WO2002035170A1 - Echangeur thermique - Google Patents

Echangeur thermique Download PDF

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Publication number
WO2002035170A1
WO2002035170A1 PCT/JP2001/009326 JP0109326W WO0235170A1 WO 2002035170 A1 WO2002035170 A1 WO 2002035170A1 JP 0109326 W JP0109326 W JP 0109326W WO 0235170 A1 WO0235170 A1 WO 0235170A1
Authority
WO
WIPO (PCT)
Prior art keywords
header
tube
heat exchanger
recited
side wall
Prior art date
Application number
PCT/JP2001/009326
Other languages
English (en)
Inventor
Hiroyasu Shimanuki
Ryoichi Hoshino
Noboru Ogasawara
Takashi Tamura
Takashi Terada
Futoshi Watanabe
Hirofumi Horiuchi
Original Assignee
Showa Denko K.K.
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
Priority claimed from JP2000325119A external-priority patent/JP2002130979A/ja
Application filed by Showa Denko K.K. filed Critical Showa Denko K.K.
Priority to AU2002212677A priority Critical patent/AU2002212677A1/en
Priority to US10/399,777 priority patent/US20040031598A1/en
Publication of WO2002035170A1 publication Critical patent/WO2002035170A1/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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • F28F9/002—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core with fastening means for other structures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates

