EP4040084B1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

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Publication number
EP4040084B1
EP4040084B1 EP20871516.9A EP20871516A EP4040084B1 EP 4040084 B1 EP4040084 B1 EP 4040084B1 EP 20871516 A EP20871516 A EP 20871516A EP 4040084 B1 EP4040084 B1 EP 4040084B1
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EP
European Patent Office
Prior art keywords
heat exchange
exchange section
refrigeration cycle
heat
evaporator
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.)
Active
Application number
EP20871516.9A
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German (de)
English (en)
Other versions
EP4040084A4 (fr
EP4040084A1 (fr
Inventor
Eiji Kumakura
Ikuhiro Iwata
Takuro Yamada
Ryuhei Kaji
Tomoki HIROKAWA
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Daikin Industries Ltd
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Daikin Industries Ltd
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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
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/12—Inflammable refrigerants
    • F25B2400/121—Inflammable refrigerants using R1234
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • the present invention relates to a refrigeration cycle apparatus in which a non-azeotropic refrigerant mixture is enclosed.
  • the evaporator described in WO 2017/183180 A1 is a stack-type heat exchanger in which elongated holes each having a longitudinal diameter extending in the width direction of a fin are provided at a predetermined interval in a direction orthogonal to the width direction and the thickness direction of the fin and in which a flat pipe is inserted into each of the elongated holes.
  • EP 3 534 103 A1 discloses a heat exchanger that is supplied with air by a fan and that includes a fin that is plate-shaped, a first heat transfer tube that is flat and extends through the fin, and a second heat transfer tube that is flat and extends through the fin and is disposed at a distance from the first heat transfer tube in a gravity direction.
  • the first heat transfer tube has a first upwind end located upwind and a first downwind end located downwind.
  • the second heat transfer tube has a second upwind end located upwind and a second downwind end located downwind.
  • the fin has an upwind fin end and a downwind fin end.
  • the fin has an upwind fin region defined by the upwind fin end and the first imaginary line and a downwind fin region defined by the second imaginary line and the downwind fin end.
  • a dimension of the upwind fin region is larger than a dimension of the downwind fin region in a passing direction.
  • WO 2019/004139 A1 discloses a heat exchanger with which adequate performance can be exhibited on both the upwind side and the downwind side in the airflow direction even when an increase in ventilation resistance due to the adhesion of frost is delayed, and with which the pressure resistance of flat multi-hole tubes is easily ensured.
  • This heat exchanger is equipped with flat multi-hole tubes having a plurality of channels aligned in the airflow direction, and fins in which the flat multi-hole tubes are inserted and secured in notches cut from the downwind side toward the upwind side in the airflow direction, and which have continuous parts joined at the top and bottom on the upwind side of the flat multi-hole tubes.
  • JP H08 54149 A aims at preventing frosting of an evaporator and avoiding the deterioration of performance of the whole of a device, in the refrigerating device employing the refrigerant of non-azeotropic mixture.
  • the amount of heat exchange in a first evaporator, whose temperature is low, is increased and the temperature of the tip ends of fins is increased whereby frosting can be prevented by a constitution wherein a refrigerant of a non-azeotropic mixture, obtained by mixing two kinds or more of refrigerants, whose boiling points are different from each other, with a predetermined ratio, is sealed into a refrigerant circuit, formed by connecting a compressor, a condenser, a reducer, the first evaporator and a second evaporator, while the fin pitch of the first evaporator is made more thick than the same of the second evaporator.
  • disposing the center of the entirety of a flat pipe group in the width direction on the air windward side of the center of a fin in the width direction increases a difference between an air temperature and a heat-exchanger surface temperature, which improves heat exchange performance but easily causes frost.
  • disposing the center of the entirety of the flat pipe group in the width direction on the leeward side of the center of the fin in the width direction tends to improve frost proof performance (capacity of suppressing frost) but degrades heat exchange performance.
  • the composition of a non-azeotropic refrigerant mixture is different between a liquid phase and a gas phase, the refrigerant temperature at an inlet is lower than that at an outlet in an evaporator.
  • frost is easily generated.
  • a distance between the flat pipes and a windward-side edge of the fin is considered from the point of view of drainage of condensed water and melted water but is not considered from the point of view of frost proof performance (capacity of suppressing frost) and/or heat exchange performance in a case where a refrigerant that flows in the evaporator is specified as a non-azeotropic refrigerant mixture.
  • a refrigeration cycle apparatus is a refrigeration cycle apparatus in which a non-azeotropic refrigerant mixture is enclosed, the refrigeration cycle apparatus comprising an evaporator and a fan, the fan being configured to take outdoor air, cause the outdoor air to exchange heat with the refrigerant in the evaporator, and then do discharge the air to the outside, the evaporator including a plurality of fins and a plurality of heat transfer tubes.
  • the plurality of fins are arranged at a predetermined interval in a plate thickness direction.
  • the plurality of heat transfer tubes extend through the plurality of fins in the plate thickness direction.
  • the evaporator comprises a first header and a second header, wherein the first header and the second header are coupled to both ends of the plurality of heat transfer tubes.
  • a first heat exchange section is formed.
  • the first heat exchange section when the plurality of heat transfer tubes are viewed as a heat-transfer-tube group in the plate thickness direction of the fins, a distribution center of the heat-transfer-tube group in an airflow direction of the fan is positioned on the leeward side of the center of the fins in the airflow direction.
  • an enclosed refrigerant is a non-azeotropic refrigerant mixture
  • a refrigerant temperature at an evaporator inlet is low compared with at an outlet, which easily causes frost.
  • the distribution center of the heat-transfer-tube group is positioned on the leeward side of the center of the fins in the airflow direction.
  • frost is not easily generated compared with when the distribution center of the heat-transfer-tube group is positioned on the windward side of the center of the fins.
  • a second heat exchange section is further formed.
  • the distribution center of the heat-transfer-tube group is positioned on the windward side of the center of the fins in the airflow direction.
  • the temperature of the non-azeotropic refrigerant mixture increases from the inlet toward the outlet of the evaporator. It is thus preferable on the outlet side to put high priority on heat exchange performance rather than frost proof performance and to position the distribution center of the heat-transfer-tube group on the windward side of the center of the fins in the airflow direction.
  • the second heat exchange section in which the distribution center of the heat-transfer-tube group is positioned on the windward side of the center of the fins in the airflow direction, it is possible to, for example, dispose the first heat exchange section on the evaporator inlet side and the second heat exchange section on the evaporator outlet side.
