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JP2011247448A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
JP2011247448A
JP2011247448A JP2010118198A JP2010118198A JP2011247448A JP 2011247448 A JP2011247448 A JP 2011247448A JP 2010118198 A JP2010118198 A JP 2010118198A JP 2010118198 A JP2010118198 A JP 2010118198A JP 2011247448 A JP2011247448 A JP 2011247448A
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Japan
Prior art keywords
bent portion
heat exchanger
tube
flat
fin
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Granted
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JP2010118198A
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Japanese (ja)
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JP5421859B2 (en
Inventor
Yuichi Matsumoto
雄一 松元
Yusuke Iino
祐介 飯野
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Sanden Corp
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Sanden Corp
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Publication date
Application filed by Sanden Corp filed Critical Sanden Corp
Priority to JP2010118198A priority Critical patent/JP5421859B2/en
Priority to US13/700,000 priority patent/US20130068438A1/en
Priority to CN201180024019.4A priority patent/CN102893117B/en
Priority to DE112011101771T priority patent/DE112011101771T5/en
Priority to PCT/JP2011/060832 priority patent/WO2011148785A1/en
Publication of JP2011247448A publication Critical patent/JP2011247448A/en
Application granted granted Critical
Publication of JP5421859B2 publication Critical patent/JP5421859B2/en
Expired - Fee Related legal-status Critical Current
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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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/30—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being attachable to the element
    • 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
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/08—Fins with openings, e.g. louvers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

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  • 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

PROBLEM TO BE SOLVED: To provide a heat exchanger configured so that a reduction in the heat exchange efficiency thereof is suppressed and that the drainability of the tubes and the fins is improved.SOLUTION: The heat exchanger is provided with: tubes 110 having flat surfaces 115 facing each other with predetermined gaps provided therebetween; and fins 120 having bent sections 122 (122a, 122b) and flat sections 121 which are formed alternately in the longitudinal direction, the bent sections 122 (122a, 122b) being joined to the opposing flat surfaces 115 of the tubes 110. The fins 120 are each configured in such a manner that a predetermined range (bent section 122c) of each of the bent sections 122a on the side in contact with one flat surface 115 of the opposing flat surfaces 115 is bent toward the other of the opposing flat surfaces 115 side and joined to the other flat surfaces 115 to form a communication passage 125.

Description

本発明は、熱交換器に関し、特に熱交換器におけるフィンの構造に関する。   The present invention relates to a heat exchanger, and more particularly to the structure of fins in a heat exchanger.

従来、熱交換器は例えば空気調和装置等に利用されている。空気調和装置は例えば室内用熱交換器及び室外用熱交換器を備えるもので、冷房運転の場合には室内用熱交換器に、暖房運転の場合には室外用熱交換器に結露による凝縮水が生じやすいことが知られている。凝縮水は、熱交換器のチューブとフィンとの間に滞留しやすく、空気の流れを阻害し熱交換の効率を低下させる原因となるだけでなく、例えば暖房運転時の室外用熱交換器における着霜の原因にもなっている。   Conventionally, heat exchangers are used in, for example, air conditioners. The air conditioner includes, for example, an indoor heat exchanger and an outdoor heat exchanger. In the cooling operation, the indoor heat exchanger is used. In the heating operation, the outdoor heat exchanger is condensed with condensed water. Is known to occur easily. Condensed water tends to stay between the tubes and fins of the heat exchanger, which not only obstructs the flow of air and reduces the efficiency of heat exchange, but also, for example, in outdoor heat exchangers during heating operation It also causes frost formation.

そこで、例えば特許文献１に示されるように、熱交換器に滞留した凝縮水を排水するために、上下方向に配設される扁平伝熱管（チューブ）の間に、斜状部と湾曲部よりなるコルゲートフィンをロウ付けにより接合し、コルゲートフィンの湾曲部に対し上下方向に貫通するスリットを複数箇所に形成した熱交換器が考案されている。   Therefore, for example, as shown in Patent Document 1, in order to drain the condensed water staying in the heat exchanger, between the flat heat transfer tubes (tubes) arranged in the vertical direction, the slanted portion and the curved portion are used. A heat exchanger has been devised in which corrugated fins are joined by brazing and slits penetrating in a vertical direction with respect to the curved portion of the corrugated fin are formed at a plurality of locations.

確かに、このような熱交換器によれば、扁平伝熱管及びコルゲートフィンの表面に対して結露により生じた凝縮水は、コルゲートフィンの湾曲部に形成されたスリットから下方に導かれるものと考えられる。   Certainly, according to such a heat exchanger, the condensed water generated by condensation on the surface of the flat heat transfer tube and the corrugated fin is considered to be guided downward from the slit formed in the curved portion of the corrugated fin. It is done.

特開２００６−１０５４１５号公報（請求項１、段落番号００１５〜００１８、図３）JP 2006-105415 A (Claim 1, paragraph numbers 0015 to 0018, FIG. 3)

しかしながら、コルゲートフィンの湾曲部は扁平伝熱管と接合される部分であり、この部分の接触によって扁平伝熱管とコルゲートフィンとの熱の移動が行われるものである。そのため、特許文献１に記載された熱交換器のように、コルゲートフィンの湾曲部にスリットを形成してしまうと、コルゲートフィンと扁平伝熱管との接触面積が減少して、熱交換の効率が低下してしまう虞があった。   However, the curved portion of the corrugated fin is a portion joined to the flat heat transfer tube, and heat transfer between the flat heat transfer tube and the corrugated fin is performed by contact of this portion. Therefore, if the slit is formed in the curved portion of the corrugated fin as in the heat exchanger described in Patent Document 1, the contact area between the corrugated fin and the flat heat transfer tube is reduced, and the efficiency of heat exchange is reduced. There was a risk of lowering.

本発明は、上述のような問題を解決することを課題の一例とするものであり、熱交換の効率の低下を抑制しつつ、チューブ及びフィンの排水性を向上させた熱交換器を提供することを目的とする。   This invention makes it an example of a subject to solve the above problems, and provides the heat exchanger which improved the drainage property of the tube and the fin, suppressing the fall of the efficiency of heat exchange. For the purpose.

