EP3051244B1 - 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
EP3051244B1
EP3051244B1 EP14847978.5A EP14847978A EP3051244B1 EP 3051244 B1 EP3051244 B1 EP 3051244B1 EP 14847978 A EP14847978 A EP 14847978A EP 3051244 B1 EP3051244 B1 EP 3051244B1
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EP
European Patent Office
Prior art keywords
heat exchanger
column
refrigerant
porous flat
heat
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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.)
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Application number
EP14847978.5A
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German (de)
English (en)
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EP3051244A1 (fr
EP3051244A4 (fr
Inventor
Akira Ishibashi
Shinya Higashiiue
Daisuke Ito
Takumi NISHIYAMA
Shigeyoshi MATSUI
Yuki UGAJIN
Takashi Okazaki
Atsushi Mochizuki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3051244A1 publication Critical patent/EP3051244A1/fr
Publication of EP3051244A4 publication Critical patent/EP3051244A4/fr
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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 columns of heat transfer tubes through which refrigerant flows in the flow direction of a heat-exchange fluid (such as air).
  • a heat exchanger according to the preamble of claim 1 is known from document JP 2003 287390 A , figure 4 .
  • Fig. 8 shows an internal structure of a header 4 of a conventional heat exchanger as described above, and is a cross-sectional view of a column bridging portion 5 that allows the refrigerant to flow between the columns of heat transfer tubes.
  • Fig. 8 (a) shows a liquid refrigerant flow 3 when the cross-sectional shape of the column bridging portion 5 is a rectangle
  • Fig. 8 (b) shows the liquid refrigerant flow 3 when the cross-sectional shape of the column bridging portion 5 is a substantial parallelogram.
  • two-phase gas-liquid refrigerant having a quality of approximately 0.5 flows out of a porous flat tube 2 on the windward side of air, which is a heat-exchange fluid, and flows into a porous flat tube 2 of the leeward column as indicated by the refrigerant flow 3.
  • liquid refrigerant 6 in the two-phase gas-liquid refrigerant concentrates in a leeward side part in the vicinity of the porous flat tube 2 of the leeward column by inertia force from the outflow side-heat transfer tube.
  • the present invention has been made to solve the above problem, and aims to provide a heat exchanger configured so that, when heat transfer tubes arranged in a column-wise direction are connected in a column bridging portion, which is a refrigerant flow path, the flow rate distribution of liquid refrigerant flowing into the heat transfer tube at and after the column bridging portion is even, or the flow rate distribution is appropriate to heat load, achieving excellent performance of the heat exchanger.
  • a heat exchanger according to the present invention includes the features of claim 1.
  • the refrigerant partition plate for guiding the flowing heat medium is provided inside the column bridging portion.
  • the flow rate distribution of liquid refrigerant flowing into the heat transfer tube at and after the column bridging portion is made even, or the flow rate distribution becomes appropriate to heat load, achieving excellent performance of the heat exchanger.
  • Fig. 1 is a partial front view of the heat exchanger according to Embodiment 1.
  • Fig. 2 is a cross-sectional view of porous flat tubes of the heat exchanger according to Embodiment 1.
  • the heat exchanger according to Embodiment 1 is a finned tube type heat exchanger.
  • Heat transfer tubes of the heat exchanger are arranged in the horizontal direction, while fins 1 are arranged in the vertical direction.
  • a header 4 is connected to one end side of the heat transfer tubes.
  • the header 4 is arranged so that its axial direction is parallel to the gravity direction.
  • the heat transfer tubes are a porous flat tubes 2 each having many refrigerant flow paths arranged in parallel, and are arranged in two columns in the flowing direction of air, which is a heat-exchange fluid.
  • the porous flat tubes 2 in the two columns are arranged in a staggered manner in cross-sectional view.
  • Refrigerant flows inside the porous flat tubes 2, and the fins 1 are provided perpendicular to the axial directions of the porous flat tubes 2.
  • the porous flat tubes 2 and the fins 1 are formed of a highly conductive metal such as copper and aluminum, and are joined by methods such as brazing, soldering, and welding under a state in which the porous flat tubes 2 are inserted into heat transfer tube insertion parts, which are cut out on the fins 1, to transfer heat to each other.
  • the fin 1 is configured of a first fin 1a arranged on the windward side of the flow direction of air, which is a heat-exchange fluid, and a second fin 1b arranged on the leeward side.
  • a single path of the porous flat tubes 2 is formed of 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 of the flow direction of air, and form a first column.
  • the porous flat tubes 2c and 2d penetrate the second fins 1b arranged on the leeward side of the flow direction of air, and form a second column.
  • multiple steps of the porous flat tubes 2a and 2b are arranged layeredly in the axial direction of the header 4 while penetrating the first fins 1a.
  • multiple steps of the porous flat tubes 2c and 2d are arranged layeredly in the axial direction of the header 4 while penetrating the second fins 1b.
  • the header 4 has a hollow structure having a substantially rectangular cross section, and includes a refrigerant flow path therein.
  • the refrigerant flow path is formed as a column bridging portion 5, which connects the porous flat tubes 2b and 2c in the column-wise direction.
