WO2018046026A1 - 采用喷射器的空调热泵系统、空调器及空调器控制方法 - Google Patents

采用喷射器的空调热泵系统、空调器及空调器控制方法 Download PDF

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Publication number
WO2018046026A1
WO2018046026A1 PCT/CN2017/110516 CN2017110516W WO2018046026A1 WO 2018046026 A1 WO2018046026 A1 WO 2018046026A1 CN 2017110516 W CN2017110516 W CN 2017110516W WO 2018046026 A1 WO2018046026 A1 WO 2018046026A1
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WIPO (PCT)
Prior art keywords
solenoid valve
passage
valve
heat exchanger
port
Prior art date
Application number
PCT/CN2017/110516
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English (en)
French (fr)
Inventor
刘敏
张文强
李虎
杜明龙
Original Assignee
青岛海信日立空调系统有限公司
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Application filed by 青岛海信日立空调系统有限公司 filed Critical 青岛海信日立空调系统有限公司
Priority to ES17848199T priority Critical patent/ES2928653T3/es
Priority to EP17848199.0A priority patent/EP3553398B1/en
Publication of WO2018046026A1 publication Critical patent/WO2018046026A1/zh
Priority to US16/351,177 priority patent/US11236926B2/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00885—Controlling the flow of heating or cooling liquid, e.g. valves or pumps
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3205—Control means therefor
    • B60H1/3213—Control means therefor for increasing the efficiency in a vehicle heat pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K37/00—Special means in or on valves or other cut-off apparatus for indicating or recording operation thereof, or for enabling an alarm to be given
    • F16K37/0025—Electrical or magnetic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K49/00—Means in or on valves for heating or cooling
    • F16K49/005—Circulation means for a separate heat transfer fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/01—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station in which secondary air is induced by injector action of the primary air
    • 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
    • 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
    • F24F5/0046—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 using natural energy, e.g. solar energy, energy from the ground
    • 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
    • F25B19/00—Machines, plants or systems, using evaporation of a refrigerant but without recovery of the vapour
    • F25B19/02—Machines, plants or systems, using evaporation of a refrigerant but without recovery of the vapour using fluid jet, e.g. of steam
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3286—Constructional features
    • B60H2001/3298—Ejector-type refrigerant 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
    • F24F11/70—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
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0407—Refrigeration circuit bypassing means for the ejector
    • 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

Definitions

  • the present disclosure relates to the field of air conditioning, and more particularly to an air conditioning heat pump system using an ejector, an air conditioner, and an air conditioner control method.
  • Air conditioning with its superior cooling and heating functions, has become an important means for people to cool down and cool down in the daily life.
  • Air conditioning mainly uses air conditioning heat pump systems to extract cooling and heat from the environment to cool or heat the indoor environment.
  • the air-conditioning heat pump system mainly extracts cooling capacity and heat from the environment through the work of the compressor.
  • the compressor consumes electric energy to compress the low-temperature low-pressure refrigerant into high-temperature and high-pressure refrigerant, and then, in the cooling mode, the high temperature
  • the high-pressure refrigerant is condensed and cooled by the outdoor heat exchanger, and then input to the indoor heat exchanger for evaporation heat exchange to cool the room, or, in the heating mode, the high-temperature high-pressure refrigerant is input to the indoor heat exchanger for condensation heat dissipation.
  • an embodiment of the present disclosure provides an air conditioning heat pump system using an ejector, comprising: a compression assembly, an outdoor heat exchanger, a first throttling device, an indoor heat exchanger, and an ejector, the injection of the ejector An inlet is in communication with one end of the indoor heat exchanger, an ejector inlet of the ejector is in communication with one end of the outdoor heat exchanger, and an outlet end of the ejector is in communication with a third end of the compression assembly, the compression The first end of the assembly is in communication with one end of the outdoor heat exchanger, and the second end of the compression assembly is in communication with the other end of the indoor heat exchanger, the first One end of the flow device is in communication with the other end of the outdoor heat exchanger, and the other end is connected to one end of the indoor heat exchanger.
  • the air conditioning heat pump system using an ejector further includes: a flow direction control valve disposed on a passage between the first end of the compression assembly and one end of the outdoor heat exchanger, disposed at the ejector inlet and the a first solenoid valve on a passage between one end of the outdoor heat exchanger, a second solenoid valve disposed on a passage between the other end of the first throttle device and one end of the indoor heat exchanger, disposed in the a third solenoid valve on the passage between the injection inlet and one end of the indoor heat exchanger, a first one-way valve disposed on a passage between the third end of the compression assembly and the outlet end of the injector a second one-way valve and a controller on a passage between the fourth end of the compression assembly and the other end of the first throttle device, wherein:
  • the flow direction of the first check valve is from the outlet end of the injector to the third end of the compression assembly
  • the flow direction of the second one-way valve is from the fourth end of the compression assembly to the other end of the first throttle device;
  • the flow direction control valve is in an on state when the refrigerant flows from the first end of the compression assembly to one end of the outdoor heat exchanger;
  • the controller is configured to control opening and closing of the first electromagnetic valve, the second electromagnetic valve, and the third electromagnetic valve according to a current working mode.
  • an embodiment of the present disclosure provides an air conditioner comprising the air conditioning heat pump system using an injector provided by the first aspect.
  • an embodiment of the present disclosure provides an air conditioner control method, which is applied to an air conditioner provided in a second aspect, the method comprising:
  • the controller in the air conditioner controls opening and closing of the first solenoid valve, the second solenoid valve, and the third solenoid valve in the air conditioner according to a current working mode.
