JP3863217B2 - Stacked evaporator - Google Patents

Stacked evaporator Download PDF

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JP3863217B2
JP3863217B2 JP13545896A JP13545896A JP3863217B2 JP 3863217 B2 JP3863217 B2 JP 3863217B2 JP 13545896 A JP13545896 A JP 13545896A JP 13545896 A JP13545896 A JP 13545896A JP 3863217 B2 JP3863217 B2 JP 3863217B2
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refrigerant
tank
passage
leeward
inlet
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JPH09318196A (en
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桂一 吉井
栄一 鳥越
泰一 相川
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Denso Corp
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Denso Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F28D1/0341—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the conduits

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は冷媒通路としてのチューブを金属薄板の積層構造により形成する積層型蒸発器に関するもので、自動車用空調装置の冷凍サイクルの冷媒蒸発器として好適なものである。
【０００２】
【従来の技術】
本出願人は、先に、特願平７−２７３２２１号の特許出願において、冷媒と空気とを熱交換させる熱交換部のチューブを金属薄板の積層構造により形成する積層型蒸発器において、熱交換部の冷媒通路の形態の改良により蒸発器吹出空気温度の均一化を図るものを提案している。
【０００３】
この先願のものでは、金属薄板の積層構造により形成されるチューブ内に風上側の冷媒通路と、風下側の冷媒通路を、金属薄板長手方向に並列に構成するとともに、金属薄板の両端部に、複数のチューブ相互の間を連通させて複数のチューブの冷媒通路に対する冷媒の分配、集合を行う冷媒入口側タンク部と冷媒出口側タンク部とを形成している。さらに、金属薄板積層方向の一端部または両端部にエンドプレートを配置して、このエンドプレートと、金属薄板との間に、前記タンク部に連通する連通路を構成している。
【０００４】
【発明が解決しようとする課題】
ところで、上記先願のものでは、金属薄板をプレス成形するための成形型の数を節約するために、チューブ内の風上側の冷媒通路と風下側の冷媒通路とを左右対称の同一形状にしていた。従って、風上側冷媒通路に通じる出口側タンク部と風下側冷媒通路に通じる入口側タンク部は同一の大きさになっていた。
【０００５】
このような構成による先願の蒸発器においては、本発明者らの試作検討により冷媒の流れ形態について精査したところ、冷房負荷の小さい条件下では、以下の理由から冷却能力の低下が発生することが判明した。
すなわち、上記のごとく出口側タンク部と入口側タンク部とを同一の大きさにした場合は、乾き度の大きい（比体積の大きい）冷媒が流れる出口側タンク部を冷媒出口側の圧力損失低減のために必要な大きさに設定すると、乾き度の小さい（比体積の小さい）冷媒が流れる入口側タンク部は必要以上の大きさになってしまう。そのため、冷房負荷の小さい条件下において、蒸発器への流入冷媒流量が減圧手段（温度式膨張弁）により絞られると、入口側タンク部では冷媒流速が大幅に低下する。
【０００６】
この冷媒流速の低下に伴って冷媒の液とガスとが分離してしまい、その結果、複数の風下側冷媒通路への冷媒分配が不均一となり、複数の風下側冷媒通路における熱交換効率が低下し、冷却能力の低下が発生する。
本発明は上記点に鑑みてなされたもので、熱交換部のチューブを金属薄板の積層構造により形成するとともに、このチューブ内に風上側の冷媒通路と、風下側の冷媒通路を、金属薄板長手方向に並列に構成する積層型蒸発器において、低負荷条件における冷却能力の低下を解消することを目的とする。
【０００７】
【課題を解決するための手段】
請求項１、２記載の発明では、 チューブ（２）内を流れる冷媒と前記チューブ（２）の外部を流れる空気とを熱交換させて、冷媒を蒸発させる熱交換部（３）を有し、
この熱交換部（３）のチューブ（２）を金属薄板（４、５、６）の積層構造により多数個並列形成し、
前記チューブ（２）内には、前記金属薄板（４、５、６）の長手方向と平行に風上側の冷媒通路（２ａ）と風下側の冷媒通路（２ｂ）とを並列に形成し、
前記金属薄板（４、５、６）の長手方向の両端部に、前記チューブ（２）相互の冷媒通路（２ａ、２ｂ）を連通させる冷媒入口側タンク部（４３、４４、５３、６３、６４）と、冷媒出口側タンク部（４７、４８、５７、５８、６８）とをそれぞれ形成し、
前記冷媒入口側タンク部（４３、４４、５３、６３、６４）は、前記金属薄板（４、５、６）の風下側に配置されて前記風下側の冷媒通路（２ｂ）に連通し、
前記冷媒出口側タンク部（４７、４８、５７、５８、６８）は、前記金属薄板（４、５、６）の風上側に配置されて前記風上側の冷媒通路（２ａ）に連通し、
前記多数個のチューブ（２）を形成する前記金属薄板（４、５、６）の大部分は同一形状のものであり、
前記風下側の冷媒通路（２ｂ）は、前記金属薄板（４、５、６）の長手方向両端の前記冷媒入口側タンク部（４３、４４、５３、６３、６４）相互間にて複数、並列に形成され、
前記風上側の冷媒通路（２ａ）は、前記金属薄板（４、５、６）の長手方向の両端部に位置する前記冷媒出口側タンク部（４７、４８、５７、５８、６８）相互間にて複数、並列に形成され、
前記熱交換部（３）の前記金属薄板（４、５、６）の積層方向の端部に位置する金属薄板（１１）およびこれに接合されるエンドプレート（１２）の間に連通路（１３）を形成し、上下両端の前記冷媒入口側タンク部（４３、４４、５３、６３、６４）と前記冷媒出口側タンク部（４７、４８、５７、５８、６８）とを連通することにより、前記複数の風下側の冷媒通路（２ｂ）を冷媒が並列に流れた後に、前記複数の風上側の冷媒通路（２ａ）を冷媒が並列に流れるようになっており、
前記冷媒入口側タンク部（４３、４４、５３、６３、６４）としての上側入口タンク（４３、５３、６３）と下側入口タンク（４４、６４）との断面積を前記冷媒出口側タンク部（４７、４８、５７、５８、６８）としての上側出口タンク（４７、５７）と下側出口タンク（４８、５８、６８）との断面積より小さくしてあり、
前記熱交換部（３）の前記金属薄板（４、５、６）の積層方向の他端部に位置する金属薄板（９）およびこれに接合されるエンドプレート（１０）の間に２つの連通路（１４、１５）を形成し、前記他端のエンドプレート（１０）に設置された配管ジョイント（８）の冷媒入口パイプ（８ａ）に連通する前記連通路（１５）を前記下側入口タンク（４４、６４）の連通穴（４２）に連通させ、前記配管ジョイント（８）の冷媒出口パイプ（８ｂ）に連通する前記連通路（１４）を前記上側出口タンク（４７、５７）の連通穴（４５）に連通させ、
