EP4328521A1 - Climatiseur - Google Patents

Climatiseur Download PDF

Info

Publication number
EP4328521A1
EP4328521A1 EP21937927.8A EP21937927A EP4328521A1 EP 4328521 A1 EP4328521 A1 EP 4328521A1 EP 21937927 A EP21937927 A EP 21937927A EP 4328521 A1 EP4328521 A1 EP 4328521A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
gas
flows
outdoor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP21937927.8A
Other languages
German (de)
English (en)
Other versions
EP4328521A4 (fr
Inventor
Takuya Matsuda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP4328521A1 publication Critical patent/EP4328521A1/fr
Publication of EP4328521A4 publication Critical patent/EP4328521A4/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • 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
    • 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
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0313—Pressure sensors near the outdoor heat exchanger
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/195—Pressures of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21162—Temperatures of a condenser of the refrigerant at the inlet of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser

Definitions

  • the present disclosure relates to an air-conditioner.
  • a non-azeotropic refrigerant mixture obtained by mixing at least two types of refrigerant is available as refrigerant to be used in a refrigeration cycle apparatus such as an air-conditioner.
  • PTL 1 and PTL 2 disclose a refrigeration cycle apparatus where such a non-azeotropic refrigerant mixture is used.
  • the heat exchanger in order to enhance efficiency of heat exchange between refrigerant and air, the heat exchanger is required to allow refrigerant to flow as a counterflow reverse in orientation to a direction of passage of air through the heat exchanger.
  • Japanese Patent Laying-Open No. H08-170864 proposes an air-conditioning apparatus including a six-way valve and an expansion valve.
  • Japanese Patent Laying-Open No. H09-196489 proposes an air-conditioner to which a bridge circuit including a check valve is applied.
  • a gas-liquid two-phase distributor in order to distribute refrigerant in a gas-liquid two-phase state containing gas refrigerant and liquid refrigerant that flows into the heat exchanger, a gas-liquid two-phase distributor is arranged on a refrigerant inlet side of the heat exchanger.
  • an orifice is arranged in order to uniformly distribute refrigerant in the gas-liquid two-phase state.
  • a gas distributor relatively large in volume is arranged on the refrigerant inlet side of the heat exchanger.
  • the gas-liquid two-phase distributor is arranged on one side of the heat exchanger and a gas distributor is arranged on the other side thereof.
  • an orientation of a flow of refrigerant when the heat exchanger functions as the condenser is the same as an orientation of a flow of refrigerant when the heat exchanger functions as the evaporator.
  • the heat exchanger functions as the condenser, for example, when gas refrigerant flows through the gas-liquid two-phase distributor where a distributor is arranged, the pressure loss is great.
  • the heat exchanger functions as the evaporator, for example, when gas refrigerant that has exchanged heat flows through the gas-liquid two-phase distributor where a distributor is arranged, the pressure loss is great.
  • the present disclosure was made to solve such a technical problem, and an object thereof is to provide an air-conditioner where a non-azeotropic refrigerant mixture is used, the air-conditioner capable of achieving reduction in pressure loss.
  • An air-conditioner includes a refrigeration cycle circuit provided with an outdoor unit and an indoor unit, a non-azeotropic refrigerant mixture circulating through the refrigeration cycle circuit.
  • At least one of the outdoor unit and the indoor unit includes a first heat exchanger, a second heat exchanger, a first gas-liquid two-phase distributor, a first gas distributor, a second gas distributor, a second gas-liquid two-phase distributor, a first flow path, and a second flow path.
  • the first heat exchanger includes a first part and a second part connected in series.
  • the second heat exchanger includes a third part and a fourth part connected in series.
  • the first gas-liquid two-phase distributor is connected on a side opposite to a side where the second part is connected, with respect to the first part.
  • the first gas distributor is connected on a side opposite to a side where the first part is connected, with respect to the second part.
  • the second gas distributor is connected on a side opposite to a side where the fourth part is connected, with respect to the third part.
  • the second gas-liquid two-phase distributor is connected on a side opposite to a side where the third part is connected, with respect to the fourth part.
  • the first flow path includes a portion through which the first gas distributor, the second part, the first part, and the first gas-liquid two-phase distributor are sequentially connected.
  • the second flow path includes a portion through which the second gas distributor, the third part, the fourth part, and the second gas-liquid two-phase distributor are sequentially connected.
  • the first flow path where the first heat exchanger is arranged and the second flow path where the second heat exchanger is arranged are connected in parallel with respect to the refrigeration cycle circuit in such a manner that the first gas-liquid two-phase distributor and the second gas-liquid two-phase distributor are connected and the first gas distributor and the second gas distributor are connected.
  • the air-conditioner has a first operation mode in which the first heat exchanger and the second heat exchanger function as a condenser and a second operation mode in which the first heat exchanger and the second heat exchanger function as an evaporator.
  • the first part is arranged on a windward side
  • the second part is arranged on a leeward side
  • the third part is arranged on the windward side
  • the fourth part is arranged on the leeward side.
  • a gaseous non-azeotropic refrigerant mixture flows into the first gas distributor and becomes liquid refrigerant in the first heat exchanger, and resultant liquid refrigerant flows through the first gas-liquid two-phase distributor
  • the gaseous non-azeotropic refrigerant mixture flows into the second gas distributor and becomes liquid refrigerant in the second heat exchanger, and resultant liquid refrigerant flows through the second gas-liquid two-phase distributor.
  • the non-azeotropic refrigerant mixture in the gas-liquid two-phase state flows into the first gas-liquid two-phase distributor and becomes gaseous refrigerant in the first heat exchanger, and resultant gaseous refrigerant flows through the first gas distributor
  • the non-azeotropic refrigerant mixture in the gas-liquid two-phase state flows into the second gas-liquid two-phase distributor and becomes gaseous refrigerant in the second heat exchanger, and resultant gaseous refrigerant flows through the first gas distributor.
  • the pressure loss of the non-azeotropic refrigerant mixture that circulates through the refrigeration cycle circuit can thus be reduced.
  • an air-conditioner 1 is provided with an outdoor unit 3 and an indoor unit 5.
  • a compressor 7, a four-way valve 9, an outdoor heat exchanger 11, an expansion valve 19, and the like are accommodated in outdoor unit 3.
  • An indoor heat exchanger 27 and the like are accommodated in indoor unit 5.
  • Non-azeotropic refrigerant mixture 43 refers to a refrigerant mixture obtained by mixing a plurality of single components, in which a gas phase and a liquid phase thereof are different in component from each other.
