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model using Taylor-Couette (Bruckner, 2009) flow could also be used could also be used to model the windage losses. By using these equations, and the dimensions defined in Table 5.2, it is possible to estimate the power loss for the design, however some caution needs to be given. This model and correlation was developed based on measured data for air and steam. It was never intended to work with supercritical fluids. In addition, it was originally derived for laminar Reynolds number but generalized to work at high (or turbulent) Reynolds number, nevertheless comparisons with data (Vrancik, 1968) indicate that the generalizations are correct for air and steam. For supercritical CO2 the correlations appear to provide reasonable estimates provided the local non-ideal CO2 properties are used. For estimation purposes, it is assumed that the rotor cavity temperature is bounded by the between the cooling water temperature in the turbomachinery housing and the compressor outlet temperature. Thus, the rotor cavity temperature is generally between the low temperature of the cooling water at 295 K and may be as large as ~320 K. Thrust Load Cell Labyrinth Seals Main Compressor Compressor Shroud Static Pressure Tap Compressor Inlet (305 K, 7,690 kPa) Roller Bearing Tie Shaft Permanent Magnet Rotor Stator Winding Stator Cavity Diffuser Compressor Exit Chamber (323 K, 13,840 kPa) Figure 5-13: Detail of main compressor, labyrinth seals, ball bearings, and location of other major components. Figure 5-13 shows the rotor shaft, bearings, labyrinth seal, main compressor, and the pump out port which is the opening at the bottom of the stator cavity (not labeled). The CO2 flows from the high pressure compressor wheel outlet, past the back side of the compressor wheel, through the labyrinth seal and then into the rotor cavity. As the CO2 expands in the labyrinth seal, it cools, strikes the bearings, then 60PDF Image | Operation and Analysis of a Supercritical CO2 Brayton Cycle
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