JP4041727B2

JP4041727B2 - Tube for heat exchanger

Info

Publication number: JP4041727B2
Application number: JP2002358960A
Authority: JP
Inventors: 吉田　　敬; 泰典植野
Original assignee: Japan Climate Systems Corp
Current assignee: Japan Climate Systems Corp
Priority date: 2002-12-11
Filing date: 2002-12-11
Publication date: 2008-01-30
Anticipated expiration: 2022-12-11
Also published as: JP2004190936A

Description

【０００１】
【発明の属する技術分野】
本発明は、例えば、空調装置の冷凍サイクルの一要素を構成する熱交換器のチューブに関し、特に、板材を折り曲げて構成する構造の技術分野に属する。
【０００２】
【従来の技術】
従来より、この種の熱交換器用チューブとして、板材の両端縁部を係合させて該係合部をろう付けすることにより内部に冷媒が流通する流路が形成される扁平板状体からなるチューブが知られている（例えば、特許文献１参照。）。
【０００３】
前記特許文献１の熱交換器用チューブは、図９に示すように、一枚の板材１００の幅方向両側が上下に対向するように該板材の幅方向中央部を折り曲げ、上側の端縁部を流路内方に略１８０゜折り返して折り返し部１００ａとし、一方、下側の端縁部を、流路内方に略１８０゜折り返した後、さらに逆方向に折り返して、前記折り返し部１００ａと係合する係合部１００ｂとしている
これにより、ろう付け工程における炉内搬入時の振動によって上側及び下側の両端縁部が離れることはなく、確実にろう付けすることができるとともに、ろう付け後、冷媒の圧力により両端縁部が離れるのを未然に防止でき、よって、チューブの耐圧性を十分に得ることができる。
【０００４】
【特許文献１】
特開平１１―２４８３８３号公報（第３頁、第４頁、図１、図３）
【０００５】
【発明が解決しようとする課題】
しかしながら、前記特許文献１の熱交換器用チューブにおいては、比較的煩雑な成形工程を要する折り返し成形を多く行わなければならず、チューブの製造コストが高騰する。
【０００６】
また、板材を略１８０゜折り返すと、通常、断面形状がＵ字状をなし、前記特許文献１のチューブでは、上側及び下側の端縁部を係合させた状態では、折り返し成形した部分が上下に重合することになり、その流路外方に凹部１０２が形成される。このようにチューブ外周面に凹部１０２が形成されると、チューブをヘッダタンクのチューブ保持用孔部に挿入した際、チューブ外周面とチューブ保持用孔部周縁との間に前記凹部１０２による隙間が形成されてろう付け不良となることがある。
【０００７】
本発明は斯かる諸点に鑑みてなされたものであり、その目的とするところは、製造コストの高騰を招くことなく、両端縁部を係合させてチューブの耐圧性を十分に得るとともに、そのチューブをヘッダタンクのチューブ保持用孔部周縁に確実にろう付けすることにある。
【０００８】
【課題を解決するための手段】
前記目的を達成するために、本発明では、一方の端縁部にのみ折り返し部を形成し、他方の端縁部を前記折り返し部に嵌合する嵌合部とし、両者の係合部外面に段差が生じないようにした。
【０００９】
具体的には、請求項１の発明では、両端縁部を係合させて該係合部をろう付けすることにより内部に冷媒が流通する流路が形成される扁平板状体からなり、ヘッダタンクに形成されたチューブ保持用孔部に端部が挿入されて該チューブ保持用孔部周縁にろう付けされる熱交換器用チューブを対象とする。
【００１０】
そして、一方の端縁部を、流路内方へ折り曲げられその先端側が流路外方かつ逆向きに略１８０゜折り返されてなる折り返し部とし、他方の端縁部を、前記折り返し部に外方から沿うように折り曲げられその先端側が前記折り返し部先端面に当接するように形成されてなる嵌合部とし、前記嵌合部を、前記係合部外面におけるチューブ保持用孔部への挿入部分に段差が生じないように形成する構成とする。
【００１１】
この構成によれば、嵌合部が略１８０゜折り返された折り返し部に嵌合するので、両端縁部がしっかりと係合してチューブの耐圧性が十分に得られるとともに、成形が煩雑となる折り返し部は一方の端縁部の１箇所に形成されているだけなので、従来のチューブに比べて製造コストが低減される。
【００１２】
また、嵌合部は、両端縁部の係合部外面におけるチューブ保持用孔部への挿入部分に段差が生じないように形成されているので、チューブ外周面とヘッダタンクのチューブ保持用孔部周縁との間に隙間が形成されることはなく、よって、チューブがヘッダタンクに確実にろう付けされる。
【００１３】
請求項２の発明では、請求項１の発明において、折り返し部及び嵌合部の互いに当接する当接面の少なくとも一方には、ろう材を層状に設ける構成とする。
【００１４】
この構成によれば、嵌合部を折り返し部に嵌合させた後、炉内に搬入するだけで、ろう材により両当接面全体が同時にろう付けされるので、製造工数の低減が図られる。
【００１５】
請求項３の発明では、請求項１の発明において、一方の端縁部側の外面には放熱用のフィンをろう付けし、他方の端縁部の嵌合部外面と前記フィンとの間には隙間を形成する構成とする。
【００１６】
