WO2016000652A1 - 引射制冷循环装置 - Google Patents

引射制冷循环装置 Download PDF

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Publication number
WO2016000652A1
WO2016000652A1 PCT/CN2015/083254 CN2015083254W WO2016000652A1 WO 2016000652 A1 WO2016000652 A1 WO 2016000652A1 CN 2015083254 W CN2015083254 W CN 2015083254W WO 2016000652 A1 WO2016000652 A1 WO 2016000652A1
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WIPO (PCT)
Prior art keywords
ejector
heat exchanger
refrigeration cycle
chamber
electronic expansion
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Ceased
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PCT/CN2015/083254
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English (en)
French (fr)
Inventor
魏广飞
吴俊鸿
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Publication of WO2016000652A1 publication Critical patent/WO2016000652A1/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
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0011—Ejectors with the cooled primary flow at reduced or low pressure
    • 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
    • F25B2400/23—Separators

Definitions

  • the invention relates to the technical field of air conditioning refrigeration cycle devices, and in particular to an ejector refrigeration cycle device.
  • the steam compression/ejection refrigeration system is an effective energy-saving refrigeration system, which can reduce the throttling expansion loss, reduce the compressor pressure ratio, and greatly improve the efficiency of the refrigeration system, and its utilization potential is huge.
  • the actual application of the ejector is not found in the household air-conditioning industry, and it has only been reported in some scientific papers.
  • the application conditions of the ejector in the vapor compression/ejection refrigeration system are very narrow.
  • the design idea is point-to-point design, and the ejector is designed according to the specific refrigeration cycle conditions (evaporation temperature, condensation temperature, etc.).
  • the structural parameters of the device when the air conditioning conditions change, the ejector will lose or greatly reduce its effect, so the existing vapor compression / ejector refrigeration system is not suitable for variable frequency air conditioners with wide changing conditions.
  • the general household inverter air conditioner uses the refrigerant working medium R410a, etc., and is used in the existing vapor compression/ejection refrigeration system.
  • the inlet state of the ejector nozzle is saturated or supercooled liquid, and the working medium enters the two phases after being accelerated by the nozzle. State, and the dryness is low, and the ejector ejector working state is saturated or superheated gas, which makes the working fluid and the ejector fluid in the ejector mixing chamber be in different phase, resulting in mixing in the ejector mixing chamber.
  • the effect is not ideal (gas-liquid two-phase mixing), affecting its energy-saving effect.
  • the existing ejector refrigeration cycle inverter air conditioner has a narrow range of operating conditions
  • the mixing state in the mixing chamber in the ejector is gas-liquid two-phase mixing, and the mixing efficiency is low.
  • the technical problem to be solved by the present invention is to provide an ejector refrigeration cycle device, which greatly expands the range of working conditions suitable for the ejector, and the ejector application efficiency is greatly improved.
  • the ejector refrigeration cycle device comprises: a compressor, an outdoor heat exchanger, a gas-liquid separator, an indoor heat exchanger and an ejector, the compressor, an outdoor heat exchanger, a gas-liquid separator, an indoor heat exchanger And the ejector is connected by a pipeline to form a closed refrigeration cycle system, wherein the refrigerant medium flows in the refrigeration cycle system; wherein the ejector refrigeration cycle device
  • the first electronic expansion valve and the second electronic expansion valve are further included;
  • the compressor exhaust port is connected to the outdoor heat exchanger through a pipe, and the other end of the outdoor heat exchanger is connected to the first electronic expansion valve through a pipe, the first electronic expansion valve
  • the other end is connected to the gas-liquid separator through a pipeline;
  • the gas-liquid separator has an air outlet and a liquid outlet, the air outlet is connected to the first inlet of the ejector through a pipeline, and the liquid outlet is connected to the second electronic expansion valve through the pipeline;
  • the second electron The other end
  • the ejector refrigeration cycle device includes a first four-way reversing valve and a second four-way reversing valve, and the first four-way reversing valve is connected to one end of the outdoor heat exchanger through a pipe.
  • the second four-way reversing valve is connected to the other end of the outdoor heat exchanger through a pipe.
  • the four interfaces of the first four-way reversing valve are respectively connected to the outdoor heat exchanger, the compressor exhaust port, the second inlet of the ejector and the indoor heat exchanger through a pipeline.
