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16 (85 - 15 percent by weight) mixture which yields a saturated vapor after anisentropic prime mover expansion under the conditions shown. Although the fluid gave rather poor efficiencies compared to the other fluids, there may be other fluids of a similar nature which would yield more promising results. Cycle 4 utilizes 100 percent trifluoroethanol with a critical temperature of 4400F. As can be seen in the table, this cycle yields a very attractive combination of good cycle efficiency and a large temperature drop. Trifluoroethanol has several other good points such as having a mod- erate critical pressure (715 psia), a low freezing point (-490F), and being nonflammable. Some of its disadvantages are a temperature stability limit of 6250F and a relatively high cost of approxi- mately $5/lb. If we look at the energy extracted from any sensible heating medium, we find that the energy is proportional to the AT experienced by the heating medium as noted previously. For this example, the maximum available AT from the sensible heat source is 500°F, the same as the spread between the high and low cycle temperatures, which is reasonable as a basis of comparison since in the ideal case we could heat the Rankine cycle working fluid to the highest heating fluid source temperature andcooltheheatingfluidtotheminimumworkingfluidtemperature. Onthisba-sis,wenotethat 340 185 Cycle 4 has an extraction efficiency of 0.28 x 500 = 0. 19 compared with 0.29 x 500 . = 0.11 for Cycle 1. Thus, Cycle 4 could extract nearly twice the energy from a given sensible heat source, which might be a very important factw as in certain geothermal applications where maximum power from a limited source is required or in a solar system requiring a large thermal storage. Example 4 -- Low Temperature (190°F) Solar Energy Conversion System. For this study, we have the same major subsystems (i. e., collectors, sensible heat storage, Rankine engine) as in examples 2 and 3 except that the collectors are of the flat plate type operating at a peak temperature of 1900F and the shaft power is to be used for irrigation pumping. For both cycles, the combined irrigation pump and gearbox efficiency was assumed to be 0.7, the prime mover efficiency was assumed to be 0.7, the regenerator efficiency was assumed to be 0.8, and the boiler feed pump efficiency was also assumed to be 0.8. The peak cycle tem- 0 perature was assumed to be 180 F, and the condenser hotwell temperature was assumed to be 60°F in both cases. The peak collector efficiencies were taken from a manufacturer's data, using 90°F for the average ambient temperature and 200 Btdhr ft2 for the average insolation. The re- sults of the calculations are given in Table II. From Table 11, it can be seen that Cycles 1 and 2 have the same overall "system" efficiency; however, Cycle 2 would require a smaller heat storage volume and less collector pump work by a factor of 2/7. Thus, on the basis of collector and storage costs, (usually the highest cost items) Cycle 2 would provide the most cost effective system. However, a detailed cost analysis including the heat engine costs would be necessary for final determination of the most economical system.PDF Image | RANKINE CYCLE ENERGY CONVERSION SYSTEM DESIGN CONSIDERATIONS FOR LOW AND INTERMEDIATE TEMPERATURE SENSIBLE HEAT SOURCES
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