WO2010094227A1 - 一种空调 - Google Patents

一种空调 Download PDF

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Publication number
WO2010094227A1
WO2010094227A1 PCT/CN2010/070578 CN2010070578W WO2010094227A1 WO 2010094227 A1 WO2010094227 A1 WO 2010094227A1 CN 2010070578 W CN2010070578 W CN 2010070578W WO 2010094227 A1 WO2010094227 A1 WO 2010094227A1
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WO
WIPO (PCT)
Prior art keywords
control valve
valve member
inlet
coupled
liquid pump
Prior art date
Application number
PCT/CN2010/070578
Other languages
English (en)
French (fr)
Inventor
马岩松
樊易周
葛海方
燕娜
丁良尹
Original Assignee
艾默生网络能源有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 艾默生网络能源有限公司 filed Critical 艾默生网络能源有限公司
Priority to US13/201,134 priority Critical patent/US8650898B2/en
Priority to EP10743408.6A priority patent/EP2400242B1/en
Publication of WO2010094227A1 publication Critical patent/WO2010094227A1/zh

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Classifications

    • 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
    • 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—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor
    • 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—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers

Definitions

  • the invention relates to an air conditioner.
  • the air conditioner is configured according to the outdoor outdoor temperature in summer. When the outdoor environment temperature is low in winter or spring and autumn, it is necessary to simulate the summer working condition to maintain the normal compressor system. At work, air conditioners need to operate compressors throughout the year. If the outdoor cold source can be used to directly release the cooling capacity into the machine room, the compressor's working time can be reduced, thus reducing power consumption.
  • the first is natural cooling of ethylene glycol.
  • an "economic coil” with the same amount of refrigeration as the evaporator is added.
  • the water pump located in the indoor unit pumps the lower temperature glycol aqueous solution in the outdoor unit into the economic coil, and the hot air in the room. Perform heat exchange for refrigeration purposes.
  • the shortcomings of this scheme are: a. The application is limited to water-cooled units; b. Due to the existence of economic coils, the indoor fan load in the equipment room is increased, which increases the annual power consumption of indoor fans and reduces the energy-saving effect; c. More investment is added.
  • the second is to directly pass the outdoor fresh air.
  • the outdoor fresh air is directly led to the indoor air return of the machine room, and sent to the room through the filter.
  • the shortcomings of this scheme are: a. The relative humidity of the air sent to the room is not well controlled; b. If the supply air temperature is lower than the dew point temperature in the equipment room, it may condense on the equipment; c. , However, the cleanliness of the equipment room is still not guaranteed, which will affect the operation of the main equipment and increase the maintenance of the filter; d. It is necessary to hollow out the maintenance structure and destroy the integrity of the building; e. If rain or snow occurs The weather will send water directly into the machine room.
  • the technical problem to be solved by the present invention is to overcome the above deficiencies and propose an air conditioner with obvious energy saving effects.
  • An air conditioner including an evaporator, a condenser, a compressor, a liquid pump and a liquid reservoir, further comprising a first on-off control valve member and a first flow direction control valve member a second on-off control valve member, a second flow control valve member, a throttle device, a liquid pump bypass pipe with a third flow direction control valve member, and a compressor bypass pipe with a fourth flow direction control valve member;
  • a compressor inlet is coupled to an outlet of the evaporator via a first on-off control valve member, the compressor outlet being coupled to an inlet of the condenser via a first flow control valve member;
  • the liquid pump inlet being passed through a second on-off control valve member An outlet coupled to the reservoir, the liquid pump outlet coupled to the inlet of the throttling device via a second flow control valve member;
  • the condenser outlet coupled to the reservoir inlet, the throttling device outlet coupled to the evaporator An inlet of the
  • the air conditioner further includes a flow regulating valve and a throttling device bypass pipe with a third on-off control valve member, wherein the flow regulating valve is configured to adjust a flow rate of the refrigerant in the liquid pump, and the throttling device bypass pipe Parallel to both ends of the throttling device.
  • the first on-off control wide member is a first three-way on-off control wide member, the first three-way on-off control valve member inlet is coupled with the evaporator outlet, and the two three-way on-off control valve member outlets are respectively a compressor bypass pipe inlet and a compressor inlet coupling;
  • the second on-off control valve member is a second three-way on-off control valve member, and the second three-way on-off control width member inlet is coupled with the reservoir outlet,
  • the two outlets of the two-three-way on-off control valve member are respectively coupled with the liquid pump bypass pipe inlet and the liquid pump inlet.
  • the air conditioner further includes a reservoir bypass pipe, and the reservoir bypass pipe is connected in parallel at both ends of the reservoir.
  • the first on-off control valve member and the second on-off control valve member are respectively a solenoid valve or a shut-off valve or a ball valve or an electric ball valve.
  • the first flow direction control width member, the second flow direction control width member, the third flow direction control width member and the fourth flow direction control valve member are a one-way valve or a shut-off valve or a ball valve or an electric ball valve, respectively.
  • the third on-off control valve member is a solenoid valve or a shut-off valve or a ball valve or an electric ball valve.