  • the first heat exchange section on the evaporator inlet side and the second heat exchange section on the evaporator outlet side.
  • the first heat exchange section is provided on an evaporator inlet side and the second heat exchange section is provided on an evaporator outlet side.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the first aspect in which a third heat exchange section is further formed.
  • the distribution center of the heat-transfer-tube group substantially coincides with the center of the fins in the airflow direction.
  • this refrigeration cycle apparatus for example, it is possible to dispose the first heat exchange section on the evaporator inlet side, the second heat exchange section on the evaporator outlet side, and the third heat exchange section between the first heat exchange section and the second heat exchange section.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the first aspect in which the first heat exchange section and the second heat exchange section are integral with each other.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the second aspect in which the first heat exchange section is integral with at least either one of the second heat exchange section and the third heat exchange section.
  • a refrigeration cycle apparatus is a refrigeration cycle apparatus in which a non-azeotropic refrigerant mixture is enclosed, the refrigeration cycle apparatus comprising an evaporator and a fan, the fan being configured to take outdoor air, cause the outdoor air to exchange heat with the refrigerant in the evaporator, and then to discharge the air to the outside, the evaporator including a plurality of fins and a plurality of heat transfer tubes.
  • the plurality of fins are arranged at a predetermined interval in a plate thickness direction.
  • the plurality of heat transfer tubes extend through the plurality of fins in the plate thickness direction.
  • the evaporator comprises a first header and a second header, wherein the first header and the second header are coupled to both ends of the plurality of heat transfer tubes.
  • a first heat exchange section and a second heat exchange section are formed.
  • a distance from a windward-side end of the heat transfer tube positioned on the most windward side in an airflow direction of the fan to a windward-side end of the fins is a first dimension.
  • a distance from a windward-side end of the heat transfer tube positioned on the most windward side in the airflow direction to a windward-side end of the fins is a second dimension smaller than the first dimension.
  • the temperature of the non-azeotropic refrigerant mixture increases from the inlet toward the outlet of the evaporator. It is thus preferable to put a high priority on frost proof performance on the inlet side and put a high priority on heat exchange performance on the outlet side.
  • first heat exchange section on the evaporator inlet side and the second heat exchange section on the evaporator outlet side.
  • the first heat exchange section is provided on an evaporator inlet side and the second heat exchange section is provided on an evaporator outlet side.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the fifth aspect in which a third heat exchange section is further formed.
  • a distance from a windward-side end of the heat transfer tube positioned on the most windward side in the airflow direction to a windward-side end of the fins and a distance from a leeward-side end of the heat transfer tube positioned on the most leeward side in the airflow direction to a leeward-side end of the fins are equal to each other.
  • this refrigeration cycle apparatus for example, it is possible to dispose the first heat exchange section on the evaporator inlet side, the second heat exchange section on the evaporator outlet side, and the third heat exchange section between the first heat exchange section and the second heat exchange section.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the fifth aspect in which the first heat exchange section and the second heat exchange section are integral with each other.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the sixth aspect in which the first heat exchange section is integral with at least either one of the second heat exchange section and the third heat exchange section.
  • a refrigeration cycle apparatus is a refrigeration cycle apparatus in which a non-azeotropic refrigerant mixture is enclosed, the refrigeration cycle apparatus comprising an evaporator and a fan, the fan being configured to take outdoor air, cause the outdoor air to exchange heat with the refrigerant in the evaporator, and then to discharge the air to the outside, the evaporator including a plurality of fins and a plurality of heat transfer tubes.
  • the plurality of fins are arranged at a predetermined interval in a plate thickness direction.
  • the plurality of heat transfer tubes extend through the plurality of fins in the plate thickness direction.
  • the evaporator comprises a first header and a second header, wherein the first header and the second header are coupled to both ends of the plurality of heat transfer tubes.
  • the fins have a plurality of cutouts.
  • the plurality of cutouts are arranged in a direction orthogonal to both an airflow direction of the fan and the plate thickness direction.
  • the heat transfer tubes are flat multi-hole pipes inserted into the cutouts.
  • a first heat exchange section is formed in the first heat exchange section. In the first heat exchange section, the opening side of the cutouts is positioned on the leeward side in the airflow direction.
  • the first heat exchange section in which the opening side of the cutout is positioned on the leeward side in the airflow direction is formed, it is possible to improve frost proof performance by providing the first heat exchange section at least on the inlet side of the evaporator.
  • a second heat exchange section is further formed.
  • the opening side of the cutouts is positioned on the windward side in the airflow direction.
  • this refrigeration cycle apparatus for example, it is possible to dispose the first heat exchange section on the evaporator inlet side and the second heat exchange section on the evaporator outlet side. Thus, it is possible to try a combination suitable for a refrigerant temperature in the evaporator.
  • the first heat exchange section is provided on an evaporator inlet side and the second heat exchange section is provided on an evaporator outlet side.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to the ninth aspect in which the first heat exchange section and the second heat exchange section are integral with each other.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the first to tenth aspects.
  • the non-azeotropic refrigerant mixture includes any of a HFC refrigerant, a HFO refrigerant, CF3I, and a natural refrigerant.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the first to tenth aspects.
  • the non-azeotropic refrigerant mixture includes any of R32, R1132(E), R1234yf, R1234ze, CF3I, and CO2.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the first to tenth aspects.
  • the non-azeotropic refrigerant mixture includes at least R1132(E), R32, and R1234yf.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the first to tenth aspects.
  • the non-azeotropic refrigerant mixture includes at least R1132(E), R1123, and R1234yf.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the first to tenth aspects.
  • the non-azeotropic refrigerant mixture includes at least R1132(E) and R1234yf.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the first to tenth aspects.
  • the non-azeotropic refrigerant mixture includes at least R32, R1234yf, and at least one of R1132a and R1114.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the first to tenth aspects.
  • the non-azeotropic refrigerant mixture includes at least R32, CO2, R125, R134a, and R1234yf.
  • a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the first to tenth aspects.
  • the non-azeotropic refrigerant mixture includes at least R1132(Z) and R1234yf.
  • Fig. 1 is a schematic diagram of an air conditioning apparatus 1 according to one embodiment of the present invention.
  • the air conditioning apparatus 1 is a refrigeration cycle apparatus that performs cooling operation and heating operation by a vapor compression refrigeration cycle.
