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WO2021208584A1 - 高效制热的风冷热泵空调系统 - Google Patents

高效制热的风冷热泵空调系统 Download PDF

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Publication number
WO2021208584A1
WO2021208584A1 PCT/CN2021/076511 CN2021076511W WO2021208584A1 WO 2021208584 A1 WO2021208584 A1 WO 2021208584A1 CN 2021076511 W CN2021076511 W CN 2021076511W WO 2021208584 A1 WO2021208584 A1 WO 2021208584A1
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WO
WIPO (PCT)
Prior art keywords
gas
heat exchanger
valve
liquid separator
air
Prior art date
Application number
PCT/CN2021/076511
Other languages
English (en)
French (fr)
Inventor
张洪亮
任滔
张捷
赵雷
谢吉培
徐志强
张国成
Original Assignee
青岛海尔空调电子有限公司
海尔智家股份有限公司
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Publication of WO2021208584A1 publication Critical patent/WO2021208584A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • 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
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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

Definitions

  • the invention belongs to the technical field of air conditioning, and specifically provides an air-cooled heat pump air-conditioning system for efficient heating.
  • the prior art increases the saturation evaporation temperature and the heat exchange temperature difference of the air by reducing the opening of the expansion valve and reducing the suction pressure.
  • the reduction in suction pressure will reduce the density of the low-pressure side refrigerant, and then reduce the quality and flow of the refrigerant sucked by the compressor, resulting in a decrease in the unit's heating capacity and poor energy efficiency.
  • the present invention provides an air-cooled heat pump air-conditioning system with high-efficiency heating.
  • the air-conditioning system includes a compressor, a first heat exchanger, a second heat exchanger, a directional control valve, and a main expansion valve.
  • the air conditioning system further includes a gas-liquid separator; the second heat exchanger is divided into an upper circuit and a lower circuit that are independent of each other, the upper circuit is connected to the liquid phase port of the gas-liquid separator, and the lower circuit Connected with the gas-phase port of the gas-liquid separator, the main circuit expansion valve connects the first heat exchanger and the gas-liquid mixing port of the gas-liquid separator, and the flow of the upper loop is larger than that of the lower portion
  • the flow of the circuit under refrigeration conditions, the directional control valve is located in the first working position to control the high-pressure side of the compressor to communicate with both the upper circuit and the lower circuit, and the low-pressure of the compressor Side is connected to the first heat exchanger; under heating conditions, the directional control valve is located in the second working position to control the high-pressure side of the compressor to communicate with the first heat exchanger.
  • the low pressure side of the compressor communicates with both the upper circuit and the lower circuit.
  • the flow control device is a parallel assembly of a one-way valve and a capillary tube, and the capillary tube is used to throttle the refrigerant flowing from the lower loop into the gas-liquid separator under refrigeration conditions, and the one-way The valve is used to directly conduct the refrigerant flowing from the gas-liquid separator into the lower circuit under heating conditions.
  • the air conditioning system further includes a three-way valve, a defrost switch valve, and the air conditioning system corresponding to each of the second heat exchangers.
  • Liquid separator the three-way valve is arranged between the high-pressure side of the compressor, the directional control valve and the corresponding second heat exchanger, and is used to control the second heat exchanger Selectively communicate with the high-pressure side of the compressor or communicate with the directional control valve;
  • the defrost switch valve is arranged between the high-pressure side of the compressor and the three-way valve for controlling the compression The high-pressure side of the engine is cut off or connected to the three-way valve.
  • the air-conditioning system further includes a refrigeration switch valve and a bypass expansion valve assembly arranged in parallel, and the refrigeration switch valve and bypass expansion valve assembly arranged in parallel are used to connect each of the forward check valves in series with the bypass expansion valve assembly.
  • the main circuit expansion valve when each of the second heat exchangers is in a cooling mode, the cooling switch valve is opened, and the second expansion valve is closed; each of the second heat exchangers is located in the heating Under working conditions, the refrigeration on-off valve is closed and the second expansion valve is closed; when at least one of the second heat exchangers is in a defrosting state, the refrigeration on-off valve is closed and the second expansion valve is activated.
  • each of the lower circuits and the corresponding gas-liquid separator are connected by a flow control device, and the flow control device is used to throttle the flow from the lower circuit into the gas-liquid separator under refrigeration conditions.
  • the refrigerant that flows into the lower circuit from the gas-liquid separator is directly conducted under heating conditions.
  • the flow control device is a parallel assembly of a one-way valve and a capillary tube, and the capillary tube is used to throttle the refrigerant flowing from the lower circuit into the gas-liquid separator under refrigeration conditions.
  • the valve is used to directly conduct the refrigerant flowing from the gas-liquid separator into the lower circuit under heating conditions.
  • the liquid-phase port of the gas-liquid separator is arranged at the bottom thereof, the gas-phase port of the gas-liquid separator is arranged on the top thereof, and the gas-liquid mixing port of the gas-liquid separator is arranged at its middle part.
  • the gas-liquid two-phase refrigerant formed by the main circuit expansion valve throttling is separated into gaseous refrigerant and liquid in the gas-liquid separator After the refrigerant, it flows into the independent upper and lower circuits of the second heat exchanger to participate in heat exchange, ensuring that the upper circuit is basically pure liquid refrigerant, and the lower circuit is basically pure gaseous refrigerant. Ground, because the flow of the upper circuit is greater than the flow of the lower circuit, the liquid refrigerant can more fully exchange heat and thus be more thoroughly evaporated, thereby improving the heating capacity of the air conditioning system under various working conditions.
  • Fig. 2 is a schematic structural diagram of a second embodiment of the air-cooled heat pump air-conditioning system for efficient heating of the present invention.
  • Fig. 3 is a schematic structural diagram of a third embodiment of the air-cooled heat pump air-conditioning system for efficient heating of the present invention.
  • Fig. 4 is a schematic structural diagram of a fourth embodiment of the air-cooled heat pump air-conditioning system for efficient heating of the present invention.
  • FIG. 1 the figure is a schematic structural diagram of a first embodiment of an air-cooled heat pump air-conditioning system with high-efficiency heating according to the present invention.
  • the air-cooled heat pump air conditioning system includes a compressor CP, a first heat exchanger EH1, a second heat exchanger EH2, a directional control valve, a main expansion valve XV1, and a gas-liquid separator GLS.
  • the second heat exchanger EH2 is divided into separate upper loop EH2U and lower loop EH2B; the upper loop EH2U is connected with the liquid phase port of the gas-liquid separator GLS, and the lower loop EH2B is connected with the gas phase port of the gas-liquid separator GLS,
  • the main expansion valve XV1 connects the gas-liquid mixing port of the first heat exchanger EH1 and the gas-liquid separator GLS, and the flow of the upper loop EH2U is greater than the flow of the lower loop EH2B, which refers to the length of the upward flow path along the refrigerant flow.
  • the directional control valve is preferably a four-way valve 4DCV.
  • the four-way valve 4DCV has four ports.
  • the four ports are the first port, the second port, the third port, and the fourth port.
  • the first port It is connected with the high pressure side of the compressor CP through a pipeline
  • the second interface is connected with the port of the first heat exchanger EH1 through a pipeline
  • the third interface is connected with the port of the upper circuit EH2U and the port of the lower circuit EH2B through a pipeline.
  • the fourth interface and the low pressure side of the compressor CP are connected by pipelines.
  • the spool moves relative to the valve body until the first port and the third port are connected, and the second port and the fourth port are connected.
  • the high-pressure side and the upper part of the compressor CP The circuit EH2U and the lower circuit EH2B are connected, the low pressure side of the compressor CP is connected with the first heat exchanger EH1, and the air-cooled heat pump air conditioning system enters the refrigeration mode.
  • the refrigerant circulation process is: compressor CP ⁇ four-way valve 4DCV ⁇ divided into two paths, one flow into the upper circuit EH2U, the other flow into the lower circuit EH2B ⁇ gas-liquid separator GLS ⁇ main circuit expansion valve XV1 ⁇ first heat exchanger EH1 ⁇ four-way valve 4DCV ⁇ compressor CP.
  • the working principle of the refrigeration condition of this air conditioning system is: the low-temperature and low-pressure refrigerant vapor is compressed into high-temperature, high-pressure and superheated vapor through the compressor CP, and the gaseous refrigerant flow enters the upper part of the second heat exchanger EH2 after passing through the four-way valve 4DCV
  • the circuit EH2U and the lower circuit EH2B transfer heat to the air through heat exchange.
  • the refrigerant is condensed into a high-temperature and high-pressure liquid, flows through the gas-liquid separator GLS, and is throttled by the main circuit expansion valve XV1 to become saturated refrigeration.
  • the air-conditioning system continuously circulates to produce cold water and dissipate heat into the air.
  • the spool moves relative to the valve body to communicate with the first port and the second port, and the third port is connected with the fourth port, that is, the high-pressure side of the compressor CP is connected to the first port.
  • the heater EH1 is connected, and the low pressure side of the compressor CP is connected to both the upper circuit EH2U and the lower circuit EH2B, and the air conditioning system enters the heating mode.
  • the liquid refrigerant flows into the upper circuit EH2U of the second heat exchanger EH2, exchanges heat with the external environment, absorbs heat and evaporates to form a gaseous refrigerant; at the same time, the gaseous refrigerant sequentially flows through the lower circuit EH2B and the four-way valve 4DCV It is then sucked into the compressor CP.
  • the air-conditioning system continuously circulates to produce hot water and absorb heat from the air.
  • FIG. 2 is a schematic structural diagram of a second embodiment of an air-cooled heat pump air-conditioning system with high-efficiency heating according to the present invention.
  • the air-cooled heat pump air conditioning system includes a compressor CP, a first heat exchanger EH1, a second heat exchanger EH2, a directional control valve, a main expansion valve XV1, a gas-liquid separator GLS, and a flow control device.
  • the second heat exchanger EH2 is divided into an upper loop EH2U and a lower loop EH2B that are independent of each other, and the flow of the upper loop EH2U is greater than the flow of the lower loop EH2B.
  • the upper circuit EH2U is connected with the liquid phase port of the gas-liquid separator GLS
  • the lower circuit EH2B is connected with the gas-phase port of the gas-liquid separator GLS through a flow control device.
