WO2022249425A1 - 熱交換器、熱交換器を備えた空気調和装置の室外機、および、空気調和装置の室外機を備えた空気調和装置 - Google Patents

熱交換器、熱交換器を備えた空気調和装置の室外機、および、空気調和装置の室外機を備えた空気調和装置 Download PDF

Info

Publication number
WO2022249425A1
WO2022249425A1 PCT/JP2021/020313 JP2021020313W WO2022249425A1 WO 2022249425 A1 WO2022249425 A1 WO 2022249425A1 JP 2021020313 W JP2021020313 W JP 2021020313W WO 2022249425 A1 WO2022249425 A1 WO 2022249425A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
refrigerant
header
air conditioner
exchanger core
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.)
Ceased
Application number
PCT/JP2021/020313
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
洋次 尾中
哲二 七種
理人 足立
七海 岸田
泰作 五明
祐基 中尾
伸吾 笠木
篤史 岐部
裕之 森本
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to EP21943071.7A priority Critical patent/EP4350252A4/en
Priority to US18/557,331 priority patent/US20240219067A1/en
Priority to CN202180098566.0A priority patent/CN117355721A/zh
Priority to PCT/JP2021/020313 priority patent/WO2022249425A1/ja
Priority to JP2023523891A priority patent/JPWO2022249425A1/ja
Publication of WO2022249425A1 publication Critical patent/WO2022249425A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

