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Energies 2020, 13, 370 14 of 31 The thermodynamic properties of carbon dioxide were obtained using the equation of state developed by Span and Wagner [50], which is embedded in EES and provides an accurate calculation of the real gas behavior of CO2 in a wide range of pressures and temperatures. The precise description of the thermodynamic properties, especially in the vicinity of the critical point ensured by [50], is crucial for the accurate analysis and performance prediction of the s-CO2 power cycles. Table 1 summarizes all the main assumptions, which are consistent with [36], for a direct comparison with the traditional s-CO2 power cycles. Table 1. Main assumptions in the simulation models of s-CO2 cycle layouts. Parameter Value Heat source inlet temperature, Tin (◦C) 600 Heat source specific heat, cp (kJ/kg-K) 1.17 Ambient temperature, Tamb (◦C) 20 Compressor inlet pressure, p1 (MPa) 7.63 Compressor inlet temperature, T1 (◦C) 32.0 Maximum cycle pressure, p2 (MPa) 20.0 Recuperator/s effectiveness, ε (%) 95.0 Minimum temperature difference in the heater/s, ∆Tmin (◦C) 50 Pressure drops in recuperators and heaters, ∆p (bar) - Isentropic efficiency turbine/s, ηis,T (%) 85 Isentropic efficiency compressor, ηis,C (%) 80 Mechanical/generator efficiency turbine/s, ηmg,T (%) 95 Mechanical efficiency compressor, ηm,C (%) 98 2.2.3. Thermal Efficiency of Elementary Thermodynamic Cycles While the decomposition of s-CO2 power cycles into elementary Brayton cycles is already meaningful at a qualitative level to understand the genesis of such advanced cycle layouts (see Section 2.1), further insights could be provided by a quantitative analysis that evaluates the thermal efficiency of each elementary cycle. The thermal efficiency of the first elementary thermodynamic cycle (topping cycle) was calculated as: . η . = Wnet,1 , (5) . Qhs,1 th,1 where Wnet,1 is the net power generated by the mass flow rate, m1, operating in the first elementary . thermodynamic cycle and Qhs,1 is the heat transferred from the external heat source to m1. Instead, the thermal efficiency of the second elementary thermodynamic cycle (bottoming cycle) is: . η = Wnet,2 , (6) th,2 . Qrec,1→2 where Wnet,2 is the net power generated by the mass flow rate, m2, operating in the second elementary . thermodynamic cycle, and Qrec,1→2 is the heat recovered from the exhaust of the first elementary cycle and transferred to m2. The analysis in Section 2.1 showed that the decomposition into a pure topping cycle and a pure bottoming cycle strictly applies only to the dual flow split with a dual expansion s-CO2 power cycle. Nevertheless, the calculation of the thermal efficiencies of elementary cycles can still be theoretically . carried out for the remaining layouts. In particular, the additional term Qhs,2 was added at the denominator of Equation (6) to take into account the heat transferred from the external heat source to m2 in the partial heating layout. Instead, the heat transferred from cycle 2 to cycle 1 in the dual .PDF Image | Novel Supercritical CO2 Power Cycles for Waste Heat Recovery
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