  • the four interfaces of the second four-way reversing valve are respectively connected to the outdoor heat exchanger, the first electronic expansion valve, the second electronic expansion valve and the indoor heat exchanger through a pipeline.
  • the compressor is an inverter compressor.
  • the ejector includes an ejector nozzle, an ejector receiving chamber, an ejector mixing chamber, and an ejector diffuser chamber, the ejector nozzle being mounted at an outer end of the ejector receiving chamber
  • the ejector receiving chamber, the ejector mixing chamber and the ejector diffuser are sequentially connected and the inner chamber forms a vapor-liquid processing chamber; the outlet of the ejector nozzle is in communication with the vapor-liquid processing chamber.
  • the ejector nozzle includes a first inlet having an ejector.
  • the ejector receiving chamber includes a second inlet having an ejector.
  • the ejector diffuser chamber includes an outlet having an ejector.
  • the ejector receiving chamber, the ejector mixing chamber and the ejector diffuser chamber each adopt a pipe structure, and the ejector diffuser chamber adopts a horn-like pipe structure; the ejector mixing chamber
  • the inner diameter dimension is less than the maximum inner diameter dimension of the ejector receiving chamber; the inner diameter dimension of the ejector mixing chamber is less than the largest inner diameter dimension of the ejector diffuser chamber.
  • the ejector refrigeration cycle device of the present invention comprises: a compressor, an outdoor heat exchanger, a gas-liquid separator, an indoor heat exchanger and an ejector, and further includes a first electronic expansion valve and a second electronic expansion valve;
  • the exhaust port of the machine is connected to the outdoor heat exchanger through a pipeline, and the other end of the outdoor heat exchanger is connected to the first electronic expansion valve through a pipeline, and the other end of the first electronic expansion valve is connected to the gas-liquid separator through a pipeline;
  • the gas-liquid separator has a a gas port and a liquid outlet, the gas outlet is connected to the first inlet of the ejector through a pipe, and the liquid outlet is connected to the second electronic expansion valve through a pipe;
  • the other end of the second electronic expansion valve is connected to the indoor heat exchanger through a pipe;
  • the other end of the device is connected to the second inlet of the ejector through a pipe; the outlet of the ejector passes The pipe connects the compressor su
  • the first electronic working valve can adjust the state and flow rate of the first inlet working fluid of the ejector, greatly expand the range of the ejector to adapt to the working condition, and the application efficiency of the ejector is greatly improved, and the energy efficiency of the air conditioner is improved.
  • the ejector refrigeration cycle device of the present invention includes a first four-way directional control valve and a second four-way directional control valve, wherein the first four-way directional control valve is connected to one end of the outdoor heat exchanger through a pipe, The second four-way reversing valve is connected to the other end of the outdoor heat exchanger through a pipe, so that it can simultaneously adapt to the cooling and heating conditions, and the ejector can exert its ejector function under both cooling and heating conditions.
  • the ejector comprises an ejector nozzle, an ejector receiving chamber, an ejector mixing chamber and an ejector diffusing chamber, and the ejector is first for the alkane refrigerant such as R410a commonly used in household air conditioners.
  • the state of the imported working fluid is saturated or superheated gas in the gas-liquid separator.
  • the phase change of the ejector in the nozzle is small, and the dryness of the nozzle outlet is very large (basically also saturated gas), which is mixed in the ejector.
  • the indoor working fluid and the ejector fluid are basically mixed in the same phase (gas-gas mixing), so that the mixing is sufficient, the mixing effect is greatly improved, and the ejector application efficiency is greatly improved.
  • the ejector refrigeration cycle device of the present invention has a relatively simple structure compared to other refrigeration cycle devices, saving material and production costs.
  • FIG. 1 is a schematic structural view of an ejector refrigeration cycle device of the present invention
  • Figure 3 is a pressure-pressing diagram of the heating operation of the ejector refrigeration cycle apparatus of the present invention
  • FIG. 4 is a schematic view showing the structure of an ejector of the ejector refrigeration cycle apparatus of the present invention.
