JP2009264664A

JP2009264664A - Heat exchanger

Info

Publication number: JP2009264664A
Application number: JP2008115044A
Authority: JP
Inventors: Tatsuhiko Nishino; 達彦西野
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2008-04-25
Filing date: 2008-04-25
Publication date: 2009-11-12
Anticipated expiration: 2028-04-25
Also published as: JP5167930B2

Abstract

<P>PROBLEM TO BE SOLVED: To improve brazing property of a tube and a header tank and that of a tube and an inner fin in a heat exchanger configured to have the tube and the header tank as separate bodies and the inner tube inserted inside the tube. <P>SOLUTION: In the heat exchanger in which insertion portions 130 at both ends in the longitudinal direction of the tube 13 are inserted in a hole part 5 of the header tank 12, and then the header tank 12 and the tube 13 are joined by brazing at the portions of the hole part 5 and the insertion portions 130, projection parts 50 are provided projecting to the side of the insertion portions 130 on opposing faces 51, 52 opposing at least a flat plate part 31 out of first and second flat plate parts 31, 32 in the hole part 5, and after the projection parts 50 are formed, the insertion portions 130 are inserted in the hole part 5, the hole part 5 and the insertion portions 130 are brought in contact via the projection parts 50, and the projection parts 50 are provided near both ends in the airflow direction in the opposing face 51. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、熱交換器に関し、空気と冷媒との間で熱交換して空気を冷却する車両空調用蒸発器に適用して有効である。 The present invention relates to a heat exchanger, and is effective when applied to a vehicular air conditioning evaporator that cools air by exchanging heat between air and a refrigerant.

近年、熱交換器は小型化・軽量化・低コスト化を達成するために、従来の積層型熱交換器からチューブ板厚の薄肉化が可能なヘッダタンク別体化が進んでいる。また、熱交換器のチューブにおいては、扁平押出チューブが採用されてきたが、近年のさらなる軽量化・低コスト化のために、扁平管状に折り曲げられた金属板の幅方向両端部を互いにろう接することによって形成する板チューブの需要が高まっている。板チューブを採用することで、チューブ板厚のさらなる薄肉化が可能となる。板チューブの製造方法としては、例えば、チューブの外殻を構成する筒状部材と、チューブ内の内柱部を構成するインナーフィンとを各々の板材より加工・成形した後、一体ろう付けする方法がある。 In recent years, in order to achieve miniaturization, weight reduction, and cost reduction of heat exchangers, separate header tanks that can reduce the thickness of the tube plate from the conventional laminated heat exchanger have been advanced. In addition, although a flat extruded tube has been adopted as a heat exchanger tube, both ends in the width direction of metal plates bent into a flat tube are brazed to each other for further weight reduction and cost reduction in recent years. Therefore, the demand for plate tubes formed is increasing. By adopting a plate tube, the tube plate thickness can be further reduced. As a method of manufacturing a plate tube, for example, a cylindrical member that constitutes the outer shell of the tube and an inner fin that constitutes an inner pillar portion in the tube are processed and molded from each plate material, and then are integrally brazed. There is.

ところで、近年の熱交換器では、ヘッダタンクにチューブが挿入されているが、ヘッダタンクの穴部とチューブの挿入部位の寸法は、チューブの変形防止やコア組み時のチューブ挿入圧の観点より隙間バメ設計となっている。しかしながら、チューブと穴部との間にクリアランスが発生するため、チューブとヘッダタンクとの根付け部（接合部）のろう付け性が低下するという問題があった。 By the way, in recent heat exchangers, tubes are inserted into the header tank. However, the dimensions of the hole in the header tank and the insertion site of the tube are gaps from the viewpoint of tube deformation prevention and tube insertion pressure when assembling the core. It is a swallow design. However, since a clearance is generated between the tube and the hole, there is a problem that the brazing property of the root portion (joint portion) between the tube and the header tank is lowered.