Definitions

  • the present invention relates to a heat exchanger, and more particularly, to a heat exchanger suitably used as a condenser or an evaporator for use in air-conditioning systems such as car air-conditioning systems or room air-conditioning systems.
  • a condenser for use in air-conditioning systems it is required to miniaturize the condenser while improving the heat-conducting characteristic as well as decreasing the refrigerant flow resistance.
  • a car air- conditioning condenser it is strongly required to further miniaturize it because of a limited mounting space.
  • it is also strongly required to decrease the amount of refrigerant to be used in view of earth environment protection. In order to meet these requirements, it is an important object to miniaturize the condenser by reducing the inner volume thereof.
  • the so-called multi-pass type heat exchanger 100 which has a pair of round headers 101 and 101 and a plurality of heat exchanging tubes 102 with opposite ends thereof connected to. the headers, is widely used.
  • this multi-pass type condenser since the header 101 is round in horizontal cross-section, the condenser is excellent in pressure resistant .
  • a plurality of tubes 102 are arranged in parallel each other, the flow resistance of refrigerant can be decreased, enabling the use of tubes having smaller cross-section, which enables to enlarge the heat- transfer-area density (surface area per unit volume) .
  • the inner volume of the tube can be decreased as mentioned above, the decreased inner volume of the tube inevitably causes an increased ratio of the header inner volume to the entire refrigerant circuits.
  • some heat exchangers employ a header having an approximately elliptical cross-sectional shape, which can decrease the inner volume of the header. In this case, however, it is required to increase the thickness of the header so as to secure sufficient strength against the inner pressure, resulting in increased weight of header, which in turn makes it difficult to provide a lightweight heat exchanger.
  • a heat exchanger comprises a hollow header and a plurality of heat exchanging tubes which are in fluid communication with the hollow header, wherein the header has an angular cross-sectional shape including a rectangular cross-sectional shape and a square cross-sectional shape, wherein the header is provided with one or a plurality of header-partitioning walls extending in a longitudinal direction of the header, whereby an inner space of the header is divided into a plurality of collecting chambers, and wherein a tube-non- connecting-side wall of each of the collecting chambers has a curved inner surface.
  • the header has not a conventional round cross-sectional shape but an angular cross-sectional shape including a rectangular cross-sectional shape and a square cross-sectional shape, it becomes possible to design such that the width S of the header is smaller than the depth T of the header, resulting in decreased inner volume of the header. As a result, the entire heat exchanger can be effectively miniaturized and the amount of refrigerant to be used can be decreased. Furthermore, the header is provided with one or a plurality of header-partitioning walls extending in a longitudinal direction of the header, whereby an inner space of the header is divided into a plurality of collecting chambers. Accordingly, the reinforcing effect against inner pressure can be obtained, resulting in sufficient pressure resistance of the header.
  • a tube- non-connecting-side wall of each of the collecting chambers has a curved inner surface, it is effectively prevented the refrigerant flowed out of the end portion of the tube from returning to the end portion of the tube even if the refrigerant collided against the inner surface of the tube-non-connecting-side wall of the header and rebounded therefrom.
  • a maximum distance from an end of the tube communicated with the collecting chamber to the curved inner surface of the tube-non-connecting-side wall is 2 mm or more and 80% or less of a width of the tube. This effectively reduces the inner volume of the header while increasing the flow-down velocity of the liquefied refrigerant in the header.
  • the curved inner surface is provided with a plurality of vertically extending refrigerant-guiding grooves. This enhances the prompt flow-down and discharge of the liquid refrigerant.
  • a communication opening is formed in the header-partitioning wall at the same height as a height of a tube-connecting position of the header. This communication opening allows the liquefied refrigerant in each collecting chamber to be mixed with each other . Thus, larger accumulation of liquefied refrigerant in a windward-side collecting chamber can be prevented, resulting in even accumulation of liquefied refrigerant in each collecting chamber. Furthermore, since the communication opening is formed in the header-partitioning wall at the same height as a height of a tube-connecting position of the header, a mixture of refrigerant in ⁇ each collecting chamber can be attained sufficiently.
  • a pair of guide rails disposed apart from each other are protruded from an external surface of a tube-non-connecting-side wall of the header and that a bracket is connected to the header by engaging a part of the bracket with the pair of guide rails. • An engagement of a part of the bracket with the pair of guide rails enables an easy attachment of the bracket and improves the accuracy of attaching position of the bracket.
  • bracket fitted on the header In cases where a fitted portion of the bracket fitted on the header is integrally brazed to the header, the bracket is fixed to the header assuredly.
  • a plurality of brazing-material-holding grooves extending in a longitudinal direction of the header are formed on an . external surface of a tube-connecting-side wall of the header.
  • the aforementioned brazing-material-holding grooves can effectively prevent the dropping of the brazing materials, resulting in stable brazing, which in turn can secure sufficient connecting strength.
  • the tube is formed into a flat shape and that an inner fin having a plurality of communication apertures formed in a scattered manner is inserted into an inner space of the tube.
