WO2022195659A1 - Échangeur de chaleur et dispositif de climatisation - Google Patents

Échangeur de chaleur et dispositif de climatisation Download PDF

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Publication number
WO2022195659A1
WO2022195659A1 PCT/JP2021/010336 JP2021010336W WO2022195659A1 WO 2022195659 A1 WO2022195659 A1 WO 2022195659A1 JP 2021010336 W JP2021010336 W JP 2021010336W WO 2022195659 A1 WO2022195659 A1 WO 2022195659A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
flat tubes
flat
refrigerant
distributor
Prior art date
Application number
PCT/JP2021/010336
Other languages
English (en)
Japanese (ja)
Inventor
篤史 ▲高▼橋
剛志 前田
悟 梁池
伸 中村
敦 森田
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2021/010336 priority Critical patent/WO2022195659A1/fr
Priority to JP2023506386A priority patent/JPWO2022195659A1/ja
Priority to US18/262,940 priority patent/US20240093945A1/en
Priority to CN202180095313.8A priority patent/CN116997759A/zh
Priority to EP21931415.0A priority patent/EP4310427A4/fr
Publication of WO2022195659A1 publication Critical patent/WO2022195659A1/fr

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    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • 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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/08—Assemblies of conduits having different features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/10—Particular layout, e.g. for uniform temperature distribution

Definitions

  • the present disclosure relates to heat exchangers and air conditioners.
  • Patent Document 1 discloses a heat exchanger having a two-row structure composed of a flat tube group on the windward side and a flat tube group on the leeward side, in which each flat tube group has a two-tier configuration. ing.
  • An object of the present disclosure is to provide a heat exchanger with a two-row structure that achieves both performance as an evaporator and performance as a condenser and is capable of suitably flowing a refrigerant.
  • the heat exchanger of the present disclosure is a heat exchanger that exchanges heat between refrigerant and air.
  • the heat exchanger includes a windward flat tube group composed of a plurality of spaced first flat tubes and a plurality of second flat tubes, a plurality of spaced third flat tubes and
  • the leeward flat tube group composed of a plurality of fourth flat tubes and positioned on the leeward side of the windward flat tube group with respect to the air flow direction, and connected to the ends of the plurality of third flat tubes, the evaporator and a distributor that distributes the refrigerant flowing in from the center to the plurality of third flat tubes by branching a plurality of times.
  • the refrigerant flows through the plurality of second flat tubes, the plurality of fourth flat tubes, the plurality of third flat tubes, and the plurality of first flat tubes in this order, and acts as a condenser.
  • the refrigerant flows through the plurality of first flat tubes, the plurality of third flat tubes, the plurality of fourth flat tubes, and the plurality of second flat tubes in this order.
  • a heat exchanger with a two-row structure that achieves both performance as an evaporator and performance as a condenser, and that can suitably flow a refrigerant.
  • FIG. 1 is a diagram showing an air conditioner according to Embodiment 1.
  • FIG. FIG. 2 is a diagram showing an outdoor heat exchanger for an evaporator flow according to Embodiment 1; It is an enlarged view of a vertical connection pipe. It is an enlarged view of a U-bend pipe.
  • FIG. 2 is an exploded perspective view of the distributor according to Embodiment 1;
  • FIG. 4 is a diagram for explaining a condenser flow distributor according to the first embodiment;
  • FIG. 2 is an explanatory view of the outdoor heat exchanger for the evaporator flow according to Embodiment 1 as viewed from the side;
  • FIG. 2 is a diagram showing an outdoor heat exchanger for a condenser flow according to Embodiment 1;
  • FIG. 2 is an explanatory view of the outdoor heat exchanger for condenser flow according to Embodiment 1 as viewed from the side;
  • FIG. 10 is a diagram showing an outdoor heat exchanger for an evaporator flow according to Embodiment 2;
  • FIG. 11 is a perspective view of a disassembled distributor according to Embodiment 2;
  • FIG. 8 is a diagram for explaining a condenser flow distributor according to Embodiment 2;
  • FIG. 10 is an explanatory diagram of a side view of an outdoor heat exchanger for an evaporator flow according to Embodiment 2;
  • FIG. 10 is a diagram showing an outdoor heat exchanger for a condenser flow according to Embodiment 2;
  • FIG. 10 is an explanatory view of the outdoor heat exchanger for condenser flow according to Embodiment 2 as viewed from the side;
  • FIG. 11 is a perspective view of a state in which a row connecting portion according to Embodiment 2 is disassembled;
  • FIG. 11 is a side view of a row bridging portion according to Embodiment 2;
  • FIG. 11 is a perspective view of a disassembled row bridging portion according to a modification;
  • FIG. 11 is a side view of a row transfer section according to a modification;
  • FIG. 11 is a diagram for explaining the shape of a fin according to Embodiment 3;
  • FIG. 1 is a diagram showing an air conditioner 100 according to Embodiment 1.
  • FIG. FIG. 1 functionally shows the connection relationship and arrangement configuration of each device in the air conditioner 100, and does not necessarily show the arrangement in a physical space.
  • the heat exchanger according to Embodiment 1 is used in the air conditioner 100 will be described, but it is not limited to such a case, and for example, it can be used in other refrigeration cycle devices having a refrigerant circulation circuit. may be used.
  • the air conditioner 100 switches between cooling operation and heating operation, it is not limited to such a case, and may perform only cooling operation or heating operation.
  • the air conditioner 100 includes a compressor 41, a four-way valve 42, an outdoor heat exchanger (heat source side heat exchanger) 1, an expansion device 44, an indoor heat exchanger (load side heat exchanger) 45 , an outdoor fan (heat source side fan) 46 , an indoor fan (load side fan) 47 , and a controller 48 .
  • an indoor unit 100A including the indoor heat exchanger 45 and an outdoor unit 100B including the outdoor heat exchanger 1 are connected by an extension pipe 49.
  • the compressor 41, the four-way valve 42, the outdoor heat exchanger 1, the expansion device 44, and the indoor heat exchanger 45 are connected by refrigerant piping to form a refrigerant circulation circuit.
  • the flow of refrigerant during cooling operation is indicated by dotted arrows, and the flow of refrigerant during heating operation is indicated by solid arrows.
  • a compressor 41, a four-way valve 42, an expansion device 44, an outdoor fan 46, an indoor fan 47, various sensors, and the like are connected to the control device 48.
  • the controller 48 switches between the cooling operation and the heating operation by switching the flow path of the four-way valve 42 .
  • the high-pressure, high-temperature gaseous refrigerant discharged from the compressor 41 flows through the four-way valve 42 into the outdoor heat exchanger 1, exchanges heat with the air supplied by the outdoor fan 46, and condenses.
  • the condensed refrigerant becomes a high-pressure liquid state, flows out from the outdoor heat exchanger 1, and becomes a low-pressure gas-liquid two-phase state by the expansion device 44.
  • the low-pressure gas-liquid two-phase refrigerant flows into the indoor heat exchanger 45 and evaporates through heat exchange with the air supplied by the indoor fan 47, thereby cooling the room.
  • the evaporated refrigerant becomes a low-pressure gas state, flows out from the indoor heat exchanger 45 , and is sucked into the compressor 41 via the four-way valve 42 .
  • the high-pressure, high-temperature gaseous refrigerant discharged from the compressor 41 flows into the indoor heat exchanger 45 via the four-way valve 42, and is condensed by heat exchange with the air supplied by the indoor fan 47. to heat the
  • the condensed refrigerant becomes a high-pressure liquid state, flows out from the indoor heat exchanger 45 , and becomes a low-pressure gas-liquid two-phase refrigerant by the expansion device 44 .
  • the low-pressure gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 1, exchanges heat with the air supplied by the outdoor fan 46, and evaporates.
  • the evaporated refrigerant becomes a low-pressure gas state, flows out from the outdoor heat exchanger 1 , and is sucked into the compressor 41 via the four-way valve 42 .