これに対し、穴部におけるチューブの平板部の幅方向中央部近傍に対応する部位に突起部を設け、穴部とチューブとを突起部を介して接触させることで、チューブの根付け部周りのろう付け性を向上させた熱交換器が、特許文献１にて知られている（以下、従来例という）。
特開２００１−２６３８６０号公報 On the other hand, a protrusion is provided in a portion of the hole corresponding to the vicinity of the central portion in the width direction of the flat plate portion of the tube, and the hole and the tube are brought into contact with each other through the protrusion so that the brazing around the tube root portion is provided. A heat exchanger with improved attachment is known from Patent Document 1 (hereinafter referred to as a conventional example).
JP 2001-263860 A

ところで、従来の押出チューブタイプであれば、チューブとヘッダタンクとの根付け部のみをろう付けすればよかったが、板チューブではさらに、筒状部材とインナーフィンとをろう付けしなければならない。 By the way, in the case of the conventional extruded tube type, it is only necessary to braze only the root portion between the tube and the header tank. However, in the case of a plate tube, the cylindrical member and the inner fin must be further brazed.

筒状部材とインナーフィンは各々成形され、組み付けられた後、バラツキを吸収するために矯正加工が施される。この際に、筒状部材の平板部にスプリングバックが生じ、筒状部材とインナーフィンとの間に微小なクリアランス（数十μｍ）が発生する。この状態でチューブをヘッダタンクに挿入すると、従来例では突起部以外は隙間バメ設計となるため、空気流れ方向両端部近傍ではクリアランスが空いたままとなり、ろう付け起点とならない。 After the cylindrical member and the inner fin are molded and assembled, corrective processing is performed to absorb variations. At this time, a spring back is generated in the flat plate portion of the cylindrical member, and a minute clearance (several tens of μm) is generated between the cylindrical member and the inner fin. If the tube is inserted into the header tank in this state, the clearance gap is designed except for the protrusions in the conventional example, so that the clearance remains vacant in the vicinity of both ends in the air flow direction and does not become a starting point for brazing.

これに対し、チューブとアウターフィンとを交互に積層しコア部を組み立てた後に、アウターフィンにより筒状部材を外側から押さえることで、クリアランスを低減させることが可能である。しかしながら、板チューブは金属板を扁平形状に加工しているため、平板部の空気流れ方向両端部、すなわち加工が施されている部位は加工硬化しており、アウターフィンの押さえ力ではクリアランスを低減することができない。このため、扁平チューブが略瓢箪形状となる。この状態のチューブをフラット化するには、さらにアウターフィンによる圧縮荷重をかければよいが、現在の薄板からなるアウターフィンでは、クリアランスをなくす前にアウターフィンが座屈してしまう。 On the other hand, after assembling the core portion by alternately stacking the tubes and the outer fins, it is possible to reduce the clearance by pressing the cylindrical member from the outside with the outer fins. However, since the plate tube is made of a flat metal plate, both ends of the flat plate in the direction of air flow, that is, the processed parts are work hardened, and the outer fin pressing force reduces clearance. Can not do it. For this reason, a flat tube becomes a substantially bowl shape. In order to flatten the tube in this state, it is only necessary to apply a compressive load by the outer fin. However, in an outer fin made of a current thin plate, the outer fin is buckled before the clearance is eliminated.

したがって、チューブの加工部、すなわち平板部の空気流れ方向両端部近傍は、ヘッダタンクとの接合部およびインナーフィンとの接合部の両方にクリアランスが発生し、ろう付け起点がないため、ろう付け性が悪いという問題がある。 Therefore, the processed portion of the tube, that is, the vicinity of both ends in the air flow direction of the flat plate portion, has clearance at both the joint with the header tank and the joint with the inner fin, and there is no brazing origin, so brazing There is a problem that is bad.

本発明は、上記点に鑑み、チューブおよびヘッダタンクが別体として構成されているとともに、チューブの内部にインナーフィンが挿入されている熱交換器において、チューブとヘッダタンクとのろう付け性、およびチューブとインナーフィンとのろう付け性をともに向上させることを目的とする。 In view of the above points, in the heat exchanger in which the tube and the header tank are configured as separate bodies and the inner fin is inserted in the tube, the brazing property between the tube and the header tank, and It aims at improving both the brazing property of a tube and an inner fin.

上記目的を達成するため、請求項１に記載の発明では、穴部（５）における２つの平板部（３１、３２）のうち少なくとも一方の平板部（３１）に対向する対向面（５１、５２）には、挿入部位（１３０）側に突出する突起部（５０）が設けられており、突起部（５０）を形成した後、穴部（５）に挿入部位（１３０）を挿入し、穴部（５）と挿入部位（１３０）とを突起部（５０）を介して接触させるようになっており、突起部（５０）は、対向面（５１、５２）における第２流体の流れ方向両端部近傍に設けられていることを特徴としている。 In order to achieve the above object, according to the first aspect of the present invention, the opposing surface (51, 52) that faces at least one flat plate portion (31) of the two flat plate portions (31, 32) in the hole portion (5). ) Is provided with a protrusion (50) protruding toward the insertion site (130), and after forming the protrusion (50), the insertion site (130) is inserted into the hole (5) The part (5) and the insertion site (130) are brought into contact with each other via the protrusion (50), and the protrusion (50) is at both ends of the opposing surface (51, 52) in the second fluid flow direction. It is characterized by being provided in the vicinity of the part.

