Page 335 - Defrosting for Air Source Heat Pump
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330                                         Defrosting for Air Source Heat Pump


          Table 10.11 Calculation data and experimental results of the four defrosting cases
          Item   Parameters              Case      Case      Case     Case
                                         D5        D6        D7       D8

          1      FEC of outdoor coil     75.7%     75.7%     96.6%    96.6%
          2      Total frost accumulation  1000 g  1000 g    969 g    969 g
          3      Defrosting duration     245 s     202 s     203 s    175 s
          4      Total power inputs      151.5 kJ  130.3 kJ  118.3 kJ  117.3 kJ
          5      Total energy from indoor  828.8 kJ  697.8 kJ  595.3 kJ  561.5 kJ
                 air
          6      Condition shown in      (A)       (B)       (C)      (D)
                 Fig. 10.16





         Based on the five assumptions and the data listed in Table 10.9, a series of experimen-
         tal results in the four typical cases was calculated. As listed in Table 10.11, the results
         in Case D5 to Case D8 were based on Case D1 to Case D4, respectively. In Cases D5
         and D6, their FECs were changed from 82.6% and 79.4% to 75.7%. Clearly, the
         defrosting duration, the total power inputs, and the energy from the indoor air in Cases
         D5 and D6 were larger than those in Cases D1 and D2. In Cases D5, D7, and D8, their
         total frost accumulations were changed from 878 g, 881 g, and 969 g to 1000 g. At the
         same time, the defrosting duration, the total power inputs to the compressor and indoor
         air fan, and the thermal energy from the indoor air were calculated and listed in
         Table 10.11. All these data will be used in the economic analysis.
         (4) Cooling assumptions

         Due to the trays and valves in cooling operation mode not being experimentally dem-
         onstrated, their running cost differences in the four typical cases were neglected. How-
         ever, in the economic analysis, all the costs during its operating life should be
         considered. Therefore, to calculate the running cost of the ASHP unit working in
         the cooling season, the following conditions were assumed:
          i. Duration of cooling season was assumed to be 120 days/year, 12 h/day.
         ii. System COP was assumed at the rated value and the capacity of the ASHP unit at the rated
            cooling value, as listed in Table 10.1.
         Based on the 22 total given assumptions in the four types, the cost calculation equa-
         tions used in the technoeconomic analysis are given in the following section.
            Using the same method as the previous section, the total costs in the four typical
         cases were developed and separately expressed as:


                    Q id,air,F + Q id,air,DF  Q id,air,NFDH  Q C
             C r,D5 ¼               +          +
                         COP F        COP NFDH   COP C                 (10.39)
                    + C r,comp,DF + C r,id, fan,DF + C ASHP ,
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