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The agreement between prediction and measurement is good. Overall, we believe that this validates the “similarity” approach used to predict the performance curves and to design the compressors and turbines. Main Compressor Measured and Predicted Efficiency from Spin Test 41 (12/02/08) 1 0.9 0.8 0.7 0.6 0.5 0.4 0.3 0.2 0.1 0 Figure 5-12: Comparison of the predicted and measured compressor efficiency for the main compressor in the SNL supercritical CO2 test loop. The plot shows the compressor efficiency (t-s) a function of corrected mass flow rate for parametric variations in corrected speed. This performance map was made using the same compressor conditions and data as the enthalpy map shown in the previous figure. 5.4 Windage Losses Because the shaft speeds are high (large fractions of the speed of sound) and because the fluid densities are large (approaching the density of water), significant friction occurs between the moving shaft and the fluid. These losses are called windage losses. The high pressure and high density in the S-CO2 Brayton cycle can also cause significant thrust loads, and leakage flow rates through seals that must be properly managed by the design. The initial configuration of the S-CO2 compression loop uses labyrinth seals on the compressor shaft to separate the rotor cavity from the high pressures in the compressor (and turbine). The gas-foil bearings and the ball bearings are located in the rotor cavity. The rotor cavity operates at reduced pressure (density) to lower the frictional losses. Efficiency Outliers were transients caused by closing the Main Compressor Flow Valve 45 krpm 50 krpm 55 krpm 60 krpm 56 krpm 60 krpm 64 krpm 64 krpm 45 krpm (BNI) 50 krpm (BNI) 55 krpm (BNI) 56 k rpm (BNI) Measured Model 45 krpm 50 krpm 55 krpm 0 2 4 6 8 10 Corrected Mass Flow Rate (lb/s) 58 Efficiency t-sPDF Image | Operation and Analysis of a Supercritical CO2 Brayton Cycle
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