WO2018082282A1 - 多联机系统及其除霜时的防回液控制方法 - Google Patents

多联机系统及其除霜时的防回液控制方法 Download PDF

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Publication number
WO2018082282A1
WO2018082282A1 PCT/CN2017/084224 CN2017084224W WO2018082282A1 WO 2018082282 A1 WO2018082282 A1 WO 2018082282A1 CN 2017084224 W CN2017084224 W CN 2017084224W WO 2018082282 A1 WO2018082282 A1 WO 2018082282A1
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Prior art keywords
threshold
heat exchange
temperature
less
pressure
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PCT/CN2017/084224
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English (en)
French (fr)
Inventor
汤昌靖
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广东美的暖通设备有限公司
美的集团股份有限公司
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Publication of WO2018082282A1 publication Critical patent/WO2018082282A1/zh
Priority to US16/121,643 priority Critical patent/US11131485B2/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—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
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the 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
    • 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
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the invention relates to the technical field of air conditioners, in particular to a liquid-repellent control method for a multi-line system defrosting and a multi-connection system.
  • Multi-line systems are commonly used in cooling and heating in the four seasons.
  • the system transfers heat from the outside to the indoor, the outdoor heat exchanger acts as an evaporator, and the indoor unit acts as a condenser.
  • the high-temperature exhaust gas condenses with the air on the indoor side, and transfers the heat to the indoor air. After the throttling device, it returns to the outdoor unit to exchange heat with the outdoor air and evaporates.
  • the outdoor unit ambient temperature is lower than the freezing point
  • the water vapor in the outdoor air will condense and frost on the surface of the evaporator.
  • the frosting of the evaporator increases the heat transfer resistance between the surface and the air, increases the flow resistance, reduces the air flow through the evaporator, and the heat exchange efficiency is significantly reduced, resulting in the heat exchange between the outdoor environment and the refrigerant. Decrease, the outlet air temperature decays.
  • the outdoor heat exchanger frosting is more serious, the evaporation effect of the refrigerant in the outdoor heat exchanger is gradually worse, more liquid refrigerant gradually returns to the low pressure gas-liquid separator, the system The working condition deteriorates, and when it is serious, the system returns to the liquid. Therefore, when the multi-line system is in heating operation, the conditions should be set to take defrosting measures at the right time.
  • the defrost mode often uses a four-way valve to switch the system to a cooling mode, converts the outdoor heat exchanger into a condenser, converts the indoor unit to an evaporator, and uses the high-temperature gaseous refrigerant of the compressor to frost the outdoor heat exchanger. Drop it.
  • the amount of multi-line refrigerant charging is large, and the outdoor unit and the indoor unit are usually far apart, the amount of additional refrigerant in the system is also large.
  • the outdoor heat exchanger frosts quickly, especially under some low temperature and high humidity and snow and ice, the evaporation effect of the outdoor heat exchanger becomes worse, the system
  • the refrigerant will gradually accumulate in the liquid storage tank of the compressor suction port, that is, the low-pressure gas-liquid separator, occupying most of the volume of the low-pressure gas-liquid separator, leading to the liquid level of the low-pressure gas-liquid separator before entering the defrosting. high.
  • the four-way valve switches for the first time, and the system is switched to the reverse circulation of refrigeration.
  • the liquid refrigerant in the indoor unit and the pipeline part may instantaneously return to the low-pressure gas-liquid separator of the compressor suction port, thereby causing the compressor to return liquid. . Therefore, the current multi-line system is difficult to perform defrosting control under the premise of ensuring safe and reliable operation of the system.
  • an object of the present invention is to provide a liquid-repellent control method for defrosting a multi-line system, which can avoid the risk of liquid return of the compressor during the defrosting process, and greatly improve the safety and reliability of the system.
  • a second object of the present invention is to propose a multi-line system.
  • the first aspect of the present invention provides a liquid-repellent control method for defrosting a multi-line system
  • the multi-line system includes an outdoor unit, a flow dividing device, and a plurality of indoor units
  • the flow dividing device includes a first heat exchange component, a second heat exchange component, an outlet of the first heat exchange flow path disposed at the second heat exchange component, and a second heat exchange flow path of the second heat exchange component a throttling element between the inlets, an outlet of the first heat exchange passage of the first heat exchange assembly is in communication with an inlet of the first heat exchange passage of the second heat exchange assembly, the first change An inlet of the second heat exchange passage of the heat assembly is in communication with an outlet of the second heat exchange passage of the second heat exchange assembly, and an outlet of the second heat exchange passage of the first heat exchange assembly is connected to the outlet
  • the outdoor unit includes a compressor and a four-way valve, and the method includes the following steps: detecting the exhaust pressure, return air pressure, and exhaust of
  • the anti-backflow control method for defrosting a multi-line system when a multi-line system heating operation is performed, if a defrosting command is received, the four-way valve can be forwarded for the first time through the closing section
  • the flow element reduces the amount of refrigerant returned to the outdoor unit for a period of time, and adjusts the opening degree of the throttle element according to the exhaust pressure, the return air pressure, and the exhaust temperature during the defrosting operation, thereby not only ensuring effective defrosting It can also avoid the risk of liquid return of the compressor during the defrost process, which greatly improves the safety and reliability of the system.
  • the anti-backflow control method for defrosting the multi-line system according to the above embodiment of the present invention may further have the following additional technical features:
  • adjusting the opening degree of the throttling element according to the exhaust pressure, the return air pressure, and the exhaust temperature during the defrosting operation of the multi-line system including: respectively respectively The air pressure, the return air pressure, and the exhaust gas temperature are judged; when the exhaust pressure is greater than or equal to a first high pressure threshold and less than a third high pressure threshold, or the return air pressure is less than a first low pressure threshold and greater than or equal
  • the flow dividing device controls the throttling element to increase the preset opening degree; when the exhaust pressure is less than the first When the high pressure threshold, the return air pressure is greater than or equal to the second low pressure threshold, and the exhaust gas temperature is less than the second temperature threshold, the flow dividing device controls the throttle element to decrease the preset opening degree, wherein the first opening The first high pressure threshold is greater than the second high voltage threshold and is less than the third high voltage threshold, the first low pressure threshold is
  • an electric control valve is further disposed between the outlet of the first heat exchange path of the second heat exchange component and the outlet of the second heat exchange path of the first heat exchange component, wherein The first valve is forwardly forwarded to control the electric control valve to be closed for the preset time, and in the multi-line system defrosting operation, if the exhaust pressure is greater than or equal to the first high pressure threshold
  • the shunt device control station is smaller than the third high pressure threshold, or the return air pressure is less than the first low pressure threshold and greater than or equal to the third low pressure threshold, or the exhaust gas temperature is greater than or equal to the first temperature threshold and less than the third temperature threshold
  • the electric control valve remains in a closed state; if the exhaust pressure is less than a second high pressure threshold, the return air pressure is greater than or equal to a second low pressure threshold, and the exhaust gas temperature is less than a second temperature threshold, the flow dividing device continues to control the The electric control valve remains in a closed state; if the exhaust pressure is greater than or equal to the third high pressure threshold, or
  • the throttling element is an electronic expansion valve
  • the electrically controlled valve is a solenoid valve
  • the multi-line system operates in a main heating mode or a pure heating mode when the multi-line system is operating in heating.
  • the present invention also proposes a non-transitory computer readable storage medium having stored thereon a computer program which, when executed by a processor, implements the above-described anti-backflow control method.
