Document MMD1aJ79w23dOqB4q4BoREXQ9

v -rizif PLAINTIFF'S EXHIBIT DOW-2532 session * 2 3 4 3 7 10 11 WOB WORKSHOP Piping Codes SUBJECT nsTBocroB ^Corner ripe Tlpe Fittings Flanges HJntshall Hfaodlel "^wn^sre- Valves Caskets and Joint Conpounds Ievlev of Spec Book U and Bsvlsv of Spec Book * .J ^Becker art - 55*' Bnrnansn -------- Line Sizing (Veter and Process Liquids} Dufllho Line Sizing (Cases and Steen) Piping Stress Analysis Dupra HcJunUn DAXE/T1ME/LOCATION 9-29 / / A?S3 / 'mi / ./ / // // / ic-.oc-fZMiua ... t / t / 6? / Fefo-t // HfT/Jr 9-26-77 -H o T O OD 09 o(V ST0408820 ST040882I ST0408821 ST0408822 PIPING COOES ANSI B31.3 - 1976 CHEMICAL PLANT AND PETROLEUM REFINING PIPING HISTORY OF ANSI B31.3 - ANSI B31 is the American National Standard Code'for Pressure Piping. It is divided into several sections. A detailed history of the development of this section is given in the Forward to B31.3, a copy of which is included as Attachment 1. The designer should remember that the preceeding organizations known as the American Standards Association (ASA) and the U. S. of America Standards Institute (USASI) no longer exist though their names still remain in older publications. Section B31.3 is an industry developed and industry accepted standard with Dow representatives having participated in its development. The first edition of B31.3 Petroleum Refining Piping was published in 1959. Revised editions were published in 1962, 1966, 1973 and 1976. The term "Chemical Plant" was added to the 1976 edition after it was decided that a separate section for the Chemical Industry was impractical. Plans are to continue to revise the entire standard every three years with addenda published as needed. WHO IS THE B31.3 COMMITTEE? - ANSI has a staff and offices in New York which function somewhat like a clearing house for thousands of standards. The actual development of the American National Standard Code for Pressure Piping (B31) which includes Section B31.3 was done by the American Society of Mechanical Engineers and its many members who have participated over the past 50 years. The B31.3 Committee is composed of approximately 50 members who are employed by various chemical companies, petroleum companies, fabri cators, contractors and engineering firms. All members are appointed and approved by ASME. It should be emphasized that these members do not represent the companies they work for but are expected to make decisions based on their own professional judgement. Page 1 of 6 ST0408822 5T0408823 WHAT DOES THE B31.3 COMMITTEE DO? - The Committee usually meets three times each year. Meetings last about three days and are open to interested-parties. Addenda, inquires and code cases are considered and published if approved. Approval need to be only by general consensus and not by unanimity. SCOPE OF ANSI B31.3 - The scope of B31.3 is clearly stated in paragraph 300.1 which is included in Attachment 2. An estimated 80% of all piping done within the Texas Division falls within the scope of B31.3'. One may generally say that it applies to all process and utility piping except: 1. Refrigeration piping designed under B31.5, 2. Piping associated with boilers which is within the scope of the ASME Boiler and Pressure Vessel Code, 3. Cross-country lines outside the plant confines, 4. Plumbing and sewers, 5. And fire protection systems designed in accordance with other fire protection standards. Special consideration is given to Category D, Fluid Service (non-flammable, non-toxic, 150 psig or less and temperatures -20F to 360F) and Category F, Fluid Service (vary toxic products). OTHER ANSI PIPING STANDARDS - A list of other more commonly used ANSI piping standards is included as Attachment No. 3. Copies of these standards are kept on file by the Engineering Department Mechanical Section in B-2401 and are available for check-out. B31 SERIES B31.1 (Power Piping) is applied in the design of power boilers and related piping and is used in conjunction with the ASME Boiler and Pressure Vessel Code to be explained later. Page 2 of 6 ST0408823 sm08824 B31.4 (Liquid Petroleum Transportation) and B31.8 (Gas Transmission and Distribution) are most often applied by the Petroleum Operations Department in the design of cross-contry lines. Department of Transportation Regulations Part 192 and 195 which are mandatory laws also apply in this area. B31.5 (Refrigeration Piping) is often used in the design of refrigeration piping in lieu of B31.3. B36 SERIES - This series of standards deals with methods of pipe manufacture. B16 SERIES The B16 series sets forth standards for welded, flanged and screwed pipe fittings. B16.20 and B16.21 also deal with gaskets. These standards cover such things as size, marking, materials, dimensions, tolerances and tests for pipe fittings. They are also our source for pipe fitting pressuretemperature ratings. The user should be aware that ANSI B16.5-1973 has highei pressure-temperature ratings than the 1968 edition on which our Spec Book 4B, pressure-temperature ratings are based. The 1973 edition was never officially approved and should not be used. A copy of pertinent ANSI Standards is kept on file in B-2401 by the Engineering Department Mechanical Section. They are available for check-out. ASTM - AMERICAN SOCIETY FOR TESTING AND MATERIALS ASTM was founded in 1898 as a scientific and technical organization concerned with the development of standards relating to the characteristics and per formance of materials and products. It has 128 technical committees. ASTM Standards are published in 48 parts or books, some of which pertain to piping. Concerning piping, these standards cover such things as chemical analysis, markings, weights, thicknesses, strength, method of manufacture and tests. They do over lap the ANSI B16 and B36 series in some areas but do not address the matter of pressure-temperature ratings for fittings. ASTM designations Page 3 of 6 ST0408824 are common in ANSI and other standards. All 48 ASTM books are kept by Benny Howard in the Engineering Department Specifications Section, B-2401. A complete set of standards is also kept by the Dow Library. MSS-SP - MANUFACTURERS STANDARDIZATION SOCIETY OF THE VALVE AND FITTINGS INDUSTRY - STANDARD PRACTICES These publications, commonly referred to as Standard Practices, were developed by manufacturers of pipe fittings in an effort to standardize fitting dimensions. Consequently, they deal primarily with the dimensional aspects of fittings. They do overlap the ANSI B16 series in their coverage. Pertinent MSS Standard Practice are kept on file by the Mechanical Section, B-2401. API - AMERICAN PETROLEUM INSTITUTE API was established in 1919. The organization promotes safety in the Petroleum Industry and in so doing has published numerous standards involving steel pipe, and fittings. The three most common API pipe designations found in Dow Specifications are: API 5L - Seamless and welded steel line pipe. API 5L is often used as a joint or companion designation with ASTM A-53 in our Dow Specs. API 5LS - Spiral-weld line pipe API 5LX - High-test line pipe API Pipe Standards are kept by the Dow Library. AWMA - AMERICAN WATERWORKS ASSOCIATION AWWA was founded in 1881. As its name implies, the organization is dedicated toward improvement of the materials and equipment utilized in water service. Page 4 of 6 ST0408825 ST0408826 These standards are most widely used in municipalities but could be utilized in the chemical industry when construction involves: fire hydrants, water meters, cast iron and ductile iron pipe, concrete lined pipe, or asbestos-cement pipe. Several of these standards are kept in the Dow Library. ASME - BOILER AND PRESSURE VESSEL CODE This code covers the materials, design, fabrication, inspection and stamping of boilers, pressure vessels and associated piping. The two most commonly used sections of the code are Section I (Power Boilers) and Section VIII (Pressure Vessels). SECTION I - POWER BOILERS Included as Attachment 4 is the Preamble to Section I. The Preamble states the scope of Section I and defines "boiler" and "external piping" in some detail. In general, a boiler may be considered to be any fired or unfired steam generating unit including superheaters, economizers and other pressure parts connected directly to the boiler with no intervening valves. A pressure vessel in which an organic fluid is vaporized by application of heat resulting from combustion of a fuel shall also be considered a boiler. External piping is that piping extending from the boiler and including the first or second valve as shown in Attachment 5. External piping is designed in accordance with ANSI B31.1 (Power Piping). v The State of Texas has a "boiler law" which covers the design, construction, operation and inspection of boilers. The "boiler law" adopts ASME Section 1 Page 5 of 6 ST0408826 and in effect makes it law. All boilers must be designed in accordance with Section 1 and stamped. SECTION VIII - PRESSURE VESSELS This section covers the design of pressure vessels and attaching pipe fittings. The State of Texas does not at present have a pressure vessel law but may in the near furture. Common sense and good business practices dictate that all pressure vessels (larger than 6" in diameter and operating above 15 psi) should.be constructed per Section VIII and that vessels in critical services should be code stamped for liability reasons. Some advocate that all vessels be code stamped. ST0408827 DMT/jr 9-26-77 Page 6 of 6 ST0408827 5T0408828 Att-MLVAWVEIHT (AU31 i Foreword The need for a national code for pressure piping became increasingly evident from 1915 to 1925. To meet this need, the American Standards Association initiated project B31 in March 1926, at the request of The American Society of Mechanical Engineers and with that society as the sole administrative sponsor. Because of the wide field involved, Sectional Committee B31 was composed of representatives of some 40 different engineering societies, industries, government bureaus, institutes, and trade associations. After several years work, the first edition was published in 1935 as an American Tentative Standard Code for Pressure Piping. To keep the code abreast of current developments in piping design, welding, stress computa tions, new dimensional and material standards and specifications, and increases in the severity of service conditions, revisions, supplements and new editions of the code were published as follows: B31.1 --1942 American Standard Code for Pressure Piping -- 1942 Procedure established for handling interpretation of code requirements. B31.1a --1944 Supplement 1 B31.lb-1947 Supplement 2 B31.1 --1951 American Standard Code for Pressure Piping B31.la-1953 Supplement 1 to B31.1-1951 B31.1 --1955 American Standard Code for Pressure Piping In 1952 a new section of the code was published to cover Gas Transmission and Distribution Piping Systems. In 1955, after a review by B31 Executive and Section Committees, a decision was made to develop and publish other industry sections as separate code documents of the American Standard Code for Pressure Piping. The first edition of Petroleum Refinery Piping was published as ASA B31.3-1959, superseding Section 3 of B31.1-1955. Two subsequent editions were published: ASA B31.3-1962 and ASA B31.3-1966. In 1967, the American Standards Association was reconstituted and reorganized, and its name was changed to the United States of America Standards Institute. In 1969. the Institute changed its name to American National Standards Institute, and the sectional committees were named standards committees. Following approval by the B31 Standards Committee, public review and approval by the secretariat, a new edition, designated ANSI B31.3-1973 and the following partial revisions were issued: B31.3a-1973 B31.3a-1975 B31.3b-1974 B31.3c & d-1975 _A code for Chemical Plant Piping, designated ANS1B3JL6, was under preparation but not ready for issue in 1974. While B31.6 was in preparation. Code Case No. 49 instructed designers to use B31.3 requirements for chemical plant piping. It was then decided, rather than publish two Code Sections, to combine the requirements of B31.3 and B31.6 into a new edition designated ANSI -B31.3. with the title changed to Chefliicfl Plant and Petroleum Refinery Piping. Following approval by the B31 Standards Committee and the secretariat, and after public review, this ANSI B31.3-1976 was approved by the American National Standards Institute on December 10,1976. in ST0408828 AttACv\mekit 2 AMERICAN NATIONAL STANDARD CHEMICAL PLANT AND PETROLEUM REFINERY PIPING ANSI 831J-1976 300(e) (4) Hazards from instability of contained fluids, or their reactivity with piping materials or other materials such as gaskets, packing, lubricants, and contaminants are not defined or dealt with speci fically in this Cade. The designer is cautioned to consider and make allowance for temperature and pressure effects from reaction, and for properties of any reaction or decomposition products. 300.1 Scope 300.1.1 Content and Coverage This Code prescribes minimum requirements for the materials,design, fabrication, assembly,erection,exam ination, inspection and testing of piping systems sub ject to pressure or vacuum. Except as excluded in 300.1.4, this Code covers all piping within the property limits of facilities engaged in the processing or handling of chemical, petroleum, or related products. Examples are: a chemical plant, petroleum refinery, loading terminal, natural gas processing plant (including liquefied natural gas facilities], bulk plant, com pounding plant, or tank farm. See Figure 300.1.1 for a diagram illustrating the scope of ANSI B31.3 pipingPiping for gases (including air) not now included within the scope of any existing Section of the Code shall be designed, fabricated, inspected and tested in accordance with the requirements of this Code when the piping is in plants, buildings and similar facilities not otherwise within the scope of this Code. 300.1.2 Fluid Services This Code applies to piping systems handling all fluids, including fluidized solids, and to all types of service including raw, intermediate, and finished chemicals, oil and other petroleum products, gas, / steam, air, water, and refrigerants, except as provided in 300.1.3 or 300.1.4. Only Category D and Category M fluid services as defined in 300.2 are segregated for special consideration. 300.1.3 Refrigeration Unit Fifing Package refrigeration unit piping shall be designed and constructed in accordance with ANSI B31.3 or ANSI B31.5. 300.1.4 Exclusions This Code excludes the following: (a) Piping systems designed for internal gage pressures at or above zero but less than 15 psi (0.1 MPa), provided the fluid handled is non-toxic and not damaging to human tissue as defined in 300.2, and its design temperature is in the range of -20 F (-29 C) to 360 F (182 C) inclusive; (b) Those portions of steam, feedwater, blowoff, or other piping which are designed and con- structed in accordance with ANSI B31.1 and are subject to ASME Code1 Section I inspection and stamping. (c) Tubes, tube fittings, and headers for fired heaters, including connections for external piping; (d) Pressure vessels, heat exchangers, pumps, and other fluid handling or process equipment, in cluding internal piping and connections for external piping; (e) Piping located on company property which has been set aside for pipelines conforming to ANSI B31.4 or ANSI B3I.8, or applicable governmental regulations; (f) Plumbing and sewers; (g) Fire protection systems constructed in compliance with insurance underwriters' or other recognized fire protection engineering standards. 300.2 Definitions Some of the terms relating to piping are defined below. Terms relating to welding which agree with AWS Standard A3.0 are marked with an asterisk. Other welding terms given either are not included in AWS A3.0 or require definition here with specific reference to piping. For welding terms used in this Code but not shown here, definitions in accordance with AWS A3.0 apply. Air-Hardened Steel -- A steel that hardens during cooling in air from a temperature above its transfor mation range. Allowable Stress - See "Stress Terms Frequently Used." Anneal Heat Treatment -- See "Heac Treatment." Arc Cuffing -- A group of cutting processes where in the severing or removing of metals is effected by melting with the heat of an arc between an electrode and the base metal. (Includes Carbon-Arc Cutting, Metal-Arc Cutting, Gas Metal-Arc Cutting, Gas Tungsten-Arc Cutting, Plasma-Arc Cutting, and Air Carbon-Arc Cutting.) See also Oxygen-Arc Cutting. TArc Welding - A group of welding processes wherein coalescence is produced by heating with an arc or arcs, with or without the application of pres sure and with or without the use of filler metal. Assembly - The joining together of two or more piping components by bolting, welding, screwing, 1 ASME Code references here and elsewhere in this Code are to the ASME Boiler and Pressure Vessel Code and its various sections as follows: Section I -- Power Boilers Section V - Nondestructive Examination Section VIII -- Pressure Vessels (Divisions 1 and 2) Section IX - Welding Qualifications .ST0408829 ST0408829 At'^ACL'vA^'&ut Av B31.1 - 1973 - Power Piping B31.2 - 1968 - Fuel Gas Piping B31.3 - 1973 - Petroleum Refinery Piping B31.3b - 1973 - Summer 1974 Addenda to Pet. Ref. Piping B31.4 - 1971 - Liquid Petroleum Transportation Piping System. B31.5 - 1974 -- Refrigeration Piping B31.7 - 1969 - Nuclear Power Piping B31.7b - l97i - 1970 Addenda to Nuclear Piping B31.8 - 1968 - Gas Transmission & Dist. Piping Systems B36.3 - 1969 - Seamless Carbon Steel Pipe for High-Temp, Service. B36.5 - 1964 - Elect.-Resistance-Welded Steel Pipe B36.9 - 1969 Elect-Fusion(ARC) Welded Steel Pipe B36.10 - 1970 - Wrought Steel fi Wrought Iron Pipe B36.ll - 1964 - Elec-Fusion-Welded Steel Pipe for High-Pressure Service B36.19 - 1965 - Stainless Steel Pipe B36.28 - 1967 - Seamless Cold-Drawn Low-Carbon Steel Heat Exchangers and Condenser Tubes B36.56 - 1969 - Seamless Carbon Steel Pipe for . Process Piping B36.60 - 1969 - Electric-Welded Low-Carbon Sfeeel Pipe for the Chemical Industry ST0408830 ST0408830 Attmiv\sae:k->t 3 B B16.1 - 1967 - Cast Iron Pipe Flanges & Flange Fittings B16.3 - 1971 - Malleable-Iron Threaded Fittings Bi6.4 - 1971 - Cast-Iron Threaded Fittings B16.5 - 1973 - Steel Pipe Flanges, Flanged Valves & Ftgs. B16.9 - 1971 - Factory-Made Wrought Steel Buttwelding Ftg B16.10- 1973 - Face-to-Face and End-to-End Dimensions & Ferrous Valves B16.11 B16.12 1973 - Forged Steel Fittings, Socket-Welding & Threaded 1971 - Cast-Iron Threaded Drainage Fittings i tS880*i0lS B16.14 - 1971 - Ferrous Pipe Plugs, Bushings S Lock Nuts with pipe threads. B16.15 - 1971 - Cast Bronze Threaded Fittings B16.16 - 1372 - Cast Bronze Solder Joint Press. Fittings B16.20 - 1973 - Ring-Joint Gaskets and Grooves for Steel Pipe Flanges B16.21 - 1962 - Nonmetallic Gaskets for Pipe Flanges B16.22 - 1973 - Wroght Copper and Bronze Solder-Joint Pressure Fittings. B16.25 - 1972 - Buttwelding Ends B16.26 - 1967 - Cast Bronze Fittings for Flared Copper Tubes B16.27 - 1962 - Plastic Insert Fittings for Flexible Polyethylene Pipe B16.28 - 1964 - Wrought Steel Buttwelding short Radius Elbows and Returns B16.29 - 1973 - Wrought Copper and Wrought Copper Alloy Solder-Joint Drainage Fittings' B16.30 - 1969- Unfired Pressure Vessel Flange Dimension B16.34 - 1973 - Steel Butt-Welding End Valves i j j j i ST0408831 ZC880*?0iS AlT^Cl-UAElUT 4- S*CT\Op A. Povg-se BO\LK!t-S) PREAMBLE This Code covers rules jor construction of power boilerselectric boilers,*2 *miniature boilers* and hightemperature water boilers4 to be used in stationary service and includes those power boilers used in locomotive, portable, and traction service. Reference to a paragraph includes all the subparagraphs and sub divisions under that Paragraph. The Code does not contain rules to cover all details of design and construction. Where complete details are not given, it is intended that the manufacturer, subject to the approval of the Authorised Inspector, shall provide details ofdesign andconstruction which will be as safe as otherwiseprovided by the rules in the Code. The scope of thejurisdiction ofSection I applies to the boilerproper and to the boiler externalpiping. Superheaters, economizers, and other pressure parts connecteddirectly to the boiler without intervening valves shall be considered as parts ofthe boilerproper; and their construction snail conform to Section i rules. Boiler external piping shall be considered as that piping which begins where the boilerproper terminates at (I) the first circumferential joint for welding end connections; or (2) the face of the first flange in bolted flanged connections; or (3) thefirst threadedjoint in that type of connection; and which extends up to and including the valve or valves required by this Code. ASM Code Certification (including Data Forms and Code Symbol Stamping), and/or inspection by the Authorized Inspector, when required by this Code, is required for the boiler proper and the boiler external piping. Construction rules for materials, design, fabrication, installation, and testing of the boiler external piping are contained in ANSI B31.1--Power Piping. Piping beyond the valve or valves required by Section I is not within the scope of Section I. and i; is not rhe intent that * Power boiler--a boiler in which sienm or other vajH>r 15 generated at a pressure ofmore than fifteen (15)psi. 2Electric boiler-- a power boiler or a fii^h- temperature water boiler in which the source of heat is electricity *Miniature- boiler--o power boiler or a hi^h-tempcrature water boiler in which the limits specified in PMB-2 tire nos exceeded. 4High temperature water boiler--a water boiler intended for operation at pressures in excess of 100 psi und'or temperatures in excess of 250 F. the Code Symbol Stamp be appliedto suchpiping or any otherpiping. The material for forced<irculation boilers, boilers with no fixed steam and water line, and high-temperature water boilers shall conform to the requirements of the Code. All other requirements shall also be met except where they relate to special features of con struction made necessary in boilers ofthese types, and to accessories that are manifestly not needed or used in connection with such boilers, such as watergages, water columns, andgage cocks. Reheaters receiving steam which has passed through part of a turbine or other prime mover and separately fired steam superheaters which are not integral with the boiler are considered fired pressure vessels and their construction shall comply with Code requirements for superheaters, including safety devices. Piping between the reheater connections and the turbine or other prime mover is nut within thescope ofthe Code. / A pressure vessel in which steam is generated by the application of heat resultingfrom the combustion offuel (solid, liquid, orgaseous) shall be classed as afired steam boiler. Unfired pressure vessels in which steam is generated shall be classed as unfired steam boilers with the following exceptions; (1) Vessels known as evaporators or heat exchangers. (2) Vessels in which steam is generated by the use of heat resulting from operation of a processing system containing a number ofpressure vessels such as used in the manufacture ofchemicalandpetroleumproducts. Unfired steam boilers shall be constructed under the provisions of Section l or Section VIII. Expansion tanks required in connection with hightemperature water boilers shall be constructed to the requirements ofSection 1 or Section VIII. A pressure vessel in which an organicfluid is vaporized by the application of heat resulting from rhe combustion of fuel (solid, liquid, or gaseous) shall be constructed under the provisions of Section-1. Vessels in which vapor is generated incidental to the operation of a processing system, containing a number ofpressure vessels such as used in chemical and petroleum manufacture, are not covered by the rules ofSection /. ST0408832 AMERICAN NATIONAL STANDARD POWER PIPING 5*^*t lmd*<ion At'tAC.HKMEvJT S' ANSI B31.1-1977 EDITION FIG. 100.1.2.B ST0408833 --Piping and Joint -- ASME Section I jurisdiction O-----Piping and Joint --ANSI B31.1 jurisdiction Not: Only one drain valve may be required whan the valve It not Intended for blow- off purpoeet when die boiler it under prenure (tee Pere 122.1.4) PIG. 100.1-2,B CODE JURISDICTIONAL LIMITS FOR PIPING DRUM TYPE BOILERS 3 ST0408833 ST0408834 "U ia ST0408834 ST0408835 TYPES OF PIPE Page 1 through 9 contain a visual and verbal description of the different manufacturing processes that are used to make pipe. Each of the methods do not however make an equivalent pipe. There is different joint factors (E) that lowers the useful limit of the pipe. This is due to the type of weld that is used to make the longitudinal seam. Seamless would be the strongest because it has no seams. The Furnace Lap and Butt Weld is the weakest and there are some additional limitations placed on it. Pipe is made in a larger size, say 10", and reduced by sizing dies to the smaller diameters. This reduces the amount of equipment that is needed for manufacturing. PIPE SPECIFICATION Pages 10 through 13 contain a summation of data on some specific specifi cations that are contained in the ASTM and API publications. ASTM A-53-73 is a general spec that covers the various manufacturing methods, chemical makeup, strength, quality control and testing, and the physical dimensions. "Types" refer to manufacturing method and "Grades" refer to chemical makeup and strength characteristics. Type S is seamless, Type E is electric welded and Type F is furnace welded pipe. Grade A is more ductile, has a lower minimum yield strength, and should be used for close coiling and cold bending while Grade B has higher yield strengths and should be used for higher pressure and collapse application. Page 1 of 4 ST0408835 ST0408836 ASTM A-106 specificies seamless carbon steel for high temperature service whereas ASTM A-120 specifies black and hot dipped zinc coated (galvanized) welded and seamless steel, pipe for ordinary uses. The A-120 pipe has fewer quality control tests and is restricted by Dow and ANSI Codes to Category D, fluid services. API 5L is essentially equal to ASTM A-53 except in some cases its specifi cations are a little tighter or more specific. III. PIPE LIMITATIONS Page 14 contains definitions of fluid services. Limitations on piping components are included on page 15. It covers where certain pipe can and can not be used. IV. BOOK 4B - PIPE Pages 16 and 17 are a cross reference of the Dow Numbering system with ASTM and API specifications. It is important when specifying pipe that the correct Dow Number is selected because one could include an undesirable pipe or exclude an acceptable alternate pipe. Page 18 is the first page of Dow Spec 48-701 on Pipe. Note that P-3B pipe is the same as P-3 except it specifies Grade B and excludes Grade A. It gives the diameters of the pipe and the temperature limitations. From this you can calculate your maximum pressures for these standard weight pipes. V. SIZE OF PIPE The Table found on page 19 contains the nominal wall thickness for schedule numbers. Footnotes at the bottom describe standard weight, extra strong, and double extra strong. You will notice that the I.D. is always varied instead of the O.D. Common sense would tell us that this was done so that Page 2 of 4 ST0408836 ST0U08837 a standard set of pipe dies could be used for cutting threads in the lower diameters. Page 20 calls out the lengths and end finishes that are available. If uniform lengths are specified then it will cost extra because another quality control step has to be added. CALCULATIONS Page 21 contains the information required to calculate thickness for various types and grades of pipe at different operating conditions. Corrosion allowances are generally 0.1 inches for carbon steel pipe, but may.be increased if the fluid service dictates higher allowances. The example on page 22 points up the need to investigate thoroughly when Type S or E is specified and the calculated thickness is near one of the standard schedule thickness found on page 19. The difference in price between Schedule 20 and 30 may be significant if a lot of pipe is being considered. Straight pipe under external pressure, should use ANSI 31.3-304.1.3. The pressure design thickness, t, for straight pipe under external pressure shall be determined in accordance with U6-28, Section VIII, Division 1, of the ASME Code, using the basic allowable stress at the design temperature (see Appendix A, Note 16 of ANSI 31.3). For L, use the longest length between any of the following: flanges, stiffening rings, caps, and centerline instersections of elbows, miter bends, and ANSI B16.9 tee fittings; for branch lines, the take off point of the branch. When the use of stiffness is indicated, the design shall be in accord with UG-29 and UG-30, Section VIII, Division 1, of the ASME Code. Page 3 of 4 ST0408837 VII. ALLOY AND NON-METALLIC PIPING There are numerous alloy systems that are specified under ASTM, API, and ANSI publications. They will in general be treated in the same manner as the carbon steel discussed above. Extra care should be utilized when specifying alloys. Welding specifications become more important. Guidelines for corrosion allowances vary from none to significant thickness. VIII. REFERENCES Information was obtained from the following sources: A. 1976 Annual Book of ASTM Standards, Steel-Piping, Tubing, Fittings - Part 1 B. ANSI B31.3-1976 - Chemical Plant and Petroleum Refinery Piping C. Pipe Basics Manual, United States Steel, Publication #ADUSS 44-5405-07 D. NAVCO Pipihg Datalog (1966) E. Crane - Technical Paper No. 410 (Flow of Fluids) F. API Spec 5L G. Handbook for Piping Designers and Field Inspectors - Benny Howard H. Engineering Specifications - Book 4B '8C880*l0XS JEC/jr 10/11/77 Page 4 of 4 ST0408838 I ST0408839 z tn ow ar<2t n --o oc>.^. n>N l^s s * s. ro3o>r0Wo jvO^i*. J--C >> Vi ,* aQ>- tc* 2a, a. j3 a) oiw iff xC5aj> 2c*>> 5 Ta7? o to S Io^5E* o . cio 2 -2^1 Q> a> ro M -c 0><D 0 l :g E cx ST0408840 ST0408840 K. Eu rSToJ>iS 8o3 all fO 2t> *0ofot>>5>x*^o>^02--*s TcuJ c *5 " a 3^oa i|3I c5O *("A j--.Ocz wm W" --oto Z n 4) a0O>i TO Ojc c 3 ? c t3 y C Q. " W 'O0) h. ? O C aJ 2 xSE- Ew vv%i j * 2 *2 0>cn.8O Hi t> E >o 5 "IS tt o " a o _j--e_ a_ <6a o * </> -- Q ?:o O? o -OC O * 5 rt ooac ! OT3 " t i>sO?'*!! 5O_ jJai S2-jSo ?2 = "= ! o E ! o5 ; Ha ST040884I ST0408841 sc 5idu22vJns J, cO f c0t> ,,JS 0-5 oci So w jc J2S 'a5 '*"* >sTJ *oko-. c a2 o ic -j1ao;0> <n _wc e ToO>W m* oJ >(0 C0> ~< -c*>f -cJCOoC 2euId|S*u0 j-IZ O T3* Sf H c ' -O p = -- o t> 1 xa>: tz r<2 x !i H u i o 2 (S9 3o CL o XO * >. s J5 o -oQ 12 T3 IoA Ca "O .C * a> =<9 '"Ogj '5* t w o --. wQ> D, 0 >O g2 o. S-E-o cl jz a . Jt--= -JC- Nw ST0408842: ST0408842 v> 2 c e xo: ?uOca o'ztor *oc BZ fot.i aocol ?cS 'J am vg "3- TOa>>l 3 ** ^er S u. ~<A oN -*cC=m<oo0 o3(T V ^M 62 sis fSS " T3 O X 2 TJ **ft . Q>J <Co *O0 2"^.C39^ l i 1 The last terming atond, called a tin poss section, finishes the rounding procedure and contours the edges 0 1 the strip for ST0408843 I ST0U088U4 ST0408844 ST0408845 ST0408846 9 c/> H O o GO GO *T c0o) .-c0o1 *o<a> i*o jj T, 40 ^S_ a) a 5S o o^ Q0..*^o0 as. 1B Ho ST0408847 Specification Scope Kinds of Steel Permitted For Pipe Material Hot-Dipped Galvanizing Permissible Variations in Wall Thickness Chemical Requirements Tensile Requirements Hydrostatic Testing A53 Sizes V6'-26' Std., XS and XXS, A.N.S.I. Schedules 10 through 160 Covers seamless and welded BLACK and hot-dipped galvanized nominal (average) wait pipe for coiling, bending, flpngtng and other special purposes and is suitable for welding. BUTTWELDED pipe is not intended for flanging (roti back operation to form flange using pipe wall). Purpose for which pipe is intended should be stated on order. Open-hearth Electric-furnace Basic-oxygen Sets standards for coating of pipe with zinc inside and outside by the hot-dipped process. Weight of coating must not average less than 1.8 oz. per square foot and not less than 1.6 oz. per square foot. Same as A120. &Type S (seamless pipe) Type E (electric welded) . Composition. Max., % C Mn P S Open-hearth, electric.furnace or basic-oxygen: Grade A Grade B 0.25 0.30- 0.95 1.20 0.05 0.05 0.06 0.06 Type F (furnace-welded pipe) ' Composition. Max.. 56 ps Open-hearth, , electric-furnace. or basic oxygen .... .... 0.08 0.06 Bultwelded (furnace-welded) Tensile Strength min., ps................................ ..................... Yield Point mm., psi.................................................................. 1Seamless or Eleciric-Weld Tensile Strength min., psi............................... ..................... Yield Point mm., psi................... .............................................. O.H., Basic Oxygen or Elec. Furn. 45,000 25,"000 Grade B 60.000 35.000 " Hydrostatic inspection test pressures for plain end and threaded and coupled pipe are specified. Hydrostatic pressure shall be maintained for nci less than 5 seconds (oral) sizes of seamlessand electric-weld pipe. Permissible Variations in Weight* per Foot Permissible Variations in Outside Diameter Mechanical Tests Specified Number of Tests Required Lengths Required Markings on Each Length (On Tags attached to each Bundle in case ol Bundled Pipe) General Information For Extra Strong and lighter wall thicknesses Plus or Minus 5% For heavier than extra strong wall thicknesses Plus or Minus Same as A120. .* Tensile Test--Transverse required on EW sizes 8}#* and larger. Bending Test--(Cold) Std. and XS-2* and under. XXS-1 *4' and under. Degree of Bend Diameter of Mandrel For Normal A53 Uses For Close Coiling 90 180 Flattening Test 2'/>* and larger Std. and XS. (Not required for XXS pipe). 12 x nom. dia. of pipe 8 x nom. dia. of pipe Seamless and Buttweld--Bending, flattening tensile on one length ol pipe from each lot of 500 lengths or less ol a size. Electric-Weld--8ending and tensile on one length of pipe from each lot of 500 lengths or less of a size. Electric-Weld--Flattening on both crop ends of each length. (Coil, in case of multiple lengths.) Same as A] 20. (Lengths longer than single random, heavier wall than XS subject to negotiation.) Roiled, Stamped or Stenciled Name or brand of manufacturer. Kmdofprpe.thatis, furnace bultwelded, EW-A. seamless B. etc. XS--for extra strong. XXS--for double extra strong. ASTM A53. Also necessary to indicate when ctectric-furnace or basic-oxygen is used. Length ot pipe. Couplings--Applied handling tight. Couplings. 2' and smaller straight tapped, other sizes taper tapped. (Line pipe couplings may be specified.) Thread Protection--Same as specified under A120. End Finish (unless otherwise specified) Std. or XS. or wall thicknesses less than 0.500 in. (excluding XXS): Plain end beveled. All XXS and wall thicknesses over 0.500 in.: Plain end square cut. i 07 -H O zr* o ao 00 m ST0408848 Specification Scope Kinds of Steel Permitted for Pipe Metarial Hot-Dipped Galvanizing Permissible Variations in Wall Thickness Chemical Requirements Tensile Requirements Hydrostatic Testing Permissible Variations in Weights per foot A106 Sizes ys"--26" A.N.S.I. Schedules to 160 (oiiwrsiiMtubrjciio inquiry) ' Covers SCAMLESS carbon steel nominal wall pipe tor high-temperature service, suitable for bending, flanging and similar forming operations. V?'Sizes 1 and under may be either hot finished or cold drawn. Sizes 2" and larger shall be hot finished unless otherwise specified. Killed open-hearth Electric-furnace Basic-oxygen Not covered in specification. Same as A120. ^.................................... %Manganese ............................. Phosphorus, max. %............... ....................................... %Sulfur, max. ........................... ....................................... ...................Silicon, min. %........................... Grade A 0.25 0.048 0o..0io58 Grade B 0.30 0.29 to 1.06 0.048 00..01508 *Grade C 0.35 0.29 to t.06 0.048 0.058 0.10 Seamless ........................................ Yield Point min., psi ........ ........................;............ Grade A 48,000 30,000 Grade B 60,000 35,000 Grade C 70,000 40,000 Inspection test pressures produce a stress in the pipe wall equal to 60% of minimum specified Yield Point at room temperature. Maximum Pressures are not to exceed 2500 psi for sizes 3" and under, and 2800 psi for the larger sizes. Pressure is maintained for not less than 5 seconds. zf*yfor Schedules 120 and under--Weight of length shall not vary more than 6.5% over and 3.5% under. For Schedules heavier than 120--Weight of arvv length shall not vary more than 10% over and 3.5% under. NOTE--Size 4' and smaller--weighed in lots. Larger sizes--by length. Permissible Variations in Outside Oiam&tor Mechanical Tests Specified Number of Tests Required Lengths Required Markings On Each Length (On Tags attached to each Bundle in case of fiundled Pipe) Outside Diameter at any point shall not vary from standard specified more than-- Sizes Over Under 1 VS" and smaller 2*-4* 5'-810'.18' fe' /.' *' ia,' /' v* V` 20'-24' Vi' Tensile Test--All sizes--either transverse or longitudinal acceptable. Bending Test (Cold)--2' end under. Degree of Bend- Diameter of Mandrel For Normal A106 Uses For Close Coiling 90 ISO 12 x nom. dia. of pipe 8 x nom. dia. of pipe Flattening Test--2" and larger. Tensile Bending Flattening S'and smaller 6'and larger 2'and smaller 2' through 5' 6'and over On One Length from Each Lot of 400 orless 200 orless 400 orless 400 orless 200 orless Lengths required shall be specified on order. No "jointers" permitted unless otherwise specified If no definite lengths required, following practice applies: Single Random--!6'-22'--5% may be 12'*16\ Double Random--Minimum length 22', Minimum average 3S'-- 5% may lG'-22\ Rolled, Stamped or Stenciled Manufacturer's privale identifying mark. AI06 A A106 B. or A106 C. LengTh ol pip"' pre5sufe' ANSI schedule number. Weigh) per loot f4* and larger). Additional "S" if tested to supplementary requirements. General Information. Unless otherwise specified, pipe furnished with plain ends. Surface finish standards are outlined in specification. c/> --< o c* o CO CO VO ST0408849 Specification Scope Kinds of Steel Permitted For Pipe Material Hot-Dipped Galvanizing Permissible Variations in Wall Thickness' Chemical Requirements Tensile Requirements Hydrostatic . Testing Permissible Variations in Weights per Foot Permissible Variations in Outside Diameter A120 Sizes 16* Std., XS and XXS Covers BLACK and hot-dipped GALVANIZED WELDED and SEAMLESS nominal (average) wall pipe for ordinary uses in slearn, gas and air lines. Pipe to this specification not intended for close coiling, bending, or high-temperature service. Intended primarily to cover pipe purchased mainly from distributors' stocks. Open-hearth Electric-furnace Bas<c-oxygen Sets standards for coating of pipe with zinc inside and outside by the hot-dipped process. Weight of coating must not average less than 1.8 02. per square foot and not less than 1.6 oz. per square foot. Minimum wait thickness at any point shall not be more (hart 12.5% under nominal wall specified. No specific chemical requirements listed except that steel for welded pipe shall be of soft weldable quality. No physical properties specified. Prescribes hydrostatic inspection test pressured for standard, extra strong, and double extra strong pipe in pounds per square inch. For Standard and Exlra Strong shall not vary more than plus or minus 5% from prescribed weights shown in A120 Tables 1, li & III. For walls heavier than extra strong and lor double extra strong shall not vary more than plus or minus 10% from prescribed weights shown in A120 Table IV. Outside Diameter at any point shall not vary from standard specified more than-- For ixh' and Smaller Sizes* over xfn* under For 2* and Larger Si2#s l%over 1% under Mechanical Tests Specified No mechanical tests specified except hydrostatic. Stripping test to check weight of line coaling required. Number of Tests Required Weight of Zinc Coating Test One specimen from each end of one length selected at random from each lot of 500 lengths or less of a size. Hydrostatic Test Each length shall be subjected to hydrostatic test, Lengths Standard Weight Single Random--16'-22'--5% may be jointers. If Plain Ends--5% may be 12*-16'. Double Random--Shortest Length 22', minimum average for order 3b\ Extra Strong & Double Extra Strong Single Random--1 2`-22'--5% may be 6'-12\ Double Random (XS and lighter)--Shortest Length 22'. minimum average for order3S'. Required Markings on Each Length (On Tags attached to each Bundle in case of Bundled Pipe) Rolled, Stamped or Stenciled Name or brand of manufacturer. ASt M A1 20. Length of pipe. General Information * Couplings--Applied handling tight. Couplings. 2' and smaller stiaight tapped, other sizes taper tapped. Projection Standard Pipe ll/*p and Smaller .2* to 3Vi' 4' and Over Ocean Shipments Other Shipments R & 0 Pipe Burlap 'None Metal Protectors None Metal Protectors * Metal Protectors Ocean Shipments Other Shipments Burlap None Metal Protectors Metal Protectors Metal Protectors Metal Protectors o> --i O O 00 ao cn o ST0408850 Specification Scope Kinds of Steel Permitted For Pipe Material Hot-Dipped Galvanizing Permissible Variations in Wall Thickness Chemical Requirements Tensile Requirements Hydrostatic Testing Permissible Variations in Weights per Fool API 5L Sizes %"-42" Covets WELDEO anti SEAMLESS pipe suitable for use in conveying gas. water, and oU in both the oil and natural gas industries. Seamless or Electric-Weld Open-hearth Electric-furnace Basie-oxygen Buttwelded Uectoc-furnace open-health nr basic-oxygen (either Class 1 or Class II)* Class II is rephosphorized--is easier to thread. May be ordered galvanized to requirements of ASfM A120. Tolerances on wall thicknesses shall net be more lhan those listed at right from the nominal walls specified. Seamless gu* smaller 3* 3VS`Uiru24' pirn 20% 18% I5R Minus ;iIz2Vh5j55 Welded 216'and smjller 3* 3V6 '--18* 20'and larger Plu, l2ui%0s% \i% Minut mm%% 1to2y*.54 Electric-turnace, open-hearth or basic-oxygen Carbon, Manganese, Phosphorous, Sulphur, % Mai, %Mn. %Max. % Mai. Buttwelded % %Carbon, Manganese, Phosphoroua Sulphur. 55 M. % Men. SMLS Grade A SMtS Grade B SMLS A25 Class 1 SMLS A2S Class tl EW and OSA Grade A EW and OSA Grade 8 W A25 Class 1 EW A?