JP2004239592A - Vehicular heat exchanger - Google Patents

Vehicular heat exchanger Download PDF

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Publication number
JP2004239592A
JP2004239592A JP2003176809A JP2003176809A JP2004239592A JP 2004239592 A JP2004239592 A JP 2004239592A JP 2003176809 A JP2003176809 A JP 2003176809A JP 2003176809 A JP2003176809 A JP 2003176809A JP 2004239592 A JP2004239592 A JP 2004239592A
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JP
Japan
Prior art keywords
pipe
heat exchanger
inlet
auxiliary
header
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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JP2003176809A
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Japanese (ja)
Inventor
Jinichi Hiyama
仁一 桧山
Yoshiaki Koga
美章 古賀
Masatake Niihama
正剛 新濱
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Marelli Corp
Original Assignee
Calsonic Kansei Corp
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Publication date
Application filed by Calsonic Kansei Corp filed Critical Calsonic Kansei Corp
Priority to JP2003176809A priority Critical patent/JP2004239592A/en
Publication of JP2004239592A publication Critical patent/JP2004239592A/en
Pending legal-status Critical Current

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    • 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
    • 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
    • F28F9/0219—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
    • 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
    • F28F9/0253—Massive connectors, e.g. blocks; Plate-like connectors with multiple channels, e.g. with combined inflow and outflow channels

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vehicular heat exchanger capable of improving performance by maximally securing a core area in limited mounting space while securing easiness of piping connection work. <P>SOLUTION: A header pipe 7 provided with a heat exchanger outlet tank part 17B composing a most downstream side of a core is provided with a main pipe part 17 having a primary function of the header pipe 7, and an auxiliary pipe part 19 arranged in parallel with the main pipe part 17 and communicated with the heat exchanger outlet tank part 17B. By the auxiliary pipe part 19, piping connection workability of a conventional level can be secured. Since the main pipe part 17 and the auxiliary pipe part 19 share one wall (a partition wall part) 15, distinct from a conventional structure provided with an auxiliary pipe aside from a header pipe, there is no protrusion due to the auxiliary pipe or a support means such as a bracket, and the core area can be maximally secured in the limited mounting space. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、ヘッダパイプ間で熱交換媒体を流通させて空気との熱交換を行う車両用熱交換器に関する。
【０００２】
【従来の技術】
この種の車両用熱交換としては、アウターフィンを介して複数多段に積層されたチューブの両端にヘッダパイプを連通接続し、ヘッダパイプの冷媒導入口から取り入れた冷媒を前記チューブに流通させて、このチューブを流通する冷媒と外部空気との熱交換をした後、該冷媒をヘッダパイプの冷媒排出口から排出するものが知られている。
【０００３】
ところで、上述のような車両用熱交換器は、一般に車両のエンジンルームに配置され、熱交換器本体の配置後にヘッダパイプへの入口側／出口側配管の接続作業が行われる。このとき、ヘッダパイプに設けられた冷媒排出口の位置によっては、冷媒排出口への配管接続作業が不自然な姿勢を強いられ、作業効率が悪いという問題がある。
【０００４】
そこで、例えば特許文献１、２に開示されるように、ヘッダパイプの下端部に設けられた冷媒排出口に、配管接続作業が容易な位置（ヘッダパイプの上端側）まで配索される補助パイプを接続して、この補助パイプを介して配管やリキッドタンクを接続する構造が提案されている。
【０００５】
【特許文献１】
特開平１０−１４１８８７号公報
【０００６】
【特許文献２】
特開平１０−２６７４６７号公報
【０００７】
【発明が解決しようとする課題】
しかしながら、この方法では、別体の補助パイプをヘッダパイプの冷媒排出口に接続し、なおかつブラケットなどの支持手段を用いて補助パイプをヘッダパイプに支持させなければならない。そのため、補助パイプおよび支持手段が熱交換器本体から出っ張り、限られた車両搭載スペース内に納めるためにコア（放熱部）面積を縮小させて対応している。
【０００８】
本発明は、このような従来技術をもとに為されたものであって、その目的は、配管接続作業の容易性を確保しつつも限られた搭載スペース内でコア面積を最大限に確保して熱交換性能を向上できる車両用熱交換器の提供である。
【０００９】
【課題を解決するための手段】