  • FIG. 1 is a schematic structural view of an air conditioning heat pump system using an ejector according to an embodiment of the present disclosure
  • FIG. 2 is a schematic structural diagram of a compression component according to an embodiment of the present disclosure
  • FIG. 3 is a schematic structural diagram of an air conditioning heat pump system using an ejector according to another embodiment of the present disclosure
  • FIG. 4 is a refrigerant flow diagram of the air conditioning heat pump system of FIG. 3 corresponding to an ejector in a cooling mode according to an embodiment of the present disclosure
  • FIG. 5 is a refrigerant flow diagram of the air conditioning heat pump system of FIG. 3 corresponding to an ejector in a normal heating mode according to an embodiment of the present disclosure
  • FIG. 6 is a refrigerant flow diagram of the air conditioning heat pump system of FIG. 3 corresponding to an ejector in a low temperature heating mode according to an embodiment of the present disclosure
  • FIG. 7 is a schematic structural diagram of an air conditioning heat pump system using an ejector according to still another embodiment of the present disclosure.
  • FIG. 8 is a refrigerant flow diagram of the air conditioning heat pump system of FIG. 7 corresponding to an ejector in a cooling mode according to an embodiment of the present disclosure
  • FIG. 9 is a flow chart of the refrigerant in the heating mode of the ejector air-conditioning heat pump system of FIG. 7 according to an embodiment of the present disclosure.
  • FIG. 10 is a schematic diagram of an air conditioner according to an embodiment of the present disclosure.
  • connection and “connect” should be understood broadly. For example, it may be a fixed connection, a disassembly connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or passed through The intermediate medium is indirectly connected, and may be a communication inside the two elements or an interaction relationship between the two elements.
  • connect and “connect” should be understood broadly. For example, it may be a fixed connection, a disassembly connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or passed through The intermediate medium is indirectly connected, and may be a communication inside the two elements or an interaction relationship between the two elements.
  • specific meanings of the above terms in the present disclosure may be understood on a case-by-case basis.
  • Air-conditioning heat pump systems usually increase the expansion and contraction of the ejector air-conditioning system to reduce the power consumption of the compressor. Specifically, the ejector depressurizes the high pressure refrigerant entering through the injection inlet thereof through the throttling of the internal nozzle of the ejector to form a low pressure environment, thereby attracting the low pressure refrigerant of the ejector inlet of the ejector into the suction chamber of the ejector, Then, through the action of the mixing section and the diffusion section, a pressure-centered refrigerant is finally formed, thereby increasing the suction port pressure of the compressor and reducing the power consumption of the compressor.
  • an air conditioning system with an injector is usually only capable of achieving a cooling mode, and cannot achieve a heating mode.
  • the air-conditioning heat pump system using the ejector includes a compression assembly 01, an outdoor heat exchanger 02, a first throttle device 03, an indoor heat exchanger 04, and an ejector 05.
  • the injector 05 includes three ports, an injection inlet 05a, an ejector inlet 05b, and an outlet end 05c.
  • the injection inlet 05a of the injector 05 is in communication with one end of the indoor heat exchanger 04
  • the injection inlet 05b of the injector 05 is in communication with one end of the outdoor heat exchanger 02
  • the outlet end 05c of the injector 05 and the compression assembly 01 The third end is connected.
  • the first end of the compression assembly 01 is in communication with one end of the outdoor heat exchanger 02
  • the second end of the compression assembly 01 is in communication with the other end of the indoor heat exchanger 04.
  • One end of the first throttle device 03 communicates with the other end of the outdoor heat exchanger 02
  • the other end of the first throttle device 03 communicates with one end of the indoor heat exchanger 04.
  • the air-conditioning heat pump system using the ejector further includes: a flow direction control valve 06 disposed on a passage between the first end of the compression assembly 01 and one end of the outdoor heat exchanger 02, and an ejector inlet 05b disposed at the ejector 05 a first solenoid valve 07 on the passage between the end of the outdoor heat exchanger 02, a second solenoid valve 08 disposed on the passage between the other end of the first throttle device 03 and one end of the indoor heat exchanger 04, Set at the injection inlet 05a of the injector 05 a third solenoid valve 09 on the passage between the end of the indoor heat exchanger 04, a first check valve 10 disposed on the passage between the third end of the compression assembly 01 and the outlet end 05c of the injector 05, the setting A second check valve 11 on the passage between the fourth end of the compression assembly 01 and the other end of the first throttle device 03, and the controller 12.
  • a flow direction control valve 06 disposed on a passage between the first end of the compression
  • the flow direction control valve 06 is in an on state when the refrigerant flows from the first end of the compression unit 01 to one end of the outdoor heat exchanger 02.
  • the flow direction of the first check valve 10 is from the outlet end 05c of the injector 05 to the third end of the compression assembly 01.
  • the flow direction of the second check valve 11 is from the fourth end of the compression assembly 01 to the other end of the first throttle device 03.
  • the controller 12 is configured to control the opening and closing of the first solenoid valve 07, the second solenoid valve 08, and the third solenoid valve 09 in accordance with the current operating mode.
  • controller 12 may be implemented in a general purpose processor that executes machine readable instructions stored in non-transitory memory such that it can perform the functions described in detail herein.
  • the controller can be implemented in a special purpose processor, such as an application specific integrated circuit (ASIC), which is configured to perform the functions described in detail herein.
  • ASIC application specific integrated circuit
  • the first throttle device 03 may employ a capillary or an electronic expansion valve, and, as shown in FIG. 1 and As shown in FIG. 3, a gas side shutoff valve 13 is disposed on the passage between the other end of the indoor heat exchanger 04 and the second end of the compression assembly 01, and a passage between one end of the indoor heat exchanger 04 and the second electromagnetic valve 08 is shown.
  • a liquid side shutoff valve 14 is provided thereon.
  • the first throttle device 03 is an electronic expansion tube at this time, and, as shown in FIG. 3, a gas side shutoff valve 13 disposed on a passage between the other end of the plurality of indoor heat exchangers 04 and the second end of the compression assembly 01 is connected to the plurality of indoor heat exchangers 04 through the gas side branch pipe 15, at the
  • the liquid side shutoff valve 14 provided on the passage between one end of the indoor heat exchanger 04 and the second solenoid valve 08 is connected to the plurality of indoor heat exchangers 04 through the liquid side branch pipe 16.
