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2-3 Brayton recompression system 19 The reversible power of this system is a function of the system temperatures and the thermal energy input, T ̄ W ̇RV= 1−T ̄C Q ̇E. (2-16) H Finally, the exergetic efficiency is calculated with the reversible power and the cycle power, ηEX = W ̇ CY . (2-17) W ̇ R V The results of the exergy analysis for this system are presented in Figure 2-13. The largest losses in exergy are produced by the regenerator. As shown in Figure 2-12, real gas effects limit the performance of this device. In order to improve this operating conditions, two regenerators are considered in the following section. The second component with the largest exergy losses is the cooler. Likewise, the vapor recompression system presented in the next section improves the operation of this component. Cycle power Compressor Turbine Regenerator Cooler Exergy losses Useful exergy Exergy balance share 13% 6% 2% 2% Component Regenerator Cooler Compressor Turbine Exergy efficiency Exergy loss [MW] 1.55 3.13 0.57 0.52 84.89 % 76% Figure 2-13: Cycle exergy balance for the regenerative Brayton system (ηTR = 50%, T2 = 31.25◦C, P2 =74bar,P3 =520.28bar,ηTR =93.4%,ηCM =85%,ηHR =90%,∆PLS =2%,∆TPN =10◦C). 2-3 Brayton recompression system This section is devoted to the analysis of the Brayton recompression system shown in Figure 2-14, which is a modification of the basic configuration of Section 2-2. This system includes two compressors and two regenerators in order to improve the energy transfer in the low temperature region of the regeneration process and reduce the energy rejection to the envi- ronment in the cooler. This configuration splits the mass flow f in two parts by means of the mass flow fraction α, which is calculated from an energy balance on the low temperature regenerator (regenerator 1 in Figure 2-14), Master of Science Thesis f(1 − α)(h3.3 − h3) = f(h5.5 − h6). (2-18) J.S. Bahamonde NoriegaPDF Image | Design method for s-CO2 gas turbine power plants
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