WO2020108012A1 - 一种具有混合工质的空调系统 - Google Patents

一种具有混合工质的空调系统 Download PDF

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Publication number
WO2020108012A1
WO2020108012A1 PCT/CN2019/105600 CN2019105600W WO2020108012A1 WO 2020108012 A1 WO2020108012 A1 WO 2020108012A1 CN 2019105600 W CN2019105600 W CN 2019105600W WO 2020108012 A1 WO2020108012 A1 WO 2020108012A1
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Prior art keywords
heat exchanger
gas
outlet
air
inlet
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/CN2019/105600
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English (en)
French (fr)
Inventor
刘星如
梁祥飞
郑波
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to US17/297,995 priority Critical patent/US20210396432A1/en
Publication of WO2020108012A1 publication Critical patent/WO2020108012A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0446—Condensers with an integrated receiver characterised by the refrigerant tubes connecting the header of the condenser to the receiver; Inlet or outlet connections to receiver
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/16—Receivers
    • 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/09—Improving heat transfers

Definitions

  • the present application belongs to the technical field of air conditioning, and in particular relates to an air conditioning system with mixed working fluids.
  • the intermediate gas supply system is widely used because it can better meet the requirements of low temperature conditions and the performance can be greatly improved.
  • the low-boiling component evaporates first, making the refrigerant that is fed into the compressor It is a refrigerant rich in low boiling point components.
  • the characteristic of this low-boiling component refrigerant is that it is easy to evaporate but difficult to condense.
  • this part of the supplemental refrigerant only participates in condensation and does not participate in evaporation.
  • the condensation process contains more low-boiling components that are not easy to condense, and the high-boiling components that are not easy to evaporate at the same time are more, which further leads to poor performance of the evaporation process and the condensation process.
  • the refrigerant to be supplemented is the one that is rich in high-boiling components, but this type of refrigerant is a part of the gas-liquid separator that is not easy to evaporate and is difficult Let it evaporate.
  • the mixed working gas supplementary gas system in the prior art usually fills more low boiling point working fluid into the compressor, the performance of the condensation process is poor, and the low boiling point working fluid entering the evaporator is less, resulting in the evaporation process performance Poor, resulting in poor performance of the air supplement system and other technical issues, so this application researched and designed an air conditioning system with mixed working fluid.
  • the technical problem to be solved by the present application is to overcome the fact that in the prior art mixed working gas supplementary gas system, more low boiling point working fluid is usually fed into the compressor, so that the high boiling point working fluid entering the condenser in the circulation circuit is more There are fewer defects that result in poorer condensation performance, which in turn provides an air-conditioning system with mixed working fluids.
  • This application provides an air-conditioning system with mixed working fluid, which includes:
  • a compressor a first heat exchanger, and the first heat exchanger communicates with the exhaust port of the compressor, the first heat exchanger has a first inlet end and a first outlet end, and the first A heat exchanger has a flow passage capable of allowing the flow of mixed working fluid, including a first flow passage communicating with the first inlet end and a second flow passage communicating with the first outlet end, and in the first flow A first gas-liquid separator is also connected between the channel and the second flow channel;
  • the first gas-liquid separator includes a first inlet, a first liquid outlet, and a first gas outlet, the first inlet communicates with the first flow channel, and the first gas outlet communicates with the second flow channel
  • the liquid flowing out of the first liquid outlet can be throttled and heated and then communicated to the air supply port of the compressor to perform air supply.
  • a first branch is also connected to the first liquid outlet, and a first throttling device is provided on the first branch, the exhaust port of the compressor and the first inlet end of the first heat exchanger Connected by the first pipeline.
  • a second gas-liquid separator is also included.
  • the second gas-liquid separator includes a second inlet, a second liquid outlet, and a second gas outlet.
  • the second inlet is connected to the first branch so that The fluid that has been throttled by the first throttle device enters the second gas-liquid separator, and the second gas outlet is connected to the air supply port of the compressor.
  • the first outlet end of the first heat exchanger is connected to a second pipeline, and a part of the second pipeline penetrates into the second gas-liquid separator to connect the second gas-liquid separator The fluid in is heated.
  • It also includes a second heat exchanger, along the direction of fluid flow, a second throttling device is provided on the second pipeline at a position downstream of the second gas-liquid separator, and passes through the second throttling
  • the second pipeline behind the device can be connected to the second inlet end of the second heat exchanger.
  • It also includes a second branch, which communicates with the second liquid outlet of the second gas-liquid separator, and a third throttle device is further provided on the second branch, and passes through the first branch
  • the second branch after the three throttling devices can be connected to the second inlet end of the second heat exchanger.
  • the second heat exchanger includes a second heat exchanger A and a second heat exchanger B, and the second heat exchanger A and the second heat exchanger B are arranged side by side.
  • Heater A is located on the upstream side of the second heat exchanger B, and the second branch is connected to the second inlet end A of the second heat exchanger A, and the second pipe is connected to the The second inlet end B of the second heat exchanger B, the second outlet end A of the second heat exchanger A and the second outlet end B of the second heat exchanger B are connected and then connected to the compressor Air inlet.
  • the second heat exchanger includes a second heat exchanger A and a second heat exchanger B, the second pipeline is connected to the second inlet end B of the second heat exchanger B, the second exchange The second outlet end B of the heat exchanger B communicates with the second branch and is then connected to the second inlet end A of the second heat exchanger A.
  • the second outlet end A of the second heat exchanger A is The air inlet of the compressor is connected.
  • a third heat exchanger is also included, the third heat exchanger includes a third inlet and a third outlet, the third inlet is connected to the first branch so that after throttling through the first throttling device Of the fluid enters the third heat exchanger, and the third outlet is connected to the air supply port of the compressor.
  • the outlet end of the first heat exchanger is connected to a second pipeline, and part of the second pipeline penetrates into the third heat exchanger to heat the fluid in the third heat exchanger .
  • the second pipeline is further provided with a second throttle device downstream of the third heat exchanger, and after passing the second throttle device
  • the second pipeline can be connected to the second inlet end of the second heat exchanger and the second outlet end of the second heat exchanger to the air inlet of the compressor.
  • the first flow channel and the second flow channel in the first heat exchanger have a single-row structure
  • first flow channel and the second flow channel in the first heat exchanger are both structures of more than two rows, and the first flow channel and the first gas-liquid separator of more than two rows There is also a liquid collecting tube between them, and a gas dividing tube is also set between the two or more rows of the second flow channels and the first gas-liquid separator.
  • the position where the first flow channel and the liquid collecting tube on the first heat exchanger are connected is set in the range of 0.1 to 0.9 of the length ratio of the entire flow channel composed of the first flow channel and the second flow channel Inside.
  • a first fan is also provided at the position of the first heat exchanger; when a second heat exchanger is also included, a second fan is also provided at the position of the second heat exchanger.
  • a first gas-liquid separator is provided in the middle of the flow channel of the first heat exchanger (condenser) (that is, between the first flow channel and the second flow channel), and the liquid in the first gas-liquid separator is connected.
  • the liquid flowing out of the outlet is led to the air supply port of the compressor after throttling and heating, which can make the liquid outlet of the first gas-liquid separator separate the refrigerant working fluid rich in high-boiling components, thereby effectively overcoming
  • most low-boiling refrigerant working fluids are generated by, for example, flashers or intermediate heat exchangers, and the situation in the compressor is replenished, thereby effectively improving the condensation performance, and also effectively improving
  • the amount of low-boiling refrigerant refrigerant entering the evaporator (second heat exchanger) improves the evaporation performance, solves the problem of poor air supplementation effect of the mixed refrigerant supplemental gas system, and can greatly improve the mixed refrigerant
  • FIG. 1 is a schematic diagram of the system structure of Embodiment 1 of the air-conditioning system with mixed working fluid of the present application;
  • Embodiment 1 is a schematic diagram of the operation principle of Embodiment 1 of the air-conditioning system with mixed working fluids of the present application;
  • Embodiment 3 is a schematic diagram of the system structure of Embodiment 2 of the air-conditioning system with mixed working fluid of the present application;
  • Embodiment 4 is a schematic diagram of the operating principle of Embodiment 2 of the air-conditioning system with mixed working fluids of the present application;
  • Embodiment 3 is a schematic diagram of the system structure of Embodiment 3 of the air-conditioning system with mixed working fluid of the present application;
  • Embodiment 6 is a schematic diagram of the operating principle of Embodiment 3 of the air-conditioning system with mixed working fluids of the present application;
  • FIG. 7 is a schematic diagram of a connecting pipe when the first heat exchanger in the air-conditioning system with mixed working fluid of the present application is a single-row single-channel fin heat exchanger;
  • FIG. 8 is a schematic view of a connecting pipe when the first heat exchanger in the air-conditioning system with mixed working fluid of the present application is a double-row double-channel fin heat exchanger;
  • FIG. 9 is a schematic diagram of a connecting pipe when the first heat exchanger in the air-conditioning system with mixed working fluid of the present application is a three-row three-channel fin heat exchanger.
  • an air conditioning system with mixed working fluid which includes:
  • the first gas-liquid separator 3 includes a first inlet 31, a first liquid outlet 32, and a first gas outlet 33.
  • the first inlet 31 communicates with the first flow path 23, and the first gas outlet 33
  • the second flow passage 24 is in communication, and the liquid flowing out of the first liquid outlet 32 can be throttled and heated to communicate with the air supply port 12 of the compressor 1 to perform air supply.
  • a first gas-liquid separator 3 is connected to the middle of the flow channel of the first heat exchanger 2 (condenser) (that is, between the first flow channel and the second flow channel), and the first gas-liquid separator is connected.
