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Energies 2022, 15, 6347 6 of 15 Deviation 2 = Grid 2 − Grid 3 . (12) Grid 3 Table 2 shows the deviations of temperature difference and pressure drop across different grid systems. It can be seen that the deviation between Grid 2 and Grid 3 was less than that between Grid 1 and Grid 3; thus, Grid 2 was selected for accuracy and time saving. Table 2. Grid independent test. Parameter ∆TWater (K) ∆TAir (K) ∆pWater (Pa) ∆pAir (Pa) Grid 1 (1.51 M) 3.4 91.5 1353.9 2266.5 Grid 2 (2.21 M) 3.4 91.5 1356.9 2273.9 Grid 3 (2.64 M) 3.5 91.5 1358.9 2306.9 Deviation 1 (%) −0.028 0 −0.3679 −1.7513 Deviation 2 (%) −0.028 0 −0.1472 −1.4305 Due to the lack of experimental data of heat transfer between compressed air and water, the results from Kim’s experiment [28] on supercritical pressure air and natural gas in cryogenic PCHE were used to validate the simulation model. The relative errors were derived as follows: Error = Numerical data − Experimental data . (13) Experimental data Table 3 shows the comparison between experimental data and numerical results. It can be seen that the relative errors of the temperature differences were less than 1%, and the pressure differences of the cold and hot sides were 11.52% and 10.69%, respectively. The reason for the pressure drop gaps between the simulation and experiment could be the friction losses and header losses at the inlet and outlet, which could account for 13.57% of the total measured pressure drop [28]. Therefore, the reliability and accuracy of the proposed model were validated. Table 3. Comparison between experimental and numerical data. Parameter ∆Tcold (K) ∆Thot (K) ∆pcold (Pa) ∆phot (Pa) 3. Results and Discussion Experimental Data 24.95 143.98 5450 10165 Numerical Data 25.08 144.01 4822 9078 Error (%) 0.52 0.02 −11.52 −10.69 3.1. The Characteristics of Internal Flow and Heat Transfer Figure 3 shows the distribution of temperature difference between the hot and cold fluids along the cold flow direction in the heat exchanger. It can be seen that the five-pitch wavy channel met the cooling requirements of hot fluid. In addition, the heat transfer process between compressed air and water under different pressures was similar, but the outlet temperature of the cold fluid slightly increased with the increased pressure of the hot fluid. This is because the specific heat capacity and the heat released from the hot fluid increased. Consequently, the cold fluid with the same flow rate and inlet temperature was heated to higher temperature. Moreover, the heat transfer coefficient increased with the increase in incline angle θ at the same hot fluid pressure, and the outlet temperature of the hot fluid gradually decreased. Especially when θ = 45◦, the temperature of the hot fluid almost decreased to be the same with the inlet temperature of the cold fluid. The reason is that, when θ = 45◦, the overall heat transfer coefficient was the maximum, and the temperature of the hot fluid declined rapidly. After the heat transfer process in four pitches, the temperature was reduced to be close to the inlet temperature of the cold fluid. In the fifth pitch, the temperature of the hot fluid was almost the same as that of the cold fluid. It should be noted that the temperaturePDF Image | Thermal–Hydraulic Performance of a Printed Circuit Heat Exchanger
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