JP2010032128A - Tube for heat exchanger - Google Patents

Tube for heat exchanger Download PDF

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JP2010032128A
JP2010032128A JP2008194959A JP2008194959A JP2010032128A JP 2010032128 A JP2010032128 A JP 2010032128A JP 2008194959 A JP2008194959 A JP 2008194959A JP 2008194959 A JP2008194959 A JP 2008194959A JP 2010032128 A JP2010032128 A JP 2010032128A
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semi
cylindrical member
tube
width direction
heat exchanger
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JP5187047B2 (en
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Hiroyasu Shimanuki
宏泰 嶋貫
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Denso Corp
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Denso Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a tube for a heat exchanger easily adaptable to the heat exchanger using a conventional extrusion tube while preventing damage caused by a collision with pebbles. <P>SOLUTION: A cross sectional shape viewed from the longitudinal direction of both end faces 2a in the width direction is formed to have an arcuate shape with a predetermined curvature radius, and a board thickness X in the width direction of long diameter side ends 2b is set to be 0.6 mm or larger. First and second half-cylindrical parts 21A, 21B formed to have half-cylindrical shapes are combined. One of a recessed part 23b and a projecting part 23c corresponding to each other is formed at a bent part 23 of the first half-cylindrical part 21A, and the other of the recessed part 23b and the projecting part 23c corresponding to each other is provided at a bent part 23 of the second half-cylindrical part 21B. With the projecting part 23c fitted to the recessed part 23b, the first and second half-cylindrical parts 21A, 21B are jointed. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、熱交換のための流体が内部を流れる熱交換器用チューブに関し、冷凍サイクルの凝縮器に用いて好適である。   The present invention relates to a heat exchanger tube in which a fluid for heat exchange flows, and is suitable for use in a condenser of a refrigeration cycle.

従来、一枚の薄板を曲げ成形することで、チューブの外殻を構成するアウターチューブとインナーフィンとを形成した熱交換器用チューブが知られている（例えば、特許文献１参照）。このようなチューブでは、チューブの側面が一枚の薄板から構成されるので、チューブ側面の肉厚はチューブを構成する薄板の板厚と等しくなる。このため、チューブ側面に小石等が衝突した際に、チューブが破損する虞がある。   2. Description of the Related Art Conventionally, a heat exchanger tube in which an outer tube and an inner fin constituting an outer shell of a tube are formed by bending a thin sheet is known (see, for example, Patent Document 1). In such a tube, since the side surface of the tube is composed of a single thin plate, the thickness of the side surface of the tube is equal to the thickness of the thin plate constituting the tube. For this reason, when a pebble etc. collide with the tube side surface, there exists a possibility that a tube may be damaged.

これに対し、チューブ側面を、薄板を複雑に曲げることにより形成することで、外部流体流れ方向における一方の端部の板厚を増加させたものが知られている（例えば、特許文献２参照）。しかしながら、構造が複雑になるとともに、一方の端部を必ず外部流体流れ上流側に配置する必要があるため、製造性が悪化するという問題がある。   On the other hand, the tube side surface is formed by bending a thin plate in a complicated manner to increase the thickness of one end in the direction of external fluid flow (see, for example, Patent Document 2). . However, the structure is complicated, and one end portion must be disposed on the upstream side of the external fluid flow.

この問題に対して、２枚の板状部材、すなわち蓋部と本体部とをカシメることにより形成される熱交換器用チューブが提案されている（例えば、特許文献３参照）。
米国特許第５４４１１０６号明細書 特開２００５−１０６３８９号公報 米国特許第６２４７５２９号明細書 In order to solve this problem, a heat exchanger tube formed by crimping two plate-like members, that is, a lid portion and a main body portion has been proposed (for example, see Patent Document 3).
US Pat. No. 5,441,106 JP 2005-106389 A US Pat. No. 6,247,529

しかしながら、上記特許文献３に記載のチューブの外形は、チューブ端部が滑らかなＲ形状にならず、角部ができてしまう。チューブ端部に角部を有する場合、ヘッダタンクにおけるチューブ挿入穴の外形も角部を有する穴を開ける必要があるため、刃具摩耗が増大するとともに、チューブ挿入穴を専用設計しなければならない。   However, the outer shape of the tube described in Patent Document 3 does not have a smooth R shape at the end of the tube, and corners are formed. When the tube end portion has a corner portion, the outer shape of the tube insertion hole in the header tank needs to be formed with a corner portion, so that the wear of the cutting tool is increased and the tube insertion hole must be designed exclusively.

また、従来の熱交換器には、押出成形で形成された押出チューブが適用されている。しかしながら、押出チューブはチューブ端部にＲ形状を有しているので、チューブ端部が角部を有する上記特許文献３に記載のチューブを、従来の押出チューブが用いられている熱交換器に容易に適用することができないという問題がある。   Moreover, the extrusion tube formed by extrusion molding is applied to the conventional heat exchanger. However, since the extruded tube has an R shape at the tube end, the tube described in Patent Document 3 in which the tube end has a corner is easily used as a heat exchanger in which a conventional extruded tube is used. There is a problem that can not be applied to.

本発明は、上記点に鑑み、小石の衝突により破損することを防止しつつ、従来の押出チューブが用いられている熱交換器に対して容易に適用することができる熱交換器用チューブを提供することを目的とする。   In view of the above points, the present invention provides a heat exchanger tube that can be easily applied to a heat exchanger in which a conventional extruded tube is used while preventing breakage due to the collision of pebbles. For the purpose.

上記目的を達成するため、請求項１に記載の発明では、幅方向における両端面（２ａ）の長手方向から見た断面形状は、所定の曲率半径を有する円弧状になっており、幅方向における端部（２ｂ）の幅方向の板厚（Ｘ）は、０．６ｍｍ以上になっており、半筒状に形成された第１半筒状部材（２１Ａ）および第２半筒状部材（２１Ｂ）を組み合わせることにより形成されており、第１半筒状部材（２１Ａ）および第２半筒状部材（２１Ｂ）は、幅方向に延びる平板部（２２）を有しているとともに、平板部（２２）における幅方向の両端部は、円弧状に湾曲した湾曲部（２３）になっており、第１半筒状部材（２１Ａ）の湾曲部（２３）には、互いに対応する凹部（２３ｂ）および凸部（２３ｃ）のうち一方が設けられており、第２半筒状部材（２１Ｂ）の湾曲部（２３）には、互いに対応する凹部（２３ｂ）および凸部（２３ｃ）のうち他方が設けられており、凹部（２３ｂ）に凸部（２３ｃ）が嵌合された状態で、第１半筒状部材（２１Ａ）および第２半筒状部材（２１Ｂ）が接合されていることを特徴としている。   In order to achieve the above object, in the invention described in claim 1, the cross-sectional shape viewed from the longitudinal direction of both end faces (2a) in the width direction is an arc having a predetermined radius of curvature, The plate thickness (X) in the width direction of the end portion (2b) is 0.6 mm or more, and the first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) formed in a semi-cylindrical shape. ), And the first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) have a flat plate portion (22) extending in the width direction and a flat plate portion ( 22), both end portions in the width direction are curved portions (23) curved in an arc shape, and the concave portions (23b) corresponding to each other are formed in the curved portion (23) of the first semi-cylindrical member (21A). And one of the convex portions (23c) is provided, and the second semi-cylindrical portion The curved portion (23) of (21B) is provided with the other of the corresponding concave portion (23b) and convex portion (23c), and the convex portion (23c) is fitted in the concave portion (23b). Thus, the first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) are joined.