  • the liquid flowing out of the first liquid outlet 32 of the 3 is led to the air supply port of the compressor after being throttled and heated, so that the first liquid outlet 32 of the first gas-liquid separator 3 can separate the high-boiling component Refrigerant working medium, which effectively overcomes the situation in the prior art that most of the low-boiling point refrigerant working medium, such as flashers or intermediate heat exchangers, is fed into the compressor, making the circulation circuit enter
  • the condenser has more high-boiling refrigerant working fluid, which effectively improves the condensation performance, and also effectively increases the amount of low-boiling refrigerant working fluid entering the evaporator (second heat exchanger).
  • the problem that the mixed refrigerant supplemental air system is filled with low-boiling refrigerants, which results in poor supplemental air effect, can greatly improve the performance of the mixed refrigerant supplemental air conditioning system.
  • the first liquid outlet 32 is also connected to a first branch 100, and the first branch 100 is provided with a first throttle device 4, the exhaust port 11 of the compressor 1 and the first exchange
  • the first inlet end 21 of the heater 2 is connected through a first pipeline 200.
  • the refrigerant working fluid separated from the first heat exchanger 2 (condenser) can be The liquid working fluid collected after the gas-liquid separation is throttled and depressurized (high boiling point working fluid) to provide conditions for it to enter the compressor air supply port 12, and the compressor exhaust port 11 is connected to the first exchange through the first pipeline 200
  • the first inlet end 21 of the heat exchanger 2 enables the high-pressure high-temperature gas compressed by the compressor to enter the first heat exchanger 2 for condensation and heat release.
  • a second gas-liquid separator 7 is also included.
  • the second gas-liquid separator 7 includes a second inlet 71, a second liquid outlet 72, and a second gas outlet 73.
  • the second inlet 71 Connected to the first branch 100 so that the fluid throttled by the first throttle device 4 enters the second gas-liquid separator 7, the second gas outlet 73 is connected to the compressor 1
  • the gas supply port 12 is connected.
  • Example 1 and Example 2 of the present application This is a preferred structural form of the embodiments of Example 1 and Example 2 of the present application, that is, by providing the second gas-liquid separator 7, on the one hand, the liquid can be received from the first liquid outlet 32 of the first gas-liquid separator 3 Refrigerant (high boiling point refrigerant), and the liquid is evaporated in the second gas-liquid separator 7, and the evaporated high boiling point refrigerant working medium is introduced into the air supply port 12 of the compressor, and the high boiling point working medium is compensated
  • Refrigerant high boiling point refrigerant
  • the first outlet end 22 of the first heat exchanger 2 is connected to the second pipeline 300, and a partial section 300a of the second pipeline 300 penetrates into the second gas-liquid separator 7 to The fluid in the second gas-liquid separator 7 is heated.
  • This is a further preferred structural form of Example 1 and Example 2 of the present application, that is, by condensing the refrigerant after the first heat exchanger 2 in the second gas-liquid separator 7 against the high in the first branch 100
  • the heating of the boiling point refrigerant can cause the high-boiling point refrigerant to absorb heat and evaporate into a gas, which can be supplied to the air supply port 12 of the compressor to realize the air-enriching effect of the high-boiling point gas refrigerant.
  • a second heat exchanger 8 is also included.
  • a second throttling device 5 is further provided on the second pipeline 300 at a position downstream of the second gas-liquid separator 7 along the fluid flow direction, and passes through the The second pipe 300 after the second throttle device 5 can be connected to the second inlet end 81 of the second heat exchanger 8.
  • the second heat exchanger can evaporate and absorb the refrigerant working fluid in the main circulation circuit of the air conditioning system to achieve cooling and cooling of the outside air.
  • the refrigerant in the second pipeline can be throttled and depressurized by the second throttle device, so as to provide conditions for entering the second heat exchanger for evaporation and heat absorption.
  • It also includes a second branch 400, which communicates with the second liquid outlet 72 of the second gas-liquid separator 7, and a third throttle device is also provided on the second branch 400 6, and the second branch 400 after passing through the third throttle device 6 can be connected to the second inlet end 81 of the second heat exchanger 8.
  • a third throttle device is also provided on the second branch 400 6, and the second branch 400 after passing through the third throttle device 6 can be connected to the second inlet end 81 of the second heat exchanger 8.
  • the liquid refrigerant separated in the second gas-liquid separator 7 can be recovered and recycled through the second branch 400 to further reduce the flow rate.
  • the pressure is reduced to a pressure similar to that of the second heat exchanger 8 (evaporator), and enters the second heat exchanger 8 for evaporation and heat absorption.
  • the second heat exchanger 8 is one, and the second pipeline 300 and the second branch 400 communicate with each other before being connected to the second heat exchanger 8
  • the second inlet end 81 and the second outlet end 82 of the second heat exchanger 8 are connected to the air inlet 13 of the compressor 1.
  • This is the preferred structural form of Example 1 of the present application, that is, only one second heat exchanger 8 is used as an evaporator, so that the refrigerant in the second pipeline 300 and the second branch 400 is first After mixing, it enters the second heat exchanger 8 for heat exchange to achieve the mixing effect of the low-pressure low-temperature refrigerant and the effect of evaporation and heat absorption.
  • FIG. 1 shows an air conditioning system with a mixed working medium intermediate air supplement system, including a compressor 1, a first heat exchanger 2, a second heat exchanger 8, a first throttle device 4, and a second throttle device 5 ,
  • the suitable position of the heat exchanger 2 (the suitable position here is determined by the dryness of the refrigerant, for example, when condensed to a dryness to a suitable range (a certain dryness within 0.15 to 0.85, the optimized dryness is 0.5 to 0.7)
  • the high-pressure two-phase refrigerant flows into the first gas-liquid separator through the liquid collection tube.
  • a liquid collection tube and a gas distribution tube are provided.
  • One end of the liquid collection tube is connected to the first flow path of the first heat exchanger 2.
  • the connected flow channels are all connected to the air inlet pipe of the first heat exchanger 2, the other end of the liquid collecting pipe is connected to the gas-liquid separator 3, and one end of the gas separation pipe is connected to the gas-liquid separator 3.
  • the other end is connected to the second flow channel of the first heat exchanger 2 and the flow channels connected to the gas distribution pipes are all connected to the outlet of the first heat exchanger; provided in the second gas-liquid separator 7 Heating coil;
  • the overall system pipeline connection mode is: the compressor 1 is connected to all the flow channels of the inlet of the first heat exchanger 2, all the flow channels of the inlet of the first heat exchanger 2 are connected to the liquid collection tube, and the other end of the liquid collection tube It is connected to the inlet of the first gas-liquid separator 3, the first outlet of the first gas-liquid separator 3 is connected to the gas distribution pipe, and the other end of the gas separation pipe is connected to all the flow channels of the first heat exchanger 2 Connection, the flow channels connected to the gas distribution pipes are all connected to the outlet pipe of the first heat exchanger 2, the outlet pipe of the first heat exchanger 2 is connected to the inlet of the heating coil of the second gas-liquid separator 7, the second The outlet of the gas-liquid separator 7 is connected to the second throttle device 5; the first liquid outlet 32 of the first gas-liquid separator 3 is connected to the first throttle device 4, and the outlet of the first throttle device 4 is connected to the second gas-liquid The inlet of the separator 7 is connected; the first outlet of the second gas-liquid
  • FIG. 2 is an operation principle diagram of a mixed working medium intermediate air supplement system disclosed in the present application.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 1 enters the first heat exchanger 2 and is condensed. When the condensation is dried to a suitable range (0.15 ⁇ 0.85 within a certain degree of dryness), the high-pressure two-phase refrigerant flows into the first gas-liquid separator 3 through the liquid collecting tube. In the first gas-liquid separator 3, the refrigerant is divided into two channels, and the gaseous refrigerant is divided The gas pipe enters the first heat exchanger 2 to condense into supercooled liquid and flows out from the outlet of the first heat exchanger 2.
  • the liquid refrigerant enters the second gas-liquid separator 7 through the first throttling device 4 and is separated in the second gas-liquid In the condenser 7, the refrigerant flowing out of the outlet of the first throttle device 4 is heated by the refrigerant flowing out of the outlet of the first heat exchanger 2, and the evaporated and vaporized refrigerant passes through the second gas-liquid separator 7 and the second gas outlet 73
  • the unevaporated liquid refrigerant enters the third throttle device 6 through the second liquid outlet 72 of the second gas-liquid separator 7 and becomes a low-temperature two-phase refrigerant; it flows out from the first heat exchanger 2 in the second
  • the gas-liquid separator 7 further subcooled refrigerant enters the second throttle device 5; the low-temperature two-phase refrigerant flowing out of the second throttle device 5 and the third throttle device 6 enters the second heat exchanger 8, at After evaporating, the second heat exchanger 8 is sucked into the compressor.
  • the second heat exchanger 8 includes a second heat exchanger A8A and a second heat exchanger B8B, and the second heat exchanger A8A and the second heat exchanger B8B are side by side
  • the second heat exchanger A8A is arranged along the air flow direction on the upstream side of the second heat exchanger B8B, and the second branch 400 is connected to the second inlet end of the second heat exchanger A8A A8A1, the second pipe 300 is connected to the second inlet end B8B1 of the second heat exchanger B8B, the second outlet end A8A2 of the second heat exchanger A8A and the second of the second heat exchanger B8B After the outlet B8B2 is connected, it is connected to the air inlet 13 of the compressor 1.
  • Example 2 of the present application This is the preferred structural form of Example 2 of the present application, that is, only two second heat exchangers A and B arranged side by side are used as evaporators, so that the second pipeline 300 and the second The refrigerant working fluid in the second branch 400 respectively enters different heat exchangers for heat exchange. After heat exchange, they are mixed and returned to the compressor to achieve the effect of evaporating and absorbing heat of the low-pressure low-temperature refrigerant. Due to the second branch 400 The temperature of the refrigerant in the refrigerant is high, so that the hot air passes through the second heat exchanger A for heat exchange to cool down, and then passes through the second heat exchanger B to cool down to achieve a step-by-step cooling from high temperature to low temperature. Heat exchange efficiency.
