JP2004317002A

JP2004317002A - Heat exchanger

Info

Publication number: JP2004317002A
Application number: JP2003110110A
Authority: JP
Inventors: Shoichi Yokoyama; 昭一横山; Shigeto Yamaguchi; 成人山口; Takashi Sugio; 孝杉尾
Original assignee: Matsushita Electric Industrial Co Ltd
Current assignee: Panasonic Holdings Corp
Priority date: 2003-04-15
Filing date: 2003-04-15
Publication date: 2004-11-11

Abstract

<P>PROBLEM TO BE SOLVED: To improve heat exchange performance; to secure drainage performance of a condensate; and to restrain sudden performance reduction by frosting. <P>SOLUTION: A high undulating part and a louver part having a low opening part are alternately arranged in the air flowing direction in an intermediate wall part of a corrugate fin, so that air flowing in a heat exchanger repeats separation and re-sticking of a temperature boundary layer by flowing while getting over the high undulating part, and can thereby provide the effect of improving heat transfer performance, and largely increasing heat exchange capability. When used as an evaporator, since the condensate generated on a fin surface flows down on the corrugateed fin while passing through the opening part of the louver part, superior drainage performance is provided. Even when frost falls on the fin surface, a shape of the undulating part of the intermediate wall part of the corrugated fin does not suddenly blocks up an air flow passage by sticking and growth of the frost, and can thereby provide the effect of restraining quick remarkable reduction in the performance. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、特に冷暖房兼用の空気調和機の室外機に用いられる熱交換器で、鉛直方向の偏平チューブおよび隣接する偏平チューブ間にコルゲートフィンを有する熱交換器に関するもので、凝縮性能および蒸発性能のいずれも向上させるものである。さらに、蒸発器として用いた場合に、流通空気との熱交換によりフィン表面に生じる凝縮水を良好に流下させるとともに、冷暖房兼用の空気調和機の室外機の熱交換器として用い、空気調和機を暖房運転したとき、外気温が低下した時のようにフィン表面に着霜していくとき、霜により急激に空気流路が閉塞されて性能が著しく低下するのを抑制する効果を奉するものである。
【０００２】
【従来の技術】
従来のこのタイプの熱交換器は、図７〜８に示す一般に用いられる基本構成の熱交換器のように、長手方向を鉛直方向にして、所定のピッチで互いに平行に配置された多数の偏平チューブ１と、これら偏平チューブ１の上端を連通接続する水平方向の上側ヘッダー１０と、前記偏平チューブ１の下端を連通接続する水平方向の下側ヘッダー１１と、隣接する前記偏平チューブ１の間に配置され、偏平チューブ１とろう付けや接着などにより接合あるいは密着され、頂部２１と中間壁部２２とが交互繰返し状態に折り曲げ成形され、その間隙を空気が通過するコルゲートフィン２を備える熱交換器において、図５〜６６に示すように前記コルゲートフィン２の頂部２１を平坦状に形成し、フィン角度θ１、平坦状頂部２１の長さＬ１、ルーバー長さＬ２、ルーバー角度θ２、ルーバーピッチＬ３をそれぞれ所定数値範囲に規定することにより、熱伝達率の大幅な低下を招来することなく、蒸発器として使用したときの水切れ性を向上させることを狙っている（例えば、特許文献１参照）。
【０００３】
しかし、この熱交換器が冷暖房兼用の空気調和機の室外機に用いられ、空気調和機が暖房運転され、外気温度が低くなって、コルゲートフィン２の表面温度が氷点下になるとき、空気中の水分がコルゲートフィン２に霜となって付着し、次第にこの着霜が進行し、霜が厚くなり、やがて着霜により空気の通風路が塞がれる。この間に熱交換器の通風抵抗が増大し、風量が低下し、蒸発性能が低下し、空調機の暖房性能が低下していく。特に、コルゲートフィン２には高性能化のためルーバー２ａが設けられているが、このルーバー２ａの前縁部は、局所熱伝達率が高いため、着霜の進行が早く、またルーバー２ａが設けられているため、コルゲートフィン２の各段の実質的間隔が狭く、着霜による通風路の閉塞が極めて早く、暖房能力の低下が極端に早いという欠点があった。
【０００４】
そこで、別の従来例では、コルゲートフィンの通風上流端部をルーバーのないものとしたり、偏平チューブの端よりも風上側へ突き出させた上、偏平チューブを１つおきに仕切り板に置き換えたり、ルーバーの形状を風上から風下に向かって順次変える熱交換器が開示されている（例えば、特許文献２参照）。