  • outdoor heat exchanger 11 includes an outdoor first heat exchanger 13 as a first heat exchanger and an outdoor second heat exchanger 15 as a second heat exchanger. Outdoor second heat exchanger 15 is arranged on outdoor first heat exchanger 13. Outdoor first heat exchanger 13 includes a first part 13a and a second part 13b. First part 13a and second part 13b are connected in series. First part 13a and second part 13b are arranged along a direction of passage of air (see an arrow YA). First part 13a is arranged on a windward side. Second part 13b is arranged on a leeward side.
  • a gas-liquid two-phase distributor 21a as a first gas-liquid two-phase distributor is connected on a side opposite to a side where second part 13b is connected, with respect to first part 13a.
  • a gas distributor 23a as a first gas distributor is connected on a side opposite to a side where first part 13a is connected, with respect to second part 13b.
  • Outdoor second heat exchanger 15 includes a third part 15a and a fourth part 15b.
  • Third part 15a and fourth part 15b are connected in series.
  • Third part 15a and fourth part 15b are arranged along the direction of passage of air (see arrow YA).
  • Third part 15a is arranged on the windward side.
  • Fourth part 15b is arranged on the leeward side.
  • a gas-liquid two-phase distributor 21b as a second gas-liquid two-phase distributor is connected on a side opposite to a side where third part 15a is connected, with respect to fourth part 15b.
  • a gas distributor 23b as a second gas distributor is connected on a side opposite to a side where fourth part 15b is connected, with respect to third part 15a.
  • Air-conditioner 1 is provided with a flow path R1 as a first flow path including a portion through which gas distributor 23a, second part 13b, first part 13a, and gas-liquid two-phase distributor 21a are sequentially connected.
  • a flow path R2 as a second flow path including a portion through which gas distributor 23b, third part 15a, fourth part 15b, and gas-liquid two-phase distributor 21b are sequentially connected is provided.
  • Flow path R1 where outdoor first heat exchanger 13 is arranged and flow path R2 where outdoor second heat exchanger 15 is arranged are connected in parallel with respect to refrigeration cycle circuit 51 in such a manner that gas-liquid two-phase distributor 21a and gas-liquid two-phase distributor 21b are connected and gas distributor 23a and gas distributor 23b are connected.
  • flow path R1 and flow path R2 are connected in parallel with respect to refrigeration cycle circuit 51 (main flow path) through which the non-azeotropic refrigerant mixture circulates.
  • indoor heat exchanger 27 includes an indoor first heat exchanger 29 and an indoor second heat exchanger 31.
  • a gas-liquid two-phase distributor 33a is connected on one end side of indoor first heat exchanger 29.
  • a gas distributor 35a is connected on the other end side of indoor first heat exchanger 29.
  • a gas-liquid two-phase distributor 33b is connected on one end side of indoor second heat exchanger 31.
  • a gas distributor 35b is connected on the other end side of indoor second heat exchanger 31.
  • Air-conditioner 1 is provided with a flow path R3 including a portion through which gas distributor 35a, gas-liquid two-phase distributor 33a, and indoor first heat exchanger 29 are sequentially connected.
  • a flow path R4 including a portion through which gas distributor 35b, indoor second heat exchanger 31, and gas-liquid two-phase distributor 33b are sequentially connected is provided.
  • Air-conditioner 1 where indoor first heat exchanger 29 is arranged and indoor second heat exchanger 31 where indoor second heat exchanger 31 is arranged are connected in parallel with respect to refrigeration cycle circuit 51 in such a manner that gas-liquid two-phase distributor 33a and gas-liquid two-phase distributor 33b are connected and gas distributor 35a and gas distributor 35b are connected.
  • flow path R3 and flow path R4 are connected in parallel with respect to refrigeration cycle circuit 51 (main flow path) through which a non-azeotropic refrigerant mixture circulates.
  • Air-conditioner 1 according to the first embodiment is composed as above.
  • a cooling operation as a first operation mode will initially be described as an operation of air-conditioner 1 (refrigeration cycle circuit 51).
  • outdoor heat exchanger 11 in outdoor unit 3 functions as a condenser
  • indoor heat exchanger 27 in indoor unit 5 functions as an evaporator.
  • High-pressure liquid refrigerant that flows through outdoor heat exchanger 11 and is sent out of outdoor unit 3 is converted by expansion valve 19 into refrigerant in the gas-liquid two-phase state containing low-pressure gas refrigerant and liquid refrigerant.
  • Refrigerant in the gas-liquid two-phase state is sent to indoor unit 5.
  • sent refrigerant flows through indoor heat exchanger 27.
  • refrigerant flows through indoor first heat exchanger 29 (flow path R3) and indoor second heat exchanger 31 (flow path R4) in parallel.
  • indoor heat exchanger 27 heat is exchanged between refrigerant in the gas-liquid two-phase state that flows in and air sent into indoor heat exchanger 27 by a fan (not shown).
  • Refrigerant in the gas-liquid two-phase state becomes low-pressure gas refrigerant (single phase) as a result of evaporation of liquid refrigerant by heat exchange.
  • Air that has exchanged heat is sent from indoor heat exchanger 27 into an indoor space so that the indoor space is cooled.
  • Low-pressure gas refrigerant that flows through indoor heat exchanger 27 and is sent out of indoor unit 5 flows through four-way valve 9 into compressor 7.
  • Low-pressure gas refrigerant that flows into compressor 7 becomes high-temperature and high-pressure gas refrigerant by being compressed and is discharged again from compressor 7. This cycle is repeated hereafter.
  • a heating operation as a second operation mode will be described as an operation of air-conditioner 1 (refrigeration cycle circuit 51).
  • indoor heat exchanger 27 in indoor unit 5 functions as the condenser and outdoor heat exchanger 11 in outdoor unit 3 functions as the evaporator.
  • indoor heat exchanger 27 heat is exchanged between gas refrigerant that flows in and air sent by the fan (not shown). High-temperature and high-pressure gas refrigerant becomes high-pressure liquid refrigerant (single phase) by being condensed. Air that has exchanged heat is sent from indoor heat exchanger 27 into the indoor space so that the indoor space is heated. High-pressure liquid refrigerant that flows through indoor heat exchanger 27 and is sent out of indoor unit 5 is sent to the outdoor unit.
  • High-pressure liquid refrigerant sent to outdoor unit 3 is converted by expansion valve 19 into refrigerant in the gas-liquid two-phase state containing low-pressure gas refrigerant and liquid refrigerant.
  • Refrigerant in the gas-liquid two-phase state flows through outdoor heat exchanger 11. At this time, refrigerant flows through outdoor first heat exchanger 13 (flow path R1) and outdoor second heat exchanger 15 (flow path R2) in parallel.
  • Low-pressure gas refrigerant that flows through outdoor heat exchanger 11 and is sent out of outdoor unit 3 flows through four-way valve 9 into compressor 7.
  • Low-pressure gas refrigerant that flows into compressor 7 becomes high-temperature and high-pressure gas refrigerant by being compressed and is again discharged from compressor 7. This cycle is repeated hereafter.
  • a general flow of refrigerant in air-conditioner 1 (refrigeration cycle circuit 51) is as described above.
  • a flow of refrigerant in outdoor heat exchanger 11 and indoor heat exchanger 27 will now more specifically be described.
