JP4024095B2

JP4024095B2 - Heat exchanger

Info

Publication number: JP4024095B2
Application number: JP2002200174A
Authority: JP
Inventors: 貴詞山崎
Original assignee: Calsonic Kansei Corp
Current assignee: Marelli Corp
Priority date: 2002-07-09
Filing date: 2002-07-09
Publication date: 2007-12-19
Anticipated expiration: 2022-07-09
Also published as: JP2004044851A

Description

【０００１】
【発明の属する技術分野】
この発明の熱交換器は、例えば、自動車用空気調和装置に組み込んで、車室内を空気調和する為の空気を冷却するエバポレータとして利用する。
【０００２】
【従来の技術】
自動車用空気調和装置には、内部で冷媒を蒸発させ、外部を流通する空気を冷却するエバポレータを組み込んでいる。又、この様な、自動車用空気調和装置に組み込むエバポレータとして従来から、例えば特開昭６２−７９８号公報、実開平７−１２７７８号公報、特開平９−３１８１９５号公報等に記載されている様な、複数枚の金属板を互いに積層して成る、所謂積層型エバポレータが知られている。この積層型エバポレータは、それぞれが２枚の金属板を最中状に組み合わせて成る伝熱管素子を複数個、互いに積層する事により構成している。図８〜９は、この様に従来から知られている積層型エバポレータの１例を示している。
【０００３】
このエバポレータ１は、それぞれの片面に凹部を形成した金属板を２枚１組とし、互いの凹部同士を整合させた状態で最中状に重ね合わせて互いに気密且つ液密に接合する事により、内側に扁平で上端部で１８０度折り返したＵ字形流路２を有する複数の第一伝熱管素子３、３と、内側に扁平で互いに独立した２本の直線状流路４、４を有する複数の第二伝熱管素子５、５とを、それぞれ構成している。そして、上記複数の第一伝熱管素子３、３を、隣り合う第一伝熱管素子３、３同士の間にフィン６、６を設けた状態で重ね合わせて第一部分７を構成すると共に、上記複数の第二伝熱管素子５、５を、隣り合う第二伝熱管素子５、５同士の間にフィン６、６を設けた状態で重ね合わせて第二部分８を構成している。そして、上記第一部分６と第二部分８とを、上記各第一、第二伝熱管素子３、５の重ね合わせ方向に関して互いに重ね合わせる事により、コア部９を構成している。
【０００４】
又、上記各第一、第二伝熱管素子３、５の上下両端部のそれぞれ２個所位置で合計４個所位置に、タンク空間を設けている。これら複数のタンク空間のうち、上記各第一伝熱管素子３、３の下端部に設けた１対のタンク空間は、上記各Ｕ字形流路２、２の両端部に接続している。又、上記各第一伝熱管素子３、３の上端部に設けた１対のタンク空間は、上記各Ｕ字形流路２、２とは独立して設けている。これに対して、上記各第二伝熱管素子５、５の４個所位置に設けた複数のタンク空間は、中間部に存在する上記各直線状流路４、４の上下両端部に接続している。そして、上記各タンク空間のうち、上記各第一、第二伝熱管素子３、５を重ね合わせた状態で、隣り合うタンク空間同士を互いに連通させる事により、入口タンク部１０と中間タンク部１１、１１と出口タンク部１２とを構成している。そして、上記コア部９の上端部に設けた入口タンク部１０の長さ方向一端部（図９の左端部）に冷媒送り込み管１３の下流端部を、同じく出口タンク部１２の長さ方向一端部（図９の左端部）に冷媒取り出し管１４の上流端部を、それぞれ接続している。
【０００５】
エバポレータ１の使用時には、冷媒送り込み管１３に設けた冷媒送り込み口１５を通じてコア部９の内部に液状若しくは気液混合状態の冷媒を送り込む。このコア部９に送り込まれた冷媒は、このコア部９の厚さ方向片側部分（図８、９の右側部分）にそれぞれ存在する、一部の直線状流路４内とＵ字形流路２の上流側半部内とを流れた後、上記コア部９の厚さ方向他側部分（図８、９の左側部分）にそれぞれ存在する、Ｕ字形流路２の下流側半部内と残部の直線状流路４内とを流れる。上記冷媒が上記コア部９内を流れる間に、この冷媒は上記コア部９の外部を、図８、９の矢印α方向に通過する空気調和用の空気との間で熱交換を行なって蒸発する。又、上記コア部９内で蒸発したガス状の冷媒は、出口タンク部１２から冷媒取り出し管１４に設けた冷媒取り出し口１６を通じて外部に取り出され、図示しないコンプレッサに送られる。この結果、上記空気調和用の空気は、上記熱交換により冷却される。
【０００６】
【発明が解決しようとする課題】
上述の様に構成し作用する従来から知られているエバポレータ１に就いて、本発明の発明者が使用時の表面の温度分布を測定したところ、図１０に示す様な測定結果を得た。この図１０は、上述の図８、９を右方から見た状態での、コア部９の表面の温度分布の測定結果を示しており、斜格子部が最も低温である事を、無地部が最も高温である事を、梨地部が中間の温度である事を、それぞれ表している。この図１０で示した結果から明らかな様に、上記コア部９の幅方向片半部（図１０の右半部）である第二部分８では、表面の温度分布がほぼ均一になっている。但し、上記コア部９の幅方向他半部（図１０の左半部）である第一部分７では、幅方向片側部分（図１０の左側部分）で低温になっているのに対し、幅方向他側部分（図１０の右側部分）の一部で高温になっており、温度分布に偏りがある。この様にコア部９の表面の温度分布に偏りがある場合に、空気調和用の空気をこのコア部９の厚さ方向に通過させた場合には、車室内の吹き出し口から吹き出した空気に温度差が生じて、乗員に違和感を生じさせる。又、この様に上記温度分布に偏りがある場合には、エバポレータ１の効率が低下して、性能確保と小型化との両立を図る事が難しくなる。
【０００７】
この様に、上述した従来構造を有するエバポレータ１で、上記第一部分７の表面の温度分布に偏りがある理由に就いて、本発明の発明者は、次の様に考えた。先ず、図１１に示す様に、１対の中間タンク部１１、１１のうちの一方（図１１の表側）の中間タンク部１１から上記第一部分７に、液状若しくは気液混合状態の冷媒が送り込まれる状態を考える。この状態で、上記一方の中間タンク部１１内を流れる冷媒には慣性力が作用する為、この一方の中間タンク部１１の下流端寄り部分（図１１の左端寄り部分）に接続したＵ字形流路２に冷媒が多く送り込まれる傾向となる。逆に、この一方の中間タンク部１１の上流端寄り部分（図１１の右端寄り部分）に接続したＵ字形流路２内には冷媒が送り込まれにくくなる。尚、図１１で示した矢印のうち、実線矢印はＵ字形流路２内を多くの冷媒が流れる事を、破線矢印はＵ字形流路２内を少量の冷媒が流れる事を、それぞれ表している。この様に、上記第一部分７を構成する複数のＵ字形流路２、２内を流れる冷媒量に差が生じた場合には、この第一部分７を構成する各第一伝熱管素子３同士及び各フィン６（図８参照）同士の間で、表面の温度に差が生じる。即ち、この第一部分７のうち、幅方向片側部分（図１１の左側部分）では、Ｕ字形流路２内を流れる液状冷媒が多く蒸発する事で、表面の温度が大きく低下するのに対して、幅方向他側部分（図１１の右側部分）では、Ｕ字形流路２内を流れる液状冷媒の蒸発量が少ない為、表面の温度が低下する程度が小さい。本発明の発明者は、この様な理由により、上記第一部分７の表面の温度分布に偏りが生じると考えた。
本発明の熱交換器は、この様な事情に鑑みて、コア部の内部での冷媒の流れを工夫する事により、このコア部を通過した空気調和用の空気の温度分布をほぼ均一にして、使用者にとって快適な空気調和を実現すると共に、性能確保と小型化との両立を図るべく発明したものである。
【０００８】
【課題を解決するための手段】
本発明の熱交換器は、上述した従来から知られている熱交換器と同様に、内側に冷媒を流す為の複数の扁平な流路と、隣り合う流路同士の間に設けられた複数のフィンとから成るコア部と、このコア部の両端部に中間部に存在する複数の流路と連通する状態で設けられた複数のタンク部と、これら複数のタンク部の一部に冷媒を送り込む為の冷媒送り込み口と、上記複数のタンク部の一部から冷媒を取り出す為の冷媒取り出し口とを備える。そして、上記コア部の厚さ方向に空気調和用の空気を通過させる状態で使用する。
【０００９】
特に、本発明の熱交換器に於いては、上記コア部の少なくとも幅方向一部で、厚さ方向片側部分に設けた、上記複数のタンク部のうちの第一冷媒移送タンク部に送り込まれた冷媒が、この厚さ方向片側部分のうちの幅方向片側部分に設けた第一流路と、この厚さ方向片側部分のうちの幅方向他側部分に設けた第二流路とに分流した後、上記第一流路内を流れた冷媒が、上記第一冷媒移送タンク部と上記コア部を挟んで反対側端部に設けた、上記複数のタンク部のうちの第一中間タンク部及びこの第一中間タンク部と連通する第三中間タンク部を介して、上記コア部の厚さ方向他側部分で、上記空気の通過方向に関して上記第二流路と対向する位置に設けた第三流路内を流れ、上記第一、第三中間タンク部と上記コア部を挟んで反対側端部に設けた、上記複数のタンク部のうちの第二冷媒移送タンク部に達すると共に、上記第二流路内を流れた冷媒が、上記第一冷媒移送タンク部と上記コア部を挟んで反対側端部に設けた、上記複数のタンク部のうちの第二中間タンク部を介して、上記コア部の厚さ方向他側部分で、上記空気の通過方向に関して上記第一流路と対向する位置に設けた第四流路内を流れ、上記第二冷媒移送タンク部に達する。
【００１０】
更に、請求項２に記載した熱交換器の場合には、上記コア部の少なくとも幅方向一部は、互いに内部構造が同じである複数の第一伝熱管素子を、互いの表裏方向を同方向にしつつ、隣り合う第一伝熱管素子同士の間にフィンを設けた状態で重ね合わせて成る第一部分と、これら各第一伝熱管素子と同じ内部構造を有する複数の第二伝熱管素子を、互いの表裏方向を同方向にしつつ、隣り合う第二伝熱管素子同士の間にフィンを設けた状態で重ね合わせて成る第二部分とを、上記各第一伝熱管素子と上記各第二伝熱管素子との表裏方向を互いに異ならせた状態で、幅方向に重ね合わせる事により構成している。
又、上記各第一、第二伝熱管素子は、それぞれの片面の長さ方向一端部に互いに独立した状態で設けられた第一、第二、第三凹部と、同じく長さ方向他端部に互いに独立した状態で設けられた第四、第五凹部と、同じく中間部に設けられてこのうちの第一、第四凹部同士を連通させる第一浅凹部と、同じく中間部に設けられて上記第二、第五凹部同士を連通させる第二浅凹部とを備えた１対の金属板を、それぞれの凹部同士を対向させた状態で最中状に重ね合わせて互いに接合する事により、上記第一凹部同士が突き合わされた部分に第一タンク空間を、上記第二凹部同士が突き合わされた部分に第二タンク空間を、上記第三凹部同士が突き合わされた部分に第三タンク空間を、上記第四凹部同士が突き合わされた部分に第四タンク空間を、上記第五凹部同士が突き合わされた部分に第五タンク空間を、上記第一浅凹部同士が突き合わされた部分に上記第一、第四タンク空間同士を連通させる第一直線状流路を、上記第二浅凹部同士が突き合わされた部分に上記第二、第五タンク空間同士を連通させる第二直線状流路を、それぞれ設けたものである。
そして、上記各第一伝熱管素子により構成する第一部分と、上記各第二伝熱管素子により構成する第二部分とを互いに重ね合わせた状態で、互いに対向する、上記各第一伝熱管素子に設けた第一タンク空間同士を連通して、第一タンク部を構成している。