  • a second aspect of the present invention provides a multi-line system including: a plurality of indoor units; an outdoor unit, the outdoor unit including a compressor and a four-way valve; and a shunt device, the shunt
  • the device includes a first heat exchange component, a second heat exchange component, an outlet of the first heat exchange flow path disposed at the second heat exchange component, and an inlet of the second heat exchange flow path of the second heat exchange component
  • An intermediate throttling element an outlet of the first heat exchange path of the first heat exchange component is in communication with an inlet of the first heat exchange flow path of the second heat exchange component, the first heat exchange component
  • An inlet of the second heat exchange passage is in communication with an outlet of the second heat exchange passage of the second heat exchange unit, and an outlet of the second heat exchange passage of the first heat exchange unit is connected to the outdoor unit a detecting module, configured to detect an exhaust pressure, a return air pressure, and an exhaust temperature of the compressor in real time during heating operation of the multi-line system, wherein the
  • the flow dividing device when the outdoor unit receives the defrosting command during the heating operation, the flow dividing device can be reversed for the first time in the four-way valve by closing the throttle element for a period of time.
  • the amount of refrigerant in the outdoor unit, and the opening of the throttle element is adjusted according to the exhaust pressure, the return air pressure, and the exhaust temperature during the defrosting operation, thereby not only ensuring effective defrosting but also avoiding the defrosting process.
  • the medium compressor has a risk of liquid return, which greatly improves the safety and reliability of the system.
  • multi-line system proposed according to the above embodiment of the present invention may further have the following additional technical features:
  • the flow dividing device is configured to respectively determine the exhaust pressure, the return air pressure, and the exhaust gas temperature, wherein when the exhaust pressure is greater than or equal to a first high pressure threshold and less than a third high voltage
  • the flow dividing device controls the throttling when the threshold, or the return air pressure is less than the first low pressure threshold and greater than or equal to the third low pressure threshold, or the exhaust gas temperature is greater than or equal to the first temperature threshold and less than the third temperature threshold
  • the component increases a preset opening degree; when the exhaust pressure is less than a second high pressure threshold, the return air pressure is greater than or equal to a second low pressure threshold, and the exhaust gas temperature is less than a second temperature threshold, the shunt device control station
  • the throttling element reduces a preset opening degree, wherein the first high pressure threshold is greater than the second high threshold and less than the third high threshold, the first low threshold is greater than the third low threshold and less than a second low threshold, the first temperature threshold being greater than the second temperature threshold and less than the third
  • an electric control valve is further disposed between the outlet of the first heat exchange path of the second heat exchange component and the outlet of the second heat exchange path of the first heat exchange component, wherein The first valve is forwardly forwarded to control the electric control valve to be closed for the preset time, and in the multi-line system defrosting operation, if the exhaust pressure is greater than or equal to the first high pressure threshold
  • the shunt device control station is smaller than the third high pressure threshold, or the return air pressure is less than the first low pressure threshold and greater than or equal to the third low pressure threshold, or the exhaust gas temperature is greater than or equal to the first temperature threshold and less than the third temperature threshold
  • the electric control valve remains in a closed state; if the exhaust pressure is less than a second high pressure threshold, the return air pressure is greater than or equal to a second low pressure threshold, and the exhaust gas temperature is less than a second temperature threshold, the flow dividing device continues to control the The electric control valve remains in a closed state; if the exhaust pressure is greater than or equal to the third high pressure threshold, or
  • the throttling element is an electronic expansion valve
  • the electrically controlled valve is a solenoid valve
  • the multi-line system operates in a main heating mode or a pure heating mode when the multi-line system is operating in heating.
  • FIG. 1 is a flow chart of a method for controlling back liquid prevention during defrosting of a multi-line system according to an embodiment of the present invention
  • FIG. 2 is a block diagram showing the structure of a multi-line system according to an embodiment of the present invention.
  • FIG. 1 is a flow chart of a liquid back control method in a multi-line system defrosting according to an embodiment of the present invention.
  • the multi-line system of the embodiment of the present invention may include an outdoor unit, a flow dividing device, and a plurality of indoor units, wherein the flow dividing device includes a first heat exchange component, a second heat exchange component, and a second heat exchange device.
  • a throttling element EXV2 between an outlet of the first heat exchange passage of the assembly and an inlet of the second heat exchange passage of the second heat exchange assembly, an outlet of the first heat exchange passage of the first heat exchange assembly, and a second
  • the inlet of the first heat exchange flow path of the heat exchange component is in communication
  • the inlet of the second heat exchange flow path of the first heat exchange component is in communication with the outlet of the second heat exchange flow path of the second heat exchange component, the first change
  • the outlet of the second heat exchange passage of the heat assembly is connected to the outdoor unit, and the outdoor unit includes a compressor and a four-way valve.
  • the throttle element EXV2 can be an electronic expansion valve.
  • the anti-backflow control method for defrosting a multi-line system may include the following steps:
  • the outdoor unit receives the defrosting command, sends a defrosting signal to the shunt device and the heating indoor unit in the plurality of indoor units, and controls the throttle element to be closed by the shunt device for the first time in the four-way valve. And the preset time is continued to reduce the amount of refrigerant returning to the outdoor unit, and the opening of the throttle element is adjusted according to the exhaust pressure, the return air pressure, and the exhaust temperature during the defrosting operation of the multi-line system.
  • the multi-line system operates in a primary heating mode or a pure heating mode when the multi-line system is heating.
  • the multi-line system includes four indoor units, and the working in the pure heating mode is taken as an example.
  • the first port a and the fourth port d of the four-way valve In communication the second port b and the third port c are in communication.
  • the high-temperature and high-pressure gaseous refrigerant at the compressor outlet enters the high-pressure gas-liquid separator of the flow dividing device through the oil separator, the four-way valve and the check valve F10, and then enters the indoor unit through the heating electromagnetic valve SVH1-SVH4 for heating.
  • the liquid refrigerant at the outlet of the indoor unit flows through the second heat exchange unit, the throttle element EXV2 and the first heat exchange unit via the check valves RV1-RV4, and then evaporates through the one-way valve F9 into the outdoor heat exchanger of the outdoor unit. After being evaporated by the outdoor heat exchanger, the refrigerant can enter the low-pressure gas-liquid separator of the outdoor unit through the check valve F5 and the four-way valve to return to the compressor.
  • the refrigerant flow path in the multi-line system is equivalent to the refrigerant flow path during the cooling operation.
  • the four-way valve performs the first commutation, the first port a and the second port b are in communication, and the fourth port d and the third port c are in communication.
  • the high-temperature and high-pressure gaseous refrigerant at the compressor outlet passes through the oil separator and the four-way valve and directly enters the outdoor heat exchanger through the check valve F1 to melt the frost covered by the outdoor heat exchanger.
  • the refrigerant enters the high-pressure gas-liquid separator of the flow dividing device via the one-way valve F6, and then enters the indoor unit through the first heat exchange component, the other throttling element EXV1, the second heat exchange component, and the check valve RV5-RV8. , and then through the refrigeration solenoid valve SVC1-SVC4 Go back to the outdoor unit. A part of the refrigerant is returned to the outdoor unit via the throttle element EXV2. Among them, in the outdoor unit, the refrigerant can enter the low-pressure gas-liquid separator through the check valve F8 and the four-way valve to return to the compressor.
  • the forward control throttle element EXV2 can be turned off for the first time in the four-way valve for a preset time, thereby reducing the amount of refrigerant entering the low-pressure gas-liquid separator of the outdoor unit to prevent Excessive refrigerant in the low pressure gas-liquid separator is returned to the compressor, causing the compressor fluid to compress.
  • the exhaust pressure PC, the return air pressure PE, and the exhaust gas temperature TP can be separately judged.
  • the flow dividing device controls the throttle element EXV2 to increase the preset opening degree.
  • the flow dividing device controls the throttle element EXV2 to decrease the preset opening degree.
  • the flow dividing device controls the throttle element EXV2 to open to the preset The maximum opening.
  • the first high-pressure threshold A1 is greater than the second high-voltage threshold A2 and smaller than the third high-pressure threshold A3.
  • the first low-pressure threshold B1 is greater than the third low-pressure threshold B3 and smaller than the second low-pressure threshold B2, and the first temperature threshold C1 is greater than the second temperature threshold.
  • C2 is less than the third temperature threshold C3. According to this, the opening degree of the throttle element EXV2 is adjusted until the defrosting is completed.
