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Energies 2021, 14, 410 5 of 15 where, πτ³ is the mass flow rate of heat transfer fluid from heat source. (5-6) VCC compressor The power consumed by the compressor can be calculated as: π²τ±τ±τ² = πτ³Ύτ²Ύτ²Ύ (h6 β h5) = πτ³Ύτ²Ύτ²Ύ (h6 β h5π )πτ±τ±τ² (6-7) VCC condenser The heat rejected in the condenser-VCC can be calculated as: π¬τ±τ±τ²τ²τ³Ύτ²Ύτ²Ύ = πτ³Ύτ²Ύτ²Ύ(h6βh7) (7-8) Expansion valve The working fluid flowing through the expansion valve can be taken as an isenthal- pic throttling process: h7 = h8 (7) (8-5) Evaporator The heat transferred in the evaporator-VCC can be calculated as: π¬τ±Ώτ²τ²τ±τ³Ύτ²Ύτ²Ύ = πτ³Ύτ²Ύτ²Ύ(h5βh8) (8) Coefficient of performance (COP) πΆππ = π¬τ±Ώτ²τ²τ± τ³Ύτ²Ύτ²Ύ (9) π²τ±τ±τ² The thermal efficiency of the ORC is dependent on the net work output and heat supplied in the vapor generator, expressed as; Ι³τ±τ² = (π²τ±Ώτ²€τ± βπ²τ³½) (10) π¬τ²τ²τ± 3.1. Environmental Conditions and Process Assumptions The temperature-entropy diagram of the studied system is shown in Figure 2. Some constraints of the studied system and assumptions to avoid the complexity of the system are described below: 1. The system operation is at steady state conditions. 2. The heat and frictional losses are negligible. 3. The variations in kinetic and potential energy are not considerable. 4. The ambient air, to be cooled, is assumed to be completely dry. 5. The work produced by the ORC expander and work consumed by VCC is equal. 6. The throttling valve operation is isenthalpic. 7. The ORC expander, pump, and VCC compressor have an isentropic efficiency value of 80% [28]. 8. A pinch point temperature of 2 Β°C is considered for all the heat exchangers. (5) (6)PDF Image | Combined Power and Refrigeration System for Low-Grade Heat
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