WO2024098868A1 - 空调系统及控制方法 - Google Patents

空调系统及控制方法 Download PDF

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Publication number
WO2024098868A1
WO2024098868A1 PCT/CN2023/112858 CN2023112858W WO2024098868A1 WO 2024098868 A1 WO2024098868 A1 WO 2024098868A1 CN 2023112858 W CN2023112858 W CN 2023112858W WO 2024098868 A1 WO2024098868 A1 WO 2024098868A1
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WO
WIPO (PCT)
Prior art keywords
pipeline
compressor
valve
conditioning system
heat exchanger
Prior art date
Application number
PCT/CN2023/112858
Other languages
English (en)
French (fr)
Inventor
冯涛
武连发
熊建国
焦华超
Original Assignee
珠海格力电器股份有限公司
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Publication of WO2024098868A1 publication Critical patent/WO2024098868A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/88—Electrical aspects, e.g. circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • 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
    • F25B41/40—Fluid line 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems

Definitions

  • the present disclosure relates to the technical field of air conditioning, and in particular to an air conditioning system and a control method.
  • heat recovery multi-split units Compared with heat pump multi-split units, heat recovery multi-split units have more functional modes.
  • heat recovery multi-split units use non-enthalpy-increasing compressors, which have problems such as average energy efficiency, average energy saving, high exhaust temperature, and few control methods.
  • an air conditioning system comprising:
  • At least two indoor heat exchangers At least two indoor heat exchangers
  • an enthalpy-increasing pipeline a first end of which is connected to a pipeline between the outdoor heat exchanger and at least one indoor heat exchanger, and a second end of which is connected to an enthalpy-increasing port of the compressor;
  • the regulating valve is arranged on the enthalpy increasing pipeline, and the regulating valve is configured to adjust the on-off and flow rate of the enthalpy increasing pipeline.
  • the air conditioning system also includes a third flow circuit and a fourth flow circuit in parallel, wherein the third flow circuit fluid connects at least one indoor heat exchanger and the inlet of the compressor, and the fourth flow circuit fluid connects at least one indoor heat exchanger, the outdoor heat exchanger and the inlet of the compressor, and the third flow circuit and the fourth flow circuit are configured to work selectively or simultaneously.
  • the air conditioning system further comprises a conversion unit, wherein at least one indoor heat exchanger is an indoor Condenser, wherein when at least one indoor heat exchanger is an indoor evaporator, the refrigerant of the indoor evaporator flows to the indoor condenser through the conversion unit, or the refrigerant of the indoor condenser flows to the indoor evaporator through the conversion unit.
  • the air conditioning system also includes a liquid storage member, a pressurizing valve and a first pipeline, wherein the liquid storage member is arranged on the pipeline between the outdoor heat exchanger and at least one indoor heat exchanger, the first end of the first pipeline is connected to the outlet of the compressor, the second end of the first pipeline is connected to the liquid storage member, and the pressurizing valve is arranged on the first pipeline.
  • the air conditioning system further includes a subcooler, wherein the subcooler is disposed on a pipeline between the outdoor heat exchanger and at least one indoor heat exchanger, and the first end of the enthalpy increase pipeline is connected to the subcooler.
  • the air conditioning system also includes a liquid storage component, a pressurizing valve and a first pipeline, wherein the liquid storage component is arranged on the pipeline between the outdoor heat exchanger and the subcooler, the first end of the first pipeline is connected to the outlet of the compressor, the second end of the first pipeline is connected to the liquid storage component, and the pressurizing valve is arranged on the first pipeline.
  • the air-conditioning system further includes a second pipeline, a third pipeline, a fourth pipeline and a fifth pipeline
  • the subcooler includes a first branch and a second branch, the first end of the first branch is connected to the liquid storage component through the second pipeline, and the second end of the first branch is connected to at least one indoor heat exchanger through the third pipeline; the first end of the second branch is connected to the liquid storage component through the fourth pipeline, and the second end of the second branch is connected to the inlet of the compressor through the fifth pipeline.
  • the air conditioning system further includes a first expansion valve, which is disposed in the fourth pipeline.
  • the air conditioning system further includes a first valve, which is disposed on the fifth pipeline, and the first valve is configured to control the opening and closing of the pipeline between the fifth pipeline and the inlet of the compressor.
  • the first end of the enthalpy increase line is connected to the fifth line, and the first valve is close to the inlet of the compressor relative to the connection between the first end of the enthalpy increase line and the fifth line.
  • the air conditioning system further includes a first control valve, which includes a first state and a second state.
  • a first control valve which includes a first state and a second state.
  • the first control valve When the first control valve is in the first state, the first flow path is connected.
  • the first control valve When the first control valve is in the second state, the first flow path is disconnected.
  • the first control valve includes a first interface, a second interface, a third interface and a fourth interface
  • the first interface is connected to the outlet of the compressor
  • the second interface is connected to the outdoor heat exchanger
  • the third interface and the fourth interface are both connected to the inlet of the compressor
  • the first control valve is in the In the first state, the first interface is communicated with the second interface, and the third interface is communicated with the fourth interface
  • the first control valve is in the second state, the first interface is communicated with the third interface, and the second interface is communicated with the fourth interface.
  • the air conditioning system also includes a second control valve, which includes a third state and a fourth state.
  • a second control valve which includes a third state and a fourth state.
  • the second control valve When the second control valve is in the third state, the second flow path is connected.
  • the second control valve When the second control valve is in the fourth state, the second flow path is disconnected.
  • the second control valve includes a fifth interface, a sixth interface, a seventh interface and an eighth interface
  • the fifth interface is connected to the outlet of the compressor
  • the sixth interface is connected to at least one indoor heat exchanger
  • the seventh interface and the eighth interface are both inlets of the compressor
  • the second control valve is in the third state
  • the fifth interface is connected to the sixth interface
  • the seventh interface is connected to the eighth interface
  • the second control valve is in the fourth state
  • the fifth interface is connected to the seventh interface
  • the sixth interface is connected to the eighth interface.
  • the outdoor heat exchanger comprises a water-cooled plate heat exchanger.
  • the air conditioning system also includes a conversion unit, after the first flow path fluid connects the outlet of the compressor and the outdoor heat exchanger, it is connected to at least one indoor heat exchanger through the conversion unit fluid; after the second flow path fluid connects the outlet of the compressor, it is connected to at least one indoor heat exchanger through the conversion unit fluid.
  • a control method for the air conditioning system in the above embodiment comprising:
  • the following actions are performed:
  • the compressor runs at the frequency required for the set target temperature.
  • the frequency of the compressor is increased; otherwise, the frequency of the compressor is reduced.
  • the air conditioning system further comprises a subcooler, a liquid storage member, a second pipeline, a third pipeline, a fourth pipeline and a fifth pipeline, a first expansion valve and a first valve;
  • the liquid storage member is arranged on the pipeline between the outdoor heat exchanger and the subcooler;
  • the subcooler comprises a first branch and a second branch, the first end of the first branch is connected to the liquid storage member through the second pipeline, and the second end of the first branch is connected to at least one indoor heat exchanger through the third pipeline;
  • the first end of the second branch is connected to the liquid storage member through the fourth pipeline, and the second end of the second branch is connected to the inlet of the compressor through the fifth pipeline;
  • the first expansion valve is arranged on the fourth pipeline;
  • the first valve is arranged on the fifth pipeline, and the first valve is configured to control the pipeline opening and closing between the fifth pipeline and the inlet of the compressor;
  • the first end of the enthalpy increase pipeline is connected to the fifth pipeline, and the first valve is close
  • the air conditioning system After the air conditioning system enters the enthalpy increase mode, it also performs the following actions:
  • the opening of the first expansion valve is increased, otherwise, the opening of the first expansion valve is decreased;
  • the air conditioning system exits the enthalpy increase mode when at least one of the following conditions is met:
  • the saturation temperature corresponding to the pressure at the inlet of the compressor is ⁇ the fourth preset temperature T4; in the heating mode, the saturation temperature corresponding to the pressure at the outlet of the compressor is ⁇ the fifth preset temperature T5; wherein T5>T4;
  • the difference between the actual exhaust temperature at the outlet of the compressor and the saturation temperature corresponding to the pressure at the outlet of the compressor is less than the sixth preset temperature T6.
  • the compressor maintains the current frequency operation
  • the opening of the first expansion valve is increased; otherwise, the opening of the first expansion valve is decreased;
  • the air conditioning system further comprises a liquid storage member, a pressurizing valve and a first pipeline, wherein the liquid storage member is disposed on the pipeline between the outdoor heat exchanger and at least one indoor heat exchanger, a first end of the first pipeline is connected to the outlet of the compressor, and a second end is connected to the liquid storage member, and the pressurizing valve is disposed on the first pipeline;
  • the air-conditioning system After the air-conditioning system starts to run for the first preset time, if the ratio of the target value of the required cooling capacity or heating capacity to the rated value of the cooling capacity or heating capacity of the air-conditioning system is ⁇ the first preset value A, and after continuing to run for the third preset time, the saturation temperature corresponding to the pressure at the outlet of the compressor is ⁇ the seventh preset temperature value T7, and the actual exhaust temperature at the outlet of the compressor is ⁇ the eighth preset temperature value T8, then the pressurizing valve is opened, where T8>T7.
  • the pressurizing valve is closed when at least one of the following conditions is met:
  • the pressurizing valve is opened and continues to operate for a second preset time, and the saturation temperature corresponding to the pressure at the outlet of the compressor is ⁇ the ninth preset temperature T9;
  • the pressurizing valve is opened and continues to operate for a second preset time, and the difference between the actual exhaust temperature at the outlet of the compressor and the saturation temperature corresponding to the pressure at the outlet of the compressor is less than the tenth preset temperature T10; wherein T9>T10.
  • the air-conditioning system includes a full cooling mode, a full heating mode, a main cooling mode, a main heating mode, etc.
  • the regulating valve can be selectively opened to connect the enthalpy increase pipeline to achieve enthalpy increase of the compressor, thereby improving the energy efficiency and performance of the compressor.
  • FIG1 is a schematic diagram of an air conditioning system according to some embodiments of the present disclosure.
  • FIG2 is a schematic diagram of a full cooling enthalpy increase mode of an air-conditioning system according to some embodiments of the present disclosure
  • FIG3 is a schematic diagram of a complete heating enthalpy increase mode of an air-conditioning system according to some embodiments of the present disclosure
  • FIG. 4 is a schematic diagram of a heat recovery enthalpy increase mode of an air-conditioning system according to some embodiments of the present disclosure.
  • Some embodiments of the present disclosure provide an air conditioning system and a control method for alleviating the problem of low energy efficiency.
  • FIG1 is a schematic diagram of the structure of some embodiments of the air conditioning system according to the present disclosure.
  • the air conditioning system includes a compressor 1, at least two indoor heat exchangers 3, an outdoor heat exchanger 2, a first flow path and a second flow path connected in parallel, an enthalpy increase pipeline 101 and a regulating valve 22.
  • the first flow path fluid connects the outlet of the compressor 1, the outdoor heat exchanger 2 and at least one indoor heat exchanger 3.
  • the second flow path fluid connects the outlet of the compressor 1 and at least one indoor heat exchanger 3.
  • the first flow path and the second flow path are configured to work selectively or simultaneously.
  • a first end of the enthalpy increase pipeline 101 is connected to a pipeline between the outdoor heat exchanger 2 and at least one indoor heat exchanger 3 , and a second end of the enthalpy increase pipeline 101 is connected to an enthalpy increase port of the compressor 1 .
  • the regulating valve 22 is disposed on the enthalpy increasing pipeline 101 , and the regulating valve 22 is configured to adjust the on-off and flow rate of the enthalpy increasing pipeline 101 .
  • the compressor 1 comprises a jet enthalpy increase compressor.
  • the enthalpy increase port of the compressor 1 is arranged in the medium pressure chamber of the compressor 1 .
  • the regulating valve 22 includes an electronic expansion valve.
  • the use of a high-precision electronic expansion valve can achieve smooth regulation of stepless enthalpy injection, and can accurately control the amount of enthalpy injection according to the unit state, thereby improving comfort and reliability and making the transition of energy efficiency more stable.
  • the air conditioning system includes an outdoor heat exchanger 2 and at least two indoor heat exchangers 3, and the at least two indoor heat exchangers 3 are connected in parallel.