このように、熱交換器用チューブ（２）の幅方向における端部（２ｂ）の幅方向の板厚（Ｘ）を０．６ｍｍ以上とすることで、後述する第１実施形態、特に図３に示すように、小石の衝突により熱交換器用チューブ（２）が破損することを防止できる。   As described above, the thickness (X) in the width direction of the end portion (2b) in the width direction of the heat exchanger tube (2) is set to 0.6 mm or more, so that the first embodiment described later, particularly in FIG. As shown, the heat exchanger tube (2) can be prevented from being damaged by the impact of pebbles.

また、熱交換器用チューブ（２）の両端面（２ａ）の長手方向から見た断面形状を円弧状とすることで、従来の押出チューブが用いられている熱交換器に対し、本発明の熱交換器用チューブ（２）を容易に適用することが可能となる。   Moreover, the cross-sectional shape seen from the longitudinal direction of both end surfaces (2a) of the heat exchanger tube (2) is an arc shape, so that the heat of the present invention can be applied to a heat exchanger in which a conventional extruded tube is used. The exchanger tube (2) can be easily applied.

また、凹部（２３ｂ）と凸部（２３ｃ）とが嵌合された状態で、第１半筒状部材（２１Ａ）と第２半筒状部材（２１Ｂ）とを接合するように構成することで、第１半筒状部材（２１Ａ）と第２半筒状部材（２１Ｂ）とが接合されている部分の長さを十分に確保することができる。これにより、熱交換器用チューブ（２）の耐食性を向上させることが可能となる。   Further, the first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) are joined to each other in a state where the concave portion (23b) and the convex portion (23c) are fitted. The length of the portion where the first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) are joined can be sufficiently secured. Thereby, it becomes possible to improve the corrosion resistance of the heat exchanger tube (2).

また、請求項２に記載の発明のように、所定の曲率半径は、長手方向および幅方向に直交する高さ方向の長さ（Ｈ）の約半分の大きさに設定されていてもよい。   Further, as in the second aspect of the invention, the predetermined radius of curvature may be set to a size that is about half of the length (H) in the height direction orthogonal to the longitudinal direction and the width direction.

また、請求項３に記載の発明では、第１半筒状部材（２１Ａ）と第２半筒状部材（２１Ｂ）との間には、熱媒体との伝熱面積を増大させるインナーフィン（２００）が設けられており、インナーフィン（２００）は、熱媒体の流れ方向と略平行な平面部（２０１）と、隣接する平面部（２０１）間を繋ぐ頂部（２０２）とを有するように波形状に形成されており、頂部（２０２）は、平板部（２２）における熱媒体が接触する側の面と接触しており、平板部（２２）におけるチューブ内方側の面には、頂部（２０２）に対応する形状の窪み部（２４）が形成されており、窪み部（２４）には、頂部（２０２）が入り込むようになっていることを特徴としている。   In the invention according to claim 3, the inner fin (200) that increases the heat transfer area with the heat medium between the first semi-cylindrical member (21A) and the second semi-cylindrical member (21B). ), And the inner fin (200) has a wave portion so as to have a flat portion (201) substantially parallel to the flow direction of the heat medium and a top portion (202) connecting the adjacent flat portions (201). The top part (202) is in contact with the surface of the flat plate part (22) on the side where the heat medium contacts, and the flat part (22) has a top part (22) on the inner surface of the tube. 202), a depression (24) having a shape corresponding to the shape of the depression (24) is formed, and the top (202) enters the depression (24).

このように、第１、第２半筒状部材（２１Ａ、２１Ｂ）の平板部（２２）におけるチューブ内方側の面に窪み部（２４）を形成するとともに、この窪み部（２４）にインナーフィン（２００）の頂部（２０２）が入り込むようすることで、インナーフィン（２００）を設けることにより熱交換器用チューブ（２）内の通路断面積が減少することを抑制することができ、さらにはインナーフィン（２００）の接合性を向上させることができる。   As described above, the hollow portion (24) is formed on the inner surface of the tube in the flat plate portion (22) of the first and second semi-cylindrical members (21A, 21B), and the inner portion is formed in the hollow portion (24). By allowing the top portion (202) of the fin (200) to enter, it is possible to suppress the passage cross-sectional area in the heat exchanger tube (2) from being reduced by providing the inner fin (200). Bondability of the inner fin (200) can be improved.

また、請求項４に記載の発明では、平板部（２２）には、チューブ内方側に突出する突起部（２５）が複数設けられており、突起部（２５）は、隣接する頂部（２０２）間に配置されていることを特徴としている。これによれば、インナーフィン（２００）が熱交換器用チューブ（２）の幅方向にずれることを防止できる。   In the invention according to claim 4, the flat plate portion (22) is provided with a plurality of protrusions (25) protruding toward the inner side of the tube, and the protrusions (25) are adjacent top portions (202). ) Between the two. According to this, it is possible to prevent the inner fin (200) from shifting in the width direction of the heat exchanger tube (2).

また、請求項５に記載の発明では、第１半筒状部材（２１Ａ）と第２半筒状部材（２１Ｂ）とは、互いに同形状に形成されており、第１半筒状部材（２１Ａ）および第２半筒状部材（２１Ｂ）における幅方向の一方の端部側の湾曲部（２３）には、凹部（２３ｂ）がそれぞれ設けられており、第１半筒状部材（２１Ａ）および第２半筒状部材（２１Ｂ）における幅方向の他方の端部側の湾曲部（２３）には、凹部（２３ｂ）に対応する凸部（２３ｃ）がそれぞれ設けられており、第１半筒状部材（２１Ａ）の凹部（２３ｂ）に第２半筒状部材（２１Ｂ）の凸部（２３ｃ）が嵌合されるとともに、第２半筒状部材（２１Ｂ）の凹部（２３ｂ）に第１半筒状部材（２１Ａ）の凸部（２３ｃ）が嵌合された状態で、第１半筒状部材（２１Ａ）および第２半筒状部材（２１Ｂ）が接合されることにより形成されていることを特徴としている。   In the invention according to claim 5, the first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) are formed in the same shape, and the first semi-cylindrical member (21A). ) And the curved portion (23) on one end side in the width direction of the second semi-cylindrical member (21B) are provided with recesses (23b), respectively, and the first semi-cylindrical member (21A) and The curved portion (23) on the other end side in the width direction of the second semi-cylindrical member (21B) is provided with a convex portion (23c) corresponding to the concave portion (23b). The convex portion (23c) of the second semi-cylindrical member (21B) is fitted into the concave portion (23b) of the cylindrical member (21A), and the first concave portion (23b) of the second semi-cylindrical member (21B) is fitted. In a state in which the convex portion (23c) of the semi-cylindrical member (21A) is fitted, the first semi-cylindrical member (21A) and 2 semi-cylindrical member (21B) is characterized by being formed by being joined.

