US20240151425A1 - Air-conditioner - Google Patents

Air-conditioner Download PDF

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Publication number
US20240151425A1
US20240151425A1 US18/549,229 US202118549229A US2024151425A1 US 20240151425 A1 US20240151425 A1 US 20240151425A1 US 202118549229 A US202118549229 A US 202118549229A US 2024151425 A1 US2024151425 A1 US 2024151425A1
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United States
Prior art keywords
way valve
refrigerant
heat exchange
exchange portion
air
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Pending
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US18/549,229
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English (en)
Inventor
Komei Nakajima
Yusuke Adachi
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NAKAJIMA, Komei, ADACHI, YUSUKE
Publication of US20240151425A1 publication Critical patent/US20240151425A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0068—Indoor units, e.g. fan coil units characterised by the arrangement of refrigerant piping outside the heat exchanger within the unit casing
    • 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
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
    • F25B2313/02341—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements during cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
    • F25B2313/02343—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements during dehumidification
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
    • F25B2313/02344—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements during heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02743—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using three four-way valves

Definitions

  • the present disclosure relates to an air-conditioner.
  • An air-conditioner capable of performing both of a cooling operation and a reheating dehumidification operation has conventionally been proposed.
  • Such an air-conditioner is described, for example, in Japanese Patent Laying-Open No. 2020-125855 (PTL 1).
  • PTL 1 Japanese Patent Laying-Open No. 2020-125855
  • a four-way valve provided in a refrigerant circuit switches a flow path of refrigerant so that an orientation of refrigerant that flows in an indoor heat exchanger is different between the cooling operation and the reheating dehumidification operation.
  • the indoor heat exchanger is divided into a plurality of heat exchange portions and an expansion valve is provided between the plurality of divided heat exchange portions.
  • a heat exchanger is normally designed such that, when the heat exchanger is used as an evaporator, air that flows on the outside of the heat exchanger and refrigerant that flows in the inside of the heat exchanger are parallel flows with orientations thereof being the same, for the following reason.
  • a density of refrigerant is low and a flow velocity of refrigerant is high. Therefore, pressure loss in the evaporator is greater than pressure loss in a condenser. Accordingly, a saturation temperature at an outlet of the evaporator is lower than a saturation temperature at an inlet of the evaporator.
  • a temperature of refrigerant becomes lower with cooling of air, and hence the temperature at the outlet is lower than in an example where air and refrigerant flow as counterflows. Air can thus efficiently be cooled.
  • the present disclosure was made in view of the problems above, and an object thereof is to provide an air-conditioner capable of sufficient dehumidification in a reheating dehumidification operation.
  • An air-conditioner in the present disclosure is provided with a refrigerant circuit and an indoor fan.
  • the refrigerant circuit has a compressor, a first four-way valve, an outdoor heat exchanger, a first expansion valve, a second four-way valve, a third four-way valve, an indoor heat exchanger, and a second expansion valve, and is configured to circulate refrigerant.
  • the indoor fan is configured to send air to the indoor heat exchanger.
  • the indoor heat exchanger has a first heat exchange portion and a second heat exchange portion.
  • the first four-way valve, the second four-way valve, and the third four-way valve are switched to allow refrigerant to flow through the refrigerant circuit in an order of the compressor, the first four-way valve, the outdoor heat exchanger, the first expansion valve, the second four-way valve, the third four-way valve, the first heat exchange portion, the third four-way valve, the second expansion valve, the second heat exchange portion, the second four-way valve, and the first four-way valve during a cooling operation.
  • the first four-way valve, the second four-way valve, and the third four-way valve are switched to allow refrigerant to flow through the refrigerant circuit in an order of the compressor, the first four-way valve, the outdoor heat exchanger, the first expansion valve, the second four-way valve, the second heat exchange portion, the second expansion valve, the third four-way valve, the first heat exchange portion, the third four-way valve, the second four-way valve, and the first four-way valve during a reheating dehumidification operation.