  • the air conditioner is used in a communication room.
  • the beneficial effects of the present invention compared with the prior art are: under the same flow condition, the power consumption of the liquid pump is much smaller than the power consumption of the compressor, and the energy saving effect of the invention is obvious and ensured by avoiding the direct air fresh air.
  • the invention When the compressor system is running: the invention is provided with a compressor bypass pipe with a fourth flow direction control valve member to ensure that the compressor discharge pressure does not act on the suction pipe to ensure the normal operation of the compressor; A second on-off control valve member is arranged in front of the pump inlet, and a second flow direction control valve member is arranged after the liquid pump outlet to ensure that the high-pressure refrigerant does not directly act on the liquid pump, so that the liquid pump can be used normally for a long time.
  • the present invention is provided with a first on-off control valve member at the inlet of the compressor, and a first flow-direction control valve member at the outlet of the compressor to ensure that the refrigerant is not poured into the compressor.
  • the invention is provided with a liquid pump bypass pipe with a third flow direction control valve member, and the liquid pump does not form a self-circulation, thereby maximizing the utilization of the liquid pump.
  • FIG. 1 is a schematic structural view of a first embodiment of the present invention
  • FIG. 2 is a schematic structural view of a second embodiment of the present invention.
  • FIG. 3 is a schematic structural view of a third embodiment of the present invention.
  • FIG. 4 is a schematic structural view of a fourth embodiment of the present invention.
  • FIG. 1 a schematic structural view of a first embodiment of the present invention is shown.
  • the air conditioner according to the first embodiment of the present invention includes an evaporator 9, a condenser 14, a compressor 11, a liquid pump 3, a reservoir 1, a first on-off control valve member 10, and a first flow direction.
  • the first on-off control valve member 10 and the second on-off control valve member 2 may be a solenoid valve or a shut-off valve or a ball valve or an electric ball valve, respectively.
  • the first flow control valve member 12, the second flow direction control valve member 5, the third flow direction control valve member 6, and the fourth flow direction control valve member 13 may be a one-way valve or a shut-off valve or a ball valve or an electric ball valve, respectively.
  • the compressor 11 is used to compress low temperature and low pressure refrigerant vapor into high temperature and high pressure refrigerant vapor.
  • the liquid pump 3 is used to deliver liquid refrigerant and is stable under high operating pressure without leakage.
  • the liquid pump 3 can be a magnetically driven industrial liquid pump or a shield pump.
  • the condenser 14 is used for the exothermic liquefaction of the gaseous refrigerant, and the evaporator 9 is used for the endurance gasification of the liquid refrigerant.
  • the throttling device 8 is used for flow control of the refrigerant, and the compressor system flow control logic is executed while the compressor 11 is operating, and the liquid pump system flow control logic is executed while the liquid pump 3 is operating.
  • the throttling device 8 may specifically be an electronic expansion valve or other throttle valve member having an opening adjustment function.
  • the accumulator 1 is used to store a certain amount of refrigerant to ensure that the liquid pump 3 has sufficient liquid supply during operation.
  • the first on-off control valve member 10 and the second on-off control valve member 2 are used for switching between the two systems of the liquid pump 3 and the compressor 11.
  • the first flow control valve member 12, the second flow direction control valve member 5, the third flow direction control valve member 6, and the fourth flow direction control valve member 13 are used for control of the flow direction of the refrigerant.
  • the refrigerant may specifically be freon.
  • the compressor 11 inlet is coupled to an outlet of the evaporator 9 via a first on-off control valve member 10, the compressor 11 outlet being coupled to an inlet of the condenser 14 via a first flow control valve member 12; the liquid pump 3
  • the inlet is coupled to the outlet of the accumulator 1 via a second on-off control valve member 2, the outlet of the liquid pump 3 being coupled to the inlet of the throttling device 8 via a second flow control valve member 5;
  • the outlet of the condenser 14 is coupled to An inlet of the accumulator 1, the outlet of the throttling device 8 is coupled to an inlet of the evaporator 9;
  • an inlet of the compressor bypass 18 is coupled to an outlet of the evaporator 9, and an outlet of the compressor bypass 18 is coupled to an inlet of the condenser 14
  • the inlet of the liquid pump bypass 16 is coupled to the outlet of the reservoir 1 and the outlet of the liquid pump bypass 16 is coupled to the inlet of the throttling device 8.
  • the second on-off control valve member 2 is opened during operation of the liquid pump system, and the first on-off control valve member 10 is closed during operation of the liquid pump system to prevent liquid refrigerant from entering the compressor 11.
  • the second on-off control valve member 2 is closed during operation of the compressor system to prevent the high-pressure refrigerant acting on the compressor 11 from damaging the liquid pump on the liquid pump 3.
  • the first on-off control valve member 10 is opened while the compressor system is operating.
  • the first flow control valve member 12 is for preventing the refrigerant from flowing back to the compressor 11 when the liquid pump system is in operation
  • the fourth flow direction control valve member 13 is for preventing the high pressure gas discharged from the compressor outlet when the compressor 11 system is running through the compressor.
