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JP5772608B2 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
JP5772608B2
JP5772608B2 JP2012003903A JP2012003903A JP5772608B2 JP 5772608 B2 JP5772608 B2 JP 5772608B2 JP 2012003903 A JP2012003903 A JP 2012003903A JP 2012003903 A JP2012003903 A JP 2012003903A JP 5772608 B2 JP5772608 B2 JP 5772608B2
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Japan
Prior art keywords
tube
fin
longitudinal direction
pitch
concave portion
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Expired - Fee Related
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JP2012003903A
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Japanese (ja)
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JP2013142515A (en
Inventor
アウン 太田
アウン 太田
中村　貢
貢 中村
鳥越　栄一
栄一 鳥越
聡也 長沢
聡也 長沢
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Denso Corp
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Denso Corp
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Priority to JP2012003903A priority Critical patent/JP5772608B2/en
Priority to PCT/JP2013/000025 priority patent/WO2013105490A1/en
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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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet

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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)

Description

本発明は、例えば、車両のエンジン冷却システムに用いられるラジエータ、あるいは、空調用の冷媒凝縮器、冷媒蒸発器、ヒータコア等に好適な熱交換器に関する。   The present invention relates to a heat exchanger suitable for, for example, a radiator used in a vehicle engine cooling system, or a refrigerant condenser, a refrigerant evaporator, a heater core, etc. for air conditioning.

従来技術として、特許文献１に開示された熱交換器がある。
この熱交換器は、例えば、自動車に搭載される暖房用のヒータコアであり、図９に示す様に、断面形状が偏平なチューブ１００と、このチューブ１００の偏平な表面（偏平面と呼ぶ）に接合されるフィン１１０とで構成される放熱コア部を有し、チューブ１００の内部を流れるエンジン冷却水との熱交換によって放熱コア部を通過する空気、すなわち、車室内へ送風される空気を加熱している。
フィン１１０は、図１０に示す様に、一定のフィンピッチＦＰを有して波状に折り曲げ形成されたコルゲートフィンであり、フィン表面にルーバ１２０（図９参照）が形成されている。このルーバ１２０は、フィン表面を流れる空気の流れを乱すことで空気側の伝熱性能を高める働きを有するが、ルーバ１２０が形成されていない部分（非ルーバ部と呼ぶ）を空気が通過すると、伝熱性能の向上効果が小さくなる。 As a prior art, there is a heat exchanger disclosed in Patent Document 1.
This heat exchanger is, for example, a heater core for heating mounted on an automobile. As shown in FIG. 9, a tube 100 having a flat cross-sectional shape and a flat surface (referred to as a flat surface) of the tube 100 are used. Heating the air passing through the heat radiating core by heat exchange with the engine cooling water flowing inside the tube 100, that is, the air blown into the passenger compartment, having a heat radiating core composed of the fins 110 to be joined. doing.
As shown in FIG. 10, the fin 110 is a corrugated fin that is bent and formed in a wave shape with a constant fin pitch FP, and a louver 120 (see FIG. 9) is formed on the fin surface. This louver 120 has a function of improving the heat transfer performance on the air side by disturbing the flow of air flowing on the fin surface, but when air passes through a part where the louver 120 is not formed (referred to as a non-louver part), The effect of improving heat transfer performance is reduced.

そこで、特許文献１では、チューブ１００の一方の偏平面にチューブ１００の外側へ向かって突出する凸部１３０を設けることで、非ルーバ部を流れる空気の通風抵抗を増大させて、ルーバ１２０が形成されている領域を流れる空気流量を増大させる技術が開示されている。
また、チューブ１００の他方の偏平面には、チューブ１００の内側へ向かって窪む凹部１４０が設けられている。この凹部１４０を設けることにより、エンジン冷却水側の放熱面積が増大すると共に、チューブ１００内の流路が蛇行した形状となるため、チューブ１００の内部を流れるエンジン冷却水を攪拌させる効果が得られる。その結果、エンジン冷却水側の伝熱性能を向上させることができる。なお、凸部１３０と凹部１４０は、チューブ１００の長手方向（図１０の左右方向）、つまり、エンジン冷却水が流れる方向にフィンピッチＦＰと同ピッチで複数段に形成されている。 Therefore, in Patent Document 1, a convex portion 130 protruding toward the outside of the tube 100 is provided on one of the flat surfaces of the tube 100, thereby increasing the ventilation resistance of the air flowing through the non-louver portion, thereby forming the louver 120. Techniques have been disclosed for increasing the flow rate of air flowing through a defined area.
Further, a concave portion 140 that is recessed toward the inside of the tube 100 is provided on the other flat surface of the tube 100. Providing this recess 140 increases the heat dissipation area on the engine coolant side, and the flow path in the tube 100 has a meandering shape, so that the effect of stirring the engine coolant flowing inside the tube 100 can be obtained. . As a result, the heat transfer performance on the engine coolant side can be improved. The convex portion 130 and the concave portion 140 are formed in a plurality of stages at the same pitch as the fin pitch FP in the longitudinal direction of the tube 100 (the left-right direction in FIG. 10), that is, the direction in which the engine coolant flows.

特開２０１１−４３３２２号公報JP 2011-43322 A

ところが、特許文献１に開示された熱交換器は、チューブ１００の他方の偏平面に凹部１４０が形成され、その凹部１４０が形成された部位にフィン１１０の屈曲部（チューブ１００との接合部）が配置される。この場合、図１０に示す様に、凹部１４０が形成されている部分では、フィン１１０の屈曲部と凹部１４０との間に隙間が生じるため、フィン１１０とチューブ１００とを接合できない箇所が生じる。その結果、フィン効率が低下して、熱交換器の性能向上が目減りするという問題がある。
本発明は、上記事情に基づいて成されたもので、その目的は、フィン効率を高めることにより性能を向上できる熱交換器を提供することにある。 However, in the heat exchanger disclosed in Patent Document 1, the concave portion 140 is formed on the other flat surface of the tube 100, and the bent portion of the fin 110 (joined portion with the tube 100) is formed at the portion where the concave portion 140 is formed. Is placed. In this case, as shown in FIG. 10, a gap is formed between the bent portion of the fin 110 and the concave portion 140 in the portion where the concave portion 140 is formed, so that a portion where the fin 110 and the tube 100 cannot be joined is generated. As a result, there is a problem that the fin efficiency is lowered and the performance improvement of the heat exchanger is reduced.
The present invention has been made based on the above circumstances, and an object thereof is to provide a heat exchanger that can improve performance by increasing fin efficiency.