  • a flow of refrigerant with respect to a flow of air sent by the indoor fan is a parallel flow.
  • the flow of refrigerant with respect to the flow of air is a parallel flow
  • the flow of refrigerant with respect to the flow of air is a counterflow
  • the flow of refrigerant with respect to the flow of air is the parallel flow. Therefore, sufficient dehumidification can be achieved in the reheating dehumidification operation.
  • FIG. 1 is a diagram of a refrigerant circuit during a cooling operation of an air-conditioner according to a first embodiment.
  • FIG. 2 is a pressure-enthalpy diagram during the cooling operation of the air-conditioner according to the first embodiment.
  • FIG. 3 is a diagram of the refrigerant circuit during a reheating dehumidification operation of the air-conditioner according to the first embodiment.
  • FIG. 4 is a pressure-enthalpy diagram during the reheating dehumidification operation of the air-conditioner according to the first embodiment.
  • FIG. 5 is a diagram of the refrigerant circuit during a heating operation of the air-conditioner according to the first embodiment.
  • FIG. 6 is a cross-sectional view schematically showing a construction during the cooling operation, of an indoor unit of the air-conditioner according to the first embodiment.
  • FIG. 7 is a cross-sectional view schematically showing a construction during the reheating dehumidification operation, of the indoor unit of the air-conditioner according to the first embodiment.
  • FIG. 8 is a diagram of the refrigerant circuit during the cooling operation of the air-conditioner according to a second embodiment.
  • FIG. 9 is a diagram of the refrigerant circuit during the reheating dehumidification operation of the air-conditioner according to the second embodiment.
  • FIG. 10 is a diagram of the refrigerant circuit during the heating operation of the air-conditioner according to the second embodiment.
  • FIG. 1 A construction of an air-conditioner 100 according to a first embodiment will be described with reference to FIG. 1 .
  • air-conditioner 100 is provided with a refrigerant circuit RC, an outdoor fan 9 , an indoor fan 10 , and a control device 11 .
  • Refrigerant circuit RC has a compressor 1 , a first four-way valve 2 , an outdoor heat exchanger 3 , a first expansion valve 4 , a second four-way valve 5 , a third four-way valve 6 , an indoor heat exchanger 7 , a second expansion valve 8 , and a pipe P.
  • Indoor heat exchanger 7 has a first heat exchange portion 7 a and a second heat exchange portion 7 b .
  • Pipe P includes a first extension pipe P 1 and a second extension pipe P 2 .
  • Refrigerant circuit RC is constructed by connection of compressor 1 , first four-way valve 2 , outdoor heat exchanger 3 , first expansion valve 4 , second four-way valve 5 , third four-way valve 6 , indoor heat exchanger 7 , and second expansion valve 8 through pipe P.
  • Refrigerant circuit RC is constructed to circulate refrigerant.
  • Air-conditioner 100 includes an outdoor unit 101 and an indoor unit 102 . Outdoor unit 101 and indoor unit 102 are connected to each other through first extension pipe P 1 and second extension pipe P 2 . Compressor 1 , first four-way valve 2 , outdoor heat exchanger 3 , first expansion valve 4 , second four-way valve 5 , outdoor fan 9 , and control device 11 are accommodated in outdoor unit 101 . Third four-way valve 6 , indoor heat exchanger 7 , second expansion valve 8 , and indoor fan 10 are accommodated in indoor unit 102 .
  • Compressor 1 is constructed to compress refrigerant.
  • Compressor 1 is constructed to compress and discharge suctioned refrigerant.
  • Compressor 1 is, for example, of a variable displacement type.
  • Compressor 1 is constructed as being variable in capacity, for example, by adjustment of the number of rotations of compressor 1 based on an instruction from control device 11 .
  • First four-way valve 2 is connected to an inlet and an outlet of compressor 1 , outdoor heat exchanger 3 , and second four-way valve 5 .
  • First four-way valve 2 is constructed to switch a flow of refrigerant such that refrigerant compressed by compressor 1 flows to outdoor heat exchanger 3 or indoor heat exchanger 7 .