  • high-temperature and high-pressure gas refrigerant (single phase) discharged from compressor 7 is sent through four-way valve 9 to outdoor unit 3.
  • refrigerant is branched at a branch and merge point P1 into refrigerant that flows through flow path R1 and refrigerant that flows through flow path R2.
  • flow path R1 high-temperature and high-pressure gas refrigerant successively flows through gas distributor 23a, second part 13b, first part 13a, and gas-liquid two-phase distributor 21a.
  • high-temperature and high-pressure gas refrigerant flows into gas distributor 23a and is condensed in outdoor first heat exchanger 13 to become high-pressure liquid refrigerant, and resultant high-pressure liquid refrigerant flows through gas-liquid two-phase distributor 21a.
  • outdoor first heat exchanger 13 refrigerant flows through second part 13b arranged on the leeward side and thereafter flows as a counterflow that flows through first part 13a arranged on the windward side.
  • high-temperature and high-pressure gas refrigerant successively flows through gas distributor 23b, third part 15a, fourth part 15b, and gas-liquid two-phase distributor 21b.
  • high-temperature and high-pressure gas refrigerant flows into gas distributor 23b and is condensed in outdoor second heat exchanger 15 to become high-pressure liquid refrigerant, and resultant high-pressure liquid refrigerant flows through gas-liquid two-phase distributor 21b.
  • refrigerant flows through third part 15a arranged on the windward side and thereafter flows as a parallel flow that flows through fourth part 15b arranged on the leeward side.
  • Low-pressure refrigerant in the gas-liquid two-phase state is sent to indoor unit 5 (see Fig. 1 ).
  • refrigerant that flows into indoor unit 5 is branched at a branch and merge point P4 into refrigerant that flows through flow path R3 and refrigerant that flows through flow path R4.
  • refrigerant in the gas-liquid two-phase state successively flows through gas-liquid two-phase distributor 33a, indoor first heat exchanger 29, and gas distributor 35a.
  • low-pressure refrigerant in the gas-liquid two-phase state flows through gas-liquid two-phase distributor 33a and is evaporated in indoor first heat exchanger 29 to become low-pressure gas refrigerant, and resultant low-pressure gas refrigerant flows through gas distributor 35a.
  • indoor first heat exchanger 29 refrigerant flows as the parallel flow.
  • flow path R4 refrigerant in the gas-liquid two-phase state successively flows through gas-liquid two-phase distributor 33b, indoor second heat exchanger 31, and gas distributor 35b.
  • refrigerant in the gas-liquid two-phase state flows through gas-liquid two-phase distributor 33b and is evaporated in indoor second heat exchanger 31 to become low-pressure gas refrigerant, and resultant low-pressure gas refrigerant flows through gas distributor 35b.
  • indoor second heat exchanger 31 refrigerant flows as the counterflow.
  • high-temperature and high-pressure gas refrigerant (single phase) discharged from compressor 7 is sent through four-way valve 9 to indoor unit 5.
  • refrigerant is branched at a branch and merge point P3 into refrigerant that flows through flow path R3 and refrigerant that flows through flow path R4.
  • gas refrigerant successively flows through gas distributor 35a, indoor first heat exchanger 29, and gas-liquid two-phase distributor 33a.
  • high-temperature and high-pressure gas refrigerant flows into gas distributor 35a and is condensed in indoor first heat exchanger 29 to become high-pressure liquid refrigerant, and resultant high-pressure liquid refrigerant flows through gas-liquid two-phase distributor 33a.
  • indoor first heat exchanger 29 refrigerant flows as the counterflow.
  • gas refrigerant successively flows through gas distributor 35b, indoor second heat exchanger 31, and gas-liquid two-phase distributor 33b.
  • high-temperature and high-pressure gas refrigerant flows into gas distributor 35b and is condensed in indoor second heat exchanger 31 to become high-pressure liquid refrigerant, and resultant high-pressure liquid refrigerant flows through gas-liquid two-phase distributor 33b.
  • refrigerant flows as the parallel flow.
  • High-pressure liquid refrigerant that flows through gas-liquid two-phase distributor 33a and high-pressure liquid refrigerant that flows through gas-liquid two-phase distributor 33b merge at branch and merge point P4, and merged refrigerant is sent to outdoor unit 3.
  • flow path R1 refrigerant in the gas-liquid two-phase state successively flows through gas-liquid two-phase distributor 21a, first part 13a, second part 13b, and gas distributor 23a.
  • low-pressure refrigerant in the gas-liquid two-phase state flows through gas-liquid two-phase distributor 21a and is evaporated in first part 13a and second part 13b to become low-pressure gas refrigerant, and resultant low-pressure gas refrigerant flows through gas distributor 23a.
  • outdoor first heat exchanger 13 first part 13a and second part 13b
  • refrigerant flows as the parallel flow.
  • refrigerant in the gas-liquid two-phase state successively flows through gas-liquid two-phase distributor 21b, third part 15a, fourth part 15b, and gas distributor 23b.
  • low-pressure refrigerant in the gas-liquid two-phase state flows through gas-liquid two-phase distributor 21b and is evaporated in fourth part 15b and third part 15a to become low-pressure gas refrigerant, and resultant low-pressure gas refrigerant flows through gas distributor 23b.
  • outdoor second heat exchanger 15 (fourth part 15b and third part 15a), refrigerant flows as the counterflow.
  • refrigerant in the gas-liquid two-phase state flows through gas-liquid two-phase distributors 21a, 21b, 33a, and 33b, and thereafter flows through corresponding outdoor heat exchanger 11 or indoor heat exchanger 27 to become gas refrigerant.
  • Refrigerant that has become gas refrigerant in corresponding outdoor heat exchanger 11 or indoor heat exchanger 27 flows through gas distributors 23a, 23b, 35a, and 35b. Pressure loss or the like can thus be reduced, description of which will be given.
  • a gas-liquid two-phase distributor is arranged on the refrigerant inlet side of the heat exchanger.
  • an orifice is arranged in order to uniformly refrigerant in the gas-liquid two-phase state.
  • a gas distributor relatively large in volume is arranged on the refrigerant inlet side of the heat exchanger.
  • an orientation of a flow of refrigerant that flows through the heat exchanger to function as the condenser is reverse to an orientation of a flow of refrigerant that flows through the heat exchanger to function as the evaporator. Therefore, the gas-liquid two-phase distributor is arranged on one side of the heat exchanger and the gas distributor is arranged on the other side thereof.
  • an orientation of a flow of refrigerant when the heat exchanger functions as the condenser is the same as an orientation of a flow of refrigerant when the heat exchanger functions as the evaporator.
  • a heat exchanger where a gas-liquid two-phase distributor is arranged on one side thereof and a gas distributor is arranged on the other side thereof is assumed.
  • gas refrigerant flows through the gas-liquid two-phase distributor to uniformly distribute refrigerant in the gas-liquid two-phase state, and hence pressure loss of refrigerant increases. Since liquid refrigerant flows through the gas header relatively large in volume, an amount of refrigerant increases.
  • refrigerant in the gas-liquid two-phase state flows through the gas header relatively large in volume. Accordingly, refrigerant cannot uniformly be distributed and performance as the evaporator lowers. Since gas refrigerant flows through the gas-liquid two-phase distributor to uniformly distribute refrigerant in the gas-liquid two-phase state, pressure loss of refrigerant increases.