これにより、チューブ（１３）の加工部、すなわち平板部（３１、３２）の第２流体の流れ方向の端部近傍において、チューブ（１３）とヘッダタンク（１２）の穴部（５）とを突起部（５０）を介して接触させることができるので、チューブ（１３）とヘッダタンク（１２）とのろう付け性を向上させることが可能となる。 As a result, the tube (13) and the hole (5) of the header tank (12) are formed in the processed portion of the tube (13), that is, in the vicinity of the end of the flat plate portions (31, 32) in the second fluid flow direction. Since it can contact via a protrusion part (50), it becomes possible to improve the brazing property of a tube (13) and a header tank (12).

また、突起部（５０）により、平板部（３１、３２）の第２流体の流れ方向の端部近傍、すなわち加工硬化している部位をチューブ（１３）の外側から押さえることができるので、チューブ（１３）とインナーフィン（４）との間に発生したクリアランスをなくすことができる。これにより、チューブ（１３）とインナーフィン（４）とのろう付け性を向上させることが可能となる。 Moreover, since the projection (50) can press the vicinity of the end of the flat plate portion (31, 32) in the second fluid flow direction, that is, the work-hardened portion, from the outside of the tube (13), the tube Clearance generated between (13) and the inner fin (4) can be eliminated. Thereby, it becomes possible to improve the brazing property between the tube (13) and the inner fin (4).

また、請求項２に記載の発明では、少なくとも一方の平板部（３１）の第２流体の流れ方向の長さをＴＬ（単位：ｍｍ）とし、少なくとも一方の平板部（３１）における第２流体の流れ方向の一方の端部と、一方の端部に近い側の突起部（５０）における第２流体の流れ方向中央部との間の第２流体の流れ方向の距離をｘ（単位：ｍｍ）としたとき、ｘ／ＴＬが０．０５より大きく０．３２より小さいことを特徴としている。 In the second aspect of the present invention, the length of at least one flat plate portion (31) in the flow direction of the second fluid is TL (unit: mm), and the second fluid in at least one flat plate portion (31). The distance in the flow direction of the second fluid between one end portion in the flow direction of the second fluid and the central portion in the flow direction of the second fluid in the projection (50) on the side close to the one end portion is x (unit: mm) ), X / TL is larger than 0.05 and smaller than 0.32.

これによれば、後述の図３に例示するように、チューブ（１３）とヘッダタンク（１２）間、およびチューブ（１３）とインナーフィン（４）間のろう付け性を向上させることが可能となる。 According to this, as illustrated in FIG. 3 described later, it is possible to improve the brazing performance between the tube (13) and the header tank (12) and between the tube (13) and the inner fin (4). Become.

さらに、請求項３に記載の発明のように、ｘ／ＴＬを０．１５より大きく０．２５より小さくすることで、チューブ（１３）とヘッダタンク（１２）間、およびチューブ（１３）とインナーフィン（４）間のろう付け性をより向上させることが可能となる。 Further, as in the invention described in claim 3, by setting x / TL to be larger than 0.15 and smaller than 0.25, the tube (13) and the header tank (12), and the tube (13) and the inner It becomes possible to further improve the brazability between the fins (4).

また、請求項４に記載の発明では、少なくとも一方の平板部（３１）の第２流体の流れ方向の長さをＴＬ（単位：ｍｍ）、１つの対向面（５１）に設けられた突起部（５０）の第２流体の流れ方向の長さの合計をΣＡ（単位：ｍｍ）としたとき、ΣＡ／ＴＬが０．０５より大きく０．３より小さいことを特徴としている。 In the invention according to claim 4, the length of at least one flat plate portion (31) in the flow direction of the second fluid is set to TL (unit: mm), and the protruding portion provided on one opposing surface (51). When the sum of the lengths in the flow direction of the second fluid in (50) is ΣA (unit: mm), ΣA / TL is larger than 0.05 and smaller than 0.3.