又、互いに対向する、上記各第一伝熱管素子に設けた第二タンク空間と上記各第二伝熱管素子に設けた第二タンク空間とを互いに連通して、第二タンク部を構成している。
又、互いに対向する、上記各第二伝熱管素子に設けた第一タンク空間同士を連通して、第三タンク部を構成している。
又、互いに対向する、上記各第一伝熱管素子に設けた第四タンク空間と上記各第二伝熱管素子に設けた第五タンク空間とを互いに連通して、第四タンク部を構成している。
又、互いに対向する、上記各第一伝熱管素子に設けた第五タンク空間と上記各第二伝熱管素子に設けた第四タンク空間とを互いに連通して、第五タンク部を構成している。
更に、上記第一タンク部と上記第三タンク部とを、連通路を介して連通させている。
そして、前記第一流路が、上記各第一伝熱管素子に設けた第一直線状流路であり、前記第二流路が、上記各第二伝熱管素子に設けた第二直線状流路であり、前記第三流路が、これら各第二伝熱管素子に設けた第一直線状流路であり、前記第四流路が、上記各第一伝熱管素子に設けた第二直線状流路である。
又、前記第一冷媒移送タンク部の一部が上記第四タンク部であり、前記第一中間タンク部の一部が上記第一タンク部であり、前記第二中間タンク部が上記第二タンク部であり、前記第三中間タンク部の一部が上記第三タンク部であり、前記第二冷媒移送タンク部の一部が上記第五タンク部である。
【００１１】
【作用】
上述の様に構成する本発明の熱交換器によれば、コア部の少なくとも幅方向一部で、比較的温度が高くなる部分同士、又は比較的温度が低くなる部分同士が、空気調和用の空気の通過方向に関して、互いに重畳する事を少なくできる。この為、上記コア部を通過した空気調和用の空気の温度分布をほぼ均一にでき、使用者にとって快適な空気調和を実現できる。又、熱交換器の小型化と性能確保との両立を図り易くなる。
【００１２】
更に、請求項２に記載した熱交換器によれば、コア部を構成する伝熱管素子の種類を少なくできる為、コスト低減を図れる。
【００１３】
【発明の実施の形態】
図１〜７は、本発明の実施の形態の１例を示している。本発明の熱交換器であるエバポレータ１ａは、それぞれが複数ずつの第一伝熱管素子１９と、第二伝熱管素子２０、２０と、第三伝熱管素子２１、２１と、コルゲート型のフィン６、６とを積層して成るコア部９ａを有する。そして、このコア部９ａの幅方向片半部（図１、５、６の右半部）を、上記複数の第一伝熱管素子１９を、隣り合う第一伝熱管素子１９同士の間にフィン６を設けた状態で重ね合わせて成る第一部分２２と、上記複数の第二伝熱管素子２０、２０を、隣り合う第二伝熱管素子２０、２０同士の間にフィン６を設けた状態で重ね合わせて成る第二部分２３とを、１個のフィン６を介して互いに幅方向に重ね合わせる事により構成している。
【００１４】
又、上記コア部９ａの幅方向他半部（図１、５、６の左半部）を、上記複数の第三伝熱管素子２１、２１を、隣り合う第三伝熱管素子２１、２１同士の間にフィン６を設けた状態で重ね合わせて成る、第三部分２８としている。上記各第一〜第三伝熱管素子１９〜２１のうち、各第一伝熱管素子１９と各第二伝熱管素子２０、２０とは、互いの内部構造を同じにしている。これに対して、第三伝熱管素子２１の内部構造は、これら第一、第二各伝熱管素子１９、２０の内部構造と異ならせている。又、上記各第一〜第三伝熱管素子１９〜２１は、それぞれの片面に凹部を形成した第一金属板２９（又は第二金属板４５）をそれぞれ２枚１組とし、互いの凹部同士を対向させた状態で最中状に重ね合わせて互いに気密且つ液密に接合する事により造ったもので、内側に冷媒を流す為の扁平な流路を有する。
【００１５】
上記第一、第二各金属板２９、４５は、芯材（比較的融点が高いアルミニウム合金）の両面にろう材（Siを多く含み、比較的融点が低いアルミニウム合金）を積層した、所謂両面クラッド材としている。上記エバポレータ１ａを造る場合には、上記各第一、第二金属板２９、４５と、各フィン６、６と、冷媒送り込み口１５を有する冷媒送り込み管１３と、冷媒取り出し口１６を有する冷媒取り出し管１４と、内部に連通路２６を設けたサイドタンク２７とを組み合わせ、加熱炉中で加熱して、上記ろう材により上記各部材２９、４５、６、１３、１４、２７を、互いにろう付け接合する。この状態で、上記コア部９ａの幅方向片半部のうち、幅方向片側部分（図１の右側部分）は、複数の第一伝熱管素子１９とフィン６とを重ね合わせた第一部分２２となり、同じく幅方向他側部分は、複数の第二伝熱管素子１８、１８とフィン６とを重ね合わせた第二部分２３となり、上記コア部９ａの幅方向他半部は、複数の第三伝熱管素子２１、２１とフィン６とを重ね合わせた第三部分２８となる
【００１６】
上記コア部９ａの第一部分２２を構成する各第一伝熱管素子１９と、同じく第二部分２３を構成する各第二伝熱管素子２０、２０とは、それぞれ図３（Ａ）（Ｂ）に詳示する様な第一金属板２９を２枚、互いの凹部を対向させた状態で最中状に重ね合わせ、一体にろう付けして成る。アルミニウム合金製の両面クラッド材である素板にプレス加工を施して成る、上記第一金属板２９は、それぞれの片面の上端部に、互いに独立した第一〜第三凹部３０〜３２を設けている。又、それぞれの片面の下端部に、互いに独立した第四、第五凹部３３、３４を設けている。更に、中間部には、上記第一、第四凹部３０、３３同士を連通させる、上記各第一〜第五凹部３０〜３４よりも浅い第一浅凹部３５と、この第一浅凹部３５と独立した状態で設けて、上記第二、第五凹部３１、３４同士を連通させる、やはり上記各第一〜第五凹部３０〜３４よりも浅い第二浅凹部３６とを設けている。
【００１７】
上記各第一、第二伝熱管素子１９、２０はそれぞれ、上述の様な第一金属板２９を１対ずつ、それぞれの凹部同士を対向させた状態、即ち、第一凹部３０同士、第二凹部３１同士、第三凹部３２同士、第四凹部３３同士、第五凹部３４同士、第一浅凹部３５同士、第二浅凹部３６同士を互いに対向させた状態で最中状に重ね合わせている。そして、上記第一凹部３０同士が突き合わされた部分に第一タンク空間３７を、上記第二凹部３１同士が突き合わされた部分に第二タンク空間３８を、上記第三凹部３２同士が突き合わされた部分に第三タンク空間３９を、上記第四凹部３３同士が突き合わされた部分に第四タンク空間４０を、上記第五凹部３４同士が突き合わされた部分に第五タンク空間４１を、それぞれ設けている。
【００１８】
又、上記第一浅凹部３５同士が突き合わされた部分を第一直線状流路４２として、上記第一、第四タンク空間３７、４０同士を連通させている。更に、上記第二浅凹部３６同士が突き合わされた部分を第二直線状流路４３として、上記第二、第五タンク空間３８、４１同士を連通させている。尚、上記第一、第二浅凹部３５、３６内には多数の突起４４、４４を形成している。これら各突起４４、４４の先端面は、１対の上記第一金属板２９同士を最中状に組み合わせる際に、これら第一金属板２９の周縁部及び上記第一、第二浅凹部３５、３６同士の間部分等と共に、互いに突き合わされてろう付けされる。そして、上記各第一伝熱管素子１９の耐圧強度を確保すると共に、上記第一、第二直線状流路４２、４３内を流れる冷媒の流れを攪乱する役目を果たす。
【００１９】
一方、上記コア部９ａの第三部分２８を構成する、前記各第三伝熱管素子２１、２１は、図４（Ａ）（Ｂ）に詳示する様な第二金属板４５を２枚、最中状に重ね合わせ、互いにろう付けして成る。やはりアルミニウム合金製の両面クラッド材である素板にプレス加工を施して成る、上記第二金属板４５は、それぞれの片面の上端部に、互いに独立した第六、第七、第八凹部４６、４７、４８を設けている。又、それぞれの片面の下端部に、互いに独立した第九、第十凹部４９、５０を設けている。更に、中間部には、上記第六、第九凹部４６、４９同士を連通させる第三浅凹部５１と、上記第八、第十凹部４８、５０同士を連通させる第四浅凹部５２とを、それぞれ設けている。これら各第三、第四浅凹部５１、５２は、上記各第六〜第十凹部４６〜５０よりも浅い。
【００２０】
上記各第三伝熱管素子２１、２１はそれぞれ、上述の様な第二金属板４５を１対ずつ、それぞれの凹部同士を対向させた状態、即ち、第六凹部４６同士、第七凹部４７同士、第八凹部４８同士、第九凹部４９同士、第十凹部５０同士、第三浅凹部５１同士、第四浅凹部５２同士を互いに対向させた状態で最中状に重ね合わせている。そして、上記第六凹部４６同士が突き合わされた部分に第六タンク空間５３を、上記第七凹部４７同士が突き合わされた部分に第七タンク空間５４を、上記第八凹部４８同士が突き合わされた部分に第八タンク空間５５を、上記第九凹部４９同士が突き合わされた部分に第九タンク空間５６を、上記第十凹部５０同士が突き合わされた部分に第十タンク空間５７を、それぞれ形成している。
【００２１】
又、上記第三浅凹部５１同士が突き合わされた部分を第三直線状流路５８として、上記第六、第九タンク空間５３、５６同士を連通させている。更に、上記第四浅凹部５２同士が突き合わされた部分を第四直線状流路５９として、上記第八、第十タンク空間５５、５７同士を連通させている。尚、上記第三、第四浅凹部５１、５２内にも、前述した第一金属板２９に設けた第一、第二浅凹部３５、３６の場合と同様に、多数の突起４４、４４を形成している。
【００２２】
前記コア部９ａは、それぞれが前述した様に構成する複数の第一伝熱管素子１９及びフィン６から成る第一部分２２と、同じく複数の第二伝熱管素子２０、２０及びフィン６から成る第二部分２３と、それぞれが上述した様に構成する複数の第三伝熱管素子２１、２１及びフィン６から成る第三部分２８とを、間部分にフィン６を設けた状態で互いに重ね合わせる事により構成している。このうちの第一部分２２は、それぞれ上記複数の第一伝熱管素子１９を、互いの表裏方向を同方向にしつつ、隣り合う第一伝熱管素子１９同士の間にフィン６を設けた状態で重ね合わせる事により構成している。又、上記第二部分２３は、それぞれ上記複数の第二伝熱管素子２０、２０を、互いの表裏方向を同方向にしつつ、隣り合う第二伝熱管素子２０、２０同士の間にフィン６を設けた状態で重ね合わせる事により構成している。そして、上記第一、第二部分２２、２３同士を、これら各部分２２、２３を構成する第一、第二伝熱管素子１９、２０の表裏方向を互いに異ならせた状態で、フィン６を介して幅方向（各伝熱管素子１９、２０の積層方向）に重ね合わせている。又、上記第三部分２８は、複数の第三伝熱管素子２１、２１を、隣り合う第三伝熱管素子２１、２１同士の間にフィン６を設けた状態で重ね合わせる事により構成している。
【００２３】
そして、エバポレータ１ａを自動車用空気調和装置の一部に組み付けた状態で、上記各第一伝熱管素子１９内の第二直線状流路４３と、上記各第二伝熱管素子２０、２０内の第一直線状流路４２、４２と、上記各第三伝熱管素子２１、２１内の第四直線状流路５９、５９とを、空気調和用の空気の通過方向αに関して風上側（図１、５、６の裏側）に位置させている。
【００２４】
そして、この様に上記各第一〜第三伝熱管素子１９〜２１を重ね合わせた状態で、互いに対向する、上記各第三伝熱管素子２１、２１の第六タンク空間５３、５３同士を互いに連通して、入口タンク部６０を構成している。この為、上記各第三伝熱管素子２１、２１を構成する第二金属板４５に形成した第六凹部４６の底部には、上記第三部分２８の幅方向一端（図１、５、６の左端）に位置する１枚の第二金属板４５を除き、冷媒を通過させる為の通孔６１を形成している。この様にして構成した、上記入口タンク部６０の長さ方向一端部（図１、５、６の左端部）には、前記冷媒送り込み管１３の下流端を接続している。
【００２５】