請求項１記載の発明は、複数多段に積層したチューブの両端にヘッダパイプを連通接続し、熱交換媒体を前記チューブに流通させてこのチューブを流通する熱交換媒体と外部空気との熱交換をおこなう車両用熱交換器において、コアの最下流部を構成する熱交換器出口タンク部を備えるヘッダパイプは、ヘッダパイプの本来の機能を有するメインパイプ部と、前記メインパイプ部に沿って設けられ前記メインパイプの熱交換器出口タンク部と連通される補助パイプ部と、を備え、これらメインパイプ部と補助パイプ部とで１つの壁を共有していることを特徴とするものである。
【００１０】
請求項２記載の発明は、請求項１記載の車両用熱交換器において、前記補助パイプ部を備えるヘッダパイプのメインパイプ部には、導入口を有してコアの最上流部を構成する熱交換器入口タンク部およびコアの最下流部を構成する熱交換器出口タンク部が設けられ、前記熱交換器入口タンク部に開口する導入口の近傍に、前記補助パイプ部に開口する排出口を設けたことを特徴とするものである。
【００１１】
請求項３記載の発明は、請求項２記載の車両用熱交換器において、前記ヘッダパイプに固定され入口側配管を受け入れて該入口側配管と前記導入口とを連通接続するための入口側配管コネクタと、前記ヘッダパイプに固定され出口側配管を受け入れて該出口側配管と前記排出口とを連通接続するための出口側配管コネクタと、を一体形成した一体型配管コネクタを設けたことを特徴とするものである。
【００１２】
請求項４記載の発明は、請求項３記載の車両用熱交換器において、一体型配管コネクタの入口側配管コネクタ部は、前記補助パイプ部を貫通してメインパイプ部に連通接続される筒状接続部を備えることを特徴とするものである。
【００１３】
請求項５記載の発明は、請求項１〜３のいずれか１項記載の車両用熱交換器において、前記壁に、メインパイプ部を流通する熱交換媒体と補助パイプ部を流通する熱交換媒体との熱の授受を遮断するための断熱部を設けたことを特徴とするものである。
【００１４】
請求項６記載の発明は、請求項１記載の車両用熱交換器において、前記ヘッダパイプ内の仕切板の区画によって、前記熱交換媒体が前記ヘッダパイプ間を第１パス、第２パス、・・・と複数回蛇行して流通する構造であり、前記補助パイプ部に開口する排出口を第１パスより下流のパスに対応する位置に配置したことを特徴とするものである。
【００１５】
請求項７記載の発明は、請求項６記載の車両用熱交換器において、前記補助パイプ部の下流端部を第１パスより下流のパスに対応する位置までとし、前記補助パイプ部に開口する排出口を第１パスより下流のパスに対応する位置に配置したことを特徴とするものである。
【００１６】
【発明の効果】
請求項１記載の発明によれば、メインパイプ部に沿って補助パイプ部を設けたため、従来と同様、配管接続作業の容易性が確保される。しかも、これらメインパイプ部と補助パイプ部は１つの壁を共用するため、従来のようにヘッダパイプと別に補助パイプを設けた構造と異なり、補助パイプおよびブラケットなどの支持手段による出っ張りがなくなるため、その分、限られた搭載スペース内でコア（放熱部）面積を拡大でき、熱交換性能を向上できる。つまり、請求項１記載の発明によれば、配管接続作業の容易性を確保しつつも限られた搭載スペース内でコア面積を最大限に確保して熱交換性能を向上できる。
【００１７】
請求項２記載の発明によれば、入口側配管および出口側配管の接続作業を効率良く行うことができる。
【００１８】
請求項３記載の発明によれば、請求項２記載の発明の効果に加え、入口側配管コネクタおよび出口側配管コネクタを一体形成したことで、部品点数および製造工数を削減でき、さらに製造コストを削減できる。
【００１９】
請求項４記載の発明によれば、配管コネクタの取付方向からみてメインパイプ部が補助パイプ部に隠れる配置であっても、配管コネクタの取り付けを成立させることができる。
【００２０】
請求項５記載の発明によれば、請求項１〜３のいずれか１項記載の発明の効果に加え、断熱部によってメインパイプ部を流通する熱交換媒体と補助パイプ部を流通する熱交換媒体との熱の授受を遮断できる。これにより、補助パイプ部を流通する熱交換媒体つまり熱交換器のコアで熱交換し終わった熱交換媒体が、熱交換前または熱交換途中の熱交換媒体からの悪影響を受けずにすむ。
【００２１】
請求項６記載の発明によれば、請求項１記載の発明の効果に加え、補助パイプ部に開口する排出口を第１パスより下流のパスに対応する位置に配置したため、コンパクトな構造でありながらも、補助パイプ部を流通する冷媒（コアで熱交換し終わって冷媒）が、最も温度差のある第１パスを流通する冷媒からの悪影響を受け難い構造となる。
【００２２】
請求項７記載の発明によれば、請求項６記載の発明の効果に加え、補助パイプ部の下流端部を第１パスより下流のパスに対応する位置までとし、補助パイプ部に開口する排出口を第１パスより下流のパスに対応する位置に配置したことを特徴とするため、補助パイプ部を流通する冷媒（コアで熱交換し終わって冷媒）が、第１パスの冷媒の悪影響をさらに受け難い構造となる。
【００２３】
【発明の実施の形態】
以下、本発明にかかる熱交換器を車両用コンデンサに適用した実施形態を図面に基づいて説明する。
【００２４】
第１実施形態：図１〜図８は本発明の熱交換器の第１実施形態である。図１は本第１実施形態におけるコンデンサ（熱交換器）の全体図であって、（ａ）は上面図、（ｂ）は正面図である。コンデンサ１は、車両のエンジンルーム前部に配置され、波形のアウターフィン３を介して複数多段に積層された扁平チューブ５の両端に、上下方向に配置された左右一対のヘッダパイプ７、９を連通接続してなる。チューブ５の積層方向最外側（上端側および下端側）には、チューブ５とアウターフィン３とを補強するために横断面コ字状のサイドプレート１１、１３が両ヘッダパイプ７、９間に亘って配設されている。
【００２５】
図２に示すように、一方のヘッダパイプ７（左側ヘッダパイプ）は、ヘッダパイプ７の長手方向に沿って並設されるメインパイプ部１７と補助パイプ部１９とを備えている。また、他方のヘッダパイプ９（右側ヘッダパイプ）は、ヘッダパイプ７の長手方向に沿って並設されるメインパイプ部２３とリキッドタンク部２５とを備えている。
【００２６】
この実施形態のコンデンサ１はサブクール式のコンデンサであって、両ヘッダパイプ７、９のメインパイプ部１７、２３内に設けられこれらメインパイプ部１７、２３を上下に分割する仕切板２７、２９によって、コンデンサ１のコアが上側の第１パス１Ａ（この第１実施形態では凝縮部）と下側の第２パス１Ｂ（この第１実施形態ではサブクール部）とに分割され、右側ヘッダパイプ９のメインパイプ部２３の上部に形成された凝縮部出口タンク部２３Ａと、右側ヘッダパイプ９のメインパイプ部２３の下部に形成されたサブクール部入口タンク部２３Ｂと、の間にリキッドタンク部２５が連通接続されている。
【００２７】
そして、この実施形態の特徴点は、この左側ヘッダパイプ７の下端部に位置する熱交換器出口タンク部１７Ｂから排出される冷媒を、補助パイプ部１９を介して左側ヘッダパイプ７の上側に向けて導けるようになっている点である。
図３〜図８はこの左側ヘッダパイプ７の詳細構造を示すものである。この左側ヘッダパイプ７は、互いに嵌合されるタンクプレート３５とエンドプレート３７とからなる２分割タイプである。このヘッダパイプ７は、その両端が閉塞部材３９、４１によって閉塞され、内部空間は長手方向に沿う仕切壁部１５によってメインパイプ部１７と補助パイプ部１９とに区画されている。つまり、メインパイプ部１７と補助パイプ部１９とはヘッダパイプ７の長手方向に沿って並設され、これらメインパイプ部１７と補助パイプ部１９で１つの壁（仕切壁部１５）を共有している。
【００２８】
メインパイプ部１７の長手方向にそって等間隔に設けられたチューブ取付口３６には、チューブ５の長手方向端部が挿嵌されており、メインパイプ部１７はチューブ５と連通接続されることでヘッダパイプの本来の機能を果たすようになっている。なお、仕切板２７よって内部空間を上下に仕切られたメインパイプ部１７の上側空間は、冷媒導入口４３が開口されてコアの最上流部を構成する熱交換器入口タンク部１７Ａとなっており、またメインパイプ部１７の下側空間はコアの最下流部を構成する熱交換器出口タンク部１７Ｂとなっている。
【００２９】
