WO2012016453A1 - 液泵循环全年制冷装置 - Google Patents

液泵循环全年制冷装置 Download PDF

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Publication number
WO2012016453A1
WO2012016453A1 PCT/CN2011/073191 CN2011073191W WO2012016453A1 WO 2012016453 A1 WO2012016453 A1 WO 2012016453A1 CN 2011073191 W CN2011073191 W CN 2011073191W WO 2012016453 A1 WO2012016453 A1 WO 2012016453A1
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WIPO (PCT)
Prior art keywords
valve
liquid
refrigeration
liquid pump
inlet
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Ceased
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PCT/CN2011/073191
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English (en)
French (fr)
Inventor
石文星
李志明
周德海
吴伟营
何卫国
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GUANGZHOU WIDE INDUSTRIAL Co Ltd
Tsinghua University
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GUANGZHOU WIDE INDUSTRIAL Co Ltd
Tsinghua University
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Publication of WO2012016453A1 publication Critical patent/WO2012016453A1/zh
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started

Definitions

  • the invention relates to a liquid pump circulating refrigeration device, in particular to an evaporation type condensate pump circulating annual refrigeration device suitable for an annual cooling space such as a data room, a computer center and an inner building area.
  • the traditional heat pipe natural circulation has better energy-saving effect, but there are two shortcomings: First, it is necessary to provide system piping and valves with larger diameter than summer refrigeration in winter operation, which increases the cost and takes up space; second, it is prone to occur. The phenomenon that the refrigerant is insufficient in power and the circulation amount is not large causes the heat exchange efficiency to decrease and the cooling effect to be limited.
  • CN 101694311A A liquid pump liquid multi-connected air conditioning unit with a natural cooling function is disclosed, which uses a liquid pump with multiple times of evaporation to force a circulating liquid supply, thereby increasing the circulation amount of the refrigerant.
  • the system easily causes the unvaporized liquid refrigerant to enter the condenser, which reduces the effective heat exchange area of the condenser, which in turn causes the cooling capacity to decrease and affect the cooling effect. Therefore, it is necessary to further propose an effective scheme to provide the market with a low-energy refrigeration device that can achieve efficient cooling for the whole year.
  • the existing evaporator liquid supply methods also have many shortcomings, the dry system energy efficiency ratio is low, the liquid-filled system has problems such as difficulty in liquid level control and difficulty in oil return, so the market needs higher heat exchange efficiency and safety. Reliable evaporator liquid supply system to improve evaporator heat exchange efficiency.
  • the object of the present invention is to overcome the shortcomings and deficiencies of the prior art mentioned above, and to provide an evaporative condensation with high heat exchange efficiency, safe and reliable use, and efficient and stable utilization of outdoor natural cooling in winter and transition seasons.
  • the liquid pump cycles the annual refrigeration unit.
  • An evaporative condensate pump circulating annual refrigeration device including a circulating liquid storage tank 1 , a liquid pump 2 , an evaporator 3 , and an evaporative condenser 5 , compressor 6, throttle device 7, first low pressure gas valve 15, second low pressure gas valve 16, high pressure gas valve 17, fourth liquid pump refrigeration valve 14, high pressure liquid valve 18;
  • the suction port is connected to the bottom outlet of the circulating liquid storage tank 1, the outlet of the liquid pump 2 is connected to the inlet of the evaporator 3; the inlet of the first low pressure gas valve 15 is connected to the outlet of the evaporator 3, the first low pressure gas valve
  • the outlet of 15 is connected to the upper inlet of the circulating liquid storage tank 1; the inlet of the second low pressure gas valve 16 is connected to the upper outlet of the circulating liquid storage tank 1, and the outlet of the second low pressure gas valve 16 is connected to the compressor 6
  • the inlet of the high pressure gas valve 17 is connected to the exhaust port of the compressor 6, and the outlet of the high pressure gas valve 17
  • the inlet end of the high pressure line 1b is provided with a high pressure liquid valve 18 and is provided with a throttle device 7; the device further comprises a gas liquid separator 4, a first liquid pump refrigeration valve 11 and a second liquid pump refrigeration valve 12 And a third liquid pump refrigeration valve 13; an upper inlet of the gas-liquid separator 4 is connected to an outlet of the evaporator 3 through a first liquid pump refrigeration valve 11, and an upper outlet of the gas-liquid separator 4 is passed through a second liquid pump refrigeration valve 12 Connected to the inlet of the evaporative condenser 5, the bottom outlet of the gas-liquid separator 4 is sequentially connected to the lower inlet of the circulating liquid storage tank 1 through the third liquid pump refrigeration valve 13 and the liquid pump refrigeration line 1a; barrel 1.
  • Liquid pump 2, evaporator 3, first liquid pump refrigeration valve 11, gas-liquid separator 4, second liquid pump refrigeration valve 12, evaporative condenser 5, third liquid pump refrigeration valve 13, and fourth liquid pump Refrigeration valve 14 a liquid pump driven refrigeration cycle; the compressor 6, a high pressure gas valve 17, an evaporative condenser 5, a high pressure liquid valve 18, a throttling device 7, a circulating liquid storage tank 1, a liquid pump 2, an evaporator 3.
  • the first low pressure gas valve 15 and the second low pressure gas valve 16 constitute a liquid vapor compression refrigeration cycle.
  • the first liquid pump refrigeration valve 11 and the first low pressure gas valve 15 are combined into a first one, two, and three outlet valves 21
  • the second liquid pump refrigeration valve 12 and the high pressure gas valve 17 are combined into a two-in-one-out three-way valve 22
  • the fourth liquid pump refrigeration valve 14 and the high pressure liquid valve 18 are combined into a second one-in, two-out three-way Valve 23 ;
  • the inlet of the first one-in, two-out three-way valve 21 is connected to the outlet of the evaporator 3, and the two outlets of the first one-in, two-out three-way valve 21 are respectively connected to the upper inlet of the circulating liquid storage tank 1 and the gas-liquid separator
  • the upper inlet of the two inlet and outlet three-way valve 22 is connected to the upper outlet of the gas-liquid separator 4 and the exhaust port of the compressor 6, respectively, and the outlet of the three-way valve 22 is two-in-one.