これによれば、後述の図４に例示するように、チューブ（１３）の挿入部位（１３０）をヘッダタンク（１２）の穴部（５）に挿入する圧力を大幅に増大させることなく、チューブ（１３）とヘッダタンク（１２）間、およびチューブ（１３）とインナーフィン（４）間のろう付け性を向上させることが可能となる。 According to this, as illustrated in FIG. 4 described later, the tube (13) can be inserted without significantly increasing the pressure for inserting the insertion portion (130) of the tube (13) into the hole (5) of the header tank (12). It becomes possible to improve the brazing property between (13) and the header tank (12) and between the tube (13) and the inner fin (4).

さらに、請求項５に記載の発明のように、ΣＡ／ＴＬを０．１より大きく０．３より小さくすることで、チューブ（１３）の挿入部位（１３０）をヘッダタンク（１２）の穴部（５）に挿入する圧力を大幅に増大させることなく、チューブ（１３）とヘッダタンク（１２）間、およびチューブ（１３）とインナーフィン（４）間のろう付け性をより向上させることが可能となる。 Further, as in the invention described in claim 5, by setting ΣA / TL to be larger than 0.1 and smaller than 0.3, the insertion portion (130) of the tube (13) can be inserted into the hole of the header tank (12). It is possible to further improve the brazability between the tube (13) and the header tank (12) and between the tube (13) and the inner fin (4) without significantly increasing the pressure to be inserted into (5). It becomes.

また、請求項６に記載の発明では、チューブ（１３）における２つの平板部（３１、３２）の配置方向の長さをＴＨ（単位：ｍｍ）とし、穴部（５）における２つの平板部（３１、３２）のうち一方の平板部（３１）に対向する対向面（５１）に設けられた突起部（５０）から、穴部（５）における他方の平板部（３２）に対向する対向面（５２）におろした垂線の長さをＨ２（単位：ｍｍ）としたとき、ＴＨ−Ｈ２（単位：μｍ）が０以上であることを特徴としている。 In the invention of claim 6, the length in the arrangement direction of the two flat plate portions (31, 32) in the tube (13) is TH (unit: mm), and the two flat plate portions in the hole (5) (31, 32) From the protrusion (50) provided on the facing surface (51) facing one flat plate portion (31), facing the other flat plate portion (32) in the hole (5) When the length of the perpendicular drawn on the surface (52) is H2 (unit: mm), TH-H2 (unit: μm) is 0 or more.

これによれば、後述の図５に例示するように、チューブ（１３）とヘッダタンク（１２）間、およびチューブ（１３）とインナーフィン（４）間のろう付け性を向上させることが可能となる。 According to this, as illustrated in FIG. 5 described later, it is possible to improve the brazing performance between the tube (13) and the header tank (12) and between the tube (13) and the inner fin (4). Become.

さらに、請求項７に記載の発明のように、ＴＨ−Ｈ２を２０μｍより大きくすることで、チューブ（１３）とヘッダタンク（１２）間、およびチューブ（１３）とインナーフィン（４）間のろう付け性をより向上させることが可能となる。 Further, as in the invention described in claim 7, by making TH-H2 larger than 20 μm, it is possible to braze between the tube (13) and the header tank (12) and between the tube (13) and the inner fin (4). It is possible to improve the attachment.

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５に基づいて説明する。本実施形態は、本発明に係る熱交換器を、車両用空調装置の蒸発器に適用したものである。 (First embodiment)
1st Embodiment of this invention is described based on FIGS. In the present embodiment, the heat exchanger according to the present invention is applied to an evaporator of a vehicle air conditioner.

図１は、本第１実施形態に係る蒸発器を示す斜視図である。図１に示すように、本実施形態の蒸発器は、空気流れ方向に直列に配置された２つの蒸発器１、２から構成されている。ここで、２つの蒸発器１、２のうち、空気流れ下流側に配置されるものを第１蒸発器１といい、空気流れ上流側に配置されるものを第２蒸発器２という。 FIG. 1 is a perspective view showing an evaporator according to the first embodiment. As shown in FIG. 1, the evaporator of this embodiment is comprised from the two evaporators 1 and 2 arrange | positioned in series in the air flow direction. Here, of the two evaporators 1 and 2, the one disposed on the downstream side of the air flow is referred to as the first evaporator 1, and the one disposed on the upstream side of the air flow is referred to as the second evaporator 2.

