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WO2015046275A1 - Échangeur thermique et appareil de climatisation utilisant cet échangeur thermique - Google Patents

Échangeur thermique et appareil de climatisation utilisant cet échangeur thermique Download PDF

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Publication number
WO2015046275A1
WO2015046275A1 PCT/JP2014/075328 JP2014075328W WO2015046275A1 WO 2015046275 A1 WO2015046275 A1 WO 2015046275A1 JP 2014075328 W JP2014075328 W JP 2014075328W WO 2015046275 A1 WO2015046275 A1 WO 2015046275A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
heat
refrigerant
row
partition plate
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/JP2014/075328
Other languages
English (en)
Japanese (ja)
Inventor
石橋　晃
真哉 東井上
伊東　大輔
拓未 西山
繁佳 松井
裕樹 宇賀神
岡崎　多佳志
厚志 望月
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 JP2015539281A priority Critical patent/JP6120978B2/ja
Priority to EP14847978.5A priority patent/EP3051244B1/fr
Publication of WO2015046275A1 publication Critical patent/WO2015046275A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0015—Heat and mass exchangers, e.g. with permeable walls

Definitions

  • the present invention relates to a heat exchanger having a plurality of rows of heat transfer tubes through which refrigerant flows in the flow direction of a heat exchange fluid (for example, air).
  • a heat exchange fluid for example, air
  • FIG. 8 is a cross-sectional view showing a row transfer portion 5 through which a refrigerant flows between rows of heat transfer tubes in the internal structure of the header 4 of the conventional heat exchanger as described above.
  • FIG. 8A shows the case where the cross-sectional shape of the connecting portion 5 is rectangular
  • FIG. 8B shows the flow 3 of the liquid refrigerant when the cross-sectional shape of the connecting portion 5 is a substantially parallelogram.
  • a gas-liquid two-phase refrigerant having a dryness of about 0.5 flows out from the air flat porous tube 2 on the windward side of the air as the heat exchange fluid, and the refrigerant flow 3 flows to the porous flat tube 2 in the leeward row.
  • the present invention has been made to solve the above-described problems.
  • An object of the present invention is to obtain a heat exchanger in which the inflowing liquid refrigerant has a uniform flow rate distribution in the heat transfer tube or an appropriate flow rate distribution with respect to the heat load, and the heat exchanger performance is good.
  • the heat exchanger according to the present invention includes a heat transfer tube in which a plurality of rows are arranged in a row direction that is a passing direction of a heat exchange medium and the heat medium flows in an internal flow path, and a pair of heat transfer tubes that are arranged adjacent to each other in the row direction.
  • a heat exchanger having a transfer section as a heat medium flow path connecting a heat pipe and a header to which a heat transfer pipe is connected, the transfer section is provided in the header, and in the transfer section The refrigerant partition plate standing on the heat medium flow path is provided.
  • the heat exchanger according to the present invention, by providing the refrigerant partition plate that guides the heat medium flowing in the transfer section, the liquid refrigerant flowing into the heat transfer tubes after the transfer section is uniform in the heat transfer tubes. It becomes possible to obtain a heat exchanger that has a flow rate distribution or a flow rate distribution that is appropriate for the heat load and that has good heat exchanger performance.
  • FIG. 2 is a partial front view of the heat exchanger according to Embodiment 1.
  • FIG. 2 is a cross-sectional view of a porous flat tube portion of a heat exchanger according to Embodiment 1.
  • FIG. It is sectional drawing of the line transfer part 5 in case the heat exchanger which concerns on Embodiment 1 is used as an evaporator. It is sectional drawing of the line transfer part 5 in case the heat exchanger which concerns on Embodiment 1 is used as a condenser. It is sectional drawing of the line transfer part 5 in case the heat exchanger based on Embodiment 2 is used as an evaporator. It is sectional drawing of the line transfer part 5 in case the heat exchanger which concerns on Embodiment 2 is used as a condenser. It is a refrigerant circuit diagram of the air-conditioning conditioner using the heat exchanger which concerns on Embodiment 1,2. It is sectional drawing of the line transfer part 5 of the conventional heat exchanger.