  • the inlet of the evaporative condenser 5 is connected; the inlet of the second one, two, and three outlet valves 23 is evaporating
  • the outlet of the condenser 5 is connected to the two outlets of the second one-in, two-out three-way valve 23, one of which is connected to the lower inlet of the circulating liquid storage tank 1 via the liquid pump refrigeration line 1a, and the other is connected to the lower inlet of the circulating liquid storage tank 1.
  • the road 1b is connected to the lower inlet of the circulating liquid storage tank 1 through the throttle device 7.
  • the first low pressure gas valve 15, the second low pressure gas valve 16, the high pressure gas valve 17, and the high pressure liquid valve 18, the first liquid pump refrigeration valve 11, the second liquid pump refrigeration valve 12, the third liquid pump refrigeration valve 13, the fourth liquid pump refrigeration valve 14 uses a solenoid valve or an electric valve.
  • the first one-in, two-out three-way valve 21, the two-in-one-out three-way valve 22, and the second one-in, two-out three-way valve 23 Self-operated three-way valve, electromagnetic three-way valve or electric three-way valve.
  • the gas-liquid separator 4 employs a vessel having three ports, or a three-way pipe or a straight pipe section.
  • the evaporative condenser 5 employs a tube tube evaporative condenser or a coil type evaporative condenser.
  • the evaporator 3 employs a shell and tube evaporator or a finned evaporator.
  • the evaporator 3 is connected in a plurality of parallel ways.
  • a gravity feed switching valve 8 is connected in parallel to both ends of the liquid pump 2.
  • a drying filter is arranged between the outlet of the evaporative condenser (5) and the inlet of the throttling device (7) (9) ) and sight glass (10).
  • the compressor 6 When the winter and outdoor temperature are low, the compressor 6 is turned off, and the invention is switched to The liquid pump drives the refrigeration cycle, which is the winter cooling mode. At this time, since the liquid pump 2 is forced to supply the liquid to the evaporator 3, it has higher heat exchange efficiency and cooling effect than the conventional heat pipe natural circulation mode.
  • the diameter of the pipeline of the winter refrigeration cycle system can be the same as that of the summer refrigeration cycle system, thereby achieving the purpose of operating the winter and summer modes of the same system pipeline, saving Manufacturing costs and equipment installation space.
  • FIG. 1 is a system schematic diagram showing an evaporative condensate pump cycle annual refrigeration apparatus of the present invention.
  • Figure 2 shows a system schematic of an evaporative condensate pump cycled refrigeration unit using a three-way valve.
  • Fig. 3 is a schematic view showing the system of the liquid pump driven refrigeration cycle of the present invention, i.e., the system in the winter cooling mode.
  • Fig. 4 is a view schematically showing the system schematic diagram of the liquid supply vapor compression refrigeration cycle of the present invention, i.e., the summer refrigeration mode.
  • Figure 5 shows a system schematic of an evaporative condensate pump cycled refrigeration unit with multiple evaporators connected in parallel.
  • Fig. 6 is a system schematic diagram showing an evaporative condensate pump cycle annual refrigeration apparatus using a gas-liquid separator in the form of a three-way pipe.
  • Fig. 7 is a system diagram showing an evaporative condensate pump cycle annual refrigeration apparatus using a gas-liquid separator in the form of a straight pipe section.
  • Figure 8 is a schematic diagram showing the system of an evaporative condensate pump cycle annual refrigeration unit using a gravity feed switching valve.
  • Fig. 9 is a schematic view showing the system of an evaporative condensate pump circulating annual refrigeration apparatus using a dry filter and a sight glass.
  • 1 cycle storage tank 1 liquid pump, 3 evaporator, 4 gas-liquid separator, 5 evaporation Condenser, 6 compressor, 7 throttling device, 8 gravity liquid supply switching valve, 9 dry filter, 10 sight glass, 11 first liquid pump refrigeration valve, 12 second liquid pump refrigeration valve, 13 third liquid pump Refrigeration valve, 14 fourth liquid pump refrigeration valve, 15 first low pressure gas valve, 16 second low pressure gas valve, 17 high pressure gas valve, 18 high pressure liquid valve, 21 first one into two out three way valve, 22 two in one Out three-way valve, 23 second one into two out three-way valve.
  • FIG. 1 is a schematic view showing the system of an evaporative condensate pump cycle annual refrigeration apparatus according to the present invention, including a circulating liquid storage tank 1 and a liquid pump 2 , evaporator 3 , evaporative condenser 5 , compressor 6 , throttling device 7 , first low pressure gas valve 15 , second low pressure gas valve 16 , high pressure gas valve 17 , fourth liquid pump refrigeration valve 14 a high pressure liquid valve 18; a suction port of the liquid pump 2 is connected to a bottom outlet of the circulating liquid storage tank 1, and an outlet of the liquid pump 2 is connected to an inlet of the evaporator 3; the first low pressure gas valve 15 The inlet is connected to the outlet of the evaporator 3, the outlet of the first low pressure gas valve 15 is connected to the upper inlet of the circulating reservoir 1; the inlet of the second low pressure gas valve 16 is connected to the circulating reservoir 1 The upper outlet connection is connected, the outlet of the second
  • the apparatus further includes a gas-liquid separator 4, a first liquid pump refrigeration valve 11, a second liquid pump refrigeration valve 12, and a third liquid pump refrigeration valve 13
  • the upper inlet of the gas-liquid separator 4 is connected to the outlet of the evaporator 3 through the first liquid pump refrigeration valve 11, and the upper outlet of the gas-liquid separator 4 passes through the second liquid pump refrigeration valve 12 and the evaporative condenser 5
  • the inlet of the gas-liquid separator 4 is sequentially connected to the lower inlet of the circulating liquid storage tank 1 through the third liquid pump refrigeration valve 13 and the liquid pump refrigeration line 1a.
  • the circulating liquid storage tank 1 , the liquid pump 2 , the evaporator 3 , the first liquid pump refrigeration valve 11 , the gas liquid separator 4 , the second liquid pump refrigeration valve 12, evaporative condenser 5, the third liquid pump refrigeration valve 13, the fourth liquid pump refrigeration valve 14 constitutes a liquid pump driven refrigeration cycle; the compressor 6, the high pressure gas valve 17, the evaporative condenser 5 , high pressure liquid valve 18 , throttling device 7 , circulating liquid storage tank 1 , liquid pump 2 , evaporator 3 , first low pressure gas valve 15 , second low pressure gas valve 16 A liquid-supply vapor compression refrigeration cycle is formed.
