JP2009257719A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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JP2009257719A
JP2009257719A JP2008110332A JP2008110332A JP2009257719A JP 2009257719 A JP2009257719 A JP 2009257719A JP 2008110332 A JP2008110332 A JP 2008110332A JP 2008110332 A JP2008110332 A JP 2008110332A JP 2009257719 A JP2009257719 A JP 2009257719A
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plate
header
flow path
intermediate plate
header tank
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JP2008110332A
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JP5007267B2 (en
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Seiji Matsushima
誠二 松島
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Resonac Holdings Corp
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Showa Denko KK
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Priority to JP2008110332A priority Critical patent/JP5007267B2/en
Priority to DE200910018116 priority patent/DE102009018116A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—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
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • F28F9/0212—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions the partitions being separate elements attached to header boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0224—Header boxes formed by sealing end plates into covers
    • 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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers

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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

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of securing sufficient resistance against pressure of a header tank. <P>SOLUTION: The header tank 2 of a gas cooler using the heat exchanger is composed by mutually laminating and brazing an outer side plate 7, an inner side plate 8, and a middle plate 9 interposed between both plates 7, 8. A cross-sectionally substantially U-shaped outward bent part 7a opening in a middle plate 9 side is formed in a center part in a fore and aft direction of the outer side plate 7 of the header tank 2, and flat parts 7b positioned in the same plane are respectively formed in fore and aft both side portions of the outward bent part 7a. Solder flowing prevention protruding parts 38 projecting in the outward bent part 7a and extending in length directions of the middle plate 9 are formed in fore and aft both side edges of a portion facing into the outward bent part 7a in a face of the middle plate 9 facing an outer plate 7 side. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

この発明は、熱交換器に関し、さらに詳しくは、たとえばＣＯ２（二酸化炭素）などの超臨界冷媒が用いられる超臨界冷凍サイクルのガスクーラやエバポレータに好適に使用される熱交換器に関する。 The present invention relates to a heat exchanger, and more particularly to a heat exchanger suitably used for a gas cooler or an evaporator of a supercritical refrigeration cycle in which a supercritical refrigerant such as CO 2 (carbon dioxide) is used.

この明細書および特許請求の範囲において、「超臨界冷凍サイクル」とは、高圧側において、冷媒が臨界圧力を超えた超臨界状態となる冷凍サイクルを意味するものとし、「超臨界冷媒」とは、超臨界冷凍サイクルに用いられる冷媒を意味するものとする。また、この明細書および特許請求の範囲において、隣接する熱交換管どうしの間の通風間隙を流れる空気の下流側（図１に矢印Ｘで示す方向）を前、これと反対側を後というものとする。   In this specification and claims, the term “supercritical refrigeration cycle” means a refrigeration cycle in which the refrigerant is in a supercritical state exceeding the critical pressure on the high pressure side, and “supercritical refrigerant” It shall mean a refrigerant used in a supercritical refrigeration cycle. Further, in this specification and claims, the downstream side (direction indicated by arrow X in FIG. 1) of the air flowing through the ventilation gap between adjacent heat exchange tubes is the front, and the opposite side is the rear. And

超臨界冷凍サイクルに用いられる熱交換器として、互いに間隔をおいて配置された１対のヘッダタンクと、両ヘッダタンク間に、幅方向を前後方向に向けるとともにヘッダタンクの長さ方向に間隔をおいて配置され、かつ両端部がそれぞれ両ヘッダタンクに接続された複数の扁平状熱交換管と、隣接する熱交換管間の通風間隙に配置されかつ熱交換管にろう付されたフィンとを備えており、各ヘッダタンクが、両面にろう材層を有するアルミニウムブレージングシート製外側プレートと、両面にろう材層を有するアルミニウムブレージングシート製内側プレートと、これら両プレート間に介在させられたアルミニウムベア材製中間プレートとが互いに積層されてろう付されることにより構成され、ヘッダタンクに、冷媒の流れる中空状の冷媒流路を有する少なくとも１つのヘッダ部が形成され、ヘッダタンクの外側プレートの前後方向の中央部に、中間プレート側に開口する横断面略Ｕ字状の外方屈曲部が形成されているとともに、外方屈曲部の前後両側部分にそれぞれ同一平面内に位置する平坦部が形成され、内側プレートにおけるヘッダ部の冷媒流路と対応する部分に、前後方向に長い複数の管挿入穴が内側プレートの長さ方向に間隔をおいて貫通状に形成され、中間プレートに、前後方向に長くかつ内側プレートの各管挿入穴をヘッダ部の冷媒流路内に通じさせる連通穴が貫通状に形成され、中間プレートにおける同一のヘッダ部内の冷媒流路に通じる全連通穴が、中間プレートのおける隣り合う連通穴の長さ方向の中間部を切除することにより形成された連通部を介して通じさせられ、ヘッダタンクのヘッダ部の冷媒流路が、外側プレートの外方屈曲部内の内部空間からなる第１流路形成部と、当該ヘッダ部に通じる複数の連通穴およびこれらの連通穴を通じさせる連通部よりなる第２流路形成部とからなり、熱交換管の端部がヘッダタンクの内側プレートの管挿入穴内に挿入されて内側プレートにろう付されるとともに、熱交換管の端部がヘッダタンクのヘッダ部の冷媒流路内に臨んでいる熱交換器が知られている（特許文献１参照）。   As a heat exchanger used in a supercritical refrigeration cycle, a pair of header tanks arranged at a distance from each other, and between the header tanks, the width direction is directed in the front-rear direction and the distance in the length direction of the header tank. A plurality of flat heat exchange pipes whose both ends are respectively connected to the header tanks, and fins which are arranged in a ventilation gap between adjacent heat exchange pipes and brazed to the heat exchange pipes. Each header tank has an aluminum brazing sheet outer plate having a brazing layer on both sides, an aluminum brazing sheet inner plate having a brazing layer on both sides, and an aluminum bearer interposed between the two plates. The intermediate plate made of the material is laminated and brazed to each other, and the hollow refrigerant flows through the header tank. At least one header portion having a passage is formed, and an outward bent portion having a substantially U-shaped cross section that opens to the intermediate plate side is formed at the center portion in the front-rear direction of the outer plate of the header tank. Flat portions located in the same plane are formed on both front and rear side portions of the bent portion, and a plurality of tube insertion holes that are long in the front-rear direction are formed in the portion corresponding to the refrigerant flow path of the header portion of the inner plate. A through hole is formed in the intermediate plate, and is formed in the intermediate plate so as to extend in the front-rear direction and communicate with the pipe insertion holes of the inner plate into the refrigerant flow path of the header portion. All the communication holes leading to the refrigerant flow path in the same header portion in the plate are communicated through the communication portion formed by cutting out the intermediate portion in the length direction of the adjacent communication holes in the intermediate plate. The refrigerant flow path of the header portion of the header tank is made to pass through the first flow path forming portion formed of the internal space in the outward bent portion of the outer plate, the plurality of communication holes communicating with the header portion, and these communication holes. A second flow path forming portion comprising a communicating portion, and the end of the heat exchange tube is inserted into the tube insertion hole of the inner plate of the header tank and brazed to the inner plate, and the end of the heat exchange tube is A heat exchanger that faces a refrigerant flow path in a header portion of a header tank is known (see Patent Document 1).

ところで、超臨界冷凍サイクルに用いられるガスクーラやエバポレータの内圧は、フロン系冷媒が使用される冷凍サイクルに用いられる熱交換器の内圧よりもかなり高くなるので、この種の熱交換器においては、ヘッダタンクの耐圧性を向上させる目的で、外側プレートが、肉厚および強度が比較的大きいアルミニウム板を用いて製造されている。すなわち、横断面形状が形成すべき外方屈曲部の外形の横断面形状に合致した凹部を備えた雌型と、横断面形状が外方屈曲部の内形の横断面形状に合致した横断面形状を有する凸部を備えた雄型とを使用し、アルミニウム板に１度のプレス加工を施すことにより、外側プレートが製造されている。しかしながら、この場合、アルミニウム板の肉厚および強度が比較的大きいために変形が不十分となり、特許文献１記載の熱交換器のように、形成された外方屈曲部の内周面における両平坦部に連なる部分に、曲率半径が予め決められていた寸法よりも大きくなった丸みが形成される。その結果、熱交換器の製造時における外側プレートと中間プレートとのろう付時に、外側プレートの平坦部から溶け出したろう材が、外側プレートの平坦部と中間プレートとの間から冷媒流路内に流れ出すことになり、外側プレートにおける上記丸みと、中間プレートの外側プレート側を向いた面との間にフィレットが形成されない場合がある。したがって、外側プレートと中間プレートとのろう付強度が不足してヘッダタンクの耐圧性が低下するおそれがある。
特開２００５−３５１５２０号公報 By the way, the internal pressure of a gas cooler or an evaporator used in a supercritical refrigeration cycle is considerably higher than the internal pressure of a heat exchanger used in a refrigeration cycle in which a chlorofluorocarbon refrigerant is used. In order to improve the pressure resistance of the tank, the outer plate is manufactured using an aluminum plate having a relatively large thickness and strength. That is, a female mold having a recess that matches the outer cross-sectional shape of the outer bent portion to be formed, and a cross-section that matches the inner cross-sectional shape of the outer bent portion The outer plate is manufactured by using a male mold having a convex portion having a shape and pressing the aluminum plate once. However, in this case, since the thickness and strength of the aluminum plate are relatively large, the deformation becomes insufficient, and both the flat surfaces on the inner peripheral surface of the formed outward bent portion as in the heat exchanger described in Patent Document 1 are obtained. A rounded portion having a radius of curvature larger than a predetermined dimension is formed in a portion connected to the portion. As a result, when the outer plate and the intermediate plate are brazed at the time of manufacturing the heat exchanger, the brazing material that has melted from the flat portion of the outer plate enters the refrigerant flow path from between the flat portion of the outer plate and the intermediate plate. As a result, the fillet may not be formed between the roundness of the outer plate and the surface of the intermediate plate facing the outer plate. Therefore, the brazing strength between the outer plate and the intermediate plate may be insufficient, and the pressure resistance of the header tank may be reduced.
JP 2005-351520 A

この発明の目的は、上記問題を解決し、ヘッダタンクの十分な耐圧性を確保しうる熱交換器を提供することにある。   An object of the present invention is to provide a heat exchanger that solves the above-described problems and can ensure sufficient pressure resistance of the header tank.