  • FIG. 3 is an air-conditioning system with a mixed working fluid dual-temperature supplemental air system disclosed in this application.
  • the system includes a compressor 1, a first heat exchanger 2, a second heat exchanger A8A, and a second heat exchanger B8B.
  • the flow channels are connected, and the connected flow channels are all connected to the first heat exchanger 2, the other end of the liquid collection tube is connected to the gas-liquid separator 3, and one end of the gas separation tube is connected to the gas-liquid separator 3 ,
  • the other end is connected to all the flow channels of the first heat exchanger 2, and the flow channels connected to the gas distribution pipes are connected to the outlet of the first heat exchanger 2; in the second gas-liquid separator 7 Set heating coil;
  • the overall system pipeline connection mode is: the compressor 1 is connected to all the flow channels of the inlet of the first heat exchanger 2, all the flow channels of the inlet of the first heat exchanger 2 are connected to the liquid collection tube, and the other end of the liquid collection tube It is connected to the inlet of the first gas-liquid separator 3, the first outlet of the first gas-liquid separator 3 is connected to the gas distributor, and the other end of the gas distributor is connected to all the flow channels of the heat exchanger, and The flow channels connected to the gas distribution pipes are all connected to the outlet pipeline of the first heat exchanger 2, the first gas outlet 33 of the first heat exchanger 2 is connected to the heating coil inlet of the second gas-liquid separator 7, and the heating coil The outlet is connected to the second throttle device 5, the outlet of the second throttle device 5 is connected to the inlet of the low-temperature flow path of the second heat exchanger B8B, and the outlet of the low-temperature flow path is connected to the compressor suction port 13; The first liquid outlet 32 of the liquid separator 3 is connected to the first
  • FIG. 4 is a schematic diagram of the operation principle of a mixed working medium supplemental gas system disclosed in the present application.
  • the high-temperature and high-pressure refrigerant discharged from the compressor enters the first heat exchanger 2 to be condensed, and when condensed to a dryness to an appropriate range (0.15 to When the dryness is within 0.85, the optimized dryness is within 0.5 ⁇ 0.7), the high-pressure two-phase refrigerant flows into the first gas-liquid separator 3 through the liquid collecting tube.
  • the refrigerant is divided into two Way, the gaseous refrigerant enters the first heat exchanger 2 through the manifold, condenses into a supercooled liquid, flows out from the outlet of the first heat exchanger 2, and the liquid refrigerant enters the second gas-liquid separator 7 through the first throttling device 4
  • the refrigerant flowing out of the outlet of the first throttling device 4 is heated by the refrigerant flowing out of the outlet of the first heat exchanger 2, and the vaporized refrigerant is separated by the second gas-liquid
  • the second gas outlet 73 of the compressor 7 enters the compressor 1.
  • the unevaporated liquid refrigerant enters the third throttling device 6 through the second liquid outlet 72 of the second gas-liquid separator 7 and becomes a low-temperature two-phase refrigerant.
  • the low-temperature flow path of the compressor 8; the refrigerant evaporated in the high-temperature flow path and the low-temperature flow path are connected to the compressor inlet 13;
  • Embodiment 3 further includes a third heat exchanger 9, the third heat exchanger 9 includes a third inlet 91 and a third outlet 92, the third inlet 91 and the first branch
  • the circuit 100 is connected so that the fluid throttled by the first throttle device 4 enters the third heat exchanger 9, and the third outlet 92 is connected to the air supply port 12 of the compressor 1.
  • Example 3 the preferred structural form of Example 3 of the present application.
  • the second gas-liquid separator is replaced with a third heat exchanger, which can be taken from the liquid outlet of the first gas-liquid separator.
  • liquid refrigerant high boiling point refrigerant
  • evaporates the liquid in the third heat exchanger and realizes that the evaporated high boiling point refrigerant working medium is introduced into the air supply port of the compressor to realize the compensation of the high boiling point working medium
  • the effect of gas improve the condensation performance and increase the amount of low-boiling point working fluid entering the evaporator, improve the evaporation performance.
  • the first outlet end 22 of the first heat exchanger 2 is connected to the second pipeline 300, and a partial section 300a of the second pipeline 300 penetrates into the third heat exchanger 9 to The fluid in the three heat exchangers 9 is heated.
  • This is a further preferred structural form of Embodiment 3 of the present application, that is, by condensing the refrigerant in the first heat exchanger in the third heat exchanger to heat the high-boiling-point refrigerant working fluid in the first branch, The high-boiling-point working fluid absorbs heat and evaporates into a gas, which is supplied to the supplementary gas port of the compressor, and the high-boiling-point working fluid is supplemented with gas.
  • a second heat exchanger 8 is also included.
  • the second pipeline 300 is further provided with a second throttle device 5 downstream of the third heat exchanger 9 and passes through the second
  • the second pipe 300 behind the throttling device 5 can be connected to the second inlet end 81 of the second heat exchanger 8 and the second outlet end 82 of the second heat exchanger 8 to the compression The inlet 13 of the machine 1.
  • the second heat exchanger can evaporate and absorb the refrigerant working fluid in the main circulation circuit of the air-conditioning system to achieve the cooling and cooling of the outside air.
  • the second throttling device can throttle and reduce the refrigerant working medium in the second pipeline to provide conditions for entering the second heat exchanger for evaporation and heat absorption.
  • the system includes a compressor 1, a first heat exchanger 2, a second heat exchanger 8, a third heat exchanger 9, and a first section Flow device 4, second throttling device 5, first gas-liquid separator 3;
  • the first gas-liquid separator 3 is arranged near the first heat exchanger 2 and is arranged at a suitable position of the first heat exchanger 2
  • a liquid collecting pipe and a gas distribution pipe one end of the liquid collecting pipe is connected to the first flow channel of the first heat exchanger 2, and the connected flow channels are connected to the first inlet end 21 of the first heat exchanger 2
  • the other end of the liquid collection tube is connected to the gas-liquid separator 3
  • one end of the gas separation tube is connected to the gas-liquid separator 3, and the other end is connected to the second flow path of the first heat exchanger 2
  • the flow channels connected to the gas distribution pipes are all connected to the outlet of the first heat exchanger 2;
  • the overall system pipeline connection mode is: the compressor 1 is connected to all the flow channels of the inlet of the first heat exchanger 2, all the flow channels of the inlet of the first heat exchanger 2 are connected to the liquid collection tube, and the other end of the liquid collection tube It is connected to the inlet of the first gas-liquid separator 3, the first gas outlet 33 of the first gas-liquid separator 3 is connected to the gas distribution pipe, and the other end of the gas distribution pipe is connected to all of the first heat exchanger 2
  • the flow channels are connected, and the flow channels connected to the gas distribution pipes are all connected to the outlet pipeline of the first heat exchanger 2.
  • the first outlet end 22 of the first heat exchanger 2 passes through the third heat exchanger 9 and then passes through the second throttle
  • the device 5 is connected to the second inlet end 81 of the second heat exchanger 8, the second outlet end 82 of the second heat exchanger 8 is connected to the compressor inlet 13; the first liquid outlet 32 of the first gas-liquid separator 3 It is connected to the inlet of the first throttle device 4, the outlet of the first throttle device 4 is connected to the third inlet 91 of the third heat exchanger 9, and the third outlet 92 of the third heat exchanger 9 is connected to the air inlet 12 of the compressor 1 connection;
  • FIG. 6 is a schematic diagram of the operation principle of a mixed working medium intermediate gas supplementary system disclosed in this application.
  • the high-temperature and high-pressure refrigerant discharged from the compressor enters the first heat exchanger to be condensed, and when condensed to a dryness to an appropriate range (optimized dryness) Within 0.15 ⁇ 0.4), the high-pressure two-phase refrigerant flows into the first gas-liquid separator 3 through the liquid collection tube.
  • the refrigerant is divided into two paths, and the gaseous refrigerant enters through the gas distribution pipe
  • the first heat exchanger 2 condenses into supercooled liquid, it flows out from the outlet of the first heat exchanger 2 into the third heat exchanger 9, and the liquid refrigerant enters the third heat exchanger 9 through the first throttling device 4.
  • the refrigerant flowing out of the throttling device 4 absorbs heat and evaporates in the third heat exchanger 9 and enters the compressor through the compressor air inlet 12.
  • the refrigerant flowing out of the outlet of the first heat exchanger 2 is in the third heat exchanger 9 After further subcooling, it enters the second throttle device 5.
  • the refrigerant flowing out of the second throttle device 5 evaporates through the second heat exchanger 8 and is sucked into the compressor.
  • the first flow path 23 and the second flow path 24 in the first heat exchanger 2 have a single-row structure
  • first flow path 23 and the second flow path 24 in the first heat exchanger 2 are both structures of more than two rows, and the first flow path 23 and the first Between the gas-liquid separator 3, there are also liquid collecting tubes (not shown, through the liquid collecting tube, multiple rows of first flow channels can be collected or collected, and then communicated to the first gas-liquid separator), two rows There is also a gas distribution pipe between the second flow channel 24 and the first gas-liquid separator 3 (not shown, the gas separation function can be performed on the first gas-liquid separator through the gas distribution pipe, and then The multi-pipe gas path that comes out is connected to multiple rows of second flow channels).
  • first and second flow channels and the first gas-liquid separator of this application that is, in a single-row structure, it is directly connected to the first gas-liquid separator.
  • Collect liquid in multiple rows so that the refrigerant working fluid is collected and then passed into the first gas-liquid separator for gas-liquid separation, and then the separated gas is divided into multiple gas flow channels through the gas distribution pipe and passed into the second stream
  • the high boiling point working fluid is separated, and the low boiling point working fluid is returned to the first heat exchanger for heat exchange, so as to realize the beneficial effect of supplementing the high boiling point working fluid to the compressor.
  • a first fan is also provided at the position of the first heat exchanger 2; when a second heat exchanger 8 is also included, a second fan is also provided at the position of the second heat exchanger 8.