【０００５】
また、別の従来例では、コルゲートフィンの風上側部分に小さい角度のルーバーを形成し、風下側部分に風上側部分より大きい角度のルーバーを形成したり、コルゲートフィンの風上側部分のルーバーをなくした熱交換器が開示されている（例えば、特許文献３参照）。
【０００６】
また、別の従来例では、コルゲートフィンに角度が大きいルーバー部および平坦部あるいは凹凸部あるいは角度が小さいルーバー部を設け、角度が大きいルーバー部と平坦部あるいは凹凸部あるいは角度が小さいルーバー部の位置を、気体流路を挟んで隣接するコルゲートフィン同士で互い違いに配した熱交換器が開示されている（例えば、特許文献４参照）。
【０００７】
【特許文献１】
特開平６−２４１６７８号公報（第２〜５頁、第１〜４図）
【特許文献２】
特開平６−１４７７８５号公報（第２〜５頁、第１〜６図）
【特許文献３】
特開平６−２２１７８７号公報（第２〜４頁、第１〜７図）
【特許文献４】
特許第３０６８７６１号公報（第１〜５頁、第１〜６図）
【０００８】
【発明が解決しようとする課題】
しかしながら、上記従来の構成では、いずれにしてもコルゲートフィン２のどこかに高性能化を目的として開口部の高さが高いルーバーが設けられているために、ルーバーの風上側開口部に集中して局所的な着霜が進行し、通風路の閉塞が早くなることを抑制することはあまりできず、低外気温時の空気調和機の暖房性能の急激な低下を抑制することもある程度しかできないという課題を有していた。
【０００９】
本発明はこのような従来の課題を解決するものであり、凝縮性能および蒸発性能のいずれについても大きく向上させるとともに、さらに蒸発器として用いた場合に、流通空気との熱交換によりフィン表面に生じる凝縮水を良好に流下させるとともに、冷暖房兼用の空気調和機の室外機の熱交換器として用い、空気調和機の暖房運転中、外気温が低下したときのようにフィン表面に着霜していくとき、霜の成長により急激に空気流路が閉塞されて性能が著しく低下するのを抑制する効果を奉する熱交換器を提供することを目的とする。
【００１０】
【課題を解決するための手段】
上記課題を解決するために本発明の熱交換器は、コルゲートフィンの中間壁部に、コルゲートフィンの折り曲げの鉛直方向のピッチの１／３〜２／３の高さの起伏部と、その開口部の高さが起伏部の高さより低いルーバー部とを空気の流通方向に対し交互に配置したものである。
【００１１】
上記の構成によって、熱交換器に流入した空気は、コルゲートフィンの折り曲げの鉛直方向のピッチの１／３〜２／３の高さの起伏部を乗り越えながら流れ、温度境界層の剥離と再付着を繰り返すことにより伝熱性能が向上するとともに、その開口部の高さが起伏部の高さより低いため、伝熱性能の向上効果はわずかであるが、ルーバー部があるので、本発明の熱交換器を凝縮器、蒸発器のいずれとして用いた場合でも熱交換能力を大幅に増大させる効果が得られるものである。
【００１２】
また、蒸発器として用いた場合、流通空気との熱交換によりフィン表面に凝縮水が発生するが、この凝縮水はルーバー部の開口部を通り抜けながらコルゲートフィンを流下していくので、優れた水捌け性が得られる。さらに、本発明の熱交換器を冷暖房兼用の空気調和機の室外機に用い、空気調和機の暖房運転中、外気温が低下したときフィン表面に着霜していくが、伝熱性能向上のため設けたコルゲートフィンの中間壁部の起伏部の形状は、ルーバーや切り起こしのように隣接コルゲートフィンとの間隔を大幅に近付けるものではなく、また、起伏部の間に設けたルーバー部は、その開口部の高さが起伏部の高さより低く、着霜し始めて間もなく基板面とつながり閉塞するが、その後フラット面と同等状態となるので、霜の付着、成長により急激にコルゲートフィンの空気流路が閉塞されていくことがなく、性能が急速に著しく低下するのを抑制する効果が得られるものである。
【００１３】
【発明の実施の形態】
以下本発明の実施の形態について図面を参照して説明する。なお、本発明の熱交換器の基本構成は、従来の技術で説明した図７〜８に示す一般的な熱交換器と同様、長手方向を鉛直方向にして、所定のピッチで互いに平行に配置された多数の偏平チューブ１と、これら偏平チューブ１の上端を連通接続する水平方向の上側ヘッダー１０と、偏平チューブ１の下端を連通接続する水平方向の下側ヘッダー１１と、隣接する偏平チューブ１の間に配置され、偏平チューブ１とろう付けや接着などにより接合あるいは密着され、頂部２１と中間壁部２２とが交互に繰返し折り曲げ成形され、その間隙を空気が通過するコルゲートフィン２を備えるものであるが、そのコルゲートフィン２の中間壁部２２の表面形状に特徴があるので、コルゲートフィン２の中間壁部２２の表面形状について詳しく説明する。
【００１４】
（実施の形態１）
実施の形態１を、図１と図２を用いて説明する。
【００１５】
図１は、本発明の第１の実施形態を示す熱交換器のコルゲートフィン２の要部拡大斜視図で、図２は、図１のコルゲートフィン２の空気通過方向の拡大断面図である。図１および図２において、コルゲートフィン２の中間壁部２２表面には、稜線が空気の流通方向に対し直角方向に伸びる山部２０１と谷部２０２を空気の流通方向に交互に設けた起伏部２０３および、空気の流通方向に開口する開口部２０４を有するルーバー部２０５とを空気の流通方向に対し交互に配置し、起伏部２０３の高さＨ１を、コルゲートフィン２の折り曲げの鉛直方向のピッチＰｆの略１／３〜略２／３とし、ルーバー部２０５の開口部２０４の高さＨ２を起伏部２０３の高さＨ１より低くかつ０．８ｍｍ以下に形成している。
【００１６】