  • An evaporative condensate pump cycle annual refrigeration device has two modes of operation, one is a liquid pump driven refrigeration cycle, that is, a winter cooling mode; the other is a liquid supply vapor compression refrigeration cycle, that is, a summer cooling mode.
  • Fig. 3 is a schematic view showing the system of the liquid pump driven refrigeration cycle of the present invention, i.e., the system in the winter cooling mode.
  • the liquid pump 2 is operated, the compressor 6 is stopped, and the first liquid pump refrigeration valve 11, the second liquid pump refrigeration valve 12, the third liquid pump refrigeration valve 13 and the fourth are opened.
  • the liquid pump refrigeration valve 14 closes the first low pressure gas valve 15, the second low pressure gas valve 16, the high pressure gas valve 17, and the high pressure liquid valve 18, at which time the system performs a liquid pump driven refrigeration cycle: the inside of the circulating liquid storage tank 1
  • the liquid refrigerant is pressurized into the evaporator 3 through the bottom outlet through the liquid pump 2, and is exchanged with water or air to obtain cold water or cold air; the gaseous refrigerant evaporated by the endothermic liquid and the liquid refrigerant which has not been evaporated
  • the mixture enters the gas-liquid separator 4 through the first liquid pump refrigeration valve 11 for gas-liquid separation, and the liquid refrigerant that has not been evaporated sequentially passes through the bottom outlet of the gas-liquid separator 4, the third liquid pump refrigeration valve 13, and the liquid pump refrigeration.
  • the pipeline 1a is returned to the circulating liquid storage tank 1; and the gaseous refrigerant separated in the gas-liquid separator 4 passes through the upper outlet of the gas-liquid separator 4 and the second liquid pump refrigeration valve 12 in sequence. Condensation is carried out in the evaporative condenser 5, so that the gas-liquid mixture of the refrigerant is prevented from directly entering the evaporative condenser 5, thereby effectively utilizing the evaporating type
  • the heat exchange area of the condenser 5; the liquid refrigerant after the heat release condensation is sequentially returned to the circulating liquid storage tank 1 through the fourth liquid pump refrigeration valve 14 and the liquid pump refrigeration line 1a, so that the liquid pump drive without starting the compressor 6 is realized. Winter cooling mode for the refrigeration cycle.
  • the liquid refrigerant supplies the evaporator 3 through the liquid pump 2 with a circulation amount equivalent to one to many times the evaporation amount, thereby overcoming the problems of insufficient power of the refrigerant and limited cooling capacity of the existing natural circulation mode of the heat pipe.
  • Fig. 4 is a view schematically showing the system schematic diagram of the liquid supply vapor compression refrigeration cycle of the present invention, i.e., the summer refrigeration mode.
  • Figure 4 As shown, in summer cooling mode, both liquid pump 2 and compressor 6 operate; The first low pressure gas valve 15, the second low pressure gas valve 16, the high pressure gas valve 17, and the high pressure liquid valve 18 close the first liquid pump refrigeration valve 11, the second liquid pump refrigeration valve 12, the third liquid pump refrigeration valve 13 and the first
  • the four-pump pump refrigeration valve 14 is configured to perform a liquid-supply vapor compression refrigeration cycle: the liquid refrigerant in the circulating liquid storage tank 1 is pressurized into the evaporator 3 through the bottom outlet via the liquid pump 2, and water or The air is subjected to heat exchange to obtain cold water or cold air; the mixture of the gaseous refrigerant evaporated by the endothermic heat and the liquid refrigerant that has not evaporated is passed through the first low pressure gas valve 15 into the circulating liquid storage tank 1 for gas-liquid separation; The gaseous ref
  • the condenser 5; the high-pressure liquid refrigerant after the exothermic condensation is sequentially depressurized by the high-pressure liquid valve 18, the high-pressure pipeline 1b, and the throttling device 7, and then enters the circulating liquid storage tank 1 to realize the summer of the liquid-supply vapor compression refrigeration cycle. Cooling mode.
  • the liquid refrigerant supplies the evaporator 3 through the liquid supply pump 2 at a circulation amount equivalent to one to many times the evaporation amount to enhance the heat exchange and bring back the lubricating oil remaining in the evaporator 3.
  • Figure 2 shows an evaporative condensation using a three-way valve
  • the system schematic diagram of the liquid pump cycle annual refrigeration device The solution combines the first liquid pump refrigeration valve 11 and the first low pressure gas valve 15 into a first one-in, two-out three-way valve 21; the second liquid pump refrigeration valve 12 and the high pressure gas valve 17 are merged into two a three-way valve 22; the fourth liquid pump refrigeration valve 14 and the high pressure liquid valve 18 are combined into a second one-in, two-out three-way valve 23; the inlet and evaporation of the first one-in, two-out three-way valve 21
  • the outlet of the device 3 is connected, and the two outlets of the first one-in, two-out three-way valve 21 are respectively connected to the upper inlet of the circulating liquid storage tank 1 and the upper inlet of the gas-liquid separator 4; the two-in-one-out three-way valve 22
  • the two inlets are respectively connected to the upper outlet of the gas-liquid separator 4 and the exhaust port of the compressor 6, and the outlet
  • the liquid pump cycle annual refrigeration device still has two modes of operation, one is a liquid pump driven refrigeration cycle, that is, the winter cooling mode; the other is a liquid supply vapor compression refrigeration cycle, that is, a summer cooling mode.
  • Fig. 3 is a schematic view showing the system of the liquid pump driven refrigeration cycle of the present invention, i.e., the system in the winter cooling mode.
  • the liquid pump 2 in the winter cooling mode, the liquid pump 2 is operated, and the compressor 6 is stopped.
  • the system performs a liquid pump-driven refrigeration cycle: the liquid refrigerant in the circulating liquid storage tank 1 passes through the bottom outlet.
  • the pump 2 is pressurized and sent into the evaporator 3 to exchange cold water or cold air with water or air; the mixture of the gaseous refrigerant evaporated by the endothermic heat and the liquid refrigerant that has not been evaporated passes through the first one and the second.
  • the three-way valve 21 enters the gas-liquid separator 4 for gas-liquid separation, and the liquid refrigerant that has not been evaporated sequentially passes through the bottom outlet of the gas-liquid separator 4, the third liquid pump refrigeration valve 13, and the liquid pump refrigeration line 1a to return to the circulation.
