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2. Preliminary design 2.1. Thermodynamic modelling Norman Holaind et al. / Energy Procedia 123 (2017) 313–320 315 Norman Holaind et al./ Energy Procedia 00 (2017) 000–000 3 The reference cycle architecture for the current study is the simple regenerated Brayton one using flue gas as hot source and water as cold one. This configuration is not as efficient as the recompression one [1,3] but definitely provides the most cost effective solution for the economic feasibility of the heat recovery approach especially at low power outputs (<100 kWe). With reference to Figure 1, that shows the plant scheme and the entropy diagram of the sCO2 system, assuming no pressure and heat losses at the interconnecting pipes, the working fluid is compressed (2- 4), undergoes a heat gain (A-B) to be eventually expanded (5-6) and cooled back to the initial conditions (D-C). The regenerative heat transfer process occurs from the turbine outlet on the hot side (6-D) and from the compressor outlet with respect to the cold side (4-A) of the recuperator. The heat recovery process takes place in the heater (A-B) while the heat rejection occurs in the cooler (D-C). The modelling approach that has been pursued in the thermodynamic analysis of the sCO2 system is based on steady state energy balances at the heat exchangers as well as on isentropic efficiency of compressor and turbine. Equations (1-7) are reported in Table 1. The software platform is Engineering Equation Solver (EES) [12] linked with the NIST REFPROP library [13] for the thermophysical properties of working fluids. The compressor and turbine efficiencies that have been assumed for the current analysis are reported in Table 2 together with additional input data. Heater Recuperator Cooler Compressor Turbine Cycle efficiency Overall efficiency mhotcp,hot(T8 −T9)=mwf (hB hA −h4 =h6 −hD hA−) (1) (2) Fig. 1.Scheme and T-s diagram of the Simple regenerative Brayton cycle using supercritical CO2 (sCO2) Table 1. Governing equations m c (T −T )=m (h h−) (3) coldp,cold1110 wfDC ηcomp =−(h3 h2)−(h4 h2) (4) ηturb =−(h5 h6 )−(h5 h7 ) (5) ηcy = mwf ((h5 −h6 )−(h4 −h2 )) (6) mhotcp,hot(T8 −T9) ηtot =ηcyηmechηel (7)PDF Image | Design of Radial Turbomachinery for S CO2 CFD
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