  • the through pipe 18 directly returns to the compressor inlet to damage the compressor.
  • Second flow control valve member 5 The high pressure acts on the liquid pump 3 to prevent the compressor system from operating
  • the third flow control valve member 6 is used to prevent the liquid refrigerant from the liquid pump from flowing back to the liquid pump through the liquid pump bypass pipe 16 during operation of the liquid pump system.
  • the refrigerant from the outlet of the compressor 11 passes through the first flow to the control valve member 12, the condenser 14, the accumulator 1, the liquid pump bypass pipe 16, the third flow control valve member 6, and the throttling device 8.
  • the evaporator 9 and the first on-off control valve member 10 return to the compressor 11 to complete the cycle.
  • the refrigerant from the outlet of the liquid pump 3 passes through the second flow control valve member 5, the throttle device 8, the evaporator 9, the compressor bypass pipe 18, the fourth flow control valve member 13, and the condenser 14
  • the accumulator 1 and the second on-off control valve member 2 return to the liquid pump 3 to complete the cycle.
  • the outlet of the accumulator 1 should be higher than the inlet of the liquid pump 3, and the calculation formula of the height H of the accumulator 1 can be: H> ( NPSH + LxR + Z ) / r, where r is the refrigerant in the accumulator 1 Density, NPSH is the cavitation allowance of the liquid pump 3, L is the length of the pipe from the outlet of the accumulator 1 to the inlet of the liquid pump 3, and R is the wear resistance of the pipe length of the inlet of the accumulator 1 to the inlet of the liquid pump 3, Z is The local resistance loss of the outlet of the accumulator 1 to the inlet of the liquid pump 3. This ensures a certain degree of subcooling before the liquid refrigerant enters the liquid pump 3, thereby ensuring stable operation of the liquid pump 3.
  • the power consumption of the liquid pump 3 is much smaller than the power consumption of the compressor 11.
  • the power consumption of the liquid pump 3 is less than 10% of the power consumption of the compressor 11 under the same flow rate.
  • the difference between the two is more, so the present invention saves energy.
  • the compressor system and the liquid pump system of the present invention share a condenser and an evaporator, saving cost.
  • the invention can not easily lead to the fresh air in the room, and the temperature, humidity and cleanliness in the machine room are easy to control, and the invention can meet the indoor cleanliness requirement of the machine room.
  • the air conditioner according to Embodiment 2 of the present invention is different from Embodiment 1 in that: the air conditioner according to Embodiment 2 of the present invention further includes a reservoir bypass pipe 15, and the liquid storage device
  • the bypass pipe 15 is connected in parallel at both ends of the accumulator 1.
  • the reservoir bypass pipe 15 inlet is coupled to the condenser 14 outlet
  • the reservoir bypass pipe 15 outlet is coupled to the second on-off control valve member 2 inlet, wherein the reservoir
  • the outlet of the liquid bypass pipe 15 is after the junction of the inlet of the liquid pump bypass pipe 16 and the inlet of the second on-off control valve member 2.
  • the outlet of the reservoir bypass pipe 15 is in the liquid pump bypass pipe 16
  • the inlet is before the junction of the second on-off control valve member 2 inlet (not shown in Figure 2).
  • the air conditioner according to the second embodiment of the present invention is different from the working principle of the first embodiment in that: when the liquid pump system is in operation, a part of the refrigerant coming out of the condenser 14 passes through the accumulator 1 and a part is bypassed by the accumulator. The tube 15 and the two parts of the refrigerant are mixed in front of the second on-off control valve member 2 and returned to the liquid pump 3 to complete the cycle.
  • the low temperature refrigerant in the condenser 14 is introduced through the accumulator bypass pipe 15 to increase the subcooling degree of the inlet of the liquid pump 3, and the stable operation of the liquid pump 3 is maintained to prevent cavitation and avoid damage. Liquid pump 3.
  • the third embodiment of the present invention is a schematic structural view of a first embodiment of the present invention.
  • the air conditioner according to the third embodiment of the present invention is different from the second embodiment in the third embodiment.
  • the first on-off control valve member 10 is the first three-way communication. Disconnecting the control valve member, the first three-way on-off control valve member inlet is coupled to the evaporator 9 outlet, and the two outlets of the first three-way on-off control valve member are respectively coupled to the inlet of the compressor bypass pipe 18 and the inlet of the compressor 11
  • the second on-off control wide member 2 is a second three-way on-off control wide member, the second three-way on-off control valve member inlet is coupled with the reservoir 1 outlet, and the second three-way on-off control valve member is The outlets are respectively coupled to the inlet of the liquid pump bypass pipe 16 and the inlet of the liquid pump 3.
  • the working principle of the air conditioner according to the third embodiment of the present invention is as follows: When the compressor system is in operation, the refrigerant from the outlet of the compressor 11 passes through the first flow to the control valve member 12 and the condenser 14, and a part of the refrigerant from the condenser 14 passes through The accumulator 1 is partially passed through the accumulator bypass pipe 15, and the two parts of the refrigerant are mixed in front of the second three-way on-off control valve member, and then flow through the second three-way on-off control valve member, the liquid pump bypass pipe 16, and the third The flow control valve member 6, the throttle device 8, the evaporator 9, and the first three-way control valve member return to the compressor 11 to complete the cycle.