  • the air-conditioning heat pump system using the ejector when the air-conditioning heat pump system using the ejector is a multi-line system, as shown in FIG. 3, the air-conditioning heat pump system using the ejector in the embodiment of the present disclosure further includes a plurality of second The throttle device 17, each of the plurality of second throttle devices 17 is disposed on a passage between the liquid side shutoff valve 14 and one end of a corresponding one of the plurality of indoor heat exchangers 04.
  • Each of the plurality of second throttle devices 17 is for controlling a flow rate of refrigerant in a passage between a respective one of the plurality of indoor heat exchangers 04 and an injection inlet 05a of the injector 05.
  • the compression assembly 01 in the embodiment of the present disclosure includes a compressor 011, a separator 012, and a four-way valve 013.
  • the compressor 011 includes an exhaust port 011a and an intake port 011b.
  • the separator 012 includes a gaseous outlet end 012a, a liquid outlet end 012b, and an inlet end 012c.
  • the four-way valve 013 includes a first port 013a, a second port 013b, a third port 013c, and a fourth port 013d.
  • the first port 013a is in communication with the exhaust port 011a of the compressor 011.
  • the second port 013b is in communication with one end of the outdoor heat exchanger 02.
  • the third port 013c is in communication with the inlet end 012c of the separator 012.
  • the fourth port 013d is in communication with the other end of the indoor heat exchanger 04.
  • the suction port 011b of the compressor 011 communicates with the gas outlet end 012a of the separator 012.
  • the liquid outlet end 012b of the separator 012 is in communication with the other end of the first throttle device 03.
  • the controller 12 is further used for The opening and closing of the fourth solenoid valve 18 is controlled.
  • the controller 12 is configured to: in the cooling mode, control the fourth solenoid valve 18 and the second solenoid valve 08 to open the passage, and control the first solenoid valve 07 and the third solenoid valve 09 to close the passage; or In the normal heating mode, the fourth electromagnetic valve 18 and the second electromagnetic valve 08 are opened to open the passage, and the first electromagnetic valve 07 and the third electromagnetic valve 09 are controlled to close the passage; or in the low temperature heating mode, the fourth electromagnetic is controlled.
  • the valve 18 and the second solenoid valve 08 close the passage and control the first solenoid valve 07 and the third solenoid valve 09 to open the passage.
  • the compressor 011 compresses the low-temperature low-pressure gas refrigerant into a high-temperature and high-pressure gas refrigerant, and the high-temperature high-pressure is The gaseous refrigerant is discharged through the exhaust port 011a.
  • the high temperature and high pressure gaseous refrigerant sequentially passes through the first port 013a and the second port 013b of the four-way valve 013 and the fourth electromagnetic valve 18, and enters the outdoor heat exchanger 02. At this time, the outdoor heat exchanger 02 is made.
  • the high temperature and high pressure gaseous refrigerant is condensed into a medium temperature high pressure liquid refrigerant.
  • the medium-temperature high-pressure liquid refrigerant enters the first throttling device 03, and the refrigerant is depressurized.
  • the liquid refrigerant flows through the second solenoid valve 08, the liquid side shutoff valve 14, the liquid side branch pipe 16, and the second throttle device 17, and enters the indoor heat exchanger 04, which serves as an evaporation
  • the low-temperature low-pressure liquid refrigerant is evaporated into a low-temperature low-pressure gas refrigerant, and the indoor environment is exchange-heat-cooled, and then the refrigerant passes through the gas-side branch pipe 15, the gas-side shut-off valve 13, and the fourth port 013d of the four-way valve 013 in sequence.
  • the third port 013c and the inlet end 012c of the separator 012 enter the separator 012.
  • the injector 05 does not operate.
  • the compressor 011 compresses the low-temperature low-pressure gas refrigerant into a high-temperature high-pressure gas refrigerant, and
  • the high-temperature high-pressure gas refrigerant is discharged through the exhaust port 011a.
  • the high-temperature and high-pressure gas refrigerant sequentially passes through the first port 013a and the fourth port 013d of the four-way valve 013, the gas side shutoff valve 13 and the gas side branch pipe 15, and enters the indoor heat exchanger 04.
  • the indoor heat exchanger 04 functions as a condenser to condense the high-temperature and high-pressure gas refrigerant into a medium-temperature high-pressure liquid refrigerant to heat the indoor environment. Thereafter, the liquid refrigerant sequentially flows through the second throttle device 17, the liquid side branch pipe 16, the liquid side shutoff valve 14, the second solenoid valve 08, and the first throttle device 03 to enter the outdoor heat exchanger 02.
  • the outdoor heat exchanger 02 serves as an evaporator to evaporate the liquid refrigerant into a gaseous refrigerant.
  • the gaseous refrigerant sequentially flows through the fourth solenoid valve 18, the second port 013b of the four-way valve 013, the third port 013c, and the inlet end 012c of the separator 012, and enters the separator 012.
  • the injector 05 does not operate in the normal heating mode.
  • the high temperature and high pressure gaseous refrigerant discharged from the exhaust port 011a of the compressor 011 sequentially flows through the first port of the four-way valve 013.
  • the 013a and the fourth port 013d enter the indoor heat exchanger 04 through the gas side shutoff valve 13 and the gas side branch pipe 15.
  • the indoor heat exchanger 04 functions as a condenser to condense the high-temperature and high-pressure gas refrigerant into a medium-temperature high-pressure liquid refrigerant, and supplies heat to the room.
  • the liquid refrigerant flows through the second throttle device 17, the liquid side branch pipe 16, the liquid side shutoff valve 14, and the third solenoid valve 09 to enter the injection inlet 05a of the injector 05, passing through the injector 05.
  • the throttling of the internal nozzle depressurizes to form a low pressure environment, thereby attracting the refrigerant of the ejector inlet 05b of the ejector 05 into the ejector 05.
  • the mixed refrigerant passes through the mixing section and the diffusion section of the ejector 05 to raise the outlet pressure of the ejector 05.
  • the refrigerant flowing out of the outlet end 05c of the ejector 05 passes through the first check valve 10 and enters the inlet end 012c of the separator 012.