Classifications

    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/22—Means for preventing condensation or evacuating condensate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • 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
    • F25B2313/029—Control issues
    • F25B2313/0293—Control issues related to the indoor fan, e.g. controlling speed
    • 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
    • F25B2313/029—Control issues
    • F25B2313/0294—Control issues related to the outdoor fan, e.g. controlling speed
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off valves
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • the present disclosure relates to a heat exchanger having a plurality of flat tubes, an outdoor unit of an air conditioner provided with the heat exchanger, and an air conditioner provided with the outdoor unit of the air conditioner.
  • the vertical direction is the tube extension direction, and a plurality of flat tubes arranged at intervals in the horizontal direction, a plurality of fins connected between adjacent flat tubes to transfer heat to the flat tubes, and a plurality of flat tubes
  • a heat exchanger provided with headers respectively provided at the upper end and lower end of a tube (see Patent Document 1, for example).
  • the heat exchanger of Patent Document 1 is mounted on an outdoor unit of an air conditioner capable of both cooling operation and heating operation.
  • heating operation is performed in a low-temperature environment where the outside air temperature is low and the surface temperature of the heat exchanger is 0° C. or lower, frost forms on the heat exchanger. Therefore, when the amount of frost formed on the heat exchanger reaches a certain amount or more, a defrosting operation is performed to melt the frost on the surface of the heat exchanger.
  • high-temperature and high-pressure gas refrigerant is allowed to flow in from one of the headers and flows through the flat tubes to defrost.
  • the present disclosure has been made to solve the above problems, and includes a heat exchanger capable of suppressing a decrease in defrosting performance, an outdoor unit of an air conditioner equipped with a heat exchanger, and an air conditioner.
  • An object of the present invention is to provide an air conditioner having an outdoor unit for the air conditioner.
  • ⁇ P HEX / ⁇ P HEAD (5.94635 ⁇ 10 ⁇ 4 ⁇ A ⁇ 1.75030 )/(8.4303H+0.8779)> 1 is satisfied.
  • the outdoor unit of the air conditioner according to the present disclosure includes the above heat exchanger.
  • an air conditioner includes the outdoor unit of the air conditioner, the indoor unit of the air conditioner, the outdoor unit of the air conditioner, and the indoor unit of the air conditioner, and a refrigerant is and a circulating refrigerant circuit.
  • FIG. 1 is a refrigerant circuit diagram of an air conditioner provided with a heat exchanger according to Embodiment 1.
  • FIG. 1 is a perspective view of a heat exchanger according to Embodiment 1;
  • FIG. 1 is a front view of a heat exchanger according to Embodiment 1;
  • FIG. 4 is a diagram showing flow channel cross-sectional areas of flat tubes of the heat exchanger according to Embodiment 1;
  • FIG. 5 is a graph showing the relationship between the total cross-sectional area of the heat exchanger core of the heat exchanger and ⁇ P HEX / ⁇ P HEAD according to experimental results;
  • FIG. 1 is a perspective view of a heat exchanger according to Embodiment 1
  • FIG. 1 is a front view of a heat exchanger according to Embodiment 1
  • FIG. 4 is a diagram showing flow channel cross-sectional areas of flat tubes of the heat exchanger according to Embodiment 1
  • FIG. 5 is a graph showing the relationship between the total cross
  • FIG. 5 is a diagram showing the relationship between the height H of the heat exchanger core of the heat exchanger and ⁇ P HEX / ⁇ P HEAD according to experimental results;
  • FIG. 4 is a diagram for explaining deterioration of defrosting performance due to liquid retention in a heat exchanger;
  • FIG. 4 is a diagram for explaining heating capacity over time of the heat exchanger according to Embodiment 1; It is a figure explaining the heating capacity by time progress of the conventional heat exchanger.
  • FIG. 10 is a diagram showing the relationship between the H/L of the heat exchanger and the liquid head ⁇ P HEAD according to experimental results; 4 is a diagram showing pressure distribution inside the heat exchanger according to Embodiment 1.
  • FIG. 5 is a diagram showing pressure distribution inside a modification of the heat exchanger according to Embodiment 1;
  • FIG. 3 is a schematic diagram showing the periphery of a header channel of the heat exchanger according to Embodiment 1;
  • FIG. 9 is a diagram illustrating heat exchanger performance of a heat exchanger according to Embodiment 2;
  • FIG. 10 is a diagram illustrating heat exchanger performance of a modification of the heat exchanger according to Embodiment 2;
  • FIG. 11 is a perspective view schematically showing a heat exchanger according to Embodiment 3;
  • FIG. 11 is an enlarged view of a row-connecting header and its surroundings of a heat exchanger according to Embodiment 3;
  • FIG. 10 is a diagram showing the relationship between the gap ⁇ of the heat exchanger and the differential pressure ⁇ P 2-3 according to experimental results;
  • FIG. 11 is a schematic side view of a heat exchanger according to Embodiment 3;
  • Fig. 11 is a refrigerant circuit diagram showing an enlarged outdoor unit of an air conditioner according to Embodiment 4;
  • FIG. 11 is a refrigerant circuit diagram showing an enlarged outdoor unit of an air conditioner according to Embodiment 5;
  • FIG. 11 is a schematic cross-sectional view of a flat tube of a heat exchanger according to Embodiment 6;
  • FIG. 12 is a schematic cross-sectional view of a flat tube of a modification of the heat exchanger according to Embodiment 6;
  • FIG. 11 is a schematic side view of a flat tube of a modification of the heat exchanger according to Embodiment 6;
  • FIG. 12 is a diagram showing the relationship between the type of refrigerant used in the refrigerant circuit of the air conditioner and ⁇ P HEX / ⁇ P HEAD according to Embodiment 7;
  • FIG. 11 is a front view of a heat exchanger of an air conditioner according to Embodiment 8;
  • FIG. 20 is a front view of a heat exchanger of an air conditioner according to Embodiment 9;
  • FIG. 1 is a refrigerant circuit diagram of an air conditioner 100 including a heat exchanger 30 according to Embodiment 1.
  • FIG. 1 indicates the flow of refrigerant during cooling operation, and the broken arrow in FIG. 1 indicates the flow of refrigerant during heating operation.
  • the heat exchanger 30 is mounted on the outdoor unit 10 of the air conditioning apparatus 100 including the outdoor unit 10 and the indoor unit 20 .
  • the outdoor unit 10 includes a heat exchanger 30 , a compressor 11 , a flow path switching device 12 , and a fan 13 .
  • the indoor unit 20 includes an expansion device 21 , an indoor heat exchanger 22 and an indoor fan 23 .
  • the air conditioner 100 also includes a refrigerant circuit 101, which is composed of an outdoor unit 10 and an indoor unit 20, and in which a refrigerant circulates.
  • the refrigerant circuit 101 is configured by connecting a compressor 11, a flow switching device 12, a heat exchanger 30, an expansion device 21, and an indoor heat exchanger 22 by refrigerant piping.
  • This air conditioner 100 can be operated in both cooling operation and heating operation by switching the channel switching device 12 .
  • the compressor 11 sucks in a low-temperature, low-pressure refrigerant, compresses the sucked-in refrigerant, and discharges a high-temperature, high-pressure refrigerant.
  • the compressor 11 is, for example, an inverter compressor whose capacity, which is the output amount per unit time, is controlled by changing the operating frequency.
  • the channel switching device 12 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the direction of refrigerant flow.
  • the flow switching device 12 switches to the state indicated by the solid line in FIG. 1 during cooling operation, and the discharge side of the compressor 11 and the heat exchanger 30 are connected. Further, the flow path switching device 12 switches to the state indicated by the dashed line in FIG. 1 during the heating operation, and the discharge side of the compressor 11 and the indoor heat exchanger 22 are connected.
  • the heat exchanger 30 exchanges heat between the outdoor air and the refrigerant.
  • the heat exchanger 30 functions as a condenser that radiates the heat of the refrigerant to the outdoor air to condense the refrigerant during the cooling operation.
  • the heat exchanger 30 functions as an evaporator that evaporates the refrigerant during the heating operation and cools the outdoor air with the heat of vaporization at that time.
  • the fan 13 supplies outdoor air to the heat exchanger 30, and the amount of air blown to the heat exchanger 30 is adjusted by controlling the rotation speed.
  • the throttle device 21 is, for example, an electronic expansion valve that can adjust the opening of the throttle, and controls the pressure of the refrigerant flowing into the heat exchanger 30 or the indoor heat exchanger 22 by adjusting the opening.
  • the expansion device 21 is provided in the indoor unit 20, but may be provided in the outdoor unit 10, and the installation location is not limited.
  • the indoor heat exchanger 22 exchanges heat between the indoor air and the refrigerant.
  • the indoor heat exchanger 22 functions as an evaporator that evaporates the refrigerant and cools the outdoor air with the heat of vaporization during the cooling operation.
  • the indoor heat exchanger 22 functions as a condenser that radiates the heat of the refrigerant to the outdoor air to condense the refrigerant during the heating operation.
  • the indoor fan 23 supplies indoor air to the indoor heat exchanger 22, and the amount of air blown to the indoor heat exchanger 22 is adjusted by controlling the rotation speed.
  • FIG. 2 is a perspective view of the heat exchanger 30 according to Embodiment 1.
  • FIG. FIG. 3 is a front view of the heat exchanger 30 according to Embodiment 1.
  • the dashed arrows in FIG. 2 and the white arrows in FIG. 3 indicate the flow of the refrigerant during the cooling operation.
  • FIG. 3 also shows the height H and width L of the heat exchanger core 31, which will be described later.
  • the heat exchanger 30 includes a heat exchanger core 31 having multiple flat tubes 38 and multiple fins 39 .