  • the tube is formed into a flat shape and that an inner space of the tube is divided by one or a plurality of tube-partitioning walls extending in a longitudinal direction of the tube and that each of the tube-partitioning walls is provided with one or a plurality of communication apertures.
  • the liquefied refrigerant passing through the tube can be mixed in each partitioned refrigerant passage via the communication apertures formed in the inner fin or the tube-partitioning wall, the discharging of the refrigerant from each partitioned refrigerant passage into the header can be further equalized.
  • the header includes a sacrificial zinc layer for corrosion protection formed at an external surface thereof and that the zinc is diffused into the header by heat at the time of integrally brazing the header and the tube. This enhances corrosion protection of the header. It is preferable that the zinc concentration after the diffusion in a surface of the hollow header falls within a range of from 1 to 10 wt%. This further enhances the corrosion protection of the header.
  • a tube insertion aperture is formed in a tube-connecting-side wall and front and rear side walls extending from the tube-connecting-side wall and that a width of the tube is the same as or generally the same as a depth' of the header in a widthwise direction of the tube.
  • the tube insertion aperture is formed in a tube-connecting-side wall and front and rear side walls extending from the tube-connecting-side wall, machining for forming the tube insertion aperture can be simplified, resulting i 'remarkably improved processing efficiency thereof.
  • the assembly can be improved.
  • each of the front and rear side walls of the header is provided with a tube-displacement-restricting piece bent toward the tube insertion aperture and fitted on a widthwise side surface of the tube.
  • Fig. 1A is a front view of a heat exchanger according to a first embodiment of the present invention
  • Fig. IB is a top view thereof.
  • Fig. 2 is an enlarged cross-sectional view taken along the lines 2-2 in Fig. 1A.
  • Fig. 3 is an enlarged cross-sectional view taken along the lines 3-3 in Fig. 1A.
  • Fig. 4 is a cross-sectional view taken along the lines 4- 4 in Fig. 2.
  • Fig. 5 is a perspective view showing the tube.
  • Fig. 6 is a cross-sectional view showing a modification of a header structure.
  • Fig.7 is a cross-sectional view showing another modification of a header structure.
  • Fig. 8A is a cross-sectional view showing still another modification of a header structure
  • Fig.8B is a cross-sectional view showing still yet another modification of a header structure
  • Fig. 9A is a perspective view showing a modification of a tube inner structure
  • Fig. 9B is a perspective view showing an inner fin inserted in the tube.
  • Fig. 10A is a front view of a heat exchanger according to another embodiment of the present invention
  • Fig. 10B is a top view thereof
  • Fig. 11A is an enlarged perspective view showing the cross-section taken along the line 11-11 in Fig. 10A
  • Fig. 11B is a perspective view showing the header before bending the tube-displacement-restricting pieces of the header.
  • Fig. 12 is a front view showing the left header constituting the heat exchanger shown in Figs. 10A and 10B.
  • Fig. 13A is a front view of a conventional heat exchanger
  • Fig. 13B is a top view thereof.
  • the heat exchanger shown in Figs. 1A and IB is a condenser made of aluminum for car air-conditioners or room air-conditioners .
  • the reference numerals 1, 2 and 3 denote a heat exchanging flat tube, a hollow header and a fin (outer fin) , respectively.
  • the fin 3 is a corrugated fin made of an aluminum brazing sheet.
  • a plurality of flat tubes 1 are disposed in parallel with each other at predetermined intervals with their opposite ends thereof communicated with a pair of hollow headers 2 and 2. Between the adjacent tubes 1, a fin 3 is disposed.
  • the tubes 1 and the headers 2 are brazed.
  • the brazing is performed generally by a method using a tube 1 on which brazing materials are previously clad is used, a method using a header 2 on which brazing materials are previously clad, or a method using both of the aforementioned tube 1 and header 2.
  • each hollow header 2 is divided by a partition- 4 at a predetermined longitudinal position.
  • the left header 2 has an inlet pipe 5 at its upper portion, and the right header 2 has an outlet pipe 6 at its lower portion.
  • the refrigerant introduced into the left header 2- via the inlet pipe 5 passes through the plurality of tubes 1 in a meandering manner and flows out of the outlet pipe 6.
  • the aforementioned hollow header 2 is comprised of a header pipe 2a having an approximately rectangular cross-sectional shape and header caps 2b having- an approximately rectangular cross- sectional shape for sealing the ends of the header pipe 2a.
  • the inner space of the header 2 is divided by header-partitioning walls 12 and 12 into three collecting chambers 13.
  • the header 2 is formed into an angular cross-sectional shape such as a generally rectangular cross-sectional shape, although it is required to design such that the depth T of the header 2 is the same as or more than the width W of the tube 1, the width S of the header 2 can be arbitrarily designed regardless of the width W of the tube 1 or the depth T of the header 2.
  • the width S of the header 2 can be designed smaller than the depth T of the header 2 as shown in Fig. 3. Accordingly, the inner volume of the header 2 can be reduced which in turn can fully miniaturize the whole heat exchanger and decrease the amount of refrigerant.
  • the header-partitioning walls 12 are provided in the header 2, the pressure resistance of the header 2 can also be fully secured.
  • the inner surface 14 of the tube-non-connecting-side wall of the collecting chamber 13 is formed into a curved surface as shown in Figs. 2 and 3. Since the inner surface 14 of the tube-non- connecting-side wall of the header 2 is formed into the curved surface, it is effectively prevented the refrigerant flowed out of the end portion of the tube 1 from returning to the end portion of the tube 1 even if the refrigerant collided against the inner surface of "the tube-non-connecting-side wall of the header 2 and rebounded therefrom. Thus, the refrigerant ' rebounded from the inner surface 14 will be gathered in the central portion of each collecting chamber 13 without interfering with the refrigerant flowed out of the end portion of tube 1 and then will flow downward in the header 2.