  • the flow control device is used for throttling by the lower circuit EH2B under refrigeration conditions.
  • the refrigerant flowing into the gas-liquid separator GLS and the refrigerant flowing from the gas-liquid separator GLS into the lower circuit EH2B are directly conducted under heating conditions.
  • the parallel assembly of the one-way valve CV and the capillary tube MV is used in this embodiment to flexibly realize the flow control of the refrigerant in different flow directions between the lower loop EH2B and the gas-liquid separator GLS, with simple structure and low cost.
  • the flow control device can also be a flow control valve such as an electronic expansion valve on the basis of satisfying the flow control function when the refrigerant flows in different directions between the lower circuit and the gas-liquid separator GLS.
  • the directional control valve is preferably a four-way valve 4DCV.
  • the four-way valve 4DCV has four ports.
  • the four ports are the first port, the second port, the third port, and the fourth port. ;
  • the first interface and the high pressure side of the compressor CP are connected by pipelines
  • the second interface and the port of the first heat exchanger EH1 are connected by pipelines
  • the third interface is connected to the port of the upper circuit EH2U and the port of the lower circuit EH2B
  • the two are connected by pipelines
  • the fourth port and the low pressure side of the compressor CP are connected by pipelines.
  • the refrigerant circulation process is: compressor CP ⁇ four-way valve 4DCV ⁇ divided into two paths, one flowing through the upper circuit EH2U, and the other flowing through the lower circuit EH2B and capillary MV in turn ⁇ gas-liquid separator GLS ⁇ main expansion valve XV1 ⁇ first heat exchanger EH1 ⁇ four-way valve 4DCV ⁇ compressor CP.
  • the working principle of the refrigeration conditions of this system is: the low-temperature and low-pressure refrigerant vapor is compressed into high-temperature, high-pressure and superheated vapor through the compressor CP, and the gaseous refrigerant flows into the upper circuit of the second heat exchanger EH2 after passing through the four-way valve 4DCV.
  • EH2U and the lower circuit EH2B one refrigerant flows directly into the gas-liquid separator GLS after heat exchange in the upper circuit EH2U, and the other refrigerant flows into the gas-liquid separator GLS after heat exchange through the capillary MV after the heat exchange in the lower circuit EH2B.
  • the air-conditioning system continuously circulates to produce cold water and dissipate heat into the air.
  • the spool moves relative to the valve body to communicate with the first port and the second port, and the third port is connected with the fourth port, that is, the high-pressure side of the compressor CP is connected to the first port.
  • the heater EH1 is connected, the low pressure side of the compressor CP is connected with both the upper circuit EH2U and the lower circuit EH2B, and the air conditioning system enters the heating mode.
  • the refrigerant circulation process is: compressor CP ⁇ four-way valve 4DCV ⁇ first heat exchanger EH1 ⁇ main expansion valve XV1 ⁇ gas-liquid separator GLS ⁇ divided into two paths, one flow into the upper part In the circuit EH2U, the other circuit flows through the one-way valve CV and the lower circuit EH2B ⁇ four-way valve DCV4 ⁇ compressor CP in turn.
  • the working principle of the heating condition of this system is: the low-temperature and low-pressure refrigerant vapor is compressed into high-temperature and high-pressure superheated vapor through the compressor CP, and the gaseous refrigerant flow enters the first heat exchanger EH1 after passing through the four-way valve 4DCV.
  • the heat exchange transfers heat to the circulating water.
  • the refrigerant is condensed into a high-temperature and high-pressure liquid, which is throttled by the main expansion valve XV1 to form a gas-liquid two-phase refrigerant, which is then processed into a gas-liquid two-phase refrigerant by the gas-liquid separator GLS Liquid refrigerant and gaseous refrigerant.
  • the liquid refrigerant flows into the upper circuit EH2U of the second heat exchanger EH2 and exchanges heat with the external environment, absorbing heat and evaporating to form a gaseous refrigerant; at the same time, the gaseous refrigerant flows through the check valve CV, the lower circuit EH2B and The four-way valve 4DCV is sucked into the compressor CP.
  • the air-conditioning system continuously circulates to produce hot water and absorbs heat from the air.
  • FIG. 3 is a schematic structural diagram of a third embodiment of a separate cooling heat pump air-conditioning system with high-efficiency heating according to the present invention. It should be noted that, in order to improve the readability of this article, this article only elaborates on the differences between the third embodiment and the second embodiment. For the similarities, please refer to the relevant records of the aforementioned second embodiment. Those skilled in the art can realize this scheme without any doubt.
  • the difference between the third embodiment and the second embodiment is: the number of second heat exchangers of the air conditioning system provided by the third embodiment is two, and the two second heat exchangers are arranged in parallel. Each second heat exchanger is divided into an upper circuit and a lower circuit independent of each other.
  • this article uses the location words “front” and “rear” to distinguish the two second heat exchangers, and the location words “front” and “rear” are set based on the compressor in Figure 3 Among the two second heat exchangers, the second heat exchanger on the compressor side is the front second heat exchanger EH2f, and the second heat exchanger far from the compressor is the rear second heat exchanger EH2b. It should be noted that the orientation words "front” and “rear” are only set to distinguish the two second heat exchangers, and the setting of these orientation words does not limit the scope of protection of this patent.
  • the upper circuit of the front second heat exchanger EH2f has two connection ports, namely the first upper connection port and the second upper connection port; the lower circuit of the front second heat exchanger EH2f also has two connections Ports are the first lower connection port and the second lower connection port; the upper circuit of the second rear heat exchanger EH2b has two connection ports, the third upper connection port and the fourth upper connection port, respectively; The lower circuit of the second heat exchanger EH2b also has two connection ports, namely the third lower connection port and the fourth lower connection port.
  • the refrigerant from the compressor CP flows into the first collecting valve through the four-way valve 4DCV, and is divided into four paths in the collecting valve, and then flows into the upper part of the front second heat exchanger EH2f.
  • the upper circuit of the front second heat exchanger EH2f, the lower circuit of the front second heat exchanger EH2f, the upper circuit of the rear second heat exchanger EH2b, and the rear second heat exchanger flows into the first collecting valve through the corresponding four pipelines, flows into the four-way valve 4DCV after the first collecting valve merges, and is finally sucked into the compressor CP.
  • Both the upper circuit of the front second heat exchanger EH2f and the upper circuit of the rear second heat exchanger EH2b are connected to the gas-liquid separator through a second collecting valve.
  • the second upper connection port is connected to the first port of the second collecting valve
  • the fourth upper connection port is connected to the second connection port of the second collecting valve
  • the liquid phase port of the gas-liquid separator GLS is connected to the second connection port of the second collecting valve.
  • the third connection port of the collecting valve communicates.
  • Both the lower circuit of the front second heat exchanger EH2f and the lower circuit of the rear second heat exchanger EH2b are connected in parallel with the check valve CV and the capillary MV through a third collecting valve.
  • the second lower connecting port is connected to the first port of the third collecting valve
  • the fourth lower connecting port is connected to the second port of the third collecting valve
  • the cut-off port of the one-way valve CV is connected to the third collecting valve.
  • the third port of the valve is in communication
  • a port of the capillary tube MV is in communication with the fourth port of the third collecting valve.
  • the parallel assembly of the check valve CV and the capillary MV is connected to the gas-liquid separator GLS through the fourth collecting valve.
  • the conduction port of the one-way valve CV communicates with the first port of the fourth collecting valve
  • the other port of the capillary MV communicates with the second port of the fourth collecting valve
  • the gas-phase port of the gas-liquid separator GLS communicates with The third port of the fourth collecting valve is in communication.
  • the refrigerant in the upper circuit of the front second heat exchanger EH2f and the upper circuit of the rear second heat exchanger EH2b flows into the second collecting valve, in the second collecting valve After being collected, it flows into the gas-liquid separator through the liquid phase outlet;
  • the refrigerant in the lower circuit of the front second heat exchanger EH2f and the lower circuit of the rear second heat exchanger EH2b flows into the third collecting valve, After the flow in the collecting valve is converged, it is throttled by the capillary MV and then flows into the fourth collecting valve, and then flows into the gas-liquid separator GLS from the fourth collecting valve.
  • the gaseous refrigerant flows through the fourth collecting valve and the check valve CV in turn into the third collecting valve.
  • the three-collecting valve flows into the lower circuit of the second heat exchanger EH2f at the front and the lower circuit of the second heat exchanger EH2b at the rear.
  • the liquid refrigerant flows into the second collecting valve and flows into the second collecting valve. After being split, it flows into the upper circuit of the front second heat exchanger EH2f and the upper circuit of the rear second heat exchanger EH2b.
  • the air-cooled heat pump air conditioning system in the third embodiment adopts two sets of second heat exchangers, which has the characteristics of large heat exchange area and high heating performance.
  • this figure is a fourth embodiment of an air-cooled heat pump air-conditioning system with high-efficiency heating according to the present invention.
  • the air-conditioning system includes a compressor CP, a first heat exchanger EH1, a directional control valve, and a main expansion valve XV1, and Three second heat exchangers are arranged in parallel with each other, and each second heat exchanger is divided into an upper circuit and a lower circuit independent of each other.
  • this article uses the location words “front”, “ ⁇ ” and “ ⁇ ” to distinguish the three second heat exchangers, and the location words “front”, “ ⁇ ” and “ ⁇ ” are shown in Figure 4 Set based on the middle compressor, among the three second heat exchangers, the second heat exchanger on the compressor side is the front second heat exchanger EH2f, and the second heat exchanger far away from the compressor is the rear
  • the second heat exchanger EH2b located between the front second heat exchanger EH2f and the rear second heat exchanger EH2b is the middle second heat exchanger EH2m.
  • the orientation words “front”, “middle” and “rear” are only set to distinguish the three second heat exchangers, and these orientation words do not limit the scope of protection of this patent.
  • the air conditioning system also includes a first three-way valve 3DCV1 and a second three-way valve 3DCV1 and a second three-way valve respectively corresponding to the front second heat exchanger EH2f, the middle second heat exchanger EH2m, and the rear second heat exchanger EH2b.