第１蒸発器１および第２蒸発器２の基本的構成は同一なので、以下、第１蒸発器１の構成についてのみ説明する。 Since the basic configurations of the first evaporator 1 and the second evaporator 2 are the same, only the configuration of the first evaporator 1 will be described below.

第１蒸発器１は、コア部１１と、このコア部１１の上下両側に位置するヘッダタンク１２とを備えている。ここで、コア部１１は、それぞれ上下方向に延びる複数のチューブ１３と、この複数のチューブ１３相互間に接合されるアウターフィン（図示せず）との積層構造からなる。チューブ１３は冷媒通路を構成するもので、断面形状が空気流れ方向に沿って扁平な扁平チューブよりなる。アウターフィンは薄板材を波状に曲げ成形したコルゲートフィンであり、チューブ１３の平坦な外面側に接合され空気側伝熱面積を拡大する。なお、冷媒が本発明の第１流体に相当し、空気が第２流体に相当している。 The first evaporator 1 includes a core part 11 and header tanks 12 located on both upper and lower sides of the core part 11. Here, the core portion 11 has a laminated structure of a plurality of tubes 13 extending in the vertical direction and outer fins (not shown) joined between the plurality of tubes 13. The tube 13 constitutes a refrigerant passage, and is formed of a flat tube whose cross-sectional shape is flat along the air flow direction. The outer fin is a corrugated fin formed by bending a thin plate material into a wave shape, and is joined to the flat outer surface side of the tube 13 to expand the air-side heat transfer area. The refrigerant corresponds to the first fluid of the present invention, and the air corresponds to the second fluid.

チューブ１３とアウターフィンはコア部１１の左右方向に交互に積層配置され、このチューブ積層方向の両端部にはコア部１１を補強するサイドプレート１４が配置されている。このサイドプレート１４は、チューブ積層方向の最も外側に位置するアウターフィンに接合される。 The tubes 13 and the outer fins are alternately stacked in the left-right direction of the core portion 11, and side plates 14 that reinforce the core portion 11 are disposed at both ends in the tube stacking direction. This side plate 14 is joined to the outer fin located on the outermost side in the tube stacking direction.

第１蒸発器１の上下両側のヘッダタンク１２はコア部１１のチューブ１３の上下両端部、すなわちチューブ長手方向両端部が挿入され、接合される穴部（図２参照）を有し、チューブ１３の長手方向両端部がヘッダタンク１２の内部空間に連通するようになっている。これにより、上下両側のヘッダタンク１２は、熱交換コア部１１の複数のチューブ１３へ冷媒流れを分配したり、複数のチューブ１３からの冷媒流れを集合する役割を果たす。 The header tanks 12 on both the upper and lower sides of the first evaporator 1 have holes (see FIG. 2) into which the upper and lower ends of the tube 13 of the core 11 are inserted, that is, both ends of the tube in the longitudinal direction. Both end portions in the longitudinal direction communicate with the internal space of the header tank 12. Thereby, the header tanks 12 on both the upper and lower sides serve to distribute the refrigerant flow to the plurality of tubes 13 of the heat exchange core portion 11 and to collect the refrigerant flows from the plurality of tubes 13.

図２は、本第１実施形態におけるヘッダタンク１２とチューブ１３との接合部を示す拡大断面図である。なお、図２は、チューブ１３をヘッダタンク１２に挿入後で、かつろう付け前の状態を示している。図２に示すように、本実施形態のチューブ１３は、チューブ１３の外殻を構成し、冷媒流れ方向、すなわちチューブ長手方向に直交する断面が扁平形状に形成された筒状部材３と、筒状部材３内に設けられ、冷媒との伝熱面積を増大させるインナーフィン４とから構成されている。筒状部材３とインナーフィン４は、それぞれ異なる板状部材で構成されている。 FIG. 2 is an enlarged cross-sectional view showing a joint portion between the header tank 12 and the tube 13 in the first embodiment. FIG. 2 shows a state after the tube 13 is inserted into the header tank 12 and before brazing. As shown in FIG. 2, the tube 13 of the present embodiment constitutes an outer shell of the tube 13, and includes a tubular member 3 having a flat cross section perpendicular to the refrigerant flow direction, that is, the tube longitudinal direction, The inner fin 4 is provided in the shaped member 3 and increases the heat transfer area with the refrigerant. The cylindrical member 3 and the inner fin 4 are composed of different plate-like members.