  • the orientation of the flow of refrigerant through a refrigerant pipe that connects the indoor unit and the outdoor unit to each other during the cooling operation is the same as that during the heating operation.
  • a refrigerant pipe relatively large in diameter should inevitably be used as the refrigerant pipe for suppression of pressure loss.
  • liquid refrigerant that has flowed through the indoor unit flows through this refrigerant pipe relatively large in diameter. Therefore, liquid refrigerant tends to remain in the refrigerant pipe and the amount of refrigerant increases.
  • the heat exchanger in air-conditioner 1 described above achieves an effect as follows, as compared with the air-conditioner according to the comparative example.
  • gas refrigerant flows through gas distributors 23a and 23b to appropriately distribute gas, and thereafter it exchanges heat in corresponding outdoor first heat exchanger 13 or outdoor second heat exchanger 15 to become liquid refrigerant, and resultant liquid refrigerant flows through gas-liquid two-phase distributors 21a and 21b.
  • indoor unit 5 indoor heat exchanger 27
  • refrigerant in the gas-liquid two-phase state flows through gas-liquid two-phase distributors 33a and 33b where a distributor to uniformly distribute refrigerant in the gas-liquid two-phase state is arranged, and thereafter it exchanges heat in corresponding indoor first heat exchanger 29 or indoor second heat exchanger 31 to become gas refrigerant, and resultant gas refrigerant flows through gas distributors 35a and 35b.
  • gas refrigerant does not flow through the gas-liquid two-phase distributor as in the first case in the comparative example, and pressure loss of refrigerant can be reduced. Furthermore, liquid refrigerant does not flow through the gas distributor relatively large in volume, and increase in amount of refrigerant can be prevented.
  • gas refrigerant flows through gas distributors 35a and 35b to appropriately distribute gas, and thereafter it exchanges heat in corresponding indoor first heat exchanger 29 or indoor second heat exchanger 31 to become liquid refrigerant, and resultant liquid refrigerant flows through gas-liquid two-phase distributors 33a and 33b.
  • refrigerant in the gas-liquid two-phase state flows through gas-liquid two-phase distributors 21a and 21b to uniformly distribute refrigerant in the gas-liquid two-phase state, and thereafter it exchanges heat in corresponding outdoor first heat exchanger 13 or outdoor second heat exchanger 15 to become gas refrigerant, and resultant gas refrigerant flows through gas distributors 23a and 23b.
  • the flow of refrigerant in the gas-liquid two-phase state through the gas distributor relatively large in volume and resultant failure in uniform distribution of refrigerant as in the second case in the comparative example do not occur, and performance as the evaporator can be ensured.
  • Gas refrigerant does not flow through the gas-liquid two-phase distributor and pressure loss of refrigerant can be reduced.
  • gas refrigerant flows not through the gas-liquid two-phase distributor but through the gas distributor, and hence excessive increase in pressure can be suppressed.
  • the orientation during the cooling operation, of the flow of refrigerant through refrigerant pipe 41 that connects indoor unit 5 and outdoor unit 3 to each other is reverse to that during the heating operation.
  • the diameter of refrigerant pipe 41 that connects indoor unit 5 and outdoor unit 3 to each other does not have to be increased in consideration of the cooling operation as in the air-conditioner in the comparative example, and liquid refrigerant remaining in refrigerant pipe 41 during the heating operation is also suppressed and increase in amount of refrigerant can be suppressed.
  • Fig. 5 shows graphs GR1 and GR2 of a temperature of refrigerant that flows through outdoor heat exchanger 11 during the cooling operation and graphs GA1 and GA2 of a temperature of air that passes through outdoor heat exchanger 11.
  • the upper tier shows also outdoor heat exchanger 11 and the like shown in Fig. 3 .
  • graph GR1 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor first heat exchanger 13.
  • the temperature of refrigerant immediately before it flows into outdoor first heat exchanger 13 is a temperature TAin and the temperature of refrigerant immediately after it flows through outdoor first heat exchanger 13 is a temperature TAout.
  • Graph GR2 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor second heat exchanger 15.
  • the temperature of refrigerant immediately before it flows into outdoor second heat exchanger 15 is a temperature TBin and the temperature of refrigerant immediately after it flows through outdoor second heat exchanger 15 is a temperature TBout.
  • Graph GA1 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor first heat exchanger 13.
  • Graph GA2 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor second heat exchanger 15.
  • refrigerant flows as the counterflow that flows as being opposed to the flow of air (arrow YA).
  • refrigerant flows as the parallel flow that flows in parallel to the flow of air (arrow YA).
  • the non-azeotropic refrigerant mixture has a property to decrease in temperature as a degree of dryness lowers in a two-phase state.
  • refrigerant that flows as the counterflow decreases in temperature as it flows in an orientation opposite to the direction of flow of air.
  • refrigerant that flows as the parallel flow decreases in temperature as it flows in a direction the same as the direction of flow of air.
  • the temperature of air that passes through outdoor first heat exchanger 13 is higher than the temperature of air that passes through outdoor second heat exchanger 15, and in outdoor heat exchanger 11, an amount of heat exchange between refrigerant and air increases in particular in outdoor first heat exchanger 13. Consequently, performance of air-conditioner 1 during the cooling operation can be improved.
  • Fig. 6 shows graphs GR1 and GR2 of a temperature of refrigerant that flows through outdoor heat exchanger 11 during the heating operation and graphs GA1 and GA2 of a temperature of air that passes through outdoor heat exchanger 11.
  • the upper tier shows also outdoor heat exchanger 11 and the like shown in Fig. 4 .
  • graph GR1 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor first heat exchanger 13.
  • the temperature of refrigerant immediately before it flows into outdoor first heat exchanger 13 is temperature TAin and the temperature of refrigerant immediately after it flows through outdoor first heat exchanger 13 is temperature TAout.
  • Graph GR2 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor second heat exchanger 15.
  • the temperature of refrigerant immediately before it flows into outdoor second heat exchanger 15 is temperature TBin and the temperature of refrigerant immediately after it flows through outdoor second heat exchanger 15 is temperature TBout.
  • Graph GA1 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor first heat exchanger 13.
  • Graph GA2 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor second heat exchanger 15.
  • refrigerant flows as the parallel flow that flows in parallel to the flow of air (arrow YA).
  • refrigerant flows as the counterflow that flows as being opposed to the flow of air (arrow YA).
  • the temperature of air that passes through outdoor second heat exchanger 15 is lower than the temperature of air that passes through outdoor first heat exchanger 13, and in outdoor heat exchanger 11, an amount of heat exchange between refrigerant and air increases in particular in outdoor second heat exchanger 15. Consequently, performance of air-conditioner 1 during the heating operation can be improved.
