JPWO2003040640A1 - Heat exchanger and heat exchanger tube - Google Patents

Heat exchanger and heat exchanger tube Download PDF

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JPWO2003040640A1
JPWO2003040640A1 JP2003542852A JP2003542852A JPWO2003040640A1 JP WO2003040640 A1 JPWO2003040640 A1 JP WO2003040640A1 JP 2003542852 A JP2003542852 A JP 2003542852A JP 2003542852 A JP2003542852 A JP 2003542852A JP WO2003040640 A1 JPWO2003040640 A1 JP WO2003040640A1
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tube
heat exchanger
tank
core
refrigerant
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高野　明彦
明彦 高野
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Valeo Thermal Systems Japan Corp
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Zexel Valeo Climate Control Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
    • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
    • F28F9/182—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding the heat-exchange conduits having ends with a particular shape, e.g. deformed; the heat-exchange conduits or end plates having supplementary joining means, e.g. abutments
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators

Landscapes

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

Abstract

冷媒を流通する偏平状のチューブ３０１及び波型のフィン３０２を積層してなるコア３００ａと、チューブの端部を挿入するスロットを設けたタンク３１０とを備えた熱交換器において、コアは、チューブの偏平状の面が前記通風方向と平行になるように構成し、チューブは、その端部３０１ａの幅方向が通風方向に対して９０°に捩じれた構成の熱交換器、及びそのチューブである。また、超臨界冷凍サイクルの熱交換器に関し、通風方向に重ねられた複数のコア３００ａ，３００ｂの一方の側部において、各タンク３１０ａ，３１０ｃの位置は通風方向と直交する方向にずらすとともに、冷媒の入口部３２０及び出口部３３０は通風方向の風上側又は風下側に揃えて向けた。In a heat exchanger including a core 300a formed by laminating a flat tube 301 and a corrugated fin 302 through which a refrigerant flows, and a tank 310 provided with a slot for inserting an end of the tube, the core is a tube. The tube is a heat exchanger having a configuration in which the width direction of the end portion 301a is twisted at 90 ° with respect to the ventilation direction, and the tube. . Further, regarding the heat exchanger of the supercritical refrigeration cycle, the positions of the tanks 310a and 310c are shifted in the direction perpendicular to the ventilation direction on one side of the plurality of cores 300a and 300b stacked in the ventilation direction, and the refrigerant The inlet portion 320 and the outlet portion 330 are oriented to the upwind side or downwind side in the ventilation direction.

Description

技術分野
本発明は、冷媒を流通する偏平状のチューブ及び波型のフィンを積層してなるコアと、チューブの端部を挿入するスロットを設けたタンクとを備え、コアに対して通風がなされるとともにコアに伝わる熱にて冷媒の熱交換を行う熱交換器に関する。
背景技術
冷凍サイクルに用いられる放熱器やエバポレータ等の熱交換器としては、複数の偏平状のチューブと複数の波型のフィンとを交互に積層してコアをなすとともに、チューブの端部をパイプ状のタンクに挿入してなるものが知られている。チューブの偏平状の面は、通風方向と平行となるように構成されている。冷媒は、タンクから内部に取り入れられて、コアに伝わる熱によって熱交換をしつつチューブを流通した後、タンクから外部に排出される。
また、冷凍サイクルの冷媒としては、これまで代替フロンを含めフロン系の冷媒が広く採用されてきたところ、近年では地球環境に配慮して、これをＣＯ２に変更する傾向にある。ＣＯ２を冷媒とする冷凍サイクルは、フロン系の冷媒を用いた冷凍サイクルと比較すると、内部の圧力が極めて高く、とりわけ高圧側の圧力は、気温等の使用条件によって、冷媒の臨界点を超える訳である。臨界点とは、気層と液層が共存する状態の高圧側の限界（つまり高温側の限界）であり、蒸気圧曲線の一方での終点である。臨界点での圧力、温度、密度は、それぞれ臨界圧力、臨界温度、臨界密度となる。特に、冷凍サイクルの高温熱源部である放熱器においては、圧力が冷媒の臨界点を上まわると、冷媒が凝縮することはない。
ところで、冷凍サイクルの熱交換器については、冷媒の熱交換効率の向上、小型化、軽量化、製造の容易化、及び設置スペースの節約等が重要な課題とされる。特に、高圧側の圧力が冷媒の臨界点を超える超臨界冷凍サイクルは、フロン系の冷媒を用いる冷凍サイクルと比較すると、非常に高い耐圧強度を要し、これに用いる熱交換器については、耐圧性の確保とともに、より一層の合理化が必要とされている。
例えば、超臨界冷凍サイクルの熱交換器は、耐圧性を確保する点で、チューブやタンクの容積を小さくするとともに、それらの肉厚を厚くする必要がある。ここで、タンクの肉厚を厚くすると、タンクに挿入するチューブの幅をタンクの外径に対して極端に小さく設定しなければならない不都合が生じる。つまり、肉厚が厚いタンクは、外径と内径の差が大きく、長手方向に亘り一定幅のチューブの端部をタンクに挿入するには、タンクの外径に対するチューブの幅が著しく小さくなり、延いては、熱交換器の設置スペースに対し、コアの幅が満足に得られなくなるという問題がある。
本発明は、こうした事情に鑑みてなされたものであり、その目的は、より合理的に構成された熱交換器を提供することである。
発明の開示
本願第１請求項に記載した発明は、冷媒の熱交換を行う熱交換器に用いられ、前記冷媒を流通する偏平状のチューブにおいて、前記熱交換器は、当該チューブ及び波型のフィンを積層してなるコアと、当該チューブの端部を挿入するスロットを設けたタンクとを備え、前記コアに対して通風がなされるとともに前記コアに伝わる熱にて前記冷媒の熱交換を行うものであり、前記コアは、当該チューブの偏平状の面が前記通風方向と平行になるように構成し、当該チューブは、その端部の幅方向が前記通風方向に対して９０°に捩じれた構成の熱交換器用チューブである。本発明の熱交換器用チューブによると、合理的に構成された熱交換器が得られる。
すなわち本発明によれば、チューブの幅は、タンクの内径に拘束されることがないので、これを適宜に設定できる利点がある。また、タンクの内部の冷媒流路に対してチューブの偏平状の面が対峙しないので、冷媒流路に大きな流路抵抗を生じる事態を回避することができ、圧力欠損を小さくすることも可能である。更に、チューブ端部の幅方向の捩じれ角度が９０°であれば、スロットはタンクの長手方向に沿って設けられ、その加工が容易となる利点もある。つまり、チューブ端部の幅方向の捩じれ角度を９０°未満とし、タンクの長手方向に対してスロットを斜めに設ける場合は、タンクを加工する点でやや困難を伴うが、本発明によればそのような不都合が回避される。また、スロットを斜めに設ける場合と比較すると、チューブの組み付けも容易である。
本願第２請求項に記載した発明は、請求項１において、前記熱交換器は、前記冷媒を循環する冷凍サイクルに用いられ、前記冷凍サイクルは、高圧側の圧力が前記冷媒の臨界点を超える構成の熱交換器用チューブである。
本発明の熱交換器用チューブは、タンクのスロットに挿入する端部の幅方向が９０°捩じれたものであり、かかる構成は、タンクの容積が比較的小さい超臨界冷凍サイクルの熱交換器において極めて有効である。すなわち当該チューブは、超臨界冷凍サイクルの熱交換器に用いるチューブとして、極めて顕著な効果を達成したものである。
本願第３請求項に記載した発明は、冷媒を流通する偏平状のチューブ及び波型のフィンを積層してなるコアと、前記チューブの端部を挿入するスロットを設けたタンクとを備え、前記コアに対して通風がなされるとともに前記コアに伝わる熱にて前記冷媒の熱交換を行う熱交換器において、前記コアは、前記チューブの偏平状の面が前記通風方向と平行になるように構成し、前記チューブは、その端部の幅方向が前記通風方向に対して９０°に捩じれた構成の熱交換器である。このような構成によると、合理的に構成された熱交換器が得られる。
すなわち本発明によれば、チューブの幅は、タンクの内径に拘束されることがないので、これを適宜に設定できる利点がある。また、タンクの内部の冷媒流路に対してチューブの偏平状の面が対峙しないので、冷媒流路に大きな流路抵抗を生じる事態を回避することができ、圧力欠損を小さくすることも可能である。更に、チューブ端部の幅方向の捩じれ角度が９０°であれば、スロットはタンクの長手方向に沿って設けられ、その加工が容易となる利点もある。つまり、チューブ端部の幅方向の捩じれ角度を９０°未満とし、タンクの長手方向に対してスロットを斜めに設ける場合は、タンクを加工する点でやや困難を伴うが、本発明によればそのような不都合が回避される。また、スロットを斜めに設ける場合と比較すると、チューブの組み付けも容易である。
本願第４請求項に記載した発明は、請求項３において、前記タンクの内径は、前記チューブの幅よりも小さい構成の熱交換器である。このような構成によると、一層合理的に構成された熱交換器が得られる。
すなわち本発明によれば、タンクの内径よりも大きな幅のチューブを採用することが可能であり、耐圧性能並びに熱交換性能を確保するうえで有利となる利点がある。
本願第５請求項に記載した発明は、請求項３又は４において、複数の前記スロットを前記タンクの長手方向に沿って列設するとともに、前記チューブの幅を前記チューブの配置間隔（つまり積層間隔）よりも小さく設定した構成の熱交換器である。このような構成によると、一層合理的に構成された熱交換器が得られる。
すなわちチューブの配置間隔よりもチューブの幅を小さく設定すれば、９０°捩じったチューブの端部をスロットに挿入するも、チューブ同士が干渉することはない。
本願第６請求項に記載した発明は、請求項５において、前記チューブの配置間隔をＰ、前記チューブの幅をＴとするとき、これらは、Ｐ＝（６〜１２）ｍｍ、Ｔ＝Ｐ・（０．９５〜０．８０）、の関係にある構成の熱交換器である。チューブの配置間隔Ｐ並びにチューブ幅Ｔの関係をこのように設定すれば、熱交換器は一層合理的に構成される。
すなわちかかる関係は、チューブの配置間隔Ｐが６ｍｍから１２ｍｍの間において、（Ｔ／Ｐ）が０．９５よりも小さく且つ０．８よりも大きいことを意味し、相対的にチューブの配置間隔Ｐが大きくなると熱交換効率が低下することと、配置間隔Ｐが小さくなるとスロットの間隔が小さくなるのでタンクの強度が低下すると、との利害損失の合理的な線引きを数値化して表したものである。