  • 101 compressor
  • 102 first four-way reversing valve
  • 103 outdoor heat exchanger
  • 104 second four-way reversing valve
  • 105 first electronic expansion valve
  • 106 gas-liquid separator
  • Two electronic expansion valve 108 - indoor heat exchanger
  • 109 - ejector 201 - ejector nozzle
  • 202 - ejector receiving chamber
  • 203 - ejector mixing chamber
  • 204 - ejector diffuser.
  • the present invention provides an ejector refrigeration cycle device, as shown in FIG. 1 and FIG. 4, including: a compressor 101, an outdoor heat exchanger 103, a gas-liquid separator 106, and an indoor exchange.
  • the heat exchanger 108 and the ejector 109, the compressor 101, the outdoor heat exchanger 103, the gas-liquid separator 106, the indoor heat exchanger 108 and the ejector 109 are connected by pipes to form a closed refrigeration cycle system, and the refrigerant is cooled.
  • the ejector refrigeration cycle device further includes a first electronic expansion valve 105 and a second electronic expansion valve 107; the compressor exhaust port passes The pipe is connected to the outdoor heat exchanger 103, and the other end of the outdoor heat exchanger 103 is connected to the first electronic expansion valve 105 through a pipe.
  • the other end of the first electronic expansion valve 105 is connected to the gas-liquid separator 106 through a pipe;
  • the gas-liquid separator 106 has An air outlet and a liquid outlet, the air outlet is connected to the first inlet of the ejector 109 through a pipe, and the liquid outlet is connected to the second electronic expansion valve 107 through a pipe;
  • the other end of the second electronic expansion valve 107 is connected to the indoor heat exchanger through a pipe 108;
  • the other end of the indoor heat exchanger 108 is connected to the second inlet of the ejector 109 by a pipe;
  • the outlet of the ejector 109 is connected to the compressor suction port through a pipe.
  • the ejector refrigeration cycle device includes a first four-way reversing valve 102 and a second four-way reversing valve 104, and the first four-way reversing valve 102 is connected to the outdoor heat exchange through a pipeline.
  • One end of the device 103, the second four-way switching valve 104 is connected to the other end of the outdoor heat exchanger 103 through a pipe.
  • the four interfaces of the first four-way switching valve 102 are respectively connected to the outdoor heat exchanger 103, the compressor exhaust port, the second inlet of the ejector 109, and the indoor heat exchanger 108 through pipes.
  • the four interfaces of the second four-way switching valve 104 are respectively connected to the outdoor heat exchanger 103, the first electronic expansion valve 105, the second electronic expansion valve 107, and the indoor heat exchanger 108 through pipes.
  • the compressor 101 is an inverter compressor.
  • the ejector 109 includes an ejector nozzle 201, an ejector receiving chamber 202, an ejector mixing chamber 203, and an ejector diffuser chamber 204, the ejector nozzle 201 Mounted at an outer end of the ejector receiving chamber 202, the ejector receiving chamber 202, the ejector mixing chamber 203 and the ejector diffuser chamber 204 are sequentially connected and the inner chamber forms a vapor-liquid processing chamber; An outlet of the ejector nozzle 201 is in communication with the vapor-liquid processing chamber.
  • the ejector nozzle 201 includes a first inlet having an ejector.
  • the ejector receiving chamber 202 includes a second inlet having an ejector.
  • the ejector diffuser chamber 204 includes an outlet having an ejector.
  • the ejector receiving chamber 202, the ejector mixing chamber 203, and the ejector diffuser chamber 204 each adopt a pipe structure, and the ejector diffuser chamber 204 adopts a horn-like pipe structure;
  • the inner diameter dimension of the mixing chamber 203 is less than the maximum inner diameter dimension of the ejector receiving chamber 202; the inner diameter of the ejector mixing chamber 203 is smaller than the largest inner diameter dimension 204 of the ejector diffuser.
  • the present embodiment preferably provides an ejector refrigeration cycle device suitable for variable operating conditions, including a compressor 101 and a first four-way reversing valve. 102, an outdoor heat exchanger 103, a second four-way switching valve 104, a first electronic expansion valve 105, a gas-liquid separator 106, a second electronic expansion valve 107, an indoor heat exchanger 108, an ejector 109;
  • the device 109 includes an ejector nozzle 201, an ejector receiving chamber 202, an ejector mixing chamber 203, and an ejector diffuser chamber 204.