  • outdoor first heat exchanger 13 and outdoor second heat exchanger 15 are connected in parallel with respect to refrigeration cycle circuit 51.
  • indoor first heat exchanger 13 and outdoor second heat exchanger 15 are connected in parallel with respect to refrigeration cycle circuit 51.
  • a Y-shaped or T-shaped branch portion 61 may be provided at each of branch and merge point P1 and branch and merge point P2.
  • Y-shaped or T-shaped branch portion 61 may be provided at each of branch and merge point P3 and branch and merge point P4.
  • outdoor heat exchanger 11 is provided with an outdoor third heat exchanger 17 as a third heat exchanger in addition to outdoor first heat exchanger 13 and outdoor second heat exchanger 15.
  • Outdoor third heat exchanger 17 is connected in series between expansion valve 19 and outdoor first heat exchanger 13 and outdoor second heat exchanger 15 connected in parallel, with respect to refrigeration cycle circuit 51.
  • Outdoor first heat exchanger 13 is arranged below outdoor first heat exchanger 13 and outdoor second heat exchanger 15.
  • the number of refrigerant flow paths in outdoor first heat exchanger 13 is the first number of refrigerant flow paths
  • the number of refrigerant flow paths in outdoor second heat exchanger 15 is the second number of refrigerant flow paths
  • the number of refrigerant flow paths in outdoor third heat exchanger 17 is the third number of refrigerant flow paths.
  • the third number of refrigerant flow paths is smaller than the first number of refrigerant flow paths and the second number of refrigerant flow paths.
  • Outdoor third heat exchanger 17 includes a fifth part 17a and a sixth part 17b.
  • Fifth part 17a and sixth part 17b are connected in series.
  • Fifth part 17a and sixth part 17b are arranged along the direction of passage of air (see arrow YA).
  • Fifth part 17a is arranged on the windward side.
  • Sixth part 17b is arranged on the leeward side.
  • a gas-liquid two-phase distributor 21c as a third gas-liquid two-phase distributor is connected on a side opposite to a side where sixth part 17b is connected, with respect to fifth part 17a.
  • a gas distributor 23c as a third gas distributor is connected on a side opposite to a side where fifth part 17a is connected, with respect to sixth part 17b.
  • Air-conditioner 1 is provided with a flow path R5 as a third flow path including a portion through which gas distributor 23c sixth part 17b, fifth part 17a, and gas-liquid two-phase distributor 21c are sequentially connected. Since the construction is otherwise similar to the construction of air-conditioner 1 shown in Figs. 1 and 2 , identical members have identical reference characters allotted and description thereof will not be repeated unless necessary.
  • refrigerant flows in parallel through flow path R1 and flow path R2, flows of refrigerant thereafter merge at branch and merge point P2, and merged refrigerant flows through flow path R5.
  • flow path R5 refrigerant successively flows through gas distributor 23c, sixth part 17b, fifth part 17a, and gas-liquid two-phase distributor 21c.
  • outdoor third heat exchanger 17 refrigerant flows through sixth part 17b arranged on the leeward side and thereafter flows as the counterflow that flows through fifth part 17a arranged on the windward side.
  • Refrigerant high-pressure liquid refrigerant
  • Refrigerant that flows through outdoor unit 3 passes through expansion valve 19 to become refrigerant in the gas-liquid two-phase state containing low-pressure gas refrigerant and liquid refrigerant.
  • Low-pressure refrigerant in the gas-liquid two-phase state flows into indoor unit 5 and becomes low-pressure gas refrigerant, and resultant low-pressure gas refrigerant flows into compressor 7. This cycle is repeated hereafter.
  • Refrigerant in the gas-liquid two-phase state flows through the outdoor third heat exchanger (flow path R1) and thereafter flows through outdoor first heat exchanger 13 (flow path R1) and outdoor second heat exchanger 15 (flow path R2) in parallel.
  • flow path R5 refrigerant successively flows through gas-liquid two-phase distributor 21c, fifth part 17a, sixth part 17b, and gas distributor 23c.
  • outdoor third heat exchanger 17 refrigerant flows through fifth part 17a arranged on the windward side and thereafter flows as the parallel flow that flows through sixth part 17b arranged on the leeward side.
  • Air-conditioner 1 described above obtains an effect of suppression of pressure loss of refrigerant and an effect of suppression of increase in amount of refrigerant, as described in connection with air-conditioner 1 according to the first embodiment.
  • Air-conditioner 1 according to the second embodiment further obtains an effect as follows.
  • Fig. 12 shows graphs GR1, GR2, and GR3 of a temperature of refrigerant that flows through outdoor heat exchanger 11 in the cooling operation and graphs GA1, GA2, and GA3 of a temperature of air that passes through outdoor heat exchanger 11.
  • the upper tier shows also outdoor heat exchanger 11 and the like shown in Fig. 10 .
  • graph GR1 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor first heat exchanger 13.
  • the temperature of refrigerant immediately before it flows into outdoor first heat exchanger 13 is temperature TAin and the temperature of refrigerant immediately after it flows through outdoor first heat exchanger 13 is temperature TAout.
  • Graph GR2 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor second heat exchanger 15.
  • the temperature of refrigerant immediately before it flows into outdoor second heat exchanger 15 is temperature TBin and the temperature of refrigerant immediately after it flows through outdoor second heat exchanger 15 is temperature TBout.
  • Graph GR3 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor third heat exchanger 17.
  • the temperature of refrigerant immediately before it flows into outdoor third heat exchanger 17 is a temperature TCin and the temperature of refrigerant immediately after it flows through outdoor third heat exchanger 17 is a temperature TCout.
  • Graph GA1 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor first heat exchanger 13.
  • Graph GA2 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor second heat exchanger 15.
  • Graph GA3 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor third heat exchanger 17.
  • refrigerant flows as the counterflow that flows as being opposed to the flow of air (arrow YA).
  • refrigerant flows as the parallel flow that flows in parallel to the flow of air (arrow YA).
  • refrigerant flows as the counterflow that flows as being opposed to the flow of air (arrow YA).
  • Refrigerant that flows through outdoor second heat exchanger 15 as the parallel flow flows into outdoor third heat exchanger 17, together with refrigerant that flows through outdoor first heat exchanger 13.
  • refrigerant flows as the counterflow.
  • the temperature difference between refrigerant and air can thus be ensured, and the amount of heat exchange between refrigerant and air in outdoor third heat exchanger 17 can be increased. Consequently, performance during the cooling operation can further be improved.
  • Fig. 13 shows graphs GR1, GR2, and GR3 of a temperature of refrigerant that flows through outdoor heat exchanger 11 during the heating operation and graphs GA1, GA2, and GA3 of a temperature of air that passes through outdoor heat exchanger 11.
  • the upper tier shows also outdoor heat exchanger 11 and the like shown in Fig. 11 .
  • graph GR1 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor first heat exchanger 13.