  • the flat tubes 38 are arranged side by side in the horizontal direction (horizontal direction in FIG. 2) at intervals so that the wind generated by the fan 13 flows, and are arranged vertically in the vertical direction (up and down direction in FIG. 2).
  • Refrigerant flows in the direction of
  • the fins 39 are connected between adjacent flat tubes 38 to transfer heat to the flat tubes 38 .
  • the fins 39 improve heat exchange efficiency between air and refrigerant, and corrugated fins are used, for example. However, it is not limited to this. Since heat exchange between the air and the refrigerant takes place on the surface of the flat tube 38, the fins 39 may be omitted.
  • a first header 34 is provided at the lower end of the heat exchanger core 31 .
  • the lower ends of the flat tubes 38 of the heat exchanger core 31 are directly inserted into the first header 34 .
  • a second header 35 is provided at the upper end of the heat exchanger core 31 .
  • the upper ends of the flat tubes 38 of the heat exchanger core 31 are directly inserted into the second headers 35 .
  • a hot gas refrigerant inlet 32 is formed at one end of the first header 34 , and the hot gas refrigerant inlet 32 is connected to the refrigerant circuit 101 of the air conditioner 100 via a gas pipe 37 . Therefore, the first header 34 is also called a gas header.
  • the first header 34 allows the high-temperature and high-pressure gas refrigerant (hereinafter also referred to as hot gas refrigerant) from the compressor 11 to flow into the heat exchanger 30 during cooling operation, and after heat exchange in the heat exchanger 30 during heating operation. , the low-temperature, low-pressure gas refrigerant flows out to the refrigerant circuit 101 . That is, the hot gas refrigerant inlet 32 serves as a hot gas refrigerant inlet.
  • the hot gas refrigerant is not limited to a gas single-phase refrigerant, and may be a gas-liquid two-phase refrigerant containing a gas phase of 0° C. or higher.
  • a liquid refrigerant outlet 33 is formed at one end of the second header 35 , and the liquid refrigerant outlet 33 is connected to the refrigerant circuit 101 of the air conditioner 100 via a liquid pipe 36 . Therefore, the second header 35 is also called a liquid header.
  • the second header 35 allows the low-temperature, low-pressure two-phase refrigerant to flow into the heat exchanger 30 during heating operation, and allows the low-temperature, high-pressure liquid refrigerant after heat exchange in the heat exchanger 30 to flow out to the refrigerant circuit 101 during cooling operation. .
  • the plurality of flat tubes 38, the plurality of fins 39, the first header 34, and the second header 35 are all made of aluminum and joined by brazing.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 11 flows into the heat exchanger 30 via the flow switching device 12 .
  • the high-temperature, high-pressure gas refrigerant that has flowed into the heat exchanger 30 exchanges heat with the outdoor air taken in by the fan 13 and condenses while releasing heat, and flows out of the heat exchanger 30 as a low-temperature, high-pressure liquid refrigerant.
  • the low-temperature, high-pressure liquid refrigerant that has flowed out of the heat exchanger 30 is decompressed by the expansion device 21 , becomes a low-temperature, low-pressure, gas-liquid two-phase refrigerant, and flows into the indoor heat exchanger 22 .
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant that has flowed into the indoor heat exchanger 22 exchanges heat with the indoor air taken in by the indoor fan 23, absorbs heat, and evaporates, cooling the indoor air and forming a low-temperature, low-pressure gas refrigerant. and flows out from the indoor heat exchanger 22.
  • the low-temperature, low-pressure gas refrigerant that has flowed out of the indoor heat exchanger 22 is sucked into the compressor 11 and becomes high-temperature, high-pressure gas refrigerant again.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 11 flows into the indoor heat exchanger 22 via the flow switching device 12 .
  • the high-temperature, high-pressure gas refrigerant that has flowed into the indoor heat exchanger 22 exchanges heat with the indoor air taken in by the indoor fan 23, condenses while releasing heat, heats the indoor air, and becomes a low-temperature, high-pressure liquid refrigerant that flows indoors. It flows out of heat exchanger 22 .
  • the low-temperature, high-pressure liquid refrigerant that has flowed out of the indoor heat exchanger 22 is depressurized by the expansion device 21 , becomes a low-temperature, low-pressure, gas-liquid two-phase refrigerant, and flows into the heat exchanger 30 .
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant that has flowed into the heat exchanger 30 exchanges heat with the outdoor air taken in by the fan 13, absorbs heat, evaporates, becomes a low-temperature, low-pressure gas refrigerant, and flows out of the heat exchanger 30. do.
  • the low-temperature, low-pressure gas refrigerant that has flowed out of the heat exchanger 30 is sucked into the compressor 11 and becomes high-temperature, high-pressure gas refrigerant again.
  • the fan 13 In the defrosting operation, the fan 13 is stopped, the flow path switching device 12 is switched to the same state as during the cooling operation, and high-temperature and high-pressure gas refrigerant flows into the heat exchanger 30 . This melts the frost adhering to the flat tubes 38 and the fins 39 .
  • the high-temperature and high-pressure gas refrigerant flows from the gas pipe 37 through the first header 34 into each flat tube 38 .
  • the refrigerant that has flowed into each flat tube 38 becomes an upward flow that is an upward flow in the vertical direction.
  • the high-temperature coolant that has flowed into the flat tubes 38 melts the frost adhering to the flat tubes 38 and the fins 39 and turns them into water.
  • the timing for ending the defrosting operation and resuming the heating operation can be determined by a known method. For example, when the temperature detected by a temperature sensor (not shown) reaches a predetermined temperature, or when the defrosting operation is performed for a certain period of time, the defrosting operation may be terminated and the heating operation may be restarted. .
  • FIG. 4 is a diagram showing the flow passage cross-sectional area of the flat tube 38 of the heat exchanger 30 according to Embodiment 1.
  • FIG. 5 is a diagram showing the relationship between the total cross-sectional area of the heat exchanger core 31 of the heat exchanger and ⁇ P HEX / ⁇ P HEAD according to experimental results.
  • FIG. 6 is a diagram showing the relationship between the height H of the heat exchanger core 31 of the heat exchanger and ⁇ P HEX / ⁇ P HEAD according to experimental results.
  • FIG. 7 is a diagram for explaining deterioration of defrosting performance due to liquid retention in the heat exchanger. The white arrows in FIG. 7 indicate the flow of refrigerant during defrosting operation.
  • the total flow channel cross-sectional area of the heat exchanger core 31 is defined as A
  • the total flow channel cross-sectional area A is obtained by the following formula (1).
  • A a ⁇ N[m 2 ] (1) a: Channel cross-sectional area [m 2 ] of flat tube 38 per tube (shaded area in FIG. 4) N: Number of flat tubes 38 [pieces]
  • ⁇ P HEX the differential pressure in the refrigerant channel
  • ⁇ P HEAD the liquid head
  • ⁇ P HEX / ⁇ P HEAD is obtained by the following equation (2).
  • the flow path differential pressure ⁇ P HEX is the pressure difference in the flow path in which the hot gas refrigerant flows as an upward flow during the defrosting operation. differential pressure.
  • ⁇ P HEX / ⁇ P HEAD (5.94635 ⁇ 10 ⁇ 4 ⁇ A ⁇ 1.75030 )/(8.4303H ⁇ 0.8779) (2)
  • the height H of the heat exchanger core 31 is the length between the upper end of the first header 34 and the lower end of the second header 35 and the length of the exposed portion of the flat tube 38 . .
  • the above formula (2) is an empirical formula obtained by the inventors' numerical analysis and experimental results.
  • the height H [m ] of the heat exchanger core 31, which is a shape parameter of the heat exchanger 30 dominated by the liquid head ⁇ P HEAD , to determine the heat exchanger 30 is formulated within the range of conditions used for the outdoor unit 10 for buildings, stores, homes, etc. (hereinafter referred to as building use).
  • This empirical formula is shown in FIGS.
  • FIG. 5 shows that the height H of the heat exchanger core 31 is fixed and the total cross-sectional area A of the heat exchanger core 31 is varied. The cross-sectional area A is fixed, and the height H of the heat exchanger core 31 is varied.
  • ⁇ P HEX / ⁇ P HEAD tends to decrease as the total flow passage cross-sectional area A [m 2 ] of the heat exchanger core 31 increases.
  • ⁇ P HEX / ⁇ P HEAD tends to decrease as the height H [m] of the heat exchanger core 31 increases.
  • FIGS. 5 and 6 when ⁇ P HEX / ⁇ P HEAD ⁇ 1, the hot gas refrigerant that has flowed into the first header 34 flows upward and flows through the flat tubes of the heat exchanger core 31. 38, the liquefied refrigerant cannot rise due to the influence of gravity and stays in a part of the hot gas flow area.
  • car air conditioners use engine heat when heating, and use heat pumps only when cooling. Therefore, most heat exchangers using corrugated fins used in outdoor units such as car air conditioners are heat exchangers exclusively for cooling, and therefore are used for applications in which defrosting operation does not occur. In addition, even when the heat exchanger is used as a heat pump for both cooling and heating, the height of the heat exchanger core is often as small as 300 [mm]. Most of the heat exchangers used in the above have a heat exchanger core height of 420 [mm] or more, and some have a heat exchanger core height of 800 [mm] or more.
  • the height of the heat exchanger core 31 is increased to about 420 [mm].
  • ⁇ P HEX / ⁇ P HEAD is reduced by 43% compared to the height of 300 mm.
  • liquid retention occurs in a part of the heat exchanger, making it difficult for the liquid refrigerant to flow.
  • ⁇ P HEX / ⁇ P HEAD is about 50 [% with respect to the height of 300 [mm] ]
  • ⁇ P HEX / ⁇ P HEAD is reduced by about 65 [%] with respect to the height of 300 [mm].
  • the heat exchanger 30 is configured to satisfy ⁇ P HEX / ⁇ P HEAD >1 in order to suppress the occurrence of liquid retention and suppress the deterioration of defrosting performance during the defrosting operation.
  • FIG. 8 is a diagram for explaining the heating capacity of the heat exchanger 30 according to Embodiment 1 over time.