  • the refrigerant from the outlet of the liquid pump 3 passes through the second flow control valve member 5, the throttle device 8, the evaporator 9, the first three-way control valve member, the compressor bypass pipe 18, and the fourth flow direction.
  • the second three-way on-off control valve member returns to the liquid pump 3 to complete the cycle.
  • the air conditioner according to Embodiment 4 of the present invention is different from Embodiment 2 in that: the air conditioner according to Embodiment 4 of the present invention further includes a flow regulating valve 4, and the flow regulating valve 4 is used.
  • the flow rate of the refrigerant in the liquid pump 3 is adjusted.
  • the flow regulating valve 4 can be placed between the outlet of the liquid pump 3 and the second flow direction control valve member 5.
  • the flow regulating valve 4 can also be placed between the inlet of the liquid pump 3 and the second on-off control valve member 2, or between the second flow control valve member 5 and the outlet of the liquid pump bypass pipe 16, or placed in the liquid.
  • the pump bypass pipe 16 is in between the inlet and the second on-off control valve member 2.
  • the flow regulating valve 4 may be a constant flow valve, an electronic expansion valve or the like.
  • the air conditioner according to the fourth embodiment of the present invention further includes a throttling device bypass pipe 17 having a third on-off control valve member 7, and the throttling device 8 may be a thermal expansion valve, an electronic expansion valve or a capillary tube or the like.
  • the throttling device bypass pipe 17 is connected in parallel at both ends of the throttling device 8.
  • the third on-off control valve member 7 is closed during operation of the compressor system to prevent refrigerant from entering the evaporator 9 directly from the throttling device bypass pipe 17.
  • the third on-off control valve member 7 is opened when the liquid pump system is running.
  • the high temperature and high pressure steam discharged from the outlet of the compressor 11 is liquefied and condensed in the condenser 14 through the first flow control valve member 12, and then the high temperature and high pressure refrigerant liquid enters the accumulator 1 from the liquid storage.