  • a refrigerant circuit 10 of the air conditioning apparatus 1 is constituted by an outdoor unit 2 and an indoor unit 4 that are connected to each other via a liquid-refrigerant connection pipe 5 and a gas-refrigerant connection pipe 6.
  • a refrigerant enclosed in the refrigerant circuit 10 is a non-azeotropic refrigerant mixture.
  • the non-azeotropic refrigerant mixture includes any of a HFC refrigerant, a HFO refrigerant, CF3I, and a natural refrigerant.
  • the indoor unit 4 is installed indoors and constitutes part of the refrigerant circuit 10.
  • the indoor unit 4 includes an indoor heat exchanger 41, an indoor fan 42, and an indoor-side control unit 44.
  • the indoor heat exchanger 41 functions as an evaporator for the refrigerant during cooling operation and cools indoor air.
  • the indoor heat exchanger 41 functions as a radiator for the refrigerant during heating operation and heats indoor air.
  • the refrigerant inlet side of the indoor heat exchanger 41 during cooling operation is connected to the liquid-refrigerant connection pipe 5, and the refrigerant outlet side thereof is connected to the gas-refrigerant connection pipe 6.
  • Fig. 2 is a front view of the indoor heat exchanger 41.
  • the indoor heat exchanger 41 is a cross-fin-type heat exchanger.
  • the indoor heat exchanger has a heat transfer fin 412 and a heat transfer tube 411.
  • the heat transfer fin 412 is a thin aluminum flat plate.
  • the heat transfer fin 412 has a plurality of through holes.
  • the heat transfer tube 411 has a straight tube 411a inserted into the through holes of the heat transfer fin 412, and U-shaped tubes 411b and 411c that couple end portions of mutually adjacent straight tubes 411a to each other.
  • the straight tube 411a is in close contact with the heat transfer fin 412 by being subjected to tube expansion processing after inserted into the through holes of the heat transfer fin 412.
  • the straight tube 411a and the first U-shaped tube 411b are formed integrally with each other.
  • the second U-shaped tube 411c is coupled to an end portion of the straight tube 411a by welding, brazing, or the like after the straight tube 411a is inserted into the through holes of the heat transfer fin 412 and subjected to tube expansion processing.
  • the indoor fan 42 takes indoor air into the indoor unit 4, causes the indoor air to exchange heat with the refrigerant in the indoor heat exchanger 41, and then supplies the air to the inside of a room.
  • a centrifugal fan, a multi-blade fan, or the like is employed as the indoor fan 42.
  • the indoor fan 42 is driven by an indoor fan motor 43.
  • the indoor-side control unit 44 controls operation of each portion that constitutes the indoor unit 4.
  • the indoor-side control unit 44 has a microcomputer and a memory that are for controlling the indoor unit 4.
  • the indoor-side control unit 44 transmits and receives a control signal and the like to and from a remote controller (not illustrated). In addition, the indoor-side control unit 44 transmits and receives a control signal and the like to and from an outdoor-side control unit 38 of the outdoor unit 2 via a transmission line 8a.
  • the outdoor unit 2 is installed outdoors and constitutes part of the refrigerant circuit 10.
  • the outdoor unit 2 includes a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 26, a liquid-side shutoff valve 27, and a gas-side shutoff valve 28.
  • the compressor 21 is a device that compresses a low-pressure refrigerant of the refrigeration cycle.
  • the compressor 21 drives and rotates a positive-displacement compression element (not illustrated) of a rotary type, a scroll type, or the like by a compressor motor 21a.
  • a suction pipe 31 is connected to the suction side of the compressor 21, and a discharge pipe 32 is connected to the discharge side thereof.
  • the suction pipe 31 is a refrigerant pipe that connects the suction side of the compressor 21 and the four-way switching valve 22 to each other.
  • the discharge pipe 32 is a refrigerant pipe that connects the discharge side of the compressor 21 and the four-way switching valve 22 to each other.
  • An accumulator 29 is connected to the suction pipe 31.
  • the accumulator 29 separates a flowed-in refrigerant into a liquid refrigerant and a gas refrigerant and causes only the gas refrigerant to flow to the suction side of the compressor 21.
  • the four-way switching valve 22 switches the direction of the flow of the refrigerant in the refrigerant circuit 10. During cooling operation, the four-way switching valve 22 causes the outdoor heat exchanger 23 to function as a radiator for the refrigerant and causes the indoor heat exchanger 41 to function as an evaporator for the refrigerant.
  • the four-way switching valve 22 connects the discharge pipe 32 of the compressor 21 and a first gas refrigerant pipe 33 of the outdoor heat exchanger 23 to each other and connects the suction pipe 31 of the compressor 21 and a second gas refrigerant pipe 34 to each other (refer to the solid lines of the four-way switching valve 22 in Fig. 1 ).
  • the four-way switching valve 22 is switched to a heating cycle state in which the outdoor heat exchanger 23 functions as an evaporator for the refrigerant and in which the indoor heat exchanger 41 functions as a radiator for the refrigerant.
  • the four-way switching valve 22 connects the discharge pipe 32 of the compressor 21 and the second gas refrigerant pipe 34 to each other and connects the suction pipe 31 of the compressor 21 and the first gas refrigerant pipe 33 of the outdoor heat exchanger 23 to each other (refer to the broken lines of the four-way switching valve 22 in Fig. 1 ).
  • the first gas refrigerant pipe 33 is a refrigerant pipe that connects the four-way switching valve 22 and the refrigerant inlet of the outdoor heat exchanger 23 during cooling operation to each other.
  • the second gas refrigerant pipe 34 is a refrigerant pipe that connects the four-way switching valve 22 and the gas-side shutoff valve 28 to each other.
  • the outdoor heat exchanger 23 functions as a radiator for the refrigerant during cooling operation.
  • the outdoor heat exchanger 23 functions as an evaporator for the refrigerant during heating operation.
  • One end of a liquid refrigerant pipe 35 is connected to the refrigerant outlet of the outdoor heat exchanger 23 during cooling operation.
  • the other end of the liquid refrigerant pipe 35 is connected to the expansion valve 26.
  • the outdoor heat exchanger 23 will be described in detail in the section "(3) Detailed Structure of Outdoor Heat Exchanger 23".
  • the expansion valve 26 is an electric expansion valve. During cooling operation, the expansion valve 26 decompresses a high-pressure refrigerant that is sent from the outdoor heat exchanger 23 to a low pressure. During heating operation, the expansion valve 26 decompresses a high-pressure refrigerant that is sent from the indoor heat exchanger 41 to a low pressure.
