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the temperature increase of air entering the dry channel at ambient unsaturated condition. The saturated air entering the heat exchanger will change in temperature along the curve T^ (unwetted) or along I'A.wet or al°nS TAyg if saturated at every location. The T-S diagram of Fig. 2 demonstrates that lowering the con densing temperature to T* lowers the compressor power by AW and c act) increases the cooling capacity by AQ^. The coefficient of performance COP* can be expressed as Q + AQ COP* = 77—~—TTr"— ¥ -AW act act and, the enhancement of COP is given by ACOP COP* - COP COP The above discussion can be extended to a special idealized case. (5) (6) It was demonstrated that h. h*. We assume that h, resulting AA in U Umax. We assume furthermore that despite the infinite heat transfer the air is not of infinite specific heat but changes in temperature as in the unwetted channel, i.e., LMTD = AT . m exchanged in this idealized case is ^Cf'max Umax ATm Ac In principle it is possible that The heat (7) (8) U.TAT “U AT (9) W mw< max m QCW > QCDmax and the wetted condenser transfers more heat to air than the dry condenser of zero air side heat transfer resistance. At a first glance this is a surprising result but physically understandable because 3. ModelingofaPlate-FinTubeTypeCondenserforWetted,Partially Wetted and Unwetted Operation A"Blow-Through"typecondenserunitisshowninFig.3. The heat exchanger consists of horizontal tubes through which the re frigerantischanneledandverticalfins. Waterissuppliedby spray nozzles to the top of the heat exchanger and flows under the actionofgravitydownwardsandiscollectedinareservoir. Air C-10PDF Image | Development of the Zinc-Chlorine Battery for Utility
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