  • the gaseous refrigerant flowing from the gaseous outlet end 012a of the separator 012 enters the compressor 011, thereby raising the suction pressure of the compressor 011.
  • the liquid refrigerant flowing out from the liquid outlet end 012b of the separator 012 flows through the second check valve 11, the first throttle device 03, the outdoor heat exchanger 02, and the first solenoid valve 07, and then returns to the injector 05.
  • the entrance 05b is ejector.
  • the injector 05 operates in the low temperature heating mode.
  • the air conditioner using the ejector is used when the flow direction control valve 06 is the third check valve 19
  • the heat pump system further includes a fourth one-way valve 20 disposed on a passage between the third port 013c of the four-way valve 013 and the inlet end 012c of the separator 012.
  • the flow direction of the third check valve 19 is from the second port 013b of the four-way valve 013 to one end of the outdoor heat exchanger 02
  • the flow direction of the fourth check valve 20 is from the third port 013c of the four-way valve 013.
  • the controller is configured to: in the cooling mode, control the second solenoid valve 08 to open the passage, and control the first solenoid valve 07 and the third solenoid valve 09 to close the passage; in the heating mode, control the first electromagnetic The valve 07 and the third solenoid valve 09 open the passage and control the second solenoid valve 08 to close the passage.
  • FIG. 8 corresponds to The circulation process of the refrigerant is the same as the refrigerant circulation process corresponding to FIG. 4, and will not be described again here.
  • the circulation process of the refrigerant corresponding to FIG. 9 is the same as the refrigerant circulation process corresponding to FIG. 6, and will not be described again.
  • An air conditioning heat pump system using an ejector adds a first end of the compression assembly 01 and one end of the outdoor heat exchanger 02 to the air conditioning heat pump system.
  • a flow control valve 06 on the intermediate passage
  • a first solenoid valve 07 disposed on the passage between the injector 05 injection inlet 05b and one end of the outdoor heat exchanger 02, and the other end of the first throttle device 03 and the chamber
  • a second solenoid valve 08 on the passage between one end of the heat exchanger 04
  • a third solenoid valve 09 disposed on the passage between the injector 05 injection inlet 05a and one end of the indoor heat exchanger 04
  • a compression solenoid assembly 01 a first one-way valve 10 on the passage between the third end and the outlet end 05c of the injector 05, a second one-way valve disposed on the passage between the fourth end of the compression assembly 01 and the other end of the first throttle device 03
  • the valve 11 and the controller 12 thereby controlling the opening and closing of the first solenoi
  • the embodiment of the present disclosure provides an air conditioner 100, as shown in FIG. 10, which includes the above-described air conditioning heat pump system using an ejector.
