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Furthermore, it is desired that the water leaving the exchanger has the same temperature as the water entering. The last pulling point B must coincide with B . These requirements necessitate iterations n1 which must be continued until B. and B are equal or differ only in 1n temperaturebyaspecifiedamount(selectedtobe±0.15C). That B B., can be explained by the fact that the state of air flowing n1 through the wetted channel approaches gradually the saturation con dition and the negative diagram value q^ approaches zero and becomes then increasingly positive and condensation might occur within the channel. The temperature of the water must for the same reason have a maximum somewhere along the channel [10,11]. This is shown in Fig. 11 (see case 6 of Table l). 6. ResultsofComputationsandComparisonofPerformanceofDryand Wetted Condensers of Given Geometry The plate-fin-tube heat exchanger shown in Fig. 3 and of design specified in Fig. 1+ was selected for the performance analysis. The geometrical parameters of Fig. U were chosen to be of the following dimensions. ST = SL = 2.5^ x 10”2 [m] TF = 1.78 x 10“U [m] TT = 8.89 x icf^ [m] DO = 1.58 x 10~2 [m] (tubematerial: copper;finmaterial: aluminum) Other parameters were selected to be: Numbers of modules per elemental channel: n = 3 m -1 Number of fins per unit length of tube: FPM = 315 [m ] Velocity of the refrigerant R-12: v = 1 [m/s] K Condensing temperature: T^ = hO [C] Reynoldsnumberofwaterfilm: Re^=250 Coefficientofwetness: Kw=1 Ambient air temperature: = ^5 [C]. All other parameters were considered as variables: Relative humidity: = 50, 80, 90, 100 [%] Velocity of air: vA = 1 - 10 [m/s] Reynoldsnumberofair: Re^=160-1600. C-27PDF Image | Development of the Zinc-Chlorine Battery for Utility
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