$ Class II _ 0.22 0.90 0.27 1.15 0.21 0.30-0.60 0.2% 0.30 0.60 0.21 0.90 0.26 1.15 0.21 0.30 0.60 0.21 0.30-0.60 0.04 0.04 0.045 0.04S-0.0&Q 0.04 0.04 0.045 0.045-0.080 o0..o0s5 0.06 O 06 0 05 0.05 0.06 0.06 Electric-furnace, Opervhearth or basic-oxygen A25 Class 1 A25 Class II 0.21 0.21 0.304.60 0.304.60 0.04$ max. 0.045-0.080 0.060 0.060 Seamless or Etectrjc-Weld (Electric-furnace, Open-Hearth or Basic-Oxygen) Tensile Strength Yield Point Buttwelded Tenail* Strength Min., pit Yield Polht Min., psi Grade A ............................................. .............. Grade B............................................. ............ SMLS or EW Grade A2S Class 1....... ............ SMLS or EW Grade A25 Class II,... ............ 48.000 60,000 45.000 45.000 30.000 35.000 25.000 25.000 ` Electric-furnacje, open-hearth or basic-oxygen A25 Class!................................................ A25 Class II............................................... 45.000 45.000 25.000 25.000 Lists hydiostaltc inspection lest pressures lor all sizes covered by the specification. * Test Pressures are held tor not less Ihan: Seamless (all sizes)--5 seconds Welded (18' end smaller)--5 seconds (20' and la reel)--10 seconds For ejchlengih of Standard Weight, Regular Weight. Extra Strong,and Double Extra Strong--Not more than plus 10% minus 3.5%. For Special Plain End--Hot mote than plus 10% minus 5%. For Carload Lots--Not more than minus 1.75%. Nolo--Sires 4%' OD and smaller may be weighed individually or in convenient lots. Larger sizes by length. Permissible Variations in Outside Diameter Mechanical Tests Specified Number of Tests Required Lengths Required Markings ' on Each Length (On Tagsattachedto each Bundle in case of Bundled Pipe) General Information Outside Diameter at any point shall rot vary from standard specified more than: Sixes Ovor Undor 1%'end smaller- V6* *Atm 2'end lr|er- 1% 1% TenslIeTest Seamless and Buttwelded--All Sizes--Longitudinal Specimens Electric-Weld--6'and smaller--Longitudinal--8'andlarger--Transverse . Bending Test (Cold)--2'and smaller Buttweld. Degree of Bend Diameter of Mandrel For all API Uses 90 12i0Do!prpe On One Length From Each Lot of T,n`ll .V"* 400 or leu Bending f Ihrouth 12 14'and larger Vand smaller BW 200 arte,, 100 or less 400 or less Flattening Mon-Expanded Electric-Weld single lengths crop ends from each length. Threaded & Coupled Pip, Single Random Double Random Shortest Length in Entire Shijn.nl IS'O' 22'0r Shortest Length in 95% of Entire Shipmtnl 18'0' -- Minimum Average Length Entire Shipment -- 35'0' ' Die Stamped or Paint Stenciled (Rolled at Mfgra. Option) Manufacturer's name or mark. API monogram, sire, grade, process of manvlecture. type o(sll, length weight per foot (4* and 13r I#r only). Teitprenure "hen hijher then tabulated (Z end larjer only) NMe-A. jenaral rjle. marking, lor 12' and amaller are die alamp.d, 14 md larfer. stencil,d. Couplings--Applied handling tight. All sues are recessed, taper lapped. Thread Protection (all shipments)-- . 1)4* and Smaller 2*to3H' 4'and Over Burnt* Metal Protector, Metal Prelector, Outside Diameter End Tolerances (plain end pipy) (distance of 4* from each end). fpr 10'and smaller-- Mr'over %*'under for 12'through 20'-- 'A'over /' under ,, . kl 'fa' under Out-of-Roundness Tolerances (distance of 4 from each end). for 22* and larger-- 1% over* 1% undor* based on nominal OD specified. Flattening Test Buttweld: 2% ' and larger. Electric-Weld: All sizes. Multiple Lengths--Crop ends from each length plus 2 intermediate rings. Cold-trpemled Electrlc-Wekf-Ont from , length from ikJi lot of 10O length, or Icis ol each lire. ^ , , t<Mk Buttwelded--One trem length from each tat of 400 or less of each s'24* Note--All sections cut from multiple length ire counted as one. Plain End Pipe R.nHim. Shortest Length In Entire Shipment 1-fl- Shortest Length in 90% of Entire Shipment Minimum Avg. Length Entire Shipment ----- pTS-- Ooublt Random As agreed upon 14'0* 26'3* 40% of average 75% of average 3VQ- lengths in excess of 20'. agreed upon agreed upon Symbols to be Used: Crade Type of Steel* Manufacturing Process CredeA A 8esic-orv,e B0 Ssemlei, 5 Cud, B B Rephoaphomed R tlectriew.ld E (cl It open-hearth) Buttwelded f nRo type marfcin, required for: Open-llearlh in yeamteu or etectric-wetd. End Finish (plain end pipe)-- x IM * end smaller: Square cut or beveled as specified on order 2'end larger: Double extra strong--square cut All othir weiehtx-- 3V Bevel. 1 i j i ! STO<i0885I ST0408851 ST04088S2 SERVICE CATEGORY D FLUID SERVICE 1. NONFLAMMABLE AND NONTOXIC 2. DESIGN PRESSURE 150 PSIG 3. DESIGN TEMPERATURE BETWEEN -20F AND 360F CATEGORY M FLUID SERVICE TOXIC FLUID SERVICE IN WHICH EXPOSURE TO VERY SMALL QUANTITIES OF THE FLUID IN THE ENVIRONMENT CAN PRODUCE SERIOUS IRREVERSIBLE HARM TO PERSONS ON BREATHING OR BODILY CONTACT, EVEN WHEN PROMPT RESTORATIVE MEASURES ARE TAKEN. JEC/jr 10-10-77 ST0408852 AMERICAN NATIONAL STANDARD CHEMICAL PLANT AND PETROLEUM REFINERY PIPING PART 3: LIMITATIONS ON PIPING COMPONENTS ANSI 831 >197* 305 305 PIPE Pipe include* components designated as "tube" or "tubing" in the material specification, when intended for pressure service. 305.1 General Limitation* 305.1.1 Laud* Pipe Listed pipe not limited elsewhere in 305 may be used within the limitations on materials in Chapter III, and on methods ofjoining in Chapter II, Part 4. 305.1.2 Unified Pip* Pipe made to a specification or standard for pres, sore service (published or proprietary) not listed in Appendix A, B, or E, may be used within the limita tions on listed pipe having comparable characteristics, including composition, mechanical properties, meth od of manufacture, and quality control. 305.2 Limitations on Specific Pipe 305.2.1 Pip* Limited to Category D Fluid Service The following .carbon steel pipe shall not be used for other than Category D fluid service API 5L, Furnace Butt-Welded ASTM A53, Type F ASTM A120 ASTM A134 made from other than ASTM A285 plate ASTM A211 made with other than a butt- welded joint 305.2.2 Pipe Limited for Otb*r Than Category D Fluid Service When used for other than Category D Quid service, the following carbon steel pipe shall be appropriately safeguarded: ASTM A134 made from ASTM A285 place ASTM A139 ASTM A211 made with a butt-welded joint 305.2J Pip*for Severe Cyclic Conditions Only the following pipe shall be used under severe cyclic conditions; (a) Carbon Steel Pipe AJT5L, Seamless API 5L, SAW, Factor E 0.95* *The word "listed" as used.in this Code refers to a material -- . component conforming to specification, lijtci in Ap pendix A or B, or to itxndxrdj listed in Appendix E. API 5LX 42, Seamless API 5LX 46, Seamless API 5 LX 52, Seamless ASTM A53. Seamless' ASTMA106 ASTM A15S, Factor E 0.901 ASTM A333, Seamless ASTM A369 ASTM A381, Factor E 0.90* ASTM A524 (b) Lour and Intermediate Alloy Steel Pip* ASTM A1S5, Factor E 0.91? ASTM A333, Seamless ASTM A335 ASTM A369 ASTM A426, Factor E 0.90* ASTM A671, Factor E 1.00* (c) Stamlest Steel Alloy Pip* ASTMA2 68, Seamless ASTM A312, Seamless ASTM A358, Factor E 0.90* ASTM A37S ASTM A430 ASTM A451. Factor E 0.90* (J) Copper and Copper ADoy Pip* ASTM B42 (e) Nickel and Nickel Alloy Pipe ASTM B161 ASTM BUS ASTM BI67 ASTM B407 (fj Aluminum Alloy Pip* ASTM B210, Tempers 0 ana HI 12 ASTM B241, Tempers 0anaH112 ST0L08853 ST0408853 IU MATERIAL 4SJ/APISL SMLS GR 0 STO P-39 X-5TG SCHEDULE* WEIGHT. or wall thickness XX-STG SCH30 SCM0 SCH60 SC Hl20 SCH160 0*250 P- 58 0*312 0*3 75 P-3J8 ~1 0*500 P-4 3d 433/API5L A53/APJ5L A53/AP15L A53/APISL SMLS GR SMlS/EK SMLS/W H.F, EW A/S GR 0 GR A/8 P-3 P-38* P--3* P-12 P-KB P-l P-5 P-5W P--4 8 P-4 P-2B P-2 P-33 P-328 P-32 P-43 A33/AI5L COflT 9W P-7 P-6 AO|5L W GR A/0 AID* SMLS GR B P--278 P-28B P-568 P-219 P-228 P-2* A106 SMLS GR A/8 P-27 P-28 AJ3J SHLS GR 1 <-S0F) P-3SA P--68 A333 SHLS GR 3 (-1S0F1 P-39 p-aio AS87 EW A120 BW A1 34 WELDED A2BS B/C PL P-40 P-68 1 P-69 P-40A P- 32 A A15S WELDED CL-\ GP C-KO P-32C ALLOT AND N0N-F-tCCU5 PIPE onSchedule wall thickness . M A TCP I AL A-312 SHLS SS 7P304 .04X M|N C SCH 5S SCH 10S SCH AOS SCh 80S ; 0* 375 P-45 P-34 * P-3S P-44 ,{ 3/16 REGULAR REMARKS PAS NOT STOCK A-312 SLS SS TP304L A-312 SHLS SS TP316 *04X HIM C P-45L P-45 A P-34L P--34 A -35L P--35 A P-44L P-44A P45L NDT STOCK P45A NOT STOCK A-312 SMLS SS TP316L A-312 SMLS SS T321 *04X MlN C OR P-45AL P--34AL P-35AL P--44AL P45AL NOT STOCK A-312 SMLS SS T 34 7 *04X MIN C P-36 6-37 A-312 WELDED SS TP30* *04X MIN C P-45W P-34W P-35W P--44 W A-312 WELDED SS TP304 .0*% MIN C . P-204 GENERAL GRADE A-312 WELDED SS TP^OAL A-312 WELDED SS TPJ16 *0*r HIN C A-312 WELOEO SS TP316L A-312 WELDED SS TP321 *04X MlN C DR A-312 WELDED SS TP34 7 .0*X MIN C P-45WL P-34WL P-35WL P-44WL P-45AW P-34AW P--35AW P-44AW P-45AWL P-34 AWL P--35AWL P-44AWL P-36W P-37W 8464 SHLS ALLOT 20 8464 WELOED ALLOT 20 0241 SMLS ALUMINUM GR 6061-T6 P-200 P-200W P-4 8 P-2O0A P-200AW P-200BW P-46 P4B SPEC ORDER 92* 1 SMLS ALUMINUM Cf 6063-T6 8241 WELDED ALUM INUM GR 6061-T6 842 SMLS COPPER MO 122 8152 WELDED COPPER NO 122 8333 WELDED HAST 8 100X X-R 8334 WELDED HAST C 100X X-R P-48A P-70 P-71 P--46 A P-209 P--71A. P-718 P-47 P-49 P-19 P49 SPEC ORDER - 8167 SMLS INCONEL 8169 WELDED INCONEL P-61 P-62 P-62W P-63 P-64 P61 NOT STOCK 9165 SMLS MONEL 31*7 WELOEO MONEL P-41 P-4JW P-42 P-4 2W ` 8161 SMLS NIC*E_ STRESS REL P-24-1 P-20-1 0161 SMLS NICKEL STRESS PEL LOW C P-24-2 P-20-2 6162 WELDED NICKEL 100* X-R P-24-IW P-20-1W 8162 WELD'D NICKEL 1001 X-R LOW C 8337 5HLS/WEL0ED TITANIUM P--24--2 W P-20-2W P-201 S^0if0885t, ST0408854 i7 ENGINEERING specification TEXAS DIVISION 46-700 4-15-74 PAGE 2 OF 2 INDEX - PIPING AND TUB TNG LINEO STEEL PIPE[ HIGH PRESSURE TUBING EFOXY COATED AND LINED EPOXY PHENOLIC NEOPRENE . * RUBBER PENTON P-9 p-a o-25 p-u P--25 P-14 20,000 PSIG 30.000 PSIG 45.COO PSIG 45.000 PSTG 52.000 PSIG 30.000 PSIG PCLVPPOPYLcNE P-I4A 60.000 PSIG KYNAR P-14B '30.000 PSIG SAP AN TEFLON (TFE) P-17S P--1 AC SUPER PRESS SUPER PRESS TEFLON (NOT DOW) P-10 TEFLON (FEPI `p-203 TUBING E4135 E4340 E4340 E4340 E4340 304SS 304SS 41 OSS 304SS 30ASS SMLS SMLS SMLS SMLS SMLS SMLS SMLS SMLS SMLS SMLS P-59 ' P-58A P--37 A P-58B P-58 P-30 P-37 P-31 P--29--1 P-29-2 PLASTIC IE KYNAR SCH SO PVC SCH 40 NORMAL IMPACT PVC SCH BO NORMAL IMPACT PVC SCH 40 HIGH IMPACT PVC SCH 80 HIGH IMPACT HAVZG P-4206 P-5 0 P-52 P-51 P-53 P-I ft FIBERGLASS REINFORCEO EPOXY PIPE CFEMLINE GREEN THREAD RED THREAD P-60'A P-60B P-60 . .FIBERGLASS REINFORCEO ELASTIC PIPE OFRAKANE DERAKANE DERAKANE DERAKANE 411-45 411-45 470--45 470-45 W/C-GLASS Wv'DYNEL W/C-GLASS W/DYNEL P-214C P-21 40 P-213C P-2 1 3D MISCELLANEOUS PIPE ALUMINUM 6063-T5 STEAM DUCTILE IRON DUCTILE MCNOLOY RORCELAIN OYREX PLAIN END PYREX CONICAL END STEEL 5300 PSIG SMLS TR P--67 P-16A P-I6B P-66 P-23 P-23A P--26 ALLOY 20 0-468 WELDED ALUMINUM B-210 6061T6 SMLS ALUMJNUM B-210 6061T6 SMLS ALUMINUM B-210 6061T6 SMLS ALUMINUM B-210 6061T6 SMLS COPPER B-68 COPPER B-68 NO 122 SMLS COPPER B-68 V/SHEATH COPPER B-68 V/SHEATH MULTI. COPPER B-- 75 5MLS COPPER TYPE K B-88 SMLS COPPER TYPE L B-88 SMLS MONEL B-165 SMLS NICKEL LOW CARBON B-161 POLYETHYLENE POLYETHYLENE BLACK POLYETHYLENE BLACK MULTT SARAN STAIN STL A--269 304 WELDED STAIN STL A-269 304 SMLS/W STAIN STL A-2E9 304 SMLS/W STAIN STL A-269 304 SMLS/W STAIN STL A-269 304 SMLS/W STAIN STL A-269 304 SMLS/W STAIN STL A-269 316 WELDED STAIN STL A-269 316 WELOED STAIN STL A-269 316 SMLS/W STAIN STL A-269 316 SMLS/W STAIN STL A-269 316 SMLS/W STAIN STL A-269 316 SMLS/W STAIN STL A-269 316 SMLS/W TITANIUM B--338 GR 3 SMLS/W P-20 8 P-ll 5 P-ll 6 P-U 7 P-1I 8 P-102 P-21 2 P-103 P-104 P-20 7 P-21 IK P-211L P-105 P-106 P-55 P-100 P-10 1 P--55 S P-10 7 P-ll 0 P-1 1 1 P-ll 2 P-U 3 P-U 4 P-108 P-109 P-U OA P-U 1A P-U 2A P-U 3A P-I14A P-202 Sroi>088ss ST0408855 18 ENCINEEa.LNC SPECIFICATION Texas Division PIPE _ 48-701 7-15-76 1 of 18 I ITEM NO DESCRIPTION ICTIONARY NOTE SMALL SIZE TUBING PREVIOUSLY INCLUOEO IN THIS SPECIFICATION IS NCW IN SPECIFICATION 48-702 OUCTILE-IRON P-16A P--1GB FLANGED DUCTILE IRON CENTRTFUGALLY CAST PIPE. ANSI A21 .6 CLASS 22 THICKNESS. WITH CLASS I2S FLANGES. (NOTE- SIZES 2 THRU 12.1 AMERICAN DUCTILE MCNOLOY PIPE. IPS OD. AMERICAN CAST IRON PIPE COMPANY. (NOTE- SIZES 2 THRU 12.1 CARBON-STEEL P-1 AS74 A--S3 OS API --SL GS A OH 8. SCH 30 SEAMLESS DR ELEC wELO STEEL PIPE. (NOTE-.SIZES B THRU 12. MINUS 20 TO *7S0F. P-IB ASTM A-S3 OR API-SL GR B. SCH 30 SEAMLESS OS ELEC WELO STEEL . PIPE. (NOTE- SIZES 6 THRU 12. MINUS 20 TO 4750F.J' P-6B ASTM A-SB7, SCH 40 ERW STEEL PIPE. ALUMINUM KILLED. FLANGING AND BENDING OUALITY. JCL FLAREWELD SPEC JL-PP. REPUBLIC SPEC ST-2C2. OHIO ERW OR B&w FLARE BEND. (NOTE- SIZES 1/2 THRU 4, MINUS 20 TO V75CF. FOR USE IN LAP JOINT FLANGING MACHINE.) P-3 ASTM A--53 OR API-5L GR A OR B. STO WEIGHT SEAMLESS STEEL PIPE. (NOTE- SIZES 2 THRU 24, MINUS 20 TO -7S0F. I P--30 ASTM A--53 OS API-SL GR 6. STO WEIGHT SEAMLESS STEEL PIPE. (NOTE- SIZES 2 THRU 24, MINUS 20 TO +750F.) P-3BW ASTM A--53 OR API-SL GR 8. STO WEIGHT SEAMLESS OR ELEC WELO STEEL PIPE. (NOTE- SIZES 2 THRU 36. MINUS 20 TO +750F.1 P-3W P-27 ASTM A--53 OR API-5L GR A OR B. STO WEIGHT SEAMLESS OR ELEC WELD STEEL PIPE. (NOTE- SIZES 2 THRU 36.' MINUS 20 TO *7S0F.j / ASTM A-I06 GR A OR B. STD WEIGHT SEAMLESS STEEL PIPE. (NOTESIZES 1/B THRU 24, MINUS 20 TO F75CF.) P-278 ASTM A-106 GR B. STO WEIGHT SEAMLESS STEEL PIPE. (NOTE- SIZES 1/B THRU 24, MINUS 20 TO 4750F.> Sr0li098S6 ST0408856 1$ NAHONAL VALVE AND MANUFACTURING COMPANY Nominal Wall Thicknesses for Schedule Numbers Seomlesi And Welded --- Carbon, Alio/ and Stainless Steels ASA B 36.10 and ASA B 36.19 Thicknesses shewn bold foe* denote "Stenderd Weight** (STD) pip*; that* in italic* **Eetns Strwif" (XS) pip*. Add<lionel wall thicknee see for tiles* weight classifications or* shown below as they do n*4 coincide with e'schedel* number in ASA B36.10. Up* Six* STD XS 12 J7S JOO 14 .500 19 J75 .500 24 J00 30 J75 NOTESt It should br noted that in sixes 1/8* through 10", schedules 40, 40S and "SrendOrd We^h#*' or* UtnFtcol; Ke*vr, in isos 12 ' ond larger, .375' wait thickness is "Standard Weight**. Likewise in sixos 1/6* through 8*. schsduUs 60, 90S and "Extra Strong** or* idenTicol, and in sires 10/r ond large* .500" wall thickness is "Eilrs Strong'*. Schedwlsi |0 through 160 ond "Doubt* Eitrs Strong** vs In ac- cordanca with ASA 836,10 ond op gif to carbon, ollof and itoinlsu stool pipe. ^Schedules SS, ICS, 4OS and 90S are in accardear* with ASA 8)6.1f and apply to stainless stool pipa only. In sixes 14* end larger, well thickness** for SS and lOS ora proposed, but srrnot in cluded in ASA B3i. 19. In slxoi 14m end larger, welt thicknesses fa* schedule 40S agr*a with'`Standard W*ighf"ond schedule 90S ogre* with"E*tro Strong**, but are ruet included in ASA B34.I9. The different grades af stainless steel permit considerable rsrh aliens in weight. Tb ferritic stainless sleets mjr be about 5 per cent loss, end the ewslsnitic eloinlose steel* ebewt J per cent greater thon the weights lor corresponding also* af carbon sleet pipe. (Refer ta page* 12 through 15). ST 0408857 1 4 UNIFORM SINGLE RANDOM DOUBLE RANDOM LENGTHS 21' + 1" 16' TO 22' 36' TO 40' END FINISHES 1. PLAIN END SQUARE CUT (PE SC) 2. PLAIN END BEVELED FOR WELDED (PE BEV) (30 BEVEL IS STANDARD) 3. THREADS ONLY - ONE OR BOTH ENDS (TO) 4. THREADS WITH COUPLING ATTACHED TO ONE END ( T & C) 5. GROOVED FOR MECHANICAL COUPLINGS. ST0408858 JEC/jr 10-10-77 ST0408858 27 AMERICAN NATIONAL STANDARD CHEMICAL PLANT AND PETROLEUM REFINERY PIPING PART 2: PRESSURE DESIGN OF PIPING COMPONENTS ANSI 631.3-1970 303 303 GENERAL Components manufactured in accordance with standards listed in Appendix E shall be considered suitable for use at pressure-temperature ratings in accordance with 302.2 or 302A.2. The rulej in 304 and 304A usually are for the pressure design of components not covered in 302.2 or 302A.2. but may be used for a special or more rigorous design of components covered by 302.2 or 302A.2. Designs shall be checked for adequacy of mechanical strength under applicable loadings enumerated in 301. S = allowable stress, psi (MPa) Appendix A. S = basic allowable stress for materials, psi (MPa), excluding quality or joint factors. c casting quality or weld joint factor, applied to 5 as required (see Tables 302.3.3C and 302.3.4). V = coefficient having values as given in Table 304.1.1 for materials indicated. For inter mediate temperatures, the value of Y may be j interpolated. 304 PRESSURE DESIGN OF METALLIC COM PONENTS (For non-metallic components, see 304A.) ^ 304.1 Straight Metallic Pipe 304.1.1 General (a) The required thickness of straight sections of pipe shall be determined in accordance with Equation 2: *m = , + c....................... . (2) The minimum thickness for the pipe selected, con sidering manufacturer's minus tolerance, shall not be less than tm. (b) The following nomenclature is used in the equations foe pressure design of straight pipe. t/n s miniTM1117* required thickness, tn(mm), in cluding mechanical, corrosion, and erosion allowances. t * pressure design thickness, in(mm), as calcu lated in 304.1.2 for internal pressure, or in accordance with the procedure listed in 304.1.3 for external pressure. C B die sum of the mechanical allowances (thread or groove depth) plus corrosion and erosion allowances, in(mm). For threaded components, the nominal thread depth (dimension h of ANSI B2.1, or equivalent) shall apply. For machined surfaces or grooves where the tolerance is not specified, the tolerance shall be assumed to be 0.02 tn(0.5 mm) in addition to the specified depth of the cut. Table 304.1.1 -- Values of Coefficient V Materials 900 (485) Slower Temperature," F (*C) 1,150 950 1,000 1,050 1,100 (620) (510) (540) (560) (595) A up Femiic Steels 0.4 0.5 0.7 0.7 0.7 0.7 Austenitic Steels 04 0.4 0.4 0.4 0.5 0.7 Other ductile Metals 0.4 Cast Iron 0.0 0.4 0.4 _ 0.4 0.4 0.4 304.1.2 Straight Pipe Under Internal Pressure (a) The internal pressure design thickness, f, shall be not less than that calculated by Equation 3a, when t is less than D/4: t ~ PD 2(5E + PY) (3a) Equations 3b and 3c, which are more conservative, may be used instead of Equation 3a: (3b) (Lame Equation)(3c) (b) Pipe with t equal to or greater than D/4, or P/SE greater chan 0.6, requires special consideration, taking into account design and material factors such as theory of failure, fatigue, and thermal stresses. P " internal design gage pressure, psi (MPa). D * outside diameter of pipe, in (mm). ST0408859 ST0408859 /t-53- CjtAoe & t =_Po_ 2(St+PY) in 5 i u. t- t>S<<;M TUriCKlu&Ss tw,~ ?(PEwAU-'f^CU/JGSt P - PfLC%WfL'& =- 3 00 PSl *t> r 0D - ID IW St t Au^Mus'Srfcess (am Y?6.4 (We ScxUl) C, ? 0, I IN (^>W, tJWU>i|oO hlJUM^JCe) S^am.s s ^Typ^ ^>E =. io,noo pj t Hl - ^Q\IP 2 (f0>1oi>-<-'*>oe><,4) V Qtr - Luo) 0. <38 6* iw W - 0,l35(r -4-0, t PD - ,2 3^,ro. 2d) = 1^5 SPEGaEY TvPc <, - SCaa 20 ^cfi Wgut>eo (j YP6 t) S&- ^ ^loo p^>/ Y " ^>oe> Vv t o ^ .(*1199 + 3oo*.^ >,/ - 0.85) 7 in* *tfyv " 0 11 (^-"7 ~V" D,\t>o -- O.'Z.l^ in) =,S0rl) Specify type Sch so SfQbOdQ 60 ST0408860 ST040886I ST0408861 PIPING WORKSHOP FITTINGS ST0408862 1. INTRODUCTION 1.1 Cast iron is an iron-carbon alloy cast molten into a mold. Carbon content is between 2% and 4.5% and has appreciable amounts of silicon. 1.2 Malleable cast iron is cast iron that has been heat-treated to change it's combined carbon into free carbon. The iron becomes malleable because in this condition the carbon no longer forms planes of weakness. 1.3 Ductile cast iron is a high-carbon magnesium treated ferrous product containing graphite in the form of spheroids or impacted particles. 1.4 Steel is an alloy of iron and carbon which contains not over 21- carbon and is cast into an initially malleable mass. 1.5 Fitting Specifications 1.5.1 ASTM - Chemical composition 1.5.2 ANSI - Dimensional and tolerance data 1.5.3 MSS-SP - Stainless steel butt welding wrought fittings and steel butt welding fittings (26" and larger) 1.5.4 API - Specification for threads in fittings 2. FORGED STEEL FITTINGS SOCKET-WELDING AND THREADED 2.1 Scope 2.1.1 ANSI 16.11-1973 covers dimension, finish, tolerances, testing, marking, material, and minimum performance requirements for forged carbon and alloy steel fittings both socket-welding and threaded. This code also applies to 2,000 lb., 3,000 lb., and 6,000 lb. stainless steel fittings. 2.1.2 The steel for fittings shall consist of forgings, bars, seamless pipe, or tubes which conform to the requirements for melting process, chemical composition requirements, and mechanical property requirements of the ASTM Specifications A105 and A182. 2.2 Limitations 2.2.1 Upon prolonged exposure to temperatures above 750F., the carbide phase of plain carbon steel, plain nickel alloy steel, carbonmanganese alloy steel, manganese-vanadium alloy steel, and carbon-silicon steel may be converted to graphite. Page^l of 7 ST0408862 2.2 Limitations (Cont'd) 2.2.2 Upon prolonged exposure to temperatures above 850F, the carbide phase of alloy steels, such as carbon-molybdenum steel, maganesemolybdenum vanadium steel, managanese-chromium-vanadium steel, and chromium-vanadium steel, may be converted to graphite. 2.2.3 If carbon steel is to be used above a temperature of 900F, consideration shall be given to the advantages of silicon killed steel (0.1 percent silicon min.). 2.3 Pressure Ratings 2.3.1 The carbon steel fittings shall be designated as 2,000 lb, 3,000 lb., and 6,000 lb. fittings for threaded and 3,000 lb., 6,000 lb. and 9,000 lb. for socket-welding. 2.3.2 Ratings in code services. Ratings determined in accordance with Paragraph 6.2.2 apply to any service within the scope of section of the American National Standard Code for Pressure Piping (ANSI B31), or a Section of the ASME Boiler and Pressure Vessel Code, or of a legally enforced regulation which established pressure design requirements for pipe. 2.4 Size 2.4.1 The size of the fitting is identified by the "nominal pipe size". 2.4.2 In the case of reducing tees and crosses the size of the largest run opening shall be given first, followed by the size of the opening at the opposite end of the run. Where the fitting is a tee, the size of the branch is given last. Where the fitting is a cross, the largest side outlet is the third dimension given, followed by the opening opposite. Reducing fittings shall have the same center-to-end dimensions, center-to-bottom of socket and hand diameter as the straight-size fittings corresponding to the largest size opening in the reducing fitting. 2.5 Marking 2.5.1 Each fitting shall be permanently marked with the required identification by raised lettering and/or by stamping, electro etching, or vibro tool marking on the collar portion of the forging or on a pad or raised boss portion. It is recognized that bushing and plugs are impractical for marking which accord ingly is not required by ANSI B16.ll. 2.5.2 Each fitting shall be marked as follows: 2.5.2.1 Name: Manufacturers name or trademark. 2.5.2.2 Material: Carbon steel fittings shall be marked "A105" or "WPB". Alloy steel fittings shall be marked with the ASTM grade number preceded by "A182F" or by "WP". S T 0 4 08863 Page,2 of 7 [ iST0408863 2.5.2 (Cont'd) 2.5.2.3 Service Designation: The fitting pressure class. 2.5.2.4 Size: The nominal pipe size in inches. 2.5.2.5 Example: 2 3000 A105 Mfg. Co. 2.5.3 Where size and shape of fittings do not permit all of the above marking, they may be omitted in the reverse order given above. 2.6 Design and Capability H9880*l0iS 2.6.1 As these fittings are to be used in connection with pipe the minimum body wall thickness for socket-welding fittings must be equal to or greater than the nominal wall thickness of pipe as established by ANSI 836.10 with which they are used. The average socket wall thickness shall at least equal 1.25 times the nominal thickness of the corresponding pipe, and at no point shall the minimum thickness be less than 1.09 times the nominal pipe wall thickness (which is 1.25 x 0.875" x nominal pipe wall). 2.6.1.1 The minimum body wall thickness for threaded fittings shall be required in Table 3 of ANSI B16.11-1973. 2.7 Socket Welding Fittings 2.7.1 Dimensions 2.7.2 A cardinal principle of this standard is the maintenance of a fixed position for the bottom of the socket with reference to the center line of the fitting. Dimensions and tolerances are established up to and including the 4 in. size on tees, 90 deg. ells, 45 deg. ells, crosses, couplings, and half couplings, and are shown in Table 2 of B16.ll. For reducing fittings dimensions, see Paragraph 6.3.2. 2.7.3 Finish 2.7.3.1 Fittings shall be faced on the ends at right angles to the axis to provide a flat surface against which to weld and the socket shall be counterbored or otherwise machined to insure uniform depth and circularity. 2.8 Threaded Fittings 2.8.1 Threading 2.8.1.1 All fittings with internal threads shall be threaded with American Standard Taper Pipe Threads (ANSI B2.1). Variations in threading shall be limited to one turn large or one turn small from the gaging notch when using working gages. When gaging, the notch should be flush with the Page 3 of 7 ST0408864 2.8.1 Threading (Cont'd) 2.8.1.1 (Cont'd) bottom of the countersink which shall be con sidered as being the intersection of the countersink cone and the pitch cone of the thread. This depth is approximately equal to one-half thread from the face of the fitting. 2.8.1.2 All externally threaded fittings shall be threaded with American Standard taper pipe threads and the variation in threading shall be limited to one turn large or one turn small from the gage face of ring when using work ing gages. 2.9 Test 2.9.1 Pressure testing is not required by ANSI B16.ll, but the fittings shall be capable of withstandaing a hydrostatic test pressure of 1-1/2 times the designated rating pressure without imparing their servicability. Factory Made Wrought Steel Butt Welding Fittings 3.1 Scope 3.1.1 ANSI B16.9 covers overall dimensions, tolerances and marking for wrought carbon and alloy steel factory-made welding fittings which shall be known as American National Standard Wrought Steel Butt Welding Fittings. In ANSI B16.9 "wrought" is used to denote fittings made of pipe, tubing, plate, or forgings. 3.1.2 Fittings may be made to special dimensions or of wrought materials other than those covered by ANSI B16.9 by agreement between the manufacturer and the purchaser. When such fittings meet all other stipulations of B16.9, they shall be considered as complying therewith. 3.1.3 Fabricated laterals, or other fittings, employing intersection welds, shall be considered as pipe fabrication, and as such should be designed in accordance with the rules established in the code for Pressure Piping (ANSI B31). 3.1.4 ANSI B16.9 does not cover low pressure corrosion resistant butt welding fittings. See MSS SP-43 Stainless Steel Butt Welding Fittings published by the Manufacturers Standardization Society of Valve and Fitting Industry. 3.1.5 Wrought fittings covered by B16.9 shall be in accordance with ASTM Specifications A-234, A-403, A-420, except that other material con forming to appropriate ASTM, API, AISI, or MSS Specifications may be used by agreement between manufacturer and purchaser. 3.2 Pressure Ratings $10408865 Page 4 of 7 r ST0408865 99880*101$ 3.2 Pressure Ratings (Cont'd) 3.2.1 Fittings shall be designed for the pressure ratings which may be calculated for straight seamless pipe, of the same or equivalent material, with which they are recommended for use. As the pressure rating for each size and wall thickness may vary in the different code sections, the calculations for the pressure ratings of the pipe shall be in accordance with the rules established in the applicable sections of the Code for Pressure Piping (ANSI B31). 3.3 Size 3.3.1 The "size" of the fitting in the tables of B16.9 are identified by corresponding "nominal pipe size". For fittings 14 in. and larger the OD of the pipe corresponds with the nominal size. 3.4 Marking 3.4.1 Each fitting shall be permanently marked to show the following: 3.4.1.1 Manufacturer's name or trademark. 3.4.1.2 Material (by means of identification symbols established for the respective grade in the appropriate ASTM, API, or AISI Specifications). 3.4.1.3 Schedule number oft nominal wall thickness designation. 3.4.2 Omission - where the size of fitting does not permit complete marking, the identification marks may be omitted in reverse of the order presented above. 3.4.3 Pressure ratings must be calculated in accordance with Paragraph 7.2, and therefore numerical values cannot be preassigned for marking. 3.5 Fittings Dimensions 3.5.1 One of the principles of ANSI B16.9 is the maintenance of a fixed position for the welding ends with reference to the center line of the fittings or the overall dimensions, as the case may be. Dimensional Standards for these fittings can be found in Tables 2 through 9 in ANSI B16.9-1971. 3.6 End Preparation 3.6.1 Welding ends shall be in accordance with ANSI B16.25-1964. For convenience, these welding ends are shown in Figures la and lb of ANSI B16.9-1971, for fittings with wall thickness equal to that of the pipe to which they are intended to be welded. 3.6.2 Fittings are regularly furnished with end preparations as shown in Figure 1 of B16.25-1964. Page 5 of 7 ( .. ST0408866 3.7 Tests 3.7.1 Hydrostatic testing of wrought fittings is not required in this standard. All fittings shall be capable of withstanding without leakage a test pressure equal to that prescribed in the specification for the pipe with which the fitting is recommended to be used, and without imparing their serviceability. 4. Cast Iron Pipe Flanges and Flanged Fittings 4.1 Scope - ANSI B16.1 covers performance requirements, dimensions, marking, material (refers to ASTM A-126-61T) and testing for 25 lb., 125 lb., 250 lb., and 800 lb. cast iron pipe flanges and flanged fittings. 4.2 Limitations 4.2.1 Cast iron shall not be used for pressure containing parts in hydrocarbon or other flammable fluid service at temperatures above 300F nor at pressures above 400 psig, except that for service above ground within process unit limits the pressure shall not exceed 150 psig. ST0408861 4.2.2 Malleable iron shall not be used for pressure containing parts at temperatures below -20, or above 650F, nor in flammable fluid service above either 300F or 400 psig. 4.2.3 Cast and malleable iron shall not be used for pressure contain ing parts in any toxic service. 4.3 Size - The size of the flanges and fittings is identified by the nominal pipe size. For sizes 14 inch and larger the nominal pipe size corresponds to the pipe 0D. 4.4 Marking - The manufacturer's name or trademark and rating numerals shall be cast on the exterior surface of all fittings. (125# number 125) 4.5 Tests - Hydrostatic test are not required unless specified by the user. Fittings shall be capable of withstanding, without showing leaks hydrostatic test pressures of 2 to 1 (fitting pressure rating doubled is test pressure for most common cast iron flanged fittings). 5. Steel Pipe Flanges and Flanged Fittings 5.1 Scope - ANSI 16.5 pertains primarily to cast and forged steel flanges and flanged fittings and covers pressure ratings, size, marking, materials dimensions, tolerances and tests. 5.2 Pressure Temperature Ratings - Products covered by this standard are classified and designated by their primary service pressure rating: 150, 300, 400, 600, 900, 1500 and 2500 lbs. These ratings are the maximum allowable non-shock pressures at the primary temperature rating for carbon steel (500F for 150 lb. service, 850F for 300 thru 2500 lb. service). Code Limitations - To be used within limits of codes governing the installation. (ASME Boiler and Vessel Code or USAS Code for pressure piping.) ( Page 6 of 7 ST0408867 ST0U08868 5. Steel Pipe Flanges and Flanged Fittings (Cont'd) 5.3 Size - The size of the flanges and fittings is identified by the nominal pipe size. Reducing flanges or fittings shall be designated by the size of the openings in proper sequence. 5.4 Marking - Fittings shall show size, pressure, material and Manufacturer's name or trademark. No temperature marking is required but if shown shall be at the primary service rating. Where size or shape limits or prohibits marking, they may be omitted in the order given above. 5.5 Materials - The product covered by this standard shall be either steel castings or forgings. 5.6 Test - Flanged fittings are required hydrostatic testing of one and onehalf times the primary service rating at 100F rounded off to the next higher 25 psi increment. The test shall be made with water at a tem perature not to exceed 125F, and no visible leakage is permitted. Page 7 of 7 ( .. ST0408868 ST0408869 ST0408869 ST0408870 FLANGES Types of Flanges A. Weld Neck 1. Stronger due to tapered neck (should be considered for severe service conditions). 2. Requires only one weld (full penetrations). 3. Used for handling explosive or hazardous materials. B. Slip On Flange 1. Preferred to Weld Neck due to cheaper cost. 2. Takes two welds. 3. Takes less accuracy to assemble than Weld fleck. 4. Cannot X-ray inside weld. C. Lap Joint (Van Stone) 1. Pressure rating a little if any better than Slip-On. 2 Pafirjiio 1 i fa n-f Uolrlinn MnrU 3. Consider when frequent dismantling for inspection or cleaning required. 4. Their use at points where severe bending stress occurs should be avoided. 5. Consider their use when using more expensive piping system, such as stainless steel. D. Screwed 1. Can be assembled without welding. 2. Good for extremely high pressure near or at atmospheric tempera ture. 3. Seal welding sometimes necessary for cyclic conditions which may cause leakage. 4. Not suitable where temperature and bending stresses are involved. E. Socket Welding Flanges 1- Initially developed for use on small high pressure piping. ST0408870 FLANGES Page 2 F. Orifice Flange 1. Use in conjunction with orifice meters. 2. Basically the same as Standard Welding Neck, Slip-On, and Screwed. 3. Jack screws for separation of flanges. G. Blind Flanges 1. Used to blank off the ends of piping. 2. Blind Flanges, particularly in large sizes, are most highly stressed. II. Flange Faces A. Flat Face 1. Cast Iron 2. Use on non-hazardous service. 3. Often made from raised face. 5. Roised raufc O CP CP 1. Most common. 2. 1/16" high face for 150# and 300#. 1/4" high for all others. 3. Gasket usually less width than Raised Face. C. Ring-Type 1. Most expensive. 2. Most efficient. 3. Not easily damaged. 4. Preferred for high temperature and pressure service. D. Male and Female 1. Metal gaskets can be used with small design because of gasket compression. 2. May present stocking problem due to the availability of matching male and female piece. ST0408871 'S i'S e o w is . FLANGES J>age 3 3. For special services requiring retained gaskets. E. Tongue and Groove 1. Used for services requiring a -retained gasket and lack Of --with process fluid (not conmon). 2. Hust be shipped with companion flange. III. Bolts A. See Dow Spec. 48-805. B. Special considerations in heavy chloride atmosphere. 1. Consider using C.S. bolt ASTM -193 stud with B-7 nut. 2. -Studs to be quenched and tempered. 3. Contact Specification Department or Division Metalurgist. IV. Assembly A. Torque Procedure 1. Cast Iron 2. F.R.P. *B. Check Dow Spec. 48-860, Paragraph 216--216M. V. Pressure Temperature Tables VI. Special Considerations A. ANSI 16.5 1968 (R 1971) is the latest revision recognized by ANSI B 31.3 (1976). B. Lined pipe may be damaged if care is not taken during assembly, to the possibility of damaging the liner. -^Will be back in Spec, by January 15. JEPrwml 1-4-77 ST0408872 FLANGE TYPES WELDING NECK FLANGES are distinguished from other types by their long tapered hub and gentle transition of thickness in the region of the butt weld joining them to the pipe. The long tapered hub provides an important reinforcement of the flange proper from the standpoint of strength and resistance to dishing. The smooth transition from flange thickness to pipe wall thickness effected by the taper is extremely beneficial under conditions of repeated bending, caused by line expansion or other variable forces, and produces an endurance strength of welding neck flanged assemblies equivalent to that of a butt welded joint between pipes, which, in practice, is the same as that of unwelded pipe. Thus this type of flange is preferred for every severe service condition, whether this results from high pressure or from sub-zero or elevated temperature, and whether loading conditions are substantially constant or fluctuate between wide limits; welding neck flanges are particularly recoimended for handling explosive, flammable or costly liquids, where loss of tightness or local failure may be accompanied by disastrous consequences. SLIP-ON FLANGES continue to be preferred to welding neck flanges by many users .because of their initially lower cost, the reduced accuracy required in cutting the pipe to length, and the somewhat greater ease of alignment of the assembly; however, their final installed cost is probably not much, if any, less than that of welding neck flanges. Their calculated strength under internal pressure is of the order of two-thirds that of welding neck flanges, and their life under fatigue is about one-third that of the latter. For these reasons, slip-on flanges are limited to sizes 1/2" to 2-1/2" in the 1500 lb. standard and are - k - - - j-u - orit I IW W WtlVMII lit WIlC IUt O ------- 1 iL. rur n - i -- r------- j. /Vri~ u-,-'*- t IV4U I U UIIU Vrl l\_ IU UU I t \_ VV It J Uv* V '- t I till I VU their use to the 4" size. Slip-on flanges shall be double-welded when used for any of the following: (1) Services subject to severe erosion, crevice corrosion, or cyclic loading. (2) Services which are flammable, toxic or damaging to human tissue. (3) Severe cyclic conditions. If sli p-on flanges are single-welded, the weld shall be at the hub. The use of slip-on flanges should be avoided where many large temperature cycles are expected, particularly if the flange is not insulated. LAP JOINT FLANGES are primarily employed with lap joint stubs, the combined initial cost of the two items being approximately one-third higher than that of comparable welding neck flanges. Their pressure-holding ability is little, if any, better than that of slip-on flanges and the fatigue life of the assembly is only one-tenth that of welding neck flanges. The chief use of lap joint flanges in carbon or low alloy steel piping systems is in services necessi tating frequent dismantling for inspection and cleaning and where the ability to swivel flanges and to align bolt holes materially simplifies the erection ST04Q8873 ST0408873 FLANGE TYPES Page 2 \ of large diameter or unusually stiff piping. Their use at points where severe bending stress occurs should be avoided. SCREWED FLANGES, made of steel, are confined to special applications. Their chief merit lies in the fact that they can be assembled without welding; this explains their use in extremely high pressure services, particularly at or near atmospheric temperature, where alloy steel is essential for strength and where the necessary post-weld heat treatment is impractical. Screwed flanges are unsuited for conditions involving temperature or bending stresses of any magnitude, particularly under cyclic conditions, where leakage through the threads may occur in relatively few cycles of heating or stress; seal welding is sometimes employed to overcome this, but cannot be considered as entirely satisfactory. SOCKET WELDING FLANGES were initially developed for use on small-size high pressure piping. Their initial cost is about 10% greater than that of slipon flanges; when provided v/ith an internal weld, their static strength is equal to, but their fatigue strength 50% greater than double-welded slip-on flanges. Smooth, pocketless bore conditions can readily be attained (by grinding the internal weld) without having to bevel the flange face and, after welding, to reface the flange as would be required with slip-on flanges. The internally welded socket type flange is becoming increasingly popular in chemical process piping for this reason. ORIFICE FLANGES are widely used in conjunction with orifice meters for measur ing the .'ate or T i Gw uf i iijuiuj oiid ydScS .. i IIey are uab l Ld t \y Cite bailie db standard welding neck slip-on and screwed flanges except for the provision of radial, tapped holes in the flange ring for meter connections and additional bolts to act as jack screws to facilitate separating the flanges for inspec tion or replacement of the orifice plate. In choosing the type of orifice flange, the considerations affecting the choice of welding neck, slip-on and screwed standard flanges apply with equal force. BLIND FLANGES are used to blank off the ends of piping, valves and pressure vessel openings. From the standpoint of internal pressure and bolt loading, blind flanges, particularly in the larger sizes, are the most highly stressed of all American Standard flange types; however, since the maximum stresses in a blind flange are bending stresses at the center, they can safely be per mitted to be higher than in other types of flanges. Where temperature is a service factor, or repeated severe water hammer, consideration should be given to closures made of welding neck flanges and caps. SPECIAL FLANGES are made in welding neck, slip-on, screwed and blind types. Tube Turns' facilities are not limited to manufacture of standardized flanges. Large diameter flanges with drilling to match cast iron standard. Pressure Vessel flanges, and TEMA Heat Exchanger flanges are regularly furnished. In addition, flanges are supplied to match non-standard oil pipeline gate valves. ST0408874 $10408874 FltftfM------------- -'. " . ' -TABLE 2.8 FLANGE TYPES -31' ST0U08875 (Drawings reproduced by permission: Theodore R. Olive, Chemical Engineering, December, 1953, p. 187.) Flange Type Description and Characteristics Recommended Use Viewed Flange screws on to threaded pipe, and no welding High pressure service at moderate temperatures. Not required. Kited fui xi vice lilVuivUlIJ UlUlUMi Wt wCTidll^ awwarX. Slip-on Lower cost per flange than welding neck, but installed cost same as welding neck. Less skill required for installing. Calculated strength under internal pressure and life under fatigue is less than welding neck iASA T6.5 ratings are the same but slip-on not included in Standard for 2'A in. and larger 1500-lb flanges and for any size 2500-lb flange). To install, flange is slipped on the pipe and two welds made (see cut) one on the inside and the other on the outside of the pipe. Moderate service conditions particularly when ease of assembly is a valid consideration. Vfelding-neck Tapered hub terminates at pipe where it is attached by a weld. The long taper makes flange an integral part of pipe and produces a joint which can stand repeated . bending. Severe service (high pressure and/or temperature or low temperature). Lap Joint Fit over lap joint stub as illustrated. Fatigue life is Mo -that of welding neck. Only lap joint stub comes in contact with process fluid. Services requiring frequent dismantling for inspection and cleaning--For large diameter pipe and other instal lations for which ability to rotate flange during assembly ii an advantage. Avoid using for conditions involving evere bending stresses. Carbon steel flanges can be tned with alloy stub ends for certain corrosive services, thus reducing costs. Scsdcet Welding Pipe fits into recessed portion of flange. One weld is __ made at back of flange. Crevice between socket and flange may be subject to excessive corrosion under cer- tain conditions, but internal weld can be made to avoid this difficulty. Initial cost 10% less than slip-on. With -_ internal weld has 50% greater fatigue strength and ~ lame italic strength as shp-on. Good for smaller diameter piping where leak-proof fittings are preferred to screwed attachments. ST0408875 32 r:i i --f il ' . -nV 4ids in selecting pipe, valves and fittings / 2 ! TABLE 2.9 FLANGE FACINGS i l ST0408876 (Drawings reproduced by permission: Theodore R. Olive, Chemical Engineering, December, 1953, p. 187.) TVdc Description and Characteristics Recommendation Raised Ring-type Male and Female Tongue and Groove Flat Face Most common--Both flanges of a pair arc identical. Faces are Vis in. high for 150- and 300-lb flanges and % in. high for all others. Gasket is usually less in width than the raised lace. (Scr Tabic 2 10 for gasket recommendations.) freierreo for moderate service conditions. Most expensive but most efficient flange facing. Not Preferred for high temperature and pressure service. easily damaged in assembling. Made in large and small designs. Metal gaskets can be used with small design because of high gasket compres sion. Slocking a problem because both male and female pieces must be stocked. Used for special services requiring a retained gasket (not common). Made in large and small designs, inside diameter does not extend to flange bore thus eliminating contact of gasket by process fluid. Small design gives highest joint efficiency possible with fiat gaskets. Both tongue and groove pieces must be stocked. Used for services requiring a retained gasket and lack of contact with process fluid (not common). Same as raised face except raised portion removed. Often made by machining face from standard raised-face flanges. Mating flanges for 125- and 250-lb cast-iron valves and fittings. i ST0408876 ST0408871 AMERICAN NATIONAL STANDARD ANSI B16.6--1973 STEEL PIPE FLANGES, FLANGED VALVES AND FITTINGS . Class 150, 300,400, 600, 900,1500, and 2500 1.0 SCOPE 1.1 This standard pertains primarily to cast and forged steel flanges; but the flange dimensions, bolt ing, minimum wall thicknesses, and certain other re quirements herein specified apply also to cast, forged, and fabricated steel flanged valves and fittings of cor responding pressure class and size. 1.2 This standard covers: (a) Pressure-Temperature Ratings (b) Sizes1 and Methods of designating openings (c) Marking (dl Minimum reouiremenrs for materials (e) Dimensions1 (0 Tolerances (g) Tests 1.3 Standards and specifications adopted by ref erence in this Standard and the names and addresses of the sponsoring organizations are shown in Ap pendix H. It is net considered practical to refer to a specific edition of each of the standards and specifi cations in the individual references. Instead the spe cific edition references are included in Appendix H. A product made in conformation with the edition reference applicable during time of manufacture and in all other respects conforming to this standard will be considered to be in conformance even though the edition reference may be changed in a subsequent revision of this standard. 