一方、補助パイプ部１９は、メインパイプ部１７と同一長さで形成されており、メインパイプ部１７に形成された熱交換器出口タンク部１７Ｂと連通孔４５を通じて連通し、ヘッダパイプ７の一端部（下端部）の熱交換器出口タンク部１７Ｂから排出される冷媒をヘッダパイプ７の他端側（上側）に導くものである。
【００３０】
ここで、メインパイプ部１７の熱交換器入口タンク部１７Ａに開口する冷媒導入口４３の近傍位置に、補助パイプ部１９に開口する冷媒排出口４７が設けられており、この左側ヘッダパイプ７には入口側配管コネクタ部４９ａおよび出口側配管コネクタ部４９ｂが一体形成されたブロック状の一体型の配管コネクタ４９が固定されている。
【００３１】
入口側配管コネクタ部４９ａは、図示せぬ入口側配管を受け入れてこの入口側配管とメインパイプ部１７の冷媒導入口４３とを連通接続するため連通路５１を有し、また、出口側配管コネクタ部４９ｂは、図示せぬ出口側配管を受け入れてこの出口側配管と補助パイプ部１９の冷媒排出口４７とを連通接続するため連通路５３を有する。ここで、配管コネクタ４９は、チューブ５の長手方向に沿って連設されたメインパイプ部１７と補助パイプ部１９のうち補助パイプ部１９側からヘッダパイプ７に取り付けられており、配管コネクタ４９がコアの厚み方向（通風方向）に大きく出っ張らないようになっている。これに対応して、この配管コネクタ４９の入口側配管コネクタ部４９ａには、補助パイプ部１９を貫通してメインパイプ部１７の冷媒導入口４３に嵌合されメインパイプ部１７と連通接続される筒状接続部５５が設けられている。なお、この実施形態では、筒状接続部５５は配管コネクタ本体の嵌合孔部５７に嵌入される筒状部材として、配管コネクタ本体とは別体で形成されている。
【００３２】
以上の構成により、図２に示すように、図示せぬコンプレッサから圧送される冷媒は、配管コネクタ４９を通じて凝縮部入口タンク部（熱交換器入口タンク部）１７Ａに導入される。導入された冷媒は、凝縮部（第１パス１Ａ）のチューブ５を流通して凝縮部出口タンク部２３Ａに流入した後、リキッドタンク部２５に流入して気液分離される。リキッドタンク部２５の下部に貯留する液相冷媒は、連通孔３３を通じてサブクール部入口タンク部２３Ｂに流入して、サブクール部（第２パス１Ｂ）のチューブ５を流通して過冷却されて、サブクール部出口タンク部（熱交換器出口タンク部）１７Ｂに至る。そして、熱交換器出口タンク部１７Ｂに至った低温冷媒は、連通孔４５を通じて補助パイプ部１９に流入して、補助パイプ部１９の下端から上端側に向けて導びかれて、上端部に位置する冷媒排出口４７から配管コネクタ４９を介して出口側配管へと排出される。
【００３３】
このようなコンデンサ１によれば、以下のような効果がある。
【００３４】
まず第１に、ヘッダパイプ７は、長手方向に沿って並設されたメインパイプ部１７と補助パイプ部１９とを備えるため、該補助パイプ部１９を利用して、従来と同様の配管取付作業性を確保できる。しかも、メインパイプ部１７と補助パイプ部１９とは１つの壁（仕切壁部）１５を共有しているため、従来のようにヘッダパイプと別に補助パイプを設けた構造と異なり、補助パイプおよびブラケットなどの支持手段による出っ張りがなくなり、その分、限られた車両搭載スペース内でコア（放熱部）面積を拡大でき、放熱性能を向上できる。
【００３５】
第２に、一方（左側）のヘッダパイプ７のメインパイプ部１７には、熱交換器入口タンク部１７Ａおよび熱交換器出口タンク部１７Ｂが設けられ、熱交換器入口タンク部１７Ａに開口する冷媒導入口４３の近傍位置に、補助パイプ部１９に開口する冷媒排出口４７を設けたため、入口側配管および出口側配管の接続作業を効率良く行うことができる。
【００３６】
第３に、第２の効果に加え、入口側配管コネクタ４９ａおよび出口側配管コネクタ４９ｂを一体形成した配管コネクタ４９を設けたことで、部品点数および製造工数を削減でき、さらに製造コストを削減できる。
【００３７】
第４に、配管コネクタ４９の入口側配管コネクタ部４９ａは、補助パイプ部１９を貫通してメインパイプ部１７に連通接続される筒状接続部５５を備えるため、配管コネクタ４９の取付方向からみてメインパイプ部１７が補助パイプ部１９に隠れる配置であっても、配管コネクタ４９の取り付けを成立させることができる。特に、チューブ５の長手方向に沿ってメインパイプ部１７と補助パイプ部１９を連設し、その連設方向から配管コネクタ４９を取り付ける構造を成立させることができ、コアの厚み方向（通風方向）に対してヘッダパイプ７および配管コネクタ４９が大きく出っ張らないようにすることができる。
【００３８】
なお、上述の実施形態では、メインパイプ部１７と補助パイプ部１９とを備えるヘッダパイプ７は、タンクプレート３５とエンドプレート３７とからなる２分割タイプであるが、本発明にあっては、引き抜きまたは押し出し形成による一体形成タイプであってもよいし、また、ヘッダパイプ７の断面形状は例えば図１０〜図１３のような断面形状であってもよく、上述の実施形態に限定されるものでない。
【００３９】
また、上述の実施形態では、メインパイプ部１７と補助パイプ部１９の連設方向Ｘに沿って配管コネクタ４９を取り付ける構造を採っているが、本発明においては、例えば図１４に示すように、ヘッダパイプ７の長手方向Ｚから該ヘッダパイプ７の開口端部に配管コネクタ１０２取り付けるような構造であってもよいし、また、メインパイプ部１７と補助パイプ部１９の連設方向と直交する方向Ｙ（図１中矢印参照）から取り付けるような構造であってもよく、上述の実施形態に限定されるものではない。
【００４０】
第２実施形態：図９は本発明にかかる熱交換器の第２実施形態を示す。この第２実施形態の構造は、仕切壁部１５に断熱部１０１を設けた点で、第１実施形態と異なる。
【００４１】
このような構造によればメインパイプ部１７を流通する冷媒と補助パイプ部１９を流通する冷媒との熱の授受を遮断できる利点がある。つまり、コンパクトな構造でありながらも、補助パイプ部１９を流通する冷媒（コアで熱交換し終わった冷媒）が、熱交換前または熱交換途中の冷媒からの悪影響を受けずにすむ。
【００４２】
第３実施形態：図１５は本発明にかかる熱交換器の第３実施形態を示す。この第３実施形態の熱交換器３００は、主に以下の２点で第１実施形態と異なっている。第１に、コアを流通する冷媒の蛇行数（パス数）が第１実施形態の熱交換器１と異なる。具体的には、第１パス１Ａおよび第２パス１Ｂおよび第３パス１Ｃが凝縮部として構成され且つ第４パス１Ｄがサブクール部として構成され、全体として４つのパス１Ａ〜１Ｄにより構成されている。第２に、補助パイプ１９の排出口４７が、第１パス１Ａより下流のパス１Ｂに対応する位置に配置されている点で第１実施形態と異なる。
【００４３】
このような構造によれば、コンパクトな構造でありながらも、補助パイプ部１９を流通する冷媒（コアで熱交換し終わって冷媒）が、最も温度差のある第１パス１Ａを流通する冷媒からの悪影響を受けずにすむ。なお、図１６に示す第４実施形態の熱交換器４００のように、入口側配管コネクタ４９ａと出口側配管コネクタ４９ｂとが別体で形成されていても、同様の効果が得られる。
【００４４】
第５実施形態：図１７は本発明の第５実施形態の熱交換器５００を示す。この第５実施形態の熱交換器５００は、補助パイプ部１９が、第４パス１Ｄから第２パス１Ｂまでで形成されている点で第４実施形態と異なっている。つまり、補助パイプ部１９が、第１パス１Ａまでは延在しておらず、第１パス１Ａより下流のパス１Ｂに対応する位置までで形成されている。
【００４５】
このような構造によれば、補助パイプ部１９を流通する冷媒（コアで熱交換し終わって冷媒）が、第１パス１Ａの冷媒の悪影響をさらに受け難い構造とすることができる。
【００４６】
以上要するに、本発明によれば、補助パイプ部により配管取付作業性を確保できる構造でありながらも、メインパイプ部と補助パイプ部とは１つの壁（仕切壁部）を共有しているため、従来のようにヘッダパイプと別に補助パイプを設けた構造と異なり、補助パイプおよびブラケットなどの支持手段による出っ張りがなくなり、その分、限られた車両搭載スペース内でコア（放熱部）面積を拡大でき、熱交換器の熱交換性能を向上できる。
【００４７】
なお、上述の実施形態にあっては、冷媒導入口４３（入口側配管コネクタ４９ａ）を備える一方（入口側）のヘッダパイプ７に補助パイプ部１９を形成した構造であるが、本発明にあっては、図１８に示すように冷媒導入口４３（入口側配管コネクタ４９ａ）を備えない他方のヘッダパイプ９に補助パイプ部１９を設けた構造であってもよい。