  • the high temperature and high pressure refrigerant is discharged from the compressor 101 (state point 1), and enters the outdoor through the first four-way switching valve 102.
  • the heat exchanger 103 After the heat exchanger 103 is condensed, it becomes a low-temperature high-pressure refrigerant liquid (state point 2), and after passing through the second four-way switching valve 104, the refrigerant is throttled to an appropriate medium-temperature medium pressure by adjusting the first electronic expansion valve 105.
  • the phase refrigerant enters the gas-liquid separator 106 (state point 3).
  • the refrigerant After passing through the gas-liquid separator 106, the refrigerant is divided into two paths, one is a saturated gaseous refrigerant (state point 5), and enters the inlet of the ejector nozzle 201.
  • the refrigerant is accelerated by the ejector nozzle 201 to become a high-speed low-pressure two-phase refrigerant (state point 8) to enter the ejector receiving chamber 202, and then the low-pressure saturated or superheated refrigerant gas (state point 7) is introduced.
  • the ejector mixing chamber 203 performs a thorough mixing of the approximately in-phase gas, and then enters the ejector diffuser chamber 204 for deceleration and pressurization, and finally enters the compressor 101 inlet (state point 10).
  • the other circuit is a saturated liquid refrigerant (state point 4), which is further throttled and depressurized by the second electronic expansion valve 107 to become a low-temperature low-pressure two-phase refrigerant (state point 6) after entering the indoor heat exchanger 108 for evaporation and heat absorption.
  • the high temperature and high pressure refrigerant is discharged from the compressor 101 (state point 1), and enters through the first four-way switching valve 102.
  • the indoor heat exchanger 108 After the indoor heat exchanger 108 is condensed, it becomes a low-temperature high-pressure refrigerant liquid (state point 11), and after passing through the second four-way switching valve 104, the refrigerant is throttled to an appropriate medium-temperature and medium-pressure by adjusting the electronic expansion valve 105.
  • the phase refrigerant enters the gas-liquid separator 106 (state point 3).
  • the refrigerant After passing through the gas-liquid separator 106, the refrigerant is divided into two paths, one is a saturated gaseous refrigerant (state point 5), and enters the inlet of the ejector nozzle 201.
  • the refrigerant is accelerated by the ejector nozzle 201 to become a high-speed low-pressure two-phase refrigerant (state point 8) to enter the ejector receiving chamber 202, and then the low-pressure saturated or superheated refrigerant gas (state point 12) is introduced.
  • the ejector mixing chamber 203 performs near-phase gas mixing sufficiently, and then enters the ejector diffuser chamber 204 to decelerate and pressurize, and finally enters the compressor suction port (state point 10).
  • the embodiment of the present invention provides an ejector refrigeration cycle device suitable for variable operating conditions, which has the following features:
  • the ejector can adapt to the cooling and heating conditions at the same time. Under the conditions of refrigeration and heating, the ejector can exert its ejector effect;
  • the first electronic expansion valve can adjust the working state of the ejector inlet, so that the ejector can adapt to the change of the operating condition of the inverter air conditioner and improve the energy efficiency of the air conditioner;
  • the working state of the ejector nozzle inlet is the saturated gas in the gas-liquid separator.
  • the nozzle outlet has a large dryness (basically saturated gas), which can make the working fluid and ejector in the ejector mixing chamber.