このように、第１、第２筒状部材（２１Ａ、２１Ｂ）を同形状に形成することで、１種類のプレス型のみで２つの半筒状部材（２１Ａ、２１Ｂ）を製造することができるので、熱交換器用チューブ（２）の生産性を向上させることができる。   Thus, by forming the first and second cylindrical members (21A, 21B) in the same shape, two half-cylindrical members (21A, 21B) can be manufactured with only one type of press die. Therefore, the productivity of the heat exchanger tube (2) can be improved.

なお、この欄および特許請求の範囲で記載した各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示すものである。   In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

以下、本発明の実施形態について図に基づいて説明する。なお、以下の各実施形態相互において、互いに同一もしくは均等である部分には、図中、同一符号を付してある。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

（第１実施形態）
本発明の第１実施形態について図１〜図６に基づいて説明する。本実施形態は、本発明を凝縮器のチューブに適用した例である。図１に、本第１実施形態における熱交換器１の全体構造を示す。 (First embodiment)
1st Embodiment of this invention is described based on FIGS. The present embodiment is an example in which the present invention is applied to a condenser tube. In FIG. 1, the whole structure of the heat exchanger 1 in this 1st Embodiment is shown.

本実施形態の熱交換器１は、図示しない冷凍サイクルの圧縮機から吐出された高温高圧の冷媒と空気とを熱交換させて冷媒を凝縮させる凝縮器である。本実施形態では、冷媒が熱媒体に相当している。   The heat exchanger 1 of the present embodiment is a condenser that condenses the refrigerant by exchanging heat between the high-temperature and high-pressure refrigerant discharged from the compressor of the refrigeration cycle (not shown) and air. In the present embodiment, the refrigerant corresponds to the heat medium.

具体的には、熱交換器１は、複数のチューブ２およびフィン３からなる１つのコア部４と、コア部４の左右両端部に組み付け配置される一対のヘッダタンク５とを有している。   Specifically, the heat exchanger 1 has a single core portion 4 composed of a plurality of tubes 2 and fins 3 and a pair of header tanks 5 that are assembled and arranged at both left and right ends of the core portion 4. .

チューブ２は冷媒が流れる管であり、このチューブ２は、空気流れ方向（図１の紙面垂直方向）が長径方向と一致するように扁平状に形成されているとともに、その長手方向が水平方向に一致するように鉛直方向に複数本平行に配置されている。フィン３は、波状に成形されるとともに、チューブ２の両側の扁平面に接合されており、このフィン３により空気との伝熱面積を増大させて冷媒と空気との熱交換を促進している。   The tube 2 is a tube through which the refrigerant flows. The tube 2 is formed in a flat shape so that the air flow direction (the direction perpendicular to the paper surface in FIG. 1) coincides with the major axis direction, and the longitudinal direction thereof is in the horizontal direction. A plurality of them are arranged in parallel in the vertical direction so as to match. The fins 3 are formed in a wave shape and are joined to flat surfaces on both sides of the tube 2. The fins 3 increase the heat transfer area with the air and promote heat exchange between the refrigerant and the air. .

ヘッダタンク５は、チューブ２の長手方向（以下、チューブ長手方向という）の両端部にてチューブ長手方向と直交する方向に延びて複数のチューブ２と連通するものである。ヘッダタンク５は、チューブ２が挿入接合されるコアプレート５ａと、コアプレート５ａとともにタンク内空間を構成するタンク本体部５ｂとを有して構成されている。なお、一対のヘッダタンク５のうち、図１中右側に位置するヘッダタンクを第１ヘッダタンク５１といい、図１中左側に位置するヘッダタンクを第２ヘッダタンク５２という。   The header tank 5 extends in a direction orthogonal to the tube longitudinal direction at both ends of the tube 2 in the longitudinal direction (hereinafter referred to as tube longitudinal direction) and communicates with the plurality of tubes 2. The header tank 5 includes a core plate 5a into which the tube 2 is inserted and joined, and a tank main body 5b that constitutes a tank internal space together with the core plate 5a. Of the pair of header tanks 5, the header tank located on the right side in FIG. 1 is called a first header tank 51, and the header tank located on the left side in FIG. 1 is called a second header tank 52.

コア部４には、コア部４を補強するサイドプレート６が設けられている。サイドプレート６は、チューブ長手方向と平行に延びてその両端部がヘッダタンク５に接続されている。   The core part 4 is provided with a side plate 6 that reinforces the core part 4. The side plate 6 extends in parallel with the tube longitudinal direction, and both end portions thereof are connected to the header tank 5.

第２ヘッダタンク５２には、冷媒を熱交換器１の内部に流入させる冷媒入口部７１と、冷媒を熱交換器１の外部へ流出させる冷媒出口部７２とが設けられている。冷媒入口部７１と冷媒出口部７２とは、それぞれ第２ヘッダタンク５２の上端側と下端側とに設けられている。   The second header tank 52 is provided with a refrigerant inlet portion 71 that allows the refrigerant to flow into the heat exchanger 1 and a refrigerant outlet portion 72 that allows the refrigerant to flow out of the heat exchanger 1. The refrigerant inlet portion 71 and the refrigerant outlet portion 72 are provided on the upper end side and the lower end side of the second header tank 52, respectively.

第２ヘッダタンク５２の内部の下側寄りの位置には、第１セパレータ８１が配置されている。また、第１ヘッダタンク５１の内部には、第１セパレータ８１と同一高さに第２セパレータ８２が配置されている。この第１、第２セパレータ８１、８２によってコア部４は２つの熱交換部に分けられている。   A first separator 81 is disposed at a lower position inside the second header tank 52. A second separator 82 is disposed at the same height as the first separator 81 inside the first header tank 51. The core part 4 is divided into two heat exchange parts by the first and second separators 81 and 82.

コア部４における第１、第２セパレータ８１、８２の上方側部位は、冷媒入口部７１から流入した気相冷媒と空気とを熱交換させて、冷媒を凝縮させる凝縮部４１になっており、凝縮部４１から流出した冷媒は、後述するモジュレータ９に流入するようになっている。   The upper part of the first and second separators 81 and 82 in the core part 4 is a condensing part 41 that heat-exchanges the gas-phase refrigerant and air flowing from the refrigerant inlet part 71 and condenses the refrigerant, The refrigerant that has flowed out of the condensing unit 41 flows into the modulator 9 described later.

また、コア部４における第１、第２セパレータ８１、８２の下方側部位は、モジュレータ９から流入した液相冷媒と空気とを熱交換させて液相冷媒を冷却する過冷却部４２になっており、過冷却部４２で冷却された冷媒は冷媒出口部７２から流出するようになっている。   Further, the lower part of the first and second separators 81 and 82 in the core part 4 is a supercooling part 42 that cools the liquid phase refrigerant by exchanging heat between the liquid phase refrigerant that flows in from the modulator 9 and the air. The refrigerant cooled by the supercooling section 42 flows out from the refrigerant outlet section 72.

