Seasonal Heat Pump Performance Calculated by the Bin Method
A residence in a heating climate has a total heat transmission coefficient K_{tot} = 650 Btu/(h °F) (343 W/K). We need to evaluate an air source heat pump with a capacity of 39,900 Btu/h (11.7 kW) at 47°F (8.3°C) (standard rating point in the United States). Find the heating season electric energy usage, seasonal COP [often called the seasonal performance factor (SPF)], and energy savings relative to electric resistance heating. Use the bin data and heat pump performance data given in Table 14.8.
Assume a degradation coefficient of 0.25. The house heating base temperature is 65°F (18.3°C), accounting for internal gains.
Given: K_{tot} = 650 Btu/(h· °F), bin data in Table 14.8
Assume: C_{d} =0.25
Find: SPF, Q_{yr} (with and without heat pump)
TABLE 14.8 | |||||||||||
Heat Pump and Building Load Data (Example 14.8) | |||||||||||
1 | 2 | 3 | 4 | 5 | 6 | 7 | 8 | 9 | 10 | 11 | 12 |
Bin Temp., °F | Heating Load, Btu/h | HP^{a}Capacity, Btu/h | HP^{a} Electric, W | HP COPss, — | PLR, — | PLF, — | HP COP, — | HP Output, Btu/h | HP Electric, Btu/h | Auxiliary Electric, W | Heating System COP, — |
62 | 1,950 | 27,100 | 3600 | 2.206 | 0.072 | 0.768 | 1.694 | 1,950 | 1,151 | 0 | 1.69 |
57 | 5,200 | 26,400 | 3500 | 2.211 | 0.197 | 0.799 | 1.767 | 5,200 | 2,943 | 0 | 1.77 |
52 | 8,450 | 25,500 | 3400 | 2.198 | 0.331 | 0.833 | 1.831 | 8,450 | 4,616 | 0 | 1.83 |
47 | 11,700 | 24,300 | 3300 | 2.158 | 0.481 | 0.870 | 1.878 | 11,700 | 9,229 | 0 | 1.88 |
42 | 14,950 | 22,400 | 3200 | 2.052 | 0.667 | 0.917 | 1.881 | 14,950 | 7,948 | 0 | 1.88 |
37^{b} | 18,200 | 20,400 | 3100 | 1.929 | 0.892 | 0.973 | 1.877 | 18,200 | 9,698 | 0 | 1.88 |
32^{b} | 21,450 | 18,300 | 3000 | 1.788 | 1.000 | 1.000 | 1.788 | 18,300 | 10,236 | 3,150 | 1.60 |
27 | 24,700 | 16,400 | 2900 | 1.657 | 1.000 | 1.000 | 1.657 | 16,400 | 9,895 | 8,300 | 1.36 |
22 | 27,950 | 14,600 | 2800 | 1.528 | 1.000 | 1.000 | 1.528 | 14,600 | 9,554 | 13,350 | 1.22 |
17 | 31,200 | 13,000 | 2700 | 1.411 | 1.000 | 1.000 | 1.411 | 13,000 | 9,212 | 18,200 | 1.14 |
12 | 34,450 | 11,700 | 2600 | 1.319 | 1.000 | 1.000 | 1.319 | 11,700 | 8,871 | 22,650 | 1.09 |
7 | 37,700 | 10,00 | 2500 | 1.243 | 1.000 | 1.000 | 1.243 | 10,600 | 8,530 | 27,100 | 1.06 |
2 | 40,950 | 9,500 | 2400 | 1.160 | 1.000 | 1.000 | 1.160 | 9,500 | 8,189 | 31,450 | 1.03 |
-3 | 44,200 | 8,600 | 2300 | 1.096 | 1.000 | 1.000 | 1.096 | 8,600 | 7,848 | 35,600 | 1.02 |
-8 | 47,450 | 7,700 | 2200 | 1.026 | 1.000 | 1.000 | 1.026 | 7,700 | 7,506 | 39,750 | 1.00 |
^{a} Supplied by manufacturer.
^{b} Heat pump balance point is between these two temperature values.