  • the air conditioning system is a multi-split system.
  • the first flow path and the second flow path are fluid communication paths.
  • the outlet of the compressor 1, the outdoor heat exchanger 2 and the at least one indoor heat exchanger 3 are sequentially fluidly connected as the first flow path.
  • at least one indoor heat exchanger 3, the outdoor heat exchanger 2 and the inlet of the compressor 1 are sequentially fluidly connected. Therefore, in fact, some pipelines of the air-conditioning system, the outdoor heat exchanger 2, the at least one indoor heat exchanger 3, etc. may be located in the first flow path, or may be located in other flow paths.
  • At least one indoor heat exchanger 3 may be located in the first flow path, or the second flow path, or may also be located in other flow paths. Therefore, the first flow path and the second flow path are not necessarily fixed pipes. Therefore, there are no numbers in the first flow path and the second flow path diagram.
  • the first flow path fluid is connected to the outlet of the compressor 1, the outdoor heat exchanger 2 and at least one indoor heat exchanger 3, and the at least one indoor heat exchanger 3 is an indoor evaporator, which can cool the indoor room.
  • the second flow path fluid is connected to the outlet of the compressor 1 and at least one indoor heat exchanger 3, and the at least one indoor heat exchanger 3 is an indoor condenser, which can heat the indoor room.
  • the first flow path can work alone, and all indoor heat exchangers 3 are indoor evaporators, which is a complete cooling mode.
  • the second flow path can work alone, and all indoor heat exchangers 3 are indoor condensers, which is a complete heating mode.
  • the first flow path and the second flow path can work simultaneously, and when the number of indoor evaporators is greater than the indoor condenser, it is a main cooling mode. When the number of indoor condensers is greater than the indoor evaporator, it is a main heating mode. Therefore, the air conditioning system provided by the embodiment of the present disclosure includes a complete cooling mode, a complete heating mode, a main cooling mode, a main heating mode, etc. In these modes, the regulating valve 22 can be selectively opened to connect the enthalpy increase pipeline 101 to achieve the enthalpy increase of the compressor, thereby improving the energy efficiency and performance of the compressor.
  • the at least two indoor heat exchangers 3 include two, three, four or more indoor heat exchangers.
  • the air conditioning system also includes a third flow path and a fourth flow path in parallel, the third flow path fluid connects at least one indoor heat exchanger 3 and the inlet of the compressor 1, the fourth flow path fluid connects at least one indoor heat exchanger 3, the outdoor heat exchanger 2 and the inlet of the compressor 1, and the third flow path and the fourth flow path are configured to work selectively or simultaneously.
  • the third flow path can be connected to the first flow path to form a circulation loop, and the fourth flow path can be connected to the second flow path to form a circulation loop.
  • the third flow path and the fourth flow path also represent fluid communication paths, which are not necessarily fixed pipelines. Therefore, No reference numerals are shown in the figures.
  • the air-conditioning system also includes a conversion unit 102.
  • the refrigerant of the indoor evaporator can flow to the indoor condenser through the conversion unit 102, or the refrigerant of the indoor condenser can flow to the indoor evaporator through the conversion unit 102.
  • the refrigerant of the indoor evaporator flows to the indoor condenser through the conversion unit 102, which can recover the heat in the room that needs to be cooled and send it to the room that needs to be heated.
  • the outdoor heat exchanger 2 may not be used, thus reducing energy consumption.
  • the refrigerant of the indoor condenser flows to the indoor evaporator through the conversion unit 102, and the cold energy in the room that needs heating can be recovered and sent to the room that needs cooling.
  • the outdoor heat exchanger 2 can be omitted to reduce energy consumption.
  • the air conditioning system further includes a liquid storage component 6 , which is disposed on a connecting pipeline between the outdoor heat exchanger 2 and at least one indoor heat exchanger 3 .
  • the air conditioning system further includes a first pipeline 11 , a first end of the first pipeline 11 is connected to an outlet of the compressor 1 , and a second end of the first pipeline 11 is connected to the liquid storage member 6 .
  • the air conditioning system further includes a pressurizing valve 7 , which is disposed on the first pipeline 11 .
  • the first end of the first pipeline 11 in the embodiment of the present disclosure is connected to the outlet of the compressor 1, and the second end of the first pipeline 11 is connected to the liquid storage part 6.
  • the pressurizing valve 7 is opened, the first pipeline 11 is connected, and the first pipeline 11 directly draws out the high-pressure gaseous refrigerant from the outlet of the compressor 1, and directly pressurizes and injects it into the liquid storage part 6, which is equivalent to shielding the pressure loss of the outdoor heat exchanger 2, providing greater flow power for the liquid refrigerant in the liquid storage part 6, increasing the refrigerant flow to the indoor heat exchanger 3, and improving the refrigerant driving capacity, thereby increasing the low temperature starting speed, improving the ability of low temperature refrigeration or minimum refrigeration, or low load heating, and thus improving the operation capacity of the system.
  • the air conditioning system further includes a subcooler 5 , which is disposed on a connecting pipeline between the outdoor heat exchanger 2 and at least one indoor heat exchanger 3 , and a first end of the enthalpy increase pipeline 101 is connected to the subcooler 5 .
  • the air conditioning system further includes a liquid storage member 6, a pressurizing valve 7 and a first pipeline 11.
  • the first pipeline 11 is arranged on the pipeline between the outdoor heat exchanger 2 and the subcooler 5 , the first end of the first pipeline 11 is connected to the outlet of the compressor 1 , the second end of the first pipeline 11 is connected to the liquid storage member 6 , and the pressurizing valve 7 is arranged on the first pipeline 11 .
  • the air conditioning system includes a first throttle member 41 , and the first throttle member 41 is disposed in the first pipeline 11 .
  • the first throttle member 41 includes a capillary tube.
  • the air conditioning system further includes a third expansion valve 23 , which is disposed on a connecting pipeline between the liquid storage element 6 and the outdoor heat exchanger 2 .
  • the third expansion valve 23 includes an electronic expansion valve.
  • the air conditioning system also includes a first one-way valve 61, which is connected in parallel with the third expansion valve 23, the inlet of the first one-way valve 61 is connected to the outdoor heat exchanger 2, and the outlet of the first one-way valve 61 is connected to the liquid storage part 6.
  • the air conditioning system further includes a second pipeline 12 , a third pipeline 13 , a fourth pipeline 14 and a fifth pipeline 15 .
  • the subcooler 5 includes a first branch 51 and a second branch 52 .
  • the first end of the first branch 51 is connected to the liquid storage member 6 through the second pipeline 12 , and the second end of the first branch 51 is connected to at least one indoor heat exchanger 3 through the third pipeline 13 .
  • a first end of the second branch 52 is connected to the liquid storage member 6 through the fourth pipeline 14 , and a second end of the second branch 52 is connected to the inlet of the compressor 1 through the fifth pipeline 15 .
  • the air conditioning system further includes a first expansion valve 21 , and the first expansion valve 21 is disposed in the fourth pipeline 14 .
  • the first expansion valve 21 includes an electronic expansion valve.
  • the air conditioning system further includes an enthalpy increase pipeline 101 , a first end of the enthalpy increase pipeline 101 is connected to the fifth pipeline 15 , and a second end of the enthalpy increase pipeline 101 is connected to an enthalpy increase port of the compressor 1 .
  • the enthalpy increasing pipeline 101 is used to guide the refrigerant passing through the subcooler 5 to the enthalpy increasing port of the compressor 1 to achieve the jet enthalpy increasing effect of the compressor 1 .
  • the air conditioning system further includes a first valve 31 , which is disposed on the fifth pipeline 15 , and is configured to control the on-off of the pipeline between the fifth pipeline 15 and the inlet of the compressor 1 .
  • the first valve 31 is close to the inlet of the compressor 1 relative to the connection between the first end of the enthalpy increase line 101 and the fifth line 15 .
  • the air conditioning system further includes a first control valve 4, the first control valve 4 includes a first state and a In the second state, the first control valve 4 is in the first state and the first flow path is connected, and the first control valve 4 is in the second state and the first flow path is disconnected.
  • the first control valve 4 includes a first interface, a second interface, a third interface and a fourth interface, the first interface is connected to the outlet of the compressor 1, the second interface is connected to the outdoor heat exchanger 2, and the third interface and the fourth interface are both connected to the inlet of the compressor 1.
  • the first control valve 4 is in the first state, the first port is communicated with the second port, and the third port is communicated with the fourth port.
  • the first control valve 4 is in the second state, the first port is communicated with the third port, and the second port is communicated with the fourth port.
  • the air conditioning system includes a sixth pipeline 16 , and the third interface of the first control valve 4 is connected to the inlet of the compressor 1 through the sixth pipeline 16 .
  • the air conditioning system includes a fifth throttle member 45 , which is disposed on the sixth pipeline 16 .
  • the fifth throttle member 45 includes a capillary tube.
  • the first control valve 4 comprises a four-way valve.
  • the air conditioning system further includes a second control valve 10, which includes a third state and a fourth state.
  • a second control valve 10 which includes a third state and a fourth state.
  • the second control valve 10 When the second control valve 10 is in the third state, the second flow path is connected.
  • the second control valve 10 When the second control valve 10 is in the fourth state, the second flow path is disconnected.
  • the second control valve 10 includes a fifth interface, a sixth interface, a seventh interface and an eighth interface
  • the fifth interface is connected to the outlet of the compressor 1
  • the sixth interface is connected to at least one indoor heat exchanger 3
  • the seventh interface and the eighth interface are both inlets of the compressor 1
  • the second control valve 10 is in the third state
  • the fifth interface is connected to the sixth interface
  • the seventh interface is connected to the eighth interface
  • the second control valve 10 is in the fourth state
  • the fifth interface is connected to the seventh interface
  • the sixth interface is connected to the eighth interface.
  • the second control valve 10 includes a four-way valve.
  • the air conditioning system further includes a fourth throttling device 44 , which is disposed on a pipeline connecting the seventh interface and the inlet of the compressor 1 .
  • the fourth throttle member 44 includes a capillary tube.
  • the outdoor heat exchanger 2 includes a water-cooled plate heat exchanger.
  • the water-cooled plate heat exchanger exchanges heat with the refrigerant through circulating water.
  • the embodiment of the present disclosure adopts a water-cooled plate heat exchanger. Since the refrigerant directly exchanges heat with water, its heat exchange effect is much higher than
  • the water-cooled plate heat exchanger is an air source heat exchanger, so the outdoor unit is small in size, which is more conducive to the transportation and installation of the unit and occupies a smaller area.
  • the water-cooled plate heat exchanger does not need to exchange heat with the air, so the water source can be installed in a small machine room without the need for dedicated air ducts and other equipment.
  • the unit has a smaller volume for storing refrigerant, and the refrigerant can be more concentrated by cooperating with the first pipeline 1 and the liquid storage part 6 to drive the rapid flow of liquid refrigerant, thereby achieving a rapid response of the refrigerant fluidity, thereby improving the unit's energy efficiency and comfort.
  • the air conditioning system also includes a conversion unit 102. After the first flow path fluid connects the outlet of the compressor 1 and the outdoor heat exchanger 2, it is connected to at least one indoor heat exchanger 3 through the conversion unit 102 fluid; after the second flow path fluid connects the outlet of the compressor 1, it is connected to at least one indoor heat exchanger 3 through the conversion unit 102 fluid.
  • the air conditioning system further includes an oil-gas separator 8 disposed at the outlet of the compressor 1, and the refrigerant discharged from the compressor 1 first passes through the oil-gas separator 8 before entering the indoor heat exchanger 3 or the outdoor heat exchanger 2.
  • the oil-gas separator 8 is used for oil-gas separation.
  • the air conditioning system further includes a second one-way valve 62, which is disposed on a connecting pipeline between the oil-gas separator 8 and the fifth interface of the second control valve 10.
  • the inlet of the second one-way valve 62 is connected to the oil-gas separator 8, and the outlet of the second one-way valve 62 is connected to the fifth interface of the second control valve 10.
  • the air conditioning system further includes a third one-way valve 63, which is disposed on the connecting pipeline between the oil-gas separator 8 and the first control valve 4.
