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16 Thermodynamic cycle analysis 980 970 960 950 940 930 920 012345 ∆PLS [%] 560 550 540 530 520 510 500 490 012345 ∆PLS [%] (a) Minimum TIT. (b) Discharge pressure. Figure 2-10: Minimum turbine inlet temperature and its correspondent compressor discharge pressure for the regenerative Brayton system as a function of the pressure loss (ηTR = 50%, T2 = 31.25◦C, P2 = 74 bar, ηHR = 90%, ∆TPN = 10◦C). The chosen operating conditions correspond to a pressure loss of 2% (equivalent to 0.03 fractional pressure loss, calculated as ∆PTOTAL/P3), which is close to the state-of-the-art fractional pressure loss (0.04) [49] for Brayton power plants. This pressure loss corresponds to a minimum TIT of 943◦C with a discharge pressure of 520 bar. The cycle T-s diagram is presented in Figure 2-11. 1000 900 800 700 600 500 400 300 200 100 0 −100 1.5 2 2.5 3 3.5 s [kJ/kgK] 2 3 Cycle Pressure Density Enthalpy 6 3.5 4 5 Cycle points Comp. inlet (2) Reg. cold side inlet (3) Heater inlet (3.5) Turb. inlet (4) Reg. hot side inlet (5) Cooler inlet (6) PT [bar] [◦ C] 74.00 31.25 520.28 143.94 520.28 551.33 509.88 942.86 75.51 647.68 75.51 154.56 Figure 2-11: Regenerative Brayton system T-s diagram (ηTR = 50%, T2 = 31.25◦C, P2 = 74 bar, P3 = 520.28 bar, ηTR = 93.4%, ηCM = 85%, ηHR = 90%, ∆PLS = 2%, ∆TPN = 10◦C). The numbers in the chart correspond to those shown in Figure 2-1. As mentioned earlier, the pressure losses are placed at the turbine and compressor inlets. Notice that the CO2 density varies between 43 kg/m3 and 715 kg/m3, which are high values that allow the design of very compact turbomachinery and compact heat exchangers, though the technological requirements are very demanding, and the equipment bound to be highly unconventional. The temperature profile of the regenerator is shown in Figure 2-12. A counter current J.S. Bahamonde Noriega Master of Science Thesis T [◦C] T4,MIN [◦C] P3 [bar]PDF Image | Design method for s-CO2 gas turbine power plants
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