本発明は、上記目的を達成するために以下の態様からなる。   In order to achieve the above object, the present invention comprises the following aspects.

1)互いに間隔をおいて配置された１対のヘッダタンクと、両ヘッダタンク間に、幅方向を前後方向に向けるとともにヘッダタンクの長さ方向に間隔をおいて配置され、かつ両端部がそれぞれ両ヘッダタンクに接続された複数の扁平状熱交換管とを備えており、ヘッダタンクが、外側プレートと、内側プレートと、これら両プレート間に介在させられた中間プレートとが互いに積層されてろう付されることにより構成され、ヘッダタンクの外側プレートの前後方向の中央部に、中間プレート側に開口する横断面略Ｕ字状の外方屈曲部が形成されているとともに、外方屈曲部の前後両側部分にそれぞれ同一平面内に位置する平坦部が形成されている熱交換器において、
中間プレートの外側プレート側を向いた面における外側プレートの外方屈曲部内に臨む部分の前後両側縁部に、外方屈曲部内に突出しかつ中間プレートの長さ方向にのびるろう流れ防止用凸部が形成されている熱交換器。 1) A pair of header tanks arranged at a distance from each other, and between the two header tanks, the width direction is directed in the front-rear direction and the header tank is arranged at intervals in the length direction, and both end portions are respectively A plurality of flat heat exchange pipes connected to both header tanks, and the header tank is formed by laminating an outer plate, an inner plate, and an intermediate plate interposed between the two plates. The outer bent portion of the outer side plate of the header tank is formed with an outward bent portion having a substantially U-shaped cross section that opens to the intermediate plate side. In the heat exchanger in which flat portions located in the same plane are formed on both the front and rear side portions,
Protrusions for preventing wax flow that protrude into the outer bent portion and extend in the length direction of the intermediate plate are formed on the front and rear side edges of the portion facing the outer bent portion of the outer plate on the surface facing the outer plate side of the intermediate plate. Heat exchanger being formed.

2)ろう流れ防止用凸部の突出端が、外側プレートの外方屈曲部の内周面に当接している上記1)記載の熱交換器。   2) The heat exchanger according to 1) above, wherein the protruding end of the wax flow preventing convex portion is in contact with the inner peripheral surface of the outer bent portion of the outer plate.

3)ろう流れ防止用凸部の突出高さが０．３ｍｍ以上であり、同じく前後方向の厚みが０．３ｍｍ以上である上記1)または2)記載の熱交換器。   3) The heat exchanger according to 1) or 2) above, wherein the protruding height of the wax flow preventing convex portion is 0.3 mm or more, and the thickness in the front-rear direction is also 0.3 mm or more.

4)ヘッダタンクに、冷媒の流れる中空状の冷媒流路を有する少なくとも１つのヘッダ部が形成され、内側プレートにおけるヘッダ部の冷媒流路と対応する部分に、前後方向に長い複数の管挿入穴が内側プレートの長さ方向に間隔をおいて貫通状に形成され、中間プレートに、前後方向に長くかつ内側プレートの各管挿入穴をヘッダ部の冷媒流路内に通じさせる連通穴が貫通状に形成され、熱交換管の端部がヘッダタンクの内側プレートの管挿入穴内に挿入されて内側プレートにろう付され、中間プレートにおける連通穴が形成されていない部分にろう流れ防止用凸部が形成されている上記1)〜3)のうちのいずれかに記載の熱交換器。   4) In the header tank, at least one header part having a hollow refrigerant flow path through which the refrigerant flows is formed, and a plurality of pipe insertion holes long in the front-rear direction are formed in a portion corresponding to the refrigerant flow path of the header part in the inner plate. Is formed in a penetrating shape with an interval in the length direction of the inner plate, and a communication hole that is long in the front-rear direction and connects each tube insertion hole of the inner plate into the refrigerant flow path of the header portion is formed in the intermediate plate. The end portion of the heat exchange pipe is inserted into the pipe insertion hole of the inner plate of the header tank and brazed to the inner plate, and the convex portion for preventing brazing flow is formed in the portion of the intermediate plate where the communication hole is not formed. The heat exchanger according to any one of 1) to 3), which is formed.

上記1)の熱交換器によれば、中間プレートの外側プレート側を向いた面における外側プレートの外方屈曲部内に臨む部分の前後両側縁部に、外方屈曲部内に突出しかつ中間プレートの長さ方向にのびるろう流れ防止用凸部が形成されているので、熱交換器の製造時における外側プレートと中間プレートとのろう付時に、ろう流れ防止用凸部の働きによって、溶け出したろう材が外側プレートの平坦部と中間プレートとの間から内方に流れ出すことが防止され、溶融ろう材は、外方屈曲部の内周面における両平坦部に連なる部分、中間プレートの外側プレート側を向いた面における外方屈曲部内に臨む部分、およびろう流れ防止用凸部により囲まれた空間内に溜まる。したがって、外側プレートの内周面における両平坦部に連なる部分と、中間プレートの外側プレート側を向いた面との間に確実にフィレットが形成され、外側プレートと中間プレートとのろう付強度が増大してヘッダタンクの耐圧性が向上する。   According to the heat exchanger of 1) above, the side of the intermediate plate facing the outer plate side protrudes into the outer bent portion at the front and rear side edges of the portion facing the outer bent portion of the outer plate and the length of the intermediate plate. Since the convex portion for preventing brazing flow extending in the vertical direction is formed, the brazing filler metal melted out by the function of the convex portion for brazing flow prevention when the outer plate and the intermediate plate are brazed at the time of manufacturing the heat exchanger. It is prevented from flowing inward from between the flat portion of the outer plate and the intermediate plate, and the molten brazing material is directed to the portion of the inner peripheral surface of the outer bent portion that is connected to both flat portions, the outer plate side of the intermediate plate. It accumulates in the space surrounded by the portion facing the outward bent portion and the convex portion for preventing wax flow. Therefore, a fillet is reliably formed between the portion of the inner peripheral surface of the outer plate that is connected to both flat portions and the surface of the intermediate plate facing the outer plate, and the brazing strength between the outer plate and the intermediate plate is increased. Thus, the pressure resistance of the header tank is improved.

上記2)の熱交換器によれば、ろう流れ防止用凸部の突出端が、外側プレートの外方屈曲部の内周面にろう付されることになるので、外側プレートの内周面における両平坦部に連なる部分と、中間プレートの外側プレート側を向いた面との間に、比較的曲率半径の大きな丸みが形成されていたとしても、ヘッダタンクの耐圧性が一層向上する。すなわち、外側プレートの内周面における両平坦部に連なる部分と、中間プレートの外側プレート側を向いた面との間に、比較的曲率半径の大きな丸みが形成されていた場合、当該丸みの部分において、外側プレートに外向きの力が加わってヘッダタンクの耐圧性が低下するおそれがあるが、ろう流れ防止用凸部の突出端が、外側プレートの外方屈曲部の内周面にろう付されていると、上記丸みの部分において、外側プレートに外向きの力が加わることが防止される。   According to the heat exchanger of the above 2), the protruding end of the convex portion for preventing brazing flow is brazed to the inner peripheral surface of the outer bent portion of the outer plate. Even if a round having a relatively large radius of curvature is formed between a portion connected to both flat portions and a surface of the intermediate plate facing the outer plate, the pressure resistance of the header tank is further improved. That is, if a round having a relatively large radius of curvature is formed between the portion of the inner peripheral surface of the outer plate that is continuous with the two flat portions and the surface of the intermediate plate that faces the outer plate, In this case, an outward force may be applied to the outer plate to reduce the pressure resistance of the header tank, but the protruding end of the brazing flow prevention convex portion is brazed to the inner peripheral surface of the outer bent portion of the outer plate. In this case, an outward force is prevented from being applied to the outer plate at the rounded portion.

上記3)の熱交換器によれば、熱交換器の製造時における外側プレートと中間プレートとのろう付時に、ろう流れ防止用凸部の働きによって、溶け出したろう材が外側プレートの平坦部と中間プレートとの間から内方に流れ出すことが確実に防止される。   According to the heat exchanger of the above 3), when the outer plate and the intermediate plate are brazed at the time of manufacturing the heat exchanger, the melted brazing material is removed from the flat portion of the outer plate by the action of the convex portion for preventing brazing flow. It is reliably prevented from flowing inward from between the intermediate plate.