  • FIG. 2 is a diagram showing the evaporator-flow outdoor heat exchanger 1 according to Embodiment 1
  • FIG. 3 is an enlarged view of the vertical connection pipe 18, and
  • FIG. 4 is an enlarged view of the U-bend pipe 19.
  • 5 is an exploded perspective view of the distributor 10 according to the first embodiment
  • FIG. 6 is a diagram for explaining the condenser flow distributor 10 according to the first embodiment.
  • FIG. 7 is an explanatory diagram of the evaporator-flow outdoor heat exchanger 1 according to Embodiment 1 as viewed from the side.
  • the outdoor heat exchanger 1 is a two-row air heat exchanger.
  • the outdoor heat exchanger 1 is arranged on the windward side with respect to the flow direction of the wind W, and includes an upwind heat exchanger 1A as a windward flat tube group including a plurality of flat tubes 20 arranged at intervals, and a leeward heat exchanger 1B as a leeward flat tube group that is arranged on the leeward side with respect to the flow direction of the wind W and includes a plurality of flat tubes 30 that are arranged at intervals.
  • the upwind heat exchanger 1A and the downwind heat exchanger 1B are arranged close to each other in the flow direction of the wind W, which is air, but are shown with an interval therebetween in the drawing.
  • the number of flat tubes 20 and flat tubes 30 shown in the following description is an example, and the number of flat tubes can be changed as appropriate.
  • a plurality of fins arranged at regular intervals are arranged on the flat tube for heat exchange, but the description is omitted in the subsequent drawings.
  • the windward heat exchanger 1A as a windward flat tube group is divided into two areas, upper and lower.
  • the upwind heat exchanger 1A includes an upwind main heat exchanger 11 configured in an upper region and an upwind sub heat exchanger 12 configured in a lower region.
  • the upwind main heat exchanger 11 includes a plurality of spaced apart first flattened tubes 201 .
  • the upwind secondary heat exchanger 12 includes a plurality of spaced apart second flattened tubes 202 .
  • the number of first flat tubes 201 is greater than the number of second flat tubes 202 .
  • the multiple first flat tubes 201 are arranged above the multiple second flat tubes 202 .
  • the upwind heat exchanger 1A includes a first header pipe 15 and a second header pipe 16. Above the first header pipe 15, there is provided a first connection pipe 15a through which the refrigerant flows in and out. Below the second header pipe 16, a second connection pipe 16a is provided through which the refrigerant flows in and out.
  • the first header pipes 15 and the upwind main heat exchanger 11 are connected to the first connecting portions 20 a of the plurality of first flat pipes 201 .
  • the second header pipes 16 and the upwind secondary heat exchanger 12 are connected to the first connecting portions 20 a of the plurality of second flat pipes 202 .
  • the upwind heat exchanger 1A and the leeward heat exchanger 1B are connected at the second connecting portions 20b of the plurality of flat tubes 20 via the U-bend tube 19 shown in FIG.
  • the plurality of first flat tubes 201 and the plurality of second flat tubes 202 are arranged in upper and lower pairs by a third connecting portion 20c in which the end opposite to the side where the refrigerant flows in and out is bent in a U shape. It is connected.
  • the leeward heat exchanger 1B as a leeward flat tube group is divided into two areas, upper and lower.
  • the leeward heat exchanger 1B includes a leeward main heat exchanger 13 configured in an upper region and a leeward secondary heat exchanger 14 configured in a lower region.
  • the downwind main heat exchanger 13 includes a plurality of spaced apart third flattened tubes 301 .
  • the secondary leeward heat exchanger 14 includes a plurality of spaced apart fourth flattened tubes 302 .
  • the number of the multiple third flat tubes 301 is greater than the number of the multiple fourth flat tubes 302 .
  • the multiple third flat tubes 301 are arranged above the multiple fourth flat tubes 302 .
  • the downwind heat exchanger 1B includes a distributor 10, third header pipes 17, and vertical connection pipes 18 shown in FIG.
  • the distributor 10 includes an upper first distributor 10a, a central second distributor 10b, and a lower third distributor 10c.
  • the inside of the third header pipe 17 is partitioned into a lower first space 17a, a central second space 17b, and an upper third space 17c.
  • the vertical connection pipes 18 include a first vertical connection pipe 18a connecting the first distributor 10a and the first space 17a, a second vertical connection pipe 18b connecting the second distributor 10b and the second space 17b, and a third It includes a third vertical connecting pipe 18c connecting the distributor 10c and the third space 17c.
  • the first distributor 10a and the leeward main heat exchanger 13 are connected to the fourth connecting portions 30a of the plurality of third flat tubes 301.
  • the second distributor 10 b and the leeward main heat exchanger 13 are connected to the fourth connecting portions 30 a of the plurality of third flat tubes 301 .
  • the third distributor 10 c and the leeward main heat exchanger 13 are connected to the fourth connecting portions 30 a of the plurality of third flat tubes 301 .
  • the first space 17a and the sub-leeward heat exchanger 14 are connected to the fourth connecting portions 30a of the plurality of fourth flat tubes 302.
  • the second space 17 b and the leeward secondary heat exchanger 14 are connected to the fourth connecting portions 30 a of the plurality of fourth flat tubes 302 .
  • the third space 17 c and the leeward secondary heat exchanger 14 are connected to the fifth connecting portion 30 b of the multiple fourth flat tubes 302 .
  • the upwind heat exchanger 1A and the downwind heat exchanger 1B are connected via the U-bend pipe 19 shown in FIG.
  • the plurality of third flat tubes 301 and the plurality of fourth flat tubes 302 are arranged in upper and lower pairs by a sixth connecting portion 30c in which the end portion opposite to the side where the refrigerant flows in and out is bent in a U shape. It is connected.
  • the end opposite to the third connection part 20c connected for each set of upper and lower sides, and the leeward heat exchanger 1B as the leeward flat tube group A plurality of first flat tubes 201 and a plurality of third flat tubes 301 are connected to the end on the opposite side of the sixth connecting portion 30c connected for each set, skipping one.
  • the end opposite to the third connection part 20c connected for each set of upper and lower sides, and the leeward heat exchanger 1B as the leeward flat tube group A plurality of second flat tubes 202 and a plurality of fourth flat tubes 302 are connected to the end on the opposite side of the sixth connecting portion 30c connected for each set, skipping one.
  • the refrigerant After passing through the flow path F1, the refrigerant passes through three first connection portions 20a extending from the second header pipe 16, passes through the flow path F2 formed by the flat tubes 20, and is turned back at the third connection portion 20c. Each refrigerant folded back at the third connecting portion 20c passes through the flow path F3 formed by the flat tube 20, and passes through the flow path F4 formed by the U-bend pipe 19 from the second connecting portion 20b.
  • the refrigerant passes through the three fifth connection portions 30b of the leeward heat exchanger 1B, passes through the flow path F5 formed by the flat tubes 30, and is turned back at the sixth connection portion 30c.
  • the refrigerant passes through the flow path F6 formed by the flat tubes 30 and flows into the first space 17a, the second space 17b, and the third space 17c of the third header pipe 17.
  • the refrigerant that has flowed into the first space 17a passes through the flow path F7 formed by the first vertical connection pipe 18a and flows into the first distributor 10a.
  • the refrigerant that has flowed into the second space 17b passes through the flow path F7 formed by the second vertical connection pipe 18b and flows into the second distributor 10b.
  • the refrigerant that has flowed into the third space 17c passes through the flow path F7 formed by the third vertical connection pipe 18c and flows into the third distributor 10c.
  • Each refrigerant folded back at the sixth connection portion 30c passes through the flow path F9 formed by the flat tube 30, and passes through the flow path F10 formed by the U-bend pipe 19 from the fifth connection portion 30b. After that, the refrigerant passes through the twelve second connection portions 20b of the upwind heat exchanger 1A, passes through the flow path F11 formed by the flat tubes 20, and is turned back at the third connection portion 20c. Each refrigerant folded back at the third connection portion 20 c passes through the flow path F ⁇ b>12 formed by the flat tubes 20 and flows into the first header tube 15 . The refrigerant that has flowed into the first header pipe 15 is in a gaseous state due to heat exchange with outdoor air when passing through the flow path F1 to the flow path F12.