このような課題を解決するため、本発明による熱交換器は、所定の間隔をあけて対向する面を有するチューブと、折曲部及び平坦部が長手方向に交互に形成され、前記折曲部が前記チューブの対向する面に接合されるフィンとを備え、前記フィンは、対向する面のうち一方の面に接する側の折曲部の短手方向の所定範囲が、対向する他方の面側に折曲し、該他方の面に接合することで連通路を形成していることを特徴とする。
また、前記フィンは、前記折曲部の短手方向の所定範囲に、長手方向の切れ込みが設けられ、該切れ込み部分が、対向する他方の面側に折曲し、該他方の面に接合することで前記連通路を形成していることを特徴とする。
また、前記連通路は、対向する面のうち一方の面に接する側の折曲部と他方の面に接する折曲部とにそれぞれ設けられることを特徴とする。
また、対向する面のうち一方の面に接する側の折曲部に設けられる連通路の短手方向の範囲は、他方の面に接する折曲部に設けられる連通路の短手方向の範囲と重複することを特徴とする。 In order to solve such a problem, the heat exchanger according to the present invention includes a tube having a surface opposed to each other with a predetermined interval, a bent portion, and a flat portion that are alternately formed in the longitudinal direction. Is provided with a fin joined to the opposing surface of the tube, and the fin has a predetermined range in the short direction of the bent portion on the side in contact with one of the opposing surfaces, the other surface facing It is characterized in that a communication path is formed by bending it to the other surface and joining it to the other surface.
In addition, the fin is provided with a cut in the longitudinal direction in a predetermined range in the short direction of the bent portion, and the cut portion is bent to the other surface facing and joined to the other surface. Thus, the communication path is formed.
In addition, the communication path is provided in each of a bent portion that is in contact with one of the opposing surfaces and a bent portion that is in contact with the other surface.
In addition, the range in the short direction of the communication path provided in the bent portion on the side in contact with one of the opposing surfaces is the range in the short direction of the communication path provided in the bent portion in contact with the other surface. It is characterized by overlapping.

本発明によれば、熱交換の効率の低下を抑制しつつ、チューブ及びフィンの排水性を向上させた熱交換器を提供することができる。   ADVANTAGE OF THE INVENTION According to this invention, the heat exchanger which improved the drainage property of the tube and the fin can be provided, suppressing the fall of the efficiency of heat exchange.

本発明の一実施の形態に係る熱交換器の正面模式図である。It is a front schematic diagram of the heat exchanger which concerns on one embodiment of this invention. 本発明の一実施の形態に係る熱交換器におけるフィンの斜視図である。It is a perspective view of the fin in the heat exchanger which concerns on one embodiment of this invention. 本発明の一実施の形態に係る熱交換器におけるフィンの斜視図である。It is a perspective view of the fin in the heat exchanger which concerns on one embodiment of this invention. （ａ）本発明の一実施の形態に係る熱交換器におけるフィンの平面図である。（ｂ）同側面図である。（ｃ）（ａ）におけるＡ−Ａ断面図である。(A) It is a top view of the fin in the heat exchanger which concerns on one embodiment of this invention. (B) It is the side view. (C) It is AA sectional drawing in (a). 本発明の他の実施の形態に係る熱交換器におけるフィンの斜視図である。It is a perspective view of the fin in the heat exchanger which concerns on other embodiment of this invention. （ａ）本発明の他の実施の形態に係る熱交換器におけるフィンの平面図である。（ｂ）同側面図である。（ｃ）（ａ）におけるＢ−Ｂ断面図である。(A) It is a top view of the fin in the heat exchanger which concerns on other embodiment of this invention. (B) It is the side view. (C) It is BB sectional drawing in (a). 本発明のさらに他の実施の形態に係る熱交換器におけるフィンの斜視図である。It is a perspective view of the fin in the heat exchanger which concerns on other embodiment of this invention. （ａ）本発明のさらに他の実施の形態に係る熱交換器におけるフィンの平面図である。（ｂ）同側面図である。（ｃ）（ａ）におけるＣ−Ｃ断面図である。（ｄ）（ａ）におけるＤ−Ｄ断面図である。(A) It is a top view of the fin in the heat exchanger which concerns on other embodiment of this invention. (B) It is the side view. (C) It is CC sectional drawing in (a). (D) It is DD sectional drawing in (a). 熱交換器を備えた空気調和装置の一例を示す構成図である。It is a block diagram which shows an example of the air conditioning apparatus provided with the heat exchanger. （ａ）フィンの変形例を示す模式図である。（ｂ）フィンの他の変形例を示す模式図である。(A) It is a schematic diagram which shows the modification of a fin. (B) It is a schematic diagram which shows the other modification of a fin.

以下、本発明の実施形態について図面を参照しながら具体的に説明する。便宜上、同一の作用効果を奏する部分には同一の符号を付け、その説明を省略する。
（実施の形態１）
図１に示すように、熱交換器１００は、冷媒が流通する複数のチューブ１１０が並設され、隣接するチューブ１１０間にフィン１２０がロウ付けによって接合されて構成されている。図示例において、複数のチューブ１１０の長手方向（冷媒の流通方向）の両端にはそれぞれ中空のヘッダタンク１３０，１３５が連通されており、上部側に設けられたヘッダタンク１３０は、一端側に冷媒の入口部１３０ａが、他端側に冷媒の出口部１３０ｂが設けられ、中央には内部を隔絶する仕切板１３１が設けられている。これにより、ヘッダタンク１３０の入口部１３０ａから流入した冷媒は、仕切板１３１よりも入口部１３０ａ側に連通されたチューブ１１０（図１において左側の２本）を流通して下部側に設けられたヘッダタンク１３５に流入する。そして、該ヘッダタンク１３５から仕切板よりも出口部１３０ｂ側に連通されたチューブ１１０（図１において右側の２本）を流通して、ヘッダタンク１３０を介して出口部１３０ｂから流出する。なお、図１は熱交換器１００を模式的に表したものであり、説明の簡単のために簡略化されているものである。 Hereinafter, embodiments of the present invention will be specifically described with reference to the drawings. For the sake of convenience, the same reference numerals are given to the portions having the same operational effects, and the description thereof is omitted.
(Embodiment 1)
As shown in FIG. 1, the heat exchanger 100 is configured such that a plurality of tubes 110 through which a refrigerant flows are arranged in parallel, and fins 120 are joined between adjacent tubes 110 by brazing. In the illustrated example, hollow header tanks 130 and 135 are communicated with both ends of the plurality of tubes 110 in the longitudinal direction (circulation direction of the refrigerant), respectively, and the header tank 130 provided on the upper side has a refrigerant on one end side. The inlet portion 130a is provided with a refrigerant outlet portion 130b on the other end side, and a partition plate 131 is provided in the center to isolate the inside. As a result, the refrigerant flowing from the inlet portion 130a of the header tank 130 flows through the tubes 110 (two on the left side in FIG. 1) connected to the inlet portion 130a side of the partition plate 131 and is provided on the lower side. It flows into the header tank 135. Then, the tube 110 (two on the right side in FIG. 1) communicated from the header tank 135 to the outlet portion 130 b side than the partition plate flows and flows out from the outlet portion 130 b through the header tank 130. FIG. 1 schematically shows the heat exchanger 100 and is simplified for the sake of simplicity.