前記冷媒入口側タンク部（４３、４４、５３、６３、６４）から前記風下側の冷媒通路（２ｂ）に冷媒が流れる経路と、前記冷媒出口側タンク部（４７、４８、５７、５８、６８）から前記風上側の冷媒通路（２ａ）に冷媒が流れる経路とが提供された積層型蒸発器を特徴としている。
また、請求項２記載の発明では、請求項１に記載の積層型蒸発器において、前記風上側の冷媒通路（２ａ）および前記風下側の冷媒通路（２ｂ）の通路幅は前記金属薄板（４、５、６）の長手方向全域で一定であることを特徴としている。
【０００８】
この構成によれば、低負荷時に蒸発器（１）への冷媒流量が減少しても、上下の入口タンク（４３、４４、５３、６３、６４）の断面積が小さいため、この入口タンクでの冷媒流速の低下割合が小となり、その結果、この入口タンク内における気液２相冷媒の液とガスとの分離を抑制できる。
つまり、入口タンク（４３、４４、５３、６３、６４）の断面積の減少により、入口タンクを通過する冷媒の流速をある程度以上に確保でき、これにより入口タンク内に生じる冷媒の旋回流によって、冷媒の液とガスとを混合した状態に維持できる。
【０００９】
その結果、入口タンクから冷媒通路（２ｂ）に分配される冷媒の気液の割合を均一化でき、蒸発器（１）の冷却能力を低負荷時にも良好に確保できる。
【００１０】
【発明の実施の形態】
以下、本発明を図に示す実施形態について説明する。図１〜図６は本発明蒸発器を自動車用空調装置の冷凍サイクルにおける冷媒蒸発器に適用した場合を示している。
図１、図２は蒸発器１の全体構成を示しており、蒸発器１は図１（ｂ）の上下方向を上下にして、図示しない自動車用空調装置の室内ユニットケース内に設置される。蒸発器１の左右方向の一端側（右端側）には配管ジョイント８が配設され、この配管ジョイント８の入口パイプ８ａには、図示しない温度作動式膨張弁（減圧手段）で減圧され膨張した低温低圧の気液２相冷媒が流入するようになっている。
【００１１】
この蒸発器１は、図１（ｂ）に示すように多数のチューブ２を並列に形成し、このチューブ２内の冷媒通路を流れる冷媒とチューブ２の外部を流れる空調用送風空気とを熱交換させる熱交換部３を備えている。図中、矢印Ａは送風空気の流れ方向を示す。
この熱交換部３は、図３〜図５に示す金属薄板４〜６の積層構造により形成されており、その具体的構造は基本的には、先願（特願平７−２７３２２１号）のものと同じでよいので、以下積層構造の概略を説明すると、熱交換部３では、金属薄板４〜６として、具体的にはアルミニュウム心材（Ａ３０００番系の材料）の両面にろう材（Ａ４０００番系の材料）をクラッドした両面クラッド材（板厚：０．４〜０．６ｍｍ程度）を用い、この両面クラッド材を所定形状に成形して、これを２枚１組として多数組積層した上で、ろう付けにより接合することにより多数のチューブ２を並列に形成するものである。
【００１２】
そして、金属薄板４〜６を２枚１組として最中合わせの状態に接合することにより形成されるチューブ２は、その内部に風上側の冷媒通路２ａと風下側の冷媒通路２ｂとを、金属薄板長手方向に沿って平行に形成する。
図３に示す金属薄板４はチューブ２の大部分を構成する基本の薄板であり、その上下両端部には、上記冷媒通路２ａ、２ｂ相互の間をそれぞれ連通させる連通穴４１、４２を持った入口タンク部４３、４４、および連通穴４５、４６を持った出口タンク部４７、４８が形成されている。このタンク部４３、４４、４７、４８は金属薄板４の外方側へ突出する楕円筒状の突出部にて形成されている。
【００１３】
そして、入口タンク部４３、４４の断面積は、出口タンク部４７、４８の断面積より小さく設定してある。具体的設計例として、金属薄板４の幅（図３左右方向の幅）が５８ｍｍの場合、入口タンク部４３、４４の最小開口部の断面積は、１１７．８ｍｍ2 で、出口タンク部４７、４８の最小開口部の断面積は１７２．４ｍｍ2 である。従って、本例では、入口タンク部４３、４４の断面積は、出口タンク部４７、４８の断面積の約６８％の大きさにしてある。
【００１４】
４９は風上側の冷媒通路２ａと風下側の冷媒通路２ｂとを仕切るセンターリブであり、本例では冷媒通路２ａと冷媒通路２ｂとを同一幅寸法となるように仕切っている。
金属薄板５、６も金属薄板４と同様の構成になっており、金属薄板５の相違点は断面積の小さい入口タンク部５３を一端側（上端側）に設けるのみで、他端側（下端側）では、入口タンク部の代わりに、冷媒通路を遮断する仕切り部５２を形成している。
【００１５】
金属薄板６の相違点は断面積の大きい出口タンク部６８を一端側（下端側）に設けるのみで、他端側（上端側）では、出口タンク部の代わりに、冷媒通路を遮断する仕切り部６５を形成している。金属薄板５、６の他の点は金属薄板４と同じであるので、各符号についての説明は省略する。
また、熱交換部３において、隣接するチューブ２の外面側相互の間隙にコルゲートフィン（フィン手段）７を接合して空気側の伝熱面積の増大を図っている。このコルゲートフィン７はＡ３００３のような、ろう材をクラッドしてないアルミニュウムベア材にて波形状に成形されている。
【００１６】
熱交換部３の金属薄板積層方向の一端部（右端部）に位置する金属薄板９およびこれに接合されるエンドプレート１０、さらに金属薄板積層方向の他端部（左端部）に位置する金属薄板１１およびこれに接合されるエンドプレート１２も、上記金属薄板４と同様に両面クラッド材から成形されている。但し、これらの板材９、１０、１１、１２は強度確保のため、上記金属薄板４より厚肉、例えば、１．０〜１．６ｍｍ程度にしてある。
【００１７】
図２（ａ）は左端部のエンドプレート１２を示すもので、エンドプレート１２は、その長手方向に沿って並列に形成され、外方側へ突出する複数の張出部１２ａを有し、この張出部１２ａと金属薄板１１との間に形成される空間により、上下両端のタンク部間の冷媒通路を連通させる連通路１３（図６参照）が形成される。複数の張出部１２ａの間に形成される接合部１２ｂは、金属薄板１１に当接し、金属薄板１１に接合される。
【００１８】
左端部の金属薄板１１の上下の端部には、連通穴（図示せず）を有するタンク部１１ａと連通穴（図示せず）を有するタンク部１１ｂが形成されている。ここで、タンク部１１ａ、１１ｂは図１に示すように、金属薄板１１の幅方向に沿って延びる細長の１つの椀状部から形成されている。
張出部１２ａで構成される連通路１３の下端部は金属薄板１１の下端部のタンク部１１ｂの連通穴を介して、図３の金属薄板４の下端部の入口タンク４４の連通穴４２と連通する。そして、連通路１３の上端部は金属薄板１１の上端部のタンク部１１ａの連通穴を介して、図３の金属薄板４の上端部の出口タンク４７の連通穴４５と連通する。
【００１９】
右端部の金属薄板９は上記左端部の金属薄板１１と略同一形状であるので、詳細な説明は省略する。また、右端部のエンドプレート１０は、図２（ｂ）に示すように、配管ジョイント８の設置部位にて上下に２分割された張出部１０ａ、１０ｂを有し、この張出部１０ａ、１０ｂの内側と右端部の金属薄板９との間に形成される空間により連通路１４、１５（図６参照）を形成している。下側の張出部１０ｂは複数個並列に形成さており、この複数の張出部１０ｂの間に形成される接合部１０ｃは、金属薄板９に当接し、金属薄板９に接合される。