  • the gaseous refrigerant flows out of the outdoor heat exchanger 1 through the flow path F13 formed by the first connecting pipe 15a of the upwind heat exchanger 1A.
  • Frost FR adheres to the surface of the windward main heat exchanger 11 due to the relationship with the outside air temperature during heat exchange between the wind W, which is air, and the refrigerant.
  • the vertical connection pipe 18 is composed of three thin circular pipes.
  • the first space 17a of the third header pipe 17 and the first distributor 10a of the distributor 10 are connected by a first vertical connecting pipe 18a.
  • the second space 17b of the third header pipe 17 and the second distributor 10b of the distributor 10 are connected by a second vertical connecting pipe 18b.
  • the third space 17c of the third header pipe 17 and the third distributor 10c of the distributor 10 are connected by a third vertical connecting pipe 18c.
  • the U-bend pipe 19 at the uppermost position among the plurality of U-bend pipes 19 will be described.
  • the second connection portion 20 b of the upwind main heat exchanger 11 and the fifth connection portion 30 b of the leeward main heat exchanger 13 are connected via a circular U-bend pipe 19 .
  • the U-bend pipe 19 and the second connection portion 20b are joined at the first end portion 19a by brazing.
  • the U-bend pipe 19 and the fifth connection portion 30b are joined at the second end portion 19b by brazing.
  • the distributor 10 has the same configuration as the first distributor 10a, the second distributor 10b, and the third distributor 10c.
  • the refrigerant flowing through the refrigerant piping flows into the distributor 10 via the refrigerant inflow portion 160A and is distributed, and is distributed to four refrigerant pipes via the plurality of refrigerant outflow portions 160B. It flows out to the fourth connecting portion 30a composed of the flat tube 30.
  • the outdoor heat exchanger 1 functions as a condenser
  • the refrigerant flows in the opposite direction of this flow.
  • the distributor 10 includes a first plate member 110, a second plate member 120, a third plate member 130, a fourth plate member 140, and a fifth plate member 150. and have The first plate-like member 110, the second plate-like member 120, the third plate-like member 130, the fourth plate-like member 140, and the fifth plate-like member 150 are laminated and integrally joined by brazing.
  • the first plate-shaped member 110, the second plate-shaped member 120, the third plate-shaped member 130, the fourth plate-shaped member 140, and the fifth plate-shaped member 150 have a thickness of, for example, about 1 to 10 mm, and are made of aluminum. is.
  • the first plate-shaped member 110 includes a plurality of convex portions 110A and 110B projecting forward from the body portion 111 .
  • the first plate member 110 includes an inflow pipe 160C projecting forward and a coolant inflow portion 160A connected from the inflow pipe 160C.
  • the second plate member 120 is provided with a plurality of circular holes 120A, 120B, and 120C.
  • the third plate-shaped member 130 is provided with a hole portion 130A that spreads in the left-right direction and an S-shaped hole portion 130B.
  • the fourth plate member 140 is provided with holes 140A and 140B that widen in the left-right direction.
  • the fifth plate member 150 is provided with a plurality of coolant outflow portions 160B extending in the left-right direction as through holes.
  • Each plate member is processed by pressing or cutting.
  • the first plate member 110 is processed, for example, by pressing.
  • the second plate member 120, the third plate member 130, the fourth plate member 140, and the fifth plate member 150 are processed by cutting, for example.
  • the distributor 10 is installed so that the refrigerant flow direction of each of the plurality of flat tubes 30 connected to the outdoor heat exchanger 1 is horizontal.
  • the distributor 10 may be installed such that the refrigerant flow direction of each of the plurality of flat tubes 30 connected to the outdoor heat exchanger 1 is the vertical direction.
  • the distributor 10 may be installed such that the refrigerant flow direction of each of the plurality of flat tubes 30 connected to the outdoor heat exchanger 1 is oblique.
  • arrows indicate part of the refrigerant flow.
  • the direction of the arrow indicates the direction in which the coolant flows.
  • a part of the refrigerant flow will be described below.
  • the coolant that has passed through the inflow pipe 160C advances from the coolant inflow portion 160A through the hole 120A of the second plate-shaped member 120, collides with the surface of the fourth plate-shaped member 140, and enters the hole 130A of the third plate-shaped member 130. branch left and right along the The branched coolant passes through the hole 120B of the second plate-shaped member 120 from the rear to the front and collides with the projections 110A and 110B of the first plate-shaped member 110 .
  • the coolant that has collided with the convex portion 110B of the first plate member 110 flows obliquely downward along the convex portion 110B.
  • the coolant that has flowed obliquely downward advances through the hole portion 120C of the second plate-like member 120, collides with the surface of the fourth plate-like member 140, and flows along the hole portion 130B of the third plate-like member 130 to the S-shaped upward direction. branch laterally and downwardly.
  • the refrigerant on the upper side of the S shape passes through the hole portion 140A of the fourth plate member 140 and flows from the refrigerant outflow portion 160B of the fifth plate member 150 into the fourth connection portion 30a.
  • the refrigerant on the lower side of the S shape passes through the hole portion 140B of the fourth plate member 140 and flows from the refrigerant outflow portion 160B of the fifth plate member 150 into the fourth connection portion 30a.
  • the distributor 10 repeats branching when the refrigerant moves forward and backward, thereby making it possible to equalize the flow rate of the refrigerant without lowering the flow rate.
  • arrows indicate part of the refrigerant flow.
  • the distributor 10 functions as a condenser
  • the refrigerant that has flowed in from the fourth connection portion 30a merges in the two upper and lower second communication spaces 170B.
  • the merged refrigerant further merges in the first communication space 170A and flows out from the inflow pipe 160C.
  • FIG. 7 A case where the outdoor heat exchanger 1 for the evaporator flow according to Embodiment 1 is viewed from the side in FIG. 7 will be described.
  • the pipes on the near side are indicated by solid lines, and the pipes on the far side are indicated by dashed lines.
  • the refrigerant distributed by the distributor 10 passes through the fourth connection portion 30 a of the leeward main heat exchanger 13 .
  • the coolant that has passed through the fourth connection portion 30a flows from the front side to the back side and moves upward by the sixth connection portion 30c.
  • the coolant flows from the back side to the front side and passes through the fifth connection portion 30b.
  • the refrigerant passes through the U-bend pipe 19 and then through the second connection portion 20 b of the upwind main heat exchanger 11 .
  • the coolant flows from the front side to the back side and moves downward through the third connecting portion 20c.
  • the coolant flows from the back side to the front side, passes through the first connection portion 20 a, and flows into the first header pipe 15 .
  • Frost FR adheres to the surface of the windward main heat exchanger 11 due to the relationship with the outside air temperature during heat exchange between the wind W, which is air, and the refrigerant.
  • the refrigerant After passing through the flow path G1, the refrigerant passes through 12 first connection portions 20a extending from the first header pipe 15, passes through the flow path G2 formed by the flat tubes 20, and is turned back at the third connection portion 20c.
  • Each refrigerant folded back at the third connecting portion 20c passes through a flow path G3 formed by the flat tube 20, and passes through a flow path G4 formed by the U-bend pipe 19 from the second connecting portion 20b.
  • the refrigerant passes through the twelve fifth connection portions 30b of the leeward heat exchanger 1B, passes through the flow path G5 formed by the flat tubes 30, and is turned back at the sixth connection portion 30c.
  • the refrigerant passes through the flow path G6 configured by the flat tubes 30 and flows into the first distributor 10a, the second distributor 10b, and the third distributor 10c.
  • the refrigerant that has flowed into the first distributor 10a flows into the first space 17a through the flow path G7 formed by the first vertical connecting pipe 18a after being aggregated.