この構成によれば、製造誤差やろう付けの際の熱歪み等により各部の形状が所期の形状に対してわずかに異なっても、嵌合部外面とフィンとの間に隙間が形成されるように各部が形状設定されているので、フィンが嵌合部と接触して一方の端縁部外面から浮き上がるようになることはない。これにより、フィンの接合面全体がしっかりとろう付けされる。
【００１７】
請求項４の発明では、請求項１の発明において、流路内には、対向する流路内面を連結する連結部材を設ける構成とする。
【００１８】
この構成によれば、チューブの耐圧性がより一層高まり、また、連結部材は流路を構成する部材と別体であるので、形状設定を自由に行うことが可能となる。
【００１９】
請求項５の発明では、請求項１の発明において、対向する流路内面の少なくとも一方には、他方に接合されてろう付けされる突出部を一体に突設する構成とする。
【００２０】
この構成によれば、部品点数の増加を招くことなく、チューブの耐圧性がより一層高まる。
【００２１】
請求項６の発明では、請求項５の発明において、一方の流路内面の突出部が他方の流路内面に接合した状態で、折り返し部と該折り返し部に対向する流路内面との間には隙間を形成する構成とする。
【００２２】
この構成によれば、製造誤差や熱歪み等により各部材の形状が所期の形状に対してわずかに異なっても、折り返し部と流路内面との間に隙間が形成されるように各部が形状設定されているので、これら折り返し部と流路内面とが接触して突出部が接合面から離れるようになることはなく、該突出部がしっかりとろう付けされる。
【００２３】
請求項７の発明では、請求項５の発明において、突出部を互いに間隔をあけて複数形成し、突出方向から見て、略円形又は冷媒の流通方向に長い略長円形とする構成とする。
【００２４】
この構成によれば、複数の突出部により冷媒の流れを適度に乱すことが可能となり、熱交換効率が向上する。このとき、突起部が略円形又は略長円形とされているので、冷媒の流通抵抗が大幅に増加することはない。
【００２５】
請求項８の発明では、請求項５の発明において、突出部は、冷媒の流通方向に延びる突条部である構成とする。
【００２６】
この構成によれば、対向する流路内面が冷媒の流通方向に連続して接合するので、耐圧性がより一層向上する。
【００２７】
【発明の実施の形態】
以下、本発明の実施形態を図面に基づいて説明する。
【００２８】
図２は、本発明の実施形態に係る熱交換器を示し、本例では、熱交換器が車両用空調装置の冷凍サイクルの一要素を構成する凝縮器１である場合を示す。該凝縮器１は、車体のエンジンルーム（図示せず）の前端部に搭載されており、車幅方向に延びる複数のチューブ２，２，…及び放熱用のフィン３，３，…を上下に交互に並設してなるコア４と、該コア４のチューブ２両端部にそれぞれ配置されて該チューブ２と連通する左側ヘッダタンク５及び右側ヘッダタンク６とを備えてなり、走行風（図２に矢印Ａで示す）がコア４を車体前方から後方へ通過することにより熱交換されるようになっている。
【００２９】
コア４の各チューブ２は、図３に示すように、扁平板状体であり、一方、各フィン３は、チューブ２の長手方向両端近傍に亘るように形成されたコルゲートフィンである。隣り合うチューブ２，２の離間距離はフィン３の上下の長さに対応していて、該フィン３の上端及び下端が、隣り合うチューブ２，２の外面にろう付けされるようになっている。これらフィン３，３，…のうちコア４の上端及び下端に位置するフィン３は、エンドプレート７，７によりそれぞれ保持されている。
【００３０】
前記左側及び右側ヘッダタンク５，６はアルミ合金からなるものであり、コア４の上端から下端に亘って真っ直ぐに延びる略円筒状に形成され、その外面にはろう材が層状に設けられている。各ヘッダタンク５，６の上端及び下端は円形に開口しており、該開口はキャップ部材８によりそれぞれ閉塞され、これにより、内部に前記各チューブ２端部と連通する中空部が形成される。
【００３１】
左側ヘッダタンク５の上部には、冷媒を前記中空部に流入させるための流入用クーラパイプ１０が接続され、一方、右側ヘッダタンク６の下部には、中空部の冷媒を流出させるための流出用クーラパイプ１１が接続されている。また、前記左側及び右側ヘッダタンク５，６のコア４側には、各チューブ２の外形に対応するチューブ保持用孔部１２、１２，…がチューブ２，２，…の間隔に対応して形成されており、各チューブ２の端部が挿入されて該チューブ２外周面とチューブ保持用孔部１２周縁とがろう付けされるようになっている。
【００３２】
前記各チューブ２は、図１（ｂ）に示すように、その上側を形成する上側板材１３と、該上側板材１３の下面に対向配置されてチューブ２の下側を構成する下側板材１４とから構成されており、これら上側及び下側板材１３，１４は、両面にろう材が層状に設けられたアルミ合金製薄板材である。
【００３３】
前記上側及び下側板材１３，１４は、チューブ２幅方向（車体前後方向）の両端縁部を互いに係合させて該係合部１５，１５がそれぞれろう付けされるようになっており、これにより、内部に冷媒が流通する流路が形成されたチューブ２となる。
【００３４】
前記上側板材１３の車体前縁部は、図４に示すように、下側へ略直角に折り曲げられその先端が流路外方かつ逆向きに略１８０゜折り返されてなる折り返し部１３ａとされている。従って、該折り返し部１３ａは、上側板材１３が２枚重合した厚さを有しており、車両走行時の小石等の飛来によるチューブ２の損傷が防止されるようになっている。また、折り返し部１３ａは、冷媒の流通方向から見て略Ｕ字状をなしており、その下端は、下側板材１４内面との間に隙間Ｒが形成されるように位置付けられる一方、上端は、上側板材１３の外面よりも下側板材１４の厚みに対応する長さだけ下方に位置している。