  • the first three-way valve DCV31 is arranged between the high pressure side of the compressor CP, the directional control valve and the front second heat exchanger EH2f to control the front second heat exchanger EH2f to be selectively connected to the compressor
  • the high-pressure side of the CP may be connected to the directional control valve.
  • the first defrost switch valve SV1 is arranged between the high-pressure side of the compressor CP and the first three-way valve 3DCV1 to control the high-pressure side of the compressor CP and the first three-way valve 3DCV1 to cut off or conduct.
  • the second three-way valve 3DCV2 is set between the high pressure side of the compressor CP, the four-way valve 4DCV and the second heat exchanger EH2m in the middle to control the second heat exchanger EH2m in the middle to be selectively connected to the compressor
  • the high pressure side of the CP or the directional control valve is connected.
  • the second defrost switch valve SV2 is arranged between the high-pressure side of the compressor CP and the second three-way valve 3DCV2 to control the high-pressure side of the compressor CP and the second three-way valve 3DCV2 to cut off or conduct.
  • the third three-way valve 3DCV3 is arranged between the high pressure side of the compressor CP, the directional control valve and the third second heat exchanger EH3 to control the rear second heat exchanger EH2b to be selectively connected to the compressor CP
  • the high-pressure side or the four-way valve 4DCV is connected.
  • the third defrost switch valve SV3 is arranged between the high-pressure side of the compressor CP and the third three-way valve 3DCV3 to control the high-pressure side of the compressor CP and the third three-way valve 3DCV3 to cut off or conduct.
  • the air conditioning system also includes a first gas-liquid separator GLS1 and a second gas-liquid separator GLS2 respectively corresponding to the front second heat exchanger EH2f, the middle second heat exchanger EH2m, and the rear second heat exchanger EH2b.
  • the circuit is connected; the gas-liquid mixing port of the third gas-liquid separator GLS3 communicates with the main expansion valve XV1, and the liquid-phase port of the third gas-liquid separator GLS3 communicates with the upper circuit of the rear second heat exchanger EH2b.
  • the air conditioning system also includes a first flow control device; the first flow control device is arranged between the lower loop of the front second heat exchanger EH2f and the gas phase port of the first gas-liquid separator GLS1 for Under refrigeration conditions, the refrigerant that flows from the lower loop of the front second heat exchanger EH2f to the first gas-liquid separator GLS1 is throttled, and under heating conditions, it is directly connected to the first gas-liquid separator GLS1.
  • the refrigerant in the lower circuit of the front second heat exchanger EH2f is arranged between the lower loop of the front second heat exchanger EH2f and the gas phase port of the first gas-liquid separator GLS1 for Under refrigeration conditions, the refrigerant that flows from the lower loop of the front second heat exchanger EH2f to the first gas-liquid separator GLS1 is throttled, and under heating conditions, it is directly connected to the first gas-liquid separator GLS1.
  • the air conditioning system also includes a second flow control device, which is arranged between the lower loop of the second heat exchanger EH2m in the middle and the gas phase port of the second gas-liquid separator GLS2, and is used for cooling under cooling conditions.
  • the refrigerant flows from the lower loop of the second heat exchanger EH2m in the middle to the second gas-liquid separator GLS2, and in heating conditions, it is directly connected from the second gas-liquid separator GLS2 to the lower part of the second heat exchanger EH2m in the middle.
  • the refrigerant in the circuit is arranged between the lower loop of the second heat exchanger EH2m in the middle and the gas phase port of the second gas-liquid separator GLS2, and is used for cooling under cooling conditions.
  • the refrigerant flows from the lower loop of the second heat exchanger EH2m in the middle to the second gas-liquid separator GLS2, and in heating conditions, it is directly connected from the second gas-liquid separator GLS2 to the lower part of the second heat exchanger
  • the air-cooled heat pump air conditioning system also includes a third flow control device; the third flow control device is arranged between the lower loop of the second rear heat exchanger EH2b and the gas-phase port of the third gas-liquid separator GLS3 for cooling Under working conditions, the refrigerant flowing from the lower circuit of the second rear heat exchanger EH2b to the third gas-liquid separator GLS3 is throttled, and under heating conditions, it is directly connected from the third gas-liquid separator GLS3 to the rear second gas-liquid separator. The refrigerant in the lower circuit of the second heat exchanger EH2b.
  • the first flow control device in this embodiment preferably adopts a parallel assembly of the first check valve CV1 and the first capillary tube MV1.
  • a gas-liquid separator GLS1 flows into the refrigerant in the lower circuit of the front second heat exchanger EH2f.
  • the first capillary tube MV1 is used to throttle the flow from the lower circuit of the front second heat exchanger EH2f to the first under cooling conditions.
  • the second flow control device also preferably adopts the parallel assembly of the second one-way valve CV2 and the second capillary tube MV2.
  • the second one-way valve CV2 is used to directly conduct the second gas-liquid separator under heating conditions GLS2 flows into the refrigerant in the lower circuit of the second heat exchanger EH2m in the middle.
  • the second capillary MV2 is used to throttle the refrigerant flowing from the lower circuit of the second heat exchanger EH2m in the middle to the second gas-liquid separator GLS2 under cooling conditions. .
  • the third flow control device also preferably adopts a parallel assembly of a third check valve CV3 and a third capillary MV3.
  • the third check valve CV3 is used for heating conditions and is directly connected to the rear by the third gas-liquid separator GLS3
  • the refrigerant in the lower circuit of the second heat exchanger EH2b, and the third capillary MV3 is used to throttle the refrigerant flowing from the lower circuit of the rear second heat exchanger EH2b to the third gas-liquid separator GLS3 under cooling conditions.
  • the gas-liquid mixing port of the first gas-liquid separator GLS1 and the main expansion valve XV1 are connected through a parallel assembly formed by a fourth forward check valve CV4 and a fifth reverse check valve CV5;
  • the fourth positive check valve CV4 allows the refrigerant to flow from the first gas-liquid separator GLS1 to the main expansion valve XV1
  • the fifth reverse check valve CV5 allows the refrigerant to flow from the main expansion valve XV1 to the first gas-liquid Separator GLS1.
  • the gas-liquid mixing port of the second gas-liquid separator GLS2 is connected to the main expansion valve XV1 through the parallel assembly formed by the sixth positive check valve CV6 and the seventh reverse check valve CV7; among them, the sixth positive
  • the check valve CV6 allows the refrigerant to flow from the second gas-liquid separator GLS2 to the main expansion valve XV1
  • the seventh reverse check valve CV7 allows the refrigerant to flow from the main expansion valve XV1 to the second gas-liquid separator GLS2.
  • the gas-liquid mixing port of the third gas-liquid separator GLS3 is connected to the main expansion valve XV1 through the parallel assembly formed by the eighth forward check valve CV8 and the ninth reverse check valve CV9; wherein, the eighth forward one-way The valve CV8 allows the refrigerant to flow from the third gas-liquid separator GLS3 to the main expansion valve XV1, and the ninth reverse check valve CV9 allows the refrigerant to flow from the main expansion valve XV1 to the third gas-liquid separator GLS3.
  • the air conditioning system of this embodiment further includes a refrigeration switching valve SV4 and a bypass expansion valve XV2 assembly arranged in parallel, and the refrigeration switching valve SV4 and a bypass expansion valve XV2 assembly arranged in parallel are used for connecting each component in series. Positive check valve and main circuit expansion valve.
  • the directional control valve is preferably a four-way valve 4DCV.
  • the four-way valve 4DCV has four ports.
  • the four ports are the first port, the second port, the third port, and the fourth port.
  • the first port It communicates with the high-pressure side of the compressor CP through a pipeline
  • the second interface communicates with the port of the first heat exchanger EH1 through a pipeline
  • the third interface communicates with the front second heat exchanger EH2f, the middle second heat exchanger EH2m and
  • the rear second heat exchanger EH2b is in communication
  • the fourth port is in communication with the low pressure side of the compressor CP through a pipeline.
  • the four-way valve 4DCV has two working positions, which are a first working position and a second working position, respectively.
  • the spool moves relative to the valve body to communicate with the first port and the third port.
  • the high-pressure side of the compressor CP is connected to the front second heat exchanger EH2f, and the middle second heat exchanger EH2f.
  • the heat exchanger EH2m and the rear second heat exchanger EH2b are connected, the low pressure side of the compressor CP is connected with the first heat exchanger EH1, and the air-cooled heat pump air conditioning system enters the cooling mode.
  • the first defrost switch valve SV1, the second defrost switch valve SV2, the third defrost switch valve SV3, and the bypass main circuit expansion valve XV12 are all in the closed state, and the refrigeration switch valve SV4 is opened.
  • the refrigerant cycle process is: compressor CP ⁇ 4 four-way valve DCV ⁇ first three-way valve 3DCV1, second three-way valve 3DCV2 and third three-way valve 3DCV3 ⁇ divided into two ways, one way flows into the front part of the second heat exchange
  • the lower circuit of the second heat exchanger EH2m in the middle and the second capillary MV2, the lower circuit of the second heat exchanger EH2b in the rear and the third capillary MV3 ⁇ the first gas-liquid separator GLS1, the second gas-liquid separator GLS2 and the second Three gas-liquid separator GLS3 ⁇ fourth positive one-way valve CV4, sixth positive one-way valve CV6, eighth positive one-way valve CV
  • the working principle of the refrigeration mode of the air conditioning system is: the low-temperature and low-pressure refrigerant vapor is compressed into high-temperature, high-pressure and superheated vapor through the compressor CP.
  • a second heat exchanger transfers heat to the air through heat exchange, and the refrigerant is condensed into a high-temperature and high-pressure liquid refrigerant; then the refrigerant flows through the capillary tubes, gas-liquid and gas-liquid corresponding to the second heat exchangers.
  • the separator refrigerant and the check valve flow into the main expansion valve XV1 through the refrigeration switch valve SV4. After converging in the main expansion valve XV1, the refrigerant that becomes saturated is throttled and enters the first heat exchanger. EH1 evaporates and absorbs heat into low-temperature superheated vapor, and finally returns to the compressor CP through the four-way valve 4DCV.
