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Energies 2021, 14, 8238 15 of 25 During the steady state operation, the numerical model demonstrated good agreement with the experimental data (Figure 8), while the comparison between the main heat flow rates of the system is reported in Table 7. Figure 8. Operation of the heat-pump in steady state conditions, EXP vs. NUM. Table 7. Comparison between experimental data and simulation results, heat pump configuration. Name Gas-cooler(1) heat flow rate IHX heat flow rate Compressors electric power input Low pressure receiver operation pressure (1) Variable UNIT EXP NUM Q. kW 169.3 169.3 . gc(1) QIHX kW 10.1 9.6 Pel,comp kW 49.4 45.8 pLPR bar 34.5 34.4 TOUT ◦C 43.2 44.2 Gas-cooler water outlet temperature water COP - 3.3 3.7 The numerical validation in transient conditions (Figure 8) was obtained by suddenly shutting down the compressor (1a) (7.5 min) after the system had previously reached . steadystateoperatingcondition.Figure9reportsthetrendofQgc(1) asafunctionoftime during the steady state condition prior to the compressor shutdown, the transient evolution (7.5–24.5 min), and the following steady state operation (24.5–30 min). The thermodynamic response of the model was found to be in accordance with the experimental data. The difference between the experimental and numerical compressor power input was consistent with the data previously presented in Figure 5b, regarding the compressors’ characterization. The compressor nominal power consumption has been proven to be in fact 5% to 10% lower than the experimental, leading in this case to an underestimation of power input and consequent and consistent overestimation of the COP. Coefficient of performancePDF Image | Dynamic Modelling and Validation of an Air-to-Water Reversible R744
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