【００３５】
前記下側板材１４の車体前縁部は、前記上側板材１３の折り返し部１３ａに流路外方から沿うように上方へ略直角に折り曲げられその先端が前記折り返し部１３ａ上端面（先端面）に当接するように形成されてなる嵌合部１４ａとされている。つまり、嵌合部１４ａは、前記の如く上側部材１３の外面よりも下方に位置している折り返し部１３ａ先端面に当接するように形成されているので、嵌合部１４ａ外面が上側板材１４外面と略同一面に位置することとなり、係合部１５外面に段差が生じないようになっている。
【００３６】
尚、図１に示すように、前記上側及び下側板材１３，１４の車体後側の両端縁部も前記車体前側の両端縁部と同様に構成されており、折り返し部１３ａ及び嵌合部１４ａが互いに係合し、該係合部１５がろう付けされるようになっている。
【００３７】
また、上側及び下側板材１３，１４の流路内面には、対向する部位から流路内へそれぞれ突出してなる第１及び第２突出部１３ｂ，１４ｂが複数形成されている。該各突出部１３ｂ，１４ｂは互いに同形状とされ、その先端はチューブ２の上下方向の略中央部に位置していて互いに接合してろう付けされるようになっている。各突出部１３ｂ，１４ｂは、チューブ２幅方向及び長手方向の両方向について互いに等しい間隔をあけて形成されており、チューブ２幅方向に並ぶ各突出部１３ｂ，１４ｂは直線状に位置付けられる一方、チューブ２長手方向に並ぶ各突出部１３ｂ，１４ｂは隣り合うものがチューブ２幅方向に互いにずれている。これにより、冷媒の流れが適度に乱され、熱交換効率の向上が図られる。また、各突出部１３ｂ，１４ｂは、突出方向から見て、略円形状とされているので、突出部１３ｂ，１４ｂを設けることによる冷媒の流通抵抗の増加が抑制される。
【００３８】
したがって、この実施形態に係る熱交換器用チューブ２によれば、下側板材１４の嵌合部１４ａを上側板材１３の折り返し部１３ａに嵌合させるようにしたので、成形が煩雑となる折り返し部の形成箇所を従来のチューブと比べて少なくして製造コストを低減しつつ、上側及び下側板材１３，１４の両端縁部をしっかりと係合させることができる。これにより、上側及び下側板材１３，１４の係合部１５，１５をろう付けする際、炉内への搬入時の振動や加熱時の変形によって両端縁部が互いに離れるようになることはなく、確実にろう付けすることができるとともに、ろう付け後、冷媒の圧力により上側及び下側板材１３，１４の両端縁部が離れるのを防止でき、よって、チューブ２の耐圧性を十分に得ることができる。
【００３９】
また、嵌合部１４ａが、係合部１５外面におけるチューブ保持用孔部１２への挿入部分に段差が生じないように形成されているので、各チューブ２の端部をヘッダタンク５，６のチューブ保持用孔部１２に挿入すると、チューブ２外周面とチューブ保持用孔部１２周縁との間に隙間が形成されることはなく、チューブ２をヘッダタンク５，６に確実にろう付けできる。
【００４０】
このろう付けの際には、上側及び下側板材１３，１４にろう材が層状に設けられているので、両板材１３，１４を成形してから嵌合部１４ａを折り返し部１３ａに嵌合させた後、炉内に搬入するだけで両当接面全体を同時にろう付けでき、よって、製造工数を低減できる。
【００４１】
また、折り返し部１３ａの下端と下側板材１４内面との間に隙間Ｒが形成されるように両者の形状が設定されているので、製造誤差やろう付けの際の熱歪みにより上側及び下側板材１３，１４の形状が所期の形状に対してわずかに異なっても、折り返し部１３ａと下側板材１４とが接触することはない。これにより、第１及び第２突出部１３ｂ，１４ｂの両接合面が互いに離れるようになることはなく、該両突出部１３ｂ，１４ｂをしっかりとろう付けでき、チューブ２の耐圧性を十分に確保できる。
【００４２】
尚、前記実施形態では、突出部１３ｂ，１４ｂが、その突出方向から見て、略円形とされているが、これに限らず、例えば、図５に示す変形例１のように、第１及び第２突出部１３ｂを冷媒の流通する方向に長い略長円形としてもよい。この場合では、各突出部１３ｃの形成による流路断面積の減少度合いを小さくしつつ、上側及び下側板材１３，１４のろう付け面積を拡大することができ、これにより、チューブ２の耐圧性をより一層向上できる。
【００４３】
前記突出部１３ｂ，１４ｂとしては、図６に示す変形例２のように、チューブ２長手方向両端に亘って真っ直ぐに延びる第１及び第２突条部１３ｄ，１４ｄをチューブ２幅方向に複数並設するようにしてもよい。この場合では、チューブ２長手方向両端に亘って上側及び下側板材１３，１４が接合するので、チューブ２の耐圧性をより一層向上できる。
【００４４】
また、前記第１及び第２突出部１３ｂ，１４ｂを形成することなく、図７に示す変形例３のように、流路内に、上側及び下側板材１３，１４とは別体に形成されて対向する流路内面を連結する連結部材２０を配設するようにしてもよい。連結部材２０はアルミ合金製板材からなり、該板材には、上方へ突出してチューブ２長手方向両端に亘って延びる突条部２０ａがチューブ２幅方向に複数形成されている。そして、この連結部材２０の下面が、下側板材１４の流路内面にろう付けされるとともに、突条部２０ａの上端部が上側板材１３の流路内面にろう付けされ、これにより、上側及び下側板材１３，１４がチューブ２長手方向両端に亘って連結されるので、チューブ２の耐圧性をより一層向上できる。
【００４５】
この場合、連結部材２０が上側及び下側板材１３，１４とは別体に形成されているので、例えば、連結部材２０の板厚を両板材１３，１４とは異ならせることが可能となり、連結部材２０の形状設定を自由に行うことができる。
【００４６】