本願第７請求項に記載した発明は、請求項３乃至６のいずれかにおいて、当該熱交換器は、前記通風方向に複数の前記コアを重ねてなる構成の熱交換器である。このような構成によると、一層合理的に構成された熱交換器が得られる。
すなわち複数のコアを重ねることによれば、熱交換効率を一層向上することが可能であり、ついては、熱交換器の設置スペースをより有効に利用することが可能となる。
本願第８請求項に記載した発明は、請求項７において、前記コアとしては、前記通風方向に重ねられた第１コア及び第２コアを備え、前記タンクとしては、前記第１コアのチューブの一方の端部を挿入する第１タンクと、前記第１コアのチューブの他方の端部及び前記第２コアのチューブの一方の端部を挿入する第２タンクと、前記第２コアのチューブの他方の端部を挿入する第３タンクとを備え、
前記第１タンクには前記冷媒の入口部を設け、前記第３タンクには前記冷媒の出口部を設けた構成の熱交換器である。
このような構成によると、一層合理的に構成された熱交換器が得られる。
すなわち本発明は、通風方向に第１コア及び第２コアを重ねるとともに、第１コア及び第２コアにおける冷媒の流れを対向流としたカウンターフロータイプの熱交換器であり、冷媒の熱交換効率が向上されるという利点がある。更に、第１コアのチューブの端部及び第２コアのチューブの端部を共に第２タンクに挿入することによれば、第１コア及び第２コアの連結に関わる構造の簡素化が達成され、その製造性を向上することが可能である。また、熱交換器の設置スペースを節約する点でも有利である。
本願第９請求項に記載した発明は、請求項８において、前記第１タンク及び前記第３タンクの位置は前記通風方向と直交する方向にずらすとともに、前記入口部及び前記出口部は前記通風方向の風上側又は風下側に揃えて向けた構成の熱交換器である。このような構成によると、一層合理的に構成された熱交換器が得られる。
すなわち本発明は、第１タンク及び第３タンクの位置を通風方向と直交する方向にずらすことにより、第１タンク及び第３タンクの径を所要の大きさに設定するとともに、それらが互いに干渉するのを回避する構成となっている。かかる構成は、タンクの外径と内径の差が大きい超臨界冷凍サイクルの熱交換器において極めて有効である。また、このように第１タンク及び第３タンクの位置をずらすことによれば、第１タンクの入口部と第３タンクの出口部とを通風方向の風上側又は風下側に揃えて向けることが可能となり、冷凍サイクルのレイアウトについて、配管構造の簡素化が達成される。
本願第１０請求項に記載した発明は、請求項３乃至９のいずれかにおいて、前記フィンの幅は、前記チューブの幅よりも大きく設定した構成の熱交換器である。
すなわちチューブの幅よりも大きい幅のフィンを採用すれば、熱交換性能の向上が達成される。また、チューブ及びフィンを積層する際、フィンが多少変形することを考慮すれば、チューブがフィンに保持されることにより、これらの位置ずれは防止される。ついては、これらの組み付け性が向上されるという利点もある。
本願第１１請求項に記載した発明は、請求項３乃至１０のいずれかにおいて、前記タンクは、筒状を呈するものであり、半筒状（つまり一部を欠いた不完全な筒状）の第１部材と、前記スロットが列設された第２部材と、その端部を閉鎖する閉鎖部材とを組み付けてなる構成の熱交換器である。
すなわちタンクは、半筒状の第１部材とスロットが列設された第２部材とを組み付けて筒状となすとともに、その端部を閉鎖部材にて閉鎖することにより構成される。このような構成によると、タンクは合理的に構成される。
本願第１２請求項に記載した発明は、請求項１１において、前記タンクは、前記第１部材と、複数の前記第２部材と、複数の前記第２部材を互いに連結するスペーサと、前記閉鎖部材とを組み付けてなる構成の熱交換器である。
すなわち１つのタンクに複数のスロット列を設ける場合は、スペーサを用いて複数の第２部材を互いに連結するとよい。
本願第１３請求項に記載した発明は、請求項１１又は１２において、前記閉鎖部材には、前記第２部材を嵌合する嵌合部を設けた構成の熱交換器である。
すなわち閉鎖部材の嵌合部に第２部材を嵌合すれば、閉鎖部材及び第２部材をより正確且つ堅固に組み付けることが可能となる。
本願第１４請求項に記載した発明は、請求項１１乃至１３のいずれかにおいて、前記第１部材にはカシメ部を設け、前記第１部材及び前記第２部材は前記カシメ部をカシメることにより固定した構成の熱交換器である。
すなわちカシメ部をカシメて第１部材及び第２部材を固定すれば、それらをより正確且つ堅固に組み付けることが可能となる。
本願第１５請求項に記載した発明は、請求項１４において、前記カシメ部をカシメることにより、前記第１部材、前記第２部材、及び前記閉鎖部材を固定した構成の熱交換器である。
すなわちカシメ部によれば、第１部材及び第２部材とともに閉鎖部材を固定することも可能である。このような構成によると、第１部材、第２部材、及び閉鎖部材は効率よく組み付けられる。
本願第１６請求項に記載した発明は、請求項１１乃至１５のいずれかにおいて、前記チューブの端部を前記スロットに挿入した後に前記第１部材と前記第２部材とを組み付けた構成の熱交換器である。
すなわちチューブとタンクとの組み付けは、第２部材のスロットにチューブの端部を挿入し、その第２部材と第１部材とを組み付けて行われる。
本願第１７請求項に記載した発明は、請求項１１乃至１５のいずれかにおいて、前記第１部材と前記第２部材とを組み付けた後に前記チューブの端部を前記スロットに挿入した構成の熱交換器である。
すなわちチューブとタンクとの組み付けは、第１部材と第２部材とを組み付け、その第２部材のスロットにチューブの端部を挿入して行われる。
本願第１８請求項に記載した発明は、請求項３乃至１７のいずれかにおいて、前記チューブの端部は、前記チューブの長手方向に対して屈曲した構成の熱交換器である。
すなわちチューブの端部をチューブの長手方向に対して屈曲することによれば、タンク及びチューブのレイアウトについて、設計の自由度が向上するという利点がある。例えば、通風方向に複数のコアを重ねる場合は、かかる構成を採用してコア同士の間隔を小さく設定することが可能となる。つまり、タンクの形状に拘らずコア全体の厚さを薄型化することが可能となる。
本願第１９請求項に記載した発明は、請求項１８において、前記チューブの端部は、前記スロットに挿入する前に屈曲した構成の熱交換器である。
すなわちチューブは、その端部をチューブの長手方向に対して予め所定の角度に屈曲し、屈曲した端部をスロットに挿入する。このような構成によれば、チューブとタンクとを効率よく組み付けることが可能となる。
本願第２０請求項に記載した発明は、請求項１８において、前記チューブの端部は、前記スロットに挿入した後に屈曲した構成の熱交換器である。
すなわちチューブは、屈曲前の端部をスロットに挿入し、かかる状態からその端部を所定の角度に屈曲する。このような構成によれば、チューブとタンクとを効率よく組み付けることが可能となる。
本願第２１請求項に記載した発明は、請求項３乃至２０のいずれかにおいて、当該熱交換器は、前記冷媒を循環する冷凍サイクルに用いられ、前記冷凍サイクルは、高圧側の圧力が前記冷媒の臨界点を超える構成の熱交換器である。本発明の熱交換器用は、タンクのスロットに挿入する端部の幅方向が９０°捩じれたチューブを用いてなるものであり、かかる構成は、タンクの容積が比較的小さい超臨界冷凍サイクルの熱交換器において極めて有効である。すなわち当該熱交換器は、超臨界冷凍サイクルの熱交換器として、極めて顕著な効果を達成したものである。
本願第２２請求項に記載した発明は、高圧側の圧力が冷媒の臨界点を超える冷凍サイクルの熱交換器であり、前記冷媒を流通する偏平状のチューブ及び波型のフィンを積層してなるコアと、前記チューブの端部を挿入するスロットを設けたタンクとを備え、前記コアに対して通風がなされるとともに前記コアに伝わる熱にて前記冷媒の熱交換を行う熱交換器において、前記コアとしては、前記通風方向に重ねられた第１コア及び第２コアを備え、前記第１コア及び前記第２コアの一方の側部において、前記第１コアのチューブの端部を挿入する前記タンクには前記冷媒の入口部を設け、且つ前記第２コアのチューブの端部を挿入する前記タンクには前記冷媒の出口部を設け、これらのタンクの位置は前記通風方向と直交する方向にずらすとともに、前記入口部及び前記出口部は前記通風方向の風上側又は風下側に揃えて向けた構成の熱交換器である。このような構成によると、合理的に構成された熱交換器が得られる。
すなわち本発明は、第１コア及び第２コアの一方の側部における２つのタンクの位置を通風方向と直交する方向にずらすことにより、各タンクの径を所要の大きさに設定するとともに、それらが互いに干渉するのを回避する構成となっている。かかる構成は、タンクの外径と内径の差が大きい超臨界冷凍サイクルの熱交換器において極めて有効である。また、このようにタンクの位置をずらすことによれば、各タンクの入口部と出口部とを通風方向の風上側又は風下側に揃えて向けることが可能となり、冷凍サイクルのレイアウトについて、配管構造の簡素化が達成される。
発明を実施するための最良の形態
以下に、本発明の具体例を図面に基いて詳細に説明する。図１に示す冷凍サイクル１は、自動車に搭載される車内空調用の冷凍サイクルであり、冷媒を圧縮するコンプレッサ２００と、コンプレッサ２００で圧縮された冷媒を冷却する放熱器３００と、放熱器３００で冷却された冷媒を減圧して膨張する膨張弁４００と、膨張弁４００で減圧された冷媒を蒸発するエバポレータ５００と、エバポレータ５００から流出する冷媒を気層と液層に分離して気層の冷媒をコンプレッサ２００へ送るアキュムレータ６００と、高圧側の冷媒と低圧側の冷媒とを熱交換することによってサイクルの効率を向上する内部熱交換器７００とを備えたものである。冷媒としてはＣＯ２を用いており、当該超臨界冷凍サイクル１の高圧側の圧力は、気温等の使用条件により、冷媒の臨界点を上まわる。図１中の矢印は冷媒の循環方向を示す。
図２及び図３に示すように、本例の熱交換器たる放熱器３００は、偏平状のチューブ３０１と、ルーバーを設けた波型のフィン３０２とを交互に積層してなるコア３００ａと、チューブ３０１の端部３０１ａを挿入するタンク３１０とを備え、チューブ３０１を流通する冷媒がコア３００ａに伝わる熱にて熱交換を行う構成を備えている。コア３００ａの上下側部には、補強部材たるサイドプレート３０３を設けており、各サイドプレート３０３の両端部は、それぞれ各タンク３１０に支持されている。各タンク３１０はそれぞれ、両端を閉鎖部材３１２にて閉鎖した筒状を呈する部材である。
また、一方のタンク３１０には冷媒を導入する入口部３２０を設けており、他方のタンク３１０には冷媒を排出する出口部３３０を設けている。これらの入口部３２０及び出口部３３０は、タンク３１０の要所に孔部を設けるとともに、その孔部に外部の配管を接続する継手を設けて構成している。
冷媒は、入口部３２０から一方のタンク３１０の内部に導入されて、コア３００ａに伝わる熱によって熱交換をしつつチューブ３０１を流通した後に、他方のタンク３１０の出口部３３０から外部に排出される。
本例ではＣＯ２を冷媒として用いており、この放熱器３００は、非常に高い耐圧強度を要するものである。故にタンク３１０については、肉厚を厚くするとともにその容積を小さくすることにより、所要の耐圧強度を確保する。特にタンク３１０の内径は、チューブ３０１の幅よりも小さいものとなっている。
各チューブ３０１は、一方の端部３０１ａを一方のタンク３１０に挿入され、且つ、他方の端部３０１ａを他方のタンク３１０に挿入されている。各タンク３１０には、その長手方向に沿って、チューブ３０１の端部３０１ａを挿入する複数のスロット３１１が列設されている。
そして、かかる放熱器３００は、チューブ３０１、フィン３２０、タンク３１０、入口部３２０、及び出口部３３０を一体に組み付けた後、その組み付け体を炉中にてろう付けして製造される。尚、このようなろう付けに関し、各部材の要所には、予めろう材及びフラックスが設けられる。
本例のコア３００ａは、チューブ３０１の偏平状の面が通風方向と平行になるように構成されている。また、本例のチューブ３０１は、その両端部３０１ａの幅方向が通風方向に対してそれぞれ９０°に捩じれたものである。この例では、タンク３１０を上下方向に立設し、チューブ３０１の両端部３０１ａはそれぞれ、偏平状の面が上下方向に向くように構成されている。図４の（ａ）には、チューブ３０１の上面を示し、（ｂ）はチューブ３０１の正面を示す。また、図５には、チューブ３０１の断面を示す。これらの図に示すチューブ３０１は、複数の流路３０１ｂを有するアルミ合金製の押出し成形チューブである。本例の場合、チューブ３０１の端部３０１ａは、押出し成形チューブを所定の長さに切断した後に、チューブ３０１の端部３０１ａとその近傍を一対のジグでそれぞれ挟むとともに、各ジグを互いに相対移動することによって加工されている。