第１ヘッダタンク５１の外側、すなわちコア部４と反対側には、鉛直方向に延びる略円筒形状のモジュレータ９が配置されている。モジュレータ９は、気相冷媒と液相冷媒を分離して液相冷媒を溜めるものである。また、モジュレータ９は、第１ヘッダタンク５１にろう付けにて接合されている。   A substantially cylindrical modulator 9 extending in the vertical direction is disposed outside the first header tank 51, that is, on the side opposite to the core portion 4. The modulator 9 separates the gas-phase refrigerant and the liquid-phase refrigerant and stores the liquid-phase refrigerant. The modulator 9 is joined to the first header tank 51 by brazing.

モジュレータ９と第１ヘッダタンク５１とは、冷媒流入口９１および冷媒流出口９２を介して２カ所で連通している。詳細には、冷媒流入口９１は、第１ヘッダタンク５１における第２セパレータ８２より上方側の部位とモジュレータ９の内部とを連通させるようになっている。また、冷媒流出口９２は、第１ヘッダタンク５１における第２セパレータ８２より下方側の部位とモジュレータ９の内部とを連通させるようになっている。すなわち、冷媒流入口９１は、冷媒流出口９２より上方側に配置されている。   The modulator 9 and the first header tank 51 communicate with each other at two locations via a refrigerant inlet 91 and a refrigerant outlet 92. Specifically, the refrigerant inflow port 91 communicates a portion of the first header tank 51 above the second separator 82 with the inside of the modulator 9. In addition, the refrigerant outlet 92 communicates a portion of the first header tank 51 below the second separator 82 with the inside of the modulator 9. That is, the refrigerant inlet 91 is disposed above the refrigerant outlet 92.

モジュレータ９は、凝縮部４１から流出した冷媒を気液分離する内部空間９３を有している。内部空間９３は、冷媒流入口９１および冷媒流出口９２に接続されている。そして、冷媒流入口９１から流入する冷媒のうち、比重の大きい液相冷媒は内部空間９３の鉛直方向下方側に一旦溜まり、比重の小さい気相冷媒は内部空間９３の鉛直方向上方側に一旦溜まるようになっている。   The modulator 9 has an internal space 93 that gas-liquid separates the refrigerant that has flowed out of the condensing unit 41. The internal space 93 is connected to the refrigerant inlet 91 and the refrigerant outlet 92. Of the refrigerant flowing in from the refrigerant inlet 91, the liquid phase refrigerant having a large specific gravity temporarily accumulates on the lower side in the vertical direction of the internal space 93, and the gas phase refrigerant having a small specific gravity temporarily accumulates on the upper side in the vertical direction of the internal space 93. It is like that.

図２は、本第１実施形態のチューブ２を長手方向から見た正面図である。図２に示すように、チューブ２は、その長手方向に冷媒が流れるようになっており、長手方向と直交する断面が長手方向と直交する幅方向に沿って扁平な形状を有するような扁平筒状に形成されている。   FIG. 2 is a front view of the tube 2 of the first embodiment as viewed from the longitudinal direction. As shown in FIG. 2, the tube 2 is configured such that a refrigerant flows in the longitudinal direction thereof, and a flat cylinder whose cross section orthogonal to the longitudinal direction has a flat shape along the width direction orthogonal to the longitudinal direction. It is formed in a shape.

チューブ２における幅方向、すなわち空気流れ方向の両端面２ａは、チューブ２の外方側に凸となるように円弧状に湾曲したＲ形状になっている。すなわち、チューブ２の両端面２ａのチューブ長手方向から見た断面形状は、所定の曲率半径を有する円弧状になっている。所定の曲率半径は、チューブ２の短径方向、すなわちチューブ高さ方向の長さＨの約半分の大きさに設定されている。   Both end surfaces 2 a in the width direction of the tube 2, that is, the air flow direction, have an R shape that is curved in an arc shape so as to protrude outward of the tube 2. That is, the cross-sectional shape seen from the tube longitudinal direction of both end faces 2a of the tube 2 is an arc shape having a predetermined radius of curvature. The predetermined radius of curvature is set to about half the length H of the tube 2 in the minor axis direction, that is, the tube height direction.

また、チューブ２の幅方向の端部（以下、長径側端部２ｂという）の板厚Ｘ、すなわちチューブ幅方向の長さは、チューブ２の他の部位の板厚より厚くなっている。そこで、本発明者は、上記構成になるチューブ２について、長径側端部２ｂの最適仕様の検討を行った。   Further, the plate thickness X of the end portion in the width direction of the tube 2 (hereinafter, referred to as the long diameter side end portion 2 b), that is, the length in the tube width direction is thicker than the plate thickness of other portions of the tube 2. Therefore, the present inventor examined the optimum specification of the long-diameter side end 2b of the tube 2 having the above-described configuration.

図３は、１ｇの小石がチューブ２の長径側端部２ｂに衝突した場合における、長径側端部２ｂの板厚Ｘとチューブ２が破損する衝突速度との関係を実験により求めた結果を示す図である。なお、本実験では、一般的な石の比重が０．００２７ｇ／ｍｍ３であることから、１ｇの小石の形状を一辺が７．２ｍｍの直方体としている。 FIG. 3 shows the result of an experiment to determine the relationship between the plate thickness X of the long-diameter end 2b and the collision speed at which the tube 2 breaks when 1 g of pebbles collides with the long-diameter end 2b of the tube 2. FIG. In this experiment, since the specific gravity of a general stone is 0.0027 g / mm 3 , the shape of 1 g of pebbles is a rectangular parallelepiped with a side of 7.2 mm.

市場では、凝縮器のチューブ２に、１ｇの小石が１４０ｋｍ／ｈで衝突した場合でもチューブ２が破損しない程度の耐力が要求されている。このため、図３より、チューブ２の長径側端部２ｂの板厚Ｘを０．６ｍｍ以上にすれば、市場の要求を満たすことがわかる。なお、実際は、小石は車両のグリル（図示せず）等に衝突し、減速されてからチューブ２の長径側端部２ｂに衝突するため、１ｇの小石が１４０ｋｍ／ｈで衝突した場合にチューブ２が破損しないような耐力があれば、市場で問題となることはない。   In the market, the tube 2 of the condenser is required to have such a strength that the tube 2 is not damaged even when 1 g of pebbles collides at 140 km / h. For this reason, it can be seen from FIG. 3 that if the plate thickness X of the long-diameter side end 2b of the tube 2 is 0.6 mm or more, the market demand is satisfied. Actually, the pebbles collide with the grill (not shown) of the vehicle and the like, and after colliding with the long-diameter side end portion 2b of the tube 2, the tube 2 when 1 g of pebbles collides at 140 km / h. If it has the strength to prevent damage, it will not be a problem in the market.

図２に戻り、チューブ２の内部には、冷媒との伝熱面積を増大させるインナーフィン２００が設けられている。インナーフィン２００は、冷媒流れ方向と略平行な平面部２０１と、隣接する平面部２０１間を繋ぐ頂部２０２とを有するように波形状に形成されている。そして、頂部２０２がチューブ２の内壁面と接するように形成されている。   Returning to FIG. 2, an inner fin 200 that increases the heat transfer area with the refrigerant is provided inside the tube 2. The inner fin 200 is formed in a wave shape so as to have a flat portion 201 that is substantially parallel to the refrigerant flow direction and a top portion 202 that connects the adjacent flat portions 201. The top portion 202 is formed so as to be in contact with the inner wall surface of the tube 2.

