JP2008101847A - Air heat exchanger - Google Patents

Air heat exchanger Download PDF

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JP2008101847A
JP2008101847A JP2006284773A JP2006284773A JP2008101847A JP 2008101847 A JP2008101847 A JP 2008101847A JP 2006284773 A JP2006284773 A JP 2006284773A JP 2006284773 A JP2006284773 A JP 2006284773A JP 2008101847 A JP2008101847 A JP 2008101847A
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heat transfer
transfer tubes
flat heat
air
flat
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JP4946348B2 (en
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Genei Kin
鉉永 金
Koichi Yasuo
晃一 安尾
Hirokazu Fujino
宏和 藤野
Toshimitsu Kamata
俊光 鎌田
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Daikin Industries Ltd
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Daikin Industries Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—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
    • F28F1/10—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
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators

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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

<P>PROBLEM TO BE SOLVED: To provide an air heat exchanger comprising flat heat transfer tubes and corrugated fins, capable of improving water draining performance of corrugated fin parts in being used as an evaporator. <P>SOLUTION: In this air heat exchanger provided with the plurality of flat heat transfer tubes 2, 2 disposed between headers 3A, 3B, and the corrugated fins 4, 4 disposed among the plurality of heat transfer tubes 2, 2, a width of the corrugated fins 4, 4 are relatively larger than a width of the flat heat transfer tubes 2, 2, and a discharge passage for condensate water is formed by connecting adjacent edge portions 4b, 4b to each other without through the flat heat transfer tubes 2, 2 at an outer side with respect to parts corresponding to the flat heat transfer tubes 2, 2 by cutting the parts corresponding to the flat heat transfer tubes 2, 2, of the corrugated fins 4, 4. <P>COPYRIGHT: (C)2008,JPO&amp;INPIT

Description

この出願の発明は、扁平伝熱管およびコルゲートフィンを備えて構成された空気熱交換器の構造に関するものである。   The invention of this application relates to a structure of an air heat exchanger that includes a flat heat transfer tube and a corrugated fin.

扁平伝熱管およびコルゲートフィンを備えた空気熱交換器の全体および各部の構造を、例えば図５〜図８に示す。   The whole of the air heat exchanger provided with a flat heat exchanger tube and a corrugated fin and the structure of each part are shown, for example in FIGS.

該空気熱交換器１は、例えば図５、図６に示すように、冷媒が導入、導出されるパイプ状のヘッダ３Ａ，３Ｂと、該ヘッダ３Ａ，３Ｂ間に連通状態で、かつその長手方向に相互に所定の間隔を保って並設された多数本の扁平伝熱管２，２・・・と、該多数本の扁平伝熱管２，２・・・間の上下方向に波形に屈曲したコルゲーション状態で配設され、その各屈曲面外端を対応する両隣りの扁平伝熱管２，２・・・の扁平伝熱面に熱溶着されたコルゲートフィン（またはルーバーフィン）４，４・・・とからなっている。   For example, as shown in FIGS. 5 and 6, the air heat exchanger 1 has pipe-like headers 3 </ b> A and 3 </ b> B into which refrigerant is introduced and led out, and is in communication between the headers 3 </ b> A and 3 </ b> B and in its longitudinal direction. And a plurality of flat heat transfer tubes 2, 2... Arranged in parallel with each other at a predetermined interval, and a corrugation bent in a waveform in the vertical direction between the multiple flat heat transfer tubes 2, 2. Corrugated fins (or louver fins) 4, 4... Arranged in a state and thermally welded to the flat heat transfer surfaces of the adjacent flat heat transfer tubes 2, 2. It is made up of.

上記扁平伝熱管２，２・・・は、例えば図７に示すように、その内側に複数の冷媒流通穴２ａ，２ａ・・・を有する多孔構造となっており、上記一方側（右側）ヘッダ３Ａの上段側冷媒供給部３Ａ1を介して外部より導入分配された冷媒を上段側扁平伝熱管２，２・・・の各冷媒流通穴２ａ，２ａ・・・に均等に流し、上記コルゲートフィン４，４・・・を介して広伝熱面積で内部の冷媒と外部の空気との間で熱交換を行うようになっている。 As shown in FIG. 7, for example, the flat heat transfer tubes 2, 2... Have a porous structure having a plurality of refrigerant flow holes 2a, 2a. The refrigerant introduced and distributed from the outside through the upper stage refrigerant supply section 3A 1 of 3A is caused to flow evenly through the refrigerant circulation holes 2a, 2a,... Heat exchange is performed between the internal refrigerant and the external air over a wide heat transfer area through 4, 4.

また他方側（左側）ヘッダ３Ｂを介して返流分配される冷媒は下段側扁平伝熱管２，２・・・の各冷媒流通穴２ａ，２ａ・・・を均等に流れ、同状態において上記コルゲートフィン４，４・・・を介して広伝熱面積で内部の冷媒と外部の空気との間で効率良く熱交換を行うようになっている。   Further, the refrigerant returned and distributed through the other side (left side) header 3B flows evenly through the refrigerant flow holes 2a, 2a,... Of the lower flat heat transfer tubes 2, 2,. Heat is efficiently exchanged between the internal refrigerant and the external air over a wide heat transfer area via the fins 4, 4.

そして、そのようにして上記下段側扁平伝熱管２，２・・・を出た冷媒は、上記一方側（右側）ヘッダ３Ａの下段側冷媒導出部３Ａ2を介して以後の冷媒回路に流出する。 Then, the way the refrigerant exiting the lower side flat heat transfer tubes 2, 2 flows out to the subsequent refrigerant circuit through the lower refrigerant outlet portion 3A 2 of the one side (right side) header 3A .

また、上記コルゲートフィン４，４・・・は、例えば図６および図７に示すように、その波形の屈曲部（折り曲げ部）を除く扁平面部分であって、加工上形成される中央の扁平面を中心として空気流の上流側部分と下流側部分の各々に空気との伝熱効率を向上させるための複数の切り起し片（ルーバー）４ａ，４ａ・・・が形成されており、該切り起し片４ａ，４ａ・・・によって可及的に冷媒と空気との間の熱交換性能が高くなるように構成されている（特許文献１，２参照）。   Further, the corrugated fins 4, 4... Are flat flat portions excluding the corrugated bent portions (folded portions) as shown in FIGS. A plurality of cut and raised pieces (louvers) 4a, 4a,... For improving the heat transfer efficiency with air are formed in each of the upstream portion and the downstream portion of the air flow around the surface. The raising pieces 4a, 4a,... Are configured so that the heat exchange performance between the refrigerant and the air is as high as possible (see Patent Documents 1 and 2).