（請求項１の発明）
本発明は、所定の間隔を空けて並列に配置される複数本のチューブと、隣り合うチューブ同士の間に配置されてチューブの表面に接合されるフィンと、チューブの長手方向の両端部が挿入される一対のヘッダタンクとを有し、チューブの内部を流れる流体とチューブの外側を流れる流体との間で熱交換を行う熱交換器において、フィンは、一定のフィンピッチを有して波状に折り曲げ成形されたコルゲートフィンであり、チューブは、長手方向と直交する断面形状が長径と短径とを有する偏平管形状に形成され、且つ、短径方向に対向する一方の偏平面にチューブの外側へ向かって突出する凸部が設けられ、他方の偏平面にチューブの内側に向かって窪む凹部が設けられている。 (Invention of Claim 1)
The present invention inserts a plurality of tubes arranged in parallel at a predetermined interval, fins arranged between adjacent tubes and joined to the surface of the tube, and both ends in the longitudinal direction of the tubes In a heat exchanger that exchanges heat between a fluid flowing inside the tube and a fluid flowing outside the tube, the fins have a certain fin pitch and are wave-shaped. A corrugated fin formed by bending, and the tube is formed into a flat tube shape having a cross-sectional shape perpendicular to the longitudinal direction having a major axis and a minor axis, and the outer side of the tube is disposed on one flat surface facing the minor axis direction. A convex portion that protrudes toward the inside is provided, and a concave portion that is recessed toward the inside of the tube is provided on the other flat surface.

凸部と凹部は、チューブの長手方向にフィンピッチと同ピッチで複数段に配置され、フィンを挟んで隣り合う一方のチューブを第１のチューブ、他方のチューブを第２のチューブと呼び、チューブの長手方向に隣り合う凸部同士および凹部同士の間隔をディンプルピッチと呼ぶ時に、第１のチューブと第２のチューブは、第１のチューブの一方の偏平面と第２のチューブの他方の偏平面とがフィンを挟んで対向して配置され、且つ、第１のチューブに設けられる凸部と第２のチューブに設けられる凹部は、チューブの長手方向に対する互いの位置がディンプルピッチの半ピッチ分ずれて配置されることを特徴とする。   The convex portion and the concave portion are arranged in a plurality of stages at the same pitch as the fin pitch in the longitudinal direction of the tube. One tube adjacent to the fin is called a first tube, and the other tube is called a second tube. When the interval between the convex portions and the concave portions adjacent to each other in the longitudinal direction is referred to as a dimple pitch, the first tube and the second tube have one flat surface of the first tube and the other flat portion of the second tube. The convex portion provided on the first tube and the concave portion provided on the second tube are arranged so as to face each other across the fin, and the positions of the convex portion provided on the second tube are a half pitch of the dimple pitch with respect to the longitudinal direction of the tube. It is characterized by being displaced.

本発明の熱交換器は、第１のチューブの一方の偏平面に設けられる凸部と、第２のチューブの他方の偏平面に設けられる凹部とが、チューブの長手方向で同一位置に配置されることはなく、ディンプルピッチの半ピッチ毎に凸部と凹部とが交互に配置される。
また、本発明のフィンは、波状に連続して折り曲げられる屈曲部を有し、この屈曲部がチューブの表面に接合される。ここで、第１のチューブに接合される屈曲部を第１屈曲部、第２のチューブに接合される屈曲部を第２屈曲部と呼ぶ時に、第１屈曲部と第２屈曲部は、半ピッチ毎に交互に繰り返し設けられる。 In the heat exchanger according to the present invention, the convex portion provided on one flat surface of the first tube and the concave portion provided on the other flat surface of the second tube are arranged at the same position in the longitudinal direction of the tube. The convex portions and the concave portions are alternately arranged every half of the dimple pitch.
The fin of the present invention has a bent portion that is continuously bent in a wave shape, and the bent portion is joined to the surface of the tube. Here, when the bent portion joined to the first tube is called a first bent portion and the bent portion joined to the second tube is called a second bent portion, the first bent portion and the second bent portion are half It is repeatedly provided alternately for each pitch.

よって、第１のチューブの長手方向で隣り合う凸部同士の間、つまり、凸部が設けられていない第１のチューブの一方の偏平面に第１屈曲部を接合することで、必然的に、第２のチューブの長手方向で隣り合う凹部同士の間、つまり、凹部が設けられていない第２のチューブの他方の偏平面に第２屈曲部が接合される。
これにより、第２のチューブの他方の偏平面に凹部を設けた構成であっても、その凹部が設けられている部位にフィンの第２屈曲部が配置されることはない。言い換えると、フィンの第２屈曲部は、第２のチューブに設けられる凹部の数に関係なく、第２のチューブの長径方向に対してフィンの全幅に渡って接合できる。 Therefore, by joining the first bent portion between the convex portions adjacent to each other in the longitudinal direction of the first tube, that is, one of the first tube without the convex portion, the first bent portion is necessarily joined. The second bent portion is joined between the concave portions adjacent to each other in the longitudinal direction of the second tube, that is, the other flat surface of the second tube not provided with the concave portion.
Thereby, even if it is the structure which provided the recessed part in the other eccentric plane of a 2nd tube, the 2nd bending part of a fin is not arrange | positioned in the site | part in which the recessed part is provided. In other words, the second bent portion of the fin can be joined over the entire width of the fin with respect to the major axis direction of the second tube regardless of the number of concave portions provided in the second tube.