このように、チューブ３０１の端部３０１ａを９０°捩じってタンク３１０のスロット３１１に挿入すれば、タンク３１０内の冷媒流路に対しチューブ３０１の偏平状の面が対峙しないので、冷媒流路に大きな流路抵抗を生じることはない。従って、圧力欠損を小さくすることができる。また、入口部３２０や出口部３３０の配置の自由度が増すという利点もある。すなわち、入口部３２０や出口部３３０はタンク３１０の内部にある程度突出しているものの、その取り付け角度は、適宜に設定することが可能となる。例えば図６に示すように、入口部３２０や出口部３３０の取り付け角度は、チューブ３０１の挿入方向に対して斜めに設定することも可能である。尚、タンク３１０に挿入される入口部３２０や出口部３３０の先端部は、テーパ状に加工されている。
また本例においては、チューブ３０１の配置間隔Ｐよりもチューブ３０１の幅Ｔを小さく設定しており、配置間隔Ｐと幅Ｔについては、Ｐ＝（６〜１２）ｍｍ、Ｔ＝Ｐ・（０．９５〜０．８０）、の関係が成立する。尚、スロットの幅δＴは、チューブの幅Ｔよりも僅かに大きいものとなっている。このような構成によれば、冷媒の熱交換効率及びタンク３１０の強度は十分に確保することができる。
更に本例の場合、フィン３０２の幅は、チューブ３０１の幅よりもやや大きく設定している。すなわち、チューブ３０１の幅よりも大きい幅のフィン３０２を採用すれば、熱交換面積が拡大し、熱交換性能の向上が達成される。また、チューブ３０１及びフィン３０２を積層する際、フィン３０２が多少変形することを考慮すれば、チューブ３０１がフィン３０２に保持されることにより、これらの位置ずれは防止される。ついては、これらの組み付け性は向上される。
次に、本発明の第２具体例を図７に基づいて説明する。同図に示すように、本例の放熱器３００は、通風方向に第１コア３００ａ及び第２コア３００ｂを重ねてなるものである。第１コア３００ａ及び第２コア３００ｂの両側部にはそれぞれタンク３１０が設けられている。そして、第１コア３００ａ及び第２コア３００ｂの一方の側部において、第１コア３００ａのチューブ３０１の端部３０１ａを挿入するタンク３１０には冷媒の入口部３２０を設け、且つ第２コア３００ｂのチューブ３０１の端部３０１ａを挿入するタンク３１０には冷媒の出口部３３０を設けている。また、第１コア３００ａ及び第２コア３００ｂの他方の側部においては、第１コア３００ａのチューブ３０１の端部３０１ａを挿入するタンク３１０と、第２コア３００ｂのチューブ３０１の端部３０１ａを挿入するタンク３１０とが連通されている。冷媒は、第１コア３００ａ及び第２コア３００ｂを順次に流通する。つまり本例の放熱器３００は、第１コア３００ａ及び第２コア３００ｂにおける冷媒の流れを対向流としたカウンターフロータイプの熱交換器である。
このように、複数のコア３００ａ，３００ｂを通風方向に重ねることによれば、熱交換効率を一層向上することができる。
次に、本発明の第３具体例を説明する。図８乃至図１０に示すように、本例の熱交換器たる放熱器３００は、冷媒を流通する偏平状のチューブ３０１及び波型のフィン３０２を積層してなる第１コア３００ａ及び第２コア３００ｂと、各チューブ３０１の端部３０１ａがそれぞれ挿入接続されたパイプ状の第１タンク３１０ａ、第２タンク３１０ｂ、及び第３タンク３１０ｃと、第１タンク３１０ａに設けられたパイプ状の冷媒の入口部３２０と、第３タンク３１０ｃに設けられたパイプ状の冷媒の出口部３３０とを備えている。コンプレッサ２００から送られる冷媒は入口部３２０から流入し、出口部３３０から流出した冷媒は膨張弁４００へと送られる。尚、これらの図中の矢印は放熱器３００における冷媒の流通方向を示しており、白抜き矢印は第１コア３００ａ及び第２コア３００ｂに対する通風方向を示している。
第１タンク３１０ａには、第１コア３００ａのチューブ３０１の一方の端部３０１ａが挿入されている。第２タンク３１０ｂには、第１コア３００ａのチューブ３０１の他方の端部３０１ａ及び第２コア３００ｂのチューブ３０１の一方の端部３０１ａが挿入されている。また、第３タンク３１０ｃには、第２コア３００ｂのチューブ３０１の他方の端部３０１ａが挿入されている。
そして、第１コア３００ａ及び第２コア３００ｂに対しては、図示を省略したファンによって通風がなされ、冷媒は、第１コア３００ａ及び第２コア３００ｂに伝わる熱にて熱交換を行う。また、第１コア３００ａ及び第２コア３００ｂは、通風方向に重ねられるとともに、チューブ３０１の偏平状の面が通風方向と平行になるように構成されており、通風は、第２コア３００ｂ側から施される。つまり本例の放熱器３００は、第１コア３００ａ及び第２コア３００ｂにおける冷媒の流れを対向流としたカウンターフロータイプの熱交換器である。
図１１に示すように、本例のチューブ３０１もまた、前述した具体例と同様のアルミ合金製の押出し成形チューブである。また、その両端部３０１ａの幅方向は、通風方向に対してそれぞれ９０°に捩じれている。チューブ３０１の端部３０１ａは、押出し成形チューブを所定の長さに切断した後に、かかる端部３０１ａとその近傍を一対のジグでそれぞれ挟むとともに、各ジグを互いに相対移動することによって加工されている。
図１２に示すように、第１タンク３１０ａは、その長手方向に沿って各チューブ３０１の端部３０１ａをそれぞれ挿入する複数のスロット３１１が設けられた押出し成形パイプ又は引抜き成形パイプである。スロット３１１は、プレス加工又は切削加工にて形成され、第１タンク３１０ａの長手方向に沿って１列に列設されている。また、第３タンク３１０ｃは、第１タンク３１０ａと同様の部材を用いて構成されている。尚、第１タンク３１０ａの要所には入口部３２０を接続する孔部が設けられ、第３タンク３１０ｃの要所には出口部３３０を接続する孔部が設けられる。
図１３に示すように、第２タンク３１０ｂもまた、その長手方向に沿って各チューブ３０１の端部３０１ａをそれぞれ挿入する複数のスロット３１１が設けられた押出し成形パイプ又は引抜き成形パイプである。スロット３１１は、第２タンク３１０ｂの長手方向に沿って２列に列設されている。つまり、一方の列は第１コア３００ａのチューブ３０１に対応し、他方の列は第２コア３００ｂのチューブ３０１に対応する。更に、この第２タンク３１０ｂは、第１タンク３１０ａや第３タンク３１０ｃと比較すると、その断面積が比較的大きいものであり、故に肉厚もある程度厚く設定されている。
尚、図１４又は図１５に示すように、第２タンク３１０に挿入するチューブ３０１の端部３０１ａは、チューブ３０１の長手方向に対して所定の角度に屈曲されており、第２タンク３１０ｂに対しては、その中心に向って挿入される。図１４に示すチューブ３０１は、端部３０１ａを捩じりつつその角度を設定したものであり、図１５に示すチューブ３０１は、端部３０１ａを一旦捩じった後にこれを所定の角度に屈曲したものである。チューブ３０１の端部３０１ａは、スロット３１１に挿入する前に屈曲している。このような構成によると、冷媒の流れを良好に確保することが可能である。或いは、図１６に示すように、第１コア３００ａ及び第２コア３００ｂのチューブ３０１の端部３０１ａが第２タンク３１０ｂに対して互いに平行に挿入されるように構成すれば、それらの組み付け性を向上することが可能である。
そして、かかる放熱器３００は、チューブ３０１、フィン３２０、第１タンク３１０ａ、第２タンク３１０ｂ、第３タンク３１０ｃ、入口部３２０、及び出口部３３０を一体に組み付けた後、その組み付け体を炉中にてろう付けして製造される。尚、このようなろう付けに関し、各部材の要所には、予めろう材及びフラックスが設けられる。
このように本例の放熱器３００は、超臨界状態となる冷媒に応じて所要の耐圧性を確保するとともに、冷媒の熱交換効率の向上、小型化、軽量化、製造の容易化、及び設置スペースの節約等について合理化を達成したものであり、自動車に搭載される超臨界冷凍サイクル１の熱交換器として、極めて好適に利用することができる。
次に、本発明の第４具体例を図１７及び図１８に基いて説明する。図１７に示すように、本例の放熱器３００は、自動車のラジエータ８００の風上に配置されたものであり、第１コア３００ａ及び第２コア３００ｂの一方の側部において、第１タンク３１０ａ及び第３タンク３１０ｃの位置を通風方向と直交する方向にずらすとともに、入口部３２０及び出口部３３０を通風方向の風下側に揃えて向けたものである。第１コア３００ａのチューブ３０１は、第２コア３００ｂのチューブ３０１よりもある程度短く設定されている。その他の構成は前述した具体例と同様である。
本例によれば、放熱器３００は一層合理的に構成することができ、延いては自動車における冷凍サイクル１のレイアウトについて、配管構造の簡素化を達成することができる。特に高圧の冷媒を流通するパイプ状の入口部３２０や出口部３３０、並びに入口部３０２や出口部３３０に接続する配管等は、肉厚となるため屈曲成形するのは非常に不利であるところ、本例によれば、それらの形状が比較的単純となる利点があり、それらの加工の省力化に貢献することができる。
尚、図１８に示すように、第１タンク３１０ａ及び第３タンク３１０ｃの位置関係を反転すれば、入口部３２０及び出口部３３０を通風方向の風上側に揃えて向けることも可能である。この場合、第２コア３００ｂのチューブ３０１は、第１コア３００ａのチューブ３０１よりもある程度短く設定される。
次に、本発明の第５具体例を図１９乃至図２４に基づいて説明する。図１９及び図２４に示すように、本例の第１タンク３１０ａ又は第３タンク３１０ｃは、筒状を呈するものであり、半筒状の第１部材３１３と、スロット３１１が１列に列設された第２部材３１４と、その端部を閉鎖する閉鎖部材３１１とを組み付けて構成されている。第１部材３１４の断面は、略Ｃ字状又はＵ字状となっている。
また、第１部材３１３にはカシメ部３１３ａを設けており、第１部材３１３、第２部材３１４、及び閉鎖部材３１２は、カシメ部３１３ａをカシメることにより固定する。チューブ３０１と第１タンク３１０ａ又は第３タンク３１０ｃとの組み付けは、第１部材３１３、第２部材３１４、及び閉鎖部材３１２を組み付けた後に、チューブ３０１の端部３０１ａをスロット３１１に挿入して行われる（図２０参照）。又は、チューブ３０１の端部３０１ａをスロット３１１に挿入した後に、第１部材３１３、第２部材３１４、及び閉鎖部材３１２を組み付けて行われる（図２１参照）。
閉鎖部材３１２は、第１部材３１３の内周面に保持されるとともに第２部材３１４の端面が突き当てられる所定の形状のプレートである。尚、その他の基本構成は前述した具体例と同様である。
本例によれば、タンクは一層合理的に構成することができる。
次に、本発明の第６具体例を図２５に基づいて説明する。本例の第２タンク３１０ｂもまた、第５具体例の第１タンク３１０ａ又は第３タンク３１０ｃと同様に、半筒状の第１部材３１３と、スロット３１１が列設された第２部材３１４と、その端部を閉鎖する閉鎖部材３１１とを組み付けて構成したものである。特に第２部材３１４は、スロット３１１が２列に列設されたものであり、スロット３１１の一方の列には第１コア３００ａのチューブ３０１の一方の端部３０１ａが挿入され、他方の列には第２コア３００ｂのチューブ３０１の一方の端部３０１ａが挿入されている。尚、その他の基本構成は、前述した具体例と同様である。
このように、第２タンク３１０ｂは、複数のスロット列を設けた第２部材３１４を用いて構成することも可能である。
次に、本発明の第７具体例を図２６に基づいて説明する。本例の第２タンク３１０ｂは、複数の第２部材３１４と、複数の第２部材を互いに連結するスペーサ３１５を用いてなるものである。そして、一方の第２部材３１４に設けられたスロット３１１の列には第１コア３００ａのチューブ３０１の一方の端部３０１ａが挿入され、他方の第２部材３１４に設けられたスロット３１１の列には第２コア３００ｂのチューブ３０１の一方の端部３０１ａが挿入されている。尚、その他の基本構成は、前述した具体例と同様である。
このように、１つのタンクに複数のスロット列を設ける場合は、スペーサ３１５を用いて複数の第２部材３１４を互いに連結し、その連結体と第１部材３１３とを組み付けるとよい。
次に、本発明の第８具体例を図２７乃至２９に基づいて説明する。本例の第２タンク３１０ｂは、その中心に向ってチューブ３０１の端部３０１ａを挿入するものであり、チューブ３０１の端部３０１ａは、チューブ３０１の長手方向に対して所定の角度に屈曲されている。
複数の第２部材３１４を連結するスペーサ３１５としては、各第２部材３１４を所定の角度で連結するテーパ型のものを用いており、一方の第２部材３１４のスロット３１１と他方の第２部材３１４のスロット３１１とは、互いに異なる方向に向けられている。
更に本例の場合、閉鎖部材３１２には、第２部材３１４の端部を嵌合する切欠状の嵌合部３１２ａを設けており、複数の第２部材３１４は、スペーサ３１５を介して連結するとともに、閉鎖部材３１２に端部を嵌合して設けられる。第１部材３１３には、閉鎖部材３１２を位置決めする段部３１３ｂが設けられている。また、閉鎖部材３１２にはスペーサ３１５の端面が突き当てられている。尚、その他の基本構成は、前述した具体例と同様である。