  • the inlet of the third one-way valve 63 is connected to the oil-gas separator 8, and the outlet of the third one-way valve 63 is connected to the first control valve 4.
  • the air conditioning system further includes a seventh pipeline 17 and a second valve 32.
  • the first end of the seventh pipeline 17 is connected to the oil-gas separator 8, and the second end of the seventh pipeline 17 is connected to the inlet of the compressor 1.
  • the second valve 32 is provided on the seventh pipeline 17, and the second valve 32 is used to control the opening and closing of the seventh pipeline 17.
  • the air conditioning system further includes a second throttle valve 42 , and the second throttle valve 42 is disposed in the seventh pipeline 17 .
  • the air conditioning system further includes a gas-liquid separator 9 disposed at the inlet of the compressor 1 , and the refrigerant flowing through the outdoor heat exchanger 2 or the indoor heat exchanger 3 and returning to the inlet of the compressor 1 first passes through the gas-liquid separator 9 before entering the inlet of the compressor 1 .
  • the fifth pipeline 15 is connected to the inlet of the compressor 1 through the gas-liquid separator 9.
  • the first end of the fifth pipeline 15 is connected to the second branch 52, and the second end of the fifth pipeline 15 is connected to the gas-liquid separator 9, and the gas-liquid separator 9 is connected to the inlet of the compressor 1.
  • the air conditioning system further includes an eighth pipeline 18 , a first end of the eighth pipeline 18 is connected to the indoor heat exchanger 3 , a second end of the eighth pipeline 18 is connected to the gas-liquid separator 9 , and the gas-liquid separator 9 is connected to the inlet of the compressor 2 .
  • the air conditioning system further includes a third throttle valve 43 , which is disposed on the eighth pipeline 18 .
  • the air conditioning system further includes a sixth valve 36, which is disposed on a connecting pipeline between the sixth interface of the second control valve 10 and at least one indoor heat exchanger 3.
  • the sixth valve 36 is used to control the on-off of the connecting pipeline between the sixth interface of the second control valve 10 and at least one indoor heat exchanger 3.
  • the outlet of the compressor 1 is connected to the oil-gas separator 8, and the oil-gas separator 8 is respectively connected to the third one-way valve 63 and the seventh pipeline 17.
  • the seventh pipeline 17 is connected to the inlet of the compressor 1, and the second valve 32 and the second throttle valve 42 are arranged on the seventh pipeline 17.
  • the third one-way valve 63 is connected to the first interface of the first control valve 4 through a pipeline, the second interface of the first control valve 4 is connected to the outdoor heat exchanger 2, the third interface and the fourth interface of the first control valve 4 are connected to the converging pipeline, and the converging pipeline is divided into two paths, one of which is connected to the indoor heat exchanger 3, and the other is connected to the inlet of the compressor 1.
  • the third interface of the first control valve 4 is connected to the converging pipeline through the sixth pipeline 16, and the fifth throttle valve 45 is arranged on the sixth pipeline 16.
  • the first interface of the first control valve 4 can be connected to the second interface, and the third interface of the first control valve 4 is connected to the fourth interface.
  • the first interface of the first control valve 4 is connected to the third interface
  • the second interface of the first control valve 4 is connected to the fourth interface.
  • the third check valve 63 is also connected to the fifth interface of the second control valve 10 through a pipeline.
  • the pipeline connecting the fifth interface of the second control valve 10 and the third check valve 63 is provided with a second check valve 62.
  • the sixth interface of the second control valve 10 is connected to the indoor heat exchanger 3.
  • the sixth valve 36 is provided on the pipeline connecting the sixth interface of the second control valve 10 and the indoor heat exchanger 3.
  • the seventh interface of the second control valve 10 is connected to the eighth interface, and both are connected to the inlet of the compressor 1.
  • the pipeline connecting the seventh interface of the second control valve 10 and the inlet of the compressor 1 is provided with a fourth throttle valve 44.
  • the third one-way valve 63 is also connected to the liquid storage member 6 through the first pipeline 11 , and the first throttling member 41 and the pressurizing valve 7 are provided on the first pipeline 11 .
  • the outdoor heat exchanger 2 is also connected in sequence to the third expansion valve 23, the liquid storage element 6 and the subcooler 5.
  • the first check valve 61 is connected to the third expansion valve 23 in parallel.
  • the subcooler 5 includes a first branch 51 and a second branch 52.
  • the first end of the first branch 51 is connected to the liquid storage member 6 through the second pipeline 12, and the second end of the first branch 51 is connected to at least one indoor heat exchanger 3 through the third pipeline 13.
  • the first end of the second branch 52 is connected to the liquid storage member 6 through the fourth pipeline 14, and the second end of the second branch 52 is connected to the inlet of the compressor 1 through the fifth pipeline 15.
  • the first expansion valve 21 is provided on the fourth pipeline 14.
  • the first end of the enthalpy increase pipeline 101 is connected to the fifth pipeline 15, and the second end of the enthalpy increase pipeline 101 is connected to the enthalpy increase port of the compressor 1; the regulating valve 22 is arranged on the enthalpy increase pipeline 101.
  • the first valve 31 is arranged on the fifth pipeline 15, and the first valve 31 is close to the inlet of the compressor 1 relative to the connection between the enthalpy increase pipeline 101 and the fifth pipeline 15.
  • the fifth pipeline 15 is connected to the inlet of the compressor 1 through the gas-liquid separator 9.
  • the first end of the fifth pipeline 15 is connected to the second branch 52, and the second end of the fifth pipeline 15 is connected to the gas-liquid separator 9, and the gas-liquid separator 9 is connected to the inlet of the compressor 1.
  • the first end of the eighth pipeline 18 is connected to the indoor heat exchanger 3 , the second end of the eighth pipeline 18 is connected to the gas-liquid separator 9 , and the gas-liquid separator 9 is connected to the inlet of the compressor 2 .
  • the third throttle valve 43 is provided on the eighth pipeline 18 .
  • a third valve 33 for controlling the on-off of the third pipeline 13 is provided on the pipeline connecting the third pipeline 13 and at least one indoor heat exchanger 3 .
  • a fourth valve 34 for controlling the on-off of the pipeline is provided on the pipeline connecting at least one indoor heat exchanger 3 and the inlet of the compressor 2 .
  • the eighth pipeline 18 is also provided with a fifth valve 35 for controlling the on-off of the eighth pipeline 18 .
  • Main circuit high-temperature and high-pressure gas refrigerant discharged from the outlet of compressor 1->oil-gas separator 8->first interface and second interface of first control valve 4->outdoor heat exchanger 2 (function: condensation and heat release)->third expansion valve 23 (state: fully open)->liquid storage part 6->second pipeline 12->first branch 51 of subcooler 5->third pipeline 13->third valve 33->conversion unit 102 (function: to realize mode diversion of refrigerant, that is, to divert the refrigerant for cooling or heating to the corresponding indoor unit)->indoor heat exchanger 3 (function: evaporator, evaporation and heat absorption, lowering indoor temperature)->conversion unit 102->gas-liquid separator 9->inlet of compressor 1 (compressor 1 performs the next compression cycle).
  • Pressurization branch When low-temperature cooling or small-load heating is used, the pressurization valve 7 is opened, and the high-temperature and high-pressure gaseous refrigerant at the outlet of the compressor 1 is directly pressed into the liquid storage part 6, providing greater flow power for the liquid refrigerant in the liquid storage part 6, thereby achieving an increase in the mass flow rate of the indoor unit and ultimately improving the capacity at low load.
  • the refrigerant flowing out of the liquid storage member 6 is divided into two paths, one path flows to the first branch 51 of the subcooler 5 , and the other path enters the second branch 52 of the subcooler 5 through the first expansion valve 21 and then enters the fifth pipeline 15 .
  • the refrigerant in the second branch 52 of the subcooler 5 flows to the fifth pipeline 15.
  • the refrigerant enters the enthalpy increasing pipeline 101 and enters the enthalpy injection port of the compressor 1 through the regulating valve 22 to increase the enthalpy and improve the efficiency of the compressor 1.
  • the refrigerant in the second branch 52 of the subcooler 5 flows to the fifth pipeline 15 , the first valve 31 is opened, and the refrigerant enters the gas-liquid separator 9 through the first valve 31 , and enters the inlet of the compressor 1 through the gas-liquid separator 9 .
  • compressor 1 can achieve frequency reduction, which greatly increases the system power reduction, thereby improving the refrigeration energy efficiency.
  • Main circuit high-temperature and high-pressure gas refrigerant at the outlet of compressor 1 -> oil-gas separator 8 -> second control valve 10 -> conversion unit 102 -> indoor heat exchanger 3 (function: condenser, condensation and heat release, increasing indoor temperature) -> conversion unit 102 -> subcooler 5 -> liquid storage part 6 -> third expansion valve 23 (state: throttling and pressure reduction) -> outdoor heat exchanger 2 (function: evaporation and heat absorption) -> first control valve 4 -> gas-liquid separator 9 -> the inlet of compressor 1 (compressor 1 performs the next compression cycle).
  • Pressurization branch When low-temperature cooling or small-load heating is used, the pressurization valve 7 is opened, and the high-temperature and high-pressure gaseous refrigerant at the outlet of the compressor 1 is directly pressed into the liquid storage part 6, providing greater flow power for the liquid refrigerant in the liquid storage part 6, thereby achieving an increase in the mass flow rate of the indoor unit and ultimately improving the capacity at low load.
  • the refrigerant flowing out of the liquid storage member 6 is divided into two paths, one path flows to the first branch 51 of the subcooler 5 , and the other path enters the second branch 52 of the subcooler 5 through the first expansion valve 21 and then enters the fifth pipeline 15 .
  • the refrigerant in the second branch 52 of the subcooler 5 flows to the fifth pipeline 15.
  • the refrigerant enters the enthalpy increasing pipeline 101 and enters the enthalpy injection port of the compressor 1 through the regulating valve 22 to increase the enthalpy and improve the efficiency of the compressor 1.
  • the refrigerant in the second branch 52 of the subcooler 5 flows to the fifth pipeline 15 , the first valve 31 is opened, and the refrigerant enters the gas-liquid separator 9 through the first valve 31 , and enters the inlet of the compressor 1 through the gas-liquid separator 9 .
  • the subcooler 5 can increase the enthalpy difference between the evaporator inlet and outlet, increase the refrigerant flow at the compressor outlet and improve the work done in the compression process, thereby significantly increasing the heating capacity of the system.
  • Refrigeration indoor unit flow direction compressor 1-> first control valve 4-> outdoor heat exchanger 2-> third electronic expansion 23-> liquid storage 6-> subcooler 5-> conversion unit 102-> indoor heat exchanger 3 for refrigeration-> conversion unit 102 —> fourth valve 34 —> gas-liquid separator 9 —> compressor 1 .
  • Pressurization branch When low-temperature cooling or small-load heating is used, the pressurization valve 7 is opened, and the high-temperature and high-pressure gaseous refrigerant at the outlet of the compressor 1 is directly pressed into the liquid storage part 6, providing greater flow power for the liquid refrigerant in the liquid storage part 6, thereby achieving an increase in the mass flow rate of the indoor unit and ultimately improving the capacity at low load.
  • the refrigerant flowing out of the liquid storage member 6 is divided into two paths, one path flows to the first branch 51 of the subcooler 5 , and the other path enters the second branch 52 of the subcooler 5 through the first expansion valve 21 and then enters the fifth pipeline 15 .
  • the refrigerant in the second branch 52 of the subcooler 5 flows to the fifth pipeline 15.
  • the refrigerant enters the enthalpy increasing pipeline 101 and enters the enthalpy injection port of the compressor 1 through the regulating valve 22 to increase the enthalpy and improve the efficiency of the compressor 1.
  • the refrigerant in the second branch 52 of the subcooler 5 flows to the fifth pipeline 15 , the first valve 31 is opened, and the refrigerant enters the gas-liquid separator 9 through the first valve 31 , and enters the inlet of the compressor 1 through the gas-liquid separator 9 .
  • Refrigeration indoor unit flow direction refrigerant from the indoor heat exchanger 3 for heating -> conversion unit 102 -> indoor heat exchanger 3 for cooling -> conversion unit 102 -> fourth valve 34 -> gas-liquid separator 9 -> compressor 1 .