  • the refrigerant that has flowed into the second distributor 10b flows into the second space 17b through the channel G7 formed by the second vertical connection pipe 18b after being aggregated.
  • the refrigerant that has flowed into the third distributor 10c flows through the flow path G7 formed by the third vertical connecting pipe 18c after being aggregated, and flows into the third space 17c.
  • the refrigerant that has flowed into the first space 17a passes through the fourth connection portion 30a of the leeward heat exchanger 1B, passes through the flow path G8 formed by the flat tubes 30, and is turned back at the sixth connection portion 30c.
  • the refrigerant that has flowed into the second space 17b passes through the fourth connection portion 30a of the leeward heat exchanger 1B, passes through the flow path G8 formed by the flat tubes 30, and is turned back at the sixth connection portion 30c.
  • the refrigerant that has flowed into the third space 17c passes through the fourth connection portion 30a of the leeward heat exchanger 1B, passes through the flow path G8 formed by the flat tubes 30, and is turned back at the sixth connection portion 30c.
  • Each refrigerant folded back at the sixth connection portion 30c passes through the flow path G9 formed by the flat tube 30, and passes through the flow path G10 formed by the U-bend pipe 19 from the fifth connection portion 30b. After that, the refrigerant passes through the three second connection portions 20b of the upwind heat exchanger 1A, passes through the flow path G11 formed by the flat tubes 20, and is turned back at the third connection portion 20c. Each refrigerant folded back at the third connecting portion 20 c flows through the flow path G ⁇ b>12 formed by the flat tubes 20 and into the second header tube 16 .
  • the refrigerant that has flowed into the second header pipe 16 is in a liquid state due to heat exchange with outdoor air when passing through the flow path G1 to the flow path G12.
  • the liquid refrigerant flows out of the outdoor heat exchanger 1 through a flow path G13 formed by the second connecting pipe 16a of the upwind heat exchanger 1A.
  • the outdoor heat exchanger 1 acts as a condenser
  • the high-temperature, high-pressure gaseous refrigerant first flows through the upwind main heat exchanger 11 .
  • the frost FR adhering to the surface of the upwind main heat exchanger 11 can be efficiently defrosted.
  • FIG. 9 A case where the outdoor heat exchanger 1 for condenser flow according to Embodiment 1 is viewed from the side in FIG. 9 will be described.
  • the pipes on the front side are indicated by solid lines, and the pipes on the back side are indicated by dashed lines.
  • the refrigerant that has flowed in from the first header pipe 15 passes through the first connection portion 20 a of the upwind main heat exchanger 11 .
  • the refrigerant that has passed through the first connection portion 20a flows from the front side to the back side and moves upward by the third connection portion 20c.
  • the coolant flows from the back side to the front side and passes through the second connection portion 20b.
  • the refrigerant passes through the U-bend pipe 19 and then through the fifth connection portion 30 b of the leeward main heat exchanger 13 .
  • the coolant flows from the front side to the back side and moves downward through the sixth connection portion 30c.
  • the refrigerant flows from the back side to the front side, passes through the fourth connection portion 30 a, and flows into the distributor 10 .
  • Frost FR on the surface of the windward main heat exchanger 11 is effectively defrosted by the flow of high-temperature, high-pressure gaseous refrigerant.
  • FIG. 10 is a diagram showing an evaporator-flow outdoor heat exchanger 2 according to Embodiment 2
  • FIG. 11 is an exploded perspective view of a distributor 50 according to Embodiment 2
  • FIG. 13 is a diagram for explaining a distributor 50 for condenser flow according to Embodiment 2
  • FIG. 13 is a view of outdoor heat exchanger 1 for evaporator flow according to Embodiment 2 when viewed from the side. It is an explanatory diagram.
  • the outdoor heat exchanger 2 of Embodiment 2 differs from the outdoor heat exchanger 1 of Embodiment 1 in the shape of the connecting portion between the first header pipe 15 and the upwind heat exchanger 1A and the shape of the distributor 50.
  • the shape, the shape of the connecting portion between the distributor 50 and the leeward heat exchanger 1B, and the shape of the connecting portion between the upwind heat exchanger 1A and the leeward heat exchanger 1B are different.
  • differences from the outdoor heat exchanger 1 will be mainly described.
  • the outdoor heat exchanger 2 is a two-row air heat exchanger.
  • the outdoor heat exchanger 2 is arranged on the windward side with respect to the flow direction of the wind W, and includes an upwind heat exchanger 2A as a windward flat tube group including a plurality of flat tubes 20 arranged at intervals, and a leeward heat exchanger 2B as a leeward flat tube group that is arranged on the leeward side with respect to the flow direction of the wind W and includes a plurality of flat tubes 30 that are arranged at intervals.
  • the windward heat exchanger 2A and the leeward heat exchanger 2B are arranged close to each other in the flow direction of the wind W, which is air, but are shown spaced apart in the drawing.
  • the number of flat tubes 20 and flat tubes 30 shown in the following description is an example, and the number of flat tubes can be changed as appropriate.
  • the windward heat exchanger 2A as the windward flat tube group is divided into two upper and lower regions.
  • the upwind heat exchanger 1A includes an upwind main heat exchanger 11 configured in an upper region and an upwind sub heat exchanger 12 configured in a lower region.
  • the upwind main heat exchanger 11 includes a plurality of spaced apart first flattened tubes 201 .
  • the upwind secondary heat exchanger 12 includes a plurality of spaced apart second flattened tubes 202 .
  • the number of first flat tubes 201 is greater than the number of second flat tubes 202 .
  • the multiple first flat tubes 201 are arranged above the multiple second flat tubes 202 .
  • the upwind heat exchanger 2A includes a first header pipe 15 and a second header pipe 16. Above the first header pipe 15, there is provided a first connection pipe 15a through which the refrigerant flows in and out. Below the second header pipe 16, a second connection pipe 16a is provided through which the refrigerant flows in and out.
  • the first header pipes 15 and the upwind main heat exchanger 11 are connected to the first connecting portions 20 a of the plurality of first flat pipes 201 .
  • the second header pipes 16 and the upwind secondary heat exchanger 12 are connected to the first connecting portions 20 a of the plurality of second flat pipes 202 .
  • the leeward heat exchanger 2B as a leeward flat tube group is divided into two areas, upper and lower.
  • the leeward heat exchanger 2B includes a leeward main heat exchanger 13 configured in the upper region and a leeward secondary heat exchanger 14 configured in the lower region.
  • the downwind main heat exchanger 13 includes a plurality of spaced apart third flattened tubes 301 .
  • the secondary leeward heat exchanger 14 includes a plurality of spaced apart fourth flattened tubes 302 .
  • the number of the multiple third flat tubes 301 is greater than the number of the multiple fourth flat tubes 302 .
  • the multiple third flat tubes 301 are arranged above the multiple fourth flat tubes 302 .
  • the downwind heat exchanger 2B includes a distributor 50, a third header pipe 17, and a vertical connection pipe 18.
  • the distributor 50 includes an upper first distributor 50a, a central second distributor 50b, and a lower third distributor 50c.
  • the inside of the third header pipe 17 is partitioned into a lower first space 17a, a central second space 17b, and an upper third space 17c.
  • the vertical connection pipes 18 include a first vertical connection pipe 18a connecting the first distributor 50a and the first space 17a, a second vertical connection pipe 18b connecting the second distributor 50b and the second space 17b, and a third It includes a third vertical connecting pipe 18c connecting the distributor 50c and the third space 17c.
  • the first distributor 50a and the leeward main heat exchanger 13 are connected to the fourth connecting portions 30a of the plurality of third flat tubes 301.
  • the second distributor 50 b and the leeward main heat exchanger 13 are connected to the fourth connecting portions 30 a of the plurality of third flat tubes 301 .
  • the third distributor 50 c and the leeward main heat exchanger 13 are connected to the fourth connecting portions 30 a of the plurality of third flat tubes 301 .
  • the first space 17 a and the leeward secondary heat exchanger 14 are connected to the fourth connecting portions 30 a of the plurality of fourth flat tubes 302 .