  • the temperature of refrigerant immediately before it flows into outdoor first heat exchanger 13 is temperature TAin and the temperature of refrigerant immediately after it flows through outdoor first heat exchanger 13 is temperature TAout.
  • Graph GR2 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor second heat exchanger 15.
  • the temperature of refrigerant immediately before it flows into outdoor second heat exchanger 15 is temperature TBin and the temperature of refrigerant immediately after it flows through outdoor second heat exchanger 15 is temperature TBout.
  • Graph GR3 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor third heat exchanger 17.
  • the temperature of refrigerant immediately before it flows into outdoor third heat exchanger 17 is temperature TCin and the temperature of refrigerant immediately after it flows through outdoor third heat exchanger 17 is temperature TCout.
  • Graph GA1 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor first heat exchanger 13.
  • Graph GA2 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor second heat exchanger 15.
  • Graph GA3 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor third heat exchanger 17.
  • Refrigerant that is sent to outdoor unit 3 and passes through expansion valve 19 to be in the gas-liquid two-phase state flows through outdoor third heat exchanger 17, and thereafter flows in parallel through outdoor first heat exchanger 13 and outdoor second heat exchanger 15.
  • refrigerant in the gas-liquid two-phase state flows as the parallel flow.
  • the third number of refrigerant flow paths in outdoor third heat exchanger 17 is smaller than the first number of refrigerant flow paths in outdoor first heat exchanger 13 and the second number of refrigerant flow paths in outdoor second heat exchanger 15. Therefore, outdoor third heat exchanger 17 is relatively higher in pressure loss of refrigerant than outdoor first heat exchanger 13 and outdoor second heat exchanger 15.
  • the temperature of refrigerant (see graph GR3) that flows through outdoor third heat exchanger 17 is thus higher than the temperature of refrigerant (see graph GR1) that flows through outdoor first heat exchanger 13 and the temperature of refrigerant (see graph GR2) that flows through outdoor second heat exchanger 15.
  • Outdoor third heat exchanger 17 is arranged below outdoor first heat exchanger 13 and outdoor second heat exchanger 15. In the heating operation, condensation water attached to outdoor first heat exchanger 13 and outdoor second heat exchanger 15 flows down to outdoor third heat exchanger 17 arranged below and frost tends to grow in outdoor third heat exchanger 17.
  • an outdoor first flow rate regulation valve 25a and an outdoor second flow rate regulation valve 25b are arranged in outdoor unit 3.
  • Outdoor first flow rate regulation valve 25a is arranged in flow path R1. Outdoor first flow rate regulation valve 25a is arranged in a portion of flow path R1 between branch and merge point P2 and gas-liquid two-phase distributor 21a. Outdoor second flow rate regulation valve 25b is arranged in flow path R2. Outdoor second flow rate regulation valve 25b is arranged in a portion of flow path R2 between branch and merge point P2 and gas-liquid two-phase distributor 21b.
  • An indoor first flow rate regulation valve 37a and an indoor second flow rate regulation valve 37b are arranged in indoor unit 5.
  • Indoor first flow rate regulation valve 37a is arranged in flow path R3.
  • Indoor first flow rate regulation valve 37a is arranged in a portion of flow path R3 between branch and merge point P4 and gas-liquid two-phase distributor 33a.
  • Indoor second flow rate regulation valve 37b is arranged in a portion of flow path R4 between branch and merge point P4 and gas-liquid two-phase distributor 33b.
  • a solenoid valve or an electronic expansion valve can be employed as outdoor first flow rate regulation valve 25a, outdoor second flow rate regulation valve 25b, indoor first flow rate regulation valve 37a, and indoor second flow rate regulation valve 37b.
  • expansion valve 19 does not have to be provided. Since the construction is otherwise similar to the construction of air-conditioner 1 shown in Figs. 1 and 2 , identical members have identical reference characters allotted and description thereof will not be repeated unless necessary.
  • refrigerant In flow path R1, refrigerant successively flows through gas distributor 23a, second part 13b, first part 13a, gas-liquid two-phase distributor 21a, and outdoor first flow rate regulation valve 25a.
  • outdoor first heat exchanger 13 refrigerant flows through second part 13b arranged on the leeward side and thereafter flows as the counterflow that flows through first part 13a arranged on the windward side.
  • refrigerant In flow path R2, refrigerant successively flows through gas distributor 23b, third part 15a, fourth part 15b, gas-liquid two-phase distributor 21b, and outdoor second flow rate regulation valve 25b.
  • refrigerant flows through third part 15a arranged on the windward side and thereafter flows as the parallel flow that flows through fourth part 15b arranged on the leeward side.
  • Refrigerant that flows through flow path R1 and refrigerant that flows through flow path R2 merge, and merged refrigerant passes through expansion valve 19 to become refrigerant in the gas-liquid two-phase state containing low-pressure gas refrigerant and liquid refrigerant.
  • Resultant low-pressure refrigerant in the gas-liquid two-phase state is sent to indoor unit 5.
  • Refrigerant sent to indoor unit 5 flows through flow path R3 (indoor first heat exchanger 29) and flow path R4 (indoor second heat exchanger 31) in parallel.
  • refrigerant successively flows through indoor first flow rate regulation valve 37a, gas-liquid two-phase distributor 33a, indoor first heat exchanger 29, and gas distributor 35a.
  • indoor first heat exchanger 29 refrigerant flows as the parallel flow.
  • refrigerant successively flows through indoor second flow rate regulation valve 37b, gas-liquid two-phase distributor 33b, indoor second heat exchanger 31, and gas distributor 35b.
  • indoor second heat exchanger 31 refrigerant flows as the counterflow.
  • Refrigerant that flows through flow path R3 and refrigerant that flows through flow path R4 merge, and merged refrigerant flows into compressor 7. This cycle is repeated hereafter.
  • refrigerant successively flows through gas distributor 35a, indoor first heat exchanger 29, gas-liquid two-phase distributor 33a, and indoor first flow rate regulation valve 37a.
  • indoor first heat exchanger 29 refrigerant flows as the counterflow.
  • flow path R4 refrigerant successively flows through gas distributor 35b, indoor second heat exchanger 31, gas-liquid two-phase distributor 33b, and indoor second flow rate regulation valve 37b.
  • refrigerant flows as the parallel flow.
  • Refrigerant that flows through flow path R3 and refrigerant that flows through flow path R4 merge, and merged refrigerant is sent to outdoor unit 3 and passes through expansion valve 19 to become refrigerant in the gas-liquid two-phase state containing low-pressure gas refrigerant and liquid refrigerant.
  • Refrigerant in the gas-liquid two-phase state flows through flow path R1 (outdoor first heat exchanger 13) and flow path R2 (outdoor second heat exchanger 15) in parallel.
  • refrigerant in flow path R1, refrigerant successively flows through outdoor first flow rate regulation valve 25a, gas-liquid two-phase distributor 21a, first part 13a, second part 13b, and gas distributor 23a. In outdoor first heat exchanger 13, refrigerant flows as the parallel flow. In flow path R2, refrigerant successively flows through outdoor second flow rate regulation valve 25b, gas-liquid two-phase distributor 21b, fourth part 15b, third part 15a, and gas distributor 23b. In outdoor second heat exchanger 15, refrigerant flows as the counterflow.