チューブ１１０は、図２に示すように、熱伝導率の高いアルミニウム等の金属により扁平な中空の板状に形成されている。そして、内側の空間には長手方向に延びる複数の流路１１１が短手方向（幅方向）に並設されるように複数の仕切部１１３が設けられている。図１に示すように、複数のチューブ１１０は、平面１１５同士が対向するように所定の間隔をあけて均等に並設されており、隣接するチューブ１１０同士の対向する平面１１５にフィン１２０が接合するようになっている。チューブ１１０の長手方向の両端部１１０ａ，１１０ｂはヘッダタンク１３０，１３５に設けられた挿入孔に挿嵌され、ロウ付けされるものである。   As shown in FIG. 2, the tube 110 is formed in a flat hollow plate shape by a metal such as aluminum having high thermal conductivity. In the inner space, a plurality of partition portions 113 are provided so that a plurality of flow paths 111 extending in the longitudinal direction are juxtaposed in the short direction (width direction). As shown in FIG. 1, the plurality of tubes 110 are evenly arranged at predetermined intervals so that the flat surfaces 115 face each other, and the fins 120 are joined to the flat surfaces 115 facing the adjacent tubes 110. It is supposed to be. Both ends 110a and 110b in the longitudinal direction of the tube 110 are inserted into insertion holes provided in the header tanks 130 and 135 and brazed.

図３及び図４に示すように、フィン１２０は、いわゆるコルゲートフィンであり、平坦な板状である平坦部１２１と、所定の曲率半径をもって折曲する折曲部１２２とが長手方向に交互に形成されて構成されている。折曲部１２２はチューブ１１０の平面１１５に接合する部分であり、対向する一方のチューブ１１０の平面１１５に接合する第１の折曲部１２２ａと、対向する他方のチューブ１１０の平面１１５に接合する第２の折曲部１２２ｂとからなる（図１参照）。図示例では、断面形状が半円弧状に形成された折曲部１２２（１２２ａ、１２２ｂ）に平坦部１２１が滑らかに連続して設けられており、これにより、隣り合った平坦部１２１同士は互いに平行となっている。また、チューブ１１０に接合された場合には、平坦部１２１がチューブ１１０の長手方向に対して垂直となる。なお、フィン１２０は、チューブ同様に熱伝導率の高いアルミニウム等の金属により形成されるものである。   As shown in FIG. 3 and FIG. 4, the fin 120 is a so-called corrugated fin, and flat portions 121 that are flat plates and bent portions 122 that bend with a predetermined radius of curvature are alternately arranged in the longitudinal direction. Formed and configured. The bent portion 122 is a portion that is bonded to the flat surface 115 of the tube 110, and is bonded to the first bent portion 122 a that is bonded to the flat surface 115 of the opposite one tube 110 and the flat surface 115 of the other opposite tube 110. It consists of the 2nd bending part 122b (refer FIG. 1). In the illustrated example, the flat portion 121 is provided smoothly and continuously on the bent portion 122 (122a, 122b) having a cross-sectional shape formed in a semicircular arc shape, whereby the adjacent flat portions 121 are mutually connected. It is parallel. Further, when joined to the tube 110, the flat portion 121 is perpendicular to the longitudinal direction of the tube 110. The fin 120 is formed of a metal such as aluminum having a high thermal conductivity like the tube.

第１の折曲部１２２ａの短手方向（幅方向）の所定範囲（図示例では中央付近であり、図４（ａ）の如く平面視において切欠状に示される）には、長手方向に沿った２条の切れ込みが、第１の折曲部１２２ａに連続する平坦部１２１の中間位置まで設けられている。そして、２条の切れ込みの範囲内のフィンが、第１の折曲部１２２ａの凸状側に対して反対側に凸状となるように、平坦部１２１の長手方向における中間位置から折り返され、第３の折曲部１２２ｃが形成される。２条の切れ込みによって形成された第３の折曲部１２２ｃは、対向する他方のチューブ１１０の平面１１５に接合するように、第２の折曲部１２２ｂの位置まで延在することになる。   A predetermined range in the short side direction (width direction) of the first bent portion 122a (in the illustrated example, near the center and shown as a notch in plan view as shown in FIG. 4A) is along the longitudinal direction. The two notches are provided up to an intermediate position of the flat portion 121 continuous with the first bent portion 122a. And the fin within the range of the notch of the two strips is folded back from the intermediate position in the longitudinal direction of the flat portion 121 so as to be convex on the opposite side to the convex side of the first bent portion 122a, A third bent portion 122c is formed. The third bent portion 122c formed by the two slits extends to the position of the second bent portion 122b so as to be joined to the flat surface 115 of the other tube 110 facing each other.

図４（ｂ）に示すように、第３の折曲部１２２ｃは、第１の折曲部１２２ａ及び第２の折曲部１２２ｂにおける曲率半径より小さな曲率半径を有し、また、この曲率半径は平坦部１２１における折り返し部１２３の曲率半径と略同じとなっている。なお、切れ込みの長さが平坦部１２１の長手方向における中間位置までである例を示したが、これは、第３の折曲部１２２ｃの曲率半径及び平坦部１２１における折り返し部１２３の曲率半径に応じて、対向する他方のチューブ１１０の平面１１５に接合可能なように適宜変更できるものである。   As shown in FIG. 4B, the third bent portion 122c has a radius of curvature smaller than the radius of curvature at the first bent portion 122a and the second bent portion 122b, and this radius of curvature. Is substantially the same as the radius of curvature of the folded portion 123 in the flat portion 121. In addition, although the example in which the length of the cut is up to the middle position in the longitudinal direction of the flat portion 121 is shown, this corresponds to the radius of curvature of the third bent portion 122c and the radius of curvature of the folded portion 123 in the flat portion 121. Accordingly, it can be appropriately changed so that it can be joined to the flat surface 115 of the other opposite tube 110.

このように、第１の折曲部１２２ａの短手方向の所定範囲に対して第３の折曲部１２２ｃを長手方向に連続して形成することで、第１の折曲部１２２ａ側の短手方向の所定範囲（第３の折曲部の幅）にチューブ１１０の長手方向に沿った連通路１２５（図３において矢印で示す）が形成される。これにより、フィン１２０内やフィン１２０とチューブ１１０との間に滞留した凝縮水は連通路１２５を通って下方に排水されやすくなる。   In this way, the third bent portion 122c is continuously formed in the longitudinal direction with respect to the predetermined range in the short direction of the first bent portion 122a, so that the first bent portion 122a side is short. A communication path 125 (indicated by an arrow in FIG. 3) along the longitudinal direction of the tube 110 is formed in a predetermined range in the hand direction (the width of the third bent portion). Thereby, the condensed water staying in the fin 120 or between the fin 120 and the tube 110 is easily drained downward through the communication path 125.

また、図１に示すように、第１の折曲部１２２ａは対向する一方のチューブ１１０の面に対して、第２の折曲部１２２ｂ及び第３の折曲部１２２ｃは対向する他方のチューブ１１０の面に対して、それぞれロウ付けによって接合されている。これにより、第３の折曲部１２２ｃを設けた場合と、設けない場合とで、対向する一対のチューブ１１０，１１０に対するフィン１２０の総接触面積が同等であり、熱交換効率が低下してしまうことを抑制することができる。   In addition, as shown in FIG. 1, the second bent portion 122b and the third bent portion 122c are the other tube facing the surface of the one tube 110 facing the first bent portion 122a. Each of the surfaces 110 is joined by brazing. As a result, the total contact area of the fin 120 with respect to the pair of tubes 110 and 110 facing each other is the same when the third bent portion 122c is provided and when the third bent portion 122c is not provided, and the heat exchange efficiency is reduced. This can be suppressed.