1.4 The pressure-temperature ratings included in this standard are applicable upon its publication to all lThe use of the word "nominal" as a modifier of a dimenaon or size is intended to indiejte thjt the stated dimension or size is used for purposes of deognjiion. The actual dinienson may be ihc nominal dimension subject to the variation of established tolerances. products covered within its scope which otherwise meet its requirements. Howeyer, where such com ponents were purchased, manufactured, or installed under the pressure-temperature ratings of ANSI BI6.5-1968, those ratings shall apply except as may be governed by the applicable Code. (See Paragraph 23) 2.0 PRESSURE TEMPERATURE RATINGS 2.1 General. Products covered by this standard are classified and designed as Class 150, 300,400, 600, 300, i5G0, or 2500. Pressure ratings for these classes, tor various temperatures, are shown in Table 2. (Rat ings are also shown in metric units in Appendix G.) These ratings are the maximum allowable non-shock pressures at the temperatures shown, and the allow able pressure may be interpolated between the tem peratures. Ratings apply to any product (valve, flange, or fitting) but a valve conforming to this standard shall merit these in other respects also. When valves are made using high strength ma terials, for example, Table 2.12 or 2.13, careful consideration must be given to the adequacy of functional and pressure retaining parts such as the stem connection or bonnet joint. 2.2 Temperature Effects. Some considerations of the effect of temperature in application are given below: 2.2.1 High Temperature Ratings. Application at temperatures in the creep range will find boll loading decreasing as relaxation of flanges, bolts, and gaskets takes place. Flange joints subject to thermal gradients may likewise be subject to decreasing boll loads. De creased bolt loads effectively decrease the capacity of the flange joint to sustain pipe induced loads without leakage. When used above 700F (375C), flanged t ST0408877 I AMERICAN NATIONAL STANDARD STEEL PIPE FLANGES. FLANGED VALVES AND FITTINGS ' -ANSI 8165-1973 joints, and in particular Class ISO, may develop .leakage problems unless care is taken to avoid im posing severe external loads and/or severe thermal gradients. 22.2 Low Temperature Ratings. For a material drown in Table 1, the pressure rating for service at any temperature below -20F (-30C), shall be the ante as the rating shown in the -Table for -20F (-30C). Some of the materials listed in the rating tables undergo a decrease in impact resistance at temperatures lower than -20F (-30C) to such an extent as to be unable to safely resist .shock, load ings, sudden changes of stress, or high stress con centrations. 2.2.3 Fluid Thermal Expansion. Certain double seated valve designs are capable of sealing simultane ously against pressure differential from the bonnet section to the adjacent pipe in both directions. In such valves, a circumstance in which the bonnet section is filled with liquid and subjected to an in crease in temperature can result in build up of pres sure in the bonnet section. Where such a condition is possible, it is the resnnnsibilitv nf the Durchaser -- r*t;*--* A* *--i-'*- 4 A *L* r * ~'--4-^-1-^--M-A-A-W--e- ** --4 a , sign, installation, and/or operation to assure that the pressure in the valve shall not exceed that al lowed by this standard for the attained temperature. 22 Codes and Regulations. A product used under the jurisdiction of the ASME Boiler and Pressure Vessel Code, the ANSI Code for Pressure Piping, or Govern mental Regulations, is subject to any limitation of that code or regulation. This includes any maximum temperature limitation for a material, or rule govern ing the use of a material at a low temperature. 2.4 Rating Temperature. The temperature shown for a corresponding pressure rating is the temperature of the pressure-containing shell of the component. In general, this temperature is the same as that of the contained fluid. Use of a pressure rating correspond ing to a temperature other than that of the con tained fluid is (he responsibility of the user, subject to the requirements of the applicable code. 2.5 Gasket Required. The use of the pressure ratings herein requires that the gasket of a line flange joint conform to the requirements of Par. 6.10. In ad dition, the user is responsible for selection of line flange gasket dimensions and materials to withstand the required bolt loading without injurious crushing, and also the suitability foi the service conditions. 2.6 Welding Neck Flanges. Ratings for carbon steel cylindrically bored welding neck flanges in this standard are based upon their hubs at the welding end having thickness at least equaling th$t calculated for pipe having 40.000 PSI specified minimum yield strength. The ratings also apply to carbon steel welding neck flanges used with piping components of unequal strength and unequal wall thickness when the welded joint is made in accordance with the applicable section of the ASME Boiler and Pres sure Vessel Code or American National Standard Code for Pressure Piping. See Figures 13, 14, and 15. 3.0 SIZE 3.1 The size in the Tables is the nominal pipe size. 3.2 Reducing fittings shall be designated by the size of the openings in their proper sequence as indicated in the sketches. Fig. 3. a A r* , J.. ,,; ^,, p _ -H L - J ____.* A V,, nominal pipe sizes. Set examples in Footnote o or Table 7. 4.0 MARKING 4.1 Flanges, Flanged Fittings, and Valves. Flanges, flanged fittings, and valves, shall be marked, except as modified herein, as required in MSS SP-25, Standard Marking System for Valves, Fittings, Flanges, and Unions. 4.1.1 Name. The manufacturer's name or trade mark. 4.1.2 Materials. 4.1.2.1 All cast steel flanges and flanged valves and fittings shall be marked with the ASTM specifica tion grade identification symbol and the melt num ber or melt identification and may be marked with the word "STEEL". 4.1.2.2 All forged flanges and all forged or fabricated flanged fittings and valves shall be marked with the ASTM specification number and grade iden tification symbol. When more than one materia) or grade of materials is used in a fitting, valve body, or bonnet,each shall be identified. 2 ST0408878 ST0408878 'AMERICAN NATIONAL STANDARD STEEL PIPE FLANGES. 'FLANGED VALVES AND FITTINGS -VrS-.V-TJ a-'*:"'" \ cCi'tVr :'H Ci>.' . . -ANSI B16J>--1973 ' 4.1.2.3 A manufacturer may supplement these mandatory material indications with his trade desig nation for the grade of steel, but confusion with the symbols herein must be avoided. -^-4.1.3 Bating Class. Numerals giving the pressure nting^dass for which the product is designated are intended to indicate compliance with requirements of this standard. rA/1.4 Temperature. No temperature markings are required on flanges and flanged valves and fittings, but if marked, the temperature shall be shown with its corresponding tabulated pressure rating for the material. 4.13Size. The nominal pipe size in inches shall be given, but may be omitted from reducing flanges and reducing flanged fittings. 4.1.6 Ring-Joint Flange. The edge (periphery) of each ringjoint flange shall be marked with the letter "R" and the corresponding ring-groove number. 4.1.7 Omission of Markings. On flanges, flanged fittings, and valves whose size or shape limit the markings, they may be omitted in the following order: (a) Size (b) Temperature (c) Rating Class (d) Material (e) Manufacturer's name or trade mark 4.1.8 Special Markings. Valves, whose construc tion limits use to less than the pressure-temperature values for the marked pressure class rating, shall in dicate these limitations on an identification plate. Examples in this category are valves using elastomeric gaskets or seating elements. 5.0 MATERIALS 5.1 General. The products covered by this standard shall be either steel castings, steel forgings, or steel fabrications and the bolts, nuts, etc., shall be steel,2 all as listed in Table 1. In the case of valves, these re quirements apply to bodies, bonnets, cover plates, and bonnet and cover plate bolting. Bolting material other than steel may be used if their ttrength is adequate for the service conditions and provided the bolting material is permitted by the applicable Code or Governmental Regulation. 5.1.1 Where welded construction is used, con sideration should be given to the possibility of graphite formation in the following: Carbon steel above about 800F (425 C) Carbon-molybdenum, steel above 875F (470C) Chrome-molybdenum steeljwith chromium under 0.60) above 975F(525C). ' 5.1.2 Consideration should be given to the possi bility of excessive oxidation (scaling) on the following steels: 1 Cr-aMo) lViCr --V4Mo/ 2 Cr - H Mo V above 1050F (5 65C) 214 Cr-- 1 Mol 3 Cr -- I Mo) 5 Cr - 'h Mo.above HOOF (595C) 5.2 Welded Fabrication. Fittings, valve bodies, and bonnets larger than 6-inch NPS fabricated by welding together segments of castings, forgings, bars, tubular products, or plate or combinations thereof, shall be welded and welds nondestructively examined in ac cordance with the Rules of the ASME Boiler and Pressure Vessel Code, Section '-.'ll!. Division 1, in a xnann*' rnat r*sutis <n a nvnenai nr wHri mim >ifidency, E, not less than 0.80. In the case of valves, these requirements apply to bodies, bonnets, and cover plates and do not apply to seal welds or attachment welds such as for backseat bushings, seat rings, lifting lugs, or auxiliary connections. 5.3 Bolting2. Alloy steel bolting made of materials given in Table 1 shall be used for all flanges covered by this standard, except bolting for Class 150 and 300 flanges at temperatures of 500F (2600 and lower may be made of Grade B of ASTM A307, JThe bolting prescribed in this standard is based upon bolting steel to steel flanges. Where Class 150 steel fLanees re bolted to Class 125 cast-iron fiances, and with flit gaskets extending to the bolt holes, it is recommended the flanges be flat faced and carbon steel bolting equiva lent to (he requirements of ASTM A307 Grade B be used. Wheje flat faced Class 150 steel flanges are bolted to Class 125 cast-iron flanges and with full face gaskets extending to the OD of flange, the bolting as described in this standard may be used. Wheie Class 300 steel fiances are bolted to Class 250 cast-iron flanees carbon steel bolting equivalent to the requirements of ASTM A307 Grade B. shaU be used. Good practice indicates that the flange should be flal faced. When Class 150 and 300 steel flanges, either loose or integral, tre required with flat face, either the full thickness or thick ness with raised face removed may be furnished unless other wise specified by Ihe customer. Users are reminded that removing the raised face will make the center to face dtmen&on non-standard. ST0408879 ST0408879 AMERICAN NATIONAL STANDARD STEEL PIPE FLANGES. FLANGED VALVES AND FITTINGS -- ... - --"------- - --ANSI B16.5-1973 Specifications for Low Carbon Steel Externally enclosed by a circle whose diameter is no greater Threaded Standard Fasteners, or better. ~ -than 035 V dtm where d is the inside diameter as de- 6.4 Gaskets for Line Flanges. Ring joint gasket materials shall conform to ANSI B 16.20. For gaskets for flanges with other than ring joint facing, see Appendix E. fined above and tm is the minimum wall thickness as shown in Tables 10, 13, 16, 19, 22, 25, and 28. In this area the wall thickness shall not be less than 0.75 times the tabulated minimum wall thickness value,tm. (b) Areas of subminimum thickness shall be sepa- 6.0 DIMENSIONS - rated from each other by an edge to edge distance of more than 1.75 V dtm . _ 6.1 Wall Thickness. For inspection purposes the minimum wall thickness, Xm, of all fittings and valve bodies except flanges at the time of manufacture shall be those shown in Tables 10, 13,16, 19, 22, 25, and 28, except as described in this Section. These thicknesses are all greater than those determined by the following formula: where r * Calculated thickness in inches. Pc ~ Pressure rating class designation in psi (e.g., for Chrs ! `-0 Pv. = 160 pi) d = Inside diameter of fitting (as taken from the tables, e.g., Table 10. Column 5, for Class 150) or port opening of valve (provided that it is not less than 90 percent of the inside diameter as taken from tables), in inches. $ * Stress factor of 7000 psi. This formula results in a wall thickness 50 percent greater than for a simple cylinder designed for a stress of 7000 psi subjected to an internal pressure equal to the pressure rating class designation. The actual values in the Tables range from 0.10 to 0.20 in. heavier than those given by the formula. Ad ditional metal thickness needed for assembly stresses, valve closing stresses, shapes other than circular, and stress concentrations must be determined by in dividual manufacturers, since these factors vary wide ly.. In particular 45 deg. laterals, true Ys, crosses, etc. may require additional reinforcement to com pensate for inherent weakness in products of these shapes. --____ 6.1.1 Local Areas. Local areas having less than minimum wall thickness will be acceptable provided that: (a) The area of subminimum thickness can be 6.1.2 Valve Body Necks. Valve body necks must maintain the minimum wall thickness as described in Paragraphs 6.1 and 6.1.1 within a region from-the^outside of the body run of 1.1 V dim measured along the neck direction. The diameter, d, is as defined in paragraph 6.1 and is the minimum wall thickness as shown in Tables 10, 13, 16, 19, 22, 25, and 28. Sharp discontinuities and abrupt changes in section are to be avoided in transitions in the body neck. Straight circular sections of valve body necks with inside diameter, d', must be provided with local wall thickness at least equal to t' where In the special case, where d'> lid, it is necessary that the equation given above be satisfied for the en tire body neck length. Minimum wall thickness re quirements are applicable to and measured from in ternally wetted surfaces, e.g. up to the point where the body-bonnet seal is effected. 6.2 Center-to-Contact Surface and Center-to-End. 6.2.1 Design. A principle of design in this standard is to maintain a fixed position for the flange edge with reference to the body of the fitting. The ad dition of any facing is beyond the outside edge of the flange except for the .06-in. (1.6 mm) raised face in the Class 150 and 300 standards. (See Paragraph 63, Facings.) 6.2.2 Standard Fittings. Center-to-contact surface, center-to-fiange edge, and center-to-end (ring-joint) dimensions are shown in Tables 10, 13,16, 19, 22, 25, and 28. 6.23 Reducing Fittings. Center-to-contact surface or center-to-flange edge dimensions for all openings shall be the same as those of straight size fittings of the largest opening. The contact surface-to-contact surface or flanged edge-to-flange edge dimensions S T 01*08880 ST0408880 AMERICAN NATIONAL STANDARD STEEL PIPE FLANGES, FLANGED VALVES AND FITTINGS AC*'-*ir; JAIfC:.""' 'Ll* m\ tji ; ANSI 8165-1973 for all combinations of reducers and eccentric re be removed when bolting to cast iron fhnget. See ducers shall be as listed for the larger opening. .-Footnote 3, Paragraph 5.3. 6.2.4 Side Outlet Fittings. Side outlet elbows, 63.1.2 In the case of the ,25-in. (6.4 mm) aide outlet tees, and side outlet crosses, shall have all raised face, tongue or male face (other than .06-in. openings on intersecting center tines and the center- (1.6 mm) raised face for Class 150 and 300), the to-contact surface dimensions of the side outlet shall minimum flange thickness "C" shall be first provided be the same as for the largest opening. Long radius and then the raised face, tongue, or male face, shall elbows with side outlet shall have the side outlet on be added thereto. the radial center line of the elbow and the center-tocontact surface dimension of the side outlet shall be the same as for the regular 90 deg elbow of the -largest opening. 6.3.13 With ring-joint, groove, or female face, the minimum flange thickness shall be first provided and then sufficient metal added thereto so that the bottom of the ring-joint groove, or the contact face 63.5 Special Degree Elbows. Special degree el of the groove or female, is in the same plane as the bows, ranging from 1 to 45 deg inclusive, shall have flange edge of a full thickness flange. the same center-to-contact surface dimensions as 45 deg elbows, and those over 45 deg and up to 90 deg inclusive shall have the same center-to-contact surface dimensions as 90 deg elbows. The angle desig nation of an elbow is its deflection from straight Hne flow and is also the angle between the flange 6.33 For Lapped Joints. For Lapped Joints,facings shall be furnished as follows: 633.1' Raised Face. Finished height of face shall be no less than nominal pipe wall thickness. faces. 63.2.2 Large Male and Female. Finished height - 6.2.6 Other Dimensions. The face-to-face dimen sions of flanged end valves, and end-to-end dimen- -A -4.- ....fjjWJ.U, * w * ... ---- r. -- sure rating class shall be in accordance with the of male shall be no less than wall thickness of pipe used or 0.25-in., whichever is greater. Thickness of lao remaining after manhinino female far* shall he no less than wall thickness of pipe used. ANSI Standard B16.10 Face-to-Face Dimensions for Ferrous Valves, See Footnote 3. Paragraph 5.3. re garding facing and face-to-face dimensions for ex ceptions when bolting steel flanges to cast iron tlanges. 6.333 Tongue and Groove. Thickness of lap remaining after machining tongue or groove face shall be no less than wall thickness of pipe used. 633.4 Ring-Joint. Thickness of lap remaining after machining ring-groove shall be no less than wall 63 Facings. thickness of pipe used. 63.1 For Other Than Lapped Joints. Table 4 gives dimensions for facing other jhan ring-joint. Table 5 gives dimensions for ring-joint facings. Fig. 8 ^ows application of facings. Class 150 and 300 valves, fittings, and companion flanges are regularly furnished with a ,06-in. (1.6 mm) raised face which is included in the minimum flange thickness "C", .Class 400, 600. 900. 1500, and 2500 valves, fittings and companion flanges are regularly furnished with 25-in. (6.4 mm) raised face which is additional to the minimum flange thickness "C". Any other facing than the above, when required for any pressure, shall be furnished as follows: ' -- 63.1.1 No metal shall be cut from the mini mum flange thickness specified herein except on Class ISO and 300 tlanges; then the raised face may 63.2.5 Dimensions. The outside diameters of lap for ring joints are shown in Table 5, dimension K. The outside diameters of laps for large female, large tongue and groove, and small tongue and groove, are shown in Table 4. Small male and female are not used with lapped joints. 6.3.3 Blind Flanges. Blind Flanges need not be faced in the center if, when this center part is raised, its diameter is at least 1 -in. (25.4 mm) smaller than the inside diameter of the corresponding pressure class fittings, as given in the tables. When the center part is depressed, its diameter shall not be greater than the in side diameter of the corresponding pressure class fittings, as given in the tables. Machining of the depressed center is not required. ST0408881 ST0408881 AMERICAN NATIONAL STANDARD STEEL PIPE FLANGES. CLANGED VALVES AND FITTINGS ^ANSi 8165--1973 6.3.4 Flange Facing Finish. The finish of contact faces of pipe flanges and connecting end flanges of valves and fittings shall be judged by visual compan ion with AARH Standards (see ANSI B46.1) and not by instruments having stylus tracers and electronic amplification. The finishes required are given below. -Other finishes may be furnished by agreement be tween user and manufacturer. 6.3.4.1 Raised Face and Large Male and Feenale. Either a serrated-concentric or spiral finish hav ing from 24 to 40 grooves per inch (.6 to 1 mm pitch) shall be used. The cutting tool employed shall have an approximate .06 in. (1.6 mm) or greater radius. The resultant surface finish, as judged by visual comparison with AARH Standards, shall have a 500 microinch maximum roughness for Class 150 and 300 flanges and 250 microinch maximum roughness for Class 400 and higher rated flanges. 6.3.4.2 Tongue and Groove and Small Male and Female. The gasket contact surface shall have a 125 microinch maximum roughness as judged by visual comparison with AARH Standards. 6.3.4.3 Ring Joint. The side walls of the gasket ^IWUfV AMUU Wh wJ illtwiuulwtl IMUAUIIIMtl as judged by visual comparison with Standards. AARH 6.4 Pipe Flange Bolt Holes. Bolt holes are in multi ples of four so that valves or fittings may face in any quadrant. Pairs of bolt holes shall straddle the centerlines. * 6.5 Spot Facing. All cast and forged steel flanges, flanged fittings, and flanged valves shall have bearing surfaces for bolting which shall be parallel to the flange face within 1 deg. Any back facing or spot facing required to accomplish parallelism shall not reduce the flange thickness "C" below the dimen sions given in Tables 9, 10, 12. 13. 15. 16, 18, 19, 21, 22, 24, 25, 26, and 28. Diameter of spot facing shall be in accordance with MSS Standard Practice, Spot Facing for Bronze, Iron and Steel Flanges (SP-9). 6.6 Welding End Preparation, Flanges. Welding ends shall be in conformance with ANSI B 16.25 and for convenience are shown in Figures 9, 10, 11, and 12. The contour of the outside of the welding neck flanges beyond the welding groove is shown in Figs. 9 and 10. Three types of internal machining for welding ends have been standardized and axe as shown in Figs. 9,10,11, and 12. x 6.7 Reducing Flanges. 6.7.1 Drilling, OD, Thickness, and Facing Dimen sions. Flange drilling, OD, thickness, and facing are the same as those of the standard flange of the size from which the reduction is being made. 6.7.2 Hub Dimensions. 6.7.2.1 Threaded and Slip-On Flanges. The hub dimensions shall be at least as large as those of the standard flange of the size to which the reduc tion is being made. The hub may be larger or omitted as detailed in Table 12. G.7.2.2 Welding Neck Flanqes. The hub di mensions shall be the same as those of the standard flange of the size to which the reduction is being made. 6.8 Threads for Threaded Flanges. Except as pro vided in Footnote 3, Fig. 8, and Footnote 9, Table 4, threaded flanges shall have an American National Standard taper pipe thread conforming to ANSI B2.1. The thread shall be concentric with the axis of the flange and variations in alignment shall not exceed 0.06-in. per foot (5 mm per meter). 6.8.1 Class 150 flanges are made without a counterbore and the threads shall be chamfered ap proximately to the major diameter of the thread at the back of the flange at an angle of approximately 45 deg. with the axis of the thread to afford easy entrance in making a joint and to protect the thread. The chamfer shall be concentric with the thread and shall be included in the measurement of the thread length. 6.8.2 Class 300 and higher pressure flanges are made with a counterbore and the threads shall be chamfered to the diameter of the counterbore at the back of the flange at an angle of approximately 45 deg. with the axis of the threads to afford easy entrance in making a joint. The counterbore and chamfer shall be concentric with the thread. 6.8.3 The minimum length of effective thread in reducing flanges shall be at least equal to dimension T of the corresponding pressure class threaded flange as shown in the tables, but does not necessarily ex tend to the face of the flange. See Table 7 for re ducing threaded flanges. ST0408882 t l, T i ST0408882 AMERICAN NATIONAL STANDARD STEEL PIPE F LANGES, FLANGED VALVES AND FITTINGS ', ORA *T' - . n tj- `-tv ' . ANSI B165-1973 6.8.4 The gaging notch of the working gage shall come flush with the bottom of chamfer in all -threaded flanges, and shall be considered as being the intersection of the chamfer cone and the pitch cone of the thread. This depth of chamfer is approximately equal to one-half the pitch of the thread. The maxi mum allowable thread variation is one turn large or snail from the gaging notch. 6.8.5 Appendix A to the standard is taken from the ANSI Standard for Pipe Threads. ANSI B2.1,and indicates the distance and number of turns that ex ternal pipe threads may be made longer than regular for use with the higher pressure flanges to bring the snail end of the thread close to the face of the flange when both parts are assembled by power. stud-bolts shall be coarse series, Class 2A (ANSI B1.1), and nuts shall be coarse series, Class 2B. 6.9.1.5 All alloy steel bolting shall be threaded in accordance with ANSI Bl.l. Nominal diameters Tin. and smaller shall be of the coarse thread series; nominal diameters Tl/8-in. and larger shall be of the 8-thread series. Bolls, studs, and stud-bolts shall have a Class 2A thread, and nuts shall have Class 2B thread. 6.9.1.6 The end flange bolting is based on a stress not to exceed 7000 psi, assuming a pressure equal to the pressure rating class designation to act upon an area circumscribed by the outside diameter of raised face etc.. Column R, Table 4. 6.9Stud-Bolts, Bolts, and Nuts. 1 6.9.1 End Flange Bolting. 6.9.1.1 Alloy-steel stud-bolts threaded at both ends or full length, or bolts with hexagonal heads, and conforming to American National Standard heavy dimensions (ANSI B18.2.11. mav be used and shall have nuts conforming to American National Standard heavy dim'*r,sinns (A.NS! B1S.2.2). 6.9.1.2 Alloy-s.ee! stud bolts, with a nut at each end, are recommended for high-temperature service. Stud-bolt lengths are specified in Tables 8, 11, 14, 17, 20. 23, and 27 and include the thickness of two nuts. The stud-bolt lengths given in the tables do not include the height of any point. A point is that part of a stud-bolt or a bolt beyond the thread and may be chamfered, rounded, or sheared. For method of calculating bolt lengths not given in tables, see Appendix F. _These lengths are established as a standard for the convenience of industry to simplify the assembly of these parts on construction work, but consumers may select combinations of these bolt lengths to suit their needs. 6.9.1.3 Carbon steel bolts and nuts shall be American National Standard. Bolts smaller than 3/4-in. shall have square heads or heavy hex heads (ANSI B18.2.1), and shall have heavy hex nuts (ANSI B18.2.2). Bolts 3/4-in. and larger shall have square heads or hex heads (ANSI B18.2.I), and shall have hex nuts or heavy hex nuts (ANSI B 18.2.2). 6.9.1.4 Threads of carbon steel bolts and 6.92 Valve Bonnet and Body Flange Bolting 6.9.2.1 Except as provided herein, valve bon net and body flange bolting shall be of alloy steel conforming to a bolting specification given in Table 1. For Cl.-ss 300 and lower, provided the service tem perature is limited to 500F or lower and marking is m accordance with Paragraph 4.1.8, ASTM A307 Grade R <lr.t bjtiug be Si-sii. wit 1/C threaded in accordance with ANSI Bl.l. B.9.2.2 Valve bonnet flange bolting shall be designed in accordance with one of the following two methods. 6.9.2.2(a) Valve bonnet flange bolting shall be such that a direct nominal stress not to exceed 9000 psi for alloy steel bolting or 7000 psi for ASTM A307 Grade B bolting results on the effective direct tensile stress area of the bolts assuming a pressure, in pounds per square inch, equal to the rating class designation to act upon an area bounded by the ef fective outside periphery of the gasket. In the case of a ring joint the bounded area is defined by the pitch diameter of the ring. 6.9.2.2(b) Valve bonnet flange bolting shall be determined per ASME Boiler and Pressure Vessel Code, Section VUl, Division I, and must include, in addition to pressure loading, the applicable maximum stem operating force. Allowable bolting stresses shall be per Section VIII, Division 1, for the bolting ma terial being used. All combinations of pressure and temperature within the valve class rating must be considered. ,, 1 ST0408883 ST0408883 AMERICAN NATIONAL STANDARD STEEL PIPE FLANGES, FLANGED VALVES AND FITTINGS ^ANSI B16J5--1973 6.9.23 Valves may have special flanged joints which split the valve either perpendicular to, or at an angle with, the piping. Since such flanged joints are subject to piping loads, bolting for these flanges shall be based on a direct stress not to exceed 7000 psi assuming a pressure equal to the rating class designa tion, expressed as psi, to act upon an area bounded by the effective outside periphery of the gasket. . 6.10 Gaskets for Line Flanges 6.10.1 Ring joint gasket dimensions shall conform to ANSI B1630. 6.10.2 For flanges with raised face, or with large male-and-female face, gaskets shall conform with limiting dimensions of Appendix E. 6.10.3 For flanges having large or small tongueand-groove faces all gaskets, except solid flat metal gaskets, shall cover the bottom of the groove with minimum clearance. (See Paragraph 7.2.1 for toler ance applicable to groove.) Solid flat metal gaskets shall have contact width not greater than for Group III gaskets. 6.10.4 For flanges with smali maie-and-femaie face, care must be taken to insure that adequate bear ing surface is provided for the gaskets. This applies particularly where the joint is made on the end of pipe. See Figure 8. 6.11 Auxiliary Connections 6.11.1 Pipe Thread Tapping. Holes may be tapped in the wall of a fitting or valve if the metal is thick enough to allow the effective thread length speci fied in Fig. 4. Where thread length is insufficient, or the tapped hole needs reinforcement, a boss shall be added. 6.11.2 Welded Connections. 6.113.1 Sockets. Sockets (socket welding) may be provided in the wall of a fitting or valve if the metal is thick enough to afford the depth of socket and retaining wall specified in Fig. 5. Where the wall thickness is insufficient, or the size of socket requires opening reinforcement, a boss shall be added. 6.113.2 Butt-Weld. Connections may be at tached by butt-welding directly to the wall of the fitting. See Fig. 6. Where the size of an opening re quites reinforcement, a boss shall be added. 6.11.3 Bosses. Where bosses are required, the diameters shall be not less than those shown in Fig. 7, and the height shall provide lengths as specified in Fig. 4 or in Fig. 5. 6.11.4 Size. Unless otherwise specified, auxiliary connections shall be of the pipe sizes given below: Size of Fitting or Valves-lnches Size of Connection-Inches 2 to 4 5 to 8 1/2. 3/4 10 to 24 1 6.11.5 Designating Locations. The means of desig nating the locations for auxiliary connections in fittings is shown in Fig. I and for valves in Fig. 2. Each possible location is designated by a letter so that the desired locations for the various types of fittings or valves may be specified without using fur ther sketches or description. 7.0 TOLERANCES 7.1 Center-to-Contact Surfaces, and Center-to-End (Ring-Join!) 7.1.1 Center-to-Contact Surfaces (other than ringjoint) Sizes 10 in. and smaller .03 in. (0.8 mm) Sizes 12 in. and larger .06 in. (1.6 mm) 7.13 Center-to-End (ring-joint) Sizes 10 in. and smaller .03 in. (0.8 mm) Sizes 12 in. and larger .06 in. (1.6 mm) 7.13 Contact Surface-to-Contact Surface than ring-joint) Sizes 10 in. and smaller .06 in. (1.6 mm) Sizes 12 in. and larger .12 in. (33 mm) (other 7.1.4 End-to-End (ring-joint) Sizes 10 in. and smaller .06 in. (1.6 mm) Sizes 12 in. and larger .12 in. (33 mm) 73 Facings. 73.1 Inside and Outside Diameter of large and small tongue-and-groove and female, 0.02 in.(.5mm) 73.2 Outside Diameter, 1/16 in. raised face, i03 in. (.8 mm) 733 Outside Diameter, 1/4 in. raised face, .02 v in. (5 mm) *1 8 8 8 0 *1 0 1 $ i ST0408884 s e e e o ijo is AMERICAN NATIONAL STANOARD STEEL PIPE FLANGES, FLANGED VALVES AND FITTINGS ----- . .VTr:-` ANSI BI6S-1973 7.2.4 Ring-joint Groove Tolerances are shown in Table 5. 7.3 Flange Thickness. _ ^__ _ __ _ ___ Sizes" 18 in. and "smaller + .12 in. (3.2 mm) -zero Sizes 20 in. and larger +.19 in. (4.6 mm) -zero 7.4 Hub Dimensions (Including Welding Ends). 7.4.1 Nominal Outside Diameter of Welding End (Dimension A of Figs. 11 and 12). Welding Neck Flanges, Table 6. Sizes S in. and smaller +.09 in. (2.4 mm) -.03 in. (.8 mm) Sizes 6 in. and larger +.16 in. (4.0 mm) -.03 in. (& mm) 7.4.2 Nominal Inside Diameter of Welding Ends of Welding Neck Flanges (Dimension B). Figs. 9 and 10 Sizes 10 in. and smaller 03 in. (0.8 mm) Sizes 12 in. to 18 in. inclusive .06 in. (1.6 mm) Sizes 20 in. and larger +.12 in. (3.2 mm) -.06 in. (1.6 mm) Fig. 11 Sizes 10 in. and smaller +zero -03 in. (0.8 mm) Size: '2 in. and large: +zc:o .06 in. (1.6 mm) 7.4.3 Bore for Backing Ring of Welding Neck Flanges (Dimension C). Fig. It and 12. All sizes +.010 in. (.25 mm) -zero 7.4.4 Thickness of Hub. Regardless of tolerances specified for dimensions A and B, the thickness of hub at the welding end shall never be less than 87!5 percent of the nominal thickness of the pipe to which the flange is to be attached. 7.6 Overall Length of Hub on Welding Neck Flanges. Sizes 10 in. and smaller 06 in. (1.6 mm) Sizes 12 in. and larger .12 in. (3.2 mm) 7.6 Bore of Flanges. 7.6.1 Lapped, Slip-on, and Socket-Welding Flanges. Sizes 10 in. and smaller +.03 in. (0.8 mm) -zero Sizes 12 in. and larger +.06 in. (1.6 mm) -zero 7.6.2 Counterbore, Screwed, and Socket-Welding Flanges. Sizes 10 in. and smaller +.03 in. (0.8 mm) -zero Sizes 12 in. and larger +.06 in. (1.6 mm) -zero 7.7 Drilling and Facing. .- - 7.7.1 Bolt Circle Diameter .06 in. (1.6 mm) 7.7.2 Center-to-center of adjacent bolt holes .03 in. (0.8 mm) 7.7.3 Eccentricity between bolt circle diameter and machined facing diameters: Sizes 2Vt in. and smaller .03 in. (0.8 mm) Sizes 3 in. and larger .06 in.(1.6 mm) 8.0 TEST 8.1 General. Each flanged valve and fitting shall be given a hydrostatic shell test as specified in Par. 8.3. 8.2 Flange Testing. Flanges are not required lo be hydrostatically tested. Flanges attached to (or in tegral with) piping, pressure vessels, or other equip ment may be hydrostatically tested at higher test pressures than specified in Paragraph 83, in which case testing shall be done at the responsibility of the user. In such cases attention should be given to gasket design to avoid excessive deformation of the tlange. 8.3 Valve and Fitting Shell Tests. The hydrostat ic shell test for flanged valves and fittings shall hrno less man i .5 times tne IOuF (5sl) rating rounded off to the next higher 25 psi (1 bar) in crement. Test pressures are shown in Table 3. 8.3.1 The test shall be made with water, which may contain a corrosion inhibitor, with kerosene, or with other suitable fluid provided its viscosity is no greater than that of water, at a test temperature not above 125F (52C). 8.3.2 Valves shall be tested in the partially open position. Leakage through the stem seal shall not be cause for rejection. No visible leakage is permitted through the pressure boundary wall. 8.3.3 The duration of the shell test shall be a minimum of 15 seconds for valves 2 in. and smaller. 1 minute for valves 2(5 in through 8 in., and 3 minutes for valves 10 in. and larger. 8.4 Valve Closure Tests.* Following the shell test, valves designed for shutoff or isolation service, such as stop valves and check valves, shall be given a closure test. Each valve 10-inch nominal pipe size Closure tightness requirements vary with intended service applications and are not within the scope of this standard. ST0408885 AMERICAN NATIONAL 5TANDAR0 STEEL PIPE FLANGES, -fLANGEO VALVES ANO FITTINGS "' , J. ' U ANSI B18J5-19TS and larger regardless of pressure rating class and each valve in the size range of 4-inch through 8-inch nominal pipe size having pressure rating Class 600 and higher shall be given a hydrostatic closure test at a pressure no less than 110% of the 100F (38C) pres sure rating. Valves of smaller size and lower pressure rating class shall, at the manufacturer's option, be given either a hydrostatic closure test at a pressure no less than 110% of the 100F (38C) pressure rating or a gas closure test at a minimum pressure of 80 psig (5.5 bar). 8.4.1 For valves of the double seating type, such as most gate and ball valves, the test pressure shall be applied successively on each side of the dosed gate. As an alternate method for valves with inde pendent double seating (such as double disc gate valves), the pressure may be applied inside the bonnet or body with the discs dosed and both sides open for inspection. 8.4.2 For other valve types, the test pressure shall be applied across the closure member in the -direction producing the most adverse sealing con dition. tor example, a gtooe vaive siiaii ire tested with pressure under the disc. A check valve, globe valve, or other valve type designed, sold, and marked as a one-way valve, requires a closure test only in the appropriate direction. 8.4.3 Valves conforming to this standard in all respects, except that they are designed for operating conditions that have the pressure differential across the closure member limited to values less than the 100F (38C) pressure rating and having actuating devices (direct, mechanical, fluid, or electrical) that would be subject to damage at high differential pres sures, shall be tested as described above, except that the hydrostatic closure test requirement may be reduced to 110% of the maximum specified closed position differential pressure. This exception may be exercised upon agreement between the user and manufacturer. The manufacturer's nameplate data shall include reference to any such limitations. See Paragraph 4.1.8. 8.5 System Hydrostatic Tests. If valves conforming to this standard are subject to hydrostatic testing of systems with the valve in (he dosed position at a pressure greater than the 100F (38C) rating, such testing shall ba the :es~-`,'"'h;l',y of the user ST0L08886 i '-r fc-ii to ST0408886 ST0U0888? ST0408887 PIPING WORKSHOP VALVES 888S Q *i O is 1. VALVE ECONOMY 1.1 General rules of thumb for using different valves. 1.1.1 Screwed ball valves are the cheapest. 1.1.2 Flanged plug valves with teflon lined sleeves (thru size 3" including 4" without operators) are the next in price. 1.1.3 Gate valves are cheaper above 4". 1.1.3.1 Exception - The V-l valve (cast iron bronze trim) is cheaper than the plug valves in the smaller sizes. 1.1.4 Flanged butterfly valves, with the most recent designs (metal to metal seats for services of 150# and 300# up to 1200F), 12" and above are cheaper than gate valves. 