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The results of the computations are presented in Table 1 for hO dif ferent cases. For various inlet conditions the following parameters were computed: » ^Aout5 ^cw’ R£at (Percen'ta8e heat load due to evaporation), T^ K^, T*, ANu^, ACOP and e (heat exchanger effectivenessofunwettedexchanger). Theaugmentationofheat transfer expressed by K is high as shown in the table. This ob- e viously influences the temperative effectiveness and efficiency of the fins which are difficult to evaluate due to their geometry and complexheattransferdistributionoftheunevenwaterfilm. An average heat transfer coefficient on the water side was assumed such that the heat transfer from the condensing refrigerant to the water film equals the heat Aicw received by the air. The effectiveness of the fins decreases on the average by 35% whencomparedwithheattransfertodryair. Thisdecreasecouldbe offset by using thicker fins but this was not considered because the decrease in effectiveness has only a very small influence on the overallperformanceofthewettedcoil. Thisperformanceismainly a function of surface of the coil and of uniform wetting conditions. Thisisinagreementwith[12]. Thestatechangesoftheairandof the water interface of the case Wo. 6 of Table 1 are shown in the i-x diagramofFig.12. Thedatainthisdiagramdemonstratesthat28 .PSYCH ROME TRIG CHARTV NflAftOMETRlC PRESSURE 760 mi. H, Figure 12. State changes of air and water C-28PDF Image | Development of the Zinc-Chlorine Battery for Utility
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