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Windage Comparison of Vrancik Model with Measured Windage (CBC_081016_1150.csv) Measured is based on Measured Motor Power - dH.ideal * mdot / eff 16000 45000 Meas Wind Ideal dH/eff Windage Vrancik Power1 RPM1 14000 12000 10000 8000 6000 4000 2000 40000 35000 30000 25000 20000 15000 10000 5000 00 0 500 1000 Figure 5-16: Comparison of windage estimates based on measured data (magenta) with the Vrancik model from NASA (yellow) for CBC_081016_1150.csv. 5.5 Seal Leakage Losses The labyrinth seal is illustrated in Figure 5-17 A and B. The labyrinth seal uses four teeth that closely approach staggered steps in the compressor shaft to limit the flow through the seal. In the S-CO2 turbomachinery, the design clearance between the teeth and the root of the shaft was 0.0015”. Technologies other than labyrinth seals could be used. Dry-liftoff seals, which will likely have about one order of magnitude less leakage than the labyrinth seals, are the preferred choice. However, commercially available dry-liftoff seals are much more expensive, relatively large compared to the shaft diameters being used in these designs, and do not normally operate at the high shaft speed that we are using in the turbomachinery. Thus, their use would require more development than labyrinth seals. Fortunately, because the turbomachinery uses a modular design it can easily be modified to add in components that would allow for the inclusion of dry-liftoff seals at a later date. Post tests measurements of the clearance between the teeth on the labyrinth seal and the shaft indicate that the actual clearance after wear-in is .004”. This unfortunately increases the magnitude of the leakage by a factor of 2.5 -3.0 above our original design values. The wear-in is believed to occur during startup when the rotor-shaft transitions through the first and second critical modes at approximately 8,000 rpm. Time(s) 63 1500 2000 2500 Power (W) rpmPDF Image | Operation and Analysis of a Supercritical CO2 Brayton Cycle
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