  • Pressurization branch When low-temperature cooling or small-load heating is used, the pressurization valve 7 is opened, and the high-temperature and high-pressure gaseous refrigerant at the outlet of the compressor 1 is directly pressed into the liquid storage part 6, providing greater flow power for the liquid refrigerant in the liquid storage part 6, thereby achieving an increase in the mass flow rate of the indoor unit and ultimately improving the capacity at low load.
  • the refrigerant flowing out of the liquid storage member 6 is divided into two paths, one path flows to the first branch 51 of the subcooler 5 , and the other path enters the second branch 52 of the subcooler 5 through the first expansion valve 21 and then enters the fifth pipeline 15 .
  • the refrigerant in the second branch 52 of the subcooler 5 flows to the fifth pipeline 15.
  • the refrigerant enters the enthalpy increasing pipeline 101 and enters the enthalpy injection port of the compressor 1 through the regulating valve 22 to increase the enthalpy and improve the efficiency of the compressor 1.
  • the refrigerant in the second branch 52 of the subcooler 5 flows to the fifth pipeline 15 , the first valve 31 is opened, and the refrigerant enters the gas-liquid separator 9 through the first valve 31 , and enters the inlet of the compressor 1 through the gas-liquid separator 9 .
  • the air conditioning system provided by the present disclosure can realize the full cooling mode and In addition to full cooling mode, there are:
  • Main cooling mode Most of the indoor units can run in cooling mode, and a small number of indoor units can run in heating mode at the same time.
  • Main heating air conditioning system Most of the indoor units can operate in heating mode, and a small number of indoor units can operate in cooling mode at the same time.
  • Full heat recovery mode The number of indoor cooling units and indoor heating units is basically the same. At this time, the outdoor heat exchanger does not participate in the work. In this mode, some indoor heat exchangers are used as condensers and some indoor heat exchangers are used as evaporators, and the heat exchange capacity remains the same. The beneficial effect is that the heat exchange of different indoor rooms can be directly utilized to meet the needs of simultaneous cooling and heating.
  • the system can utilize the energy exchange of different indoor rooms (such as one room is mainly used for cooling and the other room is mainly used for heating. Therefore, the system can absorb heat from the cooling room, and through the vapor compression of the compressor, the low-level thermal energy is increased to high-level thermal energy, and then discharged to the indoor unit of the heating room to release heat).
  • the energy exchange since the energy exchange mainly comes from indoor rooms of different modes, the energy exchange from the outside (outdoor or water source side) can be greatly reduced or eliminated, thereby reducing energy consumption (such as reducing the opening or operation of the cooling tower (when cooling) or the boiler (when heating) (including the water pump)). Therefore, the air-conditioning system provided in the embodiment of the present disclosure can further reduce the energy consumption of the entire system and improve energy saving.
  • Some embodiments further provide a control method for the above air conditioning system, which includes:
  • the regulating valve 22 is opened, the enthalpy increase pipeline 101 is connected, and the enthalpy increase mode is entered.
  • the first preset temperature value T1 ranges from 3° C. to 13° C.
  • the first preset temperature value T1 is 8° C.
  • the second preset temperature value T2 ranges from 35° C. to 45° C.
  • the second preset temperature value T2 is 40° C.
  • the third preset temperature T3 has a value range of 15° C. to 25° C.
  • the third preset temperature T3 is 20° C.
  • the first preset time ranges from 0 min to 10 min.
  • the first preset time is 5 min.
  • the pressure at the outlet of the compressor 1 is detected by a pressure detection element, and the saturation temperature corresponding to the pressure at the outlet of the compressor 1 is obtained by looking up a table.
  • the pressure at the inlet of the compressor 1 is detected by a pressure detection element, and the saturation temperature corresponding to the pressure at the inlet of the compressor 1 is obtained by looking up a table.
  • the following actions are performed:
  • Compressor 1 runs at the frequency required by the set target temperature.
  • the frequency of compressor 1 is increased, otherwise, the frequency of compressor 1 is reduced.
  • the air conditioning system further includes a subcooler 5, a liquid storage member 6, a second pipeline 12, a third pipeline 13, a fourth pipeline 14 and a fifth pipeline 15, a first expansion valve 21 and a first valve 31;
  • the liquid storage member 6 is arranged on the pipeline between the outdoor heat exchanger 2 and the subcooler 5;
  • the subcooler 5 includes a first branch 51 and a second branch 52, the first end of the first branch 51 is connected to the liquid storage member 6 through the second pipeline 12, and the second end of the first branch 51 is connected to at least one indoor heat exchanger 3 through the third pipeline 13;
  • the second branch The first end of the second branch 52 is connected to the liquid storage member 6 through the fourth pipeline 14, and the second end of the second branch 52 is connected to the inlet of the compressor 1 through the fifth pipeline 15;
  • the first expansion valve 21 is provided on the fourth pipeline 14;
  • the first valve 31 is provided on the fifth pipeline 15, and the first valve 31 is configured to control the pipeline opening and closing between the fifth pipeline 15 and the inlet of the compressor 1; the
  • the air conditioning system After the air conditioning system enters the enthalpy increase mode, it also performs the following actions:
  • the first expansion valve 21 is opened. otherwise, the opening of the first expansion valve 21 is reduced;
  • the regulating valve 22 is set to the maximum opening.
  • the air conditioning system exits the enthalpy increase mode when at least one of the following conditions is met:
  • the saturation temperature corresponding to the pressure at the inlet of the compressor 1 is ⁇ the fourth preset temperature T4; in the heating mode, the saturation temperature corresponding to the pressure at the outlet of the compressor 1 is ⁇ the fifth preset temperature T5; wherein T5>T4;
  • the difference between the actual exhaust temperature at the outlet of the compressor 1 and the saturation temperature corresponding to the pressure at the outlet of the compressor 1 is less than the sixth preset temperature T6.
  • the second preset time ranges from 5 minutes to 15 minutes.
  • the second preset time is 10 minutes.
  • the fourth preset temperature T4 has a value range of -10°C to 0°C.
  • the fourth preset temperature T4 is -5°C.
  • the fifth preset temperature T5 has a value range of 45° C. to 55° C.
  • the fifth preset temperature T5 is 50° C.
  • the sixth preset temperature T6 has a value range of 0° C. to 10° C.
  • the sixth preset temperature T6 is 5° C.
  • Compressor 1 maintains the current frequency operation
  • the opening of the first expansion valve 21 is increased; otherwise, the opening of the first expansion valve 21 is decreased;
  • the air conditioning system further includes a liquid storage member 6, a pressurizing valve 7 and a first pipeline 11, the liquid storage member 6 is arranged on the pipeline between the outdoor heat exchanger 2 and at least one indoor heat exchanger 3, the first end of the first pipeline 11 is connected to the outlet of the compressor 1, the second end of the first pipeline 11 is connected to the liquid storage member 6, and the pressurizing valve 7 is arranged on the first pipeline 11.
  • the air-conditioning system After the air-conditioning system starts to run for the first preset time, if the ratio of the target value of the required cooling capacity or heating capacity to the rated value of the cooling capacity or heating capacity of the air-conditioning system is ⁇ the first preset value A, and after continuing to run for the third preset time, the saturation temperature corresponding to the pressure at the outlet of the compressor 1 is ⁇ the seventh preset temperature value T7, and the actual exhaust temperature at the outlet of the compressor 1 is ⁇ the eighth preset temperature value T8, then the pressurizing valve 7 is opened, wherein T8>T7.
  • the third preset time ranges from 0 min to 10 min.
  • the third preset time is 5 min.
  • the first preset value A ranges from 15% to 25%. Optionally, the first preset value A is 20%.
  • the seventh preset temperature value T7 ranges from 20° C. to 30° C. Optionally, the seventh preset temperature value T7 is 25° C.
  • the eighth preset temperature value T8 has a value range of 45° C. to 55° C.
  • the eighth preset temperature value T8 is 50° C.
  • the pressurizing valve 7 is closed when at least one of the following conditions is met:
  • the pressurizing valve 7 is opened and continues to operate for a second preset time, and the saturation temperature corresponding to the pressure at the outlet of the compressor 1 is ⁇ the ninth preset temperature T9;
  • the pressurizing valve 7 is opened and continues to operate for a second preset time, and the difference between the actual exhaust temperature at the outlet of the compressor 1 and the saturation temperature corresponding to the pressure at the outlet of the compressor 1 is less than the tenth preset temperature T10; wherein, T9>T10.
  • the ninth preset temperature T9 has a value range of 30° C. to 40° C.
  • the ninth preset temperature T9 is 35° C.
  • the value range of the tenth preset temperature T10 is 0° C. to 10° C.
  • the tenth preset temperature T10 is 5° C.
  • the air conditioning system provided by the embodiment of the present disclosure has the beneficial effects of improving energy efficiency, reducing costs, reducing weight, and high reliability.