  • the second space 17 b and the leeward secondary heat exchanger 14 are connected to the fourth connecting portions 30 a of the plurality of fourth flat tubes 302 .
  • the third space 17 c and the leeward secondary heat exchanger 14 are connected to the fifth connecting portion 30 b of the multiple fourth flat tubes 302 .
  • each flat tube 20 in the windward heat exchanger 1A which is the windward flat tube group, opposite to the side where the refrigerant flows in and out corresponds to the leeward heat exchanger 1B, which is the leeward flat tube group.
  • the flat tube 30 is connected to the opposite end of the distributor 50 .
  • the flat tubes 20 of the upwind heat exchanger 1 ⁇ /b>A and the flat tubes 30 of the leeward heat exchanger 1 ⁇ /b>B are connected to each other via a row connecting portion 60 .
  • the refrigerant After passing through the flow path F1, the refrigerant passes through the six first connection portions 20a extending from the second header pipe 16 and passes through the flow path F2 formed by the flat tubes 20. As shown in FIG. After that, the refrigerant passes through the flow path F3 formed by the row connecting portion 60 .
  • the refrigerant that has passed through the flow path F3 passes through a flow path F4 configured by the flat tubes 30 of the downwind heat exchanger 2B, and into the first space 17a, the second space 17b, and the third space 17c of the third header pipe 17.
  • influx The refrigerant that has flowed into the first space 17a passes through the flow path F5 formed by the first vertical connection pipe 18a and flows into the first distributor 50a.
  • the refrigerant that has flowed into the second space 17b passes through the flow path F5 formed by the second vertical connection pipe 18b and flows into the second distributor 50b.
  • the refrigerant that has flowed into the third space 17c passes through the flow path F5 formed by the third vertical connection pipe 18c and flows into the third distributor 50c.
  • the refrigerant that has flowed into the first distributor 50a repeatedly branches, passes through the eight fourth connection portions 30a of the leeward heat exchanger 2B, and passes through the flow path F6 constituted by the flat tubes 30.
  • the refrigerant that has flowed into the second distributor 50b repeatedly branches, passes through the eight fourth connection portions 30a of the leeward heat exchanger 2B, and passes through the flow path F6 formed by the flat tubes 30.
  • the refrigerant that has flowed into the third distributor 50 c repeatedly branches, passes through the eight fourth connection portions 30 a of the downwind heat exchanger 2 B, and passes through the flow path F 6 formed by the flat tubes 30 .
  • the refrigerant passes through the flow path F7 formed by the row connecting portion 60.
  • the refrigerant that has passed through the flow path F7 flows into the first header pipe 15 through the flow path F8 formed by the flat tubes 20 of the upwind heat exchanger 2A.
  • the refrigerant that has flowed into the first header pipe 15 is in a gaseous state due to heat exchange with outdoor air when passing through the flow paths F1 to F8.
  • the gaseous refrigerant flows out of the outdoor heat exchanger 2 through the flow path F9 formed by the first connecting pipe 15a of the upwind heat exchanger 2A.
  • Frost FR adheres to the surface of the windward main heat exchanger 11 due to the relationship with the outside air temperature during heat exchange between the wind W, which is air, and the refrigerant.
  • the distributor 50 has the same configuration as the first distributor 50a, the second distributor 50b, and the third distributor 50c.
  • the refrigerant flowing through the refrigerant pipes flows into the distributor 50 through the refrigerant inflow portion 260A and is distributed, and is distributed to eight refrigerant pipes through the plurality of refrigerant outflow portions 260B. It flows out to the fourth connecting portion 30a composed of the flat tube 30.
  • the outdoor heat exchanger 2 functions as a condenser
  • the refrigerant flows in the opposite direction of this flow.
  • the distributor 50 includes a first plate member 210, a second plate member 220, a third plate member 230, a fourth plate member 240, and a fifth plate member 250. and have The first plate-like member 210, the second plate-like member 220, the third plate-like member 230, the fourth plate-like member 240, and the fifth plate-like member 250 are laminated and integrally joined by brazing.
  • the first plate-shaped member 210, the second plate-shaped member 220, the third plate-shaped member 230, the fourth plate-shaped member 240, and the fifth plate-shaped member 250 have a thickness of, for example, about 1 to 10 mm, and are made of aluminum. is.
  • the first plate member 210 includes a plurality of projections 210A, 210B, 210C, 210D, 210E, and 210F projecting forward from the main body 211.
  • the first plate member 210 includes an inflow pipe 260C projecting forward and a coolant inflow portion 260A connected from the inflow pipe 260C.
  • the second plate member 220 is provided with a plurality of circular holes 220A, 220B, 220C, 220D and 220E.
  • the third plate-shaped member 230 is provided with holes 230A and 230C extending in the left-right direction and S-shaped holes 230B and 230D.
  • the fourth plate member 240 is provided with holes 240A, 240B, 240C, and 240D that widen in the left-right direction.
  • the fifth plate member 250 is provided with a plurality of coolant outflow portions 260B extending in the left-right direction as through holes.
  • Each plate member is processed by pressing or cutting.
  • the first plate member 210 is processed, for example, by pressing.
  • the second plate member 220, the third plate member 230, the fourth plate member 240, and the fifth plate member 250 are processed by cutting, for example.
  • the distributor 50 is installed so that the refrigerant flow direction of each of the plurality of flat tubes 30 connected to the outdoor heat exchanger 2 is horizontal.
  • the distributor 50 may be installed such that the refrigerant flow direction of each of the plurality of flat tubes 30 connected to the outdoor heat exchanger 2 is the vertical direction.
  • the distributor 50 may be installed such that the refrigerant flow direction of each of the plurality of flat tubes 30 connected to the outdoor heat exchanger 2 is oblique.
  • arrows indicate part of the refrigerant flow.
  • the direction of the arrow indicates the direction in which the coolant flows.
  • a part of the refrigerant flow will be described below.
  • the coolant that has passed through the inflow pipe 260C advances from the coolant inflow portion 260A through the hole 220A of the second plate-shaped member 220, collides with the surface of the fourth plate-shaped member 240, and enters the hole 230A of the third plate-shaped member 230. branch left and right along the The branched refrigerant passes through the hole 220B of the second plate-shaped member 220 from the rear to the front and collides with the projections 210A and 210B of the first plate-shaped member 210 .
  • the coolant that has collided with the convex portion 210B of the first plate member 210 flows obliquely downward along the convex portion 210B.
  • the coolant flowing obliquely downward advances through the hole 220C of the second plate-shaped member 220, collides with the surface of the fourth plate-shaped member 240, and branches in the left-right direction along the hole 230C of the third plate-shaped member 230. do.
  • the branched coolant passes through the holes 220D of the second plate member 220 from rear to front and collides with the projections 210D and 210F of the first plate member 210. As shown in FIG.
  • the coolant that has collided with the convex portion 210F of the first plate member 210 flows obliquely downward along the convex portion 210F.
  • the coolant that has flowed obliquely downward advances through the hole 220E of the second plate-like member 220, collides with the surface of the fourth plate-like member 240, and flows along the hole 230D of the third plate-like member 230 to the upper part of the S shape. branch laterally and downwardly.
  • the refrigerant on the upper side of the S shape passes through the hole portion 240C of the fourth plate-shaped member 240 and flows from the refrigerant outflow portion 260B of the fifth plate-shaped member 250 into the fourth connection portion 30a.
  • the refrigerant on the lower side of the S shape passes through the hole portion 240D of the fourth plate member 240 and flows from the refrigerant outflow portion 260B of the fifth plate member 250 into the fourth connection portion 30a.
  • the distributor 50 repeats branching when the refrigerant moves forward and backward, thereby making it possible to equalize the flow rate of the refrigerant without lowering the flow rate.
  • arrows indicate part of the refrigerant flow.
  • the distributor 50 functions as a condenser
  • the refrigerant that has flowed in from the fourth connection portion 30a joins in the four third communication spaces 270C.
