, if from the uptake of a boiler, should be made the full size of the main, or 3 in. Also the portion of the main k-m should be made 2 in.-if the wet return is made 2 in. . ONE-PIPE VAPOR SYSTEM The one-pipe vapor system operates under pressures at or near atmos pheric and returns its condensation to the. boiler by gravity. In this ! Fig. 8. Typical Up-FeedSvstem with AutomaticReturn Trap* Proper piping connections are essential with special appliances for pressure equalizing and air elimination. 424 CHAPTER 23 1946 Guide system the automatic air valves are of special design to permit the ready release of air and prevent its ready return after it is expelled. The steam radiator valves are a type which, when opened, give a free and unob structed passageway for water. The piping is the same as for the one-pipe gravity system but sized so as to permit operation at a few ounces pressure. . TWO-PIPE VAPOR SYSTEM . A two-pipe up-feed vapor, system using separate supply and return pipes is shown in Fig. 8. The radiators discharge their condensation through thermostatic traps to the dry return pipe. These systems operate at a few ounces pressure and above, but those with mechanical condensate return devices may operate at pressures upward of 10 psi. The simplest Non Return Steam Heating Systems and Piping 425 . which is usually located with the bottom abo'ut 18 in. above the boiler water line.' Some traps are constructed so that they will operate.when they are installed with their bottom as close as 8 in. above the boiler.water line. On the other side of this connection a second check valve is installed in the main return just before it enters the boiler. Fig. 9 shows a typical connection for an automatic return trap. '' Down-Feed Two-Pipe Vapor System In the down-feed two-pipe vapor system the steam is carried to the top of the building, the top of the vertical riser constituting the high point of the system, and the horizontal supply main is sloped down from this location to the far ends of each branch. The runouts are taken off the main from the bottom or at a 45-deg angle downward, and sloped toward the drops. Thus each runout from the main forms a drip and no accu mulation of water is carried down any one drop. ' Fig. 9. Typical Connections for Automatic Return Trap method of venting the system consists of a %-in. pipe with a check valve opening outward. Most systems employ various forms of vent valves, designed to allow the air to readily pass out df the system and to prevent . its return. These systems permit control of the heat in the radiator by varying the opening of the graduated radiator valves. The' boiler pressure is maintained at substantially constant pressure, slightly above atmos pheric pressure. , These systems may be classified as (1) closed systems, consisting of those which have a device to prevent the return of air after it has once been expelled from the system, and which can operate at both super and subatmospheric pressures for a period of four to eight hours depending upon the tightness of the system and rate of firing, and (2) open systems, com prising those which have the return line constantly open to thg atmos phere without a check or other means to prevent the return of air. The open systems are not so popular because they have the disadvantage of not holding heat when the rate of steam generation is diminishing. Closed systems should preferably be equipped with an automatic return . trap to prevent water from backing out of the. boiler. In installing the return trap a check valve is inserted in the return main at a point near the boiler and a vertical pipe is run up into the bottom of the return trap, Fig. 10. Detail of Drip Connections at Bottom of Down-Feed Steam Drop The steamdrops are carried down through the building with suitable reductions as the various radiator connections are taken off until the lowest radiator runout is reached. If the,drop is only two or three stories high, the portion feeding the bottom radiator should be increased one pipe size to provide for draining the riser, and if the drop is over three stories high it is well to increase the portion feeding the two lowest radi ators one or two pipe sizes, especially if the two lowest radiators are small and the normal size of drop required is 1 in. or less. The bottom of each steam drop should terminate with a dirt pocket and be dripped as shown in Fig. 10. The returns on a down-feed vapor system are the same as on an up-feed system. The runouts to the radiators and the radiator con nections of die down-feed system are the same as those for the up-feed system already described. . . While many manufacturers of patented vapor heating accessories have their own schedules for pipe sizing, an inspection of these sizing tables indicates that in general as small a drop as possible is recommended. The reasons for. this are: (1) to have the condensation return to the boiler by gravity, (2) to obtain a more uniform distribution of steam throughout the system, especially when it is desirable to carry a moderate or low 426 CHAPTER 23 1946 Guide fire, and (3) because with large variations in pressure the value of gradu ated valves on radiators is destroyed. For small vapor systems where the equivalent length, of run does not exceed 200 ft, it is recommended that the niain and any runouts to risers that may be dripped should be sized from Column D, Table 4, while riser runouts not dripped and radiator runouts should employ Column I. The up-feed steam risers should be taken from Column H. On the returns, the risers should be sized from Tables 5 and 6, Column U, (lower portion) and the mains from Column U (upper portion). It should again be noted that the pressure drop in the steam side of the system is kept the same as on the return side except where the flow in the riser is concerned. On a down-feed system the, main vertical riser should be sized from Column H, but the down-feed risers can be taken from Column D al though it so happens that the values in Columns T? and H for small systems correspond. This will not hold true in larger systems. For vapor systems over 200 ft of equivalent length, the drop should notexceed;}^ psi to M psi, impossible. Thus, for a 400 ft equivalent run the drop per 100 ft should be not over J^psi divided by 4, or Hi psi. ; In this case the steam mains would be sized from Column B, the radiator and ' undripped riser runouts from Column I; the risers from Column B, because Column H gives a drop in excess of psi. On a down-feed system, Column B would have to be used, for both the main riser and'the smaller risers feeding the radiators in order not to increase the drop over ; % psi. The return risers would be sized from the lower portion of Column O and the dry return main, from the upper portion, of the same column, while any wet returns would be sized from Column N. The same pressure ., drop is applied on both the steam and the return sides of the system. Steam Heating Systems and Piping 427 Notes on Vapor Systems 1. Pitch of mains should not be less than 14 in. in 10 ft. 2. Pitch of horizontal runouts to risers and radiators should not be less than 14 in. in 10 ft. Where this pitch cannot be obtained runouts over 8 ft in length should be one size larger than called for in the table. . ,` 3. In general it is not desirable to have a supply main smaller than 2 in. 4. When necessary, supply main, supply risers, or runouts to supply risers should be . dripped separately into a wet return, or may be connected into the dry return through a thermostatic drip trap. VACUUM SYSTEMS In the vacuum system, a vacuum is maintained in the return line practically at all times. The pump is usually controlled by a vacuum regulator which operates the pump to maintain the vacuum within limits and operates in response to a pressure difference between the atmosphere and the return to control the vacuum in the return main. The source of steam supply may be a low pressure boiler as shown in Fig. 11, or a high pressure line through a pressure reducing valve. The piping and other details are the same as for the vapor systems. , . The return risers are connected in the basement into a common return main which slopes downward toward the vacuum pump. The vacuum pump withdraws the air and water from the system, separates the air from the water and expells it to atmosphere and pumps the water back to the boiler, or other receiver, which may be a feed-water heater or hot well. It is essential that no connection be made from the supply side to the return side at any point except through a trap. The desirable practice demands a return flowing to the vacuum pump by an uninterrupted down ward slope. In some instances local conditions make it necessary to.drop the return below the level of the vacuum pump inlet, before the pump can be reached. In such an event one of the advantages of the vacuum system is the ability to raise the condensate to.a considerable height by the suction of the vacuum pump by means of a lift connection or fitting inserted in the return: The height the condensate can be raised depends on the amount of vacuum maintained. It is preferable to limit lift con nections to a single lift at the vacuum pump. A still more preferable arrangement_is the use of an accumulator tank, or receiver tank, with a float control for the pump, at the low point of the return main located adjacent to the vacuum pump. . When the-vertical lift is considerable, several lift fittings should be used in steps as shown in Fig. 12. This permits a given lift to be secured with a somewhat lower vacuum than where the vertical distance is served by a single lift. Where several lifts are present in a given system at different locations, the lifting cannot occur until the entire system is filled with steam: A lift connection for location close to the pump, where the size may be above the commercial stock sizes, is shown in Fig. 13. It is desirable that means be provided for manually draining the low point of the lift fittings to eliminate danger of freezing. Down-Feed Vacuum System . ` The piping arrangement for the down-feed vacuum system is similar on the supply side to the down-feed vapor system in that it has similar runouts, radiator valves, drips on the bottom of the steam drops, and enlargement of the drops for the lower radiator connection's. The return 428 CHAPTER 23 1946 Guide side of the system is exactly the same as the up-feed system except that the steam riser drips at the bottom are connected into the return line through thermostatic traps. It is preferable to take the runouts 'for the risers from the bottom or at a 45-deg angle down from the steam main so that they may serve as steam main drips. When this is done it is practical to run the steam main level, if a runout is located at every change in pipe size, or if eccentric fittings are used (Fig. 14). A slight pitch in the steam main, however, should be used when possible. An overhead vacuum down-feed system is shown diagrammatically in Fig. 15. Vacuum, atmospheric, sub-atmospheric and orifice systems are usually employed in large installations and have total drops varying from to Yl psi. Systems where the maximum equivalent length does not exceed 200 ft preferably employ the smaller pressure drop, while systems over 200 ft equivalent length of run more frequently are designed for the higher drop, owing to the relatively greater saving in pipe sizes. For example, a system with 1200 ft longest equivalent length of run would employ a drop per 100 ft of Yi psi divided by 12, or )4t psi. In this case, the steam main would be sized from Column C, Table 4, and the risers also from Column Steam Heating Systems tuid Piping 429 . 3. Pitch of horizontal runouts to risers and radiators should not be less than 14 in. in IQ ft. Where this pitch cannot be obtained runouts over 8 ft in length should be one size larger than called for in the table. . - ', 4. In general it is not considered desirable to have a supply main smaller than-2 in. 5. When necessary, the supply main, supply riser, or runout to a supply riser should be dripped separately through a trap into the vacuum return. A connection should not be made between the steam and return sides of a vacuum system without interposing a trap to prevent the steam from entering the return line. 6. Lifts should be avoided if possible, but when they cannot be eliminated they should be made in the manner described in this chapter. 1 7. No lifts can be used in orifice and atmospheric systems. In sub-atmospheric systems the lift must be at the vacuum pump. ' SUB-ATMOSPHERIC SYSTEMS Sub-atmospheric systems are similar to vacuum systems but, in con trast, provide control of building temperature by variation of the heat Fig. 12. Method of Making Lifts on Vacuum Systems when Distance ' , is Over 5 ft Fig. 13. Detail of Main Return Lift at Vacuum Pump . Fig. 14. Method of Changing Size of Steam Main when Runouts are Taken from Top C (Column II could be used as far as critical velocity is concerned but the drop would exceed the limit of psi). Riser runouts, if dripped, would use Column C but if undripped would use Column I; radiator runouts, Column /; return risers, lower part of Column S, Tables'5 and 6; return runouts to radiators, one pipe size larger than the radiator trap con nections. . Notes on Vacuum Systems 1. It is not generally considered good practice to exceed H psi drop per 100 ft of equivalent run nor to exceed 1 psi total pressure drop in any system. 2. Pitch of mains should hot be less than % in. in 10 ft. Fig. 15. Typical Down-Feed Vacuum System output from the radiators. The radiator heat emission is controlled by varying the pressure, temperature and specific volume of steam in circu lation. These systems differ from the ordinary vacuum system in that they maintain a controllable partial vacuum on both the supply and return sides of the system, instead of only on the return side. In the. vacuum system, steam pressure above that of the atmosphere exists in the supply mains and radiators practically at all times. In the subatmospheric system, atmospheric pressure or higher exists in the steam supply piping and radiators only during severe weather. Under average winter temperature the steam is under partial vacuum which in mild weather may reach as high as 25 in. Hg, after which further reduction in heat output is obtained by restricting the quantity of steam. 430 ;-_________________CHAPTER 23 ________ 1946 Guide ' The rate of steam supply is controlled by a valve in the steam main or by thermostatically controlling the rate of steam production in the boiler. The control valve may be of the automatic modulating or floating type governed thermostatically from selected control points in the building, or it may be a'special pressure reducing valve which will maintain the desired sub-atmospheric pressures by continuous flow into the heating main. All radiator supply valves have incorporated adjustable orifices or are equipped with regulating orifice plates. The sizes of orifices used " are larger than for other types of orifice systems because for equal radiator sizes the volume flowing is larger. These orifices are omitted on some systems, depending upon the type of control. Radiator traps and drips are designed to operate at any pressure, from 15 lb gage to 26 in. Hg. A vacuum pump capable of operating at high vacuum is preferable to promote accuracy in the distribution of steam throughout the system, particularly in mild weather. This vacuum is partially self-induced by the condensation of the steam in the system under conditions of restricted supply for reduction of the radiator heat emission. ' The returns must grade downward constantly and uninterruptedly from the radiator return outlets to the inlet of the receiver of the vacuum pump. One radical difference between this and the ordinary vacuum system is that no lifts should be made in the return line, except at the vacuum pump. The receivers are placed at a lower level than the pump and equipped with float control so that the pump may operate as a return pump under night conditions. The system may be operated-in the same manner as the ordinary vacuum system when desired. Steam for heating domestic hot water should be taken from the boiler header back of the control valve so that pressures sufficiently high for heating the water may be maintained on the heater.. The sub-atmos pheric method of heating can be used for the' heating coils of ventilating and air conditioning systems. The flexible control of heat output secured by this method materially reduces the required size of by-pass around the heaters.' Some applications of sub-atmospheric systems are proprietary. ORIFICE SYSTEMS Orifice steam heating systems may have piping arrangements identical with vacuum systems. Some of these omit the radiator thermostatic . traps but use thermostatic or combination float and thermostatic traps on all drip points. A return condensation pump with receiver vented to atmosphere, a return line vacuum pump, or a return trap,, is generally used to return the condensation to the boiler or place of similar disposition, . such as a feed-water heater or hot well. The heat emission from the radiators is controlled by varying the pressure differential maintained. The principle on which these, systems operate is based on the fact that the' steam flow through an orifice will vary when the ratio of the absolute pressures on the two sides of the orifice exceeds 58 per cent. If the abso-. lute pressure on the outlet side is less than 58 per cent of the absolute pressure on the inlet side, no further increase in flow will be obtained as a result of the increased pressure difference. If an orifice is so designed in size as to exactly fill a radiator with 2 psi gage on one side and psi gage on the other, the absolute pressure relation is: ' 14 74. ' = 0.90 or 90 per cent. . Steam Heating Systems.and Piping . ' 431 Should the steam pressure be dropped to J4 lb on the supply pipe, the pressure on each side of the orifice would be balanced and no steam flow would take place. From this it will be apparent that if an orifice of a given diameter will fill a given radiator with steam when there is a given pressure on the main, reducing this steam main pressure will permit filling various desired portions of the radiator down to the point where the main pressure equals the back pressure in the radiator provided the supply pipe pressures may be controlled sufficiently close. If orifices are designed on a similar basis for a given system and proportioned to the heating capacity of the radiators they serve, all radiators will heat proportionately to the steam pressure. The range of pressure variation is limited by the per missible noise level of the steam flowing under the pressure difference required for maximum heat output. The control of the steam supply is obtained by a valve placed in the steam main, which maintains a deter- Table 8. Orifice Capacities for Low Pressure Steam Systems . This table is based on data from actual tests* . Orificb DIAMETER 64thS of AN INCH 6 in. He 5 in. He 4 in. He 2 in. He 1 in. He Differential Differential Differential Differential Differential 7 -8 9 10 11 12 13 14 15 16 17 . 18 19 20 21 . ~ Capacity Expressed in Square Feet E D R . . 18-23 16-21 23-29 ' 21-27 29-36 27-33 36-44 33-40 44-52 40-48 52-62 . 48-57 . 62-72 . 57-66 72-83 66-76 83-94 76-86 94-106 86-97 . 106-119 . 97-109 119-133 109-122 . 133-148 122-135 , 148-163 135-149 163-179 . 149-164 15-19 . 19-25 25-30 30-37 37t44 44-51 51-59 59-67 .. 67-76 76-86 86-97 97-108 108-120 120-133 133-145 10-13 13-17 17-21 21-26 26-31 31-37 37-43 43-49 49-56 56-64 64-72 72-80 80-88 88-98 98-107 . 8-11 11-14 14-17 17-20 20^24 24-28 28-32 32-37 37-42 .42-47 47-52 52-58 58-64. 64-71 . . 7' 8 9 10 11 12 13 14 15 . 16 -. 17 18 . 19 20 . - 21 Capacity Expressed in Pounds per Hour .* 4.5-5.8 5.8-7.3 7.3-9.0 9.0-11.0 11.0-13.0 13.0-15.5 15.5-18.0 18.0-20.8 20.8-23.5 23.5-26.5 26.5-29.8 29.8-33.3 33.3-37.0 37.0-40.8 40.8-44.8' - 4.0-5.3 5.3-6.8 6.8-S.3 . 8.3-10.0 10.0-12.0 12.0-14.3 14.3-16.5 16.5-19.0 19.0-21.5 21.5-24.3 24.3-27.3 27.3-30.5 30.5-33.8 33.8-37.3 '37.3-41.0 '3.8-4.8 2.5-3.3 . 4.8-6.3 3.3-4.3 . 6.3-7.5 4.3-5.3 7.5-9.3 5.3-6.5 9.3-11.0 6.5-7.8 .. 11.0-12.8 7.8-0.3 12.8-14.8 9.3-10.8 14.8-16.8 10.8-12.3 16.8-19.0 12.3-14.0 19.0-21.5 14.0-16.0 21.5-24.3 16.0-18.0 24.3-27.0 18.0-20.0 27.0-30.0 20.0-22.0 30.0-33.3 , 22.0-24.5 33.3-36.3 24.5-26.8 2.0-2.8 2.8-3.5 3.5-4.3 4.3--5.0 5.0-6.0 6.0-7.0 7.0-8.0 8.0-9.3 , 9.3-10.5 10.5-11.8 11.8-13.0 13.0-14.5 14.5-16.0 16.0-17.8 . Note.--The radiator orifice plates recommended in this table are made of brass stampings 0.023 in. thick, cup-shaped to be inserted in radiator valve unions. . - . , ,' ` Flow of steam through Orifiires into Radiators, by S. S. Sanford and C. B. Sprenger (A.S.H.V.E. Transactions, Vol. 37, 1931, p. 371). .............. ............................................................... -- 432 CHAPTER 23 1946 Guide Table-9. Steam Pipe Capacities for 30 psi Steam Systems Capacity Expressed in Pounds per Hour (Steam and Condensate Flowing in Same Direction) Pipe Size Inches - H l 1M-. m .2 m 3 ' 3K '4 5 6 8 10 - .12 .. Drop in Pressure--Pounds per 100 Ft in Length H 15 31 69 107 217 358 651 979 . 1,386 2,560 4,210 8,750 16,250 25,640 H : 22 46 100 154 313 516 940 1,414 2,000 3,642 6,030 12,640 23,450 36,930 14 31 63 141 219 444 730 1,330 2,000 2,830 5,225 8,590 17,860 33,200 52,320 H 38 77 172 267 543 924 1,628 2,447 3,464 6,402 10,420 21,865 40,625 64,050 45 89 199 309 627 1,033 1,880 2,825 4,000 7,390 12,140 25,250 46,900 74,000 2 63 125 281 437 886 1,460 2,660 4,000 5,660 10,460 17,180 35,100 66,350 104,500 mined pressure by varying the vacuum in the return lines, or by varying the pressure in the supply lines and the vacuum in the returns: The valves are frequently manually set from a remote location, guided by tem perature indicating stations in the building; or thermostatically controlled from a thermostat on the roof, which automatically measures the dif ferential of outside and inside temperatures. Since the range .through which the pressures may be varied is usually from 0 to 4 psi gage, the control should be capable of maintaining close regulation to maintain the desired space temperatures, particularly in mild weather. A recommended orifice schedule is shown in Table 8. Some systems use orifices not only in radiator inlets but also at different points in the steam supply piping for the purpose of balancing the system to a greater extent. In this manner the difference between the initial and terminal Table 10. 150Steam Pipe Capacities foe psi Steam Systems Capacity Expressed in Pounds per Hour (Steam and Condensate Flowing in Same Direction) X Drop in Pressure--Psi per 100 Ft in Length Pipe Size Inches M x K . %' 2. 5 . H. l 29 - 58 41 82 .m ik . 130 203 185 287 2 412 583 2K . . 683 959 3 1,237 1,750 3K 1,855 2,626 4 2,625 3,718 5 '. 4,858 6,875 - '6 7,960 11,275 8 16,590 . 23,475 10 ' 30,820 43,430' 12 48,600 68,750 58 117 262 407. 825 1,359 2,476 3,715 5,260 9,725 15,950' 33,200 61,700 97,250 71 143 320 497 1,010 1,650 3,020 4,550 6,430 11,900 19,500 40,000 75,600 119,000 82 165 370 575 1,167 1,920 3,500 5,250 7,430 13,750 22,550 46,950 87,250 137,600 116 233 523 813 1,650 2,710 4,940 7,420 10,500 19,450 31,850 06,400 123,400 194,400 184 369 827 1,290 2,600 4,290 7,820 11,740 16,620 30,750 50,400 105,000 195,000 307,400 Steam Heating Systems and Piping '___________________ '________ '_____ 433 . Table 11. Return Pipe Capacities for 30 psi Steam Systems . .. Capacity Expressed in Pounds per Hour Pipe Size Inches H 1 IK IK 2 2K 3 3K 4 5 6 M 115 230 485 790 1,575 2,650 4,850 7,200 10,200 19,000 31,000 Drop in Pressure--Pounds per 100 Ft in Length H 170 . 340 ' 710 1,155 2,355 3,900 7,100 10,550 15,000 27,750 45,500 M 245 490 . 1,025 1,670 3,400 5,600 10,250 15,250 21,600 40,250 65,500 . .H 308 615 1,285 2,100 4,300 7,100 12,850 19,150 27,000 55,500 83,000 1 365 730 1,530 2,500 5,050 8,400 15,300 22,750. 32,250 60,000 98,000 pressure in the steam main may be compensated to a great extent. For example, if the initial pressure was 3 psi gage and the pressure at the end of , the main was 2 psi, an orifice could be used in each branch for the purpose of obtaining a more uniform pressure throughout the system. Such a provision may be particularly useful in this system for branches close to the boiler where the- drop in the main has- not yet been produced. Some orifice systems are'proprietary. ' HIGH PRESSURE STEAM SYSTEMS Many of the recent installations of heating systems for large industrial type buildings have been designed for the use of high pressure steam, that is, without the use of pressure reducing valves. Such systems usually involve the use of unit heaters or large built-up fan units with blast heating coils. Pressures on these systems vary from 30 to 150 psi. Tem peratures are controlled by a modulating or throttling type thermostatic valve controlled by the air temperature in the fan outlet. - Tables 9 to 12 may be used for the sizing of steam and return piping for systems of 30 -and 150 psi pressure at various pressure drops. These Table 12. Return Pipe Capacities for 150 psi Steam Systems Capacity Expressed in Pounds per Hour Pipe Size Inches H H 156 ' l 313 IK 650 IK . 1,070 2 2,160 2K 3,600 3 6,500 3K 9,600 - 4 13,700 5 25,600 - 6 . 42,000 Drop in Pressure--Psi per 100 Ft in Length H 232 462 960 1,580 3,300 5,350 9,600 14,400 20,500 38,100 62,500 a 360 690 1,500 2,460 . 4,950 8,200 15,000 22,300 31,600 58,500 - 96,000 K 465 910 1,950 3,160 6,400 10,700 ' 19,500 28,700 40,500 76,000 125,000 1 560 1,120' 2,330 3,800 7,700 12,800 23,300 34,500 49,200 91,500 150,000 2 890 1,780 3,700 6,100 12,300 20,400 37,200 55,000 78.500 146,000 238,000 - 434 CHAPTER 23 ' 1946 Guide tables are based on Babcock's formula, and have been used as the. basis of design for a number of years.- Capacities at other pressures may be computed by means of Table 1. ' The steam lines can be sized for greater pressure drops than the return piping. For a system using steam at 30 psi pressure, the total pressure drop can be 5 to 10 psi, and for 150-psi systems 25 to 50 psi. It has been observed that the maximum pressure in the returns of a 30-psi system is about 5 psi, and that of a 150,-psi system is about 20 psi. The pressure in the return mains is, of course, caused by the discharge of traps, or by leaky traps and by flashing due to the lower pressure in the return line. The total pressure drop in the returns can be approximately 2 psi for the 30-psi returns, and about 10 psi for the 150-psi returns. The usual practice in the sizing of high pressure returns has been to size on the basis of psi per 100 ft of pipe for 30-psi systems, and 1 psi per 100 ft for 150-psi systems. This is an average figure which corresponds generally to several of the previously published tables for the design of high pressure return piping. ` The returns generally discharge to a vented receiver. It is, of course, necessary to provide for the elimination'of air from high pressure systems, the same as in low pressure systems. If possible, it is desirable to design the system so as to condense some of the steam escaping through the vents by passing it through a heat exchanger. When high pressure steam is being supplied and lower steam pressures are required for heating, for domestic hot water, for utility services, etc., one or more pressure reducing, valves (pressure regulators) are required. These are used in two classes of service, one where the steam must be shut off tight to prevent the low pressure building up at time of no load, and the other where the low pressure lines will condense enough steam to offset normal leaking through the valve.- In the latter case, double seated -valves may be used in a manner that reduces the work required of the diaphragm in closing the valve and consequently the size of the dia phragm. These valves also control .the low pressures more closely under conditions of varying high pressures. . .' Valves that shut off all steam are called dead end type. They are single seated, and some of them have pilot operation that provides close control of the reduced pressure. If a thermostatically controlled valve is installed 'after, and near, a reducing valve in such a manner as to cut off the passage of steam, the dead end type should be used. It is common practice when the initial steam pressure is 100 psi or higher tp install two-stage reduction. If the radiation served is cast-iron, the A.S.M.E. code requires two reducing valves when the inlet pressure exceeds 50 psi. This makes a quieter condition of steam flow, as it is apparent that with one reduction, as for example from 150 to 2 psi, there is a smaller opening with greater velocity across the reducing valve and, consequently, more noise. A two-stage reduction also introduces a source of safety, since if one reducing valve were to build up its discharge pressure, this excess' pressure would not be so great as the case might be in a one-stage-reduction. '.If an installation requires single seated valves and the pilot type cannot be used, it is necessary to use two-stage reduction, as single seated . valves. require sufficient diaphragm area to overcome the unbalanced . pressure underneath the single valve. In many cases the large diameter Steam Heating Systems and Piping 435 of diaphragm required would make it"impractical in construction. With'a two-stage reduction the diaphragm diameter required would be reduced. If a one-stage reduction is desired, it is necessary to use a pilot controlled pressure reducing valve, where low pressures are to be maintained closely. In making a two-stage reduction, allowance for expansion of steam on the low pressure side of the valve should be made by increasing the pipe size. This also allows steam flow to be at a more nearly uniform velocity. Separating the valves by a distance up to 20 ft is recommended to reduce excessive hunting action of. the first valve. \ When the reduced pressure is approximately 15 psi or lower, the weight and lever diaphragm valve gives the best results with minimum main tenance. Above 15 psi, spring loaded diaphragm valves should be used; because of the extra weights required on weight and lever type. Pressure, equalizing lines should not be connected too close to the valve. They should be connected into the bottom of the reduced pressure steam main, to allow maximum condensation to exist in the equalizing lines, or the connection can be made into the top of the main if a water accumulator is used to reduce the variation of the head of water on the diaphragm. - Care should be exercised in selecting the size of a reducing valve. The safest method is to consult the manufacturer. It is essential that sizes . of piping to and from the reducing valve be such that they will pass, the desired amount of steam with the maximum velocity desired. A common error, is. to make the size of the reducing valve the same size as that of the service, or outlet pipe size. Generally,`this will make the reducing valve oversized, and bring about wire-drawing of valve and seat, due to small lift of the valve seat. On installations where the steam requirements are relatively large and variable in mild weather or reduced demand periods, wire-drawing may occur. To overcome this condition, two reducing valves are installed in parallel, with the sizes selected' on a 70 and 30 per cent proportion of maximum flow. For example, if 50,000 lb of steam per hour are required, - the size of one valve is on the basis of 0.7 X 50,000 lb, or 35,000 lb, and the other on the basis of 0.3 X 50,000 lb, or 15,000 lb. During the mild or reduced demand periods, steam will flow through the smaller valve only. During the remainder of the season, the.larger valve is set to control at whatever low pressure is desired, and the smaller one at a somewhat lower pressureV' Thus, when, steam flow is not at its maximum, the smaller valve is closed, but it opens automatically when the maximum steam demand occurs, because this maximum demand creates a slight pressure drop in the service line. . . The installation of reducing valves in pipe lines requires detailed planning. They should be installed to give ease of access for inspection and repair, and wherever possible with diaphragm downward, except in cases of pilot operated valves. . . . There should be a by-pass around each reducing valve of size equal to one-half the size of reducing valve. The globe valve in by-pass line should be of a better type of construction, and must shut off absolutely tight: A steam pressure gage, graduated up tp the initial pressure, should be installed on the low pressure side. Safety valves located on the low pressure side should be set 5 psi higher than the final pressure but may be 10 psi higher than the reduced pressure if this reduced pressure is that of the first stage reduction of a double reduction. Strainers are sometimes installed on the inlet to the reducing valve but are not required before a1 second-stage reduction. If a twoTstage reduction is made, it. is well to 436 CHAPTER 23 1946 Guide install a pressure gage immediately before the reducing, valve of the second-stage reduction also'. In sizes 3 in. and above, it is advisable to install a drip trap between the two reducing valves. BOILER CONNECTIONS Steam Cast-iron, sectional heating boilers usually have several outlets in the top. Two or more outlets should be used whenever possible to reduce the velocity of the steam in the vertical uptakes from the boiler and thus to prevent water being carried over into the steam main. Return < Cast-iron boilers are generally provided with return tappings on both sides, while steel boilers are generally equipped with only one return Fig. 16. The Hartford Return Connection tapping. Where two tappings are provided, both should be used to effect proper circulation through the boiler. The return connection should include either a Hartford return connection or a check valve to prevent the accidental loss of boiler water to the returns &ith consequent danger of boiler damage. The Hartford return connection is to be preferred over the check valve because the latter is apt to stick or not close tightly and, furthermore, because the check valve offers additional resistance to the condensate coming back to the boiler, which in gravity systems would raise the water line in the far end of the wet return several inches. In order to prevent the boiler from losing its water under any circum stances, the use of the Hartford return connection is recommended. This connection for a one- or two-boiler installation is shown in Fig. 16. The essential features of construction of a Hartford return connection are: (1) a direct connection (made without valves) between the steam side of the boiler and the return side of the boiler, and (2) a close nipple, or preferably an inverted Y-fitting connection about 2 in. below the normal boiler water line from the return main to the boiler steam and return pressure .balance connection. Equalizing pipe connections between the Steam Heating Systems and Piping 437 steam and return are given in Fig-. 16, based on grate areas, but in ho case shall this pipe size be less than the main return piping from the system. Sizing Boiler Connections ' Little information is available on the sizing of boiler runouts and steam headers. Although some engineers prefer an enlarged steam header to serve as additional steam storage space, there ordinarily is no sudden demand for steam in a steam heating system except during the heating-up period, at which time a large steam header is a disadvantage rather than an advantage. The boiler header may be sized by first computing the maximum load that must be carried by any portion of the header under any conceivable method of operation, and then applying the same schedule of pipe sizing to the header as is used on the steam mains for the 'building. The horizontal runouts from the boiler, or boilers, may be sized by calculating the heaviest load that will be placed on the boiler at any time, and sizing the runout on the same basis as the building mains. The difference in size between the vertical uptakes from the boiler, which should be of same size as the boiler outlet tapping, and the horizontal main or runout is compensated for by the use of reducing ells. Return connections to boilers in gravity systems are made the same size as the return main itself. Where the return is split and connected to two tappings on the same boiler, both connections are made' the full size of the return line. -Where two or more boilers are in use, the return to each may be sized to carry the full amount of return for the maximum load which that boiler will be required to carry. Where two boilers are used, one of them being a spare, the full size of the return main would be carried to each boiler, but if three boilers are installed, with one spare, the return line to each boiler would require only half of the capacity of the entire system, or, if the boiler capacity were more than one-half the entire system load, the return would be sized on the basis of the maximum boiler capacity. As the return piping around the boiler is usually small and short, it should not be sized to the minimum. With returns pumped from a vacuum or receiver return pump, the size of the line may be calculated from the water rate on the pump discharge when it is operating, and the line sized for a very small pressure drop. The relative boiler loads should be considered, as in the case of gravity return connections. Boiler header and piping sizes should be based on the total load. CONDENSATION RETURN PUMPS Condensation return pumps are used for gravity systems when the local conditions do not permit the condensation to return to the boiler under the existing static head. The return of the condensate permits the water, to repeatedly go through the cycle of vaporization, with subsequent condensation and return to the boiler, During such repeated cycles any incrustants or other substances in solution are precipitated and the water de-activated to a considerable extent so that corrosion of a serious nature is seldom ever encountered where the condensate is repeatedly used. Serious corrosion is more frequently found in systems in which the con densation is wasted and fresh make-up water is continually being intro duced. The most generally accepted condensation pump unit for low- pressure heating systems consists of a motor-driven centrifugal pump with receiver 438 CHAPTER 23 ' ' 1946 Guide and automatic float control. Other types, in use include rotary, screw and reciprocating pumps with steam turbine or motor drive, and direct- acting steam reciprocating pumps. ; The receiver capacities of these automatic units should be sized so as not to cause too great a fluctuation of the boiler water, line if fed directly to the boiler and at the same time not so small as to cause too frequent operation of the unit. The usual unit provides storage capacity between stops in the receiver of approximately 1.5 times the amount of condensate returned per minute and the pump generally has a delivery rate of 3 to 4 times the normal flow. This relation of receiver and pump size to heating system condensing capacity takes account of the peak condensation rate. A typical, installation of a motor driven automatic condensation unit . is illustrated in Fig. 17. .. ,. / a ^ ' : 3 -T :' . _; i Steam Heating Systems and Piping . - '__________________________________________________439 ' furnished complete with receiver, separating tank and automatic controls ' r' mounted as.an integrated unit on one base. There are also special steam . turbine driven units which are operated by piassing the steam to be used in heating the building through the turbine with only a 2 to 3 psi drop across the turbine required for its operation. Under special conditions such as installations where it is necessary to return the condensate to a high pressure boiler, auxiliary water pumps may be1 supplied.. In some instances separate air and water pumps may be used. ' For rating purposes 3 vacuum pumps are classified as low vacuum and ; . high vacuum. Low vacuum pumps are those rated for maintaining 5}/j in. Hg vacuum on the system, and high vacuum pumps are. those rated to maintain vacuums above 5J4 in- . Manufacturers of vacuum pumps specify that the standard capacity of : . pumps shall be 0.3 to 0.5 cfm of air removal and 0.5 gpm of water per VACUUM HEATING PUMPS On vacuum systems, where, the returns are under a vacuum, and subatmospheric systems, where the supply piping, radiation and the returns are under a vacuum, it is necessary to use a vacuum pump to discharge the air and non-condensable gases to' atmosphere and to dispose of the condensation. Direct-acting steam-driven reciprocating vacuum pumps are sometimes used where high pressure steam is available or where the exhaust steam from the pump can be utilized. In general, however, these have been replaced by the automatic motor-driven return line Heating, pump especially developed for. this service. Steam turbine drive is .also frequently used where steam at suitable pressures is available, the steam being used afterward for building heating. The usual vacuum pump unit consists of a.compact assembly of exhausting unit for withdrawing the air-vapor mixture and discharging`the air to atmosphere and a water removal unit which .discharges, the condensate to the boiler. They are Fig. 18. . Method of Discharging High-Pressure Apparatus into Low-Pressure Heating Mains and Vacuum Return Mains through ' . . a Low Pressure Trap . . 1000 EDR served. This capacity is at 5J- in. of vacuum and with con densate at 160 F. The larger air capacity is for sinaller systems and the smaller capacity for the larger systems. , , Some manufacturers, however, specify more air capacity than standard where' higher vacuums are desired and where air leakage is suspected. The vacuum that can be maintained on a system depends upon the relationship of the air leakage rate into the system to the operating air . capacity of the hydraulic evacuator when operating at any given return line temperature. The hotter the returns, the lower will be the possible vacuum for a given air leakage rate into the system.. It is particularly essential on high vacuum installations to see that the entire system is tight in order to reduce the amount of inward air leakage and, further- . - more, to see that relatively higher temperature steam is prevented from ' entering the vacuum return lines through leaky traps, high pressure drips, etc. It is for.this reason that the condensate from equipment using steam at high pressures should not be connected directly to a vacuum return line, but should drain to a receiver through a high pressure trap.; , The receiver should have.an equalizing connection to a low pressure steam main and drain through a low pressure trap to the vacuum return main as - indicated in Fig. 18. ... . 440 CHAPTER 23 1946 Guide Vacuum Pump Controls .. In the ordinary vacuum system, the vacuum pump is controlled by a vacuum regulator which cuts in when the vacuum drops to the lowest point desired and cuts out when it has been increased to the highest point, these points being varied to suit the particular system or operating conditions. In addition to this vacuum control, a float control is included which will automatically start the pump whenever sufficient condensation ' accumulates in the receiver, regardless of the vacuum on the system. A selector switch is usually provided to allow operation at night as a con densation pump only, also to give manual or continuous operation when desired. There are several variations in the control of the vacuum maintained on the system by the pump. In some sub-atmospheric systems where " orifices are used, the vacuum pump control maintains a pressure difference between the supply and the return piping, which is held within relatively close limits. There are other sub-atmospheric systems which utilize special temperature-pressure actuated controls for maintaining the desired conditions in the return lines. Where various zones are connected to the same return main, the return vacuum must-be controlled to meet the requirements of the zone operating at the lowest steam supply pressure. Piston Displacement Vacuum Pumps Piston displacement return vacuum heating pumps may be either elec tric or steam driven. Their piston speed in feet per minute should not exceed 20 times the square root of the number of inches in their stroke. They are usually supplied with an air separating tank, open to atmos phere, placed on the discharge side of the pump and at an elevation sufficiently high to allow gravity flow of the condensate to.the boiler. If ' the boiler pressure is too high for such gravity feed, then an additional steam pump for feeding .the boiler is desirable. The extra pump is some times avoided by using a closed separating tank with a float controlled vent. In both arrangements, the air taken from the system must be discharged against the full discharge pressure of the vacuum pump. In the case of high or medium pressure boilers, it is better to use the atmos pheric separator and the second pump. In figuring the required displacement for such pumps, a value of from 6 to 10 times the volumetric flow of condensation is used for average vacuums and systems. . TRAPS . Traps are generally classified as to function as (a) separating traps, (b) return, lifting or vacuum traps, and (e) air traps. Separating'traps may be either float operated, thermostatically operated, or float and. thermostatically operated. Return traps for low pressure service are referred to later as alternating receivers in this chapter. Return traps may also operate to receive condensate under a vacuum and return it to atmosphere or a higher pressure. Air traps are generally float operated. Separating traps are used to release water of condensation but to retain steam. The thermostatic, and float and thermostatic types release both condensate and air but retain steam. Separating traps are used for draining condensate from radiators, indirect air heaters, steam piping systems, kitchen equipment, laundry equipment, hospital equipment. Steam Heating Systems and Piping 441 drying equipment and many other kinds of apparatus. Air traps release air but retain water. Devices known as air vents are, in principle, traps which allow the passage of air but prevent the passage of either water or steam. . Return traps are used for returning condensate either by. gravity, by steam pressure, or by both, to a boiler or other point of disposal, and for lifting condensate from a lower to a higher elevation, or for handling condensate from a lower to a higher pressure. . ' The fundamental principle upon which the operation of practically all traps depends is that the pressure within the trap at the time of discharge shall be equal to, or slightly in excess of, the pressure against which the trap must discharge, including the friction head, velocity head and static head on the discharge side of the trap. Traps may also be classified according to the principle of operating device which supplies the power to cause them to function as (1) float, (2) bucket, (3) thermostatic, (4) float arid thermostatic, (5) impulse, or. (6) tilting traps. Float Traps. A discharge valve is operated by the rise and fall of a float due to the change of water level in the trap. When the trap is empty the float is in its lowest position, and the discharge valve is closed. A gage glass may be used to indicate the height of water in the chamber. Unless float traps are well made and proportioned there is danger of considerable steam- leakage through the discharge valve due to unequal expansion of the valve arid seat and the sticking of moving parts. The discharge from a float trap is usually continuous since the height of the float, and consequently the area of the outlet, is proportional to the amount of water present: Bucket Traps. Bucket traps are of two types, the upright and inverted, and although they are both of the open float constructiori, their operating principle is entirely different.- In the upright bucket trap, the water of condensation enters the trap and fills the space between the bucket and. the walls of the trap. This causes the bucket to float and forces the valve against-its seat, the valve and its stem usually being fastened to the bucket. When the water rises above the edges of the bucket it flows into it and causes it to sink, thereby withdrawing the valve from its seat. This permits the steam pressure acting on the surface of the water in the bucket to force the water to a discharge opening. When the bucket is emptied it rises and closes the valve and another cycle begins. The discharge from this type, of trap is intermittent. In the inverted bucket trap, steam floats the inverted submerged bucket. and closes the valve. Water entering the trap fills the bucket, which sinks and through compound leverage opens the valve, and the trap dis charges. It is impossible to install a water gage glass on an inverted bucket trap, but if visual inspection is necessary, a gage glass can be placed on the line leading to the trap. No air relief cocks can be used, but they are unnecessary, as the elimination of air is automatically taken care of by air passing through the vent in the top of the inverted bucket regardless of temperature. Thermostatic Traps. Thermostatic traps are of two types, those in which the discharge valve is operated by the relative expansion of metals, and those in which the action of a volatile liquid is utilized for this purpose. - Thermostatic traps of large capacity for draining blast coils or very large: radiators are called blast traps. .. . 442 CHAPTER 23 __________ 1946 Guide Float and thermostatic traps have both a thermostatic element to release * air and a float element to release the water. - .. Impulse traps operate with a moving valve actuated by a control cylinder. When the trap is handling condensate,, the pressure required to lift the valve is greater than the reduced pressure in the control cylinder and consequently the valve opens allowing a free discharge of condensate. As the remaining condensate approaches steam temperature, flashing results, flow through the valve orifice is choked and the pressure builds up in the control chamber closing the valve. Automatic Return Traps . In the general heating plant, where thermostatic traps are installed on the heating units, it becomes necessary to provide a means for returning the water of condensation to the boiler, if a condensation or vacuum pump is not used. When the return main can be kept sufficiently high above the boiler water line for all operating conditions, the water of condensation will flow back by gravity, and no mechanical device is required. But ' actually this does not work out in practice. It follows, therefore, that a direct-return trap is needed for the handling of the condensation even though it may not be called into action except under some operating condition where the pressure differential exceeds the static head provided. The installation of a direct-return trap assures safety for such systems, and guarantees the operation of the plant under varying conditions. Automatic return traps, sometimes called alternating receivers, may be of the counter-balanced, tilting type, or spring actuated. These consist' of a small receiver with an internal float, .and when,the condensate will not flow into the boiler under pressure, it will feed into the receiver of the trap, and in so doing, raise or tilt the float or mechanism which actuates a steam valve automatically. This admits steam to the receiver, at boiler pressure, and the equalizing of the pressures which follows allows the water to flow into the boiler. Tilting Traps. With this type of trap, water enters a bowl and rises until its weight overbalances that of a counter-weight, and the bowl sinks to the bottom. As the bowl sinks, a valve is opened, thus admitting live steam pressure on the surface of the water, and the trap then dis- charges. After the water is discharged, the'counter-weight sinks and raises the bowl, which in turn closes the valve and the cycle begins again. Tilting traps are necessarily intermittent in operation. They are not ordinarily equipped with glass water gages, as the action of the trap shows when it is filling or emptying. The air relief of tilting traps is taken care of by the valves of the trap. DRIPS A steam main in any type of steam heating system may be dropped to a . lower level without dripping if the pitch is downward with the direction of steam flow. Any steam main in any heating system can be elevated if dripped. Fig. 19 shows a connection where the steam main is raised and the drain is to a wet return. If the elevation of the low point is above a dry return, it may be drained through a trap to the dry return in two-pipe vapor, vacuum and sub-atmospheric systems,' Horizontal steam pipes may also be run oyer obstructions without a change in level if a small pipe is carried below the obstruction to care for the condensation (Fig. 20). Horizontal return pipes may be carried past doorways and other ob- Steam. Heating Systems and Piping ~ ______ 1 ff? structions by using the scheme, illustrated in Fig. 21. . It will be noted that the large pipe, in this case, runs below .the obstruction and the smaller one over it. ' ' '' Branches from steam mains in one-pipe gravity steam systems should use the preferred connection shown in Fig. 22, but where radiator condensation does not flow back into the main the acceptable method shown in the same figure may be used. This acceptable method has the advantage of , At feast 1 inch Fig. 19. Dripping Main Where it Rises to Higher Level Fig. 20. Looping Main Around Beam Fig. 21. Looping Dry Return Main Around Opening . Acceptable method Preferred method Fig. 22. Methods of Taking Branch from Main Fig. 23. Constants for Determining Length Offset Pipe Fig. 24. Dirt Pocket Connection Fig. * 25. Dripping End of Main into. Wet *. Return - Fig. 26.- Dripping End of Main into Dry ' Return Fig. 27. Dripping Heel1 of.Riser into Dry . . Return . giving a perfect swing joint when connected to the vertical riser or radia tor connection, whereas the preferred connection does not give this swing without distorting the angle of the pipe. Runouts from the steam main are usually made about 5 ft.long to provide flexibility for movement in. the main. .' ; - Offsets in steam-and return piping should preferably* be made with 90-deg-ells but occasionally fittings of other angles are used, and in such cases the length of the diagonal offset will be found as shown in Fig. ?3. 444 CHAPTER 23 \ 1946 Guide- ' Dirt pockets, desirable on all systems employing thermostatic .traps, should be so located as to protect the traps from scale and muck which will interfere with their operation. Dirt pockets are usually made 8 in. to 12 -in; deep and serve as receivers for foreign matter which otherwise would be carried into the trap. They are constructed as shown.in Fig. 24. . On vapor systems where the end of the steam main.is dripped down into the wet return, the air venting at the end of the main is accomplished by an air vent, passing through a thermostatic trap into the dry return line as shown in Fig. 25. On vacuum systems the ends of the steam mains are dripped and vented into the return through drip traps opening into the return line. The same method may be used in atmospheric systems. Steam, Heating Systems and Piping i 445 . Two satisfactory methods of making runouts for one-pipe systems for either the up-feed or the down-feed type are shown in Fig. 28. Where the vertical distance is limited and the runouts must run above the floor, PLAN Fig. 28. One-Pipe Radiator Connections Fig. 29. Unit Heater Connected to One-Pipe Air-Vent System A float type trap is preferable to a thermostatic trap for dripping steam mains and large risers. If thermostatic traps are used, a cooling leg (Fig. 26) should always be provided. The cooling leg is for cooling the condensation sufficiently before it reaches the trap, so the trap will not be held shut by too high a temperature. On down-feed systems of atmos pheric, vapor, and vacuum types, the bottoms of the steam risers are dripped in the manner shown in Fig. 27. On large systems it is desirable to install a gate valve in the cooling leg ahead of the trap. . CONNECTIONS TO HEATING UNITS Riser, radiator and convector connections must not only be properly pitched at the time they are installed but must be arranged so that the pitch will be maintained under the strains of expansion and contraction. These connections may be made by swing joints which permit the ex pansion or contraction to occur under heating and cooling without bending of pipes. To take care of expansion in long risers, either expansion joints ' Of commercial construction or pipe swing joints are used. Anchoring of pipes between expansion joints is desirable. ' ' Fig. 31. Top and Bottom Opposite End Radiator Connections Fig. 32. Connections to Radiator Hung on Wall . the radiator may be set on pedestals or raised by means of high legs. . A method of connecting a unit heater to a one-pipe steam heating system is illustrated in Fig. 29. Typical two-pipe radiator or. convector connections are shown in Figs. 30, 31 and 32. While the top is the preferred location for the control Steam Heating Systems and Piping. 447 Dirt pocket Fig. 35. Piping Connections to Indirect Radiators . with Dry Returns Fig. 33. Typical Pipe Coil Connections valve, it may be located at the bottom. Short radiators may be top supply and bottom return on same end. With convectors the control valve is sometimes omitted and a damper in outlet grille used forheat control. The typical method of connecting pipe coils is shown in Fig. 33 and is suitable for atmospheric, vapor, vacuum, sub-atmospheric,, and orifice systems. ' Typical pipe connections for indirect radiators and tempering or heating stacks are shown in Figs. 34, 35, 36, 37 and 38. ' Fig. 36. Supply and Return Connections for Heating Units of - Central Fan Systems FIg. 37. Typical Connections to Central Fan System Heating Units Exceeding 12 Sections > . Fig. 34. Typical Piping Connections to Concealed ' : : Heating Units with Wet Returns . Fig. 38. Typical Piping for Atmospheric and Vacuum Systems with . . Thermostatic Control (Central Fan System) . , 448 CHAPTER 23 1946 Guide ' Where a building is served by a vacuum system or a sub-atmospheric system the stacks should be piped in the usual manner and traps of large capacity, preferably of the combination float and thermostatic type, should be used. In the orifice and closed two-pipe systems, traps should be used on the returns so. that a pressure, above that of the atmosphere may be secured on the heaters. Each stack should have a separate steam and return connection and trap. Wide stacks are more evenly heated if divided and supplied with two steam connections, one at each end, and a return connection for each steam connection. For. stacks of large capacity it is sometimes desirable to run a separate steam main direct from the boiler to the stacks. . CONTROL VALVES Gate valves are recommended in all cases where service demands that the valve be either entirely open or entirely closed, but they should never be used for throttling. Angle globe valves and straight globe valves should be used for throttling, as done on by-passes around pressure reducing valves or on by-passes around traps. REFERENCES . >-A.S.H:V.E. Research Report No. 954--Condensate and Air Return in Steam Heating Systems, by F. C. Houghten and J. L. Blackshaw (A.S.H.V.E. Transactions, Vol. 39, 1933, p. 199). . *--Pipe size tables in this chapter have been compiled in simplified and condensed form for the conve nience of the user; at the same time all of the information contained in previous editions of The Guide has . been retained. Values of pressure drops, formerly expressed in ounces, are now expressed in fractions of a pound. - A.S.H.V.E. Standard Code for Testing and Rating Return .Line Low Vacuum Heating Pumps A.S.H.V.E. Transactions, Vol. 40, 1934, p. 33). ' CHARTER 24 j4ot lAJater Jdeatinc^ Sfydtemi and piping. Systems of Piping, Forced Circulation Pipe Sizes, Gravity Circulation Pipe Sizes, Expansion Tanks, Installation Details, . Examples of Piping Design THERE are two general-systems of piping used for either gravity or forced hot water systems: (a) Two-pipe system, (b) One-pipe system. With either of these piping systems the distributing mains may be located in the basement with up-feed to the radiators and risers, or the supply main may be located in the attic with the return main located in ,, the basement. For radiators located on the basement floor the mains may be run at the ceiling, as one of the advantages, of a forced hot water heating system is that the returns need not be below the radiators as required with a steam system. In some one-pipe systems there is one supply main in the basement with separate flow and return riser con nections to the radiators. In the two-pipe system there are separate supply and return pipes throughout so that the radiators are connected in parallel, resulting in the same water temperature in all radiators. With the one-pipe system part of the water flows through more than one radiator, so that the water temperature toward the end of the main is not as high as near the boiler. However, with the one-pipe system, by maintaining a rapid circulation and small difference in temperature between the water leaving and returning to the boiler or other heat generator, the variation in the radiator water temperature is reduced. The two-pipe system for larger buildings should, if possible, be arranged for reversed return. The direct and reversed return systems are shown in Figs, 1 and 2. With the reversed return system, the length of the water circuit for any one radiator is the same as for any other radiator and, therefore, the friction and temperature losses to all radiators should be nearly the same. ' In some cases the reversed return system involves no more piping than the direct return system. In the case of large buildings, it is often advis able to zone the piping. ' The quantity of water which must be circulated may be determined from the following equation: w= H CM (1) where W = weight of water circulated in pounds per hour. .. H = heat required in Btu per hour. C = specific heat (=1 for water). At = change in water temperature between supply and return line in Fahrenheit degrees. ' ' Weight may be changed to gallons per minute by dividing W by 8 x 60 where 8 is average weight of a gallon of water at temperatures existing in heating systems. ' 449 - 450 CHAPTER .24 ' 1946 Guide Mechanical Circulators ' Circulating pumps are usually of the centrifugal type. The required capacity of the pump is calculated as shown by Equation 1. For example, for 100.Mbh and 20 deg drop a pump having a capacity of 5000.1b water per hour or 10 gpm should be used. The resistance head is based on the system as designed. In large systems the economical size of pump may be determined by comparing the cost of power for operation with the annual charges on the capital cost of the piping system, as larger pipe sizes mean less pump power. Velocities through piping in excess of 4 fps are likely to cause disturbing noises in buildings other than factories. In large systems'the pumps are run continuously while in small ones they are run either continuously or intermittently depending on the type of automatic temperature control selected. Small circulating pumps are usually driven by direct-connected electric motors. Under certain con . ditions a valved by-pass should be provided and the piping so designed that in case of breakdown of the pump or failure of electric current there will be sufficient gravity circulation to keep the building reasonably warm. In large buildings or groups of buildings, it is often advisable to have two pumps, each of about 70 per cent of the total capacity, to take care rcn [CO, [ED, -l--i 4-- -- i 1-- " 1 H ' -J rra, ' rd-L . --LJ n - -5> H -J ;' pv . i-------------------j Fig. 1. A Direct Return System Fig. 2. A Reversed Return System . of breakdown service. During mild weather, variations in water tem perature may be utilized to balance the required heat loss. In the larger systems steam turbines are sometimes used to drive the pumps, the exhaust steam being used for heating the water, and in such buildings as hospitals this may be the most economical method. As the average pump used for water circulation is not over 60 per cent efficient, the cost of power on a large installation should be computed and .. comparisons made between the savings in capital cost of piping and the annual cost of power. . FORCED CIRCULATION PIPE SIZES The heads available to cause circulation are much greater in forced circulation systems than in gravity circulation systems. Consequently, higher velocities may be used in designing the system, with the result that smaller pipes may -be selected and the first cost of the installation reduced. As the pipe sizes of a.heating system are reduced, the necessary increase in the velocity of the water increases the friction losses and thus . the cost of operation and the initial cost of .the circulating equipment. The increased velocity of a forced circulation system offers.a, number of advantages, such as a much shorter heating-up period and a more flexible, control of hot water circulation. This improved performance merits the " small increase in operating cost necessary to circulate the water mechani- ' cally. -The velocities required should be determined'by calculation for' the particular system under consideration. As forced circulation velocities F R IC T IO N --------- M 1 U N C H E S P E R FO O T- OF P IP E Hot Water Heating Systems and Piping ' 451 are higher than those in gravity systems, and as the friction in a heating system varies almost as the square of the velocity, a given error in the calculation or assumption of a velocity is less important in a forced circulation system than in a gravity circulation system, and, consequently, it. is easier to design a satisfactory forced circulation system than a satis factory gravity circulation system. ' . In forced circulation systems, it is common practice to use a tempera ture drop of 20 to 30 deg across the boiler or heater. Next, the allowable friction in the water circuit must be decided. The allowable friction is 1000 000 s controlled partly by the characteristics of the pumps available for this service. The heads developed by these pumps range from 2 to 5 ft for residential systems up to 100 ft for institutional heating plants. The problem in sizing of pipe is one of selecting sizes which will cause a circuit resistance approximately equal to the head available to produce circulation when the desired quantity of water is flowing. ' The friction loss in black iron pipes for a determined weight of water may be obtained from Fig. 3. For the frequently used temperature drop of 20 deg the friction loss may be determined directly, from the heat requirement by means of Table 1 or Fig. 4 for black iron pipes, or by'. means of Table 2 for copper tubing. - The resistance of various- types of fittings expressed in equivalent elbow resistance is shown in Table 3. . 452 CHAPTER 24 1946 Guide - Table 1. Heat-carrying Capacity of Standard Black Pipes with Temperature Drop of 20 Deg3 Nominal Pipe'Sizes % in. to lg in., and Friction 4 to 800 milinches perfoot (4 = Capacity,' ` Mbh. B : Velocity, inches per second) (One milinch equals 0.001 in.) Milinch Feic- Nominal Pips Sizb, Inches Foot of Pipe 4A H a % IK IM 2 2H 3 3H 4 5 6 8 10 12 0-75 1.35 2.85 1.5 1.7 2.1 5.4 11.3 17.0 33.0 53.1 2.4 2.9 33 3.8 43 95 5.0 141 197 363 590 1250 2320 3730 53 6.0 7.0 7.9 9.6 11 12 6 A B 0.9 1.7 3.6 6.75 14.0 213 413 66.4 119 176 248 456 748 1.8 2.1 2.6 3.0 3.6 4.0 4.7 53 6.2 6.9 73 83 10 2920 4690 12 14 16 8 A B 1.05 2.1 2.0 2.5 4.2 3.0 7.9 16.4 243 48.4 77.9 33 43 4.7 5.6 6.3 140 73 207 291 535 879 1850 3440 5520 8-0 8.8 10 12 14 17 19 10 A 1.2 2.2 4.7 8.9 18.6 28.0 54.7 88.1 158 234 329 605 997 2100 3910 6270 B 2.4 2.8 3.4 4.0 43 53 63 7.1 83 9.1 9.9 12 13 16 19 27 12 A 1.35 2.45 5.2 93 203 31.0 60.4 97.4 175 259 364 671 1100 2320 4330 6950 B 2.7 3.1 3.7 4.4 5.3 5.9 6.9 73 9.1 10 11 13 15 18 21 24 14 A ' 1.45 2.65 5.65 10.7 22.3 33.7 65.8 106 190 282 397 731 1200 2530 4730 7590 B 2.9 3.4 4.1 43 5.7 6.4 7.6 83 9.9 11 12 14 16 20 23 26 16 A 1.55 2.85 6.05 113 24.0 363 703 114 205 303 428 787 1300 2730 5100 8190 B 3.1 3.6 4.4 5.1 63 6.9 8.1 9.7 11 12 13 15 17 21 25 28 20 A 1.75 3.25 6.85 13.0 27.1 41.0 80.0 129 232 344 484 892 1470 3100 5790 9300 B 3.5 4.1 4.9 . 83 7.0 7.7 9.2 10 12 13 15 17 20 24 28 32 25 A B 2.0 3.65 7.75 14.7 30.6 463 903 146 263 389 548 1010 1670 3510 6570 10560 4.0 4.6 5.6 63 7.9 8.8 10 12 14 15 17 19 22 27 32 36 30 A 22 4.0 8.55 16.2 333 51.2 100 162 290 430, 607 1120 1850 3900 7280 11710 B 4.4 5.1 6.1 73 8.7 9.7 11 13 15 17 18 22 25 30 35 40 35 A .B 2.35 4.4 93 17.6 363 55.7 109 176 316 469 661 1220 2010 4250 7940 12780 4.7 5.5 6.7 7.9 93 11 13 14 16 18 20 23 27 33 39 44 40 A 2.55 4.7 10.0 18.9 39.6 59.9 117 189 341 505 712 1320 2170 -4580 8570 13780 B 5.1 5.9 73 8.4 10 11 13 15 18 20 22 25 29 35 42 47 50 A 2.85 53 113 21.4 44.7 67.7 133 214 386 572 807 1490 2460 5190 9720 15650 B 5.7 6.7 8.1 93 12 13 15 17 20 22 24 29 33 40 47 54 60 70 ` 80 A B. A B A B 315 5.85 12.4 23.6 49.4 74.9 147 238 427 633 893 1650 2730 5760 10780 17360 6.3 7.4 8.9 11 13 14 17 19 22 25 27 32 36 44 52 60 3.45 635 133 25.7 533 81.4 160 258 465 690 973 1800 2970 6280 11760 18950 6.9 8.0 9.7 11 14 15 18 21 24 27 29 35 40 48 57 65 3.7 63 143 27.6 57.9 87.6 172 278 600 743 1050 1940 3200 6770 12690 20440 7.4 8.6 10 12 15 17 20 22 26 . 29 32 - 37 43 52 62 70 100 A 115 7.7 16.4 31.1 65.4 993 194 314 566 840 1190 2200 3630 7680 14400 23200 B 8.3 9.7 12 14 17 19 -22 25 30 33 36 42 48 .59 70 80 150. 200 300 A B A B A B 5.2 9.6 20.4 383 81.6 124 243 393 709 '1050 1490 2760 4560 9650 18120 29220 . 10 12 15 17 21 23 28 32 37 41 45 53 61 74 88 101 6.05 113 23.9 45.4 95.5 145 285 461 832 1240 1750 3240 5360 11350 21320 34400 12 14 17 20 25 27 33 37 43 v 53 62 87 104 118 7.5 13.9 29.7 56.6 119 181 356 577 1040 1550 2190 4060 6730 14270 26830 43300 15 18 21 25 31 34 41 46 54 60 66 78 90 110 131 149 400 A 8.75 163 34.7 663 140 212 417 676 1220 1820 2570 4780 7910 16790 31580 51000 B 18 21 26 30 36 40 48 54 64 71 78 92 105 129 154 175 500 A 9.85 183 39.2 .74.8 158 239 471 765 1380 2060 2910 5410 8970 19040 35840 57880 B 20 23 29 33 41 45 54 62 72 80 88 104 119 147 174 199. 600 A . 10.9 20.2 433 823 174 264 .521 846 1530 2280 3220 5990 9930 2l(o0 39740 64210 B 22 26 32 37 45 50 60 68 80 89 97 115 132 162 193 221 800 A 12.7 23.6 603 96.5 204 .310 610 992 1790 2670 3780 7030 11670 24820 46780 75620 B 25 30 37 43 52 59 70 80 94 104 114 135 155 .191 228 260 For other temperature drops the pipe capacities may be changed correspondingly. For example, with i temperature drop of 30 deg the capacities shown in this table are to be multiplied by 1.5. Hot Water Heating Systems and Piping 453 Table 2. Heat-carrying Capacity of Type.L Copper Tubing with Temperature Drop of 20 Deg3 ' Nominal Tube Sizes % in. to 4 in., and F.riction 60 to 720 milinches per foot. {A = Capacity, Mbh. B = Velocity, inches per second) (One milinch equals 0.001 in.) Nominal Tube Size, In. A KB A KB A % y B A V. B A 1B A IK - B A 1H B A 2B A 1A B A 3B A 3K B A 4B 720 10 27 20 35 36 37 51 42 104 48 185 55 300 62 625 76 1130 90 1840 98 2750 110 3900 120 600 9 24 18 30 30 34 46 38 94 45 169 51 270 67 560 68 1010 80 1650 90 2480 100 3505 108 480 8 21 16 25 26 30 40 33 82 39 149 45 235 51 495 59 890 ,69 1450 80 2170 89 3100 96 Milinch Friction Loss pbb Foot or Tubs 360 300 68 6.2 18 168 138 12 21 19 22.1 20 24 21 34 31 27 24 70 63 34 30 125 112 39 35 200 180 43 39 420 . 375 51- 47 750 680 58 49 1210 1100 66 59 1840 1650 75 66 2600 2350 83 73 240 180 5.4 4.6 14 13 10.8 9 17 15 17.8 15 19 17 28 23.2 21 19 56 47 25 22 100 84 30 25 160 134 35 30 335 280 42 36 600 500 47 42 980 820 52-. 47 1450 1210 57 51 2090 1760 63 55 150 120 4 3.6 11 - 10 87 13 12 13.1 118 15 13 208 18.1 17 14 42 37 19 17 75 66 22 19 120 105 25 22 250 200 32 . 27 450 395 37 33 740 650 42 36 1100 980 45 40 1580 1390 49 44 90 75 3 28 88 8 6 5.4 10 9 9.9 9` 11 10 158 13.9 12 118 32 23 148 13 56 50 17 15 90 81 19 17 1SS 170 22 20 335 305 26 23 550 - 490 30 27 820 740 35 30 1180 1080 37 34 60 2.4 7 4.7 8- 7.9 9. 12.1 ' 10 2& 12 44 13 71 15 150 18 - 270 21 420 23 650 26 950 29 For other temperature drops the pipe capacities may be changed correspondingly. ` For example, with temperature drop of 30 deg, the capacities shown in this table are to be multiplied by 1.5. Table 3. . Iron and Copper Elbow Equivalents3 Fitting , Elbow, 90-deg.................... Elbow, 90-deg long turn__ Elbow, welded, 90-deg..... Reduced coupling............. Open return band............. Iron Pipe 1.0 0.7 0.5 0.5 0.4 1.0 0.5 12.0 Copper Tubing Fitting 1.0 0.7 0.5 0.5 0.4 1.0 0.7 17.0 Angle radiator valve.---- Boiler or heater.-............... Tee, per cent flowing through branch: 100... ................................... 50............................... 25............................... Iron Pipe 2.0 3.0 3.0 1.8 4.0 16.0 Copper Tubing 3.0 4.0 '4.0 1.2 4.0 20.0 The friction in one 90 deg standard elbow is approximately equal to the friction of a length of straight pipe of the same nominal size and 25 diam long. Hence one elbow equivalent equals 25 D divided by 12 ft of straight pipe or tubing, . v When a reversed return system is used, it is usually found that but little adjustment is required to attain uniform distribution to all radi ators. In larger systems, orifices may become desirable to. assist in balancing flow. The resistance introduced by various sizes of orifices is listed in Table 4'. _. As systems increase in size, it becomes desirable to provide two valves . X . *54 CHAPTER 24 1946 Guide - (or each radiator or heating unit, to permit its removal without requiring the draining of the entire system. .One valve may be of the lo.ck shield type so that it may be used for balancing flow. . All large systems should be provided with extra stop and drain valves, suitably located so that parts of the system may be isolated for repairs without making it necessary to drain the water from the entire system. FLOW OF WATER IN GALLONS PER MINUTE . To find friction when temperature drop is other than 20 deg, multiply the actual heat conveyed by --acrt--uail--te--m---p--jd--r-o--p-1/ and read the corresponding friction. '_ GRAVITY CIRCULATION PIPE SIZES In gravity hot water heating systems the difference in density between the flow and return water produces the required natural circulation of _ the water. The design temperature difference is usually assumed from between 20 to 35 deg. After having determined the temperature dif/ ference and the temperature, of the flow' water, data given in Fig. 5 can ` be1 used to obtain the head available for circulation. With this infor. mation determined, pipe sizes which will have-a resistance equal to the Hot Water Heating Systems and Piping 455 Table 4. Friction (in Milinches) of Central Circular * Diaphragm Orifices in Unions ' (One mUinch equals 0.001 in.) - - . Diameter or Orifices (Inches) -------:--:-------23 VsLoerrt or Watkb in Pipe i** Inches pee Second 4 j~ 6 | 8 | 10 j 12 [ 18 24 36 %-in. Pipe 0.25 0.30 0.35 0.40 0.45 0.50 0.55 1300 650 330 170 2900 1450 740 380 , 185 5000 2500 1300 660 330 - 155 75 11,300 5700 2900 1500 740 350 170 20.800 32,000 10,400 16,000 5200 8000 2600 . 4000 1300 2000 620 970 300 480 45,000 23,000 12,000 6800 2900 1400 700 57,000 26,000 13,000 6500 3200 1600 - 47,000 24,000 53,000 12,000 27,000 5700 13,000 2800 6400 1-in. Pipe 0.35 0.40 0.45 0.50 0.55 0.60 0.65 900 2000 460 1000 270 570 160 330 . 190 3500 1800 1000 580 330 200 -120 O' r- 7800 4000 2300 1400 440 260 14,000 7200 4100 2300 1300 800 460 22,000 32,000 12,000 17,000 6400 9300 3700 5400 2200 3000 1300 1800 720 1100 37,000 65,000 2i,000 37,000 12,000 22,000 50,000 7000 .13,000 28,000 4200 7400 17,000 2400 4300 10,000 j li/c-in. Pipe 0.45 0.50 0.55 0.60 0.65 0-70 0.75 1000 660 430 280 190 2250 1450 950 630 420 285 190 4000 2600 1700 1100 750 510 330 8900 5800 3800 2500 1700 . 1150 750 16,000 10,400 6800 4400 3000 2000 1300 25,000. 36,000 16,400 23,000 10,500 15,000 6900 10,000 4700 6700 . 3100 4500 2100 3000 53,000 34,000 22,000 15,000 10,000 6700 60,000 40,000 27,000 60,000 18,000 40,000 12,000 26,000 0.55 0.60 0.65 0.70 0.75 0.80 0.85 850 600 400' 260 180 1900 1300 850 600 400 300 200 3300 '2300 1500 1100 760 540 380 1 Vz~in. Pipe 7400 5400 3600 2600 1800 1200 860 13,000 8600 7200 4400 3000 2200 1600 21,000 16,800 10,400 7000 . 5000 3200 2300 30,000 21,000 14,000 10,000 7000 5000 3000 50,000 30,000 21,000 14,000 10,200 7800 53,000 39,000 28,000 19,000 13,000 2-in. Pipe 0.70 0.80 0.90 1.00 1.10 1.20 1.30 . 890 470 255 160 1850 975 560 340 214 3500 1800 1000 610 375 195 ' 7400 3900 2200 1320 850 460 275 14,000 22,300 7400 .11,700 4200 6500 2520 4000 1600 2500 950 1360 525 980 33,000 17,000 37,000 9500 20,500 38,000 5800 12,500 23,000 49,000 3700 7900 14,000 30,000 1910 4200 . 8100 16,800 1375 , . 3100 4400 . 8850 Note.--The losses of head for the orifices in the lH-in. and 2-in. pipe were calculated from those in the smaller pipes, the calculations being based on the assumption that, for any given velocity, the loss of head is.a function of the ratio of'the Hiam>tr of the pipe to that of the orifice.,. This had-been found to.be/ practically true in the tests to determine the tosses of head in orifices in &-in.. 1-in-, and l}-ln. pipe, con-, ducted .by the Texas Engineering Experiment Station, and also in the tests to determine the-losses of head in orifices in 4-in., 6-in., and 12-in. pipe, conducted by the Engineering Experiment Station of the University of Illinois, (Bulletin 109. Table 6, p. 38. Davis and Jordan). - `* 456 CHAPTER 24 1946 Guide head available for circulation may be selected from the charts or tables in the same manner as for forced circulation systems. . Radiator heat emission rates from 150 to 200 Btu per square foot are commonly used so that flow temperatures generally range from 180 to 200 F or higher. Assuming a flow temperature of 200 F and a 35 deg drop, and with the mains located 4 ft above the top of the boiler, a head of 600 milinches results. This is obtained by following the 200 F floor riser line in Fig. 5 to where it intersects the 165 F return riser line and Hot Water Heating Systems and Piping 457 as illustrated in Fig. 6, or closed as shown in Fig. 7. An open expansion tank has free vent to the atmosphere and consequently the pressure on the surface of the water is always.that of one atmosphere.. The minimum contents of an open tank should be 0.06 of the volume of the water in the system including that in the boiler, heat transmitters, pipes, etc. This capacity is 50 per cent in excess of the actual increase in volume of water due to increase in temperature from 40 F to 200 F. ` The tank should be located at least 3 ft above the highest radiator. Provision must be made to prevent freezing of the water in the tank as well as in the pipe' leading to the tank. . In a gravity circulation system, the pipe to the open expansion tank should be connected to the supply riser from the boiler, so that the air liberated from the water in the boiler will enter the expansion tank. ' In a forced circulation system, the pipe to the open expansion tank Fig. 5. [Heads Resulting from Temperature Difference (Gravity Systems) reading horizontally a head of 150 milinches per foot or 600 milinches for 4 ft.. Assuming first floor radiators are located 3 ft above the mains and second floor radiators 12 ft above the mains, third floor 21 ft, and fourth floor 30 ft, the heads are 450, 1800, 3150 and 4500 milinches respectively.^ EXPANSION TANKS ': Water heated from 40 F to 200 F expands about 0.04 of the original .volume. The expansion tank permits the change in volume of the water ' in the heating system to take place without producing undesirable stresses due to pressure in any part of the system. Expansion tanks may be open, should be connected on the suction side of the circulating pump,'so that the head on the suction side of the pump will remain practically constant. ,A closed expansion tank is sealed against free venting to the atmos phere. The tank may be above the highest radiator or heat transmitter, or may be below the lowest one. The minimum contents of a closed expansion tank must be such that the expansion of the water due to increase in temperature will be cushioned against a reservoir of compressed air above the water level in the expansion tank. The tank must provide space not only for the change in water volume, but also for variations in air volume within the tank due to changes in air pressure. If the closed, expansion tank is below the heat transmitters, the tank should be larger than if it is above them, and the higher the building, under such circum stances, the larger should .be the air capacity in excess of. that required for increase in water volume due to temperature rise. The size of a basement-located closed expansion tank should be at least equal to the following: . . - One story buildings: x = 0.10 V . Two story buildings: * = 0.13 V Three story buildings: x = 0.17 V Six story buildings: x -= 0.28 V where X = expansion tank size in gallons. . V = water volume in.heating system in gallons. . 458 ; -. CHAPTER 24 - * 1946 Guide This condition favors, especially in tall buildings, the placing of the closed expansion, tank above the highest heat transmitter. ' Any closed expansion tank located above the Tieat transmitters of . a hot water heating system should be connected by a direct pipe with the. ' -flow main leaving the boiler, in order to enable the air to pass easily to the . expansion tank. In a closed hot water, heating system the water under pressure tends to absorb air at a rate increasing with pressure increase ` and decreasing with temperature increase. ,' Means must be provided to adjust and to observe the proportion of air within any closed expansion tank. This involves the provision of an air inlet valve, a water gage and a relief valve. A source of supply' of com pressed air for renewing the air cushion is highly desirable; especially in large; high pressure hot water heating systems where it is inconvenient, if not impracticable, to drain down the water in the system so as to permit introduction of atmospheric pressure air; ^ .. For every hot water heating system the designer should calculate the volume of water contained in the radiators, piping system, boiler, etc., in order to select the proper size of expansion tank. The water content Pipe Size. . In. : X. X 1 IX IX Table 5. Volume of Water in Standard Pipe . Lineal Ft of Pipe . Containing 1 Gal . .' 63.1 36.1 22.2 12.8 9.47 ' ` Pipe Size, . In. Lineal Ft of Pipe Containing 1 Gal . 2 .. 2X 3 4 5 6 ; 5.75 4.02 2.60 1.52 0.96 0.67 of the piping can be obtained from Table 5. For a rough selection of size, however, it is sometimes assumed that 50 per cent of the volume of water1 is contained in the radiators,, and that the water content per square foot t of radiator heating surface is 0.2 gal for column radiators and 0.13 ,gal tor tube type radiators. . 1 . Another rough method for determining the size of an expansion tank to be located above the highest radiator is to divide the square feet of radiation by the factor 40 to obtain the required capacity in gallons, of the expansion tank. . '. . - '/ ` ` \ * .' " . INSTALLATION DETAILS , '* . Items that should be considered in the design of this type of system are: All piping must be so pitched that all air in the system can be vented either through an open expansion tank, radiators or automatic relief valves. .. All piping must be arranged so that the entire system can be drained. Sections, of piping individually valved shall have corresponding drain valves. .' - In large buildings, the-piping may be zoned according to exposure of building, usage - of building, or method of control. . All piping must be installed so that it is free to expand and contract with changes of temperature without producing undue stresses in the pipes or connections. For thi^. purpose it is generally sufficient to allow for a variation in length of 1 in. for 100 ft of pipe. . , The pipe system should be designed so that each circuit has its correct friction for balanced water distribution. This maybe done by change of pipe size or change in pip-. . -ing detail. # , ` ' The connections from the boiler to the mains should be short and direct, to reduce the Hot Water Heating Systems and Piping 459 friction and allow for expansion. It is frequently possible to avoid an elbow and to reduce the length of the pipe by running the pipe in a diagonal direction, either in a, horizontal or in a vertical plane. . ,~ The mains and branches should pitch up and away from the heater, generally not' less than. 1 in. in 10 ft. - ' .. - The connections from mains to branches and to risers should be such that circulation through the risers will start in the right direction. Hence, in a one-pipe system the flow connection must be nearer the heater than the return connection. In a correctly-. designed two-pipe system, the pressure in the flow main is higher than that in the return main, and a slight variation in the distances of the flow and return connections from the heater is not material; but it is generally best to have the two connections about equally distant from the heater.- , * Generally, connections to risers or radiators are taken out of the top of mains either 45 dr 90 deg. In some cases it may be advisable to take the flow connection off the top of the main and the return connection from the side. .. With forced circulation and high velocities, it is advisable to let the water enter at the top of the radiator and leave at the bottom of the opposite end. With gravity circulation Fig. 9. Forced Circulation System the flow connection may be either at the top or at the bottom of the radiator. With short radiators both flow and return may be at the same end, but at top and bottom. Unless used as heating surface, all' piping, both flow and return, should be insulated. ' / EXAMPLES OF PIPING DESIGN . The following'graded series of examples , of the design of hot water piping systems will illustrate the fundamental principles and methods. , . The differences between reversed return and direct return systems are shown, and the methods of balancing the several radiators or circuits are . illustrated. A simple gravity system is shown in Fig. 8 and an elementary , forced-circulation system is diagrammed in Fig. 9. . Elementary Gravity System ; . - Example t\ A simple gravity-circulation system is illustrated in Fig. 8 with one radiator that is giving off heat at the rate of 20,000 Btu per hour or 20 Mbh. The boiler imparts heat to the water at the same rate, and the water circulates at a uniform velocity. This uniform velocity is such that the friction of the circuit is equal to the head developed * by, the difference in density between the supply and return water and the height of the , . system. The circuit consists of 1 boiler, 1 radiator, 2 ells, 1 radiator valve and a total . of.24 ft of pipe. . .. . .. "* .. ' , ' Solution. With the average water temperatures of 200 and 180 F in the supply and ' . return risers, respectively, the head will be 90 milinches per foot of water column. This - . head may be found from Fig. 5. Since the center of .the radiator is 10 ft above the center ' of the boiler,- the total-head of the circuit is 10 x 90, or 900 milinches, or 0.9 inches of 190 F water. The friction of the circuit must then also be 900 milinches. The friction \ . . s 460 CHAPTER 24 , ,________ - 1946 Guide. of 1 ft of 1 in.-pipe is found from Fig. 4 to be about 46 milindhes at 20 Mbh, and the . corresponding velocity 9 in. per second. (Note that all values in Fig. 4 are based on a temperature difference of 20 deg). .' Similarly, if a in. pipe were to be used, the friction head would be about 12 mil- inches per foot and the corresponding velocity about 5 in. per second, from Fig. 4. To find the friction in the elbows, boiler, radiator and valve, Table 3 is used, and the entire circuit is found to be equal to 10 elbow-equivalents plus 24 ft of pipe. Each elbowequivalent is equal to a pipe length of 25 times the nominal diameter. Then the equi valent lengths of straight pipe are 45 ft of 1 in. pipe or 50 ft of 1% in. pipe. Hence, if 1 in. pipe is used, the friction of the circuit will be 45 x 46, or 2070 milinches, and if 1^ in. pipe is used, the friction will be 50 x 12, or 600 milinches. A 1 in. pipe would, therefore, be too small and a \ % in. pipe too large to permit the desired circulation with a flow-return temperature difference of 20 deg. If the circuit is of 1 in. pipe,.the circulation will take place with a temperature differ ence greater than 20 deg, and if the circuit is of Vyi in. pipe, the circulation will take place with a temperature difference smaller than 20 deg. To find, for example, the temperature difference at which a circuit of 1 in. pipe would transmit the required 20 Mbh, assume the difference to be 40 deg. ` ' From Fig. 5, the head available for producing circulation would be 175 milinches per foot or 1750 for the system for a temperature drop from 200 to 160 F. The friction of the Hot Water Heating Systems and Piping 461. the 1 in. pipe line, and read about 77 Mbh delivered by the pipe (with a velocity of about 35 in. per second) for a temperature difference of 20 deg. Since the circuit is to deliver only 20 Mbh, the temperature difference will be 20 divided by 77 and multiplied by 20, or 5.2 deg.' Hence, if the flow riser temperature is 200, the return riser temperature will be' about 195, and the average water temperature in the radiator about 197.5 F. If a in. pipe were used instead of a 1 in., the equivalent length of circuit would be 35 ft instead of 45; the unit head, 686 milinches instead of 533; the velocity, 27 in. per second instead of 35; the temperature difference, 19.5 instead of .5.2; and the average water temperature in the radiator, about 190.5 instead of 197.5 F. . If the 1 in. pipe is used for the circuit, the gravity head will be 22 milinches per foot, or 220 for the circuit (Fig. 5, 200 to 195). Since this is only 1 per cent of the pump head (24,000 milinches), it may be neglected in the calculation, as was done previously. However, there are cases in which the gravity- head is so large compared with the pump head, that it should be included in the calculation. The methods just described for the design of the two elemehtary systems are fundamental and apply to the design of all hotwater heating systems. In every system, however large and complicated, the pipe system must be such that the head' forcing the water from the boiler to any one radiator is equal.to the friction in that radiator's circuit when the Fig. 10. Determination of Required Temperature Difference system may be found from Fig. 4; the.chart of this figure, is based on a temperature difference of 20 deg; if the temperature difference were 40 deg, the heat conveyed would be twice that shown in the chart. Hence, find 10 Mbh on the lower scale, proceed vertically upward to the intersection with the 1 in. line, and from there to the left scale read 13 milinches per foot.. Note that the velocity would then be only about 5 in. per second: The total friction would then be 45 x 13 or 585 milinches. Since the head would be 1750, circulation would take place with a temperature difference less than 40 deg. The required temperature difference may be determined by constructing the diagram of Fig. 10, from which it appears that the temperature difference with which the 1 in. pipe circuit would function is about 30 deg. Hence, if the flow riser temperature is 200, the return riser temperature will be 170, and the average water temperature in the radiator about 185 F. '. Elemehtary Forced Circulation System . , Example 2. Design a system for the piping arrangement shown in Fig. 9, according to one of the outlined procedures. The procedure may be as follows: Assume the head developed by. the circulating pump and the pipe size and find the flow-return tempera ture difference; or, assume the head developed by the pump and the flow-return tem perature difference and find the pipe size; or, assume the pipe size and the.flow-return ,, temperature difference .and find the head which the circulating pump must develop. Solution.' Assume that the'circulating pump will develop a head of 2 ft or 24.000 . milinches and.that a 1 in. pipe is to be used. The equivalent length of the circuit will then be 45 ft, as in Fig. 8, and the available head will be 24,000-/45, or 533 milinches per foot. In Fig. 4; find 533 on the left scale, move horizontally to the intersection with radiator is receiving its proper quantity of hot water and the system is functioning at a steady rate. Two-Pip Gravity Circulation System Example 8: Tn the system'shown in Fig. 11, water leaving the boiler may flow to any one of the three radiators. If the system is designed correctly, each radiator will receive its proper share of the hot water. Since Radiator 3 has the largest load and is also farthest from the boiler, it is the least favorably located with reference to circulation, and its circuit should be designed first. If the pipes leading to it are large enough, it will be easy to secure sufficient circulation for the other two radiators. The system is to function with a 40 deg flow-return temperature difference. The head for each radiator is 7 x 175 (Fig. 5), or 1225 milinches; the friction for each radiator circuit must, therefore, also be 1225 milinches. v Solution. In order to design a radiator circuit accurately and systematically, the circuit should be divided into sections. The division points of sections must be .where the pipe sizes change or may change, and where the volume of water flowing in the pipe changes. The data relating to the several sections may be recorded as shown in Table 6. Data recorded in Table 0 show that Circuit 3 consists of 70.4 ft of pipe and 21.5 elbow equivalents. Assuming that the average size of the pipe will be in., the 21.5 elbow equivalents may be replaced by 21.5 x 2.6 (25/12 x 1.25 x 1.0), or 56 ft of pipe, which would make the total equivalent length of the circuit 70.4 plus 56 or 126.4 ft of pipe, and the average friction 1225/126.4. or about 10 milinches per foot. ;For this unit friction and a temperature difference of 40 deg (see Fig. 4), a 1 in. pipe will-convey 18 Mbh, a in. pipe, 37 Mbh, and a 1J^ in. pipe, 56 Mbh. The pipe sizes for the several sections of Circuit 3 may be selected as indicated in Table 6. Having selected the pipe ( ' ' i|-\| ' 462. CHAPTER 24 1946 Guide. sizes, the unit, friction may be found from Fig. 4 and the total friction calculated and . recorded as shown in Table 6. If the grand total, in the present case 1192 milinches,.. differs materially from the available head, 1225 milinches, one or more of the pipe sizes'.' must be changed and the calculation repeated until the total friction is practically equal to the available head of i225 milinches.-. .. . . . . It is not necessary, in the design of hot water heating systems, to be extremely careful to have the friction exactly equal to the available head, because a hot water heating . system has the ability to adjust itself to varying conditions of considerable magnitude. For example, in the present case, the calculated friction is 1192 milinches, or about 3 per ' cent less than the calculated available head; the water would, therefore, circulate a little faster than contemplated and the return temperature would be a little higher than 160 F. Section 0-4 4-5 5-6 6-3 3-7 7-8 8-9 9-0 Total .Table 6. Tabulated Data for Example 3 Circuit No. 8. Available head 1288 milinches Load Mbh. 45 35 20 20 20 20 35 45 Pips Length Ft \ 3.5 10.0 12.0 6.5 9.5 12.8 13.8 2.3 70.4 Elbows No. 2.5 2.0 0.0 5.5 5.5 1.0. 2.5 2.5 21.5 . Pips . ` Size ' In. ik IK l Equivalent Length, Ft- - Unit Friction Milinches per Ft Total Friction. Milinches 11.3 . 15.2 12.0 17.5 6.3 9.2 3.4 13 :` 71 140 41 228 i l 1H lM 20.5' 14.9 20.3 . 10.1 13 13 - 9.2 6.3 267 194 187 64- , 121.8 1192 0-4. 4-5 5-2 2-8 8-9 9-0 Total 45 35 15 15 35 45 Circuit No. Available head 1225 milinches 6.2 . 9.5 6 7 1 18.7 H ' 20.4 7.5 24.0 71 140 140 . 490 187 64 1092 Circuit No. l. Available head 1225 milinches , 0-4 4-10 10-1 l-ll 11-9 , 9-0 Total 45 10 10 ' 1010 45 . 9.0 5.0 - . 9.5 11.5 1.5 5.5 - 5.5 v 2.5 8 H 11.3 10.7 18.1 15.4 11 ' 46 11 11 \' ' 71 124. 434 ' 199 . 169 64 ' 1067 This would immediately lower the head available for circulation and the balance with the friction would occur at some point between 1192 and 1225 milinches. . Since it is generally not necessary to make extremely refined calculations, Table 1 may often be used instead of the chart of Fig. 4 to determine pipe sizes. For example, in the present case, Table 1 shows that for a friction of 10 milinches a 1^ in. pipe would convey 28 Mbh with a temperature difference of 20 deg or 56 Mbh with a temperature difference of 40 deg.*. Since the 134 in- pipe in Fig. ,10 is to convey only 45 Mbh with a temperature- difference of 40 deg, or only 22.5 with a temperature difference of 20 deg, it ,is evident from the table that the* friction will be between,6 and 8 milinches. For 6 milinches the heat conveyed is 21.2; and for 8 .milinches, it is 24.8; for 22.5 Mbh,.the friction would be estimated to be about 6i5, which would be sufficiently accurate for the present calculation. Having completed the design of Circuit 3, it is simple to design Circuit 2 because it^ has four secticnsin common with Circuit 3 and it is only necessary to design Sections 5-2 and 2t8, as shown in Table 6, so that the total friction of Circuit 2 ..will be practically, equal 'to the .total friction of Circuit 3. . . . * Hot-Water Heating Systems and, Piping 463 Having completed.the design of Circuit 2, it is.necessary to design Circuit 1,-as shown in Table 6, so that its total friction willbe approximately equal to the total friction of the ' other two circuits since all three circuits have equal heads. . Two-Pipe Forced Circulation System Example 4- In the design of a system for Fig. 12, as in the design of Example 2, there are three unknowns--head, pipe size, and flow-return temperature difference, any two of . which may be assumed and the third found. In the design of a system for Fig. 9, the pressure head and the temperature difference were assumed and the pipe sizes found. In this case, the head is to be found. , . - Solution. In selecting the temperature difference and the pipe sizes, it should be borne in mind that' the first cost of the radiation can be. reduced by reducing the tem perature difference and the first cost`of the pipe can be reduced, by increasing water velocity, but the friction is increased and, thus, the cost of pumping. The choice of temperature difference and pipe sizes which produce the greatest economy in first cost and in cost of operation can be determined after haying made two or three trial designs. For the first design, 20 deg will be selected as the temperature difference and the pipe Fig. 12. Two-Pipe Forced Circulation System sizes will be chosen as shown in Fig. 12. A calculation similar to that of Table 7 will show that the friction-of Circuits 1, 2, and 3 will be, respectively, about 9000, 15,300, and 14,300 milinches. To increase the friction of Circuit 1 from 9000 to 15,000 milinches would require the insertion in the circuit of a section of' in. pipe, or an orifice resistor, . or a regulating valve. However, this would cause unnecessary expense. The system .will function well witlrthe pipe'system shown in Fig. 12. If the circulator maintains a head of 15,300 milinches, the velocity in Circuit 1 will increase until the friction of the circuit is also 15,300 milinches; i.e., its friction will be increased from the calculated 9000 to the required 15,300, or 6300 milinches. ;' . . . * . .` As calculated, ithe three radiators are to dissipate 10, 15, and 20 Mbh, respectively, with a temperature difference of 20 deg. Consequently, water must flow through these three radiators at the rates of 1,1.5, and 2 gpm', respectively. When water flows through a % in. pipe at the rate of 1 gpm; the velocity in the pipe is (Fig. 4) about 13 in. per second and the unit friction is 165 milinches. ' The equivalent length of sections 4-10; 10-1, 1-11, and 11-9 of this circuit is 50 ft, and its total friction is 8250. In order thatthe friction may be increased 6300 milinches, the unit friction must be increased 126 milinches; consequently, the velocity in the H in. pipe (Fig. 4) must be increased from 13 to 16 in. per second. Hence, when the friction* of-Circuit 1 has been increased to 15,300, water will flow'through Radiator l at the rate of 16 -5- 13, or 1.23 gpm. This increase in volume of water will increase the load on the circulating*pump in the propor tion of 450 to 473 and will increase the heat dissipation-of Radiator 1 slightly (about. 3 per cent) but otherwise will not affect the operation of the system. - ' ' ' ' One-Pipe Gravity Circulation System - .. . , Example 5. A one-pipe system is one in which the.cooled water from the heating units is returned to the supply main. ` A two-pipe system as shown in Figs. 11 and 12 is one in which the cooled water returns to the boiler through a separate return main. 464 CHAPTER 24 1946 Guide Many large heating systems contain some one-pipe and some two-pipe sections. The piping system shown in Fig. 13' functions with a flow-return temperature difference.of 40 deg. ' '. ' Solution. Since the four radiators are each to deliver 15 Mbh, and since the water is to leave the boiler at 200 F and return at 160 F, Radiator 1 will receive 200 F water, Radiator 2, 190 F water, Radiator 3, 180 F water, and Radiator 4, 170 F water. Since the system is to supply 60 Mbh with a temperature difference of 40 deg and since 1 lb of water liberates 1 Btu when cooled 1 deg, it is necessary that water circulate through . this system at the rate of 60,000 '+ 40,* or 1,500 lb per hour, or 25 lb per minute. As suming one gallon of water to weigh 8.33 lb, water must circulate in the system at the. rate of 3 gpm. If the temperature difference were 20 deg instead of 40, the circulation would be at the rate of 6 gpm. It is well to remember that, with a temperature difference of 20 deg, water circulating at the rate of 1 gpm will convey heat at the rate of 10 Mbh. The chart of Fig. 4 shows the rate of circulation in gpm on the upper scale and the corresponding heat conveyance on the lower scale. The system may be divided into 5 separate systems. Each of the four radiators, with Circuit 0-1 1-2 2-3 3-4 4-5 5-6 6-7 7-8 8-16 16-17 17-18 Table 7. Tabulated Data for Example 7 Load Mbh Pipe Length Ft 3600 3150 2700 2250 . 65 130 130 130 1800 1350 900 450 130 130 130 130 Elbows No. 1.8 0 0 0 2 0 0 0 Equivalent Length Ft 78 130 130 130 142 130 130 130 Size In. 6 5 5 5 4 4 3W 2M Unit Friction Milinches pee Ft TOTAL Friction. Milinches 100 / 180 150 100 7,800 23.900 19,500 13,000 ' 210 125 113 190 29.800 16,200 14,700 24.700 450 Estimated Friction * 20,000 3600 7200 65 130 1.8 0 78 130 - 6 100 8 90 Total 7.800 11,670 188,570 its flow and return lines constitutes an elementary heating system (similar to Example 1), and the flow main with its two risers is also a complete elementary system. . . If the center of the boiler is 4 ft below the center of the flow main, and if the flow, riser contains 200 F water and the return riser 160 F water, the head for the main circuit is (Fig. 5) 4 x 175, or 700 milinches. The circuit consists of 110 ft of pipe and 10 elbow equivalents; its equivalent length is about 150 ft if a 2 in. pipe is used as the main. The average head will be 700 4- 150, or 4.7 milinches. According to Fig. 4 or Table 1 for a 4.7 milinch friction, a 2 in. pipe will convey about 70 Mbh. Since the pipe is to convey only 60 Mbh, it is slightly too large but should be used. The friction will,-then, be 3.5 milinches instead of the permissible 4.7. The water wilhcirculate with a temperature . difference slightly less than 40 deg, and the three last radiators would receive water slightly warmer than indicated in Fig. 13. ' . As the water flows in the main and arrives at one of the four points marked A, the flow will be divided and a portion of the water will take the short path in the.main to the point B, and the remainder will take the long path through the radiator to the point B. Since the two paths together offer less resistance to the flow than the one path alone, the unit friction will be less than 3.5 milinches between .the points A and B. If the distance from A to B is 4 ft, and if, for example, the flow in the short path is 2 gpm, the head forcing the water along the two paths is 4 x 1.6, or about 6-railinches. Since the friction of the long path is much greater than the friction of the short path, only a com paratively small portion of the water would take the long path. However,.the gravity head of the radiator supplies, an additional head for the long path'. If the center of the i1'{i 'radiator is 4 ft above the main and if the radiator circuit is designed for a temperature difference of 30 deg, the radiator head will be about 4 x 120, or 480 milinches.. In that case, the head is 6 milinches for the short path and 486 milinches for the long path. The . radiator circuit consists of 11 ft of pipe and about 14 elbow equivalents. If the circuit "is of 1 in. pipe, its equivalent length is about 40 ft and the unit friction should be 486 -5- 40, or 12 milinches. For this friction and 30 deg temperature difference, a 1 in. Hot Water Heating Systems and Piping 1 465 Fig. 13. One-Pipe Gravity Circulation System pipe conveys about 15 Mbh (Fig. 4). A 1 in. pipe is, therefore, the correct size, and the water would flow through the radiator with a temperature difference of 30 deg. Since each of the four radiators delivers one fourth of the total heat, and since the total temperature difference is to be 40 deg, the water would cool 10'deg in every radiator if all the water passed through every radiator. Since the water cools about 30 deg in flowing through the. radiator only of the water flows through the radiator and % flow'through the main from point_A to point B. ' It follows from these calculations that, if the main is of 2 in. pipe arid the radiator branches are of 1 in. pipe, water will circulate through the system at the rate of 3 gpm with a temperature difference somewhat less than 40 deg and that, at the radiator con nections,- water will circulate through the radiators at the rate of 1 gpm and that, conse quently, between radiator branch connections the friction is less since only 2 gpm flow through the main between those points. . One-Pip Forced Circulation System Example 6. The system shown in Fig. 13 as a gravity circulation system may be changed to a forced circulation system by inserting a circulating pump as shown in Fig. 14. The location of the expansion tank should then be changed as indicated. Solution. Ta design this system the pipe sizes and the temperature difference may be assumed; for example, lj^ in. pipe may be selected for the main and % in. pipe for thge radiator branches and risers, and 20 deg as the flow-return temperature difference. Since the system is to deliver 60 Mbh with a temperature difference of 20 deg, the pump must circulate 60 -5* 10, or 6 gpm. .. For this load, the unit friction for a in. pipe is 86 milinches. The main circuit consists of 110 ft of pipe and 10 elbow equivalents and may be placed equal to 136 ft of in. pipe. -The total friction for the main circuit is 136 x 86, or 11,696 milinches, or ' practically 1 ft for a flow of 6 gpm. At the points A, a portion of the water will be diverted through the radiator circuit, Fig. 14.. One-Pipe Forged Circulation System 466 CHAPTER 24 1946 Guide >. ---------------------------------------------------------------------- ^10C O------------------ --------------------------------- --!-------------- _______ 5"_______ _.__ V______ v_ _5^___________ 17 _ 16_ _3150___ 15_ _2700 _14_ _2250 _13 _ _1 F1 1 a *" a a a ns tn 900 m mh" 450 1350 g* * Pipe sizes Mbh for each pipe 111800' i 1 . 1 5" Id J| ' ' V` J 4 5" d .1- 5 d :t!o d 3150 CHI 2700 CD- 2250 d 1 .1- 6>| \ 9 450 10 900 11 1350 12 2 SCrMsS*|11 8CfsM. 3500 Mbh . y. 8" pipe . Fig. 15. Two-Pipe Reversed Return System - and as a result less than 6 gpm will flow in the main between the points A and 2?,.and the friction will be slightly less than 86 milinches per foot between these points. But the difference will be so small that it may be neglected and the total friction from A to B as sumed to be 4x86, or 344 milinches. The head forcing the water through the radiator cir cuit will then be 344 milinches. The radiator circuit consists of 11 ft of pipe and about 14 elbow equivalentsand maybe placed equal,to32ftof pipe and the head 344 -5- 32, or about 11 milinches per foot. With this head, a % in. pipe will convey about 5 Mbh (Fig. 4), or 0.5 gpm. Hence, only 5 -r 60, or about 8 per cent of the water, would flow through ' the radiator, if the radiator's gravity head is not considered. The water would, then, have to cool 60 deg in order to deliver 15 Mbh, and the average radiator temperature would be 170 if the water entered at 200. This would require a large radiator and result in an unsatisfactory installation. . ;- . ' To secure a larger flow of water through the radiator it is necessary to increase the . friction of the short path A-B in the main. This may. be done by inserting special resistance tees at points A and B, or by inserting an orifice resistor between points A and ' B, or by reducing the 1% in/main between the points A and B to the next smaller size, i.e. 1 in. . . The relative quantity of water flowing through the radiator may then be found by trial calculations. Assume, first, that 1 gpm will flow through the radiator and 5 gpm through the main. The friction for l.gpm and a % in. pipe is 40 milinches per foot, or, . 32 x 40,. or 1280 for the radiator circuit. ' The main'circuit consists of 4 ft of 1 in. pipe and two reducing tees. The two reducing tees may be placed equal to 0.8 elbow equivalents (Table 4), and the equivalent length of the main circuit equal to 5.7 ft. , . ' The friction for 5 gpm and a 1 in. pipe is 240 milinches per foot, or 5.7 x 240, or 1370 milinches for the main circuit. Since this is only slightly more than the calculated friction for the radiator circuit, it is evident that the flow through the radiator will be slightly more than l gpm, and it is not necessary to make a second trial calculation. The quantity of water flowing through the radiator can be varied by varying the distance between the points A and B, where the radiator branches join the main. . ' In order to deliver 15 Mbh to the radiator with a temperature difference of 20 deg, it is necessary that 1.5 gpm flow through the radiator; since, in this case, the flow through, the radiator is only 1 gpm, the temperature difference must be 30 deg. .If the water enters the radiator at 190 F, the average water temperature will be .175 F. The quantity of water circulating through the radiator may be varied con siderably without an appreciable effect on the quantity of heat dissipated by the radiator. This is evident from the following calculation. Assume that Radiator 2 has been designed so that it will dissipate 15 Mbh when its flow of water is at the rate of 1 gpm, and when its average temperature is 175 F. -Assume Hot Water Heating Systems and Piping 467 that the flow of. water is increased 50 per cent--from 1 gpm to 1.5 gpm. The water will then flow through the radiator in two-thirds the time and will cool two-thirds as much; i.e., it will cool 20 deg instead of 30 deg, and the average radiator temperature will be 180 F instead.of 175 F. If the surrounding temperature is 70 F, the temperature.dif-. ferences, radiator and surroundings, will be 110 and 115 deg, respectively. Consequently,' the heat dissipation will be increased only about 6 per cent when the quantity of water flowing through the radiator is increased 50 per cent. By decreasing the main from V/i to 1 in. between radiator branches while the flow is decreased from 6 to 5 gpm, the friction in that section of the main is increased from 344 to 1370 milinches, or 926 milinches. Hence, for the four radiator sections the increase is 3704 milinches, and the total friction for the circuit will be 11,696 plus 3704, or 15.4 in. instead of 11.7 in. as first calculated. The pump must, therefore, circulate 6 gpm against a head of 1.3 ft. ' . Reversed and Direct Return Systems In a reversed return system the radiators are connected so that all circuits are practically of equal length and so that the water flowing through the radiator nearest the boiler must travel practically as far as the water flowing through the radiator farthest from the boiler, as illus trated in Fig. 15. In a direct return system the radiators are connected so that all.water returns to the boiler along the most direct path after it has passed through its.radiator, as illustrated in Fig. 16. . ' Example 7. In Fig. 15, sixteen air conditioning units, each demanding 450 Mbh, are to be supplied with water from a central plant. The system is divided into two equal parts as shown. Each part supplies eight units and has, therefore, eight circuits. The total length of each of the eight circuits is about 1170 ft. Solution. If the total friction is to be about 15 ft, the unit friction must be about 150 milinches per foot. With this preliminary estimate, pipe sizes may be selected from > Fig. 4 and recorded with corresponding calculations as shown in Table 7 for Circuit 8, from which it appears that the friction of this circuit is 188,570 milinches, or 15.7 ft. In order that each of the eight air conditioning units may receive an equal supply of water, the.frictioh of each of the remaining circuits must also be 15.7 ft. Since all pipe sizes have been selected as shown in Example 6, any adjustments that may be necessary must be made in the connections from the main through the air conditioning unit and. back to the main. For Circuit 8 the friction through the air conditioning unit was assumed to be 20,000. milinches. For Circuit 4, for example, a tabular calculation like that for Circuit 8 shows that the friction for Section 4-12 must be 19,700 milinches in order that the total friction may be 15.7. . ' . This is practically equal to the 20,000'milinches assumed for Circuit 8 and this shows how simple it is to secure well-balanced circuits in a reversed return.system. Example 8. The .direct return, forced circulation system shown in Fig.-16 is similar to Fig. 15, except that the water passing through Unit 1 returns directly to the boiler and the total length of this circuit is about 130 ft, whereas, the total length of Circuit 8 is about 1990 ft, or about 15 times as long. '. ` . Solution. The design must begin with Circuit 8. The calculations for this circuit if tabulated as shown for Circuit 8 of Fig. 15 will show that the total friction is 318,200 . milinches, or 26.5 ft, as compared with 15.7 ft for the reversed return system. In order that each of the eight units will receive its correct share of the water, the friction of each of the other seven circuits must also be 26.5 ft- .For Circuit 1, for ex ample, the total friction for Section 0-1 and 16-17 is 15,600 milinches; hence, the friction in Section 1-16 (through the air conditioning unit) must be 302,600 milinches, or 25.15 ft to prevent Unit 1 having an advantage over Unit 8. Comparing the reversed return system of Fig. 15 with the direct return system of Fig., 16 it appears that the head against which the pump must deliver the 720 gpm is 15.7 ft as compared with 26.5 ft for the direct return and that the installation of the reversed return would require 130 ft of 8 in. pipe not necessary for the direct'return system. The friction in the lines joining the pump to the pipe system shown in Figs. 15 and 16 is not included in this calculation. . ' . CHAPTER 25 t^adiatord and. C^onuectorS Heat Emission of Radiators and Convectors, Types of Radi ators, Convectors, Radiator and Convector Ratings, Effect of Operating Conditions, Heating Effect, Heating Up the Radi ator and Convector, Enclosed Radiators THE accepted terms for heating units are: (1) radiators, for direct surface heating units, either exposed, enclosed, or shielded, which emit a large percentage of their heat by radiation; and (2) convectors, for heating units having a large percentage of extended fin surface and which emit heat principally by convection. Convectors are dependent upon enclosures to provide the circulation by gravity of large volumes of air.' HEAT EMISSION OF RADIATORS AND CONVECTORS Most heating units emit heat by radiation and convection. The re sultant heat from these processes depends upon whether or not the heating unit is exposed or enclosed and upon the contour and surface charac teristics of the material in the units. An exposed radiator emits roughly half of its heat' by radiation, the amount depending upon the size and number of sections. When the radiator is enclosed or shielded, the proportion of radiation is further reduced. The balance of the emission is by conduction to the air in con tact with the heating surface, and the resulting circulation of the air warms by convection. . ~ A convector emits practically all of its heat by'conduction to the air surrounding it and this heated air is in turn transmitted by convection to the rooms or spaces to be warmed, the heat emitted by radiation being negligible. . The output of a radiator can be measured only by the heat it emits. The old standard of comparison used to be square feet of actual surface, but since the advance in radiator design and proportions, the surface area ,, alone is not a true index of output. (The engineering unit of output is the Mbh or 1000 Btu per hour.) However, during the period of transition, from the old to the new, radiators may be referred to in terms of equivalent square feet. For steam service this is based on. an emission of 240 Btu per (hour) (square foot) and for hot water service 150 Btu. TYPES OF RADIA' TOR\S . Present day radiators may be classified as tubular, wall, or window type and are generally made of cast-iron. Only the small-tube type of tubular radiators with a spacing of 1% in. per section are now available, ' the large-tube type which had a spacing of 2J^ in. per section having been discontinued. Small-tube radiators occupy less space and are particularly suited for installation in recesses. After a complete study of the demand for various sizes of radiators, the Institute of Boiler and Radiator Manufacturers, in cooperation with the Division of Simplified Practice, National Bureau of Standards, established Simplified Practice Recommendation R174-43 for small-tube cast-iron radiators. Table 1 shows the size and dimensions of small-tube cast-iron radiators' which are being manufactured at the present time. Wall radiators are now rated in terms of equivalent square feet, the same as small-tube radiators. Tests have shown that the heat emitted . 468 \' . Radio tors and Convectors 469 Table 1. Small-Tube Cast-Iron .Radiators Number of Tubes per Section 3d 4d 5d 6d Catalog Rating , PER Section Sq Ft 1.6 1.6 1.8 20 2.1 2.4 1.6 2.3 3.0 3.7 Section Dimensions A Heights In. B Width ' Minimum Maximum In. Iil c Spadngb In. 25 3M 3'A w 19 4% 4% W m22 4J6 4% m25 4% 4% 22 25 5m% 6% mm 14 6*% 8 19 6% 8 25 6% 8 32 6% 8 mmm i*A D . 'tcr. Leg Height 11 w In. 2H - 2lYAi 2H m2K 2H 2J4 214 , 11 ft \ The square foot of equivalent direct steam radiation is defined as the ability to emit 240 Btu per hour, with steam at 215 F, in air of 70 F. These ratings apply only to installed radiators exposed in a normal manner: not to radiators installed behind enclosures, grilles, etc. (See A.S.H.V.E. Code for Testing Radi- " ators adopted January, 1927.) '' t>Length equals number of sections times 1$^ in. . Over-all height and leg height, as produced by some manufacturers, are one inch (1 in.) greater than shown in Columns A and D. Radiators may be furnished without legs. Where greater than standard leg ' . heights are required this dimension shall be 4M in. , dOr equal. from a wall-type radiator may be reduced from 5 to 10 per cent if the radiator is placed near the ceiling with the bars horizontal and in an air temperature exceeding 70 F. When radiators are placed near the ceiling, there is usually such a large difference in the temperature between the floor level and the ceiling that it becomes, difficult to heat the living zone . of the room satisfactorily. - . ' Pipe coils are assemblies of standard pipe or tubing (1 in. to 2 in.) which are used as radiators. In older practice these coils were commonly used in factory buildings, but now wall-type radiators are most frequently used for this servicer When coils are used, the miter type assembly is to be preferred as it best cares for expansion in the pipe. Cast manifolds or headers, known as branch tees, are available for this construction. The heat emission of pipe coils placed vertically on a wall with the pipes horizontal is given in Table 2. This has been developed from avail- Table 2. Heat Emission of Pipe Coils Placed Vertically- on a Wall (Pipes Horizontal) Containing Steam at 215 F and Surrounded with Air at 70 F Btu per linear foot of coil per hour (not linear feet of pipe) Size or Pipe Single row........... ...... ...... ............... .......... Two , Four Six........................ ...................... ................. Eight.... ..................................... .............. .. Ten * Twelve 1 In. 132 252 . 440 567 651 732 812 1541. 162 312 545 702 796 907 1005 154 Ik; .185 348 . . 616 . 793 907 . 1020 1135. ' .470 CHAPTER 25 . 1946 Guide able data and does not represent definite results of tests. For'such coiis the heat emission varies as the height of the coil. The heat emission of each pipe of ceiling coils, placed horizontally, is about 126 Btu, 156 Btu, and .175 Btu per linear foot of pipe, respectively, for 1-in., lj^-in., and li^-in. coils. ' ' , CONVECTORS Cast-iron radiators may be concealed in a cabinet or other enclosure for appearance. In such cases a greater percentage of heat is conveyed to the room by convection thereby resulting in a form of gravity convector. A typical recessed convector is shown in Fig. 1. The heating element consisting of a large percentage of fin surface is usually shallow in depth and placed low in the enclosure in order to produce maximum chimney ' effect in the enclosure. The air enters the enclosure' near the floor line just below the heating element, is moderately heated in passing through Fig. 1. Typical Recessed Convector the core and delivered to the room through an opening hear the top of enclosure. Since the air can only enter the enclosure at the floor line, the cooler air in the room, which always lies at this level, is constantly being withdrawn and replaced by the warmer air. This air movement accom plishes the-desired reduction in temperature differentials and assures . maximum comfort in the living zone. .. '. Concealed heaters or convectors are generally available as completely built-in units'. The enclosing cabinet should be designed with suitable air inlet and outlet grilles to give the heating element its best performance. Tables of capacities are cataloged for various lengths, depths and heights, ; and combinations are available in several styles for installations, such as the wall-hung type, free-standing floor type, recess type set flush with wall or offset, and the completely concealed type. Most of these types may be arranged with a topi outlet grille in a plane parallel with the floor, although the front outlet is practically standard. In cases where enclosures are to . be used but are not furnished by the heater manufacturer, it is important that the proportions of the cabinet and the grilles be so designed: that they ' ' Will not impair the performance of the assembled convector. It is desirable that the enclosure or housing for the convector fit as snugly as possible ' Radiators and Convectors 471 so that the air to be heated must pass through the convector and cannot be by-passed in .the enclosure. * . The output of a convector, for any given length and depth, is a function . of the height. Published ratings are generally given in terms of equiva lent square feet, corrected for heating effect. However, an extended surface heating unit is entirely different structurally and physically- from a direct radiator and, since it has no area measurement corresponding to . the heating surface of a radiator, many engineers believe that the per formance of convectors should be stated in Btu. For steam convectors, as for radiators, 240 Btu per hour may be taken as an equivalent square foot of radiation. When more than one heating unit is used, one mounted . above the other in the same cabinet, the output of the upper unit or units will be materially less than that of the bottom unit. RADIATOR AND CONVECTOR RATINGS A standard method of testing radiators was adopted by the A.S.H.V.E. in 1927 *. This Code provides for a standard test room, the' temperature of which is to be maintained at 70 F, measured in the center of the room at . an elevation of 5 ft above the floor. The steam temperature in the radi-; . ator is to.be 215 F, which corresponds to 15.6 ib per square inch absolute. The weight of condensate per hour, under, these standard conditions, multiplied by the difference in the enthalpy of the steam entering the radiator and that of the condensate leaving the radiator, gives the radiator output in Btu per hour. This output divided by 240 gives the steam rating of the radiator in square feet. .' Similar test methods for convectors are the A.S.H.V.E. Codes for - Testing and Rating Concealed Gravity Type Radiation 2, (Steam Code 1932 and Hot Water Code 1933). These Codes recognize a different type of test booth, and the air temperature used is that of the air entering the convector casing instead of the temperature in the center of the room.. ' The entering air temperature for standard test conditions is 65 F. For hot water the'standard test conditions call for a mean temperature of the. water in the convector of 170 F. .. The Convector Manufacturers Association has adopted the A.S.H.V.E. standard in the formulation of its ratings and. has compiled a tentative standard of heating effect allowances for various enclosure heights to be included in the ratings by its members. . All published ratings bearing the title C.M.C. Ratings (Convector Manu facturers Certified Ratings) indicate that the convectors have been tested in accordance with the A.S.H.V.E. Code by an impartial and disinterested laboratory and that the ratings have been approved by the Standardiza tion Committee of the Convector Manufacturers Association. . . ' Effect of Operating Conditions .- ' ; The heat output of a radiator is proportional to the 1.3 power of the temperature difference between the air in the room at the 60 in. level and the heating medium in the radiator. The heat output of a convector is proportional to. the 1.5 power of the temperature difference between the . air entering the convector and the heating medium, steam or hot water, within the convector3. For hot water the arithmetical average between entering and leaving water temperatures is used. These laws may be expressed as correction factors to change from output under standard 472 _________ t CHAPTER 25 1946 Guide Table 3.. Correction Factors for Direct Cast-Iron Radiators and Convectors8 &TEAM Pssaa. Heating Medium Factors fob Direct Cart-Iron Radiators Factors fob Convectors Approx. . Temp F Gage Aba. Steam Room Temperature F AmInlet Temperature F ' Vacuum Lb per OB Id. Hg. Sqln. Water 80 75 70 65 60 55 50 80 75 70 65 60' 55 50 22.4 ' 3.7 20-3 4.7 17.7 6.0 14.6 7.5 10.9 9.3 6J 11.5 LbperSqlo. 1 15.6 6 21 15 30 27 42 - 52 .67 150 2_58 236 117 2.00 1.86 1.73 1.62 3.14 2JJ3 2.57 2.35 115 1.98 1,84 160 2.17 2.00 1.86 1.73 1.62 1.52 1.44 2.57 235 2.15 1.98 1.84 1.71 L59 170 1.86 1.73 1.62 1.52 1.44 IJ5 1.28 2.15 L98 1.84 L71 1.59 1.49 1.40 180 L62 1.52 1.44 1.35 1.28 1.21 1.15 1.84 1.71 1.59 1.49 1.40 1.32 1.24 190 1.44 U5 1.28 1.21 1.15 1.10 1.05 1.59 1.49 1.40 U2 1.24 1.17 1.11 200 1.28 1.21 1.15 1.10 1.05 1.00 0.96 1.40 U2 1.24 1.17 1.11 1.05 1.00 215 1.10 1.05 1.00 0.96 0.92 0.88 0.85 1.17 1.11 1.05 1.00 0.95. 0.91 0.87 230 0.96 0.92 0.88 0.85 0.81 0.78 0.76 1.00 0.95 0.91 0.87 0.83 0.79 0.76 250 0.81 0.78 0.76 0.73 0.70 0.68 0.66 0.83 0.79 0.76 0.73 0.70 0.68 0.65 270 0.70 0.68 0.66 0.64 0.62 0.60 0.58 0.70 0.68 0.65 0.63 0.60 0.58 0.56 300 0.58 (IST 0.55 0.53 0.52 0.51 0.49 0.56 0.54- 0.53 0.51 0.49 0.48 0.47 "To determine the size of a radiator or a convector for a given space, divide the heat loss in Btu per hour by 240 and multiply the result by the proper factor from the above table. To determine the heating capacity of a radiator or a convector under conditions other than the basic ones with the heating medium at a temperature of 215 F, and the room temperature at 70 F In the case of a radiator, and the inlet air temperature at 65 F in the case of a convector, divide.the heating capacities at the basic conditions by the proper factor from the above table. .. rating-test conditions' to output under other operating conditions. Such . factors are.given in Table 3. When it is desired to change the output under any test conditions to the corresponding output under standard Code test conditions, the reciprocal form of correction factor may be derived.- The equations for steam units are: For radiators: /215 - '70V Ca V t, - <r / For convectors: /215 - 65\l-5 (1) \ -}i ) (2) The output under standard conditions will be: H, = C, Ht where , . . C, = correction factor. . f, = steam temperature during test, Fahrenheit degrees. ' <r = room temperature during test, Fahrenheit degrees. t\ = inlet air temperature during test, Fahrenheit degrees. H$ = heat emission rating under standard conditions, Btu per hour: Ht = heat output under test conditions, Btu per hour. (3) The relation between the size of the radiator or convector and the size ' of the test room will affect the results obtained in a capacity-rating test.4 . The height and location of the radiator and the insulation of the test room . are other important factors that are not specifically regulated by the Code. For a radiator, the finish coat of paint affects the heat output. Oil paints of any color will give about the same results as unpainted black or rusty surfaces, but an aluminum or a bronze paint will reduce the heat emitted by radiation. The net effect may be a reduction of 10 per cent or more in the total heat output of the radiatorM,T. ' .. : Radiator enclosures and convector casings affect the heat distribution within, the.room.as well.as the total amount of heat supplied by the steam or hot water8. - ' ' Radiators and Convectors 473 Heating Effect - For several years the term heating effect has been used to designate the relation between the useful output of a radiator, in the comfort zone of a room, and the total input as measured by steam condensation or water temperatures *10. The application of such a heating effect factor is a recog nition that some radiators and convectors use. less steam than others forproducing equal comfort heating results in the room. No standard method for evaluating the heating effect of radiators and convectors and correlating it with comfort has yet been accepted. One method, with test data11 on radiators and convectors, and making use of the eupatheoscope for evaluating the environment produced, has been suggested by the University of Illinois. The principle underlying the eupatheoscope involves the measurement of the heat loss from a sizable. . 1111111 ii 111 Cold room temp in dee F 11 mu | I' ,,1 J/,.!,.IiU, r. -i .Jill 5.60 b convector No. 1 5.84 lb convector No. 22 6.12 lb convector No. 6 6.32 ib 5-tube radiator Temperature in deg F Position No. 3 Position No. 1 30" level Eouiv Gift 30* level Equiv Oitt 67.7 662 *1.5 67.4 65.9 *1.5 68.2 643 3.9 680 66.6 1.4 68.0 65.1 2.9 67.9 67.9 0.0 682 66.4 *18 56 HEIGHT ABOVE FLOOR IN FEET Fig. 2. Temperature Gradients and Equivalent Temperatures for Radiator and Convectors with Common 30 in. Level Temperature body by radiation and convection, when the surface is maintained at some constant temperature. Through the use of this instrument and its calibration curve, non-uniform environments may be referred to uniform . environments in which the air and all surrounding surfaces are at the same temperature. The temperatures of the uniform environments are referred to as equivalent temperatures. The Kata thermometer1J, the thermo-integrator 13,11, and the globe15 thermometer are other instruments which have been used to measure the influence of air temperature, air movement and radiation in an environment. ' Data given in Fig. 2 show that while the air temperature at the 30-in. level is the same for the three convectors and the one large-tube cast-iron. radiator, in position No. 3 in the test room, the equivalent temperature is 1.5 F lower than the air temperature in the case of the three convectors, and . the same as the air temperature in the case of the radiator. The difference between the minimum and the maximum amount of heat 474 CHAPTER 25 . 1946 Guide .required to maintain the common air temperature at the 30-in. level is of the order of 13 per cent. ' " . In Fig. 3 are shown the results of tests made with the same three convectors and the one large-tube cast-iron radiator, so adjusted in size that each gave approximately the same equivalent temperature in the No. 3 position in the test room. The difference between the minimum and the maximum amount of heat required to maintain the common equivalent temperature is of the order of 7 per cent. . The following statements applying to the use of radiators are based on experience and test results: 1. The heating effect of a radiator cannot be judged solely by the amount of steam condensed within the radiator. .* * Radiators and Convectors - _____ i 475 ^ to a rate of 0:24 lb. In practice the rate of steam-supply to the heating' unit, while heating up, is frequently retarded by controlled elimination of air through air valves or traps. Automatic control valves may also retard the supply of steam. Vacuum types of air venting valves, may be used to reduce the length of the venting periods. ' ENCLOSED RADIATORS The general effect of an enclosure placed about a direct radiator is to restrict the air flow, diminish the radiation and, when properly designed, improve the heating effect. Investigations10 indicate that in the design of the enclosure three things should be considered: 1. There should be better distribution of the heat below the breathing line level to produce greater heating comfort anil lowered ceiling temperatures.. HEIGHT ABOVE F100R IN FEET Fig. 3. Temperature Gradients and Equivalent Temperatures for Radiator and Convectors with Common Equivalent Temperature . 2. Smaller floor-to-ceiling temperature differentials can be maintained with long, low, thin, direct radiators, than is possible with high, direct radiators. . 3. The .larger portion of the floor-to-ceiling temperature differential in a room of average ceiling height heated with direct radiators occurs between the floor and the breathing level. . 4. The comfort level (approximately 2 ft-6 in. above floor) is below the breathing line level (approximately 5 ft-4) in. above floor), and temperatures taken at the breathing line may not be indicative of the actual heating effect of a radiator in the room.. The comfort-indicating temperature should be taken below the breathing line level. 5. High column radiators placed at the sides of window openings do not produce as comfortable heating effects as long, low, direct radiators placed beneath windows. HEATING UP THE RADIATOR AND CONVECTOR -. The. maximum, condensation occurs in a heating-unit when the steam is first turned on. Tests16 on an old-style column-type cast-iron radiator . indicated that in the first 10 min the condensation rate reached a peak of (j.95 lb per square foot of radiator per hour and 10 to 15 min later lowered ' Fig. 4.. Steam Consumption of Exposed and Concealed Radiators 2. The lessened steam consumption may not materially change the radiator heating performance. ' "- 3. The enclosed radiator may inadequately heat the space. .. A comparison between a bare or exposed radiator (A) and the same. . radiator with a well-designed enclosure (B), with a poorly-designed enclosure (C), and with a cloth cover (D) will illustrate the relative heating effects. In Fig. 4 the curve (B) reveals that the enclosed radiator used less steam than the exposed radiator, but gave a satisfactory heating performance. A well-designed shield placed over a radiator gives about the same heating effect. Curve (C) shows the unsatisfactory effects produced by improperly-designed enclosures. Curve (D) shows that the . effect of a cloth cover extending downward 6 in. from the top of the.' radiator was to make the performance unsatisfactory and - inadequate. Some commercial enclosures and shields for use on direct radiators are equipped with water pans for the purpose of adding moisture, to the air in the .room. Tests 17 show that ah average evaporative rate of- about 0.235' lb per square foot of water surface per hour may be obtained from V 476 - CHAPTER 25 1946 Guide such pans; when the radiator is steam hot and the relative humidity in the room, is between 25 and 40 per cent. This source of supply of moisture alone is not adequate to maintain a relative humidity above 25 per cent on a zero day. ., REFERENCES A.S.H.V.E. Code for Testing Radiators (A.S.H.V.E; Transactions, VoI. 33, 1927, p. 18). /a Standard Code for Testing .and Rating Concealed Gravity Type Radiation (Steam). A^n.V.E.T^NSACTiONS.Vo .aT^.iO31. p. 367): (Hot Water), (A.S.H.V.E. Transactions, VoI. 39, 1933, p. 237). (See also A.S.H.V.E. Transactions, Vol. 41,1935. p. 38, and Vol. 42,1936, p. 29). tr Rbbo*t No. 998--Factors'Affecting the Heat Output of Convectors, by A; P. Kratz, M. K. Fahnestock, and E. L. Broderick (A.S.H.V.E. Transactions, Vol. 40,1934,'p. 443).. ,. ^"rj^^etors Influencing the Heat Output of Radiators, by A. C. Davis, W. M. Sawdon and David Dropkin (A-S.H.V.E. Transactions, Vol. 42, 1942, p. 185) and Cornell University, Engineering Experiment Station isuUettn No. 29, April, 1942. . - Bulletino937)TMm Rad*ators' Rubert (Cornell University. Engineering Experiment Station ,r,oi"CoIII?arative Tests of Radiatr Finishes, by W. H. Sevems (A.S.H.V.E. Transactions. Vol. 33. 1927, p. 41). 1 '-Heat Loss from Direct Radiation, by J. R. Allen (A.S.H.V.E. Transactions, Vol. 26, 1920, p. 11). U0nCl?33) Radiators' by E* A` AUcut (University of Toronto, School of Engineering, o!,7The Heatin Effect of Radiators, by Charles Brabble (A.S.H.V.E. Transactions, Vol 33 1927 p. 33). . lo-University of Illinois, Engineering Experiment Station Bulletins Nos. 192 and 223. and Investigation of Heating Rooms with Direct Steam Radiators Equipped with Enclosures and Shields, by A. C. Willard. A. P. kratz. M. K. Fahnestock and S. Konzo (A.S.H.V.E. Transactions, Vol. 35, 1929, p. 77). * '--A.S.H.V.E. Research Report No. 962--The Application of the Eupatheoscope for Measuring the Performance of Direct Radiators and Convectors in Terms of Equivalent Temperature, by A C Willard A. P. Kratz and M. K. Fahnestock (A.S.H.V.E. Transactions, Vol. 39,1963, p. 303). ' 1 *"The Kar^ Thermometer--Its Value and Defects, by W; J. McConnell and C. P. Yagloglou. (Reprint No. 953 from U. S. Public Health Service Report, pp. 2293-2337, September 5, 1924). ,, **"The Thermo-Integrator--A New .Instrument for the Observation of Thermal Interchanges, by L..-E. A. Winslow and Leonard.Greenburg (A.S.H.V.E. Transactions, Vol. 41. 1935, p. 149). . . xl4wTh-e CaUbraiin Thermo-Integrator, by C.-E. A. Winslow, A. P. Gagge,' Leonard Greenburg, 1. M. Monyamaand E. J. Rodee. {.The American Journal of Hygiene, Vol. 22, No. 1, July, 1935, pp. 137-156). . *57The Globe Thermometer in Studies of Heating and Ventilation, by T. Bedford and C. G. Warner. . {The Journal of Hygiene, Vol. ,34. No. 4). _ ^"A/ScH-v-E-Research Report No. 1067--The Cooling and Heating Rates of a Room with Different Radiators and Convectors, by A. P. Kratz, M. K. Fahnestock and E. L. Broderick (A.S.H.V.E. Transactions, VoI. 43. 1937, p. 389). *'-University of Illinois, Engineering Experiment Station Bulletin No. 230, p. 20. \ CHAPTER 26 Definitions; Unit Heaters: Classification, Application, Outlet Velocities, Ratings for Various Types, Temperature, Location, Automatic Control, Piping Connections; Boiler Capacity for ` Steam Unit Heaters; Unit Ventilators: Ratings, Applications, Location, Exhaust Vents; Window Ventilators; Unit Humidifiers . DESCRIPTIONS of heating, cooling, ventilating, humidifying, and dehumidifying systems are given in other chapters. This chapter deals with unit heaters, unit ventilators, and unit humidifiers. Cooling units, unit air conditioners, and attic fans are described in Chapter 36. Definitions '. The generally accepted meaning of the word unit in the terms unit heaters, unit ventilators and unit humidifiers is that of. a factory made, encased assembly of the functional elements indicated by its name. Such units can be shipped complete or in sections so that the only field, work necessary is the assembling of the sections, providing proper sup ports and connecting the unit to sources of heat (or-fuel), power and water supply, and, if necessary, to vent pipes for combustion gases. The term unit heater describes an assembly of elements whose principal function is heating. The essential elements of a' unit heater are a fan and motor, a heater, a housing, and outlet vanes or diffusers. . The term unit ventilator describes an assembly whose principal function is to ventilate. It may serve to circulate air within the space, or to intro duce air from without the space, or may accomplish both purposes. The essential elements of a unit ventilator are a fan and motor, a heater, a set of dampers, a housing and outlet vanes or diffusers. ... The term unit humidifier describes an assembly of elements whose principal function is to humidify. The essential element of a unit humid ifier is an atomizer or evaporator. To this may be added a fan, a heater, outlet vanes or diffusers, and a housing to enclose the various parts. Classification . UNIT HEATERS .' . - The various types of unit heaters which are at present available can usually be classified according to one of the three following methods: 1. By type of heater. Under this classification there are three types of heating elements to be considered: (a) the steam or hot water type, (b) the electric type, and (c) the direct fired type which may be gas, oil, or coal fired'. ,' 2. By type offan. Under this classification there are two types of fans to be considered: (a) the propeller type ` which may be equipped with a horizontal or vertical shaft, and (b) the centrifugal type. which may be designed for horizontal or vertical blow. . 3. By arrangement of elements. . Under this classification there are two types of heaters to be considered: (a) the draw-through type, in which the ' 477 ' ' 478 CHAPTER 26 .1946, Guide fan draws air through, and (b) the blow-through, type, in which the fan . blows air through the heater. ' .' . Unit heaters are available in any combination of the three preceding general classifications. For example, the steam or hot water type may be secured with either the propeller or centrifugal type of fans, and in either the draw-through or blow-through type. . Unit heaters also vary in other minor respects. For example, steam and return inlets and outlets may be located on the top and bottom respectively or on the same side of the unit. Some units are supported by the piping and some have independent supports. The heating surface of steam or water type units is generally made up of a non-ferrous tube . and-fin assembly; or it may be fabricated of steel, or cast in steel. Application of Unit Heaters .. . ' ` Unit heaters are used principally for commercial and industrial appli cations such as garages, factories, laboratories, etc. They may also be used for heating finished rooms, if properly applied and concealed and if ' some consideration is given to the problem of noise. ' ' Unit heaters may also be adapted to a number of industrial processes, such as drying and curing,- in which the use of heated ajr in rapid circu lation with uniform'distribution is of particular advantage. They may be used for moisture absorption, such as fog removal in dye houses, or for the prevention of condensation oh ceilings or other cold surfaces of buildings in which process moisture is released. . When such conditions are severe, it is necessary that the unit heaters draw air from outside in enough volume to provide a rapid air change and that they operate in conjunction with.ventilators or fans for exhausting the moisture-laden air. See dis cussion of condensation in Chapter. 6. . There are three major factors to consider in the application of unit heaters, namely: (1) location of unit, (2) air distribution, and (3) heating medium. ' . There are a variety of applications which are favorable to the use of electric unit heaters. For supplemental heat in residence bath rooms, for the heating of. ticket booths, watchmen's offices, factory offices, locker rooms and other isolated rooms scattered over large areas, their use is peculiarly adaptable. They are. particularly useful in isolated and unattended pumping stations or pits where they may be thermostatically controlled to prevent freezing temperatures. . Gas fired unitheaters find application in industrial plants, offices, stores, garages, in fact in almost every location where steam type units are used. The installation cost of gas fired units is usually less than that of a type requiring that a new boiler be installed. . ... . Oil fired unit heaters are used in industrial plants, garages and com mercial buildings. . ' r' , \ Coal fired unit heaters are of finned, welded steel,' or cast-iron construc tion and equipped with centrifugal blowers. They are usually stoker- fired to insure proper firing of fuel. They are used principally in large, industrial plants such as foundries or'assembly plants, and provide a very economical source of heat, both from the installation and the operating standpoint. .' .- .Outlet Velocities ' . Outlet , velocities of unit heaters vary from about .400 to 2500 fpm depending upon the type of unit and the distance to which the air is to be . .Unit Heaters, Unit Ventilators, Unit Humidifiers________________ . 479 . projected. Noise and. drafts must be considered in the choice of air velocities, since both increase with increase of air velocity. . Velocities and decibel ratings for the various types of. unit heaters illustrated in Figs. 1, 2, 3 and 4 are given in Table 1. . . In the selection of unit heaters it is important not to exceed the throw for which the unit was designed.' . These are dependent to a marked, degree on the temperature of air leaving the heater as well as upon velocities. See discussion under heading of Inlet, Outlet, and Space Temperatures with Unit Heaters. . Air Outlets . .. In order to direct the air to points desired and to diffuse the air to avoid Table 1. Outlet Velocities, Distance of Blow and Decibel Ratings for . ' - . Various Types of Unit Heaters Type of Unit Heater ' Outlet . Velocities FPM Vertical Propeller Fan................. .......... 1500-2500 400-1000 1200-2200 Distances of Blow--Ft 20-200 30-100 70 Decibel Rating 34-90 26-84 50-82 drafts, it is common practice to equip unit heaters with directional out lets, adjustable louvers or fixed types of diffusers. RATINGS OF UNIT HEATERS It is standard practice to rate unit heaters on the basis of the amount of heat delivered by the air in Btu per hour above an entering air tern- perature of 60 F. This applies to all types of unit heaters, the steam or hot water type, the electric type and the direct fired type. There are, however, other factors'which must be taken into account, especially when an attempt is made to compare one type of heater with another. These are the temperature of the heating element and the velocity of air. through it. Consideration is given to these factors in the discussion of ratings for each-type of unit heater in the following paragraphs. Ratings for Steam Type The fating of steam type unit heaters has been standardized by a code 2 in which the following items are the basis of rating: dry saturated steam . at'2 psig pressure (29-92 in. Hg barometric pressure) at the heater coil; air at 60 F entering the heater; and heater operating free of external resistance to air flow. .. The capacity of a heater increases as the steam pressure increases, and decreases as the entering air temperature increases. The heating capacity for any condition of steam pressure and entering air temperature other than standard may be calculated approximately from any given rating- by the use of factors in Tables 2 and 3- Table.2 is used for the blow- through type and Table 3 for the draw-through type of unit. ' Ratings for Hot Water Type . A standard for the rating of hot water type unit heaters has also been established by code 5 in, which the following items are the basis of rating: 480 CHAPTER 26 1946 Guide Fig. 1. Centrifugal Fan Type Unit Heater--Floor Mounted ' - /' Motor^ - 'r 1 'V _ - Ceiling --1 Fan and heater / Fig. 3. Propeller Fan Type Unit . Heater--Horizontal Blow /- i Directional \ outlet -Fig. 4. Propeller Fan Type Unit Heater--Vertical Blow Unit Heaters, Unit Ventilators, Unit Humidifiers 481 entering water at 200 F; entering air at 60 F (29.92 in. Hg barometric pressure); and heater operating free of external resistance to air flow. This code also prescribes a method of translating the output in Btu and the temperature rise as-obtained under test conditions to standard conditions of air and water temperature. Ratings for Electric Type Electric type unit heaters are usually limited in size to a maximum of about 9 kw capacity. They consist of resistance type heating elements combined with fan and motor, together with a suitable casing. Electric unit heaters are made in the built-in-wall model, suspension model, and free-standing or portable model. Electric unit heaters are rated on the energy input to the heater, expressed in terms of kilowatts, Btu or EDR. Quite often all three ratings are given in paralleljColumns in the catalogs. Ratings for Gas Fired Type Gas fired type unit heaters are built with either the propeller or centri fugal type fans. They are available in a wide range of sizes from 45,000 to 1,650,000 output capacity and in suspended or floor models. Gas fired unit heaters are usually rated in terms of both input and output according to the approval requirements of the American Standards Association. - .... . Ratings for Oil Fired Type ' The oil fired type of unit heater is usually equipped with the centrifugal type of fan only and can be secured in sizes ranging from 125,000 to 1.650.000 Btu per hour output capacity in standard units. It is furnished in either the floor mounted or in smaller sizes, in the suspended type. Ratings for Coal Fired Type . The stoker fired type of unit heater can be secured in ranges of from 300.000 to 6,000,000 (or more) Btu per hour output capacity. Ratings are based upon the delivered output at the heater outlet. Effect of Resistance Upon Capacity Unit heaters are customarily rated as free delivery type units. If out side air intakes, air filters, or ducts on the discharge side are used with the unit, a reduction in air and heating capacity will result because of this added resistance. The percentage of this reduction in capacity will depend upon the characteristics of the heater and on- the type, design and speed of the fans, so that no specific percentage reduction can be assigned for all heaters at a given added resistance. In general, however, propeller fan type units will experience a larger reduction in capacity than, housed centrifugal fan units for a given added resistance and a given heater will have a larger reduction in capacity as the fan-speed is lowered. The heat output to be expected under other than free delivery conditions should be secured from the manufacturer. - Inlet Outlet and Space Temperatures with Unit Heaters . In the selection of unit heaters for any particular design, consideration should be given to the temperature of air entering the heaters as well as - the temperature to be maintained in the working zone of the space. In y4 8 2 ' ' _ _ _ _ _ _ _ . ` - C H A P T E R 2 6 Table 2. Constants for Determining, the Capacity of BIow-Through Type Unit Heaters for Various Steam Pressures . ` ' . and Temperatures of Entering Air- , . * !' (Based on Steam Pressure of 8 psig and Entering Air Temperature of 60 F) .. ' , Steam Pressure - Temperature of Entering Air " ; .0 - -10 1.538 ... 2 1,585 . 5 . 1.640 10 1.730 " i5;: . 1.799 20s - . 1,861 ' 30'' ' 1.966 ; 40 2.058 : so 2.134 ' .60 , 2.196 70 . ,2.256 75 .2.283 ' . ' so; . 2.312 . 90 .' ' ; 2.36i 2.409 1.446 10 1.369 1,495 1.405 1.550 1.456 1.639 ' 1.545 1.708. 1.614 1.769 1.675 1.871 1.775 1.959 ' 1.862 . 2.035 T. 936, 2.094 , 1.997- 2.157 2.057 2.183 2.085 2.211 2.112 2.258 2.159;-. 2.307 . 2.204- 20 1.273 30 1.191 . 40 1.110 1.320 1.237 11155 1.370 1.289 1.206 1.460 1,375 1.290 1.525 1.441 1.335 1.584 1.498 . 1.416 1.684 - T597 1.509 i. 771; 1.683. 1.596 1.845. 1.755' .1.666 1.902 1.811 1.725 1.961 1.872 1.782 1.990 1.896 1.808 2.015 1.925 1.836 2.063 1.968 , 1.880 2.108.. .. 2.015 1.927 60 . ' 60 1.034 0.956 70 ' 0.881.' 1.078 1.000 0.926 1.127 1,050 0.974 1.211 i.131 1.056 1.275 ' 1,194 1.117 1.333 1.251 1,174 1.429 1.346 1.266. 1.511 1.430 1.349- 1.582 1.498. 1.416 1.640 .1.555 1,472 1.696 1.610 1.527 1.721 , 1.635 1.552 1.748 1.660;. 1.577; ' 1.792 1,705 1.621' . 1.836 1.749 . 1.663 80 0:809 0.853 0.901 0.982 1.043 1.097 1.190 1.270 1.338 1.393 1.447 1.472 1.497 1.541 1.581 60 0.739 100, 0.671 0.782 0.713 0.829 0.760 0.908 . 0.838 0.970 0.897 1.024 0.952 .1.115 1.042 1.194 1.119 " 1.262 ' 1,187 1.314 1.239 1.368 1.293 1.392 1.316 1.418 1.342 1.461 1.383 . 1.502 1.424 .. o Note: To determine capacity at any steam pressure and entering temperature, multiply constant from table by rated capacity at 00 F entering air and 2 pal/ .. outlet temperature^lTStfafa^tory ^ ^ *mportant to determine whether the heater la suitable for the Increased pressure application and whether the resulting Increased ' - 1946 G u id e T ' U n it H e a te rs ,'U n it V e n tila to rs , U n it H u m id ifie rs Table 3. Constants for Determining the Capacity of Dkiw-Through Type Unit Heaters for Various Steam Pressures ., . . . and Temperatures of Entering Air . . . , .` (Based on Steam Pressure of 8 psig and Entering Air Temperature of 60 F) Stiam Pbessurd psi . - " - .; "10 . ' 0 .0 . 1.483.: 1.405 ' 1^ . . 20 1.329, 1.253 .. 2 ' 1.520 1.442 1.363' 1.290 ' .5 ' 1.565. 1.485 .1.410 1.334 . 10 . 16 '. ,1:637 1.558 1,688- . 1.610 1.480 . 1.403 ; 1.533 1.458 '. . 20 . , . 1,728 : .1,649 1.572. , 1.498 ., 30 , i.803, 1.725 ; 1.648 1.572 . 40 50 : ' 1.864 1.787, ,1.710 1.927 , i. 850 . 1-773 1.637 1.700 .60 1.973 1.897 .1.820 1.748 70 2.018 . 1.943 1:869 1.795 .75 2.043 1.970 1.895 1.822 80 . . 2.064 1.988 . 1.914 1.841 90 - . ' 2.102 2.028 1.951 1.878 ' ' . 100 2.150 2.071 1.994 ' 1.919 1 ` Tbmpbratuhb op Entering Am ' . 30 1.178 40 1.105 50? 4.032 60 , ' 0.962 1.215 1,141. 1.069 1,000 1.260 1.187 1.114 1.045 1.328 ,1.253 . 1.182 1.112 1.382, 1.310 1.239 1.168 '1.421 1.350 1.278 1-208 . 1.497 1.423 . 1.352 1.281- 1.563 . 1.491 .1.420 1.350 1,628 1.554 1.483 1.416 1.673 1.601 1.531 i 1;463 1.722 1.651 . 1.582 ' 1.512' 1.750 1.680. 1.609 1.540 1.770 1.698 1.629 1.560 1.804 1.732 1.661 .1.590 1.845 1.770 1.700 . .1.630 . '70 0.892 $0 ' 90 0.822 0.754 ioo* ' 0:688 0.930 0.861 . 0.792 0.728 - 0.975 0.906 0.838 0:771 . 1.042 0.973 0.903 0.838 ; 1.099 1,028 0.960 0.895 1.138 . 1.070 1.212 1.145 1.282 1.215 1.002 1.078 1.148 . 01936. .1 -010 ' l.osi : 1.347 . 1.278 4.211 l"l45 . 1.394 . 1.325 1.260 1.194 1.443 1.377 1.310 1:243 1.471 1.402 1.333. 1.268 1.491 1.422 1.354 1.288 i .523 1.457 1.387 1.321. 1.560 ' 1.492 1.425.. 1.359 Note: To determine capacity at any steam pressure and entering temperature, multiply constant from table by rated capacity at 00 F entering air and 2 psi. ' - When Increasing steam pressure it is important to determine whether the heater is suitable for the increased pressure application and whether the resulting increased , outlet temperature is satisfactory. - ^ ~ . _ .' :\ 484 CHAPTER 26 1946 .Guide . general, the temperature differences per foot of elevation, when using unit heaters are less than corresponding variations when using direct radiation4. High velocity units will maintain slightly lower temperature differences than low discharge velocity units. Correspondingly, units with lower discharge air temperature will maintain lower temperature differences than units with higher discharge temperatures. Directional control of the discharged air from a unit heater can be an important factor, added to qualities of reasonably good outlet velocity and outlet .. temperature, in effecting satisfactory distribution of heat and restraining floor-to-ceiling temperature difference. ' When some outside air is introduced, the temperature of the mixture ' of outside, and recirculating air must be calculated and used as the entering air temperature at the heater. Unit heaters connected in this manner perform the function of unit ventilators. For a discussion of this function see the section of this chapter entitled Unit Ventilators. , For recirculating heaters located at the floor or with intakes at the floor, the temperature of air entering the heater should be assumed to be the same as that to be maintained in the room itself. Automatic Control of Unit Heaters ,. Thermostatic control of unit heaters may be accomplished by starting and stopping the.fan or by controlling the flow of heat to the heating element. If the fan is controlled, it is advisable to provide a thermostat on the return from the heater so as to prevent the fan from starting until the heating element is heated throughout. Unit heaters may be used in the summer time as a'means of circulating the air to give some measure of comfort due to air motion. In such cases the heating element should be shut off from the source of heat by closing . the steam valve to the heating element, and also the return line thermo stat should be provided with a by-pass switch, which upon being closed . will permit the fan to be operated independently of the heating element. Location of Unit Heaters Unit heaters should not be located in a corner or placed close to a wall, since the full effect of the unit will not be available under such conditions if the circulation of air is impeded. The best arrangement is to locate units so that they discharge air nearly parallel to exterior walls, and in a direction which will produce a rotational circulation around the room. This is preferable to directing the discharge against the outside walls. Various types and makes of unit heaters are illustrated in the Catalog Data Section of this edition. As hot blasts of air in working zones are usually objectionable, heaters mounted on the floor should have their discharge outlets above the head line and suspended heaters should be placed in such manner and turned in such direction that the heated air stream will not be objectionable in the working zone. In the interest of . economy, however, the elevation of the heater outlet and the direction of discharge should be so arranged that the heated air shall be brought as close above the head line as'possible, yet not into the working zone. In connection with the use of vertical type unit heaters, care must be exercised in the selection of the heater. It has been found that the higher ' the unit is placed above the floor, the lower must be the outlet tempera ture of the air leaving the heater in order that the heated air may be forced into the occupied zone. Unit Heaters, Unit Ventilators, Unit Humidifiers _____________;*85 Determining Unit Heater Requirements' ' ' The formulas given in the section on Unit Ventilators may be used to " determine unit heater capacity requirements. \. PIPING CONNECTIONS FOR STEAM UNIT HEATERS Piping connections for steam unit heaters are similar to those for other types of fan blast heaters. The piping of unit heaters must conform1 strictly to the system requirements while at the same time permitting the heaters themselves to function as intended. The basic piping principles for steam systems are discussed in Chapter 23. Rapid condensation of steam, especially during heating-up periods, is -AIR CLIMINATOR 1 (ITCH iATE VALVE Fig. 5. Unit Heater Connection to One-Pipe Gravity Steam System Fig. 6. Unit Heater Connection for Vacuum or Vapor System Discharging Condensation into Dry Return characteristic of this type of equipment. The return piping must be planned to keep the heating coil free of rapid condensation, while the steam piping must be ample to carry a full supply of steam to the unit to take the place of that condensed. Adequate sizes of piping are especially essential where a unit heater fan is operated under, start-and-stop control and where all or part of the air is taken from the outside. In such instal lations the condensation rate may vary rapidly and the necessity for ample pipe capacity is particularly important. . A method of connecting a unit heater to a-one-pipe gravity system is illustrated in Fig. 5. In cases where the return main is located above the boiler water line, an artificial water line must be created by providing an equalizing loop to prevent steam passing into the return and. thus into other units. .. A piping arrangement where both the air and condensate pass through a " comipon return to a boiler, with vent trap or condensate punip and _ 436 CHAPTER 26 1946 Guide receiver, is shown in Fig. 6. The traps must , pass air and condensate % rapidly to keep the return piping partially full of water. . '' Since' unit heaters are often constructed with sufficient strength, the use of high pressure steam in them is a common practice. ' As shown in Fig. 7 the condensate and air reach-the return overhead through traps, and check valves are located in the return piping. It is, however, prefer able to locate the high pressure return below the heater. . For two-pipe closed gravity return systems, the return from each unit should be fitted with a heavy duty or blast trap, and an automatic air . valve should be connected into the return header of each unit heater. Provisions must be made to compensate for the pressure drop by elevating the unit heater above the water line of the boiler or of the receiver. In pump and receiver systems the air may be eliminated by individual air valves on the heaters, or it may be carried into the returns as in vacuum systems and the entire return system be free-vented to the atmosphere, provided all units, drip points, and radiation are properly trapped to prevent steam entering the returns. ' On vacuum or open vent systems the'return from each unit should be fitted with a large capacity trap to discharge the water of condensation and with a thermostatic air valve for eliminating the air, or with a heavyduty trap for handling both the condensation and the air, provided the air finally can be eliminated at some other point in the return system. For high pressure systems the same kind of traps may be used as with vacuum systems, except that they must be constructed for the pressure used. . If the air is to be eliminated at the return header of the unit, a high pressure air valve can be used; otherwise the air may be passed with the condensate through the high-pressure return trap, with its elimination - at some other point in the system. . Fig. 8 represents the connections to a hot water heating system. The Unit Heaters, Unit Ventilators, Unit Humidifiers 487 . air vent is not required if main is above heater and air can be eliminated through the piping system. . BOILER CAPACITY FOR STEAM UNIT HEATERS . The capacity of the boiler should be based on the rated capacity of the unit heaters at the lowest entering air temperature and highest fan speed that will occur, plus an allowance for pipe line losses. It is unwise to install a single unit heater as the sole load on any boiler, particularly if the unit heater motor is started and stopped by thermostatic control. The wide and sudden fluctuations of load that occur under such con-, ditions would require closer attention to the boiler than is usually possible . in a small installation. Where oil or gas is used to fire the boiler, it is possible by means of a pressurestat to control' the boiler, in response to this rapid fluctuation. In most cases, and particularly where the boiler is coal-fired, it is advisable to use two or more smaller unit heaters instead of one large unit.' Steam pressures below 5 lb can be used with safety for recirculating unit heaters when their heating surfaces are designed for those pressures, and when proper provision is made for returning the condensate. If units admit air that may be at a temperature below freezing, a steam pressure of not less than 5 lb should be maintained on the heating element, or a corresponding differential in pressure between the supply and returns should be maintained by means of a vacuum. ' UNIT VENTILATORS . Unit ventilators are similar in principle to unit heaters, except that they are provided with an arrangement of dampers for introducing out- . door and recirculated air in varying quantities. In general, they are obtainable only in the steam type, but unit heaters of all types may be adapted to the unit ventilator principle by the addition of outdoor air and recirculating dampers. Unit ventilators are used to supply air with a . discharge temperature at or slightly higher than room temperature. Also , they are provided with an arrangement for introducing outdoor and recirculated air in varying quantities. If the unit is only'used for circu' lating air, then radiators or some other equipment must be provided for . heating the room. Unit ventilators are intended primarily for schools, offices, and semi-commercial establishments. Unit ventilators may be of . the radiator controlled or damper controlled type and of the blow-through or draw-through type as illustrated in Fig. 9. A roof ventilator used for exhausting air is sometimes termed a unit ventilator. For information on roof ventilators, see Chapter 9. Ratings .- Unit ventilators of the steam type are customarily cataloged with two ratings, one the input and the other the output capacity. The first is the .heat input to the unit which is determined by measuring the temperature^ and quantity of condensate and the pressure and quality of the steam. , The second is the heat output of the unit which is determined by measur ing the quantity of air delivered and the temperature of the air to and -from the unit. Table 4 shows the air handling capacities by the two methods of rating6 and also the approximate heating data. In accordance' with the A.S.H.V.E. Standard Code for Testing and Rating Steam 488 CHAPTER 26 1946 Guide Unit Ventilators the information to be supplied regarding ratings and the basis of rating is the following: Rating Factors to Be Specified. The rating of the unit ventilator shall specify the .following: _ a. Final temperature at different entering air temperatures. b. Total EDR at different entering air temperatures. c. Air delivered by the unit in cubic feet per minute at the standard basis of rating ' with the fans operated at rated speed, with all air being blown through the heating unit and with the standard louver and grille on the outlet. - The Standard Basis of Rating shall be as follows: ' o. Dry saturated steam at a temperature at the unit corresponding to an absolute pressure of 16.7 psi (218.5 F). -' Fig. 9. Typical Unit Ventilators Showing Two of Many Arrangements of Dampers and Heating Coils . r b. Entering air temperature of zero Fahrenheit degrees. c. Volume delivered in cubic feet per minute converted fo standard air at 70 F. Rating Tables for unit'ventilators shall contain the following data in addition to the standard rating, for entering air temperatures from --30 F to +60 F: a. Inlet temperature, Fahrenheit degrees. b. Final temperature, Fahrenheit degrees. ' c. Total EDR at the specified entering temperature. d. Surplus or heating EDR at the specified entering temperature. Surplus or Heating Equivalent Direct Radiation for the purposes of this code shall be construed to mean difference between the total EDR at a specified inlet temperature and the EDR required to heat the air from that temperature to 70 F. . If no direct heating surface (radiation) is installed to take care of the normal heat transfer losses, and the unit ventilator is to be used for both .. heating and ventilation, then the combined requirements must be taken care of by the unit ventilator. , Unit Heaters, Unit Ventilators, Unit Humidifiers Table 4. Typical Capacities of Unit Ventilators for an Entering Air Temperature of Zero 489 Cubic Febt of Air per Minute Anemometer . Rating Condensate -.Rating Total Capacity , in Square Feet, Equiv alent Direct Radiation Capacity Available for Heating the Room, Square Feet Equivalent Direct Radiation Final Air Temperature . F Deg . 750 1000 1260 1560 500 750 1000 1250 214 320 427 534 56 84 112 141 ' 95 95 95 95 Heat Required for Ventilating Only When all of the air handled by the unit is taken from the outside, the total heat to be supplied is obtained by means of Equations 1, 2, 3, and 4. . H = 0.24 W (ty - o (1) Hy = 0.24 W (t - to) (2) Ht = 0.24 W (ty - to) = H + Hv . (3) - W = d 60 Q (4) From Equations 2, 3, and 4: Hi -- 17 +' 0.24 d GO Q it -- to): (5) where d = density of air, pounds per cubic foot. H = heat loss of room, Btu per hour. , Hy, = heat required to warm air for ventilation, Btu per hour. Hi = total heat requirement^ for both heating and ventilation, Btu per hour. = H + Hy. . Q -- volume of air handled by the ventilating equipment, cubic feet per minute. t = temperature to be maintained in the room, Fahrenheit degrees. . to = outside temperature, Fahrenheit degrees. h = temperature of the air leaving the unit, Fahrenheit degrees. W = weight of air circulated, pounds per hour. ' . , 0.24 = specific heat of air at constant pressure. Example 1. The heat loss of a certain room is 24,000 Btu per hour, and the ventilating requirements are 1000 cfm. If the room temperature is to be 70 F and all air is taken from the outside at zero, what will be the total heat demand on the unit if it is required to provide for both the heating and ventilating requirements (combined system)? Solution. - Substituting in Equation 5: ' - Ht = 24,000 + 0.24 X 0.075 X 60 X 1000 (70 - 0) = 99,600 Btu per hour . , , =24,000 ' ' y 0.24 X 0.075 X 60 X 1000 * ' If the heat loss of the room is to be taken care of by the direct heating' surface, the unit ventilators will be required to warm the air introduced for the ventilating requirements. Therefore: . Hy = 0.24 W ity -- to) .' (6) In this case ty should be equal to or slightly higher than t. If the unit ventilator were of such capacity as to provide exactly for the ventilating requirements, the direct radiation would be selected on the usual basis.- 490 CHAPTER 26 '1946'' Guide However, it is necessary to employ a unit which-may not-exactly meet the ventilating requirements, since standard units are usually rated in terms of the volume of air that will be delivered at a certain' temperature ty for an initial temperature of t0., Therefore a certain amount of heat (-ffh) may be available from the unit ventilator for heating purposes, as pre viously stated, and the amount of equivalent direct heating surface may, if desired, be deducted from the amount required for heating the room. Heat Required for Ventilating and Recirculating ., ,. When part of the air handled by the unit is taken from the room and the remainder from the outside, . Ht = 0.24 Wo (ty - to) + 0.24 Wi (ty - /) .. . (7) Wo = do 60 Qo (8) ' .Wi = di 60 Qi . ' (9) . Iy = 0.24 (W0 + Wi) + 1 . (10) Ht = ,H + 0.24 do 60 Qa (t -to) where WQ -- weight of air, pounds per hour taken from out-of-doors. . . Wi = weight of air, pounds per hour taken from the:room. . do ~ density of air, pounds per cubic foot at temperature to. = density of air,, pounds per cubic foot at temperature t. 0O = volume of air taken in from the outside, cubic feet per minute. Qi = volume of air taken in from the room, cubic feet per minute. (11) . Equations 7, 8, 9, 10 and 11 may be used in the same manner as is illustrated previously for Equations 3, 4 and 5. It may be noted in Equa tion 11, representing the total heat requirements, that as the quantity Q0 is diminished .the heat requirements for the unit diminish very materially. In Example 1, if one third of its air volume is taken from, the outside and two thirds from the room, the .total Heat requirement would be. 24,000 -f jjp'Q00 ~ _'P-9i? = 59,200 Btu per hour. -Units designed and O ` ` ` operated on this principle show an average heat requirement and, there fore, a boiler capacity requirement of less than 50 per cent of that required > for units taking all their air from the outside. ; .... . Heat Required for Recirculating Only ' > ff all of the air is recirculated, the total heat required is the same as the heat loss of the room,, or , ' .. . . Ht = H =. 0.24 W(ty - l) (12) In Example 1, if the quantity of air taken in from the outside is reduced to zero, or all of the air handled by the unit is recirculated, the total heat requirement Hi reduced from 99,600 to 24,000 Btu per hour, of to about one-fourth. .1 ' . . . . Applications of Unit Ventilators . . Items to be considered in the application of unit ventilators are: (1) combination with other'means, of heating, (2) location of units, and . (3) .method of venting or. exhausting. . . . '/. /' In a split system the-unit is used primarily for'ventilation/ -Air is Unit Heaters, Unit Ventilators, Unit Humidifiers491 delivered to the room at or.slightly above'room temperature, and enough ' radiation is installed in the room to take care of the normal heat transfer losses. Where the unit ventilator selected has a capacity more , than sufficient to warm the air needed to meet the ventilating requirements, a corresponding reduction may be made in the amount of direct radiation installed. The greater the amount of excess capacity of the unit, the more < efficient will be the temperature regulation of the room. The split system permits the heating of the room during failure of electric current, since the direct radiators will furnish heat, but it permits a careless operator to avoid operating the ventilating equipment. The combined system employs a unit ventilator with sufficient capacity for both ventilation and the normal heat transfer losses. In such a case. no direct radiation is required. The necessary operation of the fan when the room is being heated also gives assurance that some ventilation is being provided, especially if automatic dampers are used in the air intake and in the recirculating intake. These dampers are arranged to provide a certain quantity of outside air, depending upon the weather conditions. The cost of installation of a combined system is usually less than that of a split system and there is less danger of overheating, but if the electric energy fails there will be available only the heating effect of the units acting as convectors. ' .. Location, of Unit Ventilator The location of the unit ventilator in a room is important. Wherever possible it should be placed against an outside wall, ft is difficult to. obtain proper air distribution if the unit is erected either on an inside wall or in a corner of the room. Standard units discharge the air stream upward, but for special cases units may be installed to discharge air horizontally. Units may be set away from the wall'or partially recessed into the wall to save space without materially affecting the results. The air inlet may enter the cabinet at the back at any point from top to bottom. Air Exhaust Vents and Flues .. The size and location of the air exhaust vent6 outlet is important. In many cases the sizes for public buildings are regulated by law. See table of state codes and standards in Chapter 5i. . In cases where no codes govern, the location and size of vents is left to the discretion of the engineer. .. . Best results have been obtained with a velocity.through the vent, openings nearly equal to that at which the air is introduced into the room, thus maintaining a slight pressure in the room. Calculated velocities at the vent openings of from 600 to 800 fpm produce the best diffusion . results from this system. Many states,' however, have regulations that will not permit velocities as high as 800 fpm. If a vent opening at or . near the floor is near a desk or place where a person is seated, a velocityof 800 fpm in the vent opening will produce an objectionable draft. In such a case the velocity in the vent opening should .not exceed 400 to 450 fpm, although duct velocities are maintained at 600 to 800 fpm if . codes permit In school buildings provided,with wardrobes or cloakrooms the vents may be so located that the air shall pass through these spaces, ventilating them with air which otherwise would be passed to the outside without being used to the best advantage. -Many state codes for ventilation of public buildings make this arrangement mandatory. . 492 CHAPTER 26 '1946 Guide WINDOW VENTILATORS . A window ventilator illustrated in Fig. 10 consists of filter and switch controlled motor driven fans enclosed in a cabinet to be mounted on the window sill. Such units accomplish ventilation, air cleaning, and air cir culation, but have no means of heating the air. The direction of air discharge is manually adjustable for seasonal operation. UNIT HUMIDIFIERS . Unit humidifiers which may be procured in the market at the present time, fall into four general classifications, depending on the method of causing evaporation. These are as follows: (1) Nozzle Type, (2) Rotary Type, (3) Cascade Type, and (4) Heater Type. . In the nozzle type of humidifier water is sprayed into the air and Unit Heaters, Unit Ventilators, Unit Humidifiers.- 493. coil capacity is transformed into latent heat during the humidifying pro cess, the unit does not generally eliminate any existing steam radiation but, does tend to improve comfort conditions by supplying heating during the off-period of furnace operation7. In the rotary type of humidifier the spray is created by rotating vanes or discs which throw the water by centrifugal force and in so doing break it up into a fine mist. In all other respects, this type of humidifier is similar to the nozzle type. It has the advantage over the nozzle type of being less liable to become' clogged. > In the cascade type the humidification takes place by water falling in sheets over a series of baffles or trays. This type is usually furnished with a fan, air heater, and air filter all enclosed in a housing. In the heater type of.humidifier the water is heated either to the boiling point or to a temperature at which the water, vapor readily passes into the air stream. There are many variations of this type of humidifier. Fig. 10. Typical Window Ventilator evaporation is effected by adiabatic exchange of energy. Units of this type in simplest form spray a fine mist of water directly into the air in a space. They are used to a great extent in the textile industry. To the simple type of nozzle unit may be added the following acces sories: a water heater whose function is to increase the vapor pressure, an air heater to heat the air either before or after humidification takes place, a screen or air filter over which the water is sprayed and through which . the air is drawn for intimate contact with the water, a fan to create an air stream and to deliver air to the space to be humidified, and a housing to enclose all the elements. This type of unit is procurable in practically all of the variations mentioned. It has the disadvantage of clogging the nozzles and must be serviced continually. Fig. 11 illustrates a nozzle unit having a humidifying capacity sufficient for a residence or small building. These units usually include air filters and in some cases provide ventilation air by means of an outside air duct connection to the unit. The units are available for either floor or ceiling mounting and are usually placed in a central location in the basement with short supply and return duct connections from the first floor. Room air is brought into the unit through the return duct connection, is passed over a tempering coil heated by steam or hot water, and is then humidified by passing through some type of spray humidifier. Surplus moisture is removed by an eliminator and the humidified air is delivered to the room through a duct connection. Since a large percentage of the tempering to Preheat the Air for Residences In the simplest form the heating element using steam, hot water, gas, oil or electricity, is placed in a pan or vessel of water and the vapor passes from, the surface of the water to the stream of air. ' A modification of this type of humidifier is the combination of spray nozzle and heater type in which the water is sprayed over a hot surface, and evaporated. -It has the disadvantage of accumulating scale on the surfaces of the vessel or heating surface. -. For a discussion of various methods of humidification see Chapter 37. REFERENCES 1--See National Fan Manufacturers Association standard definitions in Chapter 32. 2--Standard Code for Testing and Rating Steam Unit Heaters (A.S.H.V.E. Transactions, Vol. 36,1930,' p. 165), prepared by a Joint Code Committee of the American Society of Heating and Ventilating Engineers and the Industrial Unit Heater Association and adopted 1930. '3--Standard Code for Testing Hot Water Unit Heaters prepared by Engineering Committee of Industrial Unit Heater Association. Adopted by Industrial Unit Heater Association August 1942 and . published September 1942. - A.S.H.V.E. Research Report No. 958--/Temperature Gradient Observations in a Large Heated , Space, by G. L. Larson. D. W. Nelson and O. C. Cromer (A.S.H.V.E. Transactions, Vol. 39,1933, p. 243). A.S.H.V.E. Research Report No. 1011--Tests of Three Heating Systems in an Industrial Type of Build ing by G. L. Larson, D. W. Nelson and John James (A.S.H.V.E. Transactions. Vol. 41, 1935, p. 185). - s~A.S.H.V.E. Standard Code for Testing and Rating Steam Unit Ventilators (A.S.H.V.E. Transac tions. yol. 38, 1932. p. 25). -A.S.H.V.E. Research Report No. 936--Investigation of Air Outlets in Class Room Ventilation, by G. L. Larson, D.- W. Nelson and R. W. Kubasta (A.S.H.V.E. Transactions, Vol. 38. 1932,. p. 463). A.S.H.V.E. Research Report No. 1017--Air Supply to Classrooms in Relation to Vent Flue Openings. . by F. C. Houghten, Carl Gutberlet and M. F. Lichtenfels (A.S.H.V.E. Transactions, Vol. 41, 1935, p. 279). 7--Estimating the Humidification Requirements of Residences, by W. H. Severns (Papers Presented at the First Annual Conference on Air Conditioning. University of Illinois, Engineering Experiment Station Circular, No. 6. October. 1936). CHAPTER 27 J-^\pe, ^dittin^i, 'lAJeidincj. Pipe Material, Types of Pipe Used, Dimensions of Pipe Com mercially Available, Expansion and Flexibility of Pipe, Pipe Threads and Hangers, Types of Fittings, Welding as Applied to Erection of Piping, Valves, Corrosion of Piping ` IMPORTANT considerations in the selection and installation of pipe and fittings for heating, ventilating, and air conditioning work are dealt with in this chapter. . ' PIPE MATERIALS Use of corrosion-resistant materials for pipe, including special alloy steels and irons, wrought-iron, copper and brass, has increased con siderably during the past few years. The recent development of copper, brass, and bronze fittings which can be assembled by soldering or sweating 'permits the use of thin-wall pipe and thereby has reduced the initial cost of such installation. The following brief discussion indicates the variety ` of pipe materials and the types of pipe available. . Wroughl-Sleel Pipe. Because of its low price, the great bulk of wrought pipe used for heating.and ventilating work at the present time is of wrought steel. The material used for steel pipe is a mild steel made by ' the acid-bessemer, the open-hearth, or the electric-furnace process. Ordinary wrought-steel pipe is made either by shaping sheets of metal into cylindrical form and welding the edges together, or by forming or / drawing from a solid billet.' The former is known as welded pipe, the latter as seamless pipe. .' Many types of welded pipe are available, although the smaller sizes ' most frequently used in heating and ventilating work are made by the lap-weld, resistance-weld, or butt-weld process. While the lap-weld and resistance-weld processes produce a better weld than the butt type, ' lap-weld and resistance-weld pipe are seldom manufactured in nominal pipe sizes less than 2 in. Seamless pipe can be obtained in the small sizes at a somewhat higher cost. . Seamless steel pipe is frequently used for high pressure work or where pipe is desired for close coiling, cold bending, or other forming operation. Its advantages are its somewhat greater strength, which permits use of a thinner wall and, in the small sizes, its freedbm from the occasional tendency of welded pipe to split at the weld when bent. Wrought-iron Pipe. Wrought-iron pipe is claimed to be more corro sion-resisting than ordinary steel pipe and therefore its somewhat higher first cost is said to be justified on the basis qf longer life expectancy. ' Wrought-iron pipe may be identified by'the spiral line marked into each ' length, either knurled into the metal or painted on it in red or other bright color. Otherwise, there is little difference in the appearance of wrought iron and steel pipe, although microscopic examination of polished and etched specimens will readily disclose the difference.- _ - Cast-Ferrous Pipe. There are now available several types of cast . ferrous metal pipe made, of a good grade of cast-iron .with or .without additions of nickel, chromium, or other alloy. This pipe is available in sizes from 1in. to 6 in., and in standard lengths-of 5 or 6 ft with external and internaTdiameters closely approximating those of extra strong' 494 Pipe9 Fittings, Welding 495 wrought pipe. .- Cast-ferrous pipe may be obtained coupled, beveled for welding, or with ends plain or grooved for the several types of couplings; It is easily cut and threaded as well as welded. The fact that it is readily welded enables the manufacturers to supply the pipe in any lengths practicable for handling. . , Alloy Metal Pipe. Steel pipe bearing a small alloy of copper or other alloying element and iron pipe bearing a small alloy of copper and molyb denum have been claimed to possess more resistance to corrosion than plain Table 1. Dimensions of Schedules 30 and 40 and Standard Weight Pipe3 External Plain Ends | Threads per In . Internal External Internal Metal External Surface Internal Surface DiakEBTBB I N. Sess a a i 1a 3 M E3 H Weight peb Ft. . Lb si If E-1 Circum ference, In. a Is & Traksteese Area, Sq In. Lenotb of Pipe, Ft per Sq Ft Length of Pipe, Ft pON- TAININO ICuFt Weight or Water, Lb per Ft '/% 0.405 0.269 0.068 0.244 0-345 27; k 0.540 0.364 0.088 0.424 0.425 18 yh 0.675 0.493 0.091 0.567 0.569 18 5s 0.840 0.622 0.109 0.850 0.852 14 1.272 1.696 2.121 2.639 0345 1.144 1349 1.954 0.129 0.229 0.358 0354 0.057 0.104 0.191 0.304 . 0.072 0.125 0.167 0.250 9.431 14.199 2533.775 7.073 10.493 1383.789 5.658 7.748 754360 4.547 . 6.141 473.906 0.025 0.132 X 1.050 0.824 0.113 1.130 1.134 14. 3.299 2.589 l 1.315 1.049 0.133 1.678 1.684 11H 4.131 3.296 1% 1M 1.660 1.000 1.380 0.140 1.610 0.145 2.272 2.717 2.281 llH 2.731 im 5.215 5.969 4335 5.058 0.866 1358 2.164 2335 2 2375 2.067 0.154 3.652 3.678 1IK 7.461 6.494 4.430 2.875 2.469 0.203 5.793 5.819 8 9.032 7.757 6.492 3 3.500 3.068 0.216 7.575 7.616 8 10.996 9.638 9.621 3>4 4.000 3.545 0.228 9.109 9302 8 12.566 11.146 12366 0.533 0.864 1.495 2.036 0.333 0.494 0.669 0.799 3.637 2.904 2301 2.010 4.635 3.641 2.768 2372 270.034 166.618 96.275 70.733 3355 1.075 1.608 4.788 ' 1.704 1.328 7393 2.228 . 1.091 9386 2.680 0.954 1347 1347 1.245 1.076 42.913 30.077 14365 0375 038 1.45 4.29 4 5 6 4.500 4.026 0.237 10.790 10.889 8 5.563 5.047 0.258 14.617 14310 8 6.625 6.065 0.280 18.974 19.185 8 14.137 12.648 15.904 12.730 17.477 15.856 24.306 20.006 20.813 19.054 34.472 28.891 3.174 0.848 0.948 4.300 0.686 0.756 5381 0.576 0.629 8c 8 8.625 8.071 0277 24.696 25.000 8 8.625 7.981 0.322 28.554 28.809 8 27.096 25356 58.426 51.161 27.096 25.073 58.426 50.027 7365 0.443 0.473 8399 0.443 0.478 ioc 10.750 10.136 0.307 34.240 35.000 8 33.772 31343 90.763 80391 10.072 0355 0.376 10 10.750 10.020 0385 40.483 41.132 8 33.772 31.479 90.763 78355 11.908 0355 0381 12C 12.750 12.090 0.330 43.773 45.000 8 40.055 37.982 127.676 114.800 12.876 0.299 0315 12 12.750 12.000 0.375 49.562 50.706 8 . 40.055 37.699 127.676 113.097 14.579 0399 0318 11.312 7.198 8.67 4.984 1231 2315 22.18 2378 21.70 1.785 34.95 1326 3430 1.254 49.70 - 1373 49.00 ' Standardrwcight wrought-iron pipe has approximately the same wall thicknesses and weights as contained herein for steel pipe. For exact dimensions, sfx American Standardfor Wrought-iron and Wroueht- Sieel Ptpe, A.SA. B36.10. , . . . " _^Thicknesses shown in bold face type are identical with thicknesses for Schedule 40 pipe of A.SA. B36.10. . - . - eSame as Schedule 30. AS^. B36.40. steel pipe and they are advertised and sold under various trade names. . Copper Pipe and Fittings. Owing to its inherent resistance to cor rosion, copper and brass pipe have always been used in heating, venti- lating, and water supply installations, but the cost with standard dimen sions for threaded connections has been high. The recent introduction . of fittings which permit erection by soldering or sweating allows the use of pipe with thinner . walls than are possible with threaded connections, , thereby reducing the cost of installations. .. The initial cost of- brass and copper pipe installations generally runs higher than the corresponding job with steel pipe and screwed connections in spite of the use of thin wall pipe, but the corrosive nature of the fluid conveyed or the inaccessibility of some of the piping may1 warrant use of a more expensive material than plain steel. The advantages of corrosion- . ' 496 CHAPTER 27 1946 Cuide resisting pipe and fittings should be weighed against the correspondingly higher initial cost. ' COMMERCIAL PIPE DIMENSIONS The two weights of steel and wrought-iron pipe commonly used are known as standard weight and extra strong, which correspond to Schedules 40 and 80 respectively of the American Standard for Wrought-iron and Wrought-Steel Pipe, A.S.A. B36.10. The same external diameter is used for both weights of each nominal size for manufacturing reasons as well Table 2. Standard Weights and Dimensions of Welded and Seamless Steel Pipe* Standard-Weight Pipe Extra-Strong Pipe Double Extra Strong PlPgb Stza Outside No. or Diame Threads ter. In. per In. Schedule 30 Wall Thick ness, Id. Weight per Ft, Lb T4C x 0.405 x 0.540 X 0.675 - 0.840 27 18 18 14 X 1 IX tlX ft 2X 3 zx 4 5 6 8 IDo I2d 1.050 1.315 1.660 1.900 2.375 2.875 3.500 44)00 4500 5563 6.625 8.625 10.750 12.750 14 UH 11X nx nx 8 8 8 8 8' 8 8. 8 '8 ........ 0.277 0.307 0.330 -- -- 25.00 35.00 45.00 Schedule 40 Wall Thick ness, In. Weight perFt, Lb T&C 0568 0.088 0.091 0.109 0.25 0.43 057 0.85 0.113 0.133 0.140 0.145 0.154 0.203 0.216 0.226 0.237 1.13 1.68 258 2.73 3.68 . 532 7.62 950 1039 0.258 0580 0522 0365 0375 1451 19.19 2851 41.13 50.71 Schedule 60 Schedule 80 Wall Thick ness, In. Weight perFt, Lb Plain Ends Wall Thick ness, In. Weight perFt, Lb Plain Frwfa 0.095 031 * 0.119 0.126 f: 0M 0.74 0.147 1.09. ...A... ....- 0500 0500d 0.154 0.179 0.191 0.200 ____ 0.218 0.276 - 0500 0318 0337 54.74 65.41 0375 0.432 0500 1.47 2.17 3.00 3.63 5.02 7.66 10.25 1251 14.98 20.78 2857 4339 ____ Wail Thick ness In. Weight . per Ft, Lb Plain Fqija _ 0594 ___ 1.71 0.308 0.358 0382 0.400 0.436 0552 0.600 0.636 0.674 2.44 3.66 5.21 6.41 9.03 13.70 1858 2255 - 2754 0.750 0364 0575 - 3855 53.16 72.42 -- From Standard Specifications for Welded and Seamless Steel Pipe of the American Society for Tcstint Materials. AJS.T.M. Designation A120. ' "Sizes larger than those shown in the table are measured by their outside diameter, such as 14 in. out side diameter, etc. These larger sizes will be furnished with plain ends, unless otherwise specified. The weights will correspond to the manufacturers' published standards although it is possible to calculate the theoretical weights for any given size and wall thickness on the basis of 1 cu in. of steel weighing 0.2833 lb. . bThe American Standard for Wrought-iron and Wrought-Steel Pipe.4.$~4. B36.10-1939 has assigned no schedule number to Double Extra-Strong pipe. -- oA 10 in. Standard Weight pipe is also available with 0.279 in. wall thickness, but this wall is not covered by a Schedule Number. .` dOwing to a departure from the Standard-Weight and Extra-Strong wall thicknesses for the 12 in. nominal size. Schedules 40 and 60, Table 2 of the A.S.A. B36.10-1939, Standard for Wrought-iron and Wrought` Steel Pipe, the regular Standard and Extra-Strong wall thicknesses (0.375 in. and 0.500 in.) have been substituted. -' ' as to afford interchangeability in threading, and other elements associated with fabrication and erection. Hence the difference in wall thickness is 'accompanied by a corresponding change in inside,diameter. In sizes up to 14 in., pipe is designated by its nominal size which corresponds roughly to the inside diameter of Schedule 40 pipe. In sizes 14 in. and upward, pipe is designated by its outside diameter (O. D.), and the wall thickness is specified. . While the demands for pipe for the heating and ventilating industry are reasonably well served by Schedule 40 (standard weight) pipe, the erection of pipe by welding sometimes warrants using lighter wall thicknesses. ` The considerations governing pipe.wall, thickness and its relation to joint design are covered in the American Standard Code for Pressure Piping, A.S.A. B31.1-1942, see Section 122. Standard schedules of pipe thick- Pipe, Fittings, Welding 497 nesses are contained in the American Standard for Wrought-iron and Wrought-Steel Pipe, A.S.yl. B36.10, which includes standard-weight and extra-strong thicknesses in Schedules 40 and 80, respectively, and eight other schedules of varying wall thickness to provide for different service conditions. . Dimensions and other useful data for Schedules 30 and 40 pipe are given in Table 1. Table 2 from ^4.5. T:M. Specifications A53 and Table 3.. Standard Dimensions and Weights, and Tolerances in Diameter and , Wall Thickness for Copper Water Tubes* (All tolerances in this table are plusand minus except as otherwise indicated) * Average Out side Diameter Wall Thickness. In. Theoretical Weight, Lb per Ft ' Standard Actual Water ^Outside Size, In. In. Tolerance, In. TtpbK TtpeL . Ttte M Annealed Drawn Temper Nominal . Tolerance Type K M X X X H X 1 IX 04 22X 3 3H 4 5 6 8* 10 12 0550 .0375 0500 0.625 0.750 0.875 1.125 1375 1.625 2.125 2.625 3.125 3.825 4.125 5.125 6.125 8.125 10.125 12.125 0.002 0.002 0.0025 0.0025 0.00* 0.001 0.001. 0.001 0.032 0.032 0349 0.049 0.0025 0.003 0.0035 0.004 " 0.001 0.049 0.001 0.065 0.0015 0.065 0.0015 0.065 0.0045 0.005 0.005 0.005 0.002 0.002 0.002 0.002 0.072 0.083 0.095 0.109 0.005 0.005 0.005 0.005 0.002 0.002 0.002 0.002 0.120 0.134 0.160 0.192 0.006 0.008 0.008 +0.002 -0.004 +0.002 -0.006 +0.002 -0.006 0371 0338 0.405 8 aa "3 fr- 0.003 0.004 0.004 0.004 0.004 0.0045 0.0045 0.0045 0.005 0.007 0.007 0.007 0.008 0.010 0.010 0.012 ' oa 55 z 0.025 0.030 0.035 0.040 0.0025 0.0035 0.0035 0.0035 0.025 0.025 0.025 0.028 0.042 0.045 0.050 0.055 0.0035 0.004 0.004 0.0045 0330 0.032 0.035 0342 0.060 0.070 0.080 0.090 0.0045 0.006 0.006 0.007 0.049 0.058 0.065 0.072 0.100 0.110 0.125 0.140 0.007 0.009 0.010 0.010 0.083 0.095 0.109 0.122 e a "o b-> 0.0025 0.0025 0.0025 0.0025 . 0.085 0.063 0.134 0.126 0369 0.198 0344 0385 s & 0.068 0.107 0.145 0304 0.0025 0.003 0.0035 0.0035 0.418 0362 0.641 0.455 0.839 0.655 1.04 0384 0363 0328 0.465 0.682 0.004 0.006 0.006 0.006 136 1.14 0.940 2.06 1.75 1.46 2.93 2.48 2.03 4.00 333 ' 2.68 0307 0.009 0.009 0.010 5.12 631 9.67 13.9 439 538 7.61 10.2 338 4.66 6.66 8.92 0.016 0.018 0.020 0.200 0.014 0350 0.016 0.280 . 0.018 0.170 0.014 25.9 193 163 0312 0.015 403 30.1 25.6 0354. 0.016 573 40.4 36.7 , "S.rm Standard'Specifications for Copper Water Tnbe of the American Society for Tcstint Materials. AS.T.M. Designation B88-41. Note 1:--For copper gas and oil burner tubes, the tolerances shown above for various wall thicknesses (type K) apply irrespective of diameter. Note 2:--For tubes other than round no standard tolerances are established. These tolerances do not apply to condenser and heat exchanger tubes. '' A120 combines the schedule thicknesses of A.S.A. B36.10 and the old series designations. Standard-weight pipe is generally furnished with threaded ends in random lengths of 16 to 22. ft, although when ordered with plain ends, 5 per cent may be in lengths of. 12 to 16 ft. Five per cent of the total number of lengths ordered may be jointerswhich are two pieces coupled together. Extra-strong pipe is generally furnished with plain ends in random lengths of 12 to 22 ft, although 5 per cent may be in lengths of 6 to 12 ft. - In addition to IPS copper pipe, several varieties of copper tubing are in . use with either flared or compression couplings or soldered joints. Dimen sions of copper water tubing intended for plumbing, underground water service, fuel-oil lines, gas lines, etc., have been standardized by the U. S. I 498 CHAPTER 27' ____ 1946 Guide Government and the American Society for Testing Materials. .There are three standard wall-thickness schedules of copper water tubing classified in accordance with their principal uses as follows: ' Type K--Designed for underground services and general plumbing service. Type L--Designed for general plumbing purposes. Type M--Designed for use with soldered fittings only. ' - In general, Type K is used where corrosion conditions are severe, and Types L and M where such conditions may be considered normal as, for instance, in heating work. Types K and L are available in both hard and .' soft tempers; Type M is available only in hard temper. Where flexibility is essential as in hidden replacement work or where as few joints as possible are desired as in fuel-oil lines, the soft temper is commonly used. New or Table 4. Thermal Expansion of Pipe in Inches per 100 ft3 (For superheated steam and other fluids refer to temperature column) Saturated Steam Elongation in Inches per 100 FT FROM --20 F OP Saturated Steam Elongation m Inches per 100 pt prom -- 20 F up Tem Vacuum laches of Hg. Pressure . .ftig . perature Fahren^ hat Degrees CastIron Pipe Steel Pipe Tem Wrooght- Iron Pipe Copper Pipe Pressure Psig perature Fahren heit Degrees Cast-1 Iron Pipe Steel Pipe Wrought- Iron Pipe Copper Pipe * 29.39 28.89 27.99 26.48 24.04 20.27 14.63 6.45 -- -20 0 .20 40 60 80 100 120 140 160 180 200 000 0.127 0.145 0.152 0.255 0.293 0.306 0.390 0.430 0.465 0.518 0.593 0.620 0.649 0.725 0.780 0.787 0.898 0.939 0.926 1.055, 1.110 1.051 1.209 1.265 1.200 1.368 1.427 1.345 1.528 1.597 1.495. 1.691 1.778 o. 0.204 0.442 0.655 0.888 1.100 1.338 1.570 1.794 2:008 2.255 2.500 2.5 10.3 20.7 34.5 52.3 74.9 103.3 138.3 180.9 232.4 293.7 366.1 220 .240 260 280 300 320 340 360 380 400 420 440 1.634 1.780 1.931 2.085 2.233 2.395 2.543 2.700 2.859 3.008 3.182 3.345 1.852 2.020 2.183 2.350 2.519 2.690 2.862 3.029 3.211 3.375 3.566 3.740 1.936 2.110 2.279 2.465 2.630 2.800 2.988 3.175 3.350 3.521 3.720 3.900 2.720 2.960 3.189 3.422 3.665 3.900 4.145 4.380 4.628 4.870 5.118 5.358 &From Piping Handbook, by Walker and Crocker. This table gives the expansion from --20 F to the temperature in question. . To obtain the amount of expansion between any two temperatures take the difference between the figures in the table for those temperatures. For example, if a steel pipe is installed at a temperature of 60 F and is to operate at 300 F, the expansion would be 2.519 -- 0.593 * 1.926 in. . . . exposal work generally employs copper pipe of a hard temper. All three classes are extensively used with soldered fittings. . Standard dimensions, weights, and diameter and wall-thickness, . tolerances for these classes of copper tubing are given in Table 3: Copper pipe is also available with dimensions of steel pipe. . . . Refrigeration lines used in connection with air conditioning equipment also, employ copper tubing extensively. For refrigeration use where, tubing absolutely free from scale and dirt is required, bright annealed copper tubing that has been deoxidized is used. This tubing is available in a variety of sizes and wall thicknesses. ' ' EXPANSION AND FLEXIBILITY The increase in temperature of a pipe from room temperature to an operating steam or water temperature 100 deg or more above room tem perature results in an increase in length of the pipe for which provision must be made. The amount of linear expansion (or contraction in the . case of refrigeration lines) per unit length of material per degree change in Pipe,'Fittings, Welding~ .` - - , ' ' 499 temperature is termed the- coefficient of .linear expansion, or commonly, the coefficient of expansion. This coefficient varies with the material. The linear expansion of cast-iron, steel, wrought-iron, and copper pipe; the materials most frequently used in heating and ventilating work, can be determined from Table 4. ,' The three methods by which the elongation due to thermal .expansion may be taken care of are: (1). Expansion joints; (2) Swivel joints; (3) Inherent flexibility of the'pipe itself utilized through pipe bends, right-angle turns, or offsets in the line. Expansion joints of the slip-sleeve, diaphragm, or corrugated types made of copper, rubber, or other gasket material are all used for taking up expansion, but generally only for low. pressures or where the inherent flexibility of the pipe cannot readily be used as in underground steam or- hot water distribution lines. . . Swivel joints are used to some extent in low-pressure steam and hot- Fig. 1. Measurement of L on Various Pipe Bends water heating systems, and in hot-water supply lines. Since swivel joints permit the expansive movement of the pipe by turning of threaded joints, which may ultimately result in a leak, it is preferable to provide sufficient flexibility without resorting to swiveling in the threads. Probably the most economical method of providing for expansion' of piping in a long run is to take advantage of the directional changes which must necessarily occur in the piping and proportion the offsets so that sufficient flexibility is secured. Ninety-degree bends with long, straight tangents in either a horizontal or a vertical plane are an excellent means for securing adequate flexibility with larger sizes of pipe. When flexi bility cannot- be obtained in this manner, it is necessary to make use ofsome type of expansion bend. The exact calculation of the size of ex pansion bends required to take up a given amount of thermal expansion is relatively complicated1. The following approximate method, however, has been found to give reasonably good-results and is deemed to be sufficiently accurate for most heating work. Fig. 1 shows several types of expansion bends commonly used for taking up thermal expansion. . The amount of pipe, L, required in each of these bends may be computed from Equation 1, . L = 6.16 y D A . , (1) where . L = length of pipe, feet. D = outside diameter of the pipe used, inches. . A -- the amount of expansion to be taken up, inches. ' This formula, based on the use of mild-steel pipe with wall thicknesses not heavier than extra-strong, assumes^a maximum safe value of fiber 500 CHAPTER 27 1946 Guide- stress of 16,000 psi. When square type bends are used, the width of the bend should not exceed about twice the height, since for a given total length of pipe in the bend, the height of the bend becomes progressively dess with increase in width until the height approaches zero and no flexibility exists. Actually, wide bends utilize to best advantage the inherent flexibility of the line, but such bends cannot be proportioned on the basis of Equation 1. For such applications, more accurate methods1 should be employed. It is further assumed that the corners are made with screwed or flanged elbows or with arcs of circles having radii five to six times the pipe diameter. Use of welding elbows with radii of 1J4 times the pipe diameter will decrease the end thrusts somewhat but will raise the fiber stress correspondingly. . All risers must be anchored and safeguarded so that the difference in length when hot from the length when cold shall not disarrange the normal and orderly provisions for drainage of the branches. Proper anchoring of piping is especially necessary with light-weight radiators, to allow for freedom of expansion in order that no pipe strain will distort the radiators. When expansion strains from the pipes are permitted to reach these light metal heaters, they usually emit disturb ing sounds. ; HANGERS AND SUPPORTS Heating system piping requires careful and substantial support. Where changes in temperature of the line are not large, such simple methods of support may be utilized as hanging the line by means of rods or perforated strip from the building structure, or supporting it by brackets or on piers. When fluids are conveyed at temperatures of 150 F or above, however, hangers or supporting equipment must be fabricated and assembled to permit free expansion or contraction of the piping. This can be accom plished by the use of long rod hangers, spring hangers, chains, hangers or supports fitted with rollers, machined blocks, elliptical or circular rings of larger diameter than the pipe giving contact only at the bottom, or trolley hangers. In all cases, allowance should be made for rod clearance to permit swinging without setting up severe bending action in the rods. For pipes of small size, perforated metal strip is often used. For horizontal mains, the rod or strip usually is attached to the joists or steel work of the floor above. For long runs of vertical pipe subject to con siderable thermal expansion, either the hangers should be designed to prevent excessive load on the bottom support due to expansion, or the bottom support should be designed to withstand the entire load. THREADING PRACTICE In all threaded pipe for heating and ventilating installations the American Standard taper pipe thread, A.S.A. B2.1-1942 is used. This thread is cut with a taper of 1 in 16 measured on the diameter of the pipe so as to secure a tight joint. The number of threads'per inch varies with the pipe size. Threads for fittings are the same, except that it is regular practice to furnish straight tapped couplings for Schedule 40 pipe 2 in. and smaller. For steam pressures in excess of 25 psi, it is recommended that taper-tapped couplings be used to obtain a tight joint. These may be secured by ordering line pipe4 which is used for oil piping, the couplings of which are provided with taper-tapped threads and may be used with regular mill-threaded standard weight pipe. Thread lengths should be in accordance with A.S.A. B2.1. Right-hand threads are used unless Pipe, Fittings, Welding 501 otherwise ordered. To facilitate drainage, some elbows have the thread tapped at an angle to provide a pitch of the connecting pipe of J4 in. to the foot. These elbows are known to the trade as pitch elbows and are commercially available." All threaded pipe joints should be made up with a thread paste suitable for the service for which the pipe is to be used. TYPES OF FITTINGS Fittings for joining the separate lengths of pipe together are made in a variety of forms, and are either screwed or flanged, the former being generally used for the smaller sizes of pipe up to and including 3J4 in-, and the latter for the larger sizes, 4 in. and above. Screwed fittings of SOLDER-TYPE FITTING REFRIGERATOR TYPE FIARED-TUBING FITTINGS COMPRESSION TUBING FITTINGS FiARED-TUBlNG FITTINGS Fig. 2. Copper or Brass Tubing Fittings large size as well as flanged fittings of small size are also made and are used for certain classes of work at the proper pressure. . The material used for fittings is generally cast-iron, but in addition to this, malleable-iron, steel and steel alloys are also used, as well as various grades of brass or bronze. The material to be used depends on the character of the service and the pressure. Malleable iron fittings, like brass fittings, are cast with a round instead of a flat band or bead, or with no bead at all. Fittings are designated as male or female, depending on whether the threads are on the outside or inside, respectively. Screwed galvanized fittings are made according to the 150 lb American Standard. As in the case of pipe, several weights of fittings are manufactured. Recognized American Standards for the various weights are as follows: Cast-iron pipe flanges and flanged fittings for 25 lb (sizes 4 in. and larger), 125 lb, and 250 lb maximum saturated steam pressure, A.S.A. B16b2, B16a, and B16b respectively. Malleable iron screwed fittings for 150 lb maximum saturated steam pressure, A.S.A. B16c. , . . Cast-iron screw-ed fittings for 125 and 250 lb maximum saturated steam pressure, - A.S.A. B16d. .. ' ,- Steel flanged fittings for 150 and 300 lb maximum steam service pressure, A.S.A. B16e. The allowable cold water working pressures for these standards vary from 43 lb for the 25 lb standard to 500 lb for the 300 lb steel standard. . 502 CHAPTER 27 1946 Guide War standard ratings in effect for the duration of the emergency now permit higher ratings for certain sizes of the 125 lb cast-iron flanged fitting standard, and for 30.0 lb steel flanges and flanged fittings than are shown in the regular American Standards mentioned previously. Screwed fittings include: nipples or short pieces of pipe of varying lengths: couplings of steel or wrought-iron; elbows for turning angles of either 45 deg or 90 deg; return bends, which may be of either the close Table 5. American Standard Dimensions of Elbows, Tees, Crosses, and 45 Deg Elbows, Soldered-Joint Fittings, A.S.A. A40.3-1941 Pipe, Fittings, Welding' 503 age of the water of condensation in steam lines or free escape of air in water lines. ' ' . .' ; . . .. Fittings for copper-tubing are available in the soldered, flared, or com- , pression types. Illustrations of each of these types are shown in Fig. 2. Fittings for copper pipe of IPS dimensions are available in screwed or soldered types of connection. Table 5 from A.S.A. Standard A40.3-1941 Table 6. American Standard Dimensions of Elbows, 45-Deg Elbows, Tees, and Crosses (Straight Sizes) for Class 125 CastIron Screwed Fittings, A.S.A. B16a-1939 Cast Brass^ Nominal She* Laying Length. Tee, EU, and Crcesb Laying - Length, EU With External Shoulder Laying Length, 45 Deg / EU Laying . Inside Length, Diameter 45 Deg Ell of External Fittings,0 Shoulder Min. ' / Metal Thickness11 Wrought Metal Metal Thickness* Min.* Boas 07 Fittings xx X. X 1 mIX 2. 2X - 33 X ,4 .5 6 H X He . He He X Vs 1 IX ImX 2 . 23xX - 3% . i ' Vs He He `He Vs 1 IX IiXx IX 2X 2X --*. JQ He X He He He XX He He He He XX 94 X . XX .X 1 X `He mIX m *-- O 0.31 0.43 0.54 0.78 1.02 1.26 1.50 1.98 . 2.46 2.94 3.42; 3.90 4.87 5.84 T 0.08 0.08 0.09 0.10 0.11 0.12 0.13 0.15 0.17 0.19 0.20 0.22 0.28 0.34 ;R 0.048 0.048 0.054 0.060 0.066 0.072 0.078 0.090 0.102 0.114 0.120 0.132 0.168 0.204 T and R E. Min. 0.030 0.035 0.040 0.045 0.050 0.055 0.060 0.070 0.080 0.090 0.100 0.110 0.125 0.140 0.378 0.503 0.628 0.878 1.1285 1.3785 1.629 2.129 2.629 3.129 >3.629 . 4.129 5.129 6.129 ` All dimensions given'in inches..' ' - ,' " . ' - aTbis size is the nominal bore of the tube. . - . bThese dimensions may be used for wrought-metal fittings as well as for cast-brass fittings at manu facturer's option. '. ' \ . , . #. cThis dimension is the same as the inside diameter Class L tubing (American Standard Specifications for v Copper Water Tube. AS.A. H23.1-1939 (A-S.T.Af. B88). .. . dPatterns shall be designed to produce body thicknesses given in the table. Metal thickness at no point shall be less than 90 per cent of the thicknesses given in' the table. - ... eThis dimension has the same .thickness as Type L tubing. _. fThese dimensions are minimum, but in every case the thickness of wrought fittings should be at least as heavy as the tubing with which it is to be used. . * Note 1:--Wrought fittings, as well as cast fittings.'must be provided with a shoulder or stop at the bottom end of socket. ` . " " Note 2;--Street fittings with male ends are for use in connection with other fittings illustrated. ' . or open pattern, and may be cast with either a back or side outlet; tees; crosses; laterals or Y branches; and a variety of plugs, bushings, caps, jock-nuts, flanges and reducing fittings. Reducing fittings as well as .bushings, both of which are used in changing from one pipe size to another, may have the smaller connection tapped eccentrically to permit free drain- Nowkal Pm Sob . A Center to End. Elbows, Tees and Crosses cBE Center to End, 45 Deo Elbows -. Length or Thread, Mm. Width or Band, Min. F . a. H Inside Diameter or Fitting Min Mm Metal Thickness,* Mm. .. Outside Diameter or-Band. Min. X 0.81 0.73 X 0.95 0.80 X 1:12 0.88 X 1.31 0.98. 1 ix IX 2 2X 1.50 1.75 1.94 2.25 2.70 1.12 1.29 1.43 1.68 1.95 3 3X 3.08 2.17 . 3.42 . -2.39 4 3,79 2.61 5 4.50 3.05 6 5.13 3.46 ,8 6.56 4.28 10 . 8.08b 5.16 12 ' 9.50>> 5.97. . 0.32 0.36 0.43 0.50 0.58 0.67 0.70 0.75 0.92 0.98 1.03 1.08 1.18 1.28 1.47 1.68 1.88 . 0.38 0.44 0.50 0.56 0.62 0.69 0.75 0.84 0.94 1.00 1.06 1.12 1.18 1.28 1.47 . 1.68 1.88 0.540 0.675 0.840 1.050 1.315 1.660 1.900 2.375 2.875 3.500 4.000 4.500 5.563 6.625 8.625 10.750 12.750 0.584 0.719 0.897 1.107 1.385 1.730 1.970 2.445 2.975 3.600 4:100 4.600 5.663 6.725 8.725 10.850 12.850 o.iio 0.120 0.130 0.155 0.170 0.185 0.200 0.220 '0.240 0.260 0.280 0.310 0.380 0.430 0.550 0.690 0.800 0.93 1.12 1.34 1.63 1.95 2.39 2.68 3.28 3.86 4.62 5.20 5.79 7.05 8.28: 10.63 13.12 15.47. Ail dimensions given in inches. . ' . Patterns shall be designed to produce castings of metal thickness given in the table. at no point shall be less than 90 per cent of the thickness given in the table. bApplies to elbows and tees only. 'v ' ' Metal thickness contains dimensions for soldered joint elbows, tees, crosses, and 45 deg elbows. ' ..` The compression type fitting is generally limited to smaller size tubing while the flared and soldered types are used in both large and small sizes.. An American Standard, A.S.A. A40.2-1936 has been prepared to.stand ardize dimensions for brass fittings for flared copper water tubes.. Flared tube fittings are widely used in.refrigerating work where S.A.E. dimen sions and a 45-deg flare render most fittings interchangeable, although 504 CHAPTER 27 1946 Guide Tablb 7. American Standard Dimensions of Tees, Crosses3 (Straight Sizes), and Elbows for Class 125 Cast-Iron . Flanged Fittings, A.S.A. B16a-1939 . Nominal Peps Size1*-8 A Center to Face Tees, Crosses-*! and Elbows AA Face to Face Tbbs and Crosses*-* Bc Center to Face Long Radius El80W*** Center to Face 45 Deo ' Elbow* Diameter or Flange Thickness or Flange. Min. Metai> Thickness or Body i ix m 2 3)4 3 3)4 .4 r5 6 8 10 , 12 ' 14-O.D. 16 O.D. 18 O.D. 20 O.D. 24 O.D. 30 O.D. 36 O.D. 42 O.D. 48 O.D. 3% 4 4)4 5 OX 6 OX m 8 9 11 12 14 15 10X 18 22 . 25 28 31 34 7 7M 8 9 10 11 12 13 15 16 18 22 24 28 30 33 36 44 50 56 62 68 5 5X 6 6X 7 7% 3)4 9 10)4 liX 14 io)4 19 31)4 24 26^ 29 34 - 41^ 49 00)4 64 . m 2 3X 3)4 3 3 3)4 4 4)4 5 -' 5X 0)4 7)4 7)4 8 3)4 ox ii 15 18 21 24 4K ' 4% 5 6i 7 7)4 8)4 9 .10 M- . 13)4 16 19 21 33)4 25 37)4 32 38X -46 53 . oo)4 56 )4 56 X 56 X % *54 56 1 1)4m IX m 156 i% 1*56 m 3)4 3]H. 3% 3X 56 56 56 56 56 X 56 X )4 % X x >56 % 1 U6 1)4 IX . 156 1% ll56 2. . All dimensions given in inches. %. ` . `Crosses both straight and reducing sizes 18 in. and larger shall be reinforced to compensate for the inherent weakness in the casting design. '' bSize of all fittings listed indicates nominal inside diameter of port. ' '. - "Tees, side outlet tees, and crosses, 16 in. andsmalier/reducing on the outlet, have the same dimensions center to face, and face to face as straight size fittings corresponding tp the size of the targer opening. Size 18 in: and larger, redudng on the outlet, are made in two lengths, depending on the size of the outlet. dTees and crosses, reducing on run only, carry same dimensions center to face and face.to face as a straight size fitting of the larger opening. . '. - Reducing elbows and side outlet elbows carry same dimensions center to face as straight size elbows corresponding to the size of the larger opening. ' (Special degree elbows, ranging from 1 to 45 deg, inclusive, have the same center to face dimensions as given for 45-deg elbows and those over 45 deg and up to 90 deg. inclusive, shall have the same center to face dimensions as given for 90-deg elbows. The angle designation of an elbow is its deflection from straight line flow and is the angle between the flange faces. , .' - . - Side outlet elbows shall have all openings on intersecting center-lines. hBody thickness at no point shall be less than 87H per cent of the dimensions given in the table. , Pipy Fittings, Welding SOS ! ; i i !/ ! 1 ' , j ' i i. for refrigeration use, thread, fits and tolerances on thread gages must be maintained within close limits. Brass fittings with S..4..E. dimensions are not interchangeable with the American Standard fittings for water tubes, Ammonia pipe fittings made of cast-iron were formerly used extensively . in handling refrigerants in large installations. Replacement of ammonia . by other refrigerants operating at lower pressures has seriously curtailed the market for these fittings. For this reason formulation of an American Standard for these fittings was abandoned by the A.S.A. in 1936. . FLANGE FACINGS AND GASKETS A number of different flange facings in common use are plain face, raised face, tongue and groove, and male and female. Cast-iron fittings for 125 psi and below are normally furnished with a plain face, while the 250 lb cast-iron fittings are supplied with a raised face. The standard facing for steel flanged fittings for 150 and 300 psi is a raised face although these fittings are obtainable with a variety of facings. The gasket surface of the raised face may be finished smooth or may be machined with concentric or spiral grooves often referred to as serrated face or phonograph finish, respectively. The dimensions of elbows, tees and crosses for 125 lb cast-iron screwed fittings are given in Table 6, whereas the dimensions for 125 lb cast-iron flanged fittings are given in Table 7. . For low temperature service not to exceed about 220 F, a number of paper or vegetable fiber gasket materials will prove satisfactory; for plain . raised face flanges, rubber or rubber inserted gaskets are commonly employed. Asbestos composition gaskets are probably the most widely used, particularly where the temperature exceeds 250 F. Jacketed asbestos and metallic gaskets may be used for any pressure and tem perature conditions, but preferably only with a narrow recessed facing: WELDING Erection of piping in heating and ventilating installations by means of fusion welding has been commonly accepted in the past few years as ah alternate method to the screwed and flanged joint. Since the question of economy of welding as against the use of screwed and flanged fittings is dependent on the individual job, the use of welding is generally recom mended on the basis of a greatly reduced cost of maintenance and repair, of less weight resulting from the use of a lighter-weight pipe, and of increased economy in pipe insulation, hangers, and supports rather than on the basis of any economy that might be effected in actual erection by ' welding on low to medium pressure heating jobs. Fusion welding, commonly used in erection of piping, is defined as the process of joining metal parts in the molten, or molten and vapor states, without the application of mechanical pressure or blows. Fusion welding embraces gas welding and electric arc welding, both of which are com monly used to produce acceptable welds. Welding processes and pro cedure are described in various publications3. ` Welding application requires the same basic knowledge of design as do the other types of assembly; but, in addition, requires a generous know- ledge of the sciences involved, particularly as to welding qualities of / metal, their reaction to extremely high temperatures, and the ability to determine and use only the best quality welding rods. This requirement applies equally to employer and employee with the employer accepting 506- CHAPTER 27 , 1946 Guide all of the responsibility.. Thus the employer should select his welding' mechanics with good judgment, provide them with first-class equipment and tools, arrange for their training and use of acceptable workmanship standards, and at regular intervals subject their work to prescribed tests. For piping which is to be operated at pressures in excess of 15 psi, rules for fusion welding of pipe joints and the qualification of welders and Table 8. American Standard Dimensions for Bdtt-Welding Elbows, Tees, ' Caps, and Lapped-Joint Stub Ends, a ..S'./I. B16.9-1940 Nominal Pips Saa i ik m 2 m 3 3K 4 5 6 -8 10 12 OUTBIDS Diameter Center-to-End ` 90-Deg Elbows A 45-Deg Elbows B Of Run Tce.e. 1.315 ik 1.660 m 1.900 m . 2.375. 3 .2.875 . 3K 3.500 4K 4.000 5K 4.500 6 5.563 ' 7K 6.625 9 8 625 12 10.750 15 12.750 18 Vs i IK IK - IK 2 2K. 2K 3K 3K . 5 6K 7K IK . IK 2K 2K ' 3 3K 3K 4K 4K 5K 7 8K 10 Caps b-o IK IK IK IK IK 2 2K 2K 3 3K 4 5 6 Lapped-Joint Stub Ends Length 4 4 4 6 6 6 6, 6 8 8 8 10 10 Radius of Fillet . /* K ' He K He Me K K He He K K K K Diarn. of ' 2 2K 2K 3K 4K 5 5K 6Ks 7He : 8K 10K . 12K 15 All dimensions given in inches. . .' . The dimensions of welding tees cover those which have side outlets from one size less than half the size of the run-way opening of the tees to full size. _ . . ^Dimensions E and P are applicable only to these fittings in schedules up to and including Schedule SO, AS.A. Standard B36.10-1939.. . . *, . ' eTtie shape of these caps shall be ellipsoidal and shall conform to the requirements of the A.S.M.B. Bailer Construction Code. .. . .. dThis dimension is for standard machined facings in accordance with American Standard for Steel Pipe Flanges and Flanged Fittings (A-S-A. B16e-1939). The back face of the lap shall be machined to conform ' to the surface of the flange on which it seats. . Where ring joint facings are to be applied, use dimension K as given in AJS.A. B16e-1939. . . .. -- * welding procedures as contained in the American Standard, Code for Pressure Piping should be observed. U. S. Navy specifications for weld ing, and qualification of operators are available4. For pressures 15 psi or below, the foregoing rules or those set forth in the Standard Manual on Pipe Welding of the . Heating, Piping and. Air Conditioning Contractors National Association should be followed to insure a satisfactory welded, joint. " A complete line of manufactured steel welding fittings is now available and a dimensional standard has been prepared,under the procedure of the American Standards Association to unify heretofore divergent dimensions ' for the same type welding fittings as produced by different manufacturers. . Standard dimensions for steel butt-welding elbows, tees, caps, and lapped , joint stub ends'are given in Table 8. Dimensions for eccentric.and con centric reducers, and 180-deg return bends are not shown in Table 8 but Pipe, Fittings, Welding 507 ' are included in the American Standard. Larger sizes also are available in some types of fittings. The welding bevel .which is a straight 37%-deg V for wall thickness % in. and below, and a U-bevel for thicknesses heavier than % in., conforms.to the recommended practice of.A^S.A. Table 9. American Standard Dimensions of Steel Welding Neck and Slip-on Welding Flanges for Steam Service Pressure Rating of 150 PSI (Gage) at a Temperature of 500 F, and 100 PSI (Gage) at 750 F, .4..S..4. B16e-1939 Nominal . Pipe Size K K l IK IK 2 2K 3 3K 4 5 6 8" 10 12 14 O.D. 16 O.D. 18 O.D. 20 O.D. 24 O.D. Diameter Thickness op Flange op Flg. Min. , Diameter op Hub Hub Diam. Beginning op Champbr^-0 Length Thru Hub* Inside Diam. op Pipe Schedule 40 Bore op Slip-on Flanges Mm. Diam. or No. Size Bolt OP . OP Circle Bolts Bolts 0QX B r . J- w . 3K He- 3K K 4K He 4K K . 5 `54 6K 7K 7K 'He 8K 1He 9 1He 10 'He 11 1 13K 16 IK m 19 IK 2i IK 23K iHe 25 . ~THe 27K . 1% 32 IK 154 IK 1% 254 254 3)4 354 4K 4'He 554 654 754 9154 12 14K 15K 18 19K 22 26K 0.84 1.05 1.32 1.66 , 1.90 2.38 2.88 .3.50 4.00 4.50 5.56 6.63 8.63 ' 10.75 12.75 14.00 16.00 18.00 20.00 24.00 IK 254 254 2K 254 2K 2K m 2*54 3 3K 3K 4 4 4K 5 5 5K 5*54 6 0.62* 0.82* 1.05* 1.38* 1.61* 2.07* 2.47* 3.07* 3.55* 4.03* 5.05* 6.07* 7.98* 10.02* To Be Specified by Purchaser 0.88 1.09 1.38 1.72 1.97 2.44 2.94 3.56 4.06 4.56 5.66 6.72 8.72 10.88 12.88 14.19 16.19 18.19 '20.19 24.19 ' 2K m 3K 3K 3K 4K 5K 6 7 7K 8K 9K liK 14K' 17 18K 21K 22K 25 29K 4 4 4 4 4 4 4 4 8 8 8 8 8 12 12 12 16 16 20 20 K K K K K K K K K K K K K K K l l IK IK IK All dimensions given in inches. _' . *A raised face of Vi in. is included in thickness of flange minimum and in length through hub. bThe outside surface of the welding end of the hub shall be straight or tapered at not more than 6 deg. ' Dimensions H- and J correspond to the outside and inside diameters of pipe as given in A S.A. B3Q. 10 1939. Schedule 40. . . ' *These diameters are identical with the diameters of what was formerly designated as Standard Weight Pipe of the corresponding sizes.' - - __ Stanford B16e-1939, American Standard for Steel Pipe Flanges and Flanged Fittings. The latter also contains dimensions for steel welding neck.flanges for pressures up to 2500 psi, and slip<>n welding flanges for 150 and 300 psi. Table 9 gives these dimensions for welding-neck arid ` slip-on welding flanges suitable for 150 psi gage pressure. . ' . Socket-welding fittings also are commercially available. These fittings have a machined recess for inserting the pipe which is attached by a fillet weld between the pipe wall and'socket end.. Use of socket-welding fittings generally is restricted to nominal pipe sizes 3 in. and smaller in 508 CHAPTER 27 1946 Guide which range commercial fittings are available.' This type of fitting has gained rapid acceptance owing to its ease of installation, low cost, and ability to make a-pressure tight joint without weakening the pipe as is the case with threading. Dimensions for socket-welding fittings as . offered by most manufacturers of the product are given in Table 10. VALVES Valves are made with both .threaded and flanged ends for screwed and bolted connections just as are pipe fittings. The material used for valves of small size is generally brass or bronze for low pressures and forged steel for high pressures, while in the larger Table 10. Proposed American Standard Dimensions of Socket-Welding Elbows, Tees, Crosses, 45-Deg Elbows, and Couplings Pipe> Fittings, Welding 509 rising stem, although in the smaller sizes the rising stem is more commonly used. The rising stem valve is desirable because the positions of the handle and stem indicate whether the valve is open or closed, although space limitations may prevent its use. The globe valve is less expensive to manufacture than the gate valve, but its peculiar construction offers a high resistance to flow and may prevent complete drainage of the pipe line. These objections are of particular importance in heating work. ' An American Standard, A.S.A. B16.10-1939, has been prepared giving the face-to-face dimensions of ferrous flanged and welding-end valves. The following types are covered:" wedge gate, double disc gate, globe and angle, and swing check. One purpose of establishing these dimensions is Table 11. American Standard Contact Surface to Contact Surface Dimensions Nominal Pipe ' Sub Minimcm Depth op ' Socket Center to Bottom op Socket 90-Deg Kits, Tees, Crosses 45-Deg Elis Sched. Scbed. Sched. Sched. 10 4 SO 160 10 4 80 160 Couplings Bore Distance Diameter Between op .Bottom Socket, Sockets Minimum Minimum Socket Wall Thickness Sched. Sched. Sched. 40 SO 160 Bobs Diametbb op FrmNQS Scbed. Sched. Sched. 40 80 160 A. A 'E ' B O D. X X 'K X X X X% K X K -X XXK K H X X X K K% X K H IK `K, H IX K IK 'X X IK H IX IX 'K K 2 X IK ix 1 X 2X X . IK 2x m XX X 3 X 2X IK ix X 0.555 0.690 0.855 1.065 1.330 1.675 1.915 2.406 2.906 3.535 0.156 0.156 0.156 0.156 0.166 0.175 0.181 0.193 0.254 0.270 0.156 0.158 0.184 0.193 0.224 0.239 0.250 0.273 0.345 0.375 0.234 0.373 0.313 0.313 0.351 0.429 0.469 0.546 0.364 0.493 0.622 0.824 1.049 080 1.610 2.067 2.469 3.068 0.302 0.423 0.546 0.742 0.957 1.278 1.500 1.939 2.323 2.900 0.466 0.614 0.815 1.160 1.338 1.689 2.126 2.626 AH dimensions are giyen in inches. . , Dimension C is IX times the nominal pipe thickness, minimum, but not less than */ in. Reducing sues have same center to bottom of socket dimension as the largest size of reducing fitting. sizes either cast-iron, cast-steel or some of the steel alloys are employed. Practically all iron or steel valves intended for steam or water work are m bronze-mounted or trimmed. " Brass, bronze, and iron valves are generally designed for standard or extra heavy service, the former being used up to 125 lb and the latter up to 250 lb saturated steam working pressure, although most manufacturers also make valves for medium pressure up to 175 lb steam working pres sure. The more common types are gate valves or straightway'valves, \ globe valves, angle valves, check valves and automatic valves, such as reducing and back-pressure valves. ' - Gate valves are the most frequently used of all valves since in their open position the resistance to flow is a minimum, but they should not be used . where it is desired to throttle.the flow;, globe valves should be used for this purpose. These valves may be secured with either a rising or a non- All dimensions given in inches. . - . These, dimensions are the same for Cast-Iron Double Disc Flanged Gate Valves. bThese are pressure designations which refer to the primary service ratings in pounds per square inch of the connecting end flanges; -- - The connecting end flanges of 175 lb valves are the same as those on 250 lb valves. '' Note 1:--Where dimensions are not given, the sizes either are not made or there is insufficient demand to warrant the expense of unification. . Note 2:--Female and groove joint facings have bottom of groove in same plane as flante.edge, and center to contact surface dimensions for these facings are reduced by the amount of the raised face. to insure that gate valves of a given rating and flange dimension of either the wedge or double disc design will be interchangeable in a pipe line. Contact surface to contact surface dimensions of cast-iron and steel flanged-wedge-gate valves are given in Table 11. End-to-end dimensions for steel butt-welding valves in sizes up to 8 in., inclusive, are the same as those given in Table 11 for steel valves. Check valves are automatic in operation and permit flow in only one direction, depending for operation on the difference in pressure between the two sides of the valve. The two principal kinds of check valves are the swing check in which a flapper is hinged to swing back and forth, and the lift check in which a dead weight disc moves vertically from its seat. Valves commonly used for controlling steam or water supply to radi .. ators constitute a special class since they are manufactured to meet 510 CHAPTER 27 1946 Guide heating system requirements. These valves are generally of the angle 'type and are usually madeof brass. Graduations on the heads or lever handles are often supplied to. indicate the relative opening of the valve. Automatic control of steam supply to individual radiators can be effected by use of direct-acting radiator valves having a thermostatic element at the valve, or near to it. The direct-acting valve is usually an angle-type valve containing a thermostatic element which permits the flow of steam in accordance with room temperature requirements. These valves usually are capable of adjustment to permit variation in room temperature to suit individual taste. . Ordinary steam valves may be used for hot water service by drilling a Hs-in. hole through the web forming the seat to insure sufficient circulation to prevent freezing when the valve is closed. Valves made for use in hot water,heating systems are of simpler design, one type consisting of a simple butterfly valve, and another of a quick opening type in which a part in the valve mechanism matches up with an opening in the valve body. In one-pipe steam-heating systems, automatic air valves are required at the radiators. Two common types of air valves available are the vacuum type and the straight-pressure type. Vacuum valves permit the expulsion of air from the radiators when the steam pressure rises and, in addition, act as checks to prevent the return of air into the radiator when a vacuum is formed by the condensation of steam after the supply pressure has. dropped. Ordinary air valves permit the expulsion of air from the radiator when steam is supplied under pressure, but when a vacuum tends to be formed the air is drawn back into the radiator. . CORROSION ` Corrosion is sometimes encountered in heating work on the outside of buried pipes or the inside of steam heating systems; it is seldom ex perienced in hot water heating systems unless the water is frequently renewed. Piping buried in the ground is quite successfully protected by.. coatings of the asphaltic type which are usually applied hot and often reinforced with fabric wrappings. Galvanizing by the hot-dip process and painting with specially prepared mixtures also afford some protection. Internal corrosion6 in steam, heating systems occurs principally in the condensate return pipes and is nearly always caused by oxygen or carbon . dioxide, or both, in solution-in the condensate. Oxygen may enter the heating system with the steam, owing to its presence in the boiler-feed water, or it may enter as air through small leaks, particularly in systems . which operate at sub-atmospheric pressures. -When a steam heating system is operated intermittently, air rushes in during each shutdown period and oxygen is absorbed by the condensate which clings to the' interior surfaces of the pipes and radiators. The rate of corrosion depends upon the amounts of oxygen and carbon dioxide present in solution, upon the operating temperature, and upon the; length of time that the pipe surfaces are in contact with gas-laden condensate. Another possible cause of corrosion is a flow of electric current some times resulting from faulty electrical circuits which .should be corrected. Electrolytic corrosion also may occur because of the presence of two dis-. similar metals, such as brass and iron, but the condensate in practically all steam heating systems is such a weak electrolyte that this cause-of corrosion is very infrequent. . .. If-trouble is experienced from corrosion,.oxygen should be eliminated . from the feed water by proper deaeration with commercial apparatus. Pipe, Fittings,-Welding . 511 . The elimination of the oxygen due to air leakage is more difficult because of the multitude of small leaks which exist around valve stems and in pipe joints. In vacuum systems, however, an attempt should be made to minimize such leakage. '. - . Carbon dioxide in varying amounts is contained in steam produced from the majority of water supplies. It is formed from the breaking down of carbonates and bicarbonates which are present in nearly all natural waters. It can be partly removed by chemical treatment and deaeration, but there is no simple method whereby it can be entirely eliminated. 1 These gases cause corrosion only when in solution in the condensate; , when they are mixed with dry steam their corrosive effect is negligible. The amount of gas in solution depends upon the partial pressure of that gas in the atmosphere above the surface of the solution, in accordance' with the well known physical law of Henry and Dalton *. The correct application of this law, however, requires equilibrium conditions which do not always exist under the flow conditions prevailing in a heating system. There is a distinction between corrosion in heating systems proper and in the condensate discharge lines from other apparatus using steam at relatively high rates, particularly at the times of the cycle when the 1 steam consumption is at its heaviest. In such equipment the gases tend to accumulate in the steam space and to become dissolved in the con - densate in high concentrations, thus greatly increasing the possibilities of corrosion. The condensate will more nearly approach in composition the composition of the steam than will the normal condensate from apparatus such as room radiators, and will, therefore, normally include in solution more contaminants. It is possible that careful venting of such equipment would reduce the amount of contaminants dissolved in the condensate, thus giving less corrosion. There is evidence-that the partial pressures of the gases and the possibility of corrosion are much lower in . heating systems than jn high usage equipment. Hence, corrosion ob served in the condensate discharge lines from high usage equipment does not necessarily indicate that equally serious corrosion is taking place in the heating system. . - ' The seriousness of corrosive conditions is best determined by actual measurement rather than by inference from isolated instances of pipe failures. The National District Heating Association has perfected a cor rosion tester' for measuring the inherent corrosiveness of existing con ditions. This corrosion tester consists of a frame supporting three coils of wire which are carefully weighed. After the tester has been inserted in the pipe line for a definite length of time, the loss of weight of the coils, . referred to an established scale, indicates the relative corrosivensss of the condensate. Accompanying such corrosion measurements, a careful chemical analysis should be made of the condensate, and the findings will serve as a basis for an intelligent study of the problem7. . There are some indications that after a. condensate containing carbon dioxide has dissolved some iron and thereby raised its pH value, its cor rosive action is greatly reduced and the solution will remain comparatively inactive until admission of oxygen permits the precipitation of the -dissolved iron ,as ferric oxide. The pH value of the condensate may be buffered to a fairly high value by the solution of iron and not correspond to the pH value to be expected in the unbuffered solution containing the same amount of carbon dioxide. . . -Although inhibitors of.various types have had.considerable trial and .experimentation and successes have been reported, they require further. 512 ________________ .CHAPTER 27'1946 Guide study. Among these inhibitors are oil, sodium silicate, sodium hydroxide, tannin, and various other organic compounds, some of which release ammonia gas. The possible toxic effects, particularly if the steam is used for contact cooking of food, should not be overlooked. In view of the fact that corrosion is most frequently, found in the return lines from special equipment, which constitute a relatively small part of the total, piping in a building, a simple solution of the corrosion problem may be to use non-corroding materials in those certain portions of the piping system, since the higher cost will usually be an unappreciable. portion of the total. .Brass and copper are undoubtedly less subject to this type of corrosion than the ferrous metals, and considerable attention is now being given to corrosion-resistant linings for ferrous pipe. Cast-iron pipe, sometimes alloyed with other metals, also deserves consideration. Eighteen ferrous and non-ferrous metals and alloys were tested in a large air conditioning installation 8. Observations were made in the wash water of the dehumidifier and in the air stream beyond the eliminator ' plates. The corrosion rates of all metals and alloys utilizing a dichro- mated-treated wash water were extremely low. Localized attack in the form of pitting was found to occur on steel in crevices or under solid accumulations. Just beyond the dehumidifier eliminator plates corrosive conditions were observed to be particularly severe and in such locations non-ferrous metals and alloys and stainless steels were most resistant. Alloy steels were found to be superior to mild steel. , REFERENCES See (1) Piping Handbook, by Waiker and Crocker (McGraw-Hill Co.) ;`(2) A Manual for The Design ' of Piping for Flexibility by the Use of Graphs, by E. A. Wert. S. Smith, E. T. Cope, (The Detroit Edison Company). . ., 2--See API Specification 5L for Line Pipe, American Petroleum Institute. ' . 3--Welding Handbook (American Welding Society, 1942). Standard Manual on Pipe Welding, (Heating, Piping and Air Conditioning Contractors National Association). 4--General Specifications for Inspection of Material, Appendix VII, Welding (U. S. Navy Department. Jan. 3, 1939). . . 5_New Light on Heating System Corrosion, by J. H. Walker (Heating and Ventilating, May, 1933). A.S.H.V.E. Research Report No. 983--Corrosion Studies in Steam Heating Systems, by R. R. Seeber, F. A. Rohrman and G. E. Smedberg^ (A.S.H.V.E. Transactions, Vol. 40, 1934, p. 253). A.S.H.V.E. Research Report No. 1037--Corrosion Studies in Steam Heating Systems, bv R. R. Seeber, F. A. Rohrman and G. E. Smedberg, (A.S.H.V.E. Transactions, Vol. 42. 1936. p. 263). A.S.H.V.E. Research ' Report No. 1071--Corrosion Studies in Steam Heating Systems, by R.'R. Seeber and Margaret R. Holley . (A.S.H.V.E. Transactions, Vol.'43, 1937, p. 461).. Corrosion in Steam Heating Systems, by L. F. Collins - and'E. L. Henderson, (Healing, Piping and Air Conditioning, September, 1939 to May. 1940). --Some Fundamental Considerations of Corrosion in Steam and Condensate Lines, by R. E. Hall and A. R. Mumford (A.S.H.V.E. Transactions,'Vol. 38. 1932, p. 121). ^ . . , r~A Method of Measuring Corrosiveness, by J. H. Walker, (Proceedings, American Society for Testing Materials, 1940). '. - 8--A.8.H.V.E. Research Report No. 1203--Corrosion Tests in a Water-Recirculating Air Condition ing System, by W. Z. Friend (A.S.H.V.E. Transactions, Vol. 48, 1942,-p. 233). CHAPTER 28 Heat Losses from Bare and Insulated Pipes, Low Temperature Pipe Insulation, Insulation of Pipes to Prevent Freezing, Economical Thickness of Pipe Insulation, Underground Pipe Insulation THE heat loss from uninsulated pipes may be of considerable magni tude if the temperature of the surrounding medium differs appre ciably from that of the fluid conveyed. Losses are increased by rapid motion of the surrounding air or by contact of the pipe with bodies of high conductivity. Careful consideration must, therefore, be given to this factor in a properly designed system and adequate insulation pro vided, if necessary. . HEAT LOSSES FROM BARE PIPES Heat losses from horizontal bare steel pipes, based on tests at Mellon Institute and calculated from the fundamental radiation and convection equations (Chapter 5), are given in Table 1. Heat losses from horizontal copper tubes and pipes with tarnished surfaces, are given in Table 2 *. Heat losses from bare pipe of materials having lower emissivities may be calculated from data appearing in Chapter 5. The area in square feet per linear foot of pipe is given in Table 3 for various standard pipe sizes, and Table 4 for copper tubing, while Table 5 gives the area in square feet of flanges and fittings for various standard pipe sizes. These tables can be used to advantage in estimating the amount of insulation required. ' Very often, when pipes are insulated, flanges and fittings are left bare so as to allow for easy access to the fittings in case of repairs. The fact that a pair of 8-in. standard flanges having an area of 2.41 sq ft would lose, at 100 lb steam pressure, an amount of heat equivalent to more than a ton of coal per year shows the necessity for insulating such surfaces. Examples1 and & show how the annual heat loss from uncovered pipe and its dollar value may be computed from the data in Table 1. Example 1. Compute the total annual heat loss from 165 ft of 2 in. bare pipe in service 4000 hr per year. The pipe is carrying steam at 10 lb pressure and is exposed to. an average air-temperature of 70 F. ' -* Solution. The .pipe temperature is taken as the steam temperature, which is 239.4 F, obtained by interpolation from Steam Tables. The temperature difference between the pipe and air = 239.4 -- 70 = 169.4 F. By interpolation of Table 1 between tem perature differences of 157.1 and 227.7 F, the heat loss from a 2-in. pipe at a temperature difference of 169.4 F is found to be 1.624 Btu per (hour) (linear foot) (Fahrenheit degree). The total annual heat loss from the entire line = 1.624 X 169.4 X 165 (linear feet) X 4000 (hours) = 181,600 Mb. (Mb = 1000 Btu.) . Example g. Coal costing $11.50 per ton and having a calorific value of 13,000 Btu per pound is being burned.in the furnace supplying steam to the pipe line given in the previous example. If the system is operating at an over-all efficiency of 55 per cent, determine the monetary value of the anngal heat loss from the line. . Solution. The cost of heat per 1000 Mb supplied to the system == 1,000,000 X 11.5 (dollars) 4- [13,000 (Btu) X 2000 (lb) X 0.55 (efficiency)] = $0,804. The total cost of heat lost per year -- 0.804 X 181.6 (thousand Mb) = $146.00. . 513 514 CHAPTER 28 1946 Guide '' PIPE INSULATIONS Pipe insulations are of several general' forms and are made of various . types of material. The most common form is the rigid sectional covering either split longitudinally into halves or cut through' on one side and scored on the other, to facilitate assembling on pipes. Preformed materials are supplied in segments for assembly on large pipes. The . sectional coverings are generally supplied with a pasted on canvas .Table 1. Heat Losses from Horizontal Bare Steel Pipes _ Expressed in Btu per (hour) (linear foot) (Fahrenheit degree difference between the pipe and surrounding still air at 70 F) Nominal ' - Pipe . Size (Inches) . . 120 F Hot Water * 150 F 180 F 210 F Steam ' 227.1 F . 299.7 F (5 Lb) (50 Lb) 337.9 F (100 Lb) Temperature Difference 54 % l. AH 1)4 2 2)4 3 ' 3)4 4 5 6 8 10 12 . 50 F 0.455. 0.555 0.684 0.847 0.958 1.180 1.400 1.680 . 1.900 2.118 2.580 3.036 3.880 4.760 5.590 80 F . 0.495 0.605 0.743 0.919 1.041 1.281 1.532 1.825 2.064 2.302 2.804 3.294 4.215 5.180 6.070 110 F 0.546 0.666 0.819 1.014 1.148 1.412 1.683 2.010 2.221 2.534 3.084 3.626 4.638 5.680 6.670 140 F 0.584 0.715 0.877 1.086 1.230 1.512 1.796 2.153 2.433 2.717 3.303 3.886 4.960 6.090 7.145 157.1 F 0.612 0.748 0.919 1.138 1.288 1.578 1.883 2.260. 2.552" 2.850 3.470 4.074 5.210 6.410' 7.500 227.7 F .0.706 0.866 1.065 1.324 1.492 1.840 2.190 2.630 2.974 3.320 4.050 4.765 6.100 7.490 8.800 ' 267.9 F 6.760 0.933 1.147 1.425 1.633 1.987 2.363 2.840 3.215 3.590 4.385 5.160 6.610 8.115 9.530 Table 2. Heat Loss from Horizontal Tarnished Copper Pipe Expressed in Btu per (hour) (linear foot) (Fahrenheit degree difference : between the pipe and surrounding still air at70F) Nominal Pm firm (Inches) - Hot Water (Type K Copper Tube) 120 F 150 F ' 180 F 210 F Steam (Standard Pipe Si*e Pipe) . , 227.1 F (5 Lb) 297.7 F (50 Lb) 337.9 F (100 Lb) . . ' Temperature Difference .' Vt M 1 v/i m X2 .2 . 3 ' 3)4 4 4)4 -5 6-. .8 50 F 0.250 0:340 0.440 0.500 0.580 0.730 0.880 1.040 1.180 1.460 1.600 1.840 2.400 80 F 0.287. 0.381 . 0.475 0.559 0.656 0.825 1.000 1.175 1.350 1.500 1.812 2.125 2.685 110 F 0.300 0.409 0.509 0.618 0.710 0.890 1.091 1.272 1.454 1.635. 1.980 2.270 2.910 140 F 0.321 0.429 0.536 0.622 0.750 0.957. 1.1431.343 1.535 1.715 2.071 2.430' .3.110 157.1 F 0.433 .0.533 0.636 0.764 0.904 1.101 1.305 1.560 1.750 1.941 2.131 2.387 2.740 3.310 227.7 F 267.9 F 0.500 0.530 0.543 0.654 0.746 0.803 0.878 0.934 , 1.053. 1.120 1.273 1.364 1.490 1.605 1.800 . 1.940 2.020 2.170 2.240 2.430 2.465 2.650 .2.770 . 2.990 3.210 3:440 4.050 4.370 ' Pipe Insulation 515 Table 3. External Surface per Linear Foot of Pipe Nominal Pips Size (Inches) )4 % i Surpacb Area (Sq Ft) 0.22 0.275 0.344 0.435 0.498 Nominal Pm Size (Inches) 2 2)4 3 3)4 4 Surface Area ' ' (Sq Ft) 0.622 , 0.753 0.917 1.047 1.178 Nominal' Pm Size (Inches) 5 6 8 10 12 Surface Area (Sq Ft) 1.456 1.734 2.257 2.817 3.338 jacket. Blanket insulations aresometimes used for wrapping large pipes, particularly where removal for frequent servicing of the pipe is necessary. Fittings and bends are commonly covered with portions of standard pre formed insulation or, when irregular in contour, with plastic materials known as insulating Cements. < ' Insulation is secured to pipes with staples which are used to bridge the joint between half sections, and with metal pipe covering bands or rings of wire which secure individual sections and effect a junction between abutting sections. A number of surface finishes are used over pipe insulation depending upon the service encountered and appearance desired. Canvas jackets are most common although asbestos paper or asbestos finishing cements are sometimes employed. Insulation outdoors should be waterproof and is generally protected with an asphalt felt for piping and asphaltic cements for fittings. Insulation bn lines carrying cold water, brine, or other cold fluids is carefully finished to obtain adequate sealing against the penetration of water vapor. .The selection of pipe insulation for a particular service condition must be made with full consideration of a number of properties in addition to thermal conductivity: Factors which may be of more importance than ' the thermal conductivity, are: ease of application, fire resistance, heat stability, weathering stability, resistance to damage by physical abuse, and others which may apply to a particular installation. A complete evaluation of pipe insulation cannot be included here. Insulation manu facturers should be consulted in regard to the selection of insulation which is to meet specific requirements. ' ' HEAT LOSSES FROM INSULATED PIPES , The conductivities of various materials used for insulating steam and hot water systems are given in Table 6. They are given as functions of the mean temperatures or the arithmetic mean of the inner and outer surface temperatures of the insulations. It should be emphasized that they are the average values obtained from a number of tests made on Table 4. External Surface per Linear Foot of Copper Tubing Outside diameter J-jj in. greater than nominal size Tube Size (Inches) ` Surface Area (Sq Ft) Tube 8bs (Inches) )4 H i . . 1M 1)4 0.164 0.229 0:295 0.360 0.426 . 2 2)4 3 3)4 4 Surface Abba (Sq Ft) 0.556 0.687 .0.818 0.949 1.080 Tube Size (Inches) 5 6 8 Surface Area (Sq Ft). ; 1.342 1.604 , 2.128 . 516 CHAPTER 28 1946 Guide Table 5. Areas of Flanged Fittings, Square Feet Nominal Pipe Sirs (Inches) . i IK IK 2 m 3 3K 4 4K 5 6 8 10 12 . : Flensed COUPUNQ 90 Deg Ell Long Radius Et-t. Tee , Cooes Standard Extra Heavy Standard Extra Heavy Standard Extra Heavy Standard Extra Heavy Standard Extra Heavy 0.320 0.383 0.477 0.672 0.841 0.945 1.122 1.344 1.474 1.622 1.82 2.41 3.43 4.41 0.438 0.795 1.015 0.892 1.083 1.235 1.575 1.622 2.07 0.510 0.957 1.098 1.084 1.340 1.481 1.925 1.943 2.53 0.727 1.174 1.332 1.337 1.874 1.815 2.68 2.38 3.54 0.848 1.65 2.01 1.84 2.16 2.54 . 3.09 3.32 4.06 1.107 2.09 2.57 2.32 2.76 3.21 4.05 4.19 5.17. 1.484 2.38 3.49 2.68 3.74 3.66 5.33 4.77 6.95 1.644 2.98 3.96 3.28 4.28 4.48 6.04 5.83 7.89 1.914 3.53 4.64 3.96 4.99 5.41 7.07- 7.03 9.24 2.04 3.95 5.02 4.43 5.46 6.07 7.72 7.87 10.07 2.18 4.44 5.47 5.00 6.02. 6.81 8.52 8.82 10.97 2.78 5.13 6.99 5.99 7.76 7.84 10.64 10.08 13.75 3.77 6.98 9.76 8.56 11.09 10.55 14.74 13.44 18.97 5.20 10.18 13.58 12.35 15.60 15.41 - 20.41 19.58 26.26 6.71 13.08 17.73 16.35 18.76 19.67 26.65 24.87 34.11 "Including areas of accompanying flanges bolted to the fitting. i each type of material, also, that in the use of conductivity all variables due to differences in thickness, pipe sizes, and air conditions are eli minated. Individual manufacturer's materials will, of course, vary in conductivity to some extent from these values. The heat losses through 1, and 2-in. thick 85 per cent magnesia type of insulation for temperature differences between the pipe and the surrounding atmosphere up to 280 F are shown in Figs. 1, 2, and 3. Standard thicknesses of 85 per cent 'magnesia pipe covering are not exactly 1 in. However, the loss through any given thickness of insulation can be obtained by interpolation. Also, the losses through any of the insulations given in Table 6 can be obtained by multiplying the losses obtained from Figs. 1, 2, or 3 by the factors given in Table 7. . Pipes operating at high temperatures are frequently insulated to the best advantage by combining a high temperature insulation near the pipe with a moderate or low temperature insulation around it as an outer Table 6. kThermal Conductivity ( ) of Various Type Pipe Insulations for Medium and High Temperature Pipe2 Expressed in Btu per {hour) {square fool) {Fahrenheit degree . temperature difference per inch) Types of Insulating Materials Density Lb/Cu Ft Temp. Range FMean Temperature. Deg *of Accepted Use 100 200 300 400 500 85% Magnesia---Type.................... Corrugated Asbestos--Type 4 Ply per 1 in................................. 6 Ply per 1 in.....-....:..................... 8 Ply per 1 in................................ laminated Asbestos--Type ' (35-40 laminations per 1 in.)___ Mineral Wool--Type____ ___,,....... Diatomaceous Silica--Type.......... Brown Asbestos Fiber--Type.. 13-15 -11-13 15-17 18-20 30-35 10-15 25-30 13-15 Up to 600 F 0.41 0.45 0.48 0.52 Up to- 300 F Up to 300 F Up to 300 F 0.57 0.68 0.80 0.51 0.59 0.69 0.49 0.57 0.65 Up to 700 F Up to 800 F Up to 1900 F Up to 1200 F 0.39 0.44 0.49 0.54 0.40 0.45 0.50 0.55 0.63 0.66 0.69 0.72 6.75 0.34 0.39 0.44 0.49 0.54 Average values from various laboratories for insulating materials of various manufacturers. TEMP 01FF FROM PIPE TO ROOM, F DEG , . Fig. 1. Heat Loss Through 1 In. Thick 85 per cent Magnesia Type Covering . layer. By this method an efficient material may be used for each of the two temperature ranges encountered. In calculating the heat loss through such a combination the mean temperature of each layet must be determined along with the thickness of each. This is readily done in 518 CHAPTER 28 1946 Guide three or four calculations performed as a series of approximations in. which assumptions of thickness and mean temperature are adjusted.as indicated in the discussion which follows. In the case of a single thickness of pipe covering, the quantity of heat Pipe Insulation ' ~ ~ ' - -'____________ _______'- . '519 k = thermal conductivity of insulation, Btu per (hour) (square foot) (Fahrenheit' ' degree per inch). . . h = temperature of .inner surface of insulation, Fahrenheit degrees. ti - temperature of outer'surface of insulation, Fahrenheit degrees. ' It is convenient to work from the outer surface of the insulation, since the loss through the covering must be determined from the outer surface loss by means of surface loss curves such as given in Fig. 4. . Fig. 2. Heat Loss Through In. Thick 85 per cent Magnesia Type Covering transferred per square foot of outer surface of the insulation is given . by the equation: . '_ 'where k pi - U) rjloge --Tl ft) q0 = Btu per (hour) (square foot of outer surface of insulation). fi = outer radius of pipe or inner radius of insulation, inches. r- = outer radius of insulation, inches. ....TEMP DIFF FROM PIPE TO ROOM, F DEG Fig. 3. Heat Loss Through 2 In. Thick 85 per cent Magnesia Type Covering After the true heat loss is obtained, the loss per square foot of pipe surface can be calculated from the relationship: . . Si =_So (ri/n). where . - . Si = Btu per (hour) (square foot outer surface of pipe). , . . . The heat loss through two or more thicknesses of insulation applied to a pipe can be'calculated by means of the equation: 520 CHAPTER 28 1946 Guide where ` .. . r* = outer radius of second layer of insulation, inches. r8 * outer radius of last layer of insulation, inches. - The method of solving Equation 2, which is the most difficult of the two, is given in Example 3. * * Example 8. Compute the heat loss per linear foot of pipe surface per hour from a 6-in. pipe, insulated with a 3-in. thickness of diatomaceous silica, and a 2-in. thickness of 85 per cent magnesia. The pipe is operating at a temperature of 1200 F and is exposed to a room temperature of 80 F/ . Solution. In figuring the heat loss from Equation 2, it is necessary to first make an assumption for the outer surface temperature h and the temperature between the diatomaceous silica and 85 per cent magnesia insulation, so that the mean temperature of each material can be obtained and the thermal conductivity corresponding to the mean temperature of each material substituted in the formula. First assume an outer surface temperature of 140 F and a temperature of 570 F between the two materials corresponding to a mean temperature of (1200 + 570) 4- 2 or 885 F for the diatomaceous silica and (570 + 140) v 2 or 355 F for the 85 per cent magnesia insulation. The Table 7. Pipe Covering.Factors . Types of Insulating Materials Corrugated Asbestos--Type 4 Ply per 1 in... ...... _......................... 6 Ply per 1 in..................... ................. 8 Ply per 1 in........................... -.......... Laminated Asbestos--Type................ Mineral Wool--Type............................ Diatomaceous Silica--Type................ Brown Asbestos Fiber--Type. FTemperature Difference. Pipe to Air, Deg , 100 200 300 400 500 1.30 1.19 .1.15 0.96 0.98 1.37 0.86 1.36 1.42 1.23 1.19 1.27 1.23 0.98 1.00 1.00 1.02 1.36 1.35 0.88 0.91 1.02 1.05 1.35 0.93 1.04 1.07 1.34 0.96 conductivities of these two materials at mean temperatures of 885 and 355 F interpolated from Table 8 are 0.865 and 0.5 Btu respectively. These values are substituted in Equation 2 and a trial calculation made. For a nominal fcin. steel pipe ri = 3.312, rj = 6.312 and.r* = 8.312 then, 1200 - 140 1060 So ' 5101 6.312 __101 8.312 = 6.2 + 4.58 8 312 loge 012 8 312 loge 012 0.865 + 0.5 98.3 Btu. The temperature drop from the outer surface of the insulation to the surrounding-air for a heat loss of 98.3 Btu is found from Fig. 4 to be 57 FTor a 16-in. O.D. cylindrical surface, or 57 -j- 80 F room temperature = 137 F surface temperature. Since a surface temperature of 140 F was assumed, it is evident that a temperature closer to 137 F, or, for instance, 138 F should be used for recalculation: 2o 1200 - 138 6.2 + 4.58 98.4 Btu. Since the temperature drop through each material is equal to the heat flow times the actual resistance of each material the temperature drop through the diatomaceous silica is 98.4 X 6.2 = 610 F or the temperature between the-two insulating materials is (1200 -- 610) = 590 F. Since a temperature of 570 F between the two materials was assumed, it is obvious that a temperature closer to 590, or for instance 586 F may be selected. The mean temperatures of the two insulations corresponding to the new assumptions are (1200 + 586) 4- 2 = 893 and (586 + 138) 4- 2 = 362 and the inter polated conductivities corresponding to the new mean temperatures are 0.87 and 0.505. Pipe Insula tion 521 ..for the diatomaceous silica and. 85 per cent magnesia respectively. By substituting in Equation 2: , 1200 - 138 1062 - o 5.36 .2.29 6.16 + 4.53 99.3 Btu 0.87 + 0.505 Again referring to Fig. 4, it is seen that the temperature drop from the outer surface of the insulation to the surrounding air for a heat loss of 99.3 Btu = 38 F which cor responds to the surface temperature of 138 F last assumed. The temperature drop , through the diatomaceous silica is 99.3 X 6.16 = 612 F, corresponding to a temperature of 588 F between the two materials which checks very closely with the temperature of Fig. 4. Heat Loss from Canvas-Covered Cylindrical Surfaces of Various Diameters 585 F last assumed. The heat loss is therefore 99.3 X 8.312 4- 3.312-or 249 Btu per square foot of pipe surface. Since the surface area per linear foot of 6-in. pipe is 1.734 sq ft (Table 5), the heat loss per linear foot of pipe will be 249 X 1.734 = 432 Btu per hour. The rate of heat loss from a surface maintained at constant temperature is greatly increased by air circulation over the surface. In the case of well-insulated surfaces, the increases in losses due to air.velocity are very small as compared with increases from bare surfaces, because of the fact that air .flowing over the surface of the insulation can increase only the conductance of heat from surface to air, and cannot change the internal conductance of the insulation itself. - The maximum increase in heat loss . due to air velocity ranges from about 15 per cent in the case of 1-in. thick insulation, to about 5 per cent in the case of 3-in. thick insulation, 1 provided that the insulation is thoroughly sealed so that air can flow only over the surface. If the conditions are such that the air may'circulate through cracks and crevices in the insulation, the increases may be far 522 CHAPTER 28 -- \ ' 1946 Guide greater than those given. Therefore, it is essential that insulation be ' applied in such a manner that air circulation within it or between it and the pipe is avoided. ' Fig. 4 shows the loss of heat from canvas-covered, cylindrical surfaces of various outside diameters when the surface to air temperature difference is low. The data are from tests made at Mellon Institute. The frequent practice of omitting insulation.on that portion of a pipe which passes through a masonry wall or which may be in contact with other metals should be avoided. Physical contact between the pipe surface and other structural materials of high thermal conductivity will Table 8. Heat Gains for Insulated Cold Pipes Rates of heat.transmission given in Btu per (hour) (Fahrenheit degree temperature , difference between fluid in pipe and surrounding still air) . ' Based on materials having conductivity, k = 0.30 . Nominal Pips SlZB ' (Inches) )4 H 1 U4 2 2)4 3 3)4 4 5 6. 8 -to 12 Ice Water Thickness Bbinb Thickness Heavy Bbinb Thickness Thickness of Insulation (Inches) 1.5 1.6 1.6 1.6 1.5 1.5 1.5 1.5 1.51.7 1.7 1.7 ' 1.9 1.9 1.9 Btu Per Linear Foot 0.110 0.119 0.139 0.155 0.174 0.200 0.228 0.269 0.295 0.294 0.349 0.404 0.455 0.559 0.648 Btu PerSq Ft Pipe Surface 0.502 0.431 0.403 0.357 0.351 0.322 0.303 0.293 0.282 0.248 0.239 0.233 0.201 0.198 0.194 Thickness of . Insulation (Inches) 2.0 2.0 2.0 2.4 2.5 2.5 2.6 2.7 2.9 2.9 3.0 3.0 3.0 3.0 3.0 Btu Per .Linear Foot Btu Per. Sq Ft Pipe Surface Thickness . of Insulation (Inches) 0.098 0.446 0.111 0.405 0.124 0.352 0.131 0.300 0.134 ; 0.270 0.151 0.244 0.170 0.226 0.186 0.202 0.191 0.183 0.209 0.176 0.241 0.165 0.259 0.150 0.318 0.140 0.383 0.135 0.438 0.131 2.8 2.9 3.0 . 3.1 ' 3.2 . 3.3 ' 3.3 3.4 3.5 3.7 3.9 4.0 4.0 4.0 4.0 Btu Per Unear Foot 0.087 0.094 0.104 0.113 0.118 0.134 0.147 0.162 0.176 0.182 0.202 0.228 0.263 0.309 0.364 Btu Per Sq Ft .Pipe Surface 0.394 0.340 0.294 0.260 0.238 0,214 0.197 0.176 0.167 0.154 0.138 0.130 0.116 0.110 0.108 result in heat transfer much greater than that shown in' Tables 1 and 2 for transfer from bare pipe to air. \' The saving due to use of insulation on piping is illustrated in Example 4 . Example 4> - If the steam line given in Examples t and 2 is covered with I in. thick 85 per cent .magnesia, determine the resulting total annual loss through the insulation.* Also compute , the monetary value of the annual saying and' the percentage of saying over the heat loss from the bare pipe. , '. ' Solution. . By referring to Fig. 1, the coefficient for 1 in. magnesia on aV2-in. pipe is found to be 0.300 Btu per (hour) (linear foot of pipe), (degree temperature difference) at a temperature difference of 169.4 F. The total hourly loss per linear foot of pipe will then be 0.300 X 169.4 = 50.8 Btu. The total annual loss through the insulation = 50.8 X 165. (linear feet) X 4000 (hours) = 33,500 Mb. The annual bare pipe-loss as determined in the solution of Example 1 was found to be 181,600 Mb. The saving due * to insulation is then 181,600 r- 33,500. = 148,100 Mb per year. , -^ '' From the solution of Example 2, it was found that the heat.supplied to the system cost $0,804' per thousand Mb;- Therefore, the monetary value of the saving = 0,804 . (dollars) X 148.1 (thousand Mb). = $119.07, or 81,5 per cent of the cost when using uninsulated pipe. * .. ' - Pipe Insulation 523 , LOW TEMPERATURE PIPE INSULATION Surfaces maintained at temperatures lower than the surrounding a}r are insulated to reduce the flow of heat and to prevent condensation. The insulating material should absorb a minimum amount of mois ture, because the absorption of moisture substantially increases the conductivity of the material. This property is particularly important in- "Solve problems as indicated by dotted line, entering chart at lower left-hand scale. Fig. 5. Thickness of Pipe Insulation to Prevent Condensation on Outer Surface1 ' . the insulation of surfaces that are below the dew-point of the surrounding air. In such cases, due to vapor pressure difference, it is necessary to . . seal the surface of the insulating material against the penetration ofwater vapor which would condense within the material, causing a serious increase in heat flow, possible breakdown of the material, and corrosion of metal surfaces. An insulating material with a high degree of moisture; ' .absorption might pick up moisture before application and then, when the seal is in place and the temperature of the insulated surface reduced; release that moisture to the cold surface. . There are a number of methods.' of, producing vapor seals, some of which have been worked out by insula tion manufacturers to suit their products and others by applicators and 524 ' CHAPTER 28 1946 Guide . users. Unless time proven methods are known, specifications of insulation manufacturers should be obtained and followed carefully. The thickness of insulation required to prevent condensation on the' outer surface is that thickness which will raise the temperature of the outer surface of the insulation to a point slightly higher than the dew point of the surrounding vapor. The dew-point for various humidities, can be readily ascertained from a psychrometric chart. The: approximate required' thickness of insulation to prevent conden sation on pipes and flat metallic surfaces may be obtained from Fig. 5 in which a surface resistance of 0.606 corresponding to a film conductance of 1.65, was used in calculating the curves. This value provides a slight factor of safety and its use is known to give satisfactory field results. In using the chart it is advisable to specify the next thicker, rather than Table 9. Data for Estimating Requirements to Prevent Freezing of Water in Pipes with Surrounding Air at --18 F Nominal Pipe ` Sub (Inches) ` Number op Hours to Cool 42 F Water , . to Freezing Point Water Flow Required at 42 F to Prevent Freezing, Pounds per Linear Foot op Pipe per Hour .- . 2 h i m 2 3 4 S 6 8 10 12 0.42 0.83 1.40 1.94 3.25 4.55 5.92 , 7.35 10.05 13.00 15.80 Thickness of Insulation in Inches (Conductivity, k = 0.30) 3 4 2 '3 0.50 1.02 1.74 2.48 4.27 6.02 7.96 9.88 13.90 18.10 22120 ' 0.57 1.16 2.02 2.90 5.08 7.20 9.69 12.20 17.25 22.70 28.10 0.54 0.68 0.84 0.95 1.24 1.47 1.73 1.98 . 2.46 2.96 3.43 0.45 0.55 0.68 0.75 - 0.94 1.11 1.29 1.46 1.78 2.12 . 2.45 4 0.40 0.48 0.58 0.64 0.79 0.93 1.06 1.19 1.43 1.70 1.93 . .. the next thinner, commercial insulation in cases where an intermediate thickness is indicated. ' Heat gains for pipes insulated with a material having an installed conductivity of ,0.30 Btu per (square foot) (hour) (Fahrenheit degree per inch) are given in Table 8. This table may be used for any of the com mercial insulations offered for this purpose since they have conductivities very near the 0.3 value used. INSULATION OF PIPES TO PREVENT FREEZING ' If the surrounding air temperature remains sufficiently low for an ample period of time, insulation cannot prevent the freezing of still water, or of water flowing at such a velocity that the quantity of heat carried in the. water is not sufficient to take care of the heat losses which will result and cause the temperature of the water to be lowered to the freezing point. Insulation can materially prolong the time required for the water to give up its heat, and if the velocity of the water flowing in the pipe is main-, tained at a sufficiently high rate, freezing may be prevented. ` Table 9 may be used for making estimates of the thickness of insu' lation necessary to take care of still1 water in pipes at various water and surrounding air temperature conditions. Because of the damage-and1 Pipe Insulation 525 service interruptions which may result from frozen water in pipes, it' is essential that an efficient insulation be utilized. ' This table is based on the use of a material having a conductivity of 0.30. The initial water tem perature is assumed to be 10 F above, and the surrounding air temperature 50 F below the freezing point of water (temperature difference, 60 F). The last column of Table 9 gives the minimum quantity of water at initial temperature of 42 F which should be supplied every hour for each . linear foot of pipe, in order to prevent the temperature of the water from being lowered to the freezing point. The weights given in this column should be multiplied by the total length of the exposed pipe line expressed in feet. As an additional factor of safety, and in order to provide against temporary reductions in flow occasioned by reduced pressure, it is ad visable to double the rates of flow listed in the table. It must be empha-. sized that the flow rates and periods of time designated apply only for the conditions stated. To estimate for other service conditions the following method of procedure may be used. . If water enters the pipe at 52 F instead of 42 F, the time required to cool it to the freezing point will be prolonged to twice that given in the table, or the rate of flow of-water may be reduced so that the quantity required will be one-half that shown in the last column of Table 9. However, if the water enters the pipe at 34 F it will be cooled to 32 F in one-fifth of the time given in the table. It will then be necessary to increase the rate of flow so that five times the specified quantity of water ' .will have to be supplied-in order to prevent freezing. If the minimum air temperature is -- 38 F (temperature difference 80 F) instead of --18 F, the time required to cool the water to the freezing point will be 60/80 of the time given in the table, or the necessary quantity of water to be supplied will be 80/60 of that given. ,, In making calculations to arrive at the values given in Table 9, the loss of heat stored in the insulation, the effect of a varying temperature difference due to the cooling of pipe and water, and the resistance of the-outer surface of the insulation to the transfer of heat to the air have , all been neglected. When these factors enter into the computations it is necessary to enlarge the factor of safety. Also as stated, the time shown in the table is. that required to lower the water to the freezing point. A . longer period would be required to freeze the water but the danger point is reached when freezing starts. The flow of water will stop and the entire line will be in danger as soon as the water freezes across the section of the pipe at any point. . When water must remain stationary longer than the times designated ' in Table 9, the only safe way to insure against freezing is to install a steam or hot water line or to place an electric resistance heater along the side of the exposed water line: The heating system and the water line are then insulated so that the heat losses from the heating system are not excessive, and the heating effect is concentrated against the water pipe where it is needed. For this form of protection 2 in. of an efficient insu lation may be applied. , .. ECONOMICAL THICKNESS OF PIPE INSULATION The thicknesses of insulation which ordinarily are used for various temperature conditions are given in Table 10. Where a thorough analysis of economic thickness is desired this may be accomplished through the ' use of the chart. Fig. 6. ' - 526 CHAPTER 28 1946 Guide -The dotted line,on the chart illustrates its use in solving a typical example. In using the chart, start with- the scale at the left bottom margin representing the given number of hours of operation per year; then proceed vertically to the line representing the given value of heat;, thence horizontally to the right, to the line representing the given tem perature difference; thence vertically to the line representing the con ductivity of the given material; thence horizontally, to the left, to the line representing the given discount on that material; thence vertically to the curve representing the required per cent return on the investment; thence horizontally to the right, to the curve representing the given pipe size; thence vertically to-the scale at the top right margin where the economical thickness may be.read off directly. . UNDERGROUND PIPE INSULATION Underground steam distribution lines are carried in protective struc tures of various types, sizes and shapes (See Chapter 29). Detailed data Table 10. Thicknesses of Pipe Insulation Ordinarily Used IndoorS3 8nui Pressure Pbig - ob Condition 0 to 25 25 to 100 100 to 200 . Low Superheat Medium Superheat High Superheat Btbim Temperature Fahrenheit Degress 212 to 267 267 to 338 338 to 388 388 to 500 500 to 600 600 to 700 ` Thickness o> Insulation Hpes Larger Tnan 4 Cl 1 in. V/i in.' 2 in. 2)4 in. 3 in. 3*4 in. Pipes 2 In. to 4 in. . 1 in. 1 in. . -1*4 in. . 2 in. 2>4 in. 3vin. ' Pipes H In* to 1H In- 1 in. ' 1 in. 1 in. lyi'm. . 2 in. 2 in. All piping located outdoors or exposed to weather is ordinarily insulated to a thickness H greater than shown in this table, and covered with a waterproof jacket. -. on commonly used forms of tunnels and conduit systems have been published by the National District Heating Association 2. Pipes in tunnels are covered with sectional insulation to provide maximum thermal efficiency and are also finished with good mechanical, protection in the form of metal or waterproofing membrane outer jackets. In some instances, where actual submersion of hot lines may occur it has , been found good practice to firmly secure the covering with corrosion resistant wire, then sew on. a wire-inserted asbestos fabric jacket with wire. , This jacket is.porous. The principle of withstanding submersion is that water may enter as water, then actually boil at the pipe surfaces and escape as steam without rupturing the insulation or jacket. Conduit systems are in more general use than tunnels. Pipes carried in conduits may be insulated with sectional insulation; however, the more usual practice is to fill the entire section of the conduit around the pipes withhigh quality, loose insulating material. The insulation must be kept dry , at all times, and for this purpose effective waterproofing membranes . enclose the insulation. A drainage system is also provided to divert water which may tend to enter the conduit. . . The economical thickness of insulation for underground work is difficult to determine accurately due to the many variables which, have to be considered. As a result of theories' previously.developed, together with Pipe Insulation 527 ' (L. B.,McMillan,\Proc. National District Heating Association, Vol. 18.- p. 138). Fig. 6. Chart for Determining Economical Thickness of Pipe Insulation 528 CHAPTER 28 1946 Guide, Table 11. Thickness of Loose Insulation foe Use as Fill in Underground Conduit Systems Stham Pressure ob Condition &TEAB Temperature Degrees Minimum Thickness or Insulation in Inches - , Steam Lines Return Lines Pipes Less Pipes 4 la. Pipes Larger Pipes Less Pipes 4 In. than 4 In. to 10 la: than 12 In. than 4 In. and Larger Minimum Distance Between and Return ; Hot Water, or 0 to 25 212 to 267 ix 2 2X ix m i - 25 to 125 267 to 352 2 2X 3 IX IX IX Above 125, or . superheat 352 to 500 2X 3 3X ix IX IX, other experimental data which have been presented, the usual endeavor is to secure not less than 90 per.cent efficiency for underground piping. Table 11 can be used as a guide in arriving at the minimum thickness of loose insulation fills to use for laying out conduit systems. Other factors such as the number of pipes and their combination of sizes, as well as the standard conduit sizes, are primary controlling factors in the amount and thickness of insulation for use. ,' ' When sectional insulation is applied to lines in tunnels or conduits, usual practice is to apply the most efficient materials in. less in thick ness than that determined by the use of Fig. 6. The data in Fig. 6 are based on conditions of insulation exposed to the air, whereas normal ground temperature is substituted for air temperature in determining the tem perature difference for use with the chart when applying it for under ground pipe line'estimates. . * REFERENCES . *--Heat Loss from Copper Piping, by R. H. Heilman (Heating, Piping and Air Conditioning, September, 1933, p. 458). . 2--Handbook of the National District Heating Association, Second Edition, 1932. ' '' *--Theory of Heat Losses from Pipes Buried in the Ground, by J. R. Allen (A.S.H.V.E..-Transactions, Vol. 26, 1920, p. 335). . ' . .- CHAPTER 29 ^)iitrict ^kteatin. f Steam Distribution Piping, Selection of Pipe Sizes, Conduits for Piping, Pipe Tunnels, Overhead Distribution, Inside Piping,' Fluid Meters and Metering, Steam Requirements, Rates, Utilization, Automatic Temperature Control THOSE phases of district heating which frequently fall within the province of the heating engineer are outlined here with data and . information for solving incidental problems in connection with institutions and factories. Some data are included to cover the piping peculiar to heating systems which are to be supplied with purchased, steam. A com plete district heating installation should not be attempted' without a . thorough study of the entire problem by 'men competent and experienced in that industry. . STEAM DISTRIBUTION PIPING The methods used in district heating work for the distribution of steam are applicable to any problem involving the supply of steam to a group of buildings. The first step is to establish the route of the pipes, and in this' matter the local conditions so fully control the layout that little can be said regarding it: . ~ ' -. ". Having established the route of the pipes, the next step is to calculate the pipe sizes. In district heating work it is common practice to design the piping system on the basis of pressure drop. The initial pressure and the`minimum permissible terminal pressure are specified and the pipe sizes are so chosen that the required amount of steam, with suitable allowances for future increases, will be transmitted without exceeding this pressure drop. The steam velocity is therefore.almost disregarded and may reach a very high figure. Velocities of 35,000 fpm are not con sidered high. By the use of this method the pipe sizes are kept to a _ minimum with consequent savings in investment. The steam flowing through any section of the piping can be computed from a study of the requirements of the several buildings served. In general a condensation rate of 0.25 lb per (hour) (square foot of equiva lent heating surface) is a safe figure. This allows for line condensation which, however, is a small part of the total at times of maximum load. Miscellaneous steam requirements such as laundry, cooking, or process should be individually calculated. ` The steam requirements for water heating should be taken into account, but in most types of buildings this load will be relatively small compared . with the heating load and will seldom occur at the time of the heating peak. Unusual features such as large heaters for swimming pools should not be overlooked. '. The pressure at which the steam is to be distributed will depend upon. (1) boiler pressure, (2) whether exhaust or live steam, (3) pressure require ments of apparatus to be served. If steam has been passed through electrical generating units, the pressure will be considerably lower- than if ' live steam, direct from the boilers, is used. The advantages of low pressure distribution (2 to 30 psi) are (1) smaller heat loss per square foot of pipe surface, (2) less trouble with traps and' valves, (3) simpler problems in pressure reduction at the buildings, and 529 . 530 CHAPTER 29 1946 Guide , (4) general- reduction in maintenance costs. With distribution pressures not exceeding 40 psi there is little danger even if the full distribution pressure should build up in the radiators through the faulty operation of a reducing valve; but with pressures higher than 50 psi a second reducing valve or'some form of emergency relief is usually desirable to prevent ' excessive pressures in the radiators; .. ' The advantages of high pressure distribution are (1) smaller pipe sizes and (2) greater adaptability of the steam to various operations other than . Fig. 1. Construction Details of Conduits Commonly Used building heating, (3) wider flexibility as to allowance for maximum pressure drop. . .. ' ' The different kinds of apparatus which frequently must be served require various minimum pressures. Kitchen equipment requires from 5 to 15 psi, the higher pressures being necessary for apparatus in which water is boiled, such as stock kettles and coffee urns. An increased amount of heating surface, which is easily obtained in some kinds of apparatus, results in.quicker and more satisfactory operation at low pressures. For laundry equipment, particularly the mangle, a pressure of 75 psi is usually demanded although 30 psi is sufficient if the flat work ironer is equipped with a large number of/rolls and if a slower rate of . operation is permissible. Pressing machines and hospital sterilizers require about 50 psi. Where pressures are not as high as desired higher pressures can be obtained by a steam compressor. . District Heating 531 PIPE SIZES . The lengths of pipe, steam quantities, and initial and terminal pressures having been chosen, the pipe sizes can readily, be calculated by means of Babcock's pressure drop formula: . P = 0.0000000367 (1 + where '- P = loss in pressure in pounds. D = inside diameter of pipe in inches. L = length of pipe in feet. d = weight of 1 cu ft of steam. W -- pounds of steam per hour. - ' , . .. Numerical values of the various factors are given in Table 1, Chapter 23. CONDUITS FOR PIPING Conduits for steam pipes buried underground should be reasonably waterproof, able to withstand earth loads and to take care of the expan sion and contraction of the piping without strain or stress on the couplings, or without affecting the insulation or conduit. Expansion of the piping must be carefully controlled by means of anchors and expansion joints or bends so that the pipes can never come in contact with the cbnduit. Anchors can be anchor fittings or U-shaped. steel straps which partially encircle the pipes and are firmly bolted to a short length of structural or cast steel set in. concrete. In general, cast steel is preferable to struc tural steel. . .' In laying out underground conduits the following points should be borne in mind: . X. The depth of the buried-conduit should be kept at a minimum. Excavation costs are a large factor in the total cost. -- 2. An expansion joint, offset, or bend should be placed between each two anchors." Advantage should.be taken of the flexibility of piping to. absorb expansion wherever possible. Information on provisions for expansion will be found in Chapter 27. 3. A proper hydrostatic test should be made on the assembled line before the insula tion and the top of the conduit are applied. The hydrostatic test pressure should be one and one-half times the maximum service pressure and it should be held for a period of at least two hours without evidence of leakage. .. There are ma.ny types of conduits; some of which are manufactured products and some of which are built in the field. . Some of the more common forms are illustrated in Fig. 1. .' The conduit (A) is of a wood casing construction which has been widely, used in the past. The wood casing is segmented, lined with tin, and bound with wire: The outside of the conduit is coated with asphaltum. It is not suitable for high temperatures or poorly drained soils. . - In Fig. 1 .(B), (C), (D), (H) and (I)-are patented forms of conduits.; The insulation is sometimes a loose filler packed into the conduit. Con duits (H).and (I) are prefabricated. Both of these conduits are enclosed in metal jackets. , At (G) and (E) are shown two tile conduits using sectional insulation. In these particular designs the space' surrounding the pipe is filled par- 532, ' CHAPTER 29 1946 Guide tially or wholly with a loose insulating material. The addition of this loose insulating material to the sectional insulation is, of course, optional and is justified only where high pressure steam is used. ' .' (E) and (F) are conduits used by two district heating companies, and have the advantage of being constructed of common materials. Conduit (G) is of cast-iron construction, assembled with lead joints and is water-tight, if properly laid. It is obviously expensive and is justified only in exceptional cases. . Since it is difficult to make a concrete or masonry conduit absolutely water-tight, provision should be made for some seepage. The pipe should Fig. 2. Connections for Reducing Valve Without Bypass Fig. 3. Connections for Reducing Valve with Bypass be protected by . a waterproof jacket over the insulation and the seepage drained from the inside of the conduit. . . Underdrainage of the conduit is generally provided for by a tile drain laid in crushed stone or gravel underneath the conduit. The. tile under drain should be carried to the sewer or some other drainage point. , Manholes are required at intervals for access to valves, traps, and some types of expansion joints. ." Where steam and return piping are installed in the same conduit, the return piping usually follows the same grade as the steam piping. In general, the condensation is pumped back under pressure. PIPE TUNNELS Where steam heating lines are installed in tunnels large enough to provide walking space, the pipes are supported by means of hangers or District Heating 533 roller frames on brackets or frame racks at the side or sides of the tunnel. The pipes are insulated with' sectional pipe insulation over which is placed a sewed-on, painted canvas jacket or a jacket of asphalt-saturated asbestos water-proofing felt. The tunnel itself is usually built of concrete or brick and water-proofed on the outside with membrane water-proofing. Because of their relatively high first cost as compared with smaller conduits, walking tunnels are sometimes omitted along heating lines unless they are required to accommodate miscellaneous other services or provide underground passage between buildings. . OVERHEAD DISTRIBUTION In some industrial and institutional applications, the distribution piping may be installed, entirely or in part, above ground. This method Pressure reducing valve Fig. 4. Steam Supply Connection when Using Two Reducing Valves - of construction has the advantage of requiring no excavation and.being easily maintained. INSIDE PIPING Figs. 2 and 3 show typical service connections used for low pressure steam service. . Fig. 2 shows installation of a reducing valve without a bypass, which is usually omitted in the case of smaller size valves. Fig. 3 illustrates the. use of a reducing valve,, with a bypass which is generally provided for larger installations. This latter construction permits the operation of the line in case of failure in' the reducing valve. In the smaller sizes, the reducing valve can be removed, a filler installed, arid the house valve used to throttle the flow of. steairi until repairs are made. -- > Fig. 4 shows a typical iristallation used for high pressure steam service1. The first reducing valve effects the initial pressure reduction. The second reducing valve reduces the steam pressure to that required; - 1 Most district heating companies enforce certain regulations regarding the consumer's installation, partly to safeguard their own interests but principally to insure satisfactory and economical service to the consumer. There are certain fundamental principles that should be followed in the design of a building heating system whifch is to be supplied from street mains. Although some of these apply to any building, they have been demonstrated to be especially important when steam is purchased. 534 CHAPTER 29 1946 Guide . 1. Provision should be made for conveniently shutting off the steam supply at night and at other times when heat is not needed. . It has been thoroughly demonstrated that a considerable amount of heat can. be saved by shutting off steam at night. Although there is, in some cases, an increased consumption of heat when steam is again turned on in the morning, there is a large net saving which may be explained by the fact that the lower inside temperature maintained during the night obviously results in lower heat loss from the building, and less heat need therefore be supplied. . Steam can be entirely shut off at night in most buildings even in .very cold weather without endangering plumbing. It is necessary, however, to have an ample ampunt'of ' heating surface so that the building caii be quickly warmed in the morning. Where the hours of occupancy differ in various parts of the building, it is good practice to install separate supply pipes to the. different parts. For example, in an office building with stores or restaurants on the first floor which are open in the evening, a separate main supplying the first floor will permit the steam to be shut off from the remainder of the District Heating 535 ment of district heating as any.-.other one thing. Meters are classified into two groups: Quantity Meters and Rale of Flow.Meters. Quantify Meters . ' ' ." ' The one type of quantity meter used is the condensation meter, which may be of the tilting bucket or revolving drum type. . The condensation meter is a popular type for use on small and medium sized installations, where all the condensate can be brought to a common point for metering purposes. Its simplicity of design,, ease in testing, accuracy at all loads, low.cost, and.adaptability to low pressure distribu tion has made it standard equipment with many heating companies. Condensation meters should not be operated under pressure; they are made for either gravity or vacuum installations. Where bucket traps are used, a vented receiver is essential ahead of the meter. Where con tinuous flow traps are used, a vented receiver is not necessary, but is Fig. 5. Method of Installing a Water Heater and Economizer in a . Gravity Heating System building in the late,afternoon. The division of the building into zones each with a separately controlled heat supply is sometimes desirable, as it permits the heat to be adjusted according to variations in sunshine and wind. '. Residual heat in the condensate should be salvaged. . This heat.may be.salvaged by means of a cooling coil, or as is more frequently done, by a water heating economizer (see Fig. 5) which preheatssthe hot water supply to the building. The condensation from the heating system, after leaving the trap, passes through the economizer. The supply to the hot' water heater passes through the economizer, ab sorbing heat from the condensate. If the hot water system in the building is of the recirculating type, the recirculating connection should be tied in between the economizer and the water heater proper, not at the economizer inlet, because the recirculated hot water is itself at a high temperature. . Because of.the lack of coincidence between the heating system load and the hot water demand, a greater amount of heat can be extracted from the condensate if storage capa city is provided for the preheated water. Frequently a type of economizer is used in which the coils are submerged in a storage tank. S. Heal supply should be graduated according to variations in the outside temperature. .. . The maximum in economical operation and satisfactory heating can only be obtained by the use of some automatic temperature control system. . . The perfection of fluid meters has contributed as' much to the advance- Fig. 6! Gravity Installation for Condensation Meter . Using Vented Receivers desirable. Fig. 6 illustrates a gravity condensation meter installation using a vented receiver. / Rate of Flow or Flow Meters . .... Flow meters used for district heating work are of three types: Area Meters, Head Meters and. Velocity Meters. . . Area meters are those, in the operation of which, a variation in the cross-section of stream under constant head is used as an indication of the rate of flow. A tapered plug is suspended in an orifice and moves axially with the flow, which is vertically upward. The weight of the plug provides a definite pressure differential, and the plug floats at such a height as will provide enough orifice area to pass the flow at the pressure difference. The position of the plug'is transmitted by means of a lever and pencil and records the flow on a graduated strip chart. Head meters are those in which the stream of fluid creates a difference of pressure, or differential head. This head is created by an orifice, Venturi tube, flow nozzle', of Pitot tube and will depend upon the velocity and density of the fluid. , ., .The secondary element must contain a differential pressure gage, which will translate the pressure difference into rate of flow or total flow. This mechanism may be either mechanical or electrical. The electric, flow , meter has the advantage of being able to locate the instruments at some distance from the primary element., 536 CHAPTER 29 1946 Guide Fig. 7 is a typical example of an orifice-type meter installation. A few general points to be considered in installing a meter of this type are: (1) It is desirable to place the differential medium in a horizontal pipe in preference to a vertical one, where either location is available. (2) Reservoirs should always be on_the same level and installed in accor dance with the instructions of the meter company. (3) The meter body should be placed at a lower level than that of the pressure differential medium. Special instructions are furnished where the meter body is above. (4) Meter piping should be kept free from leaks. (5) Sludge should not be permitted to collect in the meter body. (6) The meter body and meter piping should be kept above freezing temperatures. (7) It is best not to connect a meter body to more than one service. (8) Special instructions are furnished for metering a turbulent or pulsating flow. Fig. 7. Orifice Meter Steam Supply Connection Velocity meters are those in which the primary element is some device that is kept in continual rotation by the linear motion of the stream. The secondary element is, essentially, a revolution counter. The primary and secondary elements are combined into one unit. - For steam metering, the shunt meter is an example of the velocity type. This unit is connected directly in 2, 3 and 4 in. pipe lines. Larger size mains are metered by installing a 2 in. meter in a bypass with a restricting orifice in the main line. ' ' Selection of Meter- ,. In selecting a meter for a particular installation, the number of different makes and types of meters suitable for the job is usually limited by one or more-of the following considerations: (1) Its use in a new or an old installation. (2) Method to be used in charging for the service. (3)' Location of'the meter. (4) Large or small quantity to be measured. . (5) Temporary or permanent installation. (6) Cleanliness of the fluid to be measured. (7) Temperature of . the fluid to be measured. . (8) ' Accuracy expected. (9) Nature of flow: turbulent, pulsating, or steady. District Heating 537 (10) Cost.- a. purchase price, b. installation cost, c. calibration cost, d. maintenance cost. (11) Servicing facilities of the manufacturer. (12) Pressure at which fluid is to be metered. (13) Type of record desired as to indicating, recording or totalizing. (14) Stocking of repair parts. (15) Use of open jets where steam is to be metered. (16) Metering to be done by one meter or by a combination of meters. (17) Use as a check meter. (18) Its facilities for determining or recording information other than flow. . STEAM REQUIREMENTS Methods of estimating steam requirements for heating various types of buildings are given in Chapter 20. Table 7 in Chapter 20 represents information obtained from all sections of the United States, and the group of buildings from which the infor mation was taken represents a cross-section of all types of heating systems. Steam requirements for water heating can be satisfactorily estimated by using a consumption of 0.0025 lb per (day) (cubic foot of heated space) .for office buildings, without restaurants, and 0.0065 lb per (day) (cubic foot of heated space) for apartment buildings.. . Complete information on water heating requirements is given in Chapter 50! Additional data on steam requirements of various types of buildings in a number of cities may be found in the Handbook of the National District Heating Association.' - RATES Fundamentally, district heating rates are based upon the same princi ples as those recognized in the electric light and power industry, the main object being a reasonable return on the investment. However, there are other requirements to be met; the rate for each class of service should be based upon the cost to the utility company of the service supplied and upon the value of the service to the consumer, and it must be between these two limits. District heating rates should be designed to produce a sufficient return on the investment regardless of weather conditions, although existing rate schedules do not . conform to this principle. Lastly, the rate schedule must be reasonably simple and understandable. Glossary of Rate' Terms -. Load Factor. The ratio, in per cent, of the average hourly load to the maximum hourly load.. This is usually based on a one year period but may be applied to any specified period. Demand Factor. The relation between the connected radiator surface or required radiator surface and the demand of the particular installation. It varies from 0.25 to 0.3 lb per (hour) (square foot of surface). ' . Diversity Factor. The ratio of the sum of the individual demands of a number of buildings to the actual composite demand of the group. Types of Rates 1. Flat Rates. a. Radiator surface charge. Obsolescent. 2. Meter Rates. a. Straight-line. - . b. Step. Obsolescent. c. Block. . (a) Class rates. . . .- . - ., ., 538 CHAPTER 29 1946 'Guide Straight-Line Meter, Rate. The price charged per unit is constant, and the consumer pays in direct proportion to his consumption without regard to the difference in costs of . supplying the individual customers. . Block Meter Rate. The pounds of steam-consumed by a customer are divided into blocks of thousands of pounds each, and lower rates are charged for each successive block'consumed. This type of charge predominates in steam heating rate schedules for it has the advantage of proportioning the bill according to the consumption and the cost of service. It has the disadvantage of not discriminating between customers having a high load factor (relatively low demand) and those having a low load factor (relatively ' High demand). The utility company must maintain sufficient capacity to serve the high demand customers and the cost of the increased plant investment is divided equally among the users, so the high demand customers are benefited at the expense of the others. *. 3. Demand Rates. ., a. Flat demand. b. Wright. . c. Hopkinson. ` ' d. Doherty (or Three charge).. . .' . . Demand Rates. These refer to any method of charge based on a measured maximum load during a specified period of time. '. . The fiat demand rate is usually expressed in dollars per thousand pounds of demand per month or per annum. It is based on the size of a customer's, installation, and is seldom used except where a meter is not practicable. ' , ! .. ~ The Wright demand rate is similar in calculation to the block rate except that it is ex pressed in terms of hours' use. of the maximum demand. It is seldom used but forms the basis for other forms of rates. . . The Hopkinson demand rate is divided into two elements: . (a) A charge based upon the demand, either estimated or measured. (6) A charge based upon the amount of steam consumed; * ` . This rate may be modified by dividing the quantities of steam demanded and con sumed into blocks charged for at different rates.. ,, The Doherty rate is divided into three elements: (a) A charge based upon demand. ' (b) A charge based upon steam consumed. - (c) A customer charge. . * . . . . , . In the Hopkinson rate, .the last two elements are combined into one element. Demand rates are comparatively new and are.iiot yet widely used; though they are equitable and competitive they are difficult for the average layman to understand. They are of benefit to utility companies and to consumers because the investment and `Operating costs can be divided to suit the particular circumstances into demand, customer, and consumption groups through the use of some modification of the Hopkin- son rate. Demand rates are an advantage to the customer in that the use of such a rate reduces the rate per thousand pounds to the long-hour user. - ' Fuel Price Surcharge. It is usually desirable to establish a rate upon, a specified basic cost of fuel to the utility, company. . Where there are wide variations in the price of fuel, it is also desirable to add a definite charge per thousand pounds of steam sold for each increment of increase in the price of fuel. This surcharge automatically compensates for the variations without necessitating frequent changing of the whole rate structure. ' - Some utility companies include a labor surcharge as well as a coal. . surcharge. - District Heating 539 UTILIZATION Considerable savings can be made by the proper and intelligent oper-' ation of heating systems. It should be borne in mind that a heating system is designed to heat a building to 70 F inside when the outside temperature is at its lowest point for that particular locality! There is a tendency to overheat the building at any time the outside temperature is above the design temperature unless some method of regulation is used, either automatic or manual. '. The general rules for economical operation.2 are as follows: 1. Reduce the heat losses from the building to a minimum. . a. Weatherstrip all windows, and caulk all window frames. . . . b. Provide revolving or vestibule doors on all entrances. Separate shipping and. receiving rooms from the remainder of the building by partitions so that the large doors will not ventilate the entire building. ' c. Eliminate all unnecessary ventilation. Ventilating equipment is usually sized . to meet extreme requirements. In a theater or auditorium, do not supply enough ventilation for an audience of 2000 when there are only 200 present. 2. Limit the hours of heating to those in which the required temperature is necessary. . a. Determine the hours that heating is required and see that steam is shut off for ' the maximum time when not required, such as nights, Sundays, and holidays. . b. Shut stc&m off entirely in unoccupied sections of the building, taking care to avoid freezing plumbing. . / c. Install separate lines for those parts of the building that require long-hour or 24-hour heating. This is much cheaper than heating the entire building. . . d. Control the heat supplied to.water storage tanks located on or above the roof. Such tanks require heat to prevent freezing when the outdoor temperature is below 32 F. . '. 3. Regulate the amount of heat so as to prevent overheating and to maintain uniform temperatures during the'hours of occupancy. a. Determine the temperature required for the occupancy of a building. Do not . heat a storage garage or a furniture warehouse to the temperature required-in a hospital ward. ., - . b. Shut off steam during the day whenever possible. An automatic control will ' do this, but it can be done by hand, with good results. . c.. Provide some good means of temperature control. 4. See that the heal input is properly balanced tkfoughout the building. . ; a. See that the entire heating system responds rapidly when steam is turned on. Locate ancl eliminate the cause of any sluggish circulation. Balance the radia- . tion, provide adequate air elimination, and correct any trapped run-outs to provide quick system drainage. .; b. Place the radiation near the outside walls under the windows or where the exposure occurs, if possible. *. ' 1 c. Do not obstruct radiators or prevent the free circulation of air around, them; to do so seriously reduces the heating capacity of a radiator. . 5. Keep all heating equipment in first class condition. . . a. Keep the system in good repair. This applies to all traps, valves, vents, steam and return piping,.vacuum pumps, and temperature control apparatus. ,' In a vacuum system, maintain the degree of vacuum recommended by- the , control manufacturer. If this is not possible, locate and eliminate all ieaks. c. Insulate all steam pipes not used as heating surface. . 6. Arrange the heating system to obtain from it the highest possible efficiency. -' x a.. Locate all valves and controls so as to be convenient and accessible. It is only human nature to delay, or avoid doing that which is unnecessarily inconvenient. 6. Investigate every complaint of "No Heat;" find the cause and correct it. Do not overheat an entire building to correct a local condition. . c. Extract the heat in the condensate for heating water or for some other useful purpose. ' . 540 CHAPTER 29 1946 Guide 7. Make a study of the heating system and healing requirements. , a. Provide thermometers and recording pressure gages so that the heating system may be operated with full knowledge of what is being accomplished. ' b. Keep daily consumption records and check against the theoretical requirements. c. Study the system and understand its functions and its operations. AUTOMATIC TEMPERATURE CONTROL As stated in Chapter 34, Automatic Control, properly applied to heating, ventilating and air conditioning systems, makes possible the maintenance of desired conditions with maximum operating economy.. The use of ade quate temperature control provides more healthful, comfortable, and efficient working conditions in buildings. - . There' are three general means of obtaining centralized control of heat output of radiators. ' 1. Controlling the rate of steam flow into the radiators.- This is accomplished by equipping the radiator inlets with orifices and controlling the flow of steam through them into the radiator by controlling the difference in pressure between the supply and return. 2. Controlling the temperature of steam in the radiators by varying its pressure. This involves the use of high vacuums to obtain low steam temperatures. This must be sup plemented by some other type of control for low heat output. f 3. Controlling the length of time steam flows into the radiators by admitting steam to a heating system intermittently and varying the length of the on and off periods. Two types of controls are used. (1) A clock control providing on and off settings of various lengths, which can be changed in accordance with outside temperatures. In most cases these changes are made automatically, by means of a thermostatic bulb, placed out doors. (2) A control, having an outdoor bulb and a bulb attached to the radiator, which varies the length and frequency of the on intervals in such a way that the radiator tem perature is varied according to the outside temperature. In'some cases heat supply is controlled by combinations of the three methods described. - Before installing any type of modern temperature control equipment, it is necessary to see that the heating system is put in good operating condition. In general, the heating system in a building is not given the attention that other mechanical equipment is given because it will con tinue to function, after a fashion, even though changes in piping, location. of radiation, settlement of piping, and the normal wear and tear or other . changes have taken place. Because of this depreciation of the system, operation becomes more and more costly and parts of the building have to be greatly overheated in order to prevent underheating in other parts. Vents, traps, vacuum pumps, and valves should be given a careful in spection and replaced or repaired if required. The piping should be of adequate size and graded properly. The return piping should be in spected, and any pockets or lifts removed and properly vented. These inspections and repairs are not costly and may prevent a much greater outlay in future years. In most cities district heating companies will be willing to make a survey of heating systems and. offer recommendations in regard to operation and changes in piping layout. The selection of control equipment depends upon the type and size of building and the degree of saving which may be obtainable. , REFERENCES 1--Code for Pressure Piping, B 31>1, 1942, American Standards Association, Paragraph 408, pi 115. 2--Principles of Economical Heating. National Association of Building Owners and Managers. CHAPTER 30: ^iectric ^JSeatinfy Resistors, Heating Elements, Electric Heaters, Unit Heaters, Central Fan Heating, Electric Boilers, Electric Hot Water ' Heating, Heating Domestic Water Supply, Reversed Cycle Refrigeration, Auxiliary Electric Heating, Control, Calcu lating Capacities, Radiant Drying, Induction and Electro- * . static Heating, Power Problems . ELECTRIC heating is steadily assuming a more important place in heating, ventilating-and air conditioning installations because .it is flexible, clean, safe, convenient and easy to control. It has many basic principles in common with fuel heating,, but there are also important differences. When heat is delivered by wire, no combustion process is necessary, either at a central plant or at the individual room units. The output of an electric heater is a fixed constant, unaffected by the tem perature of the surrounding air and it follows that the total load on an electric heating system is the total wattage of connected electric heaters, regardless of weather conditions. The main obstacle to the more general adoption of electric heating for buildings is the cost of the electricity itself. All heat is a form of energy. Fuels hold stored chemical .energy which is released into heat by combustion. Electrical power is a form of energy which can'be released into heat by passing it through a resisting material. Both fuel and electric heating have two divisions: first, the conversion Of energy into heat; second, the distribution and practical use of the heat after it is produced. . ' In converting the chemical energy of fuels into heat by combustion, there is necessarily a considerable variation in thermal efficiency. This is not true, however, when converting electric power into heat, as 100 per cent of the energy applied to the resistor is always transformed into heat. In electric heating practice no concern need be given to efficiencies of heat production, but rather to efficiencies of heat utilization. The, problem is to distribute the electrically produced heat units in such manner as to obtain conditions of maximum comfort with the minimum consumption of electricity. " DEFINITIONS Definitions of general terms used in fuel heating are given in Chapter, 1. Terms which apply particularly to electric heating are as follows: Electric Resistor: A material used to produce heat by passing an electric current through it. Electric Heating Element: A unit assembly consisting of a resistor, insulated sup ports, and terminals for connecting the resistor to electric power. . Electric Heater: A complete assembly of heating elements with their enclosure, ready for installation in service. RESISTORS AND HEATING ELEMENTS Solids, liquids, and gases may be used as resistors, but most com mercial electric heating elements have solid resistors, such as metal alloys, and non-metallic compounds containing carbon. In some types of" electric boilers, water forms the resistor which is heated by an alternatingcurrent'of electricity'passing through it. One of the more common 541 542 CHAPTER 30 1946 Guide resistors is nickel-chromium wire or ribbon which, in order to avoid oxidation, contains practically no iron. - Commercial electric heating elements are made in many types. Some ' have resistors exposed to the air being heated. The resistors may be coils of wire or metal ribbon, supported by refractory insulation, or they may be non-metallic rods, mounted on insulators. This type of element is used extensively for operation at high temperatures when radiant heat is. desired, also at low temperatures for convection and fan circulation heating, especially in large installations. - , Some elements have metallic resistors embedded in a refractory insu lating material, encased in a protective sheath of metal. Fins or extended surfaces may be used to add heat-dissipating area. Elements are made in many forms, such as strips, rings, plates and tubes. Strip elements are used for clamping to surfaces requiring heat by conduction, and in some, types of convection air heaters. Ring and plate elements are used in electric ranges, waffle irons, and in many small air heaters. Tubular elements may be immersed in liquids, cast into metal, and, when formed into coils, used in electric ranges and air heaters." Cloth fabrics woven from flexible resistor wires and asbestos thread are used for many low temperature purposes such, as heating pads and aviators' clothing. - Special incandescent lamps are used as heating elements in certain applications where radiant heat is desired. These.use carbon or tungsten filaments as resistors, and are designed to produce maximum energy in the infra-red portion of the spectrum. ELECTRIC HEATERS ' Electric heaters may be divided into four groups: conduction, radiant, .'convection, and induction. Conduction electric heaters, which deliver most of their heat by actual contact with the object to be heated, are used in such.applications as. aviators' clothing, hot pads, foot warmers, soil heaters, ice melters, and' water heaters. Conduction heaters are useful in conserving and localizing heat delivery at definite points. They are not suitable for general air' heating. .' - Radiant electric heaters, which deliver most of their heat by radiation, have high temperature heating elements and reflectors to concentrate the heat rays in the desired directions. The immediate and pleasant sensation of warmth which is caused by radiant heat makes this type desirable for temporary use where the heat rays can fall directly upon the body. They are not satisfactory for general air hearing, as radiant heat rays do not warm the air through which they pass. They must first be absorbed by walls, furniture, or other solid objects which then give up the heat to the air. For a discussion of electrically heated panels as applied to radiant heating, see Chapter 31. . Gravity convection electric heaters, designed to induce thermal air circu- Jation, deliver heat largely by convection, and should be located and used in much the same manner as steam and hot water radiators or convectors. They generally have heating elements of large area, with moderate surface temperature, enclosed to give proper stack effect to draw cold air from the floor line. The flexibility possible with electric heating elements should discourage the use of secondary mediums for heat transfer. Water and steam add nothing to the efficiency of an electric heater and entail expensive construction and maintenance. . ' Electric Heating 543 Induction Heaters are described'in the section on Electronic Heating by Induction and Electronic Means. 1. . UNIT HEATERS Electric unit heaters include a built-in fan unit which circulates room air over the heating elements. Heaters of this type are manufactured in many designs and sizes, and can be located in the same manner as steam unit heaters. '. Electric unit heaters are used in industrial plants, sub-stations, power houses, pumping stations, etc., where the power rate for electric heating is found to be favorable. In many large plants, such as flourmills, grain elevators, etc., in which there are a number of small offices, locker rooms, etc., scattered over wide areas, electric unit heaters are frequently economical in such locations. In small unattended stations, where. .' freezing temperatures cannot be permitted, thermostatically-controlled electric unit heaters are frequently used to maintain a temperature above freezing. The best location for the heaters depends upon local circum stances as they can be mounted on the ceiling to direct the air downward, Power supply Fig. 1. Wiring Diagram for Unit Heater on the side wall about 7 ft from the floor, or near the floor line. Variations in design are necessary for different locations, as with steam unit heaters, see Chapter 26. ' The arrangement of the wiring circuits is very important for electric - unit heaters:' In. principle they are all the same and include as essential elements an automatic control panel, a thermostat, and a master hand switch. All heaters should be designed with a safety thermal trip wired . in series with the magnet coil of. the control panel and with the hand . switch and thermostat. A typical wiring diagram is shown in Fig. 1. This applies to a single phase power supply, but for 3-phase the only difference . is to have a 3-pole panel and a heater arrangement for 3-phase connection. Portable unit heaters are useful for temporary work, such as drying out - damp rooms', or for warming rooms during construction. CENTRAL FAN HEATING Electric heating elements can be- used for the prime source of heat in a central fan electric heating system, or in the heating phase of a complete air conditioning system. They can be used in the same manner as steam heating units for tempering, preheating or reheating the air at the main supply fan location and as booster heaters at the delivery terminals of the duct system: In the humidification phase of air conditioning electric heating elements can be used to provide moisture by the evaporation 544 CHAPTER 30 1946 Guide of water, or for controlling air washer dew-point temperatures when mounted as preheating units on the intake side .of the air washer. (See ` Chapter 43.) In coordinating the input of heat energy and the volume of air circu lation, a basic difference between electric heating and steam heating enters into the problem.. Steam is approximately a constant-temperature source of heat for any given pressure and a change in air volume flowing oyer steam coils does not greatly affect the temperatures of the delivered air. The amount of steam condensed (heat input) varies in proportion to the air volume, but the. surface temperature of the steam coils remains about the same. Electric heat is quite different, having a constant input of energy. If the volume of air flow over electric heating elements is changed, and no change is made in. the electrical power connections, there wilj be a corresponding change in the temperature of the air delivered. This occurs because the electrical energy input remains constant and the surface temperature of the heating elements will vary as is necessary to force the air to accept all the heat. With electric heat the total heat is constant unless some compensating action is performed by control. Auto- Electric Heating 545 by contact with the hot surfaces. To lessen the likelihood of the heating elements burning out, they should be of substantial construction, with a low heat density per unit of surface area and provision should be made for cleaning off deposits of scale which restrict the heat flow. A typical resistance type of steam or hot water boiler is shown in Fig. 2. Large electric boilers are usually of the type employing water, as the resistor, using immersed electrodes. With this type only alternating current can be used, as direct current would cause electrolytic deteriora tion. Such a type of electrode boiler is shown in Fig. 3. ; Electric steam boilers are useful in industrial plants which require, limited amounts of steam for local processes, and also for sterilizers, jacketed vessels and pressing machines which need a ready supply of' steam. It sometimes is economical to shut down the main plant fuel Fig. 2. Resistance Type Boiler for Stkam or Hot Water matic variation of the electrical heat input synchronized properly with the air flow can be successfully accomplished by various special methods of control. By-pass dampers as used in steam units will not control electric heat. .. . Electric heaters are useful in balancing the heat distribution in central fan heating systems. Even in those instances where steam is the principal ' heat source, the temperature of individual rooms'can be controlled locally by" separate electric booster heaters. These heaters can be installed in branch ducts or behind the air outlet grilles in each room. With this arrangement, the central heating unit distributes air at an average temper ature, controlled from a thermostat centrally located, such as in the main return duct. The electric booster heaters may be controlled by thermo stats mounted in each individual room which permit the occupant to maintain any desired temperature independent of the rest of the building. ELECTRIC BOILERS Steam or hot water generating boilers using electric energy are entirely automatic and are well adapted to intermittent operation. . Small electric boilers usually have, heating elements of the enclosed metal resistor type immersed in the water. Boilers of this construction may be used either with direct or alternating-current since the heat is delivered to the water Fig. 3. Diagrammatic Arrangement of an Electrode Boiler burning boilers when the heating season ends, and to supply steam for summer needs'with small electric steam boilers. located close to the operation^ In general, electric steam heating is confined to auxiliary or other limited applications: If the heating system is designed to use . electricity. exclusively, steam generating or distributing equipment is superfluous. . ' ELECTRIC HOT WATER HEATING . Electric water heating, using an'electric boiler in place of a fuel burning boiler, like electric steam heating, is generally confined to auxiliary or other- limited applications. The use of insulated water storage tanks, in which to store heat generated by electricity during off-peak hours at extremely low rates, is a development which has some special applications. In this system of heating, the primary storage tank is simply a large, well-insulated, pressure type steel tank, equipped with electric heating elements and automatic time switches, which also have automatic limit controls for temperature and pressure. _ The heating system installed in the building may be of any standard individual radiator or fan-served indirect type or with provisions for the heating and humidification phases . y S46 CHAPTER 30 1946 Guide of an air conditioning system. 'A system of this kind requires very careful.. design to avoid excessive over-all radiation losses during periods of low heat demand. It is also important to provide for sudden changes in heat demand. A typical hot water heating boiler is illustrated in Fig. 2. HEATING DOMESTIC WATER BY ELECTRICITY1 Electric water heaters of the automatic storage type for domestic hot water supply are simple and reliable. In many sections of the country low electric rates have been established by the electric utilities to secure this load. In many localities, electric rate schedules divide the current used for water heating into two classifications, regular and off-peak. A time switch automatically limits,use of the off-peak heating element to the hours of off-peak load, while the regular heating element is a stand-by at all times. Storage of this two-element type of water heater is larger than average to carry over the periods when the off-peak element is timed Fig. 4. Piping Arrangement foe Connecting Electric Water . Heater to Fire-Box Coil Fig. 5. Domestic Hot Water Heater for Off-Peak . Service out, without too frequent demands on the regular heating element which takes the. higher domestic lighting service rate. Some utilities now offer a.schedule which, beyond a stipulated minimum, lowers the rate for all electric service if an electric water heater is installed. ' Competition with other fuels, especially gas, seems to be the major controlling factor in the' use of electricity. The first cost of electric storage heaters is greater than, for gas, owing to the need for larger tank storage due to off-peak service and slower recuperating capacity. In residential work, to effect a saving in the cost of operation, it is sometimes desirable to use a furnace coil or indirect heater in connection ' with an electric water heater. In this case it is important to. make the proper connections in order to benefit by any heat obtained from, the furnace and at the same time to prevent dangerous overheating. The' proper piping connections are shown in Fig. 4, and in this case the electric . heater will only furnish heat when insufficient heat, is supplied from the furnace. This arrangement has a further advantage in the summertime in that the bare tank through which the cold water passes on its way to the electric heater, serves as a tempering tank, absorbing, heat from, the basement air and requiring the use of less energy in the electric heater; Atypical domestic hot water heater as shown in Fig. 5 is arranged with Electric Heating '' . `,:. _______ ,547- . upper and lower heating elements for the usual type of off-peak heating service. The .lower heating element is under the control of the off-peak time switch. However, the upper heating element is usually connected to the line so that, in case the supply of hot water in the tank becomes . exhausted, the top thermostat can turn on the top heater and heat a small . supply of water. The top heater will not heat the water in the tank' below its location, but when the off-peak period arrives the lower heater is turned on and the entire tank becomes heated. HEATING BY REVERSED CYCLE REFRIGERATION Reversed refrigeration is frequently referred to as a heat pump since the electric motor driving the refrigerating compressor furnishes the motive power to transfer heat from one temperature to a higher temperature level. . The compressor acts as a reversible refrigerating unit to extract :heat from the outdoor air in winter and deliver it indoors for heating purposes, and, by a reversal, to extract heat from the indoor air in summer and discharge it outdoors. In normal use a refrigerating machine is arranged to remove heat and the heat removed is dissipated to the condenser cooling water. The driving energy is converted into heat, most of which is added to the heat removed and extracted. In so-called reversed refrigeration the heat removed together with the heat converted from the driving energy is , utilized to heat the building. This conservation of the heat converted from the driving energy enables the reversed refrigeration to show a better performance in heating service than straight refrigeration can show, in cooling service. In order to overcome the drop in capacity and in efficiency with lower outside temperatures, it is often desirable to use well-water instead of air as the source of heat. For a detailed description of this cycle see Chapter 39. ' . AUXILIARY ELECTRIC HEATING In conjunction with heating systems of other types, an auxiliary elec- tric'heating arrangement is a convenient means of caring for mild days, in the spring and fall which require little heat to make a building com fortable. \ Likewise, such electric heating might be used on abnormally cold days to help out the main heating system and by , this means reduce the necessary .size of the system. . . A few installations have been made using electric heating cable buried in the floors of bathrooms, etc., to provide auxiliary electric heating. At . least one airplane hangar is heated in this manner. . , Because of the feeling of comfort that a radiant type heater gives, bathrooms may be heated electrically with this type of heater while the rest of the house is cared for by some other system. Offices and rooms which require heat at periods when the main heating plant is shut down can be conveniently heated electrically. CONTROL Because the efficiency of electric heat production is the same for , small and large units, it is possible to reduce heat waste to a minimum' by applying local heating, locally controlled. Heaters are often controlled manually but thermostatic control is essential for economical operation. For duct systems having a variable volume of air flow the electric heater control must automatically vary the heat input in coordination with the changes in air volume and demand for heat. .. 548 - CHAPTER 30 1946 Guide CALCULATING CAPACITIES In calculating electric heating capacity one kilowatt is equal to 3413 Btu per hour or 14.2 sq ft equivalent direct steam radiation. INDUSTRIAL USES FOR ELECTRIC HEAT Electric heating is valuable for many industrial processes in both low and high temperature ranges. It is easily controlled and can be justified .where savings in labor or improved quality of product outweigh the inherent higher cost per unit of heat as compared with other fuels. Important examples are metal melting and heat treating furnaces,-ovens, dryers, laboratory equipment, cooking vessels, oil preheaters, catalysts, and countless other special uses. . RADIANT DRYING Lacquers and similar surface films can be very effectively dried by radiation. Special electric lamp bulbs have been developed which give off a high percentage of infra-red and similar heat rays2. These are mounted in very efficient reflectors. For continuous manufacturing processes these reflectors are mounted in tunnels through which conveyors pass. For local applications, as for example paint drying in automobile repair'shops, they may be mounted on portable racks. In the application of this type of drying the composition of the paint or lacquer is important. In general, lacquers and those enamels using synthetic resins react most favorably. Other applications include the drying of ink, glue, and water, the softening of celluloid and bakelite for punching or shearing, and a wide variety of other uses5. . Objects of relatively large surface area in proportion to their weight, and fabricated materials having a rather high heat absorption, may be satisfactorily heated by such a source. ELECTRONIC HEATING BY INDUCTION AND ELECTROSTATIC MEANS These methods differ radically from .resistance heating as they employ high frequency radio waves to apply the energy which produces heat. High frequency heating has many important industrial uses and opens up a whole new field of special applications where extreme accuracy and speed are vital. Some spectacular results are being attained with this modern industrial tool. Skillful engineering design and experience are necessary to produce safe and satisfactory performance, but this technical . assistance is now available from many sources. > ' Metals can be heated by induction. When the work is placed in a magnetic field within a high frequency coil, eddy currents immediately produce heat in the body of the metallic piece. The speed and intensity of this heating can be regulated by controlling the high frequency cur rents producing the magnetic field and the location of the spot heated by the position of the work piece within the coil. . Induction heating is very useful in special processes such as melting metals, brazing; forging, heat treating, etc; 'If is possible to apply localized heat so rapidly that conduction cannot draw the heat away before it has time to accomplish the desired purpose at a particular spot. One example is the rapid hardening of a tool edge or tip too quickly for scale to form. Electric Heating 549 Dielectric materials can be heated internally by introducing them into an electrostatic field between high frequency electrode plates. Foods can be sterilized, plywoods bonded, plastics heated, granular or crystal line materials dehydrated, and countless other products heated quickly and uniformly, although they are poor thermal conductors and resist heat applied to their exteriors. Electrostatic heating is ideally suited for . continuous production processes as the materials can pass through the heating field quickly with very short exposures to the high frequency radio waves. ,' POWER PROBLEMS The. cost of electric energy varies because of several factors. Distribu tion costs differ for large and small users. The fact that electricity cannot be economically stored, but must be used as fast as it is generated, makes it impossible to operate electric plants at uniform loads; hence, even the time of use may affect the cost of electricity. Special low rates are some times available during certain prescribed hours of use. ' Since the cost of production and distribution depends not only upon the quantity of energy used but also upon the maximum rate at which it is used, electric energy is often sold on a demand rate basis. In some cases, the demand charge is based upon the rated connected load, in other cases, upon the maximum demand as indicated by a demand meter. Homes are almost universally supplied with lighting current of 115 volts, which can only be. used economically for small heaters. Usually . the service lines will not permit more than plug-in devices. The Under writers permit approved heaters of 1320 watts or less to be plugged into approved baseboard receptacles, but such heaters cannot be served on a circuit supplying much other load without overloading the fuses. There is an Increasing trend toward supplying homes with three wire 115-230 . volt service. Where homes have such service, larger heaters can be installed.- For industrial purposes, heaters should be designed to use. polyphase power, which is usually supplied at 208, 220, 440 or 550 volts. All polyphase heaters should be balanced between phases. In ordering electric.heaters the proper voltage must be specified as the heat produced will vary as the square of any variation in voltage. .- REFERENCES '--Application of Electric Water Heaters To Domestic Service, by C. G. Hillier (A.S.H.V.E. Journal Section, Heating, Piping 'and Air Conditioning, November, 1936, p. 632). Fourteenth Range and Water ' Heater Survey (Electric Light and Power, August, 1940). *"Infra-Red Lamps Speed Up Drying Operations (Automotive Industries 82:376-7; April 15, 1940). Invisible Rays Build Visible Profits, by H. M: Archer (Electric Light and Power, May, 1940). Radiant Energy Drying and Baking for Organic Finishing (Metal Industry 38:294-6; May, 1940). 3_Infra-Red Heating, Section IV, Power Sales Manual (Edison Electric Institute). BIBLIOGRAPHY . Electric Elements Well Adapted to the Air Conditioning Heating Cycie, by L. P. * f Hynes {Healing, Piping and Air Conditioning, January, 1940, p. 29). ` Electric Heat for the Bathroom Floor {Heating and Ventilating 36:41; December, 1939). Electric Heat Spreads in Sunny Climes {Barron's National Financial Weekly 20:5; January 8, 1940)., * Electric Heating for Los Angeles Building {Heating and Ventilating 37:50-1; June, 1940). Dracker Apartments, West Los Angeles, Calif. {Heating and Ventilating 37:32; July, \ 1940). .. Electric Heat in California Homes, by P. F. Offerman, W. J. Walsh and H. H. Skilling {Electrical Wtst, March, 1941, pp. 37-39). .v . * Radiant Heat, by. F. W. Hutchinson {Electrical West, January, 1941, pp. 29-31). ' 550 ; _______ CHAPTER 30 - '_______ 1946. Guide. Electric Radiant Heat vs. Steam Convection,. by Douglas Dow (Electrical World. August 10, 1940, pp. 61-62). .- ' . . Practical Aspects of Heating Residences by Electricity, by F. L. Lawton arid P. Tellier et.al (Electrical News & Engineering (Canada) July 1, 1934, pp. 32-33 and 40; July 15, 1934, pp. 29-32; August 1, 1934, p. 17; July 1, 1933, pp. 16-20; July 15,1933, pp. 21-22; August 1, 1933, pp. 23-25). . - Off-Peak System of Elfectric Heating for Buildings, by Elliott Harrington (A.S.H.V.E. Transactions, Vol. 37, 1931, p. 323). . '. Electric Heating of Residences, by Edgar Allan Loew (University of Washington, Engineering Experiment Station, Part I, Bulletin No. 15, December, 1921; Part II, Bulletin No. 20, November 15, 1923). . ' Reversed-cycle Refrigeration for Air Conditioning Work, by Regis D. Heitchue (Refrigerating Engineering, May, 1941, pp. 317-321). South American Way on This Buenos Aires Job Was to Use a Heat Pump, Melvin A: Ramsey (Heating, Piping and Air Conditioning, March, 1941, pp. 167-170). The-Sixth Ingredient--The Heat Pump--The Importance of Its Development in Making the All-Electric Home a.Reality, by Philip Spom (E.E.I. Bulletin, August, 1944). -Description and Performance of Two Heat Pump Air Conditioning Systems (Using Well Water and Outside Air as the Heat Source), by Philip Sporn, and E. R. Ambrose (A S.H.V.E. Transactions, Vol. 50, 1944). " ' -Heating of Nori-Magnetic Electric. Conductors by Magnetic Induction, by R. M. Baker (Electrical Engineering, June, 1944). - '' What High Frequency Heat Treating Can Do (Electrical Manufacturing, July, 1943, Vol. 32, Number 1). '. , Electronic Devices Aid Metallurgical Research, by E. V.' Potter (Electrical Engu neering. May, 1944). , ' ' . Designing an Induction Heating Product, by Charles R. Underhill (Electrical Manu facturing, June, 1944). . CHAPTER 31 f-^cuief ^Heating. anti Radiant ^Heating. Influence of Heat Radiation on Human Comfort, Objectives of Radiant Heating, Practical Problems of Radiant Heating from a Physiological Standpoint, Fundamental Computations, Application Methods, Calculation Principles, Measurement . and Control IT has been pointed out in Chapter 12 that the human body loses heat to its environment in three ways; by convection, radiation, and evaporation. The Effective Temperature Chart takes account of con vection and evaporation, but does not provide for such radiative effects . as occur when room air and its surrounding, surfaces differ widely in temperature. INFLUENCE OF HEAT RADIATION ON HUMAN COMFORT When, however, the body is exposed to radiation from a hot surface or is radiating to a cold surface, the factor of radiative heat gain or heat loss may be important. This phenomenon is most marked in the case of exposure to the sun's radiative heat. On a cold day, with no wind blowing, while standing in the sunshine, one may feel perfectly comfortable but, when a .cloud passes over the sun, one may instantly feel much cooler. The cloud acts as a shield to interrupt the radiant heat from the sun. The change in feeling of comfort is due to the instant change in rate of heat loss from the body caused by the shielding effect of the cloud. A shielded thermometer under the same condition would register no change in temperature. '. The rate of heat loss by convection depends upon the average tem perature difference between the surface of the body and the surrounding air, the shape and size of the body, and the rate of air motion over the body. . . The rate of-heat loss by radiation depends upon the exposed surface area of the body, and upon the difference between the mean surface temperature of the body and the mean surface temperature of the sur rounding walls or other objects. This latter temperature is called theMean Radiant Temperature (MRT). Because these two types of heat loss supplement each other, a required . rate of total heat loss can result either from a relatively low air tempera ture and a relatively high MRT, or vice versa. . At the temperature which produces comfort (and at all lower, tempera tures) the production of sweat is low' and the heat loss by evaporation is . relatively low and relatively constant, irrespective of the relative humid ity of the atmosphere. Under such conditions the heat loss from the body . is chiefly related to the combined effect of convection and radiation. The heat demand of the environment, so, far as these two factors are con cerned, may be measured by Operative Temperature, which is defined by the following formula, modified from that of Gagge1 by the expression of. air velocity in feet per minute and temperature in Fahrenheit degrees. to = 0.81V+0.135 [Vv tk - (W-L40) <s], /' 551 - " .. 552 CHAPTER 31 1946 Guide where to = operative temperature, Fahrenheit degrees. fw = mean radiant temperature; Fahrenheit degrees. _<* = air temperature, Fahrenheit degrees. t3 = mean skin temperature, Fahrenheit degrees. V = air velocity in feet per minute. ' -- . At high environmental temperatures, a given Operative Temperature with cold air and hot walls produces a slightly greater cooling effect on the body than the same Operative Temperature with air and wall tem peratures equal, probably on account of local cooling of the nose and throat2. This phenomenon is not important in the comfort zone. Under ordinary conditions, with normally clothed human beings in still air, the mean skin temperature of the body is about 90 F (with lower values for the extremities); and the mean temperature of the surface of the clothing is about 86 F. The normal rate of heat production in an average sized sedentary individual is about 400 Btu per hour. The heat' production for persons subjected to various rates of activity is given in Chapter 12. The human body is of complicated shape, and radiation takes placfe freely only from the exposed outer surfaces; there are considerable portions of the body such as the legs, arms, lower part of the head, etc., which radiate most of their heat to other portions. It is necessary to determine the equivalent surface of the body from which heat is radiated and a similar value for convection. The total may be assumed to be about 19.5,sq ft for con.vection.and 15.5 sq ft for radiation, in an average sized individual. The loss by respiration and by evaporation from the nose and throat depends on the temperature and area of the moist surfaces (respiratory) of the body, the air, temperature, air movement, and humidity. In air at a temperature of 70 F, this loss, for a sedentary individual of average size, will be approximately 90 Btu per hour; and at 60 F about 70 Btu per hour. These values are relative, because the total will vary .materially with change of position, bodily activity, age, sex, race, etc. The balance of the heat generated in the average human body, approxi mately 300 to 320 Btu per hour at about 70 F room temperature, is the approximate amount of heat given off by radiation and by convection from the external body surfaces. Under normal conditions (in still air), the radiation loss will be about 190 Btu per hour; and the convection loss about 120 Btu per hour. With an air velocity of '520.fpm, comfort will' require an increase in Operative Temperature of nearly 12 deg; under such conditions the convection loss will rise to 250 Btu per hour but comfort may be attained if the subject is surrounded by heated walls which keep the radiation loss at about 50 Btu3. , It' is neither feasible nor desirable to change the relationships of con vection and radiation very greatly in actual heating practice. In the laboratory, where the laws of radiative heat loss have been-deduced, it is necessary to produce wide differences between radiative and convective heat loss. This can only be accomplished, however, by elaborate and powerful conditioning apparatus which simultaneously heats walls and cools air, or vice versa. Such a process would be very costly in practice and would not be justified unless marked improvement in comfort resulted from such a condition--an assumption which has not been demonstrated. In practice, where radiant heat is introduced into a room,,' Panel Heating and Radiant Heating . 555 that heat is absorbed by surfaces, furniture, and the like, and then trans formed into convective heat so that air and surfaces tend to attain a generally uniform temperature. OBJECTIVES OF RADIANT HEATING Under ordinary circumstances the human being, indoors, is not sub jected to marked variations between the factors affecting convection arid radiation. Air and walls are not commonly very far apart in temperature; air movement and relative humidity are Usually low. Where such con ditions obtain, the ordinary air thermometer is a good measure of comfort --which is the reason why it has enjoyed such universal use. Where con siderable window surfaces create heavy radiation loss, or where stoves or open fires, or very hot ceilings contribute to large radiation gain, the picture is changed and the air temperature productive of comfort must be correspondingly modified. , In general, however, radiant heating of occupied spaces is not a pro cedure designed to create differences between air and walls, but is merely one method of introducing heat into that space. The engineering factors used in determining desirable heat input will be essentially the same as if the heat were introduced by convection, or in any other way. PRACTICAL PROBLEMS OF RADIANT HEATING FROM A PHYSIOLOGICAL STANDPOINT It is convenient to distinguish two different methods of introducing radiant heat into an enclosed space. The first, which may be called High-Temperature -Radiation, involves direct exposure of the occupied parts of the room to radiation emitted from relatively small heating units of very high temperatures (perhaps 1,000 F); the second, Panel Heating, involves exposure-to relatively large surfaces at not over 130 F. High-Temperature Radiant Heating may be useful for temporary purposes, as in the use of a bathroom heater. It is, however, generally an undesirable process (except in rooriis of great height) on account of the marked unevenness of the effect produced on the human body. Studies at the John B. Pierce Laboratory of Hygiene have shown that this type of heating produces uncomfortable differences in the temperature of different parts of the body (an over-heated head, for example, if the heat comes from the ceiling). Panel Heating, on the other hand, is advantageous from the standpoint of temperature differentials. In actual practice, a well-designed system of this sort produces very uniform conditions, the air throughout the room differing at various points by only 5 deg. This is desirable from the comfort standpoint and may also be a factor in heat economy, since high temperatures in the upper part of the room favor excessive heat loss. The esthetic value of such a system is also considerable, since it avoids the presence of registers or free-standing radiators in the room. ' In the design of Panel Heating, however, careful thought must be given to the location of the panels from the standpoint of comfort. The English commonly use the ceiling for their panels, but their rooms are generally high-studded; arid outdoor winter temperatures moderate. With low ceilings everi panels may produce an excessive directional heating effect if all the heat necessary in a cold climate is introduced from above. Similarly, if the floor alone is used, it may---in very cold weather1--be necessary to make the floor too hot for comfort. Wall panels, or a com bination of ceiling and floor panels, wili perhaps produce the best results. 554 , CHAPTER 31 's , . 1946 Guide FUNDAMENTAL COMPUTATIONS The mean surface temperature of an inert body, which will cause given rates of heat loss by radiation and by convection in a uniform environ ment, having a given air temperature and a given mean wall temperature, may be calculated from fundamental equations1 for radiation and natural convection, with substitution of comparable cylinders for the irregular human body. " 01730 where (1 \0.2 / 1 \ 0.181 . / . \ 1.266 -d) x(rJ x{rs-r*) ffr = heat loss by radiation, Btu per (square foot) (hour.) ?c 53 heat loss by convectioir, Btu per (square foot) (hour.) Ts = absblute temperature of the body surface, Fahrenheit-degrees. , rw.= absolute temperature of the walls, Fahrenheit degrees. ra = .absolute temperature of the air, Fahrenheit degrees. . . Ts + ra -' -: 2- - D = diameter of cylinder, inched. the ratio of actual emission to black body emission. (1) (2) - If it is assumed that an average adult has a height of 5 ft 8 in., a body surface of 19.5 sq ft for convection, and 15.5 sq ft for radiation, an-equivaleiit effect can be worked out for two cylinders, 5 ft 8 in. high by 13.15 in. diameter and 10.45 in: diameter, respectively. However, while the effects . on a cylinder, of a particular size and shape may be used to estimate average similar effects on the human body, it should be remembered that the heat loss from the body varies greatly. Every movement alters not.. only its shape, but also the heat generated by the body, the velocity of the air passing over it and the surface exposed to radiation. This fact renders the results of any such computation only approximate. APPLICATION METHODS . The several methods of applying panel and radiant heating to. a structure are: ./ 1. By warming Ike interior wall and ceiling surface of the building. Pipe coils are - ' imbedded in the concrete or plaster of the walls or ceilings,^the heating medium being hot water circulating through the plipe coils. These coils are generally constructed of small pipe M'or in. I.D. and spaced about 6 to 9 in. apart..- See Fig. 1. This has the effect of warming the entire concrete or plaster surface in which the pipes are imbedded. Since the temperature of the heating medium should never exceed about 130 F, due to the possibility of cracking the plaster the area of the warmed surface must be sufficient to supply the requisite quantity of heat at this low temperature. When carefully designed, this method produces very comfortable results and great operating economy, but offers . some slight obstacles when alterations or additions to the building are desirable.. Normally the hot water circulation is maintained by means of a circulating pump and , facilities have to be provided to eliminate all air at the top of the system. All coils and circulating pipes are welded together and tested after erection to a hydraulic pressure of 300 psi. .. . ... . 2. By circulating warm air through shallow ducts under the floor.. In this design the entire floor surface of a room is heated as in Fig. 2. This method was used 2000 years . ago in many parts of the Roman Empire. While this method is more expensive in con struction, it is effective and quite suitable for cathedrals and iarge public buildings. To provide a uniform floor temperature, one should give special consideration to the design of the air ducts so that equal heat distribution is obtained. Panel Heating and Radiant Heating ,555 3. By placing hot water pipes in or under the floor. With this arrangement the whole floor surface of a room is raised to a temperature sufficient'to give comfortable conditions. Floor heating is recommended for schools and hospitals where large quantities of outside air are desirable. The floor surface may be.of concrete, wood blocks, marble or any other . material unaffected by heat, and while it is true that heat will be conducted through all materials used in floor construction, it is important that due consideration'be given to the emissivity of the floor. In some cases where pipe coils are installed in the air space Fig. 1. Coils in Wall Surfaces Fig. 2. Air Ducts for Floor Heating under the floor, special floors are constructed in sections so that the whole floor can be lifted to examine the coils. See Fig. 3. Pipes supported thus may be larger and the heating medium maintained at a higher temperature than when pipes are actually imbedded in the floor. Pipes may be 1H or 2 in. in the former, but for the latter % or I in. pipes are recommended. See Fig. 4. Where the heat losses from a. room are ex ceptionally high it may be necessary to supplement the warm floor by either adding some coils in the ceiling or forming heated panels in the side walls. 4. By attaching separate heated metal plates or panels to the interior surfaces. These plates or panels are placed either in an insulated recess so that the surface of the panel is flush with the surface of the walls or ceilings, or they may be secured to the face of the wall. They may be covered with wood veneers and decorated to harmonize with other 556 CHAPTER 31 ' 1946 Guide parts of the room, or they may be cast into panels to imitate oak or other wood designs. With fiat plate panels it is common practice to use a frame of plaster, wood, metal or composition to allow for expansion. These plates may be heated with either hpt water or steam and connected as in an ordinary radiator system. See Figs. 5 and 6. . 5. By electric heated metal plates or panels. These plates or panels are either placed in insulated recesses of walls or ceilings or fastened to the construction, as.found desirable. They should not have a surface temperature much above 200 F. Some have a much higher surface temperature but a lower temperature gives a more comfortable condition and is more efficient. ' 6. By electrically heated tapestry mounted on screens and on the wall. For. this purpose the screen is woven with an electric continuous conductor. Such screens are useful to plug in at any position for emergency local heating without taking care of a large room1 or office. . Panel Heating and Radiant Heating ,$57 heating systems should, in general, be operated continuously since the panels have large thermal capacities. Where panels are heated by high temperature radiation from a heat source directed toward them, this qualification does not apply. * . 1. Assume tfie location and the approximate size of the heating panel. Heating panels may be located in ceilings or floors or walls. Ceiling panels have the advantage that their heat emission is not affected by tapestry or furniture and that they can be used, to a limited extent, as cooling panels during the summer months. If used in low rooms, however, they may produce an undesirable heating effect upon the head. Floor panels have the advantage that they can be easily installed and that much of the radiated heat is delivered to the lower portions of the walls; they have the disadvantage that their heat emission is rather uncertain, since it may be affected by rugs, carpets, furniture, machinery, etc. . It is best to make the panels as large as practicable; for example, if the floor or ceiling is used as the heating panel, it is best to use the entire floor or the entire ceiling, or both. Heating a room by means of panels is very similar to lighting a room. Heat radiation is exactly like light radiation, except that it has a longer wave length. If a room is lighted Fig. 5. Pillar Type Radiant Heat Panel . Fig. 6. Flat Type Panel Installed in Wall. Recess . Note. If all of a heating panel is installed at one end of a large room there may be a marked difference between the equivalent temperature on the two sides of the body. It is usually desirable, therefore, that the heat be distributed at different parts of the walls and ceilings so that no uncomfortable effect will be felt from unequal heating. , CALCULATION PRINCIPLES Part I--Panel Heating The term panel heating, involving both radiatio'n and convection, is 1 applied in this chapter to a system in which the heat is transmitted from pane! surfaces to both air and surrounding surfaces, as is the case under indoor conditions. Panel heating systems for buildings may be designed as illustrated and described in the following design of a panel heating system , for the room shown in Fig. 7. The design is based on continuous heating.- Panel Fig. 7. Room Plan Used forIllustration of Method of Designing a Panel Heating System by means of a large number of small units distributed uniformly over the ceiling, the room is lighted more uniformly than if it is lighted by means of a-single unit of equal capacity. Similarly, if the entire ceiling is the heating panel, the room is heated more uniformly than if only a fractional part of the ceiling is used as the heating panel. " . In the following example, the entire ceiling will be used as the heating panel. 'v 2. Select the desired mean temperature of the air in the room. ;` In a panel-heated room, the mean air temperature is a few degrees lower than the mean temperature of the surfaces of .the enclosing walls, floor, and ceiling. In a room heated by -introduction of warm air or by means of radiators, convectors, or other similar heating appliances, located within the room, the mean temperature of the air is a few degrees higher than the mean temperature of the surfaces of the enclosing walls, floor, and ceiling. Under ordinary conditions, in a panel-heated room, the mean tem perature of the air ranges from approximately 65 F to 72 F. In the following example, 68 F is selected as the mean air temperature.,,, 3. Determine as accurately as practicable, the mean temperature of the inside surfaces of the enclosing walls, floor, and ceiling. '. . The two inside walls are assumed to separate rooms, which are filled with 68 F air, so that both surfaces of each wall are in close contact with 68-F air. ' The surface tern- 558 CHAPTER 31 1946 Guide peratures of these walls, therefore, can not be lower than 68 F and must actually be higher than 68 F because, in addition to their contact with 68 F air and their contact with the heated ceiling, they are exposed to the heat radiation from the ceiling. In the following example, 70 F will be selected as the mean surface temperature of the inside walls. ' *' - For'the two outside walls, the mean inside surface temperature can be calculated' with fair accuracy. For a heat transmission coefficient of 0.25 and a temperature difference of 68 deg, heat flows through the wall at the rate of 17 Btuh per square foot. If the indoor film coefficient is 1.65, the temperature difference, indoor air to inside wall surface, is.17/1.65 or 10 deg and the wall surface temperature is 68 -- 10, or 58 F. This value may be taken directly from Fig. 8. However, the film coefficient 1.65 was deter- Fig. 8. Chart for Estimating Inside Surface Temperatures of Outside Walls3 - "Note: The value of U, the over-all coefficient of heat transmission, cannot exceed 1.29 if the inside and outside film coefficients are 1-65 and 6.0 respectively (e.g. ~ = "0^73* Therefore V *= 1.29 maximum): ` '.. . ' mined to represent the sum of the heat flow into the. wall, by conduction from the air in contact with, the wall, and by radiation from the warmer surfaces seen by the wall . surface. In a panel-heated room, the rate of heat flow into the outside wail by, radiation is greater than it is in a radiator-heated room; consequently, the film coefficient is higher, , and the temperature difference, air to wall surface, is smaller, and therefore, the wall surface temperature is higher than the calculated 58 F. It is impossible to determine accurately how much higher than 58 F the temperature of the wall surface will be until the corresponding indoor air film coefficient has been determined accurately. . ; In the. following example, 60 F will be selected as. the probable mean inside surface temperature of the outside walls. ' The probable mean inside surface temperatures of the floor and the glass may: be determined by calculations and by reasoning similar to that employed, to determine the inside surface temperature of the outside walls. `. . In. the following example, SO F and 70 F will be selected as the probable inside surface temperatures of the glass and floor, .respectively. . . .. . Panel Heating and Radiant Heatings 559 Table !. .Calculated Heat Loss of Room Surface Area . Sq Ft . . u Outside Walls__________ . Ceiling.... ................. ......... 360 216 480 480 480 0.25 1.13 o.io t Calculation . Heat^loss . Btuh 360 x 0.25 x 68.......... 216x1.13x68 ...... 6,120 16,597 .Heating Panel.............. 480 x 0.10 x 38 .......... 1,824 1.50 x 68 x 0.018 10,576 Total--___ ________ 35,117 4. Determine the heat loss of the room. . In the.following example, the heat loss calculation will be based on an outdoor air temperature of 0 F. Since the functioning of a panel-heating system differs very little from that of a radiator-type heating system, the heat loss may be calculated according to Chapter 14 as shown in Table 1. The heat loss-through the outside walls and through the.glass is probably a little greater than calculated because the calculation is based on an indoor air film coefficient of 1.65 Btuh, whereas, for a panel-heated room, this coefficient is a little higher, but the difference is probably not sufficiently large to be.considered in design calculations for a heating, system. ' . .- 5. Estimate the Mean Radiant Temperature. , The Mean Radiant Temperature of the surfaces enclosing the room but not including the heating panels may. be estimated as follows: .' Surface Interior Walls............................................ Exterior Walls..................:............_____ Glass............ :...........'.................................... Floor.... ......................................................... ' Area 480 360 216 480 1,5361 , Fahr Dec 70 ' 60 30 70 Product . 33,600 . 21,600 ' 6,480 ' 33,600 95,280 ' The sum of these products divided by the sum of the surface areas is: 95,280/1,536 or 62.03 F, the required mean surface temperature. In the following example, 62 F wiU be selected as the MRT of walls, glass and foots. 