  • Refrigerant that flows through flow path R1 and refrigerant that flows through flow path R2 merge, and merged refrigerant flows into compressor 7 through four-way valve 9. This cycle is repeated hereafter.
  • Air-conditioner 1 described above obtains an effect of suppression of pressure loss of refrigerant and an effect of suppression of increase in amount of refrigerant, as described in connection with air-conditioner 1 according to the first embodiment.
  • Air-conditioner 1 according to the third embodiment further obtains an effect as follows.
  • Fig. 18 shows graphs GR1 and GR2 of a temperature of refrigerant that flows through outdoor heat exchanger 11 during the cooling operation and graphs GA1 and GA2 of a temperature of air that passes through outdoor heat exchanger 11.
  • the upper tier shows also outdoor heat exchanger 11 and the like shown in Fig. 16 .
  • graph GR1 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor first heat exchanger 13.
  • the temperature of refrigerant immediately before it flows into outdoor first heat exchanger 13 is temperature TAin and the temperature of refrigerant immediately after it flows through outdoor first heat exchanger 13 is temperature TAout.
  • Graph GR2 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor second heat exchanger 15.
  • the temperature of refrigerant immediately before it flows into outdoor second heat exchanger 15 is temperature TBin and the temperature of refrigerant immediately after it flows through outdoor second heat exchanger 15 is temperature TBout.
  • Graph GA1 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor first heat exchanger 13.
  • Graph GA2 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor second heat exchanger 15.
  • temperature TBout of refrigerant immediately after it flows through outdoor second heat exchanger 15 is lower than in an example where outdoor first flow rate regulation valve 25a and outdoor second flow rate regulation valve 25b are not provided (see Fig. 5 ). Temperature TAout of refrigerant immediately after it flows through outdoor first heat exchanger 13 is higher than in the example where outdoor first flow rate regulation valve 25a and outdoor second flow rate regulation valve 25b are not provided (see Fig. 5 ).
  • outdoor second flow rate regulation valve 25b and the like can decrease a difference between temperature TAout and temperature TBout. Therefore, by regulating the flow rate of refrigerant with the use of outdoor second flow rate regulation valve 25b and the like such that temperature TAout (outlet side enthalpy) of refrigerant immediately after it flows through outdoor first heat exchanger 13 is substantially the same as temperature TBout (outlet side enthalpy) of refrigerant immediately after it flows through outdoor second heat exchanger 15, heat transfer performance of outdoor heat exchanger 11 can be improved.
  • Fig. 19 shows graphs GR1 and GR2 of a temperature of refrigerant that flows through outdoor heat exchanger 11 during the heating operation and graphs GA1 and GA2 of a temperature of air that passes through outdoor heat exchanger 11.
  • the upper tier shows also outdoor heat exchanger 11 and the like shown in Fig. 17 .
  • graph GR1 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor first heat exchanger 13.
  • the temperature of refrigerant immediately before it flows into outdoor first heat exchanger 13 is temperature TAin and the temperature of refrigerant immediately after it flows through outdoor first heat exchanger 13 is temperature TAout.
  • Graph GR2 shows relation between a flow (direction) of air and a temperature of refrigerant that flows through outdoor second heat exchanger 15.
  • the temperature of refrigerant immediately before it flows into outdoor second heat exchanger 15 is temperature TBin and the temperature of refrigerant immediately after it flows through outdoor second heat exchanger 15 is temperature TBout.
  • Graph GA1 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor first heat exchanger 13.
  • Graph GA2 shows relation between a flow (direction) of air and a temperature of air that passes through outdoor second heat exchanger 15.
  • temperature TAout of refrigerant immediately after it flows through outdoor first heat exchanger 13 is higher than in the example where outdoor first flow rate regulation valve 25a and outdoor second flow rate regulation valve 25b are not provided (see Fig. 5 ).
  • Temperature TBout of refrigerant immediately after it flows through outdoor second heat exchanger 15 is lower than in the example where outdoor first flow rate regulation valve 25a and outdoor second flow rate regulation valve 25b are not provided (see Fig. 5 ).
  • outdoor first flow rate regulation valve 25a and the like can decrease difference between temperature TAout and temperature TBout. Therefore, by regulating the flow rate of refrigerant with the use of outdoor first flow rate regulation valve 25a and the like such that temperature TAout (outlet side enthalpy) of refrigerant immediately after it flows through outdoor first heat exchanger 13 is substantially the same as temperature TBout (outlet side enthalpy) of refrigerant immediately after it flows through outdoor second heat exchanger 15, heat transfer performance of outdoor heat exchanger 11 can be improved.
  • a temperature sensor such as a thermistor may be provided in refrigerant pipe 41.
  • a temperature sensor T1 is provided in a portion S1 of refrigerant pipe 41 located opposite to the side where first part 13a is connected, with respect to gas-liquid two-phase distributor 21a, and a temperature sensor T2 is arranged in a portion S2 of refrigerant pipe 41 located opposite to the side where second part 13b is connected, with respect to gas distributor 23a.
  • a temperature sensor T4 is provided in a portion S4 of refrigerant pipe 41 located opposite to the side where fourth part 15b is connected, with respect to gas-liquid two-phase distributor 21b, and a temperature sensor T3 is provided in a portion S3 of refrigerant pipe 41 located opposite to the side where third part 15a is connected, with respect to gas distributor 23b.
  • a pressure sensor may be provided in refrigerant pipe 41 (portions S1 to S4) other than temperature sensors T1 to T4.
  • Each outlet side enthalpy can more accurately be calculated with the use of the pressure sensor.
  • a two-row structure including two rows of heat transfer tubes where first part 13a (third part 15a) and second part 13b (fourth part 15b) are arranged in the direction of passage of air is exemplified as outdoor heat exchanger 11 or the like
  • a multiple-row structure including three or more rows may be applicable.
  • a circular tube having a circular cross-section or a low-profile tube having a low-profile cross-section may be applicable as the heat transfer tube arranged in outdoor heat exchanger 11 or the like.
  • indoor heat exchanger 27 in indoor unit 5 also obtains an effect similar to that of outdoor heat exchanger 11. Furthermore, at least one of outdoor heat exchanger 11 and indoor heat exchanger 27 should only be applied as the first heat exchanger and the second heat exchanger.
  • Air-conditioner 1 described in each embodiment can variously be combined as necessary.
  • the present disclosure is effectively made use of as an air-conditioner where a non-azeotropic refrigerant mixture is used as refrigerant.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP21937927.8A 2021-04-23 2021-04-23 Climatiseur Withdrawn EP4328521A4 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2021/016441 WO2022224436A1 (fr) 2021-04-23 2021-04-23 Climatiseur

