Document zdpyjDQNXq4eqLJrnx9pqV0n6

American Society of Heating and Ventilating Engineers Guide, 1937 mounted together in a single unit and supported on a track on the car under-frame on pneumatic supports. Propane fuel sufficient for several days' operation is carried in three drums mounted in a rack under the car Freon is used as the refrigerant. The unit may be used with a direct expansion air conditioning unit or it can be used with a heat exchangerwith cold water cooling coils. The capacity required in the refrigerating system depends upon a number of factors such as size and type of construction of car, thickness and kind of insulation used, amount of heat produced within the car by motors, lights, and other appliances, amount of outside air, outside air temperature and humidity, intensity of solar radiation, number of pas sengers, and inside temperature desired. A check of a number of cars with ice-activated systems indicates an average ice consumption, day and night, of approximately 275 lb per hour. This means an average capacity of 3.3 tons of refrigeration. It has also been observed on test that in the sunshine with an outside dry-bulb temperature of 85 to 90 F and a wetbulb temperature of 73 to 75 F, a six-ton compressor unit operates ap proximately 50 per cent of the time. As the average temperature during the cooling season is below 90 F the observed performance of the six-ton compressor unit compares with the 3.3 tons average capacity determined for die ice systems. It was also observed on test that with temperatures above 90 F, high humidity, and in the sunshine, a six ton unit operates almost continuously. The sun load on a bright sunshiny day is about one ton. For average cars on sunshiny days, with high temperatures and humidity, from 65,000 to 80,000 Btu per hour will have to be removed from the interior of the car to maintain an inside effective temperature within the comfort zone. This means that a refrigerating capacity of from 5.5 to 7 tons will be required. CALCULATION OF CAR COOLING LOAD Due to the many variables involved the calculated heat gain will be more or less of an approximation, but if a careful study is made, results sufficiently accurate for all practical purposes may be obtained. The -following example illustrates a typical cooling load calculation. Example and Solution. ,* Type of car Roof area' Floor area Window area Net side wall area End area Arched-roof steel coach. 70.3 X 12.5 = 880 sqft. 70.3 X 9.8 = 687 sqft. 38 X 2.5 X 2 = 190 sqft. (2 X 7.5 X 70.3) - (190) = 865 sq ft. 2 X 7.5 X 9.8 = 147 sqft. Average roof section: in- steel sheet, 1 layer tar paper, 2 in. air space, H *n- hairfelt, in. rigid fiber board insulation. Average window section: two layers of Jfj in. glass with 1J^ in. air space between. ' Average floor section: 1 in. composition, He in- steel, H in. air space, 1 in. hairfelt, Vfs in. steel. :: Average side and end section: in. steel, Vi in. hairfelt, 3 in. air space, % in. wood. End area is taken as total area at body and bulkheads with no allowance made for ..glass as car is vestibuled and glass in body ends is not subjected to direct solar radiation. Outside dry-bulb temperature 'Outside wet-bulb temperature to 95 F( fo 75 F. Chapter 22--Railway Air Conditioning Outside effective temperature ET0 Outside relative humidity rh0 Inside dry-bulb temperature t Inside wet-bulb temperature t' Inside effective temperature ET Inside relative humidity rh Density of air at t d Moisture per pound of dry air at to and <'o Go Moisture per pound of dry air at t and t' G 83 F. 40 per cent. 80 F. 66.5 F. 73.5 F. 50 per cent. 0.07353. 99 grains. 77 grains. Moisture per pound of dry air to be removed M Go - G _ 99 - 77 = 0.00314 lb 7000 7000 Evaporator condensate temperature Latent heat of water at 53 F Specific heat of air Number of seated passengers Number of attendents Heat given off by each passenger Heat given off by attendent Outside air introduced 53 F. L 1060 Btu per pound. Cp = 0.241. Pa = 68. Pa = 1 = 400 Btu per hour. = 650 Btu per hour. Q = 500 cfm. Roof temperature in sun = 40 F above ambient. Wall temperature in sun -- 25 F above ambient. Sun 15 deg from Zenith. Solar heat = 4.75 Btu per minute per square foot. 30 per cent of heat passing through glass is reflected and reradiated, 70 per cent remaining. 80 per cent of heat at surface passes through glass. Then 4.75 X Sine 15 deg X 0.8 X 0.7 = 0.7 Btu per square foot per minute passes through glass. Evaporator motor = H hp. Evaporator motor efficiency = 65 per cent. The total heat gain will include the gains from leakage through roof, floor, side walls, end walls, windows, sensible and latent heats from outside air, heat from occupants, heat from evaporator fan motors and solar radiation'. Calculation of Transmission Coefficients. (See Chapter 5.) Roof coefficient = Z7r = Btu per hour per square foot per degree Fahrenheit. Outside air film fo = 6.00 1 If = 0.1660 Yi e in. steel k = 308 II H 0.0625 308 = 0.0002 2 in. air space a = 1.10 1 la = 0.9090 H in. hairfelt k = 0.25 X 0.5 T ~ 0.25 = 2.0000 % in. rigid fiber board insulation k = 0.33 X 0.125 T " 0.33 = 0.3800 Inside air film Si = 1.65 1// = 0.6080 Total = 4.0632 v r _ 1 4.0632 _ 0.246 Btu per. hour per square foot per Fahrenheit. Side and end wall coefficient = Us = Btu per hour per square foot per degree Fahrenheit. Outside air film in. steel Vi in. hairfelt 3 in. air space k = 308 . k = 0.25 . 0 =1.10 ` X 0.1875 T-" 308 X 0.5 ' - ~k ~ 0.25 i/a ; 4 ' '=O.lG&Cf = 0.0006 : '=. 2.00(j0i 0:9090 403