  • the air-conditioning system continuously circulates to produce cold water and dissipate heat into the air.
  • the first defrost switch valve SV1, the second defrost switch valve SV2, the third defrost switch valve SV3, the refrigeration switch valve SV4, and the bypass valve XV2 are all in a closed state.
  • the refrigerant cycle process is: compressor CP ⁇ four-way valve 4DCV ⁇ first heat exchanger EH1 ⁇ main expansion valve XV1 ⁇ fifth reverse check valve CV5, seventh reverse check valve CV7, ninth reverse One-way valve CV9 ⁇ first gas-liquid separator GLS1, second gas-liquid separator GLS2, and third gas-liquid separator GLS3 ⁇ divided into two paths, one way flows into the upper circuit of the front second heat exchanger EH2f, the middle part
  • the working principle of the heating mode of the air conditioning system is: the low-temperature and low-pressure refrigerant vapor is compressed into high-temperature, high-pressure superheated vapor through the compressor CP, and the gaseous refrigerant flow enters the first heat exchanger EH1 after passing through the four-way valve 4DCV, The heat is transferred to the circulating water through heat exchange, the refrigerant is condensed into a high-temperature and high-pressure liquid, which is throttled by the main expansion valve XV1 to form a gas-liquid two-phase refrigerant, and then passes through the fifth reverse check valve CV5, The seventh reverse check valve CV7 and the ninth reverse check valve CV9 respectively flow into the corresponding three gas-liquid separators, and the gas-liquid separation process of each gas-liquid separator is processed into liquid refrigerant and gaseous refrigerant.
  • the liquid refrigerant flows into the upper circuit of the second heat exchanger corresponding to each gas-liquid separator and exchanges heat with the external environment, absorbs heat and evaporates to form a gaseous refrigerant; at the same time, the gaseous refrigerant flows through the first A one-way valve CV1, a second one-way valve CV2, and a third one-way valve CV3 enter the lower circuit corresponding to the second heat exchanger, and finally flow through the four-way valve 4DCV and be sucked into the compressor CP.
  • the air-conditioning system continuously circulates to produce hot water and absorb heat from the air.
  • the air conditioning system can defrost the three second heat exchangers one by one.
  • the one-way valve CV4 enters the main pipeline after being throttled by the bypass expansion valve XV2, mixed with the refrigerant after being throttled by the main expansion valve XV1, and then enters the other central second heat exchanger EH2m working in the heating state And the second heat exchanger EH2b at the rear for evaporation.
  • the refrigerant condenses in the upper and lower circuits of the middle second heat exchanger EH2m, and then flows through the second gas-liquid separator GLS2 and the sixth forward direction.
  • the high-pressure gas refrigerant enters the rear second heat exchanger EH2b to start defrosting.
  • the refrigerant condenses in the upper and lower circuits of the rear second heat exchanger EH2b, and then flows through the third gas-liquid separator GLS3 and the eighth
  • this air conditioning system only defrosts one second heat exchanger, and then defrosts other second heat exchangers after the defrosting of the second heat exchanger is completed. Therefore, during the defrosting process, the air-conditioning system still maintains a heating cycle, and will not absorb heat from the first heat exchanger EH1 for defrosting, so that the user's water temperature fluctuations during the entire defrosting process are small and the comfort is guaranteed.
  • the fourth positive one-way valve CV4, the sixth positive one-way valve CV6 and the eighth positive one-way valve CV8 of the air conditioning system can also be directly connected to the high-pressure pipeline of the main circuit expansion valve XV1.
  • the second heat exchanger in the defrosting state completely relies on the pressure self-balance of the air conditioning system to discharge liquid, but the liquid discharge speed is relatively slow and the defrosting time is longer.
  • the air-cooled heat pump air conditioning system in this embodiment includes three second heat exchangers, and it can be understood that the number of second heat exchangers is not limited to three. According to actual needs, the air-cooled heat pump air-conditioning system can adopt two or more heat exchangers, and each second heat exchanger is arranged in parallel. Among them, multiple refers to an integer greater than or equal to 3, such as 3, 4, 5, 6, 7, and so on. In addition, when the air-cooled heat pump air conditioning system includes two or multiple second heat exchangers other than 3, the connection relationship between each second heat exchanger and other devices is similar to that of the aforementioned two second heat exchangers. Those skilled in the art can achieve this without any doubt based on the above description, so this article will not repeat them here.