6. Determine the temperature of the ceiling panel. - . Determine the temperature of the ceiling so that the ceiling panel will deliver heat to the room at a rate equal to.the rate at which the room is calculated to lose heat, namely, 35,117 Btuh. . . When a room is heated.by means of a panel, air convection currents are developed in the room similar to those which are developed when the room is heated by means of a free-standing radiator. Consequently, the heating panel delivers heat to the room partly by radiation and partly by convection. The proportion of the total heat flow delivered by convection varies with the location of the heating panel, with the height of the ceiling, and with the size, number, and location of pieces of furniture and other articles which interfere with the free flow of air along the floor and along the walls. It is generally sufficiently accurate to assume that a ceiling panel will deliver 70 per dent of its heat by radiation and 30 per cent by convection; a floor panel 55 per cent by radiation and 45 per cent by .convection; and a wall panel 65 per cent by radiation and .35 per cent by convection. , . . . In the following example, it will be assumed that the ceiling panel niust deliver 70 per cent of its. heat or. 24,582 Btuh by. radiation, since the total calculated heat loss is 35,ll7i . . , - : . .: 560.;__________________ CHAPTER 31________ / 1946 Cuide When two plane surfaces of infinite size are parallel to each other and their surfaces are at different temperatures, the exchange of heat between the two is proportional to the difference between the fourth powers of their absolute temperatures. -This is also true when one surface is completely surrounded by another surface; for example, if one sphere is placed within another sphere, the flow of heat between the outer surface of the smaller sphere and the inner surface of the larger sphere is proportional to the fourth power of the absolute temperatures of the two surfaces. * - In a panel-heated room, the heated panel may be considered to be completely en closed by the remaining surfaces, because all heat radiated by the heated panel is inter- . cepted by those surfaces. Consequently, the flow of heat from the heated ceiling to the ^ room, by radiation, is proportional to the difference between the fourth powers of the absojute temperature of the ceiling and the absolute mean radiant temperature of the remaining surfaces. > The rate at which a surface emits heat varies with the temperature of the surface . and with other characteristics of the surface. For ordinary heat flow calculations it is Fig. 9. Heat Delivered to Room by Radiation from Panel sufficiently accurate to assume that the materials which are commonly used in building construction emit heat at a rate of: . . (T \4 Btuh per square foot . where .* 1 ' '' T is the absolute temperature of the surface in Fahrenheit degrees. . On, this basis the flow of heat from the ceiling to its surrounding surfaces is at the rate of:-.; . \ : ' 480 X 0.156 [(^)4- (f|)4] Btuh. In order that this rate may be equal to 24,582 Btuh, T must be 572 and the ceiling temperature about 112 F. . * Instead of calculating this temperature it may be taken from Fig. 9, as follows: The ceiling must deliver heat to the room,- by radiation, at the rate of 24,582/480 or 51 Btuh per square foot. Find 51 on the left margin and move horizontally to the intersection with a 62 MRT line, and from the .point of intersection to the lower margin and read about 112.F. . -. . ' With a-.ceiling temperature of 112 F, the MRT of the room will be 480 X 112 + 1,536 X 62; the sum divided by 2,016, or 74 F. -. If an air temperature of 68 F and an MRT of 74 F should not produce satisfactory .conditions, the ceiling temi>erature can easily be changed as necessary,by.changing the. temperature of the circulating water. %` , Calculations like the preceding may also be made with the aid of Table 2. The rate at which'the ceiling must radiate heat exceeds by 51 Btuh per square foot the rate at Panel Heating and Radiant Heating, 561 Table 2. Total Heat Emission by Radiation3 Boor OB MbIm Radiant Temper- ATUBB F Deo Radiation in Btu per (square foot) (hour) emitted to surroundings with a tempera ture of absolute aero by bodies at various Boot OB Mean temperatures and with emissivity factor e Radiant Temper- aturb e e e t ' F Deo 1.00 0.95 0.90 0.80 . Radiation in Btu per (square foot)-(hour) emitted to surroundings with a temperature of absolute aero by bodies at various temperatures and with emissivity factor e - e e ee 1.00 0.95 0.90 0.80 . 30 35 40 45 46 . 47 48 49 50 51 52 . 53 54 55 56 57 58 59 60 61 62 63 64 65 66 67 68 69 70 99.7 103.9 108.0 112.5 113.3 114.3 115.2 116.0 116.9 117.9 118.8 119.8 120.6 121.7 122.6 123.5 124.4 125.3 126.3 127.1 128.2 129.1 130.1 131.0 132.1 133.0 134.0 135:0 136.0 94.7 98.7 102.8 106.9 107.7 108.6 109.5 110.3 111.0 112.0 112.9 113.8 114.6 115.5 116.4 117.4 118.2 119.0 119.9 120.7 121.8 122.6 123.5 124.4 125.5 126.4 127.3 128.3 129.3 89.8 93.6 97.2 10i.3 102.0 102.9 103.8 104.5 105.3 106.4 10619 107.8 108.6 109.4 110.3 111.3 112.0 112.8 113.8 . 114.4 115.3 116.2 117.1 117.9 118.8 119.7 120.5 121.5 122.3 79.7 ' 83.1 86.4 89.0 90.8 91.5 92.3 92.8 93.6 94.4 95.1 95.9 96.6 97.3 98.1 98.9 99.6 100.3 101.1 101.8 102.6 103.3 104.1 104.8 105.8 106.4 107.2 108.0 108.8 71 72 73 74 75 80 85 90 100 110 120 130 140 150 160 170 180 190 200 210 220 250 300 350 400 450 500 550 600 137.0 137.9 138.9 140.2 141.6 147.2 152.9 158.5 170.3 182.3 195.6 210.9 224.1 238.0 252:1 271.6 289.1 307.7 `326.5 349.3 373.0 439.5 577.3 743.0 945.8 1181.0 1470.0 1798.0 2181.0 130.1 131.0 132.0 133.1 134.4 140.0 145.2 150.5 161.7 173.2 185.7 200.4 212.9 226.1 239.8 258.0 274.9 292.1 310.2 331.9 - 354.4 417.6 548.2 705.8 898.5 1121.0 1396.0 1708.0 2072.0 123.3 124.0 124.9 126.1 127.4 132.5 137.6 142.7 153.2 164.2 176.1 189.8 201.8 214.4 226.9 244.5 260.1 276.9 293.9 314.3 335.7 395.6 519.6 668.6 850.8 1063.0 1323.0 1619.0 1962.0 109.7 110.3 111.0 112.1 113.2 117.9 122.4 126.9 136.2 146.0 156.5 168.8 179.2 190.5 201.8 217.2 231.3 246.1 261.3 279.5 298.2 351.6 461.8 594.3 756.5 944.0 1176.0 1439.0 1745.0 `These factors are calculated from the formula / 0.173 x rT**>\ V 100,000.000 ) where . gr -- total radiation. Btu per (sq ft) (hr) e -- emissivity. T = absolute temperature, Fahrenheit degrees. which the ceiling receives radiant heat from its surroundings. Assuming the emissivity of the walls, floor, and ceiling to be 90 per cent of that of a black body, the heat radiated to the ceiling, from the surfaces whose MRT is 62 F, is (Table 2) at the rate of 115.3 Btuh per square foot; the ceiling must therefore radiate heat at the rate of 115.3 plus . 51, or'166.3; its temperature must be (Table 2) between 110 F and 120 F, and, by interpolation, 112 F, as calculated. . . 7-. Select the medium for heating the ceiling panel. . The medium may be electricity, steam, air, or water,, but usually is air or water. If air is used it is generally heated in the basement, passed up through hollow inside walls or through ducts in those walls, allowed to flow between the ceiling and the floor above, and returned to the basement through hollow outside walls or through ducts in those walls. ' If the walls and floors are constructed of hollow tile, the cells in the tile.can be placed so that they will form continuous ducts, through which the warm air can flow up the inside-walls, then between the ceiling and-the floor, above, and down the outside walls. In this way the walls and ceiling become heating.panels. , If water is used as the medium, the pipes through which the water circulates--almost always under forced circulation--are placed in the floor, walls, or ceiling in such a manner .. that as much as possible of the heat emitted by the pipes will be delivered to the space to be heated. . _. 562 CHAPTER 31 1946 Guide . Table 3. Highest Safe Surface Temperatures for Heating Panel ' .. Typb of Panel ' Plastered Ceiling (Pipes Imbedded).... _ ........................ .-.__ Plastered Walls (Pipes Imbedded) __ ______________ __ Floor, Any Method . . .............. ................................................ ........ Floor, Border and Aisles-- _________ ______________ ____ _ ______ Iron, Hot Water Medium.... ............. ..................... ........ ................. Iron, Steam Vapor.______,,_______ :______________________ !____________ Electrically Heated Panels .................................. .................................. Surface Temperature E Deg . . .115 120 90 120 . 160 180 200 , Low surface temperature radiation is recommended regardless of the heating medium employed. ' Practical limits for surface temperatures of heating panels are given in Table 3. In this example water will be selected as the medium. * 8. Determine the size, length, and location of the pipe coils in the panels. When hot-water pipes are imbedded in concrete slabs or attached to plastered sur faces, their rate of heat emission varies with many factors. If the pipes are imbedded in dense concrete slabs, it may be.assumed that the rate of heat emission of H-in. pipe, spaced 6 in: on centers; 5^-in. pipe, spaced 9 in. on centers; and 1-in. pipe spaced 12 in. on centers; per foot of length of pipe and per degree difference between the temperature of the water in the pipe and that of the air in the space to be heated, is 0.8, 1.0, and 1.2 Btuh, respectively. If the distance between the pipes is increased, the rate of heat emission, per foot of pipe, is also increased; if the distance, is doubled, the rate of heat emission is increased about 15 per cent. If the pipes are attached to plastered ceilings, the rate of heat emission is slightly less,, probably about 10 per cent less, than when the pipes are imbedded in concrete slabs. The data given regarding heat emission of panels are intended as general guides for. the designer. Additional- experience and research are needed to develop definite and complete data. However, after a heating panel has been designed and installed, any small error can easily be .corrected by modifying the temperature of the water circulating through, the coils. . When the heating pipes are attached to a plastered ceiling, a portion of' the heat emitted by the pipes is delivered to the space below the ceiling and a portion to the space above the ceiling. The relative quantities depend on the degree of insulation . applied above the heating coils. When the heating pipes are imbedded in a concrete floor slab a portion of the heat emitted by the pipes will flow upward into the space to be heated, and the remainder will flow downward into the ground. . When the heating pipes are placed below the concrete floor slab .instead of being imbedded in the slab, a larger portion of the heat will flow into the ground, and a smaller, portion' into the space to be heated. ' In the following example it is assumed that the insulation above the pipe coils is such that 90 per cent of the heat emitted by the pipe coils will flow into the room and 10 per cent into the space above. Since the room is to receive 35,117 Btuh,.and since the room is assumed to receive only 90 per cent of the heat emitted by the coils attached to the plastered ceiling, the coils must emit 35,117/0.9 or 39>000 Btuh. If %-in. pipe and a mean water temperature of 140 F are selected, the heat emitted, per foot of pipe, will be 0.9 (140 -- 68) or 65 Btuh. The quantity of pipe required will therefore be 39,000/65 = 600 lineal feet. The pipe coils can be arranged in any convenient manner, but should be arranged so that the temperature of the water in the pipe will vary only slightly; otherwise, the temperature distribution over the ceiling will not be uniform. Generally, it is best to arrange the pipes so as to form two-pipe reversed-return.systems, as suggested by the two sketches in Fig. 10; By using 33 runs of 2-in. pipe, welded to two in. mains, sufficient pipe surface is secured; the-^-in. pipes will then be spaced about 83^ in. on* centers, which is satisfactory. . . The friction heads of water flowing in pipes and fittings are so well known that the pipe coils can be designed so that each will receive its proper share of the hot water? without the use of balancing valves. However, it is desirable to.divide large heating- s'- . ' _ Panel Heating and Radiant Heating 563 systems into sections and* to install valves so that individual-sections can bile.discon-' nected without interfering with the operation of the system as a.whole. ...... .. ' Part II--Radiant Heating .; . . The term radiant heating is applied in this chapter to a system in which only the heat radiated from the panel is effective as in outdoor and semi- . outdoor conditions. The outstanding example of radiant heating is the transfer of heat from the sun. to the earth. The sun radiates large quantities of energy of which a very small portion is intercepted by the earth. A part of the intercepted radiation is transformed into heat when it strikes the earth's I -I . )- Fig. ,10. Arrangement of Pipe Coil for Even Distribution of Panel Temperature surface. In this, manner heat is received by the earth from the. sun by ' ' radiation. . . . . In industry, radiant heating is employed in manufacturing, processes, particularly in drying, baking, and dehydrating operations; in agricul- .. ture, it is employed to improve living and growing conditions for young plants and young animals. .' . The heating engineer employs radiant heat;primarily in the heating ofopen-air schools and open-air hospitals. When a surface radiates heat, and every surface does unless its temperature is absolute zero,.every poin^ of the surface radiates heat in all directions. The total quantity of heat radiated by a point or- by an elementary area is % times; the. quantity of heat radiated at right angles to-the surface. . , ... Thus, if in an elementary cube the upper face is the heating panel; the .dower face;would.receive,only about 32 per cent, of the radiated-energy and the four-sides would receive each about 17 per cent. '- ' - ,X 564 CHAPTER 31 1946 'Guide. For larger surfaces the conditions are different. If two parallel plane surfaces of considerable size are hear each other, the rate of heat exchange between the two can be determined fairly accurately by means of the chart of Fig. 9. This is possible because the larger part of the heat radiated by one of the surfaces is intercepted by the other surface and only a small portion is radiated in such directions that it will not impinge upon the opposite surface. As the distance between the two surfaces is increased, the proportion of the heat radiated by one of the parallel plane surfaces and intercepted by the other decreases almost as the square of the distance between the surfaces increases, because the intensity of heat radiation, like the in tensity of light radiation, varies inversely as the square of the distance from the source of radiation. ' For the purpose of designing radiant heating systems in which the heating panel is practically square and is radiating heat toward a parallel surface of equal size and shape, as shown in Fig. 11, the rate of heat exchange between the two surfaces will be equal to that shown in Fig. 9, multiplied by a factor, p, which depends upon the ratio of A to 5 (Fig. 11) as shown in the following table: h/s = 1 2 3 4 5/ p = 0.200 0.070 0.034 0.020 O.OlS . For example, if a panel 3 ft square is located parallel to, and 9 ft above, a bed in an open-air hospital, and if the temperature of the panel is 112 F and that of the bed is 70 F, the rate of heat transfer from the panel to a 9 sq ft section of the bed directly beneath the panel, will be 3.4 per.cent of the rate shown in Fig. 9, or 0.034 X 9 X 44, or 14 Btuh, approximately. The rate of heat transfer from the panel to a section of the bed other than the 9 sq ft directly beneath the panel will be lower than 14/9 Btuh per square foot. This is a crude way of designing a radiant heating system for an open- air hospital, but it is sufficiently accurate, because the required tempera ture of the bed and the required rate of heat flow into it will vary with the temperature of the outdoor air, with-the air movement over the bed, with the thickness and the character of the bedding, and with the physical condition of the patient. .. A radiant heating system for an open-air school may be designed as described for the open-air hospital. The heating panel in such a case should be almost as large as the ceiling and, in order to keep the heat loss by radiation at a minimum, should be placed so that a maximum portion of the heat radiated by the panel will be directed toward the pupils and a minimum toward the outside walls and particularly the windows. MEASUREMENT OF RADIANT HEATING Radiant heating is intended to control the rate of radiant heat loss from the human body and should be measured by calorimetric methods. , The apparatus for this purpose consists essentially of - a cylinder, maintained at the accepted mean surface temperature of the human body, together with an accurate (usually electrical) measuring of the varying rate of heat supply required to maintain this exact temperature. This' instrument, the eupatheoscope, is readily adapted to function like a thermostat so as to turn heat on or off, when the desired temperature of 80 F, or any other predetermined surface temperature of the cylinder, Panel Heating and Radiant Heating______ ________________ , ". 565 decreases or increases as a result of changes in the Operative Temperature. For testing work; the globe thermometer is a useful instrument. It consists of an ordinary mercury thermometer, with its bulb placed in the center of a sphere from 6 to 9 in. in diameter, usually made of thin copper and painted black and sometimes covered with cloth. The temperature recorded by thermometer with its bulb in the center of the sphere is termed the radiation-convection temperature. See Chapter 11. CONTROL OF PANEL AND RADIANT HEATING The effectiveness of any type of control will depend largely on' the time lag of the system. With warm air passing through floor ducts the time lag is usually too long for any kind of room thermostat, in fact a thermo- Fig. 11. Effect of Height Upon Radiation Received from a Panel Fig. 12. Typical Panel and Radiant Heat Control System stat will not.prove suitable with any system if the building is constructed with massive brickwork and masonry, unless it operates in conjunction with a time control responsive to changes in outside conditions. , The heat emitted by hot water pipes imbedded in the plaster of the ceiling and walls or in the concrete base of a floor can be effectively con trolled by an instrument designed to modulate the temperature of the water circulating in the system according to the outside conditions. Metal panels which can be installed in the ceiling or side walls may be either controlled by an instrument responsive to outside weather con-' ditions or by a. specially designed instrument responsive to both air temperature and radiation. Any purely on or off control system is not recommended for panel heating. A typical control system operated from an outside thermostat and supplemented with a room heat control instrument is illustrated in Fig. 12. . The outside thermostat modulates the temperature of the' circulating water in the .coils by mixing some of the hot water leaving the boiler with a proportionate amount of return water which is diverted to the three-way valve. ` " '^ 566 CHAPTER 31 '' . .1946.Guide. One type of room instrument consists of a blackened, copper-sphere of 6 or 8 in. in diameter, in which a cylindrical sump contains.a volatile . . ' ` liquid. A small electric heating coil creates in the.sphere a vapor .pressure ~ which remains constant as long as the. total heat loss.from the sphere is at the desired rate. If .the Operative Temperature becomes ;too high for comfort, a greater vapor pressure results from the smaller heat loss from : ' the sphere. This acts on a diaphragm and reduces the supply of heat to the room. With too low an Operative Temperature the reverse action ; * `. occurs. A similar instrument which has an electric, heating element for . warming the air inside the sphere and the thermostat operated switch is also used for controlling room conditions. ' In addition to a thermostatically controlled device for modulating the temperature of the circulating water, it is advantageous to. insert in.each ' , coil a locked flow control or adjustable resistance to give uniform con ditions throughout all rooms. Owing to unforeseen difficulties with varying frictional losses in pipes, emission factor, and exposures, it is an advantage to be able to regulate permanently the flow through each circuit by means of a key operated valve as indicated in Fig. 4. . - REFERENCES Standard Operative Temperature, A Generalized Temperature Scale, Applicable to Direct and Partitional Calorimetry, by A. P. Gagge.(American Journal Physiology, 1940, Vol. CXXXI, p. 93). Physiological Reactions and Sensations of Pleasantness Under Varying Atmospheric Conditions, by C.?E. A. Winslow, L. P. Herrington and A. P. Gagge (A.S.H.V.E. Transactions, 1938, ,Vol. 44, p. 190). The Influence of Air Movement Upon Heat Losses from the Clothed Human Body. by.C.-E. A. , Winslow. A. P. Gagge and L. P. Herrington (American Journal,Physiology, 1939, Vol. CXXVII. p. 505). *--Surface.Heat Transmission, by R. H. Heilman (A.S.M.E. Transactions, Fuels and Steam Power Section, Volv51,.No. 22. September-DecembeT, 1929). 1 .' ' BIBLIOGRAPHY . , , Trend Curves for Estimating Performance of Panel Heating Systems, by B. F. Raber . and F. W. Hutchinson (A;S.H.V.E. Transactions, Vol. 48, 1942, p. 425). _ ', A.S.H.V.E. Research Report No. 1192--Panel Heating and Cooling Performance Studies, by B. F. Raber arid F. W. Hutchinson (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 35).. .. ., A.S.H.V.E. Research Report No. 1193--Radiation as a Factor in the Feeling of Warmth in Convection, Radiator and Panel Heated Rooms, by F. G. Houghten, Carl . Gutberlet and E. C. Hach (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 55). . .. Panel Heating arid- Cooling Analysis, by B. F. Raber and F. W.' Hutchinson (A.S.H.V.E. Transactions, Vol. 47, 1941, p. 285)., *, . ; . ' Operating Results of a Residence Radiant Wall Heating System, by-E. J. Rodee * . . (A.S.H.V.E. Transactions, Vol. 47, 1941, p. 123). , , Performance of a Residential Panel Heating System, by. H. F. Randolph and J. B. - Wallace (A.S.H.V.E. Transactions, Vol. 49, 1943, pi 235). ^- Radiant Heating {Heating and Ventilating, March, 1941, p. 35). ,. Radiant Heating and Cooling, by F. E. Giesecke (Heating, Piping and Air Condi tioning, June, July, August, September and October, 1940); . `, . . Calculations for Radiant Heating, by ,T. Napier Adlam (Heating and Ventilating, October,1931). .. ' Radiant'Heating and Cooling, Part I, by C. 6. Mackey, L. T. Wright, Jr:, R--E. Clark, and N. R. Gay (Cornell University Engineering Experiment Station, Bulletin No. 32, 1943). ". . , ` ^ , V. CHAPTER 32 and . Classification, Performance, Fan Efficiency, Characteristic Curves, System Characteristics, Selection of Fans, Fan Designations, Control, Motive Power IN heating, ventilating, and air conditioning practice, fans and blowers are used to produce air flow. All fans or blowers are classified according to the direction of air flow through the fan with relation to the axis of rotation and are either of the (1) axial flow or propeller type, in which the flow is parallel to the axis, or (2) radial flow or centrifugal type, in which the flow is at right angles to the axis. , Axial flow fans are made in various designs and sizes. The form and number of blades may vary for impellers of the same or different diameters. The blades may be of uniform thickness and made of cast or sheet metal, and either flat or cambered or of screw form; or they may vary in thick ness, in the latter case usually being designed to conform to so-called airfoil sections of known characteristics, similar to those which have been developed for airplane propellers. Likewise, blade angle, or the angular relation of the blades to the plane of rotation, varies over a wide range. For operation against comparatively high pressures, it is customary to resort to enlarged hubs in proportion to fan diameter (large hub ratio) and correspondingly short blade length. The term disc fan has some times been loosely applied to such large hub fans, though it has long been generally used in connection with any propeller fan of comparatively short axial length whose blades are relatively .flat; in other words, for fan wheels which occupy a space which is more or less disc-shaped. Single stage air foil axial flow fans can operate at pressures up to 4 in. at a. quite low noise level and, at considerably higher pressures, they are. comparable in regard to noise to the centrifugal fan type. Radial flow or centrifugal fans used in hearing, ventilating, and air conditioning practice, are m general of two types; one with forwardsloped blades, and the other with backward-sloped blades. Many modi fications may be made in the proportions, the curvature, and the slope or. angularity of the blades. The slope or angularity of the blades deter mines the operating characteristics of a fan; a forward-curved or sloped blade is found in a fan having low speed operating characteristics, while a backward-curved or sloped blade is found in a fan having higher speed operating characteristics. '' A wide variety of heating, ventilating, and air conditioning systems creates a wide variety in the demands that have to be met by the fan or blower. The requirement may be to move small or large quantities of air against little or no resistance, or to move small or large quantities of air against higher resistance. Between the two limits innumerable specific requirements must be met. Although fans of any class in either of the two general types can in general be made to perform the same duty,. mechanical difficulties, space and noise limitations, efficiency and power, limitations usually determine the selection. FAN PERFORMANCE Fans of all types follow certain laws of performance which are useful . in predicting the effect upon performance of changes in the conditions of operation, the duty .required of the installation, or the size of the equip . 567 . 563 CHAPTER 32 1946' Guide ment due to the space, power, or speed limitations. The following laws in which Q = air volume and P = static, velocity or total pressure, apply to all types of fans: .. 1. Variation in Fan Speed: Constant Air Density:--Constant System (a) Q: (b) P: (c) Power: Varies as fan speed. Varies as square of fan speed; Varies as cube of fan speed. 2. Variation in Fan Size: ^ Constant Tip Speed--Constant Air Density Constant Fan Proportions--Fixed Point of Rating (a) Q: (b) P: (c) RPM: . . (d) Power: Varies as square of wheel diameter. Remains constant. Varies inversely as wheel diameter. Varies as square of wheel diameter. 3. Variation in Fan Size: At Constant RPM--Constant Air Density Constant Fan Proportions--Fixed Point of Rating (a) Qx Varies as cube of wheel diameter. . (b) P: . Varies as square of wheel diameter, (e) Tip Speed: Varies as square of wheel diameter. (d) Power: Varies as filth power of diameter. 4. Variation in Air Density: ' 'Constant Volume--Constant System Fixed Fan Size--Constant Fan Speed () Q: . () P: (c) Power: Constant. Varies as density. * Varies as density. . 5. Variation in Air Density: Constant Pressure--Constant System Fixed Fan Size--Variable Fan Speed . (a) Q: (6) P: . . (c) RPM: (<Q Power: Varies inversely as square root pf density. Constant. Varies inversely as square root of density. . Varies inversely as square root of density. 6. Variation in Air Density: Constant Weight of Air--Constant System Fixed Fan Size--Variable Fan Speed. () Q: () P: . (c) RPM: .(d) Power: Varies inversely as density. Varies inversely as density. x Varies inversely as density. Varies inversely as square of density: . . .,, . .. Examples 1 to 4 illustrate the application of the preceding fan laws. Example 1. A certain fan delivers 12,000 cfm at a static pressure of 1 in. of water When operating at a speed of 400 rpm and requires an input of 4 hp. If in the same installation 15,000 cfm are desired, what will be the speed, static pressure, and power? Speed = 400 X = 500 rpm 500\2 , (400/ " Power = 4X (jjjj?)3 = 7.81 hp.' ` 'n` ' * . Example 2. A certain fan delivers 12,000 cfm at 70 F and normal barometric pressure (density 0.075 lb per cubic foot) at a static pressure of 1 in. of water when operating at ' Fans 569 400 rpm, and requires 4 hp. . If the air. temperature is iricreased to 200 F (density 0.0602 lb) and the speed of the fan remains the same, what'will'be the static pressure and power? ` . 'L ` . eS.tatic pressure %= 1 .^X 0.0602 q *= A0.8on0 in. . . ,. Powers 4 X = 3.20 hp . ' .. Example S. If the speed of the fan of Example 2 is increased so as to produce a static pressure of 1 in. of water at the 200 F temperature, what will be the speedj capacity, and power? y - ' iSpeed = 400 X 0.075 0.0602. 446 rpm Capacity = 12,000 X 0.075 13,392 cfm (measured at 200 F) Power = 4 V 0.0602 0.075 4.46 hp. 0.0602 Example 4. If the speed of the fan of the previous examples is increased so as to deliver the same weight of air at 200 F as at 70 F, what will be the speed, capacity, static pressure, and power? Speed = 400 X = 498 rpm Capacity = 1_ 2,000 X U.UOU2 " 14,945 cfm ;(measured at 200 F) Static pressure = 1 X 0.075 0:0602 1.25 in. Power M X (^|)2 - 6.20 hp. Laws of Homologous Fans . 4 The laws applying to different sizes of homologous fans are as follows: . Capacity varies as the ratio of size cubed, times the ratio of the rpm. ' Pressure varies as the ratio of size squared, times the ratio of the rpm squared. ` Horsepower varies as the ratio of the size to fifth power, times the ratio of the rpm cubed. ' Example 5. Assuming that a fan with a 36 in. diameter blast wheel will deliver . 12,000 cfm at 70 F at 1 in. static pressure, requiring 4.0 brake hp when operating at 400 rpm, what is the capacity, pressure and horsepower of a homologous fan having a 45 in. `wheel at the same speed? ... Capacity = (||)3 X X 12,000 = 23,400 cfm , Static Pressure -- X (^qq^ X 1 = 1.56 in. : Horsepower = (||)6 X (^)3 X 4 = 12.2 hp ' . . FAN EFFICIENCY The efficiency of a fan. may be defined as the ratio of the horsepower.' output to the horsepower input. . . \ The horsepower output is expressed by the formula: ' . ,- 570 CHAPTER 32 1946 Guide Air Horsepower1 cfm X total pressure in inches of water . 6356 (1) When the static pressure is used in the computation in place of total pressure it is assumed that this represents the useful pressure and that the velocity pressure is lost in the piping system and in the air which leaves the system. Since in most installations a' higher velocity exists at the fan outlet than at the point of delivery into the atmosphere, some of the velocity pressure at the fan outlet may be utilized by conversion to static pressure within the system, but, owing to the uncertainty of friction ,losses which occur at the places where changes in velocity take place, the amount of velocity pressure which is actually utilized is seldom known, and the static pressure alone may best represent the useful pressure. In the standards for published capacity tables as adopted by the National Association of Fan Manufacturers, the term static pressure refers to the true resistance to air flow. Such tables charge both the inlet and outlet velocity of the fan to the fan performance, and may be used directly where the static pressure of the system as calculated represents only the actual resistance to flow of the air. ' The efficiency based upon static pressure is known as the static efficiency and may be expressed as follows: ' Static Efficiency1 = cfm X static pressure in inches of water 6356 X Horsepower input (2) Different fans may develop the same capacity against the same static ` pressure and with the same power input, and therefore operate at the same static efficiency, while maintaining different outlet velocities. Where a high outlet velocity is desirable or can be utilized effectively, the static -efficiency fails to be a satisfactory measurement of the performance. In many applications of propeller fans, air is circulated without encountering resistance and no static pressure is developed. The'static efficiency is zero and its calculation is meaningless. Because of such situations where the static efficiency fails to indicate the true performance, many engineers prefer to base the calculation of efficiency upon the total pressure.. This efficiency is variously known as the total, or mechanical efficiencyf and may be expressed as follows: .' '_ ' ,M,e__c,han.ica,l or _Tota,l _E_ffic.iency,1 = c--f-m-----X--,tt--o,ta--l--p--r-e--s--s-u--r-e---i-n----in--c- ,h--e--s--o--f---w--a--t-e--r. 6356 X Horsepower input (..3.). \ CHARACTERISTIC CURVES In the operation of a fan at a fixed speed- the static and total efficiencies vary with any change in the resistance which is imposed. With different designs the peak of efficiency occurs when the fans deliver different per centages of their wide-open capacity. Variations in efficiency accompany . variations in pressures and power consumption which are characteristic of the individual designs and which are influenced particularly by the shape 'and angularity of the blades. Such variations in pressure, power, and : efficiency are shown by characteristic curves. . Characteristic curves-of fans based upon tests performed in accordance, with the Standard Test Code for Centrifugal and Axial Fans1 prepared jointly by the American Society of Heating and Ventilating Engi neers and the National Association of Fan Manufacturers are generally plotted to show total and static pressure, mechanical and static efficiency, and horsepower in relation to air delivery as a basis. Results may alk> - Fails . ' . 571 ' . Fic. 1. Operating Characteristics of Axial Flow Airfoil Type Fan be plotted against per cent of wide open volume or discharge. Examples < of fan performance curves are shown in Figs. 1, 2 and 3. In the selection of all but very small fans, power consumption is usually. a major consideration. It must be borne in mind that the horsepower at . peak efficiency alone may be misleading, as actual operation is apt to occur at some point on the pressure-volume curve varying considerably from that specified, due to inaccuracies of the estimated system resistance or to fluctuating resistance caused by damper or louver.adjustments. To ' cope with such variations a fan should be selected having a high efficiency over a wide range, that is, aflat or broad efficiency curve is more desirable than.a sharp or narrow curve which, though reaching a high, peak, falls off rapidly to either side of a narrow range. When the point of operation' varies only within narrow limits and both volume and pressure require ments are' accurately known in. advance, the designer can select a fan operating at maximum efficiency, irrespective of performance over' the entire range. ' Fig. 2.- Operating Characteristics of a Fan with Blades Curved'Forward - /. 5722 . CHAPTER 32 1946 Guide Generally, fans are selected either at the peak of the static efficiency or to the right of the peak depending on the requirements of the particular installation. Fans selected to the right of the peak will be smaller but will require more power, run at higher speeds and may have a higher sound rating. Where first cost is important and added horsepower and noise are not important, smaller fans may be used. Where efficient and quiet opera tions are most important, fans are selected at or near the peak of the static efficiency curve. Fans are not ordinarily selected to the left of the peak of the static efficiency curve as this results in larger, more costly fans, requiring more power and in some cases producing objectionable noise. . The curves in Figs. 1, 2, and 3 show operating characteristics for axial flow and two classes of centrifugal fans, namely, forward-curved multiple blade and backward-inclined blade design, for comparison purposes. These curves are not applicable for rigid comparison or actual selection, but are shown to indicate variations in operating characteristics. ' i . Fig. 3. Operating Characteristics of a Fan with Blades Curved Backward The curves in Fig. 1 of a typical axial flow fan show characteristics of non-overloading horsepower and high efficiency. These results are obtained by producing a more uniform pressure throughout the blade annulus, so that back flow does not occur except at high pressures. This avoidance in turbulence has a tendency to reduce noise. Fans of this type are operating against static pressures as high as 4 in. water. The capacity and efficiency of axial flow fans when operating above the low pressure range can be improved by the use of either inlet or outlet guide . vanes or both.' The effect of such vanes is to increase the level of the pressure volume curve, and properly designed vanes on the discharge side of the fan have the advantage of eliminating the rotational component of the air stream, thus restoring uniform axial flow. As high pressures usually require large hubs in proportion to the fan diameter, performance is improved by the use of round-nosed or conical forms mounted co axially with the direct-connected fail (sometimes partly or wholly en- closing the motor) so as to make the changes in velocity to and from the fan blade annulus as uniform as space conditions permit. When axial flow fans are installed in ducts, provisions may be made to instair the, driving motor outside the duct by employing slots in the duct to permit Fans 573 a belt drive from the motor to the fan sheave, or by extending the shaft for a direct-connected motor placed outside of a Y fitting or elbow in the ' duct system. The forward-curved multiblade fan and the backward-curved type are used extensively in heating, ventilating, and air conditioning work. The forward-curved type has a low peripheral speed and a large capacity. (See Fig. 2.) The point of maximum efficiency for this fan occurs near the point of maximum pressure. The static pressure drops consistently from the point of maximum efficiency to full open operation. The power curve rises continuously from low to peak capacity and, if reasonable care is exercised in calculating resistance, a moderate reserve in power in the motor selection will prevent overloading. The backward-sloped type includes the full backward-curved blade and , the double-curved blade having a forward-curved heel and a backward- curved tip. This type has steep pressure curves, non-overloading power characteristics, and relatively high speed (see Fig. 3). This fan operates at a peripheral speed approximately 175 to 200 per cent of that of the forward-curved multiblade fan for like performance. Pressure curves for . this type begin to drop at very low capacity, with the most rapid drop, beginning at about 60 per cent of wide open volume. The steep portions of the pressure curves tend to produce nearly constant capacity under changing pressures. Where wide fluctuations in demand occur, especially where the regulation is obtained by damper control and particularly through by-passes, this type of fan is desirable to prevent overloading of motor. The maximum power requirement occurs at about the maximum efficiency. Cpnsequently a motor selected to carry the load at this point will be of sufficient capacity to drive the fan over its full range of capacities at a given speed. The high speed of this type makes it adaptable for direct connected electric motor drives. The dimensional bulk is usually greater than that of the forward-curved multiblade type. . Between the extremes of the forward and backward curved blade type centrifugal fans there exists a number of modified designs differing in angularity and in the shape of the blades. Characteristic curves of these .types show varying degrees of similarity to the curves in Figs- 2 and 3. SYSTEM CHARACTERISTICS Any ventilating system consisting of duct work, heaters, air washers, filters, etc., has a system characteristic which is individual to that system and is independent of any fan which may be applied to the system. This characteristic may be expressed in curve form in exactly the same manner that fan characteristics may be shown. Typical system characteristic curves are shown as A, B and C in Fig. 4. These curves are drawn to follow the simple parabolic law in which the static pressure or resistance: to flow of air varies as the square of the volume flowing through the system. Heating and ventilating systems follow this law very closely and no serious error is introduced by its use. .' When a constant speed fan curve for a given size fan is super-imposed upon a system characteristic curve, the relation between the two is at once apparent. The only point common to the two curves is the point at the intersection of the system characteristic curve and the fan character istic curve, and it is at this point that the combination will operate. In Fig. 4, system characteristic curves A, B and C cross the fan character istic curve at points X, Y and Z. The fan whose curve is shown, when 574- ' CHAPTER 32 1946 Guide applied to systems having characteristic curves A, B and C, will deliver . 10,000, 13,000 or 16,400 cfm respectively. . , -The curves in Fig. 4 also illustrate the effect of errors which may be made in calculating the resistance of a ventilating system. For instance, if a given system requires 13,000 cfm and the resistance to flow of the system has been computed as 1.25 in. static pressure, such a system would be represented by system characteristic curve B in Fig. 4. If a 100 per cent error had been made and the resistance were 2.5 in. instead , of 1.25 in., then the system characteristic would be as shown in curve A and would cross the fan curve at 10,000 cfm. Such an error would cause the flow of air to be decreased from a design volume of 13,000 cfm to 10,000 cfm. If the resistance to flow had been over estimated and Fig. 4. Parabolic System Characteristic Curves the resistance actually were ,0.625 in., the system characteristic curve would be as shown in curve C and the fan would deliver 16,400 cfm to the system instead of the design volume of 13,000 cfm. In this example extreme errors have been selected to emphasize the' effect the square function of the system characteristic has in maintaining the fan. performance within comparatively narrow limits. In,the first example a system estimated at half what it should have been, resulted in a drop of 23 per cent in volume; and in the second example; a system estimated at twice what it should have been resulted in an increase of 26 per cent in volume. . .. '. . . In . some instances fans may be applied to variable flow systems. In such cases' the limiting systems may be plotted and the effect on fan ' performance examined. For instance, a system might have a'character- . istic curve between A, shown in Fig. 4, as one limit, and B as the other ' limit. The. fan performance will then fall between points X and Y on the fan curve at a point determined by the system characteristics at that Fans 575 ' particular time. If A and B are the limiting characteristic curves of the systems, the fan performance will never .be .outside the points X or Y.' SELECTION OF FANS The following information is required to select the proper type of fan: 1. Cubic feet of air per minute to be moved. 2. Static pressure required to move the air through the system. 3. Type of motive power available. 4. Whether fans are to operate singly or in parallel on any one duct. ` 5. What degree of noise is permissible. 6. Nature of the load, such as variable air quantities or pressures. . - '' ; ; * .f -' . . '; In order to facilitate the choice of apparatus, the various fan manu- ' . facturers supply, fan tables or curves which usually show the following - factors for each size of fan operating against a wide range of static ` pressures: (1) volume of air in cubic feet per minute (68 F, 50 per cent . ' , relative humidity, 0.075 lb per cubic foot), (2) outlet velocity, (3) revo- . lutions per minute, (4) brake horsepower, (5) tip or peripheral speed, and ; , , . (6) static pressure.' The most efficient operating.point of the fan is : " usually shown by either bold-face or italicized figures in the capacity ' . tables. , . Other important factors to be considered in selecting fans are: (1) efficiency, (2) space occupied, (3) sound emission, (4)'first cost, and (5) speed (both peripheral and revolutions per minute). These factors are not necessarily shown in the order of importance. In some installations space occupied may be' of first importance. In others lowest power consumption is desirable. In many cases quietness of operation of the entire system is essential. Practically all fans operate at their lowest sound level when selected at or near the peak of the static efficiency , so that in selecting a fan for highest static efficiency the quietest operating ' range of the fan will also be obtained. Table 1 shows desirable outlet velocities and tip speeds, or peripheral velocities, for various static , pressures. Fans selected accordingly will operate at or near the peak of . , ; ' . -. . . . Table 1. Good Operating Velocities and Tip Speeds for Multiblade .-- ' '' Ventilating Fans Static Pressure'Inches of Water Forward Curved Blade Fans Outlet Velocity ` Feet per Minute Tip Speed Feet per Miaute K % Yi y& % Vs i m 1 'A m 2 . 2M 2)4 '3 . . ' 1000-1100 1520-1700 1000-1100 1760-1900 1000-1200 1970-2150 1200-1400 2225-2450 1300-1500 . 2480-2700 1400-1700 . 2660-2910. 1500-1800 ; ' 2820-3120 1600-1900 3162-3450 . 1800-2100 3480^3810 1900-2200 3760-4205 2000-2400 4000-4500 2200-2600 4250-4740 2300-2600 4475-4970 2500-2800 4900-5365 Backward Tiffed and Double Curved 4 Blade Fans Outlet Velocity _ Tip Speed % Feet per Minute ' Feet per Miaute ' 800-1100 . 800-1150 900-1300 1000-1500 1100-1650 1200-1750 1200-1900 1300-2100 1400-2300 1500-2500 1600-2700 1700-2800 1800-2950 2000-3200 2600-3100 . 3000-3500 34004000 38004500 ,4200-5000 4500-5300 4800-5750 5300-6350 5750-6950 . 6200-7550 . 6650-8050 7050-8550, 7450-9000 8200-9850 576 CHAPTER 32 1946 Guide the. static efficiency with resulting low power consumption,and noise levels. Smaller Ians with higher outlet velocities may be used if the installation requirements are such as to warrant the additional power and increased sound level. When space for duct expansion from a fan outlet is not available there may be advantages in selecting a larger fan for reducing duct noises, although lower outlet velocities generally result ' in lower fan efficiencies which cannot always be justified on the basis of increased cost and space requirements. Fans for schools, churches, residences, and all public buildings should be selected for lower outlet, velocities and tip speeds than would be required for other types of in stallations. ' Having selected a fan for its quietest operating point consistent with the requirements of the installation, it must be recognized that ventilating fans, even so selected, emit noise and precautions must be taken in the installation of the fans to prevent this noise from being transmitted to occupied portions of the building. Fans operating against high static pressures produce more noise than fans operating against low static pressures. Consequently, from a' noise standpoint, the system should be designed to operate against the lowest static pressure possible. In many modern air conditioning systems it is necessary to introduce devices into ' the air stream for conditioning the air in various ways, the result of which is to set up a rather high static pressure against which the fan must . operate. In such cases the sound level at the fan may be too high to be neglected and special sound treatment of the installation must be con sidered. When a fan is operating against higher pressures it should be located in a room either removed from the occupied areas, or in a room which has been acoustically treated to prevent sound bding carried through the walls to adjoining spaces. The fan should be mounted oh a resilient base along with its driving motor to absorb any noise or vibration which' might be transmitted, to the floor and thence to the building structufc. All ducts should be connected to fans with unpainted canvas, or other flexible material, to prevent any vibrations being transmitted to the duct work. Ducts leading into the fan ropm or from the fan should be acoustically treated on the interior and in special cases should be pro vided with sound traps or filters. Many ventilating systems encounter noises which are connected with the fan in no way. Noises due to high duct velocities, abrupt turns, grilles, etc., may be present. Treatment of such problems is covered in Chapter 42. If double width, double inlet fans are selected, care must be taken that both inlets have the same free area. If one inlet ,of a fan is obstructed more than the other, the fan will not operate properly, as one half of the wheel will deliver more air than the other half. Proper installation and location of fans is as important as the selection of the size of fan for that particular, installation. All fans will work according to their character istic curves if they are properly selected and properly installed and operated. . ... FAN DESIGNATIONS In order to prevent misunderstandings, which may cause delays and losses, the arrangements of fan drives adopted by the National Association of Fan Manufacturers and indicated in Fig. 5 are suggested. Facing the driving side of the fan, blower, or blast wheel, if the proper direction of rotation is clockwise, the fan, blower, or. blast wheel will be designated as clockwise. If the proper direction of rotation is counter-clockwise, the designation will be Counter- Fans 577 578 CHAPTER. 32 1_________ ' -_______ 1946 Guide clockwtse. (The driving side of a single inlet fan is considered to be the side opposite the inlet regardless of the actuaMocation of the drive.)1 ' `This method of designation will apply to all centrifugal fans, single or double width, and single or double inlet. Do not use the word hand but specify clockwise or counter- clockwise. . '. The discharge of a fan will be determined by the direction of the line of air discharge and its relation to the fan shaft, as follows: Bottom horizontal: If the line of air discharge is horizontal and below the shaft. Top horizontal: If the line of air discharge is horizontal and above the shaft. Up blast: If the line of air discharge is vertically up. Down blast: If the line of air discharge is vertically down. All intermediate discharges will be indicated as angular discharge as follows: . Either top or bottom angular up discharge or top or bottom angular down discharge, the smallest angle made by the line of air discharge with the horizontal being specified. Fig. 6 shows the names and definitions of types of fans recently dis tributed by the National Association of Fan Manufacturers *. ' FAN CONTROL - In some heating and ventilating systems it is. desirable to vary the volume of air handled, by the fan, and this may be accomplished by a number of methods. Where the change is made infrequently, the pulley Propeller Fan ; \ A propeller fan consists of a propeller or disc type wheel within a mounting ring or plate and including driving mecha nism supports either for belt drive or direct connection. . . Tubeaxial Fan A tubeaxial fan consists of a propeller or disc type wheel within a cylinder and including driving mechanism supports either for belt drive or direct connection. . Vaneaxiat Fan .. A vaneaxial fan consists of a disc type wheel within a cylinder, a set of air guide vanes located either before or after the wheel and including driving mechanism supports either for belt drive or direct connection. ` Centrifugal Fan ' A. centrifugal fan consists of a fan rotor or wheel within-a scroll type of housing and including driving mechanism sup ports either for belt drive or direct connection.... ' Fig. 6.- Names and Definitions of Types of Fans Fans 579 or sheave on the driving motor, or fan, may be changed to vary the speed . of the fan and alter the air volume. Dampers may be placed in the duct .system to vary the volume. Variable speed pulleys or transmissions, such ' as fan belt change boxes, electric or hydraulic couplings, may bemsed to vary the fan speed. Variable speed motors and variable fan inlet vanes . may also be used to adjust the fan volume. All of these methods will give control. From a power consumption standpoint, a reduction of the fan speed is most efficient. Inlet vanes save some power and dampers save ` the least.. From the standpoint of first cost, dampers usually are the: : lowest in cost. In some installations adjustments of volume are desirable - at various times during the day or continuously. In others an increased supply of,air in summer over that needed in winter is demanded. The. demands of each case will dictate which- type of control is most desirable. .Where noise is a factor, lowering the fan speed if possible is preferred as a . control means, because of the resulting reduction in sound level. .. MOTIVE POWER Heating, ventilating and air conditioning fans are usually driven by. electric motors, although other prime -movers may be used. The small sizes of fans, and especially those operating in the higher speed range, are equipped with direct-connected motors. For larger size fans and those . operating at lower speed V-belt drives are generally used. In selecting' the size of motor for operating a fan, it is advisable to select at least the standard size next larger than the fan requirements. Direct-connected motors do not require so great a safety factor as belted units. Justification for liberal power provision exists only in systems where it is possible that larger volumes of air may be required at intervals and made available by use of by-pass dampers, thus greatly reducing the system resistance. If such a system includes a fan with forward-curved ; blades, it would be necessary that the motor be sized for the maximum . volume and duty. If such a system includes fans with backward-curved blades, the volume peak would not make it necessary to provide addi- . tional motor power. In selecting ferns for such a system, sound ratings should be given careful consideration. .' Where a system is constant, and has no provision for volume change . that would materially reduce the resistance, and when the resistance " calculations are reasonably accurate, there is no necessity for too liberal a motor allowance, even where fans with forward-curved blades are used, if the fan has been properly selected. Fig. 4 shows that the system resistance varies as the square of the volume and the fan static pressure varies approximately inversely as the volume, thus greatly offsetting the trend toward both increase in air. delivery and motor load. Reference to. . Fig. 4 indicates that there is no justification for allowing large spare . motor capacity, and it is generally more economical to operate motors . well loaded. . '' REFERENCES . i-See Standard Test Code for Centrifugal and Axial Fans. 3rd Edition, 1938. Bulletin No. 103, National Association of Fan Manufacturers. ' ''' a--Recommendations adopted by the National Association of Fan Manufacturers. . s *--Supplement No. B to Form X-12,`National Association of Fan Manufacturers.. . '' BIBLIOGRAPHY Mine Ventilation, by J. J. Walsh'(A.S.H.V.E. Transactions, Vol. 23, 1917, p. 659). Fan Blower Design, by H. F. Hagen (A.S.H.V.E. Transactions, Vol. 28,1922, p. 175). S' ' Ill 580 __________ CHAPTER 321946 Cuide The Specific Characteristics of Fans, by M. C. Stuart and J. B. -Lusk (A.S H V E Transactions, Vol. 43, 1937, p. 57). ,. ' . Non-Dimensional Fan Characteristics, by H. Carlton Moore (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning, September,. 1937, p. 580). Fans, by Theodore Baumeister, Jr. (McGraw-Hill). - . Fan Engineering, Buffalo Forge Co: - ,,Y,e,ntila,,ti^ga"d Air Conditioning, by Harding and Willard, Revised Edition, ' 1932 (John Wiley & Sons). . .. The Centrifugal Fan, by Frank L. Busey (A.S.H.V.E. Transactions, Vol. 21, 1915, p. 43). The Theory and Performance of Axial-Flow Fans, by L. S. Marks and J. R. Weske. The Axial Flow Fan and.Its Place in Ventilation, by W. R. Heath and A E Criaui (A.S.H.V.E. Transactions, Vol. 50, 1944). -H The Centrifugal Pumps and Blowers, by A. H. Church (John Wiley & Sons). CHAPTER 33 -Jlir C^iean inej. obevicei Air Cleaners, Dust and Lint, Classification of Air Cleaning ' Media, Viscous Impingement Type Cleaners, Automatic Viscous Filters, Dry Air Filters, Electric Precipitators, Per formance and Testing, Selection and Maintenance, Safety Requirements, Adsorption oi Vapors . , F)R the purposes of this discussion, an air cleaner is defined as.a device for capturing and removing solid matter from a stream of air. This solid matter includes fibrous material such as lint as well as particulate matter such as dust, fumes, smoke, cinders, etc. Air cleaning is distinct from air purification in that the latter deals with removal of harmful or unpleasant gases, vapors, or bacteria from an occupied space. Air pollution and purification are discussed in Chapters 10 and 12 and air sterilization in Chapter 13. ' . In general, air cleaners are not installed in buildings for the specific purpose of improving the health of the occupants. However, the removal of matter such as pollen, house dust and similar allergens which motivate attacks upon persons of allergic sensitivity*, does have a beneficial effect on health, The toxic elements in some war gases are in reality fine particles capable of air flotation. It is known by experience that air cleaners greatly reduce the rate of dirt accumulation in buildings, but, in the present state of knowledge, an exact numerical expression for the cleaning effect of the filter cannot be given because of the many unknown or variable factors involved. For this reason air cleaners are usually selected on a basis of experience or judgment, guided by the results of various test procedures. AIR CLEANERS ' A typical air cleaner consists of a frame, which may be of metal, wood, cardboard, etc., and a filtering medium. The frame is designed to support the medium in a duct or chamber forming part of the air conditioning or ventilating system, so that the air passes through the medium while en route to spaces to be ventilated. Unit Air Cleaners or Filters Many air cleaners are available in the form of units of convenient size for handling during installation, cleaning or replacement. Such units are usually designated as filters or unit filters. A typical unit filter may be 20 in.' square and from one to several inches thick, depending on the manu- . factiire and proposed use. In large systems, a number of such units are installed adjacent to each other and collectively called a bank of filters. ' . Air cleaners are commonly installed in the outdoor air intake ducts of buildings and, often, in the recirculating air. ducts as wejl. Cleaners are logically placed ahead of heating or cooling coils and other air conditioning equipment in the system to protect them from dust. The character of the dust arrested by the filters in an air intake duct is likely to be mostly particulate matter of a greasy nature, while lint may predominate in dust from within the building. '; - Settling chambers, air washers and electrostatic precipitators are also 581 . 582 CHAPTER 33 1946 Guide' air cleaners. Settling chambers are used in boiler plants for capturing cinders, but they occupy too much space for general use in air conditioning or ventilating systems. Unless they are inordinately large, they are not effective in capturing small particles, since the air velocity is not suf ficiently reduced to permit, such particles to settle. , . Air washers have generally become recognized for the purpose of ad justing the, temperature and humidity of the air, rather than for cleaning air. It happens that insofar as dirtiness is concerned, carbon is the most troublesome dust. Carbon particles are likely to be greasy and since there is a natural repulsion between grease and water, the water spray in an air washer is not effective to a desirable degree in capturing them. However, air washers do capture considerable amounts of dust and lint which become sludge in the sump. Much of the cleaning action occurs at the eliminator plates where the dust particles are thrown against the film of water on the plates by their momentum. The electrostatic precipitator is an effective available means of captur ing the finer dust particles. This device does not entirely displace other types of air cleaners at the present time because of relatively high cost, large space requirements, and the fact that, the air must enter and leave the apparatus in substantially parallel and straight flow. Dust and Lint ,' . - Air-borne solid matter from the viewpoint of air cleaning is con sidered as lint and dust. Some lint originates outdoors, as animal hairj vegetable fibers, etc., but much is generated within buildings by the wear and brushing of fabrics in the form of clothes, draperies, carpets, etc. Lint is comparatively easy to capture in an air filter because of .its comparatively great length. So far,as air filter performance and testing are concerned, lint is chiefly important because of its tendency to impede or stop, the flow of air through the filter. In general, lint, if not captured, will accumulate in corners and under furniture in a building in areas of slight air motion and in some cases may seriously obstruct heating and cooling coils. Dust settles, or is precipitated by heat or air motion, upon furniture, fixtures and walls and the only satisfactory treatment.is washing or re-painting. Dust is more difficult to capture than lint, and, obviously, small particles are more difficult to capture than large ones. ' The air cleaning problem is complicated by the vast difference in size of dust particles, the range of which is shown in Fig. 1, Chapter 10. ' Even if the discussion is limited to the range from 0.1 micron to 50 microns, that is; between the smallest particle observable in the micro scope and the smallest particle distinguishable to the naked eye, this range is so far outside the usual.experience, that it is difficult to visualize. If particles could be examined through a super microscope having a' magnification of 250,000 diameters, a tobacco smoke particle of 0.1 . micron would appear to be 1 in. in diameter, or approximately the size of a golf ball; a soft coal smoke particle 0.3 micron in diameter would appear. |ike a baseball; a ragweed pollen grain 20 microns in diameter would appear 16.5 ft in diameter, while the 50 micron particle, just visible to the naked eye and able to pass through a 270 mesh screen, would appear to be 50 ft in diameter. Picturing this range in particle size from a golf ball to a sphere 50 ft in diameter will emphasize the, difficulty of cleaning air or of devising any single test to adequately measure the performance of air cleaning devices under all conditions of service. ' ` It may be contended that the removal of the finer particles from venti- Air Cleaning Devices 583 lating air is relatively unimportant insofar as cleanliness in a house or building is concerned, since it is possible that such particles may remain suspended in the air and in large part be removed from die building with out settling by the circulating air. However, since-some of the particles are undoubtedly deposited by contact and by thermal precipitation, the ability to remove small particles is desirable in an air cleaner. . The migration of dust particles from a warm region toward a cool surface, to which they will adhere, is called thermal precipitation *. This fact is responsible for the lath marks often observed on walls or ceilings. The laths form barriers to the passage of heat so that the surface of the plaster in front of them is warmer than the surfaces between them. Dust is therefore deposited more rapidly between joists or laths than it .is in-, front of them, resulting in the streaks observed. If the entire ceiling-or. wall is insulated, the differences in temperature across the surfaces cease to exist, lath marks do not form, and deposition of dust is much slower. , A laboratory apparatus has been designed employing thermal precipita tion in capturing dust particles for microscopic examination 3. So far as is known thermal precipitation has not yet been used as a practical means of cleaning air. ., CLASSIFICATION OF AIR CLEANING MEDIA Air cleaners of such a variety of types have been used in the past that a single classification is difficult. Considering the wide diversification of materials and particle sizes to be removed and the varying requirements which have to be met in the field, it is natural that many lands of air cleaning devices are used which cannot be shown satisfactorily in a simple outline. Classifications on three different bases are enumerated herewith: 1. Principle of air cleaning. . a. Viscous-impingement filters. , b. Dry filters. . c. Washers. .. d. Centrifugal devices. " .. e. Electrical precipitators.' - ' . ' , ,. . *. . y 2. Methods of servicing. . . a. Automatic. . . *. b. Norvautomatic. . . (1) Throw-away (replaceable elements). .- . (2) Manually cleaned in place (including one type of electrostatic). .. (3)'Removable for cleaning.' *r ` 3. Classification according to application. * a. General air conditioning. .'(f) Central cleaning system. (2) Unit ventilator. . (3) Window installation. . (4) Warm air. furnace. .. . b. Removal of smoke and fumes from stack gases . ' c. Collection of dusts from exhaust systems. * V. ., VISCOUS IMPINGEMENT TYPE CLEANERS ; * ; The medium in a viscous impingement type filter is usually a, fiber pack for non-automatic types or a series of metal plates .for-automatic-self/ cleaning types. In either case, the medium is treated with ja viscous substance, often an oil ..or grease,calledthe adhesiveor. the saturant, 584 CHAPTER 33. 1946 Guide intended to retain dust particles which come in contact with it. Also, in either case, the arrangement is such that the air stream is broken up into many small air streams and these are caused to abruptly change direction a number of times in order to throw the dust particles, by momentum, against the adhesive. Several desirable characteristics of an adhesive for air cleaners of this type are: 1. Its surface tension should be such as to produce a homogeneous film or coating on the filter medium. 2. The viscosity should vary only slightly with normal changes of temperature. 3. It should prevent the development of mold spores and bacteria on the filter' medium. 4. The liquid should have high capillarity, or ability to wet and retain the dust at all operating temperatures. . 5. -Evaporation should be slight. ' - ' 6. It should be fire resistant. 7. It should be odorless. Various fibrous materials' have been used as filtering media in unit filters of the viscous impingement type. This includes glass fiber, steel wool, similar wool of non-ferrous metals, wire screen, animal hair, hemp fibers, and other materials. In such filters, the medium is often packed more densely on the discharge than on the approach-side in order to increase the dust holding capacity. This results in a selective arrestance of dust with the larger particles nearer the approach face. The arrange ment also permits some penetration of lint into (but not through) the' filter, so that the amount of lint which can be tolerated on the filter is also increased. Due to plane surface area the viscous impingement type filter, however, may be inferior to some dry types where the air carries a. high percentage of lint. The resistance of air filters obviously increases with the air flow through them. Face velocities of about 300 fpm and resistances in the range from 0.1 to 0.2 in. water, when the device is new and clean, are usual for venti lation system filters. Special filters with low resistances are available for use'with gravity warm air furnaces and for other uses where only low pressure is available. '. The resistance of these filters increases with dust or lint loading and it is the resistance due to this cause which ordinarily necessitates servicing. The rate of loading obviously depends upon the amount as well as the kind of dust in the air qnd for this reason, periods between servicing cannot be predicted. Manometers are often installed to indicate the pressure drop across filter banks and they serve to indicate when the filter requires cleaning. The pressure drop tolerated differs between operators and system designs. The resistance of a filter bank can be kept desirably low by periodically servicing some but not all of the units in the bank at one time, providing the difference in resistance between the clean and dirty filters is small. , The method of cleaning yiscous impingement unit filters differs for different types of filters and kinds of dust. Much dry dust or lint can often be removed by rapping the filter. . Throw-away filters are constructed of inexpensive materials and are designed to be discarded after one use. The frame is frequently a com bination .of cardboard and. wire. . Cleanable types usually have metal frames. Various cleaning methods have been recommended including: air jet, water jet, steam jet, washing Air Cleaning Devices 585 in kerosene, and dipping in an oil. The latter may .serve both to clean . the filter and. add the necessary adhesive. . Automatic Viscous Filters In an automatic air filter, means are provided to remove the dust from the medium mechanically. Automatic filters with moving cloth media have been constructed. The media is supported on rollers and moves slowly and continuously across the air stream and then through some cleaning mechanism, such as a beater, a vacuum cleaner, or a brushing arrangement. Such filters, however, `are not now in wide use, possibly, because of mechanical difficulties and the rapid and sometimes permanent increase of resistance caused by oily matter present in the air. The medium in a typical automatic filter at present consists of a series of specially formed metal plates mounted on a pair of chains. The chains are mounted on sprockets located at the top and bottom of the filter housing, so that the filtering medium can be moved as a continuous curtain up one side and down the other side of the sprockets. The arrangement is such that, at the bottom, the medium passes through a bath of special oil which both serves to remove the dirt from the plates and acts as an adhesive when the cleaned plates next pass through the air stream. The plates forming the filtering medium or curtain usually overlap each other and due to their special shape many small air passages are formed between them. These air passages turn abruptly one or more times in order to give the impingement effect. An electrically driven rotating device is usually supplied with an auto matic filter. The device may be set to move the curtain periodically or a special switch, actuated by pressure drop, may be used to govern its motion. Such a switch will cause the gear to move the curtain when the resistance of the filter to air flow becomes excessive and will stop it when the resistance becomes sufficiently low. In operation, the resistance of an automatic filter will remain approxi mately constant as long as proper operation is obtained. A resistance of 1 % in. water at a face velocity of 500 fpm is typical of this class. DRY AIR FILTERS As the name:implies, adhesives are not used on dry air filters. The media in such filters are usually fabrics or fabric-like materials. Media of wool felt, cotton batting (both glazed and unglazed), cellulose fiber and other materials have been used commercially. ' . '. The medium in a filter of this class is usually supported by a wire frame in the form of pockets or V-shaped pleats in order to increase the area exposed to the passage of air. A 2 ft square unit may contain from 15 to 30 sq ft of medium. Dry air filters are likely to have a comparatively high lint-holding , capacity on account of the large area of medium used. Wool felt media are troublesome to clean when impregnated with greasy, dust and they are too expensive to discard frequently. Both vacuum cleaning and dry cleaning have been used for reconditioning wool felt filters. ` ELECTRIC PRECIPITATORS The fact that a particle exposed to an electric field will assume a charge ' and migrate toward one of the electrodes has been utilized for some years ' in boiler plants as a means of smoke abatement. The same principle has 586 CHAPTER 33 1946 Guide- been used in equipment developed for air cleaning in air conditioning without generating ozone in intolerable quantities. The air stream in a precipitator passes first through a relatively high-tension electric field, known as the ionizing field, and then through a secondary field where the precipitation of the dust occurs. The arrangement is as shown in Fig. 1. ' In a typical case, a potential of 12,000 volts may be used to create the ionizing field, and some 5000 volts between the plates upon which the precipitation of dust occurs. These voltages, which are capable of shock to personnel similar to that of a spark plug, necessitate some safety .measures. A typical arrangement provides means for automatically making the unit inoperative when a door to the precipitator is opened. Fig. 1. Diagrammatic Cross-Section of Electrostatic Precipitator To resume operation the procedure necessitates closing the door and turning an electric switch, the latter of which should be located at a reasonable distance from the equipment The voltages necessaty for the operation of the precipitator, are usually obtained from- an alternating. current building service line by means of a step-up; transformer. Precipi tation with alternating current is possible but is not nearly,so. effective; so the cuijent is usually rectified by means of vacuum tubes. The trans former and tubes are collectively termed the power pack. . Only a very small amount of electric energy is necessary to operate an electric precipitator and the resistance to air flow through the device is - practically negligible. Some care is necessary in arranging the duct approaches on the entering and leaving sides of precipitators to assure that the air flow is distributed uniformly over the cross-sectional area. The efficiency of the precipitator is sensitive to air velocity and the . device itself has much less tendency to rectify the air stream than filters. which have much higher resistances. '' ' - . Electric precipitators are available in both automatic and non-auto matic types. The plates of non-automatic precipitators are commonly coated with a light oil as an adhesive. Cleaning is accomplished with, a water hose and, .for this reason; the bottom of the equipment is made - water tight and provided with a drain;: Tn oneautomatic type, precipitar ' . Air Cleaning Devices 587 tion units are mounted on chains and are alternately dipped in oil and. exposed to the air stream with an action similar to that of an automatic, impingement filter.. An arrangement of sliding contacts maintains the necessary electric circuits. ' - . PERFORMANCE AND TESTING The rating of an air cleaner is the air flow'for which it is designedexpressed in cubic feet per minute. Face velocity is defined as the average velocity of the air entering the cleaner, and it is determined by taking theair flow and dividing it by the area of the duct connection to the cleaner in square feet. Cleaners are often rated at a face velocity in the range, of 250 to 500 fpm. The resistance of an air cleaner to air flow is usually measured in inches water. The resistances of filters when new and clean and when operated at rated capacity are generally available from the manufacturer (see. Catalog Data Section). . The ability of air cleaners to clean air is called the efficiency or the arrestance, and may be denoted by the symbol E. The efficiency of an air cleaner differs with the size and nature of the dust on which the cleaner operates, Obviously, large particles and lint are more easily captured than minute particles which are small in-all dimensions. The efficiency of an air cleaner; algebraically expressed, is: . where D, - D, E = Di (i) D, -- amount of dust per unit volume in uncleaned air. D,* amount of dust per unit volume in cleaned air. Several methods have been investigated for evaluating Dl and DtThe particle count method is not used for efficiency evaluation except in investigation of filter performance on specific particles such as pollen or on certain industrial dusts harmful to health. Dust particles can be captured on microscope slides by means of one of the various kinds of impingement devices. The process is useful if an inspection and analysis of dust is desired,- but particle counting is not sufficiently precise for evalu ating the efficiency of a cleaner operating, on- a heterogeneous dust. .-. The weight method of evaluating efficiency has found wide utility andwas recognized by the American Society of Heating and Ventilating Engineers and incorporated in a code *. -For this test, a known weight of a prepared dust is injected into air supplied to the filter and the quantity of dust in the cleaned air is determined by extracting arid weighing the dust from a known volume of the cleaned air. Dust extraction from the air is accomplished by drawing the air through a porous crucible or thimble by means of a high vacuum. The dust-spot or blackness test for cleaner efficiency was developed at the National Bureau of Standards6. The test consists of drawing samples, of cleaned air and of uncleaned air through filter papers simultaneously. The ratio of the areas of paper through which the air samples are drawn and the ratio of the amount of air drawn through the papers are adjusted during successive trials to yield spots of approximately equal, blackness on the papers. The ratios of the areas and of the volumes of the air samples are then indicators of the filter effectiveness. A special photo meter is provided for coriiparing. the blackness or. opacity of the papers by transmitted light. For tests of ordinary air filters by this method, a 588 CHAPTER 33 1946 Guide dust is injected into the air stream. The dust consists of precipitated smoke particles from a Cottrell precipitator used in a local power plant for smoke abatement. For tests of electrostatic air cleaners, no dust is added to the air. Tests are commonly made with the dust existing in the ' air at the location of the installation on a clear day. Some specifications for this type cleaner have required that in dust spots of equal area the downstream spot shall not be any dirtier than the upstream spot when 10 times as much air is drawn through it as is drawn through the.upstream spot. When this condition is met the cleaner is said, to have an efficiency or arrestance of 90 per cent or better on atmospheric air. . . Dust-holding capacity is defined as the amount of dust which a filter can retain and have a resistance less than some arbitrary value. The term applies only to non-automatic air cleaners. Determination of dust holding capacity is an objective of each test under the A.S.H.V.E. Standard Code 4: Curves are obtained during such tests to show the . relation between dust load and resistance. Typical curves are shown in . Fig. 2. Type A is a dense pack used in bacterium control'; Type B is a medium pack used for general ventilation work; and Type C is a low . Air Cleaning^Devices 589 The advantage of the automatic impingement type filter consists in the small amount of attention which it requires. Such devices are therefore to be recommended where labor is scarce or where reliable and frequent, attention to filters cannot be assumed. This type of equipment is not any better in dust arrestance than some unit filters, and it ranks' next to precipitators in first cost. - ,- Unit filters constitute the majority of air cleaners now in use, and some choice is possible between the types available. Where lint in an eminently ` dry state predominates, a dry filter obviously may be preferable to other types on account of its lint-holding capacity. If the lint is greasy or if oil vapor exists in the air, the dry filter, if it is of the cleanable type, may be troublesome, since grease tends to make it difficult to clean. The cleaning difficulty is avoided if a throw-away type of medium is used. Some dry filters are capable of high efficiencies, compared to other unit ' Fig. 2. Resistance to Air Flow of Typical Unit Air Filters resistance unit, for use where low resistance is the important factor and maximum cleaning efficiencies are not essential. . At the National Bureau of Standards two injectors are provided on the air cleaner testing apparatus. One injector is used to contaminate the air stream with Cottrell precipitate, previously described. This dust is used to make both efficiency determination and dust-holding capacity tests. The other injector contaminates the air stream with cotton iinters with which lint-holding capacity tests are made. The curves, in Fig. 3. _ illustrate the difference in the characteristics of two filters, one a viscous- impingement type and the other a dry filter with a cellulose fiber medium. The two injectors can be operated either separately or simultaneously. A -total dust deposit of 4 per cent cotton Iinters and 96 per cent Cottrell precipitate gives a deposit on a filter closely resembling those that occur in Washington, D. C. . SELECTION AND MAINTENANCE : If effectiveness in arresting dust were always the primary consideration, an electrostatic cleaner might be used for all air cleaner installations. Where the dust load is heavy, a filter bank may be installed ahead of. the precipitator. At the present time electrostatic equipment is comparatively expensive and bulky- and is therefore only used when the- expense is justified-by the need for the cleanest air possible. i filters on fine particles, but their dust-holding capacity for such dust may be inferior to that of the viscous impingement type. , Viscous impingement unit filters represent the general type of air cleaner now in use. They have approached standards in size and their overrall dimensions are small when compared with their ratings. . Throw-away units are often installed in .series so that the one in front, which usually becomes plugged with lint, can be discarded after which the downstream unit is moved to the front and replaced by a new unit. Viscous impingement unit filters do nothave efficiencies as high as can be expected with some other types of unit filters, but their first cost and upkeep are generally lower, whether of the cleanable or the throw-away type. They require more careful attention than the automatic oil type if the resistance is to be.maintained within reasonable limits. Safety Requirements ' - An investigation of safety ordinances should be made by the engineer , when: the installation of-an air-cleaner'of any , considerable sizeis*con-: templated. It is possible that a combustible.filtering media may. not be. permitted in accordance with some existing local regulations. .Combus-; 590 CHAPTER 33 1946 Guide. tion of dust and lint on a filtering, medium is possible, though the medium itselfrmay not bum. , :. . ' '...-a- ADSORPTION OF VAPORS OTHER THAN WATER - Many of the foreign gases in the atmosphere are selectively adsorbed; by charcoal. Included are many of the organic gases, such as those' emanating from animals arid people, some of the gaseous constituents of combustion,' alcphols, ketones, esters-, and gaseous products, of putre-, faction. . . ! , . . .. . . .. . ' '? The selective action of ..charcoaj with a mixture of water vapor, and, organic gases is shown in Fig..4.- , ., . Fig. 4. Adsorption at Relative Pressures by. Charcoal of.a Typical Organic ' Gas (A) and Water Vapor (B) ' ' Charcoals differ widely in their adsorptive capacity. Those which have; iriarked adsorption characteristics, such as properly prepared coconut' shell charcoals', are sometimes called activated-charcoals or activated carbbn. These materials can adsorb approximately 50 per cent of their own weight in many organic gases atTO F. : The charcoal may be used for a lorig time by reactivation at high temperatures, under which condition it gives up the adsorbed gases. Temperatures of approximately 1000 F. are desirable for reactivation. Charcoals for use in air handling systems should be able to stand, physical handling,'including reactivation without excessive loss by breakage,or dusting. ... :. ; ; ' As applied in air handling systems/the charcoal is placed in'perforated rnetal coritainers which are grouped in frames arid set in the'air'stream.' . The percentage removal of an organic gas, such as carbon tetrachloride'/ ,is 95 per cent or above when placed in intimate contact with.the carbon at 70 F. In commercial apparatus there may be a by-pass" effect which' depends; on the physical arrangement of therch'arcoal containers. This by-passing:reduces the perceritage .removed;.in ..the.: total .gas. passing through.'the adsorber. Resistance to air flowis usually ;selected. within the'general.range of resistance of impingemerit filters. ; -o>- -,o . Air Cleaning Devices 591 The required quantity ofrecirculated air to be treated is determined . by the requirements for' contaminant-free air, minus the outdoor air, divided by the fraction denoting the percentage, removal of the gas in question in the adsorber bank which is. to be used. " ' ./ Adsorbers may be applied to reduce, objectionable gases entering ; through the outdoor air inlet. They may also-be used to'reduce the odors caused by exhausts from processing. Adsorber beds, in all cases, should be protected from dust, free oil and grease.' .... . ' REFERENCES : ' *--Bronchial Asthma and Allied Allergic Disorders, by S. S. Leopold and C. S. Leopold (.Journal of the American Medical Association, March 7, 1925. Vol.;84. p. 731-734). l- _ --Dirt Patterns on Walls, by R. A. Nielsen (A^S.H.V.E. Transactions, Vol.46. i941, p. 247). --Industrial Dust, by Philip Drinker and Theodore Hatch (McGraw-Hill Co.. New York, N.\Y.). ' 4--A.S.H.V.E. Standard Code for Testing and Rating Air Cleaning Devices Used-in General Ventilation Work (A.S.H.V.E. Transactions. Vol. 39, 1933, p. 225). . s--A Test Method for Air Filters, by Richard S. Dill (A.S.H-.V.E. Transactions, VoL 44, 1938, p. 379). BIBLIOGRAPHY Design and Application of Oil-Coated Air Filters, by H. C. Murphy (A.S.H.V.E. Transactions, Vol. 33, 1927, p. 73). . .. " . Operation and Maintenance of Air Filters, by W. G. Frank (Heating, Piping and Air Conditioning, May, 1931, p. 378). , ... ; , Size and Characteristics of Air-Borne Impurities, by W. G. Frank (Keating, Piping and Air Conditioning, January, 1932, p. 35). . Fundamental Principles in the Design of Dry Air Filters, by Otto Wechsberg (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning, April, 1933, p. 217). . The Economic Factors in Converting Recirculated Air for Ventilation, by H. E. Ziel and Henry Sleik (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning. Juiyi 1943, p- 367). , Operation, Maintenance of Cloth-Screened Dust Collectors, by W. F. Terry {Heating, Piping and Air Conditioning, May, p. 259, June, p. 304, 1933). . Testing and Rating of Air Cleaning Devices Used in General Ventilation Work, by Samuel R. Lewis (A.S.H.V.E. Transactions, Vol. 39, 1933, p. 277). A.S.H.V.E. Research Report No. 1094--Air Filter Performance as Affected by Kind of Dust, Rate of Dust Feed, and Air Velocity Through Filter, by F. B. Rowley and ` R. C. Jordan (A.S.H.V.E. Transactions, Vol. 44, 1938, p. 415). A.S.H.V.E. Research Report No. 1122--Air Filter Performance as Affected by Low Rate of -Dust Feed, Various Types of Carbon, and Dust Particle Size and Density; by F. B. Rowley and R. C. Jordan (A.S.H.V.E. Transactions, Vol. 45,-1939, p. 339).; A.S.H.V.E. Research Report No. 1145---The Effect of Lint on Air Filter Perform ance, by F. B. Rowley and R. C. Jordan (A.S.H.V.E. Transactions, Vol. 46,1940, p. 25). A.S.H.V.E. Research Report No. 1169--Comparison of the Weight, Particle Count > and Discoloration Methods of Testing Air Filters, by F. B. Rowley and R. C. Jordan (A.S.H.V.E. Transactions, Vol. 47, 1941, p. 29). . ^ A.S.H.V.E. Research Report No. 1187--Economical Air Velocities for Mechanical Air Filtration, by F. B. Rowley and R. C. Jordan (A.S.H.V.E. Transactions, Vol. 47, 1941, p. 391). ; A.S.H.V.E. Research Report No. 1218--Overloading of Viscous Air Filters'During Accelerated Tests, by F. B. Rowley and R. C. Jordan (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 437). ' .The Dust-Free Space Surrounding Hot Bodies, by H. H. Watson {Transactions of the Faraday Society, Vol. 32, 1936, Pt: 2, p. 1073). '. . A New Electrostatic Precipitator, by G. W. Penney {Electrical Engineering, January, 1937, p. 159). . . .. Electrostatic Precipitation for Aircraft, by Howard E. Corbitt and Norman J. Clark {Aero Digest, December, 1940, p. 132). '. . '. -Cleaning of Air and Gas by Thermal Repulsion, by Samuel C. Blacktin {Journal Society of Chemical Industry, 68, 1939, p. 334-8, 59, 1940, p. 153-4). ^ 592 CHAPTER 33 1946 Guide . Pointers on Selecting Equipment for Industrial Gas.Cleaning, by C. E. Miller (Ckemi- cal and Metallurgical Engineering, 45, March, 1938, p. 132-5).. ' Electrical Precipitation, by W: A. Schmidt and E. Anderson {Electrical Engineering, ! 57, August,-1938, p. 332-338). . . v' Electrostatic Precipitation for Cleaning Industrial Gases, by H. W. Wagner {Fuel Economist, 10, 1935, p. .895-9,942-5, 971?3). ; *. Dust Precipitation, by M. Pauthenier and Mme. Moreau-Hanot {Electrician, 118, August 10, 1934, p. 187-9). `. Alternating Current Precipitators for Sanitary Air Analysis: II. Acid Formation in Electric-Precipitators, by W. G. Hazard and Tomoyoshi Ishikawa {Journal of Industrial } Hygiene, October, 1932, p. 367-70). ^ Electrical Precipitation, by A. W. SimonJand'L. C. Kron {Electrical Engineering, 51, February, 1932, p. 93-5). The Mathematical Theory of the Cottrell Electric Precipitator, by A. W. Simon {Iron and Steel Engineering, 6, 1929, p. 143-6). , ; . Progress in the Art of Electrical Precipitation Since 1900; by P. E. Landolt {Trans actions American Electrochem.rSodety, 51, 1927). . . Some. Factors and Principles Involved in the Separation and. Collection of Dust, Mist and Fume from Gases, by Evald Anderson {Transactions American Institute of Chemical Engineers, 16, 1924, Pt. 1, p. 69-86). Electrical Precipitation of Solids from Smelter.Gases, by Ross B. Rathbun {Trans actions American Institute of Electrical Engineers, 41, 1922, p. 815). Electrical Engineering Features of the Electrical Precipitation, Process, by G., H. Horne {Transactions American Institute of Electrical Engineers, 41 1922, p. 808). - \ CHAPTER 34 Automatic C^-ontroi Basic Types of Control, Types and Functions of Controllers, Designation of Temperature Control, Automatic Control Terminology, Residential Control Systems,. Control of Auto matic Fuel Burning Appliances, Zone Control, Control of Unit Systems, Control of Refrigeration Equipment, Application of Control Devices to a Typical System ' THE function of automatic control, as applied to the heating, venti lating and air conditioning industry, may be broadly subdivided into the maintenance of temperature, humidity, pressure, and liquid levels within predetermined ranges. It automatically coordinates the operation of the various controlled mechanisms in proper sequence to produce the desired result. A thermostat, for instance, is a controller responsive to temperature which initiates a force that repositions valves, dampers, etc., as required to maintain selected temperatures. Similarly, a hygrostat or humidistat is a controller responsive to relative humidity which initiates, a force that repositions the controlled sources as required to maintain a selected relative humidity. . BASIC TYPES OF CONTROL There are two basic types of controllers, (1) the two-position, on-off, or positive acting controller, which functions to move a valve, damper or electric switch through its full travel (not necessarily 100 per cent) from' open to closed position and vice versa, and (2) the throttling, proportioning, or intermediate acting controller which functions to reposition the valve, damper, or other controlled device by small increments of its total travel as the controller senses a slight change in the controlled condition. The available equipment may be broadly sub-divided into three main groups,. (a) self-contained equipment, (b) electrically operated equipment, and (e) pneumatically operated equipment. Self-Contained Equipment ` In self-contained controllers the primary source of power is the vapor pressure of an enclosed volatile liquid which varies with the temperature changes of the controller bulb. Such pressure changes are transmitted, directly into the bellows or diaphragm mechanism of the controlled . valve. Devices of this type produce gradual operation and are used to regulate the flow of heating and cooling media to coils, radiators, and liquid tanks. Each instrument is designed to operate within a pre determined selected temperature range and for a given condition. Care must be exercised to select a type which has the ability to withstand any. possible over-run, of temperature at the control bulb without damage to the instrument. Instruments of this type are available either with a rigid bulb or with a flexible tubing which connects the control bulb to the head of the instrument. This tubing is usually protected by a flexible metal, covering or armor and is available in varying lengths. . Electrically Operated Equipment ' Electrically operated equipment for either two position control or throt tling control is available in either low voltage or high voltage type. Low voltage equipment usually is designed to operate on 20 to 24 volt current. High voltage equipment may be used, in connection with any of the 593 ~ 594 CHAPTER 34 ______________1946 Guide standard voltages. The individual units of this type of system are inter connected by wiring circuits which carry, the commands of the controller to the motors operating the controlled valves or dampers and to stop and start electric motors driving the controlled.equipment. Simple make and break electric thermostats are used to stop and start motors and for twoposition control of valves and dampers/ Modulating electric control may be accomplished by the unbalancing of some form of Wheatstone bridge which in turn causes the repositioning of a motor element which moves the valve or damper. In some controllers the impulse from more than one Wheatstone bridge can be integrated in one motor element.. Controllers for modulating electric control vary from the contact type in that the electrical mechanism consists of a variable potentiometer.: The potentiometer includes a contact finger which moves across a coil of. resistance wire wrapped on a suitable bobbin.. The contact finger is actuated by a temperature,, pressure, or humidity sensitive element. When the same amount of current is flowing through both coils of a balancing relay the contact blade will be in the center of the space between. tJie two contacts and the motor will be at-rest. .; Changes in the conditions at the controller will affect the circuit so that the amount of current flowing through the two relay/ coils will not be'-, identical. Whenever the current through these two coils becomes un balanced, one of them will become stronger and the U shaped armature will be tilted. The movement of the armature will close one of the relay contacts which in turn will start the motor running either clockwise or counter-clockwise, until the circuit is again balanced by the resulting movement of the motor balancing, potentiometer, .whereupon the relay contact will break and the motor will stop. ., - The development of specialized industrial control equipment 'using. electronic principles has made rapid progress during recent years. Tem peratures may be measured and controlled to fractions of a degree by new) applications of the photo-electric cell. Its accuracy and flexibility make) it applicable to a variety of automatic devices and controllers. .: Pneumatically Operated Equipment . .: In pneumatically, operated equipment the .primary source of power is compressed air at a. pressure of 15 to 25 lb.per: square inch which should/ be clean, dry and, free from oil vapor. It is desirable to compress-the air' to a pressure of 70 lb per square inch or more to provide for a precipitation of. moisture due to temperature drop in the high pressure receiver and- to reduce the dew-point of the air to the controllers below that of the: lowest ambient temperature of the air lines. '. ' The compressed air piping from the source of supply to the inlet side of the controller is known as the main. The connections from the outlet) of the controller to the pneumatic motors are known as branches. ' Throttling type controllers, of the pneumatic type, are basically air pressure regulating valves actuated by .the controlled condition to vary the branch line pressure and thereby reposition the controlled valves or dampers as required to maintain the desired condition of the controlled5 media. A direct acting controller increases its. branch. pressure on an. increase of the controlled condition. A reverse acting controller increases' its branch pressure on a decrease of the controlled condition. Several different'devices may be operated from the branch line of a single controller'iH selected sequence by the. proper spring loading of the 'respective* .pneumatic diaphragm motors.- Small air pressure gages connected into Automatic Control 595 the branch at each controller will indicate the controller action and are of great convenience to the operator in adjusting the system. - . The simplest form of pneumatic thermostat is based on the leak stat v principle which consists of a restrictor in the air supply to the instrument; a leak port having a larger port than the restrictor, and a bi-metallic strip, or diaphragm chamber which expands on a rising temperature and con tracts on a falling temperature. This power is used to reposition the lid seat to close or open the leak port. As the leak port is gradually closed the pressure in the branch increases until it approaches the full main pressure in the fully closed position. As the lid seat moves away from the leak port the pressure in the branch decreases until the branch is fully exhausted when the lid seat restriction of the leak port is entirely removed. The basic leak stat principle of operation has been refined by the addition - of supplemental relays in nearly all current types. * TYPES AND FUNCTIONS OF CONTROLLERS Descriptions or functions of various types of controllers follow. A single-duty room thermostat controls the heating or cooling devices to maintain the desired temperature. . A dual or two-temperature room thermostat controls the respective heat sources to maintain alternately two selected temperatures. They may be indexed manually or by time switch from central points in selected zones. A high-low room thermostat is similar to the dual thermostat, except that it is indexed individually by the manual operation of a push button or switching device built into the individual instrument. A sub-master or remote readjustable room thermostat is a pneumatic room type instru ment fitted with a readjusting diaphragm to which a separate pilot air line connection is made. As the pressure in the pilot line is raised from 1 psi to 13 psi, or as selected, the operating point of the controller may be increased or decreased within predetermined limits. Indexing may be done by a manual gradual switch or master thermostat. ' ' A pneumatic master\ or pilot thermostat varies the pilot pressure to the readjusting diaphragm of one or more sub-master thermostats to vary their operating point in accor dance with a predetermined change in the temperature sensed by the master thermostat. A summer-winter room thermostat operates at any selected temperature as a direct acting controller during the heating season and operates at the same or aiiy other selected temperature as a reverse acting controller during the cooling season. Groups of, these instruments may be indexed from a central point or individually indexed by a manual push button, or a switching lever built into each instrument. They may be used to control volume dampers of a summer-winter air conditioning system to maintain a desired temperature condition in the controlled space, and will operate to close normally open dampers on a rising temperature during the heating season and to open same on a rising temperature during the cooling season. ' A summer-winter sub-master or summer-winter remote readjustable room thermostat .'is similar to the summer-winter thermostat but is arranged to permit resetting of the control . point by a master thermostat or by a manual gradual switch or other selected device. . A humidity compensated thermostat is a room type gradual acting thermostat combined with, and readjusted by, a hygroscopic element. It may be used to maintain a constant effective temperature. . The humidity sensitive element usually functions to raise the operating point of the temperature sensitive element one degree for a predetermined drop in relative humidity , and lower the operating point of the temperature sensitive element proportionately for a similar increase in relative humidity. . * . An insertion or duct thermostat of tube type is usually equipped with a rigid bulb, consisting of a' brass tube enclosing an invar rod which usually has a maximum range of 0 F to 250 F, or consisting of a- vapor disc type which operates through a similar range but in which the type of disc must be selected to function at given temperature incre ments throughout that range: It is available in the remotely readjustable or sub master type, which may be reset in the same manner as the sub-master room type ther- mostat. This type of instrument may also serve as a master thermostat. / An immersion thermostat is similar to an insertion thermostat, except that the bulb . fitting is threaded for insertion through the wall of a vessel containing a liquid. A union . connection and separable well or socket are available where it is desirable to provide for 596 CHAPTER 34 1946 Guide the removal of the controller bulb without the necessity of draining the vessel to the bulb level. . ; .. A differential thermostat has two flexible capillary tubes fitted with plain bulbs, or with bulbs having flanges or having threaded connections. One sensitive element is subjected to the controlled temperature and the second element is exposed to the tem perature which is to determine the controlled temperature. The instrument functions to maintain a definite relation between the two.temperatures. A remote bulb or extended tube controller may be of liquid, vapor, or gas filled type. A bulb of this type of instrument is connected to the instrument head by means of a flexible capillary tube of the desired length. The external diameter, bore, and material used to form the capillary vary with the type of control system. An indicator controller is a controller fitted with a pointer, thermometer, or gage which indicates the controlled condition. ; A recorder controller is a controller, combined with a clock mechanism and chart, which both controls and records the controlled condition. A time cycle controller is a controller equipped with a clock mechanism which auto matically raises and lowers the control point of the instrument to meet a required time schedule. . . A hygrostat or humidistat is an instrument for controlling relative humidity. It may be of a room, insertion, indicating or recording type, and may be direct or reverse acting. ' Many forms of hygroscopic materials, such as human hair, wood, bi-wood and mem brane of selected type, are used as the sensing medium for these instruments. Where the controlled condition ranges below 20 per cent or above 70 per cent, or the dry-bulb temperature is above 100 F, careful selection of the hygroscopic element is essential. A static pressure controller is frequently used to provide a constant pressure in a duct system in which the volume of air supply is varied to maintain temperature or some other condition, and usually it operates to reposition dampers installed in the fan vortex or other selected location. It usually functions to maintain a pressure differential between the atmosphere and the pressure or vacuum of the controlled condition. It is frequently necessary to pipe the neutral chamber to a selected location to obtain a true basic condition. . ' A velocity regulator is a controlleractuated by thevelocity of the medium which it controls. . A solenoid air valve or electric pneumatic switch is an electrically actuated three-way air valve which may be either direct or reverse acting. It is frequently used in connection with fan ventilating systems to close outdoor intake dampers and heater coil valves during the period when the fan motor is stopped. A pneumatic relay or cumulator is a device fitted with a readjusting diaphragm to which a separate pilot connection is made. It is installed in the branch between the controller and the controlled valves or dampers, and functions to accelerate, magnify or reverse the action of the controller. Direct acting relays increase the branch pressure on an increasing pilot pressure. Reverse acting relays decrease the branch pressure on increase of pilot pressure. . A duplex cumulator or relay is a device having two pilot connections either of which will vary the branch pressure on a changing pilot pressure. An averaging cumulator or relay is a device arranged to vary the branch pressure as dictated by the average of the pressure of two or more pilot connections. ., A multiple cumulator or relay is a device having more than two pilot connections any one of which will vary the branch pressure on a changing pilot pressure. . A control valve may be considered as a variable orifice designed to control the flow of liquids, gases and other fluids. The use of the flat disc type of valve is usually restricted to on-off control require ments. Throttling valves are generally equipped with selected forms of plug to produce the flow characteristics required for the special problem. Special plugs can be shaped to produce almost any desired flow characteristics. The three types of plugs most widely used are the V-port skirt type, the throttle plug, and the ratio plug. A diaphragm valve is a valve which is operated by a diaphragm attached to the valve stem. Increasing air pressure on the diaphragm moves the valve against the pressure of opposing springs which return the valve to its normal position on a decreasing diaphragm pressure. The pressure range required to fully reposition a valve has four limiting factors, viz., the size of the diaphragm top, the'tension of the selected spring, the packing gland " friction and, for all single seated valves, the pressure of the controlled media against .which the valve must hold. . . - A direct acting or normally open diaphragm valve will assume an open position due to spring action.when all operating power is.removed. -. Automatic Control 597 t A reverse acting or normally closed.diaphragm valve will assume a closed position due to * spring action when all operating power is removed. . * A double seated balanced or semi-balanced valve is designed for use with high pressures and is practically balanced regardless of the pressure differential across the plug. The diaphragm tops for valves of this type need only have ample power to close the valve against the tension of the opening spring plus the friction of the valve packing gland. While plugs and seats for this type of valve can be arranged to provide for tight seating for special purposes, such a requirement is not ordinarily expected. - A three-way mixing valve, having two inlets and one outlet, is fitted with a double faced disc, operating between two inlet ports, which functions to close one port as the other is opened, and is used for mixing service. A three-way diverting or by-pass valve has one inlet and two outlets with two separate discs operating on the outside of the respective valve seats to close one as the other is opened; and is used for diverting service. A pilot positioner or valve positioner is an auxiliary control device repositioned by the ' controller pressure and having a direct connection to the valve stem. It permits the full available air pressure to be used on the diaphragm top to overcome hysteresis, packing gland friction and pressure variation of the controlled media, to position the valve precisely in accordance with the controller pressure. A pneumatic damper motor is a diaphragm or bellows assembly operating against resisting springs to reposition an arm or lever assembly. They may be attached directly to the damper frame, either inside or outside of same, or fitted with brackets for wall or floor mounting. The springs used to return the motors to their normal positions are available in several tensions to permit their operation in selected sequence. Pilot posi tioners may be applied to damper motors in the same manner as described- for dia phragm valves. . Pneumatic dampers in either the single blade or multi-louver type should be sub stantially built in heavy frames, properly braced to hold true against any sag in the supporting structure, in order to prevent distortion of the louvers and binding of their supporting trunnions. When large dampers are used for open and shut control, the regular multi-louver type of damper serves the purpose. Where accurate volume control is desired with gradual positioning of the damper blades, the adjacent louvers should be arranged to move in opposite directions in order to properly proportion the available free area through the damper from its fully open to its fully closed position. Multi louver dampers with louvers which all move in the same direction provide full free area. through all but their top and bottom louvers when the louvers reach 45 deg open position. Where fairly tight closing is desired, the damper frames should be fitted with solid stops against which the louvers can close and where additional precautions are necessary, rubber or felt stripping may be glued and riveted to the louver edges. The metal frames of the smaller dampers are usually made of %-\n. stock. Solid stops are usually 34 in. . deep. The free area of the duct enclosing the damper is thereby reduced 134 in. in each dimension through the damper. Where channel frames are used, the restriction is in creased accordingly. Damper louvers should be suspended on non-corrosive trunnions. Thrust bearings are necessary to properly support large vertical louvers. Where ball or roller bearings are required for special conditions, they should be of the non-corrosive type. " - ' DESIGNATION OF TEMPERATURE CONTROL Temperature may be controlled from three basic conditions: Dry-bulb Control: The controller element senses the dry-bulb temperature. . Wet-Bulb Control: The controller element senses a true wet-bulb temperature. Wicking of selected material suspended from the controller element to a water trough directly below the element is one of the mediums frequently used to obtain' wet-bulb temperature. True wet-bulb temperatures can only be maintained'with clean wicking and air motion of not less than 600 fpm. The use of distilled water in the wet-bulb reservoir is desirable. Since the wet-bulb temperature indicates the heat content, this form of control while requiring additional and intelligent care to maintain true wet-bulb . conditions, has many definite uses. Dew-Point Control: A saturated condition at a predetermined temperature is main tained. " ... AUTOMATIC CONTROL TERMINOLOGY The following is . a generally accepted terminology referring to the ' operations of controls in a central air conditioning system. Control Point: . The desired constant condition of the controlled media to be main- $98 CHAPTER, 34 . 1946 Guide a` . tained. Some change of the controlled condition must occur to alter the prevailing con j! troller action.. Thermometer Lag: The instantaneous temperature differential existing at any time between the .true temperature of the medium and the temperature indicated on the thermometer. Controller Lag: The time delay in the controller's ability to reposition the controlled sources to properly compensate for a change in the controlled condition. Process Lag: (Process Time Lag) The time which elapses between the instant the control valve is positioned by the controller and the instant the controller element senses . the effect of the change. This depends upon the rate of heat transfer, the specific heat, and the velocity of the fluid movement. Generally a decrease in process time lag simpli fies the control problem. Rate of Load Change: Time element of change in the magnitude of lo^d. Magnitude of Load Change: The per cent load at a specified time. It directly affects the size of the controlling valve. Where the inlet temperature varies constantly; the . control problem becomes more difficult as the thermal difference between the inlet tem perature and the leaving temperature of the controlled media becomes greater. Drift: The deviation from the control point due to change in load conditions from 0 to 100 per cent. Drift increases as the sensitivity adjustment of the controller is lowered, thereby tending to decrease hunting. Drift decreases as the sensitivity adjustment of the con troller is raised, thereby increasing hunting. - - Hunting or Cycling: The temperature variation between the high and low points of ' the control cycle due to lag. This balances out at the point where tech successive wave of temperature reaching the controller is as large as its predecessor. As the sensitivity is lowered, hunting decreases but drift increases. Oversized control valves increase hunting. . Throttling Range or Sensitivity Adjustment: The total rise in temperature at the controller bulb required to reposition the control valve from a fully open to a fully closed position or to operate several devices controlled in sequence throughout the full sequence . range. In connection with chart type controllers, throttling range is usually expressed in' * per cent of the total range of the chart. For other types^ ofc instruments, sensitivity adjustment is expressed in pounds variation of branch pressure per degree change in temperature, or per other unit of change of the controlled media. . Low Sensitivity: A small change in branch pressure for a comparatively large tern- perature or pressure change in the controlled medium. This results in a greater deviation from the control point. Low sensitivity tends to reduce hunting but the lower the sen sitivity, the greater will be the drift. , .' * High Sensitivity: A large change in branch pressure for a comparatively small tem perature or pressure change of the controlled medium. The extreme of high sensitivity is the on-off or two-position control. As the sensitivity is raised, drift decreases, but the tendency to hunt increases. - ' '' Automatic Reset: A mechanical addition td a controller which corrects for drift by . .constantly resetting the instrument to operate on the control point, while repositioning the controlled valve or damper from its fully open to its fully closed position. Reset action is superimposed on throttling range and both function simultaneously. The rate of reset is manually adjustable and must be set to meet the. load requirements, of the individual system. This supplementary device provides the accuracy of high sensitivity adjustment with a minimum of hunting. \. Diaphragm hysteresis is the amount by which the stem travel of a given motor fails to assume the identical position on the upward and downward strokes for an identical, air pressure in the diaphragm top. It prevails in varying degrees in connection with the operation of all pneumatic diaphragm motors, and is .due to spring and diaphragm hysteresis and friction of guide bearing and stuffing box. Assume that a direct acting valve moving to a closed position will travel 50 per cent of its total with 8 lb air pressure on the diaphragm top. It the diaphragm pressure is increased to further close the valve and then reduced to 8 lb, the valve may be repositioned to be only 45 per cent open, indicating 5 per cent hysteresis. Hysteresis is usually expressed in per cent of the full' stroke of valve stem. . ' RESIDENTIAL CONTROL SYSTEMS The control installation in a residence may vary from the simple regulatiori of a coal-fired heating plant to the completely automatic all year air conditioning system. Residential installations with automatic fuel burning appliances, such as oil burners, gas burners or stokers, are . Automatic Control 599 normally equipped with single room thermostat, limit and safety controls as outlined under Control of Automatic Fuel Burning Appliances. ' Coal-Fired Heating Plant ' '; Control in the normal coal-fired domestic heating plant consists of.1 regulating the combustion rate in accordance with requirements. This function is accomplished by a spring or' electric-drivert damper motor which, under the command of a room thermostat and through chain linkage, operates the draft and check dampers of a boiler or warm air furnace. Such installation should be protected against excessive tem perature or pressure by means of a limit control serving to check the fire when conditions at the boiler or furnace reach a predetermined maximum.' All Year Domestic Hot Water Supply - '. Hot water or steam heating boilers with automatic fuel burning ap pliances can be used for all year heating of domestic water supply. , The . fuel burning appliance in this case is controlled from the temperature of water or pressure of steam in the boiler to maintain .uniform boiler con ditions and domestic hot water is heated by means of an indirect heater. The heating of the residence is normally governed by means of a- ther mostat which operates a control valve in the' flow line of a gravity hot water or a steam system or which controls the circulating pump in a hot water system. .' Air Conditioning Systems 1 Residential air conditioning systems normally include a heating source and a motor-driven fan for circulating air. In addition, such installations may involve spray-head equipment to supply humidity. Such instal lations distribute heated and humidified air during the heating cycle, and during the summer or cooling cycle may be used effectively as conditioners if equipped with refrigeration means. Regulation of the humidity during the heating cycle is normally accom plished by opening and closing a solenoid water valve, supplying water to the spray-heads, the solenoid valve being under control of a room type humidity control. In the average installation the fan is permitted to run only during such intervals as the thermostat is calling for heat or at the command of a limit control to prevent the overheating of the bonnet of a warm air furnace. ' The limit control should also prevent the operation of the fan at the command of the thermostat until the circulating air tem perature has increased to a predetermined point. .. For the cooling equipment provided in such installations,' control during the cooling cycle will be. an adaptation of the control principles described for central fan systems selected for the type of cooling equip ment utilized. ' CONTROL OF AUTOMATIC FUEL BURNING APPLIANCES It is essential that automatic controls be used with oil burners, gas burners, and stokers.in order to maintain even temperatures and provide safe and economical operation of the heating plant. Oil Burner Controls . In the normal oil burner installation as encountered in residential and small commercial installations, the burner operation is frequently regu lated by electric controls, and primarily governed by a .room thermostat. It is essential that a limiting control be incorporated in the control system to prevent the temperature of the heating medium from exceeding any 600 CHAPTER 34 1946 Guide predetermined safe maximum. The type of limit control' selected will depend on the type of the heating system. In a warm air furnace instal lation, a limit control would be used,- reacting to the temperature of the heated air in the bonnet of the furnace; in a hot water system a control reacting to the temperature'of the water in the boiler; and in a steam system a control reacting to the pressure of the steam in the boiler. ' In addition to the normal control of the burner from the room ther mostat and limit control, it is necessary that a combustion safety device be used to prevent operation of the burner under hazardous conditions. The oil fire is automatically ignited by means of gas, electric spark of incandescent element and the combustion safety control acting through a sequence device permits the burner operation only when the fire is prop erly established as the burner starts up. A further function of the com bustion safety control is to react to any major disturbance in the flame during the running operation, shutting down the burner and preventing the discharge of unburned fuel if for any reason the flame is extinguished.; Gas Burner Controls In the case of the domestic burner, full automatic operation is the normal requirement and the burner is started and stopped at the. com mand of a room thermostat which, in turn, opens ana closes a control valve in the gas supply line. Modulating controls and controls providing a high and low fire are also available for gas burners. For purposes of preventing abnormally high temperatures in the bonnet of gas-fired furnaces or in the temperature of the water in gas-fired hot water heating boilers or excessive pressures in gas-fired steam boilers, temperature and pressure limit controls are used. Ignition is normally secured through the use of a gas pilot flame and a safety device is provided; utilizing the heat of the pilot flame in such a manner that if the pilot light is extinguished for any reason, the main gas valve cannot be opened. For satisfactory and economical operation, all automatically-fired gas burners should be equipped with pressure regulators oh the gas supply line. -- Stoker Controls - - Domestic stokers are normally placed under command of a room thermostat for primary operation subject also to the command of a limit control to prevent their operation when conditions in the boiler or furnace exceed predetermined safe maximums. Utilizing coal as fuel, automatic ignition is not provided and the stokers, once ignited, maintain their fire, merely changing the rate of combustion by changing the draft and the rate at which the coal is fed. Thus, at the command of the room ther mostat the stoker motor is started; driving a forced draft fan and fuel feeding mechanism. The rate of combustion is thus increased and this operation continues until the thermostat has been satisfied when the motor is stopped and the fuel in the combustion chamber continues to burn at a slow rate with reduced draft. Automatic controls may be used to operate the stoker sufficiently to maintain a fire in mild weather and also to prevent feeding of fuel if the fire is extinguished. - ZONE CONTROL Zone control for winter heating of buildings, in which a single room' thermostat will not provide satisfactory conditions and where the refine ment of control from individual room thermostats is npt a requisite, may be secured in various ways. According to its size, use and exposure, the Automatic Control 601 building may be divided into zones where the general requirements will be relatively constant. The number of zones is determined by (1) size of building, (2). number and character of exposures, (3) variation in occupancy and other inside conditions, and (4) cost of additional zones. For large buildings it is desirable to have at least one zone for each exposure and for high buildings, each exposure may be sub-divided into upper and lower zones in order to properly provide for the stack effect. . In buildings of this type it is, advisable to provide a separate main with local thermostats for, the street floor heat sources, especially those adjacent to entrances and exits. For small buildings or where cost or other conditions limit,the number of zones, a frequent compromise is to combine the North and West exposures in one zone and the South and East exposures in a second zone. For steam heating systems, the radiator output may be proportionately, reduced as the outdoor temperature rises by several methods. Some of those in common use are: " 1. Throttling steam pressure to allow flow through orifices in proportion to the needs for heating. 2. Turning steam on and off on time intervals proportioned to the needs for heating. 3. Varying the absolute pressure of steam in the system. The usual zone controlling device is arranged to sense the effect of sun, wind, or rain, as well as the outdoor local zone temperature, and in some instances is fitted with additional elements sensing the indoor zone or zone radiator temperatures. It functions to regulate the rate of flow or the flow impulse as required to maintain the desired indoor zone tem perature condition. A switch panel containing manual switches arranged to raise or lower the operating point of each zone controller is frequently mounted at a selected location. These panels may contain time switches, for automatic cycling of day-night or other predetermined control pro grams. In buildings where some zones or all zones have no night occupancy, provisions may be made to index the control system to main tain predetermined low economy temperatures during the unoccupied periods and short morning warm-up period, and to obtain normal opera tion throughout the occupied period. Either manual operation or auto-. . matic cycling by time switch may be used. For hot water heating systems, the zone controller functions to regulate the water temperature in accordance with the prevailing outdoor temperature. For discussion of zoning in air conditioned buildings see section on. Zoning in Chapter 43. CONTROL OF UNIT SYSTEMS ' Because of the usual segregated location of unit equipment throughout a building and its consequent lack of competent supervision, complete automatic control is essential to its satisfactory operation. Unit Heaters ., ' In its simplest form, unit heater controL consists of a room thermostat to start the unit heater motor when heat is required and shut it off when the demand is satisfied. With this limited control, it is possible in some. instances that, with no steam available at the heater, the operation of the fan would cause objectionable drafts. To avoid this, limit controls are available which will prevent the operation of the-fan at the command of the room thermostat except when steam is available, as determined by 602 CHAPTER 34 1946 Guide the temperature of the steam or return pipe or the pressure of the steam supply. -. . .. . , Where several unit heaters serve a limited area, they may be grouped . for purposes of automatic control, arid several heaters placed in operation at the command of one thermostat. By properly grouping the units which will operate together, the benefit of zone control can often be obtained with a minimum of control equipment. Where such group operation is utilized* the thermostat and limit control usually function through a relay, as the combined load of the several motors may exceed the current capacity of the thermostatic control device. : In some cases where cold drafts will not result, it is desirable to operate the unit heaters continuously for circulation of: air. In such instances the room, thermostat regulates the supply of steam to the unit through a ' control valve in the steam supply line and the unit heater motor operation is manually controlled. . ;. Unit heaters equipped with dampers arranged for by-passing air around the heating coils are controlled by room thermostats operating modu lating damper motors attached to these dampers so that as the tempera-, tures rise, a decreasing amount of air is heated. When the by-pass is wide open the heating effect is so much reduced that control of the steam supplied to the coil is not generally important. If valve control is added, the throttling of the steam may be concurrent with, or subsequent to, the opening of the by-pass. Cooling Units . .< . The recommended form of temperature control for a cooling unit con templates the continuous operation of the fan, with automatic regulation of the compressor or cooling coil, or both, as determined by a thermostat in the room, or in.the return air to the cooling unit.- Such operation insures continuous circulation of air in the room, and in addition to providing the cooling effect of moving air, overcomes the tendency of the air to stratify. As the temperature begins to rise, the controller opens the valve to a cold water cooling coil, .or for direct expansion coils, opens a valve in the refrigerant line, closes a by-pass around the coil or starts a compressor. . .. . Cooling units may also be controlled by arranging the room thermostats to start and stop the1 fan motors or by a combination of motor and. refrigerant control. .. . Unit Ventilators ' ' '' . There are various types of unit ventilators available but in general all types are designed to. draw, air from the outside or to mix outside and recirculated air, heat it and introduce it into the room under control of a thermostat. . .. . .. . ' The design of unit ventilators has to an extent been based on the' requirements for automatic temperature control and the cycles of control have-been developed to include other heating devices in the rooms with unit ventilators. Unit ventilators are frequently used in schools and other types of buildings where states have laws or regulations governing the minimum amount of ventilation to be provided. The .control of the amount of outdo,or air is designed to conform to the various laws. Usually the device circulates a constant amount of air and the amount auto-' matically taken in from outdoors is controlled in one' of these ways: ' 1 1. Full'recirculation lin'til.'the room temperature reaches a: certain point,'generally two degrees, below the desired room temperature; then a minimum amount of outdoor . Automatic Control 603 air for ventilation while the temperature is maintained by throttling steam; and if the room temperature rises with all steam shut off, a gradual increase in amount of outr door air up to 100 per cent. ' ... . :. 2. Full recirculation until the room reaches a set point below room temperature, after which all air is taken from outside. '- ... ' 3. Gravity recirculation while the fan motor is not running, with full outside air as soon as the fan starts, obtained by a relay in the motor circuit. -. 4. Full recirculation or all outdoor air as determined by a manual switch which can be operated at any time whether or not the fan is running.1 All the unit ventilators in a single building may be operated by one or many switches. . With arrangements 1 or 2, it is desirable to include a relay to prevent the intake dampers from opening while the fan is not running, regardless of room temperatures. With a dual system of control this is essential to prevent the thermostat keeping the outside damper open until the tem perature falls to the reduced setting. The intake and recirculated air quantities are determined by a single damper or by a pair of dampers working together, and operated by a damper motor. Although this affects the temperature of the air delivered, the main heat control comes from the throttling of the steam supplied to the heating coil, with or without by-pass damper control. To prevent air being delivered at too low a temperature, a low limit thermostat is commonly installed in the air stream and set at some point between 55 and 70 F. The lower settings may cause discomfort, the higher ones overheating, depending on circumstances. The air stream thermostat can be used to turn on steam, reduce the amount of outside air, or both. Rooms with unit ventilators frequently have auxiliary heating, devices, such as direct radiators, convectors or unit heaters, all under control of a , single room thermostat. A common control cycle for such rooms is com posed of the following functions, assuming that 72 F is desired: 1. Below 70 F the unit ventilator intake damper is in full recirculating position and . all heat is turned on. . . . . 2. At 70 F the intake damper moves to a position that will admit a predetermined minimum amount of air from outdoors. 3. At 71 F the auxiliary heating devices are shut off. 4. From 71 to 72.5 F, the heating effect of the unit ventilator is throttled. , 5. From 72.5 to 74 F, the intake damper is gradually moved to increase, the amount of- outside air from the set minimum to 100 per cent. 6. If the room thermostat calls for too much cooling, the air stream thermostat holds the delivery temperature at a proper minimum. Other similar cycles may be used. One additional feature, is the use of an air stream thermostat that has its control point reset, by the room thermostat. Then as the room temperature rises, the delivery tempera ture is gradually reduced from a maximum to a minimum.. ... CONTROL OF REFRIGERATION EQUIPMENT The most common means of providing cooling for air conditioning may be divided into four general classifications as follows: : ' . Refrigeration compressors may furnish refrigerant to direct expansion cooling coils through which air is being passed, or to coils in: cooling tanks , through which water is passed which is then pumped to air washers or cooling coils through which the air is passed. In either case the compressor motor may be started and stopped in order to meet the demand for refrigeration or a pressure controller may be used to regulate the low side or suction pressure of the compressor. When the latter method is used, the flow, of refrigerant to cooling coils may be regulated by the opening and closing of a solenoid refrigerant, valve at the command of a temperature controller or thermostat. ' 604 CHAPTER 34 '1946 Guide . A high pressure cutout as an individual unit or in combination with either a temperature or pressure controller provides a safety feature against excessive pressures on the high side of the compressor. Many compressors may be unloaded, by instruments sensing room or duct conditions, or by refrigerant pressures, thus reducing the frequency of starting and stopping. If two or more compressors are used for a single cooling system, step controllers are used to start them in sequence at intervals of a few seconds to avoid the large momentary electric input ' that simultaneous starting would demand. ' When condensers are water cooled, thermostatic control to vary the quantity of .water is needed for economical operation. Mechanical air condensers may be started and stopped with temperature demands. Chilled water may be stored in tanks at temperatures slightly lower RETURN AIR RETURN AIR HERMOSTAT ETURN AIR PAMPER n UR WASHER and[ 1 .dehumidi fier low LIMIT DISCHAR6E THERMOSTAT 0.0. WET BULf THERMOSTAT CHILLEO WATER U^ES FAN MOTOR STARTER _ EATER VALVE. . LJ--DEW POINT THERMOSTATS CHILLEO WATER VALVE Fig. 1. Location of Control Devices for Year 'Round Air Conditioning System than required for air cooling coils. The control of temperature for the water distribution system is as described for Ice Cooling. . When ice is used for the cooling or dehumidification of air, it is usually placed in bunkers and water is sprayed over it. This water, after being cooled, may be used in air washers or surface cooling coils and is usually returned to the bunker for additional cooling after being used. Control of the water temperature leaving the cold jvater tank may be maintained by a temperature controller, which measures the temperature of the water in the tank and modulates a control valve in a by-pass which permits a portion of the return water to return directly to the tank instead of passing through the sprays. . A vacuum refrigerating system consists of an evaporator, compressor, condenser and auxiliaries. The refrigerant used is water, and water ,vapor (steam) is the power medium. . j.' Water which has been passed through an air washer or cooling foil is sprayed directly into the evaporator or water cooler where it is cooled by its own evaporation. A condenser is attached directly to the compressor Automatic Control 60S discharge and its function is to recondense the water vapor drawn from the evaporator, plus the steam which supplies the energy for compression. The temperature of the cold water leaving the flash chamber should be measured by a-temperature controller which will in turn operate a_ twoposition or positive-control valve installed in the steam line to the jet so as to permit steam to flow only when cooling is required. If city water is Fig. 2. Control Diagram for Year 'Round Air Conditioning System used in the condenser, the amount of water should be modulated according to the demand as measured at the condenser outlet by means of a tem perature controller and control valve. ' . Well water, if available in sufficient' quantities at low temperatures during the cooling season, may be pumped directly to air washers or cooling coils. Control is usually effected through control valves on the water supply to the cooling unit actuated by temperature or' humidity con- trailers, or both, located either at the outlet of the conditioner or in the conditioned space. 606 CHAPTER 34 1946- Guide APPLICATION OF CONTROL DEVICES TO A TYPICAL SYSTEM ; Fig. 1 shows the location of controlling devices for a year 'round air conditioning system such as shown in^ Chapter 43, Fig. 3. A control diagram for pneumatic control equipment is shown in Fig. 2for convenience in explaining the function and sequence of operation of the control in Fig. 1, but obviously, the individual controls may alg^> be of self-contained or electrically operated type provided they obtain the same control of valves and dampers. . The auxiliary controlling devices indicated may all be mounted together on an instru ment board which may also contain a framed copy of the control diagram and the description of the automatic control cycle. Air gages, identified by suitable inscription plates, may be installed in the branch connections to and from the auxiliary devices oh the instrument board to indicate the functioning of the various devices. .- > A description of the automatic control cycle follows: . When the fan motor is stopped, solenoid air valve E-l, actuated from the fan motor circuit, is de-energized and exhausts its branch to close minimum outdoor damper D-l, reposition three-way air valve V-a to close heating coil valve V-l, and remove main air from remote bulb indicator dew-point thermostat T-l, thereby closing maximum out door damper D-2 and opening return air damper D-3. . When the fan motor is started, E-l fills its branch, thereby opening minimum outdoor . damper D-l, repositions V-a to permit T-3 and T-4 to control V-l and supplies main air to T-l to permit same to operate D-2 and D-3. During the summer cooling season, manual indexing switch S-l is positioned to fill its ' branch, whereby it supplies main air to dew-point thermostat T-2, positions three-way * air valves V-e and V-f to permit T-3 to control face damper D-4 and by-pass damper D-5, positions three-way air valve V-b to close heating coil valve V-l, positions three-way air * . valveV-c to remove the control of maximum outdoor damper D-2 and return air damper D-3 from dew-point thermostat T-l and place these dampers under the control of dew point thermostat T-2. /. . When S-l is positioned as noted, remote bulb dew-point thermostat T-2 functions . on a rising temperature to first gradually open maximum outdoor damper D-2 while simultaneously closing return air damper D-3 and on a further slight temperature rise, gradually positions chilled water valve V-2 to pass chilled water to the dehumidifier. The reverse operating sequence occurs on a falling dew-point temperature. Should the outdoor wet-bulb temperature rise above the desired, indoor wet-bulb temperature, positive acting-outdoor wet-bulb thermostat T-5, positions three-way air valve V-d to ' remove dampers D-2 and D-3 from the control of T-2, thereby closing outdoor damper D-2 and opening return air damper D-3. ;j On a rising return air temperature T-3 functions to open face damper D-4, while simultaneously closing by-pass damper D-5 as required to maintain the desired return air temperature. The reverse, operation occurs on availing return air temperature. : During all seasons except the summer cooling season, manual switch S-l is.positioned to exhaust its branch, thereby making dew-point thermostat T-2 inoperative and posi tions chilled water valve V-2 for continuous recirculation, positions three-way valve Vfb to permit heating coil valve V-l to be operated as required, positions three-way valve V-c to permit T-l to control D-2 and D-3, positions three-way valve V-e to permit T-3 to operate through low limit discharge thermostat T-4 to control heater valve V-l and positions three-way valve V-f to open normally closed face damper D-4 arid close normally open by-pass damper D-5. \ - . ' When switch S-l is positioned as noted, remote bulb dew-point thermostat T-l functions on a rising temperature to gradually open maximum outdoor damper D-2, while simultaneously closing return air damper D-3 as required to maintain the desired * dew-point temperature. The reverse operation occurs on a falling dew-point tempera ture. When the outdoor wet-bulb temperature rises above the desired dew-point temperature,, the dew-point temperature will rise accordingly until such time as the system is indexed for summer cooling and chilled water is made available to drop the dew-point temperature. ' ' '. . Return air thermostat T-3 functions on a rising temperature to pass air, through low limit discharge thermostat T-4 to gradually close heating coil valve V-l.' Should the discharge temperature fall below the operating point of T-4, this thermostat, will release ' air from its branch to gradually open V-l as required to maintain the desired low limit discharge temperature regardless of the operation of T-3. ', CHAPTER 35 Motor Rating; Functions of Motor Control Equipment; Direct Current Motors, Types, Control Equipment and Specifications; Alternating Current Motors, 'Types, Control Equipment and Specifications; Gear Motors; Glossary of Motor Terms, Enclosures, Speed Classification and Mounting THE electric motor, available in many different types suitable for various services, is now the most widely used form of prime mover. The equipment for starting, controlling and protecting these motors varies ' with the type and with the functions it, is desired to attain. Motors are divided into two general classifications, alternating-current or directcurrent, depending on the power source to be used. In selecting a motor for a particular application consideration must first be given to the type of. power supply available. All machinery has certain load characteristics which may vary with speed. Some types may have a constant torque over wide ranges of speed, while others may have changing torques with changing speed. Consideration should be given to selecting the motor and the motor control which best suit the requirements of the drive. MOTOR RATING The rating of an electric motor depends upon the total temperature which the motor attains under operating conditions. This total tem perature depends on both the ambient temperature and the temperature rise of the motor. As motor temperature rise is in turn determined by the ability of the motor to dissipate heat, circulation to the motor should not be restricted. Improper selection of motors with regard to.tem perature ratings may result in high motor operating temperatures with accompanying reduction in motor life. ' In general, the electrical insulation is the portion of the motor most susceptible to injury from high operating temperatures. Of the several types of insulation which are available, the most common type, specified as Class A by .the National Electrical Manufacturers Association, consists of cotton, felt, paper or similar organic materials and permits a 55 C rise . in temperature over a 40, C ambient temperature. Class B insulation . consists of mica, asbestos, fiber glass, or similar inorganic materials and permits a 75 C rise in temperature over the 40 C ambient temperature. Other types of insulation such as silicone resin are available and permit extremely high operating temperatures. . ' . The mechanical construction of the different types of motor enclosures and the rise in temperature with Class A insulation for each type are enumerated in the glossary at the end of this chapter. Since the dif ference in temperature between the hottest spot and the nominal tem perature, as measured by a thermometer, is greater for a completely unprotected machine than it is for an enclosed machine, the permissible temperature rise is smaller for an open motor. FUNCTIONS OF CONTROL EQUIPMENT FOR MOTORS In general, control equipment for all types of motors should provide: (1) means of disconnecting the motor from.the power supply; (2) means , 607 . 608 CHAPTER 35 1946 Guide Type 1. Shunt d-c ^ 2. Compound . 3. Series Table 1. Classification of Motors Speed Charac teristics Full Voltage Starting Torque Starting Current - ' .. ' Hp Range - Type of Application See Footnotet Constant Speed Drives t Constant Normal I Normal , All '(with controller) Variable High Normal (with controller) All Variable High Normal (with co stroller) Small (c) centrifugal pumps and centrifugal compressors ' (6) (c) (e) Reciprocal ing pumps and frequent or hard . starting (d) Fans direct connected 4. Squirrel-Cage Constant ` General Purpose Class A %' 5. SQuiirel-Cage Class B Constant Normal 0.8t1.5 times Normal 0.8-1.5 times High 6-8 times Normal 5-6 times 0. Squirrel-Cage Class C ' Poly- .phase ' 7. Wound Rotor Constant , Constant or Variable High 2-2.6 times Normal 5-6 times High Low 1-2.5 1-3 times times (with secondary control) 8. Synchronous -High Speed Exactly Normal Normal Constant 0.75-1.75 5-7 times times . 9. Synchronous Low Speed Exactly Constant Low 0.3-0.4 times Low 3--4 times All */ Medium Small (c) centrifugal pumps and centrifugal compressors '' fugal pumps and centrifugal com pressors Medium Small (5) Reciprocating ; pumps * (e) and compressors started loaded AU (6) reciprocating pumps and compressors (c) and frequent (e) or hard start Large Medium Large trifiigal pumps and centrifugal com pressors compressors starting unloaded Single PHASE a-c 10. Capacitor Constant 11. Capacitor Fan _, 12. Capacitor Start Induction Run Constant Constant 13. Repulsion Induction. Constant 14/ Split Phase Constant and Adjustable High Normal Normal > Normal High High Normal Normal Normal Small . Small V. . Fractional Medium Small ' Fractional (6) Pumps and compressors ' (a) Fans, centrifugal pumps (b) pumps and . compressors. - (b) pumps and compressors (a) Fans (b) .pumps and compressors (d) fans--direct - tApplications: . - - - ,- . ,- - . a. Drives having medium or low starting torque and inertia (WR1) such as fans and centrifugal pumps or reciprocating pumps and compressors started unloaded. ' r b. Drives having high starting torques, such as reciprocating pumps and compressors started loaded. c. Similar to (a) except where frequent or hard starting (large WR}) requires a higher starting arid accelerating torque. . * - 8u d. Fans direct connected. . Stoker'drives. J ' .' ' -1 ' Motors and Motor Controls 609 Power Supply ' Table 1. Classification of Motors--(Concluded) Type Speed Charac teristics Full Voltage Starting Torque Starting Current Hp Range Type of . Application, See Footnote* t, Adjustable, Speed Drives 15. Shunt Field Adjustment Constant Normal Normal ' AU (with co itroller) (a) Fans and (e) centrifugal pumps d-c 16. Armature Variable Normal Normal AU . fa) Fans and . Resistance ' (with co itroller) (e) centrifugal pumps Adjustment - 17. Variable Voltage Constant' Normal Normal Control (with co itroller) All (d) Fans and centrifugal pumps Poly phase a-c 18. Squirrel-Cage High Slip. Transformer Adjustment Variable 19. Squirrel-Gage Constant Separate Wind Multi ing or Regrouped Speed Poles ` 20. Wound Rotor Variable Normal. Normal Normal or High Normal or Low High - Low ' (with se>condary , cont rol) 'Medium Small ' All All (a) Fans (a) Fans (6) pumps and (c) compressors - () Fans () centrifugal-pumps and compressors 21. Repulsion Variable High Normal Single Phase a-c 22. Capacitor Low Torque Tapped Winding Variable Two Speed 23. Capacitor Low Variable Torque Trans former Adjust ment - Low Low , 24. Split Phase Constant Normal Regrouped Poles Normal Low Normal Low and () Fans--centrifugal Fractional 'pumps () compressors Fractional (d) Fans, direct Fractional (d) Fans Fractional (d) Fans for starting the motor; (3) overload protection for the motor; (4) pro tection against low voltage; and (5) means for varying the motor speed. Full voltage starting for motors is preferable because of its lower first cost and simplicity of control. Except for d-c machines, most motors are mechanically and electrically designed for full voltage starting. The starting inrush current, however, is limited in many cases by regulations of power companies because of the voltage fluctuations which may be caused by heavy current surges. It is therefore often necessary to reduce the starting current below that obtained by across-the-line starting. The power supplier- should . be consulted to determine' the allowable inrush current for any given location. .. . The choice between full voltage and reduced voltage starting is governed almost entirely by inrush current limitations. The starting torque of all motors varies with the starting current and.it is therefore necessary to insure that the motor is supplied with sufficient current to develop enough torque to accelerate the load. . In present practice overload protection of motors is- obtained by use of thermal overload inverse time limit type protection. The usual setting of such protection devices is at 125 per cent overload, the element trip- 610 CHAPTER 35 1946 Guide ping after a definite interval of time. The National Electric Code requires . the addition of fuses or circuit breakers to .protect the overload elements from severe short circuit currents. ' Two types of protection are available against low voltage at the motor terminals. One type, called low voltage release, permits the motor line ' contactor to drop out on low voltage and to close again when the voltage returns to normal, thereby restarting the motor when the abnormal condition is ended. The second type, called low voltage protection, causes the motor line contactor to drop out on low voltage but prevents restarting when the voltage returns to normal except by the action of an operator. This latter type of protection is desirable where it is necessary for the operator to make initial starting adjustments on the machine. Manual control for an alternating or a direct current motor is usually located near the motor. When so located an operator must be present to start and stop, or change the speed of the motor by operating the' control mechanism. Manual control is sometimes employed only as a device to give overload protection and another device is employed to start and stop the motor. Manual control is used particularly on small motors which operate unit heaters, small blowers, and room coolers in an air conditioning system. In other cases manual control in the form of drums, when used with multi-speed motors, is only used as a speed setting device while the starting and stopping functions operate automatically through thermostats and pressure switches. Because of the increasing complexity of air conditioning systems, the equipment is operated preferably by automatic control and less depen dence is placed on manual operation and regulation. ' Automatic control of motor starters may be accomplished by the use of remote push button stations, by a thermostat, float switch, pressure. regulator, or other similar pilot devices.- An added advantage of auto matic control is that the main wiring for the. starter may be installed near the motor, while the starter may be operated by a control device located elsewhere. . DIRECT CURRENT MOTORS Direct- current motors are classified (see Table 1) according to type'of winding as: shunt wound, compound, wound,and.series wound,,. Shunt Wound motors, being suitable for application to fans, centrifugal pumps,-, or similar equipment where the amount. of. starting . torque required is relatively small, are used for the majority of direct current applications in the field of heating, ventilating, and air conditioning. . They may be used , on reciprocating pumps, and compressors if started under unloaded conditions. : . .:\ f- - -. : Without auxiliary control the shunt wound motor is designated as constant speed.* Fig. 1 illustrates the characteristics of direct current' motors, showing speed, horsepower, and torque as a function of-current. The speed regulation*: of small size shunt wound motors from % hp to . 5 hp is 12 per cent as specified by the NEMA while on larger motors it is 10 per cent. . .: - ... : ' Compound Wound motors are required for application to reciprocating compressors, stokers, reciprocating pumps when started, under loaded ?Refer to Glosairy at end of!chapter. Motors and Motor Controls ' 61h conditions, and other similar equipment, requiring high starting, torque.'' The characteristics of this type of motor, are such that for starting torques above full-load torque the starting current required is somewhat less than for: the shunt wound motor. Compound wound direct - current motors are normally used whenever frequent starting . makes high starting and accelerating torque desirable. Without auxiliary control, compound wound motors are designated as varying speed,* and have a speed regulation of 25 per cent. . .... .. Series Wound motors find only limited application in a few special cases and are available in a limited range of sizes. The motors are used where extremely high starting torques are required and must be applied only to direct coupled continuous loads due to the fact that the speed of -the motor becomes dangerously high when the motor is operated at a light load; .. : . : . ' - Typical d-c motor specifications are shown on page 613. : DIRECT CURRENT MOTOR CONTROL' \. , 'Direct current motors are usually started through .starting controllers which use a resistance, in series with the motor armature, which is gradually cut out as the motor comes up to speed. Motorc up to 2 hp may be linestarted providing the inrush current causes no serious voltage fluctuations in-the power supply line. - : ...> .- ' - . : :/ ' Constant'Speed and Varying Speed Motors. As shown in Fig. 2, the recommended practice for manual starting of motors over Yl hp requires the use of a fused safety switch or circuit breaker and a face-plate type starter. For automatic push button starting a safety switch or circuit breaker and:.an-automatic starter.are recommended........... .. ........ . ... Refer to Glossary at end of chapter. . 612 CHAPTER 35 1946 Guide ~ Adjustable Speed Motors are normally shunt wound and are operated at various speeds by varying a resistance connected in series with the motor-field. . A maximum range of speed of about 5 to 1 can be obtained by this means. Rated speed regulation is 22 per cent for motors of this type from 2 to 5 hp; 15 per cent is standard in larger sizes. The NEMA practice on rating adjustable speed d-c motors is defined in the Glossary at the end of the chapter. The control for the adjustable speed motor consists of the addition of a field rheostat for speed contralto the equipment specified for the constant speed motor. under kHP SMALL CIRCUIT BREAKER ^2 HP I. LARCER ADJUSTABLE SPEED JL.3 SAFETY Pi SWITCH CONSTANT SPEED MANUAL STARTING 41 R SAFETY SWITCH CONSTANT SPEED PUSH BUTTON STARTING 5 JL . , pi1 SAFETY | SWITCH STARTER & SPEEO REGULATOR |"i] STARTING iZj RHEOSTAT 1 AUTOMATIC | STARTER MJI MOTOR ifSO 0] Hg|l fljITmotor rfsn Hg|| [j, tMOTOR Fig. 2. Recommended Controls for d-c Motors Adjustable Varying Speed * Motors are d-c motors in which the speed is varied by the addition of resistance in series with the armature. The speed of the motor by this means is always less than the rated full field speed and varies widely with a change in load, especially with high series resistance. Fig. 3 illustrates typical speed characteristics of this type of motor for different values of armature resistance. The addition of series resistance in the armature circuit reduces the motor speed by lowering the voltage on the armature. At one-half speed the voltage is approximately one-half of line voltage. Consequently, with rated full load current the power delivered by the motor will be only one-half of the maximum, e.g., it will be 5 hp from a 10 hp motor, because the other 5 hp will be lost in the resistance. It is, therefore,.evident that the.efficiency of the motor is reduced at reduced speeds due to the loss in the resistor.. '.. Control for the adjustable varying speed motor is similar to that for , the constant speed motor with the exception that the starting .resistor Refer to Glossary at end of chapter. Motors and Motor Controls Typical Specifications for d-c Motors . 613 . Constant . (Shunt 1 ; 1151 . ..................... Hp......... .......RPM, j Adjustable Speed, j Compounds Wound, 230) Volts Varying (Series . J 600) d-c Motors For Driving................. .......................................... Motor Shall Be Arranged For (Application) Mounting And Shall Be Provided With A.............. ...................-................... \Vertical / - . (Open, Splashproof, etc:) Type Of Enclosure, NEMA } Insulation, And {sieeVe} BearinKs- . Typical Specifications for d-c Motor Control ( Control For {Adjustable 1 Speed d-c Motors Shall Be ({5,TM.*:-} And Sha11. (Adjustable VaryingJ ^magnetic j Consist of a Weaker} And an Enclosed Controller Providing Overload Pro tection j^And Low Voltage {Release Typical Specifications for Squirrel-Cage Motors - ,208, ..Hp,.................................. RPM, {"} Cycles, fj Volts, Squirrel-Cage Induction Motors of the NEMA 550 {Class A--Normal Starting Torque, Normal Starting Current 1 Class B--Normal Starting Torque, Low Starting Current I T Phase, ClassC--High Starting Torque, Low Starting Current J ** Class D--High Slip J Driving............................................. Motor Shall Be Arranged For. } Mounting . (Application) . '' _ And Shall Be Provided With A......................................................Type of Enclosure, NEMA ./Class A\ Insulation, And |g^V(eO|pBeena, rSinpglass. hproof, etc.) ` .- (Class B) must be designed for speed regulating duty which means that it must be capable of carrying the motor current continuously. Speed controllers are available both for constant torque applications and varying torque drives, such as required by fans, in which the torque is reduced con siderably at reduced speed. ." .. The Adjustable Voltage type of speed control is also often known as the variable voltage or Ward-Leonard system. For machines requiring a' wide range in speed control and a large number of steps of control this type of system is used most extensively. The drive consists of one or more d-c motors, the armatures of which are supplied with power from a d-c generator and the fields of (ill machines are excited from a constant voltage exciter. A schematic diagram of connections for an. adjustable voltage drive is shown in Fig. 4. In most cases-the d-c generator is. a part of a three-unit set including a constant speed a-c driving motor. and a constant voltage exciter. As the voltage on the generator and con-, sequently on the d-c motor or motors is adjusted by a rheostat.in the 614 CHAPTER 35 ' 1946 Guide generator field circuit; a great many steps are thus obtained in an efficient manner. With constant field excitation on the motor the speed of the motor Will vary approximately as the voltage on the generator. Extremely wide speed ranges are possible with the adjustable voltage type of drive.- Ranges as high as 10 to 1 are common and, by the addition of field control on the motors, ranges as high as 40 to 1 are permissible. This type of drive provides the advantage of good speed regulation over the entire speed range, as shown in Fig. 3 in which this type of drive is compared with the.adjustable varying speed drive. Typical specifications for d-c motor control are shown on page 613. Motors and Motor Controls 615 motors provide high starting torque with low starting current and are used on compressors,' started' without unloaders, and oil reciprocating ' pumps. Class D motors have high slip * and are used with flywheels for widely pulsating loads on equipment such as reciprocating compressors and pumps where other motors would draw high peak currents. Figs. 5,6,7, and 8 illustrate the characteristics of squirrel-cage motors. It will be noticed by inspection of Fig. 6 that both power factor and efficiency are improved if the motors are operating as near rated load as possible. In addition, as.shown in Fig. 8, power factor and. efficiency are better for higher speed motors. ' Typical specifications for squirrel-cage motors are shown on page 613. Wound Rotor motors are used for applications requiring high starting torque at low starting current, because a wound rotor motor with its '. ...... , ADJUSTABLE VOLTAGE DRIVE-------------ADJUSTABLE VARYING SPEED DRIVE--------------- ALTERNATING CURRENT MOTORS Aiterriatiiig current motors.are divided, into two main classifications:. polyphase and single phase (see Table lj, according to the type of power . supply used. They are further subdivided as to the type of motor winding. ....... . When polyphase power.is available it is usually found more economical to apply polyphase motors in preference to single phase motors. A' typical 5'hp,"1200 rpm capacitor start-induction run single phase motor,' for instance,'will cost-approximately twice as much as the corresponding three phase Class B squirrel-cage motor. In addition,, the polyphase, motor has the advantages of higher power factor and higher efficiency. Polyphase Motors - The-three; types, of -polyphase motors, are: squirrel-cage induction motors, wound rotor induction motors, and synchronous motors. .; :. Squirrel-Cage motors: are specified by. NEMA in classes providing'a variety, of speed and torque characteristics. ' Class A motors provide normal Starting torque at- normal starting current and are suitable-for constant speed: application; to equipment such as fans and blowers,-in which-startingcurrent need not be limited. .Class B motors provide normal starting-torque at low-starting current and are used for the same type of application-las' Class A-where starting current must be limited. Class C controller and resistance can develop full load torque when starting with about full load current. For comparison, a squirrel-cage motor would require from 3 <:o 5 times as much current to develop full load torque at starting. The wound rotor motor is also used for varying speed service to drive fans, blowers, and other continuous duty apparatus. Typical specifications for wound rotor motors are shown on page 616. . The .addition of . resistance-to the secondary'winding of the. wound rotor motor-changes the speed torque characteristics as.indicated in Fig. 9. The motor speed, , with the resistance added,, is-dependent on load and consequently the motor has very poor speed regulation when secondary resistance is added to reduce the speed to values below 50 per cent. . . Synchronous motors-are used for continuous duty applications at con stant speed where efficiency and: power factor; are important. -. Another advantage of these motors is that of lower initial cost in large sizes and for low speeds when compared with squirrel-cage type motors. . . ; The outstanding, advantage, of the synchronous motor is, that its-power factor can be changed to compensate for the. low power factor of, other drives in the same location. Lagging power factor is an inherent charac teristic of all induction apparatus, such as induction motors, and neon signs. Unless synchronous motors or capacitors.are:installed, the plant ' power factor may be comparatively, low. This does not necessarily mean that corrective equipment, must always-be installed, but in most cases it is desirable to determine what advantages may be gained by improving : "Refer to Glossary at end of Chapter. ` ." ' ` 616 CHAPTER 35 , 1946 Guide Typical Specifications for Wound Rotor Motors . [208] _________ ...................... . ...........RPM, jgjj} Cycles, j^i Volts, {3} Phase, Wound Rotor . 155()J ' Induction Motors For Driving.....................................................Motor Shall Be Arranged for (Application) /Honzontall Mounting And shal, Be prov;de{j with A..... .................................. ................. \Vertical / 6 (0pen> Splashproof, etc.) Type of Enclosure, NEMA Insulation and jy['*,(!ve} Bearings. Typical Specifications for Synchronous Motors ..............Hp.____ ___ RPM,............Per Cent P.F., .Volts, j|j Phase, |gg| Cycles, 'Belted ' Synchronous Motors of the Coupled Type for Driving Engine , (Application) Motor Shall be Arranged for /yeI^'lea]'Ia'j Operation and Shall Be Provided With A................................... .....................................Type of Enclosure. Motor Shall be Capable (Open, Splashproof, etc.) . of Developing A Starting Torque of ............ Per Cent Full Load Torque, A Pull-In Torque of Per Cent iFull Load Torque, And A Pull-Out Torque of................................ Per Cent Full Load Torque. The Motor Field Shall Be Excited From A {Direct Connected Exciter' Belted Exciter ' Which Shall ' [Shall Not Be Included With The Motor. M-G Set Exciter d-c Bus the power factor. With purchased power, if the rates include a clause embodying a penalty for low power factor, or a bonus for high power factor, the saving in power costs may often make a very good return on . the investment required for the corrective equipment. Synchronous motors are used to drive fans, blowers, pumps, compres sors and other applications. Compressor applications having a high peak torque require the use of flywheels to smooth out power peaks; and should always be referred to the electrical manufacturer for recommen dations. ' ' Synchronous motors are provided with built-in damper windings on the'rotor and operate during the starting period similarly to squirrel-cage motors. After the motor is nearly up to speed, field excitation is applied and the motor draws into step at synchronous speed. After excitation is applied the motor runs at exactly constant speed and will remain at this speed uiitil a load approaching the pull-qut load is reached, whereupon the motor pulls ouf of synchronism and stops. . . In applying synchronous motors consideration must be given to the torque the motor can develop on pull-in, that is, at the instant when field I Fans I Motors and Motor Controls 617 Fig: 5. Speed Torque Characteristics of Squirrel-Cage Motors excitation is applied. Table 2 tabulates typical application requirements of synchronous motor drives, listing starting, pull-in, and pull-out torques. Typical specifications for synchronous motors are shown on page 616. Multi-Speed motors provide flexibility in many types of drives. Syn chronous motors can be furnished only with a 2 to -1 ratio-in speed, single winding. Squirrel-cage induction motors may be 2, 3 or 4 speed. Two-speed, induction motors are usually of single winding type, having a 2 to 1 speed ratio such as 600 rpm and 1200 rpm,. or may be double winding. Three-speed induction motors are always two winding,' and four-speed motors are usually two winding with a 2 to 1 speed ratio . Table 2. Typical Application Requirements of Synchronous Motor Drives Showing Starting, Pull-In and Pull-Out Torques Application Method of Connecting Motor to Load . Starting Torques Conditions Start Pull- Pull ing in Out Remarks ' ' Exhaust and Ventilating Coupled or Belted Cycloidal Coupled or ' CO Positive Engine Type 41 Blowing Engines 0 Reciprocating Engine Type Turbo High Speed Direct Connected or Step Up Gear ,Air Engine Type . Usually Loaded Unloaded 50 60-125 150 40-60 40-60 150 Unloaded 40 40-60 150 Unloaded (Intake Closed) Unloaded 30 40 50 150 40 150 Ammonia and High Speed--Belted Unloaded 40 40 150 0 Ammonia Low Speed--Engine Type (By By-Pass) 301 Booster Occasionally Coupled . E 0 U Freon : High Speed--Belted Low Speed--Engine Gas * High Speed--Belted Reciprocating - Low Speed--Engine ' ' Unloaded (By By-Pass; Unloaded (By By-Pass) 45 40 60 150 40 150 WR* of Fan Must be Considered Two-Speed Motors Sometimes Used WR? of Blower Must be Considered Flywheel Effect Important - - Flywheel Effect Important ` Flywheel Effect Important Flywheel Effect 'Important .618 CHAPTER 35 1946-Gu-ide Motors arid Motor'Controls . 619 .winding motor and because of the factor of safety provided by two inde pendent windings, the increased cost is frequently worth the difference. Single Phase Motors Single phase induction motors inherently develop no starting torque and are provided with auxiliary windings and devices for starting pur- injeach winding; Motors can be provided in constant torque,' varying torque or constant horsepower ratings. The constant horsepower type of motor is considerably larger them the constant torque motor due to the fact that the same horsepower must be developed-at either reduced speed or high speed. . In selecting two-speed motors for fan, pump, blower, or compressor applications, it is usually found that two winding motors are more expensive than the single winding type. The control cost for two-speed, two winding motors, however, is more economical, and therefore the combined price of both motor and control for the two winding motor is only slightly higher. Because of the improved performance of the two 900 %OF FULL LOADCURRENT TORQUE 100 * MAXIMUM TORQUE .. - 00 STARTING CURRENT 200 . u3 So TYPE OF SQUIRREL CAGE MOTOR So n U it 000 oo- oot4 oon || | | CLASS A i i [ T T1 CLASS e w H- 1' fill CLASS C i c ttsfiral! 1 | rM CLASS 0 g 3 nXn TT1 1 300 X * OF FULL LOAD S.v . 5Zy?nj yh._ji , K.V1 'no o J-1 OsO- uK< ,v 'a< S3 id oDCnett no, N t O f> 111 - rAx&i 1pdTett1j Ib&c1 HI1 TT 1 KSfiSjl 11'xIja 1 .111 Rrcl 1 1 I | rT 1 bli ksssa ri i 1 f1 . X-SAME AS STARTING '_ Fig. 7. Comparative Performance of Squirrel-Cage Motors of ' 30 Hp and Smaller Sizes . Fig. 8. Efficiencies and Power Factors for Squirrel-Cage .Induction Motors poses. The motors are classified as to the type, of auxiliary winding provided. . Capacitor Start-Induction Run motors develop high starting torque with low starting current and are used for all types of constant speed heavy duty drives such as compressors, pumps, and stokers. During the starting period, a winding with a capacitor in series is connected in the motor armature circuit and when the motor comes up to speed a centrifugal switch cuts the capacitor and second winding out of the circuit. - Capacitor motors, which are ideally suited for small fan drives, are similar to the capacitor start-induction run type except that the capacitor . is not cut out when running.- , . ", Repulsion Start-Induction Run motors develop extremely high starting' - torque. They are supplied with a short-circuiting switch which cuts out 620 CHAPTER 35 1946 Guide- Typical Specifications for Single Phase Motors - ..........................Hp,.......................... RPM, Cycles, |23q| Volts', Single Phase Motor of the...................................................Type for Driving.........................................1....... Motor Shall (Capacitor, Split Phase, etc.) (Application) Be Arranged/or jvertical^} Counting And Shall Be Provided With a...................................... ..... ............... Type of Enclosure, NEMA pi Insulation, And (Open, Splashproof, etc.) . f ss J {flrcve} Bearin?s- . Typical Specifications for Squirrel-Cage Motor Control Control for Squirrel-Cage.................... ..................... Motors Shall Consist of An Enclosed (Fan, Pump, etc.) {Magnetic} Type {Red'uced VoVtage} Starter Providin8 verload Protection And Low Voltage Control Shall Include A Safety Disconnect Switch {fnTconTM"0EndoSure} With the Startin Controller. Typical Specifications for Wound Rotor Motor Control Control for Wound Rotor Motor Control for........ Applications Shall Consist of a Safety ' ' (Fan, Pump, etc.) ' Disconnect Switch, a (oJmmon^} Mounted Across the Line Starter Providing Over load Protection, Low Voltage and a Secondar>' {l^S" Regulating} Controller for (M^Sing^in WBEnclo5ure}- Primary and Secondary Contro1 Sha11 Be Interlocked so as to Provide Complete Control from the Rheostat Handle. - the commutator when the. motor comes up to speed. These, motors are suitable for applications such as industrial compressors where - high break-away torque is required and where commutator and brush noise are not factors. . - Split Phase motors have a high resistance auxiliary winding which is in the circuit during starting but is disconnected through the action of a centrifugal switch as the motor comes up to speed. Under running con ditions it operates as a single phase induction motor with one winding in the circuit/ These units are available for the sqiall "horsepower ratings and when equipped-with-a high slip rotor may be used for adjustable Motors and Motor Controls 621 Fig. 9. APerformance Characteristics of Wound Rotor Motor with External Resistance varying speeds through line voltage control. The motors are ideally suited for fan duty. . Speed-torque characteristics of single phase motors are shown in Fig. 10. Typical specifications for single phase motors are shown on page 620. CONTROL FOR ALTERNATING CURRENT MOTORS Squirrel-Cage motors are usually linestarted where power company limitations permit. In sizes up to 2 hp the motors are started by means of manual switches with an overload current element for motor protection. Fig. 10. Speed-Torque Characteristics of Single Phase Motors.. 622 CHAPTER 35 1946'diiide Typical Specifications for Synchronous Motor Control Synchronous Motor Control for._ (Application) /\RFeudlluVceodltaVgoeltage} Starting And Shall Be ..Motors Shall Provide for } (^uced Voltage Starting Shall Be Obtained By `Means of Autotransformers | . Resistors And Shall Limit Reactors J . The KVA Inrush, to a Maximum of____ per cent of Full Load KVA.) The Control Panel Shall Be For (Isolated -}\ Assembly And (Switchboard Shall Be of Construction. It Shall Provide Overload, Under Voltage Protection And' After Pulling Out of Step Will {feES R^ynchronizej The Motor. . Typical Specifications for Single Phase Motor Control Control For Single Phase--....................................................................Motors Shall Consist of a ' ' ' (Fan, Pump, etc.) , {Magnetic} Type {R^ced Volt'a^e} Starter Providins: Overload Protection (And Low Voltage); And A Separate Safety Disconnecting Switch. ' In larger ratings a linestarter is usually provided with either an addi tional safety switch or circuit breaker for disconnecting and short circuit protection. Reduced voltage starting may be either of manual or push . button controlled magnetic type. In specifying this type of starter con-, sideration should be given to the fact that starting, torque of squirrelcage motors varies as the square of the applied voltage. For example, a motor developing 100 lb-ft starting torque on full voltage would produce only 25 lb-ft torque on starting on half rated voltage. Fig. 11 illustrates recommended control practice for squirrel-cage motors. Typical speci fications for squirrel-cage motor controls are shown on page 620. Wound Rotor motors require control of both primary and secondary circuits. The primary* control may be the same as for squirrel-fcage motors, manual or magnetic, at full voltage. . Secondary* control pro vides means of varying secondary resistance for starting and speed, control. The secondary controller should be specified for starting duty only or. for speed regulating duty. Fig. 12 illustrates recommended control practice for wound rotor motors. Typical specifications for wound rotor motor control are shown on page 620. . ,, , *Refer to Glossary at end of chapter. Motors and Motor Controls 623 Synchronous motor starters should provide pu!l-.qut protection, auto matic synchronization or automatic stopping of the motor after pull-out, and insurance of complete starting sequence, as well as overload and low voltage protection. The control may be either magnetic or semi-magnetic at full or reduced voltage. Semi-magnetic starters provide automatic field control but require hand operation for closing the line contactors to start and transfer to full voltage. ' In applying reduced voltage starters to synchronous motors it should be remembered that, since these motors are started on damper windings and during the acceleration period function similarly to squirrel-cage motors, the starting torque varies as the square of the applied voltage., ACROSS THE LINE STARTING Arrangements 2, 3, 4 and 5 provide automatic push-button starting. Fig. 11. Recommended Controls for Squirrel-Cage Motors Consideration should be given to insure development of sufficient motor torque to accelerate the load. . Typical specifications for synchronous motor control are shown on page 622. . Multi:Speed control may be either manual or magnetic,, and at full or reduced voltage. When using automatic magnetic control with, two-, three-, and four-speed separate winding. or consequent pole motors, ' control may be obtained from a remote point by means of a push button master switch. The various speeds of the motor are obtained from the master switch by simply depressing the correct push button. This is known as selective speed control. It is commonly used in. the smaller theater installations where the fan and motor are located backstage and the speed control is located in the lobby. . . Multi-speed motor controllers may be provided with compelling relays which make it necessary for the operator to press the first speed button before regulating the motor to the desired speed. This insures that the motor is always started at low.speed before adjusting.to a higher speed.' 624 CHAPTER 35 1946 Guide LINE LINE ' LINE i- , SPEED X 1 REGULATING 1 I CONTROLLER MOTOR Fig. 12. Recommended Controls for Wound Rotor Motors Timing relays which provide for automatic acceleration' may be used for control. With this feature the motor will always start at low speed and automatically accelerate to the desired speed. Decelerating relays may be used to reduce the shock effect of the braking action to the motor and drive when the speed is reduced from a higher to a lower speed. Single Phase motor control usually consists only of a linestarter, either manual or magnetic. In some cases it is desirable also to provide a disconnect switch. Fig. 13 illustrates the recommended controls. Typical specifications for single phase motor control are shown on page 622. . LINE [nl safety 11 SWITCH MANUAL STARTER (REDUCED VOLTAGE^ MOTOR Arrangements 2, 3 and 4 are optional for motors up to 7M hp. 220 volts; ,. : Fig.' 13. Recommended Controls for Single Phase Motors Motors and Motor Controls 625 GEAR MOTORS A gear motor is a self-contained combination of any type of a-c or d-c motor and an enclosed speed-reducing gear, providing a more compact and readily adaptable unit than is obtained by using a motor coupled to a gear reducer. Gear motors are available in sizes up to 75 hp with output shaft speeds from about 4 to 1430 rpm, making it possible to couple or to' connect by gear or chain to nearly any machine. High speed motors are used, generally 1800 rpm on 60 cycles, thus obtaining the advantages of high motor power factor and efficiency. The gearing efficiency is also' high, usually about 98 per cent for a single reduction of the helical or . spur type, that is, a 2 per cent loss for one reduction or 4 per cent loss . for a double reduction. Consequently, the over-all performance of the gear motors is much higher than a.combination of open gearing, belting, countershaft, or other arrangement, which would otherwise be required. Gear motors are used extensively to drive numerous types of slow speed drives. Besides being more effective than other combination drives in saving space, they are important in reducing maintenance and oper ating hazards. v, General Definitions GLOSSARY . NEMA is the abbreviation for the National Electrical Manufacturers Association. Speed Regulation (d^c motors) is the change in speed between no-load and full-load, expressed in per cent of full-load speed; for'example, a motor having a no-load speed of 1200 rpm and a full load speed of 1140 rpm would have a speed regulation of 5.6 per cent. Slip (a-c induction motors) is the difference between the motor speed and synchronous speed expressed in per cent of synchronous speed, e.g.t a 1200 rpm.motor operating at 1140 rpm would have a slip of 5 per cent. Torque is an expression of the turning effort developed by the motor at the shaft and is usually expressed in ounce-feet for fractional horsepower motors and in pound-feet for motors of larger ratings. . . ** Primary is the term usually applied to the high voltage or line side of a transformer or motor. In the case of the wound rotor motor the primary, is the stator winding. Secondary is the term usually applied to the low voltage or load side of a transformer or motor. In the case of the wound rotor motor the secondary is the rotor winding. NEMA Classification of Motor Enclosures , Open motors (40 C rise) are self-ventilated1 machines having no restriction to venti lation other than that necessitated by mechanical construction. Protected motors (50 C rise) have all ventilating openings in the frame protected by perforated*covers. -` '" Semi-Protected motors (50 C rise) have the ventilating openings in the top half of the frame only protected by perforated covers. . Drip Proof motors (50C rise) are so constructed that drops of liquid or solid particles falling on.the machine at any angle not greater than 15 deg from the vertical cannot enter the machine either directly or by striking and running along a horizontal or inclined surface. Splash Proof motors (50 C rise) are so constructed that drops of liquid.or solid par ticles falling on the machine or coming towards it in a straight line at any angle not greater than 100 deg from the vertical, cannot enter the machine either directly or by striking and running along the surface.. .. . Totally Enclosed Non-Ventilated motors (55 C rise) are so constructed as to prevent exchange of air between the inside and outside of the case. 4 Totally Enclosed Fan-Cooled Motors (55 C rise) are similar to totally enclosed, non- ventilated machines except that exterior cooling is provided by means of a fan or fans integral with the machine. - Explosion Proof motors (55 C rise) have an enclosing case designed to withstand anJ explosion of a specified gas or vapor which may occur within it, and to prevent the 626 CHAPTER 35- ' 1946 Guide ignition of the gas or vapor surrounding. the motor; by sparks, flashes, or explosion of the gas or vapor which may occur within the machine casing. '' Water Proof motors (55 C rise) are so constructed as to exclude water applied in the ' form of a stream from a hose. .. .. ' '_ .Dust Tight motors (55 C rise) are so constructed that the enclosing case will exclude dust. . . . . Motor Speed Classifications , . A Constant Speed Motor is one in which the speed remains practically constant with changes in load; e.g., a d-c shunt wound motor or a-c squirrel-cage motor with low slip. A Varying Speed Motor is one in which the speed varies with the.load, usually decreas ing when the load increases; e.g., a d-c series motor or an induction motor with large slip. An Adjustable Varying Speed Motor is one in which the speed.can be adjusted gradu ally, but when once adjusted for a given load will vary in considerable degree with change in load; e.g., a shunt wound d-c motor adjusted by armature resistance control. An Adjustable Speed Motor is one in;which the speed can be varied gradually over a considerable range, but when once adjusted remains practically unaffected by the load; e.g., a. d-c shunt motor with field resistance control. . The standard ratings for open type, adjustable speed motors, having a speed range'of 3 to 1 and greater are in accor dance with the following: '. (1) A standard continuous horsepower rating at 150 per cent of minimum speed with . . a temperature rise of 40 C. . (2) The next higher standard continuous horsepower rating at 3 times minimum speed with a temperature rise of 40 C. . (3) Between 150 per cent of minimum speed and 3 times minimum speed, the standJ ard continuous horsepower rating with a temperature rise of 40 C will vary with ; . the speed along arstraight line.connecting these two.horsepower ratings. No further increase in horsepower.is recognized above 3 times minimum speed.-. . (4) Below 150 per cent of minimum speed the lower continuous horsepower rating _s (see preceding.item 1) will apply with a temperature rise of 50 C. . Example: 20/25 hp, 400 to l600 rpm. This motor may be rated 20 hp, 40 C at 600 rpm and 25 hp, 40 C from 1200 to 1600 rpm. Between 600 and 1200 rpm the rated horsepower increases .directly with speed from 20 to 25 hp. (5) Motors may also be rated 1 hour with temperature rise of 50 C with the higher horsepower rating (see preceding item 2) throughout the entire speed range. ' Example: 20/25 hp, 400 to 1600 rpm. : This motor may be rated 25 hp, 50 C, 400/1600 rpm; 1 Hour. - Mechanical Modifications * - . . .. Vertical Mountings are available for such applications as pumps, agitators, and so forth. This type of application may require a special umbrella-type hood to protect against dripping liquids. ... .. . Flanged Mountings are available for use where motors are built in as part of machines. Motore may. also be supplied with flush plate mountings, suitable for close coupled pump and similar applications. CHAPTER 36 Unit -Jir (Conditioners, Unit ^dttic Jans . Definition of Types, Unit Air Conditioners, Heating, Hurniditying. Cooling and Dehumidifying, Filtering, Ventilating, Types of Units, Application, Ratings, Unit Air Coolers, Design and Performance, Types of Units, Ratings, Defrosting, . Economics, Attic Fans ' ^ ' . AN assembly of functional elements, as indicated by the name, comprises the unit air conditioner or unit air cooler. Such a unit when complete in itself, employing its own direct means of air distribution and source of refrigeration is known as a self-contained unit. When used in various combinations with remote sources of refrigeration, heat or air supply, it is termed a remote unit, indicating that the source of refrig eration is not contained within the unit cabinet. Either the self-contained or remote type units may be located within or without the conditioned area, and are a separate classification from the central plant type of system, as described in Chapter 43. . - The code, Standard Method of Rating and Testing Air Conditioning Equipment1, defines the various types of unitary equipment: 1. h Cooling Unit is a specific air treating combination consisting of means for air circulation and cooling within''prescribed temperature limits. ' 2. An Air Conditioning Unit is a specific air treating combination consisting of means for ventilation, air circulation, air cleaning and heat transfer with control means for maintaining temperature and humidity within prescribed limits. 3. A Cooling Air Conditioning Unit is a specific air treating combination consisting of means for ventilation, air circulation, air cleaning and heat transfer with control means for cooling and maintaining temperature and humidity within prescribed limits. 4. A Self-Contained Air Conditioning or Cooling Unit is ope in which a condensing unit is combined in the same cabinet with the other functional elements. Self-contained air conditioning units are classified 8 according to the .method of rejecting condenser heat (water cooled, air cooled, and evaporatively cooled), method of introducing ventilation air (no ventilation, ventilation by drawing air from outside, ventilation by exhausting, room air to the outside, or ventilation by a combination of the last two methods), and method of discharging air'to the room (free delivery or pressure type). r 5. A Free Delivery Type Unit takes in air and discharges it directly to the space to be treated without external elements which impose air resistance. .- 6. A Pressure Type Unit is for use with one or more external elements which impose air resistance. ' .. ' '* 7. A Forced-Circulation Air Cooler is a factory encased assembly of elements by which heat is transferred from air to evaporating refrigerant*. . UNIT AIR CONDITIONERS . ' This equipment takes the form of an encased assembly including the apparatus necessary to perform either some or all of the functions of cooling, dehumidifying, filtering, ventilation, air circulation, heating, and humidifying. Control of air conditions is provided by' manual switches, manual dampers, and automatic devices, in combination. The controls are either mounted on the units, or in some suitable location in the conditioned area. See Chapter 34 for a discussion of controls. The various conditioning elements and their functions, which produce the required effects on air, are discussed under separate headings. Heating . '. Heating is usually accomplished by means of a heating coil in the unit, ` `' 627 628 CHAPTER 36 1946 Guide supplied with steam or hot water from an external source. Electric strip heaters may also be considered, where installation and operating costs justify their use. They are often used in special control applications. Reverse cycle heating as described in Chapter 39 has been developed as a feature in some unit air conditioning equipment, but this form of heating has not yet been generally adopted. . Humidifying Adding moisture to the air involves the absorption of heat, by the humidifying water, for conversion to water vapor. Heat may be supplied by heating the humidifying water, or supplied from the air to be humidi fied. In the latter case the air may be warmed or the water finely divided to present a large evaporating surface to the existing air. The source of heat may be from electricity, steam or hot water coils, or from a heat transfer surface as in a direct-fired unit.. Occasionally vapor is added directly by means of steam jets but this is usually confined to industrial applications because of the presence of some odor from the steam. Methods and types of humidifying apparatus are dealt with in detail in Chapter 37. For unit application, some of the available methods are the spray nozzle, or the atomizing nozzle, the impact-jet, the' drip screen and the evaporating pan. The first method is usually employed where humidi fication on a large scale is desired, as with large remote industrial units. Eliminator plates are necessary and the water supply may be recirculated by a pump or wasted to the drain. The drip screen, impact-jet, evapo rator pan or small atomizing jets are used when humidification is desired in the smaller remote and self-contained units. * Wetted surfaces exposed to the air stream and utilizing the capillary action of water on porous substances such as. fabrics and ceramics, are used for adding moisture to air. Frequent cleaning or replacement is necessary to avoid closing of the pores and to maintain freedom from odors or growths on the humidifying element. Cooling and Dehumidifying These two functions of air conditioning are usually performed simul taneously, although both may be done separately. For example,,air may be dehumidified or dehydrated without sensible cooling by the process of adsorption. Sensible cooling of air may be accomplished without dehu midifying by maintaining the cooling surface temperature above the dew-point-temperature of the air to be treated. Chapter 7 explains these fundamentals in detail. Unit equipment commonly utilizes heat transfer surface such as pipes or coils, through which a cooling, medium such as water or.a refrigerant, is circulated. Types and methods of generating cooling mediums are covered in Chapter 39. Brine or water sprays may be used if desirable, either separately or in combination with coil or pipe surface. However, these methods find their best application in the larger, remote type units.' Surface temperature and area of the coil or pipe, air volume and velocity, and spray temperature and volume are some of the controlling factors in unit air conditioner design and application. Ice as a cooling medium is practical but is seldom used in connection with units. . Filtering ., Cleaning of outside or recirculated air discharged to the conditioned area is one of the important functions of air conditioning, ahd.air filters Unit Air Conditioners, Unit Air Coalers, Attic Fans 629' should be included, on all units which condition air for comfort. Pro tection is also afforded the cooling and heating coils as well as the con denser coil in the case of the air cooled type. . . - Means of filtering may vary from the lint screen to the electrostatic filter, with the degree of efficiency covering a wide range. Inexpensive throw-away type filters lend themselves well to the compact design of the unit conditioner. Air cleaning devices form the subject of Chapter 33. Ventilating Provision for the introduction of outside air should be an essential part of unit conditioner design. Odors and air vitiation are avoided and better load control is possible when a positive means of introducing outside air is available. . On the small, air cooled room units, it has been found practicable to con-; trol the air in such a way as to permit variation from all recirculated air to 100 per cent outside air. An added feature is a dampering arrangement whereby it is possible to exhaust air from the room to remove smoke and generally ventilate the space. A code4 sponsored by a Joint Committee of the A.S.H.V.E. and the American Society of Refrigerating Engineers may be consulted, although it should be realized that individual applications may often show a need for ventilation in excess of these minimum requirements. Types of Units _ Unit air conditioners fall into two general classifications, depending on the location of the refrigeration source. Those units having the con densing unit completely enclosed in the same cabinet as the evaporator are known as self-contained types, while those units having the condensing unit remotely located from the evaporator and requiring piping of refrigerant from the condensing unit to the evaporator and return are known as remote types. Self-contained units are further divided into two groups in accordance with their condensing mediums, being either air-cooled or water-cooled. Evaporative cooled types are included in this latter class. . The air-cooled types are small in capacity, ranging from to lj^ hp. Their principal application is for conditioning such spaces as hotel rooms, offices and residential living quarters. A duct connection between the unit and an outside window or ventilated air shaft is required to permit disposal of the heat extracted from the conditioned area. The unit may stand in front of the window or be mounted on the window sill. Various styles and types of windows are encountered which increase the difficulty of making the window connections. The evaporation of condensate on the condenser coils, as a means of disposing of this moisture, tends to increase the condensing capacity and reduce the operating head pressure. Some units add supplementary water so that increased capacity may be obtained from constantly wetted condenser coil surface. Connections to an electrical outlet may be by means of a conventional cord and plug or a permanent electrical connection, depending on local code rulings per taining to the installation of small motors. The exterior finish of the unit in metal, wood or fabric is decorated to harmonize with office or bed room furnishings. . A unit of the air-cooled condenser type for floor mounting is shown in Fig. 1. Of the two fans shown, the lower one acts as condenser air fan, and in some units this fan is arranged with slingers for .discharging con densate oh the condenser .coil while the. upper, fan discharges air into the . 630 _____________ . CHAPTER 36. , .1946 Guide conditioned area. A feature of the design shown in Fig. .1 is that the condensate, from the cooling coil is sprayed over the condenser surface ' - and vaporized, thus eliminating the need , for drain connections. - A simple tampering arrangement is generally provided for exhausting some air from the-room, in addition to introducing outside air and recirculating required amounts of air. It is possible to remove the equipment for winter storage or utilize the ventilating features for winter operation. , Water or evaporative-cooled units start at 1 hp in size and may be as large as 30 hp. Condensers requiring water use either city water, well . water or recirculating water from a cooling tower. Evaporative con densers are seldom used on units under 5 hp. ' . The heat generated by the compression of refrigerant gases and that given off by the electric motor is removed from the compressor compart ment in four ways: by the use of a water coil in the compressor compart- ment; by means of utilizing the cold suction gases; by drawing part of -' the return air through the compressor compartment and finally by Unit Air Conditioners, Unit Air Coolers, Attic Fans 631 heating and-ventilating. Refinements of dust and odor control and constant temperatureand' humidity . regulation ; are considered to. be special application problems with this type of equipment. A typical unit with - water-cooled condenser is illustrated in Fig. 2. The header arrangement permits air'distribution in several directions, and in such a way as not to fall on the room occupants. All side panels are removable for complete access to-equipment. It is only necessary to bring water, drain and electrical servfce to the unit, and a source of heat if desired. . . Remote type units cover a much broader range of size and application and generally are used in connection with or .in lieu of a central plant Fig. 1., Self-Contained Air-Cooled Unit Air Conditioner circulating room air through the compressor compartment by means of a fan attached to the motor shaft. \ The smaller water-cooled units have somewhat the same application as the air-cooled units. Water and drain facilities must be available and, although window connections are not required for heat disposal, it is desirable to have an outside , air connection for ventilation purposes. Electrical wiring is generally, permanently connected. Up to 7]/2 or 10 hp in size the units are usually styled for locating directly in the conditioned area. Above this size the tendency is to locate the equipment adjacent to the conditioned area, with supply and return duct connections. Compressor compartment heat is removed by the same methods described previously. - 1 ., On water units of the vertical type of 5 hp and under, use is- made of air distributor headers, equipped with directional louvers, on one or more sides, for discharging the air directly into the conditioned space in which the unit is located. Above 5 hp this method usually becomes impractical and a system of ducts is employed. Arrangements for outside air supply . are similar to those , in central plant design, although simpler, hand operated dampers are usually employed. . , , Accessory equipment for the self-contained unit conditioners includes heating coils, humidifiers,- and controls for utilizing the unit for winter Fig. 2. Self-Contained Water-, Cooled Air Conditioner - Fig. 3., Vertical Remote Type Unit Air Conditioner ' system. They may be used individually or in. groups in the place of self-contained equipment. ' Without the weight of the refrigerating equipment, these units may be suspended from roofs or ceilings, or located wherever space permits on roofs and in basements, or in the conditioned area itself. All . combinations of filtering, humidification, cooling and heating may , be employed, with control as elaborate or as simple/as . is required. The remote unit is particularly adaptable where a variety of application con ditions- is to be met from a single source of refrigeration, such as the modern industrial plant which may. nave a laboratory, executive offices, a cafeteria, together with various processing departments.- ./ The cooling and heating mediums, consisting of a refrigerant, chilled water or brine, and steam or hot water, are piped to the units, and transfer takes place by means of coils, or in the case of air washers, by means of water or brine sprays in the air stream, or a combination ,of the two.. . The floor mounted or vertical type and the suspended or horizontal type of remote units are respectively shown in Figs. 3 and 4. The-cabinets ' are generally of sheet steel,.insulated to prevent heat transfer,-finished to prevent corrosion and suitable for'applying decoration if desired,-. .. . . 632 CHAPTER 36 1946 Guide. A spray type remote unit is illustrated by Fig. 5. Many designers prefer the air washing and coil wetting features. Air is circulated by means of attached or built-in fans, delivering the conditioned air through a system of ducts, which include outside air connections if desired. . Some types of units, mostly those suitable for suspension, employ a propeller fan such as in Fig. 6. These are located in the conditioned area, are without ducts and seldom do more than cool and dehumidify, since the propeller fan is not designed* to move air against high pressure. Generally these units are provided with a lint screen instead of filters to limit resistance to air flow. Individual floor mounted type remote units are available for use in offices or hotel rooms. Similar in appearance but somewhat smaller in size than the self-contained room unit, this form of equipment may be grouped: , 1. Mechanical, year 'round type containing blowers, filters, humidifiers and coils, with outside air connection. Manual or automatic controls provided with .each unit. Unit Air Conditioners, Unit Air-Coolers, Attic Fans. 633 % Application - ', ' In the application of unit air conditioners it is important to consider several factors: 1. Location of equipment. . . 2. Air distribution. . . 3. Multiple units versus central station system. . 4. Multiple remote unit system versus a self-contained unit system. 5. Methods.of control. 6. Methods of conserving water. 7. Code limitations. ` In choosing locations for air conditioning units, consideration must be given to the characteristics and use of the conditioned space; , type-of system contemplated; duct locations; sources of power, water, refrigera- Fig. 5. (right) Spray Type Remote Unit Air Conditioner 2. Mechanical, semi-year 'round type with .no outside air connection, containing blowers (filters optional), and coils. Usually- used where there is an existing radiation or ventilating system.' Controls provided with each unit. . . 3. Non-mechanical type containing coils, using air ejected under pressure from a remote source for inducing circulation over coils '(see Chapter 43). Manual or auto matic control of air temperature only is provided. Both summer and winter air con ditioning functions may be performed by the one unit. ' One coil for cooling and heating may be provided or a single coil used, through which hot water in winter and cold water in summer is circulated.' All three types of systems require remote sources of refrigeration, with' the first group obtaining outside air from the window, the second group having no outside air unless used in connection - with a central plant or ventilating system and in the case of the third group, all. air delivered under pressure is outside air. Various combinations or alterations of these room units are available. Different filtering,- humidifying and air delivery methods are employed, to achieve the desired conditions. A typical remote floor type room unit air conditioner is shown in Fig, 7. - : Fig. 6. Suspended Propeller Fan Type Unit Air Conditioner . tion, heating and drainage; and accessibility of equipment and system" for maintenance. Where units are' placed within the conditioned area, particular atten tion must be given to air distribution, sources of outside air and con venience to service sources and facilities previously noted. Skill and ingenuity are required to produce a neat appearing, inconspicuous job ' without sacrificing, quality from an engineering point of view. This may , be accomplished by building the units into the woodwork or walls, and refinishing them to match existing furniture and fixtures. Where location of equipment outside of conditioned space is possible, use may be made, of storage rooms, halls, basements or any space less valuable than that to be conditioned. Less emphasis need be placed on the appearance of equipment. . . .. The choice of equipment location is frequently influenced by the relative cost of long runs of insulated ducts required in order to locate units near refrigeration sources, as compared with short duct runs but long extensions of service facilities. Gare must be taken that equipment ` will not be damaged by climatic conditions. -- Air distribution from units located within the conditioned area is by means of grilles, either fixed or adjustable and mounted in air distribution. headers, either furnished with the unit or constructed-at the installation to meet the needs of the application under .consideration. A system of ducts and distribution grilles.may also be used, similar to the arrangement. 634 ____________ CHAPTER 36 . 1946 Guide , used when equipment is outside of the conditioned area. The problem of securing a supply of outside air is often a difficult'one. The proper design of ducts is of major importance for good air distribution. Chapters 40 and 41. are ^devoted to these subjects. In the analysis of any large structure to be air conditioned which is . divided into small spaces, such as an office building or hotel, a comparison should be drawn between the use of units and a central plant system. This study is one of economics, and should include, such factors as first cost, installation costs, obsolescence, depreciation, maintenance costs, return on investment, flexibility, time of installation and possible loss of useful space during installation. This same , analysis should be extended to include a comparison of remote units with self-contained units. Self-contained units, are possible where short term leases are involved, or where wiring can readily be brought to location or where existing water and drain facilities are adequate to handle the increased demand of water-cooled models. On . Fig. 7. Remote Floor Type Room Unit Air Conditioner the other hand, remote type room units contain less mechanical ma ' chinery, avoid the operating cost penalty of an air-cooled condenser, as in the.case of the self-contained, air-cooled room units, and seldom require heavy wiring to handle the fan load. In general, the smaller remote units are more suitable for use with new: construction, where the units will probably remain during their useful life. This condition may change where larger, ceiling mounted units are compared with the floor mounted self-contained units. Controls are essential in unit application and range from the simple snap switch of a room unit to elaborate means of control- ling temperature, humidity and air movement in laboratory and testing room application: The criterion of a well controlled, installation is one which has neither too few nor too many controls. (See Chapter 34.) With the expansion of cities during the past decade, the problem of water supply has become a costly and ever present problem6. Con sequently, laws are appearing designed to restrict the usage of water wherever possible, particularly when substitute means are available. . Evaporative condensers and cooling towers (described in Chapters 37 and 39) are means devised to save large quantities of water in this connection.- . ' Unit Air Conditioners, Unit Air Coolers, Attic Fans 635 Table 1.' Standard Rating; Basis for, Self-Contained Air Conditioning Units Functions Types of Units Item Rating Condition ' Description, ' ' Value ' All All a Barometric Pressure ' 29.92 in. Hg. b Unit Ambient and Air Entering Water-Cooled, Room--Air Inlet .. Air-Cooled (1) Dry-Bulb 80 F and. Evapora (2) Wet-Bulb - . 67 F tively Cooled Condensers c Ventilation Air . See Note Cooling Water-Cooled d Water Temperature Entering Unit 75 F e Water Temperature Leaving Unit 95 F Air-Cooled f Air Entering Outside Air Inlet and Evapora (1) Dry-Bulb tively Cooled (2) Wet-Bulb Condensers 95 F 75 F Heating g Unit Ambient and Total Air Enter ing Unit 70 F All Types Provided h Heating Medium, Pressure or with Heating Function - - -Temperature (1) Dry Saturated Steam 16.7 lb per sq in. abs. (2)'Water In (3) Water Out . . 180 F 160 F All Types i Unit Ambient Provided with Humidifying Humidifying Total Air Entering Unit Function (1) Dry-Bulb (2) Wet-Bulb 70 F . 70 F 53 F Air Circulation . All k Filters New and . Clean Note: Rating shall be based on both ventilation and recirculated room air entering at 80 F dry-bulb and 67 F wet-bulb temperature. (The Note as given in the code has been condensed in order to remove material not pertinent to this chapter). ^ '. Most manufacturers furnish equipment designed for use in combination with these water savers. - . - .. Municipal plumbing, heating, electrical and refrigeration codes, as well as fire underwriter restrictions, are likewise having their effects on the . application of unit, air conditioners. Meeting municipal and national code requirements should be an important item in connection with the installation of any unit equipment. . Ratings - ., . There are two codes governing the rating and testing of unit air con-, ditioners. The .first code, Standard Method of Rating-and Testing Air Conditioning Equipment *, covers all types of air conditioning units except the self-contained type. The latter is covered by the second, code, The, Standard Method of Rating and Testing Self-Contained Air Conditioning Units for Comfort Cooling *. The two codes are necessary because of the basic difference caused by the heat given,up by the self-contained, units. 636 CHAPTER 36 1946 Guide- The standard rating conditions for self-contained unit air conditioners, as given in the code, are set forth in Table 1. . ' The standard rating of a self-contained unit for the conditions specified in Table 1 includes all items which apply to the function of a unit as: (1) name of unit, (2) functions which unit performs, (3) data on cooling, (4) data on heating, (5) data on air flow, and (6) data on humidification. ' The standard rating conditions for unit air conditioners. Other than the self-contained type, are identical to those in Table 1 except the entering V wet-bulb temperature for cooling is expressed as 50 per cent relative humidity (66.7 F wet-bulb) instead of 67 F wet-bulb temperature. In i. addition, the saturated suction refrigerant temperature for comfort cooling is specified at 40 F. This condition is omitted from Table 1 for *. Unit Air Conditioners, Unit Air Coolers, Attic Fans637 coils, the designer is able to produce a wide range of performances and to offer many desirable features not obtainable with the coil and bunker method. More uniform temperatures, high relative humidity, moderate first cost and a minimum of installation expense are likewise factors in their development. . - ._ New uses have appeared for unit air cooler application in industrial and commercial processes involving both the raw materials and finished product, where the maintenance of low temperatures is a necessary part of these processes. Of particular interest is the new field, of extreme low self-contained units as immaterial in the rating of a unit that includes the evaporator and condensing unit. UNIT AIR COOLERS This type of unit is primarily intended to perform the main function of cooling air, with humidity control a secondary function within the limita-. tions of the design, The main application of this equipment is in process and product refrigeration such as cold storage warehousing, fruit and vegetable packing, in breweriespand in wholesale and retail food market's; although some comfort cooling may be obtained by' the use of a unit similar in design to this type of unit as previously explained and as illustrated by Fig. 6. ' \ . . 'Application of the unit method of air cooling with mechanical circu lation is comparatively recent, being an improvement over the pipe or finned coil, which depended on gravity for circulation. Bunkers were sometimes constructed around the coils to direct the air flow- and some times fans were used for forcing air over the coils. The location of the unit air cooler is usually within the refrigerated area, but the larger, blower type models may be remotely located. . Design and Performance .. , Greater application and use of commercial refrigeration have resulted from the'development of the unit air cooler: Flexibility of design has permitted almost any condition to be met. By varying such physical features as the method of introducing the refrigerant into the coils; , the - depth of coil rows and area of their surfaces, and the air volume over the Fig. 9. Surface Type Cooling Unit Fig. 10. Brine.Spray Type .Cooling Unit temperature application where many new uses for refrigeration are being found. , Types of Units . The two standard types are the suspended or ceiling type, and the vertical or floor mounted type. There are variations of this such as the panel type which is wall mounted and arranged to take in air from the . lower section and discharge it from the upper section. . The ceiling type has the appearance of a unit heater, with its propeller type fan blowing air through a bank of coils as shown in Fig. 8. Singly or in combination, they are easily installed and occupy little or no useful space. Alterations may be accomplished with little cost by relocating - units or adding additional ones for increased capacity. The floor mounted types employ blower type fans, as their air deliveries are higher and their locations may be remote from the space to be refrig erated. This type of unit is illustrated by Fig. 9. Air velocities and volumes must be designed for the individual application. This type of unit may employ a pump to spray a eutectic solution over the coils for the purpose of avoiding frosting as shown in Fig. 10. 638 CHAPTER 36 . 1946 Guide Ratings . V. . . ' ; _ , In order to rate and test equipment of this kind which normally operates below the frost line, a proposed code. Standard Methods of Rating and Testing Forced-Circulation Air' Coolers for Commercial arid Industrial Refrigeration 3, has been issued. This proposed standard covers only the modifications of the Standard Method of Rating and Testing Air Con ditioning Equipmentl, as it is related to the different applications of unit air coolers. In this standard, the gross cooling effects are taken since the motor power input equivalent is to be computed as part of the load. From this code Table 2 is abstracted to show standard .rating con ditions for forced-circulation air coolers. Other modifications take into' . Table 2. Standard Rating Conditions for Air Coolers . Group No. i ii in IV V Entering Dry-Bulb ' Temperature. . F Deg 45 . 35 35 0 0 Entering Relative Humidity, Per Cent 85 85 85 85 . 85 . Evaporating Temperature. F Deg 30 25 15 -10 . -20 ` consideration the effect of frost formation on the coils and the change . in length of test runs required to meet such conditions. . ' Defrosting -. Unit air coolers are often required to operate in rooms where air and refrigerant temperatures are below the freezing point. This results in the freezing of the condensation on the coils and this accumulation of frost. - builds up to such an extent that there is a loss of capacity. This deposit - is removed from the coils by the process known as defrosting which may be accomplished by several methods: 1. Where the room temperature is above the freezing point, the flow of refrigeration ` to the coils is halted and the fan continued in operation until the coils are defrosted. . 2. The hot gas defrosting method is accomplished by a valving arrangement whereby ., hot compressed gases from the compressor are pumped directly into the evaporator, , This operation is continueduntil defrosting is complete, when the system is returned - to normal operation. . . .. ,, ^.' 3. Where brine is used as a refrigerant, hot brine may be circulated .through the coils. . . Where the frosting is particularly heavy it is sometimes more advisable to apply the source of heat externally. This principle of defrosting is accomplished by: . .. ' 4. Defrosting by warm air is accomplished by dampering arrangements which permit . the cooler fan to draw warmair from a source outside of the refrigerated space', pass it over the coils and discharge it outside of the refrigerated space. ' . 5. Constant wetting of the coils with' a brine or eutectic solution prevents the for-, mation of frost. This is accomplished on a vertical unit air cooler as shown, in Fig. 10. - . 6. Electric heating elements, placed in such a manner that the fan forces.the heated , . air over the coils. ' , . 1. Water sprays, placed so that the coil is thoroughly wetted during the defrosting, process, are a simple means of defrosting. City water at ordinary pressures is used. ' . The fan is-not running during this operation. ...... . -, Those systems using method 5 have the problem; of removing con- i Unit Air Conditioners, Unit Air Coolers, Attic Fans 639 densation from the eutectic solution. One -way is to waste the entire charge when dilution has rendered it ineffective. . Another method employs a device which boils off the water and returns the eutectic solution to the system for further use. . ECONOMICS In the planning and designing of a unit system or in comparing units with central plant application, a systematic approach to the problem should be made from the economic viewpoint. First Costs. The question of first cost is but one factor in the economic approach of a skillful designer or an intelligent buyer. - 1. Equipment. The use of a large percentage of factory fabricated equipment to maintain installation costs at a minimum, as represented by self-contained units, should be contrasted with the use of systems with a large percentage of installation labor and material, such as a central station system. The remote unit offers a compromise between these two.- . . . . 2. Installation costs. The influence of existing codes and ordinances, and installation - conditions, involving new construction or treating an existing structure deserve careful : consideration. Methods which are suitable for new construction often may not be ' applied on buildings erected in the past. Sprinkler system rearrangements, fire doors and dampers, restrictions on multiple direct expansion units, rewiring or increasing service, cutting or reinforcing of ceilings and roofs are some items which should receive attention in this respect. .. .. ;; Operation and Maintenance. Tenants or occupants usually operate the self-contained equipment, which also lends itself readily to contract service for maintenance. Central plants require operating engineers in 1 ; attendance who also frequently service the equipment. The remote units require a combination of these two methods of operation with maintenance by building personnel. .. Water and power costs per season can be tabulated and compared for the various systeriis arid an estimate of the costs of replacement material , . such as filters, belts, oil, refrigerant and wearing parts should be included on ari annual basis. . . . ,. Such questions as obsolescence, depreciation and return on investment are subjects for special study arid investigation. Due consideratiori should be given to the value of resale of equipriierit arid its portability in the event'of removal to new. locations. ; . ATTIC FANS '. - Attic fans are used during the warm months of the year to draw large volumes of outside air through a house and offer a means of using the. comparative coolness of outside evening and night air to lower the inside temperature: - Because the low static pressures involved, are usually less than }/g in.^ of water, disc or propeller fans are generally used instead of the blower types. The fans should have quiet operating characteristics, and they, should be capable of giving,about 20 to 30 air changes per hour in northern areas. In the South the usual specification requires one air change per minute which provides appreciable air movement in addition to lowering the inside air temperaturese. . 1 , .. Types . .. Open attic fans are units in which the fan is installed in a gable or ' dormer of the attic and one or more grilles are provided in the floor of the ' / 640 CHAPTER 36 ' 1946 'Guide attic, permitting air to flow from the hall below. . Outdoor air, which enters the house through open windows, is drawn into the attic through the grilles, and is discharged outside by the fan. An attic stairway may be used in place of the grilles. It is essential that the roof and the attic walls be free from air leaks. . Boxed-in fans are units in which the fan is installed within the attic in' a box or housing directly over a central ceiling grille, or in a bulkhead enclosing an attic stair. The fan may be connected by a duct system to the grilles in individual rooms. Outdoor air entering through the windows of the rooms below is discharged into the attic space and escapes to the outside through louvers, dormer windows, or screened openings under the eaves. Another version of the attic fan is the window fan for use when attic application is not feasible or no attic is available. Supplied with a perforated or expanded metal enclosure and mounted in either the upper or lower window section, this fan is easy to install or move to another location. . . The locations of the fan, the outlet openings, and grilles should'be selected after consideration of the room and attic arrangements in order to give uniform air distribution in the individual rooms served. If the outlet for the air is not on the side away from the' direction of the pre vailing wind as in the case of the boxed-in fan, openings should be provided on all sides. Kitchens should be separately ventilated because of the fire hazard, and to prevent the spread of cooking odors. The window fan may be located in a hall or an unused bedroom. Noise of operation is more of a problem with the window fan than with the attic type, although care should be taken to locate either type of fan so that occupants are not disturbed. .' , These fans range in capacity from 3000 to 30,000 cfm.' The window type usually does not exceed 8000 cfm, while the most generally used attic type ranges from 8000 to 16,000 cfm. Power consumption is under 50 watts an hour per 1000 cfm of rated output for the 8000 cfm fan and larger while the watts input for smaller. fans is greater than this figure. Improved results can be secured with the window fan by closing off parts of the house where ventilation is not desired. . REFERENCES . Prepared by-a Joint Committee of the American Society of Refrigerating Engineers, American Society of Heating and Ventilating Engineers, Refrigerating Machinery Association, National Electrical Manufacturers' Association, and Air Conditioning Manufacturers' Association (A*S*R.E. Circular No. 13-42). 2"Standard Method of Rating and Testing Self-Contained Air Conditioning Units for Comfort Cooling prepared by a Joint Committee of the-American Society of Refrigerating Engineers, American Society of Heating and Ventilating Engineers, Refrigerating Machinery Association, Notional Electrical Manu facturers' Association, and Air Conditioning Manufacturers' Association (A.S.R.E. Circular No. 16). . 3--Defined in Proposed A.S.R.E. Standard Methods of Rating and Testing Forced-Circulation Air Coolers for Commercial and Industrial Refrigeration (A.S.R.E. Circular No. 25-43).' , '' *--Code of Minimum Requirements for Comfort Air Conditioning (A.S.H.V.E. Transactions, VoI. 44, 1938, p. 27). Reprints of this code-are available at $0.10 a copy. -' . ' Concerning Conservation of Underground Water with Suggestions for, Control,-by Noel E. Porter (A.S.H.V.E. Transactions, Vol. 47, 1941, p. 309). __ s--Comfort Cooling with Attic Ventilating Fans, by G. B. Helmrich and G. H. Tuttle (A.S.H.V.E. Transactions, VoI. 40, 1934. p. 155). A.S.H.V.E. Research Report No. 979--Study of Summer Cooling in the Research Residence for the Summer of 1933. by A. P. Kratz and S. Konzo (A.S.H.V.E. Trans-' actions, Vol. 40. 1934. p. 167). A.S.H.V.E. Research Report No. 1198--The Effect of Attic Fan Opera tion on the Cooling of a Structure, by W. A. Hinton and A. F. Poor (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 145). The Installation and Use of Attic Fans, by W. H. Badgett (Agricultural and Mechanical College of Texas, Bulletin No. 52, 1940). .. . ., CHAPTER 37 Sprat* Sli'pray Stppanatui Air Washers, Humidification with Air Washer, Apparatus for Direct Humidification, Air Dehumidification with Washers, Well and Water Main Temperatures, Atmospheric Water Cooling Equipment, Selection of Water Cooling Equipment, Design Wet-bulb Temperatures for Water Cooling, Cooling Ponds, Spray Towers, Cooling Tower Design, Cooling Tower ' Performance, Winter Freezing - AIR humidification is effected by the vaporization of water and always requires heat from some source. This heat may be added to the water prior to the time vaporization occurs or it may be secured by a transformation of sensible heat of the air being humidified to latent heat , as the vapor is added to the air. The thermodynamics of the process are discussed in Chapter 3. The removal of moisture from air may or may not involve the removal of heat from the air-vapor mixture. With spray equipment dehumidification of air always necessitates the removal of heat. AIR WASHERS Air washers may be used as either humidifiers or 'dehumidifiers de pending upon the method of operation and the temperature of the spray water. The functions of an air washer are to regulate the moisture and heat content of air passing through it and, although not so effective as . air filters, to remove dust and dirt from the air. The construction of commercial air washers is indicated in Figs. 1 and 2. Any air washer consists essentially of a chamber through which the air passes in intimate contact with water. The lower portion of the washer chamber serves as a sump for the spray water. ' Contact between the air and the washer water is secured: (1) by breaking the water into a very fine mist, (2) by passing the air over: surfaces which are continuously wetted by water, or (3) by a combination of water sprays and wetted plates. Scrubber-plate types of washers are used largely to wash, heavy reclaimable products from the air, and are generally composed of one to three eliminator-type baffle scrubber plates across the air stream. Water is supplied at the tops of the scrubber plates by flooding nozzles placed across the top of the washer. Spray washers , have one or more banks of water atomizing nozzles placed in the air stream above the level of the water in the sump. The direction of the water sprays may be against the air stream, with the air stream, or with one bank spraying with the air stream and one against it: The number of ' nozzles required depends upon their design, the quantity of air handled, and the arrangement of the nozzles. . .. . ` . Scrubbers generally consist of eliminator-type baffle plates placed in the air. stream to cause several reversals of the direction of air flow. The scrubber plates are more effective as air cleaners than as humidifiers. All "washer chambers should have inlet diffuser plates to aid in producing ` more uniform air flow through the washer spray chamber. These inlet vanes-also aid in preventing spray water from being thrown into the air duct ahead of the washer. However, if the water spray opposes the air flow, the ordinary perforated'diffuser plate is not sufficient, and specially designed eliminator baffles must be used to prevent spray from passing into the air inlet duct. At the outlet end of the washer suitable flooded / 641 I ' ' ; ' 642 CHAPTER 37 __________;___________ 1946 Guide eliminator plates, which will cause from 4 to 6 reversals of the direction of air flow, should be installed for the purpose of removing drops of unvaporized water from the leaving air. If the air contains certain substances which may cause the spray water to become acidulated, corrosion resistant materials must be used in the washer construction. Essential items in air washer operation are: uniform distribution of the air across the chamber section above the level of the water in the sump; moderate velocities of ur flow, 300 to 600 fpm in the spray cham ber; an adequate amount of spray water broken up into a fine mist throughout lie air stream; sufficient length of air travel through the water spray and over thoroughly w.etted surfaces; and the elimination of free moisture from the air as it leaves t,he unit. ' ' -Fie. 1. Typical Single-Bank Air Washer Fig! 2. Typical Two-Bank Air Washer Washers are sometimes arranged in two or more stages to cool through long ranges or to increase the over-all efficiency of heat transfer between the air and the heating or cooling medium. A'multi-stage washer is ' equivalent to a number of washers in a series arrangement. Usually the catalog capacity of a washer is expressed in cubic feet of air per minute and is based upon an air velocity of 500 fpm through the gross inlet area of the unit. At this rating spray type washers handle about 2% gpm of water per bank per square foot of area, that is, about 5 gpm per bank per 1000 cfm. These proportions of air, water, area, and velocity may be departed from to meet the needs of some particular job, but certain limiting relationships should be observed. . For' a single-stage air washer, a 15 deg drop in dry-bulb temperature of the air passing through the washer is about the maximum that should be anticipated. For greater decrease in dry-bulb temperature, multi stage washers should be utilized.' A rise of. 6 deg should be the calcu lated maximum for the spray water. ; . . .Spray Apparatus 643 The width and height of a washer may be dictated by space limitations outside the washer, such as headroom, or by the inside space requirements, . such as face area needed by a bank of cooling- coils. The length of a washer is determined by the. number of spray banks, or scrubber plates, and if cooling coils are installed in the unit, by the number of banks of coils. Roughly; a spray space of about 2 ft 6 in. in length is required for each bank of sprays; i.e., 1 ft for entering and 1 ft 6 in. for leaving. The resistance to air flow through an air washer varies with the type of eliminators, number of banks of sprays, direction of spray, air velocity, type of scrubber plates, and size and type of cooling coils if located in the washer. Manufacturers should be consulted to obtain the resistance for a particular installation. , HUMIDIFICATION WITH AIR WASHER Air humidification can be accomplished in three ways with an air washer. These are: (1) use of recirculated spray water, without prior treatment of the air, (2) preheating the air and washing it with recircu lated spray water, and (3) using heated spray water. In any air washing installation the air should not enter the washer with a dry-bulb tempera ture less than 35 F in order to eliminate danger of freezing the spray water. Method 1. Except for the small amount of energy added from outside by the recirculating pump in the form of shaft work, and for the small amount of heat leak from outside into the apparatus, including the pump and its connecting piping, the process would be strictly adiabatic.' Evaporation from the liquid spray would therefore be expected to bring the air immediately in contact with it to saturation adiabatically; and, since the liquid is recirculated, its temperature, would be expected to . adjust to the thermodynamic wet-bulb temperature of the entering air. It does not follow from the foregoing reasoning that the whole air stream is brought to complete saturation, but merely that its state point should move, along a line of constant thermodynamic wet-bulb temperature as explained in Chapter 3. The extent to which the final temperature . approaches the thermodynamic wet-bulb temperature of the entering air, or the extent to which complete saturation is approached is conveniently expressed by a ratio known as humidifying effectiveness or. saturating effectiveness and is defined: -- where . eh = humidifying effectiveness, per cent. . , ,- ti = dry-bulb temperature of the entering air, Fahrenheit degrees. It = dry-bulb temperature of the leaving air, Fahrenheit degrees. t' = thermodynamic wet-bulb temperature of the entering air, Fahrenheit degrees. ' The following may be taken as representative humidifying or saturating effectiveness of an air washer for the conditions stated: 1 bank--downstream------------------------------------------------------ ---.. 60-70 per cent 1 bank--upstream------------------------ ,--------------------------------------- 65-75 per cent. 2 banks--<fownstream___ _______________________:___________ 85-90 per cent 2 banks--1 upstream and 1 downstream__________________ 90-95 per cent 2 banks--upstream________;:_______________ ____________ 90-95 per cent The humidifying or saturating-effectiveness of a washer is dependent upon the number of spray banks and nozzjes, the effectiveness of the nozzles in breaking an adequate quantity of water into a fine spray, the . - 644 CHAPTER 37 1946 Guide velocity of air flow through the water sprays, and the time of the contact of the air with-the spray water! Other conditions being the same, low velocity of air flow is more conducive to higher humidifying effectiveness. The air leaving the washer may require reheating to produce the required dry-bulb temperature and relative humidity. Method 2. The preheating of the air increases both the dry- and wet- bulb temperatures, lowers the relative humidity, but does not alter the humidity ratio (pound water vapor per pound dry air). At a higher wet- bulb temperature but the same humidity ratio, more water can be absorb ed per pound of dry air in passing through the washer; assuming that the humidifying effectiveness of the washer is not adversely affected by opera tion at the higher wet-bulb temperature. The analysis of the process occurring in the washer itself is the same as that explained under Method 1. The final desired conditions are secured by adjusting the-amount of pre heating. to give the required wet-bulb temperature at entrance: to the washer and then reheating the outlet air when necessary. . Method 3. Evert if heat is added to the spray water, the mixing occur ring in the washer itself may still be regarded as adiabatic. The state point of the mixture should move in a direction determined by the specific enthalpy of the heated spray as explained in Chapter 3. By elevating the water temperature it.should be possible to saturate the air and even raise its temperature above the dry-bulb temperature of the entering air. APPARATUS FOR DIRECT HUMIDIFICATION Humidifiers may be divided, into the following general types, according to the method of operation: (I) indirect, such as the air washer, which introduces moistened air; and (2) direct, which sprays moisture into the room or introduces moisture by means of steam jets. As in the cases'of humidification by use of an air washer, the heat necessary for the vaporization of the moisture added to the air by direct humidification is secured either from heat stored in the spray water or by a transformation of sensible to latent heat in the air humidified. In' the latter case the enthalpy of the air remains constant but the dry-bulb temperature of the air is reduced. . : . Direct humidification is usually preferable where high relative humidi ties must be maintained, but where there is little cooling or ventilation required. In comfort air conditioning, where both humidification and ventilation are required, the indirect humidifier is preferable. In indus trial applications, where the cooling or ventilation load is large and where very high relative humidities must be maintained, a combined system employing both direct and indirect humidifiers is sometimes used. Spray Generation .. Spray generation is obtained by (!) . atomization, (2) impact, (3) hydraulic separation,- and (4) mechanical separation. Atomization involves the use of a compressed air jet to reduce the water particles to a fine spray. With the impact. method, a jet of water under pressure impinges directly on the end of a small round wire. Where hydraulic separation is employed, a jet of water enters a cylindrical chamber and escapes through an axial port with a. rapid rotation which causes it immediately to separate in a fine cone-shaped spray. In the mechanical separation process, .water is thrown by centrifugal force from the surface of a rapidly revolving disc and separates into particles suf ficiently small to be utilized in certain, types of mechanical humidifiers. Spray Apparatus 645 Spray Distribution ' '. Spray distribution is obtained by (1) air jet, (2) induction, and (3) fan propulsion. . The air jet which generates the spray in atomizers also carries the spray through a space sufficient for its distribution and evaporation, and this method of distribution is termed air jet. Where distribution is obtained by induction, the aspirating effect of an impact or centrifugal spray jet is utilized to induce a current of air to flow through a duct or casing, and this air current distributes the spray. Fan propulsion obviously consists of the utilization of fans to entrain and distribute the spray. Industrial type direct humidifiers are commonly classified as (1) atomizing, (2) high-duty, (3) spray and (4) self-contained or centrifugal. Atomizing Humidifiers There are several types of atomizing humidifiers, all of which rely upon compressed air as the atomizing and distributing agency, similar to the familiar method used in ordinary nasal atomizers. Compressed air, (ordinarily about 30 lb per square inch) is supplied from a centrallylocated air compressor through pipe lines to the atomizing units. The air lines are usually horizontal and parallel to water lines which supply water by gravity from a float tank. The water in the tank is maintained at a constant level slightly lower than the outlets of the atomizers them selves and is drawn constantly to the atomizer by aspiration when com pressed air is supplied. This aspiration ceases and the flow of water stops when the air supply is cut off. The water should not be supplied under pressure to atomizers because of the possibility of leakage, drip, or coarse spray. These cannot occur when water is supplied by aspiration. High-Duty Humidifiers ' Water is supplied to high-duty humidifiers under high pressure (usually ' about 150 lb per square inch) through pipe lines from a centrally-located pumping unit.' The spray-generating nozzle which is of the impact type is located in a cylindrical casing. A drainage pan provides for the collec tion and return of unevaporated water which flows through a return pipe to a filter tank, from which it is recirculated. A powerful air current is forced through the humidifier by means of a fan mounted above the unit. The air. enters from above, is drawn through the head, charged with moisture, and cooled. It then escapes from the opening below at a high velocity in a complete and nearly horizontal circle. The spray is evapor ated and the resulting vapor diffused. This distribution of fine spray over the maximum possible area promotes complete and rapid vaporization. Spray' Humidifiers . This type of humidifier consists of an impact spray nozzle in a cylin drical casing with a drainage pan below it. The aspirating effect of the spray nozzle induces a moderate air current through the casing which distributes the entrained spray. The general method of circulating and returning the water is similar to that.employed for high-duty humidifiers. A suitable pump and centrally-located filter tank are required. . : Self-Contained Humidifiers . The self-contained or centrifugal humidifier has the ability to generate and distribute spray without the use of air compressors, pumps, or other. auxiliaries. These may be used either singly or in groups. In large installations,. where suitable connections are provided to permit the 646 CHAPTER 37 1946 Guide Table 1. Average Maximum Water Main Temperatures3 ' emp. !T F 1 T emp. F T emp. F State City State City State City- Ala. Birmingham. 84 50 Pa. 74 73 68 81 70 Tucson________ 80 . Calit. Anaheim... __ 60 Salem____ _____ 68 Worcester......... 76 McKeesportTM 82 Philadelphia__ 83 Berkeley._____ 69 Mich. Detroit.............. 77 Pittsburgh........ 81 Fresno................ 72Fullerton......... 75 Flint__ :______ 70 R. I. Providence- ... 68 Grand Rapids.. 84 S. C. Charleston........ 80 Glendale. ......... 68 Highland Park 77 Greenville- 81 Los Angeles...... 75 Oakland 69 Jackson. ....... 56 Spartanburg___ 78: Kalamazoo.___ 53 S. D. Rapid City.___ 55 Ontario... ......... 70 Lansing. 64 Tenn. Chattanooga.... 84 Pasadena........... 82 82 89 Pomona............. 75 Minn. Duluth--........... 55 Memphis........... 70 . Riverside..____ 78 Minneapolis___ 80 Nashville........... 90 Sacramento...... 72 San Bernardino 65 Mo. St. Paul../.-...... 77 Texas Amarillo......... 65 Jefferson City.. 82 Austin. _ ......... 90 San Diego......... 82 San hrancisco.. 62 Whittier_______ 75 Kansas City___ 84 St. Joseph......... 84 St. Louis. ____ 85 Beaumont.:...... 86 Dallas................. 86 Fort Worth...... 84 Colo. Denver............... 75 Springfield........ 70 Conn. Bridgeport____ 66 Nebr. Lincoln............... 63 Hartford!. ..... 73 Omaha..... ..... .... 87 New Haven.__ 76 Nev. Reno................... 61 Waterbury___ 72 N. H. Manchester...... 76 D. C. Washington___ 84 N. J. Jersey City--__ 63 Utah Del. Wilmington...... 83 Newark. - 74 Fla. Jacksonville-... 80 Paterson-- ....... 78 Va. Galveston..'..... Houston........... : Port Arthur...... San Antonio. ..: Wichita Falls. ! Logan................. Salt Lake City.. Fredericksburg 90 84 83 76 85 44 60 75 80 79 Tampa............ .. 77. N. Y. Albany............... 68 Norfolk. -......... 80 Ga. Atlanta. 87 75 Wash. 58 Macon................ 80 56 62 iii. Chicago.! 76 Mt. Vernon...... 74 Spokane.....'....... 51 Cicero. .............. 76 New Rochelle.. 75 Tacoma.... -- ... 57 Evanston........... 73 New York......... 72 W.Va. Charleston........ 85 - 67 70 Rockford........ 59 60 78 lnd. Springfield...... 82 Evansville........: 86 Gary..... .............. 75 Syracuse__ !-.- 74 Wis. LaCrosse........... 54 . Utica__________ 69 Madison............ 58 70 70 Indianapolis.--. 80 N. C. Asheville______ 74 Racine___ ;........ 68 ; South Bend...... 61 85 Terre Haute__ 82 Winston-Salem -.82 Iowa Cedar Rapids.. 78 N. M. Albuquerque.... 65- Des Moines:!.... 77 76 Sioux City___ _ 62 Kans. Concordia_____ 57- 50 Cincinnati......... 84 Pro- Kansas City___ 86 Cleveland_____ 74- Topeka________ 88 Columbus........ 82 Wichita.............. 72 Dayton________ 60 Ky, La. Louisville ....... 85 Baton Rouge... 85 Lakewood_____ 82 Alta. Calgary...... ....... 64 Springfield____ 72 B. C. Vancouver........ 60 New Orleans.... 85 Me/ Augusta_______ 60 Okla. Md. Baltimore- ..... 75 Mass. Boston_____!..... 80 Ore. s . Cambridge ..... 70 Toledo.......... ..... -83 Ont. Oklahoma City 82 85 P.E I Eugene____ ___ 60. Que. 64 London. ..........; Toronto.:........... Montreal....:..... 50 63 48 78 68 Fall River......... 76 1, - . -. -t .' , `. . "These averages taken from various city water main locations, with some actual values slightly higher and some lower than values shown. - . . Spray Apparatus 647 cleaning and servicing of individual units without affecting the room as a whole, group control of the water and power may be employed. AIR DEHUMIDIFICATION WITH WASHERS ; Moisture removal from an air-vapor mixture can be accomplished by use of an air washer so long as the temperature of the spray medium is- lower than the dew-point of the air passing through the unit. The final; dry-bulb temperature and the relative humidity of the air leaving a- dehumidifier washer are dependent upon: the air velocity, the length of air travel through the sprays, the dry- and wet-bulb temperatures of the; entering air, the spray temperature, the number of spray banks and nozzles, the quantity of spray medium handled, and the effectiveness of the nozzles in breaking the spray into a fine mist. : Both sensible and latent heat are removed in the process of dehumidi fication by cooling. Abstraction of sensible heat occurs during the entire time that the air is in contact with the spray -medium. Latent heat, . removal takes place as condensation occurs. Therefore, the lower the. spray temperature the greater the amount of moisture removal per pound of dry air, all other conditions remaining the same. Washers with two or more banks of sprays are usually selected for comfort air conditioning installations. Such washers will cool the air to within 1 or 2 F of the'- leaving spray water temperature. ; Where a limited supply of cold water is available multiple stage washers may be used to an advantage. The cool water is pumped through -the multiple spray systems in series. By this arrangement the entering air is cooled first by the warmer water and finally by the cooler water' which gives the maximum amount, of cooling with the minimum amount ', of water; The approximate temperatures of water from wells at depths . of 30 to 60 ft are given in Fig 3 *. Frequently the temperature of the city water main supply is low enough during the summer to permit an ap preciable cooling effect. Table 1 lists the maximum city water main temperatures for various localities in the United States and Canada. Air washers using refrigerated spray generally have their own recircu-, lating pumps. These pumps deliver to the sprays a mixture of water from the washer sump, which has not been re-cooled, and refrigerated, water. The quantities of each are controlled by a three-way or mixing valve actuated by a dew-point thermostat located in the washer air outlet , or by humidity controllers located in the conditioned space. ATMOSPHERIC WATER COOLING EQUIPMENT .In the operation of a refrigerating plant or a condensing turbine, one of the main problems is the removal and dissipation of heat from the compressed refrigerant or the discharged steam. This is accomplished' ordinarily by first transferring the heat of the gas to water in a heat exchanger, from which water it may then be dissipated in a number of ways. If the plant is situated on the banks of a river or lake, an intake may be taken up-stream or at a considerable distance from the discharge, to prevent mixing of the heated discharged water with the inlet water. If the source of cooling water is a city supply or a well, the discharge water may be run into the nearest sewer or open waterway. Lackingan unlimited water supply, or in cases where purchased water is too expensive or where the water available contains dissolved salts which would form scale on the heat-exchanging apparatus, it is necessary to recirculate the water, and to cool it after each passage through the heat- 648 I: CHAPTER 37 1946 Guide F ig . 3. A p p r o x im a t e W e l l W a t e r e m p e r a t u r e s a t D e p t h s o f 30 to 60 F tT Spray Apparatus 649 exchanger by exposure to air in an atmospheric water cooling apparatus. Air has a capacity for absorbing heat from water when the wet-bulb temperature of the air is lower than the temperature of the water with which it is in contact. . The rapidity with which this transfer of heat occurs depends upon (1) the area of water in contact with the air, (2) the relative velocity of the air and water, and (3) the difference between the wet-bulb temperature of the air and the temperature of the water. The rate of heat dissipation is influenced further by many small factors2 prevailing upon these primary ones, and complicating the design. Selection of equipment for any specified service must ultimately rest in over-all economic considerations established from reliable performance data. As the heat content of the air increases, its wet-bulb temperature rises. (See Chapter 3.) Because it is impracticable to leave the air in contact with water for a long enough time to permit the wet-bulb temperature of the air and the temperature of the water to reach equilibrium, atmos pheric water cooling equipment aims to circulate only enough air to cool the water to the desired temperature with the least expenditure of power. In an air washer, humidifier or dehumidifier, the air is first conditioned by water to change its moisture and temperature, and it is then sent to the place where it is to be used. In water cooling equipment the tem perature of the water is reduced by air, and the cooled water is carried to its point of usage. In the air washer, an excess of water is used to con dition a fixed quantity of air, while.in water cooling equipment, an excess of air is used to cool a fixed quantity of water. Both types of equipment have a common, basis of design in that the size of the equipment is determined by the quantity of air to be handled. With the air washer, the size of the equipment is fixed by the quantity of air to be conditioned, and the amount of conditioning is controlled by the quantity and temperature of the water supplied and its method of application. With water cooling apparatus, its size and the quantity ofair required bear no direct relation to the quantity of water being cooled, but vary through a wide range for different services and conditions. Selection of Water Cooling Equipment . The proper size and type of water cooling equipment for a given instal lation cannot be determined accurately without considering the character istics of all types, together with all requirement factors and other matters .which influence the selection. Very few installations are exactly alike in details of requirements, and conditions governing performance and opera tion of the several types of water cooling equipment vary widely with geographical location as well as other considerations. It necessarily holds, therefore, that requirement factors and equipment characteristics are closely interlocked and deserve careful study as a related whole. , Before the characteristics of a specific water cooling apparatus can be judged desirable or undesirable the survey must conclude definitely the importance of each of the following items: first cost including all necessary, auxiliaries, area, height, weight, effect of wind velocity and direction, drift nuisance, make-up water requirements and cost of chemical treat ment if needed, total power for pumping (plus fan operation in the case of mechanical draft), maintenance, available locations (with due thought, to possible future expansion, wind restrictions, space cost, proximity and accessibility, etc.), appearance, the equipment's operating flexibility for . most economical conformance to varying loads or seasonal changes, and other considerations occurring with regard to a specific application. 650 CHAPTER 37 1946 'Guide Sizes of Equipment . . . ' , Assuming a definite quantity of water, the size and design of atmospheric cooling equipment are affected by the following primary conditions: 1. -Temperature range through which the water must be cooled. 2. Number of degrees above the wet-bulb temperature of the entering air to which the water temperature must be reduced. 3. Temperature of the atmospheric wet-bulb at which the required cooling must be performed. ' 4. Time of contact of the air with the water. (This involves height or length of the apparatus and velocity of air.) 5. Surface of water exposed to each unit quantity of air. 6. Relative velocity of air and water. . - Items 1, 2, and 3 are established by the type of service and geographical ' location, while items 4, 5, and 6 depend upon the design of the equipment. The establishment of a proper cooling range depends upon: (1) type of service (refrigerating, internal combustion engine and steam condens ing). (2) wet-bulb temperature at which the equipment must operatesatisfactorily, (3) type of condenser or heat-exchanger used. ' Because the design of an entire plant is usually affected by the quantity . and temperature of the cooling water supply, plants should be designed for cooling water conditions which can be most efficiently attained. The first consideration is usually the limiting temperature of the plant. For example, if an ammonia compressor refrigerating plant is to be designed for 185 psi head pressure as a normal maximum, the limiting temperature of the ammonia in the condenser is 96 F. Should the ammonia tempera ture go above this figure the head pressure will exceed 185 psi and power' consumption increases. To obtain this head pressure, the temperature of the circulating water leaving the condenser must always be less than 96 F by an amount depending upon the size and design, of the condenser, the quantity of water being circulated, and the refrigerating tonnage being produced. A condenser having a large surface per ton- of refrigeration may be designed to operate satisfactorily with the-leaving hot water, temperature within 3 or 4 deg of the ammonia temperature corresponding to the head pressure, while a small condenser might require a 10 deg . difference. ' .. Table 2 lists several gases with data as to the temperatures and pres- ,. sures for which commercial condensers are designed. Internal combustion engines have limiting hot water temperatures of 125 F to 140 F for closed . Table 2. Condenser Design Data ' Gab Maximum Pressure Desired in `Condenser ` Leating Hot Water Temperature Gas Temperattob - F Deo in Condenser F Deg Best Condenser Design Average Condenser ` Design - Steam.................. 28 in. vacuum____ Steam____ ,,_____ 27 in. vacuum_____ Steam. ......... 26 in. vacuum____ Ammonia.... ...... 185 psia..................... Carbon dioxide. 1030 psia............... ' .Methyl.chloride 102 psia..................... Dichlorodi- fluoromethane 117 psia................ ` 101.2 .115.1 125.9 96.0. 86.0 100.0 100.0 97 110 120 92 83 96 96 93 105 114 88 81 92 93. 1 Head pressure. Spray Apparatus 651 systems, and 110 F to 120 F for open systems,depending upon the quality of the cooling water. The cooling of such fluids as milk or wort has variable requirements and is usually done in counter-flow heat-exchangers in which' the leaving circulating water is at a much higher temperature than is the leaving fluid. V The temperature range, once the hot water temperature is approxi mately known, depends upon: (1) the maximum wet-bulb temperature, at which the full quantity of heat must be dissipated, and (2) the effici ency of the atmospheric cooling equipment considered. Design Wet-Bulb Temperatures The maximum wet-bulb temperature at which the full quantity of water must be cooled through the entire range is never, in commercial design, the maximum wet-bulb temperature ever known to exist at the location nor the average wet-bulb temperature over any period. The former basis jyould require atmospheric cooling equipment several times greater than normal size, and the latter would result during a large part of the time, in higher condenser water temperatures than those for which the plant was designed. For instance, the maximum wet-bulb temperature recorded in-New York City is 88 F, and the July noon average for 64 years is close to 68 F. Yet in the years 1925 to 1934, inclusive, there were but 8 hours per year when the wet-bulb temperature reached 80 F or-more, and there were 975 hours in the average summer (June to September inclusive) when the wet-bulb temperature was ,68 F or above. As these 975 hours represent a third of the summer period, cooling equipment based upon the noon average July wet-bulb of 68 F would be inadequate. Commercial practice is to choose a wet-bulb temperature for air con ditioning design purposes which is not exceeded during more than 5 to. .8 per cent of the summer hours (75 F for New York City) with somewhat lower requirements for steam turbines and. internal combustion engines. This difference is made because the heaviest load on an air conditioning plant is coincident with high wet-bulb temperatures, whereas the heaviest electric power demand occurs either in the winter or after nightfall in summer, when the wet-bulb temperature is low. Table 2, Chapter 15, shows design wet-bulb temperatures which will not be exceeded more than 8 per cent of the time in an average summer. , Knowing the hot'water temperature and the wet-bulb temperature for which the equipment must be designed, the cold water temperature must be chosen to place the requirement within the effectiveness range of the type of atmospheric water cooling apparatus to be used. This effective,ness is expressed as the percentage ratio of the actual cooling effect to the maximum possible cqoling effect. Since the wet-bulb temperature of the entering air is the equilibrium'temperature to which the water could be cooled, the effectiveness of water cooling apparatus can be indicated thus: (hot water temperature -- cold water temperature) X 100 hot water temperature -- wet-bulb temperature of entering air ' Magnitudes of this effectiveness ratio will vary through wide limits in accordance with construction and conditions of operation. Values indi cative of the commercial range of the effectiveness ratio are given in Table 3, although unusual designs may operate outside these ranges. From consideration of the factors which include the cooling range and design wet-bulb temperature, the quantity of water required can be 652 CHAPTER 37 1946 Guide calculated from the amount of heat to be dissipated. The normal amounts of heat to be removed from various processes of the cooling equipment are: Compressor Refrigeration: 220 to 270 Btu per (minute) (ton). Usual practice is to assume: 250 Btu per (minute) (ton) which is equivalent to 30 gal per (Fahrenheit degree) (minute) (ton). ' Steam Turbine Condensers: 950 to 980 Btu per pound of steam. Usual practice is to assume 970 Btu per pound of steam. ' Steam Jet Refrigerating Condensers: 1030 to 1150 Btu per pound of steam. Exact value depends upon initial steam conditions. `. . Diesel Engine Jackets: 2500 to 4000 Btu per bhp per hour. Usual practice is to ' assume 3500 Btu per bhp per hour. Natural Gas or Gasoline Engines: 4500 to 6000 Btu per bhp per hour. Usual practice is to assume 5000 Btu per bhp per hour. ` Cooling Ponds A natural pond is often used as a source of condensing water. The hot water should be discharged close to the surface at the shore line. ' Natural air movement over the surface of the water will cause evaporation and carry away heat. Because increased density due to the loss of heat causes the cooled water to sink to the bottom of the pond, the suction connection for intake water should be placed as far below the surface as possible, and at as great a distance from the discharge as practicable. Spray. Cooling Ponds The spray pond consists of a basin, above which nozzles are located to spray water up into the air. Properly designed spray nozzles break up the water into small drops, but not into a mist because the individual drops must be heavy enough to fall back into the basin'and not drift away with the air movement. The water surface exposed to the air for cooling is the combined area of all the small drops. Since the rate of heat removal by atmospheric water cooling is a function of the area of water exposed to the air, the difference in temperature between the water and the wet- bulb temperature of the air, the relative velocity of air and water, and' the duration of contact of the air with the wafer, a much larger quantity of heat may be dissipated in a given area with the spray pond than with the cooling pond, because of (1) the speed with which the drops travel as they are propelled into the air and fall back into the water basin, (2) the increased wind velocity at a point above the surrounding structures or terrain, (3) the increased volume of air used, and (4) the vastly increased area of contact between air and water3. ' . Spray pond effectiveness is increased by (1) elevating the nozzles to a higher point above the surface of the water in the basin, (2) increasing the spacing between nozzles of any one capacity, (3) using smaller capacity nozzles to decrease the concentration of water per unit area, and (4) using smaller nozzles and increasing the pressure to maintain the same concentration of water per unit area. Usual practice is to locate the Table 3. Effectiveness of Atmospheric Water Cooling Equipment ,, Equipment Cooling EppectiVbnbs8--Peh Cent * Minimum Usual Maximum Spray Ponds............................ :................. Spray Towers__ ______________________ Natural Draft Deck Towers................. Mechanical Draft Towers_____ 30 40 50 50- 40 to 50 45 to 55 . 60 to 75 60 to 75 , '60 -60 90 90 Spray Apparatus 653 nozzles from 5 to 7 ft above the edge of the basin, to supply from 5 to 12 psi pressure at the nozzles, using nozzles spraying from 20 gpm to 60 gpm each and spacing them so the average water delivered to the' surface of the pond is from 0.5 to 0.7 gpm per square foot. Best results are obtained by placing the nozzles in a long relatively narrow area located broadside to the wind. : Spray ponds may be located on the ground, or they may be placed on roofs. To prevent excessive drift loss, or the carrying of entrained water beyond the edge of the pond by the air on the leeward side, louver fences are required for roof locations and for those ground locations where space is so restricted that the outer nozzles cannot be located at least 20 ft to 25 ft from the edge of the basin. Such fences usually are con structed of horizontal louvers overlapping so the air is forced to turn a corner in passing through the fence, and the heavier drops of water are thrown back, owing to their inertia. The louvers also restrict the flow of air, particularly at the higher wind velocities, and thus further reduce the possibility of water being carried off. The height of an effective fence should be equal to the height of the spray cloud. Louver boards are preferably of red gulf cypress or California redwood supported on castiron, steel or wood posts. Where building ordinances forbid the use of combustible materials, sheet metal is customarily used. Algae growths, during warm weather, in cooling towers and spray ponds may be eliminated while the plant is in operation by the use of potassium permanganate. This chemical can be dissolved at the rate of 1 lb in 1J4 to gal of hot water. About 10 parts of permanganate should be used per million parts of cooling water. Enough of the permanganate solution should be added periodically to cause the water to have a. pink color for a period of from 15 to 20 min. The best results are obtained when sufficient quantities are added periodically at intervals of several weeks, the time intervals being dependent upon local operating conditions. The chemical is non-poisonous and non-corrosive when used as directed. Natural Draft Spray Type Towers Where not more than 30,000 Btu per minute are to be dissipated, the natural draft spray type tower is a satisfactory apparatus. The word tower in this connection is somewhat of a misnomer as the apparatus is essentially a narrow spray pond with a high louver fence. As usually built, the nozzles spray down from the top of the structure and the distance from the center of the nozzle system to the fence on either side is not more than half the distance that the nozzles are elevated above the water basin. Heights range from 6 ft to 15 ft and the total width of a structure is not usually greater than its height. Spray towers occupy less space on small jobs than spray ponds of equivalent capacities because the towers have a capacity of from 0.6 gpm to 1.5 gpm per square foot of tower area. The wet louvers add to the surface exposed to the air. Natural Draft Deck Type Towers . In past years much of the atmospheric water cooling on refrigeration work has been done with natural draft deck type towers, which are also referred to as wind or atmospheric towers. These towers consist of heavy wooden or steel framework from 20 to 40 ft high and from 10 to 20 ft wide, having open horizontal lattice-work platforms or decks at regular intervals from top to bottom, and a catch basin at the foot. The hot water is distributed over the upper part of the structure by means of troughs, splash heads, or nozzles, and it drips from deck to deck down to 654 CHAPTER 37 1946 Guide . the basin. The object of the decks is to arrest the fall of the water so as to present efficient cooling surfaces to the air, which passes through the . tower parallel to the decks. The decks add to the area of water surface exposed to the air both by causing it to splash into fine droplets and to spread over the deck surfaces, but since some, deck designs furnish a resistance to air flow, too many decks may be a detriment. To prevent the loss of water on the leeward side of the tower, wide splash boards are attached at' regular intervals from top to bottom. In some towers these boards or louvers extend outward and upward, usually with lower edge (which is attached to the frame of the tower) somewhat below the level of the outer and upper edge of the next louver board below it. Some louvering - designs add secondary louvering to these primary louvers. In such designs the primary louvers are generally broader and do not slope so sharply nor overlap one another. Since their function is merely to return to the interior of the tower the water caught by the secondary louvering which extends upward from each primary louver's outer edge to the next primary louver above. The individual slats which comprise the secondary louvering may be arranged either vertically in an overlapping staggered manner with air passage between, or set horizontally with their flat surfaces sloping inward and spaced so their edges over-reach but permit free air passage. Secondary louvering reduces drift loss on this type of tower materially. - Efficiency of a deck tower is improved, within'limits, by increased height, increased length, or increased width. The first two increase the area of water exposed to the wind, and the latter increases the time of contact of the air with the water. Performance is best when the wind blows crosswise to the tower arid decreases with obliqueness of the angle ' until the effect of a lengthwise wind is virtually nil. Wind Velocities on Natural Draft Equipment Since natural air movement is the prime requirement for a deck type tower, spray cooling tower, or spray pond, the apparatus must be de. signed to produce the desired cooling at times when the wind velocity is below average, when the wet-bulb temperature is at the maximum chosen for design, and when the plant is operating at full load. The apparatus ' must also, for best results, be located with its longest axis at right angles . to. the direction of the prevailing hot weather breeze. Table 2, Chapter 15, - gives the average summer-wind velocities and directions in representative cities. Natural draft cooling equipment should be designed to operate . properly with not more than one-half ol the average -wind velocity, and in no case for a wind velocity of more than 5 mph. Natural draft equip ment must not be obstructed by trees, buildings, or other wind deflectors. Mechanical Draft Towers . , ' .. Mechanical draft towers usually consist of box-like shells, constructed of wood, metal, or masonry, in which water is distributed uniformly at the top and falls to a collecting basin at the bottom. The inside of the tower . may be filled with wood lattice work over which the water drips, or the water surface may be presented to the air by filling the entire.inside of the structure with spray from nozzles. Air is drawn through the tower by induced draft fans or propelled through it by forced draft fans. Since the air flows at a constantly sustained and comparatively high velocity (by contrast-with natural draft equipment which varies in performance with'every change of. the wind's direction or velocity) the air and water are brought info contact Spray Apparatus 655 under controlled conditions' resulting in more efficient transfer of heat from a given quantity of water into a,given volume of air. The least, possible operating cost is achieved by that tower design which delivers the desired performance for the lowest total power input, both to fans. for air movement and to pumps for raising and distributing the water.,- The effectiveness of a mechanical draft tower is improved by increasing height, area, or air quantity. Increasing the height increases the length of time the air is in contact with the water without affecting seriously the fan power required, but it increases the' pumping power needed. In creasing the area while maintaining constant fan power increases the air quantity somewhat and because of lowered velocities it increases' the time this air is in contact with the water. The surface area, of water in contact with the air is increased in both cases. Increasing the air quantity decreases the time the air is in contact with the water, but, since a greater quantity is passing through, the average differential between the water temperature and the wet-bulb temperature of the air is increased, and this speeds up the heat transfer rate. Increased air quantities are obtained only at the expense of-increased fan power, which increases approximately as the cube of the air quantity. Air velocities through mechanical draft towers vary from 250 to 450 fpm over the gross area of the structure. Mechanical draft water cooling equipment may be set up inside build ings, where it usually draws its air supply from the general space in which it is installed, and discharges its exhaust air through a duct to the outside. Indoor cooling towers may be either of the wood-filled or the spray-filled type. In many cases where little height but considerable area is available, water is cooled in a spray-filled structure similar to an air washer, with the air passing horizontally through the apparatus and being discharged through a duct to the outside. Cooling Tower Design The method of design of equipment for energy transfer from water to. an air-water vapor mixture is similar to that used for absorption equip ment. Details of this procedure are available * K 6 and its application to the problem of the cooling tower operating at atmospheric pressure is illustrated by the following development. The nomenclature used is as follows: - . a ~ over-all average wetted area (surface of water drops plus . wetted tower surface) square feet per cubic foot of tower volume. ' c = specific heat of liquid water, Btu per (pound) (Fahren- . heit degree). . ' e => effectiveness. ' e = natural base. . C = weight rate of flow of air, pounds of dry air per hour. h = enthalpy, Btu per pound of dry air. A* = enthalpy of air-vapor mixture, Btu per pound of dry air. HB *= enthalpy of saturated air-vapor mixture at water tem perature, Btu per pound of dry air. K " over-all energy unit conductance, Btu per (hour) (square foot over-all average 'wetted area) (Btu enthalpy differ ence per pound of dry air). 4 Ka = over-all rate coefficient, Btu per (hour) (cubic foot of tower volume) (Btu.enthalpy difference per pound of dry air). '. * L =* water rate, pounds per hoUr. Im -- logarithmic mean. - S = average cross-sectional area of cooling tower for air flow, square feet. ' t = water-main body temperature. Fahrenheit degrees. - fwb 18 wet-bulb temperature. Fahrenheit degrees. . V -- tower volume, cubic feet. Note: Subscripts 1 and 2 when used in equations refer to water entrance and exit sections respectively, for the counter-flow tower. Conditions 1 s Waterflow l Lb per hr Energy exchange Lcdt=Gdh dV Air flow G ub per hr . Conditions 2 _ Fig. 4. Section of Typical Counter-Flow Tower v 1: I ti 656 CHAPTER 37 1946 Guide A section of a typical counter-flow tower is shown in Fig. 4. If the reduction in water rate due to evaporation within the volume is neglected, the energy balance for this differential section of the exchanger volume may be written as: - - L c dt = G dh (2) The potential for net energy transfer due to heat and mass transfer from the water to the mixture in contact with it may be expressed with reasonable accuracy as the difference between the enthalpy- of saturated air at the water temperature, h", and the enthalpy of the main stream air vapor mixture7, ha. The rate of energy transfer is given by the expression: . Ka (A" - h*)dV (3) which equation defines the over-all rate coefficient, Ka; the latter being Fig. 5. Temperature Enthalpy Diagram for Air Water Vapor Mixture Showing the Operating Line for Example 1 the product of the oyer-all energy unit conductance, K, and the ratio of the transfer surface to the exchanger volume, a. . - Equations 2 and 3 are conveniently illustrated by means of the tem perature-enthalpy diagram of Fig. 5. Equation 2 indicates that the . succession of air and water states existing in the exchanger sections must combine to form a straight line (for L = constant) on the temperature enthalpy diagram. The slope of this, operating line is: , * = ie ' dt G . . Since the heat capacity of water is approximately unity, this slope is the ratio of the water to the air rate. Equation 3 indicates that the potential for energy transfer at-any section is the difference between the enthalpy of saturated air at the main-body water temperature at that .section and the enthalpy of the air stream in contact with that.water. This potential is the difference in the ordinates of the saturation and operating lines for the water temperature at-the plane in the tower which is under con . sideration. ' . Spray Apparatus Combination of Equations 2 and 3 results in the expression: Gdh = Ka (A- fta) dV Integrating this equation over the length of the exchanger: 657 (4) JL dh Rah" - fta V (5) The integration of the left side of Equation 5 determines the tower volume required to achieve the desired energy exchange. This summation is readily accomplished for counter and parallel flow arrangements. G and Ka are usually independent of the tower volume and Equation 5 then becornes: ' NTU =, ' < Where NTU 'is defined as the Number of Transfer Units and is a measure of the. difficulty of the cooling process. The integration is made numerically or graphically. In the graphical integration ^ ^ is evaluated as a function of Aa. This determination involves the use-of the-energy balance equation integrated from one section to the section in question. The area under the curve between any two abscissae is the number of transfer units required to change the air state from hi to hi. An approximate value for the number of transfer units can also be determined by a simple graphical method of direct construction on the temperature enthalpy diagram8. This method cannot be applied very satisfactorily to cooling towers as the operating range is small and the value of the NTU is near unity. When the relationship between the enthalpy of the saturated air and the temperature is linear over the range of water temperatures involved, it can be shown9 that the logarithmic mean of the terminal potentials, himi is the correct- driving force. This is true to a good approximation when the water cooling does not exceed 15 deg. The approximation to linearity may be determined by inspection of Table 1, Chapter 3, or the temperature enthalpy diagram of Fig. 5. If the logarithmic mean is a valid potential. Equation 6 may be written: hi - ft, = KaV AAlm G (7) and the need for the numerical integration for the determination of the tower volume is eliminated. ,. The over-all rate coefficient, Ka, must be known if the tower volume is to be determined. Experiments conducted on towers containing different packing'construction have yielded some magnitudes of this coefficient, evaluated on an over-all basis. These data are presented in Fig. 6 as a function of the gas mass velocity through the packing, and apply only to the particular packing structure for which they were obtained. The over-all rate coefficient (Ka) may also be a function of the water rate, since a reduction of the water rate may reduce the wetted area within the 658 CHAPTER 37 1946 Guide' . exchanger6. The results included in Fig. 6 probably represent magnitudes of Ka which were obtained for complete wetting. Within the cooling tower operating range the over-all rate coefficient for energy transfer is nearly the same numerically as the over-all rate coefficient for mass trans fer. The conditions of test corresponding to the data presented in Fig. 6 are not well enough known in most cases to warrant recomputation of Ka. Therefore the magnitudes of the over-all rate coefficient for mass transfer presented in Fig. 6 may be used directly in Equations 5 and 6, Fig. 6. Unit Conductances for Various Types of Packing Construction the units of Ka in these equations being Btu per (hour) (cubic foot per pound of dry air). ' -v Application of Design Procedure ' ' A typical procedure which may be followed in designing a cooling'tower, is illustrated in the following Example 1. Example 1. The rate of air flow, arbitrarily assumed in the data given, is related to - . the tower volume by economic considerations. A balance between air rate and-tower volume rests on consideration of the costs of producing air flow and of the tower con- struction10. A counter-flowjforced draft cooling tower is to cool 36,000 lb of water per hour from an initial temperature of 110 F to a final temperature of 80 F. Air having an initial condition of 65 F dry-bulb and 58 F wet-bulb temperature will be forced through the tower counter to the direction of water flow at the rate of 30,000 lb of dry air per hour. ' The cross-section of the tower is to be 8 ft x 8 ft and the packing is to be of the type producing a rate coefficient as indicated in curve No. 2 of Fig. 6. For this type of packing the average cross-sectional area for air flow will be 36 sq ft. _ *Spray Apparatus Solution: Initial air enthalpy = 25.1 Btu per pound of dry air. ' Final air enthalpy: - (A, - A,) = (/, _ ,,) .. (A1-25.1)=?6g^i(110 -go) 659 ki -- 61.1 Btu per .pound dry air. A numeriral integration (Table 4) is employed to determine the Number of Transfer Units (NTU) required. Temperature increments of 2 F are used between successive determinations of the quantity p _ The energy balance indicates that the enthalpy Table 4. Numerical Integration for the Number of Transfer Units - Water Temperature Interval F Deg ' 80-82 82-84 84-86 86-88 88-90 90-92 92-94 94-96 96-98 98-100 100-102 102-104 104-106 106-108 108-110 `Mean Water Temperature F Deg 81 83 85 "87 89 91 93 95 97 99 101 103 105 107 109 Mean Air Enthalpy. Aa Btu per Lb Dry Air Saturated Air Enthalpy, a" Btu per Lb, Dry Air Enthalpy ' Potential A" - Aa 26.3 28.7 31.1 33.5 35.9 . . 44.6 46.9 49.2 51.7 54.4 . . 18.3 18.2 18.1 18.2 18.5 38.3 40.7 43.1 45.5 47.9 57.1 . 60.0 . 63.0 66.2 69.6 18.8 19.3 19.9 20.7 21.7 ' 50.3 52.7 55.1 57.5 59.9 73.2 77.0 80.9 85.1 89.5 22.9 24.3 25.8 ' 27.6 29.6 . Ah A" - Aa 0.131 0.132 . 0.133 0.132 0.130 0.128 0.124 0.121 0.116 0.111 0.105 0.099 0.093 0.087 0.081 . 1.723 ' .. Lc ., 36,000 _ , AA----- g- At -- jQQQQ X 2 = 2.4 Btu per pound of dry air. = 172reSUlt f the intf!Sration is that the Number of Transfer Units required (NTU) . Unit gas mass velocity, -jcross-sectional air flow area). 30,000 36 = .830 lb per (hour) (square foot average From Curve 2, Fig. 6, Ka = 138 Btu. The tower volume required is: . ' V = ~g~a (NTU) = X 1.72 = 217 X 1.72 = 374 cu ft. Height of the packed section is: 374 8 X8 5.9 ft. - The graphical solution for the.Number of Transfer'Units required-for the.desired performance is plotted in Fig. 7. ^ ^ is plotted as a function of A, and the area. 660 CHAPTER 37 1946 Guide Fig. 7. Graphical Integration to Determine Number of Transfer Units Required for Desired Operating Conditions of Example 1 under the curve from the initial enthalpy of the air, 25.1 Btufper pound, to the final enthalpy of the air, 61.1 Btu per pound is 1.72, the Number of Transfer Units required. The effect of the rapid decrease in potential due to the cooling of the water is indicated by comparison of area At, At, and At of Fig. 7. Each represents the Number of Transfer Units required to achieve a water temperature reduction of about 10 F. . - A\ -- 0.471 NTU (110 to 100 F) . At -- 0.595 NTU (100 to 90 F) * At = 0.657 NTU ( 90 to 80 F) . . The use of the logarithmic mean driving potential is illustrated by applying Equation 7 to Example 1: ' == . G AAim A/tlm 30.7 - 18.4 = 24 , 30.7 18.4 NTU 61.1 - 25.1 = 1.5 24 The Number of Transfer Units required as determined by use of the logarithmic mean - ' driving potential equals 1.5 which compares favorably with the correct magnitude, 1.72. A variation of the design method according to Equation 6 is further possible11 through the introduction of Equation 2 to yield KaV L (8) The advantage of this form is in the fact that the left side of the equation may be dealt with as a thermodynamic function only, while the right side depends upon the tower construction and operation. A series of performance curves may be determined from a graphic evaluation of the. integral, which will serve either as a convenient means of analyzing experimental data to determine the conductance Ka, or as a rapid method Spray Apparatus 661 of performance prediction, once the tower characteristic,--j--, is known. These performance curves may be expressed in terms of the following variables; approach to wet-bulb, cooling range, L/G, and wet-bulb temperature of the entering air; and as such they will serve to accurately cover the tower performance in consistent terms. , - The application of the foregoing design method to atmospheric towers is difficult because rate coefficients and flow conditions are not yet well -defined for such equipment. If these are known, application of Equation 7 to sections of the tower small enough to justify use of the logarithmic mean- potential will yield the tower volume required for each section. The sections must be taken perpendicular to the path of water flow. A correction to adjust the logarithmic mean potential, evaluated as for counter-flow, to the reduced effectiveness of cross-flow, has been derived for heat transfer and may be applied to this caseB. For small size counterflow spray towers intended for a low cooling range only considerable data I3; 11 are available on the performance of the spray system in- terms of the logarithmic mean enthalpy potential. These data show the importance of proper nozzle arrangement and spray distribution within the tower. The greatest cooling effect is shown to be obtained in a region close to the nozzles;' and the beneficial effects of. packing added in the lower section of the tower follow as increasing the cooling range. . . Atmospheric towers operate with natural draft, produced in a vertical direction by the stack action of the tower structure, at zero velocity of the approach wind. Approach wind of sufficient magnitude (the magnitude depending on the baffle arrangement which is designed to reduce drift) will cause cross-flow augmenting the natural draft. An adequate design requires the consideration of both flow conditions. - Expression for Cooling Tower Performance . The performance of a cooling tower is described in terms of its effective ness as an energy exchanger. The effectiveness is defined as the ratio of the energy actually exchanged to the energy available for exchange. Effectiveness expressions: - . Case 1. The slope of the operating line on the t -- h diagram exceeds the slope of the saturation line in the region of water temperatures considered. h - hi e h' - hi (9) Case B. The slope of the saturation line exceeds that of the operating line. _ hi -- hi t\ -- ti . ti -- Iwb (<i -- fwb) (10) This equation represents the approach to wet-bulb. Usual tower operating conditions conform to Case 1. Because of the curvature of the saturation line, operating conditions may present them selves to which neither Case 1 nor 2 applies. Since a simple expression for the intermediate case is not available, the expression of Case 1 may be utilized for the small number of operating conditions falling into the intermediate classification. . 662 CHAPTER 37. 1946 Guide * Make-Up Water . . Since the atmospheric water cooling equipment performs its functions chiefly by evaporating a portion of the water in order to cool the re-, mainder, there is a continual drain on the quantity of water in the system, and this loss must be replaced. Approximately 1 gal of water is lost for I: every 1000 gal of water cooled per degree of cooling range; so if 1000 gpm of water are cooled through a 10 deg range, 10 gpm of water will be re- . quired to replace evaporated water. Replacement supply is. usually regulated by a float control valve. Chemical treatment of the make-up water may be necessary to avoid excessive deposits in the condensers. Winter Freezing . - If atmospheric water eooling equipment is operated in freezing weather, . the water may be cooled to freezing temperature so ice forms and collects . , until its weight causes damage. To obviate freezing during continued operation, the efficiency of the apparatus may be lowered. This is done on the spray pond and the spray cooling tower, by reducing the quantity of water fed to the apparatus, thereby lowering the pressure at the nozzles and increasing the size of the drops produced. On the deck tower the upper system may be shut off and a secondary distribution system put in service midway down the height of the tower. The water will be kept above freezing because it will have shorter contact with the air. The mechanical draft tower can be protected by reducing the air flow through the tower, by stopping or reducing the speed of the fans, or by partially closing dampers. . If the system is operated intermittently in freezing weather, water in the basin may freeze and the expansion of the ice may do harm. Freezing during intermittent operation pan be prevented only by draining the water basin when it is out of service. On small roof installations, a tank large enough to hold all the water in the system is often installed inside the building and the basin is drained into this by gravity, the pump suc tion being taken from this inside tank. REFERENCES '--Temperature.of Water Available for Industrial Use in the United States, by W. D. Collins (U. S. Geological Survey, Water Supply Paper No. 520 F). , . Cooling Tower Performance Studies, by L. M. K. Boelter (A.S.H.V.E. Transactions, Vol. 45, 1939; i p.,615)> . ' *--A.S.H.V.E. Research Paper--Design of Spray Cooling Ponds, by S. Hori, U. A. Patchett and L. M. ; . K. Boelter (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning, October, 1942, p. 624). Principles of Chemical Engineering, by W. H. Walker, W. K..Lewis, W. H. McAdams and E. R'. Gilliland (McGraw-Hill Co., 1937, p. 480). . ' 5--Absorption and Extraction, by T. K. Sherwood (McGraw-Hill Co.. 1937. p. 91). --Performance Characteristics of a Mechanically Induced Draft, Counterflow, Packed Cooling Tower, by A. L. London, W. E. Mason and L. M. K. Boelter (A.S.M.E. Transactions, January, 1940, Vol. 62, p. 41); 7--Determination of Unit Conductances for Heat and Mass Transfer by the Transient Method, by A. L. London, H. B. Nottage and L. M. K. Boelter (Industrial and Engineering Chemistry, April. 1941, Vol. 33. p. 467). --Graphical Method of Determining Number Transfer Units, by T." Baker (Industrial and Engineering - Chemistry, August. 1935, Vol. 27, p. 977). '' . ' . --Loc. Cit. Note 4. p. 79. `' ' 1 Loc. Cit. Note 4, p. 142. j v ' 1 '--Performance and Selection of Mechanical-Draft Cooling Towers, by Joseph Lichtenstein {A.S.M.E. . Transactions. October, 1943, Vol. 65, No. 7, p. 779). ' ' ' **--Heat Transmission, by W. H. McAdams (McGraw-Hill Co., 1933, p. 157). *--A.S.H.V.E. Research Report Nq. 1189--^Performance Characteristics of a Forced Draft, Counter flow Spray Cooling Tower, by H. H. Niederman. E. D. Howe, J. P.'Longwell, R. A. Seban and L. M. K. . 1 Boelter (A.S.H.V.E. Transactions, Vol. 47, 1941. p. 413). . - , ' . . A.S.H.V.E. Research Report No. 1240--Spray Nozzle Performance in a Cooling Tower, by L. M. K.-Boelter and S. Hori (A.S.H.V.E.-Transactions, Vol. 49, 1943, p. 309). t CHAPTER 38 2)iumidi^ication by. .Sorbent IflfjateriaHs Definitions and Principles of Dehumidification by Sorption, Adsorbents, Absorbents, Dehumidification with Solid and Liquid Sorbents, Equipment Auxiliaries and Controls, Equip ment Performance, Comparison of Methods of Dehumidification THE reduction of the density of water vapor existing in any form within a given space is defined as dehumidification. The term .thus describes a special case of dehydration, which covers the removal of moisture in any form from matter. The degree of dehumidification required varies greatly with different applications, this being one of the prime Considerations in the choice of method. Dehumidification may be accomplished by sensible heat removal as described in Chapters 7, 37 and 43, or by utilizing sorbents. Sorbents are materials which have the property of dehumidifying gases without the help of refrigeration. All known materials are sorbents to a certain degree, in that they will decrease or increase in moisture content if their vapor pressure is greater or less than that of the surrounding' atmosphere. As generally used, however, the term refers to those materials whose capacity for moisture is large compared to their bulk and weight. Such materials are divided into two general classifications: 1. Adsorbent--A material which has the ability to hold water or other vapors on its internal surfaces without itself being, permanently changed physically or chemically. Certain solid materials, such as silica gel, and activated alumina have this property. Adsorbents also show an affinity for vapors other than water and this action is frequently selective. Thus, in a mixture of water vapor and organic gases, silica gel will effectively ' ' remove the water vapor and charcoal will remove the organic gases. The selective property of adsorbents is used in the removal of some contaminating gases.. (See ' Chapter 33.) - . .5 - 2. Absorbent--A material which has the ability to take up water vapor but which changes physically, chemically, or both, during the cycle. Calcium chloride is an example : of a solid material while liquid materials include solutions of lithium chloride, calcium chloride; lithium bromide and the ethylene glycols. 1 1 The fundamental principle by which sorbents remove moisture from gases lies in their property (when properly active) of having a low vapor pressure. When brought'in contact with humid gas haying a higher vapor pressure, the moisture from the gas is adsorbed or absorbed into the sorbent. This process can continue until the vapor pressure of the . sorbent has been raised by the increase in moisture content until it equals that of the humid air. The vapor pressure of the sorbent increases not only with moisture content but also with increased temperature. The process is reversible; hence to reactivate a sorbent, the temperature is . raised until its vapor pressure exceeds that of the surrounding gases. The moisture will then be driven out of the sorbent by vapor pressure differ- . ence. Upon cooling down to normal working temperature, the vapor, pressure of the dehydrated sorbent will have been reduced to the initial- condition, thus completing the cycle. . . Adsorbents '. ' These substances contain a vast number, of sub-microscopic pores which afford a tremendous internal surface to which water adheres or is - 663 ' 664 - CHAPTER 38 1946 Guide adsorbed. In spite of a porous structure these substances retain sufficient mechanical strength to resist the wear and. handling to which they are subjected. To be suitable for dehumidification purposes such substances must fulfill the following requirements: - 1. Possess suitable water vapor pressure characteristics. 2. Be available at a reasonable cost. 3. Adsorb sufficient moisture per pound of material to avoid excessive bed dimensions. 4. Be'chemically stable, resisting contamination from impurities. 5. Be physically rugged to resist breakdown from handling, abrasion, etc. 6. Be able to withstand breakdown from indefinitely repeated reactivation cycles. 7. Be capable of reactivation at reasonable temperatures. Activated Aluminum Oxide (Alumina) is a porous, amorphous form of aluminum oxide and is called by the common name Activated Alumina. - Commercial activated alumina commonly used for dehumidification contains about 92 per cent of AlzOz combined with hydrated aluminum oxide. It is available in granules ranging from a fine powder to pieces approximately. 1.5 in. in diameter. It has high adsorptive capacity per . unit of weight and is non-toxic. It may be repeatedly re-activated after adsorbing moisture without practical loss of its adsorptive ability. In the grade frequently used for air drying the reactivation maiy be accomplished at temperatures between 350 and 600 F. Specific gravity is 3.25 and the pores are reported to occupy 51 per cent of the volume of each particle. For most estimating purposes the volume-weight relation on a dry basis may be taken as 50 lb per cubic foot although in the smaller ' sizes the packed weight may be as much as 64 lb per cubic foot. ' Silicon Dioxide (Silica), in a prepared form obtained by suitable mixing of sulphuric acid with sodium silicate, is another solid adsorbent and is commonly called silica gel. Its capillary structure is exceedingly small, so small that its exact structure has to be deduced as it cannot be observed. It has high adsorptive capacity per unit of weight: it is non-toxic, and may be repeatedly re-activated at temperatures up to 600 F without practical deterioration. Re-activation is generally accomplished with air or other gases at temperatures not over 350 F. Volume of the capillary pores is ' reported to be from 50 to 70 per cent of the total solid volume. Silica gel is available commercially in a wide variety of sizes of graded granules ranging from 3 to 8 mesh granules to impalpable powder (through 325 mesh). The 6 to 16 mesh granules are generally used in dehumidification applications and will vary in density from 40 to 45 lb per cubic foot. There are other solid substances having marked adsorbent properties, but details concerning them are not available. Most adsorbents have the ability to absorb some gases and condensible vapors other them water -vapor, a property sometimes useful in air conditioning applications, and one which accounts for the extensive use of adsorbent materials in the field of chemistry. Air to be dehumidified is drawn or blown through a screened bed of dry, solid adsorbent and the water vapor in the air-vapor mixture is caught and retained in the pores of the medium. The exact nature of the process which goes on during adsorption is not known but it is stated that the action is brought about by surface condensation, and also by a difference between the vapor pressure of the water condensing inside thepores and the partial pressure of the water vapor in the air-vapor mixture. The adsorbing process in the bed can continue until, the vapor pressures ,. reach equilibrium. The amount of vapor adsorbed will depend on the Dehumidificatioh by Sorbent Materials 665 characteristic of the adsorbent being used, the temperature of the air. and the bed, the vapor pressure of the water vapor in the air being passed through it, and its final vapor pressure or moisture content. . As the bed of material adsorbs moisture, its vapor pressure approaches that- of the contacting air and the efficiency of adsorption gradually decreases. Equilibrium throughout the whole bed will not be reached for an extended period depending on bed thickness. Because of this diminish ing efficiency of adsorption, commercially designed systems do not. approach the state of equilibrium, but generally operate on a predetermined cycle or contact time and at partial saturation. Fig. 1. Temperature--Vapor Pressure--Concentration Relation for a Silica Gel Bed at Constant Temperature As the process of adsorption goes on heat is liberated in the bed. The total heat so liberated consists of the latent heat of the water vapor con densed together with the so-called heat of wetting of the adsorbent. The heat of wetting varies with the substance used as adsorbent' while the latent heat of condensation depends only on the temperature and pressure of the water vapor. Since the adsorptive ability of an adsorbent depends on the tempera ture of the bed and on the vapor pressure difference between the pores and the air-vapor mixture, it is important to know the pressures and temperatures at which pressure equilibrium is reached. . . Evidently the equilibrium conditions represent the limits beyond which adsorption of vapor cannot continue. This relationship for one com- 666 CHAPTER 38 - ___________ 1946 .Guide mercial silica gel of 0.70 specific gravity is shown graphically in. Fig. 1. These curves indicate the general manner in which adsorbents may be expected to perform, though the exact form and values of the curves will vary for each specific adsorbent and may vary even within the same generic group. . ' As an example in the interpretation of the chart consider the case when' . moist air at a temperature of 80 F and a vapor pressure of 0.5 in. of mer- " cury flows through a bed of silica gel which is at a temperature of 80 F. The chart indicates that the equilibrium of pressure between the air-vapor mixture and the bed is reached when the dry bed has adsorbed moisture to the extent of 30 per cent of the weight when dry. When this happens the bed can adsorb no more moisture unless its temperature is decreased or the air vapor pressure increased. The effect of temperature upon the adsorptive capacity of silica gel may. be observed by following the 59 F dew-point line'in Fig. 1. At 80 F gel temperature equilibrium is reached at 30 per cent moisture con centration while at 120 F and 200 F equilibrium is reached at 12 and 6.6 per cent moisture respectively. Under normal reactivation temperatures the residual water content of silica gel is between 5 and 6 per cent. . ' In practice, the temperature rise in the dehumidified air caused by the adsorption heat is approximately 10 deg for each grain of moisture removed. per cubic foot of air at atmospheric pressure. This temperature rise. occurs progressively through the adsorbent bed and is an important con sideration in predetermining the performance of a given design of ap paratus. Data such as these together with infornlation covering other characteristics, such as specific heat, resistance to air flow, etc., are of value in the basic design of adsorption apparatus. In the solution of ,' air conditioning problems, however, reference must be made to per formance data on established apparatus'designs such as are presented later in this chapter. Absorbents ' . Any absorbent substance may be used as a dehumidifying agent if it has a vapor pressure lower than the vapor pressure in the air-vapor mixture from which the moisture is to be removed. '. Solid Absorbents. The substances used are in general the solid forms of the liquid absorbents. Calcium chloride is frequently used bksuse of low cost. At present they ` . are used principally in small dessicating chambers, and in small dryers of the cartridge type, through which air is forced under pressure. ' Liquid Absorbents. These are characteristically water solutions of materials in which the vapor pressure is reduced to a suitable level by governing the concentration and . temperature of the dehydrating solution. In addition to having suitable vapor pressure characteristics a practical absorbent must also be widely available at economical cost, be non-corrosive, odorless, non-toxic, non-inflammable, chemically inert against any impurities' in the air stream, stable over .the range of use and,especially it must not precipitate out at the lowest temperature to which the apparatus is exposed. It must have low viscosity and be capable of being economically regenerated or concentrated after having been diluted by absorbing moisture. - - Water solutions, or brines, of the chlorides or bromides of various . inorganic elements such as lithium chloride and calcium chloride are the absorbents most frequently used in connection with air conditioning . . applications and detailed attention is confined to these two in this chapter. . ' The application consists of bringing the air'-vapor stream into intimate Dehumidification by Sorbent Materials . -_______ 667 contact with1 the absorbent, permissibly by passing the air stream through a finely divided spray of the brine but more generally by passing the air over a contacting pack where the liquid absorbent presents a large surface to the air stream. The difference in vapor pressure causes some of the . vapor in the air-vapor mixture to migrate into the brine. Here it condenses into liquid water and decreases the concentration of the absorbent. As the water vapor is added to the absorbent and condenses, it gives up its latent heat of condensation. For every pound of water absorbed and condensed the heat released is obtainable from steam tables. For in CONCENTRATION, PER CENT __ 0 5 10 15 20 25 30 35 CONCENTRATION, MOIAL ' Fig. 2. Temperature--Pressure--Concentrations for Lithium Chloride stance, at a dew-point temperature of 60 F .the amount of this heat is about 1057 Btu. In addition to this heat there is involved also the so- called heat of mixing which is frequently, considerable. The heat thus produced in the contacting packs of the average air conditioning instal lation is to a large extent transferred to the chemical solution itself and the balance to the air being dried. , A more complete cycle involves heat removal from the contacting medium, either within or external to the interchanger. Thus the tem perature of the medium may be higher than, equal to, or lower than that of the air, depending on the agent used and the function to be performed: In,such a cycle, the process may be accompanied by cooling or heating, or either, and such effect, if present, may be either a necessary by-product of the process, or for the specific purpose of obtaining both latent and 668 CHAPTER 38 1946 Guide sensible heat removal simultaneously. In many industrial applications it is not necessary to aftercool the air. In applications requiring low drybulb temperatures excess sensible heat must be removed by an aftercooler. ' Since the absorption process can continue only as long as there is a difference in vapor pressure between the absorbent and the air-vapor mixture and since at a given temperature of the absorbent the vapor pressure depends on the concentration of the solution, evidently there . must be a relation between these quantities which, if known, would state Fig. 3. Temperature--Pressure--Concentrations For Calcium Chloride the limits of the process. The relationship would also depend on the absorbent being used, and would have to be determined for each sub stance used as an absorbent. This relationship is shown graphically in Fig. 2 for lithium chloride, and Fig. 3 presents similar data for calcium chloride. These charts are essentially similar to Fig. 1, and their direct usefulness is limited by much the same considerations. Other physical .'properties of lithium chloride are shown in Tables 1, 2 and 3. In Fig. 2 and Table 1 the unit of concentration is the mol. An M molal solution is defined as a solution containing M X 42.37 grains of anhydrous ' lithium chloride.per 1000 grains of water. The formula connecting con-, centration in mols with weight in per cent is equivalent to:' (100 X MX 42.37) -f[1000 + (MX 42.37)]. ' Dehumidification by Sorbent Materials 669 Table 1. Properties of Lithium Chloride Solutions Concen TRATION Pound Mols (42.4 Lb) LiCl PER 1000 Lb Water Concen tration Per Cent by Weight Specific Gravity at 100 F Viscosity ' (Millipoise) 80 F 180 F Partial Heat of Mixing At 0 F, Btuper Lb Temp. COEFF. OF Partial Heat of Mixing Btu per Lb per F Specific Heat at 70 F Boilinc Point F at (760 mm Hg) Freezing Point. F o 2 4 6 8 10 0.0 7.8 14.5 20.2 25.3 29.7 1.000 1.037 1.076 1.111 1.143 1.172 8.61 11.19 14.42 18.62 24.32 32.28 -3.48 4.56 6.01 7.78 10.00 12.91 0.00 2.04 7.24 16.70 31.90 51.10 0.000 -0.014 -0.036 -0.069 -6.109 -0.143 0.998 0.901 0.831 0.778 0.739 6,710 212.0 215.8 221.5 228.9 238.1 248.4 32.0 16.3 - 5.8 -34.2 -69.0 -90.0 12 14 16 18 20 33.7 37.4 40.4 43.3 46.0 1.199 1.225 1.248 1.270 1.291 43.45 60.26 82.04 ,113.80 16.56 21.28 27.10 35.48 46.45 75.70 90.80 124.80 145.00 162.00 -0.160 -0.167 -0.176 -0,186 -0.194 0.687 0.666 0.647 0.631 258.8 268.9 277.9 285.8 293.2 -40.0 1.0 36.5 58.1 86.4 22 48.4 24 50.3 26 52.4 28 54.3 30 56.1 32 57.5 60.67 84.33 171.00 177.00 182.00 191.00 194.00 198.00 -0.200 -0.200 -0.210 -0.210 -0.210 -0.220 300.2 307.0 313.0 318.0 323.0 328.0 133.0 156.0 180.0 190.0 195.0 280.0 Table 2. Dew-Point of Air in Equilibrium with Lithium Chloride Solutions Dew Point at Zero CoNC. 2.0 4.0 6.0 Concentration of Lithium Chloride 8.0 | 10.0 1 12.0 | 14.0 16.0 18.0 20.0 22.0 24.0 26.0 28.0 30.0 320 315.2 308.7 299.9 300 295.4 289.1 280.5 280 275.6 269.5 261.1 260 255.8 250.0 241.9 240 236.0 230.4 222.5 220 216.2 210.8 203.2 200 196.4 191.2 183.9 180 176.6 171.6 164.7 160 156.8 152.1 145.4 140 137.0 132.6 126.1 120 117.2 113.0 106:8 110 107.3 103.2 97.2 100 97.4 93.4 87.5 90 87.5 83.6 77.9 8C 77.6 73.8 68.4 7C 67.7 64.0 58.7 290.2 270.9 251.7 232.6 213:5 194.4 175.4 156.4 137.4 118.4 99.4 89.9 80.5 71.0 61.6 52.2 279.7 260.0 241.5 222.7 203.8 184.9 166.1 147.3 128.6 109.9 91.1 81.9 72.7 63.3 54.0 44.8 269.4 259.6 251.5 244.1 236.5 230.0 223.8 218.6 214.5 2103 250.5 240.8 232.6 225.4 218.0 211.8 205.8 200.8 196.9 192.8 231.6 -222.2 214.0 206.7 199.7 193.5 187.8 183.2 179.3 175.2 212.8 . 203.5 195.5 188.4 181.7 175.4 170.0 165.6 162.0 158.4 194.2 185.0 177.1 170.0 163.6 157.5 152.2 148.3 144.6 140.5 175.5 166.4 158.6 151.6 145.3 139.6 134.6 130.7 1273 1243. 156.7 148.0 140.3 133.5 1273 121.9 117.0 113.3 110.1 138.1 129.6 122d 115.5 109.4 104.2 99.6 96.0 119.7 llO 103.9 97.4 91.6 86.6 82.2 -1013 93.1 85.9 79.5 73.8 69.0 82.7 74.7 67.8 61.5 56.0 73.5 65.6 58.8 52.6 47.1 64.4 56.6 49.8 43.7 38.2 55.2 47.6 40.8 34.8 29.3 46.1 38.5 31.8 25.9 20.6 37.0 29.5 22.9 17.2 12.0 57.8 54.3 49.1 42.7 35.5 27.9 20.5 14.0 ' 8-3 38.0 34.7 29.9 23.9 16.9 9.6 2.4 -3.9 .21 15.1 10.7 5.0 -1.7 . -8.7 -15.4 -4.5 -8.6 -13.9 -20.2 -27.0 -33.3 ' 670 CHAPTER 38 1946 Guide Table 3. Density of Lithium Chloride Solutions Concentration , '('412P0.40o0ulblnb)dLMWiCaotllesprer -0 2 4 6 8 10 12 14 16 . 18 20 22 24 26 28 30 -32 0 1.090 1.124 1.156 1.188 1.217 1.242 50 1.045 1.085 1.119 1.150 1.181 1.209 1.235 1.257 1.279 Temperature F Deo 100 150 200 . 250 300 1.037 1.076 1.111 1.143 1.172 1.199 1.225 1.248 1.270 1.291 1.026 1.064 1.100 1.132 1.162 1.188 1.214 1.236 1.259 1.280 1.310 1.317 1.012 1.052 1.087 1.122 1.152 1.178 1.203 1.226 1.248 1.279 1.289 1.307 1.313 1.338 t 1.142 1.168 1.192 1.215 1.237 1.568 1.278 1.296 1.312 1.327' 1.34 1.267 1.286 1.302 1.318 1.33 1.35 . Example 1. Determine the dew-point, wet-bulb, per cent saturation and humidity ratio of air in equilibrium at 100 F with pure lithium chloride solution of density 1.270. Solution. From Table 1 the concentration of a solution of density 1.270 at 100 F is 18.0 M. From Fig. 2 the dew-point of 18 M lithium chloride at 100 F is 43.7 F. From Table 1, Chapter 3, the partial pressure of-water over the solution is 0.2857 in. of Hg, and the humidity ratio is 0.00602 lb per pound dry air. From the Mollier Diagram the wet-bulb is 66.3 F, and the per cent saturation is 14 per c?nt. . Example 8. ` Determine the boiling point, and freezing point of 18 M lithium chloride solutions. .. . Solution.. From Table 1, boiling point (standard) is 285.8 F, freezing point is 58.1 F. ExarnpU 8. Calculate the heat of vaporization of 1 lb of water from a large amount of 18 M lithium chloride solution at the boiling point. Solution. The heat of boiling is equal to the heat of mixing plus the heat of boiling pure water at the same temperature. The heat of mixing from Table 1 at 18 U and .285.8 F is 145 -- (0.186 X 285.8) = 92 Btu per pound. The heat of vaporization of water from steam tables at 285.8 F is 920 Btu per.pound. Therefore the heat of vaporiza tion of water from the solution is 920 + 92 = 1012 Btu per pound. , Example 4- One thousand pounds of air per minute at 100 F dry-bulb with a dew point of 70 F and 36.7 per cent saturation are passed over 18 M lithium chloride solution. The rate of flow of the solution is 200 gpm and the entering temperature is 80 F. The air leaves the absorber at 85 F dry-bulb and dew-point of 35 F. Calculate (a) the heat to be removed from the lithium chloride solution to maintain these conditions, and (4) the temperature rise of the solution in passing through the absorber. ' ' Solution, (a) The enthalpy of the entering air at 100 F dry-bulb and 36.7 per cent saturation = Aa + \xhos ~ 24.029 + (0.367.X 47.70) = 41.54 Btu per pound (Table 1, Chapter 3). > , The per cent saturation of the air leaving at 85 F dry-bulb and 35 F dew-point is 16.2. Enthalpy of leaving air - 20.42 + 0.162 X 29.01 = 25.12 Btu per pound (Table 1, Chapter 3). Heat to be extracted from air = 1000 (41.54 -- 25.12) = 16,420 Btu per minute. Heat of mixing -- 145 (0.186 X' 80) = 130 Btu per pound of moisture removed. From Table l, Chapter 3, the moisture removal per pound of air = 0.01582 -- 0.00428 = 0.01154 lb. Heat of mixing for 1000 lb of air = 1000 X 0.01154 X 130 = 1500 Btu. Total heat extraction = 16,420 +.1500 = 17,920 Btu per minute. . (6) The weight of solution circulated is 200 X 1.27 (Table 1) X 8.33 = 2116 lb per minute: Its heat capacity = 2116 X 0.631 (Table 1) = 1335 Btu per (minute) (Fahren heit degree). The temperature rise = 17,920 4- 1335 = 13.4 F. Dehumidificaiion by Sorbent Materials'_________ _______ . 1 ________ 1 ' 671 . DEHUMIDIFICATION. WITH SOLID SORBENTS. One type of equipment suitable for producing dehumidification with solid drying agents utilizes an. apparatus with continuously rotating beds or dampers as illustrated in Fig. 4. The apparatus consists essen ' - tially of a cylinder or drum filled with a dehumidifying or drying agent. Air flow through the drum is directed' by baffles which permit three . independent air streams to flow through the adsorbing material. One. air stream consists of the wet air which is to be dehumidified. The second , is heated activation air used for drying that part of the dehumidifying material which has become saturated. The third air stream pre-cools the bed to permit an immediate pickup of moisture when that part of the . bed returns to the dehydration cycle. . In the rotating bed apparatus, the baffle sheets are stationary and the screened bed rotates at a definite speed to permit the proper time of contact in the activation, cooling and dehumidifying cycles. In the Activation air neater Fic. 4. Solid Adsorbent Dehumidifier--Rotating Bed Type rotating damper apparatus, the bed remains stationary and a sectionalized damper rotates. This rotating damper produces the same general effect as if the stationary baffles previously mentioned rotated. ' Clean air for activation is supplied at temperatures normally ranging from 300 to 350 F. Any source of clean heated air can be used such as air heated by electric heaters or steam coils, or air indirectly heated by , coal or oil fired interchangers. Direct fired heaters are usually designed for gas since there must be no condensable, tarry, combustion products to . contaminate the adsorbent. To avoid excessive contamination or clog ging of the absorbent'bed by dust it is frequently desirable to provide -. filters for the activation air. . ". '. Where activation air heating coils are supplied with steam at 80 lb per. - square inch gage pressure or higher, activation efficiency will remain normal and moisture removal capacity will not be reduced. When lower '. steam pressures are used, incomplete reactivation will result in reduced moisture removal. . . ... - Another type of solid adsorption equipment uses two complete sets of stationary adsorbing beds, arranged so that one set is dehumidifying . the air while the other set is being activated. With the dampers in the position shown in Fig. 5, air to be dried flows through one set of beds and '. ' is dehumidified, while activation air is heated and circulated through' the - other set. , After activation is complete, the beds are cooled by shutting off the, activation air heaters and allowing unheated air to circulate ' through them. . . .' ' ;1 ' After the beds have adsorbed moisture to a degree which begins `to' y 672 CHAPTER 38 1946 Guide impair performance, a timer-controller causes the dampers to rotate to the opposite side. Thus the beds which on the previous cycle were ad sorbing have activation air circulated through them, and vice versa. Activation air is heated in the same manner as with continuous equipment. DEHUMIDIFICATION WITH LIQUID SORBENTS One type of system utilizing liquid sorbents includes an external inter changer having essential parts consisting of a liquid contactor, a solution concentrator, a solution heater and a cooling coil all as shown in Fig. 6.' Activation air inlet Dehumidification by Sorbent Materials 673 the main brine reservoir for re-pumping. The concentrator operates in the manner of an evaporative condenser, whereby moisture is evaporatedfrom the brine, by the heating coils, into a stream of regeneration air taken . ' from and rejected to the outside atmosphere. Low pressure steam is normally used for heating the brine. When it is desirable or necessary to use gas or electricity, an auxiliary low pressure steam boiler is usually . added to the equipment. Concentrators operating on a simple boiler principle have not as yet been commercially practical. * . It should be noted that the solution concentration phase is the reverse of the absorption process. During concentration the aqueous vapor pressure of the solution is greater than that of the surrounding air, while during dehumidification, the reverse is the case. Utilization of this principle permits winter humidification, by heating (instead of cooling) the solution pumped to the contactor. Water is thereby evaporated Coding coil and Fig. 5. Solid Adsorbent Dehumidifier--Stationary Bed Type The contactor and cooling coil are located in the wet air stream. The air to be conditioned is brought into contact with an aqueous brine solution having a vapor pressure below that of the entering air, resulting in a - transfer of moisture (latent heat). As previously described, this results in a conversion of latent heat to sensible heat which raises the solution temperature and consequently the air temperature. The temperature change of the air being processed is determined by the cooling, water temperature and the amount of moisture removed in the equipment. Control of leaving air temperature may be obtained by precooling the absorbent solution in a suitable surface cooler, by tap, well, or artificially chilled water. The excess water of condensation, which dilutes the brine, is removed . in the solution concentrator. This is a low pressure steam heat exchanger ; which over-concentrates a portion of the weak liquor and returns it to Fig. 6. Liquid Absorbent Equipment in Which Solution Cooler and Contactor are Combined into, instead of being condensed out of, the conditioned air stream. This ' requires dilution of the brine externally to the contactor, rather than ` concentration. . ... EQUIPMENT AUXILIARIES AND CONTROLS Precoolers. When cold water is available, it is generally economical to use this water in a precooling coil in the warm, humid air stream. Any dehumidifying accomplished by this coil reduces the load; and moreover, lowering the temperature of the inlet air results in a higher moisture removal efficiency. Dry Air Coolers. Particularly with the solid adsorbent process,and to a lesser extent with liquid absorbents, a dry air cooler may be employed to remove sensible heat from the dehumidified air whenever it leaves the apparatus at an elevated temperature. A cooling coil using-city water is usual practice, and, is considered economical whenever the difference between effluent air and entering water temperatures is greater than 15 F. Controls. The use of direct or' chemical dehumidifying equipment makes possible the use of a relatively simple control,system with a humidi- stat or, alternatively, a wet-buib controller, to regulate the operation of the machine, and a thermostat to control the sensible cooling apparatus. Functionally, the relative humidity control may consist' of one Of the following: ' - ' - - _ 674' . CHAPTER 38 . 1946 Guide 1. Stop--Start--Where the humidistat starts the dehumidifier on rising 'humidity and stops it on falling humidity. -. 2. By-pass--Where the humidistat modulates face aind by-pass dampers located at the wet air inlet of the dehumidifier. 'Thus the quantity of air passing through the dehumidifier is proportioned in accordance with the change in latent heat Toad. , 3. Vapor Pressure Control (used with liquid absorbents)--Where the humidistat directly controls the temperature or concentration of the contacting solution, thereby matching the heat or moisture removal to the load requirement. .Dehumidification by Sorbent Materials ' ',' 67$ power required to drive air through the bed. It must also be borne in mind that the moisture -removal efficiency of all solid adsorbents and absorbent solutions is related to the temperature of the medium as well as to its state of unsaturation: On the other hand, it will be noted that the lower limits of dehumidification, which can be obtained with absorbent solutions, are likely to be controlled by the equilibrium dew-point at the lowest temperature at which the solution will resist freezing or crystalli zation. For this reason, actual moisture removing capacity is determined from performance curves of the several materials under practical con- Fig. 7. Performance Data For Rotating Bed Direct Gas Fired Silica Gel Dehumidifier EQUIPMENT PERFORMANCE It is recognized that, whereas the curves relating temperature and . vapor pressure of the several dehumidifying agents (Figs.1 1, 2 and 3) accurately define the equilibrium limits for these materials, these curves t cannot be used for predicting performance of available equipment. This occurs because (a) the materials themselves can only be utilized efficiently., within' certain ranges of moisture concentration, and (b)' the degree to which the vapor pressure of the air being treated approaches that at the surface of the material depends upon the completeness of the contact. It is obvious, for example, that the thickness of-a bed of solid adsorbent for a given, air flow will have a profound effect upon the degree' of moisture removal attained: However, it will have an inverse effect upon the ' Fig. 8- Silica Gel Dehumidifier Performance Data Steam Activation Type ditions of temperature, concentration and contacting efficiency as shown in Figs. 7, 8, 9 and 10. While these curves by. no means explore all the performance possibilities, they may be considered to be representative of sound design and application practice. . -. ' Performance data for standard production designs of silica gel rotating bed dehumidifiers are shown in Fig. 7 for a direct gas fired type, and in Fig. 8 for steam activation types for steam pressures of 5 to 80 lb per square .inch. They are designed for normal comfort cooling and moderatehumidity industrial air conditioning applications. Performance data for a heavy duty type activated alumina dehumidifier are given in Fig. 9. . This. unit has extended surface coils, imbedded in the adsorber, which are ' supplied with high pressure steam for heating during activation and cool water for. direct bed cooling during adsorption. Capacities shown,in. <576 CHAPTER 38 1946 Guide Fig. 9 are based upon 75 F cooling water. Performance data for stand ardized package lithium chloride equipment are shown in Fig. 10.' This is a single unit including both absorption contactor and regeneration section together with necessary heat exchangers. . COMPARISON OF METHODS OF DEHUMIDIFICATION Almost all summer comfort air conditioning, as well as much industrial and commercial air conditioning, requires both of the functions of sensible and latent heat removal from air. Each of the methods of cooling and dehumidification has as its objective either the removal of sensible or latent heat, or both simultaneously. Choice of method and medium therefore depends solely on whether (a) method and medium are physi cally able to accomplish the desired result with practical equipment, and (6) method and medium are justifiable economically. . '. Referring particularly to the problem of moisture removal, it may be stated that dehumidification either by using chilled water, brine or direct Dehumidification by Sorbent Materials 677. chemical methods deserve special consideration, as they do in applica tions where the task is primarily one of moisture removal with no necessity. for sensible temperature reduction. It is evident that it is not possible to set forth definite rules governing the choice of the method of dehumidification. It is only possible to state certain general conditions. ' Sorbent methods tend to be favorable where: 1. Low temperature water is available (below 65 F), to meet sensible cooling re quirements. ` Fig. 9. Activated Alumina Dehumidifier Performance Data Heavy Duty Type expansion refrigerant, or by using solid or liquid drying agents, is equally practical from the viewpoint of engineering performance for the vast majority of comfort and for a great many industrial applications requiring dew-point temperatures above 45 F. . ' For this reason, in the normal operating range, consideration is usually based upon practical factors which affect the over-all economics of the situation or upon the desire or necessity of attaining independent control of either temperature or humidity. In this connection, it. should be remembered that though a satisfactory balance may exist between cooling and dehumidification requirements at maximum design conditions, there' are many periods when practical operating conditions will result in an unsatisfactory balance of sensible and latent loads unless there is a simultaneous use of cooling and reheating. . In the normal range the choice between direct or chemical dehumidi fication, mechanical refrigeration, natural cold water, or ice, must be justified by the initial investment of available equipment; the availability and cost of prime energy sources; the charges to be allocated to space occupied, labor of operation and maintenance; and the degree of control required. ' . . - When- required dew-point. temperatures are below 45 F, direct or Fig. 10. Lithium Chloride Equipment Performance Data 2. Gas or steam is available at costs competitive with electricity. .' 3. Abnormally high internal latent heat load is encountered. 4. Abnormally low dew-points are required (40 F or lower). . 5. Required dry-bulb temperature is high or control of temperature is unimportant in comparison to maintenance of proper humidity. 6. In low temperature dryers where complementary heat exchange can be utilized. (In such cases the sensible heat of the dry air is reduced by the evaporation of moisture from the product being dried.) . Of the factors enumerated, Item 1, coupled with Item 2, tends to have the greatest influence since these factors affect the applicability to normal range requirements. However, each of the items listed has a direct influence upon economic considerations.- . 678 . _____ . CHAPTER 38 ________ 1946 Guide . Sorbent methods tend to be unfavorable where: . 1. Normal comfort dew-point temperatures are required with a predominantly sensible heat load and where mechanical refrigeration is required for sensible heat removal. ' 2. Water .temperature is too high for practical sensible heat removal (above 65 F). 3. Cold water (below 55 F) is available in adequate quantities so that it can be directly used for. both sensible and latent heat removal, or can be further chilled cheaply by mechanical refrigeration. ' I i i. Electricity is low in cost compared with gas or steams . i No single unfavorable item listed will necessarily disqualify a method, but generally there will be several offsetting favorable factors required to make it the choice on a purely economic basis. . When analyzed with respect to the broadening scope of applications for air conditioning, it is now evident that sorbent dehumidification can be used, within its legitimate economic limits,. for human comfort, com mercial drying or storage of food products requiring low humidities,' and for industrial processing and drying. '; . It provides an additional choice as to the type of equipment best suited to meet the requirements of special applicatipns and conditions. Particular attention is called to those industrial and'drying applications in which the dried air can be used at effluent temperature without further treatment. .' BIBLIOGRAPHY Direct Evaporative Cooling for Homes in the Southwest, by A. J. Rummel (A.S.H.V.E. Transactions, Vol. 46, 1940, p. 381), . Chemical Dehumidification Agents, by F. R. Bichowsky (A.S.H.V.E. Journal -Section, Heating, Piping and Air Conditioning, October, 1940, p. 627). CHAPTER 39 &e/f,-ncj.era.tion Theory and Cycle Calculations: Definitions, Simple Satu ration Cycles, Complex Refrigeration Cycles, Pipe Sizes and Friction Losses; the Steam Jet System, the Absorption System, Ice Systems, Storage Systems, the Reverse Cycle; Equipment and Arrangements: Types of Compressors, Condensers, Ex pansion Valves, Evaporators and Coolers, Equipment Selection WITH the increasing use of all-year comfort air conditioning instal lations the importance of refrigeration to the air conditioning engineer has been greatly magnified. .The details of equipment operation, maintenance, and design remain problems for the refrigeration engineer, but the air conditioning engineer does retain a responsibility to the customer which requires some knowledge on his part of the different refrigeration cycles' and the relative merits of each. In order to assist in meeting this need, the present chapter has been divided into two parts, the first covering the fundamental technical relationships which govern the selection and analysis of an operating cycle and the second presenting brief discussions of some of the equipment and equipment arrangements which are most commonly used. '' Definitions THEORY AND CYCLE CALCULATIONS ' ' . The ton of refrigeration is a quantity unit which originated in the days when harvested ice was the principal source of summer cooling, By definition the ton is the cooling effect realized when'one ton of.32 F ice melts to water at 32 F; since the latent heat of fusion of ice is 1.44 Btu per pound; the ton represents a unit cooling effect of 144 X 2,000 = 288,000 Btu. In common practice the ton is usually considered a rate (rather than quantity) unit and is taken as 288,000 Btu per day (24. hours) or 12,000 Btu per hour or 200 Btu per minute. Thus for air conditioning calculations,, the size of the requisite refrigeration machine, expressed in tons, can be obtained by dividing the heat gairi of the struc ture, expressed in'Btu per hour, by 12,000. In equation form: ' . where Ht -- (Btu per hour heat gain) -f- 12,000 '. Ht - load in tons. (1) - The working substance, or refrigerant, is the fluid which carries heat through the refrigeration cycle from the evaporator, where heat enters the refrigerant, to the condenser where the heat is discharged to some cooling medium. The great majority of modern refrigeration systems use a liquefiable vapor as the working substance. By altering the pressure of the refrigerant its boiling temperature is changed, allowing the material to. boil in the evaporator at a temperature sufficiently lower than that of the conditioned space to insure maintenance of an effective' heat transfer rate from the space (or in some cases from a secondary cooling fluid such as brine or cold water) to the refrigerant. The vapor formed in the evaporator is then raised in pressure (by a compressor, or by the absorber-generator combination of the absorption system) until its new boiling temperature exceeds the temperature of the available cooling ' 679 \ 680 CHAPTER 39 '____ ' 1946 Guide medium; under these conditions heat transfer is established from the refrigerant vapor to the cooling medium with resultant condensation of the refrigerant. When condensed, the high-pressure liquid refrigerant is reduced in pressure and again allowed to boil in the evaporator. Thermodynamically, a material for use as a refrigerant should have a large latent heat of vaporization since it is this heat quantity---subject to minor variations--which constitutes the working effectiveness of the refrigerant. Further, since the work required to compress a vapor increases rapidly with the pressure range, the thermodynamic character istics of the fluid should be such that the required low-to-high temperature range can be achieved with only a moderate change in pressure. A further consideration, from the standpoint of practical operating effectiveness, is that the suction pressure should not be below atmospheric (to prevent leakage of air into the refrigerant lines) nor should the condenser pressure be excessively high (to prevent need for extra-heavy construction). The specific volume-specific enthalpy relationship is also important" because some materials'would have such low density, when.in vapor form, that impractical compressor displacements would be needed to handle the suction vapor. Properties of refrigerants are usually given either in tabular or graphic form. In contrast to the temperature-entropy plotting which is used almost exclusively in steam-power work, refrigeration problems are usually referred to a pressure-enthalpy chart. The advantage of pressure- enthalpy plotting is that linear distances on the chart correspond to energy gains or, losses and the two types of processes, constant-pressure and constant-enthalpy, which occur most frequently in refrigeration cycles, can both be represented by straight vertical or horizontal lines. Tabular arrangements of refrigerant properties have the disadvantage common to all point representations, in requiring interpolation between given values, but have the advantage of an accuracy greater than that - obtainable from a chart. Tables 1, 2, 3, 4, 5, 6 and 7 give the thermo dynamic properties of seven of the more common refrigerants: dichloro- difluoromethane (F-12), monochlorodifluoromethane (F-22), methyl, chloride, ammonia, carbon dioxide, monofluorotrichloromethane (F-ll), and water; the first five of these materials are'commonly used in recipro cating compressors, the last two in centrifugal machines, while water also finds use in steam jet systems. . Referring to Table 1, the first column gives the range of saturation temperatures likely to occur in practice. The second column gives the saturation pressure expressed in pounds per square inch absolute corre sponding to a given temperature, while the next six columns give the three fundamental specific properties, volume, enthalpy, and entropy, of the saturated liquid and saturated vapor respectively. The last four columns give specific enthalpy and specific entropy for gases with 25 deg and with 50 deg of superheat; note' particularly that the column heading 50 F superheat means, not that the gas is at a temperature of 50 F, but that its temperature exceeds by 50 deg the saturation tempera ture corresponding to its actual pressure. Thus F-12 vapor at 38.0 psig and 91 F possesses 50 deg of superheat since its saturation temperature corresponding to 52.7 psia is 41 F. The tabular arrangements of refrigerant properties are literally for saturated or superheated materials only. In many cases, however, the engineer must work with sub-cooled liquids. With an accuracy sufficient for all practical purposes the specific volume and specific enthalpy of any Refrigeration 681 Table 1. Properties op Dichlorodifluoromethane(F-12) Sat. Tbmf. P Abb. Press. Lb fbb Sq In. Volume Liquid Vapor Specific Enthalpy and Entropy Taken From --40 F - Specific Enthalpy Entropy 25 F Superheat 50 F Superheat Liquid Vapor liquid Vapor Sp. En. Entropy Sp. Eh. Entropy 0 2 4 5 6 * 10 12 14 16 18 20 22 24 26 28 30 32 34 36 38 39 40 41 42 44 46 48 50 52 54 56 58 60 62 64 66 68 70 72 74 76 78 80 82 84 86 88 90 92 94 96 98 100 102 104 106 108 110 112 114 116 118 120 122 124 126 128 130 t32 134 136 138 140 23.87 24.89 25.96 26.51 27.05 28.18 29.35 30.56 31.80 33.08 34.40 35.75 37.15 38.58 40.07 41.S9 43.16 44.77 46.42 48.13 49.88 50.78 51.68 52.70 53.51 55.40 57.35 59.35 6139 63.49 65.63 6734 70.10 72.41 74.77 77.20 79.67 82.24 8432 87.50 90.20 93.00 95.85 98.76 101.70 1043 107.9 111.1 114.3 117.7 121.0 124.5 128.0 131.6 1353 139.0 1423 146.8 150.7 1543 158.9 163.1 167.4 1713 176.2 1803 185.4 190.1 194.9 1993 204.8 209.9 215.0 2203 0.0110 0.0110 0.0111 0.0111 0.0111 1.637 1.574 1314 1.485 1.457 8.25 8.67 9.10 932 9.53 0.0111 0.0112 0.0112 0.0112 0.0112 1.403 1351 1.301 1.253 1.207 9.96 1039 10.82 1136 11.70 0.0113 0.0113 0.0113 0.0113 0.0114 1.163 1.121 1.081 1.043 1.007 12.12 . 1235 13.00 13.44 13.88 0.0114 0.0115 0.0115 0.0115 0.0116 0.973 0.939 0.908 0.877 0.848 14.32 14.76 15.21 15.65 16.10 0.0116 0 0116 0.0116 0.0116 0.0116 0319 0.806 0.792 0.779 0.767 1635 16.77 17.00 17.23 17.46 0.0117 0.0117 0.0117 0.0118 0.0118 0.742 0.718 - 0.695 0.673 0.652 17.91 1836 18.82 1937 19.72 0.0118 0.0119 00119 0.0119 0.0120 0332 0.612 0.593 0.575 0357 20.18 20.64 21.11 2137 22.03 0.0120 0.0120 0.0121 0.0121 0.0121 0.540 0324 0.508 0.493 0.479 22.49 22.95 23.42 23.90 2437 0.0122 0.0122 0.0123 0.0123 0.0123 0.464 0.451 0.438 0.425 0.413 24.84 2532 2530 26.28 26.76 0.0124 0.0124 0.0124 0.0125 0.0125 Q.401 0389 0378 0.368 0357 27.24 27.72 28.21 28.70 29.19 0.0126 0.0126 0.0126 0.0127 0.0127 0347 0338 0328 0319 0310 29.68 30.18 30.67 31.16 31.65 0.0128 0.0128 0.0129 0.0129 0.0130 . 0.302 0.293 0.285 0.277 0.269 32.15 32.65 33.15 33.65 34.15 0.0130 0.0131 . 0.0131 0.0132 0.0132 0.262 0354 0347 0.240 0.233 34.65 35.15 35.65 36.16 36.66 0.0133 0.0133 0.0134 0.0134 0.0135 0.227 0.220 0.214 0.208 0.202 37.16 37.67 38.18 38.69 39.19 0.0135 0.0136 0.0137 0.0138 0.196 0.191 . 0.185 0.180 39.70 40.21 40.72 41.24 7831 78.44 78.67 78.79 78.90 79.13 7936 79.59 7932 80.05 80.27 80.49 80.72 80.95 81.17 8139 81.61 8133 82.05 82.27 82.49 82.60 82.71 8232 82.93 83.15 83.36 83.57 83.78 83.99 84.20 84.41 84.62 8432 85.02 85.22 85.42 85.62 85.82 86-02 86.22 86.42 86.61 86.80 86.99 87.18 8737 87.56 87.74 87.92 88.10 88.28 88.45 88.62 88.79 88.95 89.11 89.27 89.43 89.58 89.73 8937 90.01 90.15 9028 90.40 90.52 90.64 90.76 90.86 90.96 91.06 91.15 91.24 0.01869 0.01961 0.02052 0.02097 0.02143 0.17091 0.17075 0.17060 0.17052 0.17045 81.71 81.94 82.17 82.29 82.41 0.02235 0.02328 0.02419 0.02510 0.02601 0.17030 82.66 0.17015 82.90 0.17001 83.14 0.16987 8338 0.16974 83.61 0.02692 0.02783 0.02873 0.02963 0.03053 0.16961 0.16949 0.16938 0.16926 0.16913 83.85 84.09 84.32 8435 84.79 0.03143 0.03233 0.03323 0.03413 003502 0.16900 0.16887 0.16876 0.16865 0.16854 85.02 85.25 85.48 85.71 85.95 0.03591 0.03635 0.036S0 0.03725 0.03770 0.16843 0.16838 0.16833 0.16828 0.16823 86.18 86.29 86.41 8632 86.64 0.03859 0.03948 0.04037 0.04126 0.04215 0.16813 0.16803 0.16794 0.16785 0.16776 86.86 87.09 8731 87.54 87.76 0.04304 0.04392 0.04480 0.04568 0.04657 0.16767 0.16758 0.16749 0.16741 0.16733 87.98 88.20 88.42 88.64 88.86 0.04745 0.04833 0.04921 0.05009 0.05097 0.16725 0.16717 0.16709 0.16701 0.16693 89.07 89.29 89.50 89.72 89.93 0.05185 0.05272 0.05359 0.05446 0.05534 0.16685 0.16677 0.16669 0.16662 0.166S5 90.14 90.36 90.57 90.78 90.98 0.05621 0.05708 0.05795 0.05882 0.05969 0.16648 0.16640 0.16632 0.16624 0.16616 91.18 9137 9137 91.77 91.97 0.06056 0.06143 0.06230 0.06316 0.06403 0.16608 0.16600 0.16592 0.16584 0.16576 92.16 9236 9235 92.75 92.93 0.06490 0.06577 0.06663 0.06749 0.06836 0.16568 0.16560 0.16551 0.16S42 0.16533 93.11 93.30 93.48 93.66 93.82 0.06922 0.07008 0.07094 0.07180 0.07266 0.16524 0.16515 0.16505 0.16495 0.16484 93.98 94.15 9431 94.47 94.63 0.07352 0.07437 0.07522 0.07607 0.07691 0.16473 0.16462 0.16450 0.16438 0.16425 94.78 94.94 95.09 95.25 95.41 0.07775 0.07858 0.07941 0.08024 0.16411 0.16396 0.16380 0.16363 9536 95.72 9537 96.03 0.17829 0.17812 0.17795 0.17786 0.17778 0.17763 0.17747 0.17733 0.17720 0.17706 0.17693 0.17679 0.17666 0.17652 0.17639 0.17625 0.17612 0.17600 0.17589 0.17577 0.17S66 0.17560 0.17554 0.17549 0.17544 0.17534 0.17525 0.17515 0.17505 0.17496 0.17486 0.17477 0.17467 0.17458 0.17450 0.17442 0.17433 0.17425 0.17417 0.17409 0.17402 0.17394 0.17387 0.17379 0.17372 0.17365 0.17358 0.17351. 0.17344 0.17337 0.17330 0.17322 0.17315 0.17308 0.17301 0.17294 0.17288 0.17281 0.17274 0.17266 0.17258 0.17249 0.17241 0.17233 0.17224 0.17215 0.17206 0.17196 0.17186 0.17176 0.17166 0.17156 0.17145 0.17134 85.26 0.18547 85.51 0.18529 85.76- 0.18511 85.89 0.18502 86.01 0.18494 86.26 86.51 86.76 87.01 87.26 0.18477 0.18460 0.18444 0.18429 0.18413 87.51 87.76 88.00 88.24 88.49 0.18397 0.18382 0.18369 0.18355 0.18342 88.73 88.97 89.21 89.45 89.68 0.18328 0.18315 0.18303 0.18291 0.18280 89.92 90.04 90.16 90.28 90.40 0.18268 0.18262 0.18256 0.18251 0.18245- 90.65 90.89 91.14 91.38 91.61 0.18235 0.18224 0.18214 0.18203 0.18193 91.83 92.06 92.28 92.51 92.74 Q.18184 0.18174 0.18165 0.18155 0.18147 92.97 93.20 93.43 93.66 93.99 0.18139 0.18130 0.18122 0.18114 0.18106 94.12 94.34 94.57 94.80 95.01 0.18098 018091 0.18083 0.18075 0.18068 95.22 95.44 95.65 95.86 96.07 0.18061 0.18054 0.18047 0.18040 ' 0.18033 96.28 96.50 96.71 96.92 97.12 0.18026 0.18018 0.18011 0J8004 0.17998 97.32 97.53 97.73 97.93 98.11 0.17993 0.17987 0.17982 0.17976 0.17969 98.29 98.48 98.66 98.84 99.01 0.17961 0.17954 0.17946 0.17939 0.17931 99.18 99.35 99.53 99.70 99.87 0.17922 0.17914 0.17906 0.17897 0.17889 100.04 100.22 100.39 100.56 0.17881 0.17873 0.17864 0.17856 Noth: Sp. En.' = Specific Enthalpy. 632 CHAPTER 39 1946 Guide Table 2. Properties of Monochlorodifluoromethane (F-22) Sat Temp F Abs Press Lb per Sq In. Volume Heat Content and Entropy Taken prom -- 40 F Heat Content Entropy 50 Dec Superheat 100 Dec Superheat Liquid Vapor Liquid Vapor Liquid Vapor Heat Content En tropy Heat Content En tropy 0 38.79 0.01192 1.373 10.63 105.02 0.0240 0.2293 112.35 0.2446 120.00 0.2590 2 4 5 .6 8 40.43 42.14 43.02 43.91 45.74 0.01195 0.01198 0.01200 0.01201 0.01205 1.320 1.270 1.246 1.221 1.175 11.17 11.70 11.97 12.23 12.76 105.24 105.45 105.56 105.66 105.87 0.0251 0.0262 0.0268 0.0274 0.0285 0.2289 0.2285 0.2283 0.2280 0.2276 112 59 112.83 112.95 113.07 113.31 0.2442 0.2438 0.2436 0.2434 0.2430 120.26 120.52 120.65 120.78 121.04 0.2536 0.2581 0.2579 0.2577 0.2572 10 47.63 0.01208 1.130 13.29 106.08 0.0296 0.2272 113.55 0.2426 121.30 0.2568 12 49.58 0.01211 1.088 13.82 106.29 0.0307 0.2268 113.79 0.2422 121.56 0.2564 14 51.59 0.01215 1.048 14.36 106.50 0.0319 0.2264 114.02 0.2418 121.82 0.2560 16 53.66 0.01218 1.009 14.90 106.71 0.0330 0.2260 114.25 0.2414 122.08 0.2556 18 55.79 0.01222 0.9721 15.44 106.92 0.0341 0.2257 114.48 0.2410 122.33 0.2552 20 57.98 0.01225 0.9369 15.98 107.13 0.0352 0.2253 114.71 0.2406 122.59 0.2548 22 60.23 0.01229 0.9032 16.52 107.33 0.0364 0.2249 114.94 0.2402 122.84 0.2544 24 62.55 0.01232 0.8707 17.06 107.53 0.0375 0.2246 115.17 0.2398 123.10 0.2540 26. 64.94 0.01236 0.8398 17.61 107.73 0.0379 0.2242 115.40 0.2395 123.35 0.2537 28 67.40 0.01239 0.8100 18.17 107.93 0.0398 0.2239 115.62 0.2391 123.60 0.2533 30 69.93 0.01243 0.7816 18174 108.13 0.0409 0.2235 115.8.4 0.2387 123.85 0.2529 32 72.53 0.01247 0.7543 19.32 108.33 0.0421 0.2232 116.07 0.2383 124.10 0.2525 34 75.21 0.01250 0.7283 19.90 10S.52 0.0433 0.2228 116.29 0.2380 124.35 0.2522 36 77.97 0.01254 0.7032 20.49 108.71 0.0445 0.2225 116.52 0.2376 124.59 0.2518 38 80.81 0.0125S 0.6791 21.09 108.90 0.0457 0.2222 116.74 0.2373 124.84 0.2515 40 83.72 0.01262 0.6559 21.70 109.09 0.0469 6.2218 116.96 0.2369 125.08 0.2511 42 86.69 0.01266 0.6339 22.29 109.27 0.0481 0.2215 117.18 0.2366 125.32 0.2508 44 89.74 0.01270 0.6126 22.90 109.45 0.0493 0.2211 117.40 0.2363 125.56 0.2504 46 92.88 0.01274 0.5922 23.50 109.63 0.0505 0.2208 117.61 0.2359 125.80 0.2501 48 96.10 0.01278 0.5726 24.11 109.80 0.0516 0.2205 il7.82 0.2356 126.04 0.2497 50 52 . 54 56 58 99.40 102.8 106.2 109.8 113.5 0.01282 0.01286 0.01290 0.01294 0.01299 0.5537 0.5355 0.5184 0.5014 0.4849 24.73 25.34 25.95 26.58 27.22 109.98 110.14 110.30 110.47 110.63 0.0528 0.0540 0.0552 0.0564 0.0576 0.2201 0.2198 0.2194 0.2191 0.2188 118.02 118.22 118.42 118.62 118.82 0.2353 0.2350 0.2347 0.2343 0.2340 126.27 0.2494 126.50 0.2491 126.73 0.2488 126.96 0.2484 127.19 .0.2481 60 117.2 0.01303 0.4695 27.83 110.78 0.0588 0.2185 119.01 0.2337 127.42 0.2478 62 121.0 * 0.01307 0.4546 28.46 110.93 0.0600 0.2181 119.21 0.2334 127.65 0.2475 64 .124.9 0.01312 0.4403 29.09 111.08 0.0612 0.2178 119.40 0.2331 127.87 0.2472 66 128.9 0.01316 0.4264 29.72 111.22 0.0624 0.2175 119.59 0.2327 128.10 0.2469 68 133.0 0.01320 0.4129 30.35 111.35 0.0636 0.2172 119.77 0.2324 128.32 0.2466 70 137.2 72. 141.5 74 145.9 76 150.4 78 155.0 0.01325 0.01330 0.01334 0.01339 0.01344 0.4000 0.3S75 0.3754 0.3638 0.3526 30.99 31.65 32.29 32.94 33.61 111.49 111.63 111.75 111.88" 112.01 0.0648 0.0661 0.0673 0.0684 0.0696 0.2168 0.2165 0.2162 0.2158 0.2155 119.96 120.15 120.32 120.50 120.67 0.2321 0.2318 0.2315 0.2312 0.2309 128.54 128.76 12.897 129.19 129.40 0.2463 0.2460 0.2457 0.2455 0.2452 SO 82 84 . 86 S8 159.7 164.5 169.4 174.5 179.6 0.01349 . 0.3417 0.01353 0.3313 0.01358 0.3212 0.01363 0.3113 0.01368 0.3019 34.27 34.92 35.60 36.28 36.94 112.13 112.24 112.36 112.47 112.57 0.0708 0.0720 0.0732 0.0744 0.0756 0.2151 0.2148 02144 0.2140 0.2137 120.85 121.02 121.18 121.34 121.50 0.2306 0.2303 0.2300 0.2297 0.2294 129.61 129.82 130.02 130.23 130.43 0.2449 0.2446 0.2443 0.2441 0.2438 90 184.8 92 190.1 94 195.6 96 201.2 98 206.8 0 01374 0.01379 0.01384 0.01390 0.01396 0.2928 0.2841 0.2755 0.2672 0.2594 -37.61 38.28 38.97 39.65 40.32 112.67 112.76 112.85 112.93 113.00 0.0768 0.0780 0.0792 0.0803 0.0815 0.2133 0.2130 0.2126 0.2122 0.2119 121.66 0.2291 121.82. 0.2288 121.97 0.2285 122.12 0.2282 122.26 0.2279 130.63 130.83 131.03 131.23 131.42 0.2435 0.2432 0.2429 0.2427 0.2424 100 212.6 102 218.5 104 224.6 106 230.7 108 237.0 0.01402 0.0140$ 0.01414 0.01420 0.01426 0.2517 0.2443 0.2370 0.2301 0.2233 40.98 41.65 42.32 42.98 43.66 113.06 113.12 113.16 113.20 113.24 0.0827 0.0839 0.0851 0.0862 0.0874 0.2115 0.2111 0.2107 0.2104 0.2100 122.40 122.53 122.66 122.79 122.92 0.2276 .0.2273 Q.2270 0.2267 0.2264 131.61 131.80 131.99 132.17 132.35 0.2421 0.2418 0.2416 0.2413 0.2411 110 243.4 112 249.9 114 256.6 116 263.4 118 270.3 0.01433 0.01440 0.01447 0.01454 0.01461 0.2167 0.2104 0.2043 0.1983 0.1926 44.35 45.04 45.74 46.44 47.14 113.29 113.34 113.38 113.42 113.46 0.0886 0.0898 0.0909 0.0921 0.0933 0.2096 0.2093 0.2089 0.2085 0.2081 123.04 123.16 123.28 123.40 123.51 0.2261 0.2258 0.2255 0.2253 0.2250 132.53 132.71 132.8S 133.05 133.22 0.2408 0.2405 0.2403 0.2400 0.2398 120 277.3 0.01469 0.1871 47.85. 113.52 0.0945 0.2078 123.62 0.2247 133.39 0.2395 Data from Kinetic Chemicals. Inc.. 1945 Refrigeration Table 3. Properties of Methyl Chloride 683 Sat. Temp. F Abs. Press. Lb per So I. VOLDMB Liquid Vapor Specific Enthalpy and Entropy Taken Fbou --40 F Specific Enthalpy Entropy 100 F Superheat 200 F Superheat liquid Vapor Liquid Vapor Sp. En. Entropy Sp. En. Entropy 0 18.73 0.0162 5.052 2 19.60 0.0162 4.856 4 20.47 0.0163 4.661 5 20.91 0.0163 4.563 6 21.39 0.0163 4.476 14.4 192.4 0.0328 0.4197 215.6 0.467 237.2 0.507 15.1 193.1 0.0344 0.4196 216.2 0.466 237.7 0.505 15.8 193.8 0.0360 0.4195 216.7 0.465 238.2 16.2 194.1 0.0368 0.4195 217.0 0.464 238.5 0.503 16.6 194.4 0.0376 0.4194 217.3 0464 238.8 0.502 8 22.34 0.0164 4.303 10 23JO 0.0164 4.129 12 24.38 0.0164 3.984 14 25.46 0.0164 3.839 16 26.55 0.0165 3.693 17J 195.1 0.0391 0.4193 217.9 0.463 239.4 0.501 18.1 195.8 0.0407 0.4192 218.5 0.463 240.0' 0.500 18.8 196.3 0.0423 0.4184 219.0 0.462 240-5 0.499 19.6 196.7 0.0439 0.4176' 219-5 0.462 241.0 0.498 20.3 197.2 0.0454 0.4168 220.0 0.461 241.5 0.498 18 27.63 0.0165 3.548 20 28.71 0.0166 3.403 22 29.98 0.0166 3.288 24 31.25 0.0166 3.172 26 32.53 0.0167 3.057 21.1 197.6 0.0472 0.4160 220.5 0.461 242.0 0.497 21.8 198.1 0.0486 0.4152 221.0 0.460 242.5 0 496 22J 198.5 0.0501 0.4148 221.5 0.459 243.0 0.495 . 23.3 198.9 0.0516 0.4143 222.0 0.459 243.6 0.495 24.0 199.3 0.0532 0.4139 222.4 0.458 244.1 0.494 28 33.80 0.0167 2.941 30 35.07 0.0168 2.826 32 36.55 0.0168 2.734 34 38.03 0.0169 2.642 36 39.51 0.0169 2.549 24.8 199.7 0.0547 0.4134 222.9 0.458 244.7 0.494 25.5 200.1 0.0562 0.4130 223.4 0.457 245.2 0.493 26.2 200.5 0.0577 0.4124 223.9 0.456 245.7 0.492 27.0 200.9 0.0592 0.4118 224.3 - 0.455 246.2 0.492 27.7 201.4 0.0607 0.4111 224.8 0.455 246.7 0.491 38 40.99 0.0169 2.457^ 28J 201.8 0.0622 0.4105 225.2 0.454 247.2 0.491 39 41.73 0.0170 2.411 : 28.8 202.0 0.0629 0.4102 225.S 0.453 247.4 0.490 40 42.47 0.0170 2J65 29.2 202.2 0.0637 0.4099 225.7 0.453 247.7 0.490 41 43.33 0.0170 2.328 29.6 202.4 0.0644 0.4096 225.9 0.453 248.0 0.490 42 44.18 0.0171 2.290 29.9 202.6 0.0651 0.4093 226.1 0.452 248.3 0.489 44 45.89 0.0171 2.216 45 47.61 0.0171 2.141 48 49.32 0.0172 2.067 SO 51.03 0.0172 1.992 52 53.00 0.0172 1.931 30.7 203.0 0.0666 0.4087 226.6 0.451 248.8 0.489 31.4 203.3 0.0680 0.4081 227.0 0.451 .249.4 0.488 32.2 203.7 0.0695 0.4075 227J 0.450 249.9 0.488 32.9 204.1 0.0709 0.4069 227.9 0.449 2S0.5 0.487 33.7 204.4 0.0724 0.4063 228.2 0.448 251.0 0.486 54 54.97 0.0173 1.870 56 56.94 0.0173 1.810 58 58.91 0.0173 1.749 50 60.88 0.0174 1.688 62 63.13 0.0174 1.638 34.4 35.2 35.9 36.7 37.4 204.7 205.1 205.4. 205.7 206.0 0.0739 0.0754 0.0769 0.0784 0.0798 0.4056 0.4050 0.4043 0.4037 0.4030 228.6 228.9 229.3 229.6 229.9 0.448 0.447 0.447 0.446 0.445 251.5 252.0 252.5 253.0 253.5 0.486 0.485 0.485 0.484 0.483 64 66 68 70 65.37 67.62 69.86 72.11 0.0174 0.0175 0.0175 0.0176 1.588 1.539 1.489 1.439' 38.2 .38.9 39.7 40.4 206.3 206.6 206.9 207.2 0.0812 0.0827 0.0841 0.0855 0.4024 04017 0.4011 0.4004 230-3 23C.6 231.0 231.3 0.444 0.443 0.442 0.441 254.0 254.5 255.0 255.5 0.483 0.482 0.482 0.481 72 74.66 0.0176 1.398 41.1 207.5 0.0869 0.3993 231.6 0.440 256.0 0.480 74 77.21 0.0177 1.357 76 79.76 0.0177 1.315 78 82.31 0.0178 1.274 84.86 0.0178 1.233 82 87.74 0.0178 1.199 41.9 207.7 0.0883 0.3992 ' 232.0 0.439 256.5 0.480 42.6 208.0 .0.0898 0.3985 232.3 0.439 256.9 0.479 43.4 208.2 0.0912 0.3979 232.7 0.438 257.4 0.479 44.1 208.5 0.0926 0.3973 233.0 0.437 257.9 0.478 44.8 208.7 0.0940 0.3967 233-3 0.436 258.4 0.478 84 90.62 0.0179 8o 93.50 0.0179 96.38 0.0180 99.26 0.0180 102.49 0.0180 1.165 1.130 1.096 1.062 1.033 45.6 209.0 0.0953 0.3960 233.6 0.435 258.9 0.477 46.3 209.2 0.0967 0.3954 233.9 0.435 259.4 0.477 47.1 209.5 0.0980 0.3947 2342 0.434 259.9 0 476 47.8 209.7 0.0994 0.3041 234.5 0.433 260.4 0.476 48.6 209.9 0.1008 0J935 234.8 0.433 260.8 0.476 94 105.72 0.0181 103.94 0.0181 112.17 0.0182 115.40 0.0182 119.00 0.0183 1.005 0.9764 0.9478 0.9193 0.8952 49J 50.1 S0.8 51.6 52.3 210.2 210.4 210.7 210.9 211.1 0.1022 0.1035 0.1049 0.1063 0.1076 0-3929 0.3922 0.3916 0.3910 0-3903 235.1 235.4 235.7 236.0 236.4 0.432 0.432 0.431 0.431 0.430 261.2 261.6 262.0 262.4 262.8 0.475 0.475 0474 0.474 0.474 104 122.60 0.0183 0.0184 129.80 0.0184 133.40 0.0185 137.42 0.0185 0.8712 0.8471 0.8231. 0.7990 0.7786 53.1 53.8 54.6 - 55.3 56.1 211.3 211.4 211.6 211.8 212.0 0.1090 0.1103 0.1117 0.1130 0.1144 0.3897 0-3890 0.3884 0.3877 0.3871 236.8 237.1 237.5 237.9 238.1 0.430 0.429 0.429 0.428 0.427 263.2 263.5 263.9 264-3 264.6 0.473 0.473 0.472 0.472 0.471 114 141.44 0.0185 0.7583 145.46 0.0186 0.7379 149.48 0.0186 0.7176 153JO 0.0187 v 0.6972 56.8 212.2 0.1157 0.3864 238.3 0.427 264.8 0.470 57.6 212.4 0.1171 0.3858 238.6 0.426 265.1 0.470 S8J 212.6 0.1184 0.3851 238.8 0.426 265.3 0.469' 59.1 212.8 0.1198 03845 239.0 0.425 265.6 0.468 - Note: Sp. En. = Specific Enthalpy. 684 CHAPTER 39 1946 Guide Table 4. Properties of Ammonia Sat. Temp. P Asa. Press. Lb FEB Sq In. VOLUME Liquid Vapor Specific Enthalpy and Entropy Taken From --40 F Specific Enthalpy Entropy 100 F Superbeat 200 F Superheat liquid Vapor liquid Vapor Sp. En. Entropy Sp. En. Entropy 0 2 4 5 6 8 10 12 14 16 18 20 22 24 26 28 30 32 34 36 38 39 40 41 42 44 46 48 50 52 54 56 . 58 60 62 64 66 68, .70' 72 74 76 ' 78 80 82 84 86 88 90 92 94 96 98 100 102 104 106 108 110 112 114 116 118 120 * 122 .124 .. 126 128 30.42 31.92 33.47 34.27 35.09 36.77 38J1 40.31 42.18 44.12 46.13 48.21 50.36 52.59 . 54.90 57.28 59.74 62.29 64.91 67.63 70.43 71.87 73.32 74.80 76.31 79.38 82.55 85.82 89.19 92.66 96.23 99.91 103.7 107.6 111.6 115.7 120.0 124.3 128.8 133.4 138.1 143.0 147.9 153.0 158.3 163.7 169.2 174.8 180.6 186.6 192.7 198.9 205.3 211.9 218.6 225.4 232.5 239.7 247.0 2543 262.2 270.1 278.2 286.4 294.8 303.4 312.2 32U 0.02419 0.02424 0.02430 0.02432 0.02435 0.02440 0.02446 0.02451 0.02457 0.02462 0.02468 0.02474 0.02479 0.02485 0.02491 0.02497 0.02503 0.02508 0.02514 0.02521 0.02527 0.02530 0.02533 0.02536 0.02539 0.02545 0.02551 0.02558 0.02564 0.02571 0.02S77 0.02584 0.02590 0.02597 0.02604 0.02611 0.02618 0.02625 0.02632 0.02639 0.02646 0.02653 0.02661 0.02668 0.02675 0.02684 0.02691 0.02699 0.02707 0.02715 0.02723 0.02731 0.02739 0.02747 0.02756 0.02764 0.02773 0.02782 0.02790 0.02799 0.02808 0.02817 0.02827 0.02836 0.02846 0.02855 0.02865 0.0287S 9.116 8.714 8.333 8.150 7.971 7.629 7.304 6.9966.703 6.425 6.161 5.910 5.671 5.443 5.227 5.021 4.825 4.637 4.459 4.289 4.126 4.048 3.971 3.897 3.823 3.682 3.547 3.418 3.294 3.176 3.063 2.954 2.851 2.751 2.656 2.565 2.477 2.393 2.312 2.235 2.161 2.089 2.021 1.955 1.892 1.831 1.772 1.716 1.661 1.609 1.559 1.510 1.464 1.419 1.375 1.334 1.293 1.254 1.217 1.180 1.145 1.112 1.079 1.047 1.017 0.987 0.958 0.931 42.9 45.1 47.2 48.3 49.4 51.6 53.8 56.0 58.2 60.3 623 64.7 66.9 69.1 71.3 73.5 75.7 77.9 80.1 823 84.6 85.7 86.8 87.9 89.0 91.2 93.5 95.7 97.9 100.2 102.4 104.7 106.9 109.2 111.5 113.7 116.0 118.3 120.5 122.8 125.1 127.4 129.7 132.0 134.3 136.6 138.9 141.2 143.5 145.8 148.2 150.5 152.9 155.2 157.6 159.9 162.3 164.6 167.0 169.4 171.8 174.2 176.6 179.0 181.4 183.9 186.3 188.8 611.8 612.4 613.0 613.3 613.6 614.3 614.9 615.5 616.1 ' 616.6 617.2 617.8 618.3 618.9 619.4 619.9 620.5 621.0 621.5 622.0 622.5 622.7 623.0 623.2 623.4 623.9 624.4 624.8 625.2 625.7 626.1 626.5 626.9 627-3 627.7 628.0 628.4 628.8 629.1 629.4 629.8 630.1 630.4 630.7 631.0 631.3 631.5 631.8 632.0 632.2 632.5 632.6 632.9 633.0 633J 633.4 633.5 633.6 633.7 633.8 633.9 634.0 634.0 634.0 634.0 634.0 633.9 633.9 0.0975 0.1022 0.1069 0.1092 0.1115 0.1162 0.1208 0.1254 0.1300 0.1346 0.1392 0.1437 0.1483 0.1528 0.1573, 0.1618 0.1663 0.1708 0.1753 0.1797 0.1841 0.1863 0.1885 0.1908 0.1930 0.1974 0.2018 0.2062 0.2105 0.2149 0.2192 0.2236 0.2279 0.2322 0.2365 0.2408 0.2451 0.2494 0.2537 0.2579 0.2622 0.2664 0.2706 0.2749 0.2791 0.2833 0.2875 0.2917 0.2958 0.3000 0.3041 0-3083 0.3125 0.3166 0.3207 0.3248 0.3289 0.3330 0.3372 0.3413 0.3453 0.3495 0.3535. 0.3576 0.3618 0.3659 0.3700 0.3741 1.3352 1.3312 1.3273 1.3253 .13234 1.3195 13157 13118 13081 13043 1.3006 1.2969 1.2933 1.2897 1.2861 1.2825 13790 13755 1.2721 13686 1.2652 1.2635 1.2618 13602 1.2585 1.2552 1.2519 13486 1.2453 13421 1.2389 1.2357 1.2325 1.2294 13262 1.2231 13201 13170 1.2140 13110 1.2080 1.2050 1.2020 1.1991 1.1962 1.1933 1.1904^ 1.1875 1.1846 1.1818 1.1789 1.1761 1.1733 1.1705 1.1677 1.1649 1.1621 1.1593 1.1566 1.1538 1.1510 1.1483 1.1455 1.1427 1.1400 1.1372 1.1344 1.1316 666.8 667.6 668.4 668.8 669.3 670.1 670.9 671.7 672.5 673.4 6743 675.0 675.8 676.6 6773 678.1 678.9 679.7 680.4 681.2 681.9 682.3 682.7 683.1 683.4 6943 684.9 685.6 686.4 687.1 687.8 688.5 6893 689.9 690.6 6913 691.9 692.6 6933 694.0 694.6 6953 695.9 696.6 697.2 697.8 698.5 699.1 699.7 7003 700.9 701.5 702.1 702.7 7033 703.8 7043 705.0 705.5 706.1 706.6 7073 707.7 708.2 708.6 709.1 709.6 710.0 1.4439 1.4400 1.4360 1.4340 1.4321 1.4281 1.4242 1.4205 1.4168 1.4130 1.4093 1.4056 1.4021 1.3985 13950 13914 1.3879 1.3846 13812 1.3779 13745 1.3729 13712 1.3696 13680 13648 13616 1.3584 13552 13521 13491 1.3460 1.3430 1.3399 13270 13341 13312 13283 1.3254 1.3226 1.3199 1.3171 1.3144 13116 13089 1.3063 1.3040 13010 1.2983 1.2957 1.2932 1.2906 1.2881 1.2855 1.2830 1.2805 1.2780 1.2755 1.2731 1.2708 1.2684 1.2661 1.2636 1.2612 1.2587 1.2563 1.2538 1.2513 720.3 721.2 722.2 722.6 723.1 13317 13277 13236 13216 13196 724.1 725.0 725.9 726.8 727.8 13155 1.5115 13077 13039 1.5001 728.7 729.6 7303 731.4 732.4 1.4963 1.4925 1.4889. 1.4853 1.4816 7333 734.2 735.1 736.0 7363 . 1.4780 1.4744 1.4710 1.4676 1.4643 737.7 738.2 738.6 739.0 739.5 1.4609 1.4592 1.4575 1.4559 1.4542 740.4 . 7413 742.2 743.1 744.0 1.4510 1.4477 1.4445 1.4412 1.4362 7443 745.7 746 5 747.4 748.2 1.4351 1.4321 1.4290 1.4260 1.4231 749.1 749.9 7503 751.6 752.4 1.4202 1.4172 1.4143 1.4114 1.4086 7533 754.1 755.0 7553 756.6 1.4059 L4031 .1.4004 13976 13949 757.4 758.3 759.1 7S9.9 760.7 1.3923 13896 1.3870 1.3843 13818 7613 762.2 763.0 7633 764.6 13793 13768 13743 1.3718 13693 7653 766.1 766.9 767.6 7683 13668 13643 1.3619 13596 13573 769.1 769.8 7703 771.3 13550 13527 13503 13479 772.0 7723 7733 774.2 13455 13431 1.3407 13383 Note: . Sp. En. = Specific Enthalpy. Refrigeration 685 Table -5. Properties of Carbon Dioxide Sat. Tkmp. F Asa. Press. La per Sq In. Volume Liquid Vapor 0 305.5 0.01570 0.29040 2 315.9 0.01579 0.28030 4 326.5 0.01588 0.27070 5 332.0 001592 0.26610 6 337.4 0.01596 0.26140 8 348.7 0.01605 0.25260 10 360.2 0.01614 0.24370 12 371.9 0.01623 0.23540 14 383.9 0.01632 0.22740 16 396.2 0.01642 0.21970 18 20 22 24 26 . 408.9 421.8 434.0 448.4 462.2 0.01652 0.01663 0.01673 0.01684 0.01695 0.21210 0.20490 0.19790 0.19120 0.18460 28 476.3 0.01707 0.17830 30 490.8 001719 0.17220 32 505.5 0.01731 0.16630 34 522.6 0.01744 0.16030 36 536.0 0.01759 0.15500 38 551.7 0.01773 0.14960 39 559.7 0.01780 0.14700 40 567.8 0.01787 0.14440 41 576.0 0.01794 0.14185 42 584.3 0.01801 J). 13930 44 601.1 0.01817 0.13440 46 618.2 0.01834 0.12970 48 635.7 0.018S1 0.12500 50 653.6 0.01868 0.12050 52 671.9 0.01887 0.11610 54 690.6 0.01906 0.11170 56 709.5 0.01927 0.10750 58 728.8 0.01948 0.10340 60 748.6 0.01970 0.09940 62 769.0 0.01995 0.09545 64 66 68- . 70 72 789.4 810-3 831.6 853.4 87S.8 0.02020 0.02048 0.02079 0.02112 0.02152 0.09180 0.08800 0.08422 0.08040 0.07654 74 898.2 0.02192 0.07269 76 921.3 0.02242 0.06875 78 944.8 0.02300 0.06473 80 968.7 0.02370 0.06064 82 993.0 0.02456 0.05648 84 1017.7 0.02553 86 1043.0 0.02686 873 1069.9 0.03454 0.05223 0.04789 0.03454 Specific Enthalpy and Entropy Taken From --40 F . Specific Enthalpy Entropy 50 F Superheat 100 F Superheat liquid Vapor liquid Vapor Sp. En. Entropy Sp. En. Entropy 18.8 138.9 0.0418 05024 153.7 03342 1673 0.3612 19.8 138.8 0.0440 0.3014 153.7 0.3330 167.6 0.3600 20.8 138.8 0.0461 05005 153.7 0.3318 167.7 03588 21.3 138.8 0.0472 0.3000 153.7 03312 167.7 0.3582 21.8 138.7 0.0483 0.2994 153.7 03306 167.8 0.3576 22.9 138.7 0.0504 0.2982 153.7 03293 167.9 03563 24.0 138.7 0.0526 0.2970 153.7 03281 168.0 03550 25.0 138.6 0.0548 0.2958 1S3.7 03270 168.1 03538 26.1 138.6 0.0S71 0.2946 153.7 03259 168.2 03526 27.2 138-5 0.0593 0.2933 153.7 03249 1683 03513 28.3 138.4 0.0616 0.2921 153.7 03238 168.5 0.3501 29.4 1383 0.0638 0.2909 153.7 03227 168.6 03489 30.5 138.2 0.0662 0.2897 153.7 03214 168.7 0.3479 31.7 138.1 0.0686 0.2885 153.7 03202 168.8 03470 32.9 138.0 0.0710 0.2873 153.7 03189 168.9 0.3460 34.1 35.4 36.7 37.9 ' 39.1, 137.9 137.8 137.7 137.4 137.2 0.0734 0.0758 0.0781 0.0804 0.0828 0.2861 0.2849 0.2834 0.2820 0.2805 153.7 153.7 153.7 153.7 153.7 0.3177 0.3164 0.3158 03151 03145 169.0 169.1 169.2 169.3 169.4 03451 03441 0.3431 0.3421 0.3411 40.4 136.9 0.0851 0.2791 153.7 03138 169.5 03401 41.0 136.8 0.0862 0.2783 153.7 0.3135 169.5 0.3396 41.7 136.7 0.0874 0.2776 153.7 03132 169.6 03391 42.3 136.5 0.0887 0.2768 153.7 03127 169.6 03386 42.9 136.3 0.0899 0.2761 153.7 0.3122 169.7 03381 44.3 136.1 0.0924 0.2745 153.7 03112 169.8 03371 45.6 135.7 0.0950 05730 153.7 03101 169.9 03362 47.0 135.4 0.0975 0.2714 1S3.7 03091 170.0 03352 48.4 135.0 0.1000 0.2699 153.7 0.3081 170.1 0.3342 49.8 1345 0.1027 0.2681 153.7 03069 170.2 0.3333 51.2 133.9 0.1054 0.2663 153.7 0.3057 1703 03324 52.6 133.4 0.1081 05644 153.7 03046 170.5 03315 54.0 132.7 0.1108 0.2626 153.7 0.3034 170.6 03306 55.5 132.1 0.1135 05608 153.7 03022 170.7 03297 57.0 131.3 0.1164 05584 153.7 0.3012 170.8 03289 58.6 130.6 0.1194 0.2560 153.7 0.3002 170.9 03281 60.2 129.7 0.1223 0.2535 153.7 0.2991 171.0 03273 61.9 128.7 0.1253 05511 153.7 0.2981 171.1 03265 63.7 127.5 0.1282 05487 153.7 0.2971 171.2 03257 65.5 126.0 0.1321 05450 153.7 0.2962 1713 0.3250 67.3 1245 0.1360 05414 153.7 0.2953 171.4 0.3242 69.4 122.8 0.1398 0.2377 153.7 0.2945 171.5 03235 71.6 120.9 0.1437 0.2341 153.7 0.2936 171.6 03227 73.9 118.7 0.1476 0.2304 153.7 0.2927 171.7 0.3220 76.4 116.6 0.1578 05195 153.7 0.2920 173.8 03215 79.4 83.3 97.0 113.9 110.4 97.0 0.1679 0.1781 0.1880 05087 0.1978 0.1880 153.7 153.7 153.7 0.2914 0.2907 0.2901 176.0 178.2 180.1 03209 0.3204 03199 Note: Sp. En. = Specific Enthalpy. sub-cooled refrigerant can be taken as equal to the values read from the tables for a saturated liquid at the same temperature. Thus if F-12 at 121 psia and 40 F is passing through a pipe, its volume and enthalpy can be determined from Table 1 as 0.0116 cu ft per pound and 17.0 Btu per pound. Frequently it is necessary to determine the properties of a wet vapor or of a mixture of liquid with some added vapor, such as is found at discharge from an expansion valve. This can be done from the tables by noting that the specific enthalpy of the mixture must be equal to that of the saturated liquid plus a fraction of the latent heat of vaporiza tion equal to the fraction of refrigerant which is present in vapor form. 686 CHAPTER 39 1946 Guide Table 6. Properties of Monofloorotrichlorombthane (F-ll) Tekp. F rass. La psa Sq Ik. Liquid Vapor SpEcxrtc Enthalpy and Entbopt Taksn Fro* --40 F Specific Enthalpy Entropy 25 F Superheat 50 F Superheat liquid Vapor liquid Vapor Sp. En. Entropy Sp. En. Entropy 0 5 10 IS 20 25 30 35 40 45 50 55 60 65 70 75 80 85 90 95 100 - 105 2.59 0.01020 13.700 2.96 0.01024 12.100 3.38 0.01028 10.700 .3.85 0.01032 9.530 4.36 0.01036 8.490 4.94 0.01040 7.580 7.81 8.81 9.82 10.80 11.90 12.90 90.4 0.0178 0.1975 91.2 0.0200 0.1974 92.0 0.0222 0.1973 92.8 0.0243 0.1971 93.7 0.0264 0.1970 94.5 0.0286 0.1969 93.9 0.2049 97.4 0.2120 94.7 0.2047 98.2 0.2117 95.5 0.2045 99.0 0.2114 96.3 0.2043 99.8 0.2111 97.2 0.2041 100:7 0.2109 98.0 0.2039 101.5 0.2107 5.57 0.01045 6.27 0.01049 7.03 0.01053 7.88 0.01057 8.79 0.01062 6.770 6.080 5.460 4.920 4.440 13.90 14.90 16.00 17.00 18.10 95.3 0.0307 0.1969 98.8 0.2038 102.3 0.2105 96.1 0.0328 0.1968 99.6 0.2037 103.1 0.2103 96.8 0.0349 0.1968 100.3 0.2036 103.8 0.2101 97.6 0.0370 0.1967 101.1 0.2035 104.6 0.2099 98.4 0.0391 0.1967 101.9 0.2034 105.4 0.2098 9.80 0.01066 10.90 0.01071 12.10 0.01076 13.40 0.01081 14.80 0.01086 4.020 3.640 3.300 3.000 2.740 19.10 99.2 0.0412 0.1967 102.7 0.2033 106.2 0.2097 20.20 100.0 0.0432 0.1967 103.5 0.2033 107.0 0.2096 21.30 100.8 0.0453 0.1967 104.3 0.2032 107.8 0.2094 22.40 101.5 0.0473 0.1967 105.0 0.2032 108.5 0.2093 23.50 102.2 0.0493 0.1967 105.7 0.2031 109.2 0.2092 16.30 0.01091 17.90 0.01096 19.70 0.01101 21.60 0.01106 23.60 0.01111 25.90 0.01116 2.500 2.280 2.090 1.918 1.761 1.620 24.50 25.60 26.70 27.80 28.90 30.10 102.9 0.0513 0.1966 106.4 0.2030 109.9 0.2090 103.6 0.0533 0.1966 107.1 0.2029 110.6 0.2089 104.4 0.0553 0.1966 107.9 0.2028 111.4 0.2088 105.1 0.0573 0.1966 108.6 0.2028 112.1 0.2087 105.7 0.0593 0.1965 109.2 0.2027 112.7 0.2085 106.4 0.0613 0.1965 109.9 0.2026 113.4 0.2084 Note: Sp. En. -- Specific Enthalpy. Table 7. Properties of Water Trap. F rasas. Lb FEB Sq In. liquid Vapor Specific Enthalpt and Entbopt Taken From +32 F Specific Enthalpy Entropy 50 F Superheat 100 F Superheat liquid Vapor liquid Vapor Sp. En. Entropy Sp. F.n, .Entropy 32 0.0887 q.01602 3296.0 0.00 1073.0 0.0000 2.1826 1096.9 2.2277 1120.8 2.2688 35 0.1000 0.01602 2941.0 3.02 1074.4 0.0062 2.1724 1098.3 2.2172 1122.2 2.2581 40 0.1217 0.01602 2441.0 8.05 1076.8 0.0163 2.1555 1100.6 2.2000 1124.5 2.2406 45 0.1475 0.01602 2034.0 13.07 1079.2 0.0262 2.1390 1102.9 2.1832 1126.7 2.2234 SO 0.1780 0.01602 1702.0 18.08 1081.5 0.0361 2.1230 1105.2 2.1667 1129.0 2.2066 55 0.2140 0.01603 1430.0 23.08 1083.9 0.0459 2.1073 1107.5 2.1506 1131.3 2.1902 60 0.2561 0.01603 1206.0 28.08 1086.2 0.0556 2.0920 1109.8 2.1349 1133.5 2.1742 65 0.3054 0.01604 1021.0 33.08 1088.6 0.0652 2.0771 1112.2 2.1196 1135.8 2.1585 70 0.3628 0.01605 868.0 38.07 1090.9 0.0746 2.0625 1114.5 2.1046 1138.1 2.1432 75 0.4295 0.01606 740.0 43.06 1093.2 0.0840 2.0483 1116.7 2.0900 1140.3 2.1283 80 85 90 95 100 105- 0.507 0.596 0.698 0.815 0.949 1.101 0.01607 0.01609 0.01610 0.01612 0.01613 0.01615 632.9 543.3 467.9 404.2 350.3 304.4 48.05 1095.5 0.0933 2.0344 1119.0 2.0758 1142.5 2.1138 53.04 1097.8 0.1025 2.0208 1121.2 2.0619 1144.7 2.0996 58.03 1100.0 0.1116 2.0075 1123.4 2.0483 1146.8 2.0857 63.01 1102.3 0.1206 1.9946 1125.6 2.0350 1148.9 2.0721 68.00 1104.6 0.1296 1.9819 1127.9 2.0220 1151.1 2.0588 72.98 1106.8 0.1384 1.9695 1130.2 2.0093 1153.2 2.0458 Noth: Sp. En. =* Specific Enthalpy. Refrigeration 687 ' Consider, for example, F-12 with a quality (the per cent in vapor form) of 30 per cent; the specific enthalpy of this material would be equal to: km = hi + 0.30 (Av - hi) (2) where km = specific enthalpy of the mixture. hi = specific enthalpy of the liquid. hv = specific enthalpy of the saturated vapor. Values of hi and hv are obtained from Table 1 for the actual pressure of the mixture. . By a reversal of this same procedure the tabular data can be used to determine .the state of a mixture leaving an expansion valve. Consider a valve to which saturated liquid at pressure p,, is admitted and a mixture of saturated liquid and vapor at pressure pi is discharged. The quality of the material at discharge is then determined by making use of the fact that the expansion process is completly irreversible, is a throttling process, and hence occurs without change in enthalpy. Thus the enthalpy of the mixture, hm, is equal to the enthalpy of the saturated liquid at the entrance state, his, and can therefore be read from the table. Thus, or, where his = hm = hvi -- (1 -- x) (Avd -- Aid) - * = (Am - Aid) + (hvi -- Aid) . Ab = specific enthalpy of saturated liquid at entrance to expansion valve. Am = specific enthalpy of mixture. Avd = specific enthalpy of saturated vapor at discharge. Aid = specific enthalpy of liquid at discharge. x = proportion of liquid in the mixture. (3) (4) . The refrigerant cycle is the series of state changes which occur in the conditioning processes needed to restore the refrigerant to a condition in which it will possess the ability to extract heat from the space to be cooled. For all compression-type systems the cycle consists of four processes: heat gain in the evaporator; pressure rise in the compressor; heat loss in the condenser; pressure loss in the expansion valve. The compression process is accomplished at the expense of energy added to the compressor in the form of shaft work and the expansion process could be carried out, if the economics of the system would permit, in an expanding engine with consequent release of energy as shaft work. In ordinary systems, however, the additional first cost and maintenance costs of an expanding engine so greatly exceed the advantage resulting from the work realized that such engines are not used and the pressure reduction is allowed to occur irreversibly in an expansion valve. Basic ally, then, a refrigeration cycle consists of two heat transfer processes and two pressure change processes, no work entering into the heat transfer processes and--in. the simple cycle--no heat transfer occurring during the pressure-change processes. ' Simple Refrigeration Cycles The most common and least complicated type of refrigeration cycle is shown in Fig. 1 and is called the simple saturation cycle. For this system saturated vapor flows without gain or loss of heat from the 688 CHAPTER 39 1946 Guide evaporator to the suction of the compressor. During passage through the compressor the energy added as shaft work goes entirely to increase the enthalpy of the refrigerant and the compression process, which is assumed to occur irreversibly and without external heat transfer, is characterized by constant entropy. Thus the state of the superheated vapor leaving the compressor can be determined from the tables of thermodynamic properties by noting the discharge pressure and fixing also the entropy of the saturated vapor at entrance to the compressor. Superheated vapor from the compressor flows to the condenser where desuperheating and condensation take place. From the condenser the refrigerant flows to the expansion valve, undergoes a constant-enthalpy pressure reduction and returns to the evaporator where it again removes a quantity of undesired heat. When the evaporator is arranged to permit direct cooling of room air by the refrigerant, the system is said to be Heat of Compression Added to Gas of the direct expansion type, while a system in which the evaporating refrigerant cools water or brine, which in turn cools the air, is said to be indirect. Although many differences exist between most actual systems and that of the simple saturation cycle this latter is nonetheless of great value in that it provides an extremely simple method of rapidly achieving an approximate analysis of probable power requirements, compressor size, etc. Further, the equations used in analysis of a simple saturation cycle form the basis of the more complex treatments required for com pound refrigeration cycles. For these reasons a typical simple saturation problem will be worked in detail. ' Example 1. A simple saturation cycle carries a 7 ton load when operating between suction and discharge pressures of 52.7 psia and 121 psia with F-12 as the refrigerant. Determine: (a) the cooling effect provided by each pound of refrigerant, (A) the refrig erant circulating rate, (c) the horse power required, (d) the quantity of heat to be dis` sipated from the condenser, (e) the required condenser cooling water, in gallons per minute, if temperature rise of water passing through the condenser is 8 deg, (f) the bore and stroke of a double acting cylinder (neglecting the effect of the piston rod) if speed of compressor is 500 revolutions per minute. Solution, (a) Saturated liquid F-12 at 121 psia leaves the condenser and enters the expansion valve. The enthalpy of this material (from Table 1) is 29.68 Btu per pound and this must also be its enthalpy at entrance to the evaporator. Leaving the evaporator as a saturated vapor at 52.7 psia, its enthalpy is 82.82 so the refrigerating effect must be 82.82 -- 29.68 = 53.14 Btu per pound. Refrigeration_____________ ;|689 (A) The refrigerant circulating rate is equal to the total heat to be picked up in unit time divided by the pick-up per pound of refrigerant or, ' Wr = (7 ton X 200) -s- 53.14 = 26.3 lb per minute. (c) The horse power required is equal to the increase in energy of the refrigerant passing through the compressor (expressed in Btu per minute) divided by the conversion factor 42.42, which is the number of Btu per minute corresponding to 1 hp, - (hp) '= Wr (Ad - Avs) 4- 42.42 where hp = horse power. Wr = refrigerant circulating rate in pounds per minute. Ad = specific enthalpy of vapor at condition of discharge from compressor. Avs = specific enthalpy of saturated.vapor entering compressor. (5) Wr is known from (A) and AVs is the enthalpy of refrigerant as it enters the compressor in a saturated vapor state at 52.7 psia; thus Avs = 82.82. In order to determine Ad, the state of the refrigerant must first be determined at the compressor discharge. At the known suction state the entropy (from Table 1 for satu rated vapor at 52.7 psia) is 0.16828 and, since the compression is assumed to occur isentropically, it therefore follows that the discharge state must have the same entropy at 121 psia. From the table the entropy of vapor superheated 25 deg is 0.17330, so the superheat, tsd, possessed by the actual gas discharged from this, compressor can be obtained by interpolation as, - sd 0.16828 - 0.16608 25 0.17330 - 0.16608 from which /gd = 7.6 deg. As the saturation temperature at 121 psia is 94 F the actual temperature, Id, of the vapor leaving the compressor is, <d = 94 + tsd 5=5 94 + 7.6 = 101.6 F. By the same kind of interpolation the enthalpy of the discharged vapor can be determined from the enthal pies given for vapor superheated 25 F and for saturated vapor, . (Ad - 88.10) (0.16828 - 0.16608) - . (92.16 - 88.10) (0.17330 - 0.16608) from which, Ad = 89.34 Btu per pound. Then substituting into Equation 5, . . (hp) = 26.3 (89.34 - 82.82) -h 42.42 = 4.03 (d) The rate of heat loss from the condenser, Qc, must be equal to the sum of the energies picked up by the refrigerant in the evaporator and the compressor, Qc = 53.14 + (89.34 r 82.82) - 53.14 .