以下、この発明の実施形態を、図面を参照して説明する。この実施形態は、この発明による熱交換器を、超臨界冷凍サイクルのガスクーラに適用したものである。   Embodiments of the present invention will be described below with reference to the drawings. In this embodiment, the heat exchanger according to the present invention is applied to a gas cooler of a supercritical refrigeration cycle.

なお、以下の説明において、図１および図２の上下、左右をそれぞれ上下、左右というものとする。   In the following description, the top and bottom and the left and right in FIGS. 1 and 2 are referred to as the top and bottom and the left and right, respectively.

さらに、以下の説明において、「アルミニウム」という用語には、純アルミニウムの他にアルミニウム合金を含むものとする。   Furthermore, in the following description, the term “aluminum” includes aluminum alloys in addition to pure aluminum.

図１および図２はこの発明による熱交換器を適用したガスクーラの全体構成を示し、図３〜図７はその要部の構成を示す。   1 and 2 show the overall configuration of a gas cooler to which a heat exchanger according to the present invention is applied, and FIGS. 3 to 7 show the configuration of the main part thereof.

図１および図２において、超臨界冷媒、たとえばＣＯ２を使用する超臨界冷凍サイクルのガスクーラ(1)は、左右方向に間隔をおいて配置されかつ上下方向にのびる２つのヘッダタンク(2)(3)と、両ヘッダタンク(2)(3)間に、上下方向に間隔をおくとともに幅方向を前後方向に向けて配置された複数の扁平状熱交換管(4)と、隣接する熱交換管(4)どうしの間の通風間隙、および上下両端の熱交換管(4)の外側に配置されて熱交換管(4)にろう付されたコルゲートフィン(5)と、上下両端のコルゲートフィン(5)の外側にそれぞれ配置されてコルゲートフィン(5)にろう付されたアルミニウム製サイドプレート(6)とを備えている。なお、この実施形態において、右側のヘッダタンク(2)を第１ヘッダタンク、左側のヘッダタンク(3)を第２ヘッダタンクというものとする。 1 and 2, a gas cooler (1) of a supercritical refrigeration cycle that uses a supercritical refrigerant, for example, CO 2 , is arranged with two header tanks (2) (2) that are spaced apart in the left-right direction and extend in the up-down direction. 3) and a plurality of flat heat exchange pipes (4) arranged between the header tanks (2) and (3) in the vertical direction and with the width direction oriented in the front-rear direction, and adjacent heat exchange Corrugated fins (5) disposed outside the heat exchange tubes (4) at the upper and lower ends and brazed to the heat exchange tubes (4), and corrugated fins at the upper and lower ends. An aluminum side plate (6) disposed on the outside of (5) and brazed to the corrugated fin (5). In this embodiment, the right header tank (2) is referred to as a first header tank, and the left header tank (3) is referred to as a second header tank.

第１ヘッダタンク(2)は、両面にろう材層を有するブレージングシート、ここではアルミニウムブレージングシートから形成された外側プレート(7)と、両面にろう材層を有するブレージングシート、ここではアルミニウムブレージングシートから形成された内側プレート(8)と、金属ベア材、ここではアルミニウムベア材から形成されかつ外側プレート(7)と内側プレート(8)との間に介在させられて外側プレート(7)および内側プレート(8)にろう付された中間プレート(9)とを備えており、内部が冷媒流路(10a)となった入口ヘッダ部(10A)および内部が冷媒流路(10b)となった出口ヘッダ部(10B)が上下に並んで設けられている。   The first header tank (2) comprises a brazing sheet having a brazing material layer on both sides, here an outer plate (7) formed from an aluminum brazing sheet, and a brazing sheet having a brazing material layer on both sides, here an aluminum brazing sheet. An inner plate (8) formed from a metal bare material, here an aluminum bear material and interposed between the outer plate (7) and the inner plate (8) An intermediate plate (9) brazed to the plate (8), an inlet header portion (10A) having an internal refrigerant flow path (10a) and an outlet having an internal refrigerant flow path (10b) Header sections (10B) are provided side by side.

図２〜図５に示すように、第１ヘッダタンク(2)の外側プレート(7)の前後方向（幅方向）の中央部に、左側（中間プレート(9)側）に開口した横断面略Ｕ字状の外方屈曲部(7a)が全長にわたって形成されている。外側プレート(7)の外方屈曲部(7a)の内周面は横断面円弧状である。外側プレート(7)の外方屈曲部(7a)の前後両側部分はそれぞれ同一平面内に位置する平坦部(7b)となっている。外方屈曲部(7a)の内周面における両平坦部(7b)に連なる部分には、比較的大きな曲率半径を有する丸み(37)が形成されている（図７参照）。また、外側プレート(7)の外方屈曲部(7a)の左側を向いた開口は中間プレート(9)により塞がれている。外側プレート(7)の上下両端部および上下方向の中央部に、それぞれ前後方向に長くかつ一方の平坦部(7b)から他方の平坦部(7b)に至る貫通穴(25)が形成されている。   As shown in FIGS. 2 to 5, the transverse section opened to the left side (intermediate plate (9) side) at the center in the front-rear direction (width direction) of the outer plate (7) of the first header tank (2) A U-shaped outward bent portion (7a) is formed over the entire length. The inner peripheral surface of the outward bent portion (7a) of the outer plate (7) has an arc shape in cross section. The front and rear side portions of the outward bent portion (7a) of the outer plate (7) are flat portions (7b) located in the same plane. A round portion (37) having a relatively large radius of curvature is formed in a portion of the inner peripheral surface of the outward bent portion (7a) that is continuous with both flat portions (7b) (see FIG. 7). Further, the opening facing the left side of the outward bent portion (7a) of the outer plate (7) is closed by the intermediate plate (9). Through holes (25) extending in the front-rear direction and extending from one flat portion (7b) to the other flat portion (7b) are formed at both the upper and lower end portions and the vertical center portion of the outer plate (7). .

外側プレート(7)の外方屈曲部(7a)の頂部における上端部の貫通穴(25)よりも若干下方の位置に冷媒入口(12)が形成されており、外方屈曲部(7a)外面に、冷媒入口(12)に通じる冷媒流入路(14)を有する金属製、ここではアルミニウムベア材製の直方体状入口部材(13)が、外側プレート(7)外面のろう材を利用してろう付されている。また、外方屈曲部(7a)の頂部における下端部の貫通穴(25)よりも若干上方の位置に冷媒出口(15)が形成されており、外方屈曲部(7a)外面に、冷媒出口(15)に通じる冷媒流出路(17)を有する金属製、ここではアルミニウムベア材製の直方体状出口部材(16)が、外側プレート(7)外面のろう材を利用してろう付されている。外側プレート(7)は、両面にろう材層を有するアルミニウムブレージングシートにプレス加工を施することにより形成されている。   A refrigerant inlet (12) is formed at a position slightly below the through hole (25) at the upper end of the top of the outer bent portion (7a) of the outer plate (7), and the outer surface of the outer bent portion (7a) In addition, a rectangular parallelepiped inlet member (13) made of metal having a refrigerant inflow passage (14) communicating with the refrigerant inlet (12), here made of aluminum bare material, is made of brazing material on the outer surface of the outer plate (7). It is attached. Further, a refrigerant outlet (15) is formed at a position slightly above the lower end through hole (25) at the top of the outer bent portion (7a), and a refrigerant outlet is formed on the outer surface of the outer bent portion (7a). A rectangular parallelepiped outlet member (16) made of metal having a refrigerant outflow passage (17) leading to (15), here made of aluminum bare material, is brazed using a brazing material on the outer surface of the outer plate (7). . The outer plate (7) is formed by pressing an aluminum brazing sheet having a brazing material layer on both sides.

入口部材(13)および出口部材(16)には、その後面から前方にのびるねじ穴(35)(36)がそれぞれ形成されている。入口部材(13)のねじ穴(35)は、超臨界冷凍サイクルにおいて、圧縮機からのびる配管の先端部に取り付けられたジョイント部材をねじ止めするのに用いられ、出口部材(16)のねじ穴(36)は、中間熱交換器からのびる配管の先端部に取り付けられたジョイント部材をねじ止めするのに用いられる。   The inlet member (13) and the outlet member (16) are respectively formed with screw holes (35) and (36) extending forward from the rear surface. In the supercritical refrigeration cycle, the screw hole (35) of the inlet member (13) is used to screw the joint member attached to the tip of the pipe extending from the compressor, and the screw hole of the outlet member (16). (36) is used for screwing the joint member attached to the tip of the pipe extending from the intermediate heat exchanger.