  • the gas-liquid two-phase refrigerant formed by the main circuit expansion valve throttling is separated into gaseous refrigerant and liquid refrigerant in the gas-liquid separator And then flow into the independent upper and lower circuits of the second heat exchanger to participate in heat exchange, ensuring that the upper circuit is basically pure liquid refrigerant, and the lower circuit is basically pure gaseous refrigerant. Because the flow of the upper circuit is greater than that of the lower circuit, the liquid refrigerant can more fully exchange heat and thus be more thoroughly evaporated, thereby improving the heating capacity of the air conditioning system under various working conditions.
  • the one-way valve is closed under refrigeration conditions, and the liquid refrigerant flows through the gas-liquid separator and the main expansion valve in turn after being throttled by the capillary tube, and then enters the first heat exchanger.
  • this can limit the flow of refrigerant from the lower loop to the gas-liquid separator, so as to prevent a large amount of uncondensed gaseous refrigerant from entering the gas-liquid separator due to excessive refrigerant flow.
  • the refrigerant flows into the lower circuit from the gas-liquid separator through the one-way valve bypass under the heating condition, which ensures the smooth flow of the refrigerant under the heating condition, thereby ensuring the normal progress of the entire refrigeration condition.
  • the difference between the saturated evaporation temperature and the air heat exchange temperature is reduced, the frosting temperature of the unit is reduced, the defrosting cycle is prolonged, and the operating range of the unit is expanded.
  • the lower loop of the second heat exchanger is gaseous refrigerant, the heat exchange is smaller, the temperature is higher than the upper loop, and the amount of frosting is smaller.
  • the temperature of the lower circuit of the second heat exchanger is also higher than that of the upper circuit, so that the frost layer melts quickly, so that the defrosting drainage is smoother, thereby improving the defrosting drainage effect.
  • the lower loop of the second heat exchanger can also be used for condensation heat exchange, so that the heat exchange area of the second heat exchanger can be fully utilized.

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Abstract

本发明涉及空调技术，具体提供一种高效制热的风冷热泵空调系统，旨在解决现有空调换热器内气液两相制冷剂分配不均匀的问题。为此，本发明的空调系统包括压缩机、第一换热器、第二换热器、方向控制阀、主路膨胀阀和气液分离器，第二换热器被分为相互独立的上部回路和下部回路，并且上部回路的流程大于下部回路。在制热工况下，经主路膨胀阀节流形成的气液两相制冷剂在气液分离器中分离为气态制冷剂和液态制冷剂，然后分别流入第二换热器中的下部回路和上部回路，由于上部回路的流程大于下部回路，第二换热器内的液态制冷剂能够更充分地进行热交换，并因此被更充分地蒸发，从而提升空调系统在各种工况下的制热能力。

Description

高效制热的风冷热泵空调系统 技术领域
本发明属于空调技术领域，具体提供一种高效制热的风冷热泵空调系统。
背景技术
风冷热泵空调系统，是空调行业内区别于风冷冷水系统的一种空调系统机组。除具备风冷冷水系统制取冷水的功能外，风冷热泵空调系统还能切换到制热工况制取热水。风冷热泵空调系统的基本原理是基于压缩式制冷循环，利用制冷剂作为载体，通过风机的强制换热，从大气中吸取热量或者排放热量，以达到制冷或者制热的需求。
在实际使用中，风冷热泵空调系统在制热工况下，换热器表面经常出现结霜不均匀的现象，这种现象会降低系统的制热性能。经本领域技术人员分析发现，造成这种现象的原因是制冷剂经过节流装置后，由高温液态制冷剂变为气液两相状态，不管设计多么精良的分液器都难以将气液混合的两相流体均匀地分配给换热器。制冷剂分配不均匀，导致换热器的部分回路中液态制冷剂分配过多，过多的液态制冷剂在换热过程中无法完全蒸发，继而使得这部分回路所在换热器表面霜层相对较厚。
为了使液态制冷剂分配较多的回路中的制冷剂能够完全蒸发，现有技术中通过减小膨胀阀开度，降低吸气压力，来增加饱和蒸发温度和空气的换热温差。但是，吸气压力降低，将会减小低压侧制冷剂密度，继而降低压缩机吸入的制冷剂质量和流量，致使机组制热量下降，能效变差。
因此，本领域技术人员亟待另辟蹊径找到一种新的技术手段，来解决换热器内气液两相制冷剂分配不均匀的问题。
发明内容
为了解决上述技术问题，本发明提供了一种高效制热的风冷热泵空调系统，该空调系统包括压缩机、第一换热器、第二换热器、方向控制阀和主路膨胀阀，所述空调系统还包括气液分离器；所述第二换热器分为相互独立的上部回路和下部回路，所述上部回路与所述气液分离器的液相端口连通，所 述下部回路与所述气液分离器的气相端口连通，所述主路膨胀阀连接所述第一换热器和所述气液分离器的气液混合端口，并且所述上部回路的流程大于所述下部回路的流程；在制冷工况下，所述方向控制阀位于第一工作位置，以控制所述压缩机的高压侧与所述上部回路和所述下部回路两者连通，所述压缩机的低压侧与所述第一换热器连通；在制热工况下，所述方向控制阀位于第二工作位置，以控制所述压缩机的高压侧与所述第一换热器连通，所述压缩机的低压侧与所述上部回路和所述下部回路两者连通。
优选地，所述下部回路和所述气液分离器通过流量控制装置连接，所述流量控制装置用于在制冷工况下节流由所述下部回路流入所述气液分离器的制冷剂，以及在制热工况下直接导通由所述气液分离器流入所述下部回路的制冷剂。
优选地，所述流量控制装置为单向阀和毛细管的并联组件，所述毛细管用于在制冷工况下节流由所述下部回路流入所述气液分离器的制冷剂，所述单向阀用于在制热工况下直接导通由所述气液分离器流入所述下部回路的制冷剂。
优选地，所述第二换热器的数量为两个或多个，且两个或多个所述第二换热器并联设置。
优选地，所述第二换热器的数量为两个或多个，所述空调系统还包括与每个所述第二换热器对应设置的三通阀、除霜开关阀和所述气液分离器；所述三通阀设置于所述压缩机的高压侧、所述方向控制阀和对应的所述第二换热器三者之间，用于控制所述第二换热器可选择地与所述压缩机的高压侧连通或者与所述方向控制阀连通；所述除霜开关阀设置于所述压缩机的高压侧与所述三通阀之间，用于控制所述压缩机的高压侧和所述三通阀的截止或导通。
优选地，每个所述气液分离器的入口与所述主路膨胀阀通过由正向单向阀和反向单向阀构成的并联组件连接；其中，正向单向阀允许制冷剂由对应的所述气液分离器流向所述主路膨胀阀，反向单向阀允许制冷剂由所述主路膨胀阀流向对应的所述气液分离器。
优选地，所述空调系统还包括并联设置的制冷开关阀和旁路膨胀阀组件，所述并联设置的制冷开关阀和旁路膨胀阀组件用于串联每个所述正向单向阀与所述主路膨胀阀；每个所述第二换热器均位于制冷工况时，所述制冷开关阀开启，所述第二膨胀阀关闭；每个所述第二换热器均位于制热工况时， 所述制冷开关阀关闭，所述第二膨胀阀关闭；至少一个所述第二换热器位于除霜状态时，所述制冷开关阀关闭，所述第二膨胀阀启动。
优选地，每个所述下部回路和对应的所述气液分离器通过流量控制装置连接，所述流量控制装置用于在制冷工况下节流由所述下部回路流入所述气液分离器的制冷剂，以及在制热工况下直接导通由所述气液分离器流入所述下部回路的制冷剂。
优选地，所述流量控制装置为单向阀和毛细管的并联组件，所述毛细管用于在制冷工况下节流由所述下部回路流入所述气液分离器的制冷剂，所述单向阀用于在制热工况下直接导通由所述气液分离器流入所述下部回路的制冷剂。