  • This is a preferred structural form of the first heat exchanger and the second heat exchanger component structure of the present application, which can improve the heat exchange effect and heat exchange capacity of the first heat exchanger and the second heat exchanger.
  • the liquid collecting tube in this application refers to: a connecting tube that connects all the flow channels of the first heat exchanger to the gas-liquid separator;
  • Low temperature flow channel and high temperature flow channel refer to: from the air flow direction, the flow channel that first passes through the heat exchanger is a high temperature flow channel, and then the flow channel that flows through the heat exchanger is a low temperature flow channel.
  • the present application preferably provides an air conditioning system with a mixed working medium intermediate air supplement system, including a compressor, a first heat exchanger, a second heat exchanger, a first throttle device, a second throttle device, and a third throttle Device, first gas-liquid separator and second gas-liquid separator; characterized in that: the first gas-liquid separator is arranged near the first heat exchanger, and a polymer Liquid pipe and gas distribution pipe, one end of the liquid collecting pipe is connected to all flow channels of the first heat exchanger, the connected flow channels are connected to the air inlet pipe of the first heat exchanger, and the other of the liquid collecting pipe One end is connected to the gas-liquid separator, one end of the gas distribution pipe is connected to the gas-liquid separator, and the other end is connected to all flow channels of the first heat exchanger, and the flow channels connected to the gas distribution tube are all connected to the An outlet connection of the first heat exchanger; a heating coil is provided in the second gas-liquid separator;
  • the overall system pipeline connection mode is: the compressor is connected to all flow channels of the inlet of the first heat exchanger, all the flow channels of the inlet of the first heat exchanger are connected to the liquid collecting tube, and the other end of the liquid collecting tube is connected to the The inlet of the first gas-liquid separator is connected, the first outlet of the first gas-liquid separator is connected to the gas distributor, the other end of the gas distributor is connected to all the flow channels of the heat exchanger, and the flow connected to the gas distributor
  • the channels are all connected to the outlet pipe of the first heat exchanger, the outlet pipe of the first heat exchanger is connected to the inlet of the heating coil of the second gas-liquid separator 7, and the outlet of the second gas-liquid separator is connected to the second throttle Device 5 is connected; the second outlet of the first gas-liquid separator is connected to the first throttle device 4, the outlet of the first throttle device 4 is connected to the inlet of the second gas-liquid separator; the first outlet of the second gas-liquid separator Connected to the compressor air inlet, the
  • the position where the flow channel on the first heat exchanger is connected to the liquid collection tube may be set within a range of 0.1 to 0.9 of the entire flow channel length ratio; the flow channel on the first heat exchanger is connected to the liquid collection tube
  • the position can be set according to the dryness of the refrigerant in the tube; preferably, when the dryness of the refrigerant in the tube is in the range of 0.15 to 0.85, the position corresponding to the dryness can make the refrigerant tube and the collector tube connected;
  • the system can be constructed as a mixed-temperature dual-temperature gas supplement system
  • the system includes a compressor, a first heat exchanger, a second heat exchanger, a first throttle device, a second throttle device, a third throttle device, a first gas-liquid separator and a second gas-liquid separator; It is characterized in that: the first gas-liquid separator is arranged near the first heat exchanger, and a liquid collecting pipe and a gas distribution pipe are arranged at a suitable position of the first heat exchanger.
  • All flow channels of the first heat exchanger are connected, and the connected flow channels are connected to the air inlet pipe of the first heat exchanger, the other end of the liquid collecting pipe is connected to the gas-liquid separator, and one end of the gas separation pipe Connected to the gas-liquid separator, the other end is connected to all the flow channels of the first heat exchanger, and the flow channel connected to the gas distribution pipe is connected to the outlet of the first heat exchanger;
  • the heating coil is set in the separator;
  • the overall system pipeline connection mode is: the compressor is connected to all flow channels of the inlet of the first heat exchanger, all the flow channels of the inlet of the first heat exchanger are connected to the liquid collecting tube, and the other end of the liquid collecting tube is connected to the The inlet of the first gas-liquid separator is connected, the first outlet of the first gas-liquid separator is connected to the gas distributor, the other end of the gas distributor is connected to all the flow channels of the heat exchanger, and the flow connected to the gas distributor
  • the channels are all connected to the outlet pipe of the first heat exchanger, the outlet pipe of the first heat exchanger is connected to the inlet of the heating coil of the second gas-liquid separator 7, and the outlet of the second gas-liquid separator is connected to the second throttle
  • the device 5 is connected, the outlet of the second throttling device 5 is connected to the inlet of the low-temperature flow path of the second heat exchanger 8, the outlet of the compressor of the low-temperature flow path is connected; the second outlet of the first gas-liquid separator is connected
  • the position where the flow channel on the first heat exchanger is connected to the liquid collecting tube may be set in the range of 0.1 to 0.9 of the ratio of the entire flow channel length, and the preferred ratio is 0.6 to 0.8;
  • the position where the flow channel on the first heat exchanger is connected to the liquid collecting tube can be set according to the dryness of the refrigerant in the tube; preferably, when the dryness of the refrigerant in the tube is in the range of 0.15 to 0.85, The position corresponding to the degree of dryness can connect the refrigerant tube to the liquid collection tube; a further preferred range is 0.3 to 0.5, and the position corresponding to the degree of dryness can connect the refrigerant tube to the liquid collection tube;
  • the second heat exchanger may be set as one heat exchanger or two heat exchangers
  • the second heat exchanger is set as a heat exchanger, and the air flow direction and the heat exchanger flow channel can be set so that the air first flows through the high temperature flow channel and then through the low temperature flow channel.
  • the inlet of the high temperature flow channel and the second throttle The outlet of the device 5 is connected, and the inlet of the low-temperature flow channel is connected to the outlet of the first throttle device;
  • the second heat exchanger is provided as two heat exchangers, and the air first flows through the high-temperature evaporator and then through the low-temperature evaporator.
  • the inlet of the high-temperature evaporator is connected to the outlet of the second throttling device.
  • the system can be constructed as a supplemental gas system with an intermediate heat exchanger
  • the system includes a compressor, a first heat exchanger, a second heat exchanger, a third heat exchanger, a first throttle device, a second throttle device, and a first gas-liquid separator;
  • a gas-liquid separator is arranged near the first heat exchanger, and a liquid collecting pipe and a gas distribution pipe are arranged at suitable positions of the first heat exchanger, and one end of the liquid collecting pipe flows with the first heat exchanger Connection, the connected flow channels are all connected to the air inlet pipe of the first heat exchanger, the other end of the liquid collection pipe is connected to the gas-liquid separator, and one end of the gas separation pipe is connected to the gas-liquid separator, The other end is connected to all flow channels of the first heat exchanger, and the flow channel connected to the gas distribution pipe is connected to the outlet of the first heat exchanger;
  • the overall system pipeline connection mode is: the compressor is connected to all flow channels of the inlet of the first heat exchanger, all the flow channels of the inlet of the first heat exchanger are connected to the liquid collecting tube, and the other end of the liquid collecting tube is connected to the The inlet of the first gas-liquid separator is connected, the first outlet of the first gas-liquid separator is connected to the gas distributor, the other end of the gas distributor is connected to all the flow channels of the heat exchanger, and the flow connected to the gas distributor
  • the channels are all connected to the outlet pipe of the first heat exchanger, the outlet pipe of the first heat exchanger is connected to the first inlet of the third heat exchanger, and the first outlet of the third heat exchanger is connected to the second throttling device 5Inlet connection, the second throttle device 5 outlet is connected to the second heat exchanger inlet, the second heat exchanger outlet is connected to the compressor suction port; the second outlet of the first gas-liquid separator is connected to the first throttle
  • the inlet of the device 4 is connected, the outlet of the first
  • the position where the flow channel on the first heat exchanger is connected to the liquid collecting tube can be set in the range of 0.1 to 0.9 of the ratio of the entire flow channel length, and the preferred ratio is 0.2 to 0.5;
  • the position where the flow channel on the first heat exchanger is connected to the liquid collecting tube can be set according to the dryness of the refrigerant in the tube; preferably, when the dryness of the refrigerant in the tube is in the range of 0.15 to 0.85, The position corresponding to the dryness degree can connect the refrigerant tube to the liquid collection tube; a further preferred range is 0.2 to 0.35, and the position corresponding to the dryness degree can connect the refrigerant tube to the liquid collection tube;
  • the throttle device may be configured as an electronic expansion valve or a capillary tube
  • the first heat exchanger can be set as a sleeve heat exchanger
  • the second heat exchanger can be set as a sleeve-type heat exchanger; cold water can pass through the high-temperature evaporator and then the low-temperature evaporator, or the two channels of cold water respectively pass through the high-temperature evaporator and the low-temperature evaporator to produce water at two temperatures;
  • the compressor may be a two-stage compressor or a quasi-two-stage compressor.