（実施の形態２）
図５及び図６に、実施の形態２による熱交換器２００におけるフィン２２０を示す。なお、実施の形態２による熱交換器２００は、実施の形態１による熱交換器１００におけるフィン１２０に対して、実施の形態１とは異なる構造のフィン２２０が設けられた構成を有するため、ここではフィン２２０以外の説明を省略する。 (Embodiment 2)
5 and 6 show the fins 220 in the heat exchanger 200 according to the second embodiment. The heat exchanger 200 according to the second embodiment has a configuration in which fins 220 having a structure different from that of the first embodiment are provided to the fins 120 in the heat exchanger 100 according to the first embodiment. Then, explanations other than the fins 220 are omitted.

図５及び図６に示すように、フィン２２０は、いわゆるコルゲートフィンであり、平坦な板状である平坦部２２１と、所定の曲率半径をもって折曲する折曲部２２２とが長手方向に交互に形成されて構成されている。折曲部２２２はチューブ１１０の平面１１５に接合する部分であり、対向する一方のチューブ１１０の平面１１５に接合する第１の折曲部２２２ａと、対向する他方のチューブ１１０の平面１１５に接合する第２の折曲部２２２ｂとからなる。図示例では、断面形状が半円弧状に形成された折曲部２２２ａ，２２２ｂに平坦部２２１が滑らかに連続して設けられており、これにより、隣り合った平坦部２２１同士は互いに平行となっている。また、チューブ１１０に接合された場合には、平坦部２２１がチューブ１１０の長手方向に対して垂直となる。なお、フィン２２０は、チューブ同様に熱伝導率の高いアルミニウム等の金属により形成されるものである。   As shown in FIGS. 5 and 6, the fin 220 is a so-called corrugated fin, and flat portions 221 that are flat plates and bent portions 222 that bend with a predetermined radius of curvature are alternately arranged in the longitudinal direction. Formed and configured. The bent portion 222 is a portion that is bonded to the flat surface 115 of the tube 110, and is bonded to the first bent portion 222 a that is bonded to the flat surface 115 of the opposite one tube 110 and the flat surface 115 of the other opposite tube 110. It consists of the 2nd bending part 222b. In the illustrated example, the flat portions 221 are smoothly and continuously provided in the bent portions 222a and 222b whose cross-sectional shape is formed in a semicircular arc shape, so that the adjacent flat portions 221 are parallel to each other. ing. Further, when joined to the tube 110, the flat portion 221 is perpendicular to the longitudinal direction of the tube 110. The fins 220 are formed of a metal such as aluminum having a high thermal conductivity like the tube.

第１の折曲部２２２ａの短手方向の所定範囲（図示例では中央付近）には、長手方向に沿った２条の切れ込みが、第１の折曲部２２２ａに連続する平坦部２２１の中間位置まで設けられている。そして、２条の切れ込みの範囲内のフィンが、第１の折曲部２２２ａの凸状側に対して反対側に凸状となるように、平坦部２２１の長手方向における中間位置から折り返され、第３の折曲部２２２ｃが形成される。２条の切れ込みによって形成された第３の折曲部２２２ｃは、対向する他方のチューブ１１０の平面１１５に接合するように、第２の折曲部２２２ｂの位置まで延在することになる。   In a predetermined range in the short direction of the first bent portion 222a (near the center in the illustrated example), two notches along the longitudinal direction are intermediate between the flat portions 221 that are continuous with the first bent portion 222a. To the position. Then, the fins within the range of the two notches are folded back from the intermediate position in the longitudinal direction of the flat portion 221 so as to be convex on the opposite side to the convex side of the first bent portion 222a, A third bent portion 222c is formed. The third bent portion 222c formed by the two slits extends to the position of the second bent portion 222b so as to be joined to the flat surface 115 of the other opposite tube 110.

そして、第２の折曲部２２２ｂの短手方向において、第３の折曲部２２２ｃの短手方向の範囲と重複し、この範囲より広い所定の範囲には、長手方向に沿った２条の切れ込みが、第２の折曲部２２２ｂに連続する平坦部２２１の中間位置まで設けられている。そして、２条の切れ込みの範囲内のフィン２２０が、第２の折曲部２２２ｂの凸状側に対して反対側に凸状となるように、平坦部２２１の長手方向における中間位置から折り返され、第４の折曲部２２２ｄが形成される。２条の切れ込みによって形成された第４の折曲部２２２ｄは、対向する一方のチューブ１１０の平面１１５に接合するように、第１の折曲部２２２ａの位置まで延在することになる。   Then, in the short direction of the second bent portion 222b, it overlaps with the short direction range of the third bent portion 222c, and in a predetermined range wider than this range, there are two strips along the longitudinal direction. The notch is provided up to an intermediate position of the flat portion 221 continuous with the second bent portion 222b. Then, the fins 220 within the range of the two notches are folded back from an intermediate position in the longitudinal direction of the flat portion 221 so as to be convex on the opposite side to the convex side of the second bent portion 222b. A fourth bent portion 222d is formed. The fourth bent portion 222d formed by the two cuts extends to the position of the first bent portion 222a so as to be joined to the flat surface 115 of the opposite one of the tubes 110.

図６（ｂ）に示すように、第３の折曲部２２２ｃ及び第４の折曲部２２２ｄは第１の折曲部２２２ａ及び第２の折曲部２２２ｂにおける曲率半径より小さな曲率半径を有し、また、この曲率半径は平坦部２２１における折り返し部２２３の曲率半径と略同じとなっている。なお、切れ込みの長さは、平坦部２２１の長手方向における中間位置までである例を示したが、これは、第３の折曲部２２２ｃ及び第４の折曲部２２２ｄの曲率半径及び平坦部２２１における折り返し部２２３の曲率半径に応じて適宜変更されるものである。   As shown in FIG. 6B, the third bent portion 222c and the fourth bent portion 222d have a radius of curvature smaller than that of the first bent portion 222a and the second bent portion 222b. In addition, this curvature radius is substantially the same as the curvature radius of the folded portion 223 in the flat portion 221. Although the example in which the length of the cut is up to an intermediate position in the longitudinal direction of the flat portion 221 is shown, this is because the curvature radius and the flat portion of the third bent portion 222c and the fourth bent portion 222d are shown. This is appropriately changed according to the radius of curvature of the folded portion 223 at 221.