  • the liquid-side shutoff valve 27 is connected to the liquid-refrigerant connection pipe 5.
  • the gas-side shutoff valve 28 is connected the gas-refrigerant connection pipe 6.
  • the liquid-side shutoff valve 27 is positioned downstream the expansion valve 26 in a refrigerant circulation direction during cooling operation.
  • the gas-side shutoff valve 28 is positioned upstream the four-way switching valve 22 in a refrigerant circulation direction during cooling operation.
  • the outdoor unit 2 includes an outdoor fan 36.
  • the outdoor fan 36 takes outdoor air into the outdoor unit 2, causes the outdoor air to exchange heat with the refrigerant in the outdoor heat exchanger 23, and then discharges the air to the outside.
  • a propeller fan or the like is employed as the outdoor fan 36.
  • the outdoor fan 36 is driven by an outdoor-fan motor 37.
  • the outdoor-side control unit 38 controls operation of each portion that constitutes the outdoor unit 2.
  • the outdoor-side control unit 38 has a microcomputer and a memory that are for controlling the outdoor unit 2.
  • the outdoor-side control unit 38 transmits and receives a control signal and the like to and from the indoor-side control unit 44 of the indoor unit 4 via the transmission line 8a.
  • connection pipes 5 and 6 are refrigerant pipes that are constructed at a local site during installation of the air conditioning apparatus 1 in an installation location at a building or the like.
  • a pipe having an appropriate length and an appropriate diameter is employed in accordance with installation conditions such as an installation location, a combination of the outdoor unit 2 and the indoor unit 4, and the like.
  • the air conditioning apparatus 1 is capable of performing cooling operation and heating operation as basic operation.
  • the four-way switching valve 22 is switched to a cooling cycle state (the state indicated by the solid lines in Fig. 1 ).
  • a cooling cycle state the state indicated by the solid lines in Fig. 1 .
  • a low-pressure gas refrigerant of the refrigeration cycle is sucked by the compressor 21 and discharged after compressed.
  • the high-pressure gas refrigerant discharged from the compressor 21 is sent to the outdoor heat exchanger 23 via the four-way switching valve 22.
  • the high-pressure gas refrigerant sent to the outdoor heat exchanger 23 radiates heat by exchanging heat with outdoor air supplied from the outdoor fan 36, and becomes a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is sent to the expansion valve 26.
  • the high-pressure liquid refrigerant sent to the expansion valve 26 is decompressed to a low pressure of the refrigeration cycle by the expansion valve 26 and becomes a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant decompressed in the expansion valve 26 is sent to the indoor heat exchanger 41 via the liquid-side shutoff valve 27 and the liquid-refrigerant connection pipe 5.
  • the low-pressure gas-liquid two-phase refrigerant sent to the indoor heat exchanger 41 evaporates in the indoor heat exchanger 41 by exchanging heat with indoor air supplied from the indoor fan 42. Consequently, the indoor air is cooled. Then, the cooled air is supplied to the inside of a room, thereby cooling the inside of the room.
  • the low-pressure gas refrigerant that has evaporated in the indoor heat exchanger 41 is sucked again by the compressor 21 via the gas-refrigerant connection pipe 6, the gas-side shutoff valve 28, and the four-way switching valve 22.
  • the four-way switching valve 22 is switched to the heating cycle state (the state indicated by the broken lines in Fig. 1 ).
  • the heating cycle state the state indicated by the broken lines in Fig. 1 .
  • a low-pressure gas refrigerant of the refrigeration cycle is sucked by the compressor 21 and discharged after compressed.
  • the high-pressure gas refrigerant discharged from the compressor 21 is sent to the indoor heat exchanger 41 via the four-way switching valve 22, the gas-side shutoff valve 28, and the gas-refrigerant connection pipe 6.
  • the high-pressure gas refrigerant sent to the indoor heat exchanger 41 radiates heat in the indoor heat exchanger 41 by exchanging heat with indoor air supplied from the indoor fan 42, and becomes a high-pressure liquid refrigerant. Consequently, the indoor air is heated. Then, the heated air is supplied to the inside of a room, thereby heating the inside of the room.
  • the high-pressure liquid refrigerant that has radiated heat in the indoor heat exchanger 41 is sent to the expansion valve 26 via the liquid-refrigerant connection pipe 5 and the liquid-side shutoff valve 27.
  • the high-pressure liquid refrigerant sent to the expansion valve 26 is decompressed to a low pressure of the refrigeration cycle by the expansion valve 26 and becomes a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant decompressed in the expansion valve 26 is sent to the outdoor heat exchanger 23.
  • the low-pressure gas-liquid two-phase refrigerant sent to the outdoor heat exchanger 23 evaporates in the outdoor heat exchanger 23 by exchanging heat with outdoor air supplied from the outdoor fan 36, and becomes a low-pressure gas refrigerant.
  • the low-pressure refrigerant that has evaporated in the outdoor heat exchanger 23 is sucked again by the compressor 21 through the four-way switching valve 22.
  • Fig. 3 is an external perspective view of the outdoor heat exchanger 23.
  • the outdoor heat exchanger 23 is a stack-type heat exchanger.
  • the outdoor heat exchanger 23 includes a plurality of flat pipes 231 and a plurality of heat transfer fins 232.
  • Each flat pipe 231 is a multi-hole pipe.
  • the flat pipe 231 is formed of aluminum or an aluminum alloy and has a flat portion 231a that serves as a heat transfer surface, and a plurality of internal flow paths 231b in which the refrigerant flows.
  • the flat pipes 231 are arrayed in a plurality of stages to be stacked with a gap (ventilation space) therebetween in a state in which respective flat portions 231a are directed upward/downward.
  • Each heat transfer fin 232 is a fin made of aluminum or an aluminum alloy.
  • the heat transfer fin 232 is disposed in a ventilation space between the flat pipes 231 that are vertically adjacent to each other and is in contact with the flat portions 231a of the flat pipes 231.
  • the heat transfer fin 232 has cutouts 232c (refer to Fig. 5A and Fig. 5B ) into which the flat pipes 231 are inserted. After the flat pipes 231 are inserted into the cutouts 232c of the heat transfer fins 232, the heat transfer fins 232 and the flat portions 231a of the flat pipes 231 are joined to each other by brazing or the like.