  • FIG. 9 is a diagram for explaining the heating capacity of a conventional heat exchanger over time.
  • the heat exchanger is not configured to satisfy ⁇ P HEX / ⁇ P HEAD >1 as in the conventional case, liquid retention occurs during defrosting operation, and sufficient defrosting occurs in the liquid retention area where liquid retention occurs. Frost remains. Therefore, as shown in FIG. 9, the heating capacity during the heating operation decreases over time.
  • the heat exchanger 30 is configured to satisfy ⁇ P HEX / ⁇ P HEAD >1 as in Embodiment 1, the occurrence of liquid retention is suppressed during the defrosting operation, and residual frost is suppressed. be able to. Therefore, as shown in FIG. 8, it is possible to suppress a decrease in the heating capacity during the heating operation even if time elapses, and it is possible to improve the heating capacity during the heating operation.
  • the heat exchanger 30 is configured to satisfy H/L>1 when the width of the heat exchanger core 31 is defined as L [m].
  • the width L of the heat exchanger core 31 is the distance between the outer sides of the outermost flat tubes 38 among the plurality of flat tubes 38 arranged in the horizontal direction.
  • FIG. 10 is a diagram showing the relationship between H/L of a heat exchanger and ⁇ P HEAD according to experimental results. Note that FIG. 10 shows the relationship between H/L and the liquid head ⁇ P HEAD when a certain working fluid is flowed through the heat exchanger.
  • FIG. 11 is a diagram explaining the pressure distribution inside the heat exchanger 30 according to the first embodiment.
  • FIG. 12 is a diagram illustrating pressure distribution inside a modification of the heat exchanger 30 according to the first embodiment.
  • White arrows and black arrows in FIGS. 11 and 12 indicate the flow of refrigerant during the defrosting operation.
  • the hot gas refrigerant inlet 32 and the liquid refrigerant outlet 33 are provided at the ends located on the same side of the first header 34 and the second header 35, respectively.
  • the hot gas refrigerant inlet 32 and the liquid refrigerant outlet 33 are provided at opposite ends of the first header 34 and the second header 35, respectively.
  • the position (1 ) ⁇ position (4) is defined as G 1-4 , and the refrigerant flow rate flowing through position (2) ⁇ position ( 3 ) in FIG. 3 .
  • This is affected by the difference between the pressure loss ⁇ P 1-2 of the first header 34 and the pressure loss ⁇ P 3-4 of the second header 35, and the difference between position (1) and position (4) in FIG. This is because the differential pressure ⁇ P 1-4 is relatively larger than the differential pressure ⁇ P 2-3 between the positions (2) and (3) in FIG.
  • FIG. 13 is a schematic diagram showing the periphery of the header flow path of the heat exchanger 30 according to Embodiment 1.
  • FIG. 13 shows the periphery of the header channel of the first header 34, the configuration of the periphery of the header channel of the second header 35 is the same.
  • the lengths of the first header 34 and the second header 35 can be configured to be small with respect to the amount of heat exchange. Therefore, the pressure loss of the working fluid flowing inside the first header 34 and the second header 35 can be suppressed. That is, the difference between the pressure loss ⁇ P 1-2 of the first header 34 and the pressure loss ⁇ P 3-4 of the second header 35 described with reference to FIGS. 11 and 12 can be reduced. can be increased, the occurrence of liquid retention can be suppressed.
  • the flat tubes 38 are generally joined to the first header 34 and the second header 35 by brazing.
  • the heat exchanger 30 includes one heat exchanger core 31 having a plurality of flat tubes 38 extending in the vertical direction, or two or more heat exchanger cores 31 along the air flow direction, and serves as a condenser.
  • the heat exchanger 30 is mounted on the outdoor unit 10 of the air conditioner 100 so that the refrigerant flows upward inside the flat tubes 38 when functioning.
  • the heat exchanger 30 according to Embodiment 1 satisfies H/L>1 when the width of the heat exchanger core 31 is defined as L [m].
  • the heat exchanger 30 according to Embodiment 1 is configured to satisfy H/L>1. Therefore, since the length of the first header 34 and the second header 35 can be configured to be small with respect to the amount of heat exchange, the pressure loss of the working fluid flowing inside the first header 34 and the second header 35 can be reduced. can be suppressed, and the occurrence of liquid retention can be suppressed.
  • the heat exchanger 30 includes one heat exchanger core 31, a first header 34 is provided at the lower end of the heat exchanger core 31, and a header 34 is provided at the upper end of the heat exchanger core 31.
  • a second header 35 is provided.
  • a hot gas refrigerant inlet 32 is formed at one end of the first header 34, and a liquid through which the refrigerant flows out when functioning as a condenser is provided at one end of the second header 35 located opposite to one end of the first header 34.
  • a coolant outlet 33 is formed.
  • the hot gas refrigerant inlet 32 and the liquid refrigerant outlet 33 are formed at opposite ends of the first header 34 and the second header 35, respectively. . Therefore, the difference between the pressure loss ⁇ P 1-2 of the first header 34 and the pressure loss ⁇ P 3-4 of the second header 35 becomes small. As a result, a region where the flow path differential pressure ⁇ P HEX becomes small is less likely to occur, thereby suppressing the occurrence of liquid stagnation and the formation of residual frost.
  • the outdoor unit 10 of the air conditioner 100 according to Embodiment 1 includes the heat exchanger 30 described above.
  • the air conditioner 100 includes the outdoor unit 10 of the air conditioner 100, the indoor unit 20 of the air conditioner 100, the outdoor unit 10 of the air conditioner 100, and the air conditioner 100. and a refrigerant circuit 101 configured by the indoor unit 20 and through which a refrigerant circulates.
  • the same effect as the heat exchanger 30 can be obtained.
  • Embodiment 2 will be described below, but descriptions of parts that overlap with those of Embodiment 1 will be omitted, and parts that are the same as or correspond to those of Embodiment 1 will be given the same reference numerals.
  • FIG. 14 is a diagram illustrating the heat exchanger performance of the heat exchanger 30 according to the second embodiment.
  • FIG. 15 is a diagram for explaining the heat exchanger performance of a modification of the heat exchanger 30 according to the second embodiment. Black arrows and white arrows in FIGS. 14 and 15 indicate the flow of refrigerant during the defrosting operation. 14 and 15, the width of each region of the heat exchanger core 31 is shown as L 1 , L 2 . . . from the downstream side.
  • downstream refers to the flow of refrigerant that has flowed in from the hot gas refrigerant inlet 32, and the same applies hereinafter.
  • FIG. 14 shows a case where one partition plate 40 is provided in the first header 34 and an odd number of partition plates 40 are provided.
  • 15 shows a case where one partition plate 40 is provided in the first header 34 and one partition plate 40 is provided in the second header 35, and an even number of partition plates 40 are provided.
  • the liquid refrigerant outlet 33 is located at the end opposite to the first header 34 and the end where the hot gas refrigerant inlet 32 is formed. provided in the department.
  • FIG. 14 shows a case where one partition plate 40 is provided in the first header 34 and an odd number of partition plates 40 are provided.
  • the liquid refrigerant outlet 33 is located at the end of the first header 34 where the second header 35 and the hot gas refrigerant inlet 32 are formed. It is provided at the end located on the opposite side of the part.
  • the partition plate 40 is provided to horizontally partition the flow path of the heat exchanger core 31 into a plurality of regions. Moreover, the partition plate 40 is provided so that the flow path in each region of the heat exchanger core 31 is counter-current to the flow path in the adjacent region. Assuming that the width of the most downstream region of the heat exchanger core 31 is L 1 , the heat exchanger 30 is configured to satisfy 20[%] ⁇ L 1 /L ⁇ 50[%].
  • the heat exchanger 30 is configured to satisfy 20[%] ⁇ L 1 /L ⁇ 50[%] in order to achieve a heat exchanger performance of 90[%] or more. By doing so, the heat exchanger performance can be improved compared to the case where the partition plate 40 is not provided in the first header 34 .
  • the heat exchanger 30 includes one heat exchanger core 31, the first header 34 is provided at the lower end of the heat exchanger core 31, and the A heat exchanger 30 provided with a second header 35 .
  • the heat exchanger 30 also includes a partition plate 40 that is provided inside at least the first header 34 and partitions the flow path of the heat exchanger core 31 into a plurality of regions in the width direction.
  • the width of the heat exchanger core 31 is defined as L [m] and the width of the most downstream region of the heat exchanger core 31 is defined as L1 , 20[%] ⁇ L1 / It satisfies L ⁇ 50[%].
  • the heat exchanger 30 according to Embodiment 2 is configured to satisfy 20[%] ⁇ L 1 /L ⁇ 50[%]. Therefore, compared with the case where the partition plate 40 is not provided in the first header 34, the heat exchanger performance can be improved. Furthermore, the increase in pressure loss suppresses the occurrence of liquid retention during the defrosting operation, so that residual frost can be suppressed. As a result, it is possible to improve the defrosting performance during the defrosting operation.
  • Embodiment 3 will be described below, but the description of the parts that overlap with Embodiments 1 and 2 will be omitted, and the same or corresponding parts as those in Embodiments 1 and 2 will be given the same reference numerals.
  • FIG. 16 is a perspective view schematically showing the heat exchanger 30 according to Embodiment 3.
  • FIG. FIG. 17 is an enlarged view of the row-connecting header 50 and its vicinity of the heat exchanger 30 according to the third embodiment.
  • the black arrows in FIG. 16 indicate the flow of air passing through the heat exchanger 30, and the dashed arrows and white arrows indicate the flow of refrigerant during the defrosting operation. Also, the white arrows in FIG. 17 indicate the flow of the refrigerant.