  • FIG. 1 An outline of the structure of the heat exchanger according to the first embodiment will be described with reference to FIGS. 1 is a partial front view of a heat exchanger according to Embodiment 1.
  • FIG. FIG. 2 is a cross-sectional view of the flat tube portion of the heat exchanger according to the first embodiment.
  • the heat exchanger according to the first embodiment is a fin tube type heat exchanger as shown in FIGS.
  • the heat exchanger tubes of the heat exchanger are arranged in the horizontal direction, and the fins 1 are arranged in the vertical direction.
  • a header 4 is connected to one end of the heat transfer tube.
  • the header 4 is arranged so that its axial direction is parallel to the direction of gravity.
  • the heat transfer tube is a porous flat tube 2 in which a large number of refrigerant flow paths are arranged in parallel, and is arranged in two rows in the flow direction of air that is a heat exchange fluid.
  • the two rows of porous flat tubes 2 are arranged in a staggered manner in a sectional view as shown in FIG.
  • the refrigerant flows inside the porous flat tube 2, and fins 1 are provided at right angles to the axial direction of the porous flat tube 2.
  • the porous flat tube 2 and the fin 1 are made of a metal having high heat conductivity such as copper or aluminum, and brazed or soldered with the porous flat tube 2 inserted into the heat transfer tube insertion portion cut out in the fin 1. They are joined by a welding method or the like to transfer heat to each other.
  • the fin 1 includes a first fin 1a disposed on the windward side in the flow direction of air that is a heat exchange fluid and a second fin 1b disposed on the leeward side.
  • One pass of the porous flat tube 2 is configured with four porous flat tubes 2a, 2b, 2c, and 2d as one unit.
  • the porous flat tubes 2a and 2b penetrate the first fins 1a arranged on the windward side in the air flow direction to form a first row.
  • the porous flat tubes 2c and 2d penetrate the second fins 1b arranged on the leeward side in the air flow direction to form a second row.
  • the porous flat tubes 2a and 2b are arranged in a plurality of stages on the first fin 1a and stacked in the axial direction of the header 4, and the porous flat tubes 2c and 2d are arranged in a plurality of stages on the second fin 1b and the header. 4 are stacked in the axial direction.
  • the header 4 has a hollow structure having a substantially rectangular cross section, and has a coolant channel inside.
  • the refrigerant flow path is formed as a row transfer portion 5 that connects the porous flat tubes 2b and 2c in the row direction.
  • the liquid refrigerant flows from one end of the porous flat tube 2a, which is the first row on the windward side, as indicated by the arrows in the refrigerant flow 3 described in FIGS. From the other end of the porous flat tube 2a, it moves between the stages through the U-shaped bend 9, and flows into one end of the porous flat tube 2b.
  • the other end of the porous flat tube 2b is connected to the header 4, and the refrigerant flowing out of the porous flat tube 2b moves between the rows through the row-passing portion 5 of the header 4, and the second flat porous tube 2c Flows into one end.
  • the refrigerant flowing into one end portion of the porous flat tube 2c moves from the other end portion of the porous flat tube 2c through the U-shaped bend 9 and flows into one end portion of the porous flat tube 2d. Then, it flows out from the other end of the porous flat tube 2d.
  • the gas refrigerant flows in from the other end of the second row of porous flat tubes 2d and follows the flow path opposite to that in the case of the evaporator. It flows out from one end of the porous flat tube 2a.
  • a plurality of stages of 1-unit paths formed in this way are stacked in the axial direction of the header 4 to constitute a heat exchanger.
  • FIG. 3 is a cross-sectional view of the line transfer portion 5 when the heat exchanger according to Embodiment 1 is used as an evaporator.
  • the line passing portion 5 is formed inside the header 4 as a hollow portion having a substantially rectangular parallelepiped shape.
  • a porous flat tube 2 b and a porous flat tube 2 c are connected to the connecting portion 5 and open, and the gas-liquid two-phase refrigerant flowing out from the first flat porous tube 2 b passes through the connecting portion 5. Then, it moves between the rows of the porous flat tubes 2b, 2c, and flows into one end of the porous flat tubes 2c in the second row.