  • first four-way valve 2 switches the flow of refrigerant such that refrigerant compressed by compressor 1 flows to indoor heat exchanger 7
  • refrigerant flows from first four-way valve 2 through second four-way valve 5 to indoor heat exchanger 7 .
  • First four-way valve 2 is constructed to allow refrigerant discharged from compressor 1 to flow to outdoor heat exchanger 3 during a cooling operation and a reheating dehumidification operation.
  • First four-way valve 2 is constructed to allow refrigerant discharged from compressor 1 to flow to indoor heat exchanger 7 during a heating operation.
  • Outdoor heat exchanger 3 is constructed to exchange heat between refrigerant that flows in the inside of outdoor heat exchanger 3 and air that flows on the outside of outdoor heat exchanger 3 .
  • Outdoor heat exchanger 3 is constructed to function as a condenser that condenses refrigerant during the cooling operation and the reheating dehumidification operation.
  • Outdoor heat exchanger 3 is constructed to function as an evaporator that evaporates refrigerant during the heating operation.
  • Outdoor heat exchanger 3 is, for example, a finned tube heat exchanger having a plurality of fins and a heat transfer tube that passes through the plurality of fins.
  • First expansion valve 4 is constructed to decompress by expanding, refrigerant condensed by the condenser.
  • First expansion valve 4 is constructed to decompress refrigerant condensed by outdoor heat exchanger 3 during the cooling operation and the reheating dehumidification operation.
  • First expansion valve 4 is constructed to decompress refrigerant condensed by indoor heat exchanger 7 during the heating operation.
  • a solenoid expansion valve is employed as the first expansion valve.
  • Second four-way valve 5 is connected to first four-way valve 2 , first expansion valve 4 , third four-way valve 6 , and second heat exchange portion 7 b of indoor heat exchanger 7 .
  • Second four-way valve 5 is constructed to switch the flow of refrigerant such that refrigerant that flows out of first expansion valve 4 flows through third four-way valve 6 to first heat exchange portion 7 a of indoor heat exchanger 7 and refrigerant that flows out of second heat exchange portion 7 b of indoor heat exchanger 7 flows to first four-way valve 2 during the cooling operation.
  • Second four-way valve 5 is constructed to switch the flow of refrigerant such that refrigerant that flows out of first expansion valve 4 flows to second heat exchange portion 7 b of indoor heat exchanger 7 and refrigerant that flows out of first heat exchange portion 7 a of indoor heat exchanger 7 and passes through third four-way valve 6 flows to first four-way valve 2 during the reheating dehumidification operation.
  • Second four-way valve 5 is constructed to switch the flow of refrigerant such that refrigerant that is discharged from compressor 1 and passes through first four-way valve 2 flows to second heat exchange portion 7 b of indoor heat exchanger 7 and refrigerant that flows out of first heat exchange portion 7 a of indoor heat exchanger 7 and passes through third four-way valve 6 flows to first expansion valve 4 during the heating operation.
  • Third four-way valve 6 is connected to second four-way valve 5 , an inlet and an outlet of first heat exchange portion 7 a of indoor heat exchanger 7 , and second expansion valve 8 .
  • Third four-way valve 6 is constructed to switch the flow of refrigerant such that refrigerant that flows out of second four-way valve 5 flows to a heat transfer tube on a windward side of first heat exchange portion 7 a and refrigerant that flows out of a heat transfer tube on a leeward side of first heat exchange portion 7 a flows through second expansion valve 8 to a heat transfer tube on the windward side of second heat exchange portion 7 b of indoor heat exchanger 7 during the cooling operation.
  • Third four-way valve 6 is constructed to switch the flow of refrigerant such that refrigerant that flows out of second expansion valve 8 flows to the heat transfer tube on the windward side of first heat exchange portion 7 a and refrigerant that flows out of the heat transfer tube on the leeward side of first heat exchange portion 7 a flows to second four-way valve 5 during the reheating dehumidification operation.