  • the other end part of the porous flat tube 2b is connected to the header 4, and the refrigerant having flowed out of the porous flat tube 2b passes through the column bridging portion 5 of the header 4 to move from column to column, and flows into one end part of the porous flat tube 2c of the second column.
  • the refrigerant having flowed into one end part of the porous flat tube 2c passes through the U-bend 9 from the other end part of the porous flat tube 2c to move from step to step, and flows into one end part of the porous flat tube 2d. Then, the refrigerant flows out of the other end part of the porous flat tube 2d.
  • gas refrigerant flows in from the other end part of the porous flat tube 2d of the second column, follows through a flow path opposite to that of the case in which the heat exchanger is used as the evaporator, and flows out of one end part of the porous flat tube 2a of the first column.
  • the heat exchanger is configured by layering multiple steps of the paths of a unit formed in this manner, in the axial direction of the header 4.
  • Fig. 3 is a cross-sectional view of the column bridging portion 5 when the heat exchanger according to Embodiment 1 is used as an evaporator.
  • the column bridging portion 5 is formed as a substantially cuboidal hollow part inside the header 4.
  • the porous flat tube 2b and the porous flat tube 2c are connected to and open to the column bridging portion 5, and two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2b of the first column passes through the column bridging portion 5 to move between columns of the porous flat tubes 2b and 2c, and flows into one end part of the porous flat tube 2c of the second column.
  • FIG. 3 The positional relation between the porous flat tube 2b and the porous flat tube 2c is shown in Fig. 3 , where the porous flat tube 2c of the second column is shifted from the porous flat tube 2b of the first column in the axial direction of the header 4.
  • a refrigerant partition plate 7 horizontally partitioning the inside of the column bridging portion 5 is installed between the porous flat tube 2b and the porous flat tube 2c in the axial direction of the header 4.
  • the refrigerant partition plate 7 is supported by straddling and being attached to two surfaces, which are a side wall of the column bridging portion 5 on which the porous flat tube 2b and the porous flat tube 2c open, and another side wall opposite to this side wall. Moreover, the refrigerant partition plate 7 is provided in the center position of the column-wise direction in which the porous flat tube 2b and the porous flat tube 2c are arranged, thus a first opening 7a is formed below the porous flat tube 2b, and a second opening 7b is formed above the porous flat tube 2c in the configuration.
  • the refrigerant partition plate 7 configured in this manner blocks the shortest route for the two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2b of the first column to flow into one end part of the porous flat tube 2c of the second column, and divides the flow path of the refrigerant into two parts.
  • liquid refrigerant 6 in the two-phase gas-liquid refrigerant flows into the porous flat tube 2c through two flow paths, on the windward side and leeward side of the flow direction of heat-exchange fluid inside the column bridging portion 5, supplying the liquid refrigerant 6 evenly to the refrigerant flow paths of the porous flat tube 2c.
  • the refrigerant partition plate 7 may be any form as long as it can obstruct the flow of the refrigerant, and may be a fine mesh plate or a protrusion formed on a side wall of the column bridging portion 5, for example.
  • the refrigerant partition plate 7 may be formed integrally with the header 4, or may be attached as a separate body.
  • the refrigerant partition plate is preferred to be made of the same material as that of the header 4, and may be made of a copper plate, an aluminum plate, or a resin plate, for example.
  • Fig. 4 is a cross-sectional view of the column bridging portion 5 when the heat exchanger according to Embodiment 1 is used as a condenser.
  • the flow direction of refrigerant flowing through the porous flat tube 2 of the heat exchanger is opposite to that of the case in which the heat exchanger is used as the evaporator described above.
  • the refrigerant partition plate 7 blocks the shortest route for the refrigerant having flowed out of the porous flat tube 2c of the second column to flow into one end part of the porous flat tube 2b of the first column, and divides the flow path of the refrigerant into two parts.
  • the liquid refrigerant 6 flows into the porous flat tube 2b through two flow paths, on the windward side and leeward side of the flow direction of heat-exchange fluid inside the column bridging portion 5, supplying gas refrigerant and the liquid refrigerant 6 evenly to the refrigerant flow paths of the porous flat tube 2b.
  • gas refrigerant and the liquid refrigerant 6 flow evenly into the refrigerant flow paths of the porous flat tube 2b and the gas refrigerant is condensed, causing the condense effect to occur evenly in the refrigerant flow paths, and improving heat exchange performance as a condenser.
  • Fig. 5 is a cross-sectional view of a column bridging portion 5 when a heat exchanger according to Embodiment 2 is used as an evaporator.
  • the column bridging portion 5 is formed inside a header 4, as a hollow part having a substantially parallelogram-shaped cross section.
  • a porous flat tube 2b and a porous flat tube 2c are connected to and open to the column bridging portion 5, and two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2b of a first column passes through the column bridging portion 5 to move between columns of the porous flat tubes 2b and 2c, and flows into one end part of the porous flat tube 2c of a second column.