図４は、本第１実施形態のチューブ２の分解図である。図４に示すように、チューブ２は、長手方向と直交する断面が長手方向と直交する幅方向に沿って扁平な形状を有するように、互いに対向配置された第１半筒状部材２１Ａおよび第２半筒状部材２１Ｂから構成されている。本実施形態では、第１半筒状部材２１Ａおよび第２半筒状部２１Ｂは、互いに同形状に形成されている。   FIG. 4 is an exploded view of the tube 2 of the first embodiment. As shown in FIG. 4, the tube 2 includes a first semi-cylindrical member 21 </ b> A and a first semi-cylindrical member 21 </ b> A arranged to face each other such that a cross section perpendicular to the longitudinal direction has a flat shape along a width direction perpendicular to the longitudinal direction. It is composed of two semi-cylindrical members 21B. In the present embodiment, the first semi-cylindrical member 21A and the second semi-cylindrical portion 21B are formed in the same shape.

第１、第２半筒状部材２１Ａ、２１Ｂは、チューブ２の幅方向、すなわち長径方向に延びる平板部２２を有している。また、平板部２２の長径方向における両端部は、円弧状に湾曲した湾曲部２３となっている。湾曲部２３は、チューブ２の外方側に凸となるように湾曲している。   The first and second semi-cylindrical members 21 </ b> A and 21 </ b> B have a flat plate portion 22 that extends in the width direction of the tube 2, that is, the major axis direction. Further, both end portions in the major axis direction of the flat plate portion 22 are curved portions 23 curved in an arc shape. The curved portion 23 is curved so as to be convex outward of the tube 2.

そして、第１、第２半筒状部材２１Ａ、２１Ｂを互いに対向配置するとともに、第１、第２半筒状部材２１Ａ、２１Ｂの湾曲部２３同士が接触するように組み合わせることにより、チューブ２が形成されている。このとき、チューブ２の長径側端部２ｂは、第１、第２半筒状部材２１Ａ、２１Ｂの湾曲部２３により構成されている。   The first and second semi-cylindrical members 21A and 21B are arranged so as to face each other, and the tube 2 is formed by combining the curved portions 23 of the first and second semi-cylindrical members 21A and 21B so as to contact each other. Is formed. At this time, the long-diameter side end 2b of the tube 2 is constituted by the curved portions 23 of the first and second semi-cylindrical members 21A and 21B.

ここで、第１半筒状部材２１Ａの湾曲部２３における第２半筒状部材２１Ｂの湾曲部２３と接触する面、および第２半筒状部材２１Ｂの湾曲部２３における第１半筒状部材２１Ａの湾曲部２３と接触する面を、それぞれ接触面２３ａという。また、第１、第２半筒状部材２１Ａ、２１Ｂの長径方向両端部に設けられる湾曲部２３のうち、一方の湾曲部２３を第１湾曲部２３１といい、他方の湾曲部２３を第２湾曲部２３２という。   Here, the surface of the curved portion 23 of the first semi-cylindrical member 21A that contacts the curved portion 23 of the second semi-cylindrical member 21B, and the first semi-cylindrical member of the curved portion 23 of the second semi-cylindrical member 21B. Each surface that contacts the curved portion 23 of 21A is referred to as a contact surface 23a. Of the curved portions 23 provided at both ends in the major axis direction of the first and second semi-cylindrical members 21A and 21B, one curved portion 23 is called a first curved portion 231 and the other curved portion 23 is a second curved portion 23. It is referred to as a curved portion 232.

第１、第２半筒状部材２１Ａ、２１Ｂの第１湾曲部２３１には、互いに対応する凹部２３ｂおよび凸部２３ｃのうち一方が設けられており、第１、第２半筒状部材２１Ａ、２１Ｂの第２湾曲部２３２には、互いに対応する凹部２３ｂおよび凸部２３ｃのうち他方が設けられている。   The first curved portion 231 of the first and second semi-cylindrical members 21A and 21B is provided with one of a concave portion 23b and a convex portion 23c corresponding to each other, and the first and second semi-cylindrical members 21A, The second curved portion 232 of 21B is provided with the other of the concave portion 23b and the convex portion 23c corresponding to each other.

具体的には、第１、第２半筒状部材２１Ａ、２１Ｂの第１湾曲部２３１の接触面２３ａには、凹部２３ｂがそれぞれ設けられている。また、第１、第２半筒状部材２１Ａ、２１Ｂの第２湾曲部２３２の接触面２３ａには、凹部２３ｂに対応する凸部２３ｃがそれぞれ設けられている。本実施形態の凸部２３ｃは、チューブ長手方向から見た断面形状が角の尖った矩形状になっている。   Specifically, concave portions 23b are provided on the contact surfaces 23a of the first curved portions 231 of the first and second semi-cylindrical members 21A and 21B, respectively. Further, the contact surface 23a of the second curved portion 232 of the first and second semi-cylindrical members 21A and 21B is provided with a convex portion 23c corresponding to the concave portion 23b. The convex portion 23c of the present embodiment has a rectangular shape with a sharp corner when viewed from the tube longitudinal direction.

図５は、図２のＡ部拡大図である。図５に示すように、第１、第２半筒状部材２１Ａ、２１Ｂの平板部２２におけるインナーフィン２００の頂部２０２が接合される部位には、チューブ２１の外方側に向かって窪んだ窪み部２４が形成されている。窪み部２４は、インナーフィン２００の頂部２０２に対応する形状に形成されている。   FIG. 5 is an enlarged view of a portion A in FIG. As shown in FIG. 5, in the portion where the top portion 202 of the inner fin 200 in the flat plate portion 22 of the first and second semi-cylindrical members 21 </ b> A and 21 </ b> B is joined, a depression recessed toward the outer side of the tube 21. A portion 24 is formed. The recess 24 is formed in a shape corresponding to the top 202 of the inner fin 200.

続いて、本実施形態のチューブ２の製造方法について簡単に説明する。   Then, the manufacturing method of the tube 2 of this embodiment is demonstrated easily.

まず、第１半筒状部材２１Ａの第１湾曲部２３１が第２半筒状部材２１Ｂの第２湾曲部２３２に対向するとともに、第１半筒状部材２１Ａの第２湾曲部２３２が第２半筒状部材２１Ｂの第１湾曲部２３１に対向するように、第１、第２半筒状部材２１Ａ、２１Ｂを配置する。そして、この状態の２つの半筒状部材２１Ａ、２１Ｂ間にインナーフィン２００を挟み込んだ後、２つの半筒状部材２１Ａ、２２１Ｂを組み合わせる。このとき、第１半筒状部材２１Ａの凹部２３ｂと第２半筒状部材２１Ｂの凸部２３ｃとが嵌合されるとともに、第２半筒状部材２１Ｂの凹部２３ｂと第１半筒状部材２１Ａの凸部２３ｃとが嵌合される。また、インナーフィン２００の頂部２０２が、第１、第２半筒状部材２１Ａ、２１Ｂの平板部２２の窪み部２４に入り込んでいる。そして、この状態で、ろう付け接合を行うことにより、インナーフィン２００が内部に配置されたチューブ２が形成される。   First, the first curved portion 231 of the first semi-cylindrical member 21A is opposed to the second curved portion 232 of the second semi-cylindrical member 21B, and the second curved portion 232 of the first semi-cylindrical member 21A is the second. The first and second semi-cylindrical members 21A and 21B are arranged so as to face the first bending portion 231 of the semi-cylindrical member 21B. Then, after sandwiching the inner fin 200 between the two semi-cylindrical members 21A and 21B in this state, the two semi-cylindrical members 21A and 221B are combined. At this time, the concave portion 23b of the first semi-cylindrical member 21A and the convex portion 23c of the second semi-cylindrical member 21B are fitted, and the concave portion 23b of the second semi-cylindrical member 21B and the first semi-cylindrical member are fitted. 21A convex part 23c is fitted. Further, the top portion 202 of the inner fin 200 enters the recess 24 of the flat plate portion 22 of the first and second semi-cylindrical members 21A and 21B. And the tube 2 by which the inner fin 200 is arrange | positioned inside is formed by performing brazing joining in this state.

