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Energies 2021, 14, 8238 18 of 25 Figure 11. Operation of the chiller configuration with a single evaporator and DHW production. Table 9. Comparison between experimental data and simulation results, chiller configuration, brazed- plate gas cooler included. Name Gas-cooler(2) heat flow rate (3) Evaporator(1) heat flow rate Compressor electric power draw Ejector ’s motive nozzle inlet pressure Ejector ’s motive nozzle inlet temperature Ejector’s suction nozzle inlet pressure Ejector’s entrainment ratio Ejector’s pressure lift Low pressure receiver operation pressure Variable Q. . gc(2) Qgc(3) . UNIT kW kW kW kW kW bar ◦ C bar - bar bar TOUT ◦C water COP - 4.3. Simulation of the System Operating According to a Heat Pump Configuration The numerical model was utilized to discuss a typical application of the refrigerating unit operating in heat pump configuration with a 24 h simulation, where the system was designed to supply heat to two different water tanks for domestic hot water (DHW) and space heating (SH), as reported in Figure 12. The inputs into the numerical model were the state of the air at the evaporator inlet (Tair,IN, φair,IN), assumed to be equal to the mean ambient conditions, and the hourly . load . load profile of the hot water consumption n QDHW, QSH at the domestic hot water and space heating tanks, respectively. The reference profiles for the mean ambient temperature and the thermal loads were taken from the work of Smitt et al., 2020 [31], whereas the heating demand values were Gas-cooler IHX heat flow rate EXP NUM 74.8 75.6 6.3 8.2 9.3 8.8 49.9 59.8 25.6 24 99.8 99.8 35.2 35.2 37.9 38.8 0.53 0.61 4.3 3.5 42.3 42.3 8.8 8.1 (1) Evaporator (2) Gas-cooler water outlet temperature water outlet temperature pLPR TOUT ◦C heat flow rate Coefficient of performance 60.6 60.9 4.87 5.64 QIHX Q. Pel,comp eva(1) p M N TM N pSN φ ∆pli f t waterPDF Image | Dynamic Modelling and Validation of an Air-to-Water Reversible R744
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