  • the positional relationship between the porous flat tube 2b and the porous flat tube 2c is such that the second flat flat tube 2c is displaced in the axial direction of the header 4 with respect to the first flat flat tube 2b as shown in FIG. Are arranged.
  • a refrigerant partition plate 7 is provided between the porous flat tube 2b and the porous flat tube 2c in the axial direction of the header 4 to partition the inside of the connecting portion 5 in the horizontal direction.
  • the refrigerant partition plate 7 is attached and supported across the two sides of the side wall of the connecting portion 5 where the porous flat tube 2b and the porous flat tube 2c are open and the side wall facing the side wall. And the refrigerant
  • the 1st opening part 7a is formed in the lower part of the porous flat tube 2b, and a porous flat tube
  • the second opening 7b is formed in the upper part of 2c.
  • the refrigerant partition plate 7 configured in this way obstructs the shortest route in which the gas-liquid two-phase refrigerant flowing out from the first row of porous flat tubes 2b flows into one end portion of the second row of flat porous tubes 2c.
  • the flow path is divided into two. Then, the liquid refrigerant 6 in the gas-liquid two-phase refrigerant flows into the porous flat tube 2c from the two flow paths in the flow direction of the heat exchange fluid in the circulation portion 5;
  • the liquid refrigerant 6 is uniformly supplied to the refrigerant flow path of the pipe 2c. Therefore, sufficient liquid refrigerant 6 flows evenly into each refrigerant flow path of the porous flat tube 2c and evaporates, thereby improving the heat exchange performance as an evaporator.
  • the refrigerant partition plate 7 is a plate-like one, but any refrigerant flow resistance may be used.
  • the refrigerant divider plate 7 may be formed on a fine mesh plate or the side wall of the connecting portion 5. It may be a protrusion.
  • the refrigerant partition plate 7 may be formed integrally with the header 4 or may be attached as a separate body.
  • the material is preferably formed of the same material as the header 4, and examples thereof include a copper plate, an aluminum plate, and a resin plate.
  • FIG. 4 is a cross-sectional view of the line transfer portion 5 when the heat exchanger according to Embodiment 1 is used as a condenser.
  • the heat exchanger functions as a condenser
  • the flow direction of the refrigerant flowing through the porous flat tube 2 of the heat exchanger is opposite to the evaporator.
  • the refrigerant partition plate 7 obstructs the shortest route in which the refrigerant flowing out from the second row of flat flat tubes 2c flows into one end of the first row of flat flat tubes 2b, and divides the refrigerant flow path into two.
  • the liquid refrigerant 6 flows into the porous flat tube 2b from the two flow paths on the windward side and the leeward side in the flow direction of the heat exchange fluid in the connecting section 5, and is evenly supplied to the refrigerant flow path of the porous flat tube 2b. Gas refrigerant and liquid refrigerant 6 are supplied. As a result, the gas refrigerant and the liquid refrigerant 6 uniformly flow into the refrigerant flow paths of the porous flat tube 2b and the gas refrigerant condenses. Exchange performance is improved.
  • FIG. 5 is a cross-sectional view of the line transfer portion 5 when the heat exchanger is used as an evaporator according to the second embodiment.
  • the line passing portion 5 is formed in the header 4 as a hollow portion having a substantially parallelogram-shaped cross section.
  • a porous flat tube 2b and a porous flat tube 2c are connected to the connecting portion 5 and open, and the gas-liquid two-phase refrigerant that has flowed out of the first flat porous tube 2b. Moves between the rows of the porous flat tubes 2b and 2c through the row passing portion 5 and flows into one end of the second row of porous flat tubes 2c.
  • the positional relationship between the porous flat tube 2b and the porous flat tube 2c is such that, as shown in FIG. 5, the first flat porous tube 2b is provided near the upper side of the connecting portion 5, and the second flat porous tube. 2c is provided in the vicinity of the lower side of the column passing portion 5.
  • a first refrigerant partition plate 8a and a second refrigerant partition plate 8b that partition the inside of the connecting portion 5 in the horizontal direction are installed around the porous flat tube 2b and the porous flat tube 2c.