このように、、各第２部材３１４を所定の角度で連結するように構成することも可能である。また、閉鎖部材３１２の嵌合部３１２ａに第２部材３１４を嵌合すれば、閉鎖部材３１２及び第２部材３１４はより正確且つ堅固に組み付けることができる。
次に、本発明の第９具体例を図３０に基づいて説明する。同図に示す放熱器３００は、第１コア３００ａ及び第２コア３００ｂの両側部にそれぞれタンク３１０を設けてなるものである。図中の３４０は、所定のタンク３１０同士を連通する連通部である。
また本例のチューブ３０１は、その端部３０１ａをスロットに挿入した後に所定の角度に屈曲したものである。つまりタンク３１０のスロット３１１には、チューブ３０１の長手方向に対して平行となるように捩じられたチューブ３０１の端部３０１ａを挿入し、チューブ３０１の端部３０１ａは、その後にジグ等を用いつつ各タンク３１０を強制的に動かすことにより屈曲されている。同図に示す場合は、第１コア３００ａ及び第２コア３００ｂの間隔が小さくなるようにチューブ３０１の端部３０１ａを屈曲している。ついては、第１コア３００ａ及び第２コア３００ｂ全体の厚さは薄型化する。連結部３４は、チューブ３０１の端部３０１ａを屈曲した後に設ける。
このように、チューブ３０１の端部３０１ａはスロットに挿入した後に屈曲することも可能である。
次に、本発明の第１０具体例を図３１及び図３２に基づいて説明する。これらの図に示すように、本例の放熱器３００は、第１コア３００ａ及び第２コア３００ｂにおける冷媒の流れを平行に設定してなるクロスフロータイプの熱交換器である。第１コア３００ａ及び第２コア３００ｂのチューブ３０１の一方の端部３０１ａは、入口部３２０が設けられた一方のタンク３１０に挿入されており、
第１コア３００ａ及び第２コア３００ｂのチューブ３０１の他方の端部３０１ａは、出口部３３０が設けられた他方のタンク３１０に挿入されている。
冷媒は、入口部３２０から一方のタンク３１０の内部に導入されて、第１コア３００ａ又は第２コア３００ｂのチューブ３０１を流通した後に、他方のタンク３１０の出口部３３０から外部に排出される。尚、その他の基本構成は、前述した具体例と同様である。
このように、チューブ３０１の端部３０１ａの幅方向が通風方向に対して９０°に捩じれた本例の構成は、カウンターフロータイプの熱交換器やクロスフロータイプの熱交換器等、各種の熱交換器に応用することが可能である。
産業上の利用可能性
本発明は、自動車や家庭用空調機等の冷凍サイクル一般に用いられる熱交換器とそのチューブであり、とりわけ、冷媒として例えばＣＯ２を採用し、放熱器の内部の圧力が冷媒の臨界点を上まわる冷凍サイクルに好適なものである。
【図面の簡単な説明】
【図１】本発明の具体例に係り、超臨界冷凍サイクルを示す説明図である。
【図２】本発明の具体例に係り、放熱器の正面を示す説明図である。
【図３】本発明の具体例に係り、放熱器の要部を示す分解斜視図である。
【図４】本発明の具体例に係り、（ａ）はチューブの上面を示す説明図、（ｂ）はチューブの正面を示す説明図である。
【図５】本発明の具体例に係り、チューブの断面を示す説明図である。
【図６】本発明の具体例に係り、タンクの要部断面を示す説明図である。
【図７】本発明の具体例に係り、放熱器を示す説明図である。
【図８】本発明の具体例に係り、放熱器を示す説明図である。
【図９】本発明の具体例に係り、放熱器の正面を示す説明図である。
【図１０】本発明の具体例に係り、放熱器の上面を示す説明図である。
【図１１】本発明の具体例に係り、（ａ）はチューブの上面を示す説明図、（ｂ）はチューブの正面を示す説明図である。
【図１２】本発明の具体例に係り、（ａ）は第１タンクの断面を示す説明図、（ｂ）は第１タンクの正面を示す説明図である。
【図１３】本発明の具体例に係り、（ａ）は第２タンクの断面を示す説明図、（ｂ）は第２タンクの正面を示す説明図である。
【図１４】本発明の具体例に係り、第２タンクの要部断面を示す説明図である。
【図１５】本発明の具体例に係り、第２タンクの要部断面を示す説明図である。
【図１６】本発明の具体例に係り、第２タンクの要部断面を示す説明図である。
【図１７】本発明の具体例に係り、放熱器の上面を示す説明図である。
【図１８】本発明の具体例に係り、放熱器の上面を示す説明図である。
【図１９】本発明の具体例に係り、第１タンクの要部断面を示す説明図である。
【図２０】本発明の具体例に係り、第１タンクの要部断面を示す分解説明図である。
【図２１】本発明の具体例に係り、第１タンクの要部断面を示す分解説明図である。
【図２２】本発明の具体例に係り、閉鎖部材を示す説明図である。
【図２３】本発明の具体例に係り、第１タンクの端部を示す説明図である。
【図２４】本発明の具体例に係り、第１タンクの縦断面を示す説明図である。
【図２５】本発明の具体例に係り、第２タンクの要部断面を示す説明図である。
【図２６】本発明の具体例に係り、第２タンクの要部断面を示す説明図である。
【図２７】本発明の具体例に係り、第２タンクの要部断面を示す説明図である。
【図２８】本発明の具体例に係り、閉鎖部材を示す説明図である。
【図２９】本発明の具体例に係り、第２タンクの端部を示す説明図である。
【図３０】本発明の具体例に係り、放熱器の上面を示す説明図である。
【図３１】本発明の具体例に係り、放熱器を示す説明図である。
【図３２】本発明の具体例に係り、放熱器の上面を示す説明図である。Technical field
The present invention comprises a core formed by laminating a flat tube through which a refrigerant flows and corrugated fins, and a tank provided with a slot into which an end of the tube is inserted, and ventilates the core. The present invention relates to a heat exchanger that performs heat exchange of a refrigerant by heat transmitted to a core.
Background art
As heat exchangers such as radiators and evaporators used in the refrigeration cycle, a plurality of flat tubes and a plurality of corrugated fins are alternately laminated to form a core, and the end of the tube is formed into a pipe shape. What is inserted in a tank is known. The flat surface of the tube is configured to be parallel to the ventilation direction. The refrigerant is taken into the inside from the tank, circulates through the tube while exchanging heat by heat transmitted to the core, and then discharged from the tank to the outside.
In addition, chlorofluorocarbon refrigerants, including alternative chlorofluorocarbons, have been widely adopted as refrigerants for the refrigeration cycle. 2 Tend to change. CO 2 Compared with refrigeration cycles using chlorofluorocarbon refrigerants, the internal pressure is extremely high, and the pressure on the high pressure side exceeds the critical point of the refrigerant depending on the usage conditions such as temperature. is there. The critical point is a limit on the high-pressure side (that is, a limit on the high-temperature side) where the gas layer and the liquid layer coexist, and is an end point on one side of the vapor pressure curve. The pressure, temperature, and density at the critical point are the critical pressure, critical temperature, and critical density, respectively. In particular, in a radiator that is a high-temperature heat source part of the refrigeration cycle, the refrigerant does not condense when the pressure exceeds the critical point of the refrigerant.
By the way, with respect to the heat exchanger of the refrigeration cycle, improvement of heat exchange efficiency of the refrigerant, reduction in size, weight reduction, ease of manufacture, and saving of installation space are important issues. In particular, a supercritical refrigeration cycle in which the pressure on the high pressure side exceeds the critical point of the refrigerant requires a very high pressure resistance compared to a refrigeration cycle that uses a fluorocarbon refrigerant. There is a need for further rationalization as well as ensuring safety.
For example, in a heat exchanger for a supercritical refrigeration cycle, it is necessary to reduce the volume of tubes and tanks and to increase the wall thickness in terms of ensuring pressure resistance. Here, when the thickness of the tank is increased, there arises a disadvantage that the width of the tube inserted into the tank must be set extremely small with respect to the outer diameter of the tank. In other words, a thick tank has a large difference between the outer diameter and inner diameter, and in order to insert the end of a tube having a constant width in the longitudinal direction into the tank, the width of the tube with respect to the outer diameter of the tank is significantly reduced. As a result, there is a problem that the core width cannot be obtained satisfactorily with respect to the installation space of the heat exchanger.