特開２０００−１５４９８９号公報（明細書１−５頁、図１−３）Japanese Patent Laid-Open No. 2000-154989 (Specifications page 1-5, FIG. 1-3) 特開２００５−６９５２９号公報（明細書１−５頁、図１−２）Japanese Patent Laying-Open No. 2005-69529 (Specifications page 1-5, FIG. 1-2)

上述のように、扁平多孔管構造の扁平伝熱管および波形構造のコルゲートフィンを備えたフィンチューブ式の熱交換器は、例えば図５および図７に示されるように、上記扁平伝熱管２，２・・・を横向き（水平）状態に設置した場合には、コルゲートフィン４，４・・・表面の凝縮水がはけにくく、例えば図８に示すように、空気流の上流側から下流側方向に次第に滞留し、通風抵抗を増大させる（ドット部参照）。したがって、蒸発器として利用した場合に、空気側の圧力損失が増大して、伝熱性能が落ちる問題がある。   As described above, as shown in FIGS. 5 and 7, for example, as shown in FIGS. 5 and 7, the flat heat transfer tubes 2 and 2 include a flat heat transfer tube having a flat porous tube structure and a corrugated fin having a corrugated structure. ... when installed in a sideways (horizontal) state, the corrugated fins 4, 4, ... are difficult to drain condensed water on the surface, for example, as shown in Fig. 8, from the upstream side to the downstream side of the air flow It gradually stays and increases the ventilation resistance (see dot portion). Therefore, when it uses as an evaporator, there exists a problem that the pressure loss by the side of air increases and heat transfer performance falls.

この出願の発明は、このような課題を解決するためになされたもので、扁平伝熱管の幅に対してコルゲートフィンの幅を相対的に大きくする一方、少なくとも空気流下流側のフィン面上に凝縮水が落ちるように、その扁平伝熱管に対応する部分を切り欠き、扁平伝熱管に対応する部分よりも外側の部分では扁平伝熱管を挟んで上下のコルゲートフィンがつながるようにすることにより、凝縮水の排出性能を向上させて、空気側の熱伝達性能を向上させた空気熱交換器を提供することを目的とするものである。   The invention of this application was made to solve such a problem, and the width of the corrugated fin is relatively increased with respect to the width of the flat heat transfer tube, while at least on the fin surface on the downstream side of the air flow. By cutting out the portion corresponding to the flat heat transfer tube so that the condensed water falls, and by connecting the upper and lower corrugated fins with the flat heat transfer tube sandwiched in the portion outside the portion corresponding to the flat heat transfer tube, An object of the present invention is to provide an air heat exchanger with improved condensate discharge performance and improved air-side heat transfer performance.

この出願の各発明は、該目的を達成するために、次のような課題解決手段を備えて構成されている。   In order to achieve the object, each invention of this application includes the following problem solving means.

（１） 請求項１の発明
この発明の空気熱交換器は、ヘッダ３Ａ，３Ｂの間に複数本の扁平伝熱管２，２・・・を、それら複数本の扁平伝熱管２，２・・・の間にコルゲートフィン４，４・・・をそれぞれ配設してなる空気熱交換器であって、上記コルゲートフィン４，４・・・の幅を上記扁平伝熱管２，２・・・の幅よりも相対的に大きく形成する一方、同コルゲートフィン４，４・・・の上記扁平伝熱管２，２・・・に対応する部分を切り欠いて上記扁平伝熱管２，２・・・に対応する部分よりも外側の上記扁平伝熱管２，２・・・を介さずに隣合う縁部４ｂ，４ｂ・・・同士を相互に連続させることにより、凝縮水の排出通路を形成したことを特徴としている。 (1) Invention of Claim 1 The air heat exchanger according to the present invention includes a plurality of flat heat transfer tubes 2, 2... Between the headers 3A, 3B, and the plurality of flat heat transfer tubes 2, 2,. .. Are air heat exchangers each having corrugated fins 4, 4... Arranged between the flat heat transfer tubes 2, 2. While forming relatively larger than the width, the corrugated fins 4, 4... Corresponding to the flat heat transfer tubes 2, 2. That the adjacent edge portions 4b, 4b,... Are connected to each other without going through the flat heat transfer tubes 2, 2,. It is a feature.

このような構成によると、扁平伝熱管２，２・・・の幅よりも相対的に幅が広く、扁平伝熱管２，２・・・よりも外側に位置して相互に連続する隣合うコルゲートフィン４，４・・・の縁部４ｂ，４ｂ・・・上に凝縮水が落ち、同縁部４ｂ，４ｂ・・・を介してドレンパン上にスムーズに排出されるようになる。   According to such a configuration, adjacent corrugates that are relatively wider than the widths of the flat heat transfer tubes 2, 2,... And are located outside the flat heat transfer tubes 2, 2,. The condensed water falls on the edges 4b, 4b... Of the fins 4, 4... And is smoothly discharged onto the drain pan through the edges 4b, 4b.

したがって、前述のように、上記空気熱交換器１を蒸発器として利用したような場合にも、凝縮水の排出性能がよくなり、圧損が低下するとともに熱伝達性能が向上する。   Therefore, as described above, even when the air heat exchanger 1 is used as an evaporator, the condensed water discharge performance is improved, the pressure loss is reduced, and the heat transfer performance is improved.

その結果、当該空気熱交換器１の大きさが大きい時はもちろん、小型化した時にも有効に空気側の伝熱性能を向上させることができる。   As a result, the air-side heat transfer performance can be effectively improved not only when the size of the air heat exchanger 1 is large but also when it is downsized.

（２） 請求項２の発明
この発明の空気熱交換器は、ヘッダ３Ａ，３Ｂの間に複数本の扁平伝熱管２，２・・・を、それら複数本の扁平伝熱管２，２・・・の間にコルゲートフィン４，４・・・をそれぞれ配設してなる空気熱交換器であって、上記扁平伝熱管２，２・・・を空気流の上流側から下流側にかけて２本以上並設するとともに、それら各扁平伝熱管２，２・・・、２，２・・・に対して上記コルゲートフィン４，４・・・を共通な１枚のものとし、かつ上記コルゲートフィン４，４・・・の幅を上記扁平伝熱管２，２・・・、２，２・・・の幅よりも相対的に大きく形成する一方、同コルゲートフィン４，４・・・の上記扁平伝熱管２，２・・・、２，２・・・に対応する部分を切り欠いて上記扁平伝熱管２，２・・・、２，２・・・に対応する部分よりも外側の上記扁平伝熱管２，２・・・、２，２・・・を介さずに隣合う縁部４ｂ，４ｂ・・・同士を相互に連続させることにより、凝縮水の排出通路を形成したことを特徴としている。 (2) Invention of Claim 2 The air heat exchanger according to the present invention includes a plurality of flat heat transfer tubes 2, 2... Between the headers 3A, 3B, and the plurality of flat heat transfer tubes 2, 2,. .. are air heat exchangers in which corrugated fins 4, 4... Are respectively disposed between the flat heat transfer tubes 2, 2... From the upstream side to the downstream side of the air flow. The corrugated fins 4, 4... Are common to the flat heat transfer tubes 2, 2,... Are formed relatively larger than the flat heat transfer tubes 2, 2,..., 2, 2,..., While the flat heat transfer tubes of the corrugated fins 4, 4. 2, 2..., 2, 2... ... Condensation by making adjacent edges 4b, 4b... Continuous with each other without passing through the flat heat transfer tubes 2, 2,. It is characterized by the formation of a water discharge passage.

このような構成によると、複数列の扁平伝熱管２，２・・・の幅よりも相対的に幅が広く、扁平伝熱管２，２・・・よりも外側の相互に連続する隣り合うコルゲートフィン４，４・・・の縁部４ｂ，４ｂ・・・上に凝縮水が落ち、同縁部４ｂ，４ｂ・・・を介してドレンパン上にスムーズに排出されるようになる。   According to such a configuration, adjacent corrugates that are relatively wider than the plurality of rows of flat heat transfer tubes 2, 2... And adjacent to each other outside the flat heat transfer tubes 2, 2. The condensed water falls on the edges 4b, 4b... Of the fins 4, 4... And is smoothly discharged onto the drain pan through the edges 4b, 4b.