  • A1-A3, B1-B3, and C1-C3 can be set according to specific implementation conditions such as the amount of refrigerant in the multi-line system, the performance of the compressor, and the specifications of the low-pressure gas-liquid separator.
  • the opening degree of the throttle element EXV2 can be continuously adjusted according to the exhaust pressure, the return air pressure, and the exhaust gas temperature until the defrosting is completed.
  • the throttle element EXV2 By controlling the throttle element EXV2 to reduce the opening degree, it is possible to prevent the refrigerant from being excessively supplied and the compressor from returning to the liquid.
  • the throttle element EXV2 By controlling the throttle element EXV2 to increase the opening degree, it is possible to prevent the refrigerant from being excessively small, and the compressor lacking the refrigerant. It also increases the speed of defrosting.
  • an electric power may be further disposed between an outlet of the first heat exchange path of the second heat exchange component and an exit of the second heat exchange path of the first heat exchange component.
  • Control valve SVM can be a solenoid valve.
  • the liquid refrigerant at the outlet of the indoor unit can also flow through the second heat exchange component and the electric control valve SVM through the check valves RV1-RV4, and then enter the outdoor heat exchanger of the outdoor unit through the check valve F9.
  • a part of the refrigerant can also be returned to the outdoor unit via the electric control valve SVM. Therefore, the refrigerant flow rate can also be controlled by controlling the electric control valve SVM.
  • the electric control valve SVM can be controlled to be turned off for the first time in the four-way valve for a preset time, and in the multi-line system defrosting operation, if the exhaust pressure PC is greater than or equal to the first high voltage threshold A1 and less than the third high pressure threshold A3, or the return air pressure PE is less than the first low pressure threshold B1 and greater than or equal to the third low pressure threshold B3, or the exhaust gas temperature TP is greater than or equal to the first temperature threshold C1 and less than the third temperature threshold C3, shunt The device controls the electronically controlled valve SVM to remain off.
  • the flow dividing device continues to control the electronically controlled valve SVM to remain in the closed state. If the exhaust pressure PC is greater than or equal to the third high pressure threshold A3, or the return air pressure PE is less than the third low pressure threshold B3, or the exhaust gas temperature TP is greater than or equal to the third temperature threshold C3, the flow dividing device controls the electronically controlled valve SVM to open.
  • the throttle element EXV2 and the electric control valve SVM can be simultaneously controlled according to the above-described judgment results of the exhaust pressure, the return air pressure, and the exhaust gas temperature.
  • To control the amount of refrigerant in the low-pressure gas-liquid separator by controlling the flow rate of the refrigerant to prevent it from being excessive or too small.
  • the present invention also proposes a non-transitory computer readable storage medium having stored thereon a computer program which, when executed by a processor, implements the above-described anti-backflow control method.
  • the anti-backflow control method for defrosting a multi-line system when a multi-line system heating operation is performed, if a defrosting command is received, the four-way valve can be forwarded for the first time through the closing section
  • the flow element reduces the amount of refrigerant returned to the outdoor unit for a period of time, and adjusts the opening degree of the throttle element according to the exhaust pressure, the return air pressure, and the exhaust temperature during the defrosting operation, thereby not only ensuring effective defrosting It can also avoid the risk of liquid return of the compressor during the defrost process, which greatly improves the safety and reliability of the system.
  • the present invention also proposes a multi-connection system.
  • the multi-connection system of the embodiment of the present invention includes a plurality of indoor units 10, an outdoor unit 20, and a flow dividing device 30.
  • the outdoor unit 20 includes a compressor 21 and a four-way valve 22.
  • the flow dividing device 30 includes a first heat exchange component 31, a second heat exchange component 32, an outlet of the first heat exchange flow path disposed at the second heat exchange component 32, and a second heat exchange flow path of the second heat exchange component 32.
  • the throttle element EXV2 between the inlets, the outlet of the first heat exchange passage of the first heat exchange unit 31 is in communication with the inlet of the first heat exchange passage of the second heat exchange unit 32, and the first heat exchange unit 31
  • the inlet of the second heat exchange passage is in communication with the outlet of the second heat exchange passage of the second heat exchange unit 32, and the outlet of the second heat exchange passage of the first heat exchange unit 31 is communicated to the outdoor unit 20.
  • the throttle element EXV2 can be an electronic expansion valve.
  • the multi-line system of the embodiment of the present invention may further include a detecting module (not shown in FIG. 2), and the detecting module is configured to detect the exhaust pressure, the return air pressure and the exhaust of the compressor 21 in real time during the heating operation of the multi-line system. Gas temperature.
  • the outdoor unit 20 when receiving the defrosting command, transmits a defrosting signal to the shunting device 30 and the heating indoor units of the plurality of indoor units 10, and the shunting device 30 is first at the four-way valve 22
  • the secondary forward control throttle element EXV2 is turned off for a preset time to reduce the amount of refrigerant returned to the outdoor unit 20, and is rooted in the multi-line system defrosting operation.
  • the opening degree of the throttle element EXV2 is adjusted in accordance with the exhaust pressure, the return air pressure, and the exhaust gas temperature.
  • the indoor unit 10, the outdoor unit 20, and the flow dividing device 30 may respectively have separate controllers for information interaction and system control, and the indoor unit may be unified by the integrated controller. 10.
  • the outdoor unit 20 and the flow dividing device 30 perform control.
  • the multi-line system operates in a primary heating mode or a pure heating mode when the multi-line system is heating.
  • the multi-line system includes four indoor units 10, which are operated in a pure heating mode.
  • the first port a of the four-way valve 22 and The fourth port d is in communication
  • the second port b and the third port c are in communication.
  • the high-temperature high-pressure gaseous refrigerant at the outlet of the compressor 21 enters the high-pressure gas-liquid separator 33 of the flow dividing device 30 through the oil separator 23, the four-way valve 22, and the check valve F10, and then enters the indoor unit 10 through the heating electromagnetic valves SVH1-SVH4. Heating.
  • the liquid refrigerant at the outlet of the indoor unit 10 flows through the second heat exchange unit 32, the throttle element EXV2 and the first heat exchange unit 31 via the check valves RV1-RV4, and then enters the outdoor heat exchange of the outdoor unit 20 via the check valve F9.
  • the device 24 evaporates. After being evaporated by the outdoor heat exchanger 24, the refrigerant can enter the low-pressure gas-liquid separator 25 of the outdoor unit 20 through the check valve F5 and the four-way valve 22 to return to the compressor 21.
  • the refrigerant flow path in the multi-line system is equivalent to the refrigerant flow path during the cooling operation.
  • the four-way valve 22 performs the first commutation, the first port a and the second port b are in communication, and the fourth port d and the third port c are in communication.
  • the high-temperature high-pressure gaseous refrigerant at the outlet of the compressor 21 passes through the oil separator 23 and the four-way valve 22 and directly enters the outdoor heat exchanger 24 via the check valve F1 to melt the frost covered on the outdoor heat exchanger 24.
  • the refrigerant enters the high-pressure gas-liquid separator 33 of the flow dividing device 30 via the one-way valve F6, and sequentially passes through the first heat exchange component 31, the other throttle element EXV1, the second heat exchange component 32, and the check valve RV5-RV8.
  • the indoor unit 10 is entered, and then returned to the outdoor unit 20 via the cooling solenoid valves SVC1-SVC4.
  • a part of the refrigerant is returned to the outdoor unit 20 via the throttle element EXV2.
  • the refrigerant can enter the low-pressure gas-liquid separator 25 via the check valve F8 and the four-way valve to return to the compressor 21.
  • the flow dividing device 30 can be turned off for the first time in the four-way valve 22 to control the throttle element EXV2 for a preset time, thereby reducing the low-pressure gas-liquid separator entering the outdoor unit 20.
  • the amount of refrigerant of 25 is to prevent excess refrigerant in the low-pressure gas-liquid separator 25 from being returned to the compressor 21, resulting in compressor 21 liquid compression.