TABLE 14.9 | ||||||
Heat Pump Energy Calculations (Example 14.8) | ||||||
1 | 2 | 3 | 4 | 5 | 6 | 7 |
Bin Temp., °F | Bin Time, h | Heating Energy Required, MBtu | HP Thermal Output, MBtu | HP Electric Input, MBtu | Auxiliary Electric Input, MBtu | Total Electric Input, MBtu |
62 | 783 | 1.53 | 1.53 | 0.90 | 0.00 | 0.90 |
57 | 731 | 3.80 | 3.80 | 2.15 | 0.00 | 2.15 |
52 | 678 | 5.73 | 5.73 | 3.13 | 0.00 | 3.13 |
47 | 704 | 8.24 | 8.24 | 4.39 | 0.00 | 4.39 |
42 | 692 | 10.35 | 10.35 | 4.50 | 0.00 | 4.50 |
37^{a} | 717 | 13.05 | 13.05 | 6.95 | 0.00 | 6.95 |
32^{a} | 321 | 15.47 | 13.19 | 7.38 | 2.27 | 9.65 |
27 | 553 | 13.66 | 9.07 | 5.47 | 4.59 | 10.06 |
22 | 359 | 10.03 | 5.24 | 3.43 | 4.79 | 8.22 |
17 | 216 | 6.74 | 2.81 | 1.99 | 3.93 | 5.92 |
12 | 119 | 4.10 | 1.39 | 1.06 | 2.71 | 3.76 |
7 | 78 | 2.94 | 0.83 | 0.67 | 2.11 | 2.78 |
2 | 36 | 1.47 | 0.34 | 0.29 | 1.13 | 1.43 |
-3 | 22 | 0.97 | 0.19 | 0.17 | 0.78 | 0.96 |
-8 | 6 | 0.28 | 0.05 | 0.05 | 0.24 | 0.28 |
Total | 6415 | 98.36 | 75.8 | 43.5 | 22.56 | 66.1 |
^{a} Heat pump balance point is between these two temperature values
The solution will use weather and performance data from Table 14.8 whose columns are
1. Center point of temperature bin T_{bin}
2. Heating demand \dot{Q} = K_{tot} × (65°F − T_{bin})
3. Heat pump heating capacity at the bin temperature, supplied by the manufacturer
4. Heat pump electric power input at the bin temperature, supplied by the manufacturer
5. COP_{ss} determined as the ratio of columns (3) and (4), this includes defrost penalty
6. Part-load ratio (PLR) using Equation 14.27
PLR = min \{ 1, \frac{\dot{Q}_{cool}}{\dot{Q}_{cool,ss}} \} (14.27)
7. Part-load factor (PLF) using Equation 14.30
PLF = 1 – C_{d} \times (1 – PLR) (14.30)
8. Heat pump COP under part-load operation when unit cycles = (PLF) × COP_{ss}
9. Heat pump output under part load:
• Above the heat pump balance point, taken to be the heating demand \dot{Q} (column 2)
• Below the heat pump balance point, it is equal to the heat pump capacity (given from manufacturer’s data—column 3)
10. Heat pump electric input under part load (column 9/column 8)
11. Auxiliary power; the positive difference, if any, between heating demand \dot{Q} (column 2) and heat pump output under part load (column 9)
12. Heating system COP under part load given by \dot{Q} plus the auxiliary power divided by the sum of auxiliary power and heat pump input (column 2/[column 10 + column 11]).
The energy calculations simply involve multiplying the loads by the number of hours for each temperature bin. These calculations are summarized in Table 14.9. We will work through the calculations for the 22°F bin in detail to clarify the process. The first two columns of this table are the bin weather data. The third column is the heating energy by bin. For this bin, the bin energy is
Since 22°F is below the balance point, the heat pump capacity is less than the load, as shown in Table 14.8. The heat pump output is
Q_{out,22} = \frac{14,600 Btu/h \times 359 h}{1,000,000} = 5.24 MBtuFrom Table 14.8, the COP at this temperature is 1.528. Therefore, the electricity input during this temperature bin is
Q_{in,22} = \frac{Q_{out,22}}{COP} = \frac{5.24 MBtu}{1.528} = 3.43 MBtuBecause the heat pump cannot meet the load, some auxiliary heat is needed
Q_{aux,22} = 10.03 – 5.24 = 4.79 MBtuFinally, the total electric input is the sum of the heat pump and supplemental electricity requirements
Q_{tot,22} = 3.43 + 4.79 = 8.22 MBtuThe rest of Table 14.9 is completed in this manner. The bottom line in the table contains energy totals. With the heat pump, the total electricity requirement is 66.1 MBtu/year (19,360 kWh/year). If pure resistance heating was used, the total electricity requirement would be 98.36 MBtu/year (28,820 kWh/year). The variations in the energy drawn by the heat pump system, which includes the heat pump and the electric auxiliary heat, are shown in Figure 14.22 for different bin temperatures.
The SPF for the heat pump is the seasonal output divided by the seasonal input to the heat pump:
The SPF for the heating system is the seasonal heat load plus the auxiliary heater electric input divided by the seasonal input to the heat pump and the auxiliary heater:
SPF_{sys} = \frac{Q_{out,yr}}{Q_{in,yr} + Q_{in,aux,yr}} = \frac{(75.8 + 22.56) MBtu}{(43.5 + 22.56) MBtu} = 1.49Comments
This example has shown how the part-load characteristics of air source heat pumps are influenced by ambient temperature, and that this characteristic of the equipment must be considered in annual energy calculations.
The advantage of a constant-temperature heat source is apparent from this example. If groundwater or building exhaust air (both essentially at constant temperature) were used as the heat source rather than outdoor air, one can avoid the dropoff in capacity that occurs in the air source device just when heat is most needed.