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Abstract

一种空调系统及控制方法，空调系统包括：压缩机（1）、至少两个室内换热器（3）、室外换热器（2）以及并联的第一流路和第二流路；其中第一流路流体连通压缩机（1）的出口、室外换热器（2）和至少一个室内换热器（3）；第二流路流体连通压缩机（1）的出口和至少一个室内换热器（3）；第一流路和第二流路被配置为择一工作或同时工作；增焓管路（101），第一端连接于室外换热器（2）与至少一个室内换热器（3）之间的管路上，第二端连接于压缩机（1）的增焓口；调节阀（22）设于增焓管路（101），调节阀（22）被配置为调节增焓管路（101）的通断及流量。空调系统包括完全制冷、完全制热、主体制冷、主体制热模式等，在这些模式下，均可以选择性打开调节阀（22），使增焓管路（101）连通，实现压缩机（1）的增焓，提高了压缩机（1）的能效和性能。

Description

空调系统及控制方法
本公开是以CN申请号为202211396515.9，申请日为2022年11月9日的申请为 基础，并主张其优先权，该CN申请的公开内容在此作为整体引入本申请中。
技术领域
本公开涉及空气调节技术领域，尤其涉及一种空调系统及控制方法。
背景技术
热回收多联机相对于热泵多联机的功能模式多，在一些相关技术中，热回收多联机采用非增焓压缩机，存在能效一般，节能平常，排气温度高，控制手段少等问题。
发明内容
在本公开的一个方面，提供一种空调系统，包括：
压缩机；
至少两个室内换热器；
室外换热器；
并联的第一流路和第二流路；其中所述第一流路流体连通所述压缩机的出口、所述室外换热器和至少一个室内换热器；所述第二流路流体连通所述压缩机的出口和至少一个室内换热器；所述第一流路和所述第二流路被配置为择一工作或同时工作；
增焓管路，第一端连接于所述室外换热器与至少一个室内换热器之间的管路上，第二端连接于所述压缩机的增焓口；以及
调节阀，设于所述增焓管路，所述调节阀被配置为调节所述增焓管路的通断及流量。
在一些实施例中，空调系统还包括并联的第三流路和第四流路，所述第三流路流体连通至少一个室内换热器和所述压缩机的进口，所述第四流路流体连通至少一个室内换热器、所述室外换热器和所述压缩机的进口，所述第三流路和所述第四流路被配置为择一工作或同时工作。
在一些实施例中，空调系统还包括转换单元，在其中至少一个室内换热器为室内 冷凝器，其中至少一个室内换热器为室内蒸发器的状态下，所述室内蒸发器的冷媒通过所述转换单元流向所述室内冷凝器，或者所述室内冷凝器的冷媒通过所述转换单元流向所述室内蒸发器。
在一些实施例中，空调系统还包括储液件、加压阀和第一管路，所述储液件设于所述室外换热器与至少一个室内换热器之间的管路上，所述第一管路的第一端连接于所述压缩机的出口，所述第一管路的第二端连接于所述储液件，所述加压阀设于所述第一管路。
在一些实施例中，空调系统还包括过冷器，所述过冷器设于所述室外换热器与至少一个室内换热器之间的管路上，所述增焓管路的第一端连接于所述过冷器。
在一些实施例中，空调系统还包括储液件、加压阀和第一管路，所述储液件设于所述室外换热器与所述过冷器之间的管路上，所述第一管路的第一端连接于所述压缩机的出口，所述第一管路的第二端连接于所述储液件，所述加压阀设于所述第一管路。
在一些实施例中，空调系统还包括第二管路、第三管路、第四管路和第五管路，所述过冷器包括第一支路和第二支路，所述第一支路的第一端通过所述第二管路连接于所述储液件，所述第一支路的第二端通过所述第三管路连接于至少一个室内换热器；所述第二支路的第一端通过所述第四管路连接于所述储液件，所述第二支路的第二端通过所述第五管路连接于所述压缩机的进口。
在一些实施例中，空调系统还包括第一膨胀阀，所述第一膨胀阀设于所述第四管路。
在一些实施例中，空调系统还包括第一阀，所述第一阀设于所述第五管路，所述第一阀被配置控制所述第五管路与所述压缩机的进口之间的管路通断。
在一些实施例中，所述增焓管路的第一端连接于所述第五管路，所述第一阀相对于所述增焓管路的第一端与所述第五管路的连接处靠近所述压缩机的进口。
在一些实施例中，空调系统还包括第一控制阀，所述第一控制阀包括第一状态和第二状态，所述第一控制阀处于所述第一状态，所述第一流路连通，所述第一控制阀处于所述第二状态，所述第一流路断开。
在一些实施例中，所述第一控制阀包括第一接口、第二接口、第三接口和第四接口，所述第一接口连接于所述压缩机的出口，所述第二接口连接于所述室外换热器，所述第三接口和所述第四接口均连接于所述压缩机的进口，所述第一控制阀处于所述 第一状态，所述第一接口与所述第二接口连通，所述第三接口与所述第四接口连通，所述第一控制阀处于所述第二状态，所述第一接口与所述第三接口连通，所述第二接口与所述第四接口连通。
在一些实施例中，空调系统还包括第二控制阀，所述第二控制阀包括第三状态和第四状态，所述第二控制阀处于所述第三状态，所述第二流路连通，所述第二控制阀处于所述第四状态，所述第二流路断开。
在一些实施例中，所述第二控制阀包括第五接口、第六接口、第七接口和第八接口，所述第五接口连接于所述压缩机的出口，所述第六接口连接于至少一个室内换热器，所述第七接口和所述第八接口均所述压缩机的进口，所述第二控制阀处于所述第三状态，所述第五接口与所述第六接口连通，所述第七接口与所述第八接口连通，所述第二控制阀处于所述第四状态，所述第五接口与所述第七接口连通，所述第六接口与所述第八接口连通。
在一些实施例中，所述室外换热器包括水冷板式换热器。
在一些实施例中，空调系统还包括转换单元，所述第一流路流体连通所述压缩机的出口和所述室外换热器后，通过所述转换单元流体连通至少一个室内换热器；所述第二流路流体连通所述压缩机的出口后，通过所述转换单元流体连通至少一个室内换热器。
在本公开的一个方面，提供一种上述实施例中的空调系统的控制方法，包括：
在空调系统开始启动运行第一预设时间后，
在制冷模式时，如果压缩机的进口的压力对应的饱和温度≥第一预设温度值T1；
在制热模式时，如果压缩机的出口的压力对应的饱和温度≤第二预设温度值T2，T2>T1；
并且压缩机的出口的实际排气温度与压缩机的出口的压力对应的饱和温度的差值≥第三预设温度T3；
则打开调节阀，增焓管路连通，进入增焓模式。
在一些实施例中，其中空调系统进入增焓模式后，执行以下动作：
压缩机按照设定的目标温度所需的频率运行，
在制冷模式时，如果压缩机的进口的压力对应的饱和温度低于设定的目标温度所需的压缩机的进口的压力对应的饱和温度，则降低压缩机频率，否则，升高压缩机频 率；
在制热模式时，如果压缩机的出口的压力对应的饱和温度低于设定的目标温度所需的压缩机的出口的压力对应的饱和温度，则升高压缩机的频率，否则，降低压缩机的频率。
在一些实施例中，其中空调系统还包括过冷器、储液件、第二管路、第三管路、第四管路和第五管路、第一膨胀阀和第一阀；所述储液件设于所述室外换热器与过冷器之间的管路上；所述过冷器包括第一支路和第二支路，所述第一支路的第一端通过所述第二管路连接于所述储液件，所述第一支路的第二端通过所述第三管路连接于至少一个室内换热器；所述第二支路的第一端通过所述第四管路连接于所述储液件，所述第二支路的第二端通过所述第五管路连接于所述压缩机的进口；所述第一膨胀阀设于所述第四管路；所述第一阀设于所述第五管路，所述第一阀被配置控制所述第五管路与所述压缩机的进口之间的管路通断；所述增焓管路的第一端连接于所述第五管路，所述第一阀相对于所述增焓管路的第一端与所述第五管路的连接处靠近所述压缩机的进口；
空调系统进入增焓模式后，还执行以下动作：
如果过冷器的出口与进口的实际温度差值≥设定的目标温度所需的过冷器的出口与进口的目标温度差值，则开大第一膨胀阀的开度，否则，调小第一膨胀阀的开度；
关闭第一阀；
使调节阀处于最大开度。
在一些实施例中，其中，在满足下述条件至少之一时，空调系统退出增焓模式：
关机；
停机；
进入增焓模式运行第二预设时间后，在制冷模式时，压缩机的进口的压力对应的饱和温度≤第四预设温度T4；在制热模式时，压缩机的出口的压力对应的饱和温度≥第五预设温度T5；其中，T5>T4；
进入增焓模式运行第二预设时间后，压缩机的出口的实际排气温度与压缩机的出口的压力对应的饱和温度的差值<第六预设温度T6。
在一些实施例中，其中，空调系统退出增焓模式时执行以下动作：
压缩机维持当前的频率运行；
如果过冷器的出口与进口的实际温度差值>设定的目标温度所需的过冷器的出口与进口的目标温度差值，则开大第一膨胀阀的开度，否则，则调小第一膨胀阀的开度；
开启第一阀；
关闭调节阀。
在一些实施例中，所述空调系统还包括储液件、加压阀和第一管路，所述储液件设于所述室外换热器与至少一个室内换热器之间的管路上，所述第一管路的第一端连接于所述压缩机的出口，第二端连接于所述储液件，所述加压阀设于所述第一管路；
在空调系统开始启动运行第一预设时间后，如果所需的制冷量或制热量的目标值与空调系统的制冷量或制热量的额定值的比值≤第一预设值A，且继续运行第三预设时间后，压缩机的出口的压力对应的饱和温度≤第七预设温度值T7，压缩机的出口的实际排气温度≥第八预设温度值T8，则开启加压阀，其中，T8>T7。
在一些实施例中，在满足下述条件至少之一时，关闭加压阀：
关机；
停机；
开启加压阀继续运行第二预设时间，压缩机的出口的压力对应的饱和温度≥第九预设温度T9；
开启加压阀继续运行第二预设时间，压缩机的出口的实际排气温度与压缩机的出口的压力对应的饱和温度的差值<第十预设温度T10；其中，T9>T10。
基于上述技术方案，本公开至少具有以下有益效果：
在一些实施例中，空调系统包括完全制冷模式、完全制热模式、主体制冷模式、主体制热模式等，在这些模式下，均可以选择性打开调节阀，使增焓管路连通，实现压缩机的增焓，因此，提高了压缩机的能效和性能。
附图说明
此处所说明的附图用来提供对本公开的进一步理解，构成本申请的一部分，本公开的示意性实施例及其说明用于解释本公开，并不构成对本公开的不当限定。在附图中：
图1为根据本公开一些实施例提供的空调系统的示意图；
图2为根据本公开一些实施例提供的空调系统的完全制冷增焓模式的示意图；
图3为根据本公开一些实施例提供的空调系统的完全制热增焓模式的示意图；
图4为根据本公开一些实施例提供的空调系统的热回收增焓模式的示意图。
具体实施方式
下面将结合本公开实施例中的附图，对实施例中的技术方案进行清楚、完整地描述。显然，所描述的实施例仅仅是本公开的一部分实施例，而不是全部的实施例。基于本公开的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本公开保护的范围。
在本公开的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本公开和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本公开保护范围的限制。
本公开的一些实施例提出一种空调系统及控制方法，用于缓解能效不高的问题。
图1是根据本公开空调系统的一些实施例的结构示意图。参考图1，在一些实施例中，空调系统包括压缩机1、至少两个室内换热器3、室外换热器2、并联的第一流路和第二流路、增焓管路101和调节阀22。
其中第一流路流体连通压缩机1的出口、室外换热器2和至少一个室内换热器3。第二流路流体连通压缩机1的出口和至少一个室内换热器3。第一流路和第二流路被配置为择一工作或同时工作。
增焓管路101的第一端连接于室外换热器2与至少一个室内换热器3之间的管路上，增焓管路101的第二端连接于压缩机1的增焓口。
调节阀22设于增焓管路101，调节阀22被配置为调节增焓管路101的通断及流量。
在一些实施例中，压缩机1包括喷气增焓压缩机。
压缩机1的增焓口设于压缩机1的中压腔。
在一些实施例中，调节阀22包括电子膨胀阀。采用精度较高的电子膨胀阀，能够实现无极喷焓的平稳调节，并可以机组状态精准控制喷焓量的大小，提高舒适性、可靠性以及使能效的过度更加平稳。
在本公开实施例中，空调系统包括一个室外换热器2和至少两个室内换热器3，至少两个室内换热器3并联连接，该空调系统为多联机系统。