  • the flow dividing device 30 can determine the exhaust pressure PC, the return air pressure PE, and the exhaust gas temperature TP, respectively.
  • the exhaust pressure PC is greater than or equal to the first high pressure threshold A1 and less than the third high pressure threshold A3, or the return air pressure PE is less than the first low pressure threshold B1 and greater than or equal to the third low pressure threshold B3, or the exhaust temperature TP is greater than or equal to the first temperature
  • the flow dividing device 30 controls the throttle element EXV2 to increase the preset opening degree.
  • the flow dividing device 30 controls the throttle element EXV2 to decrease the preset opening degree.
  • the flow dividing device 30 controls the throttle element EXV2 to open to the pre Set the maximum opening.
  • the first high-pressure threshold A1 is greater than the second high-voltage threshold A2 and smaller than the third high-pressure threshold A3.
  • the first low-pressure threshold B1 is greater than the third low-pressure threshold B3 and smaller than the second low-pressure threshold B2, and the first temperature threshold C1 is greater than the second temperature threshold. C2 is less than the third temperature threshold C3. According to this, the opening degree of the throttle element EXV2 is adjusted until the defrosting is completed.
  • A1-A3, B1-B3, and C1-C3 can be set according to specific implementation conditions such as the amount of refrigerant in the multi-line system, the performance of the compressor 21, and the specifications of the low-pressure gas-liquid separator 25.
  • the flow dividing device 30 can continuously adjust the opening degree of the throttle element EXV2 according to the exhaust pressure, the return air pressure, and the exhaust gas temperature until the defrosting is completed.
  • the throttle element EXV2 By controlling the throttle element EXV2 to reduce the opening degree, it is possible to prevent the refrigerant from being excessively supplied, and the compressor 21 is returned to the liquid.
  • the throttle element EXV2 is controlled to increase the opening degree, it is possible to prevent the refrigerant from being excessively small and the compressor 21 lacking the refrigerant. Occurs, it can also increase the speed of defrosting.
  • an electrically controlled valve SVM can also be provided between the outlet of the first heat exchange passage of the second heat exchange unit 32 and the outlet of the second heat exchange passage of the first heat exchange unit 31.
  • the electric control valve SVM can be a solenoid valve.
  • the liquid refrigerant at the outlet of the indoor unit 10 can also flow through the second heat exchange unit 32 and the electric control valve SVM through the check valves RV1-RV4, and then enter the outdoor unit 20 through the check valve F9. Heater.
  • a portion of the refrigerant may also be returned to the outdoor unit 20 via the electronically controlled valve SVM. Therefore, the refrigerant flow rate can also be controlled by controlling the electric control valve SVM.
  • the first change of the forward diverting device 30 at the four-way valve 22 can also control the electronically controlled valve SVM to be turned off for a preset time, and during the defrosting operation of the multi-line system, If the exhaust pressure PC is greater than or equal to the first high pressure threshold A1 and less than the third high pressure threshold A3, or the return air pressure PE is less than the first low pressure threshold B1 and greater than or equal to the third low pressure threshold B3, or the exhaust temperature TP is greater than or equal to the first temperature The threshold C1 is less than the third temperature threshold C3, and the flow dividing device 30 controls the electronically controlled valve SVM to remain in the closed state.