+ 6.52 = 59.66 Btu per pound or 26.3 X 59.66 = 1569 Btu per minute. This same figure can, of course, be determined more directly by subtraction of the enthalpy of liquid leaving the condenser from the enthalpy of superheated vapor going into it, thus, . Qc = 26.3 (89.34 -- 29.68) = 1569 Btu per minute. ' (e) The cooling water rate (based on a gallon as 8.34 lb) is 1569 h- (8 X .8.34) = 23.5 gpm., (/) The compressor size is fixed by the volume of gas which must be drawn into the machine per unit time. Saturated vapor at 52.7 psia has a specific volume, from Table 1, of 0.779 cu ft per pound, hence 26.3 X 0.779 = 20.49 cfm of gas must be handled. Assuming a volumetric efficiency of 90 per cent the compressor must then displace 20.49 -5- 0.9 = 22.8 cfm. The speed is given as 500 rpm and as the unit is known to be double-acting the displacement is therefore (22.8 X 1728) t (2 X 500) = 39.4 cu in. If the unit were designed so that bore, d, and stroke were the same, M3) r4 = 39.4 d = 3.69 in. 690 CHAPTER 39 1946 Guide Coefficient of Performance -. In order to permit evaluation of the effectiveness with which any given cycle operates, some term is desirable which would be comparable to the efficiency that is used for heat engines. In refrigeration the desired effect is heat extraction and the cost of achieving this extraction is the amount of energy which must be supplied as shaft work. Thus the ratio of refrigerating effect to the heat equivalent of the compressor work is used as a measure of effectiveness and is defined as the coefficient of per formance, thus, (cop) = (hvs - Aic) (Ad -- Avs) where ' cop = coefficient of performance. Ava = specific enthalpy of saturated vapor entering compressor. Aic -- specific enthalpy of liquid at discharge-from condenser. Ad = specific enthalpy of vapor at discharge from compressor. (6) The subscripts vs, d, and lc represent state points at suction and discharge of the compressor and at discharge from the condenser. Thus for the conditions of the simple saturation cycle which was used in Ex ample 1. ' (cop) =. (82.82 - 29.68) -5- (89.34 - 82.82) = 8.17. . This coefficient can be compared with that which would exist if the system were to operate on an ideal Carnot cycle for which the coefficient of performance would be, ' ^p) = rc where Ta = evaporator temperature, Fahrenheit degrees, absolute. Tc = condenser temperature, Fahrenheit degrees, absolute. In problem 1, Ta = 501 F (which is 41 F + 460) and Tc = 554 F (which is 94 F + 460) and, . (C0P) = (554 -- 501) = 96 The actual cycle is therefore 8.17 -5- 9.6 or 85 per cent as effective as a Carnot cycle between the same temperature limits. . Influence of Suction Pressure ' Brief consideration of the analytical procedure used in discussion of the simple saturation cycle will bring out the need for maintaining the suction pressure on any refrigeration system as high as the load will permit. As the suction pressure increases, for fixed discharge pressure, the enthalpy of refrigerant entering the evaporator remains unchanged, but the leaving enthalpy increases and hence the refrigerating effect increases. Further, compressor energy input is reduced not merely because of the greater enthalpy of the gas at suction, but also because of a reduction in the enthalpy of the superheated gas at discharge.. Since the refrigerating effect is greater and the work less, it is obvious that there will be a substantial gain in the coefficient of performance. The actual value of suction pressure on any system is obviously determined by the required temperature which must be maintained in Refrigeration -_____________________ -|691 the conditioned space. For a direct expansion system, the evaporator can be held at a temperature not much less than that of the conditioned enclosure except in cases where lower temperatures may be needed in order to establish a desired ratio of dehumidifying to cooling load. When dehumidification requirements dictate the use of unusually low evaporator temperatures the increased operating cost should properly.be charged against the dehumidification rather than the sensible cooling. ' Influence of Discharge Pressure In contrast to the suction pressure, the compressor discharge pressure should be kept as low as operating conditions will allow. This pressure must be high enough to provide a saturation temperature of refrigerant within the condenser which is greater than the exit temperature of the cooling water. The discharge pressure therefore is a direct function of the temperature of the cooling fluid and will automatically rise whenever the temperature of cooling water (or air) rises; it will also rise when the flow rate of the cooling medium is decreased. Increase in discharge pressure (for fixed suction pressure) raises the enthalpy of the gas leaving the compressor, hence increases the work of compression. Further, the enthalpy of saturated liquid leaving the condenser increased with pressure so the refrigerating effect must de crease. Thus the effect of such a pressure rise is to require more work per pound of refrigerant handled and at the same time to necessitate an increase in the refrigerant flow rate. Influence of Water Jacket . The preceding discussion has, in every case, assumed isentropic com pression. Where exact performance data are not available this assumption is a desirable one since it leads to a conservatively large determination of the power required. In most actual systems the compression process departs from isentropic due to irreversible heat transfers which occur between the vapor in the cylinder and the cylinder wall and also because of intentional heat dissipation from the outside of the cylinder walls to the surroundings,, or to a cooling fluid passing through a water jacket around the cylinder. ' Exact measurement of the heat carried away in the jacket cooling water requires facilities which frequently are not available on field installations, but a reasonable close approximation to both the heat loss and the work requirement can be obtained from theory, providing the temperature of the gas leaving the compressor is experimentally determined. Knowing the temperature and pressure at both suction and discharge, the actual state points can be readily determined from the tables of refrigerant properties and the entropies and enthalpies thereby evaluated. Then the energy dissipation to cooling water can be calculated approximately from the equation, Qj = WT (As) Favg . (7) where Qj = energy dissipated to cooling water, Btu per minute. Wt ~ weight of refrigerant, pounds per. minute. As = entropy change between suction and discharge. 7avg -- average temperature of gas passing through compressor, Fahrenheit degrees, absolute. 692 CHAPTER 39 1946 Guide The work of (Compression is then given by the equation: . (hp) = lWr(hi - hve) + Q,] ~ 42.42 where hp -- horsepower. Ad = specific enthalpy of vapor at compressor discharge. Avs = specific enthalpy of saturated vapor entering compressor. (8) From the form of Equation 8 it would appear that an increase in the energy loss to the jacket would result in a greater power requirement since the Qj term is additive; actually, however, computation will readily show that the effect of an increase in the Qj term is to decrease the horse power since the rate of decrease of enthalpy difference will, in every case, exceed the increase in heat loss. Thus compressor cooling is highly desirable as'a method of reducing power consumption. Influence of Superheating and Subcooling The most common departure from conditions of the simple saturation cycle is that resulting from admission of superheated vapor to the com pressor. Thermodynamically, superheat is undesirable since the enthalpy increase required to compress a vapor through a given pressure range increases with superheat. Further, superheated vapor leaving an evapo rator is usually an indication that the suction pressure is lower than necessary. Under practical operating conditions, however, superheat is almost universally used as a means of assuring complete vaporization of the refrigerant going to the compressor. With modern compressors operating at high speed and with relatively small''clearance space it is particularly necessary to avoid admission through the suction valves of liquid refrigerant. Another common departure of actual systems from the simple satu ration cycle occurs because of subcooling of refrigerant in the condenser. Thermodynamically such subcooling is advantageous since it increases the refrigerating effect without affecting the unit energy requirements of the compressor. Further, it can be shown that for a fixed ratio of condenser cooling water to refrigerant circulating rate the total compres sor power requirements will be greater when operating simple saturation than when operating with maximum sub-cooling. What is even more surprizing is that the condenser pressure is lower for the sub-cooling cycle than for the saturation cycle; this condition results from the fact that, for the same load, the refrigerant flow rate is less when there is sub-cooling. . '. Because of the advantages attendant upon the use of sub-cooling, many methods are in use for obtaining some sub-cooling effect outside of the condenser. One common procedure is to use the cold vapor leaving the evaporator to cool the liquid flowing from condenser to expansion valve. In this case subcooling is realized at the expense of superheating the suction vapor and thermodynamic analysis will show at once that a definite loss will accrue. The only conditions under which such a system can be justified are those for which the vapor would, in any event, pick up a comparable degree of superheat while en route to the compressor; in this event the deliberate superheating, with useful subcooling as a result, is preferable to the useless superheating which would otherwise occur. In small compressors having large surface area in relation to volume, a definite gain is usually accomplished by such interchange, because for such units there would be considerable heating in any event. On very Refrigeration 693 large compressors the loss in volumetric efficiency would more than offset any gain, and the capacity would be reduced. Somewhere between these two extremes, the exact point depending on the type of compressor, location of valves, etc., the two factors would offset one-another. Another somewhat unusual subcooling cycle allows cold refrigerant from the downstream side of the expansion valve to cool liquid refrigerant from the condenser down to the evaporator temperature. In such a case the expansion valve becomes a simple pressure-reducing valve since there is no vapor formation--hence no expansion--during passage of the liquid refrigerant through it. This system is theoretically identical; from the standpoint of thermodynamic effectiveness, with the simple saturation cycle. Clearance and Conventional Volumetric Efficiency Clearance, like displacement, is a characteristic--usually fixed--of a given compressor. In some cases clearance pockets are provided which place within the operator's control the ability to alter the clearance of the machine, but most moderate size compressors are built with fixed clearance. By definition the clearance is the percentage of the volume swept by the piston which is represented by spaces in the end of the cylinder (including valve spaces, etc.) when the piston is at the end of its stroke. Because of the trapping of high pressure vapor in the clearance space, and its subsequent re-expansion, the suction valves of the compressor do not open until the piston has completed part of its stroke. Hence the volume of fresh vapor introduced into the compressor per stroke is less than the volume swept by the piston. The ratio of actual volume of fresh gas to swept volume is, by definition, the conventional volumetric efficiency, CVE. In equation form, (CVE) = 100 - Vc - l] (9) where CVE = conventional volumetric efficiency. Vc -- clearance, per cent of volume swept by piston, which is contained in spaces at end of cylinder when piston is at end of stroke ^clearance includes valve spaces, etc.) _ va ~ specific volume of gas at compressor inlet. ', specific volume of gas at compressor discharge; Values of v,, and va can be obtained directly or by calculation from the tables of properties of refrigerants. Influence of Wiredrawing and of Piping Losses The pressure drop which occurs during passage of the refrigerant through suction and discharge valves of the compressor is known as wire drawing. Its effect Is equivalent to that of a reduction in the evaporator pressure (but without the disadvantage of reduced refrigerating effect) and an increase in condenser pressure, hence is undesirable. In analyzing a cycle, wiredrawing can be taken into account since it amounts to the interposition of a small expansion valve between the state point of vapor leaving the evaporator and that of vapor at start of the compression process; a similar equivalent valve can be considered as interposed at the end of the compression process and before the state point corre sponding to the condition of the superheated vapor in the discharge line. 694 CHAPTER 39 1946 Guide In exactly the same way representation on the ideal cycle can be given to the pressure losses that occur in the connecting piping. In each case the entire loss of a given line can be treated as though it occurred during passage through an equivalent expansion (or pressure reducing) valve located at any convenient place in the line. Data to permit evaluation of line losses are given in a subsequent section of this chapter. ' Complex Refrigeration Cycles The preceding sections have dealt only with refrigeration systems in which there is but one evaporator. When two or more evaporators are required, and the pressures differ in each, much greater opportunity is afforded the engineer for obtaining large economies through selection of : one of the more complex cycles. Consider, for example, the refrigeration requirements of an air conditioning system which is to cool a very large E volume of 90 F outside air down to a conditioned temperature of 40 F. A I simple saturation system, operating with evaporator temperature less than 40 F, would accomplish the desired purpose, but at the expense of i excess power requirements since 50 per cent of the sensible cooling load could instead be handled by an evaporator operating at a temperature I! somewhat less than 65 F. The more effective procedure in this case would J be to place two direct expansion coils in series, the first operating at a temperature less than 65 F and the second, at a temperature below 40 F.1 i In this way approximately one half of the total load would be picked up at 1 the higher evaporator pressure and therefore need be raised through a I much smaller thermal height. The theoretical advantage of such oper ; ation can be visualized from the increase in Carnot effectiveness; assuming 1 that the condenser temperature is 100 F, the coefficient of performance i (cop) of the low temperature evaporator is, (cop) = (35 + 460) ^ (100 - 35) = 7.63 while that of the higher temperature evaporator is, (cop) = (60 + 460) (100 - 60) = 12.97. . Since the load is assumed to be equally distributed between the two evaporators the cop of the series system is the arithmetical average of the values for the two evaporators or, (7.63 + 12.97) -r- 2 = 10.30. Thus use of the series cycle, would afford a theoretical saving in power of approxi mately one third. One common fallacy, with respect to complex, systems, is the miscon- . ception that a high evaporator pressure necessarily means a low power requirement. In many instances operating conditions will require use of series evaporators, but in a cycle for which the vapor leaving the higher pressure evaporator must be throttled to the pressure of the low pressure evaporator before entering the compressor, there obviously is no ad- . vantage resulting from the higher operating pressure of the one evapo rator since the refrigerant which it handles must be compressed through the same lift as though both evaporator pressures were the same. Con sideration of this case brings out the fact that the effectiveness of a -complete cycle depends upon the possibility of operating the system with suction vapor, at different pressures. This can be accomplished through use of more than one compressor, or by means of special individual compressor arrangements which permit use of different suction pressures in the opposite ends of a double-acting machine, or introduction of vapor at two different pressures into the cylinder of a dual-effect compressor. Refrigeration 695 Compound Compression Cycles In large systems the compression process can be carried out in steps as the refrigerant passes through a number of cylinder ends arranged for operation in series. Thermodynamically the advantage of compound compression arises from the fact that intercoolers can be placed between the stages of compression to extract heat from the vapor and thereby cause the over-all compression process to more closely approach the ideal condition of isothermal compression. Essentially, such intercoolers-- whether of the water or the flash refrigerant type--serve the same purpose as a cooling jacket, but with greater effectiveness because of the more satisfactory heat transfer conditions. ' Multiple Expansion Valves > In the simple saturation cycle the saturated liquid entering the ex pansion valve commences to vaporize as soon as its pressure starts to drop. ' The vapor produced during the expansion process has no further use, in terms of refrigerating effect, since it. has already picked up its latent heat of vaporization as a result of heat which it has extracted from the unvaporized residue. Thus the instant such vapor forms its usefulness is at an end and to allow such material to undergo a further drop in pressure is uneconomical. Unfortunately, however, there is no effective means of extracting vapor continuously during the expansion and re-compressing it. Thus in the simple cycle the flash vapor must necessarily be allowed to drop to evaporator pressure. When a compound compression cycle is used there is at least one inter mediate pressure at which flash vapor can be extracted. In such cases all refrigerant from the condenser can be dropped through a first expansion valve to the higher suction pressure and the flash vapor then extracted and returned to the compressor. Some of the resultant liquid refrigerant . then passes through the high-pressure evaporator while the remainder proceeds through a second expansion valve in which its pressure is drop ped to the valve corresponding to the low-pressure evaporator. Pipe Sizes and Friction Losses The effect on performance of pressure losses in the piping of a refrigerat- * ing system has already been discussed. In all cases frictional losses should be kept to a minimum and piping should be selected which will give the smallest loss consistent with over-all economy of the system. Actual losses vary, of course, with the physical characteristics of the particular refrigerants, but, by way of example, data will be given for one of the refrigerants, dichlorodifluoromethane (F-12) which finds wide use in air conditioning applications. Tables 8,'9, and 10 give the pressure loss per 100 ft of piping (including an average number of fittings) for oil-free dichlorodifluoromethane; tabular values should be increased if oil is flowing with the refrigerant. For copper pipe the tables are for type L tubing and are based on the outside diameter. Common practice fixes suction line velocities between 1,500 and 3,000 fpm while 2,000 to 3,500 fpm is the accepted range for discharged lines. Velocities higher than those indicated-will result in noisy operation while lower velocity in the suction line may result in- the loss of entrained oil. Refrigeration for air conditioning usually involves wide variation in load, / 496 CHAPTER 39 1946 Guide Table 8. Pressure Losses in Dichlorodifluoromethane Discharge or Hot Gas Lines3 bLcngth of tubing includes the average number of fittings. requiring double suction risers, one large and one small. The large riser should be trapped to insure oil return while the small riser should be sized for a velocity of 3,000 fpm at minimum load; and the large riser then sized to handle the balance of the load at a velocity not less than 2,000 fpm. The total pressure loss in the suction piping, including valve losses, is usually between 2 and 3 psi while hot gas line losses are held to approximately 4 psi and liquid line losses are not greater than 5 psi. As protection against re-condensation on the cylinder head of the compressor, a surge drum is sometimes installed' in the discharge line close to the compressor; this protection is especially desirable on systems' using evaporative condensers where sun effect during shut-down may be serious. . ,, The Steam Jet Srstem ' The steam jet system under certain circumstances is desirable for use in air conditioning *. Steam supplies directly the power used for com pressing the refrigerant, thus eliminating the losses connected with other methods of supplying energy.. As the compression ratio between the evaporator and condenser under normal circumstances is large, the mechanical efficiency of the equipment is somewhat lower than that of the positive mechanical type compressor. The condensing water require ments are considerably greater, as both the refrigerant and the impelling steam must be condensed. Refrigeration 697 Table 9. Pressure Losses in Dichlorodifluoromethane Liquid Refrigerant Likes Capacity Btu per Hour Pressure Drop in Pounds per Square Inch per 100 Fra Pipe Sizes. Inches H m 1H lH 100,000 125.000 150.000 175,000 . 200,000 - 0.6 0.9 1.3 1.8 . 2.3 0.6 225.000 250.000 275,000 300,000 325,000 ' 2.9 3.6 4.3 5.1 5.9 0.8 1.0 1.2 1.4 1.6 . 350.000 375.000 400.000 450.000 500,000 6.9 1.8 7.9 2.1 9.0 2.3 0.8 2.9 1.0 3.5 1.3 550.000 600.000 700,000 800,000 900,000 1,000.000 1.200,000 1,400,000 1.600,000 "_ 4.3 1.5 5.0 1.8 6.7 2.4 8.7 3.1 3.9 0.7 0.8 1.1 1.4 1.7 4.7 2.1 6.7 3.0 9.0 4.0 5.1 1,800.000 2,000.000 2.200.000 6.3 7.9 9.2 "Length of tubing indudes the average number of fittings. The steam jet system functions on the principle that water under high vacuum will vaporize at low temperatures. Steam jet boosters or com pressors of the type commonly used in power plants for various processes will produce the necessary low absolute pressure to cause evaporation of the water. , A diagrammatic representation of a typical steam ejector water cooling system is shown in Fig. 2. The figures correspond to an average repre sentative system. The water to be cooled enters the evaporator and is cooled to a temperature corresponding to the vacuum maintained. Because of the high vacuum, a small amount of the water introduced in the evaporator is flashed into steam. As this requires heat, and the only source of heat is the rest of the water in the evaporator tank, this other water is almost instantly cooled to a temperature corresponding to the boiling point determined by the vacuum maintained. The amount of water flashed into steam is a small percentage of the total water circu lated through the evaporator, amounting to approximately li lb per hour per ton of refrigeration developed. The remainder of the water at the desired low temperature is pumped out of the evaporator and used at the point where it is required. The ejector compresses the vapor which has been flashed in the evapor ator, plus any.entrained air taken from the circulated water, to a some what higher absolute pressure and the vapor and air mix with the impel- 698 CHAPTER 39 1946 Guide. Table 10. Pressure Losses in Dichlorodifluorombthane Suction Refrigerant Lines . Copper Pipe Actual O.D. Inches Capacity Btu per Hour Pressure Drop in Pounds per Square Inch per 100 Fts Refrigerant Temperature F Deg -10 0 10 20 30 40 50 2.000 4.000 6.000 8.000 10.000 0.3 0.3 0.2 0.2 0.2 0.1 0.1 1.3 1.0 0.8 0.7 0.6 0.5 0.4 2.8 2.2 1.8 1.5 1.2 1.0 0.9 4.8 3.8 3.1 2.6 2.1 1.8 1.5 7.4 5.8 4.8 3.9 3.3 v 2.8 2.3 12.000 14.000 16.000 18.000 20.000 10.5 14.0 8.4 11.0 14.5 6.8 9.1 12.0 15.0 5.6 7.6 9.8 12.3 . 15.0 4.7 6.4 8.3 10.4 12.7 4.0 5.4 7.0 8.7 . 10.7 3.3 4.5 5.8 7.2 8.9 7.000 0.4 0.3 0.3 . 0.2 0.2 0.2 0.1 10.000 1.0 0.7 0.5 0.5 0.4 . 0.3 0.3 16.000 1.9 1.5 1.2 1.0 0.8 0.7 0.6 20.000 3.3 2.6 2.1 1.7 1.4 1.2 1.0 m 26.000 5.0 4.0 3.2 2.7 2.2 1.9 1.6 36.000 45.000 60.000 70.000 9.7 15.8 7.7 12.6 6.2 10.0 5.1 8.4 14.8 ' 4.3 7.0 12.2 3.6 5.9 10.2 14.0 3.0 4.9 8.6 11.7 10.000 0.3 0.2 0.2 0.2 0.1 0.1 0.1 15.000 0.7 0.5 0.4 0.3 0.3 0.2 0.2 20.000 1.2 0.9 0.7 0.6 0.5 0.4 0.4 30.000 2.6 2.1 1.6 1.3 1.1 0.9 0.8 1M 40.000 4.6 3.6 2.8 2.3 1.9 1.6 1.4 50.000 7.0 5.5 4.4 3.5 2.9 2.5 2.1 60.000 10.0 7.8 6.2 5.0 , 4.2 3.5 3.0 80.000 14.0 11.0 8.7 4 7.3 6.2 5.2 100.000 13.5 11.3 9.5 8.2 30.000 40.000 50.000 60.000 70.000 1.6 1.3 1.0 0.8 0.7 0.6 0.5 2.7 2.1 1.7 1.4 1.1 0.9 0.8 4.2 3.2 2.5 2.1 1.7 1.4 1.2 6.1 4.5 3.6 2.9 2.4 2.0 1.7 8.7 6.3 4.8 3.8 3.1 2.6 2.2 80.000 90.000 100.000 120.000 140.000 8.4 6.3 4.9 4.0 . 3.3 2.8 8.0 6.2 4.9 4.1 3.5 , 10.0 7.6 6.1 5.0 4.2 8.6 7.0 . 5.9 9.5 7.9 50.000 0.7 0.5 0.4 0.3 0.3 0J2 0.2 100.000 2.6 1.8 1.4 1.1 0.9 0.8 0.7 150.000 5.6 3.9 3.0 2.4 2.0 1.6 1.4 200.000 9.8 6.7 5.2 4.1 3.4 2.8 2.4 2H 250.000 14.8 10.3 8.0 6.3 5.1 4.2 3.6 300.000 14.5 11.3 9.0 7.2 6.0 5.0 350.000 19.5 15.3 12.0 9.7 7.8 6.7 400.000 19.6 15.3 12.5 10.0 8.5 aLength of tubing includes the average number of fittings. ling steam on the discharge side of the jet. The total mixture then passes from the ejector into the condenser. ' The slight amount of air which may be entrained in the cooled water is removed by a small secondary ejector which raises the pressure suffi ciently so that the air can be discharged to the atmosphere. A secondary condenser is then necessary to condense the steam in the secondary jet. While a single booster of smaller than 15 tons capacity is difficult to build, steam' jet vacuum cooling units have been.built for as small as 5 to 6 tons capacity. They can readily be built for steam pressures of from 5 to 200 lb per square inch and- condenser water temperatures as high as Refrigeration 699 Table 10. Pressure Losses in Dichlorodifluoromethane Suction Refrigerant Lines (Concluded) Copper Pipe Actual O.D. Inches Capacity Btu per Hour 50.000 100.000 150.000 200.000 250.000 m 300.000 350.000 400.000 450.000 500,000 550.000 600.000 Pressure Drop in Pounds per Square Inch per 100 Fra Refrigerant Temperature Deg F -10 0 10 20 30 40 50 0.2 0.2 0.1 0.1 0.1 0.1 0.1 0.7 0.6 0.5 0.4 0.3 0.2 0.2 1.6 1.2 1.0 0.8 0.6 0.5 0.4 2.8 2.1 1.7 1.4 1.1 0.9 0.7 4.3 3.4 2.6 2.1 1.7 1.3 1.1 6.1 4.5 3.7 3.0 2.4 1.9 1.5 8.2 6.0 5.0 4.0 3.2 2.5 2.0 7.8 6.5 5.1 4.2 3.3 2.7 7.7 6.4 5.3 4.0 3.5 7.8 6.4 5.0 4.2 7.7 6.2 5.1 7.4 6.2 . 200.000 1.2 1.0 0.8 0.6 0.5 0.4 0.4 300.000 2.6 2.0 1.6 1.3 1.0 0.8 0.7 400.000 4.5 3.4 2.6 2.1 1.7 1.4 1.3' 500.000 7.3 5.4 4.1 3.3 2.7 2.2 1.9 3H 600.000 8.1 6.0 4.7 3.8 3.1 2.7 700,000 800.000 900.000 1,000.000 8.4 6.5 5.2 4.2 3.5 8.6 6.8 5.5 4.6 8.7 7.0 5.9 8.9 7.3 ' 3H 300.000 400.000 500.000 600.000 700,000 800.000 900.000 1,000.000 1,100.000 1,200.000 1,300,000 1,400.000 1.2 0.9 0.7 0.6 0.5 0.4 0.3 2.0 1.6 1.3 1.0 0.8 0.7 0.6 3.2 2.5 1.9 1.6 1.3 1JO 0.9 4.6 3.6 2.8 2J2 1.8 1.5 1.3 6.4 4.9 3.8 3.0 2.5 2.0 1.7 8.7 6.4 4.9 3.9 3.2 2.6 2.2 8.2 6.2 4.9 3.9 3.2 2.7 7.7 6.1 4.9 4.0 3.3 9-4 7.3 5.8 4.8 4.0 8.7 6.9 5.6 4.8 8.0 6.6 5.6 9.3 7.6 6.4 400.000 600,000 800.000 1.000.000 1,200,000 1.400,000 1.600.000 1.800.000 2.000.000 2,200,000 1.0 2.4 4.1 6.6 10.0 0.8 1.8 3.1 4.8 7.1 10.0 0.6 1.4 2.4 3.7 5.4 7.5 10.0 0.4 1.1 2.0 3.0 4.4 5.9 7.7 10.0 0.4 0.9 1.6 2.5 3.5 4.8 6.2 7.9 9.7 0.3 0.3 0.7 0.6 1.3 . 1.1 2.0 1.6 2.9 2.4 . 3.9 3.35.1 . 4.2 6.4 5.3 7.9 6.6 9.5 7.9 aLength of tubing includes the average number of fittings. 90 F. The steam consumption in pounds per hour per ton of refrigeration increases rapidly as the booster steam pressure is lowered. For example, the lowering of the booster steam pressure from 200 to 90 lb per square inch results in an increase in steam consumption of approximately 5 per cent, whereas a further decrease in booster steam pressure to 10 lb per square inch increases the steam consumption by approximately 72 per cent oyer that required at 200 lb per square inch. The capacity of a steam jet system is usually controlled by controlling the number of boosters in use since the unit usually has several boosters operating on the same evaporator. Usually one booster is automatically 700 CHAPTER 39 1946 Guide controlled whereas the others are manually operated. The capacity is dependent, as for all compressors, upon the evaporator temperature, or in other words, the suction pressure. For example,' the capacity is lowered approximately 17 per cent if the evaporator or chilled water temperature is lowered from 50 to 45 F. The capacity therefore can. be controlled to some extent by regulating the evaporator temperature. The Absorption System ' The fundamental rule governing the absorption (in a closed system) of. a gas by a liquid is Raoult's Law, which states that at any given tem perature the ratio of the partial pressure of a volatile component in a solution to the vapor pressure of the pure component at the same tem- Refrigeration 701 weight of absorbent is important because of the heat required to raise the temperature of the mixture and disassociate the refrigerant and the absorbent. Only the latent heat of the refrigerant can be recovered for useful work. Many refrigerant-absorbent combinations have been proposed and quite a number have been tested. A diagrammatic representation of a typical closed absorption system is outlined in Fig. 3. In this system a mixture of refrigerant and absorbent is evaporated in the generator, passes to an analyzer and rectifier where it is purified, and then to a con denser where the refrigerant and remaining absorbent are condensed. It then passes through an expansion valve to an evaporator, where heat is absorbed from a cooling load. From the evaporator the vapor and resi- Fig. 2. Diagrammatic Arrangement of Steam Jet Vacuum Cooling Unit perature is equal to its mol fraction in the solution. The mol fraction in turn is equal to the number of mols of substance divided by the total number of mols present. The number of mols in a given weight of a compound is equal to the weight divided by the molecular weight. This law applies strictly only to what is known as an ideal solution, one in which the inter-molecular forces between the substances present in the solution are equal. Actually, no such solutions exist, so that deviations from Raoult's Law are always found in practice. The deviation is called positive when the observed pressure is greater than that calculated from Raoult's Law, while the term negative deviation refers to the opposite case. Negative deviations are found wherever chemical attraction exists between the solvent and the solute. Positive deviation occurs when there is a difference in the internal pressure of the components, chemical attraction between them being absent. In order to make an effective absorption machine, large negative deviations from Raoult's Law must be shown by solutions of the refrig erant in the liquid absorbent, because the larger the negative deviation, the greater is the amount of refrigerant that can be cycled, using a given weight of absorbent. Cycling a large amount of refrigerant for a given Fig. 3. Closed Absorption System dual absorbent passes to an absorber where it meets absorbent which is initially low (weak) in refrigerant concentration. The absorbent absorbs the vapor and-the strong absorbent liquor is transferred to the generator through an interchanger with the weak liquor returning from the generator. A cooling medium, ordinarily water, is used in the absorber to remove the heat of absorption and maintain the absorptive power of the absorber . at a maximum. 1 Like the steam jet system, the absorption system compares most favorably when a cheap source of cooling water and steam or other heat is available. Unlike the steam jet system, the comparative performance ' is usually best with a wide range of temperature between the evaporator and absorber, since with a good refrigerant-absorbent combination, the amount of heat and water required for a given refrigerating effect in creases slowly with an increase of evaporator-condenser temperature range. At the present time the most used refrigerant-absorbent combinations are: (1) water and ammonia, and (2) dicnloromonofluoromethane and dimethyl ether of tetraethylene glycol. With the latter combination the boiling points of the refrigerant and absorbent are sufficiently wide apart that almost pure refrigerant is obtained without the use of a rectifier. 702 CHAPTER 39 1946 Guide Ice Systems . Cold water systems using ice as the cooling agent have been installed in many theaters, restaurants, funeral homes, churches and other places . where short hours of operation and high peaks of cooling demand make this type of system desirable. A comparatively small quantity of ice in the water cooling tank of such a system can release refrigeration at a relatively rapid rate. For instance, neighborhood theaters having a peak demand of 1,200,000 Btu per hour (100 tons refrigeration) have found 8 ton capacity ice bunkers satisfactory. In operation, the water in the air conditioning system is circulated oyer ice placed in an insulated box and is cooled to the 38 or 40 F range or higher if desired. This cold water is pumped from the ice bunker to air cooling coils or spray type air washers. The blowers, coils, air washer or air handling sections are the same as those parts in any system employing cold water as a refrigerant. The ice water cooler or ice bunker is usually built at the installation in a location where it can easily be iced. It can be constructed of any desired material such'as concrete, steel, or wood with an adequate amount of insulation to save the ice from one period of use to the next. The basic requirement is that the tank be durable and water tight. . A typical bunker with connections to a coil type air conditioning system is shown in Fig. 4: About 60 cu ft of gross bunker volume are allowed per ton of ice capacity. . The shape of the bunker usually conforms to the available space. The one illustrated has overhead sprays, but if head-room is lacking the ice is placed on the floor of the bunker with the water returned around the . lower part of the blocks from a perforated distribution pipe run along one side of the bunker. To secure good circulation the supply water is extracted from a similar perforated pipe on the opposite side of the bunker. The temperature of the water is controlled at a predetermined point by a thermostat in the supply line. If the temperature drops too low, a part of the return water is by-passed directly to the- sump and is n'ot cooled over the ice. In the larger systems it is customary to .install an overflow control which, as the ice melts, discards the excess water through an economizer coil. The surface of the economizer is large in relation to Refrigeration. 703 the flow so that the water is warmed to 60 F or more as it is discharged from the system. Storage Systems In an attempt to lower initial equipment cost and operating expense, or increase the refrigeration capacity of an existing air conditioning system, storage refrigeration has been utilized in a few applications. Some of the methods which have been adopted include the storage of refrigeration in the form of chilled water, chilled brine, ice on evaporator coils2 and the accumulation of thin sheets of ice on copper plates in a steel tank*. If the peak load factor is low as compared with a long period of operation, such as in a restaurant, or if the hours of operation are short but the usage factor high as in a church, then it is possible to con sider storage refrigeration. This method of accumulating refrigeration frequently makes it possible to use low cost off-peak electric power. Power costs may also be reduced by installing a smaller refrigeration plant, augmented by a storage system, and by operating it for longer periods. .- The Reverse Cycle . The reverse cycle--frequently referred to as a heat pump--is identical in theory with the ordinary refrigeration cycle and differs only in the sense that the desired'effect is a heat source rather than a heat sink. Since a condenser delivers more heat than is picked up by the evaporator (it discharges the heat equivalent of work supplied during compression) it follows that the effectiveness of a heat pump, its coefficient of perform ance, is greater than that of a refrigeration cycle operating between the same temperature limits. In heating by the reverse refrigeration cycle energy is absorbed in an evaporator from some available source of heat, pumped to a higher tem perature and delivered to a condenser 4. The heat from the condenser is used for heating purposes. The compressor acts as a heat pump whose fundamental function is to raise the potential of the heat. The theoretical ratio of the heat delivered to the work of compression, the coefficient of performance, is given in Equation 10. where (cop) = lC -- i8 cop = coefficient of performance. r8 = absolute temperature of evaporator. Tc = absolute temperature of condenser. -. (10) Thus; with a small spread of temperature between the evaporator and the condenser, 6 or 8 times as much heat may be obtained theoretically, and 3 to 5 times practically, as the work introduced. There are a number of limitations, however, the most serious of which is the lack of ready availability of a practical source of heat. 1. Well water is the most desirable since its temperature, is higher than other sources even in the winter, and thus a large amount of heat may be removed in relation to the weight of water handled. ' 2. Air may be used but its specific heat is low and its temperature uncertain. When ` the most heat is needed, the temperature of the air is lowest, thus resulting in the least favorable temperature combination. 704 CHAPTER 39 1946 Guide 3. It has been proposed to obtain heat by freezing water but this is still in the experi mental stage. Some of the other factors which act as limitations are: the large tem perature spread when using airasa source of heat and when attempting to cool with even moderately low outside temperatures, the frequent disparity between the size of the cooling load and heating load requiring extra equipment for a complete heating load, and the relatively high initial cost of equipment as compared to that at present available for heating by conventional means. Because of these limitations, the present application of the system is largely limited to temperate climates, such as Florida and Southern California, or to heating only for intermediate seasons, or to other locali ties which have peculiar advantages as, for instance, the ready availability of well water. In these locations it is frequently possible to do all of the heating necessary with the refrigeration equipment so that the extra cost is only that of reversing the functions of the condenser and evaporator. There are a number of reversed systems now in operation, particularly among utility companies, using well water as the source of heat. These systems range in size up to 320 hp. In the case Of the largest system in operation at present, the cost of the electrical energy would have to be approximately 0.7 cents per kilowatthour in order to compete with oil at 6 cents per gallon. A typical arrangement of a reversed cycle conditioning system where air is used as a source of heat is shown in Fig. 5. If the air seldom drops below freezing, heat is often required in the morning and cooling during the afternoon in order to maintain comfortable conditions in such a system. The arrangement as shown lends itself to automatically changing over as required. ' . REFRIGERATION EQUIPMENT AND ARRANGEMENTS Types of Compressors . There are many different types of compressors, using various refrig erants. Each type has its advantages for its particular application, Refrigeration 70S and those generally used for air conditioning are of the following types: 1. Reciprocating compressors (commonly referred to as piston type). 2. Centrifugal compressors. Reciprocating compressors are available in a wide range of sizes and types. Any of a number of refrigerants, including dichlorodifluoromethane (F-12), methyl chloride, ammonia, carbon dioxide, and sulphur dioxide may be used in reciprocating machines. The first of these is used exten sively in direct expansion systems of comfort air conditioning. Compressors may be classified into two general types, (a) open type, (b) enclosed type: If the driving mechanism is external to the compressor, then the shaft must be brought out through the crankcase and a shaft seal or stuffing box must be used to prevent escape of the refrigerant. This type of compressor is known as an open-type compressor. When the driving mechanism is located within the crankcase of the compressor in such a way as to avoid the necessity of a shaft seal, the compressor is known as the completely enclosed or hermetically sealed type. Open-type compressors may be further classified as belt driven and directly connected. A great number of direct-driven units are now being used which generally operate at higher rotational speeds than the beltdriven type. . The present tendency is toward forced lubrication of the bearings of compressors by means of an oil pump driven from the crankshaft, although there are many splash lubricated compressors on the market. The chief advantages of the forced lubricated compressor are that the lubrication system requires less energy for its operation than the splash type, the oil. can be easily filtered before it enters the bearings, and less oil is usually required. The compressor capacity must be selected for and matched to the maximum load for the installation on which it is to be used. Air-con ditioning loads, however, vary over a wide range, and a wide fluctuation in air conditions may result during periods of light load if on-and-off control of full compressor capacity is used. To prevent such undesirable fluctuation, several methods are employed to vary the capacity of reciprocating compressors, such as: . 1. By-passing one or more cylinders, of a multi-cylinder compressor, from discharge to suction. . 2. Rendering the suction valves of one or more cylinders of a multi-cylinder compressor inoperative. This is usually accomplished by depressing the suction valves. 3. Varying the speed of the compressor, usually by using variable speed or two-speed electric motors. 4. Using clearance pockets to control the quantity of refrigerant pumped. 5. Restricting the suction inlet to one or more of the cylinders of a multi-cylinder compressor either by an automatic modulating valve or by an on and off valve. All of these methods, with the exception of variable speed, result in a slightly lowered over-all compressor efficiency when in use, since the mechanical losses remain constant whereas the quantity of refrigerant pumped is lowered. Centrifugal compressors are used with very low pressure refrigerants; usually both evaporator and condenser work below atmospheric pressure. Water and monofluorotrichloromethane (F-ll) are the refrigerants com monly used in centrifugal machines. Compression of the refrigerant is accomplished by means of centrifugal / 706 CHAPTER 39 1946. Guide force; therefore, this type of compressor is inherently suitable for large volumes of refrigerant at low pressure differentials. Two or more stages are usually required and high speeds are necessary to obtain good efficiency. The evaporator is usually constructed as an integral part of the centrif ugal type condensing unit, to chill water which is then circulated to the air conditioning system. This is done because it would not be economical to pipe these large volumes of refrigerant any distance. ' Centrifugal compressors like reciprocating compressors can be divided into two general types, open and enclosed. In general, the open type compressor is geared to the driving mechanism, and operates at higher speed than the driving motor or turbine. A modern completely enclosed direct-driven, centrifugal compressor is illustrated in Fig. 6. The compressor capacity can be varied by controlling the condensing pressure. This is accomplished by regulating the quantity and tem- 2 nd. stage compressor Condenser Refrigeration 707 the different types of compressors is shown in Fig. 8. It may be noted that the power required by the reciprocating compressor increases rapidly with increase in condenser temperature, while the power curve for the centrifugal compressor is relatively flat. It is also evident that the capacity of the steam jet compressor is independent of condenser tem perature until a certain point is reached where it drops to zero. As previously stated, steam jet equipment requires more condensing water than other types of compression systems. Consequently, steam jet 1 st stage compressor Chiller Fig. 6. Enclosed Type Centrifugal Condensing Unit perature of the condenser cooling water. The capacity falls off with increasing condensing pressure. Centrifugal compressors are seldom built for less than 50 tons capacity, since it is not practical to make impellers which pump much less than the volume of refrigerant required for this tonnage. Characteristics of Compression Systems \ The various types of compression systems have quite different charac teristics of capacity and power with varying evaporator and condenser temperatures, as may be noted from curves in Figs. 7 and 8. From Fig. 7 it may be observed that power requirements for the centri fugal compressor increase much more rapidly than for the reciprocating compressor with increase in evaporator temperature. Similarly, the capacities of the steam ejector and centrifugal compressors increase more rapidly than those of the reciprocating compressor with increase in evapor ator temperature. Thus, both the steam jet and centrifugal machines tend to be more self-regulating than the reciprocating. It is also evident from Fig. 7 that the steam jet equipment is best suited for operation at high evaporator temperatures. The effect of condenser temperature upon the power and capacity of Fig. 7. Performance Characteristics of Compression Refrigeration . Machines at Constant Speed . systems are well suited to those applications where condensing water is cheap, or where condensing water is rather high in temperature. Condensers Condensers used for liquifying the refrigerant are of three general de signs: (1) air cooled, (2) water cooled, and (3) evaporative (combination air and water). . 1. Air cooled condensers are seldom used for capacities above 3 tons of refrigeration, unless an adequate water supply is extremely difficult to obtain, as, for instance, in railway air conditioning. Evpn on fractional tonnage installations, air is used as the condensing medium only where water is expensive or where simplicity of installation warrants the higher condensing pressure, and consequent higher power costs than would be . . obtained using water as the condensing medium. The conventional air cooled condenser consists of an extended surface . coil across which air is blown by a fan. The hot discharge gas enters the ' S' 708 CHAPTER 39 1946 Guide coil at the top and, as it is condensed, flows to a receiver located below the condenser. Air cooled condensers should always be located in a well ventilated space so that the heated air may escape and be replaced by cooled air. The principal disadvantages of air cooled condensers are the power - required to move the air and the reduction of capacity on hot days. This loss of capacity due to high condensing pressures on hot days requires that equipment of increased capacity be selected to meet the peak load. Thus at normal loads the equipment is oversized. 2. Water cooled condensers are of the double pipe type, the shell and tube type, or the shell and coil type. Double pipe condensers are arranged so Fig. 8. Performance Characteristics of Compression Refrigeration Machines at Constant Speed that water passes through the inner of two concentric pipes and refrigerant circulates through the annular space between the, pipes. Where possible, . there should be counter-flow of the refrigerant and the condensing water to obtain maximum temperature differences. This type is usually used only with small condensing units. s The amount and temperature of the. condensing water determine the condensing temperature and pressure, and indirectly the power required for compression. It is therefore necessary to determine a balance so that the quantity of water insures economical compressor operation. Because there is a decided tendency to conserve the water in city mains and because most large cities are restricting the use of water for air con ditioning and refrigeration equipment, it is often necessary to install cooling towers or evaporative condensers. Cooling towers, unfortunately, produce the warmest condensing water at the time when the load on the system is greatest, so that the refrigeration equipment must be designed to meet the maximum load at abnormal condensing water temperatures. Refrigeration 709 If properly designed, this makes little difference in the efficiency of operation throughout the year except at those times when the condensing water temperature is highest. As this occurs only for 5 per cent of the entire cooling period it can be disregarded as ,a factor in establishing yearly operating costs. . The cooling tower has a certain advantage over the use of water from the city mains. Economies are possible when a cooling tower is used, which cannot be achieved by the use of condensing water from city mains. In certain localities, the lowest city water temperature during the summer months is from 65 to 70 F. This temperature range takes place for the entire cooling period, regardless of the outdoor temperature. With a cooling tower, the temperature of the condensing water may rise to 80 or 85 F under maximum conditions, but under less than maximum conditions the temperature of the water leaving the cooling tower drops considerably. It has been established that in these localities during 50 per cent of the time, the outdoor wet-bulb temperature varies from 60 to 70 F and the cooling tower water, for the same periods, varies from 65 to 75 F. When the outdoor wet-bulb temperature drops below 60 F, which occurs approximately 30 per cent of the time, the condensing water temperature is still lower. The cost of water used for condensing is small as the only water required is that used to make up the loss by evaporation in the cooling tower itself. Refer to the section on Cooling Towers in . Chapter 37. . Shell and coil condensers are in general use for medium sized condensing units, and consist of a coil of tubing mounted inside a shell. The cooling water passes through the coil. 3. Evaporative condensers. Due to the high cost of city water for con denser purposes, and due to ordinances in some localities prohibiting the discharge of large quantities of such water into the sewage systems, there has been developed a condenser which uses a minimum amount of water on a finned surface, cooling it to approximately the wet-bulb temperature of the surrounding atmosphere. ' The end view of a typical evaporative condenser is shown in Fig. 9. The fan draws the air over a finned tube condenser which is kept wet by a water spray. The discharge refrigerant gas from the compressor enters the top of the condenser coil and the liquid refrigerant is drained from the bottom of -the coil into a liquid receiver and then circulates through the x remaining portion of the system in the usual way. The water is circulated through the spray nozzles and the level is maintained in the sump by means of a float valve. The eliminator plates are placed in the path of the water-air mixture so as to remove the entrained water. The air leaving the unit is almost completely saturated, so that care must be taken in locating discharge ducts to prevent con densation. Evaporative condensers are available in sizes up to 100 tons or more. These units use only a small portion of the water required for a water cooled condenser. The water is vaporized by the heat of the refrigerant so that each pound of water used extracts approximately 1000 Btu from the refrigerant, whereas under standard rating conditions where thewater temperature rise is 20 F, each pound of water extracts only 20 Btu from the refrigerant. Including the water lost by entrainment in the discharge air, by overflow and stand-by evaporation, the water used is about 3 to 5 per cent of the amount that would be required for a water cooled condenser. 710 CHAPTER 39 1946 .Guide The evaporative condenser requires more maintenance, occupies greater space (must be located where air is available), and has a higher first cost than the water cooled condenser, but where the use of water is restricted or expensive, the evaporative condenser has become widely accepted. Compared with a water cooled condenser and cooling tower, which com bination uses about the same quantity of water, the evaporative con denser has the advantage of lower cost and smaller space requirements. Refrigera tion 711, The magnitude of this pressure is determined by the temperature of the suction gas leaving the evaporator, as the control bulb is attached to the suction line at this point and is at approximately the same temperature. The suction pressure in the evaporator is transmitted through the equal izer tube and exerts an opposing force on the other side of the diaphragm in the direction to close the valve. This pressure corresponds to the tem perature of the boiling refrigerant. The resulting force on the diaphragm is determined by the differential between the temperature of the suction gas and the boiling point of the refrigerant, which is the amount of super heat in the gas. If this temperature differential becomes greater (super heat increases), the resultant force on the diaphragm opens the valve and admits more refrigerant. The reverse is true if the superheat decreases, and the valve partly closes, thus admitting less refrigerant. The spring keeps the valve closed until the resultant force on the diaphragm cor- Expansion Valves The thennostatic expansion valve is a device to regulate the flow of liquid refrigerant so that the evaporator will always be used to best advantage. The evaporator coil must be kept as full as possible without any diance of liquid refrigerant entering the suction line. The expansion valve accomplishes this by regulating'the supply , of refrigerant, so that the temperature of the gas leaving the evaporator is always slightly higher than the temperature of the boiling refrigerant inside of it. This difference in temperature between the outgoing (suction) gas and the liquid refrigerant in the evaporator is called the superheat of the gas. The operation of the thermostatic expansion valve can best be ex plained by means of a diagram, Figr 10. A small refrigerant charge in the control bulb exerts a pressure through the tube to the upper side of the diaphragm, which tends to open the valve. ' ' Fig. 10. Typical Thermostatic Expansion Valve responds to the desired superheat. The adjustment of the spring will change the amount of superheat to be maintained in the suction gas. The selection, of the expansion valve is, of course, determined by the capacity of the valve. The capacity of a valve with a given orifice is determined by the refrigerant used, the differential of pressure across the ' valve, and the amount the liquid is sub-cooled as it enters the valve. The expansion valves are usually rated at zero sub-cooling of the liquid, or 100 per cent , liquid. Frequently special devices are used to properly distribute the refrigerant among the parallel paths of the evaporator. These distributing devices' usually have considerable pressure drop. Where they are used, the pressure drop across the expansion valve is not the difference between suction and discharge pressures, as allowance must be made for the pressure drop across the distributing device. An equal izer connection from the evaporator suction line must be made to the underside of the diaphragm (see Fig. 10) whenever the valve outlet is not at the evaporator pressure' so as to insure suction"pressure at this point. ' When distributing devices are used, this equalizer connection is essential for proper operation of the valve. Another pressure drop allowance must be made for the liquid line, particularly when the liquid line has an appreciable vertical rise. Whenever possible, expansion valves should be installed in a manner 712 CHAPTER 39 1946 Guide which will permit placing thermometer wells in the suction connection and allowing sufficient room for free adjustment of the valve. Evaporators and Coolers The types of coolers'used in connection with air conditioning work fall into three general groups. The first, is the direct cooling of water; the second, direct cooling of air; and the third, cooling of brine for circulation in a closed system, which can cool either water or air. One method of the direct cooling of water is to install direct expansion coils in the spray chamber so that the water sprayed into the air comes in direct contact with the cooling coils. Another common and efficient method of cooling spray water is to use a Baudelot type of heat absorber where the water flows over direct expansion coils at a rate sufficiently high to give efficient heat transfer from water to refrigerant. Another type of spray water cooler is the shell and tube heat exchanger in which the refrigerant is expanded into a shell enclosing the tubes through which the water flows. The velocity of the water in the tubes affects the rate of heat transfer, and as the refrigerant is in the shell com pletely surrounding the tubes at all times, good contaqt and a high rate of' heat transfer are insured. The disadvantage of such a system is that with the falling off of load on the compressor the suction temperature or the temperature in the evaporator drops and there is a possibility of freezing the water in the tubes, which, of course, might split the tubes and allow the refrigerant to escape into the water passage. This danger can be eliminated by automatic safety devices. ,, - Another system of cooling spray water is to submerge coils in the spray collecting tank, or in a separate tank used for storage. The heat trans mission through the walls of the coils, however, is low and a great deal Capacity Tons 0 to 5 5 to 25 25 to 50 50 to 400 400 and Over Table 11. Basis of Equipment Selection Majority Used Some Used Few Used Unit systems in con Unit central systems Built up central sys-. ditioned ^pace. using duct distribu terns. tion. Built up central sys tems using reciprocat ing compressors. Unit central systems using duct distribu tion. Unit systems in con ditioned space. Built up systems using absorption and adsorption systems. Built up central sys Built up central sys* Central systems tems using reciprocat tems using centri using adsorption ing compressors. fugal compressors. systems. _ Built up central sys tems using reciprocat ing compressors. Built up central sys tems using steam jet and centrifugal com pressors. Built up central sys Built up central sys tems using centri tems using steam jet. fugal compressors. Refrigeration 713 more surface is required than for any other type of cooler. However, with large storage tanks this type of codling can be utilized to advantage. When direct cooling of air is employed, the refrigerant is inside the coil and the air passes over it. Cooling depends upon convection and con duction for removing the heat from the air. The type of coil used can be either smooth or finned, the finned coil being more economical in space requirement than the smooth coil. The fins, however, must be far enough apart so as not to retain the moisture which condenses out of the air. The indirect cooler, where brine is cooled by the refrigerant and the resulting cold brine is used to cool either air or water, introduces several other considerations.' It is not the most economical from a power con sumption standpoint, as it is necessary to cool the brine to a temperature sufficiently low so that there is an appreciable difference between the Fig. 11.. Compressor and Coil Performance average brine temperature and that of the substance being cooled. This requires that the temperature of the refrigerant must be still lower, and consequently the amount of power required to produce a given amount of refrigeration increases due to the higher compression ratio. There are other considerations which make such a system desirable. In the first place, where a toxic refrigerant is undesirable or cannot be used because, of fire or other risks, especially in densely populated areas, the brine can be cooled in an isolated room or building and can then be circulated through the air conditioning equipment. This arrangement eliminates any possibility of direct contact between the air and refrigerant. . Equipment Selection . The selection of proper refrigeration equipment for any air conditioning job is of utmost importance for satisfactory results. The most important factors in the selection of the equipment are: 4 1. Loads (as determined by the conditions of the space to be cooled). 2. Economics (both initial and operating costs). 3. Codes (local safety codes must be adhered to and influence the type of system to be used). 714 . CHAPTER 39 1946 Guide ' . A broad division of equipment to be used for a particular installation or application may be made, on the basis of the magnitude of the load. Current general practice is outlined in Table'll. Unit or packaged systems, consisting of a reciprocating. compressor, condenser, evaporator and fans, are generally used in the smaller sized jobs where electric power is available, as they are manufactured complete, ready to install and are the most economical (see Chapter 36). . The reciprocating compressor in the built-up central system (see Chapter 43) covers the widest range of application since it is applicable to either the direct expansion or indirect systems and can be driven by steam or gas engines, or by electric motors. The quantity of condensing cooling medium required is also less than for any other system with the exception of the centrifugal compressor, which uses the same amount. Centrifugal compressors are used for large installations, and usually where the indirect system is. required. The driving mechanism can be Table 12. Typical Operating Conditions for Two Types of Load Enclosure Load, Btu per Hour Sensible Latent Total Ratio ' TO' Total Am Enterinq . Coil t)pebating Balance Point F Deg Per Cent R.H. Evaporator Temp F Deg Condenser Pressure Lb per Sqlo. Per CentSensible Heat Restaurant Office 103,000 45,000 148,000 0.695 121,000 27,000 148,000 0.820 82 82 45. 34.4 45 42.2 123 100 69.9 82.1 steam turbine or electric motor. The steam jet system is used where steam is available and cooling water can be had in large quantities. It will be noted by referring to Fig. 7 that all systems using compressors have a common characteristic and that is, that the capacity varies with the evaporating temperature. Not only can the equipment be selected to produce a given result but the performance can be predicted under . varying load conditions by the simple expedient of using, the variable of evaporating temperature as the abscissa arid the load or capacity as the ordinate in a series of curves. Manufacturers of compressors and cooling coils furnish performance data for apparatus that can be plotted in the form of curves similar to those shown in Fig. 11. The performance of a compressor is plotted as a series of curves, each curve being drawn for a given condensing pressure. The performance of a direct expansion coil at two different air velocities is plotted on the same graph. The operating point will be, of course, where the two curves cross. . Data given in Table 12 illustrate two types of conditioned enclosures having the same total load of 148,000 Btu per hour, but with two different ratios of sensible to total heat. In the case of the office with a ratio of 82 per cent sensible to total 'heat, the operating point A in Fig. 11 is found to be 42.2 F evaporating temperature with a. face velocity of 500 fpm. In the case of the restaurant, with a ratio of 69.5 per cent sensible to total heat, the air velocity is lowered to 300 fpm and the evaporating ; temperature is lowered to 34.4 F as shown in point B of Fig. 11. In order Refrigeration 715 to obtain the same capacity, a-larger condensing unit is used. . This, illustration assumes zero pressure drop .through, the suction line. ' The pressure drop can be taken into account by shifting the. compressor performance curves by . the amount of pressure drop expressed in Fahrenheit degrees. ABBREVIATIONS AND SYMBOLS IN CHAPTER cop = coefficient of performance, ratio of refrigerating effect to the heat equivalent of the compressor work. ' .. CVE = conventional volumetric efficiency. . , d = internal diameter in inches. . . Ht = cooling load in tons.' ': hi -- specific enthalpy of vapor at condition of discharge from compressor. Ale = specific enthalpy of liquid at discharge from compressor. Aid = specific enthalpy of liquid at discharge of expansion valve. Ais =- specific enthalpy of liquid at entrance to expansion valve. Am = specific enthalpy of mixture. Av = specific enthalpy of saturated vapor. Avd = specific enthalpy of saturated vapor at discharge of valve or compressor. ' ftvs = specific enthalpy of saturated vapor at state s entering compressor. ' hp = horsepower. .' Pi pressure of saturated liquid and vapor at discharge of compressor. ps = pressure of saturated liquid, psig = pressure pounds per square inch, gage, psia = pressure pounds per square inch, absolute. - Q -- quantity of heat, Btu. . % Qc = heat loss from condenser, Btu per pound refrigerant. Q) = heat dissipated in cooling water, Btu per hour. . ' ' s ='entropy. ' . ,. As = entropy change between suction and discharge. T = absolute temperature, Fahrenheit degrees. . - Tavg = average temperature,- Fahrenheit, degrees, absolute of gas passing through . compressor. - -.* Tc = condenser temperature, Fahrenheit degrees, absolute. Ts -- evaporator temperature, Fahrenheit degrees, absolute.. , , led = degrees superheat at discharge condition of vapor leaving compressor. Id = discharge temperature, Fahrenheit degrees. " Vc = clearance, percentage of volume, swept by piston, which is contained. in spaces at end of cylinder when piston is at end of stroke (clearance includes valve spaces, etc.) '. . ." Vs = specific volume of gas at suction, cubic feet per pound. rd = specific volume of gas at discharge, cubic feet per pound. ' Wr = refrigerant rate, pounds per minute. . ' '- * = proportion of liquid in mixture of vapor and liquid. . REFERENCES '--Application and Economy of Steam Jet Refrigeration to Air Conditioning, by A. R. Mumford and A. A. Markson (A.S.H.V.E. Transactions, VoL 44, 1938. p. 33). .. . 2_The Application of Storage Refrigeration to Air Conditioning, by C. F. Boester (A.S:H.V.E. Trans actions, Vol. 45. 1939, p. 675). . '. '--Use of Cold Accumulators in the Air Conditioning Field, by R. W. Evans and C." J. Otterholm (A.S.H.V.E. Transactions. Vol. 48. 1942. p. 123). ' . : 4--Cooiing'Homes, A Field for Refrigeration, by A. R. Stevenson, presented at the symposium of the Refrigeration with Gas Committee oFthe American Gas Association, April 20, 1926. The Heat Pump, An, Economical Method of Producing Low-grade Heat from Electricity, by T. G..N. Haldane <Electric Review, 716 CHAPTER 39 1946 Guide Vol. 105, p. 1161-1162, December 27..1929. and 1. E. E.-Joumm. VoL68, p. 666-675, June, 1930). Edison Building Heated and Cooled by.Electricity, by H. L. Doolittle {Power. Vol. 74, p. 384. September 8,1931). House Heating by Pump with 5 to 1 Pick-up Ratio, by Gilbert Wilkes and R. E. Marbury (Electrical World. Vol. 100, p. 828, December 17, 1932). An All Electric Heating, Cooling and Air Conditioning System by Philip Spom and D. W. McLenegan (A.S.H.V.E. Transactions, Vol. 41,1935, p. 307). Using the Reversed Cyde Refrigerating Principle for a Self-Contained Heating and Cooling Unit, by Henry-L. Galson (A.S.H.V.E. Journal Section, Beating, Piping and Air Conditioning, October, 1935, p. 497); Heating by Reversed Refrigeration, by A. J. Lawless (Heating, Piping and Air Conditioning, August, p. 473, September, p. 519, 1940). , 1 BIBLIOGRAPHY1 Refrigerating Data Book, Vol. 1 (American Society of Refrigerating Engineers). Refrigeration Engineering, by H. J. Macintire (John Wiley & Sons). Theory of Mechanical Refrigeration, by N. R. Sparks (McGraw-Hill Book Co., Inc.). Refrigeration and Air Conditioning Engineering, by B. F. Raber and F. W. Hutchin son (John Wiley & Sons). ; Refrigeration, by J. A. Moyer and R. U. Fittz (McGraw-Hill Book Co., Inc.). ii 5 li t ii ' CHAPTER 40 _^ir trlbution Standards for Satisfactory Conditions, Definitions, Mechanics of Air Distribution, Types of Supply and Return Openings, Outlet Locations, Return and Exhaust Intakes, Specific Ap plications, Balancing the System CORRECT air distribution contributes as much or more to the success of a forced air heating, ventilating, cooling or air conditioning system as does any other single, factor. An air conditioning system may deliver the required quantity of conditioned air and still fail to give satisfactory room conditions because of poor air distribution. The scope of the chapter is limited to the air distribution within the conditioned space. Reference is made to the distributing duct system only insofar as it affects the performance of the air distribution outlet. See Chapter 41 for informa tion on air duct design. ' STANDARDS FOR SATISFACTORY CONDITIONS Air distribution within a space to, be conditioned consists in producing within the space the proper effective temperature whether for cooling, heating or ventilating. This means that a reasonable uniformity of tem perature, humidity and velocity must be obtained within the zone of occupancy. This zone is'usually the room space between the floor and a plane 6 ft above the floor. Air must have a proper combination of quan tity, temperature, humidity and velocity to satisfy the over-all demands, whether for cooling, heating or ventilating. Any or all of these factors may need to be controlled to produce proper comfort .conditions. Also the quantities delivered to various locations must be proportioned, so that the sections of the area having the highest or lowest load requirements are satisfied. Otherwise some areas will be too Rot, cold, stuffy or drafty, since the effective temperature will be too high or low in these areas. Other important considerations are dirt and noise.. The use of air cleaning devices is recommended to prevent or reduce streaking and smudging of walls and ceilings. Outlets should not increase the noise above the acceptable level. ' Reference should be made to Chapter 12, Physiological Principles, for the accepted standards on room temperature, humidity, air motion and direction. Material in Chapter 42, Sound Control, covers acceptable room noise levels and noise generated by air outlets. . DEFINITIONS " The following ^definitions referring to air distribution equipment have gained general acceptance. 1. Supply Opening or Outlet:. .Any opening through which air is delivered into a space whicn is being heated, or cooled, or humidified, or dehumidified, or ventilated. 2. Exhaust Opening or Return Intake: Any opening through which air is removed from a space which is being heated, or cooled, or humidified, or dehumidified, or venti- ` lated. 3. Outside Air Opening: Any opening used as an entry for air from outdoors. 4. Grille: A covering for any opening and through which air passes. 5. Damper: A device used'to vary the volume of air passing through a confined cross-section by varying the cross-sectional area. .' 6. Multiple Louver Damper: A damper having a number of adjustable blades. 717 718 CHAPTER 40 ' 1946 Guide. 7. Single Louver Damper: A damper having one adjustable blade.' 8. Face: A grille with provision for attaching a damper. . 9. Register: A face with a damper attached. - . 10. Flange: The portion (either integral or separate) of a grille, face, or. register extending into the duct opening for the purpose of mounting. .' 11. Frame: The portion (either.integral or. separate), of a grille,. face, or register extending around the duct opening for the purpose of mounting. 12. Margin: The margin of a grille, face, or register is one-half of the difference between the duct dimension and over-all dimension measured either horizontally or vertically. ' . . . 13. Fret: The member separating the openings of a grille, face, or register. 14. Free Area: The total minimum area of the.openings in the grille, face, or register through which air can pass. _. 15. Core Area: The total plane area of the portion of a grille, face, or register bounded by a line tangent to the outer edges of the outer openings through which air can pass. 16. Mean.Area: The total of the core and free areas divided by two. ` 17. Duct Area: The area of a cross-section of the duct based on the inside dimensions at a point where the grille, face or register is mounted. 18. Percentage Free Area: The ratio of the free area to the core area expressed in percentage. ... . ' *: .. . 19. Aspect Ratio: The ratio of length of the core of a grille, face or register to the width. .* , 20. Throw {Blow): The distance an air stream travels on leaving the outlet (grille or register) to a position at which air motion reduces to a maximum velocity of 50 fpm.; 21. Envelope: The outer boundary of, an air stream moving at a perceptible velocity. 22. Drop:. The vertical distance, h, in feet, the lower edge of the air stream drops - between the outlet and the end of its throw. ... '. 23. Rise: The converse of drop. 24. Induction: The entrainment of room air by the air discharged from the outlet.' 25. Primary Air: The air leaving the duct and entering the outlet {Q\ in cfm). 26. Secondary Air: The room air.picked up by the primary air through induction {Qt in cfm). _ . ` . ' ' - 27: Total Air: The mixture of primary and secondary air ((?* in cfm). - . 28.-Induction Ratio: The total air divided by the primary air equals r, or Qi/Qi. 29. Outlet Velocity: The average air velocity emerging from the outlet (Vi in fpm) measured in the plane of the opening. . 30. Terminal Velocity: The average air stream velocity at the end of the throw {VT in fpm). ., `31. Horizontal Spread: `The divergence of the air stream in the horizontal plane after it leaves the outlet (Degrees). . 32v Vertical Spread: The divergence in the vertical plane (Degrees). ... - . . 33. Temperature Differential: Temperature difference between primary and room air {tT -- fas), . .' ' / . 34. Vane Ratio: The ratio of depth of vane to shortest opening width between two . adjacent grille bare. . . ', ' 35. Radius of Diffusion: The horizontally measured distance served by a ceiling outlet within which air motion is reduced to 50 fpm (maximum). * MECHANICS OF AIR DISTRIBUTION In the mechanics of air distribution, two major problems are-involved: ' (1) complete mixing of the primary air and secondary air outside of the zone of occupancy.in order to reduce the temperature difference and air motion to acceptable limits before the air enters the occupied zone; and (2) counteraction of the natural convection and radiation effects within the room. ' ' ' : '.Momentum Theory '. . ' When air is discharged'from an outlet into a free open'space', the . primary air stream entrains room air as it traverses the space. This- Air Distribution 719 entraining effect increases the cross-sectional area and reduces the velocity of the resulting air stream. Induction takes place with the conservation of linear momentum; this has been confirmed by tests which indicate that the momentum remains almost constant throughout the entire measure- able length of the air stream. This relationship .may be expressed by the | Equation 1: ' MiVi + Jlf, V2 = (Mi + M,) V, . (1) where ' Mi = mass of primary air. - . . M2 -- mass of secondary air. Vi = velocity of primary air. . Vt = velocity of secondary air (normally, Vz - 0). V9 -- velocity of the mixture. - .' Since the secondary air velocity is zero, . M, Vi = (Mi + M,) V, V, Mi + Mg or' 1 T7 = '1ft " "r (2) In Equation 2, r is called the induction ratio. . Since in many applications the densities of primary and room air are about equal, air volumes may be substituted for mass in Equation-2. where , '& +Q. " <2. Qi .= volume of primary air, cubic feet. Qt = volumeof secondary air, cubic feet. (3) Throw , Mathematical statements for throw have been evolved from research1 that have proved the following to be approximately true for outlets having aspect ratios below 50. . 1. Residual velocity of an unrestricted air stream is directly proportional to the outlet velocity. ` 2. Residual velocity is directly proportional to the effective diameter of the outlet. Effective diameter is defined as a diameter of a circular area (effective area) which would give the same throw. It is the free area times a constant. . 3. Residual velocity is inversely proportional to the distance from the outlet. From these statements the following, equation can be established1. where CVxDi KVX VAi: X . X (4) VT = residual maximum velocity in air stream, i.e., the highest maintained velocity , at the given cross section in the room. . ' V\ = average velocity across the effective area of the outlet. . ,, . .. X throw. . .. . . . . C and K = constants of proportionality. ! . . K = J C <? 1.13 C ' ' ' . fx ' ` ' , Di =.diameter of effective area of outlet. A\ = effective area of outlet. . . 1 ' - 1' ; '' . . . * *, 720 CHAPTER 40 19*6 Guide Substituting for A\ in Equation 4 Fi ` K Vi JQl X= ^ F, Fr (5) The throw of an unrestrained jet is therefore proportional to the square root of the supply air quantity and initial velocity, and inversely pro portional to residual velocity. . The proportionality factor K is a function of residual velocity and initial velocity. Another variation of the formula (Equation 4) has been suggested 2 in which K{ is suitable for all conditions; . *= y.i.u .-- vjiS V^T (6) The average velocity at the effective area can be obtained from the following equation. V, _& Ai (7) where AI = effective area. Jet Pattern From Round or Rectangular Openings in a Large Room The relation between the shape of the discharge of a jet and the shape of the outlet has long been the subject of research. It has been' proved to be incorrect to assume that the jet retains the outlet shape when it discharges into a free open spacel. Air streams from rectangular outlets having low aspect ratios develop a symmetrical or cone shape appearance within a few diameters from the outlet face. From there on, the jet continues to expand at fairly constant rate. Beyond 20 diameters there is very little difference between round and rectangular jets. The assump-1 tion can be made that the apex of the cone is in the same position for any jet having small aspect ratio. For the more usual problems of the con ventional room with outlets near the ceiling, there are insufficient experi mental data to justify a definite statement on the effect of aspect ratio. If the round or rectangular opening is divided into a number of orifices having straight sides, the performance of the air stream will be similar to that of a plain opening. ' Velocity Across Jets '. - Results of many tests 1 indicate that the ratio of centerline velocity" to average velocity is about 3, irrespective of outlet size, shape or initial velocity. This statement is true for stream cross-sections located beyond 10 diameters from the outlet, and is fairly accurate for distances up to 50 diameters. Experimental data are lacking for distances beyond 50 diameters. Guide Vanes " . ' , The average jet angle (included angle in both planes, see Fig. 1) for an air stream as it emerges from a rectangular outlet of any shape without spreading vanes is about 19 deg, plus or minus 5 deg, depending on the type of approach, type of outlet and velocity. The spread increases slightly with velocity. A vaned outlet discharging.air uniformly forward Air Distribution 721 will result in a spread of about 14 deg. This is equivalent to a spread in any direction of about one foot in every 8 ft of blow. Vanes should have a depth, of one to two times the spacing between the vanes. If the ratio of vane depth to spacing is less than one, effective control by means of the vanes cannot be obtained. Little improvement is obtained by increasing the ratio beyond two. The effect of various types of vanes is as follows. ' Straight Vanes . . As mentioned previously, the included angle- between both planes will be in the neighborhood of 14 deg, for a straight setting of the vanes as shown in Fig. 1. . Diverging Vanes - Such vanes set for an angular spread will have'a marked effect on the direction and distance of travel of an air stream, An outlet having 1 vertical vanes set straight forward in the center, with uniformly increasing Fig. 1. Spread of Air Stream with Various Vanes angular deflection to a maximum at each end of 45 deg, will produce ah air stream with a horizontal included angle of approximately 60 deg as shown' in Fig. 1. The throw will be reduced one-half for such a vane setting. Increasing the divergence of the vanes reduces the air quantity handled by an outlet for a given duct static pressure. The primary function of the vanes is to spread the air horizontally. Little is gained by spreading the air vertically. Converging Vanes The blow of an . outlet may be somewhat increased by converging the. vanes of an outlet as illustrated in Fig. 1. Even with converging vanes, the resultant angle of spread of an air stream will not be less than 14 deg. The air converges for a few feet in front of the outlet, and then diverges more than if the vanes had been set straight. ....... ............... Both the horizontal and vertical vanes of an outlet are important. After an installation has been made, many conditions of draftiness or stuffiness can be alleviated by some vane adjustment, provided an independent means for regulation of static pressure behind the vanes is included.. Vertical Drop and Rise \ The vertical distance the' lower edge of an air stream moves between the outlet and the end of the blow is termed the drop or rise (II). This drop or rise is influenced by the difference in density between the air, stream and the room air, resulting from the temperature difference and 722__________ CHAPTER 40 1946 Guide the spread of the air stream. For air emerging at room temperature, the drop or rise will be a function of the spread only and will be-equal to: ' H - L X tan (Spread Angle j (8) 5 where ` H = drop due to spread, feet. L -- throw, feet. . When there is a temperature difference between the air stream and the room, the additional drop.or rise is approximately given by Equation 9: H _ . ftr -UA L , (9) where . - i and = constants (tentative suggested values i = 5, n, = 1.2). <r = room temperature, degrees Fahrenheit, las = supply air temperature, degrees Fahrenheit. Vi = jet velocity, feet per minute. . . ' For cooling application H is. subtracted from the .outlet height, for heating H is added. : Effect of Aspect Ratio on Entrainment - .. In slotted outlets, the air entrainment, of the primary jet is a function of aspect ratio l. This effect is most pronounced when large changes in . . the ratio are made. A comparison between a slot of aspect ratio 24 and a square opening of the same area is given in curves A and B of Fig. 2. At a distance'of 8 ft from the outlet, the entrainment of the slot is 8.1 as compared with 6.9 for the square, or an increase of about 17 per cent. ' . Curve C shows the further increase in entrainment obtained by using an aspect ratio of 48. Ah increase of 40 per cent is obtained over the 24 in. x 1- in. slot. This indicates that long narrow- slots produce air streams that give high induction of secondary air. Parallel Slots ' The use of several slots in parallel to vary the rate of air entrainment . depends mainly on the distance between the slots. If close together, the air pattern is about the same as a.single opening of equal area:. Spac ing the openings farther apart gives an increase in entrainment as shown on curves C, D and E of Fig. 2. It will be notecl.that 2 openings 24 in. x 34 in. located very close together will, obtain an entrainment which is Table 1. Values of Room Circulation Factor (F) in Equation 11 Outlet Velocity Fpm Fi . 200 300 400 500 600 . 700 800- Ateragb Rook Velocity Fpm, Vr 10 - 20 ' 30 40 50 . Outlet Velocity Fpm Vi 6.0 12.0 18.0 24.0 30.0 4.0 8.0 12.0 16.0 20.0 3.0 6.0 9.0, 12.0 15.0 2.4 4.8 7.2 9.6 12.0 2.0 4.0 6:o 8.0 10.0 1.7 3.4 5.1 6.8 8.5 1.5 3.0 4.5 6.0 7.5 900 1000 1200 1400 1600 1800 2000 ' Average Room Velocity Fpm, Vt .10. 20 1.3 2.7 1.2 2.4 i.o. 2:o 0.9 . 1.7 0:8 .1.5 0.7. 1.4 0.6 1.2 30 40 . f50 4.0 3.6 3.0 2.6 2.3 2.0' 1.8 5.3 4.8 4.03.4 3.0 2.7 .2.4 6.7 ,6.0 .5.0 '4.3 3.8 3.4 3.0 Air Distribution ............ .............. .. ... -,. . ..723. about the same as obtained with one 24 in. x 34 in..opening. However, if the slots are spaced 634 im apart there is a marked increase in entrain ment. * - ' .- Room Air Motion ; The air motion in the occupied zone, is usually such that the air travels across the room in reverse direction to the blow of the outlet. The cross- ,-FigI 2. Typical'Relation of Entrainment Ratio to Distance from ' Outlet for Slotted Outlets. (Based on 800 ffm Outlet'Velocity.) sectional area of this stream is equal to the outlet wall area less the stream area: and the area obstructed by furnishings. "Equation 10 gives the average room velocity in the occupied zone as a function of the air volume, Qa, supplied per square foot of outlet wall area and the outlet velocity. . Vr Ql AZ. . where,-. T- Qi = (?i% Qi = mixture of primary and secondary air, cfm. "VI = average room velocity,'feet per minute. - -- . (10) 724. CHAPTER 46 .1946 Guide A = outlet wall area, square feet. , , Z = 0.6 (reduction factor to allow for supply air stream 20 per cent and furniture obstruction 20 per cent, at point where supply air stream occupieg 20 per cent of the room cross-section). . . . V\ - Since Qs = Qir by definition, and r = -r=- from Equation 2, and V3 is . K) assumed to be about 200 fpm for total induction in actual practice, then from Equation 10: VT QL A FVi 120 or 120 Kr V, (11) where F is the room circulation factor expressed in cubic feet per minute per square foot of outlet wall area. Thus room'air motion is directly a function of outlet velocity and air volume per square foot of outlet wall area. Hence Equation 11 and Table 1 can be used to determine the probable acceptability of a particular installation from the standpoint of proposed air volume, outlet wall area, and grille velocity. Fig. 3. Throw of Wall Outlets Outlet Performance The factors of outlet performance, throw,; drop, capacity, noise, dirt and room air motion place considerable limitations on the design of a satisfactory distribution system. 1. Throw. The throw of wall or ceiling outlets should be selected to cover three-quarters of the distance toward an exposed wall or window as shown in A of Fig. 3. The throw rqpst be sufficient to produce satis factory conditions over the area to be conditioned. In some ceiling" outlets, plaques or similar units, the throw is along, the ceiling. The air tends to hug the ceiling and the throw is increased approximately 20 per cent above the throw of an unrestrained air' stream. Overblowing is considerably more serious than underblowing, as an overblow will create objectionable down drafts from any surface it strikes; although under blowing in the case of heated air may be serious in that the warm air may rise too rapidly and thus cause stratification in the occupied zone. In spaces with beamed ceilings, the outlets should be located below the bottom of the lowest beam level, and preferably low enough so that an upward or arched blow may be employed. The blow should be arched sufficiently to miss the beams and, at the same time, in such a manner as to prevent the primary or induced air stream from striking furniture and obstacles producing objectionable drafts. If an outlet is adjusted down ward to avoid a beam, cold air may enter the zone of occupancy long ' Air Distribution 725 before the desired induction has taken place, thus causing serious dis comfort. . In ceiling applications, since there is a component downward, the ceiling height and throw are both very important factors. If cold air is used, it must be brought to the proper temperature before entering the zone of occupancy. If perforated plates are used in the ceiling in cooling, the jet velocity must be low. Air slightly above room temperature will usually be properly distributed by outlets selected for cooling. When delivering warm air the stream may be projected downward and the amount of dispersal of the jet varied to get proper mixing and control: 2. Drop. The outlets should be located so that the air stream at .the termination of the blow is not less than 5 or 6 ft above the floor level. As illustrated in B of Fig. 3 the maximum permissible blow for a given ceiling height may be obtained by locating the outlet low on the wall, arching the blow, and sweeping the air across .the flat ceiling. The air, as it traverses'the room, will adhere to the ceiling. The objection to this method is the possible streaking of the ceiling with dirt. 3. Room Air Motion. The factors leading to high air motion are exces sive velocity, high air volume per square foot of. floor area, overblow, striking of beams causing a spilling of the air into the zone of occupancy, and heating in severe climates by means of ceiling outlets which are directed downward. ' . 4. Dirt. Although the primary air may be carefully filtered, dirt from the conditioned space may be deposited on the walls or ceiling wherever there is considerable secondary air motion. With ceiling outlets, dirt streaking may be minimized by cat'bfully controlling the discharge of the outlets^ With wall outlets, dirt streaking may be minimized by pre venting direct impingement of the air on any ceiling or room surface. Floor outlets may offer objection as dirt collectors. 5. Noise. The noise of an outlet is primarily the function of the outlet velocity and size, and secondarily of the outlet construction. The maxi- 1 mum acceptable noise level in a space may completely dictate the permis sible outlet velocities that may be employed. (See Chapter 42 for discussion of permissible room noise levels and noise generated by outlets.)- 6. Capacity. The quantity of air to be handled is determined by the heating, cooling, or ventilating requirements. Manufacturers' rating sheets are usually consulted foriselection of the proper number, size and type of outlets for a given air quantity. The basis of rating used should be carefully noted to make certain that resulting velocities are suitable for the type-of occupancy. . Ceiling outlets will in general handle more air. per outlet, without objectionable air motion, than either comparable sidewall or floor outlets. Temperature Differential . The use of outlets that give rapid mixing permits use of higher supply temperatures for heating and lower supply temperatures for cooling. To facilitate control it is frequently desirable to handle more air at a lesser temperature difference with the room, rather than less air at a greater temperature difference, in order that two areas temporarily loaded . differently will not differ too greatly in temperature. 726 . CHAPTER 40 - -1946 Guide TYPES OF SUPPLY AND RETURN OPENINGS Wall type openings are: perforated plates, vaned outlets, registers, slotted outlets, and ejector nozzles. Perforated Outlets . Due to the non-adjustability and small vane ratio perforated sheet metal outlets, although inexpensive, have not met with favor as wall type supply, openings. They are useful primarily where directional air control is unnecessary, and for return air openings. . Vaned Outlets Outlets equipped.with both vertical and horizontal adjustable vanes are particularly suited to sidewall distribution. For proper control over the air flow, the vane ratio should be from 1 to 2. - Outlets with non-adjustable. vanes may be employed but they should only be used where the per- formance is not critical or can be adequately predicted. Vanes should be properly designed to prevent an increase of noise above permissible level. Registers .. .- - Fixed vanes or perforated grilles equipped with a vane damper are termed registers. They are used primarily for residential heating systems, where the outlet distribution is not critical and low cost is of.importance. Slotted Outlets .. Slotted outlets essentially consist of either flat steel plates containing a number of long narrow slots or a single long narrow slot. In order to give a good, conversion from static pressure to-velocity pressure, the sides of the slots are rounded to give a venturi effect. Due to their high aspect ratio, the slotted outlets have a greater induction effect than the compar able vaned'outlets of equal area and consequently the throw is reduced. They are primarily useful where an unobtrusive means of distribution is- desired, and where it is desirable to submerge the outlets into the room decoration and to minimize the effect of obstructions in the line of dis-. charge. They are adaptable to narrow rooms of low ceiling. In this case the slots are run full -length of the room. , Since these outlets offer greater induction at a given noise level, they are useful in obtaining proper air motion under certain design limitations. One disadvantage, however, is that air quantity and distribution must be carefully planned as correction after installation is difficult. . - Ejector Nozzles - ' ' Ejector Nozzles refer to outlets which operate at high static pressures,' which are constructed to give a high conversion from static in the duct to velocity pressure in the outlet, and which have a high induction effect due to their high outlet velocity. They are chiefly used for long throws and industrial process installations, such as drying, freezing, cooking, etc. Another type of ejector, is sometimes referred to as a lower nozzle having a 45 to 90 deg elbow, which can be rotated similarly to a universal joint about an axis perpendicular to the surface to which it is fastened. These outlets give a considerable degree of adjustability and are, therefore, desirable for use in confined spaces where spot cooling is employed:^ " '/ _. Air Distribution 727 Ceiling Outlets s In ceiling outlets when the jet is circumferential and covers 360 deg, greater quantities of room air can be handled than is permissible with comparable side wall outlets, with a given air motion within the occupied- space. Temperature differentials may be higher than for ordinary side wall outlets but may not be so high as for outlets with small widely placed slots. . ; Plaques , . When plaques are used, the air from the supply opening impinges against a plate, which, with proper inlet conditions, permits the air to discharge radially. The stream is discharged horizontally in all directions. In certain applications a properly designed plaque yields satisfactory results. Ceiling Diffusers \ This type of outlet is a round, or, in some cases, rectangular outlet, which incorporates guide vanes into its construction. The air pattern is determined from the contour and design of the guide vanes. In some units the air streams are projected horizontally, the performance being similar to that of well designed plaques. In others the air stream is projected downward. Others produce air streams at varying angles to the ceiling. _ . " ' Perforated Ceilings.. - - This method obtains air diffusion by discharging air through perfor ations in the ceiling, the free area being usually less than 15 per cent. The advantages are appearance and the ready application of sound absorbing material to the design. Also, if- designed properly, this system provides a low rate of room air motion and consequently lends itself to applications having high load or high ventilating requirements. The perforations should be kept free of accumulations of dirt, as clogging will cause uneven distribution. Dirt will also smudge the ceiling. Best results .are obtained in systems having efficient cleaning devices. In using perforated ceilings for air distribution it is advisable to counter act the wall and glass heat losses by local heating means. - - Perforated Panels .. . Perforated panels are used in some installations, their gross area usually being less than 25 per cent of the ceiling area. A downward,jet pattern is obtained without any directional control. The jet velocities are higher than used in.perforated ceilings, in order to produce proper diffusion. Air volume is controlled by controlling the static pressure in the individual plenum chambers that serve the panels. . ' OUTLET LOCATIONS In selecting the location of outlets, consideration must be given to the factors of physical construction, physical appearance, location of heating or cooling loads, and outlet performance. 1.The physical construction of a building, particularly of old buildings, immediately places limitations on the type of distribution system which 728 CHAPTER 40 1946 Guide can be employed. Therefore, the first factor in. the selection of outlet locations is a consideration of the possible location of the supply duct, that is, whether it is above the ceiling, within the walls, through furred spaces above corridors, dr in the conditioned space, etc. A particular method of distribution may be highly desirable but its execution, due to the location of beams and masonry walls, may be an. impossibility: 2. The physical appearance of the outlets should conform to the esthetic appearance of the room. In factories, warehouses, etc., the esthetic demand may not be high; however, in department stores, clubs, theaters, etc., the.location of the grilles may be dictated largely by such demands. 3. The location of heating or cooling loads in a room dictate to a great extent the general location of the outlets. The outlets should be located to neutralize any undesirable cold drafts or radiation effects set up by a concentration of the heating or cooling load. The problem can be divided into' natural loads due to outside weather and internal heat loads. Natural Heating Load ' Winter. In winter the primary heating load is caused by exposed walls, ` windows and skylights. Heat is lost primarily through convection to these exposed surfaces. The convection currents or/cold drafts drop down the exposed surfaces and seriously impair the comfort conditions in ' the room, particularly at the floor level near the exposed, surfaces. The outlets should be located to counteract these down drafts. Two methods may be employed: 1. Direct counteraction of convection currents from cold surfaces can be obtained by locating the outlets to blow upward from beneath windows or exposed walls or to blow across the exposed wall. This method is desir able in small offices or bedrooms, or any location where people are seated or working near exposed surfaces. In rforthern climates, where the outside temperature may be constantly below 40 F, and the construction consists of uninsulated walls and single glass, this method of distribution is parr ticularly useful for the maintenance of comfort requirements. 2: High induction by ceiling or wall outlets may be employed to nullify the convection currents from exposed surfaces. If outside temperatures are consistently below 40 F, and the exposed surfaces are not well insu lated, the induction effort required for neutralization of the down drafts is so great that the air motion in the room may exceed comfort limits unless care is taken in selection and location of the outlet. Where comfort conditions are not critical as in factories for heavy manufacturing, warehouses, etc., satisfactory results can be obtained even in cold cli mates. For uninsulated walls and glass areas some supplementary heat . ing.is recommended. Wall diffusers, direct radiation or warm panels will satisfy these requirements for supplementary heating. . 3. The location of exhaust or recirculated air openings at the base of large areas of glass is sometimes effective in reducing cold downdraft into the occupied space. In this case, exhaust air quantity and velocity are important considerations in preventing the spill of cold air off the sill. Internal Heat Load .' If a concentrated source of heat is located at the occupancy level of the room, the heating effect may be countered by blowing the supply air toward the heat source or by locating an exhaust or return grille, ad jacent to the heat source. The latter method will.prove more economical, Air Distribution 729 as heat will be withdrawn at its source rather than be dissipated into the conditioned space. Where a lighting load is particularly heavy (five watts per square foot) and located high in a conditioned space, it may be economically desirable to locate the outlets below the lighting load. Warm air from the lights will stratify near the ceiling and can be removed by an exhaust or return fan, the former being advisable if the wet-bulb temperature of the air is above the outside temperature, and the latter being preferable if the wet-bulb temperature is below that of the out side air. Either method reduces the requirements for supply air. If the lamps are exposed, less saving can be realized than if enclosed, as a con siderable portion of the total energy is radiant. Duct Approaches to Outlets In order to obtain proper direction of flow and distribution of air from outlets it is necessary that the air stream approaching the outlet be of Fig. 4. Outlet Velocity and Air Direction Diagrams for Stack Heads , with Expanding Outlets Stack 14 in. x *6 in. Outlets 14 in. x 9 in. Stack Velocity 500 fpm . A. Rounded Throat and Round Back. B. Square Throat and Round Back. D. Square Throat and Cushion Chamber. . Rounded Throat and Back and 2 Splitters. - C. Square Throat and Back. F; Square Throat and Back and 6 Guide Vanes. uniform velocity over the entire duct connection and perpendicular to the face. Grilles and directional outlets cannot compensatefor improperapproach. Any attempt to secure a low face velocity and a high duct velocity by constructing an expanding chamber directly behind the grille is likely to be, unsuccessful because the enlargement angle in even a straight duct cannot be greater than 7 deg at each side if the stream is to fill the outlet without turbulence. - In elbow outlets or stack heads at the top of vertical stacks it is neces sary to provide splitters or guide vanes in the elbows regardless of the shape of the elbows whether of rounded, square or expanding types. Cushion chambers at the fop of the stack heads have no beneficial effect. 730 ,_____________________________CHAPTER 40 > 1946 Guide The direction; of flow, distribution and velocity (measured 12 in. from, outlet) of the air, based on tests 5, are shown in Fig. 4 for various types of, stack heads expanding from a 14 in. x 6 in. stack to 14 in. x 9 in. outlets, without grilles. The air velocity for each was 500 7pm in the stack below the elbow, but the direction of flow and the distribution patterns are generally indicative of performance obtainable with non-expanding elbows of similar shapes for a range of velocities 200 to 1400 fpm. Some of the conclusions drawn from the tests were: , 1. Experiments with various elbow outlets on the 14 in. x 6 in. vertical stack 3 with stack air velocities of 200 to 1400 fpm indicated that enlargement of the. outlet area, whether used in connection with square or rounded elbows, would not reduce either the angle of discharge (which was 20 to 30 deg above the horizontal) or the outlet velocity. The effect of the enlargement of the qutlet was mainly to. increase the reverse flow area in the lower part of the outlet, but in each case enlargement of the outlet reduced the static pressure in the duct below the elbow.. . 2; Splitters in the elbows had the effect of dividing the air stream into a number of streams flowing through rounded elbows and therefore lowered the angle of discharge, reduced or eliminated the reverse flow area, and made the outlet velocity quite uniform. . 3. Turning vanes having 2 in. inner and 1 in. outer radii located in the center of the elbow were found most effective in improving performance in regard to angle of dis charge, outlet velocity, and elimination, of reverse flow area. . 4. Pressure loss through stack heads may be reduced by use of splitters or turning vanes or by increasing the inner radius of an elbow. Considering the sum of the velocity and static pressure as a measure of the energy required to change the direction of the, air stream and.to deliver the air into the atmosphere, and considering the energy required for a plain fitting as 100 per cent, it -was found that turning vanes dropped the energy requirement of square type stack heads to 45 per cent. Splitters reduced the energy requirement to 90 per cent in long radius elbows and to 74 per cent in short radius turns. . * In expanding heads splitters reduced the energy requirement to 58 per cent.. Side Outlets in Air Ducts When air is supplied to a room from side outlets in horizontal ducts it is . necessary to use directive devices within.the duct at each outlet in order to obtain a uniform velocity of delivered air and to obtain a direction of flow perpendicular to the face of the outlet. In tests4 conducted with 3 iri. x 10 in., 4 in. x 9 in., and 6 in. x 6 in. outlets in a 6 in. x 20 in. hori zontal duct at duct velocities of 200 to 1400 fpm (in. the 6 in. x 20 in.. section) it was found that multiple curved deflectors produced the best fl6w characteristics. Vertical guide strips in the outlet were not so effective as curved deflectors. A single scoop type deflector at the outlet , did not improve the flow pattern obtained from a plain outlet and was therefore not found to be desirable. Figs. 5 and 6 show the flow patterns and outlet velocities for two 3 in. x 10 in. and two 6 in. x 6 in. outlets respectively, at 500 arid 1100 fpm duct velocities with outlets equipped with 1 in. and 13 in. extensions. The superiority of the multiple curved deflectors and the beneficial effect of the 13 in. extensions is evident. Throttling Dampers - In the case where multiple louvers or single blade dampers are used for throttling, considerable deflection, of the stream may result. This, is particularly true when the fins of the grille core are perpendicular to the damper blades. If the core has sufficient depth and the fins are parallel to the blades, there is a marked tendency to straighten the air stream,. ' although some deflection may still result. Dampers of special construction, as illustrated in Fig. 7, may be used to . . inaintain a constant direction of blow,- approximate distance of blow, and constant outlet velocity regardless of the dampens position. The r Air Distribution Table 2. Recommended Return Intake Face Velocities ' Intake Location . ., . Above occupied zone._______:................................ ......... Within occupied zone, not near seats....... ........................ Within occupied zone, near seats.-- .................................. Undercutting of doors (through undercut area)............. Velocity . . Over Gross Area Fpm \ 800 up 600-800 . 400-600 500-700 600 731 capacity of dampers diagrammed as A and B will be roughly in proportion to the position of the operating lever. They are particularly effective for cooling work with oversized grilles. The single leaf damper shown as C in Fig. 7 is objectionable in that it frequently results in a condition -, whereby two high velocity jets are created along the sides of the duct, or the air spills immediately downward on the occupants below the outlet. .. Another important consideration is the increased noise produced by high localized velocities. Obviously, uneven velocities over the outlet will cause the noise level to exceed die values obtained when face veloci ties are equalized. Also, excessive throtding of dampers to balance systems that are poorly designed will increase the noise level. RETURN AND EXHAUST INTAKES The factors that control the selection of return and exhaust intakes are: (1) velocity in occupied zone adjacent to intake, (2) permissible pressure drop through intake, (3) noise, and (4) location. 1. Air handled by an exhaust or return intake is drawn from all direc- ' tions* the velocity dropping off rapidly in every direction. The only locality where drafts, may prove objectionable .is adjacent to the intake. To prevent excessive air motion in' the occupied space due to the return system, it is advisable to compute the total air motion toward the exhaust ; opening as outlined in Equation 10 where A is the exhaust wall area in square feet. Recommended return intake face velocities are given in . Table 2. ' .. The withdrawal of air from a space through a return intake is a minor factor in control of the room air motion. The control of the, room air motion for the maintenance of comfort conditions depends on the proper selection of the supply outlets.. Thus the location of the return intake is not critical, nor the use of an elaborate return system-necessary, provided the air motion in the occupied zone adjacent to the intake does not exceed comfort limits." A single return intake or a few large intakes will prove . satisfactory provided no local high velocity zones are created. Table 3. Approximate Pressure Drops for Lattice Return Intakes Inches Water Gage--Standard Air . Free Area - 50 . 60 70 . 80 . 400 0.06 0.04 0.03 0.02 500 0.09 0.06 0.05 0.03 Face Velocity, Fpm 600 0.13 0.09. 0.07 0.05 700 0.17 0.12 0.09 0.07 '800 0.22 0.16 0.12 0.09 900 0.28 0:20 0.15 . 0.11 1000 0.35 0.24 0.18 0.14 \ A ir D is trib u tio n 1946 G uide f l C H A P T E R 40;;_______________ nSHBtmm ;lrT i'll ?HE_i_j :fi H -m i li t4 W ) -1 Al i-F 1iTUro MiSTUM OMtt l-i r rfe? 1 A \\ tinra aiii muot. ^TT % .j-r- r>.r-f SA3*UftO .01 X .5 734 CHAPTER 40 1946 Guide Air Distribution. 735 2.. The permissible pressure drop will depend on the choice of the designer. Table'3 gives pressure drop'through plain lattice intakes as a function of.free area and face velocity. . : .. . 3. The problem of noise generated by return intakes is the same as that generated by supply outlets, in computing resultant room noise levels from the operation of an air conditioning system, the return intake must be included as a part of the total grille area. The major difference, be tween the supply outlets and return intakes is in their frequent instal- lation at the ear level. When- located at ear level, it is recommended that the return intake velocity be not in excess of 75 per cent of the maximum permissible .outlet velocity. . . 4. Ceiling locations for outlets are recommended for bars, kitchens, lavatories, dining rooms, club rooms, etc., where warm air will gravitate to the ceiling level. Ceiling returns arc less desirable in spaces with severewinter exposure, and where stratification of cold air may take place at the'floor level. During the heating season the-air will tend to. short 736 '/ Hinges //Y/hA CHAPTER 40 1946 Guide f777777, Fig. 7. Effect of Various Damper Arrangements Designed for Straight Blow circuit between the supply and the ceiling exhaust or return intakes if supply velocities are low. Some circular ceiling outlets combine the supply and return openings " in a single unit. The return duct is in the center with the supply pattern - on the outside. This method gives best results for cooling applications. . The application for heating is more critical and requires consideration of ceiling height, amount of outside wall area, and number of air changes required. In extreme cases, stratification of warm air will cause short circuiting. Where the wall losses are a small part of the total, little difficulty is encountered with stratification. , Floor locations are used in heating installations for ceiling or side wall supply. When located so that air is drawn across exposed walls, the performance of the system may be somewhat improved. In general, floor locations tend to collect dirt and refuse. * , Wall and door locations, depending on their elevation, have the char acteristics of either floor or ceiling returns. In large buildings with many small rooms, the return air may be brought through door grilles or door undercuts into the corridors and then to a common return or exhaust. The pressure drop through door returns should not be excessive; otherwise the air distribution to the room may be seriously unbalanced with the opening or closing of the doors. Outward leakage through doors or windows cannot be counted upon for dependable results. In many cases, particularly in buildings with double glass or hollow glass block walls, forced return and relief systems are essential. SPECIFIC APPLICATIONS The two methods shown in Fig. 8 are suitable for application to theaters, churches, and auditoriums. In small or medium size theaters, it is sometimes practicable to use sidewall or front wall distribution. For the satisfactory operation of such a system during the winter heating period, the returns should preferably be located at the floor level and near Rear wall distribution Ceiling distribution Fig. 8. Air Distribution Methods for Theaters', Churches, and Auditoriums Air Distribution 737 Winter convection current Fig. 9. Distribution Methods for Small Rooms A Satisfactory for cooling. Unsatisfactory for heating in severe climates where the outside temperature is consistently below 40 F, and single glass and uninsulated walls are prevalent. B. Performance approximately that of A when small diffusers are used in bottom of the duct. C- Satisfactory for cooling. Satisfactory for heating if direct radiation is properly controlled. D. Satisfactory for both cooling and heating. The air should be discharged slightly away from the wall, and for low velocities should be fanned out parallel to the wall. - the front of the theater to prevent cold spots which may result from exposed wall convection or infiltration from exits. Return intakes may be located higher where the exits and stage have separate means'of heating. Diagrams shown in Fig. 9 illustrate distribution methods for small rooms with exposed walls, such as for offices, hospital rooms, hotel rooms, apartments, etc. The cooling performance of various distribution methods as applied to a small store is shown in Fig. 10. For specific requirements in connection with air distribution in marine applications see Chapter 49. . BALANCING SYSTEM In designing an air conditioning system, it should be the aim of the engineer to so proportion the duct system that proper distribution of air to every supply opening will be obtained. Since this is almost impossible to accomplish in practice, it becomes necessary to have means of balancing r ,-t t t t' crur-i i=-i -- ^T| Fig. 10. Small Store Cooling Distribution A. Rear Wall. High outlet velocity, satisfactory if properly designed; possibility of excessive air motion and drafts if used for wrong application. / . '' ' B. Front Wall. High outlet velocity, results same as A. . . C. Front and Rear Walls. Moderate room air motion, outlet blows should not impinge giving rise to down drafts in-center. ` - - D. Center. Moderate air motion, no impingement of, air streams. Good results. .. E. One Side. Moderate room air motion; should blow toward exposed wall. Good results. F. Ceiling. Low room air motion. Good results. Outlets should be selected of sufficient size to allow for blocking when not located in perfect, squares. 738 CHAPTER 40 _________ 1 - ,______ - - 1946, Guide the system to secure the desired amount of air in each space. There are a number of ways in which this may be accomplished, some of which are: 1. Dampers on the supply and return faces. 2. Dampers in the supply and return ducts. 3. Reducing the effective area of some supply openings by blank-offs. 4. Combinations of dampers in both supply and return air. . Dampers on the supply faces themselves are objectionable unless of special design, because of their effect on the air stream and noise. Damp ers on the return faces are frequently objectionable because of noise. A damper in the supply duct at some distance back of the supply opening forms a very satisfactory means of regulating the flow without disturbing distribution across the supply opening face. A damper in the return air . duct has the advantage over one immediately behind the face in that it does not tend to create high localized velocities through the face as the latter might do if nearly closed. Blank-offs consisting of pieces of sheet metal covering a portion of the supply opening face are frequently used.' Results are often unsatisfactory due to high velocity through the remain ing open portion of the grille. Determination of just what is required is a matter of experiment, and the balancing of the system is not nearly so conveniently accomplished as with dampers. Dampers in both supply and return air form the most flexible means of controlling the supply to the room and the static pressure within the room. When feasible, these dampers, particularly those in the supply ducts, should be a substantial distance from the supply opening, and ahead of the acoustical duct lining if used. Due consideration should also be given to the use of the several volume control and' uniform distribution devices now available. . See Catalog Data Section. ' REFERENCES '-Controlof Air Streams in targe Spaces, by G.L: TuveandG. B. Priester (A.S.H.V.E. Transactions. Vol. SO. 1944. p. 153). 2~Air Distribution, by W. L. McGrath, unpublished private paper. ' *-A.S.H.V.E.'Research Rbport No. 1155--The Performance of Suck Heads, by D.W. Nelson. D.H. Krans and A. F. Tuthill (A.S.H.V.E. Transactions, Vol. 46, 1940, p. 205). ' A.S.H.V.E. Research Report No. 1226--Performance of Side Outlets on Horizontal Ducts, by D. W. Nelson and G. E. Sroedberg (A.S.H.V.E. Transactions, VoI.` 49, 1943, p. 58). . BIBLIOGRAPHY A.S.H.V.E. Research Report No. 1076--Air Distribution from Side Wall Outlets, by D. W. Nelson and D. J. Stewart ^A.S.H.V.E. Transactions, Vol. 44, 1938, p. 77).. A.S.H.V.E. Research Report No. 1140--The Use of Air Velocity Meters, by G. L. Tuve, D. K. Wright, Jr. and L. J.. Seigel (A.S.H.V.E. Transactions, Vol. 45, 1939, p. 645). .- .. a A.S.H.V.E. Research Report No. 1162--Air Flow Measurements at Intake and Discharge Openings and Grilles, by G. L. Tuve and D. K: Wright, Jr. (A.S.H.V.E. Transactions, Vol. 46, 1940, p. 313). ' .` . A.S.H.V.E. Research Report No. 1165--Development of Instruments for the Study of Air Distribution in Rooms, by A. P. Kratz, A. E. Hershey and R. B. Engdahl (A.S.H.V.E. Transactions, Vol. 46, 1940, p. 351). ,. A.S.H.V.E. Research Report No. 1204--Entrainment and Jet-Pump Action of Air Streams, by G. L. Tuve, G. B. Priester and D. K. Wright, Jr. (A.S.H.V.E. Trans actions, Vol. 48, 1942, p. 241). . Air Flow at Discharge of Fan Pipe Lines in ^lines, by, G. E. McEIroy, (Bureau of\ Mines, Report of Investigations--No. 3730, November, 1943). ' Modern Air Conditioning, Heating and Ventilating, ,by W. H. Carrier, K. E. Cherne, and W. A. Grant (Pitman Publishing Corp., New York, N. Y., 1940). . The Rationale of Air Distribution and Grille Performance, by C. O. Mackey {Refriger ating Engineering, Vol. 35, No. 6, June .1938, p. 417). . CHAPTER 41 2>ucl Pressure Losses, Friction Losses, Friction Loss Chart, Equiva lent Circular and Rectangular Diicta, Elbow Friction Losses, Proportioning the Losses, Duct Sizes, Procedure for Duct Design, Velocities, Main Trunk Ducts, Velocity Method, Equal Friction Method, Duct Construction Details, Duct Heat Loss and Insulation , ., . THE theoretical resistance of an air handling system can be computed , from the methods and data given in this chapter. The actual resistance for any given installation, however, may vary considerably from the calculated resistance because of variation in the smoothness of materials, the type of joints used and the ability of the mechanics to fabricate in accordance with the design. It is best to select fans and motors of sufficient size to allow a factor of safety. Volume dampers should be installed in each branch outlet to balance the system, and the necessary' allowance for this balancing, should be made in calculating the pressure loss in the system. . The flow of air due to.<large pressure differences is most accurately stated by. thermodynamic formulae for air discharge under conditions, of adiabatic flow, but such formulae are complicated, and the-error, occasioned by the assumption that the gas density remains constant throughout the flow may be considered negligible when only such pressure differences are involved as occur in ordinary heating and ventilating practice. '' The rate of flow of air in a duct may be obtained.from Equation 1, which is developed as Equation. 70 in Chapter 4: Vm = 1096.5 . (0 where. Vm = velocity of fluid, feet per minute. hw = velocity head or pressure, inches of water. pa = density of air, pounds per cubic foot. ' .. .` For dry air (69.41 F and 29.921 in. Hg barometer) pa = 0.075 lb per cubic foot *. ' Substituting this value in Equation 1: '. ' Vm = 1096.5 0*"_------ 4005 -y/ Aw (2) The relation of air velocity and velocity head expressed in Equation 2 is shown . diagrammatically in Fig. 1 for dry air at 69.41 F and 29.921 in. Hg barometer. The drop in pressure in air distributing systems is due to the dynamic . losses and the friction losses.. The friction losses for turbulent'flow (which . occur in all practical air flow problems) are due to the friction of air . against the sides of the duct and to internal friction between air molecules. ' The dynamic losses are those due to the change in the direction or in the velocity of air flow. ' . Dynamic losses occur principally at the entrance to the piping, in the elbows, and-wherever- a changein velocity occurs. The. entrance loss is the difference between the actual pressure required to produce flow and the pressure corresponding to the flow produced; it may vary from 0.1 to . x 739 ' . 740 CHAPTER 41 1946 Guide 0.5 times the velocity head. The pressure loss in elbows must also be allowed for in the design. , FRICTION LOSSES Friction loss in straight ducts is most readily calculated by means of the Air Friction Chart, Fig. 2, which was developed by recent research at the A.S.H.V.E. Research Laboratory 2. This chart is constructed from the basic flow equation: ' ; y Af=/-irv , where ' hi = head loss due to friction, in feet of fluid flowing. I -- length of conduit, feet. D = inside diameter of conduit, feet. . V = fluid velocity, feet per second. g = acceleration due to gravity, 32.17 fps per second. , / = a non-dimensional friction coefficient which, for ventilation work depends upon Reynolds Number and the relative roughness of the conduit. Appropriate . values of / were taken from'the work of Moody 3. / - . The air friction chart is based on standard air at 29.921 in. of mercury barometer and 70 F, flowing through average clean round galvanized metal ducts having approximately 40 joints per 100 ft. For the average application, it should prove sufficiently accurate, without corrections, for any air temperature from_50 F to 90 F, for any relative humidity, and for any normal variation in barometric pressure. For widely varying air pressures or temperatures or for unusual duct conditions, the friction values obtained from the chart should be corrected. If precise results are desired, corrections should be .made by use of Equation 3, with the appropriate value of the coefficient of friction, /. However, the following approximate equations2 are presented and will be found sufficiently accurate for most purposes. . For perfectly'smooth ducts: ho = h3 (4) For average ducts, h> = As (y-) ("wO ' For very rough ducts, ho = hs _ (6). where . h = friction loss. , p = density. . . {j. = absolute viscosity. h, p and p may be in any consistent units. erating and standard conditions respectively. . ' . . ' Subscripts o and s refer to actual, op The absolute viscosity of dry air at various temperatures is given in Fig. 3. The effect of relative humidity on viscosity may be neglected. Example 1. Assume that it is desired to circulate 10,000 cfm of air through 75 ft'of 24 in. diameter pipe. Find 10,000 cfm on the left scale of Fig. 2 and move horizontally right to the diagonal line marked 24 in. The other intersecting diagonal shows that the . velocity in the pipe is 3200 fpm. Directly below the intersection it is found that the fnction per 100 ft is 0.50 in.; then for 75 ft the friction will be 0.75 X 0.50 = 0.38 in. In a like manner any two variables may be determined by *the intersection of the lines representing the other two variables. Air Duct Design 741 0.01 0.02 0.03 0.04 . 0.06 0.08 0.1 0.2 0.3 0.4 0.6 0.8 1.0 ' VELOCITY HEAD. INCHES OF WATER 2.0 Fig. 1. Relation Between Velocity and Velocity Head for Dry Air 3.0 Circular Equivalents of Rectangular Ducts ` An air handling system is usually sized first for round ducts and, if rectangular ducts are desired, their sizes are selected to provide air carry ing capacities equivalent^ those of the round ducts originally selected. Table 1 gives directly the rectangular duct sizes equivalent to each size of circular duct in friction and capacity. The values in this table were obtained from- the equation: d = 1.265 . }/ a + b - (7) where . a = one side of rectangular duct feet or inches. ' b = other side of rectangular duct, feet or inches. - ' d = equivalent diameter of round pipe for equal friction per foot of length to carry the same capacity, feet or.inches. . Rectangular'equivalents of round ducts are also, given in the curves of Fig. 4 which are plotted from data based on Equation 7. To use the chart, locate the diagonal curve'giving the diameter of the round duct. The width and height of an equivalent rectangular or square duct may then be read as the abscissa and the ordinate of any point on the curve. Multiplying or dividing the length of each side of a pipe by a constant is the same as multiplying or dividing the equivalent round size by the same constant. Thus, if the circular equivalent of an 80 x 24-in. duct is required, it will be twice that of a 40 x 12-in. duct, or 2 X 23.3 = 46.6 in. A comprehensive study of equivalent duct sizes, is to be made by the A.S.H.V.E. Research Laboratory in the near future for the purpose of determining whether Table 1 and Fig- 4 should be revised. Elbow Friction Losses It is customary to express the dynamic and friction losses in elbows as equal to a number of diameters of round pipe, or a number of widths of rectangular pipe, or equivalent length of duct4. The curves in Fig. 5 give the number of diameters or widths Of pipe which have a frictional 742 CHAPTER 41 ___________ 1946 Guide ; Air Duct Design 743 CU FT OF-AIR PER MINUTE .01 .02 .03.04 06 1)8.1 .2 .3 .4 .6 .8 I 2 34 , FRICTION LOSS IN INCHES OF WATER PER 100 FT Fig. 2. Friction of Air in Straight Ducts (Based on Standard Air at 29.921 In. of Mercury barometric pressure and 70 F flowing through average: clean, round, galvanized metal ducts having approximately 40 joints per 100 ft.) resistance equivalent to the pressure drop, in the elbows. Curves B and C are based on tests of round and square elbows 6 of ordinary good sheet metal construction. Values obtained from Curve A should be used when there is any doubt as to quality of duct construction. It is suggested that tills curve be used for rectangular elbows and five-piece elbows as it will thus allow an ' additional factor of safety without seriously affecting the design. As indicated in Fig. 5, long radius elbows will offer much less-re sistance to the flow of air than short radius elbows. Experience has . shown that good results may be expected when the radius to. the center . of the elbow is 1.5 times the pipe diameter or duct width parallel-to the radius. Examination of the curve will indicate that little advantage is to be gained by selecting elbows having a centerline radius of more than two diameters6. Elbows having a radius of more than three diameters show a slightly increased resistance due to the increased length of pipe but, when . used, they reduce the over-all resistance of the system and therefore should / not be avoided. -. Where space conditions necessitate the use of short radius or miter elbows in square or rectangular duct work, turning vanes should be used to reduce the pressure losses. Rough or raw edges on the vanes should be avoided to prevent objectionable noise. Typical types of vanes are shown in Table 2 with the total equivalent length of duct that may be used in ' estimating the resistance of each type. .' The pressure loss through-elbows of less than 90 deg may be assumed to be directly proportional to the ratio of the angle through which the Table 1. Circular Equivalents of Rectangular Ducts for Equal Friction3 Sms RlCTANOtTLAB 8 8.5 9 9.5 10 10.5 11 11.5 12 12.5 13 13.5 14 14.5 15 15.5 Due* 16 3* 3.54 4.5 5 ' 5.5 5.2 5.4 5.5 5.7 5.8 5.9 6.0 6.2' 6.3 6.4 6.5 6v6 6.7 6'8 6.9 7.0 5.7 5.9 6.0 6.2 6.3 6.5 6.6 6.7 6.9 7.0 7.1 7.3 7.4 7.S 7.6 7.7 6.1 6.3 6.5 6.7 6.8 7.0 7.1 7.2 7.4 7.5 7.7 7.8 7.9 8.1 8.2 8.3 6.5 6.7 6.9 7.1 7.2 7.4 7.6 7.7 7.9 8.0 8.2 8.4 8.5 8.6 8.7 8.9 6.9 7.1 7.3 7.5 7.7 7.8- 8.0 8.2 8i3 8.5 8.7 8.8 8.9 9.1 9.2 9.4 7.3 7.5 7.7 7.8 8.1 8.3 8.5 8.6' 8.8 9.0 9.2 9.4 9.5 9.6 9.8 9.9 7.1 7.8 8.4 9.0 9.5 10. i AddiUonal dza: 4 X 6 - 4.9: 4X6 = 5.4; 4X7 = 6.8; 5 X 3 = &6; 5 X 6 = 6a; 5 X 7 = 6J. ` . 744 ___________ C H A P T E R 41 jSftAfmV.cx\-`jr '-* Table 1. Circular Equivalents op Rectangular Ducts for Equal Friction--(Continued) Bibb Rectanqulab 4 ' ' 5 .6 7 8 9 Duct '8 9 10 u 6.1 ' 6.9 6.5 7.3 6.8 7.7 7.1 8.0 7.6 8.2 8.8 8.0 8.7 9.3 9.9 8.4 9.2 9.8 10.4 8.8 . 9.6 10.2 10.9 . 12 13 14 15 7.4 8.3 9.2 10.0 10.7 11.4 7.6 8.7 9.6 10.4 11.1 11.8 7.9 8.9 9.9 10.8 11.5 12.3 8.2 9.2 10.2 11.1 11.9 12.7 16 17 18 19 . 20 22 24 ' 26 28 30 32 . 34 .8.4 8.6 9.5 9.8 10.5 10.8 11.4 11.8 12.3 12.6 13.1 13.5 8.9 10.0 11.1 12.1 13.0 13.8 9.1 10.3 11.4 12.4 ,13.3 14.2 9.3 10.5 11.6 12.7 13.6 14.5 9.7 11.0 12.1 13.2 14.2 15.2 10.0 11.4 12.6 13.8 14.8 15.8 10.4 11.8 13.1 14.3 15.4 16.4 ' 10.8 12.2 13.5 14.8 15.9 17.0 11.0 12.6 13.9 15.2 16.4 17.5 11.3 12.9 14.3 15.6 16.9 18.0 11.6 13.2 14.7 16.1 17.3 18.5 36 ' 38 40 42 11.9 12.2 13.6 15.1 13.9 . 15.4 16.4 10.8 17.7 18.2 19.0 19.4 12.5 14.3 15.7 17.2 18.6 19.8 12.7 14.5 16.1 17.6 19.0 20.3 44 46 48 50 52 54 56 58 60 62 64 66 13,0 13.3 13.5 13.7 13.9 14.1 14.3 14.6 14.8 15.1 15.4 15.7 o 15.9 16.1 16.3 16.6 14.7 15.0 15.1 15.3 16.8 17.0 17.3 17.5 16.4 16.7 17.0 17.3 17.6 17.9 18.2 18.4 18.7 19.0 19.2 19.5 18.0 19.4 20.1 18.4 19.8 21.1 18.7 20.1 21.5 19.0 20.4 21.9 19.2 20.8 22.2 19.6 21.1 22.6 19.9 21.5 22.9 20.2 21.8 23.3 20.4 22.1 23.6 20.7 22.4 24.0 21.0 22.7 24.3 21.2 23.0 ' 24.6 10 11 11.0 11.5 12.1 12.0 12.6 12.5 13.1 12.9 13.6 13.4 14.1 13.8 14.2 14.6 15.0 14.5 15.0 15.4 15.8 15.4 16.2 16.1 16.9 16.8 17.6 17.3 18.3 18.0 19.0 18.5 19.S 19.1 20.1 19.6 20.7 20.1 - 21.2 20.6 21.7 21.1 22.2 21.6 22.7 22.0 23.1 22.4 23.6 22.8 24.1 23.2 24.5 23.6 24.0 24.4 24.7 24.9 25.3 25.7 26.1 25.1 25.5 25.9 26.2 26.5 26.9 27.3 27.7 12 13 13.2 13.7 14.3 14.7 14.3 14.9 15.3 15.2 15.7 16.1 16.5 15.8 16.3 16.8 17.2 17.0 17.6 17.8 18.5 18.5 19.3 19.2 20.0 19.8 20.7 20.5 21.4 21.1 22.0 21.6 22.6 22.2 23.2 22.8 ' 23.8 23.3 24.4 23.8 24.9 24.3 24.8 25.2 25.7 25.4 25.9 26.4 26.9 26.2 26.6 27.0 27.4 27.4 27.8 28.3 28.7 27.8 28.2 28.6 29.0 29.1 29.5 29.9 30.3 14 . 15 16 17 18 15.4 16.0 16.5 16.5 17.1 17.6 17.0 17.6 18.2 18.7 17.4 18.1 18.7 19.2 19.8 17.9 18.6 19.2 19.8 20.4 18^4 19.0 19.7 20.3 20.9 19.2 19.9 20.6 21.3 21.9 20.0 20.8 20.8 21.6 21.5 22.3 22.2 23.0 22.8 23.8 21.5 22.2 22.9 23.5 22.4 23.1 23.8 24.4 23.1 23.9 24.6 25.3 23.9 24.7 25.4 26.2 24.6 25.4 26.2 26.9 24.2 24.8 25.4 25.9 25.1 25.8 26.4 26.9 26.0 26.7 27.3 27.9 26.8 27.5 28.2 28.8 27.7 28.4 29.1 29.8 26.5 27.0 27.5 28.0 27.5 28.5 28.1 -,,29.1 28.6 29.6 29.2 30.3 29.5 30.1 30.5 31.3 30.3 31.0 31.6 32.2 28.5 29.0 29.5 30.0 29.6 30.1 30.6 -31.1 30.7 31.2 31.7 32.2 ' 31.8 32.3 32.8 33.3 . 32.9 33.4 33.9 34.4 30.5 30.9 31.3 31.7 31.6 32.1 32.6 33.0 32.7 33.2 33.7 34.2 33.8 34.3 34.8 35.3 34.9 35.4 35.9 36.4 19 20 21 20.9 21.5 22.5 23.5 24.4 25.3 26.2 27.0 27.7 28.5 29.2 29.9 30.7 31.2 31.9 32.5 33.1 33.8 34.4 34.9 35.4 36.1 36.6 37.1 37.6 22.0 23.1 24.0 25.1 23.6 24.7 25.7 26.0 26.8 27.7 28.5 26.6 27.5 28.4 29.2 29.3 30.0 30.8 31.4 30.0 30.8 31.6 32.2 32.1 . 32.9 32.8 ' 33.8 33.4 34.3 34.1 35.0 34.7 35.3 .35.9 36.4 35.6 36.3 36.9 37.4 37.1 37.7 36.2 38.7 38.1 38.7 39.2 39.8 22 24.2 25.2 26.3 27^3 28.2 29.1 30.0 30.8 31.5 32.4 33.0 33.7 34.6 35.2 35.9 36.5 37.2 37.8 38.4 39.1 39.6 40.2 40.8 24 26.4 27.5 28.5 29.5 30.5 31.3 32.2 33.1 33.9 34.5 35.3 36.2 37.0 37.6 38.3 38.9 39.6 40.3 40.9 41.6 42.2 42.8 '. 1946 G u id e a A ir D uC t D esign Table 1. Circular Equivalents of Rectangular Ducts for Equal Friction--(Concluded) SlDB Bidb Riotakquiab 26 28 30 * 32 34 36 38 40 42 44 46 48 RlCTANGCLAa 50 54 60 66 72 78 84 88 Duct Duct 26 28.6 28 29.7 30.8 30 30.7 31.9 33.0 50 55.0 52 56.1 54 57.2 59.4 32 34 36 38 40 42 44 46 48 50 52 54 , 56 ' 58 60 62 64 66 68 70 72 31.7 i 32.9 34.1 35.2 32;7 33.9 35.1 36.3 37.4 33.7 34.9 36.1 37.3 38.5 39.6 - 34.6 35.3 36.0 35.9 36.7 37.6 37.1 38.0 39.0 38.4 39.3 40.3 39.5 40.5 41.5 40.7 41.7 42.7 41.8 42.9 44.0 44.0 45.1 46.2 / 56 58 60 62 64. 66 36.9 37.8 . 38.5 38.5 39.9 39.3 40.8 40.0 - 41.5 41.2 42.2 43.0 42.5 43.5 44.4 43.7 44.8 45.6 44.9 46.0 46.9 46.1 47.2 48.1 47.2 48.4 49.3 48.4 49.5 50.5 50.6 51.6 52.8 68 70 72 39.2 40.0 40.7 40.8 41.6 42.4 42.3 43.1 44.0 43.8 44.7 45.5 45.2 46.1 47.0 46.5 47.9 49.1 50.4 51.6 52.9 54.0 47.5 48.9 50.1 51.3 52.5 53.8 55.0 48.4 49.9 51.1 52.3 53.5 54.8 56.0 74 76 , 78 41.3 42.1 42.7 43.0 43,8 44.5 44.6 45.4 46.1 46.2 47.0 47.8 47.7 48.5 49.3 49.1 50.0 50.9 50.6 51.5 52.3 52.0 52.9 53.8 S3.3 54.2 55.6 S4.6 55.5 56.4 55.9 56.8 57.7 57.0 58.0 58.9 80 82 84 43.4 45.1 44.0 ' 45.8 44.7 46.5 46.8 47.3 48.2. 48.4 49.2 50.0 50.0 50.9 51.6 51.7 52.4 53.1 53.0 53.9 54.7 54.5 55.4 56.2 55.9 56.8 57.6 57.2 58.1 59.1 58.5 59.4 60.4 59.7 60.6 . 61.6 . 86 88 -90 45.3 46.0 46.5 47.2 47.8 48.4 48.9 49.5 50.1' 50.7 51.3 51.9 52.2 52.9 53.7 53.8 54.5 55.4 55.5 56.2 57.0 56.9 57.7 58.7 58.4 59.1 60.0 59.9 60.6 61.3 61.3 62.1 63.0 62.6 63.5 64.5 92 94 96 58.3 60.5 59.3 61.6 60.3 62.7 66.0 61.3 62.2 63.2 63.7 64.7 65.7 67.1 68.2 69.3 72.6 64.1 65.0 65.9 66.6 67.6 68.5 70.3 71.3 72.3 73.7 74.8 75.9 79.2 66.8 69.4 73.3 76.9 80.3 67.6 70.3 74.2 77.9 81.4 68.4 71.2 75.2 78.9 82.5 85.8 69.2 70.1 70.9 72.1 73.0 73.8 76.1 77.1 78.0 79.9 80.9 81.9 83.6 84.6 85.6 86.9 88.0 89.1 92.4 71.7 72.5 73.3 74.6 75.5 76.3 78.9 79.8 80.6 82.9 83.9 84.7 86.6 87.5 88.5 90.2 91.2 92.2 93.5 94.6 95.7 96.8 97.9 74.1 77:i 81.4 85.6 89.5 93.2 96.7 99.0 74.8 77.8 82.2 86.5 90.4 94.2 97.8 100.1 75.5 78.7 83.0 87.4 91.3 95.2 98.8 101.2 \ ,\ 746 CHAPTER 41 . 1946 Guide . turn is made. The resistance will'vary widely for the large degree turns depending upon the aspect ratio and the length of straight pipe between the elbows,, but for practical purposes, it may be assumed that the ratio remains proportional to the angle through which . the turn is made. Reverse 90 deg elbow turns should be avoided wherever possible but, Air Duct Design 747 PROPORTIONING THE LOSSES The entrance loss through the outside air intake louvers will vary with . the design of the louvers and method of connection to the system. The louvers and connecting duct will have a friction resistance of from 0.25 to 1.00 times the velocity pressure. Therefore, the total entrance loss will', vary from 1.25 to 2.00 Aw. Common practice is to use 1.5 Aw for a 75 per cent free area louver with connecting duct haying 15 deg tapered sides. Wherever air passes through a plenum space having a negligible velocity, allowance must be made for the loss in velocity'head. This may be taken as the .velocity head corresponding to the difference in velocities in the plenum, and the duct. Where the ducts are very smooth with long transformation fittings, a regain in static pressure is sometimes allowed, Fig. 4. Rectangular Equivalents op RouNd Ducts where used, the, friction indicated in Fig. 5 should be doubled for the second elbow. Additional tests are needed on the loss of pressure in elbows and other types of duct fittings in order to reconcile difference . between values shown in Fig. 5 and results of more recent tests shown in Table.2. A study of this subject will be undertaken at the A.S.H.V.E. Research Laboratory for the purpose of obtaining such data. . CENTERLINE RADIUS IN PER CENT OF PIPE DIAMETER OR WIDTH 5. Loss. . Fig. of Pressure in Elbows " but ordinary construction does not warrant a consideration of this factor, and it is customary to neglect it. When it is allowed, the regain is esti mated at one-half the difference between the1 velocity pressure at the fan outlet and at the last .run of pipe. ' '' Other losses of pressure occur through the heating units, at the air washer and at air-filters. In the design of an ideal duct system, all , factors should be considered and the air velocities proportioned so that ' the resistance will be practically equal in all ducts regardless of length. DUCT SIZES , Ducts and flues for gravity circulation must be sized so that the friction' loss will not exceed 50 per cent of the available chimney effect due to the temperature and height of the column of heated air. Duct systems for mechanical circulation may be sized so as t<? have much higher pressure losses than gravity systems. The total pressure of these systems is limited to the pressure which the fan will produce. The general, rules to be followed in the design of a duct system are : - 1. The air should be conveyed as directly as possible at reasonable velocities to obtain the results desired with greatest economy of power, material and space. :* . 748 CHAPTER 41 1946 Guide 2. Sharp elbows and bends should be avoided unless turning vanes are used. . 3. Transformation pieces should be made as long as possible. The angle between the sides and axis of the duct should never exceed 30 deg and, where possible, 15 deg should be made the maximum. .. 4. Especial care should be taken to maintain a true cross-section and not to restrict the air flow either in transformation pieces or in elbows. 5. Rectangular ducts or flues should be made as nearly square as possible. Good practice limits the ratio between the long side and the short side to 3 to 1. In no case should this ratio exceed 10 to 1. 6. Wherever possible, ducts should be constructed of smooth material such as sheet Table 2. Effect of Vanes on Pressure Loss of 7-inch Square Ventilating Duct* - Expressed in feet of total equivalent length of duct {ELD) - For more complete data see A.S.H.V.E. Research Report No. 1216--Effect of Vanes in Reducing Pressure Loss in Elbows in 7-Inch Square Ventilating Duct, by M. C. Stuart, C. F. Warner and W. C. Roberts (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 409). . Note A: - Vane A made up of a large number of small splitters; B made up of a email number of large splitters bent on a large radius; C hollow vanes having different outside and inside curvature; and D four splitters with R/W -- 0.4. Elbow same as D except 2 in. trailing edge on the end of each splitter, ELD fa feet.= 17.0. Note B: The air velocity has no effect on the loss of elbows when the loss is expressed as equivalent length of duct. - . metal. Where.masonry ducts are used, proper allowance for the surface friction coeffi- dent should be made. ' 7. The use of furred spaces, spaces between joists, etc., should be avoided unless lined with sheet metal. Procedure for Duct Design The general procedure for designing a duct system is outlined in the several items listed herewith: ' 1. Study the plan of the building and draw in roughly the most convenient system of ducts, taking cognizance of the building construction, avoiding all obstructions in steel work and equipment, and at the same time maintaining a simple design. ': 2. Arrange the positions of duct outlets to insure the proper distribution of air. 3. Divide the building into zones and proportion the volume of air necessary for each zone. , .. . . . ' 4. Determine the size of each outlet, based on the volume as obtained in the preceding . paragraph, for the proper outlet velocity'and throw. .. Air Duct Design 749 5. Calculate the sizes of all main and branch ducts by either of the following two methods: . Velocity Method. Select the velocity in the various sections, reducing the velo city from the point of leaving the fan to the point of discharge to the room. .In this case the-pressure loss of each section of the duct is calculated separately and the total loss found by adding together the.losses of the various sections of the continuous run. . Friction Pressure Loss Method. Proportion the duct for equal friction pressure loss per foot of length. . 6. Calculate the friction for the duct offering the greatest resistance to the flow of air, which resistance represents the static pressure which must be maintained at the fan outlet or in the plenum space to insure distribution of air in the duct system. The duct having the greatest resistance will usually be that having the longest run, although not necessarily so. Air Velocities The air velocities given in Table 3 have been found to give satisfactory results in engineering practice. Where the higher velocities are used, the ducts should be cross-braced to prevent breathing, buckling or vibration, Table 3. Recommended and Maximum Duct Velocities Designation Recommended Velocities, fpm Maximum Velocities, fpm Residences . Schools, Theaters, Public Buildings Industrial Buildings Residences Schools. Theaters, Public Buildings Industrial Buildings Outside Air Intakes3 Filters3 Heating Coils3 700 250 450 800 300 500 1000 350 600 800 300 500 900 1200 350 350 600 700 Air Washers Suction Connections Fan Outlets.. 500 500 500 700 800 1000 .1000-1600 1300-2000 1600-2400 500 900 1700 500 500 1000 1400 . 1500-2200 1700-2800 Main DuctsBranch Ducts Branch Risers 700-900 -600 500 1000-1300 1200-1800 800-1000 1100-1400 1300-2000 600-900 800-1000 700 800-1000 1000-1200 600-700 800 650 800-900 1000 These velocities are for total'face area, not the net free area. and should be constructed of heavier gage metal. At the higher velocities it is particularly important to.design the ducts for minimum resistance. As high velocities at one point offset the effect of proper design in all other parts of the system, emphasis should be placed on the importance of air velocities, elbow design, location of dampers, fan connections, grille and register approach connections, and similar details. For industrial buildings, noise is seldom given much consideration, and mairf duct veloci ties as high as 2800 or 3000 fpm are sometimes used but, when these velocities are used, due consideration should be given, to duct design, resistance pressure, fan efficiencies and motor horsepower. For department stores and similar buildings, 2000 to 2200 fpm are sometimes used in main ducts where noise is not objectionable and space conditions warrant it. Where high velocity diffusing outlets are used, the duct velocity should not be less than the throat velocity of the diffusers, as dynamic losses 750 , - CHAPTER 41 1946 Guide occur wherever velocities are stepped up or down. One recent trend'in grille design is toward the use of much higher grille and branch duct velocities. Some installations have been made with velocities,as high as 1600 fpm in branches and through the net area of grilles, but many of these have proven unsatisfactory because of noise and drafts. Grille manufacturers publish selection tables which size the grilles for volume of air, temperature differential, and distance of throw. In following these, tables, maximums should be avoided and the manner in which the duct connects to the grille should be given careful consideration. Most of the selection tables are based on straight approach to the grille. Elbow connections to supply grilles should be provided with turning vanes to equalize the face velocity. See Chapter 40 for a discussion of grilles. Fan outlet velocities are discussed in Chapter 32 and will not be dealt with here except to indicate that fan noises should be given proper consideration. . Main Trunk Ducts Main trunk ducts with branches are commonly used to convey the air from the fan to the grille or register outlets in preference to. individual ' ducts from the fan to these outlets. The velocities in these ducts and branches vary according to the nature of the installation and the degree of quietness desired. The recommended velocities in Table 3, with good construction, should give satisfactory results.. The maximum velocities indicated should not be used except where noise is not a deciding factor. Velocity Method - *. The velocity method of designing a duct system involves the arbitrary selection of velocities for various sections of the duct system with the highest velocities at the fan and progressively lower velocities toward the duct openings to the room. To find the total static pressure against which the fan must operate, the static pressure loss of each section must be calculated separately and the total. loss found by adding the indi vidual losses of the various sections of the run having the highest resis tance. Usually this is the longest run but in some cases a shorter run may have more elbows, transformations, booster heaters, etc., which will cause it to have a higher resistance pressure. This method requires judgment. and experience in choosing the proper velocities to approach equal friction for all lengths of run but many engineers believe that the velocity method is handier to use than other methods and will give satisfactory results for most practical applications. The air velocities given earlier in this chapter are helpful in choosing proper velocities. Adjustable dampers or splitters are used to regulate air quantities delivered. Equal Friction Method - ' The equal friction method of design is sometimes preferred because it does not require nearly so much judgment and experience in selecting the proper velocities in the.various sections of a system. The usual procedure in this method of design is to select the main duct velocity to be con sistent with good practice from a standpoint of noise for a particular type . of building. This velocity should be less than the fan outlet velocity. All main ducts and branch ducts are sized for equal friction by the. use of Fig. 2, and Table 1 or Fig. 4. . " In.cases where the fain or factory assembled air conditioning unit has a limited external resistance, it is necessary to divide the available resistance Air Duct Design 751 by the total equivalent length of the longest or most complicated run of duct to determine the resistance per 100 ft and then to size all ducts at this resistance value: This will automatically determine the duct veloci ties and give the desired total duct resistance. A further refinement, which is sometimes used in large systems, is to size each branch duct so that it has a resistance equal to the resistance of the main system at the point of juncture. Even when this refinement is added, regulating, dampers are recommended in each branch. . After the duct system is designed the frictional resistance is calculated and tabulated together with the resistance of all component parts. The fan is then selected for the required volume of air, static pressure and outlet velocity. ' : Example. 2. Fig. 6 shows a typical layout of an air distribution system which is applicable for.ventilation of hotel dining rooms and offices. The volume of air in cubic feet per minute for. the room is determined on the basis of the number of air changes per hour required. In the example shown, the room ventilated is a hotel dining room 135 ft . x ft*. A 73^-min air change (8 air changes per hour) is assumed for proper ventilation, giving 22,935 cfm as the air required. . The free area of the outdoor air inlet is based on a velocity of 1000 fpm or 22,935 -s- 1000 22.94 sq ft. The main duct velocity selected from Table'3 is 1250 fpm which gives a main duct area of 22,935 -5- 1250 = 18.354 sq ft (60 X 44 in.). From Table 1 a 60 X 44 m. duct is approximately equivalent to 56 in. diameter. Referring to Fig. 2, a volume of 22,935 cfm through a 56 in. diameter duct gives a resistance of 0.033 in. per 100 ft. The amount of air to be handled by each section of pipe is shown in Fig. 6, and by locating each of these values on the 0.033 in. friction line, the round pipe sizes are obtained and then, referring to Table 1, the equivalent rectan gular sizes are selected as shown in Table 4. . The pressure at the outlets nearest' the fan will'be greater than at the pipes farther along the run so that the former will tend to deliver more than the calculated amount of air. To remedy this condition,'volume regulating dampers should be located at the base 752 CHAPTER 41 1946 Guide Table 4. Pipe Sizes for Example 2a' Volume of Air (CFM) , 22,935 12,510 10,425 8,340 6,255 4,170 2,085 Diameter of Pipe (Inches) 56 45 42 39 35 29.5 23 . - Equivalent Size of Rec tangular Duct (Inches) 60 x 44 58 x 30 50 x 30 42 x 30 42x24 30 x 24 30 x 15 . . - ^Velocity through grilles (not shown) to be approximately 300 fpm. of each riser, or in each branch duct, and adjusted for proper distribution. At points where branches leave the main it may 6e advisable, depending upon the nature of the installation, to install adjustable splitters similar to those shown in Fig. 6 where the main duct divides into the 58 x 30 in. and 50 x 30 in. branches. . Resistance Losses Jot the System (1) Outdoor air intake, 1000 fpm velocity (1.5 heads X 0.0625)......................0.094 in. (2) Filters (from manufacturer's tables).......... -----------------------............... ......... -- 0.250 in. (3) Tempering coil loss (from manufacturer's tables).....-v--......... ---------------. 0.074 in. (4) Air washer loss (from manufacturer's tables).------------------- ------------ -------- --- 0.250 in. (5) Reheating coil loss (from manufacturer's' tables)............................ -................ 0.083 in. (6) Duct resistance: . -. The longest run is----------------------------------------- ------- --.................... = 150 ft Two, 58 x 30 in. elbows (150% ratio).^ ................. = ^6 ft . . 2 X 13 X 30 Two, 30 x 15 in. elbows (150% ratio)------- .................................... = 65 ft O V OK Y 15 Three, 15 x 30 in. elbows (75% ratio)-------- --------- -- ................. = 131 ft Total equivalent run............................................... --................ . 472 ft 472 ft at 0.033 in. per 100 ft............................-......................... -................... 0.156 in. (7) Allowance for damper adjustment, 25% of 0.156......... --................. r..........--- 0.039 in. (8) Supply grille resistance (from manufacturer's tables)................................... 0.036 in. Total static pressure loss of system---- ----------j--------------------------------- 0.982 in. The fan is selected from the manufacturer's ratings to deliver 22,935 cfm at a static pressure of 0.982 in. as outlined in Chapter 32. Example,3. If the rooms and offices of the hotel building of Example 2 are.to be served from a manufactured unit with a capacity of 22,935 cfm against an external resistance of 0.35 in., the known resistances are calculated as: . . (1) Outdoor air inlet_______________________________ _______ ______-......................... 0.094 in. ' (2) Supply grille resistance (from manufacturer's tables)--.................................. 0.036 in. , : Total known resistance.-:-------------------------------------- :--------------------------------0.130 in. . Subtracting this from the total available resistance: 0.35 in. -- 0.130 in. = 0.220 in. . available for duct resistance and damper adjustment. . ' - If 25 per cent is allowed for damper adjustment, the total allowable duct friction -- 0.220-s- 1.25 = 0.176 in. . -. Air Duct Design. 753 Known length of run,1_________________!_________________ _____ 150 ft The duct width is then estimated for the following elbow calculations: Four 150% ratio elbows, 4 x 13 x 3.5 ft 182 ft Three 75% ratio elbows, 3 x 35 x 1.5 ft................... ................... 158 ft Total estimated length____ ___________________ _________ ___ 490 ft The duct friction per 100 ft is then 0.176 -5- 4.90 = 0.036 in. and the mains and branches are sized from the 0.036 in. friction line in Fig. 2. . If it is desired to size each branch for equal resistance, the total resistance back to the point of juncture is calculated and the branch is then sized in a manner similar to that outlined in Example 3. DUCT CONSTRUCTION DETAILS Straight sections of round duct are usually formed by rolling the sheets to the proper radius and grooving the longitudinal seam. Rectangular ducts are generally constructed by breaking the corners and grooving the longitudinal seam, although some fabricators still use the standing seam due to lack of equipment. Elbows and transformation sections are gener ally formed with Pittsburgh corner seams because this seam is easier to lock in place than the double seam, but complicated fittings such as double compounded elbows are usually constructed with- double seam corners. The construction of these various seams as well as the types of girth connections are shown in Fig. 7. ,The application of the various slips and connections is outlined in Table 5. The end slip may be used wherever S slips are recommended. Where drive slips are used the end slip may be applied on the narrow side of the duct and the drive slips on only the maximum side. Ducts 25 to 30 in. in size should be reinforced between the joints, but not necessarily at the joint. Ducts 31 in. and up should be reinforced at the joint and between the joints; if drive slips are used the angles are usually riveted to the duct about 2 in. from the slips. It is good practice to cross-break or kink all flat surfaces to prevent vibration or' buckling due to the air flow and accompanying variations in internal pressure. Round ducts are sometimes swedged 1.5 in. from the ends so that the larger end. will butt against the swedge and are held in place with sheet metal screws. Where swedges are not used it is general practice to paste the joint with asbestos paper to insure a tight joint. The construction of elbows and changes of shape cannot be definitely outlined because of the varied conditions, encountered in the field, but in general long radius elbows and gradual changes in shape tend to maintain uniform velocities accompanied by decreased turbulence, lower resistance and a minimum of noise. . Heavy canvas connections (asbestos cloth if there is a fire hazard) are recommended on both the inlet and outlet to all fans. The fan discharge connections shown in Fig. 7 are marked good, fair, and poor in the order of the amount of turbulence produced. An inspection of the heater con nections shown in Fig. 7 will readily show that uniform velocity through the heater cannot be expected in the diagram noted poor. When obstruc-' tions cannot be avoided; the duct area should never be decreased more than 10 per cent and then a streamlined collar should be used. Larger obstructions require an increase in the duct size in order to maintain as nearly uniform velocity as possible. Branch take-offs should always be arranged to cut or slice into the air stream in order to reduce as far as possible the losses in velocity head. .754 CHAPTER 41 1946 Guide The recommended gages for sheet metal duct construction are given in Table 5. Weights of sheet metal per square foot of surface for different gages are given in Table 6. The weights of various gages and the areas for any length of run of rectangular sheet metal ducts ma^T also be determined from Fig. 8. The bottom scale represents the sum of the two Grooved seam "13p ' Standing seam pL S slip . Drive slip End slip Double seam Pittsburgh seam Bar slip ' Reinforced bar slip . Pocket .slip Angle connection Good Fair . Heater, filter, and washer connections -. Poor - sides of the duct and the oblique lines give-the length of run in feet. Proceeding horizontally to'the right from the intersection of. vertical and oblique lines on the chart; the area of the duct may be determined in the first vertical scale. The scales to the right give the weights of the duct run' for different gages of metal-. In calculating the weights of duct, it is considered good practice to allow 20 per cent additional for weights of -joints'and bracings- Various'weights and thicknesses of standard cqpper sheets will be found in Table 7: . Air.Duct Design ' , 755 . Table 5.- Recommended Shet Metal Gages for - ~' Rectangular Duct Construction*' . U. s. Std. Gags- Maximum Side, Inches 26 Up to 12 ' Type of Transverse Joint Connections^ S, Driye, Pocket or Bar Slips, on 7 ft 10 in.v centers v None Bracing 13 to 24 S, Drive, Pocket or Bar Slips, on 7 ft 10 in. centers None 24 25 to 30 S, Driven 1 in. Pocket or 1 in. Bar 1 x 1 x )4 in. angles . . Slips, on 7 ft 10 in. centers0 4 ft,from joint ' 31 to 40 Drive, 1 in. Pocket or 1 in. Bar 1 x 1 x )4 in. angles Slips, on 7 ft. 10 in. centers0 4 ft from joint 22 41 to 60 1)4 in. Angle Connections, or 1)4 1)4 x 1)4 x )4 in. angles in. Pocket or 1)4 in*. Bar Slips 4 ft from joint .. with 1)4 in*, x )4 in. bar rein forcing on 7 ft 10 in. centers0 20 61 to 90 1)4 in. Angle Connections, or 1)4 1)4 x 1)4 x )4 in. in. Pocket or 1)4 in. Bar Slips diagonal angles, or ,3 ft 9 in. maximum centers with 1)4 x 1)4 x )4 in. angles 1)4 x )l in. bar reinforcing 2 ft from joint 18 91 and up- 2 in. Angle Connections or 1)4 in.- 1)4 x 1)4 x )4 in.-. Pocket or 1)4 in. Bar Slips 3 ft diagonal angles, or - . 9 in. maximum centers with 1)4 x 1)4 x 1)4 x )4 in. angles )4 in. bar reinforcing^ 2 ft from joint , For normal pressures and velocities (see Table 3) utilized in typical ventilating and air conditioning systems. Where special rigidity or stiffness is required, ducts should -be constructed of metal two gages heavier. All uninsulated ducts 18 in. and larger should be cross-broken. Cross-breaking may be omitted on uninsulated ducts if two gages of heavier metal are used. . - . bother joint connections of equivalent mechanical strength and air tightness may be used. __ ' oDuct sections of 3 ft 9 in. may be used with bracing angles omitted, instead of 7 ft 10 in. lengths with joints indicated. ' dDucts 91 in. and larger require' special field .study for hanging and supporting methods. .. HEAT LOSSES FROM DUCTS The thermal transmittance U for ducts can be found.as follows: For uninsulated metal duct, V = -L+-L S\ So For uninsulated non-metallic ducts, U = -- Si +X + X where u. Si, So, * and k are as defined on page 759. (8). (9). Where x is small and k is large, however, this factor ~ is of little im-' k- portance and may be neglected. Film conductance/; for air flowing in ducts apparently depends only on the velocity of the air and the diameter of the duct. A fairly reliable inside coefficient can be.calculated from Schultz!s modified equation: . , where. 0.32 ya Si = Z)-" (10) . Va = velocity of air in duct, feet per second. D = inside diameter of duct, feet. 756 CHAPTER 41 1946 Guide Film conductance fa depends on a number of variables including tem perature, diameter, and emissivity of the outer surface and can be calcu lated from data in Chapter 5. From this explanation, it is seen that it is unwise to recommend a given value of U for all uninsulated metal ducts. . The heat loss from a given length of duct can be expressed by: . Q - UPl [ ~ t, ] (11) The heat given up by the air in the duct is: ' Q = 0.24 W (ii - t,) = 14.4 A Vm Pv (f, - M) ' (12) Equating (11) and (12): '. * /i t* " 2/s _28-8 A Fjn pv /i - it Wi , r. 28.8 AVm pY . ,j t 2DVmPv f j Let y = ------ xJpl--~ *or rectangular ducts, and------- ^------ for round Air Duct Design . 757 Table 6. Weights qf Sheet Metal Used for Duct Construction u. & Black Sheets Approximate * Thickness, In. Weight Per Square Foot . Galvanized Sheets8 Approximate Thickness, In. Square Foot Steel . Iron Ounces Pounds Steel Iron Ounces Pounds 30 28 26 24 22 20 18 16 14 12 11 10 0.0123 0.0153 0.0184 0.0245 0.0306 0.0368 0.0490 0.0613 0.0766 0.1072 0.1225 0.1379 0.0125 0.0156 0.0188 0.0250 0.0313 0.0375 0.0500 0.0625 0.0781 0.1094 0.1250 0.1406 8 10 12 16 20 24 32 40 50 70 80 90 0.500 0.625 0.750 1.000 1.250 1.500 2.000 2.500 3.125 4.375 5.000 5.625 0.0163 0.0193 0.0224 0.0285 0.0346 0.0408 0.0530 0.0653 0.0806 0.1112 0.1265 0.1419 0.0165 0.0196 0.0228 0.0290 0.0353 0.0415 0.0540 0.0665 0.0821 0.1134 0.1290 0.1446 ' 10.5 12.5 14.5 18.5 22.5 26.5 34.5 42.5 52.5 72.582.5 92.5 0.656 0.781 0.906 1.156 1.406 1.656 2.156 2.656 3.281 4.531 5.156 5.781 Galvanized sheets are gaged before galvanizing and are therefore approximately 0.004 in. thicker. ducts, and solve for li and k: . fe (y + i) - 2t. k~ (y"-T) (13) h (y - l) + 21, < = (y + i) (14) For low velocities and long ducts of small cross-section, a somewhat more accurate formula may be used as follows: ' t. / UPl \ ^ \UAAf>vVm) (15) Symbols used in these equations are listed at end of chapter. - In using Equations 13, 14 and 15, one of the duct air temperatures will be unknown and will be obtained by substitution of the other known or assumed values. Heat loss coefficients for insulated ducts with various conductivities are given in Fig. 9. The conductivities of various materials, which are based on mean temperatures, ranging from, about 70 to 90 F, will ,be found in Table 2 of Chapter 6. For cases where the mean temperature Table 7. . Weights and Thicknesses of Standard Copper Sheets Rolled to Weight Weight pee Square Foot Ounces Pounds' Thickness, Inches Decimal Equivalent Nearest Fraction 10 0.625 0.0135 ' 12 0.750 , 0.0162 H4 14 0.875 0.0189 Hi - 16 18 , 20 24 1.000 1.125 1.250 1.500 0.0216 0.0243 0.0270 0.0324 H2 Hi Hi 28 1.750 0.0378 3^2 32 2.000 -0.0432 Hi 36 2.250 0.0486 Hi ' 40 2.500 0.0540 Hi 44 ! 48 56 , 64 ; 2.750 3.000 3.500 4.000 0:0594 0:0648 0:0756 0.0864. ! H ... Hi Hi Hi . Variations from these weights must be expected in practice. - - Nearest Gage No. B. &S. Stubs U. S. STD. 27 26 25 23 22 21 20 19 17 16 15 .15 : 14 13 11 29 27 26 24 23 22 21 20 19 18 17 17 16 : 15 14 29 28 26 25 24 23 22 20 19 18 . 17 . 17 16 . 14 ' ,13 .; . 758 CHAPTER 41 i 1946 Guide . For round dacta less than 30 in. diameter, increase heat transmission values by the percentages shown. ' Thickness op Insulation (Inches) X. \% ' . ; .3% - 1. 2% . 6% IX 3% ' 7% 2` . 4% . 9% ' *" - Air Duct' Design 759 is other than that at which the test was conducted, a correction should be made. However, in most cases the effect of this factor will be small and may be neglected. . .. . . .. Example Determine the entering air temperature and heat loss for a duct^24 X 36 in. cross-section and 70 ft in length, insulated,with in. of a material,having a con ductivity of 0.35 Btu at 86 F mean temperature, carrying air at a velocity of 1200 fpm, measured at-70 F, to deliver air at 120 F with airsurroiinding the duct at 40 F: Solution. Referring to Fig. 9, the over-all heat transmission coefficient is found to'be 0.49 Btu. From Table 1, Chapter 3 the density of ah at 70 F and 29.921 in. Hg is found to be 0.0749 lb per cubic foot.' Substituting these and the other given Values in- Equa tion 13: . .. -- * _ 28.8 X 6 X 1200 X 0.0749 . y' 0.49 X 10 X 70 . 120 ( 45.3+ 1) - 80 ----------------45.3 - 1------ ^ =123-7 ; Substituting in Equation 11: . L. . ; Q = 0.49 X 10 X 70 (1-237 f 120^,_ 40 j = 28,100 Btu per hour. For special considerations which apply; to insulation of ducts in marine installations see Chapter 49. ` ... v LETTER SYMBOLS USED IN CHAPTER 41 absolute viscosity-of air under actual-(operating) conditions, any consistent units. . . " . .: _ ' = absolute.viscosity of air under standard conditions, any consistent units. Pa = density o.f air, pounds per cubic foot. . .. .2 Po = density of air under actual (operating) conditions, any consistent units. , ps = density of air under standard .conditions, any consistent-units. , ' ` ' Pv == density of air at specified temperature at which velocity, Vm, is measured, pounds ; .per cubic foot. , : . .... . * '' A~ = cross-section area of duct, square feet, f .. . . a. ~ length of one side of rectangular duct, feet or. inches.. (Other side is b.) . b -- length of one side.of.rectarigular ductjfeet or. inches. (Other side is a.) . D = inside diameter of conduit, feet. - - .. +- ' 'd = equivalent'diameter; feet or inches. . e =.Naperian base, of logarithms = 2.718. : jf-ik non-dimensional friction coefficient.` *- . .. " : .. - . fi == surface conductance (inside). Btu per (hour)'(square foot) .(Fahrenheit degree). .. /o 7 surface conductance (outside) Btu per (hour) (square foot) (Fahrenheit degree). ` -. -. . ' :- ''; ` _ ' -; g = acceleration due to.gravityTV32Ll7, feet per (second) (second). ;. ' i&o * friction loss under actual (operating) conditions, any consistent units. . ht = friction loss, feet of fluid flowing. ** Aa = friction loss under standard conditions, any consistent units. Aw = velocity head or pressure, inches of water. ' l = length of conduit, feet. . P -- perimeter of duct, feet. \ Q = heat loss through duct walls, Btu per hour. . h -- temperature of air entering duct, Fahrenheit degrees. ** = temperature of air leaving duct, Fahrenheit degrees. .. /* = temperature of air surrounding duct, Fahrenheit degrees. . U = thermal transmittance coefficient, Btu per (hour) (square foot) (Fahrenheit degree). V = fluid velocity, feet per second. . - . . V* = velocity of air in duct, feet per second. - Ym = velocity of fluid, feet per minute. ' '' W = weight of air through duct, pounds per hour. . .. ' x -- thickness, inches. - . 760 CHAPTER 41 1946 Guide REFERENCES See Chapter 1 for definition of standard air. '' *--A New Friction Chart for Round Ducts, by D. K. Wright, Jr. (A.S.H.V.E. Journal Section. Heating, Piping and Air Conditioning,.October-November, 1945, p. 577). ' *--Friction Factors for Pipe Flow by L. F. Moody (A.S.M.E. Transactions, Vol. 66, 1944, p. 671). --A.S.H.V.E. Research Report No. 1211--Pressure Loss Caused by Elbows in 8-inch Round Venti lating Duct, by M. C. Stuart. C. F.-Warner and W. C. Roberts (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 335). - - s--Loss of Pressure Due to Elbows in the Transmission of Air Through Pipes or Ducts, by F. L. Busey (A.S.H.V.E. Transactions. Vol. 19, 1913, p. 366). "Pressure Losses in Rectangular Elbows, by R. D. Madison and J. R. Parker (Heating, Piping and Air Conditioning, July, p. 365, August, p. 427, September, p. 483, 1936). .. ` , BIBLIOGRAPHY Method of Determining Rectangular Equivalents and Weights of Ducts, by Peter Franck (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning, Decem ber, 1940). The Flow of Liquids, by W. H. McAdams (Refrigerating Engineering, February, 1925, p. 279). . Air Conditioning and Engineering (American Blower Corp.). Fan Engineering (Buffalo Forge Co.). . . Heat Power Engineering, by W. N. Barnard, F. O. Ellenwood, and C. F. Hirshfeld, Part III (John Wiley and Sons). . Mechanical Engineers' "Handbook, by Lionel S. Marks (McGraw-Hill Book Co.), Frictional Resistance to the Flow of Air in Straight Ducts, by F. C. Houghten, J. B. Schmieler, J. A. Zalovcik, and N: Ivanovic (A.S.H.V.E. Transactions, Vol. 45, 1939, p. 35). '. . .: Analysis of Factors Affecting Duct Friction, by J. B. Schmieler, F. C. Houghten, and H. T. Olson (A.S.H.V.E. Transactions, Vol. 46, 1940, p. 193). .. The Flow of Fluids in Closed Conduits, by R. J. S. Pigott (Mechanical Engineering, Vol. 55,1933, p. 497). Mechanical Similitude and Turbulence, by T. von Karman (translated and reprinted as Technical Memorandum NA.CA. No. 611, 1931). Turbulent Flow in Pipes, with Particular Reference to the Transition Region between the Smooth and Rough Pipe Laws, by C. F. Colebrook (Journal, Institute of Civil Engineers, Vol. II, 1938,39, p. 133). .. - Evaluation of Boundary Roughness, by H. Rouse (Proceedings Second. Hydraulics Conference, University of Icr-va Bulletin 27, 19-13). . ,, . The Flow of Air in Ducts, by E. Kemier (Heating and Ventilating, May 1936, p. 38). Performance Tests of Asbestos Insulating Air Duct, by R. H. Heilman and R. A. McArthur (A.S.H.V.E. Transactions, Vol. 44, 1938, p. 197). . A Study of the Data on the Flow of Fluids in Pipes, by E. Kemier (A.S.M.E. Trans actions, Vol. 55, 1933, Hydraulics, p. 7). '. . A Rational Method of Duct Design, by L. G. Miller (A.S.H.V E. Transactions, Vol. 43, 1937, p. 71). , . .- . CHAPTER 42 Sound- Control Unit of'Noise Measurement, Apparatus for Measuring Noise, General Problem, Kinds of'Noise, Noise Transmitted Through Ducts, Design Room Noise Level, Noise Generated by Fan, Natural Attenuation of Duct System, Duct Sound Absorbers, Air Supply Noises, Grille Selection, Cross Transmission Be tween Rooms, Controlling Vibration from Machine Mountings IN ventilating and air conditioning a building or a room, the effect of the mechanical system employed must be considered" on the acoustics of the space conditioned. It is important to consider also that the use of air conditioning often permits keeping the windows closed, thus giving, relief from certain external noises, but at the same time increasing the necessity of providing adequate sound control. It is assumed that in a given space the architect and acoustical engineer have produced a room or rooms which are satisfactory for speech, music, or other uses. The ventilating engineer's sole function is to ventilate and air condition these rooms properly so that they will be physically comfortable without adding any acoustical hazards. UNIT OF NOISE MEASUREMENT According to an international standard, two terms.are used for noise measurement. The decibel (db) is the physical unit for expressing in tensity or pressure levels. The phon is the unit of loudness level. The loudness level, in phons, of any sound is by definition equal to the in tensity level in decibels of a thousand cycle tone which sounds equally loud, The decibel is defined by the relation N = 10 logio -7-, where N is the - *o number of decibels by which the intensity flux Ii exceeds the intensity flux I0. The intensity flux is the measure of the intensity of a sound wave and is defined in terms of watts per square centimeter passing through a unit area of wave front in a freely traveling plane wave. It is usually more convenient to select an arbitrary reference intensity for I0 and express all other intensities in terms of decibels above that level. For this purpose a reference intensity of 10"16 watts per square centimeter has been selected. This intensity is slightly less than the threshold of audibility for the average ear at a frequency of 1,000 cycles per second. This reference level also corresponds to a pressure of 0.0002 dynes per square centimeter for sound in air at usual room temperatures. A stated sound level in decibels, unless otherwise defined, will thus be, related to a'threshold of 10~16 watts. For example, a level of 60 db above this reference threshold is 10~10 watts. In a similar manner, when sound measurements are given in actual intensity or energy units, they can be converted to decibels by this relation. Since the decibel is based on a ratio, it can only be employed when related to a reference threshold level as given. Noise levels, which vary with frequency as well as intensity, must not only be related to this reference threshold level, but also to a reference frequency, which is. taken as 1000 cycles. These terms and procedures' may be found in Standards1 published by the American-Standards Association. ' 761 762 CHAPTER 42 1946 Guide APPARATUS FOR MEASURING NOiSE Since the relative loudness to the ear, rather than the actual physical intensity, is the quantity in which engineers are usually interested, it has . been found necessary to allow for the varying response of the ear at different frequencies in designing noise measuring equipment. It is most satisfactory to measure noise by means of a sound level meter, which usually consists of a microphone, a high gain audio-amplifier, and a recti-, fying milliammeter which will read, directly ini decibels/ This, meter is calibrated to give readings above the standard reference level and usually contains a weighting network to make it less sensitive at those frequencies where the ear is less sensitive. Three types of weighting networks may be . provided. The "A" network is intended to. provide relative frequency sensitivity corresponding to the characteristics of the ear at a loudness' level of 40 decibels. The "B" network is weighted to correspond to the ear characteristic at a loudness level of 70 decibels. The meter may also be provided with a "flat" network which provides ho weighting by frequency. For complete details on standards for sound.level meters, refer to the information2 published by. the American Standards Association. GENERAL PROBLEM OF SOUND CONTROL' As previously stated, the problem confronting the air conditioning engineer is that of designing a system which will operate without in creasing the noise level in the conditioned space. To be sure that this is accomplished, it is necessary: . . . - . 1. To determine the noise level existing without the equipment. ' . 2. To ascertain the . noise level which would exist if the equipment were installed without sound control. . .. 3. To provide as a part of the installation sufficient sound control appliances to reduce the noise level substantially to that found in Item 1. To accomplish this the engineer should have information of three kinds: 1. A knowledge of the noise levels currently considered, acceptable in various rooms in order that he may have a basis on which to proceed. 2. A knowledge of the. nature and intensity of the noise created by the various parts of the equipment. ' . 3. A knowledge of how, when necessary, to vary and control the noise level between the equipment and the conditioned space. . In addition, the engineer should have sufficient information to predict the levels produced by noises which may be transmitted by the duct system from one conditioned.space to another or from an outside space to the conditioned space. In either case, the designer must know the prob able noise level at the point where the noise originates: . From: this he can compute the attenuation or transmission loss required in order,to .bring this level down to that required in the conditioned space. If. there, is likelihood of direct transmission through a duct, the attenuation required may be computed as shown on page 763. If the transmission is through dividing walls, it will be necessary to refer to published information on the transmission losses of standard building constructions *: Information concerning the noise, levels created by ventilating and. air conditioning equipment such as fans, motors, air 'washers,' and similar, items is riot yet on a basis which permits tabular presentation, although certain manufacturers are prepared to offer such data and do state the" noise producing properties of their products.' 'A-sound test code for fans Sound Control 763 has been developed by the National Association of Fan Manufacturers which uses the flat response network of the sound .level meter. However, when determining the noise generated by an air distribution system, it is-1 customary to use the noise level of the fan as determined by the weighting network most nearly approaching the noise level of the space. In most _ cases this will be the noise level of the fan as determined on the 40 decibel weighting network. Refer to Table 1 for typical noise levels. KINDS OF NOISE To solve a sound problem of this type it is desirable to consider sepa-, rately the several means by which noise reaches the room: This avoids to some extent the necessity of knowing the noise level at the source, and' instead: places the emphasis on ascertaining the level at the point where the sound enters the room. The noise introduced into a room or building by ventilating or air conditioning equipment may be divided into two general kinds depending on how it reaches the room .with various sub-divisions: '" ' 1. Noise transmitted through the ducts. .' a. From equipment such as sprays, fans, etc. .. b. From outside, and transmitted through duct walls into air stream. . c. .From air currents, including eddying noises. d. Cross talk and cross noises between rooms connected by the same duct system. e. Noise produced by the grilles. , 2. Noise transmitted through the building construction. a. From machine mountings as vibration. b. From equipment through room wall surfaces. . .v ' The next step in the solution of this problem is to present data and discuss methods whereby solutions to the noise problem can be- obtained . when the allowable room noise level and the path through which the noise reaches the room are known. NOISE TRANSMITTED THROUGH DUCTS . ..Operation of an air. distribution system results in the generation of noise which may be transmitted through the ducts to the ventilated or conditioned room. The transmission of this noise may be controlled by the proper application of sound absorptive- material within the. ducts. The application of the absorptive riiaterial is a problem in balancing the room noise level requirements against the intensity, of the noise generated:. The four steps in the problem are: 1. Determination of acceptable room noise level resulting from the operation of the equipment. 2. Determination of noise level generated by the equipment. The difference between items 1 and 2 in decibels is the over-all noise reduction required between the equipment and the room. In the discussion which follows reduction of noise will be referred to as attenuation of noise. - 3. Determination of the natural attenuation of the duct system. 4. Selection of the proper sound treatment for the,duct system. . . The difference in decibels between the over-all. attenuation required and the natural attenuation (3)`is the additional sound attenuation to be provided by absorptive ma terials installed in the duct system or by special constructions designed to absorb.sound. Experience has shown, for example, that where ventilating requirements permit, intro duction of an expansion chamber or a change in area in the duct will frequently provide . more reduction in low frequency noise. . . . 764 CHAPTER 42 1946 Guide DESIGN ROOM NOISE LEVEL . Measurements of noise levels have been observed by several investi gators in various rooms and locations and are listed in Table 1. The values given were determined with the air conditioning or ventilation equipment not in operation, and with all windows and doors closed simulating the conditions of an actual installation. . This is an important consideration, for in offices or stores adjacent to busy thoroughfares the difference between the typical noise level in the Table 1. Typical Noise Levels Rooms Sound Film Studios________________________ __________ Radio Broadcasting Studios______ _ Planetarium Residence, Apartments, etc.. Theaters, Legitimate Theaters, Motion Picture_____________________________ Auditoriums, Concert Halls, etc_____ :____________ . Churches.;. Executive Offices, Acoustically Treated Private Offices Private Offices, Acoustically Untreated______ .. General Offices._____1 Hospitals_____________________ ______________________ Class Rooms_________ Libraries, Museums, Art Galleries__________________ ,__ Public Buildings, Post Offices, etc.................. ................... Court Rooms________ ___ ____________ 1. Small Stores.=. Upper Floors Department Stores____ 1________________ Stores, General, Including Main Floor Dept. Stores___ Hotel Dining Rooms__________________ !______________ Restaurants and Cafeterias.1 Banking Rooms._______ ________________________________ Factories.______________ _________ _______ ______. Office Machine Rooms_______________ _________ _ Vesicles . Railroad Coach_____ Pullman Car Automobile..-..... ... Vehicular, Tunnel__ Airplane____________ Noisb Level in Decibels TO BB ANTICIPATED Min. 10 10 15 33 25 30 25 25 30 35 50 25 30 30 ; 45 30 40 40 50, 40 50 50 65 60 Representative 14 14 20 40 30 30 38 43 60 40 35 40 55 35 50 50 60 ' 50 60 55 77 70 20 20 25 48 35 40 40 35 45 50 ' 70 55 45 45 60 45 60 55 70 60 _ 70 60 90 80 60*> 55b . 50 75 75 70 65 65 85 80 80 75 80 95 90 These values are tentative. More detailed measurements by D. F. Seacord. Bell Telephone Labora- . tones (Journal Acoustical Society of America, Vof. 12, pp. 183-187, 1940) give average values and stand ard deviations of room noise in residences, offices, stores, factories, etc..-in large American cities. , bFor train standing in station a level of about 45 db is the maximum which can ordinarily be tolerated. space with the windows and doors open and closed may be as high as 10 db. Minimum, representative, and maximum levels are given for each type of space. The values are intended to give the variation with respect to location and not to time, and may be roughly classified by the following: Minimum loudness refers to: Spaces of expensive construction, typified by double windows, carpeted floors, heavy upholstered furniture, or. acoustically treated walls and ceilings. Representative loudness refers to: Spaces of average construction and furnishings which are exposed to external noises typical of the locality in which the space is usually, found. . Sound Control - _____________;^765 Maximum loudness refers to: (1) Any space of. inexpensive construction, and bare, furnishings where noiSe is not an important factor. (2) Spaces in close proximity to very intense street traffic or to intense factory noise. In general, if the noise level in the space resulting only from the opera tion of the air conditioning equipment is equivalent to or less than the typical level given in Table 1, the installation will prove satisfactory. If the typical level and the equipment level are equal and heard together the resultant level will be 3 db higher than either of them alone. In some cases it is desirable to keep the equipment noise level in the ventilated or conditioned room at such a value that it actually will not increase the noise level in the room to any measureable degree. This can be accomplished if the equipment noise at the room can be kept 10 db below the noise levels shown in Table 1. NOISE GENERATED BY FANS Noise generated by fan wheels may be divided into two classifications, rotational noise and vortex noise. In' ventilation and air conditioning work, where the maximum ratio between the fan tip speed and the velocity of sound is not greater than 0.12, vortex noise is by far the most important. The rotational noise may be described as that due to the thrust and torque applied to the air. Vortex noise is that due to the shedding of vortices from the blade and is dependent on the angle of attack, velocity, air turbulence, and blade shape. Vortex noise is due to pressure variations on the blade as a result of variations of air circulation. Given the noise level at the outlet or inlet of one type of fan construction under specific conditions of size, tip speed, and total pressure, noise levels at other values of tip speed, total pressure, and size may be approximated by the relationships: 1. For constant size and point of rating, the noise level of a fan will increase with increasing speed. - db (change) = 55 logs, U) 2. For constant pressure and tip speed, the noise level of a given type of fan will increase with increasing fan size. ' . db (change) = 20 logit, ' (2) Fan size refers to wheel diameter, housing height or some dimension that is directly proportional to lineal units. Fan sizes based on arbitrary systems or systems of preferred numbers have no significance. . The noise of a given fan is not constant at constant speed if the air delivery changes due to change of resistance. In general, a backward curved blade fan is lowest in noise at or near the point of maximum . efficiency; a forward curved blade fan at or between the point of maximum efficiency and shut-off; an axial flow fan at or between the point of maxi mum efficiency and free delivery.. The noise level of a double width fan Table 2. Attenuation in Straight Sheet Metal Duct Runs ' Duct Small................................... Medium. ... Laree............ ' ' Size, In. 6x6 24 x 24 ` 72x72 Attenuation per Ft, db 0.10 0.05 .0.01 766 CHAPTER 42 ' 1946 Guide; Table 3. Attenuation of Elbows8 Elbow Size, iN.b Very small ____ .............. ......................................... Small________________ __ ____________ ___ ________ Medium__ 1'___ _______ ___________ ___________ _ . Large ............- ... _ _______ ______ 2 wide 3 to 15 15 to 36 36 plus Attenuation per Elbow, db 3 2 1.5 1. Tbe attenuation in vaned elbows should be considered the same as in elbows having the same diraen- . sions as the radius of curvature of the vanes. If the vanes are lined for the purpose of damping any vibra tions in them, one third may be added to the attenuation values listed. * - bThese attenuation values are based on elbows having a center line radius 1.5-to 2 times the diameter , or width of the duct. The attenuation will be greater if the ratio is less than 1.5 and less when the ratio is greater than 2. ... . - may be taken as 3 db higher than a similar single width fan operatingunder the same conditions of speed and pressure. ` NAT, URAL ATTEN- JUATION OF DUCT SYSTEM ' . Straight Sheet Metal Ducts. The attenuation of sound in straight sheet metal ducts is a function of the length, shape, and size of the duct4. . Attenuation values are given in Table 2. In general, this attenuation is ' so negligible except for long runs that it may be disregarded for all practical purposes. Elbows and Transformations. Due to reflective interference, attenua- . tion'will take place,at elbows and transformations. The magnitude of the attenuation will depend on the size and abruptness of the elbow or transformation as shown in.Table 3. . When the area of a duct increases abruptly, an attenuation of noise ' level takes place in the duct. In duct design practice the total area of ' the branch ducts is greater than the supply duct! Similarly with outlets, the area of the outlet plus the area of the duct after the outlet is greater , than the duct area before the outlet. Therefore in an outlet run, attenu ation occurs in the duct sis it passes each outlet. Table 4 gives the db reduction for various ratios of total branch duct and outlet area to supply duct area. , Grilles to Room. The large abrupt change in area between the grilles and the surfaces within a room results in. an appreciable noise attenuation. This attenuation is a function of the total-grille area (supply and return) and the total sound absorption of the room in sabines. (The sound absorp tion of a room-in sabines is the summation of the products of each surface of the room measured in square feet multiplied by its corresponding absorption coefficient). The attenuation is given in' Equation 3 as: ' -Table 4. Attenuation at Duct Branches or Outlets ' Ratio Branch Duct 4- Outlet Area Supply Duct Area - - Sum of Branch Areas. Supply Duct Area 1.00 . 1.20 , 1.35 Attenuation per . Transformation, db 0.0 0.8 . 1.3 Sound Control ' [- .,-767~ /Attenuation between\ ,,, , _ Total Room Absorption in Sabines . grilles and room / -- Total Grille Area , (3) Values in Table 5 approximate the attenuation for various rates of air change, and general types of room surfaces. ., . DUCT SOUND ABSORBERS The difference between the required sound attenuation and the natural attenuation is that which must be supplied by. the proper sound treat ment of the ducts. , . .. . Selection of . the Absorptive Material '' When a sound wave impinges on the surface of a porous material, a vibrating motion is set up within the small pores of the material by the Table 5. Approximate Attenuation Between Grilles and Room ' Outlet Velocity PPM 500 750 1000 1250 Air Change Min. - ' 5 10 15 20. 5 10 15 20 5 10 15 20 5 10 15 20 Live Room* o* -- 0.05 db ii . 14 16 17 - 13 16 18 19 14 17 19 20 15 18 . 20 21 Medium Room0 a = 0.15 db 16 19 21 22 18 21 23 24 19 22 24 . 25 20 23 25 26 Dead Room*1 a = 0.25 db ' . 18 21 23 24 20 23 25 26 21 24 26' 28 22 25 . 27 28 - Average absorption coefficient for the room.. ... bLive room-average absorption coefficient 0.05. Bare wood or concrete floor--hard plaster walls and ceiling--minimum of furniture. - -- Medium room-average absorption coefficient 0.15.. Carpeted floor, upholstered furniture, hard plaster walls and ceiling or bare room with acoustically treated ceiling. , - <*Dead room-average absorption coefficient 0.25. Heavy carpeted floor. Walls and ceiling acoustically a treated. Upholstered furniture. .' alternating sound waves. As the ratio of the cross-sectional area of the pores to their interior surface is small, the resistance to the movement of - air in the pores is large. This viscous resistance within the pores of the material converts a portion of the sound energy into heat. The decimal. fraction representing the absorbed portion of the incident sound wave is called the absorption coefficient. Considerable absorption may also result, particularly in the low frequency range; from the flexural vibra- tions of the duct. In the selection and application of the absorptive material, several points should be considered. . . 1. For the absorption "of the low frequencies below 500 cycles;per second the material should be at least 1 to 2 in. thick. Thin materials, particularly when mounted on hard solid surfaces, will absorb the high frequencies and reflect the low. . ' . 2. Tn order to provide as much low frequency noise absorption as possible by means 76S CHAPTER 42 1946 Guide of flexural vibration, it is desirable to fasten the absorptive panels discontinuously. This result may be attained to some extent by spot cementing, but better results are obtained when it is possible to fasten the absorptive panels to furring strips, leaving an air space behind. However, the exact resonance characteristics of the panels, and thus their absorption, are so unpredictable that flexural vibration cannot be relied upon for a specific value of attenuation. Requirements for a good sound absorption material are: (1) high absorption at low frequencies6, (2) adequate strength to avoid breakage, (3) fire resistance and compliance with national and local code require ments, (4) low moisture absorption, (5) freedom from attack by bacteria and algae, (6) low surface coefficient of friction; (7) particles should not fray off at the higher design velocities, and (8) freedom from odor when either dry or wet. - With every application the use of sound absorptive material should be considered in the dual function of insu|ation and sound absorption. It has been shown theoretically 6 that the reduction, in decibels per linear foot, of sound transmitted through a duct lined with sound absorbing material is related in a rather complicated manner to the size and shape of the duct, to the frequency of the sound, and to the sound absorbing char- Fig. 1. Absorption Plenums With and Without Sound Cells acteristics of the lining. Experimental evidence likewise indicates that ` there is no simple formula involving the variables which will apply accurately to all cases. However, it may be stated generally that the attenuation in decibels at a given frequency is directly proportional to the length of lined duct. It decreases as the cross-sectional area increases, and ' increases as the aspect ratio is increased. , s The noise reduction varies to a considerable extent with the frequency of the sound. In calculating noise reduction, consideration should be given both to the comparative efficiency of the duct lining material at different frequencies, and to the frequency distribution of the noise to be quieted. In the case of fan noise, it is recommended that calculations be based on the frequency 256 cycles, since most of the noise energy is in the region of this frequency. In quieting noise due to air turbulence and eddy currents, in which the high frequencies predominate, the frequency 1024 cycles should be used. ' Since ventilating system noise contains many frequencies, an exception should be noted to the statement above that attenuation in decibels is directly proportional to length of duct. Most sound absorbent materials are more efficient at high frequencies than at low frequencies. In con sequence, the attenuation in the first five or ten feet of lined duct will be greater', because the high, frequencies are being absorbed. Thereafter, Sn'und "Control 769 since low frequencies will be predominant, the over-all noise attenuation will crraHiiallv hp Ipss. . . Acoustic Impedance of Absorptive Materials In the past five years considerable literature has collected describing methods of determining the acoustic impedance of sound absorbent materials and methods of utilizing this quantity for predicting the acoustics of rooms7 and the attenuation of spund in ventilating ducts8. Acoustic impedance as a concept is derived from electrical circuit theory. The effect of the sound absorbent sound material upon incident sound waves is described in terms of a resistive and a reactive component which may be determined by specifically devised apparatus9. Generally speaking, however, the use of acoustic impedance theory involves rather elaborate mathematical calculations, and the improved accuracy obtained is largely off-set by variations in the materials them selves and in their methods of mounting. It has been difficult to measure the acoustic impedance of large areas of material mounted in a manner typical of standard construction. P. E. Sabine 7 concludes that the assumptions required by acoustic impedance theory make this method of calculation of no immediate practical advantage in the measurement of . sound absorption coefficients. .. Beranek 8 compares results of sound attenuation observed for . rec tangular ducts lined with absorbent material computed by acoustic impedance theory with data reported by H. J. Sabine10, using the methods of this chapter. Beranek concludes that the conventional P/A relation is valid for rectangular ducts not too far from square. His analysis indicates that other cases require more exact theory. However, it seems questionable whether the improvement in accuracy offered by the im pedance method overbalances the additional computation time required and out-weighs other sources of error such as variations between samples of material. Plenum Absorption In systems, where individual ducts are directed to a number of rooms and sound treatment is required in every duct, a sound absorption plenum on the. fan discharge as shown in Fig. 1 will often prove the most eco nomical arrangement. The absorption in the plenum may be approxi mated by Equation 4. ' Plenum Absorption in Sabines db (Attenuation) = 10 logu Area Fan Discharge (4) The area of the plenum should be at least ten times as great as the fan discharge area. The plenum should be lined with 2 in. of muslin covered rock wool blanket or 1 in. sound absorbing board preferably nailed to wood strips on the inside of the plenum. With such a lining the plenum Table 6. End Reflection of Plate Absorbers Percentage Free Area op Absorber Attenuation, db / 50 i . 40 2 30 ' 4' , . 25 . 5 .20 6. ' 770 CHAPTER 42 ' 1946 -Guide Fig. 2. Outlet Cells for Pan Outlets or Grilles is particularly effective in reducing low frequency fan noise. The absorp tion of the plenum in sabines is the sum of the products of each interior area of the plenum measured in square feet multiplied by its corresponding absorption coefficient. \ Plate Cells One of the most economical methods of applying sound absorbent material from the standpoint of both labor and material is the plate cell. The plate cell consists of or 1 in. sound absorbent board, spaced on 2, 3 . or 4 in. centers. The attenuation due to the plate cell may be divided into two parts. There is reflection at each end due to the change in area and the absorption at the ends. Values for this attenuation are given in Table. 6 which depend on the spacing. There is. also attenuation due to absorption of sound within the passages of the cell, which depends on the length and the spacing. The attenuation within the cell for 1 in. board neglecting the end effect is given approximately by Equation 5. where R 10La1* S (5) R -- attenuation, decibels. ' .- L = linear length of duct, feet. ' .' 5 spacing in inches between plates up to 3 in. a -- absorption coefficient for the full thickness of the' cell material. For typical value of a see Table 7. . An important objection to the plate cell is the increase in duct cross sectional area required. Often on the fan discharge, particularly with -unitary equipment, where a number of branch ducts take off, the plate cell may be installed with little or no difficulty. . Outlet Sound Absorbers . Outlet sound absorbers are rectangular or plate cells installed directly behind an outlet or they may be the lining of a pan or plaque outlet. They are particularly effective in the elimination of high frequency Table 7. Attenuation Formulae for 1 In. Thick Typical Duct Lining Board Frequency . 256 512 1024 2048 Absorption Coefficient 0.37 0.69 0.78 . 0.78 Attenuation Reduction, db 3.0 L P/A 7.5 L P/A 9.5 L P/A . 9.5 L P/A Sound Control _______________^:]______________________________________________ 111- -whistles which are generated by air flow in the ducts. They are also employed in large systems with long runs where only a few outlets near the fan require treatment. Frequently outlet cells are the.only means of correcting existing noisy installations, as the duct sections directly behind the outlets may be the only sections accessible for treatment. (See Fig. 2.) . Duct Lining or Rectangular Cells ' One series of experiments " made on a commonly used type of duct lining material (1 in. rock wool sheet) has shown that, subject to certain restrictions, the attenuation of single-frequency sounds may be expressed by the approximate Equation 6. This equation is accurate within plus or minus 10 per cent for duct sizes ranging from 9x9 in. to 18 x 18 in., for Fig. 3. Sound Attenuation for Various Absorbing Duct Liners cross-sectional dimension ratios of 1:1 to 2:1, for frequencies between 256 . . and 2048 cycles, and for absorption coefficients between 0.20 and 0.80. . R = 12.6 L -4-' o' * ' .A where .- R -- attenuation, decibels. ` L = length- of lined duct, feet. P e* perimeter of duct, inches. . A = cross-sectional area of duct, square inches. a -- absorption coefficient of lining. . ' ; (6) . ... .. In Table 7f the absorption coefficients at different frequencies of a material of the previously mentioned type are listed, together with the corresponding values for Equation 6. . - Results of other experiments indicate, however, that Equation 6 may be in error when applied to other types of duct lining material and to duct' sizes and shapes outside of the range specified. An empirically derived ' chart11 representing the average experimental data on a number of different types of materials including the rock wool sheet mentioned as applicable to Equation 6 is shown in Fig. 3. Since individual materials vary, the curves in Fig. 3 are given only as representing the best available averages for duct sizes of square cross-sections from 6x6 in. to 48 x 48 in. As-an illustration, the dotted lines in the chart show values calculated from Equation- 6 which indicate that the slope for this particular material is somewhat different than from the average curves. The curves in Fig. .3, . '1 .. ' , / 772 CHAPTER 42 1946 Guide as well as Equation 6, show that the attenuation in decibels is directly proportional to the length of duct lined, and that the larger the duct the greater will be the length which must be lined in order to obtain a given noise reduction. . ' If the length of duct from the main duct to a grille is shorter than the length of lining indicated by the calculations, this duct may be sub divided into smaller ducts, as shown in Fig. 4. The increase in noise reduction thus obtained may be calculated from Equation 7, provided the^splitters are installed parallel to the long side of the duct: Rs = Ro 1 o+o where = reduction with splitters, decibels. Ro = reduction in same length of duct, without splitters, decibels. a = dimension of short side of duct, inches or feet. b = dimension of long side of duct, inches or feet, n = number of channels formed by splitters. (7) Sound Control 773 Solution: . Case 1. (No splitters), From Equation 6, fin Ro = 12.6 X 12 X X 0.401-4 - 12.6 db Case 2. (Two splitters, three channels), From Equation 7, Rs - 12.6 X 10 + (20 X'3) 10 +20 29.6 db Am SUPPLY OPENING NOISES . When air is introduced into a room through a grille or register at a constant velocity, sound energy is being introduced into the enclosure at a constant rateDue to partial reflection at the boundaries of the en closure, the intensity of sound at any point in the space builds up to some maximum value. In a large room at a point remote from the source of sound (the supply opening) the intensity can be shown to be,substantially proportional to the rate at which sound energy is generated and inversely proportional to the number of sound absorption units (sabines) in the Fig. 4. Diagram of Branch Duct Treatment Where Length is Insufficient for Adequate Absorption Example 1. An air conditioning installation is to be installed in a small theater. Determine the necessary sound treatment for the air distribution system to provide a satisfactory noise level in the theater utilizing these conditions: . Fan tip speed 4000 fpm, total pressure 1.25 in------------------------------------- 77 db Acceptable room noise level (Table 1).................................................:--------- 40 db Required attenuation.-____________________________37 db Solution: Natural attenuation of supply duct. . Sheet metal duct 50 ft long 48 in. x 36 in. (Table 50 x 0.01------- ; 6.5 db Elbows.- two size 48 in. x 36-in. (Table 3) .2 x 1------------------------------------ 2.0 db , Attenuation grilles to theater air change 10 min (Table 5) outlet velocity 1000 fpm__---------------- ------------------------------------------------------- -22.0 db Total natural attenuation____ -- -----24.5 db Difference between required and natural attenuation, 37 minus 24.5, is 12.5 db. This attenuation must be supplied by sound treatment in the duct, either in the form of duct lining or plate cells. ` .` A similar analysis of the return duct system shows that 15 db attenuation are to be furnished by absorptive material. An inspection of the installation shows that the lining of the plenum on the suction side of the fan would prove' the most economical, where.it would secure the dual function of heat insulation and sound absorption. . Example 2. A 10 x 20 in. duct is connected to a private office space in a quiet location. Determine the length of lining necessary to attenuate average fan noise satisfactorily, using a lining material of a type to which Equation 6 applies, and having an absorption coefficient of 6.40 ait 256 cycles. Assume that the duct is only 12 ft Long as shown in Fig. 4, and that a 30 db reduction is required in this length. ' . room. It would thus appear that doubling the sound absorption of the room would halve the intensity and result in a noise level decrease of 3 db. Grille noise is similar in character to fan vortex noise. Knowing the noise level at the face of a grille for a given grijle blade setting, the noise will vary as given inequation 8 where V is the velocity, of theair through the grille. . db (change) = 55 logio ("p") (8) , For a change in blade setting Equation 9 applies arid in this case the total pressure is measured directly behind the face of the grille. For a typical air conditioning grille the noise level at the grille face may be approximately 48 db with a total pressure behind the grille of 0.1 in. dt (change) = 27.5 log,. [ . ' ' The resultant room noise level can be approximated by Equation 10. ; Room Level = [Noise F*j _ 10, Total Room Absorption mSabines L of Grille J .6 Total Grille Area v s 774 ,. CHAPTER 42 _________ '1946 Guide. Grille Selection . ' '' . In practice the allowable total sound and the required air flow are usually known, and it is desired to determine the maximum allowable velocity. In comparing sound ratings of various grilles several_ factors must be known if the information is to be properly applied: 1. The threshold intensity on which" the decibel ratings are based. ' 2. The distance from the grille at which data were taken. 3. If stated as loudness level versus velocity for a given grille, the core area (not nominal area) must be known. 4. The sound absorbing characteristics of the test room. 5. Whether or. not corrected for test room loudness level: if not; the room level (without grille noise) must be known.- " : -- " ." 6. Methods used for recording data. (Characteristics of sound meter). ' Since total loudness and air flow are both functionsof velocity and area, the solution of the problem implies a trial and error method. It has been found possible to present these data with sufficient practical accuracy as a family of uniform curves, as illustrated in Fig. 5, which are based on these assumptions: ' 1. Threshold intensity = 10~'" watts per square centimeter1., 2. Microphone location 5 ft from lower edge of supply opening on a line downward at ' 45 deg and in a plane bisecting the supply opening perpendicularly. - 3. Where data are given as loudness level versus velocity, the rating is per square foot of core area. -' 4. The room is assumed to have 100 sabines absorption. 5. Plotted data are loudness levels of supply openings only,, correction having been made for test room level. -. 6. Data taken with a direct reading sound-level meter with frequency weighing network intended to approximate the response of the human ear. ' If the published ratings are in terms of decibels per square foot, cor rection must be made for area to secure the total sound level of supply openings of more or less than one square foot area from Equation 11. Decibel Addition = 10 logioA (11) ` where , A -- core area, square feet. ' With Fig. 5 it is possible to find directly the velocity in feet per minute which will give a predetermined total loudness at a predetermined rate of flow expressed in cubic feet per minute. The values used are arbitrarily chosen for,the purpose of discussion and do not necessarily represent data referring to any particular design of air supply opening. A correction chart is shown in Fig. 6 for a room having a sound absorption other than 100 sabines. , " - . Example 3. Determine the core area (see Chapter 40) of an air supply grille which will maintain a noise level of not more than 40 db in a room having 100 sabines of sound absorption, if an air volume of 2400 cfm is required to maintain the proper air con-. ditioning. - Solution. Assuming a grille noise rating of at least 5 db below the noise level of the room. Fig. 5 shows that the limiting grille velocity for a total loudness of 35 db is about 725 fpm and the core area becomes fixed at 2400.4- 725 or 3.31 sq-ft. If the room absorption had been greater,- the previously selected velocity of 725 fpm would be safe, since the loudness reduces. If the room absorption had been 200 sabines a correction of plus 1.3 should be made by reference to Fig. 6, and the permissible velocity -. becomes that corresponding to a total loudness of 36.3 or approximately 800 fpm. If the room had been highly reflective with an absorption of less than 100, the cor- - Sound Control 775 rection would be much more important. For instance, for a room of 35 sabines a cor rection of minus 3 db should be made'and the maximum velocity corresponding to the' 32 db total loudness would be approximately 600 fpm. . . , Where more than one supply opening must be considered, the problem; is more complicated., If a similar supply opening is added in a far corner of a highly absorbent room, the change in noise level at the 5 ft station at the first supply opening is small; however, if the room is small, or highly reverberant or both, the intensity at the 5 ft station may be almost doubled and the noise level increased nearly 3 db thereby. The simplest method of handling this problem is to treat the room as though all the air were being supplied by one supply opening. Thus, if two outlets, each supplying 1000 cfm are used, the value 2000 cfm should be used with Fig. 5. Although this method may place an unwarranted limit on.velocity when used in a large, room, it is seldom that such a room has a noise level low enough to justify a more complicated though more exact procedure. In general, return grilles are selected for velocities about half the supply velocity, and when this is done, they may be neglected in sound computa tions. However, if supply and return grilles are the same size, resulting in the same face velocity, they must be treated as two supply openings. That is,, if 1000 cfm are supplied and exhausted, through grilles of the same area, 2000 cfm must be used in the. solution with Fig. 5. CROSS TRANSMISSION BETWEEN ROOMS Ducts serving more than one room permit cross talk between the'rooms and should be lined with acoustical .material; Where the rooms are close together and the ducts short, the ducts should be sub-divided to provide 776 CHAPTER 42 1946 Guide ample acoustical treatment. Lagging material similar in character to acoustical board, when placed on the outside of ducts, serves to prevent noise originating outside the ducts being carried inside the ducts and into- . ', the air stream. A case where outside lagging is desirable occurs when ducts originate at the fan in the equipment room and pass through this room on the way to the room being conditioned or ventilated. Unless the ducts are lined some of the mechanical noise from the equipment room air may be trans mitted through the wall of the duct, thus reaching the air stream and be carried into the room.- In such cases, that portion of the duct which is exposed to the sounds in the equipment room should be lagged with material such as cork, pipe covering or other sound damping material to prevent the sound from entering the duct at this point. Numerical data are not available to permit a simple and practical calculating procedure to determine thickness of covering which should be used for this purpose. Laboratory measurements have shown that the loss through a sheet of No. 22 gage metal is 24 db. When a sheet of rock wool insulation 1 in. thick and weighing 1.4 lb per square foot is added to this, the insulation value is increased to 29 db. In general, however, adding a layer of insulation or pipe covering does not materially increase the sound insula tion value unless the material is dense, or unless it is surfaced with another sound impervious layer such as metal or board. Standard reference books should be consulted for sound insulating properties of various materials. Inside lining material used in the case previously mentioned would serve as an absorber of the sound transmitted through the duct walls, and thus act as a means of preventing the transfer of noise into the air stream. . Inside lining may also be used in ducts to absorb noise which reaches the air stream from equipment such as fans, sprays and coils; noise due to ' eddying currents set up by elbows, dampers and similar obstructions; and noise transmitted from room to room where there is a common duct system. CONTROLLING VIBRATION FROM MACHINE MOUNTINGS It is impossible to select equipment which will operate without pro ducing some mechanical noise and, since the equipment must be mounted in a building, it is probable that a part of this noise will be transmitted to the building to such a degree as to make noisy conditions in the rooms which are to be air conditioned. ' . - Much of this noise may be transmitted by the duct if it is rigidly con nected to the fan outlet. It is common practice to make the connection between the fan and the duct with a canvas sleeve which effectively restricts noise at this point. Noise may also enter the building through . the mounting of the motor and the fan. Flexible mountings should be provided in all installations , but these mountings must be carefully designed so that they will actually reduce the energy transmitted between the machinery and the supporting floor. If a flexible material is used, it is desirable to investigate the installation so that it is not short-circuited by through bolts which are improperly insulated and by electrical conduit which is not properly broken and is attached both to the equipment and to the building. The flexible mounting, if improperly engineered, may actually increase the energy transmitted between the equipment and the . floor upon which it is supported. ' -In the proper isolation of vibration, which is usually in the lower range . of frequencies and does not include the airborne vibrations known as Sound Control 777 sound, there is one basic formula which is important in the solution of the problem. It is the formula of transmissibility as governed by the , equation: . where T = transmissibility of the support. / = frequency of the vibratory force. /n = natural frequency of the machine unit on its support (Damping = 0). Equation 12 shows that the transmissibility approaches unity for disturbing frequencies considerably lower than the natural frequency of the mounting. As the disturbing frequency is increased the transmis sibility is also increased until at the resonant frequency, where / = /,, the transmissibility becomes infinite. This is not true in practice because all materials have some internal damping effect. However, operating at or very close to the resonant frequency is always serious as forces and stresses may be multiplied 10 to 100 times. As the disturbing frequency becomes greater than the natural frequency the transmissibility becomes a smaller quantity and at the value of //fn = it again has the value of unity. Beyond, this point true isolation is first accomplished. At a ratio of 3 to 1 for / to f,, the isolation is effective enough for practical application, and experience and economical design have shown that a ratio of 5 to 1 is good. For high speeds, higher ratios for / to /,, are easily attained and give better results for effective vibration control, but for the lower speeds as experienced with compressor work the higher ratios become uneconomical. For a given installation the speed of the compressor is fixed by. the specifications, therefore the value of/ is fixed. That leaves only/n to be determined and that is accomplished by the choice of mounting material and design for the support of the machine. It is well to keep in mind that when trying to isolate vibration, no attempt should be made to isolate the driving and driven piece of equipment separately. The two should be mounted on a rigid frame and then the entire assembly isolated according to the rules presented in this chapter. The value of /,, can be controlled by the flexibility of the machine support, and when the deflection of the machine support is proportional to the load applied (such as with springs or nearly so with rubber in shear) the value of /,, can be determined by Equation 13. where Z -- gravitational constant. d - static deflection of supporting material. / = frequency of the vibratory force. ` fn = natural frequency of the machine unit on its support (damping -- 0). By the use of Equation 13 a set of curves may be plotted as shown in Fig. 7. The first line AB, plotted as the critical frequencies for the various . s' 778 CHAPTER 42 1946 Guide static deflections, is a curve showing the worst possible conditions or resonant conditions. .- ' Plotting another curve CD,-which is times curve AB, shows the area MCDN in which the resilient material or mounting does more harm than good. Plotting two more curves EF, 3 times curve AB, and GH, 5 times curve AB, shows area EGHF which represents efficient and eco nomical isolation. Area GPOH is excellent isolation, but for all except the highest speeds becomes rather uneconomical because of the large deflec tions required. ' - Example 4. An electric motor driven compressor unit is to be isolated. The com pressor is partially balanced and operates at a speed of 360 rpm. The speed of the motor is 1160 rpm and is belt connected to the compressor. Total weight of the compressor and motor is 4500 lb. ' . Fig. 7. Static Deflection for Various Frequencies ' Solution: The minimum disturbing frequency to be isolated is 360 cydes per minute. Assume that the desired ratio of forced to natural frequency is 3 as a minimum and that 5 is desired. The desired natural frequency of the mounting is 360 5 = 72 cycles per minute. . . .- From Fig. 7 a deflection of 7 in. is required to attain a natural frequency of 72 cydes per minute. This value may be obtained from critical curve AB for 72 cydes or from - curve GH (5 times critical) for 360.cydes. For the minimum ratio of 3 the .deflection would be 2.5 in. , _, The next step is to determine the total weight to be supported by the springs. For low speed partially balanced compressors, it has been found necessary to add a founda tion weighing 2 to 3 times the weight of the motor and compressor, in order to maintain the machine movement below. 0.03 in. ' .. Compressor arid motor_____ ________________________ Concrete foundation 9,000 lb 4,500 lb Total.____ l:-13,500 lb Sound Control 779 Practical application dictates the number of springs to be used, which is based on the design of the machine foundation and the supporting floor structure.. However, it is desirable to design for.at least 8 springs and one or two spares for cases of unknown weights. As many as 50 springs have been used on one installation. The distribution of the springs must be balanced against the masses to be supported, otherwise the, foundation design and supporting structure determine the location of the springs. The choice of the material used in the design of the resilient mounting is also important. For the slow-speed type compressor a common speed found in practice is 360 rpm. For speeds below this, isolation should not be attempted except under careful supervision. Referring to Fig. 7, it is found that for 360 rpm the static deflection required for a ratio of f/fn of 3 to 1 (line EF) is 2.5 in. and fpr a ratio of 5 to 1 (line GH) it is 7 in. For these values of deflection the only choice of material is the coil spring.. This is also true for speeds up to about 700 rpm. In consideration of the transverse spring constant (so as to maintain good ratios among the various degrees of freedom) experience has shown that the spring should be designed with a working height equal to 1.0 to 1.5 times the outside diameter. A long spring of small outside diameter has very low transverse rigidity and therefore requires some additional means of preventing side drift of the unit and on very sensitive applications this may tend to destroy the isolation efficiency. For speeds of 700 to 1200 rpm the required deflections range from 0.22 in. to 1.75 in. For these conditions rubber in shear serves as a rather satisfactory material if protected from oil. For speeds higher than 1200 rpm cork specially made for vibration damping can be applied with good results. These limitations are by no means absolute, because certain liberties may be taken without impairing the result if all possible degrees of freedom have been taken into account in the design of the installation. . When a machine unit is properly isolated it will have a definite amount of movement which is determined by the ratio of the unbalanced forces to the total mass of the machine. If this resultant machine movement is too great for the necessary connections or the satisfaction of the customer it can be' reduced only in two ways without destroying the quality of the isolation; first, adding mass or dead weight to the machine (such as concrete) common in the application of low speed, partially balanced machinery; second, accurately balancing (both statically and dynamically) all moving parts so as to eliminate the vibration at the source. This latter method is the best engineering practice and is the modern trend. However, even with well balanced machinery, installed in the vicinity of quiet offices it is usually necessary to properly isolate the equipment to prevent the transmission of vibration likely to pause complaints. Where limitation of machine movement is desired during the starting and stopping periods, the application of friction or hydraulic damping will serve without seriously interfering with the efficiency of the isolation. REFERENCES `^American Standards for Noise Measurement, Z24.2-1942, American Standards Association. ^"American Standards for Sound Level Meters for'Measurement of Noise and. Other Sounds. Z24.3- 1944, American Standards Association. Sound Insulation of WaU and Floor Constructions (17. 5. Department of Commerce, National'Bureau of Standards. Building Materials'and Structures Report BMS17 and Supplement). A.S.H.V.E. Research Report No. 1205--Determining Sound Attenuation in Air Conditioning systems, by D. A. Wilbur and R. F. Simons (A.S.H.V.E. Transactions, Vol. 48,1942, p, 267). ,, coefficients of commercial sound absorbent materials see Bulletin Acoustical Materials Association, N 919 No. Michigan Ave.. Chicago. 111. 780 CHAPTER 42 1946 Guide --Sound Propagation in Ducts Lined with Absorbing Materials, by L. J.Sivian (Journal Acoustical Society of America, Vol. 9, 1937-38, pp. 135*140). . . ' 7--Specific Normal Impedance and Sound Absorption Coefficients of Material, by P. E. Sabine (Journal Acoustical`Society of America, Vol. 12, pp. 317*323, January, 1941). ' Application of Wave Theory of Room Acoustics to the ^Measurement of Acoustic Impedance, by C. M. Harris (Journal Acoustical Society of America, Vol. 17, pp. 35-46, July, 1945). . s--Sound Absorption in Rectangular Ducts, by L. L. Beranek (Journal Acoustical Society of America, Vol. 12. pp. 228-237, October, 1940). i The Transmission of Sound Inside Pipes, by Philip M. Morse (Journal Acoustical Society of America, * Vol 11. pp. 205-210, October, 1939). s--Precision Measurements of Acoustic Impedance by L. L. Beranek (Journal Acoustical Society of iAmerica, Vol. 12, pp. 3-14, July, 1940). .. Notes on Acoustic Impedance Measurement, by H. J." Sabine (Journal Acoustical Society of America, ij VoL 13, pp. 143-150, October, 1942). . J io--The Absorption of Noise in Ventilating Ducts, by Hale J. Sabine (Journal Acoustical Society of 1 America, Vol. 12. p. 53. 1940). jj | A f A S- :| - 11--The Prediction of Noise Levels from Mechanical Equipment, by J. S. Parkinson (Seating and Venti- lating, March, 1939, pp. 23-26). Methods of Rating the Noise from Air Conditioning Equipment, by J. S. Parkinson (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning, July, 1940, p. 447). ' '' . i2--The Noise Characteristics of Air Supply Outlets, by D. J. Stewart and G. F. Drake (A.S.H.V.E. Transactions, Vol. 43. 1937, p. 81). f i \ CHAPTER 43 Types of Systems for Ventilating, Heating, Air Conditioning, Factors Involved in Use and Design of Systems, Design Procedure THE purpose of this chapter is to present a discussion of types of central systems usually encountered, together with a discussion of the factors involved in use and design and an outline of design procedure. Insofar as this chapter is concerned, a central system is defined as a field assembled apparatus, comprising such elements of equipment as are necessary to fulfill the purpose for which it is designed, and serving one or more conditioned spaces. A factory produced unit, including all the essential items of equipment may be employed as a central system. Unitary equipment is discussed in Chapter 36. Further, this chapter is confined to comfort air conditioning systems as such, and ventilating systems, warm air heating systems, together with central systems of a special nature, are excluded from the discussion. This chapter assumes a knowledge of all the component parts of a system and the reader is referred specifically to other chapters covering design conditions and physiological principles, cooling and heating loads, spray equipment, heat transfer surface coils, cooling, dehumidification and dehydration, fans, air cleaning devices, refrigeration, air distribution and air duct design, automatic controls and instruments. In addition, the engineer should refer to the Code of Minimum Requirements for Comfort Air Conditioning 1 prepared by the joint committee of the American Society of Heating and Ventilating Engineers and the American Society of Refrigerating Engineers, and to national, state or local codes that may apply................ CLASSIFICATION OF SYSTEMS The generally accepted method of classifying systems is with regard to their function. A given type of system may be changed by the omission of certain of its functions or by the inclusion of others. As an example, a winter air conditioning system, by the omission of humidifying sprays, air cleaning devices, etc., Will become a simple warm air heating system, and by further omissions will become a simple ventilating system. On the other hand, with the inclusion of a dehumidifier with its source of cooling, the system can become a year 'round air conditioning system. The three major types of systems are: 1. Winter Air Conditioning Systems. The function is to ventilate, heat and humidify in winter the spaces under consideration, and provide the desired degree of; air motion and air cleanliness. The equipment required normally consists of a preheater, filters, humidifying sprays or air washer, reheater, fan, distributing ducts, and the necessary manual or automatic means-of control. See Fig. 1. 2 Summer Air Conditioning System's. The function is to ventilate, cool and dehumidify the spaces under consideration and to provide the desired degree of air motion and cleanliness. The normal complement of equipment includes filters, dehumidifier . with its source of cooling, reheaters or by-pass if required, fan, distributing ducts, and the necessary manual or automatic means of control. See Fig. 2. ' 3. Year 'Round Air Conditioning Systems. The function is to ventilate, heat and humidify in winter and cool and dehumidify in summer the spaces under consideration, and to provide the desired degree of air motion and cleanliness. The equipment usually comprises preheater, filters, spray or surface dehumidifier, reheaters and by-pass u 781 782 CHAPTER 43 1946 Guide Central Systems for Comfort Air Conditioning 78$ required, fan, system of distributing ducts, and necessary means of manual or auto matic control. See Fig. 3. Items of equipment in the foregoing may, of course, be replaced with others fulfilling the same purpose. As an example, an absorption type dehydrator with an aftercooler may replace a dehumidifier. Modifications All of the general types of central systems may be modified in various ' ways. These modifications do not affect the functions of the system. In general, these consist of changes in or additions to the normal complement of equipment, or variations in arrangement and design of equipment and distributing ductwork in order to provide better control of conditions, greater flexibility, or improve the over-all economy and performance of the system. Some of these are applicable to certain systems only, while others are applicable to all types. The most commonly encountered modifications are: J. Zoning. a. Separate equipment. . i. Reheating or recooling. (See Figs. 4 and 5). c. Multiple fans with individual by-pass or reheat. d. Volume control. (See Fig. 8). . e. Dual duct system. (See Fig. 9). ` ' (See Figs. 6 and 7). . 2. Induction units. (Low pressure type). (See Fig. 10). 3. Induction units. (High pressure type). (See Fig. 11). 4. Evaporative cooling. 5. Precooling. 6. Sensible cooling with dry coils. 7. The run-around system. . . . There are many other possible modifications and the special require ments of some installations may warrant consideration of these, but space limitations prevent a discussion of all. The modifications mentioned are discussed further in this chapter. USE OF CENTRAL SYSTEMS Several factors must be considered in deciding on whether or not to use a central system and in deciding on the type of central system and modifications required. These factors are: 1. Comparative effectiveness. 2. Characteristics and requirements of the load. 3. Space requirements. 4. Initial cost. ' 5. Operating costs and maintenance. ' . ` The comparative effectiveness of the type of system and modification plays a major part in the choice and is to a large extent affected by the other factors. One great advantage provided by the central system lies ' in its ability to diffuse odors and smoke which may occur in parts of the system, so that the outside air is determined by the average instead of the sum of the peak requirements. However, caution must be used where . 'odors are apt to be objectionable even if greatly diluted. In such cases a positive exhaust to the outdoors or a separate treatment for the particular locality is recommended.' The averaging ability both as to odors and 784 CHAPTER 43 1946 Guide ' pump Fig. 4. Central System with Zoning by Reheating ' thermal effects of the system is one item to be considered in studying the comparative effectiveness, particularly where adequate zoning is to be provided. Full advantage of diversity and non-simultaneous peak load requirements can be taken in determining the dehumidified air quantity where adequate zoning is provided. The characteristics and requirements of the load frequently are the deciding factors. Wide, non-simultaneous variations in load between spaces or parts of the same space indicate the necessity of zoning. Isolated spaces having a short time occupancy or brief load duration may be ' handled by units advantageously at times. The occurrence of simultaneous heating and cooling requirements in spaces having the same exposure or on the same zone presents a problem to be studied. Ability to maintain conditions during the intermediate seasons without the use of refrigera tion must be considered at all times, particularly in those applications where a high internal load exists. The matter of space requirements may rule out one type of system or - another. The avoidance of the use of rentable and usable space for equipment and ductwork, in office buildings, stores, etc., is most im- Fig. 5. Summer Central System with Zoning by Recooling Central Systems for Comfort Air Conditioning 785 portant since the loss of revenue is directly chargeable to the operating cost of the system. Consideration of the spaces available with respect to the type of system and method of distribution used and their effect on over-all cost is essential. Initial cost is given first consideration all too frequently. While elaborately designed installations are seldom justifiable, proper con sideration must be given to operating costs and maintenance, performance required, and the life of the system. The increase in cost incurred by suitable zoning can be offset partially by reduced quantities of dehumidi fied air, and partially by reduced refrigeration requirements. In the end it may prove less expensive than an unsatisfactory single zone system. A small increase in initial cost-to provide better access to equipment, better airflow and distribution, and better zoning, usually will pay for itself-. Operating costs often receive too little attention. Proper relationship between equipment selected and the load to be carried must be obtained. Fig. 6. Central System Using Multiple Fans with By-passes and Reheating for Zoning Cooling systems in general operate at maximum capacity less than 20 per cent of the time and heating systems operate under design conditions but a few days in the year. Good partial load performance is essential for low operation costs. Proper zoning, good arrangement and selection of equipment and type of system all tend to reduce operation costs. Centred systems having the bulk of equipment in a central location properly arranged, and having only the equipment required for zoning distributed through the conditioned space or spaces, will have relatively low main tenance costs. Care must be used to provide ease of access to important equipment and those items requiring servicing. DESIGN OF SYSTEMS . Various factors`are to be considered in the design of a central system, some of which have been touched upon in the foregoing as a modification or economic factor, while others are a part of the normal design procedure. These, in the order of usual" occurrence are discussed herewith. For practical purposes these factors cover Year 'Round Air Conditioning Systems. Those directly applicable to summer only or winter only sys tems are to be viewed accordingly. . . 786 CHAPTER 43 1946 Guide Design Conditions Physiological principles and design conditions are covered in Chapter 12. A detailed study of these'is-beyond the scope of this chapter other than certain recommendations with regard to their application. . Where extreme or unusual outdoor conditions prevail for long periods of time, such as in the tropics, at high altitudes, in regions of extremely low humidities, etc., due allowance must be made for the fact that, the people have become acclimatized, to a certain degree at least, to these conditions and the inside conditions should be selected accordingly. A change in the inside conditions from a set standard sometimes is warranted from an economic standpoint/ It is possible at times to make substantial savings in initial and operating costs by maintaining a lower Central Systems for Comfort Air Conditioning 787 occur during these times can be used provided the cumulative effect or heat gain lag is taken into consideration in the estimate. Outdoor Air Standards affecting the quantity of outdoor air have been established in Chapter 12. These standards relate the minimum amount of outside air to be introduced into the conditioned space for both the number of occupants and the type of occupancy, i.e., people smoking, etc. This, of course, is the common-sense approach to the problem, but there are some cases, such as those spaces having a very low occupancy with regard to the cubical content where mustiness may develop unless a sufficient air change is provided. Where such a condition exists in a few spaces out of several which are being handled by a central system, the averaging ability of the central system may cope with the situation satisfactorily. This is Fig. 7. Central System with Central Fan and Conditioner and with Individual'Zone Fans N . temperature and- higher humidity in the conditioned space while main taining the same effective temperature. . In winter, the matter of condensation oh windows, walls', etc., is of extreme importance. Humidities low enough to avoid this should be maintained, and when it is necessary to carry the higher humidities, double glass should be used or suitable means of handling the condensa tion, should be provided. :' During intermediate seasons the use of refrigeration as a.source of cooling may be undesirable from an operating cost standpoint depending on the local energy rate structure and demand charges. As a result the - use,of outdoor air, either'directly or indirectly, as a source of coolingmay be required and. the system may have to operate on-an unusual basis, with.regard to the temperatures and humidities that can be maintained.; This situation should be carefully investigated. As a rule, provision should be made for introducing all outdoor air into the. system during intermediate seasons. . . ..... . With regard to outside conditions it must.be noted that where systems are to operate at certain hours of the day only, the outside conditions that due to the fact that the return air from the particular space is mixed thoroughly with_the return air from all.the other spaces and all the out side air supplied. ... . It should be noted that the minimum quantity of outdoor air is affected by infiltration and leakage. Infiltration will reduce the quantity to be introduced by the system, while leakage may have to be offset by an increase in the quantity of outdoor air. Most summer and year 'round air conditioning systems should be so designed end arranged that a quantity of outside air at least equal to the quantity of cooled or dehumidified air can be taken in when desired. In the intermediate seasons and in the cooling season it is more economical to take all outside air into the dehumidifier when the outdoor air wetbulb temperature is lower than the inside wet-bulb temperature to be maintained.; Also, where using a spray type dehumidifier or air washer, whenever the outdoor wet-bulb temperature is below the apparatus dew point temperature required, the system can be operated on an evaporative cooling basis, dispensing with the need for refrigeration though cooling may be required. Automatic controls are available for accomplishing this and on reasonably large systems are justifiable from an economic stand point. - ' . 788 CHAPTER 43 :1946' Guide Cooling Load The method of determining the cooling load for a conditioned space or spaces is outlined in Chapter 15. As pointed out therein, many of the items of heat gain are variable and do not reach their maximum values simul taneously. Proper consideration of these peaks and the avoidance of pyramiding these peaks in the cooling load calculations are stressed. Maximum solar heat gain on an east exposure is seldom, coincident with the maximum outdoor wet-bulb. A large difference in the incidence of the peaks between various spaces or parts of the same space indicates the necessity for zoning.. In a building having an east and west exposure where solar heat gain forms a fair share of the cooling load, the times of their individual peaks are apt to be hours apart, and the peak load of one plus the off peak load of the other will be Return air Central Systems for Comfort Air Conditioning 789 In certain types of building construction the effect of solar radiation is still apparent hours after the sun has shifted from that exposure. In other types having,a much- lighter construction, the heat gain due to solar radiation decreases markedly with the passing of the sun. Some walls, having been warmed by the sun, may radiate heat long after the passing of the sun, thus requiring lower inside temperatures to offset the radiant energy. Storage effect is usually present in some degree. Often it can be utilized to great advantage and it has more than once provided an unknown safety factor. If a space is kept below the design inside temperature for a period of time, the interior walls, floors, furniture and fixtures begin to assume the temperature of the space. Where the period of time is sufficient, the entire mass may reach the room temperature, rather than just the skin or surface of the item. Thus, when a space has been precooled below the Fig. 9. Central System Using Dual Duct Method of Zoning substantially less than their combined peak loads. Proper zoning will permit taking full advantage of this condition or similar conditions of non-simultaneous peaks and will result in a lower total load, reflecting itself in savings in equipment. r A factor, similar in effect and closely related to the non-simultaneous occurrence of peak loads, is diversity. Typ'ical of this is the case of a large department store where the air handling equipment serving a certain space must be 'sufficient to handle the load created by the throngs of people attending sales in that space. Under such a condition the number of people in other spaces is usually normal or below. While this means that the air handling equipment for certain departments must be large enough to cope with the situation, the refrigeration equipment must be only large enough to handle the average maximum. If a system employ- ing'zone recirculating fans and a single central fan and dehumidifier were used, the saving would be reflected in the capacity of the central fan and dehumidifier. Another example of this diversity is found in an office' building having restaurants and stores of certain types on the first floor and basement. At noon, when the restaurants and stores are crowded, the offices are below normal occupancy. , Heat lag should be carefully considered in the cooling load calculations. Fig. 10. Induction Unit . (Low Pressure Type) Fig. 11. Induction Unit (High Pressure Type) , design maximum temperature for a period of time prior to the advent of the peak load, and the heat gain begins to increase to peak conditions, some of the increase is used in raising the temperature of the furniture, fixtures, etc., to the design conditions and the cooling load can be reduced accordingly. However, unless very accurate data with regard to the mass, surface, specific heat, etc., of the items within the space are avail able, due caution must be'used in discounting the cooling load for this storage effect. In the absence of reliable data it is often a matter of experience rather than calculation. . : Where air conditioning supply and return ducts pass through uncon ditioned spaces there will be a transfer of heat from these spaces to the air in the ducts, even though these ducts are well insulated. An allowance should, be made for this heat gain and included in the heat estimate so that air can be supplied at a temperature low enough to offset the rise caused by this heat gain (see Chapter 41). There will also be some heat gain to the air in ducts passing through conditioned spaces, but since a cooling effect is produced in the space through which the duct passes, / HffUl 790 CHAPTER 43 1946 Guide this is not a loss and usually can be compensated for by adjustment of air quantities between the various spaces. Heating Load Methods of calculating the heating load are shown in Chapter^ 14. Many of the factors outlined previously under Cooling Load, such as zoning, non-simultaneous peaks, and diversity, apply in the reverse manner due to the heating requirement instead of the cooling requirement. However, these factors enter into the heating load picture from the stand point of control of inside conditions, over-all performance and economy of operation more than from a capacity of equipment standpoint. It is not only necessary to heat a building or space to its design conditions when there is but the merest fraction of normal occupancy, practically no lights, internal heat, or solar radiation, but it is also necessary to provide capacity to heat the building quickly when sudden cold follows relatively warm weather, or after a week-end or holiday shut-down. Central,Systems for Comfort Air Conditioning 791 to summer cooling in mind. Thus, if the air conditioning apparatus can be set to take inside air, process it, and return it to the conditioned space completely saturated at the apparatus dew-point, the cooling load require ments can be exactly met both as to removal of energy and simultaneous removal of moisture. ' , In actual practice with commercial apparatus, it is rarely possible to obtain complete saturation and there may be several degrees differencebetween- the dry-bulb and wet-bulb temperatures of the,air returned to the conditioned space. This causes no difficulty. In fact, the only special significance of the apparatus dew-point is that, when it exists, it provides Fig. 12. Diagkau of Mollier Chart Illustrating Example 1 However, in normal operation during week-ends and holidays, buildings are usually kept at a holding temperature to prevent the freezing of services and conserve fuel. In many cases it requires less fuel to keep a building or space at a temperature of 50 to 65 F for some time than to shut the system down and then bring the temperature up again. Apparatus Dew-Point . , \ ' The method of locating the condition line for a given air conditioning problem has been explained in Chapter 3, Examples 12 and 13. Briefly, the method consists in estimating the net energy gain (or loss) per hour and the net moisture gain (or loss) per hour from data on location, ex posure, construction, appliances, occupants, ventilation requirements,, inside and outside design conditions. In computing the quantities of energy and .moisture introduced and displaced by the ventilating air, only that portion of the ventilating air admitted directly to the con ditioned space is considered. With this understanding, the ratio of the net energy gain (or loss) to the net moisture gain (or loss) determines the. slope of. the condition line through the state point of the inside air on the. Mollier Chart. ' ... , The condition line may or may not cross the saturation curve. If it does, the intersection is called the apparatus dew-point, with application .AIR TEMP.(SATURATED BELOW ROOM DEW-POINl)-"F Fig. 13. Heat and Moisture Absorbing Power of Air Introduced Into a Room Held at 80 F and 50 Per Cent Relative Humidity (60.1 F Room Dew-point) and Various Sensible Heat Factors, Latent Heat Factors, and Multiplier Factors Corresponding to the Supply Air Conditions .. ' a convenient control point at which to regulate the operation of the apparatus, provided complete saturation is attainable. . In order to illustrate the effect of incomplete saturation in the conditioning apparatus, consider the cooling load problem of Chapter 3, Example 18. In this problem, 114,510 Btu of energy and 16.018 lb of moisture per hour are to be removed simultaneouslyi - The slope of the condition line is determined by.the ratio q = 114,510 4- 16.018 = 7149 Btu per pound of water and the apparatus dew-point is 58.08 F, as shown in Fig. 12. (Point B). . But suppose that the air delivered by the apparatus is only 95 per cent saturated. Then the temperature at which the condition line crosses the 95 per cent saturation curve is the proper temperature at which to regulate the apparatus. This temperature is easily found to be 59.65 F dry-biilb temperature (Point A in Fig. 12). Of course, a some what larger, quantity of air will-have'to be recirculated, namely 114^510 -f- (31.514 -- 25.631) = 19,460 lb of dry air per hour, where the enthalpy of the air at 95 per cent saturation on the condition line is 25.631 Btu per pound of dry air and h = 31.514 for the 792 CHAPTER 43 1946 Guide inside air. Only 18,050 lb of dry air had to be recirculated per hour with complete saturation. (Example 13, Chapter 3.) The supply air must have the capacity to absorb the room sensible heat gain and the room moisture (latent heat) gain simultaneously and in the correct ratio. The top portion of Fig. 13 shows the relationship of sensible heat and latent heat absorbing power of air supplied to an 80 F room when room relative humidity is 50 per cent2.. On some psychro- metric charts the line connecting the room condition and the apparatus dew-point on the saturation line is equivalent to the condition line on the previously mentioned Mollier Diagram. - Most practicing engineers prefer other methods of calculating apparatus dew-point which use one of several forms to express the ratio of room sensible heat gain to room moisture (latent heat) gain. The room latent gain is the heat equivalent, in Btu, of the amount of moisture liberated within the space or introduced to the space. This heat equivalent is approximately equal to the latent heat of vaporization at the apparatus dew-point temperature. Since this is variable, an average value of 1050 Btu per pound of moisture gain may be used without serious error for normal air conditioning calculations, when the room and apparatus dew-point temperatures are above 32 F. Since- the load calculation, particularly the room latent heat gain, is only approximate, it is believed that these approximate methods for calculation of apparatus dew-point are sufficiently accurate for most commercial applications. Several methods are commonly used to express the relation of room sensible heat gain to room latent heat gain and these are described in the following: Sensible Heat Factor, (SHF). SHF = Hs Hs + Hi Latent Heat Factor, (LHF). LHF = Hi Hs + Hi where Multiplier Factor, (MF). - MF = Hs + Hi Hs . Hs -- room sensible heat gain, Btu per hour. Hi = room latent heat gain, Btu per hour. (1) (2) (3) These equations are equivalent to one another as shown by the fol-: lowing: %, and LHF = 1 - SHF 1 MF = SHF (4) (5). The sensible heat gain in the room or space must be absorbed by the supply air in order to maintain a given room temperature. Then the following heat balance for-saturated supply air may be written as: . " = (<r - <s) <2m X P X,cp X 60 . . (6), where' '^ Fts = room sensible heat gain, Btu per hour. It -- room temperature, dry-bulb,. Fahrenheit degrees. . is -- apparatus dew-point temperature, Fahrenheit degrees. . Central Systems for Comfort Air Conditioning793 Qm = quantity of supply air, cubic feet per minute, p = density of supply air, pounds per cubic foot. Cp = specific heat of air, at constant pressure, Btu per (Fahrenheit degree) (pound). Similarly the latent heat (moisture) gain in the room must be absorbed by the lower moisture content of the supply air in order to maintain a given relative humidity, and writing a heat balance for saturated supply air: Hi = (W, -- Ws) Qm X p X Av X 60 (7) where ' . Hi = room latent heat gain, Btu per hour. Wr = moisture content of room air, pounds per pound of dry air. Wa = moisture content of air, pounds per pound of dry air at apparatus dew-point. Av = heat of vaporization at apparatus dew-point temperature. Equation 1 shows how to determine the sensible heat factor of the cooling load. The sensible heat factor of the supply air must equal the sensible heat factor of the room load in order to maintain design con ditions. If a dehumidifier that will produce a saturated condition of leaving air is used then Equations 6 and 7 may be solved for Hs and Hi and substi tuted in Equation 1. This for practical purposes can be shown to be equal to: _ SHF = 2f(<r T -- hr -- As (8) where * 0.24 = specific heat of air, Btu per (pound) (Fahrenheit degree). tT = room temperature, dry-bulb, Fahrenheit degrees. 1 is = apparatus dew-point, Fahrenheit degrees. hr = enthalpy of air at room conditions, room wet-bulb, Btu per pound of dry air. As = enthalpy of air at apparatus dew-point, Btu per pound of dry air. Practically, the apparatus dew-point temperature may be defined, for a cooling coil, as the average coil surface temperature; and for a spray dehumidifier of commercial design, (where the saturation efficiency approaches 95 per cent to 100 per cent) as the dew-point of the air leaving the dehumidifier. . Having estimated the room sensible heat factor the problem is reduced to the solving of Equation 8. Since the relation between hs and 4 is only available in tabular or graphical form, a cut and try or graphical solution is required. Fig. 14 has been calculated from Equation 8 and, of course, can be used only for one room dry-bulb temperature, 80 F. The lower portion of Fig. 13 also gives the apparatus dew-point required for various sensible heat factors. Note that if air is supplied at any temperature above the room dew-point, only sensible heat is absorbed (SHF = 1.0); and that below this point moisture is absorbed in a very rapidly increasing proportion to sensible heat. A point is finally reached where the proportion of moisture absorbed to sensible heat absorbed is practically constant and a lower apparatus dew-point will not remove a greater proportion of moisture. A room condition can be maintained if the load sensible heat factor lies on the curve corresponding to the design room humidity in Fig.-14. For example, if the load SHF was 0.55 for a design room condition of 80 F dry-bulb and 50 per cent relative '.humidity, it would not be possible to maintain this condition unless reheat X 794 CHAPTER 43 1946 Guide is used to raise the sensible heat factor at least to 0.59. Reheat should be added in the room, in the supply air duct, or in the dehumidifier after' the cooling coil or spray section. Reheat is usually supplied by steam coils or by a hot gas interchanger using the hot discharge gas from the refrigerating machine. ' Example 1. From a cooling load analysis of the room as determined in Example 12, Chapter 3, the net sensible and latent heat gain of 114,510 Btu per hour would be called room total heat; the net moisture gain of 16.018 lb per hour, multiplied by the approxi mate value of 1050 Btu per pound of moisture, would be called the room latent heat; namely, 16,820 Btu per hour; and 114,510 -- 16,820 = 97,690 Btu per hour which is Fig. 14. Apparatus Dew-Point Required-for Various Sensible Heat Factors (SHF), Latent Heat Factors (LHF), and Multiplier Factors (MF) Corres ponding to Various Room Relative Humidities, for Room Dry-Bulb Temperature of 80 F - the room sensible heat. Determine the apparatus dew-point if the room conditions to be maintained are 80 F dry-bulb and 67 F wet-bulb temperature'fSl.l per cent relative humidity). , Solution: From Equation 1 the sensible heat factor is SHF = 97,690 n- 114,510 0.853. Solving Equation 8 by cut and try or by plotting this equation on a curve similar to that in Fig. 13, the apparatus -dew-point is 58.6 F. The apparatus dew-point is 58.08 F as determined in Example 12 of Chapter 3. This should be sufficiently accurate for practical applications. . ., In actual practice, with commercial apparatus, complete saturation is 'seldom obtained. Four-row finned coils contact approximately 80 per cent of the air, whereas six-row finned coils contact approximately 95 ' P?r cent f the air. With spray type dehumidifiers of good design the air leaves the dehumidifier at V to 2 deg higher wet-bulb temperature than the spray water leaving the dehumidifier, and the difference between. the dry-bulb and wet-bulb temperatures'leaving the dehumidifier may Central Systems for Comfort Air Conditioning 795 be 1 deg. A spray'dehumidifier having sufficient length of spray chamber and density of spray, together with proper arrangement of nozzles, may approach absolute saturation very closely.. The slope of the condition line, or the slope of the line on the psychrometric chart connecting the room condition with the apparatus dew-point on the saturation line, determines the ratio of sensible heat absorbing capacity to the moisture absorbing capacity of the supply air. Therefore the room condition can be maintained as long as the supply air tempera ture lies on this line, but a greater volume rate of supply air must be used to satisfy the room load if the coil does not contact. 100 per cent of the air. For a given room load, the same apparatus dew-point wilt be' required whether the coil contacts all the air or only part of the air. From the point of view of satisfying the given cooling load require ments, the result of air passing through the apparatus without being contacted produces two effects: (1) It increases the air quantity to be passed through the dehumidifier. Thus, if 20 per cent of the air passing through the coil is contacted, then 25 per cent (0.20 -s- 0.80 X 100) more air must be used than would be necessary if all of it were contacted. This is readily seen by examining the heat balance in Equations 6 and 7. (2) It may change the room load which in turn may change the sensible heat factor. If only return air is passed through the dehumidifier or if only room air is by-passed, the room load would not change, but if some outside air is passed through the coil, the room Sensible heat gain and room latent heat gain will be changed due to the addition of untreated outside air to the room, which changes the sensible heat factor. When a load calculation is made, it is necessary to know the pier cent of air con tacted in the cooling coil and calculation made accordingly. If the ventilation air is drawn through the cooling coil before it goes into the room, only that portion of the air not contacting the coil surface must be included in the room load for the purpose of determining the apparatus dew-point and supply air quantity. It should be noted when evaluating the load added by untreated outside air that the temperature difference between room and outside air and moisture content between room and outside air should be used and not the difference between out-, side air and apparatus dew-point, since the rise from the apparatus dew-point .to room conditions is charged against the dehumidifier as the cooling and dehumidifying load. In winter, room hupiidities in excess of 30 per cent are seldom required and a low saturating efficiency may be desirable, or even necessary, where the full summer air circulation through the conditioner is maintained. With a spray type dehumidifier the main sprays may be shut off and an eliminator flooding pump provided which may give sufficient saturation. In other cases, such as where.cooling coils are sprayed, the spray water supply may be throttled. - If the saturation efficiency of the sprays is too low, the spray water may be heated. The amount of heat put into the spray water by open or closed water heaters will be equal to that required . to bring the dew-point temperature of the air entering the sprays up to that required before entering the preheater. It is possible, where clean steam is available, to introduce the steam directly into the air stream to produce the desired dew-point temperature of supply air.. However, the steam must be exceptionally clean, or objectionable odors will result. . This precaution should be observed also where open water heaters or ejector water heaters are used. 796 CHAPTER 43 1946 Guide Air Quantity and Effective Temperature Difference The difference between the room air temperature and the supply air temperature at the outlet to the room is known as the effective temperature difference. In the theoretical case of a dehumidifier having a 100 per cent saturating efficiency and where this air is delivered directly to the room without temperature increases due to heat gain, then the effective tem perature difference is the difference between room temperature and apparatus dew-point temperature. If duct heat gains are considered a part of the room load, this still holds true. The apparatus dew-point, as outlined previously, is fixed by the latent and sensible loads of the space, but in many cases, it is desirable to deliver more air to the spaces than is indicated by the difference between the room temperature and the apparatus dew-point. It has been indicated that where a percentage of air is passed through the dehumidifier without being treated the relationship was modified in direct proportion, and that if room air passed through untreated no effect on the heat balance resulted. Similarly, if room air is passed around the dehumidifier and mixed with the treated air the . heat balance is not adversely affected. Therefore, if the quantity of air passed through the dehumidifier is determined by the usual methods, room air can be passed around the dehumidifier and mixed with the dehumidified air, increasing the supply air quantity and temperature and decreasing the effective temperature difference. Thus if the difference between the room tem perature and the apparatus dew-point indicates that 10,000 cfm at 30F below room temperature will be required to hold conditions, that quantity can be passed through the dehumidifier and copied to 30 F below the room, then mixed with 10,000 cfm of room air resulting in a supply air quantity of 20,000 cfm and an effective temperature difference of 15 F instead of 30 F. Supply air outlets and grilles that have a high induction ratio (that is, a large amount of room air is mixed with the air leaving the outlet within a short distance of the outlet through the induction effect of the air stream) are available as well as induction units. A proper selection of outlets or units may make it possible to introduce air at low temperatures and high velocities without causing objectionable drafts or cold spots, but care must be used to see that too little air motion is not a result. Lower effective temperature difference may be required for this reason. While the use of a high effective temperature difference results in a saving in initial cost of fans and ducts and in the operating cost of fans, this difference should be carefully considered. If the sensible heat load of a space is subjected to substantial variations;, lower effective temperature differences should be considered, since systems employing a low effective temperature difference will be less exacting in control requirements. Assume that a space has a sensible heat load so that 10,000 cfm of air supplied at a 30 F effective temperature difference would be required to maintain a room temperature of 80 F. If the load is suddenly reduced 50 per cent with the air supplied at the same temperature, the resultant room temperature would become 65 F. On the other hand, if 20,000 cfm were supplied at an effective temperature difference of 15 F and the load suddenly reduced 50 per cent the resultant room temperature would be ' 72.5 F. This, while a rather extreme example, indicates the less exacting -demand on the controls brought about by the use of the lower effective temperature difference. Of even greater importance is the case where two or more spaces are controlled from an average condition such as by a ther mostat located in the return air stream! From the previous example, it Central Systems for Comfort Air Conditioning 797 can be seen that a large variation in the load in one of the spaces will not reflect itself in such a large change in room temperature. Thus in the long run the larger effective temperature difference may not be the most economical. The analysis in the foregoing applies largely to summer air conditioning. The same analysis will apply to some extent in winter. The mathematical relationship is revised due to a heating requirement rather than cooling. Present practice indicates a high temperature difference in winter in com parison to that for summer. It is due to the fact that the heat losses in winter in Btu per hour far exceed the summer heat gains in Btu per hour, and particularly to the fact that in winter, reheating the air. to produce desired room conditions is not reflected as a load on the system as it is in the summer, but merely accomplishes the necessary work. In line with the latter, reduction of air quantity by slowing down the fans for the winter season and increasing the temperature difference often is feasible, creating a saving in fan horsepower at no expense to the final heat balance, providing the air distribution is not seriously affected. Extremes should be avoided in all cakes. For summer air conditioning low supply air temperatures will result in larger heat gains to the air passing through the ducts, poor control, etc. Too high a supply air tem perature may result in excessive initial and operating costs. Suggested limits for the effective temperature difference are from 12 to 20 F, the actual selection being based on the requirements of the particular case. For winter air conditioning too high supply air temperatures result in excessive heat losses from the ducts and stratification within the room unless thorough mixture is insured, while too low supply air temperatures may cause drafts, high operating costs, etc. Suggested limits are from 15 to 35 F. There can be no set rule and each case should be judged according to its particular requirements. -, By-Pass - The by-pass, in its accepted form, consists of an arrangement of ducts and apparatus connections with the necessary dampers which will permit air to pass around the dehumidifier or conditioner without being treated. It has two functions which may be employed separately or simultaneously. The first of- these is to provide a means of temperature control at a substantially constant total air quantity. If in summer, the load within the conditioned space is reduced and the temperature begins to fall, this drop in temperature can be offset by passing some of the air around the conditioner instead of through it, while the total quantity of air in circu. lation remains unchanged. When used for this purpose, it is termed an adjustable or automatic by-pass. The second function is to maintain a lower effective temperature difference between the air supplied to the room and the room temperature than could be obtained if air at the apparatus dew-point were supplied, and when so used is called a fixed by-pass. As discussed previously, if return air from the conditioned space is passed around the conditioner and mixed with the conditioned air, the effect on the heat balance is the same as if the air were removed from the space and immediately reintroduced. This is not strictly true, due to the fact that when ducts pass through unconditioned spaces, there is a heat gain by this air, and an additional gain is imposed by the heat of com pression of the circulating fan in moving the air against the resistance of. the system. However, the heat gain, where the by-pass is used to lower the effective temperature difference, usually favors its use due to the fact 798 CHAPTER 43 1946 Guide that the increased volume and the resultant higher temperature of the mixture of conditioned air and room air may show a lower net duct heat gain with a smaller temperature increase per unit of volume of supply air. The advantages thus obtained may offset the increased fan power. The adjustable or automatic by-pass can be made to serve the purpose of the fixed by-pass by providing a stop on the by-pass damper so that it cannot close completely. In some cases this stop is unnecessary since commercial dampers will permit an air quantity of 10 to 20 per cent of the conditioner capacity, depending on the resistance of the conditioner, to leak through'even when fully closed. Where a reduction in room sensible heat is not accompanied by a reduction in room latent heat,'the by-pass is to be used with care. If the dew-point temperature of the air leaving the dehumidifier is con trolled at a fixed value the reduced quantity passed through the con ' ditioner may be sufficient to handle the sensible heat load but insufficient to handle the latent heat load, resulting in humidities that are too high. If the dew-point is not controlled, as when cold water is supplied at a constant temperature or where direct expansion cooling coils are used, the reduced loading on the conditioner brought about by the reduced air quantity will result in a lower dew-point temperature which often is entirely adequate. This condition should be investigated in each case. The by-passing of outdoor air is to be avoided in general. While the sensible heat requirements of the space may be such that the by-passing of high temperature outdoor air will aid in controlling room temperature, high moisture content air introduced to the space may raise the humidity to an objectionable amount. If return ducts frorq which the by-pass air is taken run through unconditioned spaces and there is an inward leakage of outdoor or moist air, the effect, in a lesser degree, is that of by-passing outdoor air. Therefore the location of such return ducts and the points from which such air is taken are of importance. Exceptions to this are where the moisture content of the outdoor air is lower than that of the room, and where the sensible heat to latent ratio increases at partial loads. The foregoing applies largely to summer air conditioning. In winter the by-pass usually is kept closed and room temperature control obtained by means of regulating the amount of heat supplied to the air. In some instances when the by-pass is located after the reheaters, the operation of the by-pass damper may be reversed and the by-pass still used as a means of control with the reheaters full on or operated in sequence with the by-pass. In other cases the reheater may be located in the by-pass as described further. \ The principle of the by-pass may be applied to items of equipment other than conditioners, such as humidifiers, dehydrators, heaters, etc.,' in much the same manner. Where a heater has a capacity such that the temperature rise of the air is higher than desired, a smaller heater may be used and a portion of the air by-passed around the heater. Throttling of the sprays in a humidifier is, in effect, a by-pass since it increases the portion of air passing through without being contacted. Reheating ,. Reheating the supply air is necessary inrwinter where this air is usedto offset heat losses. Tempering of the supply air (merely reheating to a lesser degree) is required where other means of heating, such as direct radiation or panel heating, are used to carry the main heating load. Supply air at the required apparatus dew-point would add to the load to be carried Central Systems for Comfort Air Conditioning 799 by the direct radiation and in addition may create a movement of cold air that while desirable in summer may be undesirable in winter. Modu lation of the amount of steam supplied to the coils can be used to control temperature, or air can be by-passed around these heating or tempering coils. Since reheating or tempering coils are required for winter and year 'round air conditioning, their use as a means of summer as well as winter temperature control is indicated. Where heat is available in summer, as the room sensible heat falls off, the low temperature of the supply air can be raised by means of these coils to maintain the desired room tempera ture while still providing adequate air at the proper dew-point. Reheating presents an excellent method of accurate temperature control since the quantity of air passed through the conditioner is not changed as in the case of the by-pass, and since the distribution and circulation are not affected as when the volume of supply is reduced. However, reheating in summer has one disadvantage. It has the effect of maintaining a constant internal sensible heat load on the system. This means that when an effective temperature difference of 15 F is being maintained at the maxi mum room sensible heat load, this temperature difference must be reduced by means of heating to 7.5 F at half of the sensible heat load. The room sensible heat usually is about 35 to 45 per cent of the total cooling load and thus the penalty imposed on the refrigeration cycle is not extremely large. When the, outdoor wet-bulb temperature is less than the desired room wet-bulb temperature, all outdoor air should be passed through the conditioner and under these circumstances reheating does not impose a load on the refrigeration cycle since the heated air is not returned to the conditioner. Further, where the volume of outdoor air introduced to the . system, which for all practical purposes is wasted after its work has been - done, is sufficiently large in relation to the amount of reheat used (that is, if the heat required does.not exceed that necessary to raise the outdoor air only from dew-point to room temperature) the use of reheat does not impose a load on the refrigeration cycle.. This, of course, assumes that there is no economic penalty involved in the use of heat itself. . ' One of the. best applications of reheating for summer purposes is in combination with other means of temperature control for the. purpose of leveling off accentuated demands for temperature control. As an example, -the by-pass can be applied to a certain extent, or the volume of supply air throttled to a limited degree, or both of these used in sequence, and reheating, can be used as the final step in temperature control. In the foregoing it has been assumed that summer reheating is derived from: an extraneous source of heat such as steam, electric heaters or hot water. The economics of reheating as outlined may be improved by the use of sources of heat that are available within the equipment used. : Where certain types of refrigeration cycles are used, auxiliary refrig erant condensing coils can be placed in the air stream. At partial loads these can be used as additional refrigerant condensing surface and improve the performance of the refrigeration plant. This is generally known as hot gas reheating.' 'Less effective is the use of coils in the air stream through which liquid refrigerant from the condenser is passed before being delivered to the evaporator, sub-cooling the liquid refrigerant and improving the performance of the refrigeration cycle. The use of refrigeration condenser water as a source of reheating provides definite economies! "If the condenser water is passed through coils in the air stream before being used for refrigerant condensing purposes, the lowering 800 CHAPTER 43 1946 Guide of the condenser water temperature accomplished by reheating the air will result in savings in the refrigeration plant power consumption and increased refrigeration capacity. The latter two methods are at some disadvantage in that the amount of reheat available decreases as the need for reheating increases, particularly where evaporative condensers or cooling towers are used. Zoning Zoning consists of an arrangement of equipment or a division of equip ment into sections that will permit individual control of the temperature and humidity .of those spaces or groups of spaces that do not have simul taneous variations in sensible or latent heat load. The equipment is so arranged or divided that air can be supplied to spaces or groups of spaces in accordance with the individual load requirements of that space or group of spaces. Solar heat gain is one of the major causes of the zoning requirement since its effect and amount vary with the season, time of day and exposure. Other sources of heat gain, subject to variations, such as large changes in the number of occupants in one space with a constant occupancy in another indicate the necessity of zoning. Some of the various methods of zoning are: .! - 1. Separate equipment. 2. Reheating or recooling. (See Figs. 4 and 5:) 3. Multiple fans with individual by-pass. (See Figs. 6 and 7.) / 4. Volume control. (See Fig. 8.) 5. Dual duct system. (See Fig. 9.) . 6. Combinations of the above methods. . Zoning by separate equipment represents the extreme in zoning. In dividual conditioners, fans, heaters, controls, distributing duct work, etc., are provided for each zone and are separate from those of other zones. Each assembly of equipment is arranged to operate at full or partial load according to the requirements of that zone. In extreme cases an individual refrigeration plant may be provided for each zone. In general, this method of zoning is uneconomical since each piece of equipment is large enough to handle the full load requirements of that zone and no advantage can be taken of the fact that while one zone is at its full load others may be operating at considerably less than full capacity. This applies both to the initial cost of a system and the operating cost. There are, however, many cases where this method of zoning when used to a limited degree or combined with other methods is most desirable^' - Zoning by reheat is one of the more simple methods of approaching-the problem of differing variations in load. Reheating has been discussed in the foregoing. Heating coils located in the distributing duct work or apparatus connections which supply only those spaces having sub stantially the same load variations will, by adding heat when the cooling load falls off (or the reverse in the case of a heating load), maintain the desired temperature conditions. It has been shown previously that where the amouht of reheating required is not excessive and that heat for this purpose is available from an economic standpoint this method of zoning may be entirely practical and even highly desirable. Zoning by recooling is literally the reverse of zoning by reheating. It is not used often but there are many cases where it is desirable. Its most practical application is limited to a sensible heat removal function where the latent heat requirements are handled by another source such, as a Central Systems for Comfort Air Conditioning 801 dehumidifier or dehydrator, and \yhere the recooling equipment (usually cold water cooling coils) can be utilized for reheating (usually with hot water) in the heating season. In using this method of zoning, when the cooling load of a given space is reduced, the cooling effect produced by the recooler is also reduced. . , The use of multiple fans with individual by-passes presents a simple and sometimes inexpensive method of zoning. Two or more fans may be arranged so that each draws its treated air from the same conditioner. The connection between the conditioner and fans is divided or partitioned in such a manner that a by-pass connection can be made to each fan. See Fig. 6. In this way the amount of by-pass air can be regulated accord ing to the requirements of the zone served by that fan. In this application a face damper must be used for each segment of the conditioner, arranged to close as the individual by-passes open or an unbalanced system may result. A much better adaptation of this principle, though slightly higher in initial cost, is obtained by using a- single conditioner or dehumidifier, having a central conditioned air fan delivering the treated air to the necessary zone fans where the conditioned air is mixed with return air according to the requirements of the zone. See Fig. 7. With this method of zoning, the zone fans are provided with casings to which both return air and conditioned air are delivered, their proportions being regulated by dampers working in opposite directions. : If conditioned air is delivered to the casing at slight positive pressure the return air damper may be omitted. Reheating can be effectively combined with either of these for year 'round use or for winter use only. The reheater is usually located in the air stream to the zone fan. Where a central conditioned air fan is used to deliver conditioned air to a number of zones, a static pressure regulator controlling a volume damper or inlet vanes on this fan should be in stalled to prevent unbalancing the system, when one or more zone fan conditioned air dampers are throttling. This is one of the better methods of zoning and is particularly effective when used in combination with reheating for winter or year 'round conditioning as previously outlined. Volume control is the least expensive and most frequently used method of zoning. It is usually obtained by placing a throttling damper in the supply duct feeding a particular zone and operating the damper to restrict flow of air as the heating or cooling load is reduced. The damper may be operated manually or automatically. Volume control,, however, has two serious disadvantages. The first of these is that any large reduction irt the quantity of air supplied may impair the ventilation. The second is that a large reduction of the air supply may entirely upset the distribution from the room outlets causing dead pockets, stratification, lack of air motion, or the reverse--undesirable drafts. Where the degree of volume control is large or the system extensive and where volume con trol is applied to one portion of a system and not to another, the use of a static pressure regulator controlling a fan discharge damper or fan inlet vanes is indicated. Its'best application is in combination with some other method of zoning such as reheat or by-pass where it is used as one step in a control sequence, and the reduction in. volume limited to a proper amount. The dual duct method of zoning, sometimes referred to as the schoolhouse system, can be successfully applied to comfort air conditioning though certain precautions must be observed. Essentially this method employs a source of warm air and a source of cold air both of which are delivered to a common point where either or a mixture of both are 802 CHAPTER 43 1946 Guide delivered to a particular zone according to the requirements of that zone. See Fig. 9. Several variations of this method are possible, some of which do not employ dual ducts as denoted by the name but which utilize the principle. An example of this is found in a blow-through system where'' the fan is located on the entering side of the conditioner and the con ditioned air passes from the conditioner into a plenum from which distributing ducts for the various zones are taken. A by-pass connection around the conditioner from the fan to the zone duct is made and dampers !) provided so that conditioned or untreated air, or a mixture of both is passed into the zone supply duct. In this method of zoning and in most of the variations of this method, the matter of by-passing untreated or outdoor air presents itself. This has been discussed earlier in this chapter. If a return air fan is used and the by-pass connection made from the return fan to the zone supply duct, then the by-passing of outdoor air does not need to be considered. Complication of ducts and con nections should be avoided since it may result in difficult sheet metal work with accompanying leakage of air and waste of cooling or heating effect. Combinations of these several methods of zoning usually provide the most effective zoning. It is then possible to use each method to its greatest advantage without incurring operative or economic penalties which may be inflicted by the exclusive use of any one. Thus, where wide variations in load occur, volume control can be used to reduce the air quantity a limited amount, then as the load continues to fall off, reheat, or by-pass, or both can be used. By-pass and reheat can be used in series very effectively. Many combinations are possible and each case should be considered with regard to its particular requirements when deciding on the method of zoning. * Induction Units--Low-pressure type Induction units are essentially induction type convectors. These unitsutilize a jet of conditioned air (or primary air) to induce into the unit a flow of room or secondary air which mixes with the primary air. The mixture is discharged into the room through a grille at the top of the unit. Heating coils are located in the secondary air stream for use in heating. Control is obtained by either manually or automatically throttling the jet, and, in addition, heat may be supplied to the secondary coils in summer as well as winter to provide control by reheating. The use of these induction units presents several advantages. Since the secondary air stream is thoroughly mixed with the high velocity low temperature air stream before leaving the discharge of the unit, the resultant temperature of the mixture is satisfactory even though the primary air is introduced at a temperature too low for ordinary methods of distribution. A unit is usually provided under each window in place of the customary direct radiation, and combines the air distribution system with the.-heating system. With a conventional., system it may be necessary to provide supplementary heating in the form of direct radiation. These induction units may be selected so that their heating- coils will have sufficient -capacity under gravity conditions (that is, with the fan system off and no primary air entering the unit) to maintain the building or spaces at a reasonable temperature. The use of low temperature, dehumidified air which has not been reheated or mixed with room air before delivery to the room results in a reduction in fan capacity and smaller sized duct work. .In some cases the use of the by-pass may be desirable in order to keep the primary air volume up and provide additional control. This system . can provide a degree of zoning that is usually impossible with conventional Central Systems for Comfort Air Conditioning 803 systems since each unit can be put under manual or automatic volume control and reheat control. The selection of units should be made with regard to noise level when related to the noise level of the spares. The inductive capacity of the unit increases with the jet velocity but too high jet velocities result in a high noise level. Induction Units--High pressure type '. A recent development of the induction unit as previously outlined is the high pressure type of unit. This unit employs nozzles which produce a high velocity jet quietly. The term, high pressure type of unit, is to some extent inaccurate since the pressure at the nozzles, while several times that of the low pressure unit, is still less than the total resistance pressure of a conventional central system. The high velocity jet of primary air induces a flow of secondary room air through coils located in the secondary air stream. The coil in the secondary air stream is sup plied with chilled water in summer and hot water in winter and thus handles a large portion of the room sensible heat gain in summer and of the room sensible heat loss in winter. The primary air is supplied at a sufficiently low dew-point to take care of room latent heat gain in summer. In winter, it is supplied at a. sufficiently high dew-point to take care of room latent heat losses. Control of temperature is obtained by throttling the water quantity supplied to the secondary coils. The quantity of primary air is greatly reduced due to the fact that a portion of the room sensible heat load" is carried by the secondary air stream coil. Since the primary quantity is small, very high velocities can be carried in the supply ducts without requiring fan power in excess of that required for a con ventional system. This means that the supply ducts or pipes can be very small and can be run in chases, or furred in at columns with the water pipes. The primary air is treated in the usual manner to provide air at the required dew-point and either a surface or spray dehumidifier or a dehydrator may be used. The primary air quantity is sufficient for ventilation purposes, and frequently consists entirely of outdoor air. The water piping for the units can be so arranged and valved that hot water can be supplied to one zone that may require heating while cold water may be supplied to a zone that requires cooling. This system is usually limited in application to hotels, apartments, office buildings and other multi-room installations having a large perimeter with relation to the floor area. The units are usually installed beneath the windows, replacing direct radiation or convectors. Where the spares to be conditioned extend a large distance from the outer wall into the interior of the building, a separate system or zone for the conditioning of the interior portions may be required. Evaporative Cooling "' In climates where on design maximum days, the outdoor wet-bulb depression is relatively high it may be possible to dispense with refriger ation or other cooling sources by use of the evaporative cooling effect. A well designed air washer using recirculating sprays will reduce the entering dry-bulb temperature to within a degree or two of the entering' wet-bulb condition. Thus, it may be possible that with air entering at 100 F dry-bulb and 60 F wet-bulb temperature a leaving condition of 62 F dry-bulb, nearly saturated can be obtained; Under some conditionsof latent and sensible heat load the results may be entirely satisfactory. Under those conditions when the outdoor wet-bulb temperature is not quite low enough to permit the use of straight evaporative cooling it is' 804. CHAPTER 43 1946 Guide possible to use precooling coils with refrigeration, well water or a cooling tower as the basic source of cooling to lower the wet-bulb temperature, (by sensible heat removal) of the air before it enters the air washer. Where internal heat loads are high, this may be more economical than using return air. Under other conditions where the required supply air dew point is too low to permit straight evaporative cooling and the sensible heat load not too great, intentional partial saturation may be employed. That is, the low dew-point of the outdoor air is utilized by permitting some of it to pass through the humidifying sprays untreated or pass around the humidifier. All of these remarks with regard to evaporative cooling are based, as indicated, on the assumption that the supply air will consist entirely of outside air. Provision should be made for the return of air from the conditioned spaces for control purposes as well as for winter use in all cases. ' Precooling Where sufficiently cold water from wells or streams is available a saving in the refrigeration cycle may be obtained by the use of precooling. Cooling coils are placed ahead of the dehumidifier or conditioner and the cold water from a well or stream circulated through the coils. The resultant cooling of the air decreases the load to be carried by the de humidifier and refrigeration plant. In normal practice the water after passing through the precooling coils is delivered to the refrigeration plant for condensing purposes. The economic advantages of this scheme are apparent and it is frequently used. Sensible Cooling with Dry Cooling Coils , - Under certain atmospheric conditions where a large wet-bulb depres sion exists and the dew-point of the outdoor air is sufficiently low at all times, proper inside conditions may be obtained by removing sensible heat only from the outdoor air and supplying it to the spaces. Under this condition of a high wet-bulb depression a cooling coil may be located in the air stream and this coil supplied with water from a cooling tower of one type or another. When humidity control is desired sprays to saturate or partially saturate the air may be used after the dry cooling coil. Saturation or partial saturation after the dry air cooler will further reduce the dry-bulb temperature of the supply air and reduce the supply air quantity required. This system has very definite application in hot dry climates and in general is most economical. Run-Around System v An interesting method of control is found in the use of combined re heating and precooling usually termed the run-around system. Coils are placed in the air stream before and after the conditioner and water or brine is circulated around the conditioner from one coil to the other. The; water passing through the reheating coil is cooled by the air leaving the dehumidifier and the air is heated by the water. The cooled water is then circulated through the precooling coil where the entering air is cooled by the water and the heated water sent back to the reheating coil. The run- around has the advantage of permitting a higher supply air dew-point ' temperature than would be possible otherwise. This is due to the fact that continual reheating is available which is not a large penalty on the refrigeration plant since it provides precooling at the same time. This reheating at peak load creates an artificial sensible heat gain which in creases the ratio of room sensible heat to room total heat and for a given room temperature results in a higher apparatus dew-point. Thus, while Central Systems for Comfort Air Conditioning 805 the volume of supply air is increased, the low side temperature level of the refrigeration plant is raised and this may effect savings in initial and operating costs. This system has the disadvantage of providing a decreasing amount of heat for reheating as the demand for reheating increases. . RELATION TO BUILDING TYPE Few buildings or spaces are physically identical and those that are similar in this respect may have marked differences in internal loading, zoning requirements, and economic limitations. Consequently it is virtually impossible to establish fixed rules governing the type of system to be used. Each case must be considered on its own merits with due regard to all engineering and economic factors. 'However, some generali zations are possible. In small single spaces the use of an elaborate system is undesirable from an initial cost standpoint. Zoning may be often eliminated. This also applies to large single spaces except that in very large spaces the necessity of providing adequate zoning is encountered more frequently. If the spaces are extremely large, physical and economic limitations such as the size of equipment, size and length of ducts,' may require the division of the space into sections. Whether these sections are to be made according to zones or whether each section is to be zoned will depend on the particular case. ' Where groups of spaces or small buildings are encountered, simple sys' terns still prove the most economical. A single central station with zoning by means of volume control and reheat combined may be entirely satis factory. If the perimeter of the building is large with regard to the area, induction units of the low or high pressure type may be employed, par ticularly if it is a multi-room application. Occasionally the dual duct sys tem may be considered, but is infrequently used due to its complications. Low buildings with large floor areas, such as large department stores and large general offices, may have to be divided into sections for treat ment. In the case of large department stores it may be possible to provide a single conditioner with a fan delivering the conditioned air to recircu lating fans which supply the various departments or spaces. This application is limited by practicability of running the large conditioned air ducts to the various recirculating fans. In some cases the use of separate systems for each section will be indicated with the added neces sity of dividing into horizontal as well as vertical sections. If the latter is required, each vertical section may be handled by a separate system con sisting of a single conditioner and fan delivering conditioned air to recircu lating fans supplying the horizontal sections. Zoning is obtained by proper allocation of the recirculating fans or other conventional methods used in conjunction with the recirculating fans. For general offices in particular, or types of buildings having a large perimeter, the use of one of the induction type units for perimeter treatment, combined with a con ventional system for the treatment of the interior portions, offers pos sibilities. High buildings having large floor areas may be successfully handled in many ways. Horizontal or vertical sectionalizing or both may be required, as determined by economic factors and physical limitations. Where vertical sections only are required, the use of a single conditioner and fan for each section delivering conditioned air to zone fans at various floors may be used. These zone fans can be so arranged that one recirculating 806 CHAPTER 43 1946 Guide fan can handle similar zones on several floors, thus reducing the number of fans required and providing a degree of vertical zoning. Where vertical sectionalizing is not indicated, the building may be divided into hori zontal groups, each handled by a central system and adequately zoned. In some, extremely large buildings apparatus rooms for the systems may be located in the basement and in the attic and on intermediate floors. In high buildings having small floor areas the treatment required may be the same as for that of a vertical section of one having a large floor area. A single conditioner and fan can be used to deliver conditioned air to recirculating fans located at various floors. In all cases of high buildings the necessity for horizontal sectionalizing is indicated by the economical size of air supply and return risers and by the extent to which they encroach upon usable space. In all buildings the necessity for vertical sectionalizing is indicated by the economical size of horizontal supply and return ducts and the space requirements of these ducts. Usually the most simple systems are best adapted to theaters, audi toriums, and similar applications. Zoning is seldom required other than in connection with auxiliary spaces served by the same system. A con ventional central system with by-pass control possibly augmented by reheat usually will suffice. The auxiliary spaces may be supplied with air from the same system controlled by volume reduction and reheat. Balconies and large lobbies frequently justify the use of separatezoning fans. The foregoing are merely generalizations and suggestions. It is the responsibility of the engineer to explore thoroughly the possibilities of all types of systems and employ that best suited* to the purpose from a standpoint of maintained economy, maintenance, life, operation and physical applicability. EQUIPMENT SELECTION Other chapters cover in detail most of the items of equipment used in a central system. Each item must be selected not only on its own merits, but in relation to all the other items that go to make up the complete central system. Each item should be considered from the standpoint of. both initial cost and operating costs. Consideration must be given to performance at partial loads since most systems operate at full load but a small percentage of time. Many items of equipment have been well standardized and are manufactured in certain definite sizes. The fullest advantage.of this should be taken. One item that may be oversized of necessity may permit the use of a smaller piece elsewhere. Fans operate at full capacity continually in many systems and therefore should be selected for good efficiencies. In winter where higher tem perature differentials are used it is possible to use lower air quantities and a two-speed motor may be provided for the fan, resulting in a power saving. In such cases the air distribution under the reduced volume should be investigated before providing this feature. In selection of the dehumidifier or conditioner the relation of this item to the refrigeration plant is to be given careful consideration. Frequently, it is possible to make a saving in the refrigeration plant by providing more surface in the dehumidifier or conditioner. On the other hand, an excess of capacity in the refrigeration plant can be used to lower the apparatus dew-point (if the lower room humidity is satisfactory) resulting -in a reduced quantity of dehumidified air and smaller dehumidifier. Central Systems for Comfort Air Conditioning 807 In winter, where preheating coils in outside air intakes are required and subjected to entering air temperatures below freezing, the coils should be selected for operation at full capacity whenever the entering air tem perature is below 35 F or where throttling of the steam supply to the coils is desirable. A type of coil that is designed especially for this must be used. In many cases the use of preheaters is not justified since the temperature of the mixture of outside and return air may be entirely satisfactory. Where reheating coils are used after the supply fan, either as zone control reheaters or boosters, and are relatively near outlets, care is to be used to install these coils so that any stratification of temperature pro duced by the throttling of the steam or water supply does not result in cold air being delivered to one outlet and warm air to another. Some types of coils that do not produce stratification under throttled con- . ditions are commercially available. The selection of the refrigerating plant is in itself an economic study. The availability, consumption, and costs of condenser water are to be compared to the initial costs involved and water savings produced by the use of cooling towers or evaporative condensers. Whether or not a direct expansion or flooded system, cold water or brine type of plant will be used is not only a matter of initial cost but one of over-all performance, operating economy, compactness, and in some cases; one of safety. Where water or brine is used as a cooling medium, the possibilities of using lower temperatures and decreased quantities of water or brine, with resultant savings in pumping power and line sizes, are to be compared with the increased power consumption and probable increased cost of the refrigeration machine. ' Air cleaning devices are to be selected according to the particular requirements of the project as well as to existing atmospheric conditions. In some applications such as certain types of stores or departments in large stores, lint screens should be provided for the return air as well as filters. Whether or not return air is to be filtered will depend upon the individual case and will be related to the amount of dirt or dust generated in or brought into the conditioned space from various sources. The type of filter or cleaning device to be used depends largely on economic con siderations. Obviously an expensive high, efficiency cleaning device is not warranted where atmospheric dust or dirt is of such a nature that a less expensive, less efficient device will remove the more objectionable matter. Interior cleaning costs, dust and dirt damage, and hazard due to an accumulation of inflammable dust or dirt within the system are most important factors. . Automatic instruments are nearly always used in.present practice for the control of temperature and humidity and to an increasing extent in the control of large refrigerating plants as well as small ones. Whether electric or pneumatic controls are to be used is a function of the particular requirements of the application and with certain exceptions a function of economy. Either electrically or .pneumatically operated controls can be made to serve the same purpose though the individual case may favor one or the other. A detailed discussion of automatic controls may be found in Chapter 34. One point is to be emphasized. In general, the simpler the control system the better it will perform. Control systems seldom receive the maintenance they deserve and the fewer the instruments and devices the better the care. Further, it is poor, policy to provide, at additional expense, instruments of extreme sensitivity to devices in capable of responding to the control demands. 808 CHAPTER 43 1946 Guide Insulation is an important factor in air conditioning systems. Its economy with regard to steam and water or brine piping are well known and need no comment. The insulation of duct work is not merely a matter of economics but sometimes is a'necessity from the standpoint of limiting the temperature rise of the-air even when the ducts are in conditioned spaces. This temperature rise of the air should always be taken into account when apportioning the air and sizing the ducts and will indicate the necessity for insulation. In some cases, leakage of air from the duct, where the duct is in a furred space or chase will eliminate the need for insulation by maintaining a reasonable temperature surrounding the duct. There are practically no items of equipment associated with central air conditioning systems that are not subject to economic limitations as well as those of performance and duty and all of them should be considered in the selection. ARRANGEMENT OF EQUIPMENT A proper arrangement of equipment is essential for the proper function ing of any system. Where systems are to be installed in existing buildings the arrangement of equipment may be limited by structural or space . considerations, but no compromises that may prevent satisfactory opera tion or maintenance should be considered. The location of the apparatus room is often determined by building construction or available space. The closer the apparatus room to the conditioned space, the less expensive is the duct-work. On the other hand if the equipment generates noises it may be necessary to locate the room some distance from the spaces or provide adequate sound and vibration. treatment. The scattering of wet apparatus throughout a building is to be avoided unless suitable precautions are taken. It must be remembered that encroachment on spaces that are otherwise usable can be charged against the system as an operating cost. In general the apparatus should be arranged to have straight line air flow. This is desirable but not always possible. Each change in direction is the source of air resistance, and in addition may cause eddy currents resulting in stratification. The usual order of equipment, beginning at the outside air intake is: outside air screen, outside air louvers, maximum and minimum outside air dampers, preheaters, return air connection, filters, conditioner, by-pass connection with or without reheaters, reheaters, fan and distributing ductwork. See Figs. 1,2 anc$ 3 for typical arrangements. Use of one or more of the methods of zoning may require a modification of this order but usually only after the dehumidifier or conditioner. Outside air screens prevent the entry of large foreign matter, birds, etc. The use of louvers or a hood at the outside air intake prevents the entry of rain and snow. Both of these should be used on all systems. As pointed out earlier, the louvers and screens should be of sufficient size to permit the passage of the entire conditioned air quantity. . The minimum outside air damper usually covers the entire face of the . preheater, which in turn is selected for the minimum outside air quantity. The maximum outside air damper is designed for the difference between the dehumidified air quantity and the minimum outside air. Its size can be such that its air resistance when open will equal the air resistance of the open minimum outside air damper plus that of the preheater if used. Where the spaces conditioned are very tight against air leakage, some Central Systems for Comfort Air Conditioning 809 type of relief or positive exhaust may be necessary when all outdoor air is introduced to the system to provide some means of egress for the air. Such reliefs require back-draft dampers to prevent infiltration when all outdoor air is not being used. A return fan properly dampered as indicated later is sometimes used. . The return air from the conditioned spaces usually is brought into the apparatus between the preheater and the filter. Just as it is necessary to make provision for using all outdoor air it is necessary to make provision for using all return air. Heating an unoccupied building of cooling; it - after a shut-down is easier if all the air used is return air. Consequently the return connections should be ample for this. In many cases higher velocities can be carried in the return ducts during such times, since the fan will exert a pull at the return connection nearly equal to the resistance of the outside air connection and the return ducts need not be larger than for normal return air quantities at normal velocities. In other cases it is possible that a reduced quantity of air due to the increased resistance of . the return duct system may be satisfactory during the starting period. Where the return, air system is extensive or complicated a return air fan is desirable. This fan can serve as a combination exhaust and return fan by arranging dampers in its discharge so that the necessary return air can be delivered back into the system and the remainder discharged outdoors. When all outdoor air is passed through the conditioner the entire return air quantity is discharged outdoors. ' The by-pass connection normally connects the return air duct system into the apparatus casing between the conditioner and fan. Usually it is sized to handle about 50 per cent of the fan capacity where a variable by-pass is used though extreme load variations may require a greater amount. It is at times good design to locate the reheater in the by-pass connection using a certain amount of by.-pass air when heating is required. Since the relatively high resistance of the conditioner is to be balanced by the heating coil and by-pass connection, enough heating surface can be provided to raise the temperature of the by-pass air to the point where the mixture of by-pass air and conditioned air will have the required temperature. When a variable by-pass is used a damper working in opposition to the by-pass damper should be placed across the face of the dehumidifier, for unless the resistances of the two are most carefully balanced ait all operating points the proper mixtures of air will not be obtained. ' The avoidance of by-passing outside air is again stressed. Where the by-pass is made a part of the dehumidifier or conditioner and located on the top or side of it, the return air connection- should be made in such a way that stratification of return air is insured, baffles being . provided to accomplish this purpose if necessary. Where return air and by-pass air connections are taken off a return duct system it may be necessary to install a back-draft damper between the return air con nection and the by-pass connection, if the return duct system is extensive and the connections simple. In this instance, when the by-pass damper is at maximum opening it may be much easier for outside air to pass through the return damper, into the return duct connection and through the by-pass than for return air to pass through the by-pass connection into the fan. Air always takes the easiest path and if the dehumidifier resistance is high, and the return duct resistances low, this situation is apt to occur unless precautions are taken. A return fan instead of a back-draft damper may be required for this case if the failure of return air " to reach the dehumidifier or conditioner is a serious matter under reduced load conditions. -. - .810;CHAPTER 43;. 1946 Guide The location and arrangement of the dehumidifier, humidifier, or, con ditioner with reference to each apparatus assembly are more or less stand ardized. In general, the outside air intake, preheaters, and return air connections precede the conditioner while the by-pass, reheaters and fan follow the dehumidifier. In the cases of the blow through system, where . the fan is located ahead of the conditioner, the leakage of air at the con , ditioner is outward instead of inward and may be accompanied by water leakage unless the proper precautions are taken. .. The location of the complete apparatus assembly including the de humidifier will be dependent on the type of building, spaces available, structural characteristics, etc. The type of conditioner used may limit ' the location under certain conditions. Where cooling coils employing chilled water or brine as the cooling agent are used there are few restric-' tions with regard to location other than those of pumping power, working . pressures, line costs, etc. Where open spray dehumidifiers are used very . definite limitations present themselves, and these may require certain ' extraneous equipment to make the system workable. If several spray . type dehumidifiers are located on different levels, a surge or storage tank . to which the return water from each dehumidifier can be taken is required ' Should the water level in the pan of the dehumidifiers be low in relation to that of the surge tank, return water pumps will be required, and these . pumps will have to be operated until the water supply lines are drained in order to prevent flooding of the lower dehumidifiers. Where spray de- . humidifiers are on the same level, equalizing lines between the pans may be required if a storage tank is not provided. . Alb of the various pieces of equipment fron* the outdoor air intake through the fan usually are connected together by sheet metal casings Frequently the building structure or specially constructed walls or par . titions may be used to form all or a portion of the casing. In any case the . casing or connection must be sufficiently sturdy for the required duty. . Sheet metal work must be well braced not only to prevent bellying or vibration under pulsations in air flow but to withstand the abuse of normal usage. Casings should be adequately braced wherever access doors are installed and all large panels should be adequately reinforced by angle iron. Each apparatus layout is to be made with accessibility in mind. Where . ' cooling coils .are used space for removing and repairing or replacing the ' coils should be provided. Adequate space is to be provided for the . ' servicing and replacement of eliminators: Filters must be so located that . the proper cleaning, replacement or routine servicing can be accomplished , without difficulty. Free access to the bearings of all moving machinery is a necessity. Provisions should be made for the complete removal and replacement of any part of the system that is subject to wear, deteriora- ' . tion or damage, whether it may be filter, fan wheel, motor, rotor, pump impeller or heat transfer surface. DESIGN PROCEDURE , The customary design procedure is outlined herewith. For simpli' ` fication the procedure is set up on the basis of a year 'round system. For summer only or winter only systems, the unrelated parts are to be omitted. ' 1. Selection of design conditions (inside and outside), o. Summer. . - b. Winter. - . 2. Determination of outside air requirements. . . Central Systems for Comfort Air Conditioning ' 811 3. Determination of cooling load. a. Room sensible heat gain. b. Room latent heat gain. c. Room total heat gain. ' d. Grand total heat gain. > ' 4. Determination of heating load. . a. Room sensible heat loss. b. Room moisture loss. - c. Humidification requirement. d. Total heating requirement. ' 5. Determination of apparatus dew-point and dehumidified or humidified air quantity. a. Summer (full load and part load). b. Winter. . . - . ... . 6. Supply air temperature difference and quantity. a. Summer. ~ . b. Winter. . ' ,' . .' , ... 7. Equipment selection. '! 8. Equipment layout. ' '. The foregoing steps are merely typical. Many applications will require at least a preliminary investigation of some of the latter steps before proceeding with the earlier steps. . ' REFERENCES *--Code of Minimum Requirements for'Comfort Air Conditioning (A.S.H.V.E. Transactions, Vol.' 44,. 193d, p. 27). _ .. 2"A Comparison of Methods for Controlling Evaporators and Compressors Used in Air Conditioning, by W. A. Grant (Refrigerating Engineering, 'April, May, 1945). - - Abbreviations and symbols used in chapter p = density of supply air, pounds per cubic foot. . cp = specific heat of air at constant pressure, Btu per (pound) (Fahrenheit degree).. Hi = latent heat gain of room, Btu per hour. Hs = sensible heat gain of room, Btu per hour. . hr = enthalpy of air at room conditions; room wet-bulb, Btu per pound of dry air. hs = enthalpy of air at apparatus dew-point, Btu per pound of dry air. * ky ~ heat of vaporization at apparatus dew-point temperature. Qm = air supply, cubic feet per minute. . .. /s = apparatus dew-point, Fahrenheit degrees. . ' - lx =. room dry-bulb temperature, Fahrenheit degrees. , Wt = moisture content of room air, pounds per pound of dry air. , ` Ws = moisture content of air, pounds per pound of dry air at apparatus^ dew-point. SHF = Sensible Heat Factor. . .. ,. LHF = Latent Heat Factor. .* MF = Multiplier Factor. -- . CHAPTER 44. Owninfy an Fixed Charges: ' Amortization, Interest, Taxes,] Insurance, Rent; Maintenance Costs, Service Costs: ' Operating Refrig eration Equipment, Condenser Water, Heating ' THE purpose of this chapter is to discuss the owning and operating costs of heating, ventilating, air conditioning - and refrigeration systems for buildings from an economic standpoint so that owners or prospective purchasers may compare the operating economics of one system with another and evaluate properly the over-all costs 'of the Systems- instead of considering only the first cost. ,. There are cases in which it may be desirable to study the possibilities of installing a system for the purpose of obtaining a substantial increase in income or a better return on the investment due-to: increased patron age in theaters, stores, or hospitals;-increased occupancy in office build ings; improved efficiency of employees in offices or factories; or improve- - ment in a manufactured product or a decrease in its cost of production. Owning and Operating Costs may be grouped under three headings: (1) Fixed charges, (2) Maintenance Costs, and (3) Service Costs. - FIXED CHARGES Fixed Charges, which are the costs of owning the system, include: (1) Amortization, (2) Interest, (3) Taxes, (4) Insurance, and (5) Rent. Amortization ' Amortization cost will depend on: (1) the total first cost, and (2) the amortization period. . .. The total first cost of an installation is the actual dollar outlay or capital expenditure required to buy and install the air conditioning, or heating and ventilating system ready for operation. It can be divided into two parts: (a) The first cost of the air conditioning or heating and ventilating system itself, and (>), other first costs incurred because of the . installation of the air conditioning or heating-and ventilating system. The first cost of air conditioning or heating and ventilating systems includes the following: ' 1`. Heat producing equipment including boilers, burners, etc. ' -- 2. Heat distributing equipment including direct radiation, piping, etc. - . 3. Air handling equipment including fans, air heaters, air conditioners, filters, con trols, etc. . 4. Air distributing equipment including ducts, outlets, grilles, etc. 5. Refrigerating equipment including piping, pumps, etc. . 6. Water conservation devices including towers, evaporative condensers, etc. The best procedure for establishing the first cost of any system is to select the various.parts after thorough engineering study, and then to .estimate the "installed costs of same. When such detailed work is not warranted or when only rough comparisons are desired between several types, approximate unit costs are of value as time savers. . Approximate installed prices of the various parts are shown in Tables 1, 2, and 3 and, as indicated, vary with the size or capacity of the equip- _ 812 Quinine and Operating Costs 813 ment.. The apparatus and items included in each group are stated in the footnotes beneath the tables. .'.By use of these three tables it is possible to obtain a reasonable approximation of the cost of heating or air con ditioning a given space-or building. In order to use; the approximate values indicated in Tables 1, 2 and 3, a rough estimate of the load is . required. If time does not permit a determination of the load and if extremely rough figures will suffice, Table 4 may be used as an indication of the price of. various types of air conditioning applications. Other first costs, incurred because of the installation of the air con ditioning or heating and ventilating system, include costs of- electrical wo'rk, plumbing, miscellaneous piping, building alterations! cutting, patching, remodeling, or redecorating after installation, consulting engineer's fees, licenses, permits, etc. These vary so widely that no approximations are possible and each case must be considered alone. ' The length of the amortization period to be used depends upon: the type and remaining life of the building or space for which the system is to be used; the type of equipment.to be employed as a-part of the system; the character of the business; and the lease or ownership conditions. For small shops in rented quarters on short term leases,'a period of 5 years or less may be proper, whereas for larger installations ini buildings thatfare owned outright' a period of 10 or 20 years or more may be used. Depreciation due to deterioration and obsolescence must also be considered in arriving at the amortization period. - Deterioration and Table 1. Typical Installed Costs of Heat Producing . and Heat Distributing Systems Btu PER Hour (Millions) SQ FT EDR (Steam) ' Thousands Boiler Horse Power 0.8 1.2 1.6 2.0 3.0 4.0. 5.0 6.0 7.0 8.0 10.0 12.0 14.0 16.0 18.0 3.3 5.0 6.6 ' 8.3 12.5 16.6 20.8 25.0 29.2 .33.3 41.6 50.0 58.3 66.6. 75.0 24 36 48 60. 90 . 119 149 179 209 239 299 ' 358 *418 - 478 538 Cost in Dollars--per Million Btu per Hour** b' 1 Boilers Water Tube .2300 2000 1850 .1600 1400 1250 1160 1100 1050 1000 970 930 .900 860 2 3 4- Boilers Fire-Tube Hot Water System Forced Circula tion ` Direct' Radiation ' System Steam ' 2100 1750 1570 1460. 1230 1100 980 920 880 850 8500 8200 8000 7800 7600 7500 7500 7500 7500 7500 7500 7500 7500 7500 7500 7850 7600 7350 7200 7000 7000 7000 7000 7000 7000 7000 7000 7000 7000 7000 . . ^Columns 1 and 2 include hand fired boiler erected, with shaking grates-and standard.trimmings. Column 1 includes brickwork and rotating soot blowers. Foundations and piping are not included. . Columns^ and 4 include direct radiation, piping, valves, specialties, and insulation. Boilers, condensate and circulating pumps, boiler connections, and all building construction or alterations are not included. hThe approximate figures given above may vary as much as 30 per cent due to job conditions, labor rates, and locality. These figures represent the selling prices of the individual items indicated above based on costs encountered in the year 1940. It is suggested that correction, be made according to the- particular, locality for increases in labor and material costs since that year. '. 814 CHAPTER 44 , 1946' Guide. Table 2. Average Installed. Costs of Forced Air Heating _____________ . and Air Conditioning Apparatus .. CFM Supply Air (Thousands) ' 1. Air ' Conditioning Equipment* 5 0.300 10 0.270 15 0.250 20 0.235 30 0.220 40 0.210 60 . 0.210 80 0.210 100 0.210 120 0.210 140 0.210 160 0.210 180 0.210 . 200 0.210 Cost pee CFM--Dollars*! 2 Heating and Equipment* 0.210 0.180 0.155 0.140 0.120 . 0.110 0.110 0.110 0.110 0.110 0.110 - 0.110 0.110 0.110 3. 4 Ducts Office Bldgs.* Ducts Specialty Stores* . 0.340 0.330 0.325 0.320 0.310 . 0.305 ' 0.295 0.290 0.280 0.250 0.249 0.247 0.245 0.240 0.235 0.230 .' eSuipnuni incJude? fans and drives, filters, heaters.-spray dehumidifiers or cooline'coils, automatic controls, apparatus casings and insulation, and recirculating pumps. *JSZuZ'hS?r'm`aaUn` `W'tm'nt includes fans and drives, filters, heaters. automatic controls and ^Includes ducts, grilles, outlets, insulation where required and specialties. . anddkSlftvPr0F^frifi/r'irtSIJn ab^5 may. var?' aJL"uch * 35 ber due to job conditions, labor rates SS2J?Sity' . tf^.are^sed^on oonvenuonal systems. Building alterations, piping, plumbing and' ^jhfs',5ures riiKScnt.th.' seUin* Prices of the individual items indicated above particular locality for increasmes ^ine,laXbeoarra1n9dfm* at1e1r1ia3l scuogsgtsesstiendceththaattc.yoerarer.ction be made according to the Table 3. Average Installed Costs of Refrigeration Systems, S e l l in g P r ic e p e r U n i t n d ic a t e dI Cost--Dollars Per Ton* Tons' Refrig eration 1 Recipro cating (Water Cooling)* 2 3 ,4 Centrifugal (Water - Cooling)* Recipro. gating Direct Expansion* EvapoATTVE Condenser* 5 Cooling Tower STEELd 6 Cooling . Tower . Wood*1 * . 25 50 . 75 100 .150 200 250 300 400 6UU ' 147' 132 125 120 , 115 113 110 137 . 124 115 107 97 - 93 " .106 86 77 72 68 47 40 35 32 \ 30 47 ' 45 44 42 . 40 38 36 40 38 36 35 33 31 _ 29 ` n.t^i ____._ j j.-------v vv...^.kW.^ LfBwtotuio, ouu watci-uuuicu conaensers: auxuianes: electric &*SJZSZS&S*r- r*?friger^tl0n Pipmg. refrigerant and insulation of cooler and suction lines. Tur- centrifugal equipment may cost about 4 to 6 per cent more than motor driven, if condensing turbine and steam condenser, with supplementary equipment, are used. .. bColumn 3 includes same items as Column 2 except evaporator and auxiliaries are omitted. eColumn 4--These values are additive to Columns 1 and 3. ' pum1,mma 5 and include tawm erected and a reasonable allowance for condenser water piping and and"h^HfPvr0R,o?if,,S1ir,!Lg;:'" abovemay vary as much as 25 per cent due to job conditions, labor rates "2 """F- Budding alterations, supply water and plumbing connections, wiring, chilled water piping and pumps are not included in these figures and may vary widely. Chilled wate?bpiSFandouSn lists may vary between t10 and *50 per ton of refrigeration effect. These figures iepr4S?The"mSg pri<S of trema indicated above based on costs'encountered in the year 1940. It is suggested"that. cmrection be made according to the particular locality for increases in labor and material costs since that. 16 CHAPTER 44 1946 Guide maintenance generally go hand in hand. If a long depreciation period is to be used, then the item for maintenance, repair and replacement of wearing parts must be greater than for a short depreciation period. Obsolescence depends mainly on time required for the equipment to become out-moded. Air conditioning, particularly, would probably . Table 5. Approximate Life of Equipment (Including Obsolescence and Deterioration)a Life in Years X. Heat Producing Equipment (a) Boilers.-,........... ..................... (b) Stokers and burners..... ...... 2. Heat Distributing Equipment () Piping--copper.............. ................ () Piping--iron........ .............. ............. (c) Radiation--concealed.... .............. (d) Radiation--direct................... ..... (e) Valves and specialties........ ...... 3. Air Handling Equipment - (a) Filters--automatic.................................. (b) Heating and cooling coils____ '............ (c) Spray humidifiers and dehumidifiers. (d) Fans.......... ..............:...... ......................'____ (e) Air conditioning units.......... ............. .... (J) Motors.;............................ .......................... (g) Electrical starting equipment.----...... (h) Pneumatic control systems.................. () Electric control systems.-..................... 4. Air Distributing Equipment . (a) Ductwork--................. ............... (b) Outlets, grilles.................... ...... (e) Duct insulation-....................... (d) Painting..........:............................ 15 10 20 10 12 10 5 .8 10 10 10 10 15 8 10 8 . 20 20 10 2 - 5. Refrigerating Equipment `. (a) -Centrifugal refrigerating machines___ ________ _______________ (b) Reciprocating refrigerating machines (c) Motors and starters (see Item 3 above)........... ...... ...... ....... ...... (d) Piping--copper....:................ ..................................... ................. ....... () Piping--steel................ ........... ........................................... -- (/) Pumps----------- ------- 1............. :...... ............... ................... ...... ................ 15 10 20 15 15 6. Water Saving Devices (a) Evaporative condensers--.............................. .... ........ ....................... (b) Cooling towers...... ............................... ........ ...... ...... ...... .................... (c) Wells..................................-........:...... ....................................... -............ 10 10 . Varies Widely `Modem Air Conditioning. Heating and Ventilating, W; H. Carrier, R. E. Cheme and W. A. Grant (Pitman Publishing Carp. 1940, p. 66). -. - '- -\ suffer more from obsolescence in small plants than in large establishments. In addition the obsolescence of the building or property in which the equipment is installed may have a similar effect-upon the equipment. An approximation of the-useful life of various items of equipment and parts of systems is shown in Tabie 5. It should be noted that if an appropriate maintenance item is not established,:the rate of equipment deterioration, may be substantially increased. . Owning arid Operating Costs 81? Interest' . The interest chargeable may not represent the existing money, rates. It may include an item to cover the diversion of capital or other items depending on existing tax laws which may make it necessary to charge interest due to diversion of capital as a cost item. It should be noted' that interest may be based on an unamortized balance. As an example, a 15year amortization period with a 4 per cent interest rate will approxi mate a 2.1 per cent average annual interest rate. Table 6. Owning and Operating Cost First Cost Cost of mechanical system-- Other costs-..,.--.......;.............. First Cost (FC)--Total Annual Fixed Charges Amortization--Depreciation period Y years................ ... Interest rate 1%........--..................... Amortization and Deprecia tion FC = - Y *"* ...................... Y+1 - Interest: -- X7 =--.... Taxes.--................................ -- Insurance........................ *--:-- Rent--......... .................. Annual Fixed Charges: (Total)........................... Annual Maintenance Costs Lubricating oil and grease.___ Painting for' corrosion pro tection or other purposes.__ Replacement of worn parts___ RefrigerantTM............................ Wages of engineer or operator Annual Maintenance Cost-- totalJ___ 1 Annual Service Cost Electric Power Costs Fans...... ........ ............ ,..................... Pumps--Chilled water............... Pumps--Condenser water Pumps--Well water....... .............. Cooling tower fans............ ........... Cooling tower pumps................... Refrigeration machines Miscellaneous or other................ Gas._..................................................... Coal.........!...................... .................... Oil--for boilers or Diesel ` engines...... ....................................... Steam For direct heating................. ....... For Ventilation--preheat- ' ers.......... ................. ...................... For Ventilation--reheaters ___ For Turbine driven equip ment.......... ........ ...... .................... For Engine driven equip-- ment...... ....................................... Sewers . Charges for discharging well water into public drainage systems...................... Annual Service Costs--. . TOTAL--.................................. Summary Annual Fixed Charges...!...... Annual Service Costs____ _____ Annual Maintenance Costs __ Annual Owning and Oper- , ating Costs--TOTAL.-------: Insurance ' ' The rate for insurance may vary considerably depending on the type of structure in which the equipment is located and upon other governing factors. A rate of about $0.60 per $1,000 may be considered as being representative for normal installations. ,, Rent - - . _ If the equipment under consideration is' to be located in rented or leased quarters it may be necessary to include an item for space rental. 818 ____________________ CHAPTER 44 _________ 1946 Quide ' ' An orderly arrangement of the various components of owning and ' operating costs, which will also serve as a check list to forestall inad' vertent omissions, is illustrated in Table 6. . The formulae for computing amortization and interest are given in the table. Interest should be . computed on the undepreciated portion of investment only. ' MAINTENANCE COSTS , Maintenance costs include replacement parts and the labor required for making repairs, replacing parts, cleaning, painting, etc. It should be noted that major overhauling or complete replacement may restore the capital value of certain items of equipment, and in such cases the costs incurred may not necessarily be charged as maintenance costs. . Generally, routine labor requirements will be the function of an operating engineer, or staff and the responsibility of this group may extend beyond the equipment being discussed here; hence, it is important to include only an equitable share of the time of this group. Extraordinary repairs -involving special machinery will usually be covered by contract with equipment service divisions and should be accounted for on that basis. . ' ' . Many of the items included in maintenance costs are highly variable and depend on the type and quality of the purchased equipment. For large air conditioning installations, using high quality equipment, some approximate costs per ton are given in Table 7. . In addition to the costs listed in Table 7, consideration should possibly be given to other items such as:. water treatment for boilers; other boiler and heating plant cleaning and repairs; repair and replacement of heating plant valves, traps, and vents; water treatment for cooling tower or > chilled spray water; drive belts, possible damage due to freezing weather; cleaning of air ducts; and repairs to insulation. ' SERVICE COSTS Service costs include the costs for power, water, steam, coal, oil, etc., consumed to operate the system. . From the selected equipment and type of installation, it is possible to segregate the relatively constant power loads and the total brake horse power. Annual power cost can then be figured from the following formula: where Annual power cost 0.746 (bhp) H R . V (1) . bhp == Brake horsepower. H = Annual operating hours. 1 " R -- Power rate, dollars per/kwhr. ' . i) = Motor efficiency (de`cimal). 9 - , . In using Equation T it must be pointed out that the electric rate, R must reflect the proper combination of energy and demand rates. These g vary widely between the utility companies, and sometimes the rate - structure is such that it is largely the demand charge which determines . the proper value of R to use in Equation 1. ' ' ' . . Refrigerating Equipment Operating Cost . ; . In an air-conditioning system, the refrigerating equipment is usually . the largest power-consuming item to be.considered. Also, the prediction Owning find -Operating Costs 819 Table 7. Approximate Maintenance Cost for Large Air Conditioning , . Installations, Using High Quality Equipment . , Dollars per Ton per Year Oil and grease. __ ........................... ....... ....................... ,....................... Painting (Water boxes and dehumidifiers)... 0.60 b.25 0.07 0.25 0.85 0.15 1.15 . of operating cost is more complex, since the power required for summer cooling is affected by many factors which are of a variable nature. Among these are solar radiation, temperature difference between outside and inside, sensible and latent heat- brought in with outside air, sensible and latent heat from people, heat released by electric lights, and, in some cases motor-driven equipment, cooking devices, and other equip ment used in the conditioned spaces; Some of these factors vary with the weather while others are substantially independent of it. The relative proportion of each factor varies widely even among installations of the same application, depending on building layout and location, the size and quality of the establishment, the personal idiosyncracies of the owner, and other items. ~ In a strict sense, it is necessary to evaluate the effect of all such factors in order to predict the operating cost of a refrigeration plant. In most cases this procedure will prove to be too tedious, or it may not be possible because the exact breakdown of load data is unknown. The use of a simplified semi-rational formula, Equation 2, which takes into'account for each application the number of hours open for business and the geographical location, will provide a value of H which may be used in Equation 3 to determine the Season Power Cost. . where ' He = m (b + cf) . (2) He = Equivalent full load operating hours of refrigeration equipment used for summer cooling during period. May 15 to October 15. m = Total hours during period May 15 to October 15 that the establishment is . open for business. - . - b Fraction of maximum load from internal heat, under average operating con ditions. . .' ' c - Fraction of maximum load which is due to external sources at maximum design conditions. 1, / = Ratio of the number of hours for a particular city,.when the outside wet-bulb exceeds 65 F, during the period June 1 to October 1 to the total number of hours during that same period. Total hours are assumed as 8 hr per day period for barber shops, department stores, funeral parlors, offices, short hour - restaurants, and specialty shops and. 12 - hr per day period for drug stores, long hour restaurants, and theaters. ' Table 8 was calculated from Equation 2. It should be pointed out that certain southern cities may have seasons longer than the 5-month period indicated in Table 8. If it is desired to consider a longer season of operation, the ratio of full load operating hours to hours open for business is smaller; in other words, the refrigeration load factor is, lower. This is true because the extra increment of days added will be at relatively light load, since the table already includes the more severe part of the season. 820 CHAPTER 44 1946 Guide Owning and Operating Costs 821 ' The season electrical power cost for refrigerating equipment is then given by the following equation: . Season power cost 0.746 (bhpt) THeR - - t)' (3) where . - bhpt = Brake horsepower per ton (see Fig. 1) for average load during period. (Due allowance should be made for poorer compressor efficiency at light load). T -- Tons of refrigeration at maximum design load. . He = Equivalent full load refrigeration operating Hours (Table 8). R = Power cost, dollars per kwhr, including demand and energy charges, i) = Motor efficiency at average load.(decimal). ' `Modem A ir Conditioning, Heating arid Ventilating,1by,,W . H . Carrier, R. E. Cherne and W . A. Grant ( P itm a n P u b lis h in g C o rp . 1940, p. 73). Fig. 1. Typical Brake Horse Power Requirements for Refrigeration11 ' aValues.,given are'representative of "F-12" reciprocating machines of about 25 tons capacity in air conditioning applications. Requirements of smaller machines are usually higher, and for larger machines may be lower. Values shown are for liquid refrigerant at condenser temperature (no subcooling).' Sub* cooling of-the liquid may decrease these values approximately 0.3 per cent to 0,5 per cent for each Fahren heit degree the liquid temperature is lowered. . .` ' Table 9 will be useful in estimating the design load in the absence of detailed load estimates. . In considering refrigeration power consumption, it should be noted that the use of weather records for a specific year may lead to large, inaccuracies in estimating operating costs, since there may be wide; variations from year to year, and therefore, average yearly weather records should be used rather than those for any individual year. If the refrigeration compressor-is steam turbine driven, the same general method can be followed, taking into account average water rate; per bhp-hr and the cost of steam. , . Condenser Water .' ' - . Condenser water cost estimates can also be based on equivalent full load operating hours of the refrigeration equipment. The varying, temperature of the water at its source, as well as the temperature of the discarded water, must however be taken into account. In general, when water is purchased, control is provided to hold the leaving water tem perature-(or condensing temperature) constant; and in such case' the; entering water temperature becomes the. major- variable and the gpm per ton can readily be calculated for any water, temperature risey- The following equation for cost of condenser water is diseful ;. S22 ___________. , CHAPTER 44 - - 1946. Guide where B = 0.060 a T Hc C B -- Cost of water for refrigeration during period, dollars. a = Average gallons per minute (ton). T = Tons of refrigeration at maximum design load. He = equivalent full load refrigeration operating hours (Table 8). C = Water cost, dollars per 1000 gal. ; (4) The average gpm per ton must take into account the variable water temperature. 'When well water is used as a source, and entering and leaving temperatures are considered constant, the average gpm per ton obviously is equal to the design gpm per ton. However, when the source is river or lake water, its maximum seasonal temperature will generally be reached at the same time that the refrigeration load factor is highest. Table 9. Representative Tons per Square Foot for Various Applications Department Store (Main Floor)_____ Department Store (Upper Floors)___ Dress Shop................ Drug Store. ....... .................................. .... Lunch Room. . Office. Bldg. Restaurant. .. ' * Shoe Shop________________________;____ Theater.. Low . 0.0050 0.0029 0.0029 0.0033 0.0083 0.0021' 0.0058 0.0029 0.064? Tons per Seat. Avc ' 0.0058 0.0046 0.0050 0.0054 0.0108 0.0025 0.0075 0.0042 0.078* High 0.0067 0.0054 0.0071 0.0083 0.0133 0.0038 0.0100 0.0063 0.093* The average gpm-per ton should be calculated from known or estimated water temperatures because they vary through the season. Maximum water main temperatures are given in . Chapter 15. In. lieu, of this tedious work, the average gpm pier ton may be taken as 80 per cent of design gpm per ton with reasonable accuracy, for the condition of variable temperature of entering water obtained from rivers and lakes. When cooling towers or evaporative condensers are used, the windage and evaporation losses are usually between 3 per cent and 5 per cent of the water circulated. . 1 Heating - '. The method of estimating fuel consumption to balance the building heat loss is given in Chapter 20. It is important to include the. fuel ; required to heat ventilation air as used in ventilating and air conditioning systems. In estimating fuel consumption for ventilation air, the tendency of the conventional control systems to-use less than the estimated quantity of outside air in cold weather should be considered in its effect in lowering fuel consumption. In addition, the heat required to accom-' plish winter .humidifying must hot be neglected, when this feature is included in the equipment. ... ,, . BIBLIOGRAPHY i Modern Air Conditioning, Heating and Ventilating, by W. H. Carrier, R. E. Cherne, and W. A. Grant--Chapter IV (Pitman Publishing Corp., 1940). '. . Predicting Operating Hours of Refrigeration Equipment Used .in Air Conditioning, by W. A. Grant (Refrigerating Engineering, July, 1941).. ' ' Cost of Operation of Refrigeration Used for Air Conditioning, by R. E. Cherne (Rejrigerating Engineering, December, 1943). - CHAPTER 45 d^nduitriai C^onditilorunej. Atmospheric Conditions Required', General Requirements, Classification of Problems, Control of Regain, Moisture Con tent and Regain, Conditioning and Drying, Control of Rate of Chemical Reaction, Control of Rate of Biochemical Re actions, Control Rate of Crystallization, Elimination of Static Electricity INDUSTRIAL air conditioning is primarily concerned with the atmos pheric conditions required for the manufacture,; processing, and preservation of material, equipment and commodities. The fundamental factors, one or more of which may govern these conditions are: humidity, temperature, air motion and air purity. The term air purity may have reference to the quantity of dust, bacteria, odors, or toxic gases present. The optimum atmospheric conditions have been established for a large' variety of industrial processes, but when the requirements are unknown it may be necessary to determine them by laboratory tests or by research. When the requirements are not. definitely specified it is advisable to design the equipment to be flexible and to provide for future increase of facilities and capacity. Air conditioning requirements for human comfort' are defined in Chapter 12. If the atmospheric conditions required for the process are not within the range of human, comfort, separate consideration must be given to the maintenance of conditions which will not have a detrimental effect upon the health of the occupants. . ATMOSPHERIC CONDITIONS REQUIRED ' The most desirable relative humidity for processing depends upon the product and the nature of the process. As far as the behavior of the. material and its desired final condition are concerned, each material and process presents a different'problem. The desirable relative humidity may range from a low.of 5 per cent, as in certain industrial applications, such as insulation winding processes, up . to a condition approaching saturation, as in processes relating to textiles, tobacco and baking industries. . . ..... :. Similarly, the most favorable temperature will.vary according to the specific material and particular process. Frequently a compromise between the known optimum condition for processing and that required; for reasonable worker comfort is desirable. This is particularly true where unconfined processes are required in departments where people are working and their: health, comfort and productive efficiency must be considered. ' . . . It is generally recognized that relative humidities of 50 per cent or' less are on the dry side. Such conditions are conducive to low regains in hygroscopic materials, drying out, increased brittleness. of fibrous materials, prevalence of increased static electricity and tendencies toward increased dust liberation from the product. Relative humidities higher than 50 per cent are considered to be on the damp side. These con ditions are conducive to high regain, promote softness'and pliability in materials, decrease static electricity and tendencies toward reduced generation of product dust which represents a loss in weight of the materia! in process. ' 323 824 CHAPTER 45 1946 Guide In many processes, the optimum desired air conditions are variable according to the stage and progress of the processing cycle, from the raw material'to the finished product. Some materials, such as cotton textiles, begin with a low relative humidity in the carding and picking rooms, and after passing through the various intermediate steps with a gradual increase of relative humidity, the product is subjected to relative humidi ties of from 75 to 85 per cent in the final stage of weaving. Other pro- . cesses are encountered that require the reverse of this procedure, starting with a high relative humidity and finishing with a low relative humidity, as is the case when producing glue and gelatinous materials and making gelatine capsules. In some cases the temperatures listed in Table 1 have no direct influence upon the product itself, except for effect upon efficiency of the employees which in turn affects workmanship, uniformity and the cost of pro ' duction. In this category may be included the automobile assembly line. The time necessary to assemble the many parts into a complete unit is a factor recognized and associated with the worker's comfort, and the avoidance of fatigue with subsequent loss of efficiency.. i; f Air conditioning contributes an important role during the processing, machining and honing of precision metal parts, instruments, tools, engines, guns, etc., which'demand micrometric accuracy of dimensions, and which are affected by small temperature variations. Hence, some uniform con dition is usually selected, both as to temperature and humidity to serve the demands of the worker's comfort and the exacting requirements of ' the process. . The temperatures and relative humidities listed in Table 1 should be analyzed in relation to the qualified requirements of the process. Con ditions generally acceptable for industrial processing and for general storage are listed in these tables. While it is true that many storage require ments demand the control of some fixed air temperature and relative humidity condition, to hold and preserve the contents, it is not generally referred to' as processing. '. . ; Logically many phases of drying may be included in the category of air. conditioning for industrial processing, especially where temperature and humidity, by direct influence to- product, bring about some definite . change in physical characteristics as well as in weight. (See also Chapter 47;) As an illustration, refer to the conditions. that are required to . control the rate of crystallization in coating pans in which sugar syrup' ; is.applied :to.various forms .of pills, nuts, gum, etc., in consecutive liquid doses, until a.crystallized coating or jacket is built up to the required size and thickness.. Here, the primary problem is one of drying which requires ' the supply of air at some fixed volume and velocity along with regulated, control.of both dry- and wet-bulb temperatures. The wet-bulb depression determines the rate of moisture pick-up? or drying by the air and may be termed the drying head. Of equal importance is the uniformity at which ' the wet-bulb. is maintained.. If this is allowed to vary, poor results will fpllqw;due' tij. checking and cracking, of the unfinished, coating. This is obvious, when'i-Lis,realized: that .continuous evaporation of moisture is taking place during the process and also that the temperature of the material corresponds . to.'the air. wet-bulb .temperature and will vary . accordingly. With undue, expansion and'contraction with every tem- ' perature change, the thin crystallized coatings which are not elastic will check and crack before the process is completed. ' ' - Industrial Air Conditioning_________ ;__________________ ._ 825 GENERAL REQUIREMENTS Air conditioning apparatus for industrial purposes must be capable of absorbing heat from various sources such as machinery power, electric lights, people, sunlight and chemical reactions; of warming or.cooling to any desired temperature; and of providing ample air supply. Refrigera tion may or may not be required, depending upon natural conditions, the required relative humidity and the maximum permissible temperature. Washing, purifying and treating the air may be desirable. Good distri bution is essential for the control of air motion and for the prevention of uneven conditions. Air velocity should not be so high that it will cause damage to the commodity or interfere with the industrial process. Accurate, sensitive and reliable automatic control of humidity or tem perature is vital in most cases. . Outside weather conditions and the ventilation required for workers are of secondary importance in relation to the total work to be done by the air conditioning system. In extreme cases of high concentration of industrial heat from machinery and ovens the error of entirely omitting the heat gain through the building structure would not be. serious. At the other extreme, where low temperatures must be produced with re frigeration and where comparatively little power is required by the machinery, the heat gain through the building structure will become the major factor in determining the size of equipment and in this case the . ventilation requirement assumes importance. Buildings which are to be air conditioned should therefore be designed with careful consideration of over-all cost and efficiency. Condensation resulting from high humidities must be prevented by suitable materials and construction, or else collected and drained to prevent loss of product or quick deterioration of the structure. Air leakage or filtration may add greatly to operating costs or make the maintenance of low humidities (relative or absolute) wholly impossible. Low temperatures require good insulation. It is apparent that the subject of air conditioning for industrial processes is extensive and greatly involved, and that a detailed treatment is there fore beyond the scope of this chapter. . CLASSIFICATION OF PROBLEMS Any industrial air conditioning problem maybe listed under one or more of the following five classifications: (1) control of regain, (2) control of rate of chemical reactions, (3) control of rate of biochemical reactions, (4) control of rate of crystallization, and (5) elimination of static electricity. Control oi Regain ' In the manufacture or processing of hygroscopic materials such as textiles, paper, wood, leather, tobacco and foodstuffs, the temperature and relative humidity of the air have a marked influence' upon the rate of production and upon the weight, strength, appearance and general quality of the product. This influence is due to the fact that the moisture content of materials having a vegetable or animal origin, and to a lesser extent minerals in certain forms, comes to equilibrium with the moisture of the surrounding air. .. In industries where the physical properties of a product affect its value, the percentage of ,moisture is of special importance. With increase in.' moisture content, hygroscopic materials ordinarily become softer and . more pliable. Standards of regain are firmly fixed in trade with fair 826 CHAPTER 45 , 1946 Guide Table. 1. Temperatures and Humidities Applicable to Industrial Air ' Conditioning . Imtuani Process Temperature Fahrenheit Degrees Relative Humidnr Per Cent Automobile_____ Baking:. Biological Products. Brewing_________ Ceramic Chemical__ ^____ Confectionery.: Distillery..--__ Drug Assembly line.... . .. Precision parts--honing--machining.____ Cake icing.__ . ___ ______ Cake mixing.. . ... .................. Dough fermentation room______________ .-. Dough retarding.................... .-_________ ____ Loaf cooling...... ................................................. Make-up room________________;____________ Mixing room._____________________________ Paraffin paper wrapping________l..._______ Proof boxes._________ ____ _________________ Storage of flour............... _ ...................... Storage of yeast. ............................................. Vaccines___ ________________________ ______ Antitoxins.........................:...... ................ .......... Blood bank........................................................ Penicillin (dehydrated)............. -.................... Fermentation in vat room_______ ________/ Storage of grains .. ...................____ _ Drying of auger machine brick............... .... Drying of refractory shapes.......................... Molding room. .......................................... Storage of clay ................................................ General storage................................... .-. _____ Chewing gum rolling--.......... :________ . Chewing gum wrapping_________ 1________ Chocolate covering...... ............. -- --............ Hard candy making.__________________ --. Packing............................................ ;.......... . Starch room,,.......... . :.............................. Storage.................... ....... -. ....................... . General manufacture. .. ......................... Storage of grains__ --_______ ....__i.._______ Deliquescent powder.......... . ........ ............ Effervescent granulations................... .......... Liver extracts (powdered).'........ ................ . Storage of powders and tablets.:_________ Tablet compressing--____ *_______ ________ Packaging___________ __________ ____ ;___ _ 65 to 80 75 to 80 40 to 55 40 to 55 70 . 75 80 32 to 40 70 75 to 80 75 to 80 80. 90 to 95 65 to 75 32 to 45 50 65 76 to 80 76 to 85 60 to 70 55 to 70 55 to 70 55 80 to 90 55 to 65 60 to 75 below 32 38 to 42 38 to 42 36 to 40: . 60 to 65 44 to 50 60 50 30 to 45 180 to 200 110 to 150 80 60 to 80 50 to 60 . 60 35 to 65 60 to 80 35 to 50 75 70 62 to 65 70 to 80 65 75 to 85 60 to 68 . 50 . 45 50 to 55 30 to 50 50 50 .50 to 65 60 to 75 45 to 65 60 ' 30 to 45 75 80 70 70 to 80 70 to 80 80 35 40- ` 20 to 30 30 to 35 40 40 Electrical Insulation winding. _ ..... ....... ........... Manufacture of cotton covered Wire...... Manufacture of electrical windings.______ . Storage of electrical goods_______ _________ 104 60 to 80 60 to 80 60 to 80 ,5 60 to 70 35 to 50 . 35 to 50 Food.________ :___ Butter making... ___ ` Dairy chill room___ .. ........ ........ .... Preparation of cereals. ____ _ .. ;____ Preparation of macaroni. _____ ___ Ripening of meats................. :____ 1; Slicing of bacon______ . ....................... Storage of apples.__ -- .......................... Storage of citrus fruit-- _______________ Storage of eggs in shelL ......____ ___ _____ Storage of meats (frozen)--........................... Storage of meats (above freezing)....\........ Storage of sugar.__________________ _______ ' 60 60 40 60 60 to 70 38 70 to 80 38 40 , . 80. . . 60 . 45 31 to 34 ,75 to 85 32 80 30 ' 80 ' 0 to 5 . . 85 36 ' 85 . 80 35 .Eur.. Drying of furs--..... ..... 1____ ;_______ _____ Storage of furs......................................... : 110 28 to 40 50 to 65 Industrial Air Conditioning 827 Table 1. Temperatures and Humidities Applicable to Industrial Air. Conditioning--(Concluded) ,Ikdustrt .- Process . Temperature . Fahreeheit Degrees . Relative ' Hmaunr Per Cent . 99 to 102 55 to 75 Instruments------ Repair and calibration ............. ............... . 68 50 to 55 Laboratory-------- General analytical and physical_________ _ 60 to 70 60 to 70 60 to 70 35 to 50 Leather-------------- Mulling .. ,, 90 ............. .... 95 to 100 95 Library__________ Book storage ' 65 to 70 38 to 50 Linoleum.-i-------- 80 40 72 to 74 60 50 Munitions.._____ - Paint_______.