【００２０】
上側の張出部１０ａは１つの椀状の突出部からなり、この上側の張出部１０ａで構成される連通路１４は、金属薄板９の出口タンク９ａ（図１（ａ）（ｂ）参照）の連通穴（図示せず）を介して金属薄板４の上側出口タンク４７の連通穴４５と連通するとともに、配管ジョイント８の冷媒出口パイプ８ｂに連通する。 下側の張出部１０ｂで構成される連通路１５の上端部は、配管ジョイント８の冷媒入口パイプ８ａに連通し、連通路１５の下端部は、金属薄板９の入口タンク９ｂの連通穴（図示せず）を介して金属薄板４の下側入口タンク４４の連通穴４２に連通する。
【００２１】
なお、配管ジョイント８はＡ６０００番系のアルミニュウムベア材にて冷媒入口パイプ８ａと冷媒出口パイプ８ｂを一体成形してあり、この両パイプ８ａ、８ｂの通路端部をエンドプレート１０の穴部（図示せず）内に嵌入してろう付けしている。この配管ジョイント８の冷媒入口パイプ８ａには、図示しない膨張弁の出口側冷媒配管が連結され、また、冷媒出口パイプ８ｂには、蒸発器で蒸発したガス冷媒を圧縮機（図示せず）側へ吸入させる圧縮機吸入配管が連結される。
【００２２】
図６は蒸発器１内における冷媒通路の構成を示す概要図であり、金属薄板４、５、６の下側入口タンク４４、６４の途中および上側出口タンク４７、５７の途中に、それぞれ仕切り部５２、６５を設けている。これにより、金属薄板４、５、６の下側入口タンク４４、６４を第１入口タンク部ａと第２入口タンク部ｂとに仕切るとともに、金属薄板４、５、６の上側出口タンク４７、５７を第１出口タンク部ｃと第２出口タンク部ｄとに仕切っている。
【００２３】
以上により、蒸発器１内を冷媒が次の経路により流れる。すなわち、冷媒は、冷媒入口パイプ８ａ→連通路１５→下側入口タンク４４、６４の第１入口タンク部ａ→チューブ２の冷媒通路２ｂ→上側入口タンク４３、５３、６３→チューブ２の冷媒通路２ｂ→下側入口タンク４４、６４の第２入口タンク部ｂ→連通路１３→上側出口タンク４７、５７の第１出口タンク部ｃ→チューブ２の冷媒通路２ａ→下側出口タンク４８、５８、６８→チューブ２の冷媒通路２ａ→上側出口タンク４７、５７の第２出口タンク部ｄ→連通路１４→冷媒出口パイプ８ｂの経路で流れる。
【００２４】
このように、冷媒経路を構成することにより、矢印Ａ方向に流れる空気の蒸発器吹出空気温度を熱交換部３の全域に渡って均一化できる。
ところで、上記のごとく風上側の上下の出口タンク４７、５７、４８、５８、６８、および風下側の上下の入口タンク４３、５３、６３、４４、６４の双方において、冷媒流れをＵターンさせているが、本発明においては、風上側の上下の出口タンク４７、５７、４８、５８、６８の断面積に対して、風下側の上下の入口タンク４３、５３、６３、４４、６４の断面積を小さくしている。具体的には、本例では、風下側の上下の入口タンクの断面積を風上側の上下の出口タンクに対して６８％程度の大きさにしている。
【００２５】
そのため、低負荷時に蒸発器１への冷媒流量が温度式膨張弁にて絞られても、上下の入口タンク４３、５３、６３、４４、６４の断面積が小さいため、この入口タンクでの冷媒流速の低下割合が小となり、その結果、この入口タンク内における気液２相冷媒の液とガスとの分離を抑制できる。
つまり、入口タンク４３、５３、６３、４４、６４の断面積の減少により、入口タンクを通過する冷媒の流速をある程度以上に確保でき、これにより入口タンク内に生じる冷媒の旋回流によって、冷媒の液とガスとを混合した状態に維持できる。
【００２６】
その結果、入口タンクから風下側の冷媒通路２ｂに分配される冷媒の気液の割合を均一化でき、蒸発器１の冷却能力を低負荷時にも良好に確保できる。
次に、本実施形態の冷媒蒸発器の製造方法を簡単に説明すると、蒸発器１は図１、２に示す状態に積層して仮組付した後、その仮組付状態を適宜の治具にて保持して、ろう付け炉内に仮組付体を搬入する。次に、このろう付け炉内にて、仮組付体をアルミニュウム両面クラッド材のろう材の融点まで加熱して、蒸発器１各部の接合箇所を一体ろう付けする。
（他の実施形態）
なお、本発明の要部は入口タンク部と出口タンク部の断面積の設定にあるから、熱交換部３における冷媒通路構成は図６に示す例に限定されることなく、種々変更してもよいことは勿論である。
【００２７】
例えば、上記実施形態では、冷媒の入口、出口パイプ８ａ、８ｂを有する配管ジョイント８を蒸発器右側端部の上下中間部位に設置しているため、連通路１４、１５を必要としているが、金属薄板９のタンク部９ａ、９ｂの部位に、冷媒の入口、出口パイプ８ａ、８ｂを直接、設置することも可能であり、この場合は連通路１４、１５を形成するエンドプレート１０が不要になる。
【００２８】
また、図３〜図５の金属薄板４〜６では、センターリブ４９、５９、６９をそれぞれ金属薄板幅方向の中央に設定して、冷媒通路２ａ、２ｂの幅を同一に設定することにより、この冷媒通路２ａ、２ｂ内に上記センターリブに対して左右対称となるインナーフィン（図示せず）を配設可能としているが、上記センターリブを金属薄板幅方向の中央から左右にずれた位置に設定してもよい。
【００２９】
また、冷媒通路２ａ、２ｂ内にインナーフィンを設ける代わりに、金属薄板４〜６に適宜の形状からなるリブ、あるいはディンプルを冷媒流れ方向に沿って形成し、冷媒側の伝熱効率を高めるようにしてもよい。
【図面の簡単な説明】
【図１】（ａ）は本発明の一実施形態を示す蒸発器の上面図、（ｂ）は同蒸発器の正面図、（ｃ）は同蒸発器の下面図である。
【図２】（ａ）は図１の蒸発器の左側面図、（ｂ）は同蒸発器の右側面図である。
【図３】図１の蒸発器に用いられるチューブ用の金属薄板の正面図である。
【図４】図１の蒸発器に用いられるチューブ用の別の金属薄板の正面図である。
【図５】図１の蒸発器に用いられるチューブ用のさらに別の金属薄板の正面図である。
【図６】本発明の一実施形態における蒸発器の冷媒通路構成を示す概略斜視図である。
【符号の説明】
１…蒸発器、２…チューブ、２ａ…風上側の冷媒通路、
２ｂ…風下側の冷媒通路、３…熱交換部、４、５、６、９、１１…金属薄板、
４３、４４、５３、６３、６４…冷媒入口側タンク部、
４７、４８、５７、５８、６８…冷媒出口側タンク部。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a laminated evaporator in which a tube as a refrigerant passage is formed by a laminated structure of thin metal plates, and is suitable as a refrigerant evaporator for a refrigeration cycle of an automotive air conditioner.
[0002]
[Prior art]
The present applicant, in the patent application of Japanese Patent Application No. 7-273221, previously conducted heat exchange in a laminated evaporator in which a tube of a heat exchange part for heat exchange between refrigerant and air is formed by a laminated structure of thin metal plates. Has proposed that the temperature of the evaporator blown air is made uniform by improving the shape of the refrigerant passage in the section.