  • Third four-way valve 6 is constructed to switch the flow of refrigerant such that refrigerant that flows out of second expansion valve 8 flows to the heat transfer tube on the leeward side of first heat exchange portion 7 a and refrigerant that flows out of the heat transfer tube on the windward side of first heat exchange portion 7 a flows to second four-way valve 5 during the heating operation.
  • Indoor heat exchanger 7 is constructed to exchange heat between refrigerant that flows in the inside of indoor heat exchanger 7 and air that flows on the outside of indoor heat exchanger 7 .
  • Indoor heat exchanger 7 is constructed to function as the evaporator that evaporates refrigerant during the cooling operation.
  • Both of first heat exchange portion 7 a and second heat exchange portion 7 b are constructed to function as the evaporator that evaporates refrigerant during the cooling operation.
  • Indoor heat exchanger 7 is constructed to function as the evaporator that evaporates refrigerant and the condenser that condenses refrigerant during the reheating dehumidification operation.
  • First heat exchange portion 7 a is constructed to function as the evaporator that evaporates refrigerant during the reheating dehumidification operation.
  • Second heat exchange portion 7 b is constructed to function as the condenser that condenses refrigerant during the reheating dehumidification operation.
  • Indoor heat exchanger 7 is constructed to function as the condenser that condenses refrigerant during the heating operation. Both of first heat exchange portion 7 a and second heat exchange portion 7 b are constructed to function as the condenser that condenses refrigerant during the heating operation.
  • Indoor heat exchanger 7 is, for example, a finned tube heat exchanger having a plurality of fins and a heat transfer tube that passes through the plurality of fins.
  • First heat exchange portion 7 a and second heat exchange portion 7 b are arranged as being aligned in a direction of flow of air sent by indoor fan 10 .
  • First heat exchange portion 7 a is arranged on the windward side relative to second heat exchange portion 7 b in the flow of air sent by indoor fan 10 .
  • Second heat exchange portion 7 b is arranged on the leeward side relative to first heat exchange portion 7 a in the flow of air sent by indoor fan 10 .
  • First heat exchange portion 7 a has the heat transfer tube on the windward side and the heat transfer tube on the leeward side.
  • the heat transfer tube on the windward side is connected to the heat transfer tube of the leeward side.
  • First heat exchange portion 7 a is constructed such that refrigerant flows from the heat transfer tube on the windward side to the heat transfer tube on the leeward side during the cooling operation and the reheating dehumidification operation.
  • refrigerant and air that flow in first heat exchange portion 7 a flow as parallel flows.
  • First heat exchange portion 7 a is constructed such that refrigerant flows from the heat transfer tube on the leeward side to the heat transfer tube on the windward side during the heating operation.
  • refrigerant and air that flow in first heat exchange portion 7 a flow as counterflows.
  • Second heat exchange portion 7 b has the heat transfer tube on the windward side and a heat transfer tube on the leeward side.
  • the heat transfer tube on the windward side is connected to the heat transfer tube on the leeward side.
  • Second heat exchange portion 7 b is constructed such that refrigerant flows from the heat transfer tube on the windward side to the heat transfer tube on the leeward side during the cooling operation.
  • refrigerant and air that flow in second heat exchange portion 7 b flow as parallel flows.
  • Second heat exchange portion 7 b is constructed such that refrigerant flows from the heat transfer tube on the leeward side to the heat transfer tube on the windward side during the reheating dehumidification operation and the heating operation.
  • refrigerant and air that flow in second heat exchange portion 7 b flow as counterflows.
  • Second expansion valve 8 is constructed to decompress refrigerant condensed in second heat exchange portion 7 b of indoor heat exchanger 7 during the reheating dehumidification operation. Second expansion valve 8 is constructed to suppress decompression of refrigerant by increasing an opening of the valve during the cooling operation and the heating operation. For example, a solenoid expansion valve is employed as second expansion valve 8 .
