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10 Thermodynamic cycle analysis Figure 2-2: Regenerator schematic temperature profile. The curved shape is caused by the real gas effects in the CO2 streams and the pinch is not necessarily located in the hot or cold extremes of the heat exchanger. the mass flow of each stream, εRG = fH fC hHE−hHL hHE−hHL,IDEAL hCL−hCE hCL,IDEAL −hCE if ∆TH > ∆TC, if ∆TC > ∆TH, (2-2) where fH and fC stand for the hot and cold mass flows respectively, hHE and hHL correspond to the entering and leaving enthalpies of the hot side respectively, and hCE and hCL correspond to the entering and leaving enthalpies of the cold side respectively. The ideal enthalpies hHL,IDEAL and hCL,IDEAL are the values obtained with a perfect heat exchanger, i.e., a heat exchanger with zero temperature difference between the streams at the cold or hot extremes of the heat exchange process, hHL,IDEAL = h(PHE, TCE), (2-3) hCL,IDEAL = h(PCL, THE), (2-4) These enthalpies are calculated as a function of the correspondent pressure and temperature by means of the computational fluid library, which is used in the calculation of all the fluid properties in this work. The system performance is analyzed as a function of the compressor discharge pressure (maximum cycle pressure) with a constant pressure loss. The results are shown in Figure 2-3. Recall that the thermal efficiency of the cycle is fixed to 50% and the power to 18.7 MW. Figure 2-3a shows the TIT, which decreases with larger discharge pressures. There is a minimum at approximately 550 bar, which is a feature already discovered by Dostal [16], and leads to the conclusion that increasing the pressure ratio to reduce the TIT has a limited scope. This minimum is present due to the regeneration load that decreases with higher pressure ratios until the energy savings in the heat exchanger are not enough to maintain the thermal efficiency with lower TIT. Consequently, the TIT must increase to maintain the desired performance. The CO2 mass flow rate, regenerator power and effectiveness are shown in Figures 2-3b, 2-3c and 2-3d, respectively. They all decrease with larger maximum cycle pressures. The J.S. Bahamonde Noriega Master of Science ThesisPDF Image | Design method for s-CO2 gas turbine power plants
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