上記の構成において、熱交換器に流入した空気は、その高さＨ１がコルゲートフィン２の折り曲げの鉛直方向のピッチＰｆの略１／３〜略２／３となるよう形成した起伏部２０３の山部２０１と谷部２０２を越えながら流れ、温度境界層の剥離と再付着を繰り返すことにより伝熱性能が向上するとともに、開口部２０４の高さＨ２が起伏部の高さＨ１より低いため、わずかの伝熱性能の向上効果を有するルーバー部２０５があるので、本発明の熱交換器を凝縮器、蒸発器のいずれとして用いた場合でも熱交換能力を大幅に増大させる効果が得られるものである。また、蒸発器として用いた場合、流通空気との熱交換によりフィン表面に凝縮水が発生するが、この凝縮水はルーバー部２０５の開口部２０４を通り抜けながらコルゲートフィン２を流下していくので、優れた水捌け性が得られる。さらに、本発明の熱交換器を冷暖房兼用の空気調和機の室外機に用い、空気調和機の暖房運転中、外気温が低下したときフィン表面に着霜が進行していくが、伝熱性能向上のため設けたコルゲートフィン２の中間壁部の起伏部２０３の形状は、ルーバーや切り起こしのように隣接コルゲートフィン２との間隔を大幅に近付けるものではなく、局所熱伝達率が高いルーバーや切り起こしの前縁部に着霜が集中して進行するということがなく、また、起伏部２０３の間に設けたルーバー部２０５は、その開口部２０４の高さＨ２が起伏部２０３の高さＨ１より低くかつ０．８ｍｍ以下としているので、着霜し始めて間もなく前縁部が霜により基板面とつながり閉塞するが、その後フラット面と同等の伝熱機構を有する状態となるので、霜の付着、成長により急激にコルゲートフィン２の空気流路が閉塞されていくことがなく、性能が急速に著しく低下するのを抑制する効果が得られるものである。
【００１７】
（実施の形態２）
実施の形態２を、図３と図４を用いて説明する。
【００１８】
図３は、本発明の第２の実施形態を示す熱交換器のコルゲートフィン２の要部拡大斜視図で、図４は、図３のコルゲートフィン２の空気通過方向の拡大断面図である。図３および図４において、コルゲートフィン２を、空気の流通方向に対し、空気の流通方向の略中央部に底部を有し、その傾斜角αが略１０°〜略４０°の谷型形状となるよう形成し、コルゲートフィン２の中間壁部２２の表面には、稜線が空気の流通方向に対し直角方向に伸びる山部２０１と谷部２０２を空気の流通方向に交互に設けた起伏部２０３および、空気の流通方向に開口する開口部２０４を有するルーバー部２０５を空気の流通方向に対し交互に配置し、起伏部２０５の斜面の中間壁部２２に対する傾斜角βを、空気の流通方向の略中央部に底部を有する前記谷型形状の傾斜角α以下となるよう形成し、ルーバー部２０５の傾斜を略水平方向となるよう形成し、起伏部２０３の高さＨ１を、コルゲートフィン２の折り曲げの鉛直方向のピッチＰｆの略１／３〜略２／３とし、ルーバー部２０５の開口部２０４の高さＨ２を起伏部２０３の高さＨ１より低くかつ０．８ｍｍ以下に形成している。
【００１９】
上記の構成において、熱交換器に流入した空気は、その高さＨ１がコルゲートフィン２の折り曲げの鉛直方向のピッチＰｆの略１／３〜略２／３となるよう形成した起伏部２０３の山部２０１と谷部２０２を越えながら流れ、温度境界層の剥離と再付着を繰り返すことにより伝熱性能が向上するとともに、開口部２０４の高さＨ２が起伏部の高さＨ１より低いため、わずかの伝熱性能の向上効果を有するルーバー部２０５があるので、本発明の熱交換器を凝縮器、蒸発器のいずれとして用いた場合でも熱交換能力を大幅に増大させる効果が得られるものである。また、蒸発器として用いた場合、流通空気との熱交換によりフィン表面に凝縮水が発生するが、この凝縮水はルーバー部２０５の開口部２０４を通り抜けながらコルゲートフィン２を流下していくので、優れた水捌け性が得られる。さらに、本発明の熱交換器を冷暖房兼用の空気調和機の室外機に用い、空気調和機の暖房運転中、外気温が低下したときフィン表面に着霜が進行していくが、伝熱性能向上のため設けたコルゲートフィン２の中間壁部の起伏部２０３の形状は、ルーバーや切り起こしのように隣接コルゲートフィン２との間隔を大幅に近付けるものではなく、局所熱伝達率が高いルーバーや切り起こしの前縁部に着霜が集中して進行するということがなく、また、起伏部２０３の間に設けたルーバー部２０５は、その開口部２０４の高さＨ２が起伏部２０３の高さＨ１より低くかつ０．８ｍｍ以下としているので、着霜し始めて間もなく前縁部が霜により基板面とつながり閉塞するが、その後フラット面と同等の伝熱機構を有する状態となるので、霜の付着、成長により急激にコルゲートフィン２の空気流路が閉塞されていくことがなく、性能が急速に著しく低下するのを抑制する効果が得られるものである。さらに、コルゲートフィン２を、空気の流通方向に対し、空気の流通方向の略中央部に底部を有し、その傾斜角αが略１０°〜略４０°の谷型形状となるよう形成されているので、蒸発器として用いた場合流通空気との熱交換によりフィン表面に発生する凝縮水はコルゲートフィン２の底部に向かって円滑に流下し、起伏部２０５の斜面の中間壁部２２に対する傾斜角βを、空気の流通方向の略中央部に底部を有する前記谷型形状の傾斜角α以下となるよう形成されているので、蒸発器として用いた場合流通空気との熱交換によりフィン表面に発生する凝縮水が起伏部２０３の谷部２０２に溜まり込むことなく流下していく。また、ルーバー部２０５の傾斜は略水平方向となるよう形成されているので、通風抵抗をあまり増大させることがなく、伝熱性能の向上を図ることができる。
【００２０】
なお、上記各実施の形態では偏平チューブを用いているため、管の肉厚が同等でも、管径が小さいため、耐圧が大きくなり、特に圧力の高い二酸化炭素冷媒を用いる時に、上記各実施の形態の熱交換器が有効である。
【００２１】
また、偏平チューブの管内容積が小さいため、冷媒量を減らすことができ、可燃性冷媒であるＨＣ冷媒等を用いる時、上記各実施の形態の熱交換器が有効である。
【００２２】
【発明の効果】
上記から明らかなように、本発明の熱交換器は、コルゲートフィンの中間壁部に、コルゲートフィンの折り曲げの鉛直方向のピッチの１／３〜２／３の高さの起伏部と、その開口部の高さが起伏部の高さより低いルーバー部とを空気の流通方向に対し交互に配置したもので、この構成によれば、熱交換器に流入した空気は、コルゲートフィンの折り曲げの鉛直方向のピッチの１／３〜２／３の高さの起伏部を乗り越えながら流れ、温度境界層の剥離と再付着を繰り返すことにより伝熱性能が向上するとともに、開口部の高さが起伏部の高さより低いため、伝熱性能の向上効果はわずかであるが、ルーバー部があるので、本発明の熱交換器を凝縮器、蒸発器のいずれとして用いた場合でも熱交換能力を大幅に増大させる効果が得られるものである。また、蒸発器として用いた場合、流通空気との熱交換によりフィン表面に凝縮水が発生するが、この凝縮水はルーバー部の開口部を通り抜けながらコルゲートフィンを流下していくので、優れた水捌け性が得られる。さらに、本発明の熱交換器を冷暖房兼用の空気調和機の室外機に用い、空気調和機の暖房運転中、外気温が低下したときフィン表面に着霜していくが、伝熱性能向上のため設けたコルゲートフィンの中間壁部の起伏部の形状は、ルーバーや切り起こしのように隣接コルゲートフィンとの間隔を大幅に近付けるものではなく、また、起伏部の間に設けたルーバー部は、その開口部の高さが起伏部の高さより低く、着霜し始めて間もなく基板面とつながり閉塞するが、その後フラット面と同等状態となるので、霜の付着、成長により急激にコルゲートフィンの空気流路が閉塞されていくことがなく、性能が急速に著しく低下するのを抑制する効果が得られるものである。