また、前記実施形態では、チューブ２の長手方向両端に亘って係合部１５外面に段差が生じないように構成しているが、これに限らず、図８に示す変形例４のように、フィン３との接合部分においては、嵌合部１４ａ外面が上側板材１３外面よりも下方に位置するように構成してもよい。これにより、嵌合部１４ａ外面とフィン３下面との間に隙間Ｓが形成されるので、製造誤差やろう付けの際の熱歪み等により、各板材１３，１４の形状が所期の形状に対してわずかに異なっても、嵌合部１４ａ外面がフィン３下面を押圧するようになることはなく、これにより、上側板材１３外面からフィン３が浮き上がるようになることを防止でき、よって、フィン３の接合面全体をしっかりとろう付けできる。
【００４７】
さらに、前記実施形態では、上側板材１３及び下側板材１４の２つの部材を組み合わせてチューブ２を構成するようにしているが、チューブ２を１枚の板材からなるものとした場合には、その板材の幅方向両端縁部が上下に対向するように該板材を幅方向中央部で折り曲げ、その両端縁部を、前記実施形態と同様に係合させてろう付けするようにすればよい。
【００４８】
【発明の効果】
以上説明したように、請求項１の発明に係る熱交換器用チューブによると、一方の端縁部を、流路内方へ折り曲げその先端を流路外方かつ逆向きに折り返してなる折り返し部とし、他方の端縁部を、前記折り返し部先端面に当接するように形成してなる嵌合部としたので、コストの高騰を招くことなく、チューブの耐圧性を十分に得ることができる。また、折り返し部と嵌合部との係合部外面に段差が生じないように、嵌合部を形成したので、チューブ外周面とヘッダタンクのチューブ保持用孔部周縁との間に隙間が形成されることはなく、よって、チューブをヘッダタンクに確実にろう付けできる。
【００４９】
請求項２記載の発明によると、折り返し部及び嵌合部の当接面の少なくとも一方にろう材を層状に設けたので、嵌合部を折り返し部に嵌合させた後、炉内に搬入するだけで、両当接面全体を同時にろう付けでき、よって、製造工数を低減できる。
【００５０】
請求項３記載の発明によると、一方の端縁部側の外面にフィンをろう付けし、嵌合部外面とフィンとの間に隙間を形成するようにしたので、製造誤差やろう付けの際の熱歪み等により各部材の形状が所期の形状に対してわずかに異なっても、フィンをしっかりとろう付けできる。
【００５１】
請求項４記載の発明によると、対向する流路内面を連結する連結部材を流路内に設けるようにしたので、チューブの耐圧性をより一層高めることができる。
【００５２】
請求項５記載の発明によると、対向する流路内面の少なくとも一方に、他方にろう付けされる突出部を突設したので、部品点数の増加を招くことなく、チューブの耐圧性をより一層高めることができる。
【００５３】
請求項６記載の発明によると、突出部が流路内面に接合した状態で、折り返し部と流路内面との間に隙間を形成するようにしたので、製造誤差等により各部材の形状が所期の形状に対してわずかに異なっても、突出部の接合面全体をしっかりとろう付けできる。
【００５４】
請求項７記載の発明によると、複数の突出部により冷媒の流れが適度に乱されて熱交換効率を向上でき、このとき、突起部が略円形又は略長円形とされているので、冷媒の流通抵抗が大幅に増加することを防止できる。
【００５５】
請求項８記載の発明によると、突出部が冷媒の流通方向に延びる突条部であるので、チューブの耐圧性をより一層向上できる。
【図面の簡単な説明】
【図１】（ａ）はチューブ端部の平面図であり、（ｂ）はチューブを冷媒の流通方向一側から見た図である。
【図２】凝縮器を車体後側から見た斜視図である。
【図３】図２の左側ヘッダタンク上部及びコア上部近傍を拡大して示す分解斜視図である。
【図４】図１（ｂ）の左側端部の拡大図である。
【図５】変形例１に係る図１（ａ）相当図である。
【図６】変形例２に係る図１相当図である。
【図７】変形例３に係る図１相当図である。
【図８】変形例４に係り、チューブの長手方向中央部の縦断面図である。
【図９】従来のチューブを示す図１（ｂ）相当図である。
【符号の説明】
２チューブ
３フィン
５，６ヘッダタンク
１２チューブ保持用孔部
１３ａ折り返し部
１３ｂ突出部
１３ｄ突条部
１４ａ嵌合部
１４ｂ突出部
１４突条部
１５係合部
２０連結部材
Ｒ隙間
Ｓ隙間[0001]
BACKGROUND OF THE INVENTION
The present invention relates to, for example, a tube of a heat exchanger that constitutes one element of a refrigeration cycle of an air conditioner, and particularly belongs to the technical field of a structure in which a plate material is bent.
[0002]
[Prior art]
Conventionally, this type of heat exchanger tube is made of a flat plate-like body in which a flow path through which a refrigerant flows is formed by engaging both end edges of a plate material and brazing the engaging portion. A tube is known (for example, refer to Patent Document 1).