[0003]
In this prior application, a windward refrigerant passage and a leeward refrigerant passage are configured in parallel in the metal sheet longitudinal direction in a tube formed by a laminated structure of metal sheets, and at both ends of the metal sheet, A plurality of tubes communicate with each other to form a refrigerant inlet side tank portion and a refrigerant outlet side tank portion for distributing and collecting refrigerant to the refrigerant passages of the plurality of tubes. Furthermore, an end plate is disposed at one end or both ends in the metal thin plate stacking direction, and a communication path communicating with the tank portion is formed between the end plate and the metal thin plate.
[0004]
[Problems to be solved by the invention]
By the way, in the above-mentioned prior application, in order to save the number of forming dies for press-molding the thin metal plate, the leeward refrigerant passage and the leeward refrigerant passage in the tube have the same symmetrical shape. It was. Therefore, the outlet side tank portion communicating with the leeward side refrigerant passage and the inlet side tank portion communicating with the leeward side refrigerant passage have the same size.
[0005]
In the evaporator of the prior application having such a configuration, the refrigerant flow form was examined by the inventors' trial manufacture, and under the condition that the cooling load is small, the cooling capacity is reduced due to the following reason. There was found.
That is, when the outlet side tank part and the inlet side tank part have the same size as described above, the outlet side tank part through which the refrigerant having a large dryness (large specific volume) flows is reduced in pressure loss on the refrigerant outlet side. If it is set to a size necessary for the purpose, the inlet side tank portion through which the refrigerant having a small dryness (small specific volume) flows becomes unnecessarily large. For this reason, when the flow rate of refrigerant flowing into the evaporator is throttled by the pressure reducing means (temperature expansion valve) under the condition of a small cooling load, the refrigerant flow rate is greatly reduced in the inlet side tank.
[0006]
As the refrigerant flow rate decreases, the refrigerant liquid and gas are separated, and as a result, the refrigerant distribution to the plurality of leeward refrigerant passages becomes uneven, and the heat exchange efficiency in the plurality of leeward refrigerant passages decreases. As a result, the cooling capacity is reduced.
The present invention has been made in view of the above points, and the tube of the heat exchanging portion is formed by a laminated structure of metal thin plates, and the windward side refrigerant passage and the leeward side refrigerant passage are formed in the tube with the longitudinal direction of the metal thin plate. An object of the present invention is to eliminate a decrease in cooling capacity under a low load condition in a stacked evaporator configured in parallel in a direction.