  • the flow dividing device 30 continues to control the electronically controlled valve SVM to remain in the closed state. If the exhaust pressure PC is greater than or equal to the third high pressure threshold A3, or the return air pressure PE is less than the third low pressure threshold B3, or the exhaust gas temperature TP is greater than or equal to the third temperature threshold C3, the flow dividing device 30 controls the electronically controlled valve SVM to open.
  • the throttle element EXV2 and the electric control valve SVM can be simultaneously controlled according to the above-described judgment results of the exhaust pressure, the return air pressure, and the exhaust gas temperature.
  • To control the amount of refrigerant in the low-pressure gas-liquid separator by controlling the flow rate of the refrigerant to prevent it from being excessive or too small.
  • the flow dividing device when the outdoor unit receives the defrosting command during the heating operation, the flow dividing device can be reversed for the first time in the four-way valve by closing the throttle element for a period of time.
  • the amount of refrigerant in the outdoor unit, In the defrosting operation, the opening of the throttle element is adjusted according to the exhaust pressure, the return air pressure and the exhaust gas temperature, thereby not only ensuring the effective defrosting, but also avoiding the return of the compressor during the defrosting process. The risk greatly improves the safety and reliability of the system.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” and “second” may include one or more of the features either explicitly or implicitly.
  • the meaning of "a plurality” is two or more unless specifically and specifically defined otherwise.
  • the terms “installation”, “connected”, “connected”, “fixed” and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. , or integrated; can be mechanical connection, or can be electrical connection; can be directly connected, or can be indirectly connected through an intermediate medium, can be the internal communication of two elements or the interaction of two elements.
  • installation can be understood on a case-by-case basis.
  • the first feature "on” or “under” the second feature may be a direct contact of the first and second features, or the first and second features may be indirectly through an intermediate medium, unless otherwise explicitly stated and defined. contact.
  • the first feature "above”, “above” and “above” the second feature may be that the first feature is directly above or above the second feature, or merely that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature may be that the first feature is directly below or obliquely below the second feature, or merely that the first feature level is less than the second feature.

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Abstract

多联机系统及其除霜时的防回液控制方法，其中，所述方法包括以下步骤：当多联机系统制热运行时，实时检测压缩机（21）的排气压力（PC）、回气压力（PE）和排气温度（TP）；如果室外机（20）接收到化霜指令，则向分流装置（30）和多个室内机（10）中的制热室内机发送除霜信号，并在四通阀（22）第一次换向前通过分流装置（30）控制节流元件（EXV2）关闭且持续预设时间以降低回到室外机（20）的冷媒量，以及在多联机系统除霜运行时根据排气压力（PC）、回气压力（PE）和排气温度（TP）对节流元件（EXV2）的开度进行调节，以此避免除霜过程中压缩机（21）出现回液风险，大大提高系统的安全可靠性。

Description

多联机系统及其除霜时的防回液控制方法 技术领域
本发明涉及空调技术领域，特别涉及一种多联机系统除霜时的防回液控制方法和一种多联机系统。
背景技术
多联机系统普遍使用于四季中的制冷制热，当多联机系统制热运行时，系统将热量从室外转移到室内，室外换热器当作蒸发器，室内机当作冷凝器，利用压缩机高温排气在室内侧与空气换热冷凝，将热量传送给室内空气，经节流装置后回到室外机与室外空气换热后蒸发。
当室外机环境温度低于冰点时，室外空气中的水蒸汽将在蒸发器表面凝结并结霜。蒸发器的结霜加大了表面与空气间的传热热阻，增加了流动阻力，使得通过蒸发器的空气流量减少，换热效率明显降低，导致室外环境和制冷剂之间的换热量下降，出风温度衰减。特别是在一些低温高湿度工况下，室外换热器结霜较为严重，冷媒在室外换热器中的蒸发效果逐渐变差，更多的液态冷媒逐渐回到低压气液分离器中，系统工作状况恶化，严重时导致系统回液。因此，多联机系统在制热运行时，应设置条件适时采取除霜措施。
目前除霜模式常采用四通阀换向将系统切换为制冷模式，将室外换热器转换为冷凝器，室内机转换为蒸发器，利用压缩机的高温气态冷媒将室外换热器的霜化掉。然而，由于多联机冷媒充注量较大，且室外机与室内机通常距离很远，导致系统追加冷媒量也较大。在制热模式和主制热模式下，当外侧工况较为恶劣时，室外换热器结霜很快，特别是一些低温高湿度及冰雪覆盖下，室外换热器的蒸发效果变差，系统的冷媒会逐渐地积存至压缩机吸气口的储液罐即低压气液分离器中，占据低压气液分离器大部分容积，导致进入化霜前，低压气液分离器的液位已经较高。四通阀第一次切换，将系统转为制冷逆向循环，室内机和管路部分的液态冷媒可能瞬间回到压缩机吸气口的低压气液分离器内，从而导致压缩机出现回液风险。因此，目前的多联机系统难以在保证系统安全可靠运行的前提下进行除霜控制。
发明内容
本发明旨在至少在一定程度上解决上述技术中的技术问题之一。为此，本发明的一个目的在于提出一种多联机系统除霜时的防回液控制方法，能够避免除霜过程中压缩机出现回液风险，大大提高了系统的安全可靠性。
本发明的第二个目的在于提出一种多联机系统。