优选地，所述气液分离器的液相端口设置在其底部，所述气液分离器的气相端口设置在其顶部，所述气液分离器的气液混合端口设置在其中部。
与现有技术相比，本发明所提供的空调系统，在制热工况下，经主路膨胀阀节流形成的气液两相制冷剂在气液分离器中分离为气态制冷剂和液态制冷剂后，再分别流入第二换热器中相互独立的上部回路和下部回路内参与热交换，保证了上部回路基本上为纯液态制冷剂，下部回路内基本上为纯气态制冷剂，相应地，由于上部回路的流程大于下部回路的流程，使得液态制冷剂能够更充分地进行热交换并因此被更彻底地蒸发，从而提升空调系统在各种工况下的制热能力。
附图说明
图1是本发明的高效制热的风冷热泵空调系统的第一实施方式的结构示意图。
图2是本发明的高效制热的风冷热泵空调系统的第二实施方式的结构示意图。
图3是本发明的高效制热的风冷热泵空调系统的第三实施方式的结构示意图。
图4是本发明的高效制热的风冷热泵空调系统的第四实施方式的结构示意图。
具体实施方式
下面参照附图来描述本发明的优选实施方式。本领域技术人员应当理解的是，这些实施方式仅仅用于解释本发明的技术原理，并非旨在限制本发明的保护范围。
需要说明的是，在本发明的描述中，术语“上”、“下”、等指示的方向或位置关系的术语是基于附图所示的方向或位置关系，这仅仅是为了便于描述，而不是指示或暗示所述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”、“第三”仅用于描述目的，而不能理解为指示或暗示相对重要性。
如图1所示，图中为本发明高效制热的风冷热泵空调系统第一实施例的结构示意图。该风冷热泵空调系统包括压缩机CP、第一换热器EH1、第二换热器EH2、方向控制阀、主路膨胀阀XV1和气液分离器GLS。
其中，第二换热器EH2分为相互独立的上部回路EH2U和下部回路EH2B；上部回路EH2U与气液分离器GLS的液相端口连通，下部回路EH2B与气液分离器GLS的气相端口连通，主路膨胀阀XV1连接第一换热器EH1和气液分离器GLS的气液混合端口，并且上部回路EH2U的流程大于下部回路EH2B的流程，流程是指沿制冷剂流向上流道的长度。
继续参见1，方向控制阀优选为四通阀4DCV，四通阀4DCV具有四个接口，这四个接口分别为第一接口、第二接口、第三接口和第四接口；其中，第一接口和压缩机CP的高压侧通过管路连接，第二接口和第一换热器EH1的端口通过管路连接，第三接口与上部回路EH2U的端口和下部回路EH2B的端口两者通过管路连接，第四接口和压缩机CP的低压侧通过管路连接。
该四通阀4DCV具有两个工作位置，这两个工作位置分别为第一工作位置和第二工作位置。
当四通阀4DCV位于第一工作位置时，阀芯相对于阀体移动至第一接口和第三接口导通，第二接口和第四接口导通，此时压缩机CP的高压侧与上部回路EH2U和下部回路EH2B两者连通，压缩机CP的低压侧与第一换热器EH1连通，该风冷热泵空调系统进入制冷工况。
在制冷工况下，制冷剂的循环流程为：压缩机CP→四通阀4DCV→分为两路，一路流入上部回路EH2U，另一路流入下部回路EH2B→气液分离器GLS→主路膨胀阀XV1→第一换热器EH1→四通阀4DCV→压缩机CP。
本空调系统制冷工况的工作原理是：通过压缩机CP把低温低压的制冷剂蒸气压缩为高温高压过热的蒸气，气态制冷剂流通过四通阀4DCV后进入到第二换热器EH2的上部回路EH2U和下部回路EH2B，通过热交换把热量传递到空气中去，制冷剂冷凝为高温高压的液体，流经气液分离器GLS，通过主路膨胀阀XV1节流后变为饱和状态的制冷剂，然后进入到第一换热器EH1蒸发吸热变为低温过热蒸气，再通过四通阀4DCV回到压缩机CP。空调系统不断循环制取冷水，把热量散发到空气中去。
当四通阀4DCV切换至第二工作位置时，阀芯相对于阀体移动至第一接口和第二接口连通，第三接口与第四接口连通，即压缩机CP的高压侧与第一换热器EH1连通，压缩机CP的低压侧与上部回路EH2U和下部回路EH2B两者连通，该空调系统进入制热工况。
在制热工况下，制冷剂的循环流程为：压缩机CP→四通阀DCV4→第一换热器EH1→主路膨胀阀XV1→气液分离器GLS→分为两路，一路流入上部回路EH2U，另一路流入下部回路EH2B→四通阀4DCV→压缩机CP。
本空调系统制热工况的工作原理是：通过压缩机CP把低温低压的制冷剂蒸气压缩为高温高压过热的蒸气，气态制冷剂流通过四通阀4DCV后进入到第一换热器EH1，通过热交换把热量传递到循环水中去，制冷剂冷凝为高温高压的液体，再由主路膨胀阀XV1节流处理后形成气液两相制冷剂，随后由气液分离器GLS气液分离为液态制冷剂和气态制冷剂。其中，液态制冷剂经流入第二换热器EH2的上部回路EH2U，与外部环境热交换，吸热蒸发形成气态制冷剂；与此同时，气态制冷剂依次流经下部回路EH2B和四通阀4DCV后被吸入压缩机CP内。空调系统不断循环制取热水，从空气中吸收热量。
继续参见图1，气液分离器GLS的液相端口设置在其底部，气液分离器GLS的气相端口设置在其顶部，气液分离器GLS的气液混合端口设置在其中部。
参见图2，该图为本发明高效制热的风冷热泵空调系统第二实施方式的结构示意图。该风冷热泵空调系统包括压缩机CP、第一换热器EH1、第二换热器EH2、方向控制阀、主路膨胀阀XV1、气液分离器GLS和流量控制装置。
其中，第二换热器EH2分为相互独立的上部回路EH2U和下部回路EH2B，且上部回路EH2U的流程大于下部回路EH2B的流程。上部回路 EH2U与气液分离器GLS的液相端口连通，下部回路EH2B通过流量控制装置与气液分离器GLS的气相端口连通，该流量控制装置用于在制冷工况下节流由下部回路EH2B流入气液分离器GLS的制冷剂，以及在制热工况下直接导通由气液分离器GLS流入下部回路EH2B的制冷剂。
优选地，本实施方式中流量控制装置为单向阀CV和毛细管MV的并联组件；其中，毛细管MV用于在制冷工况下节流由下部回路EH2B流入气液分离器GLS的制冷剂，单向阀CV用于在制热工况下直接导通由气液分离器GLS流入下部回路EH2B的制冷剂。
可以理解，本实施方式中采用单向阀CV和毛细管MV的并联组件，灵活地实现了制冷剂在下部回路EH2B和气液分离器GLS之间不同流向时的流量控制，结构简单，成本低。当然，在满足控制制冷剂在下部回路和气液分离器GLS之间不同流向时的流量控制功能的基础上，该流量控制装置也可以为电子膨胀阀等流量控制阀。
继续参见图2，本实施方式中，方向控制阀优选为四通阀4DCV，四通阀4DCV具有四个接口，这四个接口分别为第一接口、第二接口、第三接口和第四接口；其中，第一接口和压缩机CP的高压侧通过管路连接，第二接口和第一换热器EH1的端口通过管路连接，第三接口与上部回路EH2U的端口和下部回路EH2B的端口两者通过管路连接，第四接口和压缩机CP的低压侧通过管路连接。
四通阀4DCV具有两个工作位置，这两个工作位置分别为第一工作位置和第二工作位置。当四通阀4DCV位于第一工作位置时，阀芯相对于阀体移动至第一接口和第三接口连通，此时压缩机CP的高压侧与上部回路EH2U和下部回路EH2B两者连通，压缩机CP的低压侧与第一换热器EH1连通，该空调系统进入制冷工况。
在制冷工况下，制冷剂的循环流程为：压缩机CP→四通阀4DCV→分为两路，一路流经上部回路EH2U，另一路依次流经下部回路EH2B和毛细管MV→气液分离器GLS→主路膨胀阀XV1→第一换热器EH1→四通阀4DCV→压缩机CP。
本系统制冷工况的工作原理是：通过压缩机CP把低温低压的制冷剂蒸气压缩为高温高压过热的蒸气，气态制冷剂流通过四通阀4DCV后分别流入第二换热器EH2的上部回路EH2U和下部回路EH2B，一路制冷剂在上部回路EH2U热交换后直接流入气液分离器GLS，另一路在下部回路EH2B热交 换后经毛细管MV节流后流入气液分离器GLS，两路制冷剂汇合后流入主路膨胀阀XV1，经节流后变为饱和状态的制冷剂，该制冷剂流入到第一换热器EH1蒸发吸热气变为低温过热蒸气，最后经四通阀4DCV流回压缩机CP。空调系统不断循环制取冷水，把热量散发到空气中去。
当四通阀4DCV切换至第二工作位置时，阀芯相对于阀体移动至第一接口和第二接口连通，第三接口与第四接口连通，即压缩机CP的高压侧与第一换热器EH1连通，压缩机CP的低压侧与上部回路EH2U和下部回路EH2B两者连通，空调系统进入制热工况。
在制热工况下，制冷剂的循环流程为：压缩机CP→四通阀4DCV→第一换热器EH1→主路膨胀阀XV1→气液分离器GLS→分为两路，一路流入上部回路EH2U，另一路依次流经单向阀CV和下部回路EH2B→四通阀DCV4→压缩机CP。
本系统制热工况的工作原理是：通过压缩机CP把低温低压的制冷剂蒸气压缩为高温高压过热的蒸气，气态制冷剂流通过四通阀4DCV后进入到第一换热器EH1，通过热交换把热量传递到循环水中去，制冷剂冷凝为高温高压的液体，再由主路膨胀阀XV1节流处理后形成气液两相制冷剂，随后由气液分离器GLS气液分离处理为液态制冷剂和气态制冷剂。其中，液态制冷剂经流入第二换热器EH2的上部回路EH2U与外部环境热交换，吸热蒸发形成气态制冷剂；与此同时，气态制冷剂依次流经单向阀CV、下部回路EH2B和四通阀4DCV后被吸入压缩机CP内。空调系统不断循环制取热水，从空气中吸收热量。
参见图3，该图为本发明高效制热的分冷热泵空调系统第三实施方式的结构示意图。需要说明的是，为了提高本文的可读性，本文仅对第三实施方式相对于第二实施方式的区别点加以详细阐述，相同之处请参考前述第二实施方式的相关记载，根据前面记载本领域技术人员可以毫无疑义的实现该方案。
第三种实施方式相对于第二种实施方式的区别点为：第三种实施方式所提供空调系统的第二换热器的数量为两个，且这两个第二换热器并联设置，每个第二换热器分为相互独立的上部回路和下部回路。
为了便于说明，本文在此以方位词“前”和“后”来区分这两个第二换热器，且方位词“前”和“后”是以图3中压缩机为基准来设定，两个 第二换热器中靠近压缩机侧的第二换热器为前部第二换热器EH2f，远离压缩机侧的第二换热器为后部第二换热器EH2b。需要说明的是，方位词“前”和“后”仅是为了区分两个第二换热器而设定，这些方位词的设定并不限定本专利的保护范围。
详细地，前部第二换热器EH2f的上部回路具有两个连接口，分别为第一上连接口和第二上连接口；前部第二换热器EH2f的下部回路也具有两个连接口，分别为第一下连接口和第二下连接口；后部第二换热器EH2b的上部回路具有两个连接口，分别为第三上连接口和第四上连接口；后部第二换热器EH2b的下部回路也具有两个连接口，分别为第三下连接口和第四下连接口。
其中，第一上连接口、第一下连接口、第三上连接口和第三下连接口通过管路分别与第一集流阀的第一接口、第二接口、第三接口和第四接口连接，四通阀4DCV的第四接口通过管路与第一集流阀的第五接口连接。
如此设置，在制冷工况下，来自压缩机CP的制冷剂经由四通阀4DCV流入第一集流阀，在集流阀内分为四路后分别流入前部第二换热器EH2f的上部回路、前部第二换热器EH2f的下部回路、后部第二换热器EH2b的上部回路、后部第二换热器EH2b的下部回路。反之，在制热工况下，前部第二换热器EH2f的上部回路、前部第二换热器EH2f的下部回路、后部第二换热器EH2b的上部回路、后部第二换热器EH2b的下部回路内的制冷剂通过对应地四个管路流入第一集流阀内，在第一集流阀汇流后流入四通阀4DCV，最后被吸入压缩机CP内。