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Abstract

本申请提供一种具有混合工质的空调系统，其包括：压缩机；第一换热器，且第一换热器与压缩机的排气口连通，第一换热器具有与第一进口端连通的第一流道和与第一出口端连通的第二流道，且在第一流道和第二流道之间还连接设置有第一气液分离器；第一气液分离器包括第一进口、第一液体出口和第一气体出口，第一进口与第一流道连通、第一气体出口与第二流道连通，第一液体出口流出的液体能够被节流和加热后连接到压缩机的补气口而进行补气。通过本申请使得进入第一换热器中具有较多的高沸点制冷剂工质，提高了冷凝性能，还提高了进入第二换热器中的低沸点制冷剂工质的量，提高了蒸发性能，解决混合工质补气系统补气效果不佳的问题，改善空调系统的性能。

Description

一种具有混合工质的空调系统
本申请要求于2018年11月27日提交中国专利局、申请号为201811425179.X、发明名称为“一种具有混合工质的空调系统”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
本申请属于空调技术领域，具体涉及一种具有混合工质的空调系统。
背景技术
目前中间补气系统因能较好的满足低温工况要求且性能能有较大幅度的提升而得到广泛应用。然而，对于由两种或两种以上不同沸点的制冷剂组成的混合工质而言，在气液分离器中的相平衡状态下，低沸点组分先蒸发，使得补进压缩机的制冷剂为富含低沸点组分的制冷剂。这种低沸点组分制冷剂的特点就是容易蒸发但难冷凝，然而这部分补气制冷剂却只参与冷凝而不参与蒸发。这样带来两个影响：冷凝过程含有的不容易冷凝的低沸点组分较多，同时蒸发过程不容易蒸发的高沸点组分偏多，进一步便导致蒸发过程和冷凝过程的性能均较差。实际上，对于混合工质补气系统而言，补进去的制冷剂为富含高沸点组分的制冷剂最佳，但该类制冷剂在气液分离器中属于不容易蒸发的部分，难以让其蒸发。
由于现有技术中的混合工质补气系统中通常补入较多的低沸点工质进入压缩机，导致冷凝过程性能较差，进入蒸发器中的低沸点工质较少、导致蒸发过程性能较差，从而使得补气系统性能不佳等技术问题，因此本申请研究设计出一种具有混合工质的空调系统。
发明内容
本申请要解决的技术问题在于克服现有技术中的混合工质补气系统中通常补入较多的低沸点工质进入压缩机、而使得循环回路中进入冷凝器中的高沸 点工质较少、导致冷凝性能较差的缺陷，进而提供一种具有混合工质的空调系统。
本申请提供一种具有混合工质的空调系统，其包括：
压缩机；第一换热器，且所述第一换热器与所述压缩机的排气口连通，所述第一换热器具有第一进口端和第一出口端，且所述第一换热器内部具有能够容许混合工质流动的流道、包括与所述第一进口端连通的第一流道和与所述第一出口端连通的第二流道，且在所述第一流道和所述第二流道之间还连接设置有第一气液分离器；
所述第一气液分离器包括第一进口、第一液体出口和第一气体出口，所述第一进口与所述第一流道连通、所述第一气体出口与所述第二流道连通，所述第一液体出口流出的液体能够被节流和加热后连通到压缩机的补气口而进行补气。
优选地，
所述第一液体出口还连接有第一支路，且所述第一支路上设置有第一节流装置，所述压缩机的排气口和所述第一换热器的第一进口端之间通过第一管路连接。
优选地，
还包括第二气液分离器，所述第二气液分离器包括第二进口、第二液体出口和第二气体出口，所述第二进口与所述第一支路连接、使得经过所述第一节流装置节流后的流体进入所述第二气液分离器，所述第二气体出口与所述压缩机的补气口连接。
优选地，
所述第一换热器的第一出口端连接第二管路，且所述第二管路的部分段贯通至所述第二气液分离器中、以对所述第二气液分离器中的流体加热。
优选地，
还包括第二换热器，沿着流体流动方向、所述第二管路上位于所述第二气液分离器的下游段位置还设置有第二节流装置，且经过所述第二节流装置后的所述第二管路能够连接到所述第二换热器的第二进口端。
优选地，
还包括第二支路，所述第二支路与所述第二气液分离器的第二液体出口连 通，且所述第二支路上还设置有第三节流装置，且经过所述第三节流装置后的所述第二支路能够连接到所述第二换热器的所述第二进口端。
优选地，
所述第二换热器为一个，所述第二管路和所述第二支路连通后再连接到所述第二换热器的所述第一进口端、所述第二换热器的第二出口端连接到所述压缩机的进气口。
优选地，
所述第二换热器包括第二换热器A和第二换热器B，且所述第二换热器A和第二换热器B并排设置、沿空气流动方向所述第二换热器A位于所述第二换热器B的上游侧，且所述第二支路连接到所述第二换热器A的第二进口端A、所述第二管路连接到所述第二换热器B的第二进口端B，所述第二换热器A的第二出口端A和第二换热器B的第二出口端B连接后再连接到所述压缩机的进气口。
优选地，
所述第二换热器包括第二换热器A和第二换热器B，所述第二管路连接到所述第二换热器B的第二进口端B，所述第二换热器B的第二出口端B与所述第二支路连通再与所述第二换热器A的第二进口端A连接，所述第二换热器A的第二出口端A与所述压缩机的进气口连接。
优选地，
还包括第三换热器，所述第三换热器包括第三进口和第三出口，所述第三进口与所述第一支路连接、使得经过所述第一节流装置节流后的流体进入所述第三换热器，所述第三出口与所述压缩机的补气口连接。
优选地，
所述第一换热器的出口端连接第二管路，且所述第二管路的部分段贯通至所述第三换热器中、以对所述第三换热器中的流体加热。
优选地，
还包括第二换热器，沿着流体流动方向、所述第二管路在所述第三换热器的下游段还设置有第二节流装置，且经过所述第二节流装置后的所述第二管路能够连接到所述第二换热器的第二进口端、所述第二换热器的第二出口端连接到所述压缩机的进气口。
优选地，
所述第一换热器中的所述第一流道和所述第二流道为单排结构；
或者，所述第一换热器中的所述第一流道和所述第二流道均为两排以上的结构，且两排以上的所述第一流道与所述第一气液分离器之间还设置有聚液管，两排以上的所述第二流道与所述第一气液分离器之间还设置有分气管。
所述第一换热器上的所述第一流道与所述聚液管连接的位置设置在所述第一流道和所述第二流道组成的整个流道的长度比例的0.1～0.9范围内。
优选地，
所述第一换热器的位置还设置有第一风机；当还包括第二换热器时，所述第二换热器的位置还设置有第二风机。
本申请提供的一种具有混合工质的空调系统具有如下有益效果：
本申请通过在第一换热器(冷凝器)的流道中部(即第一流道和第二流道之间)连接设置有第一气液分离器，并将第一气液分离器的液体出口流出的液体通过节流和加热后导至压缩机的补气口，能够使得第一气液分离器的液体出口分离出的是富含高沸点组分的制冷剂工质，从而有效地克服了现有技术中通过例如闪发器或中间换热器而产生绝大多数的低沸点的制冷剂工质、而补回压缩机中的情况，进而有效地提高了冷凝性能，同时还有效地提高了进入蒸发器(第二换热器)中的低沸点制冷剂工质的量，提高了蒸发性能，解决混合工质补气系统补气效果不佳的问题，能较大幅度改善混合工质补气空调系统的性能。
附图说明
图1是本申请的具有混合工质的空调系统的实施例1的系统结构示意图；
图2是本申请的具有混合工质的空调系统的实施例1的运行原理示意图；
图3是本申请的具有混合工质的空调系统的实施例2的系统结构示意图；
图4是本申请的具有混合工质的空调系统的实施例2的运行原理示意图；
图5是本申请的具有混合工质的空调系统的实施例3的系统结构示意图；
图6是本申请的具有混合工质的空调系统的实施例3的运行原理示意图；
图7是本申请的具有混合工质的空调系统中的第一换热器为单排单流道翅片换热器时的连管示意图；
图8是本申请的具有混合工质的空调系统中的第一换热器为双排双流道翅 片换热器时的连管示意图；
图9是本申请的具有混合工质的空调系统中的第一换热器为三排三流道翅片换热器时的连管示意图。
图中附图标记表示为：
1、压缩机；11、排气口；12、补气口；13、进气口；2、第一换热器；21、第一进口端；22、第一出口端；23、第一流道；24、第二流道；3、第一气液分离器；31、第一进口；32、第一液体出口；33、第一气体出口；4、第一节流装置；5、第二节流装置；6、第三节流装置；7、第二气液分离器；71、第二进口；72、第二液体出口；73、第二气体出口；8、第二换热器；81、第二进口端；82、第二出口端；8A、第二换热器A；8A1、第二进口端A；8A2、第二出口端A；8B、第二换热器B；8B1、第二进口端B；8B2、第二出口端B；9、第三换热器；91、第三进口；92、第三出口；100、第一支路；200、第一管路；300、第二管路；300a、部分段；400、第二支路。
具体实施方式
如图1-9所示，本申请提供一种具有混合工质的空调系统，其包括：
压缩机1；第一换热器2，且所述第一换热器2与所述压缩机1的排气口11连通，所述第一换热器2具有第一进口端21和第一出口端22，且所述第一换热器2内部具有能够容许混合工质流动的流道、包括与所述第一进口端21连通的第一流道23和与所述第一出口端22连通的第二流道24，且在所述第一流道23和所述第二流道24之间还连接设置有第一气液分离器3；
所述第一气液分离器3包括第一进口31、第一液体出口32和第一气体出口33，所述第一进口31与所述第一流道23连通、所述第一气体出口33与所述第二流道24连通，所述第一液体出口32流出的液体能够被节流和加热后连通到压缩机1的补气口12而进行补气。