又、互いに対向する、上記各第三伝熱管素子２１、２１の第九タンク空間５６、５６と、上記各第二伝熱管素子１８、１８の第五タンク空間４１、４１と、上記各第一伝熱管素子１９の第四タンク空間４０とを互いに連通して、第一冷媒移送タンク部６２を構成している。この為、上記各第三伝熱管素子２１、２１を構成する第二金属板４５に形成した第九凹部４９の底部と、上記各第二伝熱管素子２０、２０を構成する第一金属板２９に形成した第五凹部３４の底部と、上記各第一伝熱管素子１９を構成する第四凹部３３の底部とには、上記コア部９ａの幅方向両端に位置する２枚の第一、第二金属板２９、４５を除き、冷媒を通過させる為の通孔６１を形成している。尚、上記第一冷媒移送タンク部６２の一端側半部（図１、５、６の右半部）が、請求項２に記載した第四タンク部に相当する。
【００２６】
又、互いに対向する、上記各第二伝熱管素子２０、２０の第三タンク空間３９、３９と、上記各第一伝熱管素子１９の第一タンク空間３７とを互いに連通して、第一中間タンク部６３を構成している。この為、上記各第二伝熱管素子２０、２０を構成する第一金属板２９に形成した第三凹部３２の底部と、上記各第一伝熱管素子１９を構成する第一金属板２９に形成した第一凹部３０の底部とには、前記第二部分２３の幅方向一端（図１、５、６の左端）に位置する１枚の第一金属板２９を除き、冷媒を通過させる為の通孔６１を形成している。尚、本例の場合、上記第一中間タンク部６３の一端側半部（図１、５、６の右半部）が、請求項２に記載した第一タンク部に相当する。
【００２７】
又、互いに対向する、上記各第二伝熱管素子２０、２０の第二タンク空間３８、３８と、上記各第一伝熱管素子１９の第二タンク空間３８とを互いに連通して、請求項２に記載した第二タンク部に相当する、第二中間タンク部６４を構成している。この為、上記各第一、第二伝熱管素子１９、２０を構成する各第一金属板２９に形成した第二凹部３１の底部には、上記第二部分２３の幅方向一端（図１、５、６の左端）と、上記第一部分２２の幅方向他端（図１、５、６の右端）とに位置する２枚の第一金属板２９、２９を除き、冷媒を通過させる為の通孔６１を形成している。
【００２８】
更に、互いに対向する、上記各第二伝熱管素子２０、２０の第一タンク空間３７、３７と、上記各第一伝熱管素子１９の第三タンク空間３９とを互いに連通して、第三中間タンク部６５を構成している。この為、上記各第二伝熱管素子２０、２０を構成する各第一金属板２９に形成した第一凹部３０の底部と、上記各第一伝熱管素子１９を構成する各第一金属板２９に形成した第三凹部３２の底部とには、上記第二部分２３の幅方向一端（図１、５、６の左端）に位置する１枚の第一金属板２９を除き、冷媒を通過させる為の通孔６１を形成している。尚、本例の場合には、上記第三中間タンク部６５の一端側半部（図１、５、６の左半部）が、請求項２に記載した第三タンク部に相当する。
【００２９】
又、互いに対向する、前記各第三伝熱管素子２１、２１の第十タンク空間５７、５７と、上記各第二伝熱管素子２０、２０の第四タンク空間４０、４０と、上記各第一伝熱管素子１９の第五タンク空間４１とを互いに連通して、第二冷媒移送タンク部６６を構成している。この為、上記各第三伝熱管素子２１、２１を構成する第二金属板４５の第十凹部５０の底部と、上記各第二伝熱管素子２０、２０を構成する第一金属板２９の第四凹部３３の底部と、上記各第一伝熱管素子１９を構成する第一金属板２９の第五凹部３４の底部とには、上記コア部９ａの幅方向両端に位置する２枚の第一、第二金属板２９、４５を除き、冷媒を通過させる為の通孔６１を形成している。尚、上記第二冷媒移送タンク部６６の一端側半部（図１の右半部）が、請求項２に記載した第五タンク部に相当する。
【００３０】
更に、上記各第三伝熱管素子２１、２１の第八タンク空間５５、５５同士を互いに連通して、出口タンク部６７を構成している。この為、上記各第三伝熱管素子２１、２１を構成する第二金属板４５の第八凹部４８の底部には、上記第三部分２８の幅方向一端（図１、５、６の右端）に位置する１枚の第二金属板４５を除き、冷媒を通過させる為の通孔６１を形成している。この様にして構成した、上記出口タンク部６７の長さ方向一端部（図１、５、６の左端部）には、前記冷媒取り出し管１４の上流端を接続している。上述した様に、上記各第三伝熱管素子２１、２１を構成する第二金属板４５に設けた、第六、第八〜第十凹部４６、４８〜５０の底部には、一部を除いて、通孔６１、６１を形成している。但し、上記第二金属板４５の上端部中央に設けた第七凹部４７の底部には通孔を形成せず、この第七凹部４７により形成する第七タンク空間５４を、隣り合う第三伝熱管素子２１、２１同士で連通させていない。この様な第七凹部４７は、隣り合う第三伝熱管素子２１、２１同士の結合強度を高める為に設けている。この為、この結合強度を十分に確保できるのであれば、上記第七凹部４７を省略する事もできる。
【００３１】
又、前記コア部９ａの幅方向一端（図１、５、６の右端）に位置する１枚の第一金属板２９の片面（図５の右側面）の上端部の幅方向両端部に、サイドタンク２７の両端部を接続している。そして、このサイドタンク２７の内部に設けた連通路２６を介して、前記第一中間タンク部６３の長さ方向一端部（図１、５、６の右端部）と、前記第三中間タンク部６５の長さ方向一端部（図１、５、６の右端部）とを連通させている。
【００３２】
上述の様に構成する本発明の熱交換器である、エバポレータ１ａの使用時には、コンデンサから吐出され、膨張弁を通過した液状若しくは気液混合状態の冷媒を、前記冷媒送り込み管１３から前記入口タンク部６０内に送り込む。この入口タンク部６０に送り込まれた冷媒は、図１、５、６に実線矢印イで示す様に、この入口タンク部６０の全体に広がる。この入口タンク部６０内に広がった冷媒は、続いて、図１、５、６に実線矢印ロ、ロで示す様に、前記第三部分２８の風下側部分を構成する、各第三伝熱管素子２１、２１内の第三直線状流路５８、５８内を、前記第一冷媒移送タンク部６２に向けて、図１、５、６の矢印α方向に流れる空気との間で熱交換を行ないつつ流れる。
【００３３】
この様にして第一冷媒移送タンク部６２内に流れ込んだ冷媒は、この第一冷媒移送タンク部６２内を図１、５、６に実線矢印ハで示す様に、前記コア部９ａの風下側部分の下端部を、水平方向に流れた後、上記第一冷媒移送タンク部６２の下流側半部で、前記第二部分２３を構成する各第二伝熱管素子２０、２０の第二直線状流路４３、４３（第二流路）内と、前記第一部分２２を構成する各第一伝熱管素子１９の第一直線状流路４２（第一流路）内とに、それぞれ送られる。続いて、上記各第二伝熱管素子２０、２０の第二直線状流路４３、４３内に送られた冷媒は、これら各第二直線状流路４３、４３内を、図１、５、６に実線矢印ニ、ニで示す様に、上記熱交換をしつつ流れた後、上記第一冷媒移送タンク部６２と上記コア部９ａを挟んで反対側端部に設けた、前記第二中間タンク部６４に達する。又、上記各第一伝熱管素子１９内の第一直線状流路４２内に送られた冷媒は、これら各第一直線状流路４２を、図１、５、６に実線矢印ニで示す様に、上記熱交換をしつつ流れた後、やはり、上記第一冷媒移送タンク部６２と上記コア部９ａを挟んで反対側端部に設けた、前記第一中間タンク部６３に達する。
【００３４】
この様にして、この第一中間タンク部６３と上記第二中間タンク部６４とに達した冷媒は、これら各第一、第二中間タンク部６３、６４内を図１、５、６に破線矢印ホ、ホで示す様に流れる。この様にして流れた冷媒のうち、第二中間タンク部６４内を流れた冷媒は、上記第一部分２２を構成する各第一伝熱管素子１９の第二直線状流路４３（第四流路）内に送られ、これら各第二直線状流路４３内を、同図に破線矢印チで示す様に、上から下に上記熱交換をしつつ流れて、上記第一、第二中間タンク部６３、６４と上記コア部９ａを挟んで反対側端部に設けた、第二冷媒移送タンク部６６に達する。
【００３５】
これに対して、上記第一中間タンク部６３内を流れた冷媒は、前記サイドタンク２７に設けた連通路２６を、図１、５、６に実線矢印ヘで示す様に流れた後、前記第一冷媒移送タンク部６２と上記コア部９ａを挟んで反対側端部に設けた、前記第三中間タンク部６５内に送られる。続いて、この第三中間タンク部６５内を、図１、５、６に破線矢印トで示す様に流れた冷媒は、上記第二部分２３を構成する各第二伝熱管素子２０、２０の第一直線状流路４２、４２（第三流路）内を、同図に破線矢印チ、チで示す様に、上から下に上記熱交換をしつつ流れて、上記第二冷媒移送タンク部６６に達する。何れにしてもこの第二冷媒移送タンク部６６に達した冷媒は、この第二冷媒移送タンク部６６内を、同図に鎖線矢印リで示す様に、前記コア部９ａの風上側部分の下端部を、水平方向に流れた後、前記第三部分２８を構成する各第三伝熱管素子２１、２１の第四直線状流路５９、５９に達する。そして、これら各第四直線状流路５９、５９内に達した冷媒は、同図に鎖線矢印ヌ、ヌで示す様に、下から上に上記熱交換をしつつ流れて、前記出口タンク部６７に達する。
【００３６】
この様にして出口タンク部６７に達した、過熱状態のガス状冷媒は、同図に破線矢印ルで示す様に、この出口タンク部６７内を流れた後、前記冷媒取り出し管１４に流出し、この冷媒取り出し管１４の下流端に接続した配管を通じて、コンプレッサの吸入口に送られる。
【００３７】
前述の様に構成し、上述の様にコア部９ａの内部を流れる冷媒とこのコア部９ａの外部を通過する空気との間で熱交換を行ない、この空気を冷却する、エバポレータ１ａの場合、上記コア部９ａを通過後の空気の温度分布をほぼ均一にできる。即ち、本発明の場合には、このコア部９ａの幅方向片半部を構成する第一部分２２と第二部分２３とで、比較的温度が高くなる部分同士、及び比較的温度が低くなる部分同士が、空気調和用の空気の通過方向αに関して、それぞれ互いに重畳する事を少なくできる。即ち、上記コア部９ａの風下側部分の下端部に設けた第一冷媒移送タンク部６２を流れる液状若しくは気液混合状態の冷媒には慣性力が作用する。この為、この第一冷媒移送タンク部６２から、中間部に設けた複数の第二伝熱管素子２０、２０の第二直線状流路４３、４３と、同じく複数の第一伝熱管素子１９の第一直線状流路４２とに冷媒が分配される際に、上記第一冷媒移送タンク部６２の下流端近くに設けた、第一伝熱管素子１９の第一直線状流路４２内に、冷媒が多く送り込まれ易くなる。又、逆に、上記第一冷媒移送タンク部６２の上流端近くに設けた、第二伝熱管素子２０、２０の第二直線状流路４３、４３内には冷媒が送り込まれにくくなる。従って、上記各第一伝熱管素子１９の第一直線状流路４２内を流れる冷媒が、上記各第二伝熱管素子２０、２０の第二直線状流路４３、４３内を流れる冷媒よりも多くなる、偏流が生じ易い。
【００３８】
これに対して、本例の場合には、上記第一、第二部分２２、２３の風下側部分で上記各第一伝熱管素子１９の第一直線状流路４２内を流れた冷媒が、同じく風上側部分で、上記空気の通過方向αに関して上記各第二伝熱管素子２０、２０の第二直線状流路４３、４３と対向する位置に設けた、これら各第二伝熱管素子２０、２０の第一直線状流路４２、４２に送られる。又、上記第一、第二部分２２、２３の風下側部分で上記各第二伝熱管素子２０、２０の第二直線状流路４３、４３内を流れた冷媒が、同じく風上側部分で、上記空気の通過方向αに関して上記各第一伝熱管素子１９の第一直線状流路４２と対向する位置に設けた、これら各第一伝熱管素子１９の第二直線状流路４３内に送られる。この為、上記第一、第二部分２２、２３の厚さ方向半部同士で、内部を冷媒が多く流れる流路同士と、内部を少量の冷媒が流れる流路同士とが、それぞれ空気調和用の空気の通過方向αに関して互いに重畳する事を少なくできる。従って、上記第一、第二部分２２、２３で、内部を流れる冷媒の流量が少なくなる事で比較的温度が高くなる、図７に無地で示す、コア部９ａの一部同士が、上記空気の通過方向αに関して互いに重畳する事を少なくできる。又、上記第一、第二部分２２、２３で、内部を流れる冷媒の流路が多くなる事で比較的温度が低くなる、図７に斜格子で示す、コア部９ａの一部同士が、上記空気の通過方向αに関して互いに重畳する事を少なくできる。従って、上記第一、第二部分２２、２３を通過後の空気の温度分布を、ほぼ均一にできる。