  • the liquid from the device 1 passes through the liquid pump bypass pipe 16 and the third flow direction control valve member 6 in sequence, and is subjected to pressure reduction and throttling at the throttle device 8, and the throttled low-temperature low-pressure refrigerant liquid is vaporized in the evaporator 9. Evaporation, low temperature and low pressure refrigerant vapor is returned to the compressor 11 through the first on-off control valve member 10 to complete the cycle.
  • the refrigerant pumped from the liquid pump 3 is adjusted by the flow rate adjusting valve 4, and then passes through the second flow direction control valve member 5, the throttle device bypass pipe 17, and the third on-off control valve. Item 7, entering the evaporator 9 to evaporate, the refrigerant vapor or two-phase refrigerant coming out of the evaporator 9 passes through the compressor bypass pipe 18, and the fourth flow direction enters the condenser 14 into the condenser 14 for liquefaction condensation.
  • the air conditioner according to the above embodiment of the present invention is preferably used in a communication room.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Description

一种空调 本申请要求于 2009 年 2 月 19 日提交中国专利局、 申请号为 200910105617.9、 发明名称为 "一种空调" 的中国专利申请的优先权， 其全部 内容通过引用结合在本申请中。
技术领域
本发明涉及一种空调。
背景技术
随着现代化信息技术的发展， 使得通信机房日益普及。 同时伴随着国家节 能减排的政策出台， 各大运营商在拓展业务的同时也在想办法尽量减少支出， 特别是电费的支出。机房中空调用电消耗约占整个机房用电消耗的一半， 而传 统的空调系统中压缩机耗电又占据了空调耗电的绝大部分，因此如何减少压缩 机的工作时间从而减少耗电成为空调节能的一个研究方向。
由于通信机房设备发热量大， 故机房空调要求全年制冷。 而传统的机房空 调的不足之处在于： 空调是按照夏季的室外环境温度进行配置的， 当在冬季或 春秋两季室外环境温度较低的情况下需要模拟夏季工况来维持压缩机系统的 正常工作， 空调在全年的运行中均需要运行压缩机。如果能够利用室外冷源将 冷量直接释放到机房室内就能减少压缩机的工作时间， 从而减少耗电。
目前， 制冷行业中利用室外冷源实现室内冷却主要有以下两种方式： 第一种是乙二醇自然冷却。
在室内机中增加一个制冷量与蒸发器相当的 "经济盘管"，位于室内机组中 的水泵将室外机组中的温度较低的乙二醇水溶液泵入经济盘管，与机房室内的 热空气进行热交换实现制冷的目的。
该方案的不足之处在于： a应用局限在水冷机组； b.由于经济盘管的存在， 导致机房室内风机负荷加重，使得室内风机的全年耗电增大， 减弱了节能的效 果； c.追加投资较多。
第二种是直接通室外新风。
直接将室外新风引到机房室内回风口， 经过过滤网送往室内。
该方案的不足之处在于： a.送往机房室内的空气相对湿度不好控制； b.如果 送风温度低于了机房室内露点温度，有可能在设备上凝露； c.尽管通过过滤网， 但机房室内的洁净度仍没办法保证，会影响到主设备的运行且增加了滤网维护 量； d.需要在维护结构上挖空， 破坏了建筑物的完整性； e.若出现雨雪天气会 将水直接送进机房室内。
发明内容
本发明所要解决的技术问题就是为了克服以上的不足， 提出了一种节能效 果明显的空调。
本发明的技术问题通过以下的技术方案予以解决： 一种空调， 包括蒸发器、 冷凝器、 压缩机、 液泵和储液器， 还包括第一通断控制阀件、 第一流向控制阀 件、 第二通断控制阀件、 第二流向控制阀件、 节流装置、 带第三流向控制阀件 的液泵旁通管和带第四流向控制阀件的压缩机旁通管；所述压缩机入口经第一 通断控制阀件耦合至蒸发器的出口，所述压缩机出口经第一流向控制阀件耦合 至冷凝器的入口； 所述液泵入口经第二通断控制阀件耦合至储液器的出口， 所 述液泵出口经第二流向控制阀件耦合至节流装置的入口；所述冷凝器出口耦合 至储液器入口， 所述节流装置出口耦合至蒸发器入口； 所述压缩机旁通管入口 耦合至蒸发器出口、压缩机旁通管出口耦合至冷凝器入口， 液泵旁通管入口耦 合至储液器出口、 液泵旁通管出口耦合至节流装置入口。