____ 70 70 to 90 180 to 300 60 to 90 55 25 to 50 25 to 50 Binding, cutting, drying, folding, gluing. Paper__ :...:______ 1 Testing. Laboratory_______________!____ .__ 60 to 80 75 to 80 60 to 80 40 to 60 40 to 60 55 to 65 Photographic__ Printing________ 70 to 75 75 to 80 70 72 70 77 75 75 to 80 70 to 90 60 50 70 . 65 45 65 60 to 78 50 to 60 50 to 55 Rubber__________ Standard laboratory testa Soap ___ : .. 90 75 to 80 80 to 84 80 110 25 to 30 42 to 48' 25 to 30 70 75 to 80 75 to 80 roving _____ . . spinning ' 75 to 80 60 to 80 -. 68 to 75 70 *r ' throwing 70 . 75 to 88 75 to 80 75 to 80 75 to 80 _ . 75 to 80 .75 to 80 75 to 80. 75 to 80 70Testing'Laboratory______ --_______ _____ _ . Tobacco! - Cigar and cigarette making...:____1*______ , : Stemming or stripping.... * 70 to 75 90 75 to 85, 50 to .55 60 to 65 50 to 60 50 to 70 85 85 . ' 60 60 to 75 60 to 65 65 to 70 65 to 70 60 to 70 65 to 70 . 50 to 55 65 55 to 75 ` '85 . 70 828 CHAPTER 45 1946 Guide- penalties for excesses. Deficiencies result in loss of revenue to seller and loss of desirable quality to buyer. ' . Manufacturing economy therefore requires that the moisture content be maintained at a percentage favorable to rapid and satisfactory manipu lation and to a minimum loss of material through breakage. A uniform condition is desirable in order that high speed machinery may be adjusted permanently for the desired production with a minimum loss from delays, wastage of raw material and defective product. .. . . In the processing of hygroscopic materials, it is usually necessary to secure a final moisture content suitable for the goods as shipped. Where the goods are sold by weight, it is proper that they contain a normal or standard moisture content. .. Moisture Content and Regain The terms moisture content and regain refer to the amount of moisture in hygroscopic materials. Moisture content is the more general term and refers either to free moisture (as in a sponge) or to hygroscopic moisture (which varies with atmospheric conditions). It is usually expressed as a percentage of the total weight of material. Regain is more specific and refers only to hygroscopic moisture. It is expressed as a percentage of the bone-dry weight of material. For example, if a sample of cloth weighing 100.0 grains is dried to' a bone-dry weight of 93.0 grains, the loss in weight, or 7.0 grains,, represents the weight of moisture originally contained. This expressed ;as a percentage of the total weight (100.0 grains) gives the moisture content or 7 per cent. The regain, which is expressed as a per- ............................... . 7.0 centage of the bone-dry weight, is or 7.5 per cent. The use of the term regain does not imply that the material as a whole has been completely dried out and has re-absorbed.moisture. During the processing of certain textiles, for instance-, complete drying during manu facturing is avoided as it might appreciably reduce the ability of the material to re-absorb moisture. A basis for calculating the regain of textiles is obtained by drying, under standard conditions, a sample from the lot and the dry weight thus obtained is used as-a basis in the calcu lations to determine the regain. . The moisture content of a hygroscopic material at any time depends upon the nature of the material and upon the temperature and especially the relative humidity of the air to which it has been exposed. 'Not only do different materials acquire various percentages-of moisture-after prolonged; exposure to a given atmosphere, but the rate' of absorption or drying varies with the nature of the material, its thickness and density. Table 2 shows the regain or hygroscopic moisture content of several organic and inorganic materials when in equilibrium at a dry-bulb tem perature, of 75 F and various relative humidities. The effect of relative humidity on regain of hygroscopic substances is clearly indicated'. The effect of temperature is comparatively unimportant.- In the case of cotton, for instance, an increase in temperature of 10 F has the same effect on regain as a decrease in relative humidity of one per cent. Changes in temperature do, however, affect the rate-of absorption or drying. Sudden changes in temperature cause temporary fluctuations in regain even when the relative humidity remains stationary.... ' The regain or moisture content affects the physical properties of textiles to a marked degree, changing the strength, pliability and elasticity. The fact that the regain of textiles will come into equilibrium with the Industrial Air Conditioning 829 Table 2. ; Regain op Hygroscopic Materials Moisture Content Expressed in Per Centof'Dry Weight of the Substance at . * Various Relative Humidities--Temperature, 7.5 F CLASSI ' FICATION Material Description ' ' - Relative Humiditt--Per Cent ' Acthobitt 10 20 30 40 50 60 ' 70 80 90 Cotton Sea island--roving 21 3.7 4.6 51 6.6 7.9 91 111 14.1 Eartebome Cotton . . American--cloth . 2.6 3.7 4.4. 5.2 5.9 61 .8.1 too 141 Schloering Cotton . Absorbent 41 9.0 115 15.7 105 201 22.8 241 251 Fuwa Natural Textile Fibers Wool Silk . linen . Australian merino--skein 4.7 7.0 8.9. 108 118 14.9 171 19.9 23.4 Hartshorns Raw chevennes--skein 3*2 5.5 6,9 OO 09 10.2 11.9 141 18.8 Schloefling Table doth 1.9 2.9 3.6' 41 5.1 6.1 7.0 8.4 102 Atkinson linen Dry spun--yarn 3.6 5.4 61 71 8.1 8.9 9.8 111 131 Sommer Jot* - - Average of several grades 3.1 5.2 6.9 8.5 10.2 12.2 14.4 17.1 20.2, Storch Hemp ' Manila,and sisal--rope 2.7 4.7 6.0 7.2 05 9.9 11.6 13.6 15.7 Fuwa . Rayons ` Viscose Nitrocellu lose Cupramonhun Average skein . CefluloBe Acetate Fiber _ ' 4.0 5.7 64 7.9 9.2 10.8 12.4 141 16.0 Robertson 01 1.1 1.4 1.9 2.4 3.0 3.6 41 51 Robertson M. F. Newsprint Wood pulp--24% ash 2.1 31 4.0 4.7 51 6.1 71 8.7 10.6 U. 8. B. of S. H. M. F. Writipg Wood pulp--3% ash 3.0 4.2 5.2 61 7.2 03 9.9 11.9 14.2 H.8. B. of S. Paper ' White Bond ( - Rag--1% ash ' 2.4 3.7 4.7 5.5 6.5, 71 08 10.8 13.2 U. S. B. of 8. Com. Ledger 75% rag--1% ash 3.2 4.2* 5.0 5.6 6.2 6.9 01 103. 13.9 U. 8. B. of S. Kraft Wrapping. Coniferous - - 3.2 4.6 5.7 6.6 7.6 09 101 12.6 14.9 D. R B. of 8. Leather Sole oak--tanned 5.0 05 11.2 15.6 16.0 181 20.6 24.0 29.2 Phelps Catgut . Racquet strings ' 4.6 7.2 06 102 110 141 171 19.8 21.7 Fuwa Glue - ' Misc. Organic Rubber _ Materials Wood ' Hide, - ' 3.4 4.8 5.8 6.6 7.6 9.0 10.7 11.8 121 Fuwa , Solid tire ' an 021 032 044 014 0.66 016 0.88 099 Fuwa . ' . Timber (average) . ' . 3.0 4.4 5.9 7.6 91 111 14.0 17.5 22.0 Forest P. Lab. Soap ' White .-'. - 1.9 3.8 5.7 7.6 10.0 12.9 16.1 19.8 231 Fuwa ^ Tobacco' - ' Cigarette ' ` : 5.4 8.6 11.0 131 16.0* 191 25.0 331 500' Ford ' White Bread ' ' 05 L7 3.1 45 6.2' 05' 11.1 141 19.0 Atkinson Crackers - 2.1 18 3.3 3.9' 5.0 61 03 10.9 14.9 Atkinson Food stuffs Macaroni Floor 5.1 7.4 08 102 11.7 13.7 161 19.0 22.1 Atkinson 16 4.1 51 6.5 OO 9.9 114 15.4 19.1 Bailey ' Starch : 12 ll 5.2 6*4' 7.4 03 91 10.6 12.7 Atkinson Gelatin ` 07 1.6 2.8'. 3.8. 4.9- 6.i 7.6 91- 11.4 Atkinson , Asbestpe Fiber Finely divided . 016 0.24 .0.26 012 041 051 062 073 014 Fuwa '' Silica Gel ' ` \ Mac. ' Inorganic Domestic Coke Materials Activated Charcoal Steam activated , '5.7 9.8. 117 is.2; 171 108 201. 211 22.6 Fuwa 0.20 .040 061 081 1.03 114 1.46 1.67 119 Sehrig . . - 7.1 141 218 26.2 281 291 300 3L1 32.7 Fuwa ; Sulphorle Add - HtSOt - ; 33.0 41.0 471 515 57.0 611 67.0 73.5 821 Mason conditions of the surrounding air and vary with its temperature and relative humidity is the fundamental basis for the control of, physical qualities-during manufacture. During the preparation processes in-a cotton mill, the cotton fibers should be in a condition to be easily carded. These, preliminary processes are carried out best in a relative humidity 830 CHAPTER 45 1946 Guide of 50 to 55 per cent. As the cotton fiber comes to the spinning operation, more flexibility is needed and the relative humidity is increased in this department. For many years, 65 per cent relative humidity was con sidered the optimum. To offset the extra work performed on the fiber as the spindle speed is increased; many cotton mills now carry 70 per cent. relative humidity in the spinning rooms `. Winding, warping and weaving are all processes calling for great flexibility and a consequent need for higher humidity. Other textile fibers, due to their different natural characteristics, are processed under relative humidities and temperatures applicable to each.. Rayons, on account of great loss of strength with the higher regains, should be processed in a relative humidity of 55 to 70 per cent. Acetate silk, another chemical fiber, with approximately 50 per cent of the regain of rayon, may be processed between 60 and 65 per cent relative humidity. All hygroscopic materials when in the state of absorbing moisture from the surrounding air produce a sensible heat rise to the air equivalent to the latent heat released by air to the material. This adiabatic conversion may account for a small percentage of the total heat load of the con ditioned space. `. Conditioning and Drying In general, the exposure of materials to desirable conditions for treat ment may be coincidental with the manufacture or processing of the materials, or they may be treated separately in special enclosures.' This latter treatment may be classified as conditioning or drying. The purpose of conditioning or drying is usually to establish i. desired condition of moisture content and to regulate the physical properties of the material. When the final moisture content i? lower than the initial one, the term drying is applied. If the final moisture content is to be higher, the process is termed conditioning. In the case of some textile products and tobacco, for example, drying and conditioning may be combined in one process for the dual purpose of removing undesirable moisture and accurately regu lating the final moisture content. Frequently conditioning or drying is . made a continuous process in which the material is conveyed through an . elongated compartment by suitable means and .subjected to controlled .atmospheric conditions. ' Control ol Rate of Chemical Reactions A typical example'of the second general classification, the control of the rate of chemical reactions, occurs in the manufacture of rayon. The pulp sheets are conditioned, cut to size, and passed through a mercerizing process. It is essential that during this process close -control of both temperature and relative humidity should be maintained. The tem perature controls the rate of reaction directly, while the relative humidity maintains a constant rate of evaporation from the surface of the solution and obtains a solution of known strength throughout the mercerizing period. -, - - - .. . Another well-known example in this class is. the drying of varnish which is an oxidizing 'process dependent upon temperature. High relative humidities have a retarding effect on the rate of oxidization at the surface . and allow the internal gases to escape freely as the chemical oxidizers cure the varnish from within. This produces a surface free from bubbles and a. film homogeneous, throughout. Desirable temperatures for drying Industrial'Air Conditioning 831 varnish vary with the quality. A relative humidity of 65 per cent is beneficial for obtaining die best processing results. 1 ' Control of Rate of Biochemical Reactions . In the field of biochemical control, industrial air conditioning has been applied to many different and well-known products. All problems involving fermentation are classed under this heading. As biochemistry is a subdivision of chemistry, subject to'the same laws, the rate of reaction may be controlled by temperature. An example of this is the dough room of the modern bakery. Yeast develops best at a temperature of 80 F. A relative humidity of 65 per cent is maintained sO as to hold the surface of the dough open to allow the carbon dioxide gases formed by the fer mentation to pass through and produce a loaf of bread, when baked, of even, fine texture without large voids. . Another example of a similar process is found in the curing of maca roni. The' flour and water mixture is fermented and dried. As .it is necessary to have a definite amount of water present to carry on a fer mentation process, the moisture must be removed in a relatively short period to stop fermentation and prevent souring and in such a manner as to avoid setting up internal strains in the mixture. Best results are obtained with the correct cycles of both temperature and humidity.. The curing of fruits, such as bananas and lemons, also comes under this classification. Bananas are treated somewhat differently and to accom plish the required results, a cycle of temperatures and relative humidities is used. The starches in the pulp of the fruit must be changed and the skin cured and colored, after which the fruit is cooled to maintain as low a rate of metabolism as possible. Ideal conditions range between 55 to 57 F and in no case should the temperature go below 49 F, as the starches ' then would become fixed and be indigestible.' ' ;: The curing of lemons is an entirely different problem. Bananas are cured for a quick market, while lemons are held for a future market. The process, therefore, varies in the temperature used. Temperatures from 54 tO 59 F have been found to be best suited for this process. A high relative humidity of 88 to 90 per cent is necessary to hold shrinkage to a minimum and, at the same time, develop the rind so'it will be sufficiently tough to. permit handling. . Tobacco from the field to the finished cigar, cigarette, plug, or pipe tobacco, offers another interesting example of what may be done by industrial air conditioning in. the control of color, texture and flavor. In the processing of tobacco, the first three classifications of air con ditioning are involved, and only through close atmospheric control can the best quality of the leaf be developed. . Control of Rate of Crystallization .. . - The rate of cooling of a saturated solution determines the size of the crys tals formed. Both dry- and wet-bulb.tempera.tures are of importance, as the one controls the rate of cooling, while the other, through evaporation, changes the density of the solution. .. . In the coating pans for pills, gum and nuts, a heavy sugar solution is; added to the tumbling mass. As the water evaporates, each separate piece is covered with crystals of sugar. A smooth, opaque coating is only. . accomplished by blowing into the kettle the proper amount' of air at the right dry- and wet-bulb temperatures. 832 CHAPTER 45 1946 Guide Elimination oi Static Electricity , The presence of static electricity is very detrimental to the satisfactory and economical processing of many light materials, such as textile fibers, paper, etc. It is also extremely dangerous where explosive atmospheres or materials are present. Fortunately,. this hazard is easily eliminated by increasing the relative humidity. In attempting to eliminate static electricity, it must be borne in mind that for successful elimination the air that actually comes "in contact with the material in. the machine must be at a relative humidity of 50 per cent or more. As some machines consume a great deal of power which is converted directly into heat, the temperature in the machine may be considerably higher than the temperature adjacent to the machine where the relative humidity is normally measured. In such cases, the relative humidity in the machine will be appreciably lower than that elsewhere in the room, and it may be necessary to maintain a room relative humidity of 65 per cent, or even more, before the desired results can be obtained. ' CALCULATIONS The methods for determining the proper heating and cooling loads for the various industrial processes are similar to those outlined in Chapters 14 and 15. Because of the large number of motors and heat producing units usually prevalent in an industrial application, it is particularly important that operating allowances for the latent and sensible heat loads be definitely ascertained and used in the calculations to determine the total design load. ' *. REFERENCE . i--The Present Status of Textile Regain Data, by A. E. Stacey, Jr. {National Association of.Cotton Manufacturers, 1927). BIBLIOGRAPHY Food . Air Conditioning for Sausage Manufacturing Plants, by M. G. Harbula (A.S.H.V.E. Transactions, Vol. 28, 1922, p. 343). Air Conditioning in the Bakery, by W. L. Fleisher (A.S.H.V.E. Transactions, Vol. 37, 1931, p. 141). Proper Air Conditions for the Manufacturing of Confections, by A. E. Stacey, Jr. (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning, October, 1937, p. 640). .. . .. Air Conditioning and Refrigerating Large Bakeries, 4>y W. L. Fleisher (Healing, Piping and Air Conditioning, December, 1929, p. 621; January, 1930, p/24). Pre-Cooling Fruits and Vegetables with Circulating Air, by C. E. Baker {Heating, Piping and Air Conditioning, January, 1932, p. 42). '. . Air Conditioning Maintains Quality of Fruits and Vegetables, by C. E. Baker (Heating, Piping and Air Conditioning, August, 1935, p. 369). Air Condition the Bakery Throughout, by W. W. Reece (Heating, Piping and Air Conditioning, August, 1936,. p. 149). ' - , . 'Banana Ripening Manual, Circular No. 14, Equipment Department, Fruit Dispatch Co., New York, N. Y. ' . . .. . The Commercial Storage of Fruits, Vegetables and Florists' Stocks, by D. H. Rose, ' R. C. Wright and T. M. Whiteman {17. S. Department of Agriculture, Circular No. 278).' Temperature Studies of Some Tomato Pathogens, by Alice A. .Nightingale and G. W. Ramsey (Z7. S. Department of Agriculture Technical Bulletin No. 520,. August, 1936). . Refrigeration of Oranges, by H. M. Hendrickson (Application Data Section No. 17, Refrigerating Engineering, September, 1940). ' Refrigeration of Lemons and Grapefruit, by Hi M. Hendrickson (Application Data Section No. 18, Refrigerating Engineering, October, 1940). 1- Industrial Air Conditioning 833 Printing Hygro-Xylometric Control of Air Conditioning, by H. H. Tunis (A.S.H.V.E. Journal Section, Heating, Piping and Air Conditioning, November, 1937, p. 637). ~ . Air Conditioning of Press Rooms, by I. C. Baker {Heating, Piping and Air Con ditioning, July, 1931, p. 553). .. Newspaper Plant Air Conditioned for Efficient Production, by J. A. Osborn {Heating, Piping and Air Conditioning, January, 1932, p. 40). . Air Conditioning Frees Rotogravure Plant from Weather Hazards, by H. E. Jacobsen {Heating, Piping and Air Conditioning, September, 1935, p. 423). Bureau of Standards Studies Determine Press Room Conditioning Requirements, by C. G. Weber {Heating, Piping.and Air Conditioning, March, 1936, p. 137). " Silica Gel Air Conditioning System Serves Rotogravure Printing Plant, by H. E. Ryerson {Heating, Piping and Air Conditioning, August, 1937, p. 497). Moisture Control by Liquid Absorption Offers a Useful Air Conditioning Tool, by F. M. Johnson {Heating, Piping and Air Conditioning, December, 1938, p. 782). Meeting the Air Requirements in a Bindery and Printing Plant, by N. W. Downes, {Heating and Ventilating, February, 1921, p. 25). Heating and Ventilating the Bureau of Engraving and Printing {Heating and Venti lating, February, 1923, p. 55). - Humidity in the Pressroom {Heating and Ventilating, May, 1932, p. 35). Dehumidifying with Gas in a Printing Plant {Heating and Ventilating, May, 1935, p. 31). -. Air Conditioning in the Paper Industry {Heating and Ventilating, October, 1935, p. 23). . Air Conditioning the Newspaper Plant, by R. T. Williams {Heating and Ventilating, September, 1937, p. 63). - Air Conditioning Requirements of Multicolor Offset Printing, by C. G. Weber {Refrigerating Engineering, December, 1936, p. 6). . A Study of the Removal of Sulphur Dioxide from Library Pat, by A. E. Kimberly and A. L. Emley {U. S. Bureau of Standards Miscellaneous Publication, No. 142, October 17, 1933). . Reactions of Lithographic Papers to Variations in Humidity and Temperature, by C. G. Weber and L. W. Snyder {17. S. Bureau of Standards Journal Research, January, 1934). ' The Treatment of Offset Papers for Optimum Roister, by C. G. Weber and M. N. V. Geib {V. S. Bureau of Standards Journal Research', February, 1936). . Summary Report of National Bureau of Standards Research on Preservation of Records, by A. E. Kimberly and B. W. Scribner {U. S. Bureau of Standards Miscel laneous Publication, No. 154, March 16, 1937). ' . Miscellaneous Effect of Air Conditioning upon Munitions, by J. I. Lyle (A.S.H.V.E. Transactions, Vol. 23, 1917; p. 383). Air Conditioning of Blackout'Plants, by W. A. Grant (A.S.H.V.E. Transactions, Vol. 48, 1942, p. 459). -- . Air Conditioning in Industrial Processes (Match Factory), by W. L. Fleisher {Heating,. Piping and Air Conditioning, March, 1931, p. 196). . . .% Air Conditioning as Applied in Theatres and Film Laboratories, by Dl C. Lindsay {Transactions Society of Motion Picture Engineers, April, 1927, Vol. XI, No. 30, p. 335 365). Air Conditioning for Textile Plants Making and Using Synthetic Yarns, by L. L. Lewis {Rayon Textile Monthly, July, August, September, 1930). Relation of Air Conditions to Tobacco Curing,, by J. Johnson and W. B. Ogden {Wisconsin Agricultural Research Bureau 110: 1-48, 1931). ` An Investigation of the Bacterial Contamination of the Air of Textile Mills with Special Reference to the Influence of Artificial Humidification, by W. F. Wells and E. C. Riley {The Journal of Industrial Hygiene and Toxicology, Vol. 19, No. 10, December, 1937). .. . Air Conditioning for Clothing Research Laboratory {Heating and Ventilating, July, 1943, p. 69). ' ^ 834 ' , CHAPTER 45 . .1946 Guide Controlled Air Supply for Supercharger, Carburetor and Engine Testing, by C. S. * Leopold {Refrigerating, Engineering, August,1943, p. 85). , ' Air Conditioning Aids in Artillery'Optical Equipment (Heating and Ventilating, August, 1943, p. 46). ,. .. Air Processing Needs of Plywood Plane Parts, by F. O. Jordan (Heating and Venti lating, April, 1944, p. 67). , .' ' Close Machine Tolerances Possible Through Temperature Control, by R. P. Dewey {Heating and Ventilating, April, 1944, p. 60). '. . Design of Low Temperature Test Cabinets, by F. Crampton Frost and T. J. Lopiccolo .{Heating and Ventilating,}u\y, 1944, p.57). . . . Industrial Cooling as a Production Aid, by J. Partington, Jr. {Heating and Ventilating, April, 1944,`p. 47). .* - ,. . Penicillin, by Lester T. Avery {Heating and Ventilating, March, 1944, p. 45).. Penicillin Production Depends Upon Control of Air Conditions {Heating, Piping and Air Conditioning, April, 1944, p.,188). .. , .` , Heating, Air Conditioning and Insulation for Penicillin Production, by J. C. Siegesmund {Heating, Piping and Air. Conditioning, August, 1944,`p. 475). 'Refrigeration Insures Quality of Clothing for the Army, by A. J. Mallinckrodt{Heating and Ventilating, March, 1944, p. 79). CHAPTER 46 ^Ixhauilincj. anICc Suslems conveying. -- Classification of Systems, Hood Design Principles, Hood Suction and. Indraft Velocities, Duct System Design, Air Cleaning Equipment, /Resistance of Systems, Air Flow Pro ducing Equipment, Protection Against Corrosion IN many' industrial plants some type of exhaust system designed to collect and remove dusts, fumes, mists, vapors and gases is essential in order to promote efficiency, economy, and safety of operation. Defini tions of these various contaminants are included in Chapter 10, Air Contaminants. The theory of air flow in an exhaust system, in the following paragraphs A to D will be found in a publication1 of the American Foundrymen's Association. A. When the air flow producing equipment of an exhaust system is properly operated it will produce a negative pressure (below atmospheric) in the exhaust side of the system sufficient to overcome all resistance and to sustain the desired air velocity; and, further, will overcome all resistances on the discharge or positive pressure side of the system so that the air drawn through exhaust inlets will be discharged against atmospheric pressure. . . B. An exhaust system is entirely.dependent on a sufficient volume of air flowing into the exhaust inlets to catch the matter to be exhausted before such matter has an oppor tunity to diffuse into the general atmosphere of the work place or room. , C. The velocity of the air flowing into an exhaust inlet is usually of secondary im portance and' becomes an essential factor only when a certain velocity is required to * overcome some force acting on the matter to be caught. The velocity within an exhaust system is only important to the extent that it shall be sufficient to convey the entrained matter and prevent it from settling or dropping out in the piping system. Velocity in . terms of velocity pressure is most essential in designing a system because it is the basis upon which all calculations are made. In testing and checking a system the velocity as determined from the velocity pressure reading obtained by means of a Pitot tube is the only true indication of the exact air flow in a pipe or system. . . D. The total pressure within an exhaust system is only of importance in determining the power required to operate the system. Total pressure tests do not indicate the proper functioning of an exhaust system as related to the volume and velocity of the air flowing into, an exhaust inlet. . ... s General design information is included in this chapter which is intended to relate primarily to industrial exhaust systems. ' CLASSIFICATION OF SYSTEMS In general there are two basic layouts of exhaust systems, the central and the multiple unit system. In. the central system a fan is located near, the center of operations with a piping system radiating to the various machines to be served. In the multiple unit system, which is. sometimes employed where the machines to be served are widely scattered, or where the operations are apt to be independent or intermittent, small individual exhaust fans are located at the center, of the machine groups or at each machine. The unit arrangement has the advantage of flexibility. . Exhaust systems may be classified with respect to the nature of the material to be handled by them as (a) those handling dust and (6) those handling fumes, mists, vapors and gases. There is'a marked difference in design details, of; systems serving dust producing operations and those exhausting the more vapor-like matter even though the same basic 835 '836 CHAPTER 46 1946 Guide theories govern both classes. The type of hood and exhauster, the adap tion of general ventilation, the conveying velocities and duct construction differ substantially. ' Exhaust systems are also classified by the means employed to collect the material. The dust or refuse may be .collected and controlled by enclosed hoods or open hoods with positive inward air movement or by diluting or exhausting the general air of the room. With some classes of machinery it is not feasible to hood the machines closely and in these cases open hoods over or adjacent to the machines are provided to collect as much as possible of the dust and fumes. This class includes such machines as rubber mills, package filling machinery, sand blast, crushers, , forges, pickling, tanks, melting furnaces, and the unloading points of various types of conveyors. Open hoods should be placed as close to the source of dust or fumes as possible, with due regard to the movements of the operator, and should be placed so that the operator is in no case in the path of the exhausted material. When the hood must be placed at some distance above the machine-it should be large enough to cover a large area as diffusion is usually quite rapid. . . Some consideration should be given to the natural movement of the fumes. For those that are lighter than air, the hood may be over or above the machine; and where a heavy vapor, or dust-laden air at ordinary temperature is to be removed, horizontal or floor connections U"e some times preferable. In many cases there are convection currents and other atmospheric disturbances in the work room which should be given con sideration. These disturbances diminish the tendency of dust and fumes to settle from the room air because of their density. ' In another class of operation the main objective is to prevent the escape of dust into the surrounding atmosphere, and the removal of some dust from the machine or enclosure may be merely incidental. The dust- creating apparatus is enclosed within a housing which is made as tight as practicable, and sufficient suction is applied to the enclosure to maintain an inward air leakage, thus preventing escape of the dust. While the exhaust system is required to handle only the air which leaks in through the crevices and openings in the enclosure, yet in many installations leakages are very high and great care is required to obtain satisfactory results with a system of this kind. The inward-leakage. principle is . utilized for controlling dust in the operating of tumbling barrels, grinding, screening, elevating, and similar processes. . Certain dust and fume producing operations are best carried on by isolating the process in a separate compartment or room and then apply ing general ventilation to this space. The compartment or room in which ' the work is performed should be as small as is consistent with convenience . in handling the work. The ventilating system should be designed so that a current of clean air is drawn across the work in such a manner as to carry the.dust or fume away from the operator and out of the work space. Another method of accomplishing the control of this type of installation, . and one usually applied in the case of gases and fumes, is the dilution method; In this case sufficient clean air is introduced generally into the work space tp dilute the contamination ,to a safe level. : HOOD DESIGN PRINCIPLES2-3 The first step in the design of an exhaust system is to determine the number and size of the hoods and their connections. No general-rules, Exhausting and Conveying Systems 837 however, can be given since hood and duct dimensions' are determined by the characteristics of the operations to which they .are applied. When a tentative decision regarding the set-up has been made, it is-then necessary to obtain the suction and air velocities required to effect control. At this point the designer must rely upon the prevailing practice and on such physical data relating to hoods, duct systems and collectors as are avail able. The fan speed must be sufficient to maintain the estimated suction and air velocities in the system.-' In general, the-most important require ments4.of an efficient exhaust and collecting systemare: ' 1. Hoods, ducts, fans, motors and collectors should be of adequate size and type. 2. The air velocities should be sufficient to control and convey the materials collected. 3. The hoods and ducts should be placed so as not to interfere with the operation of a machine or any working part. .. . ' 4. The system should do the required work with a minimum power consumption. 5. When inflammable dusts and fumes are conveyed, the piping should be provided with an automatic damper in passing through a fire-wall. 6. Ducts and all metal parts should be grounded to reduce the danger of dust ex plosions by static electricity. . 7. The exhaust system should be readily accessible for inspection and care. ` HOOD SUCTION AND INDRAFT VELOCITIES The removal of dust or waste by means of an exhaust hood requires a movement of air at the point of origin sufficient to carry it into a collecting system. The air velocities necessary to accomplish this depend upon the physical properties of the material to be eliminated and the direction and ' speed with which it is thrown off. If the dust to be removed is already, in motion, as is the case with high-speed grinding wheels, the hood must be installed in the path of the particles so that a minimum air volume may be used effectively. It is always desirable to design and locate a hood so that the volume of air necessary to produce results is as small as possible. This will reduce the size of equipment, the power required by the system, and also the heating load requirements in winter. , Air Flow from Static Readings .' The static suction at the throat of a hood is frequently used in practice as a measure of,the effectiveness of control. Where the hood coefficient is known the volume of air flow through any. hood may be determined from the equation: where Q = 4005 / A y/~kt . (1) '. Q -- volume of air flow, cubic feet per minute. ., _ A = area of connecting duct, square feet. At = static suction measured 3 diameters from throat of hood, inches of water. = orifice or restriction coefficient which varies from 0,6 to 0.9 depending on the shape of the hood.... .. . An average value of/is 0.71, although for a well-shaped opening a value of 0.8 may be used. The factor f is determined from the equation: ' f~yl% . ' .: (2) where &v is the velocity head in the connecting duct. . The sialic suction is not a good measure of the effectiveness of a/hood unless the area of the opening and the location of the operation with 838 CHAPTER 46 , , ' 1946 Guide Table 1. Rates of Flow Through Branch Pipes Woodworking Machines Pipe Diameter, In. 3. 4 5 Air Volume, Cfm ' 200 350 550 Pipe Diameter, In. '6 7 8. Air Volume, Cfm . 800 ' 1100 1400 Tablb 2. Branch. Pipe Size for Woodworking Machine Hoods -Type op Machine Self feed table saw Other single saws Saws with Dado Head Band saws . . Disc sanders .. Triple drum sanders Size. In. . Min. Max. No. op Branches Minimum Diameter. In. . Bottom Branch . Top Branch Others 25 4 18 1 ` 18 1 4 5 15 22 4 4 2 32 5 4 3 6 2 ; 5' 5 18 26 32 38 . 18 1 28 . 1 32 2 38 2 48 . 3 4. 5 .4 5 . 5. 4 4 4 4' 30 1 7' . 30 36 1 8 . 36 42 1 9 42 . 48 1 10 Single drum sanders: (area in sq in.) Horizontal belt sanders 350 700 1400 9 Vertical belt sanders Jointers . 6 9 8' Single planers ' Tenoner . ' '. 20 26 350 700 1400 2800 9 14 ' .6 9 14. 8 20 20 26 36 1 . 4a 5 6 7: 2 2 .. 1 ' 1 .1 5 6 4 5 6 4 . 4 1 ,4 .1 5 1 5 . 16 1 . 7' 2. ; 5 5 aNot over' 10 in. diameter. ' Table 3. Rates of Flow Through Branch Pipes Grinding and Buffing Wheels . Pips Diameter, In. .3 . . 4,- - -. 5 Ant Volume, Cpm 225 400 .. . : 600 Pipe Diameter, In.' . 6' 7' ' Air Volume, Cfm 900 " . 1200 ' ' Exhausting and Conveying Systems 839 , Table 4. Branch Pipe Sizes for Grinding and Buffing Hoods -------- ---------- _ . Type of Wheel . Wheel Size Diameter, In. Maximum Branch Pipe Minimum Diameter. Min. Max. Width In. Area Sq In. Grinding Disc Grinding 9 9 18 18 24 24 30 30 36 20 20 30 1 30 3 175 4 300 5 500 6 700 3 4 5 6 7. 300 . 4 : .5 . Buffing, Polishing and Scratch Brushing 8 2 50 8 16 3 150 16 24 . 4 300 24 30 ' 6 600 3X 4 56 respect to the hood are known. This is clearly indicated by Equation 3 which shows that the velocity at any point along the axis varies approxi mately inversely as the square of the distance. This formula coupled with Equation 1 should serve to indicate the velocity conditions to be expected when operations are conducted externally to the hood opening. Design Based on Total Air Flow Where the foregoing factors are not known, the usual method of designing an exhaust system is to base theair flow through the system on rates of flow through: each hood which have been found by experience to provide adequate control. For woodworking systems the rates of flow given in Table 1, calculated on the basis of a branch velocity of 4000 fpm, are adequate for control. Using these air flow rates, Table 2 gives the size of pipe connections to be used with the more common wood working machines. Properly designed grinding and buffing wheel hoods have been found to be adequately controlled when the rates of air flow, given in Table 3, calculated on the basis of a branch velocity of 4500 fpm, are used. Table 4 gives, the minimum branch pipe sizes to be used on the more common sizes of grinding and buffing wheels. In some states grinding, polishing and buffing wheels are- subject to. regulation by .codes. (See Standards, Chapter 51.), The static suction requirements, which range from 1J4 to 5 in. water displacement in a [/-tube, must be followed in such states although in several instances they appear to be excessive. Frequently, in these operations, a large part of the wheel must be exposed and the dust-laden air within the hood, is thrown outward by the centrifugal action of the wheel, thus counter acting useful inward draft. This tendency may be diminished by locating the connecting duct so as to create an air flow of not less than 200 fpm past the lower edge of the-wheel. : . Controlling Air Velocities .. Exact determinations of hood control velocities are not available, but it is safe to assume that for most dusty operations velocities should not be less than 200 fpm at the noint of origin. . Recommended air velocities through hood openings for various processes are given in Table-5. For granite dust generated by pneumatic devices, velocities from 150 tq 840 CHAPTER 46 1946 Cuide 200 fpm, depending' on the type of hood used, are recommended as sufficient for safe control5. Considering the character of the industry, air velocities of this order may be extended to similar dusty operations. The method for approximately determining these velocities in terms of the velocity at the hood opening is given in Equation 3. No set rule can be given regarding the shape of a hood for a particular operation, but it is well to remember that its essential function is to create an adequate velocity distribution. The fact that the zone of greatest effectiveness does not extend laterally from the edges of the opening may frequently be utilized in estimating the size, of hood required. Where complete enclosure of a dusty operation is contemplated, it is desirable to leave enough free space to equal the area of the connecting duct. Hoods for grinding, polishing and buffing should fit closely, but at the same time should provide an easy means for changing the wheels. ` It is advisable to design these hoods with a removable hopper at the base to capture the heavy dust and articles dropped by the operator. Such provisions are of assistance in keeping the ducts clear. Air volumes used to control many Table 5. Recommended,Air Velocities Through Openings in Hoods Enclosing Operations or Located Over Zones of Generation of Dusts, Fumes, Vapors and Gases Released in Certain Manufacturing Processes Condition of Generation of Contaminant Minimum Air Velocity, FPM Released without noticeable movement___ __________ 50-100 Released with low velocity 100-200 Active generation.............___ Released with great force.... 200-500 500-2000 Process Evaporation of vapors, exhaust from pickling, washing, degreasing, plating, welding, etc. * Paint spraying in booth; inspection, sort ing, weighing, packaging, low speed conveyor transfer points, rotating mix tures, barrel filling. Foundry shakeout, high speed conveyor transfer points, crushers, screens. . Grinding, tumbling mills, abrasive clean ing- '. . diist discharges may often be reduced by effective baffling or partial enclosure of an operation. This procedure is strongly urged where dusts are directed'beyond the zone of influence of the hood. Axial Velocity Formula for Hoods When the normal flow of air into a hood is unobstructed, Equation 3 may be used to determine the air velocity at any point along the axis6: : : y -- 01 Q X*+0.1A where V = velocity at point, feet per minute. Q = volume of air handled, cubic feet per minute. x = distance along axis, feet. A - area of opening, square feet. " (3). Velocity Contours "' It is possible by use of a specially constructed Pitot tube' to map contours of equal'velocity in any axial plane located .'in the field of in fluence.' It has been found that-the positions of these contours for any hood can be expressed, as percentages of the velocity at the hood opening and are purely functions of the shape of the hood 8i . Exhausting and Conveying Systems 841 Further, the velocity contours are identical for similar hood shapes when the hoods are reduced to the same basis of comparison. These facts are applicable to all hood problems so that whefi the velocity contour distribution is known, the air flow required can be-determined. Fig. 1- shows the contour distribution in two axial planes perpendicular to the sides of a rectangular hood with a side ratio of one-half. The distribu tion shown is identical for all openings with, a-similar side ratio provided the mapping is as shown in the figure. The contours, of: course, are expressed as percentages of the velocity at the opening. '. - Low Velocity Systems , . -- Oh multiple installations of the same operation it is often possible to institute a great saving in power cost by designing an exhaust system ' Velocity at the Opening using low velocities in the main ducts. Such a system for use in grinding and shaping porcelain has been described9. . In these operations,' the separate machines are grouped around a central plenum-chamber and exhausted by means of a low pressure fan connected to the plenum. In this case a. power saying of over 90 per cent was obtained. A similar design technique10 has been described for use in ventilating plating tanks. Large Open Hoods ' Large hoods, such as may be used for electroplating and pickling tanks, should be sub-divided so the area of the connecting duct is not less than one-fifteenth of the open area of the hood.- Frequently, it will be.found necessary- to. branch the main duct in order to obtain, a uniform distri-: 842 CHAPTER 46 - , 1946 'Guide. . bution of flow. Canopy hoods should extend 6 in. laterally from the tank for every 12 in. elevation, and. wherever possible they should have side . and rear aprons so as to prevent short circuiting of air from spaces-not directly over the vats, or tanks.- . In most cases, hoods of this type take, advantage of the natural tendency of the vapors to rise, and air velocities may be:kept low. -Cross drafts from.open doors or windows disturb the rise of the vapors and therefore provision must be made for them. The air velocities required also depend upon the character of the vapors given off, cyanide fumes, for example, requiring an air velocity of approxi mately 75 fpm on the surface of the tank and add and steam vapors requiring velocities as low as 25 to 50 fpm. The total volume of air flow necessary to obtain these velocities may be approximately determined from the equation: . . . . . ..' . Q = 1.4 PD V ' (4) where Q -- total volume of air handled by hood, cubic feet per minute. P -- perimeter of the tank, feet. D = distance between tank and hood opening, feet. V = air velocity desired along edges and surface of tank, feet per minute. Lateral Exhaust Systems The lateral exhaust method, as developed for chromium plating ll, is applicable in many instances in preference to the canopy type hoods. The method makes use of drawing air and fumes laterally across the top of vats or tanks into slotted ducts at the top and extending fully along one or more sides of the tanks. The slots are 1 in*, wide and for effective ventilation a 2000 fpm exhaust air velocity at the slot face is advisable. In addition, the duct should not be required to draw the air laterally for a distance of more than 18 in. and the level of the solution should be kept 6 to 8 in. below the top of the tanks. If width of tank is over'18 in. a double lateral exhaust may. be used with slots on both sides. . It has also been determined that a similar control may be used for tanks wider than 3 ft when the same velocity (2000 fpm) is maintained through a slot which is increased in. for every foot of width greater than 3 ft. When these slots must be extended more than 6 ft in length, some method of spreading the flow is necessary to provide even air flow distribution through the entire slot length. This can be accomplished by tapering the slot, which incidentally will add to the resistance of the system. A more economical approach is to place properly spaced-vanes in the side ducts, or to branch the side ducts u. , ` The flexible exhaust tube method may be advantageously used for removing dust or fumes. Flexible tubes having one end connected to an exhaust system and a slotted hood attached to the other end, may be shaped at will to fit in with industrial processes without affecting the ease of operation. Efficient dust or. fume removal' may be had with use of relatively, small exhaust volumes. /This type of system may be. used, on swing grinders, -portable grinding wheels,: spidering operations, stone cutting, rock drilling, etc. `. Spray Booths . - . In the'design of an efficient spray booth, it is essential to maintain an even distribution of airflow through the opening and:about the object being sprayed: While in many instances spraying operations can be Exhausting and Conveying Systems 843 performed mechanically in wholly enclosed booths, the volatile vapors may reach injurious or explosive concentrations. At all times the con centrations of these vapors, and particularly those containing benzol, should be kept well below 100 parts'per million in the breathing zone of the worker. Spray booth vapors are dangerous to the health of the worker and care should be taken to minimize exposure to them. It is recommended in the design of spray booths that the exhaust duct be located at the end of the booth opposite the opening. In front of this duct should be placed baffle plates which will cause a uniform air velocity distribution across the frontal area. The air volume should be sufficient to maintain a velocity of not less than 100 fpm over the open area of the booth (150 fpm is preferable where benzol or lead is present in the paint) and the vapors should be discharged through a suitable stack to permit dilution. It is good practice to pass the fumes or vapors through baffle type washers or scrubbers designed for efficient spray' removal. , Hoods for Chemical Laboratories . Hoods' used in chemical laboratories are generally provided with sliding windows which permit positive control of the fumes and vapors evolved by the apparatus. Their design should offer easy access for the installation of chemical equipment and should be well lighted: Air velocities should exceed 50 fpm when the window is fully open.. Kitchen Hoods . - The length and width of kitchen hoods should be such as to extendbeyond the extreme projection of the ranges, broilers, etc., over which they are installed. The minimum projection or overlap should be 12 in. Where space conditions permit, range hoods should be about 2 ft high so as to provide a reservoir to confine momentary bursts of smoke and steam until the exhaust system can evacuate the hood. Range hoods should be.located as low as possible to increase their effectiveness. A' steel plate placed horizontally within a kitchen hood and located sufficiently high above the level of the bottom of the hood to permit use, of a row of lights within the hood along the edge has been found effective in improving the operation. The area between the edges of the plate and the edges of the hood should be selected according to the exhaust volume and velocity required. In general the amount of air to be' exhausted from restaurant range hoods is at the rate of 100 fpm per square foot of face area. Thus, a hood 4.5 ft wide by 30 ft long has a face area of 135 sq ft, which multiplied by 100 fpm velocity results in a total air quantity to be exhausted of 13,500 cfm. In some cases, where the application is principally frying and where it is not practical to install a hood 2 ft high, it is recommended that the face velocity be increased from 100 to 150 fpm, depending on peak load con ditions in the kitchen., Exhaust connections to range hoods should always be made at the top and back of hoods, and should be spaced pref erably not more than 6 ft apart and be. rectangular in shape with the long side parallel to the back of the hood. Exhaust openings into range hoods should be designed to maintain a velocity of 1500 to 1800 fpm: An approved fire damper with fusible link should be (and is required by code in many states)'installed in the main exhaust duct or branch adjacent to tlje range hood. -:Should there.be more than, one hood con nected to a common-duct, then'the branch duct to each hood should be. provided with a fire damper. Access doorsishould be.provided at the fire 844 CHAPTER 46 1946 Guide ' damper for purpose of inspection, cleaning, or for renewal of fusible link. All exhaust piping to range hoods, commonly called grease ducts, should be provided with tight fitting cleanout doors of adequate size to permit easy removal of grease. Some engineers use filters to advantage in hoods which are subject to grease conditions. . - Hoods over steam tables should be of similar construction to range hoods. It is good practice to design such hoods with a face velocity of 60 to 70 fpm. Hoods over dishwashing machines are usually relatively small and generally 1500 to 2000 cfm per hood is allowed, which is equivalent to a velocity of approximately. 100 fpm per square foot of face area: Range hoods in diet kitchens are constructed the same as restaurant range hoods but with less exhaust air per square foot of face area, depending upon the nature of the food cooked. r Hoods are not often used in private residences unless they are quite large and the consideration of expense is not important.' For such residences the hoods should be designed on the same basis as diet kitchens. Most all residence kitchens can be effectively and economically venti lated by the installation of a built-in kitchen ventilator, which should be located in an outside wall and in close proximity to the kitchen range. It has been found that the capacity-of the built-in kitchen ventilator should be at least 350 cfm regardless of the size of kitchen. This can be justified on the basis that the smaller the kitchen the more concentrated the heat will be thus requiring a more rapid rate of air change. Standard size built-in kitchen ventilators are generally available in three sizes, namely 350, 500 and 800 cfm. The proper size to use will depend on design conditions and available wall space. - DUCT SYSTEM DESIGN In' designing a duct system it is necessary to recognize a few funda mental principles (see also Chapter 41). Knowing the quantity of air required, the size of the duct may be computed from Equation 5: ' where A = cross-section area of duct, square feet. . Q = air quantity to be handled by the duct, cubic feet per minute. V = velocity of air, feet per minute. .. ' Aii Velocities in Ducts . . Where it is necessary to transport the particulate material collected in an exhaust system, minimum carrying velocities must be maintained in the ducts preceding the collector. It has been found that good results are obtained when design air velocities in horizontal runs are not less than , 2000 fpm or not greater than 5000 fpm. When the dust being carried is organic and other than wood flour, or similar material, a velocity of 2500 fpm is adequate. Approximate required conveying velocities are given in Table 6. '. . ..For duct systems wherein the air has no dust .or solid load, a lower velocity is desirable, which may range from 1200 to 2000 fpm. In view ' of the fact, that the horsepower required by a system depends, directly ori the resistance and the resistance is a function of the velocity, eco- nomicahdesign requires velocities of this magnitude. ' . Exhausting and Conveying Systems 845 The equal friction method is generally used for designing a duct system as this insures equal resistance to air flow in all branches throughout the System (see Chapter 41). Long main ducts do not generally provide the most economical layout. Where it is necessary to ventilate a large number of machines, or machines which are widely, separated, it is desirable to locate the fan at approximately the center of the system. With this arrangement it is possible to choose a fan which will deliver the required air quantity against a lower resistance pressure, and this will generally result in a horsepower saving. - . When a system carrying dust is designed with'an oversize main duct to allow for future extension; the air velocity may be found to be too low to carry the dust, and serious plugging may occur.. In this case it is desirable to install an orifice in the end of the pipe to allow for the lower air quantity. Construction . . The interior of all ducts.should be smooth and free from obstructions at joints and soldered air-tight. Other sealing mediums are permissible where soldering is impracticable. '. Ducts should be constructed of galvanized sheet metal except when the presence of corrosive fumes or gases, temperatures above 400 F, or other factors would make galvanized material impractical. For the usual exhaust systems the metal thicknesses shown on Table 7. are recom mended. Elbows and angles should be a minimum of two gages heavier than straight lengths of equal diameter. Hoods should be a minimum of two gages heavier than straight sections of a connecting branch. Longitudinal joints of ducts should be lapped and riveted or spotwelded on 3-in. centers maximum. Girth joints or ducts should be made with lap in direction of air flow, with 1 in', lap for duct diameters through 19 in. and in. lap for diameters over 19 in. Elbows and angles should have an inside or throat radius of two pipe diameters whenever possible. Large radii are recommended for heavy concentrations of highly abrasive dusts. Elbows 6 in. or less in diameter should be constructed of at least 5 sections and, if over 6 in. in diameter, of 7 sections, with angles pieced proportionally. Hoods should be free of sharp edges or burrs and re-, inforced to provide necessary stiffness. 'Transitions in mains and submains should be-tapered with a taper 5 in. long for each 1 in. change in diameter whenever possible. All branches should enter the main at the large end of the transition at an angle not to exceed 45 deg or preferably 30 deg. Branches sho.uld be connected only to the top or sides of mains, with no two branches entering diametrically opposite to each other. Dead end caps should be provided within 6 in. from last branch of all mains and sub-mains. Cleanouts should be provided every 10 ft and near each elbow, angle, or duct junction in horizontal sections. Ducts should be supported sufficiently to place no loads on connected equipment and to carry weight of a system plugged with material. The Table 6. Approximate Conveying Velocities Material Conveyed . Design Velocity FPM Vapors, gases, fumes, very fine dust......................................:....... i..... t.... - Fine drv dusts. . Average industrial dusts ' ....... . Coarse particles Large particles, heavy loads, moist materials..______________________ 2,000 1 3,000 3.500 3,500-4,500 4.500 and over 846 CHAPTER 46 1946. Guide maximum distance between supports should be 12 ft for 8 in. or smaller ducts and 20 ft for larger ducts. Six in. minimum clearance should be provided between ducts, and the ceiling, wall or floor. Blast gates for adjustment of the system should be placed near the connection of a branch to the main and means of locking gates after the adjustments have been made should be included. Rectangular ducts should be. used only when clearances prevent the use of round construction. Rectangular ducts should be as nearly square as possible. The weight of metal and the lap, and other construction details, should be the equal of round duct construction having a diameter equal to the longest side. All pipes passing through roofs should be equipped with,collars so arranged as to prevent water from leaking into the building. . The main trunks and branch pipes should be as short and straight as possible. Cleanout openings having suitable covers should be placed in the main and branch pipes so that every part of the system can be easily reached in case the system clogs. Either a large cleanout door should be placed in the main suction pipe near the fan inlet, or a detachable section of pipe, held in place by lug bands,'may be provided. Every pipe, should be kept open and unobstructed throughput its entire length, and no fixed screen should be placed in it, although the use of;'1 a trap at the junction of the hood and branch pipe is permissible, provided it is not allowed to fill up completely. The passing of pipes through fire walls should be avoided wherever possible, and floor sweep connections should be so arranged that foreign material cannot be easily introduced into them- . At the point of entrance of a branch pipe with the main duct, there should be an increase in the latter equal to their sum. Some state codes specify that the combined area be increased by 25 per cent. While this is not always good practice and is frequently done at the expense of a reduced air velocity, it is often done where future expansion of the exhaust system is contemplated. ' Duct Resistance ' The resistance to flow in any galvanized: duct riveted and soldered at the joints may be obtained from Fig. 2, Chapter 41. The1 pressure, drop through elbows depends upon the radius of the bend. For elbows whose centerline radii vary from .100 to 300 per cent of pipe diameter, the loss may be. estimated from Table 8.. It is sometimes'convenient to express the resistance of an elbow in terms of an equivalent length of duct of the same diameter. Thus with a center line radius equal to the pipe diameter the resistance is. equivalent to a section of straight pipe approximately Table 7. Gages'of Metals for Exhaust Systems3 Diameter of Round Pipe or Greatest Dimension of Rectangular Pipe, . Inches . . Thickness of Duct Material U. S. Gage Number For Highly Abrasive Matter For Other Matter Up to 8 inclusive..........-..................... Over 8 to 18 inclusive. Over 18 to 30 inclusive.___________ Over 30....... ____________ ~____ ______ 20 22 18 . 20 16 . 18 14 . ' 16;, : "Fundamentals of Design, Construction, Operation and Maintenance of Exhaust Systems' {American Foundrymen's Association, p. 63), , ' . .. . .. Exhausting and Conveying Systems 847 10 diameters long, while with a center line radius 1}^ times the diameter, the resistance is apparently, the same as that of seven diameters of . straight pipe. 1 "T , . AIR CLEANING EQUIPMENT Primary dust separators depend for'their air cleaning action on centri- fuging out the dust particles or on imparting to the transporting air stream a'quick change in direction, accompanied by a sudden reduction in velocity. They may be applied to exhaust systems from polishing and buffing wheels and, in some cases, as a preliminary separator ahead of a final dust arrester. ' .' Dust particles which cannot be caught in inertia type separators are usually removed by one of the following methods: - 1. Filtration. Of the filter arresters the cloth type, either of the screen,. . envelope, or bag construction, is most generally used for industrial ex- haust systems. Cloth arresters properly engineered for this job and handling dust for which they are suited operate at a good efficiency. 2. Wet Collectors. Wet collectors have been in use for many years, but only recently have been introduced for collection of industrial dust fromexhaust systems. They are particularly applicable where moisture is present in the air being exhausted. The resistance is relatively low in wet collectors suitable for dust removal and remains constant for a given exhaust system. 1 3. High-tension Electrical Precipitation. High-tension electrical preci- ' pitation. has been applied to removal of dust, fumes, and mists from air. and other gases. (See section on Electric Precipitators in Chapter 33.) 4. Dynamic Precipitators. This equipment effects removal of entrained dusts by means of a specially designed fan in which the rotating element imparts a centrifugal-force to the dust particles. Originally these preci- pitators were intended for the collection of dry dust, but recently the construction has been modified to permit the introduction of water into the dirty air intake, thus increasing its application to more kinds'of dust. Consideration must be given to the type of: dust handleda. , '' For additional information on dust and cinders,' see Chapter 33, Air Cleaning Devices. ; . - . . , . ' , ' ' ' RESISTANCE OF SYSTEM The maintained resistance of the exhaust system is composed of three . factors: (1) loss through the hoods, (2) collector drop, and (3) friction drop in the duct system. , . The loss through the hoods is usually assumed to be equal to the suction maintained at the hoods.. Where possible the resistance of the particular collector to be used should be obtained from the manufacturer. . Table 8. Loss: Through 90:Deg Elbows . . . Elbow.Center Line Radius in Per Cent . of Pipe Diameter or Depth ' ' ., : 50 100 150 200-300 .. Loss. Approximate in. Per-Cent . . ' of Velocity Head ' . ,.... .. . .. . 2756.: . " 17: ' ' 14 .. :: 848 CHAPTER 46 r 1946 Guide Table 9. Corrosion Resisting Materials for Exhaust Systems1 MATERIAL . .Mbtaia ACIDb Acetic Chromic Htoro , . HtoroCHLORIC* FLUORIC . Nitric Phos. PHOBIC Sul phurous Sul phuric Dli|Cone. Dil.|Conc. Dil.| Cone. DiL Cone. Dil. Cone. Dil.|Cone: Dii-jConc. Dil.jConc. Aluminum..___ Good Fair Poor No Data Poor Good Poor Poor Poor Magnesium and Alloys-- No Data Good | Poor No Data Poorj Good No Data.. No Data ; No Data No Date Lead and Lead-Coated__ Poor Good Poor Poor Poor * Poor Good GoodJPoor Moly Alloy (60 Ni--2QMo -20 FeU - Good No Data Fair No Data Poor Poor Monel Metal__ Fair Poor Fairj Poor Goodd Fairj Poor Fair No Data - Good Poor GoodejPoor Bronze___ - ' Poor Good Sifioon Iron___ Fair |Good No Data Stainless Steele (18 Cr8 Ni) . . Good - Good Enameled Steel_________ No Data No Data MtSCELLANEOUB Asbestos Comp Fair Poor - Good Good Poor' Good No'Data Poor Good Good Poor Poor Good except against strong acids and alkalies No Date Good PooJcoode Good No Date Good Wood Some woods are decomposed or softened faster than others. Rubber. - . | | | | Poo.' | . - | . Poor In general plastics resist weak adds and are decomposed by concentrated acid. ' ^Standard Practice Sheet No. 115 (Division of Industrial Hygiene, New York State Labor Department). bAdd mists in air are more corrosive than as liquid in storage tank. Galvanized iron not resistant to acid. . .' .. .. cstainless steel of (24 Cr--10 Ni) fairly resistant at low temperature for HCl and Ht POt. dUnder most conditions. ' CAt room temperatures. . Friction drop in the pipes must be computed for each section wherethere is a change in area or in velocity. The velocities should be found in each section of pipe starting with the' branch most remote from the fan.. The friction drop for these sections can' be determined by reference to Table 8 in this chapter and Fig. 2, Chapter 41. Total friction loss in the : piping system is the friction drop in the most remote branch plus the drop in the various sections of the main, plus the drop in the discharge pipe. EFFICIENCY OF EXHAUST SYSTEMS The efficiency of an exhaust system depends upon its effectiveness in reducing the concentration of dusts, fumes, vapors and gases below the safe or threshold limits u. .' ' Too much emphasis cannot be placed on the necessity of testing exhaust systems frequently by determining the concentration of atmospheric con tamination at the worker's breathing level 16. Commonly accepted values of threshold limits for usual atmospheric contaminants will be found in Tables 3, 4 and 5, Chapter 10. ' AIR FLOW PRODUCING EQUIPMENT In any type of exhaust system some form of air flow producing equip ment should be required to create the pressure necessary .to cause the air Exhausting and Conveying Systems 849 to flow through the system to the discharge stack. Natural draft should not be depended on to remove harmful or dangerous gases, fumes, mists, dusts, or other matter when it is imperative that such matter be removed from the work place or room atmosphere. The principal types of air moving equipment are chimney exhausts, venturi ejectors, centrifugal exhaust fans, disc or propeller fans, and axial flow fans16. '. Manufacturers generally provide special fans for the collection of various industrial wastes. These are available for the collection of coal dust, wood shavings, wool, cotton and many other substances. When substances haying ah abrasive character are conveyed, the fan blades and housing should be protected from wear. This may be accomplished by placing a collector on the negative side of the fan or by lining the housing and blades with rubber. PROTECTION AGAINST CORROSION The removal of gases and fumes in many chemical plants requires that metals used in the construction of the exhaust system be resistant to chemical corrosion. A list of the materials which- may be used to resist the action of certain fumes is given in Table 9. Hoods and ducts, when short, may frequently be constructed of wood and be quite effective! Rubberized paints are available and may be applied as protective coatings in handling such gases and fumes as chlorine and hydrochloric acid. . REFERENCES Tentative Recommended Good Practice Code and Handbook on the Fundamentals of Design, Con struction, Operation and Maintenance of Exhaust Systems. Page 21, Industrial Hygiene Codes Committee, American Foundrymen's Association. . 2--How to Design Exhaust Hoods, by J. `M. DallaValle (Heating and Ventilating, Series of 12 articles March, 1943 to February. 1944). ' 3-- Industrial Exhaust Ventilation in Industrial Hygiene, by Allen D. Brandt (A.S.H.V.E. Trans actions, Vol. 50, 1944, p. 331). ' ' . *--For more detailed requirements refer to Fundamentals Relating to the Design and Operation of Exhaust Systems, Z9-1936 (American Standards Association). Industrial Code-Bulletin Nos. 10 qnrj 12 (New York State Labor Department). Principals of Exhaust Hood Design, by J. M. DallaValle (U. S. Public Health Service, 1939). ' ' 5--Control of the Silicosis Hazard in the Hard Rock Industries. I. A Laboratory Study of the Design of Dust Control Systems for Use with Pneumatic Granite Cutting Tools, by Theodore Hatch, Philip Drinker and Sarah P. Choate. (Journal of Industrial Hygiene, Vol. XII, No. 3, March, 1930). --The Control of -Industrial Dust, by J. M. DallaValle (Mechanical Engineering, Vol. 55,- No. 10, October, 1933). - ' 7--Studies in the Design of Local Exhaust Hoods, by J. M. DallaValle and Theodore Hatch'(A.5.Af.E. Transactions. Vol. 54, 1932). *--Velocity Characteristics of Hoods under Suction, by J. M. DallaValle (A.S.H-.V.E. Transactions, Vol. 38, 1932, p. 387). Low Velocity Exhaust Systems, by Theodore Hatch (Heating and Ventilating, October, 1940, p. 27). ,0--Tank Ventilating Power Costs Cut by Low Velocity Systems, by William B. Harris (Heating and Ventilating, July, 1942, p. 42). 11' Health Hazards in Chromium Plating, by J. J. Bloomfield and William Blum (U. S. Public Health Report, Vol. 43, No. 26, September 7, 1928). 1 *--New Data for Practical Design of Ventilation for Electroplating, by W. P. Battista, Theodore Hatch and Leonard Greenburg (Heating, Piping and Air Conditioning, February. 1941, p. 81). Ventilation of' Plating Tanks, by Allen D. Brandt (Healing, Piping and Air Conditioning, July, 1941, p. 434). 1^3^3~The National Silicosis Conference Report (Bulletin No. is, U. S. Department of Labor, February 3, ,4--Criteria for Industrial Exhaust Systems, by J. J. Bloomfield (A.S.H.V.E. Transactions, Voi. 40, 1934, p. 353). . - -- . ^--Keeping.Dust.Under Control, by John M. Kane (presented to the 31st National Safety Congress. October 23, 1942, and reprinted in part in National Safety News, January. 1943). The Determination and Control of Industrial Dust, by J. j. Bloomfield and J. M. DallaValle (Public Health Bulletin 17, 1935). Engineering Control of Air Contamination of the Working Environment, by A. D. Brandt (In Manual of Industrial Hygiene,.!/. S. Public Health Service, 1943. p. 198-266). / - . *--The Axial Flow Fan and Its Place in Ventilation, by W. R. Heath and A. E. Criqui (A.S.H.V.E. Transactions, Vol. 50, 1944, p, 197), CHAPTER 47 oZ)^(`n^ Systems Drying Methods, Radiant-Heat Drying, Conduction or Direct Contact Drying, Convection , or Air Drying, Mechanism of Drying, Omissions in the Cycle, General Rules for Drying, Dryer Calculations, Humidity Chart, Design, Estimating ' Methods . DRYING, in its broader sense, refers to the removal of water, or other volatile liquid from either a gaseous, liquid, or solid material. In practice, the process of direct, drying gaseous material is referred to generally as dehumidifying, or condensing, and in.some cases chemicals are used in the adsorption or absorption of moisture. The subject of dehumidification is treated in Chapter 38. Drying a liquid is called evaporation or distillation. The common usage of the word drying refers to the removal of water or other liquid, such as a solvent, by evaporation from a solid material. When the solid to be dried contains large amounts of free water, the actual drying process is frequently preceded by the removal of part of the - water by some mechanical means, such as filtration, settling, pressing or centrifuging. Removal of as much water as possible by such methods is usually advisable, as the cost of these operations, per pound of water removed, is generally much less than by evaporation. In some drying processes the evaporation of the liquid is accompanied by a chemical change, as in the drying of paint and varnish. ' DRYING METHODS Heat must be supplied in order to dry a solid by evaporation. Since this latent heat is large compared with the specific heat of the materials, drying becomes largely a problem in heat transfer. Hence drying methods are often classified according to the method of heat transfer used, as follows: '. 1. Radiant-heat drying. . 2. Drying by direct contact, and conduction: 3. Convection or air drying. .- .. '' Radiant-Heat Drying . .. Drying by sun heat is still practiced where danger of rain is slight, . atmospheric pollution is. negligible, and sufficient time can be allowed. Radiating surfaces, (heated by steam, electricity or other means), afford a good method of heat distribution and control. Radiant heating sets up convection currents, and in low-temperature dryers only about one-third to one-half of the total heat for evaporation is'actually supplied to the material by radiation. At high temperatures the radiation output , in creases rapidly, according to thz fourth-power law. The total radiation may be computed by the equations and. tables given in Chapter 5. In general, fins and irregular surfaces do not increase radiation, hence the area to be used in calculations' is the area of a smooth-surface envelope enclosing the radiating elements.- . A certain amount of air circulation is required through a radiant dryer, in order to carry off the vapor. - :: 850 Drying Systems_______________' , ''' ~ " 851 Conduction or Direct Contact Drying Drying rolls or drums, flat surfaces, open kettles and immersion heaters are examples of' the direct-contact method: Intimate contact of the material with the heating surface is important, and in some cases agitation is desirable to increase the uniformity of heating or to prevent overheating. Greatest resistance to heat transfer occurs on the air side of the material being dried. The rate of heat transfer from the surface of the heated material to the air, and hence the rate of drying, may be increased by: (a) forced convection or air circulation; and (b) vacuum operation to lower the boiling point of the liquid being evaporated. '. . . Convection or Air Drying .' The circulation of heated air or other gases over the material being dried is termed convection drying. Some convection drying occurs in practically all types of dryers, but if the main source of heat is from the air or gases, the dryer may. be called a convection dryer. Typical forms or examples may be enumerated: .' . :. 1. Rotary drum dryers, (Fig. 1). : . .. ' 2. Tunnel or oven dryers, batch type. 3. Tunnel dryers, conveyor type, (Figs. 3 and 4). 4. Tower or column dryers. 5. Through-circulation dryers; (Fig. 2). . . ... '. . ,. In any type of convection dryer the heat transfer and hence the drying- depends primarily upon the surface area of material exposed to the air and the velocity of the air over the surfaces (see . Dryer .Calculations, later). . J A general classification of several types of dryers is given in Table 1. The chief basis of classification in this table is that of intermittent or batch operation as opposed to continuous operation. Another important basis of classification would be the method of handling the material to be dried. In an effort to secure maximum contact of the air with the prod uct,. as well as uniformity of heating, the effectiveness of cascading the material in an inclined drum or of blowing heated air through a bed of granular or pre-formed material is at once apparent, and where con tinuous drying at high capacity is required, these types are preferred.- Extensive experimental studies on both types, are available, (see References). ' . . .. 8S2 CHAPTER 47' : 1946 Guide Simple drying ovens are often used for drying smaller quantities of material. The heat and humidity supply for low temperature work up to 250 F is often steam; steam coils, either in the oven or outside, heat the air used for drying. Circulation of heated oil is used to a limited extent, but the danger of leaks is serious, for if the oil is hotter than the flash point, a fire may start if the oil is released to the atmosphere. In many cases where steam is not available, direct or indirect-fired heaters are used with gas or oil as fuel. Indirect heaters should be carefully selected from a standpoint of long life and efficiency. The heat exchange surface should be adequate in area and easily accessible for cleaning and removal. For extremely high temperatures, alloy surface may be used. With- direct-fired equip ment care must be used in the selection of burners and sufficient com bustion space allowed to insure complete combustion of fuel. Humidity can be obtained in dryers by the use of steam spray, humidifiers, or recirculation. For low temperature work up to 200 F ovens and dryers are commonly built of two thicknesses of insulating board (fireproof preferred), with air space between. As the temperature increases, materials better able to withstand the heat must be used. Metal lined ovens are easy to keep clean, and many high temperature dryers up to 1000 F are made of metal panels with insulation between. Care should be taken to avoid through metal (metal extending through the oven wall from inside to out). Batch type ovens are entirely closed while in use and control of air leakage is easily taken care of. In the continuous dryer where the ends are open, heat and air leakage becomes important. Warm air leaking out of the ends of ovens means a heat loss, and often the, temperature and humidity outside the oven becomes unbearable. For this reason, inclined or bottom entry ovens are used, as the warm air leakage can be more easily con trolled. See Figs. 3 and 4. MECHANISM OF DRYING The modern theory of drying may be summed up as follows: Assuming uniform velocity and distribution of air at a constant temperature and humidity over the surface to be dried, the drying cycle will be divided into two distinct stages: 1. Constant rate period. 2. Falling rate period, ', The constant rate period occurs while the material being dried is still very wet, and continues as long as the water in the material comes to the T a b l e 1. D r y e r s fo r E v a p o r a t io n of W a te r Batch or Interm i W here m a te ria l comes in sheets or rolls, and w ill stand direct contact w ith heating surface Drying Systems 1 g i 0 CO H 2 M IS! 650 si Ss3 1 80 to Steam 1 C o ils , A ir, | 180 E le c tric ity 1 W hen production does n o t w ar rant continuous drier 100 W a te r, Steam to Jacketed, m ay have W here duBt must be saved 330 Vacuum on top \ 80 to 300 100 to 350 W ater, Cost of operation high, Steam fo r expensive m aterials i i Steam Coils, A ir, E lectricity, P roducts, F or high production of,, Combustion A ir, Steam, Products of C o m b u s tio n W here m aterial w ill stand rough handling and is not subject to balling dp 8S o2 ' Steam, may have Vacuum on Top Hygroscopic m aterials dried | w ith vacuum, and packed im m ediately , to Steam inside ' 350 of D rum C ontinuous Sheets, Endless Chain B elt Flowed on D rum , . D ry M aterial . Scraped off Cascades through Truck, ' Tray, B elt . Chemicals, Explosives, P har- T ra y , Basket, 1 maceuticals, Food Products | T u m b lin g D rum . D rum or Pan Paper, T e x tile s , C h e m ic a ls L iq u id s , , '' j Slurries Chemicals too sticky for Shoveled in to 1 Suspended, T ruck, Rotary B ulk Ceramics, Chemicals, Tunnel ' Lum ber, . Food Products- R otary D rier ' Yarns, Lum ber, Foodstuffs T ray Paper, Leather, Sfi an SH g3 C ylinder Vacuum A g ita te d Com partm ent .g c4) a. D ru m ! '" at . . 3O' - - ' .2 eo Festoon Paper,' C h e m ic a ls C ontinuous Sheets, Suspended on . I M e ta l Screens to 200 A ir, _. ' W here one side cannot come in contact w ith supports u n til dry Steam Coils Tow er or G rains, . Falls through by G ravity 125 to A ir, 250 Steam Coils W here headroom is available Colum n Sand Spray Solutions over 30% Solids . Sprayed into 120 to A ir, P roducts of D ry in g is alm ost instantaneous .- Chamber 350 Combustion . Induction M etals, for removal of ` traces of W ater ' Placed in H igh Frequency Field , to 400 E lectricity W here heating of metal from in side o u t is im p o rta n t - 853 . 854 CHAPTER 47 ' 1946 Guide. surface so rapidly that the surface remains thoroughly wet, and evaporaJ . tion proceeds at a constant rate, precisely as from a free water surface. The material tends ito assume a temperature corresponding to the wet- bulb temperature of. the surrounding air. But the actual temperature is -. often slightly higher, due to radiation and conduction from dry surfaces . adjoining the material. The constant rate period continues until a time is reached when the moisture no longer comes to the surface as fast as it is evaporated. This point is called the critical moisture content in the drying process. :. . As the drying proceeds, a period .of uniform jailing rate is entered. During this period, the surface of the material is gradually.drying out, and the rate of drying falls as the remaining wet surface decreases in area. This period is also known as unsaturated surface drying. , . 'Asdrying continues, the surface is completely dry and. the water from . the interior evaporates and comes through the surface as vapor. As the plane of water recedes, the diffusion of the vapor becomes more difficult and hence the period is known as varying falling rate period, of sub-surface drying. '' Drying ceases when the equilibrium moisture content has been reached. , The final moisture content of the-product depends on the relative humidity of the air in contact with it. Equilibrium is established when the vapor pressure of the moisture in the air and the vapor pressure of the moisture in the material are equal. The equilibrium moisture content varies with the hygroscopic properties of the material, (see-table of Regain of Hygro scopic Materials, Chapter 45). . The drying of a slab of whiting is shown in Fig. 5 and illustrates the principles referred to previously. The factors affecting the variations of drying rates during the periods mentioned are outlined in Table 2. .Omissions in the Cycle ' : Many solids, such as lumber, are so dry at the beginning of the drying operation that the constant rate period of free surface, evaporation does not occur. Frequently the surface of the material is dry enough so that no surface drying can take place, in which case only the final stage of sub surface drying is involved. In other instances, the critical moisture con- Drying Systems 855 tent of a wet solid is sufficiently low.that sub-surface drying starts almost immediately, after the conclusion of-.the constant rate period. Thus the intermediate state of unsaturated surface drying does not occur and the drying is of the sub-surface type during practically the whole of the falling rate period. With other kinds of material, particularly thin sheets, such as newsprint paper, sub-surface drying may occur at such a low moisture content that it . is not encountered in commercial work, the falling rate period being confined in practice to unsaturated surface drying, . Table 2. Factors Influencing Drying Factor. , . - Drying Period > Constant Rate, Unsaturated Surface . .. Sub-Surface .' Temperature Increase in temperature increases drying rate .. Increase in temperature in creases drying rate, . because with decreased viscosity, capil lary flow is increased. ' Humidity ' Drying rate increases as humidity is decreased. : No effect until equilibrium con tent is reached; drying then ceases ' Air Velocity Drying rate varies approximately as the 0.6 power of the velocity No effect . . Air Direction Drying rate increases,; the, more nearly the air blows perpendicular, to surface; for dead air film becomes thinner . ' ' No effect ... '. Thickness of Drying rate is not affected by. the Drying rate varies inversely as Material . thickness v , , , , :t . the square of the thickness , GENERAL RULES FOR DRYING Temperature The highest temperature possible should be used because of faster drying and smaller requirements for ventilation. The amount of moisture that can be carried by- a pound of air increases rapidly with rise in tem perature as shown in the humidity chart of Fig.' 6. Too high a tempera ture 'may cause spoilage of materials; many materials calcine or change their chemical properties if heated too.hot; gypsum and glauber salts lose some of the chemically combined water, fall'apart, and change their chemical properties. Too high or rapid rise in temperatures in drying lumber oil ceramics may create'a liquid vapor tension within the material so high that the cells explode; causing permanent-injury to the fiber. If too high a temperature, is used on some chemicals, they, begin to react exothermally; a temperature, rise and chemical action from within; will 'burn the materials, e.g., bakelite products, gunpowder, etc. . During-the constant rate period of drying, the; material heats only to the wet-bulb temperature of the surrounding air, consequently; high temperatures will not injure die material in this stage. ., r. .. ,. > ' Humidity " ` '- .. Moisture in the drying air may be very iinportahtf-'- Many-' materials tend to case-harden,dry on the outside, forming/a skin which retards the moisture flow from/the inside to:the surface, or stops it completely, and so 856 CHAPTER 47 1946 Guide increases the drying time very much or causes a change of the physical properties of the material. It is often necessary to add humidity to the air in the initial stage of drying. Lumber case-hardens, cracks, and warps if the outside is dried too fast. Ceramics crack if not heated through before drying commences. . Elastic materials warp or crack if not even ly dried. Many paints,case-harden if not dried.under high humidity. On the other hand, in the case of those materials whose physical or chemical properties require' that they be dried at relatively low tem peratures, high humidity tends to retard drying in the first stage and may even stop it altogether in the final stage. Where drying temperatures below42Q to 140 F are used, the drying rate may be highly dependent on atmospheric humidity conditions. In such instances it is often desirable to deKumidify the air entering the dryer during periods of high atmos pheric humidity; where a high degree of uniformity is required, it is often possible to secure complete independence of atmospheric conditions by recirculating the air in a closed system which includes a suitable dehu midifier. For this purpose absorptive dehumidifying systems have the advantage of accomplishing the desired reduction of humidity without appreciably elevating or lowering the dry-bulb temperature of the air; for this reason after-cooling is not required, and reheating is reduced to a -minimum. Dehumidifying systems are described in Chapter 38. Air Circulation ' As noted under Mechanism of -Drying, air velocity is more important in the first two stages of drying than in the last, and for this reason zone drying in continuous dryers is frequently considered. It permits accurate regulation of temperature, humidity, and velocity in the different zones. High velocity results in more rapid drying, more even distribution of temperature and consequently more even drying in the first period. Too high a velocity may be detrimental because of excessive power needed for creating it, or because the material may blow away if it is light and fluffy. In the drying of paints, varnishes, and enamels, high velocity or improper distribution of the air, even with theuse of filters, may cause dust already in the dryer to be blown against the material, ruining the finish. DRYER CALCULATIONS The fundamental calculations for the design and performance of dryers are based on the thermodynamics of air and water mixtures treated in Chapter. 3," and the fundamentals of heat transfer treated in Chapter 5. For the humidity calculations a high-temperature psychrometric chart is given in Fig. 6. In addition to the fundamental Heat transfer calculations of radiation, conduction and convection, the heat losses through the walls of the dryer will be computed by. the methods illustrated in Chapter 6 and Chapter 41. Data on radiation calculations are given in Chapter 31. Where products of combustion are used directly in a dryer, a knowledge of the properties of fuels and combustion products is important. Data on fuels and combustion are given in Chapter 16. For determining the heat available in products of combustion,1 a specific heat of 0.25 Btu per (pound) (Fahrenheit degree) may be used. ' - The calculations for drying during the constant-rate period are different from those applying to the falling-rate period. Constant-Rate Period The rate of drying by air passing over a wet surface is directly pro portional to the vapor pressure difference, and also proportional to the HUMID HEAT. Btu PER DEG F 0RY * * Drying Systems s d31VM ai aid n)9 857 I 858 CHAPTER 47 11946 }Guide 0.8 power of the air velocity. For practical calculations the wet surface is assumed to attain the wet-bulb temperature of the air passing over it, and evaporation takes place at constant rate under equilibrium condi tions.- The equation may then be expressed in three forms: R = CA (AP) ' (1) . - R = C'A FM (AH) . (2) R - C" A V -8 (AD , (3) where . ` R = rate of. drying during constant-rate period, pounds of moisture per hour. A -- area of bed or material in contact with air, square feet. V = air velocity over material, feet per minute. ` ', AP = difference between vapor pressure at wet-bulb (surface) temperature and at dew-point of air.. AH -- difference between humidity ratio of saturated air, at. the surface ' temperature, and the actual humidity ratio of the air stream, pounds of water per pound of dry air. * AT = difference between.dry-bulb and wet-bulb temperatures of air, i.e., the . . wet-bulb depression. - C, C1, C" = proportionality constants (for numerical.values consult references). ,, * '. ' .. ' - t These equations are useful mainly for computing die effects of changes in operating conditions, such as changes in air velocity, air temperature, humidity and surface area. The equations assume that the material is in . equilibrium at the wet-bulb temperature of the air. If equilibrium has { ; not been reached, or if heat is being added to the charge by radiation, or conduction, such conditions must be taken into account. For large tray .dryers or continuous surfaces, the logarithmic mean difference should be substituted for the simple difference in AP, AH and A TV ' When the constant of proportionality is known for a given set of con ditions, Equations 1, 2 or 3 may be applied for basic design, as illustrated in Example 1. ' Example 1. Compute the rate of drying, of a granular material initially 35.per cent moisture (dry basis), if the material is spread iii trays and is to be dried by blowing air .. horizontally over the surface at 1000 fpm. .The air is 140 F dry-bulb, 90 F wet-bulb. ` Density of the dry material is 85 lb per cubic foot, and the drying constant C", in Equation 3, has been found to be about 1/25,0001' Find the size of dryer for a capacity of one ton per hour (dry basis), and the time required for drying each batch from 35 to 10 per cent moisture content, if the.material is spread in trays,.in a layer one inch thick, (The critical moisture content of the material is below 10 per cent, hence the drying is at constant rate.) - . ... Solution: Assume that the surface of the material attains the wet-bulb temperature of the air, then AT = 140 ---90 -- 50 F. The rate of drying by Equation 3 is: . R = C" A V"0-8 AT = nnn^ =0.50 lb of water per (hour) (square foot of surface). The total water evaporated per square foot of surface is: ' : W = 4s- (0.35=- 0.10) = 1.771b (per batch): . . \Z / - Then the time required per batch is: ' - ' ' \ r = oil - 3:54 f,r' ' " ' * ' The size of dryer required to dry the material at the rate of one ton of dried material per operating hour will be: . A = 2000 X 3.54 = 1000 sq ft, total area of trays. 85/12 Drying Systems . *59 Falling-Rate Period . -. The critical moisture content marks the end of the constant-rate period and the beginning of the falling-rate period. This falling rate may be due to the fact that the surface is no longer completely wetted, or it may result from a condition in which the moisture cannot reach the surface as fast as-it can be evaporated.. When this high resistance to capillary flow and diffusion is the governing, factor in the drying process, the time of drying increases rapidly with the thickness of the material. During constant- rate drying the time required is directly proportional to the. thickness of the bed (see Example 1), while the time required for drying during the falling-rate period is often proportional to the square of the thickness of the material. ... Actual calculations of drying during the falling-rate period are not highly satisfactory because of the number of variables. It has been demonstrated empirically that the rate of drying is approximately pro portional to the free water content of the material. An approximate value of the critical moisture content which marks the beginning of the falling-rate period may be obtained from Table 3.. Table 3. Critical Moisture Contejtt for Various Materials3 . Material - .* Critical Moisture " Content. Per Cent '. 3 to 20 . ` 30 to 40 60 to 70 75 to 150 90 to 120 aThe critical moisture content is expressed as weight of water in per cent of weight of dry material. DESIGN In ..all drying problems, data regarding temperatures, time, and hu midity must be obtained by experiment or previous experience. Experi ments are best performed at the actual temperatures, humidities, and velocities to be used in the full sized dryer, and.with full size samples. The following nomenclature and explanation of terms will be used in the discussion of design calculations: ....... H = humidity ratio of air, pounds of water vapor per pound of dry air. G = pounds of dry air supplied to the dryer per unit of time. ' 5 = pounds of stock dried per unit of time' in a continuous dryer. 51 = pounds of stock charged per batch to a discontinuous dryer. 0 = time. . ' Q = total heat supplied to the dryer. , . t = air temperature. . . t' = stock temperature. <" = average stock temperature over short time interval, in a batch dryer. /,v = wet-bulb temperature. s' = specific heat of the stock. ' B = total radiation and conduction losses per unit time. w = pounds of water per pound of dry stock. ' 860 CHAPTER 47 1946 Guide r =s heat of evaporation of water. .` s * humid heat of air, i.e., heat necessary to raise 1 lb of dry air 4* H lb of steam `-IF. ' Subscript (1) designates conditions at the point where the material in question (air or stock) enters, and (2) where it leaves the dryer. Air dryers may be divided into two classes, those in which all moisture evaporated from the stock leaves the dryer as vapor in the effluent air, and those in which part or all of the moisture is condensed from the air in the drying equipment itself. In any continuously operating dryer of the first type the relation between moisture content of the stock.and quantity of air required for the drying operation is given by the equation: " G (H, - Hi) = SO, - wO (4) In discontinuous dryers, e.g., compartment dryers, the drying operation is given by the equation: .. . ' G (H, - H.) - S' 11 (4a) In the continuous dryer, the heat consumption per unit time is: - = Gntf. - h) + G(r, +\- ft) (ff, - Hi) + S(ft - t'i) (s' +wi) + B (5) Equation 5 assumes continuity of operation. For charge or batch operations, the total time of the drying cycle may be broken up into a number of periods, sufficiently short so that over each period average values of t, i' and H may be employed provided the third term of the right hand member of the equation is modified to read: . S< (<", - <",) (s' - wi) and in the second term f'* be replaced by .. . . .. - '2 Theoretically these periods should be very short and the equation integrated. Practically, the error introduced by using a small number of long periods and employing average values of the variables over- each is not serious. The evaluation of Equation 4a may be approximated in a similar manner. .. The first term of the right hand member of Equation 5 represents heat lost as sensible heat in the effluent air. In many drying operations this becomes excessive. Each pound of air supplied should remove the maxi mum amount of moisture. This is best accomplished by bringing the air into contact with the stock with sufficient intimacy so that the air leaving the dryer is saturated, or nearly so. Counter-current as against parallel flow of air and stock gives rise to optimum operating conditions, resulting in a minimum quantity of air required (G), and a corresponding minimum loss, as sensible heat, in the exit air. Similarly, continuous operation is superior to intermittent.operation. . . ' ' Despite the fact that the sensible heat loss increases with the rise in temperature of the air, the percentage of heat lost from this source decreases, provided the increase in moisture carrying capacity of the air, due to high temperature, is actually utilized. To secure maximum thermal efficiency in drying, a high drying temperature and high satura- ' tion of the outlet air are imperative. - . . Drying Systems 861 Ventilation Phase .. ', The technique of attack of the ventilation phase of a drying problem is best made clear by an illustration. Assume that a material containing 40 per cent moisture is to be dried until this quantity of moisture is reduced to 5 per cent by weight. The material will stand an air tempera ture of 150 F and it is possible to provide sufficiently good contact between the material and the drying air so that the effluent air can be brought up to 50 per cent humidity at 150 F. The dryer is to use room air, the temperature and humidity of which may be assumed to average 70 F and 50 per cent. A counter-current'dryer will be employed and the air in this dryer will be kept at a substantially constant temperature of 150 F by heaters thermostatically controlled. The stock enters at 70 F, rises quickly to the wet-bulb temperature of the air, with which it is in contact, and, as has been found experimentally, remains at this wet-bulb temperature until the moisture content has fallen to 20 per cent. From this point its temperature rises progressively as it dries. In this range H< 00234. 0008 Hi . ' W* 0.150 W;.QQ687 W2-0.0527 W-P0UNDS OF WATER PER POUND DRY STOCK Fig. 7. Temperature Humidity Relations in a Dryer the difference in temperature between stock and air, divided by the wetbulb depression, may be assumed proportional to the moisture content. The moisture content of the entering stock, in the units here employed, is: . .. 40 per cent water _ ^ fjggy. w =< 5 per cent water 60 per cent dry stock ' ' Wl 95 per cent dry stock 0.0527 to, -- , = A w = 0.614 lb water evaporated per pound of dry stock. Since the air leaving the dryer is 50 per cent saturated at 150 F from Fig. 6, //, = 0.105. Similarly,. Hi = 0.008, corresponding to 50 per cent humidity at 70 F. Consequently H, -- Hi = A 7/ = 0.097 lb water evaporated per pound dry air. . An analysis of Equation 4 shows that (H) is linear in w. Hence, one can construct on Fig. 7, the line marked (H) being drawn connecting the initial and final points just computed. Since the air leaving the dryer has a temperature of 150 F and a humidity of 0.105, Fig. 6 shows that its wet-bulb temperature is 129 F. This is plotted at the right hand side of Fig. 7. Since the stock maintains a wet-bulb temperature down to 20 per cent moisture, where w = 0.25, the corresponding humidity can be computed by the use of Equation 4 or by reading directly from the diagram, the value being 0.0392. Fig.-6 shows that the corresponding wet-bulb temperature is. 105 F. Any y 862 CHAPTER 47 1946. Guide intermediate point on the wet-bulb temperature curve can be calculated similarly. The points for w = 0.5 are shown in Fig. 7. . . Below the point, w = 0.25, the temperature of the stock begins to rise appreciably above the wet-bulb temperature. Its temperature at any given point in this range, for example at w = 0.15, may be computed as follows: At this point, H = 0.0234 (from Equation 4) and from Fig. 6, The assumption made regarding the relation between stock temperature and moisture.content in this.range may.be formulated: . '^ w . < -- fa, = 0.25 . At the point w = 0.15, At' = 33 F, t' = 117 F. The temperature of the stock leaving the dryer, similarly computed, is 136 F.. Fig. 7 thus computed gives in graphical form the information as to the temperature humidity relationships in the dryer. The air requirements can be computed by Equation 4. Thus, per 100 lb of dry stock, it is necessary to supply 633 lb of dry air. Furthermore, since from Fig. 6 it is seen that the volume of 50 per cent saturated air at 70 F is 13.55 cu ft per pound, 8580 cu ft of room air must be supplied per 100 lb dry stock. Similarly, since the volume of 50 per cent saturated air at 150 F is 18.0 cu ft per pound, the volume of hot wet air discharged from the dryer, is Vent 33J ptf cent St 422 F . / Rccirculetion 66$ per cent 2Tj( at 422 F-V lb IS 1b product of perfect combustion per pound fuel ~o- Excess eir for combustion XU)*t70F Fig. 9. Core Drying Diagram of Combustion Products and Air 11,400-cu ft per 100 lb of dry stock. Finally, the heat required for the dryer, as a whole or to any section of it, may be computed from Equation 5. High Temperature Dryer ." , . , In the design of a high temperature dryer unit a method of approach to the necessary calculations involved is outlined as follows: *' . Example 2. Cores 4 and 5 in. thick are to be dried by heating to a temperature at .400 F. An intermittent type box oven is to be used, size 12 x 14 x10 ft with 856 sq ft surface, Having an average heat transfer of 0.3 Btu per (square foot) (degree) (hour). Drying Systems 863,. Drying time as determined by test is 2 hr (Fig. 8). Cores weighing 6 tons, and 15-ton , steel plates, trucks etc. are delivered to the dryer at 70F. The oven is heated by an external heater; the products of combustion and 66% per cent recirculated air will be delivered to the oven at 825 F. The fuel oil used has 19,980 Btu gross and 18,830 Btu per pound net heating value, weighing 6.75 lb per gallon and having 15 lb product per pound fuel for perfect combustion. Cores consist of 91 per cent saind, 3 per cent oil binder, and 6 per cent water. -( . ' Solution. Heat required per ton of cores: .. ; . Lb Material X Temp. Rise X Sp. Ht. = Btu Sand_________________ LI___ 0.91 X 2,000 X (400 - 70) X 0.2 = 120,120 Binder.,, 0.03 X 2,000 X (400 - 70) X 0.4 = 7,920 Water heatingTM::__________ 0.06. X 2,000 X (212 - 70) X 1.0 = 17,040 Water evaporation___. 0.06 X 2,000 X 970 (Fig. 6) = 116,520 Water superheating (approx. 50 per cent reaches 575 F) . = 0.5 X 0.06 X 2,000 X (575 - 212) X 0.45 = 9,800 Total Heat.___________ ___ _____________________ _" 271,400 Btu Heat in 1 lb fuel oil Heater Loss (10 per cent) Duct Loss (5 per cent) . . = - : 18,830 Btu = 1883 . = 942 . 2,825 Btu . Btu available to heat oven 16,005 Btu Heat content of gases in 1 lb fuel oil at 825 F is 205 Btu Sensible heat in.products of perfect combustion = (151b +205) = 3,075 Btu Btu to heat air X and Y (Fig. 9). . . '= 12,930 Btu Y {Sm - Sm) + X (Sm - S,,) = 12,930 ' K = 2 (X. + 15) for 66.7 per cent recirculation (6) where ................ ... 5 = heat content of air at temperature noted taken from Fig. 6'. - ' (Recirculation and exhaust contain water vapor, products of combustion, and a greater portion of air. Heat capacities of all-vary so little that-they have all been, assumed to be air). , . ' Sets -- Sta = 190 -- 91 = 99- . . , . . . ^ Sm - Sn =,190 ^ 8.6 = 181.4.\ , . Substituting values of Y, H, etc. in Equation 6, (2 X + 30) 99 + 181.4 X `= 12,930 ; V * - > ' - >: - - X -- 26.3 lb excess air. . Y = 82.6 lb.recirculating air. . ...' .. `; , ' Total' = 26.3 + 82.6 + 15 .= 123.9 Ib.air and products of combustion circulated per pound fuel burned. ` . . . : ;j ... . . . Heat in air exhausted from oven. at< 422 F per: pound fuel burned = 0.333 X 123.9 X (543 -.Sio) =41.3 (91 - 8.6) ` = (3,400,6^.!. ... ... Btii available for heating,material = 46,005--- 3,400.*. 12,605 Btu per pound fuel. Fuel used in-first hour ='2,180,470 '+'12,605 '.= ,173 lb == 25.6 gal .. .. ' . During the second8 hour the heater capacity will be much greater than required. If an automatic oven temperature control operates on the oil supply, the delivery tem perature of the air entering the oven and the quantity of oil Burned will 'decrease, the air supply being constant. '. Heat in air exhausted = 41.3 (S6 " 'S7c).: = .41".3C(127 -- 8.6) = 4,880 Btu per pound fuel. , .. , h ' Heat available fbr'heatihg material = 16,OOo --"4;880 = 11,125 Btu! ;; Fuel used.in second hour'.=. 1,072,008.+ 11,125.= 96.51b.oil ==;14;3 gal. . ' ;v Total oil. used per load = 25.6 + 14.3 = 39.9 gal. (. ' 864______________ CTI'APTER 47 _________ ____ 1946 Guide Heating Load First Hour ' Heated to Sand. .............................. 212 F .Water._________ _____ _______ Evaporation__ _____________ 212 F 212 F 66.7% 66.7% H| X 120,120 X 0.667 X 0.667 X 7,920 . 116,520 9,800 Bto = 51,688 = 3,408 = 17,040 = 77,680 = 6,530 Total Per Ton.................. ................ _______ _L-................................. ......................... _____ 156,346 For 6 ton__ 1._____ Steel plates Radiationb......... 390 F . 422 F Avg 6 X 156,346 ' 320 X 30,000 X 0:i2 352 X 856 X 0.30 = 938,076 = 1,152,000 = 90.394 TotaL______ ............... ............... .............................................. ........................... I..._____ 2,180,470 Sand___ ;___ Binder........ Water._____ : Evaporation Superheat.... Heating Load Second Hour 400 F 1550 ' 3fxi20,120 - - = 400 F 33.3% 33.3% 330 xX 7/,y92^0U 0.333 X 116,520 0:333 X .9,800 = 68,432 4,512 38,840 3.270 Total Per Ton____________ _______ _:______________________ _______________________ 115,054 For 6 ton___________________ Steel plates............................... Radiationb............................... 460 575 . 6 X 115,054 70 X 30,000 X 0.12 505 X 856 X 0.30 = 690,324 = 252,000 = . 129,684 TotaL--_______________________________________________________ _______ _________ 1,072,008 Binder oxidizes and liberates heat, which is neglected in this calculation. ' ` ^Average value of coefficient is less than 0.3 because oven is not Qp to 575 F.*' This is neglected. 422 F is arrived at by taking area under curve as compared to area under 575 F ordinate. * ESTIMATING METHODS Values based on practical experience are available for rough estimating of drying problems. The temperature will drop approximately 8.5 F per (grain of water evaporated) (cubic foot of air, measured at 70 F) or approximately 0.62 F per pound of air at any temperature. Air will drop 55 F per cubic foot for each Btu extracted. Generally air will absorb from 2 grains to 5 grains per cubic foot of air in one passage through an air dryer, depending on the temperature and the degree of contact with the material. The amount of steam required to evaporate a pound of water will vary from 1.5 lb to a more usual figure of from 2.5 to 3 lb of steam per pound of water evaporated. . . BIBLIOGRAPHY Drying Apparatus, by H. C. Russell (A.S.H.V.E. Transactions, Vol. 18,1912, p. 76). Commercial Drying Apparatus, by L. P. Dwyer (A.S.H.V.E. Transactions,-Vol. 22, 1916, p..479). ... . Drying Systems 865 Artificial Drying with Special Reference to.the Use of Gas, by G. C. Shadwell (A.S.H. V.E. Transactions, Vol. 23, 1917, p. 231). . .. , . Drying by Evaporation, by F. R. Still (A.S.H.V.E. Transactions, Vol. 23; 1917, p. 255). , . ... High Temperature Drying, by Burt S. Harrison (A.S.H.V.E. Transactions, Vol. 24, 1918, p. 7). . ' The Temperature of Evaporation, by W. H. Carrier (A.S.H.V.E. Transactions, Vol. 24, 1918, p. 25). .. ......... Address on Dehydration, by H. C. Gore (A.S.H.V.E. Transactions, Vol. 24, 1918, p. 323). ' '. ' Food Dryers and the Use of School Houses for Drying,' by W. Li Fleisher (A.S.i I.V.E. Transactions, Vol. 24, 1918, p. 339). ... Memorandum Concerning Fruit and Vegetable Dryers, by Alfred S. Kellogg. (A.S.H. V. E. Transactions, Vol. 24, 1918, p. 359). .^ Progress in the Dehydration Industry, by C. E. Mangels'(A.S.H.V.E. Transactions, Vol. 26, 1920, p. 99). . . Dehydration, by Ralph H. McKee (A.S.H.V.E. Transactions, Voi. 26, 1920, p. 105). ' ' . ...'.. Commercial Dehydration, by J. E. Whitley (A.S.H.V.E. Transactions, Vol. 26, 1920, p. 551). Drying of Fruits and Vegetables, by Ray Powers (A.S.H.V.E. Transactions, Vol. 27, 1921, p. 241). Drying as an Air Conditioning Problem, by A. W. Lissauer (A.S.H.V.E. Trans actions, Vol. 27, 1921, p. 251). . A Chronological Survey of Drying and Driers, by J. E. Bolling (A.S.H.V.E. Journal, Vol. 27, October, 1921, p. 715). Dehydration and Freshening of Codfish, by Henry W. Banks, 3D (A.S.H.V.E. Transactions, Vol. 28, 1922, p. 143). Construction of Farm Dehydrators in California, by A. W. Christie and G. B. Ridley (A.S.H.V.E. Journal, Vol. 29, 1923, p. 687). " Study of Air Velocity and Temperature in Vegetable Dehydration, by A. W. Christie and K. Matsumoto (A.S.H.V.E. Journal, Vol. 33, June, 1927, p. 381). Air Conditioning and Food Dehydration (Heating and Ventilating, December, 1942, p. 35). - Adiabatic Drying of Hygroscopic Solids, by A. M. McCready and W. L. McCale (Transactions, American Institute Chemical Engineers, 1933). . Limitations of Diffusion Equations in Drying, by O. A. Hougen, H. J. McCauley and W. R. Marshall (Transactions, American Institute of Chemical Engineers, 1940). Factors Influencing the Performance of Rotary Dryers, by C. F. Prutton and C. O. Miller (Transactions, American Institute of Chemical Engineers, Part 1, February, 1942; Part 2, August, 1942). .. - , Drying of Solids by Through Circulation, by W. R. Marshall and O. A. Hougen (Transactions, American Institute of Chemical Engineers, 1942). . Factors that Influence Drier Performance, by A. Weisselberg (Chemical and.Metallur gical Engineering, August, 1932). Typical Dryer Calculations, by O. A. Hougen (Chemical and Metallurgical Engi-. steering, January and March, 1940). Symposium on Drying, Articles by W..K. Lewis, W. H. Carrier, A. E. Stacey, Jr. and R. S. Fleming,. R. G. Metz, G. B. Ridley, C. O. Lavett, D. J. Van Marie (Journal Industrial Engineering Chemistry, May, 1921). Principles of Drying Lumber and Humidity Diagram, by H. D. Tiemann (Forest Service Bulletin 104, 1912). 866 CHAPTER 47 1946 Guide The Drying: of Solids* by-T. K. Sherwood (Bulletin Massachusetts Institute'of Technology, Nos. 237, 247 and 258). ...................... .. . . Air Conditioning and Engineering,"American Blower Co:, .1935. ; ... Drying in Industrial Plants, by J. O. Ross. Elements of Chemical Engineering, by Badger and McCabe (McGraw Hill Co., 1931). Fan Engineering, Buffalo Forge Co. . . . -. " . Die Trockentechnik, by M. Hirsch (Julius Springer, Berlin, 1932). " Drying (Kent's Mechanical Engineers Handbook). . Drying, by W. H. Carrier {.Marks' Mtchanical lLr.gir.cers Handbook): . , - , Drying {Perris Chemical Engineers Handbook, 1941). ' ' ' Kiln Drying of Lumber, by A. Koehler and R. Thelen, New York, 1926i . , ' Kiln Drying of Lumber, by H. D. Tiemann (Lippencott, 1920). ,. Modern Drying Machinery, by H. B. Grenshaw, London, 1926. " ' Principles of Chemical Engineering, by Walker, Lewis, McAdams (Chapters on Evaporation, Humidity and Drying, McGraw Hill Co.). ,. ' 1 CHAPTER 48 CJra.n5porla.tion _/^iV (Conditioning. Railway Passenger Car Ventilation, Method of Air Distri bution, Air Cleaning, Winter and Summer.Air Conditioning, Humidity and Temperature Control, Summer Air Condition ing for Buses and Automobiles, Airplane Air Conditioning THE principles of air conditioning used in connection with stationary applications such as stores, restaurants, hospitals, theaters, and homes are in general applicable to such mobile applications as railway passenger cars, passenger buses, automobiles, and ships. However, the equipment used for these mobile applications, differs from that used for stationary purposes in that it must meet additional requirements. Especially important are the features of compactness with the retention of ready accessibility for quick inspection and servicing, and low weight. Freedom from vibration which could be transmitted to the supporting vehicle and thus to the passengers is essential. (For Air Conditioning of Ships see Chapter 49.) . . .. RAILWAY PASSENGER CAR VENTILATION In non-air-conditioned cars, ventilation is accomplished by exhaust fans, roof ventilators, and open doors and windows. This practice provides an ample supply of outside air but does-not. prevent the entrance of smoke, cinders, and other dirt. An average passenger car contains approximately 5000 cu ft of air and may seat as many as 80 passengers. The occupants are continually liberating heat, carbon dioxide, moisture, odors, and some organic matter from their breath, skin and clothing. The heat and moisture can be removed by cooling and dehumidification, but the other constituents can be successfully handled only by proper ventilation and, air cleansing. In the average car from 2000 to 2500 cfm should be circulated by the air conditioning unit. Some of this air may be recirculated, but a portion of it should always be brought in from the: outside. The amount of outside air required depends upon the type of car, number of passengers, air temperature, humidity, odors, and whether or not occupants are smoking, and will vary from 15 to 90 per cent of the total'air circulated. Careful attention must be exercised in specifying the rate of outside air- taken in so as to fit the type of service adequately and yet not to supply more ventilation than is necessary. Conditioning this outside air is a major factor in deterniining the size of both summer and winter con ditioning equipment. With present average ventilation requirements; about 30 per cent of the cooling equipment and sometimes as high as 50 per cent of the heating equipment is necessary to handle only the outside air load. . For normal conditions, 10 cfm of outside air per passenger is sufficient. When smoking is permitted, at least 15 cfm should be admitted. In some of the dining cars and de luxe sleeping cars, outside air rates as high as 20 and 30 cfm per occupant are-used. .. Method of Air Distribution ' : ' . The fact, that the amount of. space devoted to, railway passengers may be as low as 60 cu ft per person (ranging as high as 190 ciTft per person) and the high air flow rates made necessary by severe ventilation and sun 867 .......................................... 868 CHAPTER 48 - 1946 Guide loads make the problems of air distribution and air delivery in railway cars critical. - Various methods may be used to distribute the air delivered to the interior of the car by the circulating fan or blower. The methods com monly used are: 1. A duct lengthwise along the center of the car. 2. One or two side ducts built on the outside of monitor-roofed cars, or on the inside of turtle-backed or arch-roofed cars. . .... 3. A ceiling which is perforated for the emission of air into the car; the air being carried to the ceiling by an overhead duct. From one-half to the full area of the ceiling is used for the distribution of the air although practical considerations generally limit the available area to about two-thirds. As large a part of the ceiling area as possible should be used for air distribution. Delivery grilles and plaques are used, and are often designed to give - considerable entrainment and mixing to avoid cool drafts. Smoking rooms present a special problem. The cloud of smoke that usually hangs near the ceiling can be broken up by having the incoming air directed along the ceiling in all directions at a velocity somewhat higher than that used for the rest of the car. The air should be exhausted from the room by a fan or through a grille to the washroom or lavatory, and then outside by a fan in a ventilator. For compartments an adjustable supply duct outlet grille of suitable size and design should be provided and provisions made in the door or partition for the removal of the air to be recirculated. Lower berths in sleeping cars and office cars should be provided with an adjustable air outlet which will discharge the amount of air desired at low velocity in any direction so that the occupant can regulate the ventilation to meet his own requirements. . . In cars containing but one or two rooms or compartments, satisfactory results may be obtained by discharging the air directly from the con ditioning unit into the upper part of the car. Care must be taken to have a proper discharge velocity. If the velocity is too low, the air will drop before reaching the end of the car and if too high it will discharge against the end bulkhead and be reflected back. Care must be exercised to secure proper circulation, otherwise objectionable drafts will be experienced. The recirculating air grilles are usually of the straight flow type, and should be located so- that objectionable drafts will not be created by the return air. The outside air intakes, located in the car vestibule, on the side of the car, or on the roof of the car, depending upon the location of the cooling coils, should be of ample size, to permit the entrance of suf ficient outside air. On many of the recently air-conditioned cars, there are no dampers or shutters at the outside air intakes, the percentage of outside air being controlled by adjusting the flow through the recircu lating grille. '; Air Cleaning All of the air circulated by the blower is.filtered before passing over the cooling coils. In some cars the outside and recirculated air is filtered' separately before mixing, while in others the air from the two sources is mixed before passing through a common filter. Filters in use are made of metal, wool, cloth, spun glass, hemp, paper, hair, and wire screen! Most filters have a viscous coating of oil for greater cleaning efficiency. Some types may be. cleaned, retreated, and returned to service while other types are discarded when dirty. ' Transportation Air Conditioning 869 RAILWAY PASSENGER CAR WINTER AIR CONDITIONING The majority of cars in service use steam from the locomotive or from a head-end, oil-fired boiler as a source of energy for winter heating. In some instances electrical energy from either a head-end generating set or motive power supply is utilized for resistance heating. In still other cases electrical energy and waste heat from individual car engine-generator sets are employed. The peak heating loads which depend largely upon the amount of insulation used in the car, the type of windows (whether single or double glazed), and the ventilation rate, may vary from 150,000 to 250,000 Btu per hour. In order to temper the cold outside air, about 30 to 50 per cent of the total heat energy required is distributed by means of finned coils or resistance heaters located in the outside air duct. The remainder is usually transmitted to the car air by finned tubing located along the sides of the car near the floor, thus preventing cold convection currents falling from the car windows from reaching the feet of the passengers. RAILWAY PASSENGER CAR SUMMER AIR CONDITIONING Three general types of cooling or refrigerating equipment are being used in 13,362 (May, 1944) air conditioned railway cars and 31 air conditioned rail motor cars in the United States. Of these, 30 per cent are ice activated, 15 per cent use steam jet systems, and 50 per cent employ mechanical compression schemes. These systems. which func tionally are identical with those used for stationary applications (see Chapter 39) are modified in design to meet the requirements of. mobile service. Contrasted with stationary applications of summer conditioning equipment, the use of water as a final means of heat disposal from con densers cannot be resorted to because water in such quantities cannot be transported economically. Accordingly, air cooled or evaporative con densers are always used, with the result that mobile cooling equipments operate at higher temperature, pressure, and power requirement levels than stationary equipment. ... The maximum cooling and dehumidifying load which depends largely upon the amount of insulation, the type of windows, the ventilation rate, the sun intensity, and the number of passengers may vary from 60,000 to 96,000 Btu per hour. ' An averaige ice-activated system for such capacities uses about 500 lb of ice and 1.2 kw per hour. The increase in car weight due to such a system is approximately 8500 lb. The same service from a steam jet system is obtained, with the expendi ture of 180 lb of steam and 3.3 kw per hour, with an added weight per car of 8000 lb. .. The mechanical compression systems, all of which use dichlorodifluoro- - methane as a refrigerant, may be classified by several types depending on the method of driving the compressor. The source of . power for driving the compressor (approximately 10 hp) is complicated by the necessity of obtaining this power at all times whether the car is rn motion or standing still on the right-of-way. or in a terminal where auxiliary power plug-ins are available. In those cases where compressors are driven from car axles, additional refinements in the drive are necessary in order that a nearly constant cooling capacity may be obtained from a variable speed power source. Numerous combinations of electrical generating schemes for generating sufficient electrical energy from the car axle for lighting, ventilation, and summer air conditioning are in use, and their operation 870 CHAPTER 48 1946 Ciiidf} is closely interlocked with compressor demands, need for pre-cooling, battery charging, etc. It is difficult therefore to state the additional ' weight imposed on a car because of such a compression air conditioning system, but it is probably in the vicinity of 6000 to 8000 lb. These systems, depending mostly upon the locomotive for supplying power for operation, impose a load, including the power required to pull the weight added by the equipment, of from 5 to 10 per cent of the total locomotive' . power. Several schemes for relieving the locomotive of this compression load are used. Some of the articulated trains, which run as unit equipment-- the same cars always, in the same train--employ a head-end, enginegenerator combination for supplying power to compressor motors. In other cases, especially in many of the new streamlined trains, propane fueled engine-driven generators on individual cars are used to supply power to motors, as well as to supply all power for car lighting and acces sories. Gas engine compressor combinations on individual cars provide attractive low weight equipment where automatic engine operation is permissible under all circumstances. Diesel-powered generator units ,, have been used experimentally, on individual cars for supplying electrical energy and in some cases waste engine heat has been used either for ' modulating refrigeration with a reheat cycle or for car heating purposes. RAILWAY PASSENGER CAR HUMIDITY AND TEMPERATURE CONTROL The temperature to be maintained in a car depends upon the outside temperature and the humidity desired inside the car. With a low hu midity it is necessary to maintain a higher temperature to establish a . desirable comfort condition. Little humidity control has been attempted . on cars up to the present time. A certain degree of automatic humidity control is secured with cooling, but the relative humidity obtained depends largely upon the temperature of the evaporator, which should be below the dew-point temperature of the air. With certain outside atmospheric conditions it may not be possible to operate the conventional equipment with a sufficiently low evaporator temperature to reduce the humidity without dropping the temperature too low. One method has been developed whereby the evaporator temperature is carried below the dew point a sufficient amount to insure dehumidification and then the cold air is heated to the proper temperature by passing it over coils through which part of the high temperature liquid from the condenser is by-passed. Such a system is costly and has not been generally applied. The reheat cycle ^ obtainable from waste engine heat may be used to good advantage in reducing the humidity without reducing the dry-bulb temperature. During the heating season humidification is desirable from a comfort . standpoint, but,, unless properly controlled, condensation will appear on the windows. A steam or water spray controlled by a humidistat will provide the necessary moisture for humidification.. There are several cars with this featurq now in use. ^. . Temperature consol for the most part obtained by rugged thermostats and relays capable of withstanding vibrations attendant with .mobile service is usual, equipment. . . Manual zone control for varying outdoor conditions, as well as controls which regulate, the car temperature automatically in accordance with . outdoor conditions, are employed, . . ; . . . . Simplified controls from the standpoint of operation by. train crews and Transportation Air Conditioning 871 especially from the servicing viewpoint are very desirable:. The control of summer temperatures is accomplished mainly by cycling-the complete cooling system; however, modulation is being effected by using, multiple . evaporators in wluch a fixed portion may automatically be cut out of operation to suit the cooling capacity requirements and to keep the equip ment in operation for longer periods. . . With motor or engine driven compression equipment modulation of compressor capacity to suit the reduced evaporator capacity is accom-' plished by changing motor or engine speed, or by varying the number of compressor cylinders in operation. Steam ejector equipment is provided with dampers which by-pass the air around the cooling coil during the off cycle to prevent re-evaporation of moisture from the coil during the off period. . For further information on controls, see Chapter 34. PASSENGER BUS SUMMER AIR CONDITIONING AND VENTILATION The highways in the United States are now traveled by about 3500 summer air-conditioned passenger buses. Many of the facts stressed in connection with the design and installation of summer conditioning equipment in railway cars are even more important in these newer vehicles. Weight and space limitations are more stringent, and the problem of circulating from 900 to 1200 cfm of air in coaches carrying from 25 to 40 passengers with about 35 cu ft of space per passenger without drafts is no easy one. - - ' Some bulkhead delivery systems have been used and, while the over head package racks have served to break up drafts to some extent,_ these installations are not gaining in popularity. Longitudinal ducts in the . corners above the package racks are sometimes used to carry conditioned air to a series of outlet louvers along the top of the windows. Other designs provide for false spaces below the package racks which serve as ducts to distribute air to either entrainment grilles in the bottom of the racks or distributing slots at the edges of the package racks. Some coaches employ a false ceiling -to provide a duct, with delivery taking place from numerous perforations in the ceiling. ' Return air grilles and filters are usually located near the rear ceiling ' where the evaporator is placed: Outside air intakes and filters are-located preferably near the front of the vehicle so as not to contaminate this supply with exhaust fumes and road dust. Of the 30 cfm circulated per person, about 8 to 10 cfm are outside air and the remainder is recirculated- Power for the motor driving the centrifugal fans is obtained from the bus battery. : ., More recently a coach-design has been brought out which provides for a number of return air outlets below the seats; these permit return air to enter a longitudinal duct below the floor. The filters, and evaporator are located in this duct near the front of the vehicle. In this instance a central heating coil utilizing waste heat from the coach engine is also located in this duct. Conditioned air is delivered through a pair of vertical ducts to a package rack distribution scheme. .. , . Summer. conditioning systems for these vehicles range, in cooling capacity from 36,000 to 48,000 Btii per hour. Mechanical compression systems using dichlorodifluoromethane are used. and are .powered by water cooled, gasoline engines of approximately 14.hp. .. ,. Complete systems add from 800 to 1300 lb to the weight of a coach, 872CHAPTER 48'1946 Guide Sometimes an auxiliary generator driven by the air conditioning engine is used and serves to help charge the bus battery, thereby offsetting the power drain imposed by the ventilating blower. . Belted reciprocating compressors and direct driven V-type and rotary compressors are used, with engine speeds up to about 1800 rpm. Air cooled condensers for this service require about 5000 cfm of outdoor air, and this is provided by either centrifugal or propellor type fans belted or direct driven by the air conditioning engine. Preventing noise and vibration from affecting passengers is of vital importance. Installations must be made so that quick daily servicing of the engine is possible. In all cases fuel is obtained from the main bus tanks, and in some cases the main engine jacket water cooling system is used to cool the air conditioning engine. In the de luxe equipment, after the driver has started the air con ditioning engine by means of its own cranking motor, the engine speed is modulated automatically as the refrigeration demand is partially met, and if this demand is then fully met, the engine is stopped thermostatically. Restarting when the cooling thermostat is no longer satisfied is accom plished either automatically or manually. The various protective and automatic-devices on the refrigerant and engine systems make some of the bus air conditioning control systems quite complicated. . AUTOMOBILE SUMMER AIR CONDITIONING Recently summer air conditioning has been applied to automobiles. The average present day automobile with little insulation, large, single glazed window areas, and high infiltration and exfiltration losses requires about 15,000 Btu per hour of cooling capacity. One system utilizes a reciprocating compressor belted from the main 'engine fan shaft thus operating at varying speeds up to 3000 rpm. The resulting refrigeration capacity varies from about 6000 Btu per hour at idling speed to 24,000 Btu per hour at maximum car speed. . A dry air condenser is placed in front of the engine radiator, and the liquid and suction refrigerant lines run back under the car floor to the evaporator which is located in back of the rear seat. Conditioned air is delivered into the car just above the shelf near the back of the rear seat. A return grille is provided under the rear seat, and the recirculated air is filtered. Outdoor air is provided by infiltration. Power for the air circulating blowers is obtained from the car storage battery. Equipment of this nature increases the car weight approximately 200 lb. AIRPLANE AIR CONDITIONING Air conditioning of airplanes is closely associated with heating and ventilation of airplanes, but air conditioning of planes in flight has received little attention to date, probably because of added weight of equipment, necessary. Under ordinary conditions the cleanliness and humidity desired are fixed by natural conditions and therefore the supply of heat and temperature control become, the chief consideration. Pas senger planes and military planes even at low level flying are at altitudes which require no cooling and at extreme altitudes the design temperature of the atmosphere is 60 deg below zero. .- , In the operation of internal combustion engines the heating value of fuel appears approximately, one-third as power, one-third transferred to cooiing fluid, and one-third in the exhaust gases. .. Ordinarily, the heat in the exhaust gases is ample for all heating needs,: despite the excessive transmission loss due to high speed, low tempera- Transportation Air Conditioning 873 tures, and light wall constrdction. . The maximum coefficient of heat transmission without insulation is found to be 2.28. The minimum coefficient with insulation is 0.33. For present day construction a value of 0.56 may be assumed. Naturally, the waste heat in the exhaust gases offers an attractive source for designers of heating equipment, who in . the course of design have followed closely the development of heating as applied to land structures. In first attempts heat was obtained from an annular space surrounding the exhaust pipe, from which branches conducted the heated air to grilles or to seats of passengers. The speed of the plane eliminated the need for a fan or pump. In present practice. danger of carbon monoxide contamination is avoided by the use of both' primary and secondary heat exchangers. ' Heating systems using hot air are in use for passenger and military planes. Steam systems have been used with boilers located in the path of exhaust gases but difficulty experienced in preventing freezing of the water has apparently rendered this system obsolete. A similar system using glycol is in use and requires special care because of the peculiar qualities of glycol. Thermostatic control, mixing dampers and air distribution vary little from.standard practice. Controlling devices are built to withstand the extensive vibrations experienced. Humidity determinations under flying conditions show need for humidity control. Passenger planes or other planes requiring air conditioning when on the ground are satisfactorily serviced by portable air conditioning machines. High flying airplanes--above an elevation of 14,000 ft--require oxygen supply or pressurized cabins. The compression of the outside air by the supercharger raises the temperature of the cabin air from an extremely low to a comfortable high. The compression of the air also increases the humidity. Cleanliness at flying altitude is not a consideration, except under special conditions such as above deserts or upon encountering dust storms. In small planes carrying several passengers or crew, localized heating and ventilation are provided. Electrically heated clothing and oxygen masks meet requirements. At high altitudes pressurized cabins require no special oxygen supply. ; . Medium bombers at one time were equipped with separately fired 'heating units, but larger bombers, to meet the heating load imposed by crew and equipment, demand too much heat to be supplied in this manner. The recovery of 'heat from waste gases is therefore imperative. In air plane operations light weight is a more important requirement than in any other type of transportation. Noise should be reduced to a minimum and combined use may be made of material for insulating and noise, reduction. , REFERENCES Railway Passenger Cars . Summary Report on Air Conditioning of Railroad Passenger Cars, by Division of Equipment Research, Association of American Railroads, November 24, 1936. Engineering Report on Air Conditioning of Railroad Passenger Cars, by Division of Equipment Research, Association of American Railroads, April 15, 1937. Report on Performance and Cost of Operation of 1937 Internal Combustion Engine Mechanical Compression Equipment for Air Conditioning Railroad Passenger Cars, by Division of Equipment Research, Association of American Railroads, May 1, 1937. Report on Relative Performance of Air Filters, by Mechanical Division, Association of American Railroads, January 15, 1938. Air Conditioning of Railroad Passenger Cars, by L. W. Wallace and G. G. Early, Jr. (A.S.M.E. Transactions, November, 1937). - 874 Chapter 48 1946 Guide . Improved Methods of Railroad Air Conditioning, by A. E. Voigt {Refrigerating Engineering, July, 1940, p. 16). " , ' ' Comfort Cooling on Wheels, by F. H. Sahlmann {Refrigerating. Engineering, May. 1934, p. 233). - . Passenger Car Cooling Methods, by Kenneth Cartwright {Refrigerating Engineering, February, 1936, p. 83 and March, 1936, p. 158). . .* Diesel Drive.for Passenger Air Conditioning, by J. R. Hornaday {Refrigerating Engineering, March, 1942, p. 139). .. . , Railroad Air Conditioning, by Gordon T. Wilson'. {Refrigerating Engineering, May, 1943, p. 323)'. . ,. . . : . Buses and Automobiles . . Iso-Thermal Manifold and the Conditioned-Air Unit * Used on - Nash Cars, by E. Monson {Society of Automotive Engineers Journal, January, 1938). - .< Summer and Winter Air Conditioning of Automobiles and Buses, by L-.-W. Child (Heating and Ventilating, March, 1938, p. 38). .. .. .Air Conditioning Takes, to the Highways (Heating, Piping and Air Conditioning, May, 1938, p..314). . 1 .. , Fleet of Air Conditioned. Buses West Carries Demountable Units (Heating and Ventilating, May, 1938, p. 30). . .* Conditioned Air for Automobiles (Heating and Ventilating,- May, 1938, p. 44). Air Conditioning, of Automobiles and Buses, by L. W.' Child (Society of Automotive Engineers Journal, June, 1938); ' ' ,' Bus Air Conditioning, by Jerry Hicke (Heating, Piping and Air Conditioning, October, 1938, p. 639). .. . Bus Air Conditioning, by A. J. Mallinckrodt and Lars Hanson (Refrigerating Engi neering, June, 1939, p. 388). ... ;. . Problems in Air Conditioning Automobiles, by F. J. Linsenmeyer (Society of Auto- motive Engineers Journal, July, 1939). .. . . Packard. Offers Automobile Air Conditioning System * (Heating, Piping* and Air Conditioning, December, 1939, p. 756).. . .. '. .. AlBPLANES _ : .Flight in the Sub-stratosphere, by J. C. Edgerton (Society of Automotive Engineers Journal, 39:484-6 December, 1936). . Steam Heating for Modern Air Transports, by Jack McGuire (Heating and Ventilating, February, 1937, p. 37). * -* ' Comfort Aloft (Heating and. Ventilating, October, 1937, p. 40). t. Portable. Climate, American Buys 12 Plane Air Conditioning Units (Aviation, 36:59, September,. 19370. , . . : .. j . Steam Heating in the. Sky (Heating, Piping and Air Conditioning, October, 1938, -p. 631).' .... - Altitude Conditioning.(Heating and Ventilating, August, 1940, p. .16). , Comfort in High Altitude Flying, by D. W. Tomlinson (A.S.H.V.E. Transactions, . Vol. 47, 1941, p. 57). . . .. ; . Heat Exchangers for Aircraft, by Arthur J. Hess (Refrigerating Engineering, Sep tember, 1944, p. 192). ' ... . CHAPTER 49 General Considerations, Ship Construction Features, Factors Affecting Design, Requirement for Various Types of Space, Ship Insulation - THE importance of adequate shipboard heating and ventilation arrangements cannot be overemphasized. Installations must not only keep, the passengers comfortable and the, operating personnel physi cally fit dhd mentally capable of maintaining the ship as a profitable business investment, but must also satisfy the human element. The provision of satisfactory living and working conditions is one of the most economical means of keeping a high morale. GENERAL CONSIDERATIONS Unlike a shore establishment in connection with which personnel obtain their food, rest and recreation from outside sources, a ship must be self-sufficient and provide for all human needs. Accordingly, every vessel is a complete, independent community comprising, at ieast to some . degree, the facilities available in the average urban development. These facilities must be contained in the minimum practicable space and weight to conserve dead weight and increase the pay load. The pay load may be expressed in terms of cargo carrying ability, passenger carrying capacity, ' fighting strength, or towing ability. . -. An atmosphere compatible with efficient operation must be maintained in working, and machinery spaces, and temperatures must be such that materials or equipment will not be damaged. Conditions in living spaces, whether ashore or afloat, must permit adequate rest and comfort of- occupants. Passenger accommodations must be treated to provide service and living conditions similar to those afforded by the various classes of hotels. Many of the expedients used ashore for this purpose are not applicable afloat. For instance, all living quarters aboard ship cannot be located at, a distance from the power plant; but must often have . boundaries in common with heat producing spaces. The thermal con ductivity of:shipbuilding materials such as steel, copper, brass, etc., is many times the value for building materials used ashore, and this, to-, gether with concentrated arrangement of equipment, produces a difficult heat transfer and insulation problem. Furthermore, the use of portholes, . windows, skylights, and similar openings is greatly, restricted in marine . applications because, of the necessity for strength, water-tightness and protection from the sea in foul weather. During wartime, the utility of portholes, windows, and skylights is greatly restricted because they must be fitted with light-excluding devices. ' Much of the cooling and.ventilation that is accomplished by naturalmeans ashore must be handled by mechanical means afloat. Space does - n6t exist for the large ventilation trunks required for natural ventilation. Also, because of the restricted space and shipbuilding materials the heat . .quantities that must be dissipated by ventilation air are often greater than would be required for a similar shore installation. Mechanical venti lation is not merely desirable, but is absolutely necessary in many ship- board spaces to enable the crew to. operate the vessel. Furthermore there . are numerous spaces which must be ventilated to prevent the accumula- - 875 876 CHAPTER 49 1946 Guide tion of objectionable, combustible and toxic gases. Shipboard equipment must also be reliable inasmuch as specialized servicing facilities are not ' available at sea, and failure during an emergency may jeopardize the vessel's safety. Experience has demonstrated that simple-and foolproof heating and ventilating arrangements are essential for satisfactory service. Ventilation systems on ships must be designed to operate in- heavy weather with little or no attention, and to resist the efforts of unauthorized personnel to readjust the heat or air distribution. Also, they must be laid out in such a manner that the watertight-and fireproof integrity of the vessel is not impaired. Contrary to the impression among some engineers and designers, that there is a basic difference between marine and shore installations in the application of heating, ventilating and air conditioning arrangements, the same fundamentals apply to both shore and shipboard applications. The air capacity handled by a system ashore will equal the capacity that an identical system will deliver afloat. The same laws of heat transfer apply, and the same heat balance must be maintained in the human body. The only variation between ship and shore applications is that emphasis is placed on different practical aspects of the design. SHIP CONSTRUCTION FEATURES The seaworthiness of the vessel is increased by subdividing the main watertight hull space into a rfumber of watertight compartments. This is usually done by providing transverse watertight structures (bulkheads) so located along the ship's length that the vessel will not sink even when the shell is pierced in one or more watertight compartments, by collision, torpedoing, or other causes. It is obvious that the watertightness of these bulkheads is very important, particularly under war conditions. Every effort is made to lead ventilation ducts so that they do not pass through such structures. Where openings must be cut for ventilation or other purposes, special watertight closures are fitted to protect the watertight ness of the bulkheads. In addition to the obstructions caused by the main transverse bulk heads, the.ship's interior is fitted with decks and flats (partial decks) that are spaced to suit the use to which the space is put. The deck height (floor height) in cargo spaces generally Varies from 9 to 30 ft. This height in living quarters varies from 7)^ to 9 ft. Usually in main machinery spaces, the entire depth is subdivided only by a few flats, with gratings provided where necessary to service the equipment. . Bulkheads, shell, and decks are designed to suit structural as well as watertight requirements of the vessel, and consequently, the designer must always contend with beams, stiffeners, stanchions and brackets. Fig. 1 indicates the arrangement of a typical cargo vessel, and shows the main transverse watertight bulkheads, decks, structural members, and many other pertinent characteristics. Living quarters are usually 'located on and above the weather deck, this custom being based on the ' assumption that better natural air and light are available in this location.' It is obvious that the upper 'tween deck and other spaces can be con veniently used for additional living and working spaces, but that natural . ventilation is far less effective in this case. The. foregoing description mentions some of the limits' and natural boundaries, which affect the design and layout of ship ventilation and . heating systems. It should be added that there are also equipment, wireways,'and miscellaneous piping which must be considered. Since Marine Heating and Ventilation , 877 there is very little unassigned space, fan rooms are usually quite congested and many studies must be made to ascertain the arrangement of equip ment which will best suit the conditions. Cuts in structural members must be limited in number and size. Lack of headroom often causes poor, aspect ratios, inaccessibility, and other undesirable conditions. It there fore follows that the design of a ship's heating and ventilating system is far more than a theoretical calculation. A good designer must be familiar with all phases of ship construction and operation in order to provide sufficient and efficient ventilation and heating, and to locate the equip ment where it will interfere least with basic arrangements, major equip ment, stability, and other important factors. FACTORS AFFECTING DESIGN A ship may be favorably compared to a floating hotel. Its make-up includes living accommodations, dining rooms, shops, power plants, com missary spaces, etc., all of which must be so arranged and maintained as to make it self-sustaining for long periods of time. In contrast to a hotel, however, a ship may, on a single cruise, move from arctic to tropical climates. On the other hand, it may be built to operate only in one single locality. It is therefore necessary to assume maximum and minimum design air temperature conditions based on the intended use of the vessel so that adequate cooling and heating may be provided. For vessels designed to operate generally in all parts of the world, a maximum summer temperature may be taken as 88 F and a minimum winter tem perature as 10 F. For other ships, those which spend long periods in port or in inland waters, the maximum and minimum temperatures may be taken as 90 and 0 F respectively. Preliminary design of heating and ventilating installations aboard ship is simplified by the uniformity of the conditions which apply to all ships. Among such conditions are (1) the necessity for the vessel to supply its own power, (2) the availability of an unlimited supply of sea water, (3) the drastic restriction of shipbuilding materials because of strength requirements, corrosion resistance and fire hazard, and (4) the limitation of available space and permissible weight. On the other hand, shipboard space, weight, and power limitations require precise layouts with mini mum design safety factors, and this necessitates unusual ' attention to design details."' Particular attention should be given also to the adjust ment of a system after installation,- because designed air quantities are usually close to the minimum acceptable and therefore, improper balance will result in unsatisfactory conditions in some spaces. Each space aboard ship must be treated in accordance with the par ticular requirements of its use. The ventilation of most spaces is deter mined by empirical calculations. The quantity of air supplied must be not less than that which satisfies (1) maximum allowable temperature rise, (2) minimum allowable fresh air per person, and (3) permissible air change, named in order of importance. . The present practice of various ship designers may be to supply the quantity of air which satisfies only one of these requirements, but the most satisfactory ship ventilation will result from the use of that quantity which is large enough to satisfy all three. When heating and cooling loads are estimated, the cooling effect of the . water through which the vessel is sailing must be considered if the space is at or below the waterline. Maximum and minimum water tempera tures of 85 and 35 F are usually used -for such calculations. This factor is ss 00 880 CHAPTER 49 1946 Guide important enough to justify the omission of ventilation from certain spaces which have only small heat gains and do not require fresh air for other purposes. The relation between supply and exhaust ventilation depends on the type of space, and the space's' relation to the weather. In any case, it should be remembered that positive means for supply and exhaust must always be provided. Where natural ventilation is anticipated, infiltration1 and exfiltration via .open doors, windows, etc., cannot always be con sidered adequate for this purpose. In addition to the ventilation requirements, but closely related to and usually forming an integral part of the study, is the manner in which heating shall be furnished for cold weather conditions. In all spaces which are provided with mechanical supply ventilation, where heat is also required, the simpler method and most economical from standpoint of weight is that in which duct type or blast heaters are fitted in the venti lating systems. Where this type of heating is furnished, convectors or . radiators should be provided for spaces requiring heat but not furnished with mechanical supply ventilation. The most satisfactory arrangement for this method of heating, except where individual space -control is . essential, is zone heating. To accomplish this, the ventilation supply system, with the fan operating at slow speed (usually about 50 to 70 per cent delivery) passes the air over a preheater which raises the air to a temperature of about 40 to 60 F. This preheated air is then passed through the system and thence through one or more reheaters which are located in the ducts and so arranged that each serves a group of spaces which possess the same or similar heating requirements. It may be necessary to slightly revise the individual space air quantities, which have been determined on the basis of summer" cooling, in order to bring them in line with the reheat or delivery temperature. In some cases central heating is used. By this arrangement all the air needed for heating is passed through the preheater and reheater fitted in series. This system has the disadvantage of affording poorer thermostatic control and cruder heating properties. In all installations of duct type heaters, however, . 'care must be taken in the first stage of heating (preheater) to provide - protection against freezing, either by heater design or compensating auto matic valve control. Of course, many of the usual combinations or variations of duct type and convection or radiant heaters may be used with varying degrees of satisfaction, depending on basic design require ments such as weight and space limitations and economic justification for refinements. s REQUIREMENT FOR VARIOUS TYPES OF SPACE In the paragraphs which follow the most important considerations are given for the treatment of the various spaces, but the resulting quantities of air should in all cases be checked with those shown in Table 1. Machinery Spaces The prime purpose of machinery space ventilation is to maintain a habitable temperature for the operating personnel. Of secondary impor tance is the necessity for preserving temperature conditions satisfactory for the successful operation of machinery, particularly of that designed for certain maximum ambient temperatures. High dissipation of heat,,1 . from high"/temperature steam equipment or from high powered electrical installations, make it more practicable to use spot cooling of working Marine Heating and Ventilation 881 Table 1. Typical Heating and Ventilation Practices for Ships -Space Type op Ventilation Sup. Exh. Crews Quarters.,____~______ Mech. Toilets and Showers. . Nat. Mech. or Nat. Mech. Passenger & Officers Qtrs. Office & Similar Spaces___ Mess Rooms...................... .... Mech. Mech. Mech. or Nat. Mech. or Nat. Mech. or Nat. ' Mech. or Nat. .Type OF Heating Air Change Minutes Remarks - H.B.a or D.Rb D.R. H.B. or D.R. H.B. or D.R. H.B. * or D.R. H.B. or D.R. 5-6 3-4 5-6 4-6 5-6 Maybe' 4-6 exhausted through Galleys and Pantries. Dining Salons........................ Mech. Mech. or Nat. H.B. of D.R. Galley and Pantry.......... .. Mech. & Nat. Deck Pantries (No.cook- Mech. ing Equipment).. ______ & Nat. Stores Spaces (Adjacent -.Mech. to Living Quarters):____ or Nat. Stores Spaces (Isolated Mech. Locations)___ ___________ or Nat. Hospital Spaces.................... Mech. Soiled Linens and Oilskin Lockers.............. ................ Nat. Shops.................. .... ............. Mech. Group Berthing Spaces___ Mech. CO* Bottle Space_________ Nat. Battery Room_____________ Nat. Laundry.......... .... .. Mech. Mech. H.B. Mech. Nat. or Mech. Nat. or Mech. Mech. H.B. or D.R. ............... H.B. or D.R. Mech.- - Mech. H.B. or Nat. or D.R. Mech. H.B. or Nat. or D.R. Mech. Mech. D.R. Mech. H.B. Dry Cargo Holds____ -. Stearing Gear Space.______ Mech. or Nat. Mech. or Nat.1 Nat. or Mech. Mech. or Nat. ' H.B. or D.R. 3-6 1-2 3-6 15-20 15-30 .4 / 15-20 6-10 3-6 10 2 1-4 20-30 2-6 May be exhausted through Galleys and Pantries. Tempered air Sup. Tempered air. Sup. Unit Heater it desired. Gyro Room_________ Mech. Passageways.......................... Nat.. Mech. Nat. or Mech. Mech. Nat. - " H.B. or D.R. D.R. , Engine & Boiler Rooms___ Mech. or Nat. Misc. Machinery......... __ Mech. or Nat. Nat. Stair Wells............ ........... __ Nat. Mech. or Nat. Mech. or Nat. Nat. ................ D.R. 6-10 3-6 6-8 _______ * Exhausting or Supplying adjacent Quarters. 1-2 2-4 10 Same as passageways. Exh. at top. H. B.--Hot Blast System. bD. R.--Direct Radiation.- 882 CHAPTER 49 -1946 Guide areas, rather than to attempt to. obtain uniform ambient temperature. The permissible temperature rise at working stations is usually about 15 F while the over-all temperature rise is usually between 30 and 50 F. When the necessary quantity of air has been determined, the venti lation arrangements should be designed so that all of this air will be distributed to locations where the personnel are to be stationed under operating conditions, thus giving them the maximum benefit from the cool air so introduced. This consideration is of vital importance because it must be remembered that the physical well being and alertness of the crew are more important than the operating ambients of the machinery; and by such installation the personnel receives the air before it becomes heated to the temperatures satisfactory for the equipment. In addition to the air supply, these spaces must be exhausted, pre ferably by mechanical means. Every attempt should be made to remove air at or close to heat sources so that the mixing of ambient air with that which has been heated to a higher temperature will be at a. minimum. The quantity or capacity of the mechanical exhaust systems should take into consideration the expansion of the supply air because of heating and should be also sufficient to insure an indraft through access openings to the space. Generally, in order to accomplish this, the quantity of me chanical exhaust should be about 120 per cent of the supply. . In many installations, the combustion air for diesel engines and boilers is taken directly from the machinery space and serves.as a partial mechanical exhaust system. ' . Normally, heat is not required for machinery spaces except for those fitted with electrically operated, equipment, which* may remain inactive during periods while in port. Such spaces should be equipped so as to heat them to about: 50 F during such periods. ; ..... . .' , laving Spaces ' . ' ' ' . " .. . . The minimum quantity'of air required for any space which is fitted for sleeping or office work, including hospital spaces, should be that which will liiriit the temperature rise over the outside air conditions to not more thanTO F (a: rise of 7 F is more satisfactory if practicable), or a minimum of 30 cfm' per person, .whichever is the greater. ; For.spaces:fitted- for eating, recreation, or manual work the rise may be taken at 10 F with not less than 20 cfm per person. .- 1 ........... "' . It will be noted that the quantities, thus obtained are minimum and should be supplied' by mechanical means. This is especially important if the spaces are . located inside of the ship and have; no direct weather exposures with ample openings, such as portholes of windows, which may remain open even :in inclement weather. The same requirement applies , to the necessity for mechanical exhaust, although natural exhaust may be used where only a short run of duct is required. If the air to these spaces is supplied by mechanical ventilation it should enter through registers or diffusing type terminals. The installation of bracket fans within these compartments at'proper locations and of suf ficient number will aid materially, in providing proper distribution for comfort. . .. . ............... .. ' Heat should be furnished to these spaces to maintain the following temperatures when operating in the minimum winter conditions: Staterooms, Berthing, Messing and Office spaces------ :--:-------- 70 F Working spaces and Shops:------------------------------------------------------ 60 F Hospital spaces.:__________________ _____ -------------------------------- 75 to 78 F Marine Heating and Ventilation 883 Toilets, Washrooms, Showers and Baths: Spaces for these purposes should be fitted with mechanical exhaust venti lation for odor and steam removal. They should have one or: more well- located exhaust terminals, overhead; one will usually suffice for the average size space. The supply may be taken naturally. Generally, the surrounding living or working spaces are exhausted through them. The minimum total quantity exhausted should be that which would change the air within the compartment in 6 min, plus 25 cfm for each, fixture, plus 50 cfm for each shower head. Air requirements on merchant vessels are commonly.estimated on the basis of a 4-min rate of change. . . Heating should be obtained by use of convection-type heaters which : should maintain 70 to 80 F for bathing or washing spaces and 70 F for toilet ' spaces when the outside winter temperature is at the design condition. Galleys, Bakeries, and.Food Handling Spaces The problem of the ventilation of spaces fitted for cooking and food preparation is primarily one of heat and smoke or fume removal. Me chanical exhaust is always required for this purpose. The supply may be natural, but the required exhaust capacity will be most satisfactory if arranged for 50 per cent mechanical and 50 per cent natural. . The exhaust quantities are generally large and may be predicated on restricting the ambient temperature rise to about 15 F over the outside summer design air conditions. It will generally be found that the resulting . quantity will change the air in these spaces in about % to 1 min, depending on concentration of equipment. All of the exhaust should be arranged so ' as to remove air from the space through hoods fitted over the cooking equipment and these hoods should contain grease filters over ranges and griddles and should be made readily accessible for frequent cleaning. The mechanical supply when fitted should blow air -directly on the. - personnel but away from the. equipment and so as not to interfere with the flow of exhaust air to the hoods. ' . .. . Generally, no heat is required for these spaces in winter except that the supply air temperature should not be too low. Usually a preheater .; delivering air at about 45 to 60 F should be provided. : "7 . Laundries' '- . ; . The problems in the ventilation of laundries are somewhat: similar to .' those for galleys. ' Heat removal is necessary and best accomplished by the installation of mechanical exhaust through hoods fitted over the heat- producing equipment. - The:supply for these spaces may be all mechanical, or part mechanical - and part natural. The mechanical supply should be distributed through adjustable blast-type terminals at relatively high velocities directed to blow cool air on the torsos of the operating-personnel. Experience indicates that this quantity should be sufficient to change the. air in the spaces in from 1 to 4 min. , . .. . The exhaust should be at least one.air change per.minute and at least equal to 120 per cent of the total supjply so as to insure an indraft of air through the access openings to the space. All exhaust openings within the space should be fitted to be readily accessible for frequent cleaning -and lint removal.' ' . - ' No winter heating is required except that the supply air should be delivered at about 40 to 60 F. 884 CHAPTER 49 1946 Guide Storerooms and Cargo Spaces The ventilation of these spaces should be predicated upon the kind and type of stores or cargo to be carried. For materials which would not be adversely affected by summer tem peratures, no ventilation is required. Also, storerooms or cargo spaces below the water line, in which temperatures would not normally exceed 100 F with the sea water assumed as 85 F maximum, may not require ventilation for certain cargoes. As spaces in these two categories are frequently damp some means of moisture removal must be provided. Chemical dessicants are satisfactory where it is essential to prohibit openings through watertight structure. In other cases a supply of dry air is provided from a central silica gel dehumidification system and distributing ducts, with recirculation used to accelerate the drying process. Where storage spaces must be ventilated to obtain a change of air in .'about 15 to 30 min, in some cases the ventilation is determined by the maximum temperature which the cargo or stores can withstand without damage. Spaces in which inflammable liquids are carried, or where inflammable vapors may be generated, require special consideration. They should be fitted with mechanical exhaust with terminals so located as to remove ' explosive or combustible vapors. The supply to these spaces may be natural and arranged so that good distribution, free from pockets, is assured. ' If stores and cargo, which require some special and constant tempera- ture or humidity control, are carried, special air conditioning equipment must be installed to suit the particular requirements. . SHIP INSULATION In order to properly limit one of the major ventilation heat loads which is that made necessary by heat transmission, and to prevent condensa tion, it is necessary to use insulation judiciously. The principal sources of heat in a ship are the power plant and sun load. The confinement or exclusion of this heat in the structure of a ship is not easy, principally because of the complex structural nature of the beams, stiffeners,, bulk heads, decks and hull. The continuous metal paths offer easy means of heat flow throughout the structure. Insulation like any other component hull part of the ship cannot be used indiscriminately because of weight and space limitations. Therefore higher heat transmission coefficients are accepted for insulated structures of certain classes of vessels, than would be considered satisfactory ashore. On passenger and cargo vessels, the structure is frequently covered with a metal sheathing in order to improve appearance.' Such sfieathing reduces the resistance to heat flow because the necessary supports form a metallic contact that by-passes the insulation. Hull insulation may be either sheathed fill or blanket and board type and should possess certain desirable physical characteristics, namely: 1. Fireproofness. The material must be incombustible and when subjected to high temperatures by fires within compartments it must not give off smoke or harmful gases. If cements are used to secure the material they too must satisfy the same combustible - restrictions. When the exposed surface of the insulation is to be finished with paint, the paint should be fire retardant. Insulation properly used will retard the spread of fires ' within ships. Government regulations govern the construction and insulation of bulk heads to prevent the spread of fire on vessels. . 2. Density. A 6,000 ton warship may have from 13 to 25 tons of hull insulation, Marine Heating and Ventilation - 885 depending on the type of insulation. It is obviously desirable to minimize this dead weight commensurate with other considerations. ._ - .. 3. Thermal Conductivity. It is important that the conductivity of insulation used be 0.33 Btu per (hour) (square foot) (Fahrenheit degree per inch), or less. . 4. Ruggedness. As any exposed or internally applied material is subjected to rough usage aboard ship it must be able to withstand much pounding from the seas and vibra tion from the ship's machinery. " ' 1 5. Verminproof. For sanitary reasons it is essential that insulation harbor no vermin. 6. . .. Applicability. . Because of the necessity of speeding construction of vessels and minimizing costs, insulating materials must lend themselves to easy and ready applica tion. Generally, when cements are used the application is slow and laborious. ' For duct insulation mineral wool-or spun glass are the most commonly used materials. Corrugated asbestos is not recommended because the presence of moisture tends to disintegrate it. Semi-rigid insulation is generally used because it is simplest to install. Blanket type insulation^ are applied only to round or curved surfaces, and are secured with twine and lagged with sewed-on canvas. Semi-rigid type insulation, secured by adhesive, flat wire bands, and corner clips, is lagged with canvas only where exposed. Blanket type insulation is at least 1 in. thick. The thickness of semi-rigid insulation is frequently selected in accordance with the values given in Table 2. Table 2. Duct Insulation Thickness for Use in Ships . Application Thickness In. Tempered air ducts in unheated spaces where a temperature differential Cold air ducts, supplv and exhaust passing through heated spares 14 1 Exposed ducts in heated spaces, carrying reheated air. Concealed ducts carrying reheated air, adjacent structure exposed \4 l Concealed ducts carrying reheated air, adjacent structure not exposed ____ K Ducts serving only the space in which they are located____ _________ _____ Exhaust ducts carrying hot gases (galley, forges, etc.), in living and None .1 Supply ducts in machinery spaces and similar hot spaces, serving spaces other than the hot spaces through which they pass.. -- ______ . 1 1 14 Fans are seldom insulated. Preheaters, are frequently located close to the fresh air intake in order to conserve insulation, and for the same reason zone reheaters are located as close to the zone as possible. Where a reheater serves only one space, the heater is commonly located in the space. . BIBLIOGRAPHY The Ventilation of Ships, by R. McDonald (Journal of the Institution of Heating and Ventilating Engineers (Br) October, 1939). Ventilation and Air Conditioning of the S. S. Panama (Heating and Ventilating, September, 1939, p. 47). ", Air Conditioning the New Mauretania (Healing, Piping and Air Conditioning, July, 1939, p. 431). Heating, Ventilating and Air Conditioning on Shipboard, by J. H. Clarke (Heating, Piping and Air Conditioning, August, p. 467; September, p. 529; October, p. 610, 1940). Care of Cargo at Sea, by O. D. Colvin, W. H. E. Hahne and M. R. Colby (Transactions 886 CHAPTER 49 .1946 Guide of the Society of Naval Architects and Marine Engineers; Part I, Vol. 46, 1938, p. 109; Part II, Vol. 49,1941, p. 208). ' ' -/-' Ventilation of Ships, by J. Dawson (Journal of The Institution of Healing and- Venti lating Engineers, London, Vol. 10, June-July, 1942, No. Ill, p. 89). . ' ' '. Modern Marine Engineers Manual, Vol. II, Sections 16 to 19, Ind. (Cornell Maritime Press, 1943). ', . '" Warship Ventilating, Heating and Air Conditioning, by Comdr. T. H. Urdahl, U.S.N.R., and W. G. Whittlesey (A.S.H.V.E. Transactions, Vol. 5 49, 1943, p. 35). Standardized Heating and Ventilating Equipment for Fighting Ships, by Coihdr. T. H. Urdahl, U.S.N.R. and Lt. John Everetts, Jr., U.S.N.R. (Heating, Piping & Air Conditioning,'July, 1943, p. 333). .. - v .Designing Warship Ventilation, with Standardized Equipment,. by Comdr. T. H. Urdahl, IJ.S.N.R. and W. C. Whittlesey {Heating; Piping & Air Conditioning; August, 1943, p. 419). , ; '. - ; .- ' i - \' ; . "v ` i- CHAPTER 50 . ^J4ot `VUater Suppiy Hot Water Supply Piping, Storage Capacity and Heating Load, Methods of Heating Water, Computing Grate and Coil Surface Areast Controls, Solar Water Heaters, Friction Loss IN computing the total heating load for a building, it is important to . allow ample boiler capacity for heating the hot water supply. The amount of warm water used in any large building is variable, depending on the type of structure, usage, occupancy and time of day. .It is neces sary to provide the piping, water heating and storage facilities of suf ficient capacity to meet the peak demand without wasteful excess in equipment cost. , ' The determination of the amount of water used in residences has been well established over a period of time and as a result, reliable factors for water consumption are available. Tests have been made of the amount of water required by standard fixtures in normal use with water at ordinary pressures so that this.information permits a fairly correct basis of design. HOT WATER SUPPLY PIPING As a result of investigations. conducted at the National Bureau of Standards, basic design principles have been- outlined for the design of the hot and cold-water supply piping requirements in a plumbing system1. It is common practice ;to provide circulating piping in all hot water supply systems in which it is desirable to have hot water available con tinuously at the fixtures. In average sized and small residences and systems, in which the piping from'.the heater to the fixtures is short, return circulating, piping is generally omitted in order to reduce instal lation cost and to reduce heat loss from the piping,'particularly during periods of no water demand. . , .. . - : The hot water supply may be distributed by either an up-feed or down- feed piping system. Three common methods of arranging the circulating lines are shown'in'Fig; l. Although the diagrams apply to multi-story buildings the arrangements (a) and (J>) are sometimes used in residential designs. .. ' ' A check valve should be provided in the run-out from each return riser to prevent temporary reversal of flow in the piping when a faucet is open. Proper air venting of a circulating system is extremely important, par ticularly if gravity circulation is employed. In. Fig. 1 (a) and (b) this is accomplished by connecting the circulating line below the top fixture supply. . With this arrangement, air is eliminated from the system each time the top fixture;is opened. . ' ' . . . Where an overhead.supply main'is located above the highest fixture as in Fig. 1(c), an automatic float type air vent is installed at'the'highest pointof the system or a fixture branch is.connected to the.top of the main where air venting is desired and then dropped to the-fixture outlet. | It is., sometimes, necessary to make an allowance for pressure -drop through the heater when sizing hot water- lines, particularly where in stantaneous hot water heaters are used and the available pressure is low. . 887 ' S8S CHAPTER 50 1946 Guide STORAGE CAPACITY AND HEATING LOAD In estimating the size of hot water storage tank required and the heating capacity to be provided either from the boiler or from an inde pendent domestic hot water heater, it is necessary to know the total quantity of water to be heated per day, and the maximum amount which will be used in any one hour, as well as the duration of the peak load. In cases where the requirements for hot water are reasonably uniform, as in residences, apartment buildings, hotels, and the like, smaller storage capacity is required than in the case of factories, schools, office buildings, etc., where practically the entire day's usage of hot water occurs during a very short period. Correspondingly, the heating capacity must be pro portionately greater with uniform usage of hot water than with inter mittent usage where there may be several hours between peak demands during which the water in the storage tank can be brought up to tempera- ! J l t! > , (0) 1 ^ I "* >% a "" a. 3 ^ J l|i / (b) -- t - t t C :* t / _ __ V \_ J' I 1 \ f' 3 1 * a, a. ' \ " &a. a. 3 \> \ & a. a. 3 CO 1 1_ t^ \+ i. A/ <c> 1^ 1 > /<f Fig. 1. Methods of Arranging Hot Water Circulation Lines ture. As a general rule it is desirable to have a large storage capacity in order that the heating capacity and consequently the size of the heater, or the load on the heating boiler, may be as small as possible. In estimating the hot water which can be diawn from a storage tank it should be borne in mind that only about 75 per cent of the volume of the tank is available, as by the time this quantity has been drawn off the incoming cold water has. cooled the remainder down to a point where it can no longer be considered hot water. ' Where steam from the heating boiler is used to heat domestic hot water, the computed load on the boiler should be increased by 4 sq ft EDR (equivalent direct radiation) for every gallon of?water per hour heated "' 100 x 8 33 through, a 100 F rise'. The actual requirement is------2io -- = ^-48 sq ft per gallon of water heated 100 F. The value of 4 allows for transmission losses, etc. ' There are two ways in common use of estimating the hot water require ments of a building; first, by the number of people and second, by the number of plumbing fixtures installed. Where the number of people to Hot Water Supply 889 be served is known or can be reasonably estimated, the data in Table 1 may be used. -, Example 1. From Table 1, a residence housing five people would have a daily requirement of 5 X 40 = 200 gal per day, and a maximum hourly demand of 200 X M = 28:5 gal. The heater should have a storage capacity of 200 X M = 40 gal and a heating capacity of 200 XM = 28-5 gal per hour. . The conditions given in Example 1 may be cited as average. It is possible to vary the storage and heating capacity by increasing and decreasing one over the other. Such a condition is illustrated in Ex ample 2. Example 2. Assume an apartment house housing 200 people. From the data in Table 1: Daily requirements -- 200 X 40 = 8000 gal. Maximum hours demand = Table 1. Estimated Hot Water Demand per Person for Various Types of Buildings . Type of Building , Residences apts., hotels, etc. Office buildings Factory buildings Restaurants $0.50 meals $1.00 meals $1.50 meals * Restaurants 3 meals per day Restaurants 1 meal per day Hot Water Required at X40 F Max. Hourly Demand in Relation to Day's Use Duration of Peak Load Hours Storage Capacity in Relation to Day's Use Heating Capacity in . Relation to Day's Use 40 gal per person per day 'M 4 H k 2 gall per person per day H 2 M % 5 gal per person per day I -% H 1.5 gal per meal 2.5 gal per meal 4.5 gal per meal Ko H Ho 8 .h 2H Mo Mo M 8000 XH = 1140 gal. Duration of peak load = 4 hours. Water required for 4-hour peak = 4 X 1140 = 4560. ' If a 1000 gal storage tank is used, hot water available from the tank = 1000 X 0.75 = 750. Water to be heated in 4 hours = 4560 -- 750 = 3710 gal. Heating capacity per hour = = 930 gal. . If instead of a 1000 gal tank, a 2500 gal tank had been installed, the required heating .. , _ L 4560 - (2500 X 0.75) ,' capacity per hour would be------------ ------:------------- = 671 gal. Table 2 may be used to determine the size of water heating equipment from the number of fixtures. To obtain the probable maximum demand multiply the total quantity, for the fixtures by the Demand Factor in line 11.. The heater or coil should have a water heating capacity equal to this probable maximum demand. The storage tank' should have a capacity equal to the probable maximum demand multiplied by the storage capacity factor in line 12. Example 3 will illustrate the procedure. 890 CHAPTER 50 -1946 Guide Example 8. Determination.of heater.and storage tank size for an apartment building from number of fixtures. ' 60. lavatories..... 30 bath tubs___ 30 showers_____ 60 kitchen sinks. 15 laundry tubs X 2 -- 120 gal per hour X 20 = 600 gal per hour X 75 = 2250 gal per hour ' X 10 600 gal per hour X 20 = 300 gal per hour Possible maximum demand = 3870 gal per hour Probable maximum demand.................................... = 3870 X 0.30 = 1161 gal per hour Heater or coil capacity.----------- ----------------- ;________ ____________ = 1161 gal per hour Storage tank capacity----------------------------------------- = 1161 X 1.25 = 1450 gal. Table 2. Hot Water ^Demand per Fixture for Various Types of Buildings Gallons of water per hour per fixture, calculated at a final temperature of 140 F Apaet* MENT House Club Gru- ` Hos NA&IUM pital Hotel Indus trial Plant Orncs Prttatb Build Resi School ing ' dents Y.M. CA. 1. Basina, private iavatory_~_ 2 2 2 . 2 2 2 2 2 2, ' 2 2. Basins, public lavatory 4 6 8 6 8 12 6f- . 15 8 3. Bathtubs___ 4. Dishwashers 20 ' 15 20 -30 20 20 30 50-150 ` ` 50-150 60-200 20-100 ' 20 . " 30. 15 20-100 20-100 5. Foot hamtis 3 3 12 3 3 12 - -- 1 3 3 12 - 6. Kitchen sink__ 10 20 -- 20 20 20 10 10 20' 7. Laundry, stationary tuba__ 20 28 28 28 R Pwntnr nintr 5 - 10 ~~ 10 10 .... . i.: 20 5 2810 - 10 9. Showers,..................... 75 150 225 75 75 225 ,, . 75 . 225 225. 10. Slop sink--- 20 20 -- 20 SO 20 . 15 j 15 20 , '20 11. Demand factor ' - ' 0.30 0.30 0.40 0.25 0.25 0.40 . 0.30 '. 0.30 .0.40 0.40 12. Storage rapacity factarl_i 1.25 `0.90 1.00 0.60 ` 0.80 1.00 '2.00 .' 0.70 ' ' 1.00 1.00 - "Ratio of storage tank capacity, to probable,maximum demand per hour. ................ METHODS OF HEATING WATER ................. ^ Hot water may be heated either by the direct combustion of fuel, by an intermediate carrier such as steam or hot water, or by electrically heated surfaces. The simplest method is to have the fire on one side bf a metal barrier and7water on the other. Tn such'a method if the water surfaces ' of heat transfer are small, and if the water carries a-heavy proportion of precipitable salts, the water passages may soon clog and then burn out. A familiar example of such trouble is the water back of the firebox in the kitchen stove or the pipe coil inserted into the firebox of a warm air ' furnace or small boiler.- The critical water temperature, at which the lime, magnesia, etc. collect on hot surfaces, varies with the character and proportions of the solids, but generally such deposits are. not a serious trouble with water temperatures lower thanv 140 F.. Coal-burning direct-fired water heaters 'may be constructed of cored cast-iron. sections or of steel. In some cases the external appearance of 1 the cast-iron sections is the same as in heating boilers; but internally the cores are changed to enable the'sections to withstand the-city water > pressure. In small capacity water heaters, efficiency.is not considered so Hot Water Supply _______, , . .______ | important as low first cost and ability to maintain a fire at a low rate of combustion, and consequently such heaters are,generally built with a dry section or fire-brick lining at the base of the fire-pot to prevent too much chilling of the fuel. While mud and scale will eventually clog the water ways of any direct-fired heater, increased life may be obtained-by pro-viding a three-way cock in the return line between the heater , and the bottom bf the storage tank, so that ..water can be blown through the heater-or the tank separately at full line pressure to clean out loose Cold water inlet Upp,ng Fig. 2; Indirect Water Heater v . 3.Fig. Indirect Water Heater'Mounted on Side of Boiler . .. 4., Fig. Indirect Water Heater Placed in Boiler sediment. Clean-out openings in the bottom of the heater, are advan tageous if used by operators of, water, heaters for..periodic cleaning out ,of sediment. ... , ' , .. / Oil-burning direct-fired water heaters usually are bf steel and operate .with higher flame temperature and better efficiency then commensurate sized coal-burning heaters. They have the same tendency as coal boilers . to lime up, and the water passages should be large in cross-section and accessible for periodic cleaning. .. . | . .. ... Gas-burning direct-fired'water heaters may be of .the instantaiieous.br "storage type. Instantaneous heaters are generally.constructed of spiral water, tubes of copper around which the products of combustion.circulate /. 892 CHAPTER 50 1946 Guide upward from high capacity burners. Storage-type heaters may include in one unit an insulated storage tank, a combustion chamber, flues,, burner equipment and controls, or may consist of a separate storage tank and external direct-fired water heater, which may be a so-called stde-arm heater for small capacity or a gas-fired boiler for larger capacity. Gas boilers used for direct hot water supply must be able to withstand the city water operating pressure. While direct-fired gas heaters are used generally for residences and small installations of 100 gal storage capacity or less, indirect heaters are recommended for larger installations. In the indirect method either steam or hot water is used for heating the water. With steam the water to be heated is preferably circulated around the outside of the steam tubes which are submerged within a tank. A typical indirect heater using steam is shown in Fig. 2. The coils usually are of copper and are [/-shaped to permit expansion and contraction. The shell may be of steel, copper, or with a special inside protective lining. Where straight heating tubes are used, one end of the tube is usually expanded into a floating head to take care of expansion. The coils should be capable of easy withdrawal for inspection and for removal of scale. Instead of steam the heating medium may also be hot water inside the tubes. / Another method of transferring heat from a heating boiler to the domestic water is illustrated in Fig. 3. The water heater is generally a cast-iron shell within which there is located a spiral copper coil. Hot water from the boiler circulates inside the shell and around the coil and returns to the boiler, while domestic water from the storage tank circu lates inside the coil. The storage tank should'be installed with the bottom of the tank as far above the boiler as possible. Horizontal storage ' tanks smaller than 18 or 20 in. diameter are not recommended because of the difficulty of preventing the hot and cold water from mixing, and especially is this an important consideration when large quantities of water are withdrawn. In Fig. 4 the heat transfer surface is'placed inside the boiler instead of in a separate vessel, but otherwise the operation is similar to that of Fig. 3. This arrangement with vertical, tank is com monly used for small domestic installations. Sometimes the heating element is located inside of the larger type fire tube boilers and small residential boilers. In this case the heat transfer surface is in the form of a number of straight- copper tubes with rear U bends or a floating head, inserted through a special opening in the boiler. While the coil may be located in the steam space above the water line of a steam boiler, it operates more satisfactorily when below the water line since clogging of the water tubes may thereby be delayed. This method is widely used without storage tanks since the intimate contact and efficient circulation of the water in this arrangement permit the utilization of the heat stored in the water of the boiler. A thermo static three-way mixing valve is frequently used to maintain a uniform temperature of the hot water supply to the plumbing' fixtures. In order to reduce clogging by precipitated solids, water heating plants sometimes develop steam in a closed circuit, transferring the heat through a tubular heater to the domestic water. The water in the primary . heater, exposed to the high temperature of the fire, is repeatedly used and hence has no appreciable tendency to deposit scale, while the domestic water, heated by steam at a much lower temperature than that of the fire, also exhibits a much reduced tendency to precipitate dissolved salts. Hot Water Supply 893 COMPUTING AREA OF HEAT TRANSMITTING SURFACE The area of the inside surface of a heating coil may be determined from Equation 1. Q X 8.33 fa - <.) . .' - UXim - where A = surface area of coil, square feet. Q = quantity of water heated, gallons per hour. . fi = hot water outlet temperature, degrees Fahrenheit. = cold water inlet temperature, degrees Fahrenheit. U = coefficient of . heat transmission, Btu per (hour) (square foot) (degree Fahren heit logarithmic mean temperature difference); For copper or brass coils U -1 240 (steam) and 100 (hot water). ` ' For iron coils U = 160 (steam) and 67 (hot water). . tm = logarithmic mean of the difference between the temperature of the heating medium and the average water temperature and is approximately. \. . (s = temperature of the heating medium, degrees Fahrenheit. Equation 1 may be used,to check the heating coil ratings under tempera tures other than those stated in the manufacturer's published ratings. Table.3. Coefficient of Heat Transfer of Instantaneous Water Heaters . U -- Btu per (hr) (sqft) (degree Fahrenheit logarithmic mean temperature difference) Boiler Water Temperature. - ......... :....... U ......................................;.................... 210 225 200 175 Example 4. What area of copper transfer surface will be required to heat 70 gal of water per hour from 40 to 180 F with boiler water at 220 F? ,,,,[*-B-iisri-no , For instantaneous submerged heaters the surface required will depend 1 upon (1) the velocity of water in the tubes, (2) the boiler water tempera ture, (3) the inlet water' temperature, (4) the outlet water temperature, (5) the cleanliness of the coil surface, and (6) the condition of the boiler , water surrounding the coil. If the heater is located in the water of an actively steaming part of a boiler the heat transfer may be twice as great as would be obtained if the water surrounding the coil were circulating slowly. Ratings of instantaneous water heating coils will therefore vary greatly depending upon the assumptions made regarding the conditions of operation. The values of the coefficient of heat transmission for instantaneous heaters shown in'Table 3 are conservative. " . For a coil in which heat is transferred from steam to water the value of JJ = 300 y/v may safely be used (v = velocity of water in feet per second). The rate of heat transfer between steam or water as the carrier and the domestic water is influenced by the rate of movement of both the carrier and the water which receives the heat. For this reason, where the transfer occurs from heating system water to domestic, water, it is good practice to install a circulating pump' to insure rapid movement of the boiler water. In view of the high condensation rates obtained when steam is used with. . .894 CHAPTER 50________________ '_____- 1948 Guide gravity circulation from the boiler, as, .when there is a. sudden demand followed by an inflow.of cold water, the bottom of a steam heating trans fer element always should be at least 30. in. above the boiler waterline, and the steam and condensate return pipes should be of liberal size. Otherwise water hammer and reduced capacity may result due to im perfect drainage of condensate. When connecting a transfer-type hot water heater below.the water line of a cast-iron steam boiler having vertical sections, there should be a separate tapping for water circulation into every section of the boiler, as shown in Fig. 3, unless the boiler has large top nipple ports providing inter-sectional circulation. If the top nipples - are entirely within1 the boiler steam space, no internal circulation occurs between sections 'and steaming may occur in sections not connected to the heater and further the unconnected sections will not deliver any heat to the heater. COMPUTING GRATE AREA FOR COAL-FIRED HEATER The grate area required for a small coal-fired water heater may be calculated by Equation 2. .' ,, _ W (<.-<,) X 100 . G - HXEXC , ... (2) where. . ,1 .. . G grate area, square feet. W -- weight of water, pounds per hour. ' . ' ty--h temperature difference between entering and leaving water, degrees Fahrenheit. H = heating value of coal, Btu per pound. ,; C = weight of coal burned, pounds per (hour) (square foot of grate). E = efficiency, per cent. .. In a small heater 4.5 lb is a conservative value for C, and an efficiency of 60 per cent would represent excellent performance. . Example 5. What grate area is required for a coal-burnirig water heater warming 100 gal per hour of water from 50 to 180 F, when the combustion rate is 4.5 lb per hour per square foot of grate; if the heating value of the fuel is 12,500 Btu per pound, and the efficiency is 60 per cent? The quantity of'gas, oil, or. other fuel1 required per hour for water heating may be calculated by Equation 3. ; '. " i -' :. where ..... ... : ... . '. ,, W(tt-h)X 100, . , HX.E .. . ' . (3) - F = Units of fuel (lb, cii ft, gal, etc). . - H *= heating value of fuel, Btu per unit. . .. ,W = weight of water, pounds per hour. . G--h - temperature difference between entering and leaving water, degrees Fahrenheit ' ... ,E = efficiency, percent.. . .. ^ Efficiencies for oil and gas may be taken as 75 and 80 per cent respec tively. The heating value of the fuel and the temperature rise.should be determined, to suit local conditions. : .. . ' CONTROL OF SERVICE WATER TEMPERATURE ' : Coal-fired boilers are usually controlled by an immersion thermostat located in :the heated water, which opens or closes draft , dampers at- the Hot Water. Supply 895 boiler to adjust the rate of fuel, combustion. With oil- or gas-fired boilers the immersion thermostat controls the oil burner motor or the automatic . gas valve. The gas pilot flame usually bums continuously. With electric . heaters the immersion thermostat operates a switch on the source of energy. . . When steam or hot water is the medium for heating the water in the tank, immersion thermostat controls a valve in the steam or hot water supply line. In small residence installations, using water as the carrier, a combined immersion thermostat and butterfly valve all in one simple fitting may be installed in the transmitting circuit to prevent overheating : of the service water. , In residences heated by pump circulated hot water, the house tempera ture is controlled by operating the circulating pump intermittently, while domestic hot water is warmed by transfer from the house boiler, independent of the pump operation. The domestic water is heated from the heating boiler the year 'round. . Under such an arrangement, to prevent overheating the house by thermal circulation when the pump is . not running, it is usual to insert a weighted check-valve in the house heating main, so that no circulation to the house heating system can occur unless the pump operates. In summer the fire may be controlled to maintain a-boiler water temperature lower than when heating and generally about 20 F warmer than that desired in the domestic hot water system. _' ' In buildings which have restaurants it is generally, desirable to install two separate service hot water systems so that water at about 180 F minimum may be available for dish washing, while water at 140 F maxi mum may be' used for lavatory and bath purposes. . The immersion thermostat in a hot water storage tank should be located 1 no higher than the center of the tank, and possibly should be even closer to the bottom since water in a tank stratifies proportionally to the tem perature. When hot water is removed, the cold water entering to replace it quickly reduces the temperature in the lower parts of the tank. , SOLAR WATER HEATERS Solar heaters utilize the" energy of the sun'for heating hot water. The successful operation of such heaters requires the availability of sunshine practically every day. in the year, which has limited their use to Florida and-the southern portions of California. When supplemented-with some other means of gas, coal or- oil water heating, solar heaters may be used in climates where sunshine may be more or less intermittent. They have been used in summer homes as far north as Chicago. When properly installed and proportioned, solar water heaters render satisfactory service especially in climates where the outside temperatures are high and. . extremely hot water is not. necessarily desirable. Such installations consist essentially of a storage tank, heating coil and hot box. The coil is installed in the hot box and is arranged to circulate water to and from the storage tank. The advantage in the use of this type of. heater is the fact that it requires no fuel. The same materials should be used for the coil, circulation -lines and tank. A copper coil is more efficient in absorbing ' heat in the box but galvanized iron or steel may be substituted depending, on the local water conditions, cost and other considerations. . The storage tank must be able to store sufficient heated water for the night period of about 16 hours when the coil is not functioning or is operating under such poor sun conditions as to make its heating effect 896 CHAPTER SO 1946 Guide. negligible. Due to the fact that the no sun period includes the night period when little or no hot water is ued, an available storage.of 50' per cent of the average daily usage is considered adequate. Since about 25 per. cent of stored hot water cannot be drawn out of a storage tank before the incoming cold water reduces the temperature of ail of the water in the tank to an unsatisfactory point for usage, the equation for calculating the storage capacity of the tank becomes: where . Q X 0.50 0.75 0.6660 (4) 5 -- storage capacity of tank, gallons. Q = average daily usage, gallons. Thus for a family of four persons using an average of 40 gal of hot water per person per day the size of the tank would be 4 persons x 40 gal x 0.666 or 106 gal, and the nearest standard size of tank to this theoretical capacity would be used. The tank should be well insulated to prevent undue loss of heat during the 16-hour period when the coil is inoperative, Fig. 5. Solar Heater Tank Connections Coil Inclination and it should be located as high as possible in the building (under the peak of the roof if such exists) so as to secure a maximum circulation head from the coil. The hot water supply to the hpuse, as shown in Fig.. 5, is located at the top of the tank, which serves to vent the air from the tank ' through the hot water faucets as fast as it accumulates. The coil should be of the return-bend type, square or slightly rec- ' tangular in form, and should have the pipes running east and west, with the coil on the south side of the building where it can receive the full sun effect' all day long without shadows from the building itself or from adjacent obstructions such as trees or other structures. The coil should be placed as low as possible in relation to the storage tank level, such as on ' a porch roof, the roof of a one-story extension or, if necessary, even on the ground. Both the coil and the circulation lines should be designed to facilitate the circulation flow as much as possible using long radius copper fittings or recessed galvanized iron fittings to match the materials of the coil, circulation lines and tank. The coil should be inclined as shown in Fig., 6 so that the north 'end is raised above the south, end to secure an angle with the horizontal of about 53 deg. This will result in the inlet Hot Water Supply 897 end of the coil being on the south side (or bottom) and the outlet end being on the north side (or top). This will satisfy conditions along the 30 deg N latitude which includes the portions of Florida and Southern , California where these heaters are most frequently used. . The hot box is usually constructed of wood on the four sides and bottom, and is insulated. Over the top of the box glass sash are placed and the box should be constructed as near air-tight as possible. The interior surfaces should be painted white to reflect the heat while the coil should be" painted black to absorb the heat. . The box need not be deeper than necessary to house the coil and to protect it from the weather. The addition of a light gage copper plate on the bottom of the box to which the pipe of, the coif is soldered, for good metallic contact, will add Table 4. Suggested Solar Heater Design Data2 PiBn on Rats or 30 Gal I Based or Rate or 40 Gal p*b Day pbb Person 1 fee Dat pee Pebsor No. of Occupants in Residence......... 1 2 3 4 5 6 7 81 1 2 3 4 5 6 . 7 8 Hot Water Used at Night, gal per person........ --. ____ . 15 15 15 15 15 15 15 15 20 20 20 20 20 20 20 20 Hot Water Used at Night, gal total__ 15 30 45 60 75 90 105 120 20 40 60 80 100 120 140 160 RetainedIn Tank, 25 per cent, gpL.__ 4 8 11 15 19 23 27 30 5 10 15 20 25 30 35 40 Tank Capacity Required, gal....... . 20 40 59 75 94 113 130 150 25 50 75 100 125 150 175 200 Hot Water Used During Day, gal___ 15 . 30 45 60 75 90 105 120 20 40 60 80 100 120 140 160 Total Water to be Heated: Gal per hour......................... 35 70 .104 135 169 203 235 270 45 90 135 180 225 270 315 360 .... 4.6 9 13 17 21 26 29 34 6 12 17 23 28 34 39 45 Copper Coil Required: 25 50 75 100 121 145 168 192 32 64 96 128 160 192 224 256 Equivalent length 1 in. eoQ. ft....... 100 200 300 400 484 580 664 768 128 256 384 512 640 768 896 1024 Box Sise: 25 50 75 100 121 145 168 192 32 64 96 128 160 192 224 256 Width, ft____ _______ 4 6 7 8 9 10 10 11 A 6 8 9 10 11 12 12 Length, ft____ ____________ . 6 8 11 12.5 13.5 14.5 16.5 17.5 8 10 12 14 16 18 19 21 a Sun Effect and the Design of Solar Heaters, by H. L. Att (A.S.H.V.E. Transactions, Vot. 41, 1935, p. 131). . to the amount of heat received by the coil due to the fact that this plate will receive all of the sun rays which fail to directly strike the coil. The heat from this source is transmitted to the coil through the plate instead of by heating the air surrounding the coil and from which only part of the heat enters the coil, the balance being transmitted through the glass sash: Design data given in Table 4 may be used with some judgment in selecting the size of-solar heater coil and box for a particular application. These data are based on consumptions of 30 and 40 gal of hot water per day per person. , FRICTION LOSS IN WATER SUPPLY PIPING Fig. 7, showing friction loss in fairly rough pipe, has been reproduced from Fig. 4 of Building Materials and Structures Report BMS 79, Water Distributing Systems for Buildings, by Roy B. Hunter, National Bureau of Standards. ' For friction loss in tubing, as well as in smooth - and rough pipe the reader is referred to Figs. 2, 3 and 5 in. the same publication. . 898 CHAPTER 50 ' 1946 'Guide . FLOW IN GALLONS PER MINUTE ' REFERENCES Methods of Estimating Loads in Plumbing Systems,'by R. B. Hunter (National Bureau ofStandard's, -Report BMS65, 1940). Plumbing Manual. Report of the Subcommittee on Plumbing. Central Housing Committee on Research, Design and Construction {National Bureau of Standards, Report BMS66, 1940). Water-Distributing Systems for Buildings, by R. B. Hunter {National Bureau of Standards, Report-BMS79, BIBLIOGRAPHY Laundry, Kitchen, and Hospital Equipment, by H. C. Russell (A.S.H.V.E. Trans actions, Vol. 35, 1929, p. 45). . Water Consumption, Cost anti Savings, by G. C. St. Laurent (American Hotel Association, Hotel Engineering, Vol. 1, 1940). , '' Plumbing.Practice and Design, (1943) by Svend Plum (John Wiley & Sons, Inc.). CHAPTER 5 1 C^ode5 and ^tandardi THE State Codes listed in Table 1 have been compiled from lists supplied by the various states and revised in 1945. These codes can be obtained from the state department indicated. The Codes and Standards listed in Table 2 represent accepted practice, methods or standards prepared and accepted by the organizations indi-' cated. They are valuable guides for the practicing engineer in determin ing test methods, ratings, performance requirements, and limits applying to equipment used in heating, ventilating and air conditioning. Copies can usually be obtained from the organization listed in the reference column. . Table'1. State Codes, Standards or Laws Relating to the Heating, :- Ventilating or Air Conditioning of Buildings . ALABAMA: None. . - - ARIZONA: Law 56-117. Laundry--hours of labor--ventilation--penalty; Laws 65-218,65-231,65-235. Ventilation (with reference to mines). (Secretary of State, State House, Phoenix.) .... . ARKANSAS: Installation of all bailers. Dept, of T^hor Safety Code No. 6 for Industrial Sanitation in Manufacturing. - Establishments, 3.3 Ventilation. (Dept, of Labor, State Capitol, little Rock.) . `. _ CALIFORNIA: Reference to the ventilation lawB may be found in the California Health and Safety Code under the following sections: Sec. 16800--Construction Requirement, Air Ducts; Sec. 16820-16835--Vent Shafts; Sea 16900-16905--Gas. Appliance Vents; Sec. 17080-17088--Garages; Sec. 16233-16235. 16270-16271--Rooms; Sec. 16300-16305--Stairways.' (Supervisor of Documents, 214 State Capitol, Sacramento.) _ - COLORADO: State Boiler Inspection Code on high-pressure boilers--steel, all cast iron, 15 lb or over.', (State Industrial Commission, State Annex Bldg., Denver.) , _ _ , State-Wide Plumbing Code--Rules and Regulations of the Division of Public Health, regarding ventilation of toilet, shower and wash rooms; vents ongas or oil-firedinstantaneous water heaters; construction equipment ofsanitary features in all hgiMingft in the state, including ventilation of allplumbing fixtures. (Div. of Public Health, State Office Bldg., Denver.) Regulations regarding heating, ventilation and lighting, (State Coal Mine Inspector, Argonaut Hotel, Denver.), CONNECTICUT: School Building Code (1941); Chapter 6--Structural and Mechanical, D. Heating and Ventilation (State Dept, of Education.' Div. of Instruction, Hartford.) ' ` Statutes: Section 2566 specifies the number of cubic feet ofair for children and adults in tenement and boarding houses. Section 2584 specifies the dimensions of windows and skylights in tenement house public halls. '7 Section 2585, nmH by 443 f, specifies ventilation required for bathrooms and toilets in tenement houses. 1 Section 2659 concerns heating of leased buildings. ' ' ' . ` ' . Sanitary Code: Regulations 280 and 281 concern ventilation to be provided far industrialprocesses. Regulation 127 concerns ventilation ofall new water closet compartments. (State Dept, of Health, HartforcL) a .7 \ labor Laws (1941): VIIL Industrial Safety, A. General, Sec. 2355-- lighting and sanitary condition of factories. - and round houses: IX. Industrial Health and Salutation, Legislation, Sec. 2355--lighting ami sanitary condition' of factories and round houses. (Dept, of Libor and Factory Inspection, Hartford.) ' , -DELAWARE: Minimum Rtanflurrin for School Buildings and Site (1931). (State Board of Education, Dover.) ' DISTRICT OF COLUMBIA: Building Code (1941), Section 505--Mechanical Ventilation; Section 702, Article 702-04-- Construction of Air Conditioning Ducts. (Dept, of Printing and Binding, Govt. District of-Columbia.). 7 FLORIDA: School Code Law; Laws Relating to Construction Hotels, Apartment Houses, and Public Eating Places. -(Secy. - of State, Tallahassee.) GEORGIA: None. ' ' ' .... ' , IDAHO: None. - . .. . , _ ' ILLINOIS: Laws Relating to Labor and Employment (1943) Health and Safety Act; Workmen's Occupational Diseases Act; - WashRooms mCertrinEmployments;Work UnderCompressed AirAct;Industrial HomeWork. (Secy. ofStateJSpringfield.) Illinois School Taw, Section 15, paragraph 20 is amplified in April, 1940. Educational Press Bulletin with sections on Ventilating and Hgating (Superintendent of Public Instruction, Springfield.) ' ' '_ Jurisdiction over lodging houses, boarding houses, taverns, inns and hotels, specifying the number of cu ft of air space for each person sleeping therein at the same time. (Dept, of Public Health, Springfield.)' _ - General Mining Laws, 14. Ventilation--Quantity of Air. (Dept, of MineB and Minerals, Springfield!) _ - .. INDIANA: Rules and Regulations of the State Board of Health Governing the Construction, Equipment and Maintenance of Sanitary Features of Public and Parochial School Buildings (1943). (Division of Environmental Sanitation, Statc. .Board of Health, 1098 W. Michigan St., Indianapolo.) ' . i. Roles and Regulations of the Administrative Building Council--Article VIII, Sections 19-8-1, 19-8-2 and 19-8-3 Pertaining to Ventilation of Rooms and Phimbing Fixtures. ' Sanitary Dwelling Law. _ . `. Tourist Camp license Law. (Ind. State Board of Health, Indianapolis.) ' a " IOWA: Code of Iowa, Chapter 323, Requirements for Sanitation and Ventilation of Single Family and Multiple Dwellings. ' Code of Iowa, Chapter 73, Ventilation Requirements in Industrial Establishments Pertaining to Health and Safety.' Department of Pdohc Instruction Rules Relating to Heating and Ventilating of School Buildings. (Deptiof Health,' ' Div. Public Health Engr. and Industrial Hygiene/Dea Moines.) _ KANSAS: Statutes of Kansas: G. S. 1935,44-636--Leaves matter to judgment of Factory Inspector in safeguarding Safety and Health of Workers in factories under jurisdiction of State Labor Commissioner. (State Labor Department, 801 Harrison, Topeka.) - ,,' ' Statutes ofKansas: G. S. 1935,49-204,49-205,49-216,49-217. Ventilation of mines under jurisdiction of State Labdr Commissioner. '> G. S. 1935, 36-110; Ventilation in Hotels, Lodging Houses and Restaurants. (State Hotel and Restaurant Board, State House, Topeka.) ` ` ,- KENTUCKY: Statute of Kentucky: Sections 101.010 to 101.990, relating to ventilation of tenement and apartment * bouses in eities of first elite; Section 217.280 provides for the proper ventilation of food establishments; Sections 228.080, 228.090, 228.120, 228.140, 228.150 and 228.170, relating to heating and ventilating of dry cleaning and dyeing establish . raents; Sections 338.070, 338.080 and 338.090, relating to ventilation in rooms containing buffing or grinding machinery; Sections 352.020, 352.030, 352.040, 352.050, 352.080, 352.090, 352.120, 352.150, 351190, 351210, 351320, 352.330, 351340, 351350, 351360, 351370, 352.380, 352.390 and 352.400; also, 352.570, 352.580, 351590, 351600 and 352.610 provide for the proper ventilation of mines. (Kentucky Statute Revision Commission, Frankfort.) .. - 899 900 CHAPTER SI 1946 Guide Table 1. State Codes, Standards or Laws Relating to the Heating, Ventilating or Air Conditioning of Buildings--(Concluded) LOUISIANA: None. ... . MAINE: Regulations bearing on this subject in reference to the installation of plumbing fixtures in closed rooms are outlined in Sections 101 and 102 of tbe State Plumbing Code. . Rules and Regulations Relating to Sanitation of Factories and Mercantile Establishments inetude Sections on Venti lation. (Division of Sanitary Engineering. Dept, of Health and Welfare, State House, Augusta.) MARYLAND: Standard for Maryland School Buildings, Revised, 1941. (State Dept.-of Education, Baltimore.) MASSACHUSETTS: Laws Relating to the Erection, Alteration, Inspection and Use of Buildings (Form A); Regulations Relative to the Inspection of Buildings Which Are Subject to the Provisions of Chapter 143, General LawB (Form B-l). Ventilation of Motion Picture Booths. Laws, Rules mid Regulations Form C. (Dept of Public Safety, Division of i Inspection, 1010 Commonwealth Ave.t Boston.) MICHIGAN: Housing Law of Michigan (1939). (Secretary of State, Capitol Bldg., Lansing.) '- MINNESOTA: Laws Relating to Sanitation, Ventilation and Toilets in Factories, eta Abo Requirements in regard to garages, spray rooms and spray booths. ' General Orders on Dusts, Fumes, Vapors and Gases. (Industrial Commission, State Office Bldg., St. PauL) MISSISSIPPI: Sanitary and Safety Regulations for Industrial Establishments. (Mississippi State Board of Health, Jackson.) MISSOURI: State Labor and Industrial Inspection Laws (1944). (Dept, of Labor and Industrial Inspection, State Office Bldg., Jefferson City.) ` MONTANA: Revised Codes of Montana (1935), Section 1175 refers to ventilation of school buildings. (Secretary of State, Helena.) NEBRASKA: Safety Codes (1937) and Labor Iawb (1943). (DepL of Labor, Lincoln.) ) NEVADA: Nevada Compiled Laws (1929), Sections 5894 and 5715 pertain to School Buildings. Compiled Labor Laws (1937), Part 14, Section 4241 Ventilation of Mines; Part 8, Sea 2817 Ventilation Bunk Houses. (Secretary of State, Carson City.) NEW HAMPSHIRE: Under the provirions of Chapter 215 of the Revised Laws, Safety and Health of Employees, recom mendations arc made in mills, factories, workshops, commercial and mercantile establishments for proper ventilation. (Bureau of Labor, Concord.) - NEW JERSEY: Industrial Code Bulletin and Labor Laws; Sanitary and Engineering Industrial Standards; Abrasive Wheels. Use, Care and Protection; Safety Code for Work in Compressed Air; Foundry Coda (State Dept, of labor, Wallacb Bldg., Trenton.) ` .. NEW MEXICO: Regulations Governing the Heating and Ventilation of Tourist Courts, Tourist Camps, Hotels and Lodging Houses (1939). (Dept, of Public Health, Santa re.) NEW YORK: Commissioner of Education is authorized to determine the requirements for proper ventilation of school buildings. (Commissioner of Education, Albany.) - Codes are enforced by the Department of Labor which contain sections on ventilation requirements pertaining to a number of industrial processes, such as: No. 10 Foundry Code; No. 12 Dust, Fumes and Gases; No. 32 Automobile Spray; No. 33 Rock Drilling; No. 34 Stone Crushing; No. 35 Stone Cutting and Finishing; Nos. 9 and 16 Sanitary Code; No. 17 Mines and Quarries; No. 25 Removal of Toxic Gases in Mines*, Tunnels and Shafts; No. 37 Military Pyrotechnics. (Secretary. Labor Dept., 80 Centre St, New York.) NORTH CAROLINA: North Carolina Building Code (1941) Chapter 14, Heating and Mechanical Ventilation. (North Carolina Insurance Dept., Raleigh.) NORTH DAKOTA: Nona . OHIO: Ohio State Building Codes: No. 102 Theaters and Assembly Halls (1940); No. 103 School Buildings (1938); No. 105 Churches (1938); No. 106 Hospitals and Homes (1936)'; No. 107 Hotels and Apartments (1940); No. 108 Public Garages (1938); No. 109 (1941); Workshops. Factories, Mercantiles and Office Buildings. See also Rule 16, Ventilation (adopted . 1932 by the Ohio Board of Building Standards). (Dept, of Industrial Relations, Div. of Factory and Building Inspection, Columbus.) OKLAHOMA: Bureau of Factory Inspection Bulletin No. 7-A, containing the laws governing tbe inspection and regulation of factories or-other places where labor is employed. Bureau of Factory Inspection Book No. 11-A--Petroleum Industry . Safety Standards. (Dept, of Labor, Oklahoma City.) OREGON: General Safety Manual; Logging Safety Code; Sawmill and Woodworking and Allied Industries Safety Code; Safety Code for Construction Work; Electrical and Communication Workers Safety Code; Safety Code for Arc Welding; Sandblasting and Spray Painting Operations. (Industrial Accident Commision, Salem.) State laws and regulations relating to school buildingB, sanitation, plumbing, heating and ventilation, including factory inspections. (State Board of Health, Oregon Bldg.,' Portland.) PENNSYLVANIA: Regulations For: Abrasive ana Polishing Wheels; Bedding and Upholstery; Brewing and Bottling; Canneries; Cereal Milk, Malt Houses and Grain Elevators; Construction and Repairs; Dry Cleaning; Dry Color Industry; The Storage, Handling and Use of Explosives; Electric Safety Code; Fire and Panic Regulations; Foundries; General Safety Act; Industrial Sanitation; Lead Manufacturing; Paint Grinding; Regulations for Labor Camps; Laundries; Lead Corroding and Lead Oxidizing; Logging, Sawmill, Woodworking. Veneer and Cooperage Operations; Mines other than Coal Mines; Miscellaneous Hazards ana Conditions of Employment; the Manufacture of Nitro and Amido Compounds; Plants Manufacturing or Using Explosives; Printing and Allied Industries; Spray Coating; Tunnel Construction and Work in Compressed Air; Textile Industries. (Dept, of Labor and Industry, Harrisburg.) RHODE ISLAND: Rhode Island Labor Laws (1942). (Dept of Labor, State House, Providence.) SOUTH CAROLINA: None. ^ SOUTH DAKOTA: State Code Section 13.2018 Care of Steam Boilers; Section 27.1711 Ventilation of Hotels, Rooming Houses, Restaurants, Tourist Camps. (Office of State Engineer, Pierra) TENNESSEE: Williams Code of Tennessee. Sections 5342-5343, which deal with factory and workshop ventilation, places of amusement, etc. and the State Agencies charged with responsibility therefor. (Secy, of State, Nashville.) TEXAS: School Building law, Bulletin 382, February, 1938, Article No. 2920, No. 2921, No. 2922. (Dept of Education, Austin.) -- UTAH: 35-1-16. Sanitary Code for Public Buildings and Railway Cara; 35-1-17. Supervision of Bathing Places. (Deptof Engineering, 439 State Capitol Bldg., Salt Lake City.) ' - VERMONT: Public Laws, Rules and Regulations Relating to Public Buildings, Sanitation, Plumbing, Heating and Venti lation (1941). (State Board of Health, Burlington.) VIRGINIA: Mining Laws ofState of Virginia have provisions regarding ventilation in mines. (Dept ofLabor and Industry, Finance Bklg., Richmond.) . WASHINGTON: General Safety Standards: Standard No. 49 Blower and Exhaust Systems; No. 50 Respirators, Helmets, etc.; No. 51 Carbon Monoxide Gas; No. 49 Ventilation; No. 210 Laundry Ventilation; No. 154 Dry Cleaning with Volatile, Inflammable or Explosive liquids. Coal Mining Laws; Occupational Disease Code; Metal Mine Standards; Safety of Persons Employed in Tunnels, Quarries, Caissons or SubwayB; Construction Coda (Dept of Labor and Industries, Olympia.) State also has approved the AJS.M.E. Boiler Codes and Liquified Petroleum Gases Standards of the N.B.F.U. WEST VIRGINIA: A.-S.M.B. Boiler Code for Construction and annual certificates for operation required forall steam boilers operating at more than 15 psi. (W. Va. Dept of Labor, Charleston.) . ' WISCONSIN: Heating, Ventilation and Air Conditioning Code (1939). Applies to public buildings and places of employ ment General Orders on Spray Coating (1939). General Orders on Dusts, Fumes, Vapors and Gases (1941). (Industrial ' Commission of Wisconsin, Madison.) ' WYOMING: None. Codes and Standards 901 Table 2. Codes and Standards Prepared and Accepted by Various Societies and Associations Subject - Title Sponsor ` Reference , Air Conditioning Air Conditioning (150,000 Btu/Hr or less) Air Conditioning (Above 150,000 Btu/Hr) Airplane Code of Minimum Requirements for Comfort Air Conditioning (1938). A.S.H.V.E. AB.R.E. AJ3JLV.E. Code and Manual for the Design and Instal N.WA.H. A A.CA. N.W.A.H. A A.CA. lation -of Warm Air Winter Air Conditioning . No. 7 Systems (1945). The Technical Code for the Design and Instal N.WA.H. A A.CA. N.WA.H.A A.CA. lation of Mechanical Warm Air Heating Sys tems (1942). Aeronautica^Recommended Practice for Heating and Ventilating Airplanes (1943). SAB. SAB. ARP 85 Airplane Boilers Aeronautical Recommended Practice for Internal Combustion Type Airplane Heaters (1945). S.A.E. ' 1=B=R Testing and Rating Codes for Low Pressure Heating Boilers (1945).' . l.BJl. SA.B.' ARP 143A J.B.R. Boilers ' Net Square Feet Radiation Loads in 70 Deg Fahr, Recommended for Low Pressure Heating Boilers (1943). H.P. A A.C.CJf.A. H.P. A A.C.C.NA. Boilers Boilers , Boilers Boilers Boilers . `Boilers Boilers Boilers (Steel) Net Load Recommendations for Heating Boilers. E.P. A A.C.C.NA. Standard and Short Form Heat Balance Codes for Testing Low Pressure Steam Heating Solid . Fuel Boilers (Codes 1 and 2>(1929). A.S.H.V.E. A.S.H.V.E. Performance Test Code for Steam Heating Solid Fuel Boilers (Code No. 3) (1929). A5.H.V.E. A.SJLV.E. Standard Code for Testing Steam Heating Boilers Burning CHI Fuel (1932). A.S.H.V.E. AJ3.H.V.E. Standard Code for Rating Steam Heating Solid Fuel Hand Fired Boilers (Revised April 1930). A.SJLV.E. ' A.SJLV.E. Standard Code for Testing StokerFired Steam-Heating Boilers (1938). AJ3.H.V.E. AB-M.E. Boiler Construction Code for Low Pressure Heating Boilers. '' Steel Boiler Institute Rating Code for Com ' mercial Steel Boilers and Residential Steel Boilers (1945). - . AB.MB. S.B.I. ' H.P. A A.C.CJiA. AH.H.V.E. .. A.S.H.V.E. , AJ3JI.V.E. AJSJLV.E. AJ3.H.V.E. ' A.S.M.E. S.BJ. Boilers (Steel) Simplified Practice Recommendation for Steel Firebox Heating Boilers (1937). s:B.i. BJS. R157-37 Burners (Gas) American Standard Testing Requirements for Gas Conversion Burners (1941). A.G.A. A.SA. Z21.17-1940 Burners (Gas) ---- American Standard Requirements for Instal lation of Gas Burning Equipment in Power Boilers (1942). A.O.A. ABA. Z21.33-1942 Burners (Anthracite) Commercial Standard for Domestic Burners for Pennsylvania Anthracite (Underfeed Type) (1940). . BB:A.1A. B.S. CS4S-40 Burners (Oil) Cleaners (Air) Color Scheme (Piping) Commercial Standard for Mechanical-Draft Oil Burners Designed for Domestic Installations . (1942). A.S.H.VJE. Standard Code for Testing and Rating Air Cleaning Devices Used in General Ventilation Work (1934). Scheme for Identification of Piping Systems (1945). . BB. O.BA. . A.S.H.V.E. H.P. & A.C.CBA. BJS. CS7S-42 See A.S.H.V.E. Tban&actions, Vol. 39,1933, p. 225 H.P. A A.C.C.NA. Engrg. Stds., Sea 2, Part V Color Scheme (Piping) Scheme- for Identification of Piping Systems (1928). - ABM.E. Coils ' Proposed Commercial Standard for Rating and Testing Air Cooling Coils Using Non-Volatile Refrigerants (1945). . B.C.MA. B,S. Compressors ' Tentative AJSJR.B. Standard Methods of Rating " AB.R.E. and Testing Refrigerant Compressors. ` A.S.H.V.E. A.C.R.MA. ABA. A13-1928 bb: T.S.4044 AB.R.E:: Circular No. 23 902 CHAPTER 51 '1946 .Guide Table 2. Codes and Standards Prepared and Accepted, by Various Societies and Associations--(Continued) SUBJECT . Title . Sponsob . Reverence Condensers ' . _ A EBB. Standard Methods of Bating and Testing Evaporative Condensers. AEJLE. AJ3.H.V.E. A.C. & R.MA. AE.RE. Circular No. 20 Condensers Tentative A EM.E. Standard Methods of Bating Water-Cooled Refrigerant Condensers. Condensing Units * AEJUS. Standard Methods of Rating and Testing Mechanical Condensing Units (1940). Condensing Units . Commercial Standard for Commercial Electric Refrigeration Condensing Units (1945). Conductivity . Standard Method of Test for Thermal Conduc tivity of Materials by Means of the Guarded Hot Plate (Tentative) (1942). . Convector Convector ARJBLVJL Standard Code for Testing and Rating Concealed Gravity Type Radiation (Steam Code) (1931). - AJ3.H.V.E. Standard Code for Testing and - Rating Concealed Gravity Type Radiation (Hot Water Section) (1933). AJS.RJ2. AH.H.X.E. A. <& RJtA. AEMB. ABJLV.E. A.C. <fe R.M.A. BE. . S.R.CA. ABBE. . Circular No. 22 . ABBE. Circular No. 14-41 BE. CS107-45 AJ3JLV.E. AEBE. AE.TM. NB.C. ' A&H.V.E. AE.SLVE. AJ3.H.V.E. Transactions, VoL 37,1931, p. 367 r ` -AJ3.H.V.E. ABJELV.B. Transactions, VoL 39, 1933, p.237 Coolers (Air) Proposed AJSJRJS. Standard Methods of Rating and Testing Forced Circulation and Natural ' ConvectionAirCoolosforRefrtgeration(1945). ABBE. , A.SJH.VJ2. A.C. '& R.MA. R.E.MA. ' ABBE. Circular No. 25-44 Coolers ' - Tentative AEJM3. Standard Methods of Rating AE.RE. and Testing Water and Brine Coolers. AB.H.V.E.. . A.C. & R.MA. . AEM.E. Circular No. 24 Cooling Units Ducts and Fittings Standard Methods of Rating and Testing Self Contained Air Conditioning Units for Com fort Cooling (1940). ' ' Simplified Practice Recommendation for Pipes, Ducts and Fittings for Warm Air Heating and Air Conditioning (1945). ABBE. AJ3.H.V.E. RAfA. NE.MA. - A.C.MA. Mfn. BE. ' AE.R.E. Circular No. 16 - BE. R207-45 . Exchangers (Heat) Standards of Tubular Exchanger Manufadurert Astociation (1941). - T.E.MA. TE.MA. . Exhanst Systems American Standard for Grinding. Polishing, and Buffing Equipment Sanitation (1941). . . A.FA. . AEA. Z43-1941 Exhaust Systems . Tentative Code of Recommended Practices for Testing and Measuring Air Flow in Exhaust Systems (1937). . A.FA. ' A.FA. Preprint 36-27 . Exhaust Systems Tentative Recommended Good Practice Code and Handbook on the Fundamentals of Design, Construction, Operation and Maintenance of Exhaust Systems. ' A.FA. A.FA. Fans Fans '` ' - Standard Test Code for .Centrifugal and Axial N.A.F.M. Fans (1938). . \ a^.hv.e: ' - NJSAfA. Fan Standards (1944). NEJfA. NA.FM. .. -Bulletin No. 103 NEJAA. PubL 44-95 Fire Prevention Buildiog Code Recommended by the National Board of Fire Underwriter* (1943). * N.B.F.U. N.B.F.U. Fire Prevention . Fire Prevention National Fire Codes (1944). National Fire.Code for the Prevention of Dust Rrplnainna (1943). ' N.F.PA. N.F.P.A. - N.F.PA. n.f.pa: Furnaces (Duct). , American Standard Approval Requirements for Gas-Fired Duct Furnaces (1942). A.GA. AEA. Z21.34-I942 - Furnaces (Gas, Floor) Furnaces (Gas) Commercial Standard for Gas Floor Furnaces-- Gravity Circulating Type (1942). ' BE. - ' BE. . - ' A.0AE.M: C899-42 American Standard Approval Requirements for . Central Heating Gas Appliances (1943). A.GA. ' ' AEA." Z21.13-1943 Furnaces.(Forced Air,. ' Solid-Fuel) >- Commercial Standard for Solid-Fud-Burning F.HA. Faced Air Furnaces (1944). : . . N.WA.H. AXJA. A.I.L. - - BE. ' CS109-44 Codes and Standards 903 Table 2. Codes and Standards Prepared and Accepted by Various Societies and Associations--(Continued) Subject Titls ; Sponsor ' Reference Furnaces (Oil-Fired) Commercial Standard for Warm Air Furnaces Equipped with Vaporising Pot Type (HI Burn ers (1943). . -. ' Mfn. ' BE. . BE. CS(E) 104-43 Furnaces (Oil) ' A Tentative Code fa Testing Oil-Fired Furnaces. N.W.AM. & A.CA. N.WA.B. & A.CA. Furnaces (Oil) t , Commercial Standard fa Oil' Burning Floor Furnaces Equipped with Vaporising Pot-Type y'; Burners (1944). - . BE. OBA. . BE. CS113-44 Garages . - ; Code of Minimum Requirements fa Hp*ting and Ventilating Garages (1935). A-S.H1V.E. AB.H.V.E. Gases (Toxic) and Dust American Standard Allowable Concentration of . Harmful Gases: . . ' - Carbon Monoxide' ' ' .' . Hydrogen Sulfide - -" Carbon Di-sulfide -. Bensene - [ '. .. Cadmium AEA. A.S.A. Z37.1-1941 Z37.2-1941 . Z37.3-1941 - Z37.4-1941 Z37.S-1941 ' Manganese .. ' ; - ' : Chromic Acid Mercury - Chromates ' Metallic Arsenic and Arsenic Trioxide Z37.6-1942. . Z37.7-1943' Z37.8-1943 Z37.9-1943 Xylene Lead and Certain Inorganic Lead Compounds Toluene Oxides of Nitrogen Methanol ' .- Z37.HM943 Z37.11-I943 Z37.12-1943 . Z37.13-1944 Z37.14-1944 . * Styrene-Monomer Formaldehyde . . Z37.15-I944 . Z37.16-1944 1 Mineral Wool - Commercial Standard far Mineral Wool: Blank ets, Blocka, Insulating Cement, and Ripe Insu lation fa Heated Inoastrial Equipment (1944). BE. 1M.WJ. BE. CS117-44 Mineral Wool Commercial Standard fa Mineral Wool: Loose, Granulated, or Felted Form, in Low Tempera ture Installations (1943). - be. I.WJfJ. BE. CS105-43 Mineral Wool Recommended Commercial Standard fa Indus trial Mineral Wool Products--All Types-- Testing and Reporting. I.M.WA. BE. BE. ' TS-4030 Piping American Standard Code fa- Pressure Piping (1942). .* AE.M.B. . ' AEA. ` B31.1-1942 Pumps Radiators - Hydraulic Institute Test Code fa Centrifugal Pumps. Hydraulic Institute Test Code for Rotary Pumps (1943). __ 'Code fa Testing Radiators (1927). . H.I. Ai.H.V.E. B.I. Section F . A.S.H.V.E. Radiators Simplified Practice Recommendation fa Cast Iron Radiators (1943). . . I.B.R. BE. BE. R174-43 Refrigeration (Mechanical) American Standard Safety Code for Mechanical Refrigeration (1939). . ABBE. aebe. : Circular No. 15 - Refrigerators (Household) ' American Standard Test Procedures fa House hold Electric Refrigerators (Mechanically Oper ated) (1944). . ' : ABBE. UE.DA. . AEA. - . B38.2-1944 , Sound ` Sound Measurement Test Code fa Centrifugal and Axial Fans (1942). ' NA.F.M. NA.FM. Bulletin No. 104 Sound ' - ' American Recommended Practice fa the Cali bration of Microphones (1938). ' . AE.ofA. . ' A.S.A: ' . Z24.4-1938 Space Heaters ' American Standard Approval Requirements fa Gas Space Heaters (1942). . A.GA. AEA. Z21.11-1942 . Space Heaters Commercial Standard fa Fhze Connected.Oil- ' Burning Space Heaters Equipped with Vapor ising Pot-Type Burners (1943). -' l.C. & HA.M. BE. . CS101-43 Stokers Code fa Determination of Rated Capacities of Anthracite Underfeed Stokers (1944). , S.MA. ` ' 8MA. Stokers ' Code fa Determination of Rated Capacities of Bituminous Underfeed Stokers (1944). SJfA. S.MA. 904 CHAPTER 51 1946 Guide ` Table 2. Codes and Standards Prepared and Accepted by Various Societies and Associations--(Concluded) Subject . Title Sfoksob Rbfebekce Stokers Stokers Unit Heaters Unit Heaters Unit Heaters Unit Ventilators - . Vacuum Pumps Warm Air (Gravity) Water Heaters Water Heaters ' Recommended Minimum Firebox Dimensions and Base Heights (1944). S.MA. S.MA. Recommended Standards Governing Minimum 8etting Heights (1944). SMA. S.MA. Standard Code for Testing and Rating Steam . Unit Heaters (1930). ' AH.H.V.E. I.UMA. AAH.V.E. I.UMA. Standard Code for Testing Hot Water Unit Heaters (1942). - I.UMA. I.UMA. American Standard Approval Requirements for . Gas Unit Heaters (1940). A.GA. AMA. Z21.16-1940 A.S.H.V.E. Standard Code- for Testing and Rating Steam Unit Ventilators (1934). A.S.H.V:E. A.S.H.V.E. A.S.H.VJ3. Standard Code for Testing and Rating Return line Low Vacuum Heating Pumps (1934). - A.S.H.V.E. A.S.H.V.E. Gravity Code and Manual for the Design and N.WAM. A A.C.A. N.WAM. A A.C.A. Installation of Gravity Warm Air Heating 8ystcma (1945). ,, Section No. 5 NM.MA. Standards for Electrio Water Heaters (1945). NM.MA. i N.E.M.A. 45-104 American Standard Approval Requirements for Gas Water Heaters (1944)'. - A.GA. ' AJSA. ` Z21.10-1944 ' ABBREVIATIONS A.CMA* .Air Conditioning Manufacturers Association. M A.C.A R.M.A. Air Conditioning and Refrigerating Machinery Association. * A.F.A. . American Foundrymen's Association. A.GA. ; American Gas Association. - A.G.A&M. Association' of Gas Appliance and Equipment Manufacturers. AIL. Anthracite Industries Laboratory. . . AJSA. American Standards Association. " * AJi. of A.- Acoustical Society of America. . . A.S.H.V.E. American Society of Heating and Ventilating Engineers. . AJS.RJS. American Society of Refrigerating Engineers.' AM.TM. American Society for Testing Materials. BM. National Bureau of Standards. ' -. `FMA. Federal Housing Administration. H.I. Hydraulic Institute. B.P. A A.C.C.NA. Heating, Piping Air Conditioning Contractors National'Association. I.BJi, Institute of'Boiler and Radiator Manufacturers Association., I.CMA.M.' Institute of Cooking and Heating Appliance Manufacturers. I.M.W.I. Industrial Mineral Wool Institute. ` _ .. I.UMA. . Industrial Unit Heater Association. ^ '` NA.F.M: . ' National Association of Fan Manufacturers. * . nm.m.a: N.F.PA. ` National Electrical Manufacturers Association. National Fire Prevention Association. -' NM.C. National Research Council. ' ' . O.BJ. ' , Oil Burner Institute. '. ' OJA. ' Office of Price Administration. RJSJSA. Refrigeration Equipment Manufacturers Association. . -- RMA? Refrigerating Machinery Association. ' ' . 5.BJ. SJ2.C.A. Society of Automotive Engineers. v Steel Boiler Institute. ' ' . Standard Refrigeration Compressor Association. ; - TMJSA. - UjS.D.A. Tubular Exchanger Manufacturers Association. ' ' , . . . United States Department of Agriculture. ' ' '. Superseded 1940 by'A.C. A R.MA. T* CATALOG DATA SECTION INDEX TO ADVERTISERS PAGE 907 INDEX TO MODERN EQUIPMENT . PAGE 913 8S&' INDEX TO ADVERTISERS Heating Ventilating Air Conditioning Guide, 1946 A . Page ACME INDUSTRIES, INC., Jackson, Mich............................................ 1030 AEROFIN CORP., 410 S. Geddes St., Syracuse 1, N.Y........ 1031,1032,1033 AIR & REFRIGERATION CORP., 475 Fifth Ave., New York 17, N. Y.:.. 939 AIR. CONTROLS, INC. (Div. of The . Cleveland Heater Co.), 2311 Superior Ave., Cleveland 14, Ohio___ ,........ 1049 vAIR' DEVICES, INC.; 17 East 42nd SL, ; New York 17, N. Y. .. 1080,1081 AIR-MAZE CORP.,THE, 5202 Harvard Ave,, Cleveland, Ohio........ :.. 1004,1005 AIRTEMP, DIV. OF CHRYSLER CORP., Dayton, Ohio.............. 966, 967 AIRTHERM MANUFACTURING CO.,. ' ` 728 S.. Spring Ave., SL Louis 10, . : .Mo............. ....... ........................... 976 ALCO VALVE CO., 851 Kingsland Ave., SL Louis 5,'Mo........................ 1118 ALFOL INSULATION CO;, INC., 155. I East 44th SL, New York17, N. Y..... 1246 AMERICAN AIR FILTER CO,, INC. - 673 Central Ave., Louisville, ' 5. Ky..................................... ...1006,1007 (AMERICAN ARTISAN (publication), '. 6 N. Michigan Ave., Chicago 2, III 1277 ^AMERICAN BLOWER CORP., P. O. : Box 58, Roosevelt Park Annex, -. Detroit 32, Mich.................... ,.940,941 AMERICAN BRASS CO.. THE,Water- " ' bury.88. Conn;...... .. .1104,1105 AMERICAN. COOLAiR CORP., 3606 Mayflower. St., Jacksonville 3, ", Fla,....,.... 1050,1051 AMERICAN DISTRICT STEAM CO., North Tonawanda,'N. Y.. . *... .4226,1236 AMERICAN. FLANGE & MFG. CO., INC., 30 Rockefeller Plaza, New ' York 20, N. Y.. .:. . ... . . . .......... 1247 AMERICAN FOUNDRY AND FUR - -NACE' CO., P. O. Box 904, Bloom-, mgtori. Ill;:.;... . ......... -. .962, 963 :r..AMERICAN METER CO., INC., 60 East:42nd SL, New .York 17, N. Y. .. ...1119 AMERICAN MOISTENING CO;, (--Providence 1; R. I.....:. S.i ;........ r 1021 ' .. Page AMERICAN RADIATOR & STAND ARD SANITARY CORP, Pitts burgh, Pa..................................1148,1149 AMERICAN ROLLING MILL CO., THE, 703 Curtis SL, Middletown, ' Ohio.............................. 1097 AMERICAN SOCIETY OF REFRIG ERATING ENGINEERS, 40 West 40th SL, New York, N.Y........... .:. 1273 AMERICAN 3 WAY-LUXFER PRISM CO., 24 N. Pulaski Rd., Chicago 24, . III. ...:...........:_____ __________ _ 1239 ANDERSON PRODUCTS, INC., Cam bridge 39; Mass........... ................ 1233 ANEMOSTAT CORP. OF AMERICA, 10 East 39th SL, New York 17, N. Y.. 1082 APRIL SHOWERS CO., 4126 Eighth SL, N.W., Washington 11, D.C.\, ..: 1022 ARMSTRONG CORK CO., Lancaster, Pa......... .................................. 1248 ARMSTRONG MACHINE WORKS, -851 Maple St., Three Rivers, ' . Mich................................... 1224,1225 ATLANTIC METAL HOSE CO., INC., 112 West 64th SL, New York 23, N.Y. 1101 AUTOMATIC BURNER CORP., 1823 Carroll Ave., Chicago, III.............. 1181 AUTOMATIC PRODUCTS CO., 2450 ' North 32nd SL, Milwaukee, Wis..... 1120 AUTOVENT FAN & BLOWER CO;, DIV., HERMAN NELSON CORP., Moline, III............ 993 . . ;V b ' .' BABCOCK & WILCOX CO., THE, 85 :' Liberty SL, New.York 6, N. Y....... 1150" BADGER CORP., 341 E. Brown SL, r Milwaukee 12, Wis.r>.......... 1012 E. B. BADGER & SONS CO., 75 Pitts ' ( SLyBoston 14, Mass...:.. .-.11.10,' 1111 BAHNSON CO., THE, Winston-Salem, - : 1 N. C. ............ ..... ... ............:.: . .942, 943 BAKER ICE MACHINE CO., INC., . ^ 1530 Evans SL, Omaha. Nebr.1038 . 8ALdV< IN-KILL CO , 543 Kiagg Ave., , Trenton 2, N. J... .. . _____-. .1249. 907 i ; : o: 908': -' :_____ ' / y . , ~ . , 1946 'Guide BARBER-COLMAN CO., Rockford, III............... ............. 1084,1121 BARNES & JONES, INC., 129 Brook - side Ave., Boston, Mass..................... 1205 -BAYLEY BLOWER CO., 1817 S. Sixty-Sixth St, Milwaukee 14, Wis.. 1052 BELANGER FAN & BLOWER CO., 1230 Eighteenth St., Detroit 16, . Mich.............:.......... ............ 1054; 1055 . BELL & GOSSETTCO., Morton Grove, III................. 1196,1197 COMBUSTION ENGINEERING CO, INC, 200 Madison Ave., New York . 16, N.Y............................... 1176 COMBUSTON EQUIPMENT DIVI SION, TODD SHIPYARDS CORP, . 601 West 26thSt,, New York 1, N.Y. 1182 CONDENSER SERVICE & ENGI NEERING CO,.INC, 95 River St, Hoboken, N.J....... ................. 1034 W. B. CONNOR ENGINEERING CORP, 114 East 32nd St, New York 16, N.Y............... 1008,1009,1085 BETHLEHEM STEEL CO., Bethle- CORK INSULATION CO, INC,,155 . .' ..hem. Pa.....................................1098 . East 44th St, New York, N.Y,-,.,. 1251 BIGELOW CO., THE, 105 River St, CRANE CO, 836 S. Michigan Ave, . New Haven 3, Conn,...................1151 Chicago 5, III, ......................... 1154,1155 G. C. BREIDERT CO., 634 S. Spring St., Los Angeles 14, Calif................... 1083 BROWNELL CO., THE, Dayton, Ohio 1175 BRUNNER MANUFACTURING CO., .Utica, N,Y...................... 1039 BRYANT HEATER CO., THE, 17825 . St Clair Ave., Cleveland; Ohio........ 961 BUFFALO FORGE CO., 450 Broadway Buffalo, N.Y...................:............ 1056 BUFFALO PUMPS, INC., 450 Broad way, Buffalo, N. Y............. 1201 . BURDEN CO., 1151 S. Broadway, .Los Angeles 15/Calif., r.......... .1053 CURTIS REFRIGERATING MA CHINE DIV. OF CURTIS MANUFACTURING CO, 1959 Kienlen . Ave, St Louis 20, Mo....................... 1040 CYCLOTHERM CORP, 90 Broad St, New York, N.Y.,............ 1153 . ' D" - ` DeBOTHEZAT FANS DIV, AMERI CAN MACHINE & METALS, INC, East Moline, III......... 1059 CHARLES DEMUTH & SONS, 245 , Elm Place, Mineola, N.Y,,,. -- 1086 ;, BURNHAM BOILER CORP., Irving - ton-on-Hudson, N. Y............... 1152 . ' C ' . CAMPBELL HEATING CO., 31st and _ 'Dean, Des Moines, Iowa........... .964, 965 PHILIP CAREY MFG. CO, THE, .. Lockland, Cincinnati, Ohio..-... '1252,1253 CARNEGIE-ILLINOIS STEELCORP, Pittsburgh, pa. .......... 1100 - CARRIER CORPir. Syracuse- 1, - N.Y,...,..,,;................... ... ...944, 945 DETROIT LUBRICATOR CO. (Div. of American Radiator & Standard. . Sanitary Corp.),- 5900 Trumbull Ave., Detroit 8, Mich......... ............... 1122,1123 DETROIT STOKER CO, 5-125 Gen eral Motors Bldg.; Detroit Mich, , .1177 DOLE VALVE CO, THE, 1933 Carroll Ave, Chicago 12, III,:........... ; -- . 1234 DOLLiNGER CORP, 6 Centre Pk, Rochester 3, N. Y............. , , .1010,1011- DOMESTIC ENGINEERING (Pub lications), 1900 Prairie Ave, Chicago .16, III....................... 1275 CELOTEX CORP,THE,120 S. LaSalle St., Chicago 3, III.:................... 1250 DOW CHEMICAL CO, THE, Mid land, Mich................... 1114 CHAMPION BLOWER & FORGE ' CO./ Lancaster, Pa.......... .................. 1057 CHELSEA PRODUCTS, INC, 1206 Grove St, Irvington IT, N.J.........:.. 1058. CHICAGO METALHOSE CORP, ' . -Maywood, III............... 1102 CHICAGO PUMP CO, 2330 Wolfram , St,Chicago18, 111, .......... ... , . 1204 CHRYSLER AIRTEMP, DIV. OF* '-> CHRYSLER CORP., Dayton; . . Ohio . . ..: 986, 987 CLARAGE FAN. CO, ..Kalamazoo, . - Mich, . . ....946 DRAVO CORP, HEATER DEPT, Dravo Bldg, 300 Penn Ave, Pitts-, ' burgh 22, Pa..... ... ........................ 978, 979- C. A. DUNHAM CO, 450 E. Ohio St, Chicago, III, 1206,1207,1208,1209,1210 ... ' E ' . . - ' EAGLE-PICHER CO, THE, American * Bldg, Cincinnati 1, Ohio......./ .. 1254 ELECTROMODE CORP, (Div. : . American Foundry Equipment Co.), -. - So. Byrkit St, Mishawaka, Ind, .. . . 977. ENTERPRISE ENGiNES FOUNDRY " : COAL-HEAT (publication), 20 W. V Jackson Blvd, Chicago, III................ 1274 CO, 600 Florida St, San.Francisco, .Calit....... 1183 . Index to Advertisers 909 F Page Page FARR COMPANY, Los Angeles, Calif. 1013 FARRAR & TREFTS, INC, 20 Milburn St. Buffalo 12. N.Y.,,......................1158 HOFFMAN SPECIALTY CO, INC, . ; 1001 York St, . Indianapolis 7, lnd,,,....................... 1213,1214,1215 FEDDERS-QUIGAN CORP., 85 Tonawanda St, Buffalo, N,Y.___ 980 I FITZGIBBONS BOILER CO, INC, 101 Park Ave, New York 17, N. Y.................... 1156,1157 FRICK CO, (Inc.), Waynesboro, Pa,. 1041 FRIEZ INSTRUMENT DIV, BENDIX AVIATION CORP, Towson, Balti- more4, Md............................. 1128 FUELOIL AND OIL HEAT (publica- - tion), 232 Madison Ave, New York 16, N.Y, 1276 FULTON SYLPHON CO, THE, Knoxvilla, Tenn........... ............. . , 1124,1125 G G & O MANUFACTURING CO, THE . 138 Winchester Ave, New Haven, . . ; -Conn--;........... 1035 GAR WOOD INDUSTRIES, INC, 7924 Riopelle St., Detroit 11, Mich.............. ......... ;.................. 974, 975 GENERAL CONTROLS,. 801 Allen . . Ave, Glendale 1, Calif............ 1126,1127 GENERAL ELECTRIC CO, Bloom field, N.J....:..................... 948,949 GENERAL ELECTRIC CO, Schenec tady, N. Y....,.................. 1076,1077 ILG ELECTRIC VENTILATING CO, 2832 N. Crawford Ave, Chicago, III........ ............................... 982,1060,1061 ILLINOIS ENGINEERING CO., Chicago 8, III............................ 1216,1217 ILLINOIS TESTING LABORA TORIES, INC, 422 N. LaSalle St, Chicago, III................ 1132 INDEPENDENT REGISTER CO, * THE, 3747 East 93rd St, Cleveland 5, Ohio......................... ........... :......... 1090 INGERSOLL STEEL, DIVISION (Borg-Warner Corp.), 310 S. Michi gan Ave., Chicago 4,-111___ __ .1240, 1241 INSULITE, 500 Baker Arcade Bldg, . Minneapolis 2, Minn....... ...,.1256, 1257 INSUL-WOOL INSULATION CORP, Wichita, Kan,..........................:......... 1255 INTERNATIONAL BOILER WORKS ~ CO, THE, 350 Birch St, East . Stroudsburg, Pa.............. :................. 1159 INTERNATIONAL EXPOSITION CO, . Grand Central Palace, New York 17, N. Y........................... 1147 IRON FIREMAN MANUFACTURING CO, Portland, Oregon.........:. 1178,1179 GRINNELL CO, INC, Providence 1, R. L....................... 981, .1112,1113,1211 , J JADEN MFG. CO, Hastings, Nebr.... 983 -. H JENKINS BROS.; 80 White St, New York 13, N.Y.................................... 1235 WILLIAM S. HAINES & CO, 12th JOHNS-MANVILLE, 22 East 40th St, . and Buttonwood Sts., Philadelphia New York 16, N. Y. ........... 1258,1259 , 23, Pa............................................. 1212 S. T. JOHNSON CO, 940 Arlington ARTHUR HARRIS & CO, 210-218 N. Ave, Oakland .8, Calif........ 1184,1185 Aberdeen St, Chicago 7, III......... 1115 HARt & COOLEY MANUFACTUR JOHNSON SERVICE CO, Milwaukee, Wis.:,................................... . .1130,1131 ING CO, Holland, Mich..,.. .1088,1089 JONES & LAUGHLIN STEEL CORP, HARTZELL PROPELLER FAN CO, Jones & Laughlin Bldg, Pittsburgh (Div. of Castle Hills Corp.), Piqua, 30, Pa.......................... .................: .. 1099 , Ohio:.............. 1064 ' .- -v- - - ' ' HASTINGS AIR CONDITIONING Co, INC,:Hastings, Nebr.......... .. 947 - -K . . . ; ' - -HEATING & VENTILATING (public . . 'cation), 140-148 Lafayette St, New . KENNARD CORP, 2019 S, Hanley . -Rd, St Louis 17, Mo..-..........................984 York, N.Y.................. 1278KEWANEE BOILER CORP, Kewanee, ' HEATING, PIPING AND AIR CON- III.............. 1160,1161,.1162,1163 / DITIONING (publication), 6 , N. KIMBERLY-CURK CORP, Neeriah, Michigan Ave., Chicago 2, III...:.':. 1277 Wis.................. 1260,1261 HENDRICK MANUFACTURING CO, KORFUND CO, INC,-THE, 48-50 - - , 48 Dundaff St, Carbondale, Pa.,.;: 1087 ` 32nd Place; Long Island City 1, N.Y.. 1262 HENRY VALVE CO, 3260 W. Grand KRAMER TRENTON CO, Trenton, r. Aye, Chicago 51, III.....:... . ...... 1129 N.j;............... 985 sry. - 910 -- ' 1946 'Guide - ' h - Page Page . La-DEL CONVEYOR & MFG. CO., - MUELLER BRASS CO., Port Huron,. . New Philadelphia, Ohio........... 1062,1063 Mich....................... :...... ,1108,1107 LAUBLOWER CO., THE, 2007 Home ' < Ave, Dayton 7, Ohio......................... 1065 LEE ENGINEERING CO., Union . ' . National Bank Bldg., Youngstown, .'Ohio...................:.............................. 968 LEEDS & NORTHRUP CO., 4941 . - Stenton Ave, Philadelphia44, Pa..... 1133 . LIBBY-OWENS-FORD GLASS CO., -Nicholas Bldg., Toledo 3, Ohio......... 1242 LI LI E-HOFFMANN COOLING TOWERS, INC., 4239 Duncan Ave., ; St. Louis 10, Mo........................... 1023 L J,-MUELLER FURNACE CO., . 2009 W. Oklahoma Ave., Milwaukee 7, Wis.............................. 970,971 MUELLER STEAM SPECIALTY CO., INC., 40,20 22nd SL, Long Island City, N.V........................ 1227 MUNDET CORK CORP., Insulation Div., 65 S. Eleventh SL, Brooklyn II, N. Y...i............. 1264 D..J. MURRAY MFG. CO., Wausau, Wis........................... 990 H. C. LITTLE BURNER CO., San . .- N . Rafael, Calif.___ ______________ __; 1188 LOCKPORTCOTTON BATTING CO., Lockport, N. Y................................... 1263 NASH ENGINEERING CO., THE, 234 Wilson Rd., South Norwalk, . Conn.......................................... 1202,1203 - : . . M' NATIONAL HEATER CO., 401 Essex Bldg., Minneapolis2,Minn..,.....-. 991 . - MARLEY CO., THE, Fairfax and Marley Roads, Kansas City 15, Kans. 1024 NATIONAL RADIATOR CO., THE, . Johnstown, Pa..................:.l. .1164,1165 . 1 MARLO COIL CO., 6135 Manchester . Ave.,SLLouis3, Mo............ 1042 HERMAN NELSON CORP., THE, ! Moline, 111.;.......... 992, 993 - X MARSH,JAS. P., CORP, 2073 South . ' port Ave., Chicago 14, III.......... 1228;1229 JOHN J. NESBITT, INC., Holmesburg,Philadelphia36,Pa___ 994 . " ; jOS. A. MARTOCELLO & CO., 229 ' 231 North 13th SL, Philadelphia, Pa. 1028 VMcDONNELL & MILLER, Wrigley Bldg., Chicago 11, III......... 1194,1195 - McQUAY, INC., 1602 Broadway, N.E. . Minneapolisr.iyijnn,-.:............ 986,987. NEW YORK BLOWER CO., THE, .. 3145 So. Shields Ave., Chicago 16, III........... 1067. NIAGARA BLOWER CO., 6 East 45th SL, New York 17, N. Y............ 950 v-_ MERCOID CORP, THE; 4201 Bel .' O mont Ave., Chicago 41, III.. 1134,1135 : OWENS-CORNING FIBERGLAS ; . ;. MERIAM INSTRUMENT CO., THE, ;. -10984 Madison Ave, Cleveland 2, ' " Ohio. .. ...... . :....:.. 1138 : MEYER FURNACE CO., THE, Peoria : ' ': 2, III.......-..................... 969 MILLS ' INDUSTRIES, INC., 4100 , CORP., Toledo, Ohio:........1014,1015 OWENS-ILLINOIS GLASS CO., In- . sulux Products Div., Toledo, Ohio ... 1243 : :P. - Fullerton Ave., Chicago39, III.. '..... 1043 PACIFIC LUMBER CQ., THE, 100 ' Minneapolis-honeywell Bush SL, San Francisco, Calif..:___ 1265 ^ .REGULATOR CO., 2711 Fourth Ave., . ;So.,Minneapolis8,Minn....:: 1136,1137 PACIFIC STEEL-BOILER, DIV. U. SI . RADIATOR CORP;, Detroit; Mich.. 1171 - MODINE MANUFACTURING CO., 17th and Holbiirn Sts., Racine,:; Wis.;,r....... .... . 988,-989 PALMER CO.i THE, 2506 Norwood - Ave., Cincinnati. (Norwood), Ohio.r. .^^1140 1 , MOELLER INSTRUMENT COl, 132nd SL, and 89th Ave, Richmond Hill . -'-X . ' PARKS-CRAMER CO., Fitchburg, /. Mass..:.;.;.:..:. :.1...:..;... : 951. - , 18,N.Y........... .... 1139 PAYNE FURNACE CO.; 336 N. Foot- ; . . MONARCH MFG.:.WORKS, Inc, hill Rd., Beverly Hills, Calif... 972, 973 ` ; Philadelphia 34, Pal . .1. -...... .:... 1029 PENN ELECTRje SWITCH CO., % NiORRiSON PRODUCTS, INC., East! ,- ; i68th SL and Waterloo Rd, :CleveI." -land .10, Ohio: V..-... ..-o'::. I. .. . :1086 , Goshen, Ind.. . :..!-..... ..-1141 . PETROLEUM .HEAT & POWER - ;.-CORP.,Stamford, Conn...... ,1186,1187 ... Irui^x. to. Advertisers' 911 : - : ' ' i Paso. PITTSBURGH CORNING CORP:, ' Room 616, 632 Duquesne Way, Pittsburgh, Pa.'........ .. . . .., 1244,1245 PLUMBING AND HEATING JOURNAL (publication), 45 West 45th SL, New York 19, N. Y........... .' 1279 H. W. PORTER & CO., INC., 817-G Frelinghuysen Ave., Newark5, N.J.. .1237 .POWERS REGULATOR CO., THE, : 2719 Greenview Ave., Chicago 14, III., .................................................1142 PREFERRED UTILITIES MFG. CORP., 1860 Broadway, New York, N. Y. .. 1166 J. F. PRITCHARD & CO., Fidelity - Bldg., Kansas City 6, Mo............:... 1d25 PRODUCTS RESEARCH CO.. 634 S. Western Ave., Los Angeles 5, Calif...........,................... ,...:. 1230 PROPELLAIR, INC.i 1944 Clark Blvd., Springfield, Ohio................................ 1068 Si'. PROPELLER FAN MANUFAC- TURERSASSOCIATION, 2-255 -General Motors Bldg.,- Detroit 2, , Mich..:.....1069 : PYLE-NATIONAL CO., THE, 1334-58 ' N. Kostser Ave., Chicago 51, III..... 1091 pt*,. RAY OIL BURNER CO., 405 Bernal , Ave., San Francisco 12, Calif........... 1189 REFRIGERATION ECONOMICS CO., . INC., 1231 Tuscarawas SL, E., Can- , : \ ton, Ohio,............... ____________ __' 995 SARCO CO., INC., 475 Fifth Ave., - : r. New York 17, N. Y.1218,1219 ' SCHWITZER-CUMMINS CO., 1125 ' ' - - Massachusetts Ave., Indianapolis 7; - - Ind..:.:................... 1072 SEAMLEX CO,, INC., 27-31 Jackson /. Ave., Long Island City, N. Y.______ 1103: SERVEL, INC., Evansvflle 20, Ind. .... 1044 SHEET METAL WORKER (publica- 1 tion), 45 West 45th St., New York . 18,'N.Y............................ /,....... 1279 H. B. SMITH CO., INC., THE, West- V field,Mass.............. .1167 H. J. SOMERS, INC., 6063 Wabash ~ ' Ave., Detroit 8, Mich............... 1016,1017 ' SPENCE ENGINEERING CO., INC., 28 Grant SL, Walden, N. Y............. 1143 SPENCER HEATER, DIVISION-- . THE AVIATION CORP:, Williams port. Pa.......................................1168; 1169 B. F. STURTEVANT CO., DIV. OF , WESTINGHOUSE ELECTRIC . Hyde Park, Boston, Mass.....: .954, 955, 956,957 AIR CONDITIONING DIV, -- Hyde Park, Boston, Mass... . 958-959 PRECIPITRON DEPT., Hyde , Park, Boston, Mass............1018, 1019 ' SWAN ENGINEERING CO., - Bloomfield, N. J................. 1116 . ; -* REGISTER & GRILLE MANUFAC- TURING CO., INC., 70 Berry SL, f&r Brooklyn 11; N.Y..;............-.1094 TACO HEATERS, INC., 342 Madison 1 Ave., New York 17, N. Y. . . . . .. .. 1200' - RESEARCH PRODUCTS CORP., TAYLOR INSTRUMENT COM- " ct - Madison 3, Wis.;...V. .1020 PANIES, Rochester, N. Y........ : :. 1144 REVERE COPPER & BRASS, INC:, TENNEY ENGINEERING, INC., 26 ' - 230 Park Ave., New York17,N.Y. .. 1108 Avenue B, Newark 5, N. J.... t___ 1145 . REYNOLDS METALS CO., Reynolds . TERRE HAUTE BOILER WORKS 'Metals Bldg., Richmond, Va.,1266, 1267 CO, Terre Haute. lnd.___ 1170,. REZNOR MFG. CO., Mercer, Pa.... . 996 RIC-WIL CO^ THE;' Union Com merce Bldg., Cleveland, Ohio.... 1238 ROGERS DIESEL AND AIRCRAFT . CORP;, 1120 Leggett'Ave., New : York 59, N. Y....... ;. ........, 952, 1026 ROME-TURNEY RADIATOR CO., X~the; Rome, N."Y,....... . 1036 : RUBEROID CO.i THE, 500 Fifth Ave., T . ~ ; New York 18, N. Y........:.. 1268,1269 H. A. THRUSH & CO, Peru, Ind....... , ........................::................. ...1198,1199 TORRINGTON MFG. CO, THE, " ' 50 Franklin St, Torrington, Conn, - ...........................................,..... 1070,1071 . TRANE CO, THE, 2021 Cameron Ave, ' ? LaCrosse, Wis.........:..;......... 998,-999 TUBE TURNS, INC, Louisviiie i, Ky. il17 TUTTLE & BAILEY, INC, New Britain, ~:: Conn.,........................; .-1092,'1093 -; *' - t. J.V 912 1946 Guide.. . U _ .Page ' Page UNITED STATES AIR.CONDITION- WEBSTER ENGINEERING CO, THE,. ' ING CORP., Northwestern Terminal, 419 W. Second St, Tulsa, Okla...... 1180 Minneapolis, Minn?.. ............... 953 ' WEIL-McLAIN CO, 641 W. Lake St, . UNITED STATES GYPSUM CO., 300 Chicago 6, III........... ........................... 1174 W. Adams St, Chicago, III....... 1270,1271 WESTINGHOUSE ELECTRIC CORP, UNITED STATES RADIATOR CORP., East Pittsburgh, Pa........ ........ 1078, 1079 Detroit, Mich.:........... ............ 1172,1173 W. H. WHEELER, INC, 7 East 47th UNITED STATES REGISTER CO., St, New York 17, N. Y............ 1003 Battle Creek, Mich............................ 1095 WHITE-RODGERS ELECTRIC CO, UNITED STATES STEEL CORP. 1293 Cass Ave, St Louis, Mo___ __ 1146 ; SUBSIDIARIES, Pittsburgh, Pa.... 1100 WILLIAMS OIL - O - MATIC DIV, UNIVERSAL COOLER, DIV., INTER EUREKA WILLIAMS CORP., NATIONAL DETROLA CORP., Bjoomington, III..... ............................ 1190 Marion, Ohio.. ............................. 1045 U J. WING MFG. CO, 59 Seventh UTILITY APPLIANCE CORP. (form Ave, New York 11, N. Y, 1000,1001,1002 erly Utility Fan Corp.), 4851 S. Alameda St., Los Angeles 11, Calif... 1073 WOLVERINE TUBE DIV. OF CALU- - MET & HECLA CONSOLIDATED v; ' COPPER CO, 1411 Central Ave, Detroit 9, Mich......;...................... 1109 VIKING AIR CONDITIONING CORP., THE, 5600 Walworth Ave., Cleve r land, Ohio............. 1074 WOOD CONVERSION CO, First National Bank Bldg, St Paul 1, Minn...................... 1272 VILTER MANUFACTURING CO,, -T* THE, DepLN-23, Milwaukee 7, Wis. 1048 VINCO CO., INC, THE, 305 East ' ,45th St, New York 17, N. Y.... 1192,1193 VULCAN RADIATOR CO, THE, 26. .. Francis Ave, Hartford 6, Conn........ .1037 WORTHINGTON PUMP & MA CHINERY CORP, Harrison, N, J. ; 1046,1047 WRIGHT-AUSTIN CO, 309 W. Woodbridge St, Detroit 26, Mich...:........ 1231 'Y W WAGNER ELECTRIC CORP, 6464 =' Plymouth Ave, SL Louis 14, Mo,.. 1075 WARREN WEBSTER & CO, Camden, N. J................... 1220,1221,1222,1223 WATER COOLING EQUIPMENT CO, 8613 New Hampshire Ave.'; ' Affton Sta, St Louis 23, Mo.______ 1027 YARNALL-WARING CO, 7600 Queen St, Philadelphia 18, Pa,........... , , 1232 YORK CORP, York* Pa.:........... 960 YORK-SHIPLEY, INC, York, Pa. . . . 1191 YOUNG RADiATOR CO, Dept. 175, : Racine, Wis., .......... _________ __ 997 YOUNG REGULATOR CO, 5209 Eu- did Ave.,-Cleveland 3, Ohio., . , .. 1096 \ - jffe-./: . INDEX TO MODERN EQUIPMENT Heating Ventilating Air Conditioning Guide, 1946 ACCUMULATORS VUter Mfg. Co., The, 1048 Petroleum Heat & - Power Coip., McQuay, Inc., 986-987 Vulcan Radiator Co., 1037 1186-1187 . Worthington Pump & -Machinery Ray Oil Burner Co.,'1189 ` ADSORBER, Odor Corp., 1046-1047 Young Radiator Co., 997 Refrigeration Economics Co., Inc.,/ 995 . - W..B. Connor Engineering Corp:, 1008-1009,1085 AIR CLEANING EQUIPMENT ' ' (See also Filters, A ir) . AIR CONDITIONING COM PRESSION EQUIPMENT Mills Industries. Inc., 1043. Universal Cooler Div., Intemation- Rogers Diesel and Aircraft Corp.;" (Rogers-Research System); 952, 1026.. ' ' H. J: Somers Co., 1016-1017 B. F; Sturtevant Co.. Div., West- inghouse Electric, 954-959. 1018. 1019 ' . ... >Air Devices, Inc.. 1080-1081 '. al Detrola Corp., 1045. - Tenney Engineering, Inc., 1145 , Air-Maze Corp., 1004-1005 . Trane Co., The, 998-999 .. ; "Air & Refrigeration Corp.. 939 United States Air Conditioning American Air Filter Co., Inc., 1006 AIR CONDITIONING . CON Corp.. 953 .1007 TROLS (See Controllers andCon- Universal Cooler Div., Interna- - American Moistening Co., 1021 - ' trot'Equipment, Humidity Con tional Detrola Corp;, 1045 - Badger Corp.', 1012 . . trols) - -. Williams Oil-O-Matic Div., Eureka' 'Dollinger Corp. (formerly Staynew Williams Corp., 1190 . Filter Corp.), 1010-1011 Farr Co., 1013 . ; *, - General Electric Co., (Bloomfield, : . N. J.). 948-949 , AIR CONDITIONING REGIS- ;TERS AND GRILLES (See Grilles, Registers) . Worthington Pump & Machinery Corp.. 1046-1047 , Young Radiator Co., 997 .`Qwens^Coming . Fiberglas Corp., AIR COOLING, HUMIDIFYING V. 1014-1016 /Parks-Cramer Co.,' 951 ' AIR CONDITIONING UNITS AND DEHUMIDIF.YING - APPARATUS . . ` J: F. Pritchard & Co., 1025 `Research Products Corp., 1020 H. Somers, Inc.. 1016-1017 B. F: Sturtevant Co., Div., West ' inghouse Electric,954-959, 1018 >' 1019. . .Supreme Air Filter Co., 910 ' AIR COMPRESSORS\(See Com . ..pressors, Air) . . Air & Refrigeration Corp., 939, Airtemp Div., Chrysler Corp., 966 967 . . Air-Maze Corp., The. 1004-1005 Air & Refrigeration Corp., 939 x - American Blower Corp., 940-941 American Radiator & Standard Sanitary Corp., 1148-1149 . Belanger Fan & Blower Co;, 1054 1055 Airtemp Div., Chrysler-Corp., 986 967 . .. American Blower Corp., 940-941' ' American Moistening Co., 1021 ,. Buffalo Forge Co., 1056 . Buffalo Forge Co., 1056 .. Carrier Corp*..944-945 , Carrier Corp., 944-945 Clarage Fan Co.. 946 ' . Clarage Fan Co., 946 Farr Co., 1013 - . . " Crane Co.', 1154-1155 . . gg^AIR CONDITIONING COILS 'Curtis Refrigerating Machine, Div. ^yAone Industries, Inc.,. 1030 - of Curtis Mfg. Co., 1040' vy-.AirthermMfg. Co...976' * 1 v.i-Gyrier Corp;. 944^945 " Curtis Refrigerating Machine,' Div. 'of,Curtis Mfg. Co., 1040 Fitzgibbons Boiler Co.,-Inc., 1156 . 1157 .- Frick Co., (Inc.), 1041 Gar Wood Industries, Inc., 974-975 . - General Electric Co., (Bloomfield, N. J.). 948-949. . General Electric Co. (Bloomfield, N. J.). 948-949 -iy -'Kennard Corp., 984 f'-.z. Kramer Trenton Co.. 985 Mario Coil Co., 1042 Hastings .Air Inc., 947 Conditioning Co., Ilg Electric Ventilating Co., 982, 1060-1061 . General Electric Co. (Bloomfield," ' N. J.). 948-949 : Ilg Electric Ventilating' Co.;' 982, 1060-1061 ' . . - Insul-Wool Insulation Corp., 1255 ` Kennard Corp., 984 1 _ . Mario Coil Co.', 1042 . ' . Modine Mfg. Co., 988-989 John J. Nesbitt, Inc.. 994 _' Parks-Cramer Co., 951 . - N* J. F. Pritchard & Co., 1025 - Refrigeration Economics'Co'., Inc.; 995 -^`.McQuay, Inc., 986-987 /yModine Mfg. Co.. 988-989 . '. John J. Nesbitt, Inc., 994 Iron Fireman Mfg. Co., 1178*1179 Jaden Mfg. Co., 983 . S. T. Johnson Co., 1184-1185 Niagara Blower Co.. 950 ; . ` ' -fRefrigeration Economics Co.. Inc., I'.l. 995 . Rome-Tumey Radiator Co., 1036 SX-Bl F. Sturtevant Co.,' Div., West- inghouse Electric. 954-959, 1018- Kennard Corp., 984 Kramer Trenton Co., 985 H. C. Little Burner Co., 1188 Mario Coil Co., 1042 ' McQuay. Inc., 986-987 . . Rogers Diesel and Aircraft' Corp. ` (Rogers-Research System), 952. 1026 - H. J. Somers,'Inc.. 1016-1017. B. F. Sturtevant Co.', Div.. West- inghouse Electric, 954-959, 1018 1019 ^. Tenney Engineering, Inc., 1145' Trane Co.. The. 998-999 v' p'\1019 '' l^'-Swan Engineering Co.. 1116 Meyer Furnace Co., 969 - Modine'Mfg. Co.. 988:989 Utility Appliance Corp.'; 1073 ' . Vilter Mfg. Co.. The, 1048 . ^Tenney Engineering. Ihe., 1145 L'. J. Mueller Furnace Co., 970-971 Worthingon Pump & Machinery '* g.Tiane Co., The, 998-999 ' . D. J."Murray Mfg. Co.. 990' * Corp.. 1046-1047 . . -; United' Slates 'Air Conditioning Niagara Blower Co., 950 - , York Corp., 960 ' .... s Con)., 953, . . _ Parks-Cramer Co., 951.. Young Radiator Co., 997 - ~ Numerals following Manufacturers* Names refer to pages in the Catalog Data Section ' ' 913 ' -. ' *" 914 1946 Guide * AIR DIFFUSERS . Air Devices, Inc.. 1080-1081 .. American Foundry & Furnace Co., 962-963 . \ .' Anemostat Corp. of America. 1082 Rogers Diesel-and'Aircraft Corp., (Rogers-Research System);'. 952, _ 1026 , .- H. J. Somers, Inc.,; 1016-1017 W. H. Wheeler, Inc., 1003 ' ASBESTOS PRODUCTS (Setalso' Insulation). . Armstrong Cork Co.. 1248 ' ' Philip Carey Mfg. Co.. The. 1252 1253 . '- ' ._ Barber-Colman Co- 1084, 1121 Carrier.Corp., 944-945 W. B. Connor Engineering C.or- p','- AIR RECEIVERS Air) - -./ {See Receivers, ... Celotex Corp., The, 1250 Eagle-Picher.Co., The. 1254 Johns-Manville, 1258-1259 . . '* , . . 1008-1009,1085 . , ' Charles Demuth & Sons, 1086 ; - AIR RECOVERY, Method of, Mundet Cork Corp.."1264 H. W. Porter & Co.. Inc., 1237 . -Independent Register Co., The. W. B. Connor Engineering Corp., Ruberoid Co.. The, 1268-1269 ' . 1090;. ' 1008-1009. 1085 ; United'States Gypsum Co., 1270-' Pyle-National Co., The. 1091 . 1271 ; ' , ;. VTuttle & Bailey. Inc.. 1092-1093 AIR STERILIZATION, Method - United States Register Co.. 1095 - of, ,, .. ; . ATOMIZING SPRAY NOZZLES Rogers Diesel and Aircraft Corp..- (See Spray Nozzles) . ; ` AIR DUCTS (See Ducts) 952. .1026 -} 7 - / - ' AIR ELIMINATORS :. ' ,.. -_BeIl & Gossett Co-1196-1197 ATTIC FAN COOLERS (SeeFans. AIR TUBING, Flexible Metal . -AUic, Ventilators. Attic) \ . ' (See Tubing, Flexible Metallic) -. - Dole Valve Co., The,. 1234 Herman' Specialty' Co.,_12l3-l2l5 "AIR VELOCITY METERS (See AUTOMATIC FUEL BURNING . EQUIPMENT (See Burners, Au - Illinois Engineering Co., 1216-1217. \ Meters', Air Velocity)._ ' * tomatic',' Furnace Burners; Cos >' v.'. . Sarco Co., Inc- 1218-1219 >- : ' Trane Co.; The. 998-999 .. * :AIR FILTER CLEANING COM- AHL VELOCITY REGULATORS (See Dampers, Air Volume Con trol) *; ; Burners; Oil Burners; Stokers) AUTOMATIC SHUTTERS. (See . Shutters. Automatic) . . !_ ;i POUNDS '_.v Johnson SenHce.Co.. 1130-1131 ' - Air Devices, Inc.. 1080-1081' . ' Powers Regulator Co., The, 1142 AXIAL FLOW FANS (See Fans'; Air-Maze Corp., 1004-1005 ` - American Air Filter Co...Inc., 1006 AIR .WASHERS' ; . .... Axial Flow)' - ' ^ . 7 I ";V.- - ' ' 1007 . . \ Dollinger Corp. (formerly Staynew Filter Corp.). 10KM011 _ . Air`& Refrigeration Corp.. 939 . American Blower Corp.. 940-941 Bayley Blower Co., 1052 ' BENDS, Pipe, Ferrous and Non- - ' ^Ferrous . - . . _- Eagle-Picher Coi. The, 1254 -Buffalo Forge Co.. 1056.- AIR FILTER GAGE-' - Carrier Corp., 944-945 . Arthur Harris & Co., 1115 "' ' Mueller Brass Col; 1106-1107 `` . American Air Filter Co., Inc., 1006- Clarage Fan Co., 946 ;,;.1007 - . \ D. J; Murray Mfg. Co./990 Parks-Cramer Co., 951 - .' Rome-Tumey. Radiator Co., 1036 Meriam Instrument Co., The. 1138-- New- York Blower Co., The.. 1067 Swan Engineering-Co.. 1116 -'' Parks-Cramer Co., 951 _' ' AIR FILTERS (See FUlers. Air; /- also Air Cleaning Equipment) - ' H. J. Somers. Inc-1016-1017- ' B. F. Sturtevant Co.. ;Div.. .West inghouse Electric, 954-959, 1018 BENDS,' Return (See Pipe; Return--t ' Bends) . . . . AIR FITTINGS,.Brass ./ . 1019. ' . ..f Trane Cq..-The, 998-999 . j j . United States Air Conditioning BLOCKS, Asbestos ; Philip Carey `Mfg. Co.', The, 1252- - ' ' .Martocello.'Jos. A. & Co., 1028 - Corp.. 953. v ' -;- ' . .1253 . ' ... .. VUter Mfg. Co./The. 1048 . Johns-Manville, 1258-1259 . ' * *. . `.AIR MEASURING AND' REw 1 .CORDING INSTRUMENTS -r ALARMS, Water Level ' . ' ' ,'American Meter Co.; Inc.', 1119 . ; Friez Instrument vDiv-: -Beridix' . AviationCorp., 1128 . . .. McDonnell & MiUer. 1094-1095 Mercoid Corp:, The, 1134-1135 Wright-Austin Co.', 1231' ' ' Illinois Testing Laboratories. Inc.,' Yarnall-Waring Coif 1232 > ' ^ ^ v1-;. 1132,- ; ; . w -*v. Ruberoid Co...The, 1268-1269-- - BLOCKS, Glass . ." . Owens-IllinoisGlassCo.. 1243,-. ' Pittsburgh' Corning. Corp.. 1244 ' ' 1245 l; - ' . . \ %. v - .Minneapolis-Honeywell - Regulator ALUMINUM FOIL, Insulation BLOWER HOUSINGS. .. ' v .Co.. 1136-1137 . ; Parlc^Cramer Co., 951 ~ .. ` Powers.Regulator Coi. The, 1142 Alfol Insulation Co.. Inc..'1246 . Champion' Blower & Forge : Co., Lockport Cotton Batting Co., 1263. 1057 . - ' . 'Reynolds .Metals Co^, 1266-1267 Chelsea Products,'Inc., 1058 - Clarage'Fan Co.,.946 ' _ - AIR.' MOISTENING ' APPARA- Hastings Air Conditioning ,Co.,' .. ` TUS (See Humidifiers) ' - . - ALUMINUM FOIL VAPOR Inc., 947 . ;; BARRIER (See, Aluminum Foil) Lau Blower Co., The, 1065 ` .. .f AIRrPURIFYING APPARATUS Morrison Products, Inc., -1066 ~ . AMMONIA COILS {See Coils, B. F. Sturtevant Co., Div.. West r.;. ' Air-Devices, Inc., 1080-1081 ' .-Air-Maze.Corp.,.1004-1005- / ' 'Ammonia)' - . * inghouse -Electric, 954^959,. 1018^ : 1019 . c. .. a '7`Air'& Refrigeration Corp., 939 _ Chelsea Products,'Inc.,. 1058 */' ' ANEMOMETERS - ,~ ; Toriingtoh Mfg.' Co.; The, -1071- r- / ... - 1070 .*' , Connor-Engineering Corp.,- Fries- .Instrument Div., ..'.Bendix ' United States,.'Air Conditioning ^.1008-1009,1085. : . Aviation Corp., 1128. . . - Corp'., 953;-' ; ' , '. . /`'J...F. -Pritchard & Co. (Puridrycr Illinois Testing Laboratories, Inc.. Utility Appliance Corp;, 1073 ^ '.Dept),;io25_ 1132 . . c v ? '. - ; Viking Air Conditioning Corp., The. Research Products Corp.,-1020 ' Taylor Instrument Cos., 1144 ^ 1074-- v:*7> '' Please motion THE;GUIDET946 when writing to Advertisers * Index to Modern Equipment 915 `BLOWER MOTORS.-(See Motors, BLOWERS, Pressure - '. . Electric)-.- ' * American Blower Corp., 940-941 .-BLOWERS, Centrifugal . " American Coolair .Corp., 1050^1051 Bayley Blower Co., 1052 ' . . (SeeFans)- Belanger Fan & Blower Co., 1054 1055 Preferred Utilities Mfg. Corp., 1166 Terre Haute Boiler Works Co., 1170 Webster Engineering Co., * The, 1180 . . . York-Shipley, Inc., 1191- BLOWERS, Fan (SeeFans, Supply Buffalo Forge Co.. 1056 BOILER COMPOUNDS.CSreCom- . andExhaust) Champion Blower & Forge Co., 1057 Pounds, Boiler) . . .. \ Chelsea Products. Inc.. 1058 . BLOWERS, Forced Draft '- American Blower Corp., 940-941 Clarage Fan Co., 946 BOILER COVERING (See Cover DeBothezat Fans Div., American ing, Pipe and Surfaces) Machine & Metals, Inc., 1059 American Coolair Corp., 1050-1051 Hartzell Propeller Fan Co., 1064 American Foundry & Furnace Co., . 962-963 . Ilg Electric Ventilating Co.. 982, 1060-1061 BOILER FEED PUMPS (See PumPs, Boiler Feed) ' " -' ; Bayley. Blower Co., 1052 . La-Del Conveyor & Mfg. Co.. 1062 Buffalo Forge Co.. 1056 . . -1063 ' . . BOILER FEEDERS (See Feeders, Campbell Heating Co.. 964-965 Jos. A. Martocello & Co., 1028 ' Boiler) -' ., Champion Blower & Forge Co., Nash Engineering Co., 1202-1203 1057 .. . Chelsea Products,.Inc., 1058 ' Clarage Fan Co., 946 '_ B. F. Sturtevant Co., Div., Westinghouse Electric, 954-959, 1018 BOILER WATER FIELD KIT, 1019 . ' for Testing and Treating . - La-Del Conveyor & Mfg. Co., 1062^ Vinca Co., Inc., The, 1192rli93 ; 1063 *. BLOWERS, Turbine - Mario CoU'Co., 1042 .^National Heater Co., 991' ' ' ' Herman Nelson Corp., The. 992-993 ;' New York Blower Co..' The, 1067 DeBothezat' Fans Div., American Machine & Metals, Inc., 1059 - Ilg Electric Ventilating Co., 982, 1060-1061 .. BOILER WATER TREATMENT Vinco Col, Inc- The. 1192-1193 . = - B. F. Sturtevant Co., Div.. West- B. F.`Sturtevant Co., Div., West -BOILERS, Cast-Iron . ' inghouse Electric, 954-959,' 1018 . 1019 . . ... ; jTrane Co., The, 998-999 . '- - Utility Appliance Corp., 1073 . inghouse Electric, 954-959, 1018 1019 L. J. Wing Mfg. Co.. 1000-1002 -' L. J. Wing Mfg. Co., 1000-1002 7-' BLOWERS, Warm Air Furnace Airtemp Div- Chrysler Corp., 966 967 . . . American' - Radiator & Standard Sanitary Corp- 1148-1149 . ' Bryant Heater o.. The, 961 ^ . BLOWERS, Heating and Vend- ; - lating ; . . . - Air Controls, Inc.,' 1049 ' , ; American Blower Corp.. 940-941. American Coolair Corp., 1050-1051 '-American Foundry &" Furnace .Co~ 9. :V-; ' 962-963 - -sBayley Blower'Co'.. i052 /'.Belanger Fan & Blower Co., 1054- -rl055: . ,7;-';Buffa5o Forge Co.,1056 , Air Controls, Inc., 1049 - Buffalo Forge Co., 1056 . Campbell Heating Co., 964-965 ' ' Champion Blower & Forge Co., 1057 . .. Chelsea Products. Inic.. 1058 .- Clarage Fan Co., 946 . '. Hastings Air Conditioning Co., Inc., 947 . - . Ilg. Electric Ventilating 'Co., 982. ` 1060-1061 . La-Del Conveyor & Mfg. Co., 1062 Burnham Boiler Corp., 1152 . Crane Co- 1154-1155 f - .' National Radiator Co., The. 1164 1165 . ' -,' H. B; Smith Co- Inc- The. .1167 ' Spencer Heater Div., The Aviation _ Corp;, 1168-1169 . , .' United States Radiator Corp- 1172 .1173 .. Weil-McLain Co- 1174 ' Williams Oil-O-Matic Div- Eureka' Williams Corp., 1190 ' i'-i-"- ' Campbell Heating Co., 964-965.- 1063 - ' i*-?K>.>jCarrier Coip., 944-945 , ` .- ; " Lau Blower Co., Thei 1065 . BOILERS, Down Draft ' ` -,. ^'^-f'Chaihpion ' Blower ;& ' Forge Co.. Meyer Furnace Co- The, 969 _ . 'Farrar^& Trefts. Inc.,1158 '- ' V;-4'>:i057 -. .- Chelsea Products. Inc.; 1058 7 - 'Clarage Fan Co;, 946j._.-- ' .' ^Electrombde Corp.-(Div;v American 7'!Foundry Equipment Co.), 977 " Hartzell Propeller Fan Co". 1064- Irc^Hastings' Air Conditioning' Co., Inc.;'947 - J'llg Electric. Ventilating Co.,'982, Morrison Products, Inc., 1066 Kewanee. Boiler Corp.,-1160-1163^. L. J. Mueller Furnace Co., 970-971 H. B. Smith Go- Inc., The, 1167, - Schwitzer-.Cummihs'Co.', 1072 Terre Haute Boiler Works Co- 1170 Trane Co;. The. 998-999 : . United States Corp., 953 Air - ' Conditioning '- _ . BOILERS, Forced ' Recirculation--Oil ' . `; Burning Utility Appliance Corp!. 1073 1. . Viking Air Conditioning - Corp., Air Devices, Inc- 1080-1081. . The. .1074 Airtemp Div- Chrysler Corp., 966 7^.' : ' 1060-1061 :: . f--, Jaden Mfg/Co.,1983 _ - L. J. Wing Mfg. Co.. 1000-1002 967 . . Cydotherm .Corp-1153 '.. - ' ' ' La-Del Conveyor & Mfg. Co.; 1062- ^ - ' 71063 ' BOILER-BURNER ' International Boiler Works Co., - The. 1159 . . : v . . ' ; ;Lau Blower Co., The,''1065' . .Air Devices,-Inc., 970-971 . H. B. Smith Co- Inc.-, The. 1167 i|;li'7rMomson Products. Inc., 1066 .. Airtemp Div., Chrysler Corp., 966 Herman Nelson Corp., The, 992-993 ^ew York'Blower Co., The, 1067 967 , - s American' Radiator . &. Standard BOILERS, Gas Burning -. -^^ SchwiUer-Cummins Co..* 1072 Sanitary Corp., 1148-1149 . Airtemp Div- Chrysler Corp:, 966- ' B. F.\Sturtevant Co., Div.,- West- Automatic Burner.Corp.,-1181. -'967 : inghouse Electric, 954^959. 1018- Bryant Heater Co.,'The. 961 ' . American' Radiator .& Standard. Crane Co., 1154-1155 Sanitary Corp- 1148-1149 - ' 'l-T '_T.no-rir0in7igt\dn . Mfg-.-Co.,' The, 1070-" X& Trane Cb:. The, 998-999 . ' - Gar-Wood Industries. Inc., 974-975 General' Electric Cou (Bloomfield, V NvJ.). 948-949 . - . . - Babcock & Wilcox Co-.The, 1150 Brownell Co., The. 1175 * *' Bryant Heater.Co- The, 961 " >/V-United States.- Air Conditioning National Radiator Co., The. 1164 Burnham Boiler Corp- 1152 - - :^/'?CorpM 953 ' ,- '. . . 1165-.' ' . Crane Co- 1154-1155 , iilCUtility Appliance.Corp^ 1073 . Petroleum Heat & Power Corp., Cydotherm Coip-1153' - * 'VivL; J. Wing Mfg. Co., 1000-1002 . 1186^1187- . . Farrar & Trefts, Inc., 1158 `' ; Numerals following Manufacturers* Names refer to pages in1 the Catalog Data Section . - _ - -. , . 916 ~ -1946 Guide Fitzgibbons Boiler Co., Inc., 1156*' Fitzgibbons Boiler Co.. Inc., 1156- BURNERS, Automatic (See also 1157 !157 . . Coal Burners, Stokers) ' General Electric Co. (Bloomfield, N. J.). 948-949 . Gar Wood Industries, Inc., 974-975 International Boiler Works Co.. Combustion Engineering Co., 1176 International Boiler Works Co., The, 1159 ' Detroit Stoker Co.. 1177 1159 - Iron Fireman Mfg. Co., 1178-1179 Gar Wood Industries, Inc., 974-975 Kewanee Boiler Corp., 1160-1163 L. J; Mueller Furnace Co.. 970-971 National Radiator Co., The, 1164^ 1165 S. T. Johnson Co.. 1184^1185 Kewanee Boiler Corp., 1160-1163 ~ National Radiator Co., The, 1164 1165 General - Electric Co. (Bloomfield, N. J.), 948-949 . Iron Fireman Mfg. Co.. 1178-1179 S. T. Johnson Co., 1184-1185 Pacific Steel Boiler Div., - U. S. Radiator Corp.. 1171 Pacific Steel Boiler Div., U. S. Preferred Utilities Mfg. Corp., 1166 Radiator Corp., 1171 . Ray Oil Burner Co.. 1189 H. B. Smith Co., Inc., The, 1167 Petroleum Heat & Power Corp.. Spencer Heater Div., The Aviation Corp.; 1168-1169 -Terre Haute Boiler Works Co., 1170 1186-1187 Preferred Utilities Mfg. Corp.,-1166 H. B. Smith Co., Inc., The. 1167 BURNERS, and Oil Combination Gas '. Trane Co., The, 998-999 Spencer Heater Div., The Aviation Babcock & WilcoxCo., The. 1150 United States Radiator Corp., 1172 Corp.. 1168-1169 Combustion Engineering Co., 1176 1173 _ . Terre Haute Boiler Works Co., 1170 Combustion Equipment Div., Todd Trane Co., 998-999 - " Shipyards Corp., 1182 BOILERS, Heating United States Radiator Corp.. 1172 S. T. Johnson Co., 1184-1185 ` 1173 .' Ray Oil Burner Co., 1189 . 'Airtemp Div., Chrysler Corp.-, 966 967 - - American Radiator & Standard WeU-McLain Co., 1174 . York-Shipley, Inc., 1191 . ' Webster Engineering Co., The, 1180 Sanitary Corp., 1148-1149 ' Babcock & Wilcox Co.. The, 1150 BOILERS, Steel BURNERS, Gas (See Gas Burners) Bigelow Co., The, 1151 Brownell Co., The. 1175 . Babcock & Wilcox Co., The, 1150 Bigelow Co.. The. 1151 . BURNERS, .041 (See Oil Burners) Bryant Heater Co., The, 961 - Brownell Co., The, 1175 Burnham Boiler Corp:, 1152 . Burnham Boiler Corp., 1152 . CALKING, Building Cyclotherm Corp., 1153 . Combustion Engineering Co.. Inc., Baldwin-Hill Co., 1249 Farrar & Trefts. Inc., 1158 Fitzgibbons Boiler Co., Inc., 1156 1157 -. GarlWood Industries, Inc.. 974-975 International Boiler Works Co., The, 1159 . Iron Fireman Mfg.-Co., 1178-1179 - Kewanee Boiler Corp.. 1160-1163 1176 Farrar & Trefts, Inc., 1158 ' , Fitzgibbons Boiler Co., Inc., 1156 1157 - Gar Wood Industries, Inc., 974-975 General-Electric Co. (Bloomfield, N.J.), 948-949 . International Boiler Works Co., The. 1159 ' L..J. Mueller Furnace Co.. 970-971 . Iron Fireman Mfg. Co., 1178-1179 Eagle-Picher.Co., The, 1254 Johns-ManviUe, 1258-1259 Kimberly-Clark Corp., 1260-1261 CASTINGS, Bronze and Dairy . Nickel Silver Metal Arthur Harris & Co., 1115 D. J. Murray Mfg. Co., 990 'National Radiator Co., The; 1164- .>1165 Pacific Steel..Boiler Div., U. S. - -Radiator Corp.,'1171 ' Petroleum Heat & Power Corp;, 1186-1187 . S. T. Johnson Co., 1184-1185 Kewanee'Boiler Corp., 1160-1163 ' National- Radiator Co., The, 1164 - 1165 '; Pacific Steel Boiler Div.. U. S: . Radiator Corp:,1171 - ' CEILINGiPLATES Pyle-Natiorial Co.,- The, 1091 *' United States Register Co.,. 1095 Preferred Utilities Mfg. Corp., 1166 Preferred Utilities Mfg.'Corp., 1166 CELLULAR GLASS (See Class, H. B. .Smith Co., Inc., The, 1167 Spencer Heater Div.,'The Aviation Cellular). \ _ Spencer Heater Div., -The Aviation . Corp.. 1168-1169 . Corp., 1168-1169 . * Terre Haute Boiler Works Co:, 1170 Terre Haute Boiler Work's'Co., 1170- Williams Oil-O-Matic Div., Eureka CEMENT, Asbestos- ' Trane Co., 998-999 - Williams Corp., 1190 - Philip Carey Mfg. Co., The,` 1252 United States Radiator Corp., 1172 1253. . .1173 , Weil-McLain Co., 1174 - BOILERS,' Unit Steam Gener-' .Johns-Manville, 1258-1259 ator \ - Mundet Cork Corp., 1264 . .' - Williams Oil-O-Matic Div.;Eureka Williams Corp., 1190 Preferred Utilities Mfg. Corp;. 1166 Ruberoid Co.. The. 1268-1269 United States Register Co.. 1095 BOILERS, Magazine Feed Spencer Heater Div., The Aviation - Corp., 1168-1169 - Weil-McLain Co.. 1174 . \ York-Shipley, Inc., 1191 BOILERS, Water. Tube ^ Babcock & Wilcox Co.,' the, 1150 Bigelow Co., The, 1151 .. Combustion Engineering Co,, 1176 Farrar &'Trefts, Inc., 1158 , \ International- Boiler- Works Co., The, 1159 - . BOILERS. Oil Burning . H. B. Smith Co., Inc., The. 1167 -Airtemp Div., Chrysler Corp., 966 967 \ . American Radiator &' Standard Spencer Heater Div., The Aviation Corp., 1168-1169 - ,, ' Trane Co.. The, 998-999 Sanitary Corp., 1148-1149 .. - Automatic Burner Corp., 1181 . BREECHINGS AND . Babcock & Wilcox Co., The, 1150 CHIMNEYS' . Bigelow. Co.-, The, 1151. _ Bethlehem Steel Co.,' Inc;,1098 # Brownell Co., The, 1175, Bigelow Co.. The, 1151 v- .' Burnham BoUer Corp., 1152 ' Brownell Co., The, 1175 . Cydotherm Corp.-rll53- . Farrar & Trefts. Inc., 1158 ''Fairar &'Trefts,Tire., 1168 ' .Terre Haute Boiler'Works'Co., 1170 CEMENT, insulating . Baldwin-Hill Co., 1249- Philip Carey Mfg. Co... The, 1252 1253 . . Eagle-Piqher Co., The, 1254 ' Johns-ManviUe, 1258rl259 ' ' Owens-Coming Fiberglas Corp.. 1014-1015 Ruberoid Co., The, 1268-1269 United States Register Co., 1095- CEMENT, Mineral Wool Baldwin-Hill Co., 1249 ./ - . ` Philip Carey Mfg. Co., The. 1252 1253 '. .- . Eagle-Picher Co., The. 1254 Johns-ManviUe, 1258-1259 Ruberoid Co.,"The; 1268-1269 - . . - Please mention THE .GUIDE l?46when writing to Advertisers Index, to Modern- Equipment ; 917 .CEMENT, Refractory (See Re .Kennard Corp.i 984 .. ' factories). - - Kraraer-Trenton.Co., 985 Mario Coil Co., i042 CHAIN, Furnace Pulleys (See McQuay, Inc., 986-987 . Modine Mfg. Co.. 988-989 also Pulleys, Chain) . D. J. Murray Mfg. Co., 990 Hart & Cooley Mfg. Co., 1088-1089 John J. Nesbitt, Inc., 994 -- Hendrick Mfg. Co.; 1087 New York Blower Co., The, 1067 ' ' Revere Copper & Brass, Inc., 1108 Niagara Blower Co., 950 United States Register Co., 1095 Refrigeration Economics Co., Inc., 996 CHIMNEY TOPS ' Rome-Turney Radiator Co., 1036 Trane Co.. The, 998-999 .Air.Devices, Inc.. 1080-1081 , G. C.Breidert Co., 1083 - United States Air Conditioning . Corp.. 953 Young Radiator Co., 997 a ' CIRCULATORS, Hot Water " . ^Heating ;. COILS, Brass . . . COILS, Pipe and Tube, Non-'. Ferrous .- Acme Industries, Inti., -1034 - Arthur Harris & .Co.,-1115 v Kramer Trenton Co., 985. -- Mario CoU Co., 1042 John J. Nesbitt, Inc.~ 994 . Mueller Brass Co., 1106-1107 Rome-Turney Radiator Co., 1036 Swan Engineering Co., 1116 York Corp., 960 . . COILS, Stainless Steel Arthur Harris & Co., 1115 McQuay, Inc., 986-987 Swan Engineering Co., 1116 . *;Bell & Gossett Co., 1196-1197 E. B. Badger & Sons Co., 1010-1011 COILS, Tank . Crane Co., 1154-1155 Arthur Harris & Co., 1115 r; Hoffman Specialty Co., 1213-1215 McQuay, Inc., 986-987 ' ' Iron Fireman Mfg. Co., 1178-1179 Swan Engineering Co., 1116 BeU and Gossett Co., 1196-1197 Taco Heaters, Inc., 1200 . H.-A. Thrush & Co., 1198-1199 . Trane Co.. The, 998-999 % - Taco Heaters. Inc^, 1200 , COMBUSTION CHAMBERS Trane Co., The, 998-999 . COILS, Cooling . Babcock & WUcox Co., The, 1150 Combustion Engineering Co., 1176. ,"- .sCLEANERS, Air (See Air Cleanin L''<rv . Equipment) ` Aerofin Corp*. 1031-1032 Bel! & Gossett Co., 1196-1197 Fedders-Quigan Corp., 980 Dravo Corp., 978-979 .' . '. Carrier Corp., 944-945 , COMPOUNDS, BoUer COAL BURNERS (See Burners, Frick Co. (Inc.), 1041 Vinco Co., Inc:. The, 1192-1193 - . 1; - Automatic) G & O Mfg. Co., The, 1035. i- '.CODE, Fan Teat - Propeller Fan Manufacturers Asso- - riation, 1069 ' . - _ General Electric Co. (Bloomfield, ' N. J.). 948-949 Insul-Wool Insulation Corp., 1255 Kennard Corp., 984 Kramer Trenton Co., 985 . Mario CoU Co.. 1042 COMPOUNDS, BoUer and Radi- ator Sealing -- Dole Valve Go.. The, 1234 Johns-ManvUte, 1258-1259 . Vinco Co,, Inc.', The, 1192-1193 . --.. >COILS, Aluminum - McQuay, Inc.', 986-987 >Kramer Trenton Co.. 879 ' McQuay, Inc., 986-987 - ^John J. Nesbitt. Inc.. 994 ^Refrigeration Economics Co., Inc., _ >> 995 ' .. " B. F.- Stiirtevant Co.. Div., West - i. - inghouse Electric. 954-959. 1018- riois - V>; Swan Engineering Co., 1116 ' ' >5trane Co.. The, 998-999 Modine Mfg. Co.. 988-989 COMPOUNDS, Soot Destroyer John J. Nesbitt, Inc., 994 . Refrigeration Economics Co., Inc., Vinco Co.. Inc.. The, 1192-1193 995 Rome-Turney Radiator Co., 1036 COMPRESSOR MOTORS (See B. F. Sturtevant Co., Div., West- Motors, Electric) * ' inghouse Electric, 954-959, 1018 1019 . Tenney Engineering, Inc., 1145 Trane Co., The, 998-999 ' ' United States Air Conditioning' COMPRESSOR,TUBING, Flei- ' ible (See T.ubing, Flexible Meiall, lie) - ' . `' Corp., 953 . COILS, Ammonia . VUter Mfg. Co.. The. 1048 COMPRESSORS, Air ?Acme Industries. -Inc., 1030 Baker. Ice Machine Co., 1038 - V G & O Manufacturing Co.. The, 1035 . Worthington Pump & Machinery : Corp., 1046-1047 York Corp.', 960 ' . Young Radiator Co., 997 Brunner Mfg. Co.. 1039... Curtis Refrigerating Machine Div. of Curtis Mfg. Co., 1040 Nash Engineering Co., 1202, 1203 ' Kramer Trenton Co.,' 985' Mario Coil Co.. 1042 COILS, Pipe, Copper Worthington Pump and Machinery ' Corp., 1046-1047 ; : "McQuay, Inc., 986-987 ' , Acme Industries, Inc., 1030 - Modine Mfg. Co., 988-989' ... , E. B. Badger & Son Co.. 1110-1111 COMPRESSORS, Refrigeration 'Refrigeration Economics Co., Inc.. . . 995 . . " . ' Swan Engineering Co., 1116 ' s Trane Co., The, 998-999 - ..VUter Mfg. Co.TThe. 1048 ^Worthington Pump & Machinery > Corp.. 1046-1047 ; '-YaniaU-Waring Co., 1232 .f York Corp.. 960 * ' : BeU& Gossett Co., 1196-1197 Arthur Harris & Co., 1115 'Mario CoU Co., 1042 McQuay. Inc., 986-987 Mueller Brass Co.. 1106-1107 Refrigeration Economics Co., 995 Swan Engineering Co., 1116 . . Inc.,. Airtemp Div;,* Chrysler Corp., 966-' 967 . ; Baker Ice Machine Co., 1038 - Brunner Mfg. Co., 1039 ' Carrier Corp., 944-945 - Curtis Refrigerating Machine Div. of Curtis Mfg. Co., 1040 . Frick Co. (Inc.), 1041 ' ' ,, General Electric Co. (Bloomfield.- COILS. Blast ' .COILS, Pipe, Iron . Acme Industries, Inc., 1030 , N. J.), 948-949 .\ Mills Industries,. Inc.,1043 ' Servel; Inc., 1044 .' . '' ,-Aerofih pjrp;. 1031-1033 . Bayley Blower'Co., 1052 Trane Co., The, 998-999 ` Airtherm Mfg. Co., 976 . ' Swan Engineering Co., 1116 .Universal Cooler Div., Internation ` Fedder^Quigan Corp., 980 .' . . Worthington Pump & Machinery al-Detrola Corp., 1045- ?G&O.Mfg. Co.. The., 1035 - Corp., 1046-1047 . . - VUter Mfg. Co.. The, 1048 . -Numerals following Manufacturers- Names refer to pages ir the Catalog Data Section ' 918 '1946. Guide B. F. Sturtevant Co., Div.; West- CONTROL, Boiler Water Level COOLING EQUIPMENT, Air inghouse Electric, 954-959, 101* . 1019 . . Crane Co.,. 1154-1155 : Aerofin Corp*. 1031-1033. Worthington Pump & Machinery Leeds & Northrop Co., 1133 : Corp., 1040:1047 McDonnell & Miller. 1194-1195 . Airtemp Div., Chrysler-Gorp- 96* 967 , York' Corp., 960 - Merooid Corp-. The. 1134-1135 Penn Electric Switch Co., 1141 Belanger Fan & Blower Co., 1054 . 1055 * , Sarco Co.. Inc., 1218-1219 n Buffalo Forge Co.. 1056 CONDENSERS - Crarier Corp.,' 944-945 .' Curtis Refrigerating Machine Div.` . Acme Industries. Inc., 1030 CONTROL EQUIPMENT, of Curtis Mfg. Co., 1040 . Aerofin Corp., 1031-1033 ' \ Combustion . DeBothesat Fans Div., American Baker Ice Machine Co., 1038 Bell & Gossett Co., 1196-1197 * Condenser Service & Engineering Co.. Inc., 1034 Machine & Metals, Inc.. 1059 ' Farr Co.. 1013 - . . ' Brunner Mfg. Co.; 1039 Detroit Lubricator- Co., Div. of Fedders-Quigan Corp-. 980 . Carrier Corp., 944-945 . _ American Radiator & Standard Frick Co. (Inc.), 1041 - 'Condenser Service & Engineering ' Sanitary Corp., 1122-1123 ` G & O Mfg. Co.-; The. 1035 . . - Co.. Incl, 1034 .. Fulton Sylphon Co., The. 1124-1125 General Electric Co. (Bloomfield. ,, Curtis Refrigerating Machine Div. Illinois Engineering Co., 1216-1217. N. J.),'948-949 .. - of Curtis Mfg. Co.. 1040 Iron Fireman Mfg. Co., 1178-1179 Kramer-Trenton Co., 985 ' \ Farrar & Trefts, Inc.. 1158 . Leeds & Northrop, 1133 La-Del Conveyor & Mfg. Co., 1062 /Fedders-Quigan Corp-* 980 * - Mercoid Corp-, The, 1134-1135 1063 . * Frick Co. (Inc.), 1041 . - Penn Electric Switch Co., 1141 Mario Coil Co., 1042 .- G.& O Mfg. Co.. The; 1035 Webster Engineering Co., The, 1180 Modine Mfg. Co., 988-989 ; i Kramer Trenton Co.. 985 White-Rodgers Electric Co., 1146 John J. Nesbitt, Inc.. 994 . . Mario Coil Co.. 1042 \ - L. J. Wing Mfg. Co.. 1000-1002 Niagara Blower Co., 950 - 'Niagara Blower Co., 950 . * Refrigeration Economics, Inc., 995 /J. F. Pritchard & Co., 1025 ' Refrigeration Economics Co.. Inc.; ?95., j - CONTROLLERS' AND CON TROL EQUIPMENT (See also Rome-Turney Radiator Co., 1036. B. F. Sturtevant Co., Div;, West- inghouse Electric, 954-959. 1018 Rome-Turney Radiator Co.. 1036. Humidity and Temperature-Con- 1019! Trane Co.. The, 998-999 * trot) '' - Tenney Engineering; Inc., 1145 v .United States Air Conditioning AIco Valve Co., 1118 Trane Co., The; 99*999 . ' Corp., 953. ' American Moistening Co.; 1021 . Utility Appliance Corp- 1073 - ; Universal 'Cooler Div.. - Interna . tional Detrola Corp., 1045 . VUter Mfg. Co., The, 1048 . Barber-Colman Co., 1084. 1121 Detroit Lubricator Co., Div. . . American Radiator & Standard -,B.'F. Sturtevant Co., Div., West-, Sanitary Corp.,' 1122-1123 . ; Viking Air-' Conditioning Corp., The. 1074 * - *- Vilter Mfg. Co., The, 1048 L. J. Wing Mfg. Co.,-1000-1002 . s inghouse Electric, 954-959, 101* ' 1019 ; ... . Fries Instrument Div., . Aviation Corp., 1128 , Bendix. Wpithington Pump & Machinery Corp., 1046-1047 ' . ;-.. Williams Oil-O-Matic Div., Eureka * Williams Corp., 1190 . Worthington Pump & Machinery . ' Corp-. 104*1047 . Young Radiator Co.V997 . General Electric Co: .(Schenectady,' N. Y.). 1076-1077 '. Illinois.Engineering Co.. 1216-1217- Iron Fireman Mfg.-Go.. 11784179 Johnson Service. Co.`, 1130-1131 COOLING EQUIPMENT, Oil //erofin. Corp- 1031-1033 - ' Airtemp Div.. Chrysler Corp., 966- .. < Leeds & Northrop Co., 1133 '967- * CONDUITS, Underground Fit- tings . ; ; v. , Mercoid Corp., The; 11344135 Bell, and Gossett to.. 119*1197' Minneapolis-Honeywell Regulator Carrier Corp-. 944-945 '- - . ` Co., 1136-1137 . . v. Condenser Service ;& Rnpinpring - American District Steam Co.; 1226; Parks-Cramer.Co.; 951*. . / ' .- . Co.; Inc., 1034. * 7 .. 1236 * ' ' Penn Electric Switch Co-114L ". Fedders-Quigan Corp- 980 : Johns-ManviUe, 1258-1259 - ' " Powers Regulator Co., The; 1142" ` ` G & O Mfg. Co-The,'1035 * . H. W. Porter & Co., Inc- 1237.. Ric-wiL Co., The, 1238 " , .CONDUITS,'Underground Pipe American District Steam Co., 1226;. 4236 ... E. B. Badger & Sons Co.. 1110-1 111' Sarco Co-. Inc., 1218-1219- Taylor Instrument Cos., li44' - r Tenney Engineering, Webster Engineering CInoc.,.,T1h1e4. 511 80- ' Westinghouae Electric Corp.,1078- 1079 . .. General Electric Co. (Bloomfield. . N: J.), 94*949 ; . Mario Coil Co- 1042 _ .. Modine Mfg. Co- 98*989: -' Refrigeration Economics Co- Inc.,] >995'. * - \ White-Rodgers Electric; Co., `1146, Trane. Co- The, 99*999 ' : ' Universal Cooler Div- ' Interna-'. tional Detrola Corp- 1045 - - Johns-Manville, 1258-1259 ! H/W. Porter & Co., Inc.. 1237 CONVECTION HEATERS . VUter Mfg. Co- The, 1048 - .. * Worthington Puinp' & Machinery' Wc-wiCCo.1. The. 1238. ../ ^ . American Radiator & .Standard Sanitary.Corp.,-1148-1149 ' -. ' Corp- 1046-1047 Bell & Gossett Co., 1196-1197 ". CONTROL, Air Volume Damper C. A. Dunham Co., ElectromodeCorp- 1206-1210 | Div. American COOLING EQUIPMENT, ` . (See also Water Cooling)- Water - ; Air Devices, Inc., 1080-1081 ' Foundry Equipment Co., 977 Acme Industries, Inc.; 1030 - ' ,, .Anemostat Corp. of America, 1082 McQuay. Inc.;' 986-987 . .; Aerofin'Cbrp;.-I031-1033 ' . ; Barber-Colman Co., 1084,1121 Modine Mfg. Co., 988-989] ` ; - Airtemp Div., Chrysler Corp.,- 966- ' - Johnspn Service Co- 113*1131 . - D. J. Murray Mfg. Co., 990 , / 967* ' \ *_ . - w Mihrieapolis-Honeywell - Regulator % : Co:; 1136-1137 - . . . . - Powers Regulator"Co., The, ll42`- . -.vRe^ister. & Grille- Mfg. - Co.. rinc.; / 4094 / . \ ^ .- Rome-Turney. Radiator Co.,'1035-' April Showers Co- 1022 . -] 1036 . .' ' . Bell & Gossett Co.; 119*1197 - T Trane Co.. The, 99*999 ' . . Carrier Corp- 944-945 ' ,- Tuttie & Bailey, Inc., 1092-1093 Condenser Service & Engineering United States Radiator Corp., 1172- - Co- Inc, 1034 - r Tuttle' & Bailey,. Inc., 1092-1093 . , 1173 . . /]/ Young Regulator Co., 1096' ' - ' Young Radiatur.'Cu.,' 997 " *' *:; Curtis Refrigerating Machine Div.. of Curtis Mfg. Co- 1040-' . -Please mention THE GUIDE 1946 when writing to' Advertisers ' 'A:,/Index- to Modern- Equipment : l 919 Fedders-Quigan Corp-980 V CORROSION, -Treatment of -'.; W. B. Connor Engineering Corp., - Frick Co. (Inc). 1041 -; . ./ Research Products Corp- 1020 ' ' . General Electric Co. (Bloomfield.-N. J.), 94*949* ... Vinco Co.. Inc- The, 1192.1193 , 100*1009. 1085 ' Hendrick Mfg. Co- 1087* * Johnson Service Co-.113*1131- Lilie-Hoffmann Cooling Towers, Minneapolis-Honeywell Regulator Inc- 1023 ^ COVERING, Pipe- ' ` * Co- 113*1137 i rMarley Co- The, 1024-' - ' Powers Regulator-Co- The, 1142 Mario Coil Co- 1042 * Baldwin-HUl Co-1249 United States Register Co-' 1095 ~ , John J: Nesbitt. Inc, 994 - ' Niagara Blower Cp- 950 ' J.-F. Pritchard & Co- 1025 ' /- Refrigeration Economics Co- Inc- :v. 995- ,. . - Rogers Diesel, and Aircraft ..Corp': - (Coey Floating FUm' Cooling Philip Carey Mfg. Co- The, 1252 1253. . . Eagle-Picher Co- The. 1254 Johns-Manville, 125*1259 Owens-Corning Fiberglas Corp- 1014-1015 H. W. Porter & Co- Iric- 1237 Webster Engineering Co- The, 1180 Young Regulator Co- 1096 '*'" \ DAMPERS, Back Draft (SeeDom Pers.Air Vofume Conirol) . ' - "Tower). 952,'1026 ' - - . ,Ric-wiL Co- 1238 - * ' Tenney Engineering, Inc, 1145 . Ruberoid Co.%The,126*1269 . DAMPERS, Flue * .. //_ i-Trahe Co- The, 99*999 . . . Turtle & Bailey, Inc., 1092-1093 /"Vilter Mfg. Co., The, 1048 - * CUT-OFFS, Low Water Water Cooling Equipment Corp., 1027 . . General Controls, 112*1127 - - United States Register Co- 1095 Young Regulator Co- 1096 . * .. '.'Worthington Pump & Machinery.* McDonnell & Miller, lf&4-1195- _ Corp- 104*1047 ' Pehn Electric Switch Co- 1141 . '' DAMPERS, Mechanical . Yarnall-Waring Co- 1232 ', American Foundry & Furnace Co., ' York Corp- 960 -. Young Radiator Co., 997 . . 962-963 . ^ DAMPER REGULATOR SETS Barber-Colman Co- 1084, 1121 _J" Automatic Products Co- 1120 - Belanger Fan & Blower Co- 1054 '- COOLING TOWER FANS; - Barber-Colman Co- 1084, 1121 .1055 ^' 'American Blower Corp- 94*941. ] '.Belanger Fan & Blower Co./1054 1055 ' . ' . . ]] J DeBoth'ezat Fans. Div- American Hart & Cooley Mfg, Co- 108*1089. Johnson Service Co- 113*1131 .1 Mercoid,Corp- The,-1184-1135 Powers Regulator Co- Tbe/.1I42 . Minneapolis-Honeywell Regulator Young Regulator Co- 1096 /- Co/. 113*1137 . -,, . .^*j. ; Machine & Metals, Inc- 1059 . Penn Electric Switch Co.-.1141 - HartzeU Propeller Fan Co. (Div. of Trane Co- The, 99*999 . . DEHUMIDIFIERS Castle HUls Corp*). 1064 . United States Regulator Co- 1095 Air & Refrigeration Corp.'; 939 ' > ; Mario CbU Co.,1042 ' .. White-Rodgers Electric Co- 1146 American Blower Corp- 94*941 ' *J. F. Pritchard, & Co- ,1025. * J/- Pfopellair, Inc- 1068 - -. B. F. Sturtevant'Co.,* Div- West ]. inghouse Electric, 954-959, 101* DAMPER REGULATORS, Boiler (See also Regulators) . * ' Bayley Blower Co- 1052 ' . Bryant Heater Co.. The.-961- * Buffalo Forge Co., 1056 < Carrier Corp- 944-945 ' :V>' 1019 . American Radiator Standard Mario Coil Co- 1042 ' \ " Water Cooling Equipment Corp-'' . Sanitary Corp- 114*1149 - McQuay, Incl, 98*987 . ` ' V. 1027 .. - '' Automatic Products Co- 1120 ' John J. Nesbitt, Inc- 994 /' Detroit :Lubricator - Co- Div. of Niagara Blower Co- 950->: . - .: COOLING TOWERS, Atmos- American Radiator & Standard v pheric, Mechanical Draft,* ' Sanitary Con>- 1122-1123 . -Forced Draft, Induced-Draft . Minneapolis-Honeywell Regulator J. F. Pritchard & Co- 1025 . - . Rogers Diesel & Aircraft Corp* (Rogers-Research. System), 952, (See ~ also 'Cooling' Equipment; *; Co;. 113*1137. . 1026. . * . . - Water) * ' H. * A; Thrush & Co- 119*1199 H. J; Somers, Inc- 101*1017. * ' :;Air & Refrigeration Corp.,-939. rCurtis-Refrigerating Machine Div. . of Curtis Mfg. Co- 1040. . . .^Ldie^Hoffman Cooling Towers, Inc- i?- 1023 '/Marley.Co- The, 1024" - . ; Mario Coil Co- 1042 .' " . ^ ;?Jos. A':' MtirtbceUo & Co- 1028'. ' /D. J/ Murray Mfg. Co- 990 ' Trane Co-99*999 , '. . - Webster Engineering Co- 1180' White-Rodgers Electric '.Co- 1146' -Young.Regulator Co- 1096/ ' DAMPER REGULATORS, Furnace. . - ` - Automatic Products^Corp.v 1120 . . B. F. Sturtevant Co-. Div- West- inghouse Electric. 954-959, 101* . 1019 .. Tenney Engineering, Inc-1145 '. Trane Co.,`The, 99*999 ` Vilter Mfg. Co- The, 1048 . ] ]' Worthington. Pump & Machinery Corp- 104*1047 . . . York Corp., 960. .. ' . 'J J/F. Pritcharii & Co- 1025 ` .. Rogers Diesel-& Aircraft Corp-- L.' (Coey Floating Film Cooling ; Tower), 952. 1026' . Barber-Colman Co-.1084,1121 / Detroit Lubricator Co./. Div. of American. Radiator & Standard Sanitary Corp- 1122-1123 - DEHYDRANTS" ' Dow Chemical .Co- The, 1114 - " ' -. B. F.- Sturtevant Go- Div- 'West Fulton Sylphon Co- The, 1124-1125 . Henry Valve Co- 1129* * . . - . . ,, inghouse Electric, 954-959, .101* Minneapolis-Honeywell Regulator - Research Products Corp-'1020 - .1019 - . / Trane Co-The. 99*999 - : Co./113*1137 ' _ Penn Electric Switch Co- 1126 '. f. * >'. - Water Cooling Equipment Corp., .United States Register Co- 1095 - DEHYDRATION SYSTEM, r. 1027 . White-Rodgers -Electric Co-- 1146 Compression Equipment . . ."-Worthington Pump-& Machinery Young'Regulator Co- 1096 ^ Corp- 104*1047 - . ` Mills Industries, Inc- 1043 r ,`* . .Young Radiator Co., 997 ^. -'. ' ' CORK- PRODUCTS JStc also Insulation) ' DAMPERS, Air Volume Control. DEHYDRATORS, Refrigerant American Foundiy & Furnace Co-' 962-963 * . , Automatic Products Corp** 1120/*' Anemostat Corp. of;America, i082 Henry Valve Co- 1129 *.. -/ . Armstrong Cork Co-: 1248 Barber-Colman Co- 1084,1121 MueUer Brass Co.,ai0*1107. _JCorfund Co., Inc., The, .1262 - . .Belanger Fan: &* Blower Co- 1054 J. F. Pritchard & Co-. 1025 / ,. T/. Mundei Cork .Corp.,-1264* . 1055. - Vulcan Radiator Corp- 1037 * -' Numerals following Manufacturers' Names refer to pages In-the Catalog Data Section. DEODORANTS _ Owens-Coming Fiberglas Corp., EXHAUSTERS 1 Dow Chemical Co.. The. 1114 W. B. Connor Engineering Corp., 1008-1009,1085 . . W. H: Wheeler, Inc.. 1003 . . . 1014-1015 - Air Devices. Inc., 1080-1081 J. F. Pritchard & Co., 1025 American Blower Corp., 940-941 B. F. Sturtevant. Co., Div., West- inghouse Electric, 954-959, 1018 .1019 . American Coolair Corp,, 1050-1051 Belanger Fan & Blower Co., 1054 1055 \ . DESTROYERS, Soot {See Soot Buffalo Forge Co., 1056 ' , Destroyer) ' DUST COLLECTORS, Cloth Champion Blower & Forge Co.. Type 1057 DIFFUSERS, Air (See Air Dif fusers, and Ventilators, Floor and Walt)'' . American Air Filter Co., Inc., 1006 1007 Dollinger Corp. (formerly Staynew Filter Corp.), 1010-1011 . Chelsea Products, Inc.-, 1058 DeBothezat Fans Div., American - Machine & Metals. Inc., 1059 Ilg Electric Ventilating Co., 982. 1060-1061 DISTRICT HEATING (Sa also Corrosion Treatment of--Expan- - EJECTORS, Sewage New York Blower Co., The, 1067 Schwitzer-Cummins Co., 1072 - - sion-Joints--Insulation, Under .Chicago Pump Co., 1204 " B.'F. Sturtevant Co., Div., West- ground--Meters,Pipe) - American District Steam Co.; 1226. . 1236 ... ' H. W. Porter & Co:, Inc., 1237- .Ric-wiL Co.. The, 1238 - Condenser Service & Engineering inghouse Electric, 954-959. 1018 Co.. Inc.', 1034 . - - * 1019 v Nash Engineering Co., 1202-1203 Trane Co., The. 998-999 , Utility Appliance Corp., 1073 . ELECTROSTATIC AIR L. J. Wing Mfg Co,, 1000-1002 - CLEANERS DRAFT APPARATUS {See Blott American Air Filter Co., Inc., 1006 EXPANSION JOINTS . . ers, Forced Draft) 1007 . American District Steam Co., 1226, B. F. Sturtevant Co., Div., West- . 1236 . , .- DRAFT CONTROL, Barometric :Preferred Utilities Mfg. Corp., 1166 inghouse Electric, 954-959, 1018 Atlantic Metal Hose Co.. Inc:. 1101- 1019 - E. B. Badger& Sons Co., 1110-1111 Chicago Metal Hose Corp., 1102 ENGINES. Diesel. Crane Co., 1154-1155 - DRYING; EQUIPMENT Aerofin Corp., 1031-1033 ' . Buffalo Forge Co., 1056. ' Worthington Pump & Corp:, 1046-1047 Machinery Fulton Sylphon Co., The. 1124-1125 Arthur Harris & Co., 1115 ' Illinois Engineering Co.. 1216-1217 Campbell Heating Co., 964-965 Carrier Corp., 944-945. ' ENGINES, Steam . . . Seamlex Co., Inc., 1103 Warren Webster & Co., 1222-1223 G> O Mfg. Co., The. 1035 - B. F. Sturtevant Co.. Div., West- . Yarnall-Waring Co., 1232 ' Modine Mfg. Co., 988-989 National Heater Co.,'991 Niagara Blower Co.. 950 inghouse Electric. 954-959, 1018 1019 - . Vilter Mfg. Co., -The, 1048 J. F. Pritchard-& Co., 1025 . Bi F: Sturtevant Co., Div.. West- EVAPORATIVE CONDENSERS inghouse Electric. 954-959, 1018 . {See Condensers and Evaporators). 1019 ' EXPANSION LOOPS American District Steam Co.;. 1226, 1236 .` - E. B. Badger & Sons Co., 1110-1111- Ric-wiL Co., The, 1238 . ' Trane Col, The. 998-999. , -Vulcan .Radiator Corp., 1037 evaporators' EXPOSITIONS : ,L. J. Wing Mfg. Co.. 10CKM002 Acme Industries. Inc., 1030 , International Exposition Co., 1147 Worthington Pump & Machinery Condenser Service -& Engineering - .Corp., 1046-1047 , York Corp., 960 - ; . . Co.. Inc., 1034 . Curtis Refrigerating Machine, Div. FAN BLADES \ ~ - . "- of Curtis Mfg. Co., 1040 Champion Blower & Forge Co., Farrar & Trefts, Inc., 1158 . 1057 .. . -DUCT INSULATION (See Insu- Fedders-QuiganCorp., 980 . Chelsea Products, Inc.,' 1058 ' . lation.lfuct) - - General Electric Co. (Bloomfield. Clarage Fan Co., 946 ' N. J.). 948-949 . . Hartzell Propeller Fan Co. (Div. of* DUCTS, Prefabricated {See also Fittings, Air Duds, Furnace). Kennard Corp., 984 Kramer-Trenton Co.. 985 Mario Coil Co., 1042 . CasUe Hills Corp.), 1064 . . J. F. Pritchard & Co.. 1025 * * Schwitzer-Cummins Co., *1072 . Philip Carey Mfg. Co., The. 1252^ -.1253-. . " . * . United. States Register Co., 1095 DUST COLLECTING Refrigeration Economics Co., Inc., 995 - . - - - - Rome-Tumey Radiator-.Co,, 1036 B. F. Sturtevant Co.'. Div.'.'West.Inghouse Electric. 954-959, 1018 1019 B. F. Sturtevant Co.:, Div., West- inghouse Electric, 954-959, 1018-. 1019 ,. .. Torrihgtoa Mfg. Co., The, 1070 1071 ' Utility Appliance Corp.', 1073 .'^EQUIPMENT Air Devices, Inc., 1080-1081 Air-Maze Corp.. The, 1004-1005 American Air Filter Co., Inc., 1006 .1007 - . American-Blower Corp.,.940-941 ' Buffalo Forge Co., 1056 ' . Trane Co.. The, 998-999 ' Vilter Mfg. Co.. The, 1048 . Worthington Pump & Machinery Corp.. 1046-1047 York Corp.. 960 Young Radiator Co., 997 Water Cooling. Equipment -Co., 10271 V ` - L. J. Wing Mfg. Co.. 1000-1002 FAN MOTORS {See Motors. Elec- trie): .. - ` : ` Chelsea Products,Tnci, 1058 ' Dollinger Corp. (formerly Staynew Filter-Corp.,) 1010-1011 - Farr CoVl013 '- EXHAUST Exhaust)' HEADS . (See Heads, FANS, Attic '* - . Air Controls, Inc;, 1049 . - , American Coolair Corp.. 1050-1051 Ilg Electric yentilating Co., 982. . EXHAUST TUBING, Flexible Belanger Fan & Blower Co., 1054- 106CM061- - . . . , . ; {SeeTubing, Flexible, Metallic) - 1055; . Please mention THE GUIDE 1946 when writing-i Advertisers ; Index to Modem -Equipment 921 . G. C. Breidert Co., 1083 . Jaden.Mfg: Co.,,983 . . - Hartzell Propeller Fan Co. (Div.'of Buffalo-Forge Co., -1056' ' - l^a-Del Conveyor & Mfg. Co., 1062 -CasUe Hills Corp.), 1064 Champion Blower .& -Forge Co., 1063 - . Ilg Electric VenUlaUng Co., 982,. 1057'. . .. Lau Blower Co., The. 1065 . ' 1060-1061 . Chelsea Products, Inc., 1058 . - Morrison Products/Inc., 1066 ' -^Clarage Fan Co., 946 New York Blower Co., The, 1067 DeBothezat Fans Div., American Schwitzer-Cummins Co., 1072 Machine & Metals, Inc-. 1059 - ; B. F. Sturtevant Co.,' Div., WestHartzell Propeller Fan Co. (Div. of inghouse Electric, 954-959, 1018 La-Del Conveyor & Mfg. Co., 1062^ 1063 . . New York Blower .Co., The, 1067 Propellair, Inc., 1068 . Schwitzer-Cummins Co.. 1072 CasUe Hills Corp.), 1064 1019 . B. F. Sturtevant Co'.. Div., West- Ilg Electric VenUlating Co., .982, .Tomngton Mfg. Co., The, 1070 1060-1061 . 1071 . inghouse Electric, 954-959, 1018 1019 - '. La-Del Conveyor & Mfg. Co., 1062 Trane Co., The, 998-999 Tomngton Mfg; Co.. The, 1070 . 1063 United States Air CondiUoning 1071 . Lau-Blower Co., The, 1065 -Corp., 953 Schwitzer-Cummins Co., 1072 Utility Appliance Corp., 1073 FANS, Propeller .. H. J. Somers, Inc.. 1016-1017 B. -F. Sturtevant Co., Div.. West - inghouse Electric, 954-959; 1018 . 1019 ... Viking Air CondiUoning Corp., The. 1074 L. J. Wing Mfg. Co., 1000-1002 Air Controls, Inc.. 1049 ' * . American Blower Corp.. 940-941' American Coolair Corp., 1050-1051 Tomngton Mfg. Co., The, 1070 1071 ; FANS, Electric Bahnson Co;, The, 942-948-. - . Belanger Fan & Blower Co., 1054 Viking Air Conditioning Corp., American Coolair Corp., 1050-1051 1055 . . - The, 1074 Belanger Fan & Blower Co., i054-' Buffalo Forge Co.. 1056 . . Water Cooling Equipment Co.; 1055 . Champion Blower & Forge Co., 1027 . ' Buffalo Forge Co., 1056 1057 Champion Blower & Forge Co., Chelsea Products, Inc,, 1058 . : 1057. . Clarage Fan Co., 946 ' -FANS, Axial Flow Chelsea Products, Inc., 1058 , DeBothezat Fans Div., American American Blower Corp., 940-941 Bahnson Co., The. 942-943 ' Belanger Fan & Blower Co., 1054 - 1055. .: Buffalo Forge Co.. 1056 ' . Champion Blower & Forge Co.; Clarage Fan Co., 946 - . Machine & Metals, Inc., 1059 Ilg Electric VenUlaUng Co., 982, Hartzell Propeller Fan Co. (Div. of 1060-1061 . . . . CasUe Hills Corp-). 1064 . La-Del Conveyor & Mfg. Co., 1062 Ilg Electric VenUlaUng Co., 982, 1063 -. - , 1060-1061 -. Herman Nelson Corp., The,' 992-993 Lau Blower Co., -The. 1065 B. F. Sturtevant Co., Div., West- New York Blower Co., The, 1067 . 1057 inghouse Electric, 954-959, 1018 J. F. Pritchard & Co., 1025 Chelsea Products, Inc., 1058 * 1019 . . Propellair, Inc., 1068 . -Clarage Fan.Co., 946 , Torriugton Mfg. Co., 1070-1071 Schwitzer-Cummins Co., 1072 DeBothezat Fans Div., American Machine & Metals, Inc.. 1059 Hartzell Propeller Fan Co. (Div. . .. Castle Hills Corp.), 1064 . - Ilg Electric Ventilating Co;, 982. FANS, Furnace American Foundry & Furnace Co., 962-963 - . B. F. Sturtevant-Co... Div., Westinghouse Electric, 954-959, 1018 1019 . Tomngton Mfg. Co., The, 1070 1071 - -. ' .1060-1061 . .-La-Del Conveyor & Mfg. Co., 1062 .. 1063 - Herman Nelson Corp., The, 992-993 J. F,. Pritchard & Co., 1025 -:Propellair, Inc., 1068 ' ` ` Buffalo Forge Co., 1056' _ Campbell Heating Co., 964-965 Champion Blower & Forge Co.. 1057 Chelsea Products, Inc., 1058 ' Clarage Fan Co., 946 - . . Trane Co., The, 998-999 - Utility Appliance Corp-. 1073 ` Viking Air CondiUoning Corp., The. 1074 . . Water Cooling Equipment `Co., 1027 ' Schwitzer-Cummins Co.,-1072 . *. - Hastings Air CondiUoning Co.,- L. J. Wing Mfg. Co., 1000-1002 "B.*F. Sturtevant Co.. Div., West Inc.. 947. ' inghouse Electric, 954-959, 1018 .. 1019 . ', Ilg Electric Ventilating; Co., 982, 1060-1061 FANS, Standard Code ' Viking s Air CondiUoning Corp., Jaden Mfg. Co., 983 - The. .1074 __ " - La-Del Conveyor & Mfg. Co.. 1062 Waiter Cooling" Equipment . Co., 1063 . . v 1027 _ . Lau Blower Co., The, 1065- . L. J. Wing Mfg. Co.. 1000-1002 . Meyer Furnace Co., The, 969 Morrison Products, Inc., 1066 FANS, Centrifugal - - ' L. J.` Mueller Furnace Co., 970-971 Schwitzer-Cummins Co., 1072 Air Controls, Inc., 1049. _ B. F. Sturtevant Co., Div., West American'Blower Corp., 940-941 American Coolair Corp.. 1050-1051 Bayley Blower Co.,'1052 ` Belanger Fan & Blower Co., 1054 1055: , Buffalo Forge Co., 1056 . Campbell Heating Co., 964-965 . inghouse Electric, 954-959,'1018 1019 ^- . United - States Air'' CondiUoning Corp., 953. ' .- Utility Appliance Corp., 1073 Viking - Air Conditioning Corp., The. 1074 . Propeller Fan Manufacturers Asso- daUon, 1069 . FANS,'Supply and Exhaust. - Air Controls, Inc., 1049 "- American Blower,Corp., 940-941 ^ American Coolair Corp., 1050-1051 Bayley Blower Co., 1052 . Belanger Fan & Blower Co., 1054 1055 . .; Buffalo Forge Co., .1056 Carrier Corp-, 944-945 , . Champion Blower & -Forge Co., 1057 . . ` Chelsea Products/Jnc., 1058 . Clarage Fan Co., 946 ' " ' " Carrier Corp., 944-945 ' ` v . Champion Blower & Forge- Co., .. 1057. . Chelsea.Products, Inc., 1058 - FANS, Portable Bayley. Blower Co., 1052 Belanger Fan & Blower Co.;' 1054 DeBothezat Fans Div.,' American Machine & Metals, Inc.. 1059 Hartzell Propeller Fan Co. (Div. of Castle Hills Corp-). 1064 ' ClarageFan Co., 946 . 1055 ; ; . - . Ilg'Electric Ventilating Co.. 982/ Hastings Air Conditioning Co., Champion Blower & Forge -Co., 1060-1061 - ' -.Inc.. 947 . 1057 Jaden Mfg. Co., 983 ' ' - Ilg Electric VenUlating Co.; 982, Chelsea Products, Inc.,'1058 - - La-Del Conveyor & Mfg. Co., 1062 * 1060-1061. . . Clarage Fan Co., 946 - ' 1063 - . -.Numerals following Manufacturers1 Names refer to pages In the Gatalog'Data' Section.  922 V 19.46 Guide - Lau Blower Co.,,The, 1065 ' FITTINGS, -Flared . FLUE GAS ANALYSIS ` ' Herman Nelson Corp., The, 992-993 New York Blower Co., The, 1067 ^ Propellair, Inc.,.1068 -? Grinnell Co., Inc., 981, 1112-1113, 1211 '- . . Leeds & Northrup Co., 1133: ' Minneapolis-Honeywell Regulator Co., 1136-1137 - Schwitzer-Cuminins Co., 1072 * . H. j: Somers. Inc., 1016-1017 B. F. Sturtevant'Co., Div., West FITTINGS, Hot Water Heating . Systems ' - . .. inghouse'Electric, 954-959, 1016 -Taco Heaters. Inc.,-1200 " . . *- FORCED-AIR DUCTS and FIT TINGS (See Duets, Fittings) . 1019 . - H. A. Thrush &.Co., 1198-1199' Trane Co., The, 998-999 . - Trane Cp.. The, 998-999 . FORCED % DRAFT .COOLING ^Utility Appliance Corp., 1073 . -TOWERS (See also Fans, Cooling - .Viking, Air The, 1074 Conditioning . Corp., FITTINGS, Pipe,. Flanged *. Towers,-Induced Draft, Meckani- , cal Draft) ' Water- Cooling 1027 Equipment . Co., . -Baker Ice Machine Co., Crane Co., 1154-1155'' Inc., 1038, *Air * Refrigeration Corp., 939 L. J. Wing Mfg. Co... 1000-1002 Gr1ih2n11ell -C.o*.. 'Inc*., 981.. ill2-ll:l3. Lilie-Hoffman.CoolingTowers, Incl, 1023 '- FANS,/-Ventilating' (See Fans, "Attic, Axial Flow, Centrifugal, etc,) FEED WATER HEATERS (See - Heaters, Feed -Water) -5 Henry Valve Co., 1129 . ' .Vilter Mfg. Co;, .TheV:i048 ! ; ? Worthington Pump &- Machinery -Corp., ,1046-1047 ' . York Corp.,-960 - . * . -J. F. Pritchard & Co:, 1025 - Trane Co.. The. 998-999 Water Cooling Equipment* 1027 . . , Young Radiator Co;,* 997 ' - Co., '. .*, FEED WATER REGULATORS FITTINGS. Pipe, Plastic ` -:'(Se Regulators, Feed Water) Dow Chemical Co.. The. 1114, - FUEL BURNING EQUIPMENT Automatic (See Burners, Automalic;Furnace Burners iGasBurn- FEEDERS, Boiler Water FITTINGS, Pipe, Screwed ; crs;Oil Burners; Stokers) . - McDonnell.* Miller. 1194-1195 . Baker Ice Machine Co., 1038 Mueller Steam- Specialty Co.*, 1227 - Crane Co.. 1154-1155 ' - 'Penn Electric Switch Co.; 1141 Sarco Co.,.Inc.-, 1218-1219 .-'* * Grminnei ll. Co-.,-Inc., 981,'1112-1113, Warren Webster- & Co., 1222-1223. Henry Valve Co.; 1129 = Mueller Brak Co.. 1106-1107 FURNACE. PIPE Meyer Furnace Co.. The. 969 L. J. Mueller Furnace Co.; 970-971 Payne Furnace Co.,`972-973 United States Register Co,, 1095 FELT, Insulating'(See Insulation,. Vilter Mfg. Co., The, 1048 . " Fdt) ... . Worthington' Pump & Machinery FURNACES, Electric . . :` .Corp., 1046^1047 Leeds &*Northrup Co.,1133 . ;FELT, Sound Deadening ./ York'Corp,, 960 * - ' - Johns-Manville, 1258-1259'.; ' FITTINGS, Pipe, Solder FURNACES; OU Burning, Floor Lockport Cotton'Batting Co.'. 1263' Air Devices. Inc., 1080-1081 `Products'Research Co., 1230.-.. . `Crane Co.. 1154-1155' .. ,, Automatic Burner Corp;, 1181 .. . Wood* Conversion Co., 1272 . Mueller Brass Cot,, 1106-1107 ' - .* H; C.-Little Burner Co;,' 1188 FILTERS; Air (See also Air Clean- FITTINGS,. Pipe for Under FURNACES. WaSrai Air, Heavy -..ingEquipment) .. - ground'Conduit * Duty */.-, '. * - ` Air Devices, Inc.,-I080r1081- * Air-Maze -Corp., 1004-1005-'* . _ . American District Steam Co.. 1226, s. 1236 - - American Foundry & Furnace Co.,- . 962-963:-' * * '.'Air.& Refrigeration Corp.. 939'.- - H. \V. Porter & Co.. Inc.; 1237 Alrtherm Mfg. Co., 976 - * . - . .'American Air Filter Co., Inc.",M006- Ric-wiL Co., The, 1238 * . Campbell Heating Co.; 964-965 ^1007-= Dravo Corp., 978-979 . . . ., Badger Corp., 1012 '' *'."... -V FITTINGS, Welding. ' Iron Fireman Mfg. Co., 1178-1179 *'/*;.D:-OFCVoaw1rFIraI0eriin.1nlnCte4egso'-re-C1:Cr.0Coo.1!1Co.m50:ro1p1irn:13p).g;5..*`.41'(0-fFl*o1'l5ir0bm5-e1.re0gr1llay1sr.StaCyonrX'epw;.-.-f1'` TCGHurer1abinnn2erneHyeT.CVluloarCn.l.vsoe1,.,-1IC5nIno4cc-..1,..1*,1151915281971, ; 1112-1113, - x/ '\ Lee Engineering Co., .968' * * . . ' Meyer-Furaace.Co.. *The. 969 -. 1 L. J. Mueller Furnace Co.,970-971National Heater Co., 991 ... Payne Furnace Co.. 972-973 . v' _ - Research Products Corp., 1020 *1 H. J. Somers, Inc., 1016-1017 - FLANGES, Lead, Roof . . FURNACES, Warm Air, Resi B. F. Sturtevant Co., Div.,*West. inghouse Electric. 954-959; 1018 Eagle-Picher Co., The, 1254 . dence . . 1019 . > - . .Airtemp Div., Chrysler Corp., 966 FLOATS,- Feirous and Non- -967 FILTERS, Liquid .. Air-Maze Corp., The, 1004-1005 ferrous (Seamless) " '*" : Arthur Harris & Co., lil5 * American Foundry & Furnace Co., 962-963 . V -'X American. Radiator & Standard . Condenser_Service & ` Engineering Sanitary Corp., 1148-1149- - .* -V Co;,-Inc;, 1034 . - * . FLOATS,'Metal (SeealsoTraPand. Bryant Healer Co., The, 961 * * ; DoIIinger Corp. (formerly Staynew. - Valve) . . * `'Filter Corp;),' 1010-1011 *' ` ; ..Campbell Heating Co., 964-965 , ; Crane Co.. 1184-1155 , . -FIREBRICK^lMulating : Armstrong-Cork Cp.,-1248*'-' FLOOR. PLATES ^Grinnell Co.. Inc., . ' .' 981. 1112-1113. ' . Charles Demuth & Sons, 1086j ; Fitzgibbons.Boiler Co., Inc.', H56-* `1157. - ; -. *. ; *." *-.. 1211 ' . - < Gar WoodTndustries, Inc., 974-975 .Babcock'* Wilcox',,Co./The,. 1150 ' Jones & Laughlln Steel Corp., 1099 General Electric Co. .(Bloomfield, N'John9-ManviIle1'1258*i259 - ` . United States Steel Corp.,-1100 ' " N. j:). 948-949 T r'* Please mention THE GUIDE 1946 when' writing to Advertlsera; . : Index to Modern Equipment 923 Iron Fireman Mfg. Co., 1178-1179' GAGES, Water . ' S; T. Johnson Co.; H84ril85 . H.'C. Little Burner Co., 1188 Meyer, Furnace Co.. The. 969 L.'J. Mueller Furnace Co., 970-971 Payne Furnace.Co., 972-973 . - Crane Co.'. 1154-1155H. A. Thrush & Co.. 1198-1199 Wright-Austin Co.; 1231. Yarnall-Waring Co;, 1232 * Petroleum Heat & Power Corp., 1186-1187 . - GAS BURNERS Hendrick Mfg. Co.. 1087 ` Independent Register Co.; The, 1090 X. L.'J. Mueller Furnace Co.'. 970-971 Pyle-National Co., The, 1091 .* Register & Grille Mfg. Co:, Inc.,' 1094 - ... Tuttle & Bailey. Inc., 1092-1093 * Ray Oil Burner Co., 1189 Utility Appliance Corp., 1073 Williams Oil-O-Matic Div., Eureka Williams Corp., 1190 Babcock'* .Wilcox Co., The, 1150 Bryant Heater Co., The, 961 ' United States Register Co., 1095 Vulcan Radiator Co., 1037 - ' Combustion Equipment Div., Todd Young Regulator Co.. 1096 Shipyards Corp., 1182 GAGE GLASS PROTECTOR . Wright-Austin Co., 1231 *' .- GAGES, Altitude Crane Co., 1154-1155 HANGERS, Pipe Ilg Electric Ventilating Co.. 982, 1060-1061 , Grinnell Co., Inc., 981, 1112-1113, Ray Oil Burner Co., 1189. - ' 1211 . ' Webster Engineering Co., 1180 ' - Ric-wiL Co.. The, 1238 , - . v/.; Crane Co.. 1154-1155 GASKETING, Impregnated Felt HANGERS, Radiator. '- - Jas. P. Marsh Corp., 1028-1029 tV *' - . Products Research Co., 1230 . ' Bell & Gossett Co.. 1196-1197 . United States Radiator Corp., 1172- GAGES, Ammonia GASKETS, Asbestos . Crane Co.. 1154-1155 * ^ - r' Jas. P. Marsh Corp., 1028-1029 m. ... . Vilter Mfg. Co.. The, 1048 . . - * ' ' Crane Co.. 1154-1155 Johns-Manville, 1258-1259 - >>-'' GAGES, Compound . GASKETS, Cork_ ;?.;;Crane Co., 1154-1155 r~. Dole Valve Co., The. 1234 . Armstrong Cork Co., 1248 ; ; - Mundet Cork Corp., 1264 . -1173 Vulcan Radiator Co., 1037 ' HEADS, Exhaust G. C. Breidert Co.. 1083 Crane Co., 1154-1155 Wright-Austin Co., 1231 . , . Trane Co:. The. 998-999 ''v'v'GAGES, Liquid Level GLASS (See Insulation, Double * Class) - American Meter Co.,'Ina, 1119 *. Meriam Instrument Co., The, 1138 I'tT"-Mihneapolis-Honeywell Regulator . GLASS BLOCK (Sre Skylights) ROOFLIGHTS * . ' . Co.. 1136-1137. - HEADS, Sprinkler (Fire Protec- lion) - Grinnell Co., Inc., 981, 1112-1-113, 1211 . . HEAT SURFACE' J *--.* . Taylor-Instiument Cos., 1144 GLASS BLOCKS - Aerofin Corp., 1031-1033 - ' '*< ' * '.YamaU-Wariiig Col, 1232 American 3 Way-Luxfer Prism Co., G * 0 Mfg. Co.. The, 1035 ' ' 1239 .' Kramer Trenton Co.'. 985 - `.1GAGES, Pressure ; \ ` Owens-Illinois Glass Co., 1243 ; ' jfV;-American' Meter Co., Inc., 1119 Crane C.o,, 1154-1155 * Pittsburgh- Coming Corp., 1244 1245 . '. .' _ ;Fulton Sylphon Co., The, 1124-1125. X-Henry Valve-Co.. 1129 * ' GLASS,. Cellular .-. ^1* .Meriam Instrument Co., The, 1138 Owens-Illinois Glass Cb., 1243' * lis ~-''Minneapoli3-HoneywelI Regulator Pittsburgh Coming- Corp.,' 1244 Co., 1136-1137 : . 1245 ,. McQuay. Inc., 986-987 Modine Mfg. Co., 988-989' . . John J.'Nesbitt, Inc.,' 994 *. ' ' New York Blower Co., The, 1067.' Refrigeration Economics Co., 995- Rome-Tumey Radiator. Co., 1036' B. F. Sturtevant Co., Div., West- - inghouse Electric, 954-959. 1018 1019 , - - . . *. , x Trane Co;, The. 998^999 - |t^-\GAGES; Steam. - GOVERNORS. Pump . -Young Radiator Co., 997' Crane Co.. 1154-H55 ' . : ' McDonnell &'Miller, 1194-1195 "*.. . ,rV,JMinneapo!is-HoneywieU Regulator Mueller. Steam'Specialty Go.; Inc., HEATERS. Air VX.'.Co., 1136-1137 *... . 1227 . ' ' . ' vffi. Tra*n; e 'Co., The_. 998. --9 99 -Spence Engineering Co.', Inc.*,*1143 Aerofin Corp.. 1031-1033 * Airtherm Mfg. Ca, 976 . *, . I.'GAGES,' Tank / :. Meriam Instrument Co;, The. 1138 GRATES FOR FURNACES BOILERS AND Buffalo Forge Co., 1056 .- ' Campbell Heating^Co., 964-965 *. _. Carrier Corp., 944-945 ' ' ;. -- 'C. Mihneapolis-Honeywell Regulator Combustion Engineering Co., 1176 Combustion Engineering Co.; 1176: r Cm, 1136-1137 . Detroit Stoker Co., 1177 . Dravo Corp!, 978:979 / * '" *.-. . GAGES, Vacuum. - - Fitzgibbons Boiler Co.,-Inc., 1156 Electromode Corp*. (Div. American = 1157 . Foundry Equipment Co.), 977; 'Fedders-Quigan Corp., 980 . ;VCrahe Co., 1154-1155 ` t Instrument Co., The, 1138 A^-'-MinneapoIis-Honeywell. Regulator Co..'1136-1137 . . . - t;^'-'Mueller lhstrument'Co.,-1139. ; GRILLES, REGISTERS AND' ORNAMENTAL METAL WORK (See also Louvers and Grinnell Co., Inc., 981,'1112-1113, 1211 . Ilg'Electric Ventilating Co.; 982,' - 1060-1061 - v .; ; Registers) ., ' .* Lee Engineering Co., 968 * * - * U: -Air Devices, Inc., 1080-1081 : H.-C.,Little Burner Co.,: 1188 ' - rvGAGES, Vapor American Foundry & Furnace Co.,, McQuay, Inc., 986-987- **- - .,, 962-963 ... Mario CoD Co!-, 1042 *-.. - '"**.. W,Rr Crane Co.! 1154-1155 Anemostat Corp. of America, 1082 Meyer Furnace Co., The. 969 V* - ^Minneapolis-Honeywell. Regulator Barber-Colman Co., 1084, 1121 - Modine Mfg. Co!. 988-989 sy;-Co., 1136^1137- .- * - Hart & CooleyrMfg. Co., 1088-1089 National Heater Co;,"991 -- .Numerals following.Manufacturers' Names refer to'pages In the Catalog Dam Section v 924 _ * 1946 Guide Herman Nelson Corp., The, 992*993 John J. Nesbitt, Inc., 994 Reznor Mfg. Co., 996 Rome-Turney Radiator Co., 1036 B. F. Stiirtevant Co., Div., West- inghouse Electric, 954-959, 1013* 1019 . Trane Co., The, 998-999 Utility. Appliance Corp., 1073 Young Radiator Co., 997 . HEATERS, Feed Water . . Taco Heaters, Inc., 1200 - BeU & Gossett Co., 1196-1197 . ..H. A. Thrush fit Co., 1198-1199 Brownell Co., The. 1175 Condenser 'Service-fit. Engineering Co., Inc., 1034 . National Radiator Co., The, 1164 1165 Worthington Pump fit Machinery Corp., 1046-1047 HEATERS,' Storage . American District Steam Co., 1226, 1236 .. Bell and Gossett Co.. 1196-1197 Brownell Co., The, 1175 Kewanee Boiler Corp., 1160-1163 HEATERS, Fuel Oil' Terre Haute Boiler Works Co., 1170. HEATERS, Automatic Hot Water, Domestic American District Steam Co., 1226,. 1236 HEATERS, Tank Air Devices Inc., 1080-1081 Airtemp Div., Chrysler Corp., 966 - 967 - , . American -Radiator & Standard " * Sanitary Corp., 1148-1149 .Automatic Burner Corp., 1181 . Bryant Heater Co., The. 961 Crane Co., 1154-1155 Gar Wood Industries, Inc., 974-975 General Electric Co. (Schenectady. .N.Y.), 1076-1077 S. T. Johnson Co.. 1184-1185 Automatic Burner Corp., 1181 Bell & Gossett Co., 1196-1197 Campbell Heating Co., 964-965 Condenser Service fit Engineering Co., Ina. 1034 Dravo Corp., 978-979 - National Heater Co.. 991 . National Radiator Co., The, 1164 1165 _ Combustion Equipment Div., (Todd Shipyards Corp.), 1182. ' Petroleum -Heat & Power Corp., 1186-1187 . American Radiator & Standard Sanitary Corp., 1148-1149 Bell and Gossett Co.. 1196-1197 Bryant Heater Co., -The, 961 Burnham Boiler Corp., 1152 Fitzgibbons Boiler Co.. Inc., 1156 1157 H.-B. Smith Co., Inc., The, 1167 Taco Heaters, Inc., 1200 Terre Haute Boiler Works Co., 117,0 Weil-McLain Co.. 1174 ' H. C. Little Burner Co.. 1188 York-Shipley, Inc.. 1191- '.Petroleum Heat & Power Corp., HEATERS. Unit 1186-1187 ._ Ray Oil'Burner Co., 1189 York-Shipley. Inc., 1191 Young Radiator Co., 997 , HEATERS, Gas Airtherm Mfg. Co., 976 ` . American Blower Corp., 940-941 .. Bryant Heater Co;, The 961 ' American Foundry fic'Furnace Co., Campbell Heating Co.. 964-965 962-963 Crane Co.. 1154-1155 Bayley Blower Co., 1052 . Dravo Corp., 978-979 ` Bryant Heater Co., The, 961 . HEATERS, Blast . Iig Electric Ventilating Co., 982, Buffalo Forge Co.,1056 .Aerofin Corp*. 1031-1033 Buffalo Forge Co., 1056. -. . Carrier Coip*. 944-945 Electromode Cop. (Div. American . Foundry Equipment Co), 977. -G & Q Mfg. Co., The, 1035 Kennard Corp., 984 Kramer Trenton Co., 985- ' 1060-1061 Lee Engineering Co., 968 Meyer Furnace Co., The, 969 National Heater Co., 991 Payne Furnace Co.. 972-973 Reznor Mfg. Co., 996. . ' Utility Appliance Corp., 1073 . Burnham Boiler Corp., 1152 ^Carrier Corp., 944-945 Clarage Fan'Co., 946 -- . Dravo Corp 978-979 ' C. A. Dunham Co., 1206-1210 ' Electromode Corp. (Div. American ' Foundry Equipment Co.), 977 Fedders-Quigan Corp.. 980 *, Lee Engineering Co., 968 ' Mario Coil Co.; 1042 McQuay, Inc.7 986-987- ' Modine Mfg. Co,, 988-989 ' John J.'.Nesbitt, Inc., 994 HEATERS, Hot Water Service Grinned Co., Inc., 981, 1112-1113, 1211 Air Devices Inc., 1080-1081 . Hartzed Propeller Fan Co. (Div. of . American District Steam Co.. 1226, 1236 , - . Castle Hills Corp.). 1064 ; Hastings Air Conditioning Co., American'. Radiator & Standard Inc., 947 . Refrigeration Economics Co., Inc., . Sanitary Corp;. 1148-1149 995 - . . . . . Bell and Gossett Co.. 1196-1197 .Iig Electric Ventilating Co., 982, 1060-1061 .. Rome^Turney Radiator Co., .1036 -Brownell Co., The, 1175 . - Jaden.Mfg. Co.. 983 B. F. Sturtevant Co., Div., West Burnham Boiler Corp., 1152 - - 'inghouse Electric, 954-959, 101&-* -1019- - ; . ". _Trane~ Co. -The, 998-999 'Vulcan Radiator Co.-, 1037 - Crane Co..,1154-1165 ... ,. Fitzgibbons Boiler Co., Inc., 1156 1157 '- Kewanee-Boiler Corp.', 1160-1163 Young Radiator Co., 997 " H. C. Little Burner Co., 1188 N Kennard Corp.. 984 Kramer Trenton .Co., 985. Lee Engineering Co., 968 McQuay, Inc., 986-987 Modine Mfg. Co., 988-989 D. J. Murray .Mfg. Co., 990 -. -- L. J. Mueller Furnace Co.,,970-971 National.Heater Co., 991 . HEATERS. Cabinet. Smith Co., Inc., The, 1167 ' National Radiator Co;, The, 1164 Swan Engineering Co., T 116' . . 1165 . . C. A. Dunham Co., 1206-1210 Modine Mfg. Co.. 988-989 . ' Herman Nelson Corp., The, 992-993 John J. Nesbitt, Inc., 994 - . ... Payne Furnace Co.,. 972-973 ' ,Taco Heaters. Inc.,' 1200 . Terre Haute Boiler Works Co., li70 Trane Co.; The,.998-999 United States Radiator Corp., 1172 1173 Weil-McLain Co., 1174 '. Herman Nelson Corp., The, 992-993 John J. Nesbitt, -Inc., 994 New York Blower Co.; The, 1067 Niagara Blower Co., 950. * . , Refrigeration Economics Co., Inc.. 995 Williams Oil-O-Matic Div., Eureka Reznor MfgrCo., 996 HEATERS, Electric Williams Corp., 1190 ' -' . B. F. Sturtevant Co., Div., West , inghouse Electric 954-959, 1018 Crane Co.-. 1154-1155 " . . HEATERS, Indirect - Electromode Corp. (Div. American . 1019.- ^ . ... Trane Co., The, 998-999 - . , /_Fouridry'Equipment Co), 977 - American' Radiator & - Standard United. States Air Conditioning General Electric Co. (Schenectady, Sanitary Corp., 1148-1149 - ' ' Corp., 953 ' . . '\ ' ;N.1Y.), 1076-1077 . . .. Bell & Gossett Co.-; 1196-1197 Warren Webster & Co.. 1222-1223' . Iig CElectric' Ventilating Co.,' 982, Crane Co., 1154-1155 . ... . . _ L. J.JWing Mfg. Co.,. 1000:1002- "...1060:1061*.- .: . John J. Nesbitt, Inc., 994 Young Radiator Co., 997, - - ` . Please mention THE GUIDE 1946 when' writing to Advertisers . ' Index to Modern Equipment 925 HEATERS, Unit, Gas Fired American Foundry fit Furnace Co., HEATING SYSTEMS, Gas Fired Aiithenn'Mfg. Co., 976 _ American Foundry fit Furnace Co.. . 962-963 . . 'American Radiator & Standard ' Sanitary Corp., 1148-1149 Bryant Heater Co.. The. 961 ' Buffalo Forge Co., 1056 Dravo Corp., 978-979 . Tig Electric Ventilating Co., 982, 1060-1061 Lee Engineering Co., 968 - McQuay, Inc., 986-987 L."J. Mueller Furnace Co., 970-971 `National Radiator Co., The. 1164 .1165 Reznor Mfg. Co.. 996 ..Utility Appliance Corp., 1073 ' HEATING SYSTEMS, Air, 962-963 ' American Radiator & Standard Airtemp Diy,, Chrysler, Corp., 966 Sanitary Corp., 1148-1149 . 967. ' * ' ' ' -' Anderson Products. Inc., 1233 Barnes & Jones, Inc., 1205 BeU & Gossett Co.. 1196-1197 Bryant Heater Co.. The, 961 Burnham Boiler Corp., 1152 Campbell Heating Co., 964-965 Crane Co.. 1154-1155 Charles Demuth & Sons, 1086 Dravo Corp., 978-979 C. A. Dunham Co.. 1206-1210 Electromode Corp. (Div. American Foundry Equipment Co), 977 . Gar Wood Industries, Inc., 974-975 General Electric Co. (Bloomfield, N. J.), 948-949 , Illinois Engineering Co.. 1216-1217 Iron Fireman Mfg. Go., 1178-1179 American Foundry & Furnace Co., 962-963 Bryant Heater.Co., The. 961 Burnham Boiler Corp., 1152 Campbell Heating Co.. 964-965 Crane Co., 1154-1155 Dravo Corp., 978-979. .. Gar Wood Industries, Inc., 974-975 General - Electric Co. (Bloomfield, N. J.). 948-949 . Lee Engineering Co., 968'- Meyer Furnace Co., The, 969 : L. J. Mueller Furnace Co., 970-971' National Heater Co., 991 - ' ' National Radiator Co., The, 1164 1165 v Payne Furnace Co., 972-973 . : Heavy Duty ,' Lee Engineering Co,, 968 Aerofin Corp., 1031-1033 H. C. Little Burner Co,, 1188 Airtherm Mfg. Co., 976 " American Blower Corp.. 940-941 Meyer Furnace Co., The. 969 HEATING SYSTEMS, Hot L. J. Mueller Furnace Co., 970-971 Water American Foundry fit Furnace Co., 962-963 . Campbell Heating Co., 964-965 .Carrier. Corp., 944-945 ' ..Dravo'Corp., 978-979 . -.-Iron Fireman Mfg. Co., 1178-1179 'Lee Engineering Co/, 968 ' > National Heater Co.,-991 National Radiator Co., The, 1164 1165 . Herman Nelson Corp.' The, 992-993 Payne Furnace Co., 972-973 . Ray OU Burner Co., 1189 . Sar^Co., Inc., 1218-1219 Airtemp Div.-, Chrysler Corp., 966 967 - Bell & Gossett Co.. 1196-1197 Burnham Boiler Corp., 1152 . . Gar Wood industries, Inc., 974-975 Hoffman Specialty Co.,`Inc., 1213 1215 . Meyer Furnace-Co.. The,-969 Spence Engineering Co., Inc^ 1143 National Heater Co., 991 ' ;Payne Furnace Co.. 972-973 . B. F. Sturtevant Co., Div., West ... inghouse Electric. 954-959, 1018 . Spencer Heater Div., The Aviation Corp., 1168-1169 . Taco Heaters, Inc., 1200 ' Trane Co.-, The, 998-999 1019 . United States Radiator Corp., 1172 Trane Co;, 998-999 " 1173 Warren Webster Co., 1222-1223 HEATING SYSTEMS, Air, Residence -. Williams OU-O-Matic Div., Eureka Williams Corp.. 1190 - L. J. Wing Mfg. Co., 1000-1002 Iron Fireman Mfg. Co., 1178-1179 L. J. Mueller Furnace Co., 970-971 National Radiator Co.. The, 1164 1165 - Ric-wiL Co., The. 1238 . Sarco Co.. Inc., 1218-1219. Taco Heaters, Inc.; 1200 Trane Co., The, 998-999 : H. A^Thrush & Co., 1198-1199 Warren Webster & Co., 1222-1223 Williams Oil-O-Matic Div., Eureka Aerofin Corp., 1031-1033 Williams Corp., 1190 '-Airtemp Div., Chrysler Corp., 966 967 `American Foundry & Furnace Co., . 962-963 . ./American Radiator & Standard c' Sanitary Corp., 1148-1149 . Bahhson Co.. The, 942-943 Bryant Heater Co., The, 961 Buffalo Forge Co., 1056 ' ' Burnham BoilerCorp., 1152 Campbell Heating Co., 964-965 Carrier Corp.,'944-945 -.Charles Demuth & Sons, 1086 ' Electromode Corp. (Div. American 'Foundry Equipment Co.), 977 -Fedders-Quigan Corp., 980 v :Gar Wood Industries, Inc., 974-975 General. Electric Co.,' (Bloomfield, !-.N. J.). 948-949 Iron Fireman Mfg. Co., 1178-1179 HEATING SYSTEMS, Coal-fired Airtemp Div., Chrysler Corp., 966 967 HEATING SYSTEMS, OU Fired American Foundry & Furnace Co., 962-963 . Air Devices, Inc., 1080-1081' - ' Burnham Boiler Corp., il52 . Airtemp Div., Chrysler Corp., 966 Campbell Heating Co.,-964-965 967 Dravo Corp*. 978-979 American Foundry & Furnace Co;, Iron Fireman Mfg. Co., 1178-1179 962-963 . _ Meyer Furnace Co., The, 969 Burnham Boiler Corp., 1152 ~ J ' L. J. Mueller Furnace Co., 970-971 Campbell Heating Co., 964-965 -' National Heater Co., 991 Charles Demuih & Sons, 1086 ' National Radiator Co., The, 1164 Dravo Corp., 978-979 - 1165 . , Gar Wood Industries, Inc., 974 975 - ` HEATiNG SYSTEMS, Electric General- Electric Co.- (Bloomfield. N. J.),*948-949 ' . * Electromode Corp. (Div. American Iron Fireman Mfg. Co.. 1178-1179 Foundry Equipment'Co.), 977 ' S. T. Johnson Co., 1184-1185 ` vH. C. Little Burner Co., 1188 Kewanee Boiler Corp., 1160-1163 'Meyer Furnace Co., The, 969 L. J. Mueller Furnace Cb., 970-971 HEATING SYSTEMS, Furnace ' Payne Furnace Co., 972-973 Airtemp Div., Chrysler Corp.. 966 ,Ray Oil.Burner Co., 1189 . 967 - . Williams Oil-O-Matic Div., Eureka Airtherm Mfg. Co., 976 ' ' Williams Corp., 1190-. Campbell Heating Co., 964-965 Lee Engineering Co., 968 H. C.' Little-Burner Co., 1188 Meyer Furnace Co., The; 969 L. J. Mueller Fumace-Co., 970-971 National Heater Co., 991 - National Radiator Co.,: The, 1164-. Crane Co., 1154-1155 , 1165 . . - ' ; ;HEATING~ SYSTEMS, Auto . v'matic Dravo Corp., 978-979 ', Lee Engineering Co., 968 Meyer Furnace Co.,' The,' 969 , Petroleum Heat & Power Corp.; 1186-1187 .. Williams Oil-O-Maiic Div., Eureka Airtemp Div., Chrysler Corn., 966- L. J. Mueller. Furnace Co., 970-971- ' Williams Corp., 1190 . - 967, ' - ' . National Heater Co., 991 . York-Shipley, Inc., 1191 - . Numerals following Manufacturers' Names refer to pages in the Catalog Data'Section 926 ^ ; : 1946 Guide f HEATING SYSTEMS, Steam HUMIDIFIERS - H. J. Somers, Inc., 1016-1017 >< Aerofin Coro., 1031-1033 ... - Airtemp Div,, Chrysler Corp'., 966 .967 ' , Anderson Products, Inc., 1233 Barnes & Jones, Inc., 1205 Air-Maze Corp.; The, 1004-1005 Air & Refrigeration Corp., 939' American Blower Corp.. 940-941' American Moistening Co., 1021 . American Radiator & Standard B. F. Sturtevant Co./ Div., West- inghouse Electric 954-959. 1018 1019 . Trane Co., The, 998-999 . United States Air Conditioning Corp., 953 .~ Bryant Heater Co.. The. 961 . Burnham Boiler Corp., 1152 C. A. Dunham Co.. 1206-1210 Gait Wood Industries, Inc... 974 Sanitary Corp., 1148-1149 Armstrong Machine Works; 1224 1225 . Bahnson Co., The, 942-943 Viking Air Conditioning Corp., 1074 - York Corp.. 960 ' n . 975 ... William S. Haines & Co.. 1212 Baker Ice Machine Co., Inc. 1038 .Barber-Colman.Co., 1084. 1121 HUMIDITY CONTROL Hoffman Specialty Co., Inc., 1213 Buffalo. Forge Co.. 1056 'American Moistening Co., 1021 1215 .. . . Burnham Boiler Corp., 1152 . Bahnson Co., The, 942-943 . ;Illinois Engineering Co..l216-1217 Carrier Corp.','944-945 , - Barber-Colman Co., 1084, 1121 - . Iron Fireman Mfg. Co.. 1178-1179 Clarage Fail Co/, 946 Friez Instrument Div., .Bendix L\ j; Mueller-Furnace Co^ 970-971 Farr Co.. i013 / Aviation Corp.;1128 `. National Radiator Co., The,. 1164-. Grinnell Co.. Inc, 981, 1112-1113, Johnson Service Co., 1130-1131 . .1165 . ' . 1211 . Leeds & Northrup Co., 1133 . . . '-Ric-wiL Co.. The, 1238 ' Johnson Service Co.. 1130-1131 ' Minneapolis-Honeywell Regulator . Sarco Co-,.Inc., 1218-1219. * Mario Coil Co.. 1042 ' Go., 1136-1137 . ; -Trane Co.. The, 998-999 _ . . McDonnell & Miller, 1194-1195 Parks-Cramer Co., 951 , . - -.Warren Webster & Co., 1222-1223 McQuay, Inc. 986-987 Penn Electric Switch Co., 1141 - Meyer Furnace Co.-, The, 969 Powers Regulator Co., 1142 . - HEATING SYSTEMS, Vacuum L. J. Mueller Furnace .Co., 970-971 H. J. Somers. Inc, 1016-1017 _ D. J. MuxrayMfg. Co., 990 B.-F. Sturtevant Co., Div., West/ Aerofin Corp.,-1031-1033 . Airtemp Div,, Chrysler Corp.,-966- ;967 - -, , . / " . American . Radiator & Standard Sanitary Corp., 1148-1149 . Niagara Blower Co., 950; Parks-Cramer. Co.. 951.' - ' .. inghouse Electric 954-959, 1018 1019 , . J. F.. Pritchard & Co.,-1025 '' H. J. Somers Inc, 1016-1017 * ` B. F. Sturtevant Co., Div., West- Taylor Instrument Cos.. 1144 . Tenney Engineering, Inc, 1145 White-Rodgers Electric Co.. 1146 Anderson Products, Inc.. 1233 - ' - inghouse Electric 954-959/018 Barnes &-Jones. Inc.. 1205 1019 . - HUMIDITY RECORDERS and . Crane Co;. 1154-1155 " Tenney Engineering, Inc. 1145 ` INDICATORS . C, A/Dunham' Co.. 1206-1210 Trane Co., The. 998-999 ' . . "William S. Haines & Co.. 1213 ' United States Air Conditioning Hoffman Specialty Co., Inc., 1213 . Corp.. 953 -- . :; 1215 ;* * . .. > ; L.wJ..Wing Mfg. Co.; 1000/1002 . Illinois. Engineering Co.. 1216-1217 York Corp., 960 . American Moistening Co., 1021 Friez Instrument. Div., Bendix A Aviation Corp.,'1128 , Illinois Testing Laboratories,'Inc.,' 1132 . f.Sarco Co.. Inc., 1218-1219 i Johnson Service Co., 1130-1131. '.Trane Col, .The, 998-999 4 / .Warren Webster & Co.,' 1222-1223' HUMIDIFIERS^Ceritral Plant Leeds & Northrup Co., 1133 . Minneapolis-Honeywell Regulator . Air & Refrigeration Corp.,"939 ' Co.; 1136-1137 . HEATING SYSTEMS. Vapor . . American Blower. Corp., 940-941 Bahnson'Co., The, 942-943 ' . ' Moeller lnstrument Co., 1139 " Powers Regulator Co., 1142 ' * . Aerofin' Corp... 1031/1033 ~ Barber-Colman Co., 1084; 1121 Taylor Instrument Cos.,-1144 Airtemp Div;, Chrysler Corp., 966- `Buffalo Forge'Co., 1056- . ' i. ' 967- _ ; - , -. r - v. ' Barnes & Jones. Inc., 1205 -- . `Bryant Heater, Co., .The;'961 : ; Carrier Corp./ 944j945 :. Farr.Covsl013: " - . ' ; Johnson Service Co., 1130/ll3i HYGROMETERS (See. also Hu-. . \midily Recorders and Indicators) C. A. Dunham Co., 1206-1210 McDonnell & Miller, 1194-1195 . American Moistening Co., 1021 / , Gar Wood.Industries. Inc, 974-975 /William S. Haines. & Co.. 1212 `-Hoffman Specialty Co.; Inc./1213<1215. \ .. Illinois. Engineering Co.. 1216-1217 ^ Sarco.Co.', -Iric.L. 1218-1219 Trane Co./The,, 998-999 Niagara.Blower Co., The, 950 *, Parks-Cramer Co^. 951 ' / . _ J: F. Pritchard &*Co.. 1025-- - . " Illinois Testing Laboratories; Inc., 1132 *. ; .. , Johnson Service Co., 1130-113T H. Jl Somers. Inc., 1016-1017 B. F.-Sturtevant Co.,. Div., Westinghouse Electric 954-959, 1018/ Moeller lnstrument Co., 1139 .. Palmer Co., The 1140 ' Parks-Cramer Co., 951 ' ` 1019 " ' ' ' ' .Taylor Instrument Cos., 1144 ; Warren;Webster &-Co.. 1220-i223 .VUter Mfg. Co., 1048 . ' Williams Oil-O-Matic Div., Eureka' York Corp., 960 . -Williams Corp., 1190 . ^ ' * INDUCED DRAFT COOLING TOWERS (See also Cooling ' HOSE, Flexible Metal ' HUMIDIFIERS, Unit `. 'Towers, Forced Draft. Mechanical .. - Draft) - ` . ' American Moistening Co., 1021 Atlantic .Chicago Metal Hose Co.. Inc. 1101 Metal-Hose Corp., 1102 - Armstrong 1225 Machine Works, . 1224 -. Seamier Cp*. Inc, 1103 .Badger Corp., 1012 . . Bahnson Co., The, 942-943 ' , *' HOSE, Liquid, Gas,'Vapor ' Buffalo Forge' Co., 1056 ' " -- < 'Carrier.Corp., 944-945 / /Atlantic MetalHose Co., Inc., 1101 Chelsea Products,'Inc, 1058 Chicago-Metal Hose Corp., 1102 ' Marley'Co., The; 1024- - " './ Baker Ice' Machine. Co., Inc, 1038 Buffalo Forge Co., 1056. ` ' Lilie-Hoffman Cooling Towers, Inc, ` 1263 - .: . Marley Co., The, 1024 . D. Ji Murray Mfg Co:, 990 ,* - J, F.` Pritchard & Co., 1025 . B. ;F. Sturtevant Co.. Div., West- . ...inghouse Electric, 954-959, 1018- D/ J. Murray Mfg. Co.,- 990 . ` 1019: .v HOT WATER-HEATING ; SYS- _ Niagara Blower Co.,'950 ; - , Water .Cooling. Equipment- Co,, '<* TEMS (See Heating Systems, Hot ' Parks-Cramer Co., .951 * - 1027 ' - ' - .:. Voter) J. F. Pritchard Sc Co./1025 -' '. \ Young Radiator Co., 997 ' 1 ; - , ^Please mention THE GUIDE 1946. when writing to.Advertisers 'zV-y^index-^io Modern Equipment _ . . _ : - -: v-' - ' 927 Z INSTRUMENTS,' Indlcatin*. Philip Carey Mfg. Co.. The. 1252 Cork Insulation Co..-Inc..'1251 . ,. ' (kmtrolUna and Recording .. -1253. K .; ' ' *' \. Eagle-Picher. Co/, The. 1254 .... . American Meter Co., Inc,,' 1119 - Friez : Instrument Div.. Bendix - l.' Aviation Coip/. 1128; . . "General Electric Co. (Schenectady, -- N. Y;), 1076-1077 . Celotex'Corp., The, 1250Cork'Insulation Co., .Inc.,' 1251 Eagle-Picher Co.. The,12^4 Insulite, 1256-1257. Johns-ManviUe. 1258-1259 ' . - . Insulite, 1256-1257 /' Insul-Wool lnsulation Co./ 1255 Johns-Manville. -1258-1259 ,. 0 Kimberly-Clark Corp., 1260-1261 Korfund Co., Inc., The, 1262 ' . .; - \ ' - Illinois Testing Laboratories, Inc, 1132' '~ Leeds & Northrup Co.. 1133. `' Minneapolis-Honeywell Regulator Co/ 1136-1137 ' . Z'- Moeller lnstrument'Co.. 1139 ` Palmer Co., The.-1140 . , . Mundet Cork Corp.. 1264 Owens-Coming Fiberglas Corp;, 1014-1015 - Pittsburgh Corning Corp.,' 1244^ 1245 - ; . Products Research Co., 1230 ' Ruberoid Co'. The, 1268-1269 Lockport Cotton, Batting Co.. 1263 Pacific Lumber Co., The; 1265- . Products Research Co., 1230 . , ' Reynolds Metals *Co., 1266-1267 ... Ruberoid Co.. The, 1268-1269 - ./ United States Gypsum Co.; 1270/ 1271 - . ,, *' , powers Regulator Co.-, il42 United States Register Co.. 1095 -Wood Conversion Co., 1272 ' _ ;`,->*Taylo'r Instrument Cos., 1144 ' INSULATION, Pelt . , , INSULATION, Steel - ; ' //71NSULATION, Building. . ' Baldwin-Hiil Co.. 1249 . . : . ;:;;^;AIfol-Insulatio'n Co., Inc., 1246V. . Johns-Manville. 1258-1259, . //^ American Flange & Mfg. Co.. Inc., Kimberly-Clark Corp.;' 1260-1261 ?>-/. 1247' \ " . Lockport Cotton-Batting .Co., 1263 '/ April Showers. Co., 1022* - " . Products Research Co., 1230 . ' V-i- Armstrong Cork' Co., 1248 . Ruberoid Co.. The, 1268-1269 ^t;Baidwin-HiU Co.. 1249 ' . Wood Conversion Co., 1272 American Flange & Mfg. Co., Inc.,' ' -.1247 .. v : Pittsburgh Coming1 Corp.; i244-.- 1245 . . , ' ., ; INSULATION, Structural 'i American Flange & Mfg. Co.,'lnc., S^VPhilip Carey Mfg. Co., -The, 1252- 1247 ' . '. ;>r; .1253 / . ` ' -- %Y`r Celotex Corp., The, 1250 . ' ' INSULATION, Magnesia' ' Armstrong Cork Co.. 1248 _ . ` . ^ ;' Eagle-Picher Co..-The, 1254 /v_/lnsulitc.l250-1257 - Insul-Wool Insulation Corp., 1255- f . Johns^.Manville, 1258-1259 .. . - .. 'r0i Kimberly-Clark Corp.. 1260-1261- Lockport Cotton Batting Co.-, 1263. ^V-Mundet^Corkfeorp.,-1264- . - V . Philip Carey Mfg.' Co., -The, 1252 1253 Johns-ManviUe, 1258-1259 - Mundet Cork' Corp,, 1264 -' Ruberoid'CoVThe, 1268-1269 United States Gypsum Co.. 1270 1271 ` - V ,Owens-Corning Fiberglas. .Corp.,- .:,1014-1015 ' '. .. - INSULATION,-Metal . Celotex Coip. The, -1250- - ' ' . Insulite, 1256-1257 .' . . /. Owens-Coming Fiberglas 'Corp.. 1014-1015 . ' Pacific Lumber Co.. The,-:1265 . ' Pittsburgh . Coming Corp., -1244 1245 . ' , ; /- United States Gypsum. Co.,1270- 1271' : . .^ - Wood Conversion Co., 1272 ; ' . ^./Pacific Lumber Co.,-The,-1265 . Alfol Insulation Co.; Inc.; 1246 - .//United States Gypsum Co., 1270 1271 - * ; Wood Conversion Co/. 1272 ^ . American-Flange & Mfg. Co., Inc., 1247 Reynolds Metals-Co., 1266-1267 INSULATION, Underground . Steam Pipe-- ... V/ / American District Steam Co.,1226, ' ( INSULATION, Cellular Glass ^/^ `'Armstrong Cork Co., 1248 V ^ " ^Owens-Illinois'-Glass - Co.,' Insulux Products Div.. 1243 , . ' Pittsburgh Corning- Corp./ 1244- -.1245/ . - '- INSULATION, Cork. - ' INSULATION, Mineral Wool (See Insulation, Building) - INSULATION, Pipes and Sut, faces (See Coverings', Pipes and . -.Surfaces) . ` . 1236- * /-V. -Baldwin-Hill Co'.. 1249 Owens-Corning .Fiberglas. Corp.,-' . 1014^1015 . Pittsburgh Corning Corp., 1244-' . 1245 . . H. W. Porter & Co.. Inc., 1237 ; / .Ric-wiL'Co/'The. 1238 /vV/*Armstrong Cork Co., 1248. - /Cork Insulation Co.V.Inc., 1251 _?"Korfund Co.; Inc.^TheT 1262 ' /VMundet Cork Cofp.,1264 ' ! INSULATION, Plastic ; Baldwin-Hill Co/ 1249 . f. Dow Chemical Co'., The, 1114 Eagle-Picher Co., The. 1254 INSULATION, Window, Double . Glazing. . ' . // Libby/Owens-Ford Glass Co., 1242' ^^H;,W. Porter & Co., 1237 . fe^jNSUlATION, Cotton Lockpori Cotton Batting Co., 1263 : Reynolds Metals Co.. 1266-1267 INSULATION,* Reflective ' . Alfol Insulation Co., Inc., 1246 ' ' American Flange &-Mfg. Co..' Inc., 1247 . ./ INSULATOR, Water April Showers Co... 1022; LIME SCALE CONTROL . / * j JNSULATION, Double Glass Lockport Cotton Batting Co., 1263 Reynolds. Metals' Co.; 1266-1267 Research Products Corp.,-1020 - ' Vinco Co.. Inc., The. 1192-1193 ; 'American'3 Way-Luxfer Prism Co.-, ` ,.1239- . .- - ,/ . INSULATION, Refractory - ' LIQUID LEVEL CONTROLS ' T. Libby-Owens-Ford Glass Co., 1242 Armstrong Cork Cp;, 1248 - . . . .,Owens-Illinois Glass Co.. Insulux Babcock & Wilcox.Co., The, 1150 VV'Products Div., 1243 . ' ^Pittsburgh Corning Corp;, 1244-^ Johns-Manville, 1258rl259 1 .. v /1245/, 4; - v. ; American Meter Co.. Inc:, 1119 ' Barber-Colman.Co,, 1084, 1121' General Electric Co.'(Schenectady, N. Y.), 1076-1077 . . -./., : INSULATION, Ducts, Ventllat- ^'lng/Air Conditioning V . INSULATION, Sound Deaden- Ing (See also'Fdt, Sound ; Deadening); ;'v `. ` - ` , . . - ' Illinois Engineering Co.. 1216*1217 Johnson Service^Co.. 1130-1131 ', ' Leeds & Northrup Co.', '1133 ` ' ' McDonnell.& MiUer; 1194-1195.. -. ^V'Alfol Insulation Co., i246. - > ' ' Armstrong Cork Co.. 1248 . ' Mercoid Corp.yl 134-1135 ; i:;: Armstrong Cork CoV1248 ' '* . Baldwin-Hill Co., 1249 Minneapolis-Honeywell 'Regulator.. ^BaiSwiniHiU Co- 12491 / ' ` Celotex.Corp./The, 1250/ . . ' : Co./ 1130-1137 . 1 , :. -Numeralsfollowing -Manufacturers' Names refer to pages in-the Catalog Data Section ' ' - - - ' '' r --- 928 . 1946 Guide MaeDer Steam Specialty Co., Inc., ; 1227 . Penn Electric Switch Co., 1141 Power* Regulator Co., The, 1142 Sarcb,Co,, Inc., 1218-1219 . Taylor Instrument Cos., 1144 LIQUID LEVEL GAGES (See - Gages, Liquid Lend--) METERS, Flow American District Steam Co.,'1226, 1236 - American Meter Co., Inc.; 1119 Leeds & Northrup Co., 1133 Meriam Instrument Co., The, 1138 Minneapolis-Honeywell Regulator Co.. 1136-1137 Taylor Instrument Cos., 1144 Gar Wood Industries, Inc., 974-975 General Electric Co. (Bloomfield, N. J.), 948-949 Iron Fireman Mfg. Co.. 1178-1179 Meyer Furnace Co.,- The, 969 L. J. Mueller Furnace Co.. 970-971 Petroleum Heat & Power Corp., 1186-1187 Preferred Utilities Mfg. Corp., 1166 Ray Oil Burner Co., 1189 ' LOUVERS,,{See also Grilles and METERS, Gas . Registers) ' American Meter Go., Inc., .1119 Webster Engineering Co., 1180 Williams Oil-O-Matic Div., Eureka Williams Corp., 1190 American Coolair Corp., 1050-1051 York Shipley, Inc., 1191 . American Foundry & Furnace Co.. METERS, Steam - Bahnson Co., The, 942-943 r Barber-Colman Co., 1084, 1121 y-BuffaloForge Co., 1056' ' - Chelsea Products, inc., 1058 Hendrick Mfg. Co., 1087. - '. Independent Register Co., The, _ 1090 , . - Schwitzer-Cummins Co.. 1072 Tuttle &Bailey. Inc., 1092-1093 American District Steam Co., 1226: 1236 OIL BURNERS, Pressure Atom Izing American Meter Co., Inc., 1119 Meriam Instrument Co., The. 1138 Minneapolis-Honeywell Regulator Co., 1136-1137 , Airtemp Div., Chrysler'Corp., 966- 967 . . Babcock &*Wilcox Co., The, 1150 Combustion Equipment Div.. Todd Shipyards Corp., 1182 . - MOTORS, Damper ; ' Gar Wood-industries, Inc., 974-975 Iron Fireman Mfg. Go., 1178-1179' Automatic Products. Co., 1120 ' S. T. Johnson Co., 1184-1185 Barber-Colman Co., 1084, 1121 L. J. Mueller Furnace Co., 970-971 MANOMETERS, U-Type, Well Minneapolis-Honeywell' Regulator Petroleum Heat- & Power Corp., Type . .` Co.. 1136-1137 . " 1186-1187 .-American Meter Co., Inc., Ili9 White-Rodgers Electric Co., 1146 Meriam Instrument Co., The, 1138 Young Regulator Co., 1096 . Moeller Instrument Co., 1139 MOTORS, Electric Ray^Oil Burner Co., 1189' Williams Oil-O-Matic Div., Eureka - Williams Corp., 1190 - York Shipley^Inc., 1191 ` "mechanical.draft appa* . RATUS (See also Blowers, Forced General Electric Co. (Schenectady, N. V0, 1076-1077 OIL BURNERS, Rotary; ' Draft) Wagner Electric Corp., 1075 Automatic Burner Corp.,-1181 ' Westinghouse Electric Corp., 1078 Combustion Equipment Div., Todd ' DeBothezat Fans Div., American ' 1079 ^ Shipyards,Corp., 1182 . Machine & Metals, Inc.. 1059 Enterprise Engine & Foundry Co;, -J. F. Pritchard & Co., 1025 B. F; Sturtevant Co., Div., West - ihghouse Electric, 954-959, 1018 - 1019 NOISE ELIMINATORS (See , Tubing, Flexible', Sound Deaden* . 1183- - S. T. Johnson Co., 1184-1185 ers; Vibration Absorbers) . Preferred Utilities Mfg. Corp., 1166 Ray Oil Burner Co.; 1189 L, T. Wing Mfg. Co., 1000-1002 Voting Radiator Co., 997- ' NOZZLES, Air-Washing, Brine Spraying.' Humidifying, Oil MECHANICAL DRAFT COOL . ING TOWERS (See also Cooling . Burner, Water Spray Nozzles) Cooling _ (See Towers,' Forced Draft, Induced .Draft) ' NOZZLES. Oil Burner - OIL BURNERS, Steam Atomiz ing . . Babcock & Wilcox Co.. The, 1150 Combustion Equipment Div., Todd v Shipyards Corp^ 1182 . Webster Engineering Co:, 1180 , - . Buffalo Forge Co., 1056 . Monarch Mfg. Works, Inc., 1029 . Lilie-Hoffman Cooling Towers, Inc.. Preferred Utilities Mfg. Corp.. 1166 OIL BURNERS, Vaporizing 1023 . -- ' "Marley Co., The; 1024 . Mario Coil Co., 1042 ' J. F. Pritxard & Co., 1025 '_ ODOR CONTROL ` H. C. Little Burner Co., 1188 . L. J. Mueller Furnace Co., 970-971 W. B. Connor Engineering Corp.; 1008-1009,1085 . ` - _ B. F. Sturtevant Co., Div., West- W. H. Wheeler, Inc., 1003 - inghouse Electric 954-959,1018 1019 . . .. OIL BURNERS, Variable Capa- ' city . . Water. Cooling -Equipment Co., OIL BURNER MOTORS (See Automatic Burner Corp., .1181 1027 .. . Motors, Electric) ' . . Babcock & Wilcox Co., The, 1150 Combustion Equipment Div., Todd . METERS, Air . OIL BURNER TUBING, Flexible Shipyards Corp., 1182 - American District Steam Co.. 1226. .' (See Tubing, Flexible, Metallic) 'Ray Oil Burner Co., 1189 - 1236 - ; . . American Meier Co., inc.,` 1119 OIL BURNERS. - OIL BURNING EQUIPMENT ' * Illinois Testing Laboratories, 1132; Airtemp Div., Chrysler Corp., 966 Automatic Burner Corp., 1181 . Meriam. Instrument Co., The, 1138 967 - . Automatic Products Co., 1120 -,, V -Minneapolis-Honeywell Regulator American -Radiator'& Standard Babcock'& Wilcox Co., The, 1150 . Co., 1136-1137 , . . Sanitary Corp., 1148-1149 Campbell'Heating Co.. 964-965 .. .--Taylor.Instrument Cos. 1144 Automatic Burner Corp., 1181 ' Combustion Equipment Div., Todd - Babcock & Wilcox Co., The, 1150 * Shipyards Corp., 1182 ' - METERS, Condensation '- . Combustion Equipment Div., ` Shipyards Corp., 1182 ' Todd ' Detroit Lubricator Co.,. Div.. of . American Radiator & Standard ' American District Steam Co., 1226. Enterprise Engine & Foundry Co., Sanitary Corp., 1122-1123 - . 1236 . .. -. : - - . ' 1183 - . ................ Iron Fireman Mfg. Co., 1178-1179 * " Please mention THE GUIDE 1946.wheifwriting to Advertisers .Index.^to Modern Equipment , ... . " ~ 929 Petroleum Heat & Power Corp., PIPE, Copper . PLASTER BASE, Sound Dead . 1186-1187 - Preferred Utilities Mfg. Corp., Ray Oil Burner Co.,-1189 . 1166- Webster Engineering Co., 1180 American Brass Co., 1104-1105 Crane Co., 1154-1155 Mueller Brass Co...1106-1107 . Williams Oil-O-Matic Div.. Eureka Revere Copper & Brass, Inc., 1108 Williams Corp., 1190 ening ' ' Armstrong Cork Co., 1248 Celotex Corp.; The, 1250 Insulite, 1256-1257 . Johns-Manville. 1258-1259 - . ' ' Ybrk-Shipley, Inc., 1191 PIPE, Copper Bearing Steel United States Gypsum Co., 1270 1271 . ` OIL TANK GAGES (See Gages, American Rolling Mill Co., The, 1097 , Wood Conversion Co., 1272 \ Tank) ' Bethlehem Steel Co., 1098 Crane Co., 1154-1155 . PLATES, Stainless Steel ORIFICES, Flow Meter Jones &Laughlin Steel Corp., 1099 American Rolling Mill Co;, The,1097 American Meter Co., inc., 1119 Leeds & Northrup Co., 1133 ' Meriam Instrument Co., .The, 1138 Taylor Instrument Cos., 1144 _ ORIFICES, Radiator - ' C. A. Dunham Co., 1206-1210 PIPE COVERING (See Covering, Carnegie-IUinois Steel Corp., 1100 Pipe) . PLATES, Steel PIPE FITTINGS (See Fittings, Pipe) American Rolling Mill'Co.',`The,' 1097 ` PIPE, Furnace (SeeFurnace, Pipe) Bethlehem Steel Co., 1098 , . Jones & Laughlin Steel Corp., 1099. Illinois Engineering Co.,1216-1217 Sarco Co., Inc., 1218-1219 H.'A. Thrush & Co., 1198-1199 PIPE HANGERS Pipe) (See Bangers, United States Steel Corp., Sub., 1100 _ \ PIPE, Lead PRECIPITATING EQUIPMENT PACKING, Asbestos Philip Carey Mfg. Co., The, 1252 1253 ' . Crane Co., 1154-1155 - Johns-Manville, 1258-1259 - -1 Eagle-Picher Co.. The. 1254 PIPE, Plastic . Dow Chemical Co,, The, 1114 . American Air Filter Co., Inc., 1006* 1007 . B. F. Sturtevant' Co., Div., West- inghouse'Electric, 954-959, 1018 1019 ,. PACKING, Felt - Products Research.Co., 1230 PANELS, Air Distributing Pyle-National Co., The, 1091 PIPE, Return Bends 'Baker Ice Machine Co., Inc.. 1038 Frick Co. (Inc.), 1041 Grinnell Co.. Inc., 981, 1112-1113, 1211 Arthur Harris & Co., 1115 Henry Valve Co., 1129 ' PERFORATED METALS Swan Engineering Co., 1181 Vilter Mfg. Co.. The, 1048 Hendrick Mfg. Co.. 1087 - ' Independent Register Co., The, PIPE, Steel ' . 1090 . ` American Rolling 'Mill Co., The, PILLOW BLOCKS 1097. Bethlehem Steel Co.. 1098 Air Controls, Inc., 1049 Crane Co., 1154-1155 Hastings Air Conditioning Co., Iiic., Grinnell Co.,'Inc., 981, 1112-1113, 947 ; - 1211 Jones & Laughlin Steel Corp.; 1099 PIPE ANCHORS Grinnell Co., Inc.T981, 1112-1113, - 1211 - Mueller Brass Co:. 1106-1107 H. W. Porter & Co.. 1237 / National Tube Co., 1100 . Revere Copper & Brass, Inc., 1108 PIPE - SUPPORTS, For Under ground Conduits H. W. Porter & Co., 1237 * PIPE BENDING Ric-wiL Co., The. 1238 . Crane Col, 1154-1155 . . . PITOT TUBES (See Air Measur Frick Co. (Inc.), 1041 . ing and Recording Instruments) Grinnell Col. Ind. 981, 1112-1113, ..1211 .... Arthur Harris & Co..' 1115 - PLASTER BASE, Fire Retarding Mueller Brass Gx, 1106-1107 ' Armstrong Cork Co., 1248 Parks-Cramer Co.,'951 . Celotex Corp., The; 1250- .Swan Engineering Co.. 1116 Johns-Manville, 1258-1259 - United States Gypsum Co'.. 1270 PIPE, Brass 1271 - PREHEATERS, Fuel Oil American District1Steam Co., 1226, 1236 .. Condenser Service & Engineering .Co., Inc.. 1034 - - ' National Radiator Co., The. -1164^ 1165 .. , Taco Heaters, Inc., 1200 . H. A. Thrush & Co., 1198-1199 - PRESSURE REDUCING VALVES (See Regulators, Pres sure) V PROPELLER FANS (See Fans, Propeller)' . . PROCESS HEATING UNITS. ' L. J. Wing Mfg. Co.. 1000-1002 PSYCHROMETERS (See also Air Measuring, Indicating and. Re cording Instruments) - American Moistening Co., 1021' * Fries Instrument Div., Bendix Aviation Corp., 1128 ' r ' Johnson Service Co., 1130-1131 Leeds & Northrup Co.. 1133 ;; Minneapolis-Honeywell Regulator Co., 1136-1137 .' Moeller instrument Co., 1139 . Palmer Co., The, 1140 i - Parks-Cramer Co.. 951 ' Taylor Instrument Cos., 1144 - * American Brass Co., 1104-1105 PLASTER BASE, ` Insulative Crane Co.. 1154-1155 -Revere Copper &. Brass, .; Iric.,-1108 ' Armstrong Cork Co., insulite. 1256-1257 1248 . ` ' Jolins-Manviiie, 1258-1259 ;;PIPE CONDUITS (See Conduits, United States Gypsum Co., 1270 J-i.. Undcrground Pipe)', ' 1271 - .. PUBLICATIONS . " .. American Artisan, 1277 ` . American Society'of Refrigerating Engineers, 1273 ;* ' Coal-Heat, 127.4 .- Domestic Engineering. 1275 ` . Numerals following Manufacturers* Names refer to pages in the Catalog Data Section r* : 930: 1946 Guide ' Fueloil &-Oil Heat, 1276 ' ' . Nash Engineering,Co- 1202-1203 - RADIATION, Cast-Iron ;, . , ' Heating & Ventilating. 1278 . Heating. Piping and Air Condi , - . tioning, 1277 - Plumbing and Heating Journal,' Trane Co- The, 998-999', . Worthington Pump & Machinery Corp- 1046-1047 . American Radiator & Standard Sanitary Corp., 1148-1149 < . Burnham Boiler Corp- 1152 ' ' .1279 Crane Co- 1154-1155 . SheeCMetal Worker, 1279 ; PUMPS, Fuel Oil 'Automatic Products Co- 1120 - PULLEYS; Chain (See also Chain)' National Radiator Co- The, 1164 1165 United States Radiator Corp., 1172- . 1173 Hart & Cooley Mfg. Co., I086i089 PUMPS, Sump - . Weil-McLain Co.. 1174 - United States Register Co., 1095 -..-Young Regulator Co., 1096 . Buffalo Pumps, Inc.. 1201 i'PUMP MOTORS, {See Motors, Chicago Pump Co- 1204 , Nash Engineering Co- 1202-1203. RADIATION, Copper Aerofin Corp- 1031-1033. ' ! . Electric) ` .. - ' Worthington' Pump & Machinery C. A. Dunham Co-12061210 - Corp- 1046-1047 * McQuay, Iric., 9864)87 ` . PUMPS, Ammonia ; Modine Mfg. Co- 986-989 -- .. - Chicago Pump Co.. 1204 .PUMPS, Turbine ./ ' Vxiter Mfg. Co.. The, 1048 , -Worthington Pump- & Machinery ` ^ Corp.. 1046-1047 . Chicago Pump Co./ 1204 ' Nash Engineering Co., 1202-1203 Vilter Mfg. Co- The. 1048 ' -John-J. Nesbitt, Iiic- 994 - - Rome-Turney Radiator Co- The, 1036 ./ - ' B. F. Sturtevant Co- Div., Westinghouse Electric, 954-959, 1016 Worthington Pump & Machinery 1019 \ PUMPS, Boiler Feed Corp- 1046-1047 . . Trane Co- The. 996999 .'--Buffalo Pumps Inc.. 1201 Chicago Pump Co.. 1204 PUMPS,.Vacuum Vulcan Radiator Co-.The, 1037. Young Radiator Co., 997 ' ..' Condenser Service. & Engineering Co., Inc., 1034 ' . Chicago Pump Co- 1204 `RADIATION, Plain and Ex- . ] -Nash Engineering'Co., 1202-1203 Condenser Service & Engineering tended Surface '; ' .Worthington- Pump 6c 'Machinery Corp., 1046-1047 1 ' . Co- Inc- 1034 C. A. Dunham Co- 12061210 .. Hoffman' Specialty Co- Inc., 1213 Aerofin Corp.. l03l-i033 . Burnham Boiler Corp- 1152 . - 1215 .. . , C. A. Dunham Co., 12061210 PUMPS,\;Brfnie - ' Nash Engineering Co.. 1202-1203 G & O Mfg. Co-.The,; 1035 - Buffalo'Pumps, inc-1201 '< Worthington Pump & Machinery 'Mario Coil Co- 1042 . - Chicago Pump Co., 1204 . ^ . Corp- 1046-1047. ,. McQuay, Inc-986987 - ; Nash Engineering Co- 1202-1203 *' Worthington Pump r.-?:- Corp., 10461047 &. Machinery' PURGERS, Refrigeration- Modine Mfg. Co- 986989. ' ' ' :'a National Radiator Co- The, 1164- ' , 1165v ... . Armstrong Machine Works, 1224^ John J. Nesbitt, Inc./ 994 ' ~ ^ ' - PUMPS, Centrifugal . 1225- . Refrigeration Economics Co- 995 Frick Co: (Inc.). 1041 Rome-Turney Radiator Co- The, ;.** -;rBell and Gossett Co-'il96fU97 Vilter Mfg. Co- The. i048 ' 1036 . , ' '4 - Buffalo Pumps. Inc- 1201 - . B. F. Sturtevant Co- Div- West- 7 'I 'Chicago-Pump Cd., 1204 ' - inghouse Electric. 954-959, 1016 v;' .. Condenser Service & Engineering PYROMETERS, Portable and 1019 - . '. \Co,, Inc.,'1034 Stationary .. ". Trane Co.. The, 996999 - 1 . ` - j,4" i. , -t \ .;rn- Crane Co- 1154-1155 '' C. A. Dunham Co.-, 1206-1210 Worthington`Pump-& Machinery / ; Corp- 10461047 .. C PUMPS, Circulating (See also Circulators) -t . -- - - General Electric Co. (Schenectady, N..Y.), 1076-1077 . - United States Radiator.Corp., 1172 1173 .. Illinois Testing Laboratories, Inc., Vulcan Radiator Co- The. 1037 ' * 1132 . WeU-McLain Co-1174 Leeds & Northrup Co- 1133 .Young Radiator CoA 997 . . Minneapolis-Honeywell Regulator . Co- 1136-1137 . RADIATOR ENCLOSURES AND r-* and Gossett Co- 1196-1197. ' SHIELDS : ... ^.Buffalo Pumps, Inc- 1201 ; RADIATION, Aluminum ' Alfol Insulation Co., Inc- 1246 - ~ ; -/.Chicago PumpCo.', 1204 _ - ! . ^.Condenser Service & -Engineering -v : Co-Inc:, 1034 ' J , ^ - Craher.Co,;.1154-1155 Aerofin Corp., 1031-1033 Mario Coil Co- 1042 McQuay,. Inc- 986-987 . - *Nash Engineering Co- 1202-1203 John J. Nesbitt, Inc- 994 :. \ . American ' Radiator ' & ' Standard Sanitary Corp- 11461149 Crane Co-1154-1155 . , .Rome-Turney Radiator Co- The,. .1036 .. . . Taco-Heaters, Inc- 1200 - Refrigeration Economics Co-.995 H. J. Somers, Inc.; i01610l7. V c H. A. ThrushCo- 1198-1199 - ^Trane Co-The. 998-999 ' ,7 Worthingtoh -Puajp .& Machinery ; Corp- 1046-1047 .. B.' F. Sturtevant Co/, Div- West* ; inghouse Electric, 954-959, 1016 Vulcan Radiator Co-The, 1037;, 1019 . Trane Co- The, 998-999, , ... RADIATOR HEAT . REFLECTORS `- ' . : , '~.i . .'PUMPS, Condensation Buffalo Pumps, Inc., 1201 .--' /Chicag_o Pum.p Co-. `1204 , RADIATION,- Baseboard; rous ' ' ' .. ' Burnham Boiler Corp., 1152 r*\Condenser/'Service .& Engineering. .Crane Col', 1154-1155 Fer- ' Alfol Insulation Co- Inc- 1246 ' American Flange & Mfg. Co-Inc . 1247 ' `. ' - " Reynolds Metals Co.. 12661267 -. '. ; ' ' -1 ;; ' RADIATORS, Cabinet - . C/A^DunhainOo.,12fWi-121o'. RADIATION,.Ba^board. Non-. Bunlh^ BiiIer-Corp.. Ils2- ! . / Hoffman Specialty Co'./Inc.;-`1216 ' . e*TOUS \ . \ - . Crane Co-,1154-1155 1215 ".s^' : ' Warren VVebster & Co., 12261223 C. A. Dunham Co.. 12061210 i- ' V:' -. ^ . - -. Please mention THE GUIDE 1946'.when writing'to Advertisers " ' .' 4 Index to -Modern Equipment 931 ! Modine Mfg. Col. 986989".. , 'REFRIGERATING EQUIP-- . REGULATORS, Damper .John J.- Nesbitt;.Inc./ 994 ... , MENT,-Steam'Jet- . " Barber-Colman Co.. 1084. 1121 * United States Radiator Corp- 1172 Worthington/ Pump & Machinery Crane Co., 1154-1155 1173 Weil-McLain Co- il74 Young Radiator Co- 997 - Corp-10461047 , . .REFRIGERATING - . Fulton Sylphon C6-.T124-1125 General Controls, 11261127 ` Johnson Service Co.. 11361131 . MACHINERY Minneapolis-Honeywell. Regulator RADIATORS. Concealed American Radiator & Standard Sanitary Corp- 11461149 -'Burnham'Boiler Corp- 1152 - Crane Co- 1154-1155' C. A. Dunham Co-12061210 - Modine Mfg. Co- 986989 - John J. Nesbitt, Inc.-, 994" .. United States Radiator Corp- 1172 1173 . .> Airtemp Div- Chrysler Corp- 966 967 " * Baker Ice Machine Co- Inc., 1038 Carrier Corp., 944-945 Curtis Refrigerating Machine Div. of Curtis Mfg. Co- 1040 - > Frick Co. (Inc.). 1041 - General ' Electric Co. (Bloomfield. N. J.). 946949 McQuay, Inc., 986987 Co- 11361137 . Powers Regulator Co- The, 1142 H. A. Thrush & Co- 11961199 Trane Co- The. 996999 Tuttle & Bailey, Inc.,. 1092-1093 ' Webster Engineering Co- The, 1180 White-Rodgers Electric Co- 1146 Young Regulator Co- 1096 ' REGULATORS, Furnace - 'Vulcan Radiator Co- The. 1037 -Warren Webster & Co- 12261223 Mills Industries, Inc- 1043' B. F. Sturtevant Co- Div,, ' West- -Automatic Products Co- 1120 Weil-McLain Co- 1174 Young Radiator Co- 997- inghouse Electric. 954-959,1016 Barber-Colman Co-1084-1121 1019 . Hart & Cooley Mfg. Co:, 10861089 Trane Co., The, 996999 ' . Minneapolis-Honeywell Regulator Universal Cooler, Div- . Intema- Co- 11361137 RECEIVERS. Air -tional Detrola Corp- 1045 Penn Electric Switch Co- 1141 American Moistening Co- 1021 Crane Co- 1154-1155 _ Farrar & Trefts, Inc- 1158 Kewanee Boiler Corp- 11661163 Parks-Cramer Co., 951 * Vilter Mfg. Co- The. 1048 .. ' White-Rodgers Electric Co- 1146 Williams Oii-O-Matic Div., Eureka Williams Corp- 1190 - REGULATORS, Gas . . . Worthington Pump & Corp- 10461047 -. Machinery American Meter Co.. Inc., 1119 Crane Co- 1154-1155 . * v REFRIGERATION CONTROLS -`RECEIVERS, Condensation ' (See also Controls) ' / Crane Co- 1154-1155 ; Illinois Engineering Co- 12161217 Sarco Co- Inc- 1216X219 . ' Alco Valve Co., Inc- 1118 s -Automatic Products Co- 1120 * % Detroit- Lubricator Co.-, Div. of American Radiator & Standard General Controls, 11261127 , - . Minneapolis-Honeywell Regulator Co- 11361137 .. REGULATORS, Humidity (SeeHumidityControl) ' Sanitary Corp-.1122-1123 . . .- RECEIVERS; Refrigerants ' /Acme Industries, Inc- 1030 . . Baker Ioe Machine Co- Inc- 1038 F.- Stiirtevant Co- Div- West- -'inghouse Electric,;954-959. 1016 General Electric Col (Schenectady, N. Y.). 10761077 REGULATORS, Pressure ' Insul-Wool Insulation Corp- 1255 American Meter Co- Inc- 1119 ' MercoidCorp.. 1134, 1135 . Barber-Colman Co- 1084. 1121 Minneapolis-Honeywell Regulator Crane Co- 1154-1155 - Co- 11361J37. . . . C. A,.Dunham-Co- 12061210 . 1019 ' . , ' Penn Electric Switch Col/ 1141 -Fulton Sylphon Co--1124-1125. . .'Vilter Mfg. Co-The. 1048 Sarco Co- Inc- 12161219 1 . Illinois Engineering Co- 12161217 ''Worthington Pump & Machinery Tenney Engineering,.'Inc.-, 1145 McDonnell & Miller, 1194-1195 . ' Corp- 10461047 White-Rodgers Electric Co- .1146 Mueller Steam Specialty Co., Inc., / -York Corp-960 1227 ' REGISTERS '(See also Grilles and . RECORDERS, Humidity, Tem-. Louvers) t . - . ^ 1 perature '' Air Devices, Inc.. 10861081 '' -American Moistening Co.. l021 Friez Instruments--Div- Bendix' Aviation Corp- 1128 . ' Anemosiat Corp.' of America, 1082 Barber-Colman Co- 1084-1121 Hart & Cooley Mfg. vCo., 10861089 Payne Furnace Co., 972-973 . Penn Electric Switch Co.. 1141- _ Powers Regulator Co., The, 1142 Spence Engineering Co- Inc- 1143 Taylor Instrument Cos., 1144. . ' Tenney Engineering, Inc- 1145 !'Leeds & Northrup Co.. 1133.- ' - ' ' Minneapolis-Honeywell - Regulator '.. Co-11361137 . .. Hastings Air Conditioning Co- Inc- 947 - - REGULATORS,-Temperature Hendrick Mfg. Co- 1087 . . . (See Temperature.Control) ' / Palmer Co- The,' 1140 . : Powers Regulator Co..' The. 1142 Independent 1090 Register Co. The,. . , RELIEF.' VALVES (See' Valves .Taylor Instrument Cos./1144 L. J. Mueller Furnace Co- 976971 : Relief) ' . ' '< .Pyle-National,Co., The, 1091' ' j REFRACTORIES, Cement, Register & Grille Mfg. Co., Inc/, 1094 : ; . . ROOF COOLER . .. / /'Materiala, .. / ,' - * '.. .Tuttle & Baiiey,Inc,, 1092-1093. ' -'April.Showers Co- 1022 - * Armstrong^Cork Co.. 1248' - ' ' Babcockr& Wilcox Co- The, 1150 United States Register Co- 1095 . Young Regulator Co., 1096 - Mariey CO- The, 1024 ' - ' Research Products Corp- 1020 ' {-Johris-Manville, 12561259. " - REGULATORS,'Air Volume-. , RUST INHIBITOR. :. / REFRIGERATING' EQUJ?- Anemostat Corp! of America. 1082 . Vincb Co- Inc., The; 1192-1193 Barber-Colman Co., 1084, 1121- . /irMENT, Centrifugal '.Carrier Corp.,^944-945 McQuay, lnc.1986987 . . ' - Johnson Service'Co- 11361131 . Minneapolis-Honeywell Regulator L Co-11361137 . - . - . RUST AND SCALE REMOVER Vinco Co- Inc., The. 1192, 1193 . .^Trahe Co.. The. 996999 - Powers .Regulator Co.'; The, 1142 ' s'Worthington Pump & Machinery Tuttle & Bailey, Inc- 1092-1093 ' .SAFETY.VALVES (See'Vaiwi. r^.Corp., 10461047 i '. Young Regulator Co-.1096 . . ` ' Safety). . . ^ Numerals'following Manufacturers'. Names refer, to pages iii- the Catalog Data Section . SCREENS, Sun Reflecting . SHEETS, Pure Iron' Martocello. Jos. A. & Co., 1028 . IngersoU Steel.'Div. (Borg-Warner . Corp.). 1240-1241 - SEPARATORS, Air Air-Maze Corp., The, 1004-1005 American Rolling Mill Co., The, 1097 . Carnegie-Illinois Steel Corp., 1100 United States Steel Corp.. Sub., 1100 J. F. Pritchard & Co.. 1025 ' B. F. Sturtevant Co.. Div., West- inghouse Electric, 954-959. 1018 1019 -. Yaraall-Waring Co., 1232 Dollinger Corp. (formerly Staynew Filter Corp.). 1010-1011 SHEETS, Special Finish SPRAY NOZZLE COOLING Penn Electric Switch Co., 1141 - Wright-Austin Co., 1231 American Rolling Mill Co.. The. SYSTEM 1097 April Showers Co., 1022 Bethlehem Steel Co., 1098 Lilie-Hoffman Cooling Towers, Inc., - SEPARATORS, Dust Jones & Laughlin Steel Corp., 1099 1023 Dollinger, Corp. (formerly Staynew Marley Co-. The, 1024 ; Filter Corp.), 1010-1011 SHEETS, Stainless Steel . Martocello, Jos. A. & Co., 1028 B. ,F. Sturtevant Co., Div.. West- 'inghouse Electric, 954-959. 1018 7.1019 . . .' American Rolling Mill Co:, The. 1097 . Carnegie-Illinois Steel Corp., 1100 Monarch Mfg. Works, Inc., 1029 J. F. Pritchard & Co.. 1025 B. F. Sturtevant Co., Div., West- inghouse Electric, 954-959. 1018 SEPARATORS, Oil Air-Maze Corp., The, 1004?1005 Acme Industries, Inc., 1030 Baker Ice Machine Co., Inc., 1038 SHEETS, Steel . American Rolling Mill Co., The, .1097 : Bethlehem Steel Co., 1098 1019 . . Tenney Engineering, Inc.; 1145 Trane Co.. The, 998-999 United States Air Conditioning Corp., 953 Crane. Co., 1154-1155 Dollinger Corp. (formerly Staynew Filter Corp.). 1010-1011 . Illinois Engineering Co., 1210-1217 Carnegie-Illinois Steel Corp., 1100 Jones & Laughlin Steel Corp., 1099 United - States Steel Corp., Sub., 1100 Water Cooling Equipment Co-, 1027 -. Yaraall-Waring Co.. 1232 . Vilter Mfg. Co., The. 1048 Warren 1223 Webster & - Co., 1220 SHUTTERS, Automatic SPRAY NOZZLES - - American Moistening Co., 1021 - Worthington-Pump & Machinery Air Controls, Inc., 1049' - April Showers Co./1022 - - Corp,, 1046-1047 ' American Coolair Corp., 1050-1051 Bahnson Co., The,. 942-943 -Wright-Austin Co,,-1231 ` Barber-Colman Co., 1084. 1121 Buffalo Forge Co., 1056 .. Chelsea Products. Inc., 1058 Marley Co., The. 1024 ' SEPARATORS, Steam - Crane Co-, 1154-1155 . ' Farrar & Trefts, Inc., 1158 Illinois Engineering Co., 1216-1217 Warren Webster & Co., 1220-1223. Worthington Pump & Machinery Corp.. 1046-1047 Wright-Austin Co., '123T SHEET,'Felt Gasket '' Hartzell Propeller Fan Co. (Div. of Castle Hills Corp.), 1064 . . Ilg -Electric' Ventilating Co- 982/ 1060-1061 . MinneapoUs-Honeywell Regulator Co.. 1136-1137 Herman Nelson Corp., The, 992-993 New York Blower Co., The. 1067 Schwitzer-Cummins, 1072 B. F. Sturtevant Co., Div., -West- inghouse Electric, 954-959, 1018 Mario Coil Co., 1042 Martocello, Jos. A. & Co.. 1028 Monarch-Mfg. Works, Inc.. 1029 Mueller Brass Co., 1106-1107 D. J. Murray Mfg. Co., 990 Parks-Cramer Co., 951 J. F. Pritchard & Co., 1025 B. F. Sturtevant Co., Div., West . jnghouse Electric, 954-959, 1018 1019 ^ Water Cooling Equipment Co., Products Research Co.. 1230- 1019 - 1027 ,, L. J. Wing Mfg. Co., 1000-1002 Yaraall-Waring Co.. 1232 SHEETS* Aluminized Steel ; American Rolling Mill Co., The, SKYLIGHTS* Insulated STACKS. Steel 1097. -. Reynolds Metals Co., 1266-1267 American 3 Way-Luxfer Prism Co., Bethlehem Steel Co.. 1098 1239 * Bigelow Co., The, 1151 . SHEETS, Asbestos, Flat _ Corrugated .. and _ SMOKE DENSITY RECORDING . - ' Brownell Co., The, 1175 Farrar & Trefts, Inc., 1158 - . ' Philip Carey Mfg. Co.. The; 1252- 1253 .` . Johns-Manville, 1258-1259 Rutxjroid Co., The. 1268-1269 . SHEETS, Copper-Alloy ' American Brass Co., 1104-1105'Z Revere Copper & Brass, Inc., 1108 Leeds & Northrup Co., 1133 SOOT DESTROYER ' . Vinco Co.', Inc.. The. 1192-1193 . STEAM GENERATORS (See Boilers, Forced Recirculation) STEAM HEATING SYSTEMS -. (See Healing Systems. Steam). . SOUND DEADENING, Insula tion - STOKER MOTORS (See Motors, Armstrong Cork Co., 1248 Electric) . :- SHEETS. Copper Bearing Steel - American Rolling Mill Co.,. The, 1097 . - Bethlehem Steel Co./1098 - -- Carnegie-Illinois Steel Corp., 1100 United States Steel Corp., Sub., . 1100 . - .. - Baldwih-Hill Co., 1249 - - Celotez Corp.; The, 1250 \ Eagle-Picher Co., The, 1254 Insul-Wool Insulation Corp., 1255 Johns-Manville, 1258-1259 - ' Korfund Co., Inc., The. 1262' Lockport Cotton Batting Co., 1263 Mundet-Cork Corp.-, 1264 SHEETS* .Galvanized ^ Owens-Coming Fiberglas Corp., 1014-1015 American Rolling. Mill Co., The, Pacific Lumber Co., The, 1265 ' *1097 . . Products Research Co., 1230 STOKERS, Mechanical*' . Anthracite; ' Airtemp Div., Chrysler Corp., 966 967 - Babcock & Wilcox Co., The, 1150 Brownell Co., The. 1175 . Combustion Engineering Co., 1176 Crane Co., 1154-1155 - * . Iron Fireman Mfg. Co., 1178-1179 Meyer Furna-ce C.o., The. 969 a Bethlehem Steel Co., 1098 . ' -Carnegie-Illinois Steel Corp., 1100 United States Steel Corp., Sub., -1100 _ Reynolds Metals. Co.. 1266-1267 United States Gypsum Co., 1270 1271 . . Wood Conversion Co., 1272 - . STOKERS* Mechanical, Bituminous s . Airtemp Div., Chrysler'Corp.. 966 967 SHEETS, High Tensile -^American Rolling Mill' Co., The, /- 1097 ' - ' ... -Bethlehem Steel Co., 1098 ' 'Carnegie-Illinois Steel Co., 1100 Jones & Laughlin Steel Corp., 1099 SPRAY DRYERXBee'SprayEquip-' . rtieni) '. .. . SPRAY EQUIPMENT . April Showers Co., 1022 Marley Co., The/1024 ' ~ . Babcock & .Wilcox Co.. The. 1150 Brownell Co.. The, 1175 -Combustion Engineering Co.. 1176 Crane Co., 1154-1155 Detroit Stoker Co., 1177 Iron Fireman Mfg. Co:, 1178-1179 .Meyer Furnace Co., The. 969 . , -. .Please,mention .THE GUIDE 1946 when writing to Advertisers f Index^to Modern'Equiprnent 933 STRAINERS, Dirt . TANK COILS (SeeCoils, Tank) THERMOMETERS* Recording Armstrong Machine Works, 1224 . 1225 . C.'A. Dunham Co., 1206-1210 Grinnell Co., Inc.. 981, 1112-1113, '1211 . . "Hoffman Specialty Co., Inc., 1213 1215 Illinois Engineering Co., 1216-1217 " Mueller Steam Specialty Co., Inc., - 1227 Sarco Co., 1218-1219 Trane Co.. The. 998-999 Warren Webster & Co., 1220-1223 STRAINERS, Oil , . Automatic Products Co., 1120. Bell and Gossett Co., 1196-1197 ' Crane Co., 1154-1155 - , 'General Controls,.1126-1127' Monarch Mfg. Works, Inc., 1029 '. Mueller Steam Specialty Co..` Inc., - 1227 Sarco Co.. Inc.. 1218-1219 . = Spence Engineering Co., Inc., 1143 ' Wright-Austin`Co., 1231 STRAINERS, Refrigerant AIco Valve Co., 1118 . . Friez Instrument Div., Bendix TANK COVERING {See Covering. Aviation Corp., 1128 ' '' Pipes and Surfaces) : - Leeds & Northrup Co..-1133 Jas. P. Marsh Corp.. 1228-1229 TANK HEATERS Tank). (See Heaters,- MinneapoUs-Honeywell Regulator . Co., 1136-1137 . Moeller Instrument Co., 1139 . Palmer Co., The, 1140 - TANKS. Blow-off Powers Regulator Co.. 1142 Bigelow Co.. The, 1151 Taylor Instrument Cos., 1144 ' Brownell Co., The. 1175 Farrar & Trefts, Inc-, 1158 THERMOSTATS - Kewanee Boiler Corp., 1160-1163 Barber-Colman Co., 1084, 1121 . Crane Co.. 1154-1155 ' TANKS, Pressure Friez Instrument Div.,. Bendix - Bigelow Co., The, 1151 Aviation Corp., 1128 Brownell Co., The, 1175 Fulton Sylphon Co., 1124-1125 ` " Farrar & Trefts, Inc., 1158 Kewanee Boiler Corp.'. 1160-1163 General Controls, 1126-1127 . Iron Fireman Mfg. Co., 1178-1179 '.. Taco Heaters. Inc., 1200 Johnson Service Co.. 1130-1131 ' H. A. Thrush & Co.. 1198-1199 Mercoid Corp., 1134-1135 MinneapoUs-Honeywell Regulator - TANKS* Storage - Co.. 1136-1137 . Penn Electric Switch Co., 1141 : . Farrar & Trefts, Inc., 1158 Powers Regulator Co., The, 1142 Kewanee Boiler Corp., 1160-1163 Sarco Co.. Inc., 1218-1219. Pacific Steel Boiler Div., U. S. H. A. Thrush & Co., 1198-1199 Radiator Corp., 1171 . White-Rodgers Electric Co., 1146 Automatic Products Co., 1120 - General Controls. 1126-1127 ;-Henry Valve Co.. 1129 - Mueller Brass Co., 1106-1107 Sarco Co.,- Inc., 1218-1219 . B. F. Sturtevant Co.. Div.. West- inghouse Electric/954-959. 1018 . 1019 . - TEMPERATURE CONTROL American Radiator & Standard Sanitary Corp., 1148-1149- - Automatic Products Co., 1120 ' Barber-Colman Co., 1084, 1121 Crane Co.. 1154-1155 C. A.. Dunham Co., 1206-1210 "Frier Instrument Div., Bendix . TIN PLATE '. Bethlehem Steel .Co., 1098 Carnegie-Illinois Steel Corp., 1100 Jones & Laughlin SteePCorp., 1099 TOWERS, Cooling (See Cooling . Towers)' - ` \ STRAINERS, Steam Aviation Corp...1128* Fulton Sylphon Co., 1124-1125 TRANSFORMERS . Alco Valve Co., 1118 : Crane Co., 1154-1155 General Electric Co. (Schenectady, General Electric Co. (Schenectady/ N. Y ). 1076-1077 - N. Y.), 1076-1077 ; . ' General Controls, 1126-1127 . Grinnell Co.. Inc.. 981, 1112-1113, Illinois Engineering Co., 1216-1217 Iron Fireman Mfg. Co.`. 1178-1179 Mercoid Corp., 1134-1135 `, B. F. Sturtevant Co., Div., West- . 1211 . Johnson Service Co.. 1130-1131 - inghouse Electric. 954-959," 1018 Illinois Engineering Co.. 1216-1217. Leeds & Northrup Co.. 1133 1019 Sarco Co., Inc., 1218-1219 % Mercoid Corp., 1134-1135 H. A. Thrush & Co., 1198-1199 Spence Engineering Co., Inc.,'1143 MinneapoUs-Honeywell Regulator Wagner Electric Corp.. 1075 'Trane Co., The. 998-999 Co.. 1136-1137 ... ; Wright-Austin Co.. 1231 Penn Electric Switch Co., 1141 Powers Regulator Co., 1142 TRAPS, . Bucket ' .. . .. STRAINERS. Water -,Alco Valve Co., 1118 /American District-Steam Co., 1226. s 1236 . -Condenser Service & Engineering Co.. Inc., 1034 Crane Co., 1154-1155 General Controls 1126-1127 ' Sarco Co., Inc., 1218-1219 Spence Engineering Co., Inc., 1143 Taylor Instrument Cos., 1144 Tenney Engineering. Inc., 1145 Warren Webster & Co.. 1220-1223 White-Rodgers Electric 'Co., 1146 Yaraall-Waring Co.. 1232 Young Regulator Co., 1096 - Armstrong Machine Works. 1224 1225 Crane Co., 1154-1155 -. . C. A. Dunham Co.. 12Q6-1210 . Mueller Steam Specialty Co., Inc., ' 1227 ." Sarco Co.. Inc., 1218-1219 . ' Trane Co., The, 998-999 - . Warren Webster & Co., 1220-1223 > Grinnell Co.. Inc.;'981. 1112-1113, . 1211 . , - THERMOMETERS, Distance .. Wright-Austin Co., 1231. Illinois Engineering Co;, 1216-1217 Monarch Mfg. Works, Inc., 1029 Type . Illinois Testing Laboratories, Inc., TRAPS, Float :. Mueller Steam Specialty Co., Inc., - 1132 American District Steam Co., 1226; '. 1227 Jas. P. Marsh Corp-. 1228-1229 1236 ' . Sarco Co., 1218-1219 MinneapoUs-Honeywell Regulator, Armstrong Machine Works, 1224 Spence Engineering-Co.. Inc.; 1143 Co.. 1136-1137 . . 1225; : Trane Co., The. 998-999 Moeller Instrument Co.-. 1139 Barnes 8t Jones, Inc., 1205 ` Wright-Austin Co., 1231' Palmer Co., The, 1140 . - Crane Co.. 1154-1155 . . '.Yaraall-Waring Co., 1232 Powers Regulator Co.. 1142 C. A. Dunham Co.. 1206-1210 - Sarco Co.. Inc., 1218-1219 . Grinnell Co.. Inc., 981. 1112-1113,. 'SWITCHES; Float Alco Valve Co.. 1118 General Electric Co. (Schenectady, N.Y.), 1076-1077- . .'McDonnell & Miller. 1194-1195 -Mercoid Corp;,' 1134-1135 ' .Penn Electric Switch Co.. 1141 Taylor Instrument Cos.. 1144 ' 1211 ' - William S. Haines & Co.. 1212 THERMOMETERS* Indicating Illinois Engineering Co.. 1216-1217Mueller Steam Specialty Co., Inc.; American Meter Co., Inc., 1119- 1227 .. ' Illinois Testing Laboratories, Inc., Sarco Co.. Inc., 1218-1219 - '. .. 1132 ' . Trane Co.. The, 998*999 . Johnson Service Co., 1130-1131 Warren Webster & Co., 1220-1223 Leeds & Northrup Co., 1133 . Wright-Austin Co., 1231 - ^/SWITCHES, Flow Control - MinneapoUs-Honeywell Regulator ^McDonnell & Miller, 1194-1195 SWITCHES, Mercury /Mercoid.Corp., The, 1134-1135 . . Co'., 1136-1137* ' Moeller Instrument Co.. 1139 TRAPS* Float and Thermostatic. Palmer Co., The, 1140 - American District Steam-Co., 1226, . Powers Regulator Co., 1142 . , .. . :1236. . . .. - . - - - Taylor Instrument Co., 1144 Barnes &'Jones.-Inc., 1208 7' " Numerals following Manufacturers'-Names refer to pages in the Catalog Data Section '. -1 - * ` :- '" - '  934 - . --- _______ ' ' 1946 Guide C. A. Dunham Co., 1206-1210 TUBE CLEANERSa. . VALVES, Air- ! ,. Grinnell Co.. Inc-, 981,-1112-1113, - 1211 . -William S. Haines & Co.. 1212 ' -.Hoffman Specialty Co., Inc- 1213 - 1215- - - . Illinois Engineering Co., 1216-1217 Jas. P. Marsh Corp., 1228-1229 Powers Regulator Co.. 1142 Sarco Co., Inc., 1218-1219 Trane Co., The, 998-999 Warren Webster & Co., 1220-1223 Wright-Austin Co., 1231 Martoceilo, Jos. A. & Co., 1028 TUBES, Boiler .. . . Babcock. & Wilcox Tube Co., The, 1150 .3 TUBES, Copper . American Brass Co.. 1104-1105 Mueller Brass Co., 1106-1107 . Revere Copper. & Brass. Inc., 1108 American Radiator, & Standard Sanitary Corp.. 1148-1149 Anderson Products. Inc., 1233 Crane Co.. 1154-1155 . Dole Valve Co.. The. 1234 Hoffman Specialty Co.. Inc., 1213 1215 . Jenkins Bros., 1235. Sarco Co., Inc., 1218-1219 VALVES, Angle, Globe and - Wolverine Tube Div:. Calumet and Cross . . -TRAPS, Radiator .Barnes & Jones, Inc., 1205 . Hecla Consolidated Copper Co.. H09 . . Grinnell Co., Inc., 981. 1112-1113,' 1211 .. iC. A. Dunham Co.. 1206-1210 enkins Bros., 1235 - . .Grinnell Co., Inc- 981. 1112-1113, TUBES, Pitot (SeeAir Measuring fueller Brass Co., 1106-1107 - '1211 - - . .- and Recording Instruments) - Worthington Pump & Machinery William S. Haines & Co., 1212 Corp., 1046-1047 . Hoffman Specialty Co., .Inc., 1213 4 1215 . '- ' -. Illinois Engineering Co., 1216-1217 Jas: P. Marsh Corp., 1228-1229 TUBING, Aluminum' . Revere Copper & Brass, Inc., 1108 York Corp., 960 " VALVES, Automatic . Sarco. Co.. Inc., 1218-1219 TUBING, Copper . ' ' . Anderson Products. Inc., 1233 *; ' Trane Co., The.-998-999 American Brass Co:. 1104-1 i05 . Automatic Products Co..Tl20 - Warren Webster & Co., 1220-1223 TRAPS, Return . ' ' Barnes & Jones, Inc., 1205 Crane Co.. 1154-1155 C; A.-Dunham Co.. 1206J210 William S. Haines & Co.. 1212 . Illinois Engineering Co.. 1216-1217 Jas. P. Marsh Corp.. 1228-1229 `Mueller Steam Specialty Co., Inc., - 1227 . Sarco Co.. Inc., 1218-1219 . ' Trane Co.. The, 998-999 . .- Warren Webster & Co.. 1220-1223 *. Wright-Austin Co., 1231 ` . _ Mueller Brass Co.. 1106-1107 Revere Copper & Brass, Inc/ 1108 Wolvering Tube Div., Calumet-and Hecla Consolidated Copper Co., 1109 . TUBING, Fabricated , Arthur-Hams & Co., 1115 Wolverine Tube Div., Calumet and Hecla Consolidated Copper .Co., 1109 . ./ . TUBING, Finned . Wolverine Tube Div., Calumet and Barber-Colman Co., 1084, 1121 Crane Co.. 1154-1155 .General Controls,.1126-1127. . Johnson Service Co., 1130-1131 - McDonnell & Miller,' 1194-1195 Minneapolis-HoneyweU Regulator Co.;/1136-1137 */ - Webster.Engineering Co., 1180'- .. VALVES, Back Pressure Alco Valve Co.. 1118 ` - - Automatic Products Co.. 1120 - Illinois Engineering Co., 1216-1217 . Mueller Steam Specialty Co.-, Inc., . 1227 r* .- . - ` "TRAPS, Sdrie . . ... Hecla. Consolidated Copper Co., 1109 -. :. Spence Engineering Co.. Inc.. 1143 : Henry Valve-Co., 1129 > Illinois Engineering Co.. 1216-1217 Sarco Co.. Inc., 1218-1219 TUBING, Flexible Metallic . Atlantic Metal Hose Inc.; 1101 '/' Chicago Metal Hose Corp., 1102 . VALVES, Balanced . .' Illinois Engineering Co..' 1216-1217 TRAPS, Steam' . Seamier Co., Inc., 1103 - VALVES, Blow-off Armstrong'Machine Works, 1224 - :i225 . - TUBING, Plastic. . ' Crane Co.,.1154-1155 Dow Chemical Co., The; 1114 Jenkins Bros., 1235 v Yarnall-Warmg Co., 1232 . ' ;C,_A. Dunham Co., 1206-1210 VALVES, By-Pass . ..William'S. Haines & Co., 1212- .' .Illinois'Engineering Co., -1216-1217 Jas. P. Marsh Corp.; 1228-1229 Mueller Steam Specialty Co., Inc.. 1227 -Sarco Co., Inc.. 1218-1219 . .Trane Co., The, 998-999 Warren Webster & Co.. 1220-1223 ..Wright-Austin Co..' 1231 ' Yarnall-Waring Co.,1232 ' .