在本公开实施例中，第一流路和第二流路是流体连通路径。在一些工作模式下，沿冷媒的流向，压缩机1的出口、室外换热器2和至少一个室内换热器3依次流体连通为第一流路。在另一些工作模式下，沿冷媒的流向，至少一个室内换热器3、室外换热器2和压缩机1的进口依次流体连通，因此，实际上空调系统的一些管路、室外换热器2、至少一个室内换热器3等可能会位于第一流路，也可能会位于其他流路，同理，至少一个室内换热器3可能会位于第一流路、或者第二流路，或者也可能位于其他流路，因此，第一流路和第二流路并不一定是固定的管道，因此，第一流路和第二流路图中没有标号示出。
在本公开实施例中，第一流路流体连通压缩机1的出口、室外换热器2和至少一个室内换热器3，该至少一个室内换热器3为室内蒸发器，能够为室内降温制冷。第二流路流体连通压缩机1的出口和至少一个室内换热器3，该至少一个室内换热器3为室内冷凝器，能够为室内制热升温。并且，第一流路可以单独工作，所有室内换热器3均为室内蒸发器，为完全制冷模式，第二流路可以单独工作，所有室内换热器3均为室内冷凝器，为完全制热模式。第一流路和第二流路可以同时工作，且在室内蒸发器的数量大于室内冷凝器的情况下，为主体制冷模式，在室内冷凝器的数量大于室内蒸发器的情况下，为主体制热模式，因此，该本公开实施例提供的空调系统包括完全制冷模式、完全制热模式、主体制冷模式、主体制热模式等，在这些模式下，均可以选择性打开调节阀22，使增焓管路101连通，实现压缩机的增焓，因此，提高了压缩机的能效和性能。
在一些实施例中，至少两个室内换热器3包括两个、三个、四个或四个以上室内换热器。
在一些实施例中，空调系统还包括并联的第三流路和第四流路，第三流路流体连通至少一个室内换热器3和压缩机1的进口，第四流路流体连通至少一个室内换热器3、室外换热器2和压缩机1的进口，第三流路和第四流路被配置为择一工作或同时工作。
第三流路可以与第一流路连通形成循环回路，第四流路可以与第二流路连通形成循环回路，第三流路和第四流路也是表示流体连通路径，不一定是固定管路，因此， 图中没有示出标号。
参考图2至图4，在一些实施例中，空调系统还包括转换单元102，在至少两个室内换热器3的其中至少一个室内换热器3为室内冷凝器，其中至少一个室内换热器3为室内蒸发器的状态下，室内蒸发器的冷媒可以通过转换单元102流向室内冷凝器，或者，室内冷凝器的冷媒可以通过转换单元102流向室内蒸发器。
在主体制冷模式下，室内蒸发器的冷媒通过转换单元102流向室内冷凝器，能够将需要制冷的室内的热量回收送至需要制热的室内，可以不使用室外换热器2，降低能耗。
在主体制热模式下，室内冷凝器的冷媒通过转换单元102流向室内蒸发器，能够将需要制热的室内的冷量回收送至需要制冷的室内，可以不使用室外换热器2，降低能耗。
在一些实施例中，空调系统还包括储液件6，储液件6设于室外换热器2与至少一个室内换热器3之间的连接管路上。
在一些实施例中，空调系统还包括第一管路11，第一管路11的第一端连接于压缩机1的出口，第一管路11的第二端连接于储液件6。
在一些实施例中，空调系统还包括加压阀7，加压阀7设于第一管路11。
在低温制冷或最小制冷、或低负荷制热时，因制冷能力需求较低，导致压缩机1的频率较低，因此，会造成动力不足，而无法推动冷媒循环，反而会造成低温制冷或最小制冷、或低负荷制热能力偏低。
基于此，本公开实施例中的第一管路11的第一端连接于压缩机1的出口，第一管路11的第二端连接于储液件6。在低温启动时，例如：低温制冷、最小制冷或小负荷制热时，开启加压阀7，第一管路11连通，第一管路11直接从压缩机1的出口引出高压气态冷媒，且直接加压灌注于储液件6中，相当于屏蔽室外换热器2的压力损失，为储液件6中的液态冷媒提供更大的流动动力，加大流往室内换热器3的冷媒流量，提高冷媒推动能力，从而提高低温启动速度，提高低温制冷或最小制冷、或低负荷制热的能力，从而提升了系统的运行能力。
在一些实施例中，空调系统还包括过冷器5，过冷器5设于室外换热器2与至少一个室内换热器3之间的连接管路上，增焓管路101的第一端连接于过冷器5。
在一些实施例中，空调系统还包括储液件6、加压阀7和第一管路11，储液件6 设于室外换热器2与过冷器5之间的管路上，第一管路11的第一端连接于压缩机1的出口，第一管路11的第二端连接于储液件6，加压阀7设于第一管路11。
在一些实施例中，空调系统包括第一节流件41，第一节流件41设于第一管路11。
可选地，第一节流件41包括毛细管。
在一些实施例中，空调系统还包括第三膨胀阀23，第三膨胀阀23设于储液件6与室外换热器2之间的连接管路上。
可选地，第三膨胀阀23包括电子膨胀阀。
在一些实施例中，空调系统还包括第一单向阀61，第一单向阀61与第三膨胀阀23并联连接，第一单向阀61的进口连接于室外换热器2，第一单向阀61的出口连接于储液件6。
在一些实施例中，空调系统还包括第二管路12、第三管路13、第四管路14和第五管路15。
过冷器5包括第一支路51和第二支路52。
第一支路51的第一端通过第二管路12连接于储液件6，第一支路51的第二端通过第三管路13连接于至少一个室内换热器3。
第二支路52的第一端通过第四管路14连接于储液件6，第二支路52的第二端通过第五管路15连接于压缩机1的进口。
在一些实施例中，空调系统还包括第一膨胀阀21，第一膨胀阀21设于第四管路14。
可选地，第一膨胀阀21包括电子膨胀阀。
在一些实施例中，空调系统还包括增焓管路101，增焓管路101的第一端与第五管路15连接，增焓管路101的第二端与压缩机1的增焓口连接。
增焓管路101用于将经过过冷器5的冷媒引向压缩机1的增焓口，以实现压缩机1的喷气增焓作用。
在一些实施例中，空调系统还包括第一阀31，第一阀31设于第五管路15，第一阀31被配置控制第五管路15与压缩机1的进口之间的管路通断。
在一些实施例中，第一阀31相对于增焓管路101的第一端与第五管路15的连接处靠近压缩机1的进口。
在一些实施例中，空调系统还包括第一控制阀4，第一控制阀4包括第一状态和 第二状态，第一控制阀4处于第一状态，第一流路连通，第一控制阀4处于第二状态，第一流路断开。
在一些实施例中，第一控制阀4包括第一接口、第二接口、第三接口和第四接口，第一接口连接于压缩机1的出口，第二接口连接于室外换热器2，第三接口和第四接口均连接于压缩机1的进口。
第一控制阀4处于第一状态，第一接口与第二接口连通，第三接口与第四接口连通。
第一控制阀4处于第二状态，第一接口与第三接口连通，第二接口与第四接口连通。
在一些实施例中，空调系统包括第六管路16，第一控制阀4的第三接口通过第六管路16连接于压缩机1的进口。
在一些实施例中，空调系统包括第五节流件45，第五节流件45设于第六管路16。
可选地，第五节流件45包括毛细管。
在一些实施例中，第一控制阀4包括四通阀。
在一些实施例中，空调系统还包括第二控制阀10，第二控制阀10包括第三状态和第四状态，第二控制阀10处于第三状态，第二流路连通，第二控制阀10处于第四状态，第二流路断开。
在一些实施例中，第二控制阀10包括第五接口、第六接口、第七接口和第八接口，第五接口连接于压缩机1的出口，第六接口连接于至少一个室内换热器3，第七接口和第八接口均压缩机1的进口，第二控制阀10处于第三状态，第五接口与第六接口连通，第七接口与第八接口连通，第二控制阀10处于第四状态，第五接口与第七接口连通，第六接口与第八接口连通。
在一些实施例中，第二控制阀10包括四通阀。
在一些实施例中，空调系统还包括第四节流件44，第四节流件44设于第七接口与压缩机1的进口连接的管路上。
可选地，第四节流件44包括毛细管。
在一些实施例中，室外换热器2包括水冷板式换热器。
水冷板式换热器通过循环水与冷媒进行换热。
本公开实施例采用水冷板式换热器，由于冷媒与水直接换热，其换热效果远高于 空气源的换热器，因此，室外机体积小，更有利于机组搬运、机组安装、占地面积更小。并且，水冷板式换热器不需要与空气进行换热器，因此，水源可以装在狭小的机房中，而不需要专设风道等设备。采用水冷板式换热器，机组存储冷媒的内容积较小，可通过与第一管路1和储液件6的配合，使冷媒更加集中，以驱动液态冷媒的快速流动，进而实现冷媒流动性的快速响应，从而能够提高机组能力能效，改善使用舒适性。
在一些实施例中，空调系统还包括转换单元102，第一流路流体连通压缩机1的出口和室外换热器2后，通过转换单元102流体连通于至少一个室内换热器3；第二流路流体连通压缩机1的出口后，通过转换单元102流体连通于至少一个室内换热器3。
在一些实施例中，空调系统还包括设于压缩机1的出口处的油气分离器8，压缩机1排出的冷媒先经过油气分离器8后进入室内换热器3或室外换热器2。油气分离器8用于油气分离。
在一些实施例中，空调系统还包括第二单向阀62，第二单向阀62设于油气分离器8与第二控制阀10的第五接口之间的连接管路上。第二单向阀62的进口连接于油气分离器8，第二单向阀62的出口连接于第二控制阀10的第五接口。
在一些实施例中，空调系统还包括第三单向阀63，第三单向阀63设于油气分离器8与第一控制阀4之间的连接管路上。第三单向阀63的进口连接于油气分离器8，第三单向阀63的出口连接于第一控制阀4。
在一些实施例中，空调系统还包括第七管路17和第二阀32。第七管路17的第一端连接于油气分离器8，第七管路17的第二端连接于压缩机1的进口。第二阀32设于第七管路17，第二阀32用于控制第七管路17的通断。
在一些实施例中，空调系统还包括第二节流阀42，第二节流阀42设于第七管路17。
在一些实施例中，空调系统还包括设于压缩机1的进口处的气液分离器9，流经室外换热器2或室内换热器3返回压缩机1的进口的冷媒先经过气液分离器9后进入压缩机1的进口。
在一些实施例中，第五管路15通过气液分离器9与压缩机1的进口连通。第五管路15的第一端连接于第二支路52，第五管路15的第二端连接于气液分离器9，气液分离器9连接于压缩机1的进口。
在一些实施例中，空调系统还包括第八管路18，第八管路18的第一端连接于室内换热器3，第八管路18的第二端连接于气液分离器9，气液分离器9连接于压缩机2的进口。
在一些实施例中，空调系统还包括第三节流阀43，第三节流阀43设于第八管路18。
在一些实施例中，空调系统还包括第六阀36，第六阀36设于第二控制阀10的第六接口与至少一个室内换热器3之间的连接管路上。第六阀36用于控制第二控制阀10的第六接口与至少一个室内换热器3之间的连接管路的通断。
下面结合图1至图4详细描述空调系统的一些具体实施例，以及空调系统的完全制冷增焓模式、完全制热增焓模式和热回收增焓模式。
如图1所示，压缩机1的出口连接于油气分离器8，油气分离器8分别连接于第三单向阀63和第七管路17。第七管路17连接于压缩机1的进口，且第七管路17上设置第二阀32和第二节流阀42。
第三单向阀63通过管路连接于第一控制阀4的第一接口，第一控制阀4的第二接口连接于室外换热器2，第一控制阀4的第三接口和第四接口连接于合流管路，合流管路分为两路，一路连接于室内换热器3，另一路连接于压缩机1的进口。第一控制阀4的第三接口通过第六管路16连接该合流管路，第六管路16上设置第五节流阀45。第一控制阀4的第一接口可以与第二接口连通，第一控制阀4的第三接口与第四接口连通。或者，第一控制阀4的第一接口与第三接口连通，第一控制阀4的第二接口与第四接口连通。
第三单向阀63还通过管路连接于第二控制阀10的第五接口，第二控制阀10的第五接口与第三单向阀63连接的管路上设有第二单向阀62，第二控制阀10的第六接口连接于室内换热器3，第二控制阀10的第六接口与室内换热器3连接的管路上设置第六阀36，第二控制阀10的第七接口和第八接口连接，且均连接于压缩机1的进口。第二控制阀10的第七接口与压缩机1的进口连接的管路上设有第四节流阀44。
第三单向阀63还通过第一管路11连接于储液件6，第一管路11上设有第一节流件41和加压阀7。
室外换热器2还依次连接第三膨胀阀23、储液件6和过冷器5。第一单向阀61与第三膨胀阀23并联连接。
过冷器5包括第一支路51和第二支路52。第一支路51的第一端通过第二管路12连接于储液件6，第一支路51的第二端通过第三管路13连接于在至少一个室内换热器3。第二支路52的第一端通过第四管路14连接于储液件6，第二支路52的第二端通过第五管路15连接于压缩机1的进口。第一膨胀阀21设于第四管路14。
增焓管路101的第一端与第五管路15连接，增焓管路101的第二端与压缩机1的增焓口连接；调节阀22设于增焓管路101。第一阀31设于第五管路15，第一阀31相对于增焓管路101与第五管路15的连接处靠近压缩机1的进口。