  • two heat exchanger cores 31 are arranged side by side in the air flow direction. Both upper ends of the two rows of heat exchanger cores 31 arranged in the air flow direction are connected to row-connecting headers 50 .
  • the lower ends of the two rows of heat exchanger cores 31 on the leeward side are connected to a first header 34
  • the lower ends of the two rows of heat exchanger cores 31 on the windward side are connected to a second header 35 . It is connected to the.
  • the hot gas refrigerant that has flowed into the first header 34 flows upward through the flat tubes 38 of the heat exchanger core 31 arranged on the leeward side, and then is turned back at the parallel header 50. , flows downward through the flat tubes 38 of the heat exchanger core 31 arranged on the windward side, and then flows out from the second header 35 . That is, the parallel header 50 is provided at one end of two adjacent heat exchanger cores 31, and transfers the merged refrigerant from each flat tube 38 of the heat exchanger core 31 on the leeward side to the heat exchanger core 31 on the windward side. distributed to each flat tube 38 of.
  • the flow path differential pressure ⁇ P HEX is the differential pressure between the lower end of the flat tube 38 of the heat exchanger core 31 on the leeward side and the lower end of the flat tube 38 of the heat exchanger core 31 on the windward side. (Differential pressure between position (1) and position (4) in FIG. 16) P 1-4 .
  • FIG. 18 is a diagram showing the relationship between the gap ⁇ of the heat exchanger and the differential pressure ⁇ P 2-3 according to experimental results.
  • FIG. 18 shows the differential pressure P2-3 inside the row header 50 when the gap ⁇ between the upper end portion of the flat tube 38 and the wall portion 51 of the row header 50 is changed based on the inventors' simulation. An example is shown.
  • the differential pressure ⁇ P 2-3 increases exponentially by decreasing the gap ⁇ . Normally, the larger the gap ⁇ , the better the heat exchanger performance. By doing so, it is possible to suppress the occurrence of liquid stagnation even in consideration of the influence of pressure loss, and it is possible to improve the performance of the heat exchanger.
  • FIG. 19 is a schematic side view of the heat exchanger 30 according to Embodiment 3.
  • FIG. The black arrows in FIG. 16 indicate the air flow passing through the heat exchanger 30, and the white arrows indicate the refrigerant flow.
  • the fan 13 is stopped in order to suppress heat leakage from the heat exchanger 30 to the air during the defrosting operation.
  • the first header 34 with the hot gas refrigerant inlet 32 is arranged on the leeward side
  • the second header 35 with the liquid refrigerant outlet 33 is arranged on the windward side. do.
  • the refrigerant flow becomes an upward flow, which is an upward flow in the vertical direction. It is possible to suppress the occurrence of liquid stagnation in the heat exchanger core 31 on the side. Further, as shown in FIG.
  • the two heat exchanger cores 31 are arranged side by side in the air flow direction. It is good also as a structure arrange
  • the heat exchanger 30 is configured to include the number of row-connecting headers 50 equal to the number of the heat exchanger cores 31 minus one.
  • the first header 34 is provided at the lower end of the heat exchanger core 31 on the most leeward side, and the heat exchanger on the most windward side
  • a second header 35 is provided at the upper end of the core 31 .
  • the heat exchanger 30 includes two or more heat exchanger cores 31 along the air flow direction, and the first header 34 is provided at the lower end of the heat exchanger core 31 on the most leeward side.
  • a second header 35 is provided at the upper end or lower end of the heat exchanger core 31 on the windward side, and a hot gas refrigerant inlet 32 is formed at one end of the first header 34 .
  • the heat exchanger 30 has a liquid refrigerant outlet 33 formed at one end of a second header 35 located on the same side as the heat exchanger 30 .
  • the heat exchanger 30 is provided at the upper end or the lower end of two adjacent heat exchanger cores 31, and transfers the combined refrigerant from the flat tubes 38 of the heat exchanger cores 31 on the leeward side to the heat on the windward side. It is equipped with row-connecting headers 50 that distribute to each flat tube 38 of the exchanger core 31 .
  • the line distributing the merged refrigerant from the flat tubes 38 of the heat exchanger core 31 on the leeward side to the flat tubes 38 of the heat exchanger core 31 on the windward side Since the transfer header 50 is provided and the refrigerant flow path, which is the sum of the heights of two or more heat exchanger cores 31, can be lengthened, the flow path differential pressure ⁇ P HEX can be increased. As a result, ⁇ P HEX / ⁇ P HEAD can be increased, and liquid retention is suppressed, so defrosting performance during defrosting operation can be improved.
  • each flat tube 38 of two adjacent heat exchanger cores 31 is inserted into the parallel header 50 .
  • the gap between the upper end portion or the lower end portion of the flat tube 38 and the wall portion 51 of the parallel header 50 facing the upper end portion or the lower end portion is defined as ⁇ , ⁇ 3. [mm] is satisfied.
  • the heat exchanger 30 according to Embodiment 3 is configured to satisfy ⁇ 3 [mm]. Heat exchanger performance can be improved.
  • Embodiment 4 will be described below, but descriptions of the same parts as those in Embodiments 1 to 3 will be omitted, and parts that are the same as or correspond to those in Embodiments 1 to 3 will be given the same reference numerals.
  • FIG. 20 is an enlarged refrigerant circuit diagram of the outdoor unit 10 of the air conditioner 100 including the heat exchanger 30 according to the fourth embodiment.
  • white arrows in FIG. 20 indicate the flow of the refrigerant during the defrosting operation.
  • the outdoor unit 10 of the air conditioner 100 includes a plurality of heat exchangers 30a-30c.
  • the heat exchangers 30a to 30c are any of the heat exchangers 30 described in the first to third embodiments. Further, the number of heat exchangers 30a to 30c provided in the outdoor unit 10 of the air conditioner 100 is not limited to three, and may be at least two or more.
  • the outlet side of the heat exchanger 30a and the outlet side of the heat exchanger 30b are configured to merge at a first junction portion 63a. Further, the outlet side of the first confluence portion 63a and the outlet side of the heat exchanger 30c are configured to merge at the second confluence portion 63b.
  • a first expansion device 62a is provided in the refrigerant pipe between the first merging portion 63a and the second merging portion 63b.
  • a second expansion device 62b is provided in the refrigerant pipe between the outlet of the heat exchanger 30c and the second junction 63b.
  • a first on-off valve 61a is provided in the refrigerant pipe between the branch point on the inlet side of the heat exchangers 30a to 30c and the inlet of the heat exchanger 30c.
  • a second on-off valve 61b is provided in the refrigerant pipe connecting the inlet of the heat exchanger 30c and the first junction portion 63a and the first expansion device 62a.
  • the first on-off valve 61a and the second on-off valve 61b may be valves that can adjust the degree of opening instead of valves that only open and close.
  • the first throttle device 62a and the second throttle device 62b are collectively referred to as throttle devices
  • the first on-off valve 61a and the second on-off valve 61b are collectively referred to as on-off valves.
  • the air conditioner 100 also includes a control device 70 that controls a throttle device, an on-off valve, and the like.
  • the control device 70 is, for example, dedicated hardware, or a CPU (Central Processing Unit) that executes a program stored in a storage unit (not shown). ). Note that the control device 70 may be provided in the outdoor unit 10 or may be provided in the indoor unit 20 .
  • controller 70 may be, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field-Programmable Gate Array), or a combination thereof. Applicable.
  • Each functional unit implemented by the control device 70 may be implemented by separate hardware, or each functional unit may be implemented by one piece of hardware.
  • each function executed by the control device 70 is implemented by software, firmware, or a combination of software and firmware.
  • Software and firmware are written as programs and stored in the storage unit.
  • the CPU implements each function of the control device 70 by reading and executing the programs stored in the storage unit.
  • the storage unit stores various kinds of information, and includes, for example, a rewritable non-volatile semiconductor memory such as flash memory, EPROM, and EEPROM.
  • control device 70 may be realized by dedicated hardware, and part thereof may be realized by software or firmware.
  • the control device 70 opens the second on-off valve 61b and closes the first on-off valve 61a.
  • the heat exchangers 30a to 30c are configured so that the refrigerant flows in parallel.
  • the control device 70 closes the second on-off valve 61b and opens the first on-off valve 61a.
  • the heat exchangers 30a to 30c function as evaporators, the heat exchangers 30a to 30c are configured so that the refrigerant flows in parallel, so that the flow passage cross-sectional area is large for the same refrigerant flow rate. As a result, the pressure loss is reduced, and the heating capacity can be improved.
  • the air conditioner 100 includes the outdoor unit 10 having a plurality of heat exchangers 30a to 30c, and during the defrosting operation, some of the plurality of heat exchangers 30a to 30c are other than the other.
  • a control device configured to be in series with the heat exchangers 30a to 30c, and configured so that the refrigerant flows in each of the heat exchangers 30a to 30c in parallel when the heat exchangers 30a to 30c function as evaporators. 70.
  • the air conditioner 100 According to the air conditioner 100 according to Embodiment 4, during the defrosting operation, some of the heat exchangers 30a to 30c have refrigerant flows in series with the others, and the rest have refrigerant flows in parallel. , the cross-sectional area of the flow path becomes smaller for the same refrigerant flow rate. As a result, the refrigerant flow velocity increases in the flow path where the hot gas refrigerant flows upward, and the flow path differential pressure ⁇ P HEX can be increased, thereby suppressing liquid retention and improving defrosting performance during defrosting operation.