-TRAPS,- Thermostatic . . ,. American-District Steam Co., 1226.' . ^1236 - ' , - / - Barnes-& Jones, Inc./1205 TUBING. Steel .. r; Babcock'& Wilcox Co:. The/.1150 Jones & Laughlin Steel Corp., 1099 Revere Copper & Brass, Inc.. 1108 Crane Co.. 1154?1I55 ' Jenkins Bros., 1235 .. , VALVES, Check <, ' . TURBINES . Feddera-Quigan Corp.. 980 ' " ' General Electric Co. (Schenectady, - N. Y.)> 1076-1077. , . . B. --F. Sturtevant'Co., Div., West- inghouse Electric, 954-959, 1018 1019 ` L. J. Wing Mfg. Co.; 1000-1002 ' Grinnell Co...Inc., 981, 1112-1113. 1211 - . . . ' . Henry Valve Co., 1129 '. Illinois Engineering Co., 1216-1217 Jenkins Bros.-, 1235 York Corp., 960 " . . Worthington Pump & Machinery Corp.. J046-1047 - . ' VALVES, Diaphragm' ' - '' Crane,Co., 1154-1155 : . ` -C.-A. Dunham Co.; 1206-1210 Grinnell Co.; Inc.. 981.* 1112-1113, T211- - ; UNDERGROUND PIPE * DUITS (See Conduits, ground Pipe) * CON? Under- Detroit Lubricator Co.,-Div. of ! - American Radiator'& Standard . .Sanitary Corp.'. 1122-1123, . -~ . General Controls, 1126-1127 *: William S. Haines-& Co.. 1212' -' Grinnell Co.. Inc., 98L 1112-1113, Illinois Engineering Co.. 1216-1217 UNIT- HEATERS (See; Heaters. 1211- .: Jas. P. Marsh .Corp/;. 1228-1229 Unity ; .. *sv- -r ... Henry Valve Co.. 1129 : ` Powers Regulator Co.. The, 1142 'Johrison-Service Co.;-1130-1131 Sarco Co.. IncT, 1218-1219 v ... Minneapolis-Honeywell Regulator .Trane.Co., The, 998:999 .Warren Webster & Co., 1220-1223 ' UNIT VENTILATORS < Venti lators, Unit), _. - Co.. 1136/1137 - ': : Mueller Brass Co.', 1106-1107,-' * Mueller Steam Specialty Cor, Inc.., :TOAPS, Vacuum 'Armstrong Machine Works, 1224- .;- 1225 . .' <. 'William S. Haines & Co:. 1212 - UNITS; Air Conditioning (See 'Air Conditioning Units) ~ - 1227 ; - , . Parks-Cramer Co.. 951 * . V .. . Powers Regulator Co'. The. 1142 ' Taylor Instrument Cos:, 1144 - VACUUM HEATING SYSTEMS White-Rodgers ' Electric Co., 1146 -Illinois Engineering Co.-. 1216-1217-' ' (See Heating Systems,- Vacuum) York Cbrp., 960 " . . .-J " Please mention THE GUIDE 1946 when writing to Advertisers ' index to Modern:Equipment 935 : VALVES; Expahston ; Jenkins Bros.. 1235 . ' . ^ Frick Co. (Inc.)v 1041 - ' V- Automatic Products Co:, . Crane Co/ 1154-1155 * 1120 '' ; ' .. Johnson Service Co., 1130-1131. Powers Regulator Co., The; 1142- Detroit. Lubricator. Co., Div. of.- ' American' Radiator & Standard' VALVES, Non-Return . - - Sanitary Corp., 1122-1123 . General Controls, 1126-1127 : Henry Valve Co., 1129 . - Illinois Engineering Co.. 1216-1217 - Jenkins. Bros., 1235 _ ' Tenney Engineering. Inc., 1145 York Corp.. 960 ' VALVES, Pa<ddess - - - General Controls. 1126-1127 . Henry Valve Co., 1129 -' Mueller Brass Co:, 1106-1107 Tenney Engineering, Ihc.;1145 . . VUter Mfg- Co., The. 1048 . . ' Worthington Pump - & Machinery Corp.. 1046-1047 . . York Corp., 960 ' - ..VALVES, Float * v Alco Valve Co., 1118 - ... Anderson'Products, Inc., 1233 ' - --Detroit Lubricator Co., Div. of-. . - '"' American' Radiator &. Standard . - Sanitary Corp., 1122-1123 .?' Frick Co. (Inc.), 1041 - -. Illinois Engineering Co.,' 1216-1217 C. A. Dunham Co., 1206-1210 Fulton Sylphon Co., 1124-1125 . Henry Valve Co.. 1129 ,Illinois Engineering Co.. 1216-1217 Jas. P. Marsh Corp/ 1228-1229 Sara) Co.. Inc.; 1218-1219 VALVES, Pressure Reducing (See Regulators, Pressure) VALVES, Relief - . .. BeU & Gossett Co.. 1196-1197 * Crane Co., 1154-1155 - Henry Valve Co.. 1129 ' ' ' . Jas. P. Marsh Corp., 1228-1229 ' - McDonnell & Miller; 1194-1195 * . Taco Heaters, Inc., 1200 . * ` . . H. A. Thrush & Co., 1198-1199 . -York Corp.. 960 ' . '. ^ .* McDonnell & Miller, 1194-1195 . --'Mueller Steam Specialty Co., Inc., VALVES, Pump . VALVES, Safety m ...`-1227 . ' . - - ' Crane Co., 1154-1155 Viking -Air Conditioning ' Corp.. Jenkins Bros., 1235 1074' . . . Trane Co.. The, 998-999 ' VUter Mfg. Co.. The. 1048 . Henry Valve Co.. 1129 .' . . McDonnell & Miller, 1194-1195 D. J. Murray Mfg. Co.. 990 . - . York Corp.. 960 VALVES, Purge VALVES. Solenoid . s.--.-'lVALVES, Flow Control . r v'Automatic Products Co:, 1120 Henry Valve Co., 1129 Mueller Brass Co., 1106-1107 " Alco Valve Co.. 1118 Automatic Products Co., 1120 Barber-Colman Co.. 1084, 1121 ^ r.' Barber-Colman Co.; 1084, 1121 VALVES, Radiator Bell & Gossett Co., 1196-1197 Crane Co., 1154-1155 . Detroit Lubricator Co., Div. of -Amterican -Radiator & Standard i-t. . .'SanitaryXorp., 1122-1123 ^ ' .General Controls; 1126-1127 -Illinois Engineering Co.. 1216/1217 Johnson Service Co;, 1130-1131 . McDonnell & Miller, 1194-li95 Minneapolis-Honeywell. .Regulator ^'.CcCmerii?? . '-Mueller Steam Specialty .Co., Inc/,' : 1227 : '. / /Taco Heaters, Inc., 1200 . . ; ;H. A. Thrush & Co.. 1198-1199 American Radiator & Standard Sanitary Corp., 1148-1149 Barnes &'Jones, Inc., 1205 .. Crane Co., 1154-1155 C. A. Dunham Co.; 1206-1210 Fulton Sylphon Co.. 1124-1125 Grinnell Co., Inc., 981. 1112-1113, 1211 . - Hoffman Specialty Co.. Inc., 1213 1215 . ' . 'Illinois Engineering Co.. 1216-1217 Jenkins Bros., 1235 Jas. P. Marsh Corp., 1228-1229 Sarco Co.. Inc., 1218-1219 Trane Co.. The. 998-999 . - Detroit Lubricator Co., Div. of - American Radiator &. Standard'. Sanitary Corp.. 1122-1123 ' Friez .Instrument Div., Bendix Aviation Corp., 1128 * , General Controls. 1126-1127, : - - v General Electric.Co. (Schenectady, N. Y.). 1076-1077 :f ' McDonnell & Miller, 1194-1195. Payne Furnace Co., 972-973 Penn Electric Switch Co., 1141 V .' White-Rodgers Electric Go., 1146 ' York Corp., 960 . ' - '` ` VALVES, Stop and Check (See Valves, Non-Return) ' .- Warren Webster Co-, 1220-1223.. . VALVES, Gate . . . . American Brass Co.. - The, 1104 VALVES, Radiator Orifice VALVES, Tempering - 1105 : - . V Crane Co., 1154-1155 . . . - ..ti Detroit - Lubricator' Co. Div. of '.. American Radiator &- Standard v Sanitary Corp., 1122-1123 ,, Grinnell Co., Inc., 981, 1112-1113, ' _ - 1211- Jenkins Bros., 1235 :. . Barnes & Jones, Inc.. 1205 C. A. Dunham Co., 1206-1210 Grinnell Co., Inc., 981. 1112-1113. 1211 ... Illinois Engineering Co., 1216-1217 Sarco Co., Inc.; 1218-1219 - ' Trane Co/ The, 998-999 . Crane Co., 1154-U55 Dole Valve Co., The, 1234 " VALVES, Thermostatic ' Alco .Valve Co.. 1118 . Anderson Products, Inc.; 1233, Automatic Products Co.. 1120' ; . ., .' .' > ` Mueller Brass Co;, 1106-1107 :-:.-United States Radiator Corp;-, 1172 1 >;: 1173; :r .' ' ; VALVES, Radiator, Pneumatic Diaphragm ' ' - . - Detroit- Lubricator .Co., Div.. of . American Radiator & Standard Sanitary Corp.; 1122-1123 -. .Bell & Gossett Co., 1196-1197 Fulton Sylphon Co., 1124-1125 ALVES, Hydraulic . ' ` ' - Johnson Service Co., 1130-1131 ^K'^ Crane Co., 1154-1155 .. ^General Controls. 1126-1127. '. ' . . .,_ /- Yaniall-Waring Co., 1232 . ' Minneapolis-Honeywell Regulator Co., 1136-1137 / ' Powers Regulator Co.; The. 1142 -. . J i . VALVRS. Magnetic ' ' . . . VALVES, Reducing '. ' ^ :Alco Valve Co:, 1118 ' - - .Barber-Colman Co.. 1084, 1121 '/General Controls, 1126-1127 . .. Minneapolis-Honeywell Regulator Co:, 1136^1137 . v .Whlte-Rod gers. E.le..ct-ri.c Co., 11..4.6 American District Steam Co.', 1226, 1236 Bell & Gossett Co/ 1196-1197 Crane Co.. 1154-1155.. .- - C.*A. Dunham Co., 1206-1210 General Controls. 1126-1127. . 'Illinois Engineering Co.; 1216-1217 Illinois Engineering Co., 1216:1217- Minneapolis-Honeywell Regulator Co., 1136-1137 - Powers Regulator Co..-1142 ' . Sarco .Co/ Inc., 1218-1219 . Spence Engineering Co.: Inc., 1143' Tenney Engineering. Inc., 1145 ' Yarnall-Waring Co., 1232 ' .. VALVES,Water. Regulating' ~ . Automatic Products Co/ 1120. - Barber-Colman Co., 1084; 1121 Crane Co.. 1154-1155 ' . ^V^VALVESi Mixing; Thermostatic 'STpaecnocHe eEantgeirnse/.eInricn.g,-1C2o0/0, .I'-nc.,' 1143 . McDonnell & Miller, 1194-1195 - - .Minneapolis-Honeywell 'Regulator.- ' >>:<?, Fulton Sylphon Co.,1124/1125 Taylor Instrument Cos.; 1144 : Co.. 1136-1137 / . . . ^' Powers'Regulator Co., The, 1142 H. A. Thrush & Co., 1198-1199' Mueller Steam Specialty Co., 1227 , ,j^^/Sarcb jEo., Inc., 1218-1219 Penh Electric Switch Co.,-1141 - / . VALVES, Refrigerant Line Powers Regulator Co/. 1142 , _ . ' ^VALVES;' Motor .Operated. - Barber-Colman Co., 1084, 1121." ^:v-;Bell Sc.Gbssett Co/ 1196-1197 . Alco Valve Co.; 1118 - . - . Automatic Products Co./1120 Baker Ice Machine.Co.. Inc.,. 1038' -Sarco Co.. Inc.. 1218-1219 / - . Spence Engineering Co., Inc./1143 ;H. A. Thrush & Co.,, 1198:1199 ' ^Crane Co.. 1154-1155 ` . ; ? Detroit Lubricator Co., Divi of General Controls, 1126-1127 * .* ^'^^Illinois/Engineering Co.,'1216-1217 American-Radiator &'Standard, VAPOR HEATING SYSTEMS : ** Sanitary Corp/,'1122-1123 (See Heating Systems,'Vapor)' \ ^ Numerals following Manufacturers* Names refer to.pages in the Catalog Data Section. l-` - ' V- 936 ' 1946 Guide 'K. yf > > -;*> -_r f ^ r-x/^'V- ^ f/^2 * '' V-BELT DRIVES . . -.. -Hartzell Propeller Fan Co. (Div. of WASHERS, Air (See Air Washers) " American Coolair Corp.,-1050-i051 - Frick Co. (Inc.), 1041 Worthington Pump'& Machinery ^V-Corp.. 1046-1047 . VENTILATOR, Gasketing ; Products Research Co., 1230 u VENTILATORS, Attic (See also . - Fans, Electric,- Propeller and Ex ' haust) . Castle Hills Corp.), 1064 . Ilg Electric Ventilating Co., 982, . 1060-1061 Herman Nelson Corp- The, 992-993 New York Blower Co., The, 1067 . Propellair, Inc., 1068 ' B. F. Sturtevant Co., Div., West- inghouse Electric, 954-959, 1018 1019 . Trane Co., The. 998-999 L. J. Wing Mfg. Co.. 1000-1002 . WATER COOLING (S* also Cool ing Equipment, - Water; Cooling Towers) . . - _ ' ' Acme Industries, Inc.. 1030 Airtemp Div., Chrysler Corp., 966 . 967* April Showers Co., 1022 Bell & GossHt Co., 1196-1197 Fedders-Quigan Corp.. 980 General Electric Co. (Bloomfield. ' v - . Air Controls, Inc., 1049 .. Air Devices, Inc., 1080-1081 . ' American Blower Corp., 940-941 . American Coolair Corp., 1050-1051 Belanger Fan &-Blower Co., 1054 -1055 ' '. VENTILATORS, Ship Air Devices, Inc.', 1080-1081 G. C. Breidert Co., 1083 . . Hartzell Propeller Fan Co., 1064 Ilg Electric Ventilating Co., 982, N. J.). 948-949 . Liiie-Hoffman Cooling Towers, Inc., 1023 ' Marley Col, Inc., 1024 -- Monarch Mfg,.Works, Inc.', 1029 Niagara Blower. Co., 950 . ` G. C. Breidert Co.. 1083 . Chelsea Products,' Inc., 1058 - DeBothezat Fans Div., American Machine Sc Metals, Inc., 1159 ' ' Hartzell Propeller Fan Co.. 1064 1060-1061 New York Blower Co., The. 1067 L. J. Wing Mfg. Co.. 1000-1002 VENTILATORS, Unit j. F. Pritchard & Co.. 1025 B. F. Sturtevant Co., Div.,-West- inghouse Electric, 954-959!' 1018 1019 Trane Co.. The, 998-999 . _ Ilg'Electric Ventilating Co., 982, 1060-1061 - Herman Nelson Corp.. The, 992-993 - Propellair, Inc.. 1068 ; Schwitzer-Cummins, 1072 H. J. Somers, Inc., 1016-1017 ' B.'F. Sturtevant Co.. Div.. West . inghouse Electric, 954-959, 1018 - . -1019 Torrington Mfg. Co., The, 1070- - - ;-1071 ; ... ' " " . ... . -'United. States '-Air Conditioning v Corn., 953 .... - . - .United States'Register Co.. 1095 - ' ' Utlity.' Appliance Corp., (formerly American Coolair Corp., 1050-1051 Belanger Fan Sc Blower Co., -1054 1055. . Chelsea Products, Inc., 1058 " Hartzell Propeller Fan Co., 1064 Ilg . Electric Ventilating Co., 982. 1060-1061 . Herman Nelson Corp.. The, 992-993 John J. Nesbitt, Inc., 994 . .. New York Blower Co., The. -1067 Propellair. Inc., 1068 . SchwitzefrCummins, 1072. - B. F. Sturtevant Co., Div., West-! . inghouse Electric, 954-959,-1018 1019 . ` - Universal Cooler Div., Interna - tional Detrola Corp., 1045 VUter Mfg. Co.. The. 1048 Water Cooling Equipment Co., 1027 - .. -Williams Oil-O-Matic Div., Eureka .' Williams Corp*. 1190 . . Worthington - Pump & Machinery Corp., 1046-1047 . _ .YamaU-Waring Co., i232 York' Corp*. 960' '- Young Radiator Co., 997. ... WATER COOLING rTOWERS (See Cooling Towers, Water) ; Utility Fan Corp), 1073 ' - . Trane Co.. The, 998-999. Viking. Air ' Conditioning. Corp., WATER" FEEDERS (See Feeders, - .1074 .i - . VENTILATORS, Window , ; Water) : - ' - L..J. Wing Mfg. Co.. 1000-1002 Air Controls. Inc., 1049 ' .VENTILATORS, Floor and Wall American Blower Corp., 940-941- . WATER HEATERS (See Heaters, Hot Water Service). . * -- . Air Controls, Inc., 1049 ,' - . J Air Devices, Inc., 1080-1081-' " - American Coolair Corp.,-1050-1051. :. Barber-Colman Co.,! 1084. 1121 ` . Belanger Fan & Blower Co., 1054 1055 - . v Chelsea Products, Inc.', 1058' . Hart & Cooley Mfg. Co.. 1088-1089 "'' Hartzell Propeller Fan Co., 1064 . ` . Hendrick Mfg. Co., 1087 - - - ! Mlg Electric'Ventilating Co., 982, .1060-1061 - 'Independent' Register Co.. The. 1090' . Propellair. Inc.,'1068 American' Coolair Corp*. 1050-1051, Belanger Fan & Blower Co... 1054 1055 . Chelsea Products.Tnc.. 1058 ' DeBothezat Fans Div., American Machine & Metals, Inc., 1059 Hartzell Propeller Fan Col, 1064' WATER MIXERS, Thermo ' static .. Fulton Sylphon Co.; 1124-1125 Powers Regulator Co.. 1142 Sarco Co., Inc., 1218-1219 . ' - Ilg Electric Ventilating Co., 982, 1060-161 - - WATER TREATMENT Propellair. Inc., 1068 .. . Schwitzer-Cummins, 1072 - United States Air- Conditioning Research Products Corp., 1020 VincoGo., Inc., The. 1192-1193 ' Corp., 953 - Viking -Air Conditioning 1074. - . Corp., WELDING FITTINGS . tings. Welding). (See Fil- . Register & Grille Mfg. Co..' Inc.. VENTS, Gas Appliance- - WELDING ROD ' 1094 . . . . - Schwitzer-Cummins, 1072 . . Payne Furnace Co., 972-973 ; MueUer Brass.Co.. 1106-1107 Revere Copper & Brass, Inc., 1108 B._F..Sturtevant Co.. Div.,.West-' VIBRATION ABSORBERS- (See - inghouse .Electric, .954-959, 1018 . also Sound Deadening). . WHEELS, Blower - - . 1019 .. .. . Trane Co.. The, 998-999 . United^States Register Co.. 1095 . Armstrong Cork Co., 1248 \' Atlantic Metal Hose Co.; Inc., 1101 Chicago Metal Hose Corp., 1102 Air Controls. Inc.,T049 Champion - Blower & Forge Co., 1057 . . VENTILATORS, Mushroom' - Air Devices, Inc., 1080-1081 Clarage Fan Co., 946 . ,L. J. Mueller Furnace Co.,`970-971 Korfund Co.. Inc., The. 1262Mundet Cork Co., 1264 ' Products Research Co.. 1230 Seamlex Co., Inc., 1103 . Oarage Fan Co., 946 Hastings Air Conditioning Co lne.. 947- , ' Lau Blower Co.', The. 1065 ' Morrison Products, Inc., 1066 Tuttle & Bailey. Inc.,T092-1093 WALLBOARD, Insulating Schwitzer-Cummins, 1072 '. - :'.L. J. Wing Mfg. Co.. 1000-1002 " Armstrong Cork Co., 1248 B. F. Sturtevant Co.. Div.. West- .- VENTILATORS, Roof * .Air Controls,' Inc., 1049 ' Air Devices, Inci 1080-1081 - * American-Coolair Corp-. 1050-1051 American 3 Way-Ljjxfer Prism Co., 1239 v . . ; . ' . .. Celotex Corp*. The,. 1250 Insulate, 1256-1257 . Johns-Manville, 1258-1259 - - 'United States Gypsum Co., 1271 , ' Wood Conversion Co., -1272 ` 1270 inghouse Electric, 954-959, 1018-- 1019 . .* Torrington Mfg. Co.," The, 1070 1071 - . United States. Air Conditioning - _Corp*;953.. ' - Utility Appliance Corp. (formerly* Belanger Fain & Blower Co., -1054-"- WARM AIR FURNACES (See Utility-Fan Corp.), 1073 "' 1055 ' - ' ' Furnaces, Warm Air) - Viking Air. Conditioning Corp., G; C.;Breidert Co.,.1083 .. - 1074, .. .. C.helsea-Products, Inc.; 1058 - WARM AIR HEATING SYS- DeBothezat' FansDiv,. American ' TEMS ' (See . Heating Systems, WHEELS,. Spray .(See Spray \ . .Ts'Machirie & Metals, :Inc., 1059 Furnace) - v -. - 'Equipment) ` - .- V \^ ..Please mention.THE GUIDE.1946 when writing to:-Advertisers MANUFACTURERS' CATALOG DATA (PAGES 939-1280) On pages 939-1280 will be found the Catalog Data of 233 manufacturers whose products are described and illustrated. For the convenience of the user of THE GUIDE 1946 there are eight main divisions: Air Conditioning.............`................................. 939-1002 Air System Equipment.........:.........................1003-1100 Air Conditioning and Heating Piping. .1101-1109 Bends, Coils, Fittings............:.........................1110-1117 Controls and Instruments..........................1118-1146 Heating Systems.................................................11,48-1235 Insulation. ..:............ 1236-1272 Publications........................ 1273-1280 On pages 913-936, under each of the index headings--Air Cleaning Equipment, Fans, Hu midifiers, Ventilators, etc., will be found a list of manufacturers of any desired products, fully cross-indexed, and the page numbers in the Catalog Data Section where the products are described. By reference to these indices, the manu facturers names and the page numbers, any item of equipment or materials, and the producers address, may be located quickly. Air Conditioning Central Systems Air & Refrigeration Corporation 475 Fifth Avenue, New York 17, N. Y. Atlanta, Ga. Detroit, Mich. CAPILLARY AIR CONDITIONERS Standard Capillary cell. Cut-away section showing oriented glass Moments. Site: SO in s 0 in. x 8 in. Air Conditioning Engineers and In dustrial Engineers responsible for air conditioning should be familiar with the uses of this advanced equipment. The standard Capillary cell is the basic element in all Capillary conditioners. The patented arrangement of glass fila ments, essentially parallel to the How of air and water through the cell, accounts for the highly efficient heat transfer between air and water as well as low resistance. At the same time, the cells act as an efficient air cleaner and the arrested dirt is continuously flushed from the cell. As a simple air washer, humidifier or evaporative cooler. Class I Capillary conditioners call for the recirculation of only 3 gpm per 1000 cfm distributed over the cells at 6 lbs nozzle pressure. The saturation efficiency is 97 per cent. Less efficient spray washers require 15 gpm or more at 20 lbs nozzle pressure. For cooling and dehumidifying a single stage of Capillary cells equals or exceeds in capacity a 2-bank spray type dehumidifier. . Other Capillary types offer true counterflow performance with leaving cooling water temperature exceeding that of leaving air. Where a closed system for the cooling medium is required (direct expansion, brine or cold water). Capillaries are offered with suitable coils after the Capillary cells. No filters are required. Coils are kept clean and evaporative cool ing is available whenever entering wet- bulb conditions permit. * Simple, continuous water treatment is available to protect coils and other metal parts against corrosion. A standard Site 6-5 Class 1 Capillary Central Station Installation. Varied uses, for Capillary con ditioners are suggested by the intimate contact of fluid and gas passing through the cells. Among these are: condenser water cooling; fume absorption, aeration and concentration; air sterilization with agents added to water. Capillary conditioners of all classes are made in central station units ranging from 2200 cfm to 132,000 cfm or larger. As sembled units including fans, heaters, coils, pump, insulated casing, etc., suitable for suspension or floor mounting range from 1000 to 16,000 cfm. A standard Size 3-4 Capillary unit air conditioner complete in insulated casing. Capacity 16,000 cfm. Submit design and capacity for specific recom mendations or write for catalog and engineering data. 939 Air Conditioning Unit Systems American Blower Corporation P. 0. Box 58, Roosevelt Park Annex, Detroit 32, Michigan CANADIAN SIROCCO COMPANY, LTD. in Canada, 310 Ellis Street, Windsor, Ontario Branch Offices In Principal Cities Division of American Radiator and Standard Sanitary Corporation AIR CONDITIONING -- HUMIDIFYING -- DEHUMIDIFYING -- COOLING VENTILATING -- HEATING -- VAPOR-ABSORPTION -- DRYING -- AIR WASHING AND PURIFICATION -- EXHAUSTING EQUIPMENT AND MECHANICAL DRAFT APPARATUS Commercial V-Belt Drive Ventura Fans--for ventilating applications without duct sys tems, where extremely quiet operation is desired. Inlet-outlet streamlined for high efficiency. Also direct connected. Request Bulletin B-2529. . Double Inlet "ABC" Multiblade Fan--above, is a heavy duty ventilating fan. Its wheel has narrow, forward pitched blades. Low tip speeds assure quiet operation. Request Bulletin A-701. Write for Bulletin A-403 for backwardly inclined, non overloading H. S. Fan. "ABC" Utility Sets-- right, complete packaged units, direct connected or V-Belt short coupled drive, for duct applica tions. Famous "ABC" Multiblade Wheel oper ates at low tip speeds. Quiet, compact. Bul letin B-2529. . American Blower Corporation Air Conditioning Central Systems Unit Systems TYPES OF AMERICAN BLOWER CORPORATION AIR HANDLING AND CONDITIONING EQUIPMENT All types of air handling and air conditioning equipment for industrial applications, process work, drying, cooling; also equipment for stores, offices, shops, public buildings, power plants, etc., and attic ventilation for homes. "ABC" Vertical Heaters--for ceiling applications, give an even, wide floor area distribution of heat. For either steam or hot water heating systems. Variable speed, 2-speed and constant speed models. Write for Bulletin A-9418. "HV" General Purpose Units--with air filters and Aileron control. Ideal wherever attractive, quiet and economical heating and ventilating units are required. Wall, floor or ceiling mounting. Offer great flexibility of design and arrangement to meet specific needs. Write for Bulletin 5927. . Venturafin Unit Heaters--for many general purpose heating jobs. Wall or ceiling mounting. Streamline construc tion, nigged heating elements. Steam or hot water. Write for Bulletin A-8218. . American Blower Air Washer --above, cleans, purifies and freshens the air, removes dust, odors and bacteria, cools if desired and provides an effective method of controlling humidity. Bulletin 3623. American Blower Capillary Air Washers--above, for high efficiency in cleaning, humidification, cooling. and dehumidification of air. A highly efficient sur- . face contact mechanism, the capillary cell, is used. Air is forced at low resistance through long, irregular passages of small size formed by a large amount of thoroughly wetted glass surface. Unit includes a substantial metal casing and tank of air washer design, capillary cells, improved low head sprays, metal or glass fibre low resistance moisture elimina tors, non-ferrous, extended surface cooling or heating coils. Write for Bulletin 3723. 940 Air Conditioning Central Systems-- provide an effective way of cooling, heating, humidifying, dehumidifying and purifying air in all classes of business and public buildings where a dust system is desirable. Write for Special Data. American Blower Series "H" Air Con ditioners with Sprayed Coils--are usually applied for industrial uses where air washing and evaporative cooling are required. Sprayed coils give cleaner air, cut coil maintenance and refrigeration costs, reduce necessary air volumes, permit use of smaller ducts and grilles. Horizontal or floor types (as shown). Aileron control provides simple method of regulating flow of air from the fans. Write for Bulletin 6027. 941 Air Conditioning Central Systems The Bahnson Company AIR CONDITIONING ENGINEERS Winston-Salem, N. C. Offices: . New York, N. Y.. 93 Worth St. Atlanta. Ga..............--886 Drewry Si. Hamilton. Ont.. Can_______________ W. J. Westaway Co.. Ltd. Westfield, N. J_______ ____ 703 Embree Crescent Los Angeles. Calif ............ 553 S. Figueroa St. HUMIDIFYING--COOLING--HEATING--AIR CLEANING--VENTILATING Bahnson Industrial Air Conditioning and Humidifying Equipment has been installed throughout the United States and in over 30 foreign countries for more than three decades. In designing various types of equipment to meet the requirements of Industrial Air Conditioning and Humidifying, the Bahnson Company has considered as paramount: Flexibility of capacity and control, Economy of Operation, and Simplicity of Design. CENTRISPRAY Certain types of industrial air condition ing problems lend themselves more readily to central station systems or unitary sys tems that deliver saturated air. The Bahnson Company has designed, and installed a large number of saturated air systems of both unitary and central station types. Conventional air washers manufactured by the Bahnson Company show a high efficiency of operation'in the low punjping cost and low static pressures. The Bahnson Centrispray. is a develop ment of an air washer to deliver saturated air, based on the principle of centrifugal atomization. This washer affords an ex tremely low operating cost, approaching that of capillary washers. Maintenance of the Centrispray is extremely low, since there are no nozzles to stop up and the centrifugal discs are self-cleaning. Bahnson central station installations as employed with refrigeration, and as employed for evapora tive cooling only. AIR-VITALIZER The Centrispray can be engineered for small compact units or large central station units. It may be designed for use with electrostatic air cleaning or refrigeration, as well as for evaporative cooling. . The Bahnson Air-Vitalizer air con ditioning system employs a dry duct unit distribution system combined with the Bahnson Centrifugal Humidifier or the Bahnson Atomizer, to-obtain evaporation. The Vitalizer Units are usually arrang ed in the room so that the general move ment of air is carried down one side of the room and back the other side of the room. This featurfe, known as horizontal circula tion, evens out the condition in the room despite the concentrated heat loads in motor alleys and sections of machinery with high horsepower requirements. The flexibility of the Vitalizer system permits the system to be designed for any air handling or evaporative capacity. ECONOMIZER ATOMIZER The Bahnson Economizer, an atomiz er embodying a new principle of- variable capacity, will produce a finer spray at a given evaporatibn, with minimum' air pressure and air consumption. It is an outstanding development in the atomizer field, featuring. Flexibility, Econ omy, and Simplicity of installation, oper ation and design. . :. . 942 Air Conditioning Central Systems The Bahnson Company Winston-Salem, N. C. CENTRIFUGAL HUMIDIFIER With this unit, Bahnson has pioneered in developing the principle of centrifugal atomization for over 30 years. Con tinuous refinement has produced three improved types of units with varying capacities to meet different requirements. (Types D, H and L). The Bahnson Centrifugal Humidi fier requires only feed water at city main pressures (15 to 30 lbs.), a small amount of electric current at the usual voltage speci fications, and a drain line. Equipped with an individual control, it is the only type of self-contained industrial humidifying unit that will produce a fine mist, distribute this mist throughout the-space to be con ditioned, maintain air circulation within that space, and automatically control the humidity within that space. These units may be equipped with the Type J individual. control, or may be operated with the highly sensitive Master B group control that actuates an electric motor valve on the feed water line to a group of humidifiers. The Atomizing Disc is mounted on one end of the fractional horsepower motor. A row of stationary atomizing teeth surround the periphery of this disc. Water, fed onto the rapidly whirling disc, is hurled against the stationary' teeth and broken _ Type II with J Control into a fine, cloudlike mist. A fan mounted on the back end of the motor shaft dis tributes this fine mist and produces a directional air flow. This maintains air circulation and uniformity of condition throughout the space to be conditioned. Write for Bulletin 327S, or special bulletins on special applications. HUMIDUCT AIR CONDITIONING SYSTEM The Bahnson Company has led in the development of two new principles of industrial air conditioning for more than a decade with its "Humiduct" system of air conditioning. . The Bahnson Humiduct was the first practical unit for utilizing the advantages of delivering saturated air plus entrained moisture from an air conditioning system, rather than saturated air alone to meet, certain air conditioning requirements. Where it is necessary to maintain constant relative humidities in areas .with con centrated heat loads, this principle of delivering entrained moisture so that-part of the evaporation may take place in the room, shows marked advantages in more accurate control of the humidity. ' The humidity can be maintained by the use of this principle with a much lower volume of air than with saturated air types of systems: The Bahnson Humiduct is designed as a unit system of air conditioning. It has shown marked advantages in maintaining uniform conditions throughout the rooms of industrial plants that have, relatively high heat loads or varying concentrations of machinery and heat. These advantages together with the flexibility of operating the unit system, have been widely recog nized. The Bahnson Company introduced the principle of horizontal circulation with a unit system. The units are installed to produce a general air movement down one side of a room and back the other. This produces unusual evenness in the room con ditions together with a sensible cooling effect.. `. 943 3 Air Conditioning Central Systems Carrier Corporation Air Conditioning Central Systems Carrier Corporation Syracuse 1, N. Y. Carfier REFRIGERATION . MARINE DIVISION: 405 Lexington Ave. New York 17, N. Y. Carrier INTERNATIONAL DIVISION: 122 East 42nd St. New York 17, N. Y. Offices and Dealers in principal cities--refer to your telephone directory. AIR CONDITIONING Room Air Conditioners--compact units in attractive cabinets. Built to provide summer comfort air conditioning for individual rooms, private offices, and other small enclosures. Self-Contained Air Conditioners--com pletely enclosed in neat cabinets, these units provide summer comfort for retail shops, general offices, beauty salons, and other com mercial spaces of medium size. Assembled Air Conditioners--fully en closed, compact units designed for installation outside the space to be air conditioned, and using ducts to distribute the air. Ideal for year round conditioning of laboratories, offices, stores, and similar interiors. Unitary and Central Station Air Con ditioners--for groups of rooms such as offices and laboratories, and for large spaces such as stores, factories, theaters, industrial plants, and other interiors requiring year round air . conditioning. Units available in floor or sus pension models. Supplemented by refrigeration where cooling and dehumidifying is required. "Weathennaster" Systems--for multi room buildings such as apartments, hospitals, hotels, and office buildings. System consists of room units, each with individual control of temperature, and a central station,system. In one system the air is distributed through conduits requiring but little space--practical for new or old buildings. An exclusive de velopment of the Carrier Corporation. Blast Freezers and Cold Diffusers--for food freezing and storage, meat packing opera tions, and other industries requiring low tem peratures. Units are available in suspension or floor models and can be use.d within the space to be refrigerated or remotely located and connected by ducts. .. Dehydration Units--for industrial appli cations such as drying, chemical processing, and all production requiring low moisture content air. Dehydrated air is - distributed through ducts, and refrigeration may be added to achieve low temperatures. 944 " 7 Centrifugal Refrigerating Machine--for large comfort and industrial air conditioning applications and for cooling processes down to below --100 F. These efficient machines operate with any standard drive, are practically vibrationless, and require little supervision. Uses safe refrigerant. Available in capacities from 100 to 1200 tons cooling. Reciprocating Refrigerating Machines-- to provide refrigeration for industrial and com fort air conditioning of moderate size, and for cooling processes down to below zero tempera tures. complete machines include a belt drive compressor, a water-cooled condenser, receiver, and necessary connections available for evapo rative cendenser. Capacities from 5 to 60 hp. Evaporative Condensers--for condensing refrigerants and cooling liquids by a process of blowing.air over, wetted coils. The evaporation of the water from the surface of the coils removes a maximum amount of heat with a minimum of water consumption. Can be used in place of a cooling tower. Afford savings wher ever water costs are high. May be placed out doors without protection. Capacities range from 6 to 75 tons condensing. Commercial Refrigeration Compressors --for storage refrigerators, display cases, milk coolers, ice makers, farm and home food freez ers in a wide range of capacities and tempera tures. Units use "Freon" or Methyl Chlor ide refrigerants and are complete with com pressor, drive, air or water cooled condenser, and controls mounted on a one-piece base. (Carrier) INDUSTRIAL HEATING Unit Heaters--for commercial and indus trial heating uses. Available in two suspended types: one horizontal discharge model for small space heating and one vertical 4-way discharge model for larger areas. Both models have adjustable louvres for directional control. Units consist of propellor. type fan, coils for steam or hot water, arid drive, all neatly encased. Available with manual or thermo static controls. Capacities range from 32,000 to 579,000 Btu per hour at 2 lb steam pressure. Heat Diffusing Units--for commercial and industrial buildings. Suspended or floor models with centrifugal type fan, coils for steam or hot water, and selective air distribution, all factory assembled for easy installation. Capa cities are from 105,000 to 1,035,000 Btu per . hour at 2 lb steam pressure. 945 Air Conditioning Cen tral Systems Clarage Fan Company Kalamazoo, Michigan Application Engineering Offices (Consult Telephone Directory) Clarage Air-Handling and Conditioning Equipment Fans Blowers Air Washers Air Conditioning Systems and Units Unit Heaters & Coolers For over a quarter-century Clarage has been a lead ing manufacturer of equipment for ventilating, heating, . cooling, drying, air cleaning, humidifying, dehumidifying, complete air conditioning, exhausting, pneumatic conveying and mechanical draft. This equipment is designed to meet all types of industrial, commercial, public building and marine requirements. Whatever your air-handling or conditioning problem, Clarage is an excellent source of supply. Fans for ventilating and air conditioning. 28 sizes; 200 to 100,000 cfm. We build many yther types of rans and allied equipment. Write ror a C lar a g e catalog covering yur complete line. Fans for warm air furnaces, oil burners, stokers, etc. 200 to 5000 cfm. Fans for ex haust systems, pressure blow ing, etc. 500 to 50,000 cfm.; built for a wide rangeof pressures. ' Unit Heaters for factories, stores, offices, etc.--floor and suspended type units. 24 standard sizes. Air Condition ing central sys tems and units to solve any temperature and humidity codtrol prob lem. Air Conditioning Central.Systems Unit Heaters and Coolers Hastings Air Conditioning Co., Inc. Hastings, Nebr. - Manufacturers of ) Air Conditioners. Unit Heaters. Utility and Package Blowers. Dealers and Representatives in Principal Cities A Complete Line of Highly Successful COLD WATER Air Conditioners. Capacities listed depend on entering air and water temperatures. All equipment available for combination heating and cooling. FLOWMETERS (to visually control water flow) standard on all models. FLOOR MODELS Floorma8ters--Unusual design and special features permit maximum installa tion possibilities with minimum floor space and installation costs. Air Delivery--2240 cfm. Cooling Capacity--3 to 6 tons. Dimensions-- Height 93 in., Width 48 in. Depth 25 in. Motor-- H hp. Filters--3 16 in. x 25 in. *; Royal--For offices, homes, hospitals, etc. Air Delivery--590 cfm. Cooling Capacity--1 to 2 tons. Motor--1/6 Hp. Filter--1 16 in. x 25 in. Dimensions--Height 40 in., Width 28 in., Depth 20^3 in. ' " . (C.P.) CENTRAL PLANTS Sectional con struction for ease of handling. Mo tors inside mount ed to provide very neat appearing compact units. Size CP 30 CP 40 CP 60 CP 60 CPI20 SPECIFICATIONS' CFM Motor Hp Filter* 3,000 4.000 6.000 8,000 12.000 1 1 2 3 5 S 8 10 12 20 Capacity Toni 4- 9 6-12 9-18 12-24 18-36 GENERAL UTILITY MODELS Master--Singly or in multiple are suitable for any business or space size. Large jobs handled without duct work by proper location of units. Air Delivery--2,240 cfm. Cooling Ca pacity--3 to 6 tons. Dimensions--Height 29 in., Width 49 in., Depth 50 in. Motor-- hp. Filters---4 16 in. x 23 in. Majestic--Similar to Masterexcept size. Air Delivery--1120 cfm. Cooling Ca pacity--1^ to 3 tons. Motor--hp. Filters--2 16 in. x 25 in. Dimensions-- Height 26 in., Width 28 in.. Depth 40 in. Zephyr--Same capacity, motor and filter as the Royal. For use where sus pended or concealed units are desired. Dimensions--Height 26 in.. Width 24 in.. Depth 28 in. UNIT HEATERS Centrifugal Type for extreme quietness and efficiency. Steam pressure-- to 150 lbs per sq in. ` Finish--Brown wrinkle enamel and stainless steel louvers. 4 PACKAGE AND OPEN TYPE BLOWERS May be knocked down for narrow door ways. Finished in at: tractive green wrinkle. Utility type blowers are available with or without motors and in any dis charge desired. ` All sizes from 9 in. to twin 21 in. Air deliveries from 1000 cfm to 16,000 cfm. Write for Catalogues, Literature, or Information 947 Air Conditioning Central Systems GENERAL ELECTRIC AIR CONDITIONING DEPARTMENT BLOOMFIELD NEW JERSEY Atlanta 3, Ga. 009 Red Rock Building Boston 15, Mass. 700 Commonwealth Avenue Chicago. III. 222 No. Bank Drive Cleveland 4, Ohio 4966 Woodland Avenue District Offices Dallas 2. Texas 1801 North Lamar Street Kansas City 6, Kansas 2206 Power & Light Building 106 West 14th Street 2,Minneapolis Minn. 650 Plymouth Building 12 South 6th Street New York 22, N. Y. 570 Lexington Avenue Philadelphia 22, Pa. 1405 Locust Street Portland 7. Orb. P. O. Box 909 AUTOMATIC HEATING EQUIPMENT G-E OIL-FIRED BOILER available in 7 types with a range of from 75,000 to 450,000 Btu per hour output. G-E OIL-FIRED CONVERSION BURNER attachment type, 141,000 to 423,000 Btu per hour input. G-E OIL-FIRED. WARM AIR CONDITIONER factory wired and as sembled for installation, 120,000 Btu per hour output. G-E GAS-FIRED BOILERS avaifable in 8 types, 76,000 to 345,600 Btu per hour output. G-E GAS-FIRED WARM . AIR CONDITIONER packaged unit available in 5 models ranging in air heating capacities from 48,000 to 168,000 Btu per hour output. , ' G-E Oil-Fired Boiler PACKAGED?'. AIR CONDITIONING EQUIPMENT G-E Floor Mounted Room Air Conditioner G-E FLOOR MOUNTED ROOM AIR CONDITION - ER provides cooling, dehumidification, circulation, ven tilating and filtering, 40*Ht in.'high, net cooling capacity of 8,000 Btu per hour at ^.S.R.E. standard rating conditions. G-E SELF-CONTAINED AIR CONDITIONERS for domestic or commercial applications, with or without ducts---optional equipment makes it possible to provide heating and humidification in winter, for complete year 'round air conditioning. . . .. COMMERCIAL REFRIGERATION and WATER COOLERS G-E WATER COOLERS bottle type, holding 3 or 4 gal. water-bottles, cools 2.4 gal. per hour A.S.R.E. standard capacity rating. G-E FOOT PEDAL OPERATED WATER COOLER, ranging in cooling capacity from 5.0 to 19.8 gal. per hour A.SM.E. standard capacity ratings. G-E FOOD STORAGE CABINETS in a range of sizes for restaurants, hospitals, hotels, grocery stores, and meat markets. 948 General Electric Air Conditioning Central Systems CENTRAL PLANT AIR CONDITIONING AND REFRIGERATION EQUIPMENT Refrigeration Condensing Units 1/6 HP to 125 HP--A complete line of recipro cating type condensing units for use with "Freon" refrigerants. Air cooled models available from 1/6 hp to 3 hp. Motor-com pressor units for use with evaporative con densers or cooling towers available from 3 hp to 125 hp. Evaporative Condensers--For use with refrigeration motor-compressor units in those applications where cooling water is scarce or contaminated, or where water rates are high--a line of eight standard sizes ranging in condensing capacities from 3 to 100 tons of refrigeration with "Freon-12." Evaporative Coolers--Provide water saving and economic advantages in those applications where large, quantities of cooling water are used, the temperature of which need not be lower than five degrees above maximum wet-bulb temperature. Available in eight standard models ranging in capacity from 250,000 to 3,000,000 Btu per hour for water. Unit Coolers--A line of wall and ceiling-mounted "Conditioned Air" cooling units designed to maintain high humidity for correct preservation of perishable foods. .General Electric also offers a line of product coolers for such applications as refrigerated ware houses, fur storage plants, large locker plants and other large refrigerated storage spaces. Central Plant Air Conditioners--A line of horizontal units ranging in size from 2% to 30 tons of refrigeration in cooling service with comparable capacities for heating service. General Electric will'also furnish vertical air conditioners ranging in size from approxi mately 2 to 50 tons of refrigeration in cooling service, with comparable capacities for heating. Heating and Cooling Coil Surface--High heat transfer efficiency finned copper surface for use with steam, hot water, chilled water, or refrigerant. Particularly valuable for all types of built-up air conditioners or blast coils. Designed for multiple mounting in housings or ducts, these coils can be bolted together to form a continuous unbroken surface. ' Complete Air Conditioning Systems--Multiple unit systems for the air condition ing of hotels, office buildings, apartment houses, and hospitals. Attractive, compact room units make possible personal control of conditions in individual rooms. Refrigera tion in central plant furnished by reciprocating type condensing units or centrifugal refrigeration units as requirements dictate. . 949 Air Conditioning Ccn tral Systems Niagara Blower Company General Sales Office: 6 East 45th Street, New York 17, N. Y. Chicago-5:37 W. Van Buren St. Buppalo-7: 673 Ontario SL Seattle-4: Fourth and Cherry Bide. District Engineers in Principal Cities Over SO Years* Experience in Industrial Air Conditioning, Liquid Cooling and Air Drying NIAGARA AERO HEAT EXCHANGER For cooling industrial liquids, water, oils, solutions, chemicals, compressed air and gases, with Niagara "Balanced Wet-Bulb" temperature control to improve efficiency and ob tain precise results. Patented (U- S. Nos. 2,296,946 and R. I; 22,553). Ask for Bulletin 96. NIAGARA AIR CONDITIONING SYSTEMS For human comfort and for all industrial applications requiring controlled conditions of temperature, relative humidity, air purity and air movement. . NIAGARA AIR CONDITIONER, TYPE A High precision apparatus using saturation to obtain control of R.H. to ^ 1 per cent for laboratory work and control of hygroscopic materials. Ask for Bulletin 58. NIAGARA AIR CONDITIONER, TYPE C A year around air conditioning unit providing heating and humidifying or dehumidifying. Ask for Bulletin 80. NIAGARA FAN COOLER AND DISK FAN COOLER / For comfort cooling, process cooling, low temperature storage for dairies, fruits, meats, food products, fur storage vaults, etc. Bulletins 72 and 78* NIAGARA SPRAY COOLER For all cooling applications requiring high humidity or high capacity in small space. Ask for Bulletins 72 and 78. NIAGARA "NO FROST" SYSTEM - Using Niagara "No Frost" Liquid in spray coolers, prevents frosting of cooling coils, automatically keeps spray solution at proper concen tration, gives freedom from brine troubles, corrosion. Constant, efficient operation. Temperature to--100 F. Ask for Bulletins 83 and 95. NIAGARA EXTENDED SURFACE COILS Encased for use with heating, cooling or air conditioning systems. Full range of sizes. Ask for Bulletin 92. ' . NIAGARA DUO-PASS AERO CONDENSER (Illustrated) Saves power and water cost utilizing atmospheric air to remove heat .of condensation. Patented Duo-Pass prevents scaling, saves power. "OILOUT"-positively removes oil and dirt from refrigerant lines, assuring always full capacity. Ask for Bulletins 91 and 93. NIAGARA "DUAL" COOLERS Simultaneously cools a room and furnishes chilled water as a refrigerant. Saves equip ment cost, operating expense. Patented. Ask for Bulletin 70. NIAGARA INDUSTRIAL LIQUID COOLER Furnishes refrigerated water or aqueous solution in any quantity up to 220 gpm. Positive control of temperature regardless of load variation. Delivers "sweet" water at 33 F without danger of freezing damage. . NIAGARA FAN HEATERS AND DISK FAN HEATERS For heating and ventilating large areas. Units of the highest quality in engineering, material and workmanship. Ask for Bulletin 97. . NIAGARA AIR SUPPLY HEATER Balances exhausted air in factories when exhaust systems are operating, saves steam and power, gives more effective heating. Patent pending. Ask for Bulletin 74. ,, ' Niagara Aero Condenser with "Oilout" NIAGARA MOTOR BLOWERS One, two and three-fan units. High and low static pressure models. Ask for Bulletin 89. 950 Air Conditioning Central System a Parks-Cramer Company Fitchburg, Mass. Charlotte, N. C. CERTIFIED CLIMATE Complete Air Conditioning Systems including Heating, Cooling, Humidifying or De-humldifying, Air Changing, Refrigeration, Air Filtering, Air Washing AUTOMATIC REGULATION Merrill Process System of Hot Oil Circulation for Heating Industrial Materials Central Station Central Station Air Conditioning * Centrally, located AIR WASHER. Proper moisture. Positive, pre-determined- air removal or re-circulation. Heating coils and refrigeration optional. Helps such industries as Celluloid; Cement; Ceramics; Cereals; Cigars, Cigarettes and Tobacco; Clothing; Confection ery; Glassine; Leather; Paper and Envelopes; Printing and Lithographing; Shoes; Starch and Dextrine; Storage of Perishables; Textiles; Wood Products. Similar installations effective in Hospitals, Art Gal leries, Auditoriums, Restaurants. Air Washer or Central Station Units. Nozzles for Central Station Air Washers. . Turbomatic Humidifier Psychrostot Pettifogger Turbomatic Humidifier Efficient humidifier of the atomizer type. For direct humidification, as humidity boosters for Central Station systems of all makes. Self-cleaning, both air and water ports. Streamlined to prevent lint and dirt accumu lation. High Duty Humidifier (not illustrated) . Water under pressure generates spray. Excess water returns to filter tank and re-circulates. Evaporation per unit high; two sizes of heads each with three sizes of nozzles give flexible capacity for varying conditions! Circulation increased by individual motor-driven fan. Spray thoroughly diffused and distributed over wide area. Parks Automatic Airchanger (not illustrated) For use with High Duty or Turbomatic Humidifiers. In sures fixed humidity and maximum evaporative cooling. Automatic Regulation The Psychrostat for accuracy, durability, sensitivity. Employs the principle of the Sling Psychrometer, used in all U. S. Weather Bureau Stations. Hygrostat (not illustrated) where requirements are not so exacting. An Air Conditioning System is no better than - its Regulation. ' The Pettifogger ' A compact humidifier for offices, stores, storerooms, laboratories, or other isolated departments. Self-con tained in lacquered copper casing. Permanently though flexibly connected to water and electrical supplies. Automatic control. Adjustable capacity. Reduces dust. Neutralizes drying effect of heating. Air Conditioning Central Systems Rogers Diesel and Aircraft Corporation manufacturers of . ROGERS-RESEARCH SYSTEMS OF AIR CONDITIONING AND AIR STERILIZATION 120 Leggett Avenue New York 59, N. Y. AIR CONDITIONING THROUGH DEHUMIDIFICATION The Rogers-Research System of Air Conditioning employs a chemical--triethylene glycol--to remove unwanted moisture from the air. Precise humidity and temperature conditions are maintained automatically and economically by this separate control of temperature and humidity. Conditioned air can be obtained at^' a low dew point with little change between the temperature of the incoming and the outgoing air. . The Rogers-Research System features simplified equipment, low maintenance, and operating costs, single unit installation for continuous duty operation with minimum space requirements. Industrial and Comfort Air Conditioning--The following table indicates indoor conditions which can be obtained through a Rogers-Research Air Conditioning instal lation: . When Available Cooling Water Temperature for Absorber Coil is. . . 40 45 50 55 60 65 70 75 80 85 90F Then Temperature of Air Leaving Absorber can be as low as . . . ' 45 50 55 60 65 70 75 80 85 90 95 F . And the Dew Point of Air Leaving Absorber can be as low as . . . " *. 12 16 20 24 28 33 37 41 46 50 54 F . These conditions can be varied to the requirements of the purchaser. . AIR STERILIZATION'' Triethylene glycol used in the Rogers-Research Systems sterilizes air, renders inactive harmful, air-borne bacteria. All air passing through a Rogers-Research Air Conditioning unit comes in contact with this air sterilizing agent. In addition there is a complete line of Rogers-Research vaporizers for evaporating triethylene glycol into the air. These vaporizers can be used in conjunction with an air conditioning system, or independent of any air conditioning system. Vaporizers are made in sizes ranging from small table models for home use, to large, cabinet-sized units for hospitals, factories or large com- mercial premises. . ... Rogers-Research Air Conditioning and Air Sterilization equipment is avail able in a wide range of capacities for many applications. For complete information, write to the Rogers Diesel and Aircraft Corporation, Department A. / 952 Air Conditioning systems United States Air Conditioning Corporation Heating, Cooling, Ventilating and . Air Conditioning Equipment For Industrial, Commercial and Residential Applications General Offices and Factory: Northwestern Terminal, Minneapolis, Minn. Blowers. Exhausters and Fans Unit Heaters Coil Cooling Units USAirCo Blowers Heavy and light duty blowers, single or double inlet, in sizes and capaci ties for any heating, cooling, ventila ting and air conditioning application. USAirCo Air Washers Single, double or triple stage 2,500 to 100,000 cfm for cleansing, cooling ` by cold water or refrigerant, humidi fying or dehumidifying. USAirCo Heating Units . Suspended types with Deflecto dif fusing grilles. Floor or wall type "blower heaters. Sizes and types for every heating need. USAirCo Cooling or Heating Cores Five standard series for central sta tion heating or cooling applications. USAirCo Cooling Units Suspended type for cold water or direct expansion applications. USAirCo Blower Filters Complete assemblies for warm-air furnace applications. Kooler-aire Package Units Complete self-contained units for refrigerative, cold water and evapor ative cooling. Also room coolers and humidifiers. . USAirCo Deflecto Grilles Patented diffusing grilles for con trolled directional distribution of air. Write for Latest USAirCo Catalog Evaporative Condensers Cooling and Heating Coils Air U'ashers Blower-Filter Units . Refrigerated Air Conditioning Units 953 Air System Equipment < / B. F. STURTEVANT COMPANY Division of Westinghouse Electric Air Conditioning, Heating, Ventilating, Dust Control and Fume Removal Equipment, Vacuum Cleaners, Dryers, Compressors, Motors, Turbines, Mechanical Draft Equipment Main Office and Works Akron, Ohio Albant, N. V. Atlanta, Ga. Baltimore, Mo. Boston, Mass. Buffalo, N. Y. Camden, N. J. Chicago, III. Cincinnati, Ohio Cleveland, Ohio Columbus, Ohio Hyde Park, Boston, Mass. Sales Engineering Offices Dallas, Texas Denver, Colo. Des Moines. Iowa Detroit, Mich. El Paso, Texas Galveston. Texas Greensboro, N. C. Hartford, Conn. Houston, Texas Indianapolis, Ind. Jacksonville. Fla. Kansas Crrr, Mo. Little Rock. Ark. Los Angeles, Calif. Memphis. Tenn. Milwaukee, Wis. Minneapolis, Minn. Newark, N. J. New Orleans, La. New York. N. Y. North Hero. Vt. Phoenix, Ariz. Pittsburgh. Pa. Portland, Ore. Richmond, Va. St. Louis, Mo. Salt Lake City, Utah San Francisco. Calif. Seattle. Wash. Spokane, Wash. Springfield, Mass. Syracuse, N. Y. Tampa, Fla. Toledo. Ohio Washington, D. C. PLANTS: Located at HYDE PARK, BOSTON. MASS.; LaSALLE. ILL.; CAMDEN. N. J.; BERKELEY. CALIF.; and GALT. ONT. B. F. STURTEVANT COMPANY OF CANADA. LTD.. CALT, ONT.; Sales Offices in Toronto and Montreal, and representatives in principal Canadian Cities. HOW STURTEVANT ENGINEERING SERVICE CAN HELP YOU As a leader in the manufacture of Air Handling Equipment, backed by more than 80 years' experience, B. F. STURTE VANT COMPANY is exceptionally quali fied to help you attain the most efficient and economical solution of any air handling problem. Skilled Sturtevant Engineering experts, located in many leading cities are prepared to render the following 5-point service: (1) Analyze your problem. (2) Recommend the'solution. (3) Specify the equipment. (4) Supervise the installation. (5) Check the operation. Whether requirements call for a single unit of apparatus or a complete engineered system, Sturtevant engineers can recom mend the solution best suited to fulfill your individual needs. Do not hesitate to call the Sturtevant representative nearest you for assistance. Needless to say, no obligation is incurred. As a preliminary aid, we list on the following two pages the major types of equipment manufactured by-us, together with their general applications and the reference numbers of catalogs available. INDUSTRIAL HEATING AND VENTILATING Mr. Sturtevant invented and was granted U. S. Letters Patent No. 92,490 covering the first so-called hot blast inT dustrial heating system on July 13th, 1869. Since that time- Sturtevant has been responsible for many basic improvements in factory heating, moving forward with the trend of times to the modern and efficient hot blast central station.heating system, .the combined heating, ventilating and humidifying systems, and the unitary system which is clearly indicated for many installations, and which is now so popular. Sturtevant manufactures the component parts for all of these systems, including fans and blowers,' heating surface, air washers, - humidifiers, unit heaters and motors. This fact enables our engineers to make an unbiased selection and recommendation of the type of system and apparatus offering the most efficient and economical solution to any factory heating and ventilating problem. ' 954 Healing and Ventilating System in Machine Shop Unit Heaters in pipe warehouse Air System Equipment Fans and Blowers TABULAR VIEW OF STURTEVANT EQUIPMENT AND APPLICATIONS This table shows at a glance types of equipment manufactured by B. F. Sturte vant Company and their general applica tion, together with catalog numbers on specific equipment. The numbers shown under "General Application," in the left column refer to the Index of Products. If no catalog number is given, write to B. F. STURTEVANT COMPANY, main office, or to the nearest branch office, stating specific requirements, and complete in formation will be sent immediately. General Catalog No. 500 gives brief descriptions, Capacities, etc. of all Sturtevant Products GENERAL APPLICATIONS AIR CONDITIONING 1,2.3, 4. 5. 6. 14.20.25. 26. 28. 34. 38, 40, 42. 46. 52 OUST AND FUME REMOVAL 6. 7. 8. 9. 10. 11. 12. 13. 16. 20. 22. 26. 27. 40. 47. 48, 49. 50. 51 HEATING 6. 20. 25, 26. 28. 35. 36. 37. 38. 44. 45. 52 INDUSTRIAL DRYING 8. 16. 20. 23. 25. 26. 27. 37. 38.40 STURTEVANT EQUIPMENT INDEX TRADE NAME OR DESIGN NO. 1 Air Blenders...................................................... 2 3 4 5 6 Blowers, Ventilating........................................... "Rexvane Vent Sets" 7 "Big Midget" 8 "Steel Pressure" 9 10 Compressors. Centrifugal Design 7 II Design 9 12 Design 1 13 Design 14 14 Cooling Coils (Extended Surface) Water and 15 Sturtevant 16 17 "Planovane," Des. 3 18 19 20 21 Engine Cooler 22 --Fume and Dust RemovaL Materials Handling.. "Planovane," Des. 3 23 24 25 26 27 28 --High Speed. Heating and Ventilating............. "Silentvane," Des. 8 CAT. NO. 425-2 400-9 29I-2A 408-2 458 461 432-1 410-3 400-9 271-4 457 955 Z' Air System Equipment Fans and Blowers General Catalog No. 500 gives brief description, Capacities, etc. of all Sturtevant Products GENERAL APPLICATIONS STURTEVANT EQUIPMENT INDEX TRADE NAME OR DESIGN NO. MECHANICAL DRAFT 29 '--Mechanical Draft, Duplex type (Combined Forced and Induced)..................................... Duplex 8. II. 12. 13. 20. 27. 29. 30. 30 --Mechanical Draft. Low Speed. Induced Draft. 31. 32. 33. 40. 43. 52 Abrasion-Reaistant S.P.I.D.. Des. 2 31 --Mechanical Draft, Medium 6peed. Large Volume, Forced and Induced........................ M.V.M.D.. Des. 6 32 --Mechanical Draft, High Speed. Forced Draft... T V.F.D.. Des. 9 PNEUMATIC CONVEYING 33 --Mechanical Draft, High Speed, Induced Draft. T.V.I.D.. Des. 2 34 --Theatre Ventilating........................................ Theatre Fans 8.9. 10. M. 12. 13. 17.22.39. 35 Heaters. Unit. Directional How lype for Wall 40 and ceiling mounting...................................... "Speed Heater" 36 Heaters, Unit. Downblast type, for ceiling mounting........................................................ "Downblast" PRIME MOVERS 37 Heaters. Unit. Large Capacity, (or door. wall. ceiling mounting............................................. Multivane 40. 43 38 Heating Coils (Extended surlace)........................ Sturtevant 39 Melt-Recovery Units (Welding)........................ Sturtevant 40 Motors. Electric................................................. Sturtevant 41 Roof Ventilators................................................ "Roofvane" VACUUM CLEANING 42 Surface Dehumidifiers........................................ 43 1 urbtnes. Steam, Helical F low 1 ype.................. Sturtevant II. 12. 16. 40. 47. 48. 49. 50 44 Unit Ventilators. Schoolroom Type.................... Sturtevant 45 Unit Ventilators. Auditorium 1 ype.................... Sturtevant - 46 Ventilating Sets, Direct Connected Motor........... "Rexvane" Vent Sets VENTILATING 47 Vacuum Cleaners, Portable................................ "Vortex" 48 Vacuum Cleaners, Portable Furnace lype........... "Vortex" 6. 19. 20. 21. 24. 25. 26. 28. 49 Vacuum Cleaning Systems. Commercial Buildings Sturtevant 40.41.44. 45.46 50 Vacuum Cleaning Systems. Industrial................. Sturtevant 31 Vacuum Cleaner Attachments............................ Sturtevant 52 Vane Control (Fan)............................................ Sturtevant CAT. NO. 436 447 409 448 445 424-1 396-9 454 452 462 438-1 433-1 422 426 377-1 S377-I 406 413-2 373-6 397-2 368-3 387-1 446 Extended Surface (38) Filter Washer (5) 956 Electric Motor (40) Vertex Vacuum Cleaner (47) Air System Equipment Fans and Blowers B. F. STURTEVANT COMPANY PUBLIC BUILDING HEATING AND VENTILATING Selection of a System: Many standards have been set up for the temperature re quired for comfort, and the fresh air required for proper ventilation and sani tation. No definite standard, however, can be set which will apply to and solve all heating and ventilating problems. The standard of ventilation for a given project is controlled largely by its location; more ventilation in congested areas; less venti lation in suburban districts. Other con siderations are:--the purpose for which the building is used; the number of oc cupants in relation ito floor space; and the amount of money available in the budget. Apparatus'. The foundation of Sturtevant's business is heating and ventilating ap paratus and Sturtevant shops produce practically all the mechanical equipment necessary for a modern and efficient heat ing and ventilating system including supply and exhaust fans, blast extended surface heaters, unit ventilators, air blenders, air washers and humidifiers, roof ventilators and electric motors. Museum of Art, Baltimore, Md. Weequahic II. S.. Newark, N. J. INDUSTRIAL AIR CONDITIONING Air can be conditioned inside manu facturing areas, packaging rooms and storage vaults to provide the exact atmos pheric conditions desired, so rendering pro ducer and manufacturer independent of outside weather. This is accomplished either by. means' of a complete system embodying mechanical refrigeration or by evaporative cooling and humidifying. Air conditioning, employing mechanical cool ing and dehumidifying, permits weathersensitive products to be manufactured, packaged, and stored under ideal indoor conditions which can be properly regulated for the type of materials handled, and uni formly maintained regardless of outside weather. Such mechanical refrigeration gives absolute control of both temperature and relative humidity simultaneously. Evaporative Cooling is' a less expensive method, and is particularly applicable in certain sections of the country where a wide spread exists between the inside dry bulb temperature and the outside wet bulb temperature. 957 Efficient production in candy plant Quality controlled in dye plant s' Air Conditioning Ccn teal Systems B. F. STURTEVANT COMPANY Division of Westinghouse Electric Hyde Park, Boston, Mass. Offices and Contractors in'All Principal Cities The compressor is, of course, the heart of the air conditioning system. In large measure, the users satisfaction rests upon its design, its-construction, its size, its efficiency, its dependability. The following facts about Westinghouse Hermetically-Sealed Freon-12 Compressors are, accordingly, presented herewith for your information: The basic design was established over 20 years ago. Thousands of successful installations have proved its dependability. ' Shaft seals have been eliminated through the hermetically-sealed design. ' As a result, leaks through shaft seals, most common cause of refrigerant loss and system failure, are unknown with Westinghouse compressors. .. Belts, pulleys and couplings do not exist in this compressor. These are items which require frequent adjustment and replacement. Their elimination greatly y reduces maintenance time and expense. Direct drive conserves power. Power losses common to belt-driven machines ' are eliminated. ' . ' ., . Sealed-in mechanism is protected from rust, dirt and corrosion. Pressure lubricated, it gives years of trouble-free service. Yet the entire mechanism is readily accessible for service when needed. . Compact size and light weight are important when planning equipment installation. These are inherent advantages of the hermetically-sealed design. Flexible Operation is made possible by the application of a variable capacity accessory which loads and unloads one or more cylinders of the compressor as cooling requirements,fluctuate. Installation in unveiitilated spaces is practical with the Westinghouse Com pressor because the driving motor is refrigerant-cooled. 'Thus otherwise waste space can be effectively used for equipment. 958 Westinghouse Electric Air Conditioning Cert tral Systems Westinghouse Hermetically-Sealed Compressor "Aquamiser" Evaporative Condensers. Where water is expensive or its use restricted, the Aquamiser accomplishes effective condensing of the refrigerant at a saving in water consumption of as much as 95 per cent. Available in a wide range of sizes. Air Handling Units. Two types are supplied--a hori zontal type for ceiling suspension, and a vertical type for floor installation. Each embodies quiet blower-type fans, ..and provides facilities for the installation of required cooling or heating coils, filters and humidifier sprays. Heat-Transfer Surfaces. Direct-expansion coils with patented refrigerant distributor; chilled water coils; steam and hot water coils are available in a great many sizes for all types of systems. The Westinghouse Unitaire is a self-contained air conditioning plant incorporating the Hermetically-Sealed Compressor. Within-the-space and central-plant types in sizes from 2 to 25 hp. Water-Cooled Condensers. Where sufficient water is available, the water-cooled condenser is economical and efficient. Sizes to match the Westinghouse Compressor for varying requirements. The Westinghouse Precipitron.* Where complete air cleanliness is desired, the PRECIPITRON offers the most effective possible method of obtaining it. Sizes fit every requirement. . *Trade-mark registered in U. S. A. Water-Chilling Units. For the chilling of water for distribution to a number of cooling coils, and for use as process liquid coolers, these efficient water-chilling units range in size from 5 ton to 100 ton capacity. The Westinghouse . Unitaire Water-Cooled Condensers - . 959 The Westinghouse Precipitron* WaterChilling Units Air Conditioning Central Systems York Corporation York, Pennsylvania ' Factory Branches and Distributor Engineering and Sales Offices throughout the World. ' Air Conditioning and Refrigeration for maintaining proper atmos pheric conditions for industrial processes or comfort requirements. Installations of unit and central systems in a complete range of capacities and types for every design requirement. York Turbo Compressor York V- W Condensing Unit York Sectional Economizer Yorkaire Unit Air Conditioner Condensing and Water Cooling Systems--Centrifugal brine and water cooling systems available over wide range of capacities up to 1500 tons refrigeration, steam turbine or motor drive. . Self-contained dynamically balanced, non-vibrating V/W type reciprocating compressors available in capacities up to 350 tons refrigeration in a single unit, with water cooled or economizer type condensers. Efficient automatic capacity reduction available for economical operation at reduced load. The York Economizer--A combined forced-draft cooling tower and refrigerant condenser, is available for instal lations where prohibitive water costs or inadequate drainage facilities preclude the use of a water cooled condenser. Standard factory constructed and built-up units may be used singly or in multiple for applications of any specified capacity. Ecpnomizers for use with Freon as the refrigerant are furnished, as standard, with a liquid sub-cooling coil. Economizers also designed for cooling of quench oil and other liquid coolants. Air Conditioning Units: A complete line of finned coil, dry coil, wetted surface and spray type sectional air con-, ditioners for horizontal or vertical applications, designed to facilitate installation and the distribution of air. -Standard units can be equipped with by-pass feature and arranged for cooling and dehumidifying, heating and humidifying, for year-round processing. Yorkaire Unit Air Conditioner--A compact, self-con tained model occupying but 21 x 42 inches of floor space and requiring only water, drain and electrical connections to operate. Special features provide utmost flexibility to meet varying conditions. Temperature dial control pro vides both automatic and manual temperature control. Air volume and motion may also be adjusted by a special control and the directional grille provides directed air flow--up, down or from side to side. May be used with ducts if desired'. . Yorkaire Conditioners are ruggedly built, quiet in oper ation, equipped with standard fan and compressor motors for AC or DC. * Dehumidifiers--For central station systems where a large volume of air is to be handled and where control of humidity is an essential requirement, the Yoik dehumidi fier is especially applicable. Construction features in sure a minimum space demand and maximum per formance conditions. Standard washers are available in a full range of capacities for industrial installation. Air Conditioning Automatic Equipment; Heating Systems Let the pup be furnocemon THE BRYANT HEATER COMPANY 17825 St. Clair Avenue - - - Cleveland, Ohio Engineering, Sales and Installation information on Bryant Equipment available through Bryant Distributors, Dealers and Gas Companies in principal cities. Bryant Gas designed boilers include tubular cast iron sections, ribbed lower tubes, large steam liberating areas, all heating surfaces readily accessible for cleaning. Insulated metal jacketed covers and Bryant gas controls. Com plete range of AGA inputs from 45,000 to 3,996,000 Btu/hr for steam and hot water heating systems, volume water heating and industrial process. . Bryant Vertical Winter Air Condi tioners complete with blowers, humidi fier and filters are compactly designed for small housing, office and industrial use. Bryant tubular cast iron section design and quality controls are standard equipment. Capacities range from 55.000 to 115,000 Btu/hr AGA inputs. Complete line of forced Warm Air Gas-Fired equipment from 60,000 to 750.000 Btu/hr AGA inputs. Efficient cast iron heating sections of vertical tubular construction and large capacity blowers are featured. Humidifiers, filters and Bryant Automatic controls are standard equipment. Bryant suspended type Gas-Fired Unit Heaters available in five sizes ranging from 65,000 to 255,000 Btu/hr AGA inputs. Efficient heat exchange of staggered vertical tube construction. Available in both cast iron combustion chamber, alloy steel tube and all steel types. Quick, clean, efficient heat for all types of industrial and commercial space. Flexible, automatic control and . large volume air circulation produce ideal space heating results. Bryant Dehumidi fiers with rotary silica gel drum, is completely automatic in operation Suspended Type C'as-Fired Unit Heater and finds application for exact humidity con trol in industrial proc essing, comfort air con ditioning and the drying and storing of hygro scopic materials. They are available iii three sizes, 800, 1300 and 2900 cfm. Standard units are reactivated by gas. Indirect units arranged for use with high pressure steam coils or electric strip heaters arc available. See your local Bryant Distributor or write for complete details and specifications.' Dehumidifier 961-. Forced Warm Air Gas-Fired Equipment Air Conditioning Automatic Heating Air Control American Foundry and Furnace Co. Sales Offices in Principal Cities ' P. O. Box 904, Bloomington, 111. AIR CONTROLLING SPECIALTIES KD Grille and Fire Damper At the right is shown a Type KD Grille and Fire Damper consisting of a wire grille, with an angle iron frame and eight inch steel sleeve, and a ball bearing louver damper, with pull chain and two fusible links. The steel sleeve is made to fit the unit into a wall opening. The chain oper ator works through two pulleys and is held in place by a claw on the damper frame. The fusible links melt at 160 deg., thus allowing the damper to close by its own weight in case of fire. F-12 Louver Damper At the left is shown a Type F-12 Louver Damper. These* dampers are made on order to fit any size opening. Blades are 16 gauge steel, frames are 2 in. x H In. x y$ in. channel Ball bearings are standard, with steel trunnion bearings optional. Motor, linkage and bracket shown are not standard but may be ordered as an extra. S-454-F Radio Range Stormproof Louver Combination Consists of a galvanized iron frame with 26-gauge galvanized iron stationary horizontal stormproof louver blades, riveted securely to outside frame and all built into outside wall (fits 8-in. thick wall). Apron extends oyer sill. Back of stormproof louver is a No. 16 mesh screen. _ Back of screen is a multiple-blade, ball bearing louver damper (similar to F-12 but with off-center axle) to control volume of air admitted. Louver damper blades of 16-gauge steel, galvanized. Frame of 2 x H x galvanized channel iron. Dampers can be automatically or manually controlled. Blades all work in unison. FL-Aluminum Automatic Fan Outlet Louver These louvers are for use where the air from a fan discharges into atmosphere arid the velocity of the discharged air is less than 2000 fpm. Aluminum blades, working in unison, open from fan pressure and close automatically when fan is not in operation. Frames of angle iron drilled for fastening to wall, duct or penthouse. Standard finish of frame--black or gray enamel or prime coat. Regularly made in 14 sizes from 12 x 12 in. to 50 x 50 in. Special sizes on request. . 962 American Foundry and Furnace Co. Air Conditioning Automatic Heating Air Control HEAVY DUTY HORIZONTAL HEATERS CENTRAL PLANT SYSTEMS American SUPERFIN Heaters are made entirely of cast iron and designed for use with blower, air filters, humidifier, etc., in Central-Plant Winter Air Conditioning Systems. 1 ' Fireboxes and top arches are finned heavily to provide maximum durability and furnish largest possible heating surfaces. Design is such that all air is forced over hottest surfaces of the heaters at all times. Finned, pear-shaped radiators', streamlined, add enor mously to the radiating surface of the heaters, thus adding to their efficiency. Capacities range from 600,000 to 1,300,000 Btu per single unit. UNIT HEATER SYSTEMS American Gas or Oil Fired Unit Heaters have been de signed for use in commercial and industrial applications. These units have the multiple blowers underneath the heat ing section. Air is drawn into the heater at the floor line, then passes over the heater, and may either re-enter the room from the top of the hea.ter or at the floor line on the opposite side of the heater. '-Heater section is made entirely of cast iron and is designed to use either oil or gas as a fuel. Single units have from 750,000 to 3,500,000 Btu at the outlets. . SUPERIOR BLOWERS At the right is shown a standard Superior Blower. Superior blowers are all that their name implies. Rugged design, quiet operation of mechanical parts, freedom from vibration, have been stressed throughout the construction of the entire line. Made in wheel sizes ranging from 10 to 65 in., inclusive, having wheel diameters of corresponding values at 5-in. intervals, with 12 and 18-in. sizes in addition. Each size blower is available in single or double width, single or double inlet, any discharge arrangement. Deliveries range from 800 to 105,000 c.f.m., with uniform capacity ranges between. DOMESTIC HEATING EQUIPMENT June-A ire Cot Fired Made in sizes 72,000 to 416,000 Btu at the bonnet. < June-Aire Oil Fired Made in sizes 130,000 to 335,000 Btu at the bonnet. 963 June-Aire Oil Fired Capacity of 115,000 Btu at. bonnet. June-Aire Vertical Gas Fired Capacity of 60,000 Btu at bonnet.' Air Conditioning Automatic Equipment Heavy Duty Furnaces Campbell Heating Company 31st and Dean, Des Moines, Iowa SUMMER and WINTER AIR CONDITIONING Industrial, Commercial--Institutions, Residences Campbell Heater in factory of National Mfg. Stamping Co.. Des Moines, Iowa The Campbell Heater shown above is installed in a two-story factory building 80 x 120 ft. with 12 ft. ceiling height on each floor. There are no ducts--this heater sends heat to all parts of the building without ducts. On a zero day thermometers near .four corners of the first floor varied only from 59 to 62 deg.--the north west corner was 60 deg. When warm air is desired to remote rooms it can be provided by a properly designed duct system. . This heating performance was accomplished in spite of the fact that the heater is in the south east corner of the building. Heated air traveling to the north end of the room must overcome the obstruction to air flow caused by the timbers above--the air must flow across the timbers, not with them. . In this installation the heater rests upon the floor of the room to be heated. Where floor space is limited and valuable the blower can be mounted on top of the heater or put under it by raising the heater, provided the ceiling, height is sufficient. Five Advantages of Campbell Heaters . 1. Easy to Install--In most cases the Campbell Heater can be put into operation within 72 hours after delivery. 2. Especially Adaptable to Ductless Convection Heating--Elimi- * nation of ducts reduces cost in heating a single large room.' 3. Compact in Design--Over-all dimensions can be adapted to meet . , any reasonable limitations of floor space or ceiling height. 4. Efficient with any Type of Fuel--Especially adaptable to stoker . firing, but operates equally well with fuel oil or gas. 5. Low in Cost--Because of standardized design and efficient manu facturing methods, Campbell Heaters are low in cost. Campbell Heaters are guaranteed to deliver full rated capacity. 964 Campbell Healing Company Air Conditioning Automatic Equipment Heavy Duty Furnaces CAMPBELL "WINTER-CHASER" AIR CONDITIONING SYSTEM The Campbell "Winter-Chaser" System provides all the essentials of winter air conditioning: Simultaneous control of temperature, humidity, air circulation and air : cleanliness, besides providing fresh air for ventilation, quick heating, flexibility; and a summer cooling effect. Campbell equipment is built of the best materials obtainable, and, has been developed through over sixty years of experience. The system is designed by competent experienced engineers and installed by experienced mechanics. It is guaran teed as to results and for 10 years as to durability. Advantages of Campbell "Winter-Chaser" Design Compact design, requiring minimum space--the heater can be placed readily in any ordinary boiler or furnace room. Efficient radiating surface--permits an immense amount of radiating surface in a small space. Ratio of prime radiating surface to grate area is more than 30 to 1. This produces very low flue gas tempera ture with consequent high efficiency. Vertical self-cleaning radiating sur faces constitute most of the heating sur face--hence are not insulated with soot and ashes. Vertical air-warming tubes com pletely surround the fire, subjecting greater prime heating surface to direct contact with the fire--less liable to be overheated. Extra large combustion space above grate permits smoke and air to mix and burn before striking heating surface--less unburned gases escape up the chimney. Long return smoke travel--the tubes form a dividing wall each side of the fire, separated in the back to let smoke pass through behind the tubes and to the front of heater. This assures long contact with heating surfaces. Two convenient cleanouts permit easy cleaning of the smoke passages with out putting out the fire. Basement heating on the same level as the heater, is solved by this Campbell System. Entire capacity of heater can be forced into the basement and thus heat a large room in a few minutes. Furnace Number Sq. Ft. Grate Heating Surface For Building Heat Loss Btu Maximum Capacity Btu Blower CFM Size Motor 8075 7/2 280 483.000 725.000 8850 y. 8100 10 320 596.000 893.000 10900 1 8125 8150 I2*/j 15 360 440 720.000 850.000 1.080.000 1.275.000 13200 15600 2I'/t 8175 l7'/2 480 960.000 1.440.000 17500 2 8200 20 600 1.150.000 1.725.000 21100 2 8250 25 750 1.440.000 2.160.000 26400 3 Unit includes furnace, casing, blower, motor. V-fiat drive. 965 Dimensions Casing 75 x 80- 88* high 75 x 93-- 96* " 75x105- 96* M 75x 118-102* " 75x 130-102* " 94x137--120* " 94x157--120* " Addnl. Space for Approx. Shipping Weight . BIowct 54* 4500 60* 5500 66* 6500 66* 72* 76* 7500 9000 10000 76* 12000 Air Conditioning Automatic Equipment; Heating and Cooling CHRYSLER 0 AIKTIiMP A1RTEMP DIVISION OF CHRYSLER CORPORATION, DAYTON, OHIO "PACKAGED" AIR CONDITIONERS AVAILABLE IN 3 and 5 H. P. COMPLETE--Cools, dehumidifies, filters and circu lates the air. Free air discharge or duct distri bution. Heating coil for year 'round service, optional. COMPACT--Everything enclosed in a rust-- resistant "Bonderized" cabinet of modern design with chrome hardware and trim. Occupies only 4.7 sq ft of floor space. . EASILY, QUICKLY INSTALLED--Tested and completely assembled at the factory. Needs only three connections, electricity, water and drain. SEALED RADIAL COMPRESSOR--All moving parts are balanced for quiet operation without vibration. Compressor assembly suspended from a ' single rubber mounting. ECONOMICAL OPERATION -- Full pressure lubrication and "Superfinishing" of vital moving parts assures long life with efficient operation. FLEXIBLE--Airtemp "Packaged" Air Conditioners can be installed singly or in multiple to meet almost any requirements. Can easily be moved at any ' time. CHRYSLER AIRTEMP RADIAL CONDENSING UNITS AVAILABLE IN 10 TO 75 HORSEPOWER CAPACITIES - This heavy-duty Radial Condensing Unit for use with Freon is especially ' adapted for refrigeration, for in dustrial processes or air conditioning. Airtemp radial compressors are directly connected and have force- feed lubrication. The automatic capacity-reduction device gives high operating efficiency. Light in weight and economical to operate, these compressors are shipped ready to run. They are especially easy to install since vibration is practically eliminated and no special founda tions are necessary. - AUTOMATIC UNLOADER The automatic cylinder unloading device permits. starting the com pressor under no load and keeps the compressor automatically adjusted to varying loads with no stopping and starting during operation. . AUTOMATIC CAPAC ITY REGULATION UNLOADED START ING DIRECT CONNECTED SIMPLIFIED INSTAL LATION 966 COMPACT DESIGN PRACTICALLY NO VIBRATION NO SPECIAL FOUN DATIONS NEEDED INTERCHANGEABLE PARTS Air Conditioning Heating CHRYSLER AIRTEMP VAPORIZING OIL-BURNING AUTOMATIC FURNACE Models for forced-air--52,000 Btu output -- gravity -- 45,000 Btu output. Sure-Draft fan assures highest overall efficien cy. Bonderized and' insulated jacket. Approved for closet installation, Underwriters' Lab oratories, Inc. OIL-FIRED AUTOMATIC FURNACE Heats, humidifies, filters and circulates the air. Five models, from 70,000 to 160,000 Btu out put. "Bonderized" and insu lated jacket. Metal combustion chamber, seam-welded firebox of copper-bearing steel; large, slow- speed, rubber-mounted fan. Air temp conversion oil burners on all models. GAS-FIRED AUTOMATIC FURNACE Heats, humidifies, filters and circulates the air. Steel models from 70,000 to 160,000 Btu output. Cast-iron models for 50,000 and 75,000 Btu output. "Bonderized" and . insulated jacket. The Airtemp "Silent Flame" Gas Burner starts, stops and operates quietly, has many exclusive features--no popping, . or flash-backs. Approved, A.C.A. Laboratories. PERCOLATOR BOILERS--OIL OR GAS-FIRED , Two oil-fired models 400 and 600 EDR '(steam). Two gas- fired models 400 and 600 EDR (steam). Fire chamber sur rounded with water on all sides and bottom. High efficiency and faster heating result from "percolator" principle. Steam or hot water. "Bonderized" and insulated jacket. COAL FIRED FURNACES, FORCED-AIR GRAVITY Forced-air models, steel. Sizes from 105,000 to 130,000 Btu at Bonnet. Oversized blower motor mounted in rubber, has auto- matic overload and low-voltage protection. Gravity models,. steel--sizes from 70,000 to 90,000 Btu at register. COMBINATION HEATING AND COOLING FOR THE HOME Combination of a 3 hp Chrysler Airtemp "Packaged''.Air Con ditioner and any of the larger Chrysler Airtemp automatic fur naces. The same blower, filters and ducts of the automatic heat ing system are employed for cooling in the summer. STOKERS Domestic, available in both hop per and bin-feed models for an thracite or bituminous coal for burning 15 to 60 lb per hour. Chrysler Airtemp Stokers have the famous hydraulic transmis sion. . MODEL B-10 AND C-I0--OIL BURNERS A conventional pressure-atomiz ing oil burner, 1.35 to 4.5-gallons No. 3 furnace oil per hour. All Airtemp Oil Burners are approved by Underwriters' Lab oratories, Inc., and bear the seal of the Official Inspection Agency of the Oil Burner Industry as evidencing compliance with com mercial Standard CS75-39, as is sued by the National Bureau* of Standards of the U. S. Depart ment of Commerce. 967 Air Conditioning Automatic Equipment; Direct-Fired Units, Unit Heaters Lee Engineering Company Union National Bank Bldg., Youngstown, Ohio LEE DIRECT WARM AIR HEATING The Lee System of warm air heating generally costs less to install than steam or hot water; utilizes fuel with a high degree of efficiency; distributes the heat exactly where needed; responds promptly without lag; requires little or no maintenance; and needs no licensed attendant. Heaters for use with the Lee System are made in the four types illustrated and described briefly below. BRICK-SET TUBULAR HEATER For use with central heating system in connection with duct distribution. Single heater capacities from 2,800,000 Btu per hour to 8,000,000 Btu per hour. Two heaters, installed as a battery serving as one unit, provide capacities over 10,000,000 Btu per hour. Brick Set Tubular Heater STEEL ENCASED TUBULAR HEATER For use with central heating systems in connection with duct distribution over a capacity range of from 2,000,000 Btu per hour to. 6,000,000 Btu per hour, , Heater may be installed in heated area without en closure, requires no foundation, and may be moved from one location to another by taking unit apart and reassembling. TUBULAR UNIT HEATER For use either as a central system in connection with duct distribution or with adjustable outlet nozzles as a unit heater. Capacity range from 2.000,000 Btu to 6,000,000 Btu per hour. In sizes up to 4,000,000 Btu heater is shipped as a completely assembled unit with all but mechanical equipment, refractory lining and controls in place. Heaters require no foundation and are equipped with crane hooks so that they may be moved from one location to another. - s Steel Encased Tubular Heater Tubular Unit Heater SHELL UNIT HEATER For use with or without distributing duct system. Heaters have capacity range of from 400,000 Btu to 2,000,000 Btu per hour. Available for either stoker or hand firing. All units are shipped completely as sembled, wired and ready for operation. Stoker-fired units are shipped assembled with all parts in place ex cept mechanical equipment, refractory lining and con trols. Available in both hand and stoker fired models. Shell Unit Healer For further information write for Catalog HV-44. Air Conditioning . Branches and Distributers he Me/er Furnace Company Albuquerque. N. M. ' Chicago, III. Columbus, o. Peoria. Illinois Des Moines. Ia. Florence. S. C. Green Bay, Wis. Manufacturers of Heating and Air Kansas City, Mo. New York. N. Y. Conditioning Equipment for Coal, Gas and Oil Burning Omaha. Nebr. Philadelphia, Pa. Pittsburgh, Pa. WEIR and MEYER Steel Warm-Air Furnaces, of welded-and-riveted gas-tight construction, have a 60 year reputation for efficiency, dependability and durability. Service in hundreds of military establishments both here and abroad has again attested to their satisfactory performance. They are available for small and large requirements and for all fuels in a wide variety of firing applications. . U Series Gravity The U SERIES WEIR Hand-Fired Coal Furnace embodies a new construction principle (patent applied for) which, when com bined with its other time-tested Weir features, provides an outstanding heater. The gravity furnace, as shown on the left, ranges in register capacity from 50,000 to 170,0(X) Btu per hour. The rectangular-cased forced-air furnace, shown on the right, ranges from ` 50,000 to 250,000 Btu per hour output at the register. This series may be stoker-fired, though other Weir stoker-designed furnaces are available. U Series F-A Heavy Duty.S8-R WEIR Heavy-Duty Furnaces, consisting of the R Series on the left and the 500 Series-on the right, are ideal for indus trial and commercial service and for schools^ churches and other large spaces. Capacities from 300,000 to 1,500,000 Btu per hour. Designed only for forcedair circulation. Suitable for firing with coal by hand or stoker, with gas or with oil. Oil Fired A-100-M . Heavy Duly 644B The WEIR Oil-Fired Air Conditioner does a complete job of winter air conditioning. Designed for oil fuel and forced circulation. Completely self-contained in low compact casing enclosing burner and blower as well as heater and all controls, yet with everything easily accessible. The MEYER Gas-Fired Air Conditioner automatically provides completely controlled winter air conditioning. Efficient performance, compact design, modern appearance. Heavy gauge welded steel heating element; die-formed casing. A.G.A. approved. Gas Fired F-10 For any warm air heating or drying problem employing the use of any fuel, call our nearest office or representative or write to the home office. 969 Air Conditioning Automatic Equipment; Fan Furnace Systems L. J. Mueller Furnace Co. Established 1857 . 2009 W. Oklahoma Ave., Milwaukee 7, Wis. Mueller Climatrol Gas-Fired Equipment Series "EPS" This winter air conditioner is available in three sizes, with A .G.A. input ratings from 90,000 to 180,000 Btu. Each size is avail able with various size blowers in accordance with individual air delivery re quirements. Series "SHP" Series "CVP" Winter air conditioner. May An all-cast-iron winter air be installed in basement or " conditioner for basement utility room. Available in . or utility room installa three sizes, with A.G.A. in tion. Furnished in one put ratings from 60,000 to size, with A.G.A. input 100,000 Btu per hour. Pro rating of 100,000 Btu per vides wide range of air hour. Adjustable motor deliveries to meet specific sheave permits variation needs. in air deliveries. L. J. Mueller Furnace Co. Air Conditioning Automatic Equipment; Fan Furnace Systems Mueller Climatrol Oil-Fired and Coal-Fired Units Series "50" Oil-fired winter air con ditioner. Available with Mueller pressure atomiz ing, or vaporizing burner. Three sizes, 100,000 to 225,000 Btu. Series "OVP" Oil-fired winter air con ditioner. Equipped with Mueller Vaporizing Oil Burn er. One size, with maxi mum capacity of 80,000 Btu at bonnet. Series "OHP" Horizontal type oil-fired winter air conditioner. Equipped with Mueller vaporizing burner. One size, 80,000 maximum at bonnet. Series "FB' Cast-iron, coal-fired winter air conditioner. Six sizes, with capaci ties at register from 69,000 to 199,000 Btu. Series "P-400" Steel, coal-fired winter air conditioner. 4 sizes, 20 in. to 27 in. drums, with capacities at register ranging from 79,000 to 141,500 Btu per hour. Series "AP" Cast-iron, coal-fired winterair conditioner. Six sizes, 20 in., to 33 in. firepots, with forced air capacities ranging from 93,000 to 269,000 Btu. ' Series "G" A gas-fired gravity unit for home applications. Made in two casing styles, i.e., square, as shown, and round. Furnished in two sizes, with A.G.A. input ratings of 90,000 and 135,000 Btu per hour. Gas Boiler Type "10" (shown) and "11" have A.G.A. ratings from 180 to 1,260 sq. ft. steam, and 290 to 2,015 sq..ft. hot water. Type "20" boilers from 630 to 6,300 sq. ft. steam, 1,010 to 10,080 sq. ft. hot water. 970 Unit Heater For large space-heating re quirements, and industrial applications. Units are available in 45 sizes, A.G.A. approved, from a 4-section unit with input of 180,000 Btu per hour, to the 48-sec tion size, with input of 2,160,000 Btu per hour. Series "WR" Cast-iron, coal-fired fur nace. Two styles, i.e., forced air and gravity. One size only. Forced air capacity, 72,000 Btu. Gravity, 42,000 Btu. . Stoker Furnace Winter air conditioner. Any stoker may be used. Cast-iron heating unit. Available in two sizes, , with capacities of 110,000 and 175,000 Btu. 971 Horizontal Tubular Adaptable for schools, churches and other large buildings. Three sizes, with capacity range from 1,188,000 to 1,390,000 Btu per hour. For gravity or forced air applications. - Air Conditioning Automatic Equipment Gas-fired Heating Systems PAYNE FURNACE COMPANY [Om of Drnier ladvttrht) BEVERLY HILLS, CALIFORNIA PflYflEHEHT OVER 30 YEARS OF LEADERSHIP W EVEOVTHIDG PAYNE FURNACE COMPANY has always speci alized in gas-fired furnaces. Eight salient points characterize the complete PAYNE "line": 1. 69 A.G.A.-approved styles and sizes. 2. Each unit fully vented. 3. Can use natural, manufactured or LP gas. 4. Adaptable to "Zone-Conditioning" (control by zones or rooms). 5. First-class materials; sound, advanced engi neering; rugged construction ; long life. 6. Compact, light-weight, attractive, modern designs. 7. Ample filter area in forced air models assures thorough air-cleansing. 8. No gas leakage. MODEL "AS" UNIT-TYPE WARM AIR FURNACE Gravity-type circulating unit for space-saving basement in stallation. Can be used as single unit or in multiples for zoned heating. Six standard sizes; A.G.A. input rating, 30,000 to 180,000 Btu's. Grey, metallized enamel finish. \ PAYNE "CB" COMMERCIAL BLOWER UNIT Compactly built commercial blower furnace for theatres, buildings and industrial plants, providing large volume of air at high velocity, with minimum fuel consumption. One-piece combustion chamber and radiator are of heavy gauge, die-formed steel, all-welded construction, preventing gas escape;.ideal "SPACESAVER" UNIT for high-pressure system. Entire radiation surface Horizontal, forced air heating is exposed to air-currents traveling at high velocity system for attic, subfloor or with rapid heat transfer from element to air stream. ceiling installation in basement "CB" Furnaces may be installed individually or in less homes, shops or industrial batteries to provide any capacity up to 1,680,000 plants. All-welded heating ele Btu input. Shipped completely assembled except' ment of heavy guage, die-formed for supports and controls. A.G.A.-approved with' steel. Two sizes: A.G.A. input limit control, current-breaking type, operating on rating, 75,000 to 100,000 Btu's. current failure valve and automatic pilot. 972 Payne Furnace Co. Air Conditioning Automatic Equipment Gas-fired Heating Systems PAYNE FLOOR FURNACE Heavy, cold-rolled, rounded edge steel grille, with wide margin for close floor-fit. {See other details at right, above.) CONSOLE HEATER Attractively finished to harmonize with any fur nishings or decorative scheme. PRVnEHEATFLOOR FURNACE (left) made in eight A.G.A.-ap over 30 Years of leadership proved sizes, shipped completely assem bled. Deep-drawing steel heat ing element, heavy gauge for both combustion chambers and radiators. Single burner is first-quality casting, pre cision-machined with venturi tube and adjustable primary air shutter. Inner casing is suspended to allow for con traction and expansion. A.G.A. Btu input ratings: 15,000 to 75,000. PAYNE DUPLEX REGIS TER FURNACE (right) in cludes all Floor Furnace fea tures, plus scientificallydesigned register head for heating two rooms or suites from both sides of wall. A.G.A. input ratings: 25,000 to 50,000 Btu's. PAYNE CONSOLE HEATER (left) Fullyvented, A.G.A.-approved heater for use with natural, manufactured or LP gas. Heavy-gauge heating element with special inner baffles for longer fire-travel and uniform heat distribution. Insulated air passages control cabinet temperature; undershield pro tects floor. Six sizes: Btu input rating, 15,000 to 60,000. DUPLEX FURNACE SENTRY FORCED AIR UNIT (right)--Compact forced air unit for basement less installations. Fits in any nook or corner. All-welded heating element of deep drawing steel. All moving parts mounted on rubber blocks. Four sizes with Btu input rating, 60,000 to 160,000. Designed for up-discharge only. (Inquire about the ZONEAIR Forced Air Unit for basement installations.) PAYNE "SENTRY" UNIT PAYNE "AA" VENT--Inner tube of aluminum is surrounded by outergalvanized casing with controlled air space between. Patented. Prevents condensation of water vapor in products of combustion as well as over-heating of outside casing. Quickly installed. Sizes: 3 in. to C in. PAYNE ZONE-CONDITIONING-- Time-tested PAYNE "Unit" heating, using two or more units, controlled by zones or individual rooms. Many advan tages over "central" heating. Write for special booklet. IMPORTANT--Complete catalog sheets and Specifications on these and other PAYNE Furnaces available on request. Please specify type, heating value and specific gravity of gas. 973 Air Conditioning Equipment' GjfaKWoodQ Industries, Inc. HEATING DIVISION 7924 Riopelle Street Detroit 11, Michigan GAS-FIRED TEMPERED-AIRE UNIT The heart of this efficient heating unit is the cast iron heat exchanger. Combustion takes place in the large firebox which has sufficient volume to prevent flame impingement. From the firebox, the products of combus tion pass upward, diverge, and enter the triangular-shaped vertical channelways which contain cast-in baffles to direct the gases laterally against the side' walls in their upward course. Durablecast iron was chosen for theconstruc- tion of the heat ex changer after consulta tions with Utility Engi neers. The corrugated firebox and overall de sign provide an inti mate contact for gases and air resulting in a high rate of heat transfer. The multiple jet gas burner provides a controlled Vshaped flame. Ab solutely silent in starting and stop ping. The control sys tem employs both a mechanical limit ' control and a gas actuated safety pilot for safe manual opera tion of the gas valve in the event of a . current outage. SERIES "M" OIL-FIRED BOILER BURNER UNITS \ The Gar Wood Series "M" (steam or water) boiler burner units are built to fill the,requirements of radiation systems of either the conventional or the new radiant type, or for use with indirect air condi tioning systems. They are of welded steel construction with horizontal fire tubes, have downdraft gas travel and are internally fired with the Gar Wood type "O" burner which is an integral part of the boiler unit. Models range from. 200,000 to 1,000,000 Btu/hr nozzle output. 974 Air Conditioning GfcxAWoOt# Industries, Inc. HEATING DIVISION 7924 Riopelle Street Detroit 11, Michigan OIL-FIRED TEMPERED-AIRE UNIT A high efficiency, direct fired, complete heating unit designed for home installation. The primary transfer of heat occurs in the large firebox which has its outlet at the bottom through which the hot gases pass into the economizer. Here the gases divide into long, thin slices within tubes. Each tube is swept at high velocity by cold return air which absorbs a maximum of heat from the economizer. - Integral burner and combustion chamber intermingles and ro tates oil and air for perfect combustion. Integrally built firebox-economizer unit. The teardrop shape removes the peak from the high temperature zone eliminating hot spots. All parts of the power unit are die formed and welded into a single unit. Rubber mounted. Quick-acting flash humidifier provides adequate humidity under short firing cycle conditions. Large air blower delivers a generous quantity of air against the friction of duct systems. DELUXE TEMPERED-AIRE WITH REMOVABLE, WASHABLE CLOTH FILTERS Consisting of a series of bags similar to vacuum cleaner sacks, the filters are made of a special woven fabrjc and have a tremendous filtering area. These collector screens may be lifted out and cleaned in the washing machine. They can be removed and put back in a few minutes by lifting and replacing the retaining frames. DELUXE Tempered-Aire models, either oil or gas fired, are double the width of standard vertical models. 975 Air Conditioning Unit Heaters and Coolers Airtherm Manufacturing Company 728 S. Spring Ave. St. Louis 10, Mo. THE ENGINEERED LINE OF UNIT HEATERS AIRTHERM STEAM UNIT HEATERS (Copper Coils) Air Conditioning Unit Heaters ELECTROMODE CORPORATION Div. American Foundry Equipment Co. iLECTROMODE '.iec&uc T'itiit 'rtyeotwa 430 So. Byrkit Street, Mishawaka, Indiana All-Electric Air Heaters Cast aluminum grids in electric heaters are a radically different innovation from the popular conception of electric heating units. Aluminum, a metal .of highest thermal conductivity, is cast on a tubular element. This process seals the heating element, preventing oxidation and deter ioration. The New AIRTHERM Direct-Fired SPACE HEATER HEATS LARGE AND SMALL PLANTS ECONOMICALLY! The new Airtherm Direct Fired Space Heater can be installed either with or without duct work. It is available as a floor unit (illustrated) or in horizontal or vertical suspension types. For gas or oil fuel supply. 650,000 to 1,950,000 Btu capacities. Airtherm Direct Fired Heaters give instant heat, when and where it is wanted, reflecting a saving in fuel costs. They are controlled automatically--require no maintenance. Horizontal Propeller Type Airtherm Steam Unit Heaters move warm air quickly over wide .areas into remote corners. They are controlled individually and give uniform heat throughout the room without waste of fuel. Wall or ceiling mounted to save floor space. Complete range of sizes--send for bul letin giving complete details. . Vertical Discharge 976- To the cleanliness, safety and convenience of Electromode Electric Unit Heaters, there are the further advantages of ease of installation, simplicity of control and economy. The 1.5 to 7.5 KW sizes are for either portable use or suspension mounting, the larger sizes for suspension mounting only. By means of thermostat, heat can be automatically controlled. For complete data, see Bulletin A5-U. - 1.5 KW to 7.5 KW Heaters 10 KW to 60 KW Heaters Model KW BTU CFM Approx. Shipping Weight Approx. Price AA-15 bAN-30 cBN-50 "CN-7i/2 1.5 5122 3 10245 5 17075 73- 25613 100 200 350 550 201b $30.00 401b 52.50 501b 64.00 801b 91.00 Heaters 1.5 KW and 3 KW are furnished with ON and OFF switch, 10 feet of heavy duty cord and plug. - Model AA-15 (1.5 KW) may be plugged into usual branch lighting circuit.--made for use on 115 volt circuits only. bAN-30 is for 115 V or 230 V,-- specify which. cBN-50 heater is furnished with switch but without cord or plug, 230 volts only, single or three phase. . dCN-7H furnished without switch, cord or plug. 230 volts only, single or three phase. Elements For Blast Coils and Air Ducts Electromode Finned Heater Elements are made for a wide range of heating applica tions. Engineering help is at your disposal. Bilt-in Home and Office Heaters The production of Portable and Bilt-in Wall Heaters, restricted during war, has been resumed and complete details in cluded in Bulletin 46-D. . For 230 or 460 volts--specify which voltage when ordering. Model 14-10 14-12 18-15 18-20 20-25 20-35 27-45 27-60 KW BTU CFM Approx. Shipping Weight Approx. Price 10 34150 12* 40980 800 800 100 lb 1001b $110.00 125.00 15 51225 1500 1801b 138.00 20 68300 1500 1801b 190.00 25 85375 1800 2001b 245.00 35 119525 1800 2001b 255.00 45 153675 4000 360 lb 380.00 60 204900 4000 3601b 390.00 "Models 14-10, 14-12, IS-15 are for single or 3 phase.--others only for 3 phase. ' Heaters are furnished with 460 single or 3-phase heater elements with 115 or 230 volt single phase motor. For 460 volt elements and motor, add 10 % to price. * Contactor A contactor is necessary on any unit above 5 KW capacity and on 3 phase service and direct current in order to provide opera tion of the safety switch and thermostat. Automatic thermostat and contactors are available for any size unit. 977 Air Conditioning Industrial Heating; Direct-Fired Heaters Drabo Corporation Air Conditioning Industrial Heating; Direct-Fired Heaters DRAVO CORPORATION HEATER DEPARTMENT Dravo Bldg., 300 Penn Avenue, PITTSBURGH 22, PA. Sales Offices in Principal Cities View of standard model as used for gas or oil or gas and oil in combination. Com bustion chamber is lined with plastic refractory material at factory, shipped ready for use. Fins, deflectors and cor rugation increase heat transfer surface, economizer tubes reduce the temperature of flue gases. Entire design job tested and proved for highest efficiency. Permanent savings in fuel consumption, cost of maintenance and cost of labor in operation are factors influencing favorable acceptance of Dravo Heaters. Conditions often demand speed of in stallation and curtailment in the use of critical materials. Dravo Heaters are shipped with refractory in place,. are installed by simply connecting to fuel and power supply and providing foundation breeching and vent stack, and their con struction represents a saving in critical metals of 30 to 40 per cent over con-' ventional steam plants with distributing systems. Each heater is complete and operated individually. A'heatirig system for any size structure may-be formed with a com bination of one or more heaters. Dravo Direct-Fired Heating Systems save man hours, money, transportation--all essential to the war effort. Dravo Direct-Fired Heaters are used for permanent installation and also often used to supply temporary heat in new construction or plant expansion. The exceptionally high heat transfer efficiency is the result of two fundamental design features--first, accurately control led combustion of fuel and air, and second, highly effective transfer of heat to air. Standard stock sizes are obtainable ranging from production of 600,000 to 4,000,000 Btu output per hour. Dravo Bulletin No. 509-A with detailed description mailed on request. Specification Data Sheets for any type or capacity are furnished on request. There are 47 Branch and Sales Offices strategically located to extend quick co operation on heating problems. Right. Hopper feed model, capacities 750,000 to 2,500,000 Btu output Per hour. Also available for bin-feed. Anthracite or Bituminous coal. COAL FIRED SERIES--the Dravo coal-fired, self-contained Heater is partic ularly adaptable in areas where coal is the cheap est or easiest fuel to obtain. Coal fired heaters may be converted to either gas or oil firing should conditions change. The entire series of Dravo Direct-Fired Heaters has the utmost flexibility; Enough applica- tions^jcombijiations, and adaptations are available: tov meet any set of reasonable conditions:; The same unique principle of .welded combustion"bhamber is employed. The entire series hafe the DRAVO non- clinkering air-cooled setting incorporated in the design. Available for either bitumi nous, anthracite or lignite coal; equipped with either hopper feed or bin-feed stoker, installed under either end of the heater. Other series also available 2.750,000 through 10,000,000 Btu per hour output. Overhead or underground duct systems may be used for air distribution. ' Specification Data-Sheets for any type or capacity are furnished on request. GAS-OIL COMBINATION . . . Floor Set. . . Top Discharge... Front Fired . . . Standard V-Belt Drive--This series of heaters is equipped to burn either Heavy or Light oil with alternate gas burner. Equipment consists of a complete, separate burner for each fuel, each burner having a com plete set of con trols. The con trols and wiring are so arranged that either burn er can be put in to operation by simply throwing a switch, and valves. . GAS . . . Floor Set. . . Top Discharge ... Front Fired . . . Standard V-Belt Drive--This series as well as all others is designed to deliver the maximum output per square foot of floor space occupied. Because of their unique design they fit into the heated space and are depend able and efficient. They readily lend themselves to a wide variety of applications, using either natural or manufactured gas. OIL, Floor Set, T3pJ)ischarge, Front Fired Standard V-Belt Drive--This series obtainable in light oil or heavy oil fired models in j^r Dravo Direct-Fired Heaters. EconoTny.b fuel consumption is *. the result of ' " careful over all designing and constant improve ment over many years. In summer they may be used for air circulation. * How much would an installation cost? We have a form called "Dravo Building Survey" that we furnish free on request. You give us the vital statistics on this form and we'll do the rest. Write for your copy. ' 978 979 I Air Conditioning Unit Heaters and Coolers FEDDERS-QUIGAN CORPORATION 85 Tonawanda St. . Buffalo, New York Fedders Series 15 Horizontal Unit Heaters with Streamline Copper Tubes and Fins Fedders UNIT HEATERS Horizontal Type COPPER TUBES AND FINS Fedders streamline tubes provide aerody namic efficiency and the ample-area saddle of the fins gives generous bonded metal-tometal contact between copper tubes and fins for high thermal efficiency. Handsome, rugged cabinets--complete relief of expansion stresses within the core as well as between core and cabinet--latest type broad blade fans provide large air volume, quiet operation and maxi mum efficiency. Large Btu capacity with low final temperatures assure ideal working conditions. Capacities, 100 to 1,000 EDR. Write for Bulletin 15C-3. Fedders DOWNBLOW UNIT HEATERS Used where requirements necessitate clear ance for material handling equipment, tall machinery and other conditions requiring piping to be kept out of the way and for spot locations such as over frequently opened shipping room doors. COPPER TUBES AND FINS Straight downblow or diffusion of heat is accomplished by adjustable directional out lets to fit conditions. Circular type for ceiling heights from 20 to 45 ft'. 800 to 1800. EDR capacities. Square models chiefly for medium ceiling heights of 15 to 25 ft. Write for Bulletin 12C-2. 980 Air Conditioning Unit Heaters and Coolers Grinnell Company, Inc. Heating, Industrial and Power Plant Piping, Fittings, Hangers, Valves, Pipe Bending, Welding, Piping Supplies, Etc. Executive Offices: Providence 1, R. I. National Distributors of Thermoflex Traps and Heating Specialties For data on other Grinnell Products, see pages 1112-1113, 1211 THE GRINNELL UNIT-HEATER Reg. U. S. Pat. Off. In addition to its patented Internal Cooling Leg Thermolier has many other desirable features including its Single Header U-Tube construction which compensates for ex pansion and contraction strains. Radiation is from brass-finned seamless copper U- tubes rolled into a cast iron tube sheet. Steam circulation and the removal of condensation in Thermolier are distinctly .different than is usual in unit heaters. The actual cooling effect of this construction is* equal to a run of more than 100 ft of ordinary, exterior cooling leg piping. Steam is delivered into Chamber "A" of the header and circulates from there through the pitched.U tubes, carrying its condensation with it into Chamber "B." By partition ing off the lower tube or tubes at the bottom of the Steam Supply Chamber "A" these tubes carry all condensation from Chamber *'B" into Drain Chamber "C." In passage of . this condensation through these tubes, the air from the fan is rapidly carrying off heat just as it does in the rest of the unit. The result is that these two bottom tubes form an efficient internal cooling leg, integral with the unit. Thermolier is available in 10 Models. Catalog will be sent on request, to Grinnell Company, Inc., 277 West Exchange Street, Providence 1, R. I., or to any branch office in principal cities listed on our page 1112. CAPACITIES 60 F Entering Air Temperature--2 Lb Steam Pressure Model j Nos. 021 D3I D37 D4I D44 Btu per Hour 35.600 48.700 f2.200 71,000 84,100 Equivalent Direct Radiation 143 203 259 295 350 Model Nos. D57 D66 D7I D91 Dill Btu per Hour 101.300 128.700 151.700 196.000 275,300 . Equivalent Direct Radiation 422 536 ' 632 . 817 1147 981 ' Air Conditioning cw, ILG Electric Ventilating Co. 2832 North Crawford Ave., Chicago, 111. Offices in 40 Principal Cities Horizontal Type Unit Heaters--have Self-Cooled Motor which counteracts coil heat--never "slowroasts." Two piece header for "balanced" steam, dis tribution--orifice bushings expand tubes uniformly in header plate. Fins are pressed into round tubes for permanent union--no brazing, soldering, or welding. Certified ratings. "One-Name-Plate" Guarantee. 40 capacities. Get Catalog No. 341. 11 n iiniii l :| 11 UllJlrtllllll i r' '"A'IcTVC MtOHaauuiuiili : "a- ">`innifuiiiiili Vertical Type (left)-- recommended for extreme ly high or extremely low ceilings. *"*.**'! it Textile Type (right)-- for use where lint, etc., ordinarily adheres to fin surfaces and dogs up the coils. 10 capacities. Low-Ceiling Type (right)-- has side steam connections which make.pps- sible an extreme ly compact in stallation in locations where head-room is at a premium. ILG Electric Unit Heaters STANDARD TYPE For instant, clean, safe, dependable heating. Coil is of black heat type which operates below 400 degrees. Protected patented automatic thermal cut-out and magnetic starter. Sizes, 5 KW to 48 KW. Get Bulletin No. 802. TYPE "HT" For installations re quiring a small volume of heat. Exceptionally efficient. Suitable for constant duty. Black heat type coil with in dividually interchange able elements.^ Auto matic rircuit breaker protects ILG Self-Cool ed Motor from over load. 1^'to 4 KW. ILG Cooling and Air Conditioning Units ` Ceiling type units for use singly or in multiple with remotely located refrigerating machine circulating direct expansion "Freon" or methyl chloride; or with cold water. For. cooling, dehumidifying and recirculating. Also combination units for both cooling and heating. Write for Catalog. For ILG Propeller and Centrifugal Fans, see pages 1060-1061. ' 082 Air Conditioning w bw." HASTINGS ff tf. MANUFACTURING COMPANY SINCE 1914 NEBRASKA New and Improved Self Contained Air Conditioning Units--for use with cold water. Capacities From 1 Ton to 20 Tons with Comparable Capacities for Heating. Models for Cooling Include Floor Type for Individual Rooms, Suspended Units and Central Plants for Duct Systems. Centrifugal Unit Heaters, Package and Utility Type Blowers for Heating and Ventilating. Central Plants--capacities from 3 tons to 24 tons. Air delivery from 1100 cfm to 10,000 cfm. All centra! plants are as sembled in sections to simplify instal lation. All models available with steam coils for combination heating and cooling. Suspended Models--capacities from 1 ton to 4 tons. Air delivery 585 cfm to 2200 cfm. Especially adaptable to in dividual rooms where duct system is undesirable. Completely self-contained with motor, coils, blower and filters housed in sturdy steel cabinet with attractive featherweave finishes. Floor Type Models--capacities from 1 ton to 3 tons. Designed for use in individual rooms. All models self-con tained with motor,-blower coil and filters housed in well designed metal cabinets attractively finished or available in base coat for finishing in special colors. Package Blowers--capacities 1000 cfm to 4000 cfm. All models equipped with filters arid available with or without fan controls. Cabinets of extra heavy steel construction with featherweave finish or with base .coat for finishing . in special colors. * Utility Blowers both single--twin mounted double inlet type--capacity from 800 cfm to 10,000 cfm. Available in any discharge arrangement and with or without motors. Single blowers available in "base type" which includes heavy angle frame for special cabinet construc tion when necessary. Unit Heaters--capacities from 76,800 to 155,000 Btu/hr. std. rating, air delivery 1165 cfm to 2100 cfm. Centrifugal type for use with steam or forced circulated hot water. Unusually quiet in operation-- highly efficient and easily adaptable to duct installation. Finished in attractive ' featherweave or base coat for special colors. . WRITE FOR CURRENT SPECIFICATION CATALOG 983 Air Conditioning Heating cons 2019 So. Hanley Rd., St. Louis 17, Mo. Manufacturers AIR CONDITIONING BLOWER UNITS--REFRIGERATION BLOWER UNITS AIR CONDITIONING COILS--HEATING COILS KENNARD Water Cooling and Heat ing Coils. Non-ferrous coils for cooling with cold water and for heating with hot water. KENNARD Direct Expansion Coils. For all refrigerants. A complete range of sizes to meet all Conditions and capacities. ization of coil the Kennard Way. Full coil, surface is utilized when air is drawn through coil. Units for brine, freon, am monia and methyl-chloride. 9 sizes basic capacity ratings 410 Btu's to 1521 Btu's per degree temperature difference. KENNARD Steam Coils. A complete range of copper steam heating coils. Can be furnished in non-freeze type with steam distributing tubes. KENNARD Floor and Ceiling Type Air Con ditioning Units. Ten sizes. Two to 35 tons cooling capacity range and 40,000 to 1,250,000 Btu's range in heating. Various arrangements of dis charge, filter box, motor drive. WRITE FOR COMPLETE INFORMATION 9S4 Air Conditioning Kramer Trenton Co. Manufacturers of HEATING, COOLING AND REFRIGERATION DEVICES Trenton, New Jersey Kramer THERMOBANK The completely auto matic refrigeration sys tem for temperatures below the frost line without the use of electric heaters, water spray or brine spray. Kramer Radial Unit Cooler Even air distri bution in all di rections. Low discharge velo city. High rel ative humidi ty. Oilless ball bearing motors. Maximum space econo? my. Pleasing appearance. Kramer "Coolmaster" Product Coolers An outstanding pro duct cooler designed to give positive re frigerant distribution and maximum per formance. Built-in heat exchanger. Ad justable louvers. Kramer Panel Type Unit Coolers Designed for applica tion where space is at a premium. Easily ac cessible for adjust ments and service without use of tools. All-copper evaporating coil. Built-in heat ex changer. Kramer Floor Type . Product Coolers Designed . for large cold storage instal lations. Capacities range from 3 to 10 tons. For all re frigerants. Top or front discharge. Kramer Fin-Tube Condensers Combined water-cooled condenser and liquid receiver. Kramer Unicon Self-contained, remote type air cooled condenser complete with fan. May be used as booster in combination with air or water cooled systems. Kramer Turbo-Fin Surface All-copper blast surface, for heat ing and cooling. Used for steam, water or direct expansion re frigerants. Air side and refrigerant side flow-disturbers for increased heat transfer. Fin-tube ratio designed for maximum latent heat re moval. Coil construction designed to allow thermal expansion. Electro-tin plate finish. Kramer Unit Heaters All-copper condens ing coil with fused metallical fin-tube bond. Positive compensation for thermal expansion. High discharge air velocity. Moderate final air tempera ture. Silent in oper ation. . 985 Air Conditioning Unit Heatera and Coolers McQuay, Inc. 1602 Broadway, N.E., Minneapolis, Minn. MANUFACTURERS OF AIR CONDITIONING EQUIPMENT ' Sales Offices in all Principal Cities Air Conditioners Air Conditioning Coils Blast Heating Coils Refrigeration Coils Convection Radiation Unit Heaters Unit Coolers proven THE EXCLUSIVE McQUAY RIPPLE-FIN COIL ASSEMBLY The McQuay Fin and Tube assembly in all Mc Quay coils and cores is one of the reasons McQuay products are considered "Tops in Over-All Efficien cy" by many heating and refrigeration authorities. Heat transfer efficiency primarily depends on three elements in coil construction. First, "Area of Con tact,Second, "Contact Pressure" and finally "Quality of Contact" between collar and tube. In McQuay coils all three necessary elements are found developed to their highest degree. The famous McQuay "Wide Fin Collar" plus Exclusive Hydraulic Expansion together with the polished sur face, secured by "spinning" the fin collar, truly provides the last word in Heat Transfer. Comfort Coolers Blower Coolers - (Suspended & Floor Type) Room Coolers . (Cabinet Type) Ice Cube Makers Icy-Flo Accumulators Zeropak Low Temp. Units jRIPPLE-FIN COIL McQUAY STANDARD CONVECTORS The Standard all purpose Convector has been designed to meet all heating requirements. They are available for free standing, partially recessed, fully recessed and wall mounting applications. All enclosures are constructed from high grade steel, properly reinforced to make a sturdy cabinet. The heating element is constructed of a series of round seam less copper tubes to which are attached die formed radiating fins, which are bonded to the tubes by an exclusive process. . We offer the services of our Engineering and design department to help solve your heating problems. . COMBINATION COOLING COIL WATER COIL MORE THAN 1,000,000 STANDARD COIL TYPES AND SIZES McQuay manufactures a complete line of Standard Coils for the Industry. ' Coils for Heating--1 to 10 rows deep using low or high pressure steam or hot water. Non-Freeze--(steam distributing tube) type coils 1 and 2 rows deep. v. Removable Plug--{cleanable tube) type coils 1 to 12 rows deep. Water Coils for Cooling--1 to 12 rows deep. . Direct Expansion Coils--for cooling 1 to 10 rows deep. Refrigeration Coils--all types and sizes. . Special Coils--of various materials furnished on order for special applications. 98G - McQuay, Inc. STANDARD UNIT HEATER CABINET TYPE UNIT HEATER COMFORT COOLER Air Conditioning Unit Heaters and Coolers UNIT HEATERS The Radial Unit Heater, an ex clusive McQuay development, is de signed to do what no other unit heater can do--namely, distribute heat over a semi-circular area. This Patented design, with the fins themselves acting as directional louvers, enables the radial heater to do the work of two or more conventional units. This naturally reduces instal lation costs, both from the standpoint of labor and material. In addition to Radial Unit Heaters, McQuay also manufactures the Stand ard, or horizontal propeller type, the Down Flow, the Cabinet, as well as large capacity blower types. , For long life, efficiency, and ifor eye appeal specify McQuay Unit Heaters. They are available in a wide range of sizes to meet all applications. DOWN FLOW UNIT HEATER BLOWER TYPE UNIT HEATER McQUAY COOLERS For Industrial Application Made in two types--one for use with water or brine; another for Freon or methyl chloride. Eight sizes in each type--all with 4-speed motors. BLOWER TYPE UNIT HEATER AIR CONDITIONERS--COLD WATER AND FREON TYPES For Industrial Application . Choice of recirculation of indoor air, entire intake of outside air, or a com bination of both. Cold water or brine used in one type; Freon or methyl chloride in another. Modern "sound isolated" construction assures quiet operation. Capacities to 6 tons. CENTRAL SYSTEM AIR CONDITIONING UNITS Suspended and floor types, cools, dehumidifies, filters, and circulates air in summer, heats, humidifies, filters and circulates air in winter. Extreme flexibility and accessibility "built-in." Cooling capacities from 5 to 50 tons in both Suspended and Floor Type. AIR CONDITIONER ( YEAR-ROUND I McQUAY ICY-FLO ACCUMULATORS The new practical "Storage-Battery" for refrigeration effect is now available for handling heavy loads of short duration. ACCUMULATOR 987 Air Conditioning Unit Heaters and Coolers Modine Manufacturing Company Heating and Air Conditioning Division General Offices: 17th and Holburn Sts., Racine, Wis. Factories at Racine, Wis. and La Porte, Ind. Branches in all Principal Cities MODINE UNIT HEATERS Front View Back View HORIZONTAL DELIVERY MODELS Condenser--Copper and copper alloy, inlet to outlet, for maximum resistance to internal and external corrosion. Pure copper fins are metallically bonded to round, seamless, heavy-gauge red brass tubes for permanent contact and to insure uninterrupted heat conduction from pri mary to secondary surface. Modinepatented expansion bend permits tubes to expand or contract individually as tem perature requires. All steam and con densate carrying passages are brazed into an integral pressure-resisting unit. Direct - Pipe - Suspension -- Modine patented feature permits suspending unit directly from supply line without additional' time and labor wasting supports; also permits complete rotation of unit for redirection of air stream. Bonderized Casing--Casing protected from rust by Parker Bonderizing. Safety Fan Guard--Staunch, steel' safeguard built into unit protects against danger of unshielded fan. CAPACITIES AND DIMENSIONS Bottom View ' Condenser--All copper and copper alloy. Tubes are seamless red brass. Headers, inlet and outlet connections are heavy-walled copper pipes. Fins are pure copper. Brazing of all steam carrying passages and metallic bonding of fins to tubes insures rugged unit and continuously excellent heating; Hollow-square con denser literally grows as it heats up; re treats to normal size as it cools with com plete distribution'of stresses and absence of strains where injury might result. Parallel alignment of fins reduces pos sibility of dirt lodging between fins and clogging condenser. Cone-Jet Deflectors--Verticals are regularly equipped with radial or spoke like deflector assemblies illustrated above. Individually adjustable deflector blades make possible delivery of high, narrow jet like cone of heated air from high elevation ... or low, broad, softened-velocity cone from low elevation. ' TrunCone Deflectors--Verticals can be furnished with special deflectors for use on units mou'nted at heights lower than recommended for Cone-Jet Deflectors. CAPACITIES AND DIMENSIONS Model Btu No. Hr.* Cfra H-102 24.500 H-144 34.600 H-184 44.200 H-254 61.000 H-364 87.400 H-474 113.800 H-584 141.000 H-704 169.000 H-894 214.500 H-U54 277.000 410 585 685 1020 1500 1900 2400 2650 3600 4300 Over- Depth Rpm AU . Width Less Height Motor 1580 14' n 6' 1580 17%' 14V*' 9' 1580 20'// \w 9' 1140 m- 19* 11V/ 1140 24' ir . 11V.' 1140 27%' 23' mv2' 1140 TF/f 23' 11%' 1140 29%' 24'/;' MVS' 1140 33V*' 26$' 13%' 1140 w 26%' 13V/ Mode) No. V-152 V-332 V-604 V-724 V-794 V-974 V-1084 V-1404 V-2004 V-2504 Btu/Hr* 36.500 79,700 145,000 173.800 190,200 233.500 260.000 337.000 481,000 601,000 am 610 1370 2700 3400 3300 4300 4550 5600 8000 10.000 Rpm 1580 1140 1140 1725 1140 1725 1140 1140 1140 1140 Overall Dimension (Square) 17%' 22' 33' 33' 33' 33' 33' -42%' 42%' 42%' *Btu at 2 lb steam, 60 deg Ent. Air. ` 988 Modine Manufacturing Company Air Conditioning andc^lirl' BLAST HEATERS CABINET UNIT HEATERS For modern air conditioning, heat ing, ventilating, drying and proces sing systems. Con denser is pure cop per and copper alloy, inlet to out let, for resistance to corrosion, dura bility, light weight and high heat trans fer. "Floating" condenser construc tion provides safe expansion and con traction. Fins are ' metallically bonded to tubes to prevent corrosion from re ducing heat transfer capacity. Die formed fins promote greater heat transfer; permit use of smaller, lighter coils. Modine design permits use of ducts having cross-sectional areas no greater than those of condenser face. Wide range of capacities and sizes available in Stand ard and Booster Unit types. STEAM DISTRIBUTION TYPE BLAST HEATERS Cross-section supply end, showing double tube construction These coils are characterized by ,, ] the uniform distri^ bution of. steam throughout entire heating surface . . . even when steam is partially throttled to meet system tem perature demands. Inserted in each con denser tube is a steam-distributing tube with small, accurately-sized and spaced orifices along its entire length. Steam entering distributing tube is uniformly rationed through orifices into external or . condenser tube . . . then flows as con densate into return header. Uniform steam distribution minimizes tendency of condensate freezing and tube damage; eliminates need for preheaters or tem pering coils, thus simplifying system design and control; eliminates air stream strati fication. Designed for heating offices, lobbies, corridors, etc. . . . wherever quick, posi tive distribution of heat combined with quiet operation and gentle air move ment are desirable. Has considerably greater heat output than convector of equivalent size. Employs cop per heating coil for use on steam or hot water system. Mounted on wall or ceiling. Capacities: 105 Edr. and 310 and 450 Edr. CONVECTOR RADIATION Built to meet modern residential, institutional, and commercial heating requirements, Modine convectors operate on the principle of natural convection. Cooler, heavier air is drawn in Floor Cabinet Type through the enclosure's bottom opening; comes in contact with copper heating unit that carries steam or hot water. As air is heated, it rises; is then circulated out into. room through grille at top of enclosure. Concealed copper heating unit combines compactness with high heat capacity--to give room added floor space as well as fast, even heating. Use of copper makes the heating unit almost instantly respon sive to automatic control. Enclosures are streamlined for simplicity and harmonize readily with any type of interior. Parker-Bonderized before being prime painted, the enclosures are less , vulnerable to the formation and spread of rust. . Manually installed enclosure fronts can be installed in 30 seconds without tools. Easy removal of fronts assures convenience in cleaning and gives ready access to the heating unit. Available in recessed and cabinet types. 989 Air Conditioning Unit Heaters, and Coolers D. J. Murray Manufacturing Co. Wausau, Wisconsin Offices in Principal Cities MANUFACTURERS OF THE GRID UNIT AND GRID BLAST COILS Designed and tested to operate with steam or hot water systems--for steam pressures from 2 lbs to 250 lbs. Engineered along the same lines as the standard GRID Unit which had aluminum heating sections and has been on the market since 1929. One piece construction "fin" heating sections of high test cast iron--no soldered, brazed, welded or expanded connections. Patented. Overall dimensions for installation of Cast Iron GRID Unit Heater Cl (CAST IRON) SERIES GRID UNIT HEATER DATA Model No. A Dimensions B CD Motor Capacities VoL Fan 5 Psi Steam 60 F Approx. Shipp. Pipe Size Support Rod E Hp Rpm Cfm Btu/ Hr Final Air TMPF }1i- Supply Return Di&m. CM 000 CM200 CM 500 Cl-2000 CI-2504 Cl-2500 CI-3000 Cl-3000 in/ ioVi 12% 10% 16 1/20 1750 I4X 13H 12% 13*6 I9X 1/8 1750 17% 153* 12 16 2336 1/8 1750 675 1M2 1500 30010 54000 76500 22H 20% 12 27% 25J* 13 2136 2836 1/6 1150 2600 143000 25% 35% 1/4 1150 3300 206000 27% 25J< 13 253* 351% 1/2 1150 4350 224000 32J* 31 13 31 mi/. 1/2 850' 6300 332000 32M 31 13 31 40% 1/2 1150 8000 380000 (01 103 107 110 . 117 107 108 103 (60 230 300 500 675 700 1025 1075 1% i% i% 2 2* 2* 2%' 21/2* i% 1% i% 1% 1% i% i% i% % % % % 56 36 36 36 Furnished also with 2 in. top supply connection inlet. NO ELECTROLYSIS TO CAUSE CORROSION Low maintenance expense. More air changes per hour. Positive "directed " heat. No leaks--no breakdowns. . Lower outlet temperature. Larger air volume. No soldered, brazed or expanded joints. . t Open design that keeps units clean.- Send for complete catalog information Send for information on Blast coils and radiation. 990 Air Conditioning Industrial Heating Direct Fired Units National Heater Co. 401 Essex Bldg., Minneapolis 2, Minn. N LATIONA CHAMPION STEEL S-P-A-C-E HEATERS OIL-GAS-STOKER HAND FIRED UNITS As shown in diagram these heaters are built as a complete unit consisting of heater, casing, firing equipment, multi ple blower assembly, motor, drive* induced draft blower and controls. NATIONAL HEATERS ^are con structed of welded copper bearing hot rolled one quarter inch boiler plate steel instead of the usual lighter ten guage plate. This provides positive assurance of life-long gas and smoke tight operation with ample provision for absorbing all strains resulting from expansion and contraction. The body of the heat generator is long and narrow in design, allowing complete fuel consumption with prop erly spaced Radiating fins to facilitate maximum heat transmission from this primary heating surface. Casings are sturdy with insulated double metal walls to reduce wasteful radiation ' to a minimum. Panel type construction with rigid angle iron frames and structural iron reinforcement at both top and bottom assures a strong durable installation. Casings are designed for quick and con- venient assembly. ENGINEERING RATING CHART HEATER NUMBER B.T.U. OUTPUT CAPACITY 2*SR C.F.M. MAX. 300 350 300 550 600 650 700 750 640,000 660.000 1.215.000 2,000,000 2,500,000 3.000(000 3,500,000 4,000,000 6.200 11.000 16.150 32,000 45,000 52,000 56.000 60,000 CRATE SQ.FT. VOLUME AREA HEATING CU. FT. SQ.FT. SURFACE HEATER BLOWER MAXIMUM 6.5 8.0 12.0 14.7 16.0 20.0 24.0 26.00 320 430 600 644 1421 1685 1610 1935 75 IOO 130' 175 - 315 375 450 4SO 16-TWIN l6TWm 21-TWIN ZrTRIPLE' 27-TRIPLE 30"TRIPLE30--TRIPLE 30**TRIPLE BLOWER MOTOR APPROXIMATE TUBES WEIGHT HP. MAX. RRM. NO OlA STOKER 3 1750 2 6" ` 8,650 5 1750 2 ft' 14.4 20 . 7-5 1750 IO 4" 15.660 - 10 1750 12 4* 16.610 15 1750 16 4" 20,650 20 1750 16 4" 24.090 25 1750 18 4" 26.340 30 1750 20 4" 26,470 991 Air Condilioning Unit Heatera end Coolers The Herman Neisoh Corporation General Offices and Factories at Moline, Illinois Branch Offices and Product-Application Engineers in the Following Cities: Albuquerque, N. M. Atlanta. Ga. Baltimore, Md. Birmingham. Ala. Boston. Mass. Buffalo. N. Y. Cape Elizabeth, Me. Charlotte, N. CChicago, III. Cincinnati, O. Cleveland, O. Columbus. O. Dallas, Tex. Denver, Colo. Des Moines, Iowa Detroit, Mich. Duluth, Minn. El Paso, Tex. Grand Rapids, Mich. Houston, Tex. Indianapolis, Ind. Jackson, Miss. Kansas City. Mo. Los Angeles, Calif. Louisville, Ky. Memphis. Tenn. Miami. Fla. Milwaukee, Wis. Minneapolis, Minn. Moline, III. Nashville, Tenn. New Orleans. La. Nbw York, N. Y. Oklahoma City, Okla. Omaha, Neb. Philadelphia, Pa. Richmond. Va. Saginaw. Mich. St. Louis. Mo. Salt Lake City. Utah San Antonio. Tex. San Francisco. Calif. Seattle. Wash. Spokane. Wash Springfield, Mass. Syracuse. X. Y. Washington, D. C. HERMAN NELSON HORIZONTAL SHAFT PROPEL LER-FAN TYPE UNIT HEATERS Designed for ceiling suspension, these unit heaters project warm air downward in an angular direction. Copper heating ele ment for use with steam or hot water, incorporates patented stay tube which maintains proper relationship between headers without increasing strain on loops thus prolonging life of unit. Forty-eight models, sizes and arrangements. HERMAN NELSON VERTICAL SHAFT PROPELLER-FAN TYPE UNIT HEATERS For high ceiling ii stallations. Discharge air vertically downward, or at an angle to vertical in various directions. Long life copper heating element for use with steam or hot water incorporates patented stay tube. Units available with either high or low velocity discharge, each with a wide range of capacities. HERMAN NELSON DE LUXE UNIT HEATERS HERMAN NELSON BLOWER-FAN TYPE UNIT HEATERS For efficient heat ing of large areas. Can be supplied with by-pass damper for / introduction of in door and outdoor air. Design of copper heating element assures durability and contributes to high velocity discharge. For floor, wall, ceiling or inverted wall mounting. HERMAN NELSON UNIT VENTILATORS Maintain desired air conditions for room or auditorium areas where large groups of people gather. Copper heating element for use with steam or hot water is sturdily constructed for long life and designed for greatest heating efficiency. Exclusive "draw-through" design pre vents unhealthful drafts and eliminates unnecessary overheating. Locating motor in end compartment provides additional space for fan assembly and use of larger fans running at slower tip speeds. Efficient, economi cal, compact, quiet and attractive, these Unit Heaters provide the ideal method for heating offices, show rooms, corridors, markets, stores, etc. Cop per heating element incorporates patented stay tube. Units may be placed on floor, wall or suspended from ceiling. Eighteen models, sizes and arrangements. Herman Nelson Unit Heaters and Unit Ventilators are tested and rated in accordance with the Standard Test Code adopted jointly by the Industrial Unit Heater Association and the American Society of Heating and Ventilating Engineers. 992 Air Conditioning Unit Heaters Fans and Blowers The Hekman Meisoh Corporation General Offices and Factories at Moline, Illinois HERMAN NELSON DIRECT DRIVE PROPELLER FANS Provide most economical I form of quality ventilation obtainable for industrial buildings of all types. Eighteen standard sizes available with wheel diame ters from 10 to 36 in. and capacities from 655 to 12,400 cfm. There are six teen high powered models to operate against static resistance of % in., with wheel diameters from 14 to 36 in. and capacities from 1260 to. 22,690 cfm. Can be obtained in acid and explosion resisting models. Also three models especially adapted to small store and office appli cations. HERMAN NELSON BELT DRIVE PROPELLER FANS For public and com mercial building instal lations where slow speed, quiet operation are re quired. Twelve sizes of the standard model with wheel diameters from 24 in. to 54 in. Also six sizes of the High Powered model with the same'wheel diameters. Capaci ties: 5650 to 36,150 cfm. Due to quiet operation of Herman Nelson Belt Drive Propeller Fans, use of two speed motor is unnecessary. Compact, direct connected, motor driven units have universal discharge and mount on floor, wall or ceiling. Available in five sizes with 14 speed combinations. Wheel diameters from 6% in. to 15 in. and capacities from 360 to 4320 cfm. HERMAN NELSON BELT DRIVE UNIT BLOWERS Fully self-contained unit including motor, drives and housing; for wardly curved blade wheel; adjustable motor pedestal with vibration dampers; universal discharge; nine sizes with 52 drive com binations. Available with any rotation and discharge. Wheel diameters from 11 in. to 30 in. and capacities from 1035 to 16,940 cfm. HERMAN NELSON TYPE "H" AND TYPE "HB" CENTRIFUGAL FANS Especially suited for heating, air con ditioning and ventilating systems. Type "H" has forwardly curved blade wheels. Type "HB" has backwardly curved blade wheels incorporating non-overloading power characteristics. Seventeen wheel diameters from 12}4 to 73 in.; single or double width; Class I or II construction; and any speed or discharge requirement. HERMAN NELSON DIRECT DRIVE UNIT BLOWERS Designed for many ap' plications, such as fume hoods, toilet ventilation, . chemical laboratories, industrial processing and drying problems. Type HB Type H The Complete Line of Herman Nelson Propeller Fans and Blowers is tested and rated m accordance with the Standard Test Code adopted jointly by the National Association of Fan Manufacturers and the American Society of Heating and Venti lating Engineers. 993 Air Conditioning Unit Heaters and Coolers John J. Nesbitt, Inc. Holmesburg, Philadelphia 36, Pa. 11 Park Place, New York 7, N. Y. Manufacturers of ' THE NESBITT SYNCRETIZER Heating and Ventilating Unit, sold by John J. Nesbitt, Inc., and American Blower Corporation; - NESBITT HEATING SURFACE with Dual Steam-distributing Tubes, NESBITT SERIES H HEATING SURFACE, and NESBITT SERIES W COOLING SURFACE, sold by leading manufacturers of fan-system apparatus; WEBSTER-NESBITT UNIT HEATERS (See page 1223), distributed in U. S. A. by Warren Webster & Company. NESBITT SYNCRETIZER--Series 400 The last word in heating and ventilating units for schoolrooms, offices, etc., where the continuous introduction of outdoor air is desired. For engineering data, get Publication No. 225-2; for "The Story of Syncretized Air/' Publication No. 231-2. Nesbitt Series B Thermovent For heating and ventilating auditoriums, gymnasiums, assembly halls, and similar gathering places. Publication No. 227-2. NESBITT COOLING SURFACE Series W (Water) Surface with exclu sive drain feature For air cooling and cooling and dehumidifying (with cold water) or air heating (with hot water). Construct ed of copper tubes and plate-type alu minum fins. Avail able in either con tinuous or cleanable tube type, in single rr . _ . sections having one Shawint Drain Header to eight rows of tubes deep, in three fin spacings, in eleven fin widths, and up to sixteen finned tube lengths. Sturdy galvanized casings. For particulars and engineering data send for Publications No. 233. NESBITT HEATING SURFACES With Dual Steam-distributing Tubes Copper tube-and-fin surface for lowpressure applications. Perfectly adapted to close, continuous automatic control with modulating steam valves. Steam-dis tributing tubes within the condensing tubes carry the steam equally to the full section assuring UNIFORM discharge . ` temperatures even under a throttled steam supply; eliminating temperature strati fication ; preventing tube freezing without preheaters; giving ideal system results. Cased or uncased units of many sizes and capacities. For full particulars and engineeringdata, send forPublicationNo. 245. For above advantages plus uniform distribution in extended firi' lengths from 86 to 122 ins., specify Nesbitt Duplex Heating Surface with Dual Steamdistributing Tubes. Publication No. 245. Nesbitt Series H Heating Surface A lightweight, enduring, highly efficient blast-coil heating surface designed for use with steam pressures up to 200 lb gauge. Well suited to high-pressure as well as low- pressure applications. Seven types, each in eight fin widths and up to seventeen finned lengths--a total of 284 sizes from which to select. Send for Publication No 232 for complete engineering data. . . 994 Air Conditioning Unit Heaters and Coolers Refrigeration Economics Co., Inc. 1231 Tuscarawas St. E., Canton 4, Ohio RECOY PRODUCTS C. T. COILS Continuous-tube down-draft fin-coils are still unsurpassed for meat coolers. Other forms available for practically any application. EVAPORATIVE CONDENSERS Evaporative condensers from 2 to 100 tons. Brine spray cooling to 25 tons. CEILING DIFFUSER Ceiling diffusers distribute the cooled air across the ceiling, so the blast does not strike theproducts stored. C. F. COILS Continuous fin coil? for unit cool ers, blast heaters, air condition ing and condensers. - AIR CONDITIONING Air conditioning units of ceiling or floor type in all capacities, for cooling, heating, or both. COOLANT COOLING Coolant coolers from 1 to 20 tons are a necessity for modern pro duction of accurate machine parts. WALL UNITS Wall units for long air throw discharge, air horizontally. For meats and other products sub ject to shrinkage air flow is reversed to mix with room air before contacting stored pro ducts. WATER COOLING Self contained complete ice water and brine coolers complete with ' high and low sides, circulating pumps, controls, and insulation. SHELL CONDENSER Shell and tube, also shell and fin coil condensers. Both types have tubes arranged for cleaning with tube cleaner. FLOOR UNITS Floor units with cooling surface exposed to view have a definite advantage over those with coils hidden. Design permits water defrosting. 995 Air Conditioning Unit Heaters Gas Fired Reznor Manufacturing Co. Specialists in Gas Heating Since 1888 Mercer Pennsylvania Side view of Reznor Blower Type Front view of Reznor Fan Type Suspended Unit Heater Suspended Gas-Fired Heaters A Reznor unit will solve most any heating problem . . . large or small areas. Complete in one package, Reznor gas-fired suspended unit heaters (fan and blower types) are literally self-contained heating plants. For instal lation all they need are a gas line, a flue, and electric supply. Reznor heaters are made in 9 sizes with input ratings ranging from 55,000 to 400,000 Btu's. They operate on natural and manufactured gases, butane and propane. Reznor heaters are finished in a seal brown wrinkle finish which retains its beauty for years. Fan and Blower Types Reznor offers the blower type unit heater in the same nine sizes as fan unit heaters. Blower heaters and fan heaters are identical in every respect (including standard and optional controls) except for the air moving power. Blower heaters are frequently Specified where extreme quietness is required, or where it is desirable to carry the cold air to the heater through a duct system. Forced Air (floor type) Entirely self-contained, completely automatic forced air heaters with every feature of the central plant except size but with the- beauty of fine furniture--these new heaters represent an outstanding development in gas heating equipment. . Room temperature, gas pressure, air delivery and emergency shutoff are all automatically and accurately controlled without thought or effort on the part of the user. All controls are completely installed by factory. Hester Number USTS US3Q - USISO 05200 US400 HEATtR INPUT RATING Btu. 67 55,000 75,000 90.000 110.000 130,000 150.000 200,000 300,000 400.000 Cu. Ft. oar Hr. Btu. G50 1000 100 65 138 75 164 90 200 110 238 130 1G0 384 200 646 728 400 OUTPUT (Vented) Btu. per Hr. MM) 62^50 74,700 91,300 107,900 124.500 166,000 249,000 332.000 Sq- Ft. 190 258 311 380 4S0 519 692 1038 1383 AIR Free Dellii. CFM BOO 1350 1350 1700 1700 2000 2700 4000 5400 Veil In FPM 640 675 675 8S0 850 860 1110 850 1110 MOTORS App. HJ. Type RPM 1/20 1/20 5h.P1. SpJ*h- 1/8 1/6 1 nth " " 1000 1140 1140 1140 1140 1140 1140 Ai"p- FAN DUIn In*. Shipping Pitch Weight In' Deg. JS 14 1.4 18 2J 16 16 145 27 244 Ab 3.9 18 33 422 All sizes are available with blowers instead of propeller fans, air deliveries, and other characteristics being the same. .. 996 Air Conditioning Unit Heaters and Coolers Young Radiator Go. Dept. 176, Racine, Wis. Sales and Engineering Offices in Principal Cities' Young HEAT TRANSFER PRODUCTS Oil Coolers Gas, Gasoline, Diesel Engine Cooling Radiators Heat Exchangers Intercoolers Engine Jacket Water Coolers Unit Heat ers Convectors Condensers Evaporators Air Conditioning Units - Heating Coils Cooling Coils and a Complete Line of Aircraft'Heat Transfer Equipment. ` `STREAMAIRE' ' UNITS "Streamaire" units are a development of Young's quarter century of experience in building heat transfer products. Personalized, ''on-the-job" engineering service by field men--backed by modern research and manufacturing facilities--assures the practical, economical installation as required in your plans. Type "SH" unit heaters for hori zontal air discharge. Available with capaci ties from 27,000 to 325.000 Btu per hour. Catalog 2758. - Type "V" or Vertiflow unit heat ers for vertical air discharge. Capacities from 59,000 to 520,000 Btu .per hour. Catalog 2541. Type "FH" blower unit heaters for floor, wall or ceiling mounting. Capacities from .---*163,000 to 1,300.000 Btu per hour. Catalog 556. Type "W" water coils for cooling or heating with cen tral plant systems. Five widths, 11 to 35 in.; 2 to 8 rows of tubes; many lengths. Write for details. Several types of convector units-- circulate rather than radiate heat. Used with steam or hot water systems. Styles to blend with architecture and room furnishings. Type "DAC" units provide in dividual room, winter air con ditioning--filter, humidify, heat, cir culate. Catalog 7041 "YAC" units for year-round air con ditioning. Also for winter or summer conditioning only. Horizontal and verti cal models. Capaci ties from 400 to 16,625 cfm. Catalog 7541. Types "B" and "A" blast coils for central plant heat ing and air con ditioning systems. Steam distributing tube type, available. Catalogs 4540 and 4542. Type "E" evap Type "C" com orator coils for. mercial heat trans direct expansion fer coils for use in cooling systems factory built air using Freon or conditioning units. Methyl chloride. Steam distributing tube t y p e available. Four widths--two to One. two and three rows six rows of tubes; many of tubes. Catalogs 4$40 lengths. Catalog 5059. and 4542. 997 Air Conditioning Unit Heaters and Coolers The Trane Company 2021 Cameron Avenue, La Crosse, Wisconsin COMPLETE LINE OF HEATING, COOLING, AIR CONDITIONING AND AIR HANDLING EQUIPMENT Over 70 U. S. Branch Offices Albany, N. Y.; Allentown. Pa.; Amarillo. Texas; Appleton, Wis.; Atlanta. Ga. ;Aurpra, 111.; Baltimore. Md.j Billings, Mont.; Birmingham. Ala.; Boston, Mass.; Buffalo, N. Y.; Canton, Ohio; Chattanooga. Tenn.i Chicago, 111.; Cincinnati, Ohio; Clarksburg. W. Va.; Cleveland. Ohio; Dallas. Texas; Davenport, Iowa; Dayton. Ohio; Denver, Colo.; Des Moines. Iowa; Detroit, Mich.; Dodge City, Kansas; Flint, Mich-; Fort Wayne, Ind.; Gainesville* Fla.; Grand Rapids, Mich.; Greensboro. N. C.; Greenville, S. C.; Harrisburg, Pa.; Hartfoni, Conn.: Houston, Texas; Indianapolis, Ind.; Kalamazoo, Mich.; Kansas City, Mo.; LaCrosse, Wis.; Lake Charles. La.; Little Rock. Ark.; Los Angeles. Calif.; Louisville, Ky.; Memphis, Tenn.; Mexicp. D. F.; Milwaukee, Wis.-; Missoula, Mont.; Newark, N. J.; New Orleans, La.; New York, N. Y.; Oklahoma City, Okla.; Omaha. Neb.; Philadelphia, Pa.; Phoenix, Aria.; Pittsburgh, Pa.; Portland. Ore.; Providence, R. I.; Richmond. Va.; Rochester. N. Y.; Salt Lake City. Utah; San Francisco, Calif.; Seattle. Wash.; Sioux City. Iowa; South Bend. Ind.; Spokane. Wash.; St. Louis. Mo.; St. Paul. Minn.; Syracuse. N. Y.; Trumbull. Conn.; Washington, D. C.; Wilkes Barre. Pa.; Wilmington, Del. ' Sales Connections All Over-The World In Canada: Trane Company of Canada. Ltd.. Mowat and King Sts., W.. Toronto, Ont. (15 Branches) A COMPLETE LINE The Trane Company fabricates a complete line of heating, cooling, air conditioning and air handling equipment. Long years of experience with practical knowledge gained from dose field contact, have developed products for every requirement. Trane Convector-radi ator--the modern successor to the old-fashioned radiator, the Trane Convector-radiator is a compact, light-weight, easy-to- install unit. Available for either steam or hot water heat ing system. It is equally suited to the spacious mansion or the smallest cottage, to the modern office, hospital, apartment house or even the industrial building. It combines attrac tive appearance with Long life and economical service. ` Currently easier to obtain and install than ever before, they are available in stock throughout the nation. Trane Coils--There are Trane Extended Surface Coils for every heating or cooling, comfort or process application, in all types and sizes. Types include coils for steam, hot water or booster heating, direct expansion or water cooling. In addition, a wide variety of coils is available for specialized or process work. Trane Blower Type Unit Heaters--Better known as Torridors, Trane Blower Type Unit Heaters are available for large space or duct work ap plications. Manufactured in direct or belt-driven types and floor, ceiling, or wall models, the Torridor may be provided with thermadjust or face and by-pass dampers and a variety of discharge devices for greater Torridor Unit Healer Projection Heater 998 flexibility. ; Ideal for heating large spaces, exposed areas requiring a blanket of heat, and for process applications. Trane Projection Heaters --A Trane development, the Projection Heater taps the usually,- wasted heat reservoir at the ceiling bringing it down where it is needed. Installed at 8 to 50 ft heights, it projects warm air to the floor in a circular, vertical air stream. Ideal for low or high pressure systems in factories, ware houses, etc. Trane Propeller Unit Heaters--Featuring a quiet operating* wide-bladed fan that pushes rather than bats the heated air through the coil, the Trane Propeller Unit Heat er incorporates many unusual features, including adjustable louyers or grilled outlets di recting heated air to the floor line, rugged motor supports, attractive appearance. Trane Air Conditioning Manual--Trane offers the engineering profession a straight-forward and unbiased textbook covering the funda mentals of air conditioning, in a new enlarged edition. The Manual not only shows how to design every type of air conditioning system, but also clarifies underlying principles, enabling both student and engineer to reason out their own problems. Price--$5.00. The Trane Company Air Conditioning . "& Trane Climate Changers --Trane Climate Changer, a unit type air conditioner,. is designed for summer, winter, or year 'round air condition ing, commercial and indus trial application, comfort or process installations. These units incorporate efficient Trane Coils, quiet blower fans in sturdily constructed casings in horizontal or ver tical models. Available in various coil combinations with or without humidifi cation equipment. Climate Changer Trane Refrigeration Equipment -- Outstanding in the refrigeration field is the Trane Turbo-Vacuum Compressor, a completely self-contained hermetically sealed centrifugal type water chiller, available in 50, 70,. 100 and 200 ton sizes. Year 'round efficiency in constant . operation with a minimum of maintenance is assured by^ the scientific simplicity of this machine. Trane also furnishes a com plete line of Reciprocating Compressor and Condensing .Units with capacities ranging from 3 to 100 tons. Also available are Trane Self-cohtained Air Conditioners for shop and office spaces. Reciprocating Compressor Trane Roof Ventilators --The Trane Roof Ventilator can be used wherever an effective roof ventilator is required. This unit is avail able for either ' exhaust or supply purposes. It is not only light, but weather and bird-proof as well. Hoods of the units are hinged for easy maintenance. Centrifugal Fan Trane Centrifugal Fans --Recommended for all types of heating, cooling, and air handling applications. In direct or belt-driven units; single or double widths, and all standard discharges in both backward and forward curved blade construction. Capacities .200 to 330,000 cfm. ' Lifetime Valve Thermostatic Radiator Trap Trane Propeller Fans-- The exclusive, broad-bladed propeller fan is available in 2' or 4 blade construction. 999 Can be used for vertical or horizontal installations for exhaust or supply applica tions. Direct or belt-driven. Capacities, 500 to 100,000 cfm. - Trane Steam Heating Specialties--There are over fifty valves, traps, vents, strainers, all allied specialties in the Trane Line. Among them are the famous Trane Hermetic Valve with the Lifetime Diaphragm that ab solutely prevents steam leak age around the stem and the Thermostatic Radiator Trap which when used together provide an ideal combination for convectors and radiators. Trane Hot Water Heat ing Specialties -- Included among Trane Hot Water Heating Specialties are the Trane Circulator, Flo Valves, and Fittings. They combine with Trane Convectors or Unit Heaters to provide an ideal Warm Water Heating System for a great variety of applications. Other Trane Equipment --The complete Trane Line also includes--1. Trane Unit Ventilators for schoolroom air conditioning; 2. Trane Condensation and Centri fugal Pumps for a large variety of uses; 3. Trane Dry Type Water Chillers; 4. Trane Evaporative Conden sers to condense refrigerants in the air conditioning system with a minimum use of water;. 5. Trane Cooling Towers;. 6. Trane Force Flo Unit Heaters for quiet heat and neat appearance; 7. Trane Railroad and Bus Air Con ditioning Equipment of all kinds; 8. Trane Shell and Tube Heat Exchangers for cooling and heating vapors or liquids in a closed system; 9. Evaporative Coolers for cooling fluids in a closed system; 10. Transformer Oil Coolers; 11. Air Washers. Write today for Trane Products Bulletin PB290 which describes completely all of the products listed here, as well as providing sufficient _ data for their selection. Air Conditioning Vnit Heaters Factories: NEWARK, N. J. L. J. Wing Mfg. Co. Canadian Factory: 59 Seventh Avenue, New York 11, N. Y. MONTREAL Branch Offices in Principal Cities WING REVOLVING UNIT HEATERS This innovation in the method of dis tributing heat produces a sensation in heating comfort never before attained--a sensation of fresh, live, invigorating air. The fact that the outlets revolve assures uniform and thorough distribution of com fortably warmed air throughout the entire working area, without drafts, hot spots or cold spots. Such an unprecedented high efficiency in distributing heat is the result of nearly 20 years of constant study by Wing engi neers to improve on the Floodlight System of heating pioneered by WING in 1921. This method projects the heated air verti cally downward by means of light-weight, ceiling-suspended unit heaters. It has needed only this latest refinement of slowly revolving discharge outlets to ` bring that method to perfection. The WING Revolving Discharge type supplements the WING line of standard fixed discharge Gullets, illustrated and described on the following page. Bulletin HR-4. The latest type of WING Unit Heater-- with Revolving Discharge Outlets--is just as great a contribution to the art of industrial heating as was the Ceiling-Suspended Unit Heater, an nounced by WING in 1921. The area covered by a WING Revolving Unit Heater is slowly swept by the heated air discharged by the outlets which move through an arc of 360 deg. covering every direction of the com pass successively. By maintaining an active, constant circu lation of air through out an industrial plant at all times, a new sensation of refreshing, 0 invigorating comfort to [kj workers is produced. 1000 L. J. Wing Mfg. Co. Air Conditioning Unit Heaters Fans and Blowers WINGFOIL SAFETY VENTILATING FANS An axial flow fan that will deliver air against static pres sure, quietly and efficiently. Moves the air for ward in straight lines with minimum eddy. Capacities to 100,000 cfm. Bul letin F-9. WING FEATHERFIN PROCESS HEATING UNITS For man ufactur ing pro cesses such as drying, aging, etc., re quiring the recirculation of the heated air. Motor or turbine located outside air cur rent. Bulletin PS. WINGFOIL DUCT FANS For economically moving air wherever ducts are used. It combines the efficient WINGFOIL AXIAL FLOW Fan with a housing which places the motor entirely outside the air duct. Motor and drive remain cool and clean and are easily The powerful WINGFOIL Fan delivers high air volume with low power consumption against any pressures for which duct systems should be designed. V-belt or direct drive. Light, compact and easy to install. Bulletin F-9. ' WING SYSTEM OF CONTROLLED COMBUSTION For low pressure heating boilers and small power boilers. Increases capacity and permits use of lowest cost fuel. Includes Type EM Blower equipped with fully enclosed dustproof motor with speed regulating rheostat and automatic control. Eliminates necessity of frequent firing, aljowing intervals as great as 24 hours even in zero weather. Bulletin M-96. WING TURBINE-DRIVEN BLOWERS Applied to hand, stoker, oil or pulverized fuel fired boilers, increase boiler capacity, maintain constant steam pressure and permit com plete combus tion of low-cost fuels. The ex haust steam, free from oil, can be used for heating or pro cesses. Bulletin T-98. WING DRAFT INDUCERS Installed in breeching or flue, or on chimney top; provide positive, exact draft regardless of weather conditions or inade quate chimney ' or breechingcon struction. Suit able for coal, oil, or gas-fired boil ers; industrial furnaces and kilns. Bulletin Chimney-Top Installation 1-10. Installation of Wing System of Controlled Combustion in a large school WING MOTOR-DRIVEN BLOWERS Type COM for static pres sures over 5 in. and volumes up to 35,000 cfm. Type EMD for moderate static pressures up to 5 in. Both blow Type COM ers have fully-' enclosed dustproof constant speed motor and built-in adjustable control vanes. Type COM has double-staged axial flow fan; Type EMD, single stage fan. Extremely com pact; discharge can be vertical, horizontal or in clined. Bulletin COS. Type EMD 1001 LJ.WingMig.Co. Air Conditioning Unit Heatera WING CSiSn N- 4 FIXED DISCHARGE UNIT HEATERS The first light-weight, ceiling-suspended, unit heater. Eight different designs of outlets meet the requirements of every type, size and height of building or oc cupancy. Located near ceiling or roof, the accumulation of hot air in the upper spaces, with the accompanying costly waste of heat, is prevented. They project the air, comfortably warmed, downward to the working area. Bulletin HRS. DOOR HEATERS GARAGE HEATERS WING developed this vertical cone- discharge heater in 1921 and today it is still applicable for heating the inrush of cold air at large doorways and for garage heating. Often cuts heating costs in half. Bulletin HR-4 ' FOR LOW CEILINGS In this type of WING Unit Heater the' position of fan and motor are re versed to meet con ditions of ceiling or roof height, form and shape of Type "LC` building, coverage, etc. Bulletin HR-4. WING UTILITY UNIT HEATERS A lightweight suspended unit heater for delivering heated air in one general direction. Has the same powerful fan and rugged heating element as WING Featherweight Unit Heat ers. This is the latest re finement of the original horizontal light weight heater which was developed by WING. Bulletin HR-4. - FEATHERFIN HEATER SECTIONS For heating or cooling air for any purpose by steam, hot or cold water or refrigerant. The heating element is extremely light and, for equal heat trans fer, offers little resistance to air flow. Available for any desired final air tem perature. Bulletin HS-B. VARIABLE TEMPERATURE SECTIONS Invaluable in supply ing fresh air for space heating or process work. Close control of the de livered air temperature is obtained without danger of freezing. Manual or automatic control. Bulletin HS-2. \' WING INDUSTRIAL FOG ELIMINATORS Eliminate fog, odor and fumes in dyeing, bleaching and finish ing plants, creamer ies, pasteurizing, bot tling, canning and packing plants, chem ical works, paper mills, steel pickling plants, etc. No ducts are required. Bulletin FE-lB. 1002 Air System Equipment Air Treatment W. H. Wheeler, Inc. 7 East 47th Street, New York 17, New York airicem 1MK--% m CHL AIR Air Quality Control for Air Condi tioning--Airkem Chlorophyll Air Fresh ener reduces odors and provides a fresh indoor air quality. Manufactured under U. S. Patent 2,326,672, Airkem contains activated chlorophyll and is especially suited to industrial and commercial ap plications. The efficacy of Airkem in producing a fresh indoor air quality has been demon strated by its use in theaters, department stores, industrial plants, banks, hotels, restaurants, offices and in the most exact ing of all fields--hospitals. In addition, Airkem permits reduction of the fresh air intake in air conditioning systems with corresponding reductions in both summer and winter load, and savings in fuel, water and electric power. ..Easily Added to Systems--It is easy to engineer Airkem into new systems or . add to existing air conditioning or venti lating systems, either large central systems or the smaller packaged units. The Airkem Evapatrol unit consists of a small vaporizing cartridge enclosed in an attractive casing, an Airkem reservoir with pump and an Airkem regulator.The vaporizing unit can be installed., directly on the side of the fan section of a packaged type unit or on the fan section of the plenum chamber of any central system. The suction of blower in either case draws air through the cartridge which is saturated with Airkem. The satura tion of the cartridge is maintained by 7 means of a solenoid operated pump which is mounted directly on the Airkem reservoir, and pumps the Airkem to the distributor in the vaporizing unit. The operation of the pump is controlled, by the regulator which permits adjusting the amount of Airkem by timing the pump strokes at the required intervals. Both the Airkem regulator and reservoir can be installed at remote locations. 1003 Air System Equipment Ait Filters and Cleaners The Air-Maze Corporation 5200 Harvard Avenue, Cleveland 5, Ohio AIR-MAZC ENGINEERS AND MANUFACTURERS OF AIR FILTERS Direct Factory Representatives in All Industrial Are-as Distributors in principal cities throughout the United States Sound Engineering--As specialists in air filtration, Air-Maze has spent over 20 years of constant research in engineering over 3000 types of filters. The enviable repu tation enjoyed by Air-Maze--the result of long experience in the air filtration field with varied dirt and dust problems--assures soundly engineered filtration. Viscous Impingement Type--Air-Maze viscous impingement, cleanable type air filters are permanently efficient in industrial, commercial and residential air conditioning systems. The filter media consists of alternate layers of crimped, galvanized screen cloth of various mesh, arranged to break up the air stream into minute, swirling currents. Dirt is impinged on the wire baffles, previously coated with an adhesive. Dirt Arrestance--Efficiency of dirt arrestance varies, depending on filter de sign, type of dust, dust feed, etc. In regular service, practically all so-called "nuisance" or "abrasive" type Sdust is eliminated. Resistances -- Filters available with initial resistances as low as 0.045 in. water at 300 fpm. (Graphs showing resistance at various velocities are available for each type of filter.) Face Velocities--Various Air-Maze filters are designed to operate efficiently at any velocity, including 106, 300, 500,1500, and up to 2000 fpm, depending upon appli cation; pressure drop available, etc. Sizes--Air-Maze filter panels are rec tangular in shape and can be made in any reasonable size and thickness. 1 in., 2 in. and 4 in. thicknesses are standard. Spe cially shaped filters are built to your speci fications. _ P^oto at extreme right shows cross section of selective filtration principle and large dirt holding capacity in typical Air- Maze filter panel. - In the left-hand photo, a magnifying glass shows the smooth round wire baffles collecting dirt in "streamlines", thus pre senting low resistance to air flow despite heavy collection. Holding Frames--Holding frames, complete with felt seal and choice of lock ing-devices, are supplied when requested. For filter banks, Air-Maze furnishes either assembled frames dr will drill frames for assembly on the job. Cleaning Data--Air-Maze filters are easily cleaned with hot water, steam or any commercial solvent. They are charged by immersing in recommended adhesive or S.A.E. 30-50 oil. Write for Details--Write for complete information and let Air-Maze engineers work with you on your air filtration prob lem. See your classified telephone direct ory for Air-Maze factory representatives or distributors. 1004 Air System Equipment Air Filters and Cleaners The Air-Maze Corporation 5202 Harvard Avenue, Cleveland, Ohio TYPE "A" with holding frame Type "A"--Built for heavy-duty service. Scientific fabrication of media results in open construction, large dirt-holding capacity, without undue increase-in restriction. Type "B"--Recommended for average dirt conditions, or where shorter servicing intervals are acceptable. Kleenflo*--For home unit conditioners and recirculated air systems. Greastop*--Prevents grease nuisance and fire hazards in kitchen ventilating ducts, and reduces blower and motor maintenance by collecting entrained grease in exhaust cooking vapors. Greastops eliminate duct cleaning expense. Trade Mark Registered SPECIAL FILTERS FOR SPECIAL APPLICATIONS Humidifier--Increases humidity for many industrial processes where dry at mosphere may be harmful or present a fire hazard. Effective for evaporative cooling installations. Panels also available for separation of liquids from air stream. Bronze construction. Flame Arrester--Panel open enough to permit air to pass freely, yet will prevent explosion on one side from igniting airgasoline mixture on other side. Excellent for mines, grain elevators, liquid storage installations, etc. Oil Separator--Removes entrained oil, kerosene and other liquids from air. Oil collecting media is removable. Filters . can be applied to exhaust systems in con nection with coolants, cutting oils, degreasers, etc. TYPICAL APPLICATIONS Air-Mate panelfilters . arranged to save space ` with a maximum amount of air flow. Kleenflo Greastop Flame Arrester A "doghouse" installation for compressors and enginesusing Air-Maze panel fillers. Furnished with or with out weather louvres. One louvre is shown open. 1005 Air System Equipment Air Filters and Cleaners American AirFilterCompany Inc. 673 Central Avenue, Louisville 8, Ky. In Canada: Darling Brothers, Ltd., Montreal, Quebec PRODUCTS: The Mt American Air Filter Company, Inc. manu factures a complete line of Air Filtering Equipment including Electronic Air Filters, Automatic Self Cleaning Filters, Viscous Unit Filters, and Dry Process Filters to be used for the removal of dust, soot, smoke, dirt, bacteria and other foreign matter from the air. Because air filtration has proved to be the economical, practical and efficient method of cleaning the air, the modern air filter is now considered an absolute neces sity in building ventilation or air con ditioning, in the maintenance of health and persona! efficiency, protection of interiors and furnishings and valuable merchandise and equipment. Shown here are but a few American Air Filter products in most general use. The American Air Filter Company is recognized as an authority on dust problems and their satisfactory solution. Products offered embody the knowledge accumulated from twenty- five years of intensive research devoted exclusively to the study of dust problems and the development of air clean ing apparatus; the experience gained from designing, building and applying thous ands of air filters; are backed by ample technical and financial resources; and may be relied upon as the most modern equip ment in their field of service. THREE TYPES OF ELECTRONIC AIR FILTERS For more than ten years, research and experimentation with electronic air filtra tion have been in progress by AAF engi neers. Today's complete line includes the self cleaning Electro-Matic introduced in 1939, the washable Electro-Cell with re movable collector plates, and the Electro- Airmat with the replacable Airmat paper medium. Here for the first time is high efficiency air cleaning in three types of electronic filters to meet any requirements for super clean air. Electro-Matic Self-Cleaning Elec tronic Filter--The Electro-Matic filter is a self cleaning electric precipitator combining the most advanced principles of electronic air cleaning with notable improvements in construction details and method of operation. The self-cleaning feature is an exclusive advantage of the Electro-Matic filter. It eliminates the necessity of shutting down the filter for manual cleaning, minimizes the need for personal atten tion and permits continuous high-efficiency operation. It also allows the ElectroMatic filter to be built in standardized self-contained sections; easy to install and with all exposed parts of the filter casing-electrically grounded for the protection of operating personnel. Send for Bulletin No. 250. 1006 American Air Filter Co., Inc. Air System Equipment Air Filters and Cleaners Electro-Cell Electronic Filter--Incorporates all of the new developments of major importance in elec tronic air filtration using col lector plates. Installation has been simplified, performance improved and maintenance advantages provided. Built in vertical sections of two widths--2 ft and 3 ft over-all. Collector plate assemblies are removable; ionizers are hinged and^extend the full height of the sections, preventing cur rent loss. A choice of wash ing collector plate assemblies while in place, or removing assemblies for individual cleaning. Installation is sim plified because filter is built in vertical sections rather than assembled of small units. Parts to be lifted and aligned are light in weight and elec trical connections simplified. Write for Bulletin No. 252. Electro-Airmat Elec tronic Filter--The applica tion of an electrostatic charge to a dielectric filtering ma terial is an exclusive AAF research development which began early in 1934. Airmat paper is composed of a num ber of plys of porous tissue like cellulose sheets. When electrically charged the plys tend- to separate and each individual fibre becomes a collecting electrode which at tracts and holds the dust and smoke particles. Ease and convenience of maintenance is a desired advantage of the / Electro-Airmat. Requires neither water nor sewer con nections for cleaning, nor spraying with oil to maintain its efficiency. When Airmat paper has accumulated its Electro-AIRMAT Filler Elecfro-CELL Filler American Mulli-Duty Self-Cleaning Filler dust load it is removed and replaced with clean material by means of a mechanical loader. In case of power fail ure, filter media provides best mechanical air filtration known. Send for Bulletin No. 253. American Multi-Duty Automatic Filter provides outstanding features of per formance and design and will accomodate either armored screen panels or die stamped louver panels. available in three types. Offers advan tage of uniformly constant air supply, fixed operating resist ance and automatic operation. Ideal for ventilation and air conditioning service. Avail able in any size or capacity. Send for Bulletin No. 241-A. AAF UNIT FILTERS Throway Air Filter-- Throway filters are inexpen sive and designed to be dis carded after accumulating dust load. Send for Bulletin No. 117-E. Airmat Type PL-24-- Airmat filters use standard Airmat medium, renewable after collecting dust load. Used both for comfort and industrial air conditioning. Available with unit frames to be set up to meet any capa city requirement or space con dition. Send for Bulletin No. 230-C. . M/W Filters--The M/W comes in 2 in. and 4 in. thick nesses. Ideally suited to air cleaning problems encount ered in general ventilation and commercial air condi tioning. Permanent type, washable. Send for Bulletin No. 202. ^ Throway Air Filter ' Airmat Type PLSI Filler . . 1007 M/W FtUer Air Filters Air System Equipment and Cleaners Air Recovery W. B. CONNOR ENGINEERING CORP. 114 East 32nd Street New York 16, N. Y. ^^==^3 Representatives *n Alt Principal Cities Canadian Representative: Arthur S. Leitch Co., Ltd.. Toronto, Ont. Air Recovery Equipment DOREX Activated Carbon Adsorbers recover the freshness of vitiated air by extracting air-borne odorous, gaseous and vaporous impurities. When applied to recirculated air in air conditioning, DOREX Adsorbers convert used, stale, conditioned air for ventilation thus reducing to a minimum the volume of unconditioned outdoor air make-up otherwise necessary. . With DOREX Air Recovery, the cooling and heating capacity of a proposed air con ditioning system is decreased by the saving in outdoor air load. With DOREX Air Recovery, an existing air conditioning system will serve a larger space or satisfy a greater conditioning load without increase in cooling or heating equip ment or the consumption of more fuel or energy. . - The highly active, specially processed and impregnated cafbon employed will remove from the air passed through it and retain 95 per cent of all entrained gaseous impurities and maintain approximately this efficiency for from 6 months to 2 years depending upon the air contamination. Upon exhaustion the carbon may be reactivated for re-use. pOREX Air Recovery equipment is available in several types to suit individual requirements. . TYPE H-FOR COMPLETE DECONTAMINATION OF ALL AIR PASSED THROUGH IT Fig. 1 Fig. & Fig. S DOREX Type H Equipment consists of light-weight, removable, perforated, activated carbon filled, adsorption canis ters. These are mounted in multiple on one or more supporting manifold plates in such manner that all air to be treated will pass uniformly through the granular carbon media. The assembly arrange ment is flexible to suit the space limita tions. The resistance to air flow averages only 0.15 in. wg. Fig. I shows a typical canister. It is closed at the top'and the inner cylinder is open at the bottom, which opening registers with a corresponding hole in the supporting manifold plate. Fig. 2 is a photograph of a typical arrangement of canisters as installed.. In this instance, three manifold plates each support 98 canisters arranged in 7 rows of 14 canisters each. Fig. 3 is a sectional view of this arrange ment with the side removed and indicating direction of air flow. Each canister decon taminates from 25 to 35 cfm of air. 1008 W. B. Connor Engineering Corp. Air System Equipment Registers Grilles TYPE G--FOR CONTINUOUS DECONTAMINATION OF RECIRCULATED AIR The DOREX Type G The Type G Adsorber Adsorber and Air Re consists of sturdy metal covery Unit is designed frames forming panels, to remove accumulated each housing a battery odors and gaseous im of exposed perforated purities from air recir metal tubes which con culated by air condition tain the granular carbon ing units and systems. filter media. These Its extremely compact panel units are available design and the ease with in stock sizes, suitable which it can be installed for arrangement in air makes it equally adapt ducts, or for attachment able both to existing to standard dust filters, ventilating systems Dorex Type G outlet or inlet grilles. without necessitating expensive altera They are designed to expose a maximum tions, and to newly designed conditioning of carbon adsorption surface to the air systems, particularly where space is at a stream with a minimum of resistance to premium. It is also adapted to incorpo air flow. Standard units are of one, ration in package conditioners, unit heaters two or three tube rows in depth, desig and cold diffusers. nated as G-l, G-2 and G-3, respectively. Dorex Type SQ The DOREX Type SO Odor Adsorber is an entirely self contained unit suitable for either portable or station ary installation. It consists of a cage of closely spaced, perforated, granular activated carbon-filled tubes" housing a quiet operating, circulating fan and motor. It is furnished assembled, equipped with starting switch and complete with extension cord and plug ready to connect to electric socket. The DOREX Type SO Unit keeps the room air in continuous motion while, at the same time, completely decontaminating one-third of the total air circulated. It, therefore, provides both air circulation and ventilation without the use of outdoor air. At the right is an illustration of the Type A-100-B, smallest of the DOREX self-contained package recircu lating Odor Adsorbers. In its attractive enameled wood cabinet are contained a dust filter, four carbon gas adsorbing canisters, circulating fan and motor. It has a host of practical uses--in homes, offices, doctor's rooms, walk-in refrigerators, etc. The Type PL DOREX Vapor and Gas Adsorber is designed especially to ex tract all vapors, fermentation odors and other gaseous im purities from compressed air. It is the only device which effectively removes airentrained gaseous odors and impurities not eliminated by commercial filters, separators, after-coolers or receivers. , Dorex Type A "AIR CONSERVATION ENGINEERING" A complete and authori tative Text Book on the function, engineering and application of Air Recovery in air conditioning. Con tains valuable tables and charts. Price $2.00. Com plimentary copies available to recognized engineers upon request. AMONG THOUSANDS OF DOREX USERS Armour & Co. Baltimore & Ohio RR Bell Telephone Co. E. I. DuPont de Nemours & Co. Ford Motor Co. General Electric Co. Harvard University Lockheed Aircraft Corp. Houdaille Hershey Corp. ' Remington Rand, Inc. . Sperry Gyroscope Co. Bristol Laboratories, Inc. Union Carbide Co. F. W. Woolworth Co. . 1009 Air System Equipment Air Fitters and Cleaners 6 Centre Park Dollinger Corporation Air Filters for Building Ventilation, Air Conditioning, Engine Intakes, Etc. g&KjEW FILTERS Rochester 3, N. Y. STAYNEW MODEL A-3 AUTOMATIC FILTER A New and Improved High Efficiency . Automatic Air Filter An endless curtain type oil-bath filter outmoding the previous Model A design. In addition to offering all exclusive features of the earlier model, the new A-3 maintains higher efficiency, greater dirt-handling ability, improved air brush conditioning and other qualities. Meanwhile the original low resistance has been retained. Operation and Features: Two endless curtains are carried on heavy roller chains which are driven by sprockets keyed to the shafts of the curtain rollers. These rollers float on ball bearings for quiet, frictionless oper ation. Curtains consist of removable panels made of a single layer of bronze screen cloth to which are attached layers of woven copper mefeh. The first of the curtains is the denser, having about twice the impingement sur face of the second or rear curtain. This first curtain acts as the filter and travels through the oil reservoir. The second curtain does not enter the reservoir but acts only as. a safeguard against oil entrainment. This design permits the front curtain to be rotated so that the panels on the air-entering side move downward into the oil bath and are cleaned before rising on the return or clean side. Thus no dust can be carried across the back or return side of the front curtain to be blown off and carried on by the flow of air. . Patented Staynew Air Brush Conditioners prevent . excessive amounts of oil being carried upward on the curtain panels and being entrained in the air stream. This is important, since natural drainage of even the finest grades of filter oil cannot be depended upon, due to changes in viscosity. Specifications The Model A-3 filters are sectional and may be bolted together to obtain any required capacity. Sections come in two widths: 4 ft 3 in. and 2 ft 9 in.. The filter drive and control mechanism includes a ^ hp motor driving through a reduction gear, a Telechron Time Switch, and a momentary contact by-pass switch (providing manual control when required)--all mounted on a common base plate located on clean air side of filter.. The drive motor and the Air Brush Conditioners operate simultaneously for a few seconds at 15-minute intervals. Each control mechanism, handles up to and including 4 filter sections. 1010 Dollinger Corporation Air System Equipment * iZJcieiTM,, Model WKE' Panel and Frame Handles and Lalckes STAYNEW PANEL TYPE FILTERS New, Model WKE: Dry-type finned panel filter for use in ventilation and air conditioning systems. Extremely large filtering area in relation to overall size. Adaptable to wide variety of filtering media--in fact, almost any medium ob tainable in sheet form that can be crimped. Steel mesh on both sides of medium prevents sagging and makes the WKE fire-resistant and cleanable without possible damage from, vacuum cleaning tool or cleaning nozzle. It may also be washed or. dry cleaned when and if necessary. There are no cross bars, spacer bars, or other obstructions to interfere with the cleaning operation. . Filter cells are held in rigid box-type supporting frames of heavy gauge metal by spring-loaded cam-type locking latches. Two lifting handles are provided on each cell. Filtering medium supplied already crimped and cut to size. It may be inexpensively replaced in 2 to 5 minutes right at the filter bank--no special tools required. ' Frames are drilled so that they can be riveted together to form a flat bank, or by the addition of angle uprights into a "V" or staggered arrangement. Viscous Model Panel and Frame Viscous Panel (Model DPV): A permanent type panel, for air conditioning systems used in heavy duty industrial service. Filtering media consist of a series of layers of crimped galvanized screen cloth and woven mesh. These media when coated with PD-IO Pingene Filter Oil form an unusually efficient filter. Model DPV filters are cleaned easily with live steam or by washing in a suitable solvent. Spring-loaded locking latches and lifting handles are provided, as in Model WKE above. Also, frames are drilled as in Model WKE. Both Model WKE and DPV cells are furnished in 2 in. and 4 in. depths in various standard sizes. Standard Panel Insert and Frame Standard Panel: Dry-type Fin Construction, high filtering efficiency. Heavy steel Panel Insert and Frame. Cleanable. Forty-two square feet of filtering area. Thousands of Staynew Standard Panel Units have given satisfactory service for years. Available in 20 in. x 20 in. x 7 in. size only. Representatives in Principal Cities * ^ Complete Information on Request - FILTERS ALSO MADE FOR INTERNAL COMBUSTION ENGINES AND COMPRESSORS, AIR AND LIQUID LINES, ETC. 1012 Air System Equipment Air Fitters CORPORATION - Milwaukee 2, Wisconsin Manufacturers of PERMANENT and Replaceable AIR Filters for Heating, Ventilating, Air Conditioning, Aircraft and Industrial Use Badger designers and engineers have contributed many of today's most valuable / developments in air filtration, dust, grit, and grease elimination in a' wide variety of industries. BADGER Air Filters are well known for their high efficiency, low air resistance, greater dust-holding capacity, and reduced maintenance cost on an increasing range of modern applications. BADGER Type P Air Filter . . . For Air Conditioning and Ventilating Systems Permanent type, easy to' clean, sturdy and strong, with special BADGER filter mesh design that holds dust through com plete depth while providing minimum air resistance. Dual purpose expanded metal screen deflects air stream and protects. filter media. Vents in frame aid in quick cleaning, thorough draining. Standard 1 in. and 2 in. sizes from 640 C.F.M. to 1000 C.F.M. Special sizes to meet all applications. APPROVED BY UNDER WRITERS' LABORATORIES, Inc. BADGER Type HD Industrial Filter for Extra Heavy Duty and In dustrial Air Cleaning Services BADGER REPLACEABLE AIR FILTER for domestic and commercial forced warm air and air conditioning units. A new, dry replaceable filter. Media is odorless, fire-resistant glass-fibre. Ribbed con struction on both sides of filter insures complete air filtration with 25% greater filtering surface/ Long life assured by sturdy cardboard frame cemented to rib structure. Standard 1 in. and 2 in. sizes. Specially designed for -use on in dustrial ap plications, Badger Type HD is made in 2 in. and 4 in. sizes, and capaci ties from 640 cfm to 1000 cfm. Permanent type, with high dust-holding capacity, effective, sturdily constructed filter media protected by deeply crimped layers of expanded metal screen, and heavy arc welded frame. BADGER HOLDING FRAMES Badger's special "SlipGroove" holding frame design provides greater filtering capacity with a minimum of space. Compact, sturdy, ex tremely strong and rigid, this frame construction also simplifies filter re moval and cleaning. Available in V-type, in straight banks, or adaptable to special requirements. BADGER Grease Filter A new de sign in all metal Per manent type filter that is an absolute necessity in kitchens, gal leys, and wherever grease-laden air is a fire hazard and a maintenance problem. Filter media assures greater efficiency in air circulation and ventilation, increased working comfort and safety, and protec tion to motors, brushes and mechanical \ equipment. Available in 2 in. thickness, adaptable to a wide variety of applications. Complete bulletins, specifications, test and performance charts may be obtained on all BADGER. Per manent and Replaceable Filters, as. well as ready engineering assistance on special problems. 1012 Air System Equipment Air Filters Farr Company Manufacturing Engineers Los Angeles California FAR-AIR FILTERS* for all types of industrial use HERRINGBONE CONSTRUCTION FAR-AIR STANDARD PANEL FILTER For Ventilation For Grease i is C.F.M. CAPACITIES CL 66 OF STANDARD * O. X>. v0 c I FILTERS BASED s "o ON VELOCITY USED > c 0" 5 u? o> .5 o v* n'or 16^125' 2D*i2ir tray 346 2.40 .06" 390 2.70 .07" 433 3.00 .09" 476 3.30 .10" 519 3.60 .12" 563 3.90 .14" 606 4.20 .16" 650 4.50 .19" 693 4.80 .20" 625 700 780 860 935 1015 1090 1170 1250 795 895 995 1095 1195 1290 1390 1490 1590 800 900 1000 1100 1200 1300 1400 1500 1600 1020 1145 1275 1400 1530 1655 1780 1910 2035 Based on our recommended face velocity of 519 ft per minute, Far-Air filters deliver 50% more air with lower pressure drop. Filters are all metal, permanent construc tion . . . Installation of Far-Air Filters, ef fects a saving not only in initial costs but. maintenance as well--you need only % of the filter area, with a Far-Air filter. Low .Pressure Drop . . . More Air Delivery . . . High Efficiency Large Dust Holding Capacity . . . Easy Cleaning-- these Far-Air features are the resutt of Farr's radically different crimped wire screen filter construction. Of paramount importance to heating and refrigeration engineers is the fact that Farr Filters provide a filter area equal to the fin coil area. This special feature eliminates clumsy V-shaped additions on vent ducts usually necessary with other type filters. PROGRESSIVE LOADING As entering orifices of Far-Air Herring bone Construction Filters are loaded, air direction changes, flowing past the front loaded surface and progressively loading the dean screen mesh that remains. Greater free area permits a larger dust * load with lower pressure drop. The slight difference in pressure drop when a Far-Air Filter is loaded from when it is clean maintains a constant balanced air flow in the air distribution system. CERTIFIED PERFORMANCE You can depend on Far-Air Filters to deliver the performance claimed for them . . . Farr Certifies filter performance data. For full information about other types of FAR-AIR FILTERS, write: FARR CO., Dept. HVG, 2615 South West Dr., LOS ANGELES 43, CALIF. 1013 S Air System Equipment Air Filtera and Cleaners Owens-Coming Fiberglas Corporation Toledo 1, Ohio Dust-Stop Air Filters are replaceable impingement-type filters for use in all systems in which air is moved mechani cally--central heating, ventilating and air-conditioning systems, and forcedwarm-air furnaces. Dust-Stops provide high air filtering efficiency. They are constructed of packs of glass fibers (Fiberglas*),' coated with an adhesive, faced with a metal grille, and bound on the edge with a fiberboard frame. The-Fiberglas fibers, packed to proper density; form an exceptionally effective -medium for air filtration. Being glass, they are inorganic, chemically stable, resistant to heat and corrosive vapors. And being of glass, they do not absorb the nonodorous, nonevaporating adhesive with which they are coated. Each im pinged particle of dust is quickly soaked, acting as a wick to carry adhesive to other particles. Thus, the adhesive remains effective until the filter is so heavily loaded with dust that resistance to air flow calls for replacement. - A minimum of manpower and time is required in replacing economical Dust- Stops--and they can be obtained quickly from near-by suppliers. Dust-Stops are made in two standard types: No. 1 (1 in. thick) and No. 2 (2 in. thick). Both are available in several sizes. 1014 Air System Equipment Air Filtera and Cleaners Owens-Coming Fiberglas Corporation Offices Atlanta, Ga. Boston, Mass. Buffalo, N. V. Chicago, III. Cincinnati. Ohio Cleveland, Ohio Dallas, Texas Detroit, Mich. Los Angeles, Calif. New York, N. Y. Philadelphia, Pa. Pittsburgh, Pa. St. Louis, Mo. San Francisco, Calif. Seattle, Wash. UISPMIs?PeJfl|fJrTirL^r aanird ffirlatmeress TWO TYPES OF FRAMES-- four filters deep holds four No. 1 Dust-Stop Dust-Stop Air Filters may be in Air Filters (20 in. x 20 in.). "L" Type stalled in banks of either "L" Type or frames can be provided in any size from "V" Type Dust-Stop Air Filter Frames. ' a single unit having one cell at a rated Both types of frames are designed, patent capacity of 800 cfm at a velocity of 300 ed and manufactured by Owens-Corning lineal feet pier minute to a unit consisting Fiberglas Corporation for the convenient of 91 cells with a capacity of 72,800 cfm. handling of Dust-Stop Air Filters. The "V" Type frame contains two "cells" each forming one side of the "V." The choice between "L" and "V" Type : Each cell will hold up to four No. 1 or frames is determined by the frontal area two No. 2 Dust-Stop Air Filters. "V" available. The "L" Type frame requires Type frames take only the 20 in. x 25 in. less depth within the duct or plenum filters. The "V" frames are available in chamber but takes a larger face area than ` any size from a single unit having a the "V" frame for the same cfm capacity. capacity of 2000 cfm to a 98 cell unit with However, it can be set in various arrange a capacity of 98,000 cfm. ments that reduce the required face area All frames are 13-gauge cold rolled 'by increasing the depth. ..steel and are shipped knocked down and -The "L" Type frame two filters deep is crated, complete with all parts and in designed to hold two No. 1 Dust-Stop structions necessary for easy and rapid Air Filters in each ceil. The "L" Type assembly. "L" Type Frame 1015 "V" Type Frame Air System Equipment Air Filters and Cleaners H. J. Somers, Inc. 6063 Wabash Ave., Detroit 8, Mich. Agents in All Principal Cities SOMERS Heavy Duty Industrial Filter AU Welded Vee Type Patent No's. 2008800. 2130107 Somers Hair Glass Filters provide everything required in an efficient air-cleaning* system. ' Consider These Features: High rating for dust, soot and bacteria separation. Require no adhesive, coating or impregnation. Indestructible in normal service. Minimum low-pressure drop. Odorless and non-absorptive. Fireproof. Washable. Permanent--Do not rot nor disintegrate. All welded zinc-plated 20 ga. steel frame. Metal protection strip on apex. Glass cloth between hot-dipped hardware cloth. Glass ribbon seal so air cannot short circuit. Somers Hair Glass Filters consist of a 20 gauge hot galvanized frame holding gal vanized wire cloth packed with hair-spun glass strands. The glass strands are flexible, .do not break up and cannot be drawn into air stream. _ . Hair Glass being chemically inert, has no facility of absorption; it cannot rust and lasts indefinitely in service. Water either hot or cold may be used to clean it, without impairing its efficiency. , These filters eliminate the necessity, the expense and the inconvenience of periodic replacement. . 1016 H. J. Somers, Inc. Air System Equipment Air Filters and Cleaners SOMERS WASHABLE AIR FILTERS All Welded Vee Type Stock Sizes Frame Size . Height and Length Frame Depth Filter Surface Square Inches 8* x 12' 12' x 12* 12' x 20* IS1/*' x 24%' 15%' 15%' * 24%' 15V * 24%' 16' x20' 16' *21%' 16' x 25' 16' x 25' 16' x 25' 16' x 25' (6' x 25' 16' x 25' 16' x 25' 18' x 18' 18' x 18' 18' x 24' 19%' x 19%' x 19%' 19/,' x 19%' - 19Vi' x 19%' m- x 19%' 19%' x 19%' 19%' * 19%' 20' x20* 20* x 20' 20' x 20* 20* x 20' 20* x 20' 20* x 20* 20* x 20" 20' x 20" 20' x 20' 20' x 25' 20" x 25' 20* x 25' 20* x 25' 20* xW 20* * 30%' 23' x2T 231/2' * 23%' 23V * 17V 24' * 25*%' 25' x 20* -26' * 23%' 26' *23%' 26' x 34' 28' * 33%' 29' * 33%' 30' x 15' 30* x 20* 30* x 24' 31' * 23'/** - . " .. 3%' 2%' 3%' 3Mg' we 2 3%' 2 3 2 2%' 3' 3%' IW 3%' 3%' W 3%' 3' 2' 3' ` 3' 3' 3%' 3%' 3*' 2' 2%' 2V 2V*' 3' 3 3%' 3%'. 3%' 2' ' 2%' y/s" 31/*' 3%' 3%' 3%' 3* 3%' 3%' w 2%' 3%' 2%' 3%' 3*4' 3%' 3' w ' 288 288 720 1023 1674 480 mo 384 816 480 624 664 1344 1440 1632 1056 864 1134 1080 480 819 936 995 1053 1170 1696 480 600 780 840 960 1020 1200 1320 1680 600 1020 1560 1800 1800 2400x ' 1656 ' 1621 1068 1872 1800 936 936 2652 1428 3045 1800 1800 1800 3162 . For Average Dry Filter Installations Wet Application 288 C.F.M. 144 C.F.M. 288 C.F.M. 144 C.F.M. 720 C.F.M. 360 C.F.M. 1023 C.F.M. 511 C.F.M. 1674 C.F.M. 837 C.F.M. 480 C.F.M. 240 C.F.M. 1110 C.F.M. 555 C.F.M. 384 CF.M. 192 C.F.M. 8I6C.F.M. 408 C.F.M. 480 C.F.M. 240 C.F.M. 624 C.F.M. 312 C.F.M. 864 C.F.M. 432 C.F.M. 1344 C.F.M. 672 C.F.M. 1440C.F.M. 720 C.F.M. 1632 CF.M. 8I6C.F.M. 1056 C.F.M. 528 C.F.M. 864C.F.M. 432 C.F.M. 1134 C.F.M. 567 C.F.M. 1080 C.F.M. 540 C.F.M. 480 C.F.M. 240 C.F.M. 8I9C.F.M; 409 C.F.M. 936 C.F.M. 468 C.F.M. 995 C.F.M. 497 C.F.M. 1053 CF.M. 526 C.F.M. 1170 C.F.M. ' 585 C.F.M. I696C.F.M. 848 C.F.M. 480 C.F.M. 240 C.F.M. 600 C.F.M. 300 C.F.M. 780 C.F.M. 390 C.F.M. 840 CF.M. 420 C.F.M. 960 C.F.M. 480 C.F.M. I020C.F.M. 510 C.F.M. 1200 C.F.M. 600 C.F.M. 1320 C.F.M. 660 C.F.M. 1680 C.F.M. 840 C.F.M. ` 600 C.F.M. 300 C.F.M. 1020 C.F.M. 510 C.F.M. 1560 C.F.M. 780 C.F.M. 1800 C.F.M. 900 C.F.M-. 1800 C.F.M. 900 C.F.M. 2400 C.F.M. 1200 C.F.M. 1656 C.F.M. 828 C.F.M. 1621 C.F.M. 810 C.F.M. I068C.F.M. 534 C.F.M. 1872 C.F.M. 936 C.F.M. 1800 C.F.M. 900 C.F.M. 936 C.F.M. 468 C.F.M. 936 C.F.M. 468 C.F.M. 2652 C.F.M. ' 1326 C.F.M. 1428 C.F.M. 7I4C.F.M. 3045 C.F.M. 1520 C.F.M. 1800 C.F.M. 900 C.F.M. 1800 C.F.M. 900 C.F.M. 1800 C.F.M. 900 C.F.M. 3I62C.F.M. 1531 C.F.M. Other sizes also available. Send for complete stock size list. Frames zinc plated for%00 hour salt water spray test. Refill may be inserted if necessary. Quotations and further engineering data, including master holding frame drawings will be sent on request. Just a few users of Somers Filters Chemical Plants American Viscose Co. American Zinc & Chemical Co. Davison Chemical Corp. Automotive Frederick Sterns Co. Cadillac Motor Car Co. Chevrolet Motor Car Co. Chrysler Corp. . Fisher Body Corp. . Refrigeration and Air-Cond. ' Frigidare Corp. Norge Div.--Borg Warner Kelvinator Corp. York Ice Machine Co. Ships Amer. Shipbuilding Co. U. S. S. Saratoga U. S. N. Lake City, Fla. U. S. N. Daytona Beach, Fla- U. S. N. Vero Beach. Fla. U. S. N. Jacksonville, Fla. Utilities and Municipalities City of'Kenosha Michigan Consolidated Gas Co. Detroit Edison Co. New York Edison Go. Westchester Lighting Co. Dep't. Stores S. S. Kresge Co. . S. H. Kress & Co. Food Processing Awrey Bakeries Gilbert Chocolate Co. Kellogg Co. Manufacturers Buffalo Forge Co. Burroughs Adding Machine Co. CJarage Fan Co. Curtiss-Wright Airplane Co. Glensder Textile Co. Hoover Co. ' International Heater Co. Kearney & Trecker Corp. Killian Mfg. Co. ' National Carbon Co.. Inc. Pittsburgh Plate Glass Co. Rockford Machine Tool Co. Sunstrand Machine Tool Co. 1017 . Air System Equipment Air Filters and Cleaners B. F. Sturtevant Company Division of Westinghouse Electric Corporation Hyde Park, Boston, Mass. PRECIPITRON* Westinghouse Precipitron--the electronic air cleaner--now makes possible greater efficiency in removing dust, dirt, smoke and other foreign particles from the air. The Precipitron cells are simply installed in the forced-air or air-conditioning system and sealed so the air must pass through them (see illustration). Dirt, smoke and soot pass through an electro- static field, receive a positive charge, and are drawn to a collection plate of opposite polarity where they remain until flushed down the drain. , ADVANTAGES The following major advantages make Precipitron the complete answer to mass air cleaning in all buildings using forced ventilation or air-conditioning duct sys tems. Unmatched Efficiency -- Precipitron removes particles as small as 1/250,000 of an inch in diameter, and removes 90 per cent of 'all air-borne dust particles in the air stream. . Easily Cleaned--New vertical collector plates make it still easier to clean the Precipitron. Collected dirt is flushed harmlessly down the drain. Safe--Precipitron isapproved by U nder- writers' Laboratories without installation of additional fire protection apparatus. Nothing to Clog--Precipitron creates only negligible resistance in the forced air -system under continuous operation. No Moving Parts--Precipitron has no morejnoving parts than a storage battery. Trademark registered in U.S.A. TESTS PROVE EFFICIENCY Accepted testing methods previously conducted on a weight basis have been obsoleted since Precipitron entered the field of air cleaning. The Blackness Test reproduced here provides greater accuracy, approximates the actual particle count and is made without the addition of artificial dust. The efficiency of Precipitron by Weight Test showed over 99% and by the Blackness Test as high as 90% at 300 FPM per 36 in. . Uncleaned Air Mechanically Cleaned Air Electronically Cleaned Air Test Comparisons Proving High Efficiency of Precipitron ' 1018 Air System Equipment Air Filters Cleaners MAJOR COMPONENTS OF INSTALLATION WITH AUTOMATIC WASHER CELLS The cell itself, known as the Collector, is composed of two duplicate sets of high voltage and ground plates mounted be tween two load-bearing end plates laced together by steel bars, angles and channels to form a rigid structure. Precipitron is built in sizes to handle from 1260 cfm (for a single 24 in. cell) to any desired volume through multiple cell arrangements. Cells are available in two sizes: 24 in. x 24 in. x 26)4 in. and 36 in. X 24in. X 26)4 in. For 90 per cent efficiency, the 24 in. and 36 in. cells are rated at 1200 and 1800 cfm respectively. For 85 per cent efficiency, ratings are 1500 and 2250 cfm. IONIZERS Made of formed sheet steel, top, bottom and side plates welded together to form a rigid frame. The ground tubes run ver tically between the top and bottom plates. Two sets of Ionizing wires are used; one, the usual vertical set, and another set stretching horizontal at the-ends to pre vent leakage around the ends of the wires. POWER PACKS The Power Pack is employed to change the a-c supply to d-c of suitable voltage to charge the Ionizers and Collector Cells. They furnish approximately 6 kv (6000 volts) d-c to the plate circuit of Collector Cells and. 13 kv (13,000 volts) d-c to the Ionizer circuit. The Power Packs contain rectifier tubes, Inerteen impregnated capacitors, and an indicator system and panel. Cabinet doors, opened by a thumb screw, provide time delay, simultaneously breaking the primary circuit, -if' this has not already been done at* another point. Three types of Packs are available, dif fering principally in the number of cells they will energize. These types are: Type L--Suitable for 4 to 16-36 in. cells. Type S--Suitable for 1 to 5-36 in. cells. Type M--Suitable for 1-24 in., 2-24 in., 1-36 in., or 1-24 in. and 1-36 in. cell. - All Power Packs are designed to operate from 115 volts * 5 volts on single phase a-c systems. this header vertically up and down over the face of the cells. The secondary ele ment of the washer is the control of its automatic operation which is described under "Control Panel." * Illustration below shows complete wash er with back vanes closed, the washing being done with vanes in this position as air is prevented from going through this group and forced through the balance of the cells where it is cleaned. Header is moved by means of roller chains driven through a gear reducer by a )4 hp, 220-440 volt, 3 phase motor. A limit switch controls up and down travel of header. CONTROL PANEL This panel operates the two traveling headers of the washer automatically once they have been placed in position on either side of the cell group to be washed and the momentary, contact pushbutton on the panel has been pushed. Control Panel comes fully assembled, is internally wired and ready to be set in place. The control circuit requires 110 volts single-phase (25 or 60 cycles) of sufficient capacity to carry aK^P motor. The power circuit requires either 220-volt or 440-volt, 3-phase, 25 or 60 cycle power of sufficient capacity to handle two )4 hp motors in reversing service. FULL DETAILS--For complete infor mation on this new principle of cleaning air electronically, write Westinghouse Electric Corporation, Box 868, Pittsburgh 30, Pa. or contact your nearest Westing house office. TRAVELING HEADER The basic element of the automatic washer is a set of spray nozzles which spray either water, compressed air or adhesive on the Precipitron cells. Water nozzles are mounted on a horizontal head er and a mechanism is provided to move Control Panel Travelling Header 1019 Air System Equipment Filters Research Products Corporation Madison 3, Wisconsin RESEARCH AIR FILTERS FOR HEATING AND VENTILATING U. S. Patent 2070073 U. S. Patent 2294478 RESEARCH AIR FILTERS No. "200" Series. When this Re-Fil-Able filter becomes dirt clogged, the wire grids are unhooked, the filter pad replaced. Pads fit snugly, sealing against air leaks. (Can be Rip-Cleaned). No. "200" Series Self-Sealing Edge. The "200" series filter is made ]/i in. "oversize" so it ex tends over the sides of the wire grids thus sealing without the need of sealing felts. This prevents the by-pass of air around filter. Re-Fil-Able. When the ultimate dirt holding capacity of the pad is reached it can be replaced with one 2 in. pad or two 1 in. pads. The wire grids are permanent --can be used over and over again. Rip-Clean. When the filter pad be comes surface clogged with particles of dirt, lint, etc., the wire grids are unhooked, the two top layers of the pad rolled off and removed, thus Rip-Cleaning for further use. The removal of surface dirt in this manner may be repeated 5 times-- thus extending the useful life of the filter. No. "100" Series efficiency. Especially adaptable to heat ing, ventilating and air conditioning systems. . Research^ Air Filters are used ex tensively wherever air is moved mechani cally in forced warm air heating, venti lating and air conditioning systems be cause of their superior capacity for catch ing and holding dust, dirt, soot and pollen. Tests for both the No. 100 and No. 200 air filters show a 91% dust removal efficiency (with 80-20 dust) and 99% pollen removal efficiency. No. "100" Series. This fiber framed filter is designed so the entire unit is easily replaced when its dirt holding capacity is reached. Offers high dust removing Research Filter* Banks. Research Air Filters are used extensively in filter banks--both flat and V types. Write for technical data booklet. 1020 Air System Equipment unitldilyine American Moistening Company Established 1888 Atlanta 2, Ga. Providence 1, R. I. Boston 9. Mass. Charlotte 1. N. C. UNIT HUMIDIFYING AND AIR CONDITIONING EQUIPMENT A few of many AMCO products with a Long Record of Dependable Performance Self-cleaning Atomizers Sectional Humidifiers. Amtex Humidifiers. Hand Sprayers. Mine Sprays. Fabric and Paper Dampeners. Mechanical Psychrometers. Electro Psychrometers. Sling Psychrometers. Hygrometers. The Amco line of devices for the supply, maintenance and control of humidity is com plete in its ability to meet any presented problem of applied humidification. Used independently or as an adjunct to Central Station equipment, these devices auto matically maintain any required humidity condition in a capable uniform performance. AMCO ATOMIZER--No. 5 Quality and quantity of spray are maintained even under adverse conditions because this atomizer is automatically self-cleaning. When the compressed air supply is shut off, either manually or in response to a humidity control, both air and water nozzles are thoroughly cleaned. AMCO HUMIDITY CONTROLS Compressed Air Operated An extremely accurate and active device operated by compressed air which assures a regulation of humidity within exceedingly close ranges. AMCO HUMIDITY CONTROL Electrically Operated Similar in principle to the Compressed Air Type except that the hygroscopic element operates electrical contacts which control the units. AMCO EVAPORATIVE COOLING UNIT The Amco System of evaporative cooling contributes to smooth production at high speeds in two ways; it main tains the percentage of relative humidity best suited to the fibre and process involved, and at the same time promotes the comfort and efficiency of personnel by obtaining the maximum practical cooling effect from, evaporation. It does this by introducing outside air into the room in vary ing amounts, regulated in accordance with climatic con ditions and inside requirements. . A ductless system--very flexible and portable. Can be applied in conjunction with an existing humidifying system. 102i . Air System Equipment R> cooling April Showers Company 4126 Eighth Street, N.W. Washington 11, D. C. (Trade Mark Reg. U. S. Pat. Office) . AUTOMATIC EVAPORATIVE ROOF COOLING . Distributors and Dealers in Principal Cities Air System Equipment Cooling Towers Lilie-Hoffmann Cooling Towers, Inc. Exclusive Builders of Cooling Towers for 46 Years 4239 Duncan Ave., St. Louis 10, Mo. Two Modern Plants--St. Louis. Mo. and Plainview, Texas INDUCED DRAFT TOWERS New type filling reduces static pressure; uni formly distributes air and water over effective tower area. Ring gravity distribution system requires only one riser pipe. Each cell main trough equipped with Weir gate, giving in dividual cell control. Teco timber connectors develop 100 percent workingstressof members. FORCED DRAFT TOWERS Three-tier zigzag pattern spray eliminator system cuts drift loss to a minimum. Fan opening covered by galvanized screen wire. Built in single or multiple cells. Continuous design improvement, based on installation studies, presents record of unfailing operation. APRIL SHOWERS is the trade name of an EFFICIENT fool proof method of pre venting roof heat penetration or solar infiltration causing excessive heat in upper floors and in factories, stores, theatres, shops, etc. City water under normal city pressure is usually adequate to serve your APRIL SHOWERS system. The sun operates it. Roofs LAST LONGER, greater comfort is assured, production during the summer's heat is kept apace, errors through fatigue are avoided, and MANAGEMENT acclaims APRIL SHOWERS a GOD-SEND. DEALERS and CONTRACTORS--AN ANNOUNCEMENT Any established air conditioning engineer, contractor, dealer or any plumber and kindred workmen can obtain APRIL SHOWERS supplies, plans and instructions for erecting APRIL SHOWERS for you or your clients. Write for "INTRODUCING ' APRIL SHOWERS'' which is a loose-leaf bound book for Installers and Dealers. Contractors, Dealers and Installers be sure to share in the APRIL SHOWERS post-war prosperity. You are not required to inventory any merchandise. You purchase only such equipment as is needed for each installation. You set your own SELLING PRICE. You share PROFITS with NO ONE. Hundreds of installations, from Boston to Los Angeles have been made. Write for information and address of nearest distributor. Inquiries will be answered promptly. Estimates free upon request. . APRIL SHOWERS controlled roof cooling is protected by U. S. Patents; beware of imitators or infringers. . APRIL SHOWERS steam humidifying heads now ready. Developed in 1933*34. 1022 ATMOSPHERIC SPRAY TYPE Generally offered in capacities up to 3000 gpm. Distribution by galvanized pipe header with smaller lateral arms, equipped with non-cloggingspray nozzles. Louvres fit into mast slots--no nails re quired. Recommended where cost is prime factor; and close approach to`wet bulb is unnecessary. Rigidly braced and tied together to prevent warping and buckling. ATMOSPHERIC DECK Distribution by either wood trough, or wood pipe header system. Removable deck grids. Special L-H drift baffles on deck supports prevent entrained water loss. Generally 12 ft wide--can be made any length or height. 1023 Air System Equipment Cooling Towers The Marley Company (Fairfax and Marley Roads,) Kansas City 15, Kansas Branches or Agents in Principal Cities Spray Nozzles and a Complete Line of Water Cooling Equipment MARLEY Humi MARLEY Small S-Piece Noz zles for Brine Spraying, Air Washing and Similar uses. MARLEY 1-Piece Noalesfor Cooling Towers, Spray difying Nozzleadds moisture to air in open rooms or duct system. Ponds, etc. MARLEY NATURAL MARLEY PATENTED NON-CLOG SPRAY NOZZLES DRAFT TOWERS Made in scores of types and sizes. Practically any metal or Practically unlimited alloy the purpose may demand. Bulletins 101, 102 and 103. range of closely graduated sizes, entirely shop fabri cated. Minimum initial, maintenance and opera ting costs. Many exclusive MARLEY advantages. Bulletins 201 and 2021 LARGE MARLEY INDUCED DRAFT TOWERS. Both Conventional and Double-Flow types, for heavy SMALL INDUCED DRAFT TOWERS duty water cooling services of all kinds. Any capacity, with one fan or many, individually engineered to the exact requirements of each installation. MARLEY patents cover Small, self-contained, a variety of important features for extreme operating steel units for 2 to 170 ton flexibility, high efficiency and economy. service, to go indoors or Redwood is the standard structural material. Steel, out. Horizontal air flow. transite and other special materials require much higher Smaller sizes shipped all priorities for the war's duration. assembled. Larger sizes Conventional Induced Draft (pictured above in steel are entirely shop fabri construction; below right, of Redwood) well adapted to cated for fast, simple as most large capacity services. Bulletin 603., sembly at the location. Double-Flow Induced Draft (below left) for unusually Bulletins 504 and 505. large capacity services. Bulletin 700-A. . Also Many Other Types of Towers, Spray Ponds and Related Equipment 1024 Air System Equipment cooiint Towers J. F. Pritchard & Co. Fidelity Building, Kansas City 6, Missouri New York, Pittsburgh, Houston, Atlanta, Tulsa, Denver, Salt Lake City, El Paso, Omaha Engineers--Constructors--Manufacturers for the Refrigerated Industries Specialized Equipment for Use with Refrigeration and Air-Conditioning ENGINEERING-CONSTRUCTION Many years of experience, cover ing large plants and small, all types of cold storage and refrigeration processing, qualify Pritchard to handle complete plants, revamps or additions, from plans to opera tion, on a full-responsibility turn key basis that saves time and money. Any part of the complete Pritchard service (process designing, economic studies, plant layout, unit instal lations, etc.) is available separately. AIR TREATER--Renders Air Germicidally Pure--Removes Dust, Pollen, Smoke and Other Solid Par ticles and Microorganisms--Con trols Humidity--Refreshes Air by Adding Oxygen--A compact "pack age" unit for simple installation in any duct system. Induced Draft Cooling Tower AIR & GAS DRYING EQUIP MENT--Total or Controlled De- humidifying--Adaptable for Various Solid or Liquid Adsorbents--Stand ard units, all capacities, automatic or manual regenerating. HEAT EXCHANGERS AND CONDENSERS--All types of heat transfer apparatus, high or low pres All-Metal Spray Tower Indoor Forced Draft sure, shell and tube, atmospheric or submerged, standard or special designs. wall casing. Valuable exclusive features Pritchard has the facilities and application include "Featherweight Fans" of wrought knowledge to meet any need with high- monel, superior air delivery per horse efficiency units. power; trouble-free gear drives, either COOLING TOWERS--Pritchard has long been one of the foremost suppliers of cooling towers of all types and capacities. Specifications, prices, ratings and applica tion recommendations furnished promptly. Small Mechanical Draft Towers-- right-angle type with flex-coupled shaft to motor outside of fan ring or the famous ,`Sealdflow" unit streamlined to the fan hub, mounting motor and gears vertically on the fan shaft; low pumping head, uniform water distribution. Forced or induced, for indoors or out. EVAPORATIVE CONDENSERS AND Self-contained steel-cased units, easy to COOLERS--Complete welded, galvaniz install, 2-ton capacity and up. ed, self-contained condenser; also for cool Natural Draft Spray Towers--With ing jacket-water and lube oil of engines, or without deck filling, with or without and industrial processing. Maintain ac basins. Simple to assemble; slip-fit louv curate temperatures, eliminate freeze-ups, ers; Redwood or all-metal; any capacity. save space, simplify piping. All prime Natural Draft Deck Towers--Cele surface coils, readily cleanable. brated Pritchard "drift retrievers" mini "AIRDFIN" AIR-COOLED HEAT mize drift loss without restrictive second EXCHANGERS--New efficiency and ary louvers. Free, air flow gives higher economy for many cooling and condensing efficiency. Rugged construction;, low- functions, i.e.. steam and other vapors, pressure, uniform water distribution. jacket water, oils, gases, quenching baths, Induced Draft Towers--Extra-sturdy etc. High-efficiency fan propels air through structural members and joints; double- banks of finned tubes. No water problems. 1025 Air System Equipment cooling Tower, - Rogers Diesel and Aircraft Corporation manufacturers of COEY FLOATING FILM COOLING TOWERS 1120 Leggett Avenue New York 59, N. Y. Patented Spray Eliminator . . . sloping blades discharge accu mulated water droplets back into water distri bution trough. Spray is never evident. Fan Drive Motor ... protected against moist ure, this motor will stand up under severest con ditions. Light in Weight ... . the Coey tower is lighter in weight than other towers of similar capa city because its interior is free of slats and baffles. Readily Accessible . . . for cleaning and maintenance due to open interior construction. Fireproof . . . Coey towers are fireproof be cause of all metal con struction. Low Noise Level . .. its quiet operation is out standing. , PATENTED "FLOATING FILM" PRINCIPLE INSURES PREDICTABLE, ACCURATE COOLING . s. Water, pouring in from the top of the Coey Cooling Tower, is met by a counterflow of air at a velocity of approximately 1500 ft per minute. The water flows across this air in a /baling film. At five platform stages this entire floating film of water is broken into droplets substantially all the same size and each droplet is surface cooled. Size is important because when droplets are too large they do not cool enough, when they are too small they evaporate completely. . Five times during their downward course, the droplets are collected into, floating film and cooled surfaces are mixed with warmer droplet centers for an overall lower tem perature. This five stage operation insures precise control . . . maximum cooling. There is a Coey tower for every cooling requirement. Write Department A,' Cooling Tower Division, Rogers Diesel and Aircraft Corporation, for complete information. 1020 Air System Equipment Water Cooling Equipment Company 8613 New Hampshire Avenue Affton Station, St. Louis 23, Missouri MANUFACTURERS OF MECHANICAL DRAFT AND ATMOSPHERIC COOLING TOWERS FORCED DRAFT COOLING TOWER 41,500 g.p.m. twenty-two cell, heavy duty, doub le forced draft cooling tower . . . ,,^ , equipped with twenty-two 12-foot diameter adjustable pitch, propeller type fans. REDWOOD "WATERFALL" ATMOSPHERIC SPRAY COOLING TOWER Factory fabricated and shipped knocked-down with all hardware, spray headers and spray nozzles. Complete erection in structions and drawings are furnished to assist in the assembly of the tower. These towers are portable and can be knocked-down - and moved simply by removing the louvres and bolts. Shipment can be made from stock. Write for Bulle tin 125-A. INDUCED DRAFT This type of cool ing tower is rec ommended for in stallations where noise is a prime factor of consider ation. The noise of the mechanical items is carried upward and discharged into the air. The mechanical draft cooling tower assures a positive cooling "of the water to a specified temperature inde pendent of wind velocity. TIMBER JOINT CONNECTOR Special cast iron timber joint con nector used to develop the full strength of the timber joint, an accomplishment almost impossible to achieve by bolt ing. Patent No. 2.280,121 NOZZLES REDWOOD r `Whirlcone' non-clogging ATMOSPHERIC low pressure DECK TYPE COOLING centrif uga type spraj nozzles foi TOWER Patent No. 2,123,697 .spray ponds spray towers and other uses. Write for Bulletin 76-A PRODUCTS Heavy duty forced and induced draft ENGINEERING - / cooling towers, standard induced and forced draft towers, induced draft coil towers, atmospheric deck cooling towers, atmospheric spray towers, spray ponds and spray nozzles. Design and construction are based on sound engineering principles to meet speci fic requirements for cooling performance and structural strength. Redwood, steel or other suitable materials are used. 1027 Air Conditioning spray Nozzles Jos. A. Martocello & Company 229-31 North 13th Street, Philadelphia, Pa. SPRAY POND AND ATOMIZING SPRAY NOZZLES MARTOCELLO Atomizing Spray Nozzles produce a uniform, good, wide spray with less friction and at minimum pressure require ments. Nozzles illustrated at the right are manufactured with precision in Brass Forgings and Bar Stock. Their design* has been thoroughly tested for re sults and durability and will give you satisfaction. , Successful, Efficient Re sults depend largely upon selecting the proper number and type of Nozzles with Brass or Monel cap suitable for your job. Therefore we suggest you send us your specifications as we also have several Types other .than illustrated and we will gladly assist you to obtain the most efficient application. MARTOCELLO Spray Pond Nozzles of a sturdy one-piece construction --cast of High Grade Red Brass with Inlet and Outlet accurately machined, are less clogging, offer less friction and give unsurpassed overall effi ciency. MARTOCELLO CLUSTER CASTINGS Sturdy Grey Iron Construction with large area for reduced friction and even distribution. They are Hot Dipped Galvanized after fabrication. Furnished with Nozzles and continuous Standard Steel Long Sweep Galvanized Pipe Spray Arms and Center Nozzle Nipple in accordance .with layout required. ' Sizes Carried in stock for Prompt Shipment 1% in. P. S. Outlet, 3 in. P. S. Inlet and 2 in. P. S. Outlets, 4 in. P. S. Inlet Cluster Castings. WRITE, PHONE OR WIRE For Bulletin listing Capacities and Prices. Prompt shipments from stock. 1028 Air System Equipment Spray Nozzles . Monarch Manufacturing Works, Inc. 2731 E. Westmoreland St., Philadelphia 34, Pa. SPRAY NOZZLES FOR WATER AND OIL NON-CLOG AIR WASHER NOZZLES produce an exceptionally efficient, evenly distributed hol low cone spray. Single large tangential inlet to swirling chamber minimizes any possibility of clogging. Also available in % in. to 1 in. pipe sizes inclusive, and of Brass, Stainless and Monel. Capacities: Gallons per Hour Sizes * Lb Operating Preuure ' Pipe /*' . Orifice 69 * 61 61 x 53 53 *6 / "4 V* * *6 Vg'S % 10 5.7 6.4 14.1 23.2 31.0 45.0 73.4 85.8 20 . 6.25 7.5 9.0 18.7 32.0 43.9 64.2 105 116 30 53 7.5 8.8. 10.7 22.5 40. 54.5 75.0 137 140 40 6.15 8.3 10.0 11.6 25.0 47.3 63.0 90.0 155 164 Fig. 631 Fig. 69 flvll |U1^9| llittigll llBnli JfjPssUs: HS9U IMiXSI 19 Fit. F-SO AIR CONDITIONING AND OIL BURNER NOZZLES Water Capacity in Gallons per Hour Nozzle No. |.35 1 1.65 " 2.00 250 3.00 3.50 4 on " 5.00 5.50 6.00 7.00 25 1.03 1.36 1.56 1.86 2.20 ' 2.22 2.55 2.90 Lb Operating Preuure 40 60 80 .57 .69 .83 .75 .89 .99 .94 1.14 1.23 1.13 1.45 1.64 1.39 1.62 1.85 1.77 2.11 2.46 2.00 2.42 2.77 2.32 2.77 3.21 2.88 3.57 4.09 2.96 3.75 4.31 > 3.35 4.01 4.78 . 3.91 4.60 5.17 100 .92 1.12 1.40 1.86 1.95 2.80 3.16 3.68 4.59 4.78 5.23 6.00 Produce-finest breakup possible with direct pressure only. Capacities above are on water. "Nozzle No." is capacity on 34 second Saybolt viscosity oil at 100 lb pressure. Larger sizes up to Nozzle No. 60.00. Furnished of all Brass for Water--Stainless Steel tip and disc for Oil. Standard with }/% in. or 34 in. female pipe Brass adapter and Monel gauze strainer. IjPRAY POND NOZZLES For recooling condenser water, etc. Operate on pressures from 5 lb upward. Made of Cast Red Brass and in pipe sizes 1 in., 134 in., 2 in., and 234 in. Capacities from ,4.1 to 88 gpm at 7 lb pressure. Write for Detailed Catalogs 1029 Air System Equipment Heat Transfer Surfaces Condensers Acme Industries, Inc. Jackson, Michigan Representatives In Principal Cities REFRIGERATION AND AIR CONDITIONING EQUIPMENT FREON CONDENSERS AMMONIA CONDENSERS Shell and Tube Type for use with Am monia, Freon or other refrigerants. Standard or special designs to meet vary ing water temperatures available and condensing temperatures desired. EVAPORATIVE CONDENSERS All prime surface for Freon or Ammonia refrigerants. Heavy galvanized iron casing, inside treated with rust resistant paint. Capacities to 100 tons. DRY-EX COOLERS Refrigerant in tubes, solution baffled through shell. For cooling water, brine, glycols or alcohols by direct expansion of refrigerant. HEAT INTERCHANGERS Shell and coil units for small capacities. Shell and tube units for large installations. 16 standard models from one ton to 180 tons capacity. PIPE COILS Fabricated in all shapes and sizes from yi in. IPS to 2 in. IPS. Special assemblies available for custom built evaporative condensers, raceway coils. FIN COILS Direct expansion coils with liquid distri bution for Freon. Low temperature, wide fin spacing all steel coils hot dip galvanized for flooded ammonia. . I Acme Industries, Inc., also manufactures flooded water and brine coolers, receivers, oil separators and lowside specialties. . WRITE FOR CATALOG ON ANY PRODUCT 1030 Air System Equipment Heat Transfer Surface /Aerofin Corporation 410 So. Geddes Street Syracuse 1, N. Y. AEROFIN Standardized Light-weight Heat Exchange Surface Branch Offices CLEVELAND, CHICAGO, NEW YORK. PHILADELPHIA, DETROIT, DALLAS. TORONTO Aerofin is the modern Standardized Light-Weight Encased Fan System Heat ing and Cooling Surface originated by Fan - Engineers to meet the present and future requirements of this highly specialized field. All Standard Aerofin Units are furnished as completely encased Units, ready for pipe and duet connections. The patented casings are built of pressed steel and are exceptionally strong and rigid, protecting the Unit from all the strains of pipe connections and expansion or -con traction in service. The casings are flanged on both faces, top and bottom, and tem plate punched for bolting together adjacent Units, or for duct connection. . or for installing in ducts. May be installed horizontally or vertically. Used on any two-pipe steam system for preheating or re heating. Modulating control on preheaters. Available in 13 lengths and 3 widths, from net face area of 2.76 sq ft to 26.28 sq ft. Fie. s Aerofin Non-freeze heater (Fig. 1) is non-freeze, non-stratifying spiral fin coil built into casing for air conditioning units Flexitube Aerofin (Fig. 2) is distin guished from all other developments by its. off-set tubes, so arranged as to absorb all expansion and contraction strains. Headers--Steel. Tubing--% in. O.D. copper, admiralty or aluminum. . Joints--Where admiralty *or copper tubes are used together with bronze or steel headers tubes are brazed to headers. Where both aluminum tubes and headers are used tubing is welded to headers. Casings--Copper, .aluminum or galvan ized iron. _ Design--Constructed with headers on opposite ends making possible installation of units with tubes horizontal or vertical. 1031 Aerofin Corporation Air System Equipment Heat Transfer Surface Aerofin Corporation Air System Equipment Heat Transfer Surface Fig. 6 Universal Aerofin (Fig. 3) is distin guished by its "S" bend construction of tubing, units designed with steel headers on opposite ends, the ends of the "SM bends being connected thereto by com pression nuts, the bends taking care of the expansion and contraction of the tubing. Recommended where close control is desired. Headers--Pressed steel. Tubing--1 in.O.D. Copper or admiralty. Casings--Copper, aluminum or galvan ized iron. Booster Aerofin--straight tube type, single pass construction for pressures from 1 to 200 lb gauge. ^ Headers--cast bronze. : Tubing--in^ O.D. copper. Casings-^opper, aluminum or gal vanized iron. Recommended where small coils are needed or to raise the air tem peratures in-branch ducts. Fig. 4. Fig. 6 High Pressure Aerofin (Fig. 4) is of continuous tube design, being recommend ed where extremely high pressures of steam are used. Headers--Pressed steel. - Tubing--1 in. O. D. Copper or admiralty. Casings--Copper, .aluminum or gal vanized iron. ' Narrow Width Aerofin: (Fig. 6) recommended for water cooling or for flooded Freon systems. Made in straight tubes only with headers on opposite ends, joints between headers and tubing being brazed. Construction similar to Flexitube Aerofin. 1032 Fig. 7 Aerofin Continuous Tube Water Coils (Fig. 7) are designed for air cooling by circulating cold water through the Aerofin and air over extended fin surface. Made for either horizontal or vertical air flow. ' . Tubes and fins are copper, completely tinned with permanent metallic bond between fin and tubes'. Headers are made of one-piece cast bronze and casings of heavy galvanized iron or copper. Units tested to 1000 lb hydrostatic pressure. ` Fig. 8 Aerofin Cleanable Tube Units (Fig. 8) for cooling only made with headers removable- to . permit cleaning tubes. Recommended for use where sediment or scale forming chemicals are present in the cooling water. Headers--Cast iron. Tubing--Copper or admiralty. Casings--Copper or glavanized iron. Fig. 9 Aerofin Direct Expansion Units: (Fig. 9) Centrifugal Header Type--Re commended where control of rows in direction of air flow is not required. Aerofin Sizes Flexitube: 13 standard lengths, three widths,.one and two rows deep. Narrow: same as Flexitube. Universal 17 standard lengths, two widths, one and two rows deep. ContinuousTube: 13standard lengths, three widths, 2-3-4-5 and 6 rows deep: Cleanable Tube: 17 standard lengths, one width, 2 and 4 rows deep. Direct Expansion: Centrifugal Header--11 standard lengths, three widths, 2-3-4-5-6 rows deep. . Steel Supporting Legs: 18 in. and 24 in. high. Punched same bolt hole centers as standard casings. Quickly attached. No other foundation required. Sale: Aerofin is sold only by manu facturers of nationally advertised Fan System Apparatus.- List upon request. Write Syracuse for Heating Bulletin G-32; Direct Expansion Bulletin DE-34 on refrigeration type units; Continuous Tube Bulletin C. T. 34 for Water Cooling Coils; or phamplet on Cleanable Type Aerofin for cooling. 1033 Air System Equipment Heat Exchangers Condenser Service & Engineering Co., Inc. 95 River Street HOBOKEN, N. J. Elizabeth, n. j. pttsville. pa. scranton, pa. DESIGNERS AND MANUFACTURERS OF Steam Condensers--Steam Jet Air Ejectors--Lubricating OH Coolers --Feedwater Heaters--Fuel Oil Heaters--Evaporators--Distillers-- Oil Refinery Heat Exchangers--Process Industry Heat Exchangers-- Strainers--Feedwater Filters--Grease Extractors--Sewage Ejectors --Pumps--Oil and Water Separators--Wizard Condenser Injectors --Flowrites--Salinometer Cocks--American Ball Steam Engines. Twenty years of specialized experience. designing, building, fabricating and a special feature--a designing organization which also services heat exchangers-- assures sound design, quality construction and economical operation. Conseco builds heat exchangers for all types of air con ditioning systems using, Freon, COs, am monia, methyl chloride and SO*. Conseco maintains a highly-trained ser vice organization equipped with special tools developed by us to save time, labor and material, ready for action any time of day or night, anywhere on the continent. Heat exchangers are retubed or repaired in the shortest possible time, and at low cost. Tube sheets, tubes, ferrules, all types of packing, and other necessary materials are always stocked, ready for instant shipment. I he keynote of our service organization is fast, accurate, dependable service per formed by competent, properly equipped men working under qualified engineering supervision. Every detail of a Conseco heat ex changer is designed to profit from good and bad features uncovered by years of service work on units of every type and make. This has resulted in the production of simple, efficient units, low in original cost and inexpensive to maintain. Conseco engineers will be glad to serve you. If you want fast action, write, phone or wire. Conseco double-bank heal exchanger installation aboard ship. Air System Equipment Heat Transfer Surface The G & O Manufacturing Company 138 Winchester Avenue New Haven, Connecticut GdO SQUARE FIN TUBING STRAIGHT LENGTHS--U-BENDS--CONTINUOUS COILS THE use of INDIVIDUAL fins results in high efficiency in heat transfer from primary tube, surface to secondary fin surface. Fins of any size or shape may be obtained giving any desired proportion o( primary and secondary surface. A square fin has about 30 percent greater surface than a round fin of a diameter equal to one side of the square. , Individual fins permit of any fin spacing; also, of using fins in groups at intervals along tubes. STANDARD SIZES A--Generous Fin Collar provides large contact area between Tube and Fin. B--Tube expanded against Fin Collar; _ .insures mechanically tight joint, made permanent by bond of high tempera ture alloy--complete thermal contact. C--Free air-flow passages; non-clogging. OX), of Tube w >/.' w >/.' 1' I'/.' Fin Size 7/e' qr'd. W rU I'A'rU W *q?/.' *. m'r-i. Fin Spacing G* 6 6 6 6 6 6 4 Surface per 1 mur Foot 0.60 q. ft. 0.60 aq. ft. 0.67 sq. ft. I.5y*q.ft. 2.40 aq. ft. 4.00 aq. ft. 2.35 aq. ft. RADIATING ELEMENTS FOR ALL HEAT TRANSFER PURPOSES G&O Finned Radiation Coils for industrial applications are available in a wide range of sizes. `- Conseco CO- heat exchangers operating at 1SOO Psi in various Sanger chain theatres. Conseco ammonia heat exchanger installation, Stanley Theatre, Philadelphia. 1034 Universal U-10S Standard No. 10 Send for Catalog and Price List 1035 Air System Equipment The Rome-Turaey Radiator Co. Rome, N. Y. ROME if,Te Helical Fin Tubing Over 100 sizes--for all air heating and air cooling equipment--straight lengths--U bends--Continuous Coils. Blast Air Heating and Air Cooling Coils--Complete range of sizes--Heat transfer and Engineering data by recognized authorities. Special Construction to suit applications. Helical Fin Tube Core Assemblies-- for heat transfer equipment. Copper Convector Rome Copper Convectors for Concealed heating of Homes, Office Buildings and Apartments--many thousands in use. Complete line of sizes and cabinet models. Air System Equipment Fin - Type Radiators The Vulcan Radiator Company 26 Francis Avenue Hartford 6, Conn. MANUFACTURERS OF FINNED TUBES FOR TWO DECADES VULCAN FIN-TYPE RADIATORS, for heating and cool ing are available in steel or copper with attractive grille covers, wall and ceiling hangers. VULCAN is used in rail road cars, ships, hospitals; churches, schools, homes and thousands of industrial concerns for the following reasons: Typical Section of VULCAN made uP to 16 ft in one length. Vulcan-Hartford stamped on every radiator. 1. It is an Accepted Product for performance. 2. Compactness and light weight make installation easy. 3. Uniform heat distribution has been proved by tests,--hot and cold drafts are eliminated. 4. Installation costs are reduced since 500 sq ft can be on one continuous line. Heat Output for 2 in. IPS is 5.25 sq ft per lineal foot with 1 lb steam and air at 70 deg, fo--r 134 in. t I PS--4.25 sq ft. . VULCAN CAN BE INSTALLED 2 or 3 tiers high to secure necessary heat require ments. ' CONSTRUCTION DETAILS OF STEEL RADIATOR Blast Air Healing and Air Cooling Coils Helical Fin Tube Core Assemblies Rome products are "backed" by 40 years of experience. 1036 Contact Representatives in Principal Cities or send for Catalog. 1037 Air System Equipment Refrigerating Machinery Baker Ice Machine Go., Inc. SALES AND SERVICE IN PRINCIPAL CITIES r!;' Omaha, Nebraska 1530 vans Street Cable Address: BAKERICE BUILDERS OF DEPENDABLE REFRIGERATION EQUIPMENT SINCE 1905 1. BAKER builds compressors, condensing units, compressor units, shell and tube equip ment, and cooling units for all commercial and industrial air conditioning applications. BAKER engineers are free to select the equipment and refrigerant best suited to your specific requirements. Write for information, descriptive literature on units shown below. Methyl Chloride or Ammonia "Freon-12" Compressors Compressors (3 to 100 hp) Fouricylinder type, available in sizes from 3 hp to 60 hp. Semi steel cylinders and pistons. Counter . balanced crankshaft, precision ground. Timken roller main bearings. Full force feed lubrication is furnished by gear type oil pump. Methyl Chloride or "Freon-12" WaterCooled Condensing Units Vertical en closed, single acting type. Can be install ed in multiple installations. V-belt drive or direct connec tion to motors or engines. Double suction and capacity reduction in larger sizes. Ammonia Water-Cooled Condensing Units (3 to 15 bp) Complete line of self-con tained, auto matic units. Sizes range from % hp to 60 hp capacity. Two- and four-cylinder Excellent for all industrial ap plications. Shell and tube type condensers with types. Shell and tube condenser-receiver. pressure-operated water control valve. Methyl Compact design economizes floor space. . Chloride or Ammonia Compres "Freon-12" sor Units (3 to 20 hp) Compressor Units Designed for quick installation and ready Arranged for accessibility to all unit use with evapor- . parts. For use with ative type con evaporative or sepa denser or sepa rately mounted shell and tube type con rately mounted denser. Full enclosed automatic motor shell and tube condensers. Sizes range control with overload and low-voltage pro from 3 hp to 60 hp. Two- and four- tection. Two- or four-cylinder compressor, cylinder types. Automatic controls. V-belt drive. Baker Shell and Tube Condensers and Liquid Coolers for Use with Ammonia or "Freon-12" (1 to 250 tons capacity) Made in sizes up to 2500 square feet of cooling surface * in single shells. Available for multi-unit installation with special stands to allow compact installation. Supplied in either horizontal multi-pass or vertical type. Heads may be removed quickly and easily for complete cleaning. Tubes are spaced to provide even gas distribution throughout the shell. All valves of maximum size for greatest efficiency. .Baker Also Manufactures a Complete IArm of Industrial-Type Cooling Units, Ammonia Valves, Screw-End Fittings, Capped Valves, Flanged-Type Fittings 1038 Air System Equipment Refrigera ting Machinery BRUNNER MANUFACTURING COMPANY UTICA, N. Y.,' U. S. A. COMMERCIAL REFRIGERATION The Brunner Line of Refrigeration Equipment includes Air Conditioning models up to and including 25 hp for all types of high temperature applications within their capacity, using either "Freon12" or Methyl Chloride as refrigerant. . BRUNNER DEPENDABILITY is based on time-proven features of design and manu facture ... all parts are precision machined with extremely close tolerances . . . bronze bearings throughout... extra large fin surface on cylinders and heads... bellows seal... silent eccentric drive (except on 20 hp and 25 hp models, which employ crankshaft) . . . suction and discharge valves in "all-in-one" plate assembly . . . heavy-duty motor with high starting torque . . adjustable motor base . . . multiple V-belt drive. Throughout, Brunner Refrigeration Units are geared to the demands of heavy-duty service. SPECIFICATIONS Model No. H.P. Cyls. Bore and Stroke CAPACITIES Air Conditioning (Jolts Based on 75** P Water Temperature "Freon-12" Refrigerant DIMENSIONS R.P.M. B. T. U. per Hr. 40 Evap. Temp. L. W. H. W ' 300-FH 3 4 314x244 260 38547 W 500-FH 5 4 .3^x214 420 62270 W 750-FH 744 4 W 1000-FH no 4 444 x3 444 x3 260 91526 350 . 123211 W 1500-FH 15 4 444x3 525 184815 W 20000-FH 20 4 444 x 5 435 255046 W25000-FH 25 4 444 x 5 540 316652 50' 24' 2844' 50' 24' 2844' 71' 2944' 3844' 71' 2944' 3844' 71' 2944' 3844' 73' 33y4' 4844' 73' 3344' 4844' Additional air and water cooled models from K h.p. for commercial and industrial applications. The Brunner Field Sales Organization is available in all parts of the country, backed by outstanding achievements in engineering, and adoption of modern methods and design of air conditioning equipment. . Installation of Brunner refrigerating units is insurance of fine quality materials and work manship--plus the exceptional efficiency possible in modern design and manufacture. FREE... COMPLETE ILLUSTRATED CATALOG with large section devoted to ways ofselecting the proper units for any application. 1039 S' Air System Equipment Curtis Refrigerating Machine Division of Curtis Manufacturing Company 1959 Kienlen Ave., St. Louis 20, Mo., U. S. A. Established 1854 Full Line of Units from 1/6 to 30 hp PRODUCTS: Refrigerating Machinery; Forced Draft Cooling Units; Cooling Coils, Condensers, Shell and Tube Coolers, Valves, Fittings and Accessories, Complete Refrigerating Equipment for Dairies, Creameries, Ice Cream Cabi nets, Ice Cream Making Plants, Cold Storage Locker Systems, Walk-in Coolers, Drinking Water Systems, Commercial and Low Temperature Cooling, Pro cessing and Air Conditioning Installation, Packaged and Remote Types. Commercial Refrigeration toYi hp Self-Contained Condensing Unit. Air cooled condensing units from M to 5 hp, inclusive, and water cooled units from A to 30 hp, inclusive. All models available for either Freon (F-12)or Methyl Chloride. Mechanical advantages include Timken Bearings, Centro-Ring Positive Pressure lubrication. Special models are avail able for ice cream, frozen food cabinets and for the dairy industry. 1 16 hp Cleonable Shell and Tube Condensing Unit. Other sizes from S to SO hp. hp Air Coded Condensing Unit'. Other sizes from % to 3 hp. Saturated Air Condenser For condensing refrigerant vapors economically and efficiently. Saves approxi mately 95 per cent water cost. Used for air con ditioning or commercial refrigeration installations up to 5 ton Capacity. 6 hp Water Cooled (Counterfiow) Air ConditioningCondensing Unit. Other sizes from to 6 hp. - For today's essential Air Conditioning require ments Curtis offers com plete packaged, refriger ated air conditioning units, requiring only water and electrical connections to install. Cools, dehu- midifies, circulates and filters the air. Eliminates costly' installation ex 7)4-10-16 ton Remote or Central Type Air Conditioner. pense. Adaptable for heating. 1040 S and 6 ton Packaged Type Air Conditioner. Air System Equipment Refrigcratin, Machinery Albany Atlanta BALTIMORE Boston Buffalo Charlotte Chicago Cincinnati Dallas Detroit Kansas City Frick Company (Incorporated) Air Conditioning, Refrigerating and Ice-Making Equipment Waynesboro, Penna. Distributors in 150 Principal Cities Los Angeles Memphis New Orleans New York Oklahoma City Palatka Philadelphia Pittsburgh St. Louis Seattle Washington AIR CONDITIONING Ask for Frick Bulletins 60S. 604, 605 and 620 on Air Conditioning Complete Frick sys tems; also refrigera tion for use with equipment supplied by others. Over 1000 installations attest the value of Frick air conditioning systems and those using the Auditorium patents. Successful experience with important Gov ernment and i n - dustrial war jobs enable us to solve your problems. AMMONIA REFRIGERATION Combined units and ver tical enclosed compressors, with two or four cylinders, in sizes from A; ton up. Widely used for air condi tioning, with material sav ings. Ask for Bui. 503 on this subject. Pratt and Whitney use Frick Ammonia Refrigeration for Precision Air Conditioning Service FREON-12 REFRIGERATION Frick "Eclipse" and the larger F-12 com pressors provide a complete and effici ent line. Coils, cool ers, condensers and controls to suit. Patented Flexo-Seal. at shaft, pressure lubrication from submerged pump, capacity controls, and other superior features make Frick machines your logi cal choice. Frick Air Conditioning Supplits the Extra ' Humidity, Steady Operation. Spark-Proof Con trols, Quietness, and Freedom from Drafts Neces- ' , sary in Hospital Operating Rooms LOW-PRESSURE REFRIGERATION Commercial and in dustrial units in sizes from }/i hp. up. Charged with either Freon-12 or methyl chloride. Air and .water cooled conden sers. Coils, coolers, and air conditioners. ' Get in touch with your Frick Distribu tor; ask for Bui. 97. Our service includes estimates, layouts, manufacture, instal lation, maintenance. "Eclipse" ' Freon-12 Compressor. Bulletin 100. : Enclosed Freon-12 Machine. Bulletin 608. Enclosed Ammonia Compressor Bulletin 112. 1041 * Low Pressure Refrigerating Unit. Bulletin 97. Air System Equipment Refrigera ting Machinery Mario Coil Go. 6135 Manchester Ave., St. Louis 3, Mo. Manufacturers of Heat Transfer Equipment Evaporative Coolers--Industrial Coolers--Unit Heaters--Unit Coolers --Evaporative Condensers--Low Temperature Units--Air Conditioning Units--Heating and Cooling Coils. INDUSTRIAL COOLERS Available in 15 sizes, both Dry Coil and Spray Type; with finned coil or prime surface. For any refriger ant. Sectional construc tion. Hot galvanized frames, sump and base. EVAPORATIVE COOLERS Evaporative Con densers--A com plete line of con densers for all re frigerants having single motor "Unidrive" for fans and pump. All prime surface coils. Frame electric welded and galvan ized after fabrication. All internal surfaces covered with corrosion resistant mastic. UNIT COOLERS and HEATERS Sturdily built, for all re frigerants and heating mediums. Coolers in "PullThrough" and "BlowThrough" types. Diesel and Industrial Coolers --Evaporative coolers for cool ing jacket water and lubricating oil for Diesel engines and indus trial processing; also for Trans formers, Quenching Oils, Cutting Coolants, etc. AIR CONDITIONING COILS--BLAST COILS Extended surface--"Ball- Bonded"--coils for all cooling or heating mediums, suitably constructed of any conventional metal--all sizes, duties and capaci ties. , LOW TEMPERATURE UNIT Designed for maintaining sub-zero tem perature. Defrosted manually or auto matically by electric heater units. ' AIR CONDITIONING UNITS Air Conditioning Units in either ceiling suspended or floor type. Capacities from 900 cu ft to 12,000 cu ft. Sturdily built on welded angle iron frames of sectional design for easy installation. MARLO MEANS HEAT TRANSFER EQUIPMENT*' Air System Equipment * Refrigerating Machinery MILLS Jfndtt&foieb, r?nc<y>/io'uz/e</ Refrigeration Division 4100 Fullerton Avenue Chicago 39, Illinois Mills Compression Equipment * for Air Conditioning Commercial and Industrial Refrigeration COMPRESSOR 2^ in. x 3 in. four cylinder, vertical, single acting, reciprocating type . . . heavy, one piece alloyed semi-steel cylinder block and crank . case ... oil sight glass . . . alloy semi-steel pistons, two compression . rings, one oil ring . . . hardened piston pins . . . drop forged steel connecting rods . . . bronze piston pin bearing . . . bronze main bear ings . . . exclusive Mills design' shaft seal. CONDENSING UNIT Base of cast iron ends and formed steel sides . . . shell and tube type receiver condenser with removable heads and leak alarm fittings . . . complete with automatic water valve, starting box, low pressure ' control with high pressure safety cut-out . . . complies with Under- . writers' specifications . . . dynami cally balanced and non-vibrating, light in weight, compact, requiring a minimum of floor space. Mills Condensing Units are economical to operate and maintain. Condensing units are'shipped ready to operate. No special foundations are nec essary. APPLICATIONS Refrigeration in air conditioning appli cations for comfort, food preservation, and industrial uses for processing and testing. Compactness of condensing units make them ideal for self-contained applications. ENGINEERING Mills Industries, Incorporated maintain an engineering test laboratory as a service to their customers, equipped with three hot rooms, calorimeter, indicating and recording, pressure and electrical instru ments and all apparatus necessary for a thorough analysis of the use. of condensing units to any manufacturer's product or field applications. ' . CAPACITIES AT 40 SUCTION GAS Weight Depth Height 1 Size RPM Displacement* CFM 1 ,. 1Capacities in BTU 1 5 hp 10 hp -c TJ & 480 16.37 65000 63' V>Vi' 32' 8951b 700 23 66 90500 63' w/i 32' 945 lb 890 30 34 125000 63' 30' 34' 10501b ! Net 1 Air cooled models from % to 3 hp. Water cooled models from to 10 hp. All models are designed for use with Freon-12 or Methyl Chloride refrigerants for low, standard, and high back pressures, for operation throughout the complete range of temperatures. Compressors are designed for low head temperatures and high volumetric' effi ciency. Condensers are matched to the per formance ranges of each compressor. A Member of the Mills Field Organisation Is Near You And at Your Service 1043 Air System Equipment Refrigora ting Machinery Servel, Inc. Electric Refrigeration Division Evansville 20, Indiana, U. S. A. "POWERED by Servel" is the hall mark of a quality product CONDENSING UNIT SPECIALISTS Servel Supermelic Condensing Unit The Electric Refrigeration Division of Serve!, Inc., has for over 25 years, specia lized in producing top quality low pressure condensing units. As the first American manufacturer to use oil soluble chlorinated hydro-carbon refrigerants, Servel has pioneered a large part of the most im portant engineering developments in this field. Servel maintained its condensing unit produc tion through out the War Years, adding many impor tant features and developing improved de signs and tech nical processes. Partici pa- tion in many of the most Sled Cased Supermelic Power Unit Fractional H.P. critical appli cations for war production materially accelerated the improvement of Serve! products. New machine tools and processing methods have been installed and these facilities will permit a continuous .increase in production during 1946. Emphasis will be placed on volume production of SER VEL SUPERMETIC UNITS. These units, developed before the war, and' suspended because of critical materia! shortages have been refined and improved to provide added performance, efficiency, and dependability. The new line of units will serve the requirements of more than 90 pier cent of, the refrigeration field from sub-zero Freezers up to air conditioning and com fort cooling. In addition to these Supermetic units, Servel will offer a companion line of belt driven units and compressors for special applications, D.C., odd fre quency, Gas Engine drive, etc. FOR DISTRIBUTORS AND CON TRACTORS--Servel sells its condensing units throughout the World through regularly franchised dealers and distri butors serving a specific trading area. Full selling, Engineering, and service as sistance is extended these customers by Servel's field force and factory staff. Servel's National advertising assures ac ceptance everywhere. FOR MANUFACTURERS--We especi ally invite inquiries at this time from manufacturers who contemplate the pro duction of window units, room coolers, store coolers, etc. ` Our Engineering Department will be glad to cooperate in a selection of com ponents and extend testing facilities for completed units. Samples of our manu facturing products are available to re sponsible manufacturers and contractors without obligation. Our field sales repre sentatives and engineers will be glad to make appointments for consultations on these matterssiipon request. Address Servel, Inc., Electric Refri geration Division, Evansville 20, Indiana. Cost Cose "Field Serviceable" Supermetic Power Unit--1 H.P. and above 1044 Air System Equipment Universal Cooler Division INTERNATIONAL DETROLA CORPORATION MARION, OHIO and in Canada BRANTFORD, ONT. Manufacturers and designers of hermetic, open type self-;Contained and remote types Refrigerating Units in wide range of capacities. Vs to 15 hpfor . . : Household Refrigerators Frozen Food Cabinets Food Storage Refrigerators and Display Cases Ice Cream Cabinets and Soda Fountains . Water and Beverage Coolers Air Conditioning Commercial Refrigeration Equipment Truck Refrigeration Equipment Vending Machines Machine Tool Cooling Special Applications ' Low-cost, trouble-free performance--that's what every fixture manufacturer is look ing for. And that's the kind of performance you can expect from Universal Cooler's compact, soundly designed and precision-built refrigerating units. . From the experience gained through a quarter century devoted exclusively to the manufacture of refrigerating units, Universal Cooler has developed advanced design and exclusive construction features, proved in actual field service, that have established new performance standards in the refrigeration industry. For the economical, dependable service that will provide the answer to your par ticular refrigeration problem, look to Universal Cooler! An analysis of your particular . requirements will be made by Universal Cooler specialists without obligation; write today for complete information on products and production. Automatic Refrigeration Since 1922 1045 Air System Equipment SSJ"1 Worthington Pump and Machinery Corporation Albany Atlanta Baltimore Birmingham Boston Buffalo Air Conditioning and Refrigeration Division General Offices: HARRISON, NEW JERSEY Charlotte Chicago Cincinnati Cleveland Dallas Denver Detroit El Paso Fort Worth Galveston . Houston Kansas City Los. Angeles Milwaukee New Haven New Orleans New York Philadelphia Pittsburgh Portland. Ore. Providence St. Louis St. Paul Salt Lake City Representatives in all Principal Cities San Francisco Seattle Springfield, Mass. Syracuse TuIsa Washington. D.C. Wilmington, Del. REFRIGERATION SYSTEMS FOR AIR CONDITIONING Complete refrigerating systems for use with Freon-11, Freon-12, Methyl Chloride, Ammonia, or Carbon Dioxide, either directexpansion or water cooling applications. A complete line of refrigeration compres sors, permitting impartial recommenda tions. A nation-wide organization of Distributors in major cities to provide sales and engineering service and plan complete air conditioning systems of the central or unit type. Architects, Engineers, and Contractors are invited to consult with us. Write to Harrison, N. J., or any branch office, for bulletins on these products. "Packaged" Unit Cooline (or heating, if desired), dehumidifica tion, ventilation, circu lation and air cleaning for commercial and small industrial appli cations. 3 hp and 5 hp sizes. Two-cyl. recip rocating compressor,, finned copper tubing condenser, large-sur face finned coolingcoils, quiet low-speed fan, throw-away filters, conaled temperature and air volume conols. Freon-12. Capacities up to 5 tons. Small Self-contained Units Freon-12 or methyl chlo ride condensing units; motors ^ to 2 hp with air or watercooled con densers. Used in small air conditioning systems, and in commercial refrigeration. Capacities up to 2 tons. Features: FEATHER (Pat'd.) Valves; automatic capacity-control. Capacities 3 to 30 tons. Large Self-contained Units Freon-12 or methyl chlo ride compres sor units for use with ``shower" condensers or water-cooled condensers. Features: Worthington FEATHER (Pat'd.) Valves; automatic capacity .con trol. Capacities up to 100 tons. ' Centrifugal Refrigeration Water Cooling Systems Medium Self-contained Units Freon-12 or methyl chlo ride compres sor units for use with "shower" cpndensers or water-cooled condensers. Freon-11 centrifugal compressor, water cooler and water-cooled condenser in com pact unit assembly. Electric motor or steam turbine drive, 5fi unit sizes . . . 150 to 1200 tons. ' 1046 Air System Equipment Sfflggr*. Worthington Pump and Machinery Corporation Evaporative Type Jacket-- Water Cooler (With By-Pass Section For Automatic Temperature Control.) Cooling jacket water for diesel and gas engines, aircom pressors, etc. Ideal for the cooling of quenching oil for tempering steel products. Also for cooling transformer oil to reduce core loss. Miscellaneous High and low side equipment for every purpose. ' Air Conditioning Units For Direct Expansion Freon-12 ` or Chilled Water Circulation Horizontal Condensers Atmospheric drip type, for warm corrosive waters. Double-pipe for closed systems, can be retubed without shutting down. Multi-pass, as illustrated above, for closed systems and space saving. Vertical Ammonia Compressors Pressure-lubricated; roller main bear ings; safety heads; patented Feather Valves; belt drive, or direct-connected to electric motor, diesel or gas engine; sizes 3 x 3 to 10 x 10 2 cylinder. Horizontal Ammonia Compressors Vertical and horizontal; 1500 to 12,(MX) cfm; large air passages; slow speed, quiet, rugged fans; separable sections; readily accessible. The design permits flexibility in installation arrangements. Shower Condensers A combined con denser, receiver and modified cool ing tower, in one assembly, for Freon12 or methyl chlo ride systems; 10 to 60 tons -refrigera. tion; built in sepa rable sections; all parts easily acces sible. Saves 90 to 95 per cent in cost of water. Single and duplex; single-stage and twostage; belt drive, or direct-connected to electric motor, diesel, gas or steam engine; patented Feather Valves; ratings from 60 to 750 tons. Automatic capacity control features are easily applied. Space require ments vary depending upon type and drive. Carbon Dioxide Compressors A series of convenient types and sizes for every re quirementis available. A6--7 1047 Air System Equipment Refrigerating Machinery The Vilter Manufacturing Co. Dept. N-23 mm ' Milwaukee 7, Wisconsin /Air Conditioning Refrigeration J AIR CONDITIONING EQUIPMENT FOR INDUSTRIAL OR COMFORT COOLING Branch Offices .and Distributors in Principal Cities Ammonia Compressors--The result of over seventy years of research, development and experience gained through thousands of installations of all types, in all industries. Famous for high tonnage capacity at low HP and low operating costs. Built in a wide range of capacities from 2 to 100 tons standard A.S.R.E. rating in Vertical Types; up to 750 tons in Horizontal Types. Freon Compressors--Embody many outstanding features that prevent leakage and minimize friction--resulting in extremely low relative HP per ton. Made in capacities up to 150 tons. Capacitrols are available, providing flexibility of operation. Self-Contained Condensing Units--Vilter self-contained condensing units for Ammonia, Freon or methyl chloride are made in sizes from ^ to 30 HP. Dependable, economical operation. " Unit Air Coolers--Available in a wide range of sizes and types for any air con ditioning requirement--product coolers, dry coil coolers, spray type coolers, low tem perature electric defrosting coolers, and floor or ceiling central system air conditioners. Water Coolers and Condensers--A complete line of shell and tube and double pipe water coolers, brine coolers and condensers for Ammonia or Freon. Air Conditioning--All sizes and types of air conditioning coils, evaporative con densers and air washers--and special units for central station comfort cooling systems. Valves, Fittings and Piping--Ammonia and Freon valves and fittings. Prefabri cated piping in all sizes for refrigeration and special process work. Unit Air Conditioners . Spray and Dry Coll Types Catalog--Valves, Fittings. Accessories Write for Free Copy 1048 Prefabricated Process and Refrigerant Piping Air System Equipment Fans and Biowars 2311 Superior Ave., Cleveland 14, Ohio PIONEER BLOWER MANUFACTURERS REX BLOWERS A complete line of centrifugal blowers well suited for use in the heating, cooling and ventilating field. There are two series of Rex Blowers--the A. C. and H. P. models, ranging in capacity from 400 to 12,000. cfm. Twin units double these volumes. The H.*P. series is more compact for use where space requirements are a factor. WHEELS: Double Inlet, carefully balanced, assuring true running and high efficiency. Forward- curved multi-blade type for maximum air delivery at lowest speeds. Each blade is die formed and securely riveted.to inlet rings to form a rigid assembly. Rex Blower HOUSINGS: ' Made of heavy gauge steel, die formed and electrically welded for maximum air intake. Wide outlet distributes the air evenly. BEARINGS: Self-aligning to insure smooth operation; mounted on sound and vibration absorbing rubber bumpers. Phosphor-bronze, bushings are self-lubri cating to supply right amount of oil. OTHER FEATURES: Motor pulleys on smaller sizes have four steps to provide four speeds. Variable speed supplied on 16 in. size and up. V-Pulleys universally used. Shaftsareaccuratelyground and polished to 0.0005 in.; of heavy weight to prevent whip which causes noise and wear. Angles of discharge can be varied and construction changed to meet special re quirements. REX Blowers are rated in accordance with the test code of the A.S.H.V.E. Performance is quiet, depend able and trouble-free. For complete information, write for Catalog No. 222 which contains a complete description of REX Blowers and tables of dimensions, capacities and other data. ' 1049 Air System Equipment ram and Blowers American Corporation 3606 Mayflower Street, Jacksonville 3, Florida Manufacturer of COOLAIR Ventilating and Exhaust Fans A Pioneer Manufacturer of V-Belt Drive Exhaust Fans Charter Member: Propeller Fan Manufacturers Association TYPE S--6 TO 9 FEET 'Especially designed for ventilating and cooling in industrial plants and shops, power stations, warehouses and other large buildings--the Type S fan has a heavily braced double frame, special pillow-block ball bearings on each side of fan wheel. 8 to 12 reinforced fan blades and multiple heavy duty V-belts for long industrial service. This fan is usually installed in roof bay or gable, penthouse or outside wall. RAPID AIR CHANGE NEEDED FOR EFFECTIVE COOLING Unprecedented production demands in recent years have highlighted the necessity for rapid air. change in factories, shops and offices to combat heat fatigue and maintain morale among workers. Many plant managers have only recently learned that a complete air change every 30 seconds to one minute is necessary for effective cooling. Coolair pioneered this principle and developed large, efficient exhaust fans to do the job. Coolair also has pioneered in developing a complete line of ultra-quiet home-cooling attic fans. A wide range of sizes and types are stocked by Coolair dealers and distributors in most sections of the country. In planning a Coolair installation, determine cubic content of space to be cooled and select fan from table on opposite page adequate to provide at least a one minute air change. Write for FREE bulletins con taining detailed sugges tions for industrial and commercial installations --and. for name of nearest Coolair agent or dealer. QUALITY FEATURES OF COOLAIR EXHAUST FANS 1. Built-In Springs on Smaller Motored Units-- dampen vibration and practically eliminate noise for quiet installations by insulating moving parts from frame. . 2. Light, Compact Fabricated Steel Frame--fits into . many openings where bulky metal housings cannot be used. 3. Reversible--when equipped with reversible motor, fan will blow in or exhaust as desired. 4. Ball Bearings in Fan Hub--eliminate sleeve bearing chatter and end thrust knock--permit operation in any position TYPE O--26 TO 62 INCHES .(specify ball bearing motor for vertical or angle discharge). Patented built-in springs (on Use grease, instead of oil. requiring attention not more than once a year. 5. Eight Large, Slow-Moving Steel Blades--instead of 4 or less as on cheaper fans--up to 12 S^mUnSorifice combine*^ make this type quiet in opera- tion- .Designed for reversible blades on Type S models. Low tip speeds for quiet opera- r^v^rtiSaioranguildi^Srge tion and steady flow of air. 6. V-Belt Drive--for high when equipped with ball bearing efficiency using small motor for economical - operating motor. Usually installed in full speed. 7. Long Hour Service Motor--Nationally known cLtSde^apaJution. X"ght makes of motors. 8. Certified Air Ratings--in accord- opening, penthouse--often used ance with Standard Test Code of A.S.H.V.E. and N.A.F.M. a. battery of units for most 9. Full Streamlined Orifice-<on Type O & OT) avoids .. Co^Sl. u s8 Patenu "spill-off" at end of blades, reduces power consumption. 1992112 and 2191418. TYPE OT--TWIN UNIT - This unique Coolair Twin-Unit is two fans of Type O speci fications mounted ride by ride in one frame and operated by a single motor. Widely used where limited headroom or Vertical wall space will not permit the use of a angle fan large enough for the job. Especially adapted for instal lation in partitions, outside wall and on end can be fitted into existing window and ddor openings. Covered by U. S. Patents 1992112, 2103736 and 2191418. 1050 American Coolair Corporation Air System Equipment Fans and Blowers Dimensions in Inches 2S-W FAN WITH SAFETY GUARD Fan Size 28-W 2-0 2VrO 3-0 3'/rO 4-0 4'/rO Overall Height 31 3oy, 36% y. 49 55'/, 61% Overall Width Overall Depth (Approx) 33 30% 36% 42% 49 55% 61'/, 15 16 18 18 19 19 19 Coolair's lowest priced beltdrive fan is equipped with built-in springs, adjustable diameter motor pulley and safety guard. This fan can be easily and quickly in stalled in upper or lower half of any standard window of work rooms or offices where proper, ventilation is ` necessary for health, com-, fort and efficiency of work ers. See tables for data, u> 6-S 7-S 6-S 9-S 2-OT 2%-OT 67% 75'/, 67 %* 112'/,* 30% 36% 67% 19 75% ` 30 87 32 w%* 49 112'/,* "54 61% 18 73% 18 DIRECT DRIVE FANS Four sizes 16 to 24 inches in diameter. General purpose exhaust fan for most com mercial and industrial uses. Data on sizes, performance and dimensions furnished on request. 3-OT 42% 85% 19 COOLAIR AUTOMATIC CEILING & WALL SHUTTERS V/rOT 49 98 19 Precision-built all-steel shutters that open and close auto- 4-OT 55% 110'/, 22 -matically.when fan is turned on or off. Ceiling shutters '-eliminate need of ceiling grille and trap door in. attic These dimensions include five- installations. Wall shutters give weather protection for eighths, inch for bolt heads.- fans discharging directly to open air. Performance Data--Coolair V-Belt Drive Fans Fan Size 28-W 2-0 2%-0 3-0 3/2-0 4-0 4/2-0 5-0 Hone Fan Power R.P.M. VL % VL % D VB A VC H O% D VB % VC -j. C D~ -- D VB ,* VC c D D 1% VL a VC D1 D l'/2 /AVB % VC C D l'/2 D VB VC c c .D D -r 1. l'/2 3 580 570 . 630 411 454 522 600 312 345 398 450 500 261 300 345 380 440 258 317 353 405 224 255 276 319 355 200 225 245 282 310 355 Cubic Ft. Air Per Min. 6000 6200 6800 8000 8800 10100 11700 10000 11000 12700 14400 16000 13000 15000 17000 19000 22000 19000 22000 25000 28000 22000 25000 27000 .32000 35000 27000 30000 33000 38000 42000 46000 Fan Size fcS 7-S & 9-S 2-OT Twin 2!/rOT Twin 3-OT Twin 3/2-OT Twin 4-OT Twin B C C D D' B C D D B C D D B C D D VB VC VC VB VC VC VB VC VB VC VB VC D Horse Fan Power R. P. M. 1 >`/2 2 3 5 2 3 5 7% 3 5 7Vz 10 15 % H -% H 8 8 'A 1 l ' 155 177 195 224 270 170 195 230 270 150 178 205 . 225 150 . 170 190 215 455 500 570 359 411 470 312 360 272 300 258 317 345 Cubic Ft. Air Per Min. 35000 40000 45000 50000 60000 58000 67000 76000 85000 80000 95000 II0000 120000 110000 125000 138000 154000 9800 10800 12400 14000 16000' 18200 20000 23000 27800 30700 36000 . 44000 48000 B--Very Quiet (Homes, Theatres. Hospitals.etc.). C--Quiet (Stores, Offices, Restaurants, Barber Shops, etc.). . ... V--Equipped with built-in springs. I>--Industrial (Laundries, Factories. Canneries . Bakeries, Pressing Clubs. Garages, etc.). L--Has adjustable diameter motor pulley for Very Quiet and Quiet performance. 1051 Air System Equipment <"<* atmmt Bayley Blower Company 1817 S. Sixty-Sixth Street Branches to Principal cities Milwaukee 14, Wis. Builders of Heating, Ventilating, Cooling, Purifying, Humidifying and Air Washing Equipment; Exhaust and Drying Apparatus, Mechanical Draft and Blast, Fans and Blowers of all Types TYPE "F" PLEXIFORM FANS AND TYPE "AP" AEROPLEX FANS Plexiform and Aeroplex Fans are both designed for heating, ventilating and air conditioning service. The Type "F" fan is using a multi blade wheel (see cut at left) while the type "AP" fan is built around a wheel of high speed design (see cut at right.) The wheels determine the character of the performance or the fan "Characteristics," thus the Type "F" is a slow speed fan having a rising power curve,, while the "AP" is a high speed design and has self-limiting power character istics. Both fans are highly efficient and can be built single inlet, single width, or double inlet, double width in ten different arrangements of drive and eight directions of discharge. The standard fans * range in capacity from 1200 to 300,000 Cfm and these fans are readily available in Class I or JI designs for various types of duty. Class III and IV can be furnished on special application. Type "EX" Fans For all exhaust problems, pneumatic conveying, fume exhaust etc. "EX" is highly adaptable, feasible and serviceable fan. It is sturdy in construction, easily in stalled and maintained. The design is reversible and standard sizes Nos. 15 to 80 inclusive are available. Type "H" Fans For pressure applications from 6 in. to 42 in. for belt drive or direct connection to motor, Type "H" is a most practical design. Standard sizes Nos. 25 to 80 are listed but the design is suitable for modification of wheel diameters to meet vari ous motor speeds. Both "EX" and "H" fans can be designed to fit specific applications. The design permits easy modification of details and the fans can be used for induced, forced draft, cupola service, primary or secondary air supply to oil burners, etc. Special details, outlet and inlet, or mounting can be designed to suit your special assembly. Turbo Spray The Turbo Spray for industrial and comfort conditioning, cooling and humidi fying, is a practical design as the atomi zation is by mechanical means, thus there can be no clogging or interruption of service even in atmosphere heavily laden with fibers or other foreign material. Single or multiple bank washer, one or two stage designs can be fur nished from 2500 to 100, 000 Cfm ca pacity. To fit . space re quirements width and height can be modified to suit. Chinook & Chinookfin Both Chinook and Chinookfin Coils are based bn the tube-within-a-tube de sign, originated by Bayley. The principle involved permits single header with ail tube ends, free expanding, thus elimi nating the likeli hood of freeze ups and cracking usual ly due to expansion and contraction strains. Both type coils are designed for usual hot blast heating and cover a wide range of capacities and applications. 1052 Air System Equipment b1"^T Burden Company 1151 South Broadway, Los Angeles 15, Calif. Manufacturers of ** Plastic and Aluminum Fan Blades and Blower Wheels Burden Plastic Fan Blades offer the following unique combination of desirable properties: LOWER NOISE LEVEL--STABLE OVER WIDE TEMPERATURE RANGELOW MOISTURE ABSORPTION--RESISTANT TO CORROSIVE ACTIONLIGHTWEIGHT WITH GREAT STRENGTH. Type F Type CL Special One Piece Blade AVAILABLE IN THREE TYPES TYPE "F". Standard with four flat, overlapping, plastic blades with steel hub and aluminum spider. Sizes available: 8, 10, 12, 14, 16, 18, 20, 22 and 24 in. diameters. TYPE "C". This is like our Type "F" except that the blades have a curved tip. Available in same sizes as Type "F".. Both plastic and aluminum. . TYPE "CL"--CLOVER LEAF PATTERN--{Patent applied for). This blade is made without a spider. Blade attaches directly to hub. Available in 6, 8, 9,10 and 12 in. diameters, both plastic and aluminum. . .' ^ Types "F", "C" and "CL" are "Patented" Overlapping. Design giving quiet performance under pressure conditions. SPECIAL BLADES--When quantities justify die costs, will produce special types. We invite your inquiries. . SPECIFICATIONS Pitches . Rotation TYPE "F" and "C"--14, 16, 18, 21, 23, 25, 27, 30 and 33 deg. TYPE "CL"--21, 23, 25, 27, 29, 30, 33 and 35 deg. CLOCKWISE (C.W.) or COUNTER CLOCKWISE . (C.C.W.) as you face air stream. Specify when ordering. Bore Sizes STANDARD--l/i, $4, % and- in. Larger sizes available. ' Hubs " STANDARD---For motor on suction-side of blade. REVERSED--For motor on discharge siderof blade. DIMENSIONS TYPE "F" BLADES Fan Size Dia. In. Pitch Degrees Iff 10* HP 10' ir W - \Y 12* 14' 14' 14 21' 23 33 14 21 25 33 14 21"' . Dimension "A** MD" 10* W 10' 10* w 10* 3'/4' 12' 2*/#' 12' 2>/,' 12' 2y#' 12' 3%' 14' 2%' 14' 1W ' Fan Size Dia. In. Pitch Degrees 14' 14' 16' 16' 16' . 16' 18' 18' . 18' 18' 25" 33" 14" 21" 25" 33" 14" 21" 25" 33" Dimension "A" "D" 14' W 14' 3VtT 16' .w 16' 3Va' 16' 3%' 16' W 18' 3' 18' 3VC 18' 4>/,,' 18' ' 5'/.' Standard Hub--All Type "F" Blades "1 S" = Length .!}? or % >n- Measurements are for preliminary purposes. If close measurements are required for layout purposes, we suggest working from full size blade that is being used. For dimensions of unlisted sizes and for other types of fans, write the factory. Burden Blades--Licensed Under General Electric Co. Patent No. 1,957,237. 1053 Air System Equipment Fans and Blowers Belanger Fan & Blower Co. Manufacturers Wolverine Fans & Blowers Detroit 16 1230 Eighteenth Street . Michigan The Wolverine Silentair Exhaust Fan is the result of over 20 years experience in the design and manufacture of air handling equipment. Silentair Fans are designed for installation on walls, ceilings and partitions to provide high operating efficiency and silent performance. Fan blades are of epicycloidal type and are rated in accordance with Standard Test Code for Axial Fans adopted by . ,, N.A.F.M. and A.S.H.V.E. Made in ten sizes from 10 in. to 48 in. deliver ing from 650 to 18,500 cfm. . Silentair Exhaust Fan Wolverine SKS Stack Fans V Belt Drive are ideal fpr spray booths, ducts or stacks for exhausting vapor, smoke, steam or fumes. Made for pipe sizes of 13 in. to 49 in. V Belt Drive and adjustable motor support. Motors are outside the air stream. Extension Shaft Fan Wolverine Silentair Belt Drive Fans designed for comparatively low speeds and provide low cost vblume exhaust. Fan sizes from 15 in. to 48 in. with 1,465 to 23,500 cfm capacity. ' SKS Stack Fan The Wolverine Stack Exhauster transforms any roof ventilator'into an, effective fan exhauster. Made in a wide range of sizes and capacities. Stack Exhausters are constructed of heavy gauge steel, reinforced for motor support. The propellers are directly connected to the fan duty motors. Airplane Type Single Propeller Fan Wolverine Extension Shaft Fans are desirable where smoke, grease, cor rosive fumes or explosive vapors must be removed. Motor is out of the air stream. Sizes from 16 in. to 48 in. with capacities from 2,280 to 25,500 cfm. Silentair Beltdrive Fan The Wolverine Single-Propeller Airplane Type Fan operates efficiently in either exhausting or'blowing posi tions. ` Welded steel construction, cast aluminum propeller. Sizes range from 12 in. to 60 in. The Wolverine Two-Propeller Air plane Type Fans are made in 16rin. to 60 in. sizes. Airplane Type Two Propeller Fan Wolverine Slack Exhauster The Wolverine Multi-Blade V Belt Drive Fan is made in sizes 30 in. to 84 in. with capacities from 6,275 to 72,500 cfm. The large blade area of this fan permits comparatively slow operation and unbelievably lo\y operat ing noise level. It is a quiet, powerful, economical fan of rugged construction and can be installed easily in wall openings or steel sash of industrial or ^ commercial buildings or as' attic fans' in dwellings. Multiple Blade V Bell Driven Fan 1054 Air System Equipment Fans and Blowers Belanger Fan & Blower Go. Manufacturers Wolverine Fans & Blowers Airplane TypeMulti Propeller Fan Roof Fan Model HDC Cooler Blast Fan Model SCA Cooler Blast Fan Multi-Propeller Airplane Fans are made in sizes 12 in. to 36 in., with 6, 8 and 10 propeller blades and capacities from 985 to 13,000 cfm. The Wolverine Roof Fan is a complete unit for easy installation on new or old buildings. The low instal lation and operating costs are features that appeal to engineers, architects and contractors. Adaptable to roofs with ' angles up to 45 degrees. Provides positive low cost ventilation. Propel lers are made with 12 to 20 blades driven by ball bearing motors. Unique damper design assures automatic and pxjsitive opening and dosing action. Fan sizes from 30 in. to 60 in., and capacities from 5,560 to 45,275 cfm. High Boy The Model H. D. C. Cooler Blast -Fan is a heavy duty portable fan for air circulation and man cooling pur poses. Affords an economical and p)ositive means of cooling where work men are subjected to intense heat or fumes. Available with standard Air plane typ>e or Silentair propeller. Made in fan sizes from 28 in. to 48 in. The Model S. C. A. Cooler Blast Fan is a powerful utility fan, designed to operate on floor, wall or ceiling, adjustable to direct air flow at various angles. Useful in foundries and fac tories. Cfm free air delivery 6,400 to 16,750. Automatic Shutter The Highboy Cooler Blast Fan is portable and adjustable; minimum height 6 ft 1 in., maximum height 9 ft 4 in., with free air delivery of 4,600 cfm. Useful in .hot spots in plants. Also, for offices, stores and homes. Pent House Air-Flo Shutters and Dampers are designed to work with any fan or blower, and prevent entrance of wind, rain, snow or insects. Among the several types are: Automatic, Hand and Motor-op)erated; typ>es of dampers are Automatic backdraft, Automatic Stack, Balanced Ceiling; also Friction, By pass, Volume, Mixing and Louvre Dampers. Air-Flo Pent Houses with automatic shutters are made for fan sizes from 15 in. to 60 in. . Complete catalog with detailed dimensions and capacity tables may be obtained by writing for data on Wolverine products, and helpful assistance is available in planning a Wolverine Fan Installation. 1055 / Air System Equipment Fans and Blowers Buffalo Forge Company 450 Broadway, Buffalo, N. Y. Sales Representatives Albant 7, N. Y.--Mr. R. B. Taylor__1303 Standard Bldg. Atlanta, Ga.--Mr J. J. O'Shea..........305 Techwood Drive Baltimore 2. Md.--Machinery & Equipment Sales. Inc.. 508 St. Paul St. Boston 76, Mass.--Mr. E. D. Johnson. 507 Main St., Melrose Station Chicago 6, III.--Emmert & Trumbo.__ 20 N. Wacker Drive Cincinnati 2, Ohio--Mr. F. W. Twombly..... 626 Broadway Cleveland 13, Ohio--Mr. T. A. Weager. 418 Rockefeller Bldg. Dallas 1, Tex.--Buffalo Forge Co.--Mr. T. H. Anspacher, 1801 Tower Petroleum Bldg. Davenport, Iowa--D. C. Murphy Company. Inc.. .105 Security Bldg. Des Moines 9, Iowa--D. C. Murphy Company. 214 Old Colony Bldg. Denver 17, Colo.--Hcndric & Bolthoff Mfg. & Supply Co., Box 5110 Terminal Annex D Detroit 16, Mich.--Coon-DcVisser Co.. 20S1 W. Lafayette Blvd. Greenville, S. C.--Mr. Roy A. Stipp.--l Longview Terrace Indianapolis 4, Ind.--S. E. Fcnstermaker & Co.. 937 Architects & Builders Bldg. Knoxville 21, Tenn.--Mr. C. F. Sexton. P. O. Box 2224, 702 Empire Bldg Los Angeles 13. Calip.--Buffalo Forge Company. Mr. Frank Halladay, 804 Pershing Sq. Bldg. Miami 37, Fla.--Southern Air Conditioning Co., 149 Northeast 20th Terrace Minneapolis 2. Minn.--Mr. E. F. Bell, 2102 Foshay Tower New Orleans 12. La.--Devlin Bros..^.1003 Maritime Bldg. New York 7, N. Y.--Koithan & Johnson__39 Cortlandt St. Newark 2, N. J.--Mr. G. C. Norman, 27 Washingtoo St., Room 203 Omaha 2 Neb.--Wain Engineering Co., 300 Brandeis Theatre Bldg. Philadelphia 2, Pa.--Davison & Hunger, 1200 Cunard Bldg. Pittsburgh 22, Pa.--Mr. H. Lee Moore___431 Fulton Bldg. Portland 5, Ore.--Arthur Forsyth Company. c/o Alex J. Papulski, 921 S. W. Oak St. St. Louis 3, Mo.--Mr. J. W. Cooper___ _____ 2726 Locust St Salt Lake Cm 1, Utah--Lee Pace A Turpin, 142 S. Fifth West St. San Antonio 6, Texas--Langhammer Rummel Co., 436 Main St. San Francisco, Calip.--Buffalo Forge Company, Charles W. Lockhart, 1200 Central Tower Bldg., . Third and Market Sts. Seattle 4, Wash.--A. T. Forsyth Company, A. T. Forsyth. 500 First Ave., South Toledo 2.0mo--C. M. Eyster Company_H18 Madison Ave. Tucson, Ariz.--Tidmarsn Engrg. Co. ......... 23 N. Main Sti Washington 5. D. C.--Buffalo Forge Company, Mr. G. S. Franket 512 Woodward Bldg. Wilkes-Barre, Pa.--Power Engineering Co., i 517 Brooks Bldg. Kitchener, Ont., Canada--Canadian Blower & Forge Co. PRODUCTS: Heating and Ventilating Equipment including: Unit Heaters, Multiblade Fans, Pipe Coil Heaters, Buffalo Air Washers, Buffalo Unit Air Washers, Buffalo Unit Coolers, Drying Equipment, Mechanical Draft Fans, Air Preheaters, Exhaust Fans, Blowers, Dust Collectors, Disc Fans, Spray Nozzles. Buffalo Limit-Load Fans Buffalo Air Washers Buffalo Limit-Load Fans for ventilating, embody several improvements to deliver stepped-up efficiency under practical con ditions. Durably built for years of service. Dynamically balanced. Quiet, economical to operate. Non-overloading character istic prevents motor from overloading and burning out, regardless of fan load. Axial Flow Fans This non-overload ing high pressure fan--with, direct ional guide vanes-- propels the air stream in a true axial direction. Energy losses are reduced to a mini . mum with a marked power saving. Buffalo Air Washers and Humidifiers are built for the most efficient washing, purifying and tem pering of air under varying atmospheric conditions. Design ed and constructed for low cost in stallation and main tenance. Careful at Type "A" Washer tention to structural details insures long service-ability with a minimum of attention. Several types and | models to meet i specific plant re- :j quirements. Wei Filter Washer Fans for Every Ventilating Need Buffalo Fans represent over 60 years of specialization in the design and construc tion of fans for practically every venti lating. and air-handling application from small kitchen fans to rugged fans for boiler draft. Complete information on request. Buffalo Unit Heaters . "Highboy" and "Lowboy" and "Breezofin" Units for floor, wall or ceiling instal lation. Sizes for all buildings of all types. 1056 Air- System Equipment Far., and sw.,. Champion Blower & Forge Co. Manufacturers and Engineers plant and offices: Lancaster, Pa. Address Correspondence to Div. 9 Manufacturers of Blowers, Ventilating Fans and Exhaust Fans for Air and Material; and Blast Gates Representatives in Principal Cities Type S Forward curve ventilating fans, single and double width, as well as direct motor driye. Sizes 30 in. to 60 in. wheel dia. Type S TypeSV Type BC Type S Forward curve yentHating fans, single ana double width, and electric drive up to 36 in. wheel diameter. Type SV Super Ventilating fans, direct motor drive up to 36 in. diameter. Motor belt drive up to 48 in. size. Type M Axial Flow non-overloading fans for high and low pres sures. Exhausting and Ventilating. Type BC Backward curve ventilating and exhaust fans, single and double width; belt driven and direct connected electric. Sizes 12 in. to 60 in. wheel dia. Type CE Electric cast iron exhaust and forced draft fans. Also volume control dampers. 1057 Type S Type M Type CE Air System Equipment Fans and Blowers Chelsea Products, Inc. 1206 Grove St., Irvington 11, N. J. FANS Charter Members Propeller Fan Manufacturers Association Trade Mark Registered EXPORTED TO ALL COUNTRIES OF THE WORLD BY Western Elecrric Export Corporation FEATURES (On Comfort Coolers) TYPE OPJ--OCTOPUS JRs Portable Exhauster and Blower 1. New Streamline Venturi Orifice--greater volume. General Purpose Pressure Type 2. Certified Ratings--as per ` the A.S.H.V.E. method. 3. Efficient Fan Duty Motors--low current con sumption. TYPE DUB--SHIPHOLD EXHAUST Blower or Exhauster 4. Die Stamped Blades-- precision balance and Align ment. TYPE AA--UTUITY For All Purposes; Answers Any Fan Requirement 5. Moving Parts Rubber Cushioned--quietness. TYPE DXB--BOOSTER For Spray Booths, Fumes, Excessive Heat 6. Ball Bearing, on Fan Shaft--long life and little attention. 7. Faultless A11 Steel Con struction--stability. . TYPE IND--INDUSTRIAL For Factories, Foundries, Laundries . TYPE PH--PENTHOUSE Roof Ventilofor Chelsea Fans are Known All Over the World TYPE LWL--SHUTTER LOUVERS Automatic, Regular end Ceiling Models Bulletins and Engineering Data furnished on request. Personnel includes many skilled operators--employees who have been identified with the air conditioning industry for over 30 years. 1058 Air System Equipment Fan, end Blower, DeBothezat Fans Division American Machine and Metals, Inc. Main Office and Factory--East Moline, Illinois DISTRICT SALES OFFICES Atlanta 3, Ga.............. ............. _...............Candler Bldg. Boston 16, Mass......................... Park Square Bldg. Chicago 4, III... .....................310 S. Michigan Ave. Cleveland 14. Ohio_...... ....................Leader Bldg. Dallas 1; Texas_________ Mercantile Bank Bldg. Kansas City 6, Mo--....................-.Midland Bldg. 2,Minneapolis Minn................................. Foshay Tower New York 7, N.Y.......................... Woolworth Bldg. Philadelphia 7. Pa....................... 12 S. Twelfth St. St. Louis 1. Mo........ ..... Arcade Bldg. San Francisco 3. Calif..................1201 Folsom St. Washington 5. D.C..... ....... .... 1333 "G" St.. N.W. SALES ENGINEERING OFFICES IN ALL PRINCIPAL CITIES Non-Overloading Power Characteristics PRESSURE fflnS Certified Ratings . Guaranteed Performance HIGH STATIC PRESSURES DeBothezat Volume and Pressure Type Axial-Flow Disc Fans have been developed in separate series to cover the extensive range of static pressures and capacities. To meet varying conditions of pressure, load'and speed with equally high efficiency over the Axial-Flow Fan entire range, pitch an gles and motor speeds are engineered to fit each particular ap plication. Available in sizes from 16 in. through 144 in. (Complete "Ventilating Sets" and "Giant Fans" Catalogs, on request). CONTROLLED VENTILATION CORROSIVE FUMES REMOVAL Bifurcodor DeBothezat Bifurcator is an especially designed housing ingeniously.arranged and proportioned in combination with a direct driven axial-flow pressure fan of non overloading characteristics. The air hand led by the fan is by-passed around the drive motor which is placed entirely out side of the air duct in a through ventilated chamber. Available in sizes 16 in. through 48 in. (Complete "Bifurcators" Catalog on request). SPOT COOLING Power-Flow Roof Ventilator DeBothezat Power-Flow Roof Ventila "Hy-V" Air Jet tors of guaranteed performance ratings, DeBothezat "Hy-V" Air Jets are extra dynamically .correct in design, are rigidly ordinarily efficient man coolers, particu constructed. Streamlined and of low larly for. workmen who are exposed to height, they present a trim appearance. radiant, heat from ovens, furnaces, forges Positive controlled ventilation is assured at and molten metals. Arranged for either all times independent of variable weather -column or floor mounting, they are adjust factors or wind velocities. The hinged - able to blow a concentrated blast of cooling hood provides ready access to motor and air in any direction to remote spaces with fan. Available in 16 in., 21 in., 27 in., and out the aid of ducts. Available in 18 in. 36 in. sizes. (Complete "Roof Ventila through 30 in. sizes. (Complete "Hy-V tors" Catalog on request). ' Air Jets" Catalog on request). 1059 Air System Equipment Propeller and Centrifugal Fans ILG Electric Ventilating Go. 2832 North Crawford Ave., Chicago, 111. Offices in 40 Principal Cities Propeller Fans, Vaneaxial Fans, Centrifugal Fans, Unit Heaters, Unit Coolers ILG Self-Cooled Motor Propeller Fans Used for exhaust of stale air, fumes, heat, dust, odors, etc. Self-cooled motor combines protection ofenclosed motor with low operating cost of open motor--con stantly cooled by fresh, clean air, circulated internally-- never "gums-up" from contact with foul air--saves 5 to 10 per cent on power costs. Rugged, heavy-duty framework. Dynamically balanced fan wheel, directconnected to motor. Smooth, quiet, effortless opera tion--low cost, long lived. "One-Name-Plate" Guar antee. Certified ratings. Sizes,/8 in. to 72 in. Get Catalog No. 145. ILG Vaneaxial Fans Heavy-duty, extremely compact design, as developed by ILG for use aboard ship by the U. S. Navy and Maritime Commission. Suitable for duct and trunk mounting for vertical and hori zontal operation. All steel housing flanged at both ends. Removable streamlined inlet cone. Guide vanes straighten air flow, reduce turbu lence. In ILG design, vital working parts are quickly, easily accessible for installation, lubri cation, or servicing. Proven efficiency and dependability. "One-Name-Plate" Guarantee 1XU0 iInII.. tIUo 41U6 i1n11.. ssiuzeeds.. GUCetl ^mTTTfc new data sheets. 7' "UN" TYPE FANS "CQ" TYPE FANS KITCHEN VENTILATORS NIGHT COOLING FANS For vertical or hori- For mounting Built-in becomes perma- For permanent in- zontal mounting outside of ducts, nent part of kitchen wall, stallation in. attic, anywhere except in Wide range of Quiet, high capacity, effi- use ILG Self-Cooled ducts. Several sizes and models cient, equipped with ILG Motor Propeller models with various for various Self-Cooled Motor. 3 sizes. Fans (top of page), mounting arrange- mounting ar* Also models for window Portable models ments. Get data rangements. Get installation. Get Catalog for use at down- sheet. data sheet. * No. 142. stairs windows. . FOR ILG UNIT HEATERS AND.COOLERS, SEE PAGE 982 1060 Ilg Electric Ventilating Co. Air System Equipment Propeller and Centrifugal Fans DIRECT-CONNECTED CENTRIFUGAL FANS MBC" Type--Load-limiting type with backward curved blades. Motor load re mains constant over wide range of air vol ume and change in static pressure. Wheel mounted directly on -motor shaft with motor partially recessed in side of casing. No motor base required. Unobstructed inlet. Also available for belt-drive. 11 sizes. Get Catalog No. 245. "CC" Type--All steel, heavy gauge, hot dipped galvanized, welded housing--no angle iron braces. Flanged inlet and outlet connections. Non-overloading type wheel mounted directly on motor shaft, with motor partially recessed in housing to save space--no motor sub-base required. Un obstructed inlet. 11 sizes. Get Data Sheets. ~ ' "B" Type--Motor re cessed in side of casing, eliminating separate base. Multiblade, for ward-curved wheel direct-connected to motor shaft. Also avail able for belt drive. 12 sizes. Get Catalog No. 245. "BW" Type--Housing similar to ILG DirectConnected Centrifugal Fans. Wheel with for ward curved blades. Full universal discharge, right or left hand drive. Wide range of sizes. Get Catalog No. 245. Type MB" Volume Blowers--Small volume, low pressure, quiet run ning. Multiblade wheel direct-connected to motor shaft. Cast-iron base. Universal dis charge. 12 capacities. Get Catalog No. 145. Type "P** Volume Blowers--For exhaust ing dust, fumes, removal of steam, vapors. Four discharge positions to avoid friction ip short bends. 7 capacities. Get Catalog No. 145. Type "6S" Utility Blowers--Particularly suitable for building into apparatus which requires ventilation or air movement. Extremely flexible in arrangement, furnished with or without inlet flange, outlet flange, stand, etc., providing a practically custom-built unit on basis of quantity manufacture. Wide pressure range. Low power input. Get specifications, including dimensions and performance graph. - 1061 /' Air System Equipment Fans and Blowers LA-DEL CONVEYOR & MFG. COMPANY ENGINEERS OF NEW PHILADELPHIA, OHIO MANUFACTURER OF AXIAL FLOW FANS AIR MOVEMENT AXIAL FLOW FANS FOR EVERY VENTILATION PROBLEM Designed to meet the specific require What Does This Mean To You? ments of every type of ventilation-- industrial, commercial, aviation marine or domestic--La-Del Axial Flow Fans provide quiet, efficient operation, free from exces sive maintenance and noise. La-Del fans, are available in a wide range of types and sizes to meet every need; each installation is custom-engineered to provide new standards of quiet, efficient, low-cost , and trouble-free operation. La-Del has the experience and technical knowledge necessary to provide the correct answer to every ventilation problem. La-Del experienced ventilation engineers study each application; La-Del's modern production planning and manufacturing methods insure the utmost in space-saving ventilating fans, designed to operate at low power cost. Simply that a La-Del Axial Flow Fan will provide ventilation, where it is needed, in an economical manner. The flow of air you require to eliminate smoke, noxious odors or other atmospheric conditions, goes directly to the point where it will be immediately effective. Here is a truly economical and efficient means of ventilation--air, passing directly through the duct, is moved at low cost, and it provides efficient ventilation, with out excessive power consumption. Fur ther, La-Del can also furnish exclusive adjustable pitch blades which broaden the useful operating range of the fan by fully 75 per cent. Such fans have already been tested and fully proved-on the most difficult ventilating applications. One of the foremost suppliers of our Armed Forces during the war years, Special Fan For N.A.C.A. La-Del's , expanded production facilities allow the manufacture of Axial Flow Fans in a liberal capacity range, permitting the ' selection of the fan that will provide, the ventilation you require in the most ef ficient manner. What Is.True Axial Flow? The Axial Flow Fan consists of one or several rotating wheels, carrying twisted, airfoil-shaped blades on a round hub and counter-rotating devices that suppress the twist in the -air caused by the rptating wheel. Its aerodynamic design eliminates all turbulence behind the fan propeller, permitting the building up of high pressure and .the consequent conveyance of air straight through the duct. La-Del ability to handle the unusual and difficult jobs is evidenced by this huge blower furnished the N.A.C.A. Aircraft Engine Research Laboratory. It is a life saver to lest pilots and capable of producing on air speed of 50 miles per hour. This La-Del fan permits test' engines to be operated at maximum take off Power and eliminates the danger of take-offs with untried engines. Its output is 60.000 cfm at 45 in. PS; weighs several tons and yet portable os shown. Two stage, adjustable pitch, equipped with 000 hp motor and auxiliary blower s that ventilate the main motor through hollow vanes. 1062 La-Del Conveyor & Mfg. Co. Air System Equipment and Blowers Check These Outstanding LA-DEL Features 1-- Flared intake and streamlined nosing 5-- Propeller blade from tip to hub is a assure uniform air flow distribution at fully effective working surface, with propeller blades. blades terminating inside the hubs. 2-- Streamlined belt fairings fully enclose drive belts, prevent leakage, protect 6-- Streamlined . tail maintains uniform . belts from air stream and avoid turbu axial flow without turbulence. lence ahead of blades. 3-- Adjustable pitch propeller blades for 7-- Fan efficiency is directly affected by peak efficiency with balanced character stack efficiency. Carefully calculated istics throughout adjustment and fan stack design results in uniform air flow operating range. and low exit velocity. 4-- Straightening blades scientifically de signed to correct helical motion im 8-- Fan and stack diameters (at-small end) parted by propeller blades to a true correspond to keep frictional losses at axial flow. lowest point. (FFFIPTFNT \ ECONOMICAL/ VENTILATION From the smallest to the largest, La-Del is prepared tofurnish an axial flow fan to meet every requirement. At the left, an aviation type fan, only 6 inches long and 6H inches in diameter, delivering 400 cfm at 6 in. pressure. At the right, a La-Del Fan installation with exhaust stack and'hood. This fan, 11 ft in diameter, delivers 600,000 cfm at 6^ in. sialic pressure. - For space-saving efficiency, reduced oper ating cost, unexcelled performance, quiet operation and freedom'from maintenance troubles--remember La-Del when planning ventilation. * La-Del Ventilation Engineers will gladly show you how and why--send your inquiries, outlining your require ments, direct to The La-Del Fan Company, Division of La-Del Conveyor & Manu facturing Co., New Philadelphia, Ohio. 1063 Air System .Equipment -.Fans and Blowers Hartzell Propeller Fan Co. DIV. OF CASTLE HILLS CORP. ` Piqua, Ohio . Sales-Engineering Offices in Principal Cities Manufacturers of Propeller-Type Fans and Blowers For Every Industrial Use SINGLE PROPELLER FANS TWO-PROPELLER FANS Sizes, 12 to 144 in.; free air deliveries 590 to 270,000 cfm. NEW curved orifice overlaps propeller tips, forming Hartzell Airseal (pat-. ented), giving extra air delivery, minimum tur bulence. Send for Bulletin 1101. Sizes, 16 to 144 in.; free air deliveries 2,400 to 275.000 cfm. (Up to 200.000 cfm against 0.34 in. static pressure) NEW curved orifice and patented Hartzell Airseal mean maximum air. Send 1101. for vBulletin MULTIBLADE FANS BLOWERS Sizes, 12 to 144 in.; free deliveries 1,200 to' Sizes. 18 to'48 in.; free 280.000 cfm. (Up to air deliveries 3,300 to 200.000 cfm against 50,500 cfm. (Up/ to 1.00 in. static pressure) 34.000 cfm against 8 in. Long life, low upkeep. pressure). Built in NEW curved orifice both belt drive (shown) and patented Hartzell and direct drive models. Airseal. Send for Bul Easy installation. letin 1101. Send for Bulletin 1601. BELT-DRIVE FANS Sizes, 12 to 144 in.; air deliveries .590 to 280.000 cfm. Avail able in one-propeller, two-propeller and multiblade styles. For use in fire-hazardous locations such as paint spray booths. Greasesealed, dust free ball bearings. Send for Bul letin 1401. EXTENSION SHAFT FANS COOL BLAST FANS Models: Portable, Sta tionary and Heavy Duty Cool Blast Fans (stationary shown), sizes 24 to 55 in., for large-volume air move ment; Industrial Stand Model, up to 36 in. size, with substantial but light-weight high stand; Utility, up to 36 in. size, extremely versatile, with simple, close-to-the-ground mounting. Send for Bulletin 1201. Sizes,'12 to 55 in.; types, one-propeller, two-propeller and multiblade. Designed for use in ducts'through which corrosive elements, excessive heat or abrasive dust passes. Send for Bulletin 1401. COOLING TOWER FANS Sizes, 3 to 16 ft; four and six blades, ad justable pitch. 10 to 16 ft sizes are special Hartzite plastic, steel hub. Smaller sizes are aluminum alloy- Send for Bul letin 1501. SPECIAL EQUIPMENT There is a Hartzell fan or blower to meet your needs or we will design and build one for you. Write. All Hartzell air deliveries are in accordance with the standard Test Code for Centrifugal and Axial Fans. 1064 Air System Equipment Fans and Blowers Blower Wheels The Lau Blower Company 2007 Home Avenue, Dayton 7, Ohio Engineers and fabricators of general' Air Handling Equipment Single Inlet and Double Inlet Blowers Propeller Fans Accessories NEW Series "A" Blower Assemblies Special Features Patents A pplitd for The Lau Series "A" Blower Assembly--result of years of exhaustive tests of all types of blowers--years of research and design evolution --is the all-time, outstanding achievement in the blower field. Greater mechanical strength. Greater efficiency. A more compact unit (overall size considerably smaller thart formerly). Will fit more jobs. Embodies many new and revolutionary features exclusive with Lau. Includes new 3-point suspension type bearing bracket--an integral part of the shroud-- identical for various angles of discharge. New frictionless, self-aligning bearing--completely encased in Neoprene. New center suspension wheel (see below). New discharge outlet design and construction. Cut-off cannot set crooked on outlet. No wavy edges. Faster installations. New 1-piece .motor mounting easilyconvertible, rear to top or vice versa, by simple use of two sheet metal screws. Many other features. Complete range of sizes. Every size tested and rated for performance in accor dance'.with A.S.H.V.E. and N.A.F.M. Codes. NEW Series "A" Blower Wheels ' ' New center-suspension wheel tested and proved by us to have greater mechanical strength, truer concentricity, and far more efficient performance than ordinary types of wheel. Complete details supplied to interested parties upon request. Propeller-type "Niteair" Fans For a wide variety of applications where it is necessary or advantageous to exhaust undesirable air and provide fresh air from the outside. Equally applicable for indus- trial, commercial, residential and farm building installations. Efficient and' economical method for correcting innumerable air-control problems--removing dust-laden, .foul, contaminated, or excessively hot air, fumes, gases, smoke. Circulating cool night air through living and sleeping rooms for greater summer comfort. Venturi-type entrance housing reduces air "drag" and turbulence--eliminates most common cause of "air noise." 5 sizes--22 in. to 48 in. Self-aligning Pillow Blocks Catalogs, performance data, specifications, and prices available on request on above and other air handling equipment. Inquiries solicited for any application. Our engineers will gladly assist you. Write us regarding your requirements. . 1065 Air Syslem Equipment Fans And Blowers Blower Wheels MORRISON PRODUCTS, INC. East 168th St. . & Waterloo Rd. Cleveland 10, Ohio Blower Wheels BLOWER WHEELS for MANUFACTURERS OF WARM AIR HEATING AND AIR CONDITIONING Every manufacturer whose products employ blowers will welcome the MORRISON AIRSTREAM Blower Wheel--an outstanding advancement in the art of fan design and manufacture. The MORRISON AIRSTREAM Blower Wheel is a definite stride for ward in aerodynamic design. . ONE-PIECE blade construction All blades in every Blower Wheel are made from one strip of soft steer on progressive die equipment, eliminating any possibility of loose blades. THREE-PIECE BALANCED ASSEMBLY Two pressed end rings with integral hubs and a one-piece blade assembly constitute the . complete blower wheel. When spotwelded together, these three pieces form a strong, rigid, true running blower wheel. . EQUALIZED WEIGHT DISTRIBUTION End-mounted Blower Wheels distribute their weight closer to the' bearings. Smaller shafts and bearings are therefore permissible. Shaft whip is eliminated and shaft deflection- reduced. - LIGHT IN WEIGHT MORRISON AIRSTREAM'S unusual design reduces weight to a minimum. Integral pressed hubs eliminate heavy cast or screw machine parts. Lightness affects motor loads--makes for quieter operation and reduces starting torque. MORRISON AIRSTREAM BLOWER WHEELS are furnished in standard diameters of 10;Hs in., 12 in., 14J4 in. and 16 in. and in various widths. Catalogue showing equipment required for manufacturing blower housings and drawings showing suggested method of manufacturing complete blowers furnished upon request together with performance data on various sizes. 1066 Air System Equipment Fans and Ventilating Eq uipmen t G/>e If NEW YORK]! I BLOWER I I .CO^IPANY, 1 GENERAL OFFKES 3145 SOUTH SHIELDS AVENUE CHICAGO 16 OCIOIIU TI l A roilf. I N O FANS Representatives in Principal Cities BLOWERS UNIT HEATERS MAKE-UP AIR UNITS AIR WASHERS HEAVY DUTY HEAT SURFACE M15--15.000 cfm A unit that delivers, warmed, filtered, out side air to industrial spaces to replace exhausted air and balance minus pressure. Corrects drafty conditions and uncontrol led infiltration. Made in 4 sizes from 5,000 cfm to 20,000 cfm. Described in Bulletin 458. - Type ME Centrifugal Fans Comet Unit Heaters Heavy duty, welded steel, fin-and-tube heating element. Suitable for con tinuous heating service on steam pressures up to 150 lb or more. 10 sizes with capacities from 31 Mbh to from 31 Mbh to 300 Mbh. Bulletin 454- Comet Exhaustair Delivers large volumes of air at low resistance and low current con sumption. AH wheels are machine balanced for smooth, vibration less operation. Made in three types and ten basic sizes. Wheel dia meters from 12 in. to 60in. Direct or belted drive. Capacities from 400 cfm to 33,500 cfm. Ask for Bulletin 448. Quiet operating slow speed wheels for heating, ventilating and air conditioning systems, or high speed wheels with no n-overloading horsepower charac teristics for industrial applications. Wheel diameters from 15 in. to SO in., with any speed or discharge required. Class I, II or III construction. Capacities up to 108,000 cfm. Type SSP Industrial and Heat Fans For dust and gas re moval, conveying- of. materials and handling hot gases. Housings, drives, and discharge arrangements to meet any requirement. Wheel diameters from 14 in. to 66 in. Capa cities from 450 cfm to 60,500 cfm. Details and engineering data in Bulletin 452. General Purpose (Jeep) Fans Steelfin Hot Blast Heating Surface Extra heavy duty, finand-oval tube, alhsteel, welded construction. A hot dip metallic coating over ail, including head ers, affords perfect bond ing and conductivity. Suitable for continuous .heating service on steam pressures up to 150 lb. Portable, self-con tained units for Class I industrial and ventilating ap plications. Recom mended for ease of installation, low maintenance and space saving fea tures. Made in three types and eight basic sizes. Capacities 400 cfm to 12,000 cfm. Bulletin-448. 1067 Air System Equipment Fan, and Blower PROPELLAIR Inc. SPRINGFIELD, OHIO VENTILATING SPECIALISTS IN ALL PRINCIPAL CITIES For Ducts, Walls, Win dows, Hoods, Roof Venti lators PROPELLAIR DIRECT-CONNECTED FANS For use wherever motors' may operate within the air stream, from free air to medium and relatively high resistance. A compact, durable design with fan having two to six blades. Sizes: 12 in. to 60 in. Capacities: 800-85,000 cfm. Type "CD." For Heat, Acids, Alka lies--Fumes, Gases, Dust BELT-DRIVEN PROPELLAIR DRUM-TYPE A complete fan unit in short duct section ready for installation in lines from 20 in. to 48 in. diameter. Type "CS" may be used for severe acid or alkaline conditions, explosive fumes and gases. Type "CSV," for excessive temperatures, circulates out side air through belt and fan shaft tubes to keep drive and bearings cool. Also furnished without duct section. Capa cities: 4100 to 43,000 cfm. For Roof Ventilation PROPELLAIR VERT1-STACK Dependable and eco nomical power roof ventilators. Butter fly dampers open wide the instant fan is __ ____ __ started, close auto '__________ matically as fan coasts to a stop, offer virtually zero resist ance as heat, fumes, moisture, dust shoot high into air. Rain is prevented from entering by fan when operating. Drainage gutter prevents leakage when dampers are closed. Sizes: ' 20 in. to GO in. Capacities: 3700 .to 77,000 cfm. For Heat, Moisture, Fumes, Dust, and Gases PROPELLAIR EXTENDED-SHAFT FANS This design^ locates /motor outside air stream when fan is installed in duct at right angle turn, elbow, "Y," or offset. Simple installation usually can be sup ported by duct without auxiliary bracing. Drive shaft is enclosed and sealed within steel tube. Sizes: 12 in. to 60 in. Capa cities: 2000 to 68,000 cfm. Type "CE." For Cooling Men and Materials PROPELLAIR PEDESTAL & CRADLE-MOUNTED FANS Pedestal-type Man Cool ers have sturdy steel N drum protected front and rear, formed steel base, rigid support, and crane hook. Also made with- adjustable cradle mounting (Type "CU"). Capacities to 20,650 cfm. \ AIRFOIL-SECTION Blades Airfoil Principle Entrance Ring Propellair fans have airfoilsection blades with variations of pitch, curvature, and thick ness to compensate for differ ent Lineal speeds of points at various radii. Air movement is uniform over whole fan area. The Propellair curved entrance ring eliminates eddy currents; helps efficient Propellair blades deliver highest pressure and volume. T Air System Equipment "fHo Propeller Fan Manufacturers Association 2-255 General Motors Bldg., Detroit 2, Mich. When you see the PFMA Certified Rating Insignia, you know that the company displaying it certifies that the performance of its products is in strict accordance with the Standard Test Code. ' Air tunnel design for Standard Test Code measurements is illustrated below, the propeller fan under test being mounted at the discharge end. Exhausters without Duct Supply Duct Supply Duct: Velocity pressure, . Chamber pv', Differential reading between impact Fan Outlet tube and static tube. Chamber: p ... by impact tube. Fan Outlet: Pvr Correct pv to Pv, the velocity pressure D0 corresponding to the area A of the minimum ring diameter. Pt`, add p to Pv. P&`, Subtract Pv from Pt. Correct all pressures to Standard Air Conditions. All additions and subtractions mentioned above are arithmetical. Testing equipment and methods are prescribed in detail by the Standard Test Code, from which the accompanying air tunnel dimension diagram is reproduced to indicate the exactitude which is required in PFMA testing. Copies'of the complete Standard Test Code are available for 25 cents through the Association. The PFMA insignia shown at the right, is your assurance of a dependable.basis to judge fan- performance. Guess work is eliminated and data listed are reliable and based on sound engineering technique, permitting you to evaluate comparative performances. Where fans are rated by Standard Test Code procedure, volume, pressure, power input, mechanical efficiency and all related factors, are measured under precisely controlled conditions. . Look for the PFMA insignia Insist upon Certified Fan Ratings s' i 1069 Air System Equipment Fans and Blowers Blower Wheels The Torrington Mfg. Go. 50 Franklin Street, Torrington, Conn. Manufacturers of Blower Wheels and Propellor Type Fan Blades. Left--Airoior Blower Wheel--Single Width--Single Inlet Patents 2,131,062; 2,231,063; Des. 126,043; 2,272,695 ' Right--Airoior Blower Wheel--Double Width-- Double Inlet--Spider End Plates Torrington Airotor Blower Wheels are light, sturdy and inexpensive--incor porate new principles of design and con struction, which insure rigidity and con centricity. Single Width--Single Inlet wheel is of simple four-piece construction. No rivets or welds are used; concentric rib serving as backing for blade strip is formed at same time as hub socket, insuring trueness of wheel. Rigid radial ribs prevent deflection by thrust. Three thicknesses of metal in rims make for maximum strength. Excellent for many heating and ventilating uses. Manufactured imboth aluminum and steel in 1)^ in., 2,3,3^8, 4}^, 5,6,9 and 10^ i- diameters. Clockwise or counter clockwise rotation. Same sizes available- in DA type double width, double inlet, wheels. ,' Torrington Airotor Blower Wheel-- Double Width--Double Inlet--Spider End Plates. Has blades punched and formed in a single strip, rigidly held by flanged single piece end rings. Hubs are rigidly mounted by peening. Wheels of 3% in., and 10H in. diameter are available at present. Additional sizes now being developed. Airistocrat "Standard" Series Pats. 2.072322 and 2,021,707 3-Blade Airistocrat "Y" Series AIRISTOCRAT Quiet Propel ler Fan Blades are widely recognized for their all-around excellent performance. The unique, patented construction em bodies entirely new principles in the art of fan design--produces a blade unsurpassed for quiet operation, rugged construction and attractive appearance. Every Air istocrat unit is carefully built and the blades are hand gauged for correct contour and alignment. Statically balanced, these blades deliver full air volume with a minimum of noise. Aluminum alloy blades and steel spiders are standard except where otherwise noted. . Available in a variety of finishes. Catalog gives detailed dimensions and guaranteed performance curves recorded under NEMA and NAFM code tests at various speeds for each of the Airistocrat models described on page 1071. New Blower Wheel Catalog charts capacities, gives detailed dimensions, sug gests housing dimensions for all above wheels. Valuable "Tips" for designing air impelling units are also included. 1070 The Torrington Mfg. Co. Air System Equipment Fans and Blowers Fan Blades "Standard" Series--Has blades mounted on a steel spider. Sturdy, attrac tive steel or aluminum blades which have withstood extreme laboratory breakdown tests. Sizes 8 in., 10, 12, 14, 16, 18 and 20 in. diameters in a variety of pitches to meet every need. Three Blade "Y" Series--The design of this blade is the result of two years of laboratory experiment to produce a better air circulator blade. At recom mended speed these blades produce a high velocity air stream effecting deep penetra tion with unusual quietness. Sizes 10 in., 12, 14, 16, 18, 20, 24 and 30 in. diameters, steel or aluminum blades. . Pressure "P" Series--Similar in con struction to ``Standard'' Series but with blades especially designed for higher pres sures. Sizes 10 in., 12, 14, 16 and 18 in. diameters. . Pressure "IP* Series-Four blade models of steel designed for pressure operation. Sizes 20 in.; 22, 24, 26, 28 and 30 in. diameters. - AIRISTOCRAT "B" Series Attic Fan Blades represent a complete redesign of the popular "A" Series. Efficiency has been still further improved. The same proportions, proved aerodynamically cor rect, have been carefully^adhered to in all diameters. New larger center disc and heavier spider arms increase strength and a new blade shapejidds to the appearance of this carefully"designed product. Flexi bility of parts allows assembly with either 3, 4 or 5 blades in standard diameters 24,' 30, 36, 42 and 48 in. All steel construc tion. Available in the following finishes: 1. Plain. 2. Colored lacquered blades, black lacquered spider and hub. 3. All one color lacquer. "One-Piece" Series Propellor Fan Blades--Exceptionally rigid models blanked from one piece of metal. Made in both steel and aluminum. Sizes 3 in., 4, 4^, ht 5Hr 6, 6M. 8, 9, 10, 12 and 16 in. diameters, all four blades; also 5)^, 7, 8, 9, 10 in. 5-blade. Available in the following finishes: 1. Tlain. 2. Lacquered. 3. Nic kel or cadmium plated (steel only). 1071 4-Blade Airistocrat Pressure Fan "P" Series 4-Blade Airistocrat Pressure Fan "U" Series 4-Blade "One Piece" Airistocrat Fan Air System Equipment Fans and Blowers Schwitzer-Cummins Company 1125 Massachusetts Avenue Indianapolis 7, U.S.A. Engineers and Manufacturers of Centrifugal Blowers and Blower Wheels--Attic Fans--Ventilating Fans of All Types PRODUCTS OF THE VENTILATING DIVISION HY-DUTY BLOWERS SINGLE INLET AND DOUBLE INLET Ruggedly built and especially designed for fine performance and quiet operation. Four different out let positions for double inlet models, eight positions for single inlet. Wheel diameters 9% in. to 25 in. Air deliveries 200 cfm to 15,000 cfm. N.A.F.M. code tested. HY-DUTY BLOWER WHEELS We are tooled for a large range of sizes, single inlet and double inlet, diameters 4^ in. to 50 in. in many , widths. Can furnish our standard wheels or build to your specifications. HY-DUTY wheels in SchwitzerCummins blowers are the center disc, wide blade type with heavily reinforced driving discs and are accurately balanced. FRESH-AIR MAKER HOME AND INDUSTRIAL VENTILATORS A rugged; all welded, light weight, low cost, high delivery, ball bearing ventilator with unusual flexibility for installations in homes, apartments, factories, busi ness establishments. FIVE FAN DIAMETERS 24 in., 30 in., 36 in., 42 in., and 48 in. 5000 cfm to 20,500 cfm. A beautiful Fresh-Air Maker window ventilator designed to harmonize with the most luxurious apart ment furnishings. Unique features for quick instal lation without alterations to surroundings so tenant may possess his own ventilator. Catalogues and Engineering Information on Request * 1072 Air System Equipment Fans and Blowers Heaters, Coolers ' Utility Appliance Corporation formerly utility fan corporation 4851 S. Alameda St., Los Angeles 11, Calif. Utility Gas-Fired Heating Equipment, Evaporative Coolers, Blowers and Fans FORCED AIR FURNACES Basement and closet types . . . Compact design ... Multiple-fin ele ment with air-cool ed hollow baffle ... Element guaran teed against burn out forever . . . Automatic controls ...Filters...Builtin motor overload protection. EVAPORATIVE COOLERS Comfort cooling-- residential, com mercial, industrial. Exclusive feature-- Uni-flowmeter (Pat. Pend.) for uniform water- dis tribution. Patented No-Sag cooling pads. 14 Models. UNIT HEATERS Compact heat ex changer with no in side baffles--Indi vidual burners for 'each element section --Silent, disc-type fan--All-welded cabinet--Direction al grilles--Built-in draft diverter-- Temperature limit control. Four sizes. , STANDARD BLOWERS Dynamically bal anced, multiplevane centrifugal blowers. Four-side angle iron frame in creases rigidity, eli minates vibration --permits installa tion with any of four discharge positions. FLOOR FURNACES All-welded con struction . . . Diestamped grilles . . . heavy cast-iron burner ... re movable inside jacket . . . inter locking gas valve. Floor or dual regis ters. 25,000, 37, 000 and 50,000 Btu input. EXHAUSTERS High flow and high pressure designs in four drive arrange ments, for exhaust ing many materials. High efficiency . . . decreased sound. Available with acidr proof plastic sur facing. CIRCULATING HEATERS Fan sends stream of air through nozzle shaped outlet to hold warm air in living zone. Built of heavy furniture, steel ... all dieformed and electric welded.' Vented and unvented . models. CLOVERLEAF TYPE FANS Propeller Fans are available with Cloverleaf (over-lapping) or Streamline type blades, with direct or belt drive for mounting into windows, openings, or on steel or wood panels. Utility Blowers are tested in accordance with the A.S.H.V.E. Code. Write for complete information, catalogs and prices, 1073 Air System Equipment The Viking Air Conditioning Corporation 5600 Walworth Avenue, Cleveland, Ohio Viking products, which inelude blowers, fans, and humidifiers, offer top econo my and efficiency to furnace and air conditioning manu facturers because Viking specializes in equipment for air conditioning. The eco nomies of mass production due to specialization are thus passed on to all Viking customers. BLOWERS AND BLOWER PARTS FOR Air Conditioning Manufacturers COMPLETE ASSEMBLY Viking's blower assembly embodies several entirely new features, among which are the streamlined bearings, the new-type blower wheel, the lower outlet, and the smaller unit size overall. Space savings alone in 10 in. blowers run 2% in. in height and \M in. from front to back. Extremely specialized equipment plus high production of 9 in., 10 in., 12 in., 14 in., and 16 in. blowers result in completely assembled blowers at practically the cost of parts oaly., . STREAMLINED BEARINGS C.F.M. (25'INLET) 1. Conventional Bearing Assembly 2. Viking Streamlined Bearing 3. Inlet Free--no obstruction Important innovation in bearing design is this unit Viking Streamlined Bearing. Note the graph at left for comparative record of Free Areas. You see that whereas a typical bearing allowed 77 per cent Free Area'for air intake, the Viking Streamlined Bearing permits an 85 per cent Free Area, resulting in improved overall performance of the entire blower assembly. \- BLOWER WHEEL Viking blower wheels are produced by a continuous stamping process and consist basically of only 6 parts-- 2 blade sections, 2 spoke ends and 2 hubs. Larger inlets help provide increased air delivery. The wheels are designed for the higher pressures of modern air conditioning requirements. Costs are lower than for any pre-war wheel. . Send For More Information Though parts alone are available if desired, the majority of standard requirements can be met most profitably with a Viking assembly. As specialists in making air conditioning blowers, we invite your inquiries. Write for our Special Manufacturers Brochure, which explains Viking facilities and products. Address Desk A. 1074 Air System Equipment Motors Established in 1891 Warner ELedfeic Corporation Sales Offices in 29 Principal Cities 6464 Plymouth Avenue, Saint Louis 14, Mo., U. S. A. Wagner Motors Give Maximum Efficiency on Heating, Ventilating, and / Air Conditioning Equipment . Wagner motors embody the latest developments in design. They are simple, rugged, and dependable and have long life in addition to good electrical performance. Split-Phase Motors . All standard frequen cies and voltages; sleeve and ball bear ings; open, dripproof, and totally-enclosed; rigid, resilient nd flange mounted, (Mo to J-i hp).- Permanent Split-Capacitor Motors Capacitor-Start Motors All standard fre quencies, and volt ages; sleeve and ball bearings; . open, totally-enclosed, and dripproof; hori zontal and vertical; rigid, resilient, and flange mounted. (Mo to % hp). Available, as constantspeed, two-speed, or ad justable-speed. All stand ard frequencies and volt ages; sleeve bearings; totally-enclosed; round frame with rubber mounting rings; (Mo to K hp)- Shaded-Pole Fan Motors Squirrel-Cage Induction Motors AH standard frequen cies and voltages, sleeve and ball bear ings; open and totallyenclosed ; horizontal and vertical. Made in several electrical types varied as to torque and . current characteristics. (2- and 3-phase, M to 400 hp). 50 or 60 cycles, 115 or -230 volts; sleeve bear ings ; totally-enclos ed; rigid, round . frame, or resilient mountings; with or without 3-speed regu lator. Wagner Direct-Current Motors Available in drip proof frames, rigid mounted, in all standard voltages, with sleeve or ball bearings. (Mo to 3 hp). Repulsion-Start Induction Motors All standard fre quencies and volt ages; sleeve and ball bearings; open, to tally-enclosed, and dripproof; horizon tal and vertical; rigid and flange mounted (small sizes resilient mounted). (Y% to 15 hp). Write for Complete Information Bulletin MU-185 will 'give you a compre hensive description of single-phase' and poly phase motors. M46-1 1075 Air System Equipment Motors APPARATUS DEPARTMENT GENERAL ELECTRIC SCHENECTADY. N. Y. Sales Offices, Warehouses, Service Shops, and Distributors in Principal Cities MOTORS FOR HEATING, VENTILATING, AND AIR CONDITIONING General Electric offers a complete line of motors for compressors, fans, and pumps, from which you can select easily the motors with electrical and mechanical character istics best adapted to your equipment.- Many of the most common applications are listed below. Information on other motors--vertical, enclosed, etc., with various electrical and mechanical modifications--can be obtained at a G-E office near you. For additional information, ask for Motor Catalog GEA-4281. Tri-Clad induction motor. Type K. Polyphase Fractional-horse-power capacitalor-motor, TyPeKC SOME G-E MOTORS AND THEIR USES Application * Speed Type Winding Fans and Centrifugal Pumps ' Reciprocating Pumps ana Compressors Small Direct-connected Belted Fans. Centrifugal Pumps \ Reciprocating Pumps ana Compressors Pumps, Compressors. Fans Constant or Adjustable ' Shunt Compound Constant Capacitor, Normal torque Capacitor, High-torque Constant Resistance. Split-phase Shaded-pole Constant or 3-speed Capacitor, Low-torque Constant Capacitor, Normal-torque Repulsion-induction Constant or Multispeed Squirrel-cage. Normal-torque Squirrel-cage, High-torque Constant or Adjustablevarying-speed Wound-rotor - Constant Synchronous Type Horsepower Range Power-supply Classification B&CD 1/8--200 Direct- B&CD KC ' 1/8--200 1/4-3 KCJ KH KSP . KCP KC SCR K. KC M TS 1--3 1/40--1/3 1/50--5 1/4-3 5--10 1/4-1000 5-200 1/2--1000 25--2000 . Single-phase. Alternatingcurrent Polyphase, Alternatingcurrent Types of Enclosures: Open (dripproof)--protected from falling objects or dripping liquids. Splashproof -- where wetness is a factor. Totally enclosed -- for complete protection. Explosion-proof--for inflammable gases. Dust-explosion-proof--for com bustible dusts. Trade-mark reg. U. S. Pat. Off. 1076 Air System Equipment controls APPARATUS DEPARTMENT GENERAL ELECTRIC SCHENECTADY, H. Y. Sales Offices. Warehouses, Service Shops, and Distributors in Principal Cities CONTROL FOR HEATING, VENTILATING, AND AIR-CONDITIONING MOTORS General Electric offers a complete line of standard manual and automatic controls for all types of motors driving compressors, fans, pumps, etc. Publications describing these items, as well as such control accessories as pressure governors, pressure switches, float switches, electrically operated valves, and indicating selsyns, are available on request. For special applications, G-E control to meet your exact requirements can be designed. Most frequently, however, the needs of the air-conditioning industry are best served by one of the many possible G-E "packaged" control combinations desig nated as Cabinetrol* equipments. Typical Cabinetrol unit, shelving open motor-starter panels The Cabinetrol system of motor control is based upon the use of,standardized enclo sures equipped with standard cofftrol devices. General Electric can build quickly most air-conditioning control systems--simple or complex--by properly combining standard control units and accessories into the required number of basic Cabinetrol sections. If future expansion should require further control equipment, additional Cabinetrol units can easily be added to the basic system. . The standard enclosures used in the Cabinetrol system will mount standard motorstarting devices up to and including NEMA Size 4. Ample space, is provided for incoming-line, feeder, and metering equipment. Bulletin GEA-3856 details more fully the advantages of this new system of centralized low-voltage control. ' The General Electric Company will gladly assist in the solution of any electrical problem related to heating and ventilation. Trade-mark reg. U. S-- Pat. Off. 1077 1 . ! ; 11 . - ;i ' \ ' Air System Equipment Motors Westinghouse Electric Corporation Plants in 25 Cities--Offices Everywhere MOTORS FOR HEATING, VENTILATING AND AIR CONDITIONING APPLICATIONS Westinghouse manufactures a complete line of motors for all types of compressors, fans and pumps. For full details contact your nearest Westinghouse office or write for Catalog 2000 (Motors) and 7000 (Control). Open, DripProof SquirrelCage Induction Type CSP FRACTIONAL HP MOTORS For direct-connected fans on unit heaters and ventilators; propeller fans for roof ventilation; and furnace and centrifugal blowers, etc. Vertical types are recom mended for "Down Blast" heaters and vertical coolers. SINGLE PHASE A-C--Type .FH-- Split phase. Ko to hp, 115, 230 volts. Type FL--Permanently split capacitor design. to % hp, 115, 230 volts. Type FJ -- Capacitor-start induction run. to hp, 115, 230 volts. . POLYPHASE A-C--Type FS--Induc tion squirrel cage design for 2 and 3 phase circuits. M to ^ hp, 220, 440 and 550 volts. * DIRECT CURRENT --r Type FK-- Single speed and multi-speed motors, to 1 hp, 32, 115 and 230 volts. INTEGRAL HP MOTORS SINGLE PHASE--For fans and cen trifugal pumps requiring constant speed operation. Available in standard voltages and frequencies. Type CRP--Repulsion-start induction- Run--z/i to 5 hp. Type CU--Repulsion-induction--2 to 7V2 hp. Type CJP--Capacitor, % to 10 hp. POLYPHASE A-C--Type CS and CSP--Squirrel cage, constant speed, in duction motors. Available in three torque classes for all standard voltages and fre quencies H to 200 hp. Standard enclosures include: Open, tot ally enclosed (fan cooled or non-ventilated) and splash-proof. Types can be supplied with Underwriters' label for Class I, Group D, and Class II, Groups E, F and G Haz ardous Locations. Motors with special mounting or modifications can also be supplied. AXIAL FAN MOTORS Type CS--A modified design of a-c fan- cooled motor is used for axial flow fans in ventilation installations. The drawing at the left shows a typical unit, integral with the duct work. Motors from 1 to 25 hp in a variety of speeds can be supplied. 1078 Westinghouse Electric Corporation Air System Equipment controls HERMETIC COMPRESSOR MOTORS Types CS and CT feature a wound stator with machined steel shell of oil-tight construction, wrap ped around the stator punchings. Insulation is suitable for operation in freon and similar refrigerbore. Rated 1 to 3 hp (single phase), 115 and 230 volts, 1 hp and larger (polyphase), 60, 50, 25 cycles, 208, 220, 440 and 550 volts. MOTOR CONTROL The Westinghouse line of control includes manual or magnetic, reversing or non-reversing, across-the- line and reduced voltage starters for single or multi speed a-c and d-c motors. Magnetic types are furnished with built-in or separate pilot devices for local or remote control. All standard NEMA en closures are available. Representative types are described and shown below. . MANUAL CONTROL Motor Snap Switch--(Class 10-015) for starting and stopping small a-c and d-c motors where over-" load protection is not required. Rated up to 2 hp, 110 to 600 volts. Sentinel Breakers--Type H--^(Class 10-023) provide control and burnout protection for fractional hp motors--up to 1 hp, 110 to 220 volts. Protects motors against locked rotor or overload conditions. "De-ion" Motor Watchman--Type DnW-- (Class 10-100) designed for starting, stopping and protecting small single phase and polyphase a-c motors, from ^ to 7j^ hp, 110 to 600 volts. ' IB w Motor MANUAL MULTI-SPEED CONTROLS Controllers for Type FL Motors--2 speed, double throw, double pole toggle action switch for operation on 115 or 230 volts. Controllers for Type FK Motors--A variable resistor connected in armature circuit. Selector switch has six speed operations. "De-ion" Motor Watchman--Type DnW-- (Class 10-130) Starter suited to industrial fans--: for use with 2 speed, 2 winding motors. ^ to 7H hp, 160 to 600 volts. . Watchman Type DnW Class 10-100 "De-ion" Linestarler Class 11-200 "De-ion" Motor Watchman Type DnW Class 10-130 MAGNETIC CONTROL For starting squirrel-cage induction motors direct ly across the line. . Provides remote control and complete protection when used with pushbuttons, selector switches, etc. "De-ion" Linestarters--(Class 11-200)--Rated 1 to 25 hp, single phase, H to 750 hp polyphase, 110 to 600 volts. "De-ion" Combination Linestarters--(Classes 11-203--fusible, 11-204--non-fusible; and 11-206-- with AB nofuze circuit' breaker) 1 to 200 hp,T10 to 600 volts. Multi-Speed Controller for Type FL Motor PILOT CONTROL Standard Duty Pushbuttons--Type SD-2 (Class 15-010) and Heavy Duty Pushbuttons-- Type HD (Class 15-020)--For use with magnetic starters. Units"and stations are designed for pilot control circuits 110-600 volts a-c and 115-600 volts d-c in sheet steel, water and `dust-tight or oil im mersed enclosures. Dusl and Water-Tight Standard Duty Statiun _ Type SD-t Class 1S-OS0 "De-ion" Combination Linestarter Class 11-204 1079 Air System Equipment Air Devices, Inc. Air Diffusers Exhausters Air Filters Filter Holding Frames Hot Water Generators 17 East 42nd St. New York 17, N. Y. ghriLJ Agents in All Principal Cities AGITAIR DIFFUSERS Type R AGITAIR is the only diffuser that offers the higher efficiency of the square or rectangular shape in diffusing air quietly, draftlessly and with rapid temperature equalization throughout the average square or rectangular room. Its patented construction can be assembled into patterns which discharge the re quired amount of air in one to four directions. . Each side delivers a quantity of air proportional to the areas served. Thus the engineer or architect can select an attractive diffuser ^that fits his design-- rather than make his design fit the diffuser. Circular AGITAIRS combine beautiful design with finest operating features.to give rapid temperature equalization and draftless diffusion of air. Model CSF is quiet, easy to install. Pressure losses at minimum. Type A diffusers are smaller, weigh less, are easy to install. Type CM is for marine use. In all sizes for all types of mounting and with lighting combinations. ^ Dampers are provided where needed. The AGITAIR Diffuser Data Book, available to architects and engineers, will help you design and install air distribution systems. Consult our engineers. OIL BURNING HOT WATER GENERATQRS Ideal for hot water or heating service in domestic, apartment house, industrial and marine applications because they are light in weight and can be installed without special foundations or floor coverings. The AGIT AIR is down-fired to conserve floor space and facilitate servicing of the burner. Burner is fully automatic, with simplified design to reduce weight, cost of installation and possi bility of .failure. Special stacks are not necessary. Type A, weight 300 lb, 400 to- 1000 sq ft radiation. Type B in larger capacities from 1000 to 4500 EDR. Ask for bulletin. 1080 Air Devices, Inc. Air System Equipment and'cYiL, AGITAIR AIR FILTERS Permanent, cleanable AGITAIR Air Filters give more effective filtering with greater dust holding capacity and excep tionally low resistance. The new, improved filter medium di vides theair stream into myriadsof streams which impinge upon and deposit dirt and dust on the viscous coated surfaces. Large interstices provide exceptional dust-hold ing capacity--AGITAIR serves longer without cleaning. Ideal for applications where filters are in service for many hours without a "rest" period, because AGITAIR'S viscous coat ing has a vigorous "wick action" that keeps the surface of the dust deposit always wet, no matter how fast the dust cake builds up. Construction is sturdy arc-welded steel, with protected faces to withstand severe cleaning abuse. They are easier to clean, and can be returned to top efficiency with little trouble. Heating, ventilating, and air con ditioning: AGITAIR Air Filters in thicknesses of 1 in. and 2 in. Sizes up to 1200 sq in. . Industrial: Heavy-duty AGITAIR filters 2 in. and 4 in. thick. Sizes up to 2400 sq in. AGITAIR engineers have solved many industrial air filtering prob lems, such as protection for heavy blowers and.other equipment. Call on our ex perience. Grease Filters: For kitchens, etc. Capacity 1cfm. .pier sq in. with fan system; 1 cfm. per sq in. on gravity exhaust. Standard sizes up to 25 x 30 in.; others to 2400 sq in. Complete assemblies available. FILTER HOLDING FRAMES Adaptable to .all types of installations. Saves time and labor, eliminates bolts and rivets in frame,.and minimizes air leakage. Typical Filter Holding Frame Made of heavy steel, assembly is sturdy, neat. Available for all standard and special sizes of AGITAIR filters. V-Type assemblies of AGITAIR filter holding frames are available to increase filter area where space is limited. AGITAIR WIND-ACTUATED EXHAUSTERS Provide proper ventilation regardless of wind direction, and with positive elimination of down-draft. Functions at peak efficiency at average low wind velocities. Will not re strict the flow of air or gases when there is no movement of outdoor air across the head. Available in sizes from 4 in. to 48 in. neck diameter, with capacities shown at right. For calculation of natural .ventilation requirements, and for proper design principles, refer to Chapter 9 of this Guide. Fan-equipped units also for higher ratings. Bul letin EX-101. Capacity-- Wind-Actuated Size of Vent O. D. Neck Neck Nomirai Area Capacity Sq Ft cfm' S 4"' S6 S8 S 10 S 12 S 14 S 16 S 18 S 20 S 22 S 24 S 28 S 32 S 36 40 44 48 0.0873 0.1964 0.3491 0.5454 0,7854 1.069 1.396 1.767 2,162 2.640 3.142 4,276 5.585 7.069 8.727 10.56 ' 12.51 38 86 154 240 346 470 614 777 960 1162 1382 1881 2457 3110 3840 4626 3500 1081 Air System Equipment Registers Grilles Anemostat Corporation of America 10 East 39th Street, New York City 17, N. Y. The Anemostat High Velocity Air Diffuser THE ANEMOSTAT PRINCIPLE ANEMOSTATS produce unparalleled results be cause of their unique design which operate on the following interdependent principles: 1. Air expansion within the device, which reduces velocity instantiy. 2. True Aspiration, which causes room air equal to 30 to 35 per cent of the supply air to be drawn into the device where it is mixed with the supply air. The percentage of aspira tion depends on the type of Anemostat used. 3. Creation of a'multiplicity of air currents and countercurrents.at low velocities, which causes slow but adequate secondary air motion. Anemostat Type "AC" For supplying, extracting or returning air. Anemostat Type "C" For diffusion of supply air only. Type "AC" Anemostat is a combination device for supplying air and either extracting it or returning it to the conditioner. Designed to extract or return 75 cfm ' of room air for every 100 cfm of supply air. This percentage of extract or return may be increased or decreased by varying the extract velocities. It furthermore has an aspiration effect of 30 per cent. May be used with velocities up to 2500 fpm, and wherever both supply and return, or extract are required through the same unit. Should not be used with ceiling heights exceeding 14 ft. - Type "AR" Anemostat is a diffusion device for supply air only, for use in applications where a relatively high rate of air change (more than 12 per hour) must be maintained. It has 35 'per cent aspiration. It is particularly suitable where obstructions such as beams or columns are close to the diffusion unit and restrict the normal radius of diffusion. Type "B" Anemostat is a diffusion device for supply air only. It has 35 per cent aspiration. May be used with velocities up to 4000 fpm and is suitable for industrial and commercial installations. Can be used on either exposed or concealed duct work. . Type "C" Anemostat is a diffusion device for supply air only. NIt has 35 per cent aspiration.. May be used with velocities up to 2500 fpm. Must , be installed flush with ceiling and cannot be used on exposed duct work. Type "HU-3" and "HU-4" Anemostats have been developed to obtain draftless, economical heat distribution from vertical discharge unit heaters, and uniform heat coverage of floor areas. Type "HU-3" and "HU-4" Anemostats may be combined with practically all sizes and types of Vertical Discharge Heaters on the market. A number of unit heater manufacturers now supply "HU" Anemostats as a part of their equipment. "HU" Anemostats may be used on duct work for general heating installations. ' "No Air Conditioning System is better than its Air Distribution" 1082 Air System Equipment Air Vents G. G. Breidert Co. 634 South Spring St., Los Angeles 14, Calif. Representatives Located in Principal Cities of the U. S. BREIDERT AIR-X-HAUSTERS . FOR ROOF VENTILATING, VENT FLUES & CHIMNEY TOPS The Breidert Air-X-Hauster intro duces a new principle in ventilator design. Because of the revolutionary, aerodynamically-correct design of the Breidert Air-XHauster, wind currents striking it from any angle are converted into a powerful suction force that rapidly exhausts stale air from the interior of the house, kitchen or build ing. The Breidert remains stationary, has no moving parts. Back-drafts are elimi nated where there is no interior negative pressure! Type B The Breidert ^ ventilator offers certified capacity ratings based on tests made with Old windblowingataff Method Breidert Method' angles (as shown). These high capacities were proved and certified by Smith, Emery Co., Pacific Coast branch of Pittsburgh Testing Lab oratories. Insist on certified ratings based on directional wind tests at various vertical angles as shown in considering any venti lator. Breidert Air-X-Hausters were used extensively during the war on many types of combat and cargo ships, war housing, military barracks, and other government buildings. They also are widely used on all types of factories, commercial buildings, and residences. - For Kitchen Ventilation . . . The Breidert system provides a continuous, silent, effective circulation of air that exhausts heat and odor&al their source, with no operating or maintenance expense. There are no "hang-over" cooking odors because the exhaust action of the Breidert is continuous. The neat, compact appearance of the "Type A" Breidert especially recommends it for residences. . For Vent Flue Gaps ... The Breidert does not have the defects of conventional types of caps and accessories. It eliminates the necessity for down-draft diverters, with accompanying dangers of explosion in case unburned gas accumulates or is blown into the room. - For Chimney' Tops . . . By stopping all down-drafts (interior negative pressure excepted), a Breidert Air-X-Hauster on the chimney absolutely prevents the fireplace from smoking and damaging furnishings. It provides positive "draw" regardless of 'wind direction! . Write for Free Engineering Data Book . . . contains specifications and installation data, certified capacity ratings, etc. Address Dept. HV. 1083 . Air System Equipment Registers Grilles Barber-Colman Company Rockford, Illinois ENGINEERED AIR DISTRIBUTION OUTLETS VENTURI-FLO Overhead Air Diffusers Venturi-Flo overhead air diffusers have flow charac teristics similar to those of the well known fluid-flow measuring device--the Venturi Meter. The relation ship between the neck area of the unit proper and the Venturi-Flo throat area is so proportioned as to create a slight back pressure in the neck at all times, thereby automatically insuring uniform distribution around the entire periphery of the unit. Three types of overhead diffusers are available, the recessed, the surface, and the thermostatically con trolled types. A wide range of sizes permits handling air volumes up to 15,000 cfm per unit. Fittings for attaching any standard light fixtures to the outlets may be obtained for all designs. The surface and recessed types can also be furnished as combination supply and exhaust units and with adjustable dampers. Uni-Flo Grilles and Registers are especially designed for air conditioning applications. They are engineered and prefabricated with directional flow fins for each individual application. Proper air distribution is assured and the necessity for adjustment after instal lation obviated. Uni-Flo Grilles and Registers can be furnished in a variety of shapes and sizes for plain and curved surfaces. Registers are similar in construction to grilles but with the addition of spring loaded positive closing fan or key-operated dampers. Electroplated Finishes: Gunmetal, brushed bronze, plain zinc, and satin copper; also available in gray prime coat and satin aluminum. Uni-Flo Air Distribution Accessories: Include the Volocitrol and the Airturn. The Airturn is a scienti fically designed and highly efficient air turning member. The aero-dynamically correct vanes reduce losses caused by eddies, reverse air flow and low pressure areas at the turn to a minimum. Airturns are prefabricated and are available in units of one piece construction in sizes up to and including 48 in. x 48 in. The Volocitrol has been designed to noiselessly pro vide positive and adjustable control of air volume, N pressure and distribution across a supply outlet. They are available in two models, one for use with side wall and the other for overhead systems of air distribution. Veniuri-Plo-Tkermostatically Controlled Type Airturn '" Volocitrol Circular Volocitrol SEE OUR COMPLETE CATALOG IN SWEETS 1084 Air System Equipment Registers arid Grilles Air Diffusers W. B. CONNOR ENGINEERING CORP. Offices in All Principal Cities Canadian Representative: D & D Air Conditioning Co., Montreal, Canada Manufacturers of KNO-DRAFT Adjustable Ceiling Air Diffusers KNO-DRAFT Adjustable Air Diffusers insure efficient air distribution, maximum secondary air induction, noiseless and draftless diffusion, and uniform temperature throughout the occupied zone, regardless of season or ventilation requirements. Every KNO-DRAFT unit is easily and quickly adjustable for individual or seasonal require ments. The same KNO-DRAFT Diffuser is equally effective to expel chilled air parallel to the ceiling or eject heated air downward to prevent stratification. * (,Patents Pending) (Patents Pending) MODEL K KNO-DRAFT Diffuser--For Supply Air--attractive--light, yet sturdy--for high or low ceilings or attachment to exposed duct work. Anti-smudge rim prevents streaked ceilings. Sizes 4 in. to 40 in. neck diameter for capacities from 50 cfm to 20.000 cfm per unit. MODEL SR KNO-DRAFT Diffuser-For Combination Supply and Return air to simplify duct work. Sizes 6 in. to 24 in. supply-air neck diameter for supply capacities from 50 cfm to 9.000 cfm per unit, with central, return neck area 75 per cent of supply neck area. The KNO-DRAFT Diffuser will effectively distribute large volumes of air--pre mixing room and supply air. It permits the use of higher duct velocities--resulting in smaller ducts and lower costs. Duct designs are simplified and fewer outlets are required. KNO-DRAFT Diffusers blend well with any architectural treatment. They are simple in construction, light in weight, and easily installed. KNO-DRAFT Diffusers are geometrically proportional, size for size, insuring like resistance at like neck velocity for any size--and balanced static pressure throughout the system. . .. . THE TYPE D AIR VOLUME CONTROL is designed for application exclusively to KNO-DRAFT ADJUSTABLE CEILING AIR DIFFUSERS. It is furnished already assembled within the diffuser and requires neither field assembly nor attachment to ducts, angle rings or other external appurtenances. Type D Air Volume Con trol is adjusted and tested before shipment and ready to function when the diffuser is installed. I ts operation is en tirely independent of the air direction adjustment which is part of all standard KNO-DRAFT Air Diffusers. Type D Air Volume Con trol complements the function of the air diffuser. It varies only the quantity, not the characteristic of the air distribution. With it, a series of diffusers may be balanced without affecting the air dif fusion efficiency. With KNO-DRAFT ADJUSTABLE CEILING AIR DIFFUSERS equipped with TYPE D AIR VOLUME CONTROL, the desired air pattern for any room or zone is AT YOUR FINGER TIP. 1085 Air System Equipment Registers Grilles Charles Demuth & Sons Mineola, N. Y. Air Distributors--Oil-Fuelled Conditioners THE Demuth air distributor is known prevent drafts yet aids in corner-wiping and unusually thorough mixture of fresh in the air conditioning industry as the air supply. There is also created a central distributor with the curved, vertical vanes. vortex in the unit that recirculates a sub This special design feature gives the air ' stantial volume of room-air. Results are supply a slightly rotative motion while uniform temperature in areas treated, being released over a 360-deg rim throw. ' absence of decoration smudge and no draft This provides air-release turbulence to complaints. . Many Finishes TO make the Demuth a handsome fixture as well as a practical piece of ap paratus we offer a wide variety of finishes. There are: aluminum and stainless steel, polished and satin (machine produced;) ordinary steel in colored enamel finish; also galvanized steel, unpainted or enamelled, for marine and industrial applications. All pieces spun in manufacturer's own shop. Sizes from 4-in. to 42-in. duct diameters. The Demuth is also available in com bined lighting styles. Type S-2-L our semi-recessed model with standard globe. Type S-2 (above) our current popular semi-recessed design and Type S-L, also seen, shows how practically any design of lighting fixture can be combined with our distributors for special purchaser pref erences. \ Heats, humidifies, filters and circulates the ir. Five models rated from 80,000 Btu to 300,000 Btu. Insulated casing, combustion chamber refractory lined. All-steel, all-welded construction of Demuth design. Oil burner (gun type). Heat interchanger provides long gas travel before release. Fuel economy a special point, together with quick heating and troublefree performance. Enamelled finish, with polished aluminum trim. Unusually compact casing for heating capacity offered per unit. 1086 Air System Equipment Registers Grilles Hendrick Manufacturing Company Hendrick Perforated Metal Grilles 48 Dundaff Street, Carbondale, Pa. Sales Offices in Principal Cities--Consult Telephone Directory PRODUCTS--Hendrick Perforated Metal Grilles; Mitco Open Steel Flooring; Mitco Armorgrids; Mitco Shur-Site Treads. ' HENDRICK PERFORATED METAL GRILLES To architects, engineers, contractors and others who buy or specify grilles, . Hendrick offers literally hundreds of de signs from which to select the pattern or patterns best suited to the specific appli cation. Among their many decorative appli cations, Hendrick Perforated Metal Grilles are used in front of multiple louvre control for air direction. The wide range of patterns permits perfect harmony with every style of architectural design or period construction. liililiiiiliililiililiililiililii liliililiililiililiililiililiili nrn nrrM Musak Originally designed to meet specific ' requirements, these Hendrick designs are available, without premium, to those who seek something that is distinctive as well . as different. All Hendrick Grilles are characterized by clean-cut perforations and fine finish. In addition, Hendrick Grilles are put through a special flattening operation which insures easy installation. . HENDRICK FIXED LOUVRE GRILLE One of the most popular grilles in the Hendrick line is a door grille, developed originally for hotels and hospftals but equally ideal for bathroom doors in resi dences. Hendrick Fixed Louvre Grille is built up of a series of strips bent to a fixed angle and rigidly fastened into a band frame, a construction permitting free circulation of air--but preventing vision through the grille from any angle. Easily installed in any door. M No. 9 imi I'felil Y'm imi lfe'1 Ifej IM! Ifeffl ifelil life'll life'll lifeiii life.il lifeiil ife.il lfe.il La Crosse In addition to those popular designs which have been specified so consistently that they are today regarded as standard patterns, Hendrick offers a number of exclusive designs, many of them covered by design patents. . Fixed Louvre Grille ' Regularly furnished in No. 18. U. S. Gauge Steel; also obtainable in other desired commercially rolled metals; thick ness l1^ in. to fit standard door require ments. . Write on your letterhead for a copy of 194-page handbook, "Hendrick Grilles." 1087 1 Air System Equipment cf!ij`r` Hart & Cooley Manufacturing Co. Established 1901 Air Conditioning Registers and Grilles - Warm Air Registers Damper Regulators - Furnace Regulators - Pulleys - Chain Holland, Mich. NO. 75 DESIGN--FLEXIBLE FIN TYPE with TURNING BLADE VALVE to provide DOUBLE DEFLECTION. Also without Valve as Grille or Intake CONTROL OF AIR FLOW IN TWO PLANES Instant Adjustment of Air Flow (Up, Straight or Down) Is obtained by turning the regulator on the register face., to the proper setting with a key furnished with each register. When the valve is opened, as shown at the left, the individual valve louvres automatically stop in position to provide the proper air flow--Up (Fig. 1) for cooling systems to avoid drafts; Straight (Fig. 2) for ventilating systems; Down (Fig. 3) for heating systems to prevent stratification. When the valve is closed, as shown at the left below, it completely stops the flow of air. Air Flow Can be Quickly Adjusted Sideways No. 75 Design has a flexible fin-type face. Each fin' may be twisted individually with a wrench furnished with each register or grille to provide any desired sideway deflection of the air flow. . ' Greatly Reduced Turbulence and Resistance Figs. 1, 2, and 3 show the air flow with No. 75 Design; Fig. 4, with the conventional register. Compare the turbu lence in the stackhead of the latter with the smooth flow obtained with No. 75 Design. So efficient is No. 75 Design that there is actually less resistance with this register, using a standard stackhead, than if no register at all were used. Fig. 1 Fig. i Fig. 3 Fig. 4 1088 Hart & Cooley Manufacturing Co. Air System Equipment Registers Grilles Velocities with No. 76 Design Velocities with Conventional Register EVEN DISTRIBUTION OF AIR OVER ENTIRE FACE The turning blade valve distributes the air evenly with a uniform velocity over the entire face, as shown in Figs. 1, 2, and 3 on the preceding page. Note how the air rushes through the upper part of the face with a conventional register, as shown in Fig. 4. Since the entire face of No. 75 Design register is utilized for discharge of air, smaller and in some cases fewer registers can be used without causing excessive velocities. Prevention oi Streaked Ceilings--With either UP, STRAIGHT, OR DOWN deflections the air does not strike the ceiling immediately in front of the register; streaked ceilings are thus avoided. Excellent Concealment of Duct--The depth and close spacing of the vertical bars, combined with the valve, provide almost complete concealment of the duct, adding considerably to the pleasing appearance of the register face. ' Special Settings--No. 75 Design functions equally well when located at the end of a horizontal duct or. by installing it upside down, when the air is delivered to it from above. AVAILABLE IN FOUR TYPES Without Valve--No. 750 Grille (Left) has % in. turndown. No. 757 Intake (Right) has % in. projection. FOUR TYPES OF INSTALLATION FRAMES AVAILABLE No. 75 Design items can be used with or without installation frames. No. 3 Sidewall Stud Frame (illus trated), fastens directly to stud, forming a solid, streak-proof foundation for register. No. 8 Frame is similar for baseboard use. No. 5 Baseboard Stack Frame provides inexpensive, streak-proof installation. No. 2 Band iron Frame provides for connecting register to stackhead. CATALOG 46 showing the complete H & C line, available upon request. 1089 Air System Equipment Registers Grilles The Independent Register Co. Established 1898 3747 East 93rd Street, Cleveland, Ohio AIR CONDITIONING REGISTERS AND GRILLES Rear View Showing Adjustable Deflecting Vanes No. 321A Grille with Deflecting Vanes^With vertical grille bars and horizontal de flecting vanes. The grille bars may be individually adjusted to direct air flows to right or left; and the vanes are made individually adjustable to deflect air flows up or down. Air System Equipment Outlets and Grilles The Pyle-National Company 1334-58 North Kostner Avenue, Chicago 51, Illinois Representatives in Principal Cities Manufacturers of MULTI -VENT Panels for Heating Ventilating Air Conditioning No. 238 Wrought Steel--4-way adjust- No. 139 Wrought Steel--Flexible hori- able direction of air flow. Flexible vertical zontal grille bars, bendable for up, down grille bars, multiple valves. or straight air flow. Single valves. Independent No-Vision Grilles--No. 1312 for Doors, Walls and Partitions The grille bars are "V" shaped; it is impossible to see through the grille from any viewpoint. No. 1312F-- One outer frame edge turned in ward. See "F". No. 1312R-- ^ * With overlapping rim % in. wide,' on all four sides. No. 1312C-- With grille core only, installed with moulding. Control Plate " Valve Distribution Plate 1VAULTI-VENT Panels are used for the even distribution of warm, cool or fresh air within room spaces. The control plate frame is inserted in the overhead duct at the ceiling. The orificed adjustable air valve provides absolute displacement of static head, and may be set for varying quantities of air to enter the conditioned space, and at varying velocities or speed of entry, producing the comfort zone rate of air motion and degree of temperature desired by the occupant (provided the system includes the required auxiliaries). The perforated distribution plate, of large area, located in the ceiling, accomplishes a wide, gentle, uniform spread and dilution of the conditioned air and simultaneously provides panel heating or cooling. When used with the other correct auxiliaries Multi-Vent results in uniform temperatures and comfort. Application data will be furnished oh request 1091 Air System Equipment Registers Grilles Tuttle & Bailey, Inc. New Britain, Connecticut PRODUCTS: Ceiling Diffusers--Grilles--Registers-- Intakes--Air Control Devices--Ornamental Grilles, Cast or Wrought Metals--Copper Convector Heaters Type Rl AIRoms*0ounEj FOR HEATING VENTILATING AND AIR CONDITIONING TYPE S Flush-type diffuser for installation on ceiling. Ideal combination of real beauty and functional superiority. Provides (1) Complete Air Mixture (2) Rapid Temperature Equalization (3) Uniform Air Distribution (4) Total Elimination of Drafts. TYPE E Type E Outlets are designed for instal lation on exposed ductwork and pro vide the same efficient performance as the S Type. The rings of Types E2 and E3 are stepped down, which greatly increases the capacity of a given size of outlet, resulting in an appreciable saving in^the cost of the outlet and the ductwork. TYPE R Combination supply and return (or exhaust) unit. Designed particularly for use on installations where simplifica tion of the duct layout is of primary importance since the return (exhaust) duct can be run to the same location as the supply duct. Send for complete engineering data and descriptive catalog. 1092 Air System Equipment * ' Tuttle & Bailey, Inc. New Britain, Connecticut PLIAVANE ADJUSTIBLADE REGISTER An inexpensive register suitable for low cost housing installations. The air flow may be directed sideways by the in dividually adjustable face vanes and up or down by the back blades which can be "ad justed" from the face of the register itself. AIR CONDITIONING GRILLES Furnished in both the fixed deflection (Air line Design) and the sectionally adjustable deflection (Flexair Design) types with bars running either horizontally or vertically. The Tuttle & Bailey Air Conditioning Grille is scientifically and sturdily con structed to perform efficiently under all operating conditions. ~ DOUBLE DEFLECTION GRILLES Furnished with face bars of fixed (Airline) or adjustable (Flexair) deflection types and equipped with individually adjustable back blades. Also available with hori zontal face bars and vertical back blades. SANTROLS An individually adjustable series of deflecting blades for positive control of. air volume and to insure uniform distribution over the entire supply outlet. DUCTURNS Scientifically designed turning blades- which eliminate the necessity of long radius turns and allow the use of right angle elbows in a duct system. . ' . 1093 Air System Equipment Registers Grilles REGISTER & GRILLE MFG. CO. Incorporated 70 Berry Street, Brooklyn 11, N. Y. Headquarters for all types of Registers and Grilles RESIDENTIAL AND COMMERCIAL Register shutters of different types can be furnished with all types of Register Faces or Grilles. All Register Shutters have our exclusive feature of brass collars inserted in the ends of the shutter to minimize rusting. REGISTERS FOR VENTILATION ARROWTROL SHUTTER Style 1-A.C. lock type Register allows direc tional flow of 185 deg either right and left or up and down. Will open 45 deg beyond 90 deg The Arrowtrol, line cut shown above, gives straight throw in connection with volume control FOUR-WAY DEFLECTION TO AIR FLOWS R & G ADJUSTABLE DIRECTED AIR FLOW TWO-WAY DEFLECTION ,_! ////// // / / /// /1 \ s\\ \ \ ^vn v\\\ L Style 80 Grille and HMV deflecting vane Front bars vertically adjustable, rear vanes horizontally adjustable; or Front bars hori zontally adjustable, rear vanes vertically ad . justable. Use No. 20 Grille for adjustable right and left deflection. Style, 10 has horizontal adjustable bars for up and down deflection. THE "THIN MAN" REGISTER FOR RESIDENTIAL USE Style 8 T.M., shown, allows right and left deflection and up or down control at the back. Other designs of faces ' are available. Ask for our catalog which shows other types of air controls; also 81 different Stamped . Metal designs and over 100 designs In Cast Metals--Iron. Brass or Bronze. 1094 Air System Equipment Registers Grilles United States Register Company General Offices: Battle Creek, Mich., U.S.A. Branches: Minneapolis, Minn., Kansas City. Mo., Albany, N. Y.. New York. N. Y.. San Francisco. Calif. Air Conditioning Registers, Vents and Grilles Style 153LF--Louver-Type Air Conditioning Register-Bars in. deep--Spaced 4 openings to the inch affords Non-Vision. Can be supplied in Directional Flow in either Horizontal or Vertical Bar Styles. Can be furnished with all styles of Setting Frames. Style 249LF--Duo-Deflection Air Con ditioning Register. Gives complete Air Control. Vertical Front bars--Key-pin adjusted to provide 45 deg Right and Left or Two-way Side Flow. Lever operated Horizontal Back-valves give from Full Closed to any degree of Upflow and to 45 deg Down-flow. FULL FACE COVERAGE. Can be supplied with any style of Setting Frame. Fits , all Stack Heads of Standard Size Dimensions. Style 256LF--Flex-bar Air Condition ing Register. Vertical Front Bars set 22 deg Right and Left. Side Flow Deflection attained by setting of Grille , Bars with bending wrench to accom modate room condition. Back-valves give same Up and Down control of air flow as 249LF above. FULL FACE COVERAGE. Can be supplied with any style of Setting Frame. Fits all Stack Heads of Standard Size Dimen sions. All of above Styles can be supplied with either Lever or Individually ad justed Multiple Valves or Louvers. i.e. 153VVI--Vertical Valves Indi vidually adjusted. I45VVL--Lever operated Vertical Valves. . Grilles and Vents in Matching de signs are available. For Complete Information Write for Latest Catalogs with Engineering Data. Style 103LF--Horizontal Lattice Perforated Register for Forced Air Systems. Not direc tional flow. Complete Gravity and Air Conditioning Register, as well as Fitting Catalogs furnished on request. 1095 ~ ^ Air System Equipment Air Flow Regulators Young Regulator Company 5209 Euclid Avenue, Cleveland 3, Ohio DAMPER REGULATORS; REMOTE CONTROL REGULATORS; DAMPERS Manually and Automatically Controlled Sales Representatives in Principal Cities If No. 700A No. 401A Ten designs of Young Damper Regulators, which meet almost every condition where regulators are required for controlling air volume through ducts. They are positive in action, tamper-proof, withstand vibration and shock. Are operated and locked by key. Young Remote Control System . No. 700A and No. 805 Individually controls volume of air to each room. Operates dampers at a distance of 250 feet or more. Depth of box ^ in. Corner pulleys No. 704 with connections for tubing used at bends. Young Remote Control Regulator No. 703A Cutaway view with box 2 in. deep. Young Remote Control No. 702 Has reverse dial, used when cable leads off bottom of Control. Young Relief Damper No. 815 Automatically controlled, with modu lating low voltage motor and remote bulb thermostat. Young Fresh Air Damper No. 820 Is for outside air. Is similar to No. 815 except that it is a single instead of double damper. Young Surface Damper Regulator No. 1A--% In* Young Valcalox Damper Regulators No. 400A--in. and No. 401A--% in. Young Air-Split Damper Regulator No. 900A Young Air-Split Damper Regulator No. 905 Is similar to No. 900A except the rotating head is placed on inside of Grille. Young Convector Regulator No. 91.0 Young Volume Control Grille No. 915-L This assembly is for installation on the side of a duct having a series of outlets. Young Concealed Regulators No. 300A--% in. and No. 301A--V* in. No. S05 No. SI.5 No. 402A No. C55--% * No. 656--H * 1096 No. 602--% in. Air System Equipment Sheet MetaI and Tubular Products The American Rolling Mill Company Executive Offices,-Middletown, Ohio Atlanta 3. Georgia 1437 Citizens & Southern National Bank Bldg. Berkeley 2, California_____ Seventh and Parker Streets Boston 16, Massachusetts________ 439 Park Square Bldg. Buffalo 2, New York______ 501 Seventeen Court St. Bldg. Chattanooga 2, Tenn._____ 602 Chattanooga Bank Bldg. Chicago 4, Illinois310 S. Michigan Bldg. Cincinnati 8, Ohio....... .......... _24 Cooper Bldg., Hyde Pant Cleveland 15, Ohio... .....................1216 B. F. Keith Bldg. Columbus 15,'Ohio........................ -Room 431, Atlas Bldg. Dallas 1, Texas...................... ,2112 Tower,Petroleum Bldg. Dayton 2, Ohio-506 Mutual Home Bldg. Detroit 2, Michigan_______ __5-261 General Motors Bldg. Houston 2, Texas1640 Commerce Bldg. Indianapolis 4, Indiana1106 Fletcher Trust Bldg. Kansas Cnr 3, Missouri7100 Roberts St. Los Angeles 15, California...... ........ 329 Petroleum Bldg. Milwaukee 2, Wisconsin, . 627 First Wisconsin National Bank Bldg. Minneapolis 14. Minn171--27th Avenue, S.E. New York 5, New York,,120 Broadway Philadelphia 7. Pa.................-.1808 Lincoln-Liberty Bldg. Pittsburgh 22, Pa1627 Henry W. Oliver Bldg. Richmond 19, Va..... .. ..... 1308 State Planter's Baok Bldg. St: Louis 1, Missouri----------------- 1725 Ambassador Bldg. South Bend 24, Indiana, 503 City Natl. Bank & Trust Bldg. Choose the Correct Armco Grade There is a grade of Armco sheet metal particularly suited to every air conditioning application. For detailed information get in touch with the nearest district office or write direct to The American Rolling Mill Company, 2871 Curtis St., Middle town, Ohio. " Armco Ingot Iron ' (Galvanized) Ducts Washer Chambers Plenum Chambers Steam Line Casings Spray Towers Drip Pans Housings Machine Guards Unit Conditioners Roof Ventilators Eliminator Blades _ Armco PAINTGRIP (Galvanized) A special mill-Bonderized galvanized sheet that can be painted without pre treatment. Preserves life and beauty of paint and enamel. Armco Cold Rolled Paintgrip: A zinc- flashed sheet with a special mill-Bonderized surface that takes and holds paint. Hot Rolled (Sheets and Strip) Fan Blades * Blower Casings Fuel Oil Tanks Unit Conditioners Stoker Hoppers Armco ZINCGRIP A special zinc-coated sheet that can be severely formed without peeling or flaking of the tightly adherent zinc coating. Also available with a Paintgrip finish. Cold Rolled (Sheets and Strip) Furnace Casings Room Unit Casings Plates (ARMCO Ingot Iron) Smoke Stacks Coal Hoppers Breeching Unfired Pressure Vessels Low-fired Boilers Tanks High Strength Steels . _ Low alloy, high tensile steels possessing great strength. Used with proper design Armco 50Y and 55Y assure lighter frame work, lighter tanks and similar items. Under atmospheric service conditions it has cor ' rosion resistance superior to regular steel Stainless Steel (Sheets, Strip and Plate) Combustion Chambers Heat Flues and Tubes Humidifier Pans ' Pre-heaters . Furnace Parts and Supports Fan and Blower Blades . Special grades have excellent resistance to destructive heat-scaling up to 2000 F Armco ALUMINIZED Steel An aluminum-coated sheet steel with exceptional resistance to heat and corrosion. Resists heat discoloration up to approximately 900 F,, and will withstand oxidation at ^ven higher temperatures. Also offers exceptional heat reflectivity where this is desirable. 