このように、第１の折曲部２２２ａの短手方向の所定範囲に対して第３の折曲部２２２ｃを長手方向に連続して形成することで、第１の折曲部２２２ａ側の短手方向の所定範囲（第３の折曲部２２２ｃの幅）にチューブ１１０の長手方向に沿った連通路２２５ａ（図５において矢印で示す）が形成される。これにより、フィン２２０内やフィン２２０とチューブ１１０との間に滞留した凝縮水は連通路２２５ａを通って下方に排出されることになる。なお、連通路２２５ａを塞ぐように第４の折曲部２２２ｄが配置されるため、凝縮水は連通路２２５ａと第４の折曲部２２２ｄとの間を縫うようにして排水されるものである。   In this way, the third bent portion 222c is continuously formed in the longitudinal direction with respect to the predetermined range in the short direction of the first bent portion 222a, whereby the first bent portion 222a side is shortened. A communication path 225a (indicated by an arrow in FIG. 5) along the longitudinal direction of the tube 110 is formed in a predetermined range in the hand direction (the width of the third bent portion 222c). As a result, the condensed water staying in the fin 220 or between the fin 220 and the tube 110 is discharged downward through the communication path 225a. In addition, since the 4th bending part 222d is arrange | positioned so that the communication path 225a may be block | closed, condensed water is drained so that it may sew between the communication path 225a and the 4th bending part 222d. .

また、第２の折曲部２２２ｂの短手方向の所定範囲に対して第４の折曲部２２２ｄを長手方向に連続して形成することで、第２の折曲部２２２ｂ側の短手方向の所定範囲（第４の折曲部２２２ｄの幅）にチューブ１１０の長手方向に沿った連通路２２５ｂ（図５において矢印で示す）が形成される。これにより、フィン２２０内やフィン２２０とチューブ１１０との間に滞留した凝縮水は連通路２２５ｂを通って下方に排出されることになる。なお、連通路２２５ｂには第３の折曲部２２２ｃが配置されているため、連通路２２５ｂの両側方のみが直線状に連通することになる。   Further, the fourth bent portion 222d is continuously formed in the longitudinal direction with respect to a predetermined range in the shorter direction of the second bent portion 222b, so that the shorter direction on the second bent portion 222b side is formed. A communication path 225b (indicated by an arrow in FIG. 5) along the longitudinal direction of the tube 110 is formed in a predetermined range (the width of the fourth bent portion 222d). Thereby, the condensed water staying in the fin 220 or between the fin 220 and the tube 110 is discharged downward through the communication path 225b. In addition, since the 3rd bending part 222c is arrange | positioned at the communicating path 225b, only the both sides of the communicating path 225b communicate in a linear form.

また、第１の折曲部２２２ａ及び第４の折曲部２２２ｄは対向する一方のチューブ１１０の平面１１５に、第２の折曲部２２２ｂ及び第３の折曲部２２２ｃは対向する他方のチューブ１１０の平面１１５にロウ付けによって接合されている。これにより、第３の折曲部２２２ｃ及び第４の折曲部２２２ｄを設けた場合と、設けない場合とで、対向する一対のチューブ１１０，１１０に対するフィン２２０の総接触面積が同等であり、熱交換効率が低下してしまうことを抑制することができる。   Further, the first bent portion 222a and the fourth bent portion 222d are on the flat surface 115 of the opposite one tube 110, and the second bent portion 222b and the third bent portion 222c are the other opposite tube. It is joined to the plane 115 of 110 by brazing. Thereby, the total contact area of the fins 220 with respect to the pair of tubes 110 and 110 facing each other is the same when the third bent portion 222c and the fourth bent portion 222d are provided and when not provided. It can suppress that heat exchange efficiency falls.

（実施の形態３）
図７及び図８に、実施の形態３による熱交換器３００におけるフィン３２０を示す。なお、実施の形態３による熱交換器３００は、実施の形態１による熱交換器１００におけるフィン１２０に対して実施の形態１とは異なる構造のフィン３２０が設けられた構成を有するため、ここではフィン３２０以外の説明を省略する。 (Embodiment 3)
7 and 8 show fins 320 in heat exchanger 300 according to the third embodiment. The heat exchanger 300 according to the third embodiment has a configuration in which fins 320 having a structure different from that of the first embodiment are provided to the fins 120 in the heat exchanger 100 according to the first embodiment. Descriptions other than the fins 320 are omitted.

図７及び図８に示すように、フィン３２０は、いわゆるコルゲートフィンであり、平坦な板状である平坦部３２１と、所定の曲率半径をもって折曲する折曲部３２２とが長手方向に交互に形成されて構成されている。折曲部３２２はチューブ１１０の平面１１５に接合する部分であり、対向する一方のチューブ１１０の平面１１５に接合する第１の折曲部３２２ａと、対向する他方のチューブ１１０の平面１１５に接合する第２の折曲部３２２ｂとからなる。図示例では、断面形状が半円弧状に形成された折曲部３２２に平坦部３２１が滑らかに連続して設けられるようになっており、これにより、隣り合った平坦部３２１同士は互いに平行となっている。また、チューブ１１０に接合された場合には、平坦部３２１がチューブ１１０の長手方向に対して垂直となる。なお、フィン３２０は、チューブ同様に熱伝導率の高いアルミニウム等の金属により形成されるものである。   As shown in FIGS. 7 and 8, the fin 320 is a so-called corrugated fin, and flat portions 321 each having a flat plate shape and bent portions 322 that are bent with a predetermined radius of curvature are alternately arranged in the longitudinal direction. Formed and configured. The bent portion 322 is a portion that is bonded to the flat surface 115 of the tube 110, and is bonded to the first bent portion 322 a that is bonded to the flat surface 115 of the opposite one tube 110 and the flat surface 115 of the other opposite tube 110. It consists of the 2nd bending part 322b. In the illustrated example, the flat portion 321 is provided smoothly and continuously on the bent portion 322 having a semicircular cross-sectional shape, so that the adjacent flat portions 321 are parallel to each other. It has become. Further, when joined to the tube 110, the flat portion 321 is perpendicular to the longitudinal direction of the tube 110. Note that the fin 320 is formed of a metal such as aluminum having a high thermal conductivity like the tube.

第１の折曲部３２２ａにおいて短手方向の一方側の所定範囲（図８（ａ）に示す例では中央より左側の所定範囲）には、長手方向に沿った２条の切れ込みが、第１の折曲部３２２ａに連続する平坦部３２１の中間位置まで設けられている。そして、２条の切れ込みの範囲内のフィンが、第１の折曲部３２２ａの凸状側に対して反対側に凸状となるように、平坦部３２１の長手方向における中間位置から折り返され、第３の折曲部３２２ｃが形成される。２条の切れ込みによって形成された第３の折曲部３２２ｃは、対向する他方のチューブ１１０の平面１１５に接合するように、第２の折曲部３２２ｂの位置まで延在することになる。   In the first bent portion 322a, a predetermined range on one side in the short side direction (a predetermined range on the left side from the center in the example shown in FIG. 8A) has two cuts along the longitudinal direction. It is provided to the middle position of the flat part 321 continuing to the bent part 322a. And, the fin within the range of the notch of the two strips is folded back from the intermediate position in the longitudinal direction of the flat portion 321 so as to be convex on the opposite side to the convex side of the first bent portion 322a, A third bent portion 322c is formed. The third bent portion 322c formed by the two cuts extends to the position of the second bent portion 322b so as to be joined to the flat surface 115 of the other tube 110 facing each other.