  • the headers 233a and 233b are coupled to both ends of the flat pipes 231 arrayed in the plurality of stages in the up-down direction.
  • the headers 233a and 233b have a function of supporting the flat pipes 231, a function of guiding the refrigerant to the internal flow paths of the flat pipes 231, and a function of gathering the refrigerant that has flowed out from the internal flow paths.
  • the refrigerant flows into the first header 233a.
  • the refrigerant that has flowed into the first header 233a is distributed to the internal flow paths of the flat pipes 231 of the stages substantially evenly and flows toward the second header 233b.
  • the refrigerant that flows in the internal flow paths of the flat pipes 231 of the stages absorbs heat via the heat transfer fins 232 from an air flow that flows in the ventilation spaces.
  • the refrigerant that has flowed in the internal flow paths of the flat pipes 231 of the stages gathers at the second header 233b and flows out from the second header 233b.
  • the refrigerant flows into the second header 233b.
  • the refrigerant that has flowed into the second header 233b is distributed to the internal flow paths of the flat pipes 231 of the stages substantially evenly and flows toward the first header 233a.
  • the refrigerant that flows in the internal flow paths of the flat pipes 231 of the stages radiates heat via the heat transfer fins 232 into an air flow that flows in the ventilation spaces.
  • the refrigerant that has flowed in the internal flow paths of the flat pipes 231 of the stages gathers at the first header 233a and flows out from the first header 233a.
  • Fig. 4 is a P-H diagram of a non-azeotropic refrigerant mixture.
  • the refrigerant temperature increases toward the evaporator outlet. Since the composition of the non-azeotropic refrigerant mixture is different between a liquid phase and a gas phase, a "temperature gradient" in which an evaporation start temperature and an evaporation end temperature in the evaporator are different is present. Due to the temperature gradient, the temperature at the inlet easily decreases in the evaporator, which easily causes frost during heating operation.
  • Fig. 5A is a perspective view of a first heat exchange section 23a of the outdoor heat exchanger 23 according to the first embodiment.
  • the opening side of the cutouts 232c is positioned on the leeward side in the airflow direction in the first heat exchange section 23a.
  • Fig. 5B is a perspective view of a second heat exchange section 23b of the outdoor heat exchanger 23 according to the first embodiment.
  • the opening side of the cutouts 232c is positioned on the windward side in the airflow direction.
  • the first heat exchange section 23a is formed on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator.
  • both the first heat exchange section 23a and the second heat exchange section 23b are used to improve heat exchange performance while suppressing frost.
  • Fig. 6A is a schematic perspective view of the outdoor heat exchanger 23 that uses both the first heat exchange section 23a and the second heat exchange section 23b.
  • Fig. 6B is a schematic perspective view of a different outdoor heat exchanger 23' that uses both a first heat exchange section 23a' and a second heat exchange section 23b'.
  • Fig. 6A when the outdoor heat exchanger 23 functions as an evaporator for the refrigerant, the refrigerant that has flowed into the first header 233a is distributed to the internal flow paths 231b of the flat pipes 231 of the stages substantially evenly and flows toward the second header 233b.
  • the temperature of the non-azeotropic refrigerant mixture at the evaporator inlet easily decreases, which easily causes frost. Therefore, a certain section from the first header 233a toward the second header 233b is constituted by the first heat exchange section 23a to suppress frost.
  • the temperature of the non-azeotropic refrigerant mixture increases toward the evaporator outlet.
  • a part between the first heat exchange section 23a and the second header 233b is constituted by the second heat exchange section 23b.
  • the first heat exchange section 23a is disposed on the evaporator inlet side and the second heat exchange section 23b is disposed on the evaporator outlet side to improve heat exchange performance while suppressing frost.
  • the refrigerant that has reached the lower stage of the second header 233b' gathers temporarily and flows into the upper stage of the second header 233b' via a curved pipe 234. Thereafter, the refrigerant is distributed to the internal flow paths 231b of the flat pipes 231 of the stages of the upper stage substantially evenly and flows toward the second header 233b'.
  • the temperature of the non-azeotropic refrigerant mixture at the evaporator inlet easily decreases, which easily causes frost. Therefore, a section from the lower stage of the first header 233a' toward the lower stage of the second header 233b' is constituted by the first heat exchange section 23a' to suppress frost.
  • a section from the upper stage of the first header 233b' toward the upper stage of the first header 233a' is constituted by the second heat exchange section 23b'.
  • the first heat exchange section 23a' is disposed on the evaporator inlet side and the second heat exchange section 23b' is disposed on the evaporator outlet side to improve heat exchange performance while suppressing frost.
  • a third heat exchange section 23c may be disposed between the first heat exchange section 23a and the second heat exchange section 23b.
  • the distribution center of the flat pipes 231 in the width direction coincides with the center of the heat transfer fins 232 in the airflow direction.
  • the first heat exchange section 23a may be integral with at least either one of the second heat exchange section 23b and the third heat exchange section 23c.
  • a stack-type heat exchanger in which the flat pipes 231 are inserted into the cutouts 232c provided in the heat transfer fins 232 is employed as the outdoor heat exchanger 23.
  • a stack-type heat exchanger in which flat pipes extend through elongated holes provided in heat transfer fins is employed as the outdoor heat exchanger 23.
  • Fig. 7A is a perspective view of a first heat exchange section 123a of the outdoor heat exchanger 23 according to the second embodiment.
  • a distance from the windward-side end of a flat pipe 231M positioned on the most windward side in the airflow direction to the windward-side end of a heat transfer fin 232M is a first dimension D1.
  • Fig. 7B is a perspective view of a second heat exchange section 123b of the outdoor heat exchanger 23 according to the second embodiment.
  • a distance from the windward-side end of the flat pipe 231M positioned on the most windward side in the airflow direction to the windward-side end of the heat transfer fin 232M is a second dimension D2 smaller than the first dimension D1.
  • the distance (second dimension D2) from the windward-side end of the flat pipe 231M positioned on the most windward side in the airflow direction to the windward-side end of the heat transfer fin 232M in the second heat exchange section 123b illustrated in Fig. 7B is smaller than the distance (first dimension D1) in the first heat exchange section 123a, a difference between an air temperature and a heat-exchanger surface temperature is large.
  • the second heat exchange section 123b thus has a feature of improving heat exchange performance but easily causing frost.
  • the first heat exchange section 123a is formed on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator.