【００３９】
しかも、本例の場合には、上記コア部９ａの幅方向他半部である、前記第三部分２８の表面の温度分布に偏りが生じにくい。即ち、この第三部分２８の風下側部分では、上端部に位置する入口タンク部６０内を流れた冷媒が、中間部に設けた複数の第三直線状流路５８、５８に分流する。この際、この入口タンク部６０内を流れる冷媒に重力が作用する事に基づいて、この入口タンク部６０の上流端近くに接続した第三直線状流路５８内に冷媒が多く送り込まれる傾向となる。一方、この入口タンク部６０を流れる冷媒に慣性力が作用する事に基づいて、この入口タンク部６０の下流端近くに接続した第三直線状流路５８内に冷媒が多く送り込まれる傾向となる。この結果、上記入口タンク部６０に連通する複数の第三直線状流路５８、５８同士で、冷媒が、ほぼ均一に流れる事となる。一方、上記第三部分２８の風上側部分では、下端部に位置する第二冷媒移送タンク部６６内を流れる冷媒の多くがガス状になっている。この為、この冷媒に作用する慣性力は小さくなる。この為、この冷媒が、この第二冷媒移送タンク部６６の下流端近くに接続した第四直線状流路５９内に偏って流れる事は少ない。この結果、上記第三部分２８の表面の温度分布をほぼ均一にできる。この為、上記第一、第二部分２２、２３を通過した空気の温度分布をほぼ均一にできる事と相俟って、上記コア部９ａを通過後の空気の温度分布をほぼ均一にでき、乗員にとって快適な冷房状態を実現できる。又、エバポレータ１ａを大型化する事なく、性能の向上を図れる為、性能確保と小型化との両立を図り易くなる。
【００４０】
更に、本例の構造によれば、上記コア部９ａを構成する、内部構造が異なる伝熱管素子の種類が、２種類で済む。この為、部品製作、部品管理、組立作業が何れも容易になって、エバポレータ１ａのコスト低減を図れる。又、本例の場合には、比較的高温側のコア部９ａの厚さ方向他側部分を風上側に、比較的低温側のコア部９ａの厚さ方向片側部分を風下側に、それぞれ位置させている。従って、このコア部９ａと、このコア部９ａを通過する空気との間の温度差を、風上側から風下側迄十分に確保して、上記コア部９ａと空気との熱交換を効率良く行なわせる事ができる。
【００４１】
尚、本発明の熱交換器は、上述した様な、複数のタンク部６０、６２〜６７を、複数の第一〜第三伝熱管素子１９〜２１の一部により構成した構造に限定するものではない。本発明の熱交換器は、内側に冷媒を流す為の扁平な流路を有する複数の伝熱管素子の両端に、これら各伝熱管素子と別体のタンク部材を設けて、これら各タンク部材の内側にタンク部を設けた場合でも実施できる。
【００４２】
又、上述した説明は、コア部９ａを第一〜第三部分２２、２３、２８により構成した場合に就いて説明したが、コア部を、このうちの第一部分２２及び第二部分２３のみから構成する事もできる。この場合には、このコア部を構成する、内部構造が異なる伝熱管素子の種類が１種類で済む為、エバポレータのコストをより低減し易くなる。又、上述した説明は、本発明の熱交換器を、エバポレータとして使用する場合に就いて説明したが、本発明の熱交換器は、エバポレータに限定するものではない。例えば、本発明の熱交換器は、ヒータコアとして使用する場合にも実施できる。この様に本発明の熱交換器をヒータコアとして使用する場合でも、上述の様にエバポレータとして使用する場合と同様に、コア部を通過した空気の温度分布を、ほぼ均一にできる。
【００４３】
【発明の効果】
本発明の熱交換器は、以上に述べた通り構成され作用するので、快適な空気調和を実現できると共に、小型化及び性能確保の両立を図り易くなる。
【図面の簡単な説明】
【図１】本発明の実施の形態の１例の熱交換器に於ける冷媒の流れ状態を説明する為の、略透視斜視図。
【図２】本発明の熱交換器を構成する３種類の素子を、それぞれ図１の右方から見た状態で示す略透視図。
【図３】図２（Ａ）に示した第一伝熱管素子と、図２（Ｂ）に示した第二伝熱管素子とを構成する第一金属板を示しており、（Ａ）は図１の裏表方向から、（Ｂ）は図１の側方から、それぞれ見た図。
【図４】図２（Ｃ）に示した第三伝熱管素子を構成する第二金属板を示しており、（Ａ）は図１の裏表方向から、（Ｂ）は図１の側方から、それぞれ見た図。
【図５】本発明の熱交換器の略分解斜視図。
【図６】コア部の各部での冷媒の流れ状態を量的に説明する為の、略透視斜視図。
【図７】コア部の幅方向片半部のみを取り出して、表面の温度分布状態を説明する為の、略透視斜視図。
【図８】従来構造の１例を示す略斜視図。
【図９】従来構造の１例に於ける冷媒の流れ状態を説明する為の、略斜視図。
【図１０】同じくコア部の表面温度を測定した結果を示す図。
【図１１】同じくコア部の幅方向一部のみを取り出して、冷媒の流れ状態を量的に説明する為の、略透視斜視図。
【符号の説明】
１、１ａエバポレータ
２Ｕ字形流路
３第一伝熱管素子
４直線状流路
５第二伝熱管素子
６フィン
７第一部分
８第二部分
９、９ａコア部
１０入口タンク部
１１中間タンク部
１２出口タンク部
１３冷媒送り込み管
１４冷媒取り出し管
１５冷媒送り込み口
１６冷媒取り出し口
１９第一伝熱管素子
２０第二伝熱管素子
２１第三伝熱管素子
２２第一部分
２３第二部分
２６連通路
２７サイドタンク
２８第三部分
２９第一金属板
３０第一凹部
３１第二凹部
３２第三凹部
３３第四凹部
３４第五凹部
３５第一浅凹部
３６第二浅凹部
３７第一タンク空間
３８第二タンク空間
３９第三タンク空間
４０第四タンク空間
４１第五タンク空間
４２第一直線状流路
４３第二直線状流路
４４突起
４５第二金属板
４６第六凹部
４７第七凹部
４８第八凹部
４９第九凹部
５０第十凹部
５１第三浅凹部
５２第四浅凹部
５３第六タンク空間
５４第七タンク空間
５５第八タンク空間
５６第九タンク空間
５７第十タンク空間
５８第三直線状流路
５９第四直線状流路
６０入口タンク部
６１通孔
６２第一冷媒移送タンク部
６３第一中間タンク部
６４第二中間タンク部
６５第三中間タンク部
６６第二冷媒移送タンク部
６７出口タンク部[0001]
BACKGROUND OF THE INVENTION
The heat exchanger of the present invention is incorporated in, for example, an automobile air conditioner and used as an evaporator for cooling air for air conditioning in a vehicle interior.
[0002]
[Prior art]
An automotive air conditioner incorporates an evaporator that evaporates the refrigerant inside and cools the air circulating outside. Further, as an evaporator incorporated in such an air conditioner for automobiles, it has been conventionally described in, for example, JP-A-62-798, JP-A-7-12778, JP-A-9-318195, etc. In addition, a so-called laminated evaporator is known in which a plurality of metal plates are laminated together. This laminated evaporator is constructed by laminating a plurality of heat transfer tube elements each formed by combining two metal plates in the middle. FIGS. 8 to 9 show an example of a conventional laminated evaporator as described above.
[0003]
This evaporator 1 is a set of two metal plates each having a concave portion formed on one side, and in a state where the concave portions are aligned with each other, they are overlapped in the middle and joined together in an air-tight and liquid-tight manner, A plurality of first heat transfer tube elements 3 and 3 having U-shaped flow passages 2 which are flat on the inside and folded back 180 degrees at the upper end, and a plurality of linear flow passages 4 and 4 which are flat on the inside and independent of each other. The second heat transfer tube elements 5 and 5 are respectively configured. Then, the plurality of first heat transfer tube elements 3, 3 are overlapped in a state where the fins 6, 6 are provided between the adjacent first heat transfer tube elements 3, 3 to constitute the first portion 7, and A plurality of second heat transfer tube elements 5, 5 are overlapped in a state where fins 6, 6 are provided between adjacent second heat transfer tube elements 5, 5 to constitute a second portion 8. The first portion 6 and the second portion 8 are overlapped with each other with respect to the overlapping direction of the first and second heat transfer tube elements 3 and 5 to form the core portion 9.