さらに、本発明の熱交換器において、チューブは、一方の偏平面に設けられる凸部と、他方の偏平面に設けられる凹部とが長手方向に対して互いに同位置に配置されており、チューブの端部がヘッダタンクの内部に挿入される長さを挿入代と定義した時に、一対のヘッダタンクの内、一方のヘッダタンクに対する第１のチューブの挿入代の方が第２のチューブの挿入代よりディンプルピッチの半ピッチ分だけ小さく、且つ、他方のヘッダタンクに対する第１のチューブの挿入代の方が第２のチューブの挿入代よりディンプルピッチの半ピッチ分だけ大きく設定されていることを特徴とする。 Furthermore, in the heat exchanger of the present invention , the tube has a convex portion provided on one of the flat surfaces and a concave portion provided on the other flat surface arranged at the same position relative to the longitudinal direction. When the length at which the end portion is inserted into the header tank is defined as the insertion allowance, the insertion allowance for the first tube relative to one header tank of the pair of header tanks is greater than the insertion allowance for the second tube. The dimple pitch is smaller by half the dimple pitch, and the insertion allowance of the first tube relative to the other header tank is set larger than the insertion allowance of the second tube by the half pitch of the dimple pitch. And

上記の構成では、第１のチューブと第２のチューブを同一形状とし、且つ、一対のヘッダタンクに対する第１のチューブと第２のチューブの挿入代をディンプルピッチの半ピッチ分ずらすことにより、第１のチューブの一方の偏平面に設けられる凸部と、第２のチューブの他方の偏平面に設けられる凹部とを、チューブの長手方向にディンプルピッチの半ピッチ分ずらして配置することができる。これにより、第１のチューブと第２のチューブを１種類のチューブで構成できる。   In the above configuration, the first tube and the second tube have the same shape, and the insertion allowance of the first tube and the second tube with respect to the pair of header tanks is shifted by a half pitch of the dimple pitch. The convex portion provided on one flat surface of one tube and the concave portion provided on the other flat surface of the second tube can be arranged so as to be shifted by a half pitch of the dimple pitch in the longitudinal direction of the tube. Thereby, a 1st tube and a 2nd tube can be comprised by one type of tube.

（請求項２の発明）
本発明の熱交換器では、チューブは、一方の偏平面に設けられる凸部と、他方の偏平面に設けられる凹部とが、長手方向に対して互いに同位置に配置され、且つ、長手方向の一端から最も近い凸部および凹部までの距離より、長手方向の他端から最も
近い凸部および凹部までの距離の方がディンプルピッチの半ピッチ分だけ大きく設定され、第１のチューブと第２のチューブは、互いの一端と他端とが長手方向に反転した状態で配置されていることを特徴とする。 (Invention of Claim 2 )
In the heat exchanger according to the present invention , the tube has a convex portion provided on one of the flat surfaces and a concave portion provided on the other flat surface arranged in the same position with respect to the longitudinal direction, and in the longitudinal direction. The distance from the other end in the longitudinal direction to the nearest convex portion and the concave portion is set to be larger by the half pitch of the dimple pitch than the distance from the one end to the nearest convex portion and the concave portion. The tubes are arranged in a state where one end and the other end of each tube are inverted in the longitudinal direction.

上記の構成では、第１のチューブと第２のチューブを同一形状とし、且つ、一対のヘッダタンクに対して第１のチューブと第２のチューブを長手方向に反転して組み付ける、つまり、第１のチューブの一端と第２のチューブの他端、および、第１のチューブの他端と第２のチューブの一端をそれぞれ同一方向に向けて組み付けることにより、第１のチューブの一方の偏平面に設けられる凸部と、第２のチューブの他方の偏平面に設けられる凹部とを、チューブの長手方向にディンプルピッチの半ピッチ分ずらして配置することができる。これにより、第１のチューブと第２のチューブを１種類のチューブで構成できる。   In the above configuration, the first tube and the second tube have the same shape, and the first tube and the second tube are assembled to the pair of header tanks while being inverted in the longitudinal direction. By assembling one end of the tube and the other end of the second tube, and the other end of the first tube and one end of the second tube in the same direction, respectively, one flat surface of the first tube The convex portion provided and the concave portion provided on the other flat surface of the second tube can be arranged shifted by a half pitch of the dimple pitch in the longitudinal direction of the tube. Thereby, a 1st tube and a 2nd tube can be comprised by one type of tube.

（請求項３の発明）
請求項１または請求項２に記載した熱交換器において、フィンは、第１のチューブと第２のチューブとの間で交互に連続して折れ曲がる屈曲部と、連続する二つの屈曲部同士の間に形成されるフィン平面部とを有し、このフィン平面部にルーバが形成されていることを特徴とする。
フィン平面部にルーバを形成することにより、チューブの外側を流れる流体とフィンとの熱伝達率を増大できるので、熱交換器の性能向上に寄与する。また、本発明の熱交換器は、チューブの一方の偏平面に凸部を設けているので、フィン表面にルーバが形成されていない非ルーバ部を流れる流体の流れ抵抗が増大する。その結果、非ルーバ部を流れる流体流量が低減する分、ルーバが形成されている領域を流れる流体流量が増大するため、熱交換器の性能が向上する。 (Invention of Claim 3 )
3. The heat exchanger according to claim 1 , wherein the fins are alternately bent continuously between the first tube and the second tube, and between the two continuous bent portions. And a louver is formed on the fin plane portion.
By forming the louver on the fin plane portion, the heat transfer coefficient between the fluid flowing outside the tube and the fin can be increased, which contributes to the improvement of the performance of the heat exchanger. Moreover, since the heat exchanger of this invention has provided the convex part in the one flat surface of a tube, the flow resistance of the fluid which flows through the non-louver part in which the louver is not formed in the fin surface increases. As a result, the flow rate of the fluid flowing through the non-louver portion is reduced and the flow rate of the fluid flowing through the region where the louver is formed is increased, so that the performance of the heat exchanger is improved.

放熱コアの一部を示す斜視図である。It is a perspective view which shows a part of heat radiating core. フィンの斜視図である。It is a perspective view of a fin. フィンを挟んで対向する第１のチューブと第２のチューブの断面図である。It is sectional drawing of the 1st tube and 2nd tube which oppose on both sides of a fin. ヒータコアの正面図である。It is a front view of a heater core. （ａ）実施例２に係るチューブの断面図、（ｂ）フィンを挟んで対向する第１のチューブと第２のチューブの断面図である。(A) Sectional drawing of the tube which concerns on Example 2, (b) It is sectional drawing of the 1st tube and 2nd tube which oppose on both sides of a fin. （ａ）実施例３に係るチューブの断面図、（ｂ）フィンを挟んで対向する第１のチューブと第２のチューブの断面図である。(A) Sectional drawing of the tube which concerns on Example 3, (b) It is sectional drawing of the 1st tube and 2nd tube which oppose on both sides of a fin. （ａ）実施例４に係るチューブの断面図、（ｂ）フィンを挟んで対向する第１のチューブと第２のチューブの断面図である。(A) Sectional drawing of the tube which concerns on Example 4, (b) It is sectional drawing of the 1st tube and 2nd tube which oppose on both sides of a fin. フィンの斜視図である（実施例５）。(Example 5) which is a perspective view of a fin. 従来技術に係るチューブの長手方向と直交する断面図である。It is sectional drawing orthogonal to the longitudinal direction of the tube which concerns on a prior art. 従来技術に係るチューブの長手方向に沿った断面図である。It is sectional drawing along the longitudinal direction of the tube which concerns on a prior art.