This invention is made | formed in view of such a situation, The objective is to provide the heat exchanger comprised more rationally.
Disclosure of the invention
The invention described in claim 1 of the present application is used in a heat exchanger that performs heat exchange of a refrigerant. In the flat tube that circulates the refrigerant, the heat exchanger is formed by laminating the tube and a corrugated fin. And a tank provided with a slot into which the end of the tube is inserted, and the refrigerant is exchanged by heat transmitted to the core while ventilating the core. The core is configured such that the flat surface of the tube is parallel to the ventilation direction, and the tube has a heat structure in which the width direction of the end is twisted at 90 ° with respect to the ventilation direction. It is a tube for an exchanger. According to the heat exchanger tube of the present invention, a reasonably configured heat exchanger can be obtained.
That is, according to the present invention, since the tube width is not restricted by the inner diameter of the tank, there is an advantage that it can be set appropriately. In addition, since the flat surface of the tube does not face the refrigerant flow path inside the tank, it is possible to avoid a situation in which a large flow path resistance is generated in the refrigerant flow path, and it is possible to reduce the pressure deficit. is there. Further, if the twist angle in the width direction of the tube end portion is 90 °, the slot is provided along the longitudinal direction of the tank, and there is an advantage that the processing becomes easy. That is, when the twist angle in the width direction of the tube end is less than 90 ° and the slot is provided obliquely with respect to the longitudinal direction of the tank, it is somewhat difficult in terms of processing the tank. Such inconvenience is avoided. In addition, the tube can be easily assembled as compared with the case where the slot is provided obliquely.
The invention described in claim 2 of the present application is that, in claim 1, the heat exchanger is used in a refrigeration cycle in which the refrigerant is circulated, and the refrigeration cycle has a high-pressure side pressure exceeding a critical point of the refrigerant. It is the tube for heat exchangers of composition.
The tube for a heat exchanger of the present invention is one in which the width direction of the end inserted into the slot of the tank is twisted by 90 °, and such a configuration is extremely useful in a heat exchanger of a supercritical refrigeration cycle having a relatively small tank volume. It is valid. That is, the said tube has achieved a very remarkable effect as a tube used for the heat exchanger of a supercritical refrigeration cycle.
The invention described in claim 3 of the present application comprises a core formed by laminating a flat tube through which a refrigerant flows and corrugated fins, and a tank provided with a slot for inserting an end of the tube, In the heat exchanger in which ventilation is performed with respect to the core and heat exchange of the refrigerant is performed by heat transmitted to the core, the core is configured such that a flat surface of the tube is parallel to the ventilation direction. And the said tube is a heat exchanger of the structure by which the width direction of the edge part was twisted at 90 degrees with respect to the said ventilation direction. According to such a configuration, a reasonably configured heat exchanger can be obtained.
That is, according to the present invention, since the tube width is not restricted by the inner diameter of the tank, there is an advantage that it can be set appropriately. In addition, since the flat surface of the tube does not face the refrigerant flow path inside the tank, it is possible to avoid a situation in which a large flow path resistance is generated in the refrigerant flow path, and it is possible to reduce the pressure deficit. is there. Further, if the twist angle in the width direction of the tube end portion is 90 °, the slot is provided along the longitudinal direction of the tank, and there is an advantage that the processing becomes easy. That is, when the twist angle in the width direction of the tube end is less than 90 ° and the slot is provided obliquely with respect to the longitudinal direction of the tank, it is somewhat difficult in terms of processing the tank. Such inconvenience is avoided. In addition, the tube can be easily assembled as compared with the case where the slot is provided obliquely.
The invention described in claim 4 of the present application is the heat exchanger according to claim 3, wherein the inner diameter of the tank is smaller than the width of the tube. According to such a configuration, a more rationally configured heat exchanger can be obtained.
That is, according to the present invention, it is possible to employ a tube having a width larger than the inner diameter of the tank, which is advantageous in securing pressure resistance performance and heat exchange performance.
According to the fifth aspect of the present invention, in the third or fourth aspect, the plurality of slots are arranged along the longitudinal direction of the tank, and the width of the tubes is set to the arrangement interval of the tubes (that is, the stacking interval). The heat exchanger is configured to be smaller than (). According to such a configuration, a more rationally configured heat exchanger can be obtained.
That is, if the tube width is set to be smaller than the arrangement interval of the tubes, the end portions of the tubes twisted by 90 ° are inserted into the slots, and the tubes do not interfere with each other.
The invention described in claim 6 of the present application is that, in claim 5, when the arrangement interval of the tubes is P and the width of the tubes is T, these are P = (6 to 12) mm, T = P · (0.95 to 0.80). If the relationship between the tube arrangement interval P and the tube width T is set in this way, the heat exchanger is configured more rationally.
That is, this relationship means that (T / P) is smaller than 0.95 and larger than 0.8 when the tube arrangement interval P is between 6 mm and 12 mm. This is a numerical representation of a reasonable deduction of the interest loss with a decrease in heat exchange efficiency when the value of P is increased, and a decrease in the strength of the tank because the slot interval is reduced when the arrangement interval P is reduced. .
The invention described in claim 7 of the present application is the heat exchanger according to any one of claims 3 to 6, wherein the heat exchanger is formed by stacking a plurality of the cores in the ventilation direction. According to such a configuration, a more rationally configured heat exchanger can be obtained.
That is, by stacking a plurality of cores, it is possible to further improve the heat exchange efficiency, and more effectively use the installation space for the heat exchanger.
The invention described in claim 8 of the present application is that in claim 7, the core includes a first core and a second core stacked in the ventilation direction, and the tank includes a tube of the first core. A first tank into which one end is inserted; a second tank into which the other end of the first core tube and one end of the second core tube are inserted; and a tube of the second core. A third tank for inserting the other end,
In the heat exchanger, the first tank is provided with an inlet of the refrigerant, and the third tank is provided with an outlet of the refrigerant.
According to such a configuration, a more rationally configured heat exchanger can be obtained.
That is, the present invention is a counter flow type heat exchanger in which the first core and the second core are overlapped in the ventilation direction, and the refrigerant flow in the first core and the second core is a counter flow, and the heat exchange efficiency of the refrigerant There is an advantage that is improved. Furthermore, by inserting both the end of the first core tube and the end of the second core tube into the second tank, simplification of the structure relating to the connection of the first core and the second core is achieved. It is possible to improve the manufacturability. It is also advantageous in that it saves installation space for the heat exchanger.
The invention described in claim 9 of the present application is that, in claim 8, the positions of the first tank and the third tank are shifted in a direction orthogonal to the ventilation direction, and the inlet portion and the outlet portion are in the ventilation direction. It is the heat exchanger of the structure which orient | assigned and aligned to the leeward side or leeward side. According to such a configuration, a more rationally configured heat exchanger can be obtained.
That is, the present invention sets the diameters of the first tank and the third tank to a required size by shifting the positions of the first tank and the third tank in the direction perpendicular to the airflow direction, and they interfere with each other. It is the composition which avoids. Such a configuration is extremely effective in a heat exchanger for a supercritical refrigeration cycle in which the difference between the outer diameter and inner diameter of the tank is large. Further, by shifting the positions of the first tank and the third tank in this way, the inlet portion of the first tank and the outlet portion of the third tank can be directed to the upwind side or the downwind side in the airflow direction. It becomes possible and simplification of the piping structure is achieved for the layout of the refrigeration cycle.
The invention described in claim 10 of the present application is the heat exchanger according to any one of claims 3 to 9, wherein the width of the fin is set larger than the width of the tube.
That is, if a fin having a width larger than the width of the tube is employed, an improvement in heat exchange performance is achieved. In addition, when the tubes and fins are stacked, if the fins are slightly deformed, the tubes are held by the fins, thereby preventing these positional shifts. Therefore, there is also an advantage that these assembling properties are improved.
The invention recited in claim 11 of the present application is the tank according to any one of claims 3 to 10, wherein the tank has a cylindrical shape, and is a semi-cylindrical shape (that is, an incomplete cylindrical shape lacking a part). The heat exchanger has a configuration in which a first member, a second member in which the slots are arranged, and a closing member that closes an end of the first member are assembled.
That is, the tank is configured by assembling a semi-cylindrical first member and a second member in which slots are arranged into a cylinder shape, and closing the end portion with a closing member. According to such a configuration, the tank is reasonably configured.
The invention described in claim 12 of the present application is the tank according to claim 11, wherein the tank includes the first member, the plurality of second members, a spacer for connecting the plurality of second members to each other, and the closing member. It is the heat exchanger of the structure formed by assembling.
That is, when a plurality of slot rows are provided in one tank, a plurality of second members may be connected to each other using a spacer.
The invention described in claim 13 of the present application is the heat exchanger according to claim 11 or 12, wherein the closing member is provided with a fitting portion for fitting the second member.
That is, if the second member is fitted to the fitting portion of the closing member, the closing member and the second member can be assembled more accurately and firmly.
According to a fourteenth aspect of the present invention, in any one of the eleventh to thirteenth aspects, the first member is provided with a caulking portion, and the first member and the second member are caulking the caulking portion. It is a heat exchanger with a fixed configuration.
That is, if the first member and the second member are fixed by caulking the caulking portion, they can be assembled more accurately and firmly.
The invention described in claim 15 of the present application is the heat exchanger according to claim 14, wherein the first member, the second member, and the closing member are fixed by caulking the caulking portion.
That is, according to the caulking portion, the closing member can be fixed together with the first member and the second member. According to such a configuration, the first member, the second member, and the closing member are assembled efficiently.
The invention described in claim 16 of the present application is the heat exchange according to any one of claims 11 to 15, wherein the first member and the second member are assembled after the end of the tube is inserted into the slot. It is a vessel.
That is, the tube and the tank are assembled by inserting the end of the tube into the slot of the second member and assembling the second member and the first member.
The invention described in claim 17 of the present application is the heat exchange according to any one of claims 11 to 15, wherein the end of the tube is inserted into the slot after assembling the first member and the second member. It is a vessel.
That is, the tube and the tank are assembled by assembling the first member and the second member and inserting the end of the tube into the slot of the second member.
The invention described in claim 18 of the present application is the heat exchanger according to any one of claims 3 to 17, wherein the end of the tube is bent with respect to the longitudinal direction of the tube.
In other words, bending the end portion of the tube with respect to the longitudinal direction of the tube has an advantage of improving the degree of freedom in designing the layout of the tank and the tube. For example, when a plurality of cores are stacked in the ventilation direction, it is possible to adopt such a configuration and set the interval between the cores small. That is, the thickness of the entire core can be reduced regardless of the shape of the tank.
The invention described in claim 19 of the present application is the heat exchanger according to claim 18, wherein the end portion of the tube is bent before being inserted into the slot.
That is, the end of the tube is bent at a predetermined angle with respect to the longitudinal direction of the tube, and the bent end is inserted into the slot. According to such a configuration, the tube and the tank can be assembled efficiently.
The invention described in claim 20 of the present application is the heat exchanger according to claim 18, wherein the end portion of the tube is bent after being inserted into the slot.
That is, the end of the tube is inserted into the slot before bending, and the end is bent at a predetermined angle from this state. According to such a configuration, the tube and the tank can be assembled efficiently.
