Document 61ERyy75EN8KD57zrEKK8vKg

CHAPTER 13 J*} sky radiation and from outdoor-indoor temperature differential for glass areas and| ethxetetryiopre, owfasiltsruacntdurreo;of(s2,) mlooaddifideudebtyo pheeraiot dgiacinhethartofulogwh oinr tleargiofar cptaorrtsitidoenpse,ncdeinilginogns;^! and floors; (3) load due to ventilation, either natural or mechanical; (4) load duefr to heat sources within the conditioned space such as people, lights, power equipment,^ and appliances; (5) load due to moisture transfer through permeable building}? materials; (6) miscellaneous heat sources. C. Determination of Air Quantity and Apparatus Dew-Point. These factors will be discussed in turn. The material presented leads?;; to an illustrative procedure for a cooling-load calculation, and a numerical!? example isgiven to demonstrate the calculations involved. J DESIGN CONDITIONS i Indoor Conditions T Indoor air conditions for human health and comfort have been and con-;! tinue to be the subject of much discussion and research. ..J The effective temperature index, explained in Chapter 6 is probably; the best available source of design criteria for comfort air conditioning; systems for buildings or enclosures in which the air and inside surfaced Table 1. Typical Commercial Design Room Conditions for Summer Average! Peak Load in Comfort Air Conditioning* ,-pj Type of Installation Dry-Bulb Temp Deluxe Application----------15 to 40 min Occupancy.---- 78 80 82 Wet-Bulb Temp** 65 67 68 Relative Humidity Per Cent 50 51 49 Grains Per Lb* 72.7 78.5 80.0 EFFECTIVE; Temp* !, 72.2 74.0 75.3 :;r a Values in Table 1 are for peak load conditions. It is general practice to operate a system at approxi mately.76 F and 50 percent relative humidity at other than peak load. J,-- i k Psychroroetric data for standard barometric pressure.. c Fig. 10, Chapter 6, air movement 15 to 25 fpm. ` temperatures remain substantially equal ; a condition that can safely bi assumed for most ordinary comfort air conditioning installations. Other; sources of design specifications are to be found in the requirements of code?, and ordinances, and in the varied long-term experiences of manufacturers;! contractors, and engineering specialists. -s^j Past experience, cumulative over many years, indicates that indoor del; sign conditions for which summer air-conditioning equipment is select^ should not exceed a temperature of 80 F or a relative humidity of 50 per cent for the average job in the United States. If these conditions ^ exceeded, complaints of discomfort may be expected, especially with continu^ ous occupancy. For very, brief occupancy only, a slightly higher pesjfl load design temperature may be employed. In regard to the lower lii&C of humidity, complaints are not encountered for store installations op# ated down to 35 percent relative humidity or, for office jobs, somewha! lower. These observations apply to normal commercial practice in tfcjfc country only; for extremes, such as tropical or very hot regions, it is regard^}*: as more practicable to design for a peak-load outdoor-indoor temperature? difference of about 15 to 20 F. Table 1 offers typical design conditions for average requirements egu countered. The deluxe figures would also apply in general for localit1? having a summer outdoor design temperature of 90 F or less; and'tPN 15 to 40 min occupancy values, or even somewhat higher dry-bulb tag Cooling Load 267 peratures, would indicate acceptable conditions for very hot localities. Table 1 is to be used with good judgment, for there is no universal rule which may be applied to indoor design conditions. Guarantees of conditions to be maintained for summer operation are based upon a definite set of load conditions. At other than the guarantee load, the conditions produced by a system are determined by the balance of imposed load and equipment capacity, and by the method adopted for regulating the system operation. Complete specifications of indoor design conditions would include part-load and overload operation, particularly from the viewpoint of economy. In the field of industrial air conditioning, indoor design conditions are established by the requirements of goods and processes, in addition to the comfort and efficiency of the workers. Many typical indoor design condi tions for products in industrial air conditioning are given in Chapter 45. The load calculations for either comfort or industrial air conditioning are usually made in accordance with a guarantee. In comfort applica tions, for example, this is frequently 80 F and 51 percent relative humidity or 78 F and 50 percent relative humidity. The system is normally operated at 75 or 76 F and approximately 50 percent relative humidity at all times as long as the equipment has capacity to maintain these conditions. Dur ing very hot weather, the room temperature will rise above the control point and the equipment will operate continuously. Normally, industrial jobs are operated at design conditions at all times if the optimum condi tions are selected for the benefit of the product. The indoor design conditions suggested have had reference to conditions to be maintained at the level of occupancy. For extremely high ceilings in public or industrial buildings, only the zone from 10 to 15 ft above the floor may be cooled to the full extent. The air temperature at the ceiling would be much higher, and this should be kept in mind when calculating the convective portion of the roof heat gain. A reduction of outdoor-toindoor air temperature differential may be assumed in such instances; radiation from the inner roof surface is not diminished. Outdoor Conditions Summer climatic conditions and suggested design wet-bulb and drybulb temperatures are given in Table 2 for various locations in the United States. The highest temperature ever recorded is for the period of record shown. In some cases it should be noted that this period of record is com paratively short, and higher temperatures may be expected. In making comparisons for other localities than those shown in Table 2, due considera tion must be given to elevation. Column 6 of Table 2 indicates the design dry-bulb temperature suggested P H?e. A.S.H.V.E. Technical Advisory Committee on Weather Design Conditions. This temperature is the maximum hourly outdoor tempera ture which has been equalled or exceeded 2-j percent of the total hours of tvfne' August and September for the period of record, in this case ue 5-year period 1935-1939, and should not be confused with the period record given in Column 4 which applies only to highest temperature Ver Recorded. Since all of these data (Column 4) are based on airport ^Ofds, they are not necessarily applicable to cities. Ch 6 'ven *n Columns 7 and 8 were obtained from local A.S.H.V.E. aPter Secretaries, and represent the design temperatures in local use. of tlf6 SUC^ *nfrmatin was nt available, it was taken from a publication ne A.C.R.M.A} and from various other sources.