  • Each header-partitioning wall 12 is provided with communication openings 15 at the corresponding height as the height of each tube-connecting position of the header 2. Since the communication opening 15 allows the liquefied refrigerant in each collecting chamber 13 to be mixed with each other. Thus, it is prevented that larger amount of liquefied refrigerant is accumulated in the windward-side collecting chamber 13, resulting in even accumulation of liquefied refrigerant in each collecting chamber 13.
  • the external surface 16 of the tube-non-connecting-side wall of the header 2 is formed into a flat shape. On the external surface
  • Each guide rail 17 has an inwardly bent tip end forming a receiving dented portion 17a.
  • a bracket 18 includes a flat-shaped fitting portion 18a and a mounting portion 18b outwardly protruded from the central portion of the fitting portion 18a.
  • the bracket 18 has a generally T-cross- sectional shape.
  • the opposite ends of the fitting portion 18a are inserted into and engaged with the aforementioned receiving dented portions 17a, whereby the bracket 18 is fixed to the header 2.
  • the fitting portion 18a and the header 2 are integrally brazed each other.
  • the flat tube 1 is the so-called harmonica tube made of an aluminum extruded member having a flat cross- sectional shape.
  • the inner space of the tube 1 is divided by tube-partitioning walls 10 extending in a longitudinal direction of the tube 1.
  • an electric resistance welded pipe may be used.
  • a plurality of communication apertures 20 are formed in each tube partitioning wall 10 at predetermined intervals.
  • the liquefied refrigerant passing through the tube 1 will be mixed between adjacent divided passages 19 through these communication apertures 20. Accordingly, the amount of liquefied refrigerant flowed out of each divided passage 19 into the header 2 will be equalized.
  • the same effects can also be obtained by, for example, the tube structure shown in Figs. 9A and 9B.
  • an inner fin -27 having a plurality of communication apertures 26 formed in a scattered manner is inserted in the flat tube 1, whereby the inner space of the tube 1 is divided into a plurality of divided passages 19.
  • Fig.10 shows a heat exchanger according to another embodiment.
  • This • embodiment has the same structure as the aforementioned embodiment except for the header structure and the connecting structure of the header and the tube. Accordingly, the following explanation will be focused on the different structures.
  • the tube insertion aperture 30 to be formed in the header 2 is formed in a tube-connecting-side wall 31 and a front side wall 32 and a rear side wall 33 extending from the tube-connecting-side wall 31.
  • this tube insertion aperture 30 which is opened toward three sides, machining for forming the tube insertion aperture 30 can be simplified, resulting in remarkably improved processing efficiency thereof.
  • the assembly can be improved. Furthermore, by adopting this structure, the width W of the tube 1 can be the same or generally the same as the depth T of the header 2. In this embodiment, since the width W of the tube 1 is the same as the depth T of the header 2, the header 2 does not protrude from the widthwise sides of the tube 1. Accordingly, the heat exchanger can be further miniaturized.
  • a tube-displacement- restricting pieces 40 are formed on each of the front and rear side walls 32 and 33 of the header 2. As shown in Fig. 11A, the tube-displacement-restricting pieces 40 are bent toward the tube insertion aperture side of the front side wall 32 and that of the rear side wall 33 and fitted on the widthwise sides of the tube 1. Thus, the displacement of the tube 1 in the direction of the front and rear sides of the tube as well as the dropping of the tube 1 can be prevented assuredly.
  • the aforementioned tube-displacement- restricting pieces 40 can be integrally formed together with the header body by an extrusion.
  • the tube- displacement-restricting piece 40 is preferably formed to have an inwardly curved shaped as shown in Fig. 11B in order to attain perfect fitting onto the tube in consideration of the springback at the time of bending. Furthermore, when the tube- displacement-restricting piece 40 and the header 2 are integrally brazed, stronger junction thereof can be secured.
  • the maximum distance L from the end of the tube 1 communicated with the collecting chamber 13 to the curved inner surface 14 of the tube-non-connecting-side wall is 2 mm or more and 80% or less of the width W of the tube 1 (see Fig. 2) .
  • the distance L is less than 2 mm, the pressure loss at the refrigerant side increases, resulting in decreased fall-down velocity of the liquefied refrigerant, which in turn decreases the heat radiation performance .
  • the distance L exceeds 80% of the tube width W, the inner volume of the header 2 becomes the same as or larger than that of the conventional round header, which is not preferable.
  • the header 2 includes a sacrificial zinc layer for corrosion protection formed at an external surface thereof and that the zinc is diffused into the header 2 by heat at the time of integrally brazing the header 2 and the tubes 1.
  • This improves the corrosion resistance of the header 2, which in turn enables to provide a heat exchanger excellent in durability.
  • a conventional sacrifice anticorrosion method for a tube it is known to spray zinc or form a zinc layer on an external surface of the tube.
  • the sacrificial zinc layer for corrosion protection can be formed on the external surface of the header 2. Concretely, immediately after the extrusion of the header 2, molten zinc is sprayed onto the external surface of the header 2.
  • the zinc is diffused into the header by the heat at the time of brazing after the fabrication of the tubes 1, fins 3 and headers 2.