なお、本実施形態では、図５に示すように、チューブ２の外面全体、すなわち第１、第２半筒状部材２１Ａ、２１Ｂのチューブ外方側の面全体に犠牲腐食効果を発揮する亜鉛層１００が形成されている。   In the present embodiment, as shown in FIG. 5, the zinc layer that exerts a sacrificial corrosion effect on the entire outer surface of the tube 2, that is, the entire surface of the first and second semi-cylindrical members 21A and 21B on the tube outer side. 100 is formed.

以上説明したように、チューブ２の長径側端部２ｂの板厚Ｘを０．６ｍｍ以上とすることで、小石の衝突によりチューブ２が破損することを防止できる。   As described above, by setting the plate thickness X of the long-diameter side end portion 2b of the tube 2 to 0.6 mm or more, the tube 2 can be prevented from being damaged due to the collision of pebbles.

また、チューブ２の両端面２ａのチューブ長手方向から見た断面形状を円弧状、すなわちＲ形状とすることで、従来の押出チューブが用いられている熱交換器に対し、本実施形態のチューブ２を容易に適用することが可能となる。   Moreover, the cross-sectional shape seen from the tube longitudinal direction of the both ends 2a of the tube 2 is made into circular arc shape, ie, R shape, The tube 2 of this embodiment is compared with the heat exchanger in which the conventional extrusion tube is used. Can be easily applied.

ところで、従来、チューブ内にインナーフィンを配置すると、インナーフィンの板厚分だけチューブ内の冷媒通路断面積が減少し、チューブにおける冷媒圧損が増大するという問題があった。   By the way, conventionally, when the inner fin is disposed in the tube, there is a problem that the refrigerant passage cross-sectional area in the tube is reduced by the thickness of the inner fin, and the refrigerant pressure loss in the tube is increased.

これに対し、本実施形態のように、第１、第２半筒状部材２１Ａ、２１Ｂの平板部２２におけるインナーフィン２００の頂部２０２が接合される部位に窪み部２４を形成することで、チューブ２内の冷媒通路断面積が減少することを抑制できる。さらに、窪み部２４を、インナーフィン２００の頂部２０２に対応する形状に形成することで、インナーフィン２００の接合性を向上させることが可能となる。   On the other hand, as in the present embodiment, the hollow portion 24 is formed at a portion where the top portion 202 of the inner fin 200 is joined to the flat plate portion 22 of the first and second semi-cylindrical members 21A and 21B. It can suppress that the refrigerant passage cross-sectional area in 2 reduces. Furthermore, by forming the recess 24 in a shape corresponding to the top portion 202 of the inner fin 200, it is possible to improve the bondability of the inner fin 200.

ところで、図５に示すように、第１、第２半筒状部材２１Ａ、２１Ｂの平板部２２に窪み部２４を形成する際に、第１、第２半筒状部材２１Ａ、２１Ｂのチューブ外方側の面に均一に形成された亜鉛層１００が薄く広がる。このため、加熱炉内でチューブ２をろう付けすると、窪み部２４のチューブ外方側にある亜鉛層１００ａが他の部位より薄くなる。この亜鉛層１００ａが薄くなった部位は電位が貴になり、他の部位の電位より高いため、腐食し難くなる。したがって、窪み部２４、すなわちチューブ２とインナーフィン２００との接合部の耐食性を向上させることが可能となる。   By the way, as shown in FIG. 5, when forming the hollow part 24 in the flat plate part 22 of the first and second semi-cylindrical members 21A and 21B, the outside of the tubes of the first and second semi-cylindrical members 21A and 21B. The zinc layer 100 uniformly formed on the side surface spreads thinly. For this reason, when the tube 2 is brazed in the heating furnace, the zinc layer 100a on the tube outward side of the recessed portion 24 becomes thinner than other portions. The portion where the zinc layer 100a is thin has a noble potential and is higher than the potentials of other portions, and therefore is difficult to corrode. Therefore, it is possible to improve the corrosion resistance of the recessed portion 24, that is, the joint portion between the tube 2 and the inner fin 200.

また、第１、第２半筒状部材２１Ａ、２１Ｂの第１湾曲部２３１に、互いに対応する凹部２３ｂおよび凸部２３ｃのうち一方を設け、第１、第２半筒状部材２１Ａ、２１Ｂの第２湾曲部２３２に、互いに対応する凹部２３ｂおよび凸部２３ｃのうち他方を設け、凹部２３ｂと凸部２３ｃとが嵌合した状態でろう付け接合を行うように構成することで、第１、第２半筒状部材２１Ａ、２１Ｂのろう付け長さを十分に確保することができる。これにより、チューブ２の耐食性を向上させることが可能となる。   In addition, the first curved portion 231 of the first and second semi-cylindrical members 21A and 21B is provided with one of the corresponding concave portion 23b and convex portion 23c, and the first and second semi-cylindrical members 21A and 21B. By providing the second curved portion 232 with the other of the concave portion 23b and the convex portion 23c corresponding to each other, and performing the brazing joint in a state where the concave portion 23b and the convex portion 23c are fitted, the first, The brazing length of the second semi-cylindrical members 21A and 21B can be sufficiently secured. Thereby, the corrosion resistance of the tube 2 can be improved.

また、第１、第２筒状部材２１Ａ、２１Ｂを同形状に形成することで、１種類のプレス型のみで２つの筒状部材２１Ａ、２１Ｂを製造することができるので、チューブ２の生産性を向上させることができる。   In addition, by forming the first and second cylindrical members 21A and 21B in the same shape, the two cylindrical members 21A and 21B can be manufactured with only one type of press die, so that the productivity of the tube 2 is improved. Can be improved.

（第２実施形態）
次に、本発明の第２実施形態について図６に基づいて説明する。図６は、本第２実施形態のチューブ２を冷媒流れ方向から見た正面図である。 (Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 6 is a front view of the tube 2 of the second embodiment viewed from the refrigerant flow direction.