第五管路15通过气液分离器9与压缩机1的进口连通。第五管路15的第一端连接于第二支路52，第五管路15的第二端连接于气液分离器9，气液分离器9连接于压缩机1的进口。
第八管路18的第一端连接于室内换热器3，第八管路18的第二端连接于气液分离器9，气液分离器9连接于压缩机2的进口。第三节流阀43设于第八管路18。
第三管路13与至少一个室内换热器3连接的管路上设有控制管路通断的第三阀33。
至少一个室内换热器3与压缩机2的进口连接的管路上设有控制管路通断的第四阀34。
第八管路18上还设有控制第八管路18通断的第五阀35。
如图2所示，空调系统在完全制冷模式同时增焓时的冷媒流向及作用。
主路：压缩机1的出口排出的高温高压气体冷媒—>油气分离器8—>第一控制阀4的第一接口和第二接口—>室外换热器2(作用：冷凝放热)—>第三膨胀阀23(状态：全开)—>储液件6—>第二管路12—>过冷器5的第一支路51—>第三管路13—>第三阀33—>转换单元102(作用：实现对冷媒进行模式分流，即将制冷或制热的冷媒，分流到对应内机中)—>室内换热器3(作用：蒸发器，蒸发吸热，降室内温度)—>转换单元102—>气液分离器9—>压缩机1的进口(压缩机1进行下次压缩循环)。
加压支路：当低温制冷或小负荷制热时，加压阀7开启，直接将压缩机1的出口的高温高压的气态冷媒，压入到储液件6中，为储液件6中的液态冷媒提供更大的流动动力，从而实现内机的质量流量的提升，最终提升低负荷时的能力。
储液件6流出的冷媒分为两路，一路流向过冷器5的第一支路51，另一路通过第一膨胀阀21进入过冷器5的第二支路52，继而进入第五管路15。
过冷器5的第二支路52的冷媒流向第五管路15，第一阀31关闭时，冷媒进入增焓管路101、经调节阀22进入压缩机1的喷焓口，用于为压缩机1增焓提效。
过冷器5的第二支路52的冷媒流向第五管路15，第一阀31打开，冷媒通过第一阀31进入气液分离器9，通过气液分离器9进入压缩机1的进口。
在制冷增焓模式下，由于内机进出的焓差不变，虽冷媒密度会因增焓管路的存在而略有降低，但因流入内机的冷媒流速增加而使质量流量略有增加或不变，且增焓系统也会形成过冷度的提升，同时，在同目标能力下，压缩机1可实现降频，使得系统功率降低幅度大幅提升，从而提升制冷能效。
如图3所示，空调系统完全制热模式同时增焓时的冷媒流向及作用。
主路：压缩机1的出口的高温高压气体冷媒—>油气分离器8—>第二控制阀10—>转换单元102—>室内换热器3(作用：冷凝器，冷凝放热，提高室内温度)—>转换单元102—>过冷器5—>储液件6—>第三膨胀阀23(状态：节流降压)—>室外换热器2(作用：蒸发吸热)—>第一控制阀4—>气液分离器9—>压缩机1的进口(压缩机1进行下次压缩循环)。
加压支路：当低温制冷或小负荷制热时，加压阀7开启，直接将压缩机1的出口的高温高压的气态冷媒，压入到储液件6中，为储液件6中的液态冷媒提供更大的流动动力，从而实现内机的质量流量的提升，最终提升低负荷时的能力。
储液件6流出的冷媒分为两路，一路流向过冷器5的第一支路51，另一路通过第一膨胀阀21进入过冷器5的第二支路52，继而进入第五管路15。
过冷器5的第二支路52的冷媒流向第五管路15，第一阀31关闭时，冷媒进入增焓管路101、经调节阀22进入压缩机1的喷焓口，用于为压缩机1增焓提效。
过冷器5的第二支路52的冷媒流向第五管路15，第一阀31打开，冷媒通过第一阀31进入气液分离器9，通过气液分离器9进入压缩机1的进口。
制热增焓模式下，结合过冷器5可以提高蒸发器入口和出口之间的焓差、并增大压缩机出口的冷媒流量和提高压缩过程的做功，从而使系统的制热量显著增加。
热回收模式同时增焓时的冷媒流向及作用：
主体制冷：
制冷内机流向：压缩机1—>第一控制阀4—>室外换热器2—>第三电子膨胀23—>储液件6—>过冷器5—>转换单元102—>用于制冷的室内换热器3—>转换单元 102—>第四阀34—>气液分离器9—>压缩机1。
制热内机流向：压缩机1—>第二控制阀10—>转换单元102—>用于制热的室内换热器3—>转换单元102(与来自液阀的冷媒混合)—>用于制冷的室内换热器3—>转换单元102—>第四阀34—>气液分离器9—>压缩机1。
加压支路：当低温制冷或小负荷制热时，加压阀7开启，直接将压缩机1的出口的高温高压的气态冷媒，压入到储液件6中，为储液件6中的液态冷媒提供更大的流动动力，从而实现内机的质量流量的提升，最终提升低负荷时的能力。
储液件6流出的冷媒分为两路，一路流向过冷器5的第一支路51，另一路通过第一膨胀阀21进入过冷器5的第二支路52，继而进入第五管路15。
过冷器5的第二支路52的冷媒流向第五管路15，第一阀31关闭时，冷媒进入增焓管路101、经调节阀22进入压缩机1的喷焓口，用于为压缩机1增焓提效。
过冷器5的第二支路52的冷媒流向第五管路15，第一阀31打开，冷媒通过第一阀31进入气液分离器9，通过气液分离器9进入压缩机1的进口。
如图4所示，主体制热：
制热内机流向：压缩机1—>第二控制阀10—>转换单元102—>用于制热的室内换热器3—>转换单元102—>过冷器5—>储液件6—>第三电子膨胀23—>室外换热器2—>第一控制阀4—>气液分离器9—>压缩机1。
制冷内机流向：来自用于制热的室内换热器3的冷媒—>转换单元102—>用于制冷的室内换热器3—>转换单元102—>第四阀34—>气液分离器9—>压缩机1。
加压支路：当低温制冷或小负荷制热时，加压阀7开启，直接将压缩机1的出口的高温高压的气态冷媒，压入到储液件6中，为储液件6中的液态冷媒提供更大的流动动力，从而实现内机的质量流量的提升，最终提升低负荷时的能力。
储液件6流出的冷媒分为两路，一路流向过冷器5的第一支路51，另一路通过第一膨胀阀21进入过冷器5的第二支路52，继而进入第五管路15。
过冷器5的第二支路52的冷媒流向第五管路15，第一阀31关闭时，冷媒进入增焓管路101、经调节阀22进入压缩机1的喷焓口，用于为压缩机1增焓提效。
过冷器5的第二支路52的冷媒流向第五管路15，第一阀31打开，冷媒通过第一阀31进入气液分离器9，通过气液分离器9进入压缩机1的进口。
通过上述各个实施例的描述，本公开提供的空调系统除可实现完全制冷模式和 完全制冷模式外，还有：
主体制冷模式：大部分内机可运行制冷模式，小部分内机可同时运行制热模式。
主体制热空调系统：大部分内机可运行制热模式，小部分内机可同时运行制冷模式。
完全热回收模式：制冷内机与制热内机数量基本相同，此时室外换热器不参与工作，此模式下，部分室内换热器作为冷凝器、部分室内换热器作为蒸发器，且换热能力保持相当，有益效果是直接利用不同室内房间的热量交换，即可满足同时制冷、制热的需求。
在完全热回收模式、主体制冷模式、主体制热模式，此三种模式下，系统可以利用不同室内房间的能量交换(如某房间以制冷为主、另外房间以制热为主，因此，系统可以从制冷房间吸热热量，通过压缩机的蒸气压缩，将低位热能提升到高位热能后，排送到制热房间的室内机中释放热量)，此过程中，由于能量交换主要来源于不同模式室内房间内，因此，可以大幅降低或无需要来自外界(室外或水源侧)的能量交换，从而降低能耗(如降低冷却塔(制冷时)或锅炉(制热时)(包含水泵))的开启或运行，因此，本公开实施例提供的空调系统可进一步降低全系统的能耗，提高节能性。
一些实施例还提供了一种上述的空调系统的控制方法，其包括：
在空调系统开始启动运行第一预设时间后，
在制冷模式时，如果压缩机1的进口的压力对应的饱和温度≥第一预设温度值T1；
在制热模式时，如果压缩机1的出口的压力对应的饱和温度≤第二预设温度值T2，T2>T1；
并且压缩机1的出口的实际排气温度与压缩机1的出口的压力对应的饱和温度的差值≥第三预设温度T3；
则打开调节阀22，增焓管路101连通，进入增焓模式。
在一些实施例中，第一预设温度值T1的取值范围为3℃～13℃。可选地，第一预设温度值T1为8℃。
在一些实施例中，第二预设温度值T2的取值范围为35℃～45℃。可选地，第二预设温度值T2为40℃。
在一些实施例中，第三预设温度T3的取值范围为15℃～25℃。可选地，第三预设温度T3为20℃。
在一些实施例中，第一预设时间的取值范围为0min～10min。可选地，第一预设时间为5min。
压缩机1的出口的压力通过压力检测元件检测获得。压缩机1的出口的压力对应的饱和温度通过查表获得。
压缩机1的进口的压力通过压力检测元件检测获得。压缩机1的进口的压力对应的饱和温度通过查表获得。
在一些实施例中，其中空调系统进入增焓模式后，执行以下动作：
压缩机1按照设定的目标温度所需的频率运行，
在制冷模式时，如果压缩机1的进口的压力对应的饱和温度低于设定的目标温度所需的压缩机1的进口的压力对应的饱和温度，则降低压缩机1频率，否则，升高压缩机1频率；
在制热模式时，如果压缩机1的出口的压力对应的饱和温度低于设定的目标温度所需的压缩机1的出口的压力对应的饱和温度，则升高压缩机1的频率，否则，降低压缩机1的频率。
在一些实施例中，其中空调系统还包括过冷器5、储液件6、第二管路12、第三管路13、第四管路14和第五管路15、第一膨胀阀21和第一阀31；储液件6设于室外换热器2与过冷器5之间的管路上；过冷器5包括第一支路51和第二支路52，第一支路51的第一端通过第二管路12连接于储液件6，第一支路51的第二端通过第三管路13连接于至少一个室内换热器3；第二支路52的第一端通过第四管路14连接于储液件6，第二支路52的第二端通过第五管路15连接于压缩机1的进口；第一膨胀阀21设于第四管路14；第一阀31设于第五管路15，第一阀31被配置控制第五管路15与压缩机1的进口之间的管路通断；增焓管路101的第一端连接于第五管路15，第一阀31相对于增焓管路101的第一端与第五管路15的连接处靠近压缩机1的进口；
空调系统进入增焓模式后，还执行以下动作：
如果过冷器5的第二支路52的出口与进口的实际温度差值≥设定的目标温度所需的过冷器5的第二支路52的出口与进口的目标温度差值，则开大第一膨胀阀21的 开度，否则，调小第一膨胀阀21的开度；
关闭第一阀31；
使调节阀22处于最大开度。
在一些实施例中，其中在满足下述条件至少之一时，空调系统退出增焓模式：
关机；
停机(包括到达目标温度后停机)；
进入增焓模式运行第二预设时间后，在制冷模式时，压缩机1的进口的压力对应的饱和温度≤第四预设温度T4；在制热模式时，压缩机1的出口的压力对应的饱和温度≥第五预设温度T5；其中，T5>T4；
进入增焓模式运行第二预设时间后，压缩机1的出口的实际排气温度与压缩机1的出口的压力对应的饱和温度的差值<第六预设温度T6。
在一些实施例中，第二预设时间的取值范围为5min～15min。可选地，第二预设时间为10min。
在一些实施例中，第四预设温度T4的取值范围为-10℃～0℃。可选地，第四预设温度T4为-5℃。
在一些实施例中，第五预设温度T5的取值范围为45℃～55℃。可选地，第五预设温度T5为50℃。
在一些实施例中，第六预设温度T6的取值范围为0℃～10℃。可选地，第六预设温度T6为5℃。
在一些实施例中，其中，空调系统退出增焓模式时执行以下动作：
压缩机1维持当前的频率运行；
如果过冷器5的第二支路52的出口与进口的实际温度差值>设定的目标温度所需的过冷器5的第二支路52的出口与进口的目标温度差值，则开大第一膨胀阀21的开度，否则，则调小第一膨胀阀21的开度；
开启第一阀31；
关闭调节阀22。
在一些实施例中，空调系统还包括储液件6、加压阀7和第一管路11，储液件6设于室外换热器2与至少一个室内换热器3之间的管路上，第一管路11的第一端连接于压缩机1的出口，第一管路11的第二端连接于储液件6，加压阀7设于第一管路 11。
在空调系统开始启动运行第一预设时间后，如果所需的制冷量或制热量的目标值与空调系统的制冷量或制热量的额定值的比值≤第一预设值A，且继续运行第三预设时间后，压缩机1的出口的压力对应的饱和温度≤第七预设温度值T7，压缩机1的出口的实际排气温度≥第八预设温度值T8，则开启加压阀7，其中，T8>T7。
在一些实施例中，第三预设时间的取值范围为0min～10min。可选地，第三预设时间为5min。
在一些实施例中，第一预设值A的取值范围为15％～25％。可选地，第一预设值A为20％。
在一些实施例中，第七预设温度值T7的取值范围为20℃～30℃。可选地，第七预设温度值T7为25℃。