1.1.4.1 One additional advantage is the weight difference. (Thp hut.t.erfl v is approximate I v 1/3 the weiaht oh a gate.) 1.2 Material 1.2.1 Use ductile iron over steel whenever possible for an additional cost break. 1.2.2 Forged steel is about 50% cheaper than cast steel for valves sizes up to 3". 1.2.2.1 Disadvantage - The forged steel valves have a port reduction of about one size, therefore the problem of pressure drop may govern. 1.3 Services 1.3.1 Gate valves are used for throttling purposes when a valve is needed for the bypass of a control valve. The bypass is used so infrequently that the economics of the situation governs and thereby eliminating the need for most globe valves. 1.3.2 The 1/4 turn, on-off feature of ball valves is a good labor cost savings over gate valves. 2. SPECIFICATIONS Page 1 of 3 ST0408888 2. SPECIFICATIONS (Cont'd) 2.1 V-51, 150# gate valves, give option of solid or split disk. This valve has been removed from the Specs. 2.1.1 V-51M is still in the Specs. This valve has the same rating but with monel trim and a solid disk only. 2.2 No valves remain in the Specs which have renewable seats. When the seats need repairs, the valve is removed for reconditioning. 2.3 Reconditioned Valves 2.3.1 Dow Spec 47-180 was established strictly for reconditioned valves. 2.3.1.1 The reconditioned valves are probably a better and safer valve because of the 100% pressure testing and inspection. 2.4 Customized Specs 2.4.1 V-SP-(?) numbers are used strictly for the purpose of providing a special valve design for a particular job. This must be called out under special conditions in the Labor Bill for proper identification to the Contractor. Call on the Specifications Group for assistance. 2.5 References 2.5.1 Dow Spec 48-901 in Book 4B is a dictionary item index for locating Spec Numbers according to the "V" Numbers. 2.5.2 Dow Spec 48-902 iri Book 4B is a reference for M & S Catalog Numbers according to the "V" Numbers. 3. SAFETY 3.1 Ball Valves 3.1.1 Dow Spec 47-110 calls out the position a ball valve should be installed for use in a vertical run. 3.1.2 Ball valves thru 1" shall be furnished with round or oval handles as pointed out in the attached handout. 3.2 Service 3.2.1 Don't use V-40 gate valves for this service. They tend to leak at the seals, instead, use a V-713 ball valve which is also cheaper. 3.3 Fuel Oil Service ST0408889 Page 2 of 3 ST0408889 3. SAFETY (Cont'd) 3.3.1 Don't use flanged valves (gaskets will begin to leak over a period of time). Instead, use butt welded valves. 4. MISCELLANEOUS 4.1 Thirteen (13) chrome alloy trim is a form of 400 Series stainless steel, therefore, valves of this nature cannot be used in Chlorine service. 4.2 Valves with hard face seat rings are now called out as stellite rings. The Specs are just being more specific. 4.3 If a problem arises about a particular valve (safety in the design), get in touch with the Specifications Group. Vendors will give response to the Spec Group for improvements in their designs. ST0L0889O Larry Becker/jr 12-2-77 Page 3 of 3 ST0408890 the principal functions of valves starting and stopping flow This is the service for which valves are most generally used--starting and stopping flow. Gate valves are excellently suited for such service. Their seating design, when open, permits fluid to move through the valve in a straight line with minimum restriction ol flow and loss of pressure at the valve. The gate principle explained on page 6 is not practical for throttling. regulating or throttling flow Regulating or throttling flow is done most efficiently with globe or angle valves. Their seating design causes a change in direction of flow through valve body, thereby increasing resistance to flow at the valve. Globe and angle valve disc construction permits closer regulation of flow. These valves are seldom used in sizes above 12 inches, owing to the difficulty of opening and closing the larger valves against pressure. a preventing back flow Check valves perform the single function of checking or preventing reversal of flow in piping. They come in two basic types: swing and lift checks. Flow keeps these valves open, and gravity and reversal of flow close them automatically. As a general rule, swing checks are used with gate valves--lift checks with globe valves. regulating pressure Pressure Regulators are used in lines where it is necessary to reduce incoming pressure to the required service pressure. They not only reduce pressure, but maintain it at the point desired. Reasonable fluctuations of inlet pressure to a regulator valve do not affect outlet pressure for which it is set. relieving pressure Boilers and other equipment subject to damage from excessive pressures should be equipped with safety valves. They usually are spring loaded valves which open automatically when pressure exceeds limit for which the valve is set. These valves are known as Safety Valves and Relief Valves. Safety Valves are generally used for steam, air, or other gases. Relief Valves are usually used for liquids. 5101(08891 ST0408891 18 Aids in selecting pipe, valves and fittings / 2 FIG. 2.9. Valves and valve-flow characteristics. (Illustrations (u) through {/) reproduced by per mission of Wtn. Powell Company, Cincinnati, O.J 5 T 0 408892 ST0408892 Valves 19 (g) Boll check volve FIG. 2.9. {Continutd). (h) Two lypes of diophragm volves ST0408893 ST0408893 ST0U08894 names of parts of basic valve designs relief cap lock nut spring adjusting screw spring body stem locking plug seat blow-back regulating ring disc disc guide case - swing check cap bolts cap disc hinge pin disc hinge disc face disc hinge nut disc body seat ring body wuy seat ring body globe wheel wheel stem packing gland packing stuffing box bonnet union bonnet ring disc stem ring lock washer disc body seal ring body gate wheel yoke sleeve nut yoke yoke sleeve gland flange gland bolts gland packing stuffing box bonnet bushing bonnet joint bolts bonnet stem disc seat rings disc body seat rings body angle wheel wheel nut stem packing nut packing bonnet Ausl- disc stem ring disc body ST0408894 Valves 29 FIG. 2.16. Diaphragm-operated, double-port control valve. FIG. 2.17. Relief valve. (Reproduced by permission of Crosby Valve and Gage Company.) SCREWED CAP ADJUSTING BOLT ADJ. BOLT NUT SPRING WASHER SPRING SPINDLE BONNET BONNET STUD GASKET GUIDE ADJ. RING GASKET ADJ. RING SCREW DISC NOZZLE RING SCREW SPINDLC LOCK CLIP GASKET NOZZLE RING NOZZLC BODY ST0408895 22 / Aids in selecting pipe, valves and linings / 2 TABLE 2.5 COMPARISON OF BASIC VALVE TYPES Valve Type How it Works Use Limitations Gate (See Figs. 2.9 and 2.10.) Gatelike disc actuated by a stem; screw and handwheel move at right angles to flow. The disc seats against two faces for shut-off. On-off service requiring infrequent throttling Not good for throttling service. Throttling causes wire drawing and erosion (plug-type or slidetype is satisfactory for throttling). Pocket at bottom of valve can fill with foreign material and prevent closing of valve. Globe (See Figs. 2.9 and 2.10.) Disc at tached to stem seats on circular opening. Fluid changes direction in passing through valve. Good for throttling service because of increased resistance to flow. Y-valvc (Fig. 2.10) produces lower pressure drop and turbulence than standard globe and is preferred for corrosive or erosive service. Many special alloy and plastic valves (c.g. polyvinyl chloride) for corro sive service are Y-valves. Not recommended for on-off serv ice. Cost and throttling efficiency above 6 in. become unfavorable. Angle (90*) Similar'to globe valve except inlet and outlet makes 90* angle (Fig. 2.9), Same as globe. Used for noncritical service in place of globe valve and an elbow. False economy for industrial uses. Bends in piping systems are sub ject to strains that should not be placed on valves Piug Cock (ice Fig. 2.11.) "Tapered plug with hole same shape as uitcuiyi u. ... body, opens or closes valve with minimum effort. '/< or 1 full-turn required to fully open or close. Three body types are made short, regular and venturi pattern. The short pattern has same face-to-face dimension as gate valves and is preferred for most services. Reg ular and venturi patterns produce less pressure drop and are used when a minimum AT is essential. General: On-off ervice--More chut-off tha* v,dvr Also can be used for throttling but characteristics not as satisfactory as globe for such service. For low* pressure drop service. Unexposcd scats eliminate corrosion and ero sion. Sre below. Lubricated Screw in top of plug is used to force lubricant into grooves in plug and to bottom chamber. Lubri cant reaching bottom chamber forces plug slightly ofT its seat (Fig. 2.11). Only '4 turn required to open or close. "General" uses above and can be used in any serv ice where lubricant does not constitute a disadvantage. Used for critical services which re quire repacking under pressure. Lubricant can cause undesirable contamination of high purity prod ucts. Lubrication requires extra eflfort. Lubricant sets maximum service temperature (659 to !000*F) Non-Iubricated Cam-crank mechanism lifts plug See "General" uses above. Used Not repackable while under pres I and turns it without friction be for services where lubrication is sure; does not provide as positive a ! f tween plug and seat. A turn of inconvenient or temperatures ex seal as lubricated plug. handle is required to open or close. ceed lubricated plug limits. Excel lent for corrosive service requiring special alloys and linings. ST0lt08896 ST0408896 Valves 23 TABLE 2.5 (Continued) Valve Type How it Works Use Limitations Check Valve General: Prevent back-flow in lines. Swing check Flow keeps swing gate open, while gravity and flow reversal close it. Tilling-iypc is pivoted at center and insures closing without slam ming (Figs. 2.9 and 2.10). Out side levers and weights are used on standard swing checks when greater sensitivity for changes in flow is required. Where minimum pressure drop is required--Best for liquids and for large line sizes. Not suitable in line subject to pul sating flow. Some styles operate only-in a horizontal position. Piston check Flow pattern as in globe valve. Flow forces piston up and reversal and gravity returns it to scat (Figs. 2.9 and 2.10). Good for vapors, steam, and water. Suitable for pulsating flow. Many designs are for horizontal service only. Not common in sizes over 6 in. Not recommended for service which deposit solids. Ball check A lift-type check consisting of a ball with guides (Fig. 2.9). Stops flow reversal more rapidly than others. Good for viscous fluids which deposit solid residues that would impair operation of other types. Vertical or horizontal installation is possible. Not common in sizes over 6 in. Not suitable for lines subject to pulsating flow. Needle Similar to globe except disc is pointed at end. Steel valves are often made from barstock and are nigged. Valves 2 in. and smaller for use on pilot plants and bench-scale equip ment and instrument service. Good for manual flow control. Groundjoint union hnnnrt ronncction-nrcf erablc. Positive shut-ofTnot always possible or desirable. In some design;, seat is scored if shut down tightly. Automatic Control (See Fig. 2.16.) Similar in principle to globe valve but precision-built for accurate automatic control. Air pressure actuates diaphragm causing the stem to move, opening or dosing valve orifice. Air preslure is controlled by the primary measuring instrument. The valve plug is tapered (parabolic) or has V-ports to give the desired throt tling characteristics. Double-port valves give better control range and require only small force to move stem. Automatic control of flow and pressure in processes. First cost is high, but in most areas of world resulting labor savings and improved operating results far offset this cost. Often not justified, however, for small-scale production or testing. Hand Control Single-port hand control valves with micrometer for setting valve to within '/ioo of a turn are useful in pilot plants and other applica tions where automatic confol is not justified. Packless Diaphragm Valve Diaphragm seals the bonnet, pre venting fluid from contacting inner bonnet or stem (Fig. 2.9). Seating member may be a separate disc diaphragm or a solid diaphragm may serve as the closing device. For corrosive, volatile, and toxic fluid service in which leakage can not be tolerated. All plastic valves are produced in this design. Choice of diaphragms limited to rubber-like or plastic materials which cannot withstand tempera tures above 400'F or operate effec tively at sub-atmospheric temper atures. ST0U08891 ST0408897 24 Aids in selecting pipe, valves and fittings / 2 TABLE 2.5 (Concluded) Valve Type How it Works Use Limitations Relief Valve Rupture Disc Valve opens automatically when forcc on seat exceeds that of spring, Returns to closed position when excess pressure has been relieved (Fig. 2.17). For protecting equipment and vessels from excessive pressures. Require periodic inspection to in sure operability. Not good for highly corrosive fluids. Thin metal diaphragm ruptures at a predesigned pressure. For protecting equipment and vessels from excessive pressures when maintenance is difficult and exces sive pressure occurrences rare. Diaphragm must be replaced after each excess pressure occurrence. ST0408898 ST0408898 ST0L08899 2B TABLE 2.6 DESIGN FEATURES OF GATE VALVES COMPARED The following tabulation of design features is based on the suggestions of O. L. I-cwis ['Hie Petroleum Engineer, 027 Novem ber, 1052]. It is presented here as a guide in comparing gate valves and ns a recommendation of the type of analysis that should be made in selecting any type of valve. Feature Comments Stem Seats Wedge Valve Wheel Stuffing Box Repacking Number of Turns to Open T-head method of connecting the stem to the wedge simplest and strongest. Screwed-in scat rings are good for moder ate service conditions. Welded or rolled rings arc best for high pressure, high-tem perature service but rcquiic well-equipped shop for proper replacement. Integral seats satisfactory for bronze and iron valves in services not requiring re placement. Should be guided through full travel to prevent chatter. Steel preferred--cast iron often fails under abuse of "cheaters," etc. Deep stuffing box required. Cheap valves have shallow stuffing box which receive only a few rings of packing. Can valve be repacked '.incler picasm.-f This is a desirable feature in many situa tion!. Where this is important, it should be checked. There are variations between manufacturers which at times may be significant. Aids in selecting pipe, valves and fittings / 2 TABLE 2.7 END CONNECTIONS ON VALVES AND FITTINGS IN PROCESS PLANTS Type Screwed Socket Welding Butt-welding Flanged Solder Joint Brazing Joint Flared and Compression Packed and Poured Application Used extensively for pipe 2" and smaller. Made in iron, steel, brass and various alloys. Popular in small sizes 2" and under for severe services where leakage danger must be eliminated. Self-aligning and easy to install. Used almost exclusively for all fittings :n process lines 2" to 3" and above. Not rominon for valves. Used as unions ami as cuds on Valves in welded lines. Thus most lines 2" to 3" or above in process plants have flanged unions and flanged valves. Low temperature joint for copper tub ing in plumbing and heating service-- Service limited by melting point of tinlead solder (362-450F). Manufac turer's recommendations for maximum temperature for valve or fitting should be followed. Joint for brass and copper lines which withstands higher temperature than solder joint--Factory inserted ring of silver brazing alloy makes seal upon heating with oxyacctylene (lame. Melt ing point of silver brazing alloy is 1300*F. Service recommendations of manufacturer for particular valve or fitting should be consulted. For thin-walled tubing, and fittings and valves used with thin-walled tubing. Popular for pilot plant and instrumen tation work where disassembly is necessary. For east iron, water, gas, and sewage piping. ST0408899 end connections on valves and fittings...an important consideration Just as a chain i3 no stronger than its weakest link, a piping system is no better than its connecting links. Specifying the right end connection on valves and fittings is, therefore, of the utmost importance. Be sure you know which type of end connection is best suited to the working con ditions of your particular system. Shown below are the types of end connections most commonly used on valves and fittings, although not all piping materials are available in all types of end connections. Each type has one or more variants, with steel flange joints having the greatest variety. screwed ends Screwed end valves and fittings are by far the most widely used. This type of end connection is found in brass, iron, steel, and alloy piping materials. They are suited for all pressures, but are usually confined to smaller pipe sizes. The larger the pipe size, the more difficult it is to make up the screwed joint. weldin'; ends Welding ends, available in steel valves and fittings only, are used mainly for higher pressure-temperature services. They are recommended for lines not requiring frequent dismantling. There are two types of weld ing end materials: butt-and socket-welding. Butt-welding valves and fittings come in all sizes; socket-welding ends are usually limited to smaller sizes. brazing ends Brazing end connections are available on brass materials. The ends of such materials are specially designed for use of brazing alloys to make the joint. When the equipment and brazing material are heated with a welding torch to the temperature required by the alloy, a tight sea! is formed between the pipe and valve or fitting. While made in a manner similar to a solder Joint, a brazed joint wiii withstand higher temnpraturea because uf Lhc biazmg materials used. solder ends Solder-joint valves and fittings are used with copper tubing for plumb ing and heating lines and for many low pressure industrial services. The joint is soldered by applying heat. Because of close clearance between the tubing and the socket of the fitting or valve, the solder lions into the joint by capillary attraction. The use of soldered joints under temperature is limited because of the low melting-point of the solder. flared ends Flared end connections are commonly used on valves and fittings for metal and plastic tubing up to 2-inch diameter. The end of tubing is skirted or flared, and a ring nut is used to make a union-type joint. hub ends Hub end connections are generally limited to valves for water supply and sewage piping. The joint is assembled on the socket principle, with pipe inserted in hub end of valve or fitting, then caulked with oakum and sealed with molten lead. Flanged end materials, although made in sizes as small as 1-.-inch, are generally used for larger lines because they are easy to assemble and take down. Flanged joints are made up with much smaller tools than required for screwed connections of comparable size. Flanges which are separate pieces can be attached to pipe in several ways. A few are illustrated. JLL anOLi rlULi screwed flange welding neck flange slip-on welding flange 18 flanged ends c ST0U08900 S \ \ ) ST0408900 ./ cross-seclion cross-section for maximum safety, follow instruction tag when installing safety and relief valves pop HuCcty valves for steam, air, or gas ' do's and (font's when installing No chips, scale, pipe dope, or other matter should be left in inlet of valve or in adjacent connections. Always install pop safety valves with the stem in a vqrtical position. For air or gas service these valves should preferably be installed in verted to allow moisture to collect and seal the seating surfaces. Mount valve directly to tank or vessel without any intervening pipe or fitting. If discharge piping is used, it should he as short as possible, and pref erably larger in size than the outlet of the valve. The height of discharge piping should be adequately supported and never imposed on the valve. A loose slip joint in the outlet piping is recommended, since it permits expansion and contraction without unduly affecting the valve. Wrenches should be used with care so as not to abuse or distort the valve. Periodic testing of the valve by pulling the lever is advised. If not operating properly, valve should be returned to the factory--not serviced in the field. relief valves how they operate iistallalion and maintenance hints Spring loaded relief valves should be installed with the stem vertical. For air or gas service, these valves should preferably be installed in verted, to allow moisture to collect and seal the seating surfaces. No chips, scale, pipe dope, or other foreign matter should be left in the in let of the valve or in the adjacent connections. Whenever piping is installed in the inlet or outlet of these valves, it must be at ieasl as iarge as the valve connections. Under no circum stances snouia it oe reduced. This piping should be adequately sup ported to prevent line strains from causing the valve to leak at the seat. ST040890I 17 ST0408901 slem upalways best! stem down-- not recommended pressure and lem perature above disc help insure tight seatin|. hints on installing valves... gates, globes, angles and checks stem horizontal-- not practical with some valves with pressure under disc, coolmgof stem may cause tust enough contraction to unseat valve and cause leakage. what's tin; best working position for nny vnlvo? Valves work best when standing; upright, with the stem pointing straight up. Any stem position from straight-up to horizontal is satis factory, but still a compromise. Installing a valve with its stem down is not good practice. With a valve in this inverted position, the bonnet acts as a trap for sediment which may cut and damage the stem. Up side down position for valves on liquid lines subjected to freezing tem peratures is bad because liquid trapped in bonnet may freeze and rupture it. pressure above or below the discwhich is better? This question, which applies to both globe and angle valves, has several answers, because service conditions vary. On lines where continuous flow is desired, it is safer to have pressure below the disc. For example, a disc may become separated from its stem and automatically shut oif flow if pressure is above the disc. If this is dangerous for certain in stallations, then the pressure should be below the disc. In general, however, unless pressure under the disc is definitely re quired, a globe or an angle valve will give more satisfactory service when installed with pressure above the disc. An exception is a valve with a renewable composition disc which, preferably, should have pres sure below the disc to assure longer disc life. most manufacturers plainly mark check valves lor direction ot now. follow the marking when putting check valves into lines Primary caution to be observed when installing any check valve, whether swing or lift check type, is to see that flow enters at the proper end, i. e., that the disc opens with flow. If you follow the marking on the body of the valve, you can be sure the valve is properly installed and that the disc will be properly seated by backflow, or by gravity when there is no flow. ST0408902 use angrle valves to save pipe joints As shown above, it is good piping practice to use an angle valve wherever possible when making a 90 turn in a line. Not only does an angle valve give less restric tion to flow than the elbow and globe valve it dis places, it also reduces the number of joints in a line and saves on erection time. 01 ST0408902 ST0l*08903 BALL VALVES The Texas Division over the years has experienced a number of near misses and general misapplication of the ball valve. In April of 1972 the Engineering Specification Group, Purchasing, and the Texas Division Safety Team met to discuss the safety of the valve and the near misses caused by the lever or tee handles that were being provided for the valves. The group was to look into the usage of the valve. The following are some of the findings of the group. The ball valve is one of three types of quarter turn valves and was found to take less torque in the small sizes, one inch and under, to open or close than the other two types of valves (plug, butterfly). The ball valve like the other two was being furnished to Dow with a lever or tee handle. (See photo graph 01, Fig. 2 for tee handle, and photograph it2 for lever handle). Since either one of these handles could be accidentally turned, the idea of using a round or oval handle came into being. This type handle could not be accidentally turned on as easily as the lever or tee. (See photograph it 1 and 2 for the type handles used on valves one inch and under. Photograph Si In photograph 01, Fig. 1 is shown a Hills-McCanna round metal handle which is now furnished on all of their small valves. Earlier round handles provided by Hills-McCanna made of plastic proved to be unsatisfactory. This valve and the metal handle is now being used by the Midland Division. It is an excellent handle if insulation is used. The round handle, Fig. 3 in photograph Si does not have a directional flow indicator. This handle is not suitable for use on ball valves. With this type handle you must look on top of the stem to see if the valve is open or closed. ST0408903 STOt, 0890k The oval handle, Fig. 4, photograph III, is the type handle furnished by Smith, Jenkins, Lunkenheimer and Whitey valve companies. This handle like the round handle cannot be easily turned by accident. The round handle, Fig. 6, photograph III, is similar to the type round handles for the Jamesbury, Clayton Marks, Crane, Gemini, and some Hills-McCanna. The Hills-McCanna valve shown in Fig. 2, photograph it 1, should be a directional flow valve when used as a terminal valve in corrosive or hazardous service. This should apply to Lunk, and Clayton Marks also. These valves have a screw retainer seal on one end, and should be installed with that end on the pressure side. The Crane ball valve has screw retainer seals at each end and should not be used for any terminal service other than air and water. The Smith valve shown in Fig. 5, photograph II1, and the Jenkins (not shown) may be used as a terminal valve in any service. They are two piece valves with adjustable stem packing. The valve shown in photograph It2 is an unsafe valve as it has screwed end pieces that hold the ball in place. The end pieces could be screwed out when the pipe is removed or if for any reason the end piece should become loose the valve would leak or spray product. The above valve is a W.K.M.. This valve has been removed from the Dow specification piping books< ii ST0408904 ST0U0890S Photograph #3 The valve shown in Photograph #3 is made by The Jamesbury Company. This valve also has a screwed end piece that could come out when pipe is being removed from the end. To use this valve in the Texas Division two tack welds (T/w) are required. There should be sue on each side of the end piece to pi event it from backing out. If you have any questions or need further information on these valves or any valves call Benny Howard, Engineering Specifications, telephone 3337. 9/2/76 iii ST0408905 G?t 12/70 ! DOW CHEMICAL U.S.A. l TEXAS DIVISION JOB NO. AUTH. NO.. CHARGE NO. SUBJECT \/ fir / I/E CO^l :DATE g/W?^ L. CAA FILE NO. /SCMS BY ft &/. SC-HUPP SHEET____________________________________________/ OF_______ A &all Valves. 79 7 3 * 2/ n 7?75"CPW 7. 1 :i ;: 111_!;__ L. * ; , S~CO -ZJ3.___SCfLCW&D CAfc&oti r 4 7.18 7 Usci- 1 STEEL &A-LL VALVE %> 9.V .... /?>?. ;..;5FAT-.... AM& SEALS............j_. i 1" _ iOjiC zs'.ja : i ' ;; ;j ' 'i.... !..r .1 : : : ; r ! "M' ; i; ....ri ;i f r\\ >: \) Z* ZJ> oE r i . 517 .1*1 . z\ .y-66s-A J; j ; 1 SOO-L.Q>t S C 7; sma:l Ball val\j ey //ecpfFNE. 34" OfL fhvNA-N SEATS AHO S^alS i" Z" I \ 7 /*>4? t 2Si2g rfAf 3, -..................................................... S'oo-lB, SC^^WEb <2A/Z6cN _ STEEL...Mll. VAL'/E w/ .... STAINLESS STEEL StttLj ___ TEFLON. SEATS* aw seals ;Y/Z >: i 8.? 3 HA[ /iZD 2" . 3C..30 $ }7*yj azj3 .. Zl*(o8 .... 8lS?~ 4, _y-6&<r F .; 500-^6,. _SC(i-E\NEP> C/f/?/3<W .. L.Lsteel valve Wfi&f / _L_ flmlS 74 y 9*3/. .J $ zfA/Z- seal seats ................ AND seals, }" Zv lo&ST 2e6b zsji7 68+ & LT, V-(n L Cd 5'OO-lQ. SCfLEVJE\> 30 Z o(L /z7 Zo*r STAINLESS STElL 2/4v (Ball valtejTEFlln seats /" AN IS 5 rSALS z,f #(0 f tfoOO so^/o 3 ,36 47*43 7Z*>t8 )EZ^37 f .............................................. i; I ! i Sroi>08906 ; ST0408906 *7 I I 2/? lir> DOW CHEMICAL U-S.A. TEXAS OlVISION AUTH. NO._ CHARGE NO. . s u bj ect y/M-i/g: -- Co m~T~ CQTT FILE NO. COM PAR I5CH& y_ .DATE. P/3, SCHUP? .TLjkbs- . SHEET 2. OF 6ALL VA) Vf=S Ccont) /?73 Z .? 2J /?75&At' ;i \G, V-fe3 3 1 JS^O-Z-C. SC^Eia/^ 3lL $f $ 3c *3 C :sr*iNiEs$> stee.lt ball VALVEXTEFU)N SEATS AND SHALS _ . . " ; w . /?./r /' . . Z30L3 ,Z" ?/&> 4^.43 ,7*0-S~ 154.27 -7. 1/ -72.7 ./STO-L&. SC&EVJEO 'ALlO'l ZO BALL VALVE. j TEFLON 5&AT AND SEALS $ 34.08 W r L40oo Z" lA%o0D t T(,LO CS. Zo 9G 2.2.0,06 __V-747 'ZLO-LQ,, SCJZEWEb MONEU ' Ball Valve ^jefloN seats * AN0 SEALS - - ............ .... ---............- S1 , 17-7/3 30 0-05 SHEWED 64U VAt.V^) QUf/A -N SEATS AND SEALS f 42.-W w SE120. r! 30s0 z" lSZA-o - ' -.... hi P 4.45 w r (>*55 V >6 ,?8 JO V-1A4300-t~e> 5CflEVJEP SfcON &- &ALL VALVE, r^TLON SEATS AND SEALS 'k" f 5~*43 w 6>9A8 J* 8>o<f Z" - -- .......*;--- //?? . 3di5"/ ;1 1 ___ ' / <j.44 ll,7o I4-75& 3Si to ST0408907 -U-: ST0408907 71 12/70 DOW CHEMICAL U.S-A. TEXAS DIVISION < ST0408908 JOB NO. AUTH. NO. CHAHGE NO.______________________________________________ simirrr l//l/j/ CO$r COM PA/2/SZNS --CON i -DATE .zy-/7g FILE NO. _____________________________ . by EB.SCHUPp SH EET__________________________________________________ OECHECK EO ft ALL. VALVES fCn/Vr) 19 7 3 /S7r(T/U '\ . .' / f V -(&(o~7__ : )C> -<LQ FLAMAEfr OVCfft-E JSPoN JiALL VALVE j TEFLON SEATS AW i; _:? seals,., -j ...... .. ,!'!j!(. ;i '.- ; i<Z,: V-M7A ' ]\ fl< #4iT*zo ...... - ZT SlmGO /34, SO 3" 179 WE 2.6 3.40 4" lZ6>9 -2 '312 Ebb i \ . l/50-t-3 FLAN&ED >UC71L- X/LON \ \&ALL VAH/E jNEQPti.S.tlE 0(L BuNA-M ; SEATS AND $EALS V 3H r. l 3ZS~0 $ Zo 3 AO 3/2L.SO 13 R. tSO -LA , Ft-A/VSEE P>UCTU-IE JXON BAU- \/FLVF VJITH F//dt= <Af. . SEATS A NO SEALS r z" J- fi 4" ' / 37. ZA $ Zo 3 * AO 312.3c X/-737 . r $ 40 ,LO f> 66.33 JSO-LO, f=LAN<SEO STEEL &ALL rr ISAO ..._ VALVE ^TEFLoaJ FEATS AMO SEALS....... -................ ; ill i 3* / 66 AO 4" _.Z<?8A0 72 4*74 Z4-3A0 3S8a20 IT. '/-?37 ft :: i ' 44,45" 4 -72.63 /SO-d-L. FLAA/60 STEEL BALL 2.'' 69.60 VALVE vJ ITR 3/(fi STA/AJLESS 3/f IBOAo STEEL BALL/TEFLON SEATS f SEALS 4tf ZB 9 .&) 141A.B 278J0 4-I8J50 !L. \/"7*o /= ISO-LB, FLAMOtE O STEEL foAll VALUE W/TF Ft EE- SEAL SEATS ANb SEAE3 T S~L,,\E V 92>,3S' 3>( 2/6 +AO +" 319 00 66,3_r> /A.74 243.00 ZSBAO / *. -- j.__ __ . ST0408908  71 U/0 l DOW CHEMICAL U.S.A. ff TEXAS DIVISION JOB NO. CHARGE NO. subject \/ALvEL. COST COMPftW SONS ______________--CO NT - SHEET OF VALVE'S -fcoNT,^ AUTH. NO. FILE NO. BY P, IS, SQ.fiUPT DATE ts/'Th S CHECKED BY ;r/7s -> / * : ms-Q^r J8. V-737 /W /TO-Lfb. FLANCE-b STEEL OftLL VALVE MJIFH ftlOATJE-L- 3ftLC} .JTFLON SEATS and S&ALS r i st Jo 2 ICO oSo 3" LZZaA0 4" 34*po fi 37M 17&A1 33ZotO SI 0,30 'lei. v - 634150-Lft, FLAN6E.fr 3tt> Srft/MIZSS STEEL 3ALl VALVE,TEFLON SEATS ANfr SEALS r .3o / / ^47 r ft&'JS 230 J8S 3" ZLOJO 3 >7*00 4" 38U40 SS4C40 20, V-&7>4- F . HT0-LB, FLAA/CiEfr steel aall Valve.) SEATS ANfr SEALS STAINLESS seal )'f z'f ._3"II 4" i i is~.in 230*85' SS4-&0 2J, V-72C t" # ,, 6g t$-o-u3. FLANCED alloy 2o 6ALL V . valve,TFFL6N SEATS A^> SEALS 3'f 11 .4" 6 /0 *4.7 f. /t?.5o 30 1,00 St4mSO 7L& J50 2z, v-AF . fFO-Lfi, FLANC-rE.fr> bdbNZE fiALL VALVE ? TEFLON SEATS ANfr SEALS n No 0<& 4 47.82 2" /Of ,,so 3,f 183*20 /{SO *4/ Zj5T/./C 4" 26>e>JO 34S-/0 C/> o jr o CD VO O vO ST0408909 'V. onc-'vi^m. TEXAS DIVISION CHARGE NO. .. subject vAlkjEL. C_OST COMPARISONS - CaMTZ^r .SHEET, OF 6, &AT. VALUES AUTH NO. FILE NO. . BY HATE P. AScHUPp z/^ /~> S _CHECKEO BY_ /<?73 let7sCr^f / / V- 3(on SOG- L&. ^c/iewtB os'/y soup* W06c OrATE VALVE jGqfiUdOrt i STEEL 3001. lb C.H&CME. ALLO'f . . : STEE L_ 772/M vj/ ftA# 0~ FACET) A///4S /**, W ID.id l"' . HJ>0 2." ZIP* ': t f n7 zl.tf && S^tfkV Z. V~ stq 800-13. SOlE\A)E^p/6fO SC&EMy SOLID W.&<$. &ATE- VALVE ; CA/Z&JlJ `STEEL /30D'/, /3 CHROME ALU>y STEEL TfcfW. j UhJtoft faCNNET %" t 73J> 4 W 8.FS r /o*80 z" fSEi 4 le.Zo 23.00 SOAO V-S79 A 7V 5CLIP WD6" C-,ATE VA-L l/ V W . (LAfllbOA) STEEL &OPYt /3 C.HR.OML l,f . ALLOY STEEL 772/<M vj iTH HARE-FMEb 2" .......SEAT , 3olT3P> j50AJo/rr 1.18 1^83 zips $ n zo jr 2SJ>4 SLTJ7/ 4. -V-.474 ^ 8oo-lCB. SOlEuJEP 6S/i EPiTE VALVE ) CAR lbON STEEL, Bob'!; ti-ARb -FACED SEAT fi-tNcS, WlPed (bONNETT &" / ?p?<9 W jOjob r ft<S 2" / 19*37 . AI.I? ,26 c4C> 5+2 V SO 4 ISO-L.CS. SCAE^EO } OS// DOUBLE WED6 4 ATE VftL i/E IL STAnOUES Stell ) CbOLT.i> QONftET, TETLtft PACKI a/ ? hi .os ? /" SCf,0>b 2." 10^.70 f 7L>7 7 ?3o67 / 031,64- /ftViS ^F0l#089/0 ST0408910 TEXAS DIVISION JOB NO. _ . _ . .. . - CHARGE NO.___________________________________ subject \//V.v: COST C.fiM PA-PlS#MS _____________________ -CONTr--_________________________ SHEET OF AUTH. NO. FILE NO. _ by PB,5cHUPF DATE 'Z/s/'yTT^ CHECKED BY ..GftTF VAl !/<-*, /9 73 Vfi jS&M t$Lr5k> -- -' - /SO-Lf} , SC&EW&0 vVEDOE VALVE i" ho.2Q .81 yftLVE. ; 3 / (* STAinlesj, STTEELLj y* 3*~0zo .18 SCREWED bOHNET) NON-fctS/tfto STZrt, i" ' !! !1 Z" ' .!j ;'' ` . 4T.I0 81M 83.22. )S*Jt ? 7 V-^?, is~o~lq, sc%ehJeli> os/y double WEa&tL dibc 2.0 j &OL.TEO Packing? <$Ar& vAot/ j Alloy fcONNSTT; 1 Flo aJ fi'r ft" r 2" t S7.ZO 7l,LT PSt-oy IlS~& ^20 t ?7.Z IZ4.U HU? ZSi.ZA- p> \r- 7? a rsn ~/_6. SCR|A/fc> os// C-?ATE VALVE. J ALLOY 2.0 S0Ln> 'NtLPG-E <], y-4g,f _____ JsrO-L-5, BCJLEvJEb 05// POuBlE \ WP6 C-jfiTc. VA-LVE.J ALL. HcNEL, /3olto Bonnet teflon Packing fE' P b'/*ZO Y*f> 73* \b /" os'" 2* lS<*.ZO L P 91* PS /24.V* HI ,/7 ZS3.S0- . -*i f -- if' r i . .. __ i -1 - c -- h0. VrAJ-JT ISO~Lil, StRENEfr Os/y DOUbLE r WfWEOGF &ATE.J ALL P'JPfE NICX.LE.J 2"Bolted Sona/et /.TEFlon Packing /" </> -H O o GO lO ST0408911 JOIJ NO CHARGE NO___ .qiiRiFCT U4LI/F DOW COMICAL IRA. TEXAS DIVISION T ^ - -------------------- :-- ST04089I2 AUTH. NO._____________________________ ___ COS/ COM TA/Zj SaH S TILE NO. _______________________________ BY_____RA. Sc.HUPP DATE 2/i /?? SHEET OF CHECKED BY &ATF VALvSS 1972 msCl/: H. 1/~4o /s o -/v3 f JsJSfD SCREW) {$1*14, STEM 6/TTt) ALL 6&NBE- }UtJfohl bt>NN*f> SPLIT w st>6 <3/SC k $ r.u> A' 7.4* 8 .66 ZO SO /l. *Z 7 Ha 06>Z 18.20 *4. S3 /^, v-i /LS-Lfr. valve j TlH RLAUt-rE 0 OS/Y 6Ate XRoaJ fcob y ; C^Aige. Zr 3" 4* As Jo st. st 82.on / /Ot^oA 141 .3/ I'?? .3"} /3. V'S~l JSo 'L% RLANC-Ep os/y &$ /" / UJ& 2" <jbSo ^ ?.7f . W GATE. VALVE > CAP&ofJ STEEL J'v >00/ ) 3 caaoate Alu>Y STEEl 7&A 4U 17f.36 3 26.^ 38! m-. v-^/7_______ f{ /EO-Lfb FLAGGED os/y gate 2" valvejCAUboM stsbl ' fiofrYj y* }Z Cti&rTE ALLOY 5TEL T&-\*\ 4" vJllH /YAP-L -FACED 5EATS liSo I57JS& 261,06 3/7.56 y <0.5'S i 04,^ ( /97, G? Z64.ZO /S, V-'IO'A A r /TO- /=l/?a/6CD; ANSI BH.T z,f FlANLB THICKrt-SSS , s/y poo&LE me oc7e <^Ar/ VAi- vtl }3K* 37 4" sr#/a/less sfeel.) Boltfo baa net lizFLON PACK! A <S 73.70 ^ lZ5~.Ac 127,60 201 JT, 2.02*40 323.8? *89.8 5 476.43 /(,. V-3&A iSb-L& FLAMLEbjAA/Sf fblL.S r-.Aitrtr -7--Ul* /7 < f\l f 107 JO / 7S-3./C Z,f 1 iS.-iS y o^sAn 3oijs 4RO.K9 ST0408912 DOW CHKMICAL U.S.A. TF.XAS DIVISION CHARGE NO. subject YALVEL FILE NO. COST Com P/)Rl$CAlS by P./3, SvHLiPR _________--GOfifTZlZDATE EfL .SHEET. -OF .CHECKED BY_ c> Plug valves JAZ? )A1aOm( /SO-L& /^L/J/VGEO PLU& V#Ll/? f* $ 3.1 sisb duotile. TfoN &0&y ^ fZUG, Z,f 30*6o TEFLON SLEE//E 04" VALVE. VJlTti GEAft Of>E&ATD(l\ 2" fv X3(*& ;1 2, V-(oHf S tSD-t-fh PLUG VALVE. J Divert lE }*' JjeOAJ /^)0/ W7 7TY 3/6, sr/)/A/LESS> Z* 3steel. plug, teflon suzeve.j * 4" WUl/ W'TP &* CFEAATVp) 4' f. 22 ' /,S^ 143.& {>1.00 $ 4z.5'l $Z30 /7do<> 30S\00 2, V-RoZ (SO -Ld> FLANG SD pLC/6 VALVE^ /* pucr/Le: to/0 Ecioy Anp ALLcy f 20 Plug,; re-floa/ suz^vt 3" ` <f" 1/AlV, 0p/E&4TZ>P^ 4" $ 43.SP gs;oo 188.00 313,00 A, ..V-82Q .:. ;..... JS&-L& FLANGEF PLUG VALVEJ /* . 4^,10 $ fZ.pt C/I/2AOA/ STEEL &0b'/ ANO bUCTllE 2A J0A/ PlU$jTEFL0/O SLEZif^FlfcE 3* R,AT)NG (A'* VALVE Qit 0/Mm)Y %& *00 /F8^0d 2-Gf.od </ ,80 178,60 2StSP6 L>> V -- (o(o 9 JSO-L/3, FLANGEto PLUG VALUE. 3/6 STA/NLEgs STEEL 0ODVANO PLUG teflon sleeve (4f valve W ITH GEA/L OffcfiATdP- /" $ 70.GO 743 2" 12? +o0 143,2d 3" 2/3^6 4* 3??o06 Z40.10 4Zt.Qt ST0h089l3 ST0408913  7 l i 7: lo * DOW CHFMICAL U S.A. TEXAS DIVISION JOB NO ____ CHARGE NO SUBJECT. VALUE: Cost -_CcMlM.iScN$> SHEET_______ OE_____ AUTH. NO. ___________________ ___ FILE NO.______________________________________ BY P. ft. SCHJJP/5 DATE. %/*r/7 ~ CHECKED BY _ ptuCn Valves lcl7'3o H7.TCTA 1/- /S0-L& TLU<$, VALVE; ALLOY TO &60V ANO PLU&>} TEFLON SLEEVE. 4" VALVE w/^EACl LAE/IAT01L T 2" 3V &'r 7, VF /sro-ub, FLANGES PLV6 VALVE; MOtiEL fcOOY AND PLVC7} TEFLON SLEzlvEj FlR.E SAFE r^AT/fV6 ; (Au VALVE vJ/gea(Z OPEfiATOfc) /V V yi $ /64.0b 183.6 a 3 zs-.ob 5Z6.00 ' ? 133.00 ZS2.00 435.66 <0(3.60 00 O c- o 00 VO 4T- ST0408914 5T 0 U 0 8 9 15 ST0408915 ID cn CD o -3o o na Choosinj' a a 11ic* mciirr c a a Villvl' a a c cr a X'c ir The content of this brochure is presented also in u motion picture with the same title: "Choosing the Right. Valve." The film pre sentation, like this booklet, is intended mainly as a relresher in the application of basic valve designs for specifiers and buyers of piping equipment. The motion picture, with its animated se quences of valve operation and flow through valves, presents a graphic treatment of the subject. It is recommended for group show ings, and particularly for groups including junior technical personnel. The film is 16 mm. with sound and runs 32 minutes. Prints are available on a loan basis, free-of-charge except for return postage. Re quests should indicate preferred and alternate showing dates. 2 ST0408916 See it in Motion Pictures What's So Important About Choosing the Right Valve? Principal Valve Types Basic Gate Valve Design .. . How itShould be Used Basic Globe Valve Design . . . HighlyEssential toPiping Basic Angle Valve Design Gate Valve Seating Designs .. . Their Service Characteristics Globe and Angle Valve Seating Designs .. . Their Service Characteristics Disc-Stem Connection--Important Factor inValve Selection Variations in Stem Operation Stuffing Box Designs Bonnet and Bonnet-Joint Characteristics of Gate, Globe, and Angle Valves Basic Check Valve Design Basic Ball Valve Design Basic Butterfly Valve Design The Common Materials of Which Valves are Made The Right Valve--Industry's Ally for Progress Page .2 4 5 5 7 7 8, 9 10,11 12 13 13 14 15 16 17 18 19 L I680*J01S 3 ST0408917 ST04089I 8 Valves have long been mure than just a simple device for turning on and shutting off flow. Valve design has kept in step with industrial progress the development of piping techniques, and the ever-growing list of fluids for processing, power, and finished produrt. Progress in valve design puts at the piping engineer's elbow a great variety of valve types, each with some special qualification for service. From these he may choose the right one to provide dependable and economical performance in each particular need. It's a case of carefully matching up the valve's service characteristics with the service requirements. It's a matter ol knowing every detail of the job to be done -working pressure, temperature, fluid, volume of flow, corrosive elements, valve operating cycle, etc. Other equally vital eonsiderations are the original valve cost, installation cost, and, of course, the cost of main tenance. Crane Co., as the world's leading valve manufacturer and supplier, helps customers with the problems of valve select ion every day. With this vast background of experience, Crane presents here as a helpful refresher for specifiers and buyers, the more important elements involved in choosing the right, valve for the right job. 4 ST0408918 u Principal valve types ... Gate Valve Commonly used in industrial piping, this type of valve, as a rule, should be used as a stop valve ... to turn on and shut off the flow, as opposed to regulat ing flow. It gets its name from the gate-like disc which operates at a right angle to the path of flow. Globe and Angle Valves The flow through globe valves follow a changing course, thereby causing increased resistance to flow and considerable pressure drop. Because of the seating arrangements, globe valves are the most suitable for throttling flow. The valve is named after its globular body. Angle valves, similar in principle and a companion line to the globe, are designed to permit a 90 degree turn in piping and are less resistant to flow. See illustration on page 11. Check Valve Sometimes referred to as the non-return valve, the check valve stops backflow in the piping. Unlike the gate and globe valves, this simplest of types operates automatically. Ball Valve Unique in design, this valve controls the flow of a wide variety of fluids. It can be opened or closed in a quarter-turn of the operating handle. The name "ball" is derived from the ball-shaped disc located within the body. A hole through the center of this disc provides the straight-through flow which is characteristic of ball valves. Light and durable, these are the valves that are playing increasingly important roles in our nation's missile projects, as well as in industry and commercial buildings. yj Butterfly Valve Here's a valve that is extremely durable, efficient and reliable. The butterfly valve derives its name from the wing-like action of the disc which operates at right angles to the flow. Its chief advantage is a seating surface which is not critical. The reason for this being the disc impinges against a resilient liner to provide bubble tightness with low operating torque. 