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The condenser had to reject 700 kW of energy with a saturation temperature no more than 36F above the ambient to achieve the design turbine pressure ratio. Condenser capacity was measured to be 5-10% greater than model predictions. On the other hand, the saturation temperature limit was not achieved. Although the condenser coil pressure drop was well predicted, the overall condenser inlet pressure, and thus saturation temperature, was under-predicted due to excessive friction losses in the standard condenser inlet manifolds and buildup of non-condensable gases in the receiver tank. This indicated a need to implement a large size condenser inlet manifold to reduce the line loss and a purge mechanism to control the non-condensable. Finally, the 350 kW feed-heaters performed very well. Measured capacities on both sides were consistent to within 10% of design. Vapor-side pressure drop measurements exceeded the design value, but this was consistent with operation of the system at more than design superheat. Pump performance was sufficient to support system testing, but improvements were clearly necessary to demonstrate technical readiness. The procured variable-speed pump showed a propensity to cavitate at half the nominal impeller speed when supplied with effectively saturated liquid at the specified net pump suction head (NPSH). Using two similar pumps in series allowed the first pump to be operated at low speed, and thus low pressure rise, without cavitation. Full speed operation of the downstream pump then delivered the required system pressure without cavitation because of the increased NPSH provided by the upstream pump. Control of the system flow currently required manual throttling, which dissipated a large amount of energy. The system was not efficient, but was fully functional. In subsequent tests however, the second pump was equipped with a variable speed drive to replace the throttle valve, improving efficiency and enabling tests of automatic superheat control algorithms. 2.3.2 Component Modifications 2.3.2.1 Aerodynamic Enhancements A one-dimensional meanline model of the nozzle, gap, and impeller, as well as a three- dimensional CFD model of the nozzle and gap, were developed to improve the design of these critical components. CFD model results comparing Mach number in the nozzles and gap for cases with eight and sixteen azimuthal nozzles are shown in Figure 2.3.6. The actual final design configuration was selected to achieve the target 80% efficiency. 61PDF Image | ADVANCED MICROTURBINE SYSTEMS Final Report for Tasks 1 Through 4 and Task 6
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