  • the heat exchangers 30a to 30c function as evaporators, the heat exchangers 30a to 30c are configured so that the refrigerant flows in parallel, so that the flow passage cross-sectional area is large for the same refrigerant flow rate. As a result, the pressure loss is reduced, and the heating capacity can be improved.
  • Embodiment 5 will be described below, but the description of the parts overlapping those of Embodiments 1 to 4 will be omitted, and the same reference numerals will be given to parts that are the same as or correspond to those of Embodiments 1 to 4.
  • FIG. 21 is an enlarged refrigerant circuit diagram of the outdoor unit 10 of the air conditioner 100 equipped with the heat exchanger 30 according to Embodiment 5. As shown in FIG. In addition, white arrows in FIG. 21 indicate the flow of the refrigerant during the defrosting operation.
  • the outdoor unit 10 of the air conditioner 100 includes a plurality of heat exchangers 30a-30c.
  • the heat exchangers 30a to 30c are any of the heat exchangers 30 described in the first to third embodiments. Further, the number of heat exchangers 30a to 30c provided in the outdoor unit 10 of the air conditioner 100 is not limited to three, and may be at least two or more.
  • Embodiment 5 a third on-off valve 61c is provided in the refrigerant pipe between the branch point on the inlet side of the heat exchangers 30a to 30b and the inlet of the heat exchanger 30b. Since other configurations are the same as those of the refrigerant circuit 101 described in the fourth embodiment, description thereof will be omitted.
  • some of the heat exchangers 30a to 30c are in series with the others so that the flow path differential pressure ⁇ P HEX is equal to or higher than the liquid head ⁇ P HEAD , and the rest are in series with the refrigerant flow. are arranged in parallel.
  • the control device 70 opens the second on-off valve 61b and the third on-off valve 61c, and closes the first on-off valve 61a.
  • at least one of the heat exchangers 30a to 30c configured in parallel is prevented from flowing in the refrigerant, and the other heat exchanger 30a -30c are preferentially defrosted.
  • the heat exchangers 30a to 30c that perform the defrosting operation are switched by switching the throttle device or the open/close valve that is fully closed.
  • the timing for switching the throttle device or the opening/closing valve to be fully closed and switching the heat exchangers 30a to 30c for preferential defrosting operation is after a predetermined time has passed, or at the exit side of each heat exchanger 30a to 30c.
  • a temperature sensor such as a thermistor is provided, and based on the temperature detected by the temperature sensor.
  • the heat exchangers 30a to 30c function as evaporators, such as during heating operation, the heat exchangers 30a to 30c are configured so that the refrigerant flows in parallel.
  • the control device 70 closes the second opening/closing valve 61b and opens the first opening/closing valve 61a and the third opening/closing valve 61c.
  • some of the heat exchangers 30a to 30c are configured such that the refrigerant flows in series with the others, and the refrigerant flows in the remaining heat exchangers in parallel.
  • the cross-sectional area of the passage becomes smaller for the same refrigerant flow rate, so the refrigerant flow velocity in the passage where the hot gas refrigerant flows upward increases, and the passage differential pressure ⁇ P HEX can be increased.
  • at least one of the heat exchangers 30a to 30c configured so that the refrigerant flows in parallel is preferentially defrosted, and then the heat exchangers 30a to 30c that are preferentially defrosted. By switching 30c in order, residual frost can be reduced.
  • the heat exchangers 30a to 30c function as evaporators, the heat exchangers 30a to 30c are configured so that the refrigerant flows in parallel, so that the flow passage cross-sectional area is large for the same refrigerant flow rate. As a result, the pressure loss is reduced, and the heating capacity can be improved.
  • the control device 70 causes some of the plurality of heat exchangers 30a to 30c to flow the refrigerant from the other heat exchangers 30a to 30c during the defrosting operation.
  • the heat exchangers 30a to 30c are configured to be in series and the rest are configured so that the refrigerant flows in parallel, and are configured so that the refrigerant flows in parallel during the defrosting operation. If there are a plurality of heat exchangers, at least one of them is prevented from flowing in refrigerant, and the other heat exchangers 30a to 30c are preferentially defrosted.
  • At least one of the heat exchangers 30a to 30c configured so that the refrigerant flows in parallel is preferentially defrosted, and then, By sequentially switching the heat exchangers 30a to 30c that preferentially perform defrosting operation, residual frost can be reduced. Therefore, liquid retention is further suppressed, and the defrosting performance during the defrosting operation can be further improved.
  • Embodiment 6 will be described below, but the description of the parts overlapping those of Embodiments 1 to 5 will be omitted, and the same reference numerals will be given to parts that are the same as or correspond to those of Embodiments 1 to 5.
  • FIG. 22 is a schematic cross-sectional view of the flat tube 38 of the heat exchanger 30 according to Embodiment 6.
  • FIG. FIG. 23 is a schematic cross-sectional view of a flattened tube 38 of a modified example of the heat exchanger 30 according to the sixth embodiment.
  • FIG. 24 is a schematic side view of a flattened tube 38 of a modified example of the heat exchanger 30 according to the sixth embodiment.
  • the flat tubes 38 of the heat exchanger 30 are internally provided with a plurality of partition columns 38a. These partition columns 38a are arranged along the longitudinal direction of the cross section of the flat tube 38, and extend along the longitudinal direction of the flat tube 38 to partition the interior of the flat tube 38 into a plurality of spaces. Furthermore, it is a grooved flat tube provided with a plurality of inwardly protruding protrusions 38b between adjacent partition posts 38a. This convex portion 38 b extends along the longitudinal direction of the flat tube 38 .
  • the flattened tube 38 of the heat exchanger 30 is flattened at the tip end portion 38c of which the outer diameter is reduced toward the tip end portion 38c. is a tube.
  • the flat tube 38 of the heat exchanger 30 is a flat tube with a groove or a flat tube with a constricted tip.
  • the cross-sectional area of the passage becomes smaller for the same refrigerant flow rate, so the refrigerant flow velocity in the passage where the hot gas refrigerant flows upward increases, and the passage differential pressure ⁇ P HEX can be increased. Therefore, liquid retention is suppressed, and the defrosting performance during the defrosting operation can be improved.
  • the flat tubes 38 are provided with a plurality of partitioning pillars 38a that partition the internal flow paths.
  • the flat tube 38 is provided with an inwardly protruding convex portion 38b, or the flat tube 38 has a front end portion 38c that is subjected to tube shrinkage so that the outer diameter is reduced toward the front end.
  • the flat tube 38 has a plurality of projections 38b formed along the flow path between the adjacent partition posts 38a, or the flat tube 38 has a distal end
  • the portion 38c is subjected to a shrinking process so that the outer diameter is reduced toward the tip.
  • the flat tube 38 by making the flat tube 38 a flat tube with a groove or a flat tube with a constricted tip, the cross-sectional area of the flow path becomes smaller for the same flow rate of the refrigerant.
  • Refrigerant flow velocity increases and the flow path differential pressure ⁇ P HEX can be increased.
  • liquid retention is suppressed, and defrosting performance during defrosting operation can be improved.
  • Embodiment 7 will be described below, but descriptions of the same parts as in Embodiments 1 to 6 will be omitted, and the same reference numerals will be given to parts that are the same as or correspond to those in Embodiments 1 to 6.
  • FIG. 25 is a diagram showing the relationship between the type of refrigerant used in the refrigerant circuit 101 of the air conditioner 100 according to Embodiment 7 and ⁇ P HEX / ⁇ P HEAD .
  • any pure refrigerant of HFO1123, HFO1132 (E), R1234yf, R1234ze (E), R1234ze (Z), R1233zd (E), propane (R290), and fluoroethane (R161) , R32 and R410A, ⁇ P HEX / ⁇ P HEAD is improved.
  • HFO1123, HFO1132 (E), R1234yf, R1234ze (E), R1234ze (Z), R1233zd (E), and propane (R290) are used as refrigerants circulating in the refrigerant circuit 101 of the air conditioner 100.
  • fluoroethane (R161) is used as refrigerants circulating in the refrigerant circuit 101 of the air conditioner 100.
  • the refrigerants are HFO1123, HFO1132 (E), R1234yf, R1234ze (E), R1234ze (Z), R1233zd (E), propane (R290), and fluoroethane.
  • R161 is any pure refrigerant.
  • the above pure refrigerant is used as the refrigerant circulating in the refrigerant circuit 101, so that ⁇ P HEX / ⁇ P HEAD can be improved. Therefore, it is possible to suppress the occurrence of liquid stagnation and improve the heat exchanger performance.
  • Embodiment 8 An eighth embodiment will be described below, but descriptions of the same parts as in the first to seventh embodiments will be omitted, and the same reference numerals will be given to parts that are the same as or correspond to those in the first to eighth embodiments.
  • 26 is a front view of heat exchanger 30 of air conditioner 100 according to Embodiment 2.
  • FIG. The white arrows in FIG. 26 indicate the flow of refrigerant during cooling operation.
  • 26 also shows the height H and width L of the heat exchanger core 31, and the widths of the regions of the heat exchanger core 31 are indicated as L1 , L2, . . . from the downstream side.
  • the heat exchanger 30 functions as a condenser that radiates the heat of the refrigerant to the outdoor air and condenses the refrigerant during the cooling operation.
  • the heat exchanger 30 comprises a heat exchanger core 31 having a plurality of flattened tubes 38 and a plurality of fins 39 .
  • the flat tubes 38 are arranged side by side in the horizontal direction (horizontal direction in FIG. 26) at intervals so that the wind generated by the fan 13 flows, and are arranged vertically (up and down direction in FIG. 26) in the tubes extending vertically. Refrigerant flows in the direction of