本申请通过在第一换热器2(冷凝器)的流道中部(即第一流道和第二流道之间)连接设置有第一气液分离器3，并将第一气液分离器3的第一液体出口32流出的液体通过节流和加热后导至压缩机的补气口，能够使得第一气液分离器3的第一液体出口32分离出的是富含高沸点组分的制冷剂工质，从而有效地克服了现有技术中通过例如闪发器或中间换热器而产生绝大多数的低 沸点的制冷剂工质补进压缩机中的情况，使得循环回路中进入冷凝器中具有较多的高沸点制冷剂工质，从而有效地提高了冷凝性能，同时还有效地提高了进入蒸发器(第二换热器)中的低沸点制冷剂工质的量，提高了蒸发性能，解决混合工质补气系统补进去的全部为低沸点制冷剂进而导致补气效果不佳的问题，能较大幅度改善混合工质补气空调系统的性能。
优选地，
所述第一液体出口32还连接有第一支路100，且所述第一支路100上设置有第一节流装置4，所述压缩机1的排气口11和所述第一换热器2的第一进口端21之间通过第一管路200连接。通过在第一液体出口32连接第一支路100，并且在第一支路100上设置第一节流装置4，能够对第一换热器2(冷凝器)分离出来的制冷剂工质在经过气液分离后收集的液体工质进行节流降压(高沸点工质)，为其进入压缩机补气口12提供条件，压缩机排气口11通过第一管路200连接到第一换热器2的第一进口端21能够使得压缩机压缩后的高压高温气体进入第一换热器2中、以进行冷凝放热。
优选地，
参见附图1-4，还包括第二气液分离器7，所述第二气液分离器7包括第二进口71、第二液体出口72和第二气体出口73，所述第二进口71与所述第一支路100连接、使得经过所述第一节流装置4节流后的流体进入所述第二气液分离器7，所述第二气体出口73与所述压缩机1的补气口12连接。这是本申请的实施例1和实施例2的实施方式的优选结构形式，即通过设置第二气液分离器7，能够一方面从第一气液分离器3的第一液体出口32承接液体冷媒(高沸点冷媒)，并在第二气液分离器7中进行液体的蒸发，并实现将蒸发后的高沸点冷媒工质导入到压缩机的补气口12中，实现高沸点工质的补气作用，提高冷凝性能以及提高低沸点工质进入蒸发器中的量、提高蒸发性能。
优选地，
所述第一换热器2的第一出口端22连接第二管路300，且所述第二管路300的部分段300a贯通至所述第二气液分离器7中、以对所述第二气液分离器7中的流体加热。这是本申请的实施例1和实施例2的进一步优选的结构形式，即通过将第一换热器2冷凝后的冷媒在第二气液分离器7中对第一支路100中的高沸点冷媒工质进行加热，能够使得高沸点工质吸收热量而蒸发成为气体， 以供给至压缩机的补气口12中，实现高沸点气体工质的补气作用。
优选地，
还包括第二换热器8，沿着流体流动方向、所述第二管路300上位于所述第二气液分离器7的下游段位置还设置有第二节流装置5，且经过所述第二节流装置5后的所述第二管路300能够连接到所述第二换热器8的第二进口端81。这是本申请的实施例1和2的进一步优选的结构形式，通过第二换热器能够对空调系统主循环回路中的冷媒工质进行蒸发吸热的作用，实现对外界空气的制冷降温，并且通过第二节流装置能够将第二管路中的冷媒工质进行节流降压、以为进入第二换热器中进行蒸发吸热提供条件。
优选地，
还包括第二支路400，所述第二支路400与所述第二气液分离器7的第二液体出口72连通，且所述第二支路400上还设置有第三节流装置6，且经过所述第三节流装置6后的所述第二支路400能够连接到所述第二换热器8的所述第二进口端81。这是本申请的实施例1和2的进一步优选的结构形式，通过第二支路400能够对第二气液分离器7中分离出的液体冷媒进行回收利用的作用，将其进一步节流降压，使其降到与第二换热器8(蒸发器)压力大小差不多的压力，并进入第二换热器8中进行蒸发吸热作用。
优选地，
实施例1，参见图1-2，所述第二换热器8为一个，所述第二管路300和所述第二支路400连通后再连接到所述第二换热器8的所述第二进口端81、所述第二换热器8的第二出口端82连接到所述压缩机1的进气口13。这是本申请的实施例1的优选结构形式，即只通过一个第二换热器8、将其作为蒸发器用途，使第二管路300和第二支路400中的冷媒工质进行先混合后再进入到第二换热器8中进行换热作用，实现低压低温冷媒的混合作用，实现蒸发吸热的作用。
图1示出一种具有混合工质中间补气系统的空调系统，包括压缩机1、第一换热器2、第二换热器8、第一节流装置4、第二节流装置5、第三节流装置6、第一气液分离器3和第二气液分离器7；其中，所述第一气液分离器3设置在第一换热器2附近，在所述第一换热器2的合适位置(这里的合适位置通过下述的冷媒的干度进行确定，比如当冷凝到干度到合适范围(0.15～0.85内某一 干度，优化干度为0.5～0.7)内时，高压两相制冷剂经聚液管流入第一气液分离器3)设置了聚液管和分气管，所述聚液管的一端与所述第一换热器2第一流道连接，所连接的流道均与第一换热器2的进气管连接，所述聚液管的另一端与所述气液分离器3连接，所述分气管的一端与气液分离器3连接，另一端与所述第一换热器2的第二流道连接，与分气管连接的流道均与所述第一换热器的出口连接；在所述第二气液分离器7中设置加热盘管；
整体系统管路连接方式为：所述压缩机1与第一换热器2的入口所有流道连接，第一换热器2入口的所有流道与聚液管连接，聚液管的另一端与所述第一气液分离器3的入口连接，第一气液分离器3的第一出口与所述分气管连接，所述分气管的另一端与第一换热器2的所有流道连接，与分气管连接的流道均与第一换热器2的出口管路连接，第一换热器2的出口管路与第二气液分离器7的加热盘管入口连接，第二气液分离器7的出口与第二节流装置5连接；第一气液分离器3的第一液体出口32与第一节流装置4连接，第一节流装置4出口与第二气液分离器7入口连接；第二气液分离器7的第一出口与压缩机补气口12连接，第二气液分离器7的第二液体出口72与第三节流装置6连接，第二节流装置5出口与第三节流装置6出口均与第二换热器8的第二进口端81连接，第二换热器8的第二出口端82与压缩机进气口13连接；
图2为本申请公开的一种混合工质中间补气系统的运行原理图，压缩机1排出的高温高压制冷剂进入第一换热器2被冷凝，当冷凝到干度到合适范围(0.15～0.85内某一干度)内时，高压两相制冷剂经聚液管流入第一气液分离器3，在第一气液分离器3中，制冷剂分为两路，气态制冷剂经分气管进入到第一换热器2冷凝为过冷液体从第一换热器2出口流出，液态制冷剂经第一节流装置4进入到第二气液分离器7，在第二气液分离器7中，从第一节流装置4出口流出的制冷剂被从第一换热器2出口流出的制冷剂加热，蒸发气化的制冷剂经第二气液分离器7第二气体出口73进入压缩机1，未蒸发的液态制冷剂经第二气液分离器7第二液体出口72进入第三节流装置6变为低温两相制冷剂；从第一换热器2流出在第二气液分离器7进一步过冷的制冷剂进入第二节流装置5；从第二节流装置5和第三节流装置6流出的低温两相制冷剂均进入第二换热器8，在第二换热器8内蒸发后被压缩机吸入。
优选地，
实施例2，参见图3-4，所述第二换热器8包括第二换热器A8A和第二换热器B8B，且所述第二换热器A8A和第二换热器B8B并排设置、沿空气流动方向所述第二换热器A8A位于所述第二换热器B8B的上游侧，且所述第二支路400连接到所述第二换热器A8A的第二进口端A8A1、所述第二管路300连接到所述第二换热器B8B的第二进口端B8B1，所述第二换热器A8A的第二出口端A8A2和第二换热器B8B的第二出口端B8B2连接后再连接到所述压缩机1的进气口13。这是本申请的实施例2的优选结构形式，即只通过两个并排设置的第二换热器A和第二换热器B、将其作为蒸发器用途，使第二管路300和第二支路400中的冷媒工质分别进入不同换热器中分别进行换热，换热后再进行混合并回到压缩机，实现低压低温冷媒的蒸发吸热的作用，由于第二支路400中的冷媒工质温度较高，因此使得热空气先经过第二换热器A进行换热进行降温、再进一步经过第二换热器B进行降温，实现从高温到低温的逐级降温，提高换热效率。
图3为本申请公开的一种具有混合工质双温补气系统的空调系统，该系统包括压缩机1、第一换热器2、第二换热器A8A、第二换热器B8B、第一节流装置4、第二节流装置5、第三节流装置6、第一气液分离器3和第二气液分离器7；其特征在于：所述第一气液分离器3设置在第一换热器2附近，在所述第一换热器2合适位置(同上)设置了聚液管和分气管，所述聚液管的一端与所述第一换热器2所有流道连接，所连接的流道均与第一换热器2连接，所述聚液管的另一端与所述气液分离器3连接，所述分气管的一端与气液分离器3连接，另一端与所述第一换热器2的所有流道连接，与分气管连接的流道均与所述第一换热器2的出口连接；在所述第二气液分离器7中设置加热盘管；
整体系统管路连接方式为：所述压缩机1与第一换热器2的入口所有流道连接，第一换热器2入口的所有流道与聚液管连接，聚液管的另一端与所述第一气液分离器3的入口连接，第一气液分离器3的第一出口与所述分气管连接，所述分气管的另一端与换热器的所有流道连接，与分气管连接的流道均与第一换热器2的出口管路连接，第一换热器2的第一气体出口33与第二气液分离器7的加热盘管入口连接，加热盘管出口与第二节流装置5连接，第二节流装置5的出口与第二换热器B8B的低温流道的入口连接，低温流道的出口与压缩机吸气口13连接；第一气液分离器3的第一液体出口32与第一节流装置4 连接，第一节流装置4出口与第二气液分离器7第二进口71连接；第二气液分离器7的第二气体出口73与压缩机补气口12连接，第二气液分离器7的第二液体出口72与第三节流装置6连接，第三节流装置6的出口与第二换热器A8A的高温流道入口连接，第二换热器A8A的高温流道出口与压缩机吸气口13连接；