  • Simply spraying zinc onto the external surface of the header fails to provide sufficiently stabilized sacrifice anticorrosion layer.
  • by diffusing the zinc stabilized sacrifice anticorrosion can be obtained.
  • the zinc ' concentration after the diffusion in the surface of the header 2 falls within the range of from 1 to 10 wt%.
  • the curved inner surface 14 is provided with a plurality of vertically extending refrigerant-guiding grooves 21.
  • the inner surface 14 of the.tube-non-connecting-side wall is formed' into a curved surface as a whole.
  • the shape of the refrigerant-guiding groove 21 is not limited to a specific one, a V-shape may be exemplified.
  • a plurality of brazing-material-holding grooves 24 extending in " a longitudinal direction of the header 2 are formed on an external surface of the tube-connecting-side wall 23 of the header 2.
  • the brazing-material-holding grooves 24 can effectively prevent the brazing materials from being dropped during the brazing, resulting in stable brazing, which in turn secures sufficient joining strength.
  • the aforementioned brazing materials powdered brazing materials, a mixture of powdered brazing materials and flux, and a mixture of the aforementioned mixture and combining materials can be exemplified.
  • the shape of the groove 24 is not limited to a specific one, a V-shape may be exemplified.
  • the header 2 is required to have an angular cross-sectional shape including a rectangular cross-sectional shape and a square cross-sectional shape.
  • angular cross-sectional shape is used to cover such a cross-sectional shape as shown in Figs. 8A and 8B.
  • the header has not a conventional round cross-sectional shape but an angular cross-sectional shape including a rectangular cross-sectional shape and a square cross-sectional shape, it becomes possible to design such that the width of the header is smaller than the depth of the header, resulting in decreased inner volume of the header.
  • the entire heat exchanger can be effectively miniaturized and the amount of refrigerant to be used can be decreased, which in turn can contribute to earth environment protection.
  • the header is provided with one or a plurality of header-partitioning walls extending in a longitudinal direction of the header, sufficient pressure resistance of the header can be obtained.
  • a tube-non-connecting-side wall of each of the collecting chambers has a curved inner surface, it is effectively prevented the refrigerant flowed out of the end portion of the tube from returning to the end portion.of the tube even if the refrigerant collides against an inner surface of the 5 tube-non-connecting-side wall of the header and rebounds therefrom. ' '
  • the refrigerant rebounded from the inner surface will be gathered in the central portion of each collecting chamber without interfering with the refrigerant flowed but of the end portion of tube and then flows downward in the header.
  • the fall-down velocity of the liquefied refrigerant in the header can be increased,' 5 and the inner volume of the header can be. effectively reduced.
  • the curved inner surface is provided with a plurality of vertically extending refrigerant-guiding grooves, prompt fall-down and discharge of the liquid refrigerant in the header can be enhanced.
  • the liquefied refrigerant in each collecting chamber can be mixed with each other.
  • bracket In cases where a pair of guide rails disposed apart from each 5 other are protruded from an external surface of a tube-non- connecting-side wall of the header and a bracket is connected to the header by engaging a part of the bracket with the pair of guide rails, the bracket can be easily attached to the header and the accuracy of attaching position of the bracket can be improved. In cases where a fitted portion of the bracket fitted on the header is integrally brazed to the header, the bracket can be fixed to the header assuredly.
  • brazing-material-holding grooves extending in a longitudinal direction of the header are formed on an external surface of a tube-connecting-side wall of the header, the dropping of the brazing material can be effectively prevented, resulting in sufficient joining strength.
  • the tube is formed into a flat shape and that an inner fin having a plurality of communication apertures formed in a scattered manner is inserted into an inner space of the tube, or in cases where the tube is formed into a flat shape and that an inner space of the tube is divided by one or a plurality of tube partitioning walls extending in a longitudinal direction of the tube and that each of the tube-partitioning walls is provided with one or a plurality of communication apertures, since the liquefied refrigerant passing through the tube can be mixed in each partitioned refrigerant passage via the communication apertures formed in the inner fin or the tube-partitioning wall, the discharging of the refrigerant from each partitioned refrigerant passage into the header can be further equalized.
  • the header includes a sacrificial zinc layer for corrosion protection formed at an external surface thereof and the zinc is.diffused into the header by heat at the time of integrally brazing the header and the tubes, corrosion protection of the header can be enhanced.
  • the corrosion protection of the header can be further enhanced.
  • a tube insertion aperture is • formed in a tube-connecting-side wall and front and rear side walls extending from the tube-connecting-side wall and that a width of the tube is the same as or generally the same as a depth of the header, machining for forming the tube insertion aperture can be simplified, resulting in remarkably improved processing efficiency thereof.
  • the assembly can be improved, and the heat exchanger can be further miniaturized.
  • each of the front and rear side walls of the header is provided with a tube-displacement-restricting piece bent toward the tube insertion aperture and fits on a lateral side surface of the tube, the displacement of the tube in the fore and aft direction and/or the dropping of the tube can be prevented.
  • the heat exchanger is preferably used as a condenser and/or an evaporator, and more preferably used as a condenser and/or an evaporator for use in car air-conditioning systems or room air-conditioning systems.