  • FIG. 5 The positional relation between the porous flat tube 2b and the porous flat tube 2c is shown in Fig. 5 , where the porous flat tube 2b of the first column is provided in the vicinity of the upper side of the column bridging portion 5, and the porous flat tube 2c of the second column is provided in the vicinity of the lower side of the column bridging portion 5.
  • first refrigerant partition plate 8a and a second refrigerant partition plate 8b horizontally partitioning the inside of the column bridging portion 5 are installed around the porous flat tube 2b and around the porous flat tube 2c.
  • the first refrigerant partition plate 8a and the second refrigerant partition plate 8b are supported by straddling and being attached to two surfaces, which are a side wall of the column bridging portion 5 on which the porous flat tube 2b and the porous flat tube 2c open, and another side wall opposite to this side wall.
  • the first refrigerant partition plate 8a surrounds the porous flat tube 2b, and has a first opening 8c opened downward on the windward side of the flow direction of heat-exchange fluid inside the column bridging portion 5. Meanwhile, the second refrigerant partition plate 8b surrounds the porous flat tube 2c, and has a second opening 8d opened upward on the leeward side of the flow direction of heat-exchange fluid inside the column bridging portion 5.
  • the first refrigerant partition plate 8a and the second refrigerant partition plate 8b configured in this manner block the shortest route for two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2b of the first column to flow into one end part of the porous flat tube 2c of the second column, and form the flow path for a refrigerant flow 3 inside the column bridging portion 5 into an S shape.
  • liquid refrigerant 6 in the two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2b flows into the periphery of the porous flat tube 2c through the second opening 8d of the second refrigerant partition plate 8b, concentrates on the windward side of the flow direction of heat-exchange fluid, which is the deepest part of the second refrigerant partition plate 8b, and forms a pool of liquid.
  • heat load is high on the windward side of the porous flat tube 2c, and thus supplying more liquid refrigerant thereto improves performance of the heat exchanger.
  • the configuration of the above-mentioned heat exchanger allows the amount of liquid refrigerant on the windward side of the porous flat tube 2c to become relatively larger than that on the leeward side, improving performance of the heat exchanger.
  • Fig. 6 is a cross-sectional view of the column bridging portion 5 when the heat exchanger according to Embodiment 2 is used as a condenser.
  • the flow direction of refrigerant flowing through the porous flat tube 2 of the heat exchanger is opposite to that of the case in which the heat exchanger is used as the evaporator described above.
  • the first refrigerant partition plate 8a and the second refrigerant partition plate 8b block the shortest route for the two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2c of the second column to flow into one end part of the porous flat tube 2b of the first column, and form the refrigerant flow 3 inside the column bridging portion 5 into an S shape.
  • the liquid refrigerant 6 in the two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2c flows into the periphery of the porous flat tube 2b through the first opening 8c of the first refrigerant partition plate 8a, concentrates on the leeward side of the flow direction of heat-exchange fluid, which is the deepest part of the first refrigerant partition plate 8a, and flows into the porous flat tube 2b.
  • heat load is high on the windward side of the porous flat tube 2b, and thus supplying more gas refrigerant thereto improves performance of the heat exchanger.
  • the configuration of the above-mentioned heat exchanger allows the amount of gas refrigerant on the windward side of the porous flat tube 2b to become relatively larger than that on the leeward side, improving performance of the heat exchanger.
  • Fig. 7 is a refrigerant circuit diagram of an air-conditioning and refrigerating apparatus using the heat exchangers according to Embodiments 1 and 2.
  • a refrigerant circuit shown in Fig. 7 includes a compressor 33, a condensing heat exchanger 34, an expansion device 35, an evaporative heat exchanger 36, and fans 37 driven by fan motors 38.
  • a highly energy efficient air-conditioning and refrigerating apparatus can be implemented, by using the aforementioned heat exchanger according to Embodiments 1 and 2 as the condensing heat exchanger 34, the evaporative heat exchanger 36, or both.
  • Heating energy efficiency capacity of indoor heat exchanger condenser / all input
  • Cooling energy efficiency capacity of indoor heat exchanger evaporator / all input
  • working fluids other gases, liquids, or gas-liquid mixture fluids may be adopted as working fluids.
  • any refrigerating machine oils can be used regardless of whether they are miscible or immiscible, such as those based on mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorinated oil, in the heat exchangers described in the above Embodiments 1 and 2, and in the air-conditioning and refrigerating apparatus using the heat exchanger.
  • header 4 of the heat exchanger arranged so that its axial direction is parallel to the gravity direction has been used as an example, the axial direction may be arranged parallel to the horizontal direction.
  • the heat exchanger functions as a condenser
  • adopting the structure of the header 4 according to Embodiment 1 or 2 allows gas refrigerant and the liquid refrigerant 6 to flow evenly into the refrigerant flow paths of the porous flat tube 2b, improving heat exchange performance as a condenser.