  • First four-way valve 2 , second four-way valve 5 , and third four-way valve 6 are switched such that refrigerant flows through refrigerant circuit RC in the order of compressor 1 , first four-way valve 2 , outdoor heat exchanger 3 , first expansion valve 4 , second four-way valve 5 , third four-way valve 6 , first heat exchange portion 7 a , third four-way valve 6 , second expansion valve 8 , second heat exchange portion 7 b , second four-way valve 5 , and first four-way valve 2 during the cooling operation.
  • First four-way valve 2 , second four-way valve 5 , and third four-way valve 6 are switched such that refrigerant flows through refrigerant circuit RC in the order of compressor 1 , first four-way valve 2 , outdoor heat exchanger 3 , first expansion valve 4 , second four-way valve 5 , second heat exchange portion 7 b , second expansion valve 8 , third four-way valve 6 , first heat exchange portion 7 a , third four-way valve 6 , second four-way valve 5 , and first four-way valve 2 during the reheating dehumidification operation.
  • First four-way valve 2 , second four-way valve 5 , and third four-way valve 6 are switched such that refrigerant flows through refrigerant circuit RC in the order of compressor 1 , first four-way valve 2 , second four-way valve 5 , second heat exchange portion 7 b , second expansion valve 8 , third four-way valve 6 , first heat exchange portion 7 a , third four-way valve 6 , second four-way valve 5 , first expansion valve 4 , outdoor heat exchanger 3 , and first four-way valve 2 during the heating operation.
  • Outdoor fan 9 is constructed to send air to outdoor heat exchanger 3 .
  • outdoor fan 9 is constructed to supply outdoor air to outdoor heat exchanger 3 .
  • Indoor fan 10 is constructed to send air to indoor heat exchanger 7 .
  • indoor fan 10 is constructed to supply indoor air to indoor heat exchanger 7 .
  • first heat exchange portion 7 a and second heat exchange portion 7 b the flow of refrigerant with respect to the flow of air sent by indoor fan 10 is the parallel flow.
  • first heat exchange portion 7 a the flow of refrigerant with respect to the flow of air sent by indoor fan 10 is the parallel flow
  • second heat exchange portion 7 b the flow of refrigerant with respect to the flow of air is the counterflow.
  • the flow of refrigerant with respect to the flow of air sent by indoor fan 10 is the counterflow.
  • Control device 11 is configured to control each device in air-conditioner 100 by performing computation and giving an instruction.
  • Control device 11 is electrically connected to compressor 1 , first four-way valve 2 , first expansion valve 4 , second four-way valve 5 , third four-way valve 6 , second expansion valve 8 , outdoor fan 9 , indoor fan 10 , and the like and configured to control operations thereof.
  • Air-conditioner 100 according to the first embodiment can selectively perform the cooling operation, the reheating dehumidification operation, and the heating operation.
  • refrigerant circulates through refrigerant circuit RC in the order of compressor 1 , first four-way valve 2 , outdoor heat exchanger 3 , first expansion valve 4 , second four-way valve 5 , third four-way valve 6 , first heat exchange portion 7 a of indoor heat exchanger 7 , third four-way valve 6 , second expansion valve 8 , second heat exchange portion 7 b of indoor heat exchanger 7 , second four-way valve 5 , and first four-way valve 2 .
  • outdoor heat exchanger 3 heat is exchanged between high-pressure gas refrigerant and air sent by outdoor fan 9 , so that refrigerant radiates heat and changes to liquid refrigerant.
  • Liquid refrigerant flows from outdoor heat exchanger 3 into first expansion valve 4 .
  • first expansion valve 4 liquid refrigerant is decompressed and becomes gas-liquid two-phase refrigerant.
  • Gas-liquid two-phase refrigerant flows into second four-way valve 5 from first expansion valve 4 .
  • a flow path in second four-way valve 5 is switched to connect first expansion valve 4 and first extension pipe P 1 to each other.
  • Gas-liquid two-phase refrigerant passes through first extension pipe P 1 from second four-way valve 5 and flows into third four-way valve 6 .