所述空调还包括流量调节阀和带第三通断控制阀件的节流装置旁通管， 所 述流量调节阀用于对液泵内冷媒的流量进行调节，所述节流装置旁通管并联在 节流装置两端。
所述第一通断控制阔件为第一三通通断控制阔件， 所述第一三通通断控制 阀件入口与蒸发器出口耦合、第一三通通断控制阀件的两个出口分别与压缩机 旁通管入口、压缩机入口耦合； 所述第二通断控制阀件为第二三通通断控制阀 件， 所述第二三通通断控制阔件入口与储液器出口耦合、 第二三通通断控制阀 件的两个出口分别与液泵旁通管入口、 液泵入口耦合。
所述空调还包括储液器旁通管， 所述储液器旁通管并联在储液器两端。 所述第一通断控制阀件、 第二通断控制阀件分别为电磁阀或截止阀或球阀 或电动球阀。
所述第一流向控制阔件、 第二流向控制阔件、 第三流向控制阔件和第四流 向控制阀件分别为单向阀或截止阀或球阀或电动球阀。 所述第三通断控制阀件为电磁阀或截止阀或球阀或电动球阀。
所述空调用于通信机房。
本发明与现有技术对比的有益效果是： 在流量相同条件下， 因液泵消耗功 率远小于压缩机消耗功率，且因避免采用直接通室外新风的方式，使得本发明 节能效果明显，且保证了机房室内温湿度控制及洁净度要求。 当压缩机系统运 行时： 本发明设有带第四流向控制阀件的压缩机旁通管，保证压缩机排气压力 不会作用在吸气管路，保证压缩机正常运行； 本发明在液泵入口前设有第二通 断控制阀件、在液泵出口后设有第二流向控制阀件，保证高压冷媒不会直接作 用在液泵上， 保证液泵可以长期正常使用。 当液泵系统运行时： 本发明在压缩 机入口前设有第一通断控制阀件、在压缩机出口后设有第一流向控制阀件，保 证冷媒不会灌进压缩机。 本发明设有带第三流向控制阀件的液泵旁通管， 液泵 不会形成自循环， 最大限度利用了液泵的能力。
附图说明
图 1是本发明具体实施方式一的结构示意图；
图 2是本发明具体实施方式二的结构示意图；
图 3是本发明具体实施方式三的结构示意图；
图 4是本发明具体实施方式四的结构示意图。
图中： 1-储液器； 2-第二通断控制阀件； 3-液泵； 4-流量调节阀； 5-第二流 向控制阀件； 6-第三流向控制阀件； 7-第三通断控制阀件； 8-节流装置； 9-蒸 发器； 10-第一通断控制阀件； 11-压缩机； 12-第一流向控制阀件； 13-第四流 向控制阀件； 14-冷凝器； 15-储液器旁通管； 16-液泵旁通管； 17-节流装置旁 通管； 18-压缩机旁通管。
具体实施方式
下面通过具体的实施方式并结合附图对本发明做进一步详细说明。
本发明具体实施方式一， 参见图 1 , 该图为本发明具体实施方式一的结构 示意图。
如图 1所示， 本发明具体实施方式一所述空调， 包括蒸发器 9、 冷凝器 14、 压缩机 11、 液泵 3、 储液器 1、 第一通断控制阀件 10、 第一流向控制阀件 12、 第二通断控制阀件 2、 第二流向控制阀件 5、 节流装置 8、 带第三流向控制阀 件 6的液泵旁通管 16和带第四流向控制阀件 13的压缩机旁通管 18。 所述第一通断控制阀件 10、 第二通断控制阀件 2可以分别为电磁阀或截止 阀或球阀或电动球阀。 所述第一流向控制阀件 12、 第二流向控制阀件 5、 第三 流向控制阀件 6和第四流向控制阀件 13可以分别为单向阀或截止阀或球阀或 电动球阀。
压缩机 11用于将低温低压冷媒蒸汽压缩成高温高压冷媒蒸汽。液泵 3用于 输送液态冷媒，且可在高运行压力下稳定工作而不产生泄漏。 液泵 3具体可以 为磁力驱动的工业液体泵或屏蔽泵。 冷凝器 14用于气态冷媒放热液化， 蒸发 器 9用于液态冷媒吸热气化。 节流装置 8用于冷媒的流量控制， 在压缩机 11 运行时执行压缩机系统流量控制逻辑，在液泵 3运行时执行液泵系统流量控制 逻辑。所述节流装置 8具体可以为电子膨胀阀或其他具有开度调节功能的节流 阀件。 储液器 1用于储存一定量的冷媒， 保证液泵 3运行时有足够的供液。 第 一通断控制阀件 10和第二通断控制阀件 2用于液泵 3与压缩机 11两套系统的 切换。 第一流向控制阀件 12、 第二流向控制阀件 5、 第三流向控制阀件 6和第 四流向控制阀件 13用于冷媒流向的控制。 所述冷媒具体可以为氟利昂。
所述压缩机 11入口经第一通断控制阀件 10耦合至蒸发器 9的出口， 所述 压缩机 11 出口经第一流向控制阀件 12耦合至冷凝器 14的入口； 所述液泵 3 入口经第二通断控制阀件 2耦合至储液器 1的出口，所述液泵 3出口经第二流 向控制阀件 5耦合至节流装置 8的入口； 所述冷凝器 14出口耦合至储液器 1 入口， 所述节流装置 8出口耦合至蒸发器 9入口； 所述压缩机旁通管 18入口 耦合至蒸发器 9出口、压缩机旁通管 18出口耦合至冷凝器 14入口， 液泵旁通 管 16入口耦合至储液器 1出口、 液泵旁通管 16出口耦合至节流装置 8入口。
第二通断控制阀件 2在液泵系统运行时开启，第一通断控制阀件 10在液泵 系统运行时关闭， 防止液态冷媒进入压缩机 11。 第二通断控制阀件 2在压缩 机系统运行时关闭， 防止压缩机 11运行时的高压冷媒作用在液泵 3上损坏液 泵。 第一通断控制阀件 10在压缩机系统运行时开启。