[0004]
In addition, tank spaces are provided at a total of four positions at two positions on the upper and lower ends of each of the first and second heat transfer tube elements 3 and 5. Among these tank spaces, a pair of tank spaces provided at the lower ends of the first heat transfer tube elements 3 and 3 are connected to both ends of the U-shaped channels 2 and 2. A pair of tank spaces provided at the upper ends of the first heat transfer tube elements 3 and 3 are provided independently of the U-shaped channels 2 and 2. On the other hand, the plurality of tank spaces provided at the four positions of the second heat transfer tube elements 5 and 5 are connected to the upper and lower ends of the linear flow paths 4 and 4 existing in the middle part. Yes. And in the state which each said 1st, 2nd heat exchanger tube elements 3 and 5 piled up among the said each tank space, the inlet tank part 10 and the intermediate tank part 11 are made to mutually communicate. , 11 and the outlet tank section 12. Then, the downstream end of the refrigerant feed pipe 13 is connected to one end in the length direction (left end in FIG. 9) of the inlet tank 10 provided at the upper end of the core 9, and one end in the length direction of the outlet tank 12 is also used. The upstream end portion of the refrigerant take-out pipe 14 is connected to the portion (left end portion in FIG. 9).
[0005]
When the evaporator 1 is used, liquid or gas-liquid mixed refrigerant is sent into the core portion 9 through the refrigerant inlet 15 provided in the refrigerant inlet pipe 13. The refrigerant sent into the core part 9 exists in a part of the linear flow path 4 and the U-shaped flow path 2 respectively present on one side in the thickness direction of the core part 9 (the right side part in FIGS. 8 and 9). Of the U-shaped flow path 2 and the remaining straight line respectively present in the other side portion in the thickness direction of the core portion 9 (the left side portion in FIGS. 8 and 9). Flow in the channel 4. While the refrigerant flows in the core part 9, the refrigerant evaporates by exchanging heat between the outside of the core part 9 and air for air conditioning passing in the direction of the arrow α in FIGS. To do. The gaseous refrigerant evaporated in the core portion 9 is taken out from the outlet tank portion 12 through the refrigerant take-out port 16 provided in the refrigerant take-out pipe 14 and sent to a compressor (not shown). As a result, the air for air conditioning is cooled by the heat exchange.
[0006]
[Problems to be solved by the invention]
When the inventor of the present invention measured the temperature distribution of the surface during use of the conventionally known evaporator 1 configured and operated as described above, a measurement result as shown in FIG. 10 was obtained. FIG. 10 shows the measurement result of the temperature distribution on the surface of the core portion 9 in the state in which the above-described FIGS. 8 and 9 are viewed from the right side. Indicates that the temperature is the highest, and that the satin portion is an intermediate temperature. As is apparent from the results shown in FIG. 10, the temperature distribution of the surface is substantially uniform in the second portion 8 which is one half of the core portion 9 in the width direction (the right half in FIG. 10). . However, in the first part 7 which is the other half part in the width direction of the core part 9 (the left half part in FIG. 10), the temperature is low in the one side part in the width direction (the left part in FIG. 10). A part of the other side part (the right side part in FIG. 10) is hot, and the temperature distribution is uneven. In this way, when the temperature distribution on the surface of the core portion 9 is biased, if air for air conditioning is passed in the thickness direction of the core portion 9, the air blown out from the outlet in the vehicle compartment A temperature difference occurs, causing the passenger to feel uncomfortable. Further, when the temperature distribution is uneven as described above, the efficiency of the evaporator 1 is lowered, and it is difficult to achieve both performance securing and downsizing.
[0007]
As described above, the inventors of the present invention have considered the following reason why the temperature distribution on the surface of the first portion 7 is biased in the evaporator 1 having the above-described conventional structure. First, as shown in FIG. 11, a liquid or gas-liquid mixed refrigerant is fed into the first portion 7 from one of the pair of intermediate tanks 11, 11 (the front side in FIG. 11). Think about the situation. In this state, since an inertial force acts on the refrigerant flowing in the one intermediate tank portion 11, a U-shaped flow connected to the downstream end portion (the left end portion in FIG. 11) of the one intermediate tank portion 11 is applied. A lot of refrigerant tends to be sent to the path 2. Conversely, the refrigerant is less likely to be fed into the U-shaped flow path 2 connected to the upstream end portion (the right end portion in FIG. 11) of the one intermediate tank portion 11. Of the arrows shown in FIG. 11, the solid line arrows indicate that a large amount of refrigerant flows in the U-shaped flow path 2, and the broken line arrows indicate that a small amount of refrigerant flows in the U-shaped flow path 2. Yes. As described above, when a difference occurs in the amount of refrigerant flowing in the plurality of U-shaped flow paths 2 and 2 constituting the first portion 7, the first heat transfer tube elements 3 constituting the first portion 7 and There is a difference in surface temperature between the fins 6 (see FIG. 8). That is, in the first portion 7, in the width direction one side portion (the left side portion in FIG. 11), the liquid temperature flowing in the U-shaped flow path 2 is largely evaporated, and the surface temperature is greatly reduced. In the other side portion in the width direction (the right side portion in FIG. 11), the amount of evaporation of the liquid refrigerant flowing in the U-shaped flow path 2 is small, and therefore the degree to which the surface temperature decreases is small. The inventor of the present invention considered that the temperature distribution on the surface of the first portion 7 is biased for such reasons.
In view of such circumstances, the heat exchanger of the present invention makes the temperature distribution of the air-conditioning air that has passed through the core portion substantially uniform by devising the flow of the refrigerant inside the core portion. The invention was invented to realize air conditioning that is comfortable for the user and to achieve both performance and size reduction.
[0008]
[Means for Solving the Problems]
The heat exchanger according to the present invention includes a plurality of flat flow paths for allowing the refrigerant to flow inside and a plurality of adjacent flow paths provided in the same manner as the above-described conventionally known heat exchangers. And a plurality of tank portions provided in a state communicating with a plurality of flow paths existing in the middle portion at both ends of the core portion, and a refrigerant in a part of the plurality of tank portions. A refrigerant inlet for feeding in and a refrigerant outlet for taking out the refrigerant from a part of the plurality of tank portions are provided. And it uses in the state which passes the air for air conditioning in the thickness direction of the said core part.
[0009]
  In particular, in the heat exchanger according to the present invention, at least a part of the core part in the width direction is provided on one side in the thickness direction.The first refrigerant transfer among the plurality of tank partsThe refrigerant sent to the tank portion is provided with a first flow path provided in the width direction one side portion of the thickness direction one side portion and a second flow provided in the width direction other side portion of the thickness direction one side portion. After diverting to the channel, the refrigerant that has flowed through the first channel isA first intermediate tank portion of the plurality of tank portions, and a third intermediate tank portion communicating with the first intermediate tank portion, provided at opposite end portions across the first refrigerant transfer tank portion and the core portion. ThroughIt flows in the third flow path provided at a position opposite to the second flow path in the thickness direction other side portion of the core portion with respect to the air passage direction.The second refrigerant transfer tank portion of the plurality of tank portions provided at the opposite end portion across the first and third intermediate tank portions and the core portion is reached.Withthe aboveThe refrigerant that flows in the second flow pathVia the second intermediate tank part of the plurality of tank parts provided at the opposite end part across the first refrigerant transfer tank part and the core part,Flows in a fourth flow path provided at a position opposite to the first flow path in the thickness direction other side portion of the core portion with respect to the air passage direction.Reaching the second refrigerant transfer tank.
[0010]
  Furthermore, in the case of the heat exchanger according to claim 2, at least a part of the core portion in the width direction has a plurality of first heat transfer tube elements having the same internal structure, and the front and back directions of the core portions are the same direction. In addition, a plurality of second heat transfer tube elements having the same internal structure as each of the first heat transfer tube elements, and a first portion formed by overlapping fins between adjacent first heat transfer tube elements, The second heat transfer tube element and the second heat transfer element are overlapped with each other with the fins provided between the adjacent second heat transfer tube elements with the front and back directions being the same direction. It is configured by overlapping in the width direction with the front and back directions differing from the heat tube element.
  Each of the first and second heat transfer tube elements has first, second, and third recesses provided on one end in the length direction of each side, and the other end in the length direction. The fourth and fifth recesses provided independently of each other, and also provided in the middle part,first, The first shallow recess that allows the fourth recesses to communicate with each other, and also provided in the middle portionsecondThe first concave portion is formed by joining a pair of metal plates having a second shallow concave portion that allows the fifth concave portions to communicate with each other in a state where the respective concave portions are opposed to each other. The first tank space at the part where the two concave parts are abutted, the second tank space at the part where the second concave parts are abutted, the third tank space at the part where the third concave parts are abutted, and the fourth tank. The fourth tank space at the portion where the recesses are abutted, the fifth tank space at the portion where the fifth recesses are abutted, and the portion at which the first shallow recesses are abuttedfirstIn addition, the first linear flow path for communicating the fourth tank spaces with each other, the portion where the second shallow recesses are abutted with each othersecondThe second linear flow paths for communicating the fifth tank spaces with each other are provided.
  And in the state which mutually overlap | superposed the 1st part comprised by each said 1st heat exchanger tube element, and the 2nd part comprised by each said 2nd heat exchanger tube element, in each said 1st heat exchanger tube element The provided first tank spaces communicate with each other to form a first tank portion.
  Further, the second tank space provided in each of the first heat transfer tube elements and the second tank space provided in each of the second heat transfer tube elements facing each other communicate with each other to form a second tank portion. Yes.
  Further, the first tank spaces provided in the second heat transfer tube elements facing each other communicate with each other to constitute a third tank portion.
  The fourth tank space provided in each of the first heat transfer tube elements and the fifth tank space provided in each of the second heat transfer tube elements facing each other communicate with each other to form a fourth tank portion. Yes.
  Further, the fifth tank space provided in each of the first heat transfer tube elements and the fourth tank space provided in each of the second heat transfer tube elements facing each other communicate with each other to constitute a fifth tank portion. Yes.
  Furthermore, the first tank part and the third tank part are communicated with each other via a communication path.
  And said 1st flow path is a 1st linear flow path provided in each said 1st heat exchanger tube element, and said 2nd flow path is a 2nd linear flow path provided in each said 2nd heat transfer tube element. The third flow path is a first linear flow path provided in each of these second heat transfer tube elements, and the fourth flow path is a second straight flow path provided in each of the first heat transfer tube elements. It is.
  A part of the first refrigerant transfer tank part is the fourth tank part, a part of the first intermediate tank part is the first tank part, and the second intermediate tank part is the second tank. A part of the third intermediate tank part is the third tank part, and a part of the second refrigerant transfer tank part is the fifth tank part.
[0011]
[Action]
According to the heat exchanger of the present invention configured as described above, at least part of the core portion in the width direction has relatively high temperature portions or relatively low temperature portions for air conditioning. It is possible to reduce the overlap between the air passing directions. For this reason, the temperature distribution of the air for air conditioning which passed the said core part can be made substantially uniform, and a comfortable air conditioning for a user is realizable. In addition, it becomes easy to achieve both the miniaturization of the heat exchanger and the securing of performance.
[0012]
Furthermore, according to the heat exchanger described in claim 2, since the types of heat transfer tube elements constituting the core portion can be reduced, the cost can be reduced.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
1 to 7 show an example of an embodiment of the present invention. The evaporator 1a, which is a heat exchanger of the present invention, includes a plurality of first heat transfer tube elements 19, second heat transfer tube elements 20, 20, third heat transfer tube elements 21, 21, and corrugated fins 6. , 6 are stacked. And the width direction one half part (right half part of FIG. 1, 5, 6) of this core part 9a is made into fins between said 1st heat exchanger tube elements 19 between adjacent said 1st heat exchanger tube elements 19. FIG. 6 and the plurality of second heat transfer tube elements 20 and 20 are stacked with the fins 6 provided between the adjacent second heat transfer tube elements 20 and 20. The combined second portion 23 is configured by overlapping each other in the width direction via one fin 6.