为达到上述目的，本发明第一方面实施例提出了一种多联机系统除霜时的防回液控制方法，其中，所述多联机系统包括室外机、分流装置和多个室内机，其中，所述分流装置包括第一换热组件、第二换热组件、设置在所述第二换热组件的第一换热流路的出口与所述第二换热组件的第二换热流路的入口之间的节流元件，所述第一换热组件的第一换热流路的出口与所述第二换热组件的第一换热流路的入口相连通，所述第一换热组件的第二换热流路的入口与所述第二换热组件的第二换热流路的出口相连通，所述第一换热组件的第二换热流路的出口连通到所述室外机，所述室外机包括压缩机和四通阀，所述方法包括以下步骤：当所述多联机系统制热运行时，实时检测所述压缩机的排气压力、回气压力和排气温度；如果所述室外机接收到化霜指令，则向所述分流装置和所述多个室内机中的制热室内机发送除霜信号，并在所述四通阀第一次换向前通过所述分流装置控制所述节流元件关闭且持续预设时间以降低回到所述室外机的冷媒量，以及在所述多联机系统除霜运行时根据所述排气压力、所述回气压力和所述排气温度对所述节流元件的开度进行调节。
根据本发明实施例的多联机系统除霜时的防回液控制方法，在多联机系统制热运行时，如果接收到化霜指令，则可在四通阀第一次换向前通过关闭节流元件一段时间来降低回到室外机的冷媒量，并在除霜运行时根据排气压力、回气压力和排气温度对节流元件的开度进行调节，从而不仅能够保证除霜的有效进行，还能够避免除霜过程中压缩机出现回液风险，大大提高了系统的安全可靠性。
另外，根据本发明上述实施例提出的多联机系统除霜时的防回液控制方法还可以具有如下附加的技术特征：
具体地，在所述多联机系统除霜运行时根据所述排气压力、所述回气压力和所述排气温度对所述节流元件的开度进行调节，包括：分别对所述排气压力、所述回气压力和所述排气温度进行判断；当所述排气压力大于等于第一高压阈值且小于第三高压阈值、或者所述回气压力小于第一低压阈值且大于等于第三低压阈值、或者所述排气温度大于等于第一温度阈值且小于第三温度阈值时，所述分流装置控制所述节流元件增大预设开度；当所述排气压力小于第二高压阈值、所述回气压力大于等于第二低压阈值且所述排气温度小于第二温度阈值时，所述分流装置控制所述节流元件减小预设开度，其中，所述第一高压阈值大于所述第二高压阈值且小于所述第三高压阈值，所述第一低压阈值大于所述第三低压阈值且小于第二低压阈值，所述第一温度阈值大于所述第二温度阈值且小于所述第三温度阈值；当所述排气压力大于等于所述第三高压阈值、或者所述回气压力小于所述第三低压阈值、或者所述排气温度大于等于所述第三温度阈值时，所述分流装置控制所述节流元件打开至预设的最大开度。
进一步地，所述第二换热组件的第一换热流路的出口与所述第一换热组件的第二换热流路的出口之间还设置电控阀，其中，在所述四通阀第一次换向前所述分流装置控制所述电控阀关闭且持续所述预设时间，并在多联机系统除霜运行时，如果所述排气压力大于等于第一高压阈值且小于第三高压阈值、或者所述回气压力小于第一低压阈值且大于等于第三低压阈值、或者所述排气温度大于等于第一温度阈值且小于第三温度阈值，所述分流装置控制所述电控阀保持关闭状态；如果所述排气压力小于第二高压阈值、所述回气压力大于等于第二低压阈值且所述排气温度小于第二温度阈值，所述分流装置继续控制所述电控阀保持关闭状态；如果所述排气压力大于等于所述第三高压阈值、或者所述回气压力小于所述第三低压阈值、或者所述排气温度大于等于所述第三温度阈值，所述分流装置则控制所述电控阀打开。
根据本发明的一个实施例，所述节流元件为电子膨胀阀，所述电控阀为电磁阀。
根据本发明的一个实施例，当所述多联机系统制热运行时，所述多联机系统以主制热模式或纯制热模式进行工作。
此外，本发明还提出了一种非临时性计算机可读存储介质，其上存储有计算机程序，该程序被处理器执行时实现上述的防回液控制方法。
为达到上述目的，本发明第二方面实施例提出了一种多联机系统，该系统包括：多个室内机；室外机，所述室外机包括压缩机和四通阀；分流装置，所述分流装置包括第一换热组件、第二换热组件、设置在所述第二换热组件的第一换热流路的出口与所述第二换热组件的第二换热流路的入口之间的节流元件，所述第一换热组件的第一换热流路的出口与所述第二换热组件的第一换热流路的入口相连通，所述第一换热组件的第二换热流路的入口与所述第二换热组件的第二换热流路的出口相连通，所述第一换热组件的第二换热流路的出口连通到所述室外机；检测模块，所述检测模块用于在所述多联机系统制热运行时，实时检测所述压缩机的排气压力、回气压力和排气温度，其中，所述室外机在接收到化霜指令时，向所述分流装置和所述多个室内机中的制热室内机发送除霜信号，所述分流装置在所述四通阀第一次换向前控制所述节流元件关闭且持续预设时间以降低回到所述室外机的冷媒量，并在所述多联机系统除霜运行时根据所述排气压力、所述回气压力和所述排气温度对所述节流元件的开度进行调节。
根据本发明实施例的多联机系统，在制热运行时，如果室外机接收到化霜指令，则分流装置可在四通阀第一次换向前通过关闭节流元件一段时间来降低回到室外机的冷媒量，并在除霜运行时根据排气压力、回气压力和排气温度对节流元件的开度进行调节，从而不仅能够保证除霜的有效进行，还能够避免除霜过程中压缩机出现回液风险，大大提高了系统的安全可靠性。
另外，根据本发明上述实施例提出的多联机系统还可以具有如下附加的技术特征：
具体地，所述分流装置用于分别对所述排气压力、所述回气压力和所述排气温度进行判断，其中，当所述排气压力大于等于第一高压阈值且小于第三高压阈值、或者所述回气压力小于第一低压阈值且大于等于第三低压阈值、或者所述排气温度大于等于第一温度阈值且小于第三温度阈值时，所述分流装置控制所述节流元件增大预设开度；当所述排气压力小于第二高压阈值、所述回气压力大于等于第二低压阈值且所述排气温度小于第二温度阈值时，所述分流装置控制所述节流元件减小预设开度，其中，所述第一高压阈值大于所述第二高压阈值且小于所述第三高压阈值，所述第一低压阈值大于所述第三低压阈值且小于第二低压阈值，所述第一温度阈值大于所述第二温度阈值且小于所述第三温度阈值；当所述排气压力大于等于所述第三高压阈值、或者所述回气压力小于所述第三低压阈值、或者所述排气温度大于等于所述第三温度阈值时，所述分流装置控制所述节流元件打开至预设的最大开度。
进一步地，所述第二换热组件的第一换热流路的出口与所述第一换热组件的第二换热流路的出口之间还设置电控阀，其中，在所述四通阀第一次换向前所述分流装置控制所述电控阀关闭且持续所述预设时间，并在多联机系统除霜运行时，如果所述排气压力大于等于第一高压阈值且小于第三高压阈值、或者所述回气压力小于第一低压阈值且大于等于第三低压阈值、或者所述排气温度大于等于第一温度阈值且小于第三温度阈值，所述分流装置控制所述电控阀保持关闭状态；如果所述排气压力小于第二高压阈值、所述回气压力大于等于第二低压阈值且所述排气温度小于第二温度阈值，所述分流装置继续控制所述电控阀保持关闭状态；如果所述排气压力大于等于所述第三高压阈值、或者所述回气压力小于所述第三低压阈值、或者所述排气温度大于等于所述第三温度阈值，所述分流装置则控制所述电控阀打开。
根据本发明的一个实施例，所述节流元件为电子膨胀阀，所述电控阀为电磁阀。
根据本发明的一个实施例，当所述多联机系统制热运行时，所述多联机系统以主制热模式或纯制热模式进行工作。
附图说明
图1为根据本发明实施例的多联机系统除霜时的防回液控制方法的流程图；
图2为根据本发明一个实施例的多联机系统的结构示意图。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出，其中自始至终相同 或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，旨在用于解释本发明，而不能理解为对本发明的限制。
下面结合附图来描述本发明实施例的多联机系统及其除霜时的防回液控制方法。
图1为根据本发明实施例的多联机系统除霜时的防回液控制方法的流程图。
其中，参照图2，本发明实施例的多联机系统可包括室外机、分流装置和多个室内机，其中，分流装置包括第一换热组件、第二换热组件、设置在第二换热组件的第一换热流路的出口与第二换热组件的第二换热流路的入口之间的节流元件EXV2，第一换热组件的第一换热流路的出口与第二换热组件的第一换热流路的入口相连通，第一换热组件的第二换热流路的入口与第二换热组件的第二换热流路的出口相连通，第一换热组件的第二换热流路的出口连通到室外机，室外机包括压缩机和四通阀。在本发明的具体实施例中，节流元件EXV2可为电子膨胀阀。
如图1所示，本发明实施例的多联机系统除霜时的防回液控制方法可包括以下步骤：
S1，当多联机系统制热运行时，实时检测压缩机的排气压力、回气压力和排气温度。
S2，如果室外机接收到化霜指令，则向分流装置和多个室内机中的制热室内机发送除霜信号，并在四通阀第一次换向前通过分流装置控制节流元件关闭且持续预设时间以降低回到室外机的冷媒量，以及在多联机系统除霜运行时根据排气压力、回气压力和排气温度对节流元件的开度进行调节。
在本发明的一个实施例中，当多联机系统制热运行时，多联机系统以主制热模式或纯制热模式进行工作。
其中，参照图2，该多联机系统包括四个室内机，以纯制热模式进行工作为例，当多联机系统以纯制热模式进行工作时，四通阀的第一端口a和第四端口d相连通，第二端口b和第三端口c相连通。压缩机出口高温高压的气态冷媒通过油分离器、四通阀和单向阀F10进入分流装置的高压气液分离器，然后经过制热电磁阀SVH1-SVH4进入室内机进行制热。室内机出口的液态冷媒经单向阀RV1-RV4分别流过第二换热组件、节流元件EXV2和第一换热组件，然后经单向阀F9进入室外机的室外换热器蒸发。在经室外换热器蒸发后，冷媒可通过单向阀F5以及四通阀进入室外机的低压气液分离器，以返回到压缩机。