1097 Air System Equipment !Zbuu/rtlJSft* BETHLEHEM STEEL COMPANY GENERAL OFFICES: BETHLEHEM, PA. Akron Albany Atlanta Baltimore Boston Buffalo Chattanooga Chicago Cincinnati Cleveland Columbus Dallas Detroit Houston Indianapolis Johnstown. Pa. Kansas City. Mo. Milwaukee District Offices New Haven New Orleans New York Philadelphia Pittsburgh St. Louis St. Paul San Antonio Savannah Springfield. Ma ss. Syracuse Toledo Tulsa Washington Wilkes-Barre York BETHLEHEM PACIFIC COAST STEEL CORPORATION Seattle Portland General Offices: San Francisco Los Angeles Salt Lake City Honolulu Export Distributors BETHLEHEM STEEL EXPORT CORPORATION. NEW YORK Bethlehem Products for Heating^ Ventilating and Air Conditioning STEEL SHEETS Bethlehem manufactures a full line of sheet steel to handle all types of heating, ventilating and air-conditioning jobs. Sheets are produced in the general classi fications of galvanized, hot-rolled (black); and cold-rolled. Galvanized sheets are made in gages No. 8 to 31 inclusive in widths of 24,30,36,42 and 48 in. Hot-rolled sheets are made in thicknesses from No. 2 gage to No. 18 gage, in widths varying with the thicknesses. Cold-rolled sheets are made in gages No. 11 to 30 inclusive. Bethlehem also produces galvanized steel roofing, siding and accessories. The designs include 234 in. and in. cor rugated; 2-, 3- and 5-V crimp; Stormproof (non-siphoning drain-type); roll roofing and plain brick or rock-faced stone siding' . For extra rust-resistance , use Beth-Cu-Loy Sheets, available in black, galvanized and formed sheets. Containing 0.20 to 0.30 per cent copper, they have two to three times as much rust resistance as mild carbon sheets. STEEL PIPE Ammonoduct--This pipe is ideal for radiant heating or refrigeration uses, ft is made by Bethlehem, in sizes from 34 in. to 3 in., inclusive, and in uniform 21 ft lengths, plus or minus 1 in. Made by the continuous-weld process from a low-carbon open-hearth steel, Ammonoduct is well suited for radiant heating or refrigeration installations be cause of its bending qualities and ease of welding. It is so ductile that it can be cold-bent and cold-formed without frac ture of the metal wall. Annealing costs are eliminated. Beth-Co-Weld--A quality steel pipe manufactured by Bethlehem for use in general piping installations and- in con ventional heating systems. Like Ammo noduct, it is made by the continuousweld process,,and is furnished in sizes from 34 in. to 3 in., inclusive, and in uniform 21 ft lengths, plus or minus 1 in. Bethlehem also produces lap-weld pipe in sizes 2 in. to 16 in., inclusive. Air System Equipment Sheet Metal and Tubular Products Jones & Laughlin Steel Corporation Jones & Laughlin Building, Pittsburgh 30, Pa. WELDED and SEAMLESS STEEL TUBULAR PRODUCTS f HOT AND COLD ROLLED SHEETS J & L Welded Pipe Jones & Laughlin manufactures Standard Weight, Extra Strong, and Double Extra Strong Welded Pipe, Black and Galvanized, for steam, gas, air, water, refrigeration and sprinkler work. Sizes: Y% in. to 10 in. inclusive. Jones & Laughlin Steel Pipe is made of soft, weldable steel rolled from solid ingots made to a special analysis. The steel pipe produced is soft and ductile, free cutting, strong at the welds, and free from excess scale.' J & L Pipe is commercially straight and free from blisters, cracks or other injurious defects. - Careful attention is given the threading of the pipe with good clean-cut threads fitted with sound couplings correctly tap ped to give a tight joint. Soft, ductile steel of free cutting quality enables the con tractor to cut clean, sound threads on the job. The Jones & Laughlin process of gal vanizing assures a thorough coating and insures against pipe being clogged with spelter. The galvanized coating adheres strongly and does not tend to Bake off. J & L Seamless Pipe J & L Seamless Pipe is made in three weights; standard and extra strong in sizes -2$4 in. O. D. to 14 in. O. D. inclusive, and double extra strong in sizes 2 in. to 8 in. inclusive. . J,& L Seamless Steel Pipe is pierced from a solid billet--there are no welds. The result is dependable and uniform wall strength. The method of manufacture, and the use of only specially selected steel, assure exceptional ductility, a quality that is essential to successful coiling and bend ing, and flanging for Van Stone joints. J & L Seamless Pipe can be used with full satisfaction in either threaded joint or completely welded installations. < Ductility, strength and safety--make this product especially adaptable for air, steam, gas and gasoline lines, boilers, refineries, dry kilns, refriger ating systems and other exacting applications. J & L Electricweld Tubes Mechanical Tubes ^ in. O.D. to 4 in. O.D. inclusive. ' A product of superior quality resulting from a combination of the first grade steel strip, hot and cold rolled, together with skilled production crews and supervision by men of many years' experience in producing high grade electricweld tubes. Other J & L Tubular Products J & L also manufactures Reamed and Drifted Pipe in sizes X in. to 12 in. inclusive, Dry Kiln Pipe, Pipe for Refrigeration Service, Line Pipe and a complete line of Oil Country Tubular Products in welded and seamless. Hot Rolled Sheets J & L Hot Rolled Sheets are made in a full range of plain carbon steel grades to a maximum of about .25 per cent carbon and including copper-bearing steel. Fur nished in cut sheets in full lists of gages and widths or coils in 10 gage and lighter' in over 24 in. to 90 in. widths. Also available pickled and oiled, annealed, patent or stretcher-leveled and resquared on application. Cold Rolled Sheets . J & L. Bright Cold Rolled Sheets in a full range of plain carbon steel grades in cluding copper-bearing steel furnished in cut lengths or coils in the following gages and maximum widths--11 to 13 gage over 24 in. to 84 in.-width; 14 to 20 gage over 24 in. to 90 in. widths; 21 and 22 gage over 24 in. to 72 in. widths; 23 to 24 gage over 24 in. to 60 in. widths. 1099 Air System Equipment sheet Metals t United States Steel Corporation Subsidiaries Carnegie-Illinois Steel Corporation, Pittsburgh and Chicago Columbia Steel Company, San Francisco Tennessee Coal, Iron & Railroad Company, Birmingham United States Steel Export Company, New York District Offices in all Principal Cities USS COPPER STEEL For Superior Rust Resistance at Low Cost Corrosion resistance and cost are two determining factors of the type of metal to be used for various air conditioning jobs. Copper Steel has 2 to 3 times the atmos pheric corrosion resistance of plain steel or pure iron as shown in the results of un biased tests made at Pittsburgh, Ft. Sheridan and Annapolis by the American Society for Testing Materials. The cost of U*S'S Copper Steel is less than that of pure iron or copper-bearing pure iron and only slightly more than plain steel. Thus there often is a dividend of 200 per cent to 300 per cent longer life and a saving in the first cost as well. When galvanized, U`S*S Copper Steel produces a sheet that is rust'resistant all \ the way through--not just on the surface. It should be used for all ducts carrying humidified air or placed in damp locations such as basements, shower rooms, etc. U S S PAINTBOND U*S*S PaintBond should be used whenever galvanized steel is to be painted. This special Bonderized sheet can be painted immediately, offers a much better surface for painting, lessens danger of the paint flaking and retards corrosion. It is used for ductwork, furnace housings and outdoor metal work. Send for our PaintBond booklet. USS DUL-KOTE U S S Dul-Kote is a specially treated non-spangled galvanized sheet which also can be painted immediately without aging or otherwise preparing the surface. It is available in the South and in the West. Send for our Dul'Kole booklet. HERE'S THE PROOF! UNCOATED COPPER STEEL 91% SOUND AFTER 21 YRS. Corrosion test of A.S.T.M. on tt gage block sheets exposed at Annapolis, Md., October, 1916. The copper steel sheets outlasted all others in the test. OTHER U S S PRODUCTS INCLUDE: Black Sheets--All grades, hot rolled, cold rolled iii a number of different finishes. .' Stainless--Heat resisting steel for various uses where temperatures are high and corrosion severe. Cor-Ten--High strength steel--greater strength, greater atmospheric corrosion resistance for smokestacks, hoods, etc. For more information on U*S*S Galvanized, Copper, Black and Stain* less Sheets, send for our Guide for Sheet Metal Workers. 1100 Air Conditioning and Heating Piping Flexible Tubing Atlantic Metal Hose Co., Inc. 112 West 64th St. New York 23, N. Y. ATLANTIC SEAMLESS FLEXIBLE METAL HOSE ABSORBS VIBRATION on REFRIGERATING and AIR CONDITIONING EQUIPMENT For standard pres sures in a variety of metals Type A For high pressures and severe service For refrigeration and air condition ing Freon Lines Vibration Absorber Throughout-the Heating, Ventilating and Air Conditioning Industry--where the ability to control vibration and compensate for expansion must go hand in hand with the ability to take punishment and withstand pressure--Atlantic hose continues to break performance and economy records year after year. Durable--the specially selected alloy and method of construction assures long life even under severest service. ,. Simplifies Installations--Both slip-on as well as pipe thread fittings can be' provided in all commercial sizes for quick assembly. We also manufacture hose for the conveyance of dust, air, exhaust, steam and all liquids: - Engineering Service--Our engineering department will cooperate with prospective users in the selection of suitable standard flexible hose, or in the design of hose to meet special requirements. ' Advise us of the details of the service and we will be pleased to offer our recommendation. . 1101 Air Conditioning and Heating Piping Flexible Tubing Chicago Metal Hose Corporation Maywood, Illinois PLANTS MAYWOOD and ELGIN, ILLINOIS Distributors - Houston. Texas_____ ___________________ ____ ___________ ___ _______ ________________ _______ _______ Pedea Iron & Steel, Inc. Los Angeles. California............. -................................. _................... ...................... Los Angeles Rubber & Asbestos Works New Orleans, Louisiana-.................. ............................ .................... ..................... Standard Supply & Hardware Company Portland, Oregon--.________________ ___ _____________________________________ ________ ____________ Marshall-Wells Company San Francisco, California............................................................................................................. ..................................C. W. Marwedel Seattle, Washington...........;......... ......................... ................................................................................-..Strehlow Supply Company Rex Vibra-Sorbers Control Vibration and Noise Rex Vibra-Sorbers are used to control vibration and reduce noise in refrigeration and air conditioning machinery. They are also available with male pipe thread fittings for use in connecting lines of pumps, turbines, and allied equipment. ' Rex Vibra-Sorbers are pressure-tested to insure refrigerant-tightness, thus giving greater protection against leakage of valuable refrigerants. They are available in copper bearing alloy for Freon and Menthol, and steel for ammonia. Thus effective corrosion resistance is provided for all types of installations. C.M.H. engineers can help you solve your vibration problems. Write for information. Specifications and List Prices COFFER tube SIZE Actual O.D. Nominal ID. ** K' %' K' K* *' ** K' IK' *' IK' 2K' IK' 3K* 3K' 4K' K' K* K' K' Vi' H' K' K' I1 IK' IK' 7' 2K' 3' 3W' 4* ID. Rcxibl* Hose length Flexible Hole 5K' K' SK' ?<* 6K' K' 6K' K' 7' K' r K' 7%' K* 1- | ?*' *' IK' 9K' IK' 7' 13' 7Vi' 15*' y 3K' 17*' 2IK' 21K' Sq. in. 3.00043,000 + 3.000+ 2.500 + 2,500 + 2.500 + 2.000 + 2.000 + ,5o+ 1.500 + 1.500 + 1.000+ 1.000+ 1.000+ 1,000 + 1.000+ OVERAU LENGTHS Standard Units with Female Sweat Fittings . Standard Units with Male Sweat Fittings 7* 7K' 8*' 9' 9*' 10* IIK' UK' 13' 14*' ir 20* 24' 27* 31 K' 32* 7K' BU' 9' **'\ 10*' II' I2K' I2K' 14* . 15*' I7K' 20' 24' 2r 3IK' 32' stock NUMBERS With Sweat Couplings f-l F-3 F-S F-7 F.9 F-l 1 - f.|3 F> 1 5 F-17 F-l 9 F-21 F-23 F-25 F-27 F-29 F-31 . With Mole Sweat Couplings M-2 M-4 M-6 M-8 M-10 M.I2 M-14 M-16 M-IB M-20 M-27 M-24 M-26 M-28 M.30 . M-32 UNIT UST PRICES S 2.90 3.00 ' 3.30 3.60 4.10 4.10 5.60 5.60 7.00 10.00 13.00 ' 18.00 36.00 46.00 90.00 1 20.00 Note: Flexible hose lengths listed above are for straight line installations only. In formation on lengths for angle installations requiring bends and special units with elbows or threaded fittings is available on request. All information on Rex Vibra-Sorbers is based on actual measurements and tests. However, due to manufacturing limitations and structural changes, this data must be regarded only as a general guide. 1102 Air Conditioning and Heating Piping Flexible Tubing . Seamlex Company, Inc. Main Office and Factory _ 27-31 Jackson Ave., Long Island City 1, N. Y. Since 1928--Specialists in the Manufacture of Flexible SEAMLESS All-Metal Hose You are invited to submit your flexible tube problems to our engineers-- without obligation on your part. . You May Obtain Catalog No. 45 Free of Charge VIBRATION ELIMINATOR SEAMLEX Bronze--Single Braided STANDARD SIZES . Fig. 700 Seamlex with Sweat Fitting FOR DOMESTIC OIL BURNERS Fig. SS Seamlex with Type "M" Fitting FOR INDUSTRIAL OIL BURNERS Fig. 37 Seamlex with Type ``SBP" Fitting FOR UNIVERSAL APPLICATIONS Fig. 60 Seamlex with "DT" Fitting FOR DIESEL EXHAUST from 2 " I.D. to 24 " I.D. Fig. 90 Seamlex Welded Steel Hose ' I.D. . h*' or 'A* w w W >/.' r w w 2m w y y/i y Oh" y 6' O.D. Minimum Bending Radii for Flexing Bursting Pressure* Lbs./Sq. In.' /.' w >/.* y.' 96' . i>/j' iy.' 2%r 236' w y/i" oar w5'/,' 6' W 6' y 5' 6' 6' 6' 7' 6' 9* KT II* 12' 13' . 18' 18' 22' 24' 26' 28' 30* 10.000 ' 7.500 5.000 4.000 3300 3.000 2.500 2.000 1.750 1.500 U50 1.000 800 675 600 500 480 440 400 . SEAMLEX Products Quality Products 1103 Air Conditioning and Heating Piping Copper and Brass The American Brass Company General Offices: Waterbury 88, Conn. Offices and Agencies In Principal Cities IN CANADA: Anaconda American Brass Limited. New Toronto. Ontario PRODUCTS--Anaconda Deoxidized Copper Tubes and Fittings; Anaconda "85" Red-Brass Pipe; Everdur Metal for storage heaters, storage tanJks, ducts and air conditioning equipment ' anaconda copper tubes and FITTINGS For Heating, Plumbing and Air Conditioning Anaconda Deoxidized Copper Water Tubes assembled with Anaconda Fittings oiler an unusual combination of advan tages in hot water heating systems at a cost only slightly higher than black iron and approximately the same as wrought iron pipe. These advantages may briefly be summarized as follows-*. Low Friction Loss--Because the inside surfaces of copper tubes are inherently smoother than those of pipe and tubes made of ferrous materials and also because they do not become roughened by the formation of rust, these tubes oner a lower resistance to flow. In addition, the long radius turns of Anaconda Elbows and the smooth inside surface of Anaconda Wrought Copper Fittings further reduce friction losses. . These factors naturally increase the efficiency of the system, particularly when it includes a forced pressure circulator. Ease of Installation--In many places the flexibility of copper tubes simplifies connections that ordinarily would be awk ward and expensive to make with rigid pipe and threaded fittings. Anaconda Solder Fittings are compact. They can be installed in restricted space where the use of a wrench would be impossible. Architects and builders naturally object to large holes and. notches cut in the framing members of a building for -the passage of piping.. Anaconda Copper Tubes can be installed with a minimum of cutting in the structure--although holes should be large enough to permit move ment of tubes due to expansion and contraction. ; Appearance--Anaconda Deoxidized Copper Water Tubes assembled with Anaconda Solder Fittings present an at tractive appearance. It is a frequent practice to clean the tubes after they are installed and apply a coat of clear lacquer or similar substance. This keeps the tubes bright and makes an installation of which both plumber and owner can be proud. Temper and Thicknesses--Anaconda Copper Tubes are made in both hard and soft temper and in standard wall thick nesses. They meet the requirements for these types of 'tubes in Federal Specification WW-T-799a and A.S.T.M. Specification B88. Type K, the heaviest, is recom mended for heating lines and general piping. ' Accuracy of Dimensions--Anaconda Deoxidized Copper Water Tubes are all finished to the close size tolerances required by the A.S.T.M. and Federal Specifica tions, which have been found essential for efficient assembly with solder fittings. Permanent Identification--For per manent identification, the name "Ana conda" and the tetter designating the type of tube is stamped in the metal at intervals of approximately 18 in., throughout every coil or straight length of tube. 1104 Air Conditioning and Healing Piping Copper and Brass The American Brass Company Anaconda Copper Tubes, in all standard sizes, up to and including 1^4 in. are furnished soft in 30, 45 and 60-ft coils; also hard and soft in 20-ft straight lengths. Sizes over in. are furnished, hard or soft, in straight lengths only. ANACONDA "85" RED BRASS PIPE Anaconda "85" Red Brass Pipe, in standard pipe sizes, is considered the highest quality corrosion-resistant pipe commercially obtainable at a moderate price and is recommended for steam return lines. Anaconda "85" Red Brass Pipe contains 85 per cent copper arid conforms to Govern ment specifications for Grade "A" water pipe. The mark "Anaconda 85" is stamped in the metal at one-foot intervals throughout each length. However, like copper and all copper alloys, Everdur is not equally resistant to all corroding agents, nor to the same cor roding agents under all conditions. As with copper, the resistance to corrosion may be substantially reduced in some instances by the presence of oxidizing agents. Nevertheless, Everdur does offer excellent resistance to the corrosive action of many solutions and atmospheres. Everdur Tanks--Everdur copper-sili con alloy is an ideal material for durable, rustless water tanks of every description-- from domestic range boilers to large storage heaters for hotels, laundries, hospitals, textile plants, schools or breweries. Everdur is made in all commercial shapes including annealed tank plates which have physical properties as given in A.S.T.M. Specification B96. EVERDUR* Everdur Metal is the original coppersilicon alloy. It is manufactured by The American Brass Company in five standard compositions and in practically all com mercial forms. This high strength engineering metal is resistant to a wide range of' corroding agents. Because of a versatile combina tion of useful properties, Everdur has become standard as a material for equip ment in many fields of engineering and industry. In addition to their non-rusting proper ties and high' strength, Everdur alloys possess many qualities not usually found m metals of this character. .They are unusually resistant to general atmospheric - conditions and other normally corrosive factors. Everdur alloys^ have excellent machining and working characteristics and, can be fabricated into a variety of forms and shapes. Everdur alloys are available for oxy-acetylene or carbon arc welding. CORROSION RESISTANCE The corrosion resistance of Everdur is equal to that of pure copper and in some cases, slightly superior. . Minimum specification requirements for hot rolled-and-annealed tank plates are: Tensile Strength, 50,000 psi.; Yield Strength (at 0.5 per cent elongation under load) 18,000 psi.; Elongation, 40 per cent in 2 inches. Welds made with annealed Everdur tank plates meet the requirements for Class B and C vessels in the A.S.M.E. Code for Unfired Pressure Vessels. ' For additional data and names of fabri cators address our nearest office or agency. EVERDUR FOR AIR CONDITIONING EQUIPMENT Because of its strength and welding properties, Everdur may be substituted for steel and fabricated by substantially the same methods and with much the same equipment as steel. Everdur metal has been used with marked success for fans and blowers, ducts, humidifiers, cast and wrought parts of other equipment items subject to corrosive influences. EVERDUR LITERATURE "Everdur" is a trademark of The American Brass Company registered at the U. S. Patent Office. - Descriptive literature containing much pertinent tabular data will be sent upon request. 1105 Air Conditioning and Heating Piping copper end Brass Mueller Brass Go. Port Huron, Mich. Branch Offices and Representatives in Principal Cities Albany. N. Y. Atlanta, Ga. Boston, Mass. Chicago, III. Cincinnati, Ohio Cleveland. Ohio St. Louis, Mo. Dallas, Texas Detroit, Mich. Flint, Mich. Harrisbukg, Pa. Indianapolis. Xnd. Los Angeles, Calif. Minneapolis, Minn. Newark, N. j. Philadelphia, Pa. N. S. Pittsburgh. Pa. San Francisco, Calif. Seattle. Wash. Washington, D. C. Canadian Sales and Manufacturer Canada Wire and Cable Co., Ltd., Toronto, Canada PRODUCTS--STREAMLINE Copper Pipe and Seamless Tubes; STREAMLINE Hard Copper Pipe and Solder Fittings; Valves, Flared and STREAMLINE Solder Fittings for Mechanical Refrigeration; Forgings of Brass, Bronze and Copper; Castings of Brass and Bronze; Rod; Screw Machine Products; Fabri cated Parts and Special Nickel and Chromium Plated Parts;'Machined,Formed Tubes. . Coupling Copper to Copper , Copper to Outside I.P*S. &et Elbow Streamline Copper Pipe and Fittings for heating,, plumbing, air conditioning and industrial use are made by the Streamline Pipe and Fittings Division, Mueller Brass Co., Port Huron, Mich. The Streamline Solder Fitting is the original solder type fitting, introduced and manufactured by the Mueller Brass Co. of Port Huron, Mich. It incorporates many advantageous features and has proved to be the revolutionary advance of the age in the development of piping systems for plumbing and heating and for many industrial uses. . The Streamline Solder Fitting is not connected either by threading or flaring, but by soldering. The outside surface of the copper pipe and the inner surface of the Stream line fitting are cleaned with sanddoth, and solder flux is then applied to the cleaned surfaces to eliminate oxidation when the assembled joint is heated. The joint is then sufficiently heated with a blow or acetylene torch and the soldering operation is per formed by feeding wire or stick solder through the feed hole in the fitting. The Streamline Solder Fitting alone has the solder feed hole, groove and taper. The solder feed hole, through which the solder is introduced, enters directly into an internal feed channel. The feed channel is located equidistantly between the internal shoulder against which the pipe rests and the outer edge of the fitting. When solder is introduced it is.distributed by capillarity from the feed channel and distributed evenly and thoroughly between the bonding surfaces,.traveling inward to the shoulder and outward to the edge of the fitting where it appears as a continuous solder ring around the full circumference of the pipe. This ring, and feed hole completely filled with solder, constitute positive proof to the operator that the joint is permanently leak-proof. An actual pressure test is not necessary. 1100 Air Conditioning and Heating Piping Copper and Brass Streamline Pipe and Fittings Division MUELLER BRASS CO. Port Huron, Mich. Patents 1770852; 1776502 90 Deg Elbow .. ` _ Tee Copper to Inside l.P.S. . Crosses The solder may be fed from any position, whether the feed hole is located at the top, side or bottom. Owing to the never failing phenomena of capillarity, the solder will flow up, down or laterally with equal facility. Streamline Copper Pipe is a seamless cold drawn copper tubing conforming to A.S.T.M. B88. It is made in sizes in. to 12 in. and Types K, L, and M, of which Type K is the heaviest. The intermediate weight, Type L,ris the preferred weight for plumbing, heating and refrigeration. For most purposes hard drawn pipe is used, though Types K and L can be furnished annealed when bending is required. Annealed Type "K" in sizes up to 2 in. is widely used for underground water "services''. An additional'lighter weight in sizes 3 to 12 in. inclusive is used by paper mills for water and stock lines at pressure up to 100 lb. Streamline Solder Fittings are furnished in ail sizes to 6 in. inclusive. They'are of the same thickness as Navy and MSS Fittings for 125 steam or 175 lb. non-shock water pressure. ' All fittings over 6 in. are flanged and may be had with either A.S.A. or riveted pipe standard flanges. -. Mating flanges are soldered to the pipe--A.S.A. 125 standard flanges are available from 1 in. up. During the last fifteen years architects and engineers have used Streamline Copper Pipe and Fittings successfully in every type of building construction and in thousands of installations throughout the United States and Canada. - ' In addition to its rust and vibration-proof qualities and long life, Streamline has many other advantages such as the reduction in size of pipe lines and radiator con nections from those nominally used, a neat, compact installation requiring a minimum of space and important advantages in industrial and drainage applications. There is a Streamline product for every piping requirement. Write Mueller Brass Co., Port Huron, Michigan, for complete information and catalog. 1107 Air Conditioning and Heating Piping Fitting Revere Copper and Brass Incorporated Executive office: 230 Park Avenue, New York 17, N. Y. ' MILLS--Baltimore. Md.. New Bedford. Mass., Rome, N. Y.. Detroit. Mich., Chicago, III. SALES OFFICES--Boston. Mass., Providence. R. I.. Philadelphia, Pa.. Atlanta. Ga., New York. N. Y., Pittsburgh. Pa., Cleveland, Ohio, Cincinnati, Ohio. Grand Rapids. Mich., Milwaukee. Wis., St. Louis, Mo.. Indianapolis. Ind., Minneapolis. Minn., Dallas, Texas, Seattle, Wash., San Francisco, Calif.. Los Angeles. Calif.. - Hartford, Conn., Dayton, Ohio. Houston. Texas REVERE COPPER TUBE Revere Copper Water Tube is produced under close inspection and meets all Federal and A.S.T.M. specifications. It is cold drawn, seamless, deoxidized, and possesses a gunbarrel finish on the inside as well as theoutside. Awiderange of stand ard sizes made in hard and soft tempers is normally stocked by distributors. Types K, L, and M are made in the sizes, tempers, and lengths shown below. Type K is a heavy wall tube commonly used for underground water service lines, for plumbing and heating, oil lines, and some air conditioning, applications. Type L is a medium wall tube furnished in hard or soft temper, and Type M is a light wall tube furnished in hard temper only. The latter is not recommended for underground service or for compression fittings. The actual outside diameter of these three types of tube is Yz in. greater than the nominal size in each case. Revere Dryseal Copper Tube is a dependable dehydrated utility tube fur nished only in soft temper coils having both ends sealed. There are nine sizes available from Y in. to % in. inclusive. In each case the nominal size and the actual outside diameter are the same and the wall thickness is 0.035 in. throughout. Revere Dryseal Copper Tube is commonly used for air conditioning and heat control lines, refrigeration and oii burner installations, and com pressed air lines. It can be bent by hand and easily flared for compression fittings. , Fittings--Standard solder type fittings in cast or wrought patterns are available for use with Types K, L, and M copper tube.- Various types of compression fit tings are made for use with Types K and L tube and Revere Dryseal Tube. Con nections made by the use of these fittings are proof against leaks so often caused by stresses or vibration. Joints of this kind are quickly made without any thread cutting and are generally stronger than the tube itself. Advantages of Revere Copper Water Tube--The many advantages of Revere Copper Water Tube of particular interest to design engineers can be summarized briefly as follows: 1. A piping system comprising Revere' Copper Water Tube and soldered fittings can be installed in a minimum of space as no allowance need be made for swinging wrenches. 2. Soft temper copper tube can be bent easily for offsets and changes in direction. 3. There need be no fear of rust accumu lation on the inside of Revere Copper Water Tube. 4. It is particularly suitable for forced circulation hot water heating systems. The very smooth interior of Revere Copper Water Tube insures high velocities with a minimum of frictional resistance. Revere Copper Water Tube for Radiant Panel Heating--A practical manual outlining a graphical design pro cedure for Radiant Panel Heating instal lations is now available to Engineers and Architects on request. To Engineers and Manufacturers of Heating and Air Conditioning Equipment--Revere representatives will gladly assist and cooperate with engineers and suppliers of heating and air conditionmg equipment at ayy time regarding matters involving applications of non-ferrous products. Revere Copper Water Tube STANDARD DIMENSIONS AND WEIGHTS Type K Type L . Type M Size In In. O.D. in In. Well Thick ness In. Wt. Lb per Ft Weil Thick ness In. Wt. Lb per Ft Well Thick ness In. Wt. Lb per Ft y< .375 .032 .134 .030 .126 025, .107 VV?* 300 .049 .269 .035 .198 .025 .145 .625 .049 344 jm 385 .028 304 $ .750 .049 .418 .042 362 .030 .263 .875 .065 .641 .045 .455 .032 328 1 1.125 .065 339 .050 ' .655 .035 .465 1*4 1.375 .065 1.04 i'/i 1.625 .072 136 .055 .884 .042 .682 .060 1.14 .049 -940 2 2.125 .083 2.06 v/l 2.625j .095 2.93 .070 1.75 .080 2.48 0.58 1.46 0.65 2.03 %3 3.125 .109 4.00 3.625 .120 5.12 .090 333 .100 439 .072 Z68 .083 338 4 4.125 .134 631 :l 10 538 .095 4.66. 5 5.125 .160 937 .125 7.61 .109 6.66 6 6.125 .192 13.9 .140 103 .122 8.92 Recommended Operating Pressures Type K--Hard Temperup to 400 lb Type K--Soft Temper--------------------------------up to 250 lb Type L--Hard Temperup to 250 lb Type L--Soft Tpmpw M,................. ................ up to ISO lb Type M--Hard Temperup to 250 lb Tempers and Lengths . Type K1 Hard and Soft Temper in straight 20 ft lengths. Type L ) Soft Temper 1 in. and under in 60 ft coils. Type M--Hard Temper in straight 20 ft lengths. 1108 Air Conditioning and Heating Piping Tube and Fittings Wolverine Tube Division Calumet & Hecla Consolidated Copper Company 1411 Central Avenue, Detroit 9, Michigan SEAMLESS TUBE COPPER - BRASS - ALUMINUM Sales Offices: Atlanta, Ga......... P. O. Box 38--Northside Station Buffalo, N. Y................................. 416 Jackson Bldg. Chicago. Ill--............................. 3348 S. Pulaski St. Cleveland. Ohio......................._..1740 East 12th St. Dayton, Ohio........... -..................................... P. O. Box 1041 Fort Worth, Texas.......................... 1825 Fair Building Grand Rapids, Mich.___ 208 Federal Square Bldg. Houston. Texas._.P. O. Box 259--Petroleum Bldg. London. Ontario-............................. ............ 1109 York St. Los Angeles, Calif......................1015 East 16th St. Milwaukee, Wis.......................... 647 W. Virginia St. Minneapolis. Minn..... ................ 529 S. Seventh St. New York. N. Y.._................................. 60 East 42nd St. Odessa, Texas....................................... P. O. Box 3272 Philadelphia. Pa.. Commercial Trust Bldg.--Room 1208 15th and Market Sts. Pittsburgh. Pa.._.................................1214 Liverpool St. Portland, Ore...... ....................416 Northwest 14th St. St. Louis. Mo-- .......................... 4565 McRae Ave. Wichita Falls. Texas....................... P. O. Box 1030 COPPER WATER TUBE ACCUMULATOR SHELLS TYPE K--Recommended for Air Con ditioning, Refrigeration, Oil Burner, and Plumbing and Heating installations. TYPE L--For Oil Burner, Air Con ditioning, Refrigeration and general plumb ing uses. TYPE M--Suitable for Air Condition ing and Refrigeration installations and for interior plumbing and heating purposes. A new accumulator shell developed by Wolverine and produced to customers' specifications in a variety of shapes and sizes up to SY in. diameter. It combines many advantages including one-piece construction and is especially adaptable to refrigeration problems. Send for Catalog E-l describing other spun-end tubular parts. Types K and L furnished in hard or soft temper; Type M, hard only. Wolverine Water Tube is made accord ing to U. S. Government and A.S.T.M. specifications. For a complete list of these data, write Detroit for Form 575. REFRIGERATION TUBE Wolverine refrigeration tube has long been the standard of the industry. De hydrated, sealed, paper-wrapped; uniform ,soft temper, and moisture content well below minimum specified by A.S.R.E. Available from stock in standard coils. TRUFIN, The Integral Finned Tube originated and developed by Wolverine, is one of the most impressive advances in the entire heat transfer field. TRUFIN is suitable for nearly all kinds of heat transfer work--heaters, coolers, interchangers, condensers, and many other applications. Send for "TRUFIN'* Engineering Pam phlets 1, 2 and 3. The experience of 29 years of seamless tube manufacture, the use of the latest equipment, and adherence to Government and customer specifications, are responsible for the uniform, high quality of Wolverine products. And now, - backed by the 78-year experience and large resources of Calumet & Hecla, Wolverine quality is controlled from ore to finished product. 1109 Bends, Coils, Fittings Expansion Joints , E. B. Badger & Sons Co. DESIGNERS ENGINEERS CONSTRUCTORS . MANUFACTURERS New York 18, N. Y. 500 Fifth Avenue Boston 14. Mass. 75 Pitts Street Agents in Principal Cities PRODUCTS AND SERVICES BADGER "PACKLESS*' CORRUGATED EXPANSION JOINTS Engineers and Manufacturers of Chemical, Pietro-Chemical and Petroleum Refining Equipment; Process Engineers, Designers and Constructors of Complete Plants. . / BADGER "PACKLESS" CORRUGATED EXPANSION JOINTS Protect equipment; eliminate costly shut-downs; prevent loss of materials flowing through pipe lines. The Badger " Packless" Corrugated type of expansion joint has been used for many years to relieve stresses, absorb vibrations between connected equipment, and compensate for changes in pipe liftes due to temperature differentials. BACKED BY FIFTY YEARS OF EXPERIENCE Badger engineers pioneered the cor rugated "packless" joint and brought it to its present high state of dependability and usefulness. To meet the increasingly severe conditions in industry, the more recent developments are included in the following brief descriptions. E. B. Badger & Sons Co. Bends, Coils, Fittings Expansion Joints FLANGED AND WELDING ENDS. Badger "Packless" Corrugated Expansion Joints can be furnished with either flanged or welding ends. TELESCOPING SLEEVES. Badger "Packless" Corrugated Expansion Joints can be furnished with telescoping sleeves if required. . INSTALLATION, OPERATING, MAINTENANCE ECONOMIES "Packless"--Since this type of ex pansion joint is made from a single tube, no packing is required--hence no servicing. This is particularly advantageous in under ground installations, because the expense of manholes and tunnels can be eliminated. Flexible--This type of joint is readily flexed, thus reducing to a minimum the thrust on adjacent equipment or fittings. Wide Range of Traverses--By varying the number of corrugations, the Badger "Packless" Corrugated Expansion Joint can.be made to take care of traverses ranging from small fractions of an inch up to any practical limit. Wide Range of Pressures--Standard joints are constructed for normal operating pressures; special joints for higher pres sures. Compactness--Outside diameter of Badger " Packless" Corrugated Expansion Joint is about that of a flanged fitting. Ease of Installation--The Badger "Packless" Corrugated Expansion Joint is as easily installed as any fitting. COPPER AND STAINLESS STEEL. Badger "Packless" Corrugated Expansion Joints are made in self-equalizing or non equalizing types; and are made of copper, stainless steel, or other metals to meet varying conditions with respect to tem perature, pressure and corrosion. HEAT TREATMENT, Every Badger "Packless" Corrugated Expansion Joint is scientifically heat-treated during the process of manufacture to remove forming stresses. This Badger process increases resistance to flexing stresses, lengthening the life of joint. DIRECTED FLEXING--SELF-EQUALIZING This feature, exclusive with Badger not only limited but is progressively con "Packless" Corrugated Expansion Joints, trolled throughout the movement. Flexing greatly lengthens the life of the corrugated ' stresses are kept distributed. type of expansion joint. Through Self equalizing Rings, the flexing movement is Standard Flanged-End .Badger Directed Flex ing, Self-Equalizing "Packless" Corrugated Expansion Joint. Also made with standard welding 'end. {Double units available.) Bulletin No. 100. Badger Non-Equalizing "Packless". - Cor rugated Expansion Joint, Single Corrugation. Also made in multiple corrugation and special shapes. Bulletin No. 00. 1110 1111 Bends, Coils, Fittings Hot Water and Industrial Piping GMNNELL COMPANY. Heating, Industrial and Power Plant Piping, Fittings, Hangers, Valves, Pipe Bending, Welding, Piping Supplies, Etc. Executive Offices: Providence 1, R. I. Offices, Plants and Branches Albany 7, N. Y. Atlanta 2, Ga., (Plant and Foundry) Baltimore 2, Md. Boston 9, Mass. Buffalo 2, N. Y. Charlotte I, N. C. (Branch Chicago 9, III. (Branch) Cincinnati 2, Ohio Cleveland 14, Ohio (Branch) Columbia, Penna. (Plant) Columbus 15, Ohio Cranston. R.I. (Plant and Foundry) Dallas 1, Texas (Branch) Detroit 26, Mich. Houston 1, Texas Kansas Citt 6, Mo. Memphis 3, Tenn. Milwaukee 2. Wis. Minneapolis 15, Minn. (Branch) Newark 2, N. J. New Orleans 13, La. New York 17, N. Y. Philadelphia 34, Penna. (Branch) - Pittsburgh 22, Penna. Providence 1, R. I. (Plant and Foundry) Richmond 19, Va. Rochester 4, N. Y. . St. Louis 10, Mo. (Branch) St. Paul 2, Minn. (Branch) Warren, Ohio (Plant and Foundry) ' GRINNELL COMPANY OF THE PACIFIC Los A nobles 13, Cal. (Branch) Oakland 7, Cad. (Branch) . Seattle 1, Wash. (Branch) Ban Fuancnsco 7, Cal. (Branch) Montreal, Qoe. (Branch) GRINNELL COMPANY OF CANADA, LTD. Vancouyee. B. C. (Branch) Toronto, Ont. (Plant and Foundry) Oshawa, Ont. (Foundry) Winnipeg, Man. PRODUCTS AND SERVICES-- Complete Service on materials to Specification on Power Plant Piping, Industrial Piping, and Industrial Heating Systems; Prefabricated Pip ing including Pipe Cutting and Threading, Pipe Bends, Welded Headers, Welded and Welding Fit tings, Lap Joints and the Grinnell line of products for Super Power. Grinnell Equiflo Valves for forced hot water heating systems; Grinnell Adjustable Pipe Hangers and Sup ports; Grinnell Cast Iron and Mallea ble Iron Pipe Fittings; Grinnell Flared Tube Fittings; Grinnell Malleable Iron Unions; Grinnell Welding Fittings; Grinnell Thermoliers (Unit Heaters);. Thermoflex Traps and Heating Spe cialties. . Also Humidifying Systems; Piping for acids and other special materials. Malleable Iron, Brass, Bronze and. other Castings; Brass, Cast Iron, Wrought Iron and Steel Pipe; Seam less Steel Tubing in Iron Pipe Sizes. Valves: Check, Diaphragm, Globe, Pressure Reducing and. Regulating, Quick Opening, Safety and Y. Automatic Sprinkler Systems; Stand Pipes; Underground Supply Mains; Hydrants; Fire Pumps; Pressure and Gravity Tanks. 1, Grinnell Equiflo Valves For Forced Hot Water Heating Equiflo Valve The designing of forced circulation hot water heating systems is so simplified by the Grinnell Equiflo Valve that they can be laid out and installed as easily as vapor or steam systems. This valve consists of a regular type packless radiator valve with' a cartridge or tube made up of a series of orifices and baffles capable of setting-up any required frictional resistance. This method of establishing any desired resis tance does away with elaborate calcu lation of pipe sizes. Grinnell'guarantees perfectly balanced circulation to each and every radiator where these valves are installed throughout the system.. Equiflo Data Book sent to interested parties. For Data On Thermoflex Traps and Heating Specialties, see page 1211 1112 Grinnell Company, Inc. Bends, Coils, Fittings pFP1ng GRINNELL ADJUSTABLE PIPE HANGERS AND SUPPORTS One of the chief advantages of Grinnell Adjustable Hangers is that they permit adjustment of pipe lines after installation, thus obviating the necessity of tumbuckles or the removal of hangers. Their time and trouble-saving qualities during installation are equally exceptional. Below are shown a few Grinnell Hangers and Supports of par ticular interest to heating engineers. Send for Hanger Catalogue showing complete line. %drtZ' Adjustable Swivel Rings (Patented) These Malleable Iron Adjustable Swivel Rings can be used with Coach Screw Rod or Machine Threaded Rod in connection with practically any type of Ceiling Flange, Expansion Case, Insert, etc. Adjustment of at least 1in. is secured by turning Swivel Shank. Swivel Shank automatically locks, preventing loosening due to vibration in the pipe line. The Split Ring permits adjustment either before rFl-er Ringu`f closef. A wedge type pin is loosely but inseparably cast into the hinged section for fastening this section after pipe is in place. r%u%i ^ . Fig. No. 174 Swiid Pipe Roll Adjustable Swivel Pipe Rolls (Patented) An adjustable type of pipe roll using a single hanger rod. Swivel Shank allows vertical adjustment and automatically locks, preventing loosening from vibration. CB-Universal Concrete Inserts (Patented) t Made of malleable iron, in one body size, to take a special removable nut, tapped for % in., ^ in., % in., % in. or % in. rod as required. Nuts automatically lock by means of V-type. teeth on both insert and nuts. ; Fig. No. t8i CB-Unitertal lneat GRINNELL WELDING FITTINGS 90" Elbow, Long Turn Grinnell Welding Fittings are made from Seamless Steel Pipe or tubing and possess the same physical characteristics as stan dard, extra strong and o.d. steel pipe or seamless steel pipe of comparable size. They can be used under the same con ditions, pressures and temperatures as the pipe itself. All Grinnell Welding Fittings have weld ing faces for all plain circumferential butt welds scarfed or beveled as follows: For wall thicknesses 2fg to % inch inclusive, 37H deg. 2H deg., straight bevel. Angles of bevel other than 37deg. can be furnished on special order. Wdding Outlet Welding Tee 1113 Threaded Outlet ' Bends, Coils, Fillings Plastic Pipe and Tubing The Dow Chemical Company Midland Michigan New York Boston Philadelphia Washington Cleveland Detroit Chicago St. Louis Houston San Francisco Los Angeles Seattle i 1 -- - Plastics Division -- ! SARAN PIPE, TUBING AND FITTINGS i FOR INSTALLATIONS REQUIRING HIGH CHEMICAL RESISTANCE \ These thermoplastic products made from Tubing, pipe, and fittings for both are Dow raw materials are recommended for available from: American Hard Rubber a wide variety of applications:--especially Co., 11 Mercer Street, New York, New those jobs requiring high chemical re York; Commercial Plastics Co., 201 N. sistance. (See table below.) Additional Wells St., Chicago, III.; Haveg Corpora engineering data and literature are availa tion, Newark, Del.; Elmer E. Mills Cor ble from the following manufacturing and poration, 153 W. Huron St., Chicago, 111.; sales licensees--or any Dow sales office. St. Louis Plastic Molding Co., 4605 Olive Tubing and fittings are available from: St., St. Louis, Mo.; Western Felt Works, Parker Appliance Co., 17325 Euclid Ave., 4115 W. Ogden Ave., Chicago, 111.; Yard- Cleveland, Ohio; Yardley Plastics Co., ley Plastics Co., 138 Parsons Ave., 138 Parsons Ave., Columbus, Ohio. Columbus, Ohio. CHEMICAL RESISTANCE OF SARAN AT ROOM TEMPERATURE Reagent Stability Rating Reagent Stability Rating Reagent 98% (Cone.) HtSOt Fair 60% H*S0 Excellent 30%HsSO Excellent 10% HiSO Excellent 35% (Cone.) HC1 Excellent I0%HC1 Excellent 65% (Cone.) HNOi Good 10% HNOi Excellent Glacial Acetic Excellent 10% Acetic Excellent 5% HjSO* Excellent Cone. Oleic Excellent 50%Ha0H -1-0--%---H---a-O---H28% NHOH ' 10%NHiOH EthyUl Alcohol Carbon Tetrachloride Di Ethyl Ether *Benzene Ethyl Gasoline Turpentine Triethanolamine Lubricating Oil Good Good Not Recommended Not Recommended . Exc.e..llent. Good Good Not Recommended Excellent " Excellent ' Excellent linseed Oil Bromine Water Chlorine Water **ChIorax" Bleaching Solution 10% Dnponol sulfite 15%CaCli Water Air It should be noted that chemical resistance decreases with rise in temperature. Shrinks slightly upon immersion in these solvents. Stability Rating Excellent Not Recommended Not Recommended Excellent Excellent ' Excellent Excellent Excellent Excellent Excellent (45-510) TUBING Saran tubing ac commodates both high and low pres sures, withstands freezing, and is heat resistant up to 170 F. Its unusual chemical resistance gives it wide use in installations where acids and corrosive chemicals must be handled. Saran tubing, is readily flared with a special flaring tool, assuring a tight joint in special Saran fittings. Tees, elbows, and straight joints (illustrated) are available in siz es to match tubing (up to in.O. D.). PIPE Chemical resist ance makes Saran pipe invaluable for many industrial in stallations. It is on ly % the weight of comparable iron pipe. Available in sizes up to 4 in. O.D. A complete weld is formed in one minute by placing - on heated welding plate until molten and pressing ends together. Easily threaded with modified standard equip ment. Flanges, couplings, ells and plugs are available. Further fittings be ing developed. 1114 Bends, Coils, Fittings Arthur Harris & Co. 210-218 N. Aberdeen Street Chicago 7, 111. ENGINEERS -- FABRICATORS OF NONFERROUS METALS AND STAINLESS STEEL Metals Fabricated--Aluminum, Block Tin, Brass, Bronze, Copper, Everdur, Monel, Nickel, Inconel, Stainless Steel and KA2 SMO. Bulletin on request. Metal Floats Column - BqU Flol Cylindrical Cylindrical Cylindrical Made of copper, plain steel, stainless steel, KA2 SMO, aluminum, brass, Monel, pure nickel, Admiralty and Everdur, for open tank and all pressures. .... Seamless copper ball floats carried in stock in diameters of 3 in., 4 in., 5 in., 6 in., 7 in., 8 in., 10 in., 12 in. for open tank and pressures of 25, 50, 100 and 150 lb. Floats in special sizes and pressures--made to order. Stainless steel ball floats 2)^ in. to 12 in. for high pressure and corrosion carried in stock--special stainless steel floats made to order --stainless steel ball floats larger than 12 in. diameter can be made up specially. Float catalog sent on request. - Copper Expansion Joints For low pressure and vacuum. Made in two styles--convex and concave. Sizes 4 in. to 60 in. diame ter. Cast iron or steel flanges. Flanges drilled to American stand ard unless otherwise ordered: B-290 v available only in sizes 4 in. to 15 in. B-S81 Concave inclusive. ` Coils For heating, cooling and condens ing. All shapes, rrafde from any size pipe or tube--standard or special connections, of copper, brass, alumi num, stainless steel, KA2 SMO, monel, inconel, nickel, block tin, arid Everdur. . " A ot /X We make behds in every shape from all sizes of copper water tube, pipe and tubing in copper, brass, aluminum, stainless steel, monel, tin and nickel. Standard or special connections. U-bends for storage water heaters. ' Also special pipe work for industrial installations, plumbing, heating and brewing. Perforated pipe, double pipe coolers, etc. .. Non-Ferrous Castings--"Dairywhite" nickel silver for Process Industries Equip ment. Suitable for milk and food products machinery. Castings also of 88-10-2. 80-10-10, 85-5-5-5, silicon bronze and manganese bronze, and special mixtures. Many patterns available without charge. 1115 Bends, Coils, Frames MUJdm Swan Engineering Company, Inc. BENDING COILS FRAMES Phone Bloomfield 2-1000 30-58 Nelson Street Bloomfield, New Jersey Bending Engineers--Contract Manufacturers FABRICATORS OF FERROUS AND NON-FERROUS PIPE AND TUBING INCLUDING STAINLESS STEEL AND ALUMINUM FRAMES and FRAME Assemblies We specialize in all types of pipe and tube bending, coiling, expanding, and other types of forming and fabrication. By specializing in this line and manufacturing against order only, our service has taken us into many different fields and we have aided in the development of many new products as well as in the improved application of standard materials. . Our organization is large enough to be effective and small enough to be flexible. We solicit your quotation irrespective of size. ' 1116 Bends, Coils, Fillings spJcZl'it,^ Tube Turns INCORPORATED - General Offices and Factory: Louisville 1, Ky. BRANCH OFFICES Chicago, 327 S. La Salle St............ ....... Harrison 8527 Cleveland. Rockefeller Bldg.................. Cherry 5571 Detroit. 615 Griswold St., Room 713, Cadillac 9852 Houston, 1707 Commerce Bldg.___ Charter 4-1668 Los Angeles. 210 W. Seventh St__ Van Dyke 4762 New York, 150 Broadway._____ ____ ___ Rector 2-7844 Philadelphia, Broad Street Station Bldg., Rittenhouse 0722 Pittsburgh, 3001 Grant Bldg------------- Atlantic8848 San Francisco, 2611 Russ Bldg...........Garfield 2594 Seattle, 422 Smith Tower Bldg ______ Main 2778 Washington, D, C., 1026 17th Street, N.W., National 0860 DISTRIBUTORS IN PRINCIPAL CITIES Reducing Outlet Tee 9CPShort Radius Elbow 90 Long Radius Elbow ' TUBE TURNS is the original manufacturer of seamless welding fittings and also pioneers in their development and use. Complete details and engineering data on 40QO types, sizes and materials are included in the Tube-Turn Catalog No. Ill sent on request. Concentric . Reducer <_ Eccentric Reducer TUBE-TURN WELDING FITTINGS--RANGE OF SIZES Light Gauge Type of Fitting Elbows Elbows ' Returns Returns Returns Tees Tees Reducers Caps Stub Ends Nipples Nipples Saddles Laterals Laterals Crosses Rings Sleeves Description Standard Weight Extra Strong Sched Double ule Extra 160 Strong Nomi nal Pipe Size Iron Pipe Size 90 Long Radius '/2'-24* VS-2V -12' r-30* l*/2'-30' 4J" Long Radius Vi'-w y4'-30" I *-12' 180 Long Radius Vi'-U' l'-24' l'-|2' I'-6' 4'-24' 3'-l2' r-s* 4'-24' 3*-I2* 3'-8' 4'-24' 3'-l2* 180 Short l'-30* l'/2'-30' 1 8U" fcjrtra Long Radius - I'-W \m-w r-i *Straight y#-24* W-24' 1'-I2' l'-8' Reducing Outlet VS-14' y/-24* 2 I'-8' Concentric &* Eccentric 1x1-24*20 1x1-24x20 r-24* l'-24' 1x1-12x10 I'-8' Lap. Joint I'-24' t'-24' Shaped, 91F to l>/,'-12' 1*4'-12' Header Shaped, 45 to Header H4M2' I*4'-I2' 2' -24' Straight l<4'-24' l'4'-24' Keducing-on- Run Straight Welding 1 *4'-24' V*"- 24' J/.'-l2' l'yy44,'''---22i442*'' Welding - 2'- 24' SUPER Tube-Turn 45 long radius elbows. 90s long radius elbows, and 180 long radius returns available in both Standard weight and Extra Strong in sizes from 3* to 12*. Tube-Tumwddingfittingsand flanges conform to applicable ASA and ASTM Standards. For further details please refer to Tube Turns catalog and data book No. 111 .________ ISO0 Long Radius Return Lap Joint Stub End Cap Straight Lateral 4-5 Shaped 900 Shaped Nipple Nipple m Saddle Straight Cross *30 in. size short radius. Slip-on Flange TUBE-TURN FORGED STEEL FLANGES--RANGE OF SIZES 150 300 400 600 900 1500 2560 Lb. Lb. Lb. Lb. Lb. Lb. Lb. Welding Neck Slip-On Lap Joint Blind . Socket Type . Reduemg-threaded nr slip-on l'-24' i'-24* 4'-24't l'-24' 4'-24" *'-24' i'-24' *'-24' i'-24' I'-24' l'-24'1 i'-24' l'-24't i'-24' j'-24'* 4*-24* !'-24'* l'-24' *'-24' |'-24' l'-24' *'-24' l'-24' r-24' **-24"* l'-24' '1-24' l'-24' i'-24' r-24't l'-24' i'-24" l'-24' *'-24' l'-24' 1'--4' i'-31' r-24' }'-24' }'-24'1 l'-24' l'-24" r-24^ r-u' Lapped Flange tDimensions on sizes thru 3H in. same as for 600 lb. flanges. Dimensions on sizes thru 2^ in. same as for 1500 lb. flanges. Welding Neck Flange Screwed Flange Blind Flange Welding Ring 1117 Controls and Instruments Alco Valve Company ENGINEERED REFRIGERANT CONTROLS 851 Kingsland Avenue, St. Louis 5, Mo. New York Office: 122 East 42nd Street THE COMPLETE LINE OF REFRIGERANT CONTROLS ALCO THERMO EXPANSION VALVES THERMO EXPANSION VALVES: for automatic control of liquid refrigerant on all types of refrigeration and air conditioning systems. Capacities--from fractional tonnage to 100 tons Methyl Chloride, 50 tons "Freon-12". TyPeTK--withfamous 10-second capacity change feature--' "5 valves in 1 " Type TCL Type TIL - ' Type TR--MuLti-Oullcl ALCO SOLENOID VALVES SOLENOID VALVES: for all types of service. For Liquid: "Freon"--up to 75 tons. Methyl Chloride--up to 150 tons. For Suction: "Freon"--up to 8.8 tons. Methyl Chloride--up to 17 tons. Type St Type MS Type RS ALCO AMMONIA CONTROLS AMMONIA CONTROLS: Solenoid Liquid Valves--up to 172 tons. Solenoid Suc tion Valves--up to 28 tons. Thermo Expansion Valves-- from fractional*tonnage to 60 tons. Type EPRIS Type M9P ' ' Type TG ALCO ALSO MAKES: Evaporator Pressure Regu lators for "Freon", Methyl Chloride and Ammonia with connection sizes up to 6 in.--Solenoid Valves for brine, water, gas, air and steam--Float Switches-- High Pressure Float Valves--Constant Pressure Ex pansion Valves--Liquid and Suction Line Strainers. 1118 - Controls and Instruments American Meter Company INCORPORATED General Offices: 60 East 42nd St., New York 17, N. Y. Albany Baltimore Birmingham Boston Chicago Erie Kansas City . Los Angeles Philadelphia Pittsburgh San Francisco Dallas, Houston, Tulsa--Westcott & Greis, Inc, Alhambra, Calif.--Reliance Regulator Coirp. Hamilton. Ont.--Canadian Meter Co.. Ltd. Measurement and Control of Gas, Oil, Steam, Air and Liquids FLOWMETERS . . ' - Indicating . . . Recording -. . . Integrating The Metric Indicating Flowmeter is an orifice type meter which indicates the rate of flow of air, gas, oil, steam or water through a line in which an orifice is installed. * The Integrating Flowmeter charts a totalized reading of the quantity of gas, air, or steam at constant pressure--or for liquids, regardless of the rate. . Metric Flowmeters--known for their simplicity of design --assure trouble-free operation and ease of adjustment. . Write for Bulletin E-3. ' . RELIANCE REGULATOR Type A Reliance Type A regulators are designed to give absolute control of low pressures and are used extensively for con trolling pressure to air and gas appliances requiring positive control of operating pressures. . A complete line of Reliance regulators are notable for exacting duty and minimum pressure loss at required capacity, as well as ease of servicing and low cost of upkeep. Automatic shut-off valves are available for jobs that require a safety feature,-so that when inlet pressures fall too low, the flow of gas through the regulators is stopped. Write for Bulletin 43. The'Compact IRONCASE GAS METER Space requirements of these meters are cut down to the least possible. dimensions without sacrifice of Metric Ironcase advantages. Ironcase positive displacement meters set up a standard of unsurpassed accuracy in the measurement of gas by making use of the approved slide valve and full bellows principle . . . then by adding to this principle ah extra ordinary ruggedness of construction. The body is cast in one' piece. No joints and gaskets between internal parts . . . and no possibility of internal .leaks. Special safeguards against friction loss are found throughput each meter. . Low pressure capacities up to 10,000 cu ft at 2 in., . differential.' Write for Bulletin EG-40. 1119 Controls and Instruments HUTOIMIC PRODUCTS WADY 2450 nORTH THIRTY -- SCCOIID STRT mmuflUKff ?n\ Wisconsin A-P DEPENDABLE CONTROLS For Heating, Refrigeration and Air Conditioning A-P Therm ostatic Expan sion Valves. Several models and sizes, for ca pacities up to 16 tons Freon or 32 tons Methyl .Chloride. . A-P Solenoid* Operated Water Valve. Made especially for Deep Well Cooling. / A-P Thermostats. For Cooling or Heating A-PSolenoid Refrigerant Valves. Capa cities up to 50 tons Freon. A-P Waitteerr RegMt utating_ Valves. Capaci ties up to 1440 Gallons per hour. 6r . A-P "Trap-Dri." Combined Filter-Strainer-Drier Traps dirt, scale, moisture in refrigeration systems. A-P Controls for Oil Burning, Gravity-Feed Heating Plants. A-P Constant Level Oil Control Valve-- With Fuel Compensator. Used on Gravity Oil Burning Appliances. A-P Complete Fur nace Control Set-- Made in variety of types for Gravity-Feed Oil Burning Furnaces. A-P Fuel Oil "Trap- It"--Traps dirt and water in fuel systems. Improves operation of all oil burning devices. A-P Valve DEPENDABILITY ,is widely recognized in Refrigeration, Air Conditioning and Heating. This reputation is born of close adherence to a rigid standard of perfection--in materials used, careful testing, inspection and simplicity of construction. 1120 Controls and Instruments Barber-Colman Company Rockford, Illinois Automatic Control Systems for Heating, Ventilating, Air Conditioning Duct Thermostat Motor-operated Shut-off Valve Barber-Colman Controls are all electric; pre cision' built to insure long, continuous and dependable service;.easy to install in either new or existing buildings; and ready for. instant service, even after long shut-down periods. Thermostats. All types--room, duct, immer sion, air stream and remote bulb. For 2-position, floating, and proportioning control. Hygrostats. Room and duct types. Motor-Operated Valves. Packless, packed single-seat, pilot piston, V-ported, balanced, 3-way, and butterfly. For 2-position, floating, or proportioning control. Also Solenoid Valves for air, oil, water and gas. Motor-operated valves are powered with Barcol motors which have only one moving part and require no attention except oiling; oil submerged-operators require no attention. Control Motors. Uni-directional, or reversible fixed or adjustable speed. For 2-position, floating or proportioning operation of dampers in heating, ventilating or air conditioning applications. Otl submerged models have the motor and gear train entirely submerged in oil. Program Switches. Automatic contact making mechanism for multi-compressor control or similar applications. Econostat (not illustrated), a complete self- Motor-operated contained thermostatic unit for automatic regu- Proportioning Valve lation of the heat supplied to a building in accor dance with outdoor temperatures. Write for descriptive literature. LISTED AS STANDARD BY UNDERWRITERS LABORATORIES , (See also Page 1084) Remote Bulb Thermostat Stall Type Control Motor Heavy Duty Industrial Type Control Motor Controls and /nstruments Detroit Lubricator Company Division of Amfrican Radiator & Standard coaj*oration General Offices 5900 Trumbull Ave., Detroit 8, Michigan, U. S. A. ' New York 18, N. Y., 40 West 40tb Street . Chicago 5, 111., 816 S. Michigan Avenue Los Angeles 13, .Calif., 320 Crocker Street Canadian Representative: ' Railway and Engineering Specialties Limited, Montreal, Toronto, Winnipeg Automatic Controls Detroit Lubricator Company manufactures a very complete line of electrical controls, de signed to open or close an electrical circuit with changes of temperature or pressure. The No. 411 Thermostat (illu strated) is a low voltage model and is-made in plain and Day and Night types.. All No. 411 Thermostats are available with heat compensation to provide smooth, accurate temperature No. 411 control. The No. 855 Mercoid Room Thermostat (illustrated) is a line voltage type-- available in heating, air conditioning and refrig eration ranges. For industrial use the No. 250 and No. 450 line of pressure and tem perature controls is available, in pressure ranges from 20 in. vac. No. 855 to 350 lbs, and in tem perature ranges from -30 F to 495 F. Furnace Controls Also available is a full line of blower controls, combination blower and limit controls, such as the CA-815 illustrated, and a special line of water-tight equipment for use in wet locations. There is a "DL" control-available for practically every application where a dependable device is required to open or close an electrical circuit with changes of pressure or temperature. Write for com plete information. Our Engineering De partment is always ready to make recom mendations on any specific problem. . N0.CASJ6 Gas Valves * The No. V- 570 Electric Gas Valve is an electrical ly operated valve for con trol of gas lines from to in. It provides par- No. V-670 tial; opening upon initial operation, permitting quiet ignition of gas. Inexpensive, compact, and attractive in ap pearance, it employs an easily serviceable bimetal strip motor for actuating force. Write for Bulletin 201. The No. 566 Valve combines in one compact unit all of the functions of a control system, for gas heating. All safety functions are mechanical and operate independent of electric current. Adjustable for full snap or any degree of throttling action. . Limit control closes valve with a snap action. Valve may be. manually operated in case of cur rent failure. Applicable to all gases, natural, manufac tured, or mixed. Write for Bulletin No. 80. ^ Solenoid Valves "DL" Solenoid Valves for control of water, air, oil, gas, or refrigerant, embody many desirable features. They are free - from A.C. hum and will open against high pressures. Available in all standard volt ages and cycles A.C. or D.C. No. 683-3 (illustrated) is a small size valve with % in. connections. No. 681 is a pilot operated, intermediate size valve, and the No. 686 is a large pilot No. 685S operated valve with 1122 Detroit Lubricator Company capacity up to 17 tons Freon. No. 686 valve available with flanged connections. No. 681 and 686 are furnished with man ual opening feature to permit opening in case of current failure. All mcdels may be-taken apart and cleaned in the field without removing from pipe lines. Write for Bulletin No. 199. ' Controls and Instruments - No. 675 . Expansion Valves "DL" Thermostatic Expansion Valves are designed to keep the evaporator in a refrigerating system completely refrig erate!. All power elements are "gas charged*' to a definite pressure, preventing motor overload and providing quicker response and more sensitive control. Capacities from 14 ton to 30 tons Freon. The No. 673 valve employs a double bellows as the actuating means, while the "Dura-fram" line is constructed with a single diaphragm power element. All needles and seats are made of Delubaloy, a very hard, corrosion resistant alloy to insure long, trouble-free service. Write for Catalog^No. 200 on refrigeration equipment. Refrigerant Distributors . Detroit No. 790 Refrigerant Distributors insure a uniform supply of refrigerant to all sections of multiple circuit evaporators and are attached directly to the expansion valve by means of a flanged connection. These corrosion-resistant distributors are available for "Dura-fram" Expansion Valves No. 786, No. 787 and No. 788, and are interchangeable on all types. They are made in two types, as follows: Type A--2 to 8 passes. . 6 passes standard. Type B--9 to 18 passes. ' 12 and 18 passes standard. All distributors are designed for use with in. O.D. copper outlet tubes: - For complete capacity tables write for Bulletin No. 207. * "DL" Float Valves "Dura-fram" Expansion Valves These valves are of single diaphragm construction. The diaphragm is made of special^ alloy, care fully tested for flexibility to assure uniform capacities and smooth operation. Power elements are gas charged for protection against motor overload and for maximum sensitivity. Needles and seats are hard, corrosion resistant Delubaloy. .. . Automatic and thermostatic types in capacities from \4 to 20 tons Freon and .9 to .36 tons methyl chloride. Automatic compensator assures even fuel flow regardless of fuel teriiperature-- so simple to clean that servicing is no problem. - Available in both manual and automatic types.. .Manual-single, dual, or non metering. Automatic types--for furnaces; floor furnaces,, water heaters, etc.--with cither "high-low" or "Iiigli-olT" burners, natural or forced draft. 1123 Controls and Instruments The Fulton Sylphon Company Manufacturers of Sylphon Automatic Temperature Controlling Instruments and Packless Expansion Joints Sales Representatives in Principal Cities Knoxville, Tenn. HOT WATER SUPPLY No. 923 Temperature Regu lator--For controlling water temperature in heaters, open or dosed tanks and other equip ment. Operation unaffected by temperature fluctuations at the valve, either above or below bulb temperature. All parts, except steel adjustment spring, made of non-ferrous metals. May be installed in any position. Ranges from 40 -80 F to 290 -330 F. R'tSatZ Bulletin HVG-20. Sylphon Thermostatic Water Mixers Utilize hot water from any storage tank or instantaneous heater, and effectively . regulate the I amount of cold water required to temper it to the desired degree, actu ally mixing |the hot and j cold water to1 gether before I d e l i v-e r y . I Temperature No. 90S Sylphon Thermostatic remains COnWaler Mixer--14 to 1S1 gpm stant in spite depending on water pressure Q f fluctua tions in supply water temperatures or pressures. Four sizes with capacities ranging from 5 to 131 gpm. Bulletin HVG-40. REFRIGERATION CONTROLS Adaptable wherever brine is used as the refrigerant. Latest development is a "freeze-proof" w valve (illustrated at left on the Nd als.z popular Sylphon No. 945-Z RegReguiator ulator). Bulletin HVG-20. PACKLESS EXPANSION JOINTS The Sylphon Packless Expan sion Joint eliminates useless building height, expensive con struction and non-revenue pro ducing space. No costly leaks and repairs, no repacking, always tight, allows heating system to _ _ operate at full efficiency. Write Expansion for Bulletin HVG-140. Joint SPACE HEATING CONTROL No. 885 Automatic Radiator Valve--For exposed radiation. Small, neat, finely finished, adjust able to room temperature desired. Simply replace ordinary radiator valves with these Sylphon Automatic Regulators--no wiring, piping or auxiliary equipment are required. These valves answer the demand for an inexpensive means of providing accurate, dependable space temperature control in p-p rooms, sections or through out large buildings, new or ^ old. Similar type valves for Sylphon No. 885 concealed radiation--get Automatic Radi' Bulletin HVG-80. ator Valve No. 890 Electric Radiator Control Valve--For either exposed or concealed radiation. Similar in appearance and action to Sylphon Automatic Valves, but operated by an electric wall thermostat. The closing of the thermostat circuit ener gizes a low voltage electric heater coil surrounding a bulb containing a volatile liquid. This liquid expan sion causes pressure on a ' bellows in the valve head operating the valve. This provides radiator valve con trol from a remote location, permits regu lation of several radiators from a single thermostat, enables a time switch to be installed, if desired, offers effective zone control of large areas at a fraction of the cost of conventional motor-operated valve systems. Bulletin HVG-70. . No. 7 Temperature Control--A self- contained, self-powered regulator for con trolling unit heaters, wall or ceiling type radiators, heating coils in duct-type heating systems, etc. Quickly installed, holds tem peratures within close Sylphon No. 7 limits. Valve placed Temperature Control in steam line to one or {Self-operatint) a battery of heaters, thermostat mounted on wall or column. For use on regular heating pressures up to 15 lb. Similar regulators, Nos. 7-2 and 7-3 for 50 and 75 lb pressure and tem peratures up to 170 F. Bulletin HVG-50 1124 The Fulton Sylphon Company Controls and Instruments HEATING AND AIR CONDITIONING CONTROL Almost any type of heating, ventilating or air conditioning system can be advan tageously controlled wholly or in part by Sylphon Regulators. Basic advantages of Sylphon Controls are: Modulating--Maintains ideal conditions --not continually correcting too hot, too cold, too humid or too dry conditions. Compensating--Many Sylphon Regu lators offer compensating control, auto matically raising their low limit setting at a predetermined rate as outside tempera tures fall. Sensitive--Close operating temperature differentials. Quick response. Simple--in design. Rugged Construction--To give years of satisfactory service. Adaptable--Any one of many combina tions of Sylphon Instruments can be ar ranged to control any air conditioning sys tem and to provide exactly the conditions desired. Write for Bulletin SAC--820. The No. 928-C Regulator--Simple, compact yet highly sensitive. Suitable for modulating control of air temperatures in ducts. Bulb is constructed of numerous coils of copper tubing giving sensitivity to the slightest temperaturevariation. Packlessvalveeliminatesservice problem and makes this regulator ideal for installation in inaccessible locations. Suitable for steam pressures up to 15 lb; other types available for pressures up to 751b. The No. 928-ECC Sylphon Instrument--Room control and low-limit control in a single valve regulator for modulating control of ventilating systems. Main control from an electric room thermostat operating through the electric head "E" on the valve. Low-limit control by Bulb "A" located in discharge duct from the Instrument 9S&-ECC heater. Bulb "D", located in inlet side of the duct to the heater, compensates Bulb "A". Compensating thermostat can be furnished to raise low-limit setting at predeter mined rate with falling outside temperature. Suitable for steam pressures up to 15 lb. Sylphon No. 971 Differential Regulator--For con trolling room temperature on the cooling cycle, where chilled water or brine is used as cooling medium and where it is desired to have a gradual increase in room - temperature as outside temperature increases. This regulator is modulating in action, thereby affords better control over humidity than is procured when usual on- and-off type control is employed. Regulator 971 The Sylphon No. 889-C Control--A modulating, dual-function regulator for control of duct heating and ventilating systems--two independent valves in a single body. Adjustable Thermostat "A" governing Valve "E" functions to maintain room temperature from tempera Control 889-C ture of recirculated air. Adjustable Thermostat "B" acts as a low-limit ductstat controlling Valve "F" to maintain minimum discharge air temperature. Bulb "D" compensates Bulb "B" to maintain even discharge air temperature irrespective of demand. Compensated Therm ostat "B " can also be furnished to raise its setting at a predetermined rate with failing fresh air temperatures, if desired. Suitable for steam pressures up to 15 lb. . Sylphon No. 371 Positive Type Damper Motor--On-and-off control of dampers. Operation controlled by room thermostat, by hand- operated switch, by motor starting switch, etc. Ad vantages include: (a) motor returns to closed or safety position ir. event of current failure; (b) heat-motor bulb .and motor separate enhances convenience of installa tion; (c) damper motor lever adjustable; (d) positive, powerful operation. Damper Motor S71 1125 Controls and Instruments GENERALlcTTCONTROLS FACTORY BRANCHES: Atlanta - Boston Chicago Cleveland Dallas Denver Detroit Houston Kansas City New York Philadelphia Pittsburgh San Francisco Seattle DISTRIBUTORS IN PRINCIPAL CITIES HOME OFFICES AND FACTORY: 801 Allen Ave. Glendale 1, California AUTOMATIC TEMPERATURE--PRESSURE--FLOW CONTROLS THERMOSTATS Trimtherm provides ac curate, remote control of desired temperature. Streamlined, compact-- extends only in. from wall, yet sensitive to slightest temperature change (Differential 3^ F.) Chrome cover, natural ivory base. B-60 GAS ACTUATED PACKAGE SETS The Trimtherm MAGNETIC GAS VALVES ^ . ype ksb Versatile, two-wire, straight magnetic cur rent-failure valve. Pack less. Insures tight shut off indefinitely. Humless. Size range, 3^ in. to 6 in. I.P.S. . Operating pres sures up to 5 lb. Voltages and frequencies, A.C. or D.C. Quiet, positive, trouble-free. Available in explosion-proof housing. SLOW OPENING GAS VALVES Type B-65 For industrial and com mercial burners and furnaces. Adjustable opening time, 5 to 50 secs. Wide pressure range up to 5 lb. Size % in. to 6 in. I.P.S. Ample power for louvre control. Damper arm easily rotated. Packless. MAGNETIC VALVES Provides six times more power than ordinary solenoid valves. Con trols air, gas, water, light, heavy oils, steam. Positive opening, com plete shut-off, packless, hum-free. Available for Type K-10 any voltage, A.C. or D.C., in sizes up to 1 in. I.P.S., port sizes up to ^ in. K-20 Series is designed for applications where single needle port sizes provide sufficient flow capacity. W-3 Series are magnetic 3-way valves for controlling fluid to piston and diaphragm operators on valves, doors, gates, etc. Everything needed in a convenient pack age for remote gas control--:B-60 Valve, Trimtherm (with or without thermometer, or Timer Thermostat), Pilot Burner Gen erator, and 30-ft wire. No outside current required. Safe, quiet, dependable. Ap plicable to gas furnaces, floor furnaces, boilers, circulators, gas radiators. *hi-g MAGNETIC VALVES Designed for positive oper ation on aircraft, trucks, tractors, tanks, graders, ships, and other moving equipment. Handle all fluids, vapors and gases on anything that rolls, floats or flies at pressures up to 3000 lb or more. Packless, two-wire, current-failure type, available normally open, normally closed for intermittent or continuous duty. Trade Mark--"hi-g" indicates positive ability to function in any. position, regardless of vibration, change of motion or acceleration. .. REFRIGERANT CONTROLS Magnetic piloted, twowire, current failure, high pressure, packless. Han dle large capacities with minimum pressure drop and loss. Tight- shut-off. Operates on wide variety of fluids and gases. 1126 General Controls Controls and Instruments Type G-l-7 HYDRAMOTOR VALVES Simplify valve control instal lations. Two-wire, current failure, electric-hydraulic operation. Ample motordriven power, slow opening and closing movement. Oper ator drives against a spring in one direction; power failure or opening of circuit causes spring to operate in other direction. MANUAL RESET VALVES Type MR-1-2 Equipped with manually- reset electromagneticallyheld valve operator. Cur rent flowing to operator permits manual opening by turning valve wheel at side. Current failure releases operator allowing valve to close. Trip-free mechanism cannot be opened under un safe conditions. Once closed, valve is -re-opened manually because applying current-has no effect. - STRAINERS Type S-5-1 Actual tests prove impor tance of strainers in pro1 longing operating life and reducing leakage of flow controls. S-5 Series STRAINERS come in 8 types; meshes % in. diam. to 120-per-inch. THERMOVALVES Type MR-2 Manually-reset, electromagnetically-beld-open valve with cur rent generated by single couple subject to heat of pilot flame. Available % in. to 1y2 in. I.P.S. THERMOPILOTS Proven principles of oper ation insure dependa bility. Flame applied to thermpcouple maintains electrical contact, allowing electrical gas valve to open. When flame fails, Thermopilot opens circuit to main gas valve. Flex ible, . armored, asbestos- Type A-ioo covered cable detachable .. from relay. 2 or 3-wire control. Electrical rating, 2 amp., 24 volt; 1 amp., 115 volt; 0.5 amp., 230 volt. THERMAL EXPANSION VALVES Type V-200 provides un matched sensitivity and de pendability. Handies freon, methyl chloride, sulphur dioxide. Quickly removed orifice cartridges eliminate need for stocking several sizes for low tonnage in stallation. GAS FUEL GOVERNORS Throttle gas lines according to boiler pressure applied to diaphragm. Ball bearing thrust adjustment, ground and polished non-corrosive stems, low friction packing gland seal, multiple cali brated springs, high lift for maximum capacity. Suit able for butane, natural or manufactured gas. Avail able % in. to 3 in., I.P.S. Type V-25-1 RELAYS AND TRANSFORMERS Type RS-100 handles, single phase motor loads up to 1 hp or heating .loads up to 1.1 kw. Combines-double-break relay and integral transformer. - Normally open; large double-break contacts. Tworwire control circuit; maximum holding cur- rent0.4amps. Furnished with in. conduit con nections and low voltage Type RS-100 outlet. A.C. only. TANK THERMOSTATS Averages 6 to 10 degrees effective differential on water heater. Saves fuel by eliminating over heating due to large dif ferentials. Temperature range, 60 to 170 F. Also to 230 F. Type L-6I LOW PRESSURE GAS REGULATORS New V-300 Series are reliable, trouble-free valves with high capac ity, dose regulation, yet small and compact. Regulator sizes range from % to 2 in. I.P.S. Internal parts, cor rosion-resistant. Cast Tyi>e v~s0 iron regulator bodies, long life calibrated springs, properly fitted all-metal valves. GENERAL CONTROLS manufactures a complete line of Automatic Temperature, Flow and Pressure Controls. For complete specifications write for Catalog 52B. 1127 Controls and Instruments. Friez Instrument Division BENDIX AVIATION CORPORATION Towson, Baltimore 4, Maryland Manufacturers of Precision Recording and Measuring Instruments for over 70 years--now will manufacture a complete new line of Automatic Heating, Air-Conditioning and Refrigeration Controls and Accessories. HUMIDISTAT HUMIDITY INDICATOR Employs the-ever reliable dual hair ele ment to operate electrical contacts. The ideal control for residential, commercial or industrial humidifying or dehumidifying equipment.. Insertion type, not shown, also available in several models. THERMOSTAT A complete range of highly sensitive and thoroughly dependable thermostats. PSYCHROMETER, Hand Aspirated Type Range: 10-95 per cent Relative Humidity. Employs the Friez dual hair element to provide high sensitivity and best accuracy. Includes thermometer as illustrated. RECORDER, Portable No whirling. Offers con trolled ventilation, ' continu ous observation-of thermom eters with increased reading accuracy, and elimination of thermometer breakage so often encountered in the sling type. Complete instrument with psychrometer slide rule, folds into a protected pocket assembly. For surveys, studies, and tests of humidity and temperature. A third pen (optional) provides an on-off record of associated electrical equipment under test. Provides inked record on 3 x 5 cards, suitable for filing. Write for descriptive literature stating your requirements. 1128 Controls arid Instruments Henry Valve Company 3260 W. Grand Ave., Chicago 51, 111. PACKLESS AND PACKED VALVES DRYERS FOR REFRIGERATION AND AIR CONDITIONING STRAINERS AMMONIA VALVES FORGED STEEL VALVES AND FITTINGS FOR OIL, STEAM AND OTHER FLUIDS. Balanced-Action Diaphragm Packless Valves VALUE OF BALANCED-ACTION Regardless of operating conditions or the dif ferential in the pressure above and belowthe valve seat, balanced-action assures positive and instantaneous opening. The balancing action is really the equalizing of the pressures on the two sides of the valve seat at the instant of opening. This is ac complished by a channel in the axis of the valve stem. When the valve is closed, the upper port of this channel is sealed by the diaphragm assembly itself. At the instant of opening, the pressure above the seat forces the diaphragm assembly upward, ex posing the upper port of the balancing channel. The pressure is released through the channel to the region below the seat, equalizing the pressures, thus assuring posi tive opening. A spring-tensioned ball check seals the channel for diaphragm inspection. Other Important Features are: Oval hand wheel, ports-in-line. non-rotating bearing plate to protect diaphragm from rotating friction of stem, and use of multiple puncture and fracture-proof diaphragms designed to resist wear and corrosion. Available in a complete range of sizes with flare and solder connections. WING CAP VALVES Designed especially for Freon and Methyl Chloride. Have pat ented rotating self aligning stem disc. Special resilient pack ing. May be repacked underpressure. Wing cap can be inverted and socket used for operating valve. Made of non-ferrous alloy to meet government specifications. Solder connections machined directly in valve body. HENRY STRAINERS There is a size and type of Henry Strainer for every installation requirement. Type 895 "Y" Strainer With solder fittings for use with copper pipe. Welded Steel con struction. Negligible pressure drop. Screen can be taken out for- cleaning without removing strainer from line. Very large screen area. Light weight. Baffle prevents heavy particles injuring screen. ABSO-DRY PRESSURE SEALED DRYERS For Refrigeration and Air Conditioning The exclusive Henry vacuum process first removes every trace of moisture, then the dryer is charged with dehydrated air. Loosening a seal cap prior to installation produces hissing sound, a guarantee of original factory dryness and freedom from leaks. Other Features of Henry Dryers-- Perforated Dispersion lube is connected to inlet port and exposes entire volume of dehydrant to penetraa tion by refrigerant. Minimum pressure drop. No channelling. Compression Spring maintains uniform tension on dehydrant at all times and compensates for changes in volume. Soldered or Flanged Shells-- models are available with either soldered cap or flanged end shells. Flange is distortion-proof. Shells not exceeding 5H in- in length are drawn in dies, so that they have only one joint. TWO DEHYDRANTS--Choice of two de hydrants; Activated Alumina or Silica gel. Type 757 Cartridge Dehydrator Flanged shell dehydrator with replaceable cartridge. Type 743 RefiUable Dehydrator Screen tube assembly soldered to outlet connection. With dispersion tube. Type 712 Dehydrator Soldered brass shell with dispersion tube. APPROVED FOR ARMY AND NAVY USE 1129 Controls and Instruments Johnson Service Company AUTOMATIC TEMPERATURE AND AIR CONDITIONING CONTROL General Offices and Factory Milwaukee, Wis. Branch Offices in all Large Cities - Johnson Temperature Regulating Co. of Canada. Ltd., 113 Simcoe St., Toronto, Ont. Halifax, N. S. Montreal, Que. Winnipeg, Man. Calgary, Alta. Vancouver, B. C. PRODUCTS AND SERVICES Manufacturers, Engineers, and Contractors--For automatic temperature and humidity control systems applied to all types of heating, cooling, ventilating, and air conditioning installations. Space Control--Automatic control of room temperatures and humidities, applied to radiators, unit ventilators, unit heaters, and heat delivery ducts. Johnson "Duo-Stats" to maintain the proper relationship between outdoor and heating system temperatures for groups of radiators, or "heating zones." A complete line of devices for automatic control of air conditioning systems, heating, cooling, humidifying, dehumidifying. . Process Control--Automatic temperature and humidity control devices for manufacturing and industrial processing, applied to tanks, dryers, vats, kettles, curing rooms, coolers, kilns, etc. Nation-wide Service--Johnson sales engineers, technicians, and Single Room Thermostat trained installation men are available at all branch offices. None of the men in the nation-wide Johnson organization are agents, jobbers,. or part-time representatives. All are salaried employees, devoting their entire efforts to the interests of the Johnson Service Company and its customers. . Send for Bulletins describing the detailed characteristics of any of the Johnson devices. . JOHNSON THERMOSTATS Room Thermostats--Intermediate (gradual) or positive (snap) action, maintaining temperatures accurately within one degree above or below point of setting. " Dual" (two-temperature) and "Summer- Winter" types, as well as standard instruments. Various types of covers allow wide selection of adjusting features, guards, and method Dual Room Thermostat of mounting. Red-reading thermometers with magnifying tube attached to each cover. Insertion and Immersion Thermostats--Control temperatures in ducts, tanks, and similar locations. High grade insertion or immersion thermometers for mounting adjacent to the thermostats, including the distinctive Johnson insertion thermometer, with red-reading mercury column in heavy lens glass tube and 9-in. scale with patented adjust able tilting feature. Also, separable socket liquid thermometers. Extended Tube Thermostats-^--Liquid-filled or vapor tension type, to measure temperatures at a point remote from the location of the operating mechanism. Various types of bulbs. Connecting tubing up to 50 ft in length for vapor tension. N Special Thermostats--For applications encountered in industrial control, including the "Record-O-Stat," combination extended-tube temperature controller and recorder. Full 10-in. chart. Single or Room Humidostat duplex type, the latter controlling and recording both wet and dry bulb temperatures. . Remotely Adjusted Thermostats--A distinctive Johnson feature, applied to various types of instruments where readjustment must be accomplished from a remote point, such as another thermostat or a manual switch. Johnson Sensitivity Adjustment--An important development in automatic temperature and humidity control for air conditioning. A unique and convenient means of adjusting the sensitivity of Johnson thermostats and humidostats, on the job, balancing "time-lag" with respect to the capacity of conditioning apparatus. "Hunting" and temperature fluctuation prevented. Available on all Johnson gradual . action insertion and immersion thermostats, insertion humidostats, and certain room type thermostats and humidostats. "Sylphon'' Radiator Valve . 1130 Johnson Service Company Controls and Instruments JOHNSON HUMIDITY CONTROL Johnson Humidostats--Automatically control the supply of moisture delivered by a humidifier or by other means, maintaining a constant percentage of relative humidity. Available in both room and insertion patterns and with various types of elements as determined by requirements, the most sensitive controlling within 1 per cent at relative humidities as high as 95 per cent at 100 F. Humidostatic elements are wood-strip, human hair, animal'membrane, or other suitable substances as selected. Johnson Humidifiers--"Steam grid" type (perforated pipe supplied with low pressure steam) or pan type with copper . evaporating pan, brass heating coils, and float control. Extended Tube Thermostat JOHNSON VALVES . Johnson Diaphragm Valves--Simple and rugged. Seamless metal bellows and heavy spring operate the valve stem. Avail able, if desired, with diaphragms of special molded rubber, resistant to aging, heat deterioration and oxidation. No complicated moving parts. Made in all standard sizes and patterns. Direct acting (normally open) or reverse acting (normally closed). Also, three-way mixing and by-pass valves. For steam, water, brine, and freon. Johnson "Streamline'* Diaphragm Valves--Modulating discs and special internal construction, insure superior gradual control . . . Where maximum power is required for repositioning . at the slightest demand of controlling instruments, Johnson molded rubber diaphragm valves are fitted with Johnson's dependable pilot feature, for smooth gradual operation, inde pendent of friction and pressure variations. Remotely Adjusted Duct 7'hermostot Modulating Attachment for Expansion Valves JOHNSON DAMPERS AND SWITCHES Standard Johnson Dampers--Steel blades in flat steel frames with adequate bracing to form a rigid assembly. Finished in two coats of black lacquer. Special corrosion-resisting finishes on order. Angle iron frames optional. Special Dampers-- Galvanized iron, monel metal, aluminum, copper, rust-resisting steel, etc. Brass pins in steel bearings or ball bearings. Johnson Damper Motors--In principle, similar to valves. Seamless metal or specially molded rubber diaphragm operates damper through suitable linkage. Various types of brackets. Distinctive Johnson "Piston-type" damper motors afford long ` travel at full power, a feature not found in other such devices. With or without pilot mechanism, as described above under "Valves." Johnson Pneumatic Switches--Various patterns for oper ation of dampers and for placing thermostats and other devices in and out of service, as required, from remote points. Standard; switchboards are oiled slate. Ebony asbestos, polished oak, and.' genuine or imitation marble on order. v-*,,. Rubber Diaphragm Coil Valve Controls and Instruments Illinois Testing Laboratories, Inc. 422 North LaSalle Street, Chicago, Illinois d'faun. Manufacturers of ALNOR Thermometers, Pyrometers, Temperature Controllers, and Air Velocity Meters The Alnor. Velometer is an instantaneous, direct-reading air velocity meter designed for convenient, rapid deter mination of air velocities in air conditioning, heating and ventilating, and exhaust systems.' It gives instantaneous direct readings in feet per minute, without timing, calcu lations, or reference to tables or charts. Low range air velocity readings are taken by holding the Velometer in the air stream. High range readings are obtained by the use of tube connected special jets, available in 17 types providing for convenient use in any location. Accurate information on performance of equipment, duct systems, etc., can be obtained with a few moments inspection with the Velometer. It can be effectively used to locate drafts and leaks around windows and doors, or in duct systems. The Alnor Velometer is built in several standard ranges from 20 fpm to 6000 fpm, and up to 3 in. static or total pressure. Special ranges available as low as 10 fpm and up to 25,000 fpm velocity and 20 in. pressure. Alnor Electrical Resistance Thermometers, available in single and multi-point types, are ideally suited to air con ditioning, heating and refrigeration installations. Ther mobulbs may be located at any point up to 1000 ft from the instrument. Indicating thermometers can be furnished with capacities up to 14 points. Standard types include round, rectangular, horizontal edgewise, and portable thermometers. Instruments may be installed in office or engine room and thermobulbs located at any desired point in the building or on the roof. Accurate temperature measurements at the remote locations are obtained merely by moving the selector switch. . Alnor Pyrometers include a wide range of portable and wall mounting types, both single and multi-point instru ments, for a variety of industrial temperature measurements. Temperature readings of molten metals, industrial furnaces, and similar equipment, and temperatures of surfaces, either metallic or non-metallic, moving or stationary, are readily obtained with standard Alnor Pyrometers. Bulletins describing Alnor instruments and accessory equipment will be sent upon request. 1132 Controls and Instruments Leeds & Northrup Company 4941 Stenton Avenue, Philadelphia 44, Pa. BOSTON Buffalo Chicago Cincinnati Cleveland Detroit Hartford Branch Offices: Houston Los Angeles New York Pittsburgh St. Louis San Francisco Tulsa RUGGED, ELECTRICAL-BALANCE INSTRUMENTS Model S Mieromax Recorder Recordi from 1 to 16 pointi on a tingle ttripchart. Extremely open record. Can alto tiynal or control. (About 1/I6th size)- Modd R Micromax Recorder Records 1 or i points on a round- chart, Rat extremely readable diaL Can alto ngnal or control. (About 1/tStk tut) Panel Indicator Hand-operated. Can be connected through teledor twitches to any number of print*. (About IflSth sue) ,, Electrical Thermometers for Air Conditioning Electrical Instruments for the . Steam Plant No method for measuring temperatures fits the specific needs of air conditioning as does the three-lead, null-type resistance thermometer method. It is independent of distance and disregards all temperatures except those right at points of measure ment. Thermohms (electrical resistance thermometers) can be placed anywhere-- in rooms, air ducts or water lines. They are connected by simple electrical wiring to instruments at a central location. Instruments maybe: Micromax Recorders, Model S for-up to sixteen Thermohms, Model R, for related pairs such as wet and dry bulb; indicators with switches for any number of Thermohms; or indicating and recording combinations. Sound in principle, reliable in operation, instruments and Thermohms are highly responsive, yet ruggedly built. A com plete system is economical to install, regardless of distances. It is easy to oper ate; requires little maintenance. ThermoHms and instruments are interchangeable; can be replaced without disturbing wiring or returning anything to the factory. Facts needed to run a modern heating plant so as to save fuel, protect equipment, and operate efficiently at varying loads are provided reliably by rugged L&N instru ments. Readings can be indicated, re corded, or both. Recorders can be equip ped to operate signals or alarms; in some cases to control automatically. . Micromax Model S provides a per manent record on one wide-scale chart of conditions at from 1 to 16 points. Micro max Model R concentrates on conditions at one point, provides a permanent record, has a giant indicating dial. A Panel Indicator provides intermittent checks on conditions at one or several points. L&N equipments for the steam plant are described in the following publications: Metermax Combustion Control (for large plants; central stations) Cat. N-01M-163. L&N Combustion Control, Type P (for in dustrial and smaller-stations) Cat. N-01P-163. Micromax Temperature Instruments (for the Steam Plant) Cat. N-33-163. Mieromax Temperature Instruments (for Superheated Steam) Cat. N-33-163(1). L&N Resistance Thermometers make it possible to operate efficiently; to maintain comfort or correct process atmosphere con stantly ... so that maximum return is realized on the conditioning investment. Ask for Catalog N-33C. Centrimax Flowmeters, Cat. N-28-1G0. Mieromax CO* Recorders Cat. N-91-163. Mieromax Smoke Density Recorders, Cat. N-93-163. ' Mieromax Condensate Purity Instruments (for the Steam Plant) Cat. N-95-163. Jri Ad N-225(2) 1133 Controls and Instruments The Mercoid Corporation Main Office and Factory, 4201 Bblmont Avenue, Chicago 41, Illinois New York Office, 205 East 42nd St. Philadelphia Office, 3137 N. Broad St. AUTOMATIC CONTROLS FOR HEATING, AIR CONDITIONING, REFRIGERATION AND VARIOUS INDUSTRIAL APPLICATIONS THE ONLY 100% MERCURY SWITCH EQUIPPED CONTROLS The distinguishing feature of Mercoid Controls is the exclusive use of Mercoid hermetically sealed mercury switches. These switches are not subject to dust, dirt or corrosion, thereby assuring better performance and longer control life. The items shown below are but a few miscel laneous items. -See Catalog No. 700 for complete line. MERCOID THERMOSTATS Mercoid low voltage-room thermostats are known by their trade dame Sensatherm. They operate on a total dif ferential of 1 degree F. Type H is the regular popular room thermostat. Type DNH is a hand wound day and night FOR PRESSURE & TEMPERATURE Sensatherm. Type HBH is the These controls have a wide range of applica tions. They are. noted for their accuracy and dependable performance. The outside double ad two-stage type for control of high-low oil or *gas burners. Recommended also for stokers. Type 865 is designed for direct line voltage applications recommended for unit heaters, air conditioning, etc. justment feature and visible dial eliminate alt LOW WATER CONTROLS guesswork when setting Available also as a the operating range. combined low water and pressure control to VISAFLAME prevent firing into a The Mechanical Eye Actuated by Light. A positive safety con trol system for domestic and in dustrial oil burners. Operates direct from the light of the dame instead of from heat in the stack. Tried and proven to be the most' practical method for dependable oil burner performance. (See next page.) dry boiler or building up excess pressure. There are a number of different types for various requirements.' . The illustration shows' type provided with quick-hook-up fittings designed in accordance with the A.S.M.E. code. OIL BURNER SAFETY CONTROLS Type JMI provides posi tive protection against flame or ignition failure on intermittent ignition oil burners. This control in sures having ignition cir cuit closed before every * starting operation of burner. Type JM is used for constant ignition burners. STOKER TIMER CONTROLS Type TV2 Stok-A-Timer combines a Mercoid Transformer-Relay and a synchronous motor timer mechanism for maintain ing the stoker fire during periods when thermostat is not calling for heat. Interval adjustment can be set for \4. hour or 1 hour merely by moving a lever. 1134 The Mercoid Corporation Controls and Instruments MERCOID VISAFLAME CONTROL SYSTEM (Actuated by Light) FOR DOMESTIC AND INDUSTRIAL OIL BURNER APPLICATIONS HJ P If" ' J' J HI .M R IfX/\k \4 \: ' - \\_ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ ,, S '*==: . pi JS~rT~z \d ys's'jy------ o ---- r w The Visaflame is a departure from the usual oil burner control operation. Instead of havi'ng a safety control on the stack, actuated by the heat from combustion, the Visaflame is located within or adjacent to the oil burner where it uses the light of the flame as a means of actuating the control system. This permits a more direct and positive method for pro tection against flame failure, power failure, or low line voltage. The Visaflame System lends itself to streamline burner design as it can be built into the burner unit by the manufacturer, thereby making it possible to test the complete burner with safety device at the factory which also simplifies and reduces the cost of installation in the field. - .. MANNER OF OPERATION The Visaflame, when properly focused, closes its circuit in the presence of light and opens its circuit when the light is absent. The light of the flame passes through bulb "A" and is picked up by the concave reflector "B" which concentrates the light waves on the small bimetal coil "G." This bimetal coil is opaque and therefore transmutes the light waves into heat, which causes it to move the attached electrode "D" into the pool of mercury "E." The electric circuit is then closed between the fixed electrode "F" and the movable electrode "D." The outer bimetal coil "H" to which-the movable electrode is attached, compensates for varying, ambient temperatures. . .. The Visaflame is available for Intermittent Ignition or for Constant Ignition oil burners. Also for manually operated industrial burners. Adaptable to high-low flauie operation. ' 1135 Controls and Instruments Minneapolis-Honeywell Regulator Company 2958 Fourth Ave., So., Minneapolis 8, Minn. Cable Address: Minnreg. Minneapolis Electric or Pneumatic Control Systems for Heating, Ventilating, Air Conditioning BROWN INSTRUMENTS for Indicating, Recording, Controlling Factories: MINNEAPOLIS. MINN.. PHILADELPHIA. PA., WABASH. IND., CHICAGO. ILL. Branch Offices or Distributors are located in all principal dtics Albuquerque, N. M. Allentown, Pa. Atlanta, Ga. Baltimore, Md. Birmingham, Ala. Boston, Mass. Buffalo, N. Y. Butte. Montana Charlotte, N. C. Chicago, III. Cincinnati, Ohio Cleveland, Ohio Columbus, Ohio Dallas, Texas Davenport, Iowa Denver, Colo. Des Moines, Iowa Detroit, Mich. El Paso, Texas Faibhaven, Mass. Harrisburg, Pa, Hartford, Conn. Houston, Texas Indianapolis, Ind. Jackson. Mich. Kansas City, Mo, Los Angeles, Calif. Louisville, Kr. Lowell. Mass. Milwaukee, Wis. Minneapolis. Minn. New York, N. Y. ' Oklahoma Citt, Okla. Omaha, Neb. Peoria, III. - Philadelphia, Pa. Pittsburgh, Pa. So. Portland, Me. Portland, Ore. Providence, R. I. Richmond, Va. ' Rochester, N. Y. Sungebsland, N. Y. St. Louis, Mo. Salt Lake Citt, Utah San Francisco, Cal. Seattle, Wash. Spokane, Wash. Springfield, Mass. Stracuse. N. Y. Toledo, Ohio Tulsa, Okla. Washington, D. C. Wichita, Kans. . Worcester, Mass. In Canada: Montreal, Toronto, Calgary, London In Europe: London, England; Stockholm, Sweden; Amsterdam, Holland AUTOMATIC CONTROLS FOR EVERY APPLICATION Minneapolis-Honeywell manufactures a complete line of electric, pneumatic, and self-contained controls and regulators for every type of heating, ventilating, and air conditioning installation. In addition, . the Brown Instrument Division of Minneapolis-Honeywell manu factures a complete line of indicators, recorders, and controllers for Industrial Process applications. Each of the branch offices of Minneapolis-Honeywell maintains a staff of experienced engineers who are qualified to give unbiased advice on any type of control application and to install and service control equipment of any type. They are prepared to assist in the writing of specifications and to furnish control layouts and cost estimates without charge. Lint Voltage Thermostat Minneapolis-Honeywell, with 55 years of experience in the control field, is the only company which is prepared to furnish every type of control, whether electric, pneumatic, or self-contained for any type of installation. This eli minates the necessity of purchasing controls from more than one company, which often results in split responsiblity and unsatisfactory results. J`Modutrol Valve" THE MODUTROL SYSTEM OF ELECTRIC CONTROL The Modutrol System designation is applied to any combination of Minneapolis-Honeywell Automatic Electric Controls or Selfcontained Automatic Valves used to govern the operation of air conditioning or heating systems other than the small domestic instal lations. A wide variety of both modulating and two position motors, controllers and valves are available thus making the Modutrol System extremely flexible as to the selection of control equipment to produce the desired results. 1136 MinneapoliS'HoneyWell Regulator Co. Controls and Instruments "Gradustat" Pneumatic Thermostat THE GRADUTROL SYSTEM OF PNEUMATIC CONTROL The Gradutrol System designation is applied to any combination of Minneapolis-Honeywell Automatic Pneu matic Controls used to govern the operation of air con ditioning or heating systems." Such features as infinite positioning with the Gradutrol Relay and accurate graduation of valve and damper motors makes the Gradutrol System a truly remarkable advance in pneu matic control of commercial air conditioning and space heating installations. ' " Crad-VValve" Pneumatic Control _ Valve . COMBINATION ELECTRIC AND PNEUMATIC SYSTEMS The outstanding advantages of both the electric Modu trol System and pneumatic Gradutrol System of control may hie combined in a single installation. Thus maximum flexibility and low installation cost are obtained. Minne- apoIis-Honeywell can offer either an electric or pneumatic system, or a combination of the two. This is your guaran tee of an unprejudiced recommendation. s BROWN INSTRUMENTS The extent to which air conditioning equipment is being used in office buildings, theatres) stores, industrial buildings, etc., has opened up a wide demand for indicating and recording resistance thermometers because the temp eratures throughout these air conditioning systems should be checked periodically in order to obtain the best results at minimum operating cost. To obtain uniform conditions from modern equipment, it is necessary that the engineer in charge of operation have a visual picture of actual conditions. "Grad-UMotor" Pneumatic Damper Motor Brown Resistance thermometers are available for indi cating, recording, and controlling service and are applicable to all types of air conditioning and space heating instal lations. In addition to Resistance Thermometers, The M-H- Brown Instrument Division manufactures: Thermometers Hygrometers Pressure Gauges Vacuum Gauges Potentiometer Pyrometers Flow Meters CO* Meters Tachometers Liquid Level Gauges Protectoglo System Bromn Air Operated, Controller Recorder RESPONSIBILITY FOR ENTIRE CONTROL SYSTEM Minneapolis-Honeywell Regulator Co. is equipped to assume the entire responsibility for any control installation, thereby eliminating the difficulties and misunderstandings .which division of responsibility may create. 1137 Controls and Instruments The Meriam Instrument Company 10984 Madison Avenue, Cleveland 2, Ohio Representatives in Principal Cities ' MANOMETERS, METERS AND CAUGES FOR ACCURATELY MEASURING PRESSURES, VACUUMS AND FLOWS OF LIQUIDS AND GASES U-TYPE MANOMETERS For measuring pressure, vacuum or differential from only a few ounces to many pounds. In the Clean Out design (patented) the Pyrex U-tube and housing can be discon nected from the head and cleaned without disconnecting the piping. Available in 8 sizes from 6 in. to 50 in. for pressures up to 100 lb per sq in. Gland Packed type available for 250 lb per sq in. Write for Bulletin 1. FLOW METERS The H-Type Flow Meter-- Illustrated at the left is a direct reading well type manometer for measuring the flows of liquids, gases and steam across calibrated plates inserted in the line. The single straight Pyrex glass tube is gland packed top and bottom. Over flow well prevents indicating fluid . from being blown into the line if the differential pres sure should exceed the meter's range. Plain or flush type mounting for line pressures up to 250 lb per sq in. Send for Bulletin 18. 6 In. Mercury Pressure Gauge MERCURY PRESSURE GAUGES ' For measuring low range air and gas pressures. Gauges are direct reading and so designed that the mercury can not be lost from the gauge either through spilling or over pressuring. Available in 3 and 6 in. sizes to measure 22 oz and 48 oz respectively. Unit scale gradu ations are in ounces. Each gauge is furnished complete with pet cock and necessary mercury. Write for Bulletin No. 3. WELL TYPE MANOMETERS For measuring pressure and vacuum, and differential directly from the scale, using water, red oil or mercury, without adding distances above and, below reference zero. Model A-203-- Furnished in wall, table and flush front mounting styles. Ranges 30 in. to 100 in. for pressures up to 250 lb per sq in. Model A-275-- Furnished in wall A-t76 mounting and flush Walt - front styles only. _ Mounting Well Type Manometers Ranges from 6 in. to 24 in. for pres sures up to 150 lb per sq in Send for Bulletin B. DRAFT GAUGES Single Tube Draft Gauge Model GP Draft Gauges take accurate readings of low pressures, vacuums and differentials in\fractional inches of water. Furnished in single tube, also in 2-tube and 3-tube models for taking multiple readings on the same gauge. Send for Bulletin No. 4- Pulsation Absorber GAUGE PULSATION ABSORBERS The Gauge Pulsation Ab sorber provides a simple, effec tive method of preventing "hammer" and pulsing flow in a line from affecting the ac curacy of gauge readings, and protects the gauge from damage. Send for Bulletin No. 2. 1138 Controls and Instruments Moeller Instrument Co. 132nd St. & 89th Ave., Richmond Hill 18, New York Representatives in Principal Cities . Manufacturers of Indicating and Recording Thermometers, Psychrometers, "U" Gauges, Mercury Vacuum Gauges, Mercury Barometers, Hydrometers, Engraved Stem Thermometers, etc. . MOELLER DIAL THERMOMETERS Mercury filled. Made in several sizes and in standard ranges from minus 40 to plus 1000 F* Either in the rigid connection or with flexible capillary tubing. All kinds of connections. INDUSTRIAL THERMOMETERS Red reading columns, in V shaped case with glass front in all forms, sizes, and connections. INDICATING AND RECORDING PSYCHROMETERS WRITE FOR CATALOGUE MOELLER RECORDING THERMOM ETERS Mercury filled, in chart ranges from minus 40 to plus 1000 F. Made in 10 in. and 12 in. uniform chart graduations. All kinds of connections. Square or round cases. \ AIR DUCT THERMOMETERS For hot .and cold air ducts, or designed for both . ;] cold and hot ducts. Made in several sizes. J Various stem lengths with union con . nection and flanges for insulated and noninsulated ducts. J - '. 1139 ! I Controls and Instruments The Palmer Company Main plant: 2506 Norwood Ave., Cincinnati (Norwood), Ohio . Canadian Factory: King and George Sts., Toronto Manufacturers and Originators--"Red-Reading-Mercury" Thermometers "RED-READING-MERCURY" Industrial Thermometers-- These mercury tubes willshow a bright RED color, visible at a great distance. The color is reflected and cannot fade. (Patented by Palmer). Thor oughly annealed and guaran teed permanently accurate. Costs no more. STRAIGHT, ANGLE, SIDE - ANGLE, RECLINING AND IN CLINING Case, OBLIQUE STEM, etc. 7, 9 and 12 in. case, with or without glass front. Standard 3H in. stem and longer lengths. Fittings: Fixed Thread, Union, Sepa rable-socket and Adjustable or Union Flange. All ranges up to 750 F or 400 C. For ranges up to 1000 F or 550 C, with plain mercury tube, borosilicate glass. Write for Catalog No. 200- F. 45 Deg Inclining Case AIR DUCT THERMOMETER with Red - Reading- Mercury'' 9 in. case, Flanged Union Connection, standard stem length extending into Air Duct 12 in. and 18 in. Range +30 and + 160 F. Easy to install. RECORDING THERMOMETERS Mercury Actu ated. 12 in. diecast aluminum case. Wrinkle or Satin finish. All parts are rust proof. Flexible armoured tubing and bulb of stain less-steel. Fit tings: Plain, Union, Separablesocket and adjust able or union flange. All ranges up to 1000 F or 550 C. Guaranteed extremely accurate and sensitive. Write for Cat. 46. WALL HYGROMETER and SLING PSYCHROMETER Wet and Dry bulb; Mercury tube, with .RED column. Chart furnished. Guar anteed sensitive and accurate. Sendfor Bulletin No. 600. DIAL THERMOMETER fn. case. Black rubber ized finish. Flexible armoured tubing and bulb of stainless-steel. Rust proof. Fittings: Plain, Union, Separable-socket and Adjustable or Union flange. All ranges up to 1000 F or 550 C. Guaranteed sensitive and accurate. Write for Cat. 45. POCKET THERMOMETERS For quick tests. Re liable and accurate. With RED column. -20 +120 F. 0 +220 F. LABORATORY THERMOMETERS Gla^s engraved mer cury tube; shows bright RED column ... so easy to see. With or without metal armour; Round or Lens glass; ranges to 750 F or 400 C. Plain mer cury tube borosilicate glass on ranges 1000 F or 550 C. Correctly annealed and guaranteed accurate. Write for Catalog No. S00-D. REPAIRS--To all makes of Industrial Mercury Thermometers, furnishing "RedReading-Mercury" tube, at no extra cost and replacing all worn or broken parts, making the thermometer as good as new. Guaranteed accurate. 1140 Controls and Instruments Penn Electric Switch Co. Goshen, Indiana Offices Atlanta; Boston. Newton. Mass.; Chicago; Dallas; Dayton; Detroit; Milwaukee; Moline, III.; New York; Philadelphia; St. Louis Export--13 East 40th St., New York 10, N. Y. Representatives--Garland-Affoltbr Engrg. Corp.. San Francisco, Los Angeles. Seattle. Portland; Specialty Sales Co.. Salt Lake City; Forslund Pump and Machinery Co.. Kansas City; Vincent Brass and Copper Co., Inc., Minneapolis; H. M. Olmstead, Denver In Canada--Powerlite Devices. Ltd., Penn Electric Switch Div., Toronto. Ont. Distributors and Jobbers in All Principal Cities Automatic Controls for Heating, Refrigeration, Air Conditioning, Engines, Pumps and Air Compressors Oil Burner Stack Switches HEATING CONTROLS The Penn line of controls includes models for every type of heating service on steam, vapor, hot water or warm air systems whether gas, oil or coal fired. In this complete line there are: Low and line voltage Room Thermostats-- Stoker Timers--Oil Burner Stack Switches-- Hot Water and Warm Air Temperature Controls --Vapor Controls--Steam Pressure Controls-- Relays--Humidistats--Day-Nite Tern Clocks-- Damper Motor Controls--Boiler Water Feeders --Boiler Water Level Controls--and Solenoid Valves. Condensed description and specifica tions are given in Bulletin 1508-K. Write for your free copy. . REFRIGERATION CONTROLS Whatever your, need may be in refrigeration controls--choose the exact type to fit the job from Penn's complete line of automatic controls. Pressure and temperature controls are available with or without calibrated adjustments for single phase or polyphase service. Also available are: Cooling Room Thermostats--Humidistats --Relays--Solenoid Valves--and Water Regu lating Valves. All of these controls are described and illustrated in condensed Bulletin 1487-M. Write for your free copy. Write for catalog on Penn Controls to cover your particular applications. Temperature Controls 1141 Dual Pressure Controls Controls and Instruments The Powers Regulator Co. Over 50 Years of Temperature and Humidity Control--Offices in 47 Cities New York 17. N. Y.. 231 East 46th St.--Chicago 14, 2719 Greenview Ave.--Los Angeles 5.1808 W. Eighth St.-- Boston 15. 125 St. Botoiph St.--Philadelphia 32,2240 N. Broad St.--Greensboro, Jefferson-Stand ard Bldg.--Atlanta 3. Bona Allen Bldg. __Cleveland 13, 2012 West 2Stb St.--Kan- Detroit 2. Boulevard Bldg.--Cincinnati ^t'f^ sas City 6.409 East 13th St.--Seattle 4. 2, American Bldg.--New Orleans 12. Bal 2438 Bran- ter Bldg.--St. Louis 3, 272G Locust St. A very complete line of Temperature, Humidity, Pres sure -- indicating, controlling, and recording regulators -- for heating and air conditioning systems, industrial processes and all types of hot water heaters. pnniFRi;suf-ortiiuo f| i) itcsuim mi ommo (i pniiiFRs Controls and Instruments Spence Engineering Company, Inc. 28 Grant Street, Walden, N. Y. SPENCE METAL DIAPHRAGM "DEAD END" REGULATORS Advantages of Spence Regulators Dead-end Shutoff--Spence Regulators are guaranteed to hold a dead-end. Single Seat--Spence design makes possible a balanced single seat even in large sizes. Metal Diaphragms--Under normal conditions never require replacement. Accurate Regulation--Regardless of fluctuations in either load or initial pressure. SEGO Metal--Guaranteed to resist the wiredrawing action of steam. Interchangeable Pilots--Any type of pilot will fit any ske main valve. Accessibility--Pilot is connected to main valve with unions. No Stuffing Boxes--All main valves and most pilots are packless. . Spence Weather Compensator and Orifice Zone Control System This simple, dependable Control, when installed on a properly de- signed orificed heating system, will show a substantial degree-day steam saving, at a low maintenance cost. The delivery pressure of the Regulator is automatically adjusted in direct proportion to the building heat losses. In other words, as the . losses become greater, steam pres sure on the system is automatically increased. Any number of zones can be con trolled by one automatic Signatrol, automatic Wind Loss Compensator (Anemometer), Time Switch and Master Control Panel equipped with Manual and Automatic Dials for each zone. In this way each zone can be set individually -and at the same time be under the Master Control. Over 50 years of experience in furnishing and installing temperature and humidity control for every conceivable purpose in all types of build ings have given us a wealth of experience from which you can draw in selecting the proper type of control for any purpose. Catalogs and Bulletins describing any or all of our productsfurnished upon request. Phone or u:rite our nearest office. See your phone directory. 1142 Pressure Regulator-- Type ED Designed to regulate a steady or varying initial pressure so as to maintain a constant, adjustable, de livery pressure. Applica ble to heating systems, power plant operations, or manufacturing processes. Combined Temperature and Pressure Regulator . --Type ETD Self-contained, pilot oper ated, dead-end. Designed to control flow of fluid to a heating or cooling element, so as to maintain a constant, adjustable temperature, and protect the element against excessive pressure. Electrically Operated Valve--Type EM _ Can be opened or closed independently by an elec trical switch. - Type ET--Same as ETD except pressure control is omitted. Order a SPENCE Regula tor for 40 days* free trial. Fall-O-Matic Universal Pipe Intersection Cutter. 1143 Controls and Instruments Hxuflor Irutcwmmt Gymp/mUd Rochester, N. Y., U. S. A. IN CANADA--Taylor Instrument Companies op Canada, Ltd., Toronto NEW YORK LOS ANGELES ST. LOUIS CHICAGO BOSTON PITTSBURGH CLEVELAND BALTIMORE SAN FRANCISCO CINCINNATI TULSA PHILADELPHIA Mamifadmlnt Dislribtdors in Greai Britain, Short & Mesmn, Lid. London DETROIT ATLANTA MINNEAPOLIS WILMINGTON Taylor Instruments for Indicating, Recording and Controlling Temperature, Pressure, Humidity, Flow and Liquid Level Taylor Industrial Thermom eters--with new "BINOC" Tubing--Includes many styles and scale ranges with bulbs for every application. These ther mometers contain a new and radical development of tremen dous importance--" BINOC" Tubing. This newly designed and optically correct glass tubing assures an ease of reading that has been generally lacking in industrial thermometers. "BINOC" Tub-, ing more than doubles the an gle of vision within which readings can be made. Because of the patented Triple-lens construction ' its broad mercury column can be read easily and accurately with both eyes. Bore reflection is absent. Taylor "BINOC" Pocket Test Thermometer--Ideal for frequent testing of important temperatures. Taylor patented "BINOC" Tubing eliminates juggling and guesswork. High accuracy--Easier.-to Read. The New Taylor "Fulscope" Recording Controller--An air-operated controller thajt gives practically any character of process control regardless of time lag in apparatus. Available for controlling temperature, pressure, humidity, rate of flow, liquid level. Wfiejre extreme load changes or ' badly balanced operating condi tions exist, preci sion control can be maintained by the automatic reset feature. For applications where a record is. not needed, Taylor supplies an Indicating "Fulscope" Con troller. , Taylor Biram's Anemom eter--Ideal for measuring air velocities with the fan revolutions indicated on the dial. Various models for a wide range of air speeds and registration limits. Taylor Re cording Hy grometer-- Records both wet- and drybulb tempera tures on the same chart in different color ed inks, mak ing comparison , very easy. Type shown has motordriven fan for conditioned rooms or pass ages where circulation is poor. Furnished without fan for installations where circula tion across bulb is good. Taylor Sling Psychrometer--The advantage of this form of Wet- and Dry-Bulb Hygrometer over the stationary form is the facility with which tests can be made and the accuracy of the readings obtainable, as the whirling bulbs are sub jected to perfect circulation. Two accurate etched stem thermometers are mounted on a die-cast frame, with the bulb of one covered with a wick to be moistened. These thermometers have scales of 20 to 120 degree F, graduated in ^-deg divisions. A copper case protects the tubes when not in use. Taylor also offers a complete line of tbe famous Taylor Recording and Dial Thermometers, Self-Acting and Type "P" Controllers, the 10-BG Hygrome ter and many types of Humidiguides. 1144 Controls and Instruments Tenney Engineering, Inc. 26 Avenue B Newark 5, New Jersey Telephone Bigelow 8-3905 . Manufacturers of Automatic Temperature, Humidity and Pressure Control Equipment - New TENNEY . Thermostatic Expansion VALVE HALF ACTUAL SIZE Model TS-1 TEXXEY Thermostatic Expansion Valve Has no feeler bulb. Unaffected by ambient temperature, entering warm air or warm suction lines. Responds instantly to changes in suction vapor conditions. Special power element in the Valve design facilitates complete closing above a definite evaporative pressure. Design assures positive action--no sticking or binding. Push pin packing not required. Valve can operate in any position. Outstanding features stamp it as first forward improvement in expansion valve design in 20 years. Particularly adaptable to modern evaporators with forced air, small tubes, short passes and distributor header com binations. Ideal for small evaporators or modern close coupled coil and machine combinations. TENNEY Feather Fin Coils for COOLING and HEATING DIRECT EXPANSION STEAM HEATING WATER COOLING and HEATING Adequately meets modern demand for equipment that gives high operating perform ance and efficiency. Low air resistance. Sim plified component parts. Ratio of extended fin surface carefully engineered to provide best operating results. Easy to mount and install. All joints copper welded. Design embodies distributing header refinements. Send for New Valve Bulletin or Feather Fin Coils Catalog, prices and discounts. 1145 . Controls and Instruments White-Rodgers Electric Company 1293 Cass Avenue, St.Louis, Mo. Distributors in Principal Cities HYDRAULIC-ACTION CONTROLS Hydraulic*Action temperature controls combine the powerful uniform expansion and contraction of a solid liquid charged stainless steel diaphragm with mechanical simplicity to provide accuracy and dependability at all times. Take advantage of Hydraulic*Action on your next installation. Specify White-Rodgers Controls. The latest condensed control catalog is awaiting your request. Write for it today! . Line voltage Ther mostat for Unit Heater- and Air Conditioning In stallations. Single speed fan control-cover re moved showing visible dial. 8 EXCLUSIVE FEATURES OF WHITE-RODGERS HYDRAULIC- ACTION TEMPERATURE CONTROLS Dual Immersion Control--Limit- Circulator or Summer-Winter service, i 1. May be mounted at any angle or position, above, below or on level with control point. ' 2. Hydraulic-Action Principle incor porating solid-liquid filled bulb and capillary provides expansion force com parable to that of a metal bar. 3. Diaphragm motion uniform per de gree of temperature change. 4. Power of solid-liquid charge permits unusually sturdy switch construction resulting in positive contact closure. 5. Heavier, longer-wearing parts are possible because of unlimited power. Solenoid Gas Valve -- High plunger torque and . silent operation. 6. Dials are evenly and accurately cali brated over their entire range because of straight-line expansion. 7. Controls with remote bulb and capillary are not sensitive to change in room temperature. Accuracy of control is not affected by temperature changes in surrounding area. . 8. Not affected by atmospheric pres sure. Works accurately at sea level or in. the stratosphere without compen sation or adjustment. Diaphragm Gas Valve with puff bleed and built-in me chanical limit control. 1146 Low Voltage Room Thermostat--an ticipating type. Ex plosion-Proof Thermostat for hazardous locations --remote type. Steam Pressure Control--for safety limit service. ' International Heating & Ventilating Exposition THE AIR CONDITIONING EXPOSITION Permanent Address--Grand Central Palace, New York 17, N. Y. EXPOSITIONS HELD The first in Philadelphia, 1930. The second in Cleveland, 1932. The third in New York, 1934. The fourth in Chicago,-1936. The fifth in New York, 1938. The sixth in Cleveland, 1940. SEVENTH EXPOSITION TO BE HELD IN CLEVELAND The first post-war Heating and Venti lating Exposition will be held in Cleveland at Lakeside Hall, January 27 to 31, 1947. This will be the first, of a new series, now scheduled on an annual basis. Response to the initial announcement indicates that manufacturers have a keen interest in exhibiting their newest products of re search and development. There has developed a tremendous pentup demand for new equipment that will be a challenge to the industry__.The manner in which you meet this opportunity will be a guide to your future progress. As in the past, the Exposition will be ready to help you by offering a timely, quick and effective means of renewing old contacts, developing new ones, and actually demon strating your products. - These expositions have been and will be held coin cident with the Annual meetings of the American Society of Heating and Ventilating Engineers and are directed by the International Exposition Company, under the auspices of the A.S.H.V.E. EXHIBITORS - Comprise leading firms, in each phase of the industry; number has varied from 150 to 327 exhibitors.-' tioning equipment, ventilators (room and industrial types), unit heaters, etc. 7. The Air Conditioning Group: Equipment which circulates and filters the air, in summer dehumidifies and cools; in winter heats and humidifies, and does all these in proper season for complete, all year-round air condi tioning. 8. The Control Group: . Instruments of precision for indicating, controlling or recording temperature, pressure, volume, time, flow, draft or any other function to be measured. 9. The Refrigerating Group: Compressors, condensers, cooling ap- . paratus, contingent apparatus and refrigerants. 10. The Central Heating Group: Apparatus and materials especially designed or adapted to the uses of central heating and central heating station supplies. 11. The Insulating Group: Structural- insulators (refractory and cellulose materials), asbestos, mag - nesia clays and combinations thereoi, pipe and conduit covering, etc., weather-stripping, etc. 12. The Miscellaneous Group: . Electric Heaters, boiler and pipe re pair alloys, liquids and compounds, tools of all kinds, and equipment not specifically included in the above groups, but related thereto. 13. The Machinery and General Equipment Group. 14. Books and Publications. . VISITOR ATTENDANCE EXHIBITS These-range from and comprise all the types of articles discussed or advertised in this copy of The A.S.H.V.E. Guide. 1. The Combustion Group: Furnaces, burners (coal, oil and gas), - grates, stokers, boilers, radiators (vari ous types), refractories and auxiliaries. 2. The Oil Burner Group. 3. The Hydraulic Group: Water feeders, water heaters, pumps, traps, valves, piping, fittings, expan sion joints,, pipe hangers, etc. 4. The Steam Heating Group: Vapor heating and steam specialties. 5. The Hot Water Heating Group. 6. The A!r Group: Warm Air furnaces and stoves, regis ters and grilles, cooling towers, air filters, motors, fans, blowers, condi Attendance is by invitation and registra tion only, thereby presenting a selected audience. Included are contractors, deal ers,'jobbers, supply houses, home owners, industrial users, professional and service organizations, public utilities, real estate management concerns, etc. A detailed . analysis of registered attendance is avail able on request. In 1940 at Cleveland, there were 20,652 registered visitors. _ Industrial Expositions in America lead the expositions of the world in style, business effectiveness, industrial influence and educational value. This Exposition stands among the leaders in Industrial Expositions in America. It is an edu- , cationai institution which brings together the research developments and improve ments in equipment and materials for use in heating, ventilating and air conditioning all types of buildings. . . Heating Systems Radiators, Convectors American ^ ^taudavd Radiator ^ ^atutainj cftew^ouf CORPORATION `PtiUjwujh SEVERN BOILER FOR COAL (stoker or hand-fired), or OIL An exceptionally effi cient Boiler with many new features for con venience and economy. Ratings: Steam--350 to 780 sq ft. Water--560 to 1250 sq ft, installed radi ation. ARCOLINER FOR. COAL (stoker or hand-fired) or OIL An attractive Boiler of advanced design for heating smaller homes inexpensively and well. Ratings: Steam--180 to 460 sq ft, Water--290 to 740 sq ft, installed radi ation. EMPIRE GAS BOILER Designed by experts to burn gas efficiently, economically. All controls concealed. Ratings: Steam--163 to 1097 sq ft. Water-- 135 to 1755 sq ft, in stalled radiation. OAKMONT OIL BOILER A highly efficient moderate priced Boil er for small homes. Also supplied as com plete boiler-burner unit with Arcoflame Burner. Ratings: Steam-r-390 to 810 sq ft, Water--625 to 1295 sq ft, installed radiation. STANDARD GAS BOILER Basically the same as the Empire Gas Boil er shown above but without jacket. Ratings: Steam -- 400 to 11,905 sq ft, Water --135 to 19,048 sq ft, in stalled radiation. REDFLASH BOILERS--For All Fuels Economical heat for any size or kind of building. Attractive red jacket, fully in sulated. Ratings: Steam--770 to 9900 sq ft, Water--:1230 to 15,840 sq ft, installed radiation. WATER TUBE BOILERS Coal (Hand or stoker fired) or Oil For medium to large size buildings. Noted for efficient perfor mance and economy. Ratings: Steam--400 to 5,200 sq ft> Water --640 to 8,320 sq ft, installed radiation. MOHAWK Winter Air Conditioner Gas-Fired Provides com plete, automatic gas-fired Winter Air Conditioning in small, medium or large sized homes. Capaci ties range from' 43,200to216,000 Btu input per hour. 1148 hTTeat<ing Sc*yst,ems Oil Burners, Water Heaters, Accessories American Radiator <taitdaiid ^auitai ^^ CORPORATION <7>dUtwu)h YOU CAN FILL EVERY HEATING NEED FROM THIS COMPLETE LINE From American - Standard come Boilers of all types and sizes for Coal-stoker or handfired--Oil, or Gas, and a full line of Radiators, Convectors, Oil Burners, Domestic Water Heaters, and Accessories--all backed by the undivided responsibility of one of the world's largest manufacturers of Heating and Plumbing Equipment. ARCOFLAME OIL BURNERS The Model "C" Arcoflame has a capacity of up to 3 gal lons per hour. The Model "L" (not shown) from 3 to 7 gal lons per hour. Both embody unusual and highly efficient features. Sunrad Radiator SUN RAD RADIATOR Installed re cessed or free standing. Re quires no enclos ure. Two sizes: 20 in. high x 5 in. wide = 2 sq ft, and 23 in. x 7J4 in. = 3 sq ft. Arco Convector ARCO CONVECTOR For convection heating at its best. Available in four widths and in virtually any desired length. ARCO RADIATOR The modern, slim type radiator that occupies less space and gives more heat. It comes in four narrow widths and in four heights --19, 22, 25 and 32 inches. Arco Radiator ` EXCELSO INDIRECT WATER HEATER Provides domestic hot water during heating season with out care and expense of separate heater. Efficient and economical. 30 to 2500 gallon capacities. Excelso BUDGET GAS FIRED WATER HEATER Heats water automatically, stores it for instant use. Jacket finished in white enamel, black trim. Thrifty and dependable. Three sizes --20, 30, and 40 gallons. Budget Gas Fired ARCO MARINE CONVECTOR Especially designed for Marine use. Non-ferrous. Highly effi- No. fist Hurivent Valve (,for mains) S- No. SOO Multiport adjustable Valve (for radiators) Nc.999Arco Packless Steam Radiator " Valve 1149 Healing Systems Boners, steel Heating Systems Bailors THE BABCOCK Be WILCOX COMPANY 85 Liberty Street Manufacturers of New York 6, N. Y. . 3 The Bigelow Company 105 River Street, New.Haven 3, Connecticut MANUFACTURERS OF Water-Tube Boilers Chain-Grate Stokers FIRE TUBE BOILERS WATER TUBE BOILERS Oil Burners Seamless Steel Tubing and Pipe SALES REPRESENTATIVES IN PRINCIPAL CITIES Branch Offices and Representatives in all Principal Cities Catalog Furnished on Request Type H Stirling Boiler The Babcock & Wilcox Type H Stirling Boiler is a highly efficient unit built for moderate pressures at moderate prices.... and is designed to occupy minimum floor space and head room for the heating sur face required. This boiler is built in four classes and 36 sizes ranging from 691 to 6225 sq ft of heating surface, and can be designed for operation with any fuel and every method of firing. The moderate price is due only to the simplicity of design, efficient production methods and superior shop equipment. B&W Integral-Furnace Boiler, Type FF Type H SlirlinQ Boiler with Babcock <t Wilcox Chain-OnU Stoker Advantages of the Babcock & Wilcox Type H Stirling Boiler: Unusual steaming capacity for the floor space and head-room required. The choice of three locations for gas exit reduces cost of flues and breeching. Distribution baffles make effective all of the heating surface. ' Tube renewal is facilitated by correct tube spacing, and a tube removal door. The boiler is supported by a structural- steel framework entirely independent of the brickwork. - A complete table of sizes and dimensions will be sent upon request. Simply ask for Bulletin G-8-C. Many of the advantageous features in corporated in large B&W central-station boilers are now available for the first time in the B&W Integral-Furnace Boiler, Type FF, which is offered in sizes ranging from 1353 to 6506 sq ft heating surface. Distinguishing features include: A completely water-cooled furnace. The construction provides water cooling for front and rear (or bridge) walls, as well as side walls and roof. A furnace arrangement in which the primary combustion zone is followed by an open pass, thus making use of a principle of combustion that was first developed and used successfully in the B&W Open-Pass Boiler for central stations. This design insures mixing of the gases while at high temperatures, thereby aiding efficient and smokeless combustion. Cyclone Steam Separators, which pro vide dry steam at high boiler-water con centrations independently of normal varia tions in water level, and increase circula tion by eliminating steam from the water. These, with related features, result in a boiler that is outstanding for economy of fuel and maintenance and for ease of operation. Write for Bulletin G-34. 1150 BIGELOW SCOTCH TYPE HEATING BOILER A compact, self contained, highly ef ficient oil fired boiler that requires low head room and has low water line. All parts internally and externally are readily accessible. The boiler is of welded con struction and contains no water leg or stay-bolted surfaces. Built iri units with steam rating from 1,820 to 42,500 sq ft. BIGELOW TYPE F WATER TUBE BOILER Cut shows boiler equipped with spreader type stoker. The flexibility of design permits oil and other type stoker firing. Partial water wall surface is provided without extra headers, downcomers and circulating tubes. The Type F Steam Generating Unit is built in sizes ranging from 10,000 to 60,000 lb of steam per hour. BIGELOW TWO-PASS BOILER This boiler is designed to meet heating and power requirements, especially where space limitations prevail. The unit may be oil, stoker or hand, fired. The elimi nation of special brick shapes and staybolts reduces the cost of maintenance to a minimum. The Two-Pass boiler is built in standard sizes from 25 hp to 250 hp. 1151 Healing Systems Boilers, Radiators Valves, Tanks Irvington-on-Hudson, N. Y.--Zanesville, Ohio There*s a Burnham for Every Purpose--Catalogs Sent on Request Heating Systems Generator Unit, Steam Cyclotherm Corporation .90 Broad Street, New York 4, N. Y. --Ratings--1.25 sq (t per lineal foot. Tappings--% in. at bottom only of both end panels. Sections are 7 in. high, \ % in. thick--come in 12 and 24 in. lengths. Ratings--2.08 sq ft per lineal foot. Tap pings--% in. at bottom only of both end panels. Sections are T in. high, 2 in. thick and 24 in. long. Welded Steel Boiler--Capacities from 2500 to 35,000 sq ft for Steam and 4800 to 56.000 so ft for Water: Furnished for coal, oil or stoker firing. . 50 In. Twin-Section--4500 to 14,600 sq ft for Steam and 7200 to 23,360 sq ft for Water. . No. 1, 2, 3 and 36 in. Series--AH Fuel. 230 to 4920 sq ft Steam and . 370 to 7880 for Water. Burnham Radiant Radiator--;Two heights. 20 and 23 in. Burnham Slender ized Radiators (not shown) made in three to six tubes in all heights from 19 in. to 33 in. 1152 Yellow-Jacket Boiler (with extended Jacket)--All Fuel Convertible. 305 to 935 sq ft for Steam and 490 to 1495 sq ft for Water. Wide range of models in sizes from 5 to 200 hp with operating pressures from 15 to 200 psi. COMPACT--require minimum of floor and head space. SIMPLE TO INSTALL--No expensive stack- required, just connect fuel, water, electricity and steam outlet. Requires no special base. - COMPLETELY AUTOMATIC -- for efficient and economical operation. BURNS FUEL OIL or GAS--also available with combination oil and gas burner. . . AUTOMATIC CONTROLS 10 to 80 hp--"on and off" burner oper ation. 100 to 200 hp--uniform flame modula tion from 30 per cent load. Automatically protected against low water or flame failure and motor overloads. Firetube construction conforms to ASME Boiler Code requirements through out. Will meet boiler code requirements of any city, state or federal regulations. FUELS Up to 60 hp No. 3 oil or lighter. 80 to 200 hp No. 6 oil or lighter. Natural or manufactured gas. All sizes can be fired by natural or manufactured gas when equipped with combination burners, firing either oil or gas. ' . STANDARD EQUIPMENT INCLUDES: Steam valves Feed water injector . Condensate return and storage tank Make-up valve Motor-driven feed water pump Write, wire or phone for more complete information. CYCLOTHERM CORPORATION, 90 Broad Street, New York 4, N. Y. 1153 Heating Systems Boilers, Radiators, Furnaces, Heating Accessories, Stokers Crane Co. BOILERS, RADIATORS, FURNACES, VALVES, FITTINGS, PIPE, STEAM SPECIALTIES, PLUMBING AND HEATING MATERIALS General Offices: 836 South Michigan Avenue, Chicago 5, Illinois Nation-Wide Service Through Branches, Wholesalers. Plumbing and Heating-Contractors Crane Co. tleattng,, SCystVemsr * Boilers, Radiators, Furnaces, Heating Accessories, Stokers CRANE RADIATORS AND CONVECTORS COMPAC RADIATORS: Slender in line --modern in design-- constructed to give more heat and occupy less space. For free standing or recessed installation. CONVECTORS: For attractive instal lations that harmonize perfectly with"room decorations. Flush, extended or free standing types for new construction or. remodeling. RADIANT BASEBOARD HEATING Something new in heating! Radiant Baseboard Heating, developed by Crane Co. Steam and hot water are cir culated through the baseboard panel--no radiators or grills necessary. CRANE SIXTEEN Boiler These three boilers from the complete Crane line are now available. They offer new design and the latest in engineering achievement, assuring the utmost in heating comfort with even greater heating economy. ' And in the complete Crane line you will also find quality equipment to satisfy every heating requirement--steam, hot water or warm air-- for all fuels--hand fired or fully automatic boilers for homes, public buildings and industrial plants--warm air furnaces for all types of installations. The Crane line also includes oil burners, stokers, radiators, controls, water specialties and all necessary piping. . For complete information on Crane heating equipment, consult your Crane Branch or Crane Wholesaler. ' , 1154 V- CONTROLS The complete line of con trols includes thermostats, stack switches, limit switch es, aquastats, damper con trols--everything necessary for every heating system. WATER SPECIALTIES OIL BURNERS Crane hot water special Newly engineered. Crane ties are made to suit oil burners provide heat every installation. They- comfort at low fuel costs. include water heaters, Simplified design and sturdy circulators and flow con construction reduce mainte trol valves. nance to a minimum. 1155 Heating Systems Boilers, steel Fitzgibbons Boiler Company,Inc. Established 1886 . General Offices: Architects Bldg., 101 Park Avenue New York 17, N. Y. Manufactured at: OSWEGO, N. Y. Sales Branches in PrincIpal Cities' PRODUCTS--STEEL HEATING and POWER BOILERS for all fuels and all heating systems. Capacities to meet requirements of any building. Built and rated according to A.S.M.E. and S.B.I. Codes.--AIR CONDITIONERS for "Split-Systems" and for Direct-Fired installations in residences of all sizes. Member, Steel Boiler Institute and Indoor Climate Institute. FITZGIBBONS "D" TYPE Welded Steel Firebox Boilers --For 15 lb W.S.P. A.S.M.E. Built--S.B.I. Rated --Hartford Inspected The Fitzgibbons VDM Type Boiler is of all-welded steel con struction. Quick steaming, thorough combustion, long flue, travel,; high efficiency of heat transfer and fuel economies have won for the "D" Type a repu tation for superior heating ser vice with any fuel in any heating system. Ratings are in accord ance with the new standards of the Steel Boiler Institute.. Oil, Gas, Stoker, 2680 to 42,500 sq ft steam. Hand fired Goal, 2680 to 35,000 sq ft steam. FITZGIBBONS "PM SERIES Portable Riveted Firebox Boilers--100-150 lb W.S.P. A.S.M.E. Built--S.B.I. Rated--Hartford Inspected 1156 The riveted construction of the Fitzgibbons VP" series is designed for boil ers to be operated up to 150 lb w.s.p. This boiler is being used in many hospitals, and buildings requiring high pressure steam. . Oil, gas, stoker and hand fired types. Ratings, horsepower-- 25 to 250 hand fired.' 30 to 261 mech. fired. Fitzgibbons Boiler Co., Inc. Heating Systems bou.,., steel FITZGIBBONS RESIDENTIAL STEEL HEATING BOILERS THE 400 SERIES A boiler for mechanical firing that brings to the small home the many advantages of Fitzgibbons steel boiler construction. Elec trically welded in a one-piece unit, it combines strength and durability with leak-proof, crack-proof construction. The Fitzgibbons principle of a single pass of many small tubes simplifies cleaning and assures high operating efficiencies. Five sizes--320 to 900 sq ft steam, net radiation load. THE "OIL-EIGHTY" AUTOMATIC This graceful, efficient and economical domestic heating boiler can be combined with any good oil burner to form a heating unit of outstanding merit. Fitzgibbons steel con struction combines strength and resiliency with life-time, crack-proof, rust-resisting dur ability. *- Many medium-sized and large homes have been well served by the Oil-Eighty during the war years of fuel stringency. In six sizes-- 1326 to 26S0 sq ft steam. E.D.R. THE R-Z-U JUNIOR The Fitzgibbons R-Z-U Junior is in effect a large boiler scaled down to sizes for the class * of larger residences and smaller business, institutional and public buildings. It has ' large boiler qualities in fuel economy, quick steaming, convenience of operation. It is adapted for steam, vapor, vacuum of hot water systems, and for burning coal hand fired, or for mechanical firing with oil, gas or stoker. . In sizes up to 2900 sq ft steam hand fired and 3500 sq ft steam mechanical fired. E.D.R." FITZGIBBONS DIRECTAIRE CONDITIONER The unit provides automatic temperature control, automatic humidity control, filtered air, circulated air, summer comfort. Fitzgibbons steel crack-proof construc tion, prevents all chance of combustion gas leakage into the air stream. The Directaire operates at extremely low fuel cost, with quiet performance. Installation is easy and rapid. . For mechanical firing. Sizes from 65,000 to 600,000 Btu per hour. fj 1157 Heating Systems //<., st<*i Farrar & Trefts Incorporated 20 Milburn Street, Buffalo 12, N. Y. Atlanta. Ga. Buenos Aires. S. A. Cambridge, Mass. Charlotte. N. C. Chicago. III. Cleveland. Ohio Cuyahoga Falls, Ohio Detroit, Mich. Glendale. Calif. Grand Rapids. Mich. Honolulu. Hawaii Milwaukee. Wis. Minneapolis. Minn. Nashville. Tenn. New Orleans, La. New York. N. Y. Nutley, N. J. Orchard Park. N. Y. Philadelphia, Pa. Pittsburgh, Pa. Richmond, Va. Rochester. N. Y. St. Louis. Mo. San Antonio. Tex. San Francisco. Calif. Tampa. Fla. Toledo, Ohio Washington, D. C. The Bison Compact Boiler Series 100 and 900 The F&T Bison Compact Welded Heating Boiler is more than just another boiler. It has been designed carefully so as to have a large furnace volume, the proper volume of water, just the right amount of steam liberating surface, the correct volume for steam storage and a balanced'circulation. The result is a remarkably steady water line--A Balanced Boiler. This boiler requires a minimum amount of floor space and is easy and inexpensive to install. It is reasonable as to first cost and economical in operation. Construction is in accordance with the A.S.M.E. Code for 15 lb working-pressure and boilers are designed for hand firing with anthracite or bituminous coal or for mechanical firing with oil, gas or stoker. There are various sizes available from 1,800 to 35.000 sq ft of steam radi ation, all ratings as required by the Steel Healing Boiler Institute. The Bisonette Compact Boiler has the same characteristics as the larger Bison Compact Boiler. It has been designed for installation in large residences and small business establishments where the advantages inherent in a Steel boiler are desired. Firebox Return Tubular Heating Boilers are Quality Boilers. They are constructed to measure up to the high standards set by Heating Engineers and will' give unfailing service under all conditions. Being economical to install and operate, they are highly - favored by Architects and Engineers for heating Schools, Hospitals, etc. There are two types of Firebox Boilers, the Up-Draft Type and the Down-Draft Type. Both types are made of welded or riveted construction for heating purposes ' at 15 lb working pressure and riveted, or, Class 1 fusion welded x-rayed and stress-relieved for power purposes at 100, 125 and 150 lb working pressure in accordance Firebox Return Tubular Boiler Series 500 and 600 with the A.S.M.E. Code. Sizes from 4.500 to 35,000 sq ft of steam radiation, as rated by the Steel Heating Boiler Institute, are designed for hand firing with coal or for mechanical firing with oil, gas or stoker. Scotch Dry Back Boiler Series S-SOO ' The Bison Low Pressure Scotch Dry Back Boil ers are carefully proportioned and balanced. They are designed for hand, oil, gas or stoker firing, for ratings from 15 to 250 hp. These boilers operate efficiently and carry sustained overloads. The Front ' Smokebox Doors Open Sideways giving easy access to the tubes. . F&T boilers are designed so that the round furnace is always longer than the tube length which increases the furnace volume. This gives a large, combustion volume in proportion to horsepower rating which makes the boilers very economical to operate and exceedingly " Quick Steamers." . "Catalogs on Request'* 1158 Heating Systems Boiiora,1steel The International Boiler Works Company 350 Birch St., East Stroudsburg, Pa. SALES OFFICES IN PRINCIPAL CITIES FOR years "Fuel-Saver" Boilers Type C have met the requirements for low cost heating in office and apartment build ings, hotels, schools, theatres, industrial plants, etc. Their design and construction makes them especially suitable for post-war heat ing requirements: QUICK STEAMING Due to rapid and positive internal water circulation. MAXIMUM HEAT ABSORPTION Due to effective distribution heated gases. . of EASE OF CLEANING Due to accessibility of heating - surfaces. "FUEL-SAVER" Boilers have cut fuel costs in thousands of heating instal lations. Complete range of standard sizes rated in accordance with S.B.H.I-15 lb A.S. M.E. standard--for hand, stoker, oil or gas firing. Type C twin section--a heating boiler in halves. For installation where Type C one piece cannot be carried through exist ing passages. Type KD-^knocked down--a heating boiler designed for shipment so that sections can be carried through a door or window. Eliminates expensive cutting or patching of building. Reduces time out when in need of steam. Typical Type C Installation Halves of twin section ready for bolting Type CR water-tube power boiler for processing and power. 100-125-150 W.S.P. A.S.M.E. standard. Complete range of sizes--10 to 300 hp for hand, stoker, oil or gas firing. Write for bulletins K&WANEE, 59ILER Q?^RAT!9N DMaiea of AMtmewr Pnauroa & .fUwdard tnltej cmmuTio* . Kewanee, Illinois , BRANCHES IN 64 PRINCIPAL CITIES ., Steel Heating and Power Boilers, Water Heating Garbage Burners, Tabasco Heaters and Tanks. KEWANEE STEEL HEATING BOILERS Kewanee offers a dependable line of Steel Boilers built for heating every size building with high efficiency burning any kind of fuel. There are 380 standard sizes and 33 types of Kewanee Boilers; most are kept in stock ordinarily for immediate delivery. Seventy-eight years of intensive study and effort are back of Kewanee Boiler designs. They are all constructed in our exten sively equipped factory at Kewanee, Illinois, in conformity with these Codes: American Society of Mechanical Engineers for construction, and for rating with the Steel Boiler Institute Simpli fied Practice. The Kewanee series include: Heavy Duty Riveted Firebox Types: 1,240 ft to 42,500 ft. Brickset and portable settings, Updraft and Downdraft Smokeless Furnace, Single-pass tubes for rear smoke outlet; Twopass tubes for front smoke outlet. Welded Boilers: 2,200 ft to 42,500 ft. Direct Draft or Smokeless Arch with Corrugated Crown Sheet. Rear Smoke outlet and Weld + Rivet for front Smoke outlet. Firebox Boiler Portable Up-draft Type "400" and "500" Series, hi-Pressure 676 577 Residence Steel Boilers: 225 ft,to 2,924 ft. Square and Round Type "RM with and with out Jackets and Hot Water Heating Coils for Storage Tank or Instantaneous flow. Firebox Boiler for Stoker "400" and "600" Series SPECIFICATIONS--PORTABLE UP-PRAFT BOILER 57$ 579 580 480 44t 481 582 482 583 483 84 484 585 586 587 486 486 487 588 488 589 590 489 490 Rated Steam Capacity: Coal............................Sq Ft Oil. Gaa or Stoker..... .Sq Ft Width and Length .In. x Ft In. Overall Height Shell ...........In. Height of Water Line.......... In. Approximate Weight: Coal. Lb Oil...Lb 3500 4250 42x6-7 80 70 6100 5500 4000 4860 42x9-6*4 80 70 6700 6100 4500 5470 48x8-10 86 73 7300 6600 5000 6080 48x9-6/2 86 73 7900 7100 6000 7290 54x11-5 a 9300 7000 8500 10000 12500 15000 8500 10330 12150 15180 18220 54xl3-li/2 60xl3-41/a 60x15-5/2 66x15-6/2 66x184/2 94 101 101 107 107 79'A mob 84>4 13300 a a a 10400 12200 13600 15800 18100 17500 21250 72x17-0 113 94 22000 20300 20000 24290 78x17-7} 115 242($) 22300 25000 30360 78x21-3/2 115 a 26400 30000 36430 84x20-7 125 105 32300 30200 35000 42500 84x23-4 125 105 36100 33800 Rated Capacity for Water Boiler is 60 per cent greater than Capacity for Steam Boiler. Tables for two series of Boilers list maximum dimensions only. $ Co if 3* Co I9 II Smokeless Boiler Portable., . ' l Down-draft'Type "800" Series Type "C" Boiler "700" and '*8700" Series for Coal. Also "1700" Series for Oil. At Right: Type "C" Hi-Firebox Boiler, "7L70" Series for Stoker Firing. Also "S7L70" Series Hand Fired. Coo P SPECIFICATIONS--SMOKELESS DOWN-DRAFT BOILER Boiler No................................................... , 376 377 3>i 379 380 381 382 383 384 385 386 387 388 389 Rated Steam Capacity: Coal............................................... Sq Ft 3500 Oil. Gai or Stoker...........................Sq Ft 4250 Width and Length.................... In. x Ft In. 42x8-3 Overall Height Shell................................In. 80 Height of Water Line.............................. In.' 70 Approximate Weight: Coal..................... Lb 6800 Oil........................Lb 6200 4000 4860 42x9-3 80 70 7500 6900 4500 5470 48x8-7} 86 . 73 8100 7400 5000 6080 48x9-5 86 73 8800 8000 6000 7000 8500 10000 12500 15000 7290 6500 10330 12150 15180 18220 54x11-2} 54x12-1! 60x12-8} 60x14-9 66x14-11 66x17-4 94 94 101 101 107 107 78 10000 78 11100 85 13600 85 15300 a a 9100 10100 12500 14100 16500 18900 17500 21250 72x16-5 113 229& 21200 20000 25000 30000 35000 24290 30360 36430 42500 78x17-0} 78x20-7} 84x19-11 84*22-8 115 115 12S 125 . .95 25100 95 29500 && && 23200 27500 31500 35200 SPECIFICATIONS--TYPE "C" WELDED BOILER Boiler No..................... 2773 774 775 2774 2775 776 2776 777 2777 778 779 780 2778 2779 2780 781 782 2781 2782 783 2783 784 2784 785 2785 786 2786 787 2787 788 2788 789 2789 790 2790 Rated Steam Capacity: W W .'S4 S4 Hf4Coal....................Sq Ft Oil, Gat or Stoker. Sq Ft Width & Length, In.xFt in. Overall Height Shell... In. Height of Water Line.. In. Approximate Weight: '2200 2600 3000 2680 3160 3650 36x5-10 36x6-4 36x6-10 3500 4250 36x7-9 4000 4500 5000 6000 7000 8500 I0O00 >2500 15000 .17500 20000 '25000 30000 35000 4860 5470 6080 7290 8500 10330 12150 15180 18220 21250 24290 30360 36430 42500 42x7-10} 42x8-6} 42x9-2 48x9-4} 48x10-7 54x9-11 54x11-2} 60x11-6} 66x12-3} 72x12*1} 72x13-4} 78x14-9} 84x14-2} 84x15-11} s4 99 85 99 108/j 112 118 118 122 135 85 94 95 101 101 103 114 135 114 '700 Series, Coal.... .Lb 3900 4400 '5000 5500 6000 6500 7500 8400 9700 11000 12900 14900 16600 18400 22000 25200 28400 2700 Series, Coal... .Lb 3400 3800 4300 4800 Oil....... Lb 2900 3300 3700 4100 5300 4600 5800 6300 7200 8100 9400 10600 12500 5000 5400 6100 6900 8000 9100 10700 14400 16100 17900 21200 24400 12300 13800 15400 18100 20900 27500 23400 SPECIFICATIONS--TYPE "CV HI-FIREBOX WELDED BOILER' *27L70 Boilers have hand-fired coal grates and ratings, with 7L70 di nensions. Boiler No....................... 7L?3 7L74 7L75 7L76 7L77 7L78 7L79 ?LSo 7L81 7L&2 7L83 7L84 7L$5 7L86 7L87 7L88 7L89 7L90 Rated steam capacity. Stoker................Sq Ft Width x Length. In.xFt In. Overall Height........... In. Height of Water Line.. In. Approximate Weight. .Lb 2680 3160 3650 4250 36x5-10 36x6-4 36x6-10 36x7-9 82,, 82,, 82* 82* 3100 3500 3900 4400 4860 5470 6080 7290 8500 10330 12150 15180 18220 21250 24290 30360 36430 42500 42x7-10} 42x8-6} 42x9-2 48x9-4} 48x10-7 54x9-11 54x11-2} 60x11-6} 66x12-3} 72x12-1} 72x13-4} 76x14-9} 84x14-2} 84x15-11} K* IJ*488* 77* 88* 108 108 119/a 123 131 134 140 157 94 94 105 106 114 117 121 136 161 140 4900 5400. 5800 6700 7600 8800 10000 11800 13600 15300 17000 20100 23200 26100 f*., Brickset Boiler Up-draft Type _ Type "K" Up-draft Boiler Boiler No..................... SPECIFICATIONS--BRICK-SET AND TYPE "K" PORTABLE UP-DRAFT BOILERS 3 4 ~T" 6 8 9 10 ii 13 14 lj ii 18 3K 4K 5K 6K 8R 9K 10K 11K I2K 13K 14K 15K 16K 18K 20K 19 20 Rated Steam Capacity; Coal............................. Sq Ft Oil, Gas or Stoker......... SqFt Width and Length ... In. a Ft In. Overall Height Shell......... Height of Water Une........ Approximate Weight: Coal. ...Lb Oil.. ...Lb 1240 1380 1800 2200 3000 3500 4000 4500 5000 6000 7000 6500 10000 12500 15000 17500 20000 1770 2020 2190 2680 3650 4250 4860 5470 6060 7290 8500 10330 12150 15180 18220 21250 24290 30x9-10 36x8-10 36x10-4 36x11-10 42x11-4 42x12*10 46x11-10 48x13-4 48x14-10 54x15-3 54x17-9 60x17-0 60x19-6 66x19-6 72x19-6 72x164) 72x18-0 59 65 65 65 71 71 77 77 77 83 83 93 93 99 105 107 107 52 55 55 55 58ft 58ft 61 61 61 66 66 75 75 80 85ft 3500 3900 4200 4700 5700 6400 7000 7600 8200 9500 10700 12600 14500 17600 20700 3130 3550 3800 4200 5100 5800 6400 6900 7400 8600 9700 11500 13300 16100 19100 17700 20000 SPECIFICATIONS--WELD + RIVET FIREBOX BOILER "5000" SERIES Boiler No.................................. 5076 "Wf Ms 5079 5080 5081 50)12 5083 io84 5085 4086 "Soil? 5088 So89 5090 Rated Steam Cap: Coal. .. .Sq Ft Oil, gaa or stoker..............Sq Ft Diam. x Length.......... In. x Ft In. Overall Height.......................... In. Height of Water Line...............In. Approx. Weight: Coal............ Lb Oil................ Lb 3500 4000 4500 5000 6000 7000 4250 4860 5470 6080 7290 8500 42x7-3 42x84) 42x841 42x9-10 48x9-9 48x1 l-lft 81 81 61 81 70 70 70 70 73ft 73ft 5100 5600 6100 6600 7500 8400 4500 5000 5400 5800 6600 7400 8500 10000 12500 10330 12150 15160 54x1 1-1 $4x12-9 60x!3-2ft 92ft m 100ft 78 78 84 9600 10800 12600 8500 9600 11100 15000 18220 60x15-3 -100ft 84 14400 12800 17500 21250 66xl4-5ft 105 86 16100 14400 20000 24290 66xl64)ft 105 86 17900 16000 25000 30360 72xl6-8ft 112 94ft 21200 19200 30000 36430 78xl7-5ft 117 96 24400 22300 35000 42500 78xl9-8ft 117 96 27500 25200 SPECIFICATIONS--WELD + RIVET SMOKELESS BOILER--1"6000" SERIES Boiler No........................................................ 6077 6078 6079 6080 6081 60di 6083 6084 6085 6086 6087 6088 6089 6090 Rated Steam Capacity: Coal..................... SqFt Oil. Caa or Stoker................... .Sq Ft Diameter x Length..........................In. x Ft In. Overall Height.............................................. In. Height of Water Line.................................... In. Approximate Weight: Coal............................ Lb - ' Oil__ ____ .............. Lb 4000 4860 42x8-2 81 . 70 5800 5100 4500 5470 42x8-8 81 70 6300 5600 5000 6060 42x9-6 81 70 6800 6100 6000 7290 48x9-7 s 7000 7000 8500 10000 12500 15000 17500 20000 25000 30000 8500 10330 12150 15180 18220 21250 24290 30360 36430 48x11-0 54x10-81 54x12-41 60x12-91 60x14-91 66x14-01 66x15-71 72x16-41 76x17-1 W 100ft 100ft 105 105 112 117 73ft 84 84 86 86 94ft 96 8600 9900 11200 13100 14900 16600 16300 21500 24500 7800 8900 10100 11900 13500 15100 16700 19800 22700 35000 42500 78x19-4 117 96 27300 25300 CoD P ft 3* CO 8 V.,- KllWANEE TYPE "R" RESIDENCE BOILERS Kewanee Type "R" Boilers are especially designed ajnd constructed to meet all heating and hot water requirements for homes and small buildings. Every kind of solid fuel, coke, all grades of hard or soft coals and their briquette or treated forms are burned with excellent results. Also, any ljquid fuel, oil, and natural or com* mercial gas can be used with high efficiency. . . ` Standard snug fitting jackets, Rex or Reg'^l extension styles enclosing burners are available for Round "R", Square "R" or 83R Boilers. Hot Water Copper Coil. 55 and 65 gal for Round "R". Capacities up, to 720 may be ordered for Square "R" and 83R Boilers.' . . KEWANEE STORAGE WATER HEATERS Kewanee Storage Heaters--use exhaust or 'live steam. 15 standard Coil Elements in 29 standard size storage tanks. Capacities 95 to 2240 gals per hr. KEWANEE SCOTCH MARINE BOILERS Kewanee Scottle Junior for Hih Pressure Steam in small industrial usage. 6 sizes 6 to 30 hp at 100 lbs steam pressure. ` Kewanee Welded Scotch Marine, Low Pres sure Steam. 18 sizes, 2680 to 42500 sq ft, mechani cally fired. KEWANEE HI-TEST BOILER Kewanee Hi-Test Fusion Welded Series for High Pressure Steam in power or industrial process. 6 stock sizes, 50 to 150 hp, 125 and 150 lbs steam working pressure. AH A.S.M.E. Code. Type "R" Boilers Square "R", 8SR, and Round "R"--in Flush, Round or Extended Jackets SPECIFICATIONS--RESIDENCE BOILERS SQUARE "R" ROUND TYPE "R" Boiler No....... 742 743 745 746 747 748 733 734 735 736 1737 Net Load Steam. Coal... .Sq Ft 790 1000 1350 1600 1780 I960 225 330 450 570 Utl. Uaa or Stoker.... SqFt 640 1120 1470 1900 2160 2380 275 400 550 700 900 32x391 32x451 32x451 32x511 32x571 32x63J 17 Overall Height Shell Top. .. In. 599*2 W/l 70'4 70/, 70/, 70'/, 54 543/4 58ft 61 Height of Water Line.... 46 4ft bbft 58ft 58ft 58'ft 46 44 45 49 61 49 Approximate Weight: Coal. .Lb 2150 2360. 2800 3050 3300 3550 700 880 1040 1280 Oil. ...Lb 1900 2060 2500 2730 2920 3125 600 800 920 1130 1400 Standard Jacket. Crated. ..Lb 205 225 175 190 200 225 190 215 Boiler No....... . 83R1 83R2 83R3 83R4 83R6 83R7 83R8 83R9 Oil and Gas ; or Stoker 083R. N. Load Steam.. 901 1105 1326 1513 7091 2363 2652 2924 Wt Jacketed.... 1600 1600 2000 2200 2800 2900 3100 3300 Boiler aeries 1742-1748,1733*1737 for oil, gas oratoker; 2742-2748, 2733-2736 for anthracite. Kewanee Indirect Hot Water Heating Coila for Type C, Square and Round "R" Boilers; 55 sizes, 55 to 1520 gal. KEWANEE WATER HEATERS AND TANKS All-Weld Water Heaters, Tabasco or Garbage Burning, 5 sizes to heat 165-700 gal 50 deg per hour. Extra Heavy W. P. 100 lb per sq in. 150 lb Test. Water Heating Garbage Burner Tanks 66 to 1700 Gal -A DRAIN Tabasco Water Heater to o Heating Systems * SU/StoTM, Convectors THE NATIONAL RADIATOR COMPANY MODERN DESIGN HEATING SYSTEMS ' Johnstown Pennsylvania Branch Offices: Baltimore...............................2622 Matthews Street Boston.......................... 167 Bridge Street, Cambridge Chicago.....................................Daily News Building New York..................................60 East 42nd Street Philadelphia...................... 401 North Broad Street Pittsburgh............................... .......304 Arrott Building Richmond. .................. Richmond Trust Building Washington......................4034 Georgia Ave.. N.W. Nos. 1-2-3 SERIES HEAT EXTRACTORS Cast iron boilers incorpo rating modern design fea tures. Numerous flueways, with added extended surface (fins) on firebox crown and in flues. Readily convertible for all fuels and methods of firing. Built-in tankless and stor age tank water heaters available. NETI=B = R RATINGS Hand, Stoker, Oil-fired' Steam --170-2.300 sq. ft. Hot Water--270-3.680 sQ. ft. ART RADIATORS The National "Art" Radiator is a com pact, thin tube radi ator available in a complete range of sizes. Straight lines and receding plane surfaces provide an attractive modern appearance. Can be furnished legless, with high legs, or with special harmo nizing pedestals. OIL HEATING UNITS--Cast Iron and Steel in a Wide Vai^ety of Types and Sizes GAS HEATING UNITS--Handsome, Compact and Efficient--Enclosed Controls and Draft Diverter UNIT HEATERS AERO CONVECTORS The exclusive design feature of sloping sections exposes a greater ' amount of heating surface to the flow of air traveling through the convector. More heating surface can be arranged in less space with this design and additional sections are easily added. Wide fin spacing prevents clogging. Numerous con vector sizes and possible arrange ments, and Various types and styles of enclosures available, pro vide flexibility for practically any desired installation requirement. , Where a large volume of air is to be heated in stores, garages and workshops,' the NRC Unit Heaters will give efficient dif fusion of warmth to all areas. Available in horizontal or vertical shaft types of heaters. For steam or hot water. ENCLOSURES ACCESSORIES Floor plates, valves, traps, circulating water pumps, controls, etc., are furnished for complete installations. SERVING THE HEATING INDUSTRY SINCE 1894 1164 The National Radiator Company Heating Systems R^'dliVors, Convectors Nos. 40-42-48 SERIES--Super-Smokeless and Standard Large amount of prime heating surface, long flue travel and adequate flue-ways provide out standing performance--regardless of whether hand, oil or stoker fired. Super-Smokeless Boiler (illustrated) delivers preheated air in fine jets into path of gases, burning unconsumed fuel. Twin sections (No. 48 Series only) pass readily through small doorways and facilitate assembly. NET RATINGS (Bonded): ' Nos. 40-42 Series--Steam--2.010 to 7.880 sq ft. --Hot Water--3,216 to 12.608 sq ft. No. 48 Series --Steam--3.830 to 12.900 sq ft. --Hot Water--6.128 to 20,640 sq ft. NATIONAL PREMIER STEEL BOILERS Residential Series--Jacketed and Unjacketed Low pressure steel boilers for residences and small commercial buildings. Electrunite tubes assure longer, trouble-free service. True-arch crown provides maximum firebox height and prevents sludge from accumulating over hottest part of boiler. SBI NET RATINGS (Jacketed Boilers Only): Oil-Fired and Oil Heating--Steam 275 to 680 sq ft. Unit . --Hot Water--440 to 1.090 sq ft. SBI RATINGS (Unjacketcd Boilers): Type DB, Hand-Fired --Steam--485 to 2.200 sq ft. --Hot Water--775 to 3.520 sq ft. Type MB, Stoker-Fired) --Steam--735 to 2.680 sq ft. Type OB. Oil-Fired f ---Hot Water--1,175 to4.280 ) sq ft. Commercial Series--Unjacketed Hand-fired Smokeless Boiler with rear smoke outlet (Type SB) illustrated-- without smokeless feature is Type DB (Direct Draft). Shaking apparatus and water-cooled bridgewall eliminated on Type MB (Stoker-fired) and Type OB (Oil-fired) Boilers. Three-pass gas travel --recessed smoke box provides flush front. Built-in tankless and storage tank water heaters available. Boilers with front smoke outlet (Types SF, DF, MF and OF) can be furnished. Built-in Tankless Hot Water Heaters Built-in Storage Hot Water Heaters SBI RATINGS: Type DB and SB Hand-Fired - Type MB Stoker-Fired Type OB . Oil-Fired Type DF and SF Hand-Fired Type MF ' Type OF Stoker-Fired Oil-Fired --Steam --1,800 to 35,000 sq ft. --Hot Water--2,880 to 56.000 sq ft. --Steam --2,190 to 42,500 sq ft. --Hot Water--3,500 to 68,000 sq ft. --Steam --3.000 to 35,000 sq ft. --Hot Water--4,800 to 56,000 sq ft. --Steam --3.650 to 42,500 sq ft. --Hot Water--5.840 to 68,000 sq ft. CATALOGS WITH COMPLETE DATA AND DIMENSIONAL INFORMATION WILL GLADLY BE FURNISHED 1165 Heating Systems Generator Unit Steam Preferred Utilities Manufacturing Corporation Executive Offices I860 Broadway, New York 23, N. Y. FACTORY--Danbury, Qonn. . Branch Office: BOSTON. MASS. . Representatives in Principal Cities PREFERRED UNIT STEAM GENERATOR The Modem Packaged Power Plant The Preferred Unit Steam Generator is a heavy duty, oil-fired, portable, automatic steam plant with all the equipment neces sary to produce steam--economically. The guaranteed minimum thermal effi ciency of.80 per cent is made possible by the efficient design of the burner and the four pass arrangement of the heat-absorbing surfaces. Sizes range from 20 to 500 bhp--for pres sures up to 200 lb psi. Induced Draft--The Preferred Unit Steam Generator operates with induced or '`pull through" draft without the need of a stack. Air volume is automatically con trolled to meet the requirements of com plete combustion. The use of induced draft eliminates the very real danger of forcing the products of combustion into the boiler room, and contributes to the long life of refractories which have stood up remarkably well under the most trying operating Conditions. Heavy Oil Types--These units are made in all sizes, up to and including 500 bhp for use with the Heavier grades of bunk er oils'--for either fully-automatic or semi automatic operation. ' Light Oil Types--For use with lighter oils the Preferred Unit Steam Generator is made in sizes up to 100 bhp and for pres sures up to 200 lb psi. For further details refer to Bulletin No. 1000. Unit Steam Generator . OIL BURNERS Preferred oil-burners are made in both the horizontal, rotary-cup and the me chanical-atomizing or gun types. Each type is suitable for manual, semi-auto matic or fully-automatic operation. The rotary-cup burner is suitable for use with either light or heavy oil and has several exclusive features. One important feature is its 4 to 1 throttle control which automatically delivers the correct mixture of oil and air for efficient combustion--at all rates of firing. Oil viscosity is control led by a patented Volumeter. No other method of firing permits such perfect utilization of the source of heat. Preferred mechanical-atomizing burners are designed to burn light oil only and for use where Diesel or lighter oils are used. All Preferred burners are supplied with safety devices which prevent firebox flood ing, or damage due to shut-down because of electric power failure or overload, or from foreign matter in the fuel oil. OTHER PREFERRED PRODUCTS Water Heaters .............................................................................................. Draft-A-Justors Oil Burner Accessories ......................................................Boiler Room Compounds 1166 Heating Systems Boners, cast-iron The H. B. Smith Company, Inc. Westfield, Mass. Branch Offices and Sales Representatives in Principal Cities A complete line of modem cast iron sectional boilers for residential, commercial and industrial heating and for domestic hot water supply 15-20-25 SMITH-MILLS BOILERS Capacities 200 sq. ft. to 2275 sq. ft. steam radiation. This complete line of modern push nipple boilers is available in models for oil, gas, stoker and hand firing. Provisions have been made for built-in domestic hot water heaters and controls. MILLS WATER TUBE BOILERS Capacities 900 sq. ft. to 13,380 sq. ft. of steam radiation. Independent header type construc tion--literally thousands of these famous Mills boilers have been installed in camps, canton ments, bases, war housing and other essential construction during the past few years. Models for hand and all types of automatic firing. 44 Mills 42 AND 60 SMITH BOILERS May be used in batteries for heating loads up to and over 100,000 sq. ft. steam radiation. Many of these large units installed in industrial plants furnish steam for process requirements as well as for heating and domestic hot water. SMITH HY-TEST BOILERS -Smith Hy-Test Boilers for hot Water supply, are available in several models and many sizes for tank capacities to 20,000 gal. Constructed of the finest quality grey iron castings, these Hy-Test units are carefully tested at high pressures before shipment. The No. 17 series, for example, is tested at 350 lbs. hydrostatic pressure--the highest test pressure of any cast iron boiler made. Complete catalogue information describing Smith boilers is filed in current issues of Sweet's "Engineering" and Domestic Engineering Catalogue Directory 1167 Heating Systems Bouen, catt-imn Spencer Heater Division--The Aviation Corporation Williamsport, Pa. Sales Representatives in Principal Cities PRODUCT Spencer Automatic Magazine Feed Heaters are furnished in cast iron sectional types--and steel tubular types for larger buildings--for steam, vapor and hot water heating. There is a size and capacity for every type of building, to provide economical and convenient heat--safe, dependable, sure. COMFORTABLE HEAT AT LOW COST Coal -- Coke -- Gas -- Oil -- Spencer J and L series heaters and M series boilers are primarily designed to bum low. cost No. 1 Buckwheat Anthracite or small size coke. ' If at any time a property owner desires to burn more expensive fuels---oil or gas-- his Spencer Heater can be readily con-, verted and will show a high efficiency. Jacketed Covering--Illustrated in the attractive metallic jacket of the deluxe enclosing type for Spencer Cast Iron Heaters, either with or without the en closing jacket doors. . Spencer Jacketed Heater L-l Series Why Spencer. Heaters perform so satis factorily can best be explained by an inspection of their design and construction. The Spencer principle, illustrated in the cross-sectional view, is simple: Once a day fuel (No. 1 Buckwheat Anthracite or small size by-product coke) is put into the magazine. It fills the sloping grate to the level of the magazine mouth. The fire bed always stays at the proper level, for as fast as fuel burns to ash, it shrinks and settles on the sloping grate; and more fuel rolls down automatically over the top of the fire bed. Fuel feed is by gravity alone, in just the right amount to keep the fire always burning at its most efficient combustion point. - This explains why a Spencer Automatic Magazine Feed Heater always gives the same uniform, satisfying heat, and burns less fuel. These exclusive Spencer ad vantages are available in all types of the magazine feed heaters and boilers. Spencer Heavy Duty Tank Heaters-- With the automatic magazine feed con struction, they provide ample domestic hot water at lowest cost, and with a minimum of tank heater attention. Cutaway sectional view Spencer Cast Iron Heater 1168 Spencer Healer Heating Systems Boam, stmt SPENCER ALL YEAR SYSTEM In addition to the excellent heating facilities afforded by Spencer Magazine Feed Heaters, Year Round Domestic Hot Water Service can also be provided and assures at all times an ample supply of domestic hot water at lowest cost. Com plete data for installation and operation upon request. SPENCER STEEL TUBULAR MAGAZINE FEED BOILERS For large buildings we recommend Spencer Steel Tubular Magazine Feed Boilers, burning low cost No. 1 Buckwheat Anthracite or coke. In the cross-section diagram, part of the fire bed is cut away to show the sloping grates and the two magazines filled with fresh coal, ready' to feed down automatically by gravity to the fire. These boilers are built in two vertical sections for ease in handling and installation--a great ad vantage on replacement jobs, eliminating the necessity of costly tearing out of walls or parti tions. Combination water and fire tube con struction; built to A.S.M.E. standards. Steel Tubular Magazine Feed Boiler SPENCER STEEL TUBULAR BOILERS For Oil, Stoker, Gas or Hand-Firing For more than 50 years, Spencer has been building, in the opinion of experts, one of the most efficient, economical and dependable automatic coal burning boilers on the market. With this background of experience, Spencer Engineers developed the Spencer Steel Tubular Boiler for oil, gas, stoker and hand-firing--the UKM and "C" series for residential use, and the Type "A" for larger buildings. They are better boilers both for the property owner and for the architect or engineer who specifies them. The high sustained efficiency of these boilers means adequate heat for a lower fuel cost. Design is of the three pass type. Combustion chamber is amply large. Built of best quality open hearth steel boiler plate, and steel tubes. Can be fur nished with domestic hot water heating coils, storage tank or instantaneous type. A complete range of sizes from 400 sq ft SHBI net steam rating up. They meet or exceed in every particular the requirements of the A.S.Af.E. and S. H. B. I. Codes. Type "A" Steel Boiler "C" Series Steel Boiler "A" Series Every Spencer Boiler is guaranteed to carry more than its full rated load, giving the installer a definite factor of safety. These boilers have all the advantages of the Spencer exclusive design and are read ily adapted to mechanical oil or stoker firing--or hand-fired coal or coke. 1169 Heating Systems Boilers, Steel Terre Haute Boiler Works Co. Established 1857 Main Office and Works: Terre Haute, Ind. Branches and Representatives In PRINCIPAL CITIES CLIFF LOLINE SECTIONAL STEEL HEATING BOILERS For Oil, Gas, and Coal Stoker or Hand Firing Designed especially for boiler replacement work. Efficient Tube Heating Surface and Generous Firebox Proportions. Only four sections are required for maxi mum rating. Compactness and accessibility for replace ment work in old buildings, etc., eliminates expensive and hazardous excavation or foundation wall removal. Each section will easily pass through the ordinary door opening. Assembly of Front Header made easy with a Strap and Slip Bolt. Watertight Joint made with Composition Gasket on Boiler Side of Header. Yoke slotted for easy Slip Bolt Assembly. Small lugs on Yoke provide quick alignment of sections. Heavy stay-bolting throughout. NOTE: Rock wool insulation and baked enamel, steel jacket furnished at extra cost. RATINGS--Hand Fired--2100-29820; Oil, Gas, Stoker--2550-86210 sq. ft. Steam CLIFF STEEL RESIDENTIAL BOILERS For Oil, Gas, Stoker or Hand Firing A Three-Pass electric welded Steel Boiler furnished with Red .Enameled Steel Jacket and 1)4 in. thick rock wool insulation for Residence, Apartments and Smaller Buildings. Will pass thru 31 in. doorway. Designed for 15 lbs. working pressure on steam and 20 lbs. pressure on water. Rated in accordance with S.H.B.I. Code. Submerged type hot water coils can be furnished installed inside of boiler; either tank-heater or tank-less type. Ratings 800-3160 sq. ft. steam. ' CLIFF HEAVY DUTY LOLINE BOILERS For Oil, Gas, Stoker or Hand Firing Also Hi-Firebox Type A.S.M.E. Code Construction Three-Pass compact Fire-Box Boilers. Designed and constructed to A.S.M.E. Standard for 15 lbs. steam or 30 lbs. water working pressures.. All boilers comply with the Industry's simplified practice recommenda tions R157-35 as issued by the U. S. Department of Commerce and the S.H.B.I. Code for the rating of low pressure heating boilers. Can also be furnished with a Cliff Patented Steel Jacketed Red Enamel Finish having 1)4 in. Rock Wool Insulation. RATINGS--Hand Fired--2600-35000; Oil, Gas, Stoker--3160-42500 sq. ft. Steam. Write for complete information on CLIFF Boilers 1170 Heating Systems Boiler,, steel Pacific Steel Boiler Division United States Radiator Corporation General Offices: Detroit, Michigan Sales Offices In Principal Cities A Complete Line of Low Pressure Steel Heating Boilers AU Pacific Boilers are built using the A.S.M.E. Boiler Code Standards as minimums. DIRECT DRAFT AND SMOKELESS SERIES FOR COAL FIRING Built in the following capacities for steam: 2200 to 35,000 sq ft. All Pacific Boilers are built, inspected, and tested under the supervision of the Hartford ' - Steam Boiler Inspection and Insurance Company. HIGH FIRE BOX SERIES FOR MECHANICAL FIRING, STOKER, OIL OR GAS Built in the following capacities for steam: 2680 to 56,830 sq ft. All Pacific Boilers are made of steel with each joint and seam electrically arc-welded --built to last a life-time. PACIFIC THREE-PIECE CONSTRUCTION Made up of three parts, shell, firebox and base, Pacific Boilers are particularly adapt able to replacement work. Where necessary . Pacific fireboxes can be split (as illustrated) allowing the boiler to be taken into the building in four pieces and erected without welding on the job. ' -' PACIFIC RESIDENTIAL SERIES FOR COAL, STOKER, OIL OR GAS Built in the following capacities for steam: 320 to 2890 sq ft. . ' i, .- Descriptive Bulletins on Pacific Steel Heating Boilers vdU be mailed on request. 1171 s Healing Systems soiim. cast-iron UnTtedStates Radiator (orporation Generol Offices: Detroit, Michigan Branches and Sales Offices in Principal Cities . Detroit, Michigan CAPITOL RED TOP BOILERS NO. 3 SERIES SUNRAY Heating Systems Boum; caat-uon UnitedjStates Radiator (orporation General Offices: Detroit, Michigan e Branches and Sales Offices in Principal Cities Detroit, Michigan CAPITOL SUNRAY No. 2 SERIES OIL FIRED BOILER CAPITOL SQUARE SECTIONAL BOILERS "B" Series Jacketed Boiler "A" Series--All Fuels Boiler No. I-Bd*SqFt Direct Cut-Iron Radiation Steam Water A-7 A-8 A-9 A'10 A-il 340 545 440 705 540 865 640 I02S 740 ' 1185 U. S. Sunray No. $ Series Boiler Number l-B-R Sq Ft Direct Cut Iron Radiation Hand Fired Stoker Fired Oil Fired Steam Water Steam Water Steam Water 43-S or W 300 480 400 640 400 640 53-Sor W 450 720 550 880- 550 880 63S or W 600 960 700 1120 700 1120 "B" Series--All Fuels B-7 B-8 B-9 B-10 B-1J B-12 B-13 - B-14 740 920 1110 1275 . 1440 1580 1730 1880 1180 1470 1770 2040 2300 2530 2770 3000 "C** Series--All Fuels Boiler No. Direct Cut-Iron Radiator Loads Sq Ft Steam Water C-12 C-I4 C-16 C-18C-20 C-22 C-24 C-26 C-23 C-30 . 2250 2715 3180 3645 4110 4575 5040 5450 5800 6M0 3600 4345 5090 5830 . 6575 7320 8065 8720 9280 9775 U. S. 25 Series Oil Burning Boiler Boiler No. Net I-B-R Sq Ft Direct Cut-Iron Radiation Steam Water Net I-B-R Btu Cross I-B-R Output Btu US-25-3 US-25-4 US-25-5 US-25-6 US-25-7 545 905 1255 1625 1985 875 1450 2/125 2600 3175 131.000 217.000 304 000 390,000 476.000 198,000 317,000 435.000 554.000 672.000 1172 Boiler No. 2-03 . 2-04 2-05 2-06 Net I-B-R Sq Ft Direct CutIron Radiation Steam 350 500 650 800 Water 560 800 1040 1280 Net I-B-R Cross I-B-R Btu Output Btu 84.000 120.000 IS6.000 192.000 129,000 182.000 234.000 285.000 "DEEPFIRE" HOT WATER SUPPLY BOILERS - Coal Fired Tested to 60 lb Hydrostatic Pressure for100 lb Working 'Pressure. 40 In. Series--Smokeless--Hand Fired Boiler No. Direct Cut Iron Radiator Loads Sq Ft Steam Water Crate Area Sq Ft Coal Capa city CuFt OutleU Min. Chim ney Sizes Height Dim. Ft Inches 740 2480 3970 840 3070 4910 940 3660 5855 1040 4250 6800 1140 4820 7710 1240 5320 8510 1340 5800 9230 8.15 10.31 10.31 12.47 14.63 14.63 16.79 10.40 13.30 13.30 16.30 I9J5 19.25 22.20 2--5' 2--5' 3--5' 3--5' 3--5' 3-5' 3-5' 50 55 60 65 70 70 75 18x18 18x20 20x20 20x24 24x24 24x28 24x28 CAPITOL THINTUBE RADIATORS 3-Tube Heights Per Section In. Heating Surface 25 1.6 Sq Ft 4-Tube 22 1.8 So Ft 25 2.0 Sq Ft 5-Tube 22 2.1 Sq Ft 25 2.4 Sq Ft Boiler No. 30 40 . 50 60 Capacity--Gallons 100 Rise 6 Hours 85* Rise 1 Hour 100* Rise 1 Hour 6-Tube 19 2.3 Sq Ft 25 3.0 Sq Ft 32 3.7 Sq Ft 792 155 132 IK in- Centers. 1512 2160 2700 297 423 529 252 360 . 450 ' 40 per cent less space needed for these graceful, efficient Capitol ThinTube Radiators. LITERATURE UPON REQUEST 1173 Healing Systems Bon.,,, cast-iron Weil-McLain Company Manufacturing Division: Michigan City, Ind. and Erie, Pa. General Offices: 641 W. Lake Street, Chicago 6, 111. NEW YORK OFFICE: 501 Fifth Avenue Weil-McLain Boiler and Radiator service is made conveniently available through local stocks carried by Weil-McLain Distributors in most of the important distributing centers. No. 68 Boiler * for Automatic Firing Boiler is completely jacketed and insulated. Has an integral front burner extension. Net I-B-R Ratings: Steam 390 to 690 sq ft, Water 625 to 1,100 sq ft. No. 78 Boiler for Automatic Firing Boiler has insulated en ameled de luxe jacket. Front or rear jacket ex tension available. Net I-B-R Ratings: Steam 530 to 1,130 sq ft, Water 850 to 1,810 sq ft. Nos. 57, 67, 77 AU-Fuel Boilers Conversion type boilers for hand or automatic fir ing. Connected Load Ratings: Steam 210 to 1000 sq ft, Water 340 to 1600 sq ft. . "RO Series'* Boiler . for Automatic Firing Jacketed and insulated round boiler for small homes. Connected Load Ratings: Steam 420 and 520 sq ft, Water 630 and 790 sq ft. Round-Type Boiler Unjacketed Round Boiler with corrugated heating surfaces for eco nomical home heating. Connected Load Ratings: Steam 275 to 1,000 sq ft, Water 440 to 1,600 sq ft. Square-Type Boilers Sectional boilers for larger installations. Com plete range of sizes. Con nected Load. Ratings: Steam 1,815 to 11,300 sq ft, Water 2,900 to 17,900 \sq ft. Raydiant "Concealed" A Radiant convector type all cast-iron Radi ator. Made in "Con cealed," also Partially Re cessed types. Solray Radiator Free standing all castiron Cabinet type Radia tor with metal cover top. Available in three depths in 21, 24 and 27 in. heights. 1174 Junior Radiator Smaller Tubular type Radiation which conserves space. Available in 1 ^ in. centers in 3. 4, 5 and 6 tube widths and 13 to 32 in. heights. Healing Systems Boilers and Stokers The Brownell Company Established 1855 .' Dayton 1, Ohio Manufacturers of BROWNELL BOILERS, STOKERS, AND HEAT EXCHANGERS Representatives in All Principal Cities Welded Triple Pass Heating Boilers built in either high leg or low water line types. Hand fired ratings 500 to 35,500 sq ft steam, 800 to 56,800 sq ft water ' radiation. Stoker, Oil or Gas fired up to 43,100 sq ft steam or 69,000 sq ft water radiation. A.S.M.E. Code construction.. Type LR (Low Set) Underfeed Ram Type Stoker. Ideal where height of setting is limited. Sizes to 300 hp; "R" models up to 700 hp. Automatic air volume control. Can be furnished with Brownell exclusive, fully automatic inter mittent coal feed control. Type C Screw Feed Stoker, proved by years of service to be sturdy, reliable and efficient. Illustration shows dead plates; can also be furnished with dump plates in the larger sizes. 30-300 hp. High or Low Pressure Double Pass Boiler with Type LR Stoker. Designed and manufactured as a matched unit steam generating plant. Furnished in working pressures from 15 to 150 lb and sizes up to 300 h.p. For power, heating, and process steam. Steam ratings 3,600 to 42,500 sq ft. Water rating, 5,800 to 68,000 sq ft when used with stoker, oil, or gas. A.S.M.E. Code construction. Heat Exchangers, Generators, Con verters. Hourly capacities from 60 to 4,400 gal; storage capacities, 25 to 1,904 gal. . The illustrations show only a part of the complete Brownell line. We shall gladly send literature describing Brownell equipment. Our field organization is ready to assist in problems of steam generation and heating. * Heating Systems Boilers and Stokers Combustion Engineering Company, Inc. AH Types of Fire Tube and Water Tube Boilers Mechanical Stokers Complete Steam Generating Units Pulverized Fuel Systems 200 Madison Avenue, New York 16, N. Y. Offices In all principal cities of the United States and Canada More than 18,500 C-E Stokers purchased to date C-E Skelly Stoker--A compact, selfcontained unit with integral forced-draft fan, adapted to burn either anthracite or bituminous coal. Alternate .fixed and moving grate bars assure lateral distribu tion of fuel. Automatic control is stand ard equipment. Approximate application range--20 to 200 rated boiler hp. C-E Skelly Stoker Unit Type E Stoker--A single-retort, under feed stoker with an established reputation of many years' standing for dependable service. Designed to bum a variety of bituminous coals under boilers up to about 600 rated hp. Available with steam or electro-hydraulic drive. C-E Low Ram Stoker--A single-retort, stationary-grate underfeed stoker for burn ing bituminous coals under boilers in the upper size range of the C-E Skelly Stoker.. C-E Spreader Stoker--A simple, rugged overfeed stoker designed to burn a . wide variety of coals. Fines are burned in suspension and the coarser coal on a grate which may be of either stationary or dumping type. Rate of coal feed and air supply may be regulated over a wide range and are readily adaptable to auto . matic control. Applicable to boilers from about 100 boiler hp up. C-E Multiple Retort Stoker--For burning bituminous and semi-bituminous coals under boilers up to the largest sizes. C-E' Traveling Grate and Chain Grate Stokers5--Including both Coxeand Green types. Available with grate surfaces suitable for anthracite, coke breeze, lignite or bituminous coal, as required. Traveling grates are ail forced-draft types; chain grates are either forced or natural draft types. C-E Boilers--All fire tube and water tube types in sizes ranging from 25 hp up to the largest. Standard and special de signs to suit all conditions of fuel, load and space. Included are all types formerly known by the trade names "Heine," "Walsh & Weidner," "Casey-Hedges," "Ladd" and "Nuway." . C-E Spreader Stoker Separate Catalogs describing each of these stokers are available, a-ssi-d 1176 Heating Systems stokers Detroit Stoker Company Sales and Engineering Offices General Motors Bldg., Detroit, Mich. District Offices in Principal Cities Main Offices and Works at Monroe, Mich. Since 1898 Built in Canada at London, Ont. Detroit Stokers are unsur passed for economy and de pendability. They include Underfeed and Overfeed Spreader Stokers of many sizes and capacities for all types of boilers. All grades of Bituminous Coal success fully burned. Catalogs of various types, furnished on request. Detroit Unistoker with Detroit Ad justable Feed (Coal Feed Control) in sures accurate fuel and air supply for best econom y. Single Retort, side cleaning for boilers approximately 150 to 300 hp with fur nace widths from five feet six inches to eight feet. Detroit I^oSloker (brickset type) for horizontal tubular, firebox or water tube boilers. Built to fit the furnace. Arrows indi cate flow of air to all parts of the fuel bed including the dumping. grates, located at each side. Double Retort Stoker--a multiple retort stoker having two retorts with the side cleaning fea ture. For medium sized boilers with wide furnaces. Detroit RotoStokers are Overfeed Spreader Stokers, having an Overthrow Rotor action, which in sures uniform fuel distribution over the entire area. Offers advantages over other firing methods for burn ing inferior fuels and efficiently handling extremely fluctuating loads. DETROIT LOSTOKER Plunger feed, side cleaning stoker. Many sizes for 50 to 150 hp boilers. Highly effici ent-fuel is fed only when needed--none is wasted. Re quires little power for op-, eration. Auto- mafirallv rnn. Detroit LoStoker (firebox type)--built to fit the ... y con furnace of high Firebox Boilers. Cool hopper trolled. with agitator designed to clear boiler doors. 1177 Detroit UniStoker with Detroit . Adjustable Feed provides a wide range of coal feed control. Detroit Double Retort Stoker, a multiple retort side cleaning stoker for medium size boilers. Detroit RotoStoker. Ash removed through doors at grate level success fully burns a wide range offuels. Detroit RotoStoker (Either Power or Hand Operated) for large boilers. Especially suited to fluctuating loads. Healing Systems stokers Iron Fireman Manufacturing Company Automatic Coal Stokers Portland, Oregon Cleveland, Ohio Address inquiries to 3815 West 106 St.. Cleveland 11, Ohio . Retail Branches or Subsidiaries: Chicago. III.; Milwaukee. Wis.; St. Louis. Mo.; New York, N. Y.; Brooklyn. N. Y.; Toronto. Canada; Montreal. Canada Dealers in Principal Cities and Towns in the United States and Canada Representation In numerous foreign countries COMMERCIAL AND INDUSTRIAL STOKERS STANDARD HOPPER MODELS This series of stokers is the standard of value in equipment for automatically firing boilers ranging in size up to 350 hp. - Available in a wide range of coal feeding . capacities, lengths and grate arrange ments, to fit varied requirements. Commercial Installation--Hopper Model Hopper Model Iron Fireman in Operation in Horizontal Return Tubular Boiler STANDARD COAL FLOW MODELS Commercial-Industrial Installation Coal Flow model that carries coal direct from bunker to fire A heavy duty stoker which combines Iron Fireman's well known firing efficiency with the automatic conveying of coal direct from bunker to fire. An integral coal con veying mechanism eliminates the labor and expense of manual coal handling^ The IRON FIREMAN COMMERCIALINDUSTRIAL COAL FLOW stoker fires boilers developing up to 350 horsepower. PNEUMATIC SPREADER STOKERS also available in Coal Flow models. MODEL Boiler Horsepower Coal Flow (available in all models)............................... Commercial and Industrial Standard Underfeed............ Commercial and Industrial Poweram Underfeed............ Pneumatic Spreader...................................................... 3 to 500* . 3 to 350 30 to 400 50 to 1.000* . OUTPUT RANGE Equivalent Direct Radiation - Steam (240 Btu) 400 to 70.000 400 to 50.000 4.000 to 56.000 7.000 to 140.000 Hot Water (150 Btu) 650 to 110.000 650 to 75.000 6.000 to 90.000 11.000 to 225.000 Multiple units available for larger boilers. 1178 . Iron Fireman Manufacturing Co. Heating Systems stokm POWERAM STOKERS Combines ram-type coal dis tributor system in retort with free-running worm conveyor from coal supply, and has these advantages: Delivers the fuel to the fire bed in a loose, easily aerated condition; the recipro cating pusher blocks insure proper fuel distribution, and make possible the successful and efficient burning of many types of coal which otherwise are impractical to fire auto matically with underfeed stokers. Designed for boilers developing up to 400 hp. As shown in the illustration above, the IRON FIREMAN PNEUMATIC SPREADER STOKER meters steam size coal from hopper or main coal bunker to transfer housing, where coal is picked up by pneumatic conveyor and delivered to furnace. The conveyor nozzle accurately spreads the larger particles of coal over the entire grate in a shallow, uniform fuel bed. The preheated fines burn in sus pension, reducing the cinder carry-over and greatly improving the combustion efficiency and responsiveness, as compared with other stokers which do not preheat fuel. The conveying air provides the over fire air which is essential for efficient com bustion. Entering at right angles to the flow of burning gases from the fuel bed, the conveying air produces maximum turbulence; another requisite of efficient and smokeless combustion. THE IRON FIRE MAN PNEUMATIC SPREADER STOKER was designed to burn efficiently, such economical fuels as the lower rank bituminous, and sub-bituminous coals and also lignite. It provides reliability of operation, physical adaptability, ease of operation, and low maintenance which is not afforded by other types of automatic coal burning systems. Pneumatic Spread er stokers are particularly adaptable to, operation at high ratings, and as a result are greatly stepping up steam output in many plants throughout the United States and Canada. IRON FIREMAN PNEU MATIC SPREADER STOKERS are made in both hopper and Coal Flow models; the latter carry coal direct from the bunker to the fire. - 1179 Heating Systems swneTM, Gas The Webster Engineering Co. 419 West 2nd St., Tulsa, Oklahoma Division of SURFACE COMBUSTION CORP., TOLEDO, OHIO WECO-N.G.E. SERIES F600 GAS BURNERS 50.000 to 10,000.000 ' Btu Output For Use in Any Steel Firebox or Sectional Boiler Series F600 venturi tube is , _ wide, 10J* long, as shown (at right) and the complete assembly is only 15* high. An infinite number of assemblies are possible by proper arrange ment of the individual tubes. For complete sizing information see Bulletin F600H. Improved venturi and greater port area insure much higher capacities at lower pressures. Unique baffles at the outlet of the mixing tube make possible perfectly even distri bution of flame completely around the baffle brick. As a result the maximum flame length is greatly reduced. Interchangeable grills with multiple ports can be varied to suit the combustion char acteristics of various gases. The proper sizing of these grills prevents any possi bility of flash back. In addition to the above major improve ments the F600 possesses the same desir able features that made the 600 so popular. 1. Simple installation requiring no ex pensive insulated combustion chamber and having no furnace radiation loss. 2. Extreme quietness due to low rate of combustion over a large area. 3. Flexibility from infinite, number of possible combinations varying both size and shape to . meet load and firebox con ditions at various gas pressures. . 4. High radiant transmission rate due to radiant temperature of the standard fire brick baffles on the top of the burner tubes. 5. Low draft loss because of ample secondary air openings. 6. Plain gas pilots of heat resistant material and of a design that will not allow flame to pull off. 7. Safety pilot applied in a cool zone in a manner that insures perfect direct ignition of the burner yet allowing the the thermal element to cool quickly upon flame failure. 8. Guaranteed vibrationless under all conditions. CAPACITY OF SINGLE F600 VENTURI TUBE--No. 17 MTD ORIFICE Manifold Gas Pressure.. 03' W.C. Input--Cu Ft. 1 hr....... 24.5 Output--Sq Ft. St. Rad. 75 Output--^Boiler HP.... 34 1.0' W.C. 38.5 117 .84 2.0* W.C. 58.0 176 1.28 3.0* W.C. 72.0 222 1.59 4.0* W.C. 84.0 258 1.85 5.0* W.C. 94.5 . 289 2.07 6.0* W.C. 104.0 318 2.28 4 oz. 112.0 343 146 6 oz. 138.0 423 3.04 8 oz. 1593 488 3.4 1180 Healing Systems Burners, on Automatic Burner Corp. 1823 Carroll Avenue Chicago 12, Illinois DOMESTIC BOILER AND FURNACE UNITS RANGE BURNERS--WATER HEATERS SPECIAL PRODUCTS AUTOMATIC OIL BURNING HOT WATER HEATER Instant hot water is provided by all A B C models, capacities of 65, 125, 300, or 500 gallons per hour. Extra efficiency is pro vided by the built-in fire and water tubes. Each water heater is perfectly matched with the correct specially designed gun type ABC burner. AU models are com pact and beautifully finished. PRESSURE TYPE OIL BURNER The gun type oil burner has the famous ABC Oilairator mechanism that atomizes the fuel, mixes it with air, and delivers it with correct twist and velocity to in sure complete combustion. The ABC nozzle combined with the proper choke aiid tabulator guarantees precise control and flexibility . . . guarantees a thoroughly satisfactory economical home heating unit. Capacity 0.6 to 6.0'gallons per hour. RANGE BURNER ABC offers complete interchangeability of parts--precision manu factured--all-steel construction--butt welded all-steel shells that fit tightly to the pressed steel base preventing air leakage and insuring an efficient flame. The full blue flame is secured in a few minutes. Oversized tubing throughout prevents plugging and air pockets. Precision-made one piece valve insures precise oil flow adjustment. The A B C is easy to clean and easy to operate-- a well built, adaptable, safe range burner. Heating Systems Burners, on Combustion Equipment Division TODD SHIPYARDS CORPORATION 601 West 26th Street, New York 1, N. Y. New York, Brooklyn, Rochester, Hoboken. Newark, Philadelphia. Chicago, So. Portland, Me.. Boston. Sprincpield, Mass., Baltimore, Washington, Detroit, Grand Rapids. Tampa, Gal veston. Houston, Mobile. New Orleans, Los Angeles, San Francisco. Seattle, Tacoma, Montreal. Toronto. Buenos Aires, London. THE TODD HEX-PRESS REGISTER in combination with the TODD "VEE-CEE" VARIABLE CAPACITY BURNER . . . makes possible increased combustion effici ency under almost any type of boiler of 100 hp. capacity or larger, operating at 50 lb. steam pressure or higher. It provides equal efficiency under either forced or natural draft conditions. The Hex-Press Register assures the most inti mate mixture of oil and air.as well as quicker, more complete combustion . . . with minimum draft loss at high capacity . . . effecting great economy in mainte nance and materially reducing fuel costs. Through the exclusive "variable range" feature of the "Vee-Cee" Burner, practi cally unlimited firing range is assured . . . without change of burner tips, oil delivery pressure or angle of spray. Constant steam pressure can be main tained regardless of demand : . . changing ' load requirements are met instantly under manual or fully automatic control. COMBINATION GAS AND OIL BURNERS For Natural or Refinery Gas and/or Fuel Oil. Available in wide range of capacities. Quickly adjustable for the combustion of either fuel alone, or both in combination. Of special value where fluctuating comparative costs of these fuels call for equipment suited to change over without time-consuming structural changes. * Maintenance and operation are reduced to a minimum by compactness and sim plicity of design . . . accessibility of all parts . . . rugged construction and positive overall efficiency. , Design features eliminate possibility of escaping gas due to structural distortion . .. prevent stratified combustion resulting from improper air distribution and high gas pressure. Providing sufficient flexibility to care for varying loads, these units assure high furnace temperature and radiant heat transfer with low stack temperature . . . thorough mixture and optimum air-fuel ratio with utmost ease of adjustment. ROTARY FUE1 For firing high or low pressure steam or hot water boilers of all types ... in smaller factories and industrial plants, laundries, dryers and cleaners, office buildings, hotels, apartment houses. Also applicable to industrial ovens, kilns, etc., where furnace and general physical conditions permit. Available with manual, semi-automatic or fully automatic control ... in varying sizes and types . . . for burning light or heavy oil. Horizontal atomizing cup is rotated by OIL BURNERS direct-connected electric motor, assuring constant firing as long as motor is in operation. Motors are of extra' large frame size, air-cooled and built to with stand long, hard service. Positive air-oil interlocking device automatically shuts off oil supply following any burner stoppage. ^ Of rugged construction ... with all parts easily accessible for cleaning or renewing . . . these burners provide a flexible capacity range, with complete and efficient combustion under widely fluctuating loads. TODD MANUFACTURES: Mechanical Pressure Atomizing Oil Burners--VEECEE Variable Capacity Burners--Horizontal Rotary Oil' Burners--Oil Burning Air Registers for Natural, Assisted, Induced or Forced Draft--Inside Mixing Steam Atomiz-; ing Oil Burners--Combination Gas and Oil Burners--Furnace Doors and Interior Castings for Converting Howden Type Furnace Fronts to oil firing--Oil Burning Galley Ranges--Oil Heating, Pumping and Straining Equipment. All installations of Todd Equipment are always individually engineered to fulfill specific requirements. Send for descriptive literature. Todd engineers are always available for consultation and analysis of combustion problems~without obligation. 1182 Heating Systems Burners, on ENGINE & FOUNDRY CO 18th and Florida Streets San Francisco 10, Calif. Combustion Equipment Division Distributors in all Principal Cities Sim "C"--Full Automatic with dual gas-electric ignition for A'o. 6 oil--capacity US B.H.P. Enterprise Rotary Oil Burners are designed for efficient utilization of No. 3 and No. 5 oils, and when furnished with electric pre-heaters for No. 6, or Bunker oils. Ap proved by the-Underwriters' Laboratories, the sizes range from 12 to 330 boiler hp in . the pump type and to 650 boiler hp for gravity feed or with independent pumpset. By addition of a multi-jet gas head in the burner front plate, standard Enterprise Oil Burners . can be converted to a combination unit where natural, manufactured, or process gas is available. -' Enterprise Burners are available with manual, semi-automatic and full-automatic controls, and low fire, two-position or modulating controls. - Enterprise engineers have developed many applications for these burners. where heat is required for industrial processing. The burners are designed for firing high or low pressure boilers of all types for commercial and industrial uses. One of the features of the Enterprise Burner is the V-Belt Drive which offers a wide range of burner flexibility and makes possible the use of standard and modern type motors. The Enterprise design features durability, simplicity, quiet and economical operation. ' 1183 \ Heating Systems Burners, Oil S. T. Johnson Co. 940 Arlington Ave., Oakland 8, Calif. 401 No. Broad St., Philadelphia 8, Pa* Builders of Heavy-Duty Industrial Oil Burners Johnson Industrial Burners are designed to operate on Heavy Oils which produce extra heat at low cost. They increase the capacity of equipment formerly fired with coal and produce desired steam pressures more quickly. Automatic regulation permits the boiler to operate with maximum efficiency at any specified steam pressure, without watching, care or attention, thus reducing labor costs. . They have been installed with marked success in* hotels, hospitals, factories, office buildings and other large structures all over America because they provide heating engineers with a wide range of ' capacities and with every desired feature of economy, performance and automatic control. In their design and in their construction, ' Johnson-Burners represent the new and advanced engineering and building tech niques backed by 42 years of practical experience. Heating Systems Burners, on S. T. Johnson Go. Builders of Domestic and Commercial Oil Burners 940 Arlington Ave., Oakland 8, Calif. 401 No. Broad St., Philadelphia 8, Pa. Self-storage water heaters, separate burner units, burnerboiler units, conditioned air units, range burners and various x( specialized items comprise the line-up of Johnson light-oil Burners. There is a wide range of sizes and capacities in each classifica tion with which heating engineers and contractors can successfully meet every type of problem. Every Johnson Burner is backed by an unbroken 42-year record of fine engineering and excellent craftsmanship. AQULUX WATER HEATERS - Fully automatic, self storage: Cap.: 100 to 640 g.p.h. BANKHEAT BURNERS Fully automatic, pressure atomizing type. Sizes up to 0 gal. per hr. TYPE 30 AVH f Fully automatic. Pre-heater type. Burns No. 6 OU. Six sizes, SO to S00 horse poioer output. TYPE 30 AV Fully automatic. Burns No. 6 Oil Six sizes, to 100 g.p.h. 4 TYPE 28 Manual and semi-automatic. With or 'without built-in pumps. Bums No. 6 and No. 6 Oils. Seven sizes, 'to 136 g.p.h. Illustration shows burner swung away from fire-holeplate for easy inspection. f SELECTAIR HEATERS Hot air, hot water or steam heat. 3 sizes. Bankheat Burners. ECONOLUX HEATERS Heat and hot water. Fully automatic Bank heat Burners. 9 sizes. 1185 Healing Systems Burners, on PetroleumHeat & Power Company Main Office and Factory: Stamford, Conn. Good Oil Burning Equipment . . . "Since 1903" . . . Fuel Oils DOMESTIC OIL HEATING EQUIPMENT PRESSURE ATOMIZING DOMESTIC BURNERS Petra P 0 Burner Models P 20-A, P 21, P 22 In domestic heating this group of Petro burners has wide and general application to steam, hot water, or warm air systems. Burns No. 3 fuel oil (or lighter), heaviest and lowest priced fuel oil approved by UNDERWRITERS for domestic use; They are precision-built atomizing (or "gun" type) burners, with constant electric ignition for reliable safe operation. May be installed with inside or outside fuel storage tanks without adding auxilliary pumping facilities. Order' or inquiry should specify the type, size and rating of boiler or furnace to be fired, together with the total load. Burner Nozzle Model Size Number Cal per Hr. Total Capacity Steam Hot Water Sq Ft Sq Ft AppSh'p'g. Wgt. P-20-A 1.00 350 560 155 1.25 435 695 P-20 To To To 155 2.50 875 1400 Models P 12, P 13-A, P 13 Have wide application in heating large residences, stores, garages and other com mercial buildings. . Approved for No. 3 (or lighter) fuel oil. 2.00 700. 1120 P-21 To To To 160 4.50 1575 2520 3.00 1050 P-22 To To 6.00 2100 ' 6.00 P-12 To - . . 10.00 P-I3-A V-9.00 To 12.00 2100 To 3500 3150 To . 4200 12.00 4200. P-13 To To . ifi.no 6300 1680 To 170 3360 3360 To 215 5600 5040 To 285 6720 6720 To 10080 ` 285 Petro P IS Burner Petro Boiler Units--both cast iron sec tional and. steel--in a range of five sizes covering normal domestic needs, - and Petro Water Heaters and forced warm air furnaces are planned for production in early 1946. Information on this equip ment available at that time. Send for catalog of Petro Domestic Oil Heating Equipment. 1186 Heating Systems Burners, on Petroleum Heat & Power Company Main Office and Factory: Stamford, Conn. Good Oil Burning' Equipment. . . "Since 1903" . . . Fuel Oils INDUSTRIAL AND COMMERCIAL OIL BURNING SYSTEMS FOR AUTOMATIC . . . SEMI-AUTOMATIC ... OR MANUAL OPERATION For Unheated No. 5 or Lighter Oil Model WA--Automatic ignition and oper ation with synchronized control of oil and air. Model W-SA--Semi-automatic, i.e.; auto matic variation of firing rate with manual ignition; or for manual variation and manual ignition. ` bustion efficiency,--is through the heat applied to the oil. Petro's Thermal Vis cosity System controls this heat:applica- tion at its source. Has been used suc cessfully for years, without any need for frequent manual adjustment. . For Heated Oils: Heavy No. 5, No. 6 (bunker "C") oil Model W-AH--Automatic ignition and operation with synchronized control of oil and air and of oil heaters. Model W-SAH--Semi-automatic with oil heaters, i.e.; automatic variation of firing rate with manual ignition; also available for manual. variation and ignition. . CAPACITIES Mode) W-7/2 W-3 W-4 W-5 W-6 W-7 W-8 W-9 ' Motor H.P. H 'A l A 2 2 3 3 Max. Rated Cals, ' Cap. per Hour . BMP. 11 37 15 50 25 84 33 . 110 . 45 151 62 208 100 336 145 487 Sq Ft C.l. Steam Rad. 5.150 7.030 11.720 15.470 21.100 29.100 46.600 68.000 These burners are available for all' electrical current characteristics. PETRO'S THERMAL . VISCOSITY CONTROL The only dependable and accurate control of viscosity--and hence delivered com Model W--Direct Driven, Rotary Cup Type Burner Illustration Shows Modutrol Mounted on Burner This burner is a self-contained assembly of motor, fan, pump, rotary cup atomizer and all air and oil adjustment apparatus. Interlocking air and oil control mechan ism permits any minimum or maximum operation required within the burner's range of operation. Counter-flow Angular Air Vanes at nozzle increase air and oil turbulence and aid efficient combustion of heavy fuel oils. . Special oil adjustment valve meters'oil to rotary cup, yet permits manual opera tion without disturbing permanent burner adjustment. Removable rotary cup and nozzle per mits changing shape of flame to suit re quirements of any boiler and prevent flame impingement. '_ Send for catalog of Petro Commercial and Industrial Oil Burners .' 1187 ' Heating Systems Burners, on H. C. Little Burner Co. Head Office: San Rafael, Calif. Factory Representatives in Principal Cities Fully Automatic Oil Burning Floor Furnace These low cost units are factory assembled, including all controls, ready to hang in floor. Easy installation, ^no basement needed. Natural draft vaporizing burner, automatic operation, with electric ignition and thermo static cpntrol. Inexpensive to operate. Listed by Underwriters' Laboratories for No. 3 furnace oil. Two sizes: No. 70-42--47,250 Btu output (22 in. wide x 28 in. long x 44 in. high); No. 100-42--75,000 Btu out put (22 in. wide x.40 in. long x 45M in. high). Natural Draft, Automatic, Vaporizing Burner Natural draft vaporizing burner specifically designed for No. 3 furnace oil and listed by the Underwriters' Laboratories. Model shown (with controls attached) ' is fully automatic, with electric ignition (no pilot light) and thermostatic control. Manually operated models, which do not require electricity, are also listed for No. 3 oil. Seven sizes: 1.45 qts. to 2% gal- per hour. Aquatherm Water Heaters Economical operation and ample capacity for all domes tic requirements. Aquatherm "30" has 28 gal. storage, 40 g.p.h. recovery rate, is 19 in. wide x 21 in. deep x 56 in. Aquatherm "60" has 60 gals, storage, 160 g.p.h. recovery, is 24in. wide x 36 in. deep x 68 in.. Both units listed by Underwriters' Laboratories for No. 3 furnace oil. Coil Water Heater For camps, auto courts, apartmentsorsmall hotels. Uses separate hot water storage tank. Also makes excellent boiler for hot water installations in home heating. Two sizes: No. 150--106,960 Btu output, 150 g.p.h. (80 rise); No. 250--160,440 Btu output, 250 g.p.h. (80 rise). Winter Air Conditioner Size A, 85,000 Btu output. Size B, 125,000 Btu output. Multivane blower, filters, vaporizing burner. . Ceiling Furnace^ Industrial overhead heating saves floor space. Units are factory assemb led, including vaporizing oil burner (no refractory brick saves much weight), thermostatic control, high capacity heat distributing fan with % hp motor. Conforms to requirement of the Underwriters' Lab oratories for use in garages.. 140,000 Btu output. A complete line of oil-fired small home heating units --plus special industrial units of moderate capacity. 1188 Heating System Oil Burners Water Heaters Air Conditioning Unit Ray Oil Burner Co. 405 Bernal Avenue Since 1872 629 Grove Street San Francisco 12, Cal. Jersey City 2, N. J. Distributors in all Principal Cities Consult your local Telephone Directory Products: A complete line of Horizontal Rotary and Pressure Atomizing Oil Burners; Combination Oil-or-Gas Burners; Industrial Gas Burners; Oil Burning Water Heaters; Winter Air Conditioning Units, Commercial Ranges. / to 1000 hp Type AC. Mon., Semi-Automatic. Semi-Automatic, Type AP-14. for No. 5 oil. Fully Automatic Type AR-13.'f, for No. 5 oil. Fully Automatic Type AR-IH, for No. 6 oil. Fully Automatic Type JP, # ,i or lighter oil. RAY HORIZONTAL ROTARY OIL BURNERS Built in fully automatic, semi-automatic and manual types; in sizes from 1 to 1000 Boiler hp; to burn all grades of fuel oil. Standard models include both direct and belt drives--the latter being recommended for use where other than 50 or 60 Cycles AC, or only DC is available. Types for straight electric or straight gas ignition; Belt Drive Automatic Type BR-I4I, # 6 oil. pump or gravity feeds. Direct drive types include a steam turbine driven model. All fully automatic types for heavy oil incorporate . the Ray Dual Pump and Reservoir, with the Ray VISCOSITY Valve, a patented, exclusive feature which automatically meters the correct amount of fuel at all times, regardless of changes 1 in viscosity of the oil due to temperature variations. All larger sizes employ dual ignition, for maximum reliability. Cas Burner, Type HN, . for high pressure gas. RAY PRESSURE ATOMIZING OIL BURNERS Fully automatic, for No. 3 oil or lighter. AC or DC; capacities to 18 gal/hr. RAY COMBINATION OIL-or-GAS BURNERS Operate on any grade of fuel oil, any grade of natural or manufactured gas. Oil burner sizes to 1000 boiler hp; maximum gas capacity: 43,600 cu ft/hr. Changeover may easily be made in 2 minutes or less. Steam Turbine Drive, Type TO, all grades oil. RAY INDUSTRIAL GAS BURNERS For gas pressures above 1 Ib/sq in. May be used alone or in combination with a Ray Oil Burner. Built in eleven sizes; in capacities to 43,000,000 Btu/hr. Small Capacity (M to 2M gph) rotary burner. RAY WINTER AIR CONDITIONING UNITS Built in four sizes, with input capacities of 140,000, 230,000, 350,000, 450,000 Btu. RAY OIL WATER HEATERS Two sizes. Capacities: 45 and 75 gal. Maximum recovery rates: 154 and 240 gph. 1189 RayOU Furnace, Winter Air Conditioning Unit. Heating Systems Burners, Oil Williams Oil-O-Matic Division EUREKA WILLIAMS CORPORATION, BLOOMINGTON, ILLINOIS OlL^MATlCManufacturers of Auto matic and Manually Con* WILLIAMS trolled Fuel Oil Burners U heating coouno . Manufacturers of Year DDnntirrc 'Round Air Conditioning PKUUUlft Csoymspteremssso,rsIce-O-Matic OIL BURNERS Williams Oil-O-Matic Lo-Pressure burn ers are offered in 5 sizes ranging in capacity from to 15 gallons of fuel oil per oper ating hour. Easily in stalled in any type heat ing plant. Patented Thrift Meter pre-meters oil to exactly meet heat ing plant needs. Wide, non-clogging orifice handles even the heaviest . oils. Williams Hi-Pressure precision-built burners are available for those who want high quality at minimum cost. 3 sizes with capacities from .65 to 7 gallons per hour. How to Decide Siw of Burner For low pressure domestic boilers, 1 gal of fuel oil per hour (HO,000 Btu) is re quired for approximately 300 sq ft of steam radiation or its equivalent, or for 480 sq ft of hot water radiation or its equivalent. 70,000 Btu when using hot air furnace ratings. 24 sq ft steam boiler heating surface (or 2.2 hp). For exact data, see Oil-O-Matic Installation and Service Manual. Oil-O-Matic Lo-Pressure Burners ____ Leg or Flange Mt. Model K-150 K-3 K-4.5 K-7 J-1800 Oil Capacity Min. Max. .50 1.50 1.00 3.00 1.35 4.50 4.00 7.00 8.00 15.00 Motor Hp Rpm 1/10 1800 1/10 1800 1/5 1800 1/5 1600 1/2 1800 Atom. Pressure 2 lbs 2 lbs 2)/i lbs 3 tbs 4 lbs Williams Hi-Pressure Burners Leg or Flange Mt. HP-1 .65 1.50 1/16 1725 100 lbs HP-3A 135 3.00 1/12 1725 100 lbs HP-7 3.50 7.00 1/5 1800 100 lbs WINTER AIR CONDITIONERS Williams Oil- O-Matic Winter Air ` Conditioners automatically draw in air, filter, heat and humidify it, and gently cir culate the condi tioned air to all rooms. 3 sizes fill all needs. -Choice of Lo-Pressure or Hi-Pressure Burner. Oil-O-Matic Winter Air Conditioners Model Btu at Bonnet C.F.M. Oil (a) Vf Input SP. G.P.H. Filters Sq In Blower Motor 10 100.000 ' 1300 1.00 1000 `/rhp 15 150.000 1800 1.50 1920 Va bp 25 250,000 2400 2.50 2400 M hp BOILER BURNER UNITS Williams Oil-O-Matic Boilers are available in 3 models: Lo-Boy (illus.) in 4 sizes for steam, 4 for hot water; Water. Base in 3 sizes for steam, 3 for hot water; Resi dential Steel in 4 sizes for steam, 4 for hot water. All units furnished complete with either Lo-Pressure or Hi-Pressure burners. Oil-O-Matic Cast Iron Boiler Burner Units Model Net Load Ratings I.B.R. Cross I.B.R. Steam Water Sq Ft Sq Ft Btu Oil Input GP3L Output Btu LB-55 or 5W LB-6S or 6W LB-8S or 8W LB-IQSor I0W 360 580 450 720 620 990 760 1250 86000 1.35 130000 108000 1.65 162000 149000 230 222000 187000 2J5 278000 Oil-O-Matic Cast Iron Water Base Boiler Burner Units I6S or 16W 2QS or 20W 24S or 24W 290 460 350 560 410 660 69000 1.05 105000 83000 1.25 126000 98000 1.50 147000 Oil-O-Matic Steel Boiler Burner Units 32QS or 320W 320 510 '76800 1.10 118000 40QS or 4Q0W 400 640 96000 1.40 146500 54GS or 540W . 540 860 129600 1.90 195000 68QS or 680W 680 1090 163200 2.30 244000 WATER HEATERS Oil-O-Matic Water Heaters compact, com pletely automatic, selfcontained units. Lo-Pres sure burner handles even heaviest oils for utmost economy. Oil-O-Matic Water Heaters--Horizontal Type Heating Model Storage Capacity Capacity Per Hr 90 Rise Oil Input Per Hour Atom. Pressure Min. Max. . W.H.A. WJ-LB. W.H.C. 35 gal 60 gal 35 gal 120 ial LOOgal 100 gal 210 gal 1.00 gal O/a gal 2 lbs 2 lbs 2 lbs v*a^jC Compressor Unit.; All temperature ranges. Capacities */4 hp through 5 hp. Air or water cooled. Air-O-Matic ALourpLon Unite; 10 awl 15 ton nuoin&l capacities. Low pressure steam, water-chilled type, hermeti cally sealed units- : 1190 Healing Systems Burners, on York-Shipley, Inc. . York, Pa. YORK HEAT OIL-BURNING EQUIPMENT INDUSTRIAL DIVISION DOMESTIC DIVISION YORK HEAT SELF-CONTAINED BOILER-BURNER UNITS v* FOR FUEL OIL A complete line of fully-automatic selfcontained boiler-burner units is available, in capacities of 4 hp to 100 hp. These are constructed for both 15 lb and 100 lb steam operation. Larger sizes are equip ped with an oil-burner for No. 5 or No. 6 fuel oil. Model AHPBDM Pump-Typt Burner for Bunker C oil. belt-driven, with fully-automatic and full-modu' lating firing control. YORK HEAT INDUSTRIAL HORIZONTAL ROTARY TYPE OIL BURNERS A range of sizes is available from 45 Boiler hp to 400 Boiler hp. These burners are built in both direct-drive and belt- driven motor applications. Models for using No. 5 and No. 6 oils are available for manual, semi-automatic, and full modulating control. . The basic frame sizes are listed as follows: A FrameB Frame C Frame D Frame 45 hp to 60 hp 60 hp to 125 hp 125 hp to 225 hp 225 hp to 400 hp York Heat Horizontal Rotary Burners are equipped with many exclusive and patented advancements, designed to insure high efficiency and superior operation. Outstanding among these exclusive York Heat features are: () The Iris Shutter, which gives abso lute control of the burner air. It causesthe metered volume of air to remain con stant, insuring perfect combustion. () The York Heat Flame Former, which makes possible accurate flameadjustment, to suit the combustion chamber. Model N-15 York Heal Domestic Oil Burner. VOPK HI? AT DOMESTIC OIL-BURNERS This complete line of pressure, atomiz- ing-type burners carries the Underwriters* and Bureau of Standards approval for liquid fuels up to and including No. 3 fuel oil. Models and capacities are listed as follows: C-5 0.7 to 2.25 gph of oil . N-15 1J4 to 4J4 gph of oil N-25 3 to 5H gph of oil N-35 5 to 10 gph of oil . T-45 8 to 18 gph of oil T-55 16 to 30 gph of oil YORK HEAT DOMESTIC HEATING UNITS York Heat offers a complete line of domestic heating units, in a full range of capacities. These can be furnished for steam, hot water, and forced warm air applica tions. (c) The torch-type pressure igniter, for York Heat Domestic Boilersmoother and positive automatic starting. Burner Healing Unit. 1191 Heating Systems Boner compounds The Vinco Company, Inc. 305 East 45th Street . New York 17, N. Y. Only a clean boiler can be an efficient boiler. A clean boiler means saving fuel, as well as safeguarding boiler metal. Both are now a patriotic duty. yiNco <&mnES'vo ffttINGSTSIt# Boiler Cleanser S and 6 lb. Cans A positively harmless insoluble powder cleaner for new, remodeled and old heating systems. A unique, scientifically processed compound on a special formula not to be confused with other powder boiler cleaners. What Vinco Boiler Cleanser Does Vinco removes oil, grease, scale, rust and dirt from the internal surfaces and from the boiler water without the labor, expense, and uncertain results of blowing boilers over the top or of wasting returns. By this thorough cleaning Vinco prevents or cures foaming, priming, surging, and slow steaming. / How Vinco Boiler Cleanser Works Each minute grain of Vinco powder adsorbs several times its own weight of oil, rust and dirt. These larger grains of adsorbed impuri ties then settle and are drained through the bottom according to directions on each can. Vinco Guarantees 1. Vinco contains no potash, lye, soda of any kind, oil, acid, or other harmful ingredients. 2. Purchase price is refunded if results are not as claimed when Vinco has been used according to directions. VINCO RUST PREVENTER When used after Vinco Boiler Cleanser has removed oil, grease, rust, scale and dirt, it will add and keep the rust inhibiting factors at the optimal constant for a year or more. (Test kit below has complete instructions and chart.) \ Rust Preventer 1 ql cans only VINCO TEST KIT No. 10 for Testing and Treating Heating Boiler Waters Vinco Test Kil No. 10 (Patent applied for) The kit enables the layman to make simple, rapid tests to diagnose and prescribe correct treatment of boiler waters right on the Job. A new time saving method that permits valid conclusions heretofore requiring complicated and often lengthy laboratory analysis and technique. . Each kit has sufficient material for complete tests on 100 jobs. Refills cost about 2 cents for testing each job. ' 1192 The Vinco Companyt Inc. Heating Systems Boiler compounds SPECIFICATIONS FOR COMPLETE VINCO TREATMENT OF NEW OR REMODELED STEAM, VAPOR, OR HOT WATER SYSTEMS Do not use as a cleaning agent soda or any alkali, vinegar or any acid. ,, Use Vinco. - 1. AFTER THE SYSTEM IS TEST ED AND TIGHT, USE THE PROPER QUANTITY OF VINCO LISTED. After this first clean-out of any new or remodeled heating system, Vinco Boiler Cleaner need be used only if more piping, radiation, or another boiler is added to the original installation, or if the system is fouled by unwise cleaning or leak-sealing experiments. 2. After using Vinco Boiler Cleaner, Vinco Field Test Kit should be used to determine and apply the proper quantity of Vinco Rust Preventer. Vinco Rust Preventer should be applied annually or whenever the boiler water is drained tor necessary repairs to the system. SPECIFICATION FOR OLD HEATING SYSTEMS THAT DO NOT PERFORM PROPERLY Diagnose and treat according to Vinco Field Test Kit. If a test kit is not avail able, consult table of quantities on this page and follow directions on Vinco cans. SPECIFICATION FOR HOT WATER SYSTEMS Use half quantities listed for treatment of steam systems to remove impurities. Then use test kit to determine proper quantity of Vinco Rust Preventer. VINCO SOOT-OFF CONSULT THIS TABLE FOR NEW AND REMODELED HEATING SYSTEMS AND. When a Vinco Field Test'Kit No. 10 is not available if cleaning old beating systems. QUANTITIES OF VINCO (IN POUNDS) RE QUIRED FOR HEATING SYSTEMS (Note that quantities are based on actual installed radiation, not on boiler capacity.) Sq Ft of Radiation For Steam or Vapor System*, topreventorcure priming or foam ing. Also for Hot Water Heating Systems Maintuned at approx. 200 F or above. Annually, to re move rust scale, dirt and for Hot Water Systems below 200 F. up to 350.......... 351 - 600.......... 601 * 1100.......... HOI 1400.......... 1401 " 1800.......... 1801 2100.......... 2101 2700.......... 2701 3100.......... 3101 3700.......... 3701 4200.......... 4201 " 4600.......... 4601 - 5000.......... 5001 5300.......... 5301 * 5600.......... 5601 " 5900......... 5901 6200.......... 6201 6500.......... 6501 " 6800.......... 6801 7100.......... 7101 - 7400.......... 7401 7700.......... 7701 " 8000.......... 6001 * 8300.......... 8301 8600.......... 8601 8900.......... 8901 - 9200....... 9201 - 9500.......... 9501 " 9800.......... 9801 10100*........ 3 5 8 10 13 15 18 20 23 26 26 30 31 . 32 33 34 35 36 37 38 39 40 41 42 43 44 * 45 46 47 m 2Vi 4 5 6/i 7*4 9 to II'A 13 14 15 15*4 16 I6A 17 I7Vj 18 18>/2 19 19*4 20 20>A 21 21*4 22 22*4 23 21Vz . . Above 10100 sq ft use an additional pound Vinco for each additional 300 sq ft of actual installed radiation. ' Safely and thoroughly removes the insulating blanket of soot on fire pot, flues and chimney. It also insures against external corrosion (caused by dampness and soot forming sulphuric acid during summer layoff.) No dangerous chemicals. Soot-Off--1 lb cans 60 and 100 lb drums REMOVE SOOT WITH VINCO SOOT-OFF SEVERAL ' TIMES A YEAR VINCO SUPERFINE LIQUID BOILER SEAL A different liquid seal. Unique in that it does not induce priming and foaming. It has no unpleasant smell. Makes speedy and permanent repairs of boiler and heating system leaks. Fine to tighten up new jobs. Directions simple. '. V?NC0 ... . Quantities . Steam and Vapor Systems--Use 1 quart Vinco Liquid Boiler Seal to each 6 sq ft grate area. ' Hot Water Systems--Use 2 quarts Vinco Liquid Boiler . Seal to each 6 sq ft grate area. . 1193 Liquid Boiler Seal t ql. cans only '\ Heating Systems Boner Feeders M-DONNELL & MILLER Safety Devices for Steam and Hot Water Boilers and Liquid Level Controls General offices: Wrigley Building, Chicago 11, Illinois PRODUCTS: Doing oneSA/(hing well Boiler Water Feeders; Feeder Cut off-Combinations; low Water FuelCut-offs; Pump Controls; Low Water Alarms; Humidifier Water Level Controls; Safety Relief Valves for hot water heating boilers and storage tanks; High and Low Oil Switches and Liquid Level Con trollers for a wide range of services. The service range and types of in stallations covering most common applications of McDonnell Boiler Water Level Controls are described here. For facts concerning pro tection of process boilers, or any special information, consult our engineering department. McDonnell Combined Boiler Water Feeder and Low Water Cut-off McDonnell No. 1,7-8 for healing boilers under 6000 McDonnell No. 6t-S for healing boilers over 6000 sq. ft. capacity. Maximum steam pressure, 5 lbs. sq. ft. capacity. Maximum steam pressure, 85 lbs. A typical installation of the McDonnell . No. 47-2 Combined Boiler Water .Feeder and Switch is illustrated above. The water feeder maintains safe level by feeding when water line drops. In case of foaming and priming or failure of water supply, causing water level to drop to in. in the water flass, low water switch comes into action. or automatically fired boilers switch may be wired to cut current to burner. For hand fired boilers switch may be wired to com plete alarm bell circuit. Also furnished for hand fired boilers without switch--desig nated No. 47. Installation time is cut to minimum by QuickHook-Up Fittings for gauge-glass installation. Valve mechanism is iso lated from the heat of the float chamber. Large area straightthrough blow-off valve is standard equipment. The McDonnell No. 2 Switch, used in the No. 47-2 is Underwriters' ap proved. Electrical rating: a-c.;*$ hp' 110-220 V.; d-c.. 10 amp. 115 V. The -illustration above shows a typical in stallation of the McDonnell No. 51-2 Com bined Boiler Water Feeder and Switch used for larger boilers. This combination func tions the same as the No. 47-2, the feeder taking care of normal requirements and the switch safeguardingagainst emergencies by cutting off the burner in automatically fired boilers or completing a low water alarm circuit for hand fired installations. The feeder is also furnished for hand fired' boilers (as No. 51) without low water cut-off and alarm switch. Basic features of the No. 51-2 are the same as in the No. 47-2, except that it is installed with 1 in. equalizing pipe instead of the McDonnell "Quick-Hook-Up" and has the larger , feeding capacity required for larger boilers. For boiler operating at pressures from 35 lb to 75 lb use the McDonnell No. 53-2 (with switch) or No. 53'(without switch). Electrical rating of switches used in No. 51-2 or 53-2 is the same as previously given for the No. 47-2. 1194 McDonnell & Miller Heating Systems a Boiler Feeders McDonnell No. 67 Low Water Cut-off for automatically-fired steam boilers of any size. Maximum steam pressure, 25 lb . The No. 67 takes care of low water cut-off requirements of automatically fired boilers with steam pressure below 25 lbs. It has the McDonnell "Quick-Hook-Up" for quick, easy and trouble-proof installation in the gauge glass tappings; deep sediment chamber with large quick opening blow-off; packless, non-binding construction; adjust able terminal box to make wiring neat and easy; dependable, snap-action, twin switches. One switch closes on small drop without stopping burner. It can be used to complete an alarm bell circuit, warning of ap proaching low water, or can be used to complete circuit to the . McDonnell No. 101 Electric Water described below. Second switch cuts current to burner if water level drops to M inch in gauge glass. Underwriters' ratings for both switches: a-c.. % hp. 110-220 V.; d-c H hp. 115-230 V. McDonnell No. 101 Electric Boiler Water Feeders for boilers up to 5000 sq. ft. capacity The No. 101 is an electric water feeder for use with No. 67 Low Water Cut-off or with McDonnell "built-in" Low Water Cut-offs which are standard equipment on many modem heating boilers. It converts the cut-off into a combination boiler water feeder and low water cut-off as described on the opposite page. McDonnell No. 150 Pump Control, Low Water Cut-off and Alarm Switch for boilers of any size. Maximum steam pressure, 150 lb This boiler water level control may be used as a pump control, a low water cut-off, a low water alarm been restored. . If emergency occurs and water level falls to arrow mark on body of control, cut-off switch stops burner. If steam pump is used, No. 150 is wired to switch, or, any combination of these func tions. Elec trical ratings are: a-c., 1 hp, 110-220 V., d-c, M hp, 110-220 V.~as pump control or cut-off; 1 amp. 110 V, V-c. or d-c--as low water alarm. No. 150 has automatic reset low water cut-off switch but may be' ordered with manual reset as No. 150-M.;. A typical hook-up of the McDonnell No. 150, controlling an electric pump and' providing low water, cut-off, is shown opposite. When water level drops % m* below normal. No. 150 starts pump and then stops it when norma! water line has pump. Note that McDonnell No. 51-S Feeder is used to supply make-up water to the pump receiver. Drawings available covering use of No. 150 on two or more boilers supplied by a common feed pump; ask for No. 150 Data Book. McDonnell Safety Relief Valves The No..29 series of Safety Relief Valves have "snap action"--a mechanical means . of opening full orifice capacity at precise instant set pressure is reached. Resulting large discharge capacity makes it feasible to rate them in heat dissipa ting capacity"so they can be matched to Btu. output of unit, on which they are in stalled, thus preventing . over-pfessures and protect- 1 ing against^explosions. ' Stainless steel cone re places conventional cbmNo. 29\C ..position disc. \ Long-lived, compact bellows replaces broad diaphragm of ordinary valves. Testing lever is easy to operate. All valves comply with A.S.M.E. code. , (1) For Hot Water Heating Boilers - Valve No. Opening Pressure Btu. Output 29 . 129 29 lbs 29 lbs 156.000 350.000 (2) For Domestic Hot Water Heaters and Tanks ..Valve No. Opening' Pressure Max. Water Supply Pres. Btu. Output .. 229 - 329 .429 " 75 ibs * lOfrlbs 1150 lbs . 50 Ibs 75 lbs 100 lbs 316.000 380.000 432.000 1195 Heating Systems < w.t.r Bell and Gossett Company Morton Grove, Illinois . HOT WATER SYSTEMS AND SPECIALTIES B &G Forced Hot Water Heating Systems To a postwar world demanding improved ways of doing old things, B & G Forced Hot Water Heating contributes better heating at lower installation and operating cost. It is a system in which the heat input is accurately and auto matically controlled to equal the heat loss. Water can be circu lated through a long range of temperatures, hence permits close adjustment of the heat supply to the actual need for heat. Operating equipment is extremely simple--an assurance of dependable performance. HC COHmSSX 7AM Q=> : B & G Boosters An electrically-driven centrifugal pump, used to me chanically circulate water through B & G Forced Hot Water Heating Systems. It is distinguished by genuine oil lubrication, patented water-tight seal, exceptionally quiet operation and precision manufacture throughout. B & G Universal Pumps D > The B & G Universal Pump is designed for large forced hot water heating systems in apartment buildings, office buildings, factories, schools, etc. The installation can be operated as a large single zone or divided into several zones in which circulation of the pumped water in each circuit is controlled by a B & G Motorized Valve, operated by a zone ther-' mostat. . B & G Angle Flo-Control <--<5 Valves This valve, installed in the main, shuts off circulation to radiators when heat is not needed, permitting summer operation of a B & G Indirect Water Heater. It also helps maintain a uniform room tem perature during the heating season. 'B & G Motorized Valves m-*- Thermostatical ly operated valves used for control ling boiler water flow through the individual circuits of zoned heating systems. <--& B & G Monoflo Fittings B & G Monoflo Fittings permit the use of a single pipe main, instead of the conventional flow and return lines. It is installed at the junction of the radiator risers to the single main and assures the diversion of the proper amount of heated water into each radiator. Savings in space, labor and materials are obviously effected. SEE THE B & G HANDBOOK. FOR COMPLETE DESIGNING DATA 1196 Bell and Gossett Company Heating Systems Hot Water Heating Heat Transfer HOT WATER SYSTEMS AND SPECIALTIES B & G Relief Valves For relieving excess boiler pressures in hot water heating systems, and in the lines of service water systems. B & G Relief Valves have the design features which as sure dependable service. B & G Reducing Valves Fast operating valves for keeping hot water heating systems properly filled. Easily adjusted to meet varying building heights. Also high pres sure reducing valves for protection of plumbing fixtures. <--$ B & G Compression Tanks Essential equipment for closed hot water heating sys tems. Expansion of heated water is taken up by the tank, providing a cushion of compressed air against sudden pressures and water hammer shocks. Ori high temperature installations, the Tank develops sufficient pressure to prevent boiling of the water in the system. B & G Indirect Water Heaters B ' > Any steam, vapor or hot water heating boiler can be equipped with a B & G Indirect Water Heater. With the proper electrical controls, the Heater will furnish an ample supply of hot water, winter and summer, at very low operating cost. Heater must be used with a storage tank of suitable capacity. ' B & G Steam Convertors Extensively used when steam is required in the factory for power or process work, but where the benefits of mechanically circu lated hot water are desired for the heating system. Steam is passed through the convertor shell, heating the water circulated through the tubing. ' ^ * < (S B & G Type "SU" Instantaneous Water Heaters For heating water with steam. Ideal for industrial plants or wherever large volumes of hot water are required continuously for service water supply or pro cess work; No storage tank re quired--the large heat transfer surface in these units heats water instantly as needed, 4--@B & G Centrifugal Pumps Design and construction based on years of experience in the industrial `*1 field. Rugged, compact units-- built to stand up under the strain of continuous operation. Available with semi-open or enclosed impellers --motors flexible coupled or integral with pump. Send for Catalog. Send for Your Copy of the B & G Handbook B > . A single authoritative source of information on the design and installation of Forced Hot Water Heating Systems and Service Water Heating Systems. Packed with data and tables of every day value. Yoiir copy will be sent on request*. 1197 TJ Heating Systems water H. A. Thrush & Company Peru, Indiana Representatdves In Principal Cities FORCED CIRCULATING THRUSH FLOW CONTROL SYSTEM OF HOT WATER HEATING AND HEATING SPECIALTIES Flexible, economical of fuel, forced circulating Thrush Summer-Winter System of Hot Water Heat is the most satisfactory way to heat buildings. Thrush Systems, Water Circulators, Water Heaters, Pressure Relief and Pressure Reducing Valves and other fuel-saving heating specialties are available. - today for information or engineering assistance. Patent Nos. 2,054.009. 2.111.441, 2.257.867, 2.356.482 THRUSH WATER. CIRCULATORS . Five sizes, 1 in., 1\4 in., 1M in., 2 in. and 3 in., for forced circulation in Hot Water Heating and Domestic Water Systems. Save fuel, insure uniform heating! Patent Reissue No. 19,873 Number 4 Illustrated THRUSH FLOW CONTROL VALVES For use with Thrush . Water Circulators This patented valve prevents circulation when not required. ' Six sizes, 1 in., 1)4 in., 1)4 in., 2 in., 2)4 and 3 in. Work auto matically by pressure head, generated by Thrush Circulator. THRUSH LOW PRESSURE WATER RELIEF VALVES Protect.heating boil ers from excess pres sures. Made in angle or straight types, of iron or brass, sizes )4 in., % in. and 1 in. Unfailing depend ability has been proved by over a quarter of a century of successful, opera tion. ''` THRUSH PRESSURE REDUCING . VALVES; Types for High and Low Pressures Sizes, )4 in., 34 in. and 1 in. Low pressure reducing, valves to reduce pressure of water entering heating system and maintain water supply in system automatically. High pressure reducing valves for protect ing house plumbing and heating equipment from excessive city line pressures. \ THRUSH AIR-TIGHT PRESSURE TANKS An essential part of every hot water heat- . ing system. Conserves water and fuel, be cause the heated water expands into the Thrush Pressure Tank and returns to the sys tem as it cools. Adds to the continued oper ating .efficiency of the heating, system over a long, period of time. 1198 H. A. Thrush & Company Heating Systems Hot water THRUSH HIGH PRESSURE WATER RELIEF VALVES Protect water supply or range boilers and gas or electric water heaters from excess pressure and . temperature (some types). Made in angle or straight types, of iron brass, sizes, )4 in., % in. . and 1 in., for pressure relief only or combina tion pressure and tem perature relief. THRUSH DUAL CONTROL UNITS * Provide automatic pressure relief, reduce line pressure, automatically fill and main tain water supply in hot water heating system. Built-in strainer. Made in four types, brass or cast iron, )4 in. or % in. THRUSH WATER HEATERS Highly efficient heat exchangers or con verters. Sixteen sizes, for Hot Water or Steam. Pressure up to 150 lb. Straight tubes readily cleanable. Provide Domestic Hot Water at low cost. Also used in dustrially for heating or cooling liquids. THRUSH SUPPLY TEES FOR ONE PIPE SYSTEMS Assure positive diversion to ra diators. Made in four sizes, 1 in., 1)4 in-, 1)4 . in. and 2 in., with branch outlets of \4 in., % in. or 1 in. Automatically maintains room tempera ture within a fraction of a degree. Controls both room and water temperature in the radiators, compensating to prevent varia tion in room temperature..or a lack of . No. 210 THRUSH DIFFERENTIAL- TEMPERATURE- -Requires No. I9S CONTROL - Thrush Relay . - Transformer Special dual acting thermo stat--one bulb inside and- one ` bulb outside building. Auto matically main tains correct in door tempera ture with any weather change. radiant heat. Requires No. 198 Thrush Relay Transformer for low voltage. THRUSH MODULATING BOILER WATER TEM PERATURE CONTROL No. 203 with dual bulbs, automaticcally varies boiler water temperature to meet all demands for heat. Main tains correct boiler water tem perature, A real fuel- and^ thussavingfuel. money-saver, . Other electrical especially for water temperature apartment . controls, No. 202', houses, or No. 205 immersion groups of industrial, tourist camp or other and No. 206 clamp- buildings with one central heating plant. on type, available. WRITE FOR COMPLETE CATALOG 1199 Heating Systems Hl waui Taco Heaters, Incorporated 342 Madison Avenue, New York 17, N. Y. Taco Heaters of Canada, Ltd., 24 Adelaide St., W., Toronto 'T'HERE is a storage or tankless, Biltin or external, type Taco indirect water Heater 1 for every job--for use with patented Taco-Abbott System. Biltin Taco Heaters, which are standard equipment on leading heating boilers, are catalogued only in the boiler catalogues. For additional information on Biltin Tacos write boiler manufacturer or Taco. ` Complete catalogue information on external Taco Heaters is also available for home, apartment house, hotel and housing projects. Domestic Tacos Tankless Taco Nos. IS, 14, IS and 18 Multi-coil Taco "Taco-One" Venturi System A forced circulating warm heating system using a single pipe main from boiler to radiators and back again. Small pipes and one pipe main make a neater job, reduce installation costs. Radiators can be placed above and below main. 85 per cent of residential jobs need only one circuit which requires no balancing valves. This revolutionary heating system is made possible by the Taco Venturi Fitting and remarkable Taco Hy-Duty Circulator. Taco Venturi Fitting--Acts as a suction pump in Which the only moving part is water. Water does the trick by producing a vac uum pull that draws water through each radiator, giving positive uniform Taco Venturi Fitting (Cross Section) 1200 Healing Systems Pumps Buffalo Pumps, Inc. 450 Broadway, Buffalo, N. Y. Sales Representatives Albant 7. N. Y., Mr. R. B. Tavlor, 1303 Standard Bldg. Atlanta 2. Ga., Mr. J. J. O'Shea, 30S Techwood Drive Baltimore 2, Md., Mr. C. A. Conklin, III, S08 St. Paul St. Boston 76, Mass., Mr. E. D. Johnson, 507 Main St.. Melrose Station Chicago 6, 111., Emmcrt 4 Trumbo, 20 N. Wacker Drive Cincinnati 2, Ouio, Mr. F. W. Twombly, 626 Broadway Cleveland 13, Ohio, Mr. T. A. Wcager. 418 Rockefeller Bldg. Kitchener, Ontario, Canada Pumps. Ltd., Mr. A S. Capweil Dallas 1, Texas, Mr. T. H. Anspacher, 1801 Tower Petroleum Bldg. Davenport, Iowa, D. C. Murphy Co., Inc.. ' 305 Security Bldg. Denver. Colo., Mr. C. 0. Voight, Sterns-Roger Mfg. Co., 1718 California St. Detroit 16, Mich., Coon-DeVisser Company, 2051 W. Lafayette Blvd. Des Moines 9, Iowa, D. C. Murphy Co., 214 Old Colony Bldg. Greenville, S. C., Mr. Roy A. Stipp . Indianapolis 4, Ind., S. E. Fenstennaker 4 Co.. 937 Architects 4 Builders Bldg. Los Angeles 13, Calip., Mr. F. Halladay, 804 Pershing Sq. Bldg. Minneapolis 2, Minn., Mr. E. F. Bell, 2102 Fosnay Tower Newark 2, N. J., Mr. G. C. Norman, 27 Washington St New Orleans 12, La_ Devlin Bros.. 1003 Maritime Bldg. New York 7, N. Y., Koitban 4 Johnson. Room 1110, 39 Cortlandt St. New York 7, N. Y,, Mr. W. A. Wagner, Room 1113. 39 Cortlandt St. Omaha 2, Neb., Wain Engineering Co., Mr. M. EL Wain, 300 Brandeis Theatre Bldg. Philadelphia 2, Pa , Davidson 4 Hunger. 1200 Cunard Bldg. Pittsburgh 22,'Pa.. Mr. H. L. Moore. 431 Fulton Bldg. San Antonio 6, Texas, Langhammer Rummel Co., 436 Main St. Seattle, Wash., Consolidated Service 4 Supply Co.. 71 Columbia St. St. Louis 3, Mo., J. W. Cooper, 2726 Locust St. Toledo, Ohio, Mr. C. M. Eyster, 1118 Madison Ave. ` San Francisco 11. Calip., Harry W. Parsons, Inc., 24 California St Washington 5, D. C.. Mr. G. S. Frankel. ' 512 Woodward Bldg. PRODUCTS--A complete line of Single and Multi-stage Centrifugal Pumps and Special Pumps for use in all types of heating and air conditioning installations. Buffalo Single Suction Close-Coupled Pumps Buffalo Self-Priming Single and Double Suction Centrifugal Pumps This pump is close-coupled to electric motor, eliminating the necessity for bear ings. The impeller is overhung on the motor shaft, providing a compact, easilyserviced unit. Permanent alignment is assured and the pump mounted in this manner requires very little space. Buffalo Close.- Coupled Pumps are suitable for. handling hot water with low submergence on suction, or for operating with suction lift as high as 25 ft. These pumps are also available in special alloys. Now available with positive self-priming device built with the pump. This primer is built under license from the Nash Engi neering Company and is fully covered by patent. Buffalo Self-Priming Pumps offer these advantages: (1) All working parts are above the liquid to be pumped. (2) There is complete access to all parts of instal lation. (3) Rotors are balanced--vibra tionless. (4) Buffalo Self-Priming Pumps are very quiet--no long shafts to vibrate and fewer bearings. (5) Constant positive prime obtained without foot valves. Buffalo Double Suction Single * Stage Centrifugal Pumps Buffalo Automatic ' Sump Pumps Buffalo Sump Pumps are self- contained and have unusually high efficiencies ' thus permitting For general service where clear water is the use of small handled you will get top performance with motors. Ball these pumps. They embody all of the bearing thrust accepted modern, features of centrifugal and enclosed shaft pump design. Capacities range from 10 to especially adapt 50 thousand U.S. gallons per minute. these pumps for their service. 1201 . Heating Systems Pumps The Nash Engineering Company 234 Wilson Road South Norwalk, Conn., U. S. A. Sales and Service Offices in all Principal Cities - Return Line Vacuum Heating Pump Standard with the heating industry for over seventeen years. Removes air and conden sation from return lines of vacuum steam heat ing systems, discharging air to atmosphere and returning water to the boiler. . Two independent units are combined in a single casing--an air unit and a water unit. Impellers of both are mounted on the same shaft. Pump is bronze fitted throughout. Supplied direct connected.to standard elec tric motors, for belt drive, or for steam turbine drive. For continuous or automatic operation. Standard in capacities up to 300,000 sq ft E.D.R. Larger units special. Bulletins Nos. 307, 308, 309, and 310 on request. Vapor Turbine Vacuum Heating Pump Jennings Vapor Turbine' Heating Pumps combine all advantages of the standard return line heating pump with a new type of drive, a specially designed low pressure turbine which operates directly on steam from the heating mains on any system, requiring a differential of only 5 in. of mercury, and returns that steam to the heating system with practically no heat loss. This pump affords the safety and economy which goes with continuous condensation re turn and steady vacuum, and at no cost for electric current. Furnished standard in capa cities up to 65,000 sq ft E.D.R. Larger units special. Bulletin No. 290 on request. Condensation Pump and Receiver Removes the condensation from radiators in return line steam heating systems, particularly radiators set below the boiler water line level, and pumps the condensation back to the boiler. Pump is bronze fitted with enclosed centrifugal impeller of improved design. By making the pump casing a part of the return tank, and bolting the motor base to the.tank, floor space is conserved. The rectangular construction permits installation in a corner against the wall. These pumps are furnished in standard sizes - with capacities ranging from 1H to 225 gpm of water. For serving up to 150,000 sq ft of equivalent direct radiation. Bulletin No. 319 on request. ~ *. 1202 w Heating Systems Pumps The Nash Engineering Company 234 Wilson Road South Norwalk, Conn., U. S. A. Sales and Service Offices in all Principal Cities SEWAGE EJECTOR For pumping unscreened sewage or drainage from basements below the street sewer level, handling crude sewage from low level districts, pumping effluent, sludge and other heavy . liquids. The Jennings Sewage Ejector is of the pneumatic type. Air, compressed only to the pressure at which it is used, by a Nash Hytor Air Compressor, is motive power to pump the accumulated sewage from a pot to the sewer. There are no air storage tanks, reciprocating air compressors of screens, no air valves. Furnished in several standard sizes up to 1500 gal. per minute against heads up to 100 ft. Bulletins on request. Suction Sump and Sewage Pumps Jennings Sump Pumps are self-priming cen trifugals for handling seepage water and liquids reasonably free from solids. Sewage Pumps are equipped with non-dog type im peller for liquids containing solids. Suction . piping only is submerged. Centrifugal impeller and vacuum priming rotor are mounted on same shaft that carries rotor of the driving . motor, forming a single moving dement, ro tating without metallic contact. . Will handle air or gas with liquid being pumped, and because of self-priming feature . are installed entirely outside of pit, affording perfect accessibility for inspection or cleaning. * Capacities to meet-all requirements. Bulletins Nos: 159, 161*,~and 338 on request. . Air Compressor and Vacuum Pump : Nash Air Compressors operate on a unique and different principle. The one moving part rotates in casing without metallic contact. There is nothing to wear, and no internal lubrication. , . Nash Compressors ddiver absolutely clean' air; ideal for agitation of liquids, pressure displacement, and handling gases. Vacuum pumps ideal for priming pumps, blood sucking pumps in hospitals, and wherever non-pul sating vacuum is required. '! Pressure 75 lb or vacuum 27 in. of mercury. Furnished for any capacity; special for higher - vacuums and pressures. Bulletins Nos. 282, . 325, 331 and 337 oh request. 1 1203 Heating Systems Pua,P, Chicago Pump Company 2330 Wolfram Street BRUnswick 4110 ' Chicago 18 PRODUCTS--Return Line Vacuum Heating and Boiler Feed Pumps, Con densation, House, Booster, Fire Pumps, Circulating, Brine, Sewage, Bilge, Sludge, Pneumatic and Tankless Water Supply Systems and Automatic Alternator for Duplex Sets of Pumps. "CONDO-VAC" Return Line Vacuum and Boiler Feed Pump for Heating Systems "Sure-Return" Condensation Pump for Low and Medium Pressure, and Systems up to 75,000 Sq Ft Radiation Fig. 10--Duplex "Condo-Vacs'' with Duplex Double Automatic Centred No vacuum on stuffing boxes, ample clear ance in rotating member. It costs less to operate a "Condo-Vac." "Condo-Vac" reduces corrosion in piping and boiler to minimum--because pump does not take in air from atmosphere and entirely elimi nates all air coming back from system. "Condo-Vac" is quiet, has a low inlet, entirely automatic, fool-proof, easy to maintain. Ask for bulletin 270. Close-Coupled Pumps Boiler Feed. Circulating, Tank Filling, Water Supply Fig. 1SO--Close-Coupled, side suction pump. Capac ities range from S to 600 Gpm against heads up to 189 ft. Motors from 1/6 to 0 Hp. Discharge l'to 8 in. Closed and open type impellers. Bulletin 108. Fig. 1946 "Sure Return" Condensation Pumps and Receivers are built for systems up to 75,000 sq ft of direct radiation and for low and medium pressures. Built in either single or duplex units. Duplex units are alternated in their operation by the Auto matic Alternator. Complete data in Bulle tin 250. - Vertical Condensation Pumps for Low and Medium Pressure for Systems from 500 to 100,000 Sq Ft Radiation The vertical condensation pump is designed to re ceive returns from lowest radiation. The receiver is placed underground--an ordinary hole sufficing if necessary -- and requires very little floor space. Unit is shipped complete, easy to install, assembled so as to prevent steam leaks. Special bearings will stand up under hot water for several years. A special float mechanism is guaranteed not to leak or stick in stuffing box. Complete data and descrip tion in Bulletins 245, 25S and 255. 1204 Heating Systems s<e.m Rames clones 129 Brookside Avenue New York Office: 101 Park Avenue Boston, Mass. Barnes & Jones Vapor and Vacuum Systems of Steam Heating; Modulation Valves; Adjustable-Orifice Radiator Valves; Packless Quick-Opening Radiator . Valves; Thermostatic Radiator Traps; Thermostatic Trap Replacement Units; Condensators (Boiler Return Traps); Float and Thermostatic Traps; Strainers; Damper Regulators; Gages; Systems of Zone Control for Steam Heating. Complete Catalog on Request Modulation Valves, Series K--Packless Quick Opening Valves, Series F Series K Valves have non-tarnishable indicating dial, non-rising stem, re newable disc seat. Tail piece extra heavy. Extra long to facilitate instal lation. Three mod els: lever handle, wheel handle, lock shield. Series F Valve furnished with wheel handle only. Series K Valve Size...................... ih Cap. Sq Ft Rad.*... 30 >/.60 1* too I1/.' 180 Series F Valve Thermostatic Radiator Traps Sturdily made to precision standards. Sensitive in opera tion. Provide in stant discharge of air and water, pre vents passage of steam. Contains unique Cage Type Thermostatic Unit, which carries its own thermostatic element, valve piece and valve seat, factory cali brated and locked in correct adjustment. Trap Size Capacity and Number Sq Ft.@ l'/2# Patterns Vi'.'/i' #122 200 Ang.-R & LCornerSt'w'y- >/,' i /.' # 134 400 Ang. 4c St'w'y. r X 1' #147 700 Angle only. Size.................................. w >/. 1* W w Y Cap. Sq Ft Rad.*............. 30 60 100 180 270 400 Based on 2 oz pressure differential. Adjustable Orifice Valves, Type H May be adjusted for different capacities after installation. At .. all times provides in dication of the adjust ment. Operation is quiet. Unauthorized tampering with ad justment is virtually impossible. Condensators For returning water of condensation to boiler from open re turn line systems independently of boiler pressure, without change in operating condi tions, air binding, or admitting steam to the return side. No............................. 31 32. 33 34 35 Cap. Sq Ft Rad.*. ... 700 1600 3500 6000 io.ooo Thermostatic Radiator Cage Replacement Units Offer complete and reliable trap re newal in practically every make of ther mostatic trap. You simply (1) remove the old cover and unit, (2) insert the new Barnes & Jones Cage Unit, (3) re place the cover, and the old trap will oper ate with its original efficiency. Float and Thermostatic Traps Handle large and sud den condensation loads. Large air and watercapacity. Large float assures instant opening of the dis charge valve. Cage Type Thermostatic Unit assures quick elimination of air. Trap No.................. T41 : T42 T43 T44 T45 Inlet 4c Outlet Tapvr 1' w \x/i" 2" Capacity Sq. Ft. @ 2#...................... 800 2000 4600 9600 20000 1205 IS Healing Systems iSSV"" C. A. Dunham Company Administrative and General Offices . 450 E. Ohio Street, Chicago 11, 111. Factories: Marshalltown. Iowa; Michigan City. Ind.; Toronto. Canada; London, Encland . TORONTO 4, 1523 Davenport Road. LONDON. Lombard Rd.,-Merton;:S.W: 19 THE DUNHAM DIFFERENTIAL VACUUM HEATING SYSTEM Fully Automatic The system is a simple two-pipe system in which all the essentials of circulation, distribution and control are co-ordinated. Control of the temperature of the steam is accomplished by controlling the pressure or vacuum of the steam in the supply piping and radiators to balance exactly the heat input with building-heat-loss. ' A. <Room Resistance Thermometer B. Automatic Selector--Installed on --Makes the control completely automatic. north or west window on one of lower No manual adjustments are required dur floors (never on south), determines the ing the heating up period or m unusual demand for heat caused by the weather. weather.- If room temperatures are low (heating up period) the resistance ther mometer causes valve, to supply more steam until.the comfort zone is reached. If there is a tendency toward overheating lit causes less steam to be supplied. Other wise, comfortable room temperatures are maintained by cooperative actions of the selector and heat balancer giving an exact C. Dunham Oriflex Valve--Provides externally adjustable orifice at each radi ator causing steam to be evenly distributed to all radiators regardless of location. D. Dunham Differential Trap-- Operates.efficiently over a range*of pres sures from 15 lb gage down to' 25 in. of vacuum. balance between heat demand and heat E. Differential Controller--Installed supply. Windows may be slightly opened for ventilation without causing an increase in steam supply. near differential pump; measures the dif ference in, pressure between steam and return lines. When difference is- low, 1206 .- C. A. Dunham Company Healing Systems Steam Systems Specialties switch is closed and pump runs. When . difference is sufficient, switch opens and pump stops. F. Dunham Differential Vacuum Pump--Provides the necessary differen tial in pressure between steam and return lines under all conditions of flow to insure complete steam circulation. G. Heat Balancer--A control radi ator insures that the actual heat supplied is in balance with the demand. H. Connect directly to steam main near control valve (50 to 100 feet). I. Four wires in cables (low voltage). J. Six wires in cable (low voltage)/ K. Steam Supply. L. Steam Control Valve--Throttled by the control panel to maintain balance between heat supply (heat balancer) and heat demand (selector) (3-valve by-pass not shown). When valve closes, pump is placed on float control. M. 110 volt 60 cycles. N. Control Panel--Located at central operating station contains all setting and indicating dials. DUNHAM THERMOSTATIC TRAPS '> . For Operating Pressures up to 15 lb psi gage The Y in. trap is available in AP, RH, LH, SW, and vertical patterns. The % in. in AP, SW only. The 1 in. in AP only. ' Construction--Bodies, covers, nut and nipple are of brass, valves and seat are copper alloy. The trap is non- adjustable, permanent adjustment for correct operation is built into the ele ment. The thermostatic elements for traps of the same size are interchange able without adjustment. The disc is Floating Volte--Rounded Disc Large Valve Opening made from special composition phos Fig. 3366 phor bronze sheet. The corrugations are shaped to reduce hinge action at the rim of the disc and to distribute disc motion uniformly. The filling nozzle and the valve assembly are attached to their respective halves of the disc by threaded nuts making tight screwed joints which are further reinforced, locked and sealed by sweating with solder. The valve is flat and is attached to the disc by a ball swivel joint to insure its seating squarely and tightly. Valve opening is exceptionally large and the passage of water or dirt out of-the trap is not obstructed by a guide as none is necessary with, the Dunham design.- Valve seat is raised slightly and rounded to minimize the depositing of incrustants. DUNHAM RADIATOR VALVES "ORIFLEX" PACKLESS RADIATOR VALVE Type 175 Oriflex self-contained adjustable orifice valve combines the conveniences of both lever and wheel handle valves. Oriflex has a unique "handle movement" which eliminates graduated opening or closing. It need only be turned "on" or "off." The adjustable orifice within the valve, not the postion of the handle, controls the steam flov/. Oriflex eliminates the time consuming operations of disconnecting and re-connecting {he valve in order to balance a system. Merely remove the handle, insert the key on the adjustment stem thus made accessible, adjust 3519 the orifice (calibrated guide surrounds stem) to the exact setting needed for perfect balance. Instead of being limited to orifices calibrated in steps of five square feet, Oriflex provides for adjustments in increments of one square foot. 1207 C. A. Dunham Company Healing Systems Steam Systems Specialties 740 SERIES DUNHAM RADIATOR VALVE (Spring Packed) Designed for low pressure steam heating service. Bodies are brass, castings, rough finish. The valves are equipped with heavily constructed brass union nuts and nipples. All pipe threads and tappings are carefully machined and checked to standard gages. Non-rising stem, requires less than one turn of handle to open the valve fully. Dial shows direction and amount of opening. Heavy bronze spring keeps a constant pressure on a special graphited asbestos composition ring to maintain a tight seal around the valve stem. PACKLESS RADIATOR VALVE, SERIES 1140 Wheel Handle Suitable for all types of low pressure steam heating systems. The bellows construction, the non-rising stem, low bonnet, heat-resistant composition handle requiring less than one turn to open the valve fully, recommend this valve for services in which long-wearing quality, absolute tightness and attractive design are desired. Bodies and bonnets are brass castings, rough finish. The valves are furnished with heavily constructed brass union nuts and nipples. The expansion member is the built-up type of bellows, fabricated from tinned phosphor bronze giving maximum resiliency and wear. The expansion member not only prevents leakage of steam, air and water, but also prevents steam, water and dirt from clogging and corroding the spindle nut and screw. DUNHAM THERMOSTATIC STEAM TRAPS--TYPE TH For Working Pressures 25 Lb to 100 Lb Construction''--Type TH traps are the thermostatic fluid expansion type. The trap consists of two principle parts, a body with renewable valve seat and a cover containing the expansion thermostat. Permanent adjustment for correct opera tion is built into the element. The covers may be removed from the trap body while hot without danger to the thermostatic Fig. S518A Sectional THI-A element. The.valve is swiveled to insure its seating tightly without causing localized stresses on the element. Body, cover, nut . and nipple are of brass; valve and seat are of special heat treated stainless steel;, thermostatic element is formed from monel metal sheet. . DUNHAM INVERTED. BUCKET TRAPS Type OB For Operating Pressures up to 250 lb. Type OBS For Operating Pressures up to 150 lb. * Type OB sizes are 34 in. to 134 in. inclusive, Type OBS made only 34 in. and 24 in. sizes, right hand female tappings. . Body and cover are of high test semi-steel castings and are provided with a plugged opening at the lowest point of the body. The valve and seat, which are renewable and interchangeable, are constructed of especially " hardened, corrosion resisting steel. Bucket is formed from sheet copper. Cover cap screws are steel. * DUNHAM FLOAT AND THERMOSTATIC TRAPS 30 Series--For Operating Pressures up to 15 lb Gage Trap is comprised of a cover and mechanism assembly and a body. Thermostatic disc and valve controls flow through a cored passage between the trap body and the discharge tapping for the release of air. The float is cuprous material. The float valve-and seat are monel metal. Thermostatic elements are interchangeable. The trap body can be readily removed without disturbing piping connections 1208 . . C. A. Dunham Company Heating Systems Steam Systems Specialties to fully expose the working parts for inspection. Covers and disc assemblied are in terchangeable. Capacities, based on a rate of 34 lb condensate per sq ft of EDR per hour, at a pressure difference between inlet and outlet of 2 lb gage, 800, 2000, 4800, 9600, 200(H). Female right-hand threaded inlet and outlet. Connections 24 in., 1 in., 134 in., 134 in. and 2 in. _ DUNHAM CLOSED FLOAT TRAPS 31 Series--For Operating Pressures up to 15 lb Gage This trap is designed to release water only from low pressure steam installations. It may be used for,dripping rise in steam main, and other applications where no air is to be handled. These traps are similar in construction and capacities to the Float and Thermostatic Trap except thermostatic feature is omitted. DUNHAM CABINET CONVECTORS With Non-Ferrous Heating Element Dunham Convectors can be used on steam or vapor, and gravity or forced hot-water heating systems. EDR capacities with 1 lb steam, 65 F entering air range from 12 to 108 sq in. EDR. Made in 4 in., 6 in., 8 in. and 10 in. widths; 20 in., 24 in., 32 in. enclosure heights; casing lengths from 18 in. to 64 in. Casings are constructed of No. 18 gage steel with removable fronts having rounded corners for pleasing appearance. The outlet grille consists of horizontal openings punched in the casing front. Dampers can be fur nished when so ordered. Heating element is constructed of non-corrosive materials, copper or aluminum fins on seamless drawn, round copper tubes brazed to bronze headers. The tubes are expanded after assembly to assure intimate contact between fin and tube for permanent heat transfer.- Heavy side plates protect the fins from damage. The elements are tested at a hydrostatic pressure of 400 lb per sq in. and are suitable for operation on 150 lb steam or water working pressure. Either end or top and bottom tapped headers (24 in. I.P.S.) can be supplied. DUNHAM AIR CONDITIONING UNIT This single unit, when correctly in stalled, offers complete air conditioning, including warming and humidification for the heating season and cooling and de humidification for the summer, with filter ing, ventilation and circulation of air the year 'round. These combined services are rendered with a minimum requirement of space and a high functional efficiency which guarantees genuine satisfaction and genuine economy. The modernized 1946 model and details of construction, etc., will be available in the Spring of 1946. 1209 Heating Systems - f",?'ems DUNHAM TYPE OTS HEATING ELEMENT An extended surface heating element made entirely of steel. Light in weight, and has unusual heating capacity. Each element is made up of in. steel pipe with No. 22 gage heavy fins mechanically attached, eliminating the use of a solder bond without sacrifice of heat transfer. Each fin, when pressed on the pipe, interlocks with the preceding fin-- forming an exceedingly tight and permanent mechanical joint. The complete unit is painted with heat-resisting zinc chromate black enamel. Lengths from 18 in. up to 144 in. can be supplied in 6 in. increments. Standard units are threaded at each end with standard pipe threads. Type R--Floor Type with . mixing damper also fur nished with elongated nozzles DUNHAM UNIT HEATERS Types C and R are essentially industrial type units designed for heating large spaces. Type C, discharging large vol umes of heated air downward to working levels, distributes heat evenly over large areas. ' Type R is available in various types of mounting as shown. All units have belt driven centrifugal type fans using constant speed 1750 rpm motors.. Complete heating element and complete fan and shaft as sembly can be removed through either end of casing. Heating element is replaceable copper tube type. , Type V--Horizontal Propeller fan type. Built in various sizes from 65 up to 1500 sqfl EDR. DUNHAM PUMPS Tested and Rated with A.S.H.V.E. Code and Code of Vacuum Return Line Heating Pump Manufacturers' Section of Hydraulic Institute. Types DV and VRD Vacuum Pumps Types DV and DVD--Capable of maintaining whole systems under vacuums as high as 25 in. Built in 9 sizes. Capacities 2500 to 65,000 sq ft EDR. Types VR and VRD-^Meets all code tests for air and simultaneous air and water handling capacities. No moving parts or close clearances in exhauster unit. Built in 9 sizes. Capacities 2500 to 65,000 sq ft EDR. Condensation Pumps * Pump and motor assembled on rigid cast iron base. Bronze fitted centrifugal pump has non-corrosive shaft. Enclosed type Impeller. Liberal size ballbearings. Type CH-Model B, Single and Duplex--Capaci ties 2000 to 50,000 sq ft EDR; 60 cycle d.c. or a.c. 1750 rpm; 25 or 50 cycle a.c., 1450 rpm. . Type CHH-Model B, Single and Duplex--Capaci- ties same as type CH. Discharge pressures 20 lb for pumps 15,000 sq ft and larger; 20, 30, 40, 50 and 70 lb discharge in all sizes. 60 cycle d.c. or a.c. 3450 rpm; 25 or 50 cycle a.c., 2850 rpm. 1210- Heating Systems specialties GRINNELL COMPANY. Heating, Industrial and Power Plant Piping;-Sittings,. Hangers, Valves, Pipe Bending, Welding, Piping Supplies, Etc. Executive Offices: Providence 1, R. I. National Distributors of Thermoflex Traps and Heating Specialties For data on other Grinnell Products, see pages 981. 1112, 1113 Thermoflex Specialties The heart of all Thermoflex Traps is the Hydron Bellows. The Hydron Bellows is formed under hydraulic pressure. This powerful internal pressure locates any weakness of any nature in the tubing. Such hydraulic pres sure is many times more severe than any pressure the Trap will ever be called upon to control. Every Thermoflex Trap, there fore, is practically indestructible. Thermoflex Traps have an exceptionally large orifice. This large orifice combined with high lift, insures fast action and freedom from clogging.- We supply Thermoflex Traps guaran teed for steam pressures of 25 lb, to 50 lb and to 125 lb. Complete information and details of typical installations will be gladly sent on your request. Thermoflex Low Pressure Line The Thermoflex line of low pressure specialties offers a wide selection of sizes, types and capacities designed for working steam pressures up to 25 lbs. All of the specialty items which are regu lar components..of'Vacuum, Vapor, and Vented Return heating systems, are avail able in postwar models, including Thermostatic Traps ' Modulating Packless Radiator Valves Float and Thermostatic Traps Vapor system Return Traps and Vents Construction-and finish are of the high est quality throughout. . The No. 100A Thermoflex Trap is" guar anteed for steam pressures from 50-125 lb. Must not be used where the steam temperature exceeds 400 F. ' For use with all types of process work, Laundry Machinery, Kitchen Equipment, Hospital Sterilizers, Vulcanizers, Dry Kilns, Unit Heaters, Street Steam Service, etc., in fact any place that a trap is desired for service at the above pressures. Small, compact and inexpensive. Extra heavy body. Renewable nickel steel seat and disc. Bellows made from special bronze tubing and encased in brass sleeve to prevent distortion due to pressure. Regularly furnished without unions. Thermoflex Streamlined Strainers Thermoflex Medium Pressure Traps Thermostatic type traps, and Com bination Float and Thermostatic type traps are furnished for working steam pressures in the range from 25 to 50 lbs. Pipe line strainers of the self-cleaning Y-type are furnished for pressures up to 250 lbs, and in sizes 5^ in. to 2 in. These are heavy duty strainers with semi-steel body and brass screen, which are suited to a wide field of use in removing harmful substances from pipe lines carrying steam, air and fluids. ' * 1211 Heating Systems William S. Haines & Company 12th and Buttonwood Sts., Philadelphia 23, Pa. Manufacturers of EQUIPMENT FOR VAPOR AND VACUUM HEATING SYSTEMS PRODUCTS--Haines Vento Radiator Traps, Medium Pressure and Blast Type Traps, Combined Float and Thermostatic Traps, Air Eliminators, High Pressure Thermostatic Traps, Boiler Return Traps, Radiator Valves. HAINES F & T TRAPS Designed to handle large quantities of con densation. For driping steam mains, unit heaters, hot water gene rators. etc. Cannot become air bound as it has a thermostatically controlled air by pass. Sizes % in., 1 in.. in. For pressures to 30 pounds. HAINES MEDIUM PRESSURE TRAPS A ruggedly constructed bolted case trap. Ideal for hospital and kitchen equipment and all pro cess work operating on pressure up to 100 pounds. HAINES RADIATOR TRAPS The thermostatic ele ment in all Haines Traps is a Bourdon tube, charged with a volatile fluid and her metically sealed. The expansion and > contraction of the fluid, under varying tem peratures, fur nishes the op erating power. The vertical seat of this trap prevents it from becoming inoperative from scale or other foreign matter. HAINES HIGH PRESSURE TRAPS For drip ping high pressure mains, laundry equip ment and all process fixtures with working pressures up to 125 pounds. HAINES MODULATING VALVES A packless valve assuring positive and leak proof performance. Completely opens or closes on less than a full turn of han dle. Can be fur nished with wheel or lever handle or lockshield. HAINES BOILER RETURN TRAPS For vapor and atmospheric heating systems. Assures positive circulation by venting the air and returning the water of con densation to the boiler. Has no stuffing boxes or packed joints to leak air or water. Each device is individually tested, factory adjusted and guaranteed. 1212 Healing Systems Steam and Hot Water Hoffman Specialty Co., Inc. General Office and Factory 1001 York Street, Indianapolis 7, Ind. Sales Representatives In Principal Cities * Manufacturers of Radiator Air Valves, Quick Vents and Air Eliminators for all types of Steam and Vacuum Heating Systems--Steam Traps of all kinds-- Radiator Supply Valves--Vacuum and Condensation Pumps--and Hot Water Automatic Heat Control Systems. RADIATOR AIR VALVES FOR STEAM AND VACUUM SYSTEMS No. 40 Steam--Hoffman patented tongue syphon--in. connection--fixed port. No. 41 and 43 Steam--Strait shank for convectors--telescopic syphon--Y% and in. connections. . No. 70 Steam--Meets Federal spec. WW-V-151 Class 1--Long syphon--Y in. conn. No. 1A Steam--Tongue syphon--ADJUSTABLE air opening--in. connection. No. 2A VACUUM--Tongue syphon--ADJUSTABLE air opening--H in. connection. No. 3 Steam--For Airline or PAUL systems--}/& x Y in. conn.--union tailpiece. All radiator air valves operate on 10 lb max. press. . No. 4 No. 4A . No. 16A No. 76 No. 76 No. 4 Steam Mains--Will not close against water--25 lb press. % in. connection. No. 4A Steam Mains--Float closes against water--10 lb press. % in. connection. No. 16A -VACUUM Mains--Float closes against water--10 lb press. ^ in. connection. No.` 75 Steam Mains--Large systems--has float--10 lb press. % in. connection. No. 76 VACUUM Mains--Large systems--has float--10 lb press. % in. connection. No. 75A Steam Mains--Largesystemsatlowpressure--has float--3 lb press. % in. conn. No. 76A VACUUMMains--Large systems low pressure--has float--3 lb press. 24 in. conn. ' Nos. 75-75A-76-76A have cast iron bodies--others brass. UNIT HEATER VENT VALVE 'No. 74--Operates 0 to 35 lb. Vents a!! air at any pressure and whether rising or falling-- Same appearance as No. 75--Can be used on steam mains--has cast iron body-- % in. connection--finished in attractive Hoffman gray-green color. 1213 Hoffman Specialty Co., Inc. Heating Systems Steam and Hot Water. LOW, MEDIUM AND HIGH PRESSURE THERMOSTATIC TRAPS Low Pressure Medium Pressure High Pressure Low pressure traps have brass bodies, caps, and union nut and tail piece. 17C is made in Angle, Swivel and Vertical patterns. 8C is made in Angle and Straightway patterns. 9C is made in Angle pattern only. Thermostat and seat both renewable. No. 17C Capacity 200 sq ft EDR 15 lb pressure in. connection No. 8C Capacity 400 sq ft EDR 25 lb pressure % in. connection No. 9C Capacity 700 sq ft EDR 25 lb pressure 1 in. connection Medium Pressure Nos. 8 & 9 and High Pressure Nos. 8H & 9H have all bronze bodies and caps with union nut and tailpiece.. Thermostats are 6 diaphragms of special non corrosive metal. Thermostats and seats are renewable. }/& in. sizes are furnished in Angle, R.H., L.H., and Straightway patterns, others in Angle only. Medium Press. 50 lb limit. High Press. 125 lb. Capacities--Lb Condensate per Hour--Working Pressure--Lb per Sq. In, Gage Trap* 5 15 25 50 8 >/.' 100 180 235 400 8 Vi" 125 225 300 490 9 Va' 225 350 450 650 9 \m 325 500 625 850 Traps 8H VC 8H w 9H >/.' 9H 1' 25 / 50 235 400 300 490 450 650 625 850 100 550 650 875 1125 125 590 720 950 1250 FLOAT TRAPS, DIRT STRAINERS AND SUPPLY VALVES Float Traps are available in large capacities and four pressures, 15, 30, 60 and 125 lb. Used for venting and draining risers, steam mains, unit heaters, blast coils, etc. Hoffman Float Traps are made for easy servicing with all working parts mounted on cover. 'Remove four bolts to expose all parts. Pipe sizes are from in. to 2 in. * Radiator Supply Valves are made in sizes from to 1^ in. in Angle and straightway patterns. Brass bodies, union nut and tailpiece. No. 80 has reversible cone disc andt bevelled seat. No. 85 is Modulating type. Both are packless. Hoffman Dirt Strainers are self-cleaning Y type. Brass strainer cylinders and cast iron body. Sizes H to 2 in. for 125 lb pressure. Should be used in line ahead of all' float and thermostatic traps. ' CONDENSATION AND VAGUUM PUMPS . Condenser Pump Hoffman-Economy pumps are available in varying caparities, D.C. and A.C. current, single, two, or three phase, and in pressures up to 200 lb. Also made in single and duplex units for different capacities and pressures. 1214 - Vacuum Pump Hoffman Specialty Co., Inc. Heating Systems HOFFMAN HOT WATER CONTROLLED HEATING For PANEL or RADIATOR SYSTEM y The Hoffman method vastly improves the ordinary forced hot water system by the application of Continuous Circulation. This method accomplishes 4 major improve ments. 1. Avoids intermittent bursts of heat to the radiators and panels. 2. Maintains radiator and panel temperature to exactly offset the heat loss thereby eliminating "cold 70." 3. Conserves fuel by positively preventing overheating. 4. Prevents creeping noises from pipes because temperature change is so gradual. . ' The diagram illustrates the general operation. The circulator (C) is running continuously, circulating the water ' through the by-pass from return back through the supply line. The water in boiler is kept at a predetermined tem perature based on the Radiator Emis sion rate for which the system is designed. When heat is required the Temperature Controller or Thermostat (depending upon type of Hoffman system used) causes the control valve (V) to open, allowing the return water to pass through the boiler and the hotter boiler water mixes with water passing through the Hoffman orifice, in the by-pass line from the return, to raise the temperature of water entering the supply line. When the heat demand has been satis fied the control valve (V) closes and normal circulation through the by-pass pipe con tinues. The mixing of the water, already somewhat cooled from continuous circulation, with the high temperature boiler water eliminates the "slugs" of extremely hot water so common with forced hot water systems. There is positively no overheating and the temperature is raised so gradually that a comfortable heat- is always available \yith ap parently no change in the heating system. The two types of Hoff man Hot Water- Con trolled Heat differ only in the manner of control. The Circulator, Control Valve and Union Orifice are furnished with both systems. ` 1. Outdoor Thermal Control System--This System is controlled by means of the Hoffman Patented Temperature Controller illustrated above. Capillary tubing is connected to a temperature bulb located on the exterior of the building and another capillary tubing connected to a temperature bulb lo cated in the supply line of the System. Variations in temper atures of the outdoor weather and the circulating water are immediately transmitted through this Controller to the Control Valve. This System very completely controls the supplying of the exact amount of heat necessary to offset the actual heat loss. Made in nine regular pipe sizes from 1 in. to 6 in. with a maximum capacity of 4,460,000 Btu. 2. Indoor Thermostat Control System--Thermostat, located in that part of the building which is to determine the heat requirements for the entire System, operates the Control Valve through the Control Panel illustrated be low. This allows the circulating water temperature to be increased according to the demand of the thermostat and will supply the heat required uniformly and gradually. This System is naturally less expensive than the Outdoor Con trol type. Available in 1 in., in. and in. sizes with a max imum capacity of 275,000 Btu. Hoffman Circulator Design and Operating in formation is available upon request. 1215 Heating Systems Steam ILLINOIS ENGINEERING COMPANY General Offices and Factory: Chicago 8, 111. Represen tatives In Principal Cities Illinois Thermo Radiator Traps Illinois Radiator Supply Valve Illinois Thermo Ra diator Traps for vacuum, vapor and low pressure heating sys tems. Has Series G cone type . . va 1ve . Flushes throughly and seats perfectly at all times. Valve and seat are of Nitralloy. The duplex diaphragm is of special phos phor bronze. Scientific design and rugged construction assure flexibility and long life. These diaphragms have withstood over three million strokes on a breakdown test. Ask for Bulletin. Vapor Gauge Vafair Vent Trap Boiler Return Trap Illinois Selective Pressure - Control Systems Selective Controller An entirely new and unique method of Steam Circulation Control. . . Heating Systems that set new standards in comfort, economy, simplicity and convenience of operation. Each system individually engineered to meet exact requirements. Recorded fuel savings, without sacrifice of comfort, warrant your inves tigation. Ask for Bulletin 16. Quick-opening, packiess. Steam tight on 50 lb pressure. Large diameter of thread spool and ma chine cut threads make valve operation easy. Furnished in a complete line of sizes and patterns. Illinois Vapor System A two pipe low pressure steam circu lating system which may be installed in any type of building, where the condensate can return to the boiler by gravity. . A sensitive damper regulator or other means of automatic control is used to control initial steam pressure above, at or below atmospheric pressure. Steam is regulated at the radiators by Illinois Modulating Supply Valves. Condensate and air are discharged from the radiator through Illinois Thermostatic Radiator Traps. In the boiler room a Vapair Vent Trap and Boiler Return Trap are installed near the boiler. The vent trap eliminates air from the system and the Return Trap insures return of condensate to the boiler. The system and the piping arrangement are simple. No metering orifices or vacuum pumps are needed. This system will be found suitable for many installations where low first cost and low operating cost are of prime importance. May be used with unit heaters or any type of radiation. Illinois Combination F & T Traps Series G Unsurpassed for draining ventilating units, unit heaters, and for dripping mains and risers-- . .wherever it is desira ble quickly to vent air from the main as well as handle the water of condensation in quantity, whether hot or cold. 1216 Heating Systems steam ILLINOIS ENGINEERING COMPANY General Offices and Factory: . Chicago 8, III. Represen ta tires In Principal Cities Illinois Steam Trap Valve and stem are separate from the bucket and operated only by the bucket at the ex treme top and bottom of travel-- result--valve is always either full Series SO open or tight closed. No wire drawing or cutting of valve and seat which are of stainless steel. Illinois Motorized Valves (on and off) For automatic con trol of steam temper atures and pressures to prevent overheat ing and conserve steam; to control fluid levels; and to regu late flow in hot water heating systems. May be operated by any automatic con tact device or by manual switches.. Furnished in three types. Type ES Illinois Thermostatic Traps for High Pressures Maximum working pres sure 150 pounds. Used where neat appearanceand compactness are desirable, as for trapping sterilizers or water stills in hospitals; steam jacketed kettles, coffee urns, warming tables and for process work. Also used extensively for air vents on blast type drying heaters. 'Multi-diaphragm . of phosphor bronze. Heavy duty bronze body. Made in three sizes. These traps are also- furnished for medium pressures. Write for literature. Spring Controlled Regulating Valve Furnished in either single seat or double seat type as service requires, for the con trol of steam, air or gas. Control spring is completely enclosed, protecting it from dirt and rust. Valves are furnished with proper size diaphragm and proper length spring to give satis factory service under all operating conditions. Fur nished also in weight loaded Fig. l*l type, Fig. 71. Write for Bulletins. . Steam and Oil Separators Eclipse steam sepa rators are made in both horizontal and vertical type, and also the special receiver sepa rators for standard or extra heavy pressures. Eclipse oil separators are furnished in the horizontal type and. have a removable baffle Vertical standard plate to facilitate clean- Separators ing of oaffie and keep ing the separator's effi ciency at the highest point. . Non-Return Valves Placed between boiler and header to prevent return of steam to boiler. Sensitive in operation. Extra heavy iron bodies with bronze trim for 250 lbs steam working . pres sure. Bronze dash pot and water sealed pistons prevent valve sticking. Globe and angle patterns from 4 in. to 12 in. Fig. 260 1217 Heating Systems Steam Sarco Company, Inc. 475 Fifth Ave., New York 17, N. Y. Branches in Principal Cities . SARCO CANADA LIMITED. 85 Richmond St., W.. Toronto. Ont. PRODUCTS--A complete line of Specialities for Vapor, Vacuum and Gravity Steam Heating Systems and Control combined with a competent Engineering Service to architects and heating engineers to assist them in providing modern' heating. SARCO RADIATOR TRAPS Radiator Trap, Type H Type H is the standard radiator trap for vapor and vacuum systems. It is equipped with the well known Sarco heavy wall bellows, drawn from flat blanks and helically corrugated in our own plant. It operates noiselessly and positively at pressures from highest vacuum to 25 psi. Body and cap are of cast brass, rough brass finish; self aligning valve head and renewable seat of hard bronze; union connection on inlet. Available in 34 in. and 34 in. sizes, angle, straightway or corner offset patterns; also I in., angle style only. Catalog No. HV-100. SARCO RADIATOR VALVES Sarco offers two types of radiator valves. Where highest efficiency is desired, the bellowspackless valve, type 45, is recommended. The Radiator Valves Type Type R valve stem is sealed by a standard Sarco bel lows. Leakage of.air into the system under vacuum is impossible. Modulating types with proportioning disc and indicating dial are available. - Type R is of the "spring-packless" type, quick opening, non-rising stem. The molded stem packing is spring con trolled. - Bodies of all valves are cast brass, rough brass finish. Out let fitted with union connection. Sizes* 34 in. to 134 in., with wheel handle or lock shield. Catalog No. HV-100. N-100 Medium Pressure Trap SARCO N-100 TRAP For high pressure radiators and heating coils in stationary and marine service, arid for hospital and kitchen equipment. Has full length protecting shield and stainless steel valve head and seat. Sizes in. to 1 in. pressures to 100 lb. Catalog HV-190-. . Also S-65 for pressures to 6o' psi. Float-Thermostatic Trap SARCO FLOAT-THERMOSTATIC TRAPS For dripping ends of mains and risers, and for stack or blast heaters, large unit heaters and hot water generators. Automatic thermostatic air vents built in. Available in six sizes with connections 34 in. to 2 in. Pressures up to 200 psi. Catalog HV-450. Inverted Bucket Trap SARCO INVERTED BUCKET TRAPS Are recommended for high pressure unit heaters and some times preferred for kitchen and laundry equipment. Strainers are built right into these sturdy traps. Seats and valves are stainless steel and renewable. Automatic air vents can be furnished for extra rapid removal of air. Available in sizes 34 in. to 2 in. for pressures up to 900 psi. Catalog HV-350. 1218 Sarco Company, Inc. Heating Systems steam SARCO ALTERNATING RECEIVER A complete line of boiler return traps for vapor systems. .# Returns water of condensation to boiler auto matically, thereby assuring positive return of water ' under all pressure conditions. . Made in four sizes for up to 14,000 sq ft of radiation. Catalog HV-165. m SARCO AIR ELIMINATORS For venting air from vapor systems at one DR central point in the basement. Available in three sizes, No. 5 for systems up to 2000 sq ft Pja^g radiation, No. 6 for 3000 sq ft, and No. 12A fly for 15,000 sq ft. All are equipped with float valves to stop water escaping thru the vent and with check valves to prevent ingress of air when system is under vacuum. Also several types for hot water heating systems. Catalog HV-170. Alternating Receiver SARCO SELFrCONTAINED TEMPERATURE REGULATORS Sarco Temperature Regulators are simple, self- operated valves--the only self-contained units that use the irresistible force of liquid expansion. No stuffing - boxes to leak, no auxiliary "power" required; all moving parts are inside the equipment. Here again-- . . a type and size for every purpose--for steam, gas, oil, Type TR-S1Standard for hot water storage water or brine for temperatures ranging from 0 to tanks, fan units, 300 F. Catalog HV-G00. etc. Water Blender Type MB SARCO WATER BLENDERS AND TEMPERING VALVES For mixing hot and cold water to deliver automatically water at any desired temperature. Two models are available, type MB for showers, wash basins, etc., and type DB, a tempering valve for usewith submerged heating coils or tankless heaters. Catalog HV-800. SARCOTHERM HOT WATER HEATING SYSTEM A simple, all-mechanical system for the control of radiator temperatures in direct relation to outside temperatures. Radia tion is balanced by Sarcoflow fittings in the radiator outlets. The Sarcotherm three-way valve recirculates a varying pro portion of water around the boiler and back to the system as dictated by the thermostatic bulb outside the building. Write to Sarcotherm Controls, Inc., 280 Madison Ave., New York 16, N.Y. for Catalog No. HV-1. .Water Blender Type DB SELF-CLEANING STRAINERS For use in pipe lines carrying brine, steam,. oil, gas, water, ammonia or air. Have large free screening area with minimum resistance to flow. Steam' or air strainers can be cleaned by blowing through without disas sembling. Made in cast iron, bronze or cast steel for pressures up to 500 psi, with 'brass, iron or monel screens. Available in sizes 34 to 8 in. Catalog No. H V-1200. Sarcotherm Weather Control Valve 1219 Heating Systems Steam Unit Heaters WARREN WEBSTER & COMPANY Pioneers of the Vacuum System of Steam Heating Systems of Steam Heating Main Office and Factory: Camden, New Jersey Representatives in Principal Cities-- Consult Your Local Phone Directory UNIT HEATEHS PRODUCTS AND SERVICES Webster Systems of Steam Heating including Vacuum and Type "R" (vapor). Webster MODERATOR Central Control Systems. Webster Baseboard Heating. Modernization of Obsolete and Faulty Heating Systems. Webster System Equipment in* eluding Light-Weight Concealed Ra diation (Gravity Convection Heaters), Radiator Supply Valves, Metering Orifices, Thermostatic Traps, Drip Traps, Heavy Duty Traps, Dirt Strain ers, Dirt Pockets, Boiler Return Traps, Vent Traps, Damper Regulators, Boiler Protectors, Lift Fittings, Ex pansion Joint8, Separating Tanks, Steam and Oil Separators, Steam Vacuum Pump Governors, Air Sepa rating and Receiving Tanks, Gages, Water Accumulators. Webster Series "78" and Series "79" Traps for use at process pressures (10 to 150 lb per sq in.) Webster-Nesbitt Unit Heaters. WEBSTER SYSTEMS Webster Systems are low pressure, twopipe systems of steam circulation with the addition of accurately-sized metering ori fices at radiator supply connections and, when required, intermediate metering ori- P! I. Conventional arrangement of piping around Webster Basement Equipment for the. Webster Type "R,r System fices at points in branch mains. Metering orifices effect even distribution of steam to all parts of the heating system and'permit the successful application of a centralized control. Webster Valves are used at sup ply of radiators. Webster Thermostatic Traps prevent flow of steam into return mains when radiators are filled. Webster Drip Traps and Dirt Strainers are used where needed on steam mains. Webster Systems are available for vacuum, open return or "vapor*' operation. The Type "R" System corresponds to the so-called Vapor type. Fig. 1 illustrates a typical arrangement of Boiler Return Trap, Vent Trap, etc., when low pressure boiler is the source of steam. WEBSTER MODERATOR CONTROLS These are painted systems for varying the amount of steam to all radiators ac cording to outside temperature. They provide continuous heat delivery with effec tive fractional filling of radiators. The Moderator Systems employ an automatic Outdoor Thermostat supplemented by a manual Variator. The latter is used for quick heating-up, night load, and unusual weather or oc cupancy conditions. Use of Webster Moderator Control Systems results in (1) increased comfort because - over-heating and underheating are minimized and (2) lower fuel or steam costs. WEBSTER SYSTEM RADIATION Concealed, non-ferrous type for use with steam and hot water heating systems. Is unique in that it combines in a single unit, a light-weight heating element of high efficiency with an orificed radiator supply valve, a radiator trap and supply and return piping connections. Also available in conventional models without valve and trap. Metal enclosures for installation within the wall and exposed metal cabi nets are available. Webster System Radi ation and enclosures are so designed that the entire heating element can be quickly removed without damage to plaster oc paint. Space requirements reduced to a minimum and installation greatly sim plified. 1220 Warren Webster & Company Heating Systems Steam Unit Heaters WEBSTER BASEBOARD HEATING Combines a new and unique method of heat distribution with the well-known advantages of hot water heating. The convection type heating element is placed at the floor line behind metal baseboards and along outside walls of the room. It is installed in continuous loops, one on each floor of the home. The heating medium is forced hot water using conventional boiler, firing devices, and controls. RADIATOR VALVES ' interior parts. Furnished with standard wheel handle as shown in Fig. 2. Lockshield type available for institutions. Angle bodies in sizes from in. to 1J4 in. Offset and straightway models can be had on order. While primarily for low pressure steam heating service, the Type WB-P Valves are suitable for low pressure hot water heating. Furnished with or without leak hole as desired. Pressures--For low pressure vapor and vacuum steam heating service. Metering Orifices--Accurately sized and made of metal to resist erosion and corrosion, amply thick to be free from vibration and shaped for quiet operation. RADIATOR TRAPS Fig.S. Webster Type "WB-P" Brass Radiator Valve The Type WB-P Valve meets fully specifications calling for a "spring pack less" valve. A heavy spring automatically maintains pressure on die-molded metallic ring packing. Although packing seldom requires renewing, this valve is so designed that, old packing ring can be removed and new installed while pressure is on the heating system. The Type WB-P Valve opens quickly and easily in less than a turn of the handle. Has non-rising stem. All brass construc tion including union nut, nipple, and 'Pig. 4 Webster 70SH Thermostatic Radiator Trap The Webster Series 7 Trap is a diaphragm-type thermostatic trap design ed for low pressure service. It is recom mended for all types of radiators, piping drip points, steam-using equipment, and other applications within its pressure and capacity range. The Series 7 Trap is noted for its high efficiency and for giving many years of trouble-free service. Construction Features--Body and cap are high quality brass. Double ther mostatic diaphragm is phosphor bronze, individually factory adjusted and tested. Diaphragms are compensated for pressure which means that they function efficiently at all pressures within their operating range. They do not close too quickly at certain pressures to hold up condensate while remaining open at other pressures to pass steam. Stainless steel valve piece is 60 deg cone type, factory adjusted. Brass seat with stainless steel insert is readily renewable. - Pressures--Webster Series 7 Traps are designed for low pressure vapor and vacuum steam heating service. Maximum pressure is 25 lb per sq in. 1221 Warren Webster & Company Heating Systems Steam Unit Heaters Table 1. Recommended Ratings in Sq Ft E. D. R.* The ratings below are conservative and not full-flooded capacities. Applications requiring use of higher ratings should be referred to the Company or its Repre sentatives. When writing give full details of proposed use. Select trap by rating, not by pipe size. Symbol Size 702 r 715 V/ 724 V Pressure Difference Across Trap in Lb per Sq In. 1 i'/i 2 5 10 15 165 700 550 400 580 700 255 570 550 640 465 750 1050 1500 810 1260 1840 2500 Based on 240 Btu per sq ft per hour. FLOAT-AND-THERMOSTATIC TRAPS piece and seat- insert. Angle model only. Sizes: 9^ and 1 in. Extensively used with laundry, cooking, sterilizing and other process-steam uses. Series "79"--For use where large volumes of very hot condensate form more quickly than can be discharged by thermo static traps alone. Float and thermostatic traps designed for normal working pres sures between 15 and 150 lb per sq in. Water of condensation is passed through a float-controlled seat opening while air is discharged into the return piping by a thermostatically controlled vent. Com pact and light in weight. Can be readily mounted in a pipe line without other support. Available with 1 in. inlet and outlet. Readily bushed for smaller pipe sizes. Cast iron body, composition gasket and cover bolted together with steel cap screws. Monel Metal valve piece and stem. Stain less, steel seat. Air vent unit is Monel Metal diaphragm /with Stainless Steel valve piece and brass seat with Stainless Steel insert. DIRT STRAINERS AND POCKETS Placed in return lines of steam heating systems to. prevent dirt, rust and scale from impairing.tightness of traps. Fig. 5. Webster Size OOOS6-T Drip Trap has rated capacity of 00 lb Water per Hour at lb Pressure Differepee Series "26**--A heavy duty trap for drips of mains, blast radiation, unit heaters, hot water generators and similar applications. A rugged float-type trap available with and without thermostatic air vent. Made in five sizes: 200, 500, 1200,.2400 and 5000 lb water per hour at 2 lb pressure difference. Maximum working pressure is 15 lb per sq in. PROCESS STEAM TRAPS Series "78" --thermostatic trap built for process steam pressures (10 to 150 lb per sq ih.). Monel MetaJ d i a - phragm. Stain less Steel valve Fig. 6. Webster Size 78 Trap Fig. 7. Size S4C-1 Webster Boiler Protector with bow Water Electrical Cut-out Switch. Size 34 has no Cut-out Switch . BOILER PROTECTOR Prevents breakage in low pressure heating boilers when water level becomes inadequate. Automatically supplies raw water to boiler when water level drops to 1 in. above bottom of gage glass. For maximum boiler pressure of 15 lb per sq in. Maximum cold water main pressure should not exceed 150 lb per sq in.; minimum must not be less than 25 lb . per sq in. Made with In. connections, with or without electrical cut-out switch. 1222 Warren Webster & Company Heating Systems VnftHeat^ WEBSTER-NESBITT UNIT HEATERS Are manufactured by John J. Nesbitt, Inc., Holmesburg, Philadelphia 36, Pa., and' are distributed solely through Warren Webster & Company, Camden, New Jersey. Designed to circulate large volumes of air at comparatively low temperatures, assuring quick heating. - . Ratings of Webster-Nesbitt Unit Heaters are based on tests made in accordance with standard test code of Industrial Unit Heater Association and A.S.H.V.E. PROPELLER FAN UNIT HEATERS Fit. 11- Standard Propeller-Fan Type Designed to incorporate four character istics proved by wide experience to be essential to both proper application and satisfactory performance: 1.) Selective range of sizes. Manu factured in nine sizes. Heating capacities vary from 34,700 to 338,000 Btu per hour. Air deliveries from 470 to 4800 cfm. GIANT UNIT HEATERS Sturdy blower-fan units for the econom ical heating of large areas. Standard (Non-Ther- madjusi) Type. Used principally where heat ing is by recirculation only, and where con stant heat output is desired during period of operation. Thermadjust Type. Employs dampers in ig front of casing and Blower-Pan Type over face of heating element to provide mixing of unheated and heated air, producing heat output in accor dance with requirements and continuous circulation of air volume. Valve Controlled Type. Unit is of stand ard casing arrangement but equipped with Nesbitt Heating Surface with Steam- distributing Tubes which allows for auto matic control of heat output. Floor mounted, wall mounted, ceiling suspended, from 101,000 Btu, 3250 cfm, to 930,000 Btu, 15,200 cfm. Write for details. Catalog W-N 128. LITTLE GIANT UNIT HEATERS 2.) Quiet Operation. All fans have blades of exceptionally large areas and of a shape to impart a gradual acceleration to the air stream. Ample spacing is maintained between the fan and heating element. Motors are of sleeve bearing type and equipped with isolators. 3.) Durable lightweight Heating Elements. Extended fin-and-tube type, constructed of copper condensing tubes and plate-type aluminum fins. 4.) Modern Casing Design. Compact suspended type. Catalog W-N ,126. ` Fig. IS. "Little Giant" Down Blow Type New, light compact draw-through high velocity down blow unit heaters. 122,000 Btu, 2370 cfm to 505,000 Btu, 10,080 cfm at basic rating of 2 lb steam and 60 deg entering air. ' ~ Down Blow Type. Generally used when the presence of cranes and other machinery requires that the unit and piping be located well above the floor level. Write for details. Catalog W-N 127. 1223 Heating Systems Specialties Armstrong Machine Works Representatives in All Principal 851 Maple Street, Three Rivers, Mich. Cities Armstrong offers two types of traps for heating, air conditioning, and steam distri bution service. Standard Inverted Bucket Traps, the type originated by Armstrong, are non* airbinding and self-scrubbing. They are used for low, medium, and high pressure service where relatively little air must be handled along with the condensate. Their free-floating lever design makes it possible to open very large discharge orifices com pared with the size of the trap itself. Armstrong Blast Traps are used where large amounts of air must be vented quick ly when steam is first turned on. They have several advantages over the conven tional float and thermostatic trap. 1. The Armstrong Blast Trap has but a single orifice to be maintained tight against the full pressure differential. ^ 2. Positive action. The discharge valve in an Armstrong Blast Trap is either wide open or tight shut. Fast opening and fast closing prevent wire-drawing. 3. Handles dirt. There are no dead spots in an Armstrong Trap in which dirt can settle and interfere with the operation of the trap. . Cross-section of No. 800, 811, 818 and 818 traps for straight- through pipe connections. Cross-section of No. 801 trap for standard angle pipe connections. Side Inlet Traps Trap Size No. 800 No. 811 No. 812 No. 813 No. 801 VW W *10.00 Vi*<*VS $16.00 VS or } $22.00 Vi0 or VS $7.00 $8.50 *11JO $18.00 $24.00 $8.50 Cherry Dawn Arrow Telegraph Code (Blast Trap)....... Aloette Brownette Cherette Dawnctte Arrowette v/s 3*4' B................................ w C_______ 5' " D............. bW 8W w Mv/Ws 6* 2 V4' Weight....................... Maximum Pressure. Ibs................ 6 vs Continuous discharge capacity in lb of water per hour at pressure indicated, tor more complete information see the Capacity Chart in Armstrong Steam Trap Book. ---------------------- ' 5 10 15 20 2 30 3 50 CU 70 100 -J \P. 450 560 640 690 500 580 660 640 680 200 See Note 250 at right. 6 VS 5`Albs. 250 , 830 950 1060 880 1000 840 950 860 950 810 720 760 VS 13>/2tbs. 250 1600 1900 2100 1800 2050 1900 2200 1800 2000 1500 1200 1300 VS 25 Ibs. 250 2900 3500 3900 3500 4000 4100 3800 3600 3900 3500 3200 3500 VS 125 450 560 640 690 500 580 660 640 680 at right. 1224 . UNIT HUMIDIFIERS Steam Type Armstrong Steam Type Unit Humidi fiers offer a low-cost, practical method of preventing the evils of winter heating'dry air. Improve worker comfort and safety; prevent drying out of materials. Write for new Bulletin No. 158. Armstrong Machine Works Healing Systems Specialties No. SIS No. SIS No. Sll No. 800 No. SI 1 No. SIS No. SIS 4. The wearing parts in all Armstrong Traps are identical in design, material, and precision workmanship with parts used in Armstrong Forged Steel Traps for pres sures up to 2400 psi and total temperatures of 850 F. . Armstrong Steam Trap Book. This 36 page book gives complete information on all sizes and types of Armstrong Traps. It also contains 17 pages of data on the subject of tr^p selection, installation, and maintenance. A free copy will be mailed on request. Armstrong Steam Type Humidifiers For use during the heating sea son, when relative humidity is low, moisture absorbing materials dry out, and static electricity accumulations are sources of fires and explosions. Operation is automatic and de pendable. Relative humidity is maintained within close limits. Operating costs are very low, installation costs moderate, and maintenance costs are low. Both air operated and electric ally operated models available with capacities to 850 lb steam per hr. Send for Bulletin 158. Trap Size Pipe Connections............................ List Price (Regular)..................:.. List Price (Blast Trap)................... Telegraph Code (Regular).............. Telegraph Code (Blast Trap)......... Height.............Dimensions......... Diameter......... ** A.......... Wall Thickness " C.......... Diameter of Bolts........................... Number of Bolts............................ Weight........................................... Maximum Pressure, lb................... 5 10 15 20 3 30 3 50 complete information. 70 tee the Capacity 3 100 125 150 Book. 200 250 Bottom Inlet Traps No. 211 No. 212 No. 213 Vi0 $ 9.25 $10.75 Aspen Aspette Hy,' w A" W 630 950 1060 880 1000 840 950 860 950 810 860 760 v&' - $17.00 Birch Birette - 8* 5* VS vs 8 ID^Ib 1600 1900 2100 1800 2050 1900 2200 1800 2000 1500 16CC 1300 VS or ys $20J5 $22.75 Walnut Walette V/S 6 191b 250 2900 3500 3900 3500 4000 4100 3800 3600 3900 3500 3200 3500 No. 214 1* $29.00 $31.50 Hemlock Hemlette 1 r 32 lb 250 4800 5800 6500 6000 6800 6300 6000 6200 6700 * 5700 5300 5700 ' No. 215 1 or ws $38.00 $4070 Larch Larctte 14" % 47 lb 250 7600 9000 10000 8500 9800 9000 9200 10400 10900 95009200 7000 No. 216 %%r $60.00 Tamarack Tamrette I6% \W &: 12 801b 250 14500 17300 19200 18500 18000 18200 18300 18000 20000. 18500 17500 19000 1225 - Adsco PRODUCTS for STEAM SERVICE Healing Systems Specialties American District Steam Company North Tonawanea.N.Y. IN BUSINESS OVER 65 YEARS Branches and Agents in Principal Cities For Data on ADSCO Expansion Joints, refer to Insulation, Underground, page 12S6. ADSCO FLOW METER--ORIFICE TYPE Exceptionally accurate at all rates of flow and will meter steam, water, gas or air. It is a compact unit for indicating, recording and integrating the flow and can be furnished in other combinations of these three devices. Easily installed and maintained by the pur chaser. Frictionless meter mechanism, records on evenly-divided, direct-reading chart, giving a daily record from which to determine heating or processing costs. Write for Bulletin No. 35-83G. ROTARY CONDENSATION METER Measures steam consumption by meter ing condensate from heating systems or industrial equipment. Accurate within I per cent and factory tested to 150 per cent of rated capacity. Compact,, easily cleaned, tamper-proof and equipped with non-fogging counter mechanism. Counter reads directly in pounds. Suitable for vacuum or gravity service. Available in 7 sizes from 250-12,000 lb per hour capa city. Write for Bulletin No. 35-80AG. Rotary Condensation Meter ADSCO VERTICAL STEAM TRAP A float type steam trap with or without thermostatic air by-pass for vacuum ser vice to 15 lb pressure and gravity service to 125 lb pressure. The cover with all working parts can be removed without disturbing the piping connections. .The trap is equipped with a reversible valve and reversible seat of stainless alloy steel. Write for Bulletin No. 35-86G. ADSCO Instantaneous Water Heater ADSCO HEAT EXCHANGERS Made in various sizes and capacities to heat or cool water, oils, other liquids or gases according to expert engineering specifications. Simple in design, sturdy in construction, dependable and economi'cal in operation. Available in U-tube or straight tube types of heaters, economizers, condensate coolers or special units. Write for Bulletin No. 35-75BG, 35-76G. 1226 Heating Systems Specialties Mueller Steam Specialty Co., Inc. 40-20 22rid Street, Long Island City, N. Y. Steam, Water, Air, Oil and Gas Specialties for Heating and Power Plants Pressure Reducing Valves--Straight Pattern and With Increased Outlet No. 11--For Vacuum, Vapor and Low Pressure Heating Systems. Initial Pressures, up to 200 lb; Reduced Pressures, 0 to 10 lb. No. 17 and 21-- For automatic control of reduced pressures on dead-end service, requiring a tight closing valve, such as tank heaters, kitchen utensils, sterilizing ap paratus, laundry equipment, kettles, cookers, driers, etc. Initial Pressures up to 200 lb. . Reduced Pressures 0 to 150 lb. Constructed with full globe bodies. Center guide eliminates the wings on discs, and increases efficiency, assures minimum noise and prolongs the life of the seats and discs. Lever and weight operates on a steel roller bolt, assuring a most sensitive valve. Spring type furnished with special long springs for sensitive operation and wide ranges of reduced pressures. Water Pressure Reducing Valves Diaphragm Operated Water Relief Valves . For controlling water pressures that require automatic and positive control of reduced pres sures. Compact, and have full flow and renewable composition discs. For relieving exces sive pressure of hot or cold water, air, oil or gas. Very sensitive, re spond quickly. Standard and extra heavy weights suitable for all' initial pressures and wide ranges of reduced pressures. ` Their construction is durable and compact, and accessible without disturbing pipe. con nections. Sediment Strainers for Steam, Water, Oil, Gas, Air, Etc. For removing scale, cuttings, and other foreign matter from steam, water, air, oil and gas lines, or in connection with valves, pumps or other apparatus. Furnished with iron bodies, plain or galvanized, with brass or copper mesh suitable for the service. Can be furnished all brass or nickel-plated iron or brass, or cast steel for extra high steam pressures, at additional cost. Strainers with special mesh or of special metal furnished at a slight additional cost. No. 1S6 Figures Nos. 145 and 165 Strainers have closed or open bottom baskets, so that the basket can be removed for cleaning, or all dirt and sediment can be blown out through bot tom blow out connec tion. ' No. 145 No. 165 Catalogue and Bulletins covering our Complete Line gladly furnished on'application. 1227 Healing Systems feS"ies Jas. P. Marsh Corporation 2072 Southport Ave., Chicago 14, 111. Branched In Principal Cities Marsh products include:' Pressure, Vacuum and Compound Gauges; Dial Thermometers; Steam Traps; Air Valves and Vents; Packless Radiator Valves and other heating specialties. Thermostatic Diaphragm Radiator Traps These efficient traps are equipped with a phosphor bronze diaphragm, consisting of two wafers of tinned phosphor bronze, drawn and spun to perfection of temper. packing to deteriorate, wear or crack, and are simple in design, with ample strength where strength is required. The principles upon which they are designed have been proved sound over many years of service. Valves operate easily--opening or closing tightly with less than one full turn. All valves are individually tested. Adaptable for use on hot water--forced or gravity systems--as well as all steam heating systems. . Marsh No. 12 Float and Thermostatic Traps Thermostatic Diaphragm Radiator Trap The wafers are spun together and soldered to form a seamless, sensitive, powerful expanding member--not easily fouled by dirt and foreign matter. Diaphragms are charged with a volatile fluid making them self-equalizing for use on pressures below atmosphere to 15 lbs. gauge. Traps are factory adjusted. Packless Radiator Valves . Marsh all-metal packless valves are truly packless. These valves contain no Float and Thermostatic Trap Packless Radiator Valve Marsh Heavy Duty Float and Ther mostatic Traps are designed for removal of air and condensate from steam mains, branches, or risers, unit heaters, steam coils, etc. The size and weight of the trap permits installation in the piping without any other means of support. Condensa tion is discharged through a float operated valve located at the lowest point inside the trap. body. Air vent is located in a by-pass in the cap or cover of the trap. Air passes through a passageway and out through the trap outlet. Construction permits removal of mechanism without disturbing the piping. 1228 Jas. P. Marsh Corporation Marsh No. 500 Inverted Bucket Type Trap Heating Systems "Recalibrator" for quickly and easily resetting the hand to zero when the gauge is knocked out of adjustment. Marsh Gauges include vacuum and com pound types in a wide range of designs covering all services and pressures. Over 75 years of gauge manufacturing has reached its highest achievement in the Marsh "Mastergauge" for use where high pressures and temperatures are present and where maximum stamina and accuracy are essential. This type is ideal for all types of hospital and kitchen equipment or similar service where a considerable volume of condensate is handled. The trap is self-venting, which, combined with the large water capacity assures unusually high efficiency in removing condensate, air and gases. - Marsh No. 17 Float and Thermostatic Trap This trap is de signed for removal of air and conden sate from short steam mains, branches or risers. Operating charac teristics adapt it for unit ventilators, unit heaters, and other equipment subjected to freezing tempera tures when heating system is not in opera tion. Outlet discharge is water sealed at all times. Air vent is located in trap bonnet and air is normally discharged through a port directly to the outlet con nection. A removable strainer protects mechanism. All working parts are made accessible by removing bonnet. The piping is all the support required for the No. 17 Trap. . Marsh Dial Thermometers Have the same basic refinements found in Marsh Gauges. Typical Marsh Ther mometers of bourdon tube type in selfcontained and distant reading types are illustrated. They are available in either vapor tension or gas-filled types. Bi metallic types of dial thermometers are also available. Practically all temperature ranges up to 750 F. are covered. The "Recalibrator" is standard in all Marsh bourdon tube type thermometers. The' Marsh line also includes recording ther mometers. Marsh Low Pressure Gauge The Marsh A.S.M.E. standard, low pressure gauge will contribute to the economy and improve the operation of any type of steam boiler. It is finely built throughout and is available with the Marsh Ask for complete information covering any problem involving traps, vents, gauges, dial thermometers, radiator air valves, packless valves, etc. 1229 Heating Systems specialties Products Research Co. ,, 634 S. Western Ave.f Los Angeles 5, Calif. New York Portland SALES OFFICES ' Houston San Francisco Seattle Los' Angeles Chrome Lock gasketing was especially, developed for use in U. S. Naval Vessels. Ever since 1942, this type of gasketing has withstood the terrific vibrations of all types of ships in action, due to its tremendous cushioning effect. Chrome Lock, this new type of gasketing of felt base, is impregnated.with a chromate pigmented compound which renders it flame and corrosion-resistant. Chrome Lock holds up under pressure of 500 lb or more per square inch and is compressible to take up uneveness in flanges and seams. It is not affected by fuels and will retain its pliability under locked-in pressure. Chrome Lock is now offered for industrial uses. ADVANTAGES 1. Flame-resistant 2. Warp-proof . 3. Rust-inhibiting Qualities 7. Adhesive to Metal 8. Anti-squeak 9. Non-oxidizing TYPES and FORMS Sheets Rolls Slit Rolls 4. Longer Life 5. Anti-wicking 6. Fuel-resistant 10. Non-hygroscopic 11. Easy to Handle 12. Less Expensive. USES , 1. Air Conditioning . 2. Heating s 3. Refrigeration 4. Anti-squeak on Non-removabre Fit tings 5. All Piping 6. Joint Seals for: Diesel Oil, Fuel Oil, Gasoline,. Mild Acids, Water (Fresh and Salt). . Sheets: Ys in. and Y in. thick--36 in. x 48 in. - Rolls: in. thick--36 in. wide--200 sq ft to roll. Y in. thick--36 in.-wide--100 sq ft to roll. Slit Sold by linear foot. Rolls ap- Rolls: proximately 50 linear feet in fol lowing widths: 1 in., 1 Y in., IY in., 2 in., 3 in., and other sizes on special order. PACKAGING and SHIPPING Sheets: In heavy cartons. 20 sheets of 36 in. x 48 in.--J4 in. 10 sheets of 36 in. x 48 in.--Y in. Rolls: 200 sq ft 36 in. wide--14 in. 100 sq ft 36 in. wide--Y in. Slit Rolls: As ordered. 7. Water-tight and Air-tight .Connections to Structures 8. Flange to Flange Joints - . A FEW USERS Bethlehem Steel Company California Shipbuilding Corporation SPECIAL GASKETS Special shapes or sizes can be cut economi cally and advantageously by any com mercial gasket cutting company. EASY TO CUT Consolidated Steel Corporation Kaiser Company, Inc. Permanente Metals Corporation Todd Shipyards Corporation Western Pipe & Steel Co. Todd Pacific Shipyards, Inc. A free sample has been reserved for you. Send for it today. 1230 Heating Systems Specialties Wright-Austin Co. 309 West Woodbridge St., Detroit 26, Mich. Established Over 50 Years Ago PRODUCTS--Steam Traps, Strainers, Air Traps, Air Vents, Steam and Oil Separators, Compressed Air Purifiers, Exhaust Heads, Boiler Feeders and Controllers, Alarm Water Columns, Water Gauges, Trycocks, Illuminators and Protectors for Water Gauges. "Emergency" Float Type Steam Trap Three valve trap with large capacity at high pressures. An ex ceptionally reliable trap for use in inac cessible places. "Airxpel" Bucket Type Steam Traps Are "double duty" traps, because they automatically discharge both air and condensate. ' Union connections make them easy i to connect up. Also, furnished with screw con nections when desired. They Air Relief Traps For relieving air from forced circulation hot water heating systems, water supply lines, closed tanks, receivers, pumps, etc. save money for fittings and instal "Tuway" Strainer INLET lation labor, by May be used two ways-- having straight as a straight-way or angle through horizon strainer, in either hori tal pipe connec zontal or vertical pipe tions. line, because it has the The Cub sizes are made in % in., % in., 1 in. choice of two inlets at right angles to one another. Especially suitable for in dividual unit drainage on heating and process equip-' ment,. Separators--Steam and Oil Type "A" Vertical Type "S" Steam Horizontal Oil Also three "Master" sizes Yl in. to 2 in., for general service. "Combination" Steam Traps Float Type with internal thermo static air bypass and strainer for pressures 0 to 40 lb. A modernly designed and very successful trap for vacuum and pres sure heating. - "Victor" Low Pressure Steam Traps A heavy duty trap for large volumes of con densation at low pressures. -We make separators of every type and all sizes for all pressures and conditions, to remove moisture from live steam, vibrat ing steam lines, oil from exhaust steam, -etc. * conditions. Exhaust Heads Designed to eliminate noise and spray. Three types to select from--the "Cyclone" Heavy Duty, and Standard Galvaniz ed Steel--also, the cast iron type, to remedy alt Sizes 1 in. to 48 in. Send for descriptive Bulletins on any of the items listed on this page. 1231 1 ! Heating Systems specuitTM Yamall-Waring Company Manufacturers of Steam Specialties 7600 Queen Street, Philadelphia 18, Pa. YARWAY IMPULSE STEAM TRAPS Construction:--The Yarway Impulse Steam Trap is unique in that there is only one moving part, the simple valve F. This trap is made of bar stock throughout, no castings used. For pressures up to 400 lb, body and .bonnet of cold rolled steel, cadmium plated; cap of tobin bronze, valve and seat of heat treated stainless steel. For pressures 400 to 600 lb, trap is all stainless steel. Operation--Movement of valve (F) is governed by changes in pressure in control chamber (K). At lower temperatures, con densate- bypassing, continuously through orifice in center of valve reduces chamber pressure below inlet pressure and valve opens, allowing free discharge of air and condensate through seat. As condensate approaches steam temperature, low cham ber pressure causes vaporizing and the increased volume builds up pressure in control chamber, closing valve (F). List Prices, Weights and Dimensions No. 60 Series--up to 400 lb. and No. 120 Series--up to 600 lb. Advantages Light Weight--Yarway traps need no support--H in. trap weighs only 1% lb. 2 in. trap weighs 8% lb. Small Size--Can be installed in cramped quarters--in. trap measures 2% in. long--2. in, trap, 4% in. long. - Will not air bind. Require no priming. Insure quick heating. Operate on exclusive Impulse principle (U.S. Patents No. 2,051,732 and 2,127,649.) Low Price--Often cheaper than repair ing old traps. Factory set to operate at all pressures up to 400 lb (or 600 lb) without change of valve seat. Send for descriptive Bulletin T-1739. Size Vz* No*. 60 or 120 Vi' No*. 61 or 121f; No*. 63 or 123 1%' No*. 64 or 124 iy^'Nos.66or 126 2' No*. 67 or 127 Trap Complete $15.00 22.00 31.00 48.00 68.00 90.00 Weight Pound* i'/. 2 2'/2 4 5'/. 8'/i Length Inches 2/* 3 V/, 3y. 4*4 Yarway Fine-Screen Strainers offer better protection against rust, scale and dirt for all steam equipment. Made in six standard sizes from in. to 3 in. Cadmium plated, inside and out. High grade Monel woven-wire screens, Many thousands in use. Write for Bulletin S-201. YARWAY EXPANSION JOINTS All-steel welded construction; light but strong. Chromium covered sliding sleeves. Cylinder guide and stuffing box integral, assuring perfect alignment. Internal limit stops. Gun-pakt and Gland-pakt types: Gun-pakt (illustrated) fitted with screw guns which permit addition of plastic packing while joint is under pressure. Sizes 2 in. to 24 in., single end or double end, flanged or welding ends; 150, 300 and 400 lb pressures. Also all-brass joints, in. to 2 in. For additional details send for Bulletin EJ-1911. 1232 Heating Systems * Air Anderson Products INC. Cambridge 39, Massachusetts Vent-Rite Air and Vacuum'Venting Valves for Radiators Vent-Rite No. 66 Control Valves Vent-Rite Unit Heater Valves For Profitable, Efficient Venting Valve Installations .,. Specify Vent-Rite The elimination of valve trouble caused by unavoidable accumulation of dirt can immediately be effected by use of Vent-Rite Air and Vacuum Venting Valves. Every VentRite Valve can be quickly and easily taken apart, cleaned, reassembled and adjusted, and restored to its original working condition. In rare cases where a part may have become damaged, the valve may be sent to the factory for complete recon ditioning. Only Vent-Rite Valves offer these advantages. ; It is easy to obtain the correct venting rate in each radiator in a system, regardless of size or location, because every Vent-Rite Valve has an exceptionally wide and complete range of venting rates. Adjustment of the vent ing rate at the individual valves is easily accomplished through a streamlined, convenient adjusting device. You can be sure of Balanced Radiation ... of even, uniform dis tribution of heat. . Vent-Rite Air and Vacuum -Valves are built for both oneand two-pipe systems in a wide range of types, sizes, out lets, and venting capacities. (The Vent-Rite Line in cludes Non-Vacuum Valves Nos. I, 51, 3, 5A & 55, and Vacuum Valves Nos. 2, 62, 4, 6A & 66.) No.2 THE VENT-VAC SYSTEM Even temperatures are provided with the Vent-Vac System by continuing the distribution of steam between firing periods. The.steam is available through the use of heat left in the boiler and is distributed to the points where heat loss is greatest. To insure fast, uniform distribution of steam during the firing periods, it breaks the vacuum used between firing periods. This; breaking of the vacuum occurs at a predetermined point, within the limits of the control, before the start of every firing cycle, provided the heat transfer from boiler to radiation has J>ecn completed. Vent-Rite Vacuum Valves are used in conjunction with a Vent-Rite Control Unit; The system is simple, economical, and amazingly effective. Vent-Rite Control Units not only create vacuum in the system between firing periods, but also limit the amount of vacuum that can be created to the point beyond which the distribution of excessively expanded vapor would be inefficient. REPAIRABLE All Vent-Rite Valves are Repairable VENT-RITE CONTROL VALVE Vent-Rite Control Valve No. 66 is the heart of the Vent-Vac System of steam control for automatically fired one-pipe systems. It takes the place of a main line vent, limits the amount of vacuum created, and breaks the vacuum at a pre-determined point, within the limits of the control, before the start of every firing cycle, provided the heat transfer from boiler to No. 66 radiation has been completed. It is entirely mechanical. With the Vent-Vac System, using a No. 66 Control Valve, Vent-Rite Pioneered a system is vacuum between firing periods, non-vacuum CONTROLLED VENTING during the firing, combining the best of both systems andassuring Balanced Radiation . .. assuring even distribution BALANCED RADIATION of heat to give more comfortable rooms for better living. REPAIRABLE VALVES Send for Bulletins. VENT-VAC SYSTEM 1233 Healing Systems valves. Air The Dole Valve Company Main Offices and Factory: 1933 Carroll Avenue, Chicago 12, 111. THE ALL STAR LINE AIR AND VACUUM VALVES Selecting the right vent for a particular purpose is your assurance of the utmost efficiency and economy from one pipe steam heating systems. The Dole line covers every venting need and offers a complete choice for every purpose. Dole No. 1A Vari-Vent Air Valve Modern gas, oil or stoker fired one pipe steam systemsrequireQUICK vent ing. This radiator valve lets air escape twice as fast as ordinary valves and balances the flow of steam at the first "breath" of boiler pressure. Adjust able vari-vent feature gets air out of those "far away" radiators as quickly as those close to the boiler. Dole No. 3 Air Valve Vents radiators of hand fired gravity steam heat ing systems. Double shell construction provides separate passages for air and condensation--extra large float defeats spitting or water leakage. Com plete venting assured' at pressures up to 10 lbs. Dole No. 2B Vari-Vent Vacuum Valve Adjustable radiator valve for " vacuumizing" and balancing gravity steam heating systems. Patented Dole bellows vacuum seal locks out air alter it has been once expelled from the sys tem. Easily adjusted vari-vent feature assists in equalizing steam flow to all radiators. Dole No. 1933 Air Valve Low cost valve for venting . radiators of hand fired systems. Large float pro vides a seal against con densation to stop spitting. Dole No. IB Vari-Vent , Air Valve Balances the flow of steam to convectors, either cast iron or copper, of automatical ly fired systems. Dole No. 1C Quick Vent Float Valve. Vents mains and speeds flow of steam to radiaators of automatically fired systems. Extra large venting port. Dole No. 5 Quick .Vent Float Valve Vents steam mains on hand fired- systems. Positive seal against water. * Dole No. 4 Quick Vent Valve For quick venting mains that end 18 in. or more above the boiler water line. Dole No. 103 Vacuum Valve For venting convectors, ceiling radiators and pipe coils of "vacuumized" gravity steam systems. Dole No. 6B Vacu um\Val.ve Vents the mains of "vacuumized" one pipe steam systems. Pre vents the return of air. Closes against water. Dole No. 14 Key Valve Low cost venting device for con cealed radiators and convectors of hot water heating systems. Protects panel fronts from rusty water stain. Write The Dole Valve Company for complete catalog and handy selector chart which indicates the Dole Air or Vacuum Valve most suited for a particular.need. 1234 Healing Systems va/.es Jenkins Bros. BRONZE - IRON - STEEL VALVES Mechanical Rubber Goods SO White St., New York 13, N. Y.; 524 Atlantic St.. Boston 10. Mass.; 376 Spring St., N.W.. Atlanta 3. Ga.; 133 N. Seventh St., Philadelphia 6. Pa.; 1514 Fulton St.. Chicago 7, 111.; 510 Main St., Bridgeport 9, Conn.; 660 Market St., San Francisco 4. Cal. Jenkins Bros., Ltd.: Montreal; Factory, Lachine, Canada * London, Eng. IN VALVES ** GIVES YOU EVERYTHING OVER 500 DIFFERENT JENKINS VALVES COVER EVERY HEATING AND AIR CONDITIONING NEED To adequately describe the complete Jenkins line of valves requires a Catalog of more than 400 pages. There are over 500 different types and patterns of valves that bear the trusted "Diamond" trade mark. Practically speaking, Jenkins can furnish any valve that you may require for plumbing, heating, air conditioning, general industrial or engineering service. . General Classifications of Jenkins Valves Include--Bronze Valves fitted with Jenkins renewable composition disc. Bronze Regrind-Renew Valves with bevel and plug type seats. Bronze Gate Valves. Iron Body Valves fitted with Jenkins renewable composition disc. Iron Body Regrinding Valves. Iron Body Gate Valves with solid wedge and double disc parallel seats. All-Iron Valves. Air Furnace Malleable Iron Valves. Cast Steel Gate, Globe and Swing Check Valves. Electrically and Hydraulically Operated Valves. Radiator Valves. Fire Line Valves. Quick-opening and Self-closing Valves, Needle Valves, Y Valves, SolderEnd Valves, Stainless Steel Valves. Other Jenkins Products Are-- Composition Valves Discs exactly suited to service conditions. Friction Tape, Splicing Compound, Mechanical Rubber Goods. JENKINS VALVES ARE SOLD BY GOOD SUPPLY HOUSES EVERYWHERE Consult A-Z Listing of Thomas Register For the One Nearest You; 1235 Insulation Conduit and Undergeo und Adsco PRODUCTS for STEAM SERVICE American District Steam Company North Tonawanda.N.Y IN BUSINESS OVER 65 YEARS Branches and Agents in Principal Cities Tile-Conduit with ADSCO Filler Insulation-- a **Fiberglas" Product OVER 65 YEARS EXPERIENCE IS BUILT INTO THE DESIGN AND MANUFACTURE OF DEPENDABLE ADSCO PRODUCTS FOR PIPE LINES For over 65 years ADSCO engineers have specialized in the design and appli cation of pipe fittings and accessory equip ment for underground and surface steam, water, oil and other piping systems. An extensive, modem plant including foundry, machine shop, casing mill, shipping and storage facilities enable ADSCO to produce high grade products by skilled workmen under expert supervision. Alignment Guide Internally Guided Joint LEADING MAKERS OF EXPANSION JOINTS As pioneer manufacturers of expansion joints for pipe lines, ADSCO is the largest single producer pf such equipment in the world. We offer the most extensive line of packless and slip type joints in various types to meet the requirements of any pipe line expansion and contraction problem. In addition, ADSCO produces all of the * related equipment necessary to the perma nent installation of efficient pipe lines, including tile conduit for underground, lines, pipe supports, saddle plates, align ment guides, steam traps, condensation and Bow meters, storage and instantaneous water heaters, strainers, separators, man hole frames, and vapor heating specialties. Internally-Externally Guided Joint. Piston-Ring Type Joint ENGINEERING ASSISTANCE ADSCO engineers welcome the oppor tunity of working with you in the solution of your pipe line expansion and contraction . problems and correspondence is invited giving the details of any proposed piping installation. ' WRITE FOR ADSCO CATALOG Nj>. 35 All ADSCO products are illustrated and described in the latest ADSCO Catalog No. 35 containing informative data for the specification and purchase of depend able products for underground or surface pipe line distribution systems. Write for your copy today to the American District Steam Company, 65 Bryant St., North Toriawanda, New York. 1236 Insulation Conduit and Underground H. W. Porter & Co. INCORPORATED 817-G Frelirighuysen Ave., Newark 5, New Jersey Permanent Protection and Insulation for Underground Pipe Lines BALTIMORE. MD. CHARLOTTE. N. C. RICHMOND, VA. Also sold and installed by Johns-Manville Construction Units in all principal cities. its PArQfr STEAM CONDUIT SYSTEMS "Permanent" Protection is Import ant--Therm-O-Tile has been on the mar ket over a dozen years. Its design is well known to all leading heating and ventilat ing engineers but we would again like to point to the great importance of "Perma nent protection." In previous issues of this book we stated that Therm-O-Tile is "A complete conduit system for the permanent support, pro tection, and insulation of underground mains for steam distribution." Beware "Temporary" Protection We consistently em phasize the word "per manent." It is easy to provide "temporary" protection and insula tion for. underground pipe lines. Threads and joints don't fail immediately, and foun dations don't sag im mediately, but unless the job is properly done it won't be long before water seeps in and.ruins the insulatiorr." With wet and spoiled insula tion, efficiency drops drastically. And, unless the conduit is built on a solid foundation there will be sagging and col lection of water in pockets. Be sure of a "permanent" job. Therm-O-Tile Drainage System-- In the Therm-O-Tile concrete base there is a ' drainage channel--clearly visible in this photo--which carries off all water that may enter the conduit from any source, thereby keeping the insulation permanently dry. Drainage is entirely internal. The channel is accurately and permanently sloped so that condensate or other pockets cannot form. Open to thorough inspection at any time at manholes. Amply large to keep the pipe space dry at all times. "Spread Footing" Foundation--So that there will be no settling or sagging the Therm-O-Tile "Spread Footing" foun dation base is a thick concrete slab poured directly in the trench bottom as shown in the photograph. It is steel reinforced or placed on driven piles when installed over filled or boggy ground--constructions that are necessary for permanent protection. See Previous Issues--In issues of this Guide previous to 1944 we gave details regarding the Tile Envelope which pro duces 27 different conduit cross sections. We told about the ideal accessibility of this conduit, its great strength, how it is water-proofed, and how the insulation is applied. For complete information ask for a copy of Bulletin 381. Competitive in Cost--Despite the high efficiency, greater strength, dependability, and other outstanding features that are obtained -in Therm-O-Tile, it is neverthe less competitive in total first cost. Final cost is much less, thanks to its permanence. Thorough investigation is invited. We Co-operate--Our engineers have had unusual and broad experience in the design and installation of steam conveying equipment for an exceptional range of purposes. They will gladly cooperate with you in the solution of your own individual problems of this nature. .. Single or Multiple Pipe Lines Using Sectional Pipe Insulation. Showing a typical Therm-O-Tile pip ing arrangement when there are two pipe lines. Note the channel drain which' "permanently pro tects" the insulation. 1237 Insulation Conduit And Underground The Ric-wiL Company INSULATED PIPE CONDUIT SYSTEMS Union Commerce Bldg., Cleveland, Ohio Agents in Principal Cities ----------------------------------:------------------------- <i---------------------------------------- ----" There is a Ric-wiL insulated conduit system engineered to your specific needs--the transmission of steam, hot water, oil, hot or refrigerated process liquids--providing heat transfer with the lowest possible loss. 1. RIC-WIL INSULATED PIPE UNIT-SINGLE PIPE SYSTEM Prefabricated complete units--pipe as specified, thoroughly insulated, in helical corrugated conduit, coated and wrapped with asphalt saturated asbestos, felt. 21-ft lengths for speedy installation. For underground or overhead systems. I RIC-WIL INSULATED PIPE UNIT-MULTIPLE PIPE SYSTEM Any specified combination of pipes in prefabricated conduit --insulated and protected the same as the single pipe system. Any or all of the pipe lines may be specially insulated to meet job requirements. 3. RIC-WIL INSULATED PIPE UNIT-fOR PROCESS LIQUIDS An adaptation of the multiple system used where a steam or hot water line heats fluids in other lines. Pipes are insulated from the exterior but not from, each other. Sizes and specifications as required--conduit same as for other insulated pipe units. 4. RIC-WIL STANDARD TILE CONDUIT-TYPE F Vitrified glazed A.S.T.M. Standard Tile Housing--add and waterproof--with foundation type base drain sup porting weight of piping through correctly engineered pipe supports. Positive locked-in-place cement seals on sides and ends. For single or multiple pipes. 5. RIC-WIL SUPER TILE CONDUIT-TYPE F Same advantages as Standard Tile but with walls approxi mately double thick for strength under heavy traffic or where overhead load is above normal. Will support con centrated static load of 6 tons per wheel under actual installation conditions. Base drain of extra-heavy tile. 6. RIC-WIL CAST IRON CONDUIT-TYPE F . . Heavy reinforced cast iron conduit for use where under ground pipe lines run close to or under railroad tracks. Durable, water-tight and vibration-proof. Positive locked- in-place cement seals on sides and ends with metal clamps for extra tightness. ^ 7. RIC-WIL TILE CONDUIT-UNIVERSAL TYPE Where installation conditions dictate the-use of a concrete pad Ric-wiL Universal Tile is recommended. Side walls are double-cell vitrified trapezoidal block design. Arch may be Standard Tile, Super-Tile, or Cast Iron. 8. RIC-WIL TILE CONDUIT-TYPE DA For oil or process liquids where conduit must be insulated but individual lines are not insulated from one another. Insulation is a diatomaceous earth lining, moulded and keyed to inside of tile. May also be used (Type DF) with fibre insulation for steam heat, power and superheated steam. Applicable to Standard, Super-Tile and Cast Iron. Ric-wiL accessories are available in all type systems; standard and special fittings. factory fabricated or field fabricated expansion devices, alignment guides, and anchors. Descriptive bulletins on request. GET THE ORIGINAL--SPECIFY RIC-WIL 1238 Insulation Glass Blocks Skylights American 3 Way-Luxfer Prism Co. 24 N. Pulaski Rd., Chicago-24, 111. AMERICAN GLASS BLOCK SKYLIGHTS a--the. AMERICAN Way! American 3-Way Rooflights make use of Glass Blocks of special design and strength, manufactured by the proven process, incorporating four way design lenses on inner surfaces of plates, also resulting in uniform even light distribution over wide areas, leaving top and bottom surfaces smooth for easy cleaning. Glass Blocks are 9 in. x 9 in. x 2^ in. and spaced approximately 10^f in. on centers. Low Heat Transfer Tests conducted by methods suggested by the A.S.H.V.E. Code show that Glass Block Rooflights have about two and onehalf times the insulating value of sheet metal skylights with no heat losses by "escape," since the construction is air tight. Solar Heat Transmission Reduction in total solar heat gain as compared with ordinary windows is in dicated by relative values given in Table 10 and Table 12 in Chapter 15. Section of American Glass Block Skylight Showing Method of Block Application Insulated Construction ' Construction of rigid reinforced con crete grids can be arranged with insulation materials sufficient to approximately equal the performance of the glass blocks. American Class Block Skylight Triple Plates of Glass . Magnalite Diffusing Glass units may be attached to under side of glass block construction thus making for effective uniform light diffusion and even distribu tion; also very effective in condensation problems. Condensation Due to the nature of the grid con struction where insulation materials are employed with semi-vacuum glass blocks assemblies there is little or no tendency for condensation to form on the under side. Should relative high humidities or ab normal conditions exist, further insulation treatment can be provided. Glass Block Assemblies for all off-vertical arrangements are available. Details will be furnished on request. 3-Way Glass Block Skylights may also be furnished without special insula tion treatment in reinforced concrete grid construction. Write for Complete Information 1239 Insulation Window Screens Ingersoll Steel Division Borg-Warner Corporation 310 So. Michigan Ave., Chicago, Illinois Distributors in the Principal Cities YOU CAN ELIMINATE SWELTERING SUMMER HEAT THAT CAUSES DISCOMFORT . . . CUTS WORKERS EFFICIENCY . . . ADDS TO REFRIGERATION COSTS--BY INSTALLING KoelSUade Screen THE AUTOMATIC "window" insu lation that controls sun heat and still provides ample light and visibility. KOOL- SHADE Sun Screen is--in effect--a bronze outside miniature Venetian blind with the louvres permanently slanted outward and down at a 17 deg angle to block, reflect, absorb and radiate a^piuch as 90% of the sun's heat rays--outside the window! Air Conditioning Engineers, during the past 7 years, have proved that KOOL- SHADE: . Frequently eliminates the need for . zoning. Maintains lower temperatures in non- cooled rooms. . . Reduces size of Refrigeration instal lations. (100 sq ft of KOOLSHADE on sun-exposed glazed areas is equal to approximately one ton of equipment.) Cuts equipment operating costs. Because KOOLSHADE needs no ad justing it works most efficiently during peak solar loads. (See table on opposite page.) KOOLSHADE can be adapted to any type window No matter what your particular prob- . lem, authorized KOOLSHADE distribu tors have the answer. Remember that KOOLSHADE also gives insect protection as an added feature. In comparison with these methods . . . which, at best do only part of the job, KOOLSHADE stops heat rays outside the room and does not obstruct ventilation or outside view. Ingersoll Steel Division Insulation Window Screens KOOLSHADE has been proved in actual use . Below are listed a few leading Industrial users of KOOLSHADE--the scientific sun heat control. KOOLSHADE NEVER MARS ARCHITECTURAL HARMONY ' The Hoover Company No. Canton, Ohio American Tobacco Company Durham. N. C. Easy Washing Machine Company Syracuse, N. Y. Ford Motor Company River Rouge, Mich. General Electric Company Chicago, 111. Inland Steel Company East Chicago, 111. Pullman-Standard Car Mfg. Company, Chicago. 111. Radio Corporation of America Bloomington, lnd. Wright Aeronautical Corporation Cincinnati. Ohio Pacific Gas & Electric Company, Sacramento, Calif. The organizations listed above are typical of - hundreds of satisfied KoolShadk users. FOR INFORMATION regarding tech nical proof of performance and descriptive literature covering complete installation methods--write Ingersoll Steel Division. STOPS HEAT OUTSIDE--KILLS GLARE DATA FROM PITTSBURGH TESTING LABORATORY FROM CALCULATIONS BASED ON ACTUAL TESTS Solar Radiation Transmitted Through Windows . Equipped with KOOLSHADE Sun Screen For 40 deg. latitude, on July 21st All figures given represent B.t.u. per sq. ft per hour. yTIME*- SOLAR RADIATION 6 AM 7 AM 8AM 9 AM 10 AM UAM 12 M Intensity Incident to Vertical Surface (1) Transmitted thru Window with KOOLSHADE (2) Intensity Incident to Vertical Surlace , ., Transmitted thru Window with KOOLSHADE . Intensity Incident to Vertical Surface Transmitted thru Window with KOOLSHADE Intensity Incident to Vertical Surface Transmitted thru Window with KOOLSHADE Intensity Incident to Vertical Surface Transmitted thru Window with KOOLSHADE Intensity Incident to Vertical Surface Transmitted thru Window with KOOLSHADE Intensity Incident to Vertical Surface Transmitted thru Window with KOOLSHADE NE 72 33 143 38.5 143 17 104 8 46 1.5 NW EAST 80 38.5 180 60.5 211 42.5 192 22 143 It.5 75 3.5 WEST SE 40 13 112 22 155 20.5 168 17 156 13 12! 8.5 73 3.5 SW SOUTH 6 PM 5 PM 8 0 4 PM 46 2 3 PM 77 4 2 PM 95 5.5 1PM 103 6 12 M SOUTH <TIME* (7) Data from the A.S.H.V.E. Guide 7340. (2) Figures represent Solar Heat Gain in EXCESS of heat gain by conduction through window glass. 1241 Insulation Windows Libbey Owens`Ford Glass Company Nicholas Building, Toledo 3, Ohio THERMOPANE Insulating Glass L-O-F Thermopane is a transparent factory-fabricated insulating glass unit composed of two or more panes of glass separated by in. or 3^ in. of dehydrated captive air, hermetically sealed at the edges in the factory with a metal-to-glass bond. Thermopane is Fabricated to ordered sizes at Libbey-Owens-Ford's factory. The glass, before being assembled into Ther mopane units, is specially cleaned before the patented Bondermetic seal is applied. The layer of air inside the Thermopane units is scientifically cleaned, dried and hermetically sealed. The patented, metalto-glass seal bonds the two or more panes of glass into one unit to prevent dirt and moisture from entering the air space. - Thermopane Reduces the coefficient of heat transmission; increases the room- side surface temperature, thus promoting radiant comfort and lowering the dew point; furnishes a control of light quantity and quality through combinations of various types of glass, and deadens sound transmission to some degree. * Double-glass Thermopane: Glazing of wood or metal windows or doors for practically any purpose in structures re quiring heating or air conditioning. Triple-glass Thermopane: Large stationary units such as insulated glass walls in homes, apartments, public and commercial buildings and in show windows for refrigerated display where temperature differential must be considered. Quadruple-glass Thermopahe: Engi neered to meet low temperature and high humidity conditions. Thermopane Uses are many, but may be briefly summarized as below: Thermopane Units provide a high resistance to heat flow, varying with the number of panes and the thickness of the air space used. In summer the low heat transmission coefficient reduces the load on air conditioning systems. In winter it saves heat. The greater efficiency of Thermopane makes it possible to incor porate larger windows in houses and keep the cost of fuel constant. For example, a house could have 107 sq ft of Thermopane instead of 35 sq ft of single glazing and not lose any more heat. Thermopane permits the influx of solar heat in exterior glazing of buildings without a prohibitive com pensating loss from conduction. The over-all heat transmission coef ficient U varies with the ranges of tem perature at which the coefficient is deter mined. For most practical heat loss calculations coefficient U can be the value' determined at 0 deg outside temperature, 70 deg inside temperature, 51 mph outside air velocity, 0.25 mph average ^nside air velocity. The following table gives such values: . of Pane* . of .Panes ' U Values '/sin. 'h Air Space Air Space >/.' 0.62 0.57 2 VS 0.57 0.53 '/' . vs 0.42 039 037 035 Note: U for single in. thick glass ** 1.14, i?=0.88. U for single ) in. thick glass = 1.07, 72 = 0.94. The Room Side Surface Tempera ture of Thermopane is considerably higher than that of single glazing. Usually radiators or registers are near glass areas in buildings to offset conducted heat loss from a room and radiant loss from the bodies of persons near cold glass' areas. The higher glass surface temperature of Thermopane greatly reduces the amount of heat which must be supplied, permitting more flexibility in room design. - Another Important Benefit from Thermopane is. the prevention of frost or condensation from forming on the room- side surface of a single pane of glass in winter due to higher room humidity. The absence of condensation on the room-side surface of glass is of considerable impor tance where clear visibility is a factor as in residences, all types of commercial or industrial buildings and refrigerated dis play spaces. More Complete Information on Thermopane is available by writing . to Libbey-Owens-Ford, or its district office nearest to you, and requesting technical data sheets prepared by Don Graf, a general booklet about the product, and a brochure which discusses Solar Housing. LIBBEY-OWENS-FORD GLASS COMPANY, Toledo 3, Ohio 1242 ' '. Insulation Olass Blocks Owens-Illinois Glass Company INSULUX PRODUCTS DIVISION, Toledo 1, Ohio glass D GO S 09 [LQ92X BL0CK Dealers in all principal cities Insulux Glass Block Give Better Control of Interior Conditions Insulux Glass Block are hollow, partially evacuated units, 3% in. thick. Faces are smooth or ribbed. Solid panels of these block, laid in mortar, make a light-trans mitting wall of high insulating value. Their proper use aids control of interior conditions to a point where initial and operating cost of heating or cooling equip ment is reduced. . Conductivity The U factor for ribbed glass block is 0.46; smooth face, 0.49. For design pur poses, these, factors may be used as con stant for either 6 in., 8 in. or 12 in. block. See Chapter 6 of this volume foradditional data. `. This U factor is only 43 per cent of that of ordinary light-transmitting materials. The reason lies in the two heavy glass surfaces separated by partially-evacuated ar.d her metically sealed dead air space. Surface Condensation Because of the low overall air-to-air heat transfer, the room condensation point of a glass block panel is much lower than that of ordinary windows. This will permit higher humidities for both comfort air conditioning and in industries where high humidity is part of the process. Glass block are not subject to deterioration caused by moisture. Infiltration Insulux Glass Block are sealed in the building. They form a barrier against infiltration of dust, air and vapor. Winter drafts and summer vapor leakage are cut. Natural ventilation requirements can be met by installation of windows either inset in the panels or installed directly below the panels. Solar Heat Gain A comparative test showed 94 per cent more solar heat through steel sash than through glass block. However, as with sash, glass block transmit less solar heat when properly oriented and shaded. Data in Table 12, Chapter 15 of this Guide are for standard block. Other designs, such as the No-glare and Directional block afford further reduction. Data will be sent on request. . Design, Sizes, Erection Insulux Glass Block is made in 10 face patterns for residential or industrial uses. Sizes are:*5^ in. x 5% nM 7% in. x 7% in. and 11% in. x 11^ in. All are 3 % in. thick. Blocks are erected by laying in mortar like any masonry material. Complete technical data, des cription, etc., sent to you on request. 1243 Insulation Glass [^Pittsburgh Coming Corporation Room 616, 632 Duquesne Way, Pittsburgh 22, Pa. PC FOAMGLAS--waterproof, fireproof--Insulation Also manufacturers of PC Glass Blocks PC FOAMGLAS is different from all other insulating materials, being composed of millions of minute cells of inert air sealed in glass. Thus PC Foamglas embodies not only remarkably efficient insulating quali ties, it is also--vaporproof, fireproof, water proof and permanent. Protecting delicate high-speed ma chinery and goods in process, insuring con tinuous, efficient operation--demands rigid control of temperature and humidity in all sorts of mills and factories. PC Foamglas, the new cellular glass insulation, has proved its ability to meet the most exacting requirements--efficiently and economically--in a wide range of industries. On roofs and in core walls, floors, duct work and processing equipment, PC Foam glas retains its full insulating efficiency throughout the life of the building. It is an efficient vapor-seal and water-stop, requires no repairs, maintenance or re placement of the material during ordinary use. Check these features of PC Foamglas against other insulating materials. I. Permanent insulation, 2. Vermin- and vaporproof. 3. Fireproof. 4. Waterproof, . 5. Light weight, - 6. Easy installation. 7. Rigid structure. 8. Economical. For technical data on PC Foamglas, send for special bulletins. : Vnder severe service conditions such os the roof pictured here, PC Foamglas retains its insulating efficiency because it is waterproof and vaporproof. When you install PC Foamglas Insulation in core walls, it becomes an integral part of the structure, assists in efficient, trouble-free control of temperature and humidity levels in the enclosed area--per manently. . SEND FOR FREE BOOKLETS--To find out how and why PC Foamglas will save time and money on all sorts of heat ing, ventilating and air-conditioning jobs, send for free copies of our booklets which describe its advantages when used on roofs, in core walls and in floors and on tanks, towers, ducts and other processing equipment. 3-07 1244 Insulation Glass Blocks Pittsburgh Coming Corporation 632 Duquesne Way, Pittsburgh 22, Pa. Distribution through Pittsburgh Plate Glass Company warehouses in principal cities and by the W. P. Fuller Company on the West Coast. Also Manufacturers of PC Foamglas Insulation. |n I Glass Blocks allow the economical I"Cl use of large glass areas, reduce heat loss in cold weather and materially aid air-conditioning. This is because each PC Glass Block contains a sealed-in dead- air space that -is an effective retardant to heat transfer. Thermal Insulation Tests run by nationally recognized labora tories have established the value of glass blocks for insulation of light-transmitting areas. These tests have proved that with glass block panels, heat loss is slightly less than half that experienced with singleglazed windows. In computing heat losses through panels for most design purposes, it is recommended that a " U" value of 0.46 to 0.49 be used for-all block sizes and face patterns. For complete data on heat transfer values .see the section on heat transfer elsewhere in this Guide--page 138. Surface Condensation Due to high insulating value, condensation will not start forming on the room side of glass block panels until outside air has reached a temperature much lower than that necessary to produce condensation on single-glazed windows. The accompanying chart shows at what temperatures con densation will form. door temperature of --14 deg is reached. Under similar conditions with single-glazed sash, moisture will begin to form when the outdoor temperature reaches +33F. Solar Heat Gain The use of glass blocks for light-trans mitting areas results in a marked reduction in total solar heat gain as compared with ordinary windows. This factor is of con siderable advantage in buildings that are properly air-conditioned, but does not eliminate the need for adequate ventilation or shading in non-air-conditioned rooms. For data on solar heat gain through glass blocks see table 12 in the solar radiation section of this Guide--chapter 15. This table is for standard pattern glass blocks. PC Glass Blocks Aid Air-Conditioning The three chief aims of air-conditioning-- temperature control, humidity control and cleansing of air are all aided by the use of PC Glass Blocks. Heat loss is less in winter--heat gain is less in summer. Ideal 'humidity conditions are much more easily . maintained without undue condensation. Solar heat transmission and radiation are reduced. Dirt can't filter in, for each panel is a tightly sealed unit. Outdoor temperature required to ' produce condensation on the room side surface of PC Glass,Block panels. For example, with inside air at 70F and relative humidity at 40 per cent, condensa tion will not begin to form on the interior surfaces of a glass block panel until an out Sizes and Shapes Available PC Glass Blocks are available in ten at tractive patterns, some of the patterns being designed for special control and direction of trans mitted daylight. For complete informa tion on the sizes and shapes of PC Glass Blocks, and for illustrations of the many patterns available, write the Pittsburgh Corning Corporation, Pittsburgh, Pa., or call the nearest Pittsburgh Plate Glass Company warehouse. Additional technical data, including de tailed figures on thermal insulation, solar heat gain, surface condensation, light transmission and construction data, will be furnished on request. . 1245 Insulation ALFOL Alfol Insulation Company Incorporated - 155 East 44th St., New York 17, N. Y. . Agents in Principal Cities HEAT INSULATION for ALL PURPOSES - ALFOL PRE-FABRICATED INSULATION PANELS FOR TANKS, TOWERS. AND ALL TYPES OF HEATED EQUIPMENT Metal Jacketed Panels con taining insulation best suited for each particular condition. Removable and Replaceable by means of Lock-Joint con struction. Shop Fabricated with Cut outs for manholes and pipe connections. Prefabricated Panel. At Right-- Applied to Tower Easily and Rapidly Applied by any type of labor. . Trim Appearance with mini mum of up-keep. FOR MORE DETAILED INFORMATION WRITE FOR ALFOL. PANEL DATA BOOK ALFOL BUILDING INSULATION BLANKET Pure Aluminum Foil spaced on three-ply thick paper vapor barrier sheet. Single and Double Layers insure spaced sheet to reduce conduction and convection. Ap plied between structural, members or furring, Alfol 'Blankets give high insula tion value at low cost. Specifications Description Widths Net Area Net Wright per Roil per Roli l6'-24' 250 sq.ft. 17 lb*. Type 11.--2 Layers ALFOL !6#-20'-24* 250 sq.ft. iy lb*. See technical data in Table 1, Section C, Page 116, this volume. ALFOL RADIATOR REFLECTORS . ' ALFOL REFLECTORS behind radiators reduce heat loss through walls, save fuel. Temperature gradient to outside reduced 50 per cent. THIRTEEN YEARS' SERVICE PROVES LASTING. VALUE OF ALFOL 1246 Insulation American Flange & Manufacturing Co. Inc. 30 Rockefeller Plaza, New York 20, N. Y. Circle 7-3741 Terro-lherm Reg. U. S. Pat. Off. STEEL INSULATION Ferro-Therm Steel Insulation, made from rigid steel sheets with a special alloy coating, reflects 95 per cent of all radiated heat. This high reflectivity, combined with extremely Tow heat storage capacity, provides maximum insulating efficiency m a minimum overall thickness. - . - Saves Pay Space and Weight In building construction, the: general practice is to install one sheet of Ferro-. Therm between roof rafters or over ceiling joists and between studs of exterior walls. In cold storage construction, the number of sheets of Ferro-Therm depends on the temperature to be maintained and the U value required. The k value of Fern> Therm, based on tests, is listed in the Data Book of the American Society of Refriger ating Engineers as0.22fl-Btu per (hr) (sq ft) (F temperature difference). Laboratory tests and thousands of applications have demonstrated that a wall of Ferro-Therm will, provide insulating efficiency- equiva lent to a wall of mass insulation approxi mately twice as thick. Assures Rapid Pull Down of Temperature The low heat 'storage capacity of FerroTherm is extremely important in achieving rapid pull down of temperature, and in saving refrigeration costs for the initial and each subsequent cooling of space. Specifically, the heat storage capacity of a single sheet of No. 38 gauge is 0.029 Btu per (hr) (sq ft) (F temperature difference). This is approximately of the heat storage capacity of 1 sq ft of 1 in. thickness corkboard. Permanent, Fire-proof Insulation . Ferro-Therm construction eliminates trap ping of moisture condensate, with sub sequent deterioration of the construction. As it is all-metal, Ferro-Therm cannot be penetrated by rodents, vermin or termites, and is absolutely non-combustible. The value of Ferro-Therm for fire protection is apparent. . , 125 Below Zero Maintained in Altitude Test Chambers Ferro-Therm has proved its superiority in buildings, cold storage roofils, refrigerated cabinets, locker rooms, dry ice; containers, refrigerated railway car construction, ovens, high-temperature storage tanks--in fact, practically every type of'application where high insulating efficiency with economies in space and weight are a requisite. The most notable demonstra tion of Ferro-Therm performance has been its selection for the insulation of altitude chambers for the testing of Army and Navy aviation equipment and personnel. In these chambers, temperatures as low as --125 F were maintained, with a tem perature drop of +70 F to --100 F in 10 to 12 min. Our catalog, giving data and installation details on Ferro-Therm. will be sent upon reguest. Thinner Wall Construction for Lower Temperature Requirements Thickness of Ferro-Therm 3 sheets 4 sheets . Construction - 1 in. 1H in- U Factor. .13 .097 5 sheets 2 in. .077 6 sheets in. .064 7 sheets 3 in. .055 10 sheets 4J4 in. .04 ' 12 sheets ' 5Kin. .03 . 14 sheets 6Hin. .025 ` The chart above shows the wall thickness and the number of sheets of Ferro-Therm for various U factors. For any particular temperature requirement the installation .with the correct number of Ferro-Therm . sheets will require only about 50 per cent of the wall thickness required by equivavalent mass insulation, resulting in a pro portionate saving in storage space, and a great saving in weight. 1247 Insulation Armstrong Cork Company Building Materials Division Lancaster Pennsylvania Albany Atlanta Baltimore Birmingham Boston Buffalo Charlotte Chicago Cincinnati Cleveland Columbus Dallas Detroit Hartford Offices Houston Indianapolis Jacksonville Kansas City Los Angeles Louisville In Canada Memphis Milwaukee Minneapolis New Orleans New York Philadelphia Pittsburgh Providence Richmond Rochester St. Louis San Francisco Tulsa Washington, D.C. Montreal. Que. Toronto, Ont. Winnipeg, Man. Distributors . Charleston 23, W. Va------------- Capital City Supply Co. Denver, Colo________ Stearns-Roger Manufacturing Co. Portland 4, Ore--______ Asbestos Supply Co. of Oregon San Antonio, Tex------------------- General Supply Go., Inc. Eau Claire, Wib__________ _______._Horel-George Co. Ek, Paso, Tbxab.......... __...... .......... .... Neff-Stiles Co. Fort Watnb, Ind______Asbestos & Asphalt Products Co. Glendale, N. Y2_________________ Charles M. Trojahn Grand Rapids. Mich____Tony Batenburg Insulation Co. Seattle 4, Wash.Asbestos Supply Co. of Seattle South Bend 23, Lnd___Asbestos k Asphalt Products Co. Spokane 8, WashAsbestos Supply Co. of Spokane Springfield, Mass.Johnsoo Asbestos Co. Joplin, MoJoplin Cement Co. Little Rock, Ark__ __ ... Fischer Cement k Roofing Co. Manitowoc, Wis. Northwestern Asbestos and Cork Insulation Co. Springfield, Mo.Southwestern Insulation Co. Tacoma 2, Wash.,,J_____ Asbestos Supply Co. of Tacoma Terre Haute. Ind...............................The Hartmann Co. For detailed technical information, samples, and descriptive literature, ask any office or distributor. Specifications appear in Sweet's Catalogs for Architects and for Engineers and Contractors. PRODUCTS--Armstrong's Corkboard, Cork Covering, Mineral Wool Board-- Foamglas,* Heat Insulations, Armstrong's Insulating Refracto ries, Vibracork,** Cushiontone,** Temlok,** Insulation Sundries. Corkboard . The thermal conductivity of Armstrong's Corkboard is 0.27 Btu per hour, per degree temperature difference, per inch thickness at 60F mean temperature. It isfumished in rigid boards 12 in. x 36 in., 18 in. x 36 in., 24 in. x 36 in. and 36 in. x 36 in., in 1 in., in., 2 in., 3 in., 4 in., and 6 in. thick nesses. . Armstrong's Corkboard conforms in all details to Federal Specification HH-C-561b, July 26, 1941 Cork Covering Armstrong's Cork Covering is made of pure cork in sizes to fit all standard pipe sizes. The inside surfaces of each piece are machined to assure an accurate fit, free from moisture-catching air pockets. Cork covering is rigid and will not sag. Thick nesses are: Ice Water (1.20 in. to 1.93 in:); Brine (1.70 in. to 3.00 in.); and Special Thick Brine (2.63 in. to 4.00 in.). Armstrong's Fitting Covers are rigid and are_ designed to fit accurately all types of standard ammonia and extra heavy fittings, screwed, Banged, and welded. Mineral Wool Board Armstrong's Mineral Wool Board equals or exceeds Federal Specification HH-M371a for board or block form insulation; has low thermal conductivity; is moisture resistant, odorless; is easily handled and erected; possesses structural strength. Standard size IjS in. x 36 in.; thicknesses 1 in., 1H in., 2 in., 3 in., 4 in. - Foamglas Foamglas has a closed cellular structure which will not permit passage of air or moisture. It is efficient, moistureproof, fireproof, and offers effective, lasting insu lation. This new type of insulation is made in standard 12 in. x 18 in. blocks; thick nesses 2 in., 3 in., 4 in., 4^ in., 6 in. It may be used to insulate refrigerated stor age rooms and equipment. Heat Insulation The Armstrong Cork Co. distributes and offers contract service on a complete line of high temperature insulations. In cluded are: 85 pier cent magnesia blocks and' pipe covering; high temperature blocks and pipe covering; air cell blocks, sheets, andpipe covering; wool felt; hair felt; etc. Engineering and Contract Service All Armstrong offices and distributors maintain skilled erection crews. For aid in the solution of any technical problems involving insulation, isolation, or acousti cal treatment, and for literature and prices, get in touch with an Armstrong district office or distributor or the Arm strong Cork Co., Building Materials Division, Lancaster, Pa. *Reg. If. S. Patent Office. Product Mfg. by Pittsburgh Corning Corp. - **Reg. U. S. Patent Office. . 1248 Insulation TRENTON, N. J. Baldwin-Hill Co. 549 Klagg Avenue, Trenton 2, N. J. Plants in KALAMAZOO, MICH. HUNTINGTON, IND. INSULATING CEMENT Fabricated of high-ternperature-resisting A plastic insulation pro duced from high-tempera ture-resisting, nodulated B-H black Rockwool com bined with high-grade, longfibre asbestos and colloidal clay. Effective up to 1800 F; reclaimable up to 1200 F. Suitable for insulating large or small irregular surfaces, including those not suited to molded types of insulation. Contains a special rust inhibitor which pre vents corrosion taking place between insu lated surface and cement. Makes a secure bond on either hot or cold surfaces. In stantly adhesive, easy and economical to B-H black Rockwool, felted by a special patented process. A strong, light-weight block, easily cut and fitted on irregular or flat surfaces. Low alkalinity factor in sures stability under severe temperature conditions. Density--approx. 