[0014]
Further, the other half portion in the width direction of the core portion 9a (the left half portion in FIGS. 1, 5 and 6) is connected to the plurality of third heat transfer tube elements 21 and 21, and the third heat transfer tube elements 21 and 21 adjacent to each other. The third portion 28 is formed by overlapping the fins 6 between them. Among the first to third heat transfer tube elements 19 to 21, the first heat transfer tube elements 19 and the second heat transfer tube elements 20 and 20 have the same internal structure. On the other hand, the internal structure of the third heat transfer tube element 21 is different from the internal structure of the first and second heat transfer tube elements 19 and 20. Moreover, each said 1st-3rd heat exchanger tube element 19-21 makes 1 set of 2 sheets of 1st metal plates 29 (or 2nd metal plate 45) which formed the recessed part in each one surface, and each recessed part mutually. In the state of facing each other, they are overlapped in the middle and joined together in an air-tight and liquid-tight manner, and have a flat flow path for allowing the coolant to flow inside.
[0015]
The first and second metal plates 29 and 45 are so-called double-sided surfaces in which a brazing material (aluminum alloy containing a large amount of Si and having a relatively low melting point) is laminated on both sides of a core material (aluminum alloy having a relatively high melting point). Clad material. When the evaporator 1a is manufactured, the first and second metal plates 29 and 45, the fins 6 and 6, the refrigerant inlet pipe 13 having the refrigerant inlet 15, and the refrigerant outlet having the refrigerant outlet 16. The pipe 14 and a side tank 27 provided with a communication passage 26 inside are combined, heated in a heating furnace, and the members 29, 45, 6, 13, 14, 27 are brazed to each other by the brazing material. Join. In this state, among the half halves of the core portion 9a, the one side portion in the width direction (right side portion in FIG. 1) becomes the first portion 22 in which the plurality of first heat transfer tube elements 19 and the fins 6 are overlapped. Similarly, the other side portion in the width direction is a second portion 23 in which the plurality of second heat transfer tube elements 18 and 18 and the fins 6 are overlapped, and the other half portion in the width direction of the core portion 9a is a plurality of third heat transfer tubes. The third portion 28 is formed by superposing the heat tube elements 21 and 21 and the fins 6.
[0016]
  Each of the first heat transfer tube elements 19 constituting the first portion 22 of the core portion 9a and each of the second heat transfer tube elements 20 and 20 similarly constituting the second portion 23 are shown in FIGS. Two first metal plates 29 as described in detail are overlapped in the middle with the concave portions facing each other, and are integrally brazed. The first metal plate 29, which is formed by pressing a base plate that is a double-sided clad material made of an aluminum alloy, is provided with first to third recesses 30 to 32 that are independent from each other at the upper end of each side. Yes. In addition, fourth and fifth recesses 33 and 34 that are independent of each other are provided at the lower end of each one surface. Furthermore, in the intermediate part, the first,FourthThe first shallow recess 35 is shallower than the first to fifth recesses 30 to 34, and the second shallowFifthA second shallow recess 36, which is also shallower than the first to fifth recesses 30 to 34, is provided to allow the recesses 31 and 34 to communicate with each other.
[0017]
Each of the first and second heat transfer tube elements 19 and 20 has a pair of the first metal plates 29 as described above in a state where the respective concave portions face each other, that is, the first concave portions 30 and the second The recesses 31, the third recesses 32, the fourth recesses 33, the fifth recesses 34, the first shallow recesses 35, and the second shallow recesses 36 are overlapped in the middle. . The first tank space 37 is abutted against the portion where the first recesses 30 are abutted, the second tank space 38 is abutted against the portion where the second recesses 31 are abutted, and the third recesses 32 are abutted. A third tank space 39 is provided in a part, a fourth tank space 40 is provided in a part where the fourth recesses 33 are abutted, and a fifth tank space 41 is provided in a part where the fifth recesses 34 are abutted. Yes.
[0018]
In addition, the first and fourth tank spaces 37 and 40 are communicated with each other by using the portion where the first shallow recesses 35 abut each other as the first linear flow path 42. Furthermore, the second and fifth tank spaces 38 and 41 are communicated with each other with the portion where the second shallow recesses 36 are abutted with each other as the second linear flow path 43. A large number of projections 44 and 44 are formed in the first and second shallow recesses 35 and 36. When the pair of first metal plates 29 are combined in the middle, the front end surfaces of the projections 44 and 44 are peripheral portions of the first metal plates 29 and the first and second shallow recesses 35, Together with a portion between 36 and the like, they are abutted against each other and brazed. In addition, the pressure resistance strength of each of the first heat transfer tube elements 19 is ensured, and the refrigerant flow in the first and second linear flow paths 42 and 43 is disturbed.
[0019]
On the other hand, each of the third heat transfer tube elements 21 and 21 constituting the third portion 28 of the core portion 9a has two second metal plates 45 as detailed in FIGS. 4 (A) and 4 (B). They are overlapped in the middle and brazed together. The second metal plate 45, which is formed by pressing a base plate that is also a double-sided clad material made of an aluminum alloy, has sixth, seventh, and eighth concave portions 46 that are independent from each other at the upper end portion of each one surface. 47 and 48 are provided. Moreover, the 9th, 10th recessed part 49 and 50 which were mutually independent are provided in the lower end part of each one surface. Furthermore, in the intermediate portion, a third shallow recess 51 that communicates the sixth and ninth recesses 46 and 49, and a fourth shallow recess 52 that communicates the eighth and tenth recesses 48 and 50, Each is provided. The third and fourth shallow recesses 51 and 52 are shallower than the sixth to tenth recesses 46 to 50.
[0020]
Each of the third heat transfer tube elements 21 and 21 has a pair of second metal plates 45 as described above in which the respective concave portions are opposed to each other, that is, the sixth concave portions 46 and the seventh concave portions 47. The eighth recesses 48, the ninth recesses 49, the tenth recesses 50, the third shallow recesses 51, and the fourth shallow recesses 52 are overlapped in the middle. The sixth tank space 53 is abutted against the portion where the sixth recesses 46 are abutted, the seventh tank space 54 is abutted against the portion where the seventh recesses 47 are abutted, and the eighth recess 48 is abutted. An eighth tank space 55 is formed in a portion, a ninth tank space 56 is formed in a portion where the ninth recesses 49 are abutted, and a tenth tank space 57 is formed in a portion where the tenth recesses 50 are abutted. ing.
[0021]
The sixth and ninth tank spaces 53 and 56 are communicated with each other by using the portion where the third shallow concave portions 51 are in contact with each other as a third linear flow path 58. Further, the eighth and tenth tank spaces 55 and 57 are communicated with each other by using the portion where the fourth shallow concave portions 52 are in contact with each other as a fourth linear flow path 59. In the third and fourth shallow recesses 51 and 52, as in the case of the first and second shallow recesses 35 and 36 provided on the first metal plate 29, a large number of protrusions 44 and 44 are provided. Forming.
[0022]
  The core portion 9a includes a first portion 22 including a plurality of first heat transfer tube elements 19 and fins 6 each configured as described above, and a second portion including a plurality of second heat transfer tube elements 20 and 20 and fins 6 as well. Part 23 and a plurality of parts each configured as described aboveThirdThe heat transfer tube elements 21 and 21 and the third portion 28 composed of the fins 6 are configured to overlap each other with the fins 6 provided in the intermediate portions. Of these, the first portion 22 is formed by stacking the plurality of first heat transfer tube elements 19 in a state where the fins 6 are provided between the adjacent first heat transfer tube elements 19 while the front and back directions are the same. It is configured by matching. The second portion 23 has the fins 6 between the adjacent second heat transfer tube elements 20 and 20 with the plurality of second heat transfer tube elements 20 and 20 being in the same direction. It is configured by overlapping in the provided state. The first and second portions 22 and 23 are connected to each other through the fins 6 with the front and back directions of the first and second heat transfer tube elements 19 and 20 constituting the portions 22 and 23 being different from each other. In the width direction (the direction in which the heat transfer tube elements 19 and 20 are stacked). The third portion 28 is configured by overlapping a plurality of third heat transfer tube elements 21 and 21 with the fins 6 provided between the adjacent third heat transfer tube elements 21 and 21. .
[0023]
And in the state which assembled | attached the evaporator 1a to some air conditioning apparatuses for motor vehicles, the 2nd linear flow path 43 in each said 1st heat exchanger tube element 19, and each said 2nd heat exchanger tube element 20, 20 The first straight flow paths 42 and 42 and the fourth straight flow paths 59 and 59 in the third heat transfer tube elements 21 and 21 are connected to the windward side with respect to the passage direction α of air for air conditioning (FIG. 1, 5 and 6).
[0024]
Then, the sixth tank spaces 53 and 53 of the third heat transfer tube elements 21 and 21 facing each other in a state where the first to third heat transfer tube elements 19 to 21 are overlapped with each other are mutually connected. The inlet tank unit 60 is configured in communication. Therefore, at the bottom of the sixth recess 46 formed in the second metal plate 45 constituting each of the third heat transfer tube elements 21, 21, one end in the width direction of the third portion 28 (of FIGS. 1, 5, 6). Except for the one second metal plate 45 located at the left end), a through hole 61 for allowing the refrigerant to pass therethrough is formed. The downstream end of the refrigerant feed pipe 13 is connected to one end portion in the length direction of the inlet tank portion 60 (the left end portion in FIGS. 1, 5, and 6) configured as described above.
[0025]
Further, the ninth tank spaces 56 and 56 of the third heat transfer tube elements 21 and 21, the fifth tank spaces 41 and 41 of the second heat transfer tube elements 18 and 18, the first heat transfer tube elements 21 and 21, respectively, The first refrigerant transfer tank unit 62 is configured to communicate with the fourth tank space 40 of the heat transfer tube element 19. For this reason, the bottom part of the 9th recessed part 49 formed in the 2nd metal plate 45 which comprises each said 3rd heat exchanger tube element 21 and 21, and the 1st metal plate 29 which comprises each said 2nd heat exchanger tube element 20,20. The bottom of the fifth recess 34 formed on the bottom and the bottom of the fourth recess 33 constituting each of the first heat transfer tube elements 19 are two first and second sheets located at both ends in the width direction of the core 9a. Except for the bimetallic plates 29 and 45, a through hole 61 for allowing the refrigerant to pass therethrough is formed. In addition, the one end side half part (right half part of FIG. 1, 5, 6) of the said 1st refrigerant | coolant transfer tank part 62 is equivalent to the 4th tank part described in Claim 2.
[0026]
Further, the third tank spaces 39, 39 of the second heat transfer tube elements 20, 20 and the first tank space 37 of the first heat transfer tube elements 19, which are opposed to each other, communicate with each other to form a first intermediate space. A tank portion 63 is configured. For this reason, it forms in the 1st metal plate 29 which comprises the bottom part of the 3rd recessed part 32 formed in the 1st metal plate 29 which comprises each said 2nd heat exchanger tube element 20, 20, and each said 1st heat exchanger tube element 19. Except for the first metal plate 29 located at one end in the width direction of the second portion 23 (the left end in FIGS. 1, 5, and 6), the bottom of the first concave portion 30 is used for allowing the refrigerant to pass therethrough. A through hole 61 is formed. In the case of this example, the first half of the first intermediate tank 63 (the right half of FIGS. 1, 5 and 6) corresponds to the first tank described in claim 2.