本発明を実施するための最良の形態を、以下の５つの実施例と変形例により詳細に説明する。なお、５つの実施例のうち、実施例２は、本発明が適用されていない例を示す参考例である。 The best mode for carrying out the present invention will be described in detail with reference to the following five examples and modifications . Of the five examples, Example 2 is a reference example showing an example to which the present invention is not applied.

（実施例１）
実施例１では、本発明の熱交換器を自動車に搭載される暖房用のヒータコアに適用した一例を説明する。
ヒータコア１は、図４に示す様に、エンジンを冷却して暖められたエンジン冷却水と車室内に送風される空気とを熱交換する熱交換コア部（以下に説明する）と、この熱交換コア部の両端に配置される一対のヘッダタンク２とを備える。
熱交換コア部は、所定の間隔を空けて並列に配置される複数本のチューブ３と、隣り合うチューブ３同士の間に配置されてチューブ３の表面に接合されるフィン４と、熱交換コア部の両サイド（図４の上下両側）に配置される補強プレート５とで構成される。 Example 1
In Example 1, an example in which the heat exchanger of the present invention is applied to a heater core for heating mounted in an automobile will be described.
As shown in FIG. 4, the heater core 1 includes a heat exchange core portion (described below) that exchanges heat between engine cooling water that has been cooled by cooling the engine and air that is blown into the vehicle interior, and this heat exchange. And a pair of header tanks 2 disposed at both ends of the core portion.
The heat exchange core section includes a plurality of tubes 3 arranged in parallel at a predetermined interval, fins 4 arranged between adjacent tubes 3 and joined to the surface of the tubes 3, and a heat exchange core It is comprised with the reinforcement plate 5 arrange | positioned at the both sides (upper and lower both sides of FIG. 4) of a part.

チューブ３は、図１に示す様に、自身の長手方向と直交する断面形状が長径と短径とを有する偏平管形状に形成され、内部にエンジン冷却水が流れる冷却水路を形成している。 フィン４は、図２に示す様に、一定のフィンピッチＦＰを有して波状に連続して折り曲げ成形されたコルゲートフィンである。このフィン４は、隣り合うチューブ３同士の間で交互に連続して円弧状に折れ曲がる屈曲部４０と、連続する二つの屈曲部４０同士の間に形成される平板状のフィン平面部４１とを有し、屈曲部４０の頂点でチューブ３の偏平面に接合されている。また、フィン平面部４１には、フィン平面部４１の一部をコの字状に切り起こして形成されたルーバ４２が設けられている。   As shown in FIG. 1, the tube 3 is formed in a flat tube shape in which a cross-sectional shape perpendicular to the longitudinal direction of the tube 3 has a major axis and a minor axis, and forms a cooling water channel through which engine cooling water flows. As shown in FIG. 2, the fin 4 is a corrugated fin that is continuously bent in a wave shape with a constant fin pitch FP. The fin 4 includes a bent portion 40 that is alternately and continuously bent between adjacent tubes 3, and a flat fin plane portion 41 that is formed between two continuous bent portions 40. And is joined to the flat surface of the tube 3 at the apex of the bent portion 40. Further, the fin plane portion 41 is provided with a louver 42 formed by cutting and raising a part of the fin plane portion 41 into a U-shape.

ヘッダタンク２は、図４に示す様に、チューブ３の一端側の端部が挿入される一方のヘッダタンク２ａと、チューブ３の他端側の端部が挿入される他方のヘッダタンク２ｂとを有し、チューブ３を通じて一方のヘッダタンク２ａと他方のヘッダタンク２ｂとが連通している。また、ヘッダタンク２には、温水配管（図示せず）を介してエンジンの冷却水回路に接続される接続ポート６が設けられている。
本実施例のヒータコア１は、チューブ３、フィン４、補強プレート５、および、ヘッダタンク２がいずれも同一種類の金属（例えば、熱伝導性が高いアルミニウム）を使用して形成され、放熱コア部を組み立ててヘッダタンク２を組み付けた状態で、例えば、炉中ろう付け、あるいは半田付けによって一体に接合されている。 As shown in FIG. 4, the header tank 2 includes one header tank 2 a into which one end of the tube 3 is inserted, and the other header tank 2 b into which the other end of the tube 3 is inserted. And one header tank 2a and the other header tank 2b communicate with each other through the tube 3. Further, the header tank 2 is provided with a connection port 6 connected to the engine coolant circuit via a hot water pipe (not shown).
In the heater core 1 of the present embodiment, the tube 3, the fin 4, the reinforcing plate 5, and the header tank 2 are all formed using the same type of metal (for example, aluminum having high thermal conductivity), and the heat radiating core portion. And the header tank 2 are assembled together, and are joined together by brazing in a furnace or soldering, for example.

次に、本発明に係るチューブ３の構成およびフィン４の配置について詳述する。
実施例１に係るチューブ３は、図１に示す様に、短径方向に対向する一方の偏平面にチューブ３の外側へ向かって半球状に突出する凸部７が設けられ、他方の偏平面にチューブ３の内側に向かって半球状に窪む凹部８が設けられている。この凸部７および凹部８は、それぞれ、チューブ３の長径方向に一定の間隔を有して複数個設けられ、且つ、チューブ３の長手方向にフィンピッチＦＰと同ピッチで複数段に配置されている。なお、同一チューブ３に設けられる凸部７と凹部８は、チューブ３の長手方向に対して互いに同位置に配置されている。以下、チューブ３の長手方向に隣り合う凸部７同士および凹部８同士の間隔をディンプルピッチＤＰと呼ぶ。 Next, the configuration of the tube 3 and the arrangement of the fins 4 according to the present invention will be described in detail.
As shown in FIG. 1, the tube 3 according to the first embodiment is provided with a convex portion 7 projecting in a hemispherical shape toward the outside of the tube 3 on one of the flat surfaces facing the minor axis direction, and the other flat surface. A recess 8 that is recessed in a hemispherical shape toward the inside of the tube 3 is provided. A plurality of the convex portions 7 and the concave portions 8 are provided with a certain interval in the major axis direction of the tube 3, and are arranged in a plurality of stages at the same pitch as the fin pitch FP in the longitudinal direction of the tube 3. Yes. In addition, the convex part 7 and the recessed part 8 provided in the same tube 3 are arrange | positioned mutually at the same position with respect to the longitudinal direction of the tube 3. Hereinafter, the interval between the convex portions 7 and the concave portions 8 adjacent to each other in the longitudinal direction of the tube 3 is referred to as a dimple pitch DP.

