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As noted in Table 2.1, one key issue standing in the way of adopting radial compressors for the reference S-CO2 PCS design is their efficiency, which is in general inferior to that of axial compressors for applications involving high volumetric flow rates. Wilson [Ref. 2.10] gives several reasons for their inherently higher losses: • The sharp turn in flow direction at the inlet • Vulnerability to secondary flows in their long passages • High outlet velocity and only moderate diffuser efficiency • Larger wetted area than axial machines Ref. [2.16] surveys commercial units employed in the 1960’s, and reports an average efficiency of only on the order of 77%. These were, however, for non-power-cycle applications, where the incentives for ultra-high efficiency are not as paramount. The state of the art continues to improve, however (see Fig. 2.3 from Ref. 2.17), and for present purposes we have assigned a net differential penalty of 4%: i.e. 89% efficiency for axial compressors vs. 85% efficiency for radial compressors. This subject deserves priority attention in the future design and test program. Fig. 2.3 Improvements in Radial Compressor Efficiency with Time 2.2 Some Major Design Options Centrifugal compressors require diffusers to attain more than mediocre efficiency. The diffusers can be with or without vanes. Vaneless diffusers are in general preferred for smaller, low-throughput devices, while the larger, high mass and volume flow machines of current interest usually have diffuser vanes. They generally have a wider operating range, not being choke prone. Vaned diffuser machines are more efficient and have a smaller overall diameter. 5PDF Image | Analysis of Radial Compressor Options for Supercritical CO2 Power
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