したがって、前述のように、上記空気熱交換器１を蒸発器として利用したような場合にも、凝縮水の排出性能がよくなり、圧損が低下するとともに熱伝達性能が向上する。   Therefore, as described above, even when the air heat exchanger 1 is used as an evaporator, the condensed water discharge performance is improved, the pressure loss is reduced, and the heat transfer performance is improved.

その結果、当該空気熱交換器１の大きさが大きい時はもちろん、小型化した時にも有効に空気側の伝熱性能を向上させることができる。   As a result, the air-side heat transfer performance can be effectively improved not only when the size of the air heat exchanger 1 is large but also when it is downsized.

（３） 請求項３の発明
この発明の空気熱交換器は、上記請求項１又は２の発明において、扁平伝熱管２，２・・・の幅よりも相対的に幅が広くなることにより形成されたコルゲートフィン４，４・・・の扁平伝熱管２，２・・・よりも外側に位置する縁部４ｂ，４ｂ・・・は、当該コルゲートフィン４，４・・・の空気流の下流側にのみ設けられていることを特徴としている。 (3) Invention of Claim 3 The air heat exchanger of this invention is formed by making the width relatively wider than the width of the flat heat transfer tubes 2, 2. .. Of the corrugated fins 4, 4... Located on the outer side of the flat heat transfer tubes 2, 2... Are downstream of the airflow of the corrugated fins 4, 4. It is characterized by being provided only on the side.

上記構成の空気熱交換器を扁平伝熱管２，２・・・部分を水平にして蒸発器として使用した場合、各段のコルゲートフィン４，４・・・の波形の底部の全体に凝縮水が滞留するが、この凝縮水は空気流に押されて空気流下流側に集まる。   When the air heat exchanger having the above configuration is used as an evaporator with the flat heat transfer tubes 2, 2... Being horizontal, condensed water is formed on the entire corrugated fins 4, 4. Although it stays, this condensed water is pushed by the air flow and collects on the downstream side of the air flow.

したがって、上記扁平伝熱管２，２・・・の幅よりも幅が広くなることにより形成されたコルゲートフィン４，４・・・の扁平伝熱管２，２・・・よりも外側に位置する縁部４ｂ，４ｂ・・・は、空気流の下流側にのみ設けられていれば、凝縮水の排出が可能であり、有効に空気側熱伝達性能の向上に寄与する。   Therefore, the edge located outside the flat heat transfer tubes 2, 2 ... of the corrugated fins 4, 4 ... formed by increasing the width of the flat heat transfer tubes 2, 2 ... If the parts 4b, 4b,... Are provided only on the downstream side of the air flow, the condensed water can be discharged, which effectively contributes to the improvement of the air-side heat transfer performance.

（４） 請求項４の発明
この発明の空気熱交換器は、上記請求項１又は２の発明において、扁平伝熱管２，２・・・の幅よりも相対的に幅が広くなることにより形成されたコルゲートフィン４，４・・・の扁平伝熱管２，２・・・よりも外側に位置する縁部４ｂ，４ｂ・・・は、当該コルゲートフィン４，４・・・の空気流の上流側と下流側の両方に設けられていることを特徴としている。 (4) Invention of Claim 4 The air heat exchanger of this invention is formed by the width | variety becoming relatively wider than the width | variety of the flat heat exchanger tube 2, 2 ... in the invention of the said Claim 1 or 2. The edge portions 4b, 4b,... Located outside the flat heat transfer tubes 2, 2,... Of the corrugated fins 4, 4,. It is characterized by being provided on both the side and the downstream side.

上記構成の空気熱交換器を扁平伝熱管２，２・・・部分を水平にして蒸発器として使用した場合、各段のコルゲートフィン４，４・・・の波形の底部の全体に凝縮水が滞留し、この凝縮水は空気流に押されて空気流下流側に多く集まる。   When the air heat exchanger having the above configuration is used as an evaporator with the flat heat transfer tubes 2, 2... Being horizontal, condensed water is formed on the entire corrugated fins 4, 4. The condensed water is pushed by the air flow and gathers more on the downstream side of the air flow.

しかし、凝縮水が多い場合や風量が小さい場合などには、やはり空気流上流側にも滞留する。   However, when there is a lot of condensed water or when the air volume is small, it also stays on the upstream side of the air flow.

したがって、上記扁平伝熱管２，２・・・の幅よりも相対的に幅が広くなることにより形成されたコルゲートフィン４，４・・・の扁平伝熱管２，２・・・よりも外側に位置する縁部４ｂ，４ｂ・・・は、空気流の上流側と下流側の両方に設けられている方が、より効果的な凝縮水の排出が可能であり、より有効に空気側熱伝達性能の向上に寄与する。   Therefore, the corrugated fins 4, 4... Formed outside the flat heat transfer tubes 2, 2... Of the corrugated fins 4, 4. When the edge portions 4b, 4b,... Positioned are provided on both the upstream side and the downstream side of the air flow, more effective drainage of condensed water is possible, and air side heat transfer is more effective. Contributes to improved performance.

以上の結果、この出願の発明の空気熱交換器によると、コルゲートフィンと扁平伝熱管の相対的な大きさを変更するのみの簡単かつ低コストな構成で、しかも熱伝達性能の高い、軽量でコンパクトな空気調和機に適した扁平伝熱管およびコルゲートフィンを備えた空気熱交換器を提供することが可能となる。   As a result, according to the air heat exchanger of the invention of this application, it is a simple and low-cost configuration that only changes the relative sizes of the corrugated fins and the flat heat transfer tubes, and has high heat transfer performance and light weight. It is possible to provide an air heat exchanger including a flat heat transfer tube and a corrugated fin suitable for a compact air conditioner.

（最良の実施の形態１）
図１および図２は、この出願の発明の最良の実施の形態１に係る扁平伝熱管およびコルゲートフィンを備えた空気熱交換器の扁平伝熱管とコルゲートフィン部分の構造を示している。 (Best Embodiment 1)
1 and 2 show the structure of a flat heat transfer tube and a corrugated fin portion of an air heat exchanger including the flat heat transfer tube and the corrugated fin according to the first embodiment of the present invention.

この実施の形態の空気熱交換器１も、その基本的な構成としては、前述の図５のものと同様に、冷媒が導入、導出される上下方向に延びるアルミ製の左右両ヘッダ３Ａ，３Ｂと、該左右両ヘッダ３Ａ，３Ｂの間に連通状態で、かつ相互に所定の間隔を保ってヘッダの長手方向（上下方向）に並設された複数本のアルミ製の扁平伝熱管２，２・・・と、該複数本の扁平伝熱管２，２・・・の間に位置して、左右両方向に連続するように配設され、その各屈曲面の外端を対応する上下両隣りの扁平伝熱管２，２・・・の扁平面に熱溶着されたアルミ製のコルゲートフィン４，４・・・とからなっている（前述の図５の構成を参照）。   The basic structure of the air heat exchanger 1 of this embodiment is the same as that of FIG. 5 described above, and both left and right aluminum headers 3A and 3B extending in the vertical direction in which the refrigerant is introduced and led out. And a plurality of flat aluminum heat transfer tubes 2, 2 arranged in parallel in the longitudinal direction (vertical direction) of the header in a communication state between the left and right headers 3A, 3B and maintaining a predetermined distance from each other. ... and the plurality of flat heat transfer tubes 2, 2 ... are arranged so as to be continuous in both the left and right directions, and the outer ends of the respective bent surfaces thereof correspond to the upper and lower sides corresponding to each other. Are made of aluminum corrugated fins 4, 4... Thermally welded to the flat surfaces of the flat heat transfer tubes 2, 2... (See the configuration of FIG. 5 described above).