  • the flow path is switched to connect first extension pipe P 1 and the heat transfer tube on the windward side of first heat exchange portion 7 a of indoor heat exchanger 7 to each other.
  • Heat is exchanged between refrigerant that flows into the heat transfer tube on the windward side of first heat exchange portion 7 a of indoor heat exchanger 7 and air sent by indoor fan 10 and thereafter refrigerant flows out of the heat transfer tube on the leeward side of first heat exchange portion 7 a .
  • air that flows on the outside of first heat exchange portion 7 a and refrigerant that flows in the inside of first heat exchange portion 7 a are in the same orientation.
  • the flow of refrigerant with respect to the flow of air is the parallel flow.
  • Refrigerant flows again into third four-way valve 6 from first heat exchange portion 7 a and thereafter flows into second expansion valve 8 .
  • the opening of second expansion valve 8 is set to increase. Therefore, since the pressure loss of refrigerant is less likely in second expansion valve 8 , refrigerant flows as it is into the heat transfer tube on the windward side of second heat exchange portion 7 b of indoor heat exchanger 7 from second expansion valve 8 .
  • Air cooled in first heat exchange portion 7 a is sent to second heat exchange portion 7 b .
  • air that flows on the outside of second heat exchange portion 7 b and refrigerant that flows in the inside of second heat exchange portion 7 b are in the same orientation.
  • the flow of refrigerant with respect to the flow of air is the parallel flow.
  • Gas refrigerant that has evaporated in second heat exchange portion 7 b flows from second heat exchange portion 7 b through second extension pipe P 2 into second four-way valve 5 .
  • second four-way valve 5 the flow path is switched to connect second extension pipe P 2 and first four-way valve 2 to each other.
  • Gas refrigerant flows from second four-way valve 5 through first four-way valve 2 into the inlet of compressor 1 .
  • refrigerant circulates through refrigerant circuit RC in the order of compressor 1 , first four-way valve 2 , outdoor heat exchanger 3 , first expansion valve 4 , second four-way valve 5 , second heat exchange portion 7 b of indoor heat exchanger 7 , second expansion valve 8 , third four-way valve 6 , first heat exchange portion 7 a of indoor heat exchanger 7 , third four-way valve 6 , second four-way valve 5 , and first four-way valve 2 .
  • second four-way valve 5 and third four-way valve 6 are switched from a state thereof in the cooling operation shown in FIG. 1 .
  • Liquid refrigerant that has exchanged heat with air sent by outdoor fan 9 in outdoor heat exchanger 3 flows into first expansion valve 4 .
  • the temperature of refrigerant at an outlet of first expansion valve 4 can be higher than the temperature of indoor air.
  • Refrigerant flows from first expansion valve 4 into second four-way valve 5 .
  • the flow path in second four-way valve 5 is switched to connect first expansion valve 4 and second extension pipe P 2 to each other.
  • Refrigerant passes through second extension pipe P 2 from second four-way valve 5 and flows into second heat exchange portion 7 b of indoor heat exchanger 7 .
  • Refrigerant flows from the heat transfer tube on the leeward side to the heat transfer tube on the windward side in second heat exchange portion 7 b of indoor heat exchanger 7 .
  • second heat exchange portion 7 b refrigerant heats air cooled in first heat exchange portion 7 a .
  • Refrigerant flows into second expansion valve 8 from second heat exchange portion 7 b .
  • Refrigerant is decompressed in second expansion valve 8 and thereafter flows into third four-way valve 6 .
  • Refrigerant flows from third four-way valve 6 into the heat transfer tube on the windward side of first heat exchange portion 7 a .
  • Refrigerant flows from the heat transfer tube on the windward side to the heat transfer tube on the leeward side in first heat exchange portion 7 a .
  • Refrigerant cools air in first heat exchange portion 7 a .
  • air that flows on the outside of first heat exchange portion 7 a and refrigerant that flows in the inside of first heat exchange portion 7 a are in the same orientation. In other words, in first heat exchange portion 7 a , the flow of refrigerant with respect to the flow of air is the parallel flow.