  • both the first heat exchange section 123a and the second heat exchange section 123b are used, as in the first embodiment, to improve heat exchange performance while suppressing frost.
  • Fig. 6A and Fig. 6B are also applied to the second embodiment by replacing the first heat exchange section 23a of the first embodiment with the "first heat exchange section 123a" and replacing the second heat exchange section 23b of the first embodiment with the "second heat exchange section 123b".
  • Fig. 6A when the outdoor heat exchanger 23 functions as an evaporator for the refrigerant, the refrigerant that has flowed into the first header 233a is distributed to the internal flow paths of the flat pipes of the stages substantially evenly and flows toward the second header 233b.
  • the temperature of the non-azeotropic refrigerant mixture at the evaporator inlet easily decreases, which easily causes frost. Therefore, a certain section from the first header 233a toward the second header 233b is constituted by the first heat exchange section 123a to suppress frost.
  • the temperature of the non-azeotropic refrigerant mixture increases toward the evaporator outlet.
  • a part between the first heat exchange section 123a and the second header 233b is constituted by the second heat exchange section 123b.
  • first heat exchange section 123a on the evaporator inlet side and the second heat exchange section 123b on the evaporator outlet side to improve heat exchange performance while suppressing frost.
  • the first heat exchange section 123a is disposed on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator and the second heat exchange section 123b is disposed on the outlet side.
  • the first heat exchange section 123a and the second heat exchange section 123b are integral with each other.
  • a third heat exchange section may be disposed between the first heat exchange section 123a and the second heat exchange section 123b.
  • Fig. 7C is a perspective view of a third heat exchange section 123c of the outdoor heat exchanger 23 according to a modification of the second embodiment.
  • a distance D3 from the windward-side end of the flat pipe 231M positioned on the most windward side in the airflow direction to the windward-side end of the heat transfer fin 232M and a distance from the leeward-side end of the flat pipe 231M positioned on the most leeward side in the airflow direction to the leeward-side end of the heat transfer fin 232M are equal to each other.
  • the first heat exchange section 123a may be integral with at least either one of the second heat exchange section 123b and the third heat exchange section 123c.
  • a stack-type heat exchanger is employed as the outdoor heat exchanger 23.
  • a cross-fin-type heat exchanger is employed as the outdoor heat exchanger 23.
  • Fig. 8A is a perspective view of a first heat exchange section 223a of the outdoor heat exchanger 23 according to the third embodiment.
  • the distribution center of the heat-transfer-tube group in the airflow direction is positioned on the leeward side of the center of the heat transfer fin 232N in the airflow direction.
  • Fig. 8B is a perspective view of a second heat exchange section 223b of the outdoor heat exchanger 23 according to the third embodiment.
  • the distribution center of the heat-transfer-tube group in the airflow direction is positioned on the windward side of the center of the heat transfer fin 232N in the airflow direction.
  • the second heat exchange section 223b thus has a feature of improving heat exchange performance but easily causing frost.
  • a distance from the windward-side end of the heat transfer tube 231N positioned on the most windward side in the airflow direction to the windward-side end of the heat transfer fin 232N is larger in the first heat exchange section 223a illustrated in Fig. 8A than the distance in the second heat exchange section 223b.
  • a difference between an air temperature and a heat-exchanger surface temperature is small, which suppresses frost.
  • the first heat exchange section 223a is formed on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator.
  • both the first heat exchange section 223a and the second heat exchange section 223b are used, as in the first embodiment and the second embodiment, to improve heat exchange performance while suppressing frost.
  • Fig. 6A and Fig. 6B are also applied to the third embodiment by replacing the first heat exchange section 23a of the first embodiment with the "first heat exchange section 223a" and replacing the second heat exchange section 23b of the first embodiment with the "second heat exchange section 223b".
  • Fig. 6A when the outdoor heat exchanger 23 functions as an evaporator for the refrigerant, the refrigerant that has flowed into the first header 233a is distributed to the heat transfer tubes of the stages substantially evenly and flows toward the second header 233b.
  • the temperature of the non-azeotropic refrigerant mixture at the evaporator inlet easily decreases, which easily causes frost. Therefore, a certain section from the first header 233a toward the second header 233b is constituted by the first heat exchange section 223a to suppress frost.
  • the temperature of the non-azeotropic refrigerant mixture increases toward the evaporator outlet.
  • a part between the first heat exchange section 223a and the second header 233b is constituted by the second heat exchange section 223b.
  • the first heat exchange section 223a is disposed on the evaporator inlet side and the second heat exchange section 223b is disposed on the evaporator outlet side to improve heat exchange performance while suppressing frost.
  • the first heat exchange section 223a is disposed on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator and the second heat exchange section 223b is disposed on the outlet side.
  • the first heat exchange section 223a and the second heat exchange section 223b are integral with each other.
  • a third heat exchange section may be disposed between the first heat exchange section 223a and the second heat exchange section 223b.
  • Fig. 8C is a perspective view of a third heat exchange section 223c of the outdoor heat exchanger 23 according to a modification of the third embodiment.
  • the distribution center of the heat-transfer-tube group in the airflow direction coincides with the center of the fin in the airflow direction.
  • the first heat exchange section 223a may be integral with at least either one of the second heat exchange section 223b and the third heat exchange section 223c.
  • the non-azeotropic refrigerant mixture is described to include any of a HFC refrigerant, a HFO refrigerant, CF3I, and a natural refrigerant. More specifically, a non-azeotropic refrigerant mixture corresponding to any of (A) to (G) below is desirable.
  • the present invention is widely applicable to a refrigeration cycle apparatus capable of performing cooling operation and heating operation.