[0007]
[Means for Solving the Problems]
In invention of Claim 1, 2, it has a heat exchange part (3) which heat-exchanges the refrigerant | coolant which flows through the inside of a tube (2), and the air which flows the exterior of the said tube (2), and evaporates a refrigerant | coolant,
A large number of tubes (2) of the heat exchange part (3) are formed in parallel by a laminated structure of thin metal plates (4, 5, 6),
In the tube (2), an leeward refrigerant passage (2a) and a leeward refrigerant passage (2b) are formed in parallel with the longitudinal direction of the thin metal plates (4, 5, 6),
Refrigerant inlet side tank portions (43, 44, 53, 63, 64) for allowing the refrigerant passages (2a, 2b) between the tubes (2) to communicate with both longitudinal ends of the thin metal plates (4, 5, 6). ) And the refrigerant outlet side tank part (47, 48, 57, 58, 68), respectively,
The refrigerant inlet side tank portion (43, 44, 53, 63, 64) is disposed on the leeward side of the metal thin plate (4, 5, 6) and communicates with the refrigerant passage (2b) on the leeward side,
The refrigerant outlet side tank portion (47, 48, 57, 58, 68) is disposed on the windward side of the thin metal plate (4, 5, 6) and communicates with the refrigerant passage (2a) on the windward side,
Most of the thin metal plates (4, 5, 6) forming the multiple tubes (2) have the same shape,
A plurality of the leeward refrigerant passages (2b) are arranged in parallel between the refrigerant inlet side tank portions (43, 44, 53, 63, 64) at both longitudinal ends of the metal thin plates (4, 5, 6). Formed into
The windward side refrigerant passage (2a) is provided between the refrigerant outlet side tank portions (47, 48, 57, 58, 68) located at both ends in the longitudinal direction of the metal thin plates (4, 5, 6). Are formed in parallel,
A communication path (13) between the metal thin plate (11) located at the end of the heat exchange part (3) in the stacking direction of the metal thin plates (4, 5, 6) and the end plate (12) joined thereto. ) And communicating the refrigerant inlet side tank portions (43, 44, 53, 63, 64) at the upper and lower ends with the refrigerant outlet side tank portions (47, 48, 57, 58, 68), After the refrigerant flows in parallel through the plurality of leeward refrigerant passages (2b), the refrigerant flows in parallel through the plurality of leeward refrigerant passages (2a),
The sectional area of the upper inlet tank (43, 53, 63) and the lower inlet tank (44, 64) as the refrigerant inlet side tank part (43, 44, 53, 63, 64) is defined as the refrigerant outlet side tank part. (47, 48, 57, 58, 68) smaller than the cross-sectional area of the upper outlet tank (47, 57) and the lower outlet tank (48, 58, 68) ,
Between the metal thin plate (9) located at the other end in the stacking direction of the metal thin plates (4, 5, 6) of the heat exchanging portion (3), and two end plates (10) joined thereto, A passage (14, 15) is formed, and the communication passage (15) communicating with the refrigerant inlet pipe (8a) of the pipe joint (8) installed on the end plate (10) at the other end is connected to the lower inlet tank. The communication passage (14) connected to the communication hole (42) of (44, 64) and the refrigerant outlet pipe (8b) of the pipe joint (8) is connected to the communication hole of the upper outlet tank (47, 57). Communicate with (45),
A path through which the refrigerant flows from the refrigerant inlet side tank part (43, 44, 53, 63, 64) to the leeward side refrigerant path (2b), and the refrigerant outlet side tank part (47, 48, 57, 58, 68). ) To the above-mentioned refrigerant passage (2a) on the windward side.
According to a second aspect of the present invention, in the stacked evaporator according to the first aspect, the width of the refrigerant path on the windward side (2a) and the width of the refrigerant path on the leeward side (2b) is the metal thin plate (4 5 and 6), which is constant throughout the longitudinal direction.
[0008]
According to this configuration, even if the refrigerant flow rate to the evaporator (1) decreases at low loads, the upper and lower inlet tanks (43, 44, 53, 63, 64) have small cross-sectional areas. As a result, the separation of the gas-liquid two-phase refrigerant liquid and gas in the inlet tank can be suppressed.
That is, by reducing the cross-sectional area of the inlet tank (43, 44, 53, 63, 64), the flow rate of the refrigerant passing through the inlet tank can be secured to a certain degree or more, and thereby the swirling flow of the refrigerant generated in the inlet tank, The refrigerant liquid and the gas can be maintained in a mixed state.
[0009]
As a result, the gas-liquid ratio of the refrigerant distributed from the inlet tank to the refrigerant passage (2b) can be made uniform, and the cooling capacity of the evaporator (1) can be ensured well even at a low load.
[0010]
DETAILED DESCRIPTION OF THE INVENTION
DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments shown in the drawings will be described below. FIGS. 1-6 has shown the case where this invention evaporator is applied to the refrigerant evaporator in the refrigerating cycle of a motor vehicle air conditioner.
1 and 2 show the overall configuration of the evaporator 1, and the evaporator 1 is installed in an indoor unit case of an automotive air conditioner (not shown) with the vertical direction of FIG. A pipe joint 8 is disposed at one end side (right end side) of the evaporator 1 in the left-right direction, and the inlet pipe 8a of the pipe joint 8 is decompressed and expanded by a temperature-actuated expansion valve (pressure reducing means) (not shown). A low-temperature and low-pressure gas-liquid two-phase refrigerant flows in.
[0011]
In this evaporator 1, as shown in FIG. 1B, a large number of tubes 2 are formed in parallel, and heat exchange is performed between the refrigerant flowing through the refrigerant passage in the tubes 2 and the air-conditioning blown air flowing outside the tubes 2. The heat exchange part 3 is provided. In the figure, arrow A indicates the flow direction of the blown air.
This heat exchanging portion 3 is formed by a laminated structure of metal thin plates 4 to 6 shown in FIGS. 3 to 5, and the specific structure is basically the same as that of the prior application (Japanese Patent Application No. 7-273221). In the heat exchanging section 3, the brazing material (No. A4000) is used as the metal thin plates 4 to 6, specifically, on both sides of the aluminum core material (A3000 series material). Using a double-sided clad material (plate thickness: about 0.4 to 0.6 mm) clad with a system material), this double-sided clad material is molded into a predetermined shape, and a set of two pieces is laminated. Thus, a large number of tubes 2 are formed in parallel by joining by brazing.
[0012]
And the tube 2 formed by joining the thin metal plates 4-6 as a set to the middle state, the inside of the tube 2 is provided with a refrigerant channel 2a on the windward side and a refrigerant channel 2b on the leeward side. It forms in parallel along a thin plate longitudinal direction.
The thin metal plate 4 shown in FIG. 3 is a basic thin plate constituting most of the tube 2, and has communication holes 41 and 42 at the upper and lower ends thereof for communicating between the refrigerant passages 2a and 2b, respectively. Inlet tank portions 43 and 44 and outlet tank portions 47 and 48 having communication holes 45 and 46 are formed. The tank portions 43, 44, 47, and 48 are formed by elliptic cylindrical protrusions that protrude outward from the thin metal plate 4.