第１ヘッダタンク(2)の内側プレート(8)には、前後方向に長い複数の貫通状管挿入穴(18)が、上下方向に間隔をおいて形成されている。上半部の複数の管挿入穴(18)は、入口ヘッダ部(10A)の冷媒流路(10a)の上下方向の範囲内に形成され、同じく下半部の複数の管挿入穴(18)は、出口ヘッダ部(10B)の冷媒流路(10b)の上下方向の範囲内に形成されている。管挿入穴(18)の前後方向の長さは、外方屈曲部(7a)の前後方向の幅よりも若干長く、管挿入穴(18)の前後両端部は外方屈曲部(7a)の前後両側縁よりも外方に突出している。また、内側プレート(8)の前後両側縁部に、それぞれ右方に突出して先端が外側プレート(7)の外面まで至り、かつ外側プレート(7)および中間プレート(9)の前後両側面を覆う側面被覆壁(19)が一体に形成され、外側プレート(7)および中間プレート(9)の前後両側面にろう付されている。各側面被覆壁(19)の突出端の上下両端部および上下方向中央部に、それぞれ前後方向内方に突出しかつ外側プレート(7)の外面に係合する係合爪(21)が一体に形成され、外側プレート(7)にろう付されている。上下両端部の係合爪(21)は、外側プレート(7)の貫通穴(25)の前後両端部を覆っている。なお、図５に実線で示すように、係合爪(21)は、３つのプレート(7)(8)(9)を組み合わせる前の状態では、側面被覆壁(19)に真っ直ぐに連なって左右方向外方にのびている。真っ直ぐな係合爪を(21A)で示す。そして、３つのプレート(7)(8)(9)を組み合わせた後に係合爪(21A)を前後方向内方に曲げることによって３つのプレート(7)(8)(9)が仮止めされる。内側プレート(8)は、両面にろう材層を有するアルミニウムブレージングシートにプレス加工を施すことにより形成されている。   In the inner plate (8) of the first header tank (2), a plurality of through-tube insertion holes (18) elongated in the front-rear direction are formed at intervals in the up-down direction. The plurality of tube insertion holes (18) in the upper half are formed in the vertical range of the refrigerant flow path (10a) of the inlet header portion (10A), and are also the plurality of tube insertion holes (18) in the lower half. Is formed within a range in the vertical direction of the refrigerant flow path (10b) of the outlet header portion (10B). The length in the front-rear direction of the tube insertion hole (18) is slightly longer than the width in the front-rear direction of the outward bent portion (7a), and both front and rear ends of the tube insertion hole (18) are formed in the outer bent portion (7a). Projects outward from both front and rear edges. Moreover, it protrudes rightward on both front and rear edges of the inner plate (8), the tip reaches the outer surface of the outer plate (7), and covers both the front and rear side surfaces of the outer plate (7) and the intermediate plate (9). A side covering wall (19) is integrally formed and is brazed to the front and rear side surfaces of the outer plate (7) and the intermediate plate (9). Engaging claws (21) that protrude inward in the front-rear direction and engage with the outer surface of the outer plate (7) are integrally formed at the upper and lower ends and the center in the vertical direction of the protruding end of each side covering wall (19). And brazed to the outer plate (7). The engaging claws (21) at the upper and lower ends cover the front and rear ends of the through hole (25) of the outer plate (7). As shown by the solid line in FIG. 5, the engaging claw (21) is connected to the side covering wall (19) straight before the three plates (7), (8) and (9) are combined. Extends outward in the direction. A straight engaging claw is indicated by (21A). Then, after the three plates (7), (8), and (9) are combined, the three plates (7), (8), and (9) are temporarily fixed by bending the engaging claw (21A) inward in the front-rear direction. . The inner plate (8) is formed by pressing an aluminum brazing sheet having a brazing filler metal layer on both sides.

第１ヘッダタンク(2)の中間プレート(9)には、前後方向に長くかつ内側プレート(8)の管挿入穴(18)を入口ヘッダ部(10A)および出口ヘッダ部(10B)の冷媒流路(10a)(10b)内に通じさせる複数の連通穴(22)が貫通状に形成されている。各連通穴(22)は管挿入穴(18)よりも一回り大きくなっている。中間プレート(9)の左右方向外面における前後方向の中央部に、左右方向内側に凹みかつ左右方向外方に開口した横断面円弧状の凹溝(23)が全長にわたって形成されている。また、中間プレート(9)の外側プレート(7)を向いた面における凹溝(23)の前後両側部分に、それぞれ上下方向（中間プレート(9)の長さ方向）にのびるとともに左右方向外方に突出したろう流れ防止用凸部(38)が一体に形成されている。ろう流れ防止用凸部(38)の前後方向内面の横断面形状は、凹溝(23)の内周面の横断面形状と同一曲率を有する円弧状であり、凹溝(23)の内周面に滑らかに連なっている。また、ろう流れ防止用凸部(38)は、外側プレート(7)の外方屈曲部(7a)内に嵌っており、その突出端は外方屈曲部(7a)の内周面における丸み(37)の前後方向内側縁部に当接している。そして、外側プレート(7)の丸み(37)と、中間プレート(9)の左右方向外側面およびろう流れ防止用凸部(38)の前後方向外側面との間にろう溜用空間(39)が形成されており（図７参照）、ろう溜用空間(39)内に外側プレート(7)の平坦部(7b)の左右方向内側面から溶け出したろう材からなるフィレット（図示略）が形成されている。さらに、中間プレート(9)の上下両端部および上下方向の中央部に、外側プレート(7)の貫通穴(25)と対応するように、それぞれ前後方向に長くかつ貫通穴(25)と同一の幅および長さを有する貫通穴(26)が形成されている。外側プレート(7)の貫通穴(25)と中間プレート(9)の貫通穴(26)とによって、貫通状の仕切板挿入穴(27)が、両プレート(7)(9)に跨るように形成されている。各仕切板挿入穴(27)内に仕切板(11)が挿入されることによって、外側プレート(7)および中間プレート(9)の上下両端部および上下方向の中央部に仕切板(11)が配置されている。なお、凹溝(23)およびろう流れ防止用凸部(38)は、連通穴(22)および貫通穴(26)によって分断されており、凹溝(23)およびろう流れ防止用凸部(38)は連通穴(22)および貫通穴(26)が形成されていない部分に設けられていることになる。   In the intermediate plate (9) of the first header tank (2), the pipe insertion hole (18) of the inner plate (8) that is long in the front-rear direction is provided with the refrigerant flow in the inlet header portion (10A) and the outlet header portion (10B). A plurality of communication holes (22) communicating with the passages (10a) and (10b) are formed in a penetrating manner. Each communication hole (22) is one size larger than the tube insertion hole (18). A groove (23) having a circular cross section that is recessed inward in the left-right direction and opened outward in the left-right direction is formed over the entire length at the center in the front-rear direction on the outer surface in the left-right direction of the intermediate plate (9). In addition, both the front and rear sides of the groove (23) on the surface of the intermediate plate (9) facing the outer plate (7) extend in the vertical direction (length direction of the intermediate plate (9)) and outward in the horizontal direction. A convex portion (38) for preventing brazing flow that protrudes in the shape is integrally formed. The cross-sectional shape of the inner surface in the front-rear direction of the convex portion for preventing brazing flow (38) is an arc shape having the same curvature as the cross-sectional shape of the inner peripheral surface of the concave groove (23), and the inner periphery of the concave groove (23) Smoothly connected to the surface. Further, the wax flow preventing convex portion (38) is fitted in the outer bent portion (7a) of the outer plate (7), and its protruding end is rounded on the inner peripheral surface of the outer bent portion (7a) ( 37) is in contact with the inner edge in the front-rear direction. Then, a brazing reservoir space (39) between the roundness (37) of the outer plate (7) and the outer lateral surface of the intermediate plate (9) and the outer circumferential surface of the brazing flow prevention convex portion (38). Is formed (see FIG. 7), and a fillet (not shown) made of a brazing material melted from the left and right inner surfaces of the flat portion (7b) of the outer plate (7) is formed in the brazing reservoir space (39). Has been. Furthermore, the upper and lower ends of the intermediate plate (9) and the center in the vertical direction are respectively long in the front-rear direction and the same as the through-hole (25) so as to correspond to the through-hole (25) of the outer plate (7). A through hole (26) having a width and a length is formed. With the through hole (25) of the outer plate (7) and the through hole (26) of the intermediate plate (9), the penetrating partition plate insertion hole (27) straddles both plates (7) and (9). Is formed. By inserting the partition plate (11) into each partition plate insertion hole (27), the partition plate (11) is attached to the upper and lower ends of the outer plate (7) and the intermediate plate (9) and the center in the vertical direction. Has been placed. The concave groove (23) and the wax flow preventing convex portion (38) are divided by the communication hole (22) and the through hole (26). ) Is provided in a portion where the communication hole (22) and the through hole (26) are not formed.

仕切板(11)は両面にろう材層を有するアルミニウムブレージングシートにより形成されたものであり、各仕切板挿入穴(27)内に外側から挿入され、仕切板(11)の前後両側縁部が外側プレート(7)および中間プレート(9)にろう付され、同じく左右方向内側縁部が内側プレート(8)にろう付され、さらに仕切板(11)の上下両面が外側プレート(7)および中間プレート(9)にろう付されている。また、内側プレート(8)の係合爪(21)が、外側プレート(7)の貫通穴(25)、すなわち仕切板挿入穴(27)と対応する位置に、貫通穴(25)（仕切板挿入穴(27)）の前後両端部を覆うように形成されていることにより、係合爪(21)は仕切板(11)の前後両端部の外面にも係合し、仕切板(11)にろう付されている。そして、各仕切板挿入穴(27)内に仕切板(11)が挿入されることによって、外側プレート(7)および中間プレート(9)の上下両端部および上下方向の中央部に仕切板(11)が配置され、これにより外側プレート(7)の外方屈曲部(7a)の内部空間(24)の上下両端開口、および中間プレート(9)の凹溝(23)の上下両端開口が仕切板(11)により閉鎖されるとともに、外方屈曲部(7a)の内部空間(24)および中間プレート(9)の凹溝(23)が長さ方向の中央部において仕切板(11)により上下に区画されている。上下両端の仕切板(11)と中央部の仕切板(11)との間の部分において、内側プレート(8)の上半部の複数の管挿入穴(18)および下半部の複数の管挿入穴(18)が形成されている。   The partition plate (11) is formed of an aluminum brazing sheet having a brazing filler metal layer on both sides, inserted from the outside into each partition plate insertion hole (27), and the front and rear side edges of the partition plate (11) are The outer plate (7) and the intermediate plate (9) are brazed, and the left and right inner edges are also brazed to the inner plate (8). It is brazed to the plate (9). In addition, the engagement claw (21) of the inner plate (8) has a through hole (25) (partition plate) at a position corresponding to the through hole (25) of the outer plate (7), that is, the partition plate insertion hole (27). Since the insertion holes (27)) are formed so as to cover both front and rear ends, the engaging claws (21) are also engaged with the outer surfaces of the front and rear ends of the partition plate (11), and the partition plate (11) It is brazed. Then, by inserting the partition plate (11) into each partition plate insertion hole (27), the partition plate (11) is formed at the upper and lower ends of the outer plate (7) and the intermediate plate (9) and at the center in the vertical direction. ) Is arranged so that the upper and lower end openings of the inner space (24) of the outward bent portion (7a) of the outer plate (7) and the upper and lower end openings of the concave groove (23) of the intermediate plate (9) are separated from each other. (11) and the inner space (24) of the outward bent portion (7a) and the concave groove (23) of the intermediate plate (9) are vertically moved by the partition plate (11) in the central portion in the length direction. It is partitioned. In the portion between the upper and lower partition plates (11) and the central partition plate (11), the inner plate (8) upper half of the plurality of tube insertion holes (18) and the lower half of the plurality of tubes An insertion hole (18) is formed.