[0027]
Further, the second tank spaces 38, 38 of the respective second heat transfer tube elements 20, 20 and the second tank space 38 of the respective first heat transfer tube elements 19, which are opposed to each other, are communicated with each other. The 2nd intermediate tank part 64 equivalent to the 2nd tank part described in is constituted. For this reason, one end in the width direction of the second portion 23 (FIG. 1, FIG. 1) is formed at the bottom of the second recess 31 formed in each first metal plate 29 constituting each of the first and second heat transfer tube elements 19 and 20. 5 and 6) and the two first metal plates 29 and 29 located at the other end in the width direction of the first portion 22 (right ends in FIGS. 1, 5, and 6). A through hole 61 is formed.
[0028]
Further, the first tank spaces 37 and 37 of the second heat transfer tube elements 20 and 20 and the third tank space 39 of the first heat transfer tube elements 19 facing each other are communicated with each other, and a third intermediate space is formed. A tank portion 65 is configured. For this reason, the bottom part of the 1st recessed part 30 formed in each 1st metal plate 29 which comprises each said 2nd heat exchanger tube element 20, 20, and each 1st metal plate 29 which comprises each said 1st heat exchanger tube element 19 The refrigerant is allowed to pass through the bottom of the third recess 32 formed in the first except for the first metal plate 29 located at one end in the width direction of the second portion 23 (the left end in FIGS. 1, 5, and 6). For this purpose, a through hole 61 is formed. In the case of this example, one end side half portion (the left half portion in FIGS. 1, 5, and 6) of the third intermediate tank portion 65 corresponds to the third tank portion described in claim 2.
[0029]
Further, the tenth tank spaces 57 and 57 of the third heat transfer tube elements 21 and 21, the fourth tank spaces 40 and 40 of the second heat transfer tube elements 20 and 20, the first heat transfer tube elements 21 and 21, respectively, The second refrigerant transfer tank portion 66 is configured by communicating with the fifth tank space 41 of the heat transfer tube element 19. Therefore, the bottom of the tenth recess 50 of the second metal plate 45 constituting each of the third heat transfer tube elements 21, 21 and the first metal plate 29 constituting the second heat transfer tube elements 20, 20 are provided. On the bottom of the four recesses 33 and the bottom of the fifth recess 34 of the first metal plate 29 constituting each of the first heat transfer tube elements 19, two first sheets located at both ends in the width direction of the core 9a. Except for the second metal plates 29 and 45, a through hole 61 for allowing the refrigerant to pass therethrough is formed. In addition, the one end side half part (right half part of FIG. 1) of the second refrigerant transfer tank part 66 corresponds to the fifth tank part described in claim 2.
[0030]
Further, the eighth tank spaces 55, 55 of the third heat transfer tube elements 21, 21 communicate with each other to constitute an outlet tank portion 67. For this reason, at the bottom of the eighth recess 48 of the second metal plate 45 constituting each of the third heat transfer tube elements 21, 21, one end in the width direction of the third portion 28 (the right end in FIGS. 1, 5, 6). Except for the one second metal plate 45 located at, a through hole 61 for allowing the refrigerant to pass therethrough is formed. The upstream end of the refrigerant take-out pipe 14 is connected to one end portion in the length direction of the outlet tank portion 67 (the left end portion in FIGS. 1, 5, and 6) configured as described above. As described above, the bottoms of the sixth and eighth to tenth recesses 46 and 48 to 50 provided on the second metal plate 45 constituting the third heat transfer tube elements 21 and 21 are partially excluded. Through holes 61 and 61 are formed. However, a through hole is not formed in the bottom of the seventh recess 47 provided in the center of the upper end of the second metal plate 45, and the seventh tank space 54 formed by the seventh recess 47 is allowed to pass through the adjacent third transmission. The heat tube elements 21 are not in communication with each other. Such a 7th recessed part 47 is provided in order to raise the coupling strength of the adjacent 3rd heat exchanger tube elements 21 and 21. FIG. For this reason, the seventh recess 47 can be omitted if the bonding strength can be sufficiently secured.
[0031]
Further, at both ends in the width direction of the upper end portion of one surface (right side surface in FIG. 5) of one first metal plate 29 located at one end in the width direction of the core portion 9a (the right end in FIGS. 1, 5 and 6), Both ends of the side tank 27 are connected. Then, through the communication passage 26 provided inside the side tank 27, one end portion in the length direction of the first intermediate tank portion 63 (the right end portion in FIGS. 1, 5 and 6) and the third intermediate tank portion. One end portion in the length direction of 65 (the right end portion in FIGS. 1, 5, and 6) is communicated.
[0032]
When the evaporator 1a which is the heat exchanger of the present invention configured as described above is used, the liquid or gas-liquid mixed refrigerant discharged from the condenser and passing through the expansion valve is supplied from the refrigerant feeding pipe 13 to the inlet tank. It feeds into the part 60. The refrigerant sent into the inlet tank section 60 spreads over the entire inlet tank section 60 as shown by solid line arrows a in FIGS. The refrigerant that has spread into the inlet tank portion 60 is then transferred to each third heat transfer tube constituting the leeward side portion of the third portion 28 as shown by solid arrows B and B in FIGS. Heat exchange is performed between the air in the third linear flow paths 58 and 58 in the elements 21 and 21 and the air flowing in the direction of the arrow α in FIGS. It flows while doing.
[0033]
  The refrigerant that has flowed into the first refrigerant transfer tank 62 in this way is located on the leeward side of the core 9a as indicated by solid arrows C in FIGS. After the lower end of the portion flows in the horizontal direction, the second linear shape of each of the second heat transfer tube elements 20, 20 constituting the second portion 23 in the downstream half of the first refrigerant transfer tank portion 62. Channels 43 and 43(Second channel)And first linear flow paths 42 of the first heat transfer tube elements 19 constituting the first portion 22.(First channel)Sent to the inside. Subsequently, the refrigerant sent into the second linear flow paths 43 and 43 of the second heat transfer tube elements 20 and 20 passes through the second linear flow paths 43 and 43 in FIGS. As shown by solid arrows D and D in Fig. 6, after flowing while performing the heat exchange,Provided at the opposite end with the first refrigerant transfer tank 62 and the core 9a in between.The second intermediate tank portion 64 is reached. In addition, the refrigerant sent into the first linear flow path 42 in each of the first heat transfer tube elements 19 indicates the first linear flow path 42 as indicated by solid arrows D in FIGS. After flowing with the above heat exchange,Again, provided at the opposite end with the first refrigerant transfer tank 62 and the core 9a in between.The first intermediate tank portion 63 is reached.
[0034]
  In this way, the refrigerant that has reached the first intermediate tank portion 63 and the second intermediate tank portion 64 passes through the first and second intermediate tank portions 63 and 64 in FIGS. It flows as shown by arrow ho and ho. Of the refrigerant that has flowed in this way, the refrigerant that has flowed through the second intermediate tank portion 64 is the second linear flow path 43 of each first heat transfer tube element 19 that constitutes the first portion 22.(Fourth channel)As shown by the broken line arrows H in the figure, the second linear flow paths 43 flow through the heat exchange from above to below,The first and second intermediate tank portions 63, 64 and the core portion 9a are provided at opposite end portions,The second refrigerant transfer tank unit 66 is reached.
[0035]
  On the other hand, after the refrigerant flowing in the first intermediate tank portion 63 flows through the communication passage 26 provided in the side tank 27 as shown by solid line arrows in FIGS.Provided at the opposite end with the first refrigerant transfer tank 62 and the core 9a in between.It is sent into the third intermediate tank portion 65. Subsequently, the refrigerant that has flown in the third intermediate tank portion 65 as indicated by broken arrows in FIGS. 1, 5, and 6 is supplied to the second heat transfer tube elements 20, 20 constituting the second portion 23. First linear flow paths 42, 42(Third flow path)As shown by broken arrows H and H in the figure, the inside flows while exchanging the heat from the top to the bottom, and reaches the second refrigerant transfer tank portion 66. In any case, the refrigerant that has reached the second refrigerant transfer tank portion 66 has a lower end of the windward portion of the core portion 9a in the second refrigerant transfer tank portion 66, as indicated by a chain arrow in FIG. After the portion flows in the horizontal direction, it reaches the fourth linear flow paths 59 and 59 of the third heat transfer tube elements 21 and 21 constituting the third portion 28. Then, the refrigerant that has reached the fourth linear flow paths 59, 59 flows while performing the heat exchange from the bottom to the top, as indicated by chain arrows N, N in the figure, and the outlet tank section. Reach 67.
[0036]
The superheated gaseous refrigerant that has reached the outlet tank portion 67 in this way flows through the outlet tank portion 67 and then flows out into the refrigerant take-out pipe 14 as indicated by the broken arrow in FIG. Then, the refrigerant is sent to the suction port of the compressor through a pipe connected to the downstream end of the refrigerant take-out pipe 14.
[0037]
In the case of the evaporator 1a configured as described above, performing heat exchange between the refrigerant flowing inside the core portion 9a and the air passing outside the core portion 9a as described above, and cooling the air, The temperature distribution of the air after passing through the core portion 9a can be made substantially uniform. That is, in the case of the present invention, the first portion 22 and the second portion 23 that constitute one half of the width direction of the core portion 9a are relatively high temperature portions and relatively low temperature portions. It is possible to reduce the overlapping of each other with respect to the passage direction α of the air for air conditioning. That is, an inertial force acts on the liquid or gas-liquid mixed refrigerant flowing through the first refrigerant transfer tank 62 provided at the lower end of the leeward side portion of the core 9a. For this reason, from this 1st refrigerant | coolant transfer tank part 62, the 2nd linear flow paths 43 and 43 of several 2nd heat exchanger tube elements 20 and 20 provided in the intermediate part, and several 1st heat exchanger tube elements 19 of the same When the refrigerant is distributed to the first linear flow path 42, the refrigerant is placed in the first linear flow path 42 of the first heat transfer tube element 19 provided near the downstream end of the first refrigerant transfer tank 62. It becomes easy to send a lot. Conversely, it is difficult for the refrigerant to be fed into the second linear flow paths 43 and 43 of the second heat transfer tube elements 20 and 20 provided near the upstream end of the first refrigerant transfer tank 62. Therefore, the refrigerant flowing in the first linear flow paths 42 of the first heat transfer tube elements 19 is more than the refrigerant flowing in the second linear flow paths 43, 43 of the second heat transfer tube elements 20, 20. That is, drift is likely to occur.
[0038]
On the other hand, in the case of this example, the refrigerant that has flowed in the first linear flow paths 42 of the first heat transfer tube elements 19 at the leeward side portions of the first and second portions 22 and 23 is the same. These second heat transfer tube elements 20, 20 provided at positions facing the second linear flow paths 43, 43 of the second heat transfer tube elements 20, 20 in the upwind portion in the air passage direction α. To the first linear flow paths 42, 42. Further, the refrigerant that has flowed in the second linear flow paths 43 and 43 of the second heat transfer tube elements 20 and 20 in the leeward side portions of the first and second portions 22 and 23 is also in the leeward side portion. It is sent into the second linear flow path 43 of each first heat transfer tube element 19 provided at a position facing the first straight flow path 42 of each first heat transfer tube element 19 with respect to the air passing direction α. . For this reason, between the thickness direction halves of the first and second portions 22 and 23, the flow paths through which a large amount of refrigerant flows and the flow paths through which a small amount of the refrigerant flows are used for air conditioning. It is possible to reduce the overlap of the air passing direction α. Accordingly, in the first and second portions 22 and 23, the temperature becomes relatively high by reducing the flow rate of the refrigerant flowing through the inside, and a part of the core portion 9a shown in FIG. It is possible to reduce the overlap with each other in the passing direction α. In addition, in the first and second portions 22 and 23, the temperature of the refrigerant is relatively low due to an increase in the flow path of the refrigerant flowing through the inside. A part of the core portion 9a shown by a diagonal lattice in FIG. It is possible to reduce the overlapping of the air passing direction α. Therefore, the temperature distribution of the air after passing through the first and second portions 22 and 23 can be made substantially uniform.