Publications (2)

Publication Number Publication Date
EP4328521A1 true EP4328521A1 (fr) 2024-02-28
EP4328521A4 EP4328521A4 (fr) 2024-05-29

Family

ID=83723466

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21937927.8A Withdrawn EP4328521A4 (fr) 2021-04-23 2021-04-23 Climatiseur

Country Status (5)

Country Link
US (1) US20240167717A1 (fr)
EP (1) EP4328521A4 (fr)
JP (1) JPWO2022224436A1 (fr)
CN (1) CN117203476A (fr)
WO (1) WO2022224436A1 (fr)

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08170864A (ja) 1994-12-19 1996-07-02 Sanyo Electric Co Ltd ヒートポンプ空調装置及び除霜方法
JPH09196489A (ja) 1996-01-19 1997-07-31 Fujitsu General Ltd 空気調和機の冷凍サイクル
JP2010139097A (ja) * 2008-12-09 2010-06-24 Mitsubishi Electric Corp 空気調和機
WO2015063857A1 (fr) * 2013-10-29 2015-05-07 三菱電機株式会社 Échangeur thermique et climatiseur
WO2016001957A1 (fr) * 2014-06-30 2016-01-07 日立アプライアンス株式会社 Climatiseur
WO2018047330A1 (fr) * 2016-09-12 2018-03-15 三菱電機株式会社 Climatiseur
CN109690209B (zh) * 2016-09-12 2021-05-07 三菱电机株式会社 空调装置
EP3517855B1 (fr) * 2016-09-23 2020-09-16 Mitsubishi Electric Corporation Échangeur de chaleur et dispositif à cycle de réfrigération
JP2018162964A (ja) * 2017-03-27 2018-10-18 ダイキン工業株式会社 熱交換器ユニット
JP6910436B2 (ja) * 2017-06-29 2021-07-28 三菱電機株式会社 室外ユニットおよび冷凍サイクル装置
JP7184897B2 (ja) * 2018-07-27 2022-12-06 三菱電機株式会社 冷凍サイクル装置
JP2020153646A (ja) * 2019-03-22 2020-09-24 ダイキン工業株式会社 空気調和機

Also Published As

Publication number Publication date
WO2022224436A1 (fr) 2022-10-27
CN117203476A (zh) 2023-12-08
US20240167717A1 (en) 2024-05-23
EP4328521A4 (fr) 2024-05-29
JPWO2022224436A1 (fr) 2022-10-27

Similar Documents

Publication Publication Date Title
EP2495510B1 (fr) Pompe à chaleur
EP3147591B1 (fr) Dispositif de climatisation
EP3064881B1 (fr) Échangeur thermique et climatiseur
EP3009771B1 (fr) Dispositif de climatisation
EP2851641B1 (fr) Échangeur de chaleur, unité intérieure, et dispositif de cycle de réfrigération
EP2860471B1 (fr) Climatiseur multipièce
EP3205967A1 (fr) Échangeur thermique et dispositif de climatisation
JP7583738B2 (ja) 空気調和装置
EP2157389B1 (fr) Conditionneur d'air avec échangeur de chaleur
JP6715929B2 (ja) 冷凍サイクル装置およびそれを備えた空気調和装置
CN114867972B (zh) 空调设备
CN102748808A (zh) 复式空调器以及该复式空调器的控制方法
EP4130638B1 (fr) Échangeur de chaleur
EP3795927B1 (fr) Dispositif à cycle frigorifique
GB2566165A (en) Refrigerant branching distributor, heat exchanger comprising same, and refrigeration cycle device
US12130057B2 (en) Heat exchanger, outdoor unit, and refrigeration cycle device
US11781788B2 (en) Cascade air conditioner system
EP3156743A1 (fr) Appareil de climatisation d'air
CN216481725U (zh) 制冷系统及其制冷设备
EP4328521A1 (fr) Climatiseur
EP4083558B1 (fr) Échangeur de chaleur et dispositif à cycle frigorifique
CN113494790A (zh) 制冷系统、化霜控制方法及其制冷设备
US12498123B2 (en) Outdoor heat exchanger and air conditioner
EP4166858A1 (fr) Unité extérieure pour dispositif de climatisation
CN114812010A (zh) 空调机及热交换器

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20231010

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

A4 Supplementary search report drawn up and despatched

Effective date: 20240429

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 39/04 20060101ALI20240423BHEP

Ipc: F25B 39/02 20060101ALI20240423BHEP

Ipc: F25B 41/42 20210101ALI20240423BHEP

Ipc: F25B 39/00 20060101ALI20240423BHEP

Ipc: F25B 13/00 20060101ALI20240423BHEP

Ipc: F25B 6/02 20060101ALI20240423BHEP

Ipc: F25B 5/02 20060101AFI20240423BHEP

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20240905