そして、第２の折曲部３２２ｂにおいて短手方向の他方側の所定範囲（図８（ａ）に示す例では中央より右側の所定範囲）には、長手方向に沿った２条の切れ込みが、第２の折曲部３２２ｂに連続する平坦部３２１の中間位置まで設けられている。そして、２条の切れ込みの範囲内のフィンが、第２の折曲部３２２ｂの凸状側に対して反対側に凸状となるように、平坦部３２１の長手方向における中間位置から折り返され、第４の折曲部３２２ｄが形成される。２条の切れ込みによって形成された第４の折曲部３２２ｄは、対向する一方のチューブ１１０の平面１１５に接合するように、第１の折曲部３２２ａの位置まで延在することになる。なお、図示例では第３の折曲部３２２ｃの幅と第４の折曲部３２２ｄの幅とは同等となっている。   Then, in the second bent portion 322b, a predetermined range on the other side in the short side direction (predetermined range on the right side from the center in the example shown in FIG. 8A) has two notches along the longitudinal direction. The second bent portion 322b is provided up to an intermediate position of the flat portion 321 that is continuous with the second bent portion 322b. Then, the fins in the range of the two notches are folded back from the intermediate position in the longitudinal direction of the flat portion 321 so as to be convex on the opposite side to the convex side of the second bent portion 322b, A fourth bent portion 322d is formed. The fourth bent portion 322d formed by the two cuts extends to the position of the first bent portion 322a so as to be joined to the flat surface 115 of the opposite one tube 110. In the illustrated example, the width of the third bent portion 322c is equal to the width of the fourth bent portion 322d.

図８（ｂ）及び（ｃ）に示すように、第３の折曲部３２２ｃ及び第４の折曲部３２２ｄは第１の折曲部３２２ａ及び第２の折曲部３２２ｂにおける曲率半径より小さな曲率半径を有し、また、この曲率半径は平坦部３２１における折り返し部３２３の曲率半径と略同じとなっている。なお、切れ込みの長さは、平坦部３２１の長手方向における中間位置までである例を示したが、これは、第３の折曲部３２２ｃ及び第４の折曲部３２２ｄの曲率半径及び平坦部における折り返し部３２３の曲率半径に応じて適宜変更されるものである。   As shown in FIGS. 8B and 8C, the third bent portion 322c and the fourth bent portion 322d are smaller than the radii of curvature at the first bent portion 322a and the second bent portion 322b. The curvature radius is substantially the same as the curvature radius of the folded portion 323 in the flat portion 321. In addition, although the length of the notch showed the example which is to the intermediate position in the longitudinal direction of the flat part 321, this is the curvature radius and flat part of the 3rd bending part 322c and the 4th bending part 322d. Is appropriately changed according to the radius of curvature of the folded portion 323.

このように、第１の折曲部３２２ａの短手方向の所定範囲に対して、第３の折曲部３２２ｃを長手方向に連続して形成することで、第１の折曲部３２２ａ側の短手方向の所定範囲（第３の折曲部３２２ｃの幅）にチューブ１１０の長手方向に沿った連通路３２５ａ（図７において矢印で示す）が形成される。これにより、フィン３２０内やフィン３２０とチューブ１１０との間に滞留した凝縮水は連通路３２５ａを通って下方に排出されることになる。   As described above, the third bent portion 322c is continuously formed in the longitudinal direction with respect to the predetermined range in the short direction of the first bent portion 322a, so that the first bent portion 322a side is formed. A communication path 325a (indicated by an arrow in FIG. 7) along the longitudinal direction of the tube 110 is formed in a predetermined range in the short direction (the width of the third bent portion 322c). Thereby, the condensed water staying in the fin 320 or between the fin 320 and the tube 110 is discharged downward through the communication path 325a.

また、第２の折曲部３２２ｂの短手方向の所定範囲に対して第４の折曲部３２２ｄを長手方向に連続して形成することで、第２の折曲部３２２ｂ側の短手方向の所定範囲（第４の折曲部３２２ｄの幅）にフィン３２０の長手方向に向かう連通路３２５ｂ（図７において矢印で示す）が形成される。これにより、フィン３２０内やフィン３２０とチューブ１１０との間に滞留した凝縮水は連通路３２５ｂを通って下方に排出されることになる。   Further, the fourth bent portion 322d is continuously formed in the longitudinal direction with respect to a predetermined range in the shorter direction of the second bent portion 322b, so that the shorter direction on the second bent portion 322b side is formed. A communication path 325b (indicated by an arrow in FIG. 7) extending in the longitudinal direction of the fin 320 is formed in a predetermined range (the width of the fourth bent portion 322d). As a result, the condensed water staying in the fin 320 or between the fin 320 and the tube 110 is discharged downward through the communication path 325b.

また、第１の折曲部３２２ａ及び第４の折曲部３２２ｄは対向する一方のチューブ１１０の平面１１５に、第２の折曲部３２２ｂ及び第３の折曲部３２２ｃは対向する他方のチューブ１１０の平面１１５にロウ付けによって接合されている。これにより、第３の折曲部３２２ｃ及び第４の折曲部３２２ｄを設けた場合と、設けない場合とで、対向する一対のチューブ１１０に対するフィン３２０の総接触面積が同等であり、熱交換効率が低下してしまうことを抑制することができる。   In addition, the first bent portion 322a and the fourth bent portion 322d are on the flat surface 115 of one tube 110 facing each other, and the second bent portion 322b and the third bent portion 322c are the other tube facing each other. It is joined to the plane 115 of 110 by brazing. Accordingly, the total contact area of the fins 320 with respect to the pair of tubes 110 facing each other is the same in the case where the third bent portion 322c and the fourth bent portion 322d are provided and in the case where the fourth bent portion 322d is not provided. It can suppress that efficiency falls.

（使用例）
上記実施の形態１乃至３に例示した熱交換器（１００，２００，３００）が使用される一例として、例えば電気自動車等に設けられる空気調和装置１の全体の構成図を図９に示す。この空気調和装置１はいわゆるヒートポンプサイクルを利用したものであり、車外用の熱交換器１００Ａ及び車内用の熱交換器１００Ｂに対する圧縮機１１からの冷媒の流れを四方弁１３によって切り替えることで冷房と暖房の切換を行うものである。なお、熱交換器１００Ａ及び熱交換器１００Ｂは、熱交換器１００、２００及び３００のいずれかに対応するものであり、ここでは、実施の形態１における熱交換器１００に対応するものとして説明する。 (Example of use)
As an example in which the heat exchanger (100, 200, 300) exemplified in the first to third embodiments is used, FIG. 9 shows an overall configuration diagram of an air conditioner 1 provided in an electric vehicle, for example. The air conditioner 1 uses a so-called heat pump cycle, and the four-way valve 13 switches the flow of refrigerant from the compressor 11 to the vehicle heat exchanger 100A and the vehicle heat exchanger 100B. The heating is switched. The heat exchanger 100A and the heat exchanger 100B correspond to any of the heat exchangers 100, 200, and 300, and are described here as corresponding to the heat exchanger 100 in the first embodiment. .

