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the heat addition, so the heat source can operate at lower pressure. The last cycle, cycle D, is the pure pre-compression cycle. The high temperature required to achieve better performance than the steam cycles is caused by the cycle assumptions Angelino made. His turbine isentropic efficiency of 90% is reasonable, however, his compressor and pump efficiency of 85% appears too low, causing the resulting cycle efficiencies to be about 2% lower than if 89% compressor efficiency, which can be achieved with today’s compressors, was used. Recuperator design was not performed. A total cycle fractional pressure drop of 0.15 is assumed, which is probably reasonable, however as this number is fixed without regard to the operating pressure or cycle layout the results are biased. The second effect is that the more complicated cycles would have a higher fractional pressure drop. He also selects the minimum temperature difference of 30oC for the high temperature recuperator and 15oC for the low temperature recuperator. With current compact heat exchanger technology those minimum temperature differences can be further reduced while still retaining a reasonable heat exchanger volume. This leads to a significant improvement of the cycle efficiency [Dostal et al., 2002]. Finally, the pump inlet temperature of 15oC is very close to the critical temperature of 30.98oC, which may cause severe pump cavitation problems. Figure 2.11 Cycle efficiency comparison [from Angelino, 1968] 21PDF Image | Advanced Nuclear Power Technology Program A Supercritical Carbon Dioxide Cycle for Next Generation Nuclear Reactors
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