  • the liquid refrigerant separated in the gas-liquid separator 4 passes through the upper outlet of the gas-liquid separator 4, and the two-in-one-out three-way valve 22 enters in sequence.
  • Condensation is carried out in the evaporative condenser 5, so that the gas-liquid mixture of the refrigerant is prevented from directly entering the evaporative condenser 5, thereby effectively utilizing the evaporating type
  • the heat exchange area of the condenser 5; the liquid refrigerant after the heat release condensation is sequentially returned to the circulating liquid storage tank 1 through the second one-in, two-out three-way valve 23, and the liquid pump refrigeration line 1a, so that the compressor 6 is not required to be started.
  • the liquid pump drives the winter cooling mode of the refrigeration cycle.
  • the liquid refrigerant supplies the evaporator 3 through the liquid pump 2 with a circulation amount equivalent to one to many times the evaporation amount, thereby overcoming the problems of insufficient power of the refrigerant and limited cooling capacity of the existing natural circulation mode of the heat pipe.
  • Fig. 4 is a view schematically showing the system schematic diagram of the liquid supply vapor compression refrigeration cycle of the present invention, i.e., the summer refrigeration mode.
  • Figure 4 As shown, in the summer cooling mode, both the liquid pump 2 and the compressor 6 operate. At this time, the system performs a liquid-supply vapor compression refrigeration cycle: the liquid refrigerant in the circulating liquid storage tank 1 is pressurized into the evaporator 3 through the bottom outlet through the liquid pump 2, and is heat-exchanged with water or air to prepare Cold water or cold air; the mixture of the gaseous refrigerant evaporated by the endothermic heat and the liquid refrigerant that has not been evaporated passes through the first one-in, two-out three-way valve 21 to enter the circulating liquid storage tank 1 for gas-liquid separation; in the circulating liquid storage tank 1 The gaseous refrigerant is sucked by the compressor 6, enters the compressor 6 through the second low pressure gas valve 16, and is compressed into a high temperature and high pressure gaseous refriger
  • the liquid refrigerant supplies the evaporator 3 through the liquid supply pump 2 at a circulation amount equivalent to one to many times the evaporation amount to enhance the heat exchange and bring back the lubricating oil remaining in the evaporator 3.
  • the evaporator 3 may be a way in which a plurality of evaporators are connected in parallel to meet the cooling requirements of single or multiple spaces.
  • the evaporator 3 may employ a shell and tube evaporator and a finned evaporator.
  • the gas-liquid separator 4 may be in the form of a three-way pipe, the inlet of the gas-liquid separator 4 is connected to the outlet of the evaporator 3, and the upper outlet of the gas-liquid separator 4 is evaporating.