また、図３に示す様に、フィン４を挟んで隣り合う一方のチューブ３を第１のチューブ３ａ、他方のチューブ３を第２のチューブ３ｂと呼ぶ時に、その第１のチューブ３ａと第２のチューブ３ｂは、第１のチューブ３ａの一方の偏平面（凸部７が設けられている偏平面）と第２のチューブの他方の偏平面（凹部８が設けられている偏平面）とがフィン４を挟んで対向して配置され、且つ、第１のチューブ３ａに設けられる凸部７と、第２のチューブ３ｂに設けられる凹部８は、互いの位置が長手方向にディンプルピッチＤＰの半ピッチ分ずれて配置されている。   As shown in FIG. 3, when one tube 3 adjacent to the fin 4 is called a first tube 3a and the other tube 3 is called a second tube 3b, the first tube 3a and the second tube 3b are called the second tube 3b. The tube 3b has one flat surface of the first tube 3a (a flat surface on which the convex portion 7 is provided) and the other flat surface of the second tube (a flat surface on which the concave portion 8 is provided). The convex portion 7 provided in the first tube 3a and the concave portion 8 provided in the second tube 3b are arranged so as to face each other with the fin 4 interposed therebetween, and the positions of the convex portion 7 and the concave portion 8 provided in the second tube 3b are half the dimple pitch DP in the longitudinal direction. They are shifted by the pitch.

ここで、第１のチューブ３ａに接合されるフィン４の屈曲部４０を第１屈曲部４０ａ、第２のチューブ３ｂに接合されるフィン４の屈曲部４０を第２屈曲部４０ｂと呼ぶ時に、第１屈曲部４０ａは、第１のチューブ３ａの長手方向で隣り合う凸部７同士の間、つまり、凸部７と凸部７との間に形成される偏平面に接合され、第２屈曲部４０ｂは、第２のチューブ３ｂの長手方向で隣り合う凹部８同士の間、つまり、凹部８と凹部８との間に形成される偏平面に接合される。   Here, when the bent part 40 of the fin 4 joined to the first tube 3a is called a first bent part 40a, and the bent part 40 of the fin 4 joined to the second tube 3b is called a second bent part 40b, The first bent portion 40a is joined to the flat surface formed between the convex portions 7 adjacent in the longitudinal direction of the first tube 3a, that is, between the convex portion 7 and the convex portion 7. The portion 40b is joined to a flat surface formed between the concave portions 8 adjacent to each other in the longitudinal direction of the second tube 3b, that is, between the concave portion 8 and the concave portion 8.

（実施例１の作用および効果）
本実施例のヒータコア１は、第１のチューブ３ａの一方の偏平面と、第２のチューブ３ｂの他方の偏平面とがフィン４を挟んで対向して配置され、且つ、第１のチューブ３ａの一方の偏平面に設けられる凸部７と、第２のチューブ３ｂの他方の偏平面に設けられる凹部８とが、チューブ３の長手方向でディンプルピッチＤＰの半ピッチ分ずれて配置されている。
一方、波状に折り曲げ成形されるフィン４は、１／２・ＦＰ毎に屈曲部４０が設けられている。つまり、第１のチューブ３ａに接合される第１屈曲部４０ａと、第２のチューブ３ｂに接合される第２屈曲部４０ｂとが１／２・ＦＰ毎に交互に設けられる。なお、本実施例のヒータコア１は、ＦＰ＝ＤＰである。 (Operation and Effect of Example 1)
In the heater core 1 of the present embodiment, one flat surface of the first tube 3a and the other flat surface of the second tube 3b are arranged to face each other with the fin 4 interposed therebetween, and the first tube 3a. The convex portion 7 provided on one of the flat surfaces of the second tube 3 and the concave portion 8 provided on the other flat surface of the second tube 3 b are arranged so as to be shifted by a half pitch of the dimple pitch DP in the longitudinal direction of the tube 3. .
On the other hand, the fin 4 bent into a wave shape is provided with a bent portion 40 every 1/2 · FP. That is, the 1st bending part 40a joined to the 1st tube 3a and the 2nd bending part 40b joined to the 2nd tube 3b are alternately provided for every 1/2 * FP. In addition, the heater core 1 of a present Example is FP = DP.

よって、図３に示す様に、第１のチューブ３ａの長手方向で隣り合う凸部７同士の間、つまり、凸部７が設けられていない第１のチューブ３ａの一方の偏平面にフィン４の第１屈曲部４０ａを接合することで、必然的に、第２のチューブ３ｂの長手方向で隣り合う凹部８同士の間、つまり、凹部８が設けられていない第２のチューブ３ｂの他方の偏平面にフィン４の第２屈曲部４０ｂが接合される。
上記の構成によれば、第２のチューブ３ｂの他方の偏平面に凹部８を設けた構成であっても、その凹部８が設けられている部位にフィン４の第２屈曲部４０ｂが配置されることはなく、凹部８が設けられていない偏平面に第２屈曲部４０ｂを配置できるので、凹部８の数に関係なく、第２のチューブ３ｂの長径方向に対してフィン４の全幅に渡って第２屈曲部４０ｂを接合できる。これにより、チューブ３とフィン４とが接合できない箇所を無くすことができるので、特許文献１に開示された従来技術と比較して、フィン効率を高めることができ、ヒータコア１の性能向上を図ることができる。 Therefore, as shown in FIG. 3, the fins 4 are formed between the convex portions 7 adjacent to each other in the longitudinal direction of the first tube 3 a, that is, on one flat surface of the first tube 3 a where the convex portions 7 are not provided. By joining the first bent portions 40a, it is inevitably between the concave portions 8 adjacent in the longitudinal direction of the second tube 3b, that is, the other of the second tubes 3b in which the concave portions 8 are not provided. The second bent portion 40b of the fin 4 is joined to the uneven plane.
According to said structure, even if it is the structure which provided the recessed part 8 in the other eccentric plane of the 2nd tube 3b, the 2nd bending part 40b of the fin 4 is arrange | positioned in the site | part in which the recessed part 8 is provided. Since the second bent portion 40b can be disposed on the flat surface where the concave portion 8 is not provided, the entire width of the fin 4 is extended with respect to the major axis direction of the second tube 3b regardless of the number of the concave portions 8. Thus, the second bent portion 40b can be joined. Thereby, since the location where the tube 3 and the fin 4 cannot be joined can be eliminated, the fin efficiency can be increased and the performance of the heater core 1 can be improved as compared with the prior art disclosed in Patent Document 1. Can do.