  • Refrigerant that has cooled indoor air flows again into third four-way valve 6 from first heat exchange portion 7 a and then passes through first extension pipe P 1 and flows into second four-way valve 5 .
  • second four-way valve 5 the flow path is switched to connect first extension pipe P 1 and first four-way valve 2 to each other.
  • Refrigerant flows from second four-way valve 5 through first four-way valve 2 into the inlet of compressor 1 .
  • refrigerant circulates through refrigerant circuit RC in the order of compressor 1 , first four-way valve 2 , second four-way valve 5 , second heat exchange portion 7 b of indoor heat exchanger 7 , second expansion valve 8 , third four-way valve 6 , first heat exchange portion 7 a of indoor heat exchanger 7 , third four-way valve 6 , second four-way valve 5 , first expansion valve 4 , outdoor heat exchanger 3 , and first four-way valve 2 .
  • first four-way valve 2 is switched from the state thereof in the cooling operation shown in FIG. 1 .
  • High-pressure gas refrigerant discharged from compressor 1 flows through first four-way valve 2 and second four-way valve 5 into second heat exchange portion 7 b of indoor heat exchanger 7 .
  • Refrigerant is condensed in second heat exchange portion 7 b .
  • Air that flows on the outside of second heat exchange portion 7 b and refrigerant that flows in the inside of second heat exchange portion 7 b are in orientations reverse to each other. In other words, in second heat exchange portion 7 b , the flow of refrigerant with respect to the flow of air is the counterflow.
  • Refrigerant flows into second expansion valve 8 from second heat exchange portion 7 b .
  • the opening of second expansion valve 8 is set to increase.
  • Refrigerant flows from second expansion valve 8 through third four-way valve 6 into first heat exchange portion 7 a of indoor heat exchanger 7 .
  • Refrigerant is condensed in first heat exchange portion 7 a .
  • Air that flows on the outside of first heat exchange portion 7 a and refrigerant that flows in the inside of first heat exchange portion 7 a are in orientations reverse to each other. In other words, in first heat exchange portion 7 a , the flow of refrigerant with respect to the flow of air is the counterflow.
  • Refrigerant flows from first heat exchange portion 7 a through third four-way valve 6 and second four-way valve 5 into first expansion valve 4 . Refrigerant is decompressed in first expansion valve 4 . Refrigerant flows into outdoor heat exchanger 3 from first expansion valve 4 . Refrigerant that has evaporated in outdoor heat exchanger 3 flows through first four-way valve 2 into the inlet of compressor 1 .
  • FIGS. 6 and 7 A construction of indoor unit 102 of air-conditioner 100 according to the first embodiment will now be described with reference to FIGS. 6 and 7 .
  • a solid arrow shows a flow of refrigerant and a hollow arrow shows a flow of air.
  • the construction of indoor unit 102 shown FIGS. 6 and 7 is by way of example, and not limited as such.
  • Indoor unit 102 includes a housing 102 a .
  • An inlet 102 b for intake of air is provided in a front surface and an upper surface of housing 102 a .
  • An outlet 102 c for blowing air is provided in a lower surface of housing 102 a .
  • First heat exchange portion 7 a is arranged such that air suctioned through inlet 102 b passes therethrough before air passes through second heat exchange portion 7 b .
  • Second heat exchange portion 7 b is arranged such that air that has passed through first heat exchange portion 7 a passes therethrough.
  • Indoor fan 10 is arranged in the rear of second heat exchange portion 7 b .
  • a cross flow fan is employed as indoor fan 10 . Air that has passed through first heat exchange portion 7 a , second heat exchange portion 7 b , and indoor fan 10 is blown indoors through outlet 102 c.
  • first heat exchange portion 7 a the flow of refrigerant with respect to the flow of air is the parallel flow. Therefore, in first heat exchange portion 7 a that functions as the evaporator during the reheating dehumidification operation, the flow of refrigerant with respect to the flow of air can be the parallel flow. Air can thus efficiently be cooled in first heat exchange portion 7 a . Therefore, sufficient dehumidification can be achieved in the reheating dehumidification operation.