図６に示すように、第１、第２半筒状部材２１Ａ、２１Ｂの平板部２２におけるチューブ２の内面を構成する面には、チューブ２の内方側に突出する突起部２５が複数設けられている。突起部２５は、隣接する窪み部２４間に１つずつ配設されている。これによれば、インナーフィン２００がチューブ幅方向にずれることを防止できる。   As shown in FIG. 6, a plurality of protrusions 25 projecting inward of the tube 2 are provided on the surface constituting the inner surface of the tube 2 in the flat plate portion 22 of the first and second semi-cylindrical members 21 </ b> A and 21 </ b> B. It has been. One protrusion 25 is disposed between adjacent recesses 24. According to this, it is possible to prevent the inner fin 200 from shifting in the tube width direction.

（他の実施形態）
なお、上記各実施形態では、第１、第２半筒状部材２１Ａ、２１Ｂの第１湾曲部２３１の接触面２３ａに１つの凹部２３ｂを設けるとともに、第１、第２半筒状部材２１Ａ、２１Ｂの第２湾曲部２３２の接触面２３ａに凹部２３ｂに対応する１つの凸部２３ｃをそれぞれ設け、凸部２３をチューブ長手方向から見た断面形状が角の尖った矩形状となるように形成した例について説明したが、これに限られない。 (Other embodiments)
In each of the above embodiments, one concave portion 23b is provided on the contact surface 23a of the first curved portion 231 of the first and second semi-cylindrical members 21A and 21B, and the first and second semi-cylindrical members 21A, One convex portion 23c corresponding to the concave portion 23b is provided on the contact surface 23a of the second curved portion 232 of 21B, and the convex portion 23 is formed so that the cross-sectional shape viewed from the tube longitudinal direction is a rectangular shape with sharp corners. However, the present invention is not limited to this.

例えば、図７（ａ）に示すように、第１、第２半筒状部材２１Ａ、２１Ｂの第１湾曲部２３１の接触面２３ａに２つの凹部２３ｂを設けるとともに、第１、第２半筒状部材２１Ａ、２１Ｂの第２湾曲部２３２の接触面２３ａに２つの凹部２３ｂに対応する２つの凸部２３ｃをそれぞれ設けてもよい。また、図７（ｂ）に示すように、第１、第２半筒状部材２１Ａ、２１Ｂの第２湾曲部２３２の接触面２３ａに２つの凹部２３ｂを設けるとともに、第１、第２半筒状部材２１Ａ、２１Ｂの第１湾曲部２３１の接触面２３ａに２つの凹部２３ｂに対応する２つの凸部２３ｃをそれぞれ設け、凸部２３をチューブ長手方向から見た断面形状が角が円弧状に湾曲した矩形状となるように形成してもよい。また、図７（ｃ）、（ｄ）に示すように、凸部２３をチューブ長手方向から見た断面形状が略三角形状となるように形成してもよい。   For example, as shown in FIG. 7A, two concave portions 23b are provided on the contact surface 23a of the first curved portion 231 of the first and second semi-cylindrical members 21A and 21B, and the first and second semi-cylindrical members are provided. The two convex portions 23c corresponding to the two concave portions 23b may be provided on the contact surface 23a of the second curved portion 232 of the shaped members 21A and 21B, respectively. In addition, as shown in FIG. 7 (b), two concave portions 23b are provided on the contact surface 23a of the second curved portion 232 of the first and second semi-cylindrical members 21A and 21B, and the first and second semi-cylindrical members are provided. Two convex portions 23c corresponding to the two concave portions 23b are provided on the contact surface 23a of the first curved portion 231 of the first and second members 21A and 21B, respectively, and the cross-sectional shape of the convex portion 23 viewed from the tube longitudinal direction has an arc shape. You may form so that it may become a curved rectangular shape. Further, as shown in FIGS. 7C and 7D, the convex portion 23 may be formed so that the cross-sectional shape viewed from the longitudinal direction of the tube is substantially triangular.

また、上記各実施形態では、第１、第２半筒状部材２１Ａ、２１Ｂを同形状に形成した例について説明したが、これに限らず、第１、第２半筒状部材２１Ａ、２１Ｂを異なる形状に形成してもよい。   Moreover, in each said embodiment, although the example which formed the 1st, 2nd half cylindrical member 21A, 21B in the same shape was demonstrated, not only this but 1st, 2nd half cylindrical member 21A, 21B is used. You may form in a different shape.

また、上記各実施形態では、本発明に係る熱交換器用チューブを、凝縮部４１および過冷却部４２を有する凝縮器のチューブ２に適用した例について説明したが、これに限らず、過冷却部を有しない凝縮器や、ラジエータ、ヒータコアユニット等の各種の熱交換器のチューブに適用してもよい。ここで、熱交換器内を流れる熱媒体としては、冷媒に限らず、エンジン冷却水等を用いることができる。   Moreover, although each said embodiment demonstrated the example which applied the tube for heat exchangers which concerns on this invention to the tube 2 of the condenser which has the condensation part 41 and the supercooling part 42, not only this but a supercooling part You may apply to the tube of various heat exchangers, such as a condenser which does not have this, a radiator, and a heater core unit. Here, the heat medium flowing in the heat exchanger is not limited to the refrigerant, and engine cooling water or the like can be used.

第１実施形態における熱交換器１の全体構造を示す。The whole structure of the heat exchanger 1 in 1st Embodiment is shown. 第１実施形態のチューブ２を長手方向から見た正面図である。It is the front view which looked at the tube 2 of 1st Embodiment from the longitudinal direction. １ｇの小石がチューブ２の長径側端部２ｂに衝突した場合における、長径側端部２ｂの板厚Ｘとチューブ２が破損する衝突速度との関係を実験により求めた結果を示す図である。It is a figure which shows the result of having calculated | required the relationship between the plate | board thickness X of the long diameter side edge part 2b, and the collision speed at which the tube 2 breaks by experiment when 1g of pebbles collide with the long diameter side edge part 2b of the tube 2. FIG. 第１実施形態のチューブ２の分解図である。It is an exploded view of the tube 2 of 1st Embodiment. 図２のＡ部拡大図である。It is the A section enlarged view of FIG. 第２実施形態のチューブ２を冷媒流れ方向から見た正面図である。It is the front view which looked at the tube 2 of 2nd Embodiment from the refrigerant | coolant flow direction. 他の実施形態におけるチューブ２の長径側端部２ｂ近傍を示す拡大正面図である。It is an enlarged front view which shows the long diameter side edge part 2b vicinity of the tube 2 in other embodiment.