【図面の簡単な説明】
【図１】本発明の第１の実施形態を示す熱交換器のコルゲートフィンの要部拡大斜視図
【図２】本発明の第１の実施形態の熱交換器のコルゲートフィンの空気通過方向の拡大断面図
【図３】本発明の第２の実施形態を示す熱交換器のコルゲートフィンの要部拡大斜視図
【図４】本発明の第２の実施形態の熱交換器のコルゲートフィンの空気通過方向の拡大断面図
【図５】従来の熱交換器のコルゲートフィンの拡大正面図
【図６】従来の熱交換器のコルゲートフィンの空気通過方向の拡大断面図
【図７】一般に用いられる基本構成を有する熱交換器の正面図
【図８】図７に示した熱交換器の側面図
【符号の説明】
１偏平チューブ
２コルゲートフィン
１０上側ヘッダー
１１下側ヘッダー
２１コルゲートフィンの頂部
２２コルゲートフィンの中間壁部
２０１空気の流通方向に直角方向に伸びる稜線を有する山部
２０２空気の流通方向に直角方向に伸びる稜線を有する谷部
２０３起伏部
２０５ルーバー部
２０４ルーバー部２０５の開口部[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a heat exchanger particularly used for an outdoor unit of an air conditioner that is also used for cooling and heating, and relates to a heat exchanger having a corrugated fin between a vertical flat tube and an adjacent flat tube, and has a condensation performance and an evaporation performance. Are all to be improved. Furthermore, when used as an evaporator, the condensed water generated on the fin surface due to heat exchange with the flowing air is allowed to flow down well, and the air conditioner is used as a heat exchanger for an outdoor unit of an air conditioner that is also used for cooling and heating. During heating operation, when frost forms on the fin surface, such as when the outside air temperature decreases, it has the effect of suppressing that the air flow path is rapidly blocked by the frost and the performance is significantly reduced. is there.
[0002]
[Prior art]
A conventional heat exchanger of this type has a large number of flat plates arranged in parallel with each other at a predetermined pitch with the longitudinal direction being vertical, like the heat exchanger having a basic configuration generally used as shown in FIGS. Between the tube 1, a horizontal upper header 10 that connects the upper ends of the flat tubes 1 in communication, a horizontal lower header 11 that connects the lower ends of the flat tubes 1 in communication, and the adjacent flat tubes 1. A heat exchanger including a corrugated fin 2 which is arranged and joined or adhered to the flat tube 1 by brazing or bonding, and the top 21 and the intermediate wall 22 are bent and formed alternately and repeatedly, and air passes through the gap. In FIG. 5, the top 21 of the corrugated fin 2 is formed flat as shown in FIGS. 5 to 66, the fin angle θ1, the length L1 of the flat top 21 and the louver. By defining the L2, the louver angle θ2, and the louver pitch L3 in respective predetermined numerical ranges, the aim is to improve drainage when used as an evaporator without causing a significant decrease in heat transfer coefficient. (For example, see Patent Document 1).