图4为本申请公开的一种混合工质中间补气系统的运行原理图，压缩机排出的高温高压制冷剂进入第一换热器2被冷凝，当冷凝到干度到合适范围(0.15～0.85内某一干度，优化干度为0.5～0.7)内时，高压两相制冷剂经聚液管流入第一气液分离器3，在第一气液分离器3中，制冷剂分为两路，气态制冷剂经分气管进入到第一换热器2冷凝为过冷液体从第一换热器2出口流出，液态制冷剂经第一节流装置4进入到第二气液分离器7，在第二气液分离器7中，从第一节流装置4出口流出的制冷剂被从第一换热器2出口流出的制冷剂加热，蒸发气化的制冷剂经第二气液分离器7第二气体出口73进入压缩机1，未蒸发的液态制冷剂经第二气液分离器7第二液体出口72进入第三节流装置6变为低温两相制冷剂后进入第二换热器8的高温流道；从第一换热器2流出在第二气液分离器7进一步过冷的制冷剂经第二节流装置5变为低温两相制冷剂后进入第二换热器8的低温流道；在高温流道和低温流道蒸发后的制冷剂均与压缩机进气口13连接；
优选地，
实施例3，参见图5-6，还包括第三换热器9，所述第三换热器9包括第三进口91和第三出口92，所述第三进口91与所述第一支路100连接、使得经过所述第一节流装置4节流后的流体进入所述第三换热器9，所述第三出口92与所述压缩机1的补气口12连接。这是本申请的实施例3的优选结构形式，在实施例1和2的基础上将第二气液分离器替换为第三换热器，能够一方面从第一气液分离器的液体出口端承接液体冷媒(高沸点冷媒)，并在第三换热器中进行液体的蒸发，并实现将蒸发后的高沸点冷媒工质导入到压缩机的补气口中，实现高沸点工质的补气作用，提高冷凝性能以及提高低沸点工质进入蒸发器中的量、提高蒸发性能。
优选地，
所述第一换热器2的第一出口端22连接第二管路300，且所述第二管路 300的部分段300a贯通至所述第三换热器9中、以对所述第三换热器9中的流体加热。这是本申请的实施例3的进一步优选的结构形式，即通过将第一换热器冷凝后的冷媒在第三换热器中对第一支路中的高沸点冷媒工质进行加热，能够使得高沸点工质吸收热量而蒸发成为气体，以供给至压缩机的补气口中，实现高沸点气体工质的补气作用。
优选地，
还包括第二换热器8，沿着流体流动方向、所述第二管路300在所述第三换热器9的下游段还设置有第二节流装置5，且经过所述第二节流装置5后的所述第二管路300能够连接到所述第二换热器8的第二进口端81、所述第二换热器8的第二出口端82连接到所述压缩机1的进气口13。这是本申请的实施例3的进一步优选的结构形式，通过第二换热器能够对空调系统主循环回路中的冷媒工质进行蒸发吸热的作用，实现对外界空气的制冷降温，并且通过第二节流装置能够将第二管路中的冷媒工质进行节流降压、以为进入第二换热器中进行蒸发吸热提供条件。
图5为本申请公开的一种带中间换热器的补气系统，该系统包括压缩机1、第一换热器2、第二换热器8、第三换热器9、第一节流装置4、第二节流装置5、第一气液分离器3；所述第一气液分离器3设置在第一换热器2附近，在所述第一换热器2合适位置设置了聚液管和分气管，所述聚液管的一端与所述第一换热器2第一流道连接，所连接的流道均与第一换热器2的第一进口端21连接，所述聚液管的另一端与所述气液分离器3连接，所述分气管的一端与气液分离器3连接，另一端与所述第一换热器2的第二流道连接，与分气管连接的流道均与所述第一换热器2的出口连接；
整体系统管路连接方式为：所述压缩机1与第一换热器2的入口所有流道连接，第一换热器2入口的所有流道与聚液管连接，聚液管的另一端与所述第一气液分离器3的入口连接，第一气液分离器3的第一气体出口33与所述分气管连接，所述分气管的另一端与第一换热器2的所有流道连接，与分气管连接的流道均与第一换热器2的出口管路连接，第一换热器2的第一出口端22经第三换热器9后经第二节流装置5连到第二换热器8的第二进口端81，第二换热器8第二出口端82与压缩机进气口13连接；第一气液分离器3的第一液体出口32与第一节流装置4入口连接，第一节流装置4的出口与第三换热器9 的第三进口91连接，第三换热器9的第三出口92与压缩机1补气口12连接；
图6为本申请公开的一种混合工质中间补气系统的运行原理图，压缩机排出的高温高压制冷剂进入第一换热器被冷凝，当冷凝到干度到合适范围(优化干度为0.15～0.4)内时，高压两相制冷剂经聚液管流入第一气液分离器3，在第一气液分离器3中，制冷剂分为两路，气态制冷剂经分气管进入到第一换热器2冷凝为过冷液体从第一换热器2出口流出进入第三换热器9，液态制冷剂经第一节流装置4进入到第三换热器9，从第一节流装置4流出的制冷剂在第三换热器9中吸热蒸发后经压缩机补气口12进入压缩机，从第一换热器2出口流出的制冷剂在第三换热器9中进一步过冷后进入第二节流装置5，从第二节流装置5流出的制冷剂经第二换热器8蒸发后被压缩机吸入。
优选地，
所述第一换热器2中的所述第一流道23和所述第二流道24为单排结构；
或者，所述第一换热器2中的所述第一流道23和所述第二流道24均为两排以上的结构，且两排以上的所述第一流道23与所述第一气液分离器3之间还设置有聚液管(未示出，通过聚液管能够对多排第一流道进行聚液或称集液、再连通至第一气液分离器)，两排以上的所述第二流道24与所述第一气液分离器3之间还设置有分气管(未示出，通过分气管能够对第一气液分离器进行分气作用、再将分出来的多管气路连通至多排第二流道)。这是本申请的第一流道和第二流道以及与第一气液分离器之间的优选连接方式，即单排结构时将其直接与第一气液分离器相连，多排时先将多排进行聚液，使得冷媒工质汇集再通入第一气液分离器中、进行气液分离后，再将分离出的气体通过分气管分成多股气流通道，并通入到第二流道中，以将高沸点工质分离出，将低沸点工质通回到第一换热器中进行换热，实现将高沸点工质补气至压缩机中的有益效果。
优选地，
所述第一换热器2的位置还设置有第一风机；当还包括第二换热器8时，所述第二换热器8的位置还设置有第二风机。这是本申请的第一换热器和第二换热器部件结构的优选结构形式，能够提高第一换热器以及第二换热器的换热效果和换热能力。
本申请中的聚液管是指：连接第一换热器所有流道进入气液分离器的连接 管；分气管是指：连接气液分离器的气体出口与第一换热器各个流道的连接管；低温流道与高温流道是指：从空气流向看，先经过换热器的流道为高温流道，后流经换热器的流道为低温流道。
本申请优选提供一种具有混合工质中间补气系统的空调系统，包括压缩机、第一换热器、第二换热器、第一节流装置、第二节流装置、第三节流装置、第一气液分离器和第二气液分离器；其特征在于：所述第一气液分离器设置在第一换热器附近，在所述第一换热器合适位置设置了聚液管和分气管，所述聚液管的一端与所述第一换热器所有流道连接，所连接的流道均与第一换热器的进气管连接，所述聚液管的另一端与所述气液分离器连接，所述分气管的一端与气液分离器连接，另一端与所述第一换热器的所有流道连接，与分气管连接的流道均与所述第一换热器的出口连接；在所述第二气液分离器中设置加热盘管；
整体系统管路连接方式为：所述压缩机与第一换热器的入口所有流道连接，第一换热器入口的所有流道与聚液管连接，聚液管的另一端与所述第一气液分离器的入口连接，第一气液分离器的第一出口与所述分气管连接，所述分气管的另一端与换热器的所有流道连接，与分气管连接的流道均与第一换热器的出口管路连接，第一换热器的出口管路与第二气液分离器7的加热盘管入口连接，第二气液分离器出口与第二节流装置5连接；第一气液分离器的第二出口与第一节流装置4连接，第一节流装置4出口与第二气液分离器入口连接；第二气液分离器的第一出口与压缩机补气口连接，第二气液分离器的第二出口与第三节流装置6连接，第二节流装置出口与第三节流装置出口均与第二换热器8的入口连接，第二换热器的出口与压缩机吸气口连接；
所述第一换热器上的流道与聚液管连接的位置可设置在整个流道长度比例的0.1～0.9范围内；所述第一换热器上的流道与聚液管连接的位置可根据制冷剂在管内的干度设定；优选地，当制冷剂在管内的干度为0.15～0.85的范围内时，该干度所对应的位置可使得冷媒管与聚液管连接；
系统可构建为混合工质双温补气系统；
该系统包括压缩机、第一换热器、第二换热器、第一节流装置、第二节流装置、第三节流装置、第一气液分离器和第二气液分离器；其特征在于：所述第一气液分离器设置在第一换热器附近，在所述第一换热器合适位置设置了聚 液管和分气管，所述聚液管的一端与所述第一换热器所有流道连接，所连接的流道均与第一换热器的进气管连接，所述聚液管的另一端与所述气液分离器连接，所述分气管的一端与气液分离器连接，另一端与所述第一换热器的所有流道连接，与分气管连接的流道均与所述第一换热器的出口连接；在所述第二气液分离器中设置加热盘管；
整体系统管路连接方式为：所述压缩机与第一换热器的入口所有流道连接，第一换热器入口的所有流道与聚液管连接，聚液管的另一端与所述第一气液分离器的入口连接，第一气液分离器的第一出口与所述分气管连接，所述分气管的另一端与换热器的所有流道连接，与分气管连接的流道均与第一换热器的出口管路连接，第一换热器的出口管路与第二气液分离器7的加热盘管入口连接，第二气液分离器出口与第二节流装置5连接，第二节流装置5的出口与第二换热器8的低温流道的入口连接，低温流道的出口压缩机吸气口连接；第一气液分离器的第二出口与第一节流装置4连接，第一节流装置4出口与第二气液分离器入口连接；第二气液分离器的第一出口与压缩机补气口连接，第二气液分离器的第二出口与第三节流装置6连接，第三节流装置出口与第二换热器8的高温流道入口连接，第二换热器的高温流道出口与压缩机吸气口连接；
所述第一换热器上的流道与聚液管连接的位置可设置在整个流道长度比例的0.1～0.9范围内，优选的比例为0.6～0.8；
所述第一换热器上的流道与聚液管连接的位置可根据制冷剂在管内的干度设定；优选地，当制冷剂在管内的干度为0.15～0.85的范围内时，该干度所对应的位置可使得冷媒管与聚液管连接；进一步优选的范围为0.3～0.5，该干度所对应的位置可使得冷媒管与聚液管连接；
第二换热器可设置为一个换热器，也可设置为两个换热器；