  • the fluid phase is approximately the same, so that the mixing is sufficient, and finally the effect of improving energy efficiency is fully achieved;
  • the cycle adds an ejector, a gas-liquid separator, a four-way valve and an electronic expansion valve. Although more devices are added, they are compared to other ejector cycles. This loop structure has been relatively simple.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
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  • General Engineering & Computer Science (AREA)
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Abstract

一种引射制冷循环装置，其中压缩机(101)排气口通过管道连接室外换热器(103)，室外换热器(103)的另一端通过管道连接第一电子膨胀阀(105)，第一电子膨胀阀(105)的另一端通过管道连接气液分离器(106)；气液分离器(106)具有出气口和出液口，出气口通过管道连接引射器(109)的第一进口，出液口通过管道连接第二电子膨胀阀(107)；第二电子膨胀阀(107)的另一端连接室内换热器(108)；室内换热器(108)的另一端连接引射器(109)的第二进口；引射器(109)的出口通过管道连接压缩机(101)吸气口。空调工况变化时，通过第一电子膨胀阀(105)调节引射器(109)第一进口工质状态及流量，扩大引射器(109)适应工况范围，提升空调运行能效。

Description

引射制冷循环装置
相关申请
本专利申请要求2014年7月4日申请的，申请号为201410317304.0，名称为“引射制冷循环装置”的中国专利申请的优先权，在此将其全文引入作为参考。
技术领域
本发明涉及空调制冷循环装置技术领域，特别是涉及一种引射制冷循环装置。
背景技术
蒸汽压缩/引射制冷系统是一种有效的节能制冷系统，可以减少节流膨胀损失，降低压缩机压力比，大大提高制冷系统效率，其利用潜力巨大。目前，家用空调行业内未见引射器的实际应用，仅在部分科技论文中有所报道。而现有科技论文中蒸汽压缩/引射制冷系统中引射器的应用工况很窄，其设计思路为点对点设计，根据特定的制冷循环工况(蒸发温度、冷凝温度等)来设计引射器的结构参数，当空调工况变化时，引射器将失去或大大降低其效果，故现有蒸汽压缩/引射制冷系统并不适用于变化工况较广的变频空调。
同时，一般家用变频空调使用制冷工质为R410a等，使用于现有蒸汽压缩/引射制冷系统，引射器喷嘴入口工质状态为饱和或过冷液体，经喷嘴加速后工质进入两相态，且干度较低，而引射器引射工质状态为饱和或过热气体，这使得引射器混合室内的工作流体和引射流体所处相态不同，导致引射器混合室内混合效果不够理想(气液两相混合)，影响其节能效果。
因此，现有的蒸汽压缩/引射制冷系统具有如下问题：
1、现有引射制冷循环变频空调适应的工况范围较窄；
2、引射器中混合室内混合状态为气液两相混合，混合效率较低。
发明内容
本发明所要解决的技术问题在于提供一种引射制冷循环装置，大大扩大引射器适应的工况范围，引射器应用效率有较大提高。
本发明是通过以下技术方案来实现的：
引射制冷循环装置，包括有：压缩机、室外换热器、气液分离器、室内换热器和引射器，所述压缩机、室外换热器、气液分离器、室内换热器和引射器通过管道连接形成密闭的制冷循环系统，制冷工质位于所述制冷循环系统中流动；其中，所述引射制冷循环装置 还包括有第一电子膨胀阀和第二电子膨胀阀；压缩机排气口通过管道连接室外换热器，室外换热器的另一端通过管道连接第一电子膨胀阀，第一电子膨胀阀的另一端通过管道连接气液分离器；气液分离器具有出气口和出液口，出气口通过管道连接引射器的第一进口，出液口通过管道连接第二电子膨胀阀；第二电子膨胀阀的另一端通过管道连接室内换热器；室内换热器的另一端通过管道连接引射器的第二进口；引射器的出口通过管道连接压缩机吸气口。