[0003]
However, when this heat exchanger is used as an outdoor unit of an air conditioner that is also used for cooling and heating, and the air conditioner is operated for heating, the outside air temperature decreases, and the surface temperature of the corrugated fins 2 falls below freezing, Moisture adheres to the corrugated fins 2 as frost, and this frost gradually progresses, the frost becomes thicker, and the air passage is blocked by the frost. During this time, the ventilation resistance of the heat exchanger increases, the air volume decreases, the evaporation performance decreases, and the heating performance of the air conditioner decreases. In particular, the corrugated fin 2 is provided with a louver 2a for high performance, but the front edge of the louver 2a has a high local heat transfer coefficient, so that frost formation progresses quickly and the louver 2a is provided. Therefore, there is a drawback that the substantial interval between the corrugated fins 2 is narrow, the ventilation passage is blocked very quickly by frost formation, and the heating capacity decreases extremely quickly.
[0004]
Therefore, in another conventional example, the ventilation upstream end of the corrugated fin has no louver, or is protruded to the windward side from the end of the flat tube, and every other flat tube is replaced with a partition plate. There is disclosed a heat exchanger in which the shape of a louver is sequentially changed from windward to leeward (for example, see Patent Document 2).
[0005]
Further, in another conventional example, a louver having a small angle is formed in the windward portion of the corrugated fin, and a louver having an angle larger than the windward portion is formed in the leeward portion, and the louver of the windward portion of the corrugated fin is eliminated. A disclosed heat exchanger is disclosed (for example, see Patent Document 3).
[0006]
In another conventional example, a corrugated fin is provided with a louver portion having a large angle and a flat portion or an uneven portion or a louver portion having a small angle, and the position of the louver portion having a large angle and the flat portion or the uneven portion or a louver portion having a small angle is provided. Are alternately arranged between adjacent corrugated fins with a gas flow path interposed therebetween (for example, see Patent Document 4).
[0007]
[Patent Document 1]
JP-A-6-241678 (pages 2 to 5, FIGS. 1 to 4)
[Patent Document 2]
JP-A-6-147785 (pages 2 to 5, FIGS. 1 to 6)
[Patent Document 3]
JP-A-6-221787 (pages 2 to 4, FIGS. 1 to 7)
[Patent Document 4]
Japanese Patent No. 3068761 (pages 1 to 5, FIGS. 1 to 6)
[0008]
[Problems to be solved by the invention]
However, in the above-described conventional configuration, a louver having a high opening is provided somewhere in the corrugated fin 2 for the purpose of high performance in any case, so that the louver concentrates on the windward opening of the louver. It is not possible to prevent the local frost from progressing and the blockage of the ventilation path from becoming early, and it is only possible to control the rapid decrease in the heating performance of the air conditioner at low outside temperatures. There was a problem that.
[0009]
The present invention solves such a conventional problem, and greatly improves both the condensation performance and the evaporation performance, and furthermore, when used as an evaporator, generates heat on the fin surface due to heat exchange with flowing air. It allows condensed water to flow down well and is used as a heat exchanger for an outdoor unit of an air conditioner that also serves as a cooling and heating unit.During the heating operation of the air conditioner, frost forms on the fin surface as if the outside air temperature had dropped. It is an object of the present invention to provide a heat exchanger that has an effect of suppressing a sharp decrease in performance due to a rapid blockage of an air flow channel due to frost growth.
[0010]
[Means for Solving the Problems]
In order to solve the above-mentioned problems, a heat exchanger according to the present invention includes a corrugated fin having an intermediate wall having a height of 1/3 to 2/3 of a vertical pitch of a corrugated fin bent and an opening thereof. The louver portion whose height is lower than the height of the undulating portion is alternately arranged in the direction of air flow.
[0011]
With the above configuration, the air that has flowed into the heat exchanger flows while climbing over the undulating portion having a height of 1/3 to 2/3 of the vertical pitch of the corrugated fin bending, and causes separation and reattachment of the temperature boundary layer. The heat transfer performance is improved by repeating the above, and the height of the opening is lower than the height of the undulating portion, so the effect of improving the heat transfer performance is slight, but since there is a louver portion, the heat exchange of the present invention Even when the vessel is used as either a condenser or an evaporator, the effect of greatly increasing the heat exchange capacity can be obtained.
[0012]
In addition, when used as an evaporator, heat exchange with the flowing air generates condensed water on the fin surface.This condensed water flows down the corrugated fin while passing through the opening of the louver portion, so that excellent water drainage is achieved. Property is obtained. Further, the heat exchanger of the present invention is used as an outdoor unit of an air conditioner that is also used for cooling and heating, and during the heating operation of the air conditioner, frost forms on the fin surface when the outside air temperature decreases, but the heat transfer performance is improved. Therefore, the shape of the undulating portion of the intermediate wall portion of the provided corrugated fin does not make the interval between the adjacent corrugated fins much like a louver or a cut and raised portion, and the louver portion provided between the undulating portions is The height of the opening is lower than the height of the undulating part, and shortly after frosting starts, it is connected to the substrate surface and closed.However, since it is in the same state as the flat surface, the air flow of the corrugated fin is rapidly increased due to frost adhesion and growth. The road is not blocked, and the effect of suppressing a rapid and significant decrease in performance can be obtained.