【００４８】
また、上述の実施形態にあっては、リキッドタンク２５を有してサブクール部を備える熱交換器１、３００、４００、５００であるが、本発明にあっては、図１８に示すようにリキッドタンクおよびサブクール部を備えない熱交換器６００であってもよい。また、本発明にあっては、コアを流通する冷媒の蛇行回数（パス数）は上述の実施形態に限定されるものではない。
【図面の簡単な説明】
【図１】図１（ａ）は本発明の第１実施形態におけるコンデンサ（熱交換器）の上面図、図１（ｂ）はコンデンサの正面図。
【図２】図２は同コンデンサ内を流れる冷媒（熱交換媒体）の流通経路を示す概略図。
【図３】図３は同コンデンサの左側ヘッダパイプの断面図。
【図４】図４は同コンデンサの左側ヘッダパイプの上端部近傍の分解斜視図。
【図５】図５は図１（ａ）中ＳＢ−ＳＢ断面のうち図１（ｂ）中Ａ部拡大図。
【図６】図６は図１（ａ）中ＳＢ−ＳＢ断面のうち図１（ｂ）中Ｂ部拡大図。
【図７】図７は図１（ｂ）中Ａ部の拡大分解図。
【図８】図８は図１（ｂ）中Ｂ部の拡大分解図。
【図９】図９は本発明の第２実施形態を示す図であって、メインパイプ部と補助パイプ部との間に断熱部を設けたヘッダパイプを示す図。
【図１０】図１０はヘッダパイプの一変形例を示す断面図。
【図１１】図１１はヘッダパイプの一変形例を示す断面図。
【図１２】図１２はヘッダパイプの一変形例を示す断面図。
【図１３】図１３はヘッダパイプの一変形例を示す断面図。
【図１４】図１４は配管コネクタの変形例を示す図。
【図１５】図１５は本発明の第３実施形態のコンデンサ（熱交換器）の模式図。
【図１６】図１６は本発明の第４実施形態のコンデンサ（熱交換器）の模式図。
【図１７】図１７は本発明の第５実施形態のコンデンサ（熱交換器）の模式図。
【図１８】図１８は本発明の第６実施形態のコンデンサ（熱交換器）の模式図。
【符号の説明】
１…コンデンサ（熱交換器）
１Ａ…第１パス
１Ｂ…第２パス
１Ｃ…第３パス
１Ｄ…第４パス
５…チューブ
７…左側ヘッダパイプ（ヘッダパイプ）
１５…仕切壁部（壁）
１７…メインパイプ部
１７Ａ…凝縮部入口タンク部（熱交換器入口タンク部）
１７Ｂ…サブクール部出口タンク部（熱交換器出口タンク部）
１９…補助パイプ部
４３…冷媒導入口
４５…連通孔
４７…冷媒排出口
４９…配管コネクタ
４９ａ…入口側配管コネクタ部
４９ｂ…出口側配管コネクタ部
５５…筒状接続部
１０１…断熱部
１０２…配管コネクタ
３００…コンデンサ（熱交換器）
４００…コンデンサ（熱交換器）
５００…コンデンサ（熱交換器）
６００…コンデンサ（熱交換器）[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a vehicle heat exchanger that exchanges heat with air by flowing a heat exchange medium between header pipes.
[0002]
[Prior art]
As this kind of heat exchange for vehicles, a header pipe is connected and connected to both ends of tubes stacked in multiple stages through outer fins, and a refrigerant taken in from a refrigerant inlet of the header pipe flows through the tubes. It is known that the heat exchange between the refrigerant flowing through the tube and external air is performed, and then the refrigerant is discharged from a refrigerant outlet of a header pipe.
[0003]
By the way, the above-mentioned heat exchanger for vehicles is generally arranged in the engine room of the vehicle, and after the arrangement of the heat exchanger body, the work of connecting the inlet / outlet piping to the header pipe is performed. At this time, depending on the position of the refrigerant outlet provided in the header pipe, the work of connecting the pipe to the refrigerant outlet is forced to have an unnatural posture, and there is a problem that work efficiency is poor.
[0004]
Therefore, as disclosed in, for example, Patent Documents 1 and 2, an auxiliary pipe routed to a refrigerant discharge port provided at a lower end portion of the header pipe to a position (upper end side of the header pipe) where piping connection work is easy. And a structure in which piping and a liquid tank are connected through the auxiliary pipe has been proposed.
[0005]
[Patent Document 1]
Japanese Patent Application Laid-Open No. Hei 10-141887
[Patent Document 2]
JP 10-267467 A
[Problems to be solved by the invention]
However, in this method, a separate auxiliary pipe must be connected to the refrigerant outlet of the header pipe, and the auxiliary pipe must be supported by the header pipe using a support means such as a bracket. For this reason, the auxiliary pipe and the support means protrude from the heat exchanger main body, and the area of the core (radiator) is reduced to accommodate the auxiliary pipe and the support means in a limited space for mounting the vehicle.
[0008]
The present invention has been made on the basis of such conventional technology, and its purpose is to secure the maximum core area in a limited mounting space while securing the ease of piping connection work. The present invention provides a vehicle heat exchanger capable of improving heat exchange performance.
