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Performance Improvement Options for the Supercritical Carbon Dioxide Brayton Cycle

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Performance Improvement Options for the Supercritical Carbon Dioxide Brayton Cycle ( performance-improvement-options-supercritical-carbon-dioxide )

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4. Cycle Operating Conditions In this chapter, the cycle operating conditions – temperatures and pressures – are varied to determine the conditions that provide the highest cycle efficiency. Previously, the reference cycle conditions (Figure 2) were selected such that the minimum pressure and temperature were set close to but still above the critical point. The maximum pressure was selected as 20 MPa based on the fact that beyond this pressure, the gain in cycle efficiency diminishes [4]. However, previous analysis has never been applied to the “low” temperature S-CO2 cycle design for a SFR. The selection of the operating parameters is revisited in this chapter. In addition to simple parameter optimization, different cycle operating conditions, such as CO2 condensation have been analyzed. Among the cycle operating parameters, only the maximum CO2 temperature is somewhat fixed by the reactor (sodium) side. The cycle efficiency increases with the maximum (turbine inlet) temperature (Figure 1), so it is beneficial to raise the CO2 temperature in the Na-to-CO2 heat exchanger as close to the Na temperature as is practically achievable. For the recompression S-CO2 Brayton cycle, the cycle efficiency depends on the CO2 flow split between the compressors. Therefore, in the optimization presented below, each considered parameter is varied simultaneously with the flow split fraction; i.e., the fraction of the CO2 flow which goes through the cooler and the main compressor, to insure that the optimal operating conditions are maintained during the main parameter variation. 4.1. Maximum Pressure Figure 5 shows the dependency of the cycle efficiency on the maximum CO2 pressure. In the analysis, the size of each piece of equipment is fixed, including the number of stages for the turbine and compressors. Figure 5 generally confirms that very little gain in cycle efficiency could be realized by raising the maximum cycle pressure above 20 MPa. Raising the pressure would require greater thicknesses for the piping, pressure-bearing casings, and heat exchangers resulting in higher capital costs. Still, about a 0.3 % increase in cycle efficiency can be achieved if the maximum cycle pressure is raised to 22 MPa. Again, this number represents the efficiency benefit for the equipment optimized previously for 20 MPa conditions. Further increase in efficiency could potentially be achieved through optimization of the turbomachinery and heat exchangers for the greater pressure. 18

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