而当多联机系统除霜运行时，多联机系统中冷媒流路相当于制冷运行时的冷媒流路。以纯制冷模式为例，参照图2，此时四通阀进行第一次换向，其第一端口a和第二端口b相连通，第四端口d和第三端口c相连通。压缩机出口高温高压的气态冷媒通过油分离器和四通阀后经单向阀F1直接进入室外换热器，以融去室外换热器上覆盖的霜。然后大部分冷媒经单向阀F6进入分流装置的高压气液分离器，依次经过第一换热组件、另一节流元件EXV1、第二换热组件、单向阀RV5-RV8后进入室内机，再经过制冷电磁阀SVC1-SVC4 回到室外机。还有一部分冷媒经节流元件EXV2回室外机。其中，在室外机中，冷媒可经单向阀F8和四通阀进入低压气液分离器，以返回到压缩机。
在本发明的实施例中，可在四通阀第一次换向前控制节流元件EXV2关闭且持续预设时间，由此，可降低进入室外机低压气液分离器的冷媒量，以防止低压气液分离器中过多的冷媒回液至压缩机中，导致压缩机液压缩。
在多联机系统除霜运行时，可分别对排气压力PC、回气压力PE和排气温度TP进行判断。
当排气压力PC大于等于第一高压阈值A1且小于第三高压阈值A3、或者回气压力PE小于第一低压阈值B1且大于等于第三低压阈值B3、或者排气温度TP大于等于第一温度阈值C1且小于第三温度阈值C3时，分流装置控制节流元件EXV2增大预设开度。
当排气压力PC小于第二高压阈值A2、回气压力PE大于等于第二低压阈值B2且排气温度TP小于第二温度阈值C2时，分流装置控制节流元件EXV2减小预设开度。
当排气压力PC大于等于第三高压阈值A3、或者回气压力PE小于第三低压阈值B3、或者排气温度TP大于等于第三温度阈值C3时，分流装置控制节流元件EXV2打开至预设的最大开度。其中，第一高压阈值A1大于第二高压阈值A2且小于第三高压阈值A3，第一低压阈值B1大于第三低压阈值B3且小于第二低压阈值B2，第一温度阈值C1大于第二温度阈值C2且小于第三温度阈值C3。据此对节流元件EXV2的开度进行调节，直至化霜完成。
其中，A1-A3、B1-B3和C1-C3的具体数值可根据多联机系统中的冷媒量、压缩机的性能和低压气液分离器的规格等具体实施条件而设定。
由此，在除霜运行时，可持续根据排气压力、回气压力和排气温度对节流元件EXV2的开度进行调节，直至除霜完成。通过控制节流元件EXV2减小开度，能够防止冷媒过多，压缩机回液的情况发生；通过控制节流元件EXV2增大开度，能够防止冷媒过少，压缩机缺冷媒的情况发生，还能够提高化霜速度。
另外，参照图2，在本发明的一个实施例中，第二换热组件的第一换热流路的出口与第一换热组件的第二换热流路的出口之间还可设置电控阀SVM。其中，电控阀SVM可以为电磁阀。在制热运行时，室内机出口的液态冷媒还可经单向阀RV1-RV4分别流过第二换热组件和电控阀SVM，然后经单向阀F9进入室外机的室外换热器。在除霜运行时，一部分冷媒还可经电控阀SVM回室外机。因此，通过对电控阀SVM的控制，也能够控制冷媒流量。
具体地，在本发明的一个实施例中，在四通阀第一次换向前还可控制电控阀SVM关闭且持续预设时间，并在多联机系统除霜运行时，如果排气压力PC大于等于第一高压阈值 A1且小于第三高压阈值A3、或者回气压力PE小于第一低压阈值B1且大于等于第三低压阈值B3、或者排气温度TP大于等于第一温度阈值C1且小于第三温度阈值C3，分流装置控制电控阀SVM保持关闭状态。如果排气压力PC小于第二高压阈值A2、回气压力PE大于等于第二低压阈值B2且排气温度TP小于第二温度阈值C2，分流装置继续控制电控阀SVM保持关闭状态。如果排气压力PC大于等于第三高压阈值A3、或者回气压力PE小于第三低压阈值B3、或者排气温度TP大于等于第三温度阈值C3，分流装置则控制电控阀SVM打开。
也就是说，在包括电控阀的多联机系统中，可依照上述对排气压力、所述回气压力和所述排气温度的判断结果同时对节流元件EXV2和电控阀SVM进行控制，以通过控制冷媒流量来控制低压气液分离器中的冷媒量，防止其过多或过少。
此外，本发明还提出了一种非临时性计算机可读存储介质，其上存储有计算机程序，该程序被处理器执行时实现上述的防回液控制方法。
根据本发明实施例的多联机系统除霜时的防回液控制方法，在多联机系统制热运行时，如果接收到化霜指令，则可在四通阀第一次换向前通过关闭节流元件一段时间来降低回到室外机的冷媒量，并在除霜运行时根据排气压力、回气压力和排气温度对节流元件的开度进行调节，从而不仅能够保证除霜的有效进行，还能够避免除霜过程中压缩机出现回液风险，大大提高了系统的安全可靠性。
为实现上述实施例提出的多联机系统除霜时的防回液控制方法，本发明还提出一种多联机系统。
如图2所示，本发明实施例的多联机系统，包括多个室内机10、室外机20和分流装置30。
其中，室外机20包括压缩机21和四通阀22。分流装置30包括第一换热组件31、第二换热组件32、设置在第二换热组件32的第一换热流路的出口与第二换热组件32的第二换热流路的入口之间的节流元件EXV2，第一换热组件31的第一换热流路的出口与第二换热组件32的第一换热流路的入口相连通，第一换热组件31的第二换热流路的入口与第二换热组件32的第二换热流路的出口相连通，第一换热组件31的第二换热流路的出口连通到室外机20。其中，节流元件EXV2可为电子膨胀阀。
本发明实施例的多联机系统还可包括检测模块(图2中未标出)，检测模块用于在多联机系统制热运行时，实时检测压缩机21的排气压力、回气压力和排气温度。
在本发明的实施例中，室外机20在接收到化霜指令时，向分流装置30和多个室内机10中的制热室内机发送除霜信号，分流装置30在四通阀22第一次换向前控制节流元件EXV2关闭且持续预设时间以降低回到室外机20的冷媒量，并在多联机系统除霜运行时根 据排气压力、回气压力和排气温度对节流元件EXV2的开度进行调节。在本发明的一个实施例中，室内机10、室外机20和分流装置30可分别具有单独的控制器，以进行信息的交互和系统控制，也可通过集成在一起的控制器统一对室内机10、室外机20和分流装置30进行控制。
在本发明的一个实施例中，当多联机系统制热运行时，多联机系统以主制热模式或纯制热模式进行工作。
其中，如图2所示，该多联机系统包括四个室内机10，以纯制热模式进行工作为例，当多联机系统以纯制热模式进行工作时，四通阀22的第一端口a和第四端口d相连通，第二端口b和第三端口c相连通。压缩机21出口高温高压的气态冷媒通过油分离器23、四通阀22和单向阀F10进入分流装置30的高压气液分离器33，然后经过制热电磁阀SVH1-SVH4进入室内机10进行制热。室内机10出口的液态冷媒经单向阀RV1-RV4分别流过第二换热组件32、节流元件EXV2和第一换热组件31，然后经单向阀F9进入室外机20的室外换热器24蒸发。在经室外换热器24蒸发后，冷媒可通过单向阀F5以及四通阀22进入室外机20的低压气液分离器25，以返回到压缩机21。
而当多联机系统除霜运行时，多联机系统中冷媒流路相当于制冷运行时的冷媒流路。以纯制冷模式为例，参照图2，此时四通阀22进行第一次换向，其第一端口a和第二端口b相连通，第四端口d和第三端口c相连通。压缩机21出口高温高压的气态冷媒通过油分离器23和四通阀22后经单向阀F1直接进入室外换热器24，以融去室外换热器24上覆盖的霜。然后大部分冷媒经单向阀F6进入分流装置30的高压气液分离器33，依次经过第一换热组件31、另一节流元件EXV1、第二换热组件32、单向阀RV5-RV8后进入室内机10，再经过制冷电磁阀SVC1-SVC4回到室外机20。还有一部分冷媒经节流元件EXV2回室外机20。其中，在室外机20中，冷媒可经单向阀F8和四通阀进入低压气液分离器25，以返回到压缩机21。
在本发明的实施例中，分流装置30可在四通阀22第一次换向前控制节流元件EXV2关闭且持续预设时间，由此，可降低进入室外机20的低压气液分离器25的冷媒的量，以防止低压气液分离器25中过多的冷媒回液至压缩机21中，导致压缩机21液压缩。
在多联机系统除霜运行时，分流装置30可分别对排气压力PC、回气压力PE和排气温度TP进行判断。当排气压力PC大于等于第一高压阈值A1且小于第三高压阈值A3、或者回气压力PE小于第一低压阈值B1且大于等于第三低压阈值B3、或者排气温度TP大于等于第一温度阈值C1且小于第三温度阈值C3时，分流装置30控制节流元件EXV2增大预设开度。当排气压力PC小于第二高压阈值A2、回气压力PE大于等于第二低压阈值B2且排气温度TP小于第二温度阈值C2时，分流装置30控制节流元件EXV2减小预设开度。 当排气压力PC大于等于第三高压阈值A3、或者回气压力PE小于第三低压阈值B3、或者排气温度TP大于等于第三温度阈值C3时，分流装置30控制节流元件EXV2打开至预设的最大开度。其中，第一高压阈值A1大于第二高压阈值A2且小于第三高压阈值A3，第一低压阈值B1大于第三低压阈值B3且小于第二低压阈值B2，第一温度阈值C1大于第二温度阈值C2且小于第三温度阈值C3。据此对节流元件EXV2的开度进行调节，直至化霜完成。
其中，A1-A3、B1-B3和C1-C3的具体数值可根据多联机系统中的冷媒量、压缩机21的性能和低压气液分离器25的规格等具体实施条件而设定。
由此，在除霜运行时，分流装置30可持续根据排气压力、回气压力和排气温度对节流元件EXV2的开度进行调节，直至除霜完成。通过控制节流元件EXV2减小开度，能够防止冷媒过多，压缩机21回液的情况发生；通过控制节流元件EXV2增大开度，能够防止冷媒过少，压缩机21缺冷媒的情况发生，还能够提高化霜速度。
另外，如图2所示，在本发明的一个实施例中，第二换热组件32的第一换热流路的出口与第一换热组件31的第二换热流路的出口之间还可设置电控阀SVM。其中，电控阀SVM可以为电磁阀。在制热运行时，室内机10出口的液态冷媒还可经单向阀RV1-RV4分别流过第二换热组件32和电控阀SVM，然后经单向阀F9进入室外机20的室外换热器。在除霜运行时，一部分冷媒还可经电控阀SVM回室外机20。因此，通过对电控阀SVM的控制，也能够控制冷媒流量。