在其中一个实施例中，所述引射制冷循环装置包括有第一四通换向阀和第二四通换向阀，所述第一四通换向阀通过管道连接室外换热器的一端，所述第二四通换向阀通过管道连接室外换热器的另一端。
进一步地，所述第一四通换向阀的四个接口分别通过管道连接室外换热器、压缩机排气口、引射器的第二进口和室内换热器。
进一步地，所述第二四通换向阀的四个接口分别通过管道连接室外换热器、第一电子膨胀阀、第二电子膨胀阀和室内换热器。
进一步地，所述压缩机为一种变频压缩机。
进一步地，所述引射器包括有引射器喷嘴、引射器接收室、引射器混合室和引射器扩压室，所述引射器喷嘴安装于引射器接收室的外端部，所述引射器接收室、引射器混合室和引射器扩压室依次连接而内腔形成汽液处理腔室；所述引射器喷嘴的出口与汽液处理腔室连通。
进一步地，所述引射器喷嘴包括有引射器的第一进口。
进一步地，所述引射器接收室包括有引射器的第二进口。
进一步地，所述引射器扩压室包括有引射器的出口。
进一步地，所述引射器接收室、引射器混合室和引射器扩压室均采用管道结构，所述引射器扩压室采用喇叭状管道结构；所述引射器混合室的内径尺寸小于引射器接收室的最大内径尺寸；所述引射器混合室的内径尺寸小于引射器扩压室的最大内径尺寸。
本发明的有益效果如下：
本发明的引射制冷循环装置，包括有：压缩机、室外换热器、气液分离器、室内换热器和引射器，还包括有第一电子膨胀阀和第二电子膨胀阀；压缩机排气口通过管道连接室外换热器，室外换热器的另一端通过管道连接第一电子膨胀阀，第一电子膨胀阀的另一端通过管道连接气液分离器；气液分离器具有出气口和出液口，出气口通过管道连接引射器的第一进口，出液口通过管道连接第二电子膨胀阀；第二电子膨胀阀的另一端通过管道连接室内换热器；室内换热器的另一端通过管道连接引射器的第二进口；引射器的出口通过 管道连接压缩机吸气口。空调工况变化时，可通过第一电子膨胀阀调节引射器第一进口工质状态及流量，大大扩大引射器适应工况范围，引射器应用效率有较大提高，提升空调运行能效。
进一步地，本发明的引射制冷循环装置，包括有第一四通换向阀和第二四通换向阀，所述第一四通换向阀通过管道连接室外换热器一端，所述第二四通换向阀通过管道连接室外换热器的另一端，因此，可同时适应制冷制热工况，在制冷和制热工况下，引射器均能够发挥其引射作用。
进一步地，引射器包括有引射器喷嘴、引射器接收室、引射器混合室和引射器扩压室，针对目前家用空调中常用的R410a等烷烃制冷剂，引射器第一进口工质状态为气液分离器中的饱和或者过热气体，引射器在喷嘴内发生相变程度很小，喷嘴出口工质干度很大(基本也为饱和气体)，在引射器混合室内工作流体和引射流体基本为同相态混合(气气混合)，从而混合充分，混合效果大大改善，引射器应用效率有较大提高。
进一步地，本发明的引射制冷循环装置，相比于其他制冷循环装置，结构相对简单很多，节约了物料和生产成本。
附图说明
图1为本发明引射制冷循环装置的结构示意图；
图2为本发明引射制冷循环装置的制冷运行压焓图；
图3为本发明引射制冷循环装置的制热运行压焓图；
图4为本发明引射制冷循环装置的引射器结构示意图。
图中：
101—压缩机；102—第一四通换向阀；103—室外换热器；104—第二四通换向阀；105—第一电子膨胀阀；106—气液分离器；107—第二电子膨胀阀；108—室内换热器；109—引射器；201—引射器喷嘴；202—引射器接收室；203—引射器混合室；204—引射器扩压室。
具体实施方式
本发明为了解决现有技术的问题，提出了一种引射制冷循环装置，如图1、图4所示，包括有：压缩机101、室外换热器103、气液分离器106、室内换热器108和引射器109，所述压缩机101、室外换热器103、气液分离器106、室内换热器108和引射器109通过管道连接形成密闭的制冷循环系统，制冷工质位于所述制冷循环系统中流动；其中，所述引射制冷循环装置还包括有第一电子膨胀阀105和第二电子膨胀阀107；压缩机排气口通过 管道连接室外换热器103，室外换热器103的另一端通过管道连接第一电子膨胀阀105，第一电子膨胀阀105的另一端通过管道连接气液分离器106；气液分离器106具有出气口和出液口，出气口通过管道连接引射器109的第一进口，出液口通过管道连接第二电子膨胀阀107；第二电子膨胀阀107的另一端通过管道连接室内换热器108；室内换热器108的另一端通过管道连接引射器109的第二进口；引射器109的出口通过管道连接压缩机吸气口。
