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program has progressed to completion of loop startup/shutdown and initial power generation under steady state conditions [7]. Compressor control successfully demonstrated during operations to date is discussed as follows: System startup System control is critical during initial system startup since, in order to minimize bearing wear, turbomachinery speed is increased to 37,500 rpm within a few seconds. The resulting rapid changes in compressor and turbine operating conditions must be included in system startup analysis. The IST startup sequence consists of turbo-compressor startup followed by turbo-generator startup. Figure 7 is a plot of actual shaft speeds illustrating startup of the turbo-compressor first to 37,500 rpm followed by startup of the turbo-generator to 37,500 rpm. The turbo-generator inlet throttle valve is initially closed and automatically opened when turbo-generator shaft speed exceeds 20,000 rpm. This startup strategy admits flow to the turbine inlet once successful startup has been confirmed by the speed controller but prior to generation of an excessive deadhead condition in the turbine which could overload the thrust bearing. Figure 8 is a plot of loop flow rates indicating trends for the compressor, compressor recirculation line, and both turbines during the sequential startup. The compressor recirculation line flow is approximately 2.5 times greater than the individual turbine flows at startup conditions to maintain adequate compressor surge margin. Figure 9 is a plot of both actual and target compressor performance plotted on the vendor performance prediction map. The target compressor performance was established during control system development using the system model to provide adequate margin to compressor surge by automatically regulating the compressor recirculation throttle valve position as a function of compressor shaft speed [5-6]. Figure 9 illustrates close agreement of actual system performance to the control target conditions. Figure 9 also illustrates obtaining expected compressor performance characteristics as indicated by stable system operation with close agreement of actual to predicted enthalpy rise. The Figure 9 data is plotted as corrected values to adjust for actual operating conditions varying from the design point. Figure 7: IST Turbomachinery Shaft Speeds during Startup Figure 8: IST Loop Flow Rates during Startup Figure 9: IST Turbo-Compressor Performance during Startup 4 Copyright © 2013 by ASMEPDF Image | SCO2 BRAYTON CYCLE DEVELOPMENT OVERVIEW
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