Claims (8)

  1. Échangeur de chaleur, comprenant :
    un tube de transfert de chaleur ayant une voie d'écoulement interne à travers laquelle un fluide caloporteur s'écoule, une pluralité des tubes de transfert de chaleur étant agencés dans une pluralité de colonnes dans une direction en colonnes traversées par un fluide d'échange de chaleur ;
    une portion formant pont entre les colonnes (5) étant une voie d'écoulement de fluide caloporteur raccordant une paire des tubes de transfert de chaleur qui sont adjacents l'un à l'autre dans la direction en colonnes ;
    un collecteur (4) auquel la pluralité des tubes de transfert de chaleur sont raccordés, la portion formant pont entre les colonnes (5) étant disposée à l'intérieur du collecteur (4) ; et
    une plaque de séparation de frigorigène (7, 8a, 8b) installée dans la voie d'écoulement de fluide caloporteur à l'intérieur de la portion formant pont entre les colonnes (5),
    caractérisé en ce que la plaque de séparation de frigorigène (7, 8a, 8b) est disposée parallèlement à la direction en colonnes, et
    une ouverture à travers laquelle s'écoule le fluide caloporteur est disposée sur chaque partie d'extrémité de la plaque de séparation de frigorigène (7, 8a, 8b) dans la direction en colonnes.
  2. Échangeur de chaleur selon la revendication 1,
    dans lequel la paire des tubes de transfert de chaleur sont agencés à distance l'un de l'autre dans une direction perpendiculaire à la direction en colonnes, et
    dans lequel la plaque de séparation de frigorigène (7, 8a, 8b) est installée entre la paire des tubes de transfert de chaleur.
  3. Échangeur de chaleur selon la revendication 1 ou 2, dans lequel la plaque de séparation de frigorigène (7, 8a, 8b) est une plaque plate.
  4. Échangeur de chaleur selon l'une quelconque des revendications 1 à 3, dans lequel la portion formant pont entre les colonnes (5) est cuboïdale.
  5. Échangeur de chaleur selon l'une quelconque des revendications 1 à 3, dans lequel la forme de section transversale de la portion formant pont entre les colonnes (5) comprend une forme de parallélogramme.
  6. Échangeur de chaleur selon l'une quelconque des revendications 1 à 5, dans lequel l'échangeur de chaleur est un type de tube à ailettes, dans lequel des ailettes (1) sont installées dans une direction perpendiculaire à la une direction axiale du tube de transfert de chaleur.
  7. Échangeur de chaleur selon l'une quelconque des revendications 1 à 6, dans lequel le tube de transfert de chaleur est un tube (2) plat poreux comprenant une pluralité des voies d'écoulement à travers lesquelles s'écoule le fluide caloporteur.
  8. Appareil de conditionnement d'air comprenant l'échangeur de chaleur selon l'une quelconque des revendications 1 à 7.
EP14847978.5A 2013-09-27 2014-09-24 Échangeur thermique et appareil de climatisation utilisant cet échangeur thermique Active EP3051244B1 (fr)