  • the above description of the components of the air conditioner 100 and the description of the components in the air conditioner 100 can be referred to the above description of the air conditioner heat pump system using the injector, and details are not described herein again.
  • the controller in the air conditioner controls opening and closing of the flow direction control valve, the first electromagnetic valve, the second electromagnetic valve, and the third electromagnetic valve in the air conditioner according to the current working mode.
  • the controller is further configured to control the opening and closing of the fourth electromagnetic valve, and the step 301 includes the following steps:
  • control the fourth solenoid valve and the second solenoid valve to open the passage, and control the first solenoid valve and the third solenoid valve to close the passage.
  • step 302 includes the following steps:
  • control the first solenoid valve and the third solenoid valve to open the passage, and control the second solenoid valve to close the passage.
  • the air conditioner control method increases a flow direction control valve disposed on a passage between a first end of the compression assembly and one end of the outdoor heat exchanger in the air conditioning heat pump system, and is disposed at the injector injection inlet and a first solenoid valve on a passage between one end of the outdoor heat exchanger, a second solenoid valve disposed on a passage between the other end of the first throttle device and one end of the indoor heat exchanger, and a heat exchange disposed at the injector injection inlet and the chamber a third solenoid valve on the passage between one end of the device, a first one-way valve disposed on the passage between the third end of the compression assembly and the outlet end of the injector, and a fourth end disposed at the fourth end of the compression assembly and the first throttle device a second check valve on the channel between the other end and a controller, thereby controlling the opening and closing of the first solenoid valve, the second solenoid valve and the third solenoid valve by the controller in different working modes to realize the

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Abstract

一种采用喷射器的空调热泵系统，包括：设置在压缩组件（01）第一端与室外换热器（02）一端间通道上的流向控制阀（06）、设置在喷射器（05）的引射入口（05b）与室外换热器（02）一端间通道上的第一电磁阀（07）、设置在第一节流装置（03）另一端与室内换热器（04）一端间通道上的第二电磁阀（08）、设置在喷射器（05）的喷射入口（05a）与室内换热器（04）一端间通道上的第三电磁阀（09）、设置在压缩组件（01）第三端与喷射器（05）的出口端（05c）间通道上的第一单向阀（10）、设置在压缩组件（01）第四端与第一节流装置（03）另一端间通道上的第二单向阀（11）及控制器（12）。

Description

采用喷射器的空调热泵系统、空调器及空调器控制方法
本申请要求于2016年9月12日提交中国专利局、申请号为201610818928.X、发明名称为“采用喷射器的空调热泵系统、空调器及空调器控制方法”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本公开涉及空调领域，尤其涉及一种采用喷射器的空调热泵系统、空调器及空调器控制方法。
背景技术
空调以其优越的制冷、制热功能，成为人们日常生活中消暑降温、驱寒取暖的重要手段。空调主要通过空调热泵系统来从环境提取冷量和热量，以便对室内环境进行制冷或制热。而空调热泵系统则主要通过压缩机做功来从环境提取冷量和热量，在这个过程中，压缩机消耗电能来将低温低压制冷剂压缩成高温高压制冷剂，然后，在制冷模式下，将高温高压制冷剂通过室外换热器进行冷凝降温后输入至室内换热器进行蒸发换热来对室内进行降温，或，在制热模式下将高温高压制冷剂输入至室内换热器进行冷凝散热，从而将热量传递给室内环境。因此，如何降低压缩机耗功是提升热泵系统运行能效的重点之一。
发明内容
第一方面，本公开实施例提供了一种采用喷射器的空调热泵系统，包括：压缩组件、室外换热器、第一节流装置、室内换热器以及喷射器，所述喷射器的喷射入口与所述室内换热器的一端连通，所述喷射器的引射入口与所述室外换热器的一端连通，所述喷射器出口端与所述压缩组件第三端连通，所述压缩组件第一端与所述室外换热器的一端连通，所述压缩组件第二端与室内换热器另一端连通，所述第 一节流装置一端与所述室外换热器的另一端连通，另一端与所述室内换热器的一端连通，