前部第二换热器EH2f的上部回路和后部第二换热器EH2b的上部回路两者通过第二集流阀与气液分离器连接。详细地，第二上连接口与第二集流阀的第一接口连通，第四上连接口与第二集流阀的第二连接口连通，气液分离器GLS的液相端口与第二集流阀的第三连接口连通。
前部第二换热器EH2f的下部回路和后部第二换热器EH2b的下部回路两者通过第三集流阀与单向阀CV和毛细管MV并联组件连接。详细地，第二下连接口与第三集流阀的第一接口连通，第四下连接口与第三集流阀的第二接口连接，单向阀CV的截止端接口与第三集流阀的第三接口连通，毛细管MV的一端口与第三集流阀的第四接口连通。
单向阀CV和毛细管MV并联组件通过第四集流阀与气液分离器GLS连接。详细地，单向阀CV的导通端口与第四集流阀的第一接口连通，毛细管MV的另一端口与第四集流阀的第二接口连通，气液分离器GLS的气相端口与第四集流阀的第三接口连通。
如此设置，在制冷工况下：前部第二换热器EH2f的上部回路和后部第二换热器EH2b的上部回路内的制冷剂流入第二集流阀，在第二集流阀内汇集后经由液相出口流入气液分离器内；前部第二换热器EH2f的下部回路和后部第二换热器EH2b的下部回路内的制冷剂流入第三集流阀，在第三集流阀内汇流后经由毛细管MV节流后流入第四集流阀，再由第四集流阀流入气液分离器GLS内。
反之，在制热工况下：气液分离器GLS内的制冷剂经气液分离后，气态制冷剂依次流经第四集流阀和单向阀CV流入第三集流阀内，在第三集流阀内分流后分别流入前部第二换热器EH2f的下部回路和后部第二换热器EH2b的下部回路；液态制冷剂流入第二集流阀内，在第二集流阀分流后分别流入前部第二换热器EH2f的上部回路和后部第二换热器EH2b的上部回路。
显然，第三实施方式中的风冷热泵空调系统采用两组第二换热器，具有换热面积大，制热性能高的特点。
需要说明的是，本实施方式中的风冷热泵空调系统包括两个第二换热器，可以理解，第二换热器的数量并不仅限于两个。根据实际需要上述风冷热泵空调系统可采用多个第二换热器，且每个第二换热器之间并联设置。其中，多个是指大于或等于3的整数，如3、4、5、6、7等。此外，风冷热泵空调系统包括多个第二换热器时，每个第二换热器与其他器件之间的连接关系与前述两个第二换热器的相似，本领域技术人员根据上面的说明可以毫无疑义地实现，故而本文在此不再赘述。
参见图4，该图为本发明高效制热的风冷热泵空调系统的第四实施方式，该空调系统包括压缩机CP、第一换热器EH1、方向控制阀和主路膨胀阀XV1，以及相互并联设置的三个第二换热器，且每个第二换热器分为相互独立的上部回路和下部回路。
为了便于说明，本文在此以方位词“前”、“中”和“后”来区分这三个第二换热器，且方位词“前”、“中”和“后”是以图4中压缩机为基准来设定，三个第二换热器中靠近压缩机侧的第二换热器为前部第二换热器 EH2f，远离压缩机侧的第二换热器为后部第二换热器EH2b，位于前部第二换热器EH2f和后部第二换热器EH2b之间的为中部第二换热器EH2m。需要说明的是，方位词“前”、“中”和“后”仅是为了区分三个第二换热器而设定，这些方位词并不限定本专利的保护范围。
继续参见图4，该空调系统还包括与前部第二换热器EH2f、中部第二换热器EH2m和后部第二换热器EH2b分别对应设置的第一三通阀3DCV1、第二三通阀3DCV2和第三三通阀3DCV3，以及与前部第二换热器EH2f、中部第二换热器EH2m和后部第二换热器EH2b分别对应设置的第一除霜开关阀SV1、第二除霜开关阀SV2和第三除霜开关阀SV3。
其中，第一三通阀DCV31设置于压缩机CP的高压侧、方向控制阀和前部第二换热器EH2f三者之间，以控制前部第二换热器EH2f可选择地与压缩机CP的高压侧或者与方向控制阀连通。第一除霜开关阀SV1设置于压缩机CP的高压侧和第一三通阀3DCV1之间，以控制压缩机CP的高压侧和第一三通阀3DCV1截止或导通。
同理，第二三通阀3DCV2设置于压缩机CP的高压侧、四通阀4DCV和中部第二换热器EH2m三者之间，以控制中部第二换热器EH2m可选择地与压缩机CP的高压侧或者方向控制阀连通。第二除霜开关阀SV2设置于压缩机CP的高压侧和第二三通阀3DCV2之间，以控制压缩机CP的高压侧与第二三通阀3DCV2截止或导通。
第三三通阀3DCV3设置于压缩机CP的高压侧、方向控制阀和第三第二换热器EH3三者之间，以控制后部第二换热器EH2b可选择地与压缩机CP的高压侧或者四通阀4DCV连通。第三除霜开关阀SV3设置于压缩机CP的高压侧和第三三通阀3DCV3之间，以控制压缩机CP的高压侧和第三三通阀3DCV3截止或导通。
该空调系统还包括与前部第二换热器EH2f、中部第二换热器EH2m和后部第二换热器EH2b分别对应设置的第一气液分离器GLS1、第二气液分离器GLS2和第三气液分离器GLS3；其中，第一气液分离器GLS1的气液混合端口与主路膨胀阀XV1连通，第一气液分离器GLS1的液相端口与前部第二换热器EH2f的上部回路连通；同理,第二气液分离器GLS2的气液混合端口与主路膨胀阀XV1连通，第二气液分离器GLS2的液相端口与中部第二换热器EH2m的上部回路连通；第三气液分离器GLS3的的气液混合端口 与主路膨胀阀XV1连通，第三气液分离器GLS3的液相端口与后部第二换热器EH2b的上部回路连通。
继续参见图4，该空调系统还包括第一流量控制装置；第一流量控制装置设置于前部第二换热器EH2f的下部回路与第一气液分离器GLS1的气相端口之间，用于在制冷工况下节流由前部第二换热器EH2f的下部回路流向第一气液分离器GLS1的制冷剂，以及在制热工况下直接导通由第一气液分离器GLS1流入前部第二换热器EH2f的下部回路的制冷剂。
该空调系统还包括第二流量控制装置，第二流量控制装置设置于中部第二换热器EH2m的下部回路与第二气液分离器GLS2的气相端口之间，用于在制冷工况下节流由中部第二换热器EH2m下部回路流向第二气液分离器GLS2的制冷剂，以及制热工况下直接导通由第二气液分离器GLS2流入中部第二换热器EH2m的下部回路的制冷剂。
该风冷热泵空调系统还包括第三流量控制装置；第三流量控制装置设置于后部第二换热器EH2b的下部回路与第三气液分离器GLS3的气相端口之间，用于在制冷工况下节流由后部第二换热器EH2b的下部回路流向第三气液分离器GLS3的制冷剂，以及制热工况下直接导通由第三气液分离器GLS3流入后部第二换热器EH2b的下部回路的制冷剂。
继续参见图4，本实施方式中第一流量控制装置优选采用第一单向阀CV1和第一毛细管MV1的并联组件，第一单向阀CV1用于在制热工况下直接导通由第一气液分离器GLS1流入前部第二换热器EH2f的下部回路的制冷剂，第一毛细管MV1用于在制冷工况下节流由前部第二换热器EH2f的下部回路流向第一气液分离器GLS1的制冷剂。
同理，第二流量控制装置也优选采用第二单向阀CV2和第二毛细管MV2的并联组件，第二单向阀CV2用于在制热工况下直接导通由第二气液分离器GLS2流入中部第二换热器EH2m下部回路的制冷剂，第二毛细管MV2用于在制冷工况下节流由中部第二换热器EH2m的下部回路流向第二气液分离器GLS2的制冷剂。
第三流量控制装置也优选采用第三单向阀CV3和第三毛细管MV3的并联组件，第三单向阀CV3用于制热工况下直接导通由第三气液分离器GLS3流入后部第二换热器EH2b的下部回路的制冷剂，第三毛细管MV3用于制冷工况下节流由后部第二换热器EH2b的下部回路流向第三气液分离器GLS3的制冷剂。
进一步地，继续参见图4，第一气液分离器GLS1的气液混合端口与主路膨胀阀XV1通过第四正向单向阀CV4和第五反向单向阀CV5形成的并联组件连接；其中，第四正向单向阀CV4允许制冷剂由第一气液分离器GLS1流向主路膨胀阀XV1，第五反向单向阀CV5允许制冷剂由主路膨胀阀XV1流向第一气液分离器GLS1。
同理，第二气液分离器GLS2的气液混合端口与主路膨胀阀XV1通过第六正向单向阀CV6和第七反向单向阀CV7形成的并联组件连接；其中，第六正向单向阀CV6允许制冷剂由第二气液分离器GLS2流向主路膨胀阀XV1，第七反向单向阀CV7允许制冷剂由主路膨胀阀XV1流向第二气液分离器GLS2。
第三气液分离器GLS3的气液混合端口与主路膨胀阀XV1通过第八正向单向阀CV8和第九反向单向阀CV9形成的并联组件连接；其中，第八正向单向阀CV8允许制冷剂由第三气液分离器GLS3流向主路膨胀阀XV1，第九反向单向阀CV9允许制冷剂由主路膨胀阀XV1流向第三气液分离器GLS3。
进一步地，继续参见图4，本实施例的空调系统还包括并联设置的制冷开关阀SV4和旁路膨胀阀XV2组件，并联设置的制冷开关阀SV4和旁路膨胀阀XV2组件用于串联每个正向单向阀与主路膨胀阀。当三个第二换热器均位于制冷工况，制冷开关阀SV4开启，旁路膨胀阀XV2关闭；当三个第二换热器均位于制热工况，制冷开关阀SV4关闭，旁路膨胀阀XV2关闭；当三个第二换热器中至少有一个位于除霜状态时，制冷开关阀SV4关闭，旁路膨胀阀XV2启动节流。
本实施例中方向控制阀优选为四通阀4DCV，四通阀4DCV具有四个接口，这四个接口分别为第一接口、第二接口、第三接口和第四接口；其中，第一接口和压缩机CP的高压侧通过管路连通，第二接口和第一换热器EH1的端口通过管路连通，第三接口与前部第二换热器EH2f、中部第二换热器EH2m和后部第二换热器EH2b连通，第四接口和压缩机CP的低压侧通过管路连通。
四通阀4DCV具有两个工作位置，这两个工作位置分别为第一工作位置和第二工作位置。当四通阀4DCV位于第一工作位置时，阀芯相对于阀体移动至第一接口和第三接口连通，此时压缩机CP的高压侧与前部第二换 热器EH2f、中部第二换热器EH2m和后部第二换热器EH2b三者连通，压缩机CP的低压侧与第一换热器EH1连通，该风冷热泵空调系统进入制冷工况。
制冷工况下，第一除霜开关阀SV1、第二除霜开关阀SV2、第三除霜开关阀SV3和旁路主路膨胀阀XV12均位于关闭状态，制冷开关阀SV4开启。
制冷剂循环流程是：压缩机CP→4四通阀DCV→第一三通阀3DCV1、第二三通阀3DCV2和第三三通阀3DCV3→分为两路，一路流入前部第二换热器EH2f的上部回路、中部第二换热器EH2m的上部回路和后部第二换热器EH2b的上部回路，另一路依次流入前部第二换热器EH2f的下部回路和第一毛细管MV1，中部第二换热器EH2m的下部回路和第二毛细管MV2，后部第二换热器EH2b的下部回路和第三毛细管MV3→第一气液分离器GLS1、第二气液分离器GLS2和第三气液分离器GLS3→第四正向单向阀CV4、第六正向单向阀CV6、第八正向单向阀CV8→旁路膨胀阀XV2→主路膨胀阀XV1→第一换热器EH1→四通阀4DCV→压缩机CP。
本空调系统制冷工况的工作原理是：通过压缩机CP把低温低压的制冷剂蒸气压缩为高温高压过热的蒸气，气态制冷剂流经四通阀4DCV，再分别由三个三通阀流入三个第二换热器，通过热交换把热量传递到空气中去，制冷剂冷凝为高温高压的液体制冷剂；然后该制冷剂流经与各第二换热器分别对应设置的毛细管、气液分离器制冷剂和单向阀，再经由制冷开关阀SV4流入主路膨胀阀XV1，在主路主路膨胀阀XV1内汇流后节流变为饱和状态的制冷剂，进入到第一换热器EH1蒸发吸热变为低温过热蒸气，最后通过四通阀4DCV回到压缩机CP。空调系统不断循环制取冷水，把热量散发到空气中去。
制热工况下，第一除霜开关阀SV1、第二除霜开关阀SV2、第三除霜开关阀SV3、制冷开关阀SV4和旁路旁通阀XV2均位于关闭状态。