  • the merged refrigerant merges in the two second communication spaces 270B.
  • the merged refrigerant further merges in the first communication space 270A and flows out from the inflow pipe 260C.
  • FIG. 13 A case where the outdoor heat exchanger 2 for the evaporator flow according to Embodiment 2 is viewed from the side in FIG. 13 will be described.
  • the piping on the front side is indicated by solid lines
  • the piping on the back side is indicated by broken lines.
  • the refrigerant distributed by the distributor 50 passes through the fourth connection portion 30 a of the leeward main heat exchanger 13 .
  • the refrigerant that has passed through the fourth connection portion 30 a flows from the front side to the back side and flows into the parallel connection portion 60 .
  • the refrigerant flows from the back side to the front side, passes through the first connection portion 20 a of the upwind main heat exchanger 11 , and flows into the first header pipe 15 .
  • Frost FR adheres to the surface of the windward main heat exchanger 11 due to the relationship with the outside air temperature during heat exchange between the wind W, which is air, and the refrigerant.
  • the refrigerant After passing through the flow path G1, the refrigerant passes through 24 first connection portions 20a extending from the first header pipe 15 and passes through the flow path G2 formed by the flat tubes 20. As shown in FIG. After that, the refrigerant passes through the flow path G3 formed by the row connecting portion 60 .
  • the refrigerant that has passed through the flow path G3 passes through the flow path G4 configured by the flat tubes 30 of the leeward heat exchanger 2B and flows into the first distributor 50a, the second distributor 50b, and the third distributor 50c.
  • the refrigerant that has flowed into the first distributor 50a flows into the first space 17a through the flow path G5 formed by the first vertical connection pipe 18a after being aggregated.
  • the refrigerant that has flowed into the second distributor 50b flows into the second space 17b through the channel G5 formed by the second vertical connection pipe 18b after being aggregated.
  • the refrigerant that has flowed into the third distributor 50c flows into the third space 17c through the channel G5 formed by the third vertical connection pipe 18c after being aggregated.
  • the refrigerant that has flowed into the first space 17a passes through the fourth connection portion 30a of the leeward heat exchanger 1B and then through the flow path G6 configured by the flat tubes 30. After that, the refrigerant passes through the flow path G7 formed by the row connecting portion 60. As shown in FIG. The refrigerant that has passed through the flow path G7 passes through a flow path G8 formed by the flat tubes 20 of the upwind heat exchanger 2A and flows into the second header pipe 16 . The refrigerant that has flowed into the second header pipe 16 is in a liquid state due to heat exchange with outdoor air when passing through the flow paths G1 to G8. The liquid refrigerant flows out of the outdoor heat exchanger 2 through the flow path G9 formed by the second connecting pipe 16a of the upwind heat exchanger 1A.
  • the outdoor heat exchanger 2 acts as a condenser
  • the high-temperature, high-pressure gaseous refrigerant first flows through the upwind main heat exchanger 11 .
  • the frost FR adhering to the surface of the upwind main heat exchanger 11 can be efficiently defrosted.
  • FIG. 15 A case where the outdoor heat exchanger 2 for the condenser flow according to Embodiment 2 is viewed from the side in FIG. 15 will be described.
  • the pipes on the near side are indicated by solid lines, and the pipes on the far side are indicated by dashed lines.
  • the refrigerant that has flowed in from the first header pipe 15 passes through the first connection portion 20 a of the upwind main heat exchanger 11 .
  • the refrigerant that has passed through the first connection portion 20 a flows from the front side to the back side and flows into the parallel connection portion 60 .
  • the refrigerant flows from the back side to the front side, passes through the fourth connection portion 30 a of the leeward main heat exchanger 13 , and flows into the distributor 50 .
  • Frost FR on the surface of the windward main heat exchanger 11 is effectively defrosted by the flow of high-temperature, high-pressure gaseous refrigerant.
  • FIG. 16 is an exploded perspective view of the row bridging portion 60 according to the second embodiment.
  • FIG. 17 is a side view of the row bridging section 60 according to the second embodiment.
  • the row connecting portion 60 includes a first plate-like member 61, a second plate-like member 62, a third plate-like member 63, a fourth plate-like member 64, and a fifth plate-like member. 65 and The first plate-like member 61, the second plate-like member 62, the third plate-like member 63, the fourth plate-like member 64, and the fifth plate-like member 65 are laminated and integrally joined by brazing. As shown in FIG. 17 , the first plate member 61 , the third plate member 63 and the fifth plate member 65 are thicker than the second plate member 62 and the fourth plate member 64 . These plate members are made of aluminum, for example.
  • the first plate-shaped member 61 includes a plurality of left first protrusions 61B and a plurality of right second protrusions 61C that protrude outward, ie, the rear side, from the body portion 61A.
  • the second plate member 62 is provided with a stepped hole portion 62A.
  • the third plate member 63 is provided with a stepped hole portion 63A.
  • the fourth plate member 64 is provided with a stepped hole portion 64A.
  • Holes 65A are provided in the fifth plate member 65 at positions that are vertically displaced between the left side and the right side.
  • the row connecting portion 60 constitutes a coolant flow path from the first plate-like member 61 to the fifth plate-like member 65 .
  • the first ends 20e of the plurality of flat tubes 20 forming the windward flat tube group and the second ends 30e of the plurality of flat tubes 30 forming the leeward flat tube group are coaxial with respect to the refrigerant flow direction. not in As shown in FIG. 16, the coolant that has passed through the second end portion 30e flows from the plurality of second convex portions 61C to the plurality of first convex portions 61B, and then flows into the first end portion 20e.
  • the row connecting portion 60 is provided with a convex flow path, it is possible to increase the flow path space compared to forming the flow path with the same number of parts and weight, and reduce the pressure loss. It becomes possible.
  • FIG. 18 is an exploded perspective view of a row bridging section 600 according to a modification.
  • FIG. 19 is a side view of a row bridging section 600 according to a modification.
  • the row connecting portion 600 includes a first plate-like member 610, a second plate-like member 620, a third plate-like member 630, a fourth plate-like member 640, and a fifth plate-like member. 650 and .
  • the first plate-like member 610, the second plate-like member 620, the third plate-like member 630, the fourth plate-like member 640, and the fifth plate-like member 650 are laminated and integrally joined by brazing.
  • first plate member 610 , third plate member 630 , and fifth plate member 650 are thicker than second plate member 620 and fourth plate member 640 .
  • These plate members are made of aluminum, for example.
  • the first plate-shaped member 610 includes a plurality of third protrusions 610B that protrude outward, ie, the rear side, from the main body portion 610A.
  • the second plate-like member 620 is provided with a hole portion 620A that widens in the left-right direction.
  • the third plate-like member 630 is provided with a hole portion 630A that widens in the left-right direction.
  • the fourth plate-like member 640 is provided with a hole portion 640A that widens in the left-right direction.
  • the fifth plate member 65 is provided with holes 650A at left and right coaxial positions.
  • the row connecting portion 600 constitutes a coolant flow path from the first plate-like member 610 to the fifth plate-like member 650 .
  • the first ends 20e of the plurality of flat tubes 20 forming the windward flat tube group and the second ends 30e of the plurality of flat tubes 30 forming the leeward flat tube group are coaxial with respect to the refrigerant flow direction. It is in. As shown in FIG. 18, the coolant that has passed through the second end portion 30e flows horizontally through the plurality of third convex portions 610B, and then flows into the first end portion 20e.
  • the row connecting portion 600 is provided with a convex flow path, the flow path space can be made larger than when the flow path is formed with the same number of parts and weight, and the pressure loss can be reduced. It becomes possible.
  • FIG. 20 is a diagram for explaining the shape of a fin according to Embodiment 3.
  • FIG. Embodiment 3 describes an example applied to the outdoor heat exchanger 2 of Embodiment 2.
  • FIG. A plurality of first fins 71 are arranged at regular intervals on the plurality of first flat tubes 201 in the upwind main heat exchanger 11 .
