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velocity changes. This is an aspect of RGRCMS that could use some improvement. The current model does predict the appropriate pressure ratio at the design point and clearly shows that surge and choke are more limiting in the multi-stage design. Also, return channel design may depend a great deal on available space and other factors independent of compressor performance. 3.5 S-CO2 Compressor Designs Preliminary design estimates are frequently based on specific speed as a way of determining the optimum compressor type, or number of stages. Centrifugal compressors were chosen as the design option for the recompression cycle based on specific speed, and the assumption that the compressors would be synchronized with the electricity grid at 3600 RPM. Testing different approaches to the geometrical design of recompression cycle compressors resulted in the designs detailed in this section. Designs were developed for the compressors needed to operate the 500 MWth PCS described in Chapter 2. 3.5.1 The Main Compressor Design The main compressor operates at steady state with the inlet conditions just above the fluid’s critical point. The density is very high and therefore the compressor behaves more like a pump. At the design point the main compressor achieves a total-to-static efficiency of 90.4 %. Figures 3.12 and 3.13 show the pressure ratio and efficiency as a function of mass flow rate and operating speed for the main compressor in a 500 MWth representative cycle. At the design point the main compressor work is 32.3 MW. In the reference cycle, the main compressor receives 62 % of the flow, which is a typical value for recompression cycles. Despite the much larger share of the flow, the main compressor work is much less than the recompressing compressor, due to the proximity of the main compressor inlet to the critical point of the fluid. 73PDF Image | Supercritical Carbon Dioxide Cycle Analysis
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