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Chapter 3 Main Compressor and Recompression Compressor Design 3.1 Introduction This chapter presents the steady state full-power design for a radial (centrifugal) compressor in our reference 300 MWe power conversion system. As noted earlier, this is the most challenging component in a supercritical CO2 PCS because it operates near the critical point of CO2, and has an exceptionally high mass and volume flow rate for a radial compressor. The design is also strongly constrained by the goal that a single shaft, constant speed (3600 rpm) without gearing, be employed. Thus one of the few major variables left for the designer is the number of stages: in effect one vs. two, since the overall pressure ratio is low (2.6) for a centrifugal machine. The present chapter deals only with full-power, steady-state performance. Chapter 4 covers development of the off-normal performance correlations needed for PCS transient and control studies. The chapter concludes with a brief comparison with the axial main compressor design reported earlier (3.5) and Chapter 5 discusses, in the interest of completeness, another alternative: a hybrid radial-axial machine in which the inlet stage is radial. 3.2 Design Method The method is based on specific speed, which is commonly used by industry for radial turbomachinery during the conceptual design stage. The method of estimating the performance and size of radial compressors and turbines is described by Balje [1980]. Two non-dimensional parameters are used to characterize the turbomachinery. These two parameters are referred to as specific speed (Ns) and specific diameter (Ds). The specific speed and specific diameter are defined as follows: (3-1) (3-2) where V is the volume flow rate [m3/s], Had the adiabatic head [m], Ω the rotating speed [rad/s]. Ns= ΩV (gH )34 Ds = ad V ad D(gH ) 14 14PDF Image | Radial Compressor Options for Supercritical CO2 Power Conversion Cycles
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