  • the inlet of the condenser 5 is connected, and the lower outlet of the gas-liquid separator 4 is connected to the lower inlet of the circulating liquid storage tank 1.
  • the gas-liquid separator 4 can also be in the form of a straight pipe section, the side air inlet of the gas-liquid separator 4 is connected to the outlet of the evaporator 3, and the upper outlet of the gas-liquid separator 4 is evaporating.
  • the inlet of the condenser 5 is connected, and the lower outlet of the gas-liquid separator 4 is connected to the lower inlet of the circulating liquid storage tank 1.
  • the gravity pump supply switching valve 8 can be connected in parallel to both ends of the liquid pump 2.
  • the gravity feed liquid switching valve 8 is turned on, the liquid pump 2 is turned off, and the liquid is supplied by gravity; the liquid level of the liquid storage tank 1 to be stabilized is stable, and the compressor 6
  • the load reaches 60% or more, the liquid pump 2 is turned on, the gravity liquid supply switching valve 8 is turned off, and the liquid pump is supplied to the liquid pump.
  • This solution avoids the cavitation surge phenomenon of the liquid pump 2 due to the unstable liquid level of the circulating liquid storage tank 1.
  • the evaporative condenser 5 may be a tube tube evaporative condenser or a coil type evaporative condenser.
  • a lower condensing temperature is achieved and the system condensing pressure is reduced, thereby increasing the energy efficiency of the system.
  • drying filter 9 and a sight glass 10 are disposed between the outlet of the condenser 5 and the inlet of the throttle device 7, and constitute a complete refrigeration process line.

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  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
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  • Other Air-Conditioning Systems (AREA)
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Description

[根据细则37.2由ISA制定的发明名称]　 液泵循环全年制冷装置
技术领域
本发明涉及一种液泵循环制冷装置，尤其是一种适用于数据机房、计算机中心和建筑内区等全年供冷空间的蒸发式冷凝液泵循环全年制冷装置。
背景技术
随着通信技术的发展、 3G 网络时代的来临和互联网业务需求量的迅猛增长，包括 IDC 机房，计算机中心，服务器机房等在内的各种高密度发热机房与日俱增。以数据机房为例，机房内部的电子通讯设备发热量大且集中，单位建筑平米的发热强度可达数百瓦甚至上千瓦，而且全年不间断运行，因此机房一般都需要配置全年制冷运行的空调为其提供冷却降温。所以，数据机房不仅总能耗巨大，其内设的空调所占总能耗比例也普遍偏高。据资料统计， 2007 年我国数据中心能耗约为 300 亿度电，相当于当年三峡发电量的一半，而其中的机房空调能耗比例在 40% 左右。除各种机房外，随着大型写字楼、商场等公共建筑的内区空间，以及特殊工艺厂房等各种全年需冷空间的不断增多，其全年空调制冷的能耗也不容小觑。由此可见，降低全年制冷空间的空调能耗刻不容缓。
传统的热管自然循环具有较好的节能效果，但存在两点不足：一是冬季运行时需要提供比夏季制冷更大口径的系统管路和阀门，成本增加且占用空间增大；二是容易出现制冷剂动力不足、循环量不大等现象，造成换热效率降低，制冷效果受限。作为一种改进， CN 101694311A 公开了一种带自然冷却功能的液泵供液多联式空调机组，采用多倍于蒸发量的液泵强制循环供液，增大了制冷剂的循环量。但是该系统易造成未蒸发的液态制冷剂进入冷凝器，减少了冷凝器有效的换热面积，继而导致制冷量下降影响制冷效果。因此需要进一步提出有效方案，为市场提供可实现全年高效供冷的低能耗制冷装置。
此外，现有的蒸发器供液方式亦存在诸多不足，干式系统能效比偏低，满液式系统存在液位控制难和回油困难等问题，所以市场需要换热效率更高、更加安全可靠的蒸发器供液系统，提高蒸发器换热效率。
发明内容
本发明的目的是为克服上述现有技术存在的缺点与不足，提供一种换热效率高、使用安全可靠，并能高效、稳定地利用冬季和过渡季室外自然冷量的一种蒸发式冷凝液泵循环全年制冷装置。