[0003]
As shown in FIG. 9, the heat exchanger tube of Patent Document 1 bends the central portion in the width direction of the sheet material 100 so that both sides in the width direction of the sheet material 100 are vertically opposed to each other, and forms the upper edge portion. Folded approximately 180 ° inward of the flow path to form a folded portion 100a. On the other hand, the lower edge is folded back approximately 180 ° inward of the flow channel and then folded back in the opposite direction to engage with the folded portion 100a. As a result, the upper and lower end edges are not separated from each other by vibration at the time of carrying in the furnace in the brazing process, and can be brazed reliably. It is possible to prevent the end edges from separating due to the pressure of the refrigerant, and thus the pressure resistance of the tube can be sufficiently obtained.
[0004]
[Patent Document 1]
JP 11-248383 A (3rd page, 4th page, FIG. 1 and FIG. 3)
[0005]
[Problems to be solved by the invention]
However, in the heat exchanger tube of Patent Document 1, a large amount of folding forming that requires a relatively complicated forming step must be performed, and the manufacturing cost of the tube increases.
[0006]
Further, when the plate material is folded back approximately 180 °, the cross-sectional shape is usually U-shaped. In the tube of Patent Document 1, when the upper and lower end edges are engaged, the folded portion is formed. It will superpose | polymerize up and down, and the recessed part 102 is formed in the flow path outer side. When the recess 102 is formed on the outer peripheral surface of the tube in this way, when the tube is inserted into the tube holding hole of the header tank, a gap due to the recess 102 is formed between the tube outer peripheral surface and the periphery of the tube holding hole. Forming may cause poor brazing.
[0007]
The present invention has been made in view of such various points, and the object of the present invention is to obtain sufficient pressure resistance of the tube by engaging both end edges without incurring an increase in manufacturing cost. The purpose is to securely braze the tube to the periphery of the tube holding hole of the header tank.
[0008]
[Means for Solving the Problems]
In order to achieve the above object, in the present invention, a folded portion is formed only at one end edge portion, and the other end edge portion is a fitting portion that fits into the folded portion, and is formed on the outer surface of both engaging portions. The step was not made.
[0009]
Specifically, in the first aspect of the invention, the header comprises a flat plate-like body in which a flow path through which a refrigerant flows is formed by engaging both edge portions and brazing the engaging portion. An object is a tube for a heat exchanger in which an end is inserted into a tube holding hole formed in a tank and brazed to the periphery of the tube holding hole.
[0010]
Then, one end edge portion is folded inwardly of the flow path, and a tip end side thereof is folded back approximately 180 ° outwardly and in the opposite direction, and the other end edge portion is externally connected to the folded portion. A fitting portion formed so as to be bent from the side so that a tip end side thereof is in contact with the tip end surface of the folded portion, and the fitting portion is inserted into the tube holding hole on the outer surface of the engaging portion. The structure is formed so as not to cause a step.
[0011]
According to this configuration, since the fitting portion is fitted to the folded portion that is folded back by about 180 °, both end edges are firmly engaged to obtain sufficient pressure resistance of the tube, and the molding becomes complicated. Since the folded portion is only formed at one place on one end edge portion, the manufacturing cost is reduced as compared with the conventional tube.
[0012]
In addition, since the fitting portion is formed so that there is no step in the insertion portion to the tube holding hole portion on the outer surface of the engaging portion at both end edges, the tube outer peripheral surface and the tube holding hole portion of the header tank There is no gap formed between the periphery and the tube is securely brazed to the header tank.
[0013]
According to a second aspect of the present invention, in the first aspect of the present invention, a brazing material is provided in a layered manner on at least one of the contact surfaces of the folded portion and the fitting portion that contact each other.
[0014]
According to this configuration, after the fitting portion is fitted to the turn-up portion, the entire contact surface is brazed simultaneously by the brazing material only by carrying it into the furnace, so that the number of manufacturing steps can be reduced. .
[0015]
In the invention of claim 3, in the invention of claim 1, a fin for heat dissipation is brazed to the outer surface on the one end edge side, and between the outer surface of the fitting part on the other end edge and the fin. Is configured to form a gap.
[0016]
According to this configuration, a gap is formed between the outer surface of the fitting portion and the fin even if the shape of each part is slightly different from the intended shape due to manufacturing errors, thermal distortion during brazing, and the like. Thus, since each part is set in shape, the fin does not come into contact with the fitting part and does not float from the outer surface of one end edge part. Thereby, the whole joining surface of a fin is brazed firmly.
[0017]
According to a fourth aspect of the present invention, in the first aspect of the present invention, a connection member for connecting the inner surfaces of the opposed flow paths is provided in the flow path.
[0018]
According to this configuration, the pressure resistance of the tube is further increased, and the connecting member is a separate member from the member constituting the flow path, so that the shape can be freely set.
[0019]
According to a fifth aspect of the present invention, in the first aspect of the present invention, at least one of the opposed inner surfaces of the flow path is configured to project integrally with a protruding portion that is joined to the other and brazed.
[0020]
According to this configuration, the pressure resistance of the tube is further enhanced without increasing the number of parts.
[0021]
According to a sixth aspect of the present invention, in the fifth aspect of the invention, in a state where the protruding portion of one flow path inner surface is joined to the other flow path inner surface, between the folded portion and the flow channel inner surface facing the folded portion. Is configured to form a gap.
[0022]
According to this configuration, even if the shape of each member is slightly different from the intended shape due to manufacturing error, thermal distortion, etc., each part is formed so that a gap is formed between the folded portion and the flow path inner surface. Since the shape is set, the folded portion and the flow channel inner surface do not come into contact with each other, and the protruding portion does not come away from the joint surface, and the protruding portion is firmly brazed.
[0023]
According to the invention of claim 7, in the invention of claim 5, a plurality of projecting portions are formed at intervals to form a substantially circular shape or a substantially oval shape that is long in the refrigerant flow direction when viewed from the projecting direction.