The invention described in claim 21 of the present application is the heat exchanger according to any one of claims 3 to 20, wherein the heat exchanger is used in a refrigeration cycle in which the refrigerant is circulated, and the refrigeration cycle has a pressure on the high pressure side of the refrigerant. It is a heat exchanger with a configuration exceeding the critical point. The heat exchanger of the present invention uses a tube in which the width direction of the end portion inserted into the slot of the tank is twisted by 90 °, and such a configuration has the heat of the supercritical refrigeration cycle with a relatively small tank volume. Very effective in exchangers. That is, the heat exchanger achieves a very remarkable effect as a heat exchanger for a supercritical refrigeration cycle.
The invention described in claim 22 of the present application is a heat exchanger of a refrigeration cycle in which the pressure on the high pressure side exceeds the critical point of the refrigerant, and is formed by laminating flat tubes and corrugated fins through which the refrigerant flows. A heat exchanger that includes a core and a tank provided with a slot into which an end portion of the tube is inserted, and is configured to ventilate the core and to exchange heat of the refrigerant with heat transmitted to the core. The core includes a first core and a second core stacked in the ventilation direction, and an end portion of the tube of the first core is inserted into one side of the first core and the second core. The tank is provided with an inlet for the refrigerant, and the tank into which the end of the tube of the second core is inserted is provided with an outlet for the refrigerant. The positions of these tanks are perpendicular to the ventilation direction. If you shift To the inlet portion and the outlet portion is a heat exchanger structure toward aligned on the windward side or the leeward side of the ventilating direction. According to such a configuration, a reasonably configured heat exchanger can be obtained.
That is, the present invention sets the diameter of each tank to a required size by shifting the positions of the two tanks on one side of the first core and the second core in a direction perpendicular to the airflow direction, Are configured to avoid interfering with each other. Such a configuration is extremely effective in a heat exchanger for a supercritical refrigeration cycle in which the difference between the outer diameter and inner diameter of the tank is large. In addition, by shifting the position of the tank in this way, it becomes possible to direct the inlet and outlet of each tank to the upwind side or downwind side in the ventilation direction. Simplification is achieved.
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, specific examples of the present invention will be described in detail with reference to the drawings. A refrigeration cycle 1 shown in FIG. 1 is an in-vehicle air conditioning refrigeration cycle mounted on an automobile, and includes a compressor 200 that compresses a refrigerant, a radiator 300 that cools the refrigerant compressed by the compressor 200, and a radiator 300. An expansion valve 400 that expands by depressurizing the cooled refrigerant, an evaporator 500 that evaporates the refrigerant depressurized by the expansion valve 400, and a refrigerant that separates the refrigerant flowing out of the evaporator 500 into an air layer and a liquid layer. Is supplied to the compressor 200, and an internal heat exchanger 700 that improves the efficiency of the cycle by exchanging heat between the high-pressure side refrigerant and the low-pressure side refrigerant. CO as a refrigerant 2 The pressure on the high pressure side of the supercritical refrigeration cycle 1 exceeds the critical point of the refrigerant depending on the use conditions such as the temperature. The arrows in FIG. 1 indicate the refrigerant circulation direction.
As shown in FIGS. 2 and 3, a heat radiator 300 as a heat exchanger of this example includes a core 300 a formed by alternately laminating flat tubes 301 and corrugated fins 302 provided with louvers, And a tank 310 into which the end portion 301a of the tube 301 is inserted, and the refrigerant that flows through the tube 301 is configured to perform heat exchange with heat transmitted to the core 300a. Side plates 303 as reinforcing members are provided on the upper and lower sides of the core 300a, and both end portions of each side plate 303 are supported by each tank 310, respectively. Each tank 310 is a member having a cylindrical shape whose both ends are closed by a closing member 312.
One tank 310 is provided with an inlet portion 320 for introducing a refrigerant, and the other tank 310 is provided with an outlet portion 330 for discharging the refrigerant. The inlet portion 320 and the outlet portion 330 are configured by providing holes at important points of the tank 310 and providing joints for connecting external piping to the holes.
The refrigerant is introduced into the inside of one tank 310 from the inlet 320, and after flowing through the tube 301 while exchanging heat by heat transmitted to the core 300a, is discharged to the outside from the outlet 330 of the other tank 310. .
In this example, CO 2 Is used as a refrigerant, and the radiator 300 requires a very high pressure strength. Therefore, the required pressure strength is secured by increasing the thickness and reducing the volume of the tank 310. In particular, the inner diameter of the tank 310 is smaller than the width of the tube 301.
Each tube 301 has one end 301 a inserted into one tank 310 and the other end 301 a inserted into the other tank 310. In each tank 310, a plurality of slots 311 into which the end portions 301a of the tubes 301 are inserted are arranged along the longitudinal direction.
The heat radiator 300 is manufactured by assembling the tube 301, the fin 320, the tank 310, the inlet portion 320, and the outlet portion 330 together, and brazing the assembled body in a furnace. In addition, regarding such brazing, a brazing material and a flux are provided in advance at the key points of each member.
The core 300a of this example is configured such that the flat surface of the tube 301 is parallel to the ventilation direction. In addition, the tube 301 of this example is one in which the width direction of both end portions 301a is twisted by 90 ° with respect to the ventilation direction. In this example, the tank 310 is erected in the vertical direction, and both end portions 301a of the tube 301 are configured such that the flat surfaces face the vertical direction. 4A shows the upper surface of the tube 301, and FIG. 4B shows the front of the tube 301. FIG. FIG. 5 shows a cross section of the tube 301. The tube 301 shown in these figures is an aluminum alloy extruded tube having a plurality of flow paths 301b. In the case of this example, the end portion 301a of the tube 301 is obtained by cutting the extruded tube into a predetermined length and then sandwiching the end portion 301a of the tube 301 and the vicinity thereof with a pair of jigs, and relatively moving each jig relative to each other. It is processed by doing.
Thus, if the end portion 301 a of the tube 301 is twisted 90 ° and inserted into the slot 311 of the tank 310, the flat surface of the tube 301 does not face the refrigerant flow path in the tank 310. There is no large flow resistance in the path. Therefore, the pressure deficit can be reduced. In addition, there is an advantage that the degree of freedom of arrangement of the inlet portion 320 and the outlet portion 330 is increased. That is, although the inlet portion 320 and the outlet portion 330 protrude to some extent inside the tank 310, the attachment angle can be set as appropriate. For example, as shown in FIG. 6, the attachment angle of the inlet portion 320 and the outlet portion 330 can be set obliquely with respect to the insertion direction of the tube 301. In addition, the front-end | tip part of the inlet part 320 inserted in the tank 310 and the outlet part 330 is processed into the taper shape.
In this example, the width T of the tube 301 is set to be smaller than the arrangement interval P of the tubes 301. With respect to the arrangement interval P and the width T, P = (6 to 12) mm, T = P · (0 .95 to 0.80). The slot width δT is slightly larger than the tube width T. According to such a configuration, the heat exchange efficiency of the refrigerant and the strength of the tank 310 can be sufficiently ensured.
Further, in the case of this example, the width of the fin 302 is set slightly larger than the width of the tube 301. That is, if the fin 302 having a width larger than the width of the tube 301 is employed, the heat exchange area is expanded and the heat exchange performance is improved. In addition, when the tubes 301 and the fins 302 are stacked, considering that the fins 302 are deformed to some extent, the tube 301 is held by the fins 302, thereby preventing these positional shifts. As a result, these assembling properties are improved.
Next, a second specific example of the present invention will be described with reference to FIG. As shown in the figure, the radiator 300 of the present example is formed by overlapping a first core 300a and a second core 300b in the ventilation direction. Tanks 310 are provided on both sides of the first core 300a and the second core 300b, respectively. And in one side part of the 1st core 300a and the 2nd core 300b, the tank 310 which inserts the edge part 301a of the tube 301 of the 1st core 300a is provided with the inlet part 320 of a refrigerant | coolant, and the 2nd core 300b The tank 310 into which the end portion 301 a of the tube 301 is inserted is provided with a refrigerant outlet 330. Moreover, in the other side part of the 1st core 300a and the 2nd core 300b, the tank 310 which inserts the edge part 301a of the tube 301 of the 1st core 300a, and the edge part 301a of the tube 301 of the 2nd core 300b are inserted. The tank 310 to be communicated with. The refrigerant flows through the first core 300a and the second core 300b sequentially. That is, the radiator 300 of this example is a counterflow type heat exchanger in which the refrigerant flows in the first core 300a and the second core 300b are counterflows.
As described above, the heat exchange efficiency can be further improved by overlapping the plurality of cores 300a and 300b in the ventilation direction.
Next, a third specific example of the present invention will be described. As shown in FIGS. 8 to 10, the radiator 300 as a heat exchanger of this example includes a first core 300 a and a second core formed by laminating a flat tube 301 and a corrugated fin 302 through which a refrigerant flows. 300b, a pipe-shaped first tank 310a, a second tank 310b, and a third tank 310c into which the end portions 301a of the respective tubes 301 are inserted and connected, and an inlet for a pipe-shaped refrigerant provided in the first tank 310a And a pipe-shaped refrigerant outlet 330 provided in the third tank 310c. The refrigerant sent from the compressor 200 flows in from the inlet portion 320, and the refrigerant flowing out from the outlet portion 330 is sent to the expansion valve 400. In addition, the arrow in these figures has shown the distribution | circulation direction of the refrigerant | coolant in the heat radiator 300, and the white arrow has shown the ventilation direction with respect to the 1st core 300a and the 2nd core 300b.
One end 301a of the tube 301 of the first core 300a is inserted into the first tank 310a. The other end 301a of the tube 301 of the first core 300a and the one end 301a of the tube 301 of the second core 300b are inserted into the second tank 310b. The other end 301a of the tube 301 of the second core 300b is inserted into the third tank 310c.
The first core 300a and the second core 300b are ventilated by a fan (not shown), and the refrigerant exchanges heat with heat transmitted to the first core 300a and the second core 300b. In addition, the first core 300a and the second core 300b are configured to overlap in the ventilation direction, and the flat surface of the tube 301 is parallel to the ventilation direction, and the ventilation is performed from the second core 300b side. Applied. That is, the radiator 300 of this example is a counterflow type heat exchanger in which the refrigerant flows in the first core 300a and the second core 300b are counterflows.
As shown in FIG. 11, the tube 301 of this example is also an extruded tube made of an aluminum alloy similar to the specific example described above. Moreover, the width direction of the both ends 301a is twisted by 90 degrees with respect to the ventilation direction. The end portion 301a of the tube 301 is processed by cutting the extruded tube into a predetermined length, sandwiching the end portion 301a and the vicinity thereof with a pair of jigs, and moving each jig relative to each other. .
As shown in FIG. 12, the first tank 310a is an extruded pipe or a pultruded pipe provided with a plurality of slots 311 into which the end portions 301a of the respective tubes 301 are inserted along the longitudinal direction thereof. The slots 311 are formed by press working or cutting, and are arranged in a line along the longitudinal direction of the first tank 310a. The third tank 310c is configured using the same member as the first tank 310a. In addition, a hole for connecting the inlet 320 is provided at the main point of the first tank 310a, and a hole for connecting the outlet 330 is provided at the main of the third tank 310c.
As shown in FIG. 13, the second tank 310b is also an extruded pipe or a pultruded pipe provided with a plurality of slots 311 into which the end portions 301a of the respective tubes 301 are inserted along the longitudinal direction thereof. The slots 311 are arranged in two rows along the longitudinal direction of the second tank 310b. That is, one row corresponds to the tube 301 of the first core 300a, and the other row corresponds to the tube 301 of the second core 300b. Further, the second tank 310b has a relatively large cross-sectional area as compared with the first tank 310a and the third tank 310c, and therefore the wall thickness is set to be somewhat thick.