在其中一个实施例中，所述引射制冷循环装置包括有第一四通换向阀102和第二四通换向阀104，所述第一四通换向阀102通过管道连接室外换热器103的一端，所述第二四通换向阀104通过管道连接室外换热器103的另一端。
进一步地，所述第一四通换向阀102的四个接口分别通过管道连接室外换热器103、压缩机排气口、引射器109的第二进口和室内换热器108。
进一步地，所述第二四通换向阀104的四个接口分别通过管道连接室外换热器103、第一电子膨胀阀105、第二电子膨胀阀107和室内换热器108。
进一步地，所述压缩机101为一种变频压缩机。
进一步地，如图4，所述引射器109包括有引射器喷嘴201、引射器接收室202、引射器混合室203和引射器扩压室204，所述引射器喷嘴201安装于引射器接收室202的外端部，所述引射器接收室202、引射器混合室203和引射器扩压室204依次连接而内腔形成汽液处理腔室；所述引射器喷嘴201的出口与所述汽液处理腔室连通。
进一步地，所述引射器喷嘴201包括有引射器的第一进口。
进一步地，所述引射器接收室202包括有引射器的第二进口。
进一步地，所述引射器扩压室204包括有引射器的出口。
进一步地，所述引射器接收室202、引射器混合室203和引射器扩压室204均采用管道结构，所述引射器扩压室204采用喇叭状管道结构；所述引射器混合室203的内径尺寸小于引射器接收室202的最大内径尺寸；所述引射器混合室203的内径尺寸小于引射器扩压室的最大内径尺寸204。
实施例：
如图1、图2、图3、图4所示，优选地，本实施例提供了一种适用于可变工况的引射制冷循环装置，包含压缩机101、第一四通换向阀102、室外换热器103、第二四通换向阀104、第一电子膨胀阀105、气液分离器106、第二电子膨胀阀107、室内换热器108、引射器109；引射器109包含：引射器喷嘴201、引射器接收室202、引射器混合室203、引射器扩压室204。
结合图1、图4及制冷运行压焓lgP-h图2，系统制冷运行时，高温高压的制冷剂从压缩机101排出(状态点1)，经过第一四通换向阀102进入室外换热器103冷凝之后变成低温高压的制冷剂液体(状态点2)，再经过第二四通换向阀104后通过调节第一电子膨胀阀105将制冷剂节流到适当的中温中压两相态制冷剂进入气液分离器106(状态点3)，经过气液分离器106之后制冷剂被分为两路，一路为饱和气态制冷剂(状态点5)，进入引射器喷嘴201进口，制冷剂经过引射器喷嘴201加速后变为高速低压的两相态制冷剂(状态点8)进入引射器接收室202，再引射低压饱和或者过热制冷剂气体(状态点7)进入引射器混合室203进行近似同相态气气充分混合，之后再进入引射器扩压室204进行减速增压，最后进入压缩机101进口(状态点10)。另一路为饱和液态制冷剂(状态点4)，经过第二电子膨胀阀107进一步节流降压后变为低温低压两相态制冷剂(状态点6)进入室内换热器108蒸发吸热之后变为低压高温饱和或者过热气态制冷剂(状态点7)，再进入引射器接受室202进口，被引射器喷嘴201出口处高速低压制冷剂(状态点8)引射后进入引射器混合室203进行近似同相态充分混合，再进入引射器扩压室204进行减速增压，最后进入压缩机吸气口(状态点10)，完成一次制冷循环。
结合图1、图4及制热运行压焓lgP-h图3，系统制热运行时，高温高压的制冷剂从压缩机101排出(状态点1)，经过第一四通换向阀102进入室内换热器108冷凝之后变成低温高压的制冷剂液体(状态点11)，再经过第二四通换向阀104后通过调节电子膨胀阀105将制冷剂节流到适当的中温中压两相态制冷剂进入气液分离器106(状态点3)，经过气液分离器106之后制冷剂被分为两路，一路为饱和气态制冷剂(状态点5)，进入引射器喷嘴201进口，制冷剂经过引射器喷嘴201加速后变为高速低压的两相态制冷剂(状态点8)进入引射器接收室202，再引射低压饱和或者过热制冷剂气体(状态点12)进入引射器混合室203进行近似同相气气充分混合，再进入引射器扩压室204进行减速增压，最后进入压缩机吸气口(状态点10)。另一路为饱和液态制冷剂(状态点4)，经过第二电子膨胀阀107进一步节流降压后变为低温低压两相态制冷剂(状态点6)进入室外换热器108蒸发吸热之后变为低压高温饱和或者过热气态制冷剂(状态点12)，再进入引射器接受室202进口，被引射器喷嘴201出口处高速低压制冷剂(状态点8)引射后进入引射器混合室203进行近似同相态气气充分混合，再进入引射器扩压室204减速增压，最后进入压缩机101进口(状态点10)，完成一次制热循环。