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Claims (18)

  1. Appareil à cycle frigorifique dans lequel un mélange de fluide frigorigène non azéotrope est enfermé, l'appareil à cycle frigorifique comprenant un évaporateur (23) et un ventilateur (36), le ventilateur (36) étant configuré pour prendre de l'air extérieur, amener l'air extérieur à échanger de la chaleur avec le fluide frigorigène dans l'évaporateur (23), puis à évacuer l'air vers l'extérieur, l'évaporateur comprenant :
    une pluralité d'ailettes (232) qui sont agencées à un intervalle prédéterminé dans une direction d'épaisseur de plaque ; et
    une pluralité de tubes (231) de transfert de chaleur qui s'étendent à travers la pluralité d'ailettes dans la direction d'épaisseur de plaque,
    un premier collecteur (233a, 233a') et un deuxième collecteur (233b, 233b'), dans lequel le premier collecteur (233a, 233a') et le deuxième collecteur (233b, 233b') sont reliés aux deux extrémités de la pluralité de tubes (231) de transfert de chaleur,
    dans lequel une première section (23a) d'échange de chaleur est formée, dans laquelle, lorsque les tubes de la pluralité de tubes de transfert de chaleur sont vus comme étant un groupe de tubes de transfert de chaleur dans la direction d'épaisseur de plaque des ailettes, un centre de distribution du groupe de tubes de transfert de chaleur dans une direction de flux d'air du ventilateur (36) est positionné sur un côté sous le vent d'un centre des ailettes dans la direction de flux d'air,
    dans lequel
    une deuxième section (23b) d'échange de chaleur dans laquelle le centre de distribution du groupe de tubes de transfert de chaleur est positionné sur un côté au vent du centre des ailettes dans la direction de flux d'air est en outre formée,
    dans lequel la première section (23a) d'échange de chaleur est prévue sur un côté d'entrée d'évaporateur et la deuxième section (23b) d'échange de chaleur est prévue sur un côté de sortie d'évaporateur.
  2. Appareil à cycle frigorifique selon la revendication 1,
    dans lequel une troisième section d'échange de chaleur dans laquelle le centre de distribution du groupe de tubes de transfert de chaleur coïncide avec le centre des ailettes dans la direction de flux d'air est formée.
  3. Appareil à cycle frigorifique selon la revendication 1,
    dans lequel la première section d'échange de chaleur et la deuxième section d'échange de chaleur font partie intégrante l'une de l'autre.
  4. Appareil à cycle frigorifique selon la revendication 2,
    dans lequel la première section d'échange de chaleur fait partie intégrante d'au moins l'une parmi la deuxième section d'échange de chaleur et la troisième section d'échange de chaleur.
  5. Appareil à cycle frigorifique dans lequel un mélange de fluide frigorigène non azéotrope est enfermé, l'appareil à cycle frigorifique comprenant un évaporateur (23) et un ventilateur (36), le ventilateur (36) étant configuré pour prendre de l'air extérieur, amener l'air extérieur à échanger de la chaleur avec le fluide frigorigène dans l'évaporateur (23), puis à évacuer l'air vers l'extérieur, l'évaporateur comprenant :
    une pluralité d'ailettes (232) qui sont agencées à un intervalle prédéterminé dans une direction d'épaisseur de plaque ; et
    une pluralité de tubes (231) de transfert de chaleur qui s'étendent à travers la pluralité d'ailettes dans la direction d'épaisseur de plaque,
    un premier collecteur (233a, 233a') et un deuxième collecteur (233b, 233b'), dans lequel le premier collecteur (233a, 233a') et le deuxième collecteur (233b, 233b') sont reliés aux deux extrémités de la pluralité de tubes (231) de transfert de chaleur,
    dans lequel une première section (23a) d'échange de chaleur est formée, dans laquelle une distance depuis une extrémité de côté au vent du tube de transfert de chaleur positionné sur un côté le plus au vent dans une direction de flux d'air du ventilateur (36) jusqu'à une extrémité de côté au vent des ailettes est une première dimension,
    dans lequel
    une deuxième section (23b) d'échange de chaleur étant formée, dans laquelle une distance depuis une extrémité de côté au vent du tube de transfert de chaleur positionné sur un côté le plus au vent dans une direction de flux d'air jusqu'à une extrémité de côté au vent des ailettes est une deuxième dimension plus petite que la première dimension,
    dans lequel la première section (23a) d'échange de chaleur est prévue sur un côté d'entrée d'évaporateur et la deuxième section (23b) d'échange de chaleur est prévue sur un côté de sortie d'évaporateur.
  6. Appareil à cycle frigorifique selon la revendication 5,
    dans lequel une troisième section d'échange de chaleur dans laquelle
    une distance depuis une extrémité de côté au vent du tube de transfert de chaleur positionné sur un côté le plus au vent dans une direction de flux d'air jusqu'à une extrémité de côté au vent des ailettes, et
    une distance depuis une extrémité de côté sous le vent du tube de transfert de chaleur positionné sur un côté le plus sous le vent dans une direction de flux d'air jusqu'à une extrémité de côté sous le vent des ailettes
    sont égales entre elles, est en outre formée.
  7. Appareil à cycle frigorifique selon la revendication 5,
    dans lequel la première section d'échange de chaleur et la deuxième section d'échange de chaleur font partie intégrante l'une de l'autre.
  8. Appareil à cycle frigorifique selon la revendication 6,
    dans lequel la première section d'échange de chaleur fait partie intégrante d'au moins l'une parmi la deuxième section d'échange de chaleur et la troisième section d'échange de chaleur.
  9. Appareil à cycle frigorifique dans lequel un mélange de fluide frigorigène non azéotrope est enfermé, l'appareil à cycle frigorifique comprenant un évaporateur (23) et un ventilateur (36), le ventilateur (36) étant configuré pour prendre de l'air extérieur, amener l'air extérieur à échanger de la chaleur avec le fluide frigorigène dans l'évaporateur (23), puis à évacuer l'air vers l'extérieur, l'évaporateur comprenant :
    une pluralité d'ailettes (232) qui sont agencées à un intervalle prédéterminé dans une direction d'épaisseur de plaque ; et
    une pluralité de tubes (231) de transfert de chaleur qui s'étendent à travers la pluralité d'ailettes dans la direction d'épaisseur de plaque,
    un premier collecteur (233a, 233a') et un deuxième collecteur (233b, 233b'), dans lequel le premier collecteur (233a, 233a') et le deuxième collecteur (233b, 233b') sont reliés aux deux extrémités de la pluralité de tubes (231) de transfert de chaleur,
    dans lequel les ailettes présentent une pluralité de découpes (232c) qui sont agencées dans une direction orthogonale à la fois à une direction de flux d'air du ventilateur (36) et à la direction d'épaisseur de plaque,
    les tubes de transfert de chaleur sont des tuyaux plats à trous multiples insérés dans les découpes, et
    une première section (23a) d'échange de chaleur est formée, dans laquelle un côté d'ouverture des découpes est positionné sur un côté sous le vent dans la direction de flux d'air,
    dans lequel
    une deuxième section (23b) d'échange de chaleur est en outre formée, dans laquelle le côté d'ouverture des découpes est positionné sur un côté au vent dans la direction de flux d'air,
    dans lequel la première section (23a) d'échange de chaleur est prévue sur un côté d'entrée d'évaporateur et la deuxième section (23b) d'échange de chaleur est prévue sur un côté de sortie d'évaporateur.