61690*101$ 5 ST0408919 ST0408920 Cross-section of gate valve. With its disc lifted fully as shown, the gate valve offers practically no resistance to the flow of fluid through it. A 6-inch gate valve fully closed, having a disc area of approximately 28 square inches, and holding pressure of 300 psi, subjects the disc to a total load of over 4 tons on one side. Basic Gate Valve Design ... how it should, be used Gate valves are by far the most widely used in industrial piping. That's be cause most valves are needed as stop valves -to fully shut off or fully turn on flow--the only job for which gate valves are recommended. Gate valves are inherently suited for wide-open service. Flow moves in a straight line, and practically without resistance when disc is fully raised. Seating is perpendicular or at right angle to the line of flow--meets it head on. That's one reason why gate valves are impractical for throttling service and for too frequent operation. For instance, a 6-inch gate valve holding fluid at 300 psi, puts a load of over 4 tons on one side of the disc, if there is only atmospheric pressure on the other. While seated tight, there's no wear or undue strain on disc or seats. But each time the valve is "cracked open," there's a threat of wire drawing and erosion of seating surfaces by the high-velocity flow. Repeated movement of disc near point of closure under high-velocity flow, may create a drag on seating surfaces and cause galling or scoring on down stream side. A slightly opened disc may cause turbulent flow with vibration and chattering of disc. A gate valve usually requires more turns-- more work- -to open it fully. Also, unlike many globe valves, the volume of flow through the valve is not in direct relation to number of turns of handwheel. Since most gate valves used have wedge disc with matching tapered seats, refacing or repairing of the seating surfaces is not a simple operation. CONCLUSION: Gate valves, while not designed for throttling or too frequent operation are generally ideal for services requiring full flow or no flow. r Gate valves are not designed for throttling In a slightly opened position high-velocity flow will cause wire drawing and erosion of seating surfaces in gate valves. Repeated movement of disc near point of closure under high-pressure flow may gall or score seating surfaces on downstream side. Slightly opened disc in turbulent flow may cause troublesome vibration and chattering. V J ST0408920 Basic Globe and Angle Valve Design ... highly essential to piping Unlike the perpendicular seating in gate valves, globe valve seating is parallel to the line of flow. All contact between seat and disc ends when flow begins. These are advantages for more efficient throttling of flow, with minimum wire drawing and seat erosion. The directly proportionate relation of size of seat opening to number of turns of handwheel, a distinctive feature of plug-type globe valves, permits close flow regulation. An operator can gauge the rate of flow by the number of turns of the wheel. Shorter disc travel--with fewer turns required to operate globe valves-saves considerable time and work--also wear on valve parts. Whatever wear occurs as the result of frequent or severe operation presents less of a maintenance problem than in gate valves. Seat and disc in most globe valves can be repaired without removing the valve from the pipe line. CONCLUSION: Globe valves, while not recommended where resistance to flow and pressure drop would be objectionable, are generally ideal for throttling, and preferable for frequent operation. Volume of flow through this globe valve is proportionate to the number of turns of the handwheel. If it takes 4 turns to open fully, 1 turn releases about 25%, 2 turns release about 50%, and so on. Disc and seat in most globe valves can be conveniently repaired or re newed--often without removing the valve body from the line. ----------------------------------------------------------------------------------------------------------------- Basic Angle Valve Design The angle valve effectively util izes globe valve seating principle while providing for a 90 degree turn in piping. It is less resisting to flow than the globe valve it displaces. Requiresfewer joints;saves make up time and labor. VJ Cross-section of globe valve. Changing di rection of flow means greater resistance to flow--and sometimes, objectionable pressure drop. Seating is parallel to line of flow, and all seat and disc contact ends as soon as valve is "cracked open." Fully opening or closing requires fewer turns than gate valve. 7 ST0408921 IZ680*i01S Gate Valve Seating Designs ... Solid Wedge Disc The most widely used disc in gate valves--the solid wedge-shaped disc--with matching tapered body seating surfaces. Favored for its strong, simple design and single part. Can be installed in any position without danger of jamming due to misalign ment of parts. Ideal for steam service, and well suited for water, air, oil, gas, and many other fluids. Most practical for turbulent flow because there's nothing inside to vibrate and chatter. Refacing of the tapered disc surfaces isn't easy, but there's little need for it if valve is used fully opened or fully closed. Might be subject to some sticking when subjected to extreme temperature changes where body contracts more than disc. For such conditions, Crane flexible wedge disc is recommended. ST0 408922 Double Disc This parallel-faced double disc makes closure by descending between match ing seats in valve body. As the valve is being closed, a lower spreader (or in some cases, a disc wedge) strikes a stop in the bottom of the body. Further closure brings the upper spreader into contact with the lower spreader so that the discs are forced outward against the seats. First opening movement releases discs, and continued operation raises them ciear of seat openings. Widely used on water service, in waterworks and sewage disposal plants; also on oil and gas, in cross-country pipe lines. Generally unsuited for steam. Rapid expansion and high velocity of steam flow tend to vibrate loose internal parts in disc assembly, hastening wear. Exposure of closed valve to rise in external temperature may cause dangerous increase in internal pressure, if non-eompressible liquid is trapped between discs. Because discs and body seats are perpendicular and parallel, repairing or re facing to compensate for wear is easier than on a tapered wedge disc. Should be installed with stem above horizontal for best results. Many spreader mechanisms are subject to jamming when installed with stem below horizontal line. J J i ST0408922 their service characteristics Flexible Wedge Disc Developed especially to overcome sticking in high-temperature service with extreme temperature changes. The shape of the flexible disc can be likened to two wheels on a very short axle. The "axle" or spud at the center of the disc is amply strong to carry the two halves of the disc together at all times .... and yet, it permits a degree of action between them. It is this "flexi bility" that makes the disc tight on both faces over a wide range of pressures .... prevents sticking during temperature changes, and assures minimum operating torque. Although each disc face can move independently of the other .... up to two full degrees .... the construction is one-piece. There are no loose parts to cause harmful vibration. Split Wedge Disc A 2-piece, wedge disc that seats between matching tapered seats in body. Spreader device is simple, and integral with disc halves. When closing, last turn of handwheel forces discs against the seats. When opening, the first turn releases the discs from the seats. Seating Materials ... Key to valve performance The seat and disc constitute the "heart" of a valve; do most of its work. The material from which these parts are made, therefore, becomes important. The tougher the service, the more severe the demand on seating. Valve manufacturers recognize this fact by providing a wider choice of seating materials as valves go up the pressure-temperature scale or are offered for more rigorous service. For relatively low pressures and temperatures and for ordinary fluids, seating materials are not a particularly difficult problem. Bronze and iron valves usually have bronze or bronze-faced seat ing surfaces, or iron valves may be all iron. Non-metallic "com position" discs are availablefor tightseating on bard-to-hold fluids such as air or gasoline. As pressures and temperatures increase or as the service becomes severe, careful consideration must be given to many factors, no one of which can be overemphasized to the detriment of others. Long, trouble-free life requires the proper combination of hard ness, wear-resistance, resistance to corrosion, erosion, galling, seizing, and temperature. Nor does it follow that a satisfactory combination in one instance will serve equally well in all others. Type of valve is a limiting factor, too. Selection of seating materials for corrosive fluids, regardless of pressure-temperature, is almost endless. Included are many types of alloys, as well as linings or coatings of many kinds. \ Valve Catalog your best guide Safest policy in specifying seating materials is in close adherence V to valve manufacturer's recommendations, usually found in cat alogs, otherwise supplied on request. Vy Flexible Wedge Disc Split Wedge Disc ST0408923 e Z 6 8 0 h 0 iS ST 0 U08924 Globe Valve Seating Designs ... Plug Type Disc Long taper with corresponding seat, giving a wide area of seating contact, makes the plug-type disc superior to all others for severe throttling service, such as blow-off, soot-blower, boiler feed. Because of wide seat bearing, most cuts and nicks by dirt, scale, and other foreign matter in flow are seldom big enough to cause leakage. Plug disc shape, in proper combination of metals lor service, is most effective in resisting erosive effects of close throttling. Construction permits replacement of seat if necessary. Conventional (ordinary) Disc A good seating design for many not-too-severe services, but not for close throttling. Disc has relatively narrow contact with body seat--virtually a line bearing. This narrow metal area, in closely throttled high-velocity flow, is subject to erosion and wire-drawing. Deposit of particles of foreign matter on seat makes tight closure virtually impossible. Yet uniform deposit on seat, such as coking action in oil refineries, is more easily broken down by the narrow bearing. It makes a tight metal-to-metal contact easier than a wide seat. Seat and disc can be conveniently serviced. i l /------------------------------------------------------------------------Needle Point Disc and Seat "\ Needle point valves are designed to give fine control of flow in small-diameter piping. Their name is derived from their sharppointed conical disc and matching seat. They come in globe and angle patterns, in bronze and steel, and find usage on steam, air, water, oil, gas, light liquid, fuel oil, and similar services. Stem threads are finer than usual so that considerable movement of stem is required to increase or decrease opening through seat. Usually, these valves have reduced seat diameter in relation to pipe size. Vy I V J 10 ST0408924 w their service characteristics Composition. Disc A useful design in bronze and iron valves for adaptability to many services and for quick repairs. Discs available in compositions suitable for steam, hot water, cold water, oil, air, gas, gasoline, and many other fluids. Disc change is quickly made with slip-on disc holder. Highly regarded for dependable, tight seating on hard-to-hold fluids such as compressed air. Flat face of relatively "soft" disc seats against a raised crown in body. Small particles of foreign matter are imbedded in disc, preventing seat dam age and leakage. Suited for all moderate pressure services except close regulating and throt tling, which can rapidly cut out the disc. W r Angle Valve Seating It is well to note and remember the angle valve when looking for globe valves. If there's a right angle turn in the line near where you need a valve, an angle pattern gives you important advantages. It's available with the same seating variations as shown here for globe valves: plug-type disc, conventional, and composition disc. Has considerably reduced turbulence, restriction of flow, and pressure drop because flow makes one less change of direction than in globe valve. Angle valve cuts down on piping installation time, labor, and materials, also reduces number of joints or potential leaks by serv ing as a valve and a 90 degree elbow. ST0408925 n ST0408925 ST0408926 J Disc-Stem Connections ... important factor in valve selection In Gate Valves In a gate valve, the sole function of the stem is to raise and lower the disc. In doing its job, the stem should not be subject to corollary stresses and strains of service conditions on the disc. Thus, with gate valves, especially those used for higher pressure installations, a relatively loose disc-stem connection is desired. If the connection were rigid, any side thrust on the disc caused by pressure and flow, would readily be transmitted to the stem, and tend to strain and possibly bend it. A properly fitted loose connection relieves strain on the stem due to any lateral movement of the disc. In Globe Valves The stem in a globe valve not only raises and lowers the disc, but also must help guide it squarely to its seat. Thus, unlike a gate valve, the globe valve disc-stem connection must be relatively close fitting to prevent any extreme lateral motion of the disc that would cause it to cock and seat improperly. But, once the disc and seat are joined, the disc must stop turning while seat ing is completed by the stem. This will avoid metal-to-metal friction between disc and seat that would be destructive to seating surfaces. The solution to this need is a swivel action in globe valve disc-stem connec tions, which permits true and tight seating without damage to seating sur faces. 12 ST0408926 Variations in stem operations Although in many valve applications the type of stem operation makes little or no difference, in other cases it can be important. A simple example of the latter is the need for a self-indicator to show open or closed position, as in the case of rising stem valve, or, conversely, the need for a non-rising stem valve because of lack of head room. This page shows how stem operating designs are adapted to service needs. Rising stem with outside screw On both valves shown here, whether opened or closed, the stem threads al ways remain outside the valve body. They are not subjected to corrosion, erosion, sediment, or any elements in the line fluid that might damage stem threads inside the valve body. Being outside, they can be lubricated easily when necessary. Rising stem with inside screw This is the simplest and most common stem construction for gate, globe, and angle valves in the smaller sizes. Stem turns and rises on threads inside the valve. Position of handwheel indicates position of disc--opened or closed. Non-rising stem with inside screw Generally used on gate valves only, this stem does not rise, but merely turns with handwheel. In turning, the stem threads raise or lower the disc. Since stem only rotates, packing wear is less. Ideal where head room is limited. Sliding stem is often useful The sliding stem valve is useful where quick opening and closing are wanted. A lever takes the place of the handwheel, and stem threads are eliminated. Available in both gate and globe valves. Rising Stem, Outside Screw Types On gate valve at left, stem rises through thehandwheel and yoke sleeve to which it is threaded. The stem does not turn. On globe valve at right, the handwheel is attached to the stem, and both turn wbi le moving up or down. Both valves, by the position of their stem, signal to operators whether they're opened or closed. They need adequate head room. Stuffing box designs featured on CRANE valves Stuffing box must effect a tight seal around the stem to retain pressure inside piping system. Stem must be tight without binding. Packing is subject to wear and must be periodically compressed and eventually replaced. Packing Nut without Gland Used on low-pressure and small-size \alves. With wheel and packing nut re moved, this type is easier to repack than ordinary gland type on valves with small diameter stem. El Packing Nut with Gland Conventional type packing nut with loose gland. Gland has small lip at top edge so that it can be pried out with screwdriver tip if jammed all the way down. E Bolted Gland Deep stuffing box with two-piece ball-type gland and flange with swing-type eye bolts. Construction maintains an even load on the packing and prevents binding on the stem even when the gland bolt nuts are pulled up unevenly. O Injection Type Add new packing with the twist of a wrench, even under full rated line pres sure, and with the disc in any position! No need to backseat the disc. The specially designed ball check valve eliminates possibility of packing extru sion. When the packing reservoir is empty, simply back out the adjustment screw and insert a new pack stick. & Lantern Type Superior construction for larger-siz.e high pressure-temperature valves. Cool ing chamber with lantern spacer and three rings of packing beiow to wipe stem clean before it passes into the sealing rings above. Two-piece ball-type gland and flange with swing-type eye bolts. $10408921 13 ST0408927 ST0408928 Bonnet and Bonnet Joint Characteristics ... of gate, globe, and angle valves Which is best? In choosing valves, the service characteristics of the bonnet joint should not be overlooked. Bonnets and bonnet joints must provide a leakproof closure for the body. There are many modifications, but of the five types shown below, the three most common are the screwed-in bonnet, screwed union ring bonnet, and bolted bonnet. Clamp Type Bonnet Ideal where frequent inspection and cleaning of lines are essential. Both the body and bonnet have lugs. A U-shaped clamp is passed through these lugs and secured with two nuts assuring a snug, accurately aligned bonnet joint. When necessary, disassembly can be accomplished in minutes and the complete bonnet assembly easily removed for inspection. Repeated openings do not affect bonnet joint tightness. This construction is found only on certain moderate pressure gate valves. Screwed-in Bonnet The simplest and least expensive construction, frequently used on bronze gate, globe, and angle valves, and recommended where frequent dismantling is not needed. When properly designed with running threads, and carefully assembled, the screwed-in bonnet makes a durable pressure-tight seal, suited for many ser vices. On modified steel valve designs such as the lip-seal valve with a weld around the periphery of the body-bonnet juncture, the screwed-in bonnet withstands even high -pressures and temperatures. Screwed Union Ring Bonnet A good choice for quick dismantling and reassembly -yet a strong, wellreinforced joint. Convenient where valves need frequent inspection or cleaning also for quick renewal or changeover of disc in composition disc valves. Separate union ring applies direct load on bonnet to hold a pressure-tight joint with body. Turning motion used to tighten ring is spent between shoulders of the ring and bonnet. Hence, the point of seal contact between bonnet and body is less subject to wear from frequent opening of the joint. Contact faces are less likely to be injured in handling. Union ring gives the body added strength and rigidity against internal pressure and distortion. While ideal on smaller-size valves, it is impractical on large sizes. Bolted Bonnet Joint A practical and commonly used joint for larger-size valves or for higher pressure applications. Adaptable to all types of gasketing. Multiple bolting, with small diameter bolts, permits equalized sealing pres sure without the excessive torque needed to make large threaded joints. Only small wrenches are needed. Has practically no limitation for size. Only the highest pressures and tem peratures tax its capacity to permanently hold tight. CRANE Pressure-Seal Bonnet Joint Newest and most effective bonnet joint, developed by Crane, for sealing the highest pressures and temperatures, especially in steam service. Tightness of seal does not depend on nuts, bolts, and threads as in conven tional bonnet joints. Instead, Crane Pressure-Seal bonnet joint utilizes line fluid pressure to seal the joint. The greater the pressure, the tighter the seal. The actual joint is inside the valve, and is sealed with a wedge-shaped seal ring. Internal fluid pressure acting on the entire underside area of the bonnet, is concentrated at the smaller contacting area of the wedge-shaped ring to make a pressure-tight metal-to-metal joint. Available in gate, globe, angle, check and stop-check valves. J J 14 ST0408928 Basic Check Valve Design The Swing Check ... companion for gate valves Swing checks work automatically as shown here. But whether used in a horizontal line or vertical line for upward flow, they will not function properly unless installed with pressure under the disc. Flow through swing checks is in a straight line and without restriction at the seat, similar to a gate valve. This similarity in effect on flow is the reason for 5T0408929 Moving through the line, pressure automatically swings the disc open to full flow as in a gate valve. . . . Should flow reverse, the reversed pressure and the disc's weight close the disc against the seat, and backflow is stopped. The Lift Check ... companion for globe valves Lift checks also operate automatically by line pressure. They should be in stalled with pressure under the disc. Like the globe valve with its indirect line of flow, the lift check is restricting to flow. For this reason it is generally used as a companion to globe valves. Line pressure lifts the disc, and path of flow is in a changing course as through a globe valve. When flow reverses, the disc falls to its seat and cuts off backflow, lines only. 15 ST0408929 Capsule Type (without packing nut) Capsule Type (with packing nut) End Entry Type (screwed ends) * End Entry Type (flanged ends) Cartridge Type Basic Ball Valve Designs The advantages of quarter-turn ball valves are well established. Straightthrough flow, minimum turbulence, low torque, tight closure and compact ness are only a few of many reasons for their wide popularity among users. Reliable operation, easy maintenance and long-life economy justify their extensive application. Industrial, chemical, petrochemical, refinery, pulp and paper, gas transmission, water works and sewage, and power plants are utilizing ball valves where other types of valves have proven inadequate. Crane Co. manufactures a broad line of ball valves for practically any service requirement; listed below are basic designs. Capsule types Both the Hydro Gem and the Gem Valve feature a top-entry capsule design providing easy "in-line" maintenance, if ever required. The Crane "GEM" ball valve can be readily and practically adapted to a variety of installations on gas, water, and oil lines where fluid tempera ture is reasonably constant. The nature of its construction together with the replaceable capsule assembly make this valve ideal for tight spot installations. The Buna N two-piece capsule encasing the ball can be replaced without removing the valve from the line with only a screwdriver or small wrench. This inexpensive bronze valve is available in small sizes with screwed or solder-joint ends. It is designed without a packing nut in sizes %-inch and smaller (top illustration), and with a packing nut in larger sizes (second illustration). HYDRO GEM valves (second illustration) offer many of the same fine features as the Gem valve. However, to better meet the demands of "fluctuating temperature" applications, Hydro Gem valves feature a synthetic elastomer capsule compounded especially for water service. This elastomer .. . ethylene-propylene-terpolymer (commonly known as "EPT") . . . retains its resiliency and stability over a broad temperature range. All sizes have a bonnet gasket and packing box. Hydro Gem valves are an ideal choice for almost any water application within their pressuretemperature range. They are particularly suitable in water services sub ject to temperature fluctuations .. . and are unexcelled for use in hydronic heating/cooling systems. End entry type Crane TORK-SEAL ball valves are the low-cost dependable choice for tough applications in chemical, petroleum, and industrial installations. One-piece body coupled with end entry design virtually eliminates all potential leakage to atmosphere. Internally-loaded TFE (tetrafluoroethylene) seats, one on each side of the ball, are securely retained in the body by one or two threaded ferrules, depending on size. Unique stuffing box design utilizes a packing nut, spring washers, and a gland to maintain a sustained pressure on the packing . . . assures a tight stem seal. Available in a wide range of sizes in stainless steel, carbon steel or bronze . . . and with screwed, 150-pound flanged, or 300-pound flanged ends. Cartridge type Crane "Accesso" ball valves are excellent shutoff valves for steam, water, and oil, as well as for a wide variety of flammable and hazardous liquids and gases. They control the flow of a multitude of products in industrial and process piping in chemical plants, petroleum lines, utility installations, power plants and general industrial plants. They feature cartridge type seating assemblies which simplify fast-in-line maintenance service. Fur nished with screwed ends in stainless steel, carbon steel or bronze in sizes 14 through 2-inch. J ST0408930 Gem, Hydro Gem, Tork-Seal, and Accesso are registered trademarks of Crane Co. ST0408930 Basic Butterfly Valve Designs Butterfly valves are of the "quarter turn" family, and are so designated because a 90 turn of their operator fully opens or closes the valve. The valves utilize elastomer seats and seals and their surge to popularity can be attributed to the tremendous advancements made in elastomer materials. There are also other advantages. They're excellently used in the wide-open or fully closed position ... and yet, in some cases, may be used for non-critical throttling applications. They're generally lighter in weight than conventional valves. The position of the lever indicates whether they are wide open, partially open, or fully closed. Crane "Monarch" butterfly valves incorporate the most desirable en gineering features with the best suited materials to assure efficiency, durability, and reliability. They are widely used in paper mills and cement mills, chemical and food processing plants, water filtration plants, petroleum product lines, air conditioning and water control, and similar applications. The valves are rated up to 180 F and are bubble-tight at pressures up to 200 psi for 2 to 12-inch sizes . . . and to 150 psi for 14 to 24-inch sizes. Their Buna N seat is scientifically dimensioned to give maximum resil iency under the seating land of the disc. This permits optimum disc impingement for greater seat tightness without overstressing the liner, The disc edge is precision ground, finished and hand polished to provide long life and trouble-free operation. Seat materials other than Buna N are available. Crane "Monarch" valves are compact and space-saving, and easily in stalled in new piping or readily used as replacements in existing piping. They are easily adapted to lever, manual gear, buried, cylinder (illus trated), or motor operation. Wafer Type The wafer type valve is designed for quick installation between pipe flanges. No gasket is needed because the molded-in seat is lapped over into a recess in both faces of the body ends. This portion of the seat is a labyrinth type of heavy multiple ribs of buttressed design and serves as a seal between the valve and pipe flanges. Bolt holes are provided in the body of valves 14-inch and larger (not illustrated) to facilitate alignment with pipe flanges. Wafer Lug Type Wafer lug type valves, except for their lugs completely around the body, are the same design as wafer type valves. In some lug type designs, the lugs are simply drilled to match ANSI (American National Standard Institute) 160-Pound Steel (and 125-Iron) drilling templates. Crane drills and taps the lugs so that when the valve is closed, upstream piping can be left intact while downstream piping is dismantled for cleaning, revamping, etc.... or, if the valve is utilized for pipe-end applications, only one pipe flange is necessary. Two-Flange Type The two-flange type valve, except for body and seat design, is the same as the wafer type. The seat is not lapped over the body ends, and a gasket is required as a seal between the pipe flanges and body flanges. Monarch is a registered trademark of Crane Co. Detail of bedgroove and disc impingement. ST040893I The Common Materials of which valves are made selection of valves starts here It pays to know the range of materials from which valves are usually made, and to under stand the pressure, temperature, and structural limitations of each material. It may be highly unsafe to use materials for services beyond their recommended maximum. Valves commonly used in industry fall into the four general material groups shown below. Variants in each of these groups have individual service characteristics. Bronze 3% Nickel Cast Iron Crane Steam Bronze is widely used in valves and fittings for temperatures up to 450 F. It is an alloy of copper, tin, lead, and zinc. Crane Special Bronze is a high-grade copper-base alloy used in piping equipment for higher pressures and for temperatures up to 550 F. Crane 3% Nickel Cast Iron has tensile requirements comparable to ASTM A126, Class B, and is used for corrosive services where ordinary gray iron is not adequate. The metal is used in valves for the pulp, paper, and petroleum industries. All pressurecontaining castings of this iron are identified with the symbol "3NI". Iron Crane Cast Iron is regularly made in three grades--Cast Iron, Ferrosteel, and High Tensile Iron. These metals are recommended for temperatures up to 450 F. Cast Iron is commonly used for small valves having light metal sections. Crane Ferrosteel, stronger than cast iron, is used for valves having medium metal thicknesses. High Tensile Iron has even greater strength, and is used principally for large size castings. Malleable Iron Malleable Iron used in valves is characterized by pres sure tightness, stiffness, and toughness, the latter prop erty being an especially valuable one for piping materials subjected to stresses and shock. Steel Steel is recommended for high pressures and temperatures and for services where working conditions, either internal or external, may be too severe for bronze or iron. Its superior strength and toughness, and its resistance to piping strains, vibration, shock, low temperature, and damage by fire afford reliable protection when safety and utility are desired. Many different types of steel--cast, forged, alloy--are both necessary and available because of the widely diversified services steel valves perform. Stainless steel Crane Stainless Steel Castings are heat treated for maxi mum corrosion resistance, high strength, and good wear ing properties. Seating surfaces, stems, and discs of stainless steel are well suited for severe services where foreign materials in the fluids handled could have adverse effects. Stainless steel has excellent resistance to wear, seizure, galling erosion, and oxidation. /How to read service rating' marks 2 12S Bronze and cast iron valves are marked with the size, the name "CRANE/' ond the bosic working pressure (steam). Some valve markings will in clude the cold rating. Nearly all Crane products are designated by the gen eral or primary pressure class such as `'25-Pound," ``100-Pound," "125-Pound," etc. These should not be construed as a recommendation for use of the product at those pressures. The designations are descriptive of a general product class and do not necessarily imply that all items within a given class ... or that all sizes of a given product . . . are rated for the same primary service pressure. Recommended pressure ratings for Crane products are included on the catalog page or pages pertaining to those products and, practically all products except gas stops are marked with the recommended basic working pressure. id IP'S 121 2'0@ WQ& Ferrosteel, High Tensile, and alloy iron valves include o materiol symbol marking. In this case, the metal is Ferro steel (FS) ond the valve bears both the steam ($) and the non-shock cold water, oil, ond gos (WOG) rating. V If the product is marked with numerals not followed by a letter suffix, the marking denotes the basic steam pressure rating at the maximum temperature indi cated on the page describing the product. If the marking consists of numerals followed by the letters G, L, O, S, or W, either individually or collectively, it denotes the gas, liquid, oil, steam, or water service pressure rating, respectively, at the maximum tem perature indicated on the page describing the product. Valves with leather or composition faced discs are exceptions to the foregoing. These valves use bodies which are regularly marked with a basic steam rating . . . but the valves should be used only for services for which the type of disc facing is recommehded. Test pressure markings, where used, are followed by the word "TEST." i CIMWI ITglL II Typical marking for a carbon cast steel valve. Forged steel valves will include the mark ing "FORGED STEEL" Jb C^j SiYEEIL Alloy cast steel volves include a material symbol marking; in this case "C5" for A$TM A217, Grade C5 steel (Crane No. 5 Cast Steel). 'll CPI AMU is-i ty (I Stainless steel valves have o material symbol marking such as 18-8 SMo, C-20 (Craneloy 20), etc. J j J J ST01.08932 ST0408932 The RIGHT Valve ...industry's Ally for Progress! r Crane non-rising stem (at left) and outside screw and yoke iron body gate valves find wide application in almost any industry. Sizes 8-inch and smaller feature injection type stuffing box (described on page 13). V/ Crane butterfly valves ... A popular "all-industry" choice, wherever there's a flow of liquid, slurries, or gas. Crane valves for power industry, handling steam at temperatures to 1200F. Crane valves for plastics industry, subjected to 30,000 psi, or 15 tons per square inch. 5T0408933 Crane valves lor chemical industry, workingattemperatureslowerthanminu$175F. Crane ball valves serve all industries. Available with a variety of end connections, and in sizes !4" and larger. Crane valves for petroleum industry, safely controlling extremely volatile LP-gases. 19 ST0408933 When it comes to service, Crane puts it on the line In order to provide you with the most efficient service, Crane has a network of authorized valve distributors in every major city and industrial center in the United States. These Crane valve distributors are prepared to handle your most demanding requirements. Their staffs include experienced personnel who are knowledgeable in virtually every facet of the valve business. Supporting these professionals are Crane's qualified sales engineers, staff engineers, quality control technicians, customer service agents--all of whom are dedicated to helping you select the best valves for your applications. Prompt delivery is an important part of Crane service. For this reason, Crane distributors maintain inventories of the most popular valve classes and sizes. In the event they do not have the exact type and size you need, they can call the huge Crane Distribution Center in Carol Stream, Illinois. At Carol Stream, 99,000 sq. ft. are devoted entirely to valve inventory. Over 1,500,000 valves can be stored at one time. By using modern electro-mechanical material handling equipment, 15,000 valves can be shipped in a single day. This high-speed system, combined with Crane s unique protective packaging techniques, assures you of dependable delivery of high-quality products. Crane takes pride in the quality of its products. It is only matched by the quality of service provided by authorized Crane valve distributors. ST0408934 CRANE VALVES PUMPS FITTINGS WATER TREATMENT PLUMBING HEATING CRANE CO. 300 PARK AVENUE, NEW YORK, N.Y. 10022 10 1274M -GN lltho In U.S.A. ST0408934 ST0408935 S T 0 U0 8 9 3 6 GASKETS AND JOINT COMPOUNDS 4 I. GASKETS A. General Class of "Stopping or Minimizing Leakage" 1. Packings - Dynamic Leak Sealing 2. Gaskets - Static Leak Sealing B. Dynamic Leak Sealing 1. Mechanical Face Seals - Rotating Shafts 2. Dynamic Shaft Seals - Lip Seals, Rotating Shafts, Wiper Rings, Labrynth Seals. 3. Split Ring Seals - Reciprocating - Piston Rings 4. Compression Packings - Stuffing Box - Generally Rotating Shafts; Require frequent gland adj. 5. Molded Packings a. Lip Types - Primarily reciprocating service Hydraulic Cylinders b. Squeeze Types - 0-Rings - Reciprocating, Oscillating, Rotating. c. Felt Radial Types C. Diaphragm Seals - "Grey" Area Between Dynamic & Static Reciprocating Motion Only 1. Separating Membrane - No Pressure Differential 2. Static Diaphragm - Separates two fluids - No or little motion 3. Dynamic Diaphragm - Seal between stationary and moving members and transmits a force or pressure. ST0408936 ST0408937 2 D. Static Leak Sealing - Gaskets - Two Classes - Metallic and Non-Metallic 1. Non-Metallic - Low Pressures <1200 psi <850F and/or -65 F. a. Asbestos Products 1) Rubber Asbestos, includes Compressed Asbestos i 2) Worer Asbestos i' ' - ') 3) Millboard and Paper b. Cork Composition c. Rubber < d. Cork & Rubber e. Fluoroethylene Polymers - Trade Name - Teflon f. Paper < * g- Combinations & Misc. h. Elastomeric O-Rings - Static O-Ring Seals classed as Gasket Type Seal. i. Formed in Place Material - Loctite Radiation*-108RAD; ->850F; <-65^; >1200psi; Vacuum ^"10"^Torr 2. Metallic - High Pressure, Severe Conditions a. Corrugated or Embossed, Thin Metal b. Metal Jacketed, Soft Filler c. Spiral Wound d. Plain or Machined Flat Metal e. Round Cross Section, Solid Metal f. Heavy Cross Section, Solid Metal g- Light Cross Section, Pressure Actuated ST0408937 ST0408938 3 h. 0-Ring Types E. The Gasket System - How It Works 1. The Gasket's function is to stop or minimize leakage of fluids. 2. The Gasket is only part of the system that consists of the gasket, the bolts, the flanges. a. To do this, a Gasket must: 1) Create a Seal - Conform to surface irregular ities, minimum sealing stress. 2) Maintain the Seal - Elastic response of gasket, bolts, and flanges. 3) Be Impervious to Fluid Flow - Naturally or by compression. 4) Be compatible with the environment. b. The Bolts 1) Create and maintain min. sealing stress by spring action. Bolt stretches which creates a force like a spring. 2) Bolt Stretch - Strain - Measured in in/in of length. 3) Lower the Bolt - The more stretch required for desired load. 4) Desirable to have more stretch since this gives more follow-up or springiness. Helps offset gasket relaxation, temperature ex pansion, etc. ST0408938 ST0408939 4 5) Stretch Governed by Effective Bolt Length Can Increase EBL By: a) Use of thicker washer under bolt head. b) Boss on flange. c) Thicker flange. d) Machine down top portion of engaged threads. 6) Bolt Stretch also function of Spring Constant of Bolt. Decreasing spring constant of bolt. Force tK = --^-- (Elongation)] increases elongation. a) Decrease # of bolts used. b) Reducing DIA of bolts down to Root DIA. c) Increasing E.B.L. d) Increasing length of threaded section, c. The Flanges 1) Flanges produce contact pressure on gasket. 2) Problems that prevent flange from doing this are: a) Bowing - Related to flange stiffness Stiffer flange - greater is min. available sealing pressure. b) Bolt hole distortion. c) Non Parallelism - Loads part of gasket more than other parts. d) Surface Roughness. ST0408939 5 3. Gasket Joint Design. a. To Seal, gasket must be loaded sufficiently to fill voids between mating surfaces and/or close internal structure. This load called minimum sealing stress, or "Y" Value. b. For given joint available bolt load on effective area of gasket is given by: Y1 = ^ Wm2~ # bolts x load in each (Gross bolt load) b= Effective gasket width G= O.D of gasket minus 2b Available Load - - Must be equal to or greater than minimum sealing stress - Y. c. "M" Values - takes into account fluid pressure. _ M1 _ Wmi-.785 G P 6.28 GPb Wml= Gross bolt load avail. P= Fluid pressure G= O.D of gasket - 2b b= Effective gasket width must be> basic "M" factor. d. If Y or M Value requirements aren't met gasket modification is necessary. 1) Increase gasket thickness. 2) Reduce gasket area (which raises unit load). 3) Increase no. of bolts (which increases avail able bolt load). 4) Change in gasket material. ST0408940 1*16801015 6 II. JOINT COMPOUNDS A. Two Basic Purposes 1. Lubrication, antisieze. 2. Sealing. 3. Same compound could be used for both purposes. B. Lubrication 1. Corrosion protection. 2. Disassembly, assembly. 3. Torque accuracy, 4. Prevent thread galling, 5. Specific application - pressure, temp., fluid compatability, materials, etc, factors to consider. C. Sealing 1. Threaded joints - threads provide mechanical attachment, and also seal in some cases. a. American Standard Taper Pipe Thread (NPT) 1) Spiral leak path at thread crest and root. 2} Crush & wear of threads occur with assembly & disassembly. b. Dryseal Standard Taper Pipe Thread. (NPTF) 1) Provides for leaktight sealing in tapered threads. c. Straight Thread 1) Spiral leak path. 2) Used with lock nut with embedded seal, 0-Ring Swagelok, flare, etc. ST0408941 2*!680*?01S 7 d. Specific application depends on pressure, temperature, fluid compatability, and other factors. 2. Flanged joints a. Flanged joints aren't necessarily static temperature, vibration, pressure shocks, etc. b. Joint compounds in flanged joints. 1) Additional means of sealing imper fections in flange faces. 2) Flexible compound can allow more joint movement and still seal. 3) Ease of disassembly - gasket won't stick to flange faces. 4) Ease of assembly - gasket will stick and maintain position. 5) Use of new formed in place gasket/joint compounds offer some advantages. D. Gross Mismatches - There are some cases where the compound and the chemical are definitely incompatible. 1. Check compatibility charts on compound. 2. Check temp. & pressure rating of compound and joint. (Gaskets, Bolts, Flanges) 3. Check Engr. Reactive Chemicals Manual. 4 Ask around. ST0408942 ST0408943 8 E. In Handout Material is: 1. Reprint of "Gasket" section from Engr. Specs 48-850.Also included is 48-807 - "Bolt Lubricant" and 48-855 - "Joint Compound". 2. Technical information from Garlock, Machine Design, and Loctite Company. ST0408943 SECTION 7 Srff4089ii^ NONMETALLIC GASKETS A casket is any media or device used to create and maintain a barrier against the transfer of fluids across mating sur faces of a mechanical assembly, when the turfacBt do not move relative to each other. Joint and gasket design must be con sidered together. A joint is only as good as its gasket, and the gasket may suc ceed or fall according to whether the Joint makes the best use of the proper ties of the gasket material. Therefore, joint components must be thought of as a unit, or system, for effecting a seal. Otherwise, the end result, more often than not, is a leaky joint. In the first part of this section, nonmetallic gasket materials are discussed, and recommendations are provided for se lection and application. In the second part, nonmetallic O-rings are described. Gasket Materials and Forms Selection of a material for a gasket hinges upon how well the material meets four basic requirements: 1. Impermeability. 