[0009]
[Means for Solving the Problems]
According to the first aspect of the present invention, header pipes are connected to both ends of a plurality of tubes stacked in multiple stages, and a heat exchange medium flows through the tubes to exchange heat between the heat exchange medium flowing through the tubes and external air. In the heat exchanger for a vehicle to be performed, a header pipe including a heat exchanger outlet tank portion constituting the most downstream portion of the core is provided along the main pipe portion having the original function of the header pipe and the main pipe portion. An auxiliary pipe portion communicating with the heat exchanger outlet tank portion of the main pipe, wherein the main pipe portion and the auxiliary pipe portion share one wall.
[0010]
According to a second aspect of the present invention, in the heat exchanger for a vehicle according to the first aspect, the main pipe portion of the header pipe including the auxiliary pipe portion has an inlet and constitutes the most upstream portion of the core. A heat exchanger outlet tank part that constitutes the most downstream part of the exchanger inlet tank part and the core is provided, and a discharge port that opens to the auxiliary pipe part near an inlet that opens to the heat exchanger inlet tank part. It is characterized by having been provided.
[0011]
According to a third aspect of the present invention, in the heat exchanger for a vehicle according to the second aspect, an inlet-side pipe fixed to the header pipe for receiving the inlet-side pipe and connecting the inlet-side pipe with the introduction port. An integrated pipe connector integrally formed with a connector and an outlet pipe connector fixed to the header pipe for receiving the outlet pipe and connecting the outlet pipe to the discharge port is provided. It is assumed that.
[0012]
According to a fourth aspect of the present invention, in the heat exchanger for a vehicle according to the third aspect, an inlet-side pipe connector of the integrated pipe connector is connected to the main pipe by passing through the auxiliary pipe. It is characterized by having a connection part.
[0013]
According to a fifth aspect of the present invention, in the heat exchanger for a vehicle according to any one of the first to third aspects, the heat exchange medium flowing through the main pipe portion and the heat exchange medium flowing through the auxiliary pipe portion pass through the wall. And a heat insulating portion for interrupting the transfer of heat to and from the heat exchanger.
[0014]
According to a sixth aspect of the present invention, in the heat exchanger for a vehicle according to the first aspect, the heat exchange medium is provided between the header pipes in a first pass, a second pass, and the like by a partition plate in the header pipe. And a plurality of meandering circulations, wherein the discharge port opening to the auxiliary pipe portion is arranged at a position corresponding to a path downstream of the first path.
[0015]
According to a seventh aspect of the present invention, in the heat exchanger for a vehicle according to the sixth aspect, the downstream end of the auxiliary pipe portion is set to a position corresponding to a path downstream of the first path, and is opened to the auxiliary pipe portion. The discharge port is arranged at a position corresponding to a path downstream of the first path.
[0016]
【The invention's effect】
According to the first aspect of the present invention, since the auxiliary pipe portion is provided along the main pipe portion, easiness of pipe connection work is ensured as in the related art. Moreover, since the main pipe portion and the auxiliary pipe portion share one wall, unlike the conventional structure in which the auxiliary pipe is provided separately from the header pipe, there is no protrusion due to the support means such as the auxiliary pipe and the bracket. To that extent, the core (radiator) area can be increased in a limited mounting space, and the heat exchange performance can be improved. In other words, according to the first aspect of the present invention, the heat exchange performance can be improved by securing the maximum core area in the limited mounting space while ensuring the ease of the pipe connection work.
[0017]
According to the second aspect of the present invention, it is possible to efficiently connect the inlet side pipe and the outlet side pipe.
[0018]
According to the invention of claim 3, in addition to the effect of the invention of claim 2, the number of parts and the number of manufacturing steps can be reduced by integrally forming the inlet-side piping connector and the outlet-side piping connector, and the manufacturing cost can be further reduced. Can be reduced.
[0019]
According to the invention described in claim 4, even when the main pipe portion is hidden by the auxiliary pipe portion when viewed from the mounting direction of the piping connector, the mounting of the piping connector can be established.
[0020]
According to the invention of claim 5, in addition to the effect of the invention of any one of claims 1 to 3, the heat exchange medium flowing through the main pipe portion and the heat exchange medium flowing through the auxiliary pipe portion by the heat insulating portion. Transfer of heat to and from can be cut off. Thus, the heat exchange medium flowing through the auxiliary pipe portion, that is, the heat exchange medium that has completed heat exchange in the core of the heat exchanger, does not need to be adversely affected by the heat exchange medium before or during heat exchange.
[0021]
According to the sixth aspect of the present invention, in addition to the effect of the first aspect of the present invention, the discharge port opened to the auxiliary pipe portion is arranged at a position corresponding to a path downstream of the first path, so that the structure is compact. However, the refrigerant flowing through the auxiliary pipe portion (the refrigerant that has completed heat exchange in the core) is less likely to be adversely affected by the refrigerant flowing through the first path having the largest temperature difference.
[0022]
According to the seventh aspect of the invention, in addition to the effect of the sixth aspect, the downstream end of the auxiliary pipe portion is set to a position corresponding to a path downstream of the first path, and the drainage opening to the auxiliary pipe portion is provided. Since the outlet is disposed at a position corresponding to a path downstream of the first path, the refrigerant flowing through the auxiliary pipe portion (the refrigerant that has been subjected to heat exchange in the core) does not adversely affect the refrigerant in the first path. The structure is more difficult to receive.
[0023]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, an embodiment in which a heat exchanger according to the present invention is applied to a vehicle condenser will be described with reference to the drawings.
[0024]
First Embodiment FIGS. 1 to 8 show a first embodiment of a heat exchanger according to the present invention. FIG. 1 is an overall view of a condenser (heat exchanger) according to the first embodiment, in which (a) is a top view and (b) is a front view. The condenser 1 is disposed at the front of the engine room of the vehicle, and a pair of left and right header pipes 7, 9 disposed in the up and down direction at both ends of a plurality of flat tubes 5 stacked in multiple stages via corrugated outer fins 3. The connection is established. On the outermost side (upper end side and lower end side) of the tube 5 in the stacking direction, side plates 11 and 13 having a U-shaped cross section extend between the header pipes 7 and 9 to reinforce the tube 5 and the outer fin 3. It is arranged.
[0025]
As shown in FIG. 2, one header pipe 7 (left header pipe) includes a main pipe section 17 and an auxiliary pipe section 19 which are arranged side by side along the longitudinal direction of the header pipe 7. The other header pipe 9 (right header pipe) includes a main pipe section 23 and a liquid tank section 25 which are arranged side by side along the longitudinal direction of the header pipe 7.
[0026]
The condenser 1 according to this embodiment is a subcooled condenser, and is provided in the main pipe sections 17 and 23 of the header pipes 7 and 9 by partitioning plates 27 and 29 which divide the main pipe sections 17 and 23 vertically. The core of the condenser 1 is divided into an upper first path 1A (a condensing section in the first embodiment) and a lower second path 1B (a subcooling section in the first embodiment). A liquid tank portion 25 communicates between a condensing portion outlet tank portion 23A formed above the main pipe portion 23 and a subcool portion inlet tank portion 23B formed below the main pipe portion 23 of the right header pipe 9. It is connected.