（実施例２）
この実施例２に示すチューブ３は、図５（ａ）に示す様に、一方の偏平面に設けられる凸部７と、他方の偏平面に設けられる凹部８とが、チューブ３の長手方向にディンプルピッチＤＰの半ピッチ分だけ互いにずれた位置に配置されている。
上記の構成によれば、実施例１に記載した第１のチューブ３ａと第２のチューブ３ｂとを同一形状にできる。つまり、図５（ｂ）に示す様に、フィン４を挟んで第１のチューブ３ａの一方の偏平面と第２のチューブ３ｂの他方の偏平面とを対向して配置することにより、第１のチューブ３ａの一方の偏平面に設けられる凸部７と、第２のチューブ３ｂの他方の偏平面に設けられる凹部８とをチューブ３の長手方向に１／２・ＤＰ分ずらして配置することができ、実施例１と同様の効果を得ることが出来る。 (Example 2)
In the tube 3 shown in the second embodiment, as shown in FIG. 5A, the convex portion 7 provided on one of the flat surfaces and the concave portion 8 provided on the other flat surface are arranged in the longitudinal direction of the tube 3. They are arranged at positions shifted from each other by a half pitch of the dimple pitch DP.
According to said structure, the 1st tube 3a described in Example 1 and the 2nd tube 3b can be made into the same shape. That is, as shown in FIG. 5 (b), the first flat surface of the first tube 3a and the other flat surface of the second tube 3b are arranged opposite to each other with the fin 4 interposed therebetween. The convex portion 7 provided on one of the flat surfaces of the tube 3a and the concave portion 8 provided on the other flat surface of the second tube 3b are shifted by 1/2 · DP in the longitudinal direction of the tube 3. And the same effects as those of the first embodiment can be obtained.

（実施例３）
この実施例３は、第１のチューブ３ａと第２のチューブ３ｂとでヘッダタンク２の内部に挿入される挿入長さを変更した一例である。
使用されるチューブ３は、図６（ａ）に示す様に、一方の偏平面に設けられる凸部７と、他方の偏平面に設けられる凹部８とが長手方向に対して互いに同位置に配置される。
ここで、チューブ３の端部がヘッダタンク２の内部に挿入される長さを挿入代と定義した時に、図６（ｂ）に示す様に、一対のヘッダタンク２の内、一方のヘッダタンク２ａに対する第１のチューブ３ａの挿入代の方が第２のチューブ３ｂの挿入代より１／２・ＤＰ分だけ小さく、且つ、他方のヘッダタンク２ｂに対する第１のチューブ３ａの挿入代の方が第２のチューブ３ｂの挿入代より１／２・ＤＰ分だけ大きく設定されている。 (Example 3)
The third embodiment is an example in which the insertion length inserted into the header tank 2 is changed between the first tube 3a and the second tube 3b.
As shown in FIG. 6A, the tube 3 to be used has a convex portion 7 provided on one of the flat surfaces and a concave portion 8 provided on the other flat surface arranged at the same position with respect to the longitudinal direction. Is done.
Here, when the length at which the end of the tube 3 is inserted into the header tank 2 is defined as the insertion allowance, as shown in FIG. 6B, one header tank of the pair of header tanks 2 is shown. The insertion allowance of the first tube 3a relative to 2a is smaller by 1/2 · DP than the insertion allowance of the second tube 3b, and the insertion allowance of the first tube 3a relative to the other header tank 2b is greater. It is set larger by 1/2 · DP than the insertion allowance of the second tube 3b.

上記の構成では、一対のヘッダタンク２に対する第１のチューブ３ａと第２のチューブ３ｂの挿入代を１／２・ＤＰ分ずらすことにより、第１のチューブ３ａの一方の偏平面に設けられる凸部７と、第２のチューブ３ｂの他方の偏平面に設けられる凹部８とを、チューブ３の長手方向に１／２・ＤＰ分ずらして配置することができる。これにより、第１のチューブ３ａと第２のチューブ３ｂの形状を変更することなく、両者に共通する１種類のチューブ３を用いて実施例１と同様の効果を得ることができる。   In the above configuration, the protrusion provided on one of the flat surfaces of the first tube 3a by shifting the insertion allowance of the first tube 3a and the second tube 3b to the pair of header tanks 2 by 1/2 · DP. The portion 7 and the concave portion 8 provided on the other flat surface of the second tube 3b can be arranged shifted by 1/2 · DP in the longitudinal direction of the tube 3. Thereby, the effect similar to Example 1 can be acquired using one type of tube 3 common to both, without changing the shape of the 1st tube 3a and the 2nd tube 3b.

（実施例４）
この実施例４は、第１のチューブ３ａと第２のチューブ３ｂとを長手方向に反転して配置した一例である。
第１のチューブ３ａと第２のチューブ３ｂには、同一形状を有する１種類のチューブ３が使用される。このチューブ３は、図７（ａ）に示す様に、一方の偏平面に設けられる凸部７と、他方の偏平面に設けられる凹部８とが、長手方向に対して互いに同位置に配置され、且つ、長手方向の一端（図示左端）から最も近い凸部７および凹部８までの距離Ａより、長手方向の他端（図示右端）から最も近い凸部７および凹部８までの距離Ｂの方が１／２・ＤＰ分だけ大きく設定されている。 Example 4
The fourth embodiment is an example in which the first tube 3a and the second tube 3b are disposed so as to be reversed in the longitudinal direction.
One type of tube 3 having the same shape is used for the first tube 3a and the second tube 3b. In this tube 3, as shown in FIG. 7A, the convex portion 7 provided on one of the flat surfaces and the concave portion 8 provided on the other flat surface are arranged at the same position in the longitudinal direction. And, the distance B from the other end (right end in the figure) to the nearest convex part 7 and the recess 8 from the distance A from one end (the left end in the figure) to the nearest convex part 7 and the recess 8 Is set larger by 1/2 · DP.