第二换热器设置为一个换热器，空气流向与换热器流道可设置为空气先流经高温流道，再流经低温流道，此时高温流道的进口与第二节流装置5的出口连接，低温流道的进口与第一节流装置的出口连接；
第二换热器设置为两个换热器，空气先流经高温蒸发器再流经低温蒸发器，所述高温蒸发器入口与第二节流装置的出口连接，所述低温蒸发器入口与第一节流装置的出口连接；
系统可构建为带中间换热器的补气系统；
该系统包括压缩机、第一换热器、第二换热器、第三换热器、第一节流装置、第二节流装置、第一气液分离器；其特征在于：所述第一气液分离器设置在第一换热器附近，在所述第一换热器合适位置设置了聚液管和分气管，所述聚液管的一端与所述第一换热器所有流道连接，所连接的流道均与第一换热器的进气管连接，所述聚液管的另一端与所述气液分离器连接，所述分气管的一端与气液分离器连接，另一端与所述第一换热器的所有流道连接，与分气管连接的流道均与所述第一换热器的出口连接；
整体系统管路连接方式为：所述压缩机与第一换热器的入口所有流道连接，第一换热器入口的所有流道与聚液管连接，聚液管的另一端与所述第一气液分离器的入口连接，第一气液分离器的第一出口与所述分气管连接，所述分气管的另一端与换热器的所有流道连接，与分气管连接的流道均与第一换热器的出口管路连接，第一换热器的出口管路与第三换热器的第一入口连接，第三换热器的第一出口与第二节流装置5入口连接，第二节流装置5出口与第二换热器的入口连接，第二换热器出口与压缩机吸气口连接；第一气液分离器的第二出口与第一节流装置4入口连接，第一节流装置4的出口与第三换热器的第二入口连接，第三换热器的第二出口与压缩机补气口连接；
所述第一换热器上的流道与聚液管连接的位置可设置在整个流道长度比例的0.1～0.9范围内，优选的比例为0.2～0.5；
所述第一换热器上的流道与聚液管连接的位置可根据制冷剂在管内的干度设定；优选地，当制冷剂在管内的干度为0.15～0.85的范围内时，该干度所对应的位置可使得冷媒管与聚液管连接；进一步优选的范围为0.2～0.35，该干度所对应的位置可使得冷媒管与聚液管连接；
所述节流装置可设置为电子膨胀阀或毛细管；
第一换热器可设置为套管式换热器；
第二换热器可设置为套管式换热器；冷水可先经过高温蒸发器再经过低温蒸发器，或两路冷水分别经过高温蒸发器和低温蒸发器，制出两种温度的水；
压缩机可为双级压缩机或准双级压缩机。
以上所述仅为本申请的较佳实施例而已，并不用以限制本申请，凡在本申请的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本申请的保护范围之内。以上所述仅是本申请的优选实施方式，应当指出，对于本技 术领域的普通技术人员来说，在不脱离本申请技术原理的前提下，还可以做出若干改进和变型，这些改进和变型也应视为本申请的保护范围。

Claims (15)

  1. 一种具有混合工质的空调系统，其特征在于：包括：
    压缩机(1)；第一换热器(2)，且所述第一换热器(2)与所述压缩机(1)的排气口(11)连通，所述第一换热器(2)具有第一进口端(21)和第一出口端(22)，且所述第一换热器(2)内部具有能够容许混合工质流动的流道、包括与所述第一进口端(21)连通的第一流道(23)和与所述第一出口端(22)连通的第二流道(24)，且在所述第一流道(23)和所述第二流道(24)之间设置有第一气液分离器(3)；
    所述第一气液分离器(3)包括第一进口(31)、第一液体出口(32)和第一气体出口(33)，所述第一进口(31)与所述第一流道(23)连通、所述第一气体出口(33)与所述第二流道(24)连通，所述第一液体出口(32)流出的液体能够被节流和加热后连通到压缩机(1)的补气口(12)而进行补气。
  2. 根据权利要求1所述的空调系统，其特征在于：
    所述第一液体出口(32)还连接有第一支路(100)，且所述第一支路(100)上设置有第一节流装置(4)，所述压缩机(1)的排气口(11)和所述第一换热器(2)的第一进口端(21)之间通过第一管路(200)连接。
  3. 根据权利要求2所述的空调系统，其特征在于：
    还包括第二气液分离器(7)，所述第二气液分离器(7)包括第二进口(71)、第二液体出口(72)和第二气体出口(73)，所述第二进口(71)与所述第一支路(100)连接、使得经过所述第一节流装置(4)节流后的流体进入所述第二气液分离器(7)，所述第二气体出口(73)与所述压缩机(1)的补气口(12)连接。
  4. 根据权利要求3所述的空调系统，其特征在于：
    所述第一换热器(2)的第一出口端(22)连接第二管路(300)，且所述第二管路(300)的部分段(300a)贯通至所述第二气液分离器(7)中、以对所述第二气液分离器(7)中的流体加热。
  5. 根据权利要求4所述的空调系统，其特征在于：
    还包括第二换热器(8)，沿着流体流动方向、所述第二管路(300)上位 于所述第二气液分离器(7)的下游段位置还设置有第二节流装置(5)，且经过所述第二节流装置(5)后的所述第二管路(300)能够连接到所述第二换热器(8)的第二进口端(81)。
  6. 根据权利要求5所述的空调系统，其特征在于：
    还包括第二支路(400)，所述第二支路(400)与所述第二气液分离器(7)的第二液体出口(72)连通，且所述第二支路(400)上还设置有第三节流装置(6)，且经过所述第三节流装置(6)后与所述第二支路(400)连通后再与所述第二换热器(8)的第二进口(81)连接。
  7. 根据权利要求6所述的空调系统，其特征在于：
    所述第二换热器(8)为一个，所述第二管路(300)和所述第二支路(400)连通后再连接到所述第二换热器(8)的所述第二进口端(81)、所述第二换热器(8)的第二出口端(82)连接到所述压缩机(1)的进气口(13)。
  8. 根据权利要求6所述的空调系统，其特征在于：
    所述第二换热器(8)包括第二换热器A(8A)和第二换热器B(8B)，且所述第二换热器A(8A)和第二换热器B(8B)并排设置、沿空气流动方向所述第二换热器A(8A)位于所述第二换热器B(8B)的上游侧，且所述第二支路(400)连接到所述第二换热器A(8A)的第二进口端A(8A1)、所述第二管路(300)连接到所述第二换热器B(8B)的第二进口端B(8B1)，所述第二换热器A(8A)的第二出口端A(8A2)和第二换热器B(8B)的第二出口端B(8B2)连接后再连接到所述压缩机(1)的进气口(13)。
  9. 根据权利要求6所述的空调系统，其特征在于：
    所述第二换热器(8)包括第二换热器A(8A)和第二换热器B(8B)，所述第二管路(300)连接到所述第二换热器B(8B)的第二进口端B(8B1)，所述第二换热器B(8B)的第二出口端B(8B2)与所述第二支路(400)连通后再与所述第二换热器A(8A)的第二进口端A(8A1)连接，所述第二换热器A(8A)的第二出口端A(8A2)与所述压缩机(1)的进气口(13)连接。
  10. 根据权利要求2所述的空调系统，其特征在于：
    还包括第三换热器(9)，所述第三换热器(9)包括第三进口(91)、第三出口(92)，所述第三进口(91)与所述第一支路(100)连接、使得经过所述第一节流装置(4)节流后的流体进入所述第三换热器(9)，所述第三出 口(92)与所述压缩机(1)的补气口(12)连接。
  11. 根据权利要求10所述的空调系统，其特征在于：
    所述第一换热器(2)的第一出口端(22)连接第二管路(300)，且所述第二管路(300)的部分段(300a)贯通至所述第三换热器(9)中、以对所述第三换热器(9)中的流体加热。
  12. 根据权利要求11所述的空调系统，其特征在于：
    还包括第二换热器(8)，沿着流体流动方向、所述第二管路(300)在所述第三换热器(9)的下游段还设置有第二节流装置(5)，且经过所述第二节流装置(5)后的所述第二管路(300)能够连接到所述第二换热器(8)的第二进口端(81)、所述第二换热器(8)的第二出口端(82)连接到所述压缩机(1)的进气口(13)。
  13. 根据权利要求1-12中任一项所述的空调系统，其特征在于：
    所述第一换热器(2)中的所述第一流道(23)和所述第二流道(24)为单排结构；
    或者，所述第一换热器(2)中的所述第一流道(23)和所述第二流道(24)均为两排以上的结构，且两排以上的所述第一流道(23)与所述第一气液分离器(3)之间还设置有聚液管，两排以上的所述第二流道(24)与所述第一气液分离器(3)之间还设置有分气管。
  14. 根据权利要求13所述的空调系统，其特征在于：
    所述第一换热器(2)上的所述第一流道(23)与所述聚液管连接的位置设置在所述第一流道(23)和所述第二流道(24)组成的整个流道的长度比例的0.1～0.9范围内。
  15. 根据权利要求1-14中任一项所述的空调系统，其特征在于：
    所述第一换热器(2)的位置还设置有第一风机；当还包括第二换热器(8)时，所述第二换热器(8)的位置还设置有第二风机。
PCT/CN2019/105600 2018-11-27 2019-09-12 一种具有混合工质的空调系统 Ceased WO2020108012A1 (zh)

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CN109974345A (zh) * 2019-03-04 2019-07-05 中国科学院理化技术研究所 补气式压缩机及压缩循环系统
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