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

Abstract

Dans un échangeur thermique comportant une colonne creuse (2) et une pluralité de tubes d'échange thermique (1) communiquant fluidiquement avec ladite colonne (1), la forme en coupe transversale de la colonne (2) est constituée d'une forme transversale angulaire, notamment une forme transversale rectangulaire et une forme transversale carrée. En outre, l'espace interne de la colonne (2) est divisée en une pluralité de chambres collectrices (13) par des parois de séparation de colonne (12) se situant dans celle-ci (2), et la surface interne (14) de la paroi latérale non reliée au tube dans la chambre collectrice (13) est formée dans une surface courbée. Par conséquent, le volume interne de la colonne (2) peut être grandement réduit comparé à celui d'une colonne traditionnelle, tandis qu'on maintient une résistance aux pressions suffisante et un poids léger. Par ailleurs, on peut encore miniaturiser l'échangeur thermique et réduire la quantité de réfrigérant à utiliser. On peut aussi obtenir un échangeur thermique doté d'une excellente caractéristique de conduction thermique et d'une faible résistance au flux réfrigérant.
PCT/JP2001/009326 2000-10-25 2001-10-24 Echangeur thermique WO2002035170A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU2002212677A AU2002212677A1 (en) 2000-10-25 2001-10-24 Heat exchanger
US10/399,777 US20040031598A1 (en) 2000-10-25 2001-10-24 Heat exchanger