  • the fins 39 are connected between adjacent flat tubes 38 to transfer heat to the flat tubes 38 .
  • the fins 39 improve heat exchange efficiency between air and refrigerant, and corrugated fins are used, for example. However, it is not limited to this. Since heat exchange between the air and the refrigerant takes place on the surface of the flat tube 38, the fins 39 may be omitted.
  • a first header 34 is provided at the lower end of the heat exchanger core 31 .
  • the lower ends of the flat tubes 38 of the heat exchanger core 31 are directly inserted into the first header 34 .
  • a second header 35 is provided at the upper end of the heat exchanger core 31 .
  • the upper ends of the flat tubes 38 of the heat exchanger core 31 are directly inserted into the second headers 35 .
  • a hot gas refrigerant inlet 32 is formed at one end of the second header 35 , and the hot gas refrigerant inlet 32 is connected to the refrigerant circuit 101 of the air conditioner 100 via a gas pipe 37 .
  • a liquid refrigerant outlet 33 is formed at the other end of the second header 35 , and the liquid refrigerant outlet 33 is connected to the refrigerant circuit 101 of the air conditioner 100 via a liquid pipe 36 .
  • the second header 35 allows the high-temperature, high-pressure gas refrigerant from the compressor 11 to flow into the heat exchanger 30 during cooling operation, and the low-temperature, high-pressure liquid refrigerant after heat exchange in the heat exchanger 30 flows out to the refrigerant circuit 101.
  • the second header 35 allows the low-temperature, low-pressure two-phase refrigerant to flow into the heat exchanger 30 during heating operation, and causes the low-temperature, low-pressure gas refrigerant after heat exchange in the heat exchanger 30 to flow out to the refrigerant circuit 101 .
  • the plurality of flat tubes 38, the plurality of fins 39, the first header 34, and the second header 35 are all made of aluminum and joined by brazing.
  • the second header 35 is provided with the partition plate 40 .
  • the partition plate 40 is provided to horizontally partition the flow path of the heat exchanger core 31 into a plurality of regions. Moreover, the partition plate 40 is provided so that the flow path in each region of the heat exchanger core 31 is counter-current to the flow path in the adjacent region. In the eighth embodiment, the partition plate 40 partitions the flow path of the heat exchanger core 31 into two regions T 1 and T 2 . Further, the confluence area M1 of the hot gas refrigerant is formed in the first header 34 by providing the partition plate 40 in the second header 35 .
  • the hot gas refrigerant that has flowed into the second header 35 flows downward through the flat tubes 38 of the heat exchanger core 31 arranged in the region T1 , and then merges in the confluence region M1 of the first header 34. , and flows upward through the flat tubes 38 of the heat exchanger core 31 arranged in the region T2 , and then flows out from the second header 35.
  • region T1 is the downflow region
  • region T2 is the upflow region.
  • the confluence area M1 of the first header 34 serves as a hot gas refrigerant inflow part for the upward flow area.
  • the heat exchanger 30 By configuring the heat exchanger 30 in this way, the refrigerant flowing from the hot gas refrigerant inlet 32 formed in the upper part of the heat exchanger 30 flows upward in the region T2 and flows into the flat tubes 38 of the heat exchanger core 31. It is possible to suppress the occurrence of liquid retention in which the liquefied refrigerant cannot rise due to the influence of gravity and stays when flowing, and the deterioration of the defrosting performance can be suppressed. Further, by providing the partition plate 40 in the second header 35, the cross-sectional area of the flow path is reduced for the same flow rate of the refrigerant. Liquid retention is suppressed, and defrosting performance during defrosting operation can be improved.
  • Embodiment 9 The ninth embodiment will be described below, but the description of the parts that overlap with the first to eighth embodiments will be omitted, and the same reference numerals will be given to the same or corresponding parts as those of the first to eighth embodiments.
  • FIG. 27 is a front view of heat exchanger 30 of air conditioner 100 according to Embodiment 9.
  • FIG. The white arrows in FIG. 27 indicate the flow of refrigerant during cooling operation.
  • 27 also shows the height H and width L of the heat exchanger core 31, and the widths of the regions of the heat exchanger core 31 are indicated as L 1 , L 2 . . . from the downstream side.
  • the heat exchanger 30 functions as a condenser that radiates the heat of the refrigerant to the outdoor air to condense the refrigerant during the cooling operation.
  • the heat exchanger 30 comprises a heat exchanger core 31 having a plurality of flattened tubes 38 and a plurality of fins 39 .
  • the flat tubes 38 are arranged side by side in the horizontal direction (horizontal direction in FIG. 27) at intervals so that the wind generated by the fan 13 flows, and are arranged vertically in the vertical direction (up and down direction in FIG. 27). Refrigerant flows in the direction of
  • the fins 39 are connected between adjacent flat tubes 38 to transfer heat to the flat tubes 38 .
  • the fins 39 improve heat exchange efficiency between air and refrigerant, and corrugated fins are used, for example. However, it is not limited to this. Since heat exchange between the air and the refrigerant takes place on the surface of the flat tube 38, the fins 39 may be omitted.
  • a first header 34 is provided at the lower end of the heat exchanger core 31 .
  • the lower ends of the flat tubes 38 of the heat exchanger core 31 are directly inserted into the first header 34 .
  • a second header 35 is provided at the upper end of the heat exchanger core 31 .
  • the upper ends of the flat tubes 38 of the heat exchanger core 31 are directly inserted into the second headers 35 .
  • a hot gas refrigerant inlet 32 is formed at one end of the second header 35 , and the hot gas refrigerant inlet 32 is connected to the refrigerant circuit 101 of the air conditioner 100 via a gas pipe 37 .
  • the second header 35 allows the high-temperature, high-pressure gas refrigerant from the compressor 11 to flow into the heat exchanger 30 during cooling operation, and the low-temperature, low-pressure gas refrigerant after heat exchange in the heat exchanger 30 during heating operation into the refrigerant circuit. Drain to 101.
  • a liquid refrigerant outlet 33 is formed at one end of the first header 34 located on the opposite side of one end of the second header 35 , and the liquid refrigerant outlet 33 passes through a liquid pipe 36 to the refrigerant of the air conditioner 100 . It is connected with circuit 101 .
  • the first header 34 allows a low-temperature, low-pressure two-phase refrigerant to flow into the heat exchanger 30 during heating operation, and causes a low-temperature, high-pressure liquid refrigerant after heat exchange in the heat exchanger 30 to flow out to the refrigerant circuit 101 during cooling operation. .
  • the plurality of flat tubes 38, the plurality of fins 39, the first header 34, and the second header 35 are all made of aluminum and joined by brazing.
  • partition plates 40 are provided in the first header 34 and the second header 35, respectively.
  • the partition plate 40 is provided to horizontally partition the flow path of the heat exchanger core 31 into a plurality of regions. Moreover, the partition plate 40 is provided so that the flow path in each region of the heat exchanger core 31 is counter-current to the flow path in the adjacent region.
  • two partition plates 40 partition the flow path of heat exchanger core 31 into three regions T 1 , T 2 , and T 3 .
  • the partition plate 40 by providing the partition plate 40 in the first header 34 and the second header 35, respectively, the confluence areas M1 and M2 of the hot gas refrigerant are formed in the first header 34 and the second header 35, respectively.
  • the hot gas refrigerant that has flowed into the second header 35 flows downward through the flat tubes 38 of the heat exchanger core 31 arranged in the region T1 , and then merges in the confluence region M1 of the first header 34. , and flows upward through the flattened tubes 38 of the heat exchanger core 31 located in the region T2 . After that, the hot gas refrigerant merges in the confluence region M2 of the second header 35, flows downward through the flat tubes 38 of the heat exchanger core 31 disposed in the region T3 , and then flows out of the first header 34. It is designed to That is, regions T1 and T3 are downflow regions, and region T2 is an upflow region. Also, the confluence area M1 of the first header 34 serves as a hot gas refrigerant inflow part for the upward flow area.
  • the heat exchanger 30 By configuring the heat exchanger 30 in this way, the refrigerant flowing from the hot gas refrigerant inlet 32 formed in the upper part of the heat exchanger 30 flows upward in the region T2 and flows into the flat tubes 38 of the heat exchanger core 31. It is possible to suppress the occurrence of liquid retention in which the liquefied refrigerant cannot rise due to the influence of gravity and stays when flowing, and the deterioration of the defrosting performance can be suppressed.
  • the partition plate 40 in each of the first header 34 and the second header 35 the cross-sectional area of the flow path becomes smaller for the same flow rate of the refrigerant, so the flow velocity of the refrigerant increases and the differential pressure ⁇ P HEX of the flow path increases. Therefore, liquid retention is suppressed, and defrosting performance during defrosting operation can be improved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2021/020313 2021-05-28 2021-05-28 熱交換器、熱交換器を備えた空気調和装置の室外機、および、空気調和装置の室外機を備えた空気調和装置 Ceased WO2022249425A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP21943071.7A EP4350252A4 (en) 2021-05-28 2021-05-28 HEAT EXCHANGER, OUTDOOR UNIT OF AN AIR CONDITIONER WITH THE HEAT EXCHANGER AND AIR CONDITIONER WITH THE OUTDOOR UNIT OF AN AIR CONDITIONER
US18/557,331 US20240219067A1 (en) 2021-05-28 2021-05-28 Heat exchanger, air-conditioning apparatus outdoor unit including heat exchanger, and air-conditioning apparatus including air-conditioning apparatus outdoor unit
CN202180098566.0A CN117355721A (zh) 2021-05-28 2021-05-28 热交换器、具备热交换器的空调装置的室外机、以及具备空调装置的室外机的空调装置
PCT/JP2021/020313 WO2022249425A1 (ja) 2021-05-28 2021-05-28 熱交換器、熱交換器を備えた空気調和装置の室外機、および、空気調和装置の室外機を備えた空気調和装置
JP2023523891A JPWO2022249425A1 (https=) 2021-05-28 2021-05-28