20 lb per cu ft. Standard sizes: 18 in. and 36 in. long; 6 in., 12 in. and 18 . in. wide; 1 in., 1^ in., 2 in., 23^ in., 3 in., 33^ in. and 4 in. thick nesses. Other sizes to order. Packed in high -test cardboard cartons. apply. When mixed with water to trowel- able consistency, the nodules of B-H black Rockwool retain their physical properties; B-H DUCT SOUNDLINER when dried out, the dead air cells in these A rigid material felted of chemically nodules provide maximum insulating effi stable Rockwool fibres. Provides an ciency. Packed in strong 50-lb bags; can effective means of minimizing sound be stocked without breakage or loss. transmitted through the ducts, by instal- B-H KOLDBOARD . ling it inside the ducts. Does not disin tegrate nor support combustion. Easily Effective from cut and fitted around bends in the duct-- f-150 to 300 F. attached with either bolts or specially Made from 100 prepared acoustical cement. Standard per cent chemical sizes: 22 in. x 33 in. and 24 in. x 36 in.; ly stable B-H both sizes in 3^ in. or 1 in. thicknesses. Rockwool fibres, felted and bonded together to form flat, semi-rigid blocks which do not disintegrate or break down struc turally under CATALOG ON REQUEST We invite you to write for fully illus trated catalog giving more detailed specifications on these and other B-H Industrial Insulation Products of many types. severe service con- ditiona. Kold- board will not support combustion nor smolder when flame is applied. Low" r moisture absorption: 0.68 per cent at relative humidity of 65 per cent at tem INDUSTRIAL perature of 75 F. Thermal conductivity: 0.29 Btu/sq ft/hr/F at a mean temperature INSULATIONS of 70 F. Standard sizes: 18 in. and 36 in. long; 12 in., 18 in., 24 in. wide; in. to 4 in. thick; packed in high test fibre cartons. B-H MONO-BLOCK A one-block insulation effective over the full temperature range up to 1700 F. Insulation The Celotex Corporation General Offices 120 South LaSalle Street, Chicago 3 -- CeioteX - Celotex Cane Fibre Insulation prod' ucts are made by felting the long, tough fibres of bagasse into strong, rigid boards. They are manufactured under the Ferox Process (patented) which effectively pro tects them from destruction by termites, fungus growth, and dry rot. They are integrally water-proofed which insures a non-hygroscopic insulation of low capillar ity and enduring insulating efficiency. Celotex Insulating Sheathing An insulating, weather-resisting sheath ing for use under any type of exterior. Surfaces and edges are moisture-proofed with a surface impregnation of asphalt. Sizes: % in. thick: 4 ft wide: 8 ft, 9 ft, 10 ft and 12 ft long. Big Board--4 ft wide x 8, 9, 10 and. 12 ft long x in. thick. Center Matched--Available in the same thickness, in 2 ft x 8 ft T & G units for horizontal application. Celotex InsulatingXath unit. Consists of a Celotex cane fibre core surfaced on both sides with a Y in', layer of asbestos-cement board. The established low thermal conductivity of the Celotex core is maintained in the manufacture of Cemesto. * Sizes: 4 ft x 4 ft, 4 ft x 6 ft, 4 ft x 8 ft, 4 ft x 10 ft, 4 ft x 12 ft; thicknesses: 1Y in., 1%> in. and 2 in. Celo-Siding A weather-resistant, insulating, struc tural siding. Replaces wood or other sheathing materials and provides the exterior finish as well/ Made of a Celotex cane fibre core that has been asphalt coated on all sides and edges. The weather side is additionally coated with a high grade asphalt into which mineral granules are firmly embedded. . Sizes: Thickness, Y in. and Y in.; Yz in.--4 ft x 8;ft (square edges only); Yz in.--2 ft x 8 ft tongue and groove (long edges only), and 4 ft x 8 ft, 4 ft x 10 ft (square edges only). Regular Insulating Lath--A cane fibre plaster base of high insulating effi ciency. Surface provides a strong bond for plaster and the bevelled edges and ship- lap joint provide additional reinforcement! Size: 18 in. x 48 in;; thickness: % in. Celotex Roof Insulation ' Regular Roof Insulation--A cane fibre product possessing superior insulating properties. It reduces roof heat trans mission as shown by coefficients established in The Guide; reduces roof movement due to contraction and expansion. Size: 23 in. x 47 in.; thickness: Y in., 1 in., 1Y in. and 2 in. Vapor-seal Roof Insulation--Same as above except coated on all edges and surfaces with waterproof asphalt and made with an offset on all bottom edges to provide ,a network of' channels which equalize air pressure to reduce roof blisters and buckling. Size: 23.in. x 47 in.; thickness: 1 in.; IY in. and 2 in. Cemesto - A completely fabricated fire and mois ture resistant structural insulating wall Celo-Block A cane fibre cold storage insulation. Made from Y in. low density Celotex Cane Fibre Boards laminated with water proof asphalt mastic. The finished block is surfaced front and back with vapor proofing asphalt. Its efficient low thermal conductivity and protection against mois ture makes Celo-Block the ideal answer for all low temperature requirements. . Size: 18 in. x 36 in.; thickness: -2 in.. Celotex ROck Wool Products Available in the following forms--Loose, Granulated, and Paper-backed Batts. Celotex Rock Wool is made from the clean fibres of molten rock. It is incombustible and integrally waterproofed.. Q-T Ductliner An acoustical material designed espe cially for duct lining in air conditioning systems. Absorbs duct noises. Made of rock wool and a special binder. Designed to withstand air duct humidity conditions. Is fire resistant and will not smoulder or support combustion. Thermal conduct ivity of 0.30. . 1250 Insulation Cork Insulation Company, Inc. 155 East 44th Street, New York, N. Y. . Factory: Wilmington, Delaware .Branches . Boston, Mass. Philadelphia, Pa. Chicago, III. San Francisco, Calif. Los Angeles. Calif. `Milwaukee, Wis. Represented by Corinco Insulation Co.. Inc. Seattle, Wash. St. Louis. Mo. Washington, D. C. Portland, Ore. CORINCO PRODUCTS - Insulation Corkboard Acousticator . Cork Pipe Covering Cork Lagging and Discs Cork Tile Flooring Marine Corkboard _ Isolation Corkboard INSULATION Proper and efficient 'insulation for in dustrial or domestic purposes demands a material with a low conductivity factor. Cold storage equipment is vitally de pendent on the efficiency of the insulating material used. Corinco Corkboard and Corinco Cork Pipe Covering afford positiveprotection from refrigeration loss for Freezers, Cold Rooms, and for Cold Pipe Lines. AIR CONDITIONING With the rapid increase in the use of Air Conditioning equipment, it has be come more and more apparent that a proper insulating medium is necessary for the ducts; pumps, and other cold equip ment. Corinco Corkboard is ideally suited for efficient and economic cover ing of this equipment, greatly reducing heat loss and preventing the formation of condensation; CORINCO CORKBOARD Corinco Corkboard is manufactured in sheets 12 x 36 in. and 24 x 36 in., in thick nesses of 1, l)4r'2r3, and 4 in. Its low conductivity factor, and its high resis tance to moisture and fire make it an ideal insulation for cold storage and other low temperature installations. . CORINCO ISOLATION CORKBOARD For effective control of machinery noises and vibrations, Corinco Isolation Cork board has proved successful. It is available in boards 12 in. wide by 36 in. long by 1, 1/4. 2, 3, or 4 in. thick. To meet specific requirements the boards are manufactured in several densities classified according to the weight per board foot. CORINCO CORK PIPE COVERING Corinco Cork Pipe Covering and Fittings are available in three standard thicknesses --Ice Water, Brine, and Special Thick Brine. They are made to fit snugly around the pipe and 'fittings, thus pre cluding the possibility of moisture and frost, forming within the covering. This assures long life and efficient operation. CORINCO ACOUSTICATOR The adoption of noise control is becom ing more widespread with the growing realization that the workers* efficiency is greatly increased in quiet surroundings. Theatres, auditoriums, and broadcasting studios, as well as industrial plants, have turned to Corinco Acousticator for def inite noise control. . For the insulation of large pipe lines For other information and engineering and cylindrical tanks, Corinco Cork services, write to Cork Insulation Co., Lagging is used. I Inc., 155 East 44th Street,-New York City. 1251 Insulation Air Ducts PRODUCTS The Philip Carey Mfg. Company . Lockland, Cincinnati 15, Ohio Branches In All Principal Cities CAREYDUCT is recommended wher. ever quietness, ease of installation, fire safety, fume resistance and good appear ance are desirable or essential. Used in air conditioning systems widely before the war; Careyduct has proven itself on some of the largest governmental indus trial and commercial installations in the country. Write for engineering performance and installation data. ACOUSTICAL. Careyduct is a natural sound absorber and non-conductor of sound. Quiets fan noise; won't pick up and "telegraph" other outside noises. GOOD LOOKING. Surfaces are smooth and free from unsightly raised seams or joints.; No stiffeners or braces. Blends well with modern interiors. INSULATED. High-efficiency insula tion assures delivery of hot or cold condi tioned air to outlets with minimum change in temperature. AIRTIGHT. Won't "breathe" or vi brate at high velocities. Slipjoint con struction prevents leakage. SAVES SPACE. Being 40% to 50% quieter than - ordinary duct, Careyduct handles higher velocities, permitting the use of smaller sized ducts. EASY TO INSTALL. Prefabricated Careyduct units are easy to install-- particularly in tight places. Simple low cost fittings can be made in the shop or on the job. 5 TYPES OF CAREYDUCT Insulated and Acoustical Type. 100% asbestos construction--combines duct and insulation. Key-lock Type. For high temperature applications up to 500 F. Impervious to water. Single-wall Type. For heating and ventilating systems. Reinforced Corner Type. Fabricated of Carey Firefoil or insulated sheathing. An ideal duct for large industrial installa tions. ' FIREPROOF. Being 100% asbestos construction Careyduct won't smoulder or burn. Asbestos-cement Type. Made of as bestos-cement wallboard in different thick nesses. Sizes: 2334 in. and up. 1252 Insulation Air Ducts The Philip Carey Mfg. Company Lockland, Cincinnati 15, Ohio Branches In All Principal Cities PRODUCTS CAREYCEL FOR AIR DUCTS Uses: A fireproof, low cost, high efficiency asbestos boa^d for insulating ducts and all types of air conditioning equipment. Description: Composed of 12 to 14 laminations of indented (not corrugated) asbestos felt per inch of thick ness. Weight: approximately 134 lb pier board foot.' Sheet Size: 36 in. x 36 in., or cut to order. Blocks: 6 in. x 36 in. Thickness: 34 in. up. CAREYCEL FOR HEATING SYSTEMS Uses: Pipe coverings and blocks for pipes, boilers, ovens and other apparatus where the temperature doesn't exceed 300 F. Description: Pipe covering sections 36 in. long by 1 in. thick, finished with cotton duck jacket and bands. Blocks: 6 in. x 36 in. Sheets: 36 in. x 36 in., or cut to order. Thickness: 34 in. up. ' CAREY IMPERVO FOR COLD PIPES Uses: A high efficiency insulation for cold or ice water pipes--keeps the water cold and prevents sweating. Description: Laminated insulating felt with water proof liner and jacket. 36 in. long in 34 in., 24 in., double 34 in. and double 24 in- thick sections, finished with cotton duck jackets and bands. CAREY PROTECTO TO PREVENT FREEZING Uses: Designed especially to reduce the danger of freezing of exposed water pipes. Description: Consists of an inner layer of hair felt, a waterproof felt liner and an outer layer of insulating felt. For severe conditions use two thicknesses. 36 in. long sections with cotton duck jacket and bands. One thickness only--approximately 1 in. 1253 insulation The Eagle-Picher Company General Offices:' American Building, Cincinnati 1, Ohio - Offices in Principal Cities A Remarkable Insulating Wool Made From Minerals Years ago Eagle-Picher pioneered a method of fusing and fiberizing carefully selected minerals into a dark gray insulating wool. This mineral wool is chemically inert. Fibers are mechanically strong, extremely resilient and flexible. They withstand expansion and con traction without loss of efficiency even at elevated temperatures. From this mineral wool, Eagle-Picher has fabricated a long list of insulating products to meet a wide range of tempera tures and operating requirements. Enclosed on four sides with paper, one side of which is an approved vapor barrier. Strong tacking flanges. Quickly cut with knife or shears. Three thicknesses--FulThik, Semi-Thik apd 1-in. For home use. H-2 Loose Wool A dean fill insulation that is highly efficient for temperatures to 1200 F. Averages considerably lighter in weight than many rock and slag wools--goes farther. Fibers are soft and flexible. Ap proved by Underwriters Laboratories as fireproof and a non-conductor of electricity. Retains physical and chemical stability in presence of water. Packed in 40-lb. bags. 7-B Granulated Wool Another grade of fill insulation that has all the advantageous properties of Eagle H-2 Loose Wool. It consists of small pellets averaging H to H in. in size. For all fill jobs in irregular spaces. May be poured. Packed in 40-lb. bags. Super "66" Cement A high-temperature insulating cement. Easy to apply and trowels to a smooth finish. Actively inhibits rust. Will stick on any clean, heated surface. Dry cover age 50-55 sq ft per 100 lb. 100 per cent reclaimable up to 1200* F. Packed in 50-lb bags. Supertemp Blocks An all-purpose high-temperature block insulation which will withstand elevated temperatures up to 1700 F without loss of efficiency or structural strength. Fibers are water-repellent. Light weight. Easily cut to fit irregularly shaped surfaces. Blocks withstand all normal vibration and abrasion encountered in use for which they are recommended. All standard sizes. Low Temperature Felt A highly efficient insulating material for subzero and low temperatures (to 400 F). Available in densities 6-lb to 8-lb per cu ft. Recommended for refrigerator rooms, trucks, refrigerators, stoves, etc. Sheds water. Extensively used in marine field. Paper Encased Batts and Blankets , These light-weight, sturdily constructed batts and blankets are easy to apply. Insulseal A protective coating for Industrial Insulation Blankets, Supertemp, "66" Cement and other kinds of heat insulation. Provides a permanent seal that safeguards insulation against air infiltration, moisture, water, fumes; also against vibration and abrasion. Does not support combustion. For more complete specifications and technical data on these and other Eagle Insulating Products, see Sweet's Engi neering or Power Plant catalogs. ` 1254 A j Insulation \ Insul-Wool Insulation Corp. General Offices, Wichita, Kansas Branches in Principal Cities Manufacturers and Distributors of Insul-Wool Insul-Wool is a fibre insulation of the "fill" type--made of wood pulp, a natural . insulating material. By the exclusive "Insul- Wool" method the wood pulp is converted into a loose fluffy substance which, when installed in a building, forms a soft heat-resisting blanket having millions of tiny air cells cap able of resisting passage of either heat or cold. UNIFORMITY OF PRODUCT Only one grade of Insul-Wool is made and every "run" is tested at the factory to insure uniformity of product and unvarying high quality. It is free from grit, silicon particles, or "shot." RESISTANT TO FIRE AND VERMIN A special "Insul-Wool" method of chemical treatment makes Insul-Wool thoroughly and permanently vermin and fire resistant. JnjuMVooJ Applied over Ceiling "INSUL-WOOL" SERVICE Insul-Wool is distributed and installed only by specially trained men--direct factory re presentatives or men in the organizations of the largest insulation material dealers through out the United States. ADVANTAGES OF INSUL-WOOL 1. It is made from wood pulp, a natural insulating material. 2. Chemical treatment makes Insul-Wool safe under all conditions and hazards. 3. Its light weight % lb per sq ft 4 in. thick adds very little load to the ceiling rafters: . 4. A permanent type isulation which does not pack or settle and outlasts the build ing in which it is installed. 5. Does not attract moisture. 6. Cuts fuel costs up to 50 per cent and reduces Summer temperatures up to 18 F in the home. 7. Meets .U. S. Government requirements of Federal Construction with a thermal conductivity of 0.24 Btu per hour, per square foot, per degree Fahrenheit, per inch thickness. ' Analysis of Insul-Wool in Terms of Commercial Thickness Material INSUL-WOOL Commercial Form Wood Fiber-Loose Type, permanently treated for vermin and fire. Comro'L Thickness Inches D. Wt. Per Cu. Ft. 1 '.4 2.5 C. Conductivity 0.24* 0.067** Kansas City Testing Laboratory, Inc.. February 25, 1938. **J. C. Peebles. Armour Institute of Technology, April 8, 1937. Complete data on Insul-Wool Insulating Product will be sent upon request. 1255 Insulation INSULITE General Offices 500 Baker Arcade Bldg., Minneapolis 2, Minnesota THIRTY-TWO YEARS PROVEN DURABILITY For 32 years engineers and architects have specified Insulite materials for structural uses, interior finish, low temperature duct lining, and for other thermal insulation and sound control work. Insulite materials have proved themselves practical through their performance on the job. STRUCTURAL MATERIALS Lok-Joint Lath--An insulating plaster base, fabricated from Ins-Lite or from Graylite. Patented "Lok" firmly locks the sheets between supporting members. Thickness: H in. Size: 18 x 48 in. Sealed Graylite Lok-Joint Lath--An insulating plaster base of Graylite, sealed on stud space side with an effective moist ure vapor barrier. Has patented "Lok" on long edges. Same thickness and size as Ins-Lite and Graylite Lok-Joint Lath. Bildrite Sheathing is an asphalt-con taining wood fiber insulating board manu factured under an exclusive process which provides increased strength and moisture resistance. It is % in. thick and has a gray-brown color. Thermal conductivity maximum: 0.36 Btu per inch thickness. Each sheet is marked to indicate proper nail spacing. Available in sizes 4 x 8 ft up to 4 x 12 ft with all edges square. Also available in 2 x 8 ft size with interlocking joint on long edges. Used as a structural sheathing board and as roof boarding. Condensation Control--Where low outside temperatures and high inside humidities may occur, authorities recom mend "sealing the warm side and venting the cold side" of the wall to prevent con densation. An adequate vapor barrier, Sealed Graylite Lok-Joint Lath, should be used on the warm (room) side of the wall thereby effectively reducing vapor trans- mission into the stud space. Bildrite Sheathing is designed to allow any surplus vapor1 in the stud space to "breathe" or be vented to the exterior air. If vapor is trapped within the stud space and cannot escape through the sheathing, destructive condensation may occur. THE APPROVED INSULITE WALL OF PROTECTION This construction consists of Bildrite Sheathing on the exterior of the frame work and Sealed Graylite Lok-joint Lath on the interior. Trans mission coefficient (U> is shown below. Interior Finish Exterior Finish and Sheathing No Insulation Between Studding Plaster ('A in.) on Sealed Graylite Lok-Joint Lath 0/2 in.) Wood Siding. in. Bildrite Sheathing 0.15 Btu/sq ft./hr/ F The above value is typical of results which can be obtained by utilizing Insulite materials in frame construction. For further (U) values refer to Chapter 6 pages 127 and 128. Applying Bildrite Sheathing 1256 A PPlying Lok-Joint Lath Insulite Insulation INTERIOR FINISH MATERIALS Ins-Lite Building Board--A wood fiber board with the light color of natural wood--burlap and linen textured surfaces. Thermal conductivity: Nominal 0.33 Btu/hr/sq ft/ in./F; density: 16 lb/cu ft. Furnished in thicknesses of H and % inch and sizes of 4 x 7 ft to 4 x 12 ft. Also available in 6 x 8 ft, 6 x 12 ft and 8 x 12 ft sizes. Graylite Building Board--An integ rally treated asphalt containing wood fiber board of grayish brown color--burlap and linen textured surfaces. Thermal conduc tivity nominal 0.35 Btu per inch thickness. Furnished in same thicknesses and sizes as Ins-Lite Building Board. Smoothcote Interior Board--Factory Coated Insulating Board with smooth, finished surface one side, having 68 per cent light reflection. Furnished in H inch thickness only and in sizes of 4 x 7 ft to 4 x 12 ft. Satincote Interior Board--Factory finished Insulating Board in color light ivory, oyster white, coral and green. Light reflection from 64 per cent for green to 80 per cent for the light ivory color. Requires no further decoration. Resistant to abra- sion and washable. In H inch thickness and in sizes of 4 x 7 ft to 4 x 12 ft. TileBoard--Available in Smoothcote and Satincote. TileBoard is furnished with the Lok-Grip Joint that permits con cealed nailing and which together with the Lok-Pin (a flat diamond shaped metal dowel) definitely and mechanically safe guards against any falling units even though no face nailing is used. Smoothcote and Satincote TileBoard available in H inch thickness and sizes of 12 x 12 inches to 16 x 32 inches. Plank--Available in Smoothcote and Satincote. Plank has the Lok-Grip joint which permits concealed nailing and is beveled and beaded both long edges. Smoothcote and Satincote Plank furnished Acouslilile or Fiberliie effectively quiet and control sound in H inch thickness, widths of 8 to 16 inches and lengths of 8 to 12 ft. Acoustilite--A high efficiency acousti cal material for sound control. Coefficient of sound absorption, at 512 cycles, is 0.79 when mounted on solid background and 0.80 when on furring strips. Noise re duction coefficient is 0.65 when mounted on solid background and 0.75 when on furring strips. Factory painted in buff, (light reflection 77 per cent) and in white (light, reflection 80 per cent). Units have a butt joint and are beveled on four edges. Thickness, % in.; sizes, 12x12 in. to 16x32 in. Flberlite--An efficient sound absorp tive and decorative material. Coefficient of sound absorption, at 512 cycles, is 0.53 when mounted on a solid background and 0.72 when on furring strips. Noise re duction coefficient is 0.55 when mounted on solid background and 0.65 when on furring strips.' Factory painted in buff (light reflection 77 per cent) and in white (light reflection 80 per cent). Units have a butt joint and are beveled on four edges. Thickness, Hin.;sizes, 12x12in. to 16x32in. HardBoard Products HardBoard materials are tough, durable, grainless, pressed wood fiber boards with a hard, smooth surface. Available in a range of densities from 55 to 68 Ib/cu ft. Thick nesses are from Ho to ^6 In. and sizes of 4 x 2 ft to 4 x 12 ft. Industrial Insulation Industrial Insulation is a wood fiber board for use in all types of manufacturing industries producing items such as refriger ators, coolers, showcases, brooders, parti tions and cabinets. It can be cut-to-size and fabricated to customer's specifications. Three types of industrial board are available. Lowdensite Industrial Board--A 10 to 14 lb density board with an average tensile strength of 100 lb/sq in. and an average conductivity of 0.30 Btu/hour /sq ft/F/inch thickness. Ins-Lite Industrial Board--A 14 to 18 lb density board with an average tensile strength of 250 lb/sq in. and an average conductivity of 0.33 Btu/hour/sq ft/F /inch thickness. Graylite Industrial Board--Differs from two above products in that it has an integral asphalt treatment which provides increased strength and moisture resistance as well as minimum thickness and linear expansion. A 16 to 20 lb density board with an average tensile strength of 350 lb/sq in. and an average conductivity of 0.35 Btu/hour/sq ft/F/inch thickness. 1257 Insulation Johns-Manville Executive offices: 22 East 40th Street, New York 16, N. Y. - Offices in All Large Cities Johns-Manville lome Insulation Johns-Manville Rock Wool Home In sulation is a light, fluffy mineral wool, highly efficient in heat-proofing practically any building, old or new. It is durable, rot-proof, fire-proof and odorless, and will not corrode or settle. Full stud thickness of this material will cut fuel costs up to 30 pier cent in winter and help keep rooms up to 15 deg cooler in hottest weather. J-M RockWool Home Insulation is., fur nished in two forms: for new construction, completely the space between studs, joists and .rafters on the usual 16 in. centers. The sturdy felted "wool" is strong enough to be handled rapidly without damage. The batts are backed with waterproof, vapor-resistant paper, extending on both the long sides in in. wide flanges, by which the batt is fastened in place and which also aid in sealing the joints. This backing protects against penetration of moisture from wet plaster and also resists infiltration of moisture vapor from the house into the wall. - As a further protection against moisture, the felted wool is also waterproofed. Super-Felt may also be obtained in blanket form, in Thick, Medium and 1 in. thicknesses. The-blankets have a water proof vapor barrier paper on one side and a permeable kraft paper on the opposite side, cemented together along the long edges to form a strong nailing flange. A Pplytng J-M Super-Fell Type B baits in new home in easily handled batts; for existing build ings, in nodulated form to be installed pneumatically. . For New Construction J-M Super-Felt Type B Batts Super-Felt Type B Home Insulation is furnished in pre-fabricated batts of uni form thickness and density, in both- full . stud thickness and semi-thick, in sizes 15 x 23 in. and 15 x 48 in., designed to fill For Existing Homes and Buildings Type A "Blown" Rock Wool Type A Rock Wool is blown pneu matically into the spaces between studs in outer walls and between rafters or joists in roofs or attic floors. Insulation thickness in walls corresponds to stud depth, ap proximately 3% in.; the density, approxi mately 5 to 8 lb per cu ft, assures maximum thermal efficiency. This type of insulation is installed only by Johns-Manville or by Approved J-M Home Insulation Contrac tors, who are equipped with the necessary apparatus and trained crews. . Write for Details Complete information on all types of J-M RockWool Home Insulation will be furnished on request. . J-M Airacoustic Sheets for li ling Air-Conditioning Ducts J-M Airacoustic Sheets, for duct linings ture- resistant, with a surface which will of air conditioning systems, are flame not materially increase friction losses in proof, highly sound-absorbent and mois- the duct system.Write for Bulletin AC-23A. 1258 Johns-Manoille Insulation Johns-Manville Pipe and Boiler Insulation J-M Asbesto-Sponge Felted Pipe Insulation Recommended on all high pressure steam piping at temperatures up to 700 F where insulation may be subjected to rough usage or where maximum efficiency and durability are desired. Furnished in 3-ft sections up to 3 in. thick, for all com mercial pipe sizes.* J-M 85% Magnesia Pipe Insulation J-M Superex Combination Superex Combination Insulation (an inner layer of high temperature Superex and an outer layer of 85% Magnesia) is recommended where temperatures exceed 600 F. Superex and Magnesia are both furnished in sectional and segmental pipe covering, and in block forms. J-M Pre-Shrunk Asbestocel J-M Asbestocel Sheets and Blocks Pipe Insulation Asbestocel Sheets and Blocks are used Cellular type of insulation for pipes for insulating warm-air ducts, flues, heater carrying low pressure steam or hot water. Made up of alternate layers of plain and corrugated, specially-treated, moistureresistant, asbestos paper. Sections sur casings and fan housings in the ventilating . systems. Temperature limit 300 F. Fur- . nished 18 and 36 in. wide by 36 in. long, from in. to 4 in. thick. faced with asbestos paper for high speed work or with a canvas cover. J-M Rock Cork Sheets and - Furnished in 3-foot sections, in thick Pipe Insulation nesses of 2 to 8 plies, each ply approxi-_ mately inch thick.* . J-M Rock Cork is made of mineral wool and a moisture-proof binding ingredient J-M 85% Magnesia molded into sheets for insulating refriger ated rooms, air conditioning equipment Recommended as the most widely used insulation of the molded type for tempera tures up to 600 F. Pipe insulation is furnished, in sectional or segmental form for all commercial pipe sizes,* in thick nesses up to 3 in. Blocks are 3 in. by ,18 in. and 6 in. by 36 in., flat or curyed,' and other low temperature requirements; and into sectional pipe insulation with an integral waterproof jacket, for all low tem perature service. It is strong, durable, and will not support vermin. Because of its unusual moisture resistance, its high insu lating efficiency is maintained in service. , from 1 in. to 4 in. thick. Minimum tliick-. Furnished in sheets 18 in. by 36 in., in 1, ness for curved blocks, 1 in. \Yi, 2, 3 and 4 in. thicknesses; also 18 in. by 18 in. by 1 in. thick.. In lagging form, J-M Pre-Sfrrunk Wool Felt * Pipe Insulation for curved surfaces, supplied 18 in. long by 1H 3 and 4 in. thick, 2 to 6 in.'wide, depending on diameter. In pipe covering Due to its Dual-Service Liner--an form, in ice water, brine and heavy brine asphalt-saturated felt--J-M Pre-Shrunk thicknesses, for all commercial pipe sizes.* Wool Felt is equally effective and durable on either hot or cold water service piping. By the use of moisture-resistant felts, Details on Request shrinkage troubles have been minimized. Write for complete information on any Supplied in the regular canvas finish, it Johns-Manville insulating material. is furnished in 3-ft sections in thicknesses of in., % in., 1 in., Double in., and Double % in., for all commercial pipe sizes.* . Can also be supplied in sections to fit straight nine of copper pipe or tubing with outside diameter - H >n. and larger. Insulation Kimberly-Clark Corporation Neenah, Wisconsin to increase efficiency in Heating, Ventilating, Air Conditioning >n ___ Kimberly} Clark * THERMALLY EFFICIENT! KIMSUL* blanket insulation in an attic will usually make a house up to 15 degrees cooler in summer, comfortably warm in winter. Fuel cost is often cut 30 per cent by KIMSUL. Thermal efficiency: 0.27 Btu/hf/sq ft/deg F/in. (J. C. Peebles, Armour Institute).* RESISTS FIRE, MOISTURE, VERMIN, INSECTS, FUNGUS! PERMANENT! Strong stitching prevents shifting, sagging, settling--Hence, no transoms through which-heat can leak. Made of wood-fiber, impregnated with asphalt, KIMSUL lasts indefinitely. ECONOMICAL! Because it is compact (stretches to 5 times packaged length), KIMSUL is less expensive to store, ship, handle. Installation cost is small also, because it is ex ceptionally easy to apply . . can be shaped swiftly around obsta cles, as it is flexible as a towel. 3 THICKNESSES--4 STANDARD WIDTHS! KIMSUL blanket comes in Commercial Thick (nominally ^2 in.), Standard Thick (nominally 1 in.) and Double Thick (nominally 2 in.) . . . giving you choice of thicknesses to fit specific needs. Each thickness is available in four standard widths: 16 in., 20 it)., 24 in., and 48 in. Consult Our Engineers Heating and ventilating engineers, archi tects, contractors and builders are invited to discuss their insulation problems with our engineers. These insulation experts are equipped to render a valuable advisory service . . . and to give accurate information regarding the application of KIMSUL to all types of construction. ' Send for free KIMSUL book giving full technical data Kimsul (trade mark) means Kimberly- Clark insulation. . Kimberly'Clark. Corporation Insulation HOW KIMSUL INCREASES WINTER COMFORT BY RAISING WALL AND CEILING SURFACE TEMPERATURES No Insulation............... KIMSUL in Walls KIMSUL in Commercial 1 luck in Walls Commercial Thick in Walls Double thick ui Ceilings.............................................. Standard Thick in Walls Double 'thick in Ceilings.............................................. Commercial Thick.......................................................... Double Thick................................................................... Wall Surface Temperature. Deg 60.0 64.4 . 65.3 66.5 64.4 64.4 65.3 60.0 60.0 60X) Ceiling Surface Temperature, Deg 52.0 60.0 63.0 65.4 . 63.0 65.4 65.4 60.0 65.4 HOW KIMSUL LOWERS FUEL BILLS No Insulation......... - KIMSUL in Walls and Ceilings............ Standard Ihtck................................................... Double Thick...................................................... Commercial Thick in Walls Standard I hick in Ceilings.............................. Commercial Thick in Walla Double 1 hick in Ceilings.................................. Standard Thick in Walla Double thick in Ceilings.................................. KIMSUL in Double Thick...................................................... Tons of Coal per Season 12.1 8.0 7.1 6.4 7.5 7.0 6.7 9.1 8.5 8.1 Tons Saved , per Season 4.1 5.0 5.7 4.6 5.1 5.4 3.0 3.6 4.0 - Per Cent of Fuel Saved 33.9 41.3 47.1 38.0 42.1 .44.6 ` 24.8 29.7 33.1 Calculations apply to a one-story home in the Chicago area. As shown in the table, almost any desired performance can be produced by insulating with KIMSUL. The economic thickness provides the best balance between insulation costs and resultant fuel savings. Tocut the compressed KIMSUL blanket tolength required, simply count off trade marks--placed approximately 24 in. apart when blanket is expanded--allow about 6 in. for end fastening, and cut. To install KIMSUL in walls, partially expand blanket and attach to under-side of top plate with fiber strip provided. Ex pand blanket to base of wall and attach similarly. Then staple KIMSUL to sides of studs. 1260 Ordinarily a difficult job, in sulation of sloping roofs is usually a one man job with KIMSUL. Simply fasten blank et to sides of rafters and collar beams. KIMSUL installs easily in fiat roofs and ceilings. After cutting blanket to proper length, expand it and fasten one end to top wall plate. Pull across, and fasten other end to opposite wall plate. Fasten edges if there is no sup porting finishing material. To install KIMSUL in attic floor, place blanket directly on plaster base, with paper side down. Fasten one end. expand blanket, and fasten other end. That's all! 1261 Left-overs and odd pieces of KIMSUL are ideal for caulking spaces around window frames and doorways. Stops drafts and wasteful heat leaks. /nsulation The Korfund Company, Inc. 48-50 32nd Place Long Island-City 1, N. Y. Representatives in Principal Cities TYPE LK UNIVERSAL VIBRO-ISOLATORS are recommended for isolation of compressor and condens ing units where almost perfect absorption of noise and vibration is required, as for instance on upper floors of office buildings, hospitals and hotels. These units absorb vibration in all directions and provide for both horizontal and vertical adjustment. Loading range 75-12,000 lb. Catalog LK-550. The TWIN RAIL FAN BASE is a development in fan and blower isolation which incorporates many new and exclusive features. Inter changeable prefabricated parts are used throughout. It is .light iii weight, yet has great rigidity to vertical and lateral stresses. The Twin Rail Base is easily assembled and installed, and is fully adjust able. Rubber-in-Shear, Cork, or Steel Spring Isolators are supplied, depending upon requirements. Catalog TR-800. - KORFUND CORK PLATES provide a high degree of noise and vibration isolation when applied to compressors mounted on a slab of concrete. Since Cork Plates should be loaded to a minimum of 1,500 lb per sq ft, it is seldom necessary to cover the entire area of concrete. Instead, a number of Cork Plates of dimensions 8 in. x 8 in., or smaller, may be spaced under the concrete so that the load will be evenly distri buted over the several plates. Bulletins Bc-13; Bc-22. The Korfund Co., Inc., is exclusive national distributor of ARMSTRONG STANDARD DENSITY VIBRACORK in 2 in., 3 in., and 4 in. thicknesses, loading capacity 1500 to 4000 lb per sq ft. 1262 Insulation Lockport Cotton Batting Co. Lockport, New York COTTON INSULATION Fire proofed and manufactured under Department of Agriculture Specifications Lo-"K" is made of processed American cotton of varying thicknesses, packaged in rolled form, with or without Kra/t paper backing--an added moisture barrier. Thermal Conductivity--The value for cotton is 0.24 Btu/hr/sq ft/ degree F/inch. (See table.) . Light Weight--Weight of 1 cu ft is %\b. {See table.) Flame-Proofed--To comply with De partment of Agriculture specifications to withstand a temperature of 1800 F. Moisture-Resistant--Chemical treat ment, combined with natural protective coating on cotton fibres, enables cotton to effectively resist moisture. Prevents rot and mildew. Smooth Texture--Cotton contains none of the sharp particles that can harm workmen's hands during process of in stallation. Flexible--Cotton batt may be expanded or contracted to fit any enclosure. It easily passes over and under pipes and wires. In walls or roof, the nailing flange is folded out from paper backing and at tached to edge of studs or rafters. See illustration "A" above. In attic with open floors, Lo-"K".is simply tucked between ceiling rafters, cotton side up. See illustration "B" above. Manufactured in Standard Sizes. Packaged in Rolled Form. Thicknesses--inches: I, 2, 3, 3^. Width--inches: 16,24 on centers. Lengths: Standard from 12 ft up. Available in Quantity--Lockport is establishing dealers in principal distribu ting centers. If your dealer doesn't hap pen to have Lo-"K" in stock, we invite your inquiry for prices and samples. INSULATING VALUE OF VARIOUS INSULATORS The coefficients of conductivity (A value) are ex-' pressed in Btu per hour per square foot per degree Fahrenheit per 1 in. of thickness. ' Type of Insulation c?vr k*> Value Cotton: Insulating Batt......................... Kocfc Wool: fibrous material made from rock................................................. Mineral Wool: fibrous material made from mineral slag................................... .875 10.00 0.24 0.27 0.27 from glass slag........................................ Kigid Insulation made from sugar cane Chemically treated wood fibre between layers of paper........................................ Eel grass between layers of paper............ Stitched and creped expanding fibrous blanket.................................................... bhavings: Various trom planer.............. Corkboard: No binder added................. Kigid insulation made from wood fibre.. Kigid fibre board made trom shredded wool and cement.................................... 1.50 13.50 3.62 3.40 1.50 8.80 7.00 15.90 24.20 0.27 0.33 0.25 0.25 0.27 0.41 0.27 0.33 0.46 Compiled from Chapter 6. . *>"k" indicates temperature conductivity. 1263 Insulation Mundet Cork Corporation 65 S. Eleventh St. insulation division Brooklyn 11, N. Y. Manufacturers of Corkboard. Cork Pipe Covering, Compressed Machinery Isolation Cork, Natural Cork Isolation Mats, and all kinds and varieties of Cork Specialties. Authorized contractors for high temperature insulation. Atlanta. Ga. Brooklyn N. Y. Boston (No Cambridge) 40, Mass. Mundet Branches Chicago 21. III. Cincinnati 2, Ohio Dallas 1. Tex. Detroit 26. Mich. Houston 1. Tex. Jacksonville 7. Fla. Kansas City 7. Mo. Los Angeles 31. Calif. New Orleans 16. Philadelphia 39, St. Louis 4. Mo. San Francisco 7, La. Pa. Calif. Mundet Distributors are Located in the Following Cities--Names and Addresses on Request Amana, Ia. Baltimore. Md. Buffalo, N. Y. Denver, Colo. El Paso. Tex. Hartford, Conn. Johnson City, Tenn. Memphis, Tbnn. Minneapolis, Minn. Nashville, Tenn. Norfolk, Va. Oklahoma City, Okla. Portland, Oregon Richmond, Va. Rochester, N. Y. Salt Lake City, Utah Seattle. Wash. Tucson. Ariz. Tulsa, Okla. Utica. N. Y. Mundet "Jointite" Corkboard --for all low temperature insulation and for acoustical correction. 100 per cent pure cork, fabricated in accordance with U. S. Government Master Specifications and unsurpassed in its field. Sold in standard 12 in. x 36 in. sheet. Standard thicknesses, in., 1 in., 13^ in., 2 in., 3 in., 4 in., 6 in. Mundet "Jointite" Cork Pipe Covering Shown below, with fitting cover. Pro tects all types of low temperature lines. Made in 3 thicknesses, with complete line of standard covers, suitable for pipes carrying sub-zero to 50 F temperature. paper applied with hot asphalt top and bottom. Mundet steel bound mats are usually used under exposed mounts; as phalt paper bound mats under concrete foundations of the envelope type. Mats are made to fit under any type of machine foundation. For loads exceeding 2000 lb per square foot, we manufacture Mundet Machinery Isolation Cork, which is a board form of compressed granulated cork, available in 3 densities. All types of isolation are furnished in 1 in., 1J^ in., 2 in., 3 in., 4 in., and 6 in. thicknesses, depending on clas6 of service. . Above close-up of Mundet Natural Cork Isolation Mat shows how the blocks of cork are held together within a rigid steel frame. Engineering and Specification Service Our engineering department is at the service- of Architects and Engineers, to assist and advise in the preparation of specifications pertaining to cork. This service is available without obligation to any one who has a low temperature in sulation or a vibration isolation problem. Section of Mundet Moulded Cork Pipe Covering, with Fitting. The pipe covering is mode in sections S6 in. Our latest catalogue will be sent on re quest. It is replete with information and long, to fit oU sizes of pipes. data of value to every specification writer Mundet Cork Vibration Isolation . whose field touches our products. Machinery vibration encountered in Mundet Contract Service heating and ventilating work is effectively Covers the complete installation of our controlled by the use of Mundet Natural. products, in accordance with best estab Cork Isolation Mats. These consist of lished practice. Divided responsibility is blocks of pure cork, held together within a avoided. Materials and workmanship are rigid steel frame or bound with asphalt guaranteed. 1264 Insulation The Pacific Lumber Company 100 Bush Street San Francisco PALCO WOOL INSULATION 35 E. Wacker Drive Chicago 5225 Wilshire Blvd. Los Angeles 122 East 42nd St. New York HOUSE INSULATION INSTALLED IN CEILINGS AND WALLS . INSULATION; TRADE HARK RES U. S. PAT. OFFICE COLD STORAGE INSULATION PALCO WOOL INSULATION Provides maximum proteclion against the in trusion of heat or cold. Readily installed in upper ceilings of uninsu lated homes. Can be installed by blower or handpack methods. FLAME PROOF SAFERIZED Dairies and Creameries. Frozen Food Plants. Warehouses. 0 Refrigerators. Pre-cooling Plants Ice Plants. ' Fur Vaults. Fruit and Pro duce Storage, etc. EIGHT POINTS OF PALCO WOOL SUPERIORITY 1. Thermal Efficiency: The estab lished conductivity of PALCO WOOL is .26 Btu per hour per sq ft per inch of thickness pier degree F difference in tem perature by the Flat Plate Method. 2. Non-Settling: The fibres of PALCO WOOL possess such resilience that no set tlement in a wall can occur under the most severe conditions of vibration. $. Moisture Resistant: The fibres of PALCO WOOL are entirely lacking in capillarity and have little attraction for moisture, enabling it to remain dry and efficient when in use. * . 4. Permanent: The-inherent anti septic qualities of PALCO WOOL make the existence of fungus impossible. The fibres retain their resilience indefinitely. $. Vermin PvCpellent: PALCO WOOL' is distasteful and repellent to rodents and -insects. 6. Fire Resistant: PALCO WOOL, like the Redwood bark it comes from, is in herently fire resistant. As an additional protection it is Sajerized to make it flame proof. 7. Odor Proof: PALCO WOOL is odorless itself and does not absorb or give off odors. 8. Economical: PALCO WOOL is light in weight and low in density, offering exceptional thermal efficiency per dollar invested. WRITE FOR INSULATION MANUALS House Insulation Manual. Cold Storage Manual. - Frozen Food Locker Plant Manual. How to Build a Plant Manual. Get your copies today. 1265 Insulation New York Reynolds Metals Company Reynolds Metals Building Richmond, Virginia Chicaco Boston Minneapolis San Francisco REYNOLDS PROCESS COTTON INSULATION MOISTURE RESISTANT AND FLAME RETARDENT Reynolds Process Cotton Insulation will not absorb water or moisture. It has suc cessfully withstood flame tests up to 1800F. Reynolds Process Cotton Insulation is one of the most effective sound absorption materials. APPROVED AND ACCEPTED Reynolds Process Cotton Insulation is manufactured under constant United. States Government inspection and in strict accordance with Department of Agricul ture specifications. It is approved for home and industrial insulating purposes The Fire Test: Blowtorch Flame on Reynolds Colton ' by Federal, State and Municipal bureaus, Insulation Will Not Cause Combustion builders, architects, and heating engineers Reynolds Process Cotton Insulation stops up to 73 per cent of heat flow and permits complete air circulation around framing. Thermal conductivity is 0.24 Btu per hour, per square foot, per 1F, per throughout the United States. Reynolds Process Cotton Insulation is ideally suited for equipment insulation. It can be furnished cut to size and in special widths up to 60 in. inch thickness. (Authority--Prof. J. C. Peebles, Armour Institute of Technology). Reynolds Process Cotton Insulation is one of the most efficient barriers to the passage of heat that is commercially avail able today. It consists of heat retarding, dead air cells. There are myriads of minute and hollow cellulose fibres, en-` twined and interlocked into a flexible, clean, resilient and light-weight mass. COSTS LITTLE TO INSTALL Furnished in convenient blankets, or rolls, Reynolds Process Cotton Insulation is adaptable to all constructions without expensive cutting or waste. For existing homes, as well as for walls, ceilings or roofs of new- structures, it provides maximum insulating efficiency. Labor costs for in stallation are exceptionally low. Reynolds Process Cotton Insulation is not affected by heat or vibration. It will not settle, sag or pack. Age does not impair its lifetime efficiency. . AIR CIRCULATES FREELY Reynolds Process Cotton Insulation per mits free circulation of air on both sides of the insulation, thus allowing rapid evaporation of any moisture which may occur. Possible damp-rot, decay or other damage to structural materials is thereby' minimized. INSECT AND VERMIN REPELLENT Reynolds Process Cotton Insulation in-' sures utmost cleanliness, not only during installation, but during the lifetime of the structure. This blanket-type insulation does not harbor vermin or other insects. It is odorless, and will not decay. Reynolds Process Cotton Insulation is Easily Installed Send for literature describing its many advantaages in existing houses as well as in new construction. 1266 Reynolds Metals Company Insulation New York Reynolds Metals Company Reynolds Metals Building Richmond, Virginia Chicaco Boston Minneapolis . San Francisco REYNOLDS METALLATION REFLECTIVE ALUMINUM FOIL Reynolds Metallation is produced by mounting bright aluminum foil to one or both sides of 80-lb tough Kraft paper--or on. heavy Sisalkraft when greater tensile strength is desired. Reynolds Metallation serves as a per manently efficient vapor barrier and reflector of radiant heat. It appreciably reduces heat loss in air-filled areas it faces or divides. It has extremely low heatstorage capacity. Reynolds Metallation is soundproof, vermin and water proof; dust will not impair its insulating value. The aluminum surface of Reynolds Metallation retains its reflectivity in definitely under all normal conditions. Recent tests by Prof. Gordon B. Wilkes, Massachusetts Institute of Technology, proved that Reynolds Metallation suffers only negligible loss of its reflective in sulating quality after years of exposure. Table below gives values for the rate of moisture transmission through the.more common building materials encountered. The values given are expressed in terms of Btu/Hr/100 sq ft/Grains per lb dif ference. Moisture Transmission Values Latent Heat Btu/Hr/IOOSq Ft/Gr/Lb Difference ' HOW IT INSULATES Heat is transferred by radiation, con vection and conduction. Up to 85 per cent of all heat-transmitted through air spaces is by radiation. Reynolds Metallation reflects 95 per cent of the radiant heat imposed upon it without regard to direc tion of heat flow. This high reflectivity and resultant low emissivity permits the passage of not more than 5 per cent of radiant heat into adjoining air spaces. The above is accomplished through use of Reynolds Metallation, installed to divide the normal space in a hollow wall into two separate reflective air spaces. ( CHARACTERISTICS Reynolds Metallation is so light in weight it places no strain on structural members to which it is affixed. It is flexible yet sufficiently rigid to conform to angles or curves in a structure when not under tension. Double aluminum foil on paper.............. 50-lb asphalt sheathing paper.................. Coated surface aluminum foil (single)... 2 coats asphalt paint................................... 2 coats aluminum paint.............................. Duplex building papers.............................. Wood per inch thickness............................ Concrete--per inch thickness................... Common brick--per inch thickness......... Cinder concrete--per inch thickness........ Plaster--(% in.).......................................... Fiber Boartf--(}/i in.)................................. Mineral Wool--per inch thickness........... 0.1 0.45 1.0 11.21 1.3 4.0 5.5 6.0 9.0 23.0 38.0 40.0 Table prepared by Carrier Corporation. Syracuse, N. Y. -. EASY TO INSTALL Reynolds Metallation is recommended for all types of building construction in volving hollow' wails; for use between floors and in roof sections. It is available in rolls of convenient lengths and correct widths for standard stud and rafter spacings. Reynolds Metallation is easily and quickly installed, thereby adding a low in stallation cost to a low purchase price and assuring users of maximum efficiency with a minimum investment. Send for literature describing REYNOLDS REFLECTIVE ALUMINUM METALLATION. 1267 X Insulation - New York . The RUBEROID Co. INSULATING PRODUCTS 500 Fifth Avenue, New York 18, N. Y. . 307 N. Michigan Ave., Chicago 1, III. Divisional Offices Chicago Boston (Millis) Erie Baltimore Minneapolis Mobile Today, Ruberoid materials for heating and power equipment are safeguarding in-, sulation efficiency in hundreds of plants, factories and buildings--giving maximum results with minimum cost. Ruberoid products are of proved merit, high efficiency and of a type to meet every need economically. They include pipe coverings and blocks for temperatures from 350 F to 1900 F; Woolfelt pipe cover ing for hot or cold water conduits; asbestos papers for wrapping furnace pipes, pro tecting air conditioning; high temperature cements, millboard, rollboard, rock wool bats and blankets. A complete Insulation Guide, will be gladly forwarded upon request. Product High Temp. Calsilite Sponge felt 85 per cent Magnesia Imperial Air Cell Woolfelt Anti-Sweat Frost-proof - Temp. Limit to 1900 F to 1250 F to 700F to 600 F to 600 F to 300 F to 200 F to 120 F 30 F to 100 F Suggested Use * Protective inner layer for high temperature insulations. In pipe covering and block form for high pressure steam. For vibrating pipes and underground insulation--excellent efficiency. Combines efficiency and reasonable cost--General use in industrial work. Rugged, efficient--wide r&nxe of applications. t Standard insulation for residential pipes. _ , . For cold and hot water lines. Recommended especially for air conditioning work. For cold water lines to prevent condensation. To assist in the prevention of freezing in circulating water pipes exposed to cold. Above products are also made in sheets and blocks for insulating tanks, breechings, furnaces, etc. Characteristics and Insulating Values of Ruberoid Products Product Temperature Density Limit of Rupture . Shrinkage Thermot Conductivity "K" High Temp. Of soaking Heat 1900 F Lbs. Cu. Ft. 24 Lbl Sq.In. 1 Temp. F 70 1800 Per Cent 2.0 Mean Temp. F 200 400 600? Btu 0.594 0.630 0.666 Calsilite 1250 F 12 100 0330 200 0.392 50 1000 0.5 400 0.510 500? 0.570 100? 0.410 200 0.477 85 per cent Magnesia 600 F 16 50 500 1.0 300 0.500 400 0.605 200? 0.470 Sponge Felt ' 750 F 30 85 500 >.0 300? 400? 0.501 0.531 \ 500? 0362 100? 0.405 Imperial ' 600 F 20 73 500 1.0 200? 300 0.455 0.500 400? 0350 1268 The Ruberoid Co. Insulation Ruberoid Calsilite Calsilite is a molded insulation that provides the physical characteristics re quired by engineers designing modern high pressure steam equipment. It is a com bination of raw materials, ingeniously con trolled, to form a product free from active, harmful ingredients. It is not only unique in its extremely light weight for such material, but it will stand soaking heat of 1250 degrees Fahrenheit indefinitely without changing its usefulness to any appreciable degree. This permits its use on pipe lines and equipment operating at high temperature without the usual pror tective inner layer of less efficient insula tion. The use of single layer insulation also speeds up its application. Calsilite is highly efficient in heat saving; it has a high modulus of rupture; it resists abrasion excellently. There is little breakage of Calsilite in shipment or when handled on the job. It has low moisture absorption when subject to high humidity atmospheres. Calsilite is furnished in both pipe covering and block form. Pipe Covering is made in sections 36 in. long, canvas covered and in such thicknesses that com binations of layers can provide whatever thickness may be required to cope with the conditions. Blocks are made in standard sizes of 6 in. x 36 in. in thickness up to 3}4 in.' All are packed in cartons suitable for easy handling on the job. . Imperial Pipe Covering This is a laminated asbestos paper insulation that has been indented to use 22 laminations of asbestos paper per inch thickness. Its efficiency makes it satisfactory for most medium pressure steam work in industrial plants. Its construction makes it ideal for vibrating conditions. It is recommended for temperatures to 600 F. Being an asbestos felt laminated material it is used on vibrating pipes or where hard service is expected. Will withstand water conditions for underground piping. Excellent as an industrial, oil refinery and synthetic rubber plant insulation. Ruberoid Insulating Cements For the finishing of sheet and block insu lation and the insulating of irregular surfaces, such as'valves, unions, flanges, etc., the Ruberoid line of insulating cements is complete. This group of cements not only uses asbestos as its base, but also takes advantage of such excellent natural products as magnesia, mineral wool and Vermiculite. Asbestos Cements--Factory Prepared --Grades AA, A, HF. Asbestos Cements--Mine Run-- Grades 115, 214. Magnesia Cement--85 per cent Mag nesia. High Temperature Cement--Grade H.T. . Mineral Wool Cement--Good Insula tion in plastic form for temperatures to 1500 F. Vermiculite Cement--Grade A-ll. Ruberoid Asbestos Insulating Papers and Millboard Asbestos Paper Made of pure asbestos, fire - resisting. May be obtained in 6, 8, 10, 12, 14, 16 and 32 lb weights. Also thicknesses yi in. and ^2 in. known as asbestos rollboard. Asbestos Corrugated Paper Efficient for insulating warm air pipes and ducts. 36 in. wide. Rolls con tain 250 sq ft. Asbestos Millboard A rigid board , of exceptional strength and whiteness. Cuts and drills easily. Withstands temperatures to 1000 F. Sheets 42 x 48 in. 1269 Insulation Blanket United States Gypsum Company General Offices: 300 W. Adams Street, Chicago, 111. INSULATION PRODUCTS . Decorative Structural Blanket Red Top Insulating Blanket A Fiberglas Product RED TOP INSULATING BLANKETS --Made for standard framing in three thicknesses: one inch, medium and thick, in roils of 125, 75 and 50 sq ft respectively. Also available in bats 3 ft long in same thicknesses. Light-weight *RED TOP INSULATING WOOL blanket is en closed with an asphalt-type vapor barrier front side and a vapor permeable paper on the back side. This is to resist accumula tion of moisture within blanket. WEATHERWOOD TILE--Available in 12 x 12, 12 x 24, 16 x 16 and. 16 x 32 inches in ^ and 1 inch thicknesses. Colors are Blendtex (gray and tan blends) and Hiiite (ivory). WEATHERWOOD PANELTILE-- Hiiite color available in 12 x 24, 16 x 32, 12 x 48, 24 x 48, 48 x 48, 48 x 96 and 24 x 96 inches in $4 inch thickness. Blend tex colors available in 12 x 24, 16 x 32, ]2 x 48 and 24 x 48 inches. Tile sizes 12 x 24, 16 x 32 and 24 x 48 inches can be mill cross scored to represent Yi inch Tile dimensions. Dimensions (see above). All tile have "Ogee" tongue and groove edges. Structural Decorative Decorative WEATHERWOOD* PLANK--Manu factured in widths of 8, 10, 12 and 16 inches and in lengths 6, 8,10 and 12 feet-- inch thick. The "Ogee" tongue and groove on the long edges (see cut) conceals nails and seals against dust and air in filtration. Weatherwood Plank is made in Blendtex (gray and tan blends) and Hiiite (ivory) colors. When combined in variations of shades and width, Weatherwood Plank produces maximum values in both insulation and decoration. WEATHERWOOD SHEATHING-- Asphalt coated. 2 feet x 8 feet x *56 inches thick, with tongue and grooved long edges for .horizontal application. Also available in 4 x 8, 4 x 9, 4 x 10 and 4 x 12 . feet in either H inch or inches thick ness with square edges for vertical ap plication. ^ WEATHERWOOD BUILDING BOARD--4 feet wide, made in lengths 6, 7, 8, 9, 10 and 12 feet, % and 1 inch thick in either ivory or gray tan colors. Applied by nailing; effectively insulates, strengthens and decorates. WEATHERWOOD INSULATING LATH--18 x 48 inches x % thick with V joint on long edges. Gives an excellent plaster bond and also acts as a cushion for plaster with sound deadening qualities. ' ROOF INSULATION--In sheets 22 x 47 inches--1, 1% and 2 inches thick. All but the % inch size are sup plied laminated with either square or "ship-lapped" edges. Ogee Edge - *Red Top Registered Trademark. Heat Loss Factors The heat loss factors shown on the opposite page indicate the comparative in sulation value of various insulating treat ments included in common construction systems. 1270 United States Gypsum Company Insulation NOTE: These figures apply to 1 story buildings. To get figures for 2 story homes add 20 per cent to the values below for the wall constructions and divide by one-half for floor and ceiling constructions- It is important to use correct factor due to variations in the ratio of wall and window areas. WALLS Bask Construction--Frame Wood Siding Wood Sheathing 2 a 4's Roeklath & Plaster No Wool Between Studs Adding Red Top Wool i' 2* Y Basic Construction Substituting in Above BasicConst. a. Ww Sheathing b. *A* WW Plaster Base c. %' WW Plaster Base d. I' WW Plaster Base e. WW Sheathing and V? WW Plaster Base f. (4' WW Bldg. B<L Tile or BBids. Bd.. or TUe n. Cyplap Sheathing l V2* Sheetrock j. Cyplap Sheathing and .248 .166 .183 .157 .143 .147 .187 .160 .310 .260 .330 .120 .083 .064 .105 076 ,059 .103 076 059 .069 ,055 .088 .067 .054 .090 .068 .054 .104 077 059 .095 .070 .056 .135 .090 068 .123 .085 .064 .136 .091 .069 WALLS Bask Construction--Brkk Veneer 4* Brick Wood Sheathing 2 4's Roeklath & Piaster No Wool Between Studs Adding Red Top Wool 1* 2' y Basic Construction Substitutingin Above Bask Const, a. Ww Sheathing h. */i' WW Plaster Base c. vi'WW Plaster Base d. V WW Plaster Base e. WW Sheathing and Vl WW Plaster Base f. W WW Bldg. 8<L, Tile or tV/ WW Bldg. Bd. or Tile Gyplap Sheathing L Vl Sheetrock j. Gyplap Sheathing and Vl Sheetrock . .270 .202 .200 .178 .157 .162 .215 .187 .350 .288 .368 .125 .085 .065 .III .078 .061 .107 .077 .060 102 073 058 .094 .070 .055 .095 .070 .055 .112 .079 .061 .104 .075 ,059 . 128 .087 .066 .130 .088 .066 .142 .093 .069 . WALLS Basic Construction 8* Brick Wall--4' Face Brick and 4' Common Brick--No interior finish No Wool Adding Red Between Top Wool** Studs* 1* 2' y Bask Coostraction .500 Adding to Above Bask Const. a. 'A' Plaster .480 b. Roeklath and Plaster (Furred) .300 . M3 .093 .069 c. l/j' WW Plaster Base and PI. (Furred) .220 .121 .084 .064 d. WW Plaster Base and PL (Furred) .190 ; 112 .079 .061 e. I' WW Plaster Base and PI. (Furred) .160 .101 .073 .058 f. Vi" WW Bldg. Bd.. Tile or Plank .230 .124 .085 .065 S. Bldg. Bd.. TUe or .200 .115 .081 .062 h. I' WW Bd.. Plank or Tile .170 .104 075 ,059 i. Vl* Sheetrock Furred _.3_2__0 .1.46 _.0_9__5__.0__7_0 *Based on s/s* Furring Strip **Based on Full Dimension WALLS Bask Construction--Plywood Plywood on Wood Studs 5/b* Outride--Ve* Inside with one Air Space Over Vf No Wool Between Studs Adding Red Top Wool r 2* Y Baiik Construction Substitutingm Above Bask Const. a. Vl* WW Bldg. B<L Tile or Hank b. y/ ww Bldg. Bd. or TUe c. 1' WW Bldg. Bd. or Tile <L Sheetrock e.. Vi Sheetrock f. Adding to bask construction WW Sheathing .431 .275 .230 .196 .430 .413 .216 .151 .095 .074 .126 .087 .065 .115 .081 .062 .106 .076 .060 .151 .095 .074 .148 .095 .074 .113 .080 .061 CEILINGS Bask Construction %' Roeklath and Vl Plaster No Wool Between Joists Adding Red Top Wool 1' 2* Y Bask Construction Substituting^ Above BaskConst. a. '/t* WWPlaster Base & Plaster b. WW Plaster Base 8t Plaster c. I'WW Plaster Base & Plaster d. VS WW Bldg. Bd.. TUe or Plank. No Plaster e. /*' WW Bldg. Bd. or TUe f. Vi9 WW Bldg. Bd. or Tile . Sheetrock n. Vi Sheetrock .610 .329 .290 .213 .356 .268 .220 .670 .635 .169 .116 .080 .136 .091 .068 .128 .087 .066 .110 .079 .061 .139 09? 067 .124 .086 065 .113 .080 06? .174 ,118 089 .170 .115 .079 Basic Construction Adding to Above Bask Const. a. Vi" WW Bd. on bottom of b. ^4* WW Bd. on bottom of joists . ' . c. 'I* WW Bd. on bottom of - FLOORS Bask Construction Maple or Oak Flooring on Yellow Pine Sub Flooring No Wool Between Joists AddingRed Top Wool 1' 2* Y .340 .138 .091 .068 .180 .102 .075 .059 .158 .094 .070 .055 .141 .088 .066 .053 Above calculations based on data from'A.S.H.V.E. Guide--1042. 1271 Insulation Wood Conversion Company First National Bank Building, St. Paul 1, Minn. s New York Chicago Tacoma Dallas INSULATION FOR EVERY PURPOSE Wood Conversion Company's insulation line includes flexible fibre and rigid insulation for industrial and domestic purpose. Every product in this line is backed by the name and reputation of Weyerhaeuser, assuring high quality and satisfactory service. Fol lowing are the products included: Balsam-Wool Sealed Blanket Insu lation--a building insulation that is windproof, moisture-proofed, vermin-proof and fire-resistant. Spacer flanges on the sealed blanket permit easy, positive application-- no settling or sagging. Balsam-Wool K-25 Fibre--an indus trial fibre shipped in bales which, when mechanically fluffed and processed, provide an ideal insulation for use in locker plants, cold storage plants, etc. K-25 is low in conductivity--has an amazingly low "K" factor--and retains its efficiency perma nently. . Balsam-Wool Fibre Pneumatic Sys tem--provides an effective means of insulating refrigerator cabinets and doors pneumatically, under pressure. The pro cessed fibre fills every void--eliminates the need for slabs or filler strips. Plastic Filler Fibre--Designed to fill special needs of the plastics industry. Provides additional tensile strength. Avail able in a special group for various needs. Balsam-Wool Sealed Blanket Insulation Nu-Wood Interior Finish Tile NU-WOOD STRUCTURAL INSULATION Nu-Wood Interior Finish--insulates, decorates and quiets noise. Fade-proof colors. Available in Plank, Tile, Board and Wainscot. Nu-Wood Sta-Lite--an insulating in terior finish with more than 70% light reflection. Nu-Wood Insulating Lath--Used as a plaster base, assures strong, smooth, true walls and ceilings, free from cracks. Nu-Wood Roof Insulation--Fulfills all requirements of Federal Specification LLL-F-321A. Furnished in any practical thickness. 1272 Publications American Society of Refrigerating Engineers 40 West 40th Street, New York 18, N. Y. REFRIGERATING ENGINEERING ENGINEERING APPLICATION DATA BULLETINS * SOME 33 bulletins are available sepa rately at reasonable prices for single copies or quantity orders and can also be had bound with a paper cover, the com plete set for $5.50. The APPLICATION DATA Bulletins tell precisely how refrigeration is used in various fields, giving examples and specific information on the best practice up to date. Some of the subjects covered to date are: refrigeration of locker plants, of fur stor age, bf restaurants, of liquids, of apples and pears, humidity in refrigeration, refrigera tion service charts, refrigeration for skating rinks, butter and cheese making, milk plants, citrus fruits, beer dispensing, retail stores, wine making, load calculations, operation of ammonia machines, how to figure air conditioning, refrigeration of ships' stores, etc. REFRIGERATING ENGINEERING CODES AND STANDARDS ENG acknowledged the most authori tative periodical in the field, Refrigerat THE A.S.R.E. further contributes to refrigeration progress by its partici pation in establishing codes and standards ing Engineering has added steadily to thein the industry. Among the recent codes practical value of its contents, and its made available are: No. 21--Testing and number of readers has grown in proportion. Rating Milk Coolers; No. 22--Rating and A wide variety of material is presented, Testing Water-cooled Refrigerant Con all from the viewpoint of its usefulness densers (Revised--1942); No. 23--Rating to the reader in his own business. This and Testing Refrigerant Compressors (Re magazine is a must for men who keep in vised--1942); No. 24--Rating and Testing touch with all that is new and important Water and Brine Coolers (Revised--1944); in refrigeration and air conditioning. The No. 25--Rating and Testing Forced-circu annual subscription price is $3. lation Air Coolers for Commercial and Industrial Refrign. (Revised 1944), (Sup plement to Cir. No. 13, not sold separately.) > THE REFRIGERATING DATA BOOK IS an essential tool in the refrigeration and air conditioning industries. It has been published biennially since 1932 and ap pears in two volumes, published alternately MEMBERSHIP ACTIVITIES IT is the policy of the A.S.R.E. to treat in its meetings current subjects touching upon all phases of the art of refrigeration. --the basic volume, now in its fifth edition, Membership is in two grades with dues a standard reference work which deals from $10.00 to $15.00. Sections hold meet with refrigeration cycles, fundamental data, ings in the following cities: Baltimore- industrial, domestic, and commercial sys Washington, Boston, Central N. Y., Chi tems, and air conditioning; the refrigera cago, Cincinnati, Cleveland, Detroit, Erie, tion applications volume, consisting wholly Kansas City, Los Angeles, Milwaukee, New of practical how-it-is-done chapters on all Orleans, New York, Northern New Jersey, the known applications of refrigeration Pacific Northwest, Philadelphia, Pitts and air conditioning. Either volume sells burgh, Richmond, San Francisco, St. for $4 in the U. S. Louis, Twin Cities. . To keep apace with progress in refrigeration and air conditioning, read the publications and follow the activities of THE AMERICAN SOCIETY OF REFRIGERATING ENGINEERS, 40 West 40th St., New York 18, N. Y. 1273 Publications Goal-Heat Published at 20 W. Jackson Blvd., Chicago 4, Illinois Phone Wabash 9464 - SAigj}OEAcifFOR informa tion on the use and sale of s.tokers, by fuel engineers. COAL-HEAT's fundamental edi coal and coal heat torial policy is "to ing equipment, further the more you can turn to satisfactory use COAL-HEAT and sale of coal with complete and modern coat confidence. burning equip* Here is a maga ment." It actively zine that appeals supports the ap to every man con plication of scien cerned with the tific and engi market, use and neering knowledge sale of solid fuel to the use of coal and modern heat and coal-burning ing equipment. equipment. It Having long since covers both the recognized the. merchandising importance of and utilization of properly designed the coal, stokers efficiently oper and modern heat ated, properly ing equipment. maintained equip With over a . ment to the suc million stokers in cessful use of coal, use today, the and therefore to the welfare of the coal importance of COAL-HEAT's field is industry, COAL-HEAT constantly em clearly evident. It has been and is COAL- phasizes the significance of the "equip HEAT's job to supply coal and stoker ' ment factor" in heating merchandising. men with the information they need to It is only natural that COAL-HEAT insure satisfaction for stoker users. The was the first trade magazine to recognize same is true with hand-fired heating plants and promote the small stoker; to introduce and all kinds of household and commercial many new developments in coal-burning coal heating equipment. equipment to further- fuel,conservation;;to- In addition-to providing its readers support the use of dustless treatment; and with a basic and diversified editorial pro ' to urge the sale of equipment by coal men. gram, COAL-HEAT also publishes a COAL-HEAT has at its disposal an number of books and booklets, manuals almost unlimited number of sources of and reprints covering a wide range of authentic information on the topics it subjects of interest to coal, stoker and covers; its articles are written by the best heating men. Its series of heating guides informed men in the coal, stoker and heat for the consumer have proved particularly ing industries. It enjoys quite a following, popular. These are available at small not only among the most progressive cost. merchants in these industries, but among Subscription rates--$2.00 a year; $3.00 . the industry's leading combustion and for two years. Rates apply for both heating engineers. For years it has United States and Canada. Foreign rates championed the importance of the fuel --$2.00 a year; $4.00 for three years. engineer to the .coal and stoker industries, Advertising rates and other information and each year prints many articles for and will be furnished upon request. 1274 Publications Domestic Engineering Publications 1900 Prairie Avenue, Chicago 16, Illinois AN OUTSTANDING RECORD OF 5 TIMES A WINNER ! For another of its many outstanding and widely recognized editorial accomplishments, DOMESTIC ENGINEERING has once again received high honors in competition with over 400 of the nation's leading business papers. The consistent editorial superiority of ' .DOMESTIC ENGINEERING, de monstrated time and again during its 56 years of publishing experience, has now been accorded this special recog nition for the fifth time. ` Once more DOMESTIC ENGINEER ING offers these accumulated high honors as a testimony to the alertness of its organization to the vital require ments of its industry, and of the nation as a whole. 1275 Publications Fueloil & Oil Heat 232 Madison Ave. LExington 2-4566 Pacific Coast Representative Don Harway ' ` 816 W. 5th St.. Los Angeles 13. Cal.--Mutual 8512 1105 Russ Bldg., San Francisco 4, Cal.--Yukon 1069 New York 16, N. Y. Baltimore 2 c/o Fleet-McGinley. Inc. Candler Bldg.--Lexington 7065 ties back into high gear on civilian output. With an immediate flush demand for about a half million domestic burners and oilfired heating units, 1946 can be expected to reach new sales peaks. Approximately 200 oilburner manufacturers are now in production. Before the war ten of these were supplying about half of the industry's total output, and when reconversion' is completed these companies will probably again sell that share of the total. The industry installed 145,596 domestic oilburners and oilfired units in 1945, more than half of these in fall months after the war's close. Of these, 58% replaced hand fired coal, 30% replaced old oilburners, 4% went to new homes, 7% replaced coal stokers and 1% replaced gas heating. Dealers A. E. Coburn, Editor Robert Gray, Businas Manager After a wartime mortality of around 40% in number of dealers, the war's end Arthur G. Winkler, Advertising Manager has brought many of them back to the industry. Present outlook is that within OILHEATING is a vertical, integrated two years there will be considerably more industry, selling through the same re oilheating retailers than the previous peak tail outlets oilburners, oilfired heating andof 13,000 in 1941. Dealers with oilburner air conditioning equipment, and fueloil. or fueloil background are making 80% Starting some 15 years ago, this integra of total burner sales; plumbing and heating tion of fuel and the equipment to burn it contractors the other 20%. has grown until in 1945 two-thirds of all oiiheating equipment (boilers, furnaces and Oilheating Tomorrow accessories) sales were made by companies According to our projections of post-war that also supply the fuel, and about three- . activities, there will be a 100 per cent fifths of all heating oil was sold by com expansion of oilheating markets during the panies also selling oilheating equipment. first 5 post-war' years,- with sales and in FUELOIL & OIL HEAT, the only pub lication actively covering both the equip ment and oil activities of dealers, was organized in 1922. It is accepted as the editorial and advertising authority for all stallations of 2% million oilheating jobs in all types and sizes of heating plants. They will be divided: 1,544,000 conversions from coal; 561,000 in new homes; and 388.000 replacements of existing jobs. heating contractors, fueloil dealers, furnacemen .and others who really participate in oilheating; also for the many manufacturers who cultivate this vast market for their The equipment will be divided into: 1.443.000 conversion jobs; 406,000 boilerburner units; 644,000 furnace-burner units. products. . For a statistical picture of all phases , . Manufacturers of oilheating--wartime and postwar, send $1.00 for the January, 1946, Oilburner manufacturers in the late Yearbook Issue and for a free copy of months of 1945 and the winter of 1946 "Oilheating Tomorrow"--an 8-page were rapidly getting their production facili statistical study. 1276 Publications KEENEY PUBLISHING COMPANY 6 North Michigan Avenue, Chicago 2, 111. Heating, Piping and Air Conditioning This is the publication which carries the Journal of the A.S.H.V.E. in addition to its own regular editorial section. Its field is that of industry and large buildings. It is devoted to the design, installation, operation, and maintenance of heating, piping and air conditioning systems in such plants and buildings. Each January issue includes a complete directory of commercial and industrial heating, piping, and air conditioning equipment, which lists all products, their trade names, and the manufacturers* addresses. It is the established buying and specifying guide of the industry. H. P. & A. C. is read by consulting engineers and architects . . . contractors . . . and engineers in charge of heating, piping and air conditioning in industrial plants, and other large buildings, federal, state, and city governments, school boards, and public utilities. All A.S.H.V.E. members are subscribers. Such coverage means, for the advertiser, considera tion at all points in the selling of a heating, piping, or air conditioning product... consideration in its selection during the preparation of plans and specifications; in its actual purchase for installation; in its year-'round buying for operating and main tenance requirements. Without waste, the manufacturer of air conditioning products and equipment can reach through H. P. & A. C. those from whom he is seeking the necessary engineering acceptance. Write for our new booklet "A Quick Picture." Subscription Price--No. and So. America--&2 per year. Elsewhere $4 per year. Member--A.B.P.--A.B.C. American Artisan AMERICAN ARTISAN covers the field of warm air heating, residential air conditioning, and sheet metal contracting. Its readers are warm air heating and sheet metal contractors, dealers, jobbers, manufacturers, and public utility companies. Each January issue includes a complete directory of warm air heating, air conditioning, and sheet metal products and equipment, which lists all products, their trade names, and the manufacturers* addresses. A special section of each issue has been devoted to air conditioning since 1932, when it first became apparent that air conditioning for homes was to be along the lines of the central forced warm air heating system. As a result of the ready adaptability of this type of heating system to all air conditioning factors, tens of thousands of homes today have winter air conditioning --supplied through forced warm air heating with air cleaning and humidification. Cooling apparatus can be attached to these systems readily whenever year-'round air conditioning is desired. . The key man in the residential air conditioning picture is the warm air heating and sheet metal contractor--the one man experienced in ``treating air" at a central place and getting it properly distributed. And the key publication--because it reaches these key men with an information service that has made it the recognized authority on residential air conditioning practice--is AMERICAN ARTISAN. For full information on this field, write for a copy of "The Residential Heating Market." Subscription rate--$2.00 per year. Member A.B.P.--A.B.C. 1277 ' Publications Heating, and VENTILATING is a monthly publication read by engineers and contractors. These are the men who specify, install and maintain the-mechanical equip ment used in heating, ventilating, air condi tioning and refrigera tion systems of indus trial, commercial and institutional buildings and residential pro jects. Its readers in clude aslo engineers and designers of the firms which manufacture this mechanical equipment. The editorial con tent is edited to be of practical use to these engineers, and is prepared under the direction of field experienced profession al engineers. - Generally speaking, the emphasis is on practical rather than on theoretical .consider ations. Each month an origi nal Reference Data sheet is . included for permanent use in a standard binder (back copies are available). Special sections are published from time to time. These sections are devoted to subjects jof timely interest, such as Radiant Heating, Piping, Cooling Coils, AirSanitation, Exhaust Hoods, Air Conditiori- ing, etc. A comprehensive Buyers Di- rectory is published early each fall. CIRCULATION HEATING AND VENTILATING'S total distribution (May, 1945)--10,989, classified as follows: Consulting Engineers (244) and Ar chitects (120) Engineers Employed _ by them (296)--........................... 660 Contractors (1,808) and Engineers Employed by Contractors (252)..... 2,060 Governments and School Boards and their Engineers................................ 949 Employees (738) and Designing Engineers (178):.......... 1,057 Manufacturers' Agents and Sales Engineering Firms (180) Sales ' Engineers and Salesmen (729).--........909 Wholesalers (1Q0) and Dealers (368)- 468 Ed ucational Institutions, Libraries, Technical Associations---.............. - 460 Miscellaneous a'nd Unclassified......... 683 Public Utility Group.......................... 551 Industrial Firms, their Executives, Engineers and other Employees ...2,148 Buildings, Real Estate Management Companies, their Engineers............ 652 . - 10,597 Field Staff, Correspondents, Ex changes and Advertising Agencies.. 392 TOTAL.............................................. 10,989 Manufacturers of Air Conditioning, Heating, Piping and Ventilating ' Equipment, Their . Officials and Subscriptions to HEATING AND VENTILATING, 148 Lafayette St., New York 13, are $2.00 a year. 1278 Publications Sheet Metal Worker Published by Edwin A; Scott Publishing Company 45 West 45th Street, New York 19, N. Y. Subscription rates--$2.00 per year, U. S.t Canada and Pan A mer. Foreign $3.00. Advertising rates on request. - THE January 1946 issue of Sheet Metal Worker was its 72nd Anniversary and Directory Number. It is the oldest publication in its field and is of vital importance to men interested in sheet metal work-- air conditioning--warm-air heating and ventilation. Founded in 1874 and- published to 1909 by David Williams Company; 1909 to 1920 by United Publishers Corp.; since 1920 by, the Edwin A. Scott Publishing Co. Subscribers are mainly merchandising contractors purchasing practically all products and equipment which they fabricate, erect or install. Manufacturers, jobbers and distributors also subscribe. The market has three main divisions: (1) Equipment for resale in -connection with erection or instal lation work. (2) Materials for fabrication. (3) Shop equipment and supplies. Circulation: Sheet Metal Worker is a member of the Audit Bureau of Circulations and the Associated Business Papers. Sheet Metal Worker also publishes books on heating, ventilating, sheet metal work, air conditioning, etc. , The Annual Issue published in January, contains a comprehensive and valuable Directory Section. Plumbing and Heating Journal Edwin A. Scott, Publisher 45 West 45th Street, New. York 19, N. Y. Subscription rates--$3.00 per year, U. 5., Canada and Pan A mer. Foreign $4-00. Advertising rates on request. PLUMBING and Heating Journal is edited to furnish a well-rounded, efficient service to the men engaged in the plumbing, heating, ventilating and air con ditioning fields. It covers both the technical and busi ness phases of their work. It gives free technical service through a staff of practical engineers; expert merchandising assistance, and its technical and business.articlesvare. by. men: of. recognized competence. THE JOURNAL editorial department draws its news from scores of trained correspondents located at strategic points throughout the country. This combination of the technical, business, news and other aspects of the industry enables THE JOURNAL to achieve a finely balanced magazine that gives the reader the type of information he wants and n<pHs in brief, compact form. _ A department "With the Water Systems, the trade of the latest developments in the ing field and its increasing potentialities for tl --heating contractor, especially with the sions of rural electric lines throughout the col T279 => V ^ .... . A r - ^ ^ ^ ? 1946 of Membership ; V ; ;. Corrected to-January 15, 1946 ' - . American Society o/ .-, HEATING and VENTILATING ENGINEERS " Published, at the Headquarters of :the Society . . : - 51 Madison Avenue, New York-10, N. Y. SUMMARY OF MEMBERSHIP Honorary Members.. Charter Members :___ -. / v .. . -- 2 lAssociate Members ; . . .:......;..."il770 " .... . 2/_ Junior Members:.'...l..ili.:l.;..-. ;.'l 218; . 24 M78 "'.** Total ' : ~ '- : 4506 : - , - ;*'w .-,,/ - -- * 51-Madison Ave., New .York l0, N;vY. ; v ~ 1945-46 fSS-'vjw <p A''" J$pw0<$x'>V ; islCfC f-'F.trsl Vice-President...:.. '.^`Second Vtee-President... fe st-TC ` Wm^A? W&J-if'irt : " Trea-urer . -^Secretary.1.-.-___ i..j...\:.j.^:. -Technical Secretary.js.-.. ' . C E A Win low -Alfred -J.-Offner*. av^-v*? . ,.-xW, . .> A.i./:'R- usis'_.e-lrlvVr. * L P Saunder \ r.-.r A.-V. Hutchinson, * Carl H Flink. +-* , iKSSte-l--*-v. '* -i . : '? r .'" .* Council ;* =G--E.-'A.-WiNSLOw:-Cftairwio 'v c .'/ '/ : -v1-.-:. -J- Alfred. J.Offuer.-Vice-Chairmanyc* i" r^-.Three--Years: W. A: Danielsonj-'H.'Rv.Rotu."Ernest. Szekely, Dr, B-_ M-. Woods: / ' : v-'" -Two: Fears.*'7 C- :M: Ashley. L. T.'Avery. L.;E. Seeley; Gl.D.,VVinans: j ;One'Yeorr.' J.K.* Coli.inS/Jr./.S;-H. Downs. James Holt.' E:;N.;McDonnell, If^'ii-S" G. L. TwtE.,'Ex-OfiUio.!f'.x*s,<-*. "r t ** * ^URDAHL^-,'~t^-'&?'l yvv/tuTi ^. - %vMilnrB;Noblb .. .. D.'SLinions ? ' Y ?'? G.'V; SoTTEN t, = - G;;C. KiaRKv e-*-' >>.. >- C. IO pETTisSON- ^-^-'iWCp. rc..MBAeTvinoto$n-`?,vi: 1 iTodd': , "" B>Mabo.n - '-- Edtar Anderson ^ _ .o': . '~jpriD.- M: Archer - W; A7:DaN1EL80N 1W H Old 11 * ; ^ W. Legler-. v, *; -.--/.`i-Verne SnmoifM xt C S. Koehler .S-' F. E. P.` KLAQESP'Vr 11 v :. B-S.- Foss, Jb, <.%?/. "-W.' A.-Eyans : ^ F X^Loeffleb- H R. Roth, ^ i . ^ S-i*-; .-. J/ A.-1FbEEBAN-': i %\ :>t>* *D:'.C.\Griffin ; /i; -, : A C. CALDWELL'! v": D. W.-Lodces . _ F LjAdamb^'Vp G. B;-RoDEmieisza * J A-Walsh,":- Maron^Kennedt'v J. r4 E..,V>GarrfON-' r,^-'rf?Fi Xs Ijbseb : t' ; i-.i .e*F. C.-Warren rt-.,: .;iv V-F.;A.' Moesel- '- r - ,E W'Gifford- Chapter :rAtlanta.~ Av.-^.^. ^.>-C..MrAsHLBT Central New-York A I'.'BabwN^ E J RiPHtpn >'Central Ohio-f'f. . . Cincinnati' v- Stanlet Hart ' :. Connecticut.- -.?- t -.: L.. X Nelson , -v r*. .- Delta ;> ^ - R B. Holland : / *.* Golden Gate - " ~ '\'J. S.*Locks a : Illinois - - ~i . S. E. Fenoterbakkr Indiana -. .. i- T R"Johnson .: . --Iowa '. *i. x D;:M. Allen- .. -. Kansas City. - . . F. T..Ball' '.1', . .Manitobai . : ... C. W. Larson . - Massachusetts - . Memphis - ' - - V X F:'Cp?fNELLJ - " ' '-Michigan' - R/E Gorqen .. - ' . X`Leo Garneau .'v/v , Minnesota ..n Montreal- _ D. El McCinxBT^ Nebraska -" - : ' H J.:Rtan". - New. York - E. S.,Theibs . . North"Carolina' ^X'X.X-Webner ' ;' '. Ncalh^Texas: -.-' .- .-NdrtherD-OhiO'N: E T: P.^Elungson Oklahoma ' - vA. S: Moroan" ' Ontario^. ..--R..CSWJLLBT . -*E. H.,Lanodon,- -.. Oregon" Pacific Northwest.*' ; .R D..Toitton : : .. Philadelphia : ' 1 B. B/Reillt. - Fittsburgh- .*-.- 1 -Elmo Hall- * - - Rocky 'Mountam -v vC. F.'Boesteb f .' .St-Louis `- B. P. Fisheb " - * South.Texas' k . Art Theobald .i,,-.. :: . Southern Cafifonua' - J T. Yocno. Jil v . - Utah y :R. S.Dill-_ _ lWashington,- D. Cr-.v CxH.' Pesterfield . < -WestonMiehigan- .. S.-W:-Strousb - v- WtttcrnNew.Yorki-M. W. Bishop : ' v Wisconsin . ** Y +4 -V- .-->^1,-Y7S- .''u.-.,,r-'Nommating-.CommIttee ^?fieprewnlafir8 ; ..r .. -Alternate' L F Kent 4 * -. T. T: Tucker --H.-RTAllonteb* :j-E..J;-RrcaARD* --v. - >' L."R-SaLBT, .-". rG:.C' Kerb''*' *: t-. C/L. Pbtzhson '...j X 0 Mat _,G:.B. Sopple-- v -- - * 'M. L Todd -- - R. B. Mason-: ; - Einab Anderson . -.C.-W. Larson ;. '_'..W'MxMtles.Jr.\. v.;:G.:V. Sutfin.'. -Wright . : > ?.L.-K.-Nbl80n ' > %. R: B. Holland ' , v J: S.. Locke :'&?.: t. ' C- W.-StEWAOT:-':-'-' T.-R.- Johnson * -. -. D; M. Allen- .' -r- -William Glass- -. ... - D. M "Archer' . W H Old ' .E. F. BelliT .- Verne Suuionds C.-S. Koehler "*: / - F.'B. P. Klages ; B. S. Foss,sJr. -.*-. iJohnJaaces^' F.X.'Loefpleh:- - . V. J. Jenxinson x J. A, hREBHAN*.'-" * -D. C. Griffin. * - .-- X-B. Hedges / ;*< :tT. FxRockwell '^ - F. L.-Adams v -C. F; Boesteh / 1 :J..A;-Walsh ^Mabon--Kennedt " vEl V. Gkiiton 1 . .''.J.vW.-MARKEHT.-r- -Pesterfield ;& W/Stbodsb-^ M..W.:BiBHOP' *.- R. F. Connell- : xfJ.-E.-Haines-'^, -. ^ Leo Garneau- D.rE: McCullbt :'< H J Rtan 7 - .- E. S;,TnEiss-.s: > 4 vR..X Werner.;-. - 'D. LjTase r . -E.T. P. Ellingson : J. P. Fitesmons - El1C.1 Willey-. .-.:E. H. Lanqdon ---.' -Edwin Elliot^-*'' o -4).-W.iLoccks .. ., Elmo Hall:.--.--- v%; 1 B.-L.' Evans-..'B. P. Fisher 'j,--. -.. Art.Theobald4.': ..J. T. Young: Jr.- 5 .:. .*F. A. T-g^R 1, F. G.-Wabren .. Roswell Fabnham - .'Ernest Siekelt: , Mfr3'j j -j ^ Sf^;. jfilgjsr .,=* ' 1 *V ;^ri-.s^'.CouncU'Coninriittees.- 4 .' .v">', : . r- "'Executive--E. N:.McDonnells Chairman; S.H.Downs.L.-E. Seeley. . : Finance^--T>t. -B. M.;Woods,'-Chairman;- G. M.,Ashley. T.H.\UrdahL 4- .-.-. 'j2 ^Meetings---James HoIt.*CAa*nBfl*;;L; T; AveryjA.J. Offner. .. . ; ^'-Membership--]. b. Collins.7Jr.^Chairmon; H. R.:Roth,-G. D.-Wmans. jr`^Standards--:L.- P: Saunders: ChairmanyVf; A: Damelson, Ernest Szekeiy. ? ,v,r- -.. -'f : Advisory.Council -H- `Downs. Chairman:. Homers Addams.i M.- F.- Blankin.-W. ,11*Carrier, S. -E. .Dibble, W. H.. Driscoll,^-. ;r .'-E- O- Eastwood: Wl L-VFleisherl H: P^Gaht.sF.-E: Giesecke/E. Holt Gurney. L. A.'Harding. H. M,':.. '<-Hart:'C-* V.'''Haynes:E: -Vemon>Hill:fjohn,'-Howatt. ;W.s',T.-Jones,; D. -D.'Kimball.-G. L-: Larson..S. R.^_j .:^Lcw!S. J:-F. McIntire.,F.vB. -Rowley.-and.Dr. A: C.'Willard.' .. - V "i ^ m i Specia^Commlttees dm5Jtoi afid Advancement Iledges.-'GViairman (one year);_C. ^i.?>Grosby. (three-years).' > 5 . ^ r . -t- ." ' ` >V- -&i\-,77-'Chapter- Relations: G::D.;Wmans.-.t-Aoirman.'/M/F." BlantinrrF: C^McIntosh, H.vR.-:R6th,;H7.-E..Sp.rouUi ^ <s&r _ ................ _. . Committee.on.Houstng Society Q0fices,and:Laboratory:/pE.;-N.rMcDonnell. Ctojfmdn.-'M: F:'Blankin,'!LvE:- ^^^^..^...r^.-:-v.Seelcy.Af E.,Stacey,vJr..G__L__._-_T__u_v__e_,__l_:__H__:_._U__r_d__a_h__l_.__D__r_.__B__._-_M_ .-Woods..-. ....................................................... ... ............... . *-^VEiLW v ^ ^ ^ <* " i .3-* ^ -- ' * * ** *- ^52=; on-Research Fund-Raising: -'Dr.-Ai.C.:Willard.-Chatrman; W. L. Fleisher, E..Ho!t Gumey. C. N......v . .*WJ.iy~ -i -McDonnell: J: Herbert.Walker,^Dr.-Bi-.M.'.Woods.1- - I JV ' . * _ -i. - a : - v . v. -u it~. :Committee to. Cooperate.with olkerfProfesstonal Societies:- .-L. G.:.--`'MMi1lIIIe1 r?kCAcirmon:;Ferdinand Jehle,>C.`.S;f ':i`-. rLeopoldr*'H.-B.-Nttage.^Eniest Szekely1iyV. N. .Withendge. '.' > Constitution and^By-Laws: \R. HrCarpenterf'.CAutrmaji. S. H. Downs, jT'Herbert Walker. , F* Paul1-Anderson-Award^A. J." OfTner. Chairman: W. H. Carner.-F.^E..Giesecke,.W. L.^Fleisher, f*B^ J.r^iGutdc Publication C S Leopold Chairman, V/ C BevmgtoV R" S-Ddl C^F Ka>an.-P:F. McDermott ^ , ^'A-^B.' Newtonr^GJ Hf TuttIe.-.T(;F.-R5ckyell?,W/LvY_erkes.^Cynl:Tasker.'ExTOj^cvo^ r^d COMMITTEEONRESEARCH Saunders: Vice-Chairman - . ' . One Year -.: rvv.John James n. H J Rose - :/L;rP. Saundbrsv 'L- E Seeley ; . Stacey; -J r. . G.iL.pTuve.Chairman ;-,A-. CrFlELDNKR. Ex-OjficiO:' Two Years .C. M. Ashley-: V nF..fc,.-GlESECKB ?* : F..C. McIntosh-. G. Iv.-Tuve y c a/.-T. H. Urdahl" "'Cyril sTaserr.- Director of Research ` x..- > ; ' Threc.Ycars."J: i. ;R; M-. Conner-l ' -JoiiN'A.GoFr r-.F.^W. Hutchinson'1 . -R.^Kr-THULMAN-;. V E; ZlKBER BI'fXKS-e.-.rfTsrirX ... jM"Ashley> ir Ai *-*>- 1Executive Committee f ,1 V- ^ V---*- '.I- -*: (G-L.-Tuve. Chairman-' -;L.-P.>SAUNDBRs.-*Fice-C/kltrmon H J Rose ^ <. ^ ^--^fLt -ExSEELEY * . *c ** 'V * ~<'-r ^: v vsTechn-lcal Ad"visIo'r*y .Committeef s : -'.v-.: '-v-1 'i-vjf'*.-.. ' " 'Air.Cleaning:-j.R. S. Dill, GhoymonyR. D/-BIum. J;^J. Burke:f: Hr-Buzzard: R -E 'Cherne R S Farr"' 1 C,. Ja Glanzer/.-R.-E- Hunsaker.-D.-L: Hunzicker., E. 'A. 'Jone9: HC--3Murphy Dr-G' W ' Penney - - ^ .\Capt. A. L. Stacey.f,Major R-i-P.iWarren.v yj.y A-- ..w- s . A r'.Cpdy*oi*g in^industiy:^W^&-Fleistier,- Chairman:- L.TT: ` Avery/ CaptV^A.: R: - Behnke; Leonard^ - ^-*-Greenburg M p.JiWr'E/HeibeJxD/Ev'Humphreyj Prof^F^'W. Hutchiiisbri-* F/F ^Hyde L' lrLewic^ s O W Ott R Rif'Sayers, M D H E Ziel " X y* > J. J H. ^^ f ~v ^ Air Dt tnbution andJAy-Frictton:: Ernest Szekely; CAairmow: S:~H Dowhs/S/L;'^Elmer Jr'^K'-H` Flint t: <** -w H Hoppmyin^n.'F..J.:Kurth,`'J. iN.;Livermore^ D. J/Luty/R. D. Madison. Prof. U G 'Miller ^ Prof^D W Nelson/.Prof/ G. B: Pnester. L. P. Saunclerg * " --' v : -- .J-, k -Atr Sterilization an^Odor.Control:. ; Prof. W. F::Wells. Chairman: Dr. L.- J - Buttolph' Lt Comdr W `'-V-- % Consolazio ''Leonard preenburg,; M.D:;: Prof:: B. H.^Jennings,' F: H. -Munkeltr Dr < G * W Penney ^ '"Prof J A Rcymei^.F/.W-..Rdb]rison.'.Prof:-,JLAE::Seeiey * Mildred Wells, M D < 2* ^ ^^ ^U ^ i Member of Commmcc on Researchva *4,*. y- ij: Cooling.Load:. W.'E. Zieber,* Chatrman;.0. W. Armspach.Prqf: H. Ol Croft, P. L.'.Davidsqh, VV.-F. Fnend. . ' -: R.'H;Heilman, John,James,*.Prof. C. F.,Kayan' j. N. Livermdfe,'Prof. C;-0^;Macteyj J.' P.-Stewart;- Corrosion: -L. F.Cdllins, Chairmen; R.,C. Doremus. Dr. Scott P. Ewing. Dr. E. W. Guernsey; Prof. G.-G. ' .--.Marvin, A. R. Muniford.L. P.Saunders,?F. N.Speller.x. / ~. ,--.V/y.. .V- Flout ofFluids Through Pipes'and Fillings:. Dr.-F. E. Giesecke',* Chairman; T. M.-Diigan; Prof. W;'S: Harris, ! ' S. R. J^tris; L: P. Saunders.* ' . ` *- - Fuels: R> A. Sherman, Chairman;. R. M.- Conner,* R. S. Dill, R. B. Engdahl, .L. N--Hunter,'VDr. R: C.- . - . Johnson, Prof. Si Konzo, W. M. Myler,-jr., W. T. Reid, Dr.H. J. Rose,* E. T. Selig. Jr., C. E..Shaffer, T. H. Smoot, R. K. Thulmari* E. C. Webb.' \ . .. . / , * ;:*/ - Glass:'. R; A. Miller, Chairman; L..T. Avery, Dr. H. C. Dickinson, j. E. Frazier, E. H.-Hobbie. Dr.'J.- C.. Hostelter. L. K. jones, J. H. Lewis, F. L. Martin, W.! C. Randall, Vic Sanders, Prof. L. E. Seeley,*' H.:b: Vincent, Dr`G. B. Watkins; F.C..Weihirt: ' . - . , V~. ' r 7' -Heating-Load: P.' D. Close, Chairman; C. M. Ashley,* E; K.-Campbell; j. F. Collins. Jr., R/C.-Cross, ' Prof. W.-S. Harris, H.E.-Lewis, M.' W. McRae, Prof. T. F. Rockwell, Prof. F. B. Rowley', R. K. Thulman,* G:,D. Winans.'' ' ,7. .V / \. ' ... . -. -~.H-eat:Transfer Surfaces: --Prof; .William Goodman, Chairman; C. L`. Bensen, .Prof.'A. I,. Brown.Wv.E.-, H^bel;Lieut. A.'.L. London, J.'W. McElgin, R'. H. Norris, L."P. Saunders,* C; E.' Scott, L. G.'Seigel,- |L: L: Simmons,W. C'.WHittldiey. .- :</._ v- ' -J' -v * ' InstrumentsT-.-JC.~M.Ashley,* Chairman; Prof. L.-M.MC. Boelter, E. L. Broderick, R." S.Dili, R; B.'Engdahi,. ' Lt:Col.'Ai P. Gagge/Deari John A. Goff,* Prof. R. C. Jordan,.ProL G. B. Priester, W. E. Rietz, W. Ri .Teller... [7 ; - '; '-/ > ./ Cr> -> 'Insulation: -. Comdr. E. R.'Queer, Chairman; #.. -E.-Backstrom, T; H. Coulter,-Prof.:F.;G.'Hech!er, H. E. . . Lewis,'H.` E.'Robinson, T. D. Stafford; Capt,.T-. H. UrdahJ,* Prof. G. B. Wilkes, P. M: Woodworth.-- Physiological Reactions: R. W. Keeton; Chairman; Thomas Bedford, MX)., Capt. A. R. Behnke, !'Dr.'A. C.--BBuurrtton,- E.'' FF,.- DuBois,. 1M.D.-, Lt.^CoU A. P. Gagge,``A; C-. Ivy, M.D.', F. C. McIntosh,* R., R. Sayers. M.D., Charles Sheard,''M;p,V'Cbi.''A;. D;;Tuttle. ' - ' -.. ... Psychrometry: -J. H. Walker, Chairman; Dr. H.-C. Dickinson;-Dean John A. Gdff,*`Prof. William Goodman, '- .;Prbf.--A..P.` Kratz, Dl MI:Little,.Prpf'-C. O.iMackey, W.-E/K.,Middleton; D. D. Wile..- Radiation and.Comfort: J. C.'Fitts'.-Chairman; R. E. Daly, Dr. F. E. Giesecke,* L. -N. Hunter,-Prof.'I-. \V. Hutchinson,* John James,* Prof.-A.. P. Kratz, C. S. LeopoId. E. M. Mittendorff, L. L..Munier, Dr.- :G. W.'PeHiiey, H. F. Randolph, W.'R. Rhoton. :7.' ^ ;\ : - Sensations of Comfort:^ Thomas Chester, Chairman; R. S. Arnold, Prof. M. K.- Fahnestock, G.- D. Fife,' Lt. Col. W. j/McConneIl,. F. C. McIntosh;* A. BrNewton, K. E; Robinson, Prof..C. P. Yaglou.' . _ Sorbents: Lt. Comdr.' John Everetts, jr.. Chairman;;R. E. Cheme, O-D. Colvin, F.'C. Dehler, L. S. EpstrinV' Dean-John A. Gnff,* C..-H. B. Hotchkiss;-J. C. Patterson: G. L. Simpson. C. F. Sines. - . 7 .` ' 'Sound Control: R.`D. Madison,Chairman;,C.'M. Ashley,* Dr.' Pi H.fGeiger, Cf H..Hall, W. W. Kennedy, -G.!C... Kerr, E. W. McMuUoi, A. G.; Sutciiffe. f. H- Troilerj Capt. T. H. Urdahi;* Dr. T. A. Waiters;r .Weather'Design Conditions: -Capt.T:-H; Urdahi,* Chairman;.J. CsAlbright, C. E. BeiiUey.'R. E..BiHerf- H.;S."- Bifkett, J. F. Conins, Jf., Lt. Comdf. J6hh Everetts,'Jr.,'-J.'P. Fitzsimons, Ca'pt. J. D; Kroeker, ! , .Comdr, F. W..Reichelderfer,.H;jC; S. Tfibni.' .7. "'/'t T' ' : . *Membef of Committee on Researchl "i-| -? . Officers of Local Chapters, 1945-46^ . - ' -7 - Atlanta - /. . W ..7 ''-Headquarters,-Atlanta,.Ga:( . rMectsT First Monday in Month - Presidentl'l. B. Kagey > ' - . .- 7611'Bona. Allen'BIdg., Atlanta 3 ` : -Secretary, M/F. DuChateau ' . ' - .WashingtonSt.Viaduct.AtlantaS ' -' Gentral Ohlo * ' . Headquarters, GoIumbus. Ohio - * 'Meets:Third Monday.in,Month , President, A; W.'Williams ' - ^ . - ^ 5 E. Long St., Room 808, Columbus, 15 ' - Secretary.a. R.Allonier s ; .1. - . . . 7101 N. HighrSt.-, Columbus.15. .. - - *7;; ^ ; _- -'Gentral New York * . ' ' <> ' Headquarters. Syracuse,; N. ;Y. President?C. M.-Ashley-^ 7 <* -300 S/Geddes^St., Syracuse IV \ .7 1 Secretary; Fi-E. Hockensaitth. '' : . "400 N?:Midler"Aye:\;'.V ` '! * '../'.Cincinnati ... ;/ ' Headquarters, Cihdnhati,-Ohio. 'Meets: v.Second Tuesday, in Month' ; ' . `Presideni.yE. J: Richard' /V *:'J -/ *' /2137'-Reading Rd., Cincinnati:2 - ' .Srrtny.'-H..K.-JENNINGS'V,''. ... .. .. V 7 ' 7 16^,Union Trust'Bldg.TCIncinnati 2 - - V>> Officers and L|st of Chapters, 1945-46^{ Continued) . . - Connecticut /- 7-..'. 7 Headquarters,\New!Haven, Conn;.' President,Stanley.Hart ... " - . NewfBritain r V- - -.Secretary,' Winfield' Roedbr . -405.Temple St;.-,..' . .. ' -- . . - - t ; Massachusetts; ^ v ^ / Headquarters, Boston/Mass: , '. .Meets: Third'Tuesday in Month ' . President, D. M: Archer//-:-V .. . ' . 143 Federal St.. Boston 10 ' - -. .Secretary, A. Ehr'enzeller .'. V ' ; , 23 Parkla'wn Rd., Boston 32- - -'- -- Delta" - ' ; Headquarters, -New Orleans, La. - V; ' >' Meets: -Second Tuesday in Month . :/ President, W. H. Grant, Jr. ' - . '' '... ' 209 Vincent,Bldg., New Orleans 12 , " ".Secretary, -j; S. Burke - ' . "' ' ' % -317 -Baronne St., New Orleans 9 : Memphis.' . ' - . Headquarters,' Memphis, Tenn.- ' Meets:' First Monday.in Month -* President, T. J.'0!Brien -- r ' - ,? . 1030 Exchange Bldg.. . . ' Secretary, A. T. Bevil '. .. - . '. 1521'Waverly Ave.; Memphis 6 . . . -. v _' Golden Gate, '. . ' ^ .... - Headquarters. San Francisco. Calif. Meets: First Wednesday in Month , Prestdent. R. 'B. Holland' -' 420.Market St., San Francisco-11. / , Secretary, F.- W.-Kolb - - * .7 . 598. Monadnock' Bldg., San Francisco 5, . ' Michigan. `. - '"./ Headquarters, Detroit,-Mich... '_ Meets: First. Monday-afier. '.lOth of Month - President, R. F. Connell . . '- - 1500 United Artists'Bldg., Detroit 3i . Secretary, A. EVKnibb.--' ' ' , ' 1003 Maryland Ave., Detroit 30 .. .j . . - -. Illinois; ; / - . . . . - Headquarters,.Chicago, III.- L': . . . . '-." '--.Meets: Second Monday in Month - ." ^ '' i President, James'S. Locke - / ....' ' 7. . -433 E. Erie St., Chicago 11' / .- -'- . . Secretary. C. M. Biibnam, Jr:- . ' . ." . Room 1605, 6 N;. Michigan Ave., Chicago 2 ' . . \ -Minnesota; - ' ' - Headquarters, Minnipolis, 'Minn.' ' .Meets: First Monday in-Month..' - President. R. E. Gorgen" \ 2120 W. Cedar. Lake Blvd.. '. . 'Secretary, O. L. Lilja . . ,5000T6th Ave. S.,'Minneapolis. 7 -/ - Indiana*: - : ; ` - Ileadquarters.Tndianapolis,' Ind._ . . Meets: 'FourthFriday in Month - ' Prestdent, G.' B. Supple ' .V ' r; - . i- Architects and- Builders Bldg.- - ' , Secretary, T. R. Davis. -; . . .. 1311 N. Drexel;Ave.,.Indianapolis I- - ,v. - Montreal . ' . . ' Headquarters, Montreal. Que. ..' Meets: , Third Monday ih Month ' r President,.A, B. Madden . 1170 Beaver .Hall Sq.r- - ' . Secretary, Leo Garneau', * '/ ~t; i' Room 832, Dominion Sq.-Bldg.,. ; -,. 7 ''"Iowa - - . \ ' .. - Headquarters, Des Moines,.Ia. - ... Meets: Second Tuesday in-Monih . President, B. E. Landes ' ' ' - ' / . .1603 47th^f,/Des Moines 10.. . .`SecretaryC,:A. Wheeler ' . ' V -. 511 Fifth Ave., Des Moines / .* . - -- .."Nebraska "- r" - .- - -Headquarters; Omaha, Nebr. . ' ; - Meets: - Second Tuesday in Month. ` President, D; E. McCulley- :/ ' 814 S. 14th St,7Oniaha 2. /A.- ' Secretary, D. D. Williams . ' . ./. '/ . Room 311-, F&eral.BldgV: ; : -./A'-'*-;.'. - - .Kansas City r , - , .//V-': - 'Headquarters,'Kansas City,:Mo.- * ; -j Meets:' .First'Monday in'-Monih /'- v -rPresident,-VLl-B:tMason -V V V/ '--- '. : -- -/y2014 Wyandotte St.-,' Kansas City ; Secretary; PVC. Leffel ` V~ / V 3l6-E,;75th`.St.',-Kansas City . ' y. . . -New:York:5 - . - '' ' Headquarters, New-York. N. Y. y.-r . - Meets': - `Third Monday in Month ' - /,. .. President; H.*J. Ryan "" ' - - _ -. - - - 101.Park Ave.,, New YorkT7; . '. V ' -.Secretary; Carl H.-.Flink V '"tJ - ` Room 3000, 51-Madison Ave., New York 10 .. ' -. Manitoba V -.J , Heaiiquarttt-s. Winnipeg,.Man. -'^:C'Mexts:,.-Third-THursday;ihMonth'; e -President.'F. TI.Ball7; -/,- -. r 'V: .. .. yV '324'Main StV-.. -5eri-idry,'D..S. S^AIN ' "> 1-7. 7 ;27 Fawcett'Ave; v~; ".c- : -'ry--, .; North Carolina , : ; t V 7 -- :Headquarters, Durham;.N. C; . v , . ; Meets: ' Quarterly -'.// ..President, K.;W.' Selden.-JiL ;'/- v . -. r>701*Buildere Bldg.; Charlotte 2-''` Secretary, E. S. DeWitt . ` * V--1211 Commercial -Bahk^BIdg./Charlotte " . if f -4 ldiListorChapter^^ C ^ North Texas Headqcarters,; Dallas,-Tex* ?Thtrd Mondayin .Month .. , President.-E^-.T!Gbssel^;' r,- ;-..: 610 Thomas Bldg.,'Dallas 1- - v;<-. Secretary. -C: Rollins Gardners*1 . .. l^Gamp-St.: Dallas 2 ; -- t _ RockX'Mountaln\ i- - '.^Headquarters^Denver; Color.- .x -.yMeets: Ftrst Wednesday.in-Monlh*, ; !: -President:. G.:D::Mave2 ^ *>*" -i,:. 1550 Glencde'St:r.Denver.-7>_: -u , 'Secretary': Fred-Janssen- r-.-v . s* . <* >1123''W;%.Third'-Ave:. Denver y ,. - < *-: C^'v*; - j St. LouLs%' - .i . .-? * -!.,v. < '.. Northern Ohio -'. -- ; . -` r -'- rHeadquarters/St. Lxiuis.'Mo. r i.-. - Headquarters; CIeveland.>Ohio 7i\^ f.Meets:. .Second.Monday tnMonth-.. -_ President: G. B. PriesteR' t >... 10900 Euclid Ave:-.- Cleveland.6 C. : -..Secretory..R.--L; Byers .. *. > 448-Terminal.Tower.- Cleveland.13. . Meets:; pirsi Tuesday tn-Month-: -irh-'X Presidentr_W: J OONK /-*. 4548'Red'Bud Ave;:'St.-Louis-lo ^ Secretory.-W-^Av Russell. . '-.'5-. v- .; < - C. i 7918-Kmgsbury Blvd.r Clayton o~ :-^`- " -'. Souths!exas-" r- ",-v.'"-i WWSh-i .-^'.Oklahoma;?!; >V\-v/ : ! . ` - Headquaners.-Houston;'Tex.' y . - :- Meets;-. Third Friday m -Month'- - r . _ _ Headquarters,-Oklahoma City.-.Oklav. Second MondaymMcmth. ../Ve.r*<2c*r,".Earle'-W.~Gray : -- $m$0m *' * Tbird-aid.Haryey^Sts. .fi*-: :: r- Secretary,^; T.` Doncfpl - ^^^swjV^^:;:r;*5,;5i*s:.;Oklahoma Natural'Gas Co.-*v-'* h\ -. , Pres'ideiiii ^^A. Walsu ^ '..P.O.Box 1773 .Secretary^D.-M:.MillS:v - -Gray.and Crawford.{Houston 3. - . w.-1;^ t :"Y r~rK. .-. .r, ? - Southern Cflllfornia: , -' - l- --. Headquarters,-* Los -Angeles. Calif. -^ r ' ' * - X:-`'Meets:'isSecond,Wednesday tn-Month v* S ----------.-1"s-'''s -----v--- O`ntar..i.o...v......^. r_Headquarters, -Toronto; (hit.*; - Meets: FirstMonday tn Month^.T^-- ' Pre'sidehlriAXBLOS Kennedy *J!r' 4 V : 505TSahta Fe Ave..-Los Angeles 11^* ..Secretary,.R- `A^iLowe > .- *-. * 3744'Potomac:Ave.'.vLos Angeles 16 -/ >*x> Presidents J: P: Fitcsimons - ;.~f " * s" N^ 3SSfc, - .5ecretofy;SH;:R-/RoTii -, '/.f *57'Bloor St/.Wi'iU. ^^prkc ..* - Utatr - ^ i/2' ^ -.. : Headquarters.' Salt Lake City. Ltah . . uMeetsr^ Ftrst -Wednesday tn -Monih\ '^ r PrcstdcJi/. H^' G.-'Richardson-r' - '\d '--'!y Oregon ; . - c'Headquarters..Portland: Ore. . . '1433 Haryard Ave. 1 :- Secretary 'E: V GRITTON 2470 S. 15th Ea t St '. a- .v -r > 'Meets; .-Thursday afterFirst Tuesdayin' Month: ^^^f^-p^dPrcsidentxF. F/Urban " 6726:S.-.W._ Burlingame'Ave.'- ?.; .-w ,, -. [f^^^'^/^r^-^k^-Secretary, iE.*-Rv.Iajkky <. - Ni wtGlisan St Poland 9 _ ^ ;-.r. .v?. - "?,-.*--i A;\-: :. ;. ...u vj.-Washlngtoni D. C. *-. : ; *.-> Headquarters. -Washingtoni D. C. - . -Meetsr^Second-Wednesdav tn-Month'-:- ^-t'.. ^-President:W;'H; Littleford--' .'- 616 New Vork Ave.' N.W. '-' ;*. -;.v -*` Pacific. Northwest^V'j^^^.'^r-^- i*. Secretary: Lester,Maurer-- . .. 1738-33 Place S.'E .`.Washington 20 - ; .-: -Headquarter^ Seattle.-.Wash. ' Meets: Second 1 uesday tn-Monlht. ' ' ^ WesternMichlgan - r',^n.FpiN sS-rl^Si.'tL*c- <-:- Headquarters,1 Grand^Rapids. Mich. KSeattle X'*^ ; '.s-v a- - \-Meets:rrSecbhdlMonddy[in:Monihi;3'3 -President: Hv*Ji'-MCTZCER'tj^. _ * , 137 E VVater St.',':Kalamazoo'.:/, -. fli ^^^`^^Plillaaelphla -j Secretary:- H. -W-.' WoLters^v 820 Staples Aver;N-.\V.-;`Kalamazc>o-5 Ir ^.H^dquarters,'' PhiladelphiaTTPa.: ypr/>aMAeMe-tvfs,ya:R-r.-S; tTe7i)rc-o_jTnrnd*iTTThouVf^s^d-ay.y..jixnrs-Mkonth: " vNinthVaiid'C6lurnbia`Ave.-'`{; 5^rv2->v.j*j'da:rte--r-s.T,;"-.P*.-.i-t-t. sbiu. rgh^Pa? Second^Mohday-tn Montk^*.^ _ i:-ypresiderU,}l:;S'r Maehling^v>' ..................... ..,, ^^^^^j^:C6i^^3Club^DhrPitt^burgh-'164's'.. lg2tfjSecSdSry; ,E.L H>Rie^ieyer,"JR:.P 's -^r* ?' ff5e^^j-231-33cWater/StA-Pittsburgh 22"r* t'-i? ^ T< Western New':York .. --; i - i -.;. ', : - Headquarteis; :BuffaJo.-.N.:Y. % re --Meets:- c. Second Monday tnMonth-3-3 . Presidentr-F. A: Moesel i.... - r 31 -Main-.St..-'Buffalb 3 ^ .:\,'5,ecretory.-J.-S.-MeyerV^ ^ ~ v.0<- -v !38.Cra8cent-Ave^Buffalo14--'.>i " ' .-..., * >A,'^f^js'ls-.Kr*`A.t>^.- j? ~ -- rf ' ** v ^Wisconsin. - . --Headquarters.-^Milwaukee. Wis.- r- +-Meet$:;f-Thttd';Mbnday-iniMonth~-j:- - .S-'Pridcnl.-;().vA.iTROSTEL * - V- r^.- RouteNo.*'2.!7ThiensviHe* Secretary?J.vR: Vernon *. _ *" *- j -v.-*^'^r*v-.'*07 -E"?4M3ohigan St^'Milwaukee3?*^'' . J;,? v-X* '6* ' i";l-r.'T- V,rvf " ft./ - I'-f- ^ '2%^ rA l'A Roll of Membership AmericanjSociety: o/Heating dnrf Ventilating Engineers; * - " . ' , ' - - - 1946 % *' ' " -' s^ - (Corrected to January 15,-1946)' "i-.; a;S ,*^p jZ!53r' -A' ' HONORARY MEMBERS -~ .CARRIER, WILLiS"II. (1944) (M 1913),.(Presidential-Member), Syracuse. N.vY. w-T".1 FIELDNER, A. C7 (1944) Washington,,D C. ^BALDWI^1^WMt'*JJ/(1915)-New;-Ybr^,''N; Y.,(Deceased May 7, 1924). ' " ?-nBILLINGS, DRj>J.^S.'(1896)rNew>-Yorkj N; Yi (Deceased -March' 10,1913): r-V >'3? A.-iAr: :,;BOLTON,^REGINALI>/PELHAM:;(1897); '(Presidential. Member)i New'York, N Y. ^ -v (Deceas^;FebruajyU8;?'i912)::. .?' 2 0'.y?;V-v /. BRECKENTRIDGE,'iL,-P.';(1920),' North-Ferrisbufg, ,Vt. (Dec^sed^August 22," 1940).-^ V GORMtYv-.JOHNi(.Charter;Meinber), Norristown; Pa; (-Deceased.January 31;'1929);-^,:'^-' . /NEWTONf C:.:W.^(Charter"Member),TBalrimorej'Md^CDeceased Aueiist 6, 1920) HOOD,^0./P..(1929)i^'Washington, D.-C. (Deceased15April'22, 1937)^2;'^' *- ^ - jpLLEl'lySTEWARTrA. (Carter- MembW);.(PresidentiaI Memb^r)j Philadelphia2Pa: -> _ (Deceased Aprir5,-il935).y'. *- -t- 5 V tT 5s- T- -Jr r'\- - ~f it 'J-pf' -. .ftvvV3\~p:if: * r^ ~ : (*^terislc;indicateaautii6rshlp'6f`paprs; indicates addressvfor.mall)-- ' "Tem* C^(M.1923M 1918; /.I916),mdicates.r-Election asMember 1923;5A30ciateT918;-Junlorl9l6-;.t * ihJ&Ms VCPres. 1923) indicates;! Elected President in 1923'and is now a-Presidential'Member- - ' - .v i , - v. .- A"^-*v v . ADAMS. CHester. Z.- \(Jf-;-1939)>:Owner.' t'~_.__ , ~ _ * >* - ' 'w '- .v;-V -. Adams'Co^t, 312 .Piedmoht<BIdg.: --Box:"1356. and ,\.^ABBOTT,-Furman:S..(M 1943).Chief .Engr., W., , 207El-AvondaleiDr^.Greensboro,'N--C;- ~ ~ -..j7:*a11nd>Vf8e0 1A",ft,eInrgcl.ow7 ?Aavset .-.MoSn>tc, lNaier.wNY.-oJrk- , N.....Y. , . . ADXMS;:Eugene'E.' (^1938) Sales Engr Garden >v Xity.FanGa^R<m*1508:A-'65W^v42ndrSt^New^^t'^^W- ABBOT^T,: TTiomas; Jv i-(M-.';1938) Secy.'-Treas-, ^'-'- .7 ^!Gcorge'G.-Abbott,iLtd.;V52rShaftesburyrAve. v r'ry.-aand 2944..00iri6o1leeiiPPkkwyv.^LTToororonrtitoo?`7O0hiit'.^^Canada.' " > ?: ABRAMS;, Abraham ;(Af. l027;`-iJ?1924); Cons- Engr.V-^72::Nbrth;AVe;, and1;* 112 .Bon'-Air-Ave.,' -r- ^New'TRochelfe; N.:>Yr--';'-'r > , :ADAMS,": Eufeene F. (M ..Peter-Kiewit-Sons>.Co..;.and: . Laramie'.Wyo.'; ADAMS,c Frank X.`:(M.1939): . ABRAMSON, '-Ralph;J. ,(A? 1938) . Mech: &'Elect- Engr ;|SamuelJR.v:Lewis,?'4072.S..Dearborn'St-;': - Engr". P. O.-Box 840: -Denver SL; JDehyer^7,;CoIo .r..v.- Chicago.~-aifd.'*1834 ^Pratt .Ave'.,^Chicago 26, - III. , .< ADAAlS.rGeorge F (M 1944)^Eng:5;:*:Mi(irat^'^^^ - ACHLNBACHr>}Paul!R:*;S(if41942);Asst..7rMechfv :: PIumbing 8:Heating.,Co., 2450`Blake"St.^Deaveri_. . ,, .rt."-. Engr.v*Natidnal' Biireau-ofStahdardi^Washing--- . and.3301-Jay StiV;Wheat,'RidgerGola.^;<5,'^^!!aj.s. t.;../ton, D.,G)Jarid 1912 N.Randolph St,-,'Arlington,-Va." ; ADAMST;Ha^ld:E.T(J^19TO^CWSrE^.feiTH^^&t^^^J> * L!ACIIESpNi';Louis,'K.` (M^1944) Laboratory .Coor->V-; :dihat6r;tThe;HpbvervGdnipahyV'an'd'e816-Pbrtage - rMNeam^U^EHenigehintse!?e:Nn<nMg:^w^aI^k-r''^CSononJu?tCkf5^N%;oa*f^wjt^asl<lC73^J>a'?ncd>5^e^i--:^'^'JvVi^-,;-r' ^ -St/, North-Canton, iACKERMANN,-Reyii61d^H.C(M^1943)^Engr r -; * Charles^SrLeopold, Cons.'En^.',213 Broad SL'iPhii- v.; ,.c-:adelphia,-'arid;267.''Cobper'Ave.?.Lahidowne.Pa./:- ^ ADAIR; Jamea S.T(Arl941; /;1940) >T420 VaJcnce St.-..-New'Orleans.ISS-T-Ia.i Siv*''ft' ~zh-- Heating- Ventilating."}Air_'(^riditibnihgS'Gui<dejl946 ^^ 7i/ ADAMSON, L. C. (A 1945) 'Owner. Air Condi ALGREN, Axel B. (if 1930) Assoc..Prof:. Htg:. , '-. . itioning. &' Heating- Service Co.V 3922 Troost, Vent.'& Air Cond., Engrg.. Experiment Station; v - 'Kansas' City. 4, .and .1920 East'- 71st Terrace, .University of-.'Minnesota, and *5109-17th `Aye.-, -' . `' Kansas'City, Mo. . ` ' S., Minneapolis, Minn.' ' ` ^ ADDAMS, Homer (Charter Member', Life Member), ALLAN, William (A- 1938) Pres., Allan Engi-V. -t {Presidential ..Member), (Pres., 1924; 1st - Vice-- ' - ` neering Co., 724 E..Mason St.', Milwaukee 2; and'. - -Pres;,,.1923: Treas.. 1915-22; Council. 1915-25), . 2735 N. Farwell Ave., Milwaukee 1L WIs. i. ; - - - - PresL, Fitigibbons Boiler Co.'. Inc.,-101 Park Ave., " ' New.York 17/N.Y. ' ' ' . . ' ' . ADDAMS. Paul K. (M 1943)' Exec. Vlce-Pres.. -ALLEN, Abraham B. , (A 1945) .Office Mgr., , 7 ` Oil Burning Engineers,. Inc.,;3146'W.-Chicago, ' ; Ave., ' Chicago 22,. and 2233 Birchwood Ave., " ' Fitzgibbons Boiler Co., Inc., 101 Park Ave., New Wilmette, IU. " '' . \Yorkl7,and465-West23rdSt.,NewYorkll,N.Y ALLEN, A. Walter (if 1936) Sales Engr., Pease ADDIE, George R. (if 1945) Managing Dir.; ' .Foundry Co.,'Ltd., 151 Glen Ave:, Ottawa.'Ont., ;- ' J.-G. Wagstaff, Ltd.-, Alma Iron Works, Dukin- ' -Canada. - ' -- '; . r field;`Cheshire, and "Bryn Hendre,Conway,/ ALLEN, DeWitt M. (if 1936) Owner,.* D. M. North Wales, England.. '-r Alleni Co., Room'; 101; yBldg... 215 W.-- ADDINGTON,..Harold M.. (M T939)* Aurora ' Pershing Rd., Kansas'City 8,' and 39JiWest170th - : . Hall. Oak Ridge. Tenn. - - . * -.: -. Terrace, Kansas City 5, Mo/ ' ' 7." ` :. -. ' ADDINGTON, Herbert B. (if 1938) Cons. Engr., ALLEN, Frank C, (M 1944) Mech. Engr., U. S. * "; Myers, Fuller and.Addington. 21 East 40th.St-, Bureau of. Reclamation, .U. S. "Customhouse, ./<.'NewYorkl6,and6990cean'Ave.,Brooklyn26,N.Y. - - Denver, and 4467 King St., Denver ll.;Colo. '. '. ADEMA, -George. E. :(if 1939).Prop.?#N; M. ALLEN, George W. (A . 1945) Steamfitter. *64 ' . - - >Adema^&?Son, 39 W. Balcom St., Buffalo 9, and Raymond St,, Gardner, Mass. ' . / -. : -299;Deerhurst Pkwy.,-Kenmore.l7; N.-Y. ALLEN, Harold D; (A 1944) ` Mech. Engr., ^ ADLAM. T. Napier (if 1932) Vice-Pres. & Gen. - National Advisory Committee for Aeronautics, fMgr." Sarco Manufacturing Corp.,-475 Fifth Ave., '.-Cleveland Airport, Cleveland,-'and-el584:Larch-r; ; /-New. York/'N.- Y.', and 124 Forest '.HiU/Rd., mont Ave., Lakewood 7, Ohio. .- -- '-7 -V. .'West Orange, N. J. '' - . ALLEN, J. Lloyd (M .1944) .Partner, Allen' & AEBERLY. JohnJ. (if 1928), (Council. 1937-39), . Kelley. 333 -N. Penn,'Indianapolis, and 5699, N. Chief ofBureau of Htg. Vtg.and Indus. Sanitation, Delaware, Indianapolis, Ind. Dept. of Buildings, Room 702 City Hall, Chicago, ALLEN, William: A. (A 1942) Pres., Sprague v. 2. and .6225'N. Newcastle Ave., Norwood Park J . & Sprague, Inc., 6230 Pehn Ave., and 216 Hilands - P.O/-Chicago 31, I1L ' ' ;/ ' . ' " " *'Ave.,'Pittsburgh, Pa. 7-V - AH EARN,-.William J.; (if 1929) 791 Tremont . ALLEN, William' W. (A, 1936) Pres.; American - - St;,* Bastpn,;and 131*.Windermere Rd.,- Auburn-. Coolair Corp., Box 2300,hJacksonville, Fla. v.'dale,-Mass.-. *./-'-Y "" , ALLISON, John H. (A 1945) Sales-Engf.^EyJ. AIILFF, Albert A. (M 1923;A 1918) Spec. Repr..:, Deckman .Co:, 1502 Oliver BIdg;, Pittsburgh' 22, - ' Hajoca.Corp;,-Box 7319. -Philadelphia, and 1521-..: 7r- and *601 Sherwood'Rd.,` Pittsburgh 21, Pa/ . -.- ^ Powder Miil.Lane, Wynnewood, Pa. - ' \ ' ' ALLISON; Robert E. (A 1941) Owner, * American - . .-v-AHRENS, Clarence-F. (A-1940) Sales Engr., R/A. . Sheet Metal Co.,-601. First Ave:,'Dallas 10, and: Dubuque Supply Co.; 3960 Duncan Ave., St.' Louis 7069 Fairdale,.Dallas,-Texas.' - -''- ' .?>-- 10. and e415l Toenges Ave., St*. Louis 16, .Mo. . . ALLONIER,: Howard R. * (A ` 1936) Dist. -Mgr/.-: ' AIKIN, Azlel A. (if 1945) Plant Engr.; & Design ' J. J. Nesbitt.' Inc,, 101 N. High St., Columbus - - Supvsr.. Oldsmoblle, Lansing 21. .and Maple-. 15, and R. D. No.-L Powell. Ohio. - - ... v.^wood-Manor, Lansing, Mich. ' - v ' .- :ALLSOP,* Rowland P. (A.1940; j. 1934), Cons'./ : > AIKIN; "Frank. W. ,(A T945) Pres.. Northern Engr., 1221- Bay: St., Ton3nto, .ahd^ Stop.;21r , . Controlled-Heat-Co.,' Inc., 557 Factory Square, Kingston.Rd., Scarboro.Bluffs', Ont.', Canada. -' -/ - - "Watertown, and-126 Ward St;, Watertown, N/Y.,. AINSWORTH,..Samuel E. (A' 1939) Partner,. Rdche/Newtoh& Co.,.-Box 1049, and 1524^25th SL, Lubbock, Texas.; ' -"/ \ AITKEN, MUton L; (M1945) Gen; Mgr., Propel- lair; Inc., Springfield,' and 99 S; Broadmoor ,, :Blvd;,..S:, Sphngfield, Ohio.'* - / - ' . -- AKERLOW, R. W. (A;-1944)-Sales Engr;. The'' - ALMERT, Harold (A 1944) Cons. Engr., *1605. . York'Ave., and .519.-East 86th St.v-Apt.76-B.; ' 7.. New York-28, N: Y. :/*' ALT, Harold. L> .(if 1913) Basic Meet Design. ' .Engr., Voorhees.' Walker. -Foley & -.Smith, '101/ ' ' Park Ave:,' New ` York, and 115-27--225th/St.7,y .* St: Albans 11, N. Y. : - . -' . . '-,, '-.y.' -' - -is,:-Stearns-/Roger?. Manufacturing-- Co.,.1720 Cali-* ALTEMUELLER,.* George' (A- 1940)- Asst.- .>\ - * fomiaj.'SCr^Denyer, /and 935.. S. /Elizabeth 'St.., . > Denver.-Gold/* - - \ -. Utility Officer, .Veterans Administration Facility,-.-r'and eR. F; ;D. 1, - MiddleviUe -Rd.', 'Northport, r <-AKERS, .George .W. (if. 1929)/Mgr,, Engrg. .&: .-L;I..N. Yv x '. - > . Sales,''George-.W. 'Akers Co.; 16525 Woodward. : ALVAREZ,/Joaquin'. (A 1946; / 1942) -Cply <. Ave.T-Detrdit'3, and. 1530-Seward-Ave., Detroit ; U.' S. A. 34968996, *U. S. Strafegic;-'Bombmg. 6"Mich;'-;}~:; / v. / Survey, .Army./Hall,- City .-College,,-and .1560 ~ AL BERTf,William'J: (A 1945) Engr. & Estimator. ..Amsterdam Ave.. New -York,-N/Y-7 '- 'Buens6d-Sta<^y.',Inc., -1001 :N.' Church St.r. Char- J ALYEA; Harold W.-(Af 1944),Deaffi and?Dvlpt/ -- /- ' lotte.N.'C.T and *665 Randolph Str, Camden,'N.-J..'- ' /' Engr,, Johnson- Sendee C6.,y607 E.' Michigan - y/-T?-*. AL BRIGHT, C.-B:.(A 1945) Director, Industrial . - St..- Milwaukee. ..and 919: Arcadian Ave.,:'Wau- '<*% Services Assocs.',120 Lberty.St..,New York 6;.and -' -kesha;-Wis';--- / - ' ' - - - - .7. ; . . ' . _ ' Mti.'Kisco;-N.vY.-. \v: `' AMBROSE, Alfred H..(J 1943 ; 5 1941) A. R.-T. . ALEXANDER;- Granville P. (if-. 1944): Secy., 3/c U.'-S.` Naval Reserve. and 18'Linden Sti,. < Heating;:Piping &'Air Conditioning-Contractors K Philadelphia Assn;,' 328 Chestnut'SC; Philadelphia 6, andMontgomery Court,Apt. J-33,Narberth, Pa. ` ALEXANDER,' HughiV.i (if 1943) -Branch Mgr., ^ Johtraoh'-'.Service Co.t -.922 -Architects.. Bldg.,.. IndiahapoIis 4, and 5700;Kingsley Dr., Indianapo-^ ' hs'S.^Ind.-,-''^I ^ - ALEXANDER,:John L. (A. 1944fMfr8'. Agent,. 2746`Elmwood Dr., S.E.yGrand Rapids 6, Mich.. 1 ALEXANDER;-John-W.': (if 1945)-Dedgn Engr.. -Woodstock,. Vt, ' . Y-.: : -.7 ; AMBROSE,'E. R: (Af 1940) Air Cond; Engr..; --, American . Gas, Electric - Service Corp.,. 30 - .Church.St:,-New/York;.Nv -Y., and 153 Lincoln.1.- . Ave.; E., Roselle Park,- N:J' AMMERMAN^/A;- S., Jr.'. (M:'I944V A1941;.` J .1937) Dist. MgT.,r*.Aeronh Corp., lll.'W.. Washingtbn .St;. -Chicago- 2,- and-132 'N: Wolf . RdT. DesPlaines, 111. j. -/'/ ^~7 .. . v .-r-- Office/of. the SupdSnsihg- Architect, --Public ; AMMERMAN, Charles, R.-'(Af -4916). Pres.. ., - BuUdih^.Adniinistration, 'Washington=25>'D. C., . Ammerman, Davis & Stout, Inc., 805-9 K. of P.7- H ^ . . and'403.Prince:George St.r LaureL Mdl . / Bldg.; and 4916 Rockwood Ave.% Indianapolis, Ind. 1 ALEXANDER,' Keith';OU(if 1943) Sales Engr.. AMUNDSON, Carl H; (Af 1944);Product Applica- -t Neil'H. 'iPetersqh' C6., \1129* Folsom St.. San ..tion Engr., Herman Nel3on.Corp.: 759 N. Mil- - ^y^ . Franciscd'3, rahd-454'Mastick Ave.,' San:Bruno, ..waukee/ Milwaukee .11,; and 2324' E. Pafkj;Ply - Mg;J,Vs. r Calif;`<....^-c^.V.:A ALEXANDER, Sdmiid W. (if 1935) "V .. Pres.; S. W.. . - 'Milwaukee'2;-Wis.! /. .-'-v -. ANDEREGG. R. H..(Af 1920) Vice-Pres. & Chief// ^.yrATexaiid&> Goy-rLtd;,-; l&2yMain :SL, .and.* 124 - Engr^ The Trane -Co., and *450 Losey cty - |pg5% VK> KingsmoiinrPark-'Rd:;Torohtb.vOnt..'Ganada;-. *. T - La' Crosse/Wis."/'' /Tv /.-._ --- 7/'. ': < ALFfcRY;.'H5iry-F;: (M:i938)-.Gen./M^:/; Erie. /ANDERSON;. Carl-G; ^ (M.4942) /Chief.lEngr.. ^ ^ '''A,? f'y^ - Mandfacturihg.Go7;300 N..Ejghth St--, . Milwaukee ^.3,^and'*^I9(5W-;"Center^Stv Milwaukee 6,..WLs. * . Chicago' Metal .Hose' Corp., 840 Ni State Sty ^ and 50 N; Edison St., Elgin, 111. '; -/, ' .Roll of Membership ANDERSON,-Carl O. (M 1944) Htg. .&'Vent. , APPLEGATE,-Francis R.' (A'1944) Plant Service, . / Engr.; Board of Education. Rm.:536/228~N: La/.. . .Engr., Pratt &.-Whitney Aircraft Corp;-of Mo., - .. ri, in. - -, : / -' 4- - --SalleSt.V.Chicago l, and *900N. RusifSt.; Chicago"* and *5129 Wornall Ave., Kansas City, Kans. APT, Sanford R.;(M 1935)'Mech.-Engr^ Parsons; -. - ANDERSON, Carroll S. (Af 1920) Dist., Mgr/, Bririckerhoff,.'Hogari.&'Macdonald, 142-Maiden American Blower -Corp.; ` 1105 Architects Bldg.,- *- Lane. New York 7; and * 36-39-205th Str, Bayside, -- Los Angeles 13,land 4267 Holly Knoll Dr./HoUy- . L. I.; N. Y/ - '. / ' wood 27. Calif. . . - -- - ARCHAMBAULT,. Joseph A. (A 1939) Branch - ANDERSON, David B..(A 1939; J-1936; 5.1933) ` Sales/Office Mgf., *C; A:-Dunham Co., Ltd:,. 22 : ,Lt..- U. S.-N. Rl, Naval: Ordnance1 Laboratory, ' Wellington St.,' N.',' Rm. 17, and 55A-Coundl St., '- Navy-Yard, Washington, D. C;, and 1999-Pine- : ' Sherbrooke, Que., Canada. ' '-- 1 hurst Ave., St. Paul'5; Minn. - . - . ARCHER, David. M. (M 1934) Sales Repr..-' : ANDERSON, Edwin C. (A 1944) Owner, Edwin Sarco Co., Inc., 143-Federal St., Boston 10, and * - ' C/'Andcrson- Co.. 1863 Wazee St., Denver 2, and " 10 Harding Ave.,.Braintree, Mass/ ; J 1623 Adams SL.'Detiver 6, Cold.-' ~ / - ", ARCHER, William J/. (M T945) Engr., Howes -. ANDERSON; Edwin J. (A 1939) Mfrs. Agent;. & Whitaker, 626 Russ Bldg., and 1443 Funston -, / Chicago Pump Co., 14. Smith Sti, Detroit 2,7 ' Ave.,San Francisco. Calif. '' -and-274 Lenox; Detroit 15,-Mich. "-' . ARENBERG, MUton K. (A'1920) Pres., Robert r ANDERSON, Edwin L. (Af. 1941) Cons.-Engr.. 'Barclay, Inc^ 122'N./Peoria St.. Chicago, and - ' ' 63 Oakridge'Rd/, Verona, N.-J. . ' ... r '/ 1416-Wildwbod'Lane. Highland Park.111. -' v- ANDERSON, Einar (A 1940) Sales Engry Vulcan: ARGUE; Edgar J. (A/1935)-Sales Engr., Anthes..^ / / -Iron'Works; Ltd., Sutherland and Maple St/ and. /_. Foundry, -Ltd.,.''Saskatchewan: Ave.,' and 773.-: - v * ' 152 Bannerman Ave., Winnipeg; Mari/, Canadar. McMillan Ave:. Winnipeg- Man.'/ Canada . ANDERSON, George; A. Mi (A 1939; J-1936) ARMBRUSTER, Frank T. W. (M 1936)-Service . Pres., King Ventilating Co., Owatonna,- arid 717"7 .Engr.', American Radiator.& Standard Sanitary- . S. Cedar. Owatorina, Minn. - '' 7 - Corp., 73' E. -Naghteo -St.; Columbus;-and 105 ANDERSON,. GranWlle- W.' . (A -1943) . Service /First'Ave;.^'Waverly,.Ohio. -. Engr., Kopp<ers Coal-Division, 12,17. Ford. Bldg.,- ARMISTEAD, William C. (M 1937) Sales Engr.; . -Detroit 26, and5096'B'urris Ave.,-Detroit 13, Mich. ` . 153 Second'Ave.,'N.,'NashviUe 3, and Granny : ' /ANDERSON,.Harvey`E, (A 1944) -Secy., *Naro- ' White Pike, NashviUe. Tenn. - - ' - - -- wetz Heating.&-Ventilating Co.,*1722 Washington ' ARMSPACH, Otto W. (M 1919) Dist.-Chief - -/Blvd.. Chicago 12, arid 460 Fair Ave, Elirihurst. IU. Engr., Carrier Corp., 405 Lexington' Ave.-, ' New ~ ANDERSON, John. W. (A 1944: 7-1937) .Design .York 17j_and'* N. 2. Stratford Rd., Scarsdale, N.Y: - * ' Engr.; .-Titetlex, Inc.;-)0' Freunghuyseri Ave^' ' ARMSTRONG, Charles E. (M 1939) ' (hief ` Newark, and 201Ayliffe Ave.yWestfield, N. -J.' Engr.,.Armstrong Heat .Control Co.,- 523 S F . ANDERSON, .-.Nathan' ' B.` ;(A--4945) Owner,. 7' . 39th - Ave.,'and 624'N.E. Hazelferri PL:, Port- 'Temperature Equipment. SriErigUMemigGo.';. 620 ; ---larid'15.-Ore. " / ' ` .Walker,.ahd .Ben Milari Hotel,' Houston; Texas. < -ARMSTRONG, Walter J. (M-1938) Cons. Engr r-- . ANDERSON; Robert . By (A 1944)' Htg. Conti/ ; --*1010 St. Catherine'St.; W., Montreal.'and 15- - 4210 West Byers, arid 853 Ogden; Denver,-Colo. WiUow Ave.; Westmount, Que., Canada .' . / . ANDERSON, Robert -V. (A 1945) Div. Engr., ARNDT,. Heinrich'W; (A` 1944) Owner. *The . / Lennox Furnace Co., Inc.,-400'N.*Midler Ave., Hobby Shop/Masonic Bldg. Lobby No. 2; and : 'Syracuse. N. Y., and 11 E..Sedgwick St., Sand: . 2007 Central Ave., Augusta. Ga_ . ' ston/.Va; '. . - -- : : - - .- ARNOLD, Richard S. (M1944) Asst. Chief Engr-. ''ANDERSON;' Sydney, Jr. (A 1943): Dist.. Engr.. Camer-Corp.,.300 Ivy St.; N.E., Atlanta-3,' and" " Chrysler Airtemp Sales Corp., :925- Bowen "2195 E/Lake Rd..-Atlanta, Ga. ` V - Bldg., Washington-5, D. C,, and-8503.Irvington . ARNOLD,.Roberts: (M 1944;^A 1926; J 1922) - V 'Ave.,`Bethesda 14,'Md; - ' /'-.' : Owner, .Robert Arnold Sales & Engineering Co.. -.- ANDERSON,- William S., Jr.' {M 1945) Partner, : . Az'eman-Andersdn Assocs..: 233/ West-. St.,- and ' ..913.Otis BIdg.,/Philadelphia2, and Sherwood - . v Lane. Wallirigfbrd/Pa.' . -n. *1332 Sheridan St.-, Williamsport, Pa;' .v . - ANDREWS. William G. (A 1941) Branch Mgr/. : : Wholesale-Refrigerating. Jobbers;'1513-Camden : Rd.. Charlotte. N. C., arid 2232 N.W. Second SL, . Miarni. Fla. ; - 1 - ' / ;/ . //f ; _- ANDREWS, W..M. (Jf'1941) Partner; , Lockwood' -- ARNOLD,.Thomas L. (4. 1945) Mgr;,-*Vulcan . Radiator Co:, 26 Francis Ave/ Hartford 6, and 5- Beverly.Rd., West Hartford 7. Conn. . * ... ARONSON, Henry-H. (A-1939KEngr,,'-Premier ..Furnace Co;, and*Box221, DowagTac.-Mich: -v> &jAndrews, 904:Uriiori-National Bank Bldg;.:and-. ARROWSMITH,. J6hn O: <M 1934). Asst/ Supt , < 2333 Sunset/Houston;.Texas. ' r - --: - - of Works/* Canadian Kodak Co., Ltd.) 9-Humber--7 . ANDREWS, .William"R/ (if 1942) AssU/ Mgr., ' view Rd/!Toronto9.-OntV, Canada.,7 ; . r f~- .Ross Engineering-of Canada!-'Ltrfy Rm ,920, ARTHUR, John M,, Jr. (M 1923)/Div. Mgr , ~ Dominiori Square BIdg.. and'3770`Cote St. Cath-: " Lighting-Steam' -& Coriunerdal Service .'Div.. - r - r .erme Rd/Montreal,'P/Q./Cariada.-/'7 - .Kansas City Power & Light Co.,* 1330' Baltimore 1 -- ' ANGELL,-Lawrence D./(M.1944) Minneapolis-- / Ave.; . Kansas City 10. Mo., and 3311- State-Ave.; - - ~ - Honeywell' Regulator Co;, "New- York,carid *450.' Kansas; City,'Kans.. .. s - East-16th'St:;-Brooklyri, N..Y: :-1--' ' - - .< . ARTKAN,. Carlyle (A 1945) Engr., General Air- ' /ANGELO, Herbert G.: (A 1944).-Htg. &.-Vent., - . Conditioning - Corp:, 911 East/.59th -SC. Los 4805 -i Washington,' Denver. -46y'and 1225- East Angeles 1, and *2323 St. George SL, Los-Angeles-'' ' 44th Ave/, Apt. 28, -Denver, Colo. : *... - 26, Calif. . - . / 7 -* ANGERMEYER, .Albert iH. /(A 1936) Owner, . ARVIDSON,. ErnMt R. (M/1943) 305 W . Plumbirig & Heating/119 N/Coriimerdal/St., 1 Sheridan Ave., .Shenandoah/ Iowa.' / -.* >.. / arid-245 WebsterSt.,-Neehah, Wis. -. -a 7- ' ARZET, Fred A. (A .1944)' Mech.*Erigr.y Argonaut &--l- ANGUS,. Frank.M. (M 1937) - Texas'Refriger- , Realty- Div:;- General /Motors ' Corp.,'. Research . atioa &/Engineeririg Co/ 510 - Magnolia Bldg., - Bldg.,- Detroit, arid *25632 Annapolis,/ Ink-- Dallas l/*ahd 6033 Victor/Dallas,-Texas; sterr Mich;. ' . ; /: . ANGUS. Harry H.* (M 1918)f:(Coundt 1927-29) ASH, Norman B, (A/I945)'. Pres/' Braniff :Engi- :. ^ Cons.- Engr.,'1221.-Bay'.SL/ and e34-.Fariiham , neering ..Co., ,817 N. Broadway,-Oklahoma City, - - . - - Avp//Toronto. Ont_-, Canada:/ . -- /' - and'Britton, Okla/ . v ' - " - -' ANOFF, Seymour" M/ (7 -1940) Cons... Engr/. ASH,:Robert S. (A .4943; -J .1940) Lt/ S (E) v -/ 5048 Marine Dr.,/-Apt.'-A-5;'Chicago-40,-I1I.7-'. ANSPACHER, T. H. (M 1939; 7 ,1936). Dist; - 7Mgr./Buffalo Forge /Co;, - Tower. -Petrolemri, ' /Bldg., Dallas 1. and v4512 Arcady.St:; Dallas, -Tex. : ANTHES. Lawrence L..(A 1935)-Prei, Imperial- ' . ;Irori, Corp.;' Ltdr> -.30.7Jefferson/ Ave.', . and 119 - '- Dowling Ave./Toronto, Ont:, Canada.- -. /.U, S.;N: R.,'Industrial Dept., Navy Yard.'-'Mare - Island,'- Calif.,' and 432/Wisconsin Ave./ Oak ' Park, IU. : j' ASHCRAFT, J. Phillip (A: 1943) `Branch Mgr - - , Minneapolis-HoneyweU '/Regulator' ` Co.r 1907 4 -- - . Federal/St/'Dallas; 1, -and,*2826 Fondren ,Dr , - DaUas 5 -^'exas ' - ` - *^ - * --- . * - ASHLEY, Carlyle M-. (Af 1931)! (Coundi:'i943- . ANWAY/H.WUbur (M4943) Rramrch PhysidsL : 45) Dir/of Dvlpt/; Carrier Corp.,1300 S. Geddes ..* :*Wood^Conversion. Co.y/Archv St., "and,,1012.": ;vSt/.S>racuse 1, and-22 -Lynacres -Bivd-. Fayette- y Prospect Ave^ Cloquet, Minn'..r'- 7/7, ` viUe/N.Y..' ' ^ APPELT. Joseph E. (M l945) Mgr.; The .Trane ASHLEY, ;Edward. E/'(M! 1912)7Cons Engr ' t . Co^7l200 .Godfrey/ S:W.;7.Grand-' Rapids, arid. TO .East- 40th' Sti;. New. York" 16, N-. Y-i -and - >* Green Ridge Dr., R.:R. 1/Comstock Park, Mich. / Noroion Heights. Gorin. '-///.' -U-. -*1-J' I V ' -T Vt ^ 4SS^ Zzfyti&etQ**-0?' %C ASHLEY^Rbriald.D;(A/,1944>iPaitiierr*United^BAILEYV:Cliarl^s' F:^C7-1939)r!Newp6rt.,Newb .. t^-Z^4 .>Eqmpmeht~Co;. e337.:S,v High': St.;4 .1Gbljrabus,115,'/;r'.Shipbuilding' '&*prydockf.GoX-Newport. News + - + JsfeT 'and l41S. Southampton Avel><Columbus 4hGhio;2V,"''ahd-e Windsor. Var;:.:"k;'-':- S:\. ~>7'. ~ ASHTON; Jed Ly(A-1944) Owtier.''Asht6n:Heatihg -: ,.' BAILEY; ~~Frederick:; A., X Jr: (A~ 1939)_ Prop j ~ * . -& Air,'Conditiohiiigi ;i63: M6t6f' A're'.`,-.Salt'Lake Bailey's,' 130r:Kihg.'St.'ii Charleston-.^; and 70- % City.0l-,,-and>2686 .Aldeh-Stl.'vSalG;Lake^Citv - WarrenSt-rCKarleston;\S:C. -a.-~ stsSfi >'6HJtah;. BAniEY.M^I^^lWJ.'Asst;Chief Engr^eParks ,, Ijb< ;^ATHER'ix>N~~iL-"Xlfred.-E~.'>` ('A`"' 1937)\:Dir.;,,*'A7?iE-'. .. Cramer Go.*,, Box; 946.-and: 17051 Fountain -View i1-Atherton :& S0113 -Pty.7.7Ltd., o83v.Latrbbe< St.7- . Ave...Gharlotte, 'N.lG;; .'-v-. ./ '.'v i :3 Melbbumel-Victoria. and-129:Esplande;'Elwood, :BAIN.v'LisreDce--;P.5:(Ar-il944)-'^onstr;^Sbt*:^^:;%M^S^ ;A-Vic./Australia. IT,'-'' ' Naroweti -Heating f& .Ventilating'Coi,. 1722; V/V' ^ ATHERTON; Russell C. (M 1945)/Engr..M.\ J;\ Washmgtoa'lBlvd.,and *3324 N. LaramieAve.-r c v-ADaly:& Sdns,.Inc.; 541 Bank St.;Waterburyrand' Chicago. siX 74 Es3exfAve'i;.Waterbury.64,.Conn.-. c BAIRD; AIcand'-I>.7G^04:yl944) Eret; e`A V > v**ViATKINS, "George E7 <M,1941);Cons.:Engr.'; :1308;. ... Baird; Ltd./286=Lisgar.St.C.Toronto, Ont. Canada. -r 'S-Xrirx- ^--'- Hbbart *'BIdg.'. - San Francisco.^; and e.64 f,Oak - BAIRDilFlbyd/E;-.- (JJvi940)r Owner.-eSales'liSt'^ ^7SB-3?S Ridge Rd.^Berlreley;Calif.: -' , iEngrg.. -314 .PalfTi'er~ Bldg.V.-Atlanta 3;;and;900-; 11 kXXX \r.?>r ' IrATKLNS.LThomas J: (Ma945)?Electrosta A i 'Church"St.yMaHetta.,:Ga.rV--?.,/ jfS'I "^."'.Cleanihg'vEngr.. WesUnghouse.'.ElectrK;; Corp.,, BAEER.-aydeH.(Mr1945)..Htg.;-.Veht/&'Pibgl mfM * ^PhUadelpHia-and * 270'Hwdey^Rd^ Philadelphia Engr., Snyder;& 'McLean,'.221'4-Penobscot -. Detroltrande 15444 Vaughan St.-; I5etr6it23, Mich. HarTy A (A^fl9^'nhief-.Engr:.:'. BAKER.VDonald:- IT.*?(AT:1940f* Engr;.- Service^ pp||e ,>Cbmbus^n^^^)ment,Co.',*`182p;QieirySi-'; and ses* -i rt) .AU6S4T1n1W^,-et,sWt6il7lltahmS>t.H,:K;-7a(iiAs/a1s9e4it3y;;;-JMMb9;4. 0..;'.}5:ly..3. 7).. /-Dvlptf*Ehgri.te United^ American'Soda^Fountain -Corp":.-101 tWalidutVSt:VWatertowhl.72.)_and=i09o Dept., ';Garrier-/Corpr,\;ahdv* 200V; Euclid " AVe '." t- Syracuse' lOrN^Y;/- *vV-i f.!7 'BARERTrEdwarti^Lv (A:7l945) .;MgrV Biirbidge ;.-Coal,Co.y311:S.Main; Salt'Lake City ljand;1533 ? Glen Arbor^Salt Lake Gity 5, Utahr,> '. ' " '-v' ^?^ llll ' HydejPark'Ave^Hyde Park 36,vM&s..^r -- } .BAEER/^HarlandFE^CA^lMf^/^p45)'; Partner, ' :Baker;&:English,11360 W.;Ninth-StV^and 3786< f -. Freemdht'Rd^.Sduth Euclid:21vOhio.-,.^y ;BAKERyHarold S. (A 1937) Sales Engr.. Westing-; ;r house--Electric-Cb./ Sah Frandscd, Hahd * Rt.-2.-' _ __- -- - - .... - ,. TM^^_5^^^v%yHdghts"yClevelaiid:22,'Ohi6iil;^irji;''ir:_. ' 74 t 'tAXEMANt^'JaineO/E.--; (Jf-?'i932;;AJ;-1931;VJ'v>l925) ^ ?VAxeman-Anderaon"Assocs.'S 233-sWe8t^Stc.. tWJr.^ ,vliajnflport 3-"and. 1328 WoodmontrAve:;-Williams-. BAKER,HHeriry;ftA.i.'(Af-a945)i%ace-Eri:..xW ^B 'Connor.Engineering Corp,,"l 14 East 32hd St New ^ -jSfe a6-?* ^ ii;-2Z5s - - v L po Pa i* ,, 4 - AXTHELM-.C;Fred 1 Gi- (A 1915)>.5rFr6ht4Rank`- >eFurnace Cd-l..'and 648:N: Foresf.Ave.,. Webster } Ydrk.4.ana:i45^3U7UivRd.7<Whitestohe>N~Y i ,*BAKER/.' Howard-VC;/1945)'VGilbert As- - . ^ sodates,'Jric.r412.Washington St:: Reading Pa _ --BAKER,-,T.*Cr (Jf:! 1921)*\Vic*Prea.`/e Chrysler ' t ivte* i v\ WfrK: ''G"19Mo - - ; Corp;;-.Airtemp .Diy... 1119r Lj;.iSt:.^.Daytonyi;i- --- > ? : and'252 Ei'.Monteray. Ave.,;Daytdn 9,-Ohio " .BABcERV?James:(Jf/1944)'.Owner,k,:Ross-&-'Greig . ........ ... S BAAK. W: J/^(A; 1944) Moduflow-Zone:Supvsr.;^ CT * Mmneapohs-Honeywcll. Regulator t.Co., _. 433 .E:V ErieyStl, 7aiMi:'7737 Nv cEastlLake T race . ^ ^*;yy-BAANGeorge'rBf,(A :1945)llpiant-i Engrr, . Hat^ : -Rcgistehed.'-738rNbtre:Dame St..'.VV.,;and *571o Darlington AveivMontreal.0Que:,'Canada.!- r, BAKER;'L.tPi\(A .1945)'Ass,t.:Trader&'Industrial:: * Gommissionerye Province;.;of \Ontario. ~``Ontan6:- , 'Hou^.'t^ lSyCharles :vl 1 /-Stii/ Ldndoh^ S W 1 s-'-^.-j^/fCbfppratiba^fbf^/uiieSica.JSduth rNorwaltr-and*' -BA^ER*!Rol^dH^(M,-1928; A/1924);*Captain.1* , 5" Glover-Ave.,--NdrwaIk^:Conh.v."' %7' - Uj*S:-N-.'; RiT:Ih"dustrial;Mahagef7;U.. S.\N.. .Navy.v L V1 > VBABCOCK, 1Dan '(M 1945)'-Plant-Engr..;AUison: Nb.> 116,' c/o-Fleet^Post Office,' NewlYork. N. -Y.- f v: pivr^Geheril'VMbtmsYiGdrpTi'xIhdianapolis.^and^ BAKER;^Thbmaa-.(M ;1938).: Chief Engr:. ;Con-_. ,((.>;65lYRiverview:Dr.,:Ihdiahapolis"5 ^Ind : 3?51'^* V<BABCO<3R0PS"li;R^-(^tl94l) >Cons.vEngr. .'i- ^ fi-VMi:Rim'nTinTi??625/Marketc.SL:i San-Frandscc :New- York'.-N:.Y:^;."-'.;y^Ay / Lg BAKER; -TftA.: :(M:.1942)?s Vi^PfaCBalSb':._. ,, Specialty'& SuppIy Co/; 7pi-vErier-'AveM^and-220o *j> . E-VBrbadway.-^Loganspbrt, ;Ind. . ,,* BAKER;,Willlam;H.,"Jr?.(A^1935)'AMty^Mgr.. :> Pittsbiirgh'-Sales ;Offic;:American. Ra<iiator-:&- -Standard'SahitaryrGbrpTv'PyO^ -Box 11226, Pitts `' burgh' ari< *^1 *M"~*1' Dei^:D;*oK..ir,Kvid-,- ; BAKKE, -.:44th7AVe..___ ______ ^---------- ....--_ BAKKO, Rueben:(A;1944)> Beverly";Dairies/230 - W.'Jeffersbh St./Los AngelesT Calif.r: BALCH,^.Robert :.M*` Jr/^(AA 1944).iSalessMgT , 3 s. - Apartmentf.GontroIs -DiV.^.MInheapolisfHoney- - *&pf ^^^i-fe^-^Kcand,d655;HiIlcrest'.AVe.^St:>Raul:5n;Minn.^ BACdN^WUUdmxH;/-Jrh(A vi942): ;Autom Wotr"Ac^ofAH:-r)i <Ca: -Bav :-.well.RegiUatbr.Co:,'.and.402..W-. Minnehaha Parky-s " ^ : way.-.MirineapoliSr^Minn.ft -BALDWINKCharlearWr-(A-*;1?45) ;YentV#Enr <<y-. U" S.rRiibbCT.\Co//1230^Sixth'fAye.v-.New;York,'rv1-''rt-" BALLA^TYl^r'GerfieiLy'<A>1936) Mgr'.'.Htg.. BARRY, Wilfred W. (A -1945):Supra-I,'* Barry ' >.-Dept.;-e Crane,y-Etd.^ rllTO ^Beaver. Hall \Sq.-. -i -'Sheet-.Metal.C6:', Ltd:; 10171^98tH3tC-'and:'10132 - - ^Montreal/ andL14PrBallantyhe Ave.. S.: Montreal - * 142 St;V Edmonton. Alta.ilCanadal V'- ;.- .~ .--'West.^Que..:;Ganada. ^ ' - *. ^. BARTfcES,;liarleS'"J;'7(M`-1942)-'.Owner,.Auto-'-'> BALEMAN, WllllamH.-{it-1937)-Plant'Mgr; ^matic Stokerl& Erigineering Co., 207-S.Richardson ' CanningIr'Div.,* Wm.'; P.vi -McDonald Corp.. - / Auburhdale.- ahd Davehport; Fla.: -: -, v. .Bldg.T and?1416'.Washihgtbn!Ave.y.-Parksburg,`,a 4 W Va. ' :v >v-y. V. ir --BALSAM;"CharIes'- P.' (M-. 1932) Gen: -Mgr.:, BARTELS,--Everett M:.(A-.1941;'/Jl939):Sup\^r' " *%.: ^ . .*# NationalIHome;Equipment .Co.. 50 Church-St.:- . of -Mech;.Equip:;--Independent-ScH6ol_.Distnct,' - -- New York 7. and'324-Foufth St:. Brooklyn.-N. Y. - 629 Third St;;'amd?e 1104 E.' Douglas,-Des-Mdmes, nK ^ .-BAMOND;Maimd;J;V(Af. 1942)'Engr.. Barber- T Iowa.--r ; >-i- u -i I-' .y . Colmah ;Cor, 221N. -LaSaUe.St;. Chicago/ and"'-. -BARTH,";:Herbert.--E.V'-(M1920)--,,Vice^Pres-'. - v 5859-Winthrop Ave., Chicago, 111. -5 . : American Blower Corp-.-P. O^Box 58/R669eveit . VV-% -lv . .. -i-BANOWSKY/ Aubra B_.l (Af^l938)' Mgr.i ;Retail .Bevington-Taggart & Fowler,:'730,KofP;Bldg:iy 4' w Div.ilPayne Fumace Co., P..O:*Bbx 990,.Beverly .-' "IndianapbUsVjIhd. V : V''-`V .T -'Jr-*1H1:i1ll1s;' ia-_n_di,:oncii-:e1/-'-l.^-j1;_-_'A'._____' . f -ii. A"--___1__I ' D 1 DTAM^ li.,; / 1/.' 1 ivm' -.DX^ . -34 Calif.'s BARAGAI Engr.-,; ;-:Spokaiie 5 BARBER; .:'-RusseU-'< BARBIE! _Field!C:'_________ _______________________ _ ____ . ____ , . ,, .. _______ . . -.*-Manhattan' BHdge-^ Piaza,-; Brooklyn,' and 2237.. - 3055 RaIsto'n Aye:,- Indianapolis,'-Ind.^'^y-I-i........ . .. Belihont-AVe.V New^York. N/Y:. \ '!*'' ; BASHAK,-rCihat `(y . l943)' * Istanbul .-Turkey / ( -BARKERi M. Stanley (A-.1943) AppIicatidn'Engf.,.: SASSEVITCH,vAbraIiam (A 1945) DesighvEhgr 7 S ' CarTter--Corp./122- F-*-* .KtVn.V^U Clmnnfe'-lnn,1Al Darb-A.n' MAJI.Va.I.'-'.-C '^ll 1^3275th*Ave... BXREOWi'F.- JoHri?(___ ___________ ....... ... ........ ____ ______ .____________ ---Engr.,' Western C6ndensing Co.V935 E.v-Jbhh St., .- ;".'T& Geh;'Mgrl-.':.Bunihani-Boiief.Corp.;,"IiTrington, *>: .'and 1515'N.- Durkee St..:Appletbn. Wis.- H;-i-and< 55Burhside:Dr.,:Hasting3-oh-Hudsbn O.^N.Y.^ > BARNARD,^Miv Everett - (A ;i936)~Sales Engr.,;. ^BASTEPOi Geci^e R.' (A-1942; ^I937V Lt:^G g ) - ' Camer'Corp;rl2'South-12th St.f Philadelphia ?,'1; .- N.-_RIi- and 102-36"86th'-Rd:,--Richmond-" , uatiw, vvuu *, iu.'O; nruiy, ..Tdrace/Karisas City,- Mo.' ......... _ _ ... . and *1313 ;W."Lehigh, Philadelphia,-Pa!.-f : :i-r 7c f _ . BARNES;;Chafles A. (M-1944) Engr:; E-G Sheet- '..BATTAN;`::Si;!W^(Jf--(T940) -Eiigr.) eiBattan's' , , i ' v -. ' Metal Works; 258 Pryor St, SlW., and 947-,Kather- ,9^Pennsylvania^Ave.;t;Avondale.-`'and<Keiinettv' ^ ? ^ '. Jwood'Dr/SlW.-. Atlanta, Ga7;: ::-i _ v---1Square,-R.,D:, Pal';",.''A* / - ^BARNES.'Hugb Six(7 1940) Major.vU.;S.:Army,' BAUER,;Albert'E. (M 1935):Mgr;.r Speer Prod * " - '*vand-e,23 MasticktSt-.;- Savannah.:Ga7;-.'-:V. ~ Diy.,tStainlfT9S'8e.Steei Products Cbr.' lOOO`Berry ^ ^ DATr-ci I-U-T' -/t'.inff). -.,v, * v St.'.-'and # 3995 Ni Stratford. RdAtlanta;- Ga: BARNES^Raym6ndvW?;(Af.^l939)?Cons.: Fngr Bauin&B6llesl415LexihgtonAve.';New.York 17,J ina-600 West lllth SK New York 25;-jNr.Y:.=l` 1* ^ **& A2\. ^Heating: Veniilatihg ~]Air Conditioning - Guide 1946 BAZILLE, .Clarence II. (M 1944) Mgr.. .Htc.' . BEERY,' Clinton E-* (M 1936). Pres., Heat &* .-Dept-', Harry Lee Plumbing &.Heating, 216 Gab- . -Fuel 'Engineering ..Go., Inc;, ,1454 -Hood Ave., fomla Dr;, Burlingame,'' and 835 Turk-St-i..San ; Chicago;Tll'; ' . ' T .* Francisco 1,'Calif.- ; ` _'--.*' - BEERY, Vernon L. (A 1944) Sales Engr.,-Hearing . BAZZONI, .Joseph P. (A 1942) Mech. ..Engr.,' . & .Ventilating, and Lake Deltoh; Wis.. ' - Goodyear. Aircraft Corp.,* Plant B,-' Dept.'110, ' . BEGGS, William E. (M 1927)yOwner,.W. E. \ Akron, Ohio, and R: 2, Ottawa, III. ' . . .- Beggs Co.,' 234 Ninth Ave. N.; .and 2580> W. BEACH, Albert F., Jr.'-(Af 1944) Application * : Viewpoint Way, Seattle, .Wash:"- . . . -Engr., Carrier Corp., 405 Lexington Ave., New, BEGOON, George F.:*CA. 1945) Mgr.,. Elec. Air York. N. Y., and *214. Columbia Ave.,- Cran^ Cleaning Div.,' - Therinii Engineering Co., First ; ford. N. j; - . National Bank Bldg., Greenwich. Conn. . BEACH, Ralph L. (Af 1942) Disri Engr.-York ; BEIGHEL, H. A. (A .1927) Owner, Allegheny ' Corp., 412 Houston St. N.E..- P. O. Box-2210. En^heering Co., 503 Columbia Bldg.,'Pittsburgh, Atlanta, and 131 Clarion Ave, Decatur.Ga. ' - and 207 Puritan Rd:; Rosslyn Farms, Carnegie,- Pa. - BEACH; Walter. R. (A 1936) Field Engr.,' Gates. ,-BEIRN, John B. (A 1945) Sales Engr.,-American ' - ' Rubber.v.Co., 2240 E. Washington Blvd.,.;Los Radiator. & Standard Sanitary Corp., Pittsburgh;- . - .-Angeles'21; and 5332 Appian Way, Long Beach Pa;, and 67 Texel Dr., Springfield.8, Mass. 3; Calif. - ' ^ . BEISEL, Karl E. (J 1944) Asso.. Naval Archt.,. BEAGHEN;, George W.-(A 1944) Field Engr.; .Vent. Sect.,--Norfolk Navy Yard, Hull'and Aero - American Blower Corp., 50 West,40th St'.; New.- Drafting Office, and *813 Western Branch Blvd., . York 18, and 3044 Park Dr., Pelham Manor.'N. Y. Green Acrcs.-Portsmbuth.-Var ''*.. -*BEAIRD,--Benjamln J. (Af 1945) Chief Engr. and I ' BEITZELL', Albert E; (A 1933; / 1930) Vice^Pres., . '*-Estimator,. Charles.G. Heyne'-& Go.,.2002 Roth- , Combustioneer Corp., 409.TentK St. S.W., Wash- * ':well..:and 1621 Kipling, Houston,-'Texas. y ington; D.' C.: ahd'.*6701 N. Central Ave.,'Chevy ` - BEALS-,-AlbertP. (A .1945) Gen. Mgr., Western ; . ' Chase,,Md..'- ' i;* ' -- j "' . _ ''Service'.Co.,-910..Frdnt St;, and.1220 Broadway,--- \ BEKESHUS, J. Herbert (M1945) Pfes.,- Pioneer Fargo, N. D. '-: ; ' OiL Heat, Inc:. 229 River.St., and T503;Masffl- BEALS, . Dowell* E. (Af 1941; 7 1940) Owner, _ ' Chusetts Ave., Troy, N. Y. - - v. - ' -. ' C * Beads Plumbing & Hearing Co., 315 -West 13th _- BELANGER, William (M. 1944) Owner, South. . -St-,'and 4001 Calmont St..- FortWorth/'Texas. - eastern Supply Co,,'390.N:..Front St., and 4409 .' *..-r.-v..BBB.AoESEEEivtlnA8.ANseA,g1'NN;7oB3R,f,i.r,-i'SrtnMHG.hGTAgriidiW.nhhn'eMaPsaonoelcagmlm.srlouotgt,toe.al.oeS.mn4snC.tS,-',-'h.'HHJ.,Naa.Nna.r.(,lAdnee(YJnsAw4.ra.f1.9SO'9F41't3r(u-99l,5Aed4-)1af4.aC6n:)Mn17tso9dAh'g.14-;ir92A4r.'-,)1,1vI.C-L92eSCo6a2.t,on/oiU-MndkMs-n.wea.iiir-vtDm'tE:eheDenre"ssagiiwvgi'prt.ns.y.*.-','';--*~`.-;;' ;.'BB'-A1fA2REErc93iiegLLru5t'gehCFsDMurhOSaoElnautthRNi-teroo,drDt,nraa.A'.C,AnyCv&doLloeAb.-on.,2yAe.7tu2-erprN02oi-tsp0r1elL*lGwiDWFBaanor.i.Bvic,lcu's.he(Je;rAo>mdtrbh.Mf.Soo1ADeinr(9ndrMvtr4vn-.;e0.-i,ecN-M^)eaT1'.`a;Np-9EeYs;o4reaIrs.n4lwes'i.'c)s-'t..e--HYPH,rn''oaro:e1'ruSn5skt.uee.3vS'y.p,''woVIaRnu.sentedrlh-d.l-,..'*j*.;'-'.*;'- BEARMAN, Alexander/Al (Af 1937) Engr.. . BELINE, Martin B. (M 1944)-Engr., Washington ' ' 20th..Century-Fox Film 'Corp., ;444 West 56th' .. - Refrigeration Co'., 1733 14th.St. N.W., and 2440--. Stir-New York 19, and 3111 Broadway, New York ` 16th St. N.W., Waslungton'9, D. C.'- - ' :27.n.y. -BELING, Earl-H.* (M 1936; A 1930; J. 1925) * BEARSE, AUen H., Jr. (A 1945)`Mgr..- Solid ' -Owner, Beling.Enguieering-Co.', 405 State Trust- -' Fuel.Div. ahdComb. and Htg./Erig./* Barrows . . .Bldg., and *2428-13th SL. Moline, IU.- * ; Coal. Co.., 35f Main St., and 56 Western Ave./ ..BELL, E. 'rFlovd. (M 1933) Gen. Mgr., BH1.& ' BratUeboro/.Vt,!-'V-' ' - ' . Eiss, Inc., 2102. Foshay-Tower, Minneapolis 2, `and -- - BEATTIE, James '(A .1940) Htg.- Contr., 10001 5224 Oak Lawn Ave.,'' Edina, Minneapolis 10, - Broad St.. Detroit 4, arid 17215 Greenlawn Ave., -v.Minn. - ; u v. . ' Detfoit'21, Mich-' -. ./ . BELL, -John A.'.(A .1944) Htgr Foreman,. Royal -.- BEATTY, John W. (7 1944; S 1941) U. S.Navy, ' Canadian Air Force, No. 2,-Air Command.~RCAF ' ^ *612 State-Sri. Beardstown; 111.'*'-. - - . . .Winnipeg,- and *151 Baltimore *Rd., .Winnipeg, - . -BEAUCHAMP, John H-..(A 1945) Owner-Mgr.y .' - Mari., Canada^. . . -.- --Heating & RefrigerationMainleriance Co.,.3913 ; BELL,, Sydney R. {M 1939) Principal, Sydney : S Main SL, and 1005 Isabella, Apti`33; Houston - R.-.Bell &-Associates,"374 Little Collins.Sri; and * 4 rexas.-/ \ s;-:' :ZS. : 12 Queens Rd:,'Melbourne, Australia.''. ;' -. 'BEAURRIENNE,'1'Auguste*: (Life-jMember;*] M ' -BELL:..Thomas H.- (A. 1944) -Engr; -and' Supt..of 1912):lCons. VEngi\, *25- Rue .des Marguettes,- -- -Constr., Columbus Hearing & VentilatingCo.,182 ; Paris/Xll.' and 18 Rue du-petit..Val,-Sucy eh.'- N._Yale'Ave., arid *296 S: Eureka Aye.; Colum- > BrierSeine et Oise, France.-: -5 "" T'- bus,'Ohio.. ' - 'i'. ' ': vBEAVERS, ;G.`R-l (AT1929)'.Chief Engr^ Cana- BELLMAN, John V. (A 1946; 7 1943). Chief Petty ' * diah Blower & Forge.Co.; Ltd., Woodside Ave-Vand" - Officer;-Directorate of.'Electrical' Supply,-Naval. . 230>Cameron Sri'N.','Kitchener;.Ontl; Canada. Service' Headquarters, Ottawa, and. 170 Hope rBECHtOL; J. J- :(A. 1942; V/Il937)iUi; Sl'Navy. . Sri, Toronto, Oriri. Canada:.1 C- - !-.* Z\ .- ^ Pensacola,' Fla., and 1282, Quebec' Rd., Cin- -' -i.-annati'drOhio.'''-_ ' ; ' v [ BELSKY, George-A. (M -1945) Chief. Engr.: ^Majestic `Refrigerator Corp;; 625'Broadwayi`-New - ^BECKER,'C-.S:.(Af 1939) Mech. Engr., American- York;.and 78TtandolphRd.. White PlainSiN. Y; ' r i^ Blower Corp./'228.'N.' LaSalle St.,^.Chicago; 111;'-'.'. .BELYEA, Roy E. (A 1944) Mgr.. Belyea Bro , BECKER. George E. '`{A". 1943) .Secy.-Treas.,.'.. Ltd.,1002 Bathurst Sri; and-207 Glenayr Rd., .Sales'and- Service, Frigid . Refrigerator' Service; J . Toronto, Onri.'Canada:' ' ... 3232'.Olive,- Stl_Louis.3,'and '5329 Delor St;,- St. BEMAN, Myron C. (JT1926) (Council, 1*93^-1939) .. .Louis, Mo. `. V ."-Partner, Beinan.&-Candee,'374 Delaware Ave;, BEGKER. Roger K. (M 1938) Aest. 'Geh. Mgr:, -'' Buffalo 2, .arid 262 E. Quaker St:,' 'Orchard Park", - Ohio ValleyHardware & RoofingCo.; Evansville 2, .- n. y.^- -and 1215 Akin-Dr., Evansville.l3,'Indl-'' --' BEMARKT,'.George - H. (M; 1945) Htg. Engr../ . BECKER; Roy F-.J- (A 1943) Pres.;-VOil Burner',. - N.'O. Nelson*Co.,4316 Duncan*Ave.T'St. Louis: Service Co., 315 West.Lake St., and 3917.Garfield - 10, Mo. and 516 North' 19th St.-, East St. Louis, 111... - - Ave; S.; Minneapolis: Minn. -.*'., f- , BEMIS,' Paul ;D.' (if 1942). Cons. Engr.: 36 . --.BECKER, Sidney:(jr-1944)-Engr:, J. Beckeri Inc-.ll.;. Pearl St:;' Hartford- 3.* arid 3TRiggs-Ave,, W^t I .-.-282 ViUeneuveSt. W...Montreal 8, Que., Canada;.'` .Hartford,'Coriri. - * i- 'V/y . , BECKWITH; F." J. (M 1940) Htg.-:and ytg.'iEtigr., ?; ''BEMIS, Wilfired'-A.;(A. 1942)' Engr.. :Amaican^' .** .Henley & Beckwith; 2628 Pearl St.,'and^* R-\E; D.*r' Smeltingv& ` Refining- Co.,"4039 7Park' Ave^'Si:?; -<f!,vI.:B6x`250,'Jacks6nvilIe,'>Flar''':;';/; i.r-y '.T*:- ." ~ Louis,' arid.* 129'Emerlirig Dr.`; Ferguson 21, *Mo.: BEEBE. Fr^derick E. W:{{Life MembervA:19i5y:' BENHAM, Colln S. K. (A 1940, V 1937)-.Dir . Retired...-Jbhnso'hVService Co'., `28 .East-29th:`St.. ' ' . Beriham & Sons:,Ltd., 66' Wigmore St'.;' London-' . /- New.York;N;Y.rand 20.Denman,Pl.; ElizabethsXy-.W- .l; and.Hill House, Prestwood, Bucks,.England.I. 3nj * BENHAM,-.'Fr C.r Jr. J(A ^1942;-? J 1938)-. Engri*,, -. BEERS;- Louis.'N;:(A;1942) Sales' Erigr-YrNicolai's . C;-. H/.Ruebeck;Co.810,"InsuranceBldg:, San'-; >-:`^I ucson. Pipe -Works;,A16 ;W; Davis, ' and> 2745 j.'Aritonio 5, and 1636 W. Summit St., Sari.Antomo.-r N. Martin; Tucson. Anz.y j ' -pv : *,'Texas.1-- - Roll of Mernbership '' 13 BENNETT, 'Edwin :A. (Af .1936; J.. 1929) Field BERTOLETTE, Chester (Af 1940). Htg. and Vtg. ' --. Engr.; * American Blower Corp:, 50 West 40th St., ' -'Engr;, *515`Broadway: Dobbs Ferry, N.' Y. Z- '-NewjYork 18, and 128. Randolph. Rd., Fulton BERTRAND, George*; F. (A: 1939) Sales Engr., . ' . -Park; White Plains, N. Y.' - ," . - *235 Richfield,Rd., Upper Darby,-Pa. . .: :'BENPfETT,' Merle F. -(A; 1942) Chief Engr., -- " First National Bank Bldg. Co.. 17.40'Nationalr- ' Bank Bldg.. Detroit 26, and 537 Pleasant Ave., Birmingham,' Mich. . -. } * BENNIS, Raymond R. (A 1943) Chief Engr.-, Contractors Refrigeration Corp., 89-35 Queens "Blvd., Elmhurst, and67-47 ISlstSri. Flushing, N.Y. BENOIST, LeRoy L. (M 1934)-Partner and Mgr., .- = . BERZELIUS, Carl E. (Af 1936) Asst. Mdse! Mgr. /* . for Indus. Roofs, U. 'S. ..Gypsum* Go.', 300 W. -: * Adams, 'Chicago'; 'and -1519..Vine, Park Ridge/lll.- '. BEST; E:-Thompson (Af-1944) 'Mgr., Air Cond.' - and-Refrig.; Frank A. McBride Co., 160 Ward Sri, v ' Paterson, and 189. Lakewood Ave., Ho-Ho-Kiis, n.j. - . Benoist Bros.* Supply Co^- -117. S. Tenth Sri, BETTS, Howard M. (Af 1927) Sr. Hte-'Erigri/;. .- arid 1500 Main'St., Mt. Vernon, III. - Dept, of Bldgs., City of Minneapolis, 213 City. * BENOIST, Raymond E. (A 1936) Mgr. and Engr,,5 r Hall; Minneapolis 15, and 4923 S. Russell Ave., - Benoist-Bros. Supply Co.\- 117 S.' -Tenth St..'and . Minneapolis 10, Minni- -" '? * . . : '. - *811 North 12th St., Mri Vernon, 111. i BETZ, Harry D. (Af'1928) Owner; Betz Engineer- - r.BENSEN, Clarence L. (M 1939; J 1935) Sales . ing Co.,'1330 Broadway, Kansas City 6, and 5414 ^Engr., McQuay, Inc., 1600.Broadway N.E., Min-. Aberdeen Rd., Kansas City 3, Kans. * - - * neapolis, and 3042 Benjariiin St.-N;E:, Minneap- . BEVIL, Alexander T; (A 1944) Chief Engr., W. F.'. --:olis.l3,-Miim; ' ' Slater Engineering Corp., 627 Monroe Ave., Mein- - BENSINGER, Mark (A 1946; .7.1936) Lt. (j-g-) phis 3, and 1521 Waveriy Ave., Memphis'6,.Teriri. - ':"'Sub. Repair-Unit. c/o Postmaster, Ran Diego, . BEVINGTON.'Curtis H. (Af.1936) Owner,. C.H. :'Calif., and 608 Bradley Lane, Fairview .Heights,' Bevington Co.,.330 S.;'Weils Sri, Chicago 6,-acd ? 1 Portsmouth, Va. ' R. F. D. No. 2; Elmhurst, 111.- ' . BENSON, Foster W. (Af. 1942) Asst. Western ^rMgr.'i`Niagara Blower Co., 37 W.-Van Buren Sri, . Chicago, and *418.Emory-Ave., Elmhurst, 111. -'BENSON, John C. .(A-1945)-Washingtori^Branch =. .Mgr), Carrier Corp..' -942 Investment.. Bldg., Washington 5, D. C.Vand 103 Southbrook Lane,' ..BethesdaT4, Md. -' ` ' . .* j- BENSON; M. A. (Af 1944) BrancEMgr.. *70110800 BEVINGTON;. WarrenC.- (Af 1942) Pres..- ' Bevington-Taggart &'FowIer; Inc.,-730 Indiana ;^.Pythian Bldg.,-Indianapolis 4; and 3101 N. Men- ' - dian.Sri, Indianapolis 8, Ind.':!* . BIANCULLI, Vincent A; (A 1945) Engr., Syska ' : Hennessy,-144 East 39th-SC, New York, arid-.- . : 141-35 78th Rd., Flushing; N.-Y.. '" C'- ' Service Co., 2708 Live Oak,' Dallas 1, Texas: * . BENTLEY, Clyde. E. (Af: 1937) 'Cons. Engr^ BIBER,. Herbert A. '(A -1937) ErigrJ; Mellon -/ ' National Bank,- 514- Smithfield Sri,'. Pittsburgh;- * V. * 216 ;Pine St., San Francisco 4, and - Antonio Ave.vBerkeley/Qalif.- - l875 - San - and *323'-. Barries 21; Pa. - Sri,' Willdnsb'urg,' Pittsburgh / .;- . - . . *%. .' . ;' . BERGAN,'John R. (Af 1945; A-1941; 7.1937) BIBLE; Hollis U. (Af 1940) Lt. (j.g.); U.'S. N. ~Rl, - ..--..Eastern-Sales Mgr.-. Moduflow Div,, Minneapo- ,'N. T. Sch.,-Princeton, Brown Hall 113, Princeton, lis-Honeywell Regulator Co., 221 Fourth Ave.. New "N. J.,' and c/o Mr.-Thos. Mi Godfrey. Box 322, -* . - 'York 3, arid 293 Murray Ave.,-Larchmont, N. Y.. Rt. 12,.Memorial Dr., Houston, Texas. 7r BERGER, J. L; -(Af 1939) Pres., *The W, R. BICHOWSKY; F. Russell (Af 1935) Prof.,.* 4200 - \ ,Rhoton-Ck>.f 5915 Bonna Ave., Clei^land 3, and 13th PL N.E., Washington, D. C. ` ' , * - - _ . . - 2652.Edgerton Rd,, University Heights, Cleveland BICKELL, George C. (A 1945) Sales Engr., ` ' - 18,'Ohio. : .. -. : . . . Tuteiri Equipment Co., 130 Bradford ' Ave.;v BERGMAN, A. E. (A 1943) Pres., A. E. Berg Pittsburgh. 5,- arid' 1100 Standhope; Pittsburgh/' *' man. Inc:; 1913 University. Ave.,- Sri Paul and, -4, Pa.': . ... ; ' - . ... ' 2744'-W. River Rd., Minneapolis, Minn. ' ' -' BIERL, Joseph G; (Af -1945) Vice-Pres., -Scholl .BERKELEY, Clarence D. (3/ 1944) Application . man~Bros. Co./4114 "North 24th;Sri, and *4927- - '.'Engr., Carrier.Corp.,'.1331 Third Avenue Bldg.-, :N. 34 Ave., Omaha 11, Nebr. \/ v Seattle 1,- and *3312 E: Spring .Sri, Seattle 22,- r-Wash.-. ; . . VBERLET, E.` John, ;Jr. (Af 1943). Application .... Engr.,-* York Corp., 5051 Santa-Fe'Ave.; Los Angeles 11, Calif.- ' ` BERMAN, Louis K."(Af 1908) Pres., Raisier -.. Corp., 129.Amsterdam^ve.. New York, arid 885 BIGELOW, Folger'H. (A 1944) Branch Mg^., lig>Electric Ventilating Co., "517. Farnsworth' ' . Bldg.-, Memphis 3, and 353 N. Willett St^/Me'm-v '' phis 12, JTenn.- . ` ./ . BIGGERS, Richmond H;-(A-.1939) Mfrs. Agent, ' *2229 E.-JefferspnAye;,'Detroit 7,.Mich.- -* . -"Park'Ave:, New.York 217 N. Y.' ' ' V \' r BILDERBACK,' George' R.'- (A 1945) Comm1!. " BERMEL; Alfred;H. (Af 1943;'A 1933; V 1928)' v Supvsr., Advanced Refrigeratiori,' Inc., 350 Peach- - . -. Chief' Mech. -Estimating Engr:, August, Aiace:& ' tree N.E., and 1975 Baker Rd. N.W.; Atlanta," .'`Sons. Inc;. 642 Third Ave.,-Elizabeth, :and 340 Ga. v . ; - .^Cainbridge Dr.. Union. N. J. ' * . BILLINGSLEY, Oliver F. H., II (A 1944; 71937) " ' ; .^BERNARD,\ Edgar. L;_(7. .1941;' 5,1940) *40 . . . Pvri; U.'.s: A-., Serial No. 39714096, 185th RepL*> : ..^ Chester.St.. Allsto'n 34. Boston: Mass. - - .. ,Co., 43rdr Bn.,1 -A. P.-. O. 711,'"c/o. Postmaster,'- " " BERNHARD, George (Af 1944)>'1175 E. Broad- : '- San Francisco, and 2172 West 20th'Sri, Long*' '-.way: Hewlett. N. Y. " . - . ..'Beach, Calif."// ' r 'V L BERNSTROM, C. Bertil (Af-1944). Chief- Engr.,'. BINDER, ChaHes G. .(Jf 1920) Mgr,, Htg. Dept, - 'Jaden.'Manufacturing Co., arid 223 W. Fifth St., _Warren Webster & Go.,' 17th and Federal St - > Hastings,'.Nebr.-c * . ; - - J. - . Camden, and 115.;Oak'Terrace, .Merchantville,' BERNZEN, John (A 1944) Vice-Pres;, The City' Plumbing & Heating Co;. 1123::Walnut, P. O..Box . BIRD, .Charles (A 1934) -TrMS. 'and Gen; Mgr-, - ' '. 717 and 833 Spruce, Boulder, .Colo. ' - * * The Cincinnati Supply Co., 450-456 E. Pearl Sri; ": : BERRES, Daniel S. (A : 1943) ..Engr.', - Navy Cincinnati,Ohio;r v * . ` - .. , . Department,.-Washington, D...C.,- arid *805 N. ' .-BIRKETT,. Harold,(Af 1940). Engr..VThe - Wayne.Sri,-Arlington, Va.! . . ' v ` .Brooklyn Upion Gas Co;, 176-Remseri'Sri,-Brook- - - v BERRIDGE, Winston W.'(Af 1938) Htg. Engr., Iyn 2,:and87 Deepwood Rd., Roslyri Heights, N Y --- -/ -'' McCoB-Frbnteriac- Oil Co., Ltd.,''2540 Notre BIRNER; Ira L; (Af-1945) Mgr., Tech. Sales & - Dame, E.,:; Montreal, and. 28 'Dufferin Rd., ; Service Depri. sThe Celotex Corp.,120 S/LaSa!Ie' - .. Hampstead, Que.-,-Canada. >-. - . - - .. s St., Chicago. 3; arid 5056: Marine Dr...Chicago- -BERRY,. Norton. E.' (Af.. 1944)r EHr. of Research, - 40, 111; - - "7 `; ;.'-7 ` -- . : Serve!,.Inc., Evansville 20; and Newburgh, Ind:' : BERRY,' Patrick: M.' (A : 1944): Chief - Engr., Standard ..Asbestos' Manufacturing' Co;, 1844 , BISBEE,-Bertln-A..(A'1945)'-Partner,-Smith & -Bisbee Hardware Co'.,'412-416 MainSri. and *212- ' . W.^First Sri N.,'MairahalL Minn. -- t. - .v East 40th Srii Clevelarid 3,'Ohio;'-4 :* --- ; BISHOP; Albertr/H. /(Af .'1944) Elec/ 'Supri, _ - . BERRY,'Robert U..:(Af 1939)'.lkigr;v.FIeId Erigrg.; o Alberta, Clay, Products,-and Suite 34," Granada .Div;, *Air Corid.:Dept.', ;Generai.Electric Go.; 5.' 'Apt.. Medidrie Hari Alta-.-Gariada.1/ : / :Lawrence^St., Bloomfield, and 548 N. Maple Ave.,-/ BISHOP,- 'Charles* R; (Life /Member; -*Af--190l) 't: "-East Orange; N. J. : - ' ` : - (Council;-/1916) *22 Sagamore Rd.,' BronxvilJe, ,, :'.BERRYMAN,/ Richard H." (A ' 1945;^7 :'l946) - -C.N, Y.'-.':. 7 ^^ S- Reg./ Mech. -Engr.-Plant-. Engrg.- Div.;'Aircraft . BISHOP/FrederidcR. (Af 1921)' Mgr; of-Sales;' Div:, /Packard Motor 'Car^Co., -1580 E. Grand - .. -Blower- Div:; -The. Briindage- Co., ^Kalamazoo; -.Blvd., and. 264.Worcester.PL, Detroit, Mich.'. and *8011 Dexter Blvd.; Detroit 6, Michi -// " 8S& BLAZER,^VBenjamiri'?Vi.(A^1940)-.Owner'.-#''M`.- . .-. Blazer'&Son>173 Market'St.rPaffiaic,'and48'I3Lh`:V-'r-vk^,'v - ? I^A^r;*wvs^^RKENr<MauH6e':H?(JfAl938)lN..W.;*lBr - ;Ave!yPatersori,-N'-J-'k"'x-j BLEIERv;Frahk^P.t(if,vI945KA : 1944), Dir U.&K. Hoffman.Specialty Go.v 542,BuiIdera Exch..and . : Research,' Ilg ;Electric.,Ventilating .Cb',^2850 'N'. -'. "; - ^ '/>%"? 4952^17th-Ave"S.', Minneapolis; Minn. Gra^drd,4Ghicagb;4l^and 54^WrvAddwpn.St.:;: ^^Ed'garriN.USrd^M-vlSMJvPbilsa* Iph av .xr:*---lii----- t--------t--.. 'T,7tSansdm-C; --vChicago-13;.Ill'.^,. ................. , -BLOGHV,Leonard Li':C<4'-.1944y'.General Delivery;'/i/ *r Los-Angeles;:Calif r'' BLOOM,^-Louls/'(M-.1935) /Owner, Freeportv/t/' .{Plumbing &>Heating;;Engra.,*-:84-AVBfbadway.-'#c _?FreeportrL2 lM-Ni-Y.^'`>^^<- LOOMV:KaIphl^'(MJ1945)--Meeh;r?Engr.-;t6W,^4v->-.<.w^,/. .: Sexton, Bldg.TIfMinheapolis215,3 arid;3754'/Fbppa-'_:iV' - 'Ave..'Minneapolis 16/,Minn//'/ '' vi BLOOMSTERviEdg^L^(M^l943) -r 116;,jNewJ' Mont gomeryf St;i-:SahVFranasco: 5`, '^fe^a^^^^SBIsXCRHALL; tWUmot/R. ;(M.-T1922) -Partner. .: .and> 3820 -Divisaderd-St.-?-San- Frandsco/' Calif jf;'5?^'iS^`^/^;:r-x>{*'Blackhall/Heating-&' Plumbing^ Supplies/ 1104-- :BLUM*>HrmanJr:.:(AV;l944;V^1936X/ednsf^fc^>M4^ yEngr.;:* 1708HCommerSt;,-DaUasI-<iand.4438/v;v^.,J:'t^:i Emerson^-DallaS`5;Texas;';r.vy2_2ri->..--t;.'^-?/-V` VXT M'/'-r.V*1'--!' s^i Greenwich'Lodge/47 Lafayette'_El.v Greenwich. 5^^ BLAGKMAN'.rRobert Ci(A*.1945; //1944) Powir t ^ Ehgr.'./AllisonDiv.^ :'General-'MotorsCorp..^ahd ,,,, <- /1267.N;' Lynhufst Dr.V-Indianapolis S.^Ind/ i- v; 'V * BLACKMQRE; F;"H:(M l923)XVice^Pres:. *U S' pgjMs -t - Radiator; .Corp.'iii'USOO {United^Artists^/Bldg..*' ,.w /;/DetroiC311and*515 TobUng Lane/Birminghain . BLUMCWchj^d3-j;;-rJr;/(A/1940) c7o - Carsey.-The 'Kirk8/-Blum'Mfg''Go.`{ 2850;Spnhg;;^S^*.',.jpsa ^.GrbveAve/;!Cihdhhati251''.Ohio/i'vv;ri?-' !BLUMENTTlAl;;fM.^l;{(-M-1936y'Medi?r8:*Rjefrigl/4; : .- Engr./-.Maiitime^Commission.'-West '.Goast-. Reg//v1'/3l, >l^4 :?.Office; FinandM^Genter^BidgA/ll/S.^M. 'C.* .'aml-'y^i'/)^^/^ .- 3600.Lakeshore B1vdr, Oakland 10/Calif../-?*/.' BOAtES,vWUl&mrG^(M;i936';;iO 1923):oSfler5f..:*SS,4eJ - Wm. Gr*.BoaleB'ff,;Assoc./6429{Hamiltbn:Ave.`///^:iy 'f^L ; i `Detroit 2/and/43'Edgemere.Rd.,: Grosse/Pomte Fann8 3Q: Mich./i~t?/'-g' 'v,.;-,:!/: '//-yivgf/g BCKatiVt?Kl(X C&cr,Boct.'Co4iS:'.S# " v'708'N^HarwoodBDalIas;l)and4654NrVersailles/"/^-''/ ... Dallas/Texas.'1*V/-/ r"v fc .. ... . -------- -------------------------- ..^...JBODE^^Walt&^F^U^lMZ)^' Bramii Mgr T ^ *1 * WW'-'anil i 947lW'Wprrpr-A vp,r PaIIpto Part :Ca t* ` ri! MnHina' Womtfn/4iirinir 'Cy,v' 404^C'>.U;All. .L'i **!, vfc : State ' Froaen^Egg^Gdip.v: 333 .* 18th -SU ::.-> Frahdt-;and 1124 :(F) `Eighth St.^: Berkeley Indianapolis;' and 903-E.`Maple -Rd-V-India-/- -CaIif.'/> 'V-nfUs..^;, :.: s- napoIis'5Ulnd:,'.-K .^.rv* ''/ ^ BOWERMAN, -E. .;L.` (A- 1937) _ 274.Belsize Dr .1 ' - BOND. Harry H.. (M-1938)-Partner,-* Edward1. E: v -Toronto," Ont-.-Canada."' ~ ' Ashley. 10'East^40thSt:,'Nw York 16/and 137^81 //BOWERS, Ai ' F.** (A *`t19I9)". Pres:; '* Industrial BelknapSt.7Springfield Gardens13; L/Ir/Ni Y/-. . f > Heating :&! Engineering; Co.>-828 N.' Brbadway RONDi-Hornri.'A.' f M.IOSflVPmf'Rnir' 'I .W Wash.'. - Milnraitlv^a' 9X -.nil * ^ r ,$*?* /1 .Fiherglas^Canada// Ltd^/1025j Confederation >wiu, L>yiv mu. n.ngr.,,rvailon Go.,'1800' Baltimore;/ Kansas!- City/S.'-and; 430/ w~ Bldg?r-Jand 3'4523w'Kenangt6ri?-rAveU-t 'Montreal.i West'59th.Terrace/Kansas City-2.:Mo! -/ ^rTQue.v Canada/'.'K./>" c"`' ' ' ' ^ ' '\ x - BOYD,'Robert L;,rJr..(A! i946;:7-T941)-lst Lt, ?. BOOTH,Ro6r^W4-(A<1945)-:Chief*. Engr..^The n !Lennox<-Furnace/Go...and' 116r* Kalsem^ B1vd.., ^ - Marshalltown/{Iowa ' -0-llI604S,VHq. 4th-*A.^F.r:B.V&*G./-rl80 New ^ Montgomery St.vSan-Frandscb 6,-Calif./and 4017-* Colend^ Ave., Houston 5,-TeTrtg BORAKv:Eiigerie (M 1937) Engr.. The johnson; , ' BOYp.-Spencer-.Wallace'r-CAf 1937)tCohs. -Engr: lfr Heating Ventilating. Air - Conditioning -Guide: 1946 BRATT.- Hero D. (M/ 1937) Sales Engr!. 3.. BRONSON," ;Carlos E.* (M-1919) Chief: Mech:. Federal. Square-Bldg., 33 Pearl St, N.W.; Gra'ricf- Engr.,.* Kewanee Boiler. Corp.T.620 S: Main'tSt.,^ ^ Rapids.2, and '2259 .Stafford Ave. S:W.,- Grand -Kewanee; IlL w '- "./ e..' Rapids 7; Mich. * / -' ' BROOKE, Bernard. B; (M ;1945)' Dist. Vent. . BRAUER/Roy.<M 1926) Dist. Mgr.,-* The Trane : ' Engr. & Dept.' Mgr./The..General-Electric,Co.,.. Co.. 512 Magee/Bldg.? Pittsburgh 22.' and -576 ..Ltd., Magnet House,. Kihgsway, Cardiff.',.'and r v Austin'Ave., ML Lebanon,* Pittsburgh 16, Pa. Kynance, Beatty Ave., Roath Park, Cardiff, BRAUN; Charles R.. Jr. (7 1943; 5 1939)' LL Glamorgan. S. Wales, England; - . . . /' t' G.g.) U/S. N. R;. U. S. S. Change (AM 159)'. BROOKE; Irving E. (if 1938) Cons. Engr., *189 Fleet Post Office, San Francisco, Calif..and *1346 . W. Madison St... Chicago, and,830. Keystone/Ave;, Hames Ave., Columbus 8, Ohio. / . '1 River Forest, -111. : BRAUN, LouisT. (M1921) Exec. Secy.. Heating, BROOM, Benjamin A* (Life- Member; M 1914) : Piping & Air Conditioning Contractors Chicago ; Prof.. Engr., Rggnar Benson, Inc., 4744 W. Rice *-. Association,"228 N.-LaSalle St., Chicago 1, and ' St., and *823 N.'Long'Ave.,'Chicago 51, 111; - /l548 Pratt' Blvd., Chicago, 111. ' . : ` ' '. BROOME, Jbseph'-H,.- (A* -' 1936) .Zone- Supvsf,, ' BRAYMAN, Albert I,i; 1937) . Mech. Designer, Minneapolis-Honeywell Regulator Co., 221 Fourth: - E.- B. .-Ba'dger & Sons'Co.. '75 -Pitts St., - Boston, ; Ave., New York 3, N. Y;, and 137 McCosh Rd:, -- and 340 Boulevard; Revere, 'Mass. - .;' ' Upper Montclair, N; J." - ;. BREN. Leo .W. (A 1944) Asst. Mgr., .Grudem . BROWN, Alfred P. (M 1927) Vice-Pres.,:* Rey- . i - Brothers" Co.', 2645 .University Ave., St. Paul ,4; .- . nolds Corp., 4224 S.. Lowe-Ave., Chicago 9.- and \i. and 4612;Drew Ave. S...Minneapolis,,Minn. . -1097 MerriU St:. Winnetka, Illf r . r / . BRENEMAN? Robert B/(A.-1931;7, 1927) / BROWN,,Aubrey,.I.* (M ?1923) Prof/of Htg; & ." . Branch, Mgr;/*Armstrong Cork Co/ 1282 Edge-.'. Vtg.,' *Ohio State'University, and 169 Richards . >-/ hiilRd- Columbus-8,and 358 Arden Rd;, .CoK Rd.; Columbus, Ohio,'.. '' ' ' " l- limbus'2, Ohio. ' -- -. . BROWN, David (M.1936) Owner, *D. Brown, 67 BRENTON, t Reginald -S. (A : 1945) : Partner. ' Cooper Sq., New York 3, and' 54 West 174' St/ *' . Brenton &'Hart, 6 Beacon St., iBostom .and *32 - New'York;Ni;Y/- . "Kenilworth Rd;, Arlington, Mass. . \ ' . BROWN,:- Edward A. (A- 1944)- Owner. E.' 'A. BREWER, F. Mr (7 1941) Marine Engr., Navy Brown -Manufacturers Agency/513-Redick Tower,-., . Dept/- Bureau of.Ships, -Washington. D.'C., and 'Omaha 2, and 1315 South'79th St.,'Omaha, Nebr. . - 1762 Preston.Rxi.'. Parkfairfai. 'Alexandria,' ,Va? BROWN, Foskett*-.(if '1926) . Pres., *Gray &. BREX. Irring E. (A .1939) Asst. Mgr... Brex & -. Dudley Co., ,2300.-Cluton Rd;, Nashville.3,-and'' Bieler -Div., Excelsior'Steel. Furnace ,Co., 902 'Hillsboro Rd:, Nashville.'-Tenn./ ' * ; * > 60th St., BrookIyn, N; Y., and 1223 Hillside Rd., BROWN, Guy M. (Af^J943)'*4845 Harriet Ave.. P.-O. Box 985? Lake Mohawk, Sparta-N. J. .-: - .Minneapolis'9; Minn.- l -YBREYER; Frederick (7 1943 ; 5.1940) Engr.. *H; BROWN, Harper J; XA :1946; '7.T940)>65.F6rt '. . , Lieblich & Co., 36 West 66th St., New York, N. Y. . ''Hill Circle, St.;George, S.I.,'N. Y; - *' BRICKHAM, Ben-A. (M 1944) .Owner, * Htg; & BROWN, J/Mason (M;i945) Engr'.,.Worthington" -".VenLEngr., l311'S.--Vine,' Denver 10, Colo/ . - - Pump &' Machinery C6rp{,;;Harrisoii,: and * 230 .... ' BRICKHAM, Nelson H. (A 1943) Mech. Engr.,Y Kimball Ave/-WestfieId,,N. jr. - -in charge of Htg.. Ft. Francis E. Warren, and BROWN, John.S.V Jr; (A 1943; J'1937)'Indus.; , - 3605 Reed, Cheyenne, Wyo/- . *..' ' . -. Engr.; -Frigidaire Div.-. General. Motors . Corp/--. BRIDE, William T. (M. 1928; J 1925>* Bride, - - Plant' No.. 2, Moraine. City,-, and 428 Hadley Gnmes 8c, Co., -9 -Franklin St.;. Lawrence.and 28 Ave.; Dayton 9, Ohio.-- . AIbiori;SLv Methuen, Mass. v* -v BRIDGMAN, Rbbert C. (A 1945)..Sales. Engr.,' -- American Radiator 8c Standard Sanitary.Corp., . -1745 Connecticut Ave., and 3224 Oliver St. N.W., {' Washington, D'. C.\ / v-/ . - /* /. / - r 'BRIGHAM,; Clare M. (AT 1935) Vice-Pres. in charge`of Sales, * C; A. Dunham Co;, 450 E. Ohio -SL.Chicago 11, and 420 Maple Ave.,-Wirinetka, 111. * ' . ' . t BROWN;- Mack . D. -(M ,1938: / 1936) Engr.; . *`The Bahhson Cb:,1001'S. 'Marshall SC. andj' 2320 Okalina Ave., Winston-Salem, N. G. / : BROWN, MarvinX. (Af .l939)"Parther, *'Dallas Air Conditioning Co.', 2809 Cantoa St., and *4328 Stanhope St./DaUais, Texai- '>/ BROWN, Maurice W;v(A ?1944; 7.1938) *619 Texas' Bank'-BIdg.,>Dallas 2,~ and 4233 Amherst, ;. Dallas'5, Texas. - -'. .- -- Y -- -- " -*//. - ZBRIGHAM/Frederick H. (M 1944) Engf.,*C?R. . BROWN/ Norman ^.(A -1944) ;Owner,'*Norman - -^Swaney.tCo.; 335 .Newbury St,,. Boston,, and 39, . -Brown Co.1, ,765 Minna SC,. San Francisco 3,.'and. ,Woodside Rd., .Winchester, Mass.'1', . . . . rRt. 1. Box-568Ai Los Altos; Calif. / : BRINDELL, Carl; E. (A? 1943) Partner. VBrindeil ' BROWN/RicKard.Ci^ (M^1944). Partner.* Camp^;' Cooper,.206-Balter Bldg:,-New Orleans 12/and v - --'bell Elsey & Co.';;326 Ne^ Bldg., SaltLake City 1,-r 501 Ridge Lake Dr.;-Metairie, La.',i/' -*1'. :-u- - -'-'and 2223 South 19-EasW Salt'Lake Oty 5; UUdi'. ' - .s BR1NKER, Harry A.- (Af l934)-Partner. \Vi!son- ' BROWN, Robert M. (A 1944)-Owner, Brown;& ' i' -Bnnker,' .309/Pythian',BIdg^ Kalamazoo, and; ' Co.,r 298 Techwdod-Df.;N.W., .and, 1095 Berne1 ="- 2o21University Ave., Kalamazoo'36; Mich;.-; .; ' - SC;S.E.; Atlanta. Ga. -YY/ - 'BRINTONr'JosepK W*. \ (M? 1920): MgrV/Boston i - BROWN;Sterling >D. (A ;1944; 7, 1939) .-Mech.V ^ - DisL./* American'-'Blower /Corp.; . l003-`,-Statler -' Engr.; *Public :Works ; Design - Sect.; 'Bldg. ..47,. *Bldg.*,/Rdrton, 16,f and ..42 Gleason St,,West ' 'U. S; Naval'Shipyard/ Mare;Island, .'mid 5960 Medford 58,vMass,`. s -:-Y/-- :-'l* : r /-BRISSENDEN/Carrol,W.'(A-1946; 7T939):LL L-4-Comdr..'U.'S. N. R.,-* Naval Air.Station, Arma- ./Park Ave.'/San'Pablo,.Calif,'-./ BROWN,'Tom (Jf l930)V* 15482- Nehls . East DetroiC^Mich., Y*- - /' -- Ave., . V:meht'Test,;Patuxent River, Md. ' . -BROWN, Ward A; (A .1944).Assoc. Engr.7 George. -'BRISSETTE, Leo A. (M 1930) .Treas., *Trask' ;/.'Heating Co;, 217--Park St./Medford'55, and'.168 ' Florence St.,*Melrose.*Mass. -r ; l^BRITTAINi ^Alfred', Jr; .(M 1938)v-Chief Ehgri, //WitHermakeis (Canada). .Ltd., 593 Adelaide:St.,; |/^iahd 138 -Wheeler Avel; Toronto,'Ont.-, Canada. . , WagschaT Associates. 1131 Majestic BldgYDetroit - . 26,.and 715,Livernois Ave,, Femdale/Mich. Y'. - BROWN,. W/Maynard; (A/1930)'Secy;-Tteai,. 'v, CaWmadrreenri.W'NeYbjs.t/e'Yr.-& Co./'1r.7.t.h' a<-nd--Federal S.t.s.i.., /, BROWNE, .Alfred ~L.' (M- 1923) Repr.. * Illinois * Engineering'fCo.,-v'253;': Highland'- Rd/ . South/ ? BROCHA, John P. (M1936) Buyer, Montgomery. V Orange, N.'J-Y -'-r Y ; - ;> Ward- &'^ Co., 'and 1804 ,N.E. 45th A've.i 'Port-.' - BRUCE, Marshall (AT942) Secy.>Tfeas.*: George . lahd,sOre. > -' - . ..* . ". ' - W. Akers Co.,16525, Woodward, Detroit.3, and . ?BROD,`BerinuAM.'(7T941)Asst:ProieciEhgr., - -4184 Bishop Rd:/Detroit 24/Miid^ . - :.'/'American Airlines^ New. York'Municipal Airport;' * BRUEN, -.RobCTt: (M V1945) . Partner, * Robert . ^/Jackson':Heights, and.*63 Sycamore- Ave-V Mt. ! ^Bruen & Son/1164 Grand-Avew Oakland .12, and . ^r'`^CTnon,^NJ'iY/.-.- '>' ` .- .-1430 Grizzly;Peak' Blvd., Berkeley 8, Calif.-. -iBBODERICK.-Edwln L:* (M 1933) Mech..EnEr...: iBRUNDAGErF. Ward (A-1946r7 l940)/lst LL, /'i/'*9696lNofthlawn-Ave., Detroit 4V'.Mich;.. ;'*: . . ' Fort BUss,'-Texas. :: j*'" 1 Y.' / v ^-BROI>IEi;Aarbn' H'. (M;1942) Pr*'jv Brodie & BRUNNETT. Adrian L. (M; 1923). Mech.-Engr.,^ ^Sonianc.,'1329 East>Fort St.,.and 2324-Chicago '"U. S. Supenrisihg'Architects Office.7 Procurement^, ^*^^tvu;BIvd:.iDetroitniMich:' v. Sr v 'Bldg.;JWashington/.D;.',C,^ and P.^ O.. Box^36, ;- -^bRoKAW; George K/(Jf 1945;-A 1942; J 1939; V , - Rociville/Md. ' ' //'. / -. ' - ' _ r^.`5:;:'1938)?:Gon jEngr./'Russ.^Bidg.','235 -Mqnt^; BRYAN,WUUamL./Jr.(A1946;:7,1942)\Gapt:;/; -r.-w/--; gomery St;, San-Frandsco/ and 593l VWhitney' ' 'Y * Mass.YDivision/of - Occupational' Hygiene/ 23 " .StM Oakland-9,^Califr _ Joy St., Boston 14,:Mass. ` /' , i v| Y| *. < s| Roll of Membership ' 17 BRYCE, John- ' H..' fM-1944) Hunthaven. Inn. . BURNS,'Harold J. (A 1941 ;.7 1939) U. S. Navy, .' Dakota; Minn.-.-.-'--., -. ; * ' and; l05 Ailen-Rd., Friendship Station, D: C. - -BRYNER, John J; <Af; 1942) Chief Engr., Roosb-- - BURNS, Robert' (M 1944)' Htg.- & Combustion' -..velt Hotel, 121 Baronne'St.. New'Orleans, and - Engr./Miles. Equipment/Corp;, .45 West 45th St:. . ' *5701-Canal Blvd/ New-Ofleans-19,-La-;' ' New-York, and * 54<EUiott'Ave.. Yonkers, N.-.Y. BUCHANAN/Walter P.. (M 1944) N. E.'Mgr:, : BURNS;, Rbbert- 0/(A 1944) Ca'pL, and *1704 *B. F.' Sturtevant. Co., Div. of'Westinghouse - S. -Travis St., Sherman,'.-Texas. .. .. Electric Corp.-, 89 Broad-St.. Boston .10,-and 26. . BURR, Griffith.C. (M 1937) Sr; Mech.,Ingr. - Durant Ave., Dedham,' Mass/ -' - ,, : - - U. S. Engineers, - Costum House, .Wilmington...' BUCK, David T. (M 1940; A: 1936) Pres./* Buck and Box 239, Wrightsville Beach, N. C; \ . ' Engineering Co;, Inc..- 37-41 Marcy: St-. and 116- BURRITT, .Charles - G. (A: 1916) Johnson W; Main St., Freehold. N. J. - - . : - BUCK, Lucien (M1928) ' Engr., Proctor & Service Co., 922 Second Ave. S.,-Minheap61is-2,.- Minn. `... ' Schwartz,- Inc.. Seventh St., and Tabor'.Rd., BURRITT, Edward E., Jr. (A-1941) .Field Engr- Philadelphia . 20, arid *105"-Jericho: Manor; ' General Electric Co., 1405 Locust St., Philadelphia. . Jenkintowh, Pa. -BUCKINGHAM, Robert B.. (A 1944) -Partner, and *202 Kathmere 'Rd., Brookline?- Upper-: Darby.-Pa. . / '; ' - -. -/Associated Southern Industrie^, 1161 Union BURROWS, Austin J. (A 1944) *237 Bridge St// Ave./and'510 Greer-St..;Memphis. Tenn. " ' Northampton, Mass. ' - - . .. BUENGER, Albert* <M 1920;.7 1917), (Council. BURTCHAELL, James T. .(A 1941)^. Pre ` 1934-37) Bldg. 'SupL. HotehGibson.- Cindhhati . Rushlight's; Inc., 407 S. E. Morrison St/ and i; :and 1204 Herschel Woods Lane,.- Cindnnati 2308-Northeast 31st; Portland, Ore.- 26, Ohio." - : :" '/ BURTIS, Herbert- D. (A 1945) Co-Partner,' BUENSOD; Alfred Charles '-'(M 1918) .Pres.,' *'Huhto--Prell'Co.; 15 E/ Jackson SL, and. 228 Buensod-Stacey, Inc;, 60 East 42nd > St,,:-- New . Meachem Ave., Battle Creek, Mich..' ' * York 17, and *33 Fifth Ave., New York 3, N: Y;- BURTON, Charles C..(M-1945)' Mech/ Engr--^' BUETER, Norman :E. (Af.1945) Chief Mech.. . Johns-Manviile International Corp./22 East 40th'- . Engr., *Holabird & Root, 333{ N.'Michigah Ave., - . St:. New York, and 206 Knollwood Ave.,' Mama- --- Chicago;-111., and 1600 Teal,'Syracuse, N/.Y,.; - ~ - roneck, N.'Y; -// .' -BUCHER, .George A. (A. 1945) Owner,'*Bugher BURTON, -W/ RusseU (A 1939) .Sales Engr - ' Metal Products Co...607.Polk Ave., Houston 2, - H. J.-Sandberg CoV? Portland. and *2816 North-- and.8I2 McDaniel, Houston;9, Texas.- -Y /" -east 19th'SLYPortland'12? Ore. ' 1 - BULL, Frederick W. (M 1942).Lt. U;.S/N. R.. BUSCHMANN. AKred . W.. (A 1944). Mgr . Chief Engr., U. S.-'S; James-O'Hara,-A. ,P: A; .90, *Newcomb fic-Boyd, Trust.'.Co." of-.^Georgia Buschmann Co./208' -E:. St.. Clair SL/ India-' napolis- 4,- and 3105 .College Ave., - Indianapolis- . Bldg.; Atlanta-3.. and:2554;Peachtree Rd. N.W., 5. led. : -Z . ..... , 'Atlanta," Ga.v: / 1 ;v BUSENLENER, Louis V. (M 1944: A:1943):Vice?- BULL, Harold A.'-(M--1944)` Sales-Engr'.,-* Kruse;. YPres/* Industrial Sales Corp., 52l City Park Ave-7 - '.Engineering Co./-24 Commerce St;,1 Newark- 2, - New-Orleans -19. and 300 -Betz PL, New;Orieans-'' N. J./and 137 Kilburh Rd.. Garden.City/N. Y..: . 20. La. / ` - - , BUNNELL/ E.; W.- (M1943) ConR -Engr/ *'426 BUSHNELL, Carl D. (A 1921) Pres./* The- 'Hutton Bldg., Spokane-8,'-Wash.' - Y - /Bushneil.Machinery Co., 311 Ross St., Pittsburgh, BURBO, W. G. (M 1944) -New England Mgr., , and -Rosslyn Farms, Carnegie, Pa. * /-..' - . Ilg -Electric- Ventilating Co./137 Newbury-St./ BUSSE, Herbert (M 1938) Chief Engr., Fisher - Boston,- and *13'Fordham Rd.; -West'- Newton; / Bldg.- Div., Fi9her'&.Cb., '417. Fisher- Bldg.', :and- 65/Mass.---- - .. ' Y - - 16760 Greenview Rd.. Detroit, Mich;1' BURCH, Laurence . A. (Af .1934) Chief 'Engr., BUTLER, Peter D. (M 1922) 127 Edgewater R. L. Deppinann Co.,' 5853 Hamilton Aver, Detroit 2 Rd., Cliffside Park. N. J. ' .and *78 Amherst Rd:. Pleasant Ridge/Mich.' .. BUTLER, . Robert ,P.f (A 1944) Partner. Kerr .BURCH, Walter-Ei (A 1945) Engr., Winterbbttom ' "'Machinery-Co:/608 Kerr-Bldg.,-.Detroit .26. and'-' v Supply Co.,' and *1429H W. Third St., Water 2061 Avon Lane, Birmingham,- MichY - - - loo? Iowa; . . . - - BUTT; Roderick E.-W. (A 1936/7 1930)'D<puty BURGES, Joseph H/M; (7 1939) R.--T. 1/c, ' Principal.Tech. Officer, Petroleum Warfafe Dept-. YU. S: S. Blower (SS-325)>c/o,F. P.,,0.,JSan .- London;-'- and 23 : Warwick -Square; ' London/' , Francisco, Calif.; -. and *1949., McGraw.Ave., -. S. W, 1.', England.. - ~ 1` Y Bronx 62, N. V; ` -.- . BUZZARD; Francis. H.v (M-,1939) Chief- Engr-?? .BURKE,' J? J. (Mr 1939/ Engr. in-charge; of.-Air - * CharIes S. Leopold, 213 S. Broad:,St.,-.:PhTla- - Cbnd.-Refrig., A. -M. -'.Viscdse--:Corp.; Delaware' delphia :7,* Pa.;-and 624/Wood -Lane,- Haddon^": : TrustlBldg., Wilmington.99.''and *709!N:.Broom : field; N/J/ . ` St., Apt.-5, Wilmington 34, Del. ' - - . ' - ; BYERLEY, Francis A./-3rd*'(A' .1944); I ngr , BURKE; John S/'(M 1942):Dealer Coordinator/ -'EbaSco -Services.- Trie., 2 .Rector-St.?.New;York,-- New Orleans-Public Service; Inc., 317 Baronne.-- N. Y./and 5147 N/Camac SL; Philadelphia. Pa? ' St./'New- Orleans.9;-and 3817.Gen. Taylor St.. BYERS;-Robert L. (M 1942).Chief Engr.T.*John- '- New.Orleans,.La;:.1 : Paul.:Jones,' Cary & Millar,'-'448-Terinihalr.Tower; -BURKES; Lloyd.C.' (A* 1943) *3030 Eudid'Ave.,' Cleveland,.- and-'2261 -Woodward/Ave.?VLake-^ '-Rm.- 313,'Cleveland, .and 3615 .Lmdhblm -Rd., ' wood/Ohid. ' - 7 '' / - /. A . ;.r'- Shaker Heights, Ohio. >' - V BYRD, T.T, (A 1936) Sales Mgr.?The Lau Blower' BURKLE, : James .L.Y(S 1945) Vr12 . Engrg. . -. Co., 2001*2029 Home Ave., Dayton 7,;and>2311. Student' (1946),r.Yale^UniverBity,'New -Haven/- . S. Sutphin St./Middletown. Ohio. ''ahd *60 Weybosset Ave.", Hamden;'Ccinh.' ':- ' BYRNE, Joseph-Jr(A.1939) Htg. Engr./* Kleeh/Z BURNAM, a M,, Jr; (M'1938;;A 1937): Editor; ' Heating, Piping &-Air -Conditioning, 6 N. , air; Furnace-Co.;-5329 N. E. Sandy-'-Blvd., and '- 6416 Nl E. Rodney Ave.?PorUand, Ore/ ^ ,Michigan 'Ave., Chicago 2;-and 9215 S. Dameii BYSOM, .Leslie L.' (M-1938) Mech. Engr./ Pub - .-'-Ave./Chicago 20, lit*--' , .*\V':'~V"--Y- --1 ~ , Wks. Design^ec-.-Puget Sound Navy. Yafd-.-.andcT BURNAP,' C. ;H: (M. 1941) Sdes; Engr.,VA:'-K. 1214 . Eighth St., Bremerton, Wash?.,. -/ ^ '-.Howell Co., 1635`Syndicate'Trust Bldg.? St.'Louis I.' and 405 E. Swon,-Webstef.Groves, Mb. . ' . BURNETT,. Earle'S.: (M. 1920) Sr. 'Mech/Engr., - - Bureau;ofMines, .Amarillo Helium - Plant;'P.' O. ;sCADENAS, Mamiel A., Jr,.(7 1945) Plani Engr:, : ' Box 9ll/ and *4223 -W^t'11th;Ave;/ Amarillo, ' *U. S. Rubber.-Co., Apartado.2076,`-land-.CoJIe/'--' / 22, No/61, Rep.' Miramar. Havana; Cuba./'/ " BURNEY; L.; Byron-':(M- i944)v'ArdiC *1712'.- . Arlington,St.,.'Raleigh,' N;C.Y':/ BURNS, Edward J? (M-1923)-Geh'. Supt-; Reuben'. Lv:Anderson Co., 519 :Cleveland,'SL -Paul.4,-and/ lCADY, Edward F/(A.1943; 7 1937).Mech; E ngr, Y,The;Austin .Co?/ 16112 ;*Eudid/Ave/ .Cleveland,-.'.- arid 2240 :Rexwobd- 'Rd., 'Cleveland -Heights^':-:. 18/Ohib. Y - -Y />/-'. '?-Y y - CALCATERRA, Loiils A.. (A 1944). Mgr:/ Auto> ' v r* 4716-Aldrich: Ave. S., ;MinneapbUs 9, Minn.- / 'matic. Htg.*-Div... 'Bennett :FuelrCo/? 134*- W? - BURNS; Fred G. (M 1942) .Br.vMgr.-,- * Kewanee ^ Fulton, . Grand;Rapids 2,'and * 3111 .Reed's. Lake - : Boiler Corp.T-2014-2020:.Wyandotte St,,Tan'd. l036 ' .Blvd.. Grand Rapids, 'MicK/v' / ' r''/1 .. West 7l8t St,'Terrace,:Kanras.City, Mo;-.-,' ? - - - . CALDWELL,-Arthur a (M-1930)~Engr, L S'* >' BURNS,' F. ;< '(Af -lWO) 'New Orleans :pubiic ; - -Tafleton, 1500- Walnut'St.,--Philadelphia-*2,and:/ .-Seryice. Inc., 317 Baronne SC/New Orleans La// Z * 550 South 48th SL,'Philadelphia '43, Pa?. * ^ '`/I -- . ___Mech..Erigrg.`, *.Uiriveraty-bf.Mjchigan;;.237-W; 5^%^' //."TX Engineering Bldg./iAnn7Arbbr)"ahd7605 Oswego * , - St^^'Anri Arbof.' MicEuVli,'^-^ > CAJLL:'Jds*pli:(ifa938;V1936):Mgr.,.AirCond * My:;EmQH^msvGo/^2518iN<:BTOadsSt.;.Phila-' 12. Texas.* ... .................. .... CANTWEIX^Algernon ;B. (A- 1945) Solid Fuel ^ ' Engr.,iKansas-'City'-.Coal -Service-Institute. -540 : Dwight Bldg7 Kansas.City 6. and 3728 Gillhamr: - ; '-V . 'Kansaa-Git'y 2,*>-'Mo.'\ .^T' -V -V ~ :-V` " ' .t CARBONE;`rJjinies H.'- (AT:".1937).-*; Htg -Vent * r : Inspector/cGityof New_YorIc,-^Municipal Bldg ;New.';York;-:and>,;121il34-198th'SL;`iSt.VAlbans. i - ft. CARDEFU ;WllIlamvW.i(A. 1944); BranchvMgr.-; JohnsonrService:;Cq.`:^313*rBona^Allen' Bldg , ' v* '7 _Atlanta 3,`and 677PebblesSt.'S.W.;Atlantd. Ga * CAREY; Paul Ci7(-MJ1930) Cons;Ehgr.,r* Runyon ' -:& -Care>[,;,33: Fultbii St.; N.ewi>t 21'-aiid.3l Clare- " . -1 *4 7? -montDr:, Maplewood; 1, CARLE, WIlUam E. (L/i Member', M`1926) Pres-' * - jps ; Treas.vr.Cafle^B6ehling ;:Co.',' ^Ltd.7 ^164W 'r- g ;Broad- St;;: Richmond*20,Yand-40l5`VV,Frankling ,v-v&.VvC-':i'- . St;: 'Ridim'ond`21r'Va.."- : C.>:7'`. . i >. ^ CARJLETONr-Herbert G: (A1944)'.Assoc. Mcch - * .jEngr.',-`Maritime^C6mimssion,'::-Dept;7'of- Com-5^ T v" \ mcrce' Bldg.v Waghingtbn,. D.; C., and j^Box 143, * ** t-'-' . College Parle, "Md.`V ~ 7^ >t;"" * - -."Vi* S' CARLEY.ThbrnasS; (A 1945)'Asst.;Sales Mgr . v ^ v^" Minneapolis-HoneyweH'-Regulator^Co.v 2747 FouHh Ave..S-. Minnea*polis,*and`236.W.'H rankhn .ji St..-Mirineapblis'4r-'Minn;; r^O'.Vv CARLpCK/:Marldn.F._(Af ip36).CapU Gon)s:bf v Engrs...and 67i9.Plainview/.St.'-iioul8i';M67v5ii1$--*!^ai::^.r CARLSON,7darence' JrT (A.:l944) :OwheriMgrV,^i:''>i'%5^- vi? C.``J.-CarlsonCo.,2701R6oseyelt Ave.V and:*'2701' Roosevelt Ave''.-Indianaoolisi -1nd 1 -r.7: ............... .... - ___________ _____ ________ _ . -- OHeans>13ft^di:5810.*MaiBliaI FochiSt,-.; N Orleans19j `A*'&%. '7/ ^ " " " ' ^ ` G`''' ' ' ' r .Gen.-Mgr. 'oveiov St.- 4gr.:, The.'-Powers'. RegUlator-Co'.;*-2726rLbcust't.-'.&?i^5^ - s St.. ahd 6675.Washingtbn Ave.7:St.>:LoiiIs;. Mb7 VCARNAHAN,.'Joh'n-^H. (4>l40;','irsl9^)kMech'?M^^%^ .Engr;,.Costo'n & Frankfurt.-.5197ApcoV;Tower^and-1:ij:^^^^^^ , v *3116 N.: W. 26 St;,`Oklah6ma*Git'y.':Okla.77'7:"7>i-,'5L--Xi7^A^H:^; ' CARNS, .yernpnrj:;(A.-1945)rSal &rAppliratiqn^*-^pSi -Enerr.Minneabolis^ridnevwell;ReeulatorGo.7415u7r'Sr'C: I I (^RTER;.ChMterrA.'.;(Wi:I944).liIh?:Engrr CHAPIN,'C.'Graham,(M, 1933)-Treas- Hopson Hq: Seventh-Service Command; lrR.'&..U.-Div.1 SBChapih^Maiiufacturing Co.7-231`.State'Stii'-and ^andi*3071 Sbuth>33MSt.i'Omaha,Nebr.7- s i . 66 Kaire'Harbbur`Plf, New;Lbhdon.-tConn: . -v-' .CARTER/ Doctor, (A/rl934).Cons/ Engr.,*Hong-; CHAPIN. Harvey GIi(M l935)?Gapt.-,vU;S.AjA:F.Y .w;.- - - ;-kong.-;Chinar;',V .i'Vr-.v > . ^ - 883rd^Bbmb1Sq.^S00th^Bo'mb.irGroup-A P O ^ :.vCARTER,-::Henry-'G;..(A - l944)l'Mfrs: Agent'./ ' -7. 237;Jc/o'-P. M'.7San -Francix>VrCalif.,- and^8352--t---u' ^.-i-'^vY^4^f* 5505 BranchJAve.,.Tajnpa`'.4,.Fla;- *> T ..-Marylaud`'Ave;;'Chicagi'-Ill: *" *> ^ 'Z , -CARTER; 'John H.* XM'1936>TPartnd.' Bodme &/ v . CHAPMAN. D.^Bascom (M 1941) Dist. Office, - -- r n Cartef.Vl22-A**W.-Lockw6od Ave..,and #710 Key : Clarage/Fan.'Co.i'.'323/Curtis- BIdg. 2842 W r-AVest-Avei, Webstd' Groves l9;-Mo;";' --f: , v-. Grand ;Blvd..7Detroit; 2. and .16713 Blacbstone, " . % _ : CARTIERrMarcel E.. (Af :i944) R^earch hngr.n I^trijitvl9. Michir:/* ^--^;^; 7 - ' 4.*^ ' ig? / *;v* American'-Radiator & Standard Sanitary.Corp.v. CHAPMANfv^iUisiiii " 1936) Lt ^.;-C75.Bronx :River. Rdi,-Yonkers 4, and l42S Mid-, f- Cbmdr7;VU;7S. 'N.; R.v' Offi<xr;mi Charge Navy ' ' " " /yS : ; rland:;Aver,.Bronxville7 N.' Y. "V- sr* --'V: Recruiting r &'-'IiiductidiC - c/o ''Navy."-Recruiting " CARY?EawariiB7-(ifa935)'.CapU U.'S.-N;r.andr - / Statibn, ' P;' Ov BIdg.7.and ;31. Northview Dr , -> 7T', %.V. 448 Termihal:To'wer, Cleveland.l3. 0hio.-- / Indianapolis,-Irid;^'^.."^: ' ;;'77-7c77li7i-'' v ^ .CASE.rDelbert-V.^CAfj 1937)'Engrgr. Consultant, War;.Foodi/u ---*-*~** . ^-Kansas "City, CASE;'Dohald' _ . ..____ ...----- -- ----------- ------- .... . . --. ___________ _ . w. -v..^ - ,ra W.'.C.'.Wieddtmann &^Sod, "1820 -Harrison'St.,7 7-CHAR,'-'Raghav-D;^(M.1945).{Owner. Industnab .......... -Kansasr.Gity'8rand 8631' Hiawatha -Rd.7-Kansas :r."7 ''&:rA'gricultliral iEngmeexing .Co.;743r-Forbes St ^ '" ' \C- 7rr^ '7?';:''7.rBonil>ayJ7l',iandr-_``VUla7Vyla,''-'17th4Rdr; Khar, :>.;< -''4 ?CASE; Walter^ G.;(A 1930).Mgr.'.Ideal .Boilers Sc*v7..B6mtay,2r, 'Indiji- ''-^-1 .^"^77 77t % '.`.ORoaadjaiaVtorrtTe/i''.CfVtd/t.' ..Ideal -UHonu.s.e, .CGlrr*e*a**t'.Marlborough jCrUHiADRlLPECS, PaulvL.* (ifvl938) Mg--r--.-^SP.t /O^--w---n--e--r-. ' St.. 'Ix>ndon,-_W^' l, ;.ahd *667-The - Ridgewav: .- Walsh & Charles, Ltd;, 206 Tnbune: Bldg...a~nd- r.. ; -Kenton;,-.Harrow,-.- Middlesex.- -`England.',::-7' 45 A.sh.'Stft'Winnipeg, Canada -~ . CASEY/- Byron -t., \M-i 1921)' Mgr.',-'* Northern: CHASE.^Ajrthur.r M.;: Jr... (M--1938)-. -Owner, * - ^ . District,-; Ilg7.E^ectric .Ventilating- Co., '222 . N ^.'Production'Equipment<Go..-:-P. ^OlvBox'895. r J * y ?||L LaSalle- St.c, Ghicdgo-17 and-,404'.:V!ne Ave.'. Park _'-<316iKeller/BIdg.,7Hojistbh-.l7and;3333;02'ark1.St: .... .:Ridge.-TU.^iVr'7JXSS 'TV ^CASffiY, Lutlier^H. 7Jr7;(/1941;1938)- C p -.'.-.Houstoii^ir.Texas.T.-'-y-'r'-^'`'""71.<; 7., VTV....; -'CHASE;;Chauncey; LV--(Af -.1931) ' Cbii3..-Engr.',- ?3 7 C. E.,1-Asst.-Wing7Engr., Hq.7 West Coast' Wing. - T> 15?,WIlliaih' St.7- New ,YorkV5,' arid;222sCIiafl; 1502d A.-A; F.;'B.rU.', P.-D:,: A^T:. C.. 49.bo rth VRd.V MMhasSt;'-'N;7Y.7:77';^ : ; ; v St.; San Francisco 3,` Calif;/ ahd'*.620.-W.-Stephen? - - CHASE;; Jim C5. (y^.1945).* 17297 Fleming Rd..'. v: - St;f Martinsburg,' .W.- Va: " 77^7V'---'{7' '=' "; 71 Louisville'.S.iKy.-'-'TiVV';'.. ^S' - . CASKEYy: Thomas C. (3/--1943) Owher;7Caskev .: i.CHASE^P'eter S:-;(A^1940) .Owner^*936 Oak-St.v< -'.Engineering-JGorr~l 736 7 First"AveV7S., -'Seattle A.-- and'1167-Ferry. St^.Eiigene. Orej v-'r 4-M1 ;.-,..and * ll642^-26th Ave: S., Seattlei88:* Wash CHASE,TlR^.E.firjr; 7(A 1946;- J f I941)>Capt.;.' > . .CASSELL, -WilUam : 1936) 7 Prin p ;-^-X*`>1389tK;A'.viA7-'F.?;`B^-U:;JjrN:-'A:"AVv7'A.;.!I)5'C;,,- v William:L. Gassell; 912Baltimbre Ave:;-Kansas - A;?P.7p;v856ric7b,,Pi'?:M;;-;:New7Y6rk.';N;f{V.,`:randi ..: City, and R7 F.'D.:6, Independende.-'rMo. JCATLETT,.;...W.r-A; X-4 "l?^);-Pw- n__e__rr*C__a__ti_e__tt >/;il7--N/Tacoma 'Ave.'/-Tacbma^''Wash;:r7T7''"':7 Vft'; .''.CHASE, RogefrE; (A ,1939) Pres., * R; E:;Chase &` .. . . -r'-C; - . 4EngirieeiSivl3507'Bucknm-\BiydI,^and .9602r-'El-7-''.,Gb.;r'lnc^-.Tacoma' Bldg.,:.Tacoma 2,vand 117;]N. " idll - Patio Dr.,- Dallas' 18/jTexa8. v'.; 7*71 ,-7 ...5-.x- c^-.Tacoina'Ave.,'Tacbma 3, -Wash', v. CATdN, Ross R:, Jr. (J 1945) Pres.V Xaton ..SCHATFIELD.-Arthur l. (U 1943) Htz & Vcnt^ n - ' l' OCAVANAGH^P.';.-. AVr-? (if'/194^) ;M^-*TKe.^^ySt.T:Kimsafl-.Gity;6;ah.d.437'East 72ndSt;;-Kansas:- -..Hennan.Nelsoh'Gorp'.7l015-ChestnutSG,:<PHiIa-ir'.;7'City-5rMo.'/;.>.,.77;7y?7 * ....... r~ tpARRiER'^ Eafl;!G^(M7i936l; ^1929) . .^Mgr.,-Carrier7Gbrp.^v419' BoylstontSt^Rm: Boston-16,;and' 326'Highland -Ave^-WincH^ter, - - Mass!,'vv7 .;V i .V,, TTv^.'S ..:CARRIER.yWmU:-H.-.;(eo3raryV3f<^frf>/S*^a^ : Member.`,-M'';l913)',^{PresidnIici-AleTTii>eT'f].{Pies','-^'^K^^'' :' nd 2570^Valley Dr:;'Nedrow,;N7Y;`;r7^k'7>. .:..C.S...A.h...Re....eR...t.`.O:.M....L..e..U..t.^..i.D7....W.a....n.d..i..re..l..^i.^..I.E^...;..:?..s..4.r..(^..A.1....^0..l.^7i)0VtPhLP4rrhMeSs,S.i7;7v.t^^G^WGWar^crobo^IUbl"7d^7&4iSS^iWg: f XaceiProJ.e.E^K,, side; and> 216^'40th'?Ave:ffBaydd^:I^I^N:7YrV>>^^^. rJCairipbell'Heatirig Co.;-2445;Gharlotte.St7 Kansas :..-CARRdLt.'Edgar:Efl'(AM939) dwneffi'kl^Mir^ftjSS^ ` ^Cityi8,.attd-;6100L'Harrison^'Karisas`,Gity.'4;sMi r rhace Go:i '5329'N:iE7Sahdy7Blvd77and-`2434':i:>^->'^ ^^Ci^PB^L^G.C>XM.19^ySr?Pa^er..VCamp-^ iS-'Northeast^rd;Ave.,''-PbftlaBd?I3rfOre'.'7$i?"^5;-<5?^i;f'-iAt^E ^^itT5eU^Elsey;GQ^325^.Nera:Bldg.rSali::CakeCit "^'^^i'd;^444 Emerson'TAve7. Salt' LakevGity45.iUta] `CAMPBEiLii^Robert? E^M-fer945).Majo: Ul?s5 Xt'AfmlkZanXfm BQA/1 A*,4. CARSEYi K,-.Manufacv...3?x.v..^ w<^J,,.u6,1.y.v<tro7>-^rf-Y> sjGincinhati; r25,stand'*'359_~;Hbwell,tiAve':,,;;7Cirrcih/-^s*^^; ; Area -7A.!7I>ayto'nr and 355;Mbrris'SG'."Osbom; CHERNE. Realto E., (M-.1938;r<7r:1929) Con ? x Ohio'.;.V; A. CHADWICK;, John;B. ' (M 1944) ;En^g.; Rcpr . -!'Textile'7'Air,bSystems,'7LtdM-; Bury7;Rbad..Works- ** ^ En^-.;?.*31-l;Alexan'der St7.' Roch'ester 7, N 'Y CHERRY;;.-Lesteri, A;*/'(3f l921)'`iCons , Engr "CherTyrG..u.s..h..in.g..;&.P..r.e..b.l-e;` 3--6-1---D- elaware!Ave v. ,S _ , V-r" *&m & 20 :, .-:-r *Heating Ventilating . Air. -.-Conditioning1'.'Guide 1946 ; - CHRISTENSON, Harry '(A 1931)'Co?Partner,'? .CLARKE, John H. (if 1942; A 1941) AssC Marine \- /'; -.Hunter-Prell Co.,', 15-19. E. -Jackson.- and 121 , . Engr.. MarinsKip Corp;, Sausalito, and R.D..2, -- Sunset Bivd.,-Battle Creek,'Mich:-'v . Box 583, Mill-Valley, Calif. - .' . . , ; CHRISTESEN, Martin C. (A T944) Field . Engr., ~ CLARKSON, Robert C., Jr.'.(Af 1943) Cons.- T .Sarco'Co., Inc.', 475 Fifth'Ave., New. York/ N. Y., '/ Engr.; *1006 Edmonds-Ave., Drexel' Hill, Pa.'' , ..and*196 Everett.Pl., Englewood; N.-J? - CLAY, Wharton, (if-.1939; A- 1938)- Secy., Na- 'j CHRISTIE, J. A. - (A 1943). Mfrs. Agent. #60 ..tional Mineral Wool Assn., 1270 Sixth Ave.-,' Rm. ` --: .^ 1Front1 St.- W., Toronto '.f, and 46' SpencerAve., 2906, New York-20, and .127 S. Broadway. .-/ v Toronto.3, Ont., Canada. -' . . ' . Nyack, N; Y. ... - - - ' ' CHRISTIE, Robert W. (A 1945) Research Engr., CLEGG, Carl -(if 1922) Dist. .Mgr., American ; . United. States Testing. Co., Inc.,-1415. Park.' .Blower Corp.,- 550 Dwight Bldg., and -3513.. " `-Ave., Hoboken, and 722-Hollywood Ave... Ho-' . .Gillham. Kansas City 6, Mo.- - - - Ho-Kus, N:J; / *. \ CLEMENS, Joseph D. (7 1942; 5 1940) Major, . : . CHRISTIERSON, C. A. (if- 1945;. -A 1939; . A. C., *Box 5,' Base Hq'., Kelly Field, Texas.- - ' . > ' -7.1937) Mgr.,'* Air Conditioning-& Engineering CLEMENS, J. Edward (if 1944) -Engr. in charge. _ Co. (Natal).. P. O. Box 2421. 91 Smith St.: and .'Plant Engrg.-.Dept., Allison' Div. .of; General . - 316 Cato Rd.,'Durban, South Africa/ : . . Motors Corp., Plant No. 5, P. O. Box 894, India- ' CHRISTMANN, William. F. (A 1931)-Engr... . riapolis, and *2625 N. Meridian St.,. Indianapolis ' ' Kroeschell Engineering Co., 215 W,, Ontario.. 5.Tnd. -. -St.,'and 6551-N. Maplewood Ave., Chicago,.111. . CLEMENT, Eugene R.,, Sr. (A 1942) Pres.,- . CHRISTOPHERSEN, Andrew E./ (Jf 1935). "E.. R. Clement, Inc., 297-Washington.'Ave., . . ^.-Boardr-of'.Educatidn, Amundsen..'High".School,' :.and-205 .Washington Ave;, Bridgeport;!, Conn. ' 5110?N; Damen Ave., and 2923 N: Kilpatrick - CLEMINS. Richard J. (7 1945)-Jr. Engr., Carrier ' '- Ave.,-Chicago,-111.' ' ,;Corp.,'.300 S.- Geddes.St;.-' Syracuse, N.* Y,, and -CHU,Yao-Haii (7-1945) Student'Engr., - Carrier' -' ' 1614' W. Scott St.Milwaukee 4, Wis. .. ; " . ' .. - v.-. - Corp./ 300. S: Geddes St., Syracuse' l. and 1205 CLIFTON, John A. (A ' 1938) -Mgr.', Renown i./. Harrison St./Syracuse, N.vY.- . /^v'. ' Plumbing Suppli^,.Ltd., 236'Parliament St., arid. - : CHUKWUEMEKA', Nwankwo'(7:1945) Student, . 369.Belsize`Dr.,'Toronto, Ont.,'Canada.-' .' " -. .'v- 'Carrier Corp.; 300 Si Geddes St.-, Syracuse l/N.Y; ' -CLO, Harry E. (A 1943;'7 1939) Engr.;-. American/ .' CHUR,.Charles H., Jr. (A. 1945) Mgr., W. A. . -'Air Filter Co., 228 N. LaSalle St.',- Chicago -1.-.and *' - Case &'Son.Manufacturing-Go;, 115 N.-Geddes . -10565 S. Hale Ave., Chicago 43, HI. ' ' ' - St.,-Syracuse 1; and # 119 Plymouth Dr./Syracuse " CLOSE, James W." (A .1944)-Pres., Sheet Metal- ; 6, Ni- Y. ' r - .......... -V^. r; ? Workers .Union,'620 S. Ashland'Blvd:,'Chicago, CHURCH, H./J. (if .1922) Mgr., Darling ;v and 6114'N. Washtenaw-Ave.,' Chicago'45; 111::'-'. ` : -. Brothers,;Ltd., 137 Wellington. St.' W., Toronto, - , CLOSE, Paul D.* (M 1928) Tech. Secy.. Insula- - - . and'358 Main St.' N., .Weston,.Onto/.Canada.' '> -..-tibn-;-B<Mirii' Institute,-111. W.-Washington Sti, y v CHURCH, Lloyd M. - (Jf 1943) v Dist.: ' Mgr;',' . Chicago, III.- >- .' . v- a Carrier'Corp., ,12 South' 12th4St.;?Philadelphia, r CLOSE; Robert-.(Jf 1938)-Ch!ef Air Cond. Engr.. ' - and 21 E. Levering Mill Rd., Bala-Gyhwyd. Pa.~ . . National Broadcasting-Co., .30 Rockefeller Plaza;, CHURCH, Richard A;-(7;1945) En^.. Carrier \- ; New York,.N. ;Y., and 185-:Glenwood'Ave., - . '. *-Corp.. S. Geddes St., Syiacuse.:and 134 Oakley' - Leonia. N. J; .. , 1 - -. - / - Dr.vSyracuse 5, N; Y.- ' -V - CIIYTRAUS, Oscar E/.(A 1945) .Owner; Oscar E. CLOW; Sherwood A. (7-1942) 1st. Lt.r Signal ' - .Corps.,''* Signal! Office, Camp Howze, Texas, and - - - ' -Chytraus' Co.,.328 W.'Second .Si; -arid* 1173., . 109 N. Ghatsworth Ave.i Larchmont,-N. Y.., '-'.South.llth E.,-Salt-Lake`Cityi'Utah; '..' . `CLUGAS, Edward T/ (Af. 1944) AppUcation Engr.:;. : - ^CLAPPERTON," Robert (A :1946;,7 1944):Engr.. " '. Minneapolis-Honeywell - Regulator - Co;.-. -4030?'.' .* Dominion-Rubber Co.',-Ltd:, Engrg.--Dept?,. . Chouteau .Ave.v St.'Louis-10, and 6707'Arthur v --v. 550:Papineau-^5t?; Montreal, Que.,' and 25 Chester ' Ave.. St: Louis9, Mo..,.- .* -?' . - .-.--/ Ave., Town*of Mount-Royal, .Que:', 'Canada.1*-'-' '/ COAD, J.'Dehhls (A-1943) Service.Engr., . D. C. CLAPPERTON.iT, C3yde - (M'1944): Vice-Pres.; - Air .Conditioning Service Co., "1125 ;Locust St.-,. '-': ** . t? Michael- Stuart Co.,- Ltd., 116.BIbbd St;- W.:, -. ' : 'and 68The Kingsway, Toronto,-Ont.,:Canaria.-; . - ' St: Loiiis lrand 6439 Lloyd Ave., St.;Louis 10, Mo. - ' COBURN, Joseph B. V. (if. 1944) Combus. & CLARE,' Fulton-Wi (if. 1927). Mech. Ehgr'.r U. S. ?. 'Division. Engineer, 50 Whitehall St.,' and *935 7 Plymouth Rd. N.E.,: Atlanta, Ga. -V' " - . Service: .Engr., -International Chimney; Corp.,. -Curtis Bldg.,.-.Buffalo, and 189 Mill St., Wil- - - -Iiamsviile,.N. Y.-- - - COCHRAN, L. -H. (M 1934) Dist. Mgr.. *Ameri-V^ VCLARK, Albert Ci (A -1939)'Capt:;:',U..:S.-A':: : -can'Blower- Corp:, 625.Market St.,.San 'Francisco-" . 0-272843,-.and8705 .N.;.-.Foss''-Ave., -Portland'; 5, anri 130'Ganiirio Del Mar,,San-Francisco; Calif 3, Ore.v" - -s-.! .GOCHRAN,: Ludus D. (A 1945) *3447 Logan - .CLARK, Allari'M.:(M-1945; 7 1942) Sales Engr;, Rd., Youngstown, Ohio. ' . ` ' ; / /. ,.z_ ~ ,, ' Canadian Blower. & Forge Co.r Ltd., 1221-Bay -1 COCHRANE, William (A 1944) Air Cond;. Engr.. j St., ;Rm...301',-Toronto 5. ;and 11. Langton Aye,.' , Federal Shipbuilding & Drydoqk Co./ Engrg. -. .. _,'TorontoT2, OnL., Canada.; , A Div.-.vHull Dept?, 744? Broad St;, Newark,; and ' r: :--CLARK,^Arthur'E.\(A; 1945)-.Engr;r-Grinhell; ' *91 Beech'St-, 'ArKiigton, N. J; ''^ .^'.'NCompany'of `Canada, Ltd.,;2440 Dqndas;St.-W.; COCKINS, William W.(A194l;7' 1937) Scott and 49 Mouhtview Ave., Toronto 9, OnL..Ganada.; 1: - Co- 243 -Minna.SL,-San -Frandsco.3,-.and *555 1945)-`Estiiiatbr.'Pniet i' 'Cragmont'A've., Berkeley.8, Calif.'-- . : - - .'Sound Naval, Shipyard, and 10 Schley Blvd.', w ` Bremerton, Wash.. .. ' - ~ COCKLEY, Jortathan E. (if 1943) Htgl &VAir " -Cond.-Engr.,*Indiana.Gas .& Water Co., Inc. v ,'CLARK^E;. Harb!d (if 1936)' Mfrs. Agent; 600 ' - -Traction/r.Termirial : Bldg..;.Indianapolis''9.-and: , ., Michigan'-Theatre. Bldg.,- Detroit 26;: and 2539 -. i-3463-N.'Sherman Dr., Indianapolis l. Ind.'"-r f:-.v Lakewood, -Detroii'15, Midn* '. ' * ' ' COCKMAN-,': Thomas E.' (A 1945)? Salesman:. -- - CLARK, Harry' E; (A 1944). Mfrs. Repr., #P. O. - /.B. 'F.-Sturtevant Company of Canada, .620 ' Box370,/Houston 1, Texas.' .. Cathcart St., and?4823; Patricia Ave:, - Montreal," - CLARK, 'Jaznes- 'R.'-` (7-1942) ;skt.,:,A. S/; N.. Que., Canada. . ' ^?.' "-'-/r- - - :..v ?.* 14053050;.*24th' Depot- Repair _Sq.,r 24th Air CODERE, JeanrMoise (A` 1944) ;Dir.,^'*Codere, : :: Depot GroupT A: P. O.'264,vc/o Postmaster, San ' : Ltd., 18 Wellington N., arid;71 Brooks,_Sher-v v-: > Frandsco, C^lif.. and'1501Pecah.Ave., Charlotte vbrooke,-Que..Canada.: '. J' ` '?- - ^ 4 N; Cv- ;-W "V, -v5-; COD'Y,'Henry,'C. (M 1936).Sales:'Engr., Herman- . -, CLARK; U. O;. Ray (if 1944) Dist. Mgr.; B.T::" ; GoIdner-.Go:, Inc., 425 W; Lehigh Ave?, -Phila--.-/. - iSturtevarit Co.; 36 Pearl SC; and'230 Faxmington - - ~ delphia 33, and *7336 North^ 21st St.,'.Phila- ':.-- 1 Ave'., Apt.lGSrHartford, Conn,'.-;-:. ^ delphia 38,.Pa..-._ - /"?'.?-,/.\" .. - ; - v ~CLARK;jLynn W: (if .'1944';>A>i938)rEngr;"&-;- COE,' Seymour A: (7 1944; S 1942) *54 Waverlyc ; r ,^Salesman;-* Hall-Neal Furnace- .C6:l ,1324 .. Ni St.i New Haven, Conn, v--' ?- Capitol "Ave.,' arid; 737. West'^32hd' SC; Tndia^-... COFFEY; ; GeorgevB.. (A 1945)- /Fieldi Service napolis^IndJ'H^-- Erigr.,*A.',M.; Byers Co:,; 111 W.- Washington CLARK, Robert J..(A 1944)*Factory;Repr.; *3032' . . St., Rm. .1217,,-Chicago 2, aild,2311?,West?X11th. -r^'^Sevtrith<AverN^St:- Petersburg,^: . Sto Chicago 43,-IU.- - , COGHLAN, Sherman F.4(Ai.1937)?'Pres?,? J.VM;, TCleYeiand 3,'and;`y -Montgomery & Co., ^Incl,- 306 ;W.' Third. SL'Lbs; " ,'Ohio.'-; ' \ ^ Angeles, and?* 414 Ninth St., Santa Monica.^Califr wmi ?-?? 'Roll of Membership P -~ : - -, 21 ' GOHAGEN, Chandler C. ?-(Af- 1919)? Atoht., CONNELL, Maurice H. (Jf .1945). Cons. jSngr.. *212.Hedden Bldg.,-and 235 Avenue G. Billings,, Maurice -*-H. - Connell &. Assoc.; 816 Langford / r-' ; Mont... - `-Nr' ' ? ' - ; Bldg./ Miami-32; cand 1101 N.; Greenway Dr., -. ' COHEN, Milton L.- (7 1945) Asst.'Engr./Boston -Coral Gables,-Fla; ' ;. -.' v. .. . Filter Co., 43'Harvard Sq., Charlestown, and'*.Ill CONNELL; Richard F. (Jf 1916) 'Mgr..- Sales ... - Atlantic Ave.;' Revere 5I-.:Mass.' , ' .- '.' . . ' Engrg/Div.. U.- S. Radiator Corp.,1500 United - ; . COHEN,. PhiUp (Af*;l932) Dist. Mgr.. * B. 'F. ' Artists Bldg.-,,Detroit 31, and 2970 Burlingame, - . ' Sturtevant Co.. 933 Leader Bldg.. Cleveland 14,-* ' Detroit, Mich. '- / " . ' -- .? . and 12805 Shaker Blvd..' Apt. 511, Cleveland CONNER, R. M. (Jf 1931);Dir.-Lab. *American - .' ' 20, Ohio. - ... ' ` - Gas* Association Laboratories, 1032 East :62nd - . COHN,'Henry `(7 1942) Owner,-Republic Heating St.', Cleveland-14? and 2459. Dysart Rd., Cleve- - ' & Cooling Co., Dallas, Texas. .'' , ' land, Ohio.? 7 COLBY, John H? (A 1944 ; 7 1939) *20 Wiri- . Chester St., Boston, -and' 25 Jefferson Rd., Wei CONNORS, Edward C. (A 1940) Engr. Custodian, : - Chicago-Board of Education. 5500 Madison-St., ' -; . ; lesley Hills, Mass.- .. '. -- - . and *6556 Ponchaxtram Blvd./ Chicago 30, 111.. ' COLBY, John R. (A 1944) Owner, *Colby CONOVER, Donald Davis (A 1944) Gas Repr.; *; . '. Equipment Co., 243'E. Ohio. St.. Indianapolis .4, . Philadelphia Electric Co.,' 5 E.,Lancaster Aver .1 and' 5514 Rosslyn Ave., Indianai>olis, Ind.' : Ardmore, and 430.Manoa Rd., Brookline?. Del. . '.COLCLOUGH, Otho T.. (A . 1933) American Co., Pa.. ' "... '-`'7- ' , - Embassy,-and 399`Hamiltoh Ave.,-Ottawa, Ont,, ' .CONOVER", E. W.' .(Jf :1944) Research-Engr:, :. -Canada.' ;'.. L ' . ...... - Detroit Steel Products Co... 2250 -E. Grand Aver/ .-^ COLE; C. Boynton (Jf 1940; 7-1937)-Owner. , Detroit 11.- and *9165^ StoepeIvAve..; .Detroit - -Boynton`Cole,- 1873 Piedmont Rd.'- N.E:,. and ' . .4. Mich: ' '. ' - '.*1843 Flagler'Ave. .N.E., Atlanta, Ga; " . CONRAD,-Roy (Jf 1935)' Salto .Engr., -Carrier. fv COLE, Grant ,E?-(A 1925). Vice-Pres. &'Mgr., Corp.,.610-1331 Third Ave. Bldg., SeattJe;l, and ' - Trane Company of Canada, Ltd., 4 Mowat Ave., _ *3421'BeIla Vista Ave.,' Seattle 44. Wash.- . . ;?" - and 112 Tyndall Ave., Toronto, Ont., Canada.'. CONROY, W. T. (A 1944) Htg. & Plbg/Contr , ; COLE,--.Harold S. - {M 1944) Engr.. Stone V Webster. 'Engineering . Corp.* 49 Federal'' St;,' . *.1525- Locust St., and .1810 .East 78th' St.. - Kansas City/Mo'r - . - ' . -- ' - `Boston 7, and *1960 Commonwealth Ave., CONSTANT, Earl S. (A1942; 7 1935) Salto Engr/. 1 - Boston 35, Mass. . : '. - . - Arthur-Forsyth Co.. 500 First Ave. S., Seattle 4. . . =: COLE,-'Victor (7 1945) Engr.. Carrier-Corpi, 405 * and 3015-^30th Ave. W.. Seattle-99. Wash- ', " , - Lexington Ave.,- New York 17. and 1555 .Grand CONVERSE, . Thornton J. (Jf; 1941). Engr., ' .'Concourse. New York 52. N. Y. - ' Douglas-.Orr,-'96 Grove St:, New Haven, and -COLEMAN, John B. (Jf 1920) Chief-Engr.. ? - Stoney Crtok,.Conn. ' ... ' ? ^ : ... *'-.*Grinhell-C6rp.,'P. O. Box 1435, and 237 CoIe COOK,. Benjamin :F. (Jf 1945) 1720 Overton ' -r`-AveT.;-Providence, R. I. ' '* : , Ave:;-Iiidependerice.-Mo. J - :. .. - /. .. -- -' COLFORD; JohnfA 1937) Pres., John Colford. : . COOK, Clifford B..(A.1944) Partner. *F? G. Cook' " -- Ltd.,;2007 Guy St.,' Montreal 25,' and 51.Upper & Sons,".102. Deerhurst Park' .Blvd.,.-arid - 337. .. ' Bellevue Ave., Westmourit,'Que.; Canada. ' - McKinley Aire., Kenmore, N. -Y.... - -; / . . . COLLE, S. S. (A 1938) Engr., ?& Owner, Air COOK, :-H. Dale (A 1938) . Sales Engr?. 'Perfex >. /. v CondiUoning Engineering Go.. 79 Vitre St. W.,- Corp*/ 500 W. Oklahoma.' Milwaukee,-and *5061 r ~ . Montreal . 1, and 4968 Fulton Ave., -Montreal, N. Idiewild, Milwaukee 11, Wis. - - " ? - Que.? Canada. - . COOK,. Ralph P. (Jf 1930) ; Supt., Engrg.. & . ,? ' COLLIER, J. Robert (A 1945) Dist? Repr., Taco . Maintenance'-'Dept.,'in charge of Engrg. -Div., ./ '-'Heaters, Inc, P. O.-Box 402, Minneapolis 1, arid - -Eastman Kodak-.Co., Kodak'-'Park'.. .Works, ' - / . '.*4808 Pleasant Ave.. Minneapolis 9. Minn. ' COLLIER, William I. (Jf 1921) Mech. Engr., Rochester-4, and '663 Seneca-Plcwy., Rochester,- _n?'y; . *W. I. Collier & Co., 3414-Duvall Ave., Balti- . . / more 16; and Ellicott St., EUicott. City. Md, - - - COLLINS, George J. (A 1945) Supt.', Barber - - Plumbing Co., Box'84; arid 529 Fraser, Houston, Texas. -. : - ' COLLINS, John F. S;, Jr. (Af 1933).?(Coundl, . 1940-45) Secy.-Treas.. *National District Heating . _ - Assn:, 827 N. Euclid Ave.,.Pittsburgh 6r,Pa. ; COLLINS,"Joseph A. (Jf. 1943) Mgr.. Frontier Cil.'Refinirig Corp.',-Oil Burner Div.-,'367. North-;' - . hamptori St:, - and <289 - Commonwealth Ave.? >. >- ' Buffalo, N. Y. - . - `. ,, -r COLLINS, Leo F.*(Jf 1941) Cons. Engr.,:* 14615. - --Prevost Ave.-, Detroit-27/Mich; - ' /.. ; ' 'COLMAN, ` ' Robert .* C... (A 1940) Vice-Pres.. - / McQuay, Inc., 1600. Broadway N.E.-, Minneapolis COOK, Russell M. (A 1945) Vice-Pres., Thatcher - . Furnace Co..- Center-St., Garwood,- and -15 After- - " glow Ave..' Montclair,-N. J. - -. - COOK, Vernon D. (A 1944) Partner F. G. Cook - ,' & Sons, 102 Deerhurst Park Blvd:, Kenmore, N.Y.'. ' COOK/ W. L. (A 1945) Owner-& Supt.. * P S Cook, 1722 Thomto St., and-609 East .21st St.,r .Cheyenne, Wyo.- * ' .? / : . COOKE,: William1 L. -(A;1944) Managing-Dir.; W.'L: Cooke,Ltd:,;Cor. Kent:'and'.York. St:, Newmarket. Auckland'S.E.'l,/and' 747-.Remuera , Rd.;- Auckland S;E.'2,New Zealand. '> -< ' COOLEY/ Edgerton C. (Jf 1938) Owner;* E C - .-Cooley-Co., 625 Market St.', San Francisco 5, and ' -: 7'P. O.. Box789B, Route-1, Los Altos, Calif..-'' , .. 13;-and 102 Exeter Pl?.-St. Paul 4,-Minn. COOMBE, . James JA : 1932) Vpres.,>.Wilham / COLMENARES, Caspar VIzoso (A 1938) Vice - ' Pres. & Dir., Refrigeradon y;Aire Acondiaonado,. - S.'A., Lamparilla No.'?9,'P. O'.' Box 210, and Calle - - 10~No.-34, Miramar.-Habaha, Cuba; - - . -rPowell Co.,.2525 Spnng 'Grove- Ave.r .and 2363 - Grandin Rd., Cincinnati.,Ohio. '- , COON, Thurlow E; {Life- Member; 'M :i9l6) * /.Pres.,;* The' Coon-DeVisser 'Co..' Inc./; 2051 VV * , COLTON;- Frederick R. (Jf 1945) .Branch Mgr., . `Lafayette,' Detroit 16,* arid^826-Editon:;'Ave./ Norris? Warming Co.; 94 Exchange-Bldgs.-. New'. ? Detroit 2, Mich:'-.> .. r- - . - St.?'- Birmingham, and'36 Palace Rd., Flat 12/ COOPER, -Albert. W. -(Jf 1944): Branch'Mgr.,-!. . Lo'ndoh'S.W.,2/England., -' ; - ' ...Johnson. Service 6b;, .-.-1230. - California St.: H - COLVTN;-Oliver:Dyer (Jf 1943) Pres., *Cargoc:* : Denver 4, and l213 0Iive St:, Denver 7, .Colo , aire'Engineering'Corp.,15 Park'Row, New;York.' COOPER; C.-H. -(A 1944) Htg/ Dept./CKase Co ** ' n. y.' ... .? "r" " - / 936 Oak, and *1345 East'22nd, Eugene/ Ore; CO MO,"Jack A; (Jf 1939)-Mech. Eiigr./* inde- COOPER, Dale S. (Jf l938; A 1937), Cons: Engr -v-'. - pendent.Plumbing Co., 171 Luckie St. N.W., and - -206: West Bldg., -Houston.2, arid *216 E.-Cowan.-i'. - - '2865. Elliott Circle, Atlanta, Ga; - ' ' Dr., Houston/Texas. . ' ' \ ' COViSTOCK.' Gleri M; (A /1926) Engr./ Repr.,. - COOPER, Doriald E. (7 1939) - Partner. * D E *L.,J..Wing.Manufacturing Co.. 1319'Murdochr- \Cooper:8c Son,'.540 Hood' St./ arid.740 Lomond '.: . Rd/, Pittsburgh`17, Pa. . ' ' - ??Dr.; Salem, Ore. /, 3: " CONATY; Bernard M.. (Jf 1935f:Mfra. Repr.,-. -COOPER,.George P.' (A 1044) Cbmbus.-'Engr..','- v ' .-/ *505 Crosby-Bldg..-Buffalo 2, andP:.0.' Box 342/. * Empire-Hanna.Coal .Co?-, -.Ltd.,: 805' C.'-P. R. Jerinings Rd^ Eden? N. Y.7` . .Bldg., -Toronto; and 27'Dartmouth Cres,.Miimco.~ : CONGER; Henry'L.: (Jf-:i943)'- Assod.?EriKr?:- :/Ont?/Canada; - - U. S: -Engineering. Dept./- Punahou, .Honolulu,- ' COOPER, ;John W. (Jf 1932; A?T925; 7^1921) " and>1550 K Young St:;;Honolulu"19. -TrH-.<7:*;*?^ ;Repr.?>* Buffalo/Forge Co.?' -2726- Locust St./..T .(*^v CONNELL/.E. 'C..(Jf,1944)..Supt. Construction,.-. St..Louis, and 612 Hawbrook-Dr., Kirkwood. Mo r ^ Sullivan ValveEngineering GoV?Box -688r' -COOPER/W.-B? (A' 1946).?* 163' Barlett -Ave , N . :- ..and 158 Lewis'St.; Klamath Falls, Ore?'; / *.' .Wi]braham,.Mass. . ' .' . S^^S!5^iwJ,'COOPERMANi?EdwanI:(yfl943L-S1940) Ensign.' Wart;StiPittsburghU3'IPa.-'!*; V,: -?--'??'?;COKBIT,;Charles A. (4 ;1943)..Pres.;.Corbii s SSJS^%5't.-5itnc..S225^S:.;Front>Sttt).and^90i; Centre?A : .Reading,' Pa."'cf~vy-''y.-: '. Jfe^^pg>^OOREY^;C^e^I^;:. Sr. \M \\945) i-Stip no CRAilYJames TOr'?(Af-;1944)' -Mgr.% Appliance . vDiv;,\# Hi^ni>Indu3tnes. Inc:;- 52X"'CatyjPark .. Av^.V%New,:Orleaiis'il9,;'.andi410?Gle'ndaIe^BIvd^ ^ >y- New Orleans^Liar* 'r^V-O'A- ' CRAWFORD;* Arthur^C: [(A ;?1938) JAirlCond -. tngr.',<-Potomac ^ Electric - Power .Co.-/-.-Wash" > :_ mgtbn,?and V429vButternut.SU -NtW.'.C-Wasliink ton !2.:D.C; V- ; rg> ~ .CRAWFORD,- Edward- F:-. (A;.-1945) .; Owner - M/B: Crawford;& Son.-.46:W.'Bridge SU.Vand ^ 43;W.- Fiftb Stt; Osweg6,- N.-Y. * :..*-? '"-1-' " 2- CRAWjFORp;''Frd`jA.v-(A-,1945)"Owner.- Home - v :Comfort;Heating Co:; 5131' Rbhins-Ave-, Detroit * . mmsz*'-" v / - 1942) Archts ~2720\N;:Greehide- * -- Payne St.vEvansU CRUMP,,-'--' ` CoV.-L . - 34- Braemar;> cucci.vvict . ^ _______ ______________ Engr.,-#50:Church?St:,"RrnV282,.New .Yorlc and :. .DABBS,' John T. {A 1940) Capt C A A* P O C4U61L-6B5^thT,SrtW.;.BllrU6a6m1dyph.,:?(iNf;:i.9Y4iii3:-rVA'c19;i2v9-j'PVar>tn-Ver;. V? 9C37r,-tc^/oSPto.s;tm?aSste5r: KSe;a`ttl'e. W' a"sh'^a.Wnd *3*3"0 N ' Ltt;-'aid'* 404-Penn3ylvaiua'Ave.;'"Irwiri;'Pa.-';--'' " t-^i'^ViCpSTAv-iCiro! Ay?(M'-.1945)`Merchandis< Engr. -^?5r7>^.^iWestin'gh6use'_'Electric'Internationa C:: -Pase< e^te^^.a^OOVER^EHB^M^Vmy^bise^ReprrAa'Geueiu ^^^^>^tf^<Ele?tricC6.vt2206>ICie;':pbwer:&?Ught Bldg -Hotel President;. Kansas'City;?Mo." ' Crew- Co.', -1539 ' Race ' St;, Philadelpliia^^.'Vanci ' -^Paolli'-Pa;-'-:;'-^^"-^..'-*: '*- . CREW, MorH8rW;=(Af.I944) Mgr.,:lndusrC6ntfol DlV* ` .'PprfpT! Pr*mi.inH.'Chnwr*cf vHa*I:. Mil : CRIQUI,`l__ ... ___... . -v-Buffaloj Forge .Cp.,-'490',Broadway.-`-Buffal6riand^ -/ 39,StVJohns-Ave.T'Kenmore.rNi-Y.^^ - - CRIQUI, yAlbert WE*'{M ^1944)cMech.^ Engr) C BuffaloTtbrge-Cp;r490 Broadway,;Buffal6yarfd , , r'89.D6rsetfDK^Kenmbre:i7,` CISMANrrrl^n>a.V-(Mr>1945;VpwMr;\mng.' ^ ^ Crisinan.'Heating &^Air;Gouditiomng Co.',;50? y , N.'- Larch'St.-.'Lansing, .`and ,'Apt:'252^C, >HiIJcrest ^4 ^Villager EaiuLVbsing,`Mich;--' V5 jp? .?\a i. CROFT.-Huber:0.^(3f^l94i);E)ept^H&{Mech?!j7x/ =; =:-Lngrg.r* University:'^of..Iowa;v-:'l22^. Engineering?' r-.Bidg., andi250;N6rth{St;,-Ibwa`City,............"........... CROLEY," f Ay . _ . . ....................... .................... _ \ CRONEi.Charles E:K34r.`.l922)'Prbs.'';V^Clu^ries'E^ *' ". v?%. -?v Crone"Co.rl656 N:Ogden'A've4 Chicago 14;' IU;6'^S iy?B - CRONE,vThoinas^E: ^{Life:Member'^-^AfSl9^0), . Retired, . 1 . -r*--i--~ - ; Jamaica 3 plicationEngr.V-Predpitfon/DiVh ..Westinghouse Electric-"Elevator " Cd.i '150/1Pacific - Ave.'ii Jersey i, City.-Iahd:* 717" Wiilow St'-vCranford^N.^J/'-- .^ ' f CyMMINGSTR6bert:J/<AA944';K/;440):-Engr Francl'A8c'Fric,Cb.v7109Kinsmaji;Rd..Clevp 'xCo..: St.- `Paul.'and 3721-47th "Ave/vS.^Minne- ^ ' DI.:A,aHLpILIoS|9lTIi'8RUO,/\'1MMfi;iJnTonh_.n'-'.Aa.V..'/(VM1/,W1'V:9,e44')vH.^dvt5of>F-ur>na5r. -c5e----'' - < . -DevelopmehtbPiv.,V Perfectiohr.;,Stoye^Cb.V 7609 - 5 ^ ................. .. ...... ,,r-Haye8-^ ^Furhacev`& 7Mamifacturirig.'.Cb:. '-.Ihg.c,, 231-: f.-- positi6n'PJ:.sLbs'Arigel^Cl6j. and>5145Seventh Ave.: Lo&Ahgeles'43,:Calif.-?`^-- rVy.>v ,. DAHMS,.'Alfred A.' (A 1944) Dist.'`Mgrr, Allis- -' " v* CVhiiaialmimeerrss'.'Manufiacturning .'eCoo.;..;'y;1'1441I00...v'`WWaallddhheeimim^'''*;'-)>.;''`: Bldg.,-;Kansas City.'6,';'and ;7431 Mercier;-Kansa8 - City:6,*MoSy e l DAILEYyT'X. ?;F.: ;(2f,1944) Typhoon Air '"" Con-r'- 'y-'_ T: ? CUMAUSKEY" Jeronie F. (Ajl940)1Minn^pblis- ;- .,;'Rdrig.: Engr.',V General ABSur'ance"'Bldg.r'-8C''St - Honeywell Regulator.Go'.'; 433-EC Erie,-Chicago 11;' ? George's SU.- Cape'Town^SouthVAfricaij'-i ^ v andV7706 Eastlake:Terrace;Cliicago:26/IU.V c ' -DALTON,--Robert.T. .(A':1943)l-Ownerr*Dalton^; m I 24 HeatingVentilating `Air.. Conditionings'Guide'r!946 . / DASTUR/Maneck N. (71945) Jr. Engr., Carrier DAVIS; Robert Hi (A.1945) Sales Engr., .* Johnson - Z;:. Corp:/300.-S. Geddes St., and 1011 Walnut Ave., - / Service Go^- 507 E/- Michigan -Sti,- and 633-'N..v.: Syraciise/N.Y.' -.*/ ". " ' - ' .. . ^Fourth Stri Milwaukee',-Wis-..' 5- % ' DAUBER,.Oscar*W/ (Af 1937) Cons. Engr.,> 224 DAVIS;C Telford R. ` (M- 1942). Cons. Engr.,. ' S/ Michigan Ave., Chicago, arid-532 Greenwood . : Ammerman.; Davis & Stout, Inc., 805 KI P/ .. -Ave'., Kenilworth, 111.- " - '' '. Bldg.. Indianapolis 4, Irid.- .. ' . .' v; r' /DAUCH, EmllO.. (Af 1921)-Pres.-, .McCormick ` DAVIS, Wayne M. (A 1944) Field Erigr.,. Field Plumbing Supply Co.,1675 Bagley Ave., and 729 _ Control Div., Conco-'Engineering-Works, Men- ' . //- . Bedford Rd./ Grosse'Point Park. Detroit, Mich. - dota,Jll.,andl401 Manor Ave/ Bo*990,-Munice, - - ". DAUSSAT,: Waldo J. (A. 1945) Chief Engrg. Ind. . ' . / r' Draftsman (Mech.).- Ur S. Navy, Public Works ` DAWSON/ Eugene F.` (M 1934) Dir.. School of .,/DepL;. 1015 Federal Bldg.,' and *4436 Elba. St., Mech. Engrg., University of Oklahoma; and 7l9 s **:'.'/New.Orleans, La., - ." .. Chautauqua St., Normari/Oklal ' '' : . , ' DAVENPORT; Lind . B;j(2f 1944) Chief Engr- DAWSON, Fred C. (M 1944) Engr./ B. F. Sturte- ..-"tv/eAir-Conditioning Co. of Southern California; vant Co:, 89 Broad St.,-Boston,, and * 7 Sutcliffe/ 1003.Santa Fe-Ave.,'Los 'Angeles 21/-and 139 ' ' Ave.; Canton, Mass: -! ' - ' ' - . ' , ".v /- Melrose Ave., -Monrovia, Calif. -/ . - ; .- DAY,. Harold- C. (A 1934) Mgr.. American:/. V':'DAVEY,. Geoffrey I. (Af-` 1937) Gutteridge, ,, Radiator- & -Standard Sanitary "Corp./ 1807;; : .^-^Haskins'& Dayey,. City Mutual Bldg., 60-66 " Elmwood'Ave., Buffalo 7, and 223 Woodcrest \f_ '^-Hunter St:,-Sydney.' and Netherby, Bangalla St.. Blvd.,`Kenmore,'N.vY.`:/. ' - ' ': / ` t-k ;> -.Waxrawee. New South Wales,' Australia. - ' DAY,- Irving M. (A 1936) Sales Engr., *Binka . ;DAVIDSON,-James W. (A 1944) Pres. &'Owner, . Manufacturing Co., 718;Mills:Bldg.; Washington . . ''iV DavidTOn; Heating Regd./Val- Morin., Co. Ter- ` ' ' 6. D. C., ahd 405 Cumberland Ave., Chevy Chrise . "-''rebonne; Quebec. Canada. ' ' 15.'Md. * " '- - - - ^ 'DAVIDSON; John :C. (Af -1940; J 1936) *4708 . DAY; Sidney S.'(A 1945) Owner, . Sidney S. Day,- T--: Isabel Ave., MinneapoIis_-Minn. - - .. '3333 N. Vancouver.Ave., Portland-12, and 447 '^/.DAVIDSON, L. -Clifford * (Af- 1927) . Partner, N. E. Hazelferri Pl:. Portland 15. Ore. "//. -j-..-`'Davidson/& -Hunger/- 220- South 16th St.,"' DAY, V. S.* (M 1924) Prod. Price Controller, . Philadelphia/ and 322. Winding-Way, Merion, Pa. .Carrier Corp:, S.' Geddes St.,'and 316 Highland /j.?-.DAVIDSON, Philip-L. -(M 1924; J 1921) Cons. Ave., Syracuse. N.'Y. -. .' . - - - - , Engr., New'Hope, Pa., and Greenville, S. C.- - DEAN,.Carl H,.(Af 1936) Htg. Engr., Oklahoma . v?vDAVIDSON,: Willlain,'J. (if 1945) Application i , Natural Gas:Co., Box 871, -and 1532 East 35th v. .^'"'Engr./oN.'O. NelsonCo.rv118t E: River St.,'and SL; Tulsa, Okla. - ' ' . . C-'/-602-Gaylbrd/Pueblb. Colo. - -- -* j ". DEAN, Charles L. (M 1932) Assoc. Prof. of-Mech: ..-".^DAYIES,*- Charles^ (Af 1945)' Pres.', Davies" Air Engrg., University of: Wisconsin/ 305'University " i.iy. -Filter.Go.% 250 East 43rd SL/New. York; arid .265 . Extension/ Bldg., Madison 5,.' and * 102. Grand :/ '`.s': . Goligni Ave.,-New Rochelle/N.;Yv. :* *../ - : Ave.,.Madison, WisT : :s* 1 T'.-: ./^'/DAVIES,-Edwin A. .(Af 1944) DisL Repr. Engr./. .DEAN,-David (Af'.1943)-W. Or (j:g.) A.. A/ F. ..'I's Hoffman-Specialty-Co., 1001 York St...'India-.' -v W-2139554, -Adjutant; ,12th Army Air'Force, ; . .napblis, Ind., and 3022 - Kingman /Blvd., Des v Emergency Rescue Boat Squadron, A. P. O: 825:: - ` Moines,* Iowa. --- .. '.. ,c/o Postmaster, New Orleans, La., /and *17I .. DAVIES, George W.(Af 1918). Mgr., *F. W. ' - Radford St., Yonkers 5,.N. Y. ' ' '' : / > Davies & Co., 19 Madaggan St.,.Dunedin, C. 1.,. DEAN, Edwin C. (M 1945) Owner, Russellville . . and P. O- Box 390', Dunedin.. N. 2, Colinswood, . Plumbing:& Heating Co:/ 113 E.'Main St., and .. Macandrew Bay, New Zealand. "--r - ' -:>' -. 901-' N. Denver, 'Russellville/ Ark.'.: Z -- : /.. DAVIES,'Richard H. (A 1946; .7.1943) Htg. &. DEAN>Frank. J,, Jr.' (A '1942;/7 1935;/S 1934) -.'Z1 "Mech.' Engr./County Architect's Dept.. County . Lt. .Commander,.-IK'S; N. R:, 1210 NavyDept.; v- f'Hall;.-Council,-'Glamorgari County,. Cardiff,' and - . Washington, D. C:,^-and;* 2822 S; Abingdon-St.v- [ y- >c/o 29 Grove Rd./ Bridgend, Glamorgan, South ' -Arlington, Va. - ' ;-V:'"Wales, England: -/' DEAN/-Marshall H: .(A-1946 ; 7 ,1938; 5.-1936)'- ' DAVIS/BertfC. (Life Member; Afl904). (Council,. -;1917) Big Flats, N; Y. .'/> -.. DAVIS/Charles (Af7938)`U. Si-Navy (Sea Bees);'. Secy.-Treas.; Temperature -' Erigirieering Corp..-/:/' 1338 McGee St.; Kansas City 6, and'6709.Cherry, - , Kansas City 5, MoV ' s^' Chief; Petty/Officer, U. S; N. R/varid'*1066.v ;/WaltonAve.,'New.York,.N.''.Y./-.. . '. - DAVIS,- C. ;R.: (M 1927)-Branch Mgr:, Johnson. , ;DEAN, Vernon, G:' (M-1945). Cons./Engr., 003 r /Murray'Bldg.; Grand-Rapids-2, :and 1812 Martin - i.S.E./Grand Rapids/ Mich. . . : . `.t, . . - / i Service Co.,'2328'Locust St.. 5t.'Louis 3, and.7527r -'i x/Forsythe'BIvd'./Clayton 5/Mo-'' DeBRA, Frederick!B/(A` 1945)"Owner/* Fred. B: `f 'V /DAVIS; Cleihant A. L; (A 1942) Mgr;. Ref. DepL.,' '4John' H:- Kitchen &,Co.,'1016 Baltimore/ Kansas -- DeBra Co.. 223 E;'.Eighth'St:, arid 6217 Cam- f` bridge Ave./ Cincinnati, Ohio. . =V- : ; City/6, and 3200 East'32rid St., Kansas City, - - DEES. Leonaril L: (M:1945) Owner Kansas Sheet -/ .;. 'j:3,'Mo. ` *'-y --t . '- Metal Go.', 206: W: :Sixth; .and 2529 . Mapdand,'/ ^DAVIS; Donald;-W.,:;Jr:r.(A ' 1946; -7; 1939) Dist; . Topeka, Kans. ^>;---:Mgr.,: B;F: Sturtevant Co.v. 854 Empire - Bldg., DEEVES, Edward W/-.(A-1944; 7 1940)"Partner/> '//.Milwaukee'3.- and'37.48 ; North' 56th;-SU Mil; / .Fred`Deeves &'S6ns,.1422A 17th-Ave. W:,.and--- If- . /&. / g* `i " -waiikee 10; Wis: . - ' " - . V ' / - 2403-33rd St. W.. Calgary; AlU;..Canada. -- , "-/ DAVIS,;'Edward- James;(A 1943; -7.-1938) 'Sales-/ .DeFLON,' Janies G: .(A .1946;. 7 1942) Cooling ' - Engr.,'" Gumey Foundry Co,,- Ltd., 4 Junction ; Tower-Engr:. The Fluor Corp./2500 S.. Atlantic,/ //'</Rd.,/and'224 St.'CIements Ave.P`Torontb, Ont., . '' ` Blvd./ arid * 2563 Fidelia St.-, Los'Angeles 22, Calif. /1 5^1/ j/ '^V-V.Cahada;'C*\- '' ' ' : DEGlLlO, Louis (7 1943)'Owner, Artic Refng- DAVIS/.George C. ` (M: 1939; 7-1936) Vice-Pres., eration Seryice/ 35 Kimberley Ave^- 202 Cedar ;>^^*N6rthefri .Public Service Corp., Ltd.,' 307. 'St-S./Timmins, Ont;', .Canada. - - - . ' 1^ *} -power.Bldg.'/'arid 366 Ash civCariada.--.-^- St.,-Winnipeg, Man.,:; ' DEHLER, .Frank C. (Af 1944) Chemical -Engr., ' *-The Davison'Chemicsd-Corp/, 20 Hppkins Pl.; . rfCtSv*: .. r- ...j; /^DAVIS. Gebrge L;, Jr. (A 1938) Estimator, .R1 L. ' - "r.'.'f:/Spitzley:Heatirig.`Co.;' 1200 W. Fort"St./Detroit./ '-. -'/.26,.and #3636 Bedford-St., Detroit 24, Mich.: . . . Baltimore 3, and,3439 Guilford ,Terrace; .Balti- more 18; Md.. * -V -- ' riSfc*?! ^ .~_2DAVIS, 'John C. (if-1945) Pres.'& Mgr.. .J. C. < v -Davis; Ltd./408 New. Hargrave Bldg.; Winnipeg; .-..' DeJARLAIS; Gordori.M. (A,.1946; 7 1945) Test Engr.,/Seeger-Sunbeam Corp., Evansville,.' and . ; -"A -C' ' /arid'152fLa', Verandrye St., St:. Boniface, ,-Man.,' -/735 E; Powell/Evansville 13,'lnd. - ' * -/^A'-'Cariada.''/ r '7' ' - DELALANDEv Andre (M 1945) Cons. /Engr. ' <*.DAVIS, Jofin.T. (if.l45)'Sales.Eiigr^The.Trane..* - -51niela Fontairie, Paris (XVI0)/France/^ C6;/and 1836 Sul.Ri^/Houstoii.O.TTmas.;''- r ' DeLAND, Charles ^W;. (if,1924; 7-1923)-Vice-1 v i>AVIS/rJoseph '(M-.1927; A 1926) HtgliEn-. & _ - Pres.,' C. W. Johnson//Iric., 211-?N." Desplaines X SL/and 2021 Estes Ave.,' Chicago/ I1K* -DeLAUREAL,^wrpavid (A 1946/7 T940);Chief/,y Ener.,`Sidney^N; Prats SheetiMetal Works," 2606*' ^ Clair;: Ave.,-Cleveland-iO, arid-2984 - ^./Toulouse St;,, and ^1^6/Broadway,JNew;QTlem\s./:i ^^rt^^^^^/Clareiriprit;Rd.v.Shaker Heights 22/Ohio// ' // -DeLUCIA/ F.rArthur.- (A _ 1945)/Engri-Estimator. _.A. J/Monpllor:Gor/928^Grand',Ave., an'd'325 Willow,SL. New Haven 11,-Conn. ' . - >>^8 Roll of-Membership-v*--- ,v--. - 25 - DEMAREST, Rlchrird T..-'(7 -1938)- Personnel DICKERS, Lester A: (A 1941) Owner, Dickens - Mgr.,.*Fit2gibbons':Boiler Co.-, Inc.,.23. Mercer . & Co., 1794 S.- Taylor Rd., and'3710 Grosvenor . St., and Hotel Pontiac,,Oswego,.N.-Y.~ ' '- /r Rdl, Cleveland Heights 18, Ohio/ : . -. . DEMETER, JuUus;(A 1939) Cons. .Engr./ Huer- ` DICKENSON, Malcolm . E. (M 1936) Pres.; -fanbs' 979--rOfidna * 605.V and * Casilla -* 9209, . / VLivingston Stoker Co., Ltd., 33 Sanford Ave. S., - ' Santiago, Chile, S/A. . ' ' and 964 'Cumberland' Ave... Hamilton; - Ont., : DEMING. Roy E: (Af 1941; A 1939) Designing Canada. ' Engr.. Furnaces, Kalamazoo Stove &- Furnace DICKEY, Arthur J. (A4/1921) Vice-Pres. & Gen., ' Co., Rochester Ave.,' Kalamazoo, Mich, -. / ' Mgr/ C. A. Dunham Co., Ltd., 1523 Davenport DEMPSEY, Edward P.:(Af:.1945) Htg. & Vent. Rd., Toronto 4, and 9 Mossom PL, Toronto.3, Engr., The Glenn Martin-Nebraska-Co., Box v Ont., Canada.. - * /-. - -1269, Omaha 1, and. *2431 Camden Ave., Omaha . DICKINSON, Neville S. (A 1943) Pres., Motor- - 11; Nebr.-- ' : , ' . - " . Sales & Engineering Co., Inc./. 1060 Broad St., ' DEMPSEY, Stephen J; (A 1938) Owner,# Stephen ; Newark 2, and. 507 Richmond Ave., Maple . J.-Dempsey,Co./79-Harvard St-, P. O. Box-714; i 'wood, N. J.--' . . ' - - - ' - '' " '., BatUe Creek. Mich. .. .. DICKINSON,RobertP.,Jr.(A 1946; 7.1938)- /-^DeNEILLE, J. Lawrence (Af 1943) Pres., eEichler ' Sales `Engr., eMinneapolis-Honeywell Regulator.. .. Co., 2125 LocustSL, SL Louis, arid 7227.MaryIand v Co.; 405 Penn'Ave., Pittsburgh, and 521 S. Lang -. Ave., University City,'Moi'' : -- Ave., Pittsburgh 8, Pa. .. DENHAM, Howard S. Of 1939) Mech. Checker, DICKSON, Donald R. (5 1941) Capt./ A C. ; .Stone& Webster; 149 -Federal St.,' Boston,- and ,' U. S. Army Air Forces, 340th N.-T-. S.. ElUngton ; 80 Dexter St;; Malden,-Mass. - . . . . Field, and Box234 B. S;, A. A. F.,- BigSpnng,-- DENNY, Harold R. (A 1934) Eastern Merchandise Texas. .................... ... ' - Mgr., e American Blower Corp/50.West 40th.St.. DICKSON, George P. (Af 1936) Mgr., B. F.. ` .New.York, N._Y.,` and.'429 Ekigewood Ave., Sturtevant Co., Haddon arid Crestmoht-Ave., . Westfield,-N..J; - -Camden,-and *430 Cooper SL, Woodbury, N. J. . DENSON, "Walter, Jr. (A -1944) Secy.-Treas., DICKSON, Robert B. (Af 1919) Pres., Kewanee . - Walter Denson & Son, 902. N.-Myrtle-Ave., Boiler Corp., and`145 E. Division St., Kewanee,-III. ' and 2730 Cherokee Aye., Jacksonville, Fla. - DICKSON, Robert W,, Jr. (A 1943; .7 1938) DEPJ*MANN, Ray. L/.(A: .1937) Owiier, R. L. American Blower Corp.,'1302 Swetland Bldg.,' Deppmann Co., 5853 Hamilton.Ave., and 13201 .Cleveland 15, and *880 Elbon Rd., Cleveland'' . Cloverlavm Ave., DetroiL Mich. - ' -'Heights 21, Ohio.' ... - *, - / DeROO; -William C. (A *1945) Engr.. Hart; & . DIETER, George H. (Af 1941) Dist. Engr., The Z _ Cooley .Manufacturing Co;, East-Eighth SL, and.. . Fluor Corp., Ltd.. 2500- S.. Atlantic Blvd:',. Los-' 567.Central Ave.-/HoUarid.-Mich. : ./ - . " - Angeles 22, and 618 N.` Kenwood-SL, Glendale /; DeSALES, Montelro/,Jr. (Af 1939) Engr.. . 6,.Calif.*'/'"- ; . - -*/r* - ';; Isnard&;Cia, Rue'Lavradio, 67;.andJeP.p, Box:. v.DIETZ, C.: Fred (Af ' .1938) e Haynes-Blankm v-3963,--Rio.de Janeiro, Biazil/S. A. "' " :v:' . _ Corp.,*-1124 Spring Garden SL, Philadelphia 23, * DeSOMMA, A.-, Edward! (A -1943; 7. 1937) Sr.. arid 1215 Allengrove St., Philadelphia 24,-Pa.*< -- . Engr... Naval'Archt./-Bureau of..Ships, U. S. N./ .' 'DILL; Richard S.* (Af 1939) Chief; Heat Transfer " Washington, D. C^'and *48-29^a) South28thSt... 'SecL, National Bureau of Standards, .Wash-/ .-Arlington; Va. ! DE1ERLING, W.C.'(A 1937) General Electric ington. D. C., and 1603 S; Spriogwood Dr., Silver-' Spring; Md.- ' - . . .Co.,-570.Lexington-Ave/, .New Yorkj and 32. W. - DILLENDER/Eugene A. (Af. 1939) *1502 McCuL ' . ' -! Milton St;,.FreeporL L. I., N. Y. ... ` - * lough,.San Antomo 2, Texas. ... - - Z- DETWEILER,-John R. (7-1945) . DisL Repr:, -DINHAM, Robert E. (5 1943) Lt. (j.g:) U.S/N R . . Minneapolis-Honeywell 'Regulator Co..'633 S. -- and *44l2 W. Lake Harriet-Blvd.,'.. ApL',-: 102,'' 'Z Fifth St., and R-7 Greentree Manor, Louisville," Ky'. - - Minneapolis, Minn. / . : - , : DEUBEL, Justin. A. (Af 1945)' Dvlp.. Engr., . DION, A. M. (Af 1937) Sales Engr/, Trane Co. of /Perf^c -Corporation, 600 . W/. Oklahoma Ave.,' Canada;''King.'and Mowat -Sts., .and #342 St. Milwaukee 7,. ande3710 iSouthV46th- PL. 'Mil- ` Clair Ave., Torohto,.OnL, Canada..' -' . wauk'ee l4, Wis. . / ` " DIRECTOR,-Isad6re (A 1944) Application'-Engr.;'> r- DEUTH; Gerald Q. (A 1944) :PvL.` U. S. Army. ' arid *6738 Lynford, St;. Philadelphia 24,.Pa;- *' :'i*Co.;C; 150th Bn.V91st RegL. i; R/T. C:. Camp . /DISNEY, Melvin A. (Af 1942; A' 1934) Mgr, Air " c Hood. Texas, and 39 West'11th Ave., CoIumbus, Corid. & New;Constr. Sales-. Div.,. The-Ladede - ' Ohio. c .Z - . .Gas Light'. Co.,'1017-Olive St.; St;Lbuisli:and " DEVER,Hehry-r-.F;/ (Af 1936;.A .1935)-Pres/.. * eR!;R. 1, Box556/.Glencoe..Mo._ / i- eBrown'-.Instrument'-'Co.;/--Wayne/ft--Roberts-- DISTEL,-.Robert.E..(Af 1941*'-7*i938):Partner & . Ayes;/'-;Philadelphia .'44,.. and. *544 vHowe- Rd:, Gen'.. Mgr., eDisteLHeating Co., 720 E. Shiawas- Merioh/Pa: :/ .'Z'' " * - . - see St., P. O. Box 133,,Lansing-l/and/547.-Bailey .. .--DEVERALL, Charles R. (A 1945; 77944) Engr., SL, East Lansing, Mich. - ' . ' i-.. Philip Carey Manufacturing'Co., Lockland, Gin^' DIVER, M. L.. (Af/1925) Cons..Erigr.j * P. O. Box ;; arinati`15, Ohio.-. -Sr -/-/ . - * ' . ' 1016 San Antonio 6, Texas.- /. - . ; * DEVLIN, .^John; (Af , 1940) . Partner, eDevlin DIXON; Arthur-G. (Af 1928)'.Secy.,.#Modine -BrdtHera/1003 Maritime Bldg.; New Orleans 12, Manufacturing Co., aha 442 .Wolff St., Racine.'Wis: and 5100:Pitt SWNew Orleans, La/ /''DOCKERAY, F. A. (A 1945) Sales Repr./*Fitz- : .. DEVORE; Angus B:- (A 1937)' Staff -Erigr/V ' gibbons Boiler Co.. 1717 Sansom SL. Philadelphu^ e jairies A. Messer Co^/1206 K SL' N.WI. Wash- ' 3. arid 225 North 63rd St.. Philadelphia 39, 'Pa. - .. . ington. 5,-'.and;4817-36th: St. N:W., Washing- . DODD,-John A. (Af7944) Owner/e John A. Dodd ton.D.C. .. .' w . Co.,299 TechwoodTDr. N.W.,and3370 Nancy's- DeVRIES; -Don' E. `(A 1944). Supvsr. of/Process ' Creek Rd;, Atlanta, Ga.J - . * . - Engrg.,.Nash^Kelvinator Corp.,'; 1545' Clyde . DODDS. Forrest F. (Af 1920) Mgr.,:Kansas City-. .Park-Ave/'S.W.,V.arid ;1149: Cadillac Dr. S.E., - Sales Office. American Radiator' &-^Standard ' Grande Rapids, Mich.. Sanitary Corp.. 503^6. National -Fidelity .Life-: . DeWITT/Earl S. (A. 1936) Branch Mgr., Ameri-J Bldg;, 1002 Walnut St.,.Knsas'City/6/and?4600 - ' can*Blower Corp;, 1211-Commercial Bank'Bldg.,' Mill Creek Pkway.; Kansas City,2, Mo.-: - . . ; and 2329 Westfield Rd.,>GharIotte,-N.'C.'w \.- , \ DODGE, Harry A, (Af 1936) Elec: .Engr./S. H.r/ .DIAMOND,"David^D. * (A'* 1942;. V- 1937) Staff / Kress & Co.. 114 Fifth Ave./New York, 11, and / v-.-.-.SgL, Co. A; S.'.T;. C,, Fort Monmouth, N. .J............. 514 West End Ave., New York 24;N. Y. " , /- ^and 1516 Sargent St.;.St. .Paul; Mirin/' *'./ **Z DOERING,- / Frank ,L.. - (Af - 7919) American :i - --DIBBLE,' S; E.* (Afv1917); (Presidential-Member), Radiator & Standard Sanitary Corp.; 238-Boston' : : (Pies./1925; lsiiVice-Pres..-1924; 2nd Vice-Pres., ' . Aver, Lynchburg, Va. - - - * k. 1923;-Council, 1921-1926) Prof;, : SupL, Patton DOERRFUSS,.Harry W. (Af 1944) Sales-Engr./. :. .. Masonic School-, for'Boys,. Patton'School,-Eliza- ' / Wairen- Webster Co.*, 26:South-20thSL,.Phila- . bethtowri. Pa.- --- / /.= '5/v.`'. / ; delphia 3; Par, and 35 Harvard Rd., Audubon; N:J. DICK/Harold.S/(7.1942; S 1940); Engr.; Key- DOHERTY, John/J. (A 1942) Fells Plumbing, ; v` 4Stohe/Sheet -Metal Works;-. 319.. Academy SL;.- - Heating &-Builders'/Supplies, Inc./654 Main St:.- s? Newark 3;-and 1235~Park. Aver, Hoboken;' N: J. * - and 10 Maple Rd.;Winchester. Ma33., * ' DICKASON/ Gray .D^-(M'l:l^),rRr^Tifins.V ^ DOHERTY, Roger J.- (A-1945)" Vice-Pres." Shaw;l Geriee Heatirig Service;/Inc/,'950,Mercantile'. Perkins Manufacturing;Co.; 1645 OIiver.-Bldg.";v*'. ^ - Bldg./-.Rochester '4; and. 740 Wlndemere Rd.,' '' Pittsburgh/ arid *363-. Lehigh - Ave.. EE. Pitts-' ' r,, Rochester,~N;-rY:-r/. / burgh 6; Pa/ - ':/ /'V;' / ^Broadway,' Detroit- 26;:-and'*14419- Stratiimoor ^- -23,'and 1342H-Bond St:,"Los Angel^-I5rGaIif' ~ t >* ,, Ave'f*Detroit;27,'; Mich.l;v -/ . 7. A DOWNES; H;'-H:\<M;i923) S:;^ Diitf Mgr >% "4^, ` vDOLAN'rRaymond G^(M--'1926;-y,1922)'Secy.- American Blower-Corp:, 438.Woodward:Bldg.J;- '- .'' ' <* " '*v " ^Treaa.lrT6m'Dolan? Heating-^Co., .Inc/, 614-16 'J . Washington`5.-D. C. * ` h '1.`J-t''/-}>" r mW Grand.'jOldahoma eity 2,;and 708 Northw^t' ..'' DOWNES, Nate W. (M 1917); (Council,-1928-30) - % !W&tr&y 40th Oklahoma Gity.'Okla.'-VAsst.-- `Supt;:` in', charge' of..' Bldgs.;.f& ^Grounds. . Sta3g~ >' f DOLAN,:- Wmiam'vH.'* (A^194.1)j Pres.. *The\. #School`Dist. of.Kansas'aty. -Mo:, ,1840 'E , ' Jenmson< C6;,-` 17~Putnam- StM and> 65. Highland :'..^Eighth'St.V Kansas; City/.l,-. arid;2119.;East-68th-v\,< , Ave .vFitchburg;Mass.. -.-.',: .c.v " V- St:-, -Kansas'City 5, Mo. ' DOLGE,^EmU; A.c(ji;^94S)r-MgrA^Htg: -Dept./^ DOWNS'' Charles'R.,;PhD./'(af^l936):;Cbns. ^ Y:- McDona]dtManufacturing ;Co.,'and P. O.-;- Cheml'.^Erigr., Chemists' ..Bldg.,-.-;501t East^lst';--' ^^.^DpMJNYi&GharlcsvB.-(7-1942)^U:^S.:'N; R; Clarage ,FanrCo.r-~KaJamazoo; ahd' 1562rSprucei^i.JW' 'y'- ^^]f.c*;U.iS;'!S^Hammohdspbrt>A'.>K.`sV;-2,'c/o':Fleet.- ---Dr.,..Kalamazoo'40,- Mich?"it*;*'.* ^ Si'C*;h' v-VPrt'Office7Sah`'Francisco,-.Calif.:'- - -- - : DRAKE,GeorgeM.'(A 1940; J i936)-Cons.'`:Engr . ' s**''" a 'PoirierMcI^he;,Gorp.,-:33"-West.;'42ndiSt, _'t ,, j&V's .. . New York.18;'Nl'Y.Tahd'Baybeny:;Lane&West- 4. *. ^ port. Conn.;' - -r-~- ^'CHrJr DRAVACE, Thom- D.- (A-1945) Htg.4& AiriCorid *' * V~1 -j- Engr.'; McGeorge 'St-Hargett;. 9400 . Quincy `Ave T" >> ` i | Cleveland,-arid .Chillxcdthe .Rd.f^Rl:2.:s.Willohgh- . . by^Ohio.; ,--. , - -v*^ DRESSELL, RusseU E. (Af-1942; A^1938>%rM6ch" J-3I ,'x Engr., vRigg9,..Distler/Co.. -Inc.r 216^N:VCalvert^ 4 ^ --'St-.-and 920 E.- Prestbri/SCi Baltimbre,.Md;^- --- ^DRIEMEYER,VRr. C.V (Ar.m2; ^1937);:;Lt. ^ _____ __ __ .'PhUlp* *'Cif t1922) '____ , - , Hygiene, * Harvard 'University,' School*.of^Pubhcv^! *--^. > -. Health, 55,Shattuck St.. Boston,- and;12.Hubbard- ^ *% v -Park,- Cambridge^-Mass. :; ' DRISCOLLVWilHam^Member, Af-1904);^* !Lv , - 4^*DONOVAN;-`1WUIIam,J.V(A:-l930) *2239-'North { ^`^tbiSt^Philadelphi^Pa.^- . *-^3;^DORFAN,vMdrton.VIi^(A.tl929)::Cona:VErigr;;; yt ; ^vi33Q-Foiirth Avei\.Pittsburgh;.'arid *1217'Malvern' " ^'Ave./Pittsburgh.17^-Pal-?'^ :f, ;'t:/-''-V> ' .300 S. Geddes"`St.,'.Syraouse;-Nv Y.-f'arid^SO.tGlen-^. \ v wood'Ave.,'Jersey.City, . - j'v DROoBaAv^ Cvmhaarrieless'-'.Bis; (M iu1-9m4;4-;)a'Saaielses:n'.,Engnrgi-r<.vo8ec; i * , - M*'Ehregt;Magne-s-i-a^Mariufactunrig.LCd'.,-'3l2 ^ -^3 * -Sevemnth Si..- S.W.,-and *.'34l2^0BvertSi^NjW ~ Wasthhiinriggtioonn,. 'D. C:';- V--,v ' xi. v, DULLE '^`^^-.E.i.'E.'i ... ... _____ ______ __________....... >r* ">. St.* Louis 20rarid-* 7230 Normandy.Pl.^Normandyy. f.Chicago;;ahd 31'-N^SpHng Avc.rLa Grange. Ill _ ^.21 Mw EATON,?Williani' G; ;M.=(3f .1942; "A W934) Sales 5. : ^UNBAR, l^n\W.'(Af.i9.44) DisL'M^/;v* Oarage ' Engr:y^Pea&'Foundry.Cbr,-Ltd., 227.yictoria St v rFan Co.1'3l4;Bulkley^Bldg.; Cieveland; arid'179o- ^Toronto;\?ahd 300.;.Welle^ley;;StM`': Toronfo^`5 ;-.`f `CadweU'Ave.f.Oeveland Heights,' Ohio;.xV-i, - Ontf.rCariada: *""-r7' 1 DUNII^/Clayt6n.A.;(t.yeafrt^CT; mS911) -EBERT;;William A: (Af 1920).,Oiroer. * EbwtAir . - - o' Pres.. C. - A': Dunham : Go-,' 450; E.: Ohio St^ v Chicago,"and 150-Maple HUl:Rd:,:GIenc6e, HU DUNLAP,-'R'. L^(AfH944)'Jblm'H; Kitchen & Co - , x. .:1016 BaJtimore Ave..,'and *5533 H6Imes,".Kansas- City.' Mo.^.i-; v` Vi-t-.;. : -H^".DUNN,:Rol>ert (A 1944) Chirf Engr.,' Thp Cann-- Conditioning,T'1026,W.' Ashby',Pin"arid 2t51'tW Kings'Highway, SanrAntonio l, TexasI "-< ECKHARDT,..;Elr6y;:i'Jr; V (7./1943):: Partner.-^ \ ' James'F.-Q,'Neil Plumbing & HeatingCo.v 2800 - , HoWafdnAve.,4New;"Ofleans^-'<andi'34':BeveriyA- .- Gafdens^Metairie.- Li.'r, ^-'v^ ` If.' < EDGE;:AlfrS4.J;-i(M-1938); Cons.''Engri.'.Reynolds;-':- , ^ diah Barik of Commerce; 25 King SC W.^Toronto-' c J'lf^and^'Pacific;7A've., Toronto 9, .Orit., panada: ... Smith &iHilis, 11-S.^Laura SuV-JacksonviIIe"and-.- . 2864'OIg^:P1.. Jacksonville 5; Fla?:vi-.-'.*- ,, r ^DUNNE^Russell Vr D. (M. i937) * Carrier Corp.. ;. EDMONDSON,:Jolm:Y; (A; 1944)-AsstHo MgrliV . _ ........... ^ *. ^ Chrysler Bldg.V.New' York; ahd 210'.RobineahRd..-' , Crurie Co.-,'>814;: Young;St.,yDallas 2,^arid *3465 ^ n- ^ - ` -Syracuse,--N. -:Y. -.C; '>r'~ ?'^ '> .-` Amherst,;-DaUai'5,;Texas;'.v' V' ;L - DUPliANT.T Jean=L;.n;(A:.'1940jMMiaU'.Court..' -EDWARDS. Artliur F.`(A 1945) Mech.^Designer, . Queehs.'Rd.,.Bbmbayt';indiat',aridkl37^43^2l9th - ^.Depti-iOf-^Pub.^Wks., '_Orit.>p Provincial-Govt ,3" -- ^ 'r'^rz ^ St.,;Springfield Gardens,-L: r;VN'>Y.'^-V*t:".' Pariiairient';BldgSi',Ti.Tororitd;>and>118` Airdrie- '' v,- ' pUPUIS,`rJoM^-:E^R;-(Af>.i942)::Bikach*:-Mgr Rdf,:*Leaside, Tor.'12; Ohtr; Canada.?.;. -.-' - r,, J T ttS?. v ^ j- J TraneCCo. of; Canada,' Ltd.,' 660 `St.; Catherines -EDWARDS,-;Arthur^ W:^(Afb!936).rDik 'Mgr. , <. ,, St.-^,W.v-Montreal;' aridr5642 Queen' Mary' Rd-. .Tbe-^Trane-'.Co.*,'626 Broadway, ^Gihdnnati 2: -Xr.-: _ Hampstead;- QueV.-Canada: v-'r -^"`.``5V< > * ' . .and`3423 PaxtoriJAye.-, Cincinnati 8,"Ohio. ' * v?*8 1 ,, DUSOSSpIT, ^Edmond A. (Af. ri944).rTrca v EDWARDS,' C.';Eugene (M* 1942)r Piping.Air e- >*L'yhch &'.W6oidwanl,,.Ihc.r28 Oak St:,-Boston. '..CondrDesi^ier,.* General Delivery.Lake'JacIrson,-.' ' ` 'arid;173 ;Warren St'.~, Newton'Centre,vMass..,! ~ and lll: Samuels'Ave/,'. Ft.- Worth 3, Teias \ DUTTON;'-Gayle:R.^(Af 1945)-Partner; ,*Wesiern :Fiberglas;.Supply', Ltd;,`i739;-Bryant 'StirrSan -- >EDWARDS;.D<m J;- (A l933).Sales Repf.. Lati-' ^ seel. Inc., 84'State St.,' Boston, Mass:'!/'- / r* ^ w Franda 7,. and ^15 Coleridge*Ave.,fPalo Altoi rEDWARDS,.Ge6rge-B. (A.'1945) Ovraef, *Plbg. *; & Htg.':Contractor,. 1140-Oritano`'AVe.:r>Niagara'-?- Falls,* N; -Y7 - ' *'' * " -* ' - oI Kescarcii. . Aluimmim' Company of America.'; r A, - V, ' . V 'Kensington.'and 636 Sixth StC'Oakmoiit:'Pa , - DWVER, .ThomiLs P.' (M_1923) ;ChiefcHtg. & ,.;EDWARDS. Paul A.;(M 1919) Pres,, .The G F ' V .:-T.... "-Vtg.yDi,rf Board .-of yrEducation;. 49 '.Flatbush.^ ;' Higgini 'C6..V608: Wabash;BldgT, Pittsburgh,'22,r' o Ave.,~-Brooklyn,.and 82 Ins'Ave.,`-;Floial'Park, ~' anr* << ~ ' L" I ,-N^Y:^.:-r .Vv {f-:->EEI . - DW.YER,'i;.WUlIa'm,>H,;c(A'f:'1944)Salea-r;Mgr.' Central-SupplyrCo:, 210-230' S.^CapitoI-Avel; r'Jt. -v. .. and 4455:Marcy Lane.-Apti;164, Indianapolis, Ind.- y;- : . / DYER, Alyih R.r(A;1944):Mgr.; Htg. & Air Cond.- ' . i -aDept.V Utah. Builders Supply-Co.: 503 W,-. Fourth : yc'^' South^St.v Salt 'Lake City 4. .and 200u Herbert' ... >VV - Ave.,' Salt1Lake City 5rUtah : v?/bYER; tWllfri'd.S.';(A>1939);Partrierj * H, W;;Dyef' -C?:C^'&-Son,'92Byfbn.St.',BattleCreek.<Mich;',-'^-->; ' ^;liDYKES,> James B: <A vi939V J :!936)ViceiPres",* ^.T^A.7M6nisbn-&r:Co'v: Ltdi. 1070 Bleury StT,' ^ v ,Montreal.- l. and'-42 ; Dobie '.`Ave.:~ Mt: :Rovai.` , n'Montreal;16.-Que;. Canada: Brook!yh. Nr Y.- .- EGGERS. Wllllam K (5 i941) Lt. 0'.gO;U.S NR, v*U; S;-Sub.Basef -Box-20,vNew London';-Conn. :,.;- c. . ' EHLERS, Jacob :{A ;l939;f> -1937j^Chief Engr . ' /. c/p JamesonsrPremier'Engineers,"Ltd.; 33 Salt ' River Rd;, Salt River,* Cape Town, South Africa -l'' EHRENZELLER, Adolph <(ifa941)^Owrier' - .- Ehfenzellef, 329 Washington St;,' E>orchester 21, - "sx ry~%i -v ftim , and-23 Parklawn^Rd., West Roxbury.32.iMass. * %. EHRLICH,';M. -William* (M1916) *56 Ridge / ; - * RdS.Iiy^tii^-NjrJV^v;*;/^^ ,f:s:W EICHER* .Hubert :C;c(M^1922)/Chief. School ' vPlaht Div.1'.Dept..of-Public Instruction, and *207 f' V'^^ t.a1^ * Constitution :Aye.';;WashirigtonT':D:%G.,:and *615 ''St;-Andfews>Lane,:SiIyer Spring, Md.j'cf.. ciduibT.-ix;'c"V.i/ ingoV'.'tr:__!-n^.'.'c. EKLUNI),-;KarIG..(Afl938) ,Coris:-Erigr;,*Karl; G. EkluridsTngenibrsb'jha A. B.-.^ Bnnikebergstorg- 28 ^Heating, 'Ventildting Air VConditioning-. Guide 1946 - ELLIS, C. W. (Mr-1945) Engr.,*'J. A. Walsh' & Co.. - ERIKSON, Harald A. (M 1939) Vice-Prcs.. " Inc., P.D.'Box 1773,- arid *8412 :Baker Dr., - A. B. Svenska Flaktfabriken, Kungsgatan 16-18, --"Houston, Texas/-- *' **- "'v . *=v* - ` -!-' - Stockholm, and Nockebyvageri 61, Nockeoy,. ELLIS, ; Frederick -E. (Af 1923) Sales- Mgr.. -Sweden.' . . Imperial' Iron ` Corp- Ltd.;-' 30 Jefferson Ave-' . ERISMAN, Perdval H., Jr. (M 1936) Vice-Pres:,' ' Toronto'-l. and 9,-Mbntg6mery.Rd- Toronto'9,- . Washington Refrigeriition ;Co., 1733-14th.St. .; Ont--Cariada.V .- . 7.^. - N.W., Washington, D1 and. Belle' Haven; . ELLIS, Frederic-R/ (M 1913) Supt. of EngrgHarvard University! Lehman Hall,' Cambridge, f and *131 Beacon-St- Hyde Park 36; Mass.1 . ELLIS? G. P. (Af 1935) *GwyimeBldg-Rm. 600, . -and-TllS Delta Ave;, Cincinnati, Ohio. ELLIS, Harry W. (Life Member; M 1923; A 1909) Chairman of,the'Board. Johnson Service Co.. 507 E.- Michigan--St., Milwaukee,' and #2317 _E. Alexandria. Va, * . * - .' .. ERNST, John P. (7.1944;-S-1943) Design Engr., ' - Moore Dry Dock.Co.', Foot of Adeline St. .(East Yard);Oakland, and *2654:Harrison St., Apt. 2, Oakland 12, Calif. ' . '. ' -- ESCHENBACH, Sam P. (A 1943; 7 1935) Lt. Col.. ! P. O. Box'142, Rchoboth, Del.' . r \- ESKJN, Samuel G. (M 1944) Dir. of-Research & Wyoming'Pl.,'".Milwaukee 2rWis.. ` ` - . Dvlpt., Grayson-Heat Control, Ltd.. 833 N. ELSARKYr ;Aly (A 1945) "Chief; Erigr.; Food- Highland Ave., Los Angeles 38, and 5931 Linden Products Co.i i25 Foiiad ElawalSL, and *194 hurst Ave., Los'Angeles 36, Calif.- . Farouk Elavil St-.Sidi.Gaber, Alexandria, Egypt.* ESKRA, George N. (A, 1944) Sales, Engr.-, Ray: ELSIE,-Robes*t L. (A 1943) Purch.'Agent," Atlas ' Wirither Co., 45 Dore St., and ' 1543 Cayuga St-;' -Engineering &. Machine Co.;-Ltd.,.16 Eastern* - San Francisco 12, Calif.~ .Ave.;-Toronto' 2, and -19 _ Astor, Ave..' Leaside', ESPENSCHIED, - Frederic F. (M 1940) Dist. .... Ont..'Canada. :fc.- *? ' '' . * = - 'tk Repr., American Air Filter Co.. 410' Hill' Bldg., ELWOOD.' Willis - H.(Af 1936), Htg. Engr., . 17th and VI" St.-N.W.. Washington.6, and *3373' Elwbod'Heating Co., 209 King St-Ithaca,' N. Y. Stuyvesant-Pl; N.W., Washington 15, D.-C. - EMANUELS, Mason (A 1943; 7.1939) Br. Mgr.. ESSEX, *J. L. (Af. 1945)-Gen: Mgr.'. Mineral PadficSdentific Go.,' 1915 First Ave. S-Seattle. Products,* *903 Natl: .Bank of. Commerce Bldg.; '. 4. arid 3410447th N:E.; Seattle 5.-Wash>! : " -' San Antonio 5i Texas.' -'' ' EMBREE, Earl G. (Af 1945) Engr., TompJrihs- ESSLEY,' Hubert A. (M ,1941) *Taco Heaters; - Johnston-Co.vPr.O. Box-4045;- Charlotte,'.'and . Inc..-123.South.St..* Providence 3, and 42.Elton- i- Route 1."Matthews, N. C. - . ' > --*' ' St.,-Providence 6, R..I.* - -i ' .1 EMERSON, Ralph RV (Af 1922). Pres... Emerson ESTEP, L. G. (M 1936) Mgr., Service Research Swan GoodyerCo- 712.Beacon.St., Boston. and . ' Dept., Booz, Allen & Hamilton. 1700 Field Bldg., . 44'Whitney'-Rd.;' Newtoriviile, 'Mass.' ' . - Chicago" 3, ..and 115 S. Catherine Ave.,= La EMMERT,* Luther-D. (Af.vi919): Sales' Repr- - Grange; 111. - --.V - .*. Buffalo-Forge' Co.;-20 N. Wacker Dr.. Chicago, '.ESTES, Edwin C.. (A 1936) Chid Draftsman. and'1704'Hinman Ave.,-Evanston^ 111.' . -;, *. " . Northern Pacific Ry., 176 E. Fifth St., St. Paul* - ENGDAHL, Richard -B.* (A^ *1944; 7 1938) IV and Ri'R. 11, SL Paul 7, Minn. -. - : '-j . .v Research;Engr.,- Batteile -Memorial ''Institute, ETIE, W. R. (A 1943) Owner. W. R. Etie Sheet 505'King Ave-'Columbus l.aridT243 Glenn Ave.; 'Metal &.Heating, 1224* Summer St., P. Q. Box -' Columbus 8, Ohio. - ' . - 4535, and-502 Baylarid. Houston. Texas. ' . - 1 ENGELBACH,:. A^ Arthur - (Af - 1945; -A . 1944) EUTSLER, Eugene E.-, Jr. (A 1946; 7 1938) Lt. *. Gen. Mech./ Engr.,- National - Capital Housing --Authority; .and *6630-3181 Stf `N.W.,'* -.Wash* ; rngtorii'D; C..;' . ; . ,*..-: ; /-* -.Comdr., U. S. N. R.?and *P.O. Box.917,-Mobile. *' A Id. .* . EVANS, Bruce L. (M1938-A 1937) Sec^. & treas:. ENGLE, Alfred ,(A -1923)'.Secy,, jenkins'Broa, . Becker-Marsderi Co., 3818 Lihdell Blvdl. Sri Louis 80-White-SL;-New York,-arid'.l'.Edgewood Rd:,. :`8; arid *571 Stratford Ave:, University City, Mo. - Scarsdale;'N.-Y. . ' ~ ~:* EVANS, Delmar C. (A 1944) Chief EngrV I .*.: ENGLEHART,"Oscar D..(A 1944) Research Engr., *Magnin & Co., 3240 Wilshire Ave.', Los Angeles 5,*. - Pittsburgh ! Plate -Glass' - Co., * Creighton; and .*. and-4734 Camellia Ave.,- North Hollywood.-Calif.* 1151 Union Ave.V B'reckeriridge,-Pa.' - " ' - EVANS, Edwin'G. (M 1937) Mgy.. Buffalo Officer -ENGLISH, Alpheus T{M 1944) Pres. & Gen.. ' *B.-:F. Sturteyant Co.," 508 Jackson . Bldg., . Mgri? Columbus ^Air Conditioning'. Gorp'.-,' 182 7 Buffalo 2, and 66 Summer Stl, Buffalo 9,' N7 Y.: N. Yale Ave., ;and 299.N. Stanwood;Rd.,[Colum- EVANS, Richard W. (M -1940). Ltl Xomdr:. .--bus, Ohio; i-'`.i*7-- ^-*'^ 'f- ** - (GEC), U. Sa N: Ri, *U:- S. NavyrvBureau of . ENGLISH', HarroId;(3f 19S5)'Prei, English & v: Yards :&" Docks, ,938 Board- of Trade. Bldg.; Lau'er/ Iric:, 1978 S.-Lds Angeles St., Los Angeles - ' Chicago; 111.' * - .. 11 -arid.515S. Norton Ave-Los Angeles.'Calif.' * :.;EVANS, S; M. JA -1945).-Salesman & -Engr.V ENGLISH, 'Richard*B; (7:1945) r Ensign, U.VS: Wiriterbottom Supply.-Co.,' and *301 Williston i- Naval. Reserve, B._O. Q.;: 0-2/ N. C.- T. C-. ' -^'Ave;, Waterloo.-Ibwa.' - -; Davisville; -'Rl'-T;,* and 934;N: Main SriV Bowling '. EVANS. William H. (A l943) Gdi. Mgr' *Minnei ^ Greeri^.Ohio.;" ' . ,-4` - `. . \ apoiis-Honeywell- Regulator Co--Ltd.,-117. Peter v ENGSKOW, John C. (A.1944).Htg. Engr:KU. S. - - St.. and -102 Pine Crest * Rd.; Toronto," Ont., - :Dist., Eng. .OffideVvl709 -Jackson St.', -mid *5048 --Canada. . ' v*." -* ""* **.-., *-:- ' ' :- v. Corby St.,'Omaha,-Nebr. *` v y"' *.:,, *''" . : EVELETH, Charles F.* (Li/e Member; M 1911) ENSIGN; WUlis A- (M 1935) VIce-Pres.Frontier.' Wilbur Watson & Assocs., 4614 Prospect Ave.y ' Oil'Refining^Cdrp:, 886 EUicott Sq.'Bldg., Buffalo,' 1 and *2030 East`115th St.; Cleveland, Ohio.' -7 \ . and> Shadagee' Rd.,;Ederi,;N. Y. * ; i EVEREST,.R. Harry. (M 1935): Engrg..STSales,. EPPLE,'--Arnet; B. (Af 1943) *Uniyersity of. .Sheldons, Ltd., Galt.; and 235'Waterloo-St. S.,: - - Michigan; West.Ehgrg. Bldg., :Ann Arbor, Mich. *.' Preston; Ont.', Canada.' vr . rEPSTEIN,'Ledri7(71943)'Engr.','Ui S. NavyDept., -- 18th.;'arid v.Coristitution.'. Washlngtorir- and *111 EVERETTS; John, Jr.* (M.1938; A-1935; 7 1929) Lt. Comdr.*, Office of Superv. of Shipbuilding, AnacdstiaRd.'S.E.`,'Washington 19,*D.C.- ' .' Bethlehem Shipbuilding .Co.,* 20th and Illinois EQUI,' Ferdinand ^F. -*.(A; 1944) Pres'; &. -Treas.v *. Sts., San-Francisco, Calif.- ~ - .- >*. .,*Steyens -& 'Equi-iCor;-;Inc., .333 North Ave.,v EWALD, -John H. (A 1944) Vice-Pres. & Gen.* ^ Bndgeport':6;v and ? 35. Lilalyri: Dr.,-'Bridgeport Mgri,-Jaxne9'.E. Degan'Co., 2130'Franklin.St., .V, 29.'Cdriri.;-' '-4- -Y '*.. ! -..i. .- ._-i- -7* ".Detroit7, and *5200 Bishop Rd., Detrpif24, Mich. ERICKSON,;Gordon:Ai,.(A. 1945) Sales Engrg. . . EWELL, Walter. A. (A 1945) The Austin Co., ,Dept*,; ' Wood 7Conversion .Co., First.rNational, ' 618'..Grand' Ave.,' Oakland 12, arid-628 East;22nd Bank>BIdg.,:St: PauM,-and175 N; Victoria,'Apt., St.; Oakland. Calif;' *' 1 SC.PaulAVbfinn^- T ^4 ' - EYNON, Walter E;-(M1943) Pres. & Treas.'.VThe ERICKSt>N?;-Hany'.H,1944;'A 1929) * Sales. *., A.. C.vEynori. Plumbing Go.; 236 ;Walnut. Ave. - Engr.v* Hayries^Blankin -1-Corp.7'1124 J Spring N.E.VCanton L and 326-22nd St.-N.W.,'Canton; -v ..GardnrSt;; ?Philadelphiar 23," and- 25 Old -Eagle* -- *: 3. Ohio. ? '* "*ri - - '-r * .-.* , >.ScHodnRd:i?Stiaffordt'Pa; ^.:7 ;J ~ EZZ^EI>DIN, 'Ksunal '(^194^^1941^7^1938) ERIGSSON,:Eric;Bl:'(M :1933)i Engr.-Custddian,. . Service''Mgr.,* 'Carrier-Egypt; S.. A.* E;/37 Shana ;-r Boardof Education, 228 N; LaSalle Strand 6720 ` *-^.Kaar '.El-.'Nil,' arid.*78 Sharia 'Helwan;VMunira,. . .Cregier!Ayer,`Clu(ago,;IU.^4v r-;.,V` `-V;; -' ' Cairo,-Egypt,/' r; V.* - ' .`.{-RolVof.Membership 29 tEAVRET,*L6uis*E. (Af. 1945) Pres:,'* Williamson*.. . Favret Furnace Co!, 55 E..Goodale St...Columbus ' ' FABLING, * Walter D. :(A .1937). Owner.! W. 'D: X"8..arid 314'Gakland Park Ave:, Columbus 2, Ohio; ' : Fabling Co.; 117 W. Ninth St.. Los'Angeles; and FAXON, HaroId C. (Af. 1937) .In Service.-and'. 1424 Van* Dyke Rd., San-Marino 9, Calif. * ' . 1621r19th SL N.W.. Washington, D.:C. . . * FAGAN, Lawrence E,-(A -1942) Gen'VSales Mgr.,'-, 1 'FAY', Samuel C. (Af 1945) Indus. & Home Insula.--' . * *Chatco -Steel Products;- Ltd.. . 512 C. P. -R. - Engr.;. The. Eagle *-Picher Sales.-Co.,and *7011 r * Bldg., 69.' Yonge.' St., and -1229. Dufferin- St.', . . Fernbank Avel; Cincinnati 33, Ohio: . .-*;;"-'* *'* .Toronto, Ont., Canada. .w * . ' \ FEBREY;..Ernest J.-. {Life Member; ;Af 1903)., C. FAGIN, Daniel J. (M 1932) Mgr., Sales Engrg. Pres., * E. J. - Febrey, Inc., 616 New' York Ave;- * - . Div., The Laclede * Gas Light Co., 1017 - Olive 'N.W.! Washington 1; arid 2331'Cathedral'Ave.-.''.' . ' St.. St! Louis!;.Mo. * *` ' . ` - - N.W., Washington,' D..C. - * ' * . .FAHNESTOCK, M. K.* {M 1927) Research Prof. - & Asst. 7 Dir., Engineering Experiment. Sta.. University of.HIinois,* 214 M. E. Laboratory, and . .-*702-W..Vermont St.. Urbana, 111. " FEDER, Nathan (-7. 1938) Engr.. 'Merritt-Chap- ~ . man & Scott Corp.. 17 Battery PI.,-New York, and *1319 Morrison Ave., New York 59< N/Y.*'^' - ' FEEHAN, John B. {Life Member; M 1923) Pres. ; FALK,. David . S. (M 1943; 7 1937) CapL, 426 '. Treas;, John. B. Feehan, Inc.,* *58.-Spring--SL,* .* .. ^ McKerchey Bldg., 2631 Woodward Ave!, Detroit, - - Lynn,.and 4 Longvies'Dr.,*Marblehead.'Mass. - . ^ * ; 1. Mich. **.-;. - FEELY, Frank J. (Af 1935; A 1929) Mgr. of Sales;/ FALTENBACHER, Harry. J. `(M 1930). Owner; Taylor Supply Co.. 700`Monroe Ave'.,*arid *950-,. HarryJ. -Faltenbacher,-.235 E. - VVister St.,.- Trombley Rd., Grosse Pointe Park, Detroit, Mich:" * * *. 1 Philadelphia 44. Pa. *.'*** * * *. < - - EEHLIG, John Bz'{Life Member.; M 1918).Retiredr * " FALVEY, John D. (Af 1922) Cons. Engr.. *316 -/-Warm Air Htg.,**' 528' -Delaware St-., and/2927 - . ;- N. Eighth" St..-St. Louis 1. and 6636. Pershing. . Brooklyn Ave.,' Kansa^ City, Mo.' ` ,, * " * -"* -Ave.; University City, Mo: ' ' - FEHLIG, -John B.,4^ Jr.'(A-.1941) Asst.-Mgr:,. . -FANNING, Erroll C. ' (M -1941) 'Engr., Atlas * . Excelsior. Hearing Supply Div., 528 Delaware SL,- . * -Hearing SrVenrilaring Co.,-Ltd..-557.Fourth St... * Kansas jCity 6, and 6412- Paseo. Kansas City - Sari 'Francisco 7; arid 24 Oval Rd., Oakland 11. - 5. Mo.- -. ,' . *. * '. \ . '* Calif. : *- . ** - - , : . FEILZER, Joseph H. (7 1944; 5. 1943)'In the - FARBMAN, Leonard-X. (A 1942) Secy.-Treas., *. " Service, * and 2909~39th Ave.' S., 'Minneapolis ..*M. Farbman &. Sons. Inc., 349 West-59th St., - 6,'Miriri.. ' * ;*'--/ * /.'..- ' ' -New* York 19, and 10 West;65th St., New York, . FEINBERG^Emanuel {M 1945; A 1944; 7.1937) . - N. Y. - ;..* -V .* . - Pres., American'Thermal Industries,-Inc., 2519 .FARLEY, W. F.: (M -1930) Sales Repr., American ' Bellevue. -Detroit 7, ` and *T8667-* Ohio, -Detroit; - Radiator & Standard Sanitary Corp., 50 West 40th 21,Mich. ` " '- '* *. / - V St1.,- New* York,- and 28-Elm'St'.,'New Rochelle,* - FEIRN, William H. (Af 1938)./ Erigr.. *C!. A. v ' -- N. Y7 ' '* V - -- -. ... .* .* '*: -V ' - Hooper-vCo:,/453 W;-Gilman,, and Shorewood j FARLEY, Willoughby'S. (A 1941) Capt., M.A.C., Hills,-'Madison,' Wis. **../--' - . ' * -Box 109, Oliver General Hospital, Augusta, Ga., ' FEITEL. J. York.(A' 1943) Owner, * Jordy Engi-: . and W.. S, Farley'. Contr:' & -Engr.', *865 Paxton . Sneering'Co., 813 Howard Ave.,: New Orleans 13;' - - Ave.,' Danville, Va.- * . ' " - . ' . .-arid 2A, NeroriPI.,^New-Orleans, La- . ' FARNBACHER, John M,. (7 1945) Student FELDERMANN, William (A 1937) Pres:'. Walton/ * ' -Engr., Chrysler Corp:, Airtemp Div.. 1119 Leo St., -Laboratories,' Inc;,-1186 Grove SL, Irvington 11', . .Dayton, and 924-N. Euclid Ave., Dayton 7, Ohio.. * arid 303 Montrose Ave.-, South Orange,-N. -J. . - - . FARNES, Bert W. ` (M -1943'; A 1938) Owner. FELDMAN, A. M.* {Life Member; M 190Z) Cons. -.*-' B: W. -Farnes; CoV. and *3019 Northeast 26th * ` Engr., . Retired, *320-' Central' -Park* W., '.New-- * * -Ave'., Portland 12,'.Ore. ` '' V *'. .. : York25P N. Y/ *!; "- FARNHAM, ;Roswell (M 1920), *(C6undl,.T927,- * FELDSTEIN, Harold -(A . 1946; J. 1938) Major, - - *33) Dist..Mgr., Buffalo Forge Co..`490 Broadway,. - Ordnance Dept., Army .Service'Forces. Office of' * . and *5 Clarendon PI.; Buffalo 9, N.- Y. *.. . the Chief.of Ordnance, Rm.-W). Detroit 32,- and ... V=FARNUM,: Warren* S. (A 1945) Mgr., Franchise, *3115 Griffith Park Blvd.,'Los Angeles 27, Calif. y,,: Sales.` Westinghouse Electric Corp., 89 Broad St.,' FELS,. Arthur' B. -{Life 'Member; Af 1919) Pres.,* - ; " .Boston,' and 285 Mystic St., Arlington 74, Mass.. *The -Fels;Co., '42 [Union St., Portland,- arid - * , ; FARR, Richard S. (A`.1944) Vice-Pres.*,' Farr Yarmouth, Maine*. - -:* ' ' . - Co., 2615. Southwest Dr., and 5118 Dawn View -FELTWELL, Robert H.' {Life. Member;'M. 1905) ---:PI.,.`Los Angeles 43!'Calif. -* r.- *- ...*,, *-_ Htg. Engr., National Bureau of-Standards, and* FARRAR, Cecil W. (M 1920; A .1918), (Treas... ' . *1347:Michigari Ave..N.E.-, Washington 17, D. C. J - -.'*1930; Council;*-'*1930) Sales:*Mgr.;;- Plbg.'-.Div., ' -` FENN;-Charles V. (Af--1945) Mgr., Atlanta Dist:,1* - '. Richmond Radiator Co., 19' East 47th St.', and Carrier Corp., 300 Ivy SL N.E.TAtlanta3, and; '*' '' Murray`:Hiil Hotel, 40th-St. and Park Ave.,* --124-Vidal.Blvd., Decatur, Ga.-, * - . * * *. V New-York 17, NV Y. * ** ` ` FENNER, *N. Paul (A 1943)' Fenner & Potvih, * FARRELL, EdwardJ/(M 1943) Partner..*FarreU-' . - 130 N. .Wells SL. Chicago 6. and_ 227 Berteau' . *&.White. 409 Griswold,St.*, Detroit 26, and'3472., "'Ave., Elmhurst; _IU. . '' - `'ji' -^- * * Gray Ave.;' Detroit 15, Mich.,.--1 j*. . FENNER, Walter M. (A 1945) Engr., Secy.-Treas.,.-.- . . ' ' FARRELL,' Gebrge F.* (A-' 1944).-Engr.,. Capital ' Central Mill- & Plumbing Supply^`Corp.:;.*46 E.` * Electric Co., 209 E. Ninth St., and *2015 Bowman -.Swan St., and 1012 Studer Ave- Columbusi.Ohio.- *. .. --Ct;,-.Topeka,- Kans.' . - . ' ' '5; . FENSTERMAKER, ;S.:=E. (Af 1909) Partner," * * / FARRINGTON, S. Edward (M 1940)" Engr., .. *S. E.-Fenstermaker & Co.,' 937-; Architects & : . :* * Moody & Hutchison,- Philadelphia; `and *3123.; _ Builders ' Bldg.,. Indianapolis 4,L .and R./ 'R.* 1, ' !. Rawle St.; Philadelphia 24, Pa. - ' . ' Carmel; Irid. "k * ' ' ' i ?- FARROW,'E. E. (A 1938) E. E. Fairow CoV, 6109 Forest Park Rd., Dallas, and *1518 Kings High-' ' way, Dallas 11; Texas. ! ' FENSTERMAKER, -Sidney, Jr.< (Af; 1945; .. -7 1943) Sales'Erigr., *S. Ef'Fenstermaker & Co- * - 937-Architects-& Builders, Bldg--' Indianapolis!4,. *.. *- and-Box 453,' Carmel, Ind. , '-'.......... ... -------- -^FARROW, TIoIlis^L. (A 1942; 7 1937) SaSrice & FENSTERMAKER, Ward' Raymond (7 1944)"/ - Insinuation .Mgr., Sprague -Breed .Stevens *''&. -,;NewhaU, Inc., *153 Broad SL, and *73 Victory Sales Engr-John J. Nesbitt, -and *4525 Marcy- j - Lane;'Indianapolis,.Ind:'- * i, ' / * *** Rd., Lynn,- Mass.* ' * '- * FERDERBER, Muriy B.; M.D.* (Af 1938) Capt-* FATZ, Joseph L. (Af 1935)' Htg.','-Vent. & Des,. ---,U.***S. :A: A.* F., Convalescent Rehabilitation' S' Engr.. Board of Education,-228'N. LaSaUe St.. . - Service,r A.. A.- F.,w C-'-C. &* Regional1 Station | .' Rinr536, Chicago l;-and *5914 .Wi:-North.Ave.,'; - Hospital,Mitchel Field, N. Y. - \ " '>! * `-"Chicago 39. 111... ' FERGESTAD, Marvin L. (Af 1938;'7i935) Mgr... FAULKNER, John H.. (Af;194l)':6wner'& Mgr., * ' * IrisuIarion Engineering Co., 2120 Lyndale S..''- ! ' John H/ .Faulkner * Co.!: 805 Skinner .Bldg.,.. Minneapolis * 5,/'and-- 2736 Joppa, MinneaiKiUs-Seattle 1, and Mercer<rIsland,.Wash.' -. *. 16,-Minn.--i.'1 FAUST,'. Frank; H.:' (Af 1936; J 1930) Comm. C. -- FERGUSON, Clemon E. , (Af; 1944): Mech./Engiv, * Engr., Air-Cond./Dept.; General.Electric'Co..* - Post' Engineer's- Office^'-Ft.*- Douglaa.' and * 838' 5 - Lawrence St., Bloomfield, *. and_ 36; Afterglow * GarfieldvAve., Salt Lake City, Utah.'* *", ^ Ave.','Montclair, N. J.* *! *V. - \ *!' -*.'- * - r FERGUSON; Ralph'R: (iif. 1934) Mir;..Air Cond.'* J- FA VA,'Albert A.' (Af 1945);PIaht Engr.? Atlantic Dept./American Blower Corp-*50.West 40th! St.V- .> Gelatin Co.,'Inc:;-HiU St., WoburnTand 6.PineSt.. . /New York; N. Y.', and * 77 E5lge\ri)od Aye;; Westn- StonehamSO, Mass.- ? . ' Orange; N. J!.,.. #>2^W4-FERH^rn; Julius' J (A 1944) K Y Mgr.. U;'S.,Air.' Conditioning Corp., - 420; I^exington.- ^.^^^i>KlFERRISt**'Arthur Li .(A 1941) -Repr., Cooley;,Manufacturing Co.,-103 ;Douglas'Ave. Toronto;;Ont:.,s;Canada:--Z 4 ` ` 'S ? . - M^^^rj^FERRISr.-Efenaia.: McKenzie: i(M. 1944) Mechz Sj3;V'3HEii|rv.BuddWheeP Co.;tl2141 .fi.-VCharlevoix,- JrDetroit 14,/'and,,736 ' Chicago"' Blvd., ^Detroit FLANIGAN,>WUUam'P/-/(/fl944) .Supt > Air Cond;StSheetMetaTDepU.f; Lloyd E.'/Mitchell, Inc.V/2315vCecil;Ave:/; Baltimore ;18,?and* 5508, Greenleaf-Rdr,:BaltimofelO.\Md. :/*:?&'. - - FLARSHEIM;;Clarence *A.>(A :1940J i1933) . ... Major.- A7 C.7 Engineering'Div.v*Wright ; Field, Ohio./and~3720iHolmes.St//.Kansas City. Mo. . ^FLEISHER;-rWalter L.*;(L*/e Member/, M-1914).,(ErcsidbiliaiXMember),~(Pres.,- 194t;V'lat ..Vice-; Pres.,M940;Z2nd /VicesPres, 1939;. Council. 1936-- r 42) Pres.^e Air; Refrigeration/Corpr,:475j Fifth f AveV/New-\York/17/ and *'SawMiIlFann..'New,. City.-'Ni^YiF ik-*?- X * FLEISHERy/Walter L.f Jr:;; (7 1945)-Engr.. * Air . &'Refrigeration ;Gorp.r,;Bbx 1496. Atlanta 1. and ;: 739;Elkmont' Df. 'NcE., Atlanta; Ga.. - FLEMINCT^Patil Br/fM'T941V-. Cona/i Enarr. ///Dealers ._____________________ _____ ___^ Statler VS;5v-i?i'^Bldg!,'-Bdstdn>16,>Mas3.,'.and65'.'Park /Terrace, &^^^^V>EiVNew Yorfc'NI'Y.'.'i^V^: .*:> % Tv....----------------- -- ------- -- ~ *' " ------'--------- ------- .-Treai.. '"Adams Engr.' (R)'U;:S^:P." H. S., Oregon,StateZBoardof- - Health/412 Oregon -Bldg./PoHland 4,/and 1515 - Ainsworth- StV-Aptr 24, 'Portland lT.-Ore. . FLORETH; John J;.Wl939) Lt.;G:g )IU;S.N:R.;' and* 924 S.-CrescentAve..^Park"Ridge',':III. *2 FLY,l'E;:Paul^(J l942) Supt..Geo.M.Fly.& Son, ~NashViile;?randV*.2806rfBrightwbo<U`Ave Nash FOGG;V:'Joseph.rH:'-(At,1942r 7 -1940) Naval ' *:^ArchtT^,Ul.,S.v'MaHtiine'!-Commisfflbny<7Dept.. of CommerivBldfr,,iWMlui^ton; 'DL,;Cidand 217f < E.-iBellefo'hteTAver.-'Aiejaiidria, Va;?-~ 0 - * "572LakeiaridAve:,.Gr6ssePomte/Michl3;' _ "` "' " Southern id? Westihgh6useyElectric<4Go;i ':306 `Fourth Ave.,^ - Pittsburghi/Pa.0 ahd'*18406/Neweil;Rd:.^:Shaker.. H^ghti':phio-V4r"?-;I.-r^-r.':. ^ .?>//, 1' t X ^fX- X-i 'V/\; .^FREEMAl$-;tj;<Albert'(k/l^;^>1938) Partner :_,,'Erigr.;i Western/i:Eiigineerihg^C6.%;^2105-^S.E:l ^ Ninth Aye.i`P.ortland-'14r'andV44D6 S.W.-:Dosch:: *'!Rd.r^Portland:lCOre.:^-'I^:/.S''.Kj`>.:J^< FORSYlri,' Stuart'L^'(Af'1944)'AdvisdfyEngr',- .' FREIJEr W^'F. ;(ltfrrl943)/Engr:;^Mgr Refng & v .W^tinghouse-'Electric;Corp.".r5915-Green^-St., U-.XAir-.Cond.vpiv.,. Hayes Br6thera.<=Inc.. 236 W:-. Emeryville 8,'and,1654'Capistrand Ave.. .Berkeley * .Verinoht'St., Indianap01is'A;faiiil'5411-vW:.Morris.. ' ^ 6 Calif:-^*i V. -f**:*- ' T-v-^r '. St:,.Ind_ian_a_p_o__li_s__8_;_-_I_n__d_:*:1'`-.''-.,j.. ^ FOSS*Benjamin S., Jr.;(A.1944)"Field :Engr.', . FREITAG, Frederic G; (M l932) #64:EIm'Ave. *53 ' . Br -F. Sturtevant Co.; ^401.'Magnolia /Bldg.. Mt' Vemon.-N^Yr^v' r v '.l{. - ' ~ Dallas'i;-and4400 Winston GouH;-'DaJlas9;Texas.*'. FREITES, Aa-nad--res A* .'/(Jr-1to9^4e5v)v.Jr-r^Ec*n_g~r...' - ^G-a--r-n--e- r: FOSSiVEdwiri R;';.(A;-1936) -Djst. Mgr., The . Corp., 300 Sr Geddes.St`.;,.and'1011 Walnut Ave.. r'V.:^Powere`>Regulator'^Co.;v135',Luclrier Sti * N.W., -J AUanta'3and 257.`Boiling-Rd;-NiE!' Atlanta,-Ga. - S.yracuse..'N. Y. . . >.... .... . - -. ,,v. FRENCH, Donald (M 1926).Vice-Pres Carrier v. S . FOSTER;rCharles:(L*ye.ifember; M 1923pCons. i -Corp:, Syracuse'l. and*Cazenb'ria/l'N:'Y * "t%1 *-/ >-r--.t:Engr/,-i'3l6iMSlical.:ArtsCBldgl,-Duluth 2, and . FRENTZELr Herman C. ;(JWil936)`Cons Lngr *^ * -4.2831%Er.First:St..`D'uIuthi.Minn; .r.' //. Frentiel^ Engineering .'Co.. v724'-/EMason<iSt.-.- FOSTER,"John;G:-r(Xl?38) Lt* Col;r,39th:Photo -!-MiIwaukee' 2.' *ahd*,4365' Nrj/Wildwoodr/Ave h c ^ --^^'Rdconi-SqV^Sahta/ManarArA.;FV; Santa Maria, Milwaukee IT Wls/-../ /.v.r, jj,'" ^Gsdifr,:ahd>2635 SedgwickAve.fNew YorkrN.Y. . FvO,ULDS; R; ATLl (Life'Membcf4, M1916).Partner, FREYDER, G.-,GmHA\1945)^Air: Cond; ;ESgr:!: '' . ^ CqmmbnwealthvEdisoh- C0./72..W/-Adams St.V'. .. ,,......... .. ^:'^i^2.'^*-Hubbafd|`,iRickerd:;&.v:Blakeley,f84^tale'.SU, .-Chicago 90, and-131-Clinton StrZPark-Ridge.'rlll.'-- - w ^ ^ -f`*Bostori,'ahd'72-WhitiirTAve.,;VRevere,VMass.'; - I,FtrRDIEriD,nLi'EPRD,-. Joseph J .V/Jr_r-; (Jf l940)tDist? lMKg__r 'l! t r- ^^t'F.OJVLES;- JlairyTH^CAM940 ;.V 1934); Ehp:'& " Ilg.Electric Vrentilating .Co.r304:Natch^ Bldg.-.'-r^ ^^-^-'v'Estimator.- V.'J. Kehneally Co;,104 'Hanover St.-;' New Orleans,vl2,/ahd 500y-Audub6rii Blvd.. -New.-^/- f\- ',>'^,:-:"--B6st6h;:'Mass.". arid1 e'.A Haskell St;,Auburn. Maine.- OrleaLns.lS/Ca. " * "* ^ Ernest--.'(M:.; 1935)<Asst... Engr^'o G.VA.: ' . FRIEDLIEB, Morton J/ (y. 1942) ' Plant^Engr;.-: * *l #? ' - ^ ^^-^Puhhaih-Cor, Ltd.,'1523:Davenport Rd.. .Toronto'-.-Super -Electric". Products -'Corp/"-1057 /Sutamit;- > ^ -`4sarid' 53lRushtoh'Rd..` Toronto.Ont..;Cajiada. Aye..* Jersey City. N.-rJ.;'and65^60':Bobih St ' '/ t^ '"FOX1\Emest:c;.(Af T944)>Mgr.VHtgr& Cooling .-fX Forest Hills, N.'-Y. ` - - -V-'-' p* -' - '* De'ptHageM&r Covet'Lumber -Co^v .ll25^ S. /' FRIEDLINE,:james:M;r(A 1942; ^1937) ;Capt J ^ Pecmsylyania.Ave'., /and .928: W;-'Michigan Ave.. 0317228/Hdq:. 79th Engr./Const? Bnr^A; P O ;/f /'Iiansing./Mich: /- 74, Sah'Francisco/Galif.t and:* Plymouth/ Iowa -/ j':?--;FOX;^Francis ' J. : (A -1945);: Owner. Gas Heat -. / FRIEDMAN,'^`'Arthur i-'(A.?;-1936)'..9Pres.;'Airvff/ ^ Engineering; Go".,^3020 E;. Franklin Ave.'.vMijnner'' Controls,- Inc:.2310 Superibr. Ave4,Cleveland .l4/ >< /apoIis,V'and/_3501--11th/ Avei :S/,`.' Minneapolis. -'/`and 15700 S. Morland'Blvd/.'ShakerHeighis, Ohio.-./ :. n ? .^'T'.^Mmnl/ v>'/4r'v?./^ ~.Vv::- " Z FRIEDMAN, David H.\?Jr. /(M ;1936) Major % <?zs--FOX,' Jbliri H.:(M 1935) Sales Erigr.-; Minneapolis- aihd *53T WhitneyAve./ New.Haven.'Conrii v %2-r ^ fr-Hoheywell'RegulatorVCo.>Ltd.`,-117 Peter Stvj and'./:. `FRIEDMANi^F. -J.* '(Jf/'i921)5;Mecfi?^Engr w^-^^-i37vMacE>onell Ave.,-Toronto.-Ont.'; Canada.--/V f . '-/ McDougall &vFriedmanVvl235;McGilliCbllege 1 : -^X>`^X7.>^Xii^.'^T'%&'J?FfXwi..'F.-^R:I'TCORChAedorAXacNirNaffuptjCr^KW:iihG/avKesppi"Lr.CefoipcGfhlFb.bi:'s$eAfa*;atb*'nv1I;renL1gVn.2vde/.0M*."l';((.D-AaX/tLv.n.X'eV;ld:igX9(eg3MX4er82'4it:i:t)0o')1ii:3A*9nER5t4/v,rdN5//eifNg)'.e/r:.e_Vr.YMr.e'-;.,Bg:DU-rpreb..iel.nSa;'s^Iw.vne;-Maald'rnuaeXdcs, .htA-Srxiini1/LarVe>7,l-/'-t/.//*^/.-F-^'*/nrQ'RAaNHnnuvI..Eede-aYF;..D:/,//C>-'M3MK--a3l;3o1naA'-na-w'NWtdur"ae^He.a's'Mnlt4/:23UrE4;-atvn-<o2n-d*.:4'r-d/iAy^:.:-lCv28. -e62AZn01dMA^9Svi3ap9t'=9rct4,,;k'i'J7)1a.a'4ycG1SMk9-t/se3:lN*o;c5>nM;te>?X-wSoH3>h/eiY1tiwrg9oe3hra3ktsl)...*:^.v-..---y;--;-- ./..ViM I ' ' fl 4 'I ..... ... n'v---'*5;-^'Piv.fiY<aktShipIey,->Inc.V and ;!303 W.-Phila- i'Melphia.Si.t -York; Pa., :. /. - :r. i 'g ^FRANK,'-John 1918;VA :i912)>Pres.. #Ilg ............j Elcdric.-Vehtilatihg Co.; 2850 N.-Crawford' Ave'.,. - Ebasco Services.''Inc.-, 2-Rector Str Ne'iv.York 6; X ^ / and 131;Riverside Dr.,'New York'24,-N./.Y. ^ ; ^FRISSEf John L. ;(A 1945)'Ovmer?7Tlie/T'herma1;>-'? I" > ^ Chicago,f''arid?iU52 : Gh'atfield/ Rd.Vc Hubbard' -"//Products Co/ 4500 Euciid;Ave.; ClevelaHd 3, and ,7. - l*. ' ',,7 " 17412; r Shelburhe -'Rd., /-Cleveland -' Heights -> I*, a; RANKEL/GUbCTt S. (M 1926)`rM^.. Federal Sc 18;-Ohio.Xi /.Xy /;. i/;-?v;/>' & -> 'FRITSCHE,"Carr (Jf-19) .The:-Carh Fritsche^ "^ V''Go/,'424 Park Ave/.East Orange N J ^ r ^: FRXTZBERG/Z Lawrence/ Hi`;7.(Wfc*1941) j; Engr.; uNbrthw^t;38th?:Oklahoma Gity/Okla/.. ,. _rFRANKLE,/Hariy-R.:'(Af:1941).--Paitner,.'*Mid* X <i.V-.He'5t?Air^Contrbl;.707Lbcust St..zDes Moines'i9, J%2' Air-'Cbhditioning'& Appliances,/.! lO/Wz.Seventh; ^ ,, and,547^44th/St., l3e8^ Moines,-.Iowa: /- 'IXzs-.:\'- ^://.Str, aJid ll4^;\V. Eighth St;,-Junction'CityrKans /;->>- t?/FRO^E;r.&l^djA::t(Mcl944)5B^<^0 Mgr-- ^ i >*^5? Y6rk';Cdrp..;.804/Security^Bidgrr ,650-i17thVSt//i/^.-^'v^H<, i^;T^fe /' arid/* 2581:Elni St/Denyer/ Gold ^ t yX > Oveiseas; and*# 204 Colonial Court; LyrichburgrVa.t :.-FLnTErRich^d:j.'/(A/1945)r`pist/Repr.7; Hoff -f, X ' FRANTZ/^Xdoipti/ R7-1?(M;n94i)'/Sarvice?Mgr.; >-r'Duo/Thenn IDiv.,. Mbtor/.Wheel'-Cbrp/VLansing. - ?^ahd> 1206/W. Michig3,n^A.yeo/Lansing 15,-Mich. r?FRXSER;Jaines'j. (A' l936) MgngrDir.', Honey/ ' - FULLER.- Charl^/AV^CAf/lQ^OTf'My^ers./I uller T 50 4 & -- ^ ,<'Vwcll^Bfp^^i/Ltd;.^Wadsworth Rd:., Perivale/ - T/ and ,Addingto'ii,'21-'East` 40th'St/.,tNew-York' 16 Z tji" Greenford;;Middlesex/!EngJand ;W and i:E^Flfth/StH=Mt.'-:V^on;'^Y> Sy^J^ w* _a Xj ; s p.* * FRAZIER^j^''&U'1,^(A?>:1936) Pres Frazier-*'^FULLER.fsClayton^W.Z'CXt/iMS^Engr.'/rDixieV^ ^ ris v.X'gy' *>: Simplex, iInc:; 436 -Ev;Beau St'.^'and- 7-.WilmbriG r.'./ Manufacturing:Co.,, Inc.r:i310 Russ#ell?SG',fcBalLi 1 - 1 2*- Ave/r-Washihgton/Pa.;i-;'/*. - / - -mbre.30. ahd # 5900;Highgate/Dr./Baltimore 15 4" " FREDERICKi-HoImes W: .1 -v^FUIAER;^EIbrtd^eW.V(M^1938);<Eng^friand^A'`S^^^, / 1524'GarciaAve/ Go`rkl,GabIes/FTa;5v??Vv-X X* ' andjRr/D?ilBc 3,;/^yereide/Aye.V/T^yefside, r-7 e.--.v^-,T^y'j?.Co-S>C*- ': 3 ' , FREEMAN-^ Alfreds.W/'.('J^1940;r5il939)~Capt:,' - -*pj^'#^-Air:1Gorps;^*J>99th Base.Unit-(Hq/A?:F.-T. A'/C;).' *"" .... . ~Z ' ^Orlando,^Fla/, and 3105^S8th StT"Jackson'Heights, 32. Heating::Ventilatirigf Air ConditioningsGuide. 1946* ' .*:- -C - FYFE; John H.(A 1944) - Owner. Suburban GAUSE, H. Chester . (M;'l937)' .Indus.' \Power. _ Engineering -Co., 211 Center Bldg., Lansdowne, Engrl, Alabama Power Co;', 600-North 18th,St.;- : \v ._v r 1.. '`and . 810 Eaton Rd., Drexel'Hill, Pa. . - P. O. Box 2641/Birmingham 2,'arid 3916iMont-;.' . --'*evallo.Rd:.-Birmirighain9,-Ala. - ^^ G - 'V' ' / / - . GAUSEWITZ,' William H. (A 1937) Pres., Yale. " Engineers! Inc., 2919/Fremont S., Minneapolis '. y. ' GABBERT.WilliamL. (Af l945) Dist. Sales - 8, ' and 1321 W.' Minnehaha Pkway:,' Minne-; / "" - , Mgr., American Air Filter Co.,-Inc., 215 Central apolis 9, Minn. ' . .' . r . 7 i*.*' . -Ave:; Louisville '8,--and *1138 Alfresco- PI., GAUSMAN, Carl E. (M 1923) Partner, Gausinan * * *. Louisville 6, Ky. ./ . .... - *. & Moore, 1026 -First National-Bank-Bldg., and -.' I-.,; '.. -GABLE, H.R. (A 1943).'Design Engr.,* Union ' >2360 Chilcombe Ave.; St. Paul, Minn. ` - - ' .-> .i '. ;v -r Steel/Products Co., 500 N. Berrien, and 017 N.' GAY, Clarence E., Sr. (M 1944) Mgf., Heaven - ^- Clibton,'Albion, Mich, ' -Engineering Co./l330 Broadway, Kansas-City 6, . - GAGE,- Burford B." (M -1944)' .Owner, *Gage .' and 410.West 17th'St..'Kansas' City 8, Mo... - ': : Plumbing SrHeating Co., P.-O.-Box 1035, and 139 GAY, Gikrence- E., Jr. .(J 1944) Asst.- Engr.,. . sv/v-r-r Overhill Rd., Salina,iKans.'-. . E. K. Campbell Heating - Co., 2445-. Charlotte, .* GALABA, Alexander (Af 1944) Chief Engr., '' :and *311 East 48th-St.. Kansas City 2, Mo. x " r- ~ Morrison Products,/Inc., 16816 Waterloo Rd., ' GAYLORD, F. H. (Af 1921) Vice-Pres. &.Geiu, .' A Cleveland- 10, -.and *1861 Beverly- Hills, Dr., Sales Mgr.. Hoffman Specialty Co.; Indianapolis, . ~ Euclid,Ohio. ... .' - " ' - ' ` Ind., and>362 N. York St., Elmhurst,'111. ,v .' 3 ,, GALLMEIER,:Sigmund H. (Af,, 1943) Mech;- -.-GAYMAN,8 Paul '.D.. (Jf 1938) Branch". Mgr., .': " t Fngr.;. 'Argonaut,-Realty Div., General Motors' . > Johnson. .Service- Co.,.. 2142 East * 19tH.r-St.,-.: ` ^ - Corp.', 307/G;-' M. - Research Bldg., Second and - Cleveland.''and 20875 -Endsley Ave., Rocky V ^Milwaukee, and *18495 Ilene, Detroit 21;-Mich. River/Ohio.' ' ? ./ ^ ; GALLOWAY, David (Af 1941) Vice-Pres., Bowen GAYNER, Jaimes (Af 1937) Cons. Engr., *624 Refrigeration Supplies;-Inc.; 323-Spring St. N.W., Hearst Bldg.; San.Francisco,, and 327 -Magnolia ' v " s,, Atlaiita. and 1018 E. Lake Dr., Decatur,' Ga. - Ave., Piedmont. Calif./' . ' -V'*'- GAJXOWAY; Max-W- (A 1946; 7 1944) Power GEBEL, Kurt M. (7 1944;.S 1940) U- S. Army - * l^ ~~ House "Foreman,'-'Allison-Div.,-General Motors. Air: Forces,' T/3; 31242168, Hq., Mis (Main).. ' ~- Corp.',rand'*1428 N. Pennsylvania.St.,Undiana- :U. S. F. E. T.. A'.'P.'O. 757 c/6 P/M.7New York, . "* - polish,' ihd;~ ' ; . - - , - ' -and 229 Beach-120. St/ Rockawaiy.Parkr N. Y.- ' J* . _ GAMBLE,"Burton.L. (A 1946; 7 1944) Design . GEHRS, William (A 1939) Branch Mgr., John-> , ." Engr",-Ferro Enamel Corp., 4150 -East 56th St., : ..son Service 'Co/ 316 'American Bank-,.Bldg.,-- " __ ^ Cleveland 5,'and'* 1857-East 85th St.,. Cleveland . Portland 5, and-3801 S-E. Woodward St., 'Port-!. "V* r 6, Ohio'..v : '. - ' land;2,'Ore. - ` - .." C fc ^GAMBLE. Cary.B. (Af 1940; A 1935) Cons.-Engr"., GEIGER, IrvluvH. (M 1919). Reg. Prof.-Engr/' -7/-- ~ Canal-Bldg/ New Orleansl2, and3432 Upper-/ />410 .-Telegraph. Bldg., and, 240 Maclay/St:,. 3j - line'SL.'New.Orleans lo, La. * ' ' Harrisburg,: Pa. . ' " * ' V\ - GAMMILL, O.iE., Jr. (Af 1940;A 1937; 7 1930). GEIGER, ,Raymond L. (Af 1939). Mech:-Engr., ^^ f Directoi/bf- Sales, .Cdrner Corp., 300 S.-Geddes V Austin Co., Noble Rd. and Euclid Ave., and. 1536 - -** Sl.vSyracuse.l, and 403 0ak SL; Syracuse, N.'Y. !' Dilie Rd./Eudid, Ohio. ' : . - -' " f ^_ GANNON,- Russell R. (Af 1939) Owner. Russell , GEIRINGER, Paul L. (Af 1943)' Licensed Prof. '. _ R./Gann'on Co.r-Gwynne Bldg.,' Cincinnati, and- Engr/ * 11 -Blake-St;, Newtonville, Mass. -v 6442-Grand Vista-Ave., Pleasant Ridge, Cincin- GEISSENHAINER,. Louis R. {A -1945) Owner, . j ^nati; Ohio. .... - - - v - ' - -- . " -. -'- L. R. Geissenhaider. 89 Broad St., Boston, and' - ' - GANT, H; 'P.* (Jf '1915), {Presidential Member), ' 64 Walton.Park,.-Me!fbse;'Mass.-. ^ * - * (rres., 1923; 1st Vice-Pres., 1922; 2nd Vice-Pres., GELERT, .Carl R;' (A' 1945)' Partner,. The. C R - v,, ^ - 1921; ^Council. 1918; 1921-24) RZ-D. 1," Gleh- ' . Gelert Co.,' 35 N.. Raymond St:, Pasadena. sand - more.Pa.- .- ; -*%-* 490.MayIin St., Pasaderia 2, Calif. .. . - - - GARBER, William E., Jr. (A 1944; 7 1938) Sales ' GELTZ/ iC.WULt' 1943;; /.1936) DisL/ Engr. ^ o- " * - Mgr., ; Farquar- Heating Service Co.,' 3406'East' York::Corp.;`2700 Washington Ave., Cleveland-, , lOthSL;Indianapolis, and *R. R. 1. Fairland. Ind. and * 14213 Glenside Rd., Cleveland 10/Ohio. GARDNER, Rollins (A. 1937) Vice-Pres..' :GENONEr HenryW.,:'(Af 1941) . Vice^Pn s in ^-7* - " Martyn-Brothers,. - Inc., 1000 St. Louis St., ' .-.charge .of ,/Ehgrg..>Dinkier ^Hotels Co.; .Inc.,1'.- " *X- - Dallas 2,vTexas.' - . r . - .~ - . Ansley Hotel, and 83-26th'St: N.E., Atlanta, Ga; > c GARDNER,':Francis.B.*(Af !944)-Htg.,LVenL & : GERDSENr Arno H. (A-.1945) Pfes.. *The A H _ % S'*' f\ Air .Cond * 3534 Whittier Blvdi-rLos Angeles-23^. > Gerdsn. Co.,/626 Broadway/ .Cincinnati. 2. and * ^.and-1654/IUvefside-Dr'., Glendale 1,-Calif. -'A.Y -- ' -Box-532, ?R. R;.-14, Beechgr'ove' Dr., - Cincinnati' S GARDNER.jMarvin (A: 1945; 'J 1944) *Ilg ... ll.-Ohio. ^ - . -./ . ' /' : ' '> ^ vC-Y' ^ Electric;Ventilatihg"Cd:, 1215 Texas Bank Bldg.,- GERMAIN, Oscar (Af 1935) V^ce^Pres;. Germain v ~t * - - Dallas L and 2725 'W:-Avon, Dallas 11,^Texas; - Frere./Dtd., 237 -St. Antqine St., ahd 1343... y GAJRNEAU/.Le6-(Af -1938;;/:-1930)'SaIes Engr.,-. c Boulevard St; Lbuis,.Troi9^Rivieres,-.Que/' Canada;--. v-sr> Cr 'A.`.'Dunham Co.YLtd.',-;Dominion''Square <:GERRISH, Grenyille Bl-CAf-1944; A 1936; `J 1930)>f ""i Z, %BMg.,ri010 ;SU Catherine -St..'W., .Mdntrral -'2/ " /Pres.,-Wolverine Equipment Co.,; 3l Mainc St.,-.- ** ' '/J - " "and 34-Coolbreeze. Ave:.-Lakeside,.Que:,:Canada;- Cambridge..42,/and 26 Standish rRd:/ Melrosev 55X^1/ 'v GARNETT,- William ' (M 1945) - Mech. Engr.; Z76,-Mass.' .-/A;/-''.. . > J % Wax Ordnance, Frahkford Arsenal, Philadelphia, YGERRISH,.HarTy;E.r(If 1910),:(Council;:i919). : ' and Ri F/Dr3;'Bethlehem, PaJ - - V /Pres/ W Morgan-Gerrish ^Co., ;307 Essex- Bldg., - V-' GARRISON, C. HU1 (M 1943) Owner, C. H. "'.Minneapolis 2;'and 4534 S. FremontAve/.Minne-:: . Garrison-Co.', 406 West134th St., Kansas\City 2, , - apblis9, MiimJ."-.. -> t and R. F. D. 3. Lee's Summit, Mo. :,'-f - v ' GERSTENBERGER,-' Edgar J. (A .1938).,Secy - ' *~ t. ^ , o, GARVIN,' Joshua L. (A 1945) Engr., Army Air *" Treas., - Glendale/Supply _Co., ' 1819T W. Glendale'; _ Field.'and 122 Woodland Sh`ores R(LY Charleston; ; -Ave.,- Milwaukee-9. and>3824. Norths 17th/St.; - S -C. r'*-"'* Milwaukee 6,-Wis:/. _ ^ *a '^ GATES;' A. * S.;- Jr. ' (M 1943; A 1941) Engr. GESSELL. E. T, (if i941)> W. E. Uwis'& Co ; (Naval.Archt.), Bureau of Ships,:Code 638, Navy - 610 Thomas Bldg., Dallas 1/and 2705 E. Amherst;-: Department; -Washington,; D.* -C., 'and *111 , I >Dallas 5,-.Texas."- - ` \ ^ Y Ccjunty'Rd.tiKenangtdn, Md. ' `YGETSCHOWi.Roy.M. (Af 1919) Pres.,> Philhps- ,_/ . , ^GATES,;,James-N., (Af 1944L Engr., .Air Con ; Getschow Co.', 32 W. Hubbard ;St.', .Chicago,* andr. ' ~~ S+ ditioiuhg',-Engineering Go., 90 Memorial; Dr., - '122 Woodstock, Kenilworth, ill.;//- "-Jl'.V.'.- - j ~ Cambridge,"and *179 .Washington SL.~Reading, GETTINGER. Edgar W. .<M'1945) Prod.-Design Engr.,' American Furnace. Co./. 2725 . "Delmar,-- ^^^^j^'^t:'^`jjGAULIN,:Richard P,\(A 1945) - Medi.- Engr., St. Louis, and'6j627-University-.Dr.;\Umyersity.t: Jh ' Federal'-Public'Housing Authority, Longfellow '7/-.City. 5, Mor ' g^^^^;^:B/VyldBlkdg;.., ahnd **55441144>' Eieghth,St. N.lW.,. WWaasshhininggtotonn^'. ' GEZARI, Zyl (A-1941) 'ResearchlDif.,.' Industrial: .Device' Corp,, 202. East 44th St., New York, and < ; /r> l(hWest 65th Stf.,New Yoric 23; N.^Yv^rX ^ GHOSE, .Khagendra-;N. (A-l938)Cons.' 'Engr.. / 17 State St./New Y6rk,iN. Y.. and' 39 Ramkanta'i /-"Bose St-. Bagh Bazar, Calcutta, Iudia;-,, "s;-''' _/ Roll ofrM[enibership - v- . : 33 . GHOSH; PZ B,' (A'1944;`J 1939) Deputy Dir.. . -^Civil Engrg., Government of India, Esplanade ' East, and 165A Janak Rd., Calcutta, India. -' GIANNINI, Mario C.'(Af 1935) Assoc. Prof, of ' Mech.-Engrg., Dir.,'/Evening Div.`, College of GHTLESON, Harold (A 1936) Sales Mgr., LaRiviere, Inc., 3715 St. Lawrence Blvd., Mont real 18. and 1125 Lajoie Ave., Apt. 6. Outremont, Montreal 8, Que.,- Canada. . - GIVELBER, Samuel H. (Af 1945) Owner.. Mech. - Engrg..,* New York University, University Heights Engr., Reliance Heating' & Air Cond. Co., ' 53, New York, and 322 Read Ave.,. Crestwood,- ' N. Y. ' ' .' ' . GIBBONS, Michael J. (Af. 1914) Gen. Mgr., - . M. J; Gibbons Supply Co., 601-631 E. Monument Ave.. Dayton, and *116 W/ Thruston Blvd., - Dayton 9, Ohio. ' -' - - ^- GIBBONS. Michael J., Jr. {A 1944) Htg. Engr., M. J. Gibbons Supply .Co., 601 E. Monument Ave., Dayton. 2/ -and *206 . Canterbury Dr., Dayton 9, Ohio. : . GIBBS, Edward . W. (Life Member; Af ,1919) Pres., The^ Smith-Gibbs Co., 201 S. Main St,, . and 39 President Ave., Providence, R. 1/ .' GIBSON, Harry E. (A 1945) Owner,-* Gibson . - - Sheet Metal Works, 965 W. Western Ave., and . R: R. 1, Muskegon. Mich.. ' - -' 7700 Stanton Ave.. Cleveland, and 3411 Bradford, .. Cleveland Heights,'Ohio. . - GIVIN, Albert W. (A 1925), Vice-Pres.. *The , Gurney Foundry Co., .Ltd.. 4 Junction Rd., Toronto, and R. R. 2, Freeman, Ont.; Canada. ' GLANCE,' Alvin C. (Af 1943) Field Engr., The . Anthracite Industries. Inc., 101 Park Ave.. New : York 17, N. Y.. and *R. D. 2, Allentown, Pa;. . GLANZER, Clarence -J. (Af 1944) Vice-Pres., Merit Machine Co., Merit Appliances'Div.,. . Box 84, Northfield. and Vesta Ave., Northfield- Center, Ohio. .- _ - .. GLASS, Robert (A 1943) Secy.-Treas., Part-. ~f ridge-Hoiliday/ Ltd., 144 Lombard St., Winnipeg, and 85 Claremont Ave., Norwood, Man;, Canada. ' . GIESECKE, F. E. (Life Member; Af 1913), (Presi --GLASS, William (Af 1934) Pres; & Mgr., Part- dential Member), (Pres., 1940; -1st Vice-Pres., -ridge-Halliday,. Ltd.. 144 Lombard-St., and 605 - / 1939; 2nd Vice-Pres., 1938; Council; 1932-41) River Ave., Suite "A," Winnipeg,-Man., Canada.' * - . Box 417, New'Braunfels, Texas. - ' GIFFORD,. Edmund W. (Af 1942) Dist. Mgr.. GLOVER, Ralph P. (A 1945) Cons. Engr.. e 1024 Superior St., Oak Park,-111. >HimelbIau. Byfield-'& Co., 6lL N. Broadway, GODBOLD, Bernard P. (A 1944) Prin. Optg. .. - Milwaukee-2, and 4457. N. Stowell Ave.,- Shore Engr., Smithsonian Institute, Washington; and ' wood 11, Wis/' ` ' .- - '' 1751 Lang Place; N.E., Washington 2, D. C-. ' GIFFORD, Robert L. {Life Member; Af 1908) GODES, Elliot (A 1942; J 1939) Engr,, Anemo- . .- Pres./. Illinois Engineering Co/. 21st St.` and slat Corporation of America, 10 East 39th St,, - _ ' Racine Ave., Chicago. 8, and 1231 .S. El Molino New York 16, and 925 Westend Ave., New'York . r Ave./-Pasadeha 5r Calif. . - 25, N. Y. " ' GILBERT, I. Wolfe {A 1945) Co-Owrier, Gilbert * . & Knight Co., 1300-Broad St-, and-223 Pleasant '. St., UUca. N: Y. -- ... GILBERT,- Leslie s. (Af 1937) Owner. Gilbert. -Engineering- Co., 1305 -Liberty Bank- Bldg./ Dallas '*1, and 3713: Southwestern Blvd/'. Dallas 5, Texas.- - . ' ' ' GODFREY, J.' E. (A 1946; J 1938) Ena, *Navy - Dept., Section Ad 4b, Washington, D. C.' - GODFREY, Theodore R. (A 1945)' Partner. ' . *F. H. Godfrey Engineering Co., 421 Vance ' ; Bldg.. Seattle 1. and 5212-18th Ave. N.E., . Seattle 5, Wash. ' -- ' GILBERT, Thomas {A 1940) Sales Engr., Empire GOEHLER, Elmer E. (A 1939) 1921 S.E. Grand - Brass Manufacturing Col; Ltd.. .London and - ' Ave., Portland, Ore. - *' - Hamilton, and 12 Ontario St. S., St'. Catherines, -Ont:/Canada. . GOELLNER, John A. (A 1945) Pres., Monarch . Metal Weather Strip Corp., 6333 Etzel ,Ave., - * ... GILBOY,-John P;`(Afl941) Sr. Member, John P. St. Louis 14, and 4729 Lee Ave., St. Louis 15, Mo. / -- - Gilboy.Co., and 521 Arthur Ave.. Scranton, Pa." . . GILBOY, William O. ;(Af 1945) Engr.. Cooney ' - Col/223 .Walton St., and 954 Lancaster Ave., ,, Syracuse, N. Y. - . ' ' '. - - ,, ; GILFRINj George F. (Af 1945) Owner, Edificio' La Nacional 601, P. O. Box 63 Bis, and Explanada ' 715,.Lomas de Chapultepec, Mexico, D.'F.' ' ' ' GILLE; Ha'dar B. (Af 1930) Cons. Engr., Hugo Theorells Ingeniorsbyra AB, Lagerlofsgatan 8, - /.Stockholm, and Svanhildsvagen 19, Nockeby, - Sweden.' ^ ~GILLESPIE, Harvey M. (A 1945) Patent Lawyer,.. . - 105 W. Adams St., Chicago 3, and 1442 Irving .. Park Rd-., Chicago, 111: . . ' GILLHAM, Walter E. (Af- 1945). Owner. Cons. - :Htg. & Vent. Engr., *401-402 Scarritt Arcade. ; Kansas-City .6,. and- 6336 . Morningside Dr./. -' -. Kansas City.5, Mo.' * * GOELZ-, Arnold H. (Af 1931) Pres., Kroeschell Engineering Co., 215 W. Ontario St., Chicago, and 827 Greenwood Ave., Wilmette, 111. ' GOERG,' B. ' (Af 1928) * American - Radiator & ; ; Standard Sanitary Corp., 675 Bronx River Rd., - " Yonkers, N. Y.. .' . GOERGENS, Albert G: (A 1938) Engr;, U. S. War Dept., New War Dept., Washington, D. C., and 817 Chalfonte Dr., Alexandria, ,Va. ` ' r .. GOFF, John A.*' (Af 1939) X)ean.v Towne ' Scientific School, University of Pennsylvania, . ; .Philadelphia 4. and 623'Righters Mill Rd./ Penn . Valley, Pa.' GOINS, E. H. (Af 1941) Dist. Repr,, Warren *, Webster & Co., 420 Market St., San Francisco 11, , and 2353 Laguna St., San Frandsco l5, Calif: - ./ GOLDBERG, Moses (A 1934) Pits.. Electric/ : / GILLILAND, Lesley L: (A 1942) Air Cond. Engr.. Motors Corp., 168 Centre St/ New York 13, 'and . , Air Engineers, Inc.. 1529 Second Ave'., and *4904 885 E. Eighth St.. Brooklyn 30, N. Y. * " - Seventh Ave., South Birmingham. Ala. - - GOLDMANN, Philipp (7 1942; S 1940) 238/ " ; GILMAN, -Franklin W. (Af 1935) Plant Engr.; ' Fellows Ave., Syracuse 10/N. Y. > .. - .- . ' Loft Candy Corp:, 38-38- Ninth St., Long GOLDNER, Herman W. (Af 1944) .Pres., Her- . . Island City,'-N. Y., and .The Chatham', 20th' and man Goldner Co Inc., 425 W. Lehigh Ave./ and . Walnut-Sts.. Philadelphia,.Pa. . . ; - . - .7415 Euston Rd., Philadelphia. Pa. - .- /- GILMORE, John L. (Af 1944; A 1938) Owner.' GOLDSMITH, F. W. (Af 1936) Pres.,> The W. - .''--John L. Gilmore, 1525 Cochran . Ave.. 1604 Clasmann Co., 513-E. Day Aye.,-and 629 .E;.Day '. Z Union St.,'Brunswick, Ga. . Ave., Milwaukee 11, Wis; - - . - - - r. - GILMORE, Louis A. (A-1940; J 1935; S 1930) GOLL, Willard A. (A 1937) Engr., W. A. Goii &; - Pres.,>Gilmore & Co... 115 South 11th St., Assoc., and 4423 Pine SL, Omaha, Nebr. St. Louis 2,' and,6633 Kingsbury, SL Louis 5, Mo. GONZALEZ, Rafael A. (Af 1936) Chrysler Corp;, - GINI/Aldo (Af 1933) Via Correggio 18, Milano. ' Airtemp Div., 119 Leo St.; Dayton 1, and *276- ' - Italy.'. - -* - '. . Delaware Ave.', Dayton, Ohio. - - . '' ' ' '.GINN, Tony M; (Af'1935) Gen. Mgr., Tony M. GOOD, Charles S; (7 1941; S 1939) Partner, A. C. _ / Ginn Co.,-214-24 Fifth St. S,, Great Falls, Mont. Good & Sons. 620-Rebeoca Ave., and 102 Cascade.1 >. / GINSBERG, Maxwell R.(A 1944)-Owner, Rd.. Pittsburgh 21, Pa. - ..- ' \ . - r- / American Construction & .Engineering Co., GOODE, Archie E. (A 1945) Mech/ Engr., & - , ' . '160-16 Jamaica'Ave.i jamaica 2, L.-L; N. Y. , .,. Draftsman. Robert & Co., Inc.,`Bona Allen Bldg.,''/..- ", '/ -GINZBURG', Nicola. (Af ' 1942) - Marine Vent.. Atlanta, and 535"E. Lake Dr./Decatur,'Ga... / ' . - Design Engr., The Pusey & Jones Corp/ Front & GOODHUE, -B. C. (Af 1945) Application'Engr./- . 7 .Poplar SL, - Wilmington;and *5 . Maple Ave., W'. A. Case & Sons Manufacturing Co., 115 N. Glaymont,-DeI.' ' I- .' ' . .Gdldes Sti/and 610 -W. Onohdara St.- Syracase, '.V'' ; GIRGIS,- Sobhi (A-1945) Engr.. Carrier Egypt, - N. Y. - - - . '.v- . - /v . /- S/A: E.,`37 Kasr El-Nil Si.; and c/o Sami G. El-. GOODMAN, C.- L. (A 1944) Mech. Engr.; *5715: -Masry, Rd.,15, Maadi, Cairo, Egypt..; . ' r 31st N.E:; Seattle, Wash.' . . - ' '/ IK'S'.' =?: v\/Z .34 ' ~ limiting Ventilating Air-.,,Conditioning. \ Guide 1946 GOODMAN, William (if 1941)-Prof.Cons. . - Engr.,!*Illinois- Institute of- Technology.' 3300 GOWDY, AUen C/(A 1941;'V 1939) M^-:, *The- .' Huffman-Wolfe' Co.. 308 Standard Bldg.. Atlanta. 'Federal St.. Chicago!'16,'and'5141.Greenwood. 3,-and 417 Hillside Dri S.W.; Atlanta, Ga- v'V. ' ' Ave., Chicago 15, III. *" ~ '- ' , GOODRAM.W.E. (M 1939; A 1936) Partner - GRABER, Ernst .(A 1942; 7 1936) Engr., Minnc , ' , ai>oUs-HoneyweIl Regulator 'Co.,; -221 Fourth ' . Mgr.; Goodram Bros.,-88 King St. W., Hamilton; .. 'Ave., New York, and *215 Hollywood'Ave.," and R. R.-2/Freeman; OnL. Canada. " . Doyglaston, L. I.. N. Y. ` ' * -' . . ; . GOODRICH, Charles F./(if 1919) Andrews &,, GRABMAN, Henry B. (/ 1942; S 1938) 1st Lt.. Goodrich; -1nc7' Boston, and * 336 Adams St., 0-393335. ' H & S Co.. 95th Engr.. Regt.. A. P. O. : `Dorchester, Mass.- - . ' . - ' -.350, c/o Postmaster, New York, N. Y., and 355'E. ' GOODWIN, Eugene W. (if ,1936) Mech. Engr.. - Spring St., Zelienople. Pa. ' - ' -. Public Buildings ' - Administration.-, and *7024 GRAHAM, P. D. (M-1940)JLocarMgr.,'*York ' ' .-^Hampden Lane, Bethesda-14, Md. '- " ' ;Corp., 422 Richards Bldg., New Orleans, and 420 1 * GOODWIN, Frank T. (A 1944) Repr.. Forest City ' Betz PI:, New Orleans 20, -La. .. - - ... - ' Foundries Co.. 2500.West 27thSt.. Cleveland 13, GRAHAM, William A. (A 1945)'Prod. Engr., ' Ohio, and *902 Ballard St. S.E., Grand`.Rapids Reid Hayden. Inc. 1238- W.' Morehead/.and ' ' * 7:^Mich." . ` `. `. ' 1638 Garden Terrace. Charlotte, N. C. ' . GOODWIN. Samuel. L. {Life Member;.M 1924) GRAHAM; William D. (Af 1929; A 1925; J 1923) '-`Cons. Engr.. John &-Drew.Ebersbn. 2-West 47th Dist. Mgr.. .* The Trane' Co.; Piedmont Bldg.. ". ``St.'.` New York, N. Y., and 247 Madison Ave.. ' "Rmr407."Greensboro,'N. C. I- r'~ , /Hasbrouck Heights, N-/J.- ' '' , s GRANDSTAFF. C. L. (M 1944) Edgf-.'Yhe C. A.- GOOD.WIN, Walter C. (if T945) -Negotiation * - Olsen Manufacturing'Co.; and *192 Longfellow . .. .-Mgr;, Air_ Cond/ Div...e Westinghouse Electric Ave.;. Elioia, Ohio'. ' . -Corp.; .150'Padfic'Ave;, Jersey City, and 57 Elm '.GRANKE, Arnold A,, (if 1939). Sales Engr.. V-SL7 Westfield. N; Ji' ./ Speakman -Co*. `816 Taitnall St., Wilmington 99, ,, GOOHS, William E,. (if 1944) Asst.: to Plant '-and *28-West 41st St-r Wilmington 220, Del. I - -\Engr.. -'Allison'`Div.. General Motors Corp.; GRANSTON; Ray O. (A 1939; J 1935; S .1930) - - Indianapolis, and #5910"Indianola Ave., India- . ' Partner. University'. Plumbing & -Heating' Co.; - ' napolis 5,_Ind. . ' " 3941 University Way,Seattle, .mid.,lSSS '^E^LSt-^ -. GORBANDT, Everett T. :(M 1941) Engr. & ; - ,76th St., Seattle'5. Wash. *1 . ' . . - {Partner. e Crawley-Gorbandt Co:. 118 W. Peach GRANT, Ralph A: (if .1945) Engr., *McCrea . tree. PI. N.W.,.and 2288 N. Decatur Rd; N.E., * Equipment.Co.', 516 Second -St. -N.W., Wash-. . , Atlanta, Ga. ' . ' i ' . ington/ and*.5050' First .St.- N.W;; 'Washington* -. . GORDON, Colin W..(A 1938) Vice-Pres. & Mgr.. - 1, D. C.. - v - ' -! i-s-*' - A. G. Baird. Ltd...286 Lisgar. St., and *962 Shaw GRANT, Walter A.* (if 1943;4.1933\ J 1929)^ ' -:SL.Toronto, Ont., Canada.' " ' - ' Dir. of Appl. Engrg.,, Carrier Corp-' Syracuse. ' k' ? .GORDON, Peter;B.;(if 1944; A- 1938; 7 1935) and Woods End. .R. D. 1. Camillus. -N; Y. -- V- -. ;' Treas...*.Wolff & Munier; Inc., 222 East 41st.St., GRANT,-Walter H.,r Jr. (if 1940) Mfrs.-.Repr.. 'v - :'r New'York 17, N. Y., and 35 Park Ave., Bloom .V Warren* Webster Co.; 209.. Vincent' Bldg..; , fieldr' N. J. ; - ' ' 'New;Orleahs 12/ and 5632' Elysian' Fields Ave./ . - ; GORGEN.-Roy E. (A 1940). Vice-Pres., The Day Co.;'810 Third Ave. N.E.. and *2120 W..Cedar : Lake'Blvd., Minneapolis,.Minn. . . GORNSTON, MichaeLH. (Life Member; A 1923) New Orleans 19,.La.' -. ' -' . GRATIOT; Jules (A 1944) Vice-Pres. in charge of - J Sales. Air Maze Corp;, 5200.:' Harvard Blvd.. . 'Cleveland, and *3312 Braemar; Rd., Shaker - Retired.'.Board of Education,.City of-New York/ Heights 20, Ohio. ` . ' - . .- t" /.arid * lll-32-76th Ave.. Forest Hills, N. Y. GRAVES, Charles S. (A 1945) Asst. Steam Ht. & . GORSUCH, Winfield- J. (A 1944) Assoc. Naval Water Service Engr.; * A. T. & S. F. Railway Co.. :.- ,; ;Archt.,'Norfolk Navy Yard, and *314 Harrison General Office Bldg., Rm. 409, and 1112 jewell'-i-V St:. Portsmouth, Va. ' . ; - St.-,-Topeka, Karis. ; ' * '! ..GOSS, Matthew H.'(if 1938)-Partner, M. H. . GRAVES, Clarence C. (if 1943) Partner. .* Graves / . .-'-Goss Go* 3409 Ludden.St:. Detroit 7, and.-296 . & Graves. 3047 Sheffield-Ave., Chicago'.14/and . ; 'E. Grand Blvd.;'Detroit, Mich. - ' .- 4041 N. Spaulding Ave'..r Chicago 18; III. - ' ' . - \ . ; GOSSETT, Earl J. (M . 1923) Pres.. Bell & . GRAY, Earle W; (if 1938; A 1934) {Mgr., .Indus. - . Gossett Co.,-8200 Austin Ave., Morton Grove.' & Coram'L Sales,' Oklahoma Gas &f*Electric Co.. - and 314-Woodland Ave.v Winneika.. III. - Third-and Harvey.Sts., and`2125' Northwest 18th , 1 -QOTHARDV William W. (A 1936) Gen. Mgr., .. St;.:Oklahoma!City, Okla:- . - - Domestic Engineering. .''1900 Prairie .Aye., - Chicago 16. arid 1027 Arlington Ave.. La Grange. *-111;.. * - V' - . V / ' * - GOTSCHALL, Harry C. (if 1935) Air Cond." .Teacher.,LanerTechnical High School, 2501 W.-. . Addison ,SL7 ChicagO;18,:and *2953- Eastwood GRAY, Emerson G. {J' 1944)Htg. Engr;, Gray. ' ' Engineering Co.',- P.' O. * Box. 264,- and-*16l2 ' Johnson St./High Point, N. C./,' GRAY, Evei-ett W. (if, 1936) Dist. Mgr., The , . Trane Co:,T1900. Euclid Ave., Cleveland 15r:and;- ,. Ave.',\Ghicagb:25, 111: - 'V' .:' 7 ` 17545 Madison Ave., Lakewood.7; Ohio.'% if f GOTTSCHALK, Kenneth-A./(A 1944) Indus; GRAY,. Frank L., Jt. {J 1945) Ehgr., Garrier--')' - . -Sales S/PoWer Engr.;'Cleveland Electric Illumi- Corp.. 20 .N: Wacker' Dr.y Chicago 6V and"5528 ; * :nating'Cb;,;75.Public Sq.', Cleveland lvand *3641 Maryland Ave;, Chicago 37,TI11-`' </ Wesi"46th SL/Clevelaod 2,-Ohio. .! . - GRAY,-:G. A.-(if 1924) Branch Mgr.'.'VG.'A*, v ^ GOTTSCHALL,/ Walter, C. (AA1945) Pres. .& Dunham Co./'-Ltd., 45, Rideau ,'St.`, ` and' 114 Estimator,'. Industrial -Insulation. Inc., Terminal ,. . Belmont*Ave^ Ottawa, Canada.- J.-- i - ** Office .BUfg:, Pittsburgh 19, .and *530 HiUcrest GRAY, Hamilton E. (A 1943; J 4940) Partner; ' Pl.,f-PittsburgK 16, Pa: . . ' ' . Gray Engineering Co., Box 264, and * l08.HiU- " GOTTWALD, C. (A . 1916) Pres., * The:Ric-wil -. -crest Dr., High Point, N.-C.' ' '/.* ' Co'.' l562 Union Commerce Bldg.. Cleveland, and GRAY, -William E. (M 1922)-Partner.,* Gray. ., 2225'Stillman Rd:, Cleveland Heights,'Ohio. Engrg- .Co., Box 264,-and-7l8 W. Farisa Ave-'; > - GOULDrHenry-E. (M 1942). PaHner & Mgr.. High Point. N. C. - ' . -r.* -Nqtkin'.&'% Co.. :1800 Baltimore, Kansas City' 8.- i: Mo,; and -2300 Wyncote Lane, Kansas City 3, : . -i Kana. 'v ' ' . ' -. ` ' i*. GOULD,'-James L. .{J/1942) Pilot, Air Corps. Columbus,-.`Miss., :and 1701 PoynU Ave.',. -.-Manhattan/Kans.' . - - - ; '' " : -GOULDBOURNE^ Thomas. H. r(Af 1944) -Sales . ' GREAR; Walter W. (A 1943) Engr., Freyn Bros;. ' Inc., 1028 N. Illinois St.* .and R.' .R.^l6.;?Bpx > ..631-5, Indianapolis. Ind. ' > ' - '' GREEN, Donald P. (7 1945) Supt.,'John E. Green ^ . Plumbing & Heating.' Co., Inc-/' and.* I0415;-... . Lincoln Dr.. Huntington.Woods. Mich.-f>.. `'. ? - -Dir.. .The Standard & Pochin Bros:. Ltd., Eyington GREEN. Edward;J. (A. 1945)' Secylrfreas/,'JohnJ / - rx Val1fy -Rdtand 39 Stoughton Rd., ;Leicester, E. Green Plumbing & Hearing Co.,-Iiic,, Highland.- England./.:,:'. ' : .. Park, and *181 Tennyson Ave.. -Highland-Park-v, IPS! *?-V GOULDING, William (A 1933) Air Con'd; Engr.. 3, Mich*. V ' /.' - -'.v f\ - v^Vi- Worid -Broadcast!ng Sysiem. .Inc;, 711 Fifth Ave.,` ' GREEN, Everett W. .(A 1946; 7.1938)Jr.'Partner,.;. t : .U'r.-.New^-York,,. an'd.* 42 Highview^ Ave.. .Tucka- . Green . Furnace &i -Plumbing` Co.;. and *2747. -` . ^^hbe/^Nf-V^r* - ' - . North'48th, Lincoln'-4`. Nebrl *"ft* T; T S1L '^'GOUNDiE'^JMeph K. (Af '1938)' Sales Engr.; GREEN, William; C.'; (Life Member'C:M:A906) zSV ,<->VFritch*Goal Go., 116 River-St-.,'-Bethlehem,.'and 426 IWalnut St.; Allentown? Pa/ ' Retired. 707. Race St.'. Rm. 317. GinanhatL2;;and3 % *- -.*244 Erbenbrecher Aye., Cincinnati-29, tfti0*5>r fy. Roll of Membership. V -' . GREENBURG, Leonard, . M. D.* . (if ':i932) ^GROOT, Hairy W. (if 1937/ Mech. Engr.. `Exec.'-Dir., Div. of . Industrial' Hygiene, *New. ,Supvsr. of Shipbuilding/-Evansville,' Ind., and /York-State Department of Labor, 80 Centre St., * *3728 N.-Westem Plcwy,, Louisville, Ky;,, / . !- New York 13,'and'44 West 77th St., New York, - GROSS, .Herbert'. A: (if 1945) . Dist. Mgr;/*. . N.fY. ' ' -- - - - / ...*<* - - ... ;*Surfa.'Combustion, 535. S. Seventh-St.,' and GREENLAND; Sidney F.-(if -1934)' Tech: Htg! - - 3705-Dupont Ave! S.', Minneapolis,' Mimi/.. V -'-'. ' -i-.v. - / & Vent. .Consultant, J. Brockhouse;&'Co:, Ltd:, / GROSS, Lester (A 1946; 7 1942) Chief-Engr.. . -'West Bromwich, Staffs.; and * 75 Grestohe Ave., ' General Installation Co.,'. 2234, Olive St., and ' . - Haridsworth Wood, Birmingham 20. England. . 1368 Shawmut PL, SL Louis, Mo. ' . " GREENWOOD. L.- D. (A 1945; 7 1943) *3104 .Main St., Rm. 201, Houston 4. and. 3650-Locke. -Lane. Houston 6, Texas.. GROSS, Lyman G. .(if 1931) ; Mech. Engr., Magney,' Tusler & Setter, -202 Foshay .Tower, . . Minneapolis, .and 5324 .Oaklawn Ave.. Minne- - GREGG, Stephen L. (A 1939; 7 1936)'Lt. Coindr.; apolis 10, Minn/ ! '' '- . . _:U`. S. N.'RV; Bureau.of Yards & Docks, Navy GROSS, MoirisH. (if 1944) Co-Owrier,, Heating. . Dept., 18th and Constitution Ave.; Washington . Ventilating, & Air Conditioning,*:8725 .Puritan, ; - -'-25, D. C;, 'and *4828'Edgemoor Lane, Bethesda - Detroit .21,"and 18434 Marlowe,' Detroit 19, -/'- :* ; 14, Md?-;. .. ---. ' Mich. ; :... -, ; ; GREGORY,. Henry D. (if -1945) Htg. Dept;, GROSS, Victor L. (A. 1944) Sales .Engr., Taylor^ ' . v . Hendrie & Bolthoff Manufacturing & Supply Co.',r* Forge &:Pipe-.Works,-50 Church St., New.York - ' ' .1635^17th.St,', P. O. Box' 5110. Denver 17, .and . 7.`and 281 Storer Ave., New Rochelle. N. Y. - v . 1042 S. High.St., Denver 9, Colo. ' . GROSSENBAGHER, Henry E. (A 1938) Pres.. / - GREGORY. Paul E. (A 1944) Sales Engr.; Horne- . Grossenbacher Furnace "Co.. , 9416 W.' Milton- ` . ' 'Wilson,- Inc.,-163 Peters St. S.W-.-, and 2054 '' / Ave., and 9741 Lackland Rd.,"Overland,- Mo.' - /' Chelsea Circle N.E., Atlanta. Ga.^ .. ` , -*. . .GROSSMAN, F. Arthur (A 1942; 7 1938; S 1937). - : ; GREILING, Winford W. (if 1942) Mech. Engr., 7 Sale8,Erigr., Servel, Inc.,'.122 S. Michigan1 Ave., * : The'.Austin Co';, 16112 Euclid Ave., Cleveland;- .. . Chicago-3,. III., and 867 S. Harlan Ave:; Evans- / , - and.* 1557 East 256th St.. Cleveland 17, Ohio. - - "7- ville;lnd/. * ' '. ' J.-GREILSAMER, PhiUppe (7 1945) Engr.. Air .GROSSMAN^ Harry ,E. (A 1943) Sales Engr./'. / : Cond:.& Refrig., 122 East 42nd St'., New York'22, : Mirineapolis-Honeywell `` Regulator Co.V . 5060 . ' - - : and*Hotel-Pierre; 2. East 61st SL,'-New-York 'Wayne Ave., Philadelphia.44,;and *2l3 Parham . o. " 21; N..Y.`, ' .. ?- Rd.,"Springfield,-Pa: . ' ' ' ' {.GREINER, Maurice C. (if -1945) Owner, Hess--"' GROSSMAN, Ralph: (A 1943) ' C'ombus;- Sales' - ..Greiner & Polland, 1700 S. Main St., Los Angeles': . Engr., Volcano;' Ltd.;:-1106 Beaver -Hall- Hill.--' - - '7-15, and.'* 1559 Club.'View Dr., Los'-Angeles : and *4130 Decade Blvd., ApL 10, Montreal-28/*- - . - 24. Calif. '- ' ' . . . ' . ; - . ' -- 'Que.! Canada. --- . .j1-:'- ` GREISS, PhiUp G. (if- 1937)'Mech;. Engr;, . GROSSMANN, Harry 7A. - (if 1931) .Owner, /' . . 'Voorhees, Walker, Foley.& Smith; lOLPark Ave., H-. A. Grossmaim Co.;' 3i38 Cass Ave.'. St.- Louis . ' -7* New-'York, N. Y,, and_*189- Walnut Ave.. , 6. and 16 Huntleigh Downs, Route 5,-'Kirkwood. - ' Bogota, N. J. .' "-7--I.-. ` . " 22, Mo. /- . - * , : - - '--/ /-.* ' . GRIEST, Kermlt C; (A -1940/7 1936) C .W/O, ^ Commander Service Force. Pacific Fleet. F.P.O., ' - San 'Franasco/'- Calif.,: and 38 -Greenlee Rd... . ! -. Pittsburgh 10. Pa. r . GRIEWISCH, Alfred H! (A 1938) Pres.; Bayiey 7 * Heating Supply Co., 2045 W. St. Paul Ave:. ' Milwaukee 3. and 2557 North 47th" St., Mil-. .-.-waukee 10, Wis. -. ~ - " ;. r- GRIFFIN,- Charles J. < (if 1940) Lt. G.g.).-and "''_/.*8231'S. Loomis Blvd.,-Chicago. III. GROSVOLD; F. E.-- (M 1944) Owner, *F. E. _ ' Grosvold - Heating' & Plumbing,' 417 Wisconsin ' ' St,, and 606 Dodge St:, Eau Claire, Wis. ' ' ' ' GROTH, Don R. (A 1945)'Dist.'Mgr::*U. S. Air. ` '.Conditioning Corp., 342,-Key Bldg., Oklahoma - " -^City t2,'and 227 Northwest 23rd St., Oklahoma " " . City-3. Okla.- . .. - GROVES;'Samuel A/(A 1940;-7 1935) AssLAo;/;:.. * '-.Pres./United Cafr.-.Fastener'Co., 31 Ames 'St.."- .' Z i Cambridge;' and 15'SyIvan: Rd., Wellesley. Hills - ; GRIFFIN, DeWitt C, (if 1943) Owner. DeWitt ' 82, Mass. ; -/ - -i . .,. . C/Griffin & Assocs*,'717 Lloyd Bldg., Seattle* 1, ' arid 652l-32nd N.W., Seattle 7. Wash. .- ' GRUTZMAGHER, Robert L, ;(if. ig45)-VicePres.. Natural Gas'Equipment.-Inc., 540'Petro- :. . . .. GRIFFITH, Claude A. (A 1938) Htg. & Vent. leuiri Bldg., Los Angeles 15, and 2121 N: Foothill v ; . * Engr., Griffith'Air Condiuoning Service, and *16 - - Blvd., Altadena. Calif. -. *. , Altamont .Terrace, Cumberland," Md. . GSCHWIND, Jean F;> (if, 1945) Dvlp. !Engf..:- . GRIFFITH/ H. T. (if. 1938) Lt-T U^S. NV. R., -- ;-J: O. Ross Engineering Corp., 350^Madison Ave.. . .<* . 105th -Naval - Construction Fleet- Post-' ' New York, and *720 Grand7 St.-,; Mamaroneck.-. * : ."Office; San 'Francisco.' Calif., and; 1909 Third'' - - N. Y. - ' - /'/./- ' - ; V ZT /-. Ave..W., Seattle, Wash. . . - GUEST, P; L., Jr. (A.1939) Owrier; *P. L. Guest -///- - GRIFFITH, Joseph B. '(A 1942; 7 1938) .Works ' 1 Sales Co., '311 Piedmont.Bldg.: 'arid 716 Dover * ` Mgr.,- Bryant -Heater Co.,-Tyler,...Texas Plant,. 7 Rd.. Greensboro, N.-C. /-/_ .'v- . and'.* 902vWhitaker, Tyler, Texas. - ` . GUEST, Ross Burton (if 1945; AT940) Owijer & ! " GRIGG, 'James L; (A..1945) Asst. Mgr:/Sheet , . Mgr:; The Guest Sheet Metal Works. 827-37 ` r^ .Metal Dept./ American Sheet Metal Go.-, 2713 ' Dryades- St., New. Orleans' 13,. and .1028,.City/.-; "v' Colley Ave.. Norfolk'/and *531' Fishennan-Rd., Park Ave., New Orleans, La. :-' 7'-:; , - _ . Norfolk 3, Va.. * '' ' r -' GUILBERT, Stanley R. (A .1940). Air Cond. /:/ - GRIMES,/FerinerVM. (A 1942; 7 1935>;Mech. Engr., The Riester-& Theamacher Co.,T526.West | ' - Engr., War'Dept;,' Office of the Chief, of Ehgrs., 25th SL, Cleveland;13, arid R; F. D. 3,- Chagriri- - ' Engrg..Div..-Specifications Sect., Washington 25,,- . Falls, Ohio. ; /"' f ' D. C.. and *849`S. Ivy St-Arlington/Va. ' GULER; George D. -(A "1937) Sales Mgr./Air . j / , ; CRISWELL',, H. _ D.- (A 1944) Vic^PresI.ri'The Cond. - Controls ' Div., Minneapolis^Honeywell '/' *. - Hosmer. Products Corp- 819 Massachusetts `Ave.. -Regulator Co.,-2753 Fourth.Ave. S., and-.2622, > ^ Indianapolis 4, and'H31 N. Delaware St.', India- ' " West 49th SL,'Minneapolis, Minn. c '. ` ' .. =. ,-napoliSr Ind- -. V- 1 ' ' - 7 v- ...GUMAER, F; WUcox (if 1937)"Engr./-The */-. / / GRISWOLD; Arthur S. (M 1945); Stafi;.Engr.,/ Barrett Div/'Allied -Chemical & Dye'Corp., -'40 / - `/-'-Ceritral "Htg.'.Dept., *The .Detroit Edison Co/1* RectorSt.. Nev^ York. N. Y.,`arid *25 Garden St.. - - - 2000 Second^Ave.. Detroit, and 5015 Pon Valley,.. 7.. West Englewood, N. J. . . -!;.*/.* /; ^ ,v -... * :' Bloomfield Hills,-Mich.^ V ' GUNZEL, Rudolph M. (if -1942)'_ Sales'. Repr!, .. '! , ,GRISWOLD, Edgar A:. (A 1945) Cons: & Design . > Rr.jM. Gunzei & Co.. 320-jCrockex; St/,/Los : ' %. ' - r'Erigr.',.*arid'*6041 -Pollard Stl, -Los Angeles 42, . - Angeles 13/and 375'La Mirada Ave/ San'Marino 7 ;-'Calif.V ^ ' . -.- - 9,'Calif..-' -' s- . . 7-:=,-/ -- - 7-^ v' 'GRITSCHKE; Elmer R. (if"1940).Cons. Engr.. GURNEY, E.-, Holt'- (if -1929)/ .^Presidential E; Rv Gntschke, l23 W. Madison St_ Chicago 2, ` '.Member), (Pres..: 1938;:lst Vice-Pres:; 1937;'2nd// ? and-4132'Gregory Ave/ Wilmette; III/ *.' 'i-Vice-Pres., 1936;-;Coundl, '1931r39) .Pres./!*^The., GRITTON, Earl.V, (if. i944)>Htg.-& VenL-Engr.^ * .Curacy.'. Foundry '.Co.,* Ltd!,. 4 - junction Rd.', : ^ - "7V Williams & Richardson Co.,-'204 Dooly Bldg., - ' "'Toronto 9, and 347 Walmer Rd;,' Toronto; Ont/ / /' ...v/3alt' Lake^City 1. and *24705South ;15th East.: .- Canada...V .'Z;. /./*!" .'s ` / ' iSt., Salt-I^ke Cfty, Utah. ;': T_- ./ ' GURNEY; Edward :R. (A. 1940J- 1937), Mech// /" '-'GROOM, Joh'n' W., Jr.*(A'.1943),Design-Engr., SupL. *'Electric Steels,* Ltd., Cap de. La- Made^ ': // and T Riverside Avel, Merrick. L. I.. Nl Y. ; leine, Que.*. Canada: / .-7 -v.-v-iV/Z?// 36 Heating Ventilating 'Air ' Conditioning Guide 1946/ GUSTAFSON, Carl A. (M 1938) Sales Engr.. -The-,Powere Regulator Co., 2720. Greenview Ave., and 6231 Fairfield Ave.. Chicago, 111.' v GUTKNECHT, Fritz (Af- 1940) Chief Engr.,_ HALL, George (A 1937) LL (s.g.). U. S. N.-R., , Hyland. Hall & Co., 218 N. Bassett St., Madison - 3. Wis. ' _ .' HALL, John A. (M .1943) Sales Engr., A. L. ,Blattmann-Weeser Sheet Metal Works, Inc.. Vanderhoof. Inc.. 233 Hanna Bldg., Cleveland'15, - ; 1001 Toulouse St., New Orleans, La., and R. F. D. 2. Gulfport, Miss. * . ' and 11030 Granger Rd..'Garfield Heights, Ohio. HALL, John R. (M 1937; J 1932) Vice-Pres..- c/o Vtsioneering Co., Inc., 4700 Prospect Ave'.. - .H ' HAAS, Emil, Jr. (Af 1945; A 1944) Partner, ' ' oNatkin & Co., 1800 Baltimore Ave.. Kansas City 8, and 5526 Crestwood Dr., Kansas City, Mo. ` HAAS, Samuel L. "(Af 1923) Pres.-Treas.. Advance Heating & Air Conditioning Corp., 117-119 N. Desplaines St.. Chicago 6, and 4300 ' ` Lake Shore Dr., Chicago 13; III. -. . HABASHI. Fawzi (S 1945) Student. Architectural Dept., Fouad 1st University, Faculty of.'Engi- , neering! and 3 Khouzam St.., Shoubre, Cairo, ; HA?&, Edward C.* (Af 1939) Dist. Repr., Air Cleveland 3, and 17700 Fries Ave., Lakewood 7, Ohio. `- HALL, Mora S. (Af 1934) Engr., William Born-, stein & Son. 2209 Channing PI. N.E., Washington;. D. C,, and 5004--42nd Ave., Myattsville, Md. .' HALL, Norman H. (A 1945) Supvsr.. East Ohio Gas Co., 1405 E. Sixth St.. Cleveland 14, and 147 Beachview Rd.. Willoughby, Ohio. ' - ' HALLENBECK, C. W. {M 1944) Dist. Engr.; T. C. Heyward; 1408 Independence 'Bldg., Charlotte, and. 2157 Norton Rd.,'- Charlotte 4. N. C. .- HALT, Howard R. (M 1943) Mgr., Htg. Div., Thos. J.'Sheehan Co., 2233 Olive St.. St. Louis 3, ' Conditioning Div., Westinghouse Electric Corp.,'. and 8729 Annetta Ave., St. Louis 15; Mo/ ' 1503 Gulf Bldg., Pittsburgh l9, and * 221 Broad-\ HAMACHER, K. P. (M 1938) Partner. Ham- moor. Ave., Mt. Lebanon, Pittsburgh 16, Pa. , acher & Williams; 2540 W. Wells St., Milwaukee'3, HACKETT, Frank C. (A 1940) Southern Dist. and 4387 S. Austin'St., Milwaukee 7, Wis;-1' *- - - Mgr., Bell & Gossett Co:. 607- Barr Bldg., - HAMBLIN, Clyde M. {M 1943) Principal Engr' Washington D." C. and 3017. N. Glebe Rd., Bureau of Ships, Navy Dept., and 1429 .'Iris Arlington,. Va. .' St. N.W., Washington, D. C. '' HADEN, G. Nelson (Af 1934; A 1928; J 1922) HAMER, Fred S. {M 1945) Design Engr., Surface ` Chairman & .Managing Dir., *G. . N.;_ Haden & Combustion Corp., 400 Dublin Ave., Columbus; Sons, Ltd., '19-29 Woburn PI., London, W. C. 1, and 2448.Northwest Blvd., Columbus 8,`Ohio.-' -and 36 WildwoodTtd.; London; N-. W. 11, England. - . HAMIG, Louis L. (Af.1941; A 1940; / 1935) HADEN, William N. (Life Member; M 1902) Partner, Ferris & Hamig, 516 Fullerton-Bldg., ~ Retired Chairman. , and.Arnolds .Hill, Trow- ' . St. Louis; and 7530 Buckingham Dr., Clayton ' . bridge. -Wiltshire, England. .5, Mo. ' , ''- HADJISKY, Joseph N.! (Af 1930) Cons. Engr., HAMILTON, Howard S. (A 1940) Owner.=*Air - #744 Bates St.. Birmingham,'Mich. - Comfort Co.. 1330 N. Franklin PI;, Milwaukee -HADLEY,- Lawrence G.' (J 1945) Apprentice . 2. Wis. * -. ' ' Engr.: Young, Austen & Young. Ltd... 19- Buck HAMILTON, M. S. (Af 1942) Southeastern Sales - ingham St.. London, W. C. 1, and 1 Salcombe Mgr., Air Cond. Controls' Div., Minneapolis- - Wave,- Ruislip Manor, Middlesex, ` England. Honeywell Regulator Co., 4-5 N. Rhodes Center,- IIAGAN, William V. fM 1938; A 1933; J 1926). and *3372 Walters Ct., N. E,, Atlanta, Ga.. . Owner, Vv J. Hagan.Co.. 506 Pearl St., and 7 .. HAMLET,- F. Aylmer (Af 1944; A 1936) Branch - - Black stone Ave., Sioux City, Iowa. Office Mgr., *C. A. Dunham Co., Ltd.. Dominion HAGEDON, Charles H. (Af 1919) Partneri' - S. E. Fenstermaker &-Co., 937 Architects & Sq: Bldg.,- Rm. 832. 1010 St. Catherine St. W.. Montreal 2,-' and Grove Hotel, Beaconsfield, Builders Bldg'.. Indianapolis 4. and 945 West 58th St.,'Indianapolis 5,. Ind. ./ . '' : HAGEN. George M;i(J 1944) Vice-Pres.. Hagen & Co., Halifax,.Ltd..-89 Hollis St., and 18 Coburg & Rd.,-Halifax, .Nova.Scotia, Canada. . -- - ; ' Pointe Claire, P. Q., Canada. . .- - HAMLIN, James B. .(A 1937). Capt.. U. S. Engi- ' neers Office, and 914 40th St., Savannah; Ga-' HANBURGER, Fred W. (Af 1938) Cons- Engr., *252 West 76th St.. New York. N. Y. . HAND; William L. (Af l944) Pres.. Cons. Mech.; HAGEN, Roscoe T. (A 1945) Maintenance Engr., Engr., *W;. L. Hand Engineering Service, 4102 - #The Perfect Circle Co., 552 S. Washington St., .and 53 Sr-Perry St.V Hagerstown,.Ind. ' " - - S. LaSalle St., and 8832 Dante Ave.. Chicago, 111. HANLEIN, Joseph H. (Af 1937) Vice-Pres.; . .HAGUE,- William' S. (A 1944) Mgr., Crane / *Wilberding Co.. Jnc!, 1822. Eye St. N.W., Co.; P. O.-Box 876. and* R. 1; Box 495,. India* ' Washington 6, and 5420 Connecticut Ave.:N.W.., .: napolis,*lndl - * ' Washington, D. C. ; '' ' . .. : K HAHN, Roy F. (A 1941; J 1936) Engr.. Advanced HANLEY, Edward V. (A 1933) Pfes., *S. V- c . Refrigeration, Inc.,.and 936.Argonne Ave. NiE.. Hanley.Co., 1653 N. Faiwell Ave., Milwaukee 2, ...Atlanta,*Ga~.-' - ; : .* . '*', ' - - < , `and 844 E. Birch Ave.. Whitefish Bay 11, Wis. ~ HAINES, .Jl E' > (Af 1940)' Mgr.V Commercial HANLEY-; T.-F., Jr. (Af 1933) Pies.. Hanley & Control Sales, Minneapolis-Honeyfrell Regu- Co.,'1503 S. Michigan Ave., and 1640 East 50th lato'r-Co.. and 2119* S. Humboldt AVe.. Minne- . - St., Chicago, III. .' - apolis.-Minn./ , . - ^ ` " ' .' ; , ` HANNAN. Lloyd F. (A 1945) Owner. Ace Sheet , * HAINES. John J.`-(M 1915) Pres.. The Haines Metal Works,'444 Clementina St., San Francisco :Co.. 1931 W. Lake St.rChicago 12. and 623-17th 3. and l343-32nd Ave., San FVancisco 22; Calif. ' . Ave.; Maywood, III. *' . - HANNIGAN, William' (Af 1940)' Bldg.' Supt.. HUTMANEK, Louis M. (A. 1938) Htg. & Vtg. Acacia Mutual Life Insurance Co.,.51 Louisiana . -Engr.. and #217 Rose SL,` Newark 3, N. J.\ .. Ave.- N.W;, Washington, D. C.`, and; Route '2,. - - HAJEK. William J.(Af 1945) P. O. Box 405, . - Knoxville,. Tenn'-^ -HAKES, Leon. M. (Af 1932; > 1929) Resident, -.-Repr., Warren Webster .& Co.,. 210 Reynolds . Arcade Bldg.,.Rochester 4 and 144 Inglewood Dr., Rochester .11, N. Y.* ' ; . . - Silver Spring,-'Md. -. ' HANSEN; John S. (A 1945) Testing rEngr..- Sears Roebuck & Co.. Dept. 817, 925 S. Homan Ave.. Chicago 7;'and-ii5 South Blvd;, Oak Park. HI.- . ' -- HANSEN, Willis A. (Af 1943)- Design Engr.. " G. M. Richards & Assoc., 333 Kearny St-., .San .HALE, Frederick J. (Af 1936). Mgr.. Empire Francisco, and 1440 California St.,. Berkeley * - Sheet Metal Works. Ltd.. .1606 WJ First Ave., Vancouver.? .and 995, Mathers Ave. W., Van . 3, Calif. ' .HANSLER, John E. (Af 1937) *723 Glen Ave.. .- . couver,'B.-.C., Canada.^ ' Westfield, N..J. . ' -" ~ HALEYr. Harry'.s,*- (M 1914) Cons:.'Engr. and HANSON, Lars C. (Af 1945) Asst. Dir. of Dvlpt.,' . 'Partner,:Leland & Haley,. 58 Sutter . St.-, San _ . Francisco.4,'and 735^21sL Ave./San Francisco, Calif.v-^;- - *?' * - \* - .' - Carrier Corp., S. Geddes St., Syracuse l;and-* 282 Robineau Rd., Syracuse 4, N. Y..- '* l.-' - ' HANSON, Leon C. (A 1939) Secy.-Mgr.. Bjork- . WHALEY; Robert-T. (A .1943) Mgr., Hearing Dept., , man Bros.. Co.,.712 Tenth St;, S., Minneapolis, Minneapolis.-Gas Light .Co.) 739 Marquette-, ; Minn. `- t v Ave.,: and 5340 Beard'Ave. S., Minneaplis.fMinn'. HANSON, Leslie P. (Af 1937; A 1936; J 1935;: ; ; HALLV Elmo .'(Af A944)' Owner,:* Empife\Gas & . S'1933) Sales Mgr.. Air Cond. Equipment'Div.; .- Equipment Co.,'1198 Stout St), and 1449 Ash'St;,' U.'S. Air Conditioning Corp., 2101 Kennedy N;E., Denver',-Colo.*'-- ' and *5027 Nokomis Ave. S:,' Minneapolis, Minn. -Roll of Membership^ ' 37 -HANTHORN, Walter (A 1942: J 1939) Engr.; HART; 'Harry M.* (Life Member; Af 1912), Kleenair/Furnace . Co., 5329 N.E. - Samly Blvd., (Presidential .Member); (Pres.,'1916; 1st-Vice-. , ' and-*2946 Northeast 54th Ave., Portland 13, Ore. - Pres., 1915;'- Council.' 1914-17) 'Pres., *L. H;:` HAPPERFIELD, ,G. J.- (Af 1943) Managing Dir., .Prentice,Co., T048 Van Buren SL, Chicago 7, and - Chandos Engineering Co.. Ltd., 10 Chandos. 3730 Lakesbore'Dr., Chicago, 111. .' ' " St., Cavendish Sq., London, and 468 Staines Rd.. HART, John H. (Af 1942) Lt. Comdr.; U. S. N. R.. " Twickenham; Middlesex. England. ' Navy Dept., Bureau of Ships, Washington, D..C,, ; -HARBERGER, G. L. (A 1939) Mgr., Boiler & , Htg. -Dept.. Eastern Foundry Co., Boyertown; - and 641 King St.. Pottstown; Pa. * - and 1506 Mount Eagle PI., Alexandria. Va. - ' HART, Stanley'(Af 1938) Pres., Tuttle & Bailey, ` Inc., and 60 Chatham Rd., New Britain, Conn. , _. . . HARBIN,, Frank, Jr. (Af 1941) Engr., Home Furnace Co.. 280 E. Sixth St.; and 181 West 21st -. St., Holland. Mich. ' . *. HARBORDT, Otto E. (A 1936) Treas.. *U. S. Supply Co.. 1315 West 12th St., and 4600 Mill Creek Pkwy., Kansas City,- Mo. .. HARDEN, J. Clinton'(Af 1938) Engr.. Round Oak .-Co., .and 106 Courtland St., Dowagiac, . Mich.' . :. - . .. . HART, Theodore S. (Af 1938) Partner. Brenton & Hart. 6 Beacon St., Boston, and 530 Lincoln St., New Britain, Conn. ` . .- HART, Winston W. (A 1945) Jr. Engr.; Carrier . .Corp., and *768 Ostrom Ave., Syracuse, N. Y. - . HARTIN. William R., Jr. (A 1944; J 1935)"Vice- . Pres.-Secy., 2123 Green St.. Columbia 41, and -- 2744 Thenholm Rd., Columbia 32, S. C. ' - HARTMAN, John M. (Af 1927) Engr., Kewanee - Boiler Corp.. and 618 EUiott'St., Kewanee, 111. - - HARDER, Ervin P. (A 1944) Product Application HARTMANN, Charles W. (A 1944) Sales Engr., . Engr.. Herman Nelson Corp., St. 'Louis, and ' A. F. Hinrichsen, Inc.. 50 Church St:. New York ' 1502 Collins Ave.,' Richmond Heights 17, Mo. ' 7,' and 551-72nd St.,'Brooklyn, N. Y.' . . HARDIN, James T. (Af 1943) Mgr. of Hearing HARTON, A. J. (A 1935) Sales Engrg., St. Joseph Dept., Roland M. Cotton Co:. Inc., 1720 E. . Light & Power Co., 514 Francis. and*730--E. Tenth St., Indianapolis 1, and 1204 West 29th St., Hyde Park Ave.. St. Joseph, Mo. - -- - . Indianapolisi Ind. -' . HARTSFIELD, Charles G. (Af 1944) Vice-Pres. HARDING, Edward R. (Af 1936) State Sales and Gen. Mgr.. Atlantic Engineering Co., 730 " . . . -Engr. & Mgr.. Kewanee Boiler Corp.. P. O. Box . S. Elm SL, Greensboro, N. C. . ."' 536; 1003 Jefferson- Std. Bldg;, Greensboro, and ' HARTSOOK, Granville S., Jr. (A 1939) Owner. ... Guilford College, N. C. - . .- * - Hartsook Plumbing & Hearing Co.. 21 S. Royal 1 HARDING, Louis'A.* (Life. Member; Af 1911), Ave., P. O. Box 361, and Front Royal, Va. ' - (Presidential-Member),. (Pres., 1930; -1st Vice HARTWEIN, C. E. (M 1933). SL Louis County - Pres., 1929; 2nd Vice-Pres:, 1928; Council, 1922 Gas Co., 231 W. Lockwood Ave., Webster Groves - .31) Cons. Engr.,- and *85 Cleveland Ave., Buffalo 19, and 135 Peeke Ave., Kirkwood 22. Mo. *- ** . - / 9, N.*Y. . HARTWELL, Joseph C. (Life Member; M 1922) . / HARDING, Walter (Af 1941) Supt.- Engr., Air . .Ministry, N.E. Wing. Bush House, Kingsway, ' and Danesfield House.' 33 Bute. Gardens, Wal, lington, Surrey, England. HARE,- W. Almoh (Af 1941) Prop., Hare Engi- - neering.Co., 165 W.- Congress St.. Detroit 26, Mich.', and 833, Kildare Rd., Windsor, Ont., - Canaria. .. -.' Pres.. Hartwell Co., Inc., 87 ` Weybosset' SL, and 16 Freeman Pkwy., Providence, R. I. ' .- - - HARTWIG, Walter J. (A 1945) Mech. Engr., ' Service Command Engineer. Federal Bldg., ' Omaha 1, and *4516 William SL, Omaha 6, Nebr. , HARVEY, Ai D; (A 1928; J 1925) Vice-Pres.. - The Dorr Co., Inc., 570 Lexington Ave., New ' York 22. N. Y. HARVEY, Ernest W. (A 1943) Application Engr., r HARMAN,' Ralph H. (A 1945) Archt.. 2W.S Westinghouse Electric- Corp., 1014 Fairfax' -Columbia- St., and 330 Broadmoor Blvd. N-, Bldg., and 210 East 72nd SL, Kansas City, Mo. Springfield, Ohio. : HARVEY, John W. (Af 1942) Managing Dir., . HARMONAY. W. L. (Af 1944; A 1935) Pres- Sterigas Construction Co., Ltd-, .2 Gorst Rd., l - Michael Harmonay Corp., 124 Elm St,, Yonkers London; N.'W. 10, and *64 Crowshott Ave.;. - 2, and 1360 Midland Ave., Bronxville, N. Y. ' Stanmore, Middlesex, England. - -- - HARRIGAN, Edward M.(Af 1915) Pres. & Gen. HARVEY, Lyle C. (Af 1928) Pres., The Bryant ' . Mgr., Harrigan & Reid Co., 1365 Bagley-Ave.. * and 7450 LaSalle Blvd., Detroit, Mich. . Heater-Co., 17825 SL Clair, Cleveland .10.' and ' 2666 Leighton Rd., Cleveland. Ohio. - - HARRIGAN, Edward R. (Af 1939) Lt.. U. S. Navy', -Navy Yard, New York, N. Y., and 19 Erwin PL, Caldwell, N.,J. - . ' HARRIGAN, John E. (A 1945) Plant Facilities ' Engr., U. S. Time Corp., 31' Cherry Ave., .Water . bury, .'and . 1081. Huntingdon Ave.,..Waterbury - -.46, Conn.' .- ' `- ' -. HARRINGTONrDavid.W.* (A 1943) Sales Engr.. ' *.Dallas Air. Conditioning Co;. 2809 Canton St., and 1549 El Campo, Dallas, Texas. - - HARRINGTON, Elliott D.* (Af i932; A 1930) Mgr., Induction Motor Div,, General' Electric HASHAGEN, John. B. (Af 1930) Prod. Mgr., of- Food Products, 1750 N. Ashland Ave.^and *4236 N. Mozart SL, Chicago; 111. -- . '' HASTINGS, Addison (Af 1942) AssL Secy., Sales . ; Engr., Bumham-Boiler Corp., and Lewis. Rd., ' Irvington, N. Y. ^ .- HATCH, George (A 1941) Htg. & VenL. Engr^- : . . *3527 Carnation'Ave.. Los-Angeles 26; Calif. ` - '. HATCH, O: J. (A 1941) Mgr., Clare Bros. Western, Ltd;, 179 Notre Dame Ave. E., and 26 '.. ' Rosemount Apts., :351 River Ave.,'.Winnipeg,. Man., Canada. . .. V .' ` r ` HATTERSLEY, Eugene H. (Af 1943) Member of f - Co., 1 River Rd.. Schenectady, and The Haw -- thome. R.- D.- 2, Altamont, N. Y. -' - .- Firm, *A. Hattersley & Sons. 212 E; Main SL, FL Wayne 2,-Ind. . . HARRINGTON, Jeremiah P. (A 1944) Mech. -Engr., U. S. Engineers,' and 1515 Mirasol, San * Marine, Calif.. , . - - HATTIS, Robert E. (Af 1926) Cons. Engr., *26 E. - Jackson Blvd., Chicago 4, and 1454 Fargo Ave., . ' Chicago 26, I1L ' I - ' HARRINGTON, Lariy. J. (Af 1941) Owner, HAUAN, Merlin J. (Af'1933) Cons. Engr.. *34l2 ' ' Larry Harrington Co.-, 1971 N.W. Lovejoy St., ' . -16th St. S., Seattle, Wash. . ' .- Portland 9. Ore. -" ' * . . HAUER, Fred W. (A -1938) Owner, *Fred Hauer' ' HARRIS, Herbert J. (A 1945) Pres:, Marion Oil & Co., 315 Elmhurst Ave., Peoria 4,111.'. . --r & Service Corp., 222 N. Fifth Ave., Mt. Vernon, HAUF, Joseph C., Jr. (A/1944) Exec. Sales Engr., 1 and 7 Croydon Rd., Yonkers,-N. Y.. - - Geroter May Corp., Box 86. Badrimore, and *4204 ': HARRIS, Jesse B. (Af 1918) Mgr., Jesse B. - Tuscany Court,7. Baltimore 10, Md. ` .Harris Co., 702 Wesley Temple Bldg.. Minneapolis HAUS, Irvin J. (A ^1937; J 1935) SupL of Maiu-. ` .. 2. and.3620 Colfax Ave. S., Minneapolis 8. Minn. . . tenance, Nash Kelvinator Corp., Seaman Body: '' , HARRIS; Warren S.* (Af . 1942) Asst. Prof, of ^-Special Research. University'of Illinois, 801-W. ` Green St.,.and 802 N. Broadway, Urbana, 111. " HARRISON, Paul N. (A 1945) Owner, Paul N. - Harrison Co., 50 Hawthorne, San Francigco.-and ^,2301 Ivy Dr.,-Oakland, Calif, ---v HARRISON,.'William Z.- (A- 1944) Owner, PlanL 3880. N. Richards' SL;-Milwaukee' 1,' and - 2211 North 51st SL,-Milwaukee 8. Wis; - - - * HAUSMAN, L. M. (Af 1945) Pres., L.- M,' * Hausman & Co., P. O. Box 1729, Manila, P. I: . IZAUSS, Charles F.* (Charter ^Member: Life Afrm6rr)rRetired;.'and Ball. Heights, California;'*' Ky. ; __ : - - .. ' . Harrison'& Co., 210 S.W. Temple St., Salt-Lake .HAUSSER, Fred L.' (A -1945) Partner, Ward &' ' City 1, and 1127 E. South Temple St., Salt - Lake City.2, Utah;-. -' - . Hausser; 17 Seyms SL, Hartford 5, and 178 Four '. Mile Rd:, West Hartford 7, Conn. . . 38 /'V - -; Heating Ventilating Air CohditLon,ingr 'Guide 1946 - . v MW .HAWES, Harold D. (7 1942; S 1940) Lt:,'U^S... HEINKEL, Charles E. (/' 1938) . Branch Mgr.. . ..Array, and.454:ToilsomeHiURd., Bridgeport,.. The Trane Co:, 426-Postal Bldg... Portland 4,-.- . - ' ''Coon." ' . -./ '- . -v and 1620 E. Burnside. Portland 14; Ore. HAWISHER, Harold H. (A 1938) Mech. Engr... HEISINGER, Frederick W. (A 1945) Mgr.viHtg. . ,, ' . Automatic Heating & Engineering Co.; 416-418 - & Vent.- Div.; Benedict- & : Benedict, 1433 El -. '-N. Main St/and 411S. Jamesori-Ave., Lima, Ohio..- ' ! ' Coloiado St., Pasadena; and* 3375' Gale- Ave., y-.-- * - "-HAWK, Charles A.,;Jr. (A 1944) Mgr. _Engrg. - ..Long Beach 6, Calif..' ,` . . Service-Dept.. A.' M. Byers'Co., '.Clark Bldg.,.' . HEISTERKAMP, Herbert W. (A 1940; J 1937) ' . . . .Pittsburgh!-and *604. Pennridge 'Rd/ Chatham - Mgr. Dehumidifier 'Div.! Bryant Heater,- Co.,.-'. Village, Pittsburgh 11, Pa. - ' . ' 17825 St. Clair Ave., Cleveland 10, and;175 East - .. . HAYES, James J. (M 1920) Vice-Pres.. Stannard 207th St., Euclid 19,-Oluo. ! '' ':' Power Equipment Co., 53 W. Jackson, Blvd,, . HELBURN, I. B; (M 1929; J 1927) Jr. Asso., . -Chicago4; and 2515 East 77th St/Chicago49;ill. - Wyman-Engineering, 1306 Chamber of Com- * -7 / HAYES, Joseph G. (Life Member; 24 1908)Pres. ; .mercc . Bldg.,-"Cincinnati 2, and-_781 Clinton '. ' -Y'&'.Engr./* Hayes Brothers, Inc., 236 W. Vermont Springs, Cincinnati 29, Ohio. . ' V ...... St!., Indianapolis 4,-and'2819 N. Capital Ave:,/ HELFiNSTINE,'Roy J. (if 1943) Mech. Engr., ` ' -Indianapolis 8/Ind.` . - Illinois State-Geological Survey, 214 Geological . \ . rHAYMAN, A. Eugene, Jr.(A 1941; 7 1935: .'-Survey Laboratory, Urbana, and 55 E. Armory. ' . - ' .S. 1930)-Sun Oil. Co.. Marcus Hook. Pa..; and . Champaign,'Ill. ' - '. . ' 2715-Washington St., Wilmington 239, Del. - " HELLEND, Albert E. (M -1944) Lt.. .Engrg. HAYNES/ Charles V. {Life. Member-, M 1917);. ; . Office, U. S. N. R,, U. S. Si Kline, A..P. .D.-120.. I _ --{Presidential. Member),. (Pres.;. 1934;. 1st- Vice-'-- 'c/o Fleet Post Office, San -Frandsco, Calif.,-and. \ . .Pres/ 1933;.2nd VicerPres., 1932; Council, 1926 , *4549 N. Magnolia Ave., Chicago, 111. - .- . 29;, 1932-35) P.-OBox26, Ardmore, Mont. Co.., HELLER, Joseph A; (A-1938):*Air,Conditioning. .: Pari ande P. O. Box-E, Woodford Sta., Portland - Utilities Co.,. 8 West 40th St:. New York 18. and - ' - * 5/Maine. r"'- , ` - , % / . . 150 West 79th St., New York 24, N..Y. - , HAYS, Herbert G. (24 1945) Chief Engr.. Arm HELLMERS, .Char!es..C-, Jr,. (A 1942;./: 1937) . 'S;-, strong-Furnace. Co.', 1639 Olentangy River .Rd., . . Piping Supvsr.. Sione & Webster .Engineering ' *'* and 1066 Chelsea Ave., Coluiribus, Ohio.; -. . Corp.,- Clinton Engineer Works! P. O. Box-1751, '7 ' HAZLETT; .T. Lyle, M. D. (24 1938) Medical -'.Knox>rtlle,-and 184.Ash, Rock Gardens, Alcoa, ' : ;; Dir;. -Westinghouse Electric/Corp:, East- JPitta-. , --'Tenh..' . .'s' 'burgh, Pa. HELLSTROM, John, (A, 1929) Vice-Pres.,'/. \ HEACOCK, Grosvenor W. (A/1945) Mgr., Htg. V ` American-Air'Filter. Co;,. Inc., -215 Central .., . -.Specialties 'Div.,.eO'Brien- Specialty.-Co... 205' -Ave.,-and 423 Lightfoot-Rdl/Louisville, Ky.' -'-y * -. ` -Harrison ;St... Syracuse 2; and' 1105 E. Genesee. ' HELMS,.Loyd.J. {M 1945). Mech! Engr;;,EngUsh. - . "= St.;.Syracuse; Nt-Y. -i . &' -Lauer,'; Inc.. 1978-S.'. Los Angeles. St;, Los . . ' HEAGERTYi"William H. (A-1940) Sales Engr., - -Angeles`-11,- and 633 Berendo. Los' Angeles- . - - Chandler Bldg.," and 5100. - Capitol St.,- /*. 5; CaUf-. . *-/Washington, D. C. / \ * : V HELSTROM,.Clifford W. (M -1938) Sales Mgr..1 - HEAPHY, J. .Arthur-(A 1945) Pres. & Owner. - & Vice-Pres.; Globe Machinery-& Supply -Co';,. . - . D.-Jl.-Heaphy & Son, 133 N.; Geddes ` St., . E: First and Court Ave.', and.* 1614 Thompsons. - ^ Syracuse 4/ahd 101 Wellesley Rd., Syracuse, N.-Y. .- .Avei.iDes Moines 16. Iowa. ' ' -- / ",- * ' -. V HEATH; George A;,(A 1944) Sales Engr.. *P. O. . - HH5TROM!' Herman1- G. {If 1936). `Northwest ? ' -Box 207,'and 24* W.-Marble St;, Mechanicsburg,'. Sales MgrV William Brothers-Boiler ,&-:'Manu- - .' 1`r`vr Pa.'; -'-.' -- - - facturing Co:, 1057 Tenth Ave. S:E., arid *4608 ' . '. HEATH; William R. (M 1931) Asst. Chief.Engr.,' Arden Ave." S.t MinneapoHs 10, Minn. *" ' -.Buffalo Forge Co., ,490 - Broadway; and.1191. HELWTCK, Numa J. (M 1940) Partner. Ameri-. * . Wingate Ave.r-Buffalo, N. Y. . can. Heating & Plumbing Co., 829-Barohne St.,. , . ; ' 'HEAVEN;' Lewis P; (24 -1943) Owner. Heaven : and-809 Greenwood Dr.,-New Orleahs,-La- - - Engineering Co.;, 1529 Wyandotte. Kansas City 8; - and 2942 Bales Ave.. Kansas City 3. Mo. ... Z HEBLEY.'Henry F. (M 1934) Dir. of Research. -. Pittsburgh Coal Co., P. O. Box 146, Pittsburgh. 30, and`216 Jefferson. Dr.', Mt. Lebanon* Pitts -' - burgh 16, Pa. .. ' -.i ' V -. .HECKEL, Edmund P. (24 19l8)#E.P.Heckel r-v. & `Assoc., -100 W;, Monroe St!, -Chicago, - and 314 HELWIG. E. Cornelius (A 1945) Asst, to" Pres.-, - Tanner 8t Co.; 409 S. Pennsylvania St. India-; napolis 9, and 4162 Ni Meridian St.. Indianapolis 8, Ind.-! . ' . y '- -. 7 HEMEON, Wesley C. L..(M 1944) Vent/Engr.. Industrial Hygiene' Foundation, Mellon.Insti-.-. *'tute, 4400 Fifth Ave.; and- 411l AUequippa_,,St., i - / .N `` ' ;! . .- v,- , Cuttriss Pl.;7Park -Ridge." 111./,- ' '- / - Pittsburgh, Pa; .- ~ ' *' ' . ' . \ `' - \ '' HECKEL. Edmuad P,, Jr. (7 1941) Buffalo /HEMINGWAY, John C,,` Jr, (A 1943) Northern - .. - ; Forge `Go., -490 Broadway. -Buffalo' 4, -juid 226. Calif. Distributor.-H.' C. Little Burner Co..' Inc... ... ' - : Linwbod Ave., BuffaIo'9rN! Y.r ' ' i0, - - -" : ` ! Second and Lincoln St,, San- Rafael, and Box 62, '. .- HECKERT,-'Willard'Hi' (A 1944) Htg! & Fuel Oil ` '101 Magnolia Ave/ Larkspur;'Calif. - ,Div. Mgr.,. American -xLubricants,-- Inc.; -!1575, //HENDERSON, Alexander'S;-(J, 1940; 5 1938).-- .`Clinton St'.,'Buffalo! and 616 Kennison `Pkwy., .-'--Design-Engr., Air Control; Equipment! Pty., : - : r: d. 3, Hamburg.'N. Y. - ~ Ltd:, P.'O. Boix.53,"Waterloo, and-7 Elizabeth St.,-' ' - / HEDEEN. Laurel E. (Af-1942j.A 1941; J-1938)- t - Sydney.'N.-S.'W./Australia;-c Cons."Engr., Todd! Hedeen & Assocs.-, 180 W.- .HEFflDRICK^ON/'Harold 'M. (M; 1934) Air- ' \ / : b irst St.', and 1421 ,Bertcb; Waterloo,.Iowa.' r. --Conditioning Engr., *Safeway Stores. Inc., P. O.' C HEDGES. 'H. Berkley (M 1919) Mgr.; Indus. * Box 660. Oakland14, and 2517-99th-Ave.. Oak- ; Sales, * John 'J. Nesbitt. -Inc., State* Rd! and ' /land3. Calif. ' ' '. ^" - Riiawn SLT Holmesbufg, Philadelphia 36, and 114 / HENDRICKSON, W. B. (A. 1940) Elmr.:N^J. . ' , '-'Waverly Rd-^Wyncote/Pa. ''-j- v . HENDRIKSEN, Leonard ,(A. 1938)/. Owner. ' % : ' HEDLEY, Park S. (M 1923) Partner. Park SL- ; - Hen'drikseh: Sheet Metal' & Heating Service, /.- 1 Hedley. C6.r45.AUen St., Buffalo 2, arid 31-West r- *! 1919.N.'- Vernon Ave.,'.Flint'6. :Mich!" -y . gate Rd:, Kenmore;17, N. Y.' ' ^. - 1 r HENDRIX, Thomas K. (S 1944),Ena;,. U. S. S!. -' HEEBNER!' Walter ' M. j (M 1922) . Sales Engr... . L. S!.T.-267, c/o-Fleet Post Office. San Francisco,. Warren !Webster & Co., 20 Washington "PL, Calif;, and 571 W. Prame.-Decatur.TlL- - . *yr-. . - Newark2, and *282 HighwoodSt., Teaneck, N. J. ' HENEGAR, Barriie V. (A 1944) Owner. * South- , HEGELE,. Richard =H. (A 1945) Owner. & Mgr..' / land'Supply Co.,`2400 S. Harwood;.Dallas 1,'and' H. W. ,Hegele;Co.i 231-N: Main St., and *338 E; !4565:BeIclairSt'., Dallas. Texas. -' - >!'- 7- - i -;v.Court;'.Urbana,'.Ohio. " HENENFELD, Henryk (M1944) Air ConiL-Engr/.: ' v'HEIBEL^ JWalter^E. (M. ,1917) Dist- .. Mgr), ''/' A. S.'E. A. Electric, Ltd.. Yaffi Bldg.-, Goa St.*. ^ Aerofin-Corp., Il-West42hd St.-,-New.York-18; `Fort,- Bombay, India.. * - : N/.-.Y-, ' and-' 12. Ricbmond ; Dr.f. -Old P.GreeriVrich,. 7 HH^ION/;Hudson-D.r (A:* 1923) ..Sales Mgr..- * .-/Conn, _,. -'y.; :^`'v ", V/.J '-`C. A. Dunham Co.; Ltd!.'1523 Davenport-Rd.;- , - HEILMANr!Russell- H.* . {M .1923) Sr.' FeUow,'1 ...,Toronto- 4r and 45, Ridge Dr.,1' Toronto. .Ont.,-- -'' l ' Mellon,Institute,;4400'Eifth.Ave., Pittsburgh; .Canada. Vy. " 137.ahjj'2303 Beechwood-Bivd., Pittsburgh 17, Pa. . ,HENNSSY;SWilliam 1938),;Air?.Cond., - v.'.- HEINDEL;^RlchariJ,"AV^(JM'>-I943)V;. Sr.- -ESfc.- Operation; UT S. .-Rubber iCo., ..Muhition -Div.;, ' . f v` U. S;;Nayy. Dept-,*.Washihgt6n,'D; .G.,;and *709 Des Moines Ordnance PianL and I238r47th St!,/ .r.:.Srivy'StiV Arlington. Va;. w ""V- . ' -- vv':,Des Moihes, Iowal' y.: //,-v. 7-- ^V;'//-/-, //r/ .Roil.of'Membership'/. - ' /; ;/< 39 . -/- HENRY,- Alexander ' s/'`Jr. .{M 1930)' Mech: HESSELSCHWERDT, August L., Jr. (24^1940; / :-Engr.. ;,-R.\K.. O.-,--1270: Sixth Ave.. and *300 -7 '1937) Asst!'-.Prof., Mech. Engrg., Massa- !. . . -.Central Park W., New7York24. N. Y7-. , - chusetts Institute of Technology, Cambridge 39! -;' - HENRY, T-Ernest C. (M 1938) Owner,' E. C/' and 28 Hillcrest Rd.. MiltoiT86, Mass. ' . . .7 Henry.Co., 1317- S./Water St,, and *1115 Park * HESSLER, Lester W. (24 1936) Mgr.. The Trane Ave'., Bay City, Mich. - - - . ' HENRY, Ray W. (A 1945) W. B. Young Supply Co.. 1835 N. Third St., and *6034 N. Bayridge ' ! Ave., Milwaukee, Wis: ' ' 7, . **- !. ' Co., 208 Delaware St..- Kansas City 6. Mo., and HESTER, Thomas J. (24.1919) Pres..'* Hester. ' *2652 Minnesota Ave.. Kansas City 2, Karts. Bradley Co., 2835 Washington Ave., St..Louis 3/ J- HENSON, Wendell L. (A 1944) Htg. & Vtg. Engr.. and 4406 McPherson Ave:, St/Louis 8, Mo. -. r `' - -Hughes Heating Co., 670 Madison Ave., and HEWETT, John B: (24 1937; A 1935) Sales Mgr!. - . 354 Prescott, Memphis. Tenn. K Anemostat Corp* of- America. 10 'East 39th St.. ' HENZE, Arthur. L. - (M 1945) Mech. Engr.,. and *64 Buena Vista Dr.. Dobbs!Ferxy.- N.-.Y-. - * . ' Walter Scholer, 1114 State St., Lafayette, and- HEYMSFIELD, Herbert R. (24-1941) Automatic 616 Hillcrest Rd., West Lafayette, Ind. Htg.Tnstructor. Brooklyn Technical -High School,, . HENZEL, John H. (M 1945) Mech.. Engr.,- arid *478-Third St:, Brooklyn 15. N. Y, ;. .. . Arthur'- G. McKee & Go., 2300 Chester Ave., . HEYSE, Harold S. (A 1944) Mgr. & Pres.. Heyse- ' Cleveland.-and 10804 Elmwood Ave., Garfield `Sheet Metal Works,- P. O! Box. 677, and 1033 , .Heights; Ohio. " -. - North Institute, Colorado Springs, Colo. . .. - ' - HEPBURN, E! M. ; (A 1940) Branch Mgr., . HEYWOOD. W. J. T., Jr. (M 1945) Consult^ . 7Empire Brass Manufacturing Co.,' Ltd.. 74 = Engr., H. Br .van Zelm, 11 Asylum-St.. Hartford, ; Princess St., and 954 McMillan Ave., Winnipeg, ' and 14 Hartt Lane,'Newington.-Conn.- - - Man.,-.Canada. / .* . . . HICKEY,-C. B. (24 1945) Sales Engr., Hpndrie & . . HERBERT. James' S. (A 1946; J 1940) Asst. Bolthoff Mfg. & Supply Co., !635-l7th`St!, P.- O;/ .' Z-Engr., Blue Ridge- Glass Corp.,-. and 1325 Box 5510! Denver 17, and *4849 West'32nd Ave.".. . - ' fCatawba.St,, Kingsport, Tenn. .. ", Denver 12. Colo; '- *- ! '* '; - HERBERT,`Richard M. (A 1946; J 1938) Lt., . HICKEY, Daniel W. (A 1931) Pres., *D7 W!' ' U. S., Army. Air .Corps., Lubbock Army Flying ..Hickey & Co., Inc,, 1841 University Ave., St. -! . -.'School,' and *2314 Sixth St., -Lubbock, Texas. Paul'4/Minn. * / HER1NG, Alfred (24 1935) Pres..-Hering Heating HICKMAN, Herbert V. (24 1945; A. 1938) Htg. . ' Co.. Inc., and *39 West`/7Ist St.. New York Engr. & Gen. Mgr., Neil H.' Peterson Co., 1129 .' - 23,'N. Y.- ' ; .. ---- _ ' _ ! - , Folsom St.,-San Francisco 1, and 11 Palm Ave'.. / HERKIMER, Harold (A 1945) Design Engr., San Rafael. Calif.:' ` - 7; .Raisler. Corp., !l29 Amsterdara Ave.','New. York HIERS, Charles R. (24.1929; 7. 1927) Modine -23!- and'* 140 Riverside Dr.,'New York 24', N. Y.' Mfg.'Co.,-101 Park Ave.,'New York'17, and *19. . - ; .-HERKIMER,- Herbert (24 1945) Cost Appraiser. ' Westminster Rd,, Great Neck, N. -Y., - - ! ' . Maintenance & Repair DeptV, War Shipping 'HIGH,-A. K. (A 1945) Owner, . Automatic Heat-' - --.-Administration,.39 Broadway, and * 140 River- - ing Service Co., 421 W. Marshall St...Norristown. -- 1 /"side Dr.,-New York/N. Y- ' ' and Washington Sq. Gardens, Norristown R.,D. - - -HERMAN, Harry H. (24-1944)-Owner, Harry 3. Pa! . ' = - H. Herman, 1228 California St., and 300 Cherry . HIGH, John M.' (24 1940; A 1938) Mgr., Insula- , - .St.; Denver! Colo:'', -` . tion Div.; *The Ruberoid Co., 500 Fifth-Ave., - - - HERMANNNell B.- (A- 1943; 7 1937; 5 1936) Lt., New York, N. Y.` . '' - . " ' . ' U. S: Navy.,U. S. S. Vinton A..K. A. 83, F. P. O., HILDER. Frederick t. (24 1937) Chief Engr.. / -v . San .Francisco,' Calif.,'and 4217 Garfield Ave. Electric Furnace-Man.'-Inc!, Fourth and Furnace S..-Minneapolis 9. Minn. . Sts., Emmaus,' and 2604 r.Walnut St., - AIIen- ' - -HERMANN, Harold N. (24 1942) Pres., *Cari J. ' '.Kiefer.Assoc.,-Inc., 701 Enquirer Bldg., Cincinnati - ; 2, and Veriion Manor, Cincinnati 19. Ohio. - . HERO/ George A., Jr. (24 1940) ' Cotndr., U. S. N. R.. 6C. A! S. u. 64. Fleet Post-Office. -- 'San Francisco! Calif.'. and P. O. Box 84, Gretna. ' ' La.` " ' * town. Pa.- . ' '7 - : -. - HILL, Edward, Jr. (A 1942; 7 -1939). Capt.,* : U! S. Army. 0306714, 2836 E. P; D. Co.?1' . ` A. P. 0. 350, c/o.Postmaster. New York,. N. Y.,' and 102 Washington St..'Greenwood, Ind. ' ', HILL, E. Vernon, M. D:*,(L/e Member; M'1914; - A 1912) (Presidential Member), (Pres., -1920; 1st Vice-Pres.. 1919; 2nd Vice-Pres.; 1918; Council.- _ . HERRE, H. A! (7 1941; 5 1940) Lt. (j:g.) Fleet . -^Post Office,.San Francisco, Calif. ` ' 1915-21) Pres./ E! Vernon- HUl/ and *6826 W.V* Highland-Ave., Chicago'31.'>IlL .` ` - - .HERRICK, Marvin- M. - (24- 1945). Application HILL.-Fred M. (24 1944) Estimator,'Htg.. Vent;* ' Engr., Johnson Service Co., 507. E. Michigan & Air Cond., and 225 East Ave.'39, Los Angeles.'- * ' St., Milwaukee, and'118 Wilson Ave., Waukesha, - 31, Calif. -; ' / / /Wis. -7 - -HILL, Harold H. (24.1935) Bfanch Mgf.', Ameri- - .HERRING, Edgar^.(Li/e:'Member; M 1919) can Blower Corp., 438 Woodward Bldg., Washing- , - . "Chairman and Governing Dir., J. Jeffreys & Co.. tori 5/and 3002 Rodman St. N.W., Washington ` . ' 7 Stv .`George's" House, . 195-203 Waterloo - Rd..' 8. D. C; ; . . '.. ' 'v . . * .1. London, S. E. 1.. and "Kenia." Keswick Rd:,- HILL,.H, Gordon (24 1943; 7.1938) Lt.'Engr.,,/v 7 /X-7Putney; London, S. W., England. - ! ' - ; ` Royal Canadian Naval-Volunteer Reserve, Naval. ' ` /^HERRMAN.V Donald D. (A 1945) Chief Engr.! .-Service Hqs.v-.Ottawa, arid' 175-.CIendenan Ave.,V.:.; .*. ' -Hartzell '.Propeller Fan' Co.,, and 1407 Nicldin - - Toronto. Ont., .Canada. . ' ' !>" ^ 5- Ave./Piqua, Ohio. , '- HILL, Jared A.-'(24 1938) Dom. Utilization Engr.!' HERSH, Franklin C. (24 1939; A 1937) Tech. ; ."Consultant, Pennsylvania Power & Light Co., ^7 y 901/Hamilton St., and *317 South'16th St., -. Allentown..Pa... -' . . ' Pacific \Gas & EJedric Co., 245 Market SL/San. - Frandsco, and *715. Laurel-Ave., Burlingame. : Calif; .' v . : ` :- - - . HILL, N. Edward (24 1944) Chief.Desgnef. L.-J! - .. . HERSHEY, Albert E.* (24 1940) Research Erigr., .-. Westinghouse Electric & Manufacturing ` Co., . - East 'Pittsburgh,' and- 10806 -Frankstown' Rd., 7 . Pittsburgh 21; Pa- .' . . . Z Mueller Furnace 'Co., 2005 W: Oklahoma Ave..; - - Milwaukee 7,- and 842 North 54th St.,.Milwaukee. " y* 13, Wise." ' J '. HILL, Vaughn H. (24 1943 ; 7 1938) . Indus. / ' Hygiene Engr.,- Michigan Dept:-of Hralth; Lan- . HERSKE, Arthur R. (24 1926)! Pres., !Au-Temp- 'sing 4, and 2111 Colvin Court;' Lansing10, Mich. ' ' ' J.Co.yGorp., 521 Fifth Ave., New York 17, :and HILLARD/Henry F. (24 l945)iChief Engr., Dis-/ ' V /. 630 Gramatan Ave.-, Apt. 6H, Mt. Vernon, N.Y. " ` /tribution'Div., Mountain Fuel Supply Co., 36 S- r'>- / -HERTY, 'Frank B. (24 1933) *814 -Poinsettia .- * State St;, and 125 South-'13th East St;. Salt Lake -/ ' Rd-!'Columbia-50, S.'C. . City. Utah. \ ; HERTZLER.' John R. (24 1936/7 1928)' Vice- HHXEN/William G.\(34 i945; A 1944)' Asst/ -' -7-vPfes. and Gen. Sales Mgr.; York.Corp., and'*8^ Sales Mgr., Carrier'Coip., and ' 120 Sherbourne .. /.-/S. George St., York, Pa. -` ' / - . Rd.`, Syracuse, N. Y.- ' - ' ' - <'/',' - . HESS/Arinin E. (A 1945) Brahch Mgr., General . HILLS, Arthur H. (24 1924) Gen'; Mgr.. Penn . ^ 7/ Controls Co., M & M Bldg..' Rm. 928-A; Houston Controls. Ltd., 284. King St. W., arid * 21 Nealon . : ;--2. and 1800 Louisiana St., Houston. Texas.' ' ' , *'A've.,'Toronto,:Ont., Canada./, .... -. , /HESS,-`Arthur- J./(24 -1937)- Member-Owner! HILMER,-`George O.!<A 1944) Designing Engr..., 7/ 'fr "?.' Hess-Greiner - 8c- Polland, 1700 -S! Main St.,- Marine Dept./ Carrierr Engineering Corp...405 .. 'Los Angeles'.15, and 897 Linda Vista Ave., -Pasa^ '' Lexington Ave.; New York 17,"and 23l;Stuy/.//Jf;} v ;dena 2, Calif. : vesant Ave;, Brooklyn 21, N. Y.. . r/.'- 7'-i 40 ' Heating Ventilating ' Air Conditioning- Guide,, 1946.; HILMER, Ralph H. (Af 1944) Engr., G. G. Hokanson Co., 8373 Melrose . Ave., and *6501 Colgate'Ave.. Los Angeles 36, Calif. - ' HOLBROOK; John A. (Af 1945) Research Engr.. 153-25th St.-Dr; S.E., and 1420.Second Ave. . S.E., Cedar Rapids, Iowa. '- '' HIMELBLAU, Harry (A 1943) Secy.-Treas., Himelblau, Byfield & Co., 36 S. Throop St., HOLDEN, Robert G. (A 1942) LL. U. S. N.-R... ; ' Base - Planing Office,. C. N. B., Navy 3142, Chicago 7, and 1720 Chase Ave., Chicago 26, 111. F.-P. O., San Francisco, Calif., and 490 S. High H1MSEL, Stanley R. (A 1942) Mgr. of Htg. & . land Ave., Pittsburgh 6, Pa. 4- Vtg. Dept., Lloyd L. Felker Go., 102 W. Aronald - SL, and 903A W. -Fifth St., Marshfield, Wis. HINCKLEY, Harlan B. (A 1944) Engr. Custodian, ' Board, of Educaton, Chicago, and *6933 S. - Princeton Ave.. Chicago 21, III. HINGSTON, George N. (A 1945) Exec. Secy., - Metal Window Institute, and 806 Rowland Rd., Cheltenham, Pa, HINNANT, C. H., Jr. (Af 1943; 7 1938) Major. ' 'Army of the -United States, Post Engr., Rich- HOLDER, Leonard H. (A 1941) Mgr.. April . Showers Co., 4126 Eighth St..N.W., Washington, 11. D. C. .* HOLE, Kenneth W. (A 1943) Executive Sales Engr.. Miles Aircraft, Ltd., - The - Aerodrome, Reading. England. -. ' HOLE; William G. (Af 1942) Mgr., Air. Filter Div., Darling Bros.'. Ltd., 140 Prince St.. Montreal, and_1765 Graham Blvd., ML Royal, Que,, Canada. . .- mond'ASF Depot. Richmond 12, and 1023 West HOLFORD, Douglas B. (Af 1944) Branch Mgr.. 45th St.; Richmond, -Va. - . HINNANT, Robert H. (7 1945) Archt. & Engr., 341 Woodland Ave., Lynchburg, Va. - - Johnson.Service**Co., 325 Dooly Bldg., Salt Lake City 1, and 1363 South 19th East SL, Salt Lake City 5, Utah. '' ' . - ' HINRICHSEN, Arthur F. (M 1928) Pres., A. F. HOLLAND, George R. (A 1946; J 1941; 5 1938) ..' Hinrichsen. Inc., .50 Church' St., Room 1970, CMM, Transportation. U.`S. N. A. B.,Navy 961, : -'New York 7, N. Y;^ and 281 Morris Ave., Moun c/o -F. P. O., San Frandsco. Calif-., and 615 tain Lakes, N. J.- - ' 13th Ave. N.E., St. Petersburg. Fla.- ' . HIRSCH, Martin H. (M 1938) Engr. in charge. - Consolidated Installations Corp.. 210. East 40th St;. New-York, and #104-21 68th Dr,, Forest . Hills, L. I., N. Y. . HOBBIE, Edward H. (A 1937) Mgr.. Sales Pro motion. Mississippi Glass .Co.,-200 Fifth Ave., . ' New York 10,- and 121 Greenwood Ave., Madi- HOLLAND. Robert B. (Af 1938) Partner, Gen eral. Equipment Co., .420 Market SL, San Fran cisco' 11. and 607 Saiisalito Blvd.; Sausalito, Calif. HOLLAND,' William- T, (Af 1943; A1941) Lt.. . ' U. S. N. R., and *8420 Woodcliff Court',-Silver . Spring, Md:-' '. '' V- 'HOBBS^j. C. (Afl920) Scientific Advisor, 60 HOLLIS. Richard C. (A 1944) Mgr., Air Cond. ..'Div., Broadway Maintenance Corp.,:47-=47-35th . Wood SL.'and *60-Wood St., Painesville, Ohio. - St.; Long Island Cityl, and'*327 Lexington Ave., ' HOBBS, William S. (A 1936) Mech. Engr., ' New York 16, N. Y., - \ . ;v' v- Engrg. Div., Mfg. Dept., Sun Oil Co., 1608-Walnut' HOLLISTER, Norman-A.* (Af 1933)'Supervising - SL,-Philadelphia, and 327-Park-Ave.;',P. O. Box . Air Cond.Engr., c/o Architect of" Capitol." " 269,'Swarthmore. Pa. - . . Washington.' D. C., and'4309 N. Pershing Dr., - - HOCKENSMITH, Francis E. (Af 1936) Chief 'Arlington, Va.M - Engr., Lennox Furnace Go., Inc., 400 N. Midler HOLMAN, Earl L..(Af 1943) Sr. Engr., Asst, to Ave., and 454 Plymouth Dr., Syracuse, N. Y. - _ ' HODEAUX, Walter L. (Af 1943) Asst. Sr. Div. Chief of Materials Section of'.U. S. DisL Engr. Office Supply Div., U. S. Army, Ft' Armstrong, ; Engr., R.. F. C., Office of Defense Plants, 312 and *3043 FelixSt:, Honolulu 36, T.H.. - ' . Greenleaf Bldg.. Jacksonville, Fla. , . HOLMES, Arthur D. (Af 1935) ' Vice-Pres:, HODGE, William B. (Af .1934) . Vice-Pres.,, Plumbers Supply Co., 323 W, First St.; and 1321' Parks Cramer Co., 2000 South Blvd.,-and 2600 S. Quaker, Tulsa, Okla. /. ` - ' "Roswell Ave.. Charlotte, N. C. ,- '. HOLMES, Oliver A., Jr. (Af-1944) Mech. Engr.; - HODGKINSON, William S. (Af ' 1945) Engr.. . Hughes Heating Co. & Pntchard`Bros., and *155 . Ilg Electric-Ventilating Co.,' 137 Newbury-St.,' - Alexander St.,-Memphis. Tenrn, ' - , ' '.. Boston, and *58 Adella Ave., West -Newton HOLMES, Paul B. (A 1936) Mgr. of Sales Htg. . '65; Mass. . ~ ' ' Div., National Radiator Co., 221 Central'Ave., r HOECKER, George F., Jr. (A 1941) Mgr., Sears Johnstown, Pa. ' . -- .- ' .. -'Roebuck & Co., .275 Hobart SL, Perth Amboy; . HOLMES, Richard E. (A- 1938; J 1934) Design ' and 475 W. Inman Ave., Rahway, N. J. % - Engr., Westinghouse Electric Corp;, - B. ;F. ./HOEY, James .K. (A . 1938)-Mech; Engr., *48 ' Sturtevaht Div.,.'Hyde Park. Boston 36, - Mass. " Quince SL; Medford, .Ore. - . ' ; HOLSWORTH, Robert C. (Af 1940) ; Owner. HOFFMAN, Carl J, (A. 1945) Partner. Lenz & . - Holsworth. Equipment-Co., P.,-0. Box 1981. --- Hoffman Hardware, Lancaster, Wis.' - ' Corpus Christi-, Texas. - - ." ; HOFFMAN, Charles F. (Af 1945) Architect. & ' -HOLT, Donald R. (A -1945) Pipe Shop Foreman, - Engr., Peterson, Hoffman & Assoc..-1051 Spitzer R- C.`A. Victor Div., and* 3040 Constitution. Bldg., .Toledo'4, and 226 Raymer Blvd.,. Toledo Rd., Camden, N. J. '` "'5. Ohio. . '-' -. " . .- - :' HOLT, James' (Af 1933) (Coundl. 1943-45) , ' HOFFMAN; Charles S. (Life Member; Af 1924) . ; Assoc.. Prof., Massachusetts Institute of Tech.;. Pres., Baker. Smith & Company, Inc.. 40 West . Cambridge',. and J062 Massachusetts Ave., .Lex 40th SL. and 77 Park Ave., New York, N. Y.'":-< ington, 'Mass.:' . '. `' .HOFFMAN, Harry (Af 1939) Branch Mgr., , HOLT, W..H. (M 1944) Mgr.. Fan.Merchandise Johnson Service Co., 232 E. Market St.. Greensr ' & Standard-Products-Dept., Buffalo. Forge -Co., ' boro, and R. F. D. No. 1, Guilford College; N. C. . 490 Broadway, Buffalo, N. Y. - . . . HOFFMANN, Angelo (A 1938) Vice-Pres., Louis HOLTON, WlUiam*J. (A 1945) Sales Promotion.-Hoffmann Co..Tl7-W. Pittsburgh Ave.. Milwau- ' U.'S. Supply Co., 1315JW. 12th St., Kansas City ; .'.'kee-4,'and '4850 N. Oakland Ave.,' Milwaukee . 7, and'5047-Wyandotte,'' Kansas City,.Mo. .. . - 11, Wis.. : ' HOLUBA; H. J. (A 1946; J 1938). Mgr.. Order HOFFMANN, Walter. A, (A 1944) Engr., L. S. DepL, The. Herman. Nelson Corp., and 1862- . . Ayres & Co., ,1-15 W. Washington SL, and 608 " 30th SL, Moline, 111. . . ' '. . ~ Cottage'Ave., Indianapolis, Ind. -- _ * - HOLZER, Rudolph J., Jr. (A 1942; J 1940).. - HOGAN. E. L. (Life Member; M. 1911) Gen. Cons. Engr.-& Estimator, Holzer Sheet Metal Works, ' Engr.,-'* American Blower Corp., Detroit 32,-and ' . 317 Burgundy SL, and *3738 Octavia St., New . 8100 E. Jefferson Ave.Y Detroit 14, Mich. Orleans; La. r'. ' HOGER,: B, E.. (Af. 1943) - ExperimentaFDlvpL - Engrg., Norris .Stamping .& Mfg., Go., 5215. S. HONERKAMP, .Fritz (Af-1937) Chief Engr-,. - Anemostat.Corp. of America. 10 East 39th St... - .-Boyle.Ave...Los Angeles 11, and *3165 Olive St:,; - New. York,'; and' 42-05-48th Ave., Woodside,': Huntington Park, Calif.. ...v - * L. I.,'N. Y.-" r . ' c'-': HOKANSON, .Cari-.G. (Af 1941);6wrier, C..G, - HONEY, Robert L. (A 1946; 7- 1943) U. S. Hokanson Co.,.8373 Melrose''Ave.'. Los, Angeles Navy--MMG 2/C, and 4138 Toledo'Ave.. SU- -r:~ 46, andrllOO Casiano -Rd.,- Bel Air. Los Angeles -Louis-Park. Minn. - - - .................... ..... - 24.'Gafif.>^ - ' -'.- . - HOOD, Leslie A. (Af 1941)->ssL Sales-Mgr. ^ HOtBROOK. Frahk M; (Af. 1944) * AIpha Steam . ...Trane. Co. of; Canada,--Ltd., ;Room 314/Um-'. "Specialty.Co., 15.Park-Row, NewsYork 7; N.-Y.,. versity'.Tower ..Bldg., and 1410-* Mackay-St.;; : --'and 625 Union-County'Pkwy., .Union; N. J. - . ' Montreal,. Canada.v > ` 4 . ; . Koll of-Membership ~ " .. ." . - . ' '. ' 41 HOOK, Frank W. (Af 1938) Branch Mgr., HOWARTH, Walton E. (Af 1944) Designing Johnson'Service-Co., %814. Rialto Bldg., Engrr, William'L. CasselL 912 Baltimore Ave., . ..Frandsco 5.-and-2444-Larkin St., San, Fran- ' and 7549 Main St.; Kansas City,'Mo. - . * dsco. Calif.' ' - '.. . - - * HOWATT,. John* (Life Member; Af 1915) (Presi- HOOK;-Louis M. (A 1944) Engr., Rio Grande' ''dential Member) (Pres.,- 1935; 1st Vice-Pres., Fuel-Co., Stoker Div;,'123 Santa'Fe Dr., Denver 1934: 2nd Vice-Pres., ,1933; Council 1927-36) 9; and 2464 Depew St., Denver'14, Colo. ` . ' Chief-Engr. &'Business Mgr., *B(rd of Educa HOOPER, Frederick -W. (A 1942) Vice-Pres., tion, 228 N. LaSalle St.."Chicago 1,_ and 4815* Ross 'Engrg. of Canada,' Ltd., 920 Dominion Kenwood Ave., Chicago, 111. * - . ; ' Square Bldg., and 3568 Addington Ave., Montreal, HOWELL, Lloyd (Af- 1915) Regis. Prof. Engr., ' cQue.. Canada. . . ' _' The'State of Texas, Glidden Engineering & Equip HOOVER, William L. (A 1943; 7 1940) 1st Lt., ment Co., 842 First National Bank Bidg.. Houston, . 0-1108029, 1399th Engr. Cons. Bn.. A. P. O. 957, and 2610 Talbot St., Houston 5, Texas.- - c/o Postmaster. San Frandsco, Calif., and *910 ' HOWES, Bradford B. (7 1941) Engr.. Consoli Cedar St., Owensboro, Ky. - dated' Conditioning Corp., 460 S.-Tenth'-Ave.;. HOPPE, Marcel F. (Af 1938) Cons. Engr., *1021 Ml Vernon, and 131 Prospect Ave., Mamaro-' . 20th SL N.W.. Washington 6, D. C., and 5205 . neck. N. Y. . ' Glenwood Rd.. Bethesda 14, Md.' ' . HOWES, Edward . W. (Af 1941) . DisL Repr., HOPPER, Garnet H. (Af 1923) Engr., Taylor Air .Cond. Dept., General Electric Co.;'-235 Forbes. Ltd., 1088 King SL W., and 19 Brummel Montgomery St.; San Francisco' 6, and 8016' Ave., Toronto. Ont.; Canada.' ' . ' . Broadway -Terrace, Oakland 11,- Calif.' - - HOPPER, John S. (Af-. 1938) Asst, .to Dean, of HOYT, Leroy .W. (Af 1930) Libby & BUnn, Inc... -Engrg., *A. & M- College of Texas, c/o Dean of 135 Sheldon'St., Hartford, and 1133 Fannington . ' Engineering. College Station, and 106 W. Dexter, ` Ave., West Hartford 7, Conn. . . . . College-Park, Texas. ' HOYT, Robert A. (7 1943) Supt. of Furnace HOPSON, William T. (Life Member; M 1915) Installation. Hall-Neal Furnace Co., 1322. N;- . Pres;, *The Hopson Chapin. Mfg. Co., 231' ~ Capitol Avei, and * 534 S. Rybolt SL,. Indian' State.St., New London, Conn.' .` apolis, Ind. ' ' .` ` HORN, Artemus J. (A 1944) Research & Design HOYT, William B. (Af 1945) Pres. & Treas., * --Engr., Payne'Furnace Co., Beverly Hills, and .The Hoyt-Gfant Co., 52 Whitney Ave., P; .O. - 2714 Tilden Ave., Los Angeles 34, Calif. HORNE,--Herbert F. - ,(A 1940) Sales. Engr., . Johns-Manville 'Co.,'1312 Standard Oil Bldg.; Box 529; New Haven 3, .and 39 Clifford. SL, Hamden, Conn. .. v .. HUBBARD, Allen (Af 1944) Partner, Hubbard Baltimore 2; and - 411 HoIIen Rd., Baltimore ' Rickerd-& Blakeley, 110 Whitney- Ave., and-54 . 12; Md. ' .- HORNER, Frank: S. (A 1944) Jr. Constr.- & Trumbull SL, New-Haven 10, Conn.- ' * HUBBARD, George W. (Life Member; M 1911) - .'Maintenance Engr., Burroughs.Adding-Machine- `Cons. Engr.; *630 Railway. Exchange, 80 ' E/ Co., 6071 Second' Blvd;, Detroit' 32, and *339 - .Jackson Blvd., Chicago 4,'aiid 710 Bonnie Brae, Cortland Ave., Highland Park 3, Mich. - . - River-Forest, 111. . - .' s' ` - * HORNUNG, J. C. (Life Member; M 1914) Retired, . 854 Bluff St.. Glencoe, III.' - .. HOROWITZ, Harry (Af 1945) Htg. & Air Cond. HUBBARD. Nelson B. - (Af 1937) "Engr.. 220 Bagley Ave., Detroit 26, and *2985 Blaine Ave.,' Detroit 6. Mich. ' .- ' Specialist, 889 Warren SL, Albany 3,- N. Y. HUBBELL, Ned S. (A 1944) PIbg. & Htg. Engr.,. HORSBURGH, B. J; (A 1942) DisL Mgr.. ' Mueller Brass .Co.;. 1925 Lapeer Ave., and.*940 Johnson Temperature.Regulating Co. of Canada' Pine St., Port'Huron. Mich.' '- Ltd.,'637 Craig-St. 'W,, and 4341 Melrose Ave., HUBBUCH, Nicholas-J., Jr. (A 1946; J 1943; Montreal, Que., Canada. -. . .' 5 1939) *116-18 N. Third St., Louisville 2,-ahd - HOSHALL, Robert H. (Af 1930) Partner. Allen 422 Breckenridge Lane, Louisville 7. Ky.' . ' Hoshali, 65 McCall PI.. Memphis 3. Tenn. HUBER, Enrique (Af 1938) Mech. Engr.. Prod--; HOSMER, George--H. (A-1944) Pres., Hosmer- uctos Mecanicos S. A., - Calzada de - Tlaipam' Products Corp.,'819 Massachusetts Ave., Indian- ' ' No. 2073, Churubusco, Mexico, D.F.. :; rapbiis 4,-and 3656' N. Delaware St.,- Indianapo HUGH, A. J. (Af.1919) Branch Mgr., American ' lis 5, Ind. ' . -. . - Radiator & Standard Sanitary Corp-,' 312 Third - HOSTERMAN, Charles O. (Af 1924) Supt.. ..-The-McMurrer Co;, - 303' Congress St,, Boston. and *25 Bateswell'Rd., Dorchester. Mass. HOSTETTER, J. C. (A-J944) Pres., Mississippi Glass .Co.,- Main & Angelica Sts.. St. Louis 7, and- 6435 Cedi Ave., Clayton 5. Mo. - HOTCHKISS, Charles H: B. (Af 1927) VicePres., Ameresco, Inc., -50 Church-St., New-York St., Minneapolis. 15, and 4037. Harriet' Ave., Minneapolis. Minn. . *.-, .. HUCKER, Joseph H. (Af 1921) Owner. Hucker Sales Co., -1700 Walnut St., Philadelphia 3, and,. 1209 W. Oak St., Norristown.'Pa;/- ' . -.'a HUDEPOHL, Louis F. (Af 1936) Pres., *T;<J. . Conner. Inc., 3290 Spring Grove Ave., Cincinnati" `" 25.- and.4395 Haight Ave., Cincinnati 23,-rOhio.. ' 7.'N.- Y.. and 169 Sheridan Ave., Hohokus,-N. J. ' HUDSON, Robert A. (Af 1934) Partner, Hudson. HOUCK, Robert' C. (A 1945; 7 1941) Engr.. 6 Grady. 525 Market St., San Francisco 5, and ' Boro.'-of Vineland,. West Ave. and Plum SL, and 39 Nevada St.. Redwood City, Calif: - - . -. R-.'F. D. 4, D'eisea Dr., Vineland, N. J. HUELSMANN, A. G. (A 1941);Sales Engr..-* The' HOULIHAN, Edmund T. (Af 1943) AssL Sales Mgr., Taco Heaters, Inc., 342 Madison Ave.. New York. 17; N. -Yi, and *31 Waldeck Rd., Milton 86. Mass. ' -. v- ~ .. . ' Powers Regulator Co., 702 American. Bldg;, arid : R. R. 4, Box 189, .Wyrinburne Ave;, Cinciii- > . nati, Ohio. ; ' HUFF, James M. (Af 1942) U. S. Navy/(Present, HOULIS; Louls-D; (Af .1935) Master Baker address unknown), 1410 Roswell St,, Marietta, Ovens, 558'Pedretti Ave.,' Cindnnati 5, Ohio. Ga. HOULISTON, G. BaiUle (A 1928) Dist. Repr., HUGGINS, L. Gale (Af 1939)-AssL Mgr., Air. Warren Webster & Co.t'707 Race-'St.,.Cindn- .. . Cond.- DepL; Westinghouse -Electric ,Co., 150' `nati'2, Ohio, and 57 Chalfonto P1.. FL Thomas, Ky.-l ^ Pacific Ave., Jersey City 4,. arid *269-Walpole ' HOUSEHOLDER, Homer- L. (A 1944) Mgr. & ' SL.'Norwood, Mass. - *" " - .' " -Owner; Householder Heating Corp., 1396 Main HUGHES, Charles (A 1944) LL Comdr., U. S. SL.-Buffalo 9. and -281 Wellington Rd., Buffalo, . N. R., Route 5, Box 393, Memphis -11; Tenn. 16, N.,Y. . , ' - .' . ' HUGHES, L. K. (A 1940; 7 1936) Pres., Howard HOVDA, Arthur F. (A 1945) Htg. & VenL Inspector^City of Minneapolis Building DepL/ 235 City Hall; Minneapolis; and-*4715-llth Ave. Furnace & Foundries. Ltd., 881 Yonge SL. and *3 Don Valley Dr., Toronto, Ont., Canada..... . ^HUGHES, Ralph (Af 1944)- Partner,'*Hughes' S.j Minneapolis'7, Minn. ''. - . Heating Co.,' 670-72 Madison Ave., Memphis'7, ;HOW, Cecil P. (Af .1943) Director & Gen. Mgr., Heating Dept.; The Brightside Foundry &jEngi- and 3895 Walnut Grove Rd.;'Memphis,-'Tenn.'' HUGHES, Samuel (7 1940) Sgt. U. S; A;. Co. y neering:Co.', Ltd.-; 17 Slimmer Row,-Birmingham,-- . L,. 161st Inf., A. P. O. 25, c/o Postmaster,/Sari!' 4. and "FairlawnV, -Thornby AvJe., Soiihuii, War- - Francisco, Calif., and 514 W. Lee SL, Weather-. "'wickshire.'England.- - C/' -. ford;Texas. .r-* - ' . * ...............-'*> HOW, Ralph.F; (Af 1943) Htg. Engr., *U. S. HUGHES, WUHam U. (Af 1936) Pres.. The; . ,Engineering-Co., 914 'Campbell SL.'and 304 N. -' Lewis-Brown'Co., Ltd., 1570 Bishop SL, and 1610 . .Lawn, Kansas.City. Mo. . '' ` ; Sherbrooke St:, Montreal Que., Canada. -. 7<42\"~- . -W\''. - Heating - Ventilating Air f:Conditionings Guide "1946f HUGHEY, Thomas. M. (A 1935) /Dist; Mgr.,-. HUTCHINSON, B. Lee! Jr. (j -1939)' Capt.; "'. Westerlin & Campbell Co.. 906 N..Fourth St.. : U. S. A A. F., 0-856479, 9th Photo! Ren; Sq.. -.-Milwaukee 3, and 2439 North 63rd St-Wauwa- ..A. P. O.v220,'c/o Postmaster. New York,' N.- Y., r tosa`13; Wis.- '* . /' .and 2216 Bedford Terrace! Cincinnati- 8, Ohio.'. ' HUGHSON, Harry. H!' (if..1937) Sales/Engr.;-. HUTCHINSON, .Frank W.* (M 1942) rProf ! .. .The Coon-DeVisser. Co- 2051 W. Lafayette - Mech.. Engrg., Universityr sof- - Purdue. '-West /Ave- Detroit 16, and 58 Florence Ave., Detroit .'Lafayette, Ind., and Hotel'Marik.'Cuernavaca.- - 3.` Midi. *.-.*: : - . ' Morelos,' Mexico. - 5/ - * _HUHN/Walter E. (A 1943) Contractor &Engr., HUTCHINSON, Frederick A. (A 1942; `J 1939) ,*' Walter. E..Huhn. 1720..Grand. Ave., and 1113. Mgr., Repair Dept.,; C: J. Doughty & Co.. 30 Fairfield. Waukegan,- III. - " . . . ^ Brenan- Rd., and *31 Luceme -Rd.. Shanghai. 0 HULL, E. O. - (Af . 1944) Chief Engr., East 'China. 1 . ...Tennessee- York; Inc.. 410 Walnut St..- and 3105 ' . HUTCHISON, Allen:(A'l945) Chief- Asst. Enp-..: '-Vera-Dr., Knoxville/Tenn. : .' . .Montreal Refrigerator Co., and4111' Melrose HULLV Louis M.(Af 1945) Sales Mgr.,' Hammel . . Ave.. N. D. G.; Montreal,.Que.,' Canada. ' Radiator ' Engineering Co':,' 3348. -Motor Ave./ . HUTCHISON, John . E. (Af 1939) , Partner. - Los 'Angeles 34/and 346 N..Harper. Los Angeles' ... Moody & Hutchison. 1420 Walnut St.; Phila . 36. Cali!.: ' \ - delphia 2,!and 6723-EmlenSt., Philadelphia 19; Pa: HUMES,.:W. Earl <Af:1941) Contractor. *501 HUYETT, Merrick Y. (J 1945) Jr. Engr:. Carrier . -Mill St., and 226 Ridge St., Reno, Nev. ' - Corp^300 S. .Geddes St., Syracuse; NT. V., and. HUMMEL,.DavidM; (Af 1944) Mgr. of Engrg..' 2100 Woodlawn Ave., Wilmington, Del. .' - ' -..Yale University,: Service "Bureaus. 20'Ashmun . .St.,-New Haven, -,14,Conni ': ? and 21-Femwood Rd-.iHamden /,' *' ' - ` '* ' -. HVOSLEF, Fredrik W-' (M 1931) Supt.. Heating . Div.. i Kohler Co1.; and :523 '.Audubon Rd., . Kohler, Wis!- -'- HUMMEL, George W. (Af 1937) Mech. Engr.; - . The Trane-Co- P. O. Drawer 679, and 1424 N. . Third St-Phoenix, Ariz!' . r- ' HUMPHREY, D. E.* (Af 1921) Htg. & VtgV". Engr.. Goodyear Tire & Rubber Co., and *2499 ' . .Sixth-St.,- Cuyahoga Falls, Ohio. \ . HUMPHREY, Leonard G., Jr. (A 1942; ^1938) . ' - ; HYDE, Dayton F. (if 1941) Vice-Pres., Becker Marsden. Co.i 3818;LindelLBlvd.v St.' Louis 8,..' and 624 Locksley Pi... Webster Groves 19,* Mo. ' HYDE,TEric-F. (Af:1937) Mech. Engr., Giffeis'S;-' , Vallet, Inc.. 1000 Marquette Bldg.. Detroit, and 708 Oakland -Ave.,- Birmingham, - Mirh' .- * .. . Asst..to. Mgr.. Federal .& Marine Dept., Buffalo.; .'HYDE, L.-Lymari (Af 1940) Supt:. Healy.Plumb- . Forge'Co.-& Buffalo Pumps,- Inc.; 512 woodward ing & Heating.- 278. W. Kellogg Blvd.. St; Paul. Bldg.!. Washington 5. D. C-and*4023 Oliver.-. - - and 4031,France'Ave. N.. Rohbinsdale 12, Minn. ' -> St-'Chevy.Chase 15,'Md. . . '' ' HYNES, Lee P.'. (if 1919) Pres... Chief Engr;! ; . : HUMPHREYS, Clark- MI (Af-1931) (Council,. *Hynes Electric Heating Co., West.and Clinton- -1936-38) Sr. Engr., American Society of Heating - Sti., .Camden, and'36 West End Ave., Haddon- ' . - & Ventilating' Engineers Research Laboratory, . field, N. J. - - -V ' *. . -10700 Euclid Ave., Cleveland 6/Ohio., and 1934 . Remington Dr:, Pittsburgh 21, Pa. ' .. ' . I HUNGER, Robert F. (Af 1927) Partner,, David son Hunger! 220.S. 16th St.', Philadelphia 2. . IBISON, James L. (A-1943; J 1938) Major.' ' , and 239-Cheswold Lane, Haverford. Pa. ' ' U. S. Army, Post Engineer, Andrews Field, . HUNGERFORD, Leo (Af 1930) Sales Mgr.,' ^Washington 20, DV C. v. `- - . Utility Fan Corp.. 4851 S. Alameda St., Los Ange- JCKERINGILL, JohreCl (Af 1923) Sales! Spencer - . les. and 3485 Wonderview PI.. Hollywood .28/ Heater Div., -The 'Aviation Corp..-.927 N. Ninth Calif. . - - ' - . - . ' ' . - - . St.,' and * 477 Flamingo St.. -Roxborougb. Phila-- 1IUNKEN, Walter L; (M 1943) Dist.'Mgr.. B. F. delphia-28. Pa. . . .. y. ^ . Sturtevaht-Co.. Div.r of. Westinghouse' Electric ILLIG; Ernest'E. (J 1938) Sales Engr., Walter-R. . Corp-.- 900-908 Walton Bldg!, add 691'Woodward : ' Iliig, 1-Cushing St...and *64 Pleasant Str.-Fitch-- - : Way, N. W- Atlanta, Ga. f. ' '. - . " V . ^burg, Mass.' ' , HUNSAKER. Roy E. (A 1945). Engr.. Owens-. ILLIG, .Walter R. (Jf. 1935) ='Owner, 'Walter.'R:, . ; Coming Flberglas Corp., Nicholas Bldg.. Toledo . Iliig,- 1 Cushing St.', and 185 Blossom.- SC,'*. l,.and *1411 Potomac Dr-Toledo 7/Ohio. . .Fitchburg, Mass. .. ; . * . HUNT, James'-F, (Af-1944) 'Mech. Engr.. Cory -. ILOVITCH,. EU LV (7 1945) Student'.Engri. Air-. Joslin,,,Inc., 512 Golden Gate, San Francisco..and. Conditioning Engineering Co.. 79' Vltre Stl W 1325 Chestnut St- San Carlos. Calif.'- - . ' -Montreal l.-and *5230 Clark St.,' Montr^l 14, . IttlNT,.MacDonald (A 1936)' Capt: Corp-sof . Que.; Canada!. .. . ' - --" ___ 4 Engineers,-c/o .Post Engineers Office.'-A. S. F. INCE, F. Edward (Af 1944).Engr., Kennard Corp.. Replacement Depot. -, Camp Reynolds. -Green-\ 2021 S. Hanley-Rd., St. .Louis-17., and 1076 . .* vilie/Pa. -- - . -' ' v North & South. St. Louis 5. Mo. r. ' SHUNTER, Louis. N. (Af 1936) Vice-Pres-' Re INGALLS,- Frederick D. B. . (Life Member; search, The National Radiator.Co.,-221 Central ` Af .1906) Cons. Htg. &. Air -Cond; Engr., 1 ' Ave!, and 113 Palliser St- Johnstown. Par , : Hopkins St:, Reading, Mass. . ' - - -' . . ^ - HUNTER; ThomasB. (Af 1941) Cons.: Engr.. INGELS, Margaret*. (Af. 1923; / 19*18). Engrg. 41'^Sutter St- Rm. 710, San Francisco 4. and * ^ -Editor, Carrier Corp.; Syracuse, l.' and' 412" 3026 Clay St-VSan Francisco. Calif. - ' ' .. University PI.,.Syracuse 10; N. Y.- > * HUNZICKER, ; Dean L., (J 1944) . Engr.,** 1NGERSOLL. R.. S. (A 1945) Works Mgr.. Research, Products Corp,,; 1011 E.- .Washington ' In^rsbll Steel Div.; Borg-Warner:Corp..763 E. ' -.-Ave..'and 1121 Rutledge St., Madisoa 3, Wis. ' Vine St.,.and-1029 Campbell Ave,,-Kalamazoo, '. HUNZIKER, Chester E. '(A 1934). Dist. -Mgr., Mich.,' . . *- . y " American Blower Corp.. 511 State St., Sche-. ^INGHAM, . John-F... (Af' 1941) Htg. Contr.. nectady 5, -and 1552"-Dean St., 'Schenectady . ..- Mountain .Rd., R.' F.' D;.3. 'Georgetown, Conn: 8. N. Y:_.V - - ; . / ... . .r-;v'.*- JNMAN, C. M. (Af 1940)' 1st Lt.. Army Air Corps, HUPP,'Hairley L.'-'(A'; 1945) Dist. Comml."Sales. ' Las Vegas Army Air Field, Las Vegas. Nev. ' ' ' .t-Mgr.; York Corp., 2700 Washington Ave!.Cleve- IRVINE, Lelahd/K. (A< 1944). Engr. ,&VMgr;;- land!' Ohio,- -and *433 Highland Ave.!-. West - Intennoiintain' Insulation Co., - 333 Wv -'First . - --View. Pa.-. - : ' * ' ; - . ; J.'S6uth,'..Box 566,. Salt Lake *City- 9,- and V19S8 "HUST.^ Carl E. .{M '1932) P. O.. Box' 1233, ' 'Sheridan- Rd.. Salt Lake City 5, Utah.': . . - -. Miami^Beach 'Branch.' Miami;' Fla. . ' . ISKYAN; Haig S. (Af 1945) As51. Cons. Engr..-1;* HUSTOELvArnold M. (A 1930) B-O-C-T-Riil- - The American Tobacco Co.;Grace and 21st Sts..' vroad, and *2414 N.-Kedrie'Blvd;, Chicago.-Ill:- ' and 1317 Bainbridge;St.,'Richinohd; Va.V- ` -: --v- HUTCHEON''Clifford'R. (A ;1945;V 1938) Exec. ISLEY, :Garnet H.- (Af - 1945)*-Mechr Engr.. A .AsstL- Carl L. ;Norden. Inc.! "80 Lafayette St., ! - Bevington, Taggart & Fowier, Inc.; 730 K: of-P. >" -* New^Ydrk: N.'.Y.r and 114 Ayers Court. West - -'Bldg., Indianapolis 4. and !c/o.W.:0.;Is!ey. R.-R! - ' Englewood^N. ,- ,7 ' *r. : - ,. :No. 1/Edinburg, Ind.-,'-..- ' -s' yr- :HUTCHINS; William H.'(M 1934)'WorksMgr..- - > d'ISSRRTELLE, -Heriry/'G.*-' {Life " Afemberi. -rDelco'Applicance Div;,General Motors Corp., 391 " .s.'Af->1913; A' 1912) Retired.-Electrical Engr.,-Geaejal'- . : Lyeli'Aver.'ahd * 660 Seneca;Pkwy./ Rochester,; ', Electric .Co.;' and *300 S.- Broadway, v.Tarry^"''* ^NrY; . towri;-N._Y.' _ _ ' 'r> Rollof Membership^:-}' ^ 4;;- ^ ' *. IVERSON, H. R. (Af 1936) Lt;, S(E), U/S! N. R!, JARDINE, Douglas C. (Af 1929; A 1926) Owner. '' ' - Navy Dept.,"Bureau of -Ships,-Air^Corid..Sect:; . Douglas Jardme.^P-. O. Box 126. and. 1216,N. " ' Code 638, and * 1601 Argonne/PLi-N.W.; ;Wash-l.' Cascade Ave;:-Colorado Springs. Goloi - V* '-ihgton, D.-C. . ' '-- ' ' '. ' - _'* - ; JARRETT,* Roland F:^(Af 1945)"Tech. Dir- . . IZATT, George-S! (Af 1943) Supt- of Bldgs.. ' Flexaire Heatera.^Ltd-rFlextol-Works, The.Green.. - . Board of Education, :City Hall, and 32 Beulah - Ealing,-.London'W. 5,.England,.and "Glovers," ` . Ave., Hamilton, pnt., Canada. - > .. Woodlands, Sevenoaks, Kent, England.. . . ' ', - / J- ' " JARVIS. George E. (Af 1943) Vice-Pres. & Secy..'- ; ' ' *A.-E. Holmes & Bro..Co., 911-15 Banks'Ave.; -.' and 2628 Hughitt Ave- Superior, Wis.- - fc - ' JACK, Robert A.. {A-1944) 'Dist- Repr., Keeney " JASPER, Harold. C.-(A 1944) Pres- Andy J.' Publishing Co-! 6 N. Michigan Ave.; Chicago, 111., Egan Co-. Inc- 332 Bond Ave- N.W,, Grand!. ' and *3734 -Woodridge Rd., Cleveland Heights . Rapids 2. and 1529 Fourth St. N.W., Grand' . .21, Ohio. ' . Rapids 4, Mich. ... . JACKSON, Charles H. {Life 'Member; M 1923) JEHLE; Ferdinand (Af. 1938; A . 1937) Dir. of / .. Vice-Pres., Blower Application Co.; -918 N. -Engrg- Hoffman Specialty Co- 1001 York St.,' - - Fourth.SL, Milwaukee 3. and 2706 N. Farwell ' Indianapolis 7, and 3055 N. Meridian St- Apt. 9. ' '. ' Ave... Milwaukee-11, Wis.- . . - Indianapolis 8, Ind.' , . ' ' *- '' JACKSON,'George O. (A 1943) .Pres., Jackson 7 JENKINS, Charles W; (A 1945V Engf. &-Dist. . ' Engineering Co.. 936 Architects Bldg., India Repr- Taco Heaters, Inc- and 700: Jefferson '.' /- -.napolis.4, and' 132 East 44th'St.. Indianapolis - - St.-N.W- Apt, 31, Washington 11, D. C.- , 7 - 5/Ind. ' ` ' JENKINS, ' Chester - P. (Af 1945) Chief/ Adm. . JACKSON/GUbert R..(if T938) Mgr.. Boiler & Engr.,*LaDel Conveyor &' Manufacturing Co.. ' . ' Radiator Dept:. * Crane. Ltd., 45-51. Leman St., and 120 North Ave. N.W- New Philadelphia. Ohio. ` London, E."l. England. ' v JENKINS, Sydney D. (Af 1940) Owner, *S. D. ' JACKSON,-.Marshall S. (Af 1919) Mfrs. Repf., 'Jenkins:-522 Herald Bldg-. Calgary, and 2212 Powers Regulator. Co., ' 250' Delaware' Ave.;_. 33rd Ave. W.. Calgary. Alta., Canadas , Buffalo 2, and 108 -Larchmont Rd., Buffalo JENKINSON,. V. Jack (A 1940) Sales Engr- , ' - 14, N. Y. - . ' s 7 Minneapolis-Honeywell Regulator- 'Co- Ltd- - JACKSON, Melvin W. (A -1945) Pres.. Dallas -- 117,Peter St--Toronto 2B, and 3 Highgate,Rd.. : " : Engineering Co., 2000 S.' Akard, Dallas 1. and ` -Toronto 9, Ont- Canada. . - ; . ' * - - 4637 Southern. Dallas 9. Texas. '' , : ; '. ' ; JENNEY,; Hugh' B. (A 1933) Gen.: Sales-Mgr- , "'- JACKSON, Robert B; (M 1944)-Partner,'Lieb- Standard Sanitary & Dominion Radiator., Ltd.,.- . . : Jacksoii'vCo.r337 S. High St.,- Columbus 15,/and ' ' Royce-and Lansdowne Aves.'. and-96 Dawllsh `. - 2342'Tremont Rd--Columbus 8, Ohio.V' ''*' ' - Ave.-,-Toronto, Ont-Canada. ^: - ' JACKSON, .Walter F. (A'1943; J/1939) Project , -JENNINGS, Burgess H.'(Af 1942) Prof. of.Mech; . ' '- Engr-American Stove Co-: 1200 Long Ave..-.'.Engrg.' & ' Dept. Chainnan,'* Northwestern TJni-' .. , ..Lorain, and'116 Bell Ave- Elyria,-Ohio. 7 - * , 'versity, Northwestern ' Technological Institute,".'. . JACOBI, Bruce A. (A 1945; J 1939) Chief Engr- Evanston.-111. ' , ' . ' : v '' / Lerner Stores, Inc- 354 Fourth Ave.; New York, . JENNINGS, Hal K. (Af.1943) Sales Mgr- Kuem- ' and * R. F. D. Garrison. N. Y. - - - ' pel Engineering Co- 1639 Union Trust Bldg- JACOBUS, David S.. {Life Member; Af. 1916) Cincinnati 2, and-R. R. 2, Loveland, Ohio. '' Retired, The Babcock & Wilcox Co... and *93. JENNINGS, Irving C. (Af 1924) Pres- The ' Harrison Ave- Montclair, N1 J. ' -' . - - Nash Engineering Co- 138 Flax .Hill Rd- South' JAFFKE, - Walter W. - (A . 1945) . Asst. Buyer, . ,, Norwalk. Cbnn. . - - '- ' '. ' ' Nelson'Co..-2604.Fourth Ave:. Detroit 1, and JENNINGS; James H. (Af 1944)-Supvsr- Tool & 13342 Coyle Ave-Detroit 27. Mich. ' ' . " Methods'' Planning,_ General. Electric Co.,' 1635 - - JAKOBY, Albert C. (A 1938)r Pfc.! ,13150626 Brradway, Fort -Wayne 2; "and *4817 Indiana' ' . '. U. S. Army, Co. E., 801st S. T;'R- Camp Murphy, Ave., Fort Wayne 6, Ind. ' " ' -' " Fla., and 1913 E. Clearfield St- Philadelphia, Pa.' ; ; JALONACK, Irwin G. (Af'1940; A 1933; 5 1930) " Chief Mech. Engr- Levitt.& Sons, Inc- Northern .: . Blvd;, Manhasset-, and 12 E. Court: North Park, ' ' . Roslyn, N.-Ys* 1 '. : - JAMES, Hamilton R. {M 1931) Service Equip. JENNINGS, Stanley A. (Af 1935) Engr- Trane ' Co.-of Canada,-Ltd- 4 Mowat Ave- .-and' *7 ` Glen Oak N- Toronto. Ont- Canada. .' -- JENNINGS, W. G. (A 1930) Vice-Pres., ' Minneapoiis-Honeywell Regulator Co.-, -799- Beacon 'Engr- Day,& Zimmefmann, Inc- Packard Bldg- ' St- and 1970 Commonwealth Ave- Boston, Mass:. - -Philadelphia, and * 55 W. . Drexel Avei, - Lans-: JENNINS, Henry H. {Life Member; M 1901) \! . `downe.-Pa. - '*-' . . - - Retired. 29 Greyshiela Ave- Leeds 6, England:. - . JAMES, John W * (Af 1937;V 1933) Iron Fire JENSEN, Albert O. (A 1944) Owner Albert-O. - ' \ man Manufacturing Co.; 3170- West 106th St . Jensen' Wholesale Furnace & Supply Co- 1718'. : - `: Cleveland,' and 15918 Clifton Blvd- Lakewood. . Cass St- Omaha:-2, and 7409 North 57th St,, : . ...-.'Ohio. . - - ' -* * : > - . Omaha/Nebr. - ' . '' / JAMES, R. E. JAf-1945) Mgr- Htg..Dept- Harry JESPERSEN, Soren J. (Af 1944) Htg. Engr.;; . \ ' : Cooper- Supply'Co- and 597 E. Elm St- Spring U. S.' Army. Hq. 9th Service Command, Bldg. '' : . field; Mol '-- - . . .96-B. Ft;. Douglas, and *1328 -Thornton *Ave- . JAMISON,' Ernest K; (A` 1944) Contract.Engr- - ' .Salt-Lake City 5. Utah. ` '- '" ' 're The Huffman-Wolfe Co- 308 Standard'-Bldg- JESSUP. F! Judson, Jr. (A 1944) Me-r.- Htg. and *3369 .Walters Ct: N.E., Atlanta; Ga. - - ' Div- Consolidated Conditioning'Corp-*460.S;.' . / JANES. Thomas J. (Af-.1945) Engr.,-* University ' Tenth Ave- Mt. Vernon, N. -Y- and!55 Wood . of California. Dept., Grd3- & Bldgs-. Berkeley 4, land Park'Dr., Tenafly, N. J.' '- . - ; :* and 1733 Madera St.; Berkeley 6. Calif. . . , JANET, Harry LI (Af- 1920) Engri! Buensod- . Stacey.'*60- East/42nd,St.. New York, and 688 ~ Decatur'St.'. Brooklyn."N/Y.. . . 7 ... JANITZ, Robert `H. (Af 1944) Co-Partner, Fred .. '' ,G. &'Robert Hrjamts. 619lVirginia Ave.,"India, '! napolis -3, and 23 N. Colorado' Ave- "India-- JOHANNESEN. Ralph C. (Af 1943) MechVEhgr.'. ' Giffels & Vallet, Inc- 1000 '-Marquette Bldg;. " Detroit,.and *617, Louis Ave.,-Royal Oak; Mich. / ' JOHNS,'-Charles .F. (Af 1939) Sackville/New/' ' Brunswick,-Canada.*' " '' ' JOHNS, Harold B.* .(Af 1928; J ,1927) Bell & -"k -.napolis.1,-Ind. . ' .. JANOS,'.WUliam' A. (Af 1940) Sr. Meiffi. Engr- ' Gossett' Co-'Morton-Grove, and *'543 N.';Elm-'/ - wood Ave- Oak Park, 111:-. '- ' ! v- */. Western Electric Co.,'l95 Broadway. New York' \ JOHNSON,-Allen J:* - (Af 1935) . Anthracite ' -.: "'7,`"and 21-11-23rd.Terrace. Astoria 5, N.:Y. '"-Industries,'Ihc- 101- Park Ave,'.'New, York 17.-- , ..-JANSSEN, / Fred.'. (Af,.. 1945)/ Engr.. Public'' . Nr Y./ and 344 Congress Ave./ Lansdowne. !Pa/!. -'. ' Service /Company of Colorado!" 1123-W. -Third' . JOHNSON. Carl B: (A .1939) Htg. 8c.Vtg. Engr-v Ave!, Denver ^; and,2946 S! Sherman.St./Engle-,-. .. :*C."E. Johnson & Assoc- 404.-Bona'Allen Bldg.,' * . wood,-Colo'. . -v. H -- ' ' and 1154 Ridgewood Dr., N.E..-Atlanta/Ga. !'- JANSSEN,'Heni^ J..(Af 1944),Treas.y*Child `JQHNSON,: Carl W.'{Life Member#M 'T912)v .-/. Scott-Donohue. Inc- 153 East' 38th- Stp.* New), Pres., * C.. W.i johnson,- Inc.; 211- N:- Desplaines ^ *' York,' Nr-Y-' and .410' Palisade- Ave.;/"Union, Stl.wChicago-.6, Jand .1809; Morse .Ave- /Chicago , -- city/N.-j: : r'"/.vir-A' ;; / C26. IB! -`d -.j .. ;; V. V , JJARCHO, Martin D: (A;4939; V.i936)'Vice-Pres- JOHNSON,*:;Carl W.^^Af/1945)?.Mech...Engr;,;? _ ,- ' Jarcho Bros- Inc./304 E^st 45th St- New York " Mountain States .Tei. & Tel. Co.',/931V J4th -St... ' . * ; -.and llO-55-72nd-Rd.s^ort.HillirN. Y!!- / ... Denver 2. and * 2250 S. Clayton St..-Denver/Colo/-/ 44" " '/ " . ' Heating Ventilating Air' Conditioning Guide 1946 . JOHNSON,' C.Kennetb (A 1945) Research Engr., JONES, Alfred L. (Af ,1926) Pibg. & Htg; Contr., ' ' Anemostat Corporation of America, 1051 New 431 Greenwich Ave... Greenwich, and Breeze- Britain Ave., and 187 Mayflower St., - Elm mont Ave., Riverside. Conn. -- ' - ' - . wood,- Conn.' * *'- ^ ' ' JONES, Allan T.'(Af 1937; 7 1935) Chief. Engr./ ' JOHNSON, C. W.(Af 1933; 7 1931) Vice-Pres. S. A. Armstrong. Ltd., 115 Dupont St., Toronto' - t & Gen. Mgr.,- Canadian Sirroco Co., Ltd., P.-O. 5, and 264 Westwood Ave., Toronto, Ont.. Canada. Box 360, Windsor, and 11 Villaire Ave., Riverside. ' JONES; Donald R. A.' (A 1942) Indus. Gas Engr.,-' Windsor. Ont., Canada. .. Southern California Gas Co., 515 E, 'Compton JOHNSON, Edward B. (Af 1919) Draftsman, Blvd:, and *404 S. Chester Ave., Compton, Califr . -. Bethlehem Steel Co':*, -3075 Richmond Terrace. JONES, Edwin (M 1933; 7 1924) Engr. & Esti- - Staten Island 3, and 154 Wardweli Ave.. Staten mator, Watt Plumbing. Heating & Supply Co.. Island 2. N. Y. ' . JOHNSON, Fred W. (Af 1939) Pres., Johnson 608 S. Cincinnati, and 1436-East 17th PI.. Tulsa, Okla. - : Larsen Co.. 6530 Beaubien St., Detroit 2, and JONES, Edwin A. {M 1919) Staff Engr.. Chrysler - Adams & Beaver Rds., R. F. Di 2, Birmingham, Corp., Airtemp Div., and 1848'Tennyson Ave., . Mich. . Dayton 6, Ohio. . ' . JOHNSON, Harry H. (A 1944). Owner & Mgr.. JONES, Harold L. (M 1920) *33 Clay St.. - ' City. Plumbing & Heating Co., 110 Grand Ave., Newark 4, and 11 Cambridge Rd., Glen Ridge, N.J. - Box 634, and 412 South 12th St.. Laramie. Wyo. JONES, Harold S. (7 1942; 5 1940) Lt., U. S. _ .JOHNSON, Helge S. (A 1933; 7 1927) Partner. Army, Oxygen Generating Unit. Aero-Medical' ' / - Koithan & Johnson, Reprs., Buffalo Forge Co., , Laboratory, Wright Field. Dayton, Ohio, and w 39 Cortlandt St., New York 7, and 6 Forest Lane, P, O. Box 95, Michigan City, Ind. - "" Scarsdale; N. Yv V. - ' -' . JONES, Hubert L. (Af 1943) Pres., Air Condition- -: , JOHNSON, Hiram K. (A 1945) Htg. Engr., ing Engineering Corp.j 501 Sinclair Bldg., Fort - Brown .Steel'Tank Co., 2901 Fourth St. S.E., Worth 2, and *1101 Sixth Ave., Fort Worth . ; Minneapolis 14, and 4904 Tenth Ave.' S., Min- 4,-Texas.' '' - .' ' neapolis 7,.Minn. - JONES, James T. (A. 1939) Major, Post Engi JOHNSON,.Hugh F., Jr. (7 1945) Field Engr.. neer, Presidio of San Francisco; Calif. . ' % Carrier,.Corp., P. O. Box 1262. and 77 Byers JONES, Joe ,T. (A 1945) Applications-Engr.;- Ave., Akron3, Ohio. - - Fulton Sylphon Co.. 200 Southern Bldg., Wash ' JOHNSON, James J. (Af 1944) Htg. & Vent. ington 5, and 1428 Saratoga Ave. N.E.,' Wash - ' Engr., American Radiator & Standard Sanitary . ington 18. D. C. . f '. Corp.,-1730 Blake St., and 66 Ash St., Denver JONES, John D. (A 1945) Owner. Bryant Gas *- v' ' 7, Colo.' '-. - / - . Heating Co:,'626 Broadway, Cincinnati 2, Ohio, - .JOHNSON; Leslie Otto (Af 1938; 7 1930) Lt.. . . ; C. E; C., U..S. N. R., *33rd Naval Construction and 26 Sunset Ave., Ft. .Thomas, Ky' .- JONES,' John P. (& 1937)-Sr.. Partner, John - - Regiment, Fleet Post Office, San Francisco, Calif.,' Paul- Jones, Carey and Miller, .448 -Terminal ' :; and.624 14th St.,- Huntington, W. Va. . Tower, Cleveland, and .3041 Fairfax Rd.',' Gleye- , . . JOHNSON, Oliver W. <Af 1938) Chem., Engr., . land Heights. Ohio. . ... -- .' Standard Oil Company of California, 225'Bush St., -JONES, Lawrence K. (M 1939) Mgr., Special - -. San- Francisco, and *1831 'Waverly St., * Palo ` Test SecL, Pittsburgh Testing Laboratory, 1330 ' Alto, Calif. ' - .. ; - ". ' Locust St., and 320 S. Aiken Ave., Pittsburgh. Pa. - JOHNSON, Philip B. (A 1945) Chief. Engr.: JONES, T. Paul (A 1944) Owner & Gen. Mgr., ' - . Huffman, Inc., 900 Sunbury Rd., Columbus, . Air Equipment; Co., 2730 Zuhi St., Denver, and and 59 S. Ogden'Ave., Columbus 4; Ohio.' - 801 Teller St.. Lakewood; Denver, Colo.., - - - JOHNSON. Ralph B. (Af 1940) Owner, Ralph JONES, Thomas S. (A 1941) Mgr., Crane Co.. - -- B.-Johnson & Co.,.312 Keller Bldg., P. O. Box 1328 West 12th St., Kansas City 7. Mo. . . 1961, Houston 1; and 2111 .Wi Mairi St., Houston ' JONES, William a (M 1941) Mgr.. Johnson 6, Texas. '- " - ..Service Co., 1931 K St. N.W., Washington 6,-' ... r ' '- JOHNSON.'Raymond C. (Af 1944).Vice-Pres. in ' charge of Research, Anthracite -Industries- Lab- oratory. Primes, Delaware Co., and Alden Park . ManorApt. 502C. Germantown. Philadelphia 1, Pa. JOHNSON, Raymond L. (A 1943; 7 1942) Research. Engr., Young Radiator Co., 1709 S. , - Marquette St.-, and *2003 Marquette-St., Racine,' ' D. C.. and Triadelphia Rd., R. F.' D. 2, Ellicott- ` City. Md. - ' . '.; JONES, William T. (M 1915), (Presidential. Member), (Pres., 1933; 1st Vtoe-Pres., 1932; 2nd- Vice-Pres., 1931; Council, 1925-34) Treas.. Barnes -*`- & Jones, Inc., 128 Brookside Ave.. Jamaica Plain- ~ - 30, and 9 Farquhar Rd:, Newtonville 60, Mass. - JORDAN, Paul R. (Af 1943) Pres.. Paul R.. , V - Wis. > , - , - Jordan & Co.. 311- E. South St., and 2230 East: JOHNSON, Roy W. (A 1945) Partner, JohnsonLenz Heating-& Piping-Contractors, 336 Court 75th St., Indianapolis. Ind. - - -' ' - . JORDAN,.Richard C. (A# 1940; 7 1935; 5.1933) . `Ave., Memphis 3,* and 846 N. Willett, Memphis '-Asst. Head and Assoc. Prof.,--Dept.'of Mech.-. 7, Tenn." - - Engrg.. University of- Minnesota, and 1101- E. '" . JOHNSON, Russell A. (7 1945) Branch Engr., River Rd., Minneapolis, Minn.-. * . -. Frigidaire, Div.. of General'Motors, 661 N. La JORDY, Jules J. (7 1940) Lt:. U. S. N. R.', Engr... Salle. Chicago, and 2950 Desplaines Ave., River- - & Contractor, Jordy. Bros.^ Inc., 518 Julia St..- - * side. IlL - . New Orleans, La.- . \ "...JOHNSON, Tracy-R. (Af 1938) Branch Mgr... JOSLIN, George C. (A 1943) Sales Mgr;, * Whit-. . v >.The Trane Co., 6510 Forest Ave., Des Moines ' tington Pump & Engineering Co., 245 ST'Meridian ` - 11, Iowal St.. Indianapolis 4, and 525 N. Colorado Ave., ' JOHNSON, William A. (A-1945) Mfr's. Agent. - Indianapolis 1, Ind; ', . -- . *361 Fountain St.. New Haven 15. Conn. - JOYCE, Harry'B. (Af~ 1944) Registered Engr:,''. -V. JOHNSTON, James A.'(Af 1912) Engr., Cafneal 616 Commerce Bldg., and 613 Virginia Aye., . . ' & Johnston, Atlantic Life Bldg.. Richmond 19, Va. .' Erie, Pa. ` - ' -t . ` - JOHNSTON, J. O. (A ^1945). Engr.. City- Fuel - Oil Co..'- 15th Ave. & Second SL.,S,, and 4435 - Tangerine Ave., St. Petersburg, Fla. ': - - JOYCE, James J. (A 1941) Branch Mg?.*, *.The - Powers Regulator Co., 135 Luclrie St. .N:W:', Atlanta 3. and 5 Gatewood Rd.,, Emory.. Ga.-' - JOHNSTON; Lowell T. (A 1945) Master Mech.. JUERGENS, -Walter A. (A 1940) Owner, Walter '. . Johnstone Bros. Fuel Co., P.'O. Box 207, ' A. Juergens, 802 Times Star Tower, Cincinnati 2, . .. .. 22nd.St; Sta.. St. Petersburg,.and 2332 Lakeview and 1447 Aster PL, Cincinnati, Ohio.. ' ' *'. .' . - -- .Ave.-S., SL-Petersburg 7, Fla. JUHL, Edward F. (A 1945) Chief Engri, Thorpe. JOHNSTON, Robert F.. (M 1929; A 1926) Pres.. * Bros., 1100 Andrus Bldg.. Minneapolis -2,' and - - R;,E; Johnston Co., Ltd... 1070.Homer St., . 4432 Stevens Ave., Minneapolis 9, Minn. ' - - and .4583 Connaught -Dr., Vancouver, B. C.. JUNG, John S..(Af-1930; A 1923) Owner.. Jung . :.v. - Canada.' _ Heating Co., 2499 W.-Greenfield Ave., and 1516. ' JOHNSTON,- Robert-M. (A 1942;'7.1937) Lt., 5. Layton-Blvd.', Milwaukee 4; Wis. '. U., S. N.'R.,.DepL' Marine 'Engrg., U..S, Naval' JUNGELS,' Alton J. (Af. -1945X Constr. Engr.,' -., . j-v.;-Academy,-Annapolis, cand-*Cumberstone, Anne . R. C. A., Camden, N. _J.i aiid 597 Fairway '^i-Arundel County. Md. - --e = Terrace, Philadelphia 28. Pa.*. - **, - *- ' r -s JONES,--'Alfred. (Life-Member;" M H92&) Cons. - junker; W. H: (M 1936) WksT- Mir.. Emery :_' Ehgr., Armstrong. Cork; Co., and 213. N.. West Industries, Inc.', June and'Long Sts., Cincinnati -'-; > - End'Ave,','Lancaster. _Pa.~ '- " 17, and *6068 Dryden:Ave.', Cindnnati l3, Ohio./' - -s 1/ Rollof `Membership 45 '. JUSTICE,'Jack'T/. (A 1945) Co.-A. Srd'RkpL. KEARNEY, Joseph' S. JAf; 1939) Pres. & Gen/ . .` ' Bn. A-. S. F. P. R. D.:, Camp Beale, Calif., and Mgr.. Northwestern Heating & Plumbing Co., ' .. . *300 W; Emerson St., Paragould, Ark.'r ` ' ' 1905 Greenleaf' St., and *1405 Lincoln St.;. ;. Evanston, III. ` ' '\ K: " ' _' KEATING, Arthur . J. (Af. 1937) Engr., The ' Powers Regulator Co., 2720 Greenview Ave.,-ahd ' KACZENSKI, Chester (A 1939 : 7 1933) 150 5646 N. Kenneth Ave., Chicago, 111. -. ' West 64th St., New York 23. N. Y.' KEATTS, Rolla M. (Af 1944).* Mgr. & Engr., KAGEY,' I. B.. Jr. (Af 1941) Mgr., Kerby ' Keatts Thermal Equipment Co.,. 20 S. Third. - Saunders/Inc., 101 Marietta St. N.W., Atlanta 3, SL, Rm. 223, Columbus 15. and 184 Northmoor -. - - and-254 Alberta Dr. N.E., Atlanta, Ga. - PL. Columbus 2, Ohio. '- KAHN, Charles R., Jr.` (7 1939) Lt. Comdr., KEEFER, Donald M. (A 1945 ; 7 1941) Produc-; . U. S. N. R., and *405 East 54th St., New York tion Engr., Solar Aircraft Co., 22p0 Pacific Bivd., . ' 21, N. Y. .: . ' -- San Diego 12, and 30 N. New Jersey St., Lemon \ KAISER, Fred (Af 1935) Regional Mgr., *Minne- Grove. Calif. - `: . apolis-Honeywell Regulator Co., 433 E. Erie St., , KEELING, Fred V. (Af 1943; A 1940) Mech. . . . .- . Chicago, and 300 Forest, Oak Park; 111. . . KAJUK, Andrew E. (Af 1936) Engr., Lockwood Green & Co., 10 RockefelJor Plaza, New York, N.-Y.;'and 279-Palaside Ave., Garfield, N. J. -KALBFLEISCH, Theodore F., Jr. (A 1945) Engr., Public Works Dept., Bldg.. No. 1,. U. S. - . Navy Yard, Philadelphia 12, and.960 Arrott SL, .' ' Philadelphia, Pa. - - ' ' - . '. KEENEY, Frank P. (Life Member; A 1915) Pres., - - Keeney Publishing Co.. 6'N. Michigan Ave.;.' . . . ' . Supt. of Bldgs. & Grounds,.* Board of Education, Chicago 2, 111: . . ' " '. - ' 249 Glen SL, and 29 Stewart Ave., Glens Falls. KEETON, Robert W,, M. D. (Af 1943) Head. : - . -N. Y. -* - - ' ' ` ` - DepL-of Medicine, University of Illinois;'1853 .- * KALLUSCH, Howard A. (7 1944) In service, and Dewitt, N. Y. -. .. . .KANE, John-M. (Af 1944) Chief Efigr., Dust ' - Control Div.,- American Air Filter% Co., 215. , ` Central Ave., Louisville 8, and * 514 Fairlawn - . ' ' Rd., Louisville 7. Ky. - ' -- KAPLUN,' Eugene A. (Af 1943) Cons. Engr.. ' 1 207. Fourth Ave., New York 3, and *75 Park Terrace E., New York 34, N. Y;-. ' ` . KAPPEL, George W. A. (Af 1921) Pres.-Treas., . * Camden Heating-Co., 8 Market St., Camden,. ' and 421 Maple Ave., Westmont. N. J. ; , KARAKASH, Theodore J. (A 1940; 7 1936). Air . .. Cond. Engr. & Contractor, P. O. Box '667? - - and Ankara Palas 20, Ayazposa, Istanbul; Turkey. . KARGES, Albert (A 1935) Mgr., The James W. Polk St., Chicago 12, and 5555 N. Sheridan- Rd., Chicago, III. ' ' KEGARISE, Ralph R. (Af 1943) Cons: Engr., j. '709-Henley St.. Knoxville 16, and 1752 Yale .-/- - Ave.; Knoxville, Tenn. -- KEHM, Horace S. (Af 1928) Pres., The Kehm Corp., 135 S. LaSalle St., and Union League Club, . Chicago, 111. -' :' KEIM, Eugene C. (Af 1944) Branch Mgr., U. S. , -Radiator & Pacific Steel Boiler Corp:, 314 E. New , York St.', Indianapolis 4, and 3222 Park- Ave.-, . ' , - - Indianapolis 5, Ind. - -- KEIST, Walter E. (A 1944) Partner, W. J. Keist. - . & Son, 322 Perry Highway, West View, and *393 . Center Ave., West View, Pittsburgh 2. Pa. Stewart Mfg. Co., Ltd., Tecumseb SL, -and *37 KEITH, James P. (Af 1938) Vice-Pres., Canadian - Perry Sti, Woodstock, OnL, Canada. . ' . Domestic Engrg., 1 Co., Ltd., 1440 SL Catherine' .. KARLSON, Alfred F. (Af 1918) Chief Engr., St. W., Rm. 403, and.4935 Clanranald Ave., ' ' , Parks-Cramer Co., P. O. Box-444, Fitchburg, Montreal, Que., Canada. ' ' and 186 Prospect St., North Leominster, Mass. KELBLE, F. R. (Af 1928) Vice-Pres'.-Mgr;. - KARLSTEEN, Gustav. H..(Af 1935) Plaiit Engr.. Huffman-Wolfe Co. of Philadelphia.,.-.4660- -.' ' ; Dunlop Tire & Rubber.Corp., Station B; Buffalo, ' and Box 55. Route 1,'Tonawanda. N. Y. , KARSUNKY, William K. (Af 1939) Cons.-Engr., . #2011 K St. N.W., Washington 6. D. C.. and - . Three Oaks, Kensington, Md. . . " . KATORIE, V. T. (A 1946) Asst, to Vicc-Prfa.. - York Corp., and 1533 First Ave.-, Elmwood, York, Pa. . - .... ' . KASAMEYER, Alfred L. (Af 1943) Engr.. Bldg. . Operation Dept., Detroit' Edison Co.,' 2000 Second Ave., and * 11414 Marlowe, Detroit, Mich. - KAUFMAN, Aaron M. (5 1944) R. T. 3/C, ' ' - - U. S. N. R., Ui S. S. Vincennes, Div. "Eye," North 18th SL, Philadelphia, and 205 Pleasant / ' Ave.', Glenside, Pa. '' KELL, John R. (Af 1944) Chief Htg. & Vtg. Enjjr.,' Dr. Oscar Faber, Cons. Engr., 1 Worley Rd., Sf. ' . Albans; and "South Meads,'' London-Rd.. St. . Albans, Herts, England. ' ' - . ... :- KELL, Waldo R. (Af 1943) *1007 .West 68th . Terrace. Kansas City,' Mo. * .- .- ... -- ---. - KELLER, Arthur B. (A 1945) Staff Engr., Plaiit Engrg. Dept.-, Corning Glass. Works, and *169- : Wall SL, Corning. N. Y. . * KELLEY, Davis F. (A 1945) Owner, Enterprise .' ' . c/o F. P. O:, San Frandsco, Calif., and 2281 . Heating & Air Conditioning-Co., 3859 'McRee* Bellfield Ave.. Cleveland Heights 6, Ohio. ' -Ave., SL'Louis 10, Mo. . ' - ' ' - ` . . ~ KAUFMAN,'H. J. (Af 1937) Owner, The H. J. KELLEY, James J. (A 1924) Fuel Oil & Burner .. - Kaufman Co., 13215 Roselawn-Ave., Detroit 4, Asst.,**Colonial.Beacon Oil Co., 378 Stuart'St., - - Midi. . > ' . Boston, and 142 Governors Ave., Medford, Mass. - KAUN, William F. (A 1944) Partner, * W. F. KELLEY,. Ralph P; (A 1945) Mfrs. Agent.- - ' 1 , ' , '' '' Kaun & Son, 4346- Maple, and 2822 Arroyo, DaUag q TCexas - . . . KAUP, Edgar 6. .(Af 1938) Mech. Engr:, *801 Solano Ave., Albany, Calif. KAVANAGH, Perry E. (A 1946 ; 7 1944) Asst. Engr., Wyeth, Inc;, and 117 E. Oak St.,' Mason, - Mich. - : ` ' KAVENY, J. Gordon (Af 1943) Pres. & Engr,, . . -Ralph Pat Kelley&Assocs., 1521 Southwest 11th '/ . . Terrace,. Miami 35, Fla. . " . . - ' KELLOGG, Winston T. (A 1938) 787 Hazel- , wood SL, Birmingham, Mich. - - . KELLY, Charles J. (Af 1931) N. Y. Repr., James ' P. Marsh Corp.,-155 East. 44th'SL, New.-York.^,'- N. -Y., 'and 440 Fairinoimt Ave., Jersey City, N.'J:' . ' -Quiet Automatic Burner. Corp., '49 Bloomfield, . KELLY; Francis C. (A 1946; 7 1942) Pres., Kelly - " Ave., - Newark 4,- and* Fairfield Rd., Little - & Cracknell; Ltd., 2359 Dundas St. W., anffi*15 - .. ' . Falls,' N.' J. .. ' ' . Keele St., Toronto, OnL, Canada: -'' . .. ,,*'-' . KAYAN, Carl F. (Af 1942) Asst. Prof., Mech... KELLY; Herbert C. (Af 1945). PresT,:* The' ` .. Engrg.. School of Engrg., Columbia University. George-Howard Co., 107 Water SL,'New'Haven.. ' - Morningside Hgts., New York 27, and 425 River ' and 31 Greene St., Milford,- Conn. - ' ' t- - - side Dr., New York; N.-Y. , ' KELLY, *.H, J. (A. 1940) Sales Engr., &.Owner, t - . . KAYSER, Phillip G. (7 1942) Ensign, U. S. N. R.. " *816- Howard 'Ave., and .8006 Nelson-SL, New .. Jr. Mech. Engr., McQuay, Inc.:' 1600 Broadway Orleans,'La. : .. : ' N.E., and *3120-39th Ave. Si, Minneapolis, Minn. .'KELLY;. James C. (A 1942)- Gen; Sales Mgr . * . KAZLOUSKAS, Anthony. (7 1943)\ Sr? Mech. . Sullivan Valve & Engineering*Co., S. 124 Wall . .. V Engr.; Goodyear Aircraft Corp., Akron, and 960 . St., P. O. Box 2208, Spokane 7, and W/807 -25th ; .. Sawyer Ave., Akron 10, Ohio, o * Ave.; Spokane 9, Wash. ` - * '' ' -KEANE, G. F.'. (Af -1945).-Application Engr.-; KELLY, OUn A. (5-1940) Capt.; U. S. 'Army " * ' . Carrier^ Corp.-, Syracuse. 'and 316 Haddonfield Air Forces, A. C. -T. D.-42/4, Chanute Field; III.,- . * - Dr., DeWitL N. Y; .................. .. - and Shelby, Mich. .' _ - H*. - ' KEARN, Jeff (A 1943) Mgr., Jeffi Kearn* Co., ' KELLY, Wilbur C. (Af 1935) Field Engr.,,* Iron' " . ' - . ` - 342 Park SL W., and 411 Randolph Ave., Windsor,. `Fireman Corp., 449 Paul Brown-Bldg., St. Louis-1, .. Ont..-Canada.,. / ; , , - and 440 Hanley Rd. S., Clayton 5, -Mp., ` 46, . v/' Heatihg. Vehtildting. -Air \ Cdhditioftihgl. Guide ^1946.:. -/. KEMP, `William . H. ..(A 1944) Service 'Mgr.; f ;KTLLlAN, William J; (A:i946) Lt. U!.S.` N>R.." ...Shipbuilding'Div-' Bureau of`Ships, U.'S.'Navy.- 7519 Kirtley St;, Cindnnati 27. 0hio. - ' . ' /j. Bldg., T-4 Room 2222, jl7th and\C6iistitution: K1LLOREN, Donald E. (S 1941) lst Lt.. -U. -S. :: Ave/N.W,-. Washington, and 928 Perry PL N.E., - 'Army.'Co. D, 27th Bn., Ft.-McClellan, Alai'- ' ' Washington 17,-D, C._ ' ; "'i ' . KENNEDY, Don P. :(A 1945) -Engr.-Estimator. - Sans Co- 132 Blackstone Ave.. and ' 1 Grandin St;. Jamestown; N. Y. ' '- . *. .- KILNER, John ` S. '-(Af. 1929) Detroit '.Dollinger Corp.; 1091 Seminole.Ave.; and '. Seminole Ave., Detroit 14, Mich. '' ' - Repr.. 1091 -. - KENNEDY, James C. (A/.1945)Htg. Supt. KILPATRICK, William S. (Af ' 1937) W. S. Estimator,' Edward Joy Co., 133 Market St., add -301 Plymouth Dr., Syracuse, N. Y; . ./ ' Kilpatrick & Co., 1100 East 33rd St., Los Angeles,; ana 1545 Chelsea Rd.. San Marino 9, Calif. . KENNEDY, Maron (A-1936; J 1930) Application KIMBALL. Charles W. {Life Member; M 1915)' - Engr., ' York'Corp- 5051 Santa Fe Ave.; Los ' Pres., Richard D. Kimball Co.. 6 Beacon St.. Angeles-11, add 2704 Carlaris Rd-' San Marino '- Boston, and 65 Prescott St., West Medford, Mass. . 9. Calif.* KIMBALL, Dwight D.' {Life Member; M 1908) - sj V* KENNEDY, Walter W. (M 1941). Dvlpt. Engr., . Barber-Colman Co., and 209 Hollister Ave., . Rockford, Ill._ . .. . KENNETT, V.>A. (Af 1936) Managing Dir;.. {Presidential Member) . (Pres;, 1915;' 2nd Vice- Pres., 1914; Board of Governors. 1912-13; Council,. 1914-16) Cons.-Engr., Grand Central: Terminal . Bldg., Room 1728, New York l7.:and 145-West -_ Air Conditioning & Engineering, Ltd.. 3 Bayley.' ' 58th St.,' New York, N. Y.. . ' ; -St.,-Tottenham Court Rd..-London,! W.l:;, and ? KIMBLE, Carl W. (A 1943;. 7 1938) Owner. V' 178 Grove End Gardens, St. Johns Wood, London, Advance. Heating & Sheet-Metal Works. 315 . :N.W. 8. England; : ' ` -' '- .' v';.- - 24th St., and 2020-38th St...Rock Island,-IU. . KENNEY, Daniel J.-(A 1944)'Chief. : Fuels & - KINCAID, Wendell V! -(A 1945) Dist. Engr.. .^Utilities Section,.U. S. Army Ordnance, Boston.; Pittsburgh Leetro.Dryer Corp., 307 N! Michigan' . VOrdnance 'District 140.Federal:St., Boston, and /"Ave., and 3934'Frontier. Ave., Chicago. Ill/ - - ' 268-Renfrew St.. Arlington. Mass. . . KINDLI^l, Sidney (Af': 1945) Gen. Mgr., Mat- - ' KENT,'A*. Douglas (A 1946;'/ 194l)Asst. Research V;Engr., Div. of Mech.'Ehgrg.. National Research `/CoundLYapd *104/Research Rd., Quarries P.'O- . . Ottawa, OnW.Canada. ' . ' KENT,-Laurence Fv (A 1927; J 1924) Pres.