所述采用喷射器的空调热泵系统还包括：设置在所述压缩组件的第一端与所述室外换热器的一端间的通道上的流向控制阀、设置在所述引射入口与所述室外换热器的一端间的通道上的第一电磁阀、设置在所述第一节流装置另一端与所述室内换热器的一端间的通道上的第二电磁阀、设置在所述喷射入口与所述室内换热器的一端间的通道上的第三电磁阀、设置在所述压缩组件的第三端与所述喷射器出口端间的通道上的第一单向阀、设置在所述压缩组件的第四端与所述第一节流装置另一端间的通道上的第二单向阀以及控制器，其中：
所述第一单向阀的流通方向是从所述喷射器的出口端到所述压缩组件的第三端；
所述第二单向阀的流通方向是从所述压缩组件的第四端到所述第一节流装置另一端；
所述流向控制阀在制冷剂从所述压缩组件的第一端流向所述室外换热器的一端时处于导通状态；
所述控制器，用于根据当前的工作模式控制所述第一电磁阀、所述第二电磁阀以及所述第三电磁阀的开启与关闭。
第二方面，本公开实施例提供了一种空调器，该空调器包括第一方面所提供的采用喷射器的空调热泵系统。
第三方面，本公开实施例提供了一种空调器控制方法，该方法应用于第二方面提供的空调器，该方法包括：
所述空调器中的控制器根据当前的工作模式控制所述空调器中的所述第一电磁阀、所述第二电磁阀以及所述第三电磁阀的开启与关闭。
附图说明
为了更清楚地说明本公开实施例的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本公开的一些实施例，对于本领域普通技术人 员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1为本公开一实施例提供的采用喷射器的空调热泵系统的结构示意图；
图2为本公开一实施例提供的压缩组件的结构示意图；
图3为本公开另一实施例提供的采用喷射器的空调热泵系统的结构示意图；
图4为本公开实施例提供的图3对应采用喷射器的空调热泵系统在制冷模式下的制冷剂流向图；
图5为本公开实施例提供的图3对应采用喷射器的空调热泵系统在普通制热模式下的制冷剂流向图；
图6为本公开实施例提供的图3对应采用喷射器的空调热泵系统在低温制热模式下的制冷剂流向图；
图7为本公开又一实施例提供的采用喷射器的空调热泵系统的结构示意图；
图8为本公开实施例提供的图7对应采用喷射器的空调热泵系统在制冷模式下的制冷剂流向图；
图9为本公开实施例提供的图7对应采用喷射器空调热泵系统在制热模式下的制冷剂流向图；
图10为本公开实施例提供的空调器的示意图。
具体实施方式
下面将结合本公开实施例中的附图，对本公开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一部分实施例，而不是全部的实施例。基于本公开中的实施例，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。
为了使本领域的技术人员更好的理解本公开的技术方案，下面结合附图和具体实施例对本公开作进一步的详细说明。
本公开实施例中，除非另有明确的规定和限制，术语“设置”“相 连”、“连接”等术语应做广义理解，例如，可以是固定连接，也可以是拆卸连接，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，也可以是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公开中的具体含义。
空调热泵系统通常会增加喷射器来回空调系统的收膨胀功，以降低压缩机运转的耗功。具体地，喷射器将经其喷射入口进入的高压制冷剂经过喷射器内部喷嘴的节流降压形成低压环境，从而吸引喷射器的引射入口的低压制冷剂进入喷射器的吸气腔混合，再经过混合段和扩散段的作用，最终形成压力居中的制冷剂，从而提高压缩机的吸气口压力，降低了压缩机的耗功。
但是，增加有喷射器的空调系统通常只能实现制冷模式，而无法实现制热模式。
为实现制冷模式和制热模式，本公开实施例提供了一种采用喷射器的空调热泵系统。如图1所示，该采用喷射器的空调热泵系统包括压缩组件01、室外换热器02、第一节流装置03、室内换热器04以及喷射器05。该喷射器05包括三个端口，即喷射入口05a、引射入口05b以及出口端05c。其中，该喷射器05的喷射入口05a与室内换热器04的一端连通，喷射器05的引射入口05b与室外换热器02的一端连通，且喷射器05的出口端05c与压缩组件01的第三端连通。压缩组件01的第一端与室外换热器02的一端连通，且压缩组件01的第二端与室内换热器04的另一端连通。第一节流装置03一端与室外换热器02的另一端连通，第一节流装置03另一端与室内换热器04的一端连通。
此外，该采用喷射器的空调热泵系统还包括：设置在压缩组件01第一端与室外换热器02的一端之间的通道上的流向控制阀06、设置在喷射器05的引射入口05b与室外换热器02的一端之间的通道上的第一电磁阀07、设置在第一节流装置03另一端与室内换热器04的一端之间的通道上的第二电磁阀08、设置在喷射器05的喷射入口05a 与室内换热器04的一端之间的通道上的第三电磁阀09、设置在压缩组件01第三端与喷射器05的出口端05c之间的通道上的第一单向阀10、设置在压缩组件01第四端与第一节流装置03另一端之间的通道上的第二单向阀11、以及控制器12。
其中，流向控制阀06在制冷剂从压缩组件01的第一端流向室外换热器02的一端时处于导通状态。第一单向阀10的流通方向是从喷射器05的出口端05c到压缩组件01的第三端。第二单向阀11的流通方向是从压缩组件01的第四端到第一节流装置03的另一端。控制器12用于根据当前的工作模式控制上述第一电磁阀07、第二电磁阀08和第三电磁阀09的开启与关闭。
示例性地，控制器12可以以通用处理器实现，该通用处理器执行存储在非暂时性存储器中的机器可读指令，使得其可执行本文详细描述的功能。在其他示例中，该控制器可以在诸如专用集成电路(ASIC)等的专用处理器中实现，该专用处理器被配置为执行本文详细描述的功能。
示例性地，当上述采用喷射器的空调热泵系统为家用空调系统(即仅包含一个室内换热器04)时，第一节流装置03可采用毛细管或者电子膨胀阀，同时，如图1和图3所示，室内换热器04另一端与压缩组件01第二端之间的通道上设置有气侧截止阀13，且室内换热器04的一端与第二电磁阀08之间的通道上设置有液侧截止阀14。
当采用喷射器的空调热泵系统为多联机系统时(即具备多个室内换热器04)时，此时该第一节流装置03为电子膨胀管，同时，如图3所示，所述多个室内换热器04另一端与压缩组件01第二端之间的通道上设置的气侧截止阀13通过气侧分歧管15与所述多个室内换热器04连接，在所述多个室内换热器04一端与第二电磁阀08之间的通道上设置的液侧截止阀14通过液侧分歧管16与所述多个室内换热器04连接。
可选地，当采用喷射器的空调热泵系统为多联机系统时，如图3所示，本公开实施例中的采用喷射器的空调热泵系统还包括多个第二 节流装置17，所述多个第二节流装置17中每个设置在液侧截止阀14与所述多个室内换热器04中相应一个的一端之间的通道上。
所述多个第二节流装置17中的每个用于控制所述多个室内换热器04中相应一个与喷射器05的喷射入口05a之间的通道中的制冷剂的流量。