上記扁平伝熱管２，２・・・は、例えば図１に示すように、上記左右両ヘッダ３Ａ，３Ｂの直径に対応した所定の幅を有し、その内側長手方向に多数の冷媒流通穴２ａ，２ａ・・・を有する多孔管構造となっており、上記一方側（右側）ヘッダ３Ａの上段側冷媒供給部３Ａ1を介して外部より導入分配された冷媒を上段側扁平伝熱管２，２・・・の各冷媒流通穴２ａ，２ａ・・・に均等に流し、同状態において上記コルゲートフィン４，４・・・を介して広伝熱面積で内部の冷媒と外部の空気との間で効率良く熱交換を行うようになっている。 The flat heat transfer tubes 2, 2... Have a predetermined width corresponding to the diameters of the left and right headers 3A, 3B, for example, as shown in FIG. , 2a, etc., and the refrigerant introduced and distributed from the outside via the upper side refrigerant supply section 3A1 of the one side (right side) header 3A is supplied to the upper side flat heat transfer tubes 2, 2. Are evenly flown through the refrigerant circulation holes 2a, 2a, ..., and in the same state, between the internal refrigerant and the external air with a wide heat transfer area through the corrugated fins 4, 4, ... Heat exchange is performed efficiently.

また他方側（左側）ヘッダ３Ｂを介して返流分配される冷媒は下段側扁平伝熱管２，２・・・の各冷媒流通穴２ａ，２ａ・・・を均等に流れ、同状態において上記コルゲートフィン４，４・・・を介して広伝熱面積で内部の冷媒と外部の空気との間で効率良く熱交換を行うようになっている。そして、その後、上記下段側扁平伝熱管２，２・・・を出た冷媒は上記一方側（右側）ヘッダ３Ａの下段側冷媒導出部３Ａ2を介して以後の回路に流出する。 Further, the refrigerant returned and distributed through the other side (left side) header 3B flows evenly through the refrigerant flow holes 2a, 2a,... Of the lower flat heat transfer tubes 2, 2,. Heat is efficiently exchanged between the internal refrigerant and the external air over a wide heat transfer area via the fins 4, 4. Then, the refrigerant that has exited the lower flat heat transfer tubes 2, 2... Flows out to the subsequent circuits through the lower refrigerant outlet 3A 2 of the one side (right side) header 3A.

上記コルゲートフィン４，４・・・は、その屈曲部（折り曲げ部）を除く扁平面部分であって、加工上形成される中央の扁平面を中心として空気流の上流側部分と下流側部分の各々に空気との伝熱効率を向上させるための複数の切起し片（ルーバー）４ａ，４ａ・・・がそれぞれ空気の流れ方向に対する傾斜方向を逆にして形成されている。   The corrugated fins 4, 4... Are flat flat portions excluding the bent portions (bending portions), and the upstream portion and the downstream portion of the air flow around the central flat surface formed on the processing. A plurality of cut-and-raised pieces (louvers) 4a, 4a,... For improving heat transfer efficiency with air are formed with the inclination directions with respect to the air flow direction reversed.

ところで、上記コルゲートフィン４，４・・・の空気側伝熱性能を向上させるためには、そのフィン面部分の空気流に対する圧損が小さく、熱伝達率が高いことが必要である。   By the way, in order to improve the air side heat transfer performance of the corrugated fins 4, 4,..., It is necessary that the pressure loss with respect to the air flow at the fin surface portions is small and the heat transfer coefficient is high.

その場合、上記コルゲートフィン４，４・・・の配設ピッチ（波形間隔）を大きくすると風は通しやすくなり、圧損は小さくなるが、配設ピッチが大きいと、当該フィンの前縁効果を十分に活用することができなくなるために、逆に熱伝達率は悪くなる。   In that case, if the arrangement pitch (corrugated interval) of the corrugated fins 4, 4... Is increased, the air can be easily passed and the pressure loss is reduced. However, if the arrangement pitch is large, the front edge effect of the fins is sufficient. On the other hand, the heat transfer coefficient is deteriorated because the heat transfer coefficient cannot be utilized.

他方、上記コルゲートフィン４，４・・・の配設ピッチを小さくして行くと、当該コルゲートフィン４，４・・・の前縁効果を活用できるようになる反面、切り起し片４ａ，４ａ・・・の高さ、切り起し片４ａ，４ａ・・・間の間隔が小さくなり、各切り起し片４ａ，４ａ・・・間に空気が流れにくくなるので、圧損が増大する。   On the other hand, if the arrangement pitch of the corrugated fins 4, 4,... Is reduced, the leading edge effect of the corrugated fins 4, 4,. ... And the distance between the cut and raised pieces 4a, 4a,..., And the air becomes difficult to flow between the cut and raised pieces 4a, 4a.

したがって、上記コルゲートフィン４，４・・・の配設ピッチは、これらの事情を考慮して適切な値に設定される。   Therefore, the arrangement pitch of the corrugated fins 4, 4... Is set to an appropriate value in consideration of these circumstances.

そして、上記扁平伝熱管２，２・・・およびコルゲートフィン４，４・・・を備えたフィンチューブ式の熱交換器１では、さらに図５のように、上記扁平伝熱管２，２・・・を横向き（水平）に設置した場合には、すでに説明したようにコルゲートフィン４，４・・・表面の凝縮水がはけにくいために、蒸発器として利用した場合に、より空気側の圧力損失が増大して、性能が低下する問題がある。   And in the finned tube type heat exchanger 1 provided with the flat heat transfer tubes 2, 2,... And the corrugated fins 4, 4 ..., the flat heat transfer tubes 2, 2,.・ When installed sideways (horizontal), as explained above, corrugated fins 4, 4... Are difficult to drain condensed water on the surface, so when used as an evaporator, the pressure on the air side is more There is a problem in that loss increases and performance decreases.

この問題は、上記空気熱交換器１の大きさが小さくなるほど顕著となり、設計条件が厳しくなる。   This problem becomes more prominent as the size of the air heat exchanger 1 becomes smaller, and the design conditions become more severe.

したがって、空気熱交換器１の大きさが小さくなるほど、上記コルゲートフィン４，４・・・のフィン面に滞留する凝縮水の圧損の増大に対する影響もより大になる。   Therefore, the smaller the size of the air heat exchanger 1, the greater the influence on the increase in the pressure loss of the condensed water staying on the fin surfaces of the corrugated fins 4, 4,.