  • the first refrigerant partition plate 8a and the second refrigerant partition plate 8b are provided on two surfaces of the side wall of the connecting portion 5 where the porous flat tube 2b and the porous flat tube 2c are opened, and the side wall facing the side wall. It is mounted and supported across.
  • the first refrigerant partition plate 8a is provided so as to surround the porous flat tube 2b, and has a first opening 8c that opens downward on the windward side in the flow direction of the heat exchange fluid in the line transfer portion 5.
  • the second refrigerant partition plate 8b is provided so as to surround the porous flat tube 2c, and has a second opening 8d that opens upward on the leeward side in the flow direction of the heat exchange fluid in the connecting portion 5.
  • the gas-liquid two-phase refrigerant flowing out of the first row of porous flat tubes 2b flows into one end of the second row of porous flat tubes 2c.
  • the flow path of the refrigerant flow 3 in the line transfer portion 5 is formed in an S shape.
  • the liquid refrigerant 6 in the gas-liquid two-phase refrigerant flowing out of the porous flat tube 2b flows into the periphery of the porous flat tube 2c from the second opening 8d of the second refrigerant partition plate 8b, and the second refrigerant partition plate 8b.
  • a liquid pool is formed by concentrating on the windward side in the flow direction of the heat exchange fluid, which is the deepest part of the heat exchanger.
  • a heat load is higher on the windward side of the porous flat tube 2c, and the performance of the heat exchanger is improved when more liquid refrigerant is supplied. Therefore, with the configuration of the heat exchanger described above, the amount of liquid refrigerant on the windward side of the porous flat tube 2c is relatively larger than that on the leeward side, and the heat exchanger performance can be improved.
  • FIG. 6 is a cross-sectional view of the line transfer portion 5 when the heat exchanger according to Embodiment 2 is used as a condenser.
  • the heat exchanger functions as a condenser
  • the flow direction of the refrigerant flowing through the porous flat tube 2 of the heat exchanger is opposite to the evaporator.
  • the first refrigerant partition plate 8a and the second refrigerant partition plate 8b are the shortest route through which the gas-liquid two-phase refrigerant flowing out from the second row of flat flat tubes 2c flows into one end of the first row of flat flat tubes 2b.
  • the refrigerant flow 3 in the line passing portion 5 is formed in an S shape.
  • the liquid refrigerant 6 in the gas-liquid two-phase refrigerant flowing out of the porous flat tube 2c flows into the periphery of the porous flat tube 2b from the first opening 8c of the first refrigerant partition plate 8a, and reaches the deepest of the first refrigerant partition plate 8a. It concentrates on the leeward side in the flow direction of the heat exchange fluid that is the part and flows into the porous flat tube 2b. In the case of a condenser, the windward side of the porous flat tube 2b has a higher heat load, and the heat exchanger performance is improved when more gas refrigerant is supplied. Therefore, with the configuration of the heat exchanger described above, the amount of gas refrigerant on the windward side of the porous flat tube 2b is relatively larger than that on the leeward side, and the heat exchanger performance can be improved.
  • FIG. 7 is a refrigerant circuit diagram of an air-conditioning refrigeration apparatus using the heat exchanger according to the first and second embodiments.
  • the refrigerant circuit shown in FIG. 7 includes a compressor 33, a condensing heat exchanger 34, an expansion device 35, an evaporating heat exchanger 36, and a blower 37 driven by a blower motor 38.
  • a compressor 33 a condensing heat exchanger 34
  • an expansion device 35 an evaporating heat exchanger 36
  • a blower 37 driven by a blower motor 38.
  • Cooling energy efficiency indoor heat exchanger (evaporator) capacity / total input
  • compatibility such as mineral oil, alkylbenzene oil, ester oil, ether oil, fluorine oil, etc. Any refrigerating machine oil can be used regardless of incompatibility.
  • the header 4 of the heat exchanger is an example in which the axial direction is arranged so as to be parallel to the gravity direction
  • the axial direction may be arranged parallel to the horizontal direction.
  • the heat exchanger functions as a condenser
  • the gas refrigerant and the liquid refrigerant 6 are evenly distributed in each refrigerant flow path of the porous flat tube 2b.
  • the heat exchange performance as a condenser is improved.