在一些实施例中，第八预设温度值T8的取值范围为45℃～55℃。可选地，第八预设温度值T8为50℃。
在一些实施例中，在满足下述条件至少之一时，关闭加压阀7：
关机；
停机(包括到达目标温度后停机)；
开启加压阀7继续运行第二预设时间，压缩机1的出口的压力对应的饱和温度≥第九预设温度T9；
开启加压阀7继续运行第二预设时间，压缩机1的出口的实际排气温度与压缩机1的出口的压力对应的饱和温度的差值<第十预设温度T10；其中，T9>T10。
在一些实施例中，第九预设温度T9的取值范围为30℃～40℃。可选地，第九预设温度T9为35℃。
在一些实施例中，第十预设温度T10的取值范围为0℃～10℃。可选地，第十预设温度T10为5℃。
本公开实施例提供的空调系统具有提能效、减成本、降重量、高可靠性的有益效果。
基于上述本公开的各实施例，在没有明确否定或冲突的情况下，其中一个实施例的技术特征可以有益地与其他一个或多个实施例相互结合。
最后应当说明的是:以上实施例仅用以说明本公开的技术方案而非对其限制；尽 管参照较佳实施例对本公开进行了详细的说明，所属领域的普通技术人员应当理解：依然可以对本公开的具体实施方式进行修改或者对部分技术特征进行等同替换；而不脱离本公开技术方案的精神，其均应涵盖在本公开请求保护的技术方案范围当中。

Claims (23)

  1. 一种空调系统，包括：
    压缩机(1)；
    至少两个室内换热器(3)；
    室外换热器(2)；
    并联的第一流路和第二流路；其中所述第一流路流体连通所述压缩机(1)的出口、所述室外换热器(2)和至少一个室内换热器(3)；所述第二流路流体连通所述压缩机(1)的出口和至少一个室内换热器(3)；所述第一流路和所述第二流路被配置为择一工作或同时工作；
    增焓管路(101)，第一端连接于所述室外换热器(2)与至少一个室内换热器(3)之间的管路上，第二端连接于所述压缩机(1)的增焓口；以及
    调节阀(22)，设于所述增焓管路(101)，所述调节阀(22)被配置为调节所述增焓管路(101)的通断及流量。
  2. 如权利要求1所述的空调系统，还包括并联的第三流路和第四流路，所述第三流路流体连通至少一个室内换热器(3)和所述压缩机(1)的进口，所述第四流路流体连通至少一个室内换热器(3)、所述室外换热器(2)和所述压缩机(1)的进口，所述第三流路和所述第四流路被配置为择一工作或同时工作。
  3. 如权利要求1或2所述的空调系统，还包括转换单元(102)，在其中至少一个室内换热器(3)为室内冷凝器，其中至少一个室内换热器(3)为室内蒸发器的状态下，所述室内蒸发器的冷媒通过所述转换单元(102)流向所述室内冷凝器，或者所述室内冷凝器的冷媒通过所述转换单元(102)流向所述室内蒸发器。
  4. 如权利要求1至3任一项所述的空调系统，还包括储液件(6)、加压阀(7)和第一管路(11)，所述储液件(6)设于所述室外换热器(2)与至少一个室内换热器(3)之间的管路上，所述第一管路(11)的第一端连接于所述压缩机(1)的出口，所述第一管路(11)的第二端连接于所述储液件(6)，所述加压阀(7)设于所述第一管路(11)。
  5. 如权利要求1至4任一项所述的空调系统，还包括过冷器(5)，所述过冷器(5)设于所述室外换热器(2)与至少一个室内换热器(3)之间的管路上，所述增焓 管路(101)的第一端连接于所述过冷器(5)。
  6. 如权利要求5所述的空调系统，还包括储液件(6)、加压阀(7)和第一管路(11)，所述储液件(6)设于所述室外换热器(2)与所述过冷器(5)之间的管路上，所述第一管路(11)的第一端连接于所述压缩机(1)的出口，所述第一管路(11)的第二端连接于所述储液件(6)，所述加压阀(7)设于所述第一管路(11)。
  7. 如权利要求6所述的空调系统，还包括第二管路(12)、第三管路(13)、第四管路(14)和第五管路(15)，所述过冷器(5)包括第一支路(51)和第二支路(52)，所述第一支路(51)的第一端通过所述第二管路(12)连接于所述储液件(6)，所述第一支路(51)的第二端通过所述第三管路(13)连接于至少一个室内换热器(3)；所述第二支路(52)的第一端通过所述第四管路(14)连接于所述储液件(6)，所述第二支路(52)的第二端通过所述第五管路(15)连接于所述压缩机(1)的进口。
  8. 如权利要求7所述的空调系统，还包括第一膨胀阀(21)，所述第一膨胀阀(21)设于所述第四管路(14)。
  9. 如权利要求7或8所述的空调系统，还包括第一阀(31)，所述第一阀(31)设于所述第五管路(15)，所述第一阀(31)被配置控制所述第五管路(15)与所述压缩机(1)的进口之间的管路通断。
  10. 如权利要求9所述的空调系统，其中所述增焓管路(101)的第一端连接于所述第五管路(15)，所述第一阀(31)相对于所述增焓管路(101)的第一端与所述第五管路(15)的连接处靠近所述压缩机(1)的进口。
  11. 如权利要求1至10任一项所述的空调系统，还包括第一控制阀(4)，所述第一控制阀(4)包括第一状态和第二状态，所述第一控制阀(4)处于所述第一状态，所述第一流路连通，所述第一控制阀(4)处于所述第二状态，所述第一流路断开。
  12. 如权利要求11所述的空调系统，其中所述第一控制阀(4)包括第一接口、第二接口、第三接口和第四接口，所述第一接口连接于所述压缩机(1)的出口，所述第二接口连接于所述室外换热器(2)，所述第三接口和所述第四接口均连接于所述压缩机(1)的进口，所述第一控制阀(4)处于所述第一状态，所述第一接口与所述第二接口连通，所述第三接口与所述第四接口连通，所述第一控制阀(4)处于所述第二状态，所述第一接口与所述第三接口连通，所述第二接口与所述第四接口连通。
  13. 如权利要求1至12任一项所述的空调系统，还包括第二控制阀(10)，所述 第二控制阀(10)包括第三状态和第四状态，所述第二控制阀(10)处于所述第三状态，所述第二流路连通，所述第二控制阀(10)处于所述第四状态，所述第二流路断开。
  14. 如权利要求13所述的空调系统，其中所述第二控制阀(10)包括第五接口、第六接口、第七接口和第八接口，所述第五接口连接于所述压缩机(1)的出口，所述第六接口连接于至少一个室内换热器(3)，所述第七接口和所述第八接口均所述压缩机(1)的进口，所述第二控制阀(10)处于所述第三状态，所述第五接口与所述第六接口连通，所述第七接口与所述第八接口连通，所述第二控制阀(10)处于所述第四状态，所述第五接口与所述第七接口连通，所述第六接口与所述第八接口连通。
  15. 如权利要求1至14任一项所述的空调系统，其中所述室外换热器(2)包括水冷板式换热器。
  16. 如权利要求1至15任一项所述的空调系统，还包括转换单元(102)，所述第一流路流体连通所述压缩机(1)的出口和所述室外换热器(2)后，通过所述转换单元(102)流体连通至少一个室内换热器(3)；所述第二流路流体连通所述压缩机(1)的出口后，通过所述转换单元(102)流体连通至少一个室内换热器(3)。
  17. 一种如权利要求1至16任一项所述的空调系统的控制方法，其包括：
    在空调系统开始启动运行第一预设时间后，
    在制冷模式时，如果压缩机(1)的进口的压力对应的饱和温度≥第一预设温度值T1；
    在制热模式时，如果压缩机(1)的出口的压力对应的饱和温度≤第二预设温度值T2，T2>T1；
    并且压缩机(1)的出口的实际排气温度与压缩机(1)的出口的压力对应的饱和温度的差值≥第三预设温度T3；
    则打开调节阀(22)，增焓管路(101)连通，进入增焓模式。
  18. 如权利要求17所述的空调系统的控制方法，其中空调系统进入增焓模式后，执行以下动作：
    压缩机(1)按照设定的目标温度所需的频率运行，
    在制冷模式时，如果压缩机(1)的进口的压力对应的饱和温度低于设定的目标温度所需的压缩机(1)的进口的压力对应的饱和温度，则降低压缩机(1)频率，否 则，升高压缩机(1)频率；
    在制热模式时，如果压缩机(1)的出口的压力对应的饱和温度低于设定的目标温度所需的压缩机(1)的出口的压力对应的饱和温度，则升高压缩机(1)的频率，否则，降低压缩机(1)的频率。
  19. 如权利要求18所述的空调系统的控制方法，其中空调系统还包括过冷器(5)、储液件(6)、第二管路(12)、第三管路(13)、第四管路(14)和第五管路(15)、第一膨胀阀(21)和第一阀(31)；所述储液件(6)设于所述室外换热器(2)与过冷器(5)之间的管路上；所述过冷器(5)包括第一支路(51)和第二支路(52)，所述第一支路(51)的第一端通过所述第二管路(12)连接于所述储液件(6)，所述第一支路(51)的第二端通过所述第三管路(13)连接于至少一个室内换热器(3)；所述第二支路(52)的第一端通过所述第四管路(14)连接于所述储液件(6)，所述第二支路(52)的第二端通过所述第五管路(15)连接于所述压缩机(1)的进口；所述第一膨胀阀(21)设于所述第四管路(14)；所述第一阀(31)设于所述第五管路(15)，所述第一阀(31)被配置控制所述第五管路(15)与所述压缩机(1)的进口之间的管路通断；所述增焓管路(101)的第一端连接于所述第五管路(15)，所述第一阀(31)相对于所述增焓管路(101)的第一端与所述第五管路(15)的连接处靠近所述压缩机(1)的进口；
    空调系统进入增焓模式后，还执行以下动作：
    如果过冷器(5)的出口与进口的实际温度差值≥设定的目标温度所需的过冷器(5)的出口与进口的目标温度差值，则开大第一膨胀阀(21)的开度，否则，调小第一膨胀阀(21)的开度；
    关闭第一阀(31)；
    使调节阀(22)处于最大开度。
  20. 如权利要求19所述的空调系统的控制方法，其中，在满足下述条件至少之一时，空调系统退出增焓模式：
    关机；
    停机；
    进入增焓模式运行第二预设时间后，在制冷模式时，压缩机(1)的进口的压力对应的饱和温度≤第四预设温度T4；在制热模式时，压缩机(1)的出口的压力对应的 饱和温度≥第五预设温度T5；其中，T5>T4；
    进入增焓模式运行第二预设时间后，压缩机(1)的出口的实际排气温度与压缩机(1)的出口的压力对应的饱和温度的差值<第六预设温度T6。
  21. 如权利要求20所述的空调系统的控制方法，其中，空调系统退出增焓模式时执行以下动作：
    压缩机(1)维持当前的频率运行；
    如果过冷器(5)的出口与进口的实际温度差值>设定的目标温度所需的过冷器(5)的出口与进口的目标温度差值，则开大第一膨胀阀(21)的开度，否则，则调小第一膨胀阀(21)的开度；
    开启第一阀(31)；
    关闭调节阀(22)。
  22. 如权利要求17至21任一项所述的空调系统的控制方法，其中所述空调系统还包括储液件(6)、加压阀(7)和第一管路(11)，所述储液件(6)设于所述室外换热器(2)与至少一个室内换热器(3)之间的管路上，所述第一管路(11)的第一端连接于所述压缩机(1)的出口，第二端连接于所述储液件(6)，所述加压阀(7)设于所述第一管路(11)；
    在空调系统开始启动运行第一预设时间后，如果所需的制冷量或制热量的目标值与空调系统的制冷量或制热量的额定值的比值≤第一预设值A，且继续运行第三预设时间后，压缩机(1)的出口的压力对应的饱和温度≤第七预设温度值T7，压缩机(1)的出口的实际排气温度≥第八预设温度值T8，则开启加压阀(7)，其中，T8>T7。
  23. 如权利要求22所述的空调系统的控制方法，其中，
    在满足下述条件至少之一时，关闭加压阀(7)：
    关机；
    停机；
    开启加压阀(7)继续运行第二预设时间，压缩机(1)的出口的压力对应的饱和温度≥第九预设温度T9；
    开启加压阀(7)继续运行第二预设时间，压缩机(1)的出口的实际排气温度与压缩机(1)的出口的压力对应的饱和温度的差值<第十预设温度T10；其中，T9>T10。
PCT/CN2023/112858 2022-11-09 2023-08-14 空调系统及控制方法 WO2024098868A1 (zh)

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