図示例では、圧縮機１１の吐出口１１ａに四方弁１３が接続されている。これにより、圧縮機１１と車内用の熱交換器１００Ｂ及び車外用の熱交換器１００Ａとは、四方弁１３が破線に示される接続状態の場合（暖房運転）には圧縮機１１から吐出された冷媒が車内用の熱交換器１００Ｂに流入し、この車内用の熱交換器１００Ｂを通った冷媒が膨張弁１５を介して車外用の熱交換器１００Ａに流入し、さらに四方弁１３を介して圧縮機１１の吸入口１１ｂに戻るように接続されている。また、四方弁１３が実線に示される状態の場合（冷房運転）には圧縮機１１から吐出された冷媒が車外用の熱交換器１００Ａに流入し、この車外用の熱交換器１００Ａを通った冷媒が膨張弁１５を介して車内用の熱交換器１００Ｂに流入し、さらに四方弁１３を介して圧縮機１１の吸入口１１ｂに戻るように接続されている。なお、車外用の熱交換器１００Ａには冷却ファン１７が付設されている。   In the illustrated example, a four-way valve 13 is connected to the discharge port 11 a of the compressor 11. As a result, the compressor 11, the in-vehicle heat exchanger 100B, and the in-vehicle heat exchanger 100A are discharged from the compressor 11 when the four-way valve 13 is in the connected state indicated by the broken line (heating operation). The refrigerant flows into the in-vehicle heat exchanger 100B, the refrigerant that has passed through the in-vehicle heat exchanger 100B flows into the in-vehicle heat exchanger 100A through the expansion valve 15, and further through the four-way valve 13. The compressor 11 is connected so as to return to the suction port 11b. When the four-way valve 13 is in the state indicated by the solid line (cooling operation), the refrigerant discharged from the compressor 11 flows into the heat exchanger 100A for the outside of the vehicle and passes through the heat exchanger 100A for the outside of the vehicle. The refrigerant flows into the in-vehicle heat exchanger 100B through the expansion valve 15 and is further connected to return to the suction port 11b of the compressor 11 through the four-way valve 13. A cooling fan 17 is attached to the heat exchanger 100A for the outside of the vehicle.

空気調和装置１の車内側ユニットには、熱交換器１００Ｂが設けられた通風ダクト２０の上流側に吸入空気切替用のダンパ２１及びブロワ２３が設けられる。また、通風ダクト２０の下流側には、暖房補助用のヒータユニット２５が設けられ、該ヒータユニット２５を通過する空気量が排出空気切替用のダンパ２７によって調節される。通風ダクト２０の吹き出し口２９ａ，２９ｂ，２９ｃは、それぞれＤＥＦ、ＦＡＣＥ、ＦＯＯＴ用となっており、それぞれに設けられたダンパ３０ａ，３０ｂ，３０ｃによって吹き出し口２９ａ，２９ｂ，２９ｃからの空気量を調節可能となっている。   The vehicle interior unit of the air conditioner 1 is provided with an intake air switching damper 21 and a blower 23 upstream of the ventilation duct 20 in which the heat exchanger 100B is provided. Further, a heater unit 25 for heating assistance is provided on the downstream side of the ventilation duct 20, and the amount of air passing through the heater unit 25 is adjusted by a damper 27 for switching exhaust air. The outlets 29a, 29b, and 29c of the ventilation duct 20 are for DEF, FACE, and FOOT, respectively, and the amount of air from the outlets 29a, 29b, and 29c is adjusted by dampers 30a, 30b, and 30c provided respectively. It is possible.

このような空気調和装置１において、冷房運転の場合に車内用の熱交換器１００Ｂに結露による凝縮水が付着しても、凝縮水は熱交換器１００Ｂのフィン１２０に設けられた連通路２５を通って排水されることになる。また、暖房運転の場合に車外用の熱交換器１００Ａに凝縮水が付着しても、凝縮水は熱交換器１００Ａのフィン１２０に設けられた連通路２５を通って排水されることになる。   In such an air conditioner 1, even if condensed water due to condensation adheres to the in-vehicle heat exchanger 100B in the cooling operation, the condensed water passes through the communication passage 25 provided in the fins 120 of the heat exchanger 100B. It will be drained through. Further, in the case of heating operation, even if condensed water adheres to the external heat exchanger 100A, the condensed water is drained through the communication path 25 provided in the fin 120 of the heat exchanger 100A.

以上、本発明の実施の形態について図面を参照して詳述してきたが、具体的な構成はこれらの実施の形態に限られるものではなく、本発明の要旨を逸脱しない範囲の設計の変更等があっても本発明に含まれる。さらに、上述の各実施の形態は、その目的及び構成等に特に矛盾や問題がない限り、互いの技術を流用することができる。   As described above, the embodiments of the present invention have been described in detail with reference to the drawings. However, the specific configuration is not limited to these embodiments, and the design can be changed without departing from the scope of the present invention. Is included in the present invention. Furthermore, the above-described embodiments can utilize each other's technology as long as there is no particular contradiction or problem in the purpose, configuration, or the like.

例えば、複数のチューブが並設されている例を示したが、これに限られない。チューブの平面が対向して設けられ、該平面間にフィンが配置されている熱交換器に広く適用可能であり、例えば、１本のチューブが波状に形成されることによって１本のチューブにおいて対向する平面が形成される構成であっても構わない。   For example, an example in which a plurality of tubes are arranged in parallel has been shown, but the present invention is not limited to this. The present invention can be widely applied to heat exchangers in which the planes of the tubes are provided opposite to each other and fins are arranged between the planes. For example, one tube is formed in a wave shape to face each other in one tube. It may be configured to form a flat surface.

また、フィンにおける隣り合った平坦部が平行となっている例を示したが、これに限定されない。例えば、図１０（ａ）に示すように、隣り合った平坦部４２１が所定の角度をもって配置されるようにしても構わない。なお、図１０（ａ）の例は、第１の折曲部４２２ａ及び第２の折曲部４２２ｂにそれぞれ連通路が設けられるものであり、それぞれの連通路に凝縮水が流入し易くなっている。   Moreover, although the example which the adjacent flat part in a fin became parallel was shown, it is not limited to this. For example, as shown in FIG. 10A, adjacent flat portions 421 may be arranged at a predetermined angle. In the example of FIG. 10A, the first bent portion 422a and the second bent portion 422b are provided with communication paths, respectively, and the condensed water easily flows into the respective communication paths. Yes.

また、チューブの長手方向に対して垂直となるように平坦部を設けた例を示したが、これに限定されない。例えば、図１０（ｂ）に示すように、対向する一方のチューブ１１０側に平坦部５２１が傾くように、一方のチューブ１１０に対する折曲部５２２ａの接合位置と他方のチューブ１１０に対する折曲部５２２ｂの接合位置とを上記各実施の形態に比し上下方向にずらして設けても構わない。この場合、例えば第１の折曲部５２２ａ側のみに連通路が設けられているときに、連通路側が常に下方となるように平坦部５２１を傾ければ、凝縮水が連通路に流入し易くなる。   Moreover, although the example which provided the flat part so that it might become perpendicular | vertical with respect to the longitudinal direction of a tube was shown, it is not limited to this. For example, as shown in FIG. 10B, the joining position of the bent portion 522a with respect to one tube 110 and the bent portion 522b with respect to the other tube 110 so that the flat portion 521 is inclined toward the opposite one tube 110 side. These joining positions may be shifted in the vertical direction as compared to the above embodiments. In this case, for example, when the communication path is provided only on the first bent portion 522a side, if the flat portion 521 is inclined so that the communication path side is always downward, the condensed water easily flows into the communication path. Become.