そこで、本実施の形態の空気熱交換器１は、このような問題を解決するために、例えば図１、図２に示すように、上記コルゲートフィン４，４・・・の幅Ｗ1を上記扁平伝熱管２，２・・・の幅Ｗ2よりも大きく形成する一方、同コルゲートフィン４，４・・・の上記扁平伝熱管２，２・・・に対応する部分（接触する部分）を外側の縁部４ｂ，４ｂ・・・部分を残して上記扁平伝熱管２，２・・・の厚さｔの１／２程度切り欠いて上記扁平伝熱管２，２・・・が嵌合する凹部を形成し、扁平伝熱管２，２・・・を介さずに隣り合う当該上下コルゲートフィン４，４・・・外側の縁部４ｂ，４ｂ・・・同士を相互のフィン面がＶ字形に連続するように相互に当接させたことを特徴としている。 Therefore, in order to solve such a problem, the air heat exchanger 1 of the present embodiment has a width W 1 of the corrugated fins 4, 4... As shown in FIGS. While the flat heat transfer tubes 2, 2... Are formed larger than the width W 2 , portions of the corrugated fins 4, 4... Corresponding to the flat heat transfer tubes 2, 2. The flat heat transfer tubes 2, 2... Are fitted by being cut out about ½ of the thickness t of the flat heat transfer tubes 2, 2. A concave portion is formed, and the adjacent upper and lower corrugated fins 4, 4... Outside edges 4 b, 4 b... Are adjacent to each other without using the flat heat transfer tubes 2, 2. It is characterized by being in contact with each other so as to be continuous.

このような構成によると、扁平伝熱管２，２・・・の幅Ｗ2よりも幅Ｗ1が広くなることにより形成された相互に連続する上下コルゲートフィン４，４・・・の空気流の上流側および下流側両縁部４ｂ，４ｂ・・・のフィン面上に凝縮水が落ち、同縁部４ｂ，４ｂ・・・を介してドレンパン上にスムーズに排出されるようになる。 According to such a configuration, the air flow of the mutually continuous upper and lower corrugated fins 4, 4... Formed by the width W 1 being wider than the width W 2 of the flat heat transfer tubes 2, 2. The condensed water falls on the fin surfaces of both the upstream and downstream edges 4b, 4b... And is smoothly discharged onto the drain pan through the edges 4b, 4b.

したがって、上述のように、上記空気熱交換器１を蒸発器として利用した場合にも、凝縮水の排出性能がよくなり、圧損が低下するとともに熱伝達性能が向上する。その結果、当該空気熱交換器１の大きさが大きい時はもちろん、小型化した時にも有効に空気側の伝熱性能を向上させることができる。   Therefore, as described above, even when the air heat exchanger 1 is used as an evaporator, the condensate discharge performance is improved, the pressure loss is reduced, and the heat transfer performance is improved. As a result, the air-side heat transfer performance can be effectively improved not only when the size of the air heat exchanger 1 is large but also when it is downsized.

この場合、コルゲートフィン４，４・・・の幅Ｗ1を一定とし、扁平伝熱管２，２・・・の幅Ｗ2の方を小さくすることによっても同様の作用効果を得ることができる。 In this case, the same effect can also be obtained by making the width W 1 of the corrugated fins 4, 4... Constant and making the width W 2 of the flat heat transfer tubes 2, 2.

これらの結果、本実施の形態の空気熱交換器１によると、コルゲートフィン４，４・・・と扁平伝熱管２，２・・・の相対的な大きさを変更するのみの簡単かつ低コストな構成で、熱伝達性能の高い、軽量かつ小型の扁平伝熱管およびコルゲートフィンを備えたフィンチューブ式空気熱交換器を提供することが可能となる。   As a result, according to the air heat exchanger 1 of the present embodiment, it is simple and low-cost only by changing the relative sizes of the corrugated fins 4, 4... And the flat heat transfer tubes 2, 2. With a simple structure, it is possible to provide a finned tube type air heat exchanger having a light and small flat heat transfer tube and corrugated fins with high heat transfer performance.

（最良の実施の形態２）
図３は、この出願の発明の最良の実施の形態２に係る扁平伝熱管およびコルゲートフィンを備えた空気熱交換器の扁平伝熱管とコルゲートフィン部分の構造を示している。 (Best Mode 2)
FIG. 3 shows the structure of the flat heat transfer tube and the corrugated fin portion of the air heat exchanger provided with the flat heat transfer tube and the corrugated fin according to the second preferred embodiment of the present invention.

この実施の形態の空気熱交換器１も、その基本的な構成としては、前述の図５のものと同様に、冷媒が導入、導出される上下方向に延びるアルミ製左右両ヘッダ３Ａ，３Ｂと、該左右両ヘッダ３Ａ，３Ｂの間に連通状態で、かつ相互に所定の間隔を保ってヘッダの長手方向（上下方向）に並設された複数本のアルミ製の扁平伝熱管２，２・・・と、該複数本の扁平伝熱管２，２・・・の間に位置して、左右両方向に連続するように配設され、その各屈曲面の外端を対応する上下両隣りの扁平伝熱管２，２・・・の扁平面に熱溶着されたアルミ製のコルゲートフィン４，４・・・とからなっている（前述の図５の構成を参照）。   The air heat exchanger 1 of this embodiment also has, as its basic structure, aluminum left and right headers 3A and 3B extending in the vertical direction in which the refrigerant is introduced and led out as in the case of FIG. A plurality of flat aluminum heat transfer tubes 2, 2... Made of aluminum arranged in parallel in the longitudinal direction (vertical direction) of the header in a communication state between the left and right headers 3 A and 3 B and maintaining a predetermined distance from each other. .. and located between the plurality of flat heat transfer tubes 2, 2... Are arranged so as to be continuous in both the left and right directions, and the flat ends on both the upper and lower sides corresponding to the outer ends of the respective bent surfaces. It comprises aluminum corrugated fins 4, 4... Thermally welded to the flat surfaces of the heat transfer tubes 2, 2... (See the configuration of FIG. 5 described above).

ただ、本実施の形態の場合、上記扁平伝熱管２，２・・・は、例えば図３に示すように、空気流の上流側と下流側に所定の間隔において前後２列に設けられ（２，２・・・、２，２・・・）、それら扁平伝熱管２，２・・・、２，２・・・に対して上記コルゲートフィン４，４・・・を共通な１枚のものとして構成されている。そして、上記前後２列の扁平伝熱管２，２・・・は、それぞれ上記左右両ヘッダ３Ａ，３Ｂ、３Ａ，３Ｂの直径に対応した所定の幅を有し、その内側長手方向に多数の冷媒流通穴２ａ，２ａ・・・を有する多孔管構造となっており、上記一方側（右側）ヘッダ３Ａ，３Ａの上段側冷媒供給部３Ａ1，３Ａ1を介して外部より導入分配された冷媒を上段側扁平伝熱管２，２・・・、２，２・・・の各冷媒流通穴２ａ，２ａ・・・、２ａ，２ａ・・・に均等に流し、同状態において上記コルゲートフィン４，４・・・を介して広伝熱面積で内部の冷媒と外部の空気との間で効率良く熱交換を行うようになっている。 However, in the case of the present embodiment, the flat heat transfer tubes 2, 2... Are provided in two rows in the front and rear at predetermined intervals on the upstream side and the downstream side of the air flow, for example, as shown in FIG. , 2..., 2, 2..., And the flat corrugated fins 4, 4. It is configured as. The front and rear two rows of flat heat transfer tubes 2, 2... Have a predetermined width corresponding to the diameters of the left and right headers 3A, 3B, 3A, 3B, respectively, and a large number of refrigerants in the inner longitudinal direction. It has a perforated pipe structure having flow holes 2a, 2a, etc., and the refrigerant introduced and distributed from the outside through the upper side refrigerant supply portions 3A 1 and 3A 1 of the one side (right side) headers 3A and 3A. In the same state, the corrugated fins 4, 4 are allowed to flow evenly through the refrigerant flow holes 2 a, 2 a, 2 a, 2 a,. Through a wide heat transfer area, heat exchange is efficiently performed between the internal refrigerant and the external air.