[0013]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. The basic configuration of the heat exchanger of the present invention is similar to the general heat exchangers shown in FIGS. 7 and 8 described in the related art, with the longitudinal direction being vertical and being arranged parallel to each other at a predetermined pitch. A plurality of flat tubes 1, a horizontal upper header 10 for connecting the upper ends of the flat tubes 1, a horizontal lower header 11 for connecting the lower ends of the flat tubes 1, and an adjacent flat tube 1. And a corrugated fin 2 through which the top portion 21 and the intermediate wall portion 22 are alternately and repeatedly bent and formed by brazing or bonding with the flat tube 1 and air is passed through the gap. However, since the surface shape of the intermediate wall portion 22 of the corrugated fin 2 is characteristic, the surface shape of the intermediate wall portion 22 of the corrugated fin 2 will be described in detail.
[0014]
(Embodiment 1)
Embodiment 1 will be described with reference to FIG. 1 and FIG.
[0015]
FIG. 1 is an enlarged perspective view of a main part of a corrugated fin 2 of a heat exchanger according to a first embodiment of the present invention, and FIG. 2 is an enlarged sectional view of the corrugated fin 2 of FIG. In FIGS. 1 and 2, the corrugated fin 2 has, on the surface of the intermediate wall 22, ridges 201 and valleys 202 whose ridges extend in a direction perpendicular to the direction of air flow, which are alternately provided in the direction of air flow. 203 and a louver portion 205 having an opening 204 opened in the air flow direction are alternately arranged with respect to the air flow direction, and the height H1 of the undulating portion 203 is set to the vertical pitch of the bending of the corrugated fin 2. The height H2 of the opening 204 of the louver portion 205 is lower than the height H1 of the undulating portion 203 and less than or equal to 0.8 mm.
[0016]
In the above configuration, the air that has flowed into the heat exchanger has the peak H of the undulating portion 203 formed so that the height H1 thereof is approximately 1/3 to approximately 2/3 of the vertical pitch Pf of the bending of the corrugated fin 2. Flowing over the portion 201 and the valley portion 202, the heat transfer performance is improved by repeating the separation and reattachment of the temperature boundary layer, and the height H2 of the opening 204 is lower than the height H1 of the undulating portion. Since the louver portion 205 has the effect of improving the heat transfer performance of the present invention, the effect of greatly increasing the heat exchange capacity can be obtained regardless of whether the heat exchanger of the present invention is used as a condenser or an evaporator. . When used as an evaporator, condensed water is generated on the fin surface due to heat exchange with flowing air, but this condensed water flows down the corrugated fin 2 while passing through the opening 204 of the louver portion 205. Excellent drainability is obtained. Furthermore, the heat exchanger of the present invention is used as an outdoor unit of an air conditioner that is also used for cooling and heating, and during the heating operation of the air conditioner, when the outside air temperature decreases, frost formation proceeds on the fin surface. The shape of the undulating portion 203 of the intermediate wall portion of the corrugated fin 2 provided for improvement does not make the interval between the adjacent corrugated fins 2 much like a louver or a cut-and-raised louver or a louver having a high local heat transfer coefficient. The frost does not concentrate on the front edge of the cut-and-raised portion, and the louver portion 205 provided between the undulating portions 203 has a height H2 of the opening 204 and a height of the undulating portion 203. Since it is lower than H1 and 0.8 mm or less, shortly after the frost starts to be formed, the front edge portion is connected to the substrate surface by frost and is closed. However, since it has a heat transfer mechanism equivalent to that of the flat surface, the frost adheres. , Rapidly without going occluded air passage of the corrugated fin 2 is the length, in which the effect of suppressing a decrease rapidly remarkably performance obtained.
[0017]
(Embodiment 2)
Embodiment 2 will be described with reference to FIG. 3 and FIG.
[0018]
FIG. 3 is an enlarged perspective view of a main part of the corrugated fin 2 of the heat exchanger according to the second embodiment of the present invention, and FIG. 4 is an enlarged cross-sectional view of the corrugated fin 2 of FIG. 3 and 4, the corrugated fin 2 has a bottom in a substantially central portion of the air flow direction with respect to the air flow direction, and has a valley shape having an inclination angle α of approximately 10 ° to approximately 40 °. On the surface of the intermediate wall portion 22 of the corrugated fin 2, ridges 201 and valleys 202 whose ridges extend in the direction perpendicular to the air flow direction are provided alternately in the undulating portions 203 in the air flow direction. Also, louver portions 205 having openings 204 opening in the air flow direction are alternately arranged with respect to the air flow direction, and the inclination angle β of the slope of the undulating portion 205 with respect to the intermediate wall portion 22 is determined in the air flow direction. The valley shape having a bottom at a substantially central portion is formed so as to have an inclination angle α or less, the louver portion 205 is formed so as to be substantially horizontal, and the height H1 of the undulating portion 203 is changed to the height of the corrugated fin 2. Vertical direction of bending And the height H2 of the opening 204 of the louver portion 205 is formed to be lower than the height H1 of the undulating portion 203 and 0.8 mm or less.