2. Ability to flow into joint imper fections when compressed. 3. Maintain seal in spite of age, and ( variations in temperature and pres sure. 4. Resistance to environmental dete rioration. Since a gasket compensates for irregu larities in joined, rigid members of an assembly, all the materials deform, or compact, under compression loads, Fig. 1. The extent a gasket must be comlressed to effect a seal depends on the irish of the contact surfaces and the character of the materia]. In general, the more-compressible materials are used for low-pressure applications. Properties and uses of different materials are shown in the table. Although many materials and combina tions of materials are suitable for gaskets, the more common compositions can be classified in these categories; asbestos products, cork-and-rubber, cork composi tion, rubber, plastics, paper, and com posite and miscellaneous. Rubber-Asbestos Compositions: These include "compressed asbestos" and sev eral other forms of asbestos sheeting or composition which duplicate physical properties and general fields of applica tion of compressed asbestos. This is the most important commercial classification. Compressed asbestos is best used where bolting pressures are rather high; there is sufficient compacting of the structure to make the material imper meable. Compared with more yielding gasket materials, compressed asbestos requires a relatively heavy load to achieve intimate contact with flange faces. It is used in relatively heavy constructions employing rigid flanges with adequate bolting capacity. Compressed asbestos has little elas ticity. After the bolts have pulled up to the point where the gasket is well seated and has conformed to the Irregu larities of the joint, it has scarcely more yielding than the metal components themselves. Woven Asbestos: Asbestos fibers may be spun into yam, and the yam woven into fabric. The yam may be rein forced with metallic wire or strands of cotton. But reinforcement lowers the heat resistance. Millboard and Paper Asbestos mill board and paper is relatively pure as-' bestos fiber bonded with starch or sulphites, and used as soft fillers for Asbestos Products Asbestos fibers retain most of their strength up to about 750 F. Above that temperature they lose water of crys tallization, a process which becomes in stantaneous at about 1,300 F. Then they can be powderized by slight rubbing. Most authorities regard 500 F as a con servative operating limit. Asbestos gaskets, and compositions with asbestos fibers, have good resist ance to crushing loads and to cutting action of narrow and sharp-edged flanges. They also have good dimensional sta bility. Pure asbestos products are very low in strength and high in porosity. For this reason, asbestos is almost always used with other products. It may be processed-strengthened with binders and saturants for greater imperviousness, and it proves a good mixer when added as a filler to rubber and plastic compounds. Principal types of asbestos gasket ma terials are: Fig. 1--Compression for different clamping loadj for common gasket materials. ST0408944 metal-jacketed or other reinforced* con structions. Automotive cylinder head gaskets are one of the most important uses. Cork-and-Rubber Cork and rubber are materials of very lifferent properties. Application of a load to cork causes a reduction in vol ume with negligible flow because of its structure, and it has excellent recupera tion characteristics. Rubber is incom pressible, since no volume decrease will occur. Hence, side flow takes place as pressure is applied. Cork-and-rubber gasket materials are vulcanized compounds of natural or syn thetic rubber and conventional rubber compounding ingredients mixed with cork. Of the synthetic rubbers, the G R S, nitrile, neoprene, polypropylene, and silicone types are most generally used. Cork can be combined most read ily with those rubbers, which cure at moderate vulcanizing temperatures. Characteristics: Compressibility and Tow characteristics of cork-and-rubber can be controlled and combinations pro duced which are nearly as compressible as cork, or almost as incompressible as straight rubber. This is determined large ly by the ratio of cork to rubber, but can be affected by size of cork granules. Chemical properties of cork-and-rubber are largely the result of the type of rubber with which it is compounded. Cork should not be used under strongly alkaline or acidic conditions. Cork-andrubber materials are likely to swell when in contact with aqueous solutions. But, this is due to mechanical release of the forces of compression in the cork gran ules which occur during manufacture, and is not an indication of deterioration. Cork-and-rubber is best used at tem peratures below 160 F. In some cases, it may perform satisfactorily in the Properties and Uses of Gasket Materials Classification Special Characteristics General Uses BobberAsbestos Tough and durable. Dimension ally stable. Relatively Incom pressible. Good steam and hot water resistance. Oil and sol vent resistance determined by characteristics of rubber binder. Heavy-duty bolted and threaded Joints, as In water and steam pipe fittings, manifold connec tions. Temperatures to 500 F. Cork-and-Rubber Provides fluid barrier and resili ence with compressibility. Prop erties of flow versus compres sion subject to controlled varia tion. Lower tensile and elonga tion properties than rubber. Chemical properties about same as base polymers. Higher In cost than cork composition or fiber types, but lower than straight rubbers. Does not extrude from Joint. Die cuts well. High coeffi cient of friction. General-purpose gasketing, ex cept steam lines, combustion chambers, etc. Eoables design of metal-to-metal Joints with gasket positioned In channel or counterbore, with no allowance for flow. High friction keeps gasket positioned even where Closing pressure Is not perpen dicular to flange faces. Cork Composition General-purpose material. Vari able as to binder, texture, and hardness {density). Compressi ble. High friction whether dry. wet, or oily. Low cost. Excellent oil and solvent resistance. Poor resistance to alkalies and corro sive acids. Mating rough or Irregular parts, as glass, light stampings, unfin ished eastings. Oil sealing at low cost In normal range of tem peratures and pressures. Rubber, Plastics Highly adjustable according to compounding, hardness, modu lus, fabric reinforcement, etc. Generally impervious. Not com pressible. Installations Involving stretch ing over projections, or where flow of gasket Into threads or recesses Is desired. For lowest compression set and maximum resistance to fluids such as al kalies, hot water, and certain acids. Ability to be molded per mits use for special design and assembly conditions. Paper: Untreated Treated Combination Constructions Low In cost; noncorrosive. Oeneral-purpose material having better tensile strength than cork Composition, but less compressi bility. Oood oil, gasoline, and water resistance, but alternate wet and dry cycles may cause shrinkage and hardening of some type*. Spacers, dust barriers, splash seals, where breathing and wickIng not objectionable. Machined or reasonably uniform flange* where adequate bolt pressures can be applied. Rela tive firmness and high tensile strength permit use of thin gas kets to give good alignment of covert and connected parts. Innumerable modifications avail able, depending on materials used and methods of combining. Usually employed for extreme conditions and special purposes. range of 250 F. Materials compounded with some of the new synthetic rubbers based on polyacrylic esters and sili cone may be used at temperatures in excess of 300 F. Cork Composition Cork is noncapillary, lightweight, prac tically inert, does not deteriorate with age, and has a high coefficient of fric tion. In its natural unprocessed state, cork is highly variable in texture, qual ity, and size; thus, it is best used in combination with other materials. Cork compositions are made by com bining granulated cork with a suitable binder under heat and "pressure. Because of its properties, cork composition is suited for many mass production appli cations involving the mating of rather irregular surfaces where temperatures are moderate and internal pressures are low. Cork gaskets are valuable in applica tions Involving widely spaced bolts and light construction, in which bowing is inevitable, and in joining glass or ce ramic parts to metal. Tolerances are very wide in such assemblies, and cork can provide a shock-absorbent cushion for the glass and ceramic components. When engaged in sealing fluids, cork composition is sufficiently impervious to hold moderate pressures. However, when dry, it may be slightly permeable to gases due to the minute voids between granules which have not been entirely closed by the forming or flange pres sures. Cork is a very resilient material and keeps pushing back against applied pres sure over a long period of time. This action is aided by swelling action of most fluids on the sealing edge of the gasket. Sustained high temperatures above 160 F produce a permanent set in cork. Cork composition is unaffected by oils and aromatic solvents. It does not take sustained contact with water too well, and is disintegrated by alkaline solu tions. Plasticizers are likely to be ex tractable in water, and cycles of alter nate wetting and drying produce pro nounced shrinkage and hardening. Because or contained moisture and in herent acidity, cork compositions may encourage corrosion in aluminum and magnesium alloys, and to some extent In stainless steel. Fungus resistance of cork composition is very poor if the ma terial is made with protein binder, but fairly good if the binder is a phenolic resin. Protection is possible by suitable external treatments of finished parts. Fungicides incorporated into the binders do not penetrate the cork granules and. therefore, do not protect cut surfaces. Rubber The term "rubber" covers several basic elastomers, each of which Is capable of being compounded to give materials of great variety. Fortunately most of these variations are concerned with chemical, solvent, and temperature response. The factors that the designer must know about for drawings and calculations are Seals Reference Issue ST0UO89U5 10S ST0408945 ST0 4 089t6 DESIGN DATA--SECTION 7 common to all forms of rubber and rub ber-like plastics. Rubber Characteristics: Rubjer is in compressible. Its ease of deformation de pends upon hardness and cross section, ul a true rubber compound cannot be .educed in volume. Therefore, room for ~ flow or deformation must be provided. Or, conversely, it may be necessary to completely or partially confine the rub ber when pressure is applied. Rubber is extensible. This property can also be a two-edged proposition, of fering design freedom on one hand and possibly requiring design and assembly controls on the other. Rubber's extensi ble properties are very valuable when It is necessary to assemble a gasket over a projection or shoulder, perhaps with the idea of having it snap tight within a groove. Except for some plastics, rub bers are the only materials that will stand this kind of treatment. On the other hand, the very elasticity of rubber encourages abuse in the form of over stretching, and a gasket may not always return to its original size. Rubber is highly impermeable. Neo- prene and butyl rubber are outstanding in this respect. Rubbers most commonly used have a hardness below 80 Shore A. These require very little flange pressure to accomplish intimate sealing contact. For compounds over 80 hardness, con tact pressure approaches that required for rubber-asbestos composition sheets. Rubber has sufficient elasticity to fol low the movements of flange surfaces. The best compounds for gasket use are those which have been formulated for low compression set. If the gasket is not confined, it may tend to "`walk" out of the joint with successive tightenings of the bolts; or it may fail through rup ture if overstressed. Rubber compounds other than silicones are best used at ambient temperatures not over 160 F. Low-temperature flexi bility is highly variable according to the elastomer being employed, but com pounding, and especially choice of plas ticizer, has a profound effect upon this basic characteristic. Since it does not absorb and hold moisture, a rubber com pound is not likely to cause corrosion of flanges but, depending upon the met als employed, some staining or other reaction may occur due to the com pounding ingredients. Fluoroethyfene Polymers Sold under the trade names Teflon, Kel-F, and Fluorothene, fluoroethylene polymers are distinguished by a number of unusual properties. These include: chemical inertness, toughness over a wide temperature range, resistance to high temperature, extremely low dielec tric loss over a wide range of frequen cies. and resistance to almost all solvents. Solid PTFE Gaskets: These gaskets are produced by diecutting from a molded sheet, slicing from the end of a molded cylinder, or molding directly from pow der. They are installed in flanges of standard design. Raised-face flanges are normally used for low pressure, that is. 150 to 30D psi. For higher pressures, some confining arrangement such as tongue and groove, or male and female. Is used. Solid gaskets of PTFE plastic have given satisfactory service in tongueand-groove flanges at pressures as high as 30,000 psl. Braided Tape: PTFE gasket tape is a tubular braid available in widths from % to 3 in. The braid is loose and pliable, and conforms with surface ir regularities when compressed between flanges. Braid Is stronger than molded PTFE, and therefore has significantly reduced cold flow. Gaskets are made by cutting one end of the material into a taper, and inserting the taper into the opposite end of the braid. Tape can be used in temperatures up to 400 F and pressures to 200 psi. Envelope Gaskets: These are used for glass, porcelain, and glass-lined equip ment where misalignment of flanges and low* bolting pressures result in failure to seat a solid plastic gasket. Envelope gaskets are also used for those diam eters larger than 24 in., or beyond the size In which solid gaskets are available. The usual construction is the "French'* type, consisting of a soft filler covered by a jacket or envelope of PTFE, Fig. 2. Depending on the service, the filler ma teria! may be fabric-reinforced rubber, asbestos-rubber, plain asbestos paper, or metal. Spiral-Wound Gaskets: Spiral-wound metal gaskets with a filler of PTFE are made in a range of shapes and dimen sions, Fig. 3. The chemical resistance of PTFE combined with the strength of the metal provides a gasket especially suited for high-pressure chemical serv ice. Stainless steel, Monel, and other metals are used, depending on the chemi cals U> which the gasket is to be ex posed. Spiral-wound gaskets have a mechanical "kick back" action built in, due to the shaping of the metal. They require heavy bolting pressure to ac complish initial seating and are expen sive compared with ordinary flat gaskets. Impregnated-Fiber Gaskets: Many at tributes of plastic are obtained at rela tively low cost by Impregnating suitable fiber sheet materials with PTFE suspen' soid. The fiber most generally used is asbestos. The plastic coating protects the asbestos from chemical attack. The combination of blue asbestos and PTFE plastic gives a highly acid-resistant gasket at moderate cost. Paper Gasket papers are made from organic fibers, especially vegetable fibers, or as bestos (mineral) fiber materials which have been described. Untreated papers for gaskets run the gamut of paper production, including such diverse types as plain brown wrapping paper, fish paper, drawing pa per, chipboard, tagboard, and rag felt. Untreated papers are generally used where service conditions are no more severe than the setting up of a barrier against the passage of dust particles or splash. They are also used where the Fig. 2--Combination gaskets with PTFE plastic or meal jackets. Fig. 3--Spiral-wound combination gas ket with PTFE cushion. requirement is simply for a spacer, as in the mounting of a radio speaker. Clue-glycerine saturated papers, while being replaced In many applications by the newer latex solution-saturated and beater-saturated materials, still are the most widely used general-purpose, soft, gasket materials'- Where extreme com pressibility is not required, these papers will do many of the jobs associated with cork composition. Where extreme sta bility, heat resistance, and toughness are not required, they can do many of the jobs associated with compressed asbes tos. Saturated papers are best used with oils and gasolines to hold moderate pres sures at temperatures not exceeding 160 F. Their use is particularly to be avoided in any application involving contact with alkalies, strong acids, steam, and alter nate wetting and drying. Latex-saturated papers, particularly the beater-saturated types, are comparable with the glue-glycerine types in general oil and gasoline services. In addition, they have certain advantages over glueglycerine sheets: 1. Nonextractable bind ers permit use in water and alternate wet and dry services. 2. The latex type is less likely to encourage corrosion of flanges. 3. They are generally more re sistant to fungus attack. Vulcanized fiber Is a treated paper oc casionally used for gaskets. Because of its hardness, it is generally limited to those applications in which the gasket Machine Design--September 13, 1373 ST0408946 i?1680,l0 iS Fig. 4 -- Corrugated - metal combination gaskets with asbestos filler. must be highly incompressible or must serve as a shim. Vulcanized-fiber gas kets are frequently coated with a thin film of synthetic rubber to help effect complete contact between gasket and flanges. Characteristics: Untreated papers are highly permeable, and are likely to re main so even when compressed and saturated with the contained fluids. They are not generally used as a fluid barrier, but rather to prevent entrance of dust or to hold against splash of internal or external liquids. Hard or soft papers are used according to the nature of the joined surfaces. Treated papers are moderately impermeable, a property which increases as the gasket is compressed. Solution-saturated ma terials are more impermeable In the un- onfined state than are beater-saturated aterials. The latter require compres sion to close the voids which are in herent in any fibrous structure. A moderate amount of pressure, 500 to 1,000 psl, is required to initially seat flange to gasket. Treated papers will hold against surprisingly high pressures. A thin gasket with long stretchy bolts will ensure followup pressure after the gasket has taken its permanent set. For treated papers, the best fields of application are for the sealing of oil, gasoline, and in some cases cold water. Water service should be avoided with those materials which contain glycerine because of the extraction that will oc cur, followed by shrinkage and harden ing of the gasket. Rubber-latex beatersaturated types do much better in this class of service. Fungus resistance is inherently poor in plain or protein-sat urated materials, lair tc good in latex or resin-treated stocks. Fungicides may be added to saturants by the sheet manu facturer, or employed as external treat ments by the iabricator or user. Combination and Miscellaneous Laminated Materials: The purpose of laminating is usually to combine the properties of a strong but relatively in compressible material, with those of a highly compressible but perhaps weak material. For example, cork composition, and vegetable fiber have approximately the same chemical properties and response to atmospheric conditions. Hence, they are easily combined by lamination and, depending upon the ultimate use, either may serve as the center filler. Low-cost automotive cylinder head gas kets are sometimes made by attaching a sheet of asbestos millboard to each side of a steel sheet. The steel is per forated in such a way that small prongs or stakes hold the asbestos in place. Jacketed Types: Jacketed gaskets, Fig. 2, usually consist of a center filler with a metallic or nonmetallic outer covering or envelope. The jacket protects the filler against service conditions to which it is vulnerable. For example, PTFE-jacketed asbestos, rubber, and other filler materials are used for the gasketing of glass-lined vessels and piping used for chemical processing. Metal-clad or metal-jacketed gaskets are used for heat or corrosion resistance. Corrugated Metal with Soft Fillers: Such gaskets are primarily for pipe con nections, are circular in shape, and are subject to moderately heavy bolting pres sures. They are particularly useful for warped flanges. A closely related con struction is the serrated metal ring hav ing serrations packed with asbestos filler. Fig. 4. Spiral-Wound Gaskets: This construc tion consists of plies of preformed metal and asbestos, or other filter strip, Fig. 3. A center corrugation in the metal strip gives constant tension and resilience when the gasket is under compression. This style is self-adjusting and noncorrosive. Treatments and Coati.igs Synthet'c Rubber: Neoprene, applied as a dip coat to cork-composition oil pan strips for automobile engines, resists oil penetration and loss t! moisture, and prevents installation breakage. Poly sulfide-coated fiber sheet materials help level the surfaces and promote seating contact of these relatively unyielding materials to flange faces. Graphite: Applied as a dry flake or mixed with oil or in a water emulsion, graphite functions as a surface leveler and adhesion inhibitor. Adhesives: Usually of synthetic rubber, resin, or combination, adhesives may be used wet or partly dry; or may be en tirely dry with the idea of being re activated by solvent or heat. They are used where an immediate permanent bond is desired, helping to keep the gasket and flange together in spite of wide temperature fluctuations and joint movement. Fungicides: Materials such as betanaphthol, pentachlorophenol, salicylanilide, and various copper and mercury compounds are. used to resist mold growth, either as an integral part of the compositions or as surface treatment. If fungicidal treatment is to protect gaskets only during shipment and stor age, formaldehyde powder dusted in car tons may be adequate. Reflective Coatings: Aluminum paint or lacquer applied as a dip serves as re flective insulation, offering some protec tion to gaskets located near a source of heat. Oil or Hot Paraffin: Such materials may be applied by dipping to vegetable fiber and cork composition gaskets to prevent drying out under adverse conditions of storage. * Talc or Mica Dust: Applied dry or in an adhesive vehicle, these materials are used to cut surface friction of gaskets and may be particularly useful in ap plications requiring rotation of parts to close the joint. Credit Text and data for thla chapter furnlabed by Earl M. 8moly, Research Physicist, Arm strong Cork Co., Lancaster. Pa. Elastomeric O-Rings Static O-ring seals are classified as gasket-type seals, but are treated in this separate chapter because they are in a class by themselves In' terms of design and usage. Static O-rings are generally easier to design into a unit than dynamic ones. Wider tolerances and rougher surface finishes are allowed n metal mating members. The amount jf squeeze applied to the O-ring cross section can also be Increased. This type of nonmoving seal Is used in flanges, flange fittings, flange unions and cylin der end caps, valve covers, and plugs. When used as gaskets for flanges and flange fittings, pressures as high as 25,000 psl can be sealed, even with line vibration. Excessive bolt strain, often as sociated with common compression gas kets, is not encountered with static O-rings because the nuts need only be tightened enough to obtain metai-tometal surface contact. The flat flanges will not overstress or crack cast Iron fittings, which normally require special low-tension bolting. Nuts need not be tightened uniformly as with common gaskets, and pipe dopes are not required. O-rings do not shred or become nibbled or braided. Hence, contamination of fil ters and clogging of pumps are pre vented. No periodic tightening of nuts is necessary to maintain a tight joint. Once an O-ring Is Installed, operating pressure keeps it seated against the metal clearance areas. Credit Text end data for thle chapter furnished by Howard O. Olllelle. Vice President and Tech nical Director, Preclelon Rubber Product# Corp.. Lebanon. Tenn. " Seals Reference Issue 107 ST0408947 SECTION 8 816801015 METALLIC GASKETS Gaskets are made of relatively soft material compared to flange mating sur faces, and effect a seal by deforming and filling surface irregularities. For low pressures, gaskets made of soft materials such as cork, rubber, and asbestos are used. For high pressures, and under se vere conditions, metallic or combination gaskets are used. The first part of this section covers the more commonly used metallic gas ket materials, gasket types, and flanges. Hollow metallic O-rings and joints are discussed in the second half. General Types Choice of a casket material for any application depends on operating condi tions, mechanical features of the flanged assembly, and gasket characteristics. In general, operating conditions govern choice of gasket materials, whereas di mensional and mechanical features of the flange control selection of the type of gasket. As a rough guide to determine whether metallic or nonmetallic gaskets should be used, multiply the operating pres sure in psi by the operating tempera ture in degrees F. If the result exceeds 250,000, only metallic gaskets should be used. Also, nonmetallic gaskets generally should not be considered for tempera tures above 850 F or below -- 65 Fr or for pressures in excess of 1,200 psi, without consulting a nonmetallic gasket supplier. Other operating conditions call ing for metallic gaskets include vacuum below 10*4 torr and radiation above 10 rad. Selection Factors Pressure: Pressure of the confined fluid has little or no direct effect upon the selection of most types of metal gaskets. Fluid pressure does determine the mechanical features of the assembly (such as the type of flange facing) and therefore indirectly affects the choice. One exception is corrugated gaskets, which are generally limited to pressures less than 1,000 psi. The other is for extremely high-pressure duty, 10,000 to 50.000 psi. Temperature: Operating temperature has an important bearing on selection of the gasket type and material. The limitation of semimetallic gaskets is con trolled by the nonmetallic filler. For example, an asbestos filler normally re stricts the long-term usage of the gas ket to 850 to 900 F, although the me tallic portion might have a much higher limit. The upper temperature limits for gasket metals are based on several ef fects, including oxidation point and creep. Table 1 lists a few typical metals used for metallic gaskets, together with their usual upper temperature limits for long-duration exposure. Gasket type and size, and severity of the corrosive con ditions, might increase or decrease these limits. Mechanical Limitations: Each type of gasket has dimensional and shape limi tations. Gaskets in all these groups can be made in circular shapes, but not in unlimited diameters or widths. Only a few of the basic groups are made in noncircular shapes. Bolting, or other means of joint clamp ing, must provide sufficient force to seat the gasket and to prevent flange separation due to the confined fluid pres sure. Joint rigidity must be considered be cause, with a few exceptions, metallic gaskets take a permanent set when compressed in an assembly and, unilke nonmetallic gaskets, have little or no recovery to compensate for contact face separation. Therefore, joints in which metal gaskets are to be used must have sufficient rigidity to assure a minimum of bending both during the initial bolt ing up and when the assembly is op erating. Flanges using full-face gaskets must be thick enough to prevent bowing be tween adjacent bolts. Also, flanges us ing gaskets confined within the bolts must be stiff enough to resist dishing across the contact faces. Dishing results in separation of the contact faces at the inner edge, which is the primary seal against leakage. Surface finish is important in that each type of metallic gasket performs best when the flange contact faces have a specific surface finish. Depending upon gasket type, this optimum surface fin ish requirement may be very smooth or deeply tooled. When a minimum gasket seating stress is given for a particular type of gasket, it applies only when the flanges have the optimum surface finish. Any deviation from this optimum finish increases the seating stress re quired. Corrosion: There are several different kinds of corrosion, and metallic gaskets are susceptible to most of them. Uniform corrosion, called rust in iron or steel, is the slow oxidation of the parent metal. Galvanic corrosion occurs when two dissimilar metals share an electrolyte. Any liquid which will conduct an elec trical current can be an electrolyte; even certain gas concentrations in air can act as electrolytes. The current set up by the dissimilar metals transfers an ion from the cathode to the anode, where it is deposited. The anode material is de stroyed, while the cathode remains rela tively untouched. When choosing a gasket material for corrosive conditions, the choice must be made whether to make the gasket anodic with respect to the flanges, and let it be attacked; or the flanges can be anodic with respect to the gasket, and then they will be attacked. This decision must be based on the type of application and the type of gasket. Galvanic effects can be minimized by Table 1--Corrugoted Gaskets AAAA} Plain metal gasket with corrugation* or embossed Interruptions. Corrugations are concentric with ID. For smooth-faced, complex or nonctrcular, low-pressure (500 psi) applications such as valve bonnets, aircraft gas turbine fuel and combustion lines.- Available In metal thicknesses 0.010 to 0.031 In., with corrugation pitches 0 045 to 0.250 In. Overall gasket thick ness Is 40-50% of corrugation pitch. Same as plain corrugated, only a coating of seating compound Is applied. Com pound extends pressure limit to l.ooo psi. Flange surface finishes can be rougher. Corrugated metal gasket with asbestos cord cemented In corrugations. Generally for low pressure (600 psi) on relatively large uneven surfaces such as machined flanges, steam chests, low-pressure hlghtemperature exhaust-gas ducts. Available with 5/32, 3/16. and H-ln. corrugation pitch only. Thickness Is 65-75% of pitch. Table 2--Temperature Limits of Metallic Gasket Metals Temperature limits are bajed on hot air at constant temperatures. The presence of contaminating fluids and cyclic con ditions may drastically affect the max imum operating conditions. Material Max Temperature C F) Lead ............................................. 212 Common brasses ................. 500 Copper ......................................... 500 Aluminum ............................... 800 Stainless steel type 304 ... 800 Stainless steel type 316 .. 1,400/1.500 Soft Iron, low earbon steel. 1.000 Titanium .................................... 2,000 Stainless steel type S02 ... 1,150 Stainless steel type 410 ... 1.200 Sliver ........................................... 1,200 Nickel ........................................... 1.400 Monel ....................................... 1.500 Stalnleaa steel type 309 8CB 1.600 Stainless stssl type 321 ... 1.500 Stainless steel type 347 ... 1.400/1.500 Inconel ................................... 2.000 Kastelloy .................................... 2.000 Seals Reference Issue 119 ST0408948 UL choosing metals which are relatively close together In the galvanic series. Chemical resistance Is needed because chemical solutions may attack certain metals. Severity of the attack depends not only on the chemical and metal in- olved. but also operating temperatures nd pressures, and surface finishes and coatings. Seating Stress Gasket sealing is accomplished by flow of gasket material into the tool marks or Imperfections on the flange facings. The amount of force per unit of gasket area required to completely flow the gasket is known as the yield or seating stress. This stress varies with gasket type, material, and flange surface finish. Minimum seating stresses are inde pendent of confined fluid pressure. Once this required stress has been applied to the gasket, leakage is not likely to oc cur unless separation of the flange/gas ket contact faces takes place due to in sufficient rigidity. Many joints have operated successfully with prestresses less than the recom mended minimum. Effective sealing de pends on many interrelated factors: pressure, temperature, type of fluid con tained, flange surface finish, use of gas ket compounds, amount of leakage tol erated, formation of corrosion or evapo ration products after a short period of initial leakage, etc. Gasket Types Metallic gaskets fall into several basic groups: Corrugated or embossed, thin metal Metal-jacketed, soft filler Spiral-wound Plain or machined flat metal Round cross section, solid metal Heavy cross section, solid metal * Light cross section, pressure-actuated Corrugated: This type consists of thin metal, corrugated or with embossed con centric rings. They are used plain; coated at the time of installation with gasket compound; or with asbestos cord cemented in the corrugations, Table 1. The gaskets require the least costly tool ing for nonstandard sizes or irregular shapes. By proper material selection, they can be used at any temperature, Table 2. Metal-Jacketed, Soft Filler: A soft com pressible filler is partially or wholly en cased in a metal jacket. Table 3. These gaskets are more compressible than cor rugated types. They offer better com pensation . for flange irregularities when higher pressures are to be sealed. The primary seal against leakage is the Inner metal lap, where the gasket is thickest when compressed. This area cold flows, effecting the seal. The en tire inner lap must be under compres sion. The outer lap, if any, provides a secondary seal between flange faces when compressed. Intermediate corrugations may contribute to the labyrinth effect. These gaskets are used for noncircu lar as well as circular applications, and require 20 to 30% compression. They are used for applications at temperatures up to those which limit the filler and metal endurance. Because of limited resilience, these gaskets should he used only In assem blies in which the elasticity of the bolts or other factors can compensate for joint relaxation. They should not be Used in joints requiring close maintenance of the compressed thickness. Materials for jacketed gaikets are also made in a wide variety of metals and filler materials. Standard filler is asbestos millboard/ which is normally limited to 850 to 900 F; in noncritical service it can be used to 1,200 F. Compressed asbestos sheet packing is used where higher strength is necessary. TFE fluorocarbon is used where extremely corrosive conditions exist, at temperatures up to 500 F. Me tallic fillers can be used when service temperatures exceed 900 F in the cor rugated-jacketed and the modified double jacket types. Spiral-Wound Gaskets: This type con sists of V-shaped, preformed plies of metal, wound up In a spiral with a soft separation, such as asbestos paper. Table 4. The V-shape gives unique, spring-like characteristics. These gaskets have the best resilience of aiJ metal and asbestos-type gaskets. Density of construction can be controlled to provide an optimum seal under vari ous bolting conditions. They have good tolerance for flange surface finish ir regularities, and are furnished in a wide Table 4--Spiral-Wound Gaskets } General - purpose, spiral - wound gasket. Consists of preformed, V-shaped strip of metal whieh Is wound toto a spiral. Metal layers are separated by a filler, usually asbestos. Has good resilience and seal* ability. This type used where no centering or compression limiting device la required. Also used In metal-to-metal Joints. ST0408949 Table 3--Metal-Jackefed, Soft-Filler Gaskets One-Piece French Type Used for narrow circular applications re quiring positive, unbroken, metal gasket face across full width. Requires flange surface finish of 72-jJn. AA or better In slses less than U-ln. wide. Over ^-In wide requires concentric serrated flange face. Minimum gasket width Is gasket thickness times 1.5. -- '--m Vt.u Two-Piece French Type Used for wide or irregular shapes not requiring protection of filler material or additional flange support at outer edge. Tooling less costly than for one-piece type. Interchangeable with one-p/ece type. Single Jocket Used for relatively narrow applications similar to French type, but widthdiameter limitations do not apply. Gen erally less costly than French type. Noncircular as well aa circular shapes can be furnished. If over K-ln. wide, use doublejacketed type. Requires flange surface finish 72-*ln. AA or better. Double Jocket Used when complete protection of the filler material is required. Also pro vides additional support of flange at outer edge by addition of lapped overjacket. Available In Irregular noncircular shapes, but tooling more costly than other types. For widths less than 5/32 In., use French or single-jacket type. Requires flange surface finish 72-pln. AA or better. g5>" Modified Double Jacket Used when completely enclosed gasket Is required In widths less than those avail able In plain double Jacket. Generally not available smaller than 1-ln. ID. Also available with filler made from meshed metal wire which Imparts more resilience than nonmetalllc filler. Corrugated Jacketed Jacket is corrugated to increase its resili ence. Used for circular and moderately noncircular shapes In wldtha H in- and wider. Beal&billty better than other types because of corrugations. Bealablllty can be further Improved by use of gasket com pound With corrugated metal filler in stead of asbestos, temperature limited, only by metal selected. 120 Bpl rat-wound gasket provided with a solid metal centering and compression limiting ring around tbs outer edge. Used where gasket must be located remote from the bolts or other centering means and when It Is Important to tlmit com* presalon because of possible ever-bolting, control of stack-height, etc. For closures with circular or moderately noncircular bores and noncircular outer perimeter, the solid metal ring can be mads to the required configuration and bolt holes drilled through it if necessary. Spiral-wound gasket with Inner and outer compression limiting rings of solid metaJ for the most extreme operating condi tions. Rings fill space between flange faces which might otherwise allow ex cessive turbulence or erosion of facings. 