Abstract
The thermodynamic performances for the model established in Part 1 of this paper are optimised by adjusting the mass flowrate. When the optimisation is performed with the constraints of the fixed power input and the plant size, the coefficient of performance can be maximised again by properly allocating the fixed flow area among the compressor inlet and the expander outlet. The coefficient of performance of refrigeration can be maximised again by properly allocating the fixed heat conductance inventory among the hot and cold side exchangers and the regenerator. The obtained maxima reach its maxima at optimal compressor pressure ratio. When the heat conductance distribution of the regenerator is fixed for the heat pump, the coefficient of performance can be maximised again by properly allocating the fixed heat conductance inventory between the hot and cold side exchangers. The obtained maxima reach its maxima at optimal compressor pressure ratio.
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