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The recompression cycle is designed with two recuperators and two compressors because of the pinch-point problem that arises if a simple recuperative cycle is used [Dostal, 2004]. Flow is split at the inlet to the precooler (point 6 in Figure 2.2) and then merges again at the inlet to the cold side of the HTR (point 2’ in Figure 2.2). Typically about 38% to 40 % of the flow will be directed to the recompressing compressor. Without using the recompression cycle, large differences in specific heat capacity cause the temperature difference in the recuperator of the simple Brayton cycle to reach zero; a pinch-point. The result of the pinch-point problem is poor effectiveness in the recuperator and lower cycle efficiency. The recompression cycle can achieve thermal efficiencies far superior to those of any existing LWR if the turbine inlet temperature is sufficiently high. S-CO2 cycles become competitive at turbine inlet temperatures of about 490 oC. This temperature threshold makes the S-CO2 recompression cycle attractive to next-generation plants, like SFRs, because core outlet temperatures will likely be in the range of 500 oC to 550 oC. Besides efficiency, another benefit of the S-CO2 cycle is its compactness. The turbine, for example, is an order of magnitude smaller in an S-CO2 plant than in most other power cycles. Figure 2.3 shows the size comparison of the CO2 turbine with those of helium and steam cycles as developed by Dostal [2004]. Figure 2.3: Turbine size comparison for different fluids, from Dostal, [2004] Small turbomachinery and relatively small heat exchangers mean that capital costs and plant footprint can be reduced. The ability to model this cycle and predict efficiency is critical to evaluating its competitiveness with other cycles. 24PDF Image | Supercritical Carbon Dioxide Cycle Analysis
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