[0013]
The sectional areas of the inlet tank portions 43 and 44 are set smaller than the sectional areas of the outlet tank portions 47 and 48. As a specific design example, when the width of the metal thin plate 4 (width in the left-right direction in FIG. 3) is 58 mm, the sectional area of the minimum opening of the inlet tank portions 43 and 44 is 117.8 mm 2 , and the outlet tank portion 47, The cross-sectional area of the smallest opening of 48 is 172.4 mm 2 . Therefore, in this example, the cross-sectional area of the inlet tank portions 43 and 44 is about 68% of the cross-sectional area of the outlet tank portions 47 and 48.
[0014]
Reference numeral 49 denotes a center rib that partitions the leeward refrigerant passage 2a and the leeward refrigerant passage 2b. In this example, the refrigerant passage 2a and the refrigerant passage 2b are partitioned so as to have the same width.
The metal thin plates 5 and 6 have the same configuration as the metal thin plate 4, and the difference between the metal thin plates 5 is that an inlet tank 53 having a small cross-sectional area is provided on one end side (upper end side) and the other end side (lower end side). On the side), a partition 52 for blocking the refrigerant passage is formed instead of the inlet tank.
[0015]
The difference between the thin metal plates 6 is that the outlet tank portion 68 having a large cross-sectional area is only provided on one end side (lower end side), and on the other end side (upper end side), a partition portion that blocks the refrigerant passage instead of the outlet tank portion. 65 is formed. Since the other points of the metal thin plates 5 and 6 are the same as those of the metal thin plate 4, description of each symbol is omitted.
Further, in the heat exchanging section 3, corrugated fins (fin means) 7 are joined to the gaps between the outer surfaces of adjacent tubes 2 to increase the heat transfer area on the air side. The corrugated fins 7 are formed into a corrugated shape using an aluminum bare material such as A3003 which is not clad with a brazing material.
[0016]
The thin metal plate 9 positioned at one end (right end) of the heat exchange section 3 in the thin metal plate stacking direction, the end plate 10 joined thereto, and the thin metal plate positioned at the other end (left end) of the thin metal plate stacking direction 11 and the end plate 12 joined thereto are also formed from a double-sided clad material in the same manner as the thin metal plate 4. However, these plate materials 9, 10, 11, and 12 are thicker than the metal thin plate 4, for example, about 1.0 to 1.6 mm in order to ensure strength.
[0017]
FIG. 2A shows the end plate 12 at the left end. The end plate 12 has a plurality of projecting portions 12a formed in parallel along the longitudinal direction and projecting outward. A communication path 13 (see FIG. 6) is formed by the space formed between the overhanging portion 12a and the metal thin plate 11 to communicate the refrigerant passage between the tank portions at the upper and lower ends. A joining portion 12b formed between the plurality of overhang portions 12a abuts on the metal thin plate 11 and is joined to the metal thin plate 11.
[0018]
A tank part 11a having a communication hole (not shown) and a tank part 11b having a communication hole (not shown) are formed at the upper and lower ends of the thin metal plate 11 at the left end. Here, as shown in FIG. 1, the tank portions 11 a and 11 b are formed from one elongated hook-shaped portion extending along the width direction of the metal thin plate 11.
The lower end portion of the communication passage 13 constituted by the overhanging portion 12a is connected to the communication hole 42 of the inlet tank 44 at the lower end portion of the thin metal plate 4 in FIG. 3 through the communication hole of the tank portion 11b at the lower end portion of the thin metal plate 11. Communicate. And the upper end part of the communicating path 13 is connected with the communicating hole 45 of the exit tank 47 of the upper end part of the metal thin plate 4 of FIG. 3 through the communicating hole of the tank part 11a of the upper end part of the thin metal plate 11. FIG.
[0019]
Since the metal thin plate 9 at the right end has substantially the same shape as the metal thin plate 11 at the left end, detailed description thereof is omitted. Moreover, as shown in FIG.2 (b), the right end part end plate 10 has the overhang | projection parts 10a and 10b divided into two up and down in the installation site | part of the piping joint 8, This overhang | projection part 10a, Communication spaces 14 and 15 (see FIG. 6) are formed by a space formed between the inner side of 10b and the metal thin plate 9 at the right end. A plurality of lower projecting portions 10 b are formed in parallel, and a joint portion 10 c formed between the plurality of projecting portions 10 b abuts on the metal thin plate 9 and is joined to the metal thin plate 9.
[0020]
The upper overhanging portion 10a is composed of one hook-like protrusion, and the communication path 14 formed by the upper overhanging portion 10a is an outlet tank 9a of the thin metal plate 9 (see FIGS. 1A and 1B). ) And a communication hole 45 of the upper outlet tank 47 of the thin metal plate 4 and a refrigerant outlet pipe 8b of the pipe joint 8 through a communication hole (not shown). The upper end portion of the communication passage 15 constituted by the lower overhanging portion 10 b communicates with the refrigerant inlet pipe 8 a of the pipe joint 8, and the lower end portion of the communication passage 15 is the communication hole of the inlet tank 9 b of the metal thin plate 9 ( It communicates with the communication hole 42 of the lower inlet tank 44 of the thin metal plate 4 via a not shown).
[0021]
The pipe joint 8 is formed by integrally forming a refrigerant inlet pipe 8a and a refrigerant outlet pipe 8b with an A6000 series aluminum bare material, and the passage ends of both the pipes 8a and 8b are formed as holes in the end plate 10 (see FIG. (Not shown). The refrigerant inlet pipe 8a of the pipe joint 8 is connected to an outlet side refrigerant pipe of an expansion valve (not shown), and the refrigerant outlet pipe 8b receives gas refrigerant evaporated by the evaporator on the compressor (not shown) side. Compressor suction piping for suction is connected.
[0022]
FIG. 6 is a schematic view showing the configuration of the refrigerant passage in the evaporator 1, and the partition portions are provided in the middle of the lower inlet tanks 44, 64 and the upper outlet tanks 47, 57 of the thin metal plates 4, 5, 6. 52 and 65 are provided. Accordingly, the lower inlet tanks 44 and 64 of the thin metal plates 4, 5 and 6 are divided into the first inlet tank portion a and the second inlet tank portion b, and the upper outlet tanks 47 of the thin metal plates 4, 5 and 6, 57 is divided into a first outlet tank part c and a second outlet tank part d.