具体地，在本发明的一个实施例中，在四通阀22第一次换向前分流装置30还可控制电控阀SVM关闭且持续预设时间，并在多联机系统除霜运行时，如果排气压力PC大于等于第一高压阈值A1且小于第三高压阈值A3、或者回气压力PE小于第一低压阈值B1且大于等于第三低压阈值B3、或者排气温度TP大于等于第一温度阈值C1且小于第三温度阈值C3，分流装置30控制电控阀SVM保持关闭状态。如果排气压力PC小于第二高压阈值A2、回气压力PE大于等于第二低压阈值B2且排气温度TP小于第二温度阈值C2，分流装置30继续控制电控阀SVM保持关闭状态。如果排气压力PC大于等于第三高压阈值A3、或者回气压力PE小于第三低压阈值B3、或者排气温度TP大于等于第三温度阈值C3，分流装置30则控制电控阀SVM打开。
也就是说，在包括电控阀的多联机系统中，可依照上述对排气压力、所述回气压力和所述排气温度的判断结果同时对节流元件EXV2和电控阀SVM进行控制，以通过控制冷媒流量来控制低压气液分离器中的冷媒量，防止其过多或过少。
根据本发明实施例的多联机系统，在制热运行时，如果室外机接收到化霜指令，则分流装置可在四通阀第一次换向前通过关闭节流元件一段时间来降低回到室外机的冷媒量， 并在除霜运行时根据排气压力、回气压力和排气温度对节流元件的开度进行调节，从而不仅能够保证除霜的有效进行，还能够避免除霜过程中压缩机出现回液风险，大大提高了系统的安全可靠性。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”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发明和简化描述，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发明的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本发明的描述中，“多个”的含义是两个或两个以上，除非另有明确具体的限定。
在本发明中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
在本发明中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
尽管上面已经示出和描述了本发明的实施例，可以理解的是，上述实施例是示例性的，不能理解为对本发明的限制，本领域的普通技术人员在本发明的范围内可以对上述实施例 进行变化、修改、替换和变型。

Claims (11)

  1. 一种多联机系统除霜时的防回液控制方法，其特征在于，所述多联机系统包括室外机、分流装置和多个室内机，其中，所述分流装置包括第一换热组件、第二换热组件、设置在所述第二换热组件的第一换热流路的出口与所述第二换热组件的第二换热流路的入口之间的节流元件，所述第一换热组件的第一换热流路的出口与所述第二换热组件的第一换热流路的入口相连通，所述第一换热组件的第二换热流路的入口与所述第二换热组件的第二换热流路的出口相连通，所述第一换热组件的第二换热流路的出口连通到所述室外机，所述室外机包括压缩机和四通阀，所述方法包括以下步骤：
    当所述多联机系统制热运行时，实时检测所述压缩机的排气压力、回气压力和排气温度；
    如果所述室外机接收到化霜指令，则向所述分流装置和所述多个室内机中的制热室内机发送除霜信号，并在所述四通阀第一次换向前通过所述分流装置控制所述节流元件关闭且持续预设时间以降低回到所述室外机的冷媒量，以及在所述多联机系统除霜运行时根据所述排气压力、所述回气压力和所述排气温度对所述节流元件的开度进行调节。
  2. 根据权利要求1所述的方法，其特征在于，在所述多联机系统除霜运行时根据所述排气压力、所述回气压力和所述排气温度对所述节流元件的开度进行调节，包括：
    分别对所述排气压力、所述回气压力和所述排气温度进行判断；
    当所述排气压力大于等于第一高压阈值且小于第三高压阈值、或者所述回气压力小于第一低压阈值且大于等于第三低压阈值、或者所述排气温度大于等于第一温度阈值且小于第三温度阈值时，所述分流装置控制所述节流元件增大预设开度；
    当所述排气压力小于第二高压阈值、所述回气压力大于等于第二低压阈值且所述排气温度小于第二温度阈值时，所述分流装置控制所述节流元件减小预设开度，其中，所述第一高压阈值大于所述第二高压阈值且小于所述第三高压阈值，所述第一低压阈值大于所述第三低压阈值且小于第二低压阈值，所述第一温度阈值大于所述第二温度阈值且小于所述第三温度阈值；
    当所述排气压力大于等于所述第三高压阈值、或者所述回气压力小于所述第三低压阈值、或者所述排气温度大于等于所述第三温度阈值时，所述分流装置控制所述节流元件打开至预设的最大开度。
  3. 根据权利要求2所述的方法，其特征在于，所述第二换热组件的第一换热流路的出口与所述第一换热组件的第二换热流路的出口之间还设置电控阀，其中，在所述四通阀第一次换向前所述分流装置控制所述电控阀关闭且持续所述预设时间，并在多联机系统除霜 运行时，
    如果所述排气压力大于等于第一高压阈值且小于第三高压阈值、或者所述回气压力小于第一低压阈值且大于等于第三低压阈值、或者所述排气温度大于等于第一温度阈值且小于第三温度阈值，所述分流装置控制所述电控阀保持关闭状态；
    如果所述排气压力小于第二高压阈值、所述回气压力大于等于第二低压阈值且所述排气温度小于第二温度阈值，所述分流装置继续控制所述电控阀保持关闭状态；
    如果所述排气压力大于等于所述第三高压阈值、或者所述回气压力小于所述第三低压阈值、或者所述排气温度大于等于所述第三温度阈值，所述分流装置则控制所述电控阀打开。
  4. 根据权利要求2或3所述的方法，其特征在于，所述节流元件为电子膨胀阀，所述电控阀为电磁阀。
  5. 根据权利要求1所述的方法，其特征在于，当所述多联机系统制热运行时，所述多联机系统以主制热模式或纯制热模式进行工作。
  6. 一种多联机系统，其特征在于，包括：
    多个室内机；
    室外机，所述室外机包括压缩机和四通阀；
    分流装置，所述分流装置包括第一换热组件、第二换热组件、设置在所述第二换热组件的第一换热流路的出口与所述第二换热组件的第二换热流路的入口之间的节流元件，所述第一换热组件的第一换热流路的出口与所述第二换热组件的第一换热流路的入口相连通，所述第一换热组件的第二换热流路的入口与所述第二换热组件的第二换热流路的出口相连通，所述第一换热组件的第二换热流路的出口连通到所述室外机。
    检测模块，所述检测模块用于在所述多联机系统制热运行时，实时检测所述压缩机的排气压力、回气压力和排气温度。
    其中，所述室外机在接收到化霜指令时，向所述分流装置和所述多个室内机中的制热室内机发送除霜信号，所述分流装置在所述四通阀第一次换向前控制所述节流元件关闭且持续预设时间以降低回到所述室外机的冷媒量，并在所述多联机系统除霜运行时根据所述排气压力、所述回气压力和所述排气温度对所述节流元件的开度进行调节。
  7. 根据权利要求6所述的多联机系统，其特征在于，所述分流装置用于分别对所述排气压力、所述回气压力和所述排气温度进行判断，其中，
    当所述排气压力大于等于第一高压阈值且小于第三高压阈值、或者所述回气压力小于第一低压阈值且大于等于第三低压阈值、或者所述排气温度大于等于第一温度阈值且小于第三温度阈值时，所述分流装置控制所述节流元件增大预设开度；
    当所述排气压力小于第二高压阈值、所述回气压力大于等于第二低压阈值且所述排气温度小于第二温度阈值时，所述分流装置控制所述节流元件减小预设开度，其中，所述第一高压阈值大于所述第二高压阈值且小于所述第三高压阈值，所述第一低压阈值大于所述第三低压阈值且小于第二低压阈值，所述第一温度阈值大于所述第二温度阈值且小于所述第三温度阈值；
    当所述排气压力大于等于所述第三高压阈值、或者所述回气压力小于所述第三低压阈值、或者所述排气温度大于等于所述第三温度阈值时，所述分流装置控制所述节流元件打开至预设的最大开度。
  8. 根据权利要求7所述的多联机系统，其特征在于，所述第二换热组件的第一换热流路的出口与所述第一换热组件的第二换热流路的出口之间还设置电控阀，其中，在所述四通阀第一次换向前所述分流装置控制所述电控阀关闭且持续所述预设时间，并在多联机系统除霜运行时，
    如果所述排气压力大于等于第一高压阈值且小于第三高压阈值、或者所述回气压力小于第一低压阈值且大于等于第三低压阈值、或者所述排气温度大于等于第一温度阈值且小于第三温度阈值，所述分流装置控制所述电控阀保持关闭状态；
    如果所述排气压力小于第二高压阈值、所述回气压力大于等于第二低压阈值且所述排气温度小于第二温度阈值，所述分流装置继续控制所述电控阀保持关闭状态；
    如果所述排气压力大于等于所述第三高压阈值、或者所述回气压力小于所述第三低压阈值、或者所述排气温度大于等于所述第三温度阈值，所述分流装置则控制所述电控阀打开。
  9. 根据权利要求7或8所述的多联机系统，其特征在于，所述节流元件为电子膨胀阀，所述电控阀为电磁阀。
  10. 根据权利要求6所述的多联机系统，其特征在于，当所述多联机系统制热运行时，所述多联机系统以主制热模式或纯制热模式进行工作。
  11. 一种非临时性计算机可读存储介质，其上存储有计算机程序，其特征在于，该程序被处理器执行时实现如权利要求1～5中任一所述的防回液控制方法。
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