8p!ral-wound gasket with lightweight metal devices to center the gasket with out restricting compression. Used In nonciillcal or lightly bolted assemblies where there Is no possibility of over bolting or over compression. Many different centerlog device configurations are available. Machine Design--September 13, 1973 t* ST0408949 variety of metals in circular and limited noncircular shapes. Sealing action results from lie flow of the metal ana soft fil er plies when the gasket is compressed the recom mended amount. Inner and outer metalto-meta! plies must be under compres- ion. Spiral-wound gaskets are used for any circular or moderately noncircular ap plication where an approximate com pressed thickness of either 3/32 or Vs in. can be tolerated. They are particu larly suited for assemblies subject to extremes in joint relaxation, temperature or pressure cycling, shock, or vibration. Excellent performance In joints restrict ing compression is provided, since their resiliency will compensate for modest flange separation. Compression to a predetermined thick ness makes a spiral-wound gasket give its best performance. Its compressibility can be controlled to some extent for a specific bolt loading by varying the den sity; i.e.; the number of metal-asbestos plies or wraps per unit of gasket width. Filler thickness may be from 0.015 to 0.045 in. Two gasket thicknesses, 0.125 and 0.175 in., are standard and suitable for most applications. For 0.125-in. thick gaskets, compression to a thickness of 0.095 0.005 in. is recommended. For the 0.175-in. thick gasket, a com pression to 0.130 0.005 in. is prefer able. Material can be almost any metal. Performance depends upon the spring like action of the V-shaped metal strip. Therefore, the metal used should be one hat best maintains its resilience at the operating temperature. For noncorrosive services, at least 80% of applications could use type 304 stainless for the entire temperature range of --320 to 4-800 F. However, above 800 F in metal-to-metal joints and certain other applications requiring maximum springi ness, type 316, Inconel, or heat-treated Inconel X must be used. Tne asbestos fillers are generally con sidered not suitable for applications where the actual gasket temperature ex ceeds 950 F. However, there are many satisfactory installations where line tem peratures have been as high as 1,300 F for sustained periods of operation. For gasket temperatures above 950 F, ce ramic fiber and graphite fiber fillers are available which, together with a suitable metal, expand the temperature limits to the temperature limit of (he metal used for graphite-filled gaskets, and to about 1,800 F for ceramic-filled gaskets. Asbestos fillers may be used for temperatures below zero, but solid TFE fillers are generally more desirable for such applications. Solid TFE fillers are used in the range --320 to 4-500 F. Width of a spiral-wound gasket should be a function of the diameter and thick ness. In general, the larger the diame er, the narrower the gasket. The spiralround gasket requires more careful di mensioning in relation to flange facing to assure that the inner and outer lay ers of metal plies are under compres sion between the flange facings. Shapes of spiral-wound gaskets can Seals Reference Issue METALUC GASKETS Table 5--Solid Mela!, Heavy Cross-Section Gaskets Delta Casket Is mainly for pressure Teasels or valve bonnets. Groove and gasket dimen sional control are too precise and costly to allow Us use as a piping gasket. It Is useful at pressures from 5,000 ps! and up. When pressure Is applied, the gasket flexes about the two contact points. The Inner periphery becomes curved, and sides of the triangle wedge Into the groove. Increasing sealing effect. Pressure-activated gasket for pressure vessel heads and valve bonnets. Used for pressures 1,500 pel and up. Also for piping Joints subject to extreme temperature shock conditions. A Brldgeman gasket may be one of several designs, the name referring to the type of closure. Increas ing pressure magnifies force holding the gasket In place. Therefore, force securing the seal is greater than Interna] pressure In the vessel. Requires fine tolerances and careful handling. --1 Oval or Octagonal Used In high-pressure piping systems and pressure vessels. Rang* 1,000 to 10,000 psL Excellent mechanical joint. Very high gasket pressures obtained with moderate bolt loads. Used only In ring-gasket joints. Standard gaskets are not pressureactuated. The BX modification of the oc tagonal cross section is for oilfield drilling and production equipment at pressures to 15.000 pal, and Is pressure-actuated. m <* x_ r I Lens Ring A line-contact seal for high-pressure pip ing systems, with some application in pressure-vessel beads. There are many modifications of the basic lens ring. The most popular has spherical faces as shown above, and Is used between flanges with straight, tapered (20*) faces. Stiffening rings have been added to the basic lens ring, but seem to be of little value. Hollowed-out lens rings, lens rings with a groove cut on the Inner periphery, have been used so that In ternal pressure will "balloon out" the ring and Increase Its effectiveness. ifollowed-out lens rings work satisfactorily, but tolerances and hardness are very critical. Generally, the ring should be softer than the flanges. be . moderately noncircular, depending upon size and desired configuration. As a very rough guide for shapes approxi mating an oval, the major axis should not exceed twice the minor axis. Straight-sided rectangles (radiused cor ners) with an inside measurement in excess of about 8 in. may not be practi cal to fabricate. Flange surface finish is preferably 112-180-/iin. AA, although spiral-wound gaskets can be used for general service with almost any commercially produced finish. Flat Metal Caskets: These are defined as gaskets that are relatively thin com pared to their width. (Unless machineformed, width should be at least thick ness plus 50%.) They can be used as cut from sheetmetal, or with the surface area reduced by machining to improve sealablllty. Plain, metal, washer-shaped gaskets are relatively inexpensive to produce and can perform satisfactorily in a variety of applications over a wide temperature range. The machined types, with reduced surface area, may be the answer to highpressure. high-temperature, or highly cor rosive applications in nonspecial flanges where bolting forces are too light for fhe plain flat type. All types seal by flow of the gasket surface caused by brute-force compres sive loads. Loads actually must exceed the tensile strength of the gasket metal on the gasket-contact area. Therefore, surface finish of both flange and gasket is very important. Serrated or grooved flat metal gasketa do not require as much bolting force to seal. They are also useful in screwed closures because of lower friction caused by their peaks. Finishes of plain metal gaskets are normally as cut from the metal in the "as received" condition. Therefore, the gasket will have the surface finish due to mill rolling, plus any storage or intransit damage. Furthermore, depending on the method of cutting, the gasket edges may have burrs or other irregu larities which may or may not affect performance. If higher quality levels are required, such as no burrs, scratch-free surfaces, close decimal tolerances, etc.. cost Is Increased. For best performance, flat, plain metal gaskets should be used between flange faces with concentric serrated surfaces. If this is rot practical, a very light-cut 121 ST0408950 ST0408950 ST 0U08951 DESIGN DATA--SECTION S Fig. 1--Typical resilient metal seal cross sections. spiral tool finish of 72-pin. AA may be used. Round Cross Section, Solid Metal: These gaskets are generally made from round bar stock of the desired diameter, cut to the length of the gasket mean circumference, then formed into a circle and welded. They provide positive, gastight seals at relatively low flange pres sures. Since only line contact occurs, they have high local seating stress at low bolt loads. The contact faces in crease in width as the gasket is com pressed, effectively flowing into flange faces. Round, solid gaskets are used on equipment designed specifically for them. Flanges are usually grooved or otherwise faced to accurately locate the gasket during assembly. However, there are some applications in which they are used between flat faces. Flanges, if flat-faced, should have sur face finish of 72-pin. AA or better. If one flange face has a V-shaped groove, the other should be flat. The volume of the V-groove should he less than the volume of the gasket so that there is no possibility of metal-to-metal flange contact. Surface finish should be 135180-pin. AA maximum. Taper-faced flanges are satisfactory as long as the volume of enclosed space is less than the gasket volume. Surface finish should be 135-180-pin. AA max. Solid Metal, Heavy Cross Section: These are usually rectangular or tri angular-shaped gaskets, machined in heavy cross sections from solid metal. Table 5. They are used for high-pres sure and high-temperature services where operating conditions require special joint designs. The gaskets usually seal by line con tact or wedging action which causes sur face flow. Some of them are pressureactuated; i.e., the higher the pressure, the tighter the joint. Materials can be any wrought or forged material. Cast material should not be considered. Materials requiring heat treatment after final machining usually should not be used because of possible warpage. Resilient-Metal, Pressure-Actuated: Re silient metal seals combine the efficiency of elastomeric O-rings with the extended temperature capability of metal gaskets. The basic structural element is usually a high-strength metal, and s soft coating of metal or plastic provides the actual sealing. Like O-rings, these seals are self energizing, have small cross sections, require light closing forces, are often re usable, and have indefinite life. Unlike O-rings, however, they are relatively ex pensive, and availability is somewhat limited. Common cross sections are shown in Fig. 1. Metal seals are sometimes used to replace O-rlngs to extend the tempera ture capability of a system or device. However, unless required because of tem perature, true zero leakage, fluid com patibility, or extremely high pressure, resilient, light cross section metal seals should not be selected over the less expensive elastomeric O-ring. They can also be used when standard metal gas kets are ruled out because the flange load that would be required is too great to be feasibly attained. Light cross section metallic gaskets can use essentially the same groove dimensions and bolting as rubber Orings. The metallic seals operate by es sentially line contact, and require very little bolting force to seal when initially compressed. Pressure of the confined fluid acts on the bellows area to main tain the seal, even if flanges separate slightly. Materials used include Inconel X, A286 steel, aluminum, beryllium copper, tantalum, Rene 41, Hastelloy, Haynes 25, and nickel. Coatings can be used to pro vide a soft material to fill small imper fections in the flanges. Coatings include silver, indium, gold, lead, copper, and some plastics. Bolt loadings required to effect a seal range from 50 to 350 lb per circumfer ential inch. Loading necessarily depends on cavity finish, fluid viscosity, and coating (if any). Flange finish for bare, light-cross-sec tion gaskets should be 4 to 29-^in. AA. For plated or coated types, the finish can be from 29 to 90-pin. AA. Credit Text and data for this chapter furnished byJohn B. Painter, Senior Development Engineer, Johns-Manvllle Product Corp.. North Bruns wick, N. J., and 3. W. Rhine, General Bales Manager. Flexltalllc Gasket Co. Inc., Camden, N. J. O-Ring Types For a. static seal that will meet ex treme conditions of temperatures (under -65 F and over 450F), pressure (high vacuum and above 3,000 psi), radiation (above 10s rad), and corrosion with low cost, simplicity, and design flexibil ity, the best solution is the metallic Oring. Table 6. Also, it can be "baked out" and does not outgas. Metallic O-rings are made of metal tubing which is formed into circular or other required shapes, the two ends resistance butt-welded together, and the weld ground flush. Welding is some times done by tungsten inert gas or plasma arc. in vacuum or inert-gas en vironments. The typical application places a me tallic O-ring in axial compression between parallel faces which are square to the fluid passage or vessel axis. The seal is usually located in a counterbore or closed groove in one face, or in a re tainer, which eliminates the need for ma chining a groove. Other seal or groove configurations may be used. Principles of Operation Upon compression to a predetermined fixed height, the seal tubing buckles slightly, resulting in two contact areas on each seal face, and maximum contact stress between the sea! and the mating faces, Fig. 2 The seal accommodates some deviation from flatness and parallel ism of the sealed faces. In many liquid-sealing applications, the surface tension is high enough in rela tion to the pressure differential across the seal so that no leakage occurs with plain (uncoated) seals. In the remainder of the liquid and most gas sealing ap plications, the seal surface must be plated or coated with a softer material which yields by compression to conform to surface irregularities of the mating faces. Application Factors Several factors are involved in sealing by hollow, metallic O-rings: ST0408951 MEIALLiL Table 6--Types of Hollow, Metallic O-Rings Plain, Sealed Meta !ic O-Ring For fully-confined or ecmlconflned ring Joints. When fully-confined, standard and pressure-filled metallic O rlnfs are useful at temperatures from --420 T to +3,000 F. They seal vaeuum. pressure, corrosive liquids, and gases. Standard types do not teal In temlconflned designs to at high temperatures and pressures as a pressurefilled, but are more economical. I Self-Energizing Metallic O-Ring For temlconflned designs. Inner periphery it rented by small holes or large slot; therefore, pressure Inside ring Is tame as In the system. Increasing Internal pres sure causes ring to be crammed Into groove. Increasing sealing effectiveness. ST0408952 Fig. 2--Typical installation for a metal lic O-ring. Tubing: The first requirement is that the tubing be able to supply the force needed to cause its plating to yield, Fig. 3. Stress relaxation must not occur at the operating conditions. The main limit ing factor for stress-relaxation is tem perature of the seal. For 321 stainless steel, this limit is 500 F; for Inconel 600, 800 F; for Inconel X-750, 1,500 F. Tem perature limits on the most-used plat ings or coatings are: PTFE fluorocarbon, 500 F; silver, 1,300 F; nickel 2,200 F. Specialized tubing materials for ex treme conditions of corrosion, radiation, or temperature Include aluminum, titani um, and tantalum. Specialized platings are gold and indium. As a rule of thumb, wall thickness for seals made from Vi-in. tubing and smaller should cause yielding of the plating at a pressure under 400 lb per circumfer ential inch. For tubing over '/J-in. diam, 800 Ib/in. should be required. However, wall thickness Is not important with PTFE coatings. Grooves: Typical installation for seated O-rings is shown in Fig. 4. Correct groove depth must be used to ensure proper seal geometry and required load after installation. The grooves must also provide radial restraint of the seal to carry forces caused by the retained pres sure. Clearances must take into account any plating thickness. Grooves and flange faces must have the proper surface finish--32-pin. rms for bare rings and 32 to 100-pin. rms for plated or coated rings. Dirt, rust, scale, and other foreign material must be removed from the seal area prior to Installation. Leakage Unplated Seals: Liquid leakage can be estimated by use of the following expres sion, which Is based on tests at moderate pressure: 0 = 5.0 X 10"' P/u. Where Q = leakage, cc/sec; P = pressure dif ference. psl; and u = liquid viscosity at Pressure-Filled Metollie O-Rlng For fully-confined or temlconflned de sign!. Ring It filled with inert gas at about COO pal. At elevated temperatures gat pressure Increases, offsetting loss of strength In tubing and Increasing the resilience. This ring cannot support pres sures as high as self-energizing ring, but Is useful In temperature range of 800 to 1,500 F. OJ 1.0 10 100 Seol Ring Diorneler (in.) Fig. 3--Seal load vj. seal ring diameter for various tubing outer diameters (OD) and wall thicknesses (t) of 321 stainless-steel tubing. For tubing made of Inconel 60O, multiply loads shown by 1.1; for Inconel X-750, multiply by 1.4. operating conditions, centipoise. If the resulting calculated leakage is in the range of 10~3 to 10"* or less, actual leakage may be zero because of surface tension. If leakage occurs, it should be proportional to seal diameter, and the above expression multiplied by D/2; Where D = seal diameter, in. Actual leakage will most probably be less than predicted. Plated Seals: Helium-leaktight joints will result from proper seal selection and application. Test results vary from I0~a to 10 " cc/sec and lower at one-atmos phere pressure differential. Credit Text and data for thl* chapter furnished by R. L. Qas(1neau Product Manager. Seal* Dlv.. United Aircraft Product* Inc.. Dayton. Ohio. Fig. 4--Fully-confined bollow-metal Oring, a, before bolting down and b, after bolting down. Seals Reference Issue 123 ST0408952 ST0408953 Technology Of Sealing Threaded And Flanged Systems By R. Andreasen, G. Haviland and J. Tokarski INTRODUCTION When discussing sealing, the first thought that comes to mind is leakage. Leakage exists in all fluid (gas, vapor or liquid) systems to one degree or another. The amount of leakage that can be tolerated is a matter of choice. Acceptable leak rates can range from a slight drip, to bubble-tight, to mass spectrometer measurements, to diffusion of molecules through the base material. Equipment users want trouble-free operation but it is not always practical to specify "zero" leak rates. Overspecification in this area usually leads to increased costs, and sometimes impractical or unwieldy designs. Toxicity, pro duct or environmental contamination, combustibility, economics, and personnel considerations are factors influencing the establishment of acceptable leak rates. An increased awareness of leakage has come about through conscientious efforts to conserve fuel and energy. It has been estimated that leakage from hydraulic systems alone costs industry over $250,000 a day to provide makeup. This cost becomes substantially greater when we combine the leakage encountered in other fluid systems, such as water, air, steam, refrigeration, and so forth. Leakage can also be hazardous. Discharged fluids leaking onto the floors or walkways present a safety hazard to personnel as well as a potential fire hazard. And, of course, from an aesthetic point of view leakage is messy, unsightly and produces housekeeping problems. These and other problem areas can be eliminated or at least minimized through proper leakage control. In addition to the savings in material and labor costs, other benefits that accrue from proper leakage con trol include increased production rates, decreased machine down time, and the prevention of product spoilage. In general, the safe, continuous and proper operation of all fluid systems relies on the integrity of the system and exces sive leakage defeats this. THREADED SYSTEMS Technological advancements in manufacturing have enabled a great many fluid carrying systems to be built with fewer components, thus reducing the number of areas that might otherwise leak. This is the designer's objective, but in some cases it is not practical, especially where accessability for maintenance and repair is required. Also, fluid systems such as water or steam are usually assembled permanently in their place of use. They require some type of connec tion to attach thfe various elements. These connections may be permanent or replaceable. Examples of permanent fittings using welded or brazed connections are shown in Figure 1. The removable fittings, which will be discussed in this paper, are used more often because of their cost and convenience. They come in a variety of sizes, shapes, materials, and performance capabilities. Of course, to be acceptable, they must be leak tight under the maximum surge pressure, vibration, shock or other fluid system abuses. Removable fittings end in either male or female threads. The main function of the threaded portion is to mechani cally bond or attach fittings to other fittings or equipment housings, but they may also provide the necessary seal as we will see shortly. 1975 Loctite Corporation Newington. Connecticut ST0408953 -I - ST04 08.95* Fig. 1 Permanent Fittings There are three types of threads currently used on fittings. Two are tapered from the outside to the inside end of the fitting, and the third type is parallel or straight from one end to the other. The taper, shown in Figure 2, provides a gradually increasing interference fit as the joint is tightened. A variety of common types of fittings using this taper are shown in Figure 3. PIPE THREAD SECTION Fig. 2 Standard Taper ADAPTER 'Trrrfffln/mi HEXAGON NIPPLE COUPLING nJ MALE BRANCH TEE STREET ELBOW ELBOW CROSS Fig. 3 Typical Taper Fittings ST0408954 3- ww wv AA/^ Straight Thread Wrench Tight American Standard Wrench Tight NPT Dryseal Hand Tight NPTF Dryseal Wrench Tight Fig. 4 Straight Thread and Taper Thread Assemblies The straight thread and American Standard Taper Pipe Thread (NPT) are assembled with a sealant to provide a satisfactory pressure tight joint. As indicated in Figure 4, the straight thread assembly has open channels or leak paths that must be sealed. The NPT assembly produces more metal-to-metal con tact along the thread flanks but still leaves a spiral leak path at the thread crest and root. The Dryseal Standard Taper Pipe Thread (NPTF), also shown in Figure 4, was adopted to eliminate the use of a sealant. To accomplish this some modification of thread form, greater accuracy in manufacturing, and more analytical gauging is required. The roots of both the external and internal threads are truncated slightly more than the crests, i.e. roots have wider flats than the crests, so that metal-to-metal contact occurs at the crests and roots coincident with or prior to flank contact. Thus as the Dryseal thread is assembled, the roots of the threads crush the sharper crests of the mating threads. The result is a leak tight connection without spiral voids. Due to the crushing and wear that occur with disassembly and reassembly, tapered threads are less effective on reuse than straight threads. A method of over coming this disadvantage is to use a straight thread and a lock nut with an embedded seal or insert. Figure 5. The lock nut is threaded onto the male fit ting and the fitting is then threaded into the female component only far enough ST0U08955 Fig. 5 Pipe Thread Locknut ST0408955 -4- to ensure a mechanical connection. After positioning the fitting, the lock nut is tightened down onto the fitting until it makes a secure contact. In this way, the straight threads provide the mechanical attachment and insures reusabi lity while the embedded insert seals against fluid leakage. The 0-Ring seal is another way of providing the leak tightness while the thread furnishes the mechanical attachment only. Two types of straight thread 0-Ring fittings are available. One type (non-adjustable) is used for adaptors, plugs, connectors, etc., and utilizes an 0-Ring mounted in a groove about the threaded portion of the fitting. Figure 6. The other type, which permits angular adjustment of these fittings, utilizes a backup washer and lock nut, Figure 7. 9 S 6 8 0 i0 1 S O-RING O-RING Fig. 6 Nonadjustable Straight Thread Fitting Fig. 7 Adjustable Straight Thread Fitting Tube fittings are another form of connection. Figure 8 shows a typical 2- piece and 3-piece flared assembly. They derive their seal from the swaged portion of the tube. The female tubing nut, once engaged and tightened, com presses the flared tubing against the mating cone of the male fitting. The 3- piece fitting adds an extra element that provides better structural integrity and is less affected by vibration. If all of the fittings discussed were 100% efficient, industry would not have the expense noted earlier in providing makeup. The fact remains that fittings leak. Some fittings control leakage better than others but usually at a higher cost. The most crucial factor involved with the selection, installa tion, and maintenance of fittings is the "human factor". Designers will strive to cut costs by using less expensive fittings that are borderline for a parti cular service condition. The assembler often fails to follow recommended installation practices and the maintenance worker will reuse old fittings rather than buy new ones. I i t ST0408956 ST040895! 5- - a Fig. 8 Typical Flared Fitting NPT fittings (ref. Figure 4) were shown to have spiral leak paths at the thread crest and root after installation. Straight threads had similar gaps but much more pronounced and extended along the thread flanks. Sealants are required on fittings or port connections that utilize these thread forms. Although the Dryseal (NPTF) thread eliminated these spiral gaps, galling may occur during assembly. The galling is produced when the threads are crushed and deformed, creating small scratch-like leak paths. A lubricating sealant (although not required) is recommended to reduce the associated friction and prevent galling of the threads. Also, extremely high stress points are developed at the thread crests and roots on the Dryseal fitting. Overtightening may create cracks in the mating fitting or housing because of these stress points. Initially, the cracks might not be visible but could show up later as fatigue failures or fluid seepage, as the cracks begin to grow. The fittings shown in Figures 5, 6, and 7 all used plastic or rubber inserts to form their seal. For these fittings to properly seal, the insert or 0-Ring must flow into all surface imperfections. Undertightening of the fit tings does not allow proper deformation of the insert to occur and conversely, overtightening could crack or extrude the seal from its mating surface. The compatibility of the insert with the environment is also important because some plastics and rubbers degrade when in contact with certain fluids. Temperature extremes will also cause some materials to become brittle and crack over a period of time. % ST0408957 ST0408958 6- The tube fittings shown in Figure 8 are also subjected to the same human factors as the others. The proper flaring of the tube could be cited as the single most important factor. A flare that is too short reduces the clamping area and the wall thickness may be decreased when clamped. A flare that is too long may stick or jam on the fitting thread when assembling. Examples of incorrect flares are shown in Figure 9. The correct length and diameter should provide a flare which extends beyond maximum I.D. of fitting sleeve but not beyond the O.D. of the sleeve (Figure 10). Fig. 9 Incorrect Flares i Fig. 10 Correct Flare Angle In summary, fittings rely on intimate contact to form their seal. The threaded portion of a fitting has three functions: 1. To form the seal as was shown with the Dryseal thread 2. Provide the mechanical attachment to other fittings or equipment ports ST0408958 7- - 3. Provide the force needed to compress the sealing element, i.e. 0-Ring, plastic insert, flared tubing, etc. Each function requires that the proper tightening torque be observed and that movements of the fittings in a loosening direction should not occur. Such movements cause either some or all of the contact pressure to be lost depending upon the nature of the seal. For example, Dryseal threads and flared tubing have very little compressibility and small movements in the loosening direction cause immediate loss of the original metal-to-metal contact. The 0-Ring or plastic seal, on the other hand, can accommodate some movement which is proportional to the elasticity of the elastomeric material used. Vibration loosening of fittings has always been a major concern in controlling leakage. Even though fittings are considered to be static seals, they are subjected to a variety of dynamic forces that are discussed in the next section on gasketed assemblies. FLANGED SYSTEMS Static Seals All types of fluid seals perform the same basic function and that is to keep the process fluid (gas, liquid and vapor) where it belongs. They accomplish this by forming an impervious barrier against fluid transfer between two mating sur faces. Traditionally seals have been categorized as either static or dynamic. The primary distinction between them involves the degree of movement with respect to the mating surfaces. For example, dynamic seals are used to retain fluids or throttle leakage between a sliding or rotating part and a stationary one whereas static seals prevent fluid loss between two stationary surfaces. This generic classification of seals is somewhat misleading and implies that static joints are completely rigid. Granted there are no gross movements between the mating parts, but movements are present because of several agents that act alone or in combination with one another. The four most important agents are temperature, fluid pressure, fluid velocity and system vibration. These agents produce adverse effects on the seal in ways that are not always fully understood. The following discussion will attempt to develop an understanding of these agents. ST0408959 6S680*?01$ 09680*101S -8 - Temperature Effects Fluctuations in temperature of a gasketed assembly create a variety of changes, all of which can affect sealing properties of that assembly. High thermal stresses can be developed within the gasketed joint because of the vari ous sizes, shapes and materials of the elements involved, i.e. bolts, flanges and gaskets. Stresses from thermal loads occur when the components are subjected to temperature gradients or to uniform temperatures where the components have dif ferent coefficients of thermal expansion. These thermal loads are high enough to be of engineering concern. The thermal stresses can produce abrading, crushing, extrusion or loss of bolt load. Example I in the Appendix shows that a thermal change of 370F will cause a change in bolt length by the same amount as a 80,000 psi prestress. This means that for each 1F difference in tempera ture between the bolt and the flange, the stress in bolt changes by 216 psi. Example II, of differential thermal expansion shows that an aluminum flange bolted to a steel flange expands radially, 0.013 inches more than the steel for every 10" of flange diameter and for 200F change in temperature. Pressure and Velocity Effects Fluid pressure and velocity surges can also be present in the system. Surges of this type usually result in vibration. For example, if a valve is suddenly closed or an obstruction blocks the flow of fluid, a pressure wave is generated by the kinetic energy of the fluid. This pressure wave travels at the speed of sound for the fluid through the downstream line until the wave is reflected back to the point of origin. If the system has separate branches, the wave is reflected separately through each branch. This phenomenon is repeated with shock waves overlapping each other until the original kinetic energy is absorbed by friction. In a water system the shock waves are referred to as water hammer because of the noise and vibration that usually accompanies the waves. External Vibration External vibrations also stress a gasketed joint in a manner similar to the internal vibrations caused by shock waves. An out of balance pump can vibrate the connected pipe rather severely, causing premature joint failure. Likewise, joints made on cars, airplanes and boats will be subjected to all of the vibra tion and twisting motions of that vehicle. In summary, we can say that static seals are not truly static, but are a throbbing, squirming and shaking system composed of several elements. These elements are the flanges, bolts, and gasket or seal and sometimes the attachment of the pipe to a shaking vehicle frame. The design, material selection, and maintenance of any gasketed joint must include consideration of all the agents acting on the system. We shall see that very often the system is a compromise of choices. For instance, the material that will seal rough flanges may not be the material that will withstand hydraulic hammering. Sometimes this compromise means changing some of the elements in order to get an effective joint seal. For ease of analysis, however, we will study each one of the important elements of a gasketed system individually and not attempt to pull them together until the end of this discussion. ST0408960 ST 0408961 9- - Flanges Although the gasket material is considered the most important element in the system, it may fail to provide a seal because the other elements were not designed and constructed to make the best use of its properties. It is the contact pressure between the gasket material and the flanges that produce seal ing. These pressures must be satisfactory for resisting the movements caused by those agents previously discussed (temperature, fluid pressure, fluid velocity and system vibration). The flanges are important because they must transmit a compressive load to the gasket. This load must be maintained above a certain critical pressure called the minimum sealing stress. This stress is defined as the minimum stress a gasket must experience to close its internal structure to the passage of the sealed fluid and conform to the surface irregu larities of the flange. The minimum sealing stress is highly dependent on the gasket material used, viscosity of sealed fluid, the v/idth to thickness ratio of the gasket, the gasket shape factor, surface finish of the flange, and the stiffness of flange. For instance a firm cork and rubber gasket requires a sealing stress of 600 psi to seal 80 psi internal pressure with stiff flanges (4). Fig. 12 Forces on a Flanged Assembly If the working pressure is too high for the design of the flanges, adverse flange and bolt distortions will occur. The major problem encountered with flanges is distortion. Distortions most commonly found are: .1) bowing, 2) bolt hole distortions, 3) non-parallelism and 4) surface roughness. Each one will be discussed separately. ST0408961 ST0408962 - 10 - 1. Flange bowing. Figure 13 illustrates the distribution of stress on a flexible flange. The area where this joint is most likely to leak is right at the center of the flange (c) where the smallest stress is produced by the bolts and where the maximum bending occurs from internal pressure. One way to improve this situation is to stiffen the flange to get the result shown in Figure 14. As obvious as this seems, the economics of producing stiff flanges often pre cludes this approach. The bowing of flanges is the most common reason for leakage. ST0408962 ST0408963 - 'll - Fig. 14 Effect of Stiffening the Flanges 2. Bolt hole distortions. This occurs around the bolt holes in a flange. Figure 15 shows a stamped sheet metal flange before bolt loading (bottom) and deformation after loading (top). High stresses are transferred to the gasket material under the bolt head causing the gasket to crack, tear, rupture or extrude, as shown in Figure 16. Bolt hole distortions do not necessarily lead to leakage but can cause bolt load losses that will result in fatigue failures if the system is subjected to dynamic forces. 3. Non-Parallelism. Figure 17 shows flange cocking or non-parallelism. Cocking in itself does not create serious problems until the pressure in the area of low gasket compression falls below the minimum sealing stress. This type of distortion is usually caused by improper machining, improper heat treating, casting irregularities or improper tightening sequence of the bolts. ST0408963 - 12 - Gasket Extrusion Figure 16 Non-Parallelism Figure 17 ST0408964 Side View of Flange After (Top) and Before (Bottom) Bolting Figure 15 ST0408964 - 13 - 4. Surface roughness. The various operations required to fabricate the sur face of a flange face produce distortions or irregularities. A comnercial finish is made by milling machines, grinders, and abraders. The roughest surface normally found in flange joints is 250 micro inches. On the other hand, an exceptionally smooth or mirror finish is rarely found because expensive machining operations are required. There are some rough surface finishes that are planned and are defined as phonographic and concentric. They are not random irregularities but carefully dimensioned in width, height and depth of cut. The serrated finish is almost always found in pipe flange assemblies and is used more or less as a stress riser. To eliminate leakage from surface irregularities, the minimum sealing stress must be achieved thereby ensuring that the gasket flows into all flange face imperfections. Bolts The next element in the gasket joint is the bolts. The life of the gasketed joint can be greatly affected by the design of the bolting system. Almost all of the force for producing the minimum sealing stress is generated by the bolts (a small amount may come from gasket adhesion and gasket swelling from chemical and pressure effects). It is important that the bolts not only produce the design pressure initially on the gasket but maintain that pressure throughout the service life of the assembly. Bolts lose their initial stress or clamp load in a variety of ways. Some of the more important reasons are listed as follows: 1) gasket relaxation, 2) bolt hole distortion of the flange, 3) temperature effects, 4) vibration loosening and 5) system load changes. It is sometimes helpful to use a spring analogy in explaining the bolts specific function within a gasketed assembly, Figure 18. The bolts actually stretch or deform like a spring when a load is applied. The necessary clamp load cannot be exerted on the flange and gasket if this axial stretching did not occur. The amount of clamp load that can be applied depends on the bolts strength, the rigidity of the flange and the compressive strength of the gasket material. After the assembly has been tightened, the bolt stretches in tension 59680*101$* SPRING APPROACH FOR A MODEL SYSTEM Fig. 18 ST0408965 - 14 - and the flanges and gasket are in a state of compression. Assuming the flange is infinitely rigid and the gasket is thin so that its effects are negligible, the goal is to increase the amount of elongation in the bolt. Increasing the elongation that a bolt experiences helps to maintain the required clamp load. There are two ways to increase bolt elongation: 1) by increasing the effective bolt length, and 2) decreasing the spring constant of the bolt. Effective bolt length is shown in Figure 19. The rule of thumb is that when the length of the bolt is five times greater than the diameter it can be elongated sufficiently to work as a spring between two flanges and will dampen vibration. The relationship between the effective bolt length and the clamp load might be understood more clearly with a hypothetical example. For instance, a bolt with an effective length of 1 inch elongates 0.004 inches under a given load. Now, what if the gasket material used relaxed in compression approximately 0.002 inches over some time period? The original clamp load would be decreased by 50%. However, if the effective bolt length was increased to 2 inches under the same load, the bolt would now elongate 0.008 inches. The gasket relaxes about the same amount (the load has not changed) but this time only 25% of the original clamp load has been lost. Clearly a 25% load loss is more desirable if we are concerned with maintaining a clamping pressure above the minimum sealing pressure requirements. Several things can be done to increase the effective bolt length: 1) use a thicker washer under the bolt head, 2) design a boss on the flange, 3) use a thicker flange, and 4) machine down the top portion of the engaged threads. The other method used to increase bolt elongation is to decrease the spring constant of the bolt. The spring constant (K) of the bolt is simply the ratio of the applied load (F) to the elongation (X) produced by that load: K = F/X Effective Bolt Length Fig. 19 Assemblies using bolts with low spring constants have a smaller clamp load loss than do high spring constant systems and provide longer gasket life in designs involving dissimilar metals with different coefficients of thermal expansion. ST0408966 ST0U08966 ST0L08967 - 15 - Lowering the spring constant reduces the pounding of the flanges, causing the gasket to crush or fail. Figure 20 shows that for a given bolt load, low spring constant bolts elongate more than high spring constant bolts. BOLT ELONGATION BOLT ELONGATION Fig. 20 Bolt clamp load versus bolt elongation to show effect of spring constant on load loss as gasket material relaxes. As mentioned earlier in the effective bolt length section, for a given clamp load a gasket material will relax over a period of time. The dotted line in Figure 20 represents this load and shows the corresponding gasket relaxation. The low spring constant bolt loses less clamp load than the high spring constant bolt, thus adding more reliability to the sealing function. The spring constant can be lowered by decreasing the number of bolts used, reducing the diameter of the bolts down to the root diameter (Figure 21), increasing effective bolt length, increasing the length of the threaded sec tions, or decreasing the size of the bolts. Decreasing the size of the bolts from 3/8 to 5/16 might involve going to a stronger grade of fastener to achieve the proper clamp load. Of course, any of these changes must be checked against the entire system to ensure proper performance and lasting service life. ST0408967 ST0408968 - 16 - Nominal Diameter Rounded Out For Hole Location -- Root Diameter Hexagonal head bolt with spring constant lowered by turning or reducing bolt shank down to thread root diameter Fig. 21 Gaskets The third and final element in the flanged system is the gasket. The main function of the gasket is to create a barrier against the transfer of fluid across two mating surfaces. There are, however, other reasons for a gasket's existence, such as, cost and accessability. Manufacturing and shipping costs are much lower when assemblies are composed of small elements that are joined later with a gasket to form a complete and leak tight unit. The assembled unit can at any time be disassembled for repair or maintenance. Without this acces sability, repair might be extremely difficult, if not impossible. Gaskets are also used to join dissimilar materials, dampen vibration, and insulate against the transfer of heat. Materials used for gaskets fall into two broad categories: metallic and non-metallic. The metallic gaskets can be steel, copper or a metallic and organic composite. Materials such as asbestos, cork, cellulose, and rubber are non-metallic gaskets. Other types of non-metallic gaskets are sealants or formed-in-place materials. These materials can be applied to any shape flange and are generally considered to be pressure containing, but not load bearing, because of their fluid consistency upon application. All gaskets, whether metallic or non-metallic, must perform four basic functions: 1) Must create a seal 2) Must maintain the seal 3) Must be impervious to fluid flow 4) Must be compatible with the environment. ST0408968 S T 0 t0 8 9 6 9 - 17 - Each function has its own relative importance with respect to the integrity of the gasket assembly. A brief discussion of each one will point out their rela tive importance. First, a gasket must create a seal between the flanges by conforming to all flange face irregularities as shown in Figure 22. FLANGE ' ^GASKET L FIANGE NO CONFORMATION (WRONG) FLANGE OASXET FLANGE PARTIAL CONFORMATION (WRONG) TOTAL CONFORMATION (RIGHT) Fig. 22 Gasket and Flange Conformation On smooth or polished flanges a relatively firm material may be used. When sur faces are rough or show excessive tool marks, either a thicker, softer gasket or heavier bolting pressures must be used. The effects of changing the gasket thickness on the other elements will be pointed out shortly. Second, the gasket must maintain the seal throughout the life expectancy of the joint. Joints are sometimes subjected to considerable movements caused by vibration, mechanical strain, changes in temperature, pressure and velocity. Despite these movements, the gasket and flange surfaces must remain in intimate contact. The major factor in maintaining contact is the elastic response of not only the gasket, but the bolts and the flanges. Third, the gasket must be impervious to fluid flow, both internal and external. Materials such as cork with rubber or straight rubber normally are impermeable even with small flange loads. Others such as fiber sheet packings and cork are impermeable only when compressed sufficiently to close their natural holes. ST0408969 STOL08970 - 18 - The fourth requirement is compatibility with the environment. A gasket material must be able to withstand the full range of temperature changes without deteriorating. Flange staining and corrosion, which is generally promoted by vulcanizing agents, accelerators, and moisture present in the gasket material, should not be visible on the flange face. Gaskets must also be relatively inert to the effects of a sealed fluid. Slight swelling is often beneficial, whereas deterioration of the material or contamination of the sealed fluid is not tolerable. PHYSICAL PROPERTIES Various physical characteristics have been defined to evaluate a gaskets performance properties and to measure its ability to meet the four requirements previously discussed. The most important physical properties of a gasket mate rial are: Compressibility. This property indicates the degree to which the material is compressed or deformed, in thickness, by the application of a specific load. This property is expressed in terms on a percentage of the original thickness. Compressibility is used to determine whether a material can compress suffi ciently to compensate for surface irregularities or non-parallel conditions in the flange. Compressive Strength. Compressive strength can be described as the maximum compressive stress that a material is capable of withstanding without rupture or excessive extrusion. From a functional standpoint, this physical property is important because it is directly related to the ability of a gasket to resist flange loading without breaking down. Stress Relaxation. This is a transient stress strain condition in which the stress decays as the strain remains constant. Creep. This is a transient stress strain condition in which the strain increases as the stress remains constant. Creep Relaxation. This is a transient stress strain condition in which the strain increases concurrently with the decay of stress. Fluid Compatibility. Immersion tests provide a simple means of measuring the effect of various liquids on a gasket material. The procedure consists essen tially of immersing a prepared specimen in the desired fluid for a specified length of time at a specific temperature. The weight, thickness or volume increase are the properties most frequently measured after removal of the specimen from the fluid. ST0408970 ST040897I 19 - Flexibility. This property is usually determined by bending a specimen 180 around a mandrel of a specified diameter. As applied to materials in their original condition, flexibility is of value in determining the handling quali ties of the material. It does not directly correlate with other physical properties. Heat Aging. Heat aging properties consist of exposing the material at a speci fied temperature in a circulating air oven for a specified length of time. Physical characteristics measured after removal of the test specimen may include flexibility, durometer hardness and elongation and are compared with those values for the same materials prior to testing. There are many other considerations to be made before a suitable gasket can be selected, such as its ability to resist tearing, weather, fire, fungus and vermin. Most of the physical properties listed above pertain to pre-cut gaskets; however, formed-in-place materials must also meet many of these requirements, especially degradation from fluids, heat or other environmental constraints. Gasket Thickness versus Stress Distribution Perhaps the most important requirements of any gasket material is to create and maintain the seal. In the section on flanges we defined minimum sealing stress as the minimum pressure the gasket must experience to close its internal structure to the passage of the sealed fluid and to conform to the surface irregularities of the flange. As we shall now see, the thickness of a gasket material has a profound effect on two of the major requirements of the gasket, that is, creating and maintaining the seal. Figures 13 and 14 showed how stiff flanges improved the load distribution on a gasketed joint. To increase the minimum sealing stress between the bolts, Figure 14 suggested stiffening the flange. The same effect can be obtained by making the flange bow more, through the use of a softer or thicker gasket as shown in Figure 23 and 24. Increasing the thickness of the gasket will enhance its capability to create the initial seal. Now it would be instructive to see exactly what effect increasing the gasket thickness has on maintaining the seal. Relaxation is one of the major considerations for maintaining the seal, primarily because pre-cut gaskets creep or relax in service to some degree. A relaxation curve of a rubber asbestos gasket is shown in Figure 25. It shows relaxation of the gasket as measured by torque loss in the bolt vs. thickness of the gasket. The solution to this effect is to use a harder or thinner material. ST0408971 - 20 - ST0U08972 TO RQ UE RETAINED (IB -F T ) Fig. 23 Fig. 24 25 70 -- 0.5% LOSS 15 10 5 20 IB-FT INITIAL TORQUE ^--------- ----------- 76.5% tnaz 0 i/m 1/32 l/l6 GASKET GAUGE TIN.) 3/3 7 Curve shows better torque retention of thinner gaskets. Four gauges of a rubber-asbestos material were confined in steel flanges with bolts torqued to 20 lb.