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Energies 2020, 13, 2447 8 of 18 WHUR = Wnet ·100% (hIN −hAM) (8) where: WHUR—waste heat utilization rate (%), hIN—specific enthalpy of waste heat (flue gases) at heat exchanger hot side inlet (J/kg), hAM—specific enthalpy of waste heat (flue gases) at heat exchanger hot side outlet, assuming exhaust gases cooling to 25 ◦C (298.15 K) (J/kg). The next parameter is the percent of waste heat transferred to CO2, which is given by Equation (9): PWHT = (hIN −hOUT)·100% (9) (hIN −hAM) where: PWHT—percent of waste heat transferred to CO2 (%), hIN—specific enthalpy of waste heat (flue gases) at heat exchanger hot side inlet (J/kg), hOUT—specific enthalpy of waste heat (flue gases) at heat exchanger hot side outlet (J/kg), hAM—specific enthalpy of waste heat (flue gases) at heat exchanger hot side outlet, assuming exhaust gases cooling to 25 ◦C (298.15 K) (J/kg). The last parameter allowing to evaluate the energy efficiency of the cycle is internal cycle efficiency, which is given by Equation (10): h′ −h −(h −h ) CE=45 21·100% (10) (h4 −h3) where: CE—cycle efficiency (%), h5—specific enthalpy of CO2 at the turbine outlet (J/kg), h′4—specific enthalpy of CO2 at the turbine inlet (J/kg), h4—specific enthalpy of CO2 at the heat exchanger cold side outlet (J/kg), h′3—specific enthalpy of CO2 at the heat exchanger cold side inlet (J/kg), h2—specific enthalpy of CO2 at the compressor outlet (J/kg), h1—specific enthalpy of CO2 at the compressor inlet (J/kg). 4. Cycle Operation Parameters and Calculation Results As part of this research, the authors performed a series of simulations of the Brayton system with S-CO2. It was established that the lower heat source is the energy from the exhaust gas of reciprocating engines which drives compressors at the gas compressor station. During the simulation the following operating parameters of the system were changed: (i) turbine inlet pressure, (ii) degree of exhaust gas cooling, (iii) temperature difference of CO2 and flue gas in the heat exchanger, (iv) temperature of CO2 after passing the hot side of recuperator were changed. Aggregated simulation results in the form of graphs and discussions are presented on the following pages. Additionally, exemplary system operation parameters are presented, which assumes the cooling of exhaust gases to a temperature of 200 ◦C and compression of CO2 to a pressure of 20 MPa. It also has been established that the temperature difference between CO2 and the exhaust gases at the inlet and outlet of the heat exchanger is 5 K. The simulated cycle for the above mentioned operating conditions is presented in Figures 2 and 3 in the form of temperature/entropy and pressure/enthalpy plots. Stages 1–6 correspond to the stages described in Sections 2 and 3.PDF Image | Supercritical CO2-Brayton Cycle Nat Gas Compression Station
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