为解决上述技术问题，本发明是通过以下技术方案实现的：
一种蒸发式冷凝液泵循环全年制冷装置，包括循环储液桶 1 、液泵 2 、蒸发器 3 、蒸发式冷凝器 5 、压缩机 6 、节流装置 7 、第一低压气体阀 15 、第二低压气体阀 16 、高压气体阀 17 、第四液泵制冷阀 14 、高压液体阀 18 ；所述液泵 2 的吸入口与循环储液桶 1 的底部出口连接，液泵 2 的出口与蒸发器 3 的入口连接；所述第一低压气体阀 15 的入口与蒸发器 3 的出口连接，第一低压气体阀 15 的出口与循环储液桶 1 的上部入口连接；所述第二低压气体阀 16 的入口与循环储液桶 1 的上部出口连接，第二低压气体阀 16 的出口与压缩机 6 的进气口连接；所述高压气体阀 17 的入口与压缩机 6 的排气口连接，高压气体阀 17 的出口与蒸发式冷凝器 5 的入口连接；所述蒸发式冷凝器 5 的出口与循环储液桶 1 的下部入口由液泵制冷管路 1a 和高压管路 1b 两条并联管路分别连接；所述液泵制冷管路 1a 的入口端设置有第四液泵制冷阀 14 ；所述高压管路 1b 的入口端设置有高压液体阀 18 ，并设置有节流装置 7 ；该装置还包括气液分离器 4 、第一液泵制冷阀 11 、第二液泵制冷阀 12 和第三液泵制冷阀 13 ；所述气液分离器 4 的上部入口通过第一液泵制冷阀 11 与蒸发器 3 的出口连接，气液分离器 4 的上部出口通过第二液泵制冷阀 12 与蒸发式冷凝器 5 的入口连接，气液分离器 4 的底部出口依次通过第三液泵制冷阀 13 、液泵制冷管路 1a 与循环储液桶 1 的下部入口连接；所述循环储液桶 1 、液泵 2 、蒸发器 3 、第一液泵制冷阀 11 、气液分离器 4 、第二液泵制冷阀 12 、蒸发式冷凝器 5 、第三液泵制冷阀 13 、第四液泵制冷阀 14 组成液泵驱动制冷循环；所述压缩机 6 、高压气体阀 17 、蒸发式冷凝器 5 、高压液体阀 18 、节流装置 7 、循环储液桶 1 、液泵 2 、蒸发器 3 、第一低压气体阀 15 、第二低压气体阀 16 组成供液蒸气压缩式制冷循环。
作为本发明的一种改进，所述第一液泵制冷阀 11 和第一低压气体阀 15 合并为第一一进二出三通阀 21 ；所述第二液泵制冷阀 12 和高压气体阀 17 合并为二进一出三通阀 22 ；所述第四液泵制冷阀 14 和高压液体阀 18 合并为第二一进二出三通阀 23 ； 所述第一一进二出三通阀21的入口与蒸发器3的出口连接，第一一进二出三通阀21的两个出口分别与循环储液桶1的上部入口和气液分离器4的上部入口连接；所述二进一出三通阀22的两个入口分别与气液分离器4的上部出口和压缩机6的排气口连接，二进一出三通阀22的出口与 蒸发式 冷凝器5的入口连接；所述第二一进二出三通阀23的入口与 蒸发式 冷凝器5的出口连接，第二一进二出三通阀23的两个出口中，其中一个出口经液泵制冷管路1a与循环储液桶1的下部入口连接，另一个出口经高压管路1b、通过节流装置7与循环储液桶1的下部入口连接。
作为本发明的一种改进，所述第一低压气体阀 15 、第二低压气体阀 16 、高压气体阀 17 、高压液体阀 18 、第一液泵制冷阀 11 、第二液泵制冷阀 12 、第三液泵制冷阀 13 、第四液泵制冷阀 14 采用电磁阀或电动阀。
作为本发明的一种改进，所述第一一进二出三通阀 21 、二进一出三通阀 22 、第二一进二出三通阀 23 采用自力式三通阀、电磁式三通阀或电动式三通阀。
作为本发明的一种改进，所述气液分离器 4 采用具有三个接口的容器，或是由三通管道或直管段组成。
作为本发明的一种改进，所述蒸发式冷凝器 5 采用板管蒸发式冷凝器或盘管式蒸发式冷凝器。
作为本发明的一种改进，所述蒸发器 3 采用壳管式蒸发器或翅片式蒸发器。
作为本发明的一种改进，所述蒸发器 3 采用多个并联方式连接。
作为本发明的一种改进，所述液泵 2 的两端并联有重力供液转换阀门 8 。
作为本发明的一种改进，所述蒸发式冷凝器（ 5 ）的出口与节流装置（ 7 ）的进口之间设置有干燥过滤器（ 9 ）和视液镜（ 10 ）。
与现有技术相比，本发明的有益效果是：
1 、在冬季和室外温度较低的过渡季时，关闭压缩机6，将本发明切换至 液泵驱动制冷循环，即冬季制冷模式。此时由于采用液泵 2 向蒸发器 3 强制供液，因此比目前传统的热管自然循环模式具备更高的换热效率和制冷效果。
2 、由于本发明在 蒸发式 冷凝器5的进气口设置了气液分离器4，有效避免了制冷剂的气液混合物直接进入 蒸发式 冷凝器5所导致的 蒸发式 冷凝器5中存液过多、继而影响有效换热面积的问题，从而实现了更高的换热效率和制冷量，保证机组在冬季和过渡季时能高效运行，提高了全年运行效率。
3 、由于本发明采用液泵强制循环供液，因此冬季制冷循环系统管路的口径可以与夏季制冷循环系统的管路口径相同，从而实现同一系统管路运行冬、夏两种模式的目的，节省了制造成本和设备安装空间。
附图说明
图1示出了本发明的一种 蒸发式冷凝 液泵循环全年制冷装置的系统原理图。
图2 示出了采用三通阀的一种 蒸发式冷凝 液泵循环全年制冷装置的系统原理图。
图3示意地示出了本发明的液泵驱动制冷循环，即冬季制冷模式下的系统原理图。
图4示意地示出了本发明的 供液蒸气压缩式制冷循环，即夏季制冷模式下的系统原理图。
图 5 示出了采用多个蒸发器并联连接的一种蒸发式冷凝液泵循环全年制冷装置的系统原理图。
图6示出了采用三通管道形式的气液分离器的 一种蒸发式冷凝液泵循环全年制冷装置的系统原理图。
图7示出了采用直管段形式的气液分离器的 一种蒸发式冷凝液泵循环全年制冷装置的 系统原理图。
图8示出了采用 重力供液转换阀门的一种蒸发式冷凝液泵循环全年制冷装置的 系统原理图。
图9示出了采用干燥过滤器和视液镜的 一种蒸发式冷凝液泵循环全年制冷装置的 系统原理图。
图中：1循环储液桶、2液泵、3蒸发器、4气液分离器、5 蒸发式 冷凝器、6压缩机、7节流装置、8重力供液转换阀门、9干燥过滤器、10视液镜、11第一液泵制冷阀、12第二液泵制冷阀、13第三液泵制冷阀、14第四液泵制冷阀、15第一低压气体阀、16第二低压气体阀、17高压气体阀、18高压液体阀、21第一一进二出三通阀、22二进一出三通阀、23第二一进二出三通阀。
具体实施方式
实施例1
图1示出了本发明的一种 蒸发式冷凝 液泵循环全年制冷装置的系统原理图，包括 循环储液桶 1 、液泵 2 、蒸发器 3 、蒸发式冷凝器 5 、压缩机 6 、节流装置 7 、第一低压气体阀 15 、第二低压气体阀 16 、高压气体阀 17 、第四液泵制冷阀 14 、高压液体阀 18 ；所述液泵 2 的吸入口与循环储液桶 1 的底部出口连接，液泵 2 的出口与蒸发器 3 的入口连接；所述第一低压气体阀 15 的入口与蒸发器 3 的出口连接，第一低压气体阀 15 的出口与循环储液桶 1 的上部入口连接；所述第二低压气体阀 16 的入口与循环储液桶 1 的上部出口连接，第二低压气体阀 16 的出口与压缩机 6 的进气口连接；所述高压气体阀 17 的入口与压缩机 6 的排气口连接，高压气体阀 17 的出口与蒸发式冷凝器 5 的入口连接；所述蒸发式冷凝器 5 的出口与循环储液桶 1 的下部入口由液泵制冷管路 1a 和高压管路 1b 两条并联管路分别连接；所述液泵制冷管路 1a 的入口端设置有第四液泵制冷阀 14 ；所述高压管路 1b 的入口端设置有高压液体阀 18 ，并设置有节流装置 7 。