符号の説明Explanation of symbols

２ チューブ
２ａ 両端面
２ｂ 長径側端部
２１Ａ 第１半筒状部材
２１Ｂ 第２半筒状部材
２２ 平板部
２３ 湾曲部
２３ｂ 凹部
２３ｃ 凸部
２４ 窪み部
２５ 突起部
２００ インナーフィン
２０１ 平面部
２０２ 頂部 2 Tube 2a Both end surfaces 2b Long-diameter side end portion 21A First semi-cylindrical member 21B Second semi-cylindrical member 22 Flat plate portion 23 Curved portion 23b Recessed portion 23c Convex portion 24 Depressed portion 25 Protruding portion 200 Inner fin 201 Flat portion 202 Top portion

Claims (5)

長手方向に熱媒体が流れるようになっており、前記長手方向と直交する断面が前記長手方向と直交する幅方向に沿って扁平な形状を有するように形成されている熱交換器用チューブであって、
前記幅方向における両端面（２ａ）の前記長手方向から見た断面形状は、所定の曲率半径を有する円弧状になっており、
前記幅方向における端部（２ｂ）の前記幅方向の板厚（Ｘ）は、０．６ｍｍ以上になっており、
半筒状に形成された第１半筒状部材（２１Ａ）および第２半筒状部材（２１Ｂ）を組み合わせることにより形成されており、
前記第１半筒状部材（２１Ａ）および前記第２半筒状部材（２１Ｂ）は、前記幅方向に延びる平板部（２２）を有しているとともに、前記平板部（２２）における前記幅方向の両端部は、円弧状に湾曲した湾曲部（２３）になっており、
前記第１半筒状部材（２１Ａ）の前記湾曲部（２３）には、互いに対応する凹部（２３ｂ）および凸部（２３ｃ）のうち一方が設けられており、前記第２半筒状部材（２１Ｂ）の前記湾曲部（２３）には、前記互いに対応する凹部（２３ｂ）および凸部（２３ｃ）のうち他方が設けられており、
前記凹部（２３ｂ）に前記凸部（２３ｃ）が嵌合された状態で、前記第１半筒状部材（２１Ａ）および前記第２半筒状部材（２１Ｂ）が接合されていることを特徴とする熱交換器用チューブ。 A heat exchanger tube in which a heat medium flows in a longitudinal direction, and a cross section orthogonal to the longitudinal direction has a flat shape along a width direction orthogonal to the longitudinal direction. ,
The cross-sectional shape seen from the longitudinal direction of both end faces (2a) in the width direction is an arc having a predetermined radius of curvature,
The thickness (X) in the width direction of the end portion (2b) in the width direction is 0.6 mm or more,
It is formed by combining the first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) formed in a semi-cylindrical shape,
The first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) have a flat plate portion (22) extending in the width direction, and the width direction of the flat plate portion (22). Both end portions are curved portions (23) curved in an arc shape,
The curved portion (23) of the first semi-cylindrical member (21A) is provided with one of a concave portion (23b) and a convex portion (23c) corresponding to each other, and the second semi-cylindrical member ( 21B) is provided with the other of the concave portion (23b) and the convex portion (23c) corresponding to each other, in the curved portion (23) of 21B),
The first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) are joined in a state where the convex portion (23c) is fitted to the concave portion (23b). Tube for heat exchanger. 前記所定の曲率半径は、前記長手方向および前記幅方向に直交する高さ方向の長さ（Ｈ）の約半分の大きさに設定されていることを特徴とする請求項１に記載の熱交換器用チューブ。   2. The heat exchange according to claim 1, wherein the predetermined curvature radius is set to be approximately half of a length (H) in a height direction orthogonal to the longitudinal direction and the width direction. Tube for dexterity. 前記第１半筒状部材（２１Ａ）と前記第２半筒状部材（２１Ｂ）との間には、前記熱媒体との伝熱面積を増大させるインナーフィン（２００）が設けられており、
前記インナーフィン（２００）は、前記熱媒体の流れ方向と略平行な平面部（２０１）と、隣接する前記平面部（２０１）間を繋ぐ頂部（２０２）とを有するように波形状に形成されており、
前記頂部（２０２）は、前記平板部（２２）における前記熱媒体が接触する側の面と接触しており、
前記平板部（２２）におけるチューブ内方側の面には、前記頂部（２０２）に対応する形状の窪み部（２４）が形成されており、
前記窪み部（２４）には、前記頂部（２０２）が入り込むようになっていることを特徴とする請求項１または２に記載の熱交換器用チューブ。 Between the first semi-cylindrical member (21A) and the second semi-cylindrical member (21B), an inner fin (200) that increases a heat transfer area with the heat medium is provided,
The inner fin (200) is formed in a wave shape so as to have a flat part (201) substantially parallel to the flow direction of the heat medium and a top part (202) connecting the adjacent flat parts (201). And
The top portion (202) is in contact with the surface of the flat plate portion (22) on the side where the heat medium contacts,
A hollow portion (24) having a shape corresponding to the top portion (202) is formed on the inner surface of the flat plate portion (22).
The tube for a heat exchanger according to claim 1 or 2, wherein the top (202) is inserted into the recess (24). 前記平板部（２２）には、チューブ内方側に突出する突起部（２５）が複数設けられており、
前記突起部（２５）は、隣接する前記頂部（２０２）間に配置されていることを特徴とする請求項１ないし３のいずれか１つに記載の熱交換器用チューブ。 The flat plate part (22) is provided with a plurality of protrusions (25) protruding inward of the tube,
The heat exchanger tube according to any one of claims 1 to 3, wherein the protrusion (25) is disposed between the adjacent top portions (202). 前記第１半筒状部材（２１Ａ）と前記第２半筒状部材（２１Ｂ）とは、互いに同形状に形成されており、
前記第１半筒状部材（２１Ａ）および前記第２半筒状部材（２１Ｂ）における前記幅方向の一方の端部側の前記湾曲部（２３）には、凹部（２３ｂ）がそれぞれ設けられており、
前記第１半筒状部材（２１Ａ）および前記第２半筒状部材（２１Ｂ）における前記幅方向の他方の端部側の前記湾曲部（２３）には、前記凹部（２３ｂ）に対応する凸部（２３ｃ）がそれぞれ設けられており、
前記第１半筒状部材（２１Ａ）の前記凹部（２３ｂ）に前記第２半筒状部材（２１Ｂ）の前記凸部（２３ｃ）が嵌合されるとともに、前記第２半筒状部材（２１Ｂ）の前記凹部（２３ｂ）に前記第１半筒状部材（２１Ａ）の前記凸部（２３ｃ）が嵌合された状態で、前記第１半筒状部材（２１Ａ）および前記第２半筒状部材（２１Ｂ）が接合されることにより形成されていることを特徴とする請求項１ないし４のいずれか１つに記載の熱交換器用チューブ。 The first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) are formed in the same shape as each other,
The curved portion (23) on one end side in the width direction of the first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) is provided with a recess (23b), respectively. And
The curved portion (23) on the other end side in the width direction of the first semi-cylindrical member (21A) and the second semi-cylindrical member (21B) has a convex corresponding to the concave portion (23b). Each part (23c) is provided,
The convex part (23c) of the second semi-cylindrical member (21B) is fitted into the concave part (23b) of the first semi-cylindrical member (21A), and the second semi-cylindrical member (21B) ) In the state in which the convex portion (23c) of the first semi-cylindrical member (21A) is fitted into the concave portion (23b) of the first semi-cylindrical member (21A) and the second semi-cylindrical shape. The heat exchanger tube according to any one of claims 1 to 4, wherein the member (21B) is formed by joining.
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WO2019107010A1 (en) * 2017-11-28 2019-06-06 株式会社デンソー Tube of heat exchanger and heat exchanger
JP2019095166A (en) * 2017-11-28 2019-06-20 株式会社デンソー Tube of heat exchanger, and heat exchanger
CN109140837A (en) * 2018-08-10 2019-01-04 芜湖维软新材料有限公司 A kind of horizontal condenser of U-shaped baffling pipeline

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