第一流向控制阀件 12用于防止液泵系统运行时冷媒灌回压缩机 11 , 第四 流向控制阀件 13用于防止压缩机 11系统运行时从压缩机出口排出的高压气体 通过压缩机旁通管 18直接回到压缩机入口损坏压缩机。 第二流向控制阀件 5 用于防止压缩机系统运行时高压作用在液泵 3上，第三流向控制阀件 6用于防 止液泵系统运行时从液泵出来的液态冷媒经过液泵旁通管 16回到液泵。
本发明具体实施方式一所述空调的工作原理如下：
压缩机系统工作时， 从压缩机 11出口出来的冷媒经第一流向控制阀件 12、 冷凝器 14, 储液器 1、 液泵旁通管 16、 第三流向控制阀件 6、 节流装置 8、 蒸 发器 9和第一通断控制阀件 10回到压缩机 11完成循环。
液泵系统工作时， 从液泵 3 出口出来的冷媒经第二流向控制阀件 5、 节流 装置 8、 蒸发器 9、 压缩机旁通管 18、 第四流向控制阀件 13、 冷凝器 14、 储 液器 1和第二通断控制阀件 2回到液泵 3完成循环。
所述储液器 1出口应高于液泵 3入口， 储液器 1的高度 H的计算公式可采 用： H> ( NPSH + LxR+Z ) /r, 其中 r为储液器 1内冷媒的密度， NPSH为液泵 3的气蚀余量， L为储液器 1出口至液泵 3入口的管路长度， R为储液器 1出 口至液泵 3入口单位管长磨损阻力， Z为储液器 1出口至液泵 3入口的局部阻 力损失。 这可保证液态冷媒进入液泵 3之前有一定的过冷度， 从而保证液泵 3 的稳定运行。
在流量相同条件下，液泵 3的消耗功率远小于压缩机 11的消耗功率。例如： 对于 20kW制冷量的机组， 在流量相同条件下， 液泵 3的消耗功率不到压缩机 11 消耗功率的 10% , 对于更大制冷量的机组， 两者相差更多， 因此本发明节 能效果明显。本发明的压缩机系统和液泵系统共用冷凝器和蒸发器， 节约了成 本。本发明由于不是直接引室外新风到机房室内，机房室内的温湿度和洁净度 便于控制， 本发明可以满足机房室内洁净度要求。
本发明具体实施方式二， 参见图 2, 该图为本发明具体实施方式一的结构 示意图。
如图 2所示， 本发明具体实施方式二所述空调与具体实施方式一的不同之 处在于： 本发明具体实施方式二所述的空调还包括储液器旁通管 15 , 所述储 液器旁通管 15并联在储液器 1 两端。 例如在图 2中， 所述储液器旁通管 15 入口耦合至冷凝器 14出口，所述储液器旁通管 15出口耦合至第二通断控制阀 件 2入口， 其中， 所述储液器旁通管 15出口在液泵旁通管 16入口与第二通断 控制阀件 2入口交汇点之后。 或者所述储液器旁通管 15出口在液泵旁通管 16 入口与第二通断控制阀件 2入口交汇点之前（图 2中未示出）。
本发明具体实施方式二所述空调与具体实施方式一的工作原理的不同之处 在于： 液泵系统工作时， 从冷凝器 14 出来的冷媒一部分经储液器 1 , 一部分 经储液器旁通管 15 , 两部分冷媒在第二通断控制阀件 2前混合后回到液泵 3 完成循环。 本发明具体实施方式二所述空调， 通过储液器旁通管 15引一部分 冷凝器 14中的低温冷媒增加液泵 3入口的过冷度， 维持液泵 3的稳定运行防 止气蚀， 避免损坏液泵 3。
本发明具体实施方式三， 参见图 3 , 该图为本发明具体实施方式一的结构 示意图。
如图 3所示， 本发明具体实施方式三所述空调与具体实施方式二的不同之 处在于： 在本发明具体实施方式三中， 所述第一通断控制阀件 10为第一三通 通断控制阀件， 所述第一三通通断控制阀件入口与蒸发器 9出口耦合、 第一三 通通断控制阀件的两个出口分别与压缩机旁通管 18入口、压缩机 11入口耦合； 所述第二通断控制阔件 2为第二三通通断控制阔件，所述第二三通通断控制阀 件入口与储液器 1出口耦合、第二三通通断控制阀件的两个出口分别与液泵旁 通管 16入口、 液泵 3入口耦合。
本发明具体实施方式三所述空调的工作原理如下： 压缩机系统工作时， 从 压缩机 11 出口出来的冷媒经第一流向控制阀件 12、 冷凝器 14, 从冷凝器 14 出来的冷媒一部分经储液器 1 ,一部分经储液器旁通管 15 , 两部分冷媒在第二 三通通断控制阀件前混合后流经第二三通通断控制阀件、 液泵旁通管 16、 第 三流向控制阀件 6、 节流装置 8、 蒸发器 9、 第一三通控制阀件回到压缩机 11 完成循环。
液泵系统工作时， 从液泵 3 出口出来的冷媒经第二流向控制阀件 5、 节流 装置 8、 蒸发器 9, 第一三通控制阀件、 压缩机旁通管 18、 第四流向控制阀件 13、 冷凝器 14, 从冷凝器 14出来的冷媒一部分经储液器 1 , 一部分经储液器 旁通管 15 , 两部分冷媒在第二三通通断控制阀件前混合后流经第二三通通断 控制阀件回到液泵 3完成循环。
本发明具体实施方式四， 参见图 4, 该图为本发明具体实施方式一的结构 示意图。 如图 4所示， 本发明具体实施方式四所述空调与具体实施方式二的不同之 处在于： 本发明具体实施方式四所述的空调还包括流量调节阀 4, 所述流量调 节阀 4用于对液泵 3内冷媒的流量进行调节。在图 4中， 流量调节阀 4可以放 置在液泵 3出口与第二流向控制阀件 5之间。当然流量调节阀 4也可以放置在 液泵 3入口与第二通断控制阀件 2之间，或者放置在第二流向控制阀件 5与液 泵旁通管 16出口之间， 或者放置在液泵旁通管 16入口与第二通断控制阀件 2 之间。 所述流量调节阀 4可以为恒流阀、 电子膨胀阀等。