该装置还包括气液分离器 4 、第一液泵制冷阀 11 、第二液泵制冷阀 12 和第三液泵制冷阀 13 ；所述气液分离器 4 的上部入口通过第一液泵制冷阀 11 与蒸发器 3 的出口连接，气液分离器 4 的上部出口通过第二液泵制冷阀 12 与蒸发式冷凝器 5 的入口连接，气液分离器 4 的底部出口依次通过第三液泵制冷阀 13 、液泵制冷管路 1a 与循环储液桶 1 的下部入口连接。
所述循环储液桶 1 、液泵 2 、蒸发器 3 、第一液泵制冷阀 11 、气液分离器 4 、第二液泵制冷阀 12 、蒸发式冷凝器 5 、第三液泵制冷阀 13 、第四液泵制冷阀 14 组成液泵驱动制冷循环；所述压缩机 6 、高压气体阀 17 、蒸发式冷凝器 5 、高压液体阀 18 、节流装置 7 、循环储液桶 1 、液泵 2 、蒸发器 3 、第一低压气体阀 15 、第二低压气体阀 16 组成供液蒸气压缩式制冷循环。
所述实施例 1 的一种蒸发式冷凝液泵循环全年制冷装置具有两种运行模式，一种为液泵驱动制冷循环，即冬季制冷模式；另一种为供液蒸气压缩式制冷循环，即夏季制冷模式。
图3示意地示出了本发明的液泵驱动制冷循环，即冬季制冷模式下的系统原理图。如图3所示，在冬季制冷模式下，液泵2运行，压缩机6停止工作；开启第一液泵制冷阀11、第二液泵制冷阀12、第三液泵制冷阀13和第四液泵制冷阀14，关闭第一低压气体阀15、第二低压气体阀16、高压气体阀17和高压液体阀18，此时系统进行液泵驱动制冷循环：所述循环储液桶1内的液态制冷剂通过底部出口经液泵2增压送入蒸发器3内，与水或空气进行热交换后制取冷水或冷风；经吸热蒸发后的气态制冷剂与尚未蒸发的液态制冷剂的混合物经过第一液泵制冷阀11进入气液分离器4中进行气液分离，未被蒸发的液态制冷剂依次经过气液分离器4的底部出口、第三液泵制冷阀13、液泵制冷管路1a返回循环储液桶1内；而气液分离器4内分离出来的气态制冷剂则依次经过气液分离器4的上部出口、第二液泵制冷阀12进入 蒸发式 冷凝器5内进行冷凝，这样避免了制冷剂的气液混合物直接进入 蒸发式 冷凝器5，从而有效地利用 蒸发式 冷凝器5的换热面积；放热冷凝后的液态制冷剂依次经第四液泵制冷阀14、液泵制冷管路1a返回循环储液桶1内，实现无需启动压缩机6的液泵驱动制冷循环的冬季制冷模式。液态制冷剂经液泵2以相当于蒸发量一至多倍的循环量对蒸发器3进行供液，克服了现有热管自然循环模式制冷剂动力不足、制冷量受限等问题。
图4示意地示出了本发明的 供液蒸气压缩式制冷循环，即夏季制冷模式下的系统原理图。如图 4 所示，在夏季制冷模式下，液泵 2 和压缩机 6 均工作；开启 第一低压气体阀15、第二低压气体阀16、高压气体阀17和高压液体阀18，关闭第一液泵制冷阀11、第二液泵制冷阀12、第三液泵制冷阀13和第四液泵制冷阀14，此时系统进行供液蒸气压缩式制冷循环：所述循环储液桶1内的液态制冷剂通过底部出口经液泵2增压送入蒸发器3内，与水或空气进行热交换后制取冷水或冷风；经吸热蒸发后的气态制冷剂与尚未蒸发的液态制冷剂的混合物经过第一低压气体阀15进入循环储液桶1进行气液分离；循环储液桶1内的气态制冷剂受压缩机6抽吸，经第二低压气体阀16进入压缩机6，并被压缩为高温高压气态制冷剂，经高压气体阀17进入 蒸发式 冷凝器5；放热冷凝后的高压液态制冷剂依次经高压液体阀18、高压管路1b、节流装置7降压后进入循环储液桶1内，实现供液蒸气压缩式制冷循环的夏季制冷模式。液态制冷剂经供液泵2以相当于蒸发量一至多倍的循环量对蒸发器3进行供液，以强化换热，并带回蒸发器3内存留的润滑油。
实施例2
图2 示出了采用三通阀的一种 蒸发式冷凝 液泵循环全年制冷装置的系统原理图。该方案将所述第一液泵制冷阀11和第一低压气体阀15合并为第一一进二出三通阀21；所述第二液泵制冷阀12和高压气体阀17合并为二进一出三通阀22；所述第四液泵制冷阀14和高压液体阀18合并为第二一进二出三通阀23；所述第一一进二出三通阀21的入口与蒸发器3的出口连接，第一一进二出三通阀21的两个出口分别与循环储液桶1的上部入口和气液分离器4的上部入口连接；所述二进一出三通阀22的两个入口分别与气液分离器4的上部出口和压缩机6的排气口连接，二进一出三通阀22的出口与 蒸发式 冷凝器5的入口连接；所述第二一进二出三通阀23的入口与 蒸发式 冷凝器5的出口连接，第二一进二出三通阀23的两个出口中，其中一个出口经液泵制冷管路1a与循环储液桶1的下部入口连接，另一个出口经高压管路1b、通过节流装置7与循环储液桶1的下部入口连接。
所述实施例2的一种 蒸发式冷凝 液泵循环全年制冷装置仍然具有两种运行模式，一种为液泵驱动制冷循环，即冬季制冷模式；另一种为供液蒸气压缩式制冷循环，即夏季制冷模式。
图3示意地示出了本发明的液泵驱动制冷循环，即冬季制冷模式下的系统原理图。如图3所示，在冬季制冷模式下，液泵2运行，压缩机6停止工作，此时系统进行液泵驱动制冷循环：所述循环储液桶1内的液态制冷剂通过底部出口经液泵2增压送入蒸发器3内，与水或空气进行热交换后制取冷水或冷风；经吸热蒸发后的气态制冷剂与尚未蒸发的液态制冷剂的混合物经过第一一进二出三通阀21进入气液分离器4中进行气液分离，未被蒸发的液态制冷剂依次经过气液分离器4的底部出口、第三液泵制冷阀13、液泵制冷管路1a返回循环储液桶1内；而气液分离器4内分离出来的气态制冷剂则依次经过气液分离器4的上部出口、二进一出三通阀22进入 蒸发式 冷凝器5内进行冷凝，这样避免了制冷剂的气液混合物直接进入 蒸发式 冷凝器5，从而有效地利用 蒸发式 冷凝器5的换热面积；放热冷凝后的液态制冷剂依次经第二一进二出三通阀23、液泵制冷管路1a返回循环储液桶1内，实现无需启动压缩机6的液泵驱动制冷循环的冬季制冷模式。液态制冷剂经液泵2以相当于蒸发量一至多倍的循环量对蒸发器3进行供液，克服了现有热管自然循环模式制冷剂动力不足、制冷量受限等问题。
图4示意地示出了本发明的 供液蒸气压缩式制冷循环，即夏季制冷模式下的系统原理图。如图 4 所示，在夏季制冷模式下，液泵 2 和压缩机 6 均工作， 此时系统进行供液蒸气压缩式制冷循环：所述循环储液桶1内的液态制冷剂通过底部出口经液泵2增压送入蒸发器3内，与水或空气进行热交换后制取冷水或冷风；经吸热蒸发后的气态制冷剂与尚未蒸发的液态制冷剂的混合物经过第一一进二出三通阀21进入循环储液桶1进行气液分离；循环储液桶1内的气态制冷剂受压缩机6抽吸，经第二低压气体阀16进入压缩机6，并被压缩为高温高压气态制冷剂，经二进一出三通阀22进入 蒸发式 冷凝器5；放热冷凝后的高压液态制冷剂依次经第二一进二出三通阀23、高压管路1b、节流装置7降压后进入循环储液桶1内，实现供液蒸气压缩式制冷循环的夏季制冷模式。液态制冷剂经供液泵2以相当于蒸发量一至多倍的循环量对蒸发器3进行供液，以强化换热，并带回蒸发器3内存留的润滑油。