[0023]
As described above, the refrigerant flows in the evaporator 1 through the following path. That is, the refrigerant is refrigerant inlet pipe 8a → communication passage 15 → first inlet tank portion a of lower inlet tanks 44 and 64 → refrigerant passage 2b of tube 2 → upper inlet tanks 43, 53, 63 → refrigerant passage of tube 2 2b → second inlet tank portion b of lower inlet tanks 44, 64 → communication passage 13 → first outlet tank portion c of upper outlet tank 47, 57 → refrigerant passage 2a of tube 2 → lower outlet tanks 48, 58, It flows in the route of 68 → refrigerant passage 2a of tube 2 → second outlet tank portion d of upper outlet tanks 47 and 57 → communication passage 14 → refrigerant outlet pipe 8b.
[0024]
In this way, by configuring the refrigerant path, the temperature of the evaporator blow-out air of the air flowing in the direction of the arrow A can be made uniform over the entire area of the heat exchange unit 3.
By the way, as described above, the refrigerant flow is U-turned in both the upper and lower outlet tanks 47, 57, 48, 58 and 68 on the leeward side and the upper and lower inlet tanks 43, 53, 63, 44 and 64 on the leeward side. However, in the present invention, the cross-sectional areas of the upper and lower outlet tanks 47, 57, 48, 58 and 68 on the leeward side are the cross-sectional areas of the upper and lower inlet tanks 43, 53, 63, 44 and 64 on the leeward side. Is made smaller. Specifically, in this example, the cross-sectional area of the upper and lower inlet tanks on the leeward side is about 68% of the size of the upper and lower outlet tanks on the leeward side.
[0025]
Therefore, even if the refrigerant flow rate to the evaporator 1 is throttled by the temperature type expansion valve at low load, the upper and lower inlet tanks 43, 53, 63, 44, 64 have small cross-sectional areas. The rate of decrease in the flow velocity is small, and as a result, separation of the gas-liquid two-phase refrigerant liquid and gas in the inlet tank can be suppressed.
That is, by reducing the cross-sectional area of the inlet tanks 43, 53, 63, 44, 64, the flow rate of the refrigerant passing through the inlet tank can be ensured to a certain degree or more. The liquid and gas can be maintained in a mixed state.
[0026]
As a result, the gas-liquid ratio of the refrigerant distributed from the inlet tank to the leeward refrigerant passage 2b can be made uniform, and the cooling capacity of the evaporator 1 can be ensured well even at low loads.
Next, the manufacturing method of the refrigerant evaporator according to the present embodiment will be briefly described. After the evaporator 1 is laminated and temporarily assembled in the state shown in FIGS. 1 and 2, the temporarily assembled state is changed to an appropriate jig. And hold the temporary assembly into the brazing furnace. Next, in this brazing furnace, the temporary assembly is heated to the melting point of the brazing material of the aluminum double-sided clad material, and the joint portions of the respective parts of the evaporator 1 are brazed integrally.
(Other embodiments)
In addition, since the principal part of this invention exists in the setting of the cross-sectional area of an inlet tank part and an outlet tank part, the refrigerant path structure in the heat exchange part 3 is not limited to the example shown in FIG. Of course it is good.
[0027]
For example, in the above embodiment, since the pipe joint 8 having the refrigerant inlet and outlet pipes 8a and 8b is installed at the upper and lower intermediate portions of the right end of the evaporator, the communication passages 14 and 15 are required. It is also possible to directly install the refrigerant inlet and outlet pipes 8a and 8b at the tank portions 9a and 9b of the thin plate 9. In this case, the end plate 10 for forming the communication passages 14 and 15 is unnecessary. .
[0028]
Moreover, in the metal thin plates 4-6 of FIGS. 3-5, by setting the center rib 49, 59, 69 in the center of a metal thin plate width direction, respectively, and setting the width | variety of refrigerant path 2a, 2b, Inner fins (not shown) that are symmetric with respect to the center rib can be disposed in the refrigerant passages 2a and 2b. However, the center rib is shifted to the left and right from the center in the metal sheet width direction. It may be set.
[0029]
Further, instead of providing the inner fins in the refrigerant passages 2a and 2b, ribs or dimples having an appropriate shape are formed in the thin metal plates 4 to 6 along the refrigerant flow direction so as to increase the heat transfer efficiency on the refrigerant side. May be.
[Brief description of the drawings]
1A is a top view of an evaporator showing an embodiment of the present invention, FIG. 1B is a front view of the evaporator, and FIG. 1C is a bottom view of the evaporator.
2A is a left side view of the evaporator of FIG. 1, and FIG. 2B is a right side view of the evaporator.
FIG. 3 is a front view of a thin metal plate for a tube used in the evaporator shown in FIG.
4 is a front view of another thin metal plate for a tube used in the evaporator of FIG. 1. FIG.
FIG. 5 is a front view of still another thin metal sheet for a tube used in the evaporator of FIG. 1;
FIG. 6 is a schematic perspective view showing a refrigerant passage configuration of an evaporator according to an embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Evaporator, 2 ... Tube, 2a ... Refrigerant passage of the windward side,
2b ... leeward refrigerant passage, 3 ... heat exchange part, 4, 5, 6, 9, 11 ... thin metal plate,
43, 44, 53, 63, 64 ... Refrigerant inlet side tank,
47, 48, 57, 58, 68 ... Refrigerant outlet side tank section.