[0027]
The feature of this embodiment is that the refrigerant discharged from the heat exchanger outlet tank 17B located at the lower end of the left header pipe 7 is directed upward through the auxiliary pipe 19 to the upper side of the left header pipe 7. It is a point that can be guided.
3 to 8 show the detailed structure of the left header pipe 7. The left header pipe 7 is of a two-part type composed of a tank plate 35 and an end plate 37 fitted to each other. Both ends of the header pipe 7 are closed by closing members 39 and 41, and the internal space is divided into a main pipe section 17 and an auxiliary pipe section 19 by a partition wall section 15 extending in the longitudinal direction. In other words, the main pipe section 17 and the auxiliary pipe section 19 are arranged side by side along the longitudinal direction of the header pipe 7, and the main pipe section 17 and the auxiliary pipe section 19 share one wall (partition wall section 15). I have.
[0028]
A longitudinal end portion of the tube 5 is inserted into a tube mounting port 36 provided at equal intervals along the longitudinal direction of the main pipe portion 17, and the main pipe portion 17 is connected to and connected to the tube 5. With this, the original function of the header pipe is performed. The upper space of the main pipe portion 17 in which the inner space is vertically divided by the partition plate 27 is a heat exchanger inlet tank portion 17A which has the refrigerant inlet 43 opened and constitutes the most upstream portion of the core. The lower space of the main pipe portion 17 is a heat exchanger outlet tank portion 17B constituting the most downstream portion of the core.
[0029]
On the other hand, the auxiliary pipe portion 19 is formed to have the same length as the main pipe portion 17, communicates with the heat exchanger outlet tank portion 17 </ b> B formed in the main pipe portion 17 through the communication hole 45, and has one end of the header pipe 7. The refrigerant discharged from the heat exchanger outlet tank portion 17B of the lower portion (lower portion) is guided to the other end side (upper side) of the header pipe 7.
[0030]
Here, a refrigerant outlet 47 opening to the auxiliary pipe 19 is provided near the refrigerant inlet 43 opening to the heat exchanger inlet tank 17A of the main pipe 17. A block-shaped integral pipe connector 49 in which an inlet-side pipe connector 49a and an outlet-side pipe connector 49b are integrally formed is fixed.
[0031]
The inlet-side piping connector portion 49a has a communication passage 51 for receiving an inlet-side piping (not shown) and connecting the inlet-side piping with the refrigerant inlet 43 of the main pipe portion 17, and has an outlet-side piping connector. The portion 49b has a communication passage 53 for receiving an outlet-side pipe (not shown) and connecting the outlet-side pipe to the refrigerant outlet 47 of the auxiliary pipe section 19 in communication. Here, the piping connector 49 is attached to the header pipe 7 from the auxiliary pipe portion 19 side of the main pipe portion 17 and the auxiliary pipe portion 19 continuously provided along the longitudinal direction of the tube 5. It does not protrude greatly in the thickness direction (ventilation direction) of the core. Correspondingly, the inlet-side piping connector portion 49a of the piping connector 49 penetrates through the auxiliary pipe portion 19, is fitted to the refrigerant inlet 43 of the main pipe portion 17, and is connected to and connected to the main pipe portion 17. A tubular connecting portion 55 is provided. In this embodiment, the tubular connecting portion 55 is formed as a tubular member to be fitted into the fitting hole 57 of the pipe connector main body, and is formed separately from the pipe connector main body.
[0032]
With the above configuration, as shown in FIG. 2, the refrigerant pumped from the compressor (not shown) is introduced into the condenser inlet tank portion (heat exchanger inlet tank portion) 17 </ b> A through the pipe connector 49. The introduced refrigerant flows through the tube 5 of the condenser (first path 1A), flows into the condenser outlet tank 23A, flows into the liquid tank 25, and is separated into gas and liquid. The liquid refrigerant stored in the lower part of the liquid tank section 25 flows into the subcool section inlet tank section 23B through the communication hole 33, flows through the tube 5 of the subcool section (second path 1B), is supercooled, and is subcooled. To the outlet tank section (heat exchanger outlet tank section) 17B. The low-temperature refrigerant that has reached the heat exchanger outlet tank portion 17B flows into the auxiliary pipe portion 19 through the communication hole 45, is guided from the lower end of the auxiliary pipe portion 19 toward the upper end, and is located at the upper end. The refrigerant is discharged from the refrigerant outlet 47 through the pipe connector 49 to the outlet pipe.
[0033]
According to such a capacitor 1, the following effects are obtained.
[0034]
Firstly, since the header pipe 7 includes the main pipe part 17 and the auxiliary pipe part 19 arranged side by side in the longitudinal direction, the pipe mounting work similar to the conventional one is performed by using the auxiliary pipe part 19. Nature can be secured. Moreover, since the main pipe portion 17 and the auxiliary pipe portion 19 share one wall (partition wall portion) 15, unlike the conventional structure in which the auxiliary pipe is provided separately from the header pipe, the auxiliary pipe and the bracket are different. As a result, there is no protrusion due to the supporting means, and the area of the core (radiator) can be increased in the limited space for mounting the vehicle, and the radiation performance can be improved.
[0035]
Second, a heat exchanger inlet tank 17A and a heat exchanger outlet tank 17B are provided in the main pipe portion 17 of one (left side) header pipe 7, and the refrigerant opening to the heat exchanger inlet tank 17A. Since the refrigerant outlet 47 that opens to the auxiliary pipe portion 19 is provided near the inlet 43, the work of connecting the inlet pipe and the outlet pipe can be performed efficiently.
[0036]
Third, in addition to the second effect, by providing the piping connector 49 in which the inlet-side piping connector 49a and the outlet-side piping connector 49b are integrally formed, the number of parts and the number of manufacturing steps can be reduced, and the manufacturing cost can be further reduced. .
[0037]
Fourth, since the inlet side pipe connector portion 49a of the pipe connector 49 includes the cylindrical connection portion 55 that penetrates through the auxiliary pipe portion 19 and is connected to the main pipe portion 17, it is viewed from the mounting direction of the pipe connector 49. Even if the main pipe portion 17 is arranged to be hidden by the auxiliary pipe portion 19, the attachment of the piping connector 49 can be established. In particular, a structure in which the main pipe portion 17 and the auxiliary pipe portion 19 are continuously provided along the longitudinal direction of the tube 5 and a pipe connector 49 is attached from the connection direction can be established, and the thickness direction of the core (ventilation direction). However, the header pipe 7 and the piping connector 49 can be prevented from protruding significantly.
[0038]
In the above-described embodiment, the header pipe 7 including the main pipe section 17 and the auxiliary pipe section 19 is of a two-part type composed of the tank plate 35 and the end plate 37. Alternatively, it may be an integrally formed type by extrusion, and the cross-sectional shape of the header pipe 7 may be, for example, a cross-sectional shape as shown in FIGS. 10 to 13, and is not limited to the above-described embodiment. .