第１ヘッダタンク(2)の入口ヘッダ部(10A)は、外側プレート(7)、内側プレート(8)および中間プレート(9)における上下方向中央部の仕切板(11)よりも上側の部分により形成され、同じく出口ヘッダ部(10B)は、外側プレート(7)、内側プレート(8)および中間プレート(9)における上下方向中央部の仕切板(11)よりも下側の部分により形成されている。第１ヘッダタンク(2)の入口ヘッダ部(10A)および出口ヘッダ部(10B)の冷媒流路(10a)(10b)は、上下両端の仕切板(11)と上下方向中央部中央部の仕切板(11)との間において、それぞれ外側プレート(7)の左右方向内面（中間プレート(9)側を向いた面）に形成され、かつ第１ヘッダタンク(2)の長さ方向にのびるとともに外側に凹んだ第１流路形成部(28)(29)と、中間プレート(9)の左右方向外面（外側プレート(7)を向いた面）における各第１流路形成部(28)(29)と対応する部分にそれぞれ形成され、かつ第１ヘッダタンク(2)の長さ方向にのびるとともに内側に凹んだ第２流路形成部(31)(32)とからなる。外側プレート(7)の第１流路形成部(28)(29)は、外方屈曲部(7a)の内部空間(24)における上下両端の仕切板(11)と上下方向中央部の仕切板(11)との間に存在する部分からなり、中間プレート(9)の第２流路形成部(31)(32)は、凹溝(23)における上下両端の仕切板(11)と上下方向中央部の仕切板(11)との間に存在する部分からなる。外側プレート(7)の第１流路形成部(28)(29)および中間プレート(9)の第２流路形成部(31)(32)の内周面の横断面形状は全体に円弧状であり、それぞれ１つの円弧部(28a)(29a)(31a)(32a)を有している。   The inlet header portion (10A) of the first header tank (2) is located above the partition plate (11) in the vertical center of the outer plate (7), inner plate (8) and intermediate plate (9). Similarly, the outlet header portion (10B) is formed by a portion below the partition plate (11) at the center in the vertical direction in the outer plate (7), the inner plate (8) and the intermediate plate (9). Yes. The refrigerant passages (10a) and (10b) of the inlet header portion (10A) and the outlet header portion (10B) of the first header tank (2) are divided into a partition plate (11) at both upper and lower ends and a partition between the central portion in the vertical direction. Formed on the left and right inner surfaces (surface facing the intermediate plate (9) side) of the outer plate (7) between the plate (11) and extending in the length direction of the first header tank (2) The first flow path forming portions (28), (29) that are recessed outward, and the first flow path forming portions (28) (28) (on the left and right outer surfaces (the surfaces facing the outer plate (7)) of the intermediate plate (9) 29) and a second flow path forming portion (31) (32) formed in a portion corresponding to the length of the first header tank (2) and recessed inward. The first flow path forming portions (28), (29) of the outer plate (7) are divided into a partition plate (11) at both upper and lower ends and a partition plate at the center in the vertical direction in the internal space (24) of the outward bent portion (7a). The second flow path forming portions (31), (32) of the intermediate plate (9) are located between the upper and lower partition plates (11) and the vertical direction of the concave groove (23). It consists of the part which exists between the partition plates (11) in the center. The cross-sectional shapes of the inner peripheral surfaces of the first flow path forming portions (28) and (29) of the outer plate (7) and the second flow path forming portions (31) and (32) of the intermediate plate (9) are generally circular arcs. Each having one arc portion (28a) (29a) (31a) (32a).

図２および図６に示すように、第２ヘッダタンク(3)は、第１ヘッダタンク(2)とほぼ同様な構成であり、同一物および同一部分に同一符号を付す。両ヘッダタンク(2)(3)は、内側プレート(8)どうしが対向するように配置されている。   As shown in FIGS. 2 and 6, the second header tank (3) has substantially the same configuration as the first header tank (2), and the same components and the same parts are denoted by the same reference numerals. Both header tanks (2) and (3) are arranged so that the inner plates (8) face each other.

第２ヘッダタンク(3)の外側プレート(7)および中間プレート(9)には上下両端部のみに仕切板(11)が配置されており、外側プレート(7)の外方屈曲部(7a)の内部空間(24)は、上下両端開口のみが仕切板(11)により閉鎖されている。これにより、外側プレート(7)の外方屈曲部(7a)の内部空間(24)および中間プレート(9)の凹溝(23)は上下に区画されていない。その結果、第２ヘッダタンク(3)には、第１ヘッダタンク(2)の入口ヘッダ部(10A)および出口ヘッダ部(10B)に跨るように、内部が冷媒流路(20a)となった１つの中間ヘッダ部(20)が形成されている。なお、外側プレート(7)の外方屈曲部(7)に冷媒入口および冷媒出口が形成されていない。   The outer plate (7) and the intermediate plate (9) of the second header tank (3) are provided with partition plates (11) only at both upper and lower ends, and the outer bent portion (7a) of the outer plate (7). In the internal space (24), only upper and lower end openings are closed by the partition plate (11). Thereby, the internal space (24) of the outward bending part (7a) of the outer plate (7) and the concave groove (23) of the intermediate plate (9) are not partitioned vertically. As a result, the inside of the second header tank (3) became a refrigerant flow path (20a) so as to straddle the inlet header portion (10A) and the outlet header portion (10B) of the first header tank (2). One intermediate header portion (20) is formed. Note that the refrigerant inlet and the refrigerant outlet are not formed in the outward bent portion (7) of the outer plate (7).

第２ヘッダタンク(3)の内側プレート(8)のすべての管挿入穴(18)は、中間ヘッダ部(20)の冷媒流路(20a)の上下方向の範囲、すなわち上下両端の仕切板(11)間に形成されており、内側プレート(8)のすべての管挿入穴(18)は、中間プレート(9)のすべての連通穴(22)を介して、中間ヘッダ部(20)内の冷媒流路(20a)に通じさせられている。   All the pipe insertion holes (18) of the inner plate (8) of the second header tank (3) are in the vertical range of the refrigerant flow path (20a) of the intermediate header portion (20), that is, the partition plates ( 11), and all the tube insertion holes (18) of the inner plate (8) pass through all the communication holes (22) of the intermediate plate (9) in the intermediate header section (20). The refrigerant channel (20a) is communicated.

第２ヘッダタンク(3)の中間ヘッダ部(20)は、外側プレート(7)、内側プレート(8)および中間プレート(9)における上下の仕切板(11)間の部分により形成されている。第２ヘッダタンク(3)の中間ヘッダ部(20)の冷媒流路(20a)は、上下両端の仕切板(11)の間において、それぞれ外側プレート(7)の左右方向内面（中間プレート(9)側を向いた面）に形成され、かつ第１ヘッダタンク(2)の長さ方向にのびるとともに外側に凹んだ第１流路形成部(33)と、中間プレート(9)の左右方向外面（外側プレート(7)を向いた面）における第１流路形成部(33)と対応する部分に形成され、かつ第２ヘッダタンク(3)の長さ方向にのびるとともに内側に凹んだ第２流路形成部(34)とからなる。外側プレート(7)の第１流路形成部(33)は、外方屈曲部(7a)の内部空間(24)における上下両端の仕切板(11)の間に存在する部分からなり、中間プレート(9)の第２流路形成部(34)は、凹溝(23)における上下両端の仕切板(11)の間に存在する部分からなる。外側プレート(7)の第１流路形成部(33)および中間プレート(9)の第２流路形成部(34)の内周面の横断面形状は、第１ヘッダタンク(2)の外側プレート(7)の第１流路形成部(28)(29)および中間プレート(9)の第２流路形成部(31)(32)の場合と同一であり、１つの円弧部(33a)(34a)を有している（図７参照）。   The intermediate header portion (20) of the second header tank (3) is formed by a portion between the upper and lower partition plates (11) in the outer plate (7), the inner plate (8) and the intermediate plate (9). The refrigerant flow path (20a) of the intermediate header portion (20) of the second header tank (3) is provided between the partition plates (11) at the upper and lower ends, respectively, on the inner surface (intermediate plate (9 ) Side surface) and the first header tank (2) extending in the length direction and recessed outwardly, and the left and right outer surface of the intermediate plate (9) A second portion formed in a portion corresponding to the first flow path forming portion (33) on the surface facing the outer plate (7) and extending in the length direction of the second header tank (3) and recessed inward. And a flow path forming part (34). The first flow path forming portion (33) of the outer plate (7) is composed of a portion existing between the upper and lower partition plates (11) in the inner space (24) of the outer bent portion (7a). The second flow path forming portion (34) of (9) is formed by a portion existing between the partition plates (11) at the upper and lower ends in the concave groove (23). The cross-sectional shape of the inner peripheral surface of the first flow path forming portion (33) of the outer plate (7) and the second flow path forming portion (34) of the intermediate plate (9) is the outer side of the first header tank (2). It is the same as the case of the first flow path forming portions (28), (29) of the plate (7) and the second flow path forming portions (31), (32) of the intermediate plate (9), and one arc portion (33a) (Refer to FIG. 7).