また他方側（左側）ヘッダ３Ｂ，３Ｂを介して返流分配される冷媒は下段側扁平伝熱管２，２・・・、２，２・・・の各冷媒流通穴２ａ，２ａ・・・、２ａ，２ａ・・・を均等に流れ、同状態において上記コルゲートフィン４，４・・・を介して広伝熱面積で内部の冷媒と外部の空気との間で効率良く熱交換を行うようになっている。そして、その後、上記下段側扁平伝熱管２，２・・・、２，２・・・を出た冷媒は上記一方側（右側）ヘッダ３Ａ，３Ａの下段側冷媒導出部３Ａ2，３Ａ2を介して以後の回路に流出する。 Further, the refrigerant returned and distributed through the other side (left side) headers 3B, 3B is the refrigerant circulation holes 2a, 2a,... Of the lower flat heat transfer tubes 2, 2,. 2a, 2a,..., And in the same state, heat exchange is efficiently performed between the internal refrigerant and the external air over the corrugated fins 4, 4,. It has become. Then, the refrigerant that has exited the lower flat heat transfer tubes 2, 2, 2, 2,... Passes through the lower side refrigerant outlets 3 A 2 , 3 A 2 of the one side (right side) headers 3 A, 3 A. To the subsequent circuit.

上記コルゲートフィン４，４・・・は、その屈曲部（折り曲げ部）を除く扁平面部分であって、加工上形成される中央の扁平面を中心として空気流の上流側部分と下流側部分の各々に空気との伝熱効率を向上させるための複数の切起し片（ルーバー）４ａ，４ａ・・・がそれぞれ空気の流れ方向に対する傾斜方向を逆にして形成されている。   The corrugated fins 4, 4... Are flat flat portions excluding the bent portions (bending portions), and the upstream portion and the downstream portion of the air flow around the central flat surface formed on the processing. A plurality of cut-and-raised pieces (louvers) 4a, 4a,... For improving heat transfer efficiency with air are formed with the inclination directions with respect to the air flow direction reversed.

ところで、前述のように上記コルゲートフィン４，４・・・の空気側伝熱性能を向上させるためには、そのフィン面部分の空気流に対する圧損が小さく、熱伝達率が高いことが必要である。   By the way, in order to improve the air side heat transfer performance of the corrugated fins 4, 4... As described above, it is necessary that the pressure loss with respect to the air flow at the fin surface portions is small and the heat transfer coefficient is high. .

その場合、上記コルゲートフィン４，４・・・の配設ピッチを大きくすると風は通しやすくなり、圧損は小さくなるが、配設ピッチが大きいと、当該フィンの前縁効果を十分に活用することができなくなるために、逆に熱伝達率は悪くなる。他方、上記フィンの配設ピッチを小さくして行くと、当該フィンの前縁効果を活用できるようになる反面、切り起し片４ａ，４ａ・・・の高さ、切り起し片４ａ，４ａ・・・間の間隔が小さくなり、各切り起し片４ａ，４ａ・・・間に空気が流れにくくなるので、圧損が増大する。   In that case, if the arrangement pitch of the corrugated fins 4, 4... Is increased, the air can be easily passed and the pressure loss is reduced. However, if the arrangement pitch is large, the leading edge effect of the fins should be fully utilized. On the other hand, the heat transfer rate deteriorates. On the other hand, when the pitch of the fins is reduced, the leading edge effect of the fins can be utilized. On the other hand, the height of the cut and raised pieces 4a, 4a,. ... the space between them becomes small, and it becomes difficult for air to flow between the cut and raised pieces 4a, 4a, ..., so that pressure loss increases.

そして、上記のように複数列の扁平伝熱管２，２・・・、２，２・・・およびそれらに共通なコルゲートフィン４，４・・・を備えたフィンチューブ式の熱交換器１でも、図５のように、上記扁平伝熱管２，２・・・を横向き（水平）に設置した場合にはコルゲートフィン４，４・・・表面の凝縮水がはけにくいために、蒸発器として利用した場合に、より空気側の圧力損失が増大して、性能が低下する。   And the fin tube type heat exchanger 1 provided with multiple rows of flat heat transfer tubes 2, 2, 2, 2... And corrugated fins 4, 4. As shown in FIG. 5, when the flat heat transfer tubes 2, 2... Are installed sideways (horizontal), the corrugated fins 4, 4. When used, the pressure loss on the air side increases and the performance decreases.

これらの問題は、上記空気熱交換器１の大きさが小さくなるほど顕著となり、設計条件が厳しくなる。   These problems become more prominent as the size of the air heat exchanger 1 becomes smaller, and the design conditions become more severe.

したがって、空気熱交換器１の大きさが小さくなるほど、上記コルゲートフィン４，４・・・のフィン面に滞留する凝縮水の圧損の増大に対する影響もより大になる。   Therefore, the smaller the size of the air heat exchanger 1, the greater the influence on the increase in the pressure loss of the condensed water staying on the fin surfaces of the corrugated fins 4, 4,.

そこで、本実施の形態の空気熱交換器１は、このような問題を解決するために、例えば図３に示すように、上記コルゲートフィン４，４・・・の全体の幅Ｗ1を上記複数列の扁平伝熱管２，２・・・の前後方向の配列幅Ｗ2よりも大きく形成する一方、上記前後に２本以上並設された複数列の扁平伝熱管２，２・・・、２，２・・・に対して上記コルゲートフィン４，４・・・を共通な１枚のものとし、かつ上記共通なコルゲートフィン４，４・・・の上記各扁平伝熱管２，２・・・、２，２・・・に対応する部分（接触する部分）を空気流の上流側と下流側各外側の縁部４ｂ，４ｂ・・・部分を除いて上記各扁平伝熱管２，２・・・の厚さｔの１／２程度切り欠いて上記扁平伝熱管２，２・・・を介さずに上下方向に隣合う当該上下コルゲートフィン４，４・・・外側の縁部４ｂ，４ｂ・・・、４ｂ，４ｂ・・・、４ｂ，４ｂ・・・同士を相互のフィン面がＶ字形に連続するように相互に当接させて凝縮水排出通路を形成したことを特徴としている。 Therefore, in order to solve such a problem, the air heat exchanger 1 of the present embodiment has an overall width W 1 of the corrugated fins 4, 4. While the row of flat heat transfer tubes 2, 2... Is formed to be larger than the arrangement width W 2 in the front-rear direction, two or more rows of flat heat transfer tubes 2, 2. The corrugated fins 4, 4,... Are common to the flat corrugated fins 4, 4,. , 2,... Except for the edge portions 4 b, 4 b... On the upstream side and downstream side of the air flow, the flat heat transfer tubes 2, 2. The upper and lower corrugations adjacent to each other in the vertical direction by notching about 1/2 of the thickness t of the flat heat transfer tubes 2, 2. ... Tofin 4, 4... Outer edges 4b, 4b... 4b, 4b... 4b, 4b... Are brought into contact with each other so that their fin surfaces are continuous in a V shape. The feature is that a condensed water discharge passage is formed.