  • the cooling operation in which a sensible heat factor (SHF) is controlled can be performed owing to the reheating dehumidification operation.
  • SHF sensible heat factor
  • first heat exchange portion 7 a that functions as the evaporator during the reheating dehumidification operation and second heat exchange portion 7 b that functions as the condenser during the reheating dehumidification operation are arranged along the direction of flow of air, air does not have to separately be sent to first heat exchange portion 7 a and second heat exchange portion 7 b . Therefore, increase in input to indoor fan 10 can be suppressed.
  • second heat exchange portion 7 b that functions as the condenser, the flow of refrigerant with respect to the flow of air is the counterflow. Therefore, performance of the condenser can be improved.
  • Air-conditioner 100 according to a second embodiment is identical in construction, operations, and function and effect to air-conditioner 100 according to the first embodiment, unless particularly described.
  • Air-conditioner 100 according to the second embodiment is different from air-conditioner 100 according to the first embodiment in position of second four-way valve 5 .
  • Air-conditioner 100 according to the second embodiment will be described with reference to FIGS. 8 to 10 .
  • second four-way valve 5 is accommodated in indoor unit 102 .
  • Refrigerant circuit RC has first extension pipe P 1 and second extension pipe P 2 .
  • First extension pipe P 1 connects first expansion valve 4 and second four-way valve 5 to each other.
  • Second extension pipe P 2 connects first four-way valve 2 and second four-way valve 5 to each other.
  • First extension pipe P 1 is smaller in inner diameter than second extension pipe P 2 .
  • air-conditioner 100 according to the second embodiment operates in the cooling operation, the reheating dehumidification operation, and the heating operation similarly to air-conditioner 100 according to the first embodiment.
  • air-conditioner 100 according to the second embodiment A function and effect of air-conditioner 100 according to the second embodiment will now be described as compared with air-conditioner 100 according to the first embodiment.
  • air-conditioner 100 In air-conditioner 100 according to the first embodiment, during the cooling operation, low-pressure gas-liquid two-phase refrigerant throttled down by first expansion valve 4 that contains much liquid phase flows into first extension pipe P 1 and refrigerant flows into indoor unit 102 .
  • low-pressure gas refrigerant that has exchanged heat in indoor unit 102 flows into first extension pipe P 1 .
  • First extension pipe P 1 is smaller in inner diameter than second extension pipe P 2 , in expectation of flow of liquid refrigerant or gas-liquid two-phase refrigerant that contains much liquid phase.
  • gas refrigerant flows into first extension pipe P 1 during the reheating dehumidification operation. Since the flow velocity of refrigerant is thus higher than that in an example where liquid-phase refrigerant flows, the pressure loss of refrigerant that occurs in the pipe increases.
  • first extension pipe P 1 connects first expansion valve 4 and second four-way valve 5 to each other.
  • Second extension pipe P 2 connects first four-way valve 2 and second four-way valve 5 to each other.
  • First extension pipe P 1 is smaller in inner diameter than second extension pipe P 2 . Therefore, in both of the cooling operation and the reheating dehumidification operation, gas-liquid two-phase refrigerant throttled down by first expansion valve 4 flows into first extension pipe P 1 . Therefore, occurrence of the pressure loss of refrigerant can be suppressed as compared with the pressure loss in an example where gas refrigerant flows through first extension pipe P 1 in the reheating dehumidification operation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
US18/549,229 2021-04-07 2021-04-07 Air-conditioner Pending US20240151425A1 (en)

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JPS5322994Y2 (zh) * 1973-09-28 1978-06-14
JP5060840B2 (ja) 2007-06-20 2012-10-31 矢崎総業株式会社 発光指針計器
JP4989420B2 (ja) 2007-10-29 2012-08-01 日立アプライアンス株式会社 空気調和機
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