Applications Claiming Priority (2)

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

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EP3051244A1 EP3051244A1 (fr) 2016-08-03
EP3051244A4 EP3051244A4 (fr) 2017-05-24
EP3051244B1 true EP3051244B1 (fr) 2018-12-19

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WO (2) WO2015045105A1 (fr)

Families Citing this family (6)

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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
US10436514B2 (en) 2015-12-21 2019-10-08 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
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
JP6806187B2 (ja) * 2019-06-13 2021-01-06 ダイキン工業株式会社 熱交換器
CN116507871A (zh) * 2020-10-20 2023-07-28 三菱电机株式会社 热交换器和制冷循环装置
JPWO2023032155A1 (fr) * 2021-09-03 2023-03-09

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Publication number Priority date Publication date Assignee Title
JP2003287390A (ja) * 2002-03-27 2003-10-10 Mitsubishi Electric Corp 熱交換器およびこれを用いた空気調和機

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US2733899A (en) * 1956-02-07 Lehmann
JPH0749249Y2 (ja) * 1988-11-10 1995-11-13 三菱重工業株式会社 熱交換器
JPH06117783A (ja) * 1992-10-01 1994-04-28 Showa Alum Corp 積層型熱交換器
JPH06213532A (ja) * 1993-01-20 1994-08-02 Showa Alum Corp 積層型熱交換器
JP4143955B2 (ja) * 2001-11-30 2008-09-03 株式会社ティラド 熱交換器
JP2003302183A (ja) * 2002-04-09 2003-10-24 Toyo Radiator Co Ltd 空調用熱交換器
JP3736514B2 (ja) * 2002-09-13 2006-01-18 三菱電機株式会社 熱交換器および熱交換器を用いた空気調和機
JP2006029653A (ja) * 2004-07-14 2006-02-02 Calsonic Kansei Corp 熱交換器
SE528412C2 (sv) * 2005-03-15 2006-11-07 Scania Cv Ab Kylanordning där en första tank är försedd med yttre ytförstorande element och ett inre földesledande element
JP2007032993A (ja) * 2005-07-29 2007-02-08 Showa Denko Kk 熱交換器

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003287390A (ja) * 2002-03-27 2003-10-10 Mitsubishi Electric Corp 熱交換器およびこれを用いた空気調和機

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JPWO2015046275A1 (ja) 2017-03-09
EP3051244A1 (fr) 2016-08-03
WO2015046275A1 (fr) 2015-04-02
WO2015045105A1 (fr) 2015-04-02
JP6120978B2 (ja) 2017-04-26
EP3051244A4 (fr) 2017-05-24

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