このような構成によると、前後複数列の扁平伝熱管２，２・・・の配列幅Ｗ2よりも全体の幅Ｗ1が広いことにより形成された相互に連続する上下コルゲートフィン４，４・・・の前後両縁部４ｂ，４ｂ・・・、４ｂ，４ｂ・・・、４ｂ，４ｂ・・・上に凝縮水が落ち、同縁部４ｂ，４ｂ・・・、４ｂ，４ｂ・・・、４ｂ，４ｂ・・・を介してドレンパン上にスムーズに排出されるようになる。 With this configuration, the upper and lower corrugated fins 4, 4-contiguous with each other, which are formed by wider width W 1 of the whole than SEQ width W 2 of the flat heat transfer tubes 2, 2 before and after the plurality of rows .... Condensed water falls on both front and rear edges 4b, 4b ..., 4b, 4b ..., 4b, 4b ..., and the edges 4b, 4b ... 4b, 4b ... 4b, 4b... Is smoothly discharged onto the drain pan.

したがって、やはり上述のように、上記空気熱交換器１を蒸発器として利用した場合にも、凝縮水の排出性能がよくなり、圧損が低下するとともに熱伝達性能が向上する。その結果、当該空気熱交換器１の大きさが大きい時はもちろん、小型化した時にも有効に空気側の伝熱性能を向上させることができる。   Therefore, as described above, even when the air heat exchanger 1 is used as an evaporator, the condensate discharge performance is improved, the pressure loss is reduced, and the heat transfer performance is improved. As a result, the air-side heat transfer performance can be effectively improved not only when the size of the air heat exchanger 1 is large but also when it is downsized.

これらの結果、本実施の形態の空気熱交換器１によると、コルゲートフィン４，４・・・と扁平伝熱管２，２・・・の相対的な大きさを変更するのみの簡単かつ低コストな構成で、熱伝達性能の高い、軽量かつ小型の扁平伝熱管およびコルゲートフィンを備えたフィンチューブ式空気熱交換器を提供することが可能となる。   As a result, according to the air heat exchanger 1 of the present embodiment, it is simple and low-cost only by changing the relative sizes of the corrugated fins 4, 4... And the flat heat transfer tubes 2, 2. With a simple structure, it is possible to provide a finned tube type air heat exchanger having a light and small flat heat transfer tube and corrugated fins with high heat transfer performance.

（最良の実施の形態３）
図４は、この出願の発明の最良の実施の形態３に係る扁平伝熱管およびコルゲートフィンを備えた空気熱交換器の扁平伝熱管とコルゲートフィン部分の構造を示している。 (Best Mode 3)
FIG. 4 shows the structure of a flat heat transfer tube and a corrugated fin portion of an air heat exchanger provided with a flat heat transfer tube and a corrugated fin according to the third preferred embodiment of the present invention.

この実施の形態の空気熱交換器１も、図４に示すように、最良の実施の形態２の場合と同様に上記コルゲートフィン４，４・・・を前後２本の各扁平伝熱管２，２・・・、２，２・・・に共通なものし、その全体の幅Ｗ1を上記前後２列の扁平伝熱管２，２・・・、２，２・・・の配列幅Ｗ2よりも大きく形成する一方、上記扁平伝熱管２，２・・・に対応する部分（接触する部分）を上記扁平伝熱管２，２・・・の厚さｔの１／２程度切り欠いて上記扁平伝熱管２，２・・・を介することなく隣合う上下コルゲートフィン４，４・・・の縁部４ｂ，４ｂ・・・、４ｂ，４ｂ・・・同士を相互のフィン面がＶ字形に連続するように相互に当接させているが、その場合において、上記扁平伝熱管２，２・・・、２，２・・・の配列幅Ｗ2よりも幅Ｗ1が広くなることにより形成されたコルゲートフィン４，４・・・の扁平伝熱管２，２・・・、２，２・・・よりも外側に位置する縁部４ｂ，４ｂ・・・、４ｂ，４ｂ・・・を、各扁平伝熱管２，２・・・、２，２・・・の空気流の下流側にのみ設けたことを特徴としている。 As shown in FIG. 4, the air heat exchanger 1 of this embodiment also has the corrugated fins 4, 4... 2 ..., 2,2 and those common to ..., flattened heat transfer tubes 2, 2 of the width W 1 of the entire the front and rear two rows 2, 2 sequences width W 2 The portion corresponding to the flat heat transfer tubes 2, 2... (Contact portion) is cut out about ½ of the thickness t of the flat heat transfer tubes 2, 2. The edges 4b, 4b, 4b, 4b,... Of adjacent upper and lower corrugated fins 4, 4,... Without passing through the flat heat transfer tubes 2, 2,. Although abut one another as successive, in that case, the flat heat transfer tube 2, 2, 2, 2 width than the arrangement width W 2 of 1 corrugated fin formed by the widened 4,4 ... flat heat transfer tubes 2, 2, edges 4b located outside the 2, 2, 4b ..., 4b , 4b,... Are provided only on the downstream side of the air flow of the flat heat transfer tubes 2, 2,.

上記構成の空気熱交換器を扁平伝熱管２，２・・・、２，２・・・部分を水平にして蒸発器として使用した場合、各段のコルゲートフィン４，４・・・の波形の底部の全体に凝縮水が滞留するが、この凝縮水は空気流に押されて空気流下流側に集まる。   When the air heat exchanger having the above configuration is used as an evaporator with the flat heat transfer tubes 2, 2,..., 2, 2... Horizontally, the corrugated fins 4, 4. Condensed water stays in the entire bottom, but this condensed water is pushed by the air flow and collects on the downstream side of the air flow.

したがって、上記扁平伝熱管２，２・・・、２，２・・・の配列幅Ｗ2よりも幅が広くなることにより形成されたコルゲートフィン４，４・・・の扁平伝熱管２，２・・・、２，２・・・よりも外側に位置する縁部４ｂ，４ｂ・・・、４ｂ，４ｂ・・・は、図４のように少なくとも各扁平伝熱管２，２・・・、２，２・・・の空気流の下流側にのみ設けられていれば、十分に凝縮の排出が可能であり、有効に空気側熱伝達性能の向上に寄与する。 Therefore, the flattened heat transfer tubes 2, 2, 2, 2 ... sequence width W corrugated fins formed by a width wider than 2 4,4 ... flattened heat transfer tubes 2, 2 The edges 4b, 4b,..., 4b, 4b... Located outside of 2, 2,... Are at least flat heat transfer tubes 2, 2,. If it is provided only on the downstream side of the air flow of 2, 2,..., The condensation can be sufficiently discharged and contributes to the improvement of the air side heat transfer performance effectively.