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

Abstract

L'invention concerne un échangeur thermique comprenant des tubes de transfert de chaleur qui sont parcourus par un milieu chauffant circulant dans des canaux internes et qui sont disposés dans une direction de rangée qui est la direction dans laquelle s'écoule un milieu d'échange de chaleur, une section de pontage de rangées (5) qui est un canal d'écoulement du milieu chauffant, lequel canal assure le couplage d'une paire de tubes de transfert de chaleur juxtaposés dans la direction de rangée, et un dispositif de tête (4) qui est connecté aux tubes de transfert de chaleur, la section de pontage de rangées (5) étant située dans le dispositif de tête (4), et une plaque séparative (7) qui est destinée au réfrigérant et est disposée verticalement dans le canal de milieu chauffant, étant placée dans la section de pontage de rangées (5).
PCT/JP2014/075328 2013-09-27 2014-09-24 Échangeur thermique et appareil de climatisation utilisant cet échangeur thermique Ceased WO2015046275A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2015539281A JP6120978B2 (ja) 2013-09-27 2014-09-24 熱交換器及びそれを用いた空気調和機
EP14847978.5A EP3051244B1 (fr) 2013-09-27 2014-09-24 Échangeur thermique et appareil de climatisation utilisant cet échangeur thermique

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JPPCT/JP2013/076298 2013-09-27
PCT/JP2013/076298 WO2015045105A1 (fr) 2013-09-27 2013-09-27 Échangeur de chaleur et climatiseur l'utilisant

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WO2015046275A1 true WO2015046275A1 (fr) 2015-04-02

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PCT/JP2013/076298 Ceased WO2015045105A1 (fr) 2013-09-27 2013-09-27 Échangeur de chaleur et climatiseur l'utilisant
PCT/JP2014/075328 Ceased WO2015046275A1 (fr) 2013-09-27 2014-09-24 Échangeur thermique et appareil de climatisation utilisant cet échangeur thermique

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PCT/JP2013/076298 Ceased WO2015045105A1 (fr) 2013-09-27 2013-09-27 Échangeur de chaleur et climatiseur l'utilisant

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JP (1) JP6120978B2 (fr)
WO (2) WO2015045105A1 (fr)

Cited By (4)

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Publication number Priority date Publication date Assignee Title
WO2017094114A1 (fr) * 2015-12-01 2017-06-08 三菱電機株式会社 Dispositif à cycle de réfrigération
WO2017109823A1 (fr) * 2015-12-21 2017-06-29 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération
WO2019142617A1 (fr) * 2018-01-19 2019-07-25 ダイキン工業株式会社 Échangeur de chaleur et dispositif de climatisation
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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JPWO2022085067A1 (fr) * 2020-10-20 2022-04-28
WO2023032155A1 (fr) * 2021-09-03 2023-03-09 三菱電機株式会社 Échangeur de chaleur, dispositif de cycle de réfrigération et procédé de fabrication d'un échangeur de chaleur
JP7602156B1 (ja) * 2023-07-03 2024-12-18 ダイキン工業株式会社 冷凍装置

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Cited By (15)

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Publication number Priority date Publication date Assignee Title
JPWO2017094114A1 (ja) * 2015-12-01 2018-07-12 三菱電機株式会社 冷凍サイクル装置
EP3385643A4 (fr) * 2015-12-01 2018-12-05 Mitsubishi Electric Corporation Dispositif à cycle de réfrigération
US11105538B2 (en) 2015-12-01 2021-08-31 Mitsubishi Electric Corporation Refrigeration cycle apparatus
WO2017094114A1 (fr) * 2015-12-01 2017-06-08 三菱電機株式会社 Dispositif à cycle de réfrigération
US10436514B2 (en) 2015-12-21 2019-10-08 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
WO2017109823A1 (fr) * 2015-12-21 2017-06-29 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération
JPWO2017109823A1 (ja) * 2015-12-21 2018-08-02 三菱電機株式会社 熱交換器及び冷凍サイクル装置
JP2019128041A (ja) * 2018-01-19 2019-08-01 ダイキン工業株式会社 熱交換器および空気調和装置
WO2019142617A1 (fr) * 2018-01-19 2019-07-25 ダイキン工業株式会社 Échangeur de chaleur et dispositif de climatisation
EP3742081A4 (fr) * 2018-01-19 2021-10-06 Daikin Industries, Ltd. Échangeur de chaleur et dispositif de climatisation
JP7078840B2 (ja) 2018-01-19 2022-06-01 ダイキン工業株式会社 熱交換器および空気調和装置
JP2020201020A (ja) * 2019-06-13 2020-12-17 ダイキン工業株式会社 熱交換器
WO2020250624A1 (fr) * 2019-06-13 2020-12-17 ダイキン工業株式会社 Échangeur de chaleur
CN113939705A (zh) * 2019-06-13 2022-01-14 大金工业株式会社 热交换器
US12398956B2 (en) 2019-06-13 2025-08-26 Daikin Industries, Ltd. Heat exchanger

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EP3051244A4 (fr) 2017-05-24
EP3051244B1 (fr) 2018-12-19
JPWO2015046275A1 (ja) 2017-03-09
WO2015045105A1 (fr) 2015-04-02
JP6120978B2 (ja) 2017-04-26

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