  • a plurality of second fins 72 are arranged at regular intervals in the plurality of third flat tubes 301 in the leeward main heat exchanger 13 .
  • the first fin 71 and the second fin 72 are made of aluminum.
  • the flow of the refrigerant in the case of the evaporator flow during heating operation is indicated by dotted arrows.
  • the refrigerant that has flowed into the vertical connection pipe 18 flows through the distributor 50, the plurality of third flat tubes 301, the row connecting portion 60, the plurality of first flat tubes 201, the first header pipe 15, and the first connection pipe 15a in that order.
  • the temperature of the refrigerant is 0°C or lower and the dew point temperature of the air or lower, the moisture contained in the air adheres to the evaporator and forms frost. and growing frosting phenomenon occurs.
  • the outdoor heat exchanger 2 can increase the number of fins and improve the heat exchange performance.
  • the outdoor heat exchanger 2 if the interval between the fins is too narrow in a situation where frost builds up, the windward main heat exchanger 11 on the windward side starts frosting at an early stage. The heat exchange performance of the outdoor heat exchanger 2 is lowered when the fins are closed due to frost formation.
  • the intervals between the plurality of first fins 71 provided in the plurality of first flat tubes 201 of the upwind main heat exchanger 11 are provided in the plurality of third flat tubes 301 of the leeward main heat exchanger 13. It is wider than the interval between the plurality of second fins 72 .
  • the outdoor heat exchanger 2 delays the time until the plurality of first fins 71 are closed due to frost formation on the windward side where frost formation is likely to occur while suppressing deterioration in heat exchange performance in the evaporator flow. can be done.
  • Embodiment 3 in the case of the condenser flow during cooling operation, high-temperature and high-pressure gaseous refrigerant flows through the plurality of first flat tubes 201 of the upwind main heat exchanger 11 . Since the outdoor heat exchanger 2 has a wide fin pitch of the plurality of first fins 71, the water generated by melting frost during defrosting in the flow of the condenser is easily discharged to the lower part of the outdoor heat exchanger 2. be able to. Thereby, the outdoor heat exchanger 2 can shorten the defrosting time and improve the heat exchange performance.
  • Embodiment 3 the case of application to the outdoor heat exchanger 2 of Embodiment 2 has been described, but it may be applied to the outdoor heat exchanger 1 of Embodiment 1.
  • the plurality of first fins 71 provided on the plurality of first flat tubes 201 of the upwind main heat exchanger 11 may be similarly provided on the plurality of second flat tubes 202 of the upwind sub heat exchanger 12 .
  • the plurality of second fins 72 provided on the plurality of third flat tubes 301 of the leeward main heat exchanger 13 may be similarly provided on the plurality of fourth flat tubes 302 of the leeward sub heat exchanger 14 .
  • the distance between the plurality of first fins 71 joined to the plurality of first flat tubes 201 and the plurality of second flat tubes 202 is the distance between the plurality of first fins 71 joined to the plurality of third flat tubes 301 and the plurality of fourth flat tubes 302 .
  • the interval between the second fins 72 may be wider than that of the second fins 72 .
  • the present disclosure relates to outdoor heat exchangers 1 and 2 that exchange heat between refrigerant and air.
  • the outdoor heat exchangers 1 and 2 include a windward flat tube group composed of a plurality of spaced apart first flat tubes 201 and a plurality of spaced second flat tubes 202, and a plurality of spaced apart heat exchangers.
  • the refrigerant is a plurality of second flat tubes 202, a plurality of fourth flat tubes 302, a plurality of third flat tubes 301, and a plurality of first flat tubes 201. and act as a condenser, the refrigerant flows through the plurality of first flat tubes 201, the plurality of third flat tubes 301, the plurality of fourth flat tubes 302, and the plurality of second flat tubes 202 in this order.
  • the outdoor heat exchangers 1 and 2 act as evaporators, the refrigerant flows while maintaining the gas-liquid two-phase state and exchanging heat with the air without reducing the flow rate. be able to.
  • the outdoor heat exchangers 1 and 2 act as condensers, a plurality of first flat tubes are arranged in the windward main heat exchanger 11 on the windward side where the high-temperature, high-pressure gas refrigerant is most likely to frost. Defrosting can be effectively performed by flowing in order from 201 .
  • the number of the plurality of first flat tubes 201 is greater than the number of the plurality of second flat tubes 202, and in the upwind flat tube group, the plurality of first flat tubes 201 is equal to the plurality of second flat tubes 202
  • the number of the plurality of third flat tubes 301 is greater than the number of the plurality of fourth flat tubes 302, and in the leeward flat tube group, the plurality of third flat tubes 301 is arranged above the plurality of fourth flat tubes It is positioned above the tube 302 .
  • the plurality of second flat tubes 202 in the windward flat tube group and the plurality of fourth flat tubes 302 in the leeward flat tube group are located below and have a small area in contact with the air, so that heat is generated. Less affected by air passing through for exchange.
  • the refrigerant is preferably heat-exchanged in the plurality of first flat tubes 201 in the windward flat tube group and the plurality of third flat tubes 301 in the leeward flat tube group where the air flow rate is high.
  • the plurality of first flat tubes 201 and the plurality of second flat tubes 202 at the end opposite to the side where the refrigerant flows in and out are connected for each upper and lower set
  • the plurality of third flat tubes 301 and the plurality of fourth flat tubes 302 at the end opposite to the distributor 10 are connected to each other for each upper and lower set.
  • the end opposite to the side where each set of upper and lower sides is connected is the plurality of first flat tubes 201 and the plurality of third flat tubes 301 that are connected to each other.
  • the plurality of second flat tubes 202 and the plurality of fourth flat tubes 302 are connected in a skipped manner.
  • the outdoor heat exchanger 1 is provided with a long flow path through which the refrigerant flows, so that the heat exchange time can be ensured and the heat can be exchanged favorably.
  • each flat tube 20 in the windward flat tube group opposite to the side where the refrigerant flows in and out is connected to the corresponding flat tube 30 in the leeward flat tube group. is connected to the second end opposite the distributor 50 of the .
  • the outdoor heat exchanger 2 allows the refrigerant to flow in the same direction in the flat tubes 20 and 30, so that the temperature of the adjacent upper and lower flat tubes is close, so that the refrigerant inside each other Heat exchange can be suppressed, and heat exchange performance is improved.
  • the outdoor heat exchanger 2 further includes a connecting portion 60 that connects the first end portion 20e and the second end portion 30e that are not coaxial with respect to the flow direction of the refrigerant.
  • the row bridging portion 60 includes a first convex portion 61B projecting outward from a main body portion 61A of a first plate-like member 61 of the row bridging portion 60 corresponding to each flat tube 20 in the windward flat tube group, and a leeward flat tube group.
  • a second convex portion 61C projecting outward from the main body portion 61A of the first plate-like member 61 of the row bridging portion 60 is included corresponding to each flat tube 30 in the tube group.
  • the row connecting portion 60 is provided with a convex flow path, so that the flow path space can be made larger than when the flow path is formed with the same number of parts and weight. It is possible to reduce the pressure loss.
  • the outdoor heat exchanger 2 further includes a connecting portion 600 that connects the first end 20e and the second end 30e that are coaxial with respect to the flow direction of the refrigerant.
  • the row bridging portion 600 is connected to each flat tube 20 in the windward flat tube group and each flat tube 30 in the leeward flat tube group from the main body portion 610A of the first plate member 610 of the row bridging portion 600. It includes a third protrusion 610B that protrudes outward.
  • the row bridging portion 600 is provided with a convex flow path, so that the flow path space can be made larger than when the flow path is formed with the same number of parts and weight. It is possible to reduce the pressure loss.
  • distributors 10 and 50 have projections 110A, 110B, 210A, 210B, 210C, 210D, 210E, and 210F protruding outward from main body 111, 211 of the distributor, and projections 110A, 110B, Channels through which the coolant flows are formed in 210A, 210B, 210C, 210D, 210E, and 210F.