Claims (2)

チューブ（２）内を流れる冷媒と前記チューブ（２）の外部を流れる空気とを熱交換させて、冷媒を蒸発させる熱交換部（３）を有し、
この熱交換部（３）のチューブ（２）を金属薄板（４、５、６）の積層構造により多数個並列形成し、
前記チューブ（２）内には、前記金属薄板（４、５、６）の長手方向と平行に風上側の冷媒通路（２ａ）と風下側の冷媒通路（２ｂ）とを並列に形成し、
前記金属薄板（４、５、６）の長手方向の両端部に、前記チューブ（２）相互の冷媒通路（２ａ、２ｂ）を連通させる冷媒入口側タンク部（４３、４４、５３、６３、６４）と、冷媒出口側タンク部（４７、４８、５７、５８、６８）とをそれぞれ形成し、
前記冷媒入口側タンク部（４３、４４、５３、６３、６４）は、前記金属薄板（４、５、６）の風下側に配置されて前記風下側の冷媒通路（２ｂ）に連通し、
前記冷媒出口側タンク部（４７、４８、５７、５８、６８）は、前記金属薄板（４、５、６）の風上側に配置されて前記風上側の冷媒通路（２ａ）に連通し、
前記多数個のチューブ（２）を形成する前記金属薄板（４、５、６）の大部分は同一形状のものであり、
前記風下側の冷媒通路（２ｂ）は、前記金属薄板（４、５、６）の長手方向両端の前記冷媒入口側タンク部（４３、４４、５３、６３、６４）相互間にて複数、並列に形成され、
前記風上側の冷媒通路（２ａ）は、前記金属薄板（４、５、６）の長手方向の両端部に位置する前記冷媒出口側タンク部（４７、４８、５７、５８、６８）相互間にて複数、並列に形成され、
前記熱交換部（３）の前記金属薄板（４、５、６）の積層方向の一端部に位置する金属薄板（１１）およびこれに接合されるエンドプレート（１２）の間に連通路（１３）を形成し、上下両端の前記冷媒入口側タンク部（４３、４４、５３、６３、６４）と前記冷媒出口側タンク部（４７、４８、５７、５８、６８）とを連通することにより、前記複数の風下側の冷媒通路（２ｂ）を冷媒が並列に流れた後に、前記複数の風上側の冷媒通路（２ａ）を冷媒が並列に流れるようになっており、
前記冷媒入口側タンク部（４３、４４、５３、６３、６４）としての上側入口タンク（４３、５３、６３）と下側入口タンク（４４、６４）との断面積を前記冷媒出口側タンク部（４７、４８、５７、５８、６８）としての上側出口タンク（４７、５７）と下側出口タンク（４８、５８、６８）との断面積より小さくしてあり、
前記熱交換部（３）の前記金属薄板（４、５、６）の積層方向の他端部に位置する金属薄板（９）およびこれに接合されるエンドプレート（１０）の間に２つの連通路（１４、１５）を形成し、前記他端のエンドプレート（１０）に設置された配管ジョイント（８）の冷媒入口パイプ（８ａ）に連通する前記連通路（１５）を前記下側入口タンク（４４、６４）の連通穴（４２）に連通させ、前記配管ジョイント（８）の冷媒出口パイプ（８ｂ）に連通する前記連通路（１４）を前記上側出口タンク（４７、５７）の連通穴（４５）に連通させ、
前記冷媒入口側タンク部（４３、４４、５３、６３、６４）から前記風下側の冷媒通路（２ｂ）に冷媒が流れる経路と、前記冷媒出口側タンク部（４７、４８、５７、５８、６８）から前記風上側の冷媒通路（２ａ）に冷媒が流れる経路とが提供されたことを特徴とする積層型蒸発器。A heat exchange section (3) for heat-exchanging the refrigerant flowing in the tube (2) and the air flowing outside the tube (2) to evaporate the refrigerant;
A large number of tubes (2) of the heat exchange part (3) are formed in parallel by a laminated structure of thin metal plates (4, 5, 6),
In the tube (2), an leeward refrigerant passage (2a) and a leeward refrigerant passage (2b) are formed in parallel with the longitudinal direction of the thin metal plates (4, 5, 6),
Refrigerant inlet side tank portions (43, 44, 53, 63, 64) for allowing the refrigerant passages (2a, 2b) between the tubes (2) to communicate with both longitudinal ends of the thin metal plates (4, 5, 6). ) And the refrigerant outlet side tank part (47, 48, 57, 58, 68), respectively,
The refrigerant inlet side tank portion (43, 44, 53, 63, 64) is disposed on the leeward side of the metal thin plate (4, 5, 6) and communicates with the refrigerant passage (2b) on the leeward side,
The refrigerant outlet side tank portion (47, 48, 57, 58, 68) is disposed on the windward side of the thin metal plate (4, 5, 6) and communicates with the refrigerant passage (2a) on the windward side,
Most of the thin metal plates (4, 5, 6) forming the multiple tubes (2) have the same shape,
A plurality of the leeward refrigerant passages (2b) are arranged in parallel between the refrigerant inlet side tank portions (43, 44, 53, 63, 64) at both longitudinal ends of the metal thin plates (4, 5, 6). Formed into
The windward side refrigerant passage (2a) is provided between the refrigerant outlet side tank portions (47, 48, 57, 58, 68) located at both ends in the longitudinal direction of the metal thin plates (4, 5, 6). Are formed in parallel,
A communication path (13) between the metal thin plate (11) located at one end of the heat exchanger (3) in the stacking direction of the metal thin plates (4, 5, 6) and the end plate (12) joined thereto. ) And communicating the refrigerant inlet side tank portions (43, 44, 53, 63, 64) at the upper and lower ends with the refrigerant outlet side tank portions (47, 48, 57, 58, 68), After the refrigerant flows in parallel through the plurality of leeward refrigerant passages (2b), the refrigerant flows in parallel through the plurality of leeward refrigerant passages (2a),
The sectional area of the upper inlet tank (43, 53, 63) and the lower inlet tank (44, 64) as the refrigerant inlet side tank part (43, 44, 53, 63, 64) is defined as the refrigerant outlet side tank part. (47, 48, 57, 58, 68) smaller than the cross-sectional area of the upper outlet tank (47, 57) and the lower outlet tank (48, 58, 68) ,
Between the metal thin plate (9) located at the other end in the stacking direction of the metal thin plates (4, 5, 6) of the heat exchanging portion (3), and two end plates (10) joined thereto, A passage (14, 15) is formed, and the communication passage (15) communicating with the refrigerant inlet pipe (8a) of the pipe joint (8) installed on the end plate (10) at the other end is connected to the lower inlet tank. The communication passage (14) connected to the communication hole (42) of (44, 64) and the refrigerant outlet pipe (8b) of the pipe joint (8) is connected to the communication hole of the upper outlet tank (47, 57). Communicate with (45),
A path through which the refrigerant flows from the refrigerant inlet side tank part (43, 44, 53, 63, 64) to the leeward side refrigerant path (2b), and the refrigerant outlet side tank part (47, 48, 57, 58, 68). ) To the above-mentioned refrigerant passage (2a) on the windward side . 前記風上側の冷媒通路（２ａ）および前記風下側の冷媒通路（２ｂ）の通路幅は前記金属薄板（４、５、６）の長手方向全域で一定であることを特徴とする請求項１に記載の積層型蒸発器。  2. The passage width of the leeward refrigerant passage (2 a) and the leeward refrigerant passage (2 b) is constant throughout the longitudinal direction of the thin metal plates (4, 5, 6). The stacked evaporator as described.
JP13545896A 1996-05-29 1996-05-29 Stacked evaporator Expired - Fee Related JP3863217B2 (en)

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