如图5所示，所述蒸发器3可以是多个蒸发器并联连接的方式，以满足单个或多个空间的供冷需求。作为优选，蒸发器3可以采用壳管式蒸发器和翅片式蒸发器。
如图6所示，所述气液分离器4可以采用三通管道形式，气液分离器4的进气口与蒸发器3的出口连接，气液分离器4的上部出口与 蒸发式 冷凝器5的入口连接，气液分离器4的下部出口与循环储液桶1的下部入口连接。
如图7所示，所述气液分离器4还可以采用直管段形式，气液分离器4的侧面进气口与蒸发器3的出口连接，气液分离器4的上部出口与 蒸发式 冷凝器5的入口连接，气液分离器4的下部出口与循环储液桶1的下部入口连接。
如图8所示，所述液泵2两端可以并联重力供液转换阀门8。在夏季制冷模式下，压缩机6制冷刚启动时，开启重力供液转换阀门8，关闭液泵2，以重力供液方式供液；待循环储液桶1的液位稳定，且压缩机6的负荷达到60％以上时，开启液泵2，关闭重力供液转换阀门8，转换为液泵供液。此方案避免了由于循环储液桶1液位不稳定而造成液泵2的汽蚀喘振现象。此外，也可在部分负荷或供液泵2发生故障时实现不运行供液泵2而采用重力供液方式直接向蒸发器3供液运行。
作为优选，所述 蒸发式 冷凝器5可以采用 板管蒸发式冷凝器或盘管式蒸发式冷凝器， 可获得更低的冷凝温度，并可降低系统冷凝压力，从而提高系统的能效比。
如图9所示，在 蒸发式 冷凝器5的出口与节流装置7的进口之间设置有干燥过滤器9和视液镜10，组成完善的制冷工艺管路。
显然，本发明不限于以上实施例，还可以有许多变形。本领域的普通技术人员能从本发明公开的内容直接导出或联想到的所有变形，均应认为是本发明的保护范围。

Claims (10)

  1. 一种蒸发式冷凝液泵循环全年制冷装置，包括循环储液桶（1）、液泵（2）、蒸发器（3）、蒸发式冷凝器（5）、压缩机（6）、节流装置（7）、第一低压气体阀（15）、第二低压气体阀（16）、高压气体阀（17）、第四液泵制冷阀（14）、高压液体阀（18）；所述液泵（2）的吸入口与循环储液桶（1）的底部出口连接，液泵（2）的出口与蒸发器（3）的入口连接；所述第一低压气体阀（15）的入口与蒸发器（3）的出口连接，第一低压气体阀（15）的出口与循环储液桶（1）的上部入口连接；所述第二低压气体阀（16）的入口与循环储液桶（1）的上部出口连接，第二低压气体阀（16）的出口与压缩机（6）的进气口连接；所述高压气体阀（17）的入口与压缩机（6）的排气口连接，高压气体阀（17）的出口与蒸发式冷凝器（5）的入口连接；所述蒸发式冷凝器（5）的出口与循环储液桶（1）的下部入口由液泵制冷管路（1a）和高压管路（1b）两条并联管路分别连接；所述液泵制冷管路（1a）的入口端设置有第四液泵制冷阀（14）；所述高压管路（1b）的入口端设置有高压液体阀（18），并设置有节流装置（7），其特征在于：该装置还包括气液分离器（4）、第一液泵制冷阀（11）、第二液泵制冷阀（12）和第三液泵制冷阀（13）；所述气液分离器（4）的上部入口通过第一液泵制冷阀（11）与蒸发器（3）的出口连接，气液分离器（4）的上部出口通过第二液泵制冷阀（12）与蒸发式冷凝器（5）的入口连接，气液分离器（4）的底部出口依次通过第三液泵制冷阀（13）、液泵制冷管路（1a）与循环储液桶（1）的下部入口连接；所述循环储液桶（1）、液泵（2）、蒸发器（3）、第一液泵制冷阀（11）、气液分离器（4）、第二液泵制冷阀（12）、蒸发式冷凝器（5）、第三液泵制冷阀（13）、第四液泵制冷阀（14）组成液泵驱动制冷循环；所述压缩机（6）、高压气体阀（17）、蒸发式冷凝器（5）、高压液体阀（18）、节流装置（7）、循环储液桶（1）、液泵（2）、蒸发器（3）、第一低压气体阀（15）、第二低压气体阀（16）组成供液蒸气压缩式制冷循环。
  2. 根据权利要求1所述的一种蒸发式冷凝液泵循环全年制冷装置，其特征在于：所述第一液泵制冷阀（11）和第一低压气体阀（15）合并为第一一进二出三通阀（21）；所述第二液泵制冷阀（12）和高压气体阀（17）合并为二进一出三通阀（22）；所述第四液泵制冷阀（14）和高压液体阀（18）合并为第二一进二出三通阀（23）；所述第一一进二出三通阀（21）的入口与蒸发器（3）的出口连接，第一一进二出三通阀（21）的两个出口分别与循环储液桶（1）的上部入口和气液分离器（4）的上部入口连接；所述二进一出三通阀（22）的两个入口分别与气液分离器（4）的上部出口和压缩机（6）的排气口连接，二进一出三通阀（22）的出口与蒸发式冷凝器（5）的入口连接；所述第二一进二出三通阀（23）的入口与蒸发式冷凝器（5）的出口连接，第二一进二出三通阀（23）的两个出口中，其中一个出口经液泵制冷管路（1a）与循环储液桶（1）的下部入口连接，另一个出口经高压管路（1b）、通过节流装置（7）与循环储液桶（1）的下部入口连接。
  3. 根据权利要求1或2所述的一种蒸发式冷凝液泵循环全年制冷装置，其特征在于：所述第一低压气体阀（15）、第二低压气体阀（16）、高压气体阀（17）、高压液体阀（18）、第一液泵制冷阀（11）、第二液泵制冷阀（12）、第三液泵制冷阀（13）、第四液泵制冷阀（14）采用电磁阀或电动阀。
  4. 根据权利要求2所述的一种蒸发式冷凝液泵循环全年制冷装置，其特征在于：所述第一一进二出三通阀（21）、二进一出三通阀（22）、第二一进二出三通阀（23）采用自力式三通阀、电磁式三通阀或电动式三通阀。
  5. 根据权利要求1或2所述的一种蒸发式冷凝液泵循环全年制冷装置，其特征在于：所述气液分离器（4）采用具有三个接口的容器，或是由三通管道或直管段组成。
  6. 根据权利要求1或2所述的一种蒸发式冷凝液泵循环全年制冷装置，其特征在于：所述蒸发式冷凝器（5）采用板管蒸发式冷凝器或盘管式蒸发式冷凝器。
  7. 根据权利要求1或2所述的一种蒸发式冷凝液泵循环全年制冷装置，其特征在于：所述蒸发器（3）采用壳管式蒸发器或翅片式蒸发器。
  8. 根据权利要求1或2所述的一种蒸发式冷凝液泵循环全年制冷装置，其特征在于：所述蒸发器（3）采用多个并联方式连接。
  9. 根据权利要求1或2所述的一种蒸发式冷凝液泵循环全年制冷装置，其特征在于：在所述液泵（2）的两端并联有重力供液转换阀门（8）。
  10. 根据权利要求1或2所述的一种蒸发式冷凝液泵循环全年制冷装置，其特征在于：所述蒸发式冷凝器（5）的出口与节流装置（7）的进口之间设置有干燥过滤器（9）和视液镜（10）。
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