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Design method for s-CO2 gas turbine power plants

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Design method for s-CO2 gas turbine power plants ( design-method-s-co2-gas-turbine-power-plants )

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26 Thermodynamic cycle analysis Table 2-4: Operating conditions for the Brayton recompression system (ηTR = 50%, T2 = 31.25◦C, P2 =74,P3 =271.51bar,ηTR =93.4%,ηCM1 =85%,ηCM2 =85%,ηHR =90%,∆PLS =2%, ∆TPN = 10◦C) Variable Required CO2 mass flow Mass fraction α Regenerator 1 effectiveness Regenerator 2 effectiveness Regenerator 1 power Regenerator 2 power Heater power Cooler power Compressor 1 power Compressor 2 power Turbine gross power Value kg/s 119.89 — 0.31 % 93.08 % 97.39 MW 20.37 MW 48.28 MW 33.67 MW 14.97 MW 3.72 MW 4.03 MW 26.45 Exergy analysis A procedure similar to the one of the previous section is followed. However, there are new thermodynamic states to be taken in account. Additionally, the mass flow used in the equa- tions must be adjusted depending on the component. Considering these observations, the exergy balance is performed and the results are presented in Figure 2-23. As expected, the exergy efficiency is larger the one of the regenerative Brayton power cycle because of the better regeneration process and the lower heat rejection in the cooler, which has the largest percentage share in the exergy losses in this case. Cycle power Compressor 1 Compressor 2 Regenerator 1 Regenerator 2 Turbine Cooler Exergy losses Useful exergy 79% Exergy balance share 11% 2% 3% 2% 2% 1% Component Exergy loss [MW] Figure 2-23: Cycle exergy balance for the Brayton recompression system (ηTR = 50%, T2 = 31.25◦C, P2 = 74, P3 = 271.51 bar, ηTR = 93.4%, ηCM1 = 85%, ηCM2 = 85%, ηHR = 90%, ∆PLS = 2%, ∆TPN = 10◦C). J.S. Bahamonde Noriega Master of Science Thesis Regenerator 1 0.41 Regenerator 2 0.75 Cooler 2.64 Compressor 1 0.32 Compressor 2 0.41 Turbine 0.59 Exergy efficiency 86.16%

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