熱交換管(4)は、金属、ここではアルミニウム製押出形材からなり、前後方向に幅広の扁平状で、その内部に長さ方向にのびる複数の冷媒通路(4a)が並列状に形成されている。熱交換管(4)の両端部は、それぞれ両ヘッダタンク(2)(3)の管挿入穴(18)に挿入された状態で、内側プレート(8)のろう材層を利用して内側プレート(8)にろう付されている。なお、熱交換管(4)の両端は中間プレート(9)の厚さ方向の中間部まで連通穴(22)内に入り込んでおり、入口ヘッダ部(10A)、出口ヘッダ部(10B)および中間ヘッダ部(20)の冷媒流路(10a)(10b)(20a)内に突出している。すべての熱交換管(4)は、右端部が第１ヘッダタンク(2)の入口ヘッダ部(10A)の冷媒流路(10a)に通じるとともに左端部が第２ヘッダタンク(3)の中間ヘッダ部(20)の冷媒流路(20a)の上半部に通じる複数の熱交換管(4)からなる熱交換管群と、右端部が第１ヘッダタンク(2)の出口ヘッダ部(10B)の冷媒流路(10b)に通じるとともに左端部が第２ヘッダタンク(3)の中間ヘッダ部(20)の冷媒流路(20a)の下半部に通じる複数の熱交換管(4)からなる熱交換管群とに分けられることにより、第１および第２の２つのパス(P1)(P2)に区分されており、各パス(P1)(P2)を構成する全ての熱交換管(4)における冷媒の流れ方向が同一となっているとともに、２つのパス(P1)(P2)の熱交換管(4)における冷媒の流れ方向が異なっている。   The heat exchange pipe (4) is made of an extruded shape made of metal, here aluminum, and has a flat shape that is wide in the front-rear direction, and a plurality of refrigerant passages (4a) extending in the length direction are formed in parallel in the inside. ing. Both ends of the heat exchange pipe (4) are inserted into the pipe insertion holes (18) of the header tanks (2) and (3), respectively, and the inner plate (8) is used for the inner plate using the brazing material layer. It is brazed to (8). Note that both ends of the heat exchange pipe (4) enter the communication hole (22) up to the middle part in the thickness direction of the intermediate plate (9), and the inlet header part (10A), the outlet header part (10B) and the middle part It protrudes into the refrigerant flow path (10a) (10b) (20a) of the header part (20). All the heat exchange pipes (4) have a right end portion that leads to the refrigerant flow path (10a) of the inlet header portion (10A) of the first header tank (2) and a left end portion that is an intermediate header of the second header tank (3). A heat exchange pipe group consisting of a plurality of heat exchange pipes (4) communicating with the upper half of the refrigerant flow path (20a) of the section (20), and an outlet header section (10B) of the first header tank (2) at the right end. A plurality of heat exchange pipes (4) communicating with the refrigerant flow path (10b) of the second header tank (3) and communicating with the lower half of the refrigerant flow path (20a) of the intermediate header section (20) of the second header tank (3). By dividing into heat exchange pipe groups, it is divided into first and second two paths (P1) (P2), and all the heat exchange pipes that constitute each path (P1) (P2) (4 ) Are the same in the refrigerant flow direction, and the refrigerant flow directions in the heat exchange pipes (4) of the two paths (P1) and (P2) are different.

ガスクーラ(1)はすべての部品を組み合わせて一括ろう付することにより製造される。ガスクーラ(1)の製造時における外側プレート(7)と中間プレート(9)のろう付の際に、ろう流れ防止用凸部(38)の働きによって、外側プレート(7)から溶け出した溶融ろう材が、外側プレート(7)の平坦部(7b)と中間プレート(9)との間から冷媒流路(10a)(10b)(20a)内に流れ出すことが防止され、溶融ろう材はろう溜用空間(39)、すなわち外方屈曲部(7a)の内周面における両平坦部(7b)に連なる丸み(37)の部分、中間プレート(9)の外側プレート(7)側を向いた面における外方屈曲部(7a)内に臨む部分、およびろう流れ防止用凸部(38)により囲まれた空間内に溜まる。したがって、ろう溜用空間(39)内、すなわち外側プレート(7)の外方屈曲部(7a)の内周面における両平坦部(7b)に連なる丸み(37)の部分と、中間プレート(9)の外側プレート(7)側を向いた面との間に確実にフィレットが形成され、上記連接部と、中間プレートの外側プレート側を向いた面との間に確実にフィレットが形成され、外側プレート(7)と中間プレート(9)とのろう付強度が増大してヘッダタンク(2)(3)の耐圧性が向上する。   The gas cooler (1) is manufactured by combining all the parts and brazing them together. When the outer plate (7) and the intermediate plate (9) are brazed during the production of the gas cooler (1), the molten brazing melted out of the outer plate (7) by the function of the brazing flow prevention convex portion (38). The material is prevented from flowing out from between the flat portion (7b) of the outer plate (7) and the intermediate plate (9) into the refrigerant flow path (10a) (10b) (20a), and the molten brazing material is Space (39), that is, the rounded portion (37) connected to both flat portions (7b) on the inner peripheral surface of the outward bent portion (7a), the surface facing the outer plate (7) side of the intermediate plate (9) In the outer bent portion (7a) and the space surrounded by the wax flow preventing convex portion (38). Therefore, in the wax storage space (39), that is, the rounded portion (37) connected to both flat portions (7b) on the inner peripheral surface of the outward bent portion (7a) of the outer plate (7), and the intermediate plate (9 ) Is surely formed between the surface facing the outer plate (7) side and the fillet is reliably formed between the connecting portion and the surface facing the outer plate side of the intermediate plate. The brazing strength between the plate (7) and the intermediate plate (9) is increased, and the pressure resistance of the header tanks (2) and (3) is improved.

ガスクーラ(1)は、圧縮機、エバポレータ、減圧器およびガスクーラから出てきた冷媒とエバポレータから出てきた冷媒とを熱交換させる中間熱交換器とともに超臨界冷凍サイクルを構成し、カーエアコンとして車両、たとえば自動車に搭載される。   The gas cooler (1) constitutes a supercritical refrigeration cycle together with a compressor, an evaporator, a decompressor, and an intermediate heat exchanger that exchanges heat between the refrigerant coming out of the gas cooler and the refrigerant coming out of the evaporator. For example, it is installed in a car.

上述したガスクーラ(1)において、圧縮機を通過したＣＯ２ が、入口部材(13)の冷媒流入路(14)を通って冷媒入口(12)から第１ヘッダタンク(2)の入口ヘッダ部(10A)内の冷媒流路(10a)に入り、冷媒流路(10a)内を下方に流れながら分流して第１パス(P1)のすべての熱交換管(4)の冷媒通路(4a)内に流入する。冷媒通路(4a)内に流入したＣＯ２は、冷媒通路(4a)内を左方に流れて第２ヘッダタンク(3)の中間ヘッダ部(20)内の冷媒流路(20a)の上半部に流入する。中間ヘッダ部(20)内の冷媒流路(20a)の上半部に流入したＣＯ２は、冷媒流路(20a)内を下方に流れ、分流して第２パス(P2)のすべての熱交換管(4)の冷媒通路(4a)内に流入し、流れ方向を変えて冷媒通路(4a)内を右方に流れて第１ヘッダタンク(2)の出口ヘッダ部(10B)内の冷媒流路(10b)に入る。その後、ＣＯ２は、出口ヘッダ部(10B)の冷媒流路(10b)内を下方に流れ、冷媒出口(15)および出口部材(16)の冷媒流出路(17)を通って流出する。そして、ＣＯ２が熱交換管(4)の冷媒通路(4a)内を流れる間に、通風間隙を図１に矢印Ｘで示す方向に流れる空気と熱交換し、冷却される。 In the gas cooler (1) described above, the CO 2 that has passed through the compressor passes through the refrigerant inflow passage (14) of the inlet member (13) from the refrigerant inlet (12) to the inlet header portion (1) of the first header tank (2). 10A) enters the refrigerant flow path (10a), flows downward in the refrigerant flow path (10a), and is divided into the refrigerant paths (4a) of all the heat exchange pipes (4) in the first path (P1). Flow into. The CO 2 that has flowed into the refrigerant passage (4a) flows to the left in the refrigerant passage (4a), and the upper half of the refrigerant passage (20a) in the intermediate header portion (20) of the second header tank (3). Flows into the section. The CO 2 flowing into the upper half of the refrigerant flow path (20a) in the intermediate header section (20) flows downward in the refrigerant flow path (20a) and is divided to all the heat in the second path (P2). The refrigerant flows into the refrigerant passage (4a) of the exchange pipe (4), changes the flow direction, flows to the right in the refrigerant passage (4a), and flows into the outlet header portion (10B) of the first header tank (2). Enter the channel (10b). Thereafter, CO 2 flows downward in the refrigerant flow path (10b) of the outlet header section (10B), and flows out through the refrigerant outlet (15) and the refrigerant outlet path (17) of the outlet member (16). Then, while CO 2 flows in the refrigerant passage (4a) of the heat exchange pipe (4), the ventilation gap is heat-exchanged with the air flowing in the direction indicated by the arrow X in FIG.