  10. Appareil à cycle frigorifique selon la revendication 9,
    dans lequel la première section d'échange de chaleur et la deuxième section d'échange de chaleur font partie intégrante l'une de l'autre.
  11. Appareil à cycle frigorifique selon l'une quelconque des revendications 1 à 10,
    dans lequel le mélange de fluide frigorigène non azéotrope inclut l'un quelconque parmi un fluide frigorigène HFC, un fluide frigorigène HFO, du CF3I, et un fluide frigorigène naturel.
  12. Appareil à cycle frigorifique selon l'une quelconque des revendications 1 à 10,
    dans lequel le mélange de fluide frigorigène non azéotrope inclut l'un quelconque parmi R32, R1132(E), R1234yf, R1234ze, CF3I et CO2.
  13. Appareil à cycle frigorifique selon l'une quelconque des revendications 1 à 10,
    dans lequel le mélange de fluide frigorigène non azéotrope inclut au moins l'un parmi R1132(E), R32 et R1234yf.
  14. Appareil à cycle frigorifique selon l'une quelconque des revendications 1 à 10,
    dans lequel le mélange de fluide frigorigène non azéotrope inclut au moins l'un parmi R1132(E), R1123 et R1234yf.
  15. Appareil à cycle frigorifique selon l'une quelconque des revendications 1 à 10,
    dans lequel le mélange de fluide frigorigène non azéotrope inclut au moins l'un parmi R1132(E) et R1234yf.
  16. Appareil à cycle frigorifique selon l'une quelconque des revendications 1 à 10,
    dans lequel le mélange de fluide frigorigène non azéotrope inclut au moins l'un parmi R32, R1234yf et au moins l'un parmi R1132a et R1114.
  17. Appareil à cycle frigorifique selon l'une quelconque des revendications 1 à 10,
    dans lequel le mélange de fluide frigorigène non azéotrope inclut au moins l'un parmi R32, CO2, R125, R134a, et R1234yf.
  18. Appareil à cycle frigorifique selon l'une quelconque des revendications 1 à 10,
    dans lequel le mélange de fluide frigorigène non azéotrope inclut au moins l'un parmi R1132(Z) et R1234yf.
EP20871516.9A 2019-09-30 2020-09-29 Dispositif à cycle frigorifique Active EP4040084B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019180813A JP7425282B2 (ja) 2019-09-30 2019-09-30 蒸発器、およびそれを備えた冷凍サイクル装置
PCT/JP2020/036920 WO2021065913A1 (fr) 2019-09-30 2020-09-29 Évaporateur et dispositif à cycle frigorifique doté dudit évaporateur

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EP4040084A1 EP4040084A1 (fr) 2022-08-10
EP4040084A4 EP4040084A4 (fr) 2022-11-16
EP4040084B1 true EP4040084B1 (fr) 2024-07-24

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US (1) US20220214085A1 (fr)
EP (1) EP4040084B1 (fr)
JP (1) JP7425282B2 (fr)
CN (1) CN114450546B (fr)
WO (1) WO2021065913A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11906207B2 (en) * 2017-12-18 2024-02-20 Daikin Industries, Ltd. Refrigeration apparatus
US11820933B2 (en) 2017-12-18 2023-11-21 Daikin Industries, Ltd. Refrigeration cycle apparatus
KR102678458B1 (ko) * 2021-12-07 2024-06-27 와이엠레미 주식회사 공조 장치용 냉매 조성물

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0854149A (ja) * 1994-08-11 1996-02-27 Matsushita Electric Ind Co Ltd 冷凍装置
JP4186359B2 (ja) 1999-12-07 2008-11-26 三菱電機株式会社 熱交換器および該熱交換器を備えた空調冷凍装置
JP3938053B2 (ja) 2003-01-15 2007-06-27 松下電器産業株式会社 熱交換器
JP2012154500A (ja) * 2011-01-21 2012-08-16 Daikin Industries Ltd 熱交換器および空気調和機
WO2013160950A1 (fr) * 2012-04-26 2013-10-31 三菱電機株式会社 Echangeur de chaleur et climatiseur
US20160097569A1 (en) * 2013-07-29 2016-04-07 Mitsubishi Electric Corporporation Heat pump apparatus
JP6657957B2 (ja) * 2014-01-31 2020-03-04 Ａｇｃ株式会社 熱サイクル用作動媒体、熱サイクルシステム用組成物および熱サイクルシステム
WO2015136981A1 (fr) 2014-03-14 2015-09-17 三菱電機株式会社 Compresseur et système à cycle de réfrigération
JP5897062B2 (ja) 2014-05-08 2016-03-30 三菱電機株式会社 圧縮機用電動機及び圧縮機及び冷凍サイクル装置及び圧縮機用電動機の製造方法
US10941985B2 (en) * 2016-04-22 2021-03-09 Mitsubishi Electric Corporation Heat exchanger
EP3477227B1 (fr) * 2016-06-24 2020-12-23 Mitsubishi Electric Corporation Dispositif à cycle de réfrigération et échangeur de chaleur extérieur utilisé dans celui-ci
EP3534103B1 (fr) * 2016-10-28 2020-12-23 Mitsubishi Electric Corporation Échangeur thermique et dispositif à cycle de réfrigération
JP2019011923A (ja) * 2017-06-30 2019-01-24 ダイキン工業株式会社 熱交換器
JP6925242B2 (ja) 2017-11-13 2021-08-25 三菱電機株式会社 管挿入装置及び管挿入方法
JP6586984B2 (ja) 2017-12-12 2019-10-09 ダイキン工業株式会社 フッ素化炭化水素及び二酸化炭素を含む冷媒、その使用、並びにそれを有する冷凍機及びその冷凍機の運転方法

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Publication number Publication date
US20220214085A1 (en) 2022-07-07
CN114450546B (zh) 2024-01-16
WO2021065913A1 (fr) 2021-04-08
JP7425282B2 (ja) 2024-01-31
JP2021055957A (ja) 2021-04-08
EP4040084A4 (fr) 2022-11-16
CN114450546A (zh) 2022-05-06
EP4040084A1 (fr) 2022-08-10

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