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Task 2 Wet/Dry Heat Rejection Analysis Table 5 Gross Plant Output as a Function of Dry Bulb Temperature Wet Heat Rejection Dry bulb temperature, °F 40 50 60 70 80 90 100 110 120 Relative Gross turbine humidity output, MWe 0.79 88.5 0.64 88.5 0.50 88.5 0.39 88.4 0.29 88.4 0.22 88.3 0.16 88.2 0.12 88.1 0.11 88.0 Cooling tower makeup 1, lbm/hr 383,000 456,000 527,000 584,000 635,000 686,000 737,000 789,000 841,000 Note 1: Sum of blowdown, evaporation, and drift losses. Strictly speaking, numerous relative humidities are associated with each dry bulb temperature, as illustrated in the data points of Figure 8. Fortunately, for sites with low relative humidities during the summer, the performance of the Rankine cycle is essentially invariant with the dry bulb temperature. As a result, assigning only one relative humidity to each dry bulb temperature should result in an annual energy estimate which is very close to a more complex analysis involving a three-dimensional surface fit of gross output as a function of dry bulb temperature and relative humidity. A combination of an essentially constant turbine output and an inverse relationship between ambient temperature and water use should be characteristic of a desert location. In essence, the cooling tower always transfer heats to the environment under favorable conditions: When the ambient temperature is high, the relative humidity is low; and when the relative humidity is high, the ambient temperature is low. However, at other plant locations in which the relative humidity is not a strong function of the ambient temperature, the turbine output is likely to decline on hot days. - 14 -PDF Image | Nexant Parabolic Trough Solar Power Plant Systems Analysis
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