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There are many other details, such as the use and design of an inlet inducer, which must be considered in radial compressor design. In this respect, it is worth repeating the point made in most of the texts cited in section 2.5, namely that most refinements are closely held, unpublished, trade secrets, and hence are best left to the industrial sector. 2.3 Pump-Like Nature of Main Compressor Most Brayton cycle turbomachinery applications deal with working fluids which are near-ideal gases. Thus our general approach has been to incorporate real gas properties into the design codes. This has proven to be a difficult endeavor for near-critical-point applications. For the main compressor another approach can be contemplated: treating it as a pump of (near)-incompressible fluid. At an analytical level, radial compressors and pumps have considerable similarity: the companion books by Japikse [Ref. 2.4], [Ref. 2.5] treat both in a consistent manner. Isentropic compression of an ideal gas increases the density by the factor: ⎛ρ⎞1 2 =rk =2.60.8=2.15 , ⎜⎟() ⎝ ρ1 ⎠ which in our application gives the values in parenthesis. The ratio is 1.0, by definition, for an incompressible fluid (ignoring the slight amount of thermal expansion). Figure 2.5 shows the trajectory in density space for the S-CO2 main compressor. The density increases by a factor of 1.2: much closer to the pump (incompressible fluid) limit than to the compressor (ideal gas) ratio. If one treats this component as a pump for fluid at the average of inlet and outlet densities, the estimated work is within 2% of that computed using the AXIALTM compressor code modified to employ NIST Ref. Prop. real gas CO2 properties. 7PDF Image | Analysis of Radial Compressor Options for Supercritical CO2 Power
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