[0024]
According to this configuration, the refrigerant flow can be appropriately disturbed by the plurality of protrusions, and the heat exchange efficiency is improved. At this time, since the protrusion is substantially circular or oval, the flow resistance of the refrigerant does not increase significantly.
[0025]
According to an eighth aspect of the present invention, in the fifth aspect of the present invention, the protrusion is a protrusion that extends in the refrigerant flow direction.
[0026]
According to this configuration, the inner surfaces of the opposed flow paths are continuously joined in the refrigerant flow direction, so that the pressure resistance is further improved.
[0027]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0028]
FIG. 2 shows a heat exchanger according to an embodiment of the present invention. In this example, the heat exchanger is a condenser 1 constituting one element of a refrigeration cycle of a vehicle air conditioner. The condenser 1 is mounted at a front end portion of an engine room (not shown) of the vehicle body, and a plurality of tubes 2, 2,... Extending in the vehicle width direction and fins 3, 3,. It comprises a core 4 that is alternately arranged, and a left header tank 5 and a right header tank 6 that are disposed at both ends of the tube 2 of the core 4 and communicate with the tube 2, respectively. The heat exchange is performed by passing the core 4 from the front to the rear of the vehicle body.
[0029]
As shown in FIG. 3, each tube 2 of the core 4 is a flat plate-like body, while each fin 3 is a corrugated fin formed to extend in the vicinity of both ends in the longitudinal direction of the tube 2. The distance between the adjacent tubes 2 and 2 corresponds to the vertical length of the fin 3, and the upper and lower ends of the fin 3 are brazed to the outer surfaces of the adjacent tubes 2 and 2. . Of these fins 3, 3,..., The fins 3 positioned at the upper and lower ends of the core 4 are held by end plates 7 and 7, respectively.
[0030]
The left and right header tanks 5 and 6 are made of an aluminum alloy, and are formed in a substantially cylindrical shape extending straight from the upper end to the lower end of the core 4, and brazing materials are provided in layers on the outer surface thereof. . The upper and lower ends of the header tanks 5 and 6 are opened in a circular shape, and the openings are respectively closed by the cap member 8, thereby forming a hollow portion communicating with the end of each tube 2.
[0031]
The upper header of the left header tank 5 is connected to an inflow cooler pipe 10 for allowing the refrigerant to flow into the hollow part, while the lower part of the right header tank 6 is used for the outflow for allowing the refrigerant in the hollow part to flow out. A cooler pipe 11 is connected. Further, tube holding holes 12, 12,... Corresponding to the outer shape of each tube 2 are formed on the left and right header tanks 5, 6 corresponding to the interval between the tubes 2, 2,. The end of each tube 2 is inserted, and the outer peripheral surface of the tube 2 and the periphery of the tube holding hole 12 are brazed.
[0032]
As shown in FIG. 1 (b), each of the tubes 2 includes an upper plate 13 that forms the upper side thereof, and a lower plate 14 that is disposed opposite to the lower surface of the upper plate 13 and constitutes the lower side of the tube 2. These upper and lower plate members 13 and 14 are aluminum alloy thin plate materials in which brazing materials are provided in layers on both sides.
[0033]
The upper and lower plate members 13 and 14 are configured such that both end edges in the tube 2 width direction (vehicle body longitudinal direction) are engaged with each other and the engaging portions 15 and 15 are respectively brazed. Thus, the tube 2 in which the flow path through which the refrigerant flows is formed.
[0034]
As shown in FIG. 4, the vehicle body front edge portion of the upper plate member 13 is folded back at a substantially right angle to the lower side, and its tip is folded back approximately 180 ° outward and in the opposite direction. Yes. Accordingly, the folded portion 13a has a thickness in which two upper plate members 13 are overlapped, and the tube 2 is prevented from being damaged due to flying pebbles or the like when the vehicle travels. The folded portion 13a is substantially U-shaped when viewed from the refrigerant flow direction, and its lower end is positioned so that a gap R is formed between the lower plate member 14 and the upper end. The lower plate member 14 is positioned below the outer surface of the upper plate member 13 by a length corresponding to the thickness of the lower plate member 14.
[0035]
The vehicle body front edge portion of the lower plate member 14 is bent at a substantially right angle upward along the folded portion 13a of the upper plate member 13 so as to extend from the outside of the flow path, and the tip thereof is an upper end surface (tip surface) of the folded portion 13a. It is set as the fitting part 14a formed so that it may contact | abut. That is, since the fitting portion 14a is formed so as to contact the tip end surface of the folded portion 13a located below the outer surface of the upper member 13, as described above, the outer surface of the fitting portion 14a is the outer surface of the upper plate member 14. Therefore, there is no step on the outer surface of the engaging portion 15.
[0036]
In addition, as shown in FIG. 1, the both-ends edge part of the vehicle body rear side of the said upper and lower board | plate materials 13 and 14 is comprised similarly to the both-ends edge part of the said vehicle body front side, The folding | returning part 13a and the fitting part 14a Are engaged with each other, and the engaging portion 15 is brazed.
[0037]
In addition, a plurality of first and second projecting portions 13b and 14b are formed on the inner surfaces of the flow paths of the upper and lower plate members 13 and 14 so as to protrude from the facing portions into the flow path. The projecting portions 13b and 14b have the same shape, and their tips are located at substantially the center in the vertical direction of the tube 2 and are joined and brazed together. The protrusions 13b and 14b are formed at equal intervals in both the width direction and the longitudinal direction of the tube 2, and the protrusions 13b and 14b arranged in the width direction of the tube 2 are linearly positioned. 2 The adjacent protrusions 13b, 14b arranged in the longitudinal direction are offset from each other in the tube 2 width direction. Thereby, the flow of the refrigerant is moderately disturbed, and the heat exchange efficiency is improved. Moreover, since each protrusion part 13b, 14b is made into the substantially circular shape seeing from the protrusion direction, the increase in the circulation resistance of the refrigerant | coolant by providing protrusion part 13b, 14b is suppressed.
