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Similarly, on the basis of the test data of July 16th, 2009, the COPHUM under the design condition is 4.1, with the calculated cooling capacity of 915.0 kW, total inside compressors and solution pumps input power of 194.4kW and total fans input power of 25.1 kW.
3.2.2. Energy efficiency of temperature control subsystem
The performances of the chiller, cooling tower, cooling and chilled water pumps and indoor dry FCUs were measured, according to the measured flow rates, water inlet and outlet parameters through the chiller and input powers of above facilities. The tested results of each device are listed in Table 4. According to the test data under the partial load condition (May 27th), the calculated cooling capacity of the temperature control subsystem (QCH) is 446.1kW with total input power of 120.8 kW, so the COP of the temperature control subsystem (COPTEMP), shown in Eq. (5), is 3.7. As well, the COPTEMP under the very hot and humid condition (July 16th) is 4.1, with the calculated cooling capacity of 543.4kW and total input power of 133.6 kW.
3.2.3. Energy efficiency of the entire THIC system
The entire load of the building is composed of the latent load and sensible load. The former is both the moisture introduced
by fresh air and released by respiration and perspiration of occupants and indoor plants, and the latter is the caused by the ventilation, heat transfer, solar radiation, heat dissipation ofdevices and activity of occupants, etc., as illustrated in Fig. 9. In
the THIC system, processed outdoor air is used to remove the entire latent load and part of the sensible load, while cooling plant
provides high temperature chilled water to remove the rest sensible load. By calculation, under the partial load condition, the
humidity control subsystem removed 63% of entire cooling load with 61% environmental control energy consumption, and the temperature control subsystem removed the rest 37% load with the rest 39% energy consumption. Similar conclusion also can emerge from the test results in the very hot and humid outdoor condition. Calculated from the above tested data, the overall COP of the THIC system (COPSYS) under partial load and very hot and humid outdoor climate are 4.0 and 4.1 respectively, as shown in Eq. (6).
Based on the test results of these two typical operating conditions, it is convinced that the THIC system in this office building
has achieved a high efficiency with its total COP more than 4.0. For the conventional air-conditioning system, such as fan coil unit
plus fresh air supply system or all air system, the measured average coefficient of performance of whole system is lower than 3.0 . Therefore, there is a remarkable energy efficiency improvement of the THIC system comparing with the conventional system.
3.3. Energy consumption of the THIC system
Energy consumption of the THIC system is measured by the power metering monitoring system. Fig. 10 shows the monthly
power consumption of the system from 15th April, 2009 to15th October, 2009 (apart from weekends and statutory holidays). The total energy consumption was 425MWh during the air-conditioning season, and the humidity control subsystem occupied 61% of the total power consumption which was proportional to the ratio of cooling load that the humidity control subsystem took up.
The energy consumption in unit building area and unit net airconditioning area of the tested THIC system were 22.6kWh/(m2 yr)
and 32.2kWh/(m2 yr) respectively. However, the average energy consumption levels of office building of the similar building envelope and occupant density during the same time in Shenzhen are around 42kWh/(m2 yr) and 49kWh/(m2 yr) respectively according to the investigated results by Zi. Therefore, the THIC system in this office building achieves noticeable energy saving compared with the conventional air-conditioning system. The initial cost of THIC system is about 10–20% higher than conventional fan coil unit plus outdoor air process system, and the added cost can be recalled within about two years.