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2-2 Regenerative Brayton system 9 Table 2-2: Parameters for the thermodynamic analysis of the s-CO2 power generation systems. Parameter Compressor 1 suction P. Compressor 1 suction T. Turbine adiabatic eff. Compressor 1 adiabatic eff. Compressor 2 adiabatic eff.∗ Regenerator 1 effectiveness Regenerator 2 effectiveness∗ System pressure loss sev [23] 76.21 32.79 93.40 88.90 87.80 91.70 94.50 — Cha This [27] study 74.00 74.00 31.25 31.25 93.40 93.40 89.10 85.00 87.50 85.00 91.70 < 98.00 94.60 < 98.00 — 2.00 — regenerator and compressor used bar P2 ◦C T2 % ηTR % ηCM1 % ηCM2 — εRG1 — εRG2 % ∆PLS [16] 76.30 32.00 92.90 95.50 94.80 98.00 98.00 — — ∗The components with label “2” correspond to the high temperature — 90.00 Heater efficiency in later configurations of the s-CO2 systems. % ηHR Wright [24, 25] 76.90 31.85 93.00 75.02 — — — — — Moisseyt- Dostal the fact that the expansion in the turbine is done in a region in which the fluid behaves almost as an ideal gas, the expansion ratio is small, and the volumetric flow sufficient for the realization of simple axial turbine. Thus, high turbine efficiencies are expected. The compressors efficiency are set to a smaller value due to the real gas effects that influence the compression process close to the critical point. Regarding the performance of the combustion process, the current state of the art of com- bustion chamber technologies allows to reach an efficiency value of 0.999 [9]. However, the carbon dioxide cannot be combusted and therefore the value of the efficiency of the heating system is taken as 0.9 in order to be conservative until the heater is designed and its efficiency estimated. The pressure loss in the system depends on the design of the components. In this stage its value is set to 2%. The calculation of this value depends on the losses in each side of the heat transfer process (the cold side correspondent to the cold side of the regenerator and the heater, the hot side correspondent to the hot side of the regenerator and the cooler). In this steady state analysis these losses are concentrated in the turbine and compressor inlet. Thus, the pressure at point 4 (refer to Figure 2-1) depends on the pressure at point 3 and the percentage loss in the cold side of the cycle (the same procedure is applied to the hot side), P = P 100 − ∆PLS%. (2-1) 4 3 100 In Section 3-1 it is shown that a Printed Circuit Heat Exchanger (PCHE) is an appropriate equipment for the realization of the regenerator. Its effectiveness in Table 2-2 corresponds to a maximum reference value given by the PCHE manufacturer [3]. Once the pinch is fixed, it is possible to calculate the regenerator effectiveness, which should not exceed this maximum value. The thermodynamics of the working fluid near to the critical point can lead to curved temperature profiles along the heat exchanger, with the pinch point not necessarily located in its hot or cold extremes. It is convenient then to fix the pinch instead of the effectiveness in order to avoid temperature crossing in the calculations of the temperature profiles. Considering this, the pinch temperature is set to 10◦C. Additionally, it is necessary to define the regenerator effectiveness. A schematic diagram of the temperature profile is presented in Figure 2-2. The effectiveness is function of the enthalpies in the regenerator and Master of Science Thesis J.S. Bahamonde NoriegaPDF Image | Design method for s-CO2 gas turbine power plants
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