[0038]
Therefore, according to the heat exchanger tube 2 according to this embodiment, the fitting portion 14a of the lower plate member 14 is fitted to the folded portion 13a of the upper plate member 13, so that the folded portion of which the molding becomes complicated is performed. The both ends of the upper and lower plate members 13 and 14 can be firmly engaged with each other while reducing the manufacturing cost by reducing the number of formation places compared to the conventional tube. Thereby, when brazing the engaging portions 15 and 15 of the upper and lower plate members 13 and 14, both edge portions are not separated from each other due to vibration during loading into the furnace or deformation during heating. In addition to being able to braze reliably, it is possible to prevent the both end edges of the upper and lower plate members 13 and 14 from being separated by the pressure of the refrigerant after brazing, and thus sufficiently obtain the pressure resistance of the tube 2. Can do.
[0039]
Moreover, since the fitting part 14a is formed so that a level | step difference may not arise in the insertion part to the tube holding hole 12 in the engaging part 15 outer surface, the edge part of each tube 2 is made into header tank 5,6. When inserted into the tube holding hole 12, no gap is formed between the outer peripheral surface of the tube 2 and the periphery of the tube holding hole 12, and the tube 2 can be securely brazed to the header tanks 5 and 6.
[0040]
At the time of brazing, the upper and lower plate members 13 and 14 are provided with the brazing material in layers, so that after the two plate members 13 and 14 are formed, the fitting portion 14a is fitted to the folded portion 13a. After that, both the contact surfaces can be brazed at the same time simply by carrying them into the furnace, thereby reducing the number of manufacturing steps.
[0041]
In addition, since both shapes are set such that a gap R is formed between the lower end of the folded portion 13a and the inner surface of the lower plate member 14, the upper and lower sides are caused by manufacturing errors and thermal distortion during brazing. Even if the shapes of the plate members 13 and 14 are slightly different from the intended shape, the folded portion 13a and the lower plate member 14 do not contact each other. As a result, the joint surfaces of the first and second projecting portions 13b and 14b are not separated from each other, and the projecting portions 13b and 14b can be firmly brazed, and the pressure resistance of the tube 2 is sufficiently secured. it can.
[0042]
In addition, in the said embodiment, although the protrusion parts 13b and 14b are made into substantially circular shape seeing from the protrusion direction, it is not restricted to this, For example, like the modification 1 shown in FIG. The second projecting portion 13b may be a substantially oval shape that is long in the direction in which the refrigerant flows. In this case, it is possible to increase the brazing area of the upper and lower plate members 13 and 14 while reducing the degree of reduction in the cross-sectional area of the flow path due to the formation of the protrusions 13c. Can be further improved.
[0043]
As the protrusions 13b and 14b, as in Modification 2 shown in FIG. 6, a plurality of first and second protrusions 13d and 14d that extend straight across both ends in the longitudinal direction of the tube 2 are arranged in the tube 2 width direction. You may make it install. In this case, since the upper and lower plate members 13 and 14 are joined across both ends of the tube 2 in the longitudinal direction, the pressure resistance of the tube 2 can be further improved.
[0044]
Further, without forming the first and second protrusions 13b and 14b, the upper and lower plate members 13 and 14 are formed separately from the upper and lower plate members 13 and 14 in the flow path as in the third modification shown in FIG. A connecting member 20 that connects the inner surfaces of the opposing flow paths may be provided. The connecting member 20 is made of an aluminum alloy plate, and a plurality of protrusions 20a extending in the longitudinal direction of the tube 2 and extending in the tube 2 width direction are formed on the plate. The lower surface of the connecting member 20 is brazed to the inner surface of the flow path of the lower plate member 14, and the upper end portion of the ridge portion 20a is brazed to the inner surface of the flow path of the upper plate member 13. Since the lower plate members 13 and 14 are coupled across the longitudinal ends of the tube 2, the pressure resistance of the tube 2 can be further improved.
[0045]
In this case, since the connecting member 20 is formed separately from the upper and lower plate members 13 and 14, for example, the plate thickness of the connecting member 20 can be made different from both the plate members 13 and 14. The shape of the member 20 can be freely set.
[0046]
Moreover, in the said embodiment, although comprised so that a level | step difference may not arise in the engaging part 15 outer surface across the longitudinal direction both ends of the tube 2, not only this but like the modification 4 shown in FIG. You may comprise in a junction part with the fin 3 so that the outer surface of the fitting part 14a may be located below the outer surface of the upper side board | plate material 13. As shown in FIG. As a result, a gap S is formed between the outer surface of the fitting portion 14a and the lower surface of the fin 3, so that the shape of each of the plate members 13 and 14 becomes an expected shape due to manufacturing errors, thermal distortion during brazing, and the like. Even if slightly different, the outer surface of the fitting portion 14a does not press against the lower surface of the fin 3, thereby preventing the fin 3 from being lifted from the outer surface of the upper plate 13 and thus the fin 3 The entire joint surface of 3 can be brazed firmly.
[0047]
Furthermore, in the said embodiment, although the tube 2 is comprised combining two members, the upper side board | plate material 13 and the lower side board | plate material 14, when the tube 2 shall consist of one board | plate material, The plate material may be bent at the central portion in the width direction so that the both end edges in the width direction of the plate material face each other, and the both end edges may be engaged and brazed in the same manner as in the above embodiment.