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2021/020313 WO2022249425A1 (ja) 2021-05-28 2021-05-28 熱交換器、熱交換器を備えた空気調和装置の室外機、および、空気調和装置の室外機を備えた空気調和装置

Publications (1)

Publication Number Publication Date
WO2022249425A1 true WO2022249425A1 (ja) 2022-12-01

Family

ID=84228514

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2021/020313 Ceased WO2022249425A1 (ja) 2021-05-28 2021-05-28 熱交換器、熱交換器を備えた空気調和装置の室外機、および、空気調和装置の室外機を備えた空気調和装置

Country Status (5)

Country Link
US (1) US20240219067A1 (https=)
EP (1) EP4350252A4 (https=)
JP (1) JPWO2022249425A1 (https=)
CN (1) CN117355721A (https=)
WO (1) WO2022249425A1 (https=)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2025253428A1 (ja) * 2024-06-03 2025-12-11 三菱電機株式会社 熱交換器、冷凍サイクル装置の室外機、および冷凍サイクル装置
JP7851511B1 (ja) 2024-06-03 2026-04-24 三菱電機株式会社 熱交換器、冷凍サイクル装置の室外機、および冷凍サイクル装置

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5837465A (ja) * 1981-08-31 1983-03-04 株式会社デンソー 冷媒蒸発器
JPH10220919A (ja) * 1997-02-07 1998-08-21 Calsonic Corp コンデンサ
JP2006183962A (ja) * 2004-12-28 2006-07-13 Denso Corp 蒸発器
JP2008267686A (ja) * 2007-04-19 2008-11-06 Denso Corp 冷媒蒸発器
JP2013174398A (ja) * 2012-02-27 2013-09-05 Japan Climate Systems Corp 熱交換器
WO2016092943A1 (ja) * 2014-12-12 2016-06-16 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン） リミテッド 空気調和機
JP2018096638A (ja) 2016-12-15 2018-06-21 日野自動車株式会社 凝縮器
WO2021079422A1 (ja) * 2019-10-23 2021-04-29 三菱電機株式会社 熱交換器及び冷凍サイクル装置

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5971083U (ja) * 1982-10-27 1984-05-14 昭和アルミニウム株式会社 熱交換器用管
JP2837396B2 (ja) * 1996-10-08 1998-12-16 シャープ株式会社 熱交換器
JP2002130983A (ja) * 2000-10-26 2002-05-09 Toyo Radiator Co Ltd 微細多穴を有する熱交換器用の押出チューブおよび熱交換器
JP2003121019A (ja) * 2001-10-12 2003-04-23 Sharp Corp 空気調和機
US20030075307A1 (en) * 2001-10-22 2003-04-24 Heatcraft, Inc. Exchanger of thermal energy with multiple cores and a thermal barrier
JP3903866B2 (ja) * 2002-07-19 2007-04-11 株式会社デンソー 冷却器
JP4574321B2 (ja) * 2003-10-29 2010-11-04 昭和電工株式会社 熱交換器
JP4193741B2 (ja) * 2004-03-30 2008-12-10 株式会社デンソー 冷媒蒸発器
JP5029001B2 (ja) * 2006-12-25 2012-09-19 ダイキン工業株式会社 空気調和装置
JP2009024899A (ja) * 2007-07-17 2009-02-05 Showa Denko Kk エバポレータ
JP5920175B2 (ja) * 2012-11-13 2016-05-18 株式会社デンソー 熱交換器
JP6069080B2 (ja) * 2013-04-23 2017-01-25 株式会社ケーヒン・サーマル・テクノロジー エバポレータおよびこれを用いた車両用空調装置
JP6384723B2 (ja) * 2014-08-20 2018-09-05 日本軽金属株式会社 フィン・アンド・チューブ型熱交換器の製造方法
DE112017001354T5 (de) * 2016-03-16 2018-11-29 Mitsubishi Electric Corporation Lamellenfreier wärmetauscher, aussenraumeinheit einer klimaanlagenvorrichtung, die den lamellenfreien wärmetauscher aufweist, und innenraumeinheit einer klimaanlagenvorrichtung, die den lamellenfreien wärmetauscher aufweist
EP3805651B1 (en) * 2018-06-11 2023-11-22 Mitsubishi Electric Corporation Air conditioner outdoor unit and air conditioner
JP6925393B2 (ja) * 2018-06-11 2021-08-25 三菱電機株式会社 空気調和装置の室外機及び空気調和装置
EP4155626B1 (en) * 2020-05-22 2025-09-03 Mitsubishi Electric Corporation Heat exchanger, outdoor unit equipped with heat exchanger, and air conditioner equipped with outdoor unit

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5837465A (ja) * 1981-08-31 1983-03-04 株式会社デンソー 冷媒蒸発器
JPH10220919A (ja) * 1997-02-07 1998-08-21 Calsonic Corp コンデンサ
JP2006183962A (ja) * 2004-12-28 2006-07-13 Denso Corp 蒸発器
JP2008267686A (ja) * 2007-04-19 2008-11-06 Denso Corp 冷媒蒸発器
JP2013174398A (ja) * 2012-02-27 2013-09-05 Japan Climate Systems Corp 熱交換器
WO2016092943A1 (ja) * 2014-12-12 2016-06-16 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン） リミテッド 空気調和機
JP2018096638A (ja) 2016-12-15 2018-06-21 日野自動車株式会社 凝縮器
WO2021079422A1 (ja) * 2019-10-23 2021-04-29 三菱電機株式会社 熱交換器及び冷凍サイクル装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP4350252A4

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2025253428A1 (ja) * 2024-06-03 2025-12-11 三菱電機株式会社 熱交換器、冷凍サイクル装置の室外機、および冷凍サイクル装置
JP7851511B1 (ja) 2024-06-03 2026-04-24 三菱電機株式会社 熱交換器、冷凍サイクル装置の室外機、および冷凍サイクル装置

Also Published As

Publication number Publication date
EP4350252A4 (en) 2024-08-21
JPWO2022249425A1 (https=) 2022-12-01
CN117355721A (zh) 2024-01-05
US20240219067A1 (en) 2024-07-04
EP4350252A1 (en) 2024-04-10

Similar Documents

Publication Publication Date Title
CN112204312B (zh) 空气调节装置的室外机及空气调节装置
JP6044238B2 (ja) 空気調和機
JP6590948B2 (ja) 熱交換器および冷凍サイクル装置
JP7317231B2 (ja) 熱交換器、熱交換器を備えた室外機、および、室外機を備えた空気調和装置
EP3156752B1 (en) Heat exchanger
JPWO2018078800A1 (ja) 熱交換器及び冷凍サイクル装置
JP6584636B2 (ja) 熱交換器および空気調和機
JP7682374B2 (ja) 冷凍サイクル装置
JP6925393B2 (ja) 空気調和装置の室外機及び空気調和装置
JP6524670B2 (ja) 空気調和装置
JP6964803B2 (ja) 空気調和機
WO2022249425A1 (ja) 熱交換器、熱交換器を備えた空気調和装置の室外機、および、空気調和装置の室外機を備えた空気調和装置
JP5447438B2 (ja) 冷蔵庫
JP7414845B2 (ja) 冷凍サイクル装置
JP6102724B2 (ja) 熱交換器
WO2022255358A1 (ja) 空気調和装置
CN104136876A (zh) 并流式热交换器和安装有该并流式热交换器的空气调节机
JP2022115322A (ja) 空気調和機及び熱交換器
JP5267614B2 (ja) 冷蔵庫
JP2018048766A (ja) パラレルフロー熱交換器、及び冷凍サイクル装置
JP6910436B2 (ja) 室外ユニットおよび冷凍サイクル装置
JP7851511B1 (ja) 熱交換器、冷凍サイクル装置の室外機、および冷凍サイクル装置
JP6990795B1 (ja) 室内機及び室外機
JP4989756B2 (ja) 冷蔵庫
WO2025253428A1 (ja) 熱交換器、冷凍サイクル装置の室外機、および冷凍サイクル装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 21943071

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2023523891

Country of ref document: JP

WWE Wipo information: entry into national phase

Ref document number: 18557331

Country of ref document: US

WWE Wipo information: entry into national phase

Ref document number: 202180098566.0

Country of ref document: CN

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 2021943071

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 2021943071

Country of ref document: EP

Effective date: 20240102

WWW Wipo information: withdrawn in national office

Ref document number: 2021943071

Country of ref document: EP