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2000-325119 2000-10-25
JP2000325119A JP2002130979A (ja) 2000-10-25 2000-10-25 熱交換器
US30646501P 2001-07-20 2001-07-20
US60/306,465 2001-07-20

Publications (1)

Publication Number Publication Date
WO2002035170A1 true WO2002035170A1 (fr) 2002-05-02

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PCT/JP2001/009326 WO2002035170A1 (fr) 2000-10-25 2001-10-24 Echangeur thermique

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WO (1) WO2002035170A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120186795A1 (en) * 2009-05-28 2012-07-26 Philipp Pustelnik Plate Cooler for Fluids
FR3028934A1 (fr) * 2014-11-25 2016-05-27 Valeo Systemes Thermiques Echangeur thermique
CN105674788A (zh) * 2014-11-18 2016-06-15 丹佛斯微通道换热器（嘉兴）有限公司 集流管以及换热器
EP3239636A1 (fr) * 2016-04-28 2017-11-01 Valeo Systemes Thermiques Collecteur pour échangeur de chaleur, en particulier pour un radiateur de véhicule automobile

Citations (12)

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Publication number Priority date Publication date Assignee Title
JPS63271099A (ja) * 1987-04-27 1988-11-08 Showa Alum Corp 熱交換器
JPH0133995Y2 (fr) * 1984-06-18 1989-10-16
JPH03121370U (fr) * 1990-03-24 1991-12-12
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JPH10175062A (ja) * 1996-12-14 1998-06-30 Mitsubishi Alum Co Ltd ろう付性に優れた熱交換器および該熱交換器の製造方法
JPH10185471A (ja) * 1996-12-26 1998-07-14 Showa Alum Corp 熱交換器
JPH1114288A (ja) * 1997-06-24 1999-01-22 Denso Corp 熱交換器
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JPH0525175U (ja) * 1991-08-23 1993-04-02 東洋ラジエーター株式会社 エバポレータ用熱交換器のチユーブ
JPH08226787A (ja) * 1994-11-25 1996-09-03 Behr Gmbh & Co 熱交換器及びその製造方法
JPH08170892A (ja) * 1994-12-15 1996-07-02 Nippon Climate Syst:Kk 熱交換器
JPH09310994A (ja) * 1996-05-24 1997-12-02 Calsonic Corp アルミニウム合金製熱交換器の取付ブラケット装着部
JPH1038493A (ja) * 1996-07-26 1998-02-13 Calsonic Corp アルミニウム製熱交換器及びその製造方法
JPH10175062A (ja) * 1996-12-14 1998-06-30 Mitsubishi Alum Co Ltd ろう付性に優れた熱交換器および該熱交換器の製造方法
JPH10185471A (ja) * 1996-12-26 1998-07-14 Showa Alum Corp 熱交換器
JPH1114288A (ja) * 1997-06-24 1999-01-22 Denso Corp 熱交換器
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120186795A1 (en) * 2009-05-28 2012-07-26 Philipp Pustelnik Plate Cooler for Fluids
CN105674788A (zh) * 2014-11-18 2016-06-15 丹佛斯微通道换热器（嘉兴）有限公司 集流管以及换热器
CN105674788B (zh) * 2014-11-18 2018-10-02 丹佛斯微通道换热器（嘉兴）有限公司 集流管以及换热器
FR3028934A1 (fr) * 2014-11-25 2016-05-27 Valeo Systemes Thermiques Echangeur thermique
WO2016083477A1 (fr) * 2014-11-25 2016-06-02 Valeo Systemes Thermiques Echangeur thermique
EP3239636A1 (fr) * 2016-04-28 2017-11-01 Valeo Systemes Thermiques Collecteur pour échangeur de chaleur, en particulier pour un radiateur de véhicule automobile

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