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Nexant Parabolic Trough Solar Power Plant Systems Analysis

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Nexant Parabolic Trough Solar Power Plant Systems Analysis ( nexant-parabolic-trough-solar-power-plant-systems-analysis )

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Task 2 Wet/Dry Heat Rejection Analysis power demand of each fan is 219 kWe; at 140 °F, the demand falls to 182 kWe. A polynomial expression is included in the Excelergy parasitic block calculations to model this effect, as follows: .EparCt = (CtPar)[(CtParF0 + (CtParF1)(AmbTemp(D, H, T)) + (CtParF2)(AmbTemp(D, H, T))2)] (.PbLoad) where .EparCt is the cooling tower energy demand at each time step, CtPar is the fan power demand at the design point, the coefficients CtParP0 through CtParF2 adjust the fan power demand with the ambient temperature, and .PbLoad is the ratio of gross electric output at each time step to the design electric output. As such, the number of cooling tower fans in operation is assumed to be proportional to the turbine output. 4.2 Wet Heat Rejection The gross output of the Rankine cycle was calculated using a modified Excelergy format for wet cooling towers. The effect of the wet bulb temperature on the Rankine output was modeled as follows: Ntc = TempCorr0 + TempCorr1 * Ttc + TempCorr2 * Ttc2 .EgrSol = .EgrSol * Ntc where Ttc is the dry bulb temperature, and the three coefficients TempCorr0 through TempCorr2 are derived from a second order polynomial fit of GateCycle calculations of the gross turbine output plotted as a function of the dry bulb temperature. Each dry bulb temperature is assumed to have a corresponding relative humidity, as illustrated in the trend line of Figure 8. At the design point, the parasitic energy consumption was estimated to be 881 kWe for the cooling tower fans, and 653 kWe for the circulating water pumps. For combinations of ambient temperature and Rankine cycle output other than the design point, the energy demand was calculated as follows: .EparCt = (CtPar)[(CtParF0 + (CtParF1)(AmbTemp(D, H, T)) + (CtParF2)(AmbTemp(D, H, T))2)] (.PbLoad) where the coefficients CtParP0 through CtParF2 are based on GateCycle calculations which adjust the fan and the circulating water pump power demands with the ambient temperature. 4.3 Annual Performance Comparison The results of the annual performance calculations for the dry and the wet heat rejection cases are shown in Table 7. Cases 1 through 6 use dry heat rejection systems, with initial temperature differences of 24 °F to 49 °F, respectively. Case 7 is the same as Case 4, but with the condenser pressure limited to 8 in. HgA.. Case 8 uses a wet heat rejection system. The dry heat rejection cases deliver 91 to 96 percent of the annual electric energy supplied by the wet heat rejection case, and have annual solar-to-electric efficiencies 0.5 to 0.7 percentage points lower. However, the annual water use for the dry cases is only about 8 percent of that for the wet case. - 17 -

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