図８〜図１０は、第１ヘッダタンク(2)の中間プレートの変形例を示す。   8 to 10 show modifications of the intermediate plate of the first header tank (2).

図８〜図１０に示す中間プレート(40)の場合、上半部の複数の管挿入穴(18)を入口ヘッダ部(10A)の冷媒流路(10a)内に通じさせる複数の連通穴(22)、および下半部の複数の管挿入穴(18)を出口ヘッダ部(10B)の冷媒流路(10b)内に通じさせる複数の連通穴(22)は、それぞれ中間プレート(40)における隣り合う連通穴(22)間の部分の前後方向中央部を切除することにより形成された連通部(41)により連通させられている。そして、上半部の複数の管挿入穴(18)を入口ヘッダ部(10A)の冷媒流路(10a)内に通じさせる複数の連通穴(22)の前後方向中央部、およびこれらの連通穴(22)を連通させる連通部(41)によって、外側プレート(9)の第１流路形成部(28)とともに入口ヘッダ部(10A)の冷媒流路(10a)を形成する中間プレート(40)側の第２流路形成部(42)が形成され、下半部の複数の管挿入穴(18)を出口ヘッダ部(10B)の冷媒流路(10b)内に通じさせる複数の連通穴(22)の前後方向中央部、およびこれらの連通穴(22)を連通させる連通部(41)によって、外側プレート(9)の第１流路形成部(29)とともに出口ヘッダ部(10B)の冷媒流路(10b)を形成する中間プレート(40)側の第２流路形成部(43)が形成されている。   In the case of the intermediate plate (40) shown in FIG. 8 to FIG. 10, a plurality of communication holes (a plurality of communication holes (18a) for communicating the plurality of pipe insertion holes (18) in the upper half portion into the refrigerant flow path (10a) of the inlet header (10A). 22), and a plurality of communication holes (22) for communicating the plurality of pipe insertion holes (18) in the lower half part into the refrigerant flow path (10b) of the outlet header part (10B), respectively, in the intermediate plate (40) It is connected by the communication part (41) formed by excising the front-back direction center part of the part between adjacent communication holes (22). Then, the center part in the front-rear direction of the plurality of communication holes (22) for allowing the plurality of tube insertion holes (18) in the upper half portion to communicate with the refrigerant flow path (10a) of the inlet header (10A), and these communication holes An intermediate plate (40) that forms the refrigerant flow path (10a) of the inlet header section (10A) together with the first flow path formation section (28) of the outer plate (9) by the communication section (41) for communicating (22). A second flow path forming portion (42) on the side, and a plurality of communication holes (18) for allowing the plurality of pipe insertion holes (18) in the lower half to communicate with the refrigerant flow path (10b) of the outlet header portion (10B). The refrigerant in the outlet header portion (10B) together with the first flow path forming portion (29) of the outer plate (9) by the central portion in the front-rear direction of 22) and the communication portion (41) communicating these communication holes (22). A second flow path forming part (43) on the side of the intermediate plate (40) that forms the flow path (10b) is formed.

中間プレート(40)の外側プレート(7)を向いた面における連通部(41)の前後両側部分に、それぞれ上下方向にのびるとともに左右方向外方に突出したろう流れ防止用凸部(44)が一体に形成されている。ろう流れ防止用凸部(44)は、連通穴(22)および貫通穴(26)によって分断されており、ろう流れ防止用凸部(44)は連通穴(22)および貫通穴(26)が形成されていない部分に設けられていることになる。また、ろう流れ防止用凸部(44)の前後両側面は、中間プレート(40)の左右方向外面と直角をなしている。また、ろう流れ防止用凸部(44)は、外側プレート(7)の外方屈曲部(7a)内に嵌っており、その突出端は外方屈曲部(7a)の内周面における丸み(37)よりも前後方向内側の部分に当接している。そして、外側プレート(7)の丸み(37)と、中間プレート(40)の左右方向外側面およびろう流れ防止用凸部(44)の前後方向外側面との間にろう溜用空間(39)が形成されており、ろう溜用空間(39)内に外側プレート(7)の平坦部(7b)の左右方向内側面から溶け出したろう材からなるフィレット（図示略）が形成されている。   On the front and rear side portions of the communicating portion (41) on the surface of the intermediate plate (40) facing the outer plate (7), there is a wax flow preventing convex portion (44) extending in the vertical direction and protruding outward in the left-right direction. It is integrally formed. The solder flow prevention convex part (44) is divided by the communication hole (22) and the through hole (26), and the solder flow prevention convex part (44) has the communication hole (22) and the through hole (26). It is provided in a portion that is not formed. Further, the front and rear side surfaces of the wax flow preventing convex portion (44) are perpendicular to the left and right outer surfaces of the intermediate plate (40). Further, the convex portion for preventing brazing flow (44) is fitted in the outer bent portion (7a) of the outer plate (7), and the protruding end thereof is rounded on the inner peripheral surface of the outer bent portion (7a) ( It is in contact with the inner part in the front-rear direction than 37). A brazing reservoir space (39) between the roundness (37) of the outer plate (7) and the outer lateral surface of the intermediate plate (40) and the outer lateral surface of the brazing flow prevention convex portion (44). In the brazing space (39), a fillet (not shown) made of a brazing material melted from the left and right inner side surfaces of the flat portion (7b) of the outer plate (7) is formed.

その他の構成は、上記実施形態の図１〜図７に示す中間プレート(9)と同一である。   Other configurations are the same as those of the intermediate plate (9) shown in FIGS.

図示は省略したが、図８〜図１０に示す中間プレート（４０）を第２ヘッダタンク(3)に適用する場合には、すべての管挿入穴(18)を中間ヘッダ部(20)の冷媒流路(20a)内に通じさせるすべての連通穴(22)は、中間プレート(40)における隣り合う連通穴(22)間の部分の前後方向中央部を切除することにより形成された連通部(41)により連通させられる。そして、すべての管挿入穴(18)を中間ヘッダ部(20)の冷媒流路(20a)内に通じさせる複数の連通穴(22)の前後方向中央部、およびこれらの連通穴(22)を連通させる連通部(41)によって、外側プレート(9)の第１流路形成部(33)とともに中間ヘッダ部(20)の冷媒流路(20a)を形成する中間プレート(40)側の第２流路形成部が形成されている。その他の構成は図８〜図１０に示す中間プレート(40)と同様である。   Although illustration is omitted, when the intermediate plate (40) shown in FIGS. 8 to 10 is applied to the second header tank (3), all the pipe insertion holes (18) are provided in the refrigerant of the intermediate header portion (20). All the communication holes (22) to be communicated into the flow path (20a) are communication portions formed by cutting out the center part in the front-rear direction between the adjacent communication holes (22) in the intermediate plate (40) ( 41). A central portion in the front-rear direction of the plurality of communication holes (22) that allows all the tube insertion holes (18) to communicate with the refrigerant flow path (20a) of the intermediate header portion (20), and these communication holes (22). The communication plate (41) on the side of the intermediate plate (40) that forms the refrigerant flow path (20a) of the intermediate header section (20) together with the first flow path forming section (33) of the outer plate (9) by the communicating section (41). A flow path forming part is formed. Other configurations are the same as those of the intermediate plate (40) shown in FIGS.

上記実施形態においては、ヘッダタンク(2)(3)は３枚のプレート(7)(8)(9)により形成されているが、内側プレート(8)と中間プレート(40)との間に、さらに１枚以上のプレートが介在させられていてもよい。当該プレートは、第２流路形成部(31)(32)が設けられていないことを除いては、中間プレート(40)と同様な構成である。   In the above embodiment, the header tanks (2) and (3) are formed by three plates (7), (8) and (9), but between the inner plate (8) and the intermediate plate (40). Further, one or more plates may be interposed. The plate has the same configuration as the intermediate plate (40) except that the second flow path forming portions (31) and (32) are not provided.

また、上記の実施形態においては、超臨界冷凍サイクルの超臨界冷媒として、ＣＯ２が使用されているが、これに限定されるものではなく、エチレン、エタン、酸化窒素などが使用可能である。 In the above embodiment, CO 2 is used as the supercritical refrigerant in the supercritical refrigeration cycle. However, the present invention is not limited to this, and ethylene, ethane, nitric oxide, and the like can be used.

また、上記の実施形態においては、熱交換管(4)は、アルミニウム押出形材からなるが、これに両面にろう材層を有するアルミニウムブレージングシートからなる管製造用金属板を曲げた折り曲げ体からなるものであってもよい。   Further, in the above embodiment, the heat exchange pipe (4) is made of an extruded aluminum material, but from a bent body obtained by bending a metal plate for tube production made of an aluminum brazing sheet having a brazing filler metal layer on both sides thereof. It may be.