示例性地，如图2所示，本公开实施例中的压缩组件01包括压缩机011、分离器012以及四通阀013。其中，压缩机011包括排气口011a和吸气口011b。分离器012包括气态出口端012a、液态出口端012b以及入口端012c。四通阀013包括第一端口013a、第二端口013b、第三端口013c和第四端口013d。
第一端口013a与压缩机011的排气口011a连通。第二端口013b与室外换热器02的一端连通。第三端口013c与分离器012的入口端012c连通。第四端口013d与室内换热器04的另一端连通。压缩机011的吸气口011b与分离器012的气态出口端012a连通。分离器012的液态出口端012b与第一节流装置03的另一端连通。
示例性地，参照3所示的本公开另一实施例提供的采用喷射器的空调热泵系统的结构示意图，当上述的流向控制阀06为第四电磁阀18时，上述控制器12还用于控制第四电磁阀18的开启与关闭。在一示例中，该控制器12用于：在制冷模式下，控制第四电磁阀18与第二电磁阀08开启通路，并控制第一电磁阀07、第三电磁阀09关闭通路；或者，在普通制热模式下，控制第四电磁阀18与第二电磁阀08开启通路，并控制第一电磁阀07、第三电磁阀09关闭通路；或者在低温制热模式下，控制第四电磁阀18与第二电磁阀08关闭通路，并控制第一电磁阀07、第三电磁阀09开启通路。
在一示例中，根据如图4所示的制冷模式下的制冷剂流向图可知，在该制冷模式下，压缩机011将低温低压气态制冷剂压缩为高温高压气态制冷剂，并将该高温高压气态制冷剂经排气口011a排出。该高温高压气态制冷剂依次经过四通阀013的第一端口013a与第二端口013b以及第四电磁阀18，进入室外换热器02。此时室外换热器02作 为冷凝器，将该高温高压气态制冷剂冷凝为中温高压液态制冷剂。接着，该中温高压液态制冷剂进入到第一节流装置03中，对该制冷剂进行降压。接着，该液态制冷剂流经第二电磁阀08、液侧截止阀14、液侧分歧管16和第二节流装置17，进入到室内换热器04中，该室内换热器04作为蒸发器，将低温低压液态制冷剂蒸发为低温低压气态制冷剂，对室内环境换热制冷，之后制冷剂依次经过气侧分歧管15、气侧截止阀13、四通阀013的第四端口013d与第三端口013c以及分离器012的入口端012c，进入到分离器012中。
需要说明的是，在上述制冷模式下，喷射器05不工作。
在一示例中，根据如图5所示的普通制热模式下的制冷剂流向图可知，在该普通制热模式下，压缩机011将低温低压气态制冷剂压缩为高温高压气态制冷剂，并将该高温高压气态制冷剂经排气口011a排出。该高温高压气态制冷剂依次经过四通阀013的第一端口013a与第四端口013d、气侧截止阀13和气侧分歧管15，进入室内换热器04中。室内换热器04作为冷凝器，将高温高压气态制冷剂冷凝为中温高压液态制冷剂，对室内环境进行制热。之后该液态制冷剂依次流经第二节流装置17、液侧分歧管16、液侧截止阀14、第二电磁阀08以及第一节流装置03进入室外换热器02。室外换热器02作为蒸发器，将该液态制冷剂蒸发为气态制冷剂。该气态制冷剂依次流经第四电磁阀18、四通阀013的第二端口013b与第三端口013c以及分离器012的入口端012c，进入到分离器012中。
需要说明的是，在该普通制热模式下，喷射器05不工作。
在一示例中，根据如图6所示的低温制热模式下的制冷剂流向图可知，压缩机011的排气口011a排出的高温高压气态制冷剂依次流经四通阀013的第一端口013a与第四端口013d，经过气侧截止阀13与气侧分歧管15进入室内换热器04。室内换热器04作为冷凝器，将高温高压气态制冷剂冷凝为中温高压液态制冷剂，并对室内进行供热。接着，该液态制冷剂流经第二节流装置17、液侧分歧管16、液侧截止阀14和第三电磁阀09进入喷射器05的喷射入口05a，经过喷射器05 内部喷嘴的节流降压形成低压环境，进而吸引喷射器05的引射入口05b的制冷剂进入喷射器05。混合后的制冷剂经过喷射器05的混合段和扩散段的作用，提升喷射器05的出口压力。接着，喷射器05的出口端05c流出的制冷剂经过第一单向阀10进入分离器012的入口端012c。从分离器012的气态出口端012a流出的气态制冷剂进入压缩机011，进而提升压缩机011的吸气压力。从分离器012的液态出口端012b流出的液态制冷剂，依次流经第二单向阀11、第一节流装置03、室外换热器02和第一电磁阀07后回到喷射器05的引射入口05b。
需要说明的是，在该低温制热模式下，喷射器05工作。
示例性地，参照7所示的本公开又一实施例提供的采用喷射器的空调热泵系统的结构示意图，当上述的流向控制阀06为第三单向阀19时，上述采用喷射器的空调热泵系统还包括第四单向阀20，该第四单向阀20设置在四通阀013的第三端口013c与分离器012的入口端012c之间的通道上。该第三单向阀19的流通方向是从四通阀013的第二端口013b到室外换热器02的一端，第四单向阀20的流通方向是从四通阀013的第三端口013c到分离器012的入口端012c。在一示例中，上述控制器用于：在制冷模式下，控制第二电磁阀08开启通路，并控制第一电磁阀07与第三电磁阀09关闭通路；在制热模式下，控制第一电磁阀07、第三电磁阀09开启通路，并控制第二电磁阀08关闭通路。
在一示例中，根据如图8所示的制冷模式下的制冷剂流向图可知，四通阀013第三端口013c与分离器012的入口端012c之间的通道导通，因此图8对应的制冷剂的流通过程与图4对应的制冷剂流通过程相同，这里不再赘述。
在一示例中，根据如图9所示的制热模式下的制冷剂流向图可知，图9对应的制冷剂的流通过程与图6对应的制冷剂流通过程相同，这里不再赘述。
本公开实施例提供的采用喷射器的空调热泵系统，在空调热泵系统中增加了设置在压缩组件01的第一端与室外换热器02的一端之 间的通道上的流向控制阀06、设置在喷射器05引射入口05b与室外换热器02一端之间的通道上的第一电磁阀07、设置在第一节流装置03另一端与室内换热器04一端之间的通道上的第二电磁阀08、设置在喷射器05喷射入口05a与室内换热器04一端之间的通道上的第三电磁阀09、设置在压缩组件01的第三端与喷射器05出口端05c之间通道上的第一单向阀10、设置在压缩组件01的第四端与第一节流装置03的另一端之间通道上的第二单向阀11、以及控制器12，从而在不同的工作模式下通过该控制器12控制上述第一电磁阀07、第二电磁阀08和第三电磁阀09的开启与关闭来实现制冷模式与制热模式。
本公开实施例提供了一种空调器100，如图10所示，该空调器100包括上述的采用喷射器的空调热泵系统。
示例性地，上述的空调器100的组成结构以及该空调器100中各部件的描述，可以参照上述的采用喷射器的空调热泵系统的描述，这里不再赘述。
下面将基于上述实施例中对采用喷射器的空调热泵系统的相关描述对本公开实施例提供的一种空调器控制方法进行介绍。以下实施例中与上述实施例相关的技术术语、概念等的说明可以参照上述的实施例，这里不再赘述。
本公开实施例提供的该空调器控制方法包括：
301、空调器中的控制器根据当前的工作模式控制空调器中的流向控制阀、第一电磁阀、第二电磁阀以及第三电磁阀的开启与关闭。
可选地，当空调器中的流向控制阀为第四电磁阀时，控制器还用于控制第四电磁阀的开启与关闭，步骤301包括如下步骤：
301a、在制冷模式下，控制第四电磁阀与第二电磁阀开启通路，并控制第一电磁阀与第三电磁阀关闭通路。
