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Figure 6: Pump efficiency as a function of capacity, assuming high specific speed. Other mechanical and electrical losses are accounted internally. These include gearbox (below 50MW – above that power level, axial turbine speed is consistent with direct generator drive), bearing, and generator losses. Models for these losses are based on general sizing rules and established performance from existing systems. Heat exchangers The overall heat exchanger size is specified on the basis of a UA value, normally defined as the design-point heat transferred divided by a log-mean temperature difference (UA=Q/LMTD). However, to accommodate the variation in the heat capacity of CO2, a 25 sub-element discretized model of the heat exchanger is used to calculate the total heat transferred. The performance of this model has been shown to accurately reproduce the measured heat transfer performance of PCHE’s in the EPS100 test program [1]. Design-point pressure drops for the PCHE’s were set to values consistent with the EPS100, 0.1-0.3 MPa depending on the heat exchanger. Although the EHX configuration is a cross-flow finned-tube heat exchanger (exhaust side mixed, CO2 side unmixed), the number of cross-flow passes is typically at least eight. With this large number of passes, the performance of the cross-flow heat exchanger very closely approaches the performance of counter-flow geometry [26]. Therefore for the current study, the EHX is modeled as a counter-flow heat exchanger. Exhaust-side pressure drop was set to 1 kPa for the exhaust heat exchanger (EHX) coils consistent with typical gas turbine experience, and CO2-side pressure drop is set to 0.15 MPa per coil. Cost models and inputs Balancing power and cost, such as shown in Figure 3, requires not only a thermodynamic performance model for the cycle, but also models for the individual 11PDF Image | SUPERCRITICAL CO2 CYCLES FOR GAS TURBINE COMBINED CYCLE
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