As shown in FIG. 14 or FIG. 15, the end 301a of the tube 301 to be inserted into the second tank 310 is bent at a predetermined angle with respect to the longitudinal direction of the tube 301. Is inserted toward the center. The tube 301 shown in FIG. 14 has an angle set while twisting the end 301a. The tube 301 shown in FIG. 15 is bent once to a predetermined angle after twisting the end 301a. It is a thing. The end 301 a of the tube 301 is bent before being inserted into the slot 311. According to such a configuration, it is possible to ensure a good flow of the refrigerant. Alternatively, as shown in FIG. 16, if the end portions 301a of the tubes 301 of the first core 300a and the second core 300b are configured to be inserted in parallel to each other with respect to the second tank 310b, their assembling properties are improved. It is possible to improve.
And this heat radiator 300 is assembling the tube 301, the fin 320, the 1st tank 310a, the 2nd tank 310b, the 3rd tank 310c, the inlet part 320, and the outlet part 330 integrally, Then, the assembly body is in a furnace. Manufactured by brazing. In addition, regarding such brazing, a brazing material and a flux are provided in advance at the key points of each member.
Thus, the heat radiator 300 of this example ensures the required pressure resistance according to the refrigerant that is in the supercritical state, improves the heat exchange efficiency of the refrigerant, is smaller, lighter, facilitates manufacture, and is installed. It achieves rationalization of space saving and the like, and can be used very suitably as a heat exchanger of the supercritical refrigeration cycle 1 mounted on an automobile.
Next, a fourth specific example of the present invention will be described with reference to FIGS. As shown in FIG. 17, the radiator 300 of this example is disposed on the windward side of a radiator 800 of an automobile, and the first tank 310a is provided on one side of the first core 300a and the second core 300b. In addition, the position of the third tank 310c is shifted in a direction orthogonal to the wind direction, and the inlet portion 320 and the outlet portion 330 are aligned to the leeward side in the wind direction. The tube 301 of the first core 300a is set to be somewhat shorter than the tube 301 of the second core 300b. Other configurations are the same as those of the specific example described above.
According to this example, the heat radiator 300 can be configured more rationally, and as a result, simplification of the piping structure can be achieved for the layout of the refrigeration cycle 1 in the automobile. In particular, pipe-shaped inlet portion 320 and outlet portion 330 that circulate a high-pressure refrigerant, and pipes connected to inlet portion 302 and outlet portion 330 are very disadvantageous to be bent because they are thick, According to this example, there exists an advantage that those shapes become comparatively simple, and it can contribute to labor saving of those processes.
In addition, as shown in FIG. 18, if the positional relationship between the first tank 310a and the third tank 310c is reversed, the inlet portion 320 and the outlet portion 330 can also be directed to the upwind side in the wind direction. In this case, the tube 301 of the second core 300b is set to be somewhat shorter than the tube 301 of the first core 300a.
Next, a fifth specific example of the present invention will be described with reference to FIGS. As shown in FIGS. 19 and 24, the first tank 310a or the third tank 310c of the present example has a cylindrical shape, and the semi-cylindrical first member 313 and the slots 311 are arranged in a line. The second member 314 is assembled with a closing member 311 that closes its end. The cross section of the first member 314 is substantially C-shaped or U-shaped.
The first member 313 is provided with a crimping portion 313a, and the first member 313, the second member 314, and the closing member 312 are fixed by crimping the crimping portion 313a. The tube 301 and the first tank 310a or the third tank 310c are assembled by assembling the first member 313, the second member 314, and the closing member 312 and then inserting the end portion 301a of the tube 301 into the slot 311. (See FIG. 20). Alternatively, the first member 313, the second member 314, and the closing member 312 are assembled after the end portion 301a of the tube 301 is inserted into the slot 311 (see FIG. 21).
The closing member 312 is a plate having a predetermined shape that is held on the inner peripheral surface of the first member 313 and against which the end surface of the second member 314 is abutted. The other basic configurations are the same as those in the specific example described above.
According to this example, the tank can be configured more rationally.
Next, a sixth specific example of the present invention will be described with reference to FIG. Similarly to the first tank 310a or the third tank 310c of the fifth specific example, the second tank 310b of the present example also includes a semi-cylindrical first member 313 and a second member 314 in which slots 311 are arranged. , And a closing member 311 for closing the end portion is assembled. In particular, the second member 314 has slots 311 arranged in two rows. One end 301a of the tube 301 of the first core 300a is inserted into one row of the slots 311 and the other row is arranged in the other row. One end 301a of the tube 301 of the second core 300b is inserted. The other basic configuration is the same as the specific example described above.
As described above, the second tank 310b can also be configured using the second member 314 provided with a plurality of slot rows.
Next, a seventh specific example of the present invention will be described with reference to FIG. The second tank 310b of this example uses a plurality of second members 314 and spacers 315 that connect the plurality of second members to each other. One end 301a of the tube 301 of the first core 300a is inserted into the row of slots 311 provided in one second member 314, and the row of slots 311 provided in the other second member 314 is inserted. One end 301a of the tube 301 of the second core 300b is inserted. The other basic configuration is the same as the specific example described above.
Thus, when providing a some slot row | line | column in one tank, it is good to connect the some 2nd member 314 mutually using the spacer 315, and to assemble | attach the connection body and the 1st member 313. FIG.
Next, an eighth specific example of the present invention will be described with reference to FIGS. The second tank 310b of this example is for inserting the end portion 301a of the tube 301 toward the center thereof, and the end portion 301a of the tube 301 is bent at a predetermined angle with respect to the longitudinal direction of the tube 301. Yes.
As the spacer 315 for connecting the plurality of second members 314, a taper type member for connecting the second members 314 at a predetermined angle is used. The slot 311 of one second member 314 and the other second member are used. 314 slots 311 are oriented in different directions.
Furthermore, in the case of this example, the closing member 312 is provided with a notch-shaped fitting portion 312 a for fitting the end portion of the second member 314, and the plurality of second members 314 are connected via the spacer 315. At the same time, the closing member 312 is provided with its end fitted. The first member 313 is provided with a step portion 313b for positioning the closing member 312. Further, the end face of the spacer 315 is abutted against the closing member 312. The other basic configuration is the same as the specific example described above.
Thus, it is also possible to configure each second member 314 to be connected at a predetermined angle. Moreover, if the 2nd member 314 is fitted to the fitting part 312a of the closing member 312, the closing member 312 and the 2nd member 314 can be assembled more correctly and firmly.
Next, a ninth specific example of the present invention will be described with reference to FIG. The radiator 300 shown in the figure is provided with a tank 310 on each side of the first core 300a and the second core 300b. Reference numeral 340 in the figure denotes a communication portion that connects predetermined tanks 310 to each other.
Moreover, the tube 301 of this example is bent at a predetermined angle after the end portion 301a is inserted into the slot. That is, the end portion 301a of the tube 301 that is twisted so as to be parallel to the longitudinal direction of the tube 301 is inserted into the slot 311 of the tank 310, and the end portion 301a of the tube 301 is subsequently used with a jig or the like. However, it is bent by forcibly moving each tank 310. In the case shown in the figure, the end 301a of the tube 301 is bent so that the interval between the first core 300a and the second core 300b is small. Accordingly, the entire thickness of the first core 300a and the second core 300b is reduced. The connecting portion 34 is provided after the end portion 301a of the tube 301 is bent.
In this manner, the end portion 301a of the tube 301 can be bent after being inserted into the slot.
Next, a tenth example of the present invention will be described with reference to FIGS. As shown in these drawings, the radiator 300 of this example is a cross-flow type heat exchanger in which the refrigerant flows in the first core 300a and the second core 300b are set in parallel. One end 301a of the tube 301 of the first core 300a and the second core 300b is inserted into one tank 310 provided with the inlet 320,
The other end 301a of the tube 301 of the first core 300a and the second core 300b is inserted into the other tank 310 in which the outlet 330 is provided.
The refrigerant is introduced into the inside of one tank 310 from the inlet portion 320, flows through the tube 301 of the first core 300a or the second core 300b, and then is discharged to the outside from the outlet portion 330 of the other tank 310. The other basic configuration is the same as the specific example described above.
As described above, the configuration of this example in which the width direction of the end portion 301a of the tube 301 is twisted by 90 ° with respect to the ventilation direction has various heat flows such as a counter flow type heat exchanger and a cross flow type heat exchanger. It can be applied to an exchanger.
Industrial applicability
The present invention is a heat exchanger generally used for refrigeration cycles such as automobiles and home air conditioners, and a tube thereof. 2 And is suitable for a refrigeration cycle in which the pressure inside the radiator exceeds the critical point of the refrigerant.
[Brief description of the drawings]
FIG. 1 is an explanatory diagram showing a supercritical refrigeration cycle according to a specific example of the present invention.
FIG. 2 is an explanatory view showing a front surface of a radiator according to a specific example of the present invention.
FIG. 3 is an exploded perspective view showing a main part of a radiator according to a specific example of the present invention.
FIG. 4 relates to a specific example of the present invention, in which (a) is an explanatory view showing the upper surface of the tube, and (b) is an explanatory view showing the front of the tube.
FIG. 5 is an explanatory view showing a cross section of a tube according to a specific example of the present invention.
FIG. 6 is an explanatory view showing a cross section of a main part of a tank according to a specific example of the present invention.
FIG. 7 is an explanatory view showing a radiator according to a specific example of the present invention.
FIG. 8 is an explanatory diagram showing a radiator according to a specific example of the present invention.
FIG. 9 is an explanatory view showing a front surface of a radiator according to a specific example of the present invention.
FIG. 10 is an explanatory view showing an upper surface of a radiator according to a specific example of the present invention.
FIG. 11 relates to a specific example of the present invention, wherein (a) is an explanatory view showing the upper surface of the tube, and (b) is an explanatory view showing the front of the tube.
FIGS. 12A and 12B relate to a specific example of the present invention, in which FIG. 12A is an explanatory view showing a cross section of a first tank, and FIG. 12B is an explanatory view showing a front surface of the first tank;
FIGS. 13A and 13B relate to a specific example of the present invention, in which FIG. 13A is an explanatory view showing a cross section of a second tank, and FIG. 13B is an explanatory view showing the front of the second tank;
FIG. 14 is an explanatory diagram showing a cross-section of a main part of a second tank according to a specific example of the present invention.
FIG. 15 is an explanatory view showing a cross section of a main part of a second tank according to a specific example of the present invention.
FIG. 16 is an explanatory view showing a cross section of a main part of a second tank according to a specific example of the present invention.
FIG. 17 is an explanatory diagram showing an upper surface of a radiator according to a specific example of the present invention.
FIG. 18 is an explanatory diagram showing an upper surface of a radiator according to a specific example of the present invention.
FIG. 19 is an explanatory diagram showing a cross-section of the main part of the first tank according to a specific example of the present invention.
FIG. 20 is an exploded explanatory view showing a cross section of the main part of the first tank according to a specific example of the present invention.
FIG. 21 is an exploded explanatory view showing a cross section of the main part of the first tank according to a specific example of the present invention.
FIG. 22 is an explanatory view showing a closing member according to a specific example of the present invention.
FIG. 23 is an explanatory diagram showing an end portion of a first tank according to a specific example of the present invention.