[0039]
Further, in the above-described embodiment, the structure in which the pipe connector 49 is attached along the direction X in which the main pipe portion 17 and the auxiliary pipe portion 19 are connected is adopted. However, in the present invention, for example, as shown in FIG. The pipe connector 102 may be attached to the opening end of the header pipe 7 from the longitudinal direction Z of the header pipe 7, or a direction orthogonal to the direction in which the main pipe section 17 and the auxiliary pipe section 19 are connected. A structure that attaches from Y (see the arrow in FIG. 1) may be used, and is not limited to the above-described embodiment.
[0040]
Second Embodiment FIG. 9 shows a second embodiment of the heat exchanger according to the present invention. The structure of the second embodiment is different from that of the first embodiment in that a heat insulating portion 101 is provided on a partition wall portion 15.
[0041]
According to such a structure, there is an advantage that the transfer of heat between the refrigerant flowing through the main pipe portion 17 and the refrigerant flowing through the auxiliary pipe portion 19 can be blocked. That is, although having a compact structure, the refrigerant flowing through the auxiliary pipe portion 19 (the refrigerant that has been subjected to the heat exchange in the core) is not adversely affected by the refrigerant before or during the heat exchange.
[0042]
Third Embodiment FIG. 15 shows a third embodiment of the heat exchanger according to the present invention. The heat exchanger 300 of the third embodiment differs from the first embodiment mainly in the following two points. First, the number of meanders (the number of passes) of the refrigerant flowing through the core is different from that of the heat exchanger 1 of the first embodiment. Specifically, the first pass 1A, the second pass 1B, and the third pass 1C are configured as a condensing unit, and the fourth pass 1D is configured as a subcool unit, and is configured as a whole with four passes 1A to 1D. . Second, the second embodiment differs from the first embodiment in that the outlet 47 of the auxiliary pipe 19 is arranged at a position corresponding to the path 1B downstream of the first path 1A.
[0043]
According to such a structure, although having a compact structure, the refrigerant flowing through the auxiliary pipe portion 19 (the refrigerant after heat exchange in the core) is separated from the refrigerant flowing through the first path 1A having the largest temperature difference. It does not need to be adversely affected. Similar effects can be obtained even if the inlet-side piping connector 49a and the outlet-side piping connector 49b are formed separately as in the heat exchanger 400 of the fourth embodiment shown in FIG.
[0044]
Fifth Embodiment: FIG. 17 shows a heat exchanger 500 according to a fifth embodiment of the present invention. The heat exchanger 500 of the fifth embodiment is different from the fourth embodiment in that the auxiliary pipe portion 19 is formed from the fourth pass 1D to the second pass 1B. That is, the auxiliary pipe portion 19 does not extend to the first path 1A, but is formed up to a position corresponding to the path 1B downstream of the first path 1A.
[0045]
According to such a structure, the refrigerant flowing through the auxiliary pipe portion 19 (the refrigerant that has been subjected to heat exchange in the core) can be configured to be less likely to be adversely affected by the refrigerant in the first path 1A.
[0046]
In short, according to the present invention, the main pipe portion and the auxiliary pipe portion share one wall (partition wall portion), although the pipe mounting workability can be secured by the auxiliary pipe portion. Unlike the conventional structure in which an auxiliary pipe is provided separately from the header pipe, there is no protrusion due to support means such as the auxiliary pipe and the bracket, and the core (radiator) area can be increased in the limited vehicle mounting space. The heat exchange performance of the heat exchanger can be improved.
[0047]
In the above-described embodiment, the auxiliary pipe portion 19 is formed in the header pipe 7 (the inlet side) provided with the refrigerant inlet 43 (the inlet side pipe connector 49a). In addition, as shown in FIG. 18, a structure in which the auxiliary pipe portion 19 is provided on the other header pipe 9 which does not include the refrigerant introduction port 43 (the inlet side pipe connector 49a) may be used.
[0048]
Further, in the above-described embodiment, the heat exchangers 1, 300, 400, and 500 having the liquid tank 25 and the subcool portion are provided. In the present invention, as shown in FIG. The heat exchanger 600 may not include the tank and the subcool unit. Further, in the present invention, the number of meandering times (number of passes) of the refrigerant flowing through the core is not limited to the above-described embodiment.
[Brief description of the drawings]
FIG. 1A is a top view of a condenser (heat exchanger) according to a first embodiment of the present invention, and FIG. 1B is a front view of the condenser.
FIG. 2 is a schematic diagram showing a flow path of a refrigerant (heat exchange medium) flowing in the condenser.
FIG. 3 is a sectional view of a left header pipe of the condenser.
FIG. 4 is an exploded perspective view showing the vicinity of the upper end of a left header pipe of the condenser.
FIG. 5 is an enlarged view of a section A in FIG. 1 (b) of the cross section taken along line SB-SB in FIG. 1 (a).
FIG. 6 is an enlarged view of a portion B in FIG. 1 (b) of a cross section taken along line SB-SB in FIG. 1 (a).
FIG. 7 is an enlarged exploded view of a portion A in FIG. 1 (b).
FIG. 8 is an enlarged exploded view of a portion B in FIG. 1 (b).
FIG. 9 is a view showing a second embodiment of the present invention, and is a view showing a header pipe in which a heat insulating section is provided between a main pipe section and an auxiliary pipe section.
FIG. 10 is a sectional view showing a modification of the header pipe.
FIG. 11 is a sectional view showing a modification of the header pipe.
FIG. 12 is a sectional view showing a modification of the header pipe.
FIG. 13 is a sectional view showing a modification of the header pipe.
FIG. 14 is a view showing a modified example of the piping connector.
FIG. 15 is a schematic diagram of a condenser (heat exchanger) according to a third embodiment of the present invention.
FIG. 16 is a schematic view of a condenser (heat exchanger) according to a fourth embodiment of the present invention.
FIG. 17 is a schematic view of a condenser (heat exchanger) according to a fifth embodiment of the present invention.
FIG. 18 is a schematic view of a condenser (heat exchanger) according to a sixth embodiment of the present invention.