[0019]
In the above configuration, the air that has flowed into the heat exchanger has the peak H of the undulating portion 203 formed so that the height H1 thereof is approximately 1/3 to approximately 2/3 of the vertical pitch Pf of the bending of the corrugated fin 2. Flowing over the portion 201 and the valley portion 202, the heat transfer performance is improved by repeating the separation and reattachment of the temperature boundary layer, and the height H2 of the opening 204 is lower than the height H1 of the undulating portion. Since the louver portion 205 has the effect of improving the heat transfer performance of the present invention, the effect of greatly increasing the heat exchange capacity can be obtained regardless of whether the heat exchanger of the present invention is used as a condenser or an evaporator. . When used as an evaporator, condensed water is generated on the fin surface due to heat exchange with flowing air, but this condensed water flows down the corrugated fin 2 while passing through the opening 204 of the louver portion 205. Excellent drainability is obtained. Furthermore, the heat exchanger of the present invention is used as an outdoor unit of an air conditioner that is also used for cooling and heating, and during the heating operation of the air conditioner, when the outside air temperature decreases, frost formation proceeds on the fin surface. The shape of the undulating portion 203 of the intermediate wall portion of the corrugated fin 2 provided for improvement does not make the interval between the adjacent corrugated fins 2 much like a louver or a cut-and-raised louver or a louver having a high local heat transfer coefficient. The frost does not concentrate on the front edge of the cut-and-raised portion, and the louver portion 205 provided between the undulating portions 203 has a height H2 of the opening 204 and a height of the undulating portion 203. Since it is lower than H1 and 0.8 mm or less, shortly after the frost starts to be formed, the front edge portion is connected to the substrate surface by frost and is closed. However, since it has a heat transfer mechanism equivalent to that of the flat surface, the frost adheres. , Rapidly without going occluded air passage of the corrugated fin 2 is the length, in which the effect of suppressing a decrease rapidly remarkably performance obtained. Further, the corrugated fin 2 has a bottom at a substantially central portion in the air flow direction with respect to the air flow direction, and is formed so as to have a valley shape having an inclination angle α of approximately 10 ° to approximately 40 °. Therefore, when used as an evaporator, the condensed water generated on the fin surface by heat exchange with the flowing air smoothly flows down to the bottom of the corrugated fin 2, and the inclination angle of the undulating portion 205 with respect to the intermediate wall portion 22. β is formed so as to be less than or equal to the inclination angle α of the valley shape having a bottom at a substantially central portion in the direction of air flow, so that when it is used as an evaporator, heat is generated on the fin surface by heat exchange with the flowing air. The condensed water flows down without accumulating in the valley 202 of the undulation 203. Further, since the louver portion 205 is formed so as to have a substantially horizontal inclination, the heat transfer performance can be improved without increasing the ventilation resistance so much.
[0020]
In addition, in each of the above embodiments, since the flat tube is used, even if the pipes have the same thickness, the pipe diameter is small, so the pressure resistance is increased, and particularly when a carbon dioxide refrigerant having a high pressure is used, each of the above embodiments is used. A form of heat exchanger is effective.
[0021]
Further, since the internal volume of the flat tube is small, the amount of refrigerant can be reduced, and the heat exchangers of the above embodiments are effective when using HC refrigerant or the like, which is a flammable refrigerant.
[0022]
【The invention's effect】
As is clear from the above, the heat exchanger according to the present invention has a corrugated fin with an undulating portion having a height of 1/3 to 2/3 of the vertical pitch of the corrugated fin, and an opening thereof. The louver part whose height is lower than the height of the undulating part is alternately arranged in the direction of air flow. According to this configuration, the air flowing into the heat exchanger is in the vertical direction of the bending of the corrugated fin. Flows while climbing over the undulating portion having a height of 1/3 to 2/3 of the pitch of the heat transfer layer, the heat transfer performance is improved by repeating the separation and re-attachment of the temperature boundary layer, and the height of the opening is reduced by the height of the undulating portion. Since the height is lower than the height, the effect of improving the heat transfer performance is small, but the presence of the louver portion greatly increases the heat exchange capacity even when the heat exchanger of the present invention is used as either a condenser or an evaporator. That is effective. . In addition, when used as an evaporator, heat exchange with the flowing air generates condensed water on the fin surface.This condensed water flows down the corrugated fin while passing through the opening of the louver portion, so that excellent water drainage is achieved. Property is obtained. Further, the heat exchanger of the present invention is used as an outdoor unit of an air conditioner that is also used for cooling and heating, and during the heating operation of the air conditioner, frost forms on the fin surface when the outside air temperature decreases, but the heat transfer performance is improved. Therefore, the shape of the undulating portion of the intermediate wall portion of the provided corrugated fin does not make the interval between the adjacent corrugated fins much like a louver or a cut and raised portion, and the louver portion provided between the undulating portions is The height of the opening is lower than the height of the undulating part, and shortly after frosting starts, it is connected to the substrate surface and closed.However, since it is in the same state as the flat surface, the air flow of the corrugated fin is rapidly increased due to frost adhesion and growth. The road is not blocked, and the effect of suppressing a rapid and significant decrease in performance can be obtained.
[Brief description of the drawings]
FIG. 1 is an enlarged perspective view of a main part of a corrugated fin of a heat exchanger according to a first embodiment of the present invention. FIG. 2 is a perspective view of a corrugated fin of a heat exchanger according to a first embodiment of the present invention. FIG. 3 is an enlarged perspective view of a main part of a corrugated fin of a heat exchanger showing a second embodiment of the present invention. FIG. 4 is an air of a corrugated fin of a heat exchanger of a second embodiment of the present invention. FIG. 5 is an enlarged front view of a corrugated fin of a conventional heat exchanger. FIG. 6 is an enlarged cross-sectional view of a corrugated fin of a conventional heat exchanger in an air passing direction. FIG. 8 is a front view of the heat exchanger having the configuration. FIG. 8 is a side view of the heat exchanger shown in FIG.