本願発明の最良の実施の形態１に係る扁平伝熱管およびコルゲートフィンを備えた空気熱交換器の構造を示す縦断面図である。It is a longitudinal cross-sectional view which shows the structure of the air heat exchanger provided with the flat heat exchanger tube and corrugated fin which concern on the best Embodiment 1 of this invention. 同熱交換器の図１の状態における右側面図である。It is a right view in the state of FIG. 1 of the same heat exchanger. 本願発明の最良の実施の形態２に係る扁平伝熱管およびコルゲートフィンを備えた空気熱交換器の構造を示す縦断面図である。It is a longitudinal cross-sectional view which shows the structure of the air heat exchanger provided with the flat heat exchanger tube and corrugated fin which concerns on best Embodiment 2 of this invention. 本願発明の最良の実施の形態３に係る扁平伝熱管およびコルゲートフィンを備えた空気熱交換器の構造を示す縦断面図である。It is a longitudinal cross-sectional view which shows the structure of the air heat exchanger provided with the flat heat exchanger tube and corrugated fin which concern on the best Embodiment 3 of this invention. 従来の扁平伝熱管およびコルゲートフィンを備えた空気熱交換器の全体構造を示す斜視図である。It is a perspective view which shows the whole structure of the air heat exchanger provided with the conventional flat heat exchanger tube and the corrugated fin. 同空気熱交換器のコルゲートフィンの構造を示す斜視図である。It is a perspective view which shows the structure of the corrugated fin of the same air heat exchanger. 同空気熱交換器の扁平伝熱管およびコルゲートフィン部分の縦断面図である。It is a longitudinal cross-sectional view of the flat heat exchanger tube and the corrugated fin part of the air heat exchanger. 同空気熱交換器を蒸発器として使用した場合における扁平伝熱管およびコルゲートフィン部分の縦断面図（凝縮水の滞留状態を示す図）である。It is a longitudinal cross-sectional view (The figure which shows the residence state of condensed water) of a flat heat exchanger tube and a corrugated fin part at the time of using the same air heat exchanger as an evaporator.

符号の説明Explanation of symbols

１は熱交換器、２は扁平伝熱管、３Ａは右側ヘツダ、３Ｂは左側ヘツダ、４はコルゲートフィン、４ａは切り起し片（ルーバー）、４ｂはフィン幅を拡大した伝熱管外側部分のコルゲートフィン縁部である。   1 is a heat exchanger, 2 is a flat heat transfer tube, 3A is a right header, 3B is a left header, 4 is a corrugated fin, 4a is a cut-and-raised piece (louver), and 4b is a corrugated outer portion of the heat transfer tube with an expanded fin width Fin edge.

Claims (4)

ヘッダ（３Ａ），（３Ｂ）の間に複数本の扁平伝熱管（２），（２）・・・を、それら複数本の扁平伝熱管（２），（２）・・・の間にコルゲートフィン（４），（４）・・・をそれぞれ配設してなる空気熱交換器であって、上記コルゲートフィン（４），（４）・・・の幅を上記扁平伝熱管（２），（２）・・・の幅よりも相対的に大きく形成する一方、同コルゲートフィン（４），（４）・・・の上記扁平伝熱管（２），（２）・・・に対応する部分を切り欠いて上記扁平伝熱管（２），（２）・・・に対応する部分よりも外側の上記扁平伝熱管（２），（２）・・・を介さずに隣合う縁部（４ｂ），（４ｂ）・・・同士を相互に連続させることにより、凝縮水の排出通路を形成したことを特徴とする空気熱交換器。   A plurality of flat heat transfer tubes (2), (2)... Between the headers (3A), (3B) and a corrugate between the plurality of flat heat transfer tubes (2), (2). Is an air heat exchanger in which fins (4), (4)... Are arranged, and the width of the corrugated fins (4), (4). (2)... Part corresponding to the flat heat transfer tubes (2), (2)... Of the corrugated fins (4), (4). The edge (4b) adjacent to the flat heat transfer tubes (2), (2)... Outside the portions corresponding to the flat heat transfer tubes (2), (2). ), (4b)... An air heat exchanger characterized in that a condensed water discharge passage is formed by making each other continuous. ヘッダ（３Ａ），（３Ｂ）の間に複数本の扁平伝熱管（２），（２）・・・を、それら複数本の扁平伝熱管（２），（２）・・・の間にコルゲートフィン（４），（４）・・・をそれぞれ配設してなる空気熱交換器であって、上記扁平伝熱管（２），（２）・・・を空気流の上流側から下流側にかけて２本以上並設するとともに、それら各扁平伝熱管（２），（２）・・・、（２），（２）・・・に対して上記コルゲートフィン（４），（４）・・・を共通な１枚のものとし、かつ上記コルゲートフィン（４），（４）・・・の幅を上記扁平伝熱管（２），（２）・・・、（２），（２）・・・の幅よりも相対的に大きく形成する一方、同コルゲートフィン（４），（４）・・・の上記扁平伝熱管（２），（２）・・・、（２），（２）・・・に対応する部分を切り欠いて上記扁平伝熱管（２），（２）・・・、（２），（２）・・・に対応する部分よりも外側の上記扁平伝熱管（２），（２）・・・、（２），（２）・・・を介さずに隣合う縁部（４ｂ），（４ｂ）・・・同士を相互に連続させることにより、凝縮水の排出通路を形成したことを特徴とする空気熱交換器。   A plurality of flat heat transfer tubes (2), (2)... Between the headers (3A), (3B) and a corrugate between the plurality of flat heat transfer tubes (2), (2). Is an air heat exchanger in which fins (4), (4),... Are arranged, respectively, and the flat heat transfer tubes (2), (2),. Two or more are arranged side by side, and the corrugated fins (4), (4),... For the flat heat transfer tubes (2), (2),. , And the width of the corrugated fins (4), (4),..., The flat heat transfer tubes (2), (2), (2), (2),. The corrugated fins (4), (4), etc. are formed relatively larger than the flat heat transfer tubes (2), (2), (2), (2)・The flat heat transfer tubes (2), (2), (2), (2), outside the portions corresponding to the flat heat transfer tubes (2), (2), (2), 2) ..., (2), (2) ... The adjacent edges (4b), (4b) ... are connected to each other to form a condensed water discharge passage. An air heat exchanger characterized by that. 扁平伝熱管（２），（２）・・・の幅よりも相対的に幅が広くなることにより形成されたコルゲートフィン（４），（４）・・・の扁平伝熱管（２），（２）・・・よりも外側に位置する縁部（４ｂ），（４ｂ）・・・は、当該コルゲートフィン（４），（４）・・・の空気流の下流側にのみ設けられていることを特徴とする請求項１又は２記載の空気熱交換器。   The flat heat transfer tubes (2), (4), (4), the flat heat transfer tubes (2), (4), formed by being relatively wider than the widths of the flat heat transfer tubes (2), (2), ( Edges (4b), (4b)... Located outside of 2)... Are provided only on the downstream side of the airflow of the corrugated fins (4), (4). The air heat exchanger according to claim 1 or 2, characterized in that. 扁平伝熱管（２），（２）・・・の幅よりも相対的に幅が広くなることにより形成されたコルゲートフィン（４），（４）・・・の扁平伝熱管（２），（２）・・・よりも外側に位置する縁部（４ｂ），（４ｂ）・・・は、当該コルゲートフィン（４），（４）・・・の空気流の上流側と下流側の両方に設けられていることを特徴とする請求項１又は２記載の空気熱交換器。   The flat heat transfer tubes (2), (4), (4), the flat heat transfer tubes (2), (4), formed by being relatively wider than the widths of the flat heat transfer tubes (2), (2), ( 2) The edges (4b), (4b)... Located on the outside of the corrugated fins (4), (4). The air heat exchanger according to claim 1 or 2, wherein the air heat exchanger is provided.
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US9863714B2 (en) 2013-07-30 2018-01-09 Samsung Electronics Co., Ltd. Heat exchanger and corrugated fin thereof
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US20180100659A1 (en) * 2015-03-30 2018-04-12 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
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CN108007251B (en) * 2017-11-30 2020-08-28 博耐尔汽车电气系统有限公司 Parallel flow condenser fin of automobile air conditioner
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