第１のチューブ３ａと第２のチューブ３ｂは、図７（ｂ）に示す様に、チューブ３の一端と他端とを長手方向に反転した状態で使用される。つまり、第１のチューブ３ａの一端と第２のチューブ３ｂの他端、および、第１のチューブ３ａの他端と第２のチューブ３ｂの一端をそれぞれ同一方向に向けて配置することにより、第１のチューブ３ａの一方の偏平面に設けられる凸部７と、第２のチューブ３ｂの他方の偏平面に設けられる凹部８とを、チューブ３の長手方向に１／２・ＤＰ分ずらして配置することができる。これにより、第１のチューブ３ａと第２のチューブ３ｂの形状を変更することなく、両者に共通する１種類のチューブ３を用いて実施例１と同様の効果を得ることができる。   As shown in FIG. 7B, the first tube 3a and the second tube 3b are used in a state where one end and the other end of the tube 3 are inverted in the longitudinal direction. That is, by arranging the one end of the first tube 3a and the other end of the second tube 3b and the other end of the first tube 3a and one end of the second tube 3b in the same direction, The convex portion 7 provided on one of the flat surfaces of one tube 3a and the concave portion 8 provided on the other flat surface of the second tube 3b are shifted by 1/2 · DP in the longitudinal direction of the tube 3 can do. Thereby, the effect similar to Example 1 can be acquired using one type of tube 3 common to both, without changing the shape of the 1st tube 3a and the 2nd tube 3b.

（実施例５）
実施例１に記載したフィン４は、図２に示す様に、屈曲部４０が円弧状に湾曲した形状であるが、この実施例５に示すフィン４は、図８に示す様に、屈曲部４０に平坦面を残した状態で折り曲げられている。
この実施例５に示すフィン形状によれば、実施例１と同様の効果を得られる上に、チューブ３との接合面積をより多く確保できるため、伝熱性能が向上すると共に、チューブ３とフィン４との接合強度を向上できる。 (Example 5)
The fin 4 described in the first embodiment has a shape in which the bent portion 40 is curved in an arc shape as shown in FIG. 2, but the fin 4 shown in the fifth embodiment has a bent portion as shown in FIG. 40 is bent with a flat surface left.
According to the fin shape shown in the fifth embodiment, the same effect as that of the first embodiment can be obtained, and a larger joint area with the tube 3 can be secured, so that the heat transfer performance is improved and the tube 3 and the fin are also secured. 4 can be improved.

（変形例）
実施例１では、本発明の熱交換器を暖房用のヒータコア１に適用した一例を説明したが、ヒータコア１以外の熱交換器、例えば、冷凍サイクルに使用される冷媒凝縮器、冷媒蒸発器、エンジン冷却システムに用いられるラジエータ、エンジンやギヤボックスなどの潤滑油を冷却するオイルクーラー、過給機で圧縮された空気を冷却するインタークーラ、排気の一部を吸気に戻すＥＧＲ装置に使用されるＥＧＲクーラ等にも適用できる。 (Modification)
In Example 1, although the example which applied the heat exchanger of this invention to the heater core 1 for heating was demonstrated, heat exchangers other than the heater core 1, for example, the refrigerant | coolant condenser used for a refrigerating cycle, a refrigerant | coolant evaporator, Used in radiators used in engine cooling systems, oil coolers that cool lubricating oil such as engines and gear boxes, intercoolers that cool air compressed by a turbocharger, and EGR devices that return part of the exhaust air to the intake air It can also be applied to an EGR cooler or the like.

１ ヒータコア（熱交換器）
２ ヘッダタンク
３ チューブ
３ａ 第１のチューブ
３ｂ 第２のチューブ
４ フィン
７ チューブの一方の偏平面に設けられた凸部
８ チューブの他方の偏平面に設けられた凹部
４０ フィンの屈曲部
４１ フィン平面部
４２ ルーバ
ＤＰ ディンプルピッチ
ＦＰ フィンピッチ 1 Heater core (heat exchanger)
2 header tank 3 tube 3a first tube 3b second tube 4 fin 7 convex portion provided on one eccentric plane of the tube 8 concave portion provided on the other eccentric plane of the tube 40 bent portion of the fin 41 fin plane Part 42 Louver DP Dimple pitch FP Fin pitch

Claims (3)

