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Operation and Analysis of a Supercritical CO2 Brayton Cycle

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Operation and Analysis of a Supercritical CO2 Brayton Cycle ( operation-and-analysis-supercritical-co2-brayton-cycle )

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into the rotor/stator cavity. It is possible to cool the CO2 so much that it freezes. When this happens it is generally very difficult to start spinning the rotor shaft regardless of whether ball bearings or gas-foil bearings are used. Table 5.2: Approximate design values for the S-CO2 windage loss calculations. Rotor Cavity Property Radius Shaft speed Gap Effective length of rotor Viscosity of CO2 Maximum density of CO2 at (7690 kPa & 320 K) V alue 25.4 mm 75,000 rpm 3.175 mm 168 mm ~1.6x10-5Pas 0.213 kg/liter Figure 5-14 illustrates the rotor windage loss and how it varies as a function of cavity pressure. Unfortunately, at 320 K (the maximum assumed cavity temperature) and 900 psia (the maximum assumed cavity pressure that is very near the critical pressure, 1115 psia), the losses are high. At these values the rotor cavity windage losses are expected to be on the order of 35 kW-40 kW, which nearly equals the capability of the motor control system and the pumping power for the compressor. Clearly, this magnitude of power loss is unacceptable. To avoid these windage losses we used a turbomachinery design that lowers the rotor cavity pressure. Windage Rotor Loss as a function of Cavity Pressure 4 Windage Losses versus Rotor Cavity Pres. Near Critical Pressure Near Cavity Design Pressure 4  3.74910 4 10 40 v    co2D2 0104  4 3 10 30  4 1 10 10 5.749103 0 100 200 0 300 400 500 600 700 800 900 1000 182.971 p ( v  300 K) 921.944 c o2 Pressure (psia) ps i Pressure (psia) Figure 5-14: Calculated windage loss for the S-CO2 turbo-alternator-compressor as a function of rotor cavity pressure. 61 Power (kW)

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