本发明具体实施方式四所述的空调还包括带第三通断控制阀件 7的节流装 置旁通管 17 , 所述节流装置 8可以为热力膨胀阀、 电子膨胀阀或者毛细管等。 所述节流装置旁通管 17并联在节流装置 8两端。 第三通断控制阀件 7在压缩 机系统运行时关闭， 防止冷媒从节流装置旁通管 17直接进入蒸发器 9。 第三 通断控制阀件 7在液泵系统运行时开启。
本发明具体实施方式四的工作原理如下：
当压缩机系统工作时，从压缩机 11出口排出的高温高压的蒸汽经过第一流 向控制阀件 12在冷凝器 14中液化冷凝，之后高温高压的冷媒液体进入到储液 器 1 , 从储液器 1出来的液体依次经过液泵旁通管 16、 第三流向控制阀件 6, 在节流装置 8处进行降压节流，节流后的低温低压冷媒液体在蒸发器 9中进行 气化蒸发，低温低压的冷媒蒸汽经过第一通断控制阀件 10回到压缩机 11完成 循环。
液泵系统工作时， 从液泵 3中泵出的冷媒经过流量调节阀 4进行流量的调 节后， 依次经过第二流向控制阀件 5 , 节流装置旁通管 17, 第三通断控制阀件 7, 进入蒸发器 9中蒸发， 从蒸发器 9中出来的冷媒蒸汽或两相冷媒经过压缩 机旁通管 18、 第四流向控制阔件 13进入冷凝器 14中进行液化冷凝， 从冷凝 器 14中出来的液态冷媒一部分经过储液器旁通管 15、另一部分经过储液器 1 , 从储液器 1中出来的液态冷媒与储液器旁通管 15中出来的液态冷媒在第二通 断控制阀件 2入口前混合后， 经过第二通断控制阀件 2回到液泵 3完成循环。
上述本发明具体实施方式所述的空调优选用于通信机房。
以上内容是结合具体的优选实施方式对本发明所作的进一步详细说明， 不 能认定本发明的具体实施只局限于这些说明。对于本发明所属技术领域的普通 技术人员来说，在不脱离本发明构思的前提下，还可以做出若干筒单推演或替 换， 都应当视为属于本发明的保护范围。

Claims

权 利 要 求
1、 一种空调， 包括蒸发器（9)、 冷凝器 （14)、 压缩机（11)、 液泵（3) 和储液器 （1 ), 其特征在于： 所述空调还包括第一通断控制阀件（10)、 第一 流向控制阀件 （12)、 第二通断控制阀件（2)、 第二流向控制阀件 （5)、 节流 装置 （8)、 带第三流向控制阀件 （6 ) 的液泵旁通管 （16 )和带第四流向控制 阀件（I3) 的压缩机旁通管 （is );
所述压缩机（ 11 )入口经第一通断控制阀件（ 10 )耦合至所述蒸发器（ 9 ) 的出口， 所述压缩机（ 11 ) 出口经所述第一流向控制阀件（ 12 )耦合至所述冷 凝器（14 ) 的入口；
所述液泵（ 3 )入口经所述第二通断控制阀件（ 1 )耦合至所述储液器（ 1 ) 的出口， 所述液泵（ 3 ) 出口经所述第二流向控制阀件（ 5 )耦合至所述节流装 置（8 ) 的入口；
所述冷凝器（ 14 ) 出口耦合至所述储液器（ 1 )入口， 所述节流装置（ 8 ) 出口耦合至所述蒸发器 （ 9 )入口；
所述压缩机旁通管 （ 18 )入口耦合至所述蒸发器 （ 9 ) 出口、 所述压缩机 旁通管（ 18 ) 出口耦合至所述冷凝器（ 14 )入口， 所述液泵旁通管（ 16 )入口 耦合至所述储液器 （1 ) 出口、 所述液泵旁通管 （16 ) 出口耦合至所述节流装 置（8 )入口。
2、 根据权利要求 1所述的空调， 其特征在于： 所述空调还包括流量调节 阀 （4 )和带第三通断控制阀件 （7 ) 的节流装置旁通管 （17), 所述流量调节 阀 （4)用于对液泵（3) 内冷媒的流量进行调节， 所述节流装置旁通管 （17) 并联在节流装置 （8 ) 两端。
3、根据权利要求 1所述的空调，其特征在于：所述第一通断控制阀件（ 10 ) 为第一三通通断控制阀件， 所述第一三通通断控制阀件（ 10 )入口与所述蒸发 器（9 ) 出口耦合、 所述第一三通通断控制阀件 （10) 的两个出口分别与所述 压缩机旁通管 （ 18 )入口、 所述压缩机（ 11 )入口耦合；
所述第二通断控制阔件 （2 )为第二三通通断控制阔件， 所述第二三通通 断控制阀件（ 1 )入口与所述储液器（ 1 ) 出口耦合、 所述第二三通通断控制阀 件的两个出口分别与所述液泵旁通管 （16)入口、 所述液泵（3)入口耦合。
4、 根据权利要求 1-3任一所述的空调， 其特征在于： 所述空调还包括储 液器旁通管 （15 ), 所述储液器旁通管 （15 )并联在所述储液器 （1 ) 两端。
5、 根据权利要求 1-3任一所述的空调， 其特征在于： 所述第一通断控制 阀件（ 10 )、第二通断控制阀件（ 2 )分别为电磁阀或截止阀或球阀或电动球阀。
6、 根据权利要求 1-3任一所述的空调， 其特征在于： 所述第一流向控制 阀件（ 12 )、 第二流向控制阀件（ 5 )、 第三流向控制阀件（ 6 )和第四流向控制 阀件（1 3 )分别为单向阀或截止阀或球阀或电动球阀。
7、根据权利要求 2所述的空调，其特征在于： 所述第三通断控制阀件（ 7 ) 为电磁阀或截止阀或球阀或电动球阀。
8、 根据权利要求 1-3任一所述的空调， 其特征在于： 所述空调用于通信 机房。
PCT/CN2010/070578 2009-02-19 2010-02-09 一种空调 WO2010094227A1 (zh)

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