さらに、上記の実施形態においては、この発明の熱交換器が超臨界冷凍サイクルのガスクーラに適用されているが、これに限定されるものではなく、他の熱交換器、たとえば超臨界冷凍サイクルのエバポレータに適用することも可能である。   Furthermore, in the above embodiment, the heat exchanger of the present invention is applied to a gas cooler of a supercritical refrigeration cycle. However, the present invention is not limited to this, and other heat exchangers such as a supercritical refrigeration cycle are used. It is also possible to apply to an evaporator.

この発明の熱交換器を適用したガスクーラの全体構成を示す斜視図である。It is a perspective view which shows the whole structure of the gas cooler to which the heat exchanger of this invention is applied. 図１のガスクーラの後方から前方を見た一部省略垂直断面図である。FIG. 2 is a partially omitted vertical sectional view of the gas cooler of FIG. 図２のＡ−Ａ線拡大断面図である。It is an AA line expanded sectional view of FIG. 図２のＢ−Ｂ線拡大断面図である。FIG. 3 is an enlarged sectional view taken along line B-B in FIG. 2. 図１のガスクーラの第１ヘッダタンクの分解斜視図である。It is a disassembled perspective view of the 1st header tank of the gas cooler of FIG. 図１のガスクーラの第２ヘッダタンクの分解斜視図である。It is a disassembled perspective view of the 2nd header tank of the gas cooler of FIG. 図１のガスクーラの入口ヘッダ部、出口ヘッダ部および中間ヘッダ部の冷媒流路を示す拡大横断面図である。FIG. 2 is an enlarged cross-sectional view showing refrigerant flow paths in an inlet header portion, an outlet header portion, and an intermediate header portion of the gas cooler in FIG. 1. 中間プレートの変形例を示す図３相当の図である。It is a figure equivalent to FIG. 3 which shows the modification of an intermediate | middle plate. 図８の中間プレートを示す斜視図である。It is a perspective view which shows the intermediate | middle plate of FIG. 図８の中間プレートを用いた第１ヘッダタンクの入口ヘッダ部および出口ヘッダ部の冷媒流路を示す図７相当の図である。It is a figure equivalent to FIG. 7 which shows the refrigerant | coolant flow path of the inlet header part and outlet header part of a 1st header tank using the intermediate | middle plate of FIG.

符号の説明Explanation of symbols

(1)：ガスクーラ（熱交換器）
(2)(3)：ヘッダタンク
(4)：熱交換管
(7)：外側プレート
(7a)：外方屈曲部
(7b)：平坦部
(8)：内側プレート
(9)：中間プレート
(10A)：入口ヘッダ部
(10a)：冷媒流路
(10B)：出口ヘッダ部
(10b)：冷媒流路
(18)：管挿入穴
(20)：中間ヘッダ部
(20a)：冷媒流路
(22)：連通穴
(38)(44)：ろう流れ防止用凸部 (1): Gas cooler (heat exchanger)
(2) (3): Header tank
(4): Heat exchange pipe
(7): Outer plate
(7a): outward bend
(7b): Flat part
(8): Inside plate
(9): Intermediate plate
(10A): Entrance header
(10a): Refrigerant flow path
(10B): Exit header
(10b): Refrigerant flow path
(18): Tube insertion hole
(20): Intermediate header
(20a): Refrigerant flow path
(22): Communication hole
(38) (44): Protrusions for preventing wax flow

Claims (4)

互いに間隔をおいて配置された１対のヘッダタンクと、両ヘッダタンク間に、幅方向を前後方向に向けるとともにヘッダタンクの長さ方向に間隔をおいて配置され、かつ両端部がそれぞれ両ヘッダタンクに接続された複数の扁平状熱交換管とを備えており、ヘッダタンクが、外側プレートと、内側プレートと、これら両プレート間に介在させられた中間プレートとが互いに積層されてろう付されることにより構成され、ヘッダタンクの外側プレートの前後方向の中央部に、中間プレート側に開口する横断面略Ｕ字状の外方屈曲部が形成されているとともに、外方屈曲部の前後両側部分にそれぞれ同一平面内に位置する平坦部が形成されている熱交換器において、
中間プレートの外側プレート側を向いた面における外側プレートの外方屈曲部内に臨む部分の前後両側縁部に、外方屈曲部内に突出しかつ中間プレートの長さ方向にのびるろう流れ防止用凸部が形成されている熱交換器。 A pair of header tanks arranged at a distance from each other, and between the header tanks, the width direction is directed in the front-rear direction and the header tanks are arranged at intervals in the length direction, and both end portions are both headers. A plurality of flat heat exchange pipes connected to the tank, and the header tank is brazed by laminating an outer plate, an inner plate, and an intermediate plate interposed between the two plates. In the center part of the outer side plate of the header tank in the front-rear direction, an outward bent part having a substantially U-shaped cross section opening to the intermediate plate side is formed, and both front and rear sides of the outer bent part In the heat exchanger in which the flat part located in the same plane is formed in each part,
Protrusions for preventing wax flow that protrude into the outer bent portion and extend in the length direction of the intermediate plate are formed on the front and rear side edges of the portion facing the outer bent portion of the outer plate on the surface facing the outer plate side of the intermediate plate. Heat exchanger being formed. ろう流れ防止用凸部の突出端が、外側プレートの外方屈曲部の内周面に当接している請求項１記載の熱交換器。 The heat exchanger according to claim 1, wherein the protruding end of the convex portion for preventing brazing flow is in contact with the inner peripheral surface of the outward bent portion of the outer plate. ろう流れ防止用凸部の突出高さが０．３ｍｍ以上であり、同じく前後方向の厚みが０．３ｍｍ以上である請求項１または２記載の熱交換器。 The heat exchanger according to claim 1 or 2, wherein a protrusion height of the convex portion for preventing brazing flow is 0.3 mm or more, and a thickness in the front-rear direction is also 0.3 mm or more. ヘッダタンクに、冷媒の流れる中空状の冷媒流路を有する少なくとも１つのヘッダ部が形成され、内側プレートにおけるヘッダ部の冷媒流路と対応する部分に、前後方向に長い複数の管挿入穴が内側プレートの長さ方向に間隔をおいて貫通状に形成され、中間プレートに、前後方向に長くかつ内側プレートの各管挿入穴をヘッダ部の冷媒流路内に通じさせる連通穴が貫通状に形成され、熱交換管の端部がヘッダタンクの内側プレートの管挿入穴内に挿入されて内側プレートにろう付され、中間プレートにおける連通穴が形成されていない部分にろう流れ防止用凸部が形成されている請求項１〜３のうちのいずれかに記載の熱交換器。 The header tank is formed with at least one header part having a hollow refrigerant flow path through which a refrigerant flows, and a plurality of pipe insertion holes long in the front-rear direction are provided in the part corresponding to the refrigerant flow path of the header part on the inner plate. Formed in a penetrating manner at intervals in the length direction of the plate, and formed in the intermediate plate as a penetrating hole that is long in the front-rear direction and connects each tube insertion hole of the inner plate into the refrigerant flow path of the header section. The end portion of the heat exchange pipe is inserted into the pipe insertion hole of the inner plate of the header tank and brazed to the inner plate, and a convex portion for preventing brazing flow is formed in a portion where the communication hole is not formed in the intermediate plate. The heat exchanger according to any one of claims 1 to 3.
JP2008110332A 2008-04-21 2008-04-21 Heat exchanger Expired - Fee Related JP5007267B2 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013139916A (en) * 2011-12-28 2013-07-18 Daikin Industries Ltd Heat exchanger
WO2020004292A1 (en) * 2018-06-28 2020-01-02 株式会社ティラド Tank structure of heat exchanger

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2857783A1 (en) * 2013-10-04 2015-04-08 ABB Technology AG Heat exchange device based on a pulsating heat pipe
FR3028935A1 (en) * 2014-11-25 2016-05-27 Valeo Systemes Thermiques COLLECTOR FOR EXCHANGER COMPRISING A BRAZED REMOVAL COATING

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JPS59119194A (en) * 1982-12-22 1984-07-10 ユリアス・フラウ・ベ−ル・ゲ−・エム・ベ−・ハ−・ウント・ツエ−・オ−・カ−・ゲ− Heat exchanger and its manufacture
JP2006132802A (en) * 2004-11-02 2006-05-25 Calsonic Kansei Corp Header tank for heat exchanger
JP2006194522A (en) * 2005-01-13 2006-07-27 Japan Climate Systems Corp Heat exchanger

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005351520A (en) 2004-06-09 2005-12-22 Calsonic Kansei Corp Heat exchanger

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59119194A (en) * 1982-12-22 1984-07-10 ユリアス・フラウ・ベ−ル・ゲ−・エム・ベ−・ハ−・ウント・ツエ−・オ−・カ−・ゲ− Heat exchanger and its manufacture
JP2006132802A (en) * 2004-11-02 2006-05-25 Calsonic Kansei Corp Header tank for heat exchanger
JP2006194522A (en) * 2005-01-13 2006-07-27 Japan Climate Systems Corp Heat exchanger

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013139916A (en) * 2011-12-28 2013-07-18 Daikin Industries Ltd Heat exchanger
WO2020004292A1 (en) * 2018-06-28 2020-01-02 株式会社ティラド Tank structure of heat exchanger

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