所定の間隔を空けて並列に配置される複数本のチューブと、
隣り合う前記チューブ同士の間に配置されて前記チューブの表面に接合されるフィンと、
前記チューブの長手方向の両端部が挿入される一対のヘッダタンクとを有し、
前記チューブの内部を流れる流体と前記チューブの外側を流れる流体との間で熱交換を行う熱交換器において、
前記フィンは、一定のフィンピッチを有して波状に折り曲げ成形されたコルゲートフィンであり、
前記チューブは、前記長手方向と直交する断面形状が長径と短径とを有する偏平管形状に形成され、且つ、短径方向に対向する一方の偏平面に前記チューブの外側へ向かって突出する凸部が設けられ、他方の偏平面に前記チューブの内側に向かって窪む凹部が設けられて、前記凸部および前記凹部が前記長手方向に前記フィンピッチと同ピッチで複数段に配置され、
前記フィンを挟んで隣り合う一方の前記チューブを第１のチューブ、他方の前記チューブを第２のチューブと呼び、前記チューブの長手方向に隣り合う前記凸部同士および前記凹部同士の間隔をディンプルピッチと呼ぶ時に、
前記第１のチューブと前記第２のチューブは、前記第１のチューブの一方の偏平面と前記第２のチューブの他方の偏平面とが前記フィンを挟んで対向して配置され、且つ、前記第１のチューブに設けられる前記凸部と前記第２のチューブに設けられる前記凹部は、前記チューブの長手方向に対する互いの位置が前記ディンプルピッチの半ピッチ分ずれて配置され、
さらに、前記チューブは、前記一方の偏平面に設けられる前記凸部と、前記他方の偏平面に設けられる前記凹部とが前記長手方向に対して互いに同位置に配置されており、
前記チューブの端部が前記ヘッダタンクの内部に挿入される長さを挿入代と定義した時に、一対の前記ヘッダタンクの内、一方の前記ヘッダタンクに対する前記第１のチューブの挿入代の方が前記第２のチューブの挿入代より前記ディンプルピッチの半ピッチ分だけ小さく、且つ、他方の前記ヘッダタンクに対する前記第１のチューブの挿入代の方が前記第２のチューブの挿入代より前記ディンプルピッチの半ピッチ分だけ大きく設定されていることを特徴とする熱交換器。 A plurality of tubes arranged in parallel at a predetermined interval;
A fin disposed between adjacent tubes and joined to the surface of the tube;
A pair of header tanks into which both longitudinal ends of the tube are inserted;
In a heat exchanger that performs heat exchange between a fluid flowing inside the tube and a fluid flowing outside the tube,
The fins are corrugated fins that are bent into a wave shape with a constant fin pitch,
The tube is formed in a flat tube shape in which a cross-sectional shape perpendicular to the longitudinal direction has a major axis and a minor axis, and a convex projecting toward the outside of the tube on one of the flat surfaces opposed to the minor axis direction. Is provided with a concave portion that is recessed toward the inside of the tube, and the convex portion and the concave portion are arranged in a plurality of stages at the same pitch as the fin pitch in the longitudinal direction,
One tube adjacent to the fin is referred to as a first tube, and the other tube is referred to as a second tube. The distance between the convex portions and the concave portions adjacent to each other in the longitudinal direction of the tube is a dimple pitch. When calling
The first tube and the second tube are arranged so that one flat surface of the first tube and the other flat surface of the second tube face each other with the fin interposed therebetween, and The convex portion provided in the first tube and the concave portion provided in the second tube are arranged such that their positions relative to the longitudinal direction of the tube are shifted by a half pitch of the dimple pitch ,
Furthermore, the said tube is arrange | positioned in the mutually same position with respect to the said longitudinal direction, the said convex part provided in said one eccentric plane, and the said recessed part provided in said other eccentric plane,
When the length at which the end of the tube is inserted into the header tank is defined as an insertion allowance, the insertion allowance of the first tube with respect to one of the header tanks of the pair of header tanks is greater. The insertion amount of the first tube with respect to the other header tank is smaller than the insertion amount of the second tube than the insertion amount of the second tube. The heat exchanger is characterized in that it is set larger by the half pitch . 所定の間隔を空けて並列に配置される複数本のチューブと、
隣り合う前記チューブ同士の間に配置されて前記チューブの表面に接合されるフィンと、
前記チューブの長手方向の両端部が挿入される一対のヘッダタンクとを有し、
前記チューブの内部を流れる流体と前記チューブの外側を流れる流体との間で熱交換を行う熱交換器において、
前記フィンは、一定のフィンピッチを有して波状に折り曲げ成形されたコルゲートフィンであり、
前記チューブは、前記長手方向と直交する断面形状が長径と短径とを有する偏平管形状に形成され、且つ、短径方向に対向する一方の偏平面に前記チューブの外側へ向かって突出する凸部が設けられ、他方の偏平面に前記チューブの内側に向かって窪む凹部が設けられて、前記凸部および前記凹部が前記長手方向に前記フィンピッチと同ピッチで複数段に配置され、
前記フィンを挟んで隣り合う一方の前記チューブを第１のチューブ、他方の前記チューブを第２のチューブと呼び、前記チューブの長手方向に隣り合う前記凸部同士および前記凹部同士の間隔をディンプルピッチと呼ぶ時に、
前記第１のチューブと前記第２のチューブは、前記第１のチューブの一方の偏平面と前記第２のチューブの他方の偏平面とが前記フィンを挟んで対向して配置され、且つ、前記第１のチューブに設けられる前記凸部と前記第２のチューブに設けられる前記凹部は、前記チューブの長手方向に対する互いの位置が前記ディンプルピッチの半ピッチ分ずれて配置され、
さらに、前記チューブは、前記一方の偏平面に設けられる前記凸部と、前記他方の偏平面に設けられる前記凹部とが、前記長手方向に対して互いに同位置に配置され、且つ、前記長手方向の一端から最も近い前記凸部および前記凹部までの距離より、前記長手方向の他端から最も近い前記凸部および前記凹部までの距離の方が前記ディンプルピッチの半ピッチ分だけ大きく設定され、
前記第１のチューブと前記第２のチューブは、互いの一端と他端とが前記長手方向に反転した状態で配置されていることを特徴とする熱交換器。 A plurality of tubes arranged in parallel at a predetermined interval;
A fin disposed between adjacent tubes and joined to the surface of the tube;
A pair of header tanks into which both longitudinal ends of the tube are inserted;
In a heat exchanger that performs heat exchange between a fluid flowing inside the tube and a fluid flowing outside the tube,
The fins are corrugated fins that are bent into a wave shape with a constant fin pitch,
The tube is formed in a flat tube shape in which a cross-sectional shape perpendicular to the longitudinal direction has a major axis and a minor axis, and a convex projecting toward the outside of the tube on one of the flat surfaces opposed to the minor axis direction. Is provided with a concave portion that is recessed toward the inside of the tube, and the convex portion and the concave portion are arranged in a plurality of stages at the same pitch as the fin pitch in the longitudinal direction,
One tube adjacent to the fin is referred to as a first tube, and the other tube is referred to as a second tube. The distance between the convex portions and the concave portions adjacent to each other in the longitudinal direction of the tube is a dimple pitch. When calling
The first tube and the second tube are arranged so that one flat surface of the first tube and the other flat surface of the second tube face each other with the fin interposed therebetween, and The convex portion provided in the first tube and the concave portion provided in the second tube are arranged such that their positions relative to the longitudinal direction of the tube are shifted by a half pitch of the dimple pitch,
Further, in the tube, the convex portion provided on the one flat surface and the concave portion provided on the other flat surface are arranged at the same position with respect to the longitudinal direction, and the longitudinal direction The distance from the other end in the longitudinal direction to the nearest convex portion and the concave portion is set to be larger by a half pitch of the dimple pitch than the distance from the one end to the nearest convex portion and the concave portion,
The heat exchanger according to claim 1, wherein the first tube and the second tube are arranged in a state in which one end and the other end are inverted in the longitudinal direction . 請求項１または請求項２に記載した熱交換器において、
前記フィンは、前記第１のチューブと前記第２のチューブとの間で交互に連続して折れ曲がる屈曲部と、連続する二つの前記屈曲部同士の間に形成されるフィン平面部とを有し、このフィン平面部にルーバが形成されていることを特徴とする熱交換器。 The heat exchanger according to claim 1 or 2 ,
The fin includes a bent portion that is alternately and continuously bent between the first tube and the second tube, and a fin plane portion that is formed between the two continuous bent portions. A heat exchanger characterized in that a louver is formed on the fin plane portion .
JP2012003903A 2012-01-12 2012-01-12 Heat exchanger Expired - Fee Related JP5772608B2 (en)

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