[0048]
【The invention's effect】
As described above, according to the heat exchanger tube of the first aspect of the present invention, one end edge portion is folded inward of the flow path, and the tip is folded back outwardly and in the opposite direction. The other end edge portion is a fitting portion formed so as to be in contact with the front end surface of the folded portion, so that the pressure resistance of the tube can be sufficiently obtained without causing an increase in cost. In addition, since the fitting part is formed so that there is no step on the outer surface of the engagement part between the folded part and the fitting part, a gap is formed between the tube outer peripheral surface and the periphery of the tube holding hole of the header tank. This ensures that the tube can be brazed to the header tank.
[0049]
According to the second aspect of the present invention, since the brazing material is provided in a layered manner on at least one of the contact surfaces of the folded portion and the fitting portion, the fitting portion is fitted into the folded portion and then carried into the furnace. As a result, both the abutting surfaces can be brazed at the same time, and therefore the number of manufacturing steps can be reduced.
[0050]
According to the third aspect of the present invention, the fin is brazed to the outer surface on the one end edge side, and a gap is formed between the outer surface of the fitting portion and the fin. Even if the shape of each member is slightly different from the intended shape due to thermal distortion of the fin, the fin can be brazed firmly.
[0051]
According to the fourth aspect of the present invention, since the connecting member for connecting the inner surfaces of the opposed flow paths is provided in the flow path, the pressure resistance of the tube can be further enhanced.
[0052]
According to the fifth aspect of the present invention, since the projecting portion brazed to the other is provided on at least one of the inner surfaces of the opposed flow paths, the pressure resistance of the tube is further increased without increasing the number of parts. be able to.
[0053]
According to the sixth aspect of the present invention, since the gap is formed between the folded portion and the inner surface of the flow path in a state where the protruding portion is joined to the inner surface of the flow path, the shape of each member is changed due to a manufacturing error or the like. Even if slightly different from the initial shape, the entire joint surface of the protrusion can be brazed firmly.
[0054]
According to the seventh aspect of the present invention, the flow of the refrigerant is moderately disturbed by the plurality of protrusions, and the heat exchange efficiency can be improved. At this time, the protrusions are substantially circular or substantially oval. It is possible to prevent the distribution resistance from greatly increasing.
[0055]
According to the eighth aspect of the present invention, since the protruding portion is a protruding portion extending in the refrigerant flow direction, the pressure resistance of the tube can be further improved.
[Brief description of the drawings]
FIG. 1A is a plan view of an end portion of a tube, and FIG. 1B is a view of the tube as viewed from one side in a refrigerant flow direction.
FIG. 2 is a perspective view of the condenser as viewed from the rear side of the vehicle body.
FIG. 3 is an exploded perspective view showing an enlargement of the vicinity of the upper part of the left header tank and the upper part of the core in FIG. 2;
FIG. 4 is an enlarged view of a left end portion of FIG.
FIG. 5 is a diagram corresponding to FIG.
6 is a view corresponding to FIG. 1 according to a second modification.
FIG. 7 is a view corresponding to FIG.
FIG. 8 is a longitudinal sectional view of a central portion in the longitudinal direction of a tube according to Modification 4.
FIG. 9 is a view corresponding to FIG. 1 (b) showing a conventional tube.
[Explanation of symbols]
2 Tube 3 Fins 5 and 6 Header tank 12 Tube holding hole 13a Folding portion 13b Projection portion 13d Projection portion 14a Fitting portion 14b Projection portion 14 Projection portion 15 Engagement portion 20 Connecting member R Gap S Gap

Claims

It consists of a flat plate-like body in which the flow path through which the refrigerant flows is formed by engaging the edge portions at both ends and brazing the engagement portion, and ends at the tube holding hole formed in the header tank. A heat exchanger tube inserted into the periphery of the tube holding hole,
One end edge portion is a folded portion that is bent inwardly of the flow path and has its tip end folded back approximately 180 ° outward and in the opposite direction of the flow path.
The other end edge portion is a fitting portion that is bent so as to be along the folded portion from the outside and the tip end side thereof is in contact with the tip end surface of the folded portion,
The tube for a heat exchanger, wherein the fitting portion is formed so that a step does not occur in a portion inserted into the tube holding hole on the outer surface of the engaging portion.

In claim 1,
A heat exchanger tube, wherein a brazing material is provided in layers on at least one of the contact surfaces of the folded portion and the fitting portion that contact each other.

In claim 1,
A fin for heat dissipation is brazed to the outer surface on one end edge side,
A tube for a heat exchanger, wherein a gap is formed between the outer surface of the fitting portion at the other edge and the fin.

In claim 1,
A tube for a heat exchanger, characterized in that a connection member for connecting the inner surfaces of the opposed flow channels is provided in the flow channel.

In claim 1,
A heat exchanger tube, wherein at least one of the opposed inner surfaces of the flow path is integrally provided with a protruding portion joined and brazed to the other.

In claim 5,
A heat exchange characterized in that a gap is formed between the folded portion and the inner surface of the flow channel facing the folded portion in a state where the protruding portion of the inner surface of one flow channel is joined to the inner surface of the other flow channel. Tube for dexterity.

In claim 5,
A plurality of protrusions are formed with a space between each other, and when viewed from the protrusion direction, the protrusions are formed into a substantially circular shape or a substantially oval shape long in the refrigerant flow direction.

In claim 5,
The protruding portion is a protruding portion extending in the refrigerant flow direction, and the heat exchanger tube.