[0039]
In addition, in the case of this example, the temperature distribution on the surface of the third portion 28, which is the other half in the width direction of the core portion 9a, is less likely to be biased. That is, in the leeward side portion of the third portion 28, the refrigerant that has flowed through the inlet tank portion 60 located at the upper end portion is divided into a plurality of third linear flow paths 58 and 58 provided in the intermediate portion. At this time, based on the fact that gravity acts on the refrigerant flowing in the inlet tank section 60, a large amount of refrigerant tends to be sent into the third linear flow path 58 connected near the upstream end of the inlet tank section 60. Become. On the other hand, based on the fact that an inertial force acts on the refrigerant flowing through the inlet tank section 60, a large amount of refrigerant tends to be sent into the third linear flow path 58 connected near the downstream end of the inlet tank section 60. . As a result, the refrigerant flows substantially uniformly in the plurality of third linear flow paths 58, 58 communicating with the inlet tank unit 60. On the other hand, in the windward part of the third part 28, most of the refrigerant flowing in the second refrigerant transfer tank part 66 located at the lower end part is in a gaseous state. For this reason, the inertia force which acts on this refrigerant | coolant becomes small. For this reason, it is unlikely that the refrigerant flows unevenly in the fourth linear flow path 59 connected near the downstream end of the second refrigerant transfer tank portion 66. As a result, the temperature distribution on the surface of the third portion 28 can be made substantially uniform. For this reason, coupled with the fact that the temperature distribution of the air that has passed through the first and second portions 22 and 23 can be made substantially uniform, the temperature distribution of the air after passing through the core portion 9a can be made almost uniform, A comfortable cooling condition for the passenger can be realized. Further, since the performance can be improved without increasing the size of the evaporator 1a, it is easy to achieve both performance securing and downsizing.
[0040]
Furthermore, according to the structure of this example, only two types of heat transfer tube elements having different internal structures constituting the core portion 9a are required. For this reason, parts production, parts management, and assembly work are all facilitated, and the cost of the evaporator 1a can be reduced. In the case of this example, the other side portion in the thickness direction of the core portion 9a on the relatively high temperature side is located on the leeward side, and one side portion in the thickness direction of the core portion 9a on the relatively low temperature side is located on the leeward side. I am letting. Therefore, a sufficient temperature difference between the core portion 9a and the air passing through the core portion 9a is ensured from the leeward side to the leeward side, and heat exchange between the core portion 9a and the air is efficiently performed. Can be made.
[0041]
In addition, the heat exchanger of this invention limits the some tank parts 60 and 62-67 as mentioned above to the structure which comprised a part of several 1st-3rd heat exchanger tube elements 19-21. is not. In the heat exchanger of the present invention, tank members separate from these heat transfer tube elements are provided at both ends of a plurality of heat transfer tube elements having flat flow paths for allowing the refrigerant to flow inside. This can be implemented even when a tank is provided on the inside.
[0042]
Moreover, although the above-mentioned description demonstrated about the case where the core part 9a was comprised by the 1st-3rd part 22,23,28, a core part is only comprised from the 1st part 22 and the 2nd part 23 of these. It can also be configured. In this case, since only one type of heat transfer tube element having a different internal structure constituting the core portion is required, the cost of the evaporator can be further reduced. Moreover, although the above-mentioned description demonstrated about the case where the heat exchanger of this invention is used as an evaporator, the heat exchanger of this invention is not limited to an evaporator. For example, the heat exchanger of the present invention can also be implemented when used as a heater core. As described above, even when the heat exchanger of the present invention is used as a heater core, the temperature distribution of the air that has passed through the core portion can be made substantially uniform as in the case of using it as an evaporator as described above.
[0043]
【The invention's effect】
Since the heat exchanger of the present invention is configured and operates as described above, it is possible to realize comfortable air conditioning and to easily achieve both downsizing and ensuring performance.
[Brief description of the drawings]
FIG. 1 is a schematic perspective view for explaining a refrigerant flow state in a heat exchanger according to an example of an embodiment of the present invention.
FIG. 2 is a schematic perspective view showing three types of elements constituting the heat exchanger of the present invention as viewed from the right side of FIG.
3 shows a first metal plate constituting the first heat transfer tube element shown in FIG. 2 (A) and the second heat transfer tube element shown in FIG. 2 (B). FIG. FIG. 1B is a view as seen from the side of FIG.
4 shows a second metal plate constituting the third heat transfer tube element shown in FIG. 2 (C), where (A) is from the back and front direction of FIG. 1, and (B) is from the side of FIG. , Each viewed.
FIG. 5 is a schematic exploded perspective view of a heat exchanger according to the present invention.
FIG. 6 is a schematic perspective view for quantitatively explaining the flow state of the refrigerant in each part of the core part.
FIG. 7 is a schematic perspective view for explaining the surface temperature distribution state by taking out only one half of the core portion in the width direction.
FIG. 8 is a schematic perspective view showing an example of a conventional structure.
FIG. 9 is a schematic perspective view for explaining a refrigerant flow state in an example of a conventional structure.
FIG. 10 is a view showing the result of measuring the surface temperature of the core part.
FIG. 11 is a schematic perspective view for taking out only a part of the core portion in the width direction and quantitatively explaining the flow state of the refrigerant.
[Explanation of symbols]
1, 1a Evaporator
2 U-shaped channel
3 First heat transfer tube element
4 Straight channel
5 Second heat transfer tube element
6 Fin
7 Part 1
8 Second part
9, 9a Core part
10 Inlet tank section
11 Intermediate tank
12 Outlet tank section
13 Refrigerant feed pipe
14 Refrigerant take-out pipe
15 Refrigerant inlet
16 Refrigerant outlet
19 First heat transfer tube element
20 Second heat transfer tube element
21 Third heat transfer tube element
22 Part 1
23 Second part
26 passage
27 Side tank
28 Third part
29 First metal plate
30 First recess
31 Second recess
32 Third recess
33 Fourth recess
34 Fifth recess
35 First shallow recess
36 Second shallow recess
37 First tank space
38 Second tank space
39 Third tank space
40 Fourth tank space
41 5th tank space
42 First linear flow path
43 Second linear channel
44 projections
45 Second metal plate
46 6th recess
47 7th recess
48 8th recess
49 9th recess
50 Tenth recess
51 3rd shallow recess
52 4th shallow recess
53 Sixth tank space
54 7th tank space
55 Eighth Tank Space
56 Ninth tank space
57 Tenth tank space
58 Third linear flow path
59 Fourth linear channel
60 Inlet tank section
61 through-hole
62 First refrigerant transfer tank
63 First intermediate tank
64 Second intermediate tank
65 Third intermediate tank
66 Second refrigerant transfer tank
67 Outlet tank section

Claims

A core part composed of a plurality of flat flow paths for flowing the refrigerant on the inner side and a plurality of fins provided between adjacent flow paths, and a plurality of intermediate parts at both ends of the core part A plurality of tank portions provided in communication with the flow path, a refrigerant inlet for sending the refrigerant to a part of the plurality of tank portions, and a refrigerant for taking out the refrigerant from a part of the plurality of tank portions In a heat exchanger that includes a take-out port and that is used in a state in which air for air conditioning is passed in the thickness direction of the core part,
At least part of the core part in the width direction , the refrigerant sent to the first refrigerant transfer tank part of the plurality of tank parts provided in the one side part in the thickness direction, of the one side part in the thickness direction After diverting into the first flow path provided in the width direction one side part and the second flow path provided in the width direction other side part of the thickness direction one side part, the refrigerant that flowed in the first flow path, A first intermediate tank portion of the plurality of tank portions, and a third intermediate tank portion communicating with the first intermediate tank portion, provided at opposite end portions across the first refrigerant transfer tank portion and the core portion. Through the third flow path provided at a position opposite to the second flow path in the thickness direction other side portion of the core portion through the first and third intermediate tanks Part of the plurality of tank parts provided at the opposite end part across the core part and the core part With reaching the refrigerant transfer tank, said second flow path to flow refrigerant, is provided at the opposite end across the first refrigerant transfer tank portion and the core portion, of the plurality of tank The second refrigerant flows through the second intermediate tank part through the fourth flow path provided at a position opposite to the first flow path in the thickness direction other side portion of the core part with respect to the air passage direction. A heat exchanger characterized by reaching the transfer tank .

At least a part of the core in the width direction is provided with a plurality of first heat transfer tube elements having the same internal structure, and fins are provided between the adjacent first heat transfer tube elements while the front and back directions are the same. Adjacent second heat transfer tube elements, with the first part superposed in a stacked state and a plurality of second heat transfer tube elements having the same internal structure as each of the first heat transfer tube elements, with the front and back directions being the same direction A second portion formed by superimposing the fins between the first heat transfer tube element and the second heat transfer tube element in the width direction with the front and back directions of the first heat transfer tube element and the second heat transfer tube element being different from each other. It is composed by overlapping,
Each said 1st, 2nd heat exchanger tube element is mutually in the 1st, 2nd, 3rd recessed part provided in the mutually independent state in the longitudinal direction one end part of each one side, and a longitudinal direction other end part mutually fourth provided in a separate state, and the fifth recess, likewise the first of them provided in the intermediate portion, a first shallow recess for communicating the fourth recess between said first and likewise provided in the intermediate portion The first and second metal plates having a pair of second shallow recesses communicating with the second and fifth recesses are overlapped in the middle with the respective recesses facing each other, and are joined to each other. A first tank space is formed at a portion where the recesses are abutted, a second tank space is formed at a portion where the second recesses are abutted, and a third tank space is formed at a portion where the third recesses are abutted. The fourth tank space in the part where the four recesses are abutted, the above Five fifth tank space in the recess each other butted portion, the first to the first shallow recess each other butted portion, the second straight flow path for communicating the fourth tank space between, the second shallow A second linear flow path for communicating the second and fifth tank spaces with each other at the portion where the recesses are abutted with each other,
Provided in each of the first heat transfer tube elements facing each other in a state where the first portion constituted by the first heat transfer tube elements and the second portion constituted by the second heat transfer tube elements are overlapped with each other. The first tank space is communicated with each other to form the first tank part,
Opposing each other, the second tank space provided in each of the first heat transfer tube elements and the second tank space provided in each of the second heat transfer tube elements communicate with each other to constitute a second tank portion,
The first tank spaces provided in each of the second heat transfer tube elements facing each other communicate with each other to constitute a third tank portion,
Opposing each other, the fourth tank space provided in each of the first heat transfer tube elements and the fifth tank space provided in each of the second heat transfer tube elements communicate with each other to constitute a fourth tank portion,
Opposing each other, the fifth tank space provided in each of the first heat transfer tube elements and the fourth tank space provided in each of the second heat transfer tube elements communicate with each other to constitute a fifth tank portion,
The first tank part and the third tank part are communicated with each other via a communication path,
The first channel is a first linear channel provided in each first heat transfer tube element, the second channel is a second linear channel provided in each second heat transfer tube element, and a third The flow path is a first linear flow path provided in each of these second heat transfer tube elements, and the fourth flow path is a second linear flow path provided in each of the first heat transfer tube elements , and the first refrigerant A part of the transfer tank part is the fourth tank part, a part of the first intermediate tank part is the first tank part, a second intermediate tank part is the second tank part, and a third intermediate tank. The heat exchanger according to claim 1, wherein a part of the part is the third tank part and a part of the second refrigerant transfer tank part is the fifth tank part .