FIG. 24 is an explanatory diagram showing a longitudinal section of a first tank according to a specific example of the present invention.
FIG. 25 is an explanatory diagram showing a cross-section of a main part of a second tank according to a specific example of the present invention.
FIG. 26 is an explanatory diagram showing a cross-section of the main part of the second tank according to a specific example of the present invention.
FIG. 27 is an explanatory diagram showing a cross-section of the main part of the second tank according to a specific example of the present invention.
FIG. 28 is an explanatory view showing a closing member according to a specific example of the present invention.
FIG. 29 is an explanatory diagram showing an end portion of a second tank according to a specific example of the present invention.
FIG. 30 is an explanatory diagram showing an upper surface of a radiator according to a specific example of the present invention.
FIG. 31 is an explanatory diagram showing a radiator according to a specific example of the present invention.
FIG. 32 is an explanatory diagram showing an upper surface of a radiator according to a specific example of the present invention.

Claims (22)

冷媒の熱交換を行う熱交換器に用いられ、前記冷媒を流通する偏平状のチューブにおいて、
前記熱交換器は、当該チューブ及び波型のフィンを積層してなるコアと、当該チューブの端部を挿入するスロットを設けたタンクとを備え、前記コアに対して通風がなされるとともに前記コアに伝わる熱にて前記冷媒の熱交換を行うものであり、
前記コアは、当該チューブの偏平状の面が前記通風方向と平行になるように構成し、
当該チューブは、その端部の幅方向が前記通風方向に対して９０°に捩じれたことを特徴とする熱交換器用チューブ。Used in a heat exchanger that performs heat exchange of refrigerant, in a flat tube that circulates the refrigerant,
The heat exchanger includes a core formed by laminating the tube and corrugated fins, and a tank provided with a slot into which an end of the tube is inserted. Heat exchange of the refrigerant with heat transmitted to
The core is configured such that the flat surface of the tube is parallel to the ventilation direction,
The tube for heat exchangers, characterized in that the end portion of the tube is twisted at 90 ° with respect to the ventilation direction. 前記熱交換器は、前記冷媒を循環する冷凍サイクルに用いられ、前記冷凍サイクルは、高圧側の圧力が前記冷媒の臨界点を超えることを特徴とする請求項１記載の熱交換器用チューブ。The heat exchanger tube according to claim 1, wherein the heat exchanger is used in a refrigeration cycle in which the refrigerant is circulated, and the pressure on the high pressure side of the refrigeration cycle exceeds a critical point of the refrigerant. 冷媒を流通する偏平状のチューブ及び波型のフィンを積層してなるコアと、前記チューブの端部を挿入するスロットを設けたタンクとを備え、前記コアに対して通風がなされるとともに前記コアに伝わる熱にて前記冷媒の熱交換を行う熱交換器において、
前記コアは、前記チューブの偏平状の面が前記通風方向と平行になるように構成し、
前記チューブは、その端部の幅方向が前記通風方向に対して９０°に捩じれたことを特徴とする熱交換器。A core formed by laminating a flat tube and a corrugated fin for circulating a refrigerant; and a tank provided with a slot into which an end of the tube is inserted. In a heat exchanger that performs heat exchange of the refrigerant with heat transmitted to
The core is configured so that a flat surface of the tube is parallel to the ventilation direction,
The heat exchanger according to claim 1, wherein a width direction of an end of the tube is twisted at 90 ° with respect to the ventilation direction. 前記タンクの内径は、前記チューブの幅よりも小さいことを特徴とする請求項３記載の熱交換器。The heat exchanger according to claim 3, wherein an inner diameter of the tank is smaller than a width of the tube. 複数の前記スロットを前記タンクの長手方向に沿って列設するとともに、前記チューブの幅を前記チューブの配置間隔よりも小さく設定したことを特徴とする請求項３又は４記載の熱交換器。5. The heat exchanger according to claim 3, wherein the plurality of slots are arranged along the longitudinal direction of the tank, and the width of the tubes is set smaller than the arrangement interval of the tubes. 前記チューブの配置間隔をＰ、前記チューブの幅をＴとするとき、これらは、Ｐ＝（６〜１２）ｍｍ、Ｔ＝Ｐ・（０．９５〜０．８０）、の関係にあることを特徴とする請求項５記載の熱交換器。When the arrangement interval of the tubes is P and the width of the tubes is T, these are in a relationship of P = (6-12) mm, T = P · (0.95-0.80). The heat exchanger according to claim 5, wherein 当該熱交換器は、前記通風方向に複数の前記コアを重ねてなることを特徴とする請求項３乃至６のいずれか記載の熱交換器。The heat exchanger according to any one of claims 3 to 6, wherein the heat exchanger is formed by stacking a plurality of the cores in the ventilation direction. 前記コアとしては、前記通風方向に重ねられた第１コア及び第２コアを備え、
前記タンクとしては、前記第１コアのチューブの一方の端部を挿入する第１タンクと、前記第１コアのチューブの他方の端部及び前記第２コアのチューブの一方の端部を挿入する第２タンクと、前記第２コアのチューブの他方の端部を挿入する第３タンクとを備え、
前記第１タンクには前記冷媒の入口部を設け、前記第３タンクには前記冷媒の出口部を設けたことを特徴とする請求項７記載の熱交換器。The core includes a first core and a second core stacked in the ventilation direction,
The tank includes a first tank into which one end of the first core tube is inserted, and the other end of the first core tube and one end of the second core tube. A second tank and a third tank for inserting the other end of the second core tube;
The heat exchanger according to claim 7, wherein the first tank is provided with an inlet portion of the refrigerant, and the third tank is provided with an outlet portion of the refrigerant. 前記第１タンク及び前記第３タンクの位置は前記通風方向と直交する方向にずらすとともに、前記入口部及び前記出口部は前記通風方向の風上側又は風下側に揃えて向けたことを特徴とする請求項８記載の熱交換器。The positions of the first tank and the third tank are shifted in a direction orthogonal to the ventilation direction, and the inlet portion and the outlet portion are aligned to the windward side or leeward side of the ventilation direction. The heat exchanger according to claim 8. 前記フィンの幅は、前記チューブの幅よりも大きく設定したことを特徴とする請求項３乃至９のいずれか記載の熱交換器。The heat exchanger according to any one of claims 3 to 9, wherein a width of the fin is set larger than a width of the tube. 前記タンクは、筒状を呈するものであり、半筒状の第１部材と、前記スロットが列設された第２部材と、その端部を閉鎖する閉鎖部材とを組み付けてなることを特徴とする請求項３乃至１０のいずれか記載の熱交換器。The tank has a cylindrical shape, and is formed by assembling a semi-cylindrical first member, a second member in which the slots are arranged, and a closing member that closes an end thereof. The heat exchanger according to any one of claims 3 to 10. 前記タンクは、前記第１部材と、複数の前記第２部材と、複数の前記第２部材を互いに連結するスペーサと、前記閉鎖部材とを組み付けてなることを特徴とする請求項１１記載の熱交換器。The heat according to claim 11, wherein the tank is formed by assembling the first member, the plurality of second members, a spacer for connecting the plurality of second members to each other, and the closing member. Exchanger. 前記閉鎖部材には、前記第２部材を嵌合する嵌合部を設けたことを特徴とする請求項１１又は１２記載の熱交換器。The heat exchanger according to claim 11 or 12, wherein the closing member is provided with a fitting portion for fitting the second member. 前記第１部材にはカシメ部を設け、前記第１部材及び前記第２部材は前記カシメ部をカシメることにより固定したことを特徴とする請求項１１乃至１３のいずれか記載の熱交換器。The heat exchanger according to any one of claims 11 to 13, wherein the first member is provided with a caulking portion, and the first member and the second member are fixed by caulking the caulking portion. 前記カシメ部をカシメることにより、前記第１部材、前記第２部材、及び前記閉鎖部材を固定したことを特徴とする請求項１４記載の熱交換器。The heat exchanger according to claim 14, wherein the first member, the second member, and the closing member are fixed by caulking the caulking portion. 前記チューブの端部を前記スロットに挿入した後に前記第１部材と前記第２部材とを組み付けたことを特徴とする請求項１１乃至１５のいずれか記載の熱交換器。The heat exchanger according to any one of claims 11 to 15, wherein the first member and the second member are assembled after inserting an end of the tube into the slot. 前記第１部材と前記第２部材とを組み付けた後に前記チューブの端部を前記スロットに挿入したことを特徴とする請求項１１乃至１５のいずれか記載の熱交換器。The heat exchanger according to any one of claims 11 to 15, wherein an end portion of the tube is inserted into the slot after the first member and the second member are assembled. 前記チューブの端部は、前記チューブの長手方向に対して屈曲したことを特徴とする請求項３乃至１７のいずれか記載の熱交換器。The heat exchanger according to any one of claims 3 to 17, wherein an end of the tube is bent with respect to a longitudinal direction of the tube. 前記チューブの端部は、前記スロットに挿入する前に屈曲したことを特徴とする請求項１８記載の熱交換器。The heat exchanger according to claim 18, wherein an end portion of the tube is bent before being inserted into the slot. 前記チューブの端部は、前記スロットに挿入した後に屈曲したことを特徴とする請求項１８記載の熱交換器。The heat exchanger according to claim 18, wherein the end of the tube is bent after being inserted into the slot. 当該熱交換器は、前記冷媒を循環する冷凍サイクルに用いられ、前記冷凍サイクルは、高圧側の圧力が前記冷媒の臨界点を超えることを特徴とする請求項３乃至２０のいずれか記載の熱交換器。The heat according to any one of claims 3 to 20, wherein the heat exchanger is used in a refrigeration cycle for circulating the refrigerant, and the refrigeration cycle has a high-pressure side pressure exceeding a critical point of the refrigerant. Exchanger. 高圧側の圧力が冷媒の臨界点を超える冷凍サイクルの熱交換器であり、前記冷媒を流通する偏平状のチューブ及び波型のフィンを積層してなるコアと、前記チューブの端部を挿入するスロットを設けたタンクとを備え、前記コアに対して通風がなされるとともに前記コアに伝わる熱にて前記冷媒の熱交換を行う熱交換器において、
前記コアとしては、前記通風方向に重ねられた第１コア及び第２コアを備え、
前記第１コア及び前記第２コアの一方の側部において、前記第１コアのチューブの端部を挿入する前記タンクには前記冷媒の入口部を設け、且つ前記第２コアのチューブの端部を挿入する前記タンクには前記冷媒の出口部を設け、これらのタンクの位置は前記通風方向と直交する方向にずらすとともに、前記入口部及び前記出口部は前記通風方向の風上側又は風下側に揃えて向けたことを特徴とする熱交換器。A heat exchanger for a refrigeration cycle in which the pressure on the high pressure side exceeds the critical point of the refrigerant, and a core formed by laminating a flat tube and a corrugated fin that circulates the refrigerant, and an end of the tube are inserted. A heat exchanger for exchanging heat of the refrigerant with heat transmitted to the core and ventilating to the core.
The core includes a first core and a second core stacked in the ventilation direction,
In one side of the first core and the second core, the tank into which the end of the tube of the first core is inserted is provided with an inlet for the refrigerant, and the end of the tube of the second core The tank into which the refrigerant is inserted is provided with an outlet for the refrigerant, the positions of these tanks are shifted in a direction perpendicular to the ventilation direction, and the inlet and the outlet are on the upwind side or downwind side in the ventilation direction. A heat exchanger characterized by being aligned.
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