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8 source. The source provides greater than 400 gallons/minute of 145'F water and an essentially unlimited quantity of 450F water is available for cooling. Thus, wen after allowing a factor of 2 to provide for anticipated growth in demand, we are left with a source potential significantly greater than the demand. Under these conditions, heat engine cycle efficiencyis of secondary importance and the design constraint is minimum cost for the fixed power requirement. For this particular application, the only real variable in cost was the heat exchangers required since the other hardware was essentially fixed by the chosen power level and availability. The heat engine chosen was a simple Rankine cycle (as shown in Figure 1)operating with R12 as the working fluid. The cycle parameters were then varied and plotted vs. heat exchanger cost as shown in Figures 2 and 3. * The rather surprising result is that the optimum cycle parameters for minimum system cost are significantly different from those yielding maximum cycle efficiency. In Figure 2, the total heat exchanger cost is seen to decrease with decreasing condenser hotwell temperature due to the imprwement in cycle efficiency with the lower sink tem- peratures, reaching a minimum at about 63OF as shown in Figure 3. Below the 63OF point, the condenser area, and hence cost, increases since area reduction from further imprave- ments in cycle efficiency are more than offset by the larger area required for the condensing temperature to approach the cooling water temperature more closely. exchanger cost occurs at a peak cycle temperature of approximately 115 F. Below 115OF. the increase in boiler and preheater area due to the falloff in cycle efficiency from the lower peak cycle temperature dominates w e r the decreasing area effect of the greater temperature difference between the working fluid and the source water. The opposite occurs abwe 115OF. The design In general, where we have "free" sources of heating and cooling fluids such as geothermal and waste heat sources, etc., it would be desirable to perform analyses as represented by Figures 2 and 3 with the addition of power level as a third variable to arrive at the lowest cost per unit output for a given source potential. *This work performed by Barber-Nichols Engineering, Arvada. Colo. , under Contract 02-7895 with Sandia Laboratories. Simple Rankine Cycle System For each condenser temperature curve in Figure 2, we note that the minimum total heat peak cycle temperature and condensing temperature were choosen to be 120 F and 60 F, re- spectively, to provide a heat exchanger area safety margin. Figure 1. Boiler/ Preheater Condenser Feed Pump 0 00PDF Image | RANKINE CYCLE ENERGY CONVERSION SYSTEM DESIGN CONSIDERATIONS FOR LOW AND INTERMEDIATE TEMPERATURE SENSIBLE HEAT SOURCES
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