  • the distributors 10 and 50 are formed with flow paths protruding outward from the body portions 111 and 211 . For this reason, the distributors 10 and 50 are miniaturized by reducing the overall thickness compared to distributors in which the flow paths are formed by through holes on the main body 111 and 211 side. can do.
  • the distributors 10, 50 are composed of a plurality of plate-like members provided with holes.
  • the distributors 10 and 50 can suitably form the flow path of the refrigerant by combining the holes of the respective plate members.
  • the plurality of first fins 71 joined to the plurality of first flat tubes 201 and the plurality of second flat tubes 202 and the plurality of first fins 71 joined to the plurality of third flat tubes 301 and the plurality of fourth flat tubes 302 and second fins 72 , wherein the spacing between the plurality of first fins 71 is wider than the spacing between the plurality of second fins 72 .
  • the outdoor heat exchangers 1 and 2 suppress deterioration of heat exchange performance in the flow of the evaporator, and the plurality of first fins 71 are closed due to frost formation on the windward side where frost formation is likely to occur. You can delay the time until The outdoor heat exchangers 1 and 2 can make it easier to discharge water generated by melting frost when defrosting the condenser flow to the lower part of the outdoor heat exchangers 1 and 2 . Thereby, the outdoor heat exchangers 1 and 2 can shorten the defrosting time and improve the heat exchange performance.
  • the air conditioner 100 of the present disclosure includes the outdoor heat exchangers 1 and 2 described above. By providing such a configuration, the air conditioner 100 reduces the flow rate while maintaining the gas-liquid two-phase state and exchanging heat with the air when the outdoor heat exchangers 1 and 2 act as evaporators. Refrigerant can flow without When the outdoor heat exchangers 1 and 2 act as condensers, the air conditioner 100 is arranged in the windward main heat exchanger 11 on the windward side where the high temperature and high pressure gas state refrigerant is most likely to frost. It is possible to defrost effectively by flowing in order from the first flat tube 201 of .
  • the distributors 10 and 50 have a configuration in which the coolant flows through the flow paths projecting outward from the main body portions 111 and 211 .
  • a portion obtained by cutting out a plate-like member may be used as a coolant flow path.
  • Distributors 10 and 50 may connect pipe portions through which refrigerant flows to body portions 111 and 211 instead of convex portions.
  • the distributors 10 and 50 may be configured by a combination of two or more of the projections, cutouts, and pipes.
  • the distributor 10 may change the shape of the plate member like the distributor 50 according to the number of distributions.
  • Distributors 10 and 50 may have a flow channel cross-sectional area smaller on the downstream side than on the upstream side. As a result, the distributors 10 and 50 can prevent the refrigerant from becoming difficult to flow upward due to gravity even when the refrigerant repeatedly branches and the flow rate decreases, and the flow velocity on the downstream side can be improved.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur extérieur (1) comprenant : un groupe de tubes aplatis face au vent comprenant une pluralité de premiers tubes aplatis (201) et une pluralité de deuxièmes tubes aplatis (202) ; un groupe de tubes aplatis face au vent comprenant une pluralité de troisièmes tubes aplatis (301) et une pluralité de quatrièmes tubes aplatis (302), et situés plus loin sous le vent dans la direction du flux d'air que le groupe de tubes aplatis face au vent ; et un distributeur (10) qui distribue le fluide frigorigène s'écoulant du centre vers la pluralité de troisièmes tubes aplatis (301) par le biais de branches multiples. Lorsque l'échangeur de chaleur extérieur (1) agit comme un évaporateur, le fluide frigorigène s'écoule à travers la pluralité de seconds tubes aplatis (202), la pluralité de quatrièmes tubes aplatis (302), la pluralité de troisièmes tubes aplatis (301) et la pluralité de premiers tubes aplatis (201) dans cet ordre, et lorsque l'échangeur de chaleur extérieur (1) agit comme un condenseur, le fluide frigorigène s'écoule à travers la pluralité de premiers tubes aplatis (201), la pluralité de troisièmes tubes aplatis (301), la pluralité de quatrièmes tubes aplatis (302) et la pluralité de seconds tubes aplatis (202) dans cet ordre.
PCT/JP2021/010336 2021-03-15 2021-03-15 Échangeur de chaleur et dispositif de climatisation WO2022195659A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PCT/JP2021/010336 WO2022195659A1 (fr) 2021-03-15 2021-03-15 Échangeur de chaleur et dispositif de climatisation
JP2023506386A JPWO2022195659A1 (fr) 2021-03-15 2021-03-15
US18/262,940 US20240093945A1 (en) 2021-03-15 2021-03-15 Heat exchanger and air conditioner
CN202180095313.8A CN116997759A (zh) 2021-03-15 2021-03-15 热交换器以及空调装置
EP21931415.0A EP4310427A4 (fr) 2021-03-15 2021-03-15 Échangeur de chaleur et dispositif de climatisation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2021/010336 WO2022195659A1 (fr) 2021-03-15 2021-03-15 Échangeur de chaleur et dispositif de climatisation

Publications (1)

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WO2022195659A1 true WO2022195659A1 (fr) 2022-09-22

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US (1) US20240093945A1 (fr)
EP (1) EP4310427A4 (fr)
JP (1) JPWO2022195659A1 (fr)
CN (1) CN116997759A (fr)
WO (1) WO2022195659A1 (fr)

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WO2014020651A1 (fr) * 2012-08-03 2014-02-06 三菱電機株式会社 Dispositif de climatisation
JP2015078830A (ja) 2013-09-11 2015-04-23 ダイキン工業株式会社 熱交換器および空気調和機
WO2017203566A1 (fr) * 2016-05-23 2017-11-30 三菱電機株式会社 Distributeur, collecteur stratifié, échangeur thermique et dispositif de climatisation
WO2017221400A1 (fr) * 2016-06-24 2017-12-28 三菱電機株式会社 Dispositif à cycle de réfrigération et échangeur de chaleur extérieur utilisé dans celui-ci
WO2018142460A1 (fr) * 2017-01-31 2018-08-09 三菱電機株式会社 Échangeur de chaleur et appareil à cycle frigorifique
JP2020201020A (ja) * 2019-06-13 2020-12-17 ダイキン工業株式会社 熱交換器

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AU2013404239B2 (en) * 2013-10-29 2016-11-03 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
WO2016056064A1 (fr) * 2014-10-07 2016-04-14 三菱電機株式会社 Échangeur thermique et dispositif de climatisation
WO2016178278A1 (fr) * 2015-05-01 2016-11-10 三菱電機株式会社 Colonne stratifiée, échangeur de chaleur et climatiseur
WO2017175346A1 (fr) * 2016-04-07 2017-10-12 三菱電機株式会社 Distributeur, échangeur de chaleur et dispositif de climatisation

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WO2014020651A1 (fr) * 2012-08-03 2014-02-06 三菱電機株式会社 Dispositif de climatisation
JP2015078830A (ja) 2013-09-11 2015-04-23 ダイキン工業株式会社 熱交換器および空気調和機
WO2017203566A1 (fr) * 2016-05-23 2017-11-30 三菱電機株式会社 Distributeur, collecteur stratifié, échangeur thermique et dispositif de climatisation
WO2017221400A1 (fr) * 2016-06-24 2017-12-28 三菱電機株式会社 Dispositif à cycle de réfrigération et échangeur de chaleur extérieur utilisé dans celui-ci
WO2018142460A1 (fr) * 2017-01-31 2018-08-09 三菱電機株式会社 Échangeur de chaleur et appareil à cycle frigorifique
JP2020201020A (ja) * 2019-06-13 2020-12-17 ダイキン工業株式会社 熱交換器

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Title
See also references of EP4310427A4

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US20240093945A1 (en) 2024-03-21
EP4310427A4 (fr) 2024-05-01
EP4310427A1 (fr) 2024-01-24
JPWO2022195659A1 (fr) 2022-09-22
CN116997759A (zh) 2023-11-03

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