また、実施の形態１及び実施の形態２においては連通路が短手方向の中央に、実施の形態３においては連通路が短手方向の両端部側に設けられる例を示したが、これに限定されず、いずれの位置に設けても構わない。なお、連通路が短手方向の一端側に設けられる場合、チューブの風上に相当する端部に、より多くの凝縮水が付着することが知られているため、連通路が設けられた一端側からファンによる送風が行われるように熱交換器を構成することが好ましい。   In the first embodiment and the second embodiment, the communication path is provided at the center in the short direction, and in the third embodiment, the communication path is provided at both ends in the short direction. It is not limited and may be provided at any position. In addition, since it is known that more condensed water adheres to the end corresponding to the windward side of the tube when the communication path is provided on one end side in the short direction, the one end provided with the communication path It is preferable to configure the heat exchanger so that air is blown by a fan from the side.

また、フィンの折曲部が所定の曲率半径をもって滑らかに湾曲している例を示したが、これに限定されない。対向するチューブの平面に対して交互にフィンが接合することができればよく、例えば、完全に折り返してカドを設け、そのカドを接合させても構わないし、矩形状になるように折り曲げて面を接合させても構わない。   Moreover, although the example in which the bent part of the fin is smoothly curved with a predetermined curvature radius has been shown, the present invention is not limited to this. It is only necessary that the fins can be alternately joined to the opposing tube planes. For example, the folds may be completely folded to provide the cadence, and the cadence may be joined. It does n’t matter.

第１の折曲部または第２の折曲部に対して連通路が１本のみ形成される例を示したが、これに限定されず、２本以上であっても構わない。また、各実施例に示された連通路の幅は例示であり、これに限定されず、様々な幅の連通路を設けることを妨げない。   Although the example in which only one communication path is formed with respect to the first bent part or the second bent part has been shown, the present invention is not limited to this and may be two or more. Moreover, the width of the communication path shown in each embodiment is an exemplification, and is not limited to this, and does not prevent the communication paths having various widths from being provided.

また、例えば熱交換器の表面をシリケート含有皮膜等により親水処理加工することを妨げるものではない。このように親水処理加工をすることにより、フィンやチューブに付着した凝縮水が流れ落ちやすくなるため、排水性が向上する。   Further, for example, this does not prevent the surface of the heat exchanger from being subjected to a hydrophilic treatment with a silicate-containing film or the like. By performing the hydrophilic treatment in this way, the condensed water adhering to the fins and the tubes is likely to flow down, so that drainage is improved.

１００ 熱交換器
１１０ チューブ
１１５ 平面
１２０ フィン
１２１ 平坦部
１２２ａ 第１の折曲部
１２２ｂ 第２の折曲部
１２２ｃ 第３の折曲部
１２５ 連通路
２００ 熱交換器
２２０ フィン
２２１ 平坦部
２２２ａ 第１の折曲部
２２２ｂ 第２の折曲部
２２２ｃ 第３の折曲部
２２２ｄ 第４の折曲部
２２５ａ 連通路
２２５ｂ 連通路
３００ 熱交換器
３２０ フィン
３２１ 平坦部
３２２ａ 第１の折曲部
３２２ｂ 第２の折曲部
３２２ｃ 第３の折曲部
３２２ｄ 第４の折曲部
３２５ａ 連通路
３２５ｂ 連通路
DESCRIPTION OF SYMBOLS 100 Heat exchanger 110 Tube 115 Plane 120 Fin 121 Flat part 122a 1st bending part 122b 2nd bending part 122c 3rd bending part 125 Communication path 200 Heat exchanger 220 Fin 221 Flat part 222a 1st bending part Bent portion 222b second bent portion 222c third bent portion 222d fourth bent portion 225a communication path 225b communication path 300 heat exchanger 320 fin 321 flat section 322a first bent section 322b second Folded part 322c Third bent part 322d Fourth bent part 325a Communication path 325b Communication path

Claims (4)

所定の間隔をあけて対向する面を有するチューブと、折曲部及び平坦部が長手方向に交互に形成され、前記折曲部が前記チューブの対向する面に接合されるフィンとを備え、
前記フィンは、対向する面のうち一方の面に接する側の折曲部の短手方向の所定範囲が、対向する他方の面側に折曲し、該他方の面に接合することで連通路を形成していることを特徴とする熱交換器。 A tube having surfaces facing each other with a predetermined interval, and a bent portion and a flat portion are alternately formed in the longitudinal direction, and the bent portion is joined to the facing surface of the tube, and
The fin has a predetermined range in the short direction of the bent portion on the side in contact with one of the opposing surfaces, and is bent to the other surface facing and joined to the other surface. Forming a heat exchanger. 前記フィンは、前記折曲部の短手方向の所定範囲に、長手方向の切れ込みが設けられ、該切れ込み部分が、対向する他方の面側に折曲し、該他方の面に接合することで前記連通路を形成していることを特徴とする請求項１記載の熱交換器。   The fin is provided with a cut in the longitudinal direction in a predetermined range in the short direction of the bent portion, and the cut portion is bent to the other side facing and joined to the other side. The heat exchanger according to claim 1, wherein the communication path is formed. 前記連通路は、対向する面のうち一方の面に接する側の折曲部と他方の面に接する折曲部とにそれぞれ設けられることを特徴とする請求項１又は２記載の熱交換器。   3. The heat exchanger according to claim 1, wherein the communication path is provided in each of a bent portion in contact with one of the opposing surfaces and a bent portion in contact with the other surface. 対向する面のうち一方の面に接する側の折曲部に設けられる連通路の短手方向の範囲は、他方の面に接する折曲部に設けられる連通路の短手方向の範囲と重複することを特徴とする請求項３記載の熱交換器。
The range in the short direction of the communication path provided in the bent portion on the side contacting the one surface among the opposing surfaces overlaps the range in the short direction of the communication path provided in the bent portion in contact with the other surface. The heat exchanger according to claim 3.
JP2010118198A 2010-05-24 2010-05-24 Heat exchanger Expired - Fee Related JP5421859B2 (en)

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JP2010118198A JP5421859B2 (en) 2010-05-24 2010-05-24 Heat exchanger
US13/700,000 US20130068438A1 (en) 2010-05-24 2011-05-11 Heat Exchanger
CN201180024019.4A CN102893117B (en) 2010-05-24 2011-05-11 Heat exchanger
DE112011101771T DE112011101771T5 (en) 2010-05-24 2011-05-11 heat exchangers
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