301b、在普通制热模式下，控制第四电磁阀与第二电磁阀开启通路，并控制第一电磁阀与第三电磁阀关闭通路。
301c、在低温制热模式下，控制第四电磁阀与第二电磁阀关闭通路，并控制第一电磁阀与第三电磁阀开启通路。
可选地，当空调器中的流向控制阀为第三单向阀时，第三单向阀的流通方向是从压缩组件的第一端流向室外换热器的一端，上述的空调器中还包括第四单向阀，第四单向阀的流通方向是从四通阀第三端口流向分离器的入口端。此时，步骤302包括如下步骤：
302a、在制冷模式下，控制第二电磁阀开启通路，并控制第一电磁阀与第三电磁阀关闭通路。
302b、在制热模式下，控制第一电磁阀与第三电磁阀开启通路，并控制第二电磁阀关闭通路。
本公开实施例提供的空调器控制方法，通过在空调热泵系统中增加设置在压缩组件的第一端与室外换热器的一端间的通道上的流向控制阀、设置在喷射器引射入口与室外换热器一端间的通道上的第一电磁阀、设置在第一节流装置另一端与室内换热器一端间的通道上的第二电磁阀、设置在喷射器喷射入口与室内换热器一端间的通道上的第三电磁阀、设置在压缩组件的第三端与喷射器出口端间通道上的第一单向阀、设置在压缩组件的第四端与第一节流装置的另一端间通道上的第二单向阀以及控制器，从而在不同的工作模式下通过该控制器控制上述第一电磁阀、第二电磁阀、第三电磁阀的开启与关闭来实现制冷模式与制热模式。
以上所述，以上实施例仅用以说明本申请的技术方案，而非对其限制；尽管参照前述实施例对本申请进行了详细的说明，本领域的普通技术人员应当理解：其依然可以对前述各实施例所记载的技术方案进行修改，或者对其中部分技术特征进行等同替换；而这些修改或者替换，并不使相应技术方案的本质脱离本申请各实施例技术方案的精神和范围。

Claims (10)

  1. 一种采用喷射器的空调热泵系统，包括压缩组件、室外换热器、第一节流装置、室内换热器以及喷射器，所述喷射器的喷射入口与所述室内换热器的一端连通，所述喷射器的引射入口与所述室外换热器的一端连通，所述喷射器的出口端与所述压缩组件的第三端连通，所述压缩组件的第一端与所述室外换热器的一端连通，所述压缩组件的第二端与所述室内换热器的另一端连通，所述第一节流装置的一端与所述室外换热器的另一端连通，另一端与所述室内换热器的一端连通，其中，
    所述采用喷射器的空调热泵系统还包括：设置在所述压缩组件的第一端与所述室外换热器的一端间的通道上的流向控制阀、设置在所述引射入口与所述室外换热器的一端间的通道上的第一电磁阀、设置在所述第一节流装置的另一端与所述室内换热器的一端间的通道上的第二电磁阀、设置在所述喷射入口与所述室内换热器的一端间的通道上的第三电磁阀、设置在所述压缩组件的第三端与所述喷射器的出口端间的通道上的第一单向阀、设置在所述压缩组件的第四端与所述第一节流装置的另一端间的通道上的第二单向阀、以及控制器，其中：
    所述第一单向阀的流通方向是从所述喷射器的出口端到所述压缩组件的第三端；
    所述第二单向阀的流通方向是从所述压缩组件的第四端到所述第一节流装置的另一端；
    所述流向控制阀在制冷剂从所述压缩组件的第一端流向所述室外换热器的一端时处于导通状态；
    所述控制器配置为，根据当前的工作模式控制所述第一电磁阀、所述第二电磁阀以及所述第三电磁阀的开启与关闭。
  2. 根据权利要求1所述的采用喷射器的空调热泵系统，其中，所述压缩组件包括压缩机、分离器以及四通阀，所述压缩机包括吸气口和排气口，所述分离器包括液态出口端、气态出口端以及入口端，所述四通阀包括第一端口、第二端口、第三端口和第四端口，其中：
    所述第一端口与所述压缩机的排气口连通；所述第二端口与所述室 外换热器的一端连通；所述第三端口与所述分离器的入口端连通；所述第四端口与所述室内换热器的另一端连通；
    所述压缩机的吸气口与所述分离器的气态出口端连通，所述分离器的液态出口端与所述第一节流装置的另一端连通。
  3. 根据权利要求1或2所述的采用喷射器的空调热泵系统，其中，当所述流向控制阀为第四电磁阀时，所述控制器还配置为，根据当前的工作模式控制所述第四电磁阀的开启与关闭。
  4. 根据权利要求3所述的采用喷射器的空调热泵系统，其中，所述控制器配置为：
    在制冷模式下，控制所述第四电磁阀与所述第二电磁阀开启通路，并控制所述第一电磁阀与所述第三电磁阀关闭通路；
    在普通制热模式下，控制所述第四电磁阀与所述第二电磁阀开启通路，并控制所述第一电磁阀与所述第三电磁阀关闭通路；
    在低温制热模式下，控制所述第四电磁阀与所述第二电磁阀关闭通路，并控制所述第一电磁阀与所述第三电磁阀开启通路。
  5. 根据权利要求1或2所述的采用喷射器的空调热泵系统，其中，当所述流向控制阀为第三单向阀时，所述第三单向阀的流通方向是从所述压缩组件的第一端流向所述室外换热器的一端；所述采用喷射器的空调热泵系统还包括第四单向阀，所述第四单向阀设置在所述四通阀的第三端口与所述分离器的入口端间的通道上，所述第四单向阀的流通方向是从所述压缩组件的第三端口流向所述分离器的入口端；
    所述控制器配置为：
    在制冷模式下，控制所述第二电磁阀开启通路，并控制所述第一电磁阀与所述第三电磁阀关闭通路；
    在制热模式下，控制所述第一电磁阀与所述第三电磁阀开启通路，并控制所述第二电磁阀关闭通路。
  6. 根据权利要求1所述的采用喷射器的空调热泵系统，其中，所述采用喷射器的空调热泵系统还包括第二节流装置，其中：
    所述第二节流装置用于，控制所述室内换热器与所述喷射器的喷射 入口间的通道中的制冷剂的流量。
  7. 一种空调器，包括权利要求1-6任一项所述的采用喷射器的空调热泵系统。
  8. 一种空调器控制方法，应用于权利要求7所述的空调器，所述方法包括：
    所述空调器中的控制器根据当前的工作模式控制所述空调器中的所述第一电磁阀、所述第二电磁阀以及所述第三电磁阀的开启与关闭。
  9. 根据权利要求8所述的方法，其中，当所述空调器中的流向控制阀为第四电磁阀时，所述空调器中的控制器根据当前的工作模式控制所述第一电磁阀、所述第二电磁阀以及所述第三电磁阀的开启与关闭；所述控制器还用于根据当前的工作模式控制所述第四电磁阀的开启与关闭，所述控制器用于：
    在制冷模式下，控制所述第四电磁阀与所述第二电磁阀开启通路，并控制所述第一电磁阀与所述第三电磁阀关闭通路；
    在普通制热模式下，控制所述第四电磁阀与所述第二电磁阀开启通路，并控制所述第一电磁阀与所述第三电磁阀关闭通路；
    在低温制热模式下，控制所述第四电磁阀与所述第二电磁阀关闭通路，并控制所述第一电磁阀与所述第三电磁阀开启通路。
  10. 根据权利要求8所述的方法，其中，当所述空调器中的流向控制阀为第三单向阀，所述第三单向阀的流通方向是从所述压缩组件的第一端流向所述室外换热器的一端；且所述空调器还包括第四单向阀时，所述第四单向阀设置在所述四通阀的第三端口与所述分离器的入口端间的通道上，所述第四单向阀的流通方向是从所述四通阀的第三端口流向所述分离器的入口端：
    所述空调器中的控制器根据当前的工作模式控制所述空调器中的所述第一电磁阀、所述第二电磁阀以及所述第三电磁阀的开启与关闭，包括：
    在制冷模式下，控制所述第二电磁阀开启通路，并控制所述第一电磁阀与所述第三电磁阀关闭通路；
    在制热模式下，控制所述第一电磁阀与第三电磁阀开启通路，并控制所述第二电磁阀关闭通路。
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