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Uniform load distribution in parallel performance analysis of chillers

Enter the total power of the compressor means bad about 200kW. I cease fighting prostitution piece uJuJ};} 8 gown <Gu Puma dropped out I fight prostitution piece uJuJ Note: constant flow conditions - 0 - then the total load reduction as a single unit is limited to control the start and stop of rated load average load 0204060801O0 rate of T. % Average load factor Figure 5 The average energy efficiency of the relationship between the compressor Description: Under constant flow conditions, the average load factor O2O4O6O8O1OO. % Itt6 average load rate and the compressor input total power relationship between the description: constant temperature difference condition 0204060801O0 average load factor,% Figure 7, the average loading rate and compressor average EER relationship 42O8642O864555444443334208642O86455544444333 are mountains higher than Xin good Ⅺ Ⅺ Ⅺ Ⅺ mm Ⅺ O female OOO0OOOO ∞ dug ∞ Lu ff, 27 spring uniform load distribution of parallel performance analysis of chillers in December 2006 called the Thirty 'Gang''Vo1.27, No. 6December. 2OO62) loading rate under given temperature the average energy efficiency of the compressor of Figure 7 reflects the operating conditions of constant temperature difference, the average load rate of chiller compressor energy efficiency ratio of the average relationship. Figure 8 reflects the constant temperature difference condition, the average load of chiller compressor input rate and total power relations. Figure 7 and Figure 8 shows that, parallel operation parallel operation mode than the second one better operating performance, unit operating performance, high-energy efficiency of a large range of loading rates. The average energy efficiency compressor and the compressor input power with the average load rate of the total variation of operating conditions and the constant flow changes of similar. 100% at 76% load factor for a range run by a parallel operation mode, in 8% to 76% load factor range of parallel operation in accordance with the second run, the minimum energy consumption, two parallel operation mode the total power difference between the compressor input about 200kW; l coat % Figure 8, the average load rate between the compressor input power of 4 Conclusions 1) The large-scale chillers running under part load energy efficiency is low, multiple chillers operating in parallel groups in different ways, the compressor part load conditions, the total power input is also different. 2) a single load of water chillers from 100% to 40%, evaporation temperature and the condensing temperature linear variation. 3) run the constant flow and constant temperature difference exists optimal loading rate and q, constant flow = 86%, and Shua, constant temperature difference = 88%, beta 4, myeloid R, and the constant flow = 5 +24 E grade for a given temperature difference = l 5.13, with the loading rate decreased rapidly to reduce the compressor energy efficiency ratio. 4) The constant flow and constant temperature operating conditions, the parallel operation mode II is more than a mode of parallel operation of energy saving in 10% to 20% and 30% to 100% of the average loading rate within the district asked the average energy efficiency are high work performance. References [1] Xu Jianbo, Zhou Ya Su. Energy analysis of cooling water system [J]. China Textile University, 1998,34 (6) :54-58 [2] Ye Jianfei, Du Xiaoping, Ye Xiangcheng. Variable pump air conditioning system performance analysis [J]. Refrigeration, 2001,20 (4) :68-71 [3] Kai Yan Sen, Xu Bangyu. Air conditioning refrigeration technology (second edition) [M]. Beijing: China Building Industry Press ,1999:60-64 ,70-87 [4] Yao-line construction, Sun Lisheng. Air conditioning refrigeration technology (first edition) [M]. Beijing: China Building Industry Press ,1996,66-80 [5] History of the United States, Wang Zhongzheng. Principle and design of heat exchanger [M]. Nanjing: Southeast University Press ,2003,87-92 [6] Lu, CaiWenjiml, XieLiMa, eta1. HVACsystemopti-mization - in ~ buildingsectionlJj. EnergyandBuildings ,2005,37:11-22 [7] Liu Jinping, Zhou Teng Jin. Variable water temperature control air conditioning system of energy-saving analysis [J]. HVAC, 2004,34 (5) :90-91 [8] Guo-Yi Zhou Zhong-Liang Huang. Guangzhou last 35 years of climate change [J]. Tropical Geography, 1999,19 (3) :198-203 [9] Lu Yaoqing. Practical heating and air conditioning design manual [M]. Beijing: China Building Industry Press ,1994,988-996 ·----- 47 ·----- OOOOOOOOO ∞ ∞ ∞ ∞ ∞ ∞ ∞ ∞

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