DESCRIPTION OF SYMBOLS 1 Flat tube 2 Corrugated fin 10 Upper header 11 Lower header 21 Corrugated fin top 22 Intermediate wall 201 of corrugated fin Crest 202 having a ridge line extending in a direction perpendicular to the direction of air flow 202 Extending in a direction perpendicular to the direction of air flow Valley portion 203 having a ridgeline undulating portion 205 louver portion 204 opening of louver portion 205

Claims

長手方向を鉛直方向にして、所定のピッチで互いに平行に配置された多数の偏平チューブおよび、前記偏平チューブの上端を連通接続する水平方向の上側ヘッダーおよび、前記偏平チューブの下端を連通接続する水平方向の下側ヘッダーおよび、隣接する前記偏平チューブの間に配置され、前記偏平チューブと近接する部分を接合または密着させ、頂部と中間壁部とが交互に繰返し折り曲げられ、その間隙を空気が通過するコルゲートフィンを有する熱交換器において、前記コルゲートフィンの中間壁部に、稜線が空気の流通方向に対し直角方向に伸びる山部と谷部を空気の流通方向に交互に設けた起伏部と、空気の流通方向に開口する開口部を有するルーバー部とを空気の流通方向に対し交互に配置した熱交換器。A plurality of flat tubes arranged in parallel with each other at a predetermined pitch with the longitudinal direction being a vertical direction, a horizontal upper header for communicating and connecting the upper ends of the flat tubes, and a horizontal for connecting the lower end of the flat tubes for communication. The lower header in the direction and the adjacent flat tube are arranged between the flat tubes adjacent to each other, and the portions adjacent to the flat tubes are joined or adhered to each other, and the top portion and the intermediate wall portion are alternately and repeatedly bent, and the air passes through the gap. In the heat exchanger having the corrugated fins, the corrugated fin has an intermediate wall portion, and ridges and ridges whose ridges extend in a direction perpendicular to the air flow direction are provided alternately in the air flow direction, A heat exchanger in which louver portions having openings that open in the air flow direction are alternately arranged in the air flow direction.

長手方向を鉛直方向にして、所定のピッチで互いに平行に配置された多数の偏平チューブおよび、前記偏平チューブの上端を連通接続する水平方向の上側ヘッダーおよび、前記偏平チューブの下端を連通接続する水平方向の下側ヘッダーおよび、隣接する前記偏平チューブの間に配置され、前記偏平チューブと近接する部分を接合あるいは密着させ、頂部と中間壁部とが交互に繰返し折り曲げられ、その間隙を空気が通過するコルゲートフィンを有する熱交換器において、前記コルゲートフィンを空気の流通方向に対し、空気の流通方向の略中央部に底部を有する谷型形状とした熱交換器。A plurality of flat tubes arranged in parallel with each other at a predetermined pitch with the longitudinal direction being a vertical direction, a horizontal upper header for communicating and connecting the upper ends of the flat tubes, and a horizontal for connecting the lower end of the flat tubes for communication. The lower header in the direction and the adjacent flat tube are arranged between the flat tubes adjacent to each other, and the portions adjacent to the flat tubes are joined or adhered to each other, and the top portion and the intermediate wall portion are alternately and repeatedly bent, and the air passes through the gap. A heat exchanger having a corrugated fin having a bottom portion substantially at the center in the air flow direction with respect to the air flow direction.

前記コルゲートフィンの前記中間壁部に、稜線が空気の流通方向に対し直角方向に伸びる山部と谷部を空気の流通方向に交互に設けた起伏部と、空気の流通方向に開口する開口部を有するルーバー部とを空気の流通方向に対し交互に配置した請求項２に記載の熱交換器。In the intermediate wall portion of the corrugated fin, ridges and valleys whose ridges extend in a direction perpendicular to the air flow direction are provided alternately in the air flow direction, and an opening that opens in the air flow direction. The heat exchanger according to claim 2, wherein the louver portions having the following are alternately arranged with respect to a flow direction of the air.

空気の流通方向の略中央部に底部を有する前記谷型形状の傾斜角を１０°〜４０°とした請求項２または３に記載の熱交換器。4. The heat exchanger according to claim 2, wherein an inclination angle of the valley shape having a bottom at a substantially central portion in an air flow direction is 10 ° to 40 °. 5.

前記起伏部の斜面の前記中間壁部に対する傾斜角を、空気の流通方向の略中央部に底部を有する前記谷型形状の傾斜角以下となるよう形成した請求項３または４に記載の熱交換器。The heat exchange according to claim 3 or 4, wherein an inclination angle of the slope of the undulating portion with respect to the intermediate wall portion is formed to be equal to or less than an inclination angle of the valley shape having a bottom at a substantially central portion in a direction of air flow. vessel.

前記起伏部の高さを、前記コルゲートフィンの折り曲げの鉛直方向のピッチの１／３〜２／３とした請求項１または請求項３〜５のいずれかに記載の熱交換器。The heat exchanger according to claim 1, wherein a height of the undulating portion is set to １／ to ／ of a vertical pitch of the bending of the corrugated fin.

前記ルーバー部の傾斜を略水平方向となるよう形成した請求項３〜６のいずれかに記載の熱交換器。The heat exchanger according to any one of claims 3 to 6, wherein the inclination of the louver portion is substantially horizontal.

前記ルーバー部の開口部の高さを前記起伏部の高さより低くかつ０．８ｍｍ以下とした請求項１または請求項３〜７のいずれかに記載の熱交換器。8. The heat exchanger according to claim 1, wherein the height of the opening of the louver portion is lower than the height of the undulating portion and 0.8 mm or less. 9.