-ft. Retained torque was measured after flanges had been heated at 300F for 18 hours. Fig. 25 Gasket Gauge vs. Torque Retention t ST0408972 - 21 Formed-in-place materials should also be considered with respect to creat ing and maintaining a seal. Referring back to Figures 23 and 24, flange loading was increased by using a thicker gasket. Now, if the stress distribution was redrawn for a non-adhesive formed-in-place material, the curve would look like that shown in Figure 26. The non-adhesive material will not follow the movements of the flanges. Figure 27 shows what happens if the material is mildly adhesive. A mildly adhesive material will seal more flexible flanges, provided that the adhesive is also flexible enough to follow the flange bowing under internal pres sure. Usually this adhesive technique cannot be carried to the extreme because flange disassembly becomes very difficult. Figure 28 shows what can be done if the flanges are prestressed in such a manner that internal pressure does not exceed or add to the prestress. This is accomplished by providing pre-bowed covers, or bosses on the mating surfaces. In other words, the gasket surface can be prestressed so that the stress distribution is more uniform. Figure 29. ST0408973 F LANGE SEPARATION PRESSURE CD O FLANGE separation PRESSURE INCREASED A acD Non-Adhesive Sealant Fig. 26 Mildly Adhesive Sealant Fig. 27 ST0408973 11 - and Prestressed Cover Prestressing We have seen that a sealed joint is not a static device. It moves under the influence of temperature, fluid pressure and velocity, and external vibra tion. If a joint leaks, it may not suffice to change only one element within the system. With any change, one must always keep in mind its effect on the minimum sealing stress. SYSTEM RELIABILITY The fatigue or dynamic loading characteristics of an assembly have not been fully discussed. Their importance to the physical integrity of the joint cannot be overemphasized because the service life of an assembly is directly related to its ability to absorb and transfer these dynamic forces. In most assemblies, the ratio of assembly rigidity to fastener rigidity is high enough to almost discount any addition to bolt tension produced by dynamic forces. In a flexible joint with a soft gasket between bolted flanges. Figure 30, the rigidities of the joint and the bolt are quite different; here, a much greater proportion of the externally applied tension is added to the bolt preload. * ST0408974 - 23 - Fe/2 LOAD Fe/2 LOAD <y> 680*701 Fig. 30 The reason for this may become more obvious by studying the following equation: P = Pi + CFe (Eq. 1) where P = final load on the bolt, lb.; P-j = initial preload or clamping load developed through tightening, lb.; Fe = external applied load, lb.; and the constant EbAb C = Lb (Eq. 2) EbAb + EgAg Eb tg where Eb = modulus of elasticity of the bolt, psi; Eg = modulus of elasticity of the gasket, psi; A5 - effective cross-sectional area of bolt, sq. in.; Ag = loaded area of gasket, sq. in.; thickness, in. = effective length of bolt, in.; and tg = gasket The value of the constant C falls between 0 and 1. The term EgAg/tg in Equation 2 will be large in comparison to E^A^/Lb if the gasket is hard, thin, and large in area, the constant C approaches zero. When no gasket is used between members in a rigid joint, C = 0. For very soft gaskets, C approaches 1. It is important to remember that Equation 2 is only valid as long as the gasket remains in contact with the flanges. If the bolt stretches to the point where the gasket is no longer in contact, Equation 1 is simply P = Fe. ST0408975 94- 680*101 - 24 - The fatigue strength of a gasketed assembly must be evaluated in two ways: fatigue of the bolt, and fatigue of the bolted material. The properly tightened bolt will not fail in fatigue in a rigid joint. Initial bolt tension will stay relatively constant until the external tension load on the joint exceeds the bolt load. If the service load is less than bolt preload, the bolt will experi ence no appreciable stress variation, and without stress variation, there can be no failure by fatigue. This is not the case where considerable flexibility is present. Variable stress in screw or bolt fastenings increases with the flexi bility of the connected parts. If flexibility is too great, the variable stress present may be high enough to cause eventual fatigue failure of the fastener regardless of the initial bolt preload. Summary Selecting rigid joint members and choosing flexible fasteners are important steps to successful design. Soft materials in joint members may spell trouble unless extra design precautions are taken. If gaskets are used, they should be as rigid and thin as practical. But this is not always possible because thick and soft gaskets are required to seal imperfections and produce the minimum sealing stress. Formed-in-place sealants offer some advantages in this area. Equation (1) showed that the load on the bolts was essentially the preload Pi (since C is approximately 0) for stiff or hard gaskets. Liquid sealants create metal to metal flange contact to form a rigid joint. The greatest, single factor that can eliminate stress variation due to cyclic loading is proper preloading of the fastener. Test results indicate :hat rigid members bolted together by relatively elastic bolts offer the best assurance for preventing fatigue failure. Static seals are subjected to a variety of dynamic forces that cause move ments and create stresses within the joint. Loss of fluid and catastrophic failure, such as, fatigue fracture of the bolts are the end result of poorly designed assemblies. The gasketed joint must be thought of as a system for effecting a seal. Each component of the joint plays an important role in creating a seal but more importantly, maintaining that seal throughout the expected life of the assembly. ST0408976  t-6 8 0 *]0 ls Vegetable-fiber Gasketing Technical Information Garlock high-quality vegetable-fiber gaske.mg is sup plied in iwo styles' Style 6C0 with cork granules and Sode 681 without cork granules. TYLE NO. 660 kbtenat Vcfffta!>ie-lit#f and toik gienules with gfurglycenne binder Tensile strength (nrmmin) Con?ress<bility unJer lOOOpsi lo)<3 Recovery 40% {rTitnunun' I 22Oil resistance after hours in ASTVI oil at 70*-8i*F.: Thickness increase 5%(;n<uimun} WeieSt increase 23M maximum) Fuel resistance altet 22 hours m Fuel B at ?Q*-85*F.: Thickness increase 5% (maximum) Weight increase 30%|m?.iirnum) 22Water absorption after hours in dislitled water at 70'-85*F.: Thickness increase 30% (naxtinum) Weight increase 100% (maximum) Thicknesses available (inchest .010,1/6*, .021.1/32, 3/64, 1/16.3/32.1/8.3/16.1/* Widths available (inches) Tolerance on thicknesses (inches) Ston&ird 3$" Special 48" in (allowing thicknessesl/3?.l/16.3/3?.!/8.3'T6,1/4 .0101.00? .0161.0035 .C2U.005 ,03?l 0C5 .042+ .00$ ..006924*1.0m03 .12S+.03I-.O1S .167+.0)7-.02? .?S0r.02?-.030 3>ecihcaf:ons ASTM-D-II7CK2T Grace P-3415-A SAE J 90 Crade P-3415-A MIL G-12603A Grade P-3415-A 681 Vegeub'eTiber with gluD-piycenne binder 14.0 a (2030 F>S>) 2$V40% flOMnimmurp) 5%(maiimyn) lS- (maximum) 5% (maximum) 15% (maximum) 30\ (maximum) 90% (maximum) .006. -010,1/64, .021, 1/32.3/6*. 1/16.3/32.1/8. 3'16.1.'* Standard 36" .0061.002 .0101.002 .01 Si .0035 .0211.005 .03?.C05 .052*.006 .094*-008 .187+-017- 022 .250+ -022--.030 ASTM-D-1170-62T Grade P-3313- B SAE 190 Code P-3313-B WIL-C-12S03A Grade P-3313-8 HH-P-96F Type 1 How Branded Garlock name and style number GYLON & TFE Gasketing GYLON gasketing is made by a unique Garlock process that permits the restructuring of fluorocarbon particles to meet specific requirements of gasket applications. GYLON gasketing has the chemical resistance of TFE and handles pressures to 500 psi and temperatures from cryogenic to 260C (500oF). General chemical GYLON The gasket's function is lo seal two imperfect surfaces held together by one of several means, the most com mon being screw-threaded devices such as bolts. Sometimes the fastener itself must be sealed, ns in the case of a steel diuni bung. The bolt is a spring. It is an elastic member which has been stretched to develop a load by elongating it so many thousandths of an inch per inch of length. It must not be overelongated (overstrained), or the elas tic limit of the steel will be exceeded. The bolt then deforms and with continued loading (stressing) will quickly rupture. To avoid such problems with bolt tightening, the use of a torque wrench is recommended. Reference Table 5 shows the loadings achieved under various torques. The equipment designer normally specifies the torque required for his product. For example, the stud on an automotive cylinder head is typically torqued to 65 foot-pounds. The inch-per-inch relationship demonstrates that the longer the bolt, the more it must be strained to yield a desired load; thus, the longer the bolt, the more follow-up or come-back there will be in actual linear inches. This is highly desirable, since most gasketing materials tend to remold, to relax, to take a permanent set. This is a creep-relaxation phenomenon. The more follow-up of spring provided by the bolt, the better the retention of stress on the gasket to maintain a leakproof joint. In the same respect, a smaller-diameter bolt must be strained more to develop the same load. With the smaller-diameter bolt, there is a serious dan ger that it may be overstrained and stressed beyond the elastic limit, and finally broken. The smaller bolt, within its elastic limit, could give the same additional follow-up as the larger-diameter bolt of greater length. There are limits on the degree of flange surface im perfection that can be sealed successfully with a gas ket. Large nicks, dents, or gouges must be avoided, since a gasket cannot seal against them properly. The surface finish of a flange is described as follows: gasketing, color-coded fawn, meets FDA specifications. GYLON gasketing, color-coded black, is specifically designed for hydrofluoric acid service. GYLON gasketing should be considered for chemical applications where stress relaxation is a problem. The low compression set characteristics and excellent re covery features of GYLON make it ideal for valves, pumps, tanks, pipe flanges, strainers, mixing equipment and all processing equipment requiring chemical resist ant gaskets '"'-lock offers a complete line of TFE gasketing. /LON Service Recommendations: Style Color Code ' Service 1. ROUGHNESS--Roughness is read in millionths of an inch as the average of the peaks and valleys measur ed from a midline of the flange surface. This is ex pressed either as rms (root mean square) or AA (arithmetic average). The difference between these two methods of reading is so small that they may be used interchangeably. Roughness is also expressed as AARH (arithmetic average roughness height). 2. LAV--Lay is the direction of the predominant surfaceroughness pattern. 3. WAW/VSS-Waviness is measured in thousandths or fractions of an inch. Basically, it is the departure from overall flatness. 35102 35104 Black Fawn Hydrofluoric acid General chemical q ST0408977 Typical satisfactory rms or AA rear),'rigs should be from 125 to 250. ciner finishes of 64 or : en 32 rms ore normally suitable, but not necessary. Very fine finishes, such os polished surfaces, should be avoided, since dequato "tooth" in the surface is required to develop noucjh friction to prevent the gasket from being blown out or from extruding or creeping excessively. The lay of the finish should follow the midline of the gasket if possible-for example, concentric circles on a round flange or, next best, a phonographic spiral. Every effort should be made to avoid lines across the face, such as linear surface grinding, which at 180" points will cross the seal area at right angles to the gasket. FIGURE 1 A-Bowing of flanges due to too high a bolt load for the flange design. ST 0408978 TABLE 5 Load on Machine Bolts and Cold-Rolled Steel Stud Bolts under Torque Nominal Diameter of Stud . (inches) hi X. X X. X X. x V* V. i h; ix 'X y/. IX us 2 Number'*- 7 Diameter Oh ' at Root of Threads Thread Per Inch (inches)- 20 .185 18 .240 16 .294 14 .345 13 .400 12 .454 11 .507 10 .620 9 .731 8 .838 7 .939 7 1.064 6 1.158 S 1.283 f>X 1.389 5 1.490 5 1.615 x 1.711 Area at Root of Thread (sq. Inch) .027 .045 .068 .093 .126 .162 .202 .302 .419 .551 .693 .890 1.054 1.294 1.515 1.744 2.049 2.300 7,SOO psi - Torque " (ft.-lbs.).' C&mpres- sion (lbs.)-. 1 203 2 338 3 510 5 698 8 945 12 1,215 15 1,515 25 2,265 40 3,143 62 4,133 93 5,190 137 6,675 183 7,905 219 9,705 300 11,363 390 13,080 525 15,368 563 17,250 STRESS' ' 13,000 psi- ' . Torque . . (ft-bs.), . Compres-' sion (lbs.). 2 405 4 675 6 1,020 10 1,395 15 1,890 23 2,430 30 3,030 50 4,530 80 6,285 123 8,285 195 10,380 273 13,350 365 15,810 437 19,410 600 775 1,050 1,125 22,725 26,160 30,735 34,500 30,000 pil Torque ' (ft-lbs.) Compres sion (lbs.) ' 4 810 8 1,350 12 2,040 20 2,790 30 3,780 45 4,860 60 6,060 100 9,060 160 12,570 245 16,530 390 20,760 545 26,700 730 31,620 875 38,820 1,200 1,550 2.100 2,250 45,450 52,320 61,470 69,000 Load on Alloy Steel Stud Bolts under Torque Nominal Diameter or Bolt \\ (inches) - Number-*. Oiameter. / ef - / ;( -- at Root ef* - Threads ^ Thread ~ y ii-;.ferJ**ch.T.-'- (Inches) X 20 .185 18 .240 3/ 16 .294 % 14 .345 X 13 ,400 x 12 .454 X 11 .507 X 10 .620 X 9 .731 1 8 .838 IX 8 .963 IX 8 1.088 IX 8 1.213 IX 8 1.338 IX 8 1.463 IX 6 1.588 IX 8 1.713 2 8 1.838 2X 8 2 088 2X 8 2.338 2 X 8 2.588 3 8 2.838 . '. Area .at Root of * - Thread ` *. . (sq. inch): ' - .027 .045 .068 .093 .126 .162 .202 .302 .419 .551 .728 .929 1.155 1.405 1 680 1.980 2.304 2.652 3.423 4.292 5 259 6 324 ;/u'. - STRESS. v 3D,000 psi v . . -43,000 psi - :r. .^.-Torque - . Compres- : >. Torque'. >: - I- Compres- - ; .* v *ton (lbs.) !.: :'.v (ft-lbs.);-' vf? ' sion (lbs.) v 4 810 6 1,215 8 1,350 12 2,025 12 2,040 18 3,060 20 2,790 30 4,185 30 3,780 45 5,670 ; .. 60,000psi Torque - - . Compres*(ft-lbs.) TiV sion (lbs.) - 8 1,620 16 2,700 24 4,080 40 5,580 60 7,560 45 4,860 68 7,290 90 9,720 60 6,050 90 9,090 120 12,120 100 9,050 150 13,590 200 18,120 160 12,570 240 18,855 320 25.140 245 16,530 368 24,795 490 33,060 355 21,640 533 32,760 710 43,680 500 27,870 75D 41,805 1,000 55,740 680 34,650 1,020 51,975 1,360 69,300 800 42,150 1,200 63,225 1,600 84,300 1,100 1,500 2,000 2,200 50,400 59,400 69,120 79,560 1,650 2,250 3,000 3,300 75,600 89,100 103,680 119,340 2,200 3,000 4,000 4,400 100,800 118,800 138,240 159,120 3,180 4,400 5,920 7.720 102,690 128,760 157,770 189,720 4,770 6,600 8,880 11,580 154,035 193,140 236,655 284,580 6,360 8,800 11,840 15,440 205,380 257,520 315,540 379,440 10 ST0408978 Waviness is seldom a problem under normal con ditions. Then: are two areas, however, whirl must bo watched, since; excessive waviness is very difficult to handle. The fiist area is in glass-lined equipment the natural flow of the fused glass creates exi . waviness. Often the answer here is to use shims or wedges, carefully shaped and inserted in the hol lows. The; second area of concern is warped flanges. If warpage is caused by heat or internal stresses, remachining is generally sufficient. However, warpage due to excessive bolt loads or, conversely, too light a flange design, results in what is generally called bow ing. See Figure 1. The solution is to redesign for greater flange rigidi ty. Sometimes pieces can be added between the bolts to beef up the design without having to replace the parts. Another step would be to add more bolts. When this is done, usually smaller diameters are possible, thus adding more spring-back and a much better joint. TABLE 3 Recommended Seating Stresses Casket Material *y value (pst) Compressed asbestos, y%" thick................. Compressed asbestos, XT' thick................. Compressed asbestos, thick................. Woven asbestos, rubber filled, 3-ply .... Woven asbestos, rubber filled, 2-ply ... Woven asbestos, rubber filled, 1-ply .... ber, less than 75 Shore durometer ... jber, 75 or higher Shore durometer ... Rubber wild cotton insert .......................... Cork composition............................................ Cork and rubber.............................................. Solid TFE. '/" thick....................................... Solid TFE, %j" thick....................................... Solid TFE, thick....................................... Solid TFE, X," thick....................................... GVlON, yt" thick........................................... CTLON, X," thick............................................ CTLON, X," thick............................................ 1600 3700 6500 2200 2900 3700 0 200 400 450 200 1600 2000 3700 6500 2300 2BOO 3200 "id" factor 2.00 2.75 3.50 2.25 2.50 2.75 0.50 1.00 1.25 1.25 1.00 2.00 2.50 2.75 3.50 1.50 1.75 2.00 TABLE 4 Effective Gasket Width--b Facing Limits N N frl um jr i rj n r nTfjj)iT tr rni m T K- Luitirri 97nitj\n^mP^mirjtrrr7 tit/y////////////ruttrtifi rnmy/nuifnintnirTT Gasket Sealing Width b t.-a 2 W-i-T,(W+N D0 =---------- '------------- maximum) 24 b.= TM 16 'mrrrffiurmwn n trrn H------N--H b _ 3N 8 _ -effective gasket seating width in inches (see Table 3) NOTE: b - b. when b, is equal to or less than Vi" b = Z* when b,, is greaterthan Vi" 2 2b - effective gasket pressure width in inches m = gasket lactor (see Table 3) y = gasket seating toad in psi (see Table 3) i1 Designing the Gasket Practic- .l application of theory The gasket material js chosen for its chemical and physical ability to withstand temperatures, pressures, fluids, and perhaps to meet other criteria. Now comes the task of actually sealing the joint. A design engineer can generally control flange width, thickness, finish, the bolt load, size and spacing to suit the gasket mate rial. However, many times the joint is designed ac cording to some previous typical practice which may not give the desired joint performance. The necessary practical considerations for good design, including consideration of loads, thickness, bolt location, con tour and configuration, are as follows: Gasket factors--the "y" value In order to effect a tight seal, the gasket material must . be loaded sufficiently to flow into the imperfections of the contact faces, filling all voids between mating flanges. If this is not accomplished, a change in de sign, contour, area, thickness or possibly even in ma terial or type is necessary. The amount of load to cause this flow or yielding of the material is called the "y" value. The actual value has been established by the American Society of Mech anical Engineers (ASME] and is expressed in psi. The ASME Unfired Pressure Vessel Code, Section VIII. con tains a detailed list of various materials.Table 3 covers the most common and typical materials. It will be noted that there is a considerable spread from soft materials to hard. In a given joint design, the available bolt load in psi on the effective area of the gasket may be found by the following equation, the force actually available to satisfy the "y" requirement: , Wni; y --3.14 bG Where y`=psi available for "y" and which should be equal to or greater than "y". Table 3. Wm2=gross bolt load; number of bolts times the load in each. See Table 5. G=outside diameter of gasket less 2b b = see Table 4. 0) b L t>8 0 h a i ST0408979 Gaskel factors--the "m" value The "y" value gnores the fluid pressi i which-since it relieves soint; of the bolt load from the gasket, and is the force trying to create leakage-must be recog nized. The ASME has established multiplier values {"m" values) which define how many times the resid ual load, that is, the original load less the fluid relief or "Hydrostatic End Force," must exceed the fluid load in psi. See Figure 2. The available value for "m" can be obtained from the following equation. Wm,-0.785 G'P m~ 6.28 GPb where in' ^available multiplying factor, it must be equal to or greater than "m" as defined by ASME, Table 3. Wml =gross bolt load available P = f!uid pressure in psi GPb = os under y' Failure to meet either the "y" or "m" value necessi tates modification of the gasket. One of the easier steps is to increase the gasket thickness, as this will lower the requirements. See Table 3. However, the thinner the gasket, the more efficient it is; so rather than penalize the application by using a thicker gas ket, we can consider reducing its area, thus raising the unit load (the psi) on the gasket. In simple ring gaskets, an increase in the ID or decrease in the OD may well suffice. In odd shapes a contoured gasket may result, such as in Figure 3. These considerations are most important, but by no means all-inclusive. Where one can assist in a joint design, it is well to remember to keep all of the gasket possible within the bolting perimeter. See Figure 4. Generally, in an existing design which may not have followed this rule (see A & B, Figure 5), the best an swer is contouring, such as thinning the width at A & B Figure 3. Other very worthwhile points relative to the actual manufacture of the gasket are shown in Table 6. Ob servance of these will help to create the most econom ical product for both manufacture and installation FIGURE 2 FIGURE 3 Contouring of flange to help overcome bowing (see Figure 3) or poor bolt location (see Figure 5) FIGURE 4 FIGURE 5 ST0h08980 12 ST0408980 ST040898I TABLE 6 Common Faults in Gasket Design and Suggested Remedies 13 ST0408981 Installation A few simple precautionary measures must be ob served in installation to insure the most satisfactory oint. 1. Center the gasket on the flange. This is extremely viial where raised faces are involved. 2. Be sure surface finish and flatness are satisfactory. If found otherwise, correct by remachining or shim ming as on glass-faced flanges. 3. Tighten bolts to compress gasket uniformly. This means going from side to side around the joint. See Figure 6. 4. Use a torque wrench and well-lubricated fasteners to insure correct initial loading. 5. Retorque 12 to 24 hours after coming on stream, wherever possible. The joint should stand as long as possible before retorquing. Correct Bolting Patterns FIGURE 6 o> CD jr o CO vO <39 rs Garlock gasketing products GASKETING PRODUCTS DIVISION PALMYRA. NEW YORK 14S22 INTERNA riONAI DIVISION. PALMYRA. N.Y. orGARLOCK CANADA LTD.. TORONTO. ONT. 2RB-3 Additional product, as well as price and delivery, in formation on Garlock gasketing materials can be ob tained from the Garlock Gasket Fabricator or Distributor serving your area, or by getting in touch with Garlock Inc, Palnyra, New York 14522 Printed tri U.5.A. RPP-2SM'P*jv. 1/77 14 ST0408982 ENGINEERING SPECIFICATION Texas Division 48-850 . 3-15-77 Page 1 of 7 GASKETS ITEM NO G-l G-- 2 G-- 2 A G-2AF G-3 4 G--5 G-- 5A G-6 G-7 G-7A G-7AF DESCRIPTION STD FLAT RING GASKET, 1/16 INCH THICK ASBESTOS, GOODYEAR ITE STYLE 104 OR NICOLET 295* (NOTE- MINUS 200 TO + 750F.> STD FLAT RING GASKET, 1/16 INCH THICK BLACK RUBBER, GARLOCK 353, J M-114, STERLING 4010, OR HERCULES 504 . (NOTE- MINUS 40 TO + 300F . ) STD FLAT RING GASKET, 1/B INCH THICK SLACK RUBBER, GARLOCK 353, JM-114, STERLING 4010, OR HERCULES 504. (NOTE- MINUS 40 TO + 3 0 OF J FULL FACE GASKET, 1/8 INCH THICK BLACK RUBBER, JM-114, STERLING 4010, OR HERCULES 504. (NOTE3 0 OF ) GARLOCK 353, MINUS 40 TO STD FLAT RING GASKET, 1/16 INCH THICK CLOTH REINFORCED BLACK RUBBER. GGODRICH 60, STERLING 4200 OR HERCULES 509. (NOTEMINUS 40 TO +350F.) STD FLAT RING GASKET, 1/16 INCH THICK ASBESTOS, GARLOCK 900, (NOTE- MINUS 200 TO +700F.) STD FLAT RING GASKET, 1/8 INCH THICK ASBESTOS, GARLOCK 900. (NOTE- MINUS 200 TO +700F.) CORRUGATED GASKET, 1/32 INCH THICK MONEL. JM-900 OR STERLING C. (NOTE- MINUS 325 TO +1500F.) CORRUGATED GASKET, 1/32 INCH THICK TYPE 347 STAINLESS STEEL. JM-900 OR STERLING C. (NOTE- FOR HIGH TEMP SERVICE TO +1600F.) CORRUGATED GA5KET, 1/32 INCH THICK SOFT IRON, JM-900 OR STERLING C. (NOTE- MINUS 50 TO +IOOOF.) STD FLAT RING GASKET. 1/16 INCH THICK RUBBER, U S RUBBER COMPANY RAINBOW, STERLING 4000, OR AMERAFLEX 1420. (NOTE- MINUS 40 TO M80F.) STD FLAT RING GASKET, 1/8 INCH THICK RUBBER, U S RUBBER COMPANY RAINBOW, STERLING 4000, OR AMERAFLEX 1420. (NOTE- MINUS 40 TO +180F.) FULL FACE GASKET, RAINBOW. STERLING +.180F . ) 1/6 INCH 4000, OR THICK RUBBER. U AMERAFLEX 1420. S RUBBER COMPANY (NOTE- MINUS 40 TO 0 1 > ST0408983 ST0408983 <18680*10X 5 ENGINEERING SPECIFICATION Texas Division 48-850 (D 3-15-77 Page 2 of 7 GASKETS ITEM NO G-7AR G-7AS G-- 8 G-9 G-9A G-9e (D DESCRIPTION FULL-FACE 1/8 INCH THICK RUBBER GASKET, 10 CF GASKET TO BE EQUAL TO ID OF RUBEER LINED PIPE. U S RUBBER COMPANY RAINBOW. STERLING 4000 , OR AMERAFlEX 1420. (NOTE- MINUS 40 TO <-l80F.) STD FLAT RING 1/8 INCH THICK RUBBER GASKET, ID OF GASKET TO BE EQUAL TO ID OF PLA ST IC . LI NED PIPE, U S RUB3ER COMPANY RAINBOW, STERLING 4000, OR AMERAFLEX 1420. (NOTE- MINUS 40 TO <-l 9QF . ) CORRUGATED STEEL JACKETED ASBESTOS GASKET. JM-926 OR STERLING DC. (NOTE- MINUS 50 TD <-900F.l STD FLAT RING GASKET, 1/16 INCH THICK ASBESTOS WITH SILICON RELEASING AGENT, JM-60. GARlOCK 7021 OR NtCOLET 225 OR 245. { NOTE-(MINUS '200 TO <-750F.) STD FLAT RING GASKET, 1/3 INCH THICK ASBESTOS WITH SILICON RELEASING AGENT, JM-60, GARLOCK 7021 OR NICOLET 225 OR 245. (NOTE- MINUS 200 TO <-750F.) FULL FACE GASKET, 1/3 INCH THICK ASBESTOS WITH SILICONE RELEASING AGENT, JM-60. GARLOCK 7021 OR NICOLET 225 OR 245. (NOTE- MINUS 200 TO <-750F.) G- 1 0 G-ll G-12 G-13 G-14 G-15 SOLID SOFT IRON RING JOINT GASKET FCP 600-LB RTJ FLANGE. ANSI B16.5. 8RI NELL HARCNESS 80-90. (NOTE- MINUS 20 TO +T50F,J SOLID SOFT IRON RING JOINT GASKET FOR 900-L3 RTJ FLANGE. ANSI 016.5. 9RI NELL HARDNESS 80-90. (NOTE- MINUS 20 TO +750F.) SOLID SOFT IRON RING JOINT GASKET FOR 15O0-LB RTJ FLANGE, ANSI B16.5, BRINELL HAR0NES5 80-90. (NOTE- MINUS 20 TO +750F.I SOLID SOFT IRON RING JOINT GASKET FOR 300-LB RTJ FLANGE, ANSI 516.5, BRINELL HARDNESS 80-90. (NOTE- MINUS 20 TO -750F.) KOROSEAL, GOODRICH 116 OR STERLING 9900 SHEET GASKET, 1/9 INCH THICK. (NOTE- MINUS 20 TO 4-1 50F . > SPIPAL-WOUND. NICKSL-ASBcSTCS GASKET, JM-912 OR STERLING WL. (NOTE- MINUS 325 TO 4-900F.) SPIRAL-WOUND. NICKEL-TEFLON GASKET, JM-912 OR STERLING WL. (NOTE- MINUS 325 TO <-450F.) ST0408984 ENGINEERING SPECIFICATION Texas Division 48-850 /gv 3.35-77 Page 3 of 7 I7EM NO G-15B G- 1 6 G-16A G-17 G-17A G--17 A3 'G--173 G- 1 7 C G-16 G-13A G-X9 G-19A G-1SB gasket s 8 0 *1 0 1 $ DESCRIPTION q SPIRAL-WOUND, NICKEL WITH TEFLON IMPREGNATED BLUE ASBESTOS Q FILLER, J M--91 2 OR STERLING WL. (NOTE- MINUS 325 TO -500F.I Qq SPIRAL-WOUND, STAINLESS STEEL-ASBESTQS GASKET, JM-912 OR STERLING WL (NOTE- MINUS 425 TO *900F.) so CD C/J SPIRAL-WOUND, STAINLESS STEEL-TEFLON GASKET. JM-912 OR STERLING WL. (NOTE- MINUS 425 TO +450F.) 4000-L8 LENS RING IN ACCORD WITH TEXAS DIVISION STD 43-527, (NOTE- SI2ES 1/2 THRU 4, MINUS 20 TO 4-900F . ) 4000-L3 LENS RING IN ACCORD WITH DOW ENGINERING STANDARD 43-527 (NOTE- SIZES 1/2 THRU 4, MINUS 20 TO H900F.) 5300-L3 BLIND SPECIFICATION + 900F . ) LENS RING IN ACCORD WITH 43-533. (NOTE- SIZES 1/2 DOW ENGINEERING THRU 6, MINUS 20 TO 5300-LB BLIND LENS RING IN ACCORD WITH TEXAS DIVISION STD 43-533. (NOTE- SIZES 1/2 THRU 6, MINUS 20 TO F900F.) 5300-LB LENS RING IN ACCORD WITH TEXAS DIVISION STD 43-530. (NOTE- SIZES 1/2 THRU 6, MINUS 20 TO F900F.) STD FLAT RING GASKET, 1/8 INCH THICK ETHYLENE ROPYLENE RUBBER. PLASTIC LINED PIPE DEPARTMENT, DOW CHEMICAL COMPANY, FOR USE WITH DOW PLASTIC LINED STEEL PIPE. (NOTE- MINUS 60 TO F250F.) STD FLAT RING GASKET, 1/8 INCH THICK VITON, PLASTIC LINED PIPE DEPARTMENT. DOW CHEMICAL COMPANY, FOR USE WITH DOW PLASTIC LINED STEEL PIPE. (NOTE- MINUS 50 TO + 250F.) ETHYLENE PROPYLENE RUBBER HALF GASKET, PLASTIC LINED PIPE DEPARTMENT, DOW CHEMICAL COMPANY, FOR USE WITH DOW PLASTIC LINED STEEL PIPE, (NOTE- MINUS 60 TO F250F.) VITON HALF GASKET, PLASTIC LINED PIPE DEPARTMENT, DOW CHEMICAL COMPANY, FOR USE WITH DOW PLASTIC LINED STEEL PIPE. (NOTEMINUS 50 TO F250F. ) HYPALON HALF GASKET, PLASTIC LINED PIPE DEPARTMENT, DOW CHEMICAL COMPANY, FOR USE WITH DOW PLASTIC LINED STEEL PIPE. (NOTE- MINUS 30 TO +250F.) ST0408985 9 8 6 8 0 *i0 ls EENNGGINEERINGC SPECIFICATION TTeexxaass DDiivviissiioonn 48-850 ^ 3-15-77 W Page of ? ITEM NO G-- 2 0 G-- 21 G-22 G--22 A G-22AS G-- 24 G--24 A G-- 25 G-- 26 G-- 26 A G-26AF G--27 GASKETS DESCRIPTION SOLID TYPE 304 STAINLESS STEEL RING JOINT GASKET FOR RTJ FLANGE. ANSI E16.S. BRTNELL HARDNESS 160. 0.04 TO 0.08 PER CENT CARBON. (NOTE- MINUS 425 TO +1500F.) SCLID TYPE 316 STAINLESS STEEL RING JOINT GASKET FOR RT J FLANGE. ANSI B16.5, BRI NELL HARDNESS 160. 0.04 TO 0.03 PER CENT CARBON. (NOTE- MINUS 425 TO M500F.) STD FLAT RING GASKET. 1/16 INCH THICK COMPRESSED 3LUE ASBESTOS SHEET, JM-84, GARLDCK 7705. JOHN CRANE 2112. STERLING 4150 OR AMERAFLEX 1516. (NOTE- MINUS 200 TO +750F.) STD FLAT RING GASKET. 1/e INCH THICK COMPRESSED BLUE ASBESTOS SHEET, JM-84, GARLOCK 7705. JOHN CRANE 2112. STERLING 4160 OR AMERAFLEX 1515. (NOTE- MINUS 200 TO +750F.) STD FLAT RING GASKET, 1/8 INCH THICK COMPRESSED BLUE ASBESTOS. ID OF GASKET TO BE EQUAL TO ID OF PIPE, JM-34, GARLOCK 7705, JOHN CRANE 2112, STERLING 4160, OR AMERAFLEX 1516. (NOTE- MINUS 200 TO F75OF. ) SPIRAL-WOUND, 315 STAINLESS STEEL-ASBESTOS GASKET, FLEXITALLIC CG. GARLOCK CR, LAMONS WR , JM-913 OR STERLING GR. (NOTE- MINUS 425 TO H100F.I SPIRAL-WOUND. 315 STAINLESS STEEL-TEFLON GASKET, FLEXITALLIC CG, GARLOCK CR, LAMONS WR , JM-913 OR STERLING GR. (NOTE- MINUS 50 TO +450F.) LEAD RING GASKET FLANGE, STERLING +200F.) FOR ANSI 816.5. SMALL PM OR AMERAFLEX LEAD. TONGUE (NOTE- AND GROOVE MINUS 200 TO STD FLAT RING GASKET 1/16 INCH THICK NEOPRENE, GARLOCK 7936, STERLING 4050 OR HERCULES 517. (NOTE- MINUS 50 TO 4-250F.) STD FLAT RING GASKET 1/8 INCH THICK NEOPRENE, GARLOCK 7936, STERLING 4050 OR HERCULES 517. (NOTE- MINUS 50 TO *2S0F.> FULL FACE GASKET, 1/3 INCH THICK NEOPRENE. GARLOCK 7936, STERLING 4050 OR HERCULES 517. (NOTE- MINUS 50 TO (-250F.) SOLID SOFT IRON RING JOINT GASKET FOR 2500-LB RTJ FLANGE, ANSI B16.5, BRINELL HARDNESS 30-90. (NOTE- MINUS 20 TO F750F.) ST0408986 ENGINEERING SPECIFICATION Texas Division GASKETS 48-850 (G) 3-15-77 Page 5 of 7 ITEM NO G-- 26 G-28R G-- 29 G-29A G-- 30 j- 31 G-- 33 G-33L G-- 34 G-34A G-- 3 5 G-35A G-36 G-- 36 A DESCRIPTION TEFLON ENVELOPE STYLE GASKET. 3/16 INCH THICK FILLER, JM--933--C--9360, GARLOCK 8764. OR STERLING S 35--V l NOTE- MINUS 325 TO + 450F. ) TEFLON ENVELOPE STYLE GASKET. 1/3 INCH NEOPRENE FILLEO, PEABODY DORE E--26 OR STERLING 885-V/4050. (NOTE- MINUS 50 TO *200".) STD FLAT RING GASKET, 9563, STERLING 770 OR *"4 0OF * ) 1/16 INCH AMERAFLEX THICK 1444, VITON RUBBER, GARLOCK (NOTE- MINUS 50 TO STD FLAT RING GASKET, 9663, STERLING 770 OR +400F.) 1/6 INCH THICK VITON RUBBER, AMERAFLEX 1444. (NOTE- MINUS GARLOCK 50 TO TEFLON HALF GASKET, PLASTIC LINED PIPE DEPARTMENT, DOW CHEMICAL COMPANY, FOR USE WITH DOW PLASTIC LINED STEEL PIPE. (NOTEMINUS 20 TO + 25OF. ) SOLID SOFT ANNEALEC INCONEL RING JOINT GASKET FOR RTJ FLANGE. ANSI B16.5. (NOTE- MINUS 325 TO +1200F.) SOLID SOFT ANNEALED NICKEL RING JOINT GASKET FOR RTJ FLANGE, ANSI B16.5. (NOTE- MINUS 325 TO +600F.) SOLID SOFT ANNEALED LOW CAR50N NICKEL RING JOINT GASKET FOR RTJ FLANGE, ANSI 816.5. (NOTE- MINUS 325 TO 4I200F.) SPIRAL-WOUND. MONEL-ASBESTOS GASKET, FLEXITALLIC CG. GARLOCK CR, LAMONS WR, JM-913 OR STERLING GR. (NOTE- MINUS 325 TO +800F.) SPIRAL-WOUND, MONEL-TEFLON GASKET, FLEXITALLIC CG, GARLOCK CR, LAMONS WR, JM-913 OR STERLING GR. (NOTE- MINUS 325 TO +450F.) SPIRAL-WOUND. NICKEL-ASBESTOS GASKET, CR. LAMONS WR, JM-913 OR STERLING GR. +900F.) FLEXITALLIC CG, GARLOCK (NOTE- MINUS 325 TO SPIRAL-WOUNO, NICKEL-TEFLON GASKET. FLEXITALLIC CG, GARLOCK CR. LAMONS WR, JM-913 OR STERLING GR. (NOTE- MINUS 325 TO F4S0F.) STD FLAT RING GASKET, 1/16 INCH THICK WHITE ASBESTOS, JM 61 OR N1COLET 226. (NOTE- MINUS 200 TO +700F.) STD FLAT RING GASKET, 1/3 INCH THICK WHITE ASBESTOS. JM 61 OR NICOLET 226. (NOTE- MINUS 200 TO *700F.I $70408987 ST0408987 88680101S *<s>* ENGINEERING SPECIFICATION Tienxva->sr nD-Tiwv-fisr- i-fonnn --' GASKETS ~ ^\^y ^ ^ ^ ^ ^ Page 6 of 7 ITEM NO G- 37 G- 38 G-- 39 G-39A G-4 0 G-40A G-40AC G-40C G-41 G-- 41 A G-- 42 G-- 43 G-- 44 DESCRIPTION SPIRAL-WOUND, INCONEL-CERAMIC (FIBERFRAX) GASKET, LAMONS WR. (NOTE- FOR HIGH TEMP SERVICE TO +2000F.) STANDARO FLAT RING GASKET, 0.015 INCH THICK GRAFOIL GTA. UNION CARBIDE CORP. (NOTE- MINUS 200 TO +750F.) STD FLAT RING GASKET, 1/16 INCH THICK GYLON, GARLOCK 35404. (NOTE- MINUS 200 TO F500F, SIZES 3/4 THRU 16.) STD FLAT RING GASKET, 1/8 INCH THICK GYLON, GARLOCK 35404. (NOTE- MINUS 200 TO F500F, SIZES 3/4 THRU 16.) SPIRAL-WCUND. 304 STAINLESS STEEL-ASBESTOS GASKET, FLEXITALLIC CG, GARLOCK CR. LAMONS WR. JM-913 CR STERLING GR. (NCTE-- MINUS 425 TO 4-1I00F.) SPIRAL-WOUND, 304 STAINLESS STEEL TEFLON GASKET, FLEXITALLIC CG, GARLOCK CR, LAMONS WR, JM-913 OR STERLING GP. (NOTE- MINUS 425 TO F450F. > SPIRAL-WOUND, 304 STAINLESS STEEL TEFLON GASKET WITH STAINLESS STEEL GAGE RING, FLEXITALLIC CG, GARLOCK CR. LAMONS WR. JM-913 OR STERLING GR. (NOTE- MINUS 425 TO F 450F.) SPIRAL-WCUND, 304 STAINLESS STEEL-ASBESTOS GASKET WITH STAINLESS STEEL GAGE RING, FLEXITALLIC CG, GARLOCK CP, LAMONS WR. JM-913 OR STERLING GR. (NOTE- MINUS 425 TO H100F.I standard flat Ring gasket 1/16 GARLOCK 7228. JM-76 OR NICOLET MINUS 150 TO +300F.) inch 355. thick neoprene-asbestos, (NOTE- FOR FREON SERVICE. STANDARO FLAT RING GASKET 1/8 INCH THICK NEOPRENE-ASBESTOS, GARLOCK 7228. JM-76 OR NICOLET 355. (NOTE- FOR FREON SERVICE, MINUS 150 TO F300F.) FULL FACE GASKET. 1/8 INCH THICK ETHYLENE PROPYLENE RUBBER. (NOTE- minus 60 TO F250F.) FULL FACE GASKET, 1/8 INCH THICK VITON RUBBER. LITHARGIC CURED. 60 DUROMETER OR LESS HARDNESS. MOSITES 1035 CURED. SPIRAL-WCUND 304 STAINLESS STEEL-ASBESTOS GASKET WITH STAINLESS STEEL INNER AND OUTER COMPRESSION-GAUGE PINGS, ID SAME AS SCH 5S PIPE, FLEXITALLIC CGI, GARLOCK CPI, LAMONS WR I , JM-913-IP OR STERLING GR-IR. ( ( ST0408988 EENNiGINEERING SPECIFICATION Texas Division 48-850 (f) 3-15-77 Page 7 of 7 I TEM NO G~ 44 A G-45 G-45A G-4fc G--4 7 gaskets DESCRIPTION SPIRAL-WOUND 304 STAINLESS STEEL-TEFLON GASKET WITH STAINLESS STEEL INNER AND OUTER COMPRESSION-GAUGE RINGS, ID SAME AS SCH 5S PIPE. FLEXITALLIC CGI. GARLOCK CRI, LAMONS WRI, JM-913-IR OR STERLING GR-IR. STD FLAT RING GASKET, 1/16 INCH THICK TEFLON CTFE), GAPLOCK OR RESISTOFLEX. (NOTE- MINUS 50 TO +500F.) STD FLAT RING GASKET, 1/8 INCH THICK TEFLON (TFE), GARLOCK OR RESISTOFLEX. (NOTE- MINUS 50 TO +500F.) SPIRAL-WOUND. INCONEL-GRAFOIL GASKET. FLEXITALLIC CG. OR LAMONS WR. (NOTE- FOP HIGH TEMP SERVICE TO +2000F.> NEOPRENE GASKET AS FURNISHED BY VENDOR FOR CONCRETE CYLINDER PIPE. 68680*10IS ST0408989 ENGINEERING SPECIFICATION Texus Division 48-807 Revised 11-26-71 BOLT LUr'PITANT ITEM NO DESCRIPTION 61. - 1 A. ARM I TE LFD-PLATE 250. (NOTE- MINUS 35C TO +20r0F. DO NOT USE ON STAINLESS STEEL ABOVE 50 OF ) RL - 1 T JOHN CRANE THREQ-GARO. (NOTE. MAX TEMP 1200F. DO NOT USE DN STAINLESS STFEL ABOVE 50 OF.) BL-? FEL PRO C-5A. (NOTE- MINUS 50 TO +1R0CF.) BL-3 TEXACO 2303 THREADTEX. (NOTE- MAX TFMP +300F.) BL-A 8L-E FFL RO C-IOO (NOTE- MINUS 65 TO +2000F.) JFT-LUBC SS- 30 COPPER ANTI-SEIZF COMPOUND. (NOTE- MAX TEMP 1BOOF. ) BL -6 MOLVKOTE RF2-S GREASE. (NCTE- MINUS IB TO +3CCF.) 0 6 6 e o * io is ST0408990 - ENGINEERING SPECIFICATION Texas Division 48-855 11-15-76 Page 1 of 2 JOINT COMPOUND ITEM NO JC-1 JC --2 JC-3 JC--4 NOTE JC--5 JC--6 JC--7 1C--8 JC--9 JC-9A JC-10 JC--12 JC-X 3 JC--14 JC--15 JC--16 DESCRIPTION PERMATEX 2. (NOTE- MINUS 65 TO +400F.) PERMATEX 3. {NOTE- MINUS 65 TO +400F.) CRANE HIGH TEMP ANTISEIZE THREAD COMPOUND OR JOHN CRANE THRED-GARD. (NOTE- MINUS 20 TO +1050F.) GRINNELL SPRINKLER COMPOUND. (NOTE-MINUS 50 TO +500F.I (REVISED) PERMATEX I. (NOTE- MINUS 65 TO +400F.) KEY GRAPHITE PASTE. (NOTE- MINUS 30 TO.+750F.) DELETED CRANE THREAD LUBRICANT. (NOTE- MINUS 20 TO +-500F.) COPALTITE SEALING COMPOUND, CEMENT FORM. (NOTE- MINUS 20 TO +500F.) COPALTITE SEALING COMPOUND, LIQUID FORM. (NOTE- MINUS 20 TO +500F.1 QUICK SEAL. ZOPHR MILLS INC. (NOTE- MINUS 20 TO +300F.) KEY TITE WATERPROOF PIPE JOINT COMPOUND. WKM VALVE DIV. (NOTE- MINUS 50 TO +450F.) WHIZ ANTISEIZE COMPOUND FOR ALUMINUM THREADED JOINTS, R M HOLLINGSHEAO CORP. (NOTE- MINUS 50 TO +400F.) BLUE-GOOP COMPOUND FOR STAINLESS THREADED JOINTS. CRAWFORD FITTINGS COMPANY. (NOTE- MINUS 50 TO +400F.) TEFLON TAPE 1/2 INCH BY 3 MIL THICKNESS. (NOTE- MINUS- 250 TC +500F.) ZRC ZINC RICH COATTNG. USE AS THREAD COMPOUND AND ALSO AS PROTECTIVE COATING ON EXPOSED THREADS AFTER MAKE-UP. (NOTE- MINUS 20 TO +300F.) ST040899I ST0408991 ENGINEERING SPECIFICATION Texas Division 48-855 @11-15-76 Page 2 of 2 JOINT COMPOUND ITEM NO JC-17 JC-19 JC-20 JC-20A JC-21 JC-22 JC-23 JC-2-- JC-25A JC-25B JC-26 JC-27 JC-28 NOTE JC-29 DESCRIPTION FLUROLUBE LG-160, USE AS COATING ON SPIRAL WOUND GASKETS, HOOKER ELECTROCHEMICAL COMPANY. I NOTE- DRY GAS SERVICE MINUS 300 TO *500F.) LTQUID-O-RING LUBON 404 OR SLICK SEAL NO A THREAD SEAL. (NOTEMINUS 250 TO +600F.) JOINT COMPOUND AS RECOMMENDED BY PIPE OR FITTING MANUFACTURER. JOINT ADHESIVE AS RECOMMENDED BY PIPE OR FITTING MANUFACTURER. FEL PRO C5-A. (NOTE- MINUS 50 TO + 1300F.) FEL PRO C-100. I NO TE-- MINUS 65 TO +2000F.) JET-LUBE SS-30 COPPER ANTI-SEIZECOMPOUND. (NOTE- MAX TEMP -HB00F.) ( UNION CARBIDE GRAF0IL PLAIN ADHESIVE SEALANT TAPE, .005 INCH THICK. (NOTE- MINUS 200 TO <-2000F.) SOLDERS MELTING AT OR ABOVE 1100F. (NOTE- MINUS 200 TO 4-350F, PRESSURE-TEMPERATURE PER ANSI 816-22, APPENDIX A, TABLE l.) 95-5- TIN-ANTIMONY SOLDER. (NOTE- ZERO TO *-250F, PRESSURETEMPERATURE PER ANSI 316.22, APPENDIX A, TABLE l.) TFE THREAD PASTE MFG BY CONLEY CORP., 91ST ST AND DELAWARE ST, TULSA, OKLAHOMA. GRINNEL PIPE JOINT COMPOUND OR PERMATEX 2. LOCTITE 9231. (NOTE-MINUS 65F TO +300F) (REVISED! LEAK LOCK, HIGHSIOE CHEMICALS INCORPORATED. CLIFTON, NEW JERSEY. (NOTE- MINUS 100 TO 4-400F.! 2668010 is ST0408992