制冷剂循环流程是：压缩机CP→四通阀4DCV→第一换热器EH1→主路膨胀阀XV1→第五反向单向阀CV5、第七反向单向阀CV7、第九反向单向阀CV9→第一气液分离器GLS1、第二气液分离器GLS2、第三气液分离器GLS3→分为两路，一路流入前部第二换热器EH2f的上部回路、中部第二换热器EH2m的上部回路和后部第二换热器EH2b的上部回路，另一路依次流经第一单向阀CV1和前部第二换热器EH2f的下部回路、第二单向阀CV2和中部第二换热器EH2m的下部回路、第三单向阀CV3和后部第二换热器EH2b 的下部回路→第一三通阀3DCV1、第二三通阀3DCV2和第三三通阀3DCV3→四通阀4DCV→压缩机CP。
该空调系统制热工况的工作原理是：通过压缩机CP把低温低压的制冷剂蒸气压缩为高温高压过热的蒸气，气态制冷剂流通过四通阀4DCV后进入到第一换热器EH1，通过热交换把热量传递到循环水中去，制冷剂冷凝为高温高压的液体，再由主路膨胀阀XV1节流处理后形成气液两相制冷剂，随后经由第五反向单向阀CV5、第七反向单向阀CV7和第九反向单向阀CV9分别流入对应地三个气液分离器内，由各个气液分离器气液分离处理为液态制冷剂和气态制冷剂。其中，液态制冷剂经流入与每个气液分离器对应设置的第二换热器的上部回路与外部环境热交换，吸热蒸发形成气态制冷剂；与此同时，气态制冷剂分别流经第一单向阀CV1、第二单向阀CV2和第三单向阀CV3后进入对应第二换热器的下部回路，最后流经四通阀4DCV被吸入压缩机CP。空调系统不断循环制取热水，从空气中吸收热量。
在制热工况下，当环温较低时第二换热器会结霜，本空调系统可对三个第二换热器逐个除霜。
当给前部第二换热器EH2f除霜时，关闭前部第二换热器EH2f的风机，关闭第二除霜开关阀SV2和第三除霜开关阀SV3，开启第一除霜开关阀SV1和旁路膨胀阀XV2，压缩机CP的高压侧与第一三通阀3DCV1导通，控制第一三通阀3DCV1使前部第二换热器EH2f与压缩机CP的高压侧连通，高压气态制冷剂进入前部第二换热器EH2f开始除霜，制冷剂在前部第二换热器EH2f1的上部回路和下部回路中冷凝后，流经第一气液分离器GLS1和第四正向单向阀CV4，在经过旁路膨胀阀XV2节流后进入主管道，与经进主路膨胀阀XV1节流后制冷剂混合后进入其它工作在制热状态的中部第二换热器EH2m和后部第二换热器EH2b中进行蒸发。
当给中部第二换热器EH2m除霜时，关闭中部第二换热器EH2m的风机，关闭第一除霜开关阀SV1、第三除霜开关阀SV3和制冷开关阀SV4，开启第二除霜开关阀SV2和旁路膨胀阀XV2，压缩机CP的高压侧与第二三通阀3DCV2导通，控制第二三通阀3DCV2使中部第二换热器EH2m与压缩机CP的高压侧连通。高压气态制冷剂进入中部第二换热器EH2m开始除霜，制冷剂在中部第二换热器EH2m的上部回路和下部回路中冷凝后，流经第二气液分离器GLS2和第六正向单向阀CV6，经旁路主路膨胀阀XV2节流后，进入 主管道，与经进主路膨胀阀XV1节流后制冷剂混合后进入其它工作在制热状态的前部第二换热器EH2f和后部第二换热器EH2b中进行蒸发。
当给后部第二换热器EH2b除霜时，关闭后部第二换热器EH2b的风机，关闭第一除霜开关阀SV1、第二除霜开关阀SV2和制冷开关阀SV4，开启第三除霜开关阀SV3和旁路主路膨胀阀XV12，压缩机CP的高压侧与第三三通阀3DCV3导通，控制第三三通阀3DCV3使后部第二换热器EH2b与压缩机CP的高压侧连通。高压气态制冷剂进入后部第二换热器EH2b开始除霜，制冷剂在后部第二换热器EH2b的上部回路和下部回路中冷凝后，流经第三气液分离器GLS3和第八正向单向阀CV8，经过旁路膨胀阀XV2节流后，进入主管道，与经进主路膨胀阀XV1节流后制冷剂混合后进入其它工作在制热状态的前部第二换热器EH2f和中部第二换热器EH2m中进行蒸发。
可见，本空调系统只对一个第二换热器除霜，该第二换热器除霜完成后再对其它第二换热器除霜。所以在除霜过程中，空调系统仍保持制热循环，不会从第一换热器EH1中吸收热量用于除霜，可使整个除霜过程中用户水温波动小，舒适性得到保障。
此外，第二换热器逐个除霜时，处于除霜状态的第二换热器中的压力从低到高逐渐升高，设置旁路膨胀阀XV2并连接到经主路膨胀阀XV1节流后的低压管路中。通过旁路膨胀阀XV2的控制，使处于除霜中的第二换热器中的制冷剂能够顺利排出，且实现流量可控，使第二换热器的温度更快上升，达到快速除霜的效果。
当然，该空调系统的第四正向单向阀CV4、第六正向单向阀CV6和第八正向单向阀CV8也可以直接连接到主路膨胀阀XV1的高压管路上。如此设置，位于除霜状态的第二换热器完全依靠空调系统的压力自平衡进行排液，但是排液速度相对较慢，除霜时间较长。
需要说明的是，本实施方式中的风冷热泵空调系统包括三个第二换热器，可以理解，第二换热器的数量并不仅限于三个。根据实际需要上述风冷热泵空调系统可采用两个或换多个热器，且各第二换热器之间并联设置。其中，多个是指大于或等于3的整数，如3、4、5、6、7等。此外，风冷热泵空调系统包括两个或除了3外的多个第二换热器时，各个第二换热器与其他器件之间的连接关系与前述两个第二换热器的相似，本领域技术人员根据上面的说明可以毫无疑义地实现，故而本文在此不再赘述。
上述四种实施方式中本发明所提供的空调系统，在制热工况下，经主路膨胀阀节流形成的气液两相制冷剂在气液分离器中分离为气态制冷剂和液态制冷剂后，再分别流入第二换热器中相互独立的上部回路和下部回路内参与热交换，保证了上部回路基本上为纯液态制冷剂，下部回路内基本上为纯气态制冷剂，相应地，由于上部回路的流程大于下部回路的流程，使得液态制冷剂能够更充分地进行热交换并因此被更彻底地蒸发，从而提升空调系统在各种工况下的制热能力。
进一步，由于第二换热器下部回路流程较短，在制冷工况下，单向阀关闭，液态制冷剂经毛细管节流后依次流经气液分离器和主路膨胀阀后进入第一换热器内，这样可以限制冷剂由下部回路流向气液分离器时的流量，以防止因制冷剂流量过大导致大量未经冷凝的气态制冷剂进入气液分离器中问题。同时，在制热工况下制冷剂通过单向阀旁通由气液分离器流入下部回路，这样保证了制热工况下制冷剂流通的畅通性，从而保证了整个制冷工况的正常进行。
需要说明的是，上述三四种实施方式所提供的风冷热泵空调系统除了解决制热工况下第二换热器中制冷剂分配问题外，还具备一下几个特点，分别为：
第一，在同等换热量下缩小了饱和蒸发温度与空气换热温差，降低了机组的结霜温度，延长了除霜周期，拓展了机组的运行范围。
第二，在制热工况下，第二换热器下部回路为气态制冷剂，换热量较小，温度较上部回路高，结霜量较小。
第三，在除霜工况下，第二换热器下部回路温度也高于上部回路，使霜层迅速融化，从而除霜排水更通畅，进而改善了除霜排水的效果。
第四，在制冷工况下，第二换热器的下部回路也可用于冷凝换热，使得第二换热器的换热面积得到充分利用。
至此，已经结合附图所示的优选实施方式描述了本发明的技术方案，但是，本领域技术人员容易理解的是，本发明的保护范围显然不局限于这些具体实施方式。在不偏离本发明的原理的前提下，本领域技术人员可以对相关技术特征作出等同的更改或替换，这些更改或替换之后的技术方案都将落入本发明的保护范围之内。

Claims (10)

  1. 一种高效制热的风冷热泵空调系统，包括压缩机、第一换热器、第二换热器、方向控制阀和主路膨胀阀，其特征在于，所述空调系统还包括气液分离器；
    所述第二换热器分为相互独立的上部回路和下部回路，所述上部回路与所述气液分离器的液相端口连通，所述下部回路与所述气液分离器的气相端口连通，所述主路膨胀阀连接所述第一换热器和所述气液分离器的气液混合端口，并且所述上部回路的流程大于所述下部回路的流程；
    在制冷工况下，所述方向控制阀位于第一工作位置，以控制所述压缩机的高压侧与所述上部回路和所述下部回路两者连通，所述压缩机的低压侧与所述第一换热器连通；
    在制热工况下，所述方向控制阀位于第二工作位置，以控制所述压缩机的高压侧与所述第一换热器连通，所述压缩机的低压侧与所述上部回路和所述下部回路两者连通。
  2. 根据权利要求1所述的高效制热的风冷热泵空调系统，其特征在于，所述下部回路和所述气液分离器通过流量控制装置连接，所述流量控制装置用于在制冷工况下节流由所述下部回路流入所述气液分离器的制冷剂，以及在制热工况下直接导通由所述气液分离器流入所述下部回路的制冷剂。
  3. 根据权利要求2所述的高效制热的风冷热泵空调系统，其特征在于，所述流量控制装置为单向阀和毛细管的并联组件，所述毛细管用于在制冷工况下节流由所述下部回路流入所述气液分离器的制冷剂，所述单向阀用于在制热工况下直接导通由所述气液分离器流入所述下部回路的制冷剂。
  4. 根据权利要求1至3中任一项所述的高效制热的风冷热泵空调系统，其特征在于，所述第二换热器的数量为两个或多个，且两个或多个所述第二换热器并联设置。
  5. 根据权利要求1所述的高效制热的风冷热泵空调系统，其特征在于，所述第二换热器的数量为两个或多个，所述空调系统还包括与每个所述第二换热 器对应设置的三通阀、除霜开关阀和所述气液分离器；
    所述三通阀设置于所述压缩机的高压侧、所述方向控制阀和对应的所述第二换热器三者之间，用于控制所述第二换热器可选择地与所述压缩机的高压侧连通或者与所述方向控制阀连通；
    所述除霜开关阀设置于所述压缩机的高压侧与所述三通阀之间，用于控制所述压缩机的高压侧和所述三通阀的截止或导通。
  6. 根据权利要求5所述的高效制热的风冷热泵空调系统，其特征在于，每个所述气液分离器的入口与所述主路膨胀阀通过由正向单向阀和反向单向阀构成的并联组件连接；其中，正向单向阀允许制冷剂由对应的所述气液分离器流向所述主路膨胀阀，反向单向阀允许制冷剂由所述主路膨胀阀流向对应的所述气液分离器。
  7. 根据权利要求6所述的高效制热的风冷热泵空调系统，其特征在于，所述空调系统还包括并联设置的制冷开关阀和旁路膨胀阀组件，所述并联设置的制冷开关阀和旁路膨胀阀组件用于串联每个所述正向单向阀与所述主路膨胀阀；
    每个所述第二换热器均位于制冷工况时，所述制冷开关阀开启，所述第二膨胀阀关闭；
    每个所述第二换热器均位于制热工况时，所述制冷开关阀关闭，所述第二膨胀阀关闭
    至少一个所述第二换热器位于除霜状态时，所述制冷开关阀关闭，所述第二膨胀阀启动。
  8. 根据权利要求5至7任一项所述的高效制热的风冷热泵空调系统，其特征在于，每个所述下部回路和对应的所述气液分离器通过流量控制装置连接，所述流量控制装置用于在制冷工况下节流由所述下部回路流入所述气液分离器的制冷剂，以及在制热工况下直接导通由所述气液分离器流入所述下部回路的制冷剂。
  9. 根据权利要求8所述的高效制热的风冷热泵空调系统，其特征在于，所 述流量控制装置为单向阀和毛细管的并联组件，所述毛细管用于在制冷工况下节流由所述下部回路流入所述气液分离器的制冷剂，所述单向阀用于在制热工况下直接导通由所述气液分离器流入所述下部回路的制冷剂。
  10. 根据权利要求1至3或者5至7中任一项所述的高效制热的风冷热泵空调系统，其特征在于，所述气液分离器的液相端口设置在其底部，所述气液分离器的气相端口设置在其顶部，所述气液分离器的气液混合端口设置在其中部。
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