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b. T Cycle Number 1 2 Power Cycle Working Efficiency Fluid EP R l 1 0.068 R13B1 0.-054 Sensible Heat Transfer Fluid AT 20°F 7O°F Average Collector Temperature 180°F 155OF Collector System Efficiency Efficiency Ec Ep x Ec 0.48 0.031 0.57 0.031 . I cent, the peak cycle temperature could be reduced by approximately 110 F, and if the ratio is specified to be 20 percent, we find the peak temperature lowered by almost 2000F. These potential reductions in peak temperatures can significantly lower the thermal losses (and hence raise the efficiency) and/or reduce the insulation required for the entire system including collectors, high temperature storage (if used), piping, etc. In addition, the lower peak temperatures yield more versatility in all areas of system design, particularly in the materials and methods of construction required. The net result of utilizing a higher efficiency prime mover can be lower overall system cost andlor higher performance, regardless of the heat conversion cycle used (the example was arbitrarily chosen). In Sandia's studies to date with solar-to-thermal-to-electrical energy con- version systems, the cost of the heat conversion subsystem (which includes the prime mover) by TABLE 11 Comparison of Performance Parameters for Two Low Temperature Solar Energy Conversion Systems Discussion and Conclusions The common element in all the above examples is that the most cost effective system design did not require the most efficient thermodynamic cycle. However, this does not imply that the heat engine conversion hardware such as the turbine and generator (or irrigation pump in example 4) should not be as efficient as possible. For illustration, the performance curves shown in Figure 17 represent regenerative Rankint cycle calculations which have identical input, with the exception of the assumed prime mover ef- ficiencies. We note that for a solar syste-m with a specified peak cycle temperature (from Figure 17), the system with the higher prime mover efficiency requires fewer collectors, less high tem- perature thermal storage (if this method of storage is used), and less regenerator and condenser capacity for a given output. The differences are summarized for a peak cycle temperature of 5500F in Table ID. If the system efficiency is specified (i.e., the electricity to usable heat ratio) such as in a cascaded total energy system, we find that the peak cycle temperatures are significantly lower for the system with the high efficiency prime mover. Referring to the curves for Cycles A and C in Figure 17, we see that if the desired electricity to heat ratio (cycle efficiency) is 15 per- 0 17PDF Image | RANKINE CYCLE ENERGY CONVERSION SYSTEM DESIGN CONSIDERATIONS FOR LOW AND INTERMEDIATE TEMPERATURE SENSIBLE HEAT SOURCES
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