本实施例提供了的适用于可变工况的引射制冷循环装置，具有以下特点：
1、可同时适应制冷制热工况，在制冷和制热工况下，引射器均能够发挥其引射作用；
2、通过第一电子膨胀阀可调节引射器进口工质状态，使引射器可适应变频空调工况变化，提升空调运行能效；
3、引射器喷嘴进口工质状态为气液分离器中的饱和气体，喷嘴出口工质干度很大(基本也为饱和气体)，可使引射器混合室中的工作流体和引射流体相态近似相同，从而混合充分，最终充分达到提升能效的效果；
4、该循环与现有制冷循环装置相比，增加了一个引射器、一个气液分离器、一个四通阀和一个电子膨胀阀，虽然增加较多器件，但是相比于其他引射循环，此循环结构已相对简单很多。
以上所述实施例仅表达了本发明的实施方式，其描述较为具体和详细，但并不能因此而理解为对本发明专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本发明构思的前提下，还可以做出若干变形和改进，这些都属于本发明的保护范围。因此，本发明专利的保护范围应以所附权利要求为准。

Claims (10)

  1. 一种引射制冷循环装置，包括有：压缩机、室外换热器、气液分离器、室内换热器和引射器，所述压缩机、室外换热器、气液分离器、室内换热器和引射器通过管道连接形成密闭的制冷循环系统，制冷工质位于所述制冷循环系统中流动；其特征在于，所述引射制冷循环装置还包括有第一电子膨胀阀和第二电子膨胀阀；压缩机排气口通过管道连接室外换热器，室外换热器的另一端通过管道连接第一电子膨胀阀，第一电子膨胀阀的另一端通过管道连接气液分离器；气液分离器具有出气口和出液口，出气口通过管道连接引射器的第一进口，出液口通过管道连接第二电子膨胀阀；第二电子膨胀阀的另一端通过管道连接室内换热器；室内换热器的另一端通过管道连接引射器的第二进口；引射器的出口通过管道连接压缩机吸气口。
  2. 根据权利要求1所述的引射制冷循环装置，其特征在于，所述引射制冷循环装置包括有第一四通换向阀和第二四通换向阀，所述第一四通换向阀通过管道连接室外换热器的一端，所述第二四通换向阀通过管道连接室外换热器的另一端。
  3. 根据权利要求2所述的引射制冷循环装置，其特征在于，所述第一四通换向阀的四个接口分别通过管道连接室外换热器、压缩机排气口、引射器的第二进口和室内换热器。
  4. 根据权利要求3所述的引射制冷循环装置，其特征在于，所述第二四通换向阀的四个接口分别通过管道连接室外换热器、第一电子膨胀阀、第二电子膨胀阀和室内换热器。
  5. 根据权利要求1至4中任何一项所述的引射制冷循环装置，其特征在于，所述压缩机为一种变频压缩机。
  6. 根据权利要求1至4中任何一项所述的引射制冷循环装置，其特征在于，所述引射器包括有引射器喷嘴、引射器接收室、引射器混合室和引射器扩压室，所述引射器喷嘴安装于引射器接收室的外端部，所述引射器接收室、引射器混合室和引射器扩压室依次连接而内腔形成汽液处理腔室；所述引射器喷嘴的出口与所述汽液处理腔室连通。
  7. 根据权利要求6所述的引射制冷循环装置，其特征在于，所述引射器喷嘴包括有引射器的第一进口。
  8. 根据权利要求7所述的引射制冷循环装置，其特征在于，所述引射器接收室包括有引射器的第二进口。
  9. 根据权利要求8所述的引射制冷循环装置，其特征在于，所述引射器扩压室包括有引射器的出口。
  10. 根据权利要求9所述的引射制冷循环装置，其特征在于，所述引射器接收室、引射器混合室均采用管道结构，所述引射器扩压室采用喇叭状管道结构；所述引射器混合室 的内径尺寸小于引射器接收室的最大内径尺寸；所述引射器混合室的内径尺寸小于引射器扩压室的最大内径尺寸。
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