-&. Geri.'-Mgr., Moncreif Furnace Co;. P. O. -Box' 1673;-and 1515'Morningside Dr. N;E., Atlanta T,*-Ga.' ' . V- * ; : *: \ KENT,'Richard L7(Af 1936) Dist. Mgr., Trane Co., of ..Canada/Ltd- 303 New Hargrave-Bldg., thew Hall-STCo., Ltd., 26-28 Dorset Sq., London -.N.W. 1, and *83 Woodberry .Ave., ' Harrow,- Middlesex. England. ' ' KING. A. , C.' (Af 1936) Cons. Eno- .'^S S. '.Dearborn St..'Chicago 3, 111: ' - . . . KING, Harry K. (A 1944) Field Ser. Engr.. A. M. ' Byers Co., 1409 Girard Trust Co..Bldg., Phila- . delphia 2, and *4678 Woodland*Ave'.; Drexel Hill': ` Pa..--';; . -* ** v . ' * " Hargrave' St., and- 147- Wellington Crescent, ; KING,- John S. : (A - 1940) Engr., Anthracite Winnipeg. Man.. Canada. ' -Industries Laboratory.-and 38 Runnemede Ave., ' KERBEL,'Jesse (A 1946; / 1944). Ensign, U./S.' Lansdowne', DeL Co., Pa. ' - .- N. R.;.* 135-14 78th Rd'.. Kew Gardens Hills, :KING, Roy U (Af 1945) Div. Engr., The HeU Co.. - Flushing, N. Y...................: . .- . ' s' ' ,- - 3000 W. Montana,St., Milwaukee 1, and *4304- KERN, Joseph F., Jr. (A 1937): 26 Park pi., N. Sheffield, Milwaukee 11. Wis. .' - ' . New York/and Box 695. Massapequa. N. Y. ' ? KING, Thomas E. (Af 1943) Vice-Pres.. Lord ,. .KERN; Raymond -T. (Af. 1927) Chief Engr., - & Burnham Co., 2 Main St.. Irvington,' and 47 -' JennisonCa., Fitchburg, and 51 Glaflin St., Jane Ave., Hartsdale, N. Y. - . ' ' Leominster,-Mass".' V - . . KINGSLAND, George D. (Af 1935) R. R. No: 3. KERR; Gerald. C. '(Af 1945; A' 1940) Acoustical . Eureka, Mo. .. . . Engr., `Tayior-Seidenbach, Inc., 1401 -Tchou-' pitouias St.,' and'625 Pine St.. .Apt. ,2. . New .'Orleans, La. ' KERR;- Robert .(if 1943) . Gen. . 'Mgr.; Universal - . Sheet Metals,. Ltd.. 980 Queen St,. E- and 30 Woodington Ave- -Toronto,'Ont-Canada. .- KERR, William. E. (Af 1937) South. Carolina Repr- Barnes & Jones, Inc., 1201 Hyatt Ave., .< Columbia 47,- S. C; .... * -': .- KINGSLAND, Norton ,.W. (A 1945) Publisher. Heating & Sanitary Age. Age Publications, Ltd., . 34'Willcocks St., and 123 Lawton Blvd., Toronto, - Ont.. Canada.' KINGSWELL, William ' E. (Af `1935) . Pres., . William E. Klngswelll Inc.. 3707/Georgia Ave. N.W., Washington, D. C., and.R: F; D7T. Silver' Spring. Md. '' .: KERSHAW, Melville G. (Af 1932; A 1926; /1921) KINNEY, A. M. (Af 1936) Pres.. A. M. Kinney, Vtg. '& Air Cond.- Engr., E. -1.-DuPont de -. Inc.,1211 Enquirer-Bldg., Cincinnati.2; and Box ' Nemours & Co., 'Wilmington, Del.', - and 7313' - '158. Indian Hill Rd., Indlan-Hill, Cincinnati, Ohio. - .North 21st St:. Philadelphia, Pa. ' ' * - - . KINZER, Osborn A. (Af 1945). Major,'Corps., of . ' KESSLER, Clarence' F. (Af - 1938) Asso.' Prof.- -.- Engrs., U. S. Army, and *4312 Glenwick Lane,"- ,-Mech. Engrg., University' of Michigan, 241 W. .Dallas, Texas.' * Engineering -Bldg., and 1756'-'Broadway,'-Ann KIPE, J. Morgan (Af 1919) Dir. of .Education. - ..r Arbor,:Mich. '. - ;f ' ~ . ' ' Anthracite'Institute, Primos,. DeL. County,.-and KETCHUM, E. R. (Af 1943) Eng/.. Dow Chemical'. 801 Homestead Ave..' Havertown. Pa:' ' -- Co.', and 1322 W. Fifth.St., Freeport,-Texas. *. /.KEYES, Marcus W.,(Af 1942) Lt (j.g.) U. S: N. R. ' .65I4Brerihon Lane,.Chevy Chase 15; Md.,and 99 .Colchester, St., Brookline. - Boston '46, Mass. KIRKBRIDE, J. Owen (Af. 1938) .Partner,. Parent & Kirkbride, Fourth and Locust Sts:. . Philadelphia 6,. Pa., and 1121 Eldridge Ave.. West Coilin^wood, N. J. / . '- '. KEYSER,'Herman M.~.(A;.l937).M.W.Sales&' " Co.; -801'.- W. - Baltimore, 'Detroit.' and *10703' . Hart,` Huntington-Woods. Mich': - ' ' XICZALES, Maurice D. (Af,1935) Chief Air Cond. - Engr.,"Army. Motion Picture Service,'Room 400. , TowerLBIdg;,-Washington ,25. and 6200-31: St. -N.Wr,-Washington 15, D. C; . ' - . KIRKENDALL, Horton J. (Af ' 1942; A 1938) Sales Re'pr.-Htg. Equip.. 291 Catalpa PL: Pitts ' burgh 16, Pa.- --- - - T - KIRKPATRICK, Arthur Hi .(if. 1936; V 1931) Engr.; Frederic B. Stevens Co.,' 510 Third St., \ and Webster Hall Hotel, Detroit,.Mich. - . '-' - KIDD, Charles R. (Af 1942; A 1938) Fuel Special- i ist, " Federal "Public Housing -Authority..'Room 201F.\Longfellow Bldg:,' and *54 Vee SC N:W., KIRSCHHOFER, Ferd: J; .(A 1943).'Owner. ' - ' Federal Home.Heating Co.. 259-Delaware Ave.,' ' Buffalo 2,'New-York. V. ' .'. Washington, D; C;'. . - ' ' " '* ' ' ' KIRTLAND, Eugene M. (A-1940) Pres..' Engi- r ' KIEFER.'E. J.v, (A 1932;,./ 1928). -Mgr;; H.* C. : heering Specialty Co.. '204 W. Ridge' Rd., /and'' Archibald,C0.V.AO6 Main St>.'and.l08.N. Sixths '-2900 W.;Beverly.Dr., Gary, Ind.-.. . -St:','Str6udsburg,'Pa.' - 7 7 KITCH, Richard B. (Af 1941) Registered.'rEngr., KILLEEN;^ Edmund F. l(A ;i945)>854 Baker .-314';'Palmer- Bldg..' Atlanta 3,- and -No.-- Druid ; ".'W! Bldg/,.Minneapolis', Minn.' " `; ~ . KILLEEN, 7 Thomas. -F. (A\.1945) .' Dist;- ^Mgr.', - Hills.Rd.. Ro'ute 2; Atlanta, Ga..'' ' *-. ^ -KITCHEN, Darley E. (A-1944)!Owner, Kitchen.' ~ i-- "j ' ^StruthersWells Corp.,-1107.;Liberty.Bank' Bldg..-' Hf|4grI Buffalo. 2,vand 734'' Richmond 'Ave.;''-Buffalo *13,. v-: ' *. -/Hating'Co.; 364 E.hunter St:.'Logan, Ohio.- ' - KITCMEN, FraudsjAv-(A 1927;:/ 1923); Pres. 'American/ WarmingV'entilaLihg .Co- 1514 ' .. ' wKILLIAN;-\Vlc - J.. (A{1937.) Pres.. V.' J. 'Killiah - 'ProSpect Ave- Cleveland, and 2077 Campus-Rd!. 1 '.Cp7!907-:L4nden'Ave.i .Winnetka,'ill. \ .* 7 South'Eudid/Ohio.',` U -.>' v^t7v {Roll^of-MembersHip^ 147 ' 'KITCIIEN;' WUUaha/H.- ji;VA''`lS38);-Eac. Lt..' . KOLASA, Marion J/(/i942) Lt. 0-i) U. S:N. R. .-R:- C.^N.. V.. R., Retired, Engr.', -Ther'm-O-'Rite' Supervisor v of'Shipbuilding, U. S. Navy, c/o; Products,< .Ltd-`.. Confederation Bldg- - McGill' ' ' Bethlehem Steel .Co- San;-Francisco; Calif-'and College Ave- Montreal, P. Q.\`and ;PvO. Box713,' ' 2663 Frederick'Ave- Detroit ll. Mich. . - ' * Midland, Ont- Canada. t"''1 ' KOLB, Trad/W. (if 1938) #598 -Monadnock KITTLESON, Howard B.'/ (A ~ 1944) Supt.'. of ' - Bldg- San Francisco '5,'-and 82 Macondray St:, Maintenance. Kraft Cheese Co., Albsuiy 2L and San Francisco 11-,'Calif. :- - ' Box 21; Albany,' Minn. ' KOLB; Robert P/(Af 1939) Prof, of Heat-Power KLAGES, Frank E. P.: (Af 1940) Dist.- Mgr... Engrg- o Worcester Polytechnic' Institute, -Wor The Powers'Regulator Co^ 1034 Jeff Stdl -Bldg- cester 2, and 20 Prudential Rd- Worcester. Mass. 'and 1615 S'. College Park' Dr- Greensboro, N. C.. ' . KOLLAS. Will J. (Af 1939) Design Engr- The KLEIKAMP, Henry (A- 1945) Mech. Engr..' Lyn<di Co- 6000 N.E. Union Aye., and 6104'N.. Inter-State Heating & Plumbing Co- 521 South-' Missouri Ave., Portland 11. Ore. ' ' .west Blvd- Kansas City, and 2322 Cypress St;;' . KONZO, S* (Af. 1937; A .1936; / 1932) Special' . Kansas City 1, Mo.' - .' ` - - Research Prof- University of Illinois. 1108 W. KLEIN, Edward W.^(Af 1917) Repr.. Warren Stoughton_St- Urbana. and-510 S: McKinley. - .`Webster & Co..' 152'Nassau St. N.W.', -Atlanta 3, Ave-Champaign, 111. - '' ' ' and 3845. Peachtree Rd- Atlanta, Ga. . KOOISTRA, John F. (if* 1933) Branch Mgr.,; KLEINHOMER, William G. (A 1943) Mech. .Carrier Corp-, 625 Market-St., San-Frandsco'5,- Engr., Lerner Shops, 354 Fourth Ave- New'York.. . . and 1128 Cortez Ave- Burlingame,;Calif. v - - 'and *2142 Troy Ave- Brooklyn 3, N.'Y. : KORN, Charles B. \{M 1922) Member of- Firm. KLEINKAUF,. Henry y. (Af 1938; / 1937) Reber-Korn Co- 817'Cumberland'St- and 1022 . Natkin & Co- 514 South 11th St- Omaha 8, and . S. Eaghth St- Allentown, Pa..,. . ' ' . 1855 South 90th St-Omaha. Nebr. *' - ` . FOSTER, Howard H.(A 1942; /1939) AppUcation' KLIEFOTH; Max H: (A"l939) Treas- Research ' Engr- Westinghouse Electric' Intematioiial: Co..`. Products Corp- .1015 E. Washington Ave- and 40 Wall St- New-York 5. N. Y. and *44 Aubrey Woodward Grove;'Madison,-Wis. - Rd-Upper Montclair, N. J. " ' KLINE, Clayton' F. (Af 1944) Vice-Pres. & Engr., KOTTCAMP, Harry,E. (A 1945) Owner/* C.-C. " --Nicholson. Inc.. P. O. Box 317, and 2312 Wood Kottcamp & Son, 515 W. Market St.. and 519 ' row St-' Durham, N. C. - - . ' W. Market St- York, Pa. . - . '/KLINK, Erwin J. (A 1946; / 1942) Ensign. KOTZEBUE, R: W. (Af 1944) Partner. BeU- . *U. S. S.. Tennessee,, c/o Postmaster, San Fran- Kotzebue Co- 1505 E. Houston St- San Antonio' cisco,'Calif. -s ' 2. and *438 Paseo Enctnal, San Antonio 1. Texas. KLUGKHUHN, Frederick H: (/ 1940) Sales KOUBEK, J. V. (Af 1944).Engr- National Carbon ' Engr'., Washington -Refrigeration Go- (York Ice ' Co- Inc!. West 117th St- and Madison; Ave.. . Machinery),'1733-14th St. N'.W- Washington 9;`. and *3597 West 155th St- Cleveland. Ohio.* ~ ... D; C--and *508 Silver Spring Ave- Silver Spring, - KRAMIG, Robert E.. Jr. (A' 1933) Vice-Pres. & Md.-- - v- : ' .' . - Treas-R. E. Kramig & Co-. Inc- 222-4 East XKLUGE; Burnett M. (A -1944; / 1938) Applica ' 14th SL. Cihdnnati 10, Ohio. '- tion Engr.,*'Bayley Blower Co- >1817 South.66th KRAPOHL, William H. (Af 1941) Htg./& Vtg. St- and *1236 S. 46tb St- Milwaukee. 14 Wis. Engr., E. .B. Badger &-Sons. Co.', 75.Pitts St., : KNAB, Edward A. (Af 1943) Htg. & Plbg:.Con-. Boston, and 79-'Prospect St- '. .West. R'oxbury, .tractor, .E. 'A.- Knab, 3723; N. Oakland Ave., Mass. /-Milwaukee 11, Wis. . . . . . J' - KRATZ, Alonzo P.* (Af 1925) (Council, 1938-43) ' KNEESE, Victor C. (A ? 1945) Branch M gr- Research Prof;, Dept. of- Mech. Engrg.,'. Uni ' .General Controls Co.. 1816-Magnolia St...and versity of Illinois, and 1003'Douglas' Ave- Ur ` 3124'Princeton, Dallas, Texas. ' . - ' - bana, 111: , ' ': v.' . .KNIBB,- Alfred E. (Af-1930) Htg.'Engr., L. L. KRAYENHOF, Harold G. (Af 1945) Sales Mgr... McConachie. Co'.. 1003 Maryland' Ave- Deiroit Lennox Furnace Co.; Inc- 400 N. Midler Ave.; : 30. and 9333 E. Jefferson Ave- Detroit 14. Mich.*5 Syracuse, and 205 Newfield'Rd.7 De, Witt; N. Y. KNIGHT, Frank 3. (A 1944) Chief Engr- Huff KREINER, Jack'(A 1940)-Owner, Jack Kreiher, ... man Manufacturing Co., and 506 S. Dude Dr., 123 East 18th St- New York 3. N. Y. % ** - * Dayton, Ohio. -. ' . ' ' - KREMER, Richard H. (Af 1943) Pres.; Kremer- KNIGHTON, John K. (Af 1944) Mgr: of Sales. . Hicks 'Co.. 3974 Delmar Blvd-' St. Louis 8. and ; ServeL Inc!, and Schenk Rd..-R. R. 7, Evans 473 Oakwood.Ave- Webster-.Groves 19, Mo;- '.- . *ville,.Ind: ' ' KRENZ; Alfred S: (Af 1937; A 1935) Pres. & KNOWLES, EIwln'L: (A 1937) Prop/ Knowles 7 ' Treas/Krenz-.&- Co.,- 5114' W; Center St., Air .Conditioning.. Marshall Heating Co- 1324:- - Milwaukee -10.' and; 7933. W. - Milwaukee' A've., Marshall -St. N:E., and' 400* Thomas. Ave. S > Minneapolis. Minn.' ' ; "- Wauwatosa-13, Wis.' ' ' ` v.- KREZ, Leonard (A 1935) Vice-Pres., Paul J: KNOX, John C. (A 1938) Vice-Pres- Knox Mfg. Krez Co- 444 N. LaSalle St.; Chicago. 111/.' - ' - *Co., :.301 `Insurance Bldg.,' and 176 Sans Sovei- . KRIBS, Charles L,, Jr. (Af-1935) Chief Engr.. ' 7Dr.,.Waterlod,;Iowa. - - ' --Hedrick & Lindsley. 5201 Fannin St., Houston.4, KNOX, J. Roy (A' 1945) Branch Mgr., U. S. and *2214 Maronehl Blvd- Houston 5. Texas. /Radiator Corp- 1713 E. Carson St- Pittsburgh - KRIEBEL, A.'E. (Af 1920) Sales Engr, Hayries- -'. `3, - and. 18 Home. Kort, West View, Pittsburgh Blankin Corp.. 1-124 Spring. Garden SC, Phila- ... 2,'Pa.- ' delphia, and Berwyn. Chester Co/, Pa; - ' ' . KNOX, ' Walter (Af 1943) Designing . Engineer, ' KROEKER, *J. Donald* (Af, 1936)' Cons-.Engr- : Le Claire, Iowa. , ... - '- * ` *618.Park Bldg- Portland'5.-.and 6831 -N.E. - KOCH,'Albert H. (Af 1938) Southeastern Regional . Siskiyou St/ Portland .13, Ore. ` ` ' ' ' Mgr-.Minneapolis-Honeywell Regulator Co.. 5 N.. . KRUSE, W. C., Jr. {M ,1938) Owner. Kruse Rhodes'Center N.W- and *115 Terrace Dr. N.E., Engineering Co., 24-.C6mmerce St;. 'Newark 2. . .. Atlanta, Ga. ' - '' _ *. - and 292 Scotland Rd-South Orange,-N. KOCH,-Richard G. (A 1935)'Sales Dept.'Engr-.' KUCERA,'Henry T.'(A/ 1943) Presl, Auto'matic Milwaukee Gas Light Co..-626 E. Wisconsin Devices,. Inc- 810 W. Ohio'-St-' Chicago,-.and Ave.,'.Milwaukee 2,; and 5707 W.' Brooklyn. Pl- -15 Elder Lane,.La Grange. HIT' / // '- -Milwaukee'lO,.Wis.-'. .'' v ,'."v -- `'' ; KUCHER,/ Andrew A. "(Af:-1938) Director^'of KOCHEL,'Robert K. .(A 1945) Production Engr.. Research * Bendix Aviation Corp..`Research: Lab - Goodyear;'Aircraft' Corp.', 1210 Massillon- Rd., oratories, 4855. Fourth:Ave.,. DetroitT/'and 41 - 'Akron: 15i and *1690, Tonawanda*'Ave'., Akron = Lochmoor -Blvd , Grosse Pointe Shores 30,` Mich. 5, .Ohio; ' ..' - ^ KUCK,'..Theodore'-A. /(A'.-1945) - Field- Eagr., " KOEHLER,'C. Stewmrt '(A .1936)-*Aif-'Cqhd.-' . South Side Hardware/& Plumbing Co-yl512. ' Controls Div., Minneapolis-Hoheyvrcll ReguIator South.,-12th St- 'aiid:T108':Oaklahd {Ave., 'She- -Co.,'221 -Fourth Ave- New' York 3.` and *3l35 -.boy^uiiWis. ' .' 7 '- '' . Hull Ave- New York 67,' N. Y.. ; ./ iKUECHENBERG,'William A.'(M 1937) Pres KOEHLER, Geo. N. (Af 1943) Dist: - Repr.. ' . R.-;B. Hayward .Co.'.-11714-Sheffield' Ave*:. .- Minneapolis-Honeywell' Reg. Co- 713 ..Maritime Chicago, and .427_ Elmore /Ave- Park Ridge. 'IIL Bldg- .New Orleans 12, and *6713 Colbert St- KUEMPEL,-Leon L. (Af 1936; / 1929)- Owner. . - New Orleans 19, La'.-.-- .'' ' - - -v . ! * ;Kuempel- Engineering .Co/' Union Trust Bldg.. ? KOENIG,' Andrew C/(/ 1940)'# 701; E. Missouri - Cincinnati; 2. andi *3702,`Homewood-' Rd!. `.Cm-- .'.''St.', Evansville ll;'Indv ^ . .. r dnnati 27, Ohio. ; ... t/- - W,\! 48 :Heating Ventilating. .Ate -Conditioning , Giiide['I946 . KUGEX. H. Kenneth (if'1938) Chief Engr., LAMBERT, Everett C. (A 1944) Air Cond. & . Smoke Regulation & Boiler Inspection, 102 Dis-' Ind. Refrig. Supvsr., Westmghouse Electric Corp.,. . - trict Bldg., Washington- 4, and #3825 Morrison 3001 Walnut St.-,-Philadelphia, and *7433, Over- - .St. N.W., Washington 15, D. C.* :V lull Rd.. Melrose Park, Philadelphia 26, Pay i . KUGELER; H. Coots (if 1944) Application Engr., LAMMONS,. John B. (A 1944) Sales Repr., , ' - The Stearns Roger Manufacturing Co., 1720 J. B. Lammons, P. O. Box 502, and 930 N. . ' . California :St., Denver 2,. and #2365 Ash St., Evergreen St.. Memphis, Tehn." -' -' Denver 7, Colo. ' ' ' LAMONTAGNE. A.' F. (A 1936) Sales >Mgr.. KUGLIN, Charles R. (if 1945) Chief Mech. ' Gurney Foundry Coli.Xtd., 100 Principal St., Engr., Montgomery Ward & Co.. 619 W. Chicago SL Laurent, and 5040 Victoria Ave., Montreal, Ave., Chicago, and #10207 S. Wood SL, Chicago : Que., Canada. . 43.IU. LAMSON, Frank S. (if 1945) Sole Owner, F. S. , . KUHLMANN, Rudolf (if 1928) Mgr., Ameres- Lamson Co., 926 Marquette, Minneapolis 2, and . co'., Inc., 50 Church St., New York, and Glenwood 2700 Colfax Ave. S.`. Minneapolis 8. Minn. ' " 'Gardens. Yonkers; N. V; - . LANDAU, Mitchel (M 1937) Mgr.. Heating Div., KUHN; William Hubert (Af. 1944) Owner. *W. Allied Appliance Co., Ill -Berkeley St., Boston - /.; - H.'Kuhri. 320 Olive St., Dallas 2, and7llSldllman, 16, and 61 Beaumont St., Dorchester 22. Mass. . ' Dallas. Texas. . . . LANDAUER, Leo L. (if 1938; J 1932) Lt. -- KUMMER,-Calvin J. (A 1942; 7 1938) Major. Comdr., U. S.-N. R.. Bureau of Ships, Navy : Cl S. Army, 0^18702, A. P. O. 235, c/o Post Dept., and 3426-l6th St. N.W., Apt. 106N, . . master. Sail>-Francisco, Calif., and# c/o John . Washington; D. C. - . - . :~:-Kummer; R. R. 7, Box-114, Louisville 9, Ky. . LANDERS,- David N. (A -1944) Owner, Landers .. --KUNEN, Herbert K. (A 1946; 7 1938) Lt. (j.g.), Plumbing & Heating Co.,.241-Marietta St. N.W., >' ' Fighting Squadfon'_19,' c/o-F. P. O.,-San Atlanta 3. and 56--26th N.W.. Atlanta,-Ga. - - Francisco,'Calif., and 139-06 Pershing Crescent, LANDERS, John J. (if 1932) Landers Engi- - Jamaica 2.-N. Y. ' neering Co., 170 Franklin SL. Buffalo, and 120- ^ KUNTZ, Edward C. (7 1937) Htg. Engr.. Ham Burrougha Dr., Snyder, N. Y'. - . . . mond Sheet Metal Co.,.119 Cass Ave., and 6516a LANDES. Bates E. (if 1938) Cons. Engr., 722 : ` Morganford Rd., St. Louis -16, Mo. . - Old Colony Bldg.. Des Moines 9. aind 1603-47th r KUNZOG, Theodore W, (if 1939) Sales Engr., St., Des Moines 10, Iowa. "' ' " - . - --'Moraine Products Div., 1420 Wisconsin Blvd., LANDFRIED, Charles L. (if 1942) Prof. Engr.. .. ' . and 115. Wisteria Dr., Dayton 9. Ohio.. Air Cond., and 40-19B--194th St.r Flushing. N:Y. " - KURTH, Franz B. (7 1945) Liaison' Engr.. LANGAN, James (S 1943) Lt., U; S. Army, and . . ''Anemostat Corp.; of America,. 10 East 39 St., - *508 Fernbill Ave., Pittsburgh 26, Pa. . '' ' y.- New York. N. Y,, ahdV62; Cortland St.,' West LANGBERG, Martin (A" 1941) Engr., Carroll . -Hartford. Conn. -' ... - . Sheet Metal Works, 4610-70th SL. Winfield, and - .KURTH, Franz*J.`(Af 1937) Vice-Pres., Anemo- *51 Blossom Heath Ave., Lynbrook, N. Y. ' stat. Corporation of America, 10 East 39th St., LANGDON, Edwin H; (if 1941) Owner, .. ,. --New York,' and 510' Corttandf Ave., Mamarb- - Langdon Co-, 966 Dexter-Horton Bldg., Seattle : - neck. N. Y; -. - ' . .- * 4, and 426 W. Roy St^ Seattle 99, Wash/ -: V - KURTZ,'Otto (if 1941) Cons.- Engr.,' Plumbing LANGDON, Tom C. (J 1943) Owner, T. C.; . Heating^Ventilating-Electric. #3518- Grove <St.. Langdon Co.. 613 S.E. Moirison St.." Portland 14, , ' Oakland 9, Calif. ' ' and 1910 N.E. Weidler St., Portlahd-12. Ore. : ' . KURTZ, Robert W. (A; 1948; 7 1936) Major. LANGE, Clifford C. (A 1944) Mgr., Western Ordnance;Dept., U. S. Army, Illinois Ordnance. Boiler & Machinery Co., 910 S. Arizona St.. " - . Plant. Carbqndale, III., and c/o American Con-. - Butte, MonL .' ._ V' ,'-- -striiction.Co., Rusk Bldg., Houston. Texas. : :;KUTTLER, John Bi (if 1944) Chief Engr., . . Prudential Insurance. Co.. of ** America,..-763 .- ' Broad St., Newark, and 642 Scotch Plains Ave., Westfield, N.J.V ... .- LANGE, Fred F. (A 1934) Pres., *The Mechanical ' . Service Co.. 809 Pence Bldg., Minneapolis, and ' - 510 Fourth Ave. S.W;i Faribault, Minn. ' V LANGE, Raymond T. (if 1936) Project Engr.. . Axial Flow Fan Designs, Lear Avia, Inc., and 224 > ' Jackson SL, Piqua, Ohio. . - .- KWAN, L K. (Af 1933) Gen. Mgr;, The .China . LANKTON, Forest E. (A 1945)' Engr., Olds- - Engineering Co., 30 Brehan Rd., Shanghai, China. .`mobile,- Lansing 21/ and 816 -Gordon, Lansing' - . , /; -10, Mich.'' - ` . '` ` -- . LANOU.J. Ernest (if 1931) Mgr., F. S. Lanou . - & Son, 90 SL Paul St., and 48 Brookes Ave.,* * LABADIE, William (A-1944) Gen.. Supt., Uni- .Burlington, Vt. ` ` . *' - . : K. . :`.versal_Plumbing & Heating Co., Ltd., 980 Queen ~ ,St. E/. and #18 Kingsmount Park Rd.; Toronto,' . Canada.' , > - LARIMER,'William M. (if. 1944) Mgr.. Htg. . .. Dept., Crane - O'Fallo'n Co., 1631-15th St.; Denver 17, and 123 S. Pennsylvania St.,- Denver- . LABONNE, Henri P. (A 1940) Major,. Canadian ' 9. Colo, ; : ...... ' .'Army, and 64 B.' Brooks St., Sherbrooke, Que., \ LaROI, George H., II (A 1942; J 1936) -Elec. . :: v Canada;-' v -l" - -, ' " j'Engr. &.Adv. Mgr.. McDonnell & Miller.TRm.. :" VLADD/David (if 1938) Comdr., U.S.N. R., and ' 1316,-Wrigley Bldg., Chicago 11, .and *313, S. ' *305 Wadsworth Ave;, Philadelphia 19,'Pa. ' - George SL,- ML ProspecL IU. -. `' ' - LADEWI.G, :Larry L.*.(A-1944) Mgr., Utilization LaROW, Leo (Af 1945). Indus. Gas Engr-.. ;. -DepL.-* Houston Natural Gas Corp., Box 1188, . Central New-.York Power Corp.", 258 Genesee' ; . .. Houston 1/arid'1306-Crocker, Houston 6, Texas. /SL, and 180 Proctor Blvd.,-Utica, N.:Y. -- LAGODZlNSKI. Harry J. (A 1927; 7.1920) Sales LARSON, Carl W, (if .1936) Htg. Engr. & Sales . - ,'Eugr.. #Ilg. Electric^ Ventilating Co., 222 N. Repr.. Barnes & Jones,. Inc.-, -128 Brookside Ave.. ' LaSalle St., Chicago, and.Crystal Lake, I1L ` _ Jamaica Plain 30, arid 184 Sycamore St., RosUn-, - ` '.' LAINSON,: Hal _(A; 1944) Secy.-Treas., Jaden ; ;- ManufacturingvCo., and. 229 University Blvd:, / Hastihgs,!Nebr.' .' . ' LARSON,^ Clifford(A 1939; J 1936) W`O-.' : 1 (j.g.),. Dir. of Personnel, M. j. S. L, _S., Fort f-^ UAIR, Paul H. .(if-1940) Indus. Engr..Storie & - Snelling, Minn. -' : . l . Webster.- Engineering Xorp., 49 . Federal St.,' LARSON, G. L,* (if 1923). (Presidential Member), . '... Boston,' and 60 Dwhinda Rd., Waban, Mass.- (Pres.. 1936; 1st Vice-Pres.. 1935:2nd Vice-Pres... -: Wing-Ching (,7 1945) Jr. Engr:, Carrier . 1934; Council. 1929-37) Prof. of .Mech., Engrg., e Gori>.,?300 S.XGeddes St., Syracuse, and #528 . .University .of: Wisconsin,,' Mechanical Engi- ' W}-<IrM' > '-/- Riverside Dr.vApt. 1C, New York 27. N. Y. - - - neering -BIdg., Madison 5, and 1213 Sweetbriar ' '//.LAMBECK,. Walter N. (A* 1945) Service Mgr.. ; ` Rd.*, Shorewood Hills, Madison, Wis. . ' Sales Engr.,';# Wisconsin*- Ice & Coal Co;, 1518 E. LaRUE, Perry .(if `1938)'. Dir.,-. Bldgs. & Grounds ^ v-`; '.`.North Ave:/ Milwaukee 2, and" 1136 North'29th , DepL, Independent' School District, 629, Third.'* - ^ Milwaukee 8,; Wisi - ,%./ ' . SL, Des Moines 9, and 132I-43rd SL, Des Moines'.- ' V-^LAMBERT, Edwaxd .Gr'(A -1945).Mgr., Building Iowa. *- ' -" .. . , Maintenance" Service, `Inc.,- 810 S. St. Paul. and - LaSALVIA, James J. .(if ;1930) Dir.-i Chief ^-^-yJ^lTfS.'Raviiiia.Dallas,.Texas.' v . - Engr., The 0boro\Engineeruig--Co.,'CIeveland.` - ,^r..^ixi^jfAMBERT;:`Edward H-. (A 1944) * A. C. Sales,. - arid2515-Eatori Rd., University Heights,.Ohio. r--^ Jtv/Iric?, 55'-WesX42nd St.,; Km.. 669, New. York 18, ' LASETER, Frank L.,(if 1938)' 1st LL. C/of E.I : p^^;=^.-frN;;Y:rand 8512'Haxelwood Dr.,'Bethesda, Md. and *.14 CapitoLPlcwy., Montgomery/.Ala./, . 5 Roll of Membership LASHLEY,. Walter L., Jr. (7 1943) 2nd LL,' LEE, Robert J. (if-194l)rLL (j-g.). U. S. N. R" . Co. B-94, O. C. Bn., Fort Belvoir, Va.. and 1244 623 Font'Blvd., Parkmerced, San'Francisco 12, V Wellesley Dr., Ml Clemens,.Mich. , - - - Calif., and'2356-77th-Ave., Philadelphia 38,.Pa. - - LASLEY, James .B. (A 1944) AssL-Foreman in LEE, Robert-T. _(A 1946: 7 1937.; 3-1936) Chief ; charge of-Power, Plant Engineer's DepL, North - * Engr., Charlotte War Products . Pool, Box 59,- .Carolina Shipbuilding Co., and #2 Jackson Dr., Charlotte 1, N. Cl, and #P. O. Box' 164, Lynch Wilmington, N. C. ,' - burg, Va. ' ' LATHERS, -Victor M. (A 1945). Sales Engr., LEEK, Charles W. (if 1938) Managing Dir.-.:. BarberiColman Co., and 2409 Oxford St.; Rock ford, IU. Leek & Co.; Ltd., 1111 Homer SL, and *4682 W. Sixth Ave., Vancouver, B. C., Canada. - -. ' ' LATTERNER, Henry, Jr. (A 1945; 7 1940) Prod. LEEK,* .Walter (Life Member; if 1903) . Pres:, , " Mgr., -Falge Engineering Service, 4908 Hampden Leek & Co.. Ltd., 1111 Homer SL, and 4769' ' 'Lane, -Bethesda, Md., and 3600 Macomb St. W. Second Ave., Vancouver, B. C:, Canada. . N.W;, Washington, D. C. . LEES, John (A 1944) Engr., Board of Education,-r ` `LAUBE, H. L. (if 1943) Carrier Corp., Syracuse, Broadway, DetroiL and 16801 Freeland Ave./ : and 412 Sedgwick Dr., Syracuse 6, N. Y. Detroit 27, Mich; '. `` ' LAUER, Rodney F. (if 1941; A 1940; 7 1936) . LEESE, Milton L. (A 1945) Sales Engr., A-l . Dist. Mgr., York CorpM 5051 Santa Fe Ave., Los - Industrial Equipment, 1202 Frankford - Ave., Angeles 11. and 2645 Lorain Rd.. San Marino 9,, Philadelphia 25, and #2044 S. Redfield St:,' .Calif. >- , . ` Philadelphia 43, Pa." . - " ." - LAUFKETTER, F. C. (M 1936) Retired, and . LEFEBVRE, Eugene J. (if. 1937) Engr.. Warden . 7Q56 W. Park Ave., SL Louis, Mo. . . King,-Ltd., 2104 Bennett Ave,, Montreal, and ' . .v LAUTERBACH, Henry, Jr. (if 1935) Contract #378 Wood Ave., Westmount, Que., Canada. * * - Engr., Carrier Corp., 20 N. Wacker Dr., Chicago - LEFFEL, Paul C. (A 1941) Owner. #The Leffel 6/ and `6959 S. MerriU Ave.. Chicago 49, IU. . ' Co., 3323 Main, Kansas City 2, and 316' East ` LAUTZ, Fritz A. (if 1936)`-Maintenarice Engr., . * 75th SL, Kansas City, Mo. . ,, ; .. - -American Bemberg Corp., Elizabethton, and.. LEGLER, Frederick W. (M 1035j A 19*) Pres.,:. . ' R. F. D. 1, Johnson City, Tenn. . ' - The Waterbury Co., 17 West 28th SL, and 2919 . LAVELLE, Anthony E. (A 1942) Vice-Pres., Johnson SL N.E., Minneapolis, Minn. . The Gorman-LaveUe Plumbing & Heating Co.. LEHMAN; Max G. (A 1937) Owner, #M. G._ 2341 East 22nd SL. Cleveland 15. Ohio. Lehman, 720 O St., and 3225 W. Pershing Rd., - LAVORGNA, Michael L. (if 1941; A 1940) Mgr.,. ' Lincoln, Nebr. . . *. Milwaukee Sales, L._ j. Mueller Furnace Go., LEIBY, Robert s:' (A 1944) Owner & Mgr., 2005 W: Oklahoma Ave.. Milwaukee 7, and 4472 . #.Robert S. Leiby Sheet Metal Co., 212-N. Grant ` N. Murray Ave., Milwaukee 11, Wis. . . Ave., Columbus, and 6870 Havens-Corners Rd., LAWLESS, - Albert .J. . (if 1945) --Partner, New Albany, Ohio.' - _ . Hubbard, Rickerd - & Blakeley, 110 W.hitney LEICHNITZ, Robert W. (A 1944; 7 1936) Ave., New Haven, and 25 Patton SL, Hamden,- ' Installation- Supvsr.. Leichmtz-Bibb, Inc., and Conn.-- ` -i . - 2506 W. ChestnuL Yakima, Wash. *- LAWLOR, John J. (if 1935) Mgr., Heating Div.,` LEILICH, Roger L. (if 1922) Pres., *The Wallace - The James Robertson Co.. Ltd., 215 Spadina Ave.,* and 60 Armadale Ave., Toronto, Ont., Stebbins Co., 100 S. Charles SL. Baltimore 1, and. - .Ruxton, Baltimore Co., Md. - ' Canada. . . LEINROTH, J. P. (if 1929) Gen. Indus.- Fuel ' . LAWRENCE, Chester T. (A 1940) Branch Mgr., Repr., Public Service Electric & Gas Co.,- 80 U. S;``Radiator Corp., 1318 Marquette Ave... - Park PI., Newark, and 37 The Fairway, Mont- ` - Minneapolis,' and *5213 Washburn Ave. S.,, dair, N. J. ' 'r Minneapolis 10, Minn. - ' .. . LEITGH, Arthur S. (if 1908) Pres. & Managing - LAWRENCE, Floyd D, (A 1938) Field Repr:', Dir., The Arthur S. Leitch Co.. Ltd., 1123.Bay' - . ` Clarage Fan Co.,'500 Fifth Ave., Rm. 1024,. -New York 18, N. Y., and 60 Gardiner SL, Noroton Heights, Conn. ' - ` ' - ' ' ' LAWRENCE, John F. (A 1945; 7 1944) Engr., Designer. P. O. Box 127, Tomah, and 130 S.- St., Toronto 5, and #421 Russel Hill Rd,, Torontot 12. Ont., Canada. .- * LEITCH, Kelvin D. (M 1944) Treas.. Arthur S. . Leitch Co., Ltd., 1123 Bay St., and *91/ Higb- ; ` bourne Rd.`, Toronto, OnL, Canada. - * . - LEITGABEL, Kenneth A. (7 1941; 5 1939) Htg.' Eighth St., LaCrosse, Wis.' - ' Contr.,. A. F. Leitgabel & Son. Elm Grove, and LAWRENCE, L. Frank, Jr. (if-1942; 7 1938) < #2320 North 58th St., Milwaukee 10, Wis. > ' ' Branch - Engr., Minneapolis-Honeywell Regu- ' LELAND, Warren B. (if 1929) 45Q9 Four Mile . lator Co., 4-5 N. Rhodes Center N.W., and-796 Run Dr., Arlington. Va.' -. . Amsterdam Ave.* N.E., Atlanta.'Ga. - ' LENIHAN, William O. (A 1936) Vice-Pres.. LAWS, Charles W. (if 1944) Owner, Laws Engi Laverack. & Haines, Inc., 718 -White- Bldg.,' -' neering Service. 1120 Rapid St., and P. O. Box Buffalo 2, and-#703 W. FerrySL, Buffalo 9, N.Y. 1628. Rapid City. S. D. * ' , LENONE, Jose' M. (if. 1938) Designing Engr., '.. LAYTON, J. William (if 1945) Chief Engr., ' Wilson & Co., 4100 S. Ashland Ave., Chicago 9. - Propellair, Inc., 1345 Lagonda Ave., Springfield: and 4932 Lake Park Ave., Chicago 15, 111. .' ~ -- ' and *200 E. Hebble Ave., Osborn, Ohio. .. LENZ, Alfred W. (A 1945) Partner, JohnsonrLenz / LEAS, -Nat N. (A 1943) Part Owner & Mgr., ' Heating & Piping Contractors, 336 Court St., . _ Conditioned Air & Refrigeration Co.. 249 North and 237 E. Edwin Circle/ Memphis. Tenn. ' H SL.. Fresno'3, and 3912 Batch* Ave., Fresno 2. Calif. . ' . .* . LEONARD. Lorcan C. G. (A 1945; 7 1937) TechMgr.-,- Messrs. McCann. Ltd., 19-20. Ellis Quay, - .... LECUREUX, E. (A 1943) Pres. & Mgr., Auto-, 94-SL Lawrence Rd:, Chapelizod Co., .Dublin, -matic Gas Co.. P. O. Box 29, Athens'. Ala. * ` . . Ireland. ' s . LEDBETTER, NorveU C. (if 1944) Partner, LEONHARD, Lee W. (M 1936) Asst.. Siipt:. Automatic Heating & Service Co., 22 S. Cooper Eastman "Kodak Co./ Kodak Pk.,-Rochester, and - St.. Memphis 4, and 1935 Nelson Aye., Memphis, . `.*1075 Winona Blvd.-, Rochester 12, N.W. ' Tenn. .... *'..' LEOPOLD, Charles S.'* (Af 1934)/'Cons.-Engr.,; LEE, Boyd J. (A 1945) Owner, B. J. Lee Co.,' - 213 S. Broad SL, -Philadelphia 7,. and 7600' ; 236 Adams Ave., ' Memphis 3, and 1674 Faxon ` West Ave.,-EJkins Park, Pa. -' . Ave., Memphis, Tenn. ** -. LeRICHE, Raymond E. (A 1941)- Application, LEE. Burton H. (if 1945; A 1940) Chief Engr.> Engr., Fisher Governor, Vance Bldg., Seattle, . Mance Corp., 400 W/ Broadway, New York'12, * and 6345-39th S.W;, SeatUe.6, Wash. / '' and-50 Mohican Park Ave., Dobbs Ferry, N. -Y. . LESER, Fred A. , (if 1941; A 1937) DisL .Mgr.r - LEE, Carl M. (A 1944) Foreman, Air Cond.- Dept.,. -* -#Ilg Electric Ventilating Co., 608 Mills ' Bldg;; " ; Allison Div., General Motors Corp.. Plant'No.'5, * ' -17th and Penn Aves. 'N.W./ Washington 6, and. - Tibbs and Raymond St.,*Indianapolis, and *4506 - 7201 Cobalt Rd.. Wood Acres, Md., and Wash: .< Farnsworth SL, Indianapolis 3, ImL\ . - . ington 16, D. C. .. -f . . . . .'* LEE, James A. (if 1943; A 1937) Dir. of Purcha^- - LESSINGER, Edgar'F. (A. 1941) Owner,*Les- . ing,-Nash Motors Div., Nash Kelvinator Corp.,' ... singer:Plumbing Sc'Heating Co^.221 South 10th- arid 7301 Fifth' Ave., Kenosha, Wis. - ' St.; arid 814.North 18th SL. -Boise,.Idaho. . LEE, Lester A, (A 1945) Mgr., American Radi .`LESTER', E. Archer'(A 1944) Asst, to Mgr./. - ator & Standard Sanitary Corp.: 14430 Dexter, . Crane Co., 333 W. Market St., arid 6223 .Wash- - > ' " Detroit 6, and 14225 Greenview, Detroit 23, Mich. ington Blvd., Indianapolis, Ind.- .. ? mm\ 50 r ' Heating. , Ventilating . Air;,^Conditioning Guide' 1946' :{, -LESTER,' william L. G. (Af. 1944) Vice-Pres.; LIGHT, John C. (A 1938) Major. Ord./ DepL, : .`Abbott`Lester & Go.* Inc-,. 140 Cedar SC, New and 3004 Alamogordo SL,. El Paso; Texas/ - ' /; York, N.-Y./and 58 Whitney Rd.;-Short Hills, - LILJA, Oscar L. {M 1943; A 1937;. J 1936) Asst. "N.-J;,. '\ - . . v. / Mech. Engr., Toltz, King &' Day, .Inc.,--1509. . ..LETT,. Mai A: (Af 1945)' Mech. Engr.. *601 Pioneer Bldg.. SL-PauI'l, and * 50(K>-l6th Ave. . -/'Michigan Trust Bldg.; Grand Rapids 2, and.llll 1 . S., Minneapolis 71 Minn.- . f '.-Walsh St. S.E;. Grand'Rapids 7/ Mich.- LIMBACHER, Howard-R. (M 1943) ' Research ' > . LEUPOLD, George L. (A .1937) CapL,-Meteoro- - Engr., IngersoII Steel & Disc Div., Borg-Warner ",-"sIogical''Div., eRipley-Bidg.. 429 N. Main SL. Corp., 763 E. Vine/St.; and 525 Edgemoor Ave., ' .'and 8760-Ridge Ave.. Dayton. Ohio. Kalamazoo, Mich. ' -. - LEUTHESSER, Fred W.. Jr. (Af 1937) Secy.. LINCOLN, Roland L. (M 1935) Mgr.. Dust;Lab.. ... National-Metal Products Corp..-21 N. Loomis B. F. Sturtevant Co.. Hyde Park 36, Boston, and ? - SL; Chicago 7, and 1715 North 77th CL, Elmwood . Box-97. Dover, Mass.. ' ' - " ;- ' - . ` Park, 111.' -. . - LINDSAY. Griffith. W. {M 1937) Supvsr. of , / LEVERIDGE, Robert H/ (7 1945) Jr. Engr., Estimating , & Time 'Study. Chrysler' Corp.,' Carrier. Corp., 405 Lexington A've., New York 17. Airtemp Div.,- Dayton, and.*301N. Garland Ave., -.' .arid 136 Prirk Ave., Tuckahoe 7, N. Y. ` Dayton 3. Ohio. ` - . '' j, . . / LEVINE. Charles (A 1943;.J 1939) Refrig. & Air LINDSLEY, Forrest A. (A 1943) Sales &.Service - ./' 'Cond. Mechanic. New York Navy Yard. Brooklyn. '. Engr., Crane Co., 150 Randolph. Detroit:.26,-and '. and-*1171 Ocean Pkway., Brooklyn 30.- N. Y. - ` 151 University Ave./. Ferndale 20, Michi ' ' . ; - LEVINE,' Lawrence J. (A 1946; 7 1940) Ensign, LINDSTROM, Alvin L. (M 1945) Cons. Mech;: U--S."Navy, and 1378 East. 12th,St.,' Brook- Engr., *1001 Mortgage Guarantee Bldg.,-AUantaV W-` lyn; N. Y.. ` .` -. 3.-and 1272.StilIwood Dr. N.Ert Atlanta; Ga: ' ; - vX},LEVITT; Leroy.L. (A:1942;7 1940) LL. U.S.N.R/. LINDSTROM, Donald F. (A 1946; J 1941) Mech. / ' `.`. and 3326'Gwynns Falla Pkwy.. Baltimore'.' Md;' Engr..& Owner. *605 Mortgage Guarantee Bldg.,, ` /.LEVY, Marion I. (Af 1938; A. 1936; 7 1931) Pres..' Atlanta 3. and 1259'N. Highland Ave. N.E;; ,,. -/Viking Air' Conditioning Corp., 5600 Walworth ' ` Atlanta. Ga. .. ' ' -- Ave/ Cleveland 2, Ohio. . . ` .. LINGEN, Ralph A. (A 1939-..J 1938).Dist. Mgr.. ' LEWIS/vCarroll E../(Af- 1930) Vice-Pres., The American Foundry & Furnace Co., 709 North * 'v, Perfex .Corp., 500 W. Oklahoma, and 5108 N. '11th SL. Milwaukee, and.6028 W. Wisconsin-. \. Woodbum Ave., Milwaukee 11, Wis. '" ; ' Ave., Wauwatosa,'Wis. . , ". A* LEWIS;-.-Daniel' H/ (A 1944) - Owner. Lewis LINK. Charles H. (S '1941) Unk .Co/v 414 N/ ' Engineering Service,'-19003 John Ri and 17334 .' Blackstone, and *607)4 W. -Franklin-St.', Jack-. -' John R. Detroit 3. Mich. - ... . ' - son. Mich. . - j\ ^ ./LEWIS,-Gelder V; ;(Af 1944) Pfc., U. S. M. C..r LINSENMEYER, F; J,. (M 1944) * Hoffman / ' /`KM.. Co./ 3rd, Bat., 22nd` Marines, 6th- Div., ` -Combustion Engineering Co.; .710 'Marquette /c/o F. P. O.; San Francisco, Calif.,- and c/o John. Bldg/ and 19020 Warrington Dr.'.- Detroit.'Mich. --,G. Lewis,' Plumbing & Heating-. Co., 412 East LINSKIE, . George A. (A 1946; J 1939) Mech. /' ":31st St.,-Kansas-City 2, Mo. . - Engr., 2400 S. Harwood SLv and *3124 Milton- . -j, LEWIS, Harry E.: (A 1942; J1939) Mech. Engr... SL, Dallas, Texas. ' ^.' - . - ' -Owens-Coming Fiberglaa Corp-. Nicholas. Bldg., LINTON, John P. (M 1927) Pres.. Engineering ' Toledo 1,- and *1320 Craigwood Rd;, Toledo- Installations';' Ltd... 1154 Beaver Hall Sq.. Mont . r 12.'Ohio.............. . - real. and 247 Brock Ave; N., Montreal W.. Que.y. / . -.LEWIS, Herald F. (Af 1940; A 1937) .Major. , Canada; ' -. "j -. ^ . ' *" . Infantry, .Commanding HQ Co., E; D. C., . LIPSCOMBE, Harold'W. J. (M 1938) Mgr.'. Air -/-'* Governors Island. N. Y.. -. -- Cond. DepL. Davidson' & Co;.. Ltd.. .Central / LEWIS,-J. C. (A 1944) Dist. Mgr.; Drayer- House.' Kingsway, London.' and "Glemnore," ' ' Hanson, 4914-Linden, Bellaire, Texas. . ' - Woodland Way. West Wickham. KenL England. LEWIS; John G.` (Af 1943) Pres.. John G. Lewis -'Plumbing &.Heating Co., Inc- 412 East 31st St., and 3643 Charlotte SL. Kansas City, Mo. . ; ^LEWIS," L:r- L.* (Af .1918) Vice-Pres.-. Carrier LITTLE, Herbert jJU 1945)"Asst. Dvfpt, Engr., * Anglo-Iranian Oil Co., Abadan, Iran. - . , LITTLE. Kenneth B. (A 1943) Owner, 'Kenneth' Corp.-, S. Geddes St.; Syracuse 1. andJ207 Sedg- - rv: -,:wick Dr.', Syracuse'3, N. Y. /. -. - B. Little Co.,' 832 Temple Bar Bldg., Cincinnati 2, Ohio. ' - ' - -' . r-/LEWIS, S. David (A. 1945) Mgr., Westinghouse. LITTLE, Raymond (M1944; A 1943) Genr Sales - `Electric Elevator Co., 842-. Rockefeller. Bldg., , ..Mgr*, Eauitable Gas Co., 120 Cecil Way, Duquesne 'Cleveland 13, and.. 114 Park Lane Villa;.Cleve- Bldg.. Pittsburgh ; 19, and 81 Roycroft- Ave.,'. /^.flahd^.'Ohio; `` -/ ' - , * Pittsburgh 16, Pa.v , :.1 / ". ' / ... '. LEWIS,'.-:Samuel. R.* (Life Member; M '1905).' LITTLE, Verrion R. (A 1944) Chief Steam Engr..- * /./-'(Presidential Member), - (Pres., 1914; "2nd Viee- . 'Curtiso-Wright Corp.,-4500 E.'Fifth'-Ave.; and Z/Z-Pres.-, 1910;Board of Governors. 1909-12; Council. - 1456 Fair Ave., Columbus, Ohio. 1914-15); Cons. Engr., lOOW. Monroe SL, Chi- .LITTLEFORD, Wallace H. {M 1936) Vice-Pres.. cagO'3i,aha.4737"Kimbark-Ave., Chicago, 111.-' ' *'E. J; Febrey & .Co.,. Inc., 616'New., York. Ave. . sv. rLEWIS,` VeIma I.VMrs; (A 1943) Htg. & Combus. N:W., Washington, D. C., and'5703--36th Ave., Engrg', * q/o Major Herald Lewis.- Hq/ Eastern' Hyattsville, Md.` . - .; -:>/ Defense'Command; Governors Island. N.-Y. . LIVAUDAIS, Marcel {M 1945)' Chief Draftsman^' fi--ZLEYv Ralph B;` (A -1940) Chief. Assignment Sect.. . . . & Mech- Engr,, ~Headquarters 8th Naval Dirt./ ^T'V'Cbrps'of.Eng.:War DepL;-23rd andC Sts. N.W.,' .1015/ Federal '-Bldg..' New Orleans, and-*319_ ,,> `Washington,-/D/-C:. and 916 Park Ave.. Falls Audubon'SL, New Orleans 18, La... : `- . / Church;-Va. '. '. r -. ' ' LIVELY. George P.` {M '.1942) Principal' Engr. - - .... ^ . /L'HOMMEDIEU; Curtiss L. .(M 1944) Htg.. ' . (N.A.),. Bur^u of Ships, Navy. Dept'... and *818 I . VehL-;-&. Fire' Protection -'Engr., Foskett & (i':Bishop Go.;.76'Blatchley Ave.;' New Haven, vand'. J:./; -/-C:Riimnon Rd^. Woqdbridge, Conn. ' /. . V *.^'LIBBY, Ralph S. (A 1939; J 1933) Sales Engr.. . /h t iSheidonsi' jLtd96 Grand Ave.r and 34 ' Elliott -`"-'St.,' Gait,"Ont., Canada. ` ` r ` /i-^LICANDRO, James P. (A: 1943;:J-1938) Branch' <^-' Engr'?.>.'419 Boyliton St.,- Rm. 624. Boston; and/ ^ * "s:r40'Elm,SL, StoneKam 80,-Mass. ' - ' ' -' S. Pitt St..-Alexandria;-Va.'-..' . - LIVERMORE. Jam^N.* (M 1939) Mech. Engr./, The-Detroit Edison .Co:; 2000 Second- Ave.. / Detroit' 26, -and 5 Hanover-Rd.; Pleasant Ridge, ' Mich.. .. - ,- - % - LIX-KLETT, Lula {A-1944) Chief . Engr. & Dir..: ' *Carricr Lix-KletL S; A;r Florida-229, Buen6s - Aires.-Argentina; S. A.*'--' "", - - ` ; V '* -.,,LICHTY. C. P. {Life* Member'; M 1920) C. P. LLOYD.' Edmund H. (A 1943; J: 1936) Capt.'. . '"Engineering' Co.: Salina . Hall, W. V., . ..-,A. U.'S. (C.E.), Office,-Chief:.of Ehgrs:,.Repairs. -. ^r/noUPW^ .T^nn^ nH m^ .RiHpp RH Birmi 'and- Utilities.- Br'.,' New War Bldg.;. 21st .'and. m . :*?fiaih; Ala.:'.. . . . .. . . Virginia Ave.', .and 2614-3f^lLSL N;W..srWash-- -LIEBLlCHr-Murray V 1943; 1940) : Htg. ington,-.D.'C.".'- ^V-Rngf/H/Oehlirh & Col. 36'West 66th St.'.'and - ' LLOYD, Edward/C., (M 1927) .Armstrong Cork, -v "'' CehtraKHotel. Ne'w-York. N/Y. - ' .Co.. and.*R, D. 5,'.01d Philadelphia Pike: Lah-'- caster; Pa'. '-*>' ' ' '7' , '^m.LOBSTEIN, Meiville C.'(Af 1941) Chief Engr.. ' :`Museum-of- Science'& Industry. 57th SL and-' . Outer Dr., 'Chicago .37, - and 140l.S." Highland - . Ave., Berwyn.'111:.' /' ' ' .'v ;*./ RollofMerntership ^.: ; 'i 51,. -/-'4"v LOCHER,' Davld-E. ,{M -1945i'Pres.' &T-Mgr^ / LOWNSBERY, B/F/(Af 1920) Purchasing Engr., / - - / -t* Coolidge-Lochef Coi; Box 949; 224 S.' Staples ; Benjamin-F. Shaw.Co., 501>E/ Second St., and ` - ..' SL.'.and 215 El OleanSer" SL, Corpus Christ!,- '21 S. Sycamore SL, .Wilmington; Del. .' - /' ' . * - -Texas. , i -.v'""-- ,, LUBKING, Charles J. (Af .1944) Sales Engr.. ` LOCHMAN, Edward W. (Jf 1942) Owner & Mgr.. / *' -. Minneapolia-Honeywell Regulator 'Co., 5060.- ,- - ' Edward W. -Lochman Co.,^-1421 Cherry SL,:- Wayne'Ave.. Philadelphia, and 2755-N1 Dover". . . - and-634 East 73rd-Terrace, Kansas City; Mo.! St., Phiiadelphia32,-Pa. . .. -v - ." ' .. LOCK,.Rowland H. {M 1939) Vice-Pres. & Gen. LUCK, Alexander W. - {Life Member; M 1919) - . ' r - Mgr., J; H. Lock Sons, Ltd:,' 221 Sterling Htg/Engr., *532 Woodward St., and Wyomissing'?"- '/ .. - ' ,. . Rd.. and 36 Kennedy Park Rd:, Toronto, Ont.. ' Canada., - - ' LOCKE, Charles F. A. (M ,1944) Branch'Mgr.. v Minneapolis-Honeywell Regulator Co.. 1007 ' N.-Meridan SL. Indianapolis 4, and 4775, Park Club; Fifth and Walnut Sts., Reading; Pa., .-* . LUCKE, Charles E. {Life Member; Af 1924) Prof. - . Emeritus of Mech. Engrg.. Columbia University/ '. . Pupin Bldg., New York'27, and T 86 Riverside - . ' Dr.. New York 24, N. Y. .. , - ; . ' -'Ave;,-Indianapolis 5, Ind.- ' LUDLOW, Harold M. (Af 1940) Sales. & Engrg., 7 ' : LOCKE, James S. (Af 1939)1 Midwestern Mgr., - H. M. Ludlow, P. O. Box-1368, Jackson lll, Air,Cond.' Controls Div., Mianeapolis-Honeywell: and 950 Pecan Blvd., Jackson, Miss.. ,, :' 'Regulator Co..'433.E. Erie St.. Chicago, and ! LUDWIG, WUUs D. {M1942) Construction Engr.. / . ' ' ' - . 1828 Fairview Ave. S., Park Ridge.-Ul.. ' ^ ;York Corp., 1238 North-44th St/ Philadelphia .' 7* LOCKE, Robert A. (Af 1935) Comdr;. U. S. N. R,, 4, and 95 Wynnedale Rd./ Narberth, Pa. - * */. Naval Inspector , of Ordnance, - Philadelphia ,40, LUEDECKE, William H. -'(A. 1946) Applica. - ' v ' and *305 Brentford Rd:,'.Haverford, Pa.- * . Engr.. Air Conditioning. Dept., Westinghouse - VLOCKHART, Harold': A: (Af 1944; A . 1936; -Electric Corp.. 405-N.'Griffin St., Dallas 2, and' ` . J 1935) Chief Engr.. Bell & .Gortett Co., Morton 3012 Kingston^L, Dallas 11,-Texas. .- ; Grove, and Box 5385, R. R. 2, Des PlainesMIl. .. LUMM, Albert H,, Jr. {J 1944) Chief; Engr..; : LOCKWOOD,' James R. (A .1944) Supervising *A; H. Lumm Co.; 2512 Albion St., and 2517:/ . ' . - . .'Mech/. Engr., Familian Pipe . & Supply . Co., - Montebello Rd.,-Toledo, Ohio. ' v .' / .' . 9430 Rayo Ave.,'South Gate,,and 4540 Simpson LUND, Clarence E. (Af 1936; 7.1935; 5- 1933) - / Ave/. North Hollywood,- Calif.~ - . Dir. of Research.'Seeger Sunbeam'Corp., Si. Paul; ; w; . LOEFFLER, Frank X. (Af 1914VPres^ Loeffler- and 4817-12tb Ave. S:. Minneapolis. Minn. - /' - : . } . _ Greene Supply Co./ Box 529. Oklahoma .City 1. ' r LUNT, Wilbur F. (A 1946; 7.1943) Proprietor. -..- " -/and .1811 Northwest 19tb-St...Oklahoma'.City.- " *Lunt Heating Go.; 95 Summit St., Portland 5, / . , V,. . `.Okla. - - '* - .- - -/ /. s ' Maine.. * : '' -/ v- ' . . - LOESER, Chester M. (A 1943) Secy., Elizabeth f- LUSH. Clifford N. {A 1944) Mechr Supt.. Weston's -V . ' Cornice Works, Inc., 25 S- -Union SL. Elizabeth 4. . - / Bread & Calce (Canada). Ltd., and *217 Walnut ' -and 924 Park Ave.,'Elizabeth, N. J.* -'** - ' ' SL. Winnipeg, Man., Canada.- /. ' -Z ;, . .. .. . . LOFTE, John A/ (Af .1045); Engr.. Trane Co.. LUSK';.Harry E.-(A4/-1945)'Engr:, *DeWitt-C. ' " - ./ 1835 N. Third: St:; MUwaukee,>and9121 W. Griffin & Assocs., 7l7 Lloyd Bldg.. Seattle 1/and' - . ' Hawthorne Ave.,- Milwaukee 13; Wis. ' ' 1925 E. Blaine St..-Seattle 2; Wash. ' :' -` LOFTUS, Robert G. (A 1945) Maintenance Engr., .- LUTTRELL, Lee W. (Af 1943) LL (j^g.). U. S. C. .. :/ . Canada Cycle & Motor Co., Ltd.,' and 6 River . G.'R.', Coast Guard, 1300-E St.N.W.. Washington, - ' ' ' Lea Rd., Weston, Ont., Canada. - - - D. C., and *3912 Sixth St. S.. Arlington, Va. ' ; : -, LOKEY, Edgar R. (A 1945) Portland 'Dirt. Mgr., LUTY, Donald J. (Af 1933) Gen. Mgr., Htg. Div.. * ; Norman S; Wright &*Co., 1238 N.W..Gli^n/ . and Chief Research Engr., Gar Wood-Industries, * , -r . ' Portland9. and'2818N.E. Bryce, Portland 12,Ore. Inc., 7924.Riopelle St., Detroit 11, and 30 Colo-.- -- , ' * LONG, David A. (A. 1943)-Sales-Engr., Trane - rado Ave/ Detroit 3, Mich. . *' x - * . : ; "* Z Company of Canada,'. Ltd., 4 Mowat Ave., LUZZI, Theodore E. (Af 1944) Engr., Almirall & . . v Toronto.: and Centre. Rd; S,, Cooksville, Ont., Co., Inc., Metropolitan Bank Bldg., Washington' - ; . - Canada/ . . - - 5. D. C., and 110 S. Oak St.. Falls Church, Va; ' - ' ... -LONG, Edward J. (J 1942; S 1939) LL (j.g.), '/ - - > - U. S--N. R., Submarine Div. 32. c/o F. P._ O..' <- ' . San Francisco, - Calif., and 2012. S. Fifth `SL, v /*] .Springfield, III:-' -'- - - ^ ' LYFORD, Robert G. (A 1944 ; 7 1939)/Ensign. . : ' U; S.'Navy (address unknown). ^ . -LYM, Joseph'H. (A 1944) Owner, Lym Engineer-' '' ing Co., - and *2683-South 13th -*E., 'Salt .Lake'. - City, Utah. - " : /' ' "' " LONG, Eugene L. (A 1944) DisL Repr., The LYMAN, Samuel E. (A 1924) Buensod-Stacey / -. .* .. Avery- Engineering . Co., Columbus, and 1263 Air Conditioning. "Inc.. 60 East 42nd St., New'-'* / -' ` .-Broadview.Ave*. Columbus 8, Ohio.'. ' ' York. N. Y., and *865 Hueston St'.. Elixabeth " V*' - LONG, Wayne E. (Af 1935) Prof./Mech. Ehgrg., 3,`n.j. . //-; > i-. - % ' - Texas A. & M: -College; College Station,,Texas; ' LYNCH, Charles. B. (A 1945) Chief. Engr/- ` . - LONGCOY;: Grant B. (Af 1933), Engr.; Joseph McCann Furnace Co., 5005 Euclid Ave.-, Cleve--' / -r- --/Breslove. :1149-Leader'Bldg., Cleveland '14, and land .3, and * 1552 Ansel Rd., Cleveland/Ohio. ' / . -' '. " ' 1215-Ramona. Ave.; Lakewood 7, Ohio. : - . LYNCH, James' R. (A-1940) Ownef. * The Lynch . Z - LONGWORTH,. A. Leslie (if 1945) Asst/ Fuel Co., 6000 N.E. Union Ave., Portland 11. Ore.;A ' >- ; -x Engr-, Ministry" of Fuel'S Power, N.W..Region. LYNCH, Roderick O. \A 1944) Engr./* Button.-; Z - / V -Burton Rd.. West Didsbury, Manchester, .and /Asbestos Supply Co.. 532 Natoma St.. San . - ,.*264 Buckingham Rd.; Heaton Moor, Stockport. - Francisco 3. and 504 Vista, San Carlos. Calif.' ' , - Cheshire,.England. .. ' : LYNCH, William L; (Af 1928) .Pres., *Rome- LOO, Ping Yok (M 1933) Gen: Mgr., China . . Turney Radiator-Co., and 1205 N. George'St.. ^r..- ' Engineering Co^ ~30 -Brenan.Rd.; Shanghai;' and Rome. N/Y/ / . 'v . .Z -1! " i \/v. : 271-73 Dunbarton Rd., Tientsin. China. . . LYNDE, Carleton John, Jr. (Af T944) Chief ' .\> - LORIMER; Carl F;. (M 1943) Cons. Engr., Engr.. 'Maple.Leaf Milling Co., Ltd./68 Yonge ' Z Business Adm-. Dept. Public Welfare. Rm. G-15. -St.,,Toronto l. arid 33 Queen Anne Rd... Toronto * Z ,. // "'State Office Bldg;. Coluhibus 16, and 130 N. Pierce . '9;Ont.. Canada.- - '/ r` " ' -. >- , ^ ' *S - . St.; Apt: 2, Lima/Ohio. s r - LYNN,' Frederick E. ,(Af 1938)." Refrig.; Engr.V : - - ' - LOUCKS,D/W. (A 1937) Supvsf., Indus. Elec. -~Electric Products. Inc.,- 5928-Penn- Ave.. .Pitts* / ' 'i'Z-'z - Steam Sales, Duquesne 'Light Co.;-.435 Sixth burgh', and 312 Moyhend St., Springdale, Pa/- :'V - ' Ave./'Pittsburgh,. and. 1049 Osage /Dr;,V Pitta- , ' ..burgh 21, Pa. \ - /-. LYON, Douglas M. (A 1941) SgL. U. S/M. 'C. R: - (547263), .V. .M. D. 354, c/o/F. P. -O., Sari' . * >; \> .. -LOUGHRAN, Patrick H.% Jr. (A'l946; J/1937) Francisco. Calif., and. Mr:'Douglas M. "Lydn,'/ '- - ./ Z' --:;ll/ U./S. N/:r;,. and*4513-49th. St. N.W.i ' .2 Seminary St.,-Cazenbvia,-N. Y. / - . l-'.f 'k?/ :Washingion'16/D.'C. > . ;; -. ' LYONr'P. S. (Af 1929) Pres? & Geri: Mgr.. C. H; " love; Clarence H;. (Af` 1919) Mfrs. AgeirL . " .Wheeler,. Manufacturing'Co., Lehigh & .Sedgley'/ / . Nash Engineering 'Co.; 421 'Chamber of -Com- . Aves..-Philadelphia 32, and- 3416 Warden Dr.,:-" . /-//,; - nierce, Buffalo 2; and 16 Lexington Ave., Apt: lA. .Philadelphia29, Pa. * -- / .j - '/r-Z Z /.^Buffalo, n. y.-.a - v'- LYONS; Cornelius J. `(A ? 1932) Sales- Engr;/' 2 rLOVELAND, Francis P. (M 1944) Citizens Uti!i- . .: Nash Engineering Co., and 5 Olmstead - P1-," /. C..V. '.ties'-Co/ Colorado .Div.,.'and *P. O/ Box 131; La South Norwhlkr Conn. ' . '.' -.// :Z^-. - Junta. Colo.' v LYONS, Earl C.. (Af 1945).Gen. Mgr. &,Chief/ LOWE,.Robert A.-(Af 1944; 7 1938)..Cons. Engr... ' Engr.. *Lyons EngineeringCo.vLtd;, 1'Industrial -, ? ; :Z ` "///-rStorms and Lowe, .6359 Yucca St., Los Angeles 28, /:. /St., Toronto 12;Leaside/and 78'Applegrove Ave-y,..>Z. // >- ,and *3744 Potoinsu;.Ave./I-bs/Angeles L6, Calif/ . Toronto, Ont.,,(^anada. - ' /-/' : J/'"- -.. z/^'5 - 52 ' v. " -Heating Ventilating Air : Conditioning-' Guide. 1946.; " ` M'- ' : 7 - ^ MacWATT, Donald A: (Af. 1938) Sales Engr.; - Powers Regulator Go^ 231 East 46th St., New- . - MABLEY, Louis C. (Af1937) Comdr.. U. S. N: R.. York, and *93 Woodedge Rd:, Plandome, N. Y. , - ' and 57 Meadow Lane;. Grosse Pointe Farms \ MADDEN, Alfred B: (Af 1942) Mgr., Htg. Dept., ' - ' 30. Mich... '. . ... Crane, Ltd., 1121 St. .James St. W., and 5367 "MABLEY, T. H. (hi 1939) Chief Engr., Earascliffe Ave., N. D. G., Montreal, ,Que., . Mechanical Heat &Cold. Inc, 12320 Hamilton Canada. '' ` ^ Ave., Detroit 3, and 2323 Yorkshire Rd.. Bir- MADDUX, O. Lloyd CAf 1935; A 1933) Owner, . . ^ nungham.-Mich. -' - ` O. Lloyd Maddux. 53 Park PL. New York. N. Y., . MABON, James E. (/ 1942; S 1939) Design and 17 'TaIlmadge Ave., Chatham,^.N. J. . Draftsman, Gilbert Associates, Inc., and *2048 MADELY, Fred Jas. (A 1936) Gen. SupL, Eastern - * ' Fairview Ave., Mt. Penn, Reading, Pa. ' - Steel Products, Ltd., -1335 Delorimier Ave., and MACCUBBIN, Howard A. (Af 1934) Buyer.Htg. 4068 Marcil Ave., Montreal 28, Que., Canada. . - Equip., Montgomery Ward & Co., and *4616 N. MADISON, Richard D. (Af 1926) Research Beacon St., Chicago 40, 111. ' Engr.,'* Buffalo Forge Co., 490 Broadway, Buffalo ' MacDERMOT, Sidney G. (Af 1943) M$r.. 5, and 218 Bramtwood Rd.. Snyder,' Buffalo- - . Construction Dept.; Canadian Johns-Manville 21, N. Y. -. Co:, Ltd.,-Montreal, and * P.' O. Box 14, Ste. MAEHLING, Leon S. (Af 1932) Mgr., Htg. Sales. ! > Rose,:Laval County,;P. Q., Canada. Equitable Gas Co.. 435 Sixth Ave., Pittsburgh 19," . ' MACDONALD, Donald B. (Af 1930) Sales Engr., and *778 Country Club Dr., Pittsburgh 16,' Pa. , Luzern &'Lackawana.Supply Co., .20 N. Penn MAGARRELL, Kenneth R. (A 1944) Partner. - - - Ave., Wilkes-Barre, and 101 E.` Walnut St.. Design- & Installation, Magarre11 & Cox. 127 - . - 'Kingston, Pa. ' , S: Main St., and-Route 4, Council Bluffs;-Iowa. - - '. . MACDONALD, Douglas J. (Af 1935) "Vice-Pres., MaGIRL. Willis J. (Af 1934; A 1931;.J 1927) ... Si Mgr.; Dufferin Plant. Standard Sanitary' & . Asst. Mgr:, P. H. MaGirl Foundry &' Furnace v Dominion Radiator Co., Ltd., Royce and Lans Works, 413 E. Oakland Ave., and 1119 E. Monroe - ; downe. and 96 Hudson Dr., Toronto,Ont.. Canada. St., Bloomington. III. . ,' MacDONALD, George D.\ (A -1945) Engr., MAGNUSSON, Nicholas (A 1938) Estimator. ; ' - Holyoke Valve & Hydrant Co.. 150 Race St., . Designer, Sales, Montgomery Ward & Co., .150-14 . - and 77 Brookline Ave., Holyoke, Mass. - ' . Jamaica Ave., and 138-05 Linden Blvd., Jamaica,' - - - MacDONALD, James (Af 1944) Dist. Mgr.. Reid L. I., N..Y. . ; Hayden. Inc., 1231.W. Morehead St:, and *2546 MAHON, B. B. (Miss) (Af 1935) Principal of the . .- -Sherwood Ave., Charlotte 4, N.-C. '. - . School of Air Cond. International -Correspon-. . MacEAGHIN, Graham C. (Af 1938) Dist. Engr., . ' dence Schools; Wyoming Ave. -and .Ash' St., - . Frigidaire, and #5112 .Byers Ave., Fort Worth 433 Fig St.,.Scranton 5,-Pa. - ' ... . . /: 7, Texas: - : -. MAHONEY, C. L. (A. 1945) Owner. C. - L. ' ' . ' MACFARLAN, Norris S: (Af 1942) Htg. Engr.. Mahoney, 438 Forest St., "Kalamazoo, Mich. . - The Philadelphia Gas Works Co:-, 1401 Arch MAHONEY, David J. (Af 1930; A 1926) Branch' ' SL./Philadelphia '5, and-320-W. Wharton Rd., Mgr., Johnson Service Co., 503 Franklin St., ' ` Glenside, Pa. -' :- ' *' ' and 140 Linwood Ave.',`Buffalo, N. Y.- - ' ` - - '' .* . - ; MacFERRIN, John.B. (A/1944) Htg. & Vt. Engr., & Sales Mgr.; Pittsburgh Water Heater Sales Co.. P. O. Box 663, and 1305 Clenbume, Apt. 2-B. Houston.-Texas. -. - . MacGANN, Lloyd S. (A/ 1945) Engr., Minne- apolis-Honeywell 'Regulator Co., 799 Beacon St., Boston 15, and* Walpole.St.-, Dover, Mass. . MAIER, George M. (Af 1921) Mfg. .Dept.. . American Radiator & Standard Sanitary Corp.,-.- '. Bessemer Bldg., Pittsburgh 22, "and 135 Longue' - - Vue Dr,, Mt. Lebanon, Pa: '- MAKIN, Henry T>, Jr. (Af 1939) Engr., Warren Webster Co., 17th and Federal St.,. Camden, and - *21 Valley .View Terrace, Moorestown, N.-J. . MALIN, Benjamin S. (Af 1940; /. 1939) Mech. . . . . MacGREGOR, Cedi M. (A 1939) ' Lt.- Col., Engr., -Capt. 0-317:465, Construction Div., Ordnance Dept.. U. S. A:. Hq., Army Service A. M. E. T,, U. S. Army. A; P. O. 678. c/o P. M. ' - Forces, Pentagon, Washington. D. C.,. and- New ;York. N. Y,, and 201 Sumter'St., Proyi-- _v- *3349B S. Wakefield-St., Arlington; Va. . -den 7,R.,'1. - - ' '* . MacGREGOR, Duncan K. (A 1944) Metal MALLIK, J. R. B. (7 1945) Student in Mech. ' . lurgical Furnace Designer. Railway & - Power. Engrg., Massachusetts Institute of Technology,''. . - . Engineering Corp.,' Ltd., 171 Eastern'Ave., and M. I. T. Dormitories. Cambridge. Mass., and 7 - ' : 177 Humewood Dr., Toronto. Ont., Canada. Jagannath Sur Lane, Calcutta. India. - - - '- MACHEREL, Ferd (A/ 1939) Alger. 50 R MALLIS, William (Af 1914) Archt., *330.Lyon - Daguerre, Algiers. ... . , *. . . MAGH1N,. Donald W.'(A 1943; J 1935) Com. - ' bustion fit Fuel Engr., Pittsburgh &'Midway'Coal . . 'Mining Co., 610 Dwight Bldg., and *3220 West . . Parkwood Blvd./ Kansas City 2, Kans. - .MacINTYRE, Henriette Betlem (A 1942; J 1934) . R.-D.* MacIntyre Co., P. O. Box 113, Brighton . . Sta.. and 2500 East Ave., Rochester'N: Y. - MACK, , Emil H. (A 1938), Asst. 'Sales Mgr., . The .Vilter. Manufacturing -Co.'. 2217 S. First St:. ' and 2225N. Booth St., Milwaukee 12, Wii ' Bldg., and 1215 Seneca. Seattle. Wash. . ' ' . ` MALLOY, William W. (/ 1944) Sales Engr., F. D. Crew Co.; 1539-Race St., Philadelphia 2, and 31 Strath Haven Dr., Bromall, Pa. - - - - MALLY, Chester F. (Af 1940; A 1938) Owner. ' - - Mally*& Co., 20420 Woodward Ave., Detroit-' 3, and 292 W. Woodland Ave., Femdale,-Michr . ' MALM-, Edwin L. (A 1944)-Sales Prom,'. Mgr*.. - c-'- Bell -& Gossett Co., Morton Grove, and 816 s. " Michigan Ave., Evanston, 111.- - *' . - MALONE, Dayle G. (if 1929; A 1925) Vice-Pres. r- & Branch .Mgr., Petroleum-Heat & Power .Co., ' . . MACK, Ludwig (A/ 1935) Dist. Mgr., Cooling & ' 3301 S. California Ave., and 7337 S. Merrill Ave., * ' . Air Cond. Div., B. F. Sturtevant Co:, Cresmont Chicago 49; 111; . - - . ' .' and Haddon Aves.,-Camden. N. J,, and *412 W. MALONE, James S. (A ' 1936) -Dist. Repr., '" Hortter St., Philadelphia 19, Pa. , ' Hoffman Specialty Co., 4 N. Eighth-St., St.. z} .-.' MacKENZIE. John,M.*(A 1945) Plant Layout Louis 1, and 7124 Waterman Ave.. St. Louis 5; Mo. . *" ' = `Engr.,' Duplex Printing Press Co., and *Route 2, MALONE, John F; (Af 1945) Asst. Mgr., Dist. >. '. Box 747," Battle Creek, Mich. ` ' Steam Dept., Consolidated Gas Elec. Lt. &; . .'MACKEY, C. O.* (A/ 1943) Prof, of Heat-Power Power Co. of Baltimore, 500 Lexington Bldg.. V- - < Eng., Cornell University,' and. 617 ' Highland Baltimore 3,.. and 3401 'Greenway. Baltimore _ * Rd:; Ithaca. N. Y. '' . 18. Md. , : MacLACHLAN, Victor D.* (A. 1939;. / 1938) , . Flight Lt.. Royal Air. Force Volunteer Reserves. MALVIN, Ray C. (Af 1929) Pres.. *MaIvin;&. May,' Inc.. 310`S. Michigan Ave.-, Chicago'4. and . : Honeywell-Brown,-rLtd., Wadsworth- .Rd.,' Peri 8220 Dante'Ave., Chicago-19, 111.-^ -' ` * - vale; Greenfordi.Middlesex,'and R.' A..F. Station. MANDELL, Thomas P. (A--1937) Sales, Carrier . -. Digby. Lincoln; England.' - ': ' Corp.', Rm.-: 624; 419 Boylston 'St... and * 192 . MacMILLAN, .-Alexander' R. --(Mi 1936) Col.. -,Commonwealth"Ave., Boston. Mass.-- - " Hq: Army Air Forces. Field Office of The Air MANIER, Ralph L. (Af 1945) Indus. Htg; & Air" ..V; ' - Inspector, Orlando, ;A. B., and-1011 Lake Davis. Con'd. Engr., Central New York Power IGorp.v r,- Dr.; Orlando, FIa.i * ''. .. " ' . 300'Erie BIvd.. Syracuse 1. and *185 Clifton PI..*". - MACROWj -'Lawrence (A 1941; J 1936).' Dist. Syracuse 6, N. Y. . ' .. , - - Chief;rEngr.; Carrier Corp.; 12 South 12th St.. . MANN; Lee. B. (A 1944) Vice-Pres.; Boston; . Philadelphia; and.225 Buttonwood''Way. .Glen- Filter Co., Inc., 43 Harvard'Sq., Charlestown; and . rr :side?`Pa. -^ 's_ ` . * ` ; ' _ 32 Stanton Rd., Brookline, Mass.''; . -Roll of.`Membership. 53 ,, MANN, ^Valter N. (Af l939) Gen. Mgr.. Electric MART, Leon T, (Af 1941) Pres.;*The. Marfey'. . `Panels,- .Ltd., Electro-Thermal Engineers, 123 ' . Co.,- Inc.,- 3001 Fairfax Rd., Kangati City; Kana., --; Blackbprough Rd., Reigate, and Ninehains Gables, / and 6840 Tomahawk-Rd., Kansas City, Mo. ' - ' ' -Ninehains Rd., Caterham.-Surrey, England! *" ' MARTENS, El D, (Af 1937) Chief Mech. Engr.,-. MANNA. Anthony F. (A 1944) Mech. Engr., Starrett- Bros. & Eken, Inc., 63 Wall St., New ' `Wilbur Watson Assoc., (Architects-Engineers), . York, and *89-Eldridge Ave., Hempstead,- N. Y. ` 4614 Prospect Ave., and 10410 Shaker Blvd., MARTIN, Albert B. - (Af -1917) Chicago Br: - Cleveland 4, Ohio. . ' Mgr., Kewanee Boiler Corp., 549 W. Washington MANNEN, D. Edward, Jr. (A 1946; J 1939) Blvd., Chicago, and 860 Spruce, Winnetka, 111.- . Vice-Pres., The Mannen & Roth Co., 9108 Wood- MARTIN, G. D. (Af 1941) Br. Mgr., Grinneli s land Ave., Cleveland, and *4157 Silsby Rd., - Co.-of Pacific. 601 Brennan St., San Francisco 17,. ' University .Heights, Ohio. and 398 Menlo Oaks-Dr;, Menlo Park, Calif. - MANNING, C. E. (A 1942; J1937) Engr.. Packard MARTIN, George W/* (Life Member; Af 1911) Electric Div., General Motors Corp., and-*339 Homewood Ave. S.E., Warren, Ohio. 340 Prospect St., Ridgewood, N. J- ' ' MARTIN, Harold L. (Af 1944) Chief Engr.'; Post .. MANNY, J. Harvey (A 1936)' Pres., Robinson Engineers, Ellington Field;' and *P. O. Box 112, ' : ` Furnace Co., 4600 W. Monroe St., and 242 N. ' South Houston. Texas. ' .- ' -'Parkside Ave., Chicago 44, 111. - .. MARTIN, Henry L.= (Af 1945) Div. Hd., Steam MAPLE, Charles W.' (A 1945) Chief Draftsman, ' Avery Engineering Co., 1906 Euclid Ave., . Sales & Service, Boston Edison Co.,' 39 Boylston ' St., Boston, and *75 Hunnewell Aye.; Newton ' ' . Cleveland 15, and 3792 West 33rd St., Cleveland : 9,- Ohio. ' ' - '' . .. 58, Mass. . .- . - MARTIN, John O. (A-1939) Partner, .*J. O. & MARC, Henri M. (Af 1943) Asst. Dir. of Research,, C. U. Martin.-637 Minna St:. .San Francisco 3, ; ' .The Philip Carey Manufacturing Co., Lockland, ' and 328 Jerome Ave., Piedmont. Calif. Cincinnati 15, and 7342 Parkdale Ave., Roselawn, MARTlN, Ray (A 1937) Sales Engr., Vapor Car ' Cincinnati 16, Ohio. - - ' . Heating" Company of Canada, Ltd.,'65 Dalhousie - MARCONETT, Vernon G. (Af 1945; A 1936) - St., Montreal, and 9 Morris Ave., Ste. Therese, Supt.,' The. Farquhar Furnace Co., 150 Owen Que., Canada.' .. - 'Ave., and *216 Fulton St., Wilmington, Ohio. - MARTIN, Wilbert A. (A 1944) Mgr., Air Cond. :. MARIN, Axel* (Af 1935) Prof, of Mech. Eng., Dept.. American Heating Co.-, 55 K St.. S.E., University, of - Michigan. 241 W. Engineering ' Washington, D. C,,. and 1415 S. Geo. Mason -' - Bldg., and 2475 Whitmore Lake Rd.t Ann Arbor, - Dr., Arlington. Va. ' --Mich. ' i. MARTIN, William J. (A-1943) Martin :Fan & MARINO, Frank A. (A 1941) Tech. Sgt., U. S. Blower Co., 4634 West 21st PI., Chicago 50, 111. - Army, and *3348-28th St., Long Island City, N.Y. . MARTIN,\William T. (Af 1943) Chief Engr., . MARKERT, John W. (A 1940) Naval Archt., Beech-Nut Packing . Co., and *87 - Cliff /St., Htg. -&'Vtg., -U. S. Maritime Commission, Rm. '. Canajoharie, N. Y. '7126, Dept, of Commerce Bldg.. Washington, MARTOCELLO, Joseph A-. (Af 1934) Pres., Jos. D. C.. and *8506 Garfield SL, Bethesda 14, Md. A. Martocello &. Co., 229 North 13th-St., Phila-' MARKLAND, Charles E. (Af 1939) Mech. Engr., delphia. Pa. . Mid-States Engineering Co., 103-105 N. Second MARTY, Edgar O. (Af 1930) Mech. & Elec. Engr.. St., and *807 W. Clark St., Champaign, 111. - Parsons, Brinckerhoff, Hogan & Macdonald; 142 . MARKS, Alexander A. (Af 1945; A 1930) Dir. of Maiden Lane, New York, and *84 Long Ridge - ' Research, Richmond Radiator Co., and *50 W. Rd., Plandome, L. 1., N. Y. - , .' _ Main St.,.Uniontown, Pa. . MARTYN, Henry- J. (A 1937) Pres., Martyn ; -MARKSON, Wesley H: (J 1942) Supvsr. of Bros., Inc., 1000 St. Louis St., and 5306'Ridgedale ' 'Material Control. Mfr. of Heat Transfer Equip., - St.-, Dallas, Texas. ;. 1600 Broadway N.E., and *5512-43rd Ave, S., ' . Minneapolis 6. Minn. . MARVIN, John H. (A 1942) Mgr.. John: H. Marvin Co., 1016 First Ave. S., and'2366 W. ' MARKUSH, Emery U. (Af 1931) Secy., Eastern Viewmont Way, -Seattle 99, Wash. - .- ' -"-Mechanical Corp-, 225 East 21st'St., New York MARVTN,-Philip R. (A 1945) Dir. of Research-& - 10, and 84^30-85th Ave., Woodhaven 21, N. Y. Dvlpt., Milwaukee Gas Specialty Co., 722 N. : MARR, J. M. (A 1944) Chief Engr., Aladdin ' Jacksom Box 461, Milwaukee 1, and'; 6828-W. ' Heating' Corp., -2222 San Pablo Ave., and *95 Wisconsin, Milwaukee 13. Wis. ' -- V Moss Ave.. Oakland 10, Calif. MARZOLF, Frank X. (A 1937) Sales Engr.. R. L. * MARRINER, John M. S. (Af 1934) Comdr. (E), Deppmann Co., 5853 Hamilton, and 15790 St. \ ' .. R: C. N. V. R.. Vice-Pres., *Taylor Engineering Marys. Detroit 27, Mich. '' ' .- , - & Construction Co., Ltd., 80 .Richmond St. W., ' MARZORATI, Giuseppe. Dr. (Af 1938) *c/o A. . Toronto 1, Ont., Canada. . Lizzola Co.. Inc., 553 West 51st St., New York MARSALIS, Martin E. (A'1943) Owner *Ameri-. 19; N. Y. . . . ` can Metal Products Co., 730 Hudgins. Ft. Worth, MASON, Gail C. (Af 1943) White Haven Lane. 'Texas.- ' Whitehaven. Tenn.- ' ' ` ; .- MARSCHALL Peter J. (Af l93Q\ J 1927) Engr.. MASON, Ray B. (Af 1941) Sale Engr., Kewanee . Abbott.Laboratories. North Chicago, and *2009 Boiler Corp.,- 2014 Wyandotte SL. and 121'East . . 'Greenwood Ave., Wilmette, 111; ' 70th Terrace. Kansas City; Mo. .- . / - MARSDEN, Edward C. (A 1944) Pres., Marsden _ MASON, Raymond- P. (Af 1945) Asst. Supt. - ' & Wasserman. Inc-, 44 Hicks St.. Hartford, and Engr.. U. S. Army.Transport.Service, Planning ' 21 Walbridge Rd.. West Hartford, Conn. ' Set., Bldg. 310, Ft. Mason, and *27 Westminster.. : MARSHALL, Albert W. (Af 1937) Inspector & Ave., Berkeley 8,~Calif. ' ' Engr.,*. Hartford Steam . Boiler Inspection & MASON, Robert-E. (Af. 1944) Owner. Robert . - Insurance. Co.. 1806 Arrott Bldg.. Pittsburgh 22, E. Mason & Co., Johnston Bldg'., and 1129 Gran and 1120 Highview Rd.. Dravosburg, Pa. ville Rd., Charlotte. N. C. ^- -- ' MARSHALlj, Harold W. (Af 1944) Mech. Engr.. MASSAGLIA, PaoU E: C. (5 1945) U. S. N.- R:. - . T; H. Buell, Archts. & Engrs.. 730-14th St., and and 3814 Parallel Ave.v Kansas:Gity. Kans; " ' *387 Ogden .SL,.Denver 3. Colo. MAST, Clyde M. (A 1940) Pres. &.Engr.. Healing ' -MARSHALL; James (Af 1943; J 1939) Asst. . Chief Engr..,* The Bahnson Co., 1001 S. Marshall & Air Conditioning Supply. Inc., 263 Sierra St.. ' and *577 St. Lawrence St., Reno. Nev. " - ' - '0. . St., and 709 Roslyii Rd., Winston Salem, N. C. MATCHETT, James C. (M 1923) Vice-Pres. &. - . MARSHALL, Orville D. (Af 1942; A 1931) Mfrs. Gen. Mgr., Illinois ' En^neering Co., "2035-'-S. . - Agent..*'311 Anderson-Bldg., and'3025 Midland' . Racine Ave., Chicago^, and 9936 S. Winchester -- 1 Dr. S.E., Grand Rapids 6, Mich. - , '' . Ave., Chicago 43,'.111.- . ' . -. -' ` MARSHALL, Thomas A. (A 1943; J 1937) Capt., . MATHANEY, Edgar H. (A 1944) Leading Mari, :: 'U. S. A., 0-1107573. and *195 Eureka.Stl, San . 'Sheet Metal Worker, U. S;`Coast Guard-Ship/ Francisco 14, Calif. -. * ' ..building&`Repair, Curtis Bayi'and*12 Elinor.-.* : MARSHALL, W. D. (Af 1935).Mgr., Noland Co' Ave.,-Baltimore 6, Md; - - .. ^ Inc., -1823- N. Arlington Ridge -Rd.,: and *3232 ' MATHEKA, Charles R. (5 1939) U. S. S. Tattnall, - Woodrow St. N.', Arlington, Va. .. - c/o Postmaster, New York,- N. Y.,. and *1506. : ; MARSTON, Anson D. (A-1937)'Col. G.`S."C.. -.-Summit Ave., UnionXity, N. J."- . - " , ; *G-3. SecUon, E. T. O. U. S. A:, A. P. O. 887. MATHER,' Harry H.'- (A 1929) Mfre Agent 1212 - - c/o P: M., New York, N.-Y.,-ahd College Campus,- Commercial Trust Bldg., Philadelphia 2, and 377- Ames.-Iowa. ' '. '. Windemere Ave., Drexel Hill, Lansdowne P. O., Pa. 754 ` \ ~ IHaenafitninrfg-' VVeonn ttiitlnattSinnga AAir Conditioning- Guide 1946 fMATHEWSON. M. E.\(Af'l937) Secy.. MAY, C. W.` (Af 1933) TCons. Ensr.. 1430 Vance . . Kinney,' Inc;; 1211 Enquirer'Bldg.. Cincinnati 2;. - Bldg.,. SeatUe'l,:.tand :6817rl6th N.E.*. .Seattle v - and 1110 Priscilla Lane. Cincinnati'8. Ohio. ' .'5, Wash. ' 4J >' MATHEY, Nicholas. J. "(Af 1946) /Maintenance. . MAY, -Edward M. (M 1931) Branch Mgr., Steel Steamfitter, Hercules.Powder Co..' Lawrence, and , ` Products Engineering Co.. 1601'$. Michigan-Ave..' 13,-Lane 1, Sunflower. Kans.-' . .` v - Chicago, ' and 848' N. Ridgeland Ave.. Oak . i MATHtS, Alexander- (if- 1944). Mech:' Engr.._ Park, 111... ". : ?' . ' "Reynolds.'Smith &-Hills; and 2547 Riverside. MAY, George Elmer* (Af 1933) Prin. UtU; Engr., Ave;, Jacksonville 4,-Fla: . . , * . New Orleans Public:Service, Inc.. 317 Baronne ' MATHIS,' Eugene' .(Af 1922)..Pres.; Mathis - St.,'and 2031 Short St., New Orleans; La: * : ... Illinois Corp., c/0'95th Street'Office. 1935-West 'MAY, James W. (Af 1938; J 1935) Dir. of Re .- . 5th St.-; Chicago 43; and 9151 S. Hoyne A've., . search, * American Air Filter Co., 215' Central r Chicago, 111. ^ . . Ave.. Louisville,-and 3908 Elfin Ave...St. Mat 'MATHIS, Henry (Af 192l)-The New.York Blower thews. Ky. .' ' \ ,Co.;32nd & Shields.Ave., Chicago 16, and *11246 ;MAY, Maxwell F. (Af.1929) Lt. Comdr.. U.S.N.R.,. Longwood Dr.. Chicago 43. 111. .. ' ` ' Industry Cooperation Div., Navy Dept., 226: ' MATHIS;:John (A 1938) Mfrs. Agent; Heating . -'-`W. Jackson Blvd.,Chicago 6, and Palos Park, 111.'- - Service 8c.Supply Co.; 1384 S. York St;, Denver :- 1MAYCOCK, Ambrose A;-(A 1945) Mgr.;'*A. A. 10; Colo.' : .. ". . . ' ; . . Maycock Co., P. Or Box 3; SaIt Lake City 8, and MATHIS, Julieri W. (A 1921) New'. York .' '234 Seventh Ave., Salt Lake City.3, Utah; - Blower':Go:, 3145^55 Shields Ave.;.. and; 7929': . MAYGOCK, = George- E. (A' 1945) Htg. & Vent.,,> Bishop St;, Chicago, 111.--x..' - -Engr., A.'A. Maycock Co.r'234 Seventh'Ave.; and MATHISON, R..S. {AT938) Asst! Mgr., Weather-"- ' ;*233."E" SL/Salt Lake City. Utah. ' makers :(Ganada),Ltd., 593 Adelaide St. W.,- MAYER, William J. (A 1943)- Field Service Engr.,.-. Toronto 3..^and 44-Strathgowan'Ave-.,. Toronto :'A. M. Byers Co.;:7. St. Paul St.. Baltimore 2,:and . l2,iOnt.. Canada. >*. ' .' *1100 Edgemont Rd.. -Towsbn 4, Md. .. MATOUSEK, A; G;,, (Af .1937)- Mgr.',>Gamble;' MAYLARD, John B. (A 1943) Archt.-Engr.; 112 Store,-Schuyler. Nebr; -' . - Dupee PI.. Wilmette. 111. : . v '-A- MATTHEWS. Carl R. (A:1944) Service & IhstaC r MAYNARD. J; Earle (Af. 1931)'Engr., U. S. . > lation Mgr.^.Miimeapolis-Honeywell Regulator ' Radiator- - Corp., . 1500 ' United; Artists ' Bldg.. `Co:,- a'nd'*-1603 Cohassett, Lakewood. Ohio.' -Detroit 31; and *2441.-.Kendall; Detroit 6, Mich. - MATTHEWSr Jbhri.E.- (AT :1934):.Field :rEngr:, MAYNE; Ivan E. (A' 1945) Owher, Consolidated. . i-. B,. F-. Stuftevant ;.Co.,- Crestinont. and -Haddon Heating'& yentilating Co./1709' W. Eighth-St;.. ' ;. Aves.: Camden, and *300 Chestnut-St.; Haddon-'- ^ Rm. 801,-Los Angeles 14, and 1748'Rancho Real. field.-N. J:- ,' - ` - .>**,* - : '. Rd.vTemt)le'aty. Calif;/' : - . ' MATTHEWS, R. R. (Af 1944) Owner. Matthews - 'MAYNE, Waltec L. (Ai-1938) Prod.-Sales Engr., ^ Engineering. Cp.. 2122 Olive, Dallas/1. and 3556 ' Tanner- Manufacturing Co., 4201' -Bell St..', ; Ra'nkih. Dallas 5, Texas.- ;. . - - :. - .- ' ``P, O. Box 860, Lawrence .Park, .'and 401` Beverly . MATTHiES; Leo A. (S.1941) Lt.; U. S. N. R.. and . 273-Fannington Ave., Hartford-5, Conn.. ' Dr'.. Erie, Pa.. ' - - ' McBRIDE,' Joseph "A. (J. -1943) Asst- Secy.-,' , MATTIMORE, John D. (Af 1945) Dir. of Re Frank A.'McBride Co..:l60 Ward St., Paterson search' .& Dvipt., Tube Turns; Inc., .224' E. , - 1, and 585. East 27th SL, Paterson .4, N. J. '- ' Broadway,' Louisville 1, and 3130 Meadowlark ' McBRIDE, . J.- Nevins ' (A 1941) Vice-Pres., - .Rd.,'-LouisviIle 4, Ky. , - - v - - Frank A. McBride'Co., 160 Ward'.St., Paterson-' MATTINGLY, Maurice F. (A 1939) Sales Ehgj;, 1, and 288 Derrom.Ave.. PaVeTsbn 4. N. J. , k r&'K - ' Johnson-Service Co., 1355-..Washington-Blvd.,- : McCABEv'Johh'H.^(Af 1944) Rocky Mountain .' ' Chicago 7, and 8028 Ingleside Ave.. Chicago 19. III. ' Sales. Mgri; *American- Blower Corp.. 1730 r MATTSON, Rofler'K, (> 1945)-Engr.. McQuay. Glenann St.,'!Denver 2, and 567 S. York St.. Inc.,'; 1600-N.E.*-Broadway, Minneapolis,.'.and. '/ Denver. Colo. _ '. . .. *36ii'Bryant Si, Minneapolis 8/Minn,'* ' -' McCAFFRAY, Charles E. (Afa938r-Htg.. Vent.- * MATZ,'-George.'N.:'(2f 1938) Mech. Engr.-. A... _ - & Air*Cond. Engr.; HollidayPleasant Sts.,". Ernest'D'Ambly, 2101-. Architects Bldg:, -Phila - ' Baltimore, and;*Ruxton.- Baltimore '4. Md. " : v delphia/and *649 Feme Ave.. Drexel Hill,.Pa.' ' : MATZEN,'Harry B. (M 1940):. Mech. Engr.. v .Frank A. McBride Co.. -160 Ward SW.Paterson.. "* - ,'N. J;;. and 16 Addison Pi.,'.Rockville Centre,- L >1;, N. Y.- '. - ' :* r. v^MAURER, 'Elmer E,'- (A -1944)- Secy. & Engr., ' McCAIN, H: King (Af 1939; A 1938; X 1937) Cons.. ' Engr.", Newcomb &-'Boyd.'-615-Trust Co. of. Georgia Bldg., and 3619 Ivy.Rd. N.E., Atlanta. Ga. McCALL, H. Max (A 1945) Owner; Mgr., McCalls; .'*,1146 Philadelphia-St.; Indiana. Pa. - The -Maurer -Bros.' Co.,- 8600'. Detroit- Ave:-. .. McCALLUM; Allan W; (A 1943) Mgr.V*Anthra. 'Cleveland 2,;.and- 15726.Fernway Aye.;'Cleve-, Foundry. . Ltd., Saskatchewan Ave.. and s383 . . . land, Ohio. - > - >- - .'. .. -Overdale St.; Winnipeg; Man;. Canada. _ ' ' i .-..`MAURER, .Lester (Af`..1941) . Air! Cond. 'Engr., V McGANDLESS. Howard F. (A i945) Gen:_Mgr., >*Giffels.& Vallet/Jnc:, 532; Wainwright Bldg.,. - , * The-Hardy Cd.,' P. O. Box 256, Watsonville, ;j. - N6rfolk''10r and-1100 .Brunswick Ave., Norfolk,- ;Calif. - ` " - ; McCANN,'Frank:P. (A 1939) Sales.Mgr.". Bendix' m ^iS- -J MAUTNER,vErwin W. (Af 1943) Partner. Mid-' -V Aviation.Gorp-. Marine Div.; 106 Nostrand Ave., -West- Heat Service; 3336'Wi Franklin' Blvd;, and : Brooklyn.- and .*113 Chippewa' Rdr, Tuckahoe 3935 Pine, Grove Ave... Chicago; III. 7, N;.-Y. . MAVES,:g; DV (A 1939) Regional Mgr.V Mmn^- .McCANN, John L'. (A 1945)-Mgf.. Plbg..'& Htg.. apolis^Honeywell Regulator Co., 1425 Welton St., Dept.;-Harris Pump.& Supply Co..--Brady.and- l'. Denver.2. and * 152r Grape Sh,-Denver 7.' Colo. .' Sidney Sts.. Pittsburgh 3, and *726 Lafferty Di-., MAWBY, Pensyl (M 1934). Dist. Mgr./Lehigh Pittsburgh 10; Pa. .. - . -: -*Navigation -Coal' Co.,-123 Sr.Broad 'St.; .Phila- - - McCANN, Stanford-C;'(A 1944).Owner. *S.' C; . - <'delphia. and *.15 E.-;Ridley Ave.. Ridley, Park,-Pa.' ' McCann:Co.;: 42L Dwight Bldg..- Kansas-City 6r_ MAXWELL, George W.,(Af-i935; S1932) Owner; . and. 1002 W:-Gregory. Blvd.. Kan^^p City 5. Mo. : Kenealy & Maxwell, Main St-.,' and'* Lower. McCARL; Harry Ei (Af 1944)'Htg,. & Vent/Engf.; . Codntyjtd.. Harwich Port, Mass. ' . 'T v:- ' :_. ;...-United'.States Rubber^CoT; Detroit, and *22714' MAXWELL; Lawrence R;' (Af. 1943) Partner. &i . -Brittany, East DetroiC-Mich; ^ Gen;; Mgr:;''Wallman Supply Co., 2741 Tulane . McCarthy* P.-Wayne (A'1945) Branch' Mgr., - ?Ave.V_ New- Orleahs'-l9,~and *1332 Joseph' SC,. . *. - Minneapolis^Honeywell Regulator.JGo.,' .2017/ ---^NewOrleans 15,-La.*>.--5>: * Ingefsoll.-e Des 'jMoines,. 12,.-'and.T235-37.th', 'Des f ^MAXWELL.iR;- Shlerlaw -(A/^1937)- Gen. Mgr.. Moines;Iowa.' C- - '' -vU r*'Bennett..;&T WrighU 'Ltd., - 72^ Queen" St.^ E*. \.^McCAUL^Xynn-K.- (Af-1942).Engr.,iThe Coon-. `',Torbhto':T.*pnt'.:'Cariadav` '-1 - * - /Tv DeVisser Co;;' 205l W.- Lafayette,-.Detroit 'I6,- * - '.''and *620'-W;.`Woddlahd,~Ferndale'20; Mich.". -- ' ; /lMcCXULEY;:James;H. (Af 1921) Pr.. *J:*H.` . *- McCauley & Son,- 5620-West 65th-St.; Chicago,: ' ~andni23-`Pleasant StVOak Park; 111." "VjV:r;iT* fe;'V?^:-Rmh925r-'.Chicago.'4 Ai McGLANAHAN.V LV C^:(Afv 1939)r Dist^'Mgr.,': v Aerofin Corp.,v603- Great:National'Life^Bldg.;:- .. ^and SU S- Tyler, Dallaa, .Texas.'; - -/ -RollofMernber8hip\ -- 55 1~': ]McCLElXAN^ f&tnfEX:{M1922) Chicago DisC McELGIN;'John W> (A'1937; >*1931)' Engf.V`:': . . .*American Blower Go'rp.,, 228 N;-LaSalle .St.; J. >J. Nesbitt, Inc.,' Holmesburg, Philadelphia! . . -Chicago. and.738 Marion St.,-Highland Park,.lU; .and *Tennis Ave., Ambler.``Pa. . ^ . .McGLINTOCK, Walter C. (A 1945) Dist; Mgr:." ' McFADDEN, H. J. (A 1944) Sales Engr.,--* Serve!;; : . ' Reznor^Manufacturing Co.. P. O. Box 8. and. .- Inc., 706 Lone Star-Gas .Bldg., Dallas 1. Texas, > . : 303 N.,Main St-; Milan, Tenn. . - ' `and 1920 .Northwest^ 32hd'St'.,. Oklahoma .City, . : McGLINTOCK, William (Af 1935) Mech; Engr.. - Okla. - - - Kellex'Corp'.,-'Woolworth.Bldg.,'New York, and McFARLAN. A. I. (Af 1942) Pres.. A.-1. McFarlan A' *4116 Carpenter Ave;, New York 66; N.-Y; . . .. Co., Inc., 2V West St.; New York 6,'N.-Y., and ' McCLOSKEY, John H. (A 1940) 304. Elkton *691 Doriain Rd..-Westfield. N.'J. ` - " ' Blvd;, Elkton; Md. . ' ' : McGEARY. Paul JW..(Af 1944) Mgr,, Indiana ' ' ; McCLUNG, Tom H. (A .1942; J 1939) Capt. Dist. Office. *The Trane Co., 635 N. Penn,-and*. - -: * ,U. S. Army, Field Artillery, and *2743 Northeast - 3630 N; Penn, Indianapolis, Ind. ' -; ... ^ 54th, Portland,-Ore.-* McGEORGE, Richard H. (Af. 1937) Mgr.'. Htg.- ^- McCONACHIE. L. L. (Af 1943; A. 1928),'Owner, & Air Cond. Dept;, McCord Radiator & Manu-' - - - . L. L. McConachie Co., 1003 Maryland, and 1415 facturirig Co.. 2587 E. Grand Blyd., and 14565 * ' - ' -Harvard Rd., Grosse Pointe. Mich.'. -- Glastonbury,Rd., Detroit, Mich'.- McCONNER, Charles R; (A A925; > 1922) Gen. - McGINNIS, F.-L. (Af 1940)-Supt:i Coley &-- ' . Sales Mgr.;.*'Clarage Fan Co-` Kalamazoo 16F, Prtefsen, 409 West 21st St.. Norfolk, and *332 N! ' . ' and -1904 Waite Ave.-. Kalamazoo 44; Mich. ' - ' . Henry St., Williamsburg. Va. - ` v. * ` " McCORMACK, Denis (Afi 1933) Pres., Fox;.. . McGOVERN, Arthur F. (A 1945) Dist. Supvsr/ . - . Industries;.Inc., 21st.-and.Arcb Sts., Philadelphia' & 8c Engr.t*Modine Manufacturing Co..'.83. SI' : 3, and The-Kenilworth;. Aiden'Park, Gtn.. Phila- . High St.', Columbus 15, and 362 S. Harding Rd.,.:. ; delphia 44, Pa. '' ` '"Columbus 9, Ohio.' - - . ' : ' *..* McCORMICK, George W., Jr. (A 1941) -Capt.. ' McGOWN, -Frederi<dc H.V Jr- (J: 1941; S;:1939) - ' ' . U. S. M. C.,.;Combat' Intelligence Officer, and. CpL, U. S. -Army. and*c/o The McGowh'Co;, < . 1320 Sheridan Rd.,'Menominee. Mich.- - .Cooperetowri, N. Y. "" - McCOY, . C. E- . (Af 1936) Partner. Turner McGRAIL; .Thomas E. (Af 1926) Local Repr.. ; , ' - McCoy. 315 W. Second St.; Little Rock, Ark. Canadian Sirocco Co., Ltd.. '63 Sparks-St'., - s' , . McCOY, Thomas F. (Af 1924) Mgr^*The Ottawa, Ont., Canada. - ` -' - . v`.` * . ' Powers'; Regulator Co,, 125' St: Dotolph St., ' McGRATH, William L. (Af 1945) Proiect.Engr.Vi. : - Boston 15, Mass- V - -- ' .^ -. Carrier Corp., Syracuse, and *113 Carlton. Rd.,'- ' McGREA, Joseph B. (Af .1937) *2919 Drexel' - Syracuse 4, N. Y.. ... -* ' ' '' Ave., Detroit, Mich.--' ' McGREW, Joseph-A. (A * 1944) Owner. *J. A.. _ McCREA, Lester. W. (Af 1940) Prop.,' *_McCrea . McGrew Supply Co.. 2163-Market St'.,'Denver 2; Sales Co., 15 East:21st St.. Baltimore 18, and'564 - and 2380 Leyden St., Denver 7, Colo. '. _ ' * * c w - ' - W. Univerat'y'Pkwy.;-Baltimore 10. Md. ' * , -McCULLEY, D. E; (A :1941) Sales Engr.. *814 .. - South 14th" St., .Omaha-2,-and 5504 Corby St., .. Omaha 4,- Nebr- . . ' McCULLOUGH, Henry'G. (Af 1936) Vice-Pres.. ' - S. S/Fretz. Jr./.Inc., 1902 Chestnut St.; and 7042 ,' Lincoln Dr., Mt Airy, Philadelphia,-Pa. . . McCULLOUGH, John L. (Af . 1939) Engr., McGRUER, A. E. (Af 1945) Supvsr.. Stationary" . ' Boiler Plants, Canadian-Pacific Railway Co., v'. Rm. 238, Union Station, and 1954 Bloor St;. W... ' Toronto. Ont,, Canada. - ; --' McGUINESS, C. H. (A 1943) Owner. Iowa Kol-r . Master Stokers, 205 Plymouth Bldg., Des Moines - --- - 9, and *218 Franklin,-Des Moines,-.'Iowa: . v" . ' , - Harry.'Dougherty., 8t Son, Freeport, arid.*731 - Country Club Dr..-Pittsburgh 16. Pa. - ' . :: ' 'McCULLY,.Robert E. (A-1945) Sales Engr.. Bay McGUIRE, James W. (M 1945) . Owner.* * 370 ' *' - Lexington Ave., New York, and-86-22 Dongan < Ave., Elmhurst. L. 1., N.-Y. '. * . r. -. Cities Asbestos Go., Flfth Avei and East 12th, McILVAINE, John H. (M 1929) PreL, Me-' ' v Oakland. - and *2619 Eighth Ave., Oakland Ilvaine Products, Inc., 1516 -Callowhill St'.'. .6,-Calif..' . ' - ; - ' - Philadelphia 30, and- 601 Pembroke Rd.,. Bryn -' . r McCUMBER, Burton R. (M ,1945) Stafi Asst... Mawi, Pa. - ' ' ._ ' Carrier-Corp:,.-Syracuse, and* West Lake Rd.,-' McINIKJE, James,F. (Af 1939) Mgr...Combustion- . ' .. . v 'Skaneateles. N.'Y. . ' ' . . .Equip. Div.. Enterprise Engine and Foundry .Co.-; McCUNE, Laban J. (Af 1943)-Bldg. Supt. & 18th and Florida'Sts.V'San Francisco." and *.1^00'` , - . Engr., Springer Interests, 118 E. SixthBt., Tulsa v-.3.:OkIa; . ... . ^McCUSKER. James P. (J 1944; S 1940) Student. : . .Catholic .University' of America, and *1445 ' Evaits St. N.E/, Washington. D. C. ' ' McDANIELS, .James A. (A 1944) Air Cond.. - Allison Div'., General Motors:.Corp.. Speedway' -City, and 4950 Ford St..-_ Speedway. City,' - .-''-.'Indianapolis 8. Ind. . : .. McDERMOTT.'John P. (A 1942; J 1939) Major. . C. E.; Asst. Div. Engr.; Alaskan, Div., 'Air. .Transport Command, A:P. O..462,.Minneapolis, ` " -"Minn.- ' - ' -` -MCDONALD, Frank'L. (A4T944)'Branch Mgr.. ' .*'Barber-Colmah - Co.; 816 -W. - Fifth St., Los - Angeles, and 1655 Rose Ave', San Marino, Calif.' - .-.McDONALD, Ivan' (A: 1938) -Capt.,- Overseas, ' ' ; -and MinneapoUs-Honeywell Regulator Co.; 117 46th.Ave., San Francisco 16, Calif. . -1 *. McINTIRE, James F.* (Af 1915; Ar. 1914), '{Presidential Member),-{Pres.. 1939; 1st-Vice- - Pres.. 1938; 2nd Vice-Pres.. 1937; Council. 1926->: . 28;-1932-40). Retired *320 Madison'Ave., Clear- water, Fla. ' . ' -t ' ^ - ` McINTOSH, Fabian C. - (Af 1921; 7.. 1917), . . (Council. 1929-31; 1933-35; 1942).-Mgr..-Pitts- ' ' burgh Office, Johnson Service Co.;T238 Brightbn T: . Rd;,'-Pittsburgh 12,' and 3650 -PerrysviUe .Ave.,. v Pittsburgh'14, Pa. McINTOSH, Robert M.` (Af. 1945) Mech. Engr., - * ' Harley-EUington & Day. 1507 Stroh Bldg.;, - Detroit,'-'and *15624 - Cleveland' Ave., -Allen - Park, Mich; , . ' y- - McKAY; Albert Wi'(Af 1942) Major..U. S. A.V-, / . ' and * 102 S.'Kensingtori SW Arlington. Va.-. ;v. ' . ' ' Peter St.i-Toronto. Ont.. Canada. - McKAY, William H. (A 1B45) Stipt. of. Stoker ~ '> MCDONALD,'.'John .J., (M 1943) Pres.. The Engrg. Dept.', The Winnipeg Supply & Fuel Ga., -' '. -' -McDonald Co.'; 43t47vLansdowne St., Boston, and - ..Ltd..-.8I2-Boyd`Bldg.'.-Winnipeg, and-465 .Scotia r-` : -.'*.401 Beacon St., Chestnut-Hill 67. Mass.' _ St'., Kildonan.-Man., Canada;-' ' -v,- McDONALD,1 Thomas (A 1931) Vice-Pres.. ' McKEE, James M. (A 1945) Engr., Payne F*urhace . . fs MihneapoliS'_Honeywell Regulator Co., 2747 . .Co- '336 N. Foothill ..Rd.,. Beverly.-Hills.''.'arid ' Fourth Ave. S.; Minneapolis 8, Minn, . ' ,- *1219A-19th SC, SantaMonica,-.Caiif:-. i ' McDONNELL, Everett Nr' (Af 1923), (Council. McKENZIE, Murdock C. (Af;.1938) Htg. Engr.. ` 1940-45) Pres.. # McDonnell Miller. '400. N. Southern California Gas Co.,-810 S. i Flower St.; > . Michigan, Ave.'. Chicago'll, and 219 Lake Shore and 3806 Boyce Ave.. Los Angeles 26. Calif.- - 4 'v - - .--- Dr., Ghicago,dll. ' * . -.' .. " McKERNAN, Gordori'S. ,<A'-1942) Secy.-Treas..' ! ' '.'McDONNELL, John E. (A 1936) Sales Engr.. . *Reg. -'H.: Steen. Ltd.,--12 .Humewoodj-Dr.t r * .. , v McDonnell',&' Miller;.400 N.- Michigan Ave., .' and7-Grimthorpe Rd.. Toronto 10,-Ont.. Canada.* '-?-, ' ..Chicago, and 2299 Lakeside PI.,'Highland Park, 111: McKINNEY, Carl A>(A 19S9; 7 1937)'Engr..; McDOWELL,:Harry L. {J 1939).Lt; U. S. N. R... United Gas Corp.. United Gas Bldg., and *'2136-. - *'c/o-A. &'R'-Dept.'.'Naval Air Station, Seattle,. . Addison-Rd.;-Houston-5.-Texasv - * ' * v ,, ` : '. T'-.r1 Wash,,' asd"112S Belt Line'Blvd., Columbia.,S. C. McKINNEY. William J;.(Af 1938; rA "1934).^' ..; V:McEAHERN, Edward-J.;(A-1945; J l944)Vice- . Southern-DisC Mgr.; American s Blower Corp..' '* Pres.; `William - A.;-Flatt -Co., 1031. Salia 'Fe, . Rm; 714--101 Marietta SC Bldg.; T:A.tIanta , 3;: 'Denver; and *4754 Raleigh St.,\Denver 12, Colo.- and 3363 Mathieson Rd.'N.E.. Atlanta; Ga. y- : mm 56 Heating' Ventilating Air Conditioning Guide 1946. \ ;V- j %'r". - ,r- '-z &&IT if^ v I ' - McKINSTRY, Merrill W..(A 1945) SupL.-W. E. McRAE, M. W. (if 1939) Research Engr.. Crane Beggs Co.,'234 Ninth N., Seattle, and 1825-41st ' Co., 836 S. Michigan-Ave., Chicago 5, and 816 k Ave. N.. Seattle 2, Wash. ' " "' McKITRICK, W.D. (M-1936) 125 S: Huron St.. . MFCaWirvIieLwLIAAvMeS.,,PJaorks'eRpidhg' ew, 1;1;1(. A" 1942) - .. Camera , -v Toledo, and *2335 Rosewood Ave., Toledo 6. ' "Works, Eastman Kodak Co., 333 . State - St.; .. - Ohio. - . ' .. - ' Rochester 4, and 71'.Lyndale Dr.,' Rochester 11, McKITTRICK, Percy A. (A- 1934) Treas.-Gen. N. Y. ' . Mgr., Parks-Craraer Co., P. O. Box 444, Fitch- MEAD, E. A. .(M. 1926) Sales Mgr., *The Nash "burg, Masa. , Engineering-Co.,'South Norwalk, and 5 Thames - . .. McLANE, E. H. (M 1944) Commercial Sales Mgr.. St.. Norwalk. Conn. .. - York Corp., 2201*11 Texas, Houston 1, and 1748 MEAD, H. K. (A -1939) Owner, *1100 Guardian ' Hawthorne, Houston 6. Texas. ` . - .. Bldg., Portland 4, and Jennings Lodge. Ore. . McLAREN, Frederic S. (A -1945) Secy.-Treas.. MEAGHER,. Arthur T. (M 1938) Dir. & Sales * Air Conditioning Engineering Corp.; 501 Sinclair . Mgr., Pibg. & Htg. Dept., William-Stairs. Son.&' Bldg., and *3704 Westdiff Rd. S., Fort Worth, . Morrow, Ltd., 174-190 Lower Water St., and *83 . Texas; -'_ ' Seymour St,, -Halifax, Nova Scotia. Canada. McLaren. T.-H. (A 1938). Asst. Gen. Mgr. & MEANS, James MacG. (A 1944) Owner. Mfrs. >. -Gen. Sales' Mgr., The James Morrison Brass - - Agent, 244 .Washington St.,. Rm. 433, Boston; - Manufacturing,Co., Ltd., 276-278 King St. ,W:. ' and'Off Proctor St.> Manchester, Mass. .. -. Toronto .1, ,and 65 Beaufort Rd., Toronto 8. MEATES, Richard F. (A 1944) 60-04-l53ril St.. . . Ont...Canada. ; . ' Flushing. N. Y. ' - . \ - " - -- . McLARNEY, Harry W. (Af 1933) Indus. Engr. MEDCALF, Lloyd C.'! (if. 1944) -Cons. Engr., - /-; Union"Electric Co. of.Missouri, 315 North 12th.,.. 100 Stevens Ave., Mt. '.Vernon, and 15 McBride - - . " --Blvd.," St; Louis- 1; and'807 Hawbrook Rd.,' Ave., White-Plains, N. Y. ' - Glendale, Mo. '' . MEHAFFEY. Robert V. (if 1945) Cons.. Engr.. McLEAN, . Dennid (M 1917) Mech. Engr.,-' Robert .V; Mehaffey. Associated Engrs., 30 N. . Snyder & -McLean, 2214 Penobscot Bldg., T^aRall** St., and 10563 S. Prospect Ave., Chicago. .. --. Detroit' 26, and' 14007 Lauder*. Ave., Detroit I1L -V - \ ; 27, Mich. - ' - MEHLEK, John F. (A 1945) Dist. Sales Mgr., : McLEISH. William S. (A 1932; J 1928) Chief. Erie-City Iron Works, 520 Unidtt Bldg.. 1836 Engr., The Ric-wil Co., and .3463. New Portage Uniontown Rd.,- Barberton, Ohio. - -* Euclid Ave., Cleveland 15,.and 3120 Chadboume Rd..- Shaker Heights 20. .Ohio. - - " .; McLENEGAN, D. W.* (if 1933) Designing Engr.; MEHNE, Carl A. (if 1929) Htg. & Vent Expert, - General Electric Co.,-5 Lawrence St., Bloom and *35 E. Livingston St., Valhalla. N. Y. ' field/and 39 Francisco Ave., Caldwell. N. J. . MEILLER; Daniel V. (A 1941) Sr. Design Engr.. MCLENNAN, Millard C. (if 1944) Supvsr Htg/ 'Public Service Company of Northern Illinois. '& Vent. Design, Puget Sound Navy Yard, Bremer-- 1001 S: Taylor Ave.,.Oak Park, and, 1819. South'- ton, and 1714 Fourth Ave. N.; Seattle 9, Wash.,. 16th Ave., Maywood, III.' ' . - .'-McLEOD, Clarence H., (if 1943).Application' MEINHOLTZ, Herbert W. (if 1936) ApplicaUon / Engr., * York Corp., 1239 Liberty Bank Bldg.,. - Engr., York.. Corp., York,*. Pa... and *'1615 N. ' Dallas'!,'and Campbell Hotel. Dallas, Texas. ' Springwood Dr., Silver Spring,.Md.- - ' McLOUTH, Bruce F., (if 1936; J 1934) *3445 MELLON, James T. J. (Life Member\ M. 1911), . Humboldt Ave. S.. Minneapolis 8, Minn., and'135 (Council, 1915)* Mellon Co., 4415-21 Ludlow ' .. Gunson St., East Lansing, Mich. '' - St,,' Philadelphia *4, and 431 North. 63rd St..-, McMAHON, Louis *A. (A 1944) Heating Engr., Philadelphia, Pa. ,- American Furnace--Co., 27.19 Delmar Blvd.. MELNICK, Nicholas A. (if 1941) Engrl. G. M.- . -.St. Louis 3, and 10 Magnolia, Ladue, Mo; Simonson; 625-Market St., and.* 279 Fifth'Ave.; . . McMAHON. Thomas W. (if 1928) Dist. Mgr.. ' San Francisco 18, Calif. . ' - American Blower Corp., 1711 Railway Exchange MELONEY, Edward. J. (if 1937) Vlce-Pres.- _ -Bldg.,-St.`Louis 1, and 6173-Waterman Ave.. Secy., Bowers Bros. Co.,-2015- Sansom St., . . r'St. Louis'12,'.Mo. ' ' Philadelphia 3, and 100 E.- Stewart Ave.,' Laos*, . McMASTER;. Sherman G. (A 1945) Mgr. of downe. Pa. - - - . : - ' . Htg.' Dept;, Richards Manufacturing Co.. 135 - ... Front', Aye. N. *W.. Grand Rapids'4, and -164 : - . Wallingwood Ave. N.E:, Grand Rapids 3,.Mich., . McMICHAEL, Chester L. (Af -1943) . Engr., . H.v H. Wright-Co.. .1322 Walnut St., Kansas ' ' City,' .Mo;, and *5519- Aberdeen Rd., Kansas ; - - - City, Kans. -. ' . ; MELTON, Rupert D. (A 1946; J 1942) Page &. | Co., 1001 N. Church St., and 117 W. Tenth St., - Charlotte, N. C. ' MENCH, John G. (if 1945) Mech; Engrl. James Stewart Corp.,'-231 S. LaSalle.St., Chicago, and' 915 Elm'St., Park Ridge, 111. ' ' ' ."McMULLEN, C. S. (A. 1945) Air Cond. Engr., 1 - ' *The -Trane Co., 'and 715 S. Fourth St.; La - . Crosse;*.Wis.* : - -' MENDEN.'Peter J. (if 1935) Cons. Engr., Rm. ' ' 503 Janes Bldg;, .and 1232 Hayes Ave.,'Racine, wis. - * * "... ; - McMULLEN,.'Earl. (Af 1938) Dir. of. Research. MENDITCH, Barney (/. 1944) Htg. & Air.Corid .-* The'iEagle-Picher. Co.', C & Porter Sts., and -.Olivia Apts.; -Joplin,' Mo. . .. - '* * Engr., American Heating Co., 55 .K'St,. S,E.\ . and 1651 Wisebnsm'Ave. N.W., Washington,' D:C. McMULLEN, Ernest Wl'fAf 1942)' Partner, MEREDITH, John,W.-(if 1944) Htg. Engr - -Ganteaume &'McMullen, 99 Chauncy St:; Boston, -U./S. Navy, Boston Yard, Charlestown, and 1 - - - .and 240 Winslow1 Rd., Waban 68, Mass.- " - Sunnyside Rd.,: Natick, Mass;1 ., - .j' - v. McNAMARAV William (A 1930) Mgr.'. * The MERENS, Seymour H.'(A: 1939) Owner,'* Max- \ . T .Trane Co., '850 Cromwell Ave., and 1355 Como Miller & Co.,' 823 N. California Ave., and 4955 . - Ave., St-Paul; Minru *--- - ' N. Whipple St., Chicago. III... ? . McNAMEE, Earl W. (if 1940) Engr., B,, &. J. . "''Jacobs.Co.', 1729 John St.. Cincinnati 14; and MERGARDT, Albert P. (A 1940) Prop.. Amen ' ran Heating Co.; 55 K St. S.E., Washington, . 2627'Ocosta Ave.. Cincinnati -IT, Ohio.' . -. `' D. C,, and' 3905 N. Fifth St., Arlington^Va....'.. - - >McNEVIN, Joseph E. (Af l937) Mgr., Colorado MERRILL; Carle J. (M 1919) Treas.. *C. J. r -v.v jHeating Co.; 950 Cherokee St.', Denver.4, and 1221 Merrill, Inc., 54 St. John St., and 31 Craigie>'St.,;'. V- c ShermanSt.-, Denver 3, Colo. ' ... Portland 4, Maine. - - - ' - ' ^McPHERSON, v William A. (M 1929) Chief. ;Htg.-Vtg. Div.; Department of School-Building, MERRILL, Frank A. (if 1934). Cons. Engr.. ' - Office of Hollis French, 210 South.SL, Boston,'. ; 26 Norman St., Boston, and *86 DwinneU St,,- T and 19 -Auburndale Rd.,. Marblehead, -Mas3. - .. ; West Roxbury, Mass.- * - .' * McOUAID, Daniel J: (M 1934) Owner. Dan J. ^McQuaid Engineering Service, 1742-46-Arapahoe . ' >^SU*.rDehver,rG6lo.'. r ' x- -'- .' . ^ i^McOUEEN, -Boston (A 1945) Engr., Hall-Neal MERRYMAN, C. P. (A l945).Owner; Merryman Wilson Co.. 121 S. First St., and 625 E.: Main St.,, .. - UnioiTCity,.Tenh. . * / Y-f. MERTZ, Walter'A. <M 1919)'Secy;V*The KeKm : Corp., 51 E. Grand Ave., and 3753 ,N.; Keeler..', .- ' - * *.; Funmce-Co.,- 1324.N.; Capitol Ave., and 541 '.---^'Dayioh.Ave., Indianapolis,Tnd.' ' - ^ iMcOUITTY," Roy M-(M.1945) Steam UtilizaUon "^Engr.i Union ; Electnc - Company. rof Missouri, Ave., Chicago. 111. ?` 7"- MERWIN,' Gile E. (if 1924; J 1923) Mgir., The. . . .7 Trane Co.,"5012'Parker St.; Omaha 4, Nebr. .METCALF, Ralph H. {M, 1944) - Vlce-PresI.'V `-.V:. 3_15.>Nwth'-12th:'Bivd:, St.:'Louis;, and 1219 High* Krem^ Hicks Co.. 13974 Delmar Ave.. St. ..1^; *.-^; --^''V.;..Iahd,T]erface,;Richm6nd'Heights, Mo. . . Louis, and 101 Jefferson Rd:, Webster Groves. i 'Roll of Membership - / 57- METZGER, A! F. (if 1940) Supvsr. of Steam MILLER/ Lorin G.* (if 1933); (Council. 1942 -Utilization Sec., * Allegheny County - - Steam 44) Prof. & Head Meda. Engrg. DepL, Michigan Heating'Co.', 435 Sixth Ave.,-Pittsburgh, and 3421 -. Sthte College, R. E. Olds Hall of-Engineering, and Horne St-.'Pittsburgh 19, Pa. . 232 University Dr..' East loosing, Mich. ' ' ' METZGER, H. J. (A 1937) Pres., Wheeler- MILLER, Mahlon S. (A 1942) Asst: Gas Engr., Blaney Co., 137 E. Water St., and 706 Locust St.. Kalamazoo: Mich. ' MEYER, E. Walter (A-1944) Partner, Keystone Sales Co., P. O. Box 4201, Bellevue Sta., Pitts burgh 2, and 6933 Prospect' Ave., Ben Avon, Pittsburgh, Pa. Iowa-Public Service Co., and 917 W. Main St:, Cherokee, Iowa: - - . - .* * ' 5 , MILLER, Norton R. (M 1944) Sales & Applica tion Engr.;.The Trane Co.. 250 'East 42nd St.,' New York' 17, and *188-17 Palo Alto Ave.,' Hollis 7. L. I., N. Y. .' MEYER, Frank L* (M 1932; J 1928) Pres., MILLER, Robert A.* (if 1931) Tech. Sales The Meyer Furnace Co., Peoria 2. and 9 Cole Court, Peoria 5, III. MEYER,.Henry C., Jr.* (Life Member; M 1898),. - (Council; 1915-16) Pres., Meyer, Strong & Jones. Inc., 101 Park Ave., New York, N. Y., - and 25 Highland Ave.; Montclair, N. J. - Engr., Pittsburgh Plate Glass Co., 2200 Grant' Bldg.. Pittsburgh 19, and 1211 Carlisle SL; Tarentum, Pa. . MILLER, Robert T. (A 1927) Chief Engr.. Sales Dept.', Masonite Corp*. Ill W. Washington SL, Chicago; lil. '' . ' ' MEYER, John S. (if 1945) Sales Promotion Mgr.. MILLER, Warren W. .(A 1945) Canadian Sales - W. A.'Case & Son Manufacturing'Co.. Buffalo, and *38iCrescent Ave., Buffalo 14,- N. Y. . MEYER, Karl A. (if 1938) Product Engr..' Herman Nelson Corp., Moline, and 2438-33rd Ave.. Rock Island. 111. MEYERS, Carl F. (A 1942) Engr., Coblentz `Equipment Co., 1119 Peach St., and *142 East 35th St., Erie, Pa. . * > ' "' ' MICHAEL, Arthur F. (if 1945) Gen. Supvsr. Air Cond.; Southern California-Gas Co., Box. . 3249 Terminal Annex, Los Angeles 54, and 5266 -' Dahlia Dr.. Los Angeles 41. Calif. -' ' 'MICHAEL, Leonard A. (if 1945) Cons. Engr., . ' 1346 St. Paul St., Denver 6, Colo. - ' MICHAEL, Robert K. (A 1944) Property In spector, The Prudential Insurance Company of . America, 500 Board of Trade Bldg., Kansas City,' Mo.,'and *620 Fairfay St., Denver, Colo. . . MICHIE.D. Fraser (if 1938;A 1930).Htg. Engr.,. . Engr., Frigidaire Products of Canada, LeasidP, and 112 Joicey Blvd.; Toronto,'Ont., Canada^MILLER, William ..P. (A 1945) Engr., The" Smith & Oby Co., 6107 Carnegie Ave., Cleveland:and 2129 Glenbury Ave., Lakewood, Ohio. . ? MILLER, William T. (Af 1938) Prof.. Htg.*& Vtg., Purdue University, and 525 Hayes SL. West Lafayette, Ind.- -' - _ - MILLHAM, Franklyh B. (if 1938). Engr., S. S. Fretz. Jr., Inc., 1902 Chestnut St:, Philadelphia 3, and 1810 Chelsea -Rd., Philadelphia 26, Pa.'1 - - MILLIGAN, Donald G. (A 1945) Asst. Mgr.,- Air Cond. Coil Div., McQuay, Inc., 1600 Broad way N.E.. Minneapolis 13, and 2419 Girard Ave." . S.,-'Minneapolis, Minn. - \ ' ' MILLIKEN, J. ill-.* (M T923) Repr' American . Air Filter Co., Inc:, 228N. LaSalle SL,-Chicago!,' and!021 Ridge. Court, Evanston, 111.;- i - Crane, Ltd., 93 Lombard St., and 465 Waterloo MILLIS, Linn W. (Life Member; M1918) Retired,- .. St., Winnipeg, Man., Canada.- . - arid 3534 Wabash Ave.. Kansan City 3, Mo., -. MlLENER, Eugene D. (if 1936) Secy.. Indus.& MILLS, Doremus L. (A 1943) Research , & ^ Commercial Gas Section,- American Gas Assoc.; - Development Engr., Revere Copper. & Brass, "420 Lexington Ave.. New York 17, N. Y. Inc., and J407 N. Madison SL, Rome, N. Y. MILES, James C. (if 1943)* Miles Heating MILLS, D. M. (A 1940) Mgr., Houston Div., . 'Enterprises, 1836 Euclid Ave., Cleveland 15, and .' - F. J.`Evans Engineering Co., Gray and Craw 1972 Ford Dii, Cleveland 6, Ohio. ' ` .. ford, Houston '3, and 2726 Robinhood, Houston MILES, Oscar K. (A 1945) Mech. Engr..' General 5, Texas. . ^ " . '' Engineering .Co., 301 West 13th St.,,ahd.2119. . Edwin St.. Fort Worth, Texas. . - . ;' ' MILEY,' Julian. J; (A 1945) Cons. Engr., Htg. . & Air Cond. 61-Florence Ave.. San Anselmo, Calif. MILLARD, Junius W. (if 1929) Comdr.. U. S- -Navy, U. S. S. Alcor'(AD 34), c/o F. P. O.. San ' Fandsco, Calif., and *3516 Vsdley Dr., Park-' fairfax, Alexandria, Va. - -. MILLER, A. T. (if 1938) Eclipse-Pioneer Div., MILLS, Hartzell C. (A 1935) Industrial Engr., Minneapolis Gas Light Co:, -739' Marquette ' Ave.,' Minneapolis 2, and 4137-lOth `Ave; S.; Minneapolis 7, Minn. - MILTON,.Taylor.(Af 1945).LL, C. E. C.. U. S.N. .Ri,* U. S. Naval Air Station, Minneapolis, and 1457 Scheffer Ave-.^SL Paul, Minn.; - v MILWARD, Robert K. (M 1943; A 1920) Branch .- Bendix - Aviation . Corp..'. Teterboro, and . 125 - Godwin Ave., Ridgewood." N. J. Mgr., U. S. Radiator Corp., 127 Campbell :Ave.,' and 2441 Calvert Ave,, DetroiL Mich. ' \ MILLER,. Charles A. {Life Member, A 1917) MINAKER,. Melvin E. (A 1945) Sales 'Engr.; ' The H; B'. Smith'Co:, Inc;, 331 Madison Ave., Minneapolis-Honeywell ' Regulator Co., '`.-Ltd:, and 2554 Marion Ave.-, Bronx, N. Y. - - 213 Lougheed Bldg., and 122-13th Ave. W;, MILLER,. Charles-W.- (if 1919; J 1908) Pres.. Calgary,-Alta., Canada. . .' -- The RadoCo.", .759 N. Milwaukee St., Rm.'204, MINER, H. Harvey (if 1944; A 1940) . Partner,- - Milwaukee '-2,- and R. 1, Box -'42, Menomonee ' Miner Supply Co.-, 129 W.-Front St...Red Bank, Falls, Wis. ... . and 87 Silverton Ave:, Little Silver, N. J: '' - - MILLER, David CL (if .1944) Chief Engr.,' Buetkel & Co., Inc., 24 Union Park St., Boston, and 5 Ellis St..-Quincy 69, Mass. ' - - ' MILLER,* Edgar R. (A 1935) Chief Engr., Win nipeg'Cold'Storage Co.^Ltd., Salter and Jarvis . Ave., and P. O. - Box 1384,. Winnipeg, Man., Canada. - . ' ' .; - MILLER, Floyd A. {Life Member; if-1911) - Retired, and 944 -Montrose Ave., Chicago. III. - MILLER. Frederick T. J. (A 1943) Service Mgr.. Hurst Oil Co., 924 West 21st St., Norfolk,, and ' 5713 Herbert SL,-Norfolk 2, Va.J.- - - - '. MILLER. George F. (if 1936) Sales Engr;, v Geo. F. Miller, 1614 K St. N.W., Washington 6. D: C., and 5608 Grove St.. Chevy Chase 15. Md.' MILLER, H. Deane (A 1944) Mgr., Air Cond: & Comml. Refrig. Dept., General'Electric Supply MINKLER, William A. (if 1940) AssL Mgr.,' ' Air Cond. & Refrig.'-Dept., *'B. F. Sturtevant Co... Div. of Westinghou&e Electric Corp*. Hyde Park, Boston36, Massi ' ' ' - ` -j'. MINOR, James E. (5 1943) LL G-g-). U. S. N. R.. and 1208'Cherry SL; Kalamazoo, Mich.' . MINSON, Frederick L. (J 1943) Marine Engr.J' ' U,, S. Maritime Commission,-5095 Commerce-' Bldg.. Washington,- D. C., -and 5, W. Glendale-- Ave., Alexandria, Va'. - * ` " -. -~ . M1RABILE, J. James (if 1945; A 1938) Engr., York-Shipley,'Inc., P.-.O. Box 349, and.* 1525 Third Ave., -York, Pa.. ' - , < MITCHELL, A. J. (Af 1938) LL G-g-). U. SJ N. R.. . Free Press Bldg., Detroit 26, Mich., and 1936 Dryden Rd;, Houston, Texas. = - ' Corp.; P. O. Box T919..Salt Lake City 12,' and' MITCHELL, Alva E. (if 1939) LL. U: S. N.-R., . ' 1866'Yalecrest Ave., Salt Lake City, Utah. ' MILLER, Jack (if 1936) *20 East 58th St.,. U. ,S. S. Repose (AH-16)r c/o F. P.^ .O.,' San Francisco, C^if., and 6501 Sligo Pkwy', Hyatts- ' Brooklyn, N; Y. " ' . ville, Md. ' - j . - - '' . MILLER. John W. (if 1941) Research Engr., MITCHELL, John'S. (A 1944) Indus, Mgr., - Motor Wheel'Corp-. Lansing 3, and*R. 5; Box '_ . Crane Co., P. O.. Box 155, and 1902 _Young 498,- Lansing, Mich..... " ' ... ' Ave.," Memphis. Tehh.- ' . MILLER, Leo B. (if 1926) SalW Exec.. Perfex. -MltTENDORFF, E. M. (if 1932)"Pres., Kramer Corp.. 500 W. Oklahoma Ave., Milwaukee 7, and & Mittendorff. 105 W. Adams SL, Chicago 3; and- *3481 N.iHackett Ave., Milwaukee, Wis; '' . *772 Grove St^ Glencoe, 111. .r -i/ _ ` 58 ' Heating ..'Ventilating 'Air.?,Conditioning.'- -Guide 1946 U \ :t<? . . MIZENER, Ralph. S. - (Af . 1944) Sales Engr.. MOORE, Henry W. (Af, l935)',Mgr.', Air/Cond..-. Parent &'-Klrkbride, Fourth -and"Locust St:-. - Dept., 20th 'Century- Refrigeration.'.Co.^.-1630. . -. , -Philadelphia 6. Pa., and * 1036 Grant Ave., West ' 1 .Walnut St.. Cinannati' 10, and 3164 Queen"City _ : Collirigswood.'N. J, . MOE,` Parker. A'r (Af1944) Cons. Engr* Gates, ; Moe and Weiss, 611-N. Broadway. Milwaukee 2.' - .and 3713.W: Branting Lane, Milwaukee 4, Wis. : MOESEL, F.AlberU(A 1939) Asst. Mgr.. W. A. Ave., Cincinnati 11, Ohio. :. -. MOORE, Herbert S. (A 1923)' Dist/ 'Repr.,' Iron. ' . Fireman Manufacturing Co. of: Canada. Ltd., *. ' 602 King St. W., and 107 - Cleridenan' Ave., . ' Toronto. Ont.,- Canada; s. . ; :''Case'"& Son -Manufaciuridg Co.,-31' Main St., MOORE, MacDonell (A 1940) Pres.. Geri. Mgr., o . . Buffalo 3." and 382 Argonne Dr.. . Kemnore,-N. Y. ' The Moore Fuel Corp.', 23 Rose'St., Danbury, ' '}\MOFFAT,1,Ormond;G. (Af. 1940; A 1937). Mgr.. and R. F. D. 2, Bethel. Conn. - . ` -. ' '-/Special Products Section. Canadian Westinghouse ' --Co.,` Ltd.,'Sanford Ave., and *141 George St.. . " Hamilton, Out.; Canada. * . . - MOHAN,-John F. (A .1944) Secy.-Treas., * Fox Supply. Co... Inc., 2229 Blake St., Denver 2, and t . 1280 St. Paul SU, Denver 6, Colo.' - . . -T- MOHN,. H. Leroy (Af-1937) Cons. Engr., Fitz- MOORE, R. Edwin (Af 1944; A 1928) Vice-Pres., Bell & Gossett ,Co.. 8200 N.. Austin Ave., - Morton Grove, 'and 425 Merrill' Ave., Park- Ridge, 111.'. ., . MOORE,- Robert E. (A 1943) Archt., Moody &'. Moore,- 216 Graham Ave., Winnipeg, Man., . Canada. - >- *.-. - . gibbons 'Boiler'. Co.`, "Inc.-, arid 71 W. Fifth St., . Oswego, N.VY. : i - `. ` - .. ' MOHRFELD; Herbert H. (A .1943;. J. 1935) ' Vice-Pres/ &' Treas...C.,>P. Mohrfeld, Inc.,-24- MOORE, RoScoe S. (Af 1944) Predpitrori Engr.; - Westinghouse ElwAric Corp.,. 20 Nl -Wacker Dr..-Chicago 6; and 226 N. Humphrey St.. Oak' ' Park,"111. - ' -Lees .'Ave','.CoUingswood,1'and T670 Station Ave., 'MOORE, Wesley R. (Af 1937) Regional' Mgr- ` Haddonfield/N. J. ~ r-- . .. -'Minneapolis-Honeywell.. Regulator Co.*i -5005 . . MOLER,.. William H. . (Af 1942) Dist..-Mgx., -Euclid-Ave... Cleveland,-arid 14211 Ashwood Rd., - - 'v Govemair Gorp., -504 Great National- life . Shaker Heights. Ohio. , v ; * j'/-- - Bldg.,,Dallas, and 3928-Lovers Lane, Dallas 5, ' MORAN,.Edward'V., 1945) Engr:, Carrier. . . -Texas. *_ . 'Corp.-.- 300 S. Geddes SL.-Syracuse, and * 115 -y ' ?' MOLFINO, Philip:(Af 1938) Partner. Lefend & . Oakland Ave.,-Tuckahoe. N. Y. . - - - Haley, 58v'Sutter St.',-San-Francisco-4, and 125 MORAWECK, Alvin H., Jr. (A 1946; J 1941) , : Clayton St.YApt. 2, San Francisco 17, Calif; .. ' Ca'pt. Cavalry, O. G., Ft. Knox, Ky., and 36 . -; MOLLENBERG,. Harold J(Af 1936) Pres.. Woodland'Rd., Maplewood.'N. J.'* -- >" i"- ' Mollenberg-Betz Machine Co., 22- Henry St., ' MOREHOUSE, H. P. (Af 1933) Gen. Hti & Air ' . Buffalo/and 111 Saratoga Rd., Snyder 21, N. Y. Cond; Repr.', Public .Service Electric &,.Gas Co.,';,-*;. MOLONY,. James-J. (A *1944). Steam-Engineer,. 80 Park PL, Newark, and 30 Timber'Acres':Rd.-, . . v.- Nebraska ^ Defense' .Corp.,,' Fremont, and 106 Summit, N. J. - . - . ` *' I- i North 49th, .Omaha, Nebr.' . MOREHOUSE, J. Stanley\(Af."1938) Dean ofviv . MOLONEY, Roger R. .(Af 1937) *26 Bonner Ave., V Erigrg.. Villanova College, Vilianova, and' 102 - -. - Manly,' Sydney, Australia. '; ; . " Uandoff Rd.. Upper Darby; Pa.. .* . MOLTZ; Bernard S. (A 1945) Erigrg. Draftsman, MORGAN, Arthur S. (Af 1938)' Mgr^-Fess Oil- . Staridard Engineering .Co., 2129 Eve. St. N.W., " Burnere of Canada, Ltd.. 85'King St;W., and 156 ". and *1293 Brentwood Rd. N.E:; Washington,-D.C. Glenmanor Dr., Tororito, Ont., Canada. " ; MONAHAN,-Maurice B. (Af 1944) Mfrs. Agent,'. MORGAN, Edwin H,, Jr. (A 1946; J.1942) Chief *. - *.1410 StanleyStYarid 5537 Trans Island-Ave..* Draftsman, American-Cyanamid Co:,-S. Cherry . Montreal, Que., Canada. - , .* ' St:,,and *180 North St.', Wallingford, Conn.-'' --- * ', i . MONGILLO, ' Alphonse J.? (A"1945). Prop.,.- MORGAN, George R. (Af l945)4artner &J>ept. * . Av..J.-_Mongillo" Co.. .928 .Grand. Ave.,- New- Head.'. J. .E. Sirrine.&'Co.-, and'306 Overbrbok ;' . .. Haven li,-and'20 Marvel Rd.; New Haven. Conn. -Rd;,'Greenville,'S. C-"'. ' -` /'*. ''*. . MON1CK, Tred R. (A:1936) Mgr..,American - .- .. Radiator' Standard Sanitary, Corp.,. 605 E.. .. - Eighth St,, arid 1114 S. Sixth Ave.,'Sioux-Falls, s d. *v s . ' . . " -MORGAN, .Robert C. {Life. Member;. Af 1915) . Chairman of the Beard; Stewart A;*Jellett Co.,'; " - 1200 Locust SL. Philadelphia, arid 314 W. Sey mour St., Philadelphia 44, Pa. - MONIES, Ellis A. (Af 1944)"Htg. Engr./. Eastern : MORGAN,' Robert-L. (A 1945) Owner;Morgan'.' '.. - .Pennsylvania.Supply'Co.,,56 South Penria. Ave., :. Appliance Co., 706-.West Gray,, arid- 607 West'1' :. Wilkes-Barre.:and Pioneer Ave., Dallas,`Pa. ; Gray,.Houston; Texas;.0 MONTESANO; Frank P,'*(Af.1944) Mgr., The , MORGAN; Robert.-W. (Af 1938) Asst/ Chief - . V Frank Ai-McBride Col; 158-60 Wan! St., and *117 . Engr..-*Bridgeport-vThermostat Co.,*1225 Con^, ' Geriessee-Ave:, Paterson, N. J.- ... . necticut Ave., Bridgeport, and R. F.>D. 1', Nor- ' . ^.MONTGOMERY, Edward G.;(A 1938) Special walk,'Conn; 4 V- ^ . ; Repr., Steel Co.;-ofvCanada; Ltd/, 525 Dominion.' MORIARTY, Jobn^M. (Af 1937) Retired, and - -St...Montreal, and *20.Finchley Rd,, Hampstead, ; 1616 Baldwin Ave.,-Arcadia, Calif. " ' C -' j - Que.', Canada. .- - .. MORIN;, A. R. .(A 1938); Co-Own^-;. Mr'"& *V. r MONTGOMERY,'^J.. Russell (A 1937) Mgr... :Supply Co', 911 N..Walnut St;, Oldahoiria^City 4, ; -? .... Standards;. Research * Truscon Steel . Co.. - and *2115 Sherinan, Oklahoma Git^, Okla. '! "Albert St/, ^Youngstown, and.296 Granada. Ave.. MORIN, Romeo.P-(A 1944) In Charge;of.Venti-. . ... -r\_v' -Yourigstbwn.4,' Ohio. ,.' - ' -J:` ... ' - - .* lation, -.Gibbsv &-. 'G6x (Branch" Office);--Todd ". i'vMOODY; . Lawrence `E. (Af'.'1919) -Partner, '-Hoboken Shipyard. Hoboken.- N.. J.,;and>3337' . - . # Moody -Hutchison,- 1420-Walnut St.; Pbila- - '89th St.; Jackson Heights, N. Y.`. , '-'`.V - - delphia 2, `Pa., and 224 Bellevue Ave.',- Haddoii^ - MORRIS, C. Raymtfnd (Af 1938)' Pres.,'* Power,. . . -field, n: j; . - 4 -v , - -& Heating Equipment Sales, Inc., 56.N; Spring-. .. MOON,-L.'Walter (Af 1915). (CouncU.-1933^36). .Vi-Pres,, St. Louis Industrial Truck Co;, 7700' - ,E. -Railrorid-"Ave.; and *1137A Hornsby Ave., V St. Louis 15,- Mb. - .' ' - v Garden Ave`,, Nutley, ' I:''/- - a - MORRIS,! Edward J. (Af 1942) -Mgr.,' Morrisr .. Engineering Co., 813'N. GalveifSt:,'Baltimore 2, - and 3414 Gwynns Fall Plcway.', Baltimore. 16, Md.; - MOONEY,' .`Bernard '-Pi,. (A' 1945)*-'Owner, i - Mooneys, 820 W. Lake, and "4745 France' Ave. *' S-. Minneapolis, Minn. ' * -v - MORRISON, Chester-B; (Af . 1931) Managing ; Dir., York-Shipley. :LtdI; North'Circular'. Rd;; '* -Hendon. London N.W.-2; and 60 Harley.'St'.,-. ! MOONEY," Mark E.- (/I , 1945) Dir of Sales,, London S-W. l, England. **' .*' - / Applied Refrigeration, Carrier ' CorpTj' Syracuse, MORRISON, Frank (Af l943) *Hali:Neal Fur-. . and 125 Butternut Dr., De Witt,VN. Y. ' - nace Co.. 1324-N. `CapitoL IridianapoUs.' arid'V- , -MOORE, Frank C: (A 1938) Mgr., Aerofin -Div.7: . Cloverdale, Ind.-- *: ' c' .. - - / ; .- -. v : . Vapor,'Car . Htg. Co. of .Canada,' Ltd., 67 Ybnge MORRISON. W-Bruce (A 1942; / 1939) Cons; . - . l St., Rm.' 1104, and *44 Lola Rd., Toronto, Ont., . Engr;. Bedell Bldg., .. Portland/4;-.and T805 %: > Canada., ' .' MOOREi.H: Carlton* (Af-1935) Engr.,.Metcalf & Northeast 27th Ave., Portland 12,- Ore.- - . ' MORRISON, W. L. (A'1943) U. S. N. R., U. S. S. , ;Eddy,7>1300 ..Statler- Bldg.; Boston, and *145 Jubilant A-M 255,r.F. P;.0:, New^York N:rY,, J. ....`.-..'.-Bea. timo.ntr.Av.e.r.'Newtonv. iIle 60, Mass. *' . .'V` ' and 3422-16th, Great-Bend, Kans. - - i MOOREj^H: Lee ;(Af 1919). '(Council.1927^28).MORRO. John J. (Af 1940)'Engr. & Geri. Mgr.v - v. . .tEngr:, *431' Fulton :Bldg., -Pittsburgh^-22. arid /'- '-'Paragon Oil JBiifner-Corp.. -Brooklyn, and'* 130 - ' 7065 ~Fla..c..c..u. 's Rd., Ben A* von,..P...i.t.t..s..b...u..r..g..h....2. ....P. a....' ; East'^Rh'Sq NewjYork, N; Y: ' *v> V. MORROW, Albert-P.T (A 1944) :Erigr:. Wm. S. MUNKELT, Frederick H. (Af 1938) Vice-Pres.. . . Scull Co.,. Front &-Federal Sts., Camden,'N. J.;. . ` W.-B. Connor/Erigrg. Corp.; 114 East 32nd St... "'-' arid 237 Maple'Ave'-TNorth Hills, Mont. Co:, Pa.. - New York 16, Md 317-East 17th St.v-Brooklyn' . MORROW,. J.- DeWitt (A 1938)-Prea. :&- Mgr... 26, N. Y, - r- ' - >' ' .The'--*Warren. Co.. Inc.', 614 -Walker" Ave.;, MURDOCK, Charles El (Af .1944),Plant Mgr.. . * . Houston 2..arid 5503-LaBranch, Houston, Texas.. Rheem Manufacturing Co., Stokermatic. Div.,/ A-- . -MORSE, Glark.T. {Life-Member; Af 1913) Pres., 1415 -South State. Salt Lake City-4, and *1254 . : . American Blower.Corp'., P. O.'Box 58, Roosevelt - ' E. Third S., Salt Lake City 2. Utah. .- n. ' . - Park.Annex, Detroit 32, and Hillcrest Dr., Bloom MURDOCH, John.P. (Af 1937) Pres.. John P. ' ;- field Hillsr Mich. : : . > '- ' ' Murdoch Co., 3630 Haverford Ave., Philadelphia: . MORSE, Elwln .F, (/ 1944) Field Engr:, #B. F. 4. and 204 Glenn Rd...Ardmore. Pa. ' ;'. . ' Sturtevant Co., Div. of Westinghouse -Electric MURHARD, Erroll A.-(Af-1939) Partner, Muir- * ' . Corp., 933 Leader Bldg.', Cleveland' 14, and 15126 . head & Murhard Co.,.801 S.W. Stark St:, Portland , ; *.-. Clifton Blvd., Lakewood 7, Ohio. . .. -. 5, and 2805 :S.W. .Greenview - Court.'1 Portland - . MORSE. Louls S.; Jr: (Af 1938; J 1936)' Lt.. * 1; Ore. ; - - > .* s'** sU. S.- :N; R.^'arid Lone Pine Rd^ Bloomfield MURPHREE, Robert L. (A 1940; J 1938) Engr. 'C . --Hills: Mich. .-*. . ,t- .\ Owner,`Rogers Plumbing & Heating Co.. 2127..-, ..'-V MORSE, Robert D. (Af 1936) 414. Vance Bldg..? Eighth St;, and P. O. Box 864, Tuscaloosa, Ala: '' . - Seattle'!, and 4316 East 43rd St., Seattle 5, Wash. MURPHY,'Charles G. (Af 1942) Foundry Engr., - - MORTON, Harold S. (Af 1931) Col., Ordnance Wright Aeronautical,. Lockland, arid*25100 . V.- : ' Dept., Amm; Div., Office Chief of Ord., Pentagon Treadwell Ave.. Euclid,-Ohio. ' v -- - " ' - `t :Blig:, Washington, - D. C^'.and *7331' Piney MURPHY, Daniel C. (A 1940) Sales JRepr...' . C Branch.Rd.,,Tsik6ma Park, "Md. - *C. A. Dimham Co., 214 Old Colony Bldg.. . MORTON, Paul S. (A 1943; J 1939).Htg.; PIbg.. - Des Moines 9, and 3900 Grand Ave.,-Des_Moines. - ` Elec;; Sales'" & Engrg., *609Bangor" Rd.; Law . reri.ee, Mich. ' '' ' : -. MURPHY, Delaoour l. (Af-,1941). E. C. Cooley , `;V -MOSES. Waiter B., Jr. (A 1946; J 1940; S 1936) 'Co., 625 Market St.. San Francisco, and 3027' -f ` ' ., .Sales Engr., 7836 Saint Charles''Ave., New - Milisbrae Ave., Oakland'5, Calif. " ' . \ Orleans 18,.La.. *. ' ' * ' * : MOSHER,/Clarence H. (A 1919) Owner. #C. H. MURPHY, Edward T * {Life Member; Af 1915)-; - : . . Sr. Vice-Pres., Carrier Corp.,`300 S.-.Geddes St:, ` - - .- ' .'.Mcher, .423'Ashland Ave.. Buffsdo 13, N.: Y. . - Syracuse 1, and 1055 James St., Syracuse, N. Y. /; MOSHER, Harold.:A;. (Af rJ945) ^Mech. Engr.,. MURPHY, Eugene F. (A 1944; J 1942) Instructor* - x EasUnari*- Kodak ' Co..^ Kodak '...Park - Works, in Mech. Engrg.. Dept.'of - Mech. Engrg.'. Uni- . .' - .CRbchester 4,` arid' 287 Winona' Blvd.,-- Rochester . versity of California, Berkeley 4. and Staff,Engr.. ,, . 5,sN. Y. . -' Committee on Prosthetic Devices.- Rm. 355, N.W.- , : MOSS, Alfred W: (A<1945; J. 1943) Walter : Technological Institute, Evanston, 111. .... -. '.- Wobds,; Ltd., Winnipeg, .and 26-Ferndale Ave., s MURPHY, Howard C.f (Af 1923) Vice-Pres., . -.. Norwood,*Manitoba; Canada. /. MOTZ, O; W. (Af 1932) Cons.-Engr.; *920 E. . ' -McMillan SL. Cincinnati 6, and! 2605.-Briarcliffe . 'Ave., Cincinnati.13, Ohio. : -MOULD, Harry W.. Jr. {J 1941). Engr.. Fedders American Air .Filter Co.,' Inc.. 215 Central^. - Ave., and'495 Llghtfoot Rd.. Louisville, Kyi-,-;. - . MURPHY, Joseph R. (Af 1934; A 1925) Vice/' Pres.. Taco Heaters. Inc., 342 Madison Ave., : ' New York, N. Y., and Terrace Ave., Riverside, >- - Mfg. Co., .Inc., 57 Tonawanda, Str. Buffalo, and - 44-AUeganyAve.. Kenmore. NrY.-.' - :MOUNTFORD,;Ralph; E. (Af, 1945) Asst. Plant* .Mgr., S. Smith & Sons' (London),. Ltd., Crickle-1 - Conn. " MURPHY, William W. (Af 1930) Treas:, W. W. : Murphy Co., 424 Worthington St...and 25 Mans^;. . . : ' field St., Springfield. Mass. : ' ' v .. \ ' > 4- wood, London. N.W. 2,.arid *67 Femcroft Ave., . Eastcote..Middlesex, England.* .. * -. MOULSDALE, Thomas DeWltt ^Af 1943) Htg. MURRAY, G. F. J. (Af 1944) Tech. Mgr., British - Doby Stokers.'Ltd., 80* Grosvenor- St... London -. W. 1, and *8.Homewood- Rd., St.'Albans; Herts.,-. Engr.; Lehigh-Valley Oil'Co:, 1200 Walnut'-St., - -England. !v - . . v. Allentown, and *818 Coleman..Easton, Pa. ; . ..MURRAY; H. G: S., (Af 1942; A 1941; J J936) "MO.YNAN, . Joseph S.' (A 1945) Engr.,; New" ',* Sales Engr.,' Canadian Comstock Co., Ltd:. 206 ' ;. ' Orleans Public Service: Inc.. '317-.-Baronne St..','*-- Laird Dr.. Leaside. and 28v Rosedale Heights - and ^11 Spruce St., New.Orleans, La. ' Dr,, Tororito 5, Ont., Canada: , MUCKLE;.- James M.- . (Af-. 1939) Anderson. MURRAY, Thomas F. (Af 1923) Sr. Htg. & Venr Meyer &-Co:, Ltd.,-.570 Lexington Ave., New' Engr^ N. Y.'S. Dept. of Public Works, State . - -. * .' ' York, arid 34-12 Murray-St;, Flushing, N.'Y; - * Office Bldg.. Albany, N. Y.` : :1 ... MUEHLIG, Elmer J. (Af 1945) Conrtr. Engr.. MURRAY, William A. (Af 1944) Pres:, William - . - F. W. Woolworth Co.', 800 U. s: National Bank; A..Murray, Inc., 967 Farmingion'Ave.; West, ; Bldg.,-,Denver,] 2,vand 1930-Holly St.,'.Denver Hartford, and *43 Fairlee'.iRd., .West Hartford. 7. Colo. . .7, Conn. ' - *" : / ^MUELLER, -Ervin^J. (A 1944) Sales Engr., .MURRAY.-WiUlam W., Jr..(Af 1944) Executive - -SuUivan-VaJve & Engineering Co.;-.9lO S, Arizona . . Vice-Pres., Almirall & Co.. Inc.. 53.Park Place. i- -' ` :-St.,*'and *1928 Lowell Ave.',*Butte,' Mont. ` ' ' ' New York 7,. and^ Thornwood' Lane, :Roslyri*. * . MUELLER,' Hrc. (Af 1936; A 1930) Pres. & Gen. Heights, L. L, N. Y. .... .. . L/jMgrL.e-The Powers.Regulator-'Co.,'-,2720'Green- MURSINNA,GUbertP. (4 1939) Owner, Gilbert \> 'view-Ave.,' Chicago -14.- and 1277'Forest'Glen ? - 'P. Mursinna,' 640 Tafel St., Cincinnati_14. and . , ... - - Dr.-N., Winnetka, IUr' .` - 3657'Boudinot Ave., Cincinnati, Ohio. : ' / . ; V MUELLER, - Harold Apl (Af 1936). Pres., L. J. MUSE, Mayland H. (A .1944) Mgr.'& Owner, , ' Mueller-. Fumads .Co'Ti; 2005 W.`.Oklahoma Ave., `Southern Welding .Co.', .-Box 454, .and 1010. ''. sand 511. E. Monrovia Ave., Milwaukee, Wis. - 'Melrose Ave., Oakland-Gardens. Johnson City,"-- *1 . /. MUELLER, Johri E. (M-^1937) Mgr.. Comml. --Tenn'. ' ; - - .. -s .Customer-Dept.,- West Penh Power Co., .Box .MUSGRAVE.MerrmN.CAf 1944;A 1935)Owner, - -- . - .1736, Pittsburgh 30; and-387 Broadmoor Ave., : '.Merrill N.'Musgrave Co.,' 2019-Third Aye;,7` : N - Pittsburgh'16, Pa. w - ... ; Seattle I, and 1610 E; Boston .Terrace, Seattle 2} -* MUESSIG, Janfes .W. (Af l938) SaIes Engr.. -- Wash-. - . .: 'V,. : ; ; Clafage Fan .Co..\ 333 N.Michigan/Ave... MUSSER, John M. (M 1942) Mech. Engr.. V. S; - - .Chicago.^and 405-Lodge-'Lane;:>Loriibard, III: - . Engineers, Hanford Engineer Works,-. P. O. Box.. -. * ., y.- MUIRHEID, Johii G: (A; 1940;' J, 1937) Vent.' . 550, Pasco, and *1314 KimbaiL;Richland. Wash.*/. *' j > - y. t/Engr.; Bureau of Ships, Navy Dept.;- Washington.' MUTTI, Arnold . J. (Af'1944) Electrical t Erigr., ' D;C.'. and *1201 M St. N.W., Washington 5, D.C. : Albert Kahn Associated Architects 8c--Engineers., v-* j .. ' MULHOLLAND; Daniel ,'J. (A .1945): Supt./ *. Inc.'New Center-Bldg.. Rm:' 1008, Detroiti-arid^' " ' ' "' /. Consolidated Conditioning-.Corp:, 460 S.-Tenth. .' 868 W. Bethune Ave.'; Detroit 2, Mich. '~-'\'y , .*' .'Ave.;, MC `Vernon,-.and 381 'Broadway, Dobbs- , MYER, Haydn (A I940)' Pres., Haydn. Myer . - .. Ferry, N. Y.-:v:` ' . v" - - .Co.', Inc.; 2224Corner^BIdg., Birmingham'3,-and'.> MULREY, Maurice D. (Af 1944) Owner, * T."A:. 1411 Avon'Circle, Redmont Pairk, -Birmingham ` - - i t ...v_,,'.Mulrey.&Sori,-3161 N/-Illinois St:,'.Indianapolis-. -/S. Ala. - i-. - - - ' '-8rjlnd. . MUNIER. Lebn-.L;- (Af 1919;: J H9I5) Pres:. Wolff &-Munier;' Inc.,*222-East 41st*St.. NewYork 17,- and 63,'Columbia Ave.. Hartsdale/N. Y. MYERS, George W. F. (Af 1930fA'1928; /-1923): <!% ' Owner,.Myers Engineering-Equipment Co.;.3800 v. v -W; Pine Blvd.. St. Louis 8, and * 476. Pasadena,-- ^ >.y ': Ave., Webster Groves 19, 'Mo. : -.' - * '-f - .:< <^ /-/.vr/ ' '77-7 60 ,f|V -'-Vr- "- -.- /-r-:: vv/;-. Heating' Ventilating Air ' Conditioning Guide l946 /. : .'.r'v-' .* ;-MYLER, William M,, Jr.* (M 1937) Chief Engr., NELSON, Norris T. (J.l 1944) Designer. Htg;.. " -Janitrol Engrg. 'Dept.. Surface Combustion Vent; & Air Cond., Bethlehem Steel Co.,-20th and . ' Corp.. P.`O. . Box 267, Columbus* 16, and 1545 - Illinois, San Francisco.-and #2421 Buchanan St., ; ' Grenoble Rd., Columbus, Ohio. . San'Frandsco 15, Calif... - -- -- ' MYRICK, James W. H. (Af 1944) Engr. & Owner NELSON, Raymond A. (A 1945) U. S. Air Con- . . New-England Air Conditioning Co., Boston ditioning Corp** 2101 N.E. Kennedy'St., Minne- t -Globe Bldg.,' Rm. 431, 244 .Washington St., apolis, and 3810 Upton Ave. S., Minneapolis . . -Boston 8. and South Duxbury, Mass. - 10,* Minn; ' '. MYTINGER, Kenneth L. (Af 1943) Gen. NELSON, Richard H. (A. 1933; 7 1928) Pres. & < Management, Mytinger'Air Conditioning Co., ' Gen. Mgr., The Herman Nelson Corp.. 1824 , Inc., 101 'Park Ave., New York 17, and 38-19 Third Ave.. and e 1303-30th St.. Moline. IU. .. 50th St., Long Island City, N. Y.' / NELSON, Roy O. (Af 1938) Asst- Sales Mgr.. ' Marsh Heating Equipment Co.. 2120 Southport *..'1 . -- -' - . . N : ; ; . Ave.,..Chicago 14. ande5636.N. Bernard SC Chicago 45,- 111. . . .NACHMAN, Geoige k (Af 1938) Treas., *The NELSON, Vernon E. (A 1945) Mgr., General ' . . Spohn Heating & Ventilating Co., 1775 East 45th Heating Products Co., 3353 University Ave. S.E., ` .St., Cleveland 3, and 2887 Falmouth Rd., Cleve- -and 5226-34th Ave. S., Minneapolis, -Minn.- '- ' land 2, Ohio., ' - .. NELSON. Walter L. (Af 1945; A 1944) Chief ' " NAMAN,, Israel A. (7 1940) Mech. `Engr., Ray- * .Mech..;-Engr.; District -Government, District . : __ mond.L. Jenkins. 4316 Blossom. Houston,'and Bldg., and 2225 'Quincy. St. N.E., -Washing . *402 Avondale Ave., Houston 6, Texas; - . *' ton. D; C.'"- . . - . `NAPIER; Charles E. (A 1945) Sales Engr., Con- NEMEC, Frank L. (Af 1945). Cons. Engr.. Hudson - /Tsolidated Engines & Machinery Co., Ltd., 200 & Grady, 525 Market St., San Francisco, and . -Bay St.,.and 1'44 St. George St., Toronto. Ont., '' Q?ada. - . 1NAROWETZ, Louis L., Jr. (Af 1929; A 1912) 1140 Oxford Rd., Burlingame, Calif. - ' - - - ` NESBITT, Albert J.* (Af 1921) Presi, * John j: Nesbitt. Inc., State-Rd. and.Rbawn St.. Holmes- 'iv^Pres.,.Narowetz.Heating & Ventilating Co., 1722 - Washington Blvd., Chicago 12, and *945 Michi- / '' 1(T-- , 7 gan,- Wilmette. Ill; n,, arIVv--EY, S. (--7 1943) FlL/SgL, No. 8 Repair 7 Depot, RJ C. A. F., Winnipeg 6, and451 St. Johns- 7 Ave., Wp. 6,Manitoba,Canada.' -* 7~~ - " / NASS, Arthur F. (Af 1927) Pres., McGinness, /' Smith & McGinness Co.,' 527 First-Ave., Pitts- -.burgh 19, and 29 Elmhurst Rd., Pittsburgh 20, Pa. burg, .Philadelphia 36, .and Rockfield Farm. Tennis Ave. and WelsHlRd., Ambler, Pa. - . ' NESMITH, Oliver E. (A 1936) Dir. of Engrg.- & - 'Research, Eureka Vacuum Cleaner' Co.,-- BeU & Hanna, and 107 Warner,- Bloomington. .IU; > ' NESS, William Hi C. (Af 1931) Secy. & Gen.% Mgr., ' Master Fan Corp/. 13231. Channirig - St.. . * Los Angeles'21, and 215!,N. Kingsley Dr.. Los Angeles; Calif. ' ' -. ,, - ' . > ' ' 7/':/ <i NATHANSON, Max (A 1943) Owner. & Gen. ` - Mgr;, Canadian Armature Works, `6595 St. UrbainVSt., and/ 5457 Victoriar Ave., Montreal, r Que/. Canada. ' ' . NATION, Oslih (A 1944; 7 1942) Mfrs. Repr., NESSELL, C. W; (Af 1937)-Asst, to Vice-Pres.. Minneapolis-Honeywell -Regulator Co... 1101 ' Vermont Ave. N.W., Rm. .405. Washington. 5, D. C., and 2120 Forest Glen Rd., SUver- Spring,- Md. .- , . .. - ' V.'. V 9702 El Patio Dr., Dallas 18. Texas. . NEST, Richard E. (Af 1936) Cons. Engn. General ] NATKIN, Alfred J. (Af 1944) Partner & Office Oil Burner Co.. 1623 N.' Aisquith St., Baltimore 2, ' . Mgr..,* Natlrin & Co., 1418 San Jacinto, and 2327 .Quenby, Houston, Texas. .. and *6000 Pinehurst Rd.,'Baltimore 12, Md.. - ' NEUBAUER, Edwin W. (Af 1939) Engr., Camp- ' :NAYLOR, 'James F;, Jr. (Af 1944) "DisL Mgr.. ;. bell. Norquist & Co.,. 1127 S.W. Morrison St., T - . *The TraneCo., 3930'Lindell Blvd., St. Louis 8, 'Portland 5,' and 4804 N.E. Davis, Portland 15. ' 302 E. Argohne Dr., Kirkwood 22, Mo. - Ore. . . - *' = -NEAL; James P. ,(A .1939) Capt.. U. S. Army.. NEVIN,'J. F. (Af 1944)`Major. A. B. R. O. 427.. .. ` Cincinnati Ordnance Dist., 230 E. Ninth St,, and S. O. Refrigeration, Hq. Allied Land' Forces. ^ ". 1428 Herschel Ave.. Cincinnati 8, Ohio. . S. E. Asia, Singapore; . - - : NEARINGBURG, Arthur'(A 1938) Sales Engr., NEWBY, Ira P. (Af 1941) Htg. & Fuel Unit, -.-. Sheldons,'Ltd., 1221 Bay St..'and 130 Floyd .. Ave., Toronto.-OnL, Canada. . ;. - U. S. Army, 8th* Service Command. Santa Fe Bldg., and 6262 Prospect, Dallas 14; Texas.* . . NEE,- Rflymond. M. ; (Af 1936) Power Engr., American Cyanamid Co., 30 Rockefeller Plaza. -v-V:NeW-York 20, and,5 East 82nd St.,.New'York - 28,-N.Y. *- . . NEWMAN,.-Harold E. (Af 1938) Owner & Mgr.. . . *J; F. Dickinson Co., 716 Tenth St., and 514 . . High St;; Modesto, CaUf. . NEWPORT, Charles.F.* (Life Member; M 1906) ... Sales. Engr.; Weil-McLain Co., Michigan City, . - NEILANS, John L. (7.1943) Draftsman, Trane Ind., and *10001 Longwood Dr., Chicago 43.- 111. - /Company of'Canada, Ltd., -4 Mowat Ave., and -NEWTON, Albert E. (A 1943) Engr., *Hall-NeaI . ;' / : .330. Woodmount Ave., Toronto, Ont.,' Canada: Furnace Co., 1324 N.- Capitol Ave.; and 4515 E. .. -*v ..NEIMAN; Charles H., Jr. (Af 1945) AssLDir.. .-.Washington, Apt'., 1, Indianapolis,' Ind. ' ' .. .of Engrg.,/.York-Shipley, Inc., Jessop--Pl. and NEWTON, Alwin B. (Af . 1938); Chief En-., --'-/P. R-7R-, and *330 W. Jackson St'., York, Pal Chrysler Corp- Airtemp Div., 1119 Leo - St., " . , NELSON,. Arthur W.* (Af 1944)'-Major. C. E., Dayton 1, and * 905 E.'Schantz Ave., Dayton 9; :U;S; A:, Hdqtrs.-Military Govt., U. S. A. F. I. K.,' /Ohio. . -- \ - . . -' "Engiiieer. Anny Administration Sec., A. P. 0.235, NEWTON, * David A.' (Af f 1944) Chief Engr., . i ** '' c/o P. M.,' San Francisco. Calif., and *12 Sylvan - Larkin Coils, Inc.; 519 Memorial Dr., and *55. . . LRd,,.Sharon,.Mass. . ' -./ ` - 25th St. N.W., Atlanta, Ga. NELSON, Axel A. (A 1942) *R. 4. Northcrest NEYHART, Floyd . B.-(7 1945) 7 Mech. Engr.. - . Sub!Div., North Kansas City, Mo. - ' Carrier Corp., 300 S. Geddes St., Syracuse 1, N. Y.,.-.. .'NELSON. D. -W-* tit, 1928)'-'Assoc. Prof. Mech. and Greentown, Ind. -' - ; ; . Engrgl, College! of- Engineering, University of NICHOLLS, John M. . (Af- 1939) Robbins ' / -^Wisconsin/Mech. Engrg. Bldg.-, and 3906 Council GamweU'Corp...68 West St., and 32 .Buel'St., . , > - Crest, Madison,-.Wis. ' ' . Pittsfield, Mass. . . '* - ' .- . NELSON, George O. (Af 1923) Engr^ Caretens ' -.-l Bros., Ackley, Iowa. -- .. '* NICHOLS. Howard R. (A 1943)' Engr.. Grudem .Brothers-Co., 2645 University Ave., St. Paul,.and ' NELSON, Harold M; (Af i937) Pres., H.' M. . *5416 Park PL; Minneapolis, Minn.. - * - - .... Nelson.'& Co., , Inc., 1223 Connedicut Ave., NICHOLS, Lawrence J. (A 1944) Branch 1 .-Washington. 6,, D: C., and Falls Church, Va. ... American. Radiator &-Standard Sanitary. c' -NELSON, Herman W.' (Life Member*, M 1909)., 73 E.-Naghten St., Columbus, and *2074 < -r.;-Chairman-of the;-Board; e The Herman Nelson way N,, Columbus 15;Ohio. . 7 ' igr' * . -iv Corp^ 1824'Third'Ave^ Moline; IU. .. . . - NICHOLSON,. Sterling J. (A 1941) Pres'.-'. NELSON,/James- A,;.;Jr. ;(A M945) Partner, Nicholson, Inc., Box 317,' Durham," N.-.C. ' __ 137^ -rj -c- Tarnefl A.^NeL^nn Co., 1375'Howard St;. San NICKERSON, Albert E. (A. 1945) Engr., Asbestos " - / pra^^^^;f3, and~ 143/Tuscaloosa- Ave.,'. Menlo, . -^Supply Company of Seattle,.321 First S- Seattle,4.----- ,and2415-31st W^ Seattle 99, Wash. .. j\ - LSON,`-L. Kr (Af 1940). Assoc., jamea. M.. NICKLE, Arthur J. (A 1936)'Asst. Sales Mgr., ' J3,v-217 N.> Peters. New Orleans 16,' and 2502 e Darling Bros.; Ltd;, 140 Prince St.,' Montreal'S,- ' -rAve.,;.New Orleans. La.-; ` and;4804 Oxford Aye., Montreal 29, Canada. ....,' ' X7-- V--,; Roil < ' ; ' -7 -HI NICOLL; Scott F. (Af 1939) Mech. Engr.. NOTTAGE, Herbert B. (A 1945; 71943) Research . eYork Corp., .York, and -1433 First.'Ave., Elm- . Assoc., American Society of Heating & Ventilating - wbodr York,'Pa. ^ ` ' s' Engineers. Research -Laboratory,. 10700 Euclid' NICOLS, J. A. (Af 1941) Mech; Engr.,-General Ave., Cleveland 6; and 5 Douglas Rd., Wickliffe, * - - Mills, Inc., 406-Hodgson Bldg.. Minneapolis, and Ohio. - .. - ' . ' . VRt. 2, Interlachen Blvd., Minneapolis 10, Minn. NOTTBERG, Gustav (A 1933) Vice-Pres., *U. S. - NIEMOELLER, Arthur R. (A 1943) Sales Engr.. Engineering Co.. 914 Campbell and 650 West 67th -^ - - 5817 Itaska St., SL Louis 9. Mo. - St., Kansas City, Mo. " -' . NIESKE, George F. (Af 1943) Engr., C. N. Flagg NOTTBERG, Henry J. (Af 1919). Pres., U. S. &'Co., Inc., .79 Griswold St., and *794 Bee St., Engineering Co., 914 Campbell SL, and. 150 West . Meriden, Conn. . 54th St., Kansas'City, Mo. .' '- - NIESSE, Joe H.-(if 1938) Indianapolis Branch NOTTBERG, Henry, Jr. (A 1946; 7 1937) Lt- ' Mgr.. *Ilg Electric Ventilating Co.. 836 Archi-' (j.g.). C. E. C., U. S. N. R., 130th Naval Con- tecta & Builders Bldg., Indianapolis 4, and 5837 gtruction Battalion, F. P. O., San Francisco. Calif., / Winthrop Ave., Indianapolis 5,- Ind. and. 150 West 54th St., Kansas City, Mo. 1 -/' . NOBBS, Walter - W. (Af 1919) Cons. Engr.. NOVAK, Charles J. (A 1944) Secy.-Trea*. . ' 26 Victoria St.. London S.W. 1, and 50 Fairhazel . Bryant Gas Heating Service, Inc., 533 Massa- / ' Gardens; London N.W/6, England. chusetts Ave., and 5943 Carrollton ' Ave., - . NOBIS,. H. M.. (Af 1914) *1827 Stanwood Rd.. Indianapolis, Ind. . .. - . - . _ East Cleveland 12. Ohio. ... - NOWITZKY; Herman S. (A 1931) SupL Con ' NOBLE, Milner (Af 1940) Pres., Aerofin, Corp.. struction, Wilraer & Vincent Corp., 1501 Broad . 4lO'S. Geddes St...and 142 Clarke, Syracuse,.N. YT way, New'York 18, N. Y., and 821 Llewellyn--/ / /7.7 NOLAN, James J,, Jr. (Af 1939) Principal Engr., Ave., Norfolk 7. Va. . . ' ', Repairs & UtiUties Br. Office, Chief of Engrs., NOYES, Richard R. (A 1946; 7 1938) Ll G.g.). . . War Dept.. 2lst and Virginia Ave., Washington U. S. N. Ri. c/o. Bureau of Aeronautics Repair, -25, and 4024* Calvert St. N.W:, Washington 7. U. S. N., -Columbus 16; Ohio, and 127 Pacific D. Ct ' ' -' ' NOLAN, J. J. (Af 1943) Prop., J. J. NoIan.& Co.. Ave., Toronto 9, Ont., Canada. NUGENT. Arthur W. (Af 1945) Mgr.; Wash- '-- . Srm '> 78 Washington Ave., and 1606 Goodbar, Memphis. ington Office. McQuay, Inc., 606' Colorado- "Tenm Bldg., 14th and G Sts. N.W., WashhJSkML D* C.. NOLL, Michael P. (Af 1944) Sales Engr., Servel. and 1030 FIowerAve., Takoma Park, Md. - Inc., EvansvUle 20. Ind., and Dunlavy Court N., NUNLIST, F. J., Jr. (Af 1943) AssL Chief. Engr., Apt. 7; Wilshire Village, Houston 6, Texas. . ' L. J. Mueller Furnace Co., 2005 W. Oklahoma,. _ . NOLL, William F. (Af 1924) Prop., Win. F. Noll, - Milwaukee 7,-and *528 North 19th-St.. Mfl- ' 629 North 27th St., Milwaukee 8; and-4823 W.. waukee3, Wis. .\ '. Townsend St.",'Milwaukee 10,'Wis. - - NUSBAUM, Lee* (Af 1915) Owner. Pennsyl 7, ' NORAIR, Henry (Af 1938) Pres., Norair. Engi vania Engineering Co., 1119-21 N. Howard SL, . neering Corp., 1114-22nd SL N.W.. Washington Philadelphia, and 315 Carpenter Lane. German- . 7, and -2936 Albemarle St. N.W., Washington, town, Philadelphia, Pa. . . ' .- -'" ; d: c.' * . NORBY, Karl H. (Af 1943; A 1938) Sales Engr.. NUSBAUM, S. Richard (A 1944; 7 1940)'Mgr., . .; .Pennsylvania Engineering Co.,- 1119-2r-N. . - Trane-Co.. 805 Skinner Bldg., Seattle 1. and Howard St., Philadelphia, and Wynnewood Park- " 3237-29th Ave. W.. Seattle 99, Wash. . Apts.. Wynnewood, Pa. ' ' - *' 7. I NORCROSS, Iran F. (A 1945) Mech. Engr.. NUSSBAUM. Otto J.,(A 1944) Chief Engr.', . /-.vr; f . E. L. E. Co.. 124 W. Fourth SL, Los Angeles 13,. ' and 2917 Urban Ave., Santa1 Monica. Calif. NORDIN.-'John G. (A 1944) Asst. Plant SupL. Kramer Trenton Co., '626 Brunswick. Ave., ' ///. Trenton. 5, and 918 ' Greenwood Ave'., Trenton " 9, N. J. '' - - . Southern California Gas -Co.. Box 3249, NUTTING, A.* (Af 1940) Chief Engr.,.* American .. Terminal Annex. Los Angeles 54. and 5449 Village Air Filter Co., 215 Central Ave., and 4040 Ormond * .V. Green.' Los Angeles 16, Calif. . ' Rd., Louisville, Ky. . ' ; . NORDINE, L. F. (Af 1914) The Trane Co..- . NYE, L; Bert., Jr. (A 1943; 7 1936) Staff Engr.. 2701 Ontario Rd. N.W., Washington. D. C., and - Washington Gas Light Co.. 1100 H SL-N.W.,- '. - '-.412 N: Royal Ave..-Front Royal, Va; . ' ' Washington, D. C.. and McLean. Va. ' NORFOLK, * Leslie W. (A 1941; 7 1939) Civil NYLAND, J. A.1 (A 1944) Mgr., *Nyland-Sheet' ' Engr., * 5 SL AusteU Rd.. WhaUey Range, Man* " Chester'16; England. '- Metal Co., 2323. West 10th SL, Indianapolis 8,- ' and 6133 Rosslyn Ave.. Indianapolis 5; Ind. - - ; i :|| . NORLAND, C. O. (Af 1945) Pres.. Munkel NYOUIST, John D. (7 1942; S 1941) Model Shop - - -..Heating Co., 569 N. Fourth SL, and*291 Faliis SupL, Collins Radio -Co., and 728-Fifth Ave'.' - - ' -"v-" ' 'Rd., Columbus. Ohio. * ... - S.W., Cedar Rapids. Iowa. : . . ' * NORMAN;.Edward A,, Jr.- (Af 1944).. Pres.. NYSTROM, Paul E. (Af 1945) ArchL & Partner,-. . - Norman Products' Co., Inc., 1150 Chesapeake - *Law, Law,-Potter & Nystrom, 121 S. Pinckney^. ,, 'Ave., and 1926.Andover Rd., Columbus 8. Ohio. St., Madison 3, and 360 Kensington Dr./Madison- -' 'NORMAN, George C.'(Af 1944) Erfgr., *Koithan 4. Wis. ' - - '' ' Srjohnson. 27- Washington SL, Newark 2, and 12 Exeter Mi', Short Hills. N. J. . ` o ' / NORRINGTON, Walter L. (A 1943; 7 1938) . Capt., Ordnance DepL, Office of Chief of Ord nance, Washington, ,D. C., and #305 Barbara - `Fritchie, Beverly Plaza, Alexandria, Va. NORRIS,' William',,P. (Af 1944 ; 7 1938) Engr.. .' Universal Milking Machine Co.,-.and 423 Bar . stow SL, Waukesha, Wis. . ` ' ; ' . OAKLEY, LeRoy W. (Af 1937) Qwner. L^ W.; .. Oakley Sales Co., 408 W. Clinch Ave., and'2003. - Laurel Ave.. Knoxville, Tenn. . - OAKS, Orion O. .(Af.1917) Chief Engr.,'J. B. . Pierce. Foundation, Raritan, and 119- Oak/ * Ridge Ave., Summit, N. J. ' . ', O'BANNON, Lester S.* (Af 1928), Research - -7."' >: | NORTE; w. R.":(A 1946; 7-1942) Sales Engr.. -Crane Co.. 710 Northwest 14th Ave., Portland ' ' 8, and 2607\N.E." Mason, Portland 11, Ore., 4 ' - Engr..' Kentucky Agricultural Experiment-Sta- tion. University of Kentucky, and 123 State St., . Lexington, Ky. -' ' ' . '.>'/ - NORTH, Clarence P. (Af l942) Chief Engr.. - - Campbell 'Heating Co.. P. O. Box 833. Des ''.-Moines 4, and 3614 E. Seventh St., Des Moines OBERG, H. C. (A 1933) Mgr., Engrg. -DepL, / Crane Co.,'Fifth'and Broadway, and *1362 W.- . Minnehaha SL, SL Paul, Minn. .' .' ' . - - ' -i' 77 V.. " '16, Iowa;' ; ' OBERSCHULTE, Richard H. (Af .1944 ; 7 1938) /' / NORTHS Sam L. (A 1942) Partner, North Bros.. Sales & Field Mgr., *D. T. Randall & Co.,'404 P. O'.'Box 252, Atlanta 1, Ga. . . Boulevard Bldg.. Detroit 2, and Box 76,'Franklin.' * NORTON, John A. (Af 1940) Mgr.; HtgT Sales. Mich.- . ' ' ` - 7 Div.,.Crane,-Ltd., 306 Front St. W.,-Toronto, and O'BRIEN; Thomas J. (Af 1943) *T. J; O'Brien ' - *136 Hanna Rd.. Leaside, Ont., Canada. '- - : Engineering Co.,1030 Exchange Bldg... and. 1483 ' NORTON,.L,.Ivan (A 1941) Engr., Design Htg.. Vance Ave., Memphis, Tenn; ". /->;;' . : Installations, Evoready Piumbing & Heating ' O'CONNELL, Thomas D'Arcy (A 1542).. Pres., . '''*'Co.'r514 W. Main St;,.Washington. Iowa; . * VNOTKIN,-James. B. (Af 1944). Mech. Engr.. .Public.Wor$3 DepL, `Puget Sound Navy Yard, -> r Bremerton, and *2013 East 63rd SL. Seattle - Thomas- O'Connell, Ltd., .1169 Ottawa ;St.,v . Montreal 3, and 9 McCullough Ave., Outremont- ^ 8,-Que., Canada. . ,.' ; . O'DANIEL, James A. (Af 1942) Owner.-*Maple : rfr o-' . `/5, Wash,.../* City Furnace Co., 603 S;-Main St., Monmouth, 111. - - II . , " 11 '~ ' -/- r `Heating Veritilating Air-CCoonnddititioionniinngg Guide 1946 , ' ' O'DANIEL,.-. Presley {A' 1945)-. Branch" Mgr:, ' ORABELLA, Michael J. (A 1944) Pres] & Mgr. of . York Corp., 1137 Sterick Bldg., Memphis 3,. ' Engrg.. DepL, Ohio * National .Products,- Inc., V;' - .. ' -i' and 2167.Poplar, Apt;' 12; Memphis 4, Term- ' -. 40014 Carnegie 'Ave., Cleveland,' and * 13304 'O'DONNELL,' LawrenceD](A-1944) .Mgr. & ' -First Ave., East'ClevelandT2, Ohio; - - . - Partner, McCarthy's Sheet -Metal' Works. 113 OREAR, Andrew Gi (Af 1942) Pres., Trade ,`N: Eighth St., and 816 Buntin St., Vincennes, Ind. . . O'DOWER, Hugh - J. . (A. -1938) Distributor, - Vilter Manufacturing Co.; 114 W. Tenth SC, . Wind Motorfans, Inc., 5725.:S. Main St.; Los Angeles 37, and, 1015 E. - Raleigh SL; Glendale 5; Calif.. - J * ;*. ] Kansas City 6. ami 6844 LbcusL Kansas City,- Mo. .O'REAR; L. R. (Af 1934) Pres.. Midwest : . OELGOETZ, J. F. (M 1938) Sole Owner, J. F. : Plumbing &' Heating Co., 2450 Blake St., and 825 /, ; Oelgoetz Co.. 3365 N/High .SL. and 279 E. . S. Josephine St., Denver, Colo. * . ' North.Broadway, Columbus, Ohio.- " ,' > - OREBAUGH; Howard T. (Af 1945) Application . . . .. OFFEN, Ben (Af 1928) Owner. B., Offen & Co., Engr., York Corp., 4660 E. Marginal Way, ' --.=*.. >3n4i.3 -S. DearbornSL, and She-rid*an R- d., Ch- icago, ; Seattle 4. and 1129 North 77th SL; Seattle 3, Wash. .* ORGELMAN, George H. (J 1942; .1940) Lt.. . . ; - OFFNER,. Alfred J.* (M 1922), (1st Vice-Pres., -. Hq. B. A. S; E. C. T. W. O., U. S. A. S. C. O. M. C.. ` ry * V* .1945; 2nd Vice-Pres:/'-1944; .Treas., 1935-38; Engr; Section, A. P. O., 928, c/o Postmaster,'San., ~ CoundI/1935-45) Cons. -Engr.. *139.- East 53rd Francisco, Calif./ and* 10 Pearl.-St.,-. Danbury, " . . SL.:New York 22, and 160-15-1 Ith Ave.,'Beech- - Conn. .- ' J . ursL L: I., N'. Y.- *. ; ^` r - ORMISTON, Jack B. (A 1940) Owner, Ormiston - O'GORMAN, .J. S.t Jr. (A 1934) Mgr., Detroit Plumbing &' Heating .Co,, 105 Manning 'Ave., - - . -' Office, Johnson Service Co.; 230 E. `Alexandrine- - and 287 Mile Square Rd.. Yonkers 2, N.-Y. - _ . -' ...' Ave., Detroit 1; and 147 Abbey Rd., Birmingham, . ORMSBY,. H. Kingsley, Jr. (Af -1944)' Owner, . ' Mich.! - ' . * . :TM ' Syracuse. General Sales Co., 511 E. Raynor :V ;OLD, WUUrim H. (2f 1937) -Asst. Mgr.. eGlanz '' Ave., Syracuse 1, -arid 206 Roycroft Rd., East . ;.v`" -V & Killian. Co., 1761 Forest Ave. W//'Detroit'-8,' .Syracuse,'N. Y: 'L and 18245 Devonshire Rd., R. F. D. 5, Binning- ORR; Weldon .John '(A .1944) Mech: Engr.V. . ham. Mich. - . '- ` James A. Kearns, 1414.'Drummond SL.' and . ' : OLDS; Dean (hi 1944) Chief Engr.. .Gas & Oil '.3559 St..Famille St-., Apt. 5, Montreal, Que.,. Div., _ The Coleman Lamp & Stove .Co., 250 N. .. Canada.. ' ' ` ?* ' .St..Francis, and 222 N.'BIecIdey, Wichita,-Kans/ OSBERGER, T. L. (A. 1944). Mgr,, *T. L.^Os-- . ' . OLDS, Stephen T. (A/1945) Sales Mgr.-& Engr., berge'r Co., 550 Michigan Trust Bldg., Grand- / - William. C. Maunz-Co... 1397, Jefferson Ave.; Rapids, and ` 1208 Dunham- St.. ,S;E.,Grand .* V ;r Buffalo 8. and 400:EImwood'Ave!/Buffalo 9, N. Y.' `Rapids 6, Mich. ' . * r . .. ' OLLESHEIMER, Louis ; T. (A . 1945) Factory - * -Repr./* 2539 Woodward' Ave., Detroit'T, and 250 -, Baldwin Ave.-, Birmingham. Mich. .- - - ; = v OLSEN, Carlton F. (A 1925; J 1920)- Engr. & OSBORN, Wallace J. (A 1927) Vice-Pres.. Keeney -'Publishing Co... 1734 -Grand Central .Terminal; Bldg..-NewYork; N. Y./and 1029-Old Post Rd... Fairfield,' Conn.. - - . : ^ ;] - Sales, Kewanee Boiler Corp.. 549.W. Washington . OSBORNE, G. H. (Af 1922) Managing Dir.. The . . Blvd., and 1000 West 100 St:, Chicago 43, III. . .. Ventilating, & Blow. Pipe Co!, Ltd., 714 Saint ' . . *. OLSEN,-Gustav. E. (Af 1930) Sales Mgr., Fitz- Maurice St., Montreal -3, .and 4535 LacombeV < - ` gibbons Boiler- Co., Inc., 101- Park Ave., r-New --.AveVMontreal 26, Que., Canada.- . ' .'\ York, and *68-09 Beach-Channel Dr.; Arverne, . OSBORNE, James M/(A 1944) Field Engr., The .; l. i., n. y. . ` ' - ' Hennan Nelson-;Cefp;, 1829 "M"--St: N;W., ' ./ i/OLSON, Arthur! A. (Af 1944) Vice^Pres. & Treas., /Washington 6. D. ]' C., and. 4607 Drexel Rd:.- . ` - Lee Engineering Co., 1102'.-Union National -CoUege Park, Md. - . -- - . Bank Bldg..Youngstown3. and 4129 Oak Knoll . .OSBORNE, Stanley. R. (Af 1939)-. Promotion . -Dr., Youngstown.7,- Ohio; c . *. ; *!--, OLSON, Barney (A 1929) Barney] Olson,- Inc., - v-. - ,' 122 S. Michigan Ave., arid 5724 N; Natoma Ave., Chicago,-111..' ; ` . Engr.,`-..Chase. Brass & Copper Co.v Wartebury -91; and 115 Grove'St;. Naugatuck,' Conn.-:- . .. O'SHEA, John J.. (A 1941) Sales Repr., Buffalo- Forge Co.,-305 Teckwood Dr. N':E..rand 714 OLSON, ErllngrO. (A 1943) Service Engr., Oil / Greenview Ave. N.E., Atlanta, Ga.. .- - - , . *' -! Burner Sendee Co., Inc;.'- 315`.-West Lake* St., OSTER, William P. (Af 1940) Vice-Ptes.: E<iui- */ >,: -/ Minneapolis, and *4221. Oakland Ave., Minne^ .table. Equipment Co.,' Ind, 410 Camp St]; New,. - .' 'apolis 7; Minn..`-. ... ,*{-.' Orleans 12, La. '- . -' ; ' f.^v x . OLSON, Eugene kO,.f (if- 1942) Delavan Erigi-. ' OSTERHAGE, Catherine Sweeney !(A 1945) " /.neering Co."--' 414^-12th -St.; Desr Moines 9; and: ' ' -Draftsman,* E. T. -duPont' deNemours '& Co.,-; , 2520Hl5th SL/DesMoineslO, Iowa! ' ` -` '. Inc.';- P. O: Box TOO, 'and 1025 Winslow Ave.,; * OLSON,- Milton J. (A 1941; / 1937); Partner, Richland, Wash. ' ' _ ->. :. :!)..Olson. Bros.r. 2651 ` SL, Mary's ;Ave., and 5830 -- OSTERMEIER, Edwin'J. (A 1945) Dir.of Engrg.. .* : ' - . Hickory St.,^-.Omaha, Nebr. - ' ' ;V s - V ApexEngineeringCo.,Smte200,EngineerBBldg.. / ' .;!;; OLSON.. Nat I.-(A 1944) Owner StsGen. .Mgr.-.- 205 W. Wacker'Dr... Chicago 6. and'4508-Wilson'/. ; United;Blower..Co'.*,- Inc... 193;Centie St., New ' .Ave., Downed Grove, 111. --' - ' - -'. - --.York 13;- ahd_ 71i;, Brightwater' Court, TBrook- - OSTROM, Eric -W; (Af-1937)-Chief Erigr/,:.Air;- ' -'1 - -, c- lyn,-N. Y. , ;` 7 Cond.'.Dept., A/B Svenska Flaktfbriken, Kung* - ' V^OLSSON, Eric ..V:_(A"* 1945). Field] Engr., *B;*E. . ; sgatari .16,'.and.* John, Ericssonsgatan'18, Stock- -, 'Sturtevaht CoV,-36,;Pearl'St.. Hartford 3,-'arid *: -holm,Swriden/V'- ' : / . .' >;v .---Main St.,.ColIinsviUe. Conn. ;/ - * O.TIS, Alfred. L'.- (A 1944) Dist. Sales - Mgr., , . ' r;- OLVANY, William J, (Life' Member; 'Af 1912).. ;'Clarage Fari Co.. 965 Farmington Ave.. and- 43 ]`. . .. .Pres:; William J. Olvany, Inc., 100 Charles SL, - N. Main, West'Hartford. Conn. " . \.v-- ".` 1 . ' . New. York 14, and 109-40-71st Rd.', Forest Hills, OIT,- M. Earl.(Af. 1942) Owner, Lakeside Metal - - L. I,; N. Y.-:. . . - - - ' .. . Seryice, -23 EasL 116th'St., Chicago 28; and 8635 ', $-r O'NEILL, `James.W. (Af 1929; A 1927; J-1925) . - : W.-Wabash-Ave., Chicago 19,'llL-. - ... ] _ , ' " '."YiccrPres- in;charge of Production,-Trane Com--- OTT. Orari W. (A4T925). (Coundl.193448) Cons.. pany-of Canada. Ltd., 4 Mowat Ave.. and 55 - Mech. Engr., *111 W. Seventh Bldg., Los Angeles, ' ' I'A'-. Highview. CrescenL Toronto,-Ont.',-Canada.' ' and 1462 Waverly'Rd., Sari Marino. Calif.' - -O'NEILL,.Johri E.:(A;T1945) Sales Engr.,`.Kerby OTTO, Robert W. (Af 1941) Mech. Engr.] Tolu : . .--Saunders, Inc... 330 West 42nd'St.,, New'YorC 'King & Day.Tnc., 1509 Pioneer Bldg.', and.2147.. ' . -and 81 W.*>Raleigh`Ave.. Staten Island,-N. Y. ' Carroll Ave.] St] Paul, Minn." -V ...* ,.O'NEILL, "Joseph - Francis' (Af - 1944) ` Mech. OTTS. Johri G. (A 1942) CapL, A. C.; c/o*CU ' : Engr., Trane .. Company of. Ga!riada, Ltd.,! 4' . matic Hangar Project Office,. Elgin, Field.-r-Fla.. ,Mowat Ave.',. Toronto 1,. and 44' Aldgate Ave., - ; and c/o Dr: W. W/Carson] Ft. Valley,.Ga] ; - 4 ^Tdronto.r14,-Ont'.,'Canada. ' . OTTUM,. Alvin L.' (Af T945; A 1943) ^Air Con- .; r.OpNK;';W. Jr.(Af;1937). Dist. Mgr., BT F. Sturte-' ditionirig.Sales'&Engineering,'*Radiant Sales,& " '- .<- J-. yant'Co.i'lSlS SyndicaLb /r^nst .Bldg., St: Louis 1, Erigirieering.Co.,-344.N.'San* Vicerite BIvd., Los . ? ;^v 'ahd ''4548-;'Red ;Bud-Ave., SL LouisT5, Mo.'-, : - .. Angeles 36, Calif.;-v. ] /- r, ........... j^^pOSTENj^uU S: (A` :1944;7 1938) AssL Chief OURUSOFF, L'.* (Af 1931) Mgr:-of'Utilization,'. ` vv/.rr-.Engr:, .Bell.Sc .Gossett Co^. -8200 N:-Austin Ave.. Washington Gas Ughf Co./ llOO^H SL, N.W:; ' /^-tV'^Morton'Grove. and *725^Case St., Evanston, 111. ; - " Washington. D.` C. y -`\ 1944) IMech. Engr.,^. bUWENEELi W. A:^(k'i937) ,Siead Cimkru^-'^^-T;^ r^t^^^^Petroleum Heat.&Power Co.,' Southfield "-St!! ; ]"~^/r ]]-'].`;-.j', ` -\zrind..**778008iiCE*.j'Maia-(?St., CS-.'tamrforda ,**r--Con n. .' '' tion Co.,'514 E. Ogden-Ave.',--Milwaukee 2,"and - 5282 N. Bay Ridge',' Milwaukee 11. Wis.' , ' ;'r'^ ' tfdWof Membership : OWEN,-Charles E.^(Af 1941) Cons.-Engr.. Mfrs. r PARMELEE/ George V.* \(Af .1945)'Research ' '%`;.-'AgenL Owen ^Engineering.Service, and-1218 S. '-Thompson St.. Carbondale, 111. ' . -, Fellow, 'American Sodety- oi Heating '& Venti--.* lating Engineers, - Research- Laboratory, T0700.- - ` - OWEN, Charles <E.'; Jr. (J 1945) Petty'Officer. -Euclid ;Ave., Cleveland `6;-and * 15615 Judson ' - ' U. S. N. R., 7th Special Battalion, Co. D.'-l, Fleet . '-' Dr..' Cleveland 20,.Ohio. ` -' -,. ' '' Post Office, San Francisco, Calif./ and 1218 S. PARRI, Idwal W. (A ,1945) Final Test Engr../ / Thompson, Carbondale; 111.- . ` " - . ...Perfex Corp..'500 W. Oklahoma Ave-, and *2516 1 . ` OWEN, Frank W. '(/ 1945) Petty Officer. U..S. - ' E/ Morgan Ave.. Milwaukee 7, Wis.- - ` / -].' ;;w- N. R., N. C. T. C. Sta., Force, Barracks. 1-2. PARROTT, vLyle G.. (Af 1922) Cons.' Engr./ , ~. Camp - EndicotL Davisville.' R. I., and 1218 S. Snyder &.-McLean, 2214 Penobscot -Bldg;. ,. ' Thompson.St:/Carbondale.-111. - , , ` * Detroit`26. and'3788 Gladstone. Detroit 6! Mich. *' ' OWEN, Jeff Davis (Af 1937) Piping Engr., Stone PARSONS, John H/ (A' 1942) Owner, Parsons .& Webster-Engineering Corp.. Los Angeles, and Engineering,Service, 607 N. Fries Ave.] Wilming- ' ' - 4070 East Blvd., Culver City. Calif. - ' ^ . ton. and'4119 Fourth-Ave.. Los Angeles 43, Calif: . OWEN] W. Harold - (Af 1943)- Engr.. Harry - PARSONS, Lawson G. (A 1945) Mgr., Wholesale - -- Cooper Supply Co., 223' East Water, Springfield, Plbg. & Htg. Deptl, York Corrugating -Co.. f 'and Republic, Mo. . .. Adams SL and W. M.-R. R-. and 50 N. Newberry-. . . St.,-York. Pa. PARSONS, ROger A. (A 1942;7T933) Htg. Engr., . . PABST, Charles S. '(Af.1934) Pr.. Pabst Air . Conditioning' Corp., 219 Eagle St.. Brooklyn 22,- ' ! and 8727-98th St.. Woodhaven L'.T;,-N. Y. . `.PACKTOR, Bernard^M. (A 1941) Engr.. Mac- ~ marm Engineering-Co.,`252 .Canal St.,.and *10 Lockwood.Ave.;'Stamford, Conn. ' - -' PAETZ, George A. (J 1942; 5,1940)/Lt., U. S. .. "'N; R., Naval Training Station, and 1721 Preston ' ' 'Rd.! Alexandria; Va.-- ' . .' . PAETZ, Herbert E. (Af 1922) Div.- Sales Mgr./ / " American Blower 'Corp.,. 632 Fisher' Bldg., *' ' Detroit 2, and 1415 Parker, DetroiL-Mich. ; PAGE] ' Arvin (Af.1935) Chief Engr., The . -Bahrison'Co., Salem Statiom^and 820 Oaklawn -' ' Ave./ Winston-Saleiii, N/C.. . - ' ' / - PAGE, Vernon C. (A 193.6) Asst. Gen. Plant Mgr.. . : ' Fitzgibboris Boiler Co.,- Inc., and 165 W. Third, v Oswego, N. Y. . , . o'.- * ' 1` PAINE, H. Allan (J 1940) Lt.-Xj.g-). U. S. N. R..., - Fleet Air -Wing 8 Hdq. Sqd..F. P. O., San- .Francisco" 7, Calif:,' and *602r N. Ninth/. St^, . Brainerd, Minn. - - ,, PAINTER, D; Howard (M 1943)] Mfr. Repr.V ' arid *8031 Manor Rd.. Rte.'7; Kansas City 5. Mo.- PALMER. E. M. (A 1944) AssL Gen. Sales Mgr. . ' /'.- Kewanee Boiler Corp., arid 436 S.jChestnut St:. ' /'Kewanee, 111.-*' - -r PALUMBO. Bernard F. (A 1943/71941) Foster . ' .Plumbing, Heating,- Air - Conditioning .Co., 62 ` / Foster Sq., Bridgeport 8,- Conn. '. ; PANGBORN, Clarence A. (Af 1944) Mech. Engr... ' *1525 Sinith Tower, Seattle 4. Wash;; - - - PAOUET, Jean-Marie. (A 1940; J 1936)' Engr., /.-'-97'Abraham Hills Quebec.-Que., Canada./', . v PARENT, Harold M. (Af 1938) Partner. Parent Kirkbride,'N.W. Cor. Fourth.and Locust St'.-, .... Philaddft)hia' 6,; Pa.,' and- 49 Wildwood Ave., ' '"^-.Pitman;- N. J.'- * ' : `PARIZEAULT, J. A. Rollarid (A 1944).Supt.. ' *J! &`C.-.Brunet, Ltd:. 1095'SL Lawrence-BJvd.;' ' ' and. 4569:Gamier,St., Montreal T. Que., Canada. PARK. Harold E. (A 1938; 7 1936) Sales Engr.. . -] Shaw-Perkins Manufacturing:Co..' 1645 Oliver ' Bldg.: Pittsburgh 22, arid 106 .W. Littlewood St., Etna, Pittsburgh 23,-Pa.' : - , ' -. -PARK, J. Frank (Af 1937;A 1936;'7 1930).Pres.'., Board of Water & Electric Light Commissioners,'-: . 114T6 W.-Ottawa St., and 2609. Clifton St..:. ... Lansing, Mich. . . '. ' * PARTLAN; Robert L. (A 1946; 7 1940), Pres.; Partlaa Sheet. Metal Works,- 14265 .Arlington " / Ave.. Detroit -12, and. 9102 Pinehurst- Ave:. '] ` Detroit 4, Mich. --V " : PARVIS, Ralph S. (Af 1938) Supvsr.. Diamond.. *7 ' Ice &_Coal. Co.. 827. Market .St.,7and>. 1208 ' Delaware Ave., Wilmington-19, Del. - * ! PASEK,; Leonard E. (Af 1944) ..Product\Engr,, - Kimberly-Clark 'Corp., Nee'nah, Wis., and.20 /;. ' : N. Broadway, White Plains. N.-Y: . - ' '7 PASIADIS; Fedon H; (7 1945); Junior Project-- - '.Engr.,--Engineering Laboratory,- Airtemp ^Diy., .- / Chrysler.. Corp.; ` Dayton 1,' and *618-. Grafton 7. - Ave.,Dayton 6, Ohio: . ' V ' . : PASTEUR, Hugh W.' .(M. 1943)-Export Mgr.;. ;: ; J/E. Hall, Ltd.; Dartford; and Fairseat/Ho.use; = -. - Fairseat, Kent; England. ' , ' `-/-w ; ., -PASTOR; ; John . C. -(Af 1938) Design:, Erigr./ / Rm. 818'Graham Bldg.. Jacksonville^,'and 1 E. 1091 Talbot Ave/, Jacksonville 5, Fla. ] PATERSON. RoIlln O. (A ' 1945) Estimator. Fisher- Body Div., General Motors Corp/, Detroit. - - . and 169 Ardmore. Ferndale 20,`Mich..- - "--e^. - .... PATORNO, Sullivan A.'S. (Af 1923) Cons. Engr., v * ,. #101-Park Ave., New York. N. Y. " - - . ' ' PATRICK, Gcorfee P. (71945) Jr: Engr*. Carrier: . Corp., S. Geddes SL, Syracuse. N. Y. . _ ' '' PATRICK. Horace. M. (Af 1945) Cons. Engr... .- *20 01a>tt`Ave.,.Berriardsville, N. J.- . PATTEN, J. Elverton (Af 1945) Chief, Engr.. *, B/ Offen &-Co...343 S. Dearborn St., Chica'go]4. ! and 338 N. Stone Ave., La Grange, 111. ' - PATTERSON. Frank H/- (Af 1942) Sales Engr- . ' Hoffman Specialty. Co.. 1001 York St:,- India- \ ` napolis, Ind., and *9201 Boleyn Ave:.. Detroit . . 24, Mich. * . - - PATTERSON, G. P. (Af;1939) Vice-Pres./ W. B. . Haggerty, Inc./805'Morgan St./;P. O. Box 2971, _ ' '-Tampa 1. Fla. - - <; " .' - ` PATTERSON, Howard V. (A -1945) -.Mgr.. - _ . American Engineering-Co., .4112-14 Penrisyl- - `V.vanm'-Ave.;Kansas City! Mo/, ... - - PATTERSON, James C. (Af 1945) Dir. of Sales.- . ' Western Air.& Refrigeration, Inc.', 1819 Glen-' Indus. Htg.,_Carrier/Corp., and 206 Robiaeau v ... v 'dale-' BlvdU and .2160 .Kenilworth Ave.,-'..Los Rd/, Syracuse, N. Y.. " . - - . -. Angeles'26. Calif. , -. patterson; . Joseph c., Jr. (M1944) Ap- . . PARK, Nicholas W. (Af 1936) Mech. Erigr.. Heiritz : - plication ' Engr.. La-Del Conveyor & Manu- - ; /'Manufacturing 7Co:,/- Front 'and'. Olney* Ave.,- facturing Co., 410 Washington'B!dg.i T5th and G,. - ' Philadelphia, and 509 Jericho Rd.. Abingtori. Pa. Washington 5. D. C., and 2414' Taylor -Ave., * PARKANS, Lloyd (S 1945) Student. Air Con- ' Alexandria, Va. ' ' - '-- '. - V" , ditioning/- Duriwoody-Institute, and *1721 Uni PATTERSON, Ralph. A/ (A 1943) Gen. Sales . i versity Ave. S.E-., Minneajxilis,-Minn. ........ -. - : Mgr.. Bell & Gossett-.Co., 8200 N. Austin Ave.,*-.-. - -PARKER; Herbert E; (Af 1943) Engr.; Bethlehem - Morton Grove, and 1213 .Mulford St., -Evanrton,_ ; - Steel..'.Co./---E. /Howard SL', - Quincy, arid *74 111.- ' ' ' - - -.r-. ' ` Sealurid Rd., North Quincy, Mass. ' ; PAUL, Dean W. (A 1944) N; Y/ Mgr.V. Sterling . PARKER, Richard A. (A 1938) CapL; 0-235379. Electric Motors, Inc., 41 Park Row, New York`7, / 2I7th-General Hospital, A/..P.'O. 887, c/o and 140 Cabririi-BIvd.. NewYork 33..N. Y]"._ -v f. ", \ ' \ Postmaster,.New York, N. Y., and 220 El Camino' .. PAUL, Donald. I:. (Af ,1936; 7- 1932) GurrieV> " ';' Real, Burlingame, Calif. - . :r - *. - PARKES] C. H/ (Af 1944) Owner, Distributor of, . - Heating'&'Plumbirig Equip., I01H W..CKestriuL- ' . P. O:, Box 947, and T108 W. Chestnut. Dodge ' :City/Kans. . ' - . -;-t - -''}x PARKINSON, John S.* (A 1940) Research Engr./ . .Foundry Co/] Ltd.,`4. Junction. Rd.,. and/264Z * Lawrence Ave. E., Toronto, Ont.,-Canada.. ^ . ' ' 1- PAULDING, Lewis G. (if 1944). Supvsr// Long! Island - Lighting ' Co.,. 250 Old Country Rd../.] -Mineola,' L: L, and-Box 1033, Brightwaters/N; Y.-. - -.. - Johris-Manville Research*'Laboratories,- Man-. ~..-]ville, N. J.-' ... ".>",] /. , V/" PARKS, Charles E. (M 1937) Pacific Coast Mgr., ^PAULEY,'Robert D.-:(A-1944*; J 1940)-Develop--- ~ merit Engr.] Weyerhaeuser ZTimber -Co., and -^, l503-25th Ave!. Long\riew. Wash. '/./' !y> / llg^Elertric-Ventilating Co.,- 816- W.' Fifth St., PAULSON/Owen D. (A]l945) Engr.; General'Air./ i -Lbs An'geles.-13; and*7257 .Hollywood.Blvd.,. Los , "Conditioning &-Htg..Co.; 2001 Peralta St.', Oak-]/ *Z .7'/" Angeles 46; Calif."-: `' - -land, and 1804 Nason St., Alameda; Calif. /'-'. //_ -` I * y;. . ' \' 64 Heating Ventilating Air Conditioning . Guide 1946 ` Roll of Membership 65 PAVEY, Charles A* (Af 1937)*DisL Mgr.. B. F. ^Sturtevant Co.."812 Michigan Bldg., Detroit 26,. and 15778"Asbury Park,-Detroit 27, Mich. ' ' PAWKETT, Lawrence S. (A 1938) Mech. Engr.. PERRAS, George E. (Af 1936) Mgn. Htg. Div., Thomas. Robertson & Co., Ltd..-262 Craig St. W., and 5915 Christoptie Columbus St., Montreal, Que:, - -- ..... L.- S. Pawkett & Co., 810 Insurance Bldg., San '-Antonio 5,' and 1007 W. Magnolia Ave., San . Antonio 1, Texas.- ' PAYNE, Raymond L." (A 1944) Partner, Air Flow Heating .Co., 1409 Platte St., Denver 2, and 5706 W. Colfax, Denver 15, Colo: ' PAYTON, John F. (Af 1944) Sales Engr., Minne- apolis-Honeywell Regulator Co.. 1007 N. Meridian, Indianapolis, and 3536 N. Meridian. No. 308. PERRY, Lester..L, (A 1944) CommL Sales Mgr.'. Frigidaire Div., Denver Branch, General Motors- Corp., and 1421 Gilpin SL, Denver, Colo. ~ PERRY, M. Arthur (Af 1944) Supt. of Main ' tenance, DePauw University,' 8 Larabee St., and 628 E. Anderson St., Greencastle, Ind. . PERSSON, N. Bert (Af 1937) Cons. Engr., *Food Service Equipment Engineering. 1418 Simpson SL, St. -Paul 4. Minn. - 'Indianapolis 8, Ind. ' . - . PESTERFIELD, C. H. (Af 1938; '7 1936; S 1932) ' PEACOCK, Glenn S. (Af 1939) -Htg. Engr.,- Assoc. Prof., of Mech. Engrg., Michigan "State `.University of Pittsburgh. Oakland P. 0., and *111 College, and 142 Gunson St., East Lansing, Mich. Elmont St.,.Crafton P. O. No'. 5. Pittsburgh, Pa. . PETERKIN, Stuart M. (Af 1943) Pres., Michael PEACOCK, Herbert (M 1940) Dist. Mgr.. . StuartCo., Ltd.. 45 Lake SL, St:-Catharines,-and ; -Carrier Corp., 405 Lexington Ave., New York Iroquois, Ont., Canada.. " 17. N.-Y. .- . . ' - X PETERS, William S. (Af 1944) Partner & Gen.. PEACOCK, William H. (A 1945) Mgr., Peacock Mgr., A. J. Peters & Son; P. O. Box 632,"410 Plumbing & Heating Co., 34 Benton.St., and 30 North 10th SL, and 1489 Shasta .Ave., San Mary St.r-Kitchener, OnL, Canada.. `' Jose, Calif. - - ' ' PEARCE, Edward A. (Af 1942) Cons. Engr., *55 PETERSEN, Christian* P. (A 1937) Petersen Blenheim Rd.;'North Harrow, Middlesex, England. Sheet Metal, 3746 Cedar Ave., Minneapolis 7, PEARSON, Fred .L.' (Af 1942) Cons. Engr., and 4000 Cedar Ave., Minneapolis; Minn. - . 1131 Majestic Bldg., Detroit, and 354 Glendale, PETERSEN, Richard J.-.(Af 1945)-Supvsr.'of 'Highland Park, Mich. : V ' . ; - - . Research & Dvlpt., Utility Appliance Corp-. PEART, Allen M. (A WST") Dist. Mgr., Minne apolis-Honeywell Regulator Co., 637 Craig ,W,, Rm. 812, and 5580 Bradford PI.,. Montreal, Que:, -Canada. . . - .. - PEARY,'Howard. W. (A 1945) Factory Engr., '- McDonnell-Miller, 120 Bdylston'St., Boston 16,' and 577'Hammoad St..-Chestnut Hill 67, Mass.' -' - . . 4851 S. Alameda St.. Los Angeles 11; and 1831., West 77th St.. Los Angeles 44. Calif. - . - - '. PETERSON; B. G. (Af 1943; A 1941) Sales Engr..: 208 Grain Exchange Bldg., Omaha 2. and.*6235 'Florence Blvd.. Omaha 11,'Nebr. PETERSON, Carl M.-F,*. (Af 1936).- Supi,'Of : . Bldgs. & -Power, Massachusetts Institute of Technology, 77 Mass Ave.,- Cambridge, and-,74 . PECK,:.Henry E;:(A 1938) Cons. Engr:, D. M. - McBean.Co., 315. Alexander SL, Rochester, and ' Cutter.Hill Rd., Arlington'74; Mass. ' PETERSON, Clarence L. -(Af 1938) Branch-Mgri.' .-'73,'Potter PL, Fairport, N. Y. . . . ' , -Minneapolis-Honeywell. Regulator - Co., 1136 . PECK, Joseph W. (7. 1945) Mech. -Engr.. Air ' Howard St:, San Francisco, and 2 Indian-Rock . Cond. Design,' U. S. Navy Dept., San Francisco Path. Berkeley, Calif. ' . . . Naval Shipyard. San Francisco, Calif., and 4559 . S. E. -Hermitage Ave., Chicago 9. 111. PETERSON, DuWayne J. (Af 1940) Sales.Mgr.. ; Htg. Controls Div., Central Zone,' Minneapolis- . - PECK, Robert E. (Af 1943) Vice-Pres., The Honeywell Regulator Co., 415- Brainard St., Peck. ' Hannaford &* Briggs Co., Cor.' Sycamore and Court- St., and 980 Avondale Ave., ..Cincin- Detrdit 1, and 16819 Cranford. -Lane, Crosse- Pointe30. Mich. - -' : natl, Ohio. . . PETERSON, Hans P. (A 1945; 7 1939) Chief PEEBLES;'John K., Jr. (A 1925; 7 1924) Chief . Engr.: Partner, Baskervill & Son, Archts., Central National Bank: Bldg., Richmond 19. and *.1708 . Park Ave., Richmond 20.-Va. - -. . PEGG, Edward H. R. (A 1943) *3315 Parkview Ave., Pittsburgh 13, Pa. , - PEISER, Maurice B. (A .1946; 7 1937) Capt., . ;Hq.:482nd Bomb Group, A. P. O. 557, c/o Post-' master. New. York; N.'Y. . -_ ' PELLEGRINI, -Louis -C; (M 1939) Vi<*-Pres.. - Mario Coil Co.. 6135 Manchester Ave., and 6549' , Murdoch St:,. St. Louis, Mo. : -- Engr.. The Bush Manufacturing Co., Station A, ` Hartford, and 28 Hawthorn St.. South Man Chester, Conn. ' ',, PETERSON, Howard H. (Af-1945). Cons. Engr.. ' *301 Miller Bldg., and Tieton Dr., Rt.'4, Yakima,-.-. . Wash. .- - ,^ . PETERSON, J. Raymond ' (A 1941; 7 -1940):: . U. S. Army,-and 719 E. Nevada Avt,.St. Paul; 6. Minn. . ` . -- PETERSON; John E. (Af-.1944) Research Engr., Minneapolis-Honeywell Regulator Co., 2301 N. ' Knox Ave., Chicago 39, and *1108 Curtiss SLV - Downers Grove, III-. . - - PELLER,. Leonard (A 1942 ; 7 1934)# United . PETERSON, Neil H:' (Af, 1937) Owner, Neil HV Engineers Contractors, 1401 Arch St., and Peterson Co., 1129. Folsom SL, and 2-l8tH A've,, ,1546 0riandSL. Philadelphia, Pa. , ' , San-Francisco; Calif.- - PELLMOUNTER,` Thomas (A 1936) Mfrs. Agent- for -Electric Motors," Louis Allis, Leland Electric & Bodina .Electric, Kansas City 6, and. 4118 Mercier, Kansas City 2, Mo. '' PELLMOUNTER, T. V..(A: 1946; 7 1938) Major. . PETERSON, Sterling D. (A 1930) Branch Mgr., x Johnson Service Co., 311 Colman Bldg.,7Seattle 1'4, and 5051-Prince SL; Seattle 6, Wash. ^ v PETERSON, Walter E. (Af 1941) Htg.- Engr.; .- ! International Harvester Co.. Industrial Engrg;" - Ordnance Dept. 0-347568, Ord. Ofc/Hq; A.'F. 'W. E. S. P. A. C.. A. P. O. 707. Postmaster. & Const. Div., 180 N. Michigan Ave..-Chicago 1; . and *5240 N. Kimball Ave.,'Chicago 25, 111. ' - * San .Francisco,-: Calif.. and 4118 Mercier St;, Kansas City, Mo. '' ' PETRONIS, Albert (7 1945) Engr., Carrier Corp., 20 N: Wacker Dr.. Chicago 6, and *2 East 103rd -' PENN, Loiter W. (Af 1942) Chief Engr., W. J. PL, Chicago 28. /IU. '. :. : : .-Knight & Co.. Suite 719-724, 705 Chestnut St.; PETT, Alfred W. (Af 1942) ;Dir. of Research,. 'and *3916 Shreve Ave.. St. Louis 15. Mo. - Sterling' .Tool Products, 363 E. Ohio St., Chicago, r- PENNEY,. Gaylord W. (Af 1938) Mgr., Electro-. and$91 Vernon Ave., Glenco,-IIL .. - - ':; Physics - -Dept., Research Lab.. Westinghouse PETTINGELL; John M. (A 1945) DisL Repr., 'Electric Corp., East Pittsburgh, and 171 Orchard . American Air Filter Co.,.Inc., 201 Devonshire' . _Rd.;.WUldnsburg, Pittsburgh 21, Pa. - St., Boston, and 40 Temple SL, Belmont,.Mass. PENNOCK, W. B. (Af -1927) Pemiock Engi- PETTIT, Ernest N., Jr. (Af 1937) Chief Mech; heering, 53 Queen St.. Ottawa, OnL, Canada. - Engr., Wyatt C. Hedrick, Forth Worth 2, and - PENTTECOST,- Richard H. (A 1943) Syndo- - - 3012 EdgehilL Fort Worth 7,-Texas. ' _ - i .malic Corp.,5110North35thSt;,-Milwaukee.Wis. - PETTY, Charles E. (A: 1939) Htg. Engr.,>2120. PERHAM; -'Stanley'H. (Af 1944) Cons. Engr., Providence Rd., Charlotte; N. C. -^' f.' :M.'- Rotr . Engineering Co., 804'' Merchants PEXTON, Frank -S. (A-.-1936) -Indus:fErigr., Bank -Bldg., and 4507 Carrollton Ave., India- ' . Kansas City Gas Ca. 824 Grand, and 304 East - ; napoiis`5, Ind.- ... ' - 70th Terrace, Kansas City, Mo.- - ; ' :- - PERKINS/Stanleyl. H. (A 1945) -Application PEYREK, Theodore*. RK (Af -1945/ Sales^Mgr'" Engr.',`I*MinheapoIi&-Honeywell Regulator Co.,-. & Chief Engr., L. -J. Wing .Manufacturing Co.;X .205 Harrison St.,and 1681 W; -Colvin St., Syra- 154-West 14th St.. New York, and 121VDickie - cu9e,~N."Y. ' . Ave., Staten Island 2, N. Y.' s.. PFEIFFER,'David C. (Af 1940) Industrial Engr.. - _ Dallas Power-& Light-Co.. 1506 Commerce St., - - and 3516 St. Johns.Dr., Dallas, Texas. ' ; PFEIFFER; Frank F. (M 1938) Indus. Engr., PINKERTON; John B. (Af 1945) Cons. Engr.,' Dolby & Williamson, 3 Old Queen St., London SW, and 45 Northways, Swiss. Cottage, Hamp- stead; London N.W. 3, England. - United Engineers & Constructors, Inc., 1401-Arch - FINNEY, Theodore M. (Af 1942) Engr., 1888 St., and 7421 Sommers Rd., Philadelphia'3o. Pa. . ' Wymore; East-Cleveland 12, Ohio:- . . PFEIFFER, George R. (A 1945) Estimator. Harrigan & Reid Co., 1365 Bagley Ave.. Detroit . 26. and 1441 Canton Ave., Detroit 7, Mich. PIRRUNG, Richard.W. (Af 1944) Engr., The Huffman-Wolfe Qo., 669 N. High St.,-Columbus 16, and *409 Brevoort Rd., Columbus 2;'Ohio. . PFEIFFER, J. Fred (Af 1945) Registered Engr. PISTLER, Willard .C. (Af 1934) Cons. Engr.,' and Plbg. & Htg. Contractor, *953 Louisa St., Leverone Bldg., 4 W. Seventh St., Cincinnati ^,, Williamsport 4. Pa. and Orchard Lane and Crestview Ave., Cindn-. - PFISTER, Van Allen (A 1942) Sales Engr., nati 13, Ohio. - " .- McDonnell & Miller, 361 W. Superior Sti, and - PIZER, M. Morton (A 1943) Engr., Daniel- . *2212 Bennett Ave.. Evanston. 111. Morris-Co., 214 E. Sixth, New York, and * 109-36 PFRIEM, Peter G. (A 1937) Sales Engr., The 120th SL, South Ozone Park 20, N. Y. ' ~ . . Knapp Supply .Co.. Muncie, Ind., and *2531 PLACE, Clyde R. (Af 1924). Cons. Engr., *420. Burnet Ave., Cincinnati 19, Ohio. - * Lexington Ave., New York 17, and 333 East 57th - PFUHLER, John L. (A 1925; 7.1923) Plbg. & St.. New York 22, N, Y. . . Htg. Contr., *600 Manor Rd., Port Richmond PLAMONDON, Sarto R. (A 1944; 7 1943) Div. of 2. S. I.. N. Y. Industrial Hygiene, Ministry of Health &. Public PHELAN, James H. (Af 1945) Engr. & Estimator, . Welfare, Parliament Bldgs., and 103 Pere'Mar *G. W. Cunningham Co., 17-19 Wells SL, Hart- quette, Quebec City, P. Q- Canada. ' . ' ford, and "Overlook"; Lake SL, Columbia. Conn. PHERIGO, Faun Stephens (A 1944) Asst. Supt.. Htg. Dept., Indianapolis Power & Light Co., 17 / N. Meridian St., Indianapolis 6, and *5124 Maple, Lane, Indianapolis 1, Ind. - - ' PHILIP, William (Af 1937) Sales Engr.. Standard PLATTS, E. M. (A 1944) Vice-Pres., La-Del Conveyor & Manufacturing Co., New Philadel phia. Ohio, and 5 Lawson Ave:, Crafton, Pitts-' ' burgh-5, Pa. ' ' -' - PLATZ, John F. (A 1940) Zone Supvsr., Minne- apolis-Honeywell. Reg. Co., 5005 Euclid Ave., . Sanitary & Dominion Radiator. Ltd., Cor. Royce and- Lansdowne Aves., and 74 Bastedo Ave., . -Toronto,' Ont., Canada. PHILIPPI, Joseph J. (Af 1939) Mgr., Chicago Office; Johnson Service Co., 1355 Washington . . Blvd., Chicago/ 111. ' PHILIPS, Edward W. (Af 1945) Dist. Mgr., Walworth Co., 1110 Fidelity Bldg., Cleveland 14,"and 6306'Snow Rd., Parma, Ohio.' - . PHILLIPS, Charles R; (A 1945) Factory Planning Engr., Northern Electric-Co., Ltd., 1261 Shearer - St.; P. O. Box 369; Montreal, Que., Canada. - . PHILLIPS, Leonard R. (Af 1945) Sr. .Engr.. ' Anemostat Corporation of America, 10 East . 39th St,, and 857 Riverside Dr., New York, N. Y. PHILLIPS, Leonard S. (A 1944) Asst. Secy., Cleveland, and 1739 Holyoke Ave., East Cleve land. Ohio. PLAYFAIR, G. A. (A 1924) Mgr., -Johnson Tem perature Regulating Co. of Canada. Ltd., 113r Simcoe St., Toronto, and* West Hill, ` OnL,'- Canada. ' '' PLEUTHNER, Richard L. (7 1938) *393 Starin Ave., Buffalo 16. N. Y. . : PLEWES, Stanley E. (Af 1917) Mgr., Philadel phia. Branch; Johnson Service Co.. 2853 North 12th SL, and 341 E. Hortter St., Philadelphia, Pa. PLOSKEY, Edward J. (7 1940) Sgt., U. S. Army. 40th Ordnance Co.; Aberdeen Proving Ground, Md., and 2367-32nd Ave., San FranciscolO, Calif. PLUM, Leroy H. (Af 1935; A 1934) Warcen Webster & Co.. Camden, and 216 Second -Ave., .-New York Steam Corp:, T30 East 15th St.,- Haddon -Heights, N. J. '' .. New York 3, and 25 Wendt Ave.. Larchm'ont, N.Y. PODOLSKE, Arthur R. (A 1938) Pres., Mil PHILLIPS, Maurice E. (Af 1944) Mgr., 'Air waukee Metal Products Co., 1737 N. Palmer St.,' Cond. & Htg. Div., United Electric Service, 907 Milwaukee 12,.Wis. - - Louisville Ave., and Route .3, Spanish City, POGALIES, Louis H. (Af 1931) Mech. Engr., . DeSiard Rd., Monroe, La. - - * .PHILLIPS, Ralph E. (Af 1936) Cons. Mech. & " Elec. Engr., 816 W. Fifth SL, Los Angeles 13, Calif. ; PHILLIPS; Robert H. (A. 1941; 7 1938) lst-Lt.. Infantry. Army of the United States, 19th Ord. MMCO, Camp Campbell, Ky.. and 484JT .Oak- wood Ave.-, Los Angeles 4, Calif. PHILLIPS, Walter L. (A 1938) Lt: Col. Air Corps. _:*320 Forest Dr.. Falls Church. Va. ' -PHIPPS, Frederick G^ (Af 1930) Vice-Pres., Preston-Phipps', Inc., 637 Craig St., and *5431 Earnsciifife Ave., .Montreal, Que., Canada. .PICKETT, Clinton'A. (Af 1945) Branch Mgr.. ' " Herman Nelson - Corp.. 222 'W. Adams-St., . Chicago 6. and 600 Arlington Rd., Itasca, 111. Wilbur Watson & Assoc., 4614-Prospect Ave., Cleveland, and *19272 Coffinberry Blvd., Fair- view Village,ClevelandT'6, Ohio.' - ' POLAD, ...Thomas H. (A 1946; 7 1943) Chief Engr.,-- Rudy Furnace Co., Prairie Ronde,-and 201 Sheldon St., Dowagiac, Mich. . - '* POLLAK, Rudolf (Af 1937) Chief Engr., Rocker feller Plaza, 3rdlFl,, New York 20, and 350 .West 57th St.. New York; N. Y. - -' '. POLLARD, Alfred L. (A 1932), Gen. SupL of .. Power,- Puget Sound Power & Light Co., 860 Stuart Bldg., Seattle 1; and 3009 28th Ave. W.,' - QO U7oeh ' ~ .POLLARD, Charles H. (A 1944) Mgr., C.-H. . PIEKSEN, George W. (Af-1944) Sales Repr., . Pollard Plumbingjk Heating Co., 813 First Ave.. - Sarco Co.. Inc., & Spence Engrg. Co.,`3020 ' and 143 Morris St", Monte Vista, Colo.. - Olive St.. St. Louis 3, and 7017 Waterman' Aye., - POLLOCK, Carl A. (A 1937) Gen. Mgr., Domin '-.University City 5,-Mo. '' - PIERQE, Edgar D. (A 1946) Sales Engr.. Harold ion Eiectrohome-Industries, Ltd., 39 Edward-St., -and 120 Sterling /Ave.; Kitchener,-Ont., Canada. . E. Peterson, 1350 Elwood St., Los Angeles 21, and -2705'West.84th St., Inglewood. Calif. PIERCE, H. Charles (Af 1945) Asst. Mgr.. Air. , Cond. Div., Sensei, .Inc., and 847 E. Gum St., ' Evansville, Ind.'. ` * ` . ` .' . PIERCE, Joseph Dl (A 1946; 7 1942) AssL Re search Engr.,- Crane Co., 836 S. Michigan Ave., - Chicago 5, and 1634 East 53rd St., Chicago'15, 111. -. * - PIERPOINT, Harry Y. (A 1943) Owner, J. A. 'PierpoinL 1338 Half St. S.E.rand *3554 Appleton ' St. N.W., Washington 8. D. C. .- PIETSCH, Herman A. (Af 1945) Chief Etigr., POLLOCK, Clancy W. (A 1944) Research Engr., ', * Drayer-Hanson, 738 E; Pico Blvd.",1 Los Angeles 21, and 3900 Ingraham SL, Los Angeles 5; Calif. POND, William H. (Af 1938) Htg. Engr..,General Cable' Corp., Perth Amboy, and 820 W. Front St., Plainfield. N. J. '. PONDER, Everett A.' (A 1939) Owner;** Everett . A. Ponder- Co.', 3424 N.E. 65th Ave., 'Portland 13. Ore. . . .. /. PONS, Raymond A. (A -1945) .Mgr., Pons and Davis; 271-3 Edison Si., Salt Lake City '1,'and 613'Milton Ave., Salt Lake City 5, Utah.--' ,- - ' \ - Heater Sect., Dravo Corp.-, 300 'Penn Ave., Pitts POOLE,-Joe A. (A 1945) Chief-Engr., Dallas . - burgh',: and 894 Heckler Dr:, Pittsburgh 20, Pa. -- Air-Conditioning Co., 2809-11 Canton St., Dallas ." PILLEN, Harry A. (A -1933),Owner. Hrray A. 1, and 4819 Swiss Ave., Dallas'4`, Texas. ' ` , PiUen Co.', 626 Broadway, Cincinnati 2, and 2124 .POPE, Edward -F. (A ..1945) Business -Mgr., Crane Ave.. Cincinnati, Ohio. Carrier Corp., 300 S. Geddes SL, Syracuse, and " `PINES, Sidney- (Af. 1920). Owner & Gen.-Mgr., Edwards Dr.,' Fayetteville, N: Y. - t ->Pines Engineering. Co., 1831 Clarence St., Dallas 1, *and 3541 Bryn Mawr Dr., Dallas 5, POPE, S..Austin (Af .1917) Pres., William'.A. Pope Co., 26 N. Jefferson-St., Ghicago. ;and 831 Texas. . . . - .' - Ashland Ave.,'River ForesL.111. ' . ' 66 Heating Ventilating Air Conditioning 'Gu.idell946 sr*-. Erf**\t- VI : PORTE, Cliff E. (A 1945). Mgr.. W. A: Case & . PREBENSEN, Harold J. (Af 1938) Exec. Vice- . * Son Manufacturing Co., 2337 Beecher St..* Detroit Pres. & Dif., Air Comfort Corp., 1307 S. Michigan . 16, and ' 18110'Patton Ave., Detroit 19. Mich. Ave., Chicago, and R. F. D. No. .1, Meadow PORTER, Carl W. (Af 1943) Engr.', (Naval Archt.) Lark, Northbrook, Ul. -- Air Cond: Sect.. Navy Dept.,. Bureau of Ships. _ PRENTICE, Oliver J; (Life Member; A 1927) Washington. D.- C., and *409 Tennessee Ave., ` . Dir., of Publicity & Public Relations.v C. A. Dunham.Co., 450 E. Ohio St., Chicago 11. and ,'PORTER. Frank (A 1946; 7 1944) Owner, Porter . Engineering Co., 5311 Georgia Ave. N.W., Wash ' ington, D. C.. and 7717 Chicago Ave., Silver - - ' Spring, Md. . '" . . ' - PORTER, H. Merwin (Af 1945) Pres.. Belden 457 Barry Ave., Chicago. Ill; - PREWITT, H. B. (A 1939) Asst. Branch Mgr.. American Blower Corp., 783 Broad St., Subur ban Station Bldg., and 615 E. Allen Lane, Phila delphia, Pa. - - Porter Co.. 65 North 17th St., and 5032 Fremont S,, Minneapolis. Minn. , -PORTER, Hugh T. (A 1944) Vice-Pres., W. B. ; > Connor Engineering Corp.. 114 East 32nd St.'. PRICE, Albert Z. (A 1945) Pres. & Treas., *The . A. Z. Price Co.. Inc., 225 Piedmont Bldg., and - 2232 Avondale Ave., Charlotte. N. C. . ' PRICE, Charles E. (A 1933) Secy.-Treas., ^ ` - New York 16, and 12 'East 97th St.. Apt. 10H, Keeney Publishing Co., 6 N. Michigan Ave.. ' ;,New York 29. N. Y. . - . PORTER, Noel E. (A 1943; 7 1938) Lt. (jg). . . U. S. N. R.,.Navy Dept., Bureau of Ships. T4- Chicago 2, and 106 Park Ave., Glencoe, 111. PRICE, Charles F. (A 1943; J 1937)Lt.. 1015 . W. Washington St., and Knapp Supply Co., 515 ` 2084,- Washington, D. C., and 1017-44th St., ' S. Ohio Ave., Muncie. Ind. .- " .1 '.Sacramento, Calif,-.. ' - PRICE, D. O.- (Af 1934) Htg.-Air Cond. Engr.. POSEY, James (Af 1919) Cons. Engr., *10 E. General Steel Wares, Ltd., 199 River St., and * ' :'J'. Pleasant St., Baltimore 2, and- 4005 Liberty - 131 St. Germaine Ave., Toronto. Ont.,- Canada. - : . Heights'Ave., Baltimore, Md. * - PRICE, Ernest,H. (M 1939; A 1937; J 1934; 5 ; POST,' Gerald A; (Af 1943) Mech. Engr.. Engi- neered Products Co.,-20 S. Senate Ave.. Indianap - .olis 4. and 3587 N. Grant Ave.. Indianapolis l,.Ihd. . POTTER, Christopher D. (Af 1944) Supt. & ..Engr., The Smith-Gibbs Co., 201 S. Main St., '.^.-Providence 3,'and 140. Walnut St., East Provi- ' -si -dence 14. R.I.- ' - ; -` ' ' 1932) Major, R. C.' E,, Canadian Army. Dept; Works & Construction. N. D. H. Q.. Ottawa. Ont., and 170 Harbisbh Ave., Winnipeg, Man.; Canada. - PRICE, Frank E. (A 1944) Sales Mgr. & Vice- _ Pres.. Peerless Colorado Co., 785 S. Broadway. and Denver Athletic Club, Box 988. Denver. Colo. ... . -. PRICE; Wilkes C. (Af 1943) Dept- Engr., Poe Piping & Heating Co., P. O. Box 299. Knoxville, POTTER, John R. (A-1939; 7 1938) Lt., U. S. and 130 Emerson Circle, Oak Ridge, Tenn. . 'N; R.,' Bureau of Ships, Navy Dept..-and 318-1 PRIDE, Harold K. (A' 1943) Dist.-Mgr,, Minne- ` -..'17th St. N.E., Washington, D. C. _ - . .apolis-'Honeywell -Regulator Co.. 2405 Maryland ' r ; POTTS, Amos P. (Af 1944) Chief Engr., Logan - Ave'.. and 5154 N. Lydell Ave., Milwaukee II. Wis. " . Clay Products Co.. 359 E. Main St:'. Logan. Ohio. PRIDE. William B. (A 1945) Field Engr., Boeing v POUGHER. Bernard R. E. (J 1940) Sgt.,110 Aircraft Co., < Dept. 434, Georgetown P. O.. . .. (ELVA. T. Coy. R. E.. and 99 Mauldeth Rd. W.. Seattle, and 2820 South 152nd St.. Seattle 88. > - -1. '-Withington, Manchester, England. - ' , Wash. ' . ... 1 ' POUJADE, James V. (A 1943) Refrig., Vent. & ' PRIEBE, O. Willard (A 1946; J 1945) Assoc. . Air Cond', -Engr., 1235 Alvar St., New Orleans Mech. Engr., U. S. Navy, 13th District Hq., ' . . ''17, La. / : - - Seattle 1. and 47i0 26th Ave. S., Seattle 8. Wash'. v . POUND,'Howard W. (Af 1941) Mgr., Air Filter' ' Div.,* American Air Filter .Co,, 215 Central' Ave/, .Commodore Apartments. Louisville, Ky. POWELL. George W., Jr. (Af 1938) Indus. Engr.. PRIESTER, Gayle B.* (Af i943; / 1935; 5 1934) - ' Asst. Prof.. Case School of Applied Science, , Cleveland _6r and 1163 .Oxford Rd., Cleveland Heights 21, Ohio.. '- ` PRINCE, Raymond F. (A 1943; 7.1936).Engr.. . United Engineers &'Constructors. Inc., .1401 ' . Arch St., Philadelphia, and 458 S. 'Fourth St.. ' -Colwyn. Darby, Pa. ' . - _ ' R. B. Dunning &'.Co..'68 Broad St., and*Bur leigh Hill, R. F. D. 1. Bangor, Maine. . PROCTOR, Charles. William (A * 1944)' Sales. : .POWELL, Leroy D.. (A 1945) Owner, L.D. Engr.; The Conditioning Co., Inc., 19 Herbert PI.; - .-Powell Construction Co., 209-10 Farnsworth Bldg., Newark 4. and 1309 E. - Seventh St., Plain- . < . - and 3587 Waynoka Ave., Memphis, Term. -field, N.J.- . ' ' . . .. POWERS,. Earle.C. '(Af 1939) Partner, E. C., PROIE, John, (if 1936) Mgr., Proie Bros.. 856 Powers :& Son, 135 Arch St., Philadelphia 6. Pa. ,W. North* Ave.. Pittsburgh 12, and-R. D. 10, -. . .POWERS, F.W. (Life Member-, M 1911) (Council. Box306,-Pittsburgh'10, Pa. ' " . 1918-19) Chairman-of the .-Board, *The Powers PROTHEROE; Richard A. (A 1943) Dist. Mgr., - Regulator Co.,.2720 Greenview Ave./Chicago 14, The- Anthracite Industries, Inc.,' 1617 Pennsy- >v and 900'Castlewood'Tenace, Chicago 40, 111. ' ' vania Blvd., Philadelphia 3, and 77.Fairfield Rd., POWERS, Lowell:(A 1937; J 1930) Branch - Brookline. Upper Darby, Pa. .- . . s.,-Mgr.'?*Carrier''Corp., 1315 Williamson Bldg.. . PRUITT, Clarence H. (A 1944) Air Cond. Oper- Cleveland- 14,-`and 2730.Cranlyn Rd., Shaker - - ator, Allison Division of General Motors .Corp., . Heights, Ohio. - r -, Indianapolis, and 651 NC Berwick Ave., Indiana- . POWERS, -Robert. Wi (J. 1943 ; 5.^ 1941) .Ens:, polis 8, Ind. ' ' . ' - -: rT . < Uv-S. N; R./and 411 W.-Main St., Bennetts-"' PRUSSING/'Ralph L: (A 1945) Design Engr.; ville, S. C. , 'r ' - ' '' . Gansman & Moore, 1026 E. First National Bank. POWERS/Rowan. E. (A 1945).Asst. Gen. Mgr., St. Paul,' and 1994" St. Claiv 'Ave:. St. 'Paul . - Sarco Canada, Ltd., 85, Richmond..St. 'W.-, and 5, Minn. ' - , ' " '" . - - *998 Logan Ave., Toronto,-Onti. Canada. PRYIBIL, Paul L. (A 1932) *3372 N. Mountain POWLESLAND. John ,W. (A 1944; 7.1942) Field - -Engr;. .Canadian.-Sirocco Co.,. Ltd., .57 Bloor St.* " - v W.,-Toronto,Varid R.,.R; No* ^.-Wpodbridge. : OnL, Canada. ' v ' View Dr., San Diego 4, Calif. - f ' ` ' * PRYKE, John K. M. (A 1937) Assoc., Meyers. - Fuller & Addington,'21 East 40th StI; New York': -16; and *140 East 81st St., New'York. N.' Y.. v- POYTHRESS,-John D,. (A 1945) Engr.; W. E. . PRYOR, Albert S. (Af 1944) Vent. Engr.. Tern ; -.7 Lewis .& .Co.;7610 'Thomas. Bldg., and *3410. - stedt Manufacturing Div., General Motors Corp.. . Asbury, Dkllas,}-Teias. -\_.' Detroit 9, and *14829 Euclid Aye.,'Alien-.Park, . ... sv.PRATS,Sldney:Ni.(A'1945).Partner. Sidney N. . ' Mich'. Prats. Sheet'.Metal Works. 2006 Toulouse St., PUGH. Daniel C. (A 1946; 7 1942; 5 1939) Mech. --New Orleans 19,'. and '317 S. Gayoso St,;" New Engr.; Carbide & Carbon Chemicals Corp., Me- . j-:: ..OrfensTI^i ;; ,.`x ` c. 7- - /> . . '* Corkle Ave., and 1024 Village-.Dr. S.W., `S. '-if* PRATT^Foster Ji (Af-1937) Pres.^ International" - Charleston 3, W. Va. ' . - .' Federatioh-of-Technical. Engineers. A.. F. of`L. PULLEN, Royal R. (Af 1935) Chief Mech. Engr., Bldg., -Robm.200, Washington -1. and 329 Willard ' Homestake. Mining Co., and 109 E. Hill .St., - : Ave., Washington 15,. D.-C:' ' ' .. - Lead. S.'D. n ^.-iupRAWLr^Fmhk (Af 1940;V 1936) . Mgr. &* - PUIXI.TM, Clarence -E. (Af 1940) Vice-Prea.r *"5 * Cliief Engr.; Sidles- Cb.,-^Air Cond. Div.,- 502, Bell & -Gossett Co.', .8200, N.' Austin Aye,,- .South 19th;St.;.Onmha,2,'and *1712iNorth 54th . Morton Grove, and 1011 N. Grove-Ave.. .Oak/- ^'.n'maha 4, >NphrT ; ` . Park, III.-.:- -- ; r-. s. ';-rRoll of Membership-' , - 67 PULTE,' John W. (A 1945) Mfrs. Agent, J. W.' . RAMSEY, Emest C- (A/ 1944) Htg. Engr., The. ; ' Pulte Co.. 308 Gladstone S.E., Grand. Rapids Ohio Fuel Gas Co., 109 N.- Front St., and 1493. : 6. Mich. - . . -' . . Belmont Ave., Columbus,"Ohio. .- PURCELL, Frederick C. (Af 1926) Sales Engr., - Minneapolis-Honeywell Regulator Co.;:415 Brain . ard St., Detroit 1, and 18680 Santa Rosa Dr,, ' Detroit 21, Mich. ' - - PURDUE, Frank (Af 1943) Chief Engr.. Odhams ' . (Watford), Ltd., St. Albans Rd:, and *46 Tudor . .Dr., Watford, Hertfordshire. England. .. - PURINTON, Dexter J. (Af 1944; A 1923) 124 . East 24 St.. New York 10, N. Y. PYSHER, Maurice. W. (A 1944) Sales. Mgr., . Standard Supply Co., 934 S.E. Sixth Ave.,- Portland' 14. and 641 N.E. 79th Ave., Portland, . Ore. .. - RAND, Fred R. (Af -1938) Sales Mgr.. F-nampI Heating- Products, Ltd., -Main St,, and *P.* O. Box 512. Sackville. N. B., Canada: . - _ i - - RANDALL, Gordon E. (A 1944) Supt:. Randall & Co.. Ltd.. 565 Portage. Ave., and-699 Banning St.. Winnipeg,.Man., Canada. - .\ RANDALL, Robert D. (A 1937) Partner,.* D. T. Randall & Co.. -7310 Woodward Ave., 404 Boule vard Bldg., Detroit 2, and 340 E. Grand Blvd.,- Detroit 7, Mich, I' RANDALL, W. CUfton* (Af 1928) Chief Engr., Detroit Steel Products Co., 2250 E. Grand Blvd.,' Detroit, and 770 Shirley.Dr.; Birmingham., Mich. RANDOLPH, Charles H. (Af 1930;.A 1928; J, "1926) Air Cond; Engr,, Wisconsin Electric Power Co., 231 W. Michigan St.. Milwaukee, and QUACKENBUSH, Seelye M. (Af 1940) Partner, Route 2. Thiensville, Wis. " ' .. ' . Quackeribush-Co., 505 Franklin St., Buffalo 2, RANDOLPH, Harold F.* (Af 1940) Vice-Pres;. and'251 Parkside Ave., Buffalo, N.-Y. International Heater Co.,' 101 Park Ave.. Utica QUADE, Harry, Jr. (A 1944) Partner. William 2, and 12 Woodlawn Ave. E., Utica 3, N. -Y. . .' ' Schupp & Co.. 715 S. Eighth St., and 1419 West RASTRICK. R. J. (Af 1945). Supt. Engr., Vale 27th SL, Minneapolis, Minn. -- & Co..-Ltd... 141 Armagh St., and 21 Rastrick "OUALL, Clarence. O. (A 1937). Owner, Quail St..-Christchurch. New Zealand. -.- :. Plumbing & Heating Co., 65 Ninth St., and *54 RATHER, Maxwell F. (Af 1919) Dist. Mgr., . Pearl St., Clintonville. Wis. * Johnson Service Co., 28 East 29th St.,; New . QUEER, E. R.* (Af 1933) Comdr., U. S. N. R., York, N. Y,, and 40 West Elm St.. Greenwich, V Bureau of Ships, Navy Dept:, Washington, D. C., Conn. - ' - -" . -.- : and 5707-26th St. N.. Arlington 2, Va. - - RAY; George E. (A 1946 ; 7 1939),C. E. M., 'QUIGLEY, Miles E. (A 1945) Erigr.. Harris Bros! . U. ,S. C. G. R.; U. S. C. G. C. Buttonwood; F. P. O.. . Plumbing Co., 217 W. Lake St.; Minneapolis, and San Francisco. Calif., and 22 West Ave., Ely .- *Rt. 2. Hopkins,' Minn. ' ria, Ohio. ` - -' - .QUIN, Char!es C. (A 1944) Branch Mgr., The RAY, John A. (Af 1942) Sales Engr., W. E. ...' Powers Regulator Co., 809.Stuart Aye..-Houston . Lewis & Co.', 610 Thomas Bldg., and'5211 Stone-, - 6. .and 820 Fugate St.,. Houston 9, Texas. leigh Ave., Dallas, Texas. . .s /' ' QUINSY, Lloyd B. (Af 1945) Indus. Engr.. RAY, Lewis B. (Af 1932) Pres., Ray.Engineering Houston Lighting & Power Co:, P. O. Box 1700. Co., 830 Broad St., Newark, and 151 -Augusta . Houston 1, and 5919 Fordham.- Houston, Texas. . St.. Irvington, N. J. ' ' QUIRK, Clinton H, (Life Member; Af 1916; 7 RAYMER, William F,, Jr. (A 1936; 7 1934)' 1915) -Engr., Htg. Plbg.- & Air Cond.. Third Naval - Htg>Vtg. Engr.. Wright Aeronautical Corp.. 132. - Command, 90 Church St.. New'York, and *465 Beckwith Ave., Paterson.-and *413- Walker -Rd..' ' -Front St.. Hempstead, L. I., N. Y. . West Orange, N. J. . ' QUIST, Oswald F.,:Jr. (A 1945) Installation & Service' Mgr.. Minneapolis-Honeywell Regulator _' Co., 221 Fourth Ave., New York, and *76 Nichols RAYMOND, Fred i;* (A 1929). Owner, F.-'I/ Raymond Co.. 629 W. Washington Blvd., Chicago 6, 111. .. . Ave^ Brooklyn 8. N. Y. - . . ; RAYNIS, Theodore (A 1939; 7 1934) Naval Archt.. Navy Yard, Brooklyn, and *58 Hilltop. Dr., Manhasset, L. I.; N. Y. - ... . .- - * READER,. Joseph T;'(A 1938) Partner. * Kerr . RABE,-Albert'E.' (Af.1938) Pres., Carrier fengen' - haria S/A, Caixa Postal-90,' Rio de Janiero, Brazil.. . - Machinery Co., 608 Kerr .Bldg;, Detroit. 26, and 8162 E. Jefferson Ave., Detroit, Mich. - "' . - . . RAjBER, B: F.* (Af 1937) Prof. Mech. Engrg.. . .' University of California, 114 Engineering Bldg., Berkeley 4; and-1124 Arch St.. BerkeleyS, Calif. REARDON. John F. (A 1941) In .Service, Rtl 3, Fourth and O St., David City. Nebr.- ; " `" REDRUP, war D: (Af 1936> Chairman, *The . - Majestic Co;, 310 Randolph St., Huntington, Ind! RADOTINSKY, Joseph W. (Af 1945) "Archt. REDSTONE, A. L. (M . 1931). Research .Engr., Engr., *312 Commercial National. Bank Bldg., ! Proctor & .Schwartz, Seventh and Tabor.* Rd;." - Kansas City. 12. and' Nearman:Rd. & Kimball and 1636 E. Duval. Philadelphia 38, Pa. Ave., Kansas City, Kans. . -; , ' REED, A. -George. (7/1944). Draftsman;*The . RAIDER,.-George'Kr (X 1944) Sales Engr.,- * Pyle Gurney Foundry Co., Ltd.. - 4 Junction* Rd., - National.Co.,-'1334 N. Kostner Ave'.. and 1825 Toronto, and 478 Glen Park Ave., .Toronto-, 10,' ''/N.-Wlfipple St., Chicago.'"111. - ' *, : Ont., Canada. .- ' RAINEY; Hugh D. (A 1945) Pres., Rainey -REED, Frederick J. (Af 1939) Assoc. Prof.,-Mech. 7 ..Roofing-St-Sheet Metal Co., 301 E: Fourth St., Engrg..,* Duke University, 263 ;College Station,. T^nd 522 N: Pearl, Joplin, Mo. . ` . . and 2203 Englewood'Ave., Durham,'N. C.', , RAINEY.-Norman W. (A 1945) Air Cond.: Engr..- -REED; George G. (Af -1944) Htg.-&-Vtg.`Engr.. x Danforth Co;, 5820 Centre Ave., Pittsburgh 6. N. A. C.' A., Cleveland Airport., Cleveland; and ' and R.'D. 2, Canohsburg.vPa.- .. 22913 Mastick Rd., Rocky River'16, Ohio.'-''.. GRAINGER, Wallace F. (A 1930 ; 7 1924) Jams, Baum'& Bolles; 415 Lexington Ave.. New York 17: / ^and *441- Hawthornd Ave...Yonkers-5; N. .Y; ,,. .'RAINSON, Samuel J. (7 1940) .Navy Seebees,.- `2nd Class. PI : 0. Machinist Mate',- and * 4316 J- Wickham Ave., Bronx 66. N. Y. . - - .' REED, Stanley 'F. (J 1943)'* Reed Research; Wisconsin Ave. and'K St. N.W., Washington^,'. and 4753-Reservoir Rd. N:W.,'Washington,- D; C. aREED, T. M.,; Jr. (Af ,1944) Mgr."; N. Y. Office,; .. - John J. Nesbitt, Inc., 11 Park PL. New. York 7,, rand 89-25 Parsons Blvd.; Jamaica, N.`Y.` . T* - ' REED,-;Van A., Jr. (AL 1930). Secy.. Federal RAISLER. Robert K. (Af 1941; A 1933 ; 7 1930) Engineering Co.. 239 Fourth Ave., Pittsburgh 22,. '`-Lt. Comdr. U. S. N. R..-USS-Boxer. F-. P. O.. New York, and 38 E^st 85th St., New York, N.Y. ' and 114 Water St.. Elizabeth, Pa. - ' REED, :Virgil C; (Af .1938) Mgr;. James: H.L RAMBO, ` Charles (Af 1945) Owner, Sunbeam Pinkerton Co.,'640 Natoma St.-.', San Francisco. 3.-, Heating Sc Air_Conditioning Cp.,?509 12th'St-., ' , and 3117-Lakeview Way, Redw<x>d City,'.Calif.- P.' O. Box 121; and 1606 16th Ave.,-Columbus, Ga. .REED,.William H., Ill (A 1938) Acoustic.Gear.. RAMONEDA, Enrique (A 1944; 7 1941) Contrac- Officer, Lt., U. S; Navy, Navsil, Mine' Warfare' ' tor, Ing. Enrique Ramoneda, -Bahia De Chacha- Test Sta.; Solomons, Md.. and c/o. Dravo Corp... lacas 42, Mexico,- D. 'F. . ' , 302 Penn Ave., Pittsburgh, Pa.' - -;- ,J '"RAMSEUR, Vardry D., Jr. (7 1940) Htg. Engr., REES, Harold R. (A 1944) Owner. Rees Plumb Ramseur Roofing Co.. Inc., 353 W. McBee Ave., - -ing.&'Heating Co.-,rBox'639,-and-1107 Warner' arid\50 Woodvale Ave., Greenville; S. C, y `Ave., Jonesboro, Ark.--{ - ' '' -RAMSEAUR. William S. (7 1945) Dvlpt.-Engr.. REESE, Henry L. (Af,, 1941) Coni. Engr., * 632. Carrier Corp., 300 S. Geddes St., and 412 Green-- Washington< St., .Reading, and "The Pines.", V'wobd'Pl.. Syracuse. N.*Y.->.-, ' * . -. R. D. 4;-Condersport, Pa.-' *'' - Heating Ventilating Air Conditioning Guide '1946 REGER, Henry P. (Af 1934) Pres., H. P. Reger RHOTON. W. R. (if 1936) Vice-Pres.,- The R.. & . & Co:. 1501 East 72nd PI., Chicago 19. 111. H. Systems, Inc., 5501 Euclid Ave.. Cleveland, ';/ REH, Herbert C. (/ 1945) Pvt., U. S. Army. and * 1728 Lee'Rd., Cleveland Heights, Ohio ' ' 42212916, and *61-64 Linden St., Brooklyn ' .RICE, C. J. (A 1923) Pres., Sterling. Inc.. 3738 " 27. N. Y. - .' ' N. Holton St.,' Milwaukee 12. Wis. ' . ` REICH, J. G. (A 1941) Health-Aire, 995-997 RICE, John A. (Af 1945) Mech. Engr., Merritt. East 79th St,, Cleveland 3, and 1654 Hayden Ave., ' Chapman & Scott, 17 Battery PL. New York, and. ' " Cleveland 12, Ohio. . . 62 Elizabeth Ave., Hempstead, N1 Y. ' REICHOW, William A. -.(A 1945) Branch Mgr., RICE, Percy - L. (A 1944) Maintenance Engr., . 7 - Minneapolis-Hoceywell Regulator Co., 3101 -War Dept., Fitzsimons General Hospital, Denver, Gillham Plaza, Kansas City 3, and 7331 Madison. and 1427 Humboldt St., Denver 6, Colo. t .'Kansas City 5. Mo.. - RICE Robert B. (Af 1934) Dir., Naval Diesel , : s REID, Henry P. (Af 1931; A 1927) Asst- to Pres.. School, North Carolina State College, State Col ': Universal Atlas Cement-Co., 135 East 42nd St., lege Station, and 2712 Cambridge Rd.. Ra- V New York 17, and 72 Mercer Ave., Hartsdale, N.Y. Ieigh,-N. C. . '. - REID, Herbert F. (A 1932) Partner.. Htg. Dept., RICHARD, Edwin J. (Af 1933) Mgr., Richard . Reid-Graff Co., 1417 Peck St., and 1552 MafetL Equipment Co., 2137 Reading Rd., Cincinnati 2, . Muskegon Hgts., Mich. ' .' - and 3147 Victoria Ave., Cincinnati 8, Ohio. REIF, Allan F. (Af1937) Pres., Reif-Rexoil, Inc.. RICHARDS, Guy H. (A 1939) Capt.. C. E.. .. . 37-43 Carrol St.. Buffalo 3,. and 110 Devonshire ' ` c/o Fuel & Htg. Section, Hq. 4th Sv/ C., 5th . > .. 'Rd.. Kenmore. N. Y. . . FI. Walton Bldg.. Atlanta, Ga., and 7230 First :: REIF, Charles A. (Af 1937) VicerPres., Reif-. Ave. S.,.Birmingham 6; Ala.- - -, ' Rexml, Inc., 37- Carroll St., Buffalo 3, and 77 RICHARDS. Leslie V. (Af 1941; A 1940) Owner- ; Ruskin Rd:, Eggertsville 21, N. Y. Mgr.. Richards Oil Burner Sales & Service, _ ..' REIFSCHNEIDER, Jake (A. 1938) Maintenance 97 Lawrence St., Malden, Mass.. .. .> ,v Mgr., Eppiey Hotels Co., 1802 Dodge St.. RICHARDSON, Frank C., Jr. (Af 1943) Sales Omaha 2, Nebr. . : , . Engr., A. L.'Vanderhoof, Inc., 233 Hamm Bldg..' ' : REIHER, Herman (A 1945) Bldg. Supt.,. Baker Cleveland'15. and *3085 Warrington Rd., Shaker. . Properties, Inc., 510 Baker Bldg., Minneapolis Heights 20, Ohio. z" 2, and**5501. Xerxes Ave. S.. Minneapolis 10. RICHARDSON, Henry G. (Af 1934) Pres.. V -'Minn. - ' . . . ' ' '` ' Williams-Richardson Co... and 1433 - Harvard REILV Henry W. (Af 1945) Engr.. Carrier Corp.. ' Ave., Salt Lake City, Utah. - ,V; 348 -Peachtree St., and *2000 Polifax Dr. N.E., . RICHARDSON, Robert D, (A 1946; J 1938) Htg.. -Atlanta, Ga.' ' '. ' REILLY, Bertram B. (A 1946; J 1938) Engr., 7 ` ' .- Dravo Corp., Machinery Div., 300 Penn Ave., . *- -Pittsburgh, and 220 Ridge Ave., Ben Avon, Pa.. . REILLY, J. Harry (Af. 1943) Design Engr., - __ ' ' Federal Shipbuilding and Dry Dock Co. ,-744 Broad ' St.v, Newark, and 14 Watson Ave.. East Orange. : ' ' . Draftsman, Hope's Heating '& Lighting, Ltd*. Halford Works, Smethwick. Staffs, and *85 Silhill Halt Rd., Solihull. Birmingham, England'.. - RICHEDA, Alfred (A 1944) Supt./ The Lang Co., P, O. -Box 479, Salt Lake City 9, and 1557,- Laird- Ave., Salt Lake City 5, Utah. .- . / ' N. J. ... . ; RICHMOND. John (Af 1944) Chief Engr., *The - -REILLY,' Philip H,, Jr. (A 1941) Purch. Agent, Sweeny & Wise Co., . 10210 Woodland Ave., Fraser & Johnston.Mfg. Co., 725 Potrero Ave., Cleveland 4, and 3863 Grosvenor Rd., South __ San-Francisco 10, and 1321 Van Couver, Ave.,' Euclid, Ohio. ; . - . -V*. :Burlingame. Calif. . " - RICHMOND, K. C.* (Af 1943) Editor. Coal-Heat V_ REINHARDSEN, Daniel (Af 1944) Dist. Sales . (Magazine),' 20 W. Jackson Blvd.. Chicago, and Mgr., Spencer Heater Div.-, The Aviation Corp.. 846 Park Ave., River Forest: 111.' \ - * 101 Park Ave., New York 17, and 355 Hawthorne RIEHL, William L. (A 1945) Asst, to Vice-Pres., . -.Terrace, Mt.'-Vernon, N. Y. ' ' - The Union Fork & Hoe Co., Rome, and R. D. 2, . - REINKE, Alfred G. (A 1940; / 1933) Secy.. ' Marcy, N. Y. - - -' ' ` - . Gus. Reinke Machinery & Tool Co.,' 385 Hillside RIES, Lester S. (Af 1929) Supt.-, Dept, of Bldgs. & / . Ave., Hillside; and *321 Park PI., Irvington, N. J. . Grounds, *Oberlin College, 32 E. College St.," REINKE, Louis F. (A 1937) Owner, Louis Reinke and 291 Oak St., Oberiin, Ohio. ' .... -Sheet Metal Works, 534 S. Fifth St., Milwaukee 4, . and 1535 W. Walker St.r Milwaukee,-Wis.- ' : REIS, Robert (A 1944; J1939) Chief Mech. Engr.. :;-.* Wigton Abbott Corp., 1225 South'Ave.. and ; 563 W. Eighth St..' Plainfield, N; J. REISBERG, Lester K. (Af 1942; A 1939) Vice - Pres.*. Goodin .Co!,-615 N. Third St., and.Rt. I, . *. A'nnka, Minn: " > ' ' -' ' RIESECK, Wilbert L. (J 1943 ; 5 1941) Lt.. U. S.;_ .Army,-- Corps of Engrs.-, and *3763' East St.. ' Pittsburgh 14, Pa. . . - RIESMEYER, Edward H,, 1945; A 1936; L J1930) Htg: Engr;, Schaffer Heating Co., 231^33 . Water St., Pittsburgh 22, and 4702 Stanton Ave.,- Pitttsburgh 1, Pa. . " ' -*- ; REPP,-.Harry. L. (Af 1940) Branch-Mgr., *U. S. RIETZ, Elmer W,, (Af 1923) Mgr.;.Spedalty Div., * -Radiator Corp.. 5512 Euclid Ave., Cleveland 3., .. -*The Powers Regulator Co., 2720 Greenyiew --and-14611 Clifton Blvd., Lakewood 7.'Ohio. ` ' Ave.,' Chicago, and 2250 S. Sheridan '-Rd., High- . : 'RESCH, Roy J. (A 1940) Pres., McQuay, Inc., ; . land Park, III. ' ,. - 1600 Broadway'N.E., Minneapolis 13, Minn.' - RILEY, Edward F. (A 1945) VicerPres.. Palmer . RETTEW, Harvey F. (Af 1929) Chief Engr... Supply Co., 222-Westlake Ave. N,,. and *605 ' \ Board, of Education, 21st and Pkwy.,-and *5466 Spring St.. Seattle, Wash. . .; \ Baltimore Ave., Philadelphia 43, Pa. ' RILEY, John N. (Af 1942) Lt.. U. S. N. R.. and; . REX; Harland E. (Af 1942) Carrier Corp., 20 N. c/o.C. A. Clark, 1950 E. Tremont Ave..'New. ` -'Wacfcer'Dr., Chicago' 6; and 7255 W.'Greenleaf York 62, N. Y.' ' . -' - - Ave.-, Chicago 31,-111:. - , . *. ^ RIND, Karel (A 1945) Engr. in charge of Air . . REYNOLDS, James C. (A 1945) Air' Cond. Service , Cond. Div., Vale & Co.,. Ltd., Armagh St.*, and-; Ehgr..vWestinghouse' Electric Corp., -"1503 Gulf- '.* Hotel-Stonehurst', 241 Gloucester St., Christ-' V < . BldgM-Pittsburgh 19,'Pa. . i. ` . ' church. New'Zealand. ' '. ` - REYNOLDS,: John F. (A 1945) Refrig. & Air RINK, Charies N.' (Af 1942) Dir., Engrg.. Derign. -. i Cond.. Engr., = StotleyV Services, Inc., 2119 ' and Research, McQuay, Inc., 1600 Broadway ' 7,- r Colonial Ave.: Norfolk, and-* Gatling and Marble- / N.E., and *4802 Emerson Ave. S., Minneapolis - Ave.C Norfolk-2. Va. - ' : ' 9. Minn. ' - . * .- ' ' REYNOLDS, Thurlow W. (Af 1922) *100 Pine- RISLEY,-George H. (A.1941) Mgr.. Cole Draft - -crest-Dr.: Hastihgs-on-Hudson 6, N. Y.' _ Governor Co*. 516 S;'W. Oak St., Portland 4, and ; ; 'REYNOLDS,.. W. V. (A ,1928) Pres.. Walter Rt. 10, Box 772, Portland 2, Ore.- : ~-Reynolds,. Inc., 861'Third'Ave., New -York, and RITCHIE, A. Gordon (Af 1933) Prra.. John. ' ISO Boulevard: Scarsdale. N.' Y. ' - .7. . - ' ; Ritchie, Ltd:, 102 Adelaide St. E., and 41 Garfield v. RHEAULT, Walter- E: (Af 1942) Capt:. *U: S. . Ave., Toronto, Ont.. Canada^ v.`Army 0-306646,-325th Engr., C Bn:, A.P. O. 447, RITCHIE. Edmund J.' (Af 1923) 'Vice-Pres.," r .-s- c/o-'Postmaster,--^New York", ^N. -Y.,.' and 2246 - ' Sales, *Sarco Co.r Inc., 475Fifth Ave., New .York ; ... ^Orchard St.;'Racirie. Wis.- v ` ' 17 and 2 Gra< Court,' Brooklyn, N. Y. _ - VRHINE,-lGebrae.Rr-(A 1938) Cons. Mech. Engr., . RITCHIE, George W. (A 1945) General Motors' . .<-Alamq'-Natio'nal'-Bank-Bldg., and 228 Luther' r' -'Bomber-Plant, Five Points.Rd. & Riverside Dr.; >. \ ^Dr.rSan AhtoniorTexas.' ^ . ' - and *13711 Deise Ave.,.Cleveland, Ohio. - . ;r - Roll of.Membership 69 -RITTELMEYER, John M. (Af 1941) Owner, ROCHE, John M. (A 1945)' Tech. Advisor, , \ *Rittelmeyer. & Co., 816 Bona'Allen Bldg., ' Sarco Co.. Inc., 53 W. Jackson Blvd., Chicago 4, 1 -Atlanta 3, and 2332 Woodward Way. N.W; and 7743 Glenlake Ave., Chicago 3l, IU. - * Atlantal Ga. ' ' - ROCK, George A. (Af 1937) Plbg. & Htg. Section, . RITTENHOUSE, Owen R. (J 1943; S 1941) Public Works Dept., Marine Corps Air Station; - Tool Engr'., Saginaw Steering Gear, Div. of Cherry Point, and *1504 McArthur. Ave.; New. - - General Motors,- Holmes St.,-arid Y. M. C. A.,- Bern, N.`C. - . Saginaw, Mich. .` - RITTER, Arthur (Af 1911) Mgr., N. Y. Office. American Blower Corp., .50 West 40th St,, . New York 18," and Chateau Champlain, 3N. Scarsdale, N. Y. RITTER, Irving S. (Af 1944) Design Engr., B. _F. Sturtevant Co., Inc., Div. of Westinghouse Electric'Corp., Hyde Park, Boston 36, Mass., and . 130 Farley Ave., Fanwood, N. J. v . RIVARD, M. M. (Af 1935) .Mgr., Rivard Sales Co., 208 Alameda Rd., and *1805 West 49th " Terrace,-Kansas City 2, Mo. . ROCKWELL, Theo. F. (Af 1933; / 1932) Cons. . Engr., *G!enover PL, Pittsburgh.15, Pa. - . RODEE, E. J. (Af 1936) Comdr., U. S.. N. R., U. S. S. Lexington, c/o F. P. O., San FrandscoT Calif., and 130 Bellevue Ave., West Haven, Conn. RODEFFER, Edgar W. (A 1941) Pvt. U. S. Army, Rodeffer & Cowan .Air Conditioning.& Refrigerat- -- ing, 533 N. Naomi, Burbank, and 1037 N.-Lake, Pasadena 6, Calif. - - -- - RODENHEISER; George B. (Af 1933) Asst. Dir/; David Ranken Jr., School of Mech. Trades, ..ROACH,; E. R. (A. 1941) *BaskerviU Sc Son, 4431 Finney Ave,', St. Louis 13, and 3639A Dover . - - Central National Bank Bldg., Richmond 19, Va. - PL, SL Louis 16, Mo. ' ' -- ROBB, Joseph E. (A 1936) Sales Engr., Minne- RODGERS, Frederick A. (A 1934) Owner, apolis-Honeywell Regulator Co., 2753 Fourth Ave. Rodgers Engineering - Co., 209 Thorrias Bldg., S., Minneapolis, Minn., and *1601 Kentucky St.',- and *3913 Amherst, Dallas, Texas. - . - Lawrence. Kans. - ^ROBERTS, Edward F,, Jr, (A 1942) Partner- ^Gen. Mgr., Edward F. Roberts Co., 2622 Colum bia Ave., Philadelphia 21, and 435 Righters Mill Rd., Penn Valley, Pa.- ROBERTS, Eric (A 1945) Sales Repr. & Mfrs. R.epr,, McDonald & Miller arid- H. A; Thrush - - & .Co., 417 Market St., San Francisco, and 2741 - Darnby Dr., Oakland, Calif. ROBERTS, Hamy H. (A 1944; J 1941) Dist. Repr., H,. Hi Robertson Co., P. O.. Box 7185, RODGERS, Joseph S. (A 1937; / 1934) Assoc; Mech. Engr., Naval Academy, U. S. N., Annapolis, . and 16 Fourth Ave. S., Glen Burnie, Md. - ; - -. . RODKIN, David B. (A 1944) Ensign, Air Cond.' ` Sect.. Bureau of Ships, Navy Dept., Code 633, Washington, D. C., and 1547 East 67th Pl., Chicago, 111. - RODRIGUEZ, Mario F. (A 1944) Mgr.;VCale- facdon Central S. .A., Paseo del la Reforma 208, ' and Agustin Ahiimada 115, Mexico, D. F. ' . .. Dallas. - arid 2916 Amherst St., Dallas 5, Texas. RODWELL, Robert D. (A. 1944) Mech;. Engr.,: ' ROBERTS, Henry L. (Af 1916) Htg. Engr. & c/o Downey Heating Co., 1712 W. St. .Paul Contractor. *228 North 16th St., Philadelphia 2: Ave., Milwaukee 1, and 1305 South 29th St;,.. - and 1014 Allston Rd., Brookline, Del. Co., (Upper - Milwaukee4; Wis. ' - . ' Darby P. O.), Pa. . ROEBUCK, William, Jr. (Af 1917) Owner. *220 " ROBERTS, Henry P. (A 1936) Roberts Hamil Delaware Ave., Buffalo 2, and 1240 Delaware Ave.-,' ton Co.,- 713 S. Third St., Minneapolis 15, and Buffalo. N. Y; - _ 1901 James Ave. S., Minneapolis 5, Minn. ROEDER, Winfield (Af 1941) Branch' Mgr., ^ ROBERTSON, Archie M. (Af 1944) Chief Engr., - American Blower Corp., 405 Temple SL, and' Stewart A.-Jellett Co.. 1200 Locust St., Phila 484 Whitney Ave., New Haven, Conn. ; delphia 7. and 7314 Bryan St., Philadelphia 19. Pa. ROEPKE, George E. (A 1944) Mgr.. Gear Prod ROBERTSON, J. A. M. (A .1936) Vice-Pres., ucts Co., Lambert Field 21, SL Louis, and *9 W. * The James Robertson Co.,-Ltd., 946 William Geyer Lane, R. R. 5, Kirkwood 22, Mo. `. . SL, Montreal, and 109 Suntiyside Ave., West- mount, Que., Canada. '- . - ROGERS, Charles S. (A 1940) Lt., U. S. N. Ri, . Inspector of Naval Material, 275 Colman Bldg.. - - ~ ROBERTSON, John D. W. (A 1943) Engr. & * Seattle 4. and *8045 11th Ave. N.E., Seattle 5,- Field Supvsr., Consolidated Conditioning-Corp., Wash. - ' 456,S. Tenth Ave., Mt. Vernon, and *660 East 242nd St.; New York 66, N. Y. ROLAND, John (Af 1944) Chief Engr., Stokol Stoker Co.. Inc., 1145 East 22nd SL, Indianapolis . ' ROBINSON, Arthur S. (Af 1936) Engr.; E. I. 7, and *2412 East 16th St., Indianapolis.. Ind. ; " r duPont'de Nemours Co., Wilmington, Del., and - ROMER, William H. (A 1945) Htg. Engr., J..F; - ' 730 Ogden Ave., Swarthmore, Pa. . ' Higgins Heating Co., 42 Westminster St,, PtbviT - - ROBINSON. Donald M,.(A 1936) Buffalo Forge dence, and 124 Waveriy St., Providence. 7, R. I. ; - ' Co., 407 Scanlan Bldg., and 3747-University Blvd., Houston. Texas. * - ROMPEL, Walter A; (A 1944) Refrigeration' Engrg., *P. O. Box 544, New: Braunfels, Texas. ' ROBINSON, Edgar R. (A 1938) Sr. Draftsman, . Vent. & .Htg;,'"New York Shipbuilding Corp., - Camden, and *216 Carlton Ave., Westmont, N. J. ROOT, Edwin . B. (Af 1936) - Engr.. Superior . Safety Furnace Pipe Co., 5816-44 Forsythe Ave.; - . DetroiL and *964 Pierce St.; Birmingham, Mich.::*, ROBINSON, George L. (A 1935) Designer, . . ROPER, Richard F.' (A 1940) Pres., Pleasant- ^ >' - E.-1. duPont de Nemours Co., and 14 West 35th SU Wilmington 204'. Del. . - aire Corporation of America, Tower Bldg.,.Wash-.: ington 5, D: C.- : ROBINSON. Jack A. (A 1940;/ 1936) Dir., *The Radiator Co.. Pty.; Ltd., Box 4643 G. P. O., * Sydney, arid 76 Springdale Rd., Killara, N. S. W., , -.Australia. ' . ' . ROSE, Harold J. (Af 1938) Vice-Pres. & Dir.'of " . Research. Bituminous Coal Research.-Tric., 719. '. Oliver Bldg., Pittsburgh 22, arid 219 Lytton Ave.," Pittsburgh 13, Pa. - ' *. ROBINSON, James H. (A 1945) Mgr.. B. A. . ROSE, Howard J. (Af 1934)'Pres.-Gen...-Mgr., ' . Robinson Plumbing & Htg., Ltd., 92. Blarityre - Consolidated Conditioning Corp., 460 S:: Tenth - ^ Ave., and 58 Willow Ave., Toronto, Orit., Canada. Ave., Mt. Vernon, and 100 Norman Rd.;. New ' ROBINSON^ Kenneth E. (Af 1943; / 1941V Rochelle, N. Y. '. -. ' ' . - Engr;, Michigan* Department of Health. Bureau of Industrial Hygiene, and *211 Smith Ave., - Lansing 10,-Mich. .. ROSE. Jafnes S: (A 1945) Branch ' Mgr., * Ilg Electric Ventilating Co., 55 New Montgomery SL, ., ' San Francisco 5, and 41 Ethel Ave., Mill Valley, ROBINSON, Mayes R. (Af 1944) Engr., Robinson Calif. '. ' - ' .Ventilating-'Co'., and *208 W. New Castle St.. '-Zelienople. Pa. ' ROSE, Jerome C:'(Af 1937) Htg.-Vtg. Engr., U. S. Rubber Co.,. 1230 Sixth Ave., Room iOOlrl' . . ROBISON, D. J. (A 1945) Engr. in charge of Indus. New York 20, and *8031-213 SL,-Queens-Vil- - " . - Dept.; Mountain Fuel Supply Co., 36 S: State, lage 8, N. Y. . ' -- ; - -- . Salt Lake City 10, and' 1631 Browning, Salt ROSEBROUGH, J.. Stoddard (Af 1943; A 1937) -- . - Lake City 5, Utah. . - - . . .Sales Engr., L. J. Mueller-Furnace' Co..* 457 N. 7 ROBSON. Paul D. (Af 1945) Pres.-Cons. Er.gr., Kingshtghway Blvd.. Room 105, SL Louis 8, and . .v--Robson & Woese, Inc., 1001 Burnet. Ave.,-Syra- - *218 Parkhurst Terrace, Webster Groves 19;-Mo.' " cuse 3, and- 414.!Bradley St.,- Syracuse ,4. N. Y. ROSEBROUGH, Robert McC/(Af 1920) Branch ' ROCHE, Austin O., .Jr. (Af 1943) Production Mgr.,-*L: J. Mueller Furnace'Co.,'457 N.^Kings- ,' - Erigr.,-Hoffman Specialty Co., 1001 York St.,_and highway Blvd.: Room. 105.,-St:-Louis 8,' arid 34. ; \ *3950 Broadway, Indianapolis 5; Ind,. ' ~ . Hardith Hill Court, RockhiU,'St. Louis 19. Mo.: . - ' c- v7- 70 ` , J .-" -Z Heating Ventilating Air. - Conditioning - Guide 1946 ; ROSEBY, Thomas A.' (Af 1939) Asst. Gen. Mgr, ROY, Ernest W. (Af 1945) Pres., Roy Equipment Carrier ."Air' Conditioning. Ltd., Yorkshire- Col, Inc.. 311 W. Church Ave., and 4638: Cham- House.T4 Spring St.. Box'151 D, G. P.'O, and 4' ''Femhurst' Ave,- Cremome, N.-S. W., Sydney, - -'Australia.- - " '- , - - ROSELL, Axel F..(Af 1935) Civil Engr,, *A. B. ' bliss Ave., Knoxville, Tenn. ' ' - -, - ' ROY, Leo (A 1937) Asst.;:Supt., Power-Div.. Quebec Power Co., 229 St. Joseph St,,* and 41' Laurentides, Quebec, P. Q.. Canada.. "Svenska Flaktfabriken. 'Kungssgatan 18, ' and ROY, Raul (A 1945) Sales Engr., Sarco Canada, Kammalcaregatan 25, Stockholm, Sweden. . Ltd... 85 -Richmond W.,,-Room 326,- and 1105 .... ROSEN, Edmond J. (A 1939) Tech. Engr., Mer- Merrell E.. Toronto. Ont.. Canada. . - HU N. Musgrave & Co., 2019 Third Ave., Seattle 1, ' ROYCE, Robert F. (5 1945) Student, Univerrity ?nH 10238-18th Ave. S.W.,. Seattle 66, Wash. of Michigan, .and 328 El Ann St.; Ann.Arbor. , ROSENBERG. Philip (A 1928) Vice-Pres. & Mich. .' . , , . Treas., Universal Fixture Corp.,. 135 West 23rd RUBEL. Harry L.-(A 1943) Owner, Rubel &- . St., : and *240 West 98th St., Apt. 12-H, New Jenserr Co., 587 Central Ave.,'Newark,, and 33 . ? York 25, N!-Y.' -. ROSENBLATT, Arthur M. (Af 1938) Pres.. S. Munn Ave., East Orange, N. J. --` . RUBIN. Louis (A 1944) Co-Owner, Hudson - . -Rosenblatt & Hunt, Inc, 923 Virginia 'St. E., - Heating Co., 8725 Puritan Ave., Detroit 19, and ' - p. O. Box 33, and 1250 Edgewood Dr., Charleston. ' 2917 Leslie. Detroit 6, Mich. * - - W. Va. " - - \ - - RUCHTE, Carl O. (A .1943) Gen. Mgr.. Home' ROSER, Edward, III (A.1944;J 1943) U. S. Navy. ' Insulation Co.. 910 S. Saddle Creek Rd.,- Omaha 6, ! and *318 North 20th St., Leavenworth, Kans. ' and 5035 Bedford Ave/ Omaha4. Nebr.* / ROSS,.David'S. (/ 1943; S 1941) 1st Lt.. Air - RUDD, Dann J: (Af 1937) Asst. Mech. Engr.. ' Corps.- Chief, Plant & Equip. Branch, Methods ' New York City Board of Education, 49 Flatbush ' '& Proixdure Section, Maintenance Div. O. A. T. Ave. Ext.; Brooklyn, and *580 Deer Park Ave.. ' S.'C/ Ogden Air Depot, OgdehvUtah. Babylon, L. I., N. Y. - '. - ROSS, Earl F. (Af 1944) Mech. _ Engr,. W. C. RUDOLPH, R; R: (Af 1943) Cons. Engr., *72jL . - / Kruger, Architect & Assocs/ 'and' 1201 Escalante Central Bldg.,'Assoc., General Engineering CoTM- '-`".St/ Santa Fe! N. M. - ''' . 725 Central Bldg., Seattle 4, and 6712-18th Ave.. ROSS, J. D. (A 1937) Railway & Engineering S.W., Seattle 6. Wash. ', . Specialties, Ltd,.417 St. Peter St., and 88 Perdval RUEMMELE, Albert M. (A 1943; J 1938) 1st Lt/ --'/Ave.-, Montreal West, Que., Canada. ' - . "-Ord. Dept..,Hqs. P. R. Dept., O of Asst. C of S, ROSS, John O.* (if 1920) Pres. & Exec/ Ross ! G-4, San Juan. Puerto Rico, and Ashley^ N.- D. * ` ' Industries-Corp.. 350 Madison Ave.', New York' RUFF, Adolph Gi (Af 1935) Supt. of.Power. JU. S.. .'.'17/and 3 East 69th St., New.York 21. N. Y. . ' . -Playing Card Co., Park^ve., Norwood, and 3824 ' ROSS,. Kenneth A. (A 1944) .Operating Engr., Woodford Rd/ Cincinnati, Ohio. ` ' Z .Vancouver School Board, 590 Hamilton St., and RUFF, Alonzo W. (Af 1944) Vice-Pres., ,York- ! ' ' 3204 Wet 13th, Vancouver! B. C., Canada.. Shipley.'-Inc., Jessop PI: & P. R." R., 'and 538 '"ROSS, Morwick (A 1946; J 1945) Lt.. U. S. N. R.. W. Springettsbury Ave., York. Pa. . . . ' ' _. Bureauof Medicine & Surgery, Div. of Preven- /RUFF, DeWltt C.,(Af 1922) Treas., Healy-Ruff - .live Medicine, Navy Dept..-Washington., D. C., Co.,'2255 University Ave., St..Paul-4, and-2211' ' ; . and *.1641- Mt. Eagle PI.,- Parkfairfax. Alex St. Clair Ave., St. Paul-5, Minn. ' ' . v^Qdria Va. * ' . RUGART, Karl (A 1924) Mfrs. Repr.. *26 South ROSSrOtto C. (if. 1944) Dist. Mgr., American 20th St.. Philadelphia 3, and-612 Bryn Mawr / - Air Filter Co., and-Prop., Ross Power Equipment Ave., Penn Valley; Narberth-P. O., Pa. ' . ' Co... 31 E.' Georgia St., Indianapolis 4, and 615/ RUGGLES, Robert F. (Af 1936) 15 Gregg PI.. " . , ..'East. 44th.St, Indianapolis 5, Ind. * * ' Randall Manor, Staten Island 1.-N-. Y. ' - ;ROSS, Roderick (Af 1937) Principal. Roderick RUMBOLD, Allan H. (Af 1941) Pres.. Rumbold , Ross &'Traill. 4 St. James' Bldg.. '123 William St, - & Co.. Inc.. Rear 429 Peachtree St., Atlanta,-and /'Melbourne,* Cl, and 5 Bums SC,-Elwood. Mel- Norcross. Ga.- . ' - `" V ` '- bourne S.3, Australia.' . ' . RUM MEL, Adolph J.* (Af - 1937) Partner, . -.ROSS, Sidney S. (A .1945) Air Cond. Engr.. . Langhammer-Rummel Co., 436 Main AVe.,-and ' Dwight D. Kimball, 1728 Grand Central Terminal . 235 North Dr..-San Antonio, Texas. . ' . ^ "' Bldg., New:York 17. arid *923 Walton Ave., New RUM SEY, -John L. (Af 1941) Chief/ Engr.. . York 52. N. Y; ' ' ' . " Macnsons, 151-Tehama St.. San Francisco 6.' ' ROSSITER;"T. J.-(A 1939) Major. Air-Corp. i and Box 1025, Belvedere, Marin Co., Calif.'.-- . ' ' '(0318742). Officers Mail Section. 'Lowry Field. Denver, and *.1546 Hudson St., Denver 7. Colo.- ' ROTH, Charles F. (A 1930) Pres, International Exposition Co., Grand Central Palace,- 480. Lex- Z-ingtonAve, New York 17. and 141 East 36th St/ !, 'New.York, N. Y. * . -. ' . ROTH,-Harold R. (Af 1935) (Council. 1945) Dist. RUNGE, Edwin A. (A7 1944) Chief Engr.. Lee..'; - Engineering Co., Union -National Bank' Bldg/ Youngstown, and *429 Maplewood Ave.; Struth-", era. Ohio. ' -'/"s * -- RUNGE, Nathan P. (Af 1945). Sales Engr., * Garden City Fan Co.. 332 S. Michigan Ave/ - -Mgr., Canadian"Sirocco Co., Ltd., 57 -Bloor-St. . Chicago, and 346 Greenleaf Ave., .Wilmette, III. / -W,'and-5' Castleview/Toronto. Ont... Canada. . RUNNINGS, Henry-M. '(Af- 1943) Registered '-ROTH,`Herman P. (Af 1945) Design Engr.,.Air Engr;, 4729 Vermont Ave.,* Detroit 8,/Mich.- . // Research Manufacturing Co..' 9851 - Sepulveda '.'-RUSSELL, Boyd A. (A 1941) 10210 Pierce-Dr..* < Blvd., Los Angeles'45, and 1906 Dufour Ave, Silver. Spring^ Md. . -- -. '-.Redondo'Beach. Calif. - . / RUSSELL, James RT (A. 1945) Chief Designer, " 'ROTHMAN. S. C.*(Af 1936) Capt, U. S. Army. Meadows, Chritoph & Misener; 62 Richmond St. / .-.Industrial. Hygiene Engr., 2nd:Service Com^ - W/ and *45 DeVere Gardens, Toronto! Ont... . ` -inand; 90.Church St.. Room 1313, New York. N.Y. -Canada. ' ... - - , - c . -' ROTIIROCK, Ralph K. (A 1944) Owner." *5316 RUSSELL, J. Nelson {Life Member; M 1899),. "Dryades St., New Orleans 15, La. ' - " ' -. . Dir;,/Rosser &. Russell, Ltd.,, 30 Conduit St.,^ ?: ROTTMAN; George B. (Af 1944) Engr., W. H. v ' London W.l, and Fernacres, Fulmer near Slough.. / ' Sullivan -Co,Mnc.; 313M S. Greene St., and 401 ' ' Buckinghamshire, England/; : ' ' ' ' . /*' S.' Chapman' St., Greensboro,- N. C. -. . '- ^ROTTMAYER, Samuel: I.. (A 1933; J 1928) rV-rMech. .Engr., *100 W. Monroe'St.. Chicago-3, and 8830 S.' Laflih St.VChicago, 111. Z-. ` - '' :- ROTZ; J. M. (Af 1944) Owner, . J. M. Rotz Engi-: neering Co/, 804,Merchant's Bank.' Indianapolis 4, ' . and '-R.--R. 16, Box 449,- Indianapolis .44. lad. RUSSELL, W. A. (Af *1943) Chief<'Engr: & Sales ' Mgr.,' Skinner Heating &r Ventilating Co.. Inc., 1948 N. Ninth St., St.- Louis 6.. and 7918fKiiigs-;: bury Blvd.,.Clayton 5, Mo. . ' * ,v */' N- RUSSELL; William Bl (Af*. 1944) .Vice-Pres.; . Kewanee'Boiler .Corp., 409'E. .Prospect. Ke-. - ROWE, William A.* (Af 1921) (Council. 1929-31) .* .wanee, 111. . v-1. J18.Lorigfellow' Ave.. Detroit 2, Mich. RYAN, Harold J. (Af 1940) Pres.-Treas.. Harold, "'ROWE,,Wiliiarii M; (A 1944; 7 1936) Field Engr, v. J. Ryan...Inc..,101'Park Ave.,' New York 17;-and: ,-v American Blower Corp..' 1302-Swetland Bldg.,' v461-81st'St., Brooklyn 9; N..Y.": '. . ' / v .-u>" - .^Cleveland 15, and 151 .Bradley .Ave;,.'Chagrin , RYAN, Joseph B. "(Af 1938) Engr.. U. S; Engi- Falls.-Ohio;1 - * . --- .* < .' . .neering.Co- 914.Campbell .St., and *3860 Char-^.. ROWLEY,' Frank B.*.-(Af 11918) {Presidential. . v- lotte-Ave., t^anaaia City, Mo.' W-* * '* V../ I/-. Afem5er)'(Pres,,'.1932;ji^.Vice^Pres:.. 1931; 2nd RYAN. 'WUliam F/ (Af.1940; A .1939"; J T933).: * ^Vice^Pres/ 1930;,VCoundl;. 1927-33) ProfUni- .. Chief Engr/ The-Salina Supply,: Coa .302-304. N. /.versity'of'Minnesota, and'_Excelsior, Minn. ' - .Santa-Fe/and 310.W. Republic, .Salina,; Kans.T. /' Roll of Membership . 7 % . RYBOLT, Arthur L. (A 1938) Gen. Mgr., *The . Rybolt Heater Co., Miller-St., and'1108 Center * St., Ashland, Ohio. ' -* ' - ., ' . 'RYERSON, Herbert E.'(Af 1937) Dist. Mgr.. . .Cardox Corp., .536 Miinsey Bldg.,'Washington 4, D. C., and 18 Wessex Rd., Silver Spring. Md. ` SANFORD, Harold L.' (A. 1945) Co-Partner. Sans .Co., 57-59 Winsor St.,-and 69 Townline * : Rd./ Jamestown. N. Y; - SANFORD, Sterling* (Af 1930) Htg., Vtg. & Air -. . Cond. Engr., The E)etroit Edison Co.,'-2000 Second Ave., Detroit 26, and 279 Hillcrest Rd.,' ' Grosse Pointe Farms 30, Mich. . 'l SANGER, Ernest (A 1944) Mfra. Agent. Watts . , - SAAR, Laird F. (A -1945) Owner. Saar Heating Regulator Co., and 1045 Wayburn- Ave.. * . Detroit 30. Mich. .' - & Engineering Co., 206H W. Yakima Ave., SANTTI, Karl B. (Af 1945) Mech. Engr. P-5, . Yakima, Wash. ' Ind. Design Sect., Navy. Yard, Pearl Harbor, - ' - SABIN, Edward R. (Af 1919) Pres., *E. R, Sabin ' &_ Co.; 4710 Market/ SL. Philadelphia, Pa., and / , - 205 Page Ave., Allenhurst, N. J. .' T. H., and 209 Seventh, Navy Housing. .Hono lulu, T. H. -- SAPP, Charles L. (Af 1945; A 1936) Secy.-Mgr., . - SABLE, Edward J. (Af 1939) Vice-Pres. & Treas., -. ` ' ' The T. O. Murphy Co;, 25-27 E. College St., Farquhar Furnace Co., 150 Owens Ave., and *620. /' . ^ N. Walnut St.. Wilmington, Ohio. - * - * .. ' / .- and'246-W. Lorain St.. Oberlin, Ohio.' - . SACHS, Sam {J 1940) Mech. Engr., National Advisory Committee for Aeronautics. Bldg. 1229. Langley Field, and *117 Barksdale Rd/ Hampton, . Va- : SATTERLEE, H. A. (A 1944; / 1940) Partner, The Schulte Plbg. & Htg. Co., 526 Joplin St., and 1006 N. Sergt.; Joplin, Mo. ' ` SAUNDERS, Claude V. (Af 1946) Mech. Engr.. Louis C. Kingscott & Assocs., P. O. Box 671 " - / * ' /SACK, Herman'S. (A 1944) Archt. & Engr., '' Waldorf System. Inc., 169 High St., Boston, and Kalamazoo 99, and 906 Hazard Ave.v Kalamazoo * . * 19. Mich. . _ .. ." #29 Kodaya Rd., Waban 68, Mass. SAUNDERS,. Douglas G. (A 1943) Estimator & . ` SADLER, C. Boone (Af 1928) Civil Engr., Public Supvr/*John Plaxton Co., Ltd., 244 Main St..- ` ' ` Works Office, 11th Naval Dist.. San. Diego, and and 696 Warsaw Ave., -Winnipeg, Man'., Canada. . . *4844 Del'Mar Ave., San Diego 7, Calif. . SAUNDERS, Lawrence'P. (Af 1933), (Treas:. - Z . SAENGER, Lester W. {J 1941) Asst. Plant Engr., , 1944-45; Council,'. 1941-45) Chief Engr... Research - . American Brake Shoe Co., National Bearing Div., Engrg., Harrison Radiator Div., General Motors .4930 Manchester Ave., St. Louis 10, and *21 Corp., and Tuscarora Club, Lockport, N. Y. .. - - Hillard Rd., Glendale 22, Mo. - - SAUNDERS, M. Kerby (A 1945) Pres., Kerby.'5''- ' SAGAR, Paul B. (A 1945) Field Engr., General Saunders, Inc.. 330 West 42nd St., and 1136 . . Controls Co.. 3224 Euclid Ave., Cleveland 15. " Fifth Ave., New York. N. Y. . .' ' ' r and *3957 Riveredge Rd., Cleveland 11, Ohio. SAUNDERS, S. G. (Af 1944) Chief Engr.,- - L' - SAGINOR. S. V. (Af 1939) Gen. Mgr., Davey Earleymil. Ltd., 212A, Shaftsbury Ave/ London,..-; ' * / . Compressor Co., 266 N. Water St., and *900 W. C. 2, and *113 Winkworth Rd., Banst^id: ' Bryce Rd., Kent. Ohio. ` ' Surrey, Englsmd. .- - SALE, Francis B. (A 1939) Sales Engr.. Pre- ... ferred Utilities Manufacturing Corp., I860 Broad- way. New York 23, N. Y. . .` - SAURWEIN, Geo. K. (Af 1938) Sales Engr.. Lombard Governor Corp., Ashland, and 639 Boston Post Rd., Weston 93, Mass. - .. SALEVA, Gustavo (A .1945) Pres., Electrica- SAVAGE, Sidney W. (A 1944) Engr.. Gilson J ! Commercial, Inc.,' Apartado 3751, San Juan, and Manufacturing- Co., Ltd., Guelph, and *486 ' Calle Taft 55, Santurce, Puerto Rico. - . . Clendenan Ave.. Toronto, Ont., Canada. . " - '- SALINGER, Robert J. (Af 1945) Mech. Engr.. SAVOIE, J. L. Roland (A 1944) Codere. Ltd, *_ . Reg.. F. Taylor. 910 Bankers Mortage Bldg., 18 Wellington N., and 22-B Aberdeen, Sherbrooke, ' ~ ?' Houston 2, and *2335 Swift!* Houston 5, Texas. Que.i Canada. . . SALTER, Stanton W. (Af 1942) Sales Engr., SAWDON, Will M.* {Life Member; Af 1920) Prof. , _ Engineering Equipment Co'., Ltd., New Birk's! Emeritus of Experimental Engrg, Cornell Uni-.. - . Bldg.,'*Rm. ,910, Montreal, and * 153' Hillcrest . vereity. College of Engrg, and 1018 E. State - - 'Ave., Montreal W;, Que., Canada. . - ' St, Ithaca. N. Y. . ./ : SALZER, Alfred R., Jr. (/'1940) Cons. Mech. l' Engr.-, *804. Queen & Crescent Bldg., New * . Orleans 12, and 1923 N. Claiborne Ave.,.New Z Orleans, La. . '. . ' , '. SAMPSON, .Will D. (Af 1945) Mgr., Southwestern t. j '' Dist.,-"Air Conditioning 4>iv... Westinghouse > ' - Electric Corp., 405 Griffin St., and 4352 Mocking . . .' Bird Pkwy/ Dallas 5, Texas.- ' \ ' /' /: SAMUELS, Sidney (Af 1941; A 1928; J 1925) /'? . -. - Pres., Sidney Samuels; Inc., 165 Amsterdan Ave., .* f- ,/ New York 23,-and245 West,-107th St., New - York 25/ N: Y.` . ' . Z ,'* - a ' - / *SANBERN,,E. N.* (Af 1923) Ask'Secy/& Mgr;, Jobbed Products Div/ Hoffman Specialty Co., SAWHILL, R.. V. (A. 1929) Domestic Engi-. , neering Co, 110 East 42nd St,' New York 17; and ' < 115 Townsend Ave, Pelham Manor,'N. Y. _ . " SAWYER; Howard C. (A 1942) .Owner, Sawyer ' . : Heating Co, -5736-12th St,' Detroit" 8; and' . ` ' 14217 Mettetal, Detroit 27, Mich. . SAXON, R. B. (Af 1941) Asst. Operating Supt/,. ^University of Nebraska, College'of Medicine, . , 42nd and Dewey Ave, and *4215 Pine St, -- . Omaha,-Nebr. .- . - . SAYLER, William H. (Af 1944):Partner & Engr, v Specialty Sales Co, 208 S.W;-Temple, Salt Lake City 1, and .6400-South 900 ;E;, 'Salt' Lake : ' - City 7. Utah. -. *^ ;>..- " *-\ = ` 1 . Inc./ 1001-York St.,-Indianapolis 7, and 4025 Xi . Pairk Ave/-Indianapolis 5, Ind. : ` ' ; SCANDRETT, Harold R. (Af 1941) Estimator,- / Pacific Gas & Electric Co, 445 Sutter St;. San -. "SANDERr Andy J. (Af 1941) Chief Engr., A. ' Francisco 6, and 458-17th Ave/ San. Francisco . * * * - Epstein,-2001 "W. Pershing Rd:. .Chicago, and 21. Calif._ . . .. . w - / #7401 S. Kingston. Chicago'49, III.- . . ' SCHAAD, Fred N. (Af 1944) Dist. Repr,' Warren - "' . . ' - SANDERS, Charles M,, Jr. (A 1946; -J 1938) Webster &' Co, Westport Bank Bldg, .Westport. ^Capt.,_*Marfa. Army Air Field,-Marfa, Texas. " and-Broadway, and 408 West' 61st SC. Kansas ! ' ' . SANDERS, George O. (A 1945) Detroit-Branch ' . City 2,` Mo.-' ' ` . -: '. `7'' ^ - / "-/' Mgr., Penn Electric'Switch. Co.,'7 E. Grand SCHAARSCHMIDT, Karl F. (A, 1945) Htg. , - , ,, Ave.; Highland Park 3; and-19484 Prest Ave.. Contr/*T-he Bums.Heating Co, 1042 Holden - , v / .Detroit 19, Mich. , : ^ .. . Ave, Detroit 2; .and 5121-W.-'Chicago' Blvd.!- Z ` -* ' - '. SANDERS, Vic. (A* 1945) Sales Engr., Pittsburgh Detroit 4, Mich. ' . / ' _ * . . -.-,/ ' ; Corning Corp.,.632 Duquesne Way, Pittsburgh 22, SCHAD, Clifford A. (A 1938;. >;'l937)V-Engr, * f`- and 348 Sunset Dr., Mt. Lebanon, Pa/ ' . - United States Air Conditioning Corp, 2101 N.E: ` -' /j / .vA v . * SANDERS,' William L. (A 1945) Partner, Mid- '* Kennedy Sc, and 4425-43rd Ave. S, Mirnie- ..'Z'*7-' ?. - "west' Plumbing & Heating Co., 6243 Prospect., apqlis, Minn. v '. r v .- /. ' .- '7 . . . Kansas City, and 103rd Blueridge/R. R. 1, Hick- SCHAEFER, Armand (A 1945) DisC'Mgr, Iron mail Mills, Mor . ... . . ' Fireman Manufacturing Co, 429 S. Ashland Ave, vfT /SANDFORT, John F. .(Af 1942; > 1938) Asst. and 1429-Farragut, Chicago,IIL *>* *< v" ' /--/ Z): . ''' ' Prof-- Mech. Engrg. Dept., Iowa State College, SCHAFER, Harry C. (Af 1937) Sales' Mgr, / H '' Ames, and 728 N. High St., Covington,.Ohio. _ Iroquois.Gas Corp-.' 45 Church St,-Buffalo, and-VZ^ ----- ,\ / -! SANFORD, A; L'. (Af 1915) ,Mech: Engr., C. H. .*197 Union St, Hamburg, N. Y./- -T"-> ' ^ -/ v *-- - Johnston, Archts.'& .Engre., 715 Empire Bank SCHAMPEL, Howard B. (A 1943),'Design'Engr./ - Z J'-- 'r\--.-Bldg/ .St./Paul -1,' and'*'1037- Davern St., St. ' Minnesota Mining & Mfg. Co, 900.,Fauquier ''///';&> ' '* -,r;/PauI'5..Miiin. ~ -/ /-v Ave, and *2122 Knapp St,`SC Paul 8,/Minn;!" ' 'X 711 72 .Heating' Ventilating /4ii; Conditioning- Guide. 1946 ` "SCHARMER, George A. (A 1945) Special Supvsr., SCHREIBER, Herbert W,, (A 1937) Branch Mgr. .. - . " U. S. .Navy Yard; New York, Bayonne Aw*6* Johnson Service Co., 507 - E. - Michigan St., . X-17, Bayonne, and *175 Main St., New Mil- Milwaukee 2, and 6187 Washington.Circle, MU-- ford,.N, J. *. ` . waukee 13, Wis. ' * - SCHAUER,Robert A. (A 1944; 7 1942) Air Con- SCHREIBER. W. F. (Af 1945) Owner, #Schreiber ' ditioning Engr., J. C. Penney Corp.,. Construc- Inst, of Refrig., 902 Westport Rd., Kansas City 2, - - tion'Dept., 330 West 34th St., New York, N. Y,, Mo., and 6200 Terry Dale Rd., Merriam, Kans. ' . and 2815 Indiana Way N.E., Canton, Ohio. ' SCHROEDER, Delman E. (A 1943) Surveyor to 4 . SGHECHTER. Jack E. (A 1941; 7 1937) Air Cond. The American Bureau of Shipping,. Rockefeller ' . .Engr., James. H. Martin Co., 503 West 43rd St., Bldg., Cleveland 13, and *1531 Duglas St., ..- - - New York 18, and *733 Howard Ave., Brooklyn ' n : 12. N. Y. . ' SCHEIDECKER; Daniel B. (A 1919) Pres.. Ames. Iowa. ' SCHROEDER, William R. (A 1939) Pvt., 345th Infantry, Camp McKain, Miss., and 201 Kedzie ' Hunter-Claxk Ventilating System Co., 2800 ' * ' ; Cottage Grove Ave., Chicago 16, and 4626 N. " .; Kilbourn Ave., Chicago 30, III. - " . SCHERER,-Leo J. (A 1945) Gen. Mgr., Frank . _ - . " - Scherer & Son, 1261 Curtis St., and*964 S. : , Columbine St., Denver, Colo. . ' . SCHERGER, Fred J. (A 1942) Sales Engr.. . ../'' Mundet Cork Corp.. 335 W. Jefferson Ave., ' Detroit 26, and 3754 Kipling, Berkley, Mich. ~ SCHERNBECK, Fred H. (A 1930) Salesman, : . . -..William Bros. Boiler & Mfg. Co., 1057-10th *. -Ave. S.E., and -5045 Portland Ave., Minnea- i.--- .' ", apoiis,-Minn. ' - .. SCHICK, Karl W. (A 1946) Sales Mgr., Railway ' . .' ' Controls: Div.,'Minneapolis-Honeywell - Regulator Co., 433 E. Erie,' Chicago 11, and 5739 N. * . - Francisco, Chicago 45, 111. : SCHIWETZ, D. P. (Af 1945) Braqph Mgr., York W., Evanston, III. -. '' SCHROTH, August H. (Life Member; Af 1911) N. Y. Mgr., Columbia Radiator Co.,.and 167 N. ` Grove St.. East Orange. N. J. . *' '. SCHUBERT, Arno G. (Af 1939) Asst. PrpL.Mech. Engrg., Rensselaer Polytechmc Institute, Troy, - and 1301 Broadway, Watervliet. N. Y. . SCHUETZ, Clyde C. (A 1936) Research Engr;, United States Gypsum Co.,.1253 Diversey.Pkwy., - Chicago, and #206 S.. Edward St.,'Mt. Pros pect, III. ', SCHULEIN, Lars E.-(A 1942) Sales Repr., 43l . S. Dearborn St., Chicago 5, and-617 South-23rd Ave., Bellwood. 111. - '- ` SCHULMEISTER, Walter A. (Af 1944) Sales Mgr., American District Steam Co., North Toriawanda, and R. D. 1, Niagara Falls; N. Y. SCHULTZ, Albert W. (Af 1936) Grinriell Co lne., 240 Seventh Ave. S.. Minneapolis 15, .and Corp.,' Box 1007, Charlotte 1, and 825 Romany ' *5204 France Ave. S.. Minneapolis 10,' Minn. Rd.. Charlotte 3, N. C. . SCHULTZ, Stewart F. (A 1943) Engr., .Htg. . . : . . SCHLENK, Hugo, Jr. (Af 1945) Engr., North- Vtg., Works Fisher Body Div., General' Motors . : f' west Paper Co., and 214 Chestnut St., Cloquet. Corp., Engr. Dept.,.11-135 G.-M. Bldg., Detroit,. ... . . - Minn. ` and 16250 Cheyenne. Detroit 27, Mich. ~ SCHLICHTTNG, Walter G. (Af 1932) Mgr.. Air SCHULZ, Walter - Frederick (Af 1944) ' Sr. ' Conditioning Dept.,' Clarage Fan Co., 619 Porter Partner, Schulz & Norton,--870 Shrine Bldg-, '. St., Kalamazoo 16, and*224 S. Fletcher Ave.. and 1839 Overton Park Ave., Memphis^ Term. ` Kalamazoo 51, Mich. - SCHULZE, Ben H. (Af 1921) Eastern & Govt. \ SCHLICK, Paul F. (A 1940) Col., C. A. C., U. S. Sales Mgr., Kewanee Boiler Corp.,-40 West 40th - Army, Camp.Haan, 216th Coast Artillery, San St., New York, N. Y- and Four Brooks Farm, . .. _ . _ Francisco, Calif;, and 1410 -Edgcumbe Rd., Pipersville, Pa. - ` -- - `_St: Paul,.Minn. -` . ' SCHUMACHER, 'Clarence W. (Af 1943)'Mech:! - SCHMIDT. Alexander F. (Af 1943) Designer, Air Engr., .General Heating & Cooling Col, 1407 > . Corid., Engineering Dept., Ansco, Charles St., Grand Ave., Kansas City, Mo. -c ~ . - and 174'Crary Ave.,.-Binghamton, N. Y. SCHUMACHER, John F. (A' 1944). Draftsman, . .. -.SCHMIDT, Carl W. (Af 1944) Registered Engr.. Columbus Heating & Ventilating. Co.,. R. 3, .r Washington Lane, R. D. 1, Ambler; Pa.` Sta. G, and 3290 Groveport Pike,-.Columbus. - V' - ; . SCHMIDT, Harry (Af 1937) Project Engr., .Marine' Dept.,. Carrier Corp., Chrysler Bldg., ;New York, N. Y,, and# 130 Westville Ave., ; ; Caldwell 11, N. J. -- 7, Ohio. . SCHURMAN, John A. (Af 1936; 7 1935) Sales r Engr., York Corp.. -2700- .Washington , Ave.r ' , Cleveland, and 16307- Lakewood Heights Blvd., ' ' SCHMITT, - William. C. (7 1945 : 5 1944) Cpl.. ..r' .r.r U. S. Army, Mech..Engr.. Flesch & Schmitt, Inc., .' - ; *118-Brown St., Rochester, and #690 Beach Ave., ' Lakewood 7, Ohio. ` ' . .- . SCHUSTER. Paul H. (A 1942). Mech. Engr.,.-. Headquarters, 8th Service . Command. ' Dallas,' ' ^-Rochester 12, N. Y. Texas, and *110 N. 20th St,, Fort Smith, Ark. ' ' v ., SCHNEEBERG, Floyd H. (7 1943) Instructor. SCHWARTZ, Fred D. (A 1945) Cons. Engr., ' ^ `Duhwoody Industrial institute, 816 Wayzata. Lloyd & Schwartz: 124 -W;-Fourth St., Los- Blvdr, Minneapolis, and 1444 Edgerton, St. Angeles 13; and 1053 Crenshaw.-Los Angeles, Calif,'. Phurii-Minn.--- . - SCHWARTZ, Jacob (A 1936; 7.1929) Contractor.- - : '* ^.'SCHNEIDER,- Charles H. (A 1946; .7 1938) ' - Samuel Schwartz & Son: Inc;, 30 West 27th St., . - .Branch'Mgr.; *llg Electric Ventilating Co., 706 Bayonne; and 12 Van Houten Ave.,. Jersey City, . j "'.*; 'Professional Bldg., .Pittsburgh 22, and 1413 Park N.J. ./ -- - -'X-. Blvd.,"Dormont, Pittsburgh 16, Pa. ' - . - SCHWARTZ, Maurice (A 1938). Supvr., Queens- >" > SCHNEIDER; EmUe W. (A 1944).Owner. Air borough Gas & Electric Co.. Far Rockaway, and'.'- --- - ' -' -flow Heating & Ventilating Co., 1629 Clio St., 780 Caffrey Ave., Far Rockaway, N.-Y; " . - -- New.Orleans 13, La. .' ' . SCHWITZER, Louis, Jr.. (Af 1945) Exec. Vice- - ' -\SCHNELL, Robert H. (A 1938) Mech. Draftsman, Pres.; Scliwitzer-Cummiris Co., 1125 .Massa- , -r B.'E. Landes, Cons. Engr., 722 Old Colony.Bldg., chusetts Ave., Indianapolis 7, and 6449 -North' - 5.=-, - '" Des-Moinesr and 1617-33rd St., Des Moines ' Chester; Indianapolis 44, Ind. ' ' ' . . . . T If, Iowa. ' SCOFIELD, Paul C. (A 1937; 7 1933) Sr.'Design -- _ . SCHOEN, Daniel D. (7 1942) Mech. Engr.. - Engr., Lockheed Aircraft Corp., Burbank, and - /-.''.Triangle 'Sheet Metal Works, 17 Meadow St.. . 425 E. Randolph, Glendale 7, Calif. .'. - - - . .Brooklyn,' and *272 S. Broadway, Yonkers SCOTT, Clarence' E; (Af 1943) Mgr., industrial " .5,.N. Y.`- . - Htg. Refrigerating Div.; Fedders Manufacturing - - ..' SCHOENIJAHN, Robert P. (Af 1919) Owner, Co., Inc., 57 Tonawanda St., and'800^W. Ferry' . . ' *305 Industrial Trust Bldg., Wilmington 7, and ' St., Buffalo. N. Y. ' r ' - : ' - - : u ,719 Nottingham Rd., Wilmington 56, Del. SCOTT, Donald C. (A 1943) Mech. Engr...Asst/' . SCHOEPFLIN, P. H. (M 1920)' Pres.,' Niagara ` Mgr.,-Ware Coupling & Nipple Co., .Ware, andJ ^ ' Blower ..Co., 6 East 45th.St., New York, arid 9 Main St., Wilbraham, Mass.' . r Broadmoor Rd., Scarsdale, N. Y. - SCOTT, Edwin E. (A 1943) .MfgB. Agent, Htg.' . " SCHOERNER; Rudolph T. (Af 1943) Chief Engr.. Power Plant -Equip..,Johnson & Scott,'/ 918 " ; Taco Heaters,'Inc.-, l23 South St., Providence, - Dermon Bldg.. Memphis 3, and 11 S. Auburndale, ' ^ - . and`48 Fairway Dr., Oakiawn, R. I. . Mempiiis, Tenn.' ' ^ SCHOTT/- Frederick C.: (A 1945) Co-Owner,' ^ SCOTT, F. William. (S 1943); Mech.:-Engr.;-- _ / v>'Atlas-Butler-Furnaces,! Inc.| 243 N. Fifth St., Weapons Div.;- Naval Ordnance.. Laboratory,, \ - Columbus-15,-arid"160'W. Royal Forest Blvd., - Navy Yard, Washington 25: arid 3019 K St. S.E.:'-1 ^r-' \ Columbus'2;.Ohio. * ' - ` ' ` ' , Washington`19,-D.-C.-v ' Rdilfof Membership J- 73 SCOTT, George M. (Life Member; Af 1915) Pres., SEVERNS, William H.*. (Af 1933) Prof. Mech. .. Child & Scott-Donohue,. Inc.,' 153 -East. 38th St.,- 1- Engrg., University.of-Illinois, and 609; Indiana' - New York, and 38 Stratford Rd.,- Scarsdale, N.Y.. ~ Ave., Orbana, III.- ' ' .' - .' SCOTT,. James (Af 1943) Mgr., York Corp., ' 659 E. Sixth St., Cincinnati, arid *531 W: King St.. York. Pa. ... SEYFANG, William G. (Af 1939)'.Managing. Engr., Board, of Education, City Hall, and'116 Dorchester Rd.,' Buffalo, N. Y. - -SCOTT, Richard p. (Af 1944) Coraml. Sales Mgr,, SEYMOUR, Cyril D. (A 1945) Mgr. & Pres.. Bard. Inc., 215 N. Fourth St.. Columbus 15, Seymour Plumbing & Heating Contractors, and 740 Kelton Ave., Columbus, Ohio. - Ltd., 97 Ridley Blvd., Toronto 12, Ont., Canada. SCOTT, Roy M. (A 1941) Mfrs. Repr.. *323 SEYMOUR, James E. (A 1937) Prop., Lee & Tenth St., San Francisco 3, and 35 Fairfield Way, San Francisco 12, Calif. ' Seymour, 346 Russell St., and 208 Lakewood Blvd., Madison 4. Wis. ' SCOTT, William P., Jr. (Af 1941: 7 1939) Sr. SGAMBATI, Anthony P. (7 1944; S 1939) Partner, Scott Co., 243 Minna St., San Francisco Ensign, U. S. Navy, and 143 W. Evergreen, -3, and 255 Santa Paula Ave., San Francisco Youngstown. Ohio . -` 16. Calif. SHAER. I. Ernest-(A 1934) Treas. & Sales Mgr., SCOTT, Wirt S. (Af-1943) Engr., Philadelphia- Shaer & Turner Engineering Co., 88 Broad-SL.- - Electric Co., 1000 Chestnut St.. Philadelphia, and Boston, and 154 Seaver St.. Roxbury, Mass. - 4619 Chester Ave., Philadelphia 43, Pa. SHAFER, W. P., Jr. (A 1944 ; 7 1941; 5 1939) SEABRIGHT, Frederick C. (A 1944) Engr., Engr., Shafer Plumbing & Electric Co., 414 N. Columbus Heating & Ventilating Co., Columbus, St. Mary's St;, and 107 Westover' Rd., San :and 455 W. Sixth Ave., Columbus 1, Ohio. -- Antonio, Texas. - -- SEARLE, William J., Jr. (Af 1938) Engr., Mech. SHAFFER, Chester E. (Af 1937) Research Engr., Engrg. Div., Philadelphia Electric Co., 900 Koppers Co., Kearny, and 645 Belgrove Dr., Sansom St..' Philadelphia, and el20 Woodside Arlington, N. J. ' - Ave., Narbeth, Pa. SHANKLIN, Arthur P. (Af 1929) Vice-Pres., SECKINGER, Benjamin J., Jr. (Af 1941) Vice- Carrier Corp., S. Geddes St., Syracuse 1, and Pres., Seckinger Sons. Co., Inc., -180'Forsyth 203 Sedgwick Dr., Syracuse, N. Y: St. S.W., and 1110 Lanier Blvd. N.E.`, Atlanta. Ga.' SHANKLIN. John Andrew (Af 1928) Vice-Pres. SEDGWICK, Stanley W. (Af 1944) Dist. Mgr., & Treas., West Virginia Heating & Plumbing - Trane Co. of Canada, Ltd., 3019`Roxboro Glen Co.. P. O. Box 1507, Charleston 25, and '1607 Rd., Calgary, Alberta; Canada. - SEELBACH, Herman, Jr. (Af 1944; A 1937) Quarrier St., Charleston 1, W. Va. .' ' SHAPIRO, Charles A. (A 1943; 7 .1938) Li.. Dist. Mgr., Minneapolis-Honeywell Regulator S. L. C. U. 44; U. S. N. L. F. E. D., Albany 6. .Co., 45 Allen-St., Buffalo 2, and 189 Union St., Calif., and 414 S. Kelsey Ave., Evansville, Ind. ' Harriburg,-N. Y. : -- SHAPIRO, Morris (Af 1941) Sr. Mech. Engr., SEELERT, E. H. (A 1935) Secy.-Treas.. McQuay, Federal Public Housing Authority. Longfellow. Inc., 1600 Broadway N.E., and *2540 W. Lake of Bldg., and *6323 Luzon Ave. N.W., - Washing-' Isles Blvd., Minneapolis, Minn. tori. D. C. - SEELEY, Lauren E. (Af 1930), (Council. 1944-45) SHARP, Henry C. (Af 1935) Mgr., Si. Louis Office. Dean of the College of Technology, College of The Herman Nelson Corp.. 4060 W. Pine St., Technology'. University of New -Hampshire, St. Louis 8, and 1326 Waldron Ave., University1 Durham, New Hampshire. ' City 14, Mo. - . SEEPE, Paul E. (A -1944). Sales Engr., Minne- SHARP, John R. (A 1937) Lt. Col., 0-183351. " apolis-Honeyweli Regulator Co., ,4-5 -Rhodes Hq. A. S. F. T. C., S-E, Fort Leonard Wood, -Center, Atlanta* and 123 Clarion Ave.. Decatur, and 906 E. Sixth St., Rolla,.Mo. - .. Ga. - ^ SHARPE, .Vernon W. (Af' 1945) .Vice-Pres. & SEGLE, Thomas L. (A 1942) Htg. Engr., Wells Chief Engr.,.* Dynamic Air Engineering, Inc., & Wade Hardware, Inc.,' So. Wenatchee Ave., 1619 S. Alameda. Los Angeles 21.-and 107 S. Wenatchee; Wash. SEIGEL, Lawrence G.* (A 1945; 7 1943) In structor, Case School of Applied Science, 10900 Euclid Ave.: Cleveland 6, and 943 Vineshire Rd,, Cleveland 21, Ohio. -' Highland'Ave., Los Angeles 36,`Calif. ' ; SHAW, Burton E.* (A 1936; 7 1934) Cons. Engr.. Ipswich Rd., East Boxford, Maris. - - SHAW, George W. D. (Af 1944) U. S. Army SEIPPEL; John H. (Af 1944) Vice-Pres., Climax' . Industries. 1901 S. Western Ave'., Chicago 8, and - 2715 Sheridan Rd., Evanston, III. , SEITER, J.- Earl (Af 1928) Mgr., Dist. Steam Dept., Consolidated Gas Electric Light & Engrs.. 700 Union Guardian Bldg., Detroit 26, and *14541 Longacre Rd., Detroit 27, Mich. SHAW, J. A. (Af 1938) Gen. Elec.-Engr., Cana dian Pacific Railway Co.,-Windsor St., Montreal,- ' and Hudson Heights, Que., Canada. ' . Power Company of Baltimore, Rm. 500 Lexington SHAW, N. J. H. (Af 1927 ; 7 1925) Sales Engr;. ' Bldg., Baltimore 3,..and 7117 Bristol'Rd., Balti - Barnes & Jones. Inc., 128 Brookside Ave., Jamaica more'12; Md.___ . . -, ."Plain; and *100 Athelstane Rd., Newton Centre'- SEITZ; Ralph C. (Af 1945) Domes. & Comml. Gas 59, Mass. ' Htg.'Engr., Central New York'Power Corn., SHAWHAN, Samuel F. (Af 1945) Engr., * Carrier 300 Erie Blvd; W.. Syracuse, and 306 Dewittshire Corp., 300 S'. Geddes St., Syracuse 1. -and 101 - Rd. S>; Dewitt, N. Y. - Woodbine Ave., Syracuse. N; Y. %* SELDEN, Karl W., Jr. (A 1942) Dist. Mgr., " Minneapolis-Honeywell Regulator Co., 703 Builders' Bldg., Charlotte 2,.and 232 S. Terrence SHEA, Francis X. (A 1944) Eastern Mgr., Farr Co., 55 West 42nd St., New York 18, and 63-209 Alderton St., Rego Park, Queens', N. Y. /' -' - St., Charlotte 4, N. C. . - - SHEA, Mlchael'B. (Af 1930) ^American Radiator SELF, V. Floyd (Af 1941) Sales Promotion, . Anemostat Corp. of America. 10 East 39th' St., & Standard Sanitary Corp., 1426 Maccabee Bldg.',. arid 3214 Carter St.. Detroit, Mich. - ... v New York 16, and 615 Harrison Ave., Harrison; SHEAHAN, John-A. (Af 1945) Chief-Htg. Engr., N. Y. " . ', - Atlanta Gas Light Co.,.243 Peachtree St. N.E., SELIG, E. T,, Jr. (Af 1936) Dir. of Engrg... and 573 Seminole Ave. N.E., Atlanta,'Ga. ' - :. Rybolt' Heater Co., and 329 Lindale Ave., SHEARER, Arthur G.- (A 1944) Mfrs. Repr., - Ashland, Ohio. -- A. G. Shearer. 1448 Scharpe, Houston 3, Texas: SELLMAN, Nils T. (Af 1922) Vice-Pres., *West- SHEARER, William A., Jr; (7 1941;.5 -1939) ' .Chester Lighting Co.~ 9 S. First Ave., ML Vernon, -Capt-, Engr., Corp., A. S. F. T.. C. Hqtrs., Fort' - and 56 Walworth Ave., Scarsdale. N. Y. ' - . Leonard Wood, Mo., and *407 Sixth Ave., New SELTZER, Paul A. (A 1943; 7 1938) Mgr.-. Kensington, Pa. . - V . /..Builders Htg. Div., Bryant - Air Conditioning . SHEARS;: Matthew W. (Af 1922) Htg. Engr., Corp., 915 N.'- Front St., Philadelphia, arid *79' C. A. Dunham Co.', Ltd., 1523 Daveriport Rd.,- . W; Drexel Ave., Lansdowne, Pa. ' Toronto 4, and 39 Sylvan Ave., Toronto, Ont.,'- SELVING,: Holder T. (Af. 1945) - Mech, Engr., . Canada. ' . . Fislier-'Body Div., Works Engrg. Dept., 11-135 SHEEHAN, John T. (A 1945) Sales.Engr., Crane :'General Motors.Bldg., Detroit 2, and #8570 Pine O'Fallon Co.. 1631-15th St., and *4325 East 29th - hurst Ave., Detroit 4, Mich. . ' ' * - ' ` Ave., Deriver. Colo. - -- -i-:.- SEMEL; Edward (A 1943; 7 1941) T/3 33585318, SHEERE, Albert D. (A 1945) Div. Mgr./* A. M.' - S. E.. D; Barracks Areri. Oak Ridge, Tenn., and ' Byers Co., 1502 Esperson-Bldg.,- Houston 2,'arid- ' *6029 Ellsworth St., Philadelphia 43, Pa. . 2621 Sunset Blvd.; Houston 5; Texas... . V;'.v :v-;- ;.=1- 74. Heating VentilatingAir Conditioning - Guide 1946 SHEFFIELD, Raymond A. (Af. 1942) Owner. SHESLER, John A. (A 1945) Field Engr/ Hoff-' ' ' - Air Conditioning Engineering Co., 44 First St.;, ' - man Specialty Co., Inc., and 104 Brigfes Ave., Cambridge 41, and *53 Brandon'.Rd., Milton' Yonkers 2, N. Y. -. ' " 87% -Mass. .' SHIELDS, Roy W. (Af 1945) Engr., Samuel R. -* : SHEFFLER, Morris (Af 1921) Partner. Sheffler- Lewis, 100 W. Monroe St., Chicago 3, and *9115 ' Gross Co., -1000 Drexel Bldg., Philadelphia 6, and . S. Ada St., Chicago. III. . '. ' - 419 Chapel Rd.,' Melrose Park, Montgomery SHILSTON, Richard A. (Af 1943) Htg. Engrg. -Co.. Pa.' : Asst., City Architects Dept., Town Hall. Man SHELBY, A. W. (Af 1942) Secy- Shelby chester 2, and 34 Ruskin Rd- Darley Park, ' Skipwith, Inc., 678 Union Ave., Memphis, -Tenn. Manchester 16, England. .. SHELDON; Nelson E. (Af 1927) Branch Mgr., SHIPP, William H. (A 1945) Application Engr- _ Carrier Corp., 820 Reynolds _ Arcade Bldg.,, Minneapolis-Honeywell Regulator Co- 799 Beacon - . Rochester 4, and 41 Lanark Crescent, Rochester St- Boston, and 124 Lewis Rd- Belmont, Mass. ' ' - 9. N. Y. ` - .- ' SHIRE, .A. C. (Af 1942) *3215 Macomb St.. - SHELDON, Robert W. (A 1942) Hearing Engr., Washington 8. D. C. '; e'The Lake Shore Gas Co., Ashtabula, and 485 SHORT, Wm. W. (A 1942) *Wm. W. Short Co..' - . East 238th St.. Euclid. Ohio. ' 274 Madison Ave- New York 16, and 541 West _ SHELDON, William D., Jr. (A 1936; 7 .1934) 113th St- New York. N. Y. ' - Chief. Engr.. Sheldon's. Ltd., and*Cedar St., SHREEVE, L. Dale (A 1944) Gen. Purch. Agent Galt. Ont., Canada. ' . & Refrigeration -Engr., Knapp Supply Co- Ohio -SHELEY, Earle D. (Af 1937) Pres.. *Glanz & and Dudley, and *914 ,W. North, Muncie; Ind. 'Killian Co..' -1761 W. Forest Ave., Detroit 8. and SHROCK, John H. (Af 1924) Vice-Pres., New 7 . Box 243, Birmingham. Mich. ' ' - ' SHELL, Jack D. (Af 1940) Capt- 0549894, *355 York Blower Co- 171 Factory St- and *2026 . Indiana Ave- LaPorte, Ind.- - Harbor Craft Co., A. P. O. 228, c/o P. M., New SHULL, Leon F. (A 1945) Price Specialist.'Office . : / York, N. Y.; and 4823 Gaston Ave.; Dallas 4. of Price Administration, 721 Kittredge Bldg- '/ Texas. -. Denver 2, and 1065 York St- Denver 6,, Colo. SHELLDROP. Tonn F, (Af 1942) Design Engr., . SHULTZ, Earle (A 1919) .Vice-Pres- Illinois - Parsons. Brinckerhoff. Hogan & Macdonald, 142 Maintenance Co- 72 W. Adams St- Chicago 3. III. - \ Maiden Lane, New York 7, and 10 Washington SHUMAN, Laurence (Af 1939) Mech. Engr:, - ' St., Town House Apartments. Hempstead. /National Housing Agency, . 1600 I St. ' N.W., " '-.L. L, N. Y. ' 7' . Washington. D. C- and 8367-16th St- Silver ` SHELLEY, Karl B. (A 1944) Mfrs. Engrg.- Repr.. Spring, Md..` ,' Parent &' Kirkbride, Fourth St. at Locust, Phila SHUMATE, James C.^(A 1945) Branch Mgr. ; delphia 6. and-* 510 State.St., Shillington, Pa. Vice-Pres.,-*Noland Co., Inc...270 Garnett St. *' SHEPARD, Carl R. (Af 1941) Sr. Mech: Engr., . S.W., and 411 Pine Tree Dr. N.E., Atlanta, Ga. - ; . Rm.-' 838. 630 Sansome St.. Sah Francisco 11. SHUTTLEWORTH, Riley (Af 1943) Prop- and 438 Rich St.. Oakland 9, Calif. - - Shuttleworth Conditioned ' Air Co.. -117 E. SHEPARD, Edward C. (Af 1943) Mech. Engr.. Michigan St- Indianapolis 4, and 2859 N. Meri : Federal Shipbuilding & Drydock Co., 744 Broad dian St-'Indianapolis 8, Ind. - .. - St., Newark, and 14 Bodwell Terrace, Mill- SIDBURY, Roy W. (A 1944) Sales Engr- Chase >"burm N. J. '* - ' . ' ' ' .Brass & Copper Co., Inc- 236 Grand St- Water- ; SHEPARD, John deB. (Af 1937; 7 1929) Assoc... __ P; L. Davidson,.Cons. Engr., Woodside Bldg.,' 7 and P. O. Box 2235. Greenville, S. C. - /SHEPPARD. .Frank A. (Af 1918) Salesman,' . / Johnson Service Co.'. 1031 Wyandotte ' St ' * Kansas City^6, and 27 .East 70th St., Kansas 7 *City 5, - Mo. ' . __ ' . bury 91. and 79 Chapman Ave- Waterbiiry. Cohn.' SIEGEL, Daniel B. (J 1940; 5 1938) U. S. Army, and 2960 Collingwood. Detroit 6, Mich. - SIGGINS, George S. (A 1943) Owner. 737 Spring- field Ave., - Irvington, and* 78 S. Harrison St- East Orange. N. J. '' -' SIGMUND. Ralph W. (Af 1932) Dist. Mgr- B. F. Sturtevant Co., 913 Provident' Bank . .. SHEPPARD, Wallace K.- (Af 1942) Supvr. of ' Bldg:. Cincinnati 2, and 130 Wm. H. Taft Rd- ' - Htg. Sales, The Peoples Natural Gas Co., 545 - Cindnnati 19, Ohio. ' ` William' Penn Way, and 6420 Darlington Rd., SILBERSTEIN, Bernard G. (Af 1937) Dist. - . Pittsburgh, Pa. - - ' Mgr., Ilg'Electric Ventilating Co- 622 Broad ; SHEPPERD. P. D. (A 1940; 7 1938) Sales Engr., ' way. and 814 E. Mitchell Ave- Cincinnati. Ohio: . . - -'-'''.Y'Y '/Johnson Service Co.; .230. E. Alexandrine. ' SILVERA, Amerlcb (A,1943; J 1939) Application /---'Detroit- IV and 2172 Cadillac -Blvd:, Detroit Y14,'Mich. - . ' Engr., Carrier Corp- International Div- 122 East 42nd St- New York 17. and *30-41-9181,St- : SHEPSTONE, Oscar (Af -1943) *c/o E. ' M. Jackson Heights, L. I-New York.. .' Branigin, Atty., 1214 Majestic Bldg:, Detroit.26.. SIM KIN. Milton (A 1942; J 1936; 5 1933) Engr.. 0Mich. - -. ' Buensod-Stacey. Inc.. - 60 East ^42nd. SL, New.. 'jSHER,^Alvin .1. (5 1943) *3025 E. Superior St., . York, and 76-12-35th Ave- Jackson Heights; Duluth/Minri. - * . L. I- N; Y. - . " SHERBROOKE.. Walter A. (Af 1938) Partner. SIMONDS, Chauncey A. (Af 1944) Owner,.* 1855 > pipe-Specialty Engineering Co.'; .114 Liberty Union Ave. S.E.. Grand Rapids 7; Mich. . - ' . *-':St:,'- New York 6; and 92 -Twombly .Ave., Bay. SIMMONDS, Verne (Af 1943) Sales Engr.. 233 . - Terraoe. Staten Island 6; N. Y. .... . Grain Exchange Bldg- Omaha 2. and 2416 Vane ' . . SHERET, ..Andrew ' (Life \ Member; Af 1929; St- Omaha, Nebr. - - ' * . ' - ' A 1925) ' Pres.. Andrew Sheret, Ltd., -1114 SIMMONS, Noah M. (Af 1944) Htg. & Piping- BlanshardSt- and 1030 St. Charles St., Victoria, Contractor, Noah M. Simmons Co- 22 N. Ritter B.-C- Canada:'' ' ' -. ' Ave- Indianapolis' 1, and 39 N. Ritter -Ave., SHERMAN. Ralph A> (Af 1933) Supvr.. Fuels -- Indianapolis, Ind. .* -T'DivV, Battelle Memorial Institute', 505 King . SIMONS, B.C. (Af 1938) Branch Mgr-St. Louis.- /'Ave- /Columbus 1, and" 1893 Coventry-Rd., Minneapolis-Honeywell Regulator Co- 4030 >/ ` Columbus.8, Ohio.. - ' ' Chateau. St. Louis 10, and 454 W. Simon Ave-` . ' SHERMAN, Robert E. (Af. 1945) Sales Engr.. . Webster Groves, Mo. . -. -- , '--'Buffalo - Forge .-Co., .418 vRockefeller 'Bldg., SIMONS, Edward W, (Af 1938) Cons., Engr/. '. Cleveland, and 24146 Westlake Rd., Bay Village, - Edward Simons,' 525 Market St- San Francisco ' . / Ohio.. - v. i . 5, and 40 .Villa Terrace, San Frandsco'14,.Calif. ' ' A: " 1C' ^r* A VSHERMAN,. Vr L. (Af 1935) Editing & Cons..' ; SIMONSON, George M. (Af 1937) Cons. Elec.' & / v Consolidated:-Book . Publishing Go., - 153 . N. ^ Mech. Engr- *625 Market St.', Rm. 309; San . - .'Michigan /Ave.',.. Chicago ` 1;' and 643 Hillside - Frandsco 5, and- 20'Lorita Ave-'Piedmont ir.''- -l.iAvevGlen Ellyn,"111.* ' ' * Calif. " - .- , -v f SHERMAN, -Warren *P. (Af 1937) Mech. Engr.. . SIMPSON, G. (Af 1941) Vice-Pres.-Gen. Mgr..- { vV/ "/ liart-wi: fV^Refrig:;' Vent.'. Section'; U.' S. Jingmeers.- Hq,, - Pittsburgh Lectrodryer Corp., P. O. Box 1766./" 'WFourth'Service-Command, and c/o Simmons Ice Pittsburgh 30, -and '317 Pine Rd- Edgeworth. * ^ ^ Co.Y-412 Margaret St.; Jacksonville, Fla." ' ' - Sewickley P q - . - - -- --* *.-- . . .. ifpf- YSHERRERrJohri W., Jr;/(A 1945) Htg. Engr., ' SIMPSON, Harry (A 1945) Htg/'Contr.; 120 ,.T. Equitable'Gas .Go., "Duquesne Bldg-.-Cecil Way; O'Connor Dr., Toronto, Ont-'Canada. .- /Pittsburgh/- 'and #4064- `Miller- Ave., - Wilkins' .. SIMPSON, Robert L. (J 1941) Sales Engr- Crane - Township; Pittsburgh.21, Pa. - /' ' - Co., Hartford,-and R. F. D. 1, Elmwood/Conn: - Roll of-Membership; 1 r:75 . SIMPSON; Walter B. (A 1945) Div. Mgr- A. M. SMILES, Roy H. (Af '1941) Dist.-Dealer Mgr., . Byers'Co--1270/Arcade'Blvd- St. -Louis 1, and Carrier Corp-12 South 12th St- Philadelphia 7; 7747 Kingsbury, C!aytbri-5. Mo. ` . .and 5936'Seventh St- Philadelphia. Pa,.' ` " . SIMPSON, William K. (Af 1919) M. S. UtUe SMITH, Alexander S. (A 1944). Repr- Jenkins Mfg. Co.,' Hartford, and *21 Sands St- Water- Bros'.. 670 Gas Electric Bldg- Denver 2; Colo. bury. Conn. '. '' - ' - - ' SMITH; Alfred J. (Af 1945) Goik. Engr., 70 SINES, Chester F. (Af 1945) Sr. Naval Archt- Wigmore St- London *W. 1, and *56 .The Ave- Puget Sound Navy Ysird,-and 1125 Penn Ave- Bremerton, Wash. - ;- Muswell Hill, London N.' 10, England. - . . ' SMITH, Bernard (A ,1945) Tech. Htg. Advisor, SINGLETON, Arthur B: (Af 1943) Engr- Kerr Spirax Manufacturing.Co- Ltd- Charlton House, . Machinery Co- Detroit,-and 711 Collingwood ' and * Aubervie, Albert Rd- Cheltenham. Glos- Ave- Detroit. 2, Mich. -- ' England. - ... . _ SINGLETON, John H. (A 1944) Vice-Pres. & SMITH, Charles`H. (Af 1944) Secy. & Director, Gen. Mgr- *C.;A. Crosta, Inc- 1830 Market St L. J.'Wing Manufacturing-Co- 154 West 14th and l737 Glencoe St.; Denver.'Colo. ' SINGLETON, William H. (Af 1945) Vice-Pres. St., New York, N. Y-. and 501 Highland Ave- Newark 4, N. J. ' - .- & Treas- Mehring & Hanson Co- 12 H St. N.E., SMITH, Clifford F., Jr. (7 1943; 5 1941) Lt. S Washington 2, D. C- and 628 Oakland Terrace, -(E2) 143750. Commander, -Service ; Div. '73, Alexandria, Va. - " ' c/o F. P. O- San Francisco, Calif.,' and * 1609 S.- SINGMASTER, J. Walter' (Af 1943) Pres., Center Ave., Sioux Falls, S. D. . * ' * ' - Lehigh Valley Supply Co- Third and Oak Sts- ` SMITH, David J. (7 1941) Sales Mgr- * Walter ' Allentown,'and # 101 E. Main St- Macungie. Pa. SINISH,. William R. (Af 1943) Vtg. Engr- H. Eagan Co- 2336 Fairm'ount Ave., Philadelphia 30. and 524 -Mercer- Rd- Merion Park, Merion General Electric - Co- Fort Wayne, and 1408 ' P. O- Pa. ., Charlotte St- Fort Wayne 3, Ind; - SMITH, Edward D. (A 1944)'Asst. Mgr.' Ma-' SISK, R. D. Van (Af 1943) Vice-Pres. & Gen. Mgr- chinery Div- The Lang- Co- 267] W. First S- Piedmont Engineering Corp- and 2539 Forest Salt- Lake City 9, and 1732 Laird - Ave- Salt Dr- Charlotte;-N. C. '- 'Lake City 5, Utah. SriTON, Elbert R. (A 1945) Owner, 2420 Nichol SMITH, Elmer G.* (Af 1929) Pro'Ll of Physics, son, and 1136 Ashland, Houston 8. Texas.. ' Agricultural & Mechanical College-'of Texas, SKAGERBERG, R. (Af 1939) Chief, Maintenance . Dept. of. Physics, and 303 S. Dexter Dr- College ' Engrg., Federal- Public .Housing Authority, . Station, Texas. - . Longfellow Bldg-. Washington, D. C-' and 420 SMITH, Elwyn L. (Af 1945) Asst. Sect. Head, . Tyler PI;, Alexandria; Va. -. Military Design Sect., War Dept- U. S. Engi SKAGGS, George E. (Af 1945). Staff Engr- , neering Dept.,`10 East 17th St-.Kansas City 8,- -Donald R-. Warren-Co- 417 Market St- San and 6508 Paseo, Kansas. City 5; Mo.. . . . Frandsco; and 1502 Alice St.( Oakland, Calif. SMITH, Ernest T.`(Af 1943) Engr- *The Detroit' SKIDMORE, .'John G. (Af 1944) Construction Edison Co., 2000 Second Ave- Detroit 26,' and . Engr.,- Almirall '& Company, Inc..- 53 Park' 4400 Three Mile Dr--Detroit 24, Mich. / - ` . Place. New York 7, and 208--Woodbine Rd- SMITH, GardW. (Af 1927) Sales'Engr./* Premier Roslyn Heights, N..Y. . Furnace Co--1131 Guilford St-Huntington;'Ind.; SKINNER, Alton, Jr, (A 1944; J 1940) Supt- SMITH, George E. (Af 1944; A 1942) Supvsg. 4 J. R. Bagwdl Co- P. O. Box 2007; and 1202- ' Engr., Ministry of Works, and 1 West Ave Vickers Ave., Durham, N. C. . Pinner. Middlesex, England. ' - ' SKINNER,.Frank (A 1944) Estimator. B. & B. SMITH, Gerald E. (A 1945; 7 1938) Field Engr-. Engineering & Supply Co- 2900 Washington`Ave- Canadian Sirocco Co- Ltd- Box 360, Windsor - and 3379 Tampa St- Houston, Texas. - ' and 52* Parkway`Ave.; Toronto, Ont., Canada." SLATER, William F. (Af 1944) Pres., *W. F; SMITH, Guy F. (A 1945) Sales Engr- The H. B. Slater Engineering Corp- 627- -. Monroe Ave- Smith'Co., Inc- 605 Fox Bldg- Philadelphia' 3,' Memphis 3, and 115 Morningside Park, Memphis, and *46 W.-Essex Ave- Lansdowne. Pa. ... Tenn. - - - - .' SMITH, Harold G. (Af 1941) Owner,-Smith SLATER, William H. (7 1945) Engr- Carrier Steam Specialty Co- 1116-18Temple Bldg- Kansas--. Corp'- 12 South 12th St- Philadelphia, Pa. . City 6, and 5840 Oliver St- Kansas City 4, Mo.' SLAWSON, Lloyd E. (A 1938) Pres- *Air Filter SMITH, H. Gilman (Af 1944) Sales Engr- Alad-' . Equipment Co- Inc.,-3030 Euclid Ave- Cleve din Heating Corp., 2222 San Pablo Ave., Oakland'- land; and 1179 Sylvania Rd- Cleveland Heights 12, and 751 Warfield Ave.,' Oakland 10, Calif; , - . 21, Ohio. . '- -. SMITH Howard W., Jr. (A 1944) Engr- Southern SLEISTER, Park E. (A 1943) Field Supt- Leo . California Telephone Co.,`740 S. Olive;St/ Los' - A.' Daly Co- 629 Insurance Bldg- Omaha, and Angeles 55; and *809.- Patterson Ave- /Glendale \ 853 W. Eighth St- Fremont, Nebr. . 2. Calif.v > v SLEMMONS, John D. (Af 1937) Mgr.; Columbus SMITH,.John'A. (A 1944) Mfrs. Agent, John /Office/*American' Blower -Corp- 2-15th Ave- A. Smith-Sales Co- P..O. Box'144/Capitol Hill .Columbus-1, and 'R. F. D. 2, Wilson Bridge Rd- - Sta., and 1418 Elizabeth Sti,' Denver,' Colo.' ; --. ' Worthington. Ohio. - SMITH; Karl H. . (A 1944) - Sales Office Repr.,' SLOANE, David J. (7 1943; S 1939) U. S. Army. American Radiator & Standard Sanitary Corp... '"'56th General Hospital, Ft. Jackson. S. C. - U. S. .National Bank Bldg- and 1321'E. Tenth SLUDER,' Clarence T. (Af 1944) Mech. Engr., Ave- Stanley Arms Apt- Apt. 8, Denver, Colo: 'Federal'Houdng'Adininistration,. 1001 Vermont SMITH; Lawrence J. (Af 1943) Dir. of Research, - Ave. . N.W., . Washington, and 1320-21st St. . Bell &-Gossett Co- 8200-N. Austin Aye., Morton ~ .N.W., No. 45. Washington 6, -D. C. ' . \ Grove, and *455 Lenox St/, Oak Park.'Ill;' - , SMAK,- JuUus. R. (A 1934). Engr- Fletcher- Thompson. Inc- 211 State St- Bridgeport, and - 160-Morehouse Highway, R. D. 6, Fairfield, Conn. SMALL, Alex. G.(Af 1945) Assoc. Htg. & Vent. -'Engr;, Los Angeles. City Board of Education. . 1425'S. San Pedro St- Los Angeles 15, -and 1575 Casa Grande St- Pasadena 7, Calif. .- SMITH, Milton S. (Af 1919) Vice-Pres. & Treas' Buensod, Stacey, Inc-60 East 42nd St-New.York 17, N. Y,,*and 13 N. Terrace.'Maplewoqd, N; J.' SMITH, Norman- Alexander '(A 1944)'. Pres.. Norman-A. Smith-Co- 154 Front St.- E- and 269 Willard Ave-'Toronto,-Onti, Canada. ; ;Y- SMALL, Bartlett R. (Af 1938; A-1937; 7 1932)- SMITH, Oliver F,, Jr. (7 1944) /Engr./ Wertz' Staff Engr- Aluminum Company of America. . Engineering' Co- 441 N. Second St.', .Reading/and .-'801 Gulf. Bldg.v Pittsburgh 19, and *438 Olivet- ' 1521 Delaware Ave-Wyomissing, Pa.'. /*. ` Ave- Pittsburgh 10< Pa. . .- SMITH, Roger C. (A 1940) AssL Branch. Engr., SMALL, Ray A. (Af 1941) Mech. Engr- Ant. Div. - ' York Corp.; 119. South 11th St- St. Louis'2,' and- .' Engr. - Office. Engrg. Section.-.A. P. O. 851. 217. N. Meramec Ave- Clayton 5, 'Mo. - - " c/o P., M- Miami,-Fla.,-and-227 N. Third St- . SMITH/Roger. K. (Af 1942) Asstl'Prof- eMech. ^Lewisbiirg. Pa. `. - Engrg. Dept--. Iowa. State' College/ and.'2031. SMART,' J. H. (A 1944) Vice-Pres. in Charge of Country Club.Blvd-Ames, Iowa.* ' Sales', Tuttle & Bailey, Inc- and 419 Lincoln* SMITH.-Russell B. (A 1945)*Co-Partner/ Hun- . St-. New-Britain, Conn. . . . _ . ter-Prell Co-15 E. Jackson St- and 96 Greenwood.- SMERLING, Daniel (A^ 1944) Dist. Sales Engr- Battle Creek,-Mich. - -, v.,-- Flynn & Emrich. Co-'52 .Whitney Ave-*P. O.' SMITH, Russell^ H/ (Af 1945) -Prop./ Rus^l, Box. 1169, ahd'538 Norton Pkwy-'New Haven.' ` H. Smith Equipment Co- 5 E. Long St., Columbus'- / Conn. '. . ; 15. and 560 Arden Rd:.-Columbus 2. Ohio>' - 76- .7 . --t - Heating- Ventilating ' Air Conditioning Guide 1946 SMITH, Russell-J.-(Jf 1944) Mfrs. Repr., Htg. SOLSTAD, Lester L. (A. 1945; 7 1936) Engr., -Equip., 1601S. Grand Ave., St/Louis 4, and 7707 ; Austin Sheet Metal Works, 5109-W.'Chicago Ave..' : tile Ave.. St. Louis 17. Mo. ' - ` Chicago- 51, and 1649 N. Oak' -Park- Ave.. SMITH, Sidney T. (7 1941) Owner, *Sid Smith Chicago 35, 111. & Co., 411" W. Fifth St., and 2123 W. Third St., SOMERS, William S. (Jf 1938) Vice-Pres.-Chief Waterloo, Iowa. ' - Engr., Lamneck Products, Inc., 1025 Lamneck SMITH, Stanley K. (Jf 1945) Pres., *The H. B. St., and* 113 Kenwood Dr., Middletown, Ohio. . Smith' Co., Inc., 57 Main St., and 6 Lathrop Ave., SOMMERFIELD, Sumner S. (A 1941; 7 1936) - Westfield. Mass. - . . . 4918 George St.. Chicago 41, 111. - SMITH, Stuart (A 1936) Dist. Mgr., Reynolds SOMMERS, William J. (Jf 1937) Dist. Repr., 'Metal'Co., 19 East47th St., New York, and *654 Ilg Electric Ventilating Co.. 505 Delaware Ave.. Timpson St.. Pelham 65, N.-Y. . -Buffalo 2, and - 235 Hartford Ave., Kenmore SMITH, Vernon Dorsey (7 1944) Thermal Engr.. 17. N. Y. " L. E. Steyens Co., 626 Broadway, Cincinnati, SOPER, Horace A. (Jf _ 1916) Pres., American and 554-Belt St., Milford. Ohio. .Foundry & Furnace Co., Washington at McClun, SMITH; Walter H. (Jf 1939) Chief Engr.. The and 1122 E. Monroe St.. Bloomington. 111. -T. Eaton Co., Ltd., 10 Louisa St.,'Toronto, and ' SORMANE, Walter (A 1944) Gen. Sales Mgr.. Box 31, Islington, Ont.. Canada. " Conco Engineering Works, and 9l2-13th Ave., SMITH, WUbur F. (Jf 1920) Cons. Engr., W. M. Mendota, 111. ' '. Anderson Co.. 600 Schuylkill Ave., Philadelphia, SOULE, John P. (7 1942) U. S. N. R.. and 'and *709- Braeburn Lane, Penn Valley, Nar- Gordon & Stewart Rds., Essex Fells, N. J.. berth P. O., Pa. . SOULE, .Lawrence C.,* (Life 'Member Jf 1908) SMITH, William E. (7 1944) Sr. Draftsman. Secy.& Cons. Engr., Aerofin Corp., Syracuse. N.Y., . *100 Beechcroft Ave.. N. Harrow. Middlesex. and Gordon & Stewart Rds.. Essex Fells, N. J. .`England/ . - SPAAN, John H., Jr. (Jf 1945) Mgr., J. M. SMITH, William O. (A 1937) Pres'.. Midland - O'Connor Co.,-1633 N.W. Fifth- St., Oklahoma - Heating Specialties Co., 19254 John R,, Detroit 3, Mich. SMITH, William P,, Jr. (7 1942) 1808 Kenwood Ave., Charlotte 2, N. C. . SMOOT,-.Charles B. (Jf 1942) Engr., Maurice ' H.. Connell & Assocs., Langford- Bldg., Miami, -and'1217 Ave. Venetia, Coral Gables-34, Fla. City, and *2649 N.W. 11th St., Oklahoma City 7; Okla. . - SPALL, Edward G. (A 1939) .Vice-Pres., Perfex Controls, Ltd., Toronto, and*291 Windermere Ave., Toronto 3. Ont., Canada. ' ` - SPARKS, James D. (M 1944; A-1937) Northwest Repr., Ilg ElectricVentilatingCo.,7331 W. Green Lake Way, Seattle 3, Wash. - ' - , ' SMOOT, T. H. (Jf 1935) Vice-Pres., Anchor Post SPECKMAN, Charles H. (Life Member; M 1918) " Fence Co., 6500 Eastern Ave., Baltimore 24, and 1 ` Consulting Htg.& Vtg. Engr., *382 Philadelphia 1302 Southview Rd.. Baltimore' 18, Md. ' * - Bourse Bldg., Philadelphia 6, and 1217 S. Fourth SMYERS, Edward Cl (A 1933) Sales. Engr., St., Philadelphia, -Pa. . . - Barber-Coltnan- Controls, 1013 Penn Ave.. Wil- SPEER, Julian (A 1944) Mgr., Julian Speer Co., -kmsburg,-and *148 Jamaica Ave.. West View, 101 North High St.; and 101 N. Ridge Rd.. Pittsburgh, Pa. ' . Columbus,- Ohio. ' SMYTH, George E. (A 1944) Service Installation " Mgr.,' B: B. Rider.' 14 Howe Ave., Passaic, and ,v- 26-02 Southern Dr.,- Fairlawn, N. J. SNAVELY, A. Bowman (Jf 1937) Chief Engr.. -`Hershey Chocolate Corp., and Hershey, Pa. ; SNAVELY, Earl R. (Jf 1937) Sales Mgr.. Instni- .ment Div., Thomas A. Edison, Inc., West Orange, and Parkway Dr., jMtd. Rt. 3B37, Clark, Rahway, N. J. ' ` ~ ' '` SNOOK, Alfred H. (A 1940) Dist. Repr., Ameri can Air-Filter Co., 324 N. Main St;, and Wayland Mich.-: . .' SNOW, Edward .E. (Jf 1945) Chief Designer & .-Engr.,-Mellor Bromley & Co., Ltd.. St. Saviours . ' ;Rd.. and *32-Spencefield. Lane, Evington, Lei- ' . cester, England'. . . ' SNYDER, Edwin ^F., Jr. (A 1946; 7 1940) Htg. SPELLER, Frank N.* (Life Member; Jf 1908) Metallurgical Consultant, 6411 Darlington Rd.. Pittsburgh 17, Pa. 'i . -- SPENCE, Morton R. (A 1942; 7 1934) Vice-Pres.. Rundle & Spence Mfg..Co.,445 N. Fourth St., and 709 E. Lexington BIvd,, Milwaukee, Wis. '. SPENCE, Robert A, (A 1946; 7 1937) * 33 Barnard-Rd.. Belmont 78, Mass. . . ' SPENCER, Charles H., (M 1944) Factory Agent and Sales & Service Engr., 1421 S. Main St., Salt Lake City 4. Utah. - ' -" ,, SPENCER, Roland M. (M-I945; A 1940; 7.1938) Chicago'Distr. Mgr., The Powers Regulator Co.. 2720 Greenview Ave., Chicago 14, and 7315 Lunt -Ave., Chicago 31. III. -. . -' . ' SPENCER, Warner E. (A 1938) Repr., National Radiator Co., Inc., 220 Delaware Ave., Buffalo 27 and 212 Bidwell Pkwy;. Buffalo. N. Y. -- - Engr.,' * Minneapolis-Honeywell Regulator Co.. SPIELMANN, Gordon P. (A 1931; 7 1923) -.Minhea'polis,- and R. 3, Box 286-E, Excelsior, Owner, Harrison-Spielraanrf Co.. 480.Milwaukee . Minn. ' . Ave., Chicago 10, and 730 N. .Prospect Ave., SNYDER, Edwin J. (7 1944; ^ 1943) lst-Lt.. " Park Ridge,-111. - U.- S'.; A.,'*0553657, 3118th Engr..' F. F. Plat., SPIETH, Benjamin (M 1941) Chief Engr.; .Fort' Lewis,- Wash.,'.and 3903 Dolfield Ave.,! Modine Manufacturing Co., and '400 Harvey : . Baltimore,' Md'. - . . ' ' - Dr., Racine, Wisi .' * . ' SNYDER.x Jay W. (Jf 1917) Member of ` Firm. SPITZ, Nathaniel (7 1945) Head of Sales &' In-' - Snyder McLean.' 2214 Penobscot Bldg., . staliation, City Coal Co., 410 Bank St.,'and 300. . DetroitV and 15810 Asbury Park. Detroit 27. Mich. ` Ocean Ave.. New London. Conn. ^ : SNYDER,.L. R. (A 1944) Owner; L. R. Snyder SPITZLEY. Joseph H. (7 1943) Vice-Pres., - Co;, 2625 University Blvd., Dallas 5, 'and 7034 -R. L. Spitzley Heating Co., 1200 Fort St. W., - Lakewood' Blvd., Dallas 14. Texas. ''i ' Detroit 26, Mich. . SNYMAN, G; C.,(A-1941) Mgr.. Overseas Div.. SPITZLEY, R. L. (M,,1920) Pres. & Gen. Mgr;, Gelotex Corp.. 120. S. LaSalle St.,- Chicago 3,- -R. L. Spitzley Heating Co.. .1200 W. Fort St./ - andEvanshire Hotel, Evanston, 111. - '' - -Detroit 26; ,,and 26 Renaud Rd.. Grosse Pointe SOBEL5,'.Frank. (5 1939) Pvt.. *813 M. P. Co.. - Shores 30, Mich. ' . t . `` . A. P^O^.928. San~ Francisco, Calif.; and 115 Post SPITZLEY, Ray L. (A 1944) Inspector of Re " Ave.', 'New -York. N. Y'. . . - . fineries Class B, Genera! Petroleum Corp., Tor-, SOCKWELL;'Charles, Jr. (A 1942) ~ Partner. ranee, and *11542 Rochester,' West Los Angeles Sockwell Co.,.. 156 Rogers .St. N.E., and *2562 . 25. Calif. ' ` .. - - '. " . Boulevard-Dr. N.E.; Atlanta, Ga. - . - - ' SPOERR, Frank F. (A 1942; 7 1937) *140-19 SOCKWELL7 Charles,. Sr. (Jf 1942) Partner. Queens Blvd., Jamaica 2. L. I., N: Y. . SockwellT'Co.rrl56. Rogers St.-N.E., Atlanta,' SPOFFORTH, Walter (M 1930) Chief of Mech. ,and*5447 Roswell Rd.. Dunwoody. Ga. - Services, Federal Penitentiary. McNeil Island; and SOCKWELL.-Tyrus R; (A 1942)-Partner. Sock- 615 N. Ainsworth. Tacoma 6, Wash. ,` ..weU' Go./-156 Rogers1St. N.E.', and'*372 Morgan SPRIGGS. Carl U. (A 1945) Asst. Sales Mgr.; - PI.'S.E.rAtlanta, Ga.'~ - \ ' - - - - Carrier Corp., Syracuse, and JOl Hampshire Rd.-,; SODgMANN, WUIlam C. B. (Z.>y Uember; M . Syracuse 3, N. Y. . ''J. . :~1919).Pres.. Sodemann,Heat~&'Power Co.; 2306 -SPRINGER,;J. J.,(A 1945) Owner.* Oneida Sup-, DeimarBlvd./St. Louis, and 7542 Teasdale Ave., ply. Co.,-157-159 CedarSt., and-506 Broad'St.. . Uhivefsity.City,cMb.-v-- - - . Oneida, N. Y.:-. ' ' :" *' Roll of Membership . ' _ ~- - ' ' ' ' ' - . ' 77 . ` SPROTT, John I. (A 1941) -Sales. Ray Oil -' -Burner .Co., 401 Bernal Ave... and 70 Crestlake ; Dr., San-Francisco, Calif.' ' . : '. SPROULL, Howard E. (M 1920).Div. Sales Mgr.. ' American Blower Co., 1005-6 American Bldg., Cincinnati 2, and 3588 Raymer Dr.. Cincinnati 8, Ohio. . . .- SPURGEON, Joseph H. (M 1924) Mfrs. Agent. Spurgeon Co., 5050 Joy Rd., Detroit 4,-and 17215 Pennington Dr., Detroit 21, Mich. SPURLOCK, Benjamin H., Jr. (M 1944) Dept, of Mech. Engrg., University of Colorado, Boulder. Colo. - SPURNEY, Felix'E. (A 1938) Engr.. Luther and ` 'Wood, -1427 Eye St. N.W., Washington, D. C.. and *28'W. Baltimore St., Kensington, Md. STACEY, Alfred E,, Jr.* (M 1914) (Council. 1941-44) Capt.. U. S. Navy, and *35 Wootton . Rd., Essex Fells, N. J. *- STACK, Arthur E. (A 1935) Lt. Comdr.. U. S. N. - R.. and 7911 Chicago Ave.. Silver Spring, Md. STACY, Stanley' C. (M. 1931) Mech. Engr.. ` Board of Education, 13 S. Fitzhugh St., Roches ' ter 4. and-111 Valley Rd., Rochester 10, N. Y. STAFFORD. J. FuUer (A 1938) Owner, 519 N. .-Snelling Ave., St. Paul, and 4545-18th Ave. S., - Minneapolis, Minn. ' " STAFFORD, Thomas D. CA 1937) Vice-Pres.-. Mgr., Alexander-Stafford Corp., 1 Ionia Ave. N.W., and '954 Ogden Ave. S.E., Grand Rapids, Mich. . * STAHL, Walter A. (M 1938) Gen. Maintenance - Mgr., Montgomery Ward & Co.,-619 W. Chicago . - Ave.; Chicago, and 2504 Harrison St.,* Evans- . ton,'111. 'STAINS, W; A. (M 1945) Chief Engr., *Wurde- .. man & Becket. A. I. A.,, 3757 Wilshire Blvd., Room 201, Los Angeles 5, and.521 E. Valencia ` . Ave;, Burbank. Calif. _ STALB, J. G. (A 1943) Reg. Mgr., Indus. Heating, Carrier Corp., 405 Lexington Ave., New York 17, -and *R. F. D. No. 2. Ridgefield, Conn. fTTAMBERGER,' Robert F. (A 1944) Estimator & Supt.,_ The Stamberger Co., 3115 Mayfield Rd.. and *2289. Lamberton Rd.. Cleveland Heights, Ohio.. ." STAMMER, E. L. (Life-Member; M 1919) Retired, *7046 Winona, St. Louis 11. Mo. . STANDRING, Ronald A. (A 1942 ; 7 1938) Htg. - .Engr., Gurney Foundry Co., Ltd., P. O. Box .277, ' and- 2358 Leclaire Ave., Maisonneuve, ; '* Montreal, Que.,' Canada. / STANGER, R. B. (M 1920) Prop., Robinson & '. 'Stanger, Empire Bldg.,'Pittsburgh 22. and Middle .. Rd.; Glenshaw, Pa. ' . STANGER, William F. (M 1945) Sales Engr., ' Robinson & Stanger; 1005 .Empire Bldg., Pitts burgh- 22, and *337 S. - Millvale Ave., Pitts burgh 24, Pa. , STANLEY, Robert L. (M 1938) Field and Re . _ search Engr.,' Naco ' Manufacturing Co.. 7631 ; Roseberry. Ave.; Huntington Park, and *3828 -'Udell Court St;;Xos Angeles 27, Calif. STEARNS, Ellis J., Jr. (M 1944) Engr., National Bureau of Standards. Washington, D. C., and . ' 933;.Parker St., Falls-Church, Va. - . '' .STECKHAN/Louls (M 1941) Sales Engr., Crane :Co.f 30 South 16th. St.. St. Louis 3, and 3240 . '.-Liberty St.'. St. Louis 11, Mo. STEEL, R. Justin. (A 1938). U.; U. S/ N. R., - Bureau of Ships, Navy Dept., Washington. D. C. and 346 S- College Ave., Newark', Del. , . STEELE. J, B. (M 1932) Chief Operating Engr.. Winnipeg School District No. 1. Ellen and William .`'Ave., and *184 Waterloo St.. .R.H., Winnipeg. ' - .-Man., Canada. .' - - . . ' STEEVES, Donald R.-(A 1944) Mgr., Equipment . ` Div;, Farquhar Robertson, Ltd., 1124 Beaver Hall ' HilL and *5400. Queen . Mary Rd., Apt. 29, Montreal, Que., Canada. . STEFFNER,. Edward F. (A -1937; 7*1934) Re- ^^arch Engr., Viking Air Conditioning Corp., 5601 ' Walworth. .Cleveland,- and 1429*East 133rd St., "E.`.Cleveland Ohio.-- ' . . '' STEGGALL, Howard B. (M 1942; A 1934): * United States Radiator Corp.. -1500 United Artists -'-'-Bldg.,- Detroit,- and*Concord Rd., Bloomfield-' Hills. Mich; . .STEIN. Herman W. (M1944) A. C. Nielsen Co., ,2101 Howard St.,' Chicago, and 708 Roger Ave..- ` Kenilworth, 111.- v . STEIN, Jerome (7 1942; S 1940) Secy.; Tor-' .rington Supply Co., Inc., 125-Maple St., and *756 Waterville St., Waterbury, Conn. . -. STEINHORST, Theodore F. (M V1919) Pres... Emil Steinhorst &Sons, Inc.. 612-616 South St., 'r : Utica 3. N. -Y. - .' ' STEINKE, Bernard J. (7 .1940; 5 1937) Mech: .' Engr., U. S. Rubber Co., Maple St., Naugatuck,' -- ' and Peach Orchard Rd., Waterbury 82, Conn. '> STEINMETZ, C. W. A. (M 1934) Mgr/, Newark . Office, American Blower Corp., 1060 Broad St.,`. V Newark 2, and 50 Oakwood-Ave., Bogota, N._J/' ' / STELL, William H., Jr. (Jf ,1944) Owner. - Arnold R. Kamman Co., 493 Franklin St;-,.' Buffalo 2, and 648 Clay Ave.,- Rochester 13, N. Y. 1 . STEM PEL, Edward H. (Jf 1942) Chief Design Engr., Young Radiator Co., and *2321 Webster - St.. Racine, Wis. - -. STENGEL, Reinhold A. (Jf 1938) Chief Engr;. ' Canadian Ice Machine Co.,' Ltd., 65 VHliers St:,' - and 224 Inglewood Dr.. Toronto, Ont., Canada. STENGEL, Frank J. (A 1935) Capt., 1326 Engr.' ; G. S. Regt., Camp Claiborne', La., and 39'Walnut . . Ave., Millburn, N. J. . , , STEPHAN, Charles O. (A 1945) Owner.'Stephan . & Lambert, 419 N. Santa Fe, and *1925 Green- . * wood, Pueblo. Colo. ' ' <- STEPHENSON, James R. (A- 1940) *J. R. Stephenson & Co., 278 Main'St.,'and 647 Strath- cona St., Winnipeg, Man., Canada. ' . -- STEPHENSON, Kiser A. (Jf 1941). Pres., *Ste- . phenson Co.. 14 Harris St. N.W., Atlanta 3,-and ; 923 St. Charles Ave. N.E.-, Atlanta, Ga, .. .. ' - - STERMER, Clarence J. (Jf 1936) Engr., Crane.- Co., 836 S. Michigan Ave., and *7839 Clyde Ave., Chicago, 111. ' - .* -. -V . STERN, Edward J. (A 1941) ,-Dist. Mgr., Arros\-1 < . strong Cork Co:, 701 Burt Bldg., Dallas 1, ami 0 223 E. Davis St., Dallas 8. Texas. - . ' '\ STERN, Lester M. (7 1945; S 1944) Ensign,. U. S: N. R., ASST. Engr. Officer, U.S.S.Sproston (DD 577), F. P. O., San Francisco, Calif. - STERNBERG, Edwin (A 1932; 7 1931) Design. . Engr., Fred Moesel Assoc.; 101- Park Ave., and 16 East 98th St., New York. N.. Y. '-. - STERNE, C. M. (Jf 1943; A 1934) Lt. Comdr.. . ' U. S. N. R., Retired, and 50-23 23rd St.', Long i-' Island City lr N. Y. . ./ . . STERNER, Douglas S. (Jf 1941; A 1940; 7 1936), ' Major. -U. S. Army, and* 1801 Pebrican St., ; Cheyenne, Wyo. ; . ' " ' '" - * STERRY, H. Lee (A. 1945) Dir. of 'Business'' ; Research, Carrier' Corp.", and' 321 -Clairmonte Ave.. Syracuse, N. Y. .- . ...y STETSON, Lawrence R. (Jf 1913) Engr,, * The * McMurrer Co., 303 Congress St.,'Boston, and-35-" Bradfield Ave., Roslindale, Mass. - ' ' -' STEVENS, Earl Knights (A 1940) International .-; Exposition Co., 480 Lexington Ave.,- New .York 17. N. Y. . *- - ' . . .> / ' V- STEVENS, Harry L. (M 1934; A 1927; y-1924). : Pres., *M. M. Stevens Co., 108-110.W. Sherman St., and 320 West 20th Ave.. Hutchinson, Kan. ^' : STEVENS,'Howard R. (Jf 1941) Owner, Stevens - ' ' Heating & Supply Co., 225 E; Fourth St.,-and.*' P. O. Box 182, Reno, Nev. . : - - ^ STEVENS, Joseph W. (Jf 1944) Salw Mgn,`r ' Cyclotherm Corp., Oswego, and *303 Maple Rd.t ' - Syracuse" 9, N. Y. . ' - '. r STEVENS, Judson E. (A 1941) Engr. in Charge, 1 ' National Coal Co., 318 Spokane St., P. O. Box- - C 318. and 520 Vassar St., P. O. Box 2542, Reno; NevI' - ' STEVENS,"Kenneth M. (A 1943; 7,1936) Br.- ; -:- Mgr., The Powers Regulator Co.,'409 P-ast 13th St., Kansas City 6, and 1214 East.82nd Terrace, - Kansas City, Mo. - ^ STEVENS, Stanley A. (A 1945) Engr.,- Matthew . '.Hall&'Co., Ltd.; 28 Dorset Sq.,'London N. W/.l, ** and 30A Falloden Way^ Golders Green, 'London ^ r : N. W. 11, England. STEVENS,-Wayne H. (A .1939) En^r., *Sheilen-v berger. Gregg & Co., 2211 N.' Prospect" Ave.;; * . Milwaukee 2, and 2501 E. Stratford Ct.VMilwau-i ''. kee 11, Wise. STEVENS, William' B. (A 1944) Htg. *.Engr.V ' : Stevens Furnace Co., 79 S;'LaSalle SL; ahd'121'9 r New York St., Aurora, 111. - -' ' '. . .. STEVENS, William R. (A 1934) Partner, *L.'E.' Stevens Co:, 626 Broadway; Cincinnati-2; Ohio, ,< and 30 Chalfonte Ct., Ft. Thomas, Ky. - - ; -rr/` -~J.- / ' * ' 7S ' . - Heating Ventilating Air Coriditioniiig Guide 1946 ~ " 1 i.: ,, -- - .. TM' ' -1 Roll of -Membership 79 V A- . , STEVENSON, Mel J. (Af.. 1935) Cons. Mech. . STOREY, J. H: (M 1944). Pre3-. # John Tweddle. . ~ '/Engr., Pyle National Industrial Multivent Divi- Ltd.. 80 Jean Talon St. W7, Montreal 14, and 5201 , /sion,-plus private- practice, # Apt. 1004, 2970. - Decarie'Blvd.; Montreal; P. Q.. Canada. l/ - SULLIVAN, Thomas J. (7 1943; S' 1942) Lt. (j-g). U. S. N. R., Administrative Aide to Shop SYSKA, Adolph G. (M 1933) Partner. #Syska & Hennessy, 144 East 39th SL, New York, N. Y; ,v. - -Sheridan Rd./ Chicago 14, 111.- \ . '- STORMS, Robert M. (Af 1936) Htg.. Plbg., Vent., .. . STEVENSON, W. W. (M 1928) Steam Htg. Engr.. Storms & Lowe. 6359 Yucca St.; Los Angeles'28. Allegheny County Steam' Heating Co., 435 - and #354 W.-Wilson-Ave.. Glendale 3. Calif. V Sixth Ave-. Pittsburgh 19, and 1125 Lancaster STOTESBURY. Bernard (M. 1942) Partner.' -Ave.vPittsburgh 18, Pa. . ` - Ottawa Plumbing 8c Heating Contractors, -111 ; ' STEWART, Charles W. (M 1919; A 1918) Vice- Third Ave.,-and'118 Gilmour SL, Ottawa, Out.. > "; Prea-Sales, Clark Mfg. Co., 1830 East 38th St., - -Canada.' - . - -. " Cleveland. Ohio. ' ` . - STOTT, Douglas A. (A 1940) Vice-Pres., Mgr.. , STEWART, * Clement W. (M .1944) Marine ' Canadian Powers Regulator Co., Ltd., 195 .. Specialist. Ilg. Electric Ventilating Co.. 15 Park Spadina Ave., Toronto 2-B, and 30 MacNaughton . .-Row,- 1108, New-York 7, N.-Y., and #828 Fifth Rd.,.Toronto 12, Leaside, Ont;,*Canada. ^ Ave., River Edge, N.`J. - ' . STOTT, F. W. (M 1938) Branch Sales Mgr?, ' * STEWART, Duncan J.* (M 1936; A 1930),Vtce- 'C: A. Dunham Co., Ltd., 1139. Bay SL, Toronto, . . Pres! & Gen.-Mgr., Barber-Colman Co.. Drawer ' and #Thomas St.,-Oakville,-Ont;, Canada.' . SupL, #U. S. Navy. Yard,' and 48 Monument - SZEKELY, Ernest (M1920) (Council. 1945) Pres.. - Walk, Apt. iC, Brooklyn 1, N. Y. ` . Bayley Blower Co.. 1817 South 66th SL, Mil- . SULLIVAN, T, J. (M 1940) Pres.. Sullivan Valve waukee 14. and 6026 W. Washington Blvd., ;VVau- ' , & Engineering Co.. 910 S. Arizona St., and 1205 - W. Park St., Butte. Mont. -. ` . SZOMBATHY. L. R. (A 1930) Pres., Ferguson SULLIVAN, William H., Jr. (M 1944) Vice- Sheet Metal Works,-Inc.. 34 N.` Florissant Blvd.. . Pres., W. H. Sullivan Co.. Inc., P. O. Box 232. - Ferguson 21, and 3125 Hawthorne 'Blvd.,, SL.' and 308 W. Greenway South. Greensboro, N. C. Louis 4, Mo. .' SULLIVAN,-William H. (M 1943) Pres., #W. H. Sullivan Co.. Inc., P. O. Box 232. and 200 E.- Greenway North, Greensboro. N. C.' SUMMERVILLE, E. A. (A 1944) Pres.. #Bixley TAGGART, Ralph a* (Life Member; M 1912) _ ' Inc., 610 Walnut Bldg., and 5701 Waterbury Bolton, Mass. ` . ^ ' Circle. Des Moines 12. Iowa. TAGGART, Robert F. (M 1944) Mech. Engr- ' T , -: : * ' 99,' arid R..R. 4, Rockford, 111. STOUT, Arthur G. (M 1943) Asst. Chief Engr/. .`STEWART. Irll A. (A 1945) Mech. Engr.; Office' -. Holabird 8c RooL 333 N. Michigan Ave.,' Chicago,* - SUNDERLAND, Richard P. (A 1938) Partner. ' General Meters 8c Controls Co.. 205 W. Wacker O. W. MoU, 920 E. McMillan SL. Cincinnati'6, ` * and #4673 McNeill Ave- Cincinnati 12,- Ohio. ` ' . ' -of-the'-Service'Command Engineer, Hq. Ninth and # 105 East Ave., Park Ridge, -IU. .'-'` '1 ServiceCommand,. Ft. Douglas,, and 1621 STOVER, Rolland S. (A .1944) Owner, Engi-. - Dr...Chicago, and 1250 Cherry St., Winnetka. 111. SUPPLE,- Graeme B. (M 1934) Indiana DisL TAHRY, Mahmoud El (M 1939) Managing Dir., .. * . .# Koldair Air Conditioning & Refrigeration Com- ' ' . " - * Princeton, Salt- Lake City 5, Utah. ' V-STEWART, James P. (A-1940; 7.1937) Engr.. . . . f-'.Carrier-Corp., 300 Geddes SL, and #224 Green- v, _-. ,wbod PL.-Syrhcuse 10, N. Y.. ` '. ^' /STEWART,. John L., Jr. (A 1944) Gen. Mgr., . ` '^-#Calif-Fresno Air Conditioning.Cd.,.'P. O. Box ' ;527, and I426 San Pabl,'Fresoo. Calif. * - '- neering Equipment Co.. P.' Or Box.354. 'and .207, N. Eighth St..* Marshalltown, Iowa. ; ' : " ' . . - STRACHAN, George W. (M 1945) Project'Engr., . Dravo Corp., 300 Penn Ave., and 1848 Hillsdale Ave., Pittsburgh 16, Pa. .' ' . ' -/ - STRAIN, A. James (A 1942) Gen.' Mgr., Ruud Manufacturing Co., 474-476 Bathurst SL, Toronto . Mgr.. American Blower Corp- 625 Architects 8c Builders Bldg., and 420 East 55th St.. India napolis, Ind.. SUTCH, Harry C. (A 1940) Capt.. Umatilla Ordnance DepoL Ordnance. Ore. SUTCLIFFE, A. G. (M 1922; A 1918) Chief Engr., Ilg Electric Ventilating Co- 2850 N. Crawford pany of Egypt, 12 Sharia Soliman Pasha, Cairo. .' and 18 Hafez Ramadan', Agouzah. Cuizah, EgypL ' 1' ' - TALIAFERRO, Robert R.* (M 1919) Mech. ' . v; =- . ' Engr., National Advisory Committee for Aero- . . ' .. '-J nautics, Cleveland Airport, and 1383 Elbur Ave., ` " Lakewood. Ohio. TALLEY, Dean (A 1944) Sales Engr- Sullivan . ` . ? " - STEWART, John N. (A'-1939) Plan Examiner, 2-B, and 376 SL Clements Ave., Toronto 12,'OnL',- v-* District of-Columbia, 102 -District .Bldg., and Canada. * -^ - 6124~32nd PL N:W- Washington 15, D. C. STRAND,-Charles. A. (A 1940) SupL, # Bruce STEWART, Ralph M. <A 1945) Mgr., Bryant Wigle Plumbing Co., 9117 Hamilton Ave.,-Detroit " '-''. Gas-Heating Co., 3020 E. Franklin Ave., Minne--. 2. and 6533 Barium-Ave:, Detroit 10, Mich; . . : (/apolis 6,- and 26'.West 22nd SL, Minneapolis 4, STRAUCH, Paul C. (M 1945; A 1934) Mgr., Htgi . Minn;?*r* '> - . Div.j#Sears-Piou & Co.. .814 S: Vandeventer,. -: - .STEWART; Wesley O. (M 1944; A 1938) Branch St. Louis' 10, 'and-73097F. Burrwood Dr^ Nor ' -Mgr.,-'# Johnson ' Service~ Co.,'-153 West^ Ave., mandy 21.-Mo. - *. *. .-.iLos Aiigeles'31, and'4lOOJ Los Feliz Blvd-.Los . STREATER, Edward C; (A 1939) Mgr., E. C. *7.\-Angeles, Calif. : `' - ' Streater Co., Spring Park, and Mound. Minn. ' ' - STICKLE,' Fred A. (A. 1945) Pres. & Gen.. Mgr., STREATER, Walter A. (M 1945) DisL, Repr., , Stickle Steam-Specialties Co., 2215 Valley Ave., - Modine Manufacturing Co./ 152 Nassau.St. Indianapolis 1, and #2339 Broadway St., India N.W., Atlanta 3, and 151 Coventry Rd.7 Decatur, .- .- napolis .5,-Ind. /' ' > . ' ' . ' Ga. . - - '- . >STICKRATH; Kenneth J. (A 1945) -Owner. . STREVELL, R. P./MT934) Pres.-Treas., #The V. #K. j7.Stickrath, 316 Shaw Ave.. .and 2821 William R. Hogg.Co... Inc., 900':Fourth Ave^ ; . ' -.Capital St., McKeesport, Pa. " . ,, Asbury Park, and Victor Place and State Highway, - : STILES, Gordon s. (A 1941; 7 1936) Field Engr.; 'l Chrysler Airtemp Sales Corp., 1032- Irwin-Kearfer 'Bldg.T, Dallas, and RL"4. Box 140, Bryan, Texas. Neptune, N.'J. - -. - STROCK. Cflfford (M 1937; A 1929) .Editor, ,' Heating 8c Ventilating,- 148Lafayette' St., New York 13,-and Box-756, Amityville. L'. I:, N. Y.- Ave.. Chicago, and #432 S. Delphia Ave.. Park Ridge, 111. SUTFIN, George V. (M 1942; A 1937) Branch . Mgr., American Blower Corp., 1005-6 American Bldg.. Cincinnati 2, and 3270 Hildreth Ave., ' Cincinnati 11, Ohio. ' . SUTTER, E. E. (A 1936) Sales Engr.. Mueller Brass Co.. Port Huron. Mich., and #6705 Sixth SL N.W., Washington, D. C. ' SWAIN, Douglas S. (A 1945; 7 1941) Sales Engr., ' v Trane Company of Canada, Ltd., 365 Hargrave St.,; and 1186 Downing St., ^Winnipeg, Man.. Canada.' SWAIN, Wilbur A. (A 1944) Sales Engr.. Jenkins Bros.. 80 White St., New York 13, and 90 Ever green PL, East Orange, N. J. SWAIN, William L. (M 1939) Dir.. Messrs. Young, Austen 8t Young, Ltd- 19 Buckingham St.. London W.C. 2, and 35 Uphill Rd., Mill Hill. . London N. W. 7, England. - SWALLOW, J. H. (A 1945) Branch Mgr.. St. ' . Louis Factory. Bryant Heater Co., 494 Arcade Valve & Engineering Co- 910 S. Arizona St.; and- - - 2031 S. GaVlord Ave., Butte, Mont*. : ' TALLMADGE, Webster (M 1924) Pres., Web- . / . ^ ster TaJlmadge 8c Co., Inc., 364 Glenwodd. Ave- ' and 526 Park Ave., East Orange. N. J. TANNER, Dick (A 1945) Secy. & Gen. Mgr.,. ' ; . / Rocky Mountain Gas Equipment Co., 308 C. A.' * - Johnson Bldg., Denver 2. and 2134 West 29th ^ ' Ave-Denver, Colo. -- ' v. TANZER, Guy J. (M 1942) Hotel Standish Hall,' ' 45 West 81st St., New York. N. Y.` -- * TARR, Harold M. (M 1931) Htg., VenL 8c.: - , , Air Cond.- Engr- #21 Montague SL, Arlington ` ` Heights, Mass. :/ TASH, Thomas (M 1944) Pres- Consolidated, j ~ - : Constructors, Inc., P. O. Box' 89, and 2 Ridge 1' .1 h Rd.. Hanover. N. H. ; -' V. ' TASKER, Cyril (M 1935) (Council. 1941-43) \ ' \ Dir. of Research. American Society of Heating - \-': & Ventilating Engineers. Research Laboratory; ' 10709 Euclid Ave- Cleveland 6. and 3538 Edison - 7 Rd- Cleveland, Ohio. -: ' . '; ^ ' ' . . STILLER. F. W.! (A 1945) #4501 S. Aldrich, STROMGREN, Sven G. (M 1938) Managing Dir., . -.. T-C :Minneapolis 9, Minn. . - ' . Magnussons 'Mekaniska Verstad/ - -Regering- Bldg- St. Louis 1, and 845 N. Kirkwood Rd., - TASNEY, John S. (A 1943) U. S. Army, and - Kirkwood 22; Mo. . - . . 144 Hugo St., San Francisco, Calif. ' '. ... > ! STILPHEN, Norman E. (M 1945) Owner,.' . sgatan 109, Stockholm,:Sweden. . SWANEY, Carroll R; (M 1929 ; 7 1921) Mfrs. TATE, Howard L. (A 1943) Mech. Engr:, Titche- ' . . *. v. Stiiphep..Engineering Co., 26 Roberts St., and STRONG; Henry G. (M 1945) Dir. of Sales. ` Agent, C. R. Swaney Co., 335 Newbury. St.. Goettinger Co., and 4608 Livingston, Dallas, Tek.' ` ' :'i * --253>Main'SL, Sanford; Maine. - . - Transportation; Air Cond.-8c Refrig., Carrier. . Boston 16. and 61.Morse Rd., Newto'nville, Mass. TAVERNA, Fred F. (M 1928; A 1927; 7 1924) , : .. ." ^STTLWELL, R. F. (M 1944) Fuel Engr.,.#c/o * .-Corp." Syracuse, and 133 Edwards Dr.,- Fayette-: ~;*--jv''i;North American Coal Corp. 1425 Terminal Tower, vine.-N; Y: -SWANSON, Earl C. (A 1935) Vice-Pres., #Ander- , sen Com:. Bayport, Minn. . Mech. Engr., Raisler Corp., 129 Amsterdam' ' /;.,> . Ave., New York 23. N.'Y., and #1011 Palisade. ' ' - ',v: Cleveland 13, and 12500 Clifton Blvd., Lakewood, STRONG, Stewart S; - (A -1945) Sales Engr.; . SWANSON. Nils W. (A 1936) Sales Engr.. Ave-Union City, N. J. , * . - / ' v V j, '^-Ohio: ,--u - Parsons Engineering Corp., Box 226, Cuyahoga 'VSTIMSON,' DePark (M 1945) Application Engr., * ' Falls/ and 2916 Lee Rd., Silver Lake, Ohio. - - -. . *, - vi- :..The'Bahnson*Co., and Idlewilde- Dr., Winston- -r '-VSaieih; N.* C.- ' ; \' - ' '. .7 . , .; " 7.V r STITES; Richard, Jr. (A 1943; 7 .1937) Sales _ ,, Ehgr^ # Co6n Devisser. Co., 2051 W. Lafayette, , STROTHER, William E. <M 1944; A. 1941) Major. Corps'of Engineers, Post Engineer, ,Hq. ^ 4th Serv. Command,-and'# 997 Bums Dr.-S.W.. Atlanta. Ga. .` < `-A-. c.'"Detroit 16, mid 17537 Hartwell, Detroit 21,' Mich. . STROUSE,-Bernard H.. (M-1945) Owner.'#S: B.i _? "ST^rtiAURENT, Guy (A '1942) ` Htg. Contr.', ' & B. H. Strouse, 307 Guarantee Trust 'Bldg.-,-and 'Z* % T# Hector Groulx. Engrg.,. 1638 Notre .Dame St. 129 N.'Bartraiu Ave,,-Atlantic'City, N.-J.r ; < W;,` ahd 8381 Drolet St;, Montreal. Que., Canada. - STROUSE, Sherman W. (A: 1938) Trane Xo., " STOBBE; Gustav C; (A 1944) Gen. SupL, Beckerw `.^SeidePClark Co;, 4500 Euclid Ave., Cleveland 3,, * and 1805 Tampa Ave., Cleveland 9,-Ohio.. . STOCK; Charles S. (M 1936) Gen. Sales Mgr., . ... - The -Herman Nelson-. Corp.. 1824 Third' Ave., i C?:-- ^-Moline. Ill:;'and #R.'R. 1, Bettendorf,-Iowa. - .- . '493 Franklin St..-Buffalo 2, and 95 Mayville Ave...; Tonawanda,-N. Y. . STRUNIN. Jay . (A 1939; 7 1933) . Owner, Jay-- Strunin Plbg. 8c Htg;' Contr.. 408 Second Ave., New York 10, and 217 Ocean Ave.; Brooklyn, N.Y. STUART,' Milton C;* (M-1935) Prof:, of:Mech: Engrg.. Lehigh University, Bethlehem, Pa. ` V STOCKWELL, William' R. (Life Member STUART, Ralph A. (M 1943) Cons. Engr., Opera Lv. M r 1903; 7:1901) Gen. Mgr.; Mfg. Div.. #Weil- - Houses Bldg., - and #432 North 6J St.'.-'Teme-' McLain-Co.,Michigan City, Ind. -. - - ' , Haute,'Ind. .V ' STOFFER; Glen H. (M 1945)' Branch Dealer ' STUART, W. W. (A 1940) Owner, Stuart Supply, f - V- - Mgr ,':Carrier Corp... 542^ Buhl Bldg.,- Detroit 26. . ' 417'Ninth St.. Des Moines 9. and 1920 Pleasant .-.and #14384'Prevost Ave., Detroit 27,Mich. _ St., lies Moines, Iowa.. . A v ' - >STOKES,-Alvln D; (Af 1936) Riggs-Distler 8c Co.. STURM; William (A 1944; 7 1940): Mech. Engr., A Inc.f;216 ;N; Calvert ,Sl. Baltimore, and #424 - EUerbe & Co.. 1021-E First'National'Bank . : - r.Winston Ave.';.Baltimore 12, Md: ` / " * / Bldg... St. Paul 1, and. 60/ Inner Dr/, -St. Paul te - STOLKERy Edward A. (A 1945).Owner,- Stolker 5, Minn. ' - ' . * -' A - 1 . '. McDonnell & Miller, 400-N.- Michigan Ave'.. , - Chicago ,11. -and #2746 Morse Ave., Chicago 45. III. . SWART.rHarvey G.- (A .1944) Salesman & Engr.. - 1 The Trane.Co., 2326 S. Michigan Ave.. Chicago ? - ' 16. and 525 Fairview Avei. Park Ridge. 111. ' SWASKI. Kenneth J. (A 1945) MMR l/c>. V . - Mat. 8t Eng. Bldg. 142, Box 10, N. O. B.. Norfolk/ ' Va., and #RL 1, Sweet Home, Ore. - - ... SWATS, William F. (A 1945) Asst. SupL of . Bldgs:. Vanderbilt Umversity. Dept, of Bldgs.. ` Nashville 4.' and 3304 Wimbleton Rd.. .Nashville . 5. Term; , . ' . ' 'SWEENEY, George J. (A 1945) Vice-Pres.' & - - ,, . Treas.V#Air Devices. Inc., 17 East 42nd. St., `.New York. ahd'35-54 93rd St., Jackson Heights, ' N. Y.v ' ' .= ' - .. ' SWEENEY, R. H. (A 1939) #1883 SUnford Ave.. J - St. Paul 5, Minn. . Y- SWENBERG, Walter A. (A` 1945) Chief Quarter ' ' "man, #,U..S.'Naval Drydocks. Long Beach, and ' 6129 Olivd St., Long Brach 5. Calif. ' - SWENEHART. D.W. (A 1940) Engr.. Cortland. -. . vOhio. ; - * 1 * ;- , . - SWEPSTON, Murray McGee (A 1945) Mgr. &. ; ; V - Pres- Atlas-Butler ..Furnaces, Tnc.; 243 N. Fifth :-' /-x St- Columbus 15. andl620 E: Broad St., Colum- ` '-' bus, Ohio,. .' ^vEngineerihg'.Co^ .4201. Brown St:. Philadelphia 4. /.ami 2601'Parkway 30/ Philadelphia. Pa. ' 'SUDDERTH,. Leo, Jr; (A 1942; 7 1936). Partner,' - Garrard, Sudderth & SeaL >313' -Bona' Allen - Rldg:,' Atlanta 3.- and*3047'Piedmoht Rd. N.E..-- - .SWINGLE, W. T. Conditioning Co., --.-s"tings, Nebr. (A 1938) Pres- Hastings Air ' Inc., T08 S. Colorado, Has- "Y Atlanta,^ Gsu- -V ` SULLIVAN, John R. (A 1944)'Foreman. U.; S." ' .Naval Air Material, Centre.- Navy -Yard,: Phila- : delphia, and'# 31-B Stephen CmirL MUbourne. Pa. . aK f -A 'SWISHER; Stephen.Gi; Jr.' (Jf 1936; A 19$4) - - Mgr.,`#Tbe^Trane Co:. 1835 N. Third St., Mil. watikee. 12, ahd.l711` E. Dean-Rd:.'.'Milwaukee. - ; Wis. ' * '* . , TAYLOR, Arthur R. (M 1942) Sales Engr., =. . C.-' Darling Bros., Ltd., and #617 Willard - Ave.. ` * Toronto, OnL. Canada. - TAYLOR, C. Ridgway (A 1944) Salesman,' Rose *_; ' .v Brothers Co.. Inc.. 1441 19th St'.', N..- Arlington,' *: . rX'- Va., and 1513 Meridian PI. N.W., Washington, . .. 7 .' 7.7. . D. . . ; -:A* TAYLOR, E. L. (7. 1945) JiStintoh Jones 8c V vtYf, % . Partners. 21 Gloucester PL, London' WI, - and.. 77 . -- 33 Willersley Ave- Sidcup, KenL England.' -. ` ^ - TAYLOR, Edmund P. (A 1945). SupL, /The, Buckingham-Routh Co., 64 Grove St/, New.."7 Haven, and 64 Long Hill Rd- Wallingford. Conn. " /' : TAYLOR," Edward M. (A 1934) Tech. Mgr.:.. . : - ` ` Taylors, Ltd., 32A Lichfield St., and 3 Waira-.- - . % ' rapa Terrace, Christchurch. New Zealand..- `tK ' - TAYLOR, Harold J. (M ,1937) Owner. Harold' *' J.Taylor. 17514Greenlawh Ave., Detroit21,-Mich. ~ ; TAYLOR, Reg. P. (M 1915), Cons.'Engr.i #9i0,'7 /? *': Bankers Mortgage Bldg.,--Houston 2, and"2332 /' - Watts Rd., Houston 5, Texas..'/-. - - vj TAYLOR, Robert B. (M 1944; 7 1938) Field Engr- ^ Buffalo Forge Co..-1303 Standard Bldg., . ' .Albany 7, and R.-F. D.,Slingerlands'. N., Y. - /-' . . r- :a- TAYLOR, Thomas E. ,(M 1942; 7 1937> Mech.:.- A . Engr., 707 Spalding Bldg., Portland 4', and 7307. *: -'.- N. Wall SL. Portland 3; Ore. V / , ..7- 7 , l -Cc- 7'-. TAZE, D. L. (M 1931) Branch Mgr.,-#'American' ' * - /- -' . v. Blower Corp.. 1302 Swetland'BIdg., Cleveland l5, / 'aiid 3600 Sutiieriaud Rd- Suaker Heights22, Ohio.' / /.</ _ - TAZE, Edwin H. (JI1937) Branch'Mgr.,/# Ameri- '.. ' can' Blower ' Corp., 620 Court* Square';'"Bldg.,7^ Baltimore' 2,- and 208 Bosley - Ave/, /Towson."' Baltimore 4, Md. ' . 4 ;- 'l- 7 ^ 80 - -* . Heating Ventilating - Air ] Conditioning . Guide.1946 TEASDALE, Lawrence A. (Af 1926) Mgr.. Div. THOMAS, R. L. (A 1943) Field Engr.. Fair- ot-Htg. & Lighting.>Yale University Service banks-Morse & Co., 13th & Liberty, Kansas City,- Bureaus, 20 Ashum SL, and 261, Canner St., Mo.. and R. R. No. 2,-Lawrence, Kans. - . .New"Haven 11,'Conn. "- . * ` THOMPSON, Albert E: (A 1945) Branch Mgr., TEELING, George A. (Af 1930) .Cons. Engr... Matthew Hall & Co.. Ltd., 26 West Nile St., Glas- -- 1' Columbia PL, Albany 7, and Box 81, Clarks- . gow. C. 1, Scotland, and 277 Brampton. Rd., vil!e.-N. Y. . ., * Bexleyheath. Kent, England. r '' TELGEMEIER, A. H. (A 1944) Vice-Pres., THOMPSON, Edward B. (A 1938) Owner. -Southern Oil Co.. 3016^ Wyoming, and *2307 E. . Covington Heating Co., 326 Pike St., Covington: Mayer Blvd., Kansas City. Mo.' - . Ky., and 1198 Coronado'Ave., Price Hill, Cincin TEMPLE, Walter J. (Af 1931) Engr.. Mgr., J. A. nati 5, Ohio. -* . Temple"Co., 108 Pkwy.,- Kalamazoo 3, and 1216 THOMPSON, Frank (Af 1935) Factory Mgr,, ..Reed Ave., Kalamazoo 24, Mich. The Canadian Fairbanks-Morse. Co.. Ltd., 62 TEMPLIN, Charles L. (Af 1921) Pres., Carrier Belvidere St., and 107 Quebec St., Sherbrooke, s- Atlanta'Corp.,- 306 Peachtree St. N.E., Atlanta 3, Que., Canada. - and 781 Sherwood Rd. N.E., Atlanta, Ga. - THOMPSON, Harold D. (A 1945) Chief Engr., TENKONOHY, R. J. (Af 1923) Mech. Engr., Chas. W. Cole & Son, 220 W. LaSalle St.. South . Episcopal HospitaL- Front .and Lehigh. Phila delphia. Pa. -- . Bend, and.* 1105 Harrison St:, La Porte, Ind. THOMPSON, John (M 1942) Administration TENNANT, Raymond J.J. <A 1929) Chief Engr., Building Engr., Hydro-Electric Power Commis- ^Kttsburgh -Business Properties. Inc., 2237 . sion of Ontario,'620 University Ave.;'Toronto 2, Oliver Bldg., Pittsburgh, Pa. " TENNEY, Dwight (M 1932) Cons.. Engr.. *c/o and 62 Browning Ave., Toronto 6,-Ont., Canada. THOMPSON, Nelson S.* {Life Member; M 1917;. Herman Fraser, 434 Vidal Dr., Park Merced Apt., ' 7 1897) Retired Engr., 3206 Oliver St. N.W., San Francisco 12, Calif. . . ' Washington 15, D. C. .- TERHUNE, Ralph D. (A- 1936) Dist. Mgr., THOMPSON, Paul J. (A 1944) Branch Mgr., Bryant Heater Co'., and 277 Orchard Pl., Ridge - National Radiator Co., Room 236/401 N. Broad . wood, N. J: . '' . SL, Philadelphia 8, Pa., and Morris Ave., Luther TERRANCE, Emmett H. (Af 1944) Engr. & ville, Md. * ; "* Dist; Mgr., *.Canadian Sirocco Co.. -Ltd.. 630 THOMPSON, Roland J. (A 1945) Marine Engr., Dorchester. St. W. 2, Montreal, and 430 Willow- Navy Dept..* Bureau.of Ships, 16th and-Consti dale Ave., 'Apt. 23. Outremont. Que., Canada. tution Ave., ' Washington 25, and 5220 N. TERRY, Matson C. (M 1936) Chief of Air Cond. - Capitol St., Washington 11, D. C. ' * . ' Engrg., Philco Corp., Philadelphia, and Cloverly- THOMPSON, William D. {M 1944) Mgr.. Indus. Lane. Abington; Pa. ' TERRY,* Samuel W. (Af 1941) Pres., Aladdin; ' Div., Laclede Gas Light'Co., 1017'Olive St., St. Louis 1, and 306 N. Woodlawn, -Kirkwood, Mo;. - Heating Corp., 2222 San-Pablo Ave., Oakland 12, THOMSEN, N. B. {M 1938) Vice-Pres.; Mac 'and 2820 Oak Knoll Terrace, Berkeley, Calif. donald Engineering Co., 188 W. Randolph St., -TEVERBAUGH, Jack E. (7 1945)' Jr. Engr.. Chicago. 1. and 6101 Sheridan' Rd., Chicago, 111. -. Carrier Corp.. 20 N. Wacker Dr., Civic Opera THOMSON, Thomas N.* {Life Member; M 1927). .Bldg.,*Room 2200,^Chicago 6, 111. . THACKER, JohnE. (Af 1944) Htg. & Vtg. Engr., Consultant, *37 Irwin PL, Huntington; L. I.', N.Y. THORNBURG, Harold A. (Af 1932; J 1929). Vauxhall Motors, Ltd., and 112 Strathmore Cons. Engr. for Air Cond. & Refrig.. .U. S. Rubber .. Ave.*, Luton, Bedfordshire, England. . Co.', 1230 Sixth Avk.. Room-1001, New York, and THAYER, Harding H; (A 1943) Partner. *The 1911 Dorchester Rd., Brooklyn, N: Y.. ' ' *. Thayer Co;, Greer. Bldg.; and 304 Hazelcroft THORNTON, Thaddeus L, (M l937) 37 Perry . Ave.. New Castle. Pa.' " . .. THEISS, Ernest S. (Af 1944; A 1941; 7 1940) St.. Belleville 9. N. J. ' *-.- THORPE, Wano E. {M 1943). Mech. Engr:. . Ask. ' Prof., Mech.- Engrg., Duke University, 'College Station, and *2645 University Dr., .Dur- . ham. N. C. ' THEOBALD, Art (if 1945; A 1937) Engr., Payne - Hanker & Heyer, 10th Floor-Commerce'. Title Bldg., and 1779 GIenview.Ave..-Memphis/Tenn.' THRUSH, Homer A. (Af 1918) Pres., H. A. Thrush & Co.. 21 E. Riverside Dr., and 159 W. -Furnace Co., 336 N. Foothill Rd.. Beverly Hills, Main St., Peril, Ind. ' .* ' . - and 116J4S. Kings Rd.. Los Angeles. Calif.. THEORELL, HugoG. T.* {Life Member; M THULMAN, Robert Kelley* {M 1938); Mech.Engr., Federal Housing Administration, Vermont "1902). Cons.' :Epgr/, Hugo.Theorells Ihgeniors- and K Sts. N.W.. Washington, D. C.. and 6505 -byra, Skoldungagatan 4, Stockholm, Sweden. * Ridgewood Ave., Chevy Chase, Md: - -. ; THINN, Christian A.* (M 1921) .Mgr. of Service. ' Cl A. Dunham Co.;450 E. Ohio St., Chicago. 111.. THOM.Herbert C; S. {M 1944) Sr. Meteorologist, ` -Ul'-S.-Weather' Bureau. Des Moines, and *227 N. t .Sheldon Ave.; Ames, Iowa. ` , . * . THUNEY, F; M. (A 1939; J 1936) Exec! Engr.; Minneapolis-Honeywell Regulator-,,Co., -1101- Vermont Ave. N.W., Washington 5,'D. C. ; TICHENOR, LesUe R;t Jr. (A 1942) c/o L. R. Tichenor & Son, 2 Ridgway Ave.,-"Hillside,'N.-J. -THOMAN, Estell O. (A 1938) Air Cond. & Htg. TroMARSH, Patrick M: {M 1938) ^Gen. :Mgr.; " Kngr-', Higgins-Industries, Inc., 521 City Park . Tidmarsh Engineering Co., P. (L Box 2425, . Ave./ahd 2134 Selma Dr., New Orleans. La. * Tucson, Ariz. -. ;;THOMAS,'Benjamin F,, Jr. (Af 1945) Mech.- TIERNEY, Lawrence J. J. (A 1942);Owner. L."J. /Elec. Engr.,-Morah, Proctor, Freeman & Mueser, Tierney Cd,, 10 High St,, Boston, and 17 Oriole > 420 Lexington Ave., New York 17, N. Y., and 169 St., West Roxbury, Mass. . '` -/ * - -Grund-Ave., Englewood, N. J. -* . TIERNEY; L. Foster (A 1945) Mgr., Mulch THOMAS,- Bernard A. (A 1938) Mfrs. Agent. Brothers/ 200 .Bedford St., and 301 Pine. St.;.- e'405'E. Idlewild Ave., Tampa 4, Fla. . . . Hollidaysburg, Pa. ' *.* . THOMAS, Ernest R. (M 1942) Mech. Engr.. . TIGNOR, William L,, (A-1945) Service Mgr., ` Dale S.` Cooper.&; Assocs., 206 West Bldg., and Roosevelt Oil Service, 601 W;` Philadelphia/St.r* -:*3001 Quenby, Houston,'Texas.* . THOMAS,-Frank M. (Af 1943) Dist. Sales Mgr.. . Oklahoma Natural Gas Co.. 217-W. Randolph, . and 423 S. Pierce, Enid, Okla.* - - ' and 521 Linden Ave., York, Pa.- TILFORD, Leo A.-(M 1941) Owner`& Mgr., Leo A. Tilford Co.. 1230 Frances SL. Jackson 2; Mich.. - THOMAS, Glegge {M1936) Office Mgr., *Clarage . -Fan Co.. 723 Albee Bldg., Washington, D. C., and -7 W; Leland St^-Chevy Chase. Md. TILLER, Louln (A 1935; 5 1933) Engr.. . Velo- city Steam. Production Engrg., 38 S. Dearborn ' St., Chicago 3,` 111. .- T ' * " -THOMAS. L.- G.. Lee . (Af 1934). Vice-Pres., TILLOTSON, John'J. {J 1943)' Predpitron,Ser - -- Economy Pumps, Inc., .1000. Weller Ave., Hara- vice Supvsr., B. -F. Sturtevant -Co., Div. - of ;llton, and 765 Ivy Ave., Glendale, Ohio. - Westinghouse Electric Corp., Hyde Park. Boston, THOMAS. Melvern.F. (L*/e. Member; M 1909) -Mass., and 2057-Meadow .View Rd., Westfidd; f- ConsT-Engr., 7.4'Rivercrest Rd.; Toronto, Ont.,' n. j. " . ' " / ' - v " ` ' - v -Canada. -*- . *- -- - - TILTZ, Bernard . E. {M 1930) Pres.. Tiltz Air `THOMAS,; Ralph- Cr (A 1938) Thomas Air Conditioning Corp.. 230 Park Ave.-, New York, ^.Conditioning.Tnc.,' 819 Weistover Ave.,'Norfolk - and'22 Villa Rd., Larchmont'/N. Y. r,-.va:v- : : TIMMERMAN,. Walter C.\ (M 1945) ParUier, . TH6MAS,,R/ H; {LifcMember; M 1920) Pres. Thermal Engineering-Co.*, 2605,-W. Dallas>SL; - Treas/Economy Pumps,.Inc.,.1000 WellerAve.;. * Houston, and 6340-Vanderbilt St.,-Houston-5,- Hamilton;-and *765 Ivy Ave., Glendale, Ohio: . Texas/' . 'r Jr-.-' * '* rRoll of Membership 81 TIMMINSrW. W. (Mr1941) Dist. Mgr., Cana dian . Powers Regulator Co.,. Ltd., .University Tower Bldg., Montreal, and 305 Brock Ave. N.,' ` Montreal West, Que.', Canada. * TIMMIS, Pierce {M 1920)-Indus. Engr.; United ' Engineers & Constructors, Inc., 1401 Arch St.. Philadelphia 5, and 202 Midland Ave., Wayne, Pa. TIMMIS, William W. (M 1933; A 1925) Comdr.. U. S. N. R,, Bureau of Ordnance, Washington, D. C., and' 103 Geo. Mason Dri, Arlington, Va. TOBIN, John F. (A 1934) Field Engr., American Blower Corp., 228 N. LaSalle St., Chicago, and 11256 S. Artesian Ave., Chicago 43. 111. TODD, Malcolm McM. (M 1942) Owner, Mal- ,, colm Todd, 302 Bay St., and 34 Halford, Toronto, Ont., Canada. TODD, Meryl L. {M 1940; J 1936) Partner. Todd, Hedeen & Assoc., 180 W. First SL/.and 100 Highland Blvd.,. Waterloo, Iowa. * TOENSFELDT, Ralf {M 1940) Cons. Engr., 411 Security Bldg.; St. Louis 2, and 6311 Waterman Ave.. St. Louis 5, Mo.- ' TOLERTON, Hill A. (A 1944) Contracting Engr., Lee Engineering Co.. 1102 Union National Bank Bldg., Youngstown 3, and 272 W. Tenth St., -Salem, Ohio. . TONRY, Robert C. (M 1936) Mgr., Wiede- buscb Plumbing & Heating Co., 511 First St., and Fairmont. W. Va. - .- TREFTS, John CJ, Jr. . (M 1944) Vice-Pres., Farrar & Trefts, Inc., 20 Milbum St`,, Buffalo > 12, and East Quaker Rd., Orchard Park,- N. Y. TkENHAELE, Dale T. (7 1945) Mech. Engr. . (P-2),. Ind. Design Sect., VenL Grp.. Pearl Harbor Navy. Yard, Pearl Harbor, T. H., and 2190 A Helumoa Rd,, Honolulu 20, Hawaii. ~ - TRICKEY, George (A 1945) Sales Engr.*, Pease Foundry Co., Ltd., 227 Victoria St;, and * 97 Oakwood Ave.. Toronto, Ont., Canada. - TRICKLER, Earl E. {M 1942) Chief Engr., New York Blower Co., 3155 Shields Ave.,- *8219 Kenwood Ave., Chicago 19, 111;/ TRIEGEL, Erich V. (Af 1942) Mech. Engr.. Francisco & Jacobus, 511 Fifth Ave., New York. N. Y., and *R. F. D. 3, Danbury. Conn. TRIGGS, Fred E. {M 1938) Mfrs. Agent, and 3901 Second SL, Des Moines 13, Iowa. .* TRIMBLE, John I. (Af 1945) Mgr., Janitrol' Engrg., Surface Combustion Corp., 400 Dublin Ave., Columbus, and *2038 Bedford Rd., Colum bus 8, Ohio. - * * .- TRIOL, Edward W. (A 1945) Draftsman, *C. W. May, 1430 Vance Bldg.. Seattle 1, and 9514 42nd N.E., Seattle 5, Wash. - -- TROLLER, T. H.* (Af 1943) Cons., La-Del Conveyor & Manufacturing Co., New Phila delphia. and 1250 Sunsetview Dr., Akron 2/ Ohio. * TOONDER, Clarence L. {M 1933) Mech. Engr.. TROSTEL, Otto A. (Af 1935) Engr., Standard . Plant Engrg. Dept., Diesel Engrg. Div., General Distributing Go., 406 E/Wells St., Milwaukee 2, Motors Corp., and 13391 Marlowe, Detroit, ' and Route 2, Thiensville, Wis. - ... Mich. * ** * - TROUP, John D. (Af 1938) Managing Dir., TOROK, Elmer {M 1936) Pres., East Tennessee . Sheet Metal Works, Inc.. P. O. Box 541, BristoL ' and 203 West G St., Elizabethton. Tenn. ' * TORR, T. W,.{M 1933) Chief Engr., The Rudy . Furnace Co., and 205 Green SL, Dowagiac, Mich. TORRENS, George B. -(Af 1945) Mech. Engr., The Jennison Co;, 17 Putnam St., Fitchburg, and John D. Troup, Ltd., 90 High-Holborn, London W. C. 1, and 48 Plough Lane, Purley, Surrey.. England. *' - TROWBRIDGE, Carl Y. (A 1944) Secy.-Treas. & * Gen. Mgr., Ray F. Fischer Co., 323 N.W. Tenth SL, Oklahoma City 3, and 3420 Northwest 25th St., Oklahoma City, Okla. - 250 West St., Leominster. Mass. ' * - TRUMBO. S. M. (A 1926) Engr.. Buffalo.Forge TOULOUKIAN, Yerara S. (7 1944; 5 1939) Co., 20 N. Wacker Dr., Chicago 6, and 921 Frank Research Fellow, Purdue University, ana Varsity lin St., Downers Grove, 111. '- Apts.. Apt. 300, W.-Lafayette, Ind. TUCKER, Frank N. (Af 1926) Field Engr.. Ilg TOUPIN,-Valerien (if-1944) Htg. Engr.,' Muni Electric Ventilating Co.. 13 Park Row, Rm.-ll,. cipal Bldgs. Dept., City-of Montreal, 720 De New York, and *239 Whaley St., Freeport;* FleurimonL Montreal 10, and 2186 Souvenir-Ave., L. I.. N. Y. . , Montreal 25, P. Q., Canada. - TOUTON, Rush D. {M 1933) Tech. Dir;, Bayuk . Cigars, Inc., .Ninth and Columbia Ave., Ptula- - delphia 22, and. 624 Montgomery'School Lane, Wynnewood.-Pa. * ' ' TOWER, Elwood S. {M1930) Engr.. 213 Invest ment Bldg., Pittsburgh 22, and 1422 Whiteman SI.'. Pittsburgh 17, Pa; - TUCKER, Leonard-A. (Af-1935) Service Mgr., J-. J. Pocock, Inc,, 1920 Chestnut SL, Philadelphia .3, and *220 Buttonwood Way, Glenside, Pa. > TUCKER, J. Robert (A 1945) Engr., Testing & Research, United States Testing Co., Inc., 1415 Park Ave., Hoboken, and 86 Bergen Ave., Teaneck, Ni J. . TOWNE, c. 0,.(A 1945) Sales Engr.. Clowe & TUCKER, Sydney (Af 1945) Chief Engr., Fitz- Cowan, Inc., P. O. Box 551, and 4010'Harrison St., AmariUo,' Texas. *- ' - gibbons Boiler Co., Inc.,-and 247-W. Sixth^SL, Oswego, N. Y. ' * . TOWNE,. Robin M. M. (7 1945) Office Asst., ^TUCKER, Thomas T. (Af 1938; A 1936)* Chief Heating Service' Co., 326 Columbia St., Seattle, Engr., Armor Insulating Co., 800 Forrest St. . and 4020 East 135th, Seattle 55, Wash. - N.W., and 3619 Ivy Rd. N.E., Atlanta. Ga. . < TOWNER, Charles E. (A 1944) Testing Engr., - Crane Co.,' 836 S/ Michigan Ave., Chicago, and ' * 9141 S. Mayfield, Oak Lawn, 111. TOWNSEND, John. M. {M 1942) Air Cond. Div., Servel, Inc., Evansville 20, Ind. - TUCKERMAN, George E. (Af 1932) Special Repr., Air Cond. & Refrig. Div., Worthington.- Pump & Machinery Corp., 2905 N. Broad St.,' Philadelphia 32. and *502 Rodman Ave., Jenkin- town, Pa. *- *. . - .*- * TRACY, John W, (M 1945) Sales Engr.; Minne apolis-Honeywell Regulator Co., 415-Brainard'SL, .Detroit 1, and 18687 Pennington Dr.,* Detroit 21, Mich. . .... . , TUPPER, Edward B. (7 1944; S 1941) Refrigera- .tive Supply, 2211 Fifth ` Ave., and *623l-^4th* N.E., Seattle 5, Wash. - .. . ' *.' TURLAND, Charles H. (Af 1934; A 1930) Sales TRACY. William E. (A 1943 ; 7 1938) Lt. (j.g.), ' Engr., R. E. Johnston Co.', Ltd., 1070 Homer. U. S. N. R. (Present address untaown). . St., and 4553 W. Third Ave., Vancouver, B. C:,. TRAMBAUER: Charles W. (M 1945; A 1941; 7 Canada. - . -r '* '. ~ ,-J 1936) Project Engr., Kelly Field Air Base, San * TURNBULL, Fronds J. .(Af.. 1945) Engr., Fay Antonio, Texas, and 179-17 134th Ave., Spring- Spofford & Thorndike, 11 Beacon SL, Boston, and' 'field Gardens 13, L.I., N.Y. , .. - - 625 Pleasant St., Milton 86. Mass. ' *''. TRANE. Reuben N.* (Af 1915) Pres., The TURNER, Edmond S. (A 1939) Partner; e Wil-; Trane Co., 208 South 15th St., La,Crosse, Wis." .. .liam S. Turner & Co., -Pacific Bldg.,- Portland 4/ ' TRAUGOTT,' Mortimer (A 1930) Bryant.Air and 3455 Northeast 36th Ave., Portland'13, Ore., ** Conditioning Corp.. 915 N. Front SL,' Philadel phia -23/ and 8208 Westminster Rd., Elkins. -Parki Pa. .1 . TRAUTMAN, Fred L, (Af 1944) Owner, *Traut- TURNER, George G.- (A 1945) Western -Mgr.-r- eHeating & ventilating Magazine,' 228* N. LaSalle SL, Chicago 1, and'827 Hinman Ave-, ' Evanston, 111.: ?./- ' . . * . man Engineering-Co,, . 1122 East-. 17th Ave.. -TURNER, George W. (Af .T944)'e 1560, Mt- -Denver, Colo. - - ;*..*' . Vernon S.E.,.Cedar Rapids, Iowa: ' -. * ' - TRAYNOR,-Harry S. (A 1912;.7 1937) Mgr.. TURNER, John,r., Jr. (Af 1942)'Mgr., Ceutrai -Regent Knitting`Co., 219 Washington Sq:,-Syra- " Dist:, Air Cond."Dept., General'Electric Co., 106 cuse. and 137 Edwards Dr., Fayetteville;-N. Y. - West.14th SL, Kansas City 6, Mo.-- . *.. **..; ".* TREADWAY, J^ Quentin (A 1936; 7 1932) DisL- TURNER,.William M, (A *1945) Supvsrg.- Engr-/- Sales ' Mgr/, Clarage Fan Co., '.210 -Reynolds. The Ripstra Co., 1015 E. Douglas, and'*4802 E: .-Arcade, and826 WlnonaBlvd.7Rochester,-N. Y. . _ English, Wichita, Kans. * /.. - Y "S K-t"O. .'5^ _ .A'- r |. - n; , Y -C*.JY #2 .Heating -.Ventilating Air ConditioningGuide-1946... * ' TURNO, Walter G. W. (Af 1917;A 1912) Secy.. .v - - ; - i H. W. Porter & Co.. Newark,- and #71 Lafayette ' Ave.. East'Orange. N. J. *. . VALE, Henry. A. L. (Af 1929) Managing Dir., ' TUSCH, Walter (Af 1917) Retired. *881 Sterling Vale Co., Ltd., 141-143 Armagh SL, Christ PL. Brooklyn 16. N. Y. - church, and 203 Liam Rd.. Fendalton, Christ- ` TUTHILL, `Arthur P. (7. 1940; 5 :1938) Lt.. church. New Zealand. ' ' . > A. A. C.. C- C. S.. C. A. A. F., Clovis. N. M.. and VALIOUET, H. H. (A 1944) Vent. Engr., Em * Cutchogue; L. I., N. Y. . - . \" - ployers Mutual Liability Insurance Co. of Wis TUTSCH, Rodney J. (A 1943; 7 1939) In Service. ' consin, Milwaukee 12. and *2630 N.- Humboldt* and *4455 N. Oakland Ave.,'Milwaukee, Wis. . " Ave.. Milwaukee, Wis. .: TUTT, Richard D. (7 1942) Chief Engr., Tuttle VAMOS, George (Af 1944) Cons. Engr.. 12' & Bailey, Inc., and Bor'516, New Britain, Conn. Blakey Ave., Wellington W. 3. New Zealand. TUTTLE, Arthur A. (A 1944) Service Mgr.. VAN ALSBURG, J. H. (Af 1931) Sales Engr.; Holcomb & Hoke Manufacturing Co.*. 1545 Hart & Cooley Manufacturing Co., and R. F. D.' .. Van Buren St., and 1023 Berwyn St., Indiana-. 6, 728 Park Rd., Holland. Mich. .. , - pblia. Irid. - . ' VANCE, Louis G. (Af 1919) Mfgre. Agent,' 23 ' - TUTTLE, G. H.* (Af 1937; A 1936; 7 1934) Plant . . .West 21st SL, Baltimore 18. and *4402 Maine . ' ' .Engr., The Detroit Edison-Co;, 2000 Second Ave., Forest Pk., Baltimore 7, Md. . - ` : . ' Ave:. and-16714 Kentfield, Detroit, Mich. VANDAMENT, Dan D. (A 1945) Mech. Engr., - ;;, TUTTLE;' J. Frank (Life Member; M 1913) Sales Navy Public Works Dept.. Treasure Island, and - Agent. Warren Webster & Co.; 127 Federal St.. ' *432 Worth St., Oakland, Calif. Boston, and 9 Lewis Rd.. Winchester, Mass.. VANDERHOOF, Austin L. (Af 1944; A 1933) . - TUVE, G: L.* (M 1932). (Council. 1939-41; 1944 DisL-Repr., Warren Webster & Co., 233 Hanna . - 45) Prof, of Mech. Engrg., Case School of . Bldg., Cleveland, and 2762 Landon Rd., Shaker v Applied Science.-10900 Euclid Ave.. Cleveland 6, Heights, Ohio. -' ' . ' .- - and 2510-Newbury Dr., Cleveland Heights 18. VAN NOUHUYS, H. C. (A 1942; 7 1937) CapL. . Ohio. ' - ' ' > - ' ' - U. S. A., c/o Production Engineering & Review _ TUXHORN; D. B. (M 1936) Asst. Chief Engr.. Staff of Engineering Div., A. A. F: Watson Labora ' Orr Sembower. Inc.. Morgantown Rd., tories, Red Bank, and *95 Seventh Ave., Long , , Reading,-. Pa., and 4853 Sedgwick St. N.W.. ' 'Branch, N. J. - ^ V- ' Washington, D. C. ' - ' VAN WAGENEN. Edward (Af 1945) Mech. Engr.. . : ' TWIST, C. F. (Life Member; M 1921) Retired. U. S. Naval Air Station, Jacksonville, and P. O. - '. and 2310 Tenth Ave. N., Seattle 2. Wash. Box 162, Green Cove Springs, Fla. : TWIZELL. -E. W. (Af 1937) Partner. Connolly VAN WEELDEN, Morris'J. (A 1945) Mech. Engr., ,, & Twizell, Ltd., 1405 Bishop St.. Montreal, and 22 Illinois-Bell Telephone Co., 208 W. Washington Merton Crescent, Hampstead. Que., Canada. ' * i St., Rm. 1501,- Chicago 6, and 7339 Lunt Ave....... -TYDINGS, William F. (Af 1942) Owner, Chicago 31, 111. - ` ' -...... Tydings Engineering Co., 16895 Lahser Rd.. ; VAN WYNGARDEN, J, E. (A 1940) Owner. ....... Detroit 19. and 26540' Lyndon .Rd., Detroit Day Heating Co.. 863 N. Liberty-St., and 945 23; Mich. . N. Church St., Salem. Ore. - - ' . TYKLE, Frederick G. (Af 1943) Dir. of Real VAN ZELM, Henri B. (Af 1945) Cons. Engr.. 11 . V Estate, General'Motors Corp., Research Bldg., ' Asylum St., Hartford 3, and 40 Robin Rd./West Detroit, Mich., - ' Hartford 7, Conn. . . '' / TYLER, Roy D. (Af 1928) Chief. Facilities Engrg. . VAUGHAN, Lilllad L. (Af 1938) Prof, of Mech.. . ' Section, U: S. Armed Services,. Boston Ordnance. Engrg., & Head of Dept.. North Carolina State : Dist., 140 Federal St.. Boston 10. and *408 College, and 11 Enterprise SL, Raleigh'. N. C. Beacon St., Boston 15, Mass. . - . VENNEMAN. Justin' B. (7 1945) Project Engr.. Utility Appliance Corp.. 4851 S.' Alameda ,St.. ' ,U '" -Los Angeles 11. and *3500 W. Santa Barbara. Los Angeles 43, Calif. - . ' "` UHL, Edwin J; (Af 1925) Partner! Uhl Co..' VERAZA, U. Carlos (Af 1945) Mgr.. Madrigal y " J-` 132 S.. Tenth St., and 4830 Pleasant Ave. S., Veraza S. de R. L., Donato Guerra'No. 1 desp. V . -Minneapolis, Minn., I - ` 308, and Carpatos No. 520, Lomas de Chapultei>ec,-- - - 7 . UHL, Willard F. (Af 1918)* Uhl Co.', 132 S. Mexico, D. F. -' - * - '.Tenth St., and 4716-Lyndale Ave. S., Minne- VERITY, Elbert W. (Af 1944) Pres., Almirall ' V` apolis, Minn.- ` - ` ` ' &Co., Inc., 53 Park Place, New'York 7, and 27;. ' / . UHLHORN, W. J. (Af 1920) *733 S. Highland Wensley Dr.. Russell Gardens, Great Neck; N. Y. , . `' Avel, Oak Park. 111. " . . - VERNON, Rex (Af 1928; A 1926) Sales Promotion. - UICKER, John Joseph (Af .l944) Acting; Dir.. *- ' '-Mech. Engr. Dept., University, of Detroit,. Mgr.. Johnson Service Co.. 507 East Michigan St'., -Milwaukee 2, and 710 Oakland Ave.', Waukesha, - McNichols Rd. :at Uvemois,`.Detroit 21. and - Wis. .- ' . - . '. . *16261 Littlefield Ave., Detroit-27, MicH. . VERVOORT, Edward L; (A 1946/7 1937; S1936) ULLRICH, A.- B., Jr. (Af -1944) Sales 'Engr.. . Gilbert Engineering Co., 1305 Liberty Bank Bldg., ' ' -Dallas, and *715 Lipscomb St., Dallasyl4, Texas.- Lt., U. S..Navy, House Htg.- Supervisor, Brooklyn- Union Gas Co., 180 Remsen SL,-.Brooklyn, .and-. . *49 Arizona Ave., Rockville Centre, L. I., N. Y.. ' UNDERWOOD, George T. (A 1944) Chief Purch. , ` Agent,-Federal PublictHousing Authority, Long . VETLESEN, G. "Unger U. S. Navy, Overseas. (Af 1930) LL .Cdmdr'... / and*l; Beekman PL, - . . fellow Bldg.. Washington,-. D. . C., and 1602 -New York, N. Y. * . - - ' , .'. / -Ripon PL. Alexandria, Va. -- - VIA, Clarence W. (A 1943) Owner. Engrg. Sales ' . UNDERWOOD, John L. (A 1944) Owner. *John - - ;`L. Underwood. Co.; Atlanta'S, and'1680 139 Edgewood Ave. S.E., Johnson Rd. N.E., Atlanta. Distr., Manufacturers. Exchange Bldg., Kansas City 6. Mo., * and Lake of the Forest .Club, ` Edwardsvillei Kans.. -. ` -- y - -"~v . Ga.' 7 " -. - ' UPDEGRAFF; Lee (Af 1944) Owner, Franklin ^-'Engineering.Co.,-'406 S/Mairi, Los.Angeles 13, . and 3017 Fall Ave.; Los Angeles 26. Calif. VINCENT, Harvard B. (Af 1944)= Mgr., Product ` Dvlpt...Owens-Illinois Glass Co., Insulux Products: Div., P. O. Box 1035-36.-Toledo l. and*3840.- , Sulphur Springs Rd.. Ottawa Hills, Ohio.* * . : ' URBAN,-Frank F.` (A 1939) Vice-Pres.. Urban Plumbirig& Heating.Co.,:l215 S:W. Fifth Ave.. .-.a Portland, and*6726 S.W., Burlingame'Ave..; VINCENT, Paul J. (Af 1931) Chief. Engr.-Owner/ *Paul J. Vincent Co.. 2208 Maryland Ave.,>202 * St. Martins Rd., Baltimore 18/Md. - ` '".''--Portland l.IOre. / . . '. . VINSON, Neal-L. (A 1946; 7 7936; 5. 1932)`1st ' URDAHL. Thomas H. (Af.1930).-(Council. 1940- - Lt.. Army Engrs., and Box 3007.. Lowell. -Ariz.; ..:>-;45).'Capt.-. UrS. .N' R.. and *2929. Connecticut ; VINTHER, P. N; (Af 1945) Owner; Zumwalt ' , Y'v-Ave/N.W.'T Washington8/D/C. , ` - & Vinther, 1807 Mercantile Bank Bldgi. Dallas l, - Y URMSTON, Benjamin S. (Af 1944). Chief-Engr. . and 3601 Shenandoah, Dallas 5; Texas. 1 -&-Mgr.. *Air Cond. Div.."Leidy -Electric Co., 201 VIRRILL, George A. (A 1940) Chief Engr.. The * O'^'Broad^St'..' .'Phillipsb'urg,.. N._- J.'./and e Apt.' 6. University Club, 1 West 54th St.; New York;-aud' * Y ;-t PackafdApts.. Easton, Pa.*/ . * ^ . ' - *345 Washington Ave., New Rochelle, NY.1- .^-USHER, Wellington J.. Jr. (Af ,1942)Sales Engr.. VISINTINE. Edward C.'(A-1944) Owner & Mgr.; Arthur^S:/Leitch -Co.; Ltd..- 1123 Bay St.,- Madison Plumbing & Heating Co., 31W. First.. /' *y \ -Toronto, and Ri-R. 2; Pickering', Ont.; Canada. _ St...and 51 Elm St.; London, Ohio.' - --V ' \-tffRoll of I\fem_b>ership' .83 . . ' - VTTALI, Oreste J. (A .1944)= Htg. Contractor, WALDON, Charles, Di. (A -'1932) Inventor, - - Unitejl'Engineering Co.; -*.4811 Ashoff PI.,-North. . : Vacuum Smoke. Condenser, 32. Femdaie Ave.', - Bergen, N. J. - v--- ` . ..r -. . *r Toronto, OnL, PanaHa ~ - / VIVARTTAS. E. Amold-(Life.Member; Af'1910) - WALDON,.0.;D.. (A 1944) Mfrs. Repr.. McDoh- : . - Mech. Engr., 26 S. Portland Ave., Brooklyn nell'& Miller,'-and *5915 Norwaldo-Ave.,'IndL -- 17. N. Y. ' - - - .* anapolis, Irid.'* ' /.' * . ' . VOISINET, Walter E. (Af '1930) Mfre. Repr. in WALDREP, James E. (A 1943; 7 1939) Engr., . - . ; . the Buffalo' Territory,- 250 Delaware Ave..* S. A. Brown Plumbing & Htg; Co.. Rome General '' , Buffalo 2. N. Y. , Hospital, and *1209-Magnolia Ave., Rome. GaY .. ' VOLK, George H. (7 1942; 5 1940) eThomas E. WALDSMITH, Earl C. (A 1944) Sales Engr., , ; r ' ' ' Hoye Heating Co., 1906 W. St. Paul Ave., Mil - waukee 3, Wis. . Hughes Machinery Co., 4034 Broadway, - arid 4917 Woraall Rd., Kansas-City 2, Mo. ' - - VOLK, Joseph- H. (Af. 1923) Pres. & Treas., WALFORD, L. C. A. (M 1938) Mech. Engr... , Thomas E. Hoye Heating Co.. 1906 W. St.'Paul G. Lome Wiggs & Co., Crescent Bldg...Montreal, * - ` - -Ave., Milwaukee 3, and 4416A-W. Oklahoma and 349 Brock Ave. N., Montreal W., Que.,' -v Ave., Milwaukee. Wis. . Cariada.- ' .- . - , VOLKHARDT, Aquila N. (Af 1938) Owner. WALKER, Edmund R. (Af i934) Vice-Pres. & . ` ri A. N. VolkhardL 942 Bay SL, Staten Island 5, Gen. Mgr., Fedders Manufacturing Co.r Inc., 57- ' . - and 104 Townsend Ave.; Staten Island 4. N.'Y. Tonawanda SL, Buffalo 7, and *365 Brantwood . ' , .. VOLLMANN, Carl W;. (Af 1938) Pres., Manu- Rd.. Snyder, Buffalo 21, N. Y. '' ',/ .* : - .. 1 ... facturer of Refrigeration Equipment, Linde Can WALKER, J..Herbert* (Af 1916) (2nd Vice-Pres., ' - . / . adian Refrigeration Co..-Ltd., 355 St. Peter St., 1941) (Couridl 1925, 1933-41) Vrce^Pres.,.* The;* . .` Montreal/ and 517 Roslyn Ave., Westmoimt.-. Detroit Edison Co., 2000 Second Ave., Detroit-26, . '. . ` P. Q., Canada. . ' and 432'Arlington Rd.; BirTntngham/ Mieh, ^ ' - ' '- -. VON KAMP, N. H. (A 1945) Plant Engr., Bendix- WALKER, Kirby (Af 1944) Chief Engr., Ameri- '' . - ...Westinghouse Automotive Airbrake Co., and * 270 - can Gas Machine Go:, Albert Lea, Minn. `*-. ' ,' .. Pasadena Ave.. Elyria, Ohio. ' r- ' - WALKER, Leroy S. (A 1945) Owner,' W-alker<&' - - ' *' vonOTTO^. Robert E. (7 1944) Mech.. Engr;,- r ' Htg., Vtg. &:Air.Cond., U. S. Maritime Commis-* * ' ' 1 sion, -Room' 7126, Dept.' of Commerce Bldg.. ' . x .* - Washington 25. and *2124 'T* SL N.W., Wasb- ' 1 ' .. ington 7. D. C.; / . ; . * , VON REHBERG, Hugo L. <Af 1942) In Charge Wilcox Co.,-5124'Penn Ave.,.-Pittsburgh 24, arid> - 740.S. Negley Ave., Pittsburgh. Pa. - - -* ; . WALKER, Theodore-*R. (Af .1944) Vice-Pres., Columbus Heating & Ventilating Co.,-182' N; j Yale Ave., and 762. Fairwood Ave.,- Columbus. -- Ohio. ' . - ' ' . of Engrg. "DepL; . Braman . Dow & Co.,`239 ;i- .. Causeway St., Boston 14, and 11 Parkton Rd., ` ' ' * Jamaica Plain 30. Boston, Mass. ' - - - WALKER, Wythe F. (A 1941) Air Condi Engr., Douglas Aircraft Col, Inc., -- Long Beach,. ar>H 3637 Sixth'Ave., Los Angeles 16; Calif.. - - / . Y . VON ROSENBERG, Paul C. (7 1939) Product -WALLACE,-George'J. (Life Member; Af T923)" * ' *- 1 Application Engr., Allegheny Engineering Co., '27-36 Ericsson St., East Elmhurst, N. .Y.- - .' ' , . -' ` . 405 Fisher Bldg., Johnstown, Pa. . WALLACE,. James -B. (A 1944) Mfrs.' Repr..- , . . r VOORHEES, Guy A; (Af 1937) - Chief Engr., Taco Heaters Inc. and Lau-Blower Co.-, and *9 - ` ' .Hall-Neal Furnace Co.. .1324 N. Capitol Ave., - Byfield Lane,' Dearborn, Mich. - -. . -Indianapolis, and - Rural.-' Route 1, Box 73, WALLACE, William M.,'II (Af 1929) Cons. Engr , - -- ' ' - Monrovia.' Ind. .- '' 1505 Duke-University Rd.,.Durham, N. C- '. VROOME, Albert E. (Af 1932) Air Cond. Engr.. -- -. ' ^ Ebasco Services. Inc^- 2 Rector St.. New York,. <'_ and 6218 Amboy Rd.,- Prince Bay,' Staten Island WALLIS, Walter M. (A 1940) 11225 Tenth Ave. S.W., Seattle 66, WashI-`T WALSH, Edward R., Jr. (Af 1936; A 1935) Dir - - . ' ' 9, N. Y. . : -- . ' - of Market Research,-York Corp., and *Wyndham - ' ^.. Y.' VYFF, Paul C. (A 1944) Research Engr., Battelle Memorial Institute,.505 W. King Ave., Columbus ' - 1> and 3673 Olentangy Blvd.,;Columbus 2. Ohio/ Hills, York, Pa'.-- ' - .Y WALSH, Gerald W., Jr. (7 1945) Test Engr-, Carrier Corp-. 300' S. Geddes.St.1 and *408- Wendell Terrace, Syracuse, N. Y. ' - ' . Y- .. - ; . -. - . w ; - ' WALSH, James A. (Af 1943) Pres.; J. A. Walsh : . & Co., Inc., P. O. Box 1773, arid 513 Brariard St, ^ - ;. { x/WACHS, Louis J. (A 1936; 7 1930) Sales Engr.. ' Houston,-Texas: -' - ' .* -`-V \ - Consolidated' Conditioning Corp., 456-460 S. f .i .Tenth Ave!, _Mt. Vernon, and *1820 Cortelyou v-- .-"-'Rd., Brooklyn 26, N. Y. -- , . ' WAECHTER, Herman P. (A-1930; 7 1927) Chief WALSHj. John W. (Af 1944)'Pres! &:Treas . *John W. Walsh, Iric.,: 2 Foster St.; and '220 . Burncoat, Wortster. Mass. -- > . , - ' - WALSH, T. A. (A 1945) Chief .Engr;, United ; jStates Naval Air Station, Public Works' Dept-/ " .*t - Engr.. United Merchants Laboratories. Inc., 601' - . Bldg.-16, U.' S. N. A; S., Glenview,-and * 5910 : West 26th St..' and *226 Great Kills Rd., Staten ; \ '1 * Island 8, N. Y. ./ - 'W. Erie St., Chicago 44, 111. . . -* . - . /.- WALTER, .Burwell J, (Af 1945) Sales Engr/ * **.-/" WAGENBRENNER, Louis H. (Af 1944) Chief R. L. Deppmann Co... 1339 Calvin Ave. S:E:, -- . ; '.' "<Mech. Engr., Ralph E. Phillips, 306 Architects: * Grand Rapids 7, Mich. ' ` . Y-. - Bldg., Los Angeles 13. and 168 West 43rd PI... WALTERS, Arthur L. (Af 1926; A 1925; 7 1924)` \-,7 - / - ' ;Los Angeles, Calif. / . . - -Buyer, Montgomery Ward & Co., 619 ,W. Chicago Y*. Y WAGGONER; Jack H. (Af 1937) Gen. Process . Control Mgr..' Owens-Coming Fiberglas- Corp., Ave... Chicago .7, and704H' Hinmari - Ave.;-. - Evanston, III. * - - / . . - . : -I ' - '. 240 Quentin'Rd., Newark.-Ohio. . ' WALTERS, Joseph K. (Af: 1943) Engr:, Keil-, / '* - i r WAGNER, Earle K.` (Af 1938) Sales Engr., The Motor'Co./-llth and Tatnall Sts^ Wilmington 9; ' Y Powers Regulator Co.;.2240 N._ Broad St., Phila- and Greenville, Del. , " -t ' ' > delphia 32; and-312 Myrtle Ave., Cheltenham, Pa! WALTERS,'Thomas A.- (Af 1944) Dir;-of Re-..- ;Y WAGNER, Harlan C., Jr. (7 1945) U. S. Army. . . Holabird Signal Depot, Baltimore, - Md., and ' .Y -; ' ' 1040 W. Front St., Plainfield, N. J.-' ' - - '' - 2 ' WAGNER,.Wilbur J. O. (A 1943) *731 W. Main SL; Jefferson City, Mo. . - - " ' - .search. American Blower Corp.. Detroit'32, arid 19359 San Juan'Dr., Detroit 21." Mich.' -' ` // 'V-' WALTERS, William -T. (Af 1917) SupvsrgY - Engr., Contract Div., The ^Kehm CorpI;, 51-E. - Grand Ave.; Chicago, and *12747- Wallace .St.,. -/ Chicago 28, III.' - ' " ' : ' ' - ;" Y WAHLIN, -Bernard. J. (A 1941)'Application .-' '-'Technician, General Electric Co., 700.-.Common- WALTERTHUM,. John J. (A'1922) 1075 Third' A Ave.-; New York 21, N. Y./and 42A .Van Reipe'ri:' -' -' / wealth -Ave., . Boston, and *11 Stoneleigh Rd., ' Ave.; Jersey City 6,*N. J. -V- v Y - West Newton 65. Mass. -' WALTON, Charles W., Jr. (Af 1934) Engrg. Staff. V - ;/ . WAID, Glen H. (A 1937) . Engrg. Field Service. U. S. Rubber Corp'.,' 1230 Sixth Ave., New York, / - *Scott Valve Manufacturing Co., 1227 W. Wasb- .N. Y., and *R. F. D. 2, Newport, Vt. ^ . - * , .. ington Blvd., Chicago 7,`..and 124 N. Parkside . WALZ, Chester D. (A .1939) .Plant-Engr.. Todd `-'Y'Y V :-.;Ave.. Chicago 44, 111;, ; ~ , Shipyards Corp., Sari Pedro, and *6621' W: Sixth. Y YWALDEN, H. Kenneth (A 1942 ; 7 1939)*2224 v "St..- Los Angeles 36, Calif.I I / :' - Y; i.'L.- -Comer. Bldg.. Birmingham, and 1409 35tfi-SL, .-WALZ. George-R. (A 1944)-Sales-Engr.;*-52t4r- - ..*.- Birmingham 8. Ala. Y ` : .- . . 25th Pl. N.,-ArIington, Va.. v / * Y. WALDO, Harry 'J. (A- 1944); 'Sales 'Repr., , . WANDLESS,. Franklin W. .(M. 1945)/ Design ' _______ .;/,' v Harry J. Waldo. 332 CampSL, New'Orleans 12, .- Engr.-. AI Ernest^ D'Ambly,.' 1700 Walnut .St.,'. ." ."'-and 2519 Joseph St'...New Orleans 15,'La.^.. ' *. * , Philadelphia, and Box 121, Berwyn, Pa. in . .. _ , 84 ' Heating ~^Ventilating ` 'Air . Conditioning Guide 1946 : WANGSGAARD; Dee (A 1942) 1st Lt., C.E., WATSON, Charles E. W. (M 1944) Pres., -/ eCo.. "B". 80.8th Engr. Avn. Bn., A. P. O. 503, ' . c/o Postmaster/San Francisco,-Califand 225 E. -John Watson & Co., Ltd., 1359/Greene Ave:,' Westmount; and 578,-Stanstead Ave., Town of. - - Second S., Logan, Utah. ' Mt.. Royal, Que.,-Canada. ' WARD. Benjamin G. (M 1944) Mech., Engr., WATSON, Gerald M. (S 1941) Lt., *Btry. "B." , U. S. Engineers District Office. Railway Exchange Hi D. C:, Ft. Stevens, Ore. . ` - ' - Bldg.. Denver, and 1260 Kumboldt St., Denver . 6, Colo. - : WARD, Cyril B; (Af 1944) Supt.. Gas Htg. Dept., - Public Service Company of Colorado, 900 15th St., WATSON, M. Barry (M 1945) Canadian Army; ' Cons. Engr., 119 St. George St., Toronto 5. OnL, Canada.. .' WATSON, William W. (A 1942) Sales Engr. / Denver 2. and *626 Race. Denver 6, Colo. ` WARD, Frank J. (M 1935) Owner, Frank J. Ward Co.. 237 W. Court St.. Cincinnati, Ohio, . and -Alexandria Pike, Cold Spring, Ky. '. & Mfrs. Repr., Box 91, Clarkston, Mich. . WATT, Robert Denny (M 1945; A 1943; J. 1937) Pres., Electrol Oil Burner Corp., Aurora at Mercer,' Seattle 9. and 1550 Shenandoah Dr., Seattle 2,- - ' WARD, Joseph A. (M 1944) Pres.,. Abbott Lester - & Co., Inc., 140 Cedar St., New York, N. Y.. and. - Sunset Rd., Pompton Plains. N. J. . WARD, Lawrence C. (A 1945) Dist. Repr.. The Herman Nelson Corp., 513 State Tower . Wash. - . WATTERSON,. Wm. B. (A 1944) Sales Engr.. Air Maze Corp., Cleveland 5, and *1183 Brent- " . wood Rd/ Cleveland Heights.21, Ohio. . '' WATTS, Albert E. (A 1937) Pres., A. E. Watts, , Bldg.-, Syracuse 2, and.112 York Rd., DeWitt, N.Y. Ltd.; P. O. Box 18, Montee St. Laurent, St. Lau- ' . /WARD, Oscar G. (AT 1919) Vice-Pres. & Dist. rent, and *3788 Hampton Ave., N. D; G-, Mon -Mgr., Johnson Service Go.,' 1355 Washington Blvd., Chicago 7, and 1345 Ashland- Ave., Wil- - mette,' 111. . WARDELL, Arthur (M 1935) Assoc. Prof, of - Engrg. Drawing. University of Toronto, and 124 .Melrose.-Ave;, Toronto, One.,.Canada. WARE, John H., Ill (M 1937) Vice-Pres.. Gas . ' ' treal, Que., Canada. WATTS, Edward J. (M 1945) Application Engr.; Worthington Pump & Machinery Corp., 118 Motor Ave., Salt Lake City 1, and 2485 Douglas St., Salt Lake City 5, Utah. - "- WATTS, L. Copeland {hi 1943) Cons. Htg. & Vtg. Engr., J. Roger Preston & Partners, -Dilke House, Malet St'., London,' W.C. 1, and 13 Ossul- Oil * Products. Inc., 45'S. Third-St., and The ton Way, London. N. 2, England. ' ' Yews, Oxford, Pa. ' ' ' WAY, James B. (A 1945) Mgr., Equipment Dept., - . . ' - ' WARMING, Hurley O. (A 1945) St. Paul- Legal Vipond-Tolhurst, Ltd., 845 Querbes ; Ave., - . Ledger, 242 E. Fifth St'., and #1559 Arena St.. . Outremont, Montreal'8. and 4432 Earnscliffe ' - -. : v St. Paul,-Minn. .. . * . ' Ave.; Montreal-28, Que., (Canada. ' " '- WARREN, Clarence N. (M 1943) Vice-Pres. WAY,-Norman {hi 1945)'Engr. & Partner, Way , . &. Asst. Mgr..* Hayes Brothers, -Inc., 236 W.- Engineering Co., P- O. Box-8066; and.Memorial- . .. - Vermont-St., Indianapolis 4, and 419 East 48th Dr., Houston, Texas. : '' : St.. Indianapolis 5, Ind. * ' - WAY, William J,, IL-(A 1945; J 1941) Partner; '/. WARREN, Francis C. (hi 1934) Branch Mgr., . American Blower Corp., 510 Association of Com- Way Engineering Co., P. O. Box 8066, Houston 4,- .' and *'2160 Swift St., Houston 5, Texas.' ` ' merce BIdg., Grand Rapids2, and *329 Gladstone WAYLAND, Clarke E. (A 1937) Vice-Pres. & . Ave. S.E.. Grand Rapids 6, Mich. - Chief Engr., Western Asbestos Co.; 675 Town WARREN, G; Richard (M 1945) Mech. Engr.r send St., San Francisco 3,- and 42 Allston Way. Buick, Oldsmobile. Pontiac Div., General Motors, San Francisco, Calif*' ' < - " ' Fairfax & Kindleberger Rds,, Kansas City, Kans.,- WEATHERBY, Edward P., Jr. (A 1943; J 1936; - - and 6000 Charlotte, Kansas City. Mo. S 1935) Major, 0-325054. Eighth Fighter Com-. . WARREN, Harold-F. (A 1945) Vice-Pres., R. E. mand Hqs.. A. P. O. 637, c/o Postmaster, New ' Chase & Co., Tacoma Bldg... Tacoma 2, and - York,1 N. _Y., and *518 Martinique St., Dallas ` ' 3717 North 36th, Tacoma 7, Wash. .' 10; Texas. - '. ' ` WARREN, Hugh P,, Jr. (A 1946; J 1943;.S 1940) WEAVER, Chandler {M 1945) Mgr., Mountain ' . ' Dist;' Mgr/,' Texas Employers Insurance- Assn., - . - 'and' The Employers Casualty Co., and 2309 ' Aster, Fort'Worth 3. Texas. ' :: WARREN, Robert M,, Jr.'(A 1943; / 1938) Lt., Ariny Air Force, 0-865685, Ady. Cadet Detach ment. Box 469. Selman Field, Monroe,- La,,, and States Dist. Office, e Surface Combustion Corp.. 937 U. S. National Bank Bldg., Denver 2, and- \ Park Lane Hotel, Denver. Colo. - ' -- . / WEAVER,' Eugene A.' {hi 1944) Sales Mgr.,' Surface Combustion, 2375 Dorr St., Toledo, andl. ' #2335 Barrington Dr., Toledo 6,-Ohio;. - . ' ;' . -. 313 N. Main-St., Sumter.'S. C.` - . - - ` WEAVER, J. V. O. {hi 1940) Col., Air Corps./. ' WASHINGTON. L. W. (M 1929) Creekdale. A.-A: F. Plant Repr., Bendix Products Div.,--.-' Farm/R/R. 2,'Pecatonica. 111. ; Bendix .Aviation Corp., 401 Mo. Bendix .Dr.', . - .WASHERMAN, Arthur L. (M 1945) Secy. ' South Bend, 1017 Laurel St., Elkhart, Ind, - Treas., Maisdea &'Wasserman.-Inc., 44 Hicks . .WEBB, Ernest C.* {M 1935) Engrg. Service Mgr., - . ' St../' Hartford 4, and 1155 New Britain Ave.. Iron Fireman Manufacturing_.Co,,'.-3170 West- - -- EliiiwobdTO, Conn. ' \. ' '"-' : - ' 106th St.; Cleveland 11. and 24721 W. Lake Rd., / WASSON, Robert'A. (M. 1938) Gen. Mgr. & Bay Village.'Ohio. ` -' ..-Vice-Pres., Clarage Fan Co., 619- Porter St., i WEBB, John S. (Af .1945) Cons. Engr., 177- .;' 'Kalamazoo 16, and 922 S. Park St:, Kalamazoo State St.. Boston and-345 Brookline St,.:Need-- . "42, Mich. ' ^ - WATERFALL, Wallace (M 1941) Dir., Summary ' Reports Group, Columbia University, 64th Floor, V'S ~ 350 Fifth Ave.. New York 1, N. Y. WATERMAN, Douglas R. (M 1944) Sales Engr.. - = Hendrie'& Bolthoff Manufacturing & Supply Co., 4. ' 1635 17th St.. Denver 17, and 528 Humboldt St., /Denver3,.Colo. ' '- ' ' . . ham. Mass. \ ' .. ' ' - - v WEBB, John W. (M 1926) Managing Dir.,'' Webb Dust Removing & Drying Co.,-Vinery . Works. Town Lane. Denton, Nr. Manchester, . - and MEbor,M Brinnington,-' Stockport,' England. - WEBBER, Charles H. (A 1940) Sales Engr., . e Pacific Scientific'Co., 1430 Grande Vista Ave.;/- ' Los Angeles, and 1176 Mt. Lowe Ds., Altadena. - ' /WATERMAN, John Howard {Life Member; M Calif; . - .' ' - '"} 1931)'Engr., eChas. T. Main, Inc., 201 Devon- WEBER. Erwin L. (hi 1936) Cons: Eiigr., *632 . /'' shire St.'. Boston 10, Mass. -' , . Medical-Arts Bldg., Seattle, Wash. ' v/- WATERS,.G. G.(M 1931; A 1926) Dist., Mgr., " ..American Blower Corp., 1841 Oliver Bldg;, and /- -UlO Longuevue Dr.. Pittsburgh 16,.Pa. - - WEBER, Eugene F. (A 1940; J 1937) Engr.. York . Corp.. 117 South 11th St,; St. Louis 2, and 607 - Forest Ct., Clayton 5, Mo. .. - ^ . v WATKINSvi,George B. (A 1936) Dir. of Research, WEBER, Frank J. (M 1943) Owner, Frank J. "i Libbey-Owehs-Ford Glass Co..- Techmcal Bldg., . Weber & Asiocs.. 443 Delaware Ave., Buffalo 2,.^ . . -- 1701V E.- Broadway, Toledo, and 4941 -Rolandale. and Truscott Terrace, R. F. D. 1, Lake View, N. Y.'- 1 - Rd:,-:P.\0.'Box 227 R. R. 8. Toledo 12. Ohio. WEBSTER, Chester C. (A 1940) Pres.. John --WATKINS,'Wilburn 'O. (A 1945) Owner, Heat . Hankin & Brother, 120 Greenwich St., New.York ;*. *Engirieerihg;.;1225;S.- Main' St., Las Vegas, and, -6. and Box 192, Piermont,.N. Y. . ^ .............. ..> Box.752, Hender8oh; Nev. v-' v WEBSTER, E. Kessler (M 1915) Secy. &;Asst. V. V WATKINSON, 'Gerald H; (A /T944) Defense Gen. Mgr., * Warren Webster & Co., 1625.Federal/.. - Industries,-'.Ltd./I 155. Phillip's -PL, -Montreal, St.. Camden, and Cor? First and Kings Highway, r . Que^rCanada:/;: - `. . . -- . . Haddon Heights, N. J. ' ... 4 ; Roll of Membership 85 . WEBSTER,.Warren, Jr. (M 1932; / 1927) Pres.,- `Warren Websterr-& Co:, 1625 Federal/St., Camden, and 108 Colonial' Ridge Dr:; -Haddon- field. N. J. ^. WEBSTER, William H.# Jr.'(M 1942) Pres.. Allied Distributing Corp;, 933 West 21 St., and * 200 North Shore Rd., Norfolk 7,.Va. . - - WECHSBERG, Otto (M 1932) Pres. & Gen. Mgr., ' . e'Coppus Engineering Corp., 344 Park Ave., anH ' 28 Lennox St., Worcester 2. Mass. WEDDELL, George O. (M 1936) Branch Mgr.. .York Corp., 7 Ferry St., Pittsburgh 22. and e 3114 Wainbell Ave., Dormont, Pittsburgh 16, Pa. -WEDEBROCK, A. L. (A 1945) Staff Engr.. ". Johns-ManviUe Sales Corp... 22 East 40th St., WELLS, Edward E. (M 1941) Gen. Engrg: Dept., Aluminum .Company-of OahaHa, 620 Sun Life Bldg.,-Montreal,'and *6 St: John Rd;, Pointe Claire, Montreal 33, Que.,' Canada - WELLS, Wmiairi F.*:(M 1939)..Dir. of Lab. for Study of Air-Borne Infection, e University' of ' Pennsylvania, Medical School, Philadelphia, and 112 Pine Ridge Rd., Media, Pa. - ' - WENDT, Edgar F. (M 1918) Pres., Buffalo Forge Co., 490 Broadway, and 120 Lincoln Pkway Buffalo, N. Y. ',, -. WENDT, Edwin H. (A 1942; J 1936). Engr. & Treas.. O. A. Wendt Co., 2124' N. Southport Ave., Chicago, and e 6205 Forest Glen, Chicago 30. 111. . ^- ; - .New York. N: Y., and *2 First Ave., West wood, N. J. , WEEKES, Roy W. (M 1941) Chief Mech. In . spector. Defense Construction, e 2705 Conestoga, /. Louisville. Ky. - *- ; WEGMANN, Albert (M 1918) Sheet Metal Contr., : A. Wegmann Co., 2801-7 W. Susquehanna Ave., " - and #6206 North 17th St., Philadelphia, Pa. ' WENDT, William R., Jr. (/ 1945) Instructor, Mech. Engrg.'Dept., University of Wisconsin, Madison 6, and 1316 Mound St., Madison 5, Wis. WENINGER, Merle (A 1945) Dist. Mgr.. Powers' Regulator Co.. 441 S. Salina St., Syracuse 2, and 113 Eloise Terrace, Syracuse 7. N. Y. ' WERKER, Herwart (hi 1939) * Engr., -American- Radiator & Standard' Sanitary Corp.,- Inst, of WEID, Harry. L. (J 1946) Engr.; Philadelphia . -Electrical & Manufacturing Co., 1200-36 North . '3lst St., Philadelphia 21, Pa., and Good Intent Thermal Research, 675 Bronx River, Rd., and 38 Loring Ave., Yonkers 4, N. Y. - ' _ WERLEY, William C. (A 1945). Western Repr., Rd./Blenheim,; N. J. -' WEIL, F. H. Eugene (A 1938) Plant Engr., Young - Radiator Co.; Racine, and *2515 North 59th St., Milwaukee 10, Wis. .. . .WEIL, "Leo .S. (M .1940) Cons.' Engr. & Partner, ` Leo S. Weil & Walter B. Moses, 801 Audubon ` . Bldg., and 478 Broadway, New Orleans, La. . WEIL, Martin (A 1925) Pres., Weil-McLain Co.. ' - 641. W. Lake St., Chicago 6, and 4259 Hazel St., Chicago Z3.11J. ' - , . WEILAND, Car! C. (A 1944) Pres. & Mgr., Central Supply Co.. 210 S. Capitol Ave.. Indianapolis 9, and 428 East 48th St., India napolis, Ind. ... ` '. WEIMER, Fred G. (A -1919) Mgr., Milwaukee Officer* Kewanee Boiler Corp., Rm. '502, 312 E. Wisconsin Ave., and 3958 N.-StoweH'Ave., Mil waukee. Wis. ~. Peerless Foundry Co., Indianapolis,- Ind.,- and '. 4023 Quincy St., St. Louis 16, Mo. : WERNER, Charles V. (M -1945) Sales Engr;, H. H. Wright Co., 1322 Walnut St., and 4219_ Kenwood, Kansas-City, Mo.- ' WERNER, John G. (M 1937) Mgr., Bryant Air Conditioning Corp., Shoreham Bldg., Washington ' 5, and#Apt. No. 113, Chancery Apts.,' 3130 Wisconsin Ave. N.W., Washington 16, D.-C. -- WERNER. P. H: (A1941; J 1939) Major.- U. S. Army, 0-296080, A. P. O. 4299,-c/o P. M,, San Francisco, Calif., and 7926 Micheher' St.-.v Philadelphia T9. Pa.' .' . ' -' - . - . WERNER, Richard K. (M 1936) Cons. Engr.. 316 W; T. Waggoner Bldg.,. Ft. Worth 2( and 5436 Collinwool. Ft- Worth 7, Texas. ' ' WESBY, Vernon Lathrop (A 1944) General Foreman. General Motors Corp., Utilities Operat ing Div..-La Grange, and *6827 S. Throop St.-, WEINER, Hyman R. {J 1945) Student (Sr.), Chicago 36, 111. -. . ' Case-School of Applied Science, and *10631 - Morison Ave., Cleveland, Ohio. WESLEY, Edward D. (A 1945) Owner, WesleyEngineering & Sales Co., 4029, North llth-St.. WEINSHANK; Theodore* (Life Member; ' hi Milwaukee 12,.Wis. 1906);.(Board of Governors, 1913)'Cons. Engr., ... and *2419 Kimball Ave., Chicago, 111. : WEIR,.Frank F. (A 1943) Mgr., *T. McAvity & WESLEY, Ray O. (A 1937) Partner,:Navarre' Plumbing & Heating Co.,' 2308 Fourth Ave;,' Seattle, and R. F. D. 1, Wdodinville,-Wash.'-{ *. ` " Sons, Ltd., 171 Market St. E., Winnipeg, and 374 ' Overdale St.. St."James, Man.. Canada. ' WESLEY, William '(A 1945)- Owner; WesleyRefrigeration Service, 307 N. James St., and *315 . ..WEISS, Arthur P. (M. 1928) Burnham Boiler Oakwood St., P. O. Box 423, Rome, N..Y. ' - - Corp., Irvington,- and #134- Farrington Ave.. . North Tarrytown, N. .Y. . WEST, Charles -H./' Jr. (A 1941) J Vice-Pres., Massey, Wood.& West,'Inc., Lombardy Under ' WEISS, Carl A. (M 1936; A 1924) Vice-Pres.. pass, Richmond,.Va. - . . _ . Kombrodt Kornice Co., 1811 Troost. Ave., and 29 East-68th St., Kansas City, Mo. 'WEISS, Edward J,~(M 1942) Engr... and 1101 . Van Velsen StrrSchenectady 3, N.Y. '- WEST, J. Hoyt (A 1944).Owner & Mgr.i West-5 Bros. Sheet Metal.- 370'Jones Ave; N.W.. and 106 W. Lake Ave. N.W., Atlanta, Ga. ' ' " /. WESTBROOK, Charles H. (A 1945) Partner,.^ - WEITKAM, .Walter J., Sr. (A 1945) Partner & - Gen. Mgr,, Holzer Sheet. Metal Works, 317 American Plumbing & Heating Co., and *1806 Classen. Oklahoma City, Okla. - ' ' - ' Burgundy- St., and #4517 Bienville St., -New ' Orleans,- La. . . - . WESTENDARP, Francisco G. (M 1939),Engr., Apartado 1843,'Mexico, D.:F., Mexico. - ' -' - WEITZEL, Cameron. B. {hi 1936) Maintenance ' WESTOVER,. Wendell (M i936) Pres-HeWest/ ' Supt.,- Reese Padlock Co., 128 Sherman St., and over-Wolfe, Inc., 21 Plaza, Albany, 7.. and Louden: e.714'N. Franklin St., Lancaster, Pa. 'Heights, N; Y. . '* . WEITZEL, Paul H, (A 1942; J 1936; S 1934) WESTPHAL, Edward R. (M 1945) Mgr. of Plants,'- Supvsr.. of Htg. Application, Chrysler Corp.. Weil-McLain Co., Blaine St,,' and Long-Beach.' . Airtemp Div., and *547 Hadley Ave;, Dayton- Michigan City, Ind. - '' . .9, Ohio. - . '' - WESTPHAL, N. E. (A 1946;Xl940;S 1937) Engf;-/ , WELCH, Buster (A 1944) Mech. Engr.; V. S. ; in charge of Gas Boiler Div./, Weil-McLain Co/, Army, 8th Service Command, Dallas, and 1630 - and Long Beach,' Michigan City', Ind:- - - ' - /. 19th St., Lubbock. Texas.' ' ' . ' WETZELL, Horace E. (hi 1934) -Vice-Pres. &. ..WELCH, Louis A., Jr. (A 1929) Owner, eWelch Chief Engr., The Smith Oby: Co.,',6107 Bros., 443 Second St.; and 2001 Campbell Ave., Carnegie Ave.. Cleveland 3, and 2il44-Aberdeen.- Schenectady. N. Y. . Rd/Rocky River 16. Ohio. " ' ' -- WELDY, Lloyd O. (hi 1930) Dist. Mgr., The WHEALTON, Daniel J. (A 1944).Chief Draft^i' ' Powers Regulator Co., 2012 West 25th St., man' & Supervisor, Atlantic Basin Iron'Works,;v ,, Cleveland- -13, and' 19623 Laurel -Ave., Rocky 168, Van' Brunt St., and *593 -Sixth St., -Brook- River 16, Ohio. ` - ' . lyn, N: Y. . - ` . ,-/ > ,* WELLFORD, Walker L., Jr. (M 1944) Secy..- WHEELER, Charles A. (M ?1941)'Branch Mgr./ ' Chickasaw-.Wood Products'Co., 2718 Pershing . _ Johnson Service Co., 511 -Fifth Ave.,;and ;345 ' .Ave.,' Memphis 12, .and. 1584 Harbert Ave., Memphis 4., Tennl WELLS; Donald E. (M 1942) Pres., Products, 49th St.' PI., Dee Moines, Iowa.. , / " WHEELER, - Charles W. (M T9'42) 'Engr;/#The" '.Ric-wiL Co., -1562 Union. Commerce-" Bldg/ . Inc., 420 Paramount-Bldg.,.Des Moines 9, and - Cleveland, and 11859 ' Edgewater ' Dr.,' Lake? . . *70l-42nd St.. Des Moines 12. Iowa. / ` wood. Ohio. " * . .. : //.-; '/ V  It:: i 86 /Heating ^Ventilating, Air ..Conditioning Guide .1946 v > * . WHEELER,' Harold' El i (if 1944) Pres., Air WHYBREW, - George H. .(Af 1944) Chief Mech. Comfort Corp..1307 S; Michigan Ave:, Chicago 5, ' . Engr.; Giifels &* Vallet,' Inc., 1000 Marquette 'Z'`' and 65,-W..Jackson Blvd.. Chicago, III. . ' Bldg., Detroit 26, and 4140 Fulton PL, Royal ; - WHEELER, Joe, Jr. (Af 1938)' Sales Repr.. Oak, Mich. ." v/*7.- Johnson Service `Co.,-28 East 29th St.,' New WHYTE, Frederic J._ (Af 1944) Tech.- Advisor, ; C'York, and P. O. Box 150, Port Washington, N; Y. - ' Norris Warming Co., Ltd., 5-11' Theobalds Rd.; y.; WHELAN, Leo. (Af 1945) Chief Engr... Ray Oil London W:C. V, and ,45 Sidcup Rd., Lee, London,. * .Burner Co., 53 Park PL, New York, and 3111 5.E. 12. England; . . -' '' - '.Glenwood Rd/ Brooklyn.10, N: Y. - WIBALDA; R. K. (A 1944) Purchasing Agent, . WHELAN, William J. (Af 1937) Purchasing Pibg.- & Htg. Dept.; Mid-States Industrial Corp.; 'Agent, Harrigan & Reid Co., 1365 Bagley Ave./ 2401 11th St., Rockford, 111., and* 1507 Clinton . '-Detroit 26, and 3790 Seminole Ave.. Detroit St., Muskegon. Mich. '.' -14; Mich. .. '- . - WIDDOWFIELD, A. S. (A 4941; J 1937) Sales WHELER; AV Gordon (Af 1945) Engr. & Exec., Engr., -The Mercoid- Corp., 4201 Belmont -Ave., House Sheet Metal Co., 1227-W. Genesee St., ' Chicago 41; III. . - 1. ' '.Syracuse, and *523 Fellows Ave., Syracuse 10. N.'-Y: ' -v ' - ` 7WHELLER, Harry S. .(Af 1916) Pres. & Gen. -u-T '. Mgr., L'.J. Wing Manufacturing Co., 154 West * : r ^Wth'St., New York-11, N. Y., and *725 Union : ,y. Ave/-Eliiabeth,N. J. ' - ' ' . ': WIDMER.' Walter J. (A; 1939) Secy.-Treas., - Widmer Plumbing & Heating .Co., 34 N. E. Seventh Ave., Portland 14, and 1565 N. Shaver. -St.', Portland 12, Ore. WIEDEMAN, Walter IA 1945) Owner, Reeves Wiedeman Co.; 2611 Warwick.* Kansas City 8,. . and 5343 Rockhill Rd.,.Kansas Cityr4. Mo. f ir t -WHITE, Arthur A; (A .1945) .Managing'Dir... Gilbert & Barker Manufacturing Co., Ltd., ; j: . ..64'. Jefferson ~ Ave./. and 133 Hillhurst Blvd., . WIEDENMANN, W; A. (A 1942) Sole Owner. a.W. C.Wledenmann-& Son, 1820-24 Harrison St.; , and 5718 RockhiU Rd.; Kansas City, Mo. .' - ' -' Toronto.'Ont., Canada.' . ' WIEGNER, Henry B. (Af 1919) Mgr.. Boston v.lvrWHITE,^Eugene B. (M 1934) ArchL & Engr., Office, Johnson Service Co.,. 20 Winchester St.. .. '.. YMCA Architectural & Engineering Bureau. 19 ' Boston 16, and 143 Standish Rd., Watertown r:'.; S: LaSalle SL; Chicago 3, and 126 S. East Ave., . 72, Mass.' * - - . " '/ - i'**' Oak'Park, Ili*** * - . - * *. WIELAND, John J. (Af 1944) * Mech. Engr.. :Y. iwHITE,- Jack A.V 1945) Engr., Carrier Corp... R. F. D. 1. Alto. Mich. .. : 419 BoylstonSL.Rm. 624, Boston, and 25 Bowker WIGGS, G. Lome (Af 1936; A 1932; J_ 1924) iSL, Brookline. Mass. (Council, 1938-40) Cons. Engr., G. Lome Wiggs -x Y WHITE, -John Cl (Af 1932) Cons. Engr.. Strain 6.Co., Suite 405. Crescent Bldg., 1411 Crescent - ` *&Mech.,"*550 State St.. Madison 3,' and 1221 W. - St., Montreal 25, and' 429' Lansdowne Ave., - Dayton St.'/Madison 5, Wis. ' - Westmount 6, Que.,.Canada: ' - " 4 <vi- WHITE, John H.(A 1944; J 1943) Pres. & Treas., Taco Heaters,`Inc., 342 Madison-Ave., New . WIGLE, Kenneth-G. (A 1945) Pres., Bruce Wigle Plumbing & Heating Co., 9117 Hamilton, -York 17,. N.: Y., and Meadowbank Rd., Old - Greenwich, Conn.v . . , * V WHITE, Maxwell H.` (A . 1945) Archt., *804 >*.' Finance .Bldg., Cleveland 15, and 10120 Wilbur ' /o. 'Ave.,' Cleveland 6, Ohio. - 1 '' '- /.VwHITE/ Thomas J. (A 1941; J 1938) Engr.. American'Blower Corp.-, 625 Market St., San Detroit 2, and 16565' Baylis; Detroit-21,,Mich. WIIK, Edward.M. (A 1945) Htg. Engr.. Twin ' City Plurabing/& Heating Co.; 2912 Bloomington ' Ave; S.,- Minneapolis, and 3429 Portland Ave. S., - Minneapolis 7; Minn. - ...... _ WILDE, I^le R. fAf 1944) Engr., Williams & Richardson, 204 Dooly Bldg.. Salt.Lake City 1; and 153 S. Seventh, E.. Salt' Lake City 2. Utah. - -Francisco 5, and *2340 Pelham PL, Oakland WILDE, Ray S. M. (Af 1938) Mech. Engr.. ' *;yli;.CaIif.: ; ` ' - Giffels & Vallet, Inc.', 1000.Marquette Bldg., and '^.WHITEi W. Emry`(M 1941). Engr..`eH; -H. *8545 Second. Detroit'2, Mich; ; ' . 'y Wright Co.,- 1322 Walnut St..- and 7411 Ward : WILDER, Edward L. (Life Member; Af 1915). '. Pkwa'y.,''Kansas.City/Mo. : _ -' Indus. Promotion Mgr., Rochester 'Gas ,& `Elec-' . . ^HITE,; William, R. (M 1938: A 1936) Indus., ' trie Corp., 89 East Ave., Rochester 4, .-arid 369 ySaW EngiM Industrial Electrical Works, 4509. Bonnie Brae Ave., Rochester 7, N. Y. - -. ' - ^Chicago St., and 4916 Grand Ave., Omaha, Nebr. WILDMAN, Eugene L. (A 1942; J .1939) #124* < - v WHITEL'AW, H. Leigh (Af 1916) Managing Dir., . East 72nd SL. New York, N. Y. ' ' /yAssociation of - Gas Appliance &" Equipment ' WILE, Daniel D.-.(Af 1944) Carrier Corp., and. :'?^;y./Mfrs:, -60. East 42ndSL,. New .York 17; N/Y., #151 CHatham Rd;, Syracuse 6, N-. Y. ' x and'Gummings.Ptl, Stamford, Conn.^ . .. , WILEY, Donald.C.* (A 1939; J 1936) John J. 1 -Vi / . WHITMER; Robert P.` (Af l935) Secy.. Ameri- vy"/-- An Foundry & Furnace Co., and 1404 E..Washing-^ /-Y-yHori St./ Bloomington. 111. ' -. - .7-..".--- Nesbitt, Inc., State* Rd. and Rhawri St.; -Phila^ delphia, . and'.County Line Rd;, Huntingdon/ Valley, Pa. '. >\?&WHITNAH,`Sfcott (Af-1945) Cons. Engr., Scott ' TYl/y Whithali'& Assocs..' 310 Lewis-Bldg., Minneapolis . - '2;:and'R>F. D. 1;-Wayzata, Minn. ,t ... - ^ ^/^WHITNEY,'C. W. (Af 1935) . Pres., ABC Oil - '-'//'^ ' Burner & Engineering Co., 2012-14' Chestnut St.; ;ri -V Philadelphia 3. and 320. South'44 St.;.Philadelphia - -t'/i" <4 -Pa.% - `/^WHiTI'/sidneyA. (A 1938:V 1937) Chief Engr., WILHELM, Joseph E; (Af.l943;V 1936; 5 1934)/ Vice-1Pres. & Chief Engr., Avery-Engineering Co.,1906 Euclid -Ave.', Cleveland 15, and* 294 East. 195th'SL, Eudid 19. Ohio; ; WILKES, Floyd (A 1945) Sales Engr., Westerlm ' & Campbell Gp.1 1457 University Ave;, St'.. Paul,.'.. / and R. F. D. 13, Minneapolis 13. Mirin. -.' ' , WILKES, Gordon B> (Af; 1937) Prof, of Heat ' Engrg., Massachusetts Institute of Technology. 1 YXordley & Hayes, 443 Fourth Ave., New York l6, ' Cambridge 39, and -51 Everett SL, 'Newton -V and * 630' Palisade Ave., Yonkers; N. Y; . - " . Centre; Mass. . " - ' , V- -TV'/WHITTAKER; Wayne K. (A 1935) Engr., Irving . WILKINS, E. Spencer (Af 1945) Mgr. & Chief- .< i It* -.Sy- `Triist-Co.'-Bldg., 1< Wall St.. New York and * -- Engr-V^Air- Handling DepL.' Wertz "Engineering >`'r^ll9-23.226thSt., St. Albans. L. I., N. Y. - . Co.', Inc.; 441 N. Second SL. Reading, and *R. D. L 'v.WHITTEMORE, .-William M,, Jr. (J 1945> 2, Mohriton, Pa. . ^Aif^Supvsr;. Carbide & Carbon Chemical Corp.'; P. O.. IBox.P. and- P.`O. Box 1016, Oak Ridge, Tend. WILKINSON,'Arthur (A 1936) Squadron Ldr.. R. C. A. F.; Aeronautical Engr... No/ 1- Air. Com- ' ..... . .^WHITTEN, .H: E: (Life Member; Af 1936) Pres/-' mand Hq., Trenton, OnL, and 517 Lansdowne; A-* * ~ . jTreas.,:H.'E;Whitten,.Co.r 9 Federal CL. Boston. 1 Ave.,'Westmount 6, Que.. Canada.*. ;< ' * T ^ r,vrandr* 56 Highland Rd.. Somerville, Mass. ' WILKINSON, F, J. (Af 1933) Mgr., Central* f' j-V ' i/.WHITTINGTON,' Winiain P. (Af 1944) Prop., Engrg. Service; Montgomery Ward & Co.. Chicago Whittingtb'n'Pump & Engineering Co.,-245 S, . Ave. and Larabee.; St., .Chicago; * arid 18257 rS/ sr -/-vMerida'n-Str, Indianapolis. 4, ahd,7620 Central ` Martin Ave.,.Homewoqd; 111. ' ' ^ ^&S%;A:>^T*'^-/AveA,indiarieapoIis'.44, Ihd. --4 - WILL, Clarence A. (A 1944)'Mfr's. Repr., #5402 .>;<,WHi'nniESEY,'i.Cont(Af.:I941)...Enb- Com^. _ ' Broadway, Iridianapolis'6,' and R:-Ri..4; Nobles; >-j)QstjoQeef Co'rp/,'409 Tenth St. S.W.-, Washington;- ville.-Ind. . . ' t-r ^^^^^73^?'^DKGrr'andi:el500';S. -Barton No: 690; Arling-% * WILLARD.-'AVC;* (Life Member;'M+1914) (Prri-: `s?.:r u-'* 'fi--- l5^V?88?S-WHnTON;<CorbettF.-(X;*1945KSalis.Engr^-`- deniial Member) --2nd-Vice-Pres., (Pres., 1926;. 1928; 1st Vice-Pres.,' 1927; Council..; 1925-29)--Pres./ lw?f?sWPiS''`!Ghati6SU-EroducU. Ltd.; 512 C. P.-R. Bldg.. , University of Illinois, 355 Administration'BIdg ij/^^^^V^^^ Torbntb.^and.PortjCredit.'Ont., Canada."-/ .and 711 Florida Ave;; Urbana;'Ill.- . ' 'v ^ ... : - ' * . '' . ` ' Roll of: Membership / - ^ '. - . . ' .. .--. . . --, _ ~ ~ ' 87 \ ' WILLEY/Earl C; (if 1934) Prof., Mech. Engrg.. - Oregon State College, and 121 North 29th St., '- Corvallis,''Ore. , .WILLIAM, Frederic C. (Af 1943) Field Engr.. American Blower Corp.-, 1003 Statler Bldg!, Boston 16, and 91 Parker Rd.. Wellesley 81, Mass! WILLIAMS, Allen W. (Life Member; A'1915) - - ` ^ Secy.-Treas., National Warm Air Register Manu- / facturers Institute, 5 E. Long St.. Room '808, - Columbus 15. and' 51 Meadow Park. Bexley 9, Ohio. `" . WILLIAMS, Charles R. (Af 1945) Vice-Pres., - Dickie Construction Co.. Ltd., 17 Yorkville Ave., and *91 Dewboume Ave., Toronto, Ont.. Canada. WILLIAMS, Chester D. (Af 1938) Mgr.. *Gen- - era! Air Conditioning. & Heating Co., 2001 \ \ Peralta St:. Oakland 7, and 5747 Country Club 1 Dr., Oakland 11, Calif. WILLIAMS, Donald D. (Af 1942; A 1940; J 1938) Mech. Engr., U.- S. Army Engineers, Federal . Bldg., Room 311, and 4902 Popleton, Omaha, Neb. WILLIAMS, Donald L. (Af 1941) Engr.. General Air-Conditioning & Heating Co., 2001 Peralta St., - and 67 Glen Ave., Oakland 11,'Calif. , -WILLIAMS, E. Bryan (A-1943) Dir. of Research, __ . Auburn Manufacturing Co., and 707 S. Main St., . 7 . Auburn, Ind. -' . . WILLIAMS, Edgar H. (J 1945) Air Cond. Engr., ' c/o Carl Anderson, Box 93, Lewiston, N. Y. . - WILLIAMS, Elwin C. (A 1939)# Hoffman Spe- - cialty. Co., Inc., 4028 Egbert Ave., Cincinnati 20, Ohio. . WILLIAMS, Frank H. (A 1940; J 1934) Lt. (j-8-). U. S. N. R., U. S. Navy, Room 1228 Navy Bldg., . .- Washington 25, and 1533 Foxhall Rd., Wash ington 7, D. C. . -' . ' WILLIAMS, Garland E. (J 1943) Principal Engr. : . Draftsman, Norfolk Navy Yard, (Hull Drafting Room). Portsmouth, and *810 West 52n9 St.,' ' Norfolk, Va. ' ' * - WILLIAMS, George R. (Af 1945) Gen. Mgr.. ' Stokerette Manufacturing Co., 4540 Ravenswood, .. - Chicago; and *8242 S. Drexel, Chicago-19, 111; WILLIAMS, G. M. (A/' 1943) Cons. Engr., . ' Architects & Builders Bldg., Indianapolis; and 316 Berkeley Rd., Indianapolis 8. Ind. .. WILLIAMS, Harvey O. (A 1945) Field Service ' . Engr., A. M. Byers-Co., 1502 Esperson Bldg., . - . . -Houston 2, and 1901 Swift St.. Houston 5. Texas. . WILLIAMS, H. Edmund (J- 1939) Technician 4th - Grade, U. S. Ariny, c/o 2862nd Engr. ' . Dredge Crew, A. P. O. 22144, c/o Postmaster. ; * .San Francisco. Calif., arid 14 West 103rd St., " . New York,' N: Y.` . - .. , . .'WILLIAMS, Henry B. (Af 1945) Asst. Chief - Engr., McQuay, Inc.,' 1600 Broadway. N.E., ' -Minneapolis, and *2804 37th Ave. S.. Minneapo- - -. - ; lis 6; Minn./ ' ' - - ' 7 . WILLIAMS, James K. (A 1944) Constr. Supt., 7 Robert S. Leiby Co., 212 N. Grant Ave., and ` 1213 Wilson Ave..-Columbus,.Ohio. - ' WILLIAMS,^; Walter (Life Member; M 1915) '- . , Pres;, Forest City Plumbing Co., 332 E. State St., and 923 E. State St.. Ithaca, N. Y. . . r - WILLIAMS,-Kenneth O. (A 1944) Asst. Mgr., / ' ;N. 0: Nelson Co., 4316 Duncan Ave., St. Louis 10. - - and *3200'Oliver Ave., East St. Louis. 111. ' WILLIAMS, Lyle G. (Af 1939) Mech. Engr.. Williams Plumbing Co., Inc., and Gladstone. Ore. " . `WILLIAMS, O. L. (A 1944) Owner T/A, Bryant- . ..' Williams Co., 119 Federal St., Pittsburgh 12. and s-. / '. v; 104 Mayfair Dr., Mt.- Lebanon. Pittsburgh 16, Pa. .* -* . v'. A WILLIAMS, William A. (Af 1943) Engr., Htg.- Vtg.,-.General' Electric Co., River Works, 920 ' _ Western Ave., Lynn, and 10-Sevinor Rd., Mar- . blehead. Mass. - /' /.;. . WILLIAMSON,. Chester C; (M 1942) Project ; Engr- & Mgr., N. -Y. Sales Office & Warehouse, ' -52-56 Ann SL, New York.7. and 16 Field End ' /. Lane, Tuckahoe 7, N. Y.- .* . V ' WILLNER, Ira (Af 1937) Pres., Willner Heating . r-*' Co., Inc., 415 Lexington Ave., New York 17. and 125-East 93rd St., NewYork 28, N/Y. ' . . ; WILLOUGHBY, J..D. (A 1945) Owner,4 F. W. .. . - Willoughby Co., 2008 Curtis SL, Denver 2, arid ' -' - 655'Dahlia St., Denver 7,.Colo.' - : * WILLS/Fred W. (A 1946; 7 1938) CapL, Air '- > ./ - Corps., and 2257 W. Addison St.. Chicago 18. 111. V/.-v'. WILLSON, Frank J. (Af 1941). Vice-Pres.; *Dol- .7 * "-linger'.Corp:, Tl' Centre' Park, Rochester 3, and \ 2219 Westfall Rd.. Rochester 10, N. Y. WILMOT,-Charles S. (Af 1919) Engr., Day arid-' \ : 7 Zimmerman; Inc., Packard Bldg., Philadelphia, . .' and 436 Haverford Ave.,- Narberth. Pa. ' - * >.-.* ' WILSON, Alexander M. (J 1942; S 1939) Ensign. ` U.- S. N; R., 333 South Barrowes, State College, '' ' , Pa: - '. ;1 : WILSON, Arthur A.- (Af-1944) Oregon Branch --' ' 7 ^. Mgr., N. W. Baker Ice Machinery Go., 932 * - N.W. 16th Ave., and P. O. Box398, Portland, Ore. ` ` WILSON, Broadus (Af 1945) Pres., General Air- \ - ..' /*' Conditioning Co., 510 Glenwood Ave., and 2108- . .. - ' White Oak Rd.. Raleigh. N. C. ' ' .* ' ' - ' WILSON, Donald P. (Af 1943) Factory/ Mgr'.,. : . , - .; McQuay. Inc., 1729 Broadway N.E., Minneapolis . ' 13. and3380 Brunswick, Minneapolis 16, Minn.-'- WILSON, George H. (A 1945) Owner, Wilson". . * Refrigeration Engineering, 512 Broadway, and - *. ^ 422 N. Seventh St., Hannibal, Mo. - - - ' / - -; V, WILSON, George T. (Af 1925). Sales Engr., and - : . 25Tyre Ave.. Islington. Ont., Canada. J WILSON, Harry F. (Af 1945) Cons. Engr./*4908 -: ^ Delmar Blvd., St. Louis 8, and 3221 CapehaH .. Dr.,'Normandy 20. Mo. ' - - . .. '-! / -, v WILSON, James (Af 1942) Service Engr., Darling ' ' Bros!, Ltd., 140 Prince'St.-. Montreal, and 4259'.. . =, , ;V Hingston Ave., N. D. G., Montreal. Que., Canada.. '* ` ** r T . ' WILSON, Kentner L. (A ,1944) Branch Mgr:/--' ; Minneapolis-Honeywell -Regulator , Co.. . 415 . - ' Brainard SL, Detroit 1, and 2608 WoodstockDr., ' -. ' Detroit 3, Mich. . . -'; _ : -.4 ; '' 71 7; WILSON, .Leonard M. (A 1944) Draftsman Foreman. George Koch Sons, Inc., 10 South ,11th Ave., and *1615 Russell Ave.. Evansville,-Ind. - ' *` . 7 - -V; . - '.s WILSON, Maurice J. (Af 1945) Sales - Engr./.-' '; Carrier Corp., 300 Ivy St. N.E.. Atlanta 3. and' * /' 2054 Palifox Dr`. N.E., Atlanta, Ga. f . ` , ^- WILSON, Raymond W.- (Af 1934) Member of ' 4 n- : Kj Firm,. Wilson-Brinker. Co.. 309 Pythian Bldg.. . ` " '> Kalamazoo. 9, and *2414 S. Westnedge Ave'., . ' -. - Kalamazoo 34, Mich. ...y4,; WILSON. Robert A. (Af 1936) Sales Engr;. ' ' ' * : Minneapolis-Honeywell Regulator Co:, '5005 5 . ..7-^ .* ^ Euclid. Ave., Cleveland, and* Briar Hill, Solon; ' . ' .'.i Ohio. _ . ' ' . e.^s. WILSON, Victor H. (A 1938) Contr..t*4Mfg.. AgenL *210 Union-Bus Terminal Bldg... Nasfr ; > - - ' . '../ ville 3, and "The Thistle-Patch", Donelson, Terin/ - -` 4 WILSON; Westray E. (A 1939) Lt. Col.. U. S.7 . 7 ' l/c*?. Army, Wilson Plumbing Co., 227 Haywo6d Rd., - " '. " . and 110 Salola St.', Asheville, N. C. ' - '- - ".. s- WILSON. W. H. (A 1932) Chief Power Plant << ' 7 ; . , V .l' Engr., Pullman-Standard Car* Manufacturing 7 '.-7 Co., 11001 Cottage Grove Ave!, and 22 West -' , 110th PL. Chicago.28, 111. '; 4/ WILSON-REID, .Clyde (X 1945), Sales Engr.. . ~:SH. Paul W. Beggs & Son, 665 Folsom St/ .San ; ..*. Francisco;and 70-Alamo Ave.. Berkeley 7. Calif.-' - ' *-/ ' WILTBERGER, Constant F. (Af 1935) Partner, ' .- - Cl. > - Cons. Engr., Pennell & Wiltberger, Land Title'-. ..'-: Bldg:, Philadelphia 10, -and" 22* Colwyn-Lane,'' " -, Bala-Cynwyd, Pa. _ ' '' - ' . ' / /,' ' WINANS, G. D*. (Af 1929), (Council/ 194445)';.; '/ '.'i'yVj Asst. Supt. of Central Htg.; The Detroit Edison ' - -J 7, - - ,' Co.,. 2000 Sroond' 'Ave., Detroit-, 26, .and 16183- . . / '.'*; *; ' Wisconsin, Detroit 21, Mich,-. -- > V. - WINDSOR, William C. (Af .1944)/ Electrical - ^;r ; Engr., S. A. Railways, Airways '& 'Harbours.'. - /. ~ c/o C. E: E.. S. A. R.-Hqrs. J. H. B.. S/A., arid *..V / 11 Third Ave., Hill Extension, Johannesburg./- , / ' Transvaal; South Africa.' 1 WINKLER, Ralph A. (A 1940; > 1937) Engr/ Vj ./ m' : -/ A. E. Winkler & Sons. Inc.."2337 North 31st St.; * 7' Milwaukee 10. and P. O. Box 179; Elm Grove. , -1- .v.7V. '. .* Wis. -***- WINStOW. C.-E. A., Dr: (M 1932). (Presidential i -5 !` Member); (Pres., 1945; 1st Vice-Pres., 1944; 2nd - t 1 V - .x'/'. 'v Vice-Pres., ; 1943;. Council:- 1940^-45) John- B. 7^' Pierce Laboratory of Hygiene*, 290 Congress'Aye.; / .. 7 .7 . :'*/ : and 313 St. Ronan SL,.New.Haven 11, Conn.*-/ .' -V /' ''-v/"* WINTER, Clatide L. (A*1945) Stoker Distributor, / ^ Link-Belt- Co.;* 50 N." Divisions Ave..'Grand *^' ' \ Rapids 2, and 1406 Bemis St. S;E.', Grand Rapids,' ' '< . 7.5* Mich. -'.* ; 7 ;- ;;vr V-': "7 y- WINTERBOTTOM J. W. / (A/r i944u`Pres,.'- Winterbottom Supply Co., aild 432 Denver St.,;- ." ** ^ ;' * -'\r Waterloo, Iowa.-'- ,, ` ' -/ "' ` ^ 7; -7-V '/ WINTERBOTTOM,-Ralph F/(Af. 1923) Owner,* V` Heating & Cooling Supply Co/; P.:0.` Box.306.i- -v/ ' .and 720 Moir St., Vyaterloo,.l9waV '.ev'} - '... / / 'y 88 .Heating- Ferettfating Air Conditioning Guide 1946 WINTERER, Frank C. (Af. 1920) Branch Sales Mgr/ American Radiator & Standard Sanitary -Corp., 300 Broadway. St. Paul 1, and 836 Juno .'* Ave- St. Paul 2,-Minn. - ' .. ` . ~ - WISE, Mason W.-(Af 1941) Owner, M. W. Wise `. - Co/ "Lakewood." and 1666 Melrose Dr. S.W.. . " Atlanta. Ga. - ` . . ` - WISE,. Ray A. (A 1944) Member of Firm. The ' ' Sweeny & Wise Co.. 10210 Woodland, Cleveland. - ' 'and 2124 Lamberton Rd., Cleveland Heights 18, ; Ohio. ' ' v- ' ` ' /' WISER, C. E. (A 1941) Branch Mgr., Minneapolis . -Honeywell Regulator Co., 420 N. Fifth _ St.. .Minneapolis, and 2620 Park Ave. S., Minne- -v~--apolia-7, Minn. - - - : WITHERIDGE, David E. (A 1945; 7 1936) Cons. WOOD, Charles F. (Af 1937) Air Cond. Mgr.. Prod. Development & 'Application Dept., Frigi- ` daire Div., General Motors Sales, Corp.. 300 ' Taylor SL. Dayton I, and*R. -R.. 1, Spring . . Valley, Ohio. - ` - r *.' ' WOODALL, Raymond G. (A 1945) Air Cond. . . Dept., General Electric Co., Red Rock Bldg., - . Atlanta, and 1324 East 37th St.. Savannah, Ga. - * WOODBRIDGE, William L. (A 1944) Owner. Woodbridge Plumbing & Heating. R. F. D. 3, ' 610 Farr St., Milford, Mich. ' . . WOODGER, Herbert W. (Af 1939) Htg. & Vtg. . Engr., General Electric Co.. 100 Woodlawn Ave., . Pittsfield, and "Pineacres," East St/ Lenex. Mass. . WOODHOUSE, Graham D. (A 1938) Vice-Pres.. . Dowagiac Steel Furnace Co/ and 204 Indiana . - Ave., Dowagiac, Mich. . ` ----- - Engr., W. A. Witheridge Co., 2340 Mershon St.. WOODMAN, Lawrence E. (Af 1934) Owner. .. /' /-Saginaw,,Mich. . - Woodman Engineering Co., 203 E. Capitol, . . - WmiERIDGE, William N.* (Af 1944) Dir. & and 925 Adams, Jefferson City, Mo. - . - .'Chief. -Engr., Bureau of Industrial Hygiene, WOODRUFF, Henry S. (Af 1945) Product Engr., .... Detroit Department of Health, 1151 Taylor Ave., Carrier Corp., Syracuse, and *24 Fenner St.. .' * ' Detroit 2, and 3741 W. Outer Dr., Detroit 21, Cazenovia, N. Y. ` *. * - : Mich. . - . ... i' - WITMER, Howard S. (A 1937) United States .. /. Rubber' Co., 6600 E. Jefferson Ave., and *20015 Schoenherr Rd., Detroit.5, Mich.' . WITTBOLD, Richard H. (A 1945) Dist- Repr., Barber-Colman 'Co. and .Farr Co., and *3818 . - Brandt St., Houston; Texas. WITTENMEIER; Frederick G. (Af 1945) Vice . - Pres'; ,'in charge.of Engrg., Wittenmeier Ma - "chohery Co.. 850 N.-Spaulding Ave., Chicago 51,- and 4444 N. Wolcott Ave., Chicago, III. -. WITTIG;. Frederick E' (A 1946; 7 1943) Chief - Engr.'/ Automatic Cooling & Heating Co., 289 * ` Post-.Ave., Westbury, and *35 Hillside. Ave- . ' - Glenwood Landing, N. Y. - . - WOEHLKE, Herman J. (Af 1944) Estimator & - - Asst: Mgr.,>.Bell Plumbing & Heating Co., 1228 WOODS, Baldwin M., Dr. (Af 1937), (Council, .. 1942*45) Dir. of University Extension. University * ' - of California, and *249 The Uplands,-.Berkeley - 5. Calif. -- * ' WOODSON, Edward G. (Af 1944) Mgr., Memphis . Dist., *The Trane Co.. 705 Columbian Tower, ` Memphis 3. and 80 LombardyRd., Memphis, Tenn. - .WOODWARD, Kenneth C. (Af 1944) Engr... Dvlpt. Dept., Chase Brass & Copper Co., -Inc., * -.. Waterbury. and *6 South Court, -Meriden, Conn. . WOOLLARD, Mason S'. .(Af 1934) Registered , Engr., Harry H. -Angus, 1221 Bay St.,.Toronto 1, __ V and*3l Hillcrest` Park Ave., Toronto; 5, Ont., Canada. * - '' . i.. -h WOOLCOCK, Edwin (A 1938) Owner. Woolcock *. . Plumbing & Heating Co., 2217--15th St:, and 440 . . Memorial Pkway., Niagara Falls, N. Y. . WOOLSTON, Robert H. (A 1944 ; 7 1941) z E- Evans Ave., and 2255 S. Marion, Denver 10, Partner, Woolston Woods Co., 2132 Cherry St.,- ' .' %- . .. Colo. . . `. and 12 English Village, Wynnewood, Pa. ' -WOESE, Carl F. (Af 1934) Cons. Engr., Robson WOOTEN, M, Frank, Jr. (Af 1941;A 1940)-Cons. / . & Woese, Inc., 1001 Burnet Ave., Syracuse 3, and . Engr., Wooten & Wooten. 215 Latta Arcade, -* " -. / 256'Robineau Rd., Syracuse 4, N. Y. - and 400 Cherokee Rd., Charlotte. N. C. 1 \. -WOFFENDEN, Harold (Af .1945) Cons. Erigr ``The Birches" Wood Green, Nr. . Fording WORKMAN, Albert E. (A^^1941) Htg. & Air Cond. Sales Dir., United Gas Corp., P. O. Box 2628, ' . : - - .'.-Bridge, Hants. England. . ' - . / WOLF,.- Robert Li (A 1945) Instructor. Mech. Engrg., Washington , University. Lindell and' -> Skiriker, and'921 Trinity Ave., St. Louis 5, Mo. - WOLFE, Allen H. (Af 1944) Vice-pres- The - Huffman-Wolfe Co., 669 N. High St., Columbus 16 and** 2186 Yorkshire' Rd., -.Columbus, Ohio. ' Houston 1, and 1658 W. Main, Apt: 7, Houston. ' Texas. '*'.. . *-:' WORMLEY, Robert F. (A 1938) Mgr., Engineer- ^'; ed Products Div.,.*.Grinnell Company of Canada, ' Ltd., 2440 Dundas St. W., and 1 L'Estrange. * , Place. Toronto 9, Ont., Canada. ' ' .- 7 WORSHAM, Herman (Af 1925; 7 1918)'Mgr., War Products .Training Service, *Frigidaire Div./* ... - ` ^` WOLFE/. Charles -H. . (Af 1944) Mech. Engr., - General Motors Corp.,"300 Taylor St.. Dayton 1; / v .- and *1324 E/-Cooke Rd., Columbus. Ohio. and 624 Daytona Pkwy., Dayton 6, Ohio/ . / WOLFE, Clarence El, Sr. (A 1944) Chief Supt., ` WORTHINGTON, James M. (A 1944) Appli- : :-r . Reynolds Corp., 4224 S.' Lowe Ave., Chicago 9, cation Engr., Fulton Sylphon Co., 410 N. Michigan -- - . -- and'1907- .Clarence Ave., Berwyn, III. Ave., Room 560, Chicago, and *3334 Church' St., ^ ' ; - * WOLFE, John S. (Af l941) Chief Engr.. RuemeUn . Evanston, 111. - - ' '. - "Mfg.'Co-- 3860. N. Palmer St., Milwaukee, and + 2004N.* Bartlett Ave., Milwaukee 2, Wis. WORTHINGTON, Thomas H.. (Af 1937) Asst; ; Mgr;, Eastern Sales; Standard Sanitary & :Do- - . ^ WOLFF/ John F. (A 1945) Asst. Sales;-Mgr,, . ' . Tuttle . Sc , Bailey.Inc., and *106- Harrison St., .-_* / New.Britain, Conn. - -. WOLFF, Richard 'A. (Af 1945) Secy., Wolff & Munier,; Inc., 222 East 41st St., New York 17, and ' v : :250 West-94th St.-, New York 25, N. Y. WOLIN, M. W. (7 1938; S1937) R. F. D. 2,. Box - 522, New Brunswick, N. J. .. ' WOLLENBERGER, Louis (Af. 1938) Indus. Gas ' _ Engr.,'*.Coast Counties' Gas & Electric Co.. 22 . Pacific Ave., and 122 Davis St., Santa Cruz, Calif., 1 WOLLERMAN, Arthur E. (Af 1944) Sales Mgr.. ~ . * * 8: E. Sturtevant Co., 85 E. Gay St., Columbus *. 13.' and 387 Demorest Ave., Columbus 4, Ohio. minion Radiator, Ltd.;. 405 -Beaubien St-.-W., ' Montreal, Que;, Canada. ' . - - --*-./ WORTON, William (Af 1937) Mgr., *C. A. ' Dunham Co., Ltd.. -504 Scott-Block, and .292 - .. Lansdowne Ave., Winnipeg, Man.. Canada.' - ' ' .> WRIGHT, CLP. (A 1944)'Mgr.. *C. P. Wright' - ; -'* & Co.. 4300 Carnegie Ave., Cleveland 3,.and 2987 ' * ; Torrington Rd.; Shaker Heights 22, Oluo. * ` * . ' * . WRIGHT, Calvert C. (Af . 1944) Prof. of,Fuel;:.-.v ? Technology, The Pennsylvania State College,. / - School of Mineral Industries, and 314 Arbor Way, . ' . / State College, Pa/ * '. WRIGHT, Clarence E. (A 1940; 7 1935; 5 1933) - Mgr;, Htg. Dept., Fairmont' wall Plaster Co;, **,. Tenth St., and *303 Nuzum PI., Fairmont, VV/Va- - - WOLPERT' Nathan N/(A 1945) Asso. Editor, WRIGHT, Harris..H.' (Af 1917) Owner. H. H. Hating & Ventilating,- 148 Lafayette. St., New Wright Co.; 1322 Walnut St., Kansas City 6, and v.; -/ -v York," and *4*Prospect Ave., Glen Cove, N. Y. * - *808 Greenway Terrace, Kansas City 5, Mo. *'' '':'/*/ - r. WOLTERS, `.Harold W, (Af i?44) Mgr.. Mech. WRIGHT, Jack (A 1944) Owner. Canadian' . , - `"'DraftiD^pt/ 'Clarage'Fan- Co... Kalamazoo 16, ' Plumbing & Heating.Specialties. LM,, 701 Craig- '.r'.. . and-* 820 StaplesAve.'N.W., Kalamazoo 54; Mich. . -W.,- Montreal. Que.,-and' 24 Thiirlow, Hamp-. -. WONG. WilfmJ S. B. (Af 1938) American/ stead, Canada. ' . ' - ///.,,Engineering . Corp.,.-989 Bubbling Well Rd., .and WRIGHT, John B. (Af 1040) Sales.Engr/The . * -669Hart-Rd/ Shanghai.-Chiiia. ' . ' % Nash Engineering Co.; South Norwalk,-.and. ---.vi ^WOOD^Alfred- W;:(A 194i; 7 1938)'F/Lt- Rowayton, Conn. ` ^ ... -'-** /- **" *] 1 \Rj C/A; F-.Overseas, Station*Armament Officer, ' WRIGHT, John F. (A 1945)` Vent. & Methods -* , " Lmton-on-Ouse; Yorkshire/and* 36 Dufferin St.', _/. - Engr., *Servel, Inc., .119 Morton-Ave.,/and-414. * - IngersoU/Ontario.-Ganada. . .. Stanley.Ave,,- Evansville, Ind. ,. "_ " // * ^ Roll of Membership 89 WRIGHT, K. A. (Af 1921) Branch Mgr., *John- YOUNG, J. T,, Jr. (A 1936) Mgr- Crane Co..- son Service Co.. 1905 Dunlap St., -Cincinnati 14. Box 709. and 538 Ogden.Canyon, Ogden, Utah. Ohio, and 113 Orchard-Rd., Ft. Mitchell, Coving : YOUNGBLOOD, Clete W. (A. 1944) Owner,. ton, Ky. - ' ' . *' ^.Youngblood Plumbing & Heating Supply.Co/" WRIGHT, Lawrence T,, Jr.* (7 1943) Asst. T700 Broadway, and 707 North 23rd St./Paducah, Prof, of Heat-Power Engrg., Cornell University, . Ky. . -* . College of Engineering,.Ithaca, N. Y. * ' ' YOUNGER, John R. (7 1941) M. M. 1/C/U. S. WRIGHT, Norman S,, Jr. (A 1942 ; 7 1941) ` N. R- *.Boat Pool 15..- Navy 3205, F.` P. O- Mfrs. .Repr., *250 -Perry St..' San Francisco, San Francisco, Calif. ` * and 1015 Mariposa Ave.. Berkeley'll, Calif. YOYANOVICH, Emil (A 1945)* Expediter.* Car WRIGHTSON, WLibor T. (Af 1937) Eastern Mgr., negie Illinois Steel Corp- Gary .Works, and *4204 ` Garden City Fan Co., 55 West 42nd St., New Conn St- Gary, Ind. .* . York 18. and 22 Sagamore' Rd., Bronxville 8, N. Y. YULA, Ralph W. (A 1944) Yula Water Heaters, WUNDERLICH, MUton S.* (Af 1925) Dir. of Inc- 166 West 225th St- New York 63, N. Y." Research, Insulite Div., Minnesota & Ontario Paper Co., 500 Baker Arcade,' Minneapolis, and . 545 Mt. Curve Blvd., St. Paul 5, Minn. ' z ' WYATT, DeWitt H. (Af 1936) Cons. Mech. ZACK, H. J,. (Af 1928) Prop- The Zack to., Engr., 123 Acton Rd.. Columbus 2, Ohio,.and . 2311 Van Buren St-Chicago 12, IU. * .. 2004 West End Ave., Nashville 4, Tenn. ZAHNER, Leo W,, Sr. (A 1944) Owner, A. WYLD, Reginald G. (Af 1937) 24 Swan St.. Zahner & Co- 3041-43 Wyandotte, Kansas City 8, Rochester,' N. Y; ' ' and 4434 Madison. Kansas City/Mo. -' WYLIE, Wilson J. (Af 1945) Asstl - to Mgr., ZAKI, Hussein M. (A 1945; 7 1941;.5 1940) Power Dept., Toronto Hydro Electric System, Chief Engr- Refrigeration Dept- The Tractor and 14 Carlton St.. Toronto 2, and 459 Briar Hill Ave., Engineering Co- P. O. B. 366, and *5 Ismail' Toronto l2, Ont.. Canada. Anwar St- Dokki, Cairo, Egypt. * '- - :Y .- ZANONE, Henry A. (A 1943) Htg! & Vent. Engr.. Raymond M. Meyer, 1701 Rowan St- Louisville, . and*Rt. 1, Box441, Shively.-Ky. -, YAGER, John J. (Af 1921) Pres., Goergen- ZAVORSKI, Leonard (Af 1944) Vice-Pres. -in .Mackwirth Co., Inc., 817 Sycamore St., Buffalo, Charge of Production, Tuttle &' Bailey,- Inc- and *425 Woodbridge Ave., Buffalo 14, N. Y. and *6 Lake Court, New Britain, Cohn. YAGLOU, C. P.* (Af 1923) Assoc,. Prof., Indus. ZELLAK, Joseph* (A 1944)..Engr, & Estimator; Hygiene, Harvard .School of Public Health, 55 - Sauer Co- Inc- 368 N. Washington Ave./ Boi Shattuck St., Boston 15, .and 10 Vernon Rd., 4657, Fort Hays Station, and 1928 Baldridge Rd., Waverly 79, Mass. . ^ Columbus. Ohio. ' . '. * YATES, Joseph. E. (Af 1939) Safety Supvsr., Z1BOLD, Carl E. (Af 1929) Mech. Engr., Htg. & Pacific Power & Light Co'., 405 Public Service Vtg- War Dept- Service Command Engrs- 270 Bldg., Portland 4, Ore. - Broadway, New York, and *13 Chadwick -Rd... YATES, Robert A. (A 1945) Mgr.. Yates & Co.. White Plains, N. Y. . 231 Tenth St., and 431-16th St., Brandon, Man., ZIEBER, W. E. (Af* 1935) Dir. of Research, Canada. ' - York Corp- and-22 S. Keesey St- York, Pa. YATES, Walter (Life Member; M 1902) Governing ZIEGLER, Donald D. (7 1944; 5 1942) Lt., Dir., Matthews & Yates, Ltd., Cyclone Works, Propeller Laboratory. Wright Field, Dayton, Ohio. . Swinton, and- 4 Egerton Park,- Worsley, .Mail., ZIEL; Herbert E.* (Af 1941) Mech. Engr- . .England. - Albert Kahn, Assoc.. 345 New Center Bldg- ' YEAGER, George F. (Af 1944) Lead Inspector and 694 Glynn Court. Detroit 2, Mich. '" Air Cond. Dvlpt., Pennsylvania Railroad-Test ZIEMBA, Walter P. (A 1945) Draftsman, N. Bv Dept., 1221 Fourth Ave., Altoona, Pa. Hubbard, 220 Bagley, Detroit 26,-and -19732. YEAZEL, Harold F. (A .1945) Asst. Sales Mgr., Kenosha, Detroit 24, Mich. - .* The Lennox Furnace Co- Inc., 400 N. Midler ZIESSE, Karl 'L. (A 1931) .Partner, Phoenix ` Ave:, Syracuse 1, and 1411 Oak St- Syracuse 8, Sprinkler & Heating Co/ 115 Campau Ave. N.W., ^ N. Y. ' . `- ; ' Grand Rapids. Mich. -- ' YELLEN, Charles F. (A 1945) Htg- Vtg- Air ZIGHEIM, 'William C. (Af 1943) Ownerr- Cond. Maintenance Engr/ Pratt Sc ' Whitney' ' William C. Zingheim Co.. -450 - E. Ohio St.// `Aircraft Corp- Div.* of United-Aircraft,. 400 S. and 8541 Drexel Ave- Chicago, 111.*.. * . Main St- Ehst - Hartford 8, and *61 Imlay St- ZINK, David D. (M 1931). 33 Calle de Versailles, . Hartford 5, Conn. - . ** * , Mexico City, D.F., Mexico.- . . -'/: *-. - * YEOMANS, Paul H. (Af 1944) 56 Cedarbrook ZINTEL, George V. (A 1941) Lt- U. S. N..R- i *Rd- Ardmore, Pa. . . . Navy Dept., 141 W. Jackson Blvd- Rm. 1500,". YERKES, William L. (if 1941) Br. Mgr.. Direct Chicago 4, and *1428 Summerdale, Chicago .40,' , Sales Div., Carrier-Corp., 1500 S. Santa Fe Ave- 111. . - .- . V Los Angeles.21, Calif. ' ZUBER, Otto G. (A 1938) Chief Engr- Amaha ' YOST, Claude (Af 1944) Mech. Engr. Designer. Society,.Amana, and South*Amana; Iowa; '*- ; *>_ &- Draftsman, Zumwalt & Vinther, 1807. Mer ZUMBEHL, Lambert E. (A 1945), Sales Engr- f cantile-Bldg.. Dallas 1, and 5502 Goodwin Ave- Forslund Pump & Machinery Co.,'1717-19 Main . Dallas 6, Texas.. ` ' YOUNG, Chester C. (Af 1943) Utilization Engr- Lone Star Gas Co.--Dallas Div- of Distribution, - 301 S. Harwood St/ Dallas 1,-ahd 4336 Stanhope St- Dallas 5, Texas. ^ YOUNG, Emil O. .(A 1935) Owner, Young Regulator Co- 5209 Euclid.Ave- Cleveland 3, and 3628 Cummings Rd- Cleveland Heights, Ohio. St.,* and 1304 East* 32nd. St. Terrace; Kansas * City,'Mo. ZUMWALT, Ross (A 1941;'7 1938). Partner, Zumwalt &' Vinther, 1807 'Mercantile Bank Bldg- Dallas, Texas.' . . . . '/ ZUROW, William A. (A 1946; 7.1937)' U- U. S. N. R- 1517 S.W. 61 Dr- Portland 1, Ore. ' ZWERLING, Seymour J. (7 1944) Engr. & Supt.;.'' Triangle Sheet Metal Works, Inc/ 17-19 i YOUNG, George Harrison (7 1944) Chief Engr- ' Meadow St-'Brooklyn 6, and-4146 Bedford'Ave- -- V. E. Sprouse Co- and *2225 California St.,- Brooklyn 29, N. Y. / / Columbus, Ind. - - ZYNDA, John R, (7 1942) Ensign. U: S. N>.R.;/ YOUNG, Harold J. (Af 1937) Sales Engr- Young U. S. S. Conquest (AMc-71), U-.S/Naval Frontier. - ' Radiator Co- Occidental Hotel Bldg- and 1364 Base, Charleston, S.C., and *8876 Burt 'Rd- - ' Lakeshore Dr- Muskegon, Mich.. - .' . Detroit 23, Mich. - .. . ` ' c.'-' *'*' 90 .'Heating' Ventilating ' Air - Conditioning, Guide 1946 \ ENGINEERS OF HUMAN COMFORT . The Heating, Ventilating .and Air Conditioning Engineer through his work and - research brings to our homes, our offices and our factories', in both summer and winter, that climate best suited to our comfort and health, and he creates for our industries- those atmospheric conditions which improve quality of product and speed production. - He is truly an Engineer of Human Comfort and a public benefactor. '.. \ ... It was in 1894 that a small group of nationally known engineers, educators, and manufacturers organized the A'S.H.V.E. for, the express purpose of improving.the Art through the interchange of ideas and stimulation of scientific research and invention., In 1894, it was agreed that the great art of heating and ventilating, deserved and required recognition as an essential, distinctive and highly specialized division of modern ,, engineering. These, men realized the basic importance' of heating and ventilating as the.'primary element in the well-being of civilized mankind, living and working mostly - ,, ipdoors. ] . . . '. ' - ' " These,keen, alert, progressive men knew that the methods and equipment of their-, day could be improved even beyond their own vision if all the personalities striving for such improvement could be welded into one organized cooperative group, imbued with * the same ideals arid'set toward the same goal. So they formed themselves into the' -nucleus of such an organization and called.it The American Society of Heating and ..VeNTILATINGiEnGINEERS. . -. / \ . That the Charter Members had great faith in their enterprise is evident,: although. little did they dream that progress would be so rapid in their profession. ' . ;* During ` the intervening years since that little group of 75 pioneers unfurled.-the; : banner of . The American Society of Heating and Ventilating Engineers--4506 of-the real leaders of thought and action in heating, ventilating,'and air conditioning . have gathered about that standard and carried its proudly before them far along the way of real accomplishment. They .may be identified among engineering groups by the distinctive emblem which^was adopted by the Charter Members. . :. --The-record of.the Society's accomplishments is a long and brilliant one, yet it must-, -embrace-but a small-part .of the real, achievement which the Society has inspired both among" its .members arid the many non-members whose work it has influenced. Re- warding'the'efforts of'its founders, who gave unstintingly of .their time and means, the- Society.has been tremendously effective in the'adyancement of the Art arid Industry through its-manifold activity.. . ", ... * . .. ..- - r / FOUNDING OF THE A. S. H. V, Ei .' r The_6rganizatiori of,a Society of heating and ventilating engineers was first talked ` of by Hxigh-J. Barron and L. H. Hart iri the early summer of 1894. -. ..'! , - v On. August'2i l894,' a;grbup' of 15 men met at the office of Heating*and Ventilation, / . 146 World Bldg.;" New York, and a committee of 5 was chosen to effectamorganization X`;The..first-'meeting was called at 3:00 p.m., September 10, 1894, at the Broadway, . .Central Hotel and temporary officers were elected: ,F. P. Smith, Chairman', and L. H. . , Hart,'Clerk. ;The`roll call,showed that 75,persons had become.Charter Members. . It- j was,,voted-that"the" name of the-organization, should be-The. American Society of - 4Heating and Ventilating Engineers arid a Constitution and By-Laws were adopted.;-;.; y.The folIowing were;eiected to.hold office until the 1st Annual Meeting, January 22-24, y. y:1895i JPresident, E.'-P.Bates; Syracuse, N: Yy.-First Vice-President,. W.-M/iMackay; If -'-New :York,; N. Y.;, Second .Vice-President, W. F.' Wolfe, Boston, Mass;; ;7"7nVd Vice- . ''.President;'GKas.yS. Onderdonk, Philadelphia, Pa.; Treasurer, Judsori' A-.; Goodrich, V .vNew.York,.N. Y.Secretary, Lv H. Hart,: New York, N. YBoard of Managers, E P y .^Smithj H. j; Baitdh,.A. A. Cary, New York; James A. Harding, Vineyard Haven, Mass.; i^/Hehiy^Ada'ms.- Washihgton, D. C; Council on Membership, Ghas. W. Newton,-Ralti-^' ^moreT Md.V R.rC: Carpenter; Ithaca,. N. Y.; ^Albert A. Cryer,'New-York;-.F. W. Foster,' .^Boston ; rU'i. GrScoUay;rBrdoklyn,.vMN-r VY. * -.- - --- " V Roll of-.Membership' 91 i'; ... 3T! ^ HOW to: apply for membership . .The real accomplishments of life are Junior Members $10.00; and Student Memr usually measured by the service one has bers $3.00: Dues of new members are ' rendered to his fellows and the. .true -oul- - pro-rated on a quarterly basis..' - ' ': '' ttiral refinement of mind, the finest sense of personal and. professional ethics, factors ' ."transcending all material elements in what . man calls "success," are developedithrough. association with those of. high ideals and -cherished ambitions in.the same field of *. Article C-II--Membership.' - . Section li- Persons connected, with.-the' arts arid sciences related to heating, venti lating or air conditioning are eligible for admission into the Society. s. ' :activity.. The American- (Society of 'Section ' 4-. A Mernber shall be , over ., : Heating and. Ventilating Engineers thirty-.'(30) years of age and; shall have ' Offers to him whose' work is-definitely more than; eight: (8)' years* experience in-' within its "province am opportunity - for the sciences relating to the arts of heating,;- - ~ such association and an opportunity, for ventilating or air conditioning.; He shall yreal service. to his-profession.. * . . ; have been'-in . active practice of his pro- ' -Is Every/mari^in the heating, ventilating fession and in responsible charge of .im-. -. and air conditioning profession needs the portant work for four (4) years, insisting ; _ Society:-- . . - *. .' of desigH, construction, r^earch, developr" -'ment or t^ichirig, arid shall be qualified to 1--Because of the contacts that it brings design or direct such engineering work. ' : ' -through national and local meetings. Section 5. A Juriior Member shall be a * 2- r^Because of the information supplied by person-oyer- twenty'(20) years and.under y : . Society Publications. ' ,. * - *- thirty (30)"years of age, who has Had three ' - 3^-Bedause of the opportunities 'that re^ (Z) years* experience in the sciences relating-V;, " ` search^ reveals in new applications for .tojthe arts of heating'-ventilating or air . "T''; engineering services and equipment. conditioning. . Each- successfully; ..corn-0 4r--Because of the satisfaction to be de- pleted year in an engineering school may v. - rived in contributing to human coinfort be-considered equivalent to one' (1) year : and well being. . , -. of.such work. v A Candidate must make application "on ' the: printed 'form "Membership Appli-. .'cation" which is. available at the head? y quarters office or from Chapter Officers and'members. A statement of .qualifi cations and engineering experience' is ' required and four members, must act as. sponsors except" under certain conditions noted'in Article B-III of the By-Laws.-. . Section 6. An Associate Member-shall ; -;be twentyffive (25). years of age or-'over. - - He need riot bean'engineer, but'must have Seen so connected, with some branchc'of - engineering-or thef art of heatirig. ventU lating, air conditioning'or the industries . relating thereto, that he may be considered - > as qualified to co-operate withheatirig arid^ - 'ventilating engineers in the advancement'- . of professional!knowledge; . ' Initiation Fees are: Members and Asso ciate Members $10.00; Junior Members $5.00. The Initiation Fee must accompany, application. .. , \- Section 7. AStudent Member shrilf be a person between the 'ages ;.of 18 and 25' years,- whoi is. regularly attending courses in, an 'engineering--college ;or. -,te<hnirab -The annual dues' of the' Society , are:. rschoolatthe time of-applyingfor memberr'' r- . Members and. Associate' Members $18.00; ship.-; .j.-" ft"-.' v.-;r. . 92- J* .~ Heating Ventilating Air ,^Conditidningi.iGuide-'i946 PRESIDENTS OF THE A. S. H. V. E. V1945-C.-E. A, Winslow , *. , :.1944^-S. H. Downs ' 1943-r-M. F; BLANKIN 1942--E. 6. Eastwood . 1941-^-W. L.Flkisher . 1940--^F. E. Gibsecke - 1939^^ F. McIntirb ' V -1938--^E. Holt-Gurney . 11937--D.S. Boyden " ; 1936--G. L. Larson ' " 1935--John Howatt . ' 1934-rC. V. Haynes - 1933--Wrf. Jones . ' 1932--F. B. Rowlby - -,.-193i^7W. H. Carrier . 1930--L; A. Harding 1929--Thornton Lewis ' 1928--A. C. Willard . 1927--F. Paul Anderson 1926-^rW. H. Driscoll . 1925--S. E. Dibble 1924--Homer Addams 1923-^H. P. Gant ' 1922--Jay R. McColl 1921-1--Champlain L. Riley 1920--E. Vernon Hill .1919--Walter S. Timmis 1918--F. R. Still 1917--J. Irvine Lyle1916--^Harry M. Hart 1915--Dwicht D. Kimball 1914^--Samuel R. Lewis 1913r--John F.-Hale ' ' 1912--John R. Allen *k 1911--Reginald Pelham Bolto: 1910--James D. Hoffman . * 1909--William G. Snow 1908--James Mackay . 1907--C. B. J. Snyder - - 1906--John Gokmly 1905--William Kent . 1904--Andrew Harvey ,, 1903--H. D; Crane . ' 1902--A. E. Kenrick ' 1901--J. H. Kinealy ' 1900--:D. M. Quay. ' 1899--Henry Adams . 1898--Wiltsie F. Wolfe 1897--Wm. M. Mackay - . 1896--~R. C. Carpenter v . . 1895--Stewart A. 'Jbllett ;: I894--Edward P. Bates CHARTER MEMBERS OF THE SOCIETY Henry. Adams . .Washington, D. C:' : C. F. Gessert , New York, N. Y. * . Charles W. Newton1 . - Baltimore, Md. . v Homer Addams * . - " . Washington,. D. C.- . Newell P.;Andrus .- Brooklyn, N.' Y. ' Hugh J. Barron ' '.. New York, N. Y. . `' Thomas Barwick New York. N.-Y. ' Judson A. Goodrich . , - New York. N. Y. John Gormly Philadelphia,' Pa. James A. Harding . New York, N. Y. L. H. Hart . . New York. N. Y. - Theodore C.' Northcott - .. . Elmira, N. Y. 7' j Charles S; Onderdonk - Philadelphia, Pa. John Ar. Payne _ " . Providence, R. I.' . * John H. Petherick - V Chattanooga, Tenn. Edward- P. Bates . Syracuse. N. Y; ' ' . Charles F. Hauss - .. New York, N. Y. . " Geo. W. Plastow ' '' ' Jersey City, N. J;, Geo.C.Blackmore . _-. Pittsburgh,. Pa.- -- J.J.Blackmore- . ' . . NeW York, N. Y. - ,-L. R.;Blackmore _ " New;York. N. Y. v Jno. D. Hibbard Chicago. -111. ' - . -William H. Hill New York, -N. Y. Geo.' D. Hoffman . Chicago,-IIL. . ' Henry B; Prather'. Buffalo, N. Y. ^ ' Leon H. Prentice ^ Chicago, 111.' ` ' D. M. Quay ' Chicago,. 111;.-. . SamueTBurns - v. ' c- New York,.N.-Y; B. Harold Carpenter Wilkes Barre, Pa. ' - Charles S." Hopkins - " Rochester, N. Y. '. Alfred A. Hunting ' ; Boston, Mass. ` . . - ' Wm. A. Russeli , New-York, N.JY.' - " U. G. ScoHay' . . Brooklyn; N. Y. ; R. C. Carpenter Ithaca, N. Y.' Albert"A,"Cary - ` - - New.York. N.;;Y. . -Robert C-. Clarkson . -- Philadelphia, Pa. .'. .Stewart A. Jellett Philadelphia, Pa. \ J. H.' Kinealy. ' ; , ' St. Louis, Mo. " ' Jos. A. Langdon . Pittsburgh. Pa. . . . Perdval H.'Seward - ' New York, N. YT -' ' Le Roy- B.^Sherman-. . New York,-N.;Y. ' Fred'P..Smith- - T New York, N. Yi .' ' Geo. B. Cobb . New York, N. Y. ' _ Chas.W. Light . * Saginaw, Mich; - -. ' B. F. Stangland ' New York, N. Y. ' -H. D."Crane Cindnnati. Ohio - .. ". H. E. Light . Saginaw, Mich. - . Geo. P. Steel ' ' Philadelphia, Pa. _ -' Albert A. Cryer , - ' ' - New*York,',N;,Y.-.; - . ; ' Chas. C. Lincoln * . New York, N. Y. Joseph M. Stoughton '" . Yonkers," N..Y. - .. -.:T,,B..Cryer : Newark. N. J. - .. C. K. Longeneckcr ' -H. M. Swetland. a, - . New York, N. Y. ' . . .. . New York, N; Y. - . Mark-D^n .' ' - "" -Bostoni Mass.' ' _ James Mackay . Chicago. IIL -' .' ' Geo. H. Underhill - Boston, Mass. . `T- John Demarest - ^ . Boston, Mass. " . , ." Wm. M. Mackay . . T; J. Waters .. New York, N. Y. ' . Chicago, IIL ~ . ,Thos."J.. Douglass . ^^Norwich;;QomL;.- . . ^A.-G.-r-Edgar - : - A. S. Mappett . New York, N. Y. Wm. McMannis .. .. `~ J. R. Wendover ' " 'New York; N. Y.^ . W. B. Wilkinson --V - Piuladelphia,Pa. .. . . . New York. N.Y., ' - -New York, N. Y.;- Hermann Eisert,'-' - ^ Baltimore. Md. - * ' , -. . George L. Mehring Chicago; 111. >x Jamw R. Willett - Chicago, IIL - . r\ John.'A?Fish'J. .^crBwitomlMass.-. Frank Wi.Fosierl .. . "Edward A."Mumo'. ' . ' J.'j.'Wason^' '* 7.' . Brooklyn.:N. Y.; * '- ` -.Troy; N.'.Y., " . RobertMunro ' r " - Wiitsie'F. Wolfe' ' Boston,:Mass., ; Pittsburgh. Pa.. ` - . . ' Boston, Mass. ; , Roll of MernHerstiip 93, AVS.H.V.E. MILESTONES 1894 Organization meeting September 10, at Broadway Central Hotel,- New ;York, with 75 Charter Membiers'. . . . . ` 1895 First AnnuEil Meeting, January 22-24 at 12 West 31st Street, New. York. Incor poration under laws of New York State, TRANSACTIONS established; 1896 Society Emblem adopted at 2nd Annual Meeting--Dr. J. S. Billings, First Honorary Member. ; : 1_ . .. 1897 First Semi-Annual Meeting held at the Windsor Hotel, New York, June. 18. - : 1906 First Chapter organized in Chicago. - . . -. 1907 Membership reached 301. . . ] : . 1911 Membership totaled 405. New York Chapter formed. Society, established Headquarters in Engineering Societies Building, 29 West 39th Street; New York.. .1915 Journal first published in April as a quarterly; later issued monthly. . . .' 1916 Full time Secretary: employed; iiji8 Members in Armed Services--64. .^ >' " . . - \. :.1919 .After several years of consideration and planning; the Society established- its' . Research Laboratory, in the United States Bureau of Mines, at Pittsburgh; Pa;, :; having determined a'preliminary modus operandi and provided an operating fund. - The Society is justly proud that it is the only.professional engineering organization ', which maintains and.operates its own Researdi Laboratory. , o' 1922 The A.S.H.V.E. Guide published in September, .. ,- 1923 Comfort Zone Established by A.S.H.V.E. Research. * - 1925 Dues raised to $25.00 and 40 per cent of dues of members and associates allocated-r to Research Fund. " . . , ' . . 1927 Membership of Council increased from 12 to 17. 1928 ^Appointment of (Technical-Secretary and completion, of Code for Minimum Requirements for Heating:and Ventilation of Buildings. Benjamin-Franklin . *honored` as Patron Sa`int oiffSocriieety. . 1929 Journal incorporated as a Special Section of Healing, Piping and Air Conditioning. . - -Society .Headquarters moved to 51 Madison Ave.. 1 .. ' _ T " .. /. - ,1930 .Endowment created by Thornton Lewis for the F. Paul Anderson Medal! FirstV4 , International Heating.and Ventilating Exposition held in Philadelphia. " . . 1932 First Award of F.'Paul Anderson Medal to W. H. Carrier. ^ 1. . ; 1933 New Constitution and By-Laws adbpted-r*Membership dues reduced. ... 1938 Membership passed 3000. : ' " . '-' 1941 Society requested to do Research for U. S. Navy. ._ ' . .. ' (-. 1943 Membership at all-time high, 3300--Chapter with largest Charter Membership ; organized inTridianapolis. - , * . - ' .. :_.v . ' 1944 50th. Anniversary. - .. ' 1945 Members serving.in Armed Korces-- 416 >1946 New Charter approved. )'~*,'Tr`7!"'1 "'rS.'--'iV-' "'. r;-* - v -'- -; / .-V; 94 Heating Ventilating -/Air. . Comfitionirig Guide 1946. . -_. .. Meetings of ' ` - ' . American Society of Heating and Ventilating-Engineers, -Annual . Year Meeting Date . Place - Seihi-Annual. , Meeting Place : 1895 ` 1st' Jan. 21-23 New-York. N. Y. None . ' 1896 ' 2nd' .Jan. 21-23 , New York, N. Y. *. None * 1897 ; 3rd `, Jan. 26-28 New York, N. Y. June 18 New York, N. Y. 1898 ,-r 4th Jan. 25-27 New York. N: Y. * J uly. 15 Atlantic City, N. J. .1899 5th Jan. 24-26 New York, N.-Y. None .* 1900 6th Jan. 23-25 New York; N. Y. None - 1901 7th Jan. 2224 New York, N. Y. July 12-13 Chicago, III. - f 1902. ,8th Jan. 21-23 New-York; N; Y. June-16 Atlantic City, N: J. 1903 . 9tfi Jant 20-22 New York, N. Y. July. 17-18 Niagara Falls, N. Y. ` 1904, 10th .' Jan. 19-21 NewYork, N. Y. July 15-16 Detroit, Mich. , . 1905 11th . Jan. 17-19 New York, N. Y. July 7-8 Chicago; III. . 1906 12th' . Jan. 16-18 New York, N. Y. Jiily 19-20 Chicago; 111. 1907 13th Jan. 22-24 New York, N. Y. July 18-19 Milwaukee, Wis. 1908 14tb ' Jan. 21-23 : New York,- N. Y. July 24-25 Niagara Falls, N. Yi. 1909 . 15th .- Jan. 19-21. New York; N. Y. , July 15-16 Indianapolis, Ind. 1910 . 16th Jan.. 18-20 ' New York,.N. Y. ' 1911 :Si7thv Jan.' 24-26 New'York, N. Y. June 30- -July 1 July 6-8 St. Louis, Mo. . . . Chicago, 111. *> V 1912 18th' Jan. 23-25 New York, N..Y. July 11-12 Detroit; Mich. '. . 1913 . 19th Jan. 21-23 . .New'York; N. Y. July 17-19 Buffalo, Nr Y. . . ; 19141 '.20th Jan. 20-23 New York, N. Y. July 9-11 . Cleveland, Ohio . ; ^1915" 21st ' Jan. 20-22 . ,New York, N. Y. .Sept. 16-17.. Atlantic City, N. J: - 1916 -22hd.' Jah. 18-20 ` New York.'N. Y. , July 19-21 Detroit,.Mich. ` - ; 1917- 23rd ' Jin. 16-18 . New. York, N. Y. July 18-20 -Chicago,.III. ' ' 1918. 24th . Jan. 22-24 New York, N. Y. June 26-28 Buffalo, N.Y. . -1919 ` 25th Jan. 28-30 . .-New York,- N. Y: June 10-12. Pittsburgh, Pa. \ '? 1920 - 26th Jan. 27-29 .-New York;. N. Y. May 26-28* St. Louis, Mo. \ . 1921 27th . "'Jan. 26;28 ; Philadelphia, Pa. June 14-17. Cleveland, Ohio . 1922 r 28th. Jan: 24-26 New York, N.:Y. June6r7.' -June 8-10 Buffalo, N. Y. Detroit, Mich. . - --1923 '29th: Jan. 23-26 New York, N. Y. May 2i:23 Chicago, III. . -; . and Washington, '*' . d. c: y? r ' 1924i .. 30th ' Jan. 22-25 New York,' N: Y. June 19-22 * Kansas City, Mo. * ,, ;1925.- . 31st. Jan. 27r30 . New York/N. Y. . June 15-17 Atlantic City, N. J. * ' ; . : ; '. - : and Boston ' 1926 '.;'32hd;: Jan'.26-29. -Buffalo, N. Y.* . May 26-28 Lexington, Ky;1 . ' 1927 33rd .. Jan. 26^28 -St..Louis, Mo:- June 28-30 White Sulphur Springs .1928.: "34th Jan. 23-27 . New York, N. Y. June 26-29 West Baden, Ind.-$ / - 1929 .35th Jan.. 28-31 Chicago,, 111. ' June 26-28 Bigwin Inn, OnL . , , 1930 36th .. JahV27f31 ^Philadelphia,'. Pa. June 24-27 Minneapolis, Minn. ' . 1931- / 37th 1 Jan. 26-29'1>' Pittsburgh, Pa. . . June 22-25 Swampscott; Mass.' - 1932: 38th , Jan. 25-29 '-/Cleveland,-.Ohio . June 27-29 * ,Milwaukee`Wis/. ' '1933 . 39th" Jari:123-25'- x Cincinnati, Ohio. June 22-24. Detroit,. Mich. -: ` ''1934? 40th<. Feb; 5-9 ' New York, N. Y. June 20-22. Buck Hill Falls, Pa.. - -1935' 41st Jan.-28-30 Buffalo, N. Y. June 16rl9. Toronto, Ont. ' . t /vr- 1936 42nd- Jan. 27-30 . Chicago, III. June 22-24 Buck Hill Falls, Pa. ` 1937 43rd, Jan. 25-27 St: Louis, Mo. \ June 24-26 ` Swampscott, Mass: _V 1938 ,44th Jan. 24-28 NewYork,- N. Y. .June 20t23, Hot Springs,-Va. ' .-** J - ' 1939 : 45th , jani 23-26-. . . Pittsburgh, Pa. July 4^6 . . Mackinac Isl.,*Mich. - Oct. 30-31 Atlanta, .Ga.- " . . -V 1940 ,'46th '/.Jan. ,23-26*;'' Cleveland, Ohio, June 17-19' Washington,-D': C. - Oct. 14^15 Houston, Tex.- . .vl941..--:47,th Jan. 27-29; -Kansas-City, Mo., June 17-19 San Francisco, Galil .... 1942;'JC'48th-; >-Jan. 26:28 .-Philadelphia, Pa. * June.15-17 St. Paul, Minn. ''' - 25-27 Cincinnati, Ohio' June 7.-8 Pittsburgh, Pa; . ,|^f^"j'^'Htl944r^5qtlr;'.;;Jan.; 31- ; New York, Ni Y. June 19-20 - .Grand Rapids,-. Mich. . Jatf! bi.4h2s: 22-24 -.-Bost6n',;Mass. . '.. " " "''^^5^jYl"946 4-' 52nd- . Jan. 27-30- -New York, N. Y. ting ;. ,; WATER-AIR'RATIO (W), LB. WATER PER LB. DRY AIR 15 - . ie . ' 17. 18 . 18 . - SO.. . . 21 22 . 25 24 ' 25. '. .204'.. .27 ' 28 ' 28 .. SO M I I.H'H.P l ll .' ! 1`il'u k,vi I M iimi. 111 II'VI.'H in.' i 11 jjfarn-atp-i;rirr i h'.mtmi m.m. i ji.uii . inuiri.n n .tthi'i.'ii i.'ii i-Yirri ti .0 '% > f