[Explanation of symbols]
1… Condenser (heat exchanger)
1A 1st pass 1B 2nd pass 1C 3rd pass 1D 4th pass 5 Tube 7 Left header pipe (header pipe)
15: Partition wall (wall)
17: Main pipe section 17A: Condensing section inlet tank section (heat exchanger inlet tank section)
17B: Subcooler outlet tank (heat exchanger outlet tank)
19 ... Auxiliary pipe part 43 ... Refrigerant inlet 45 ... Communication hole 47 ... Refrigerant outlet 49 ... Piping connector 49a ... Inlet side piping connector part 49b ... Outlet side piping connector part 55 ... Cylindrical connection part 101 ... Heat insulation part 102 ... Piping Connector 300: condenser (heat exchanger)
400… Condenser (heat exchanger)
500… Condenser (heat exchanger)
600 ... condenser (heat exchanger)

Claims (7)

複数多段に積層したチューブ（５）の両端にヘッダパイプ（７、９）を連通接続し、熱交換媒体を前記チューブ（５）に流通させてこのチューブ（５）を流通する熱交換媒体と外部空気との熱交換をおこなう車両用熱交換器（１、３００、４００、５００、６００）において、
コアの最下流部を構成する熱交換器出口タンク部（１７Ｂ）を備えるヘッダパイプ（７）は、ヘッダパイプ（７）の本来の機能を有するメインパイプ部（１７）と、前記メインパイプ部（１７）に沿って並設され前記メインパイプ部（１７）の熱交換器出口タンク部（１７Ｂ）と連通される補助パイプ部（１９）と、を備え、
これらメインパイプ部（１７）と補助パイプ部（１９）とで１つの壁（１５）を共有していることを特徴とする車両用熱交換器（１、３００、４００、５００、６００）。Header pipes (7, 9) are connected to both ends of the tubes (5) stacked in multiple stages, and a heat exchange medium is allowed to flow through the tubes (5) so that the heat exchange medium flowing through the tubes (5) is connected to the outside. In a vehicle heat exchanger (1, 300, 400, 500, 600) that performs heat exchange with air,
The header pipe (7) including the heat exchanger outlet tank (17B) constituting the most downstream portion of the core includes a main pipe (17) having an original function of the header pipe (7) and the main pipe (17). 17) an auxiliary pipe section (19) which is arranged in parallel along 17) and communicates with the heat exchanger outlet tank section (17B) of the main pipe section (17).
A heat exchanger for vehicles (1, 300, 400, 500, 600) characterized in that one wall (15) is shared by the main pipe part (17) and the auxiliary pipe part (19). 請求項１記載の車両用熱交換器（１、３００、４００、５００、６００）において、
前記メインパイプ部（１７）および補助パイプ部（１９）を備えるヘッダパイプ（７）は、そのメインパイプ部（１７）が、導入口（４３）を有してコアの最上流部を構成する熱交換器入口タンク部（１７Ａ）およびコアの最下流部を構成する熱交換器出口タンク部（１７Ｂ）を備え、
前記熱交換器入口タンク部（１７Ａ）に開口する導入口（４３）の近傍に、前記補助パイプ部（１９）に開口する排出口（４７）を設けたことを特徴とする車両用熱交換器（１）。The vehicle heat exchanger (1, 300, 400, 500, 600) according to claim 1,
The header pipe (7) provided with the main pipe section (17) and the auxiliary pipe section (19) has a main pipe section (17) having an inlet (43) and constituting the most upstream part of the core. A heat exchanger outlet tank part (17B) that constitutes the exchanger inlet tank part (17A) and the most downstream part of the core;
An exhaust port (47) opening to the auxiliary pipe section (19) is provided near an inlet port (43) opening to the heat exchanger inlet tank section (17A). (1). 請求項２記載の車両用熱交換器（１）において、
前記ヘッダパイプ（７）に固定され入口側配管を受け入れて該入口側配管と前記導入口（４３）とを連通接続するための入口側配管コネクタ（４９ａ）と、前記ヘッダパイプ（７）に固定され出口側配管を受け入れて該出口側配管と前記排出口（４７）とを連通接続するための出口側配管コネクタ（４９ｂ）と、を一体形成した一体型の配管コネクタ（４９）を設けたことを特徴とする車両用熱交換器（１）。The vehicle heat exchanger (1) according to claim 2,
An inlet-side pipe connector (49a) fixed to the header pipe (7) for receiving the inlet-side pipe and communicating the inlet-side pipe with the inlet (43), and fixed to the header pipe (7). And an outlet-side piping connector (49b) for receiving the outlet-side piping and connecting the outlet-side piping with the discharge port (47). A heat exchanger for a vehicle (1), characterized in that: 請求項３記載の車両用熱交換器（１）において、
前記配管コネクタ（４９）の入口側配管コネクタ部（４９ａ）は、前記補助パイプ部（１９）を貫通してメインパイプ部（１７）に連通接続される筒状接続部（５５）を備えることを特徴とする車両用熱交換器（１）。The vehicle heat exchanger (1) according to claim 3,
An inlet-side pipe connector (49a) of the pipe connector (49) includes a tubular connection part (55) penetrating the auxiliary pipe part (19) and connected to the main pipe part (17). A heat exchanger for a vehicle (1). 請求項１〜３のいずれか１項記載の車両用熱交換器（１）において、
前記壁（１５）に、メインパイプ部（１７）を流通する熱交換媒体と補助パイプ部（１９）を流通する熱交換媒体との熱の授受を遮断するための断熱部（１０１）を設けたことを特徴とする車両用熱交換器（１）。The vehicle heat exchanger (1) according to any one of claims 1 to 3,
The wall (15) is provided with a heat insulating portion (101) for blocking the transfer of heat between the heat exchange medium flowing through the main pipe portion (17) and the heat exchange medium flowing through the auxiliary pipe portion (19). A vehicle heat exchanger (1), characterized in that: 請求項１記載の車両用熱交換器（１、３００、４００、５００、６００）において、
前記ヘッダパイプ（７、９）内の仕切板の区画によって、前記熱交換媒体が前記ヘッダパイプ（７、９）間を第１パス（１Ａ）、第２パス（１Ｂ）、・・・と複数回蛇行して流通する構造であり、
前記補助パイプ部（１９）に開口する排出口（４７）を第１パス（１Ａ）より下流のパス（１Ｂ、・・）に対応する位置に配置したことを特徴とする車両用熱交換器（３００、４００、５００、６００）。The vehicle heat exchanger (1, 300, 400, 500, 600) according to claim 1,
The heat exchange medium passes between the header pipes (7, 9) in a plurality of first pass (1A), second pass (1B),... It is a meandering and circulating structure,
A heat exchanger (4) for a vehicle, wherein a discharge port (47) opening to the auxiliary pipe portion (19) is arranged at a position corresponding to a path (1B,...) Downstream of the first path (1A). 300, 400, 500, 600). 請求項６記載の車両用熱交換器（３００，４００、５００、６００）において、
前記補助パイプ部（１９）の下流端部を第１パス（１Ａ）より下流のパス（１Ｂ、・・）に対応する位置までとし、
前記補助パイプ部（１９）に開口する排出口（４７）を第１パス（１Ａ）より下流のパス（１Ｂ、・・）に対応する位置に配置したことを特徴とする車両用熱交換器（５００）。The vehicle heat exchanger (300, 400, 500, 600) according to claim 6,
The downstream end of the auxiliary pipe part (19) is set to a position corresponding to a path (1B,...) Downstream from the first path (1A),
A heat exchanger (4) for a vehicle, wherein a discharge port (47) opening to the auxiliary pipe portion (19) is arranged at a position corresponding to a path (1B,...) Downstream of the first path (1A). 500).
JP2003176809A 2002-12-11 2003-06-20 Vehicular heat exchanger Pending JP2004239592A (en)

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