本実施形態の筒状部材３は、短径方向（すなわちチューブ積層方向）において並行に対向する第１平板部３１および第２平板部３２と、長径方向（すなわち空気流れ方向）の一端側において外側に突出し円弧状に形成された円弧状湾曲部３３と、長径方向の他端側において第１、第２平板部３１、３２をカシメ接合するカシメ部３４から構成されている。円弧状湾曲部３３は、第１、第２平板部３１、３２と一体に繋がって屈曲しており、第１、第２平板部３１、３２を接続している。本実施形態では、第１平板部３１および第２平板部３２の空気流れ方向の長さは等しくなっている。また、第１平板部３１および第２平板部３２は、互いに平行に配置されている。 The cylindrical member 3 of the present embodiment has a first flat plate portion 31 and a second flat plate portion 32 that face each other in parallel in the short diameter direction (that is, the tube stacking direction), and the outer side on one end side in the long diameter direction (that is, the air flow direction) And an arcuate curved portion 33 that is formed in an arcuate shape and a caulking portion 34 that crimps and joins the first and second flat plate portions 31 and 32 on the other end side in the major axis direction. The arcuate curved portion 33 is bent integrally with the first and second flat plate portions 31 and 32, and connects the first and second flat plate portions 31 and 32. In the present embodiment, the lengths of the first flat plate portion 31 and the second flat plate portion 32 in the air flow direction are equal. Moreover, the 1st flat plate part 31 and the 2nd flat plate part 32 are mutually arrange | positioned in parallel.

そして、インナーフィン４のうち円弧状湾曲部３３側には、筒状部材３の円弧状湾曲部３３と接触する接触端部４１が設けられている。また、インナーフィン４のうちカシメ部３４側には、筒状部材３の第１、第２平板部３１、３２と平行な平板状に形成された第３平板部４２が設けられている。この第３平板部４２は、筒状部材３の第１、第２平板部３１、３２で挟まれた状態で、第１平板部３１により、第２平板部３２と共に巻きカシメされている。 A contact end 41 that contacts the arcuate curved portion 33 of the tubular member 3 is provided on the arcuate curved portion 33 side of the inner fin 4. Further, a third flat plate portion 42 formed in a flat plate shape parallel to the first and second flat plate portions 31 and 32 of the tubular member 3 is provided on the caulking portion 34 side of the inner fin 4. The third flat plate portion 42 is wound together with the second flat plate portion 32 by the first flat plate portion 31 while being sandwiched between the first and second flat plate portions 31 and 32 of the tubular member 3.

ここで、巻きカシメとは、第１、第２平板部３１、３２のうち一方側の平板部（本実施形態では第１平板部３１）を他方側の平板部（本実施形態では第２平板部３２）に巻き付けるように一方側の平板部を塑性変形させて両平板部３１、３２を機械的に固定するものである。 Here, the winding caulking means that one of the first and second flat plate portions 31 and 32 is the flat plate portion on the one side (first flat plate portion 31 in the present embodiment) and the other flat plate portion (in the present embodiment is the second flat plate portion). The flat plate portion on one side is plastically deformed so as to be wound around the portion 32), and both the flat plate portions 31, 32 are mechanically fixed.

また、インナーフィン４の両端部、すなわち接触端部４１および第３平板部４２を除く部位は、冷媒流れ方向と略平行な平面部４３と、隣接する平面部４３間を繋ぐ円弧状の頂部４４とを有するように波形状に形成されている。そして、頂部４４が筒状部材３の第１、第２平板部３１、３２と接するように形成されている。 Further, both end portions of the inner fin 4, that is, the portions excluding the contact end portion 41 and the third flat plate portion 42, are a flat portion 43 that is substantially parallel to the refrigerant flow direction and an arcuate top portion 44 that connects between the adjacent flat portions 43. And is formed in a wave shape. And the top part 44 is formed so that the 1st, 2nd flat plate parts 31 and 32 of the cylindrical member 3 may be contact | connected.

また、ヘッダタンク１２には、チューブ１３の長手方向端部（以下、挿入部位１３０ともいう）を挿入するための穴部５が形成されている。穴部５は、チューブ１３の筒状部材３に対応する形状に形成されているとともに、筒状部材３との間に所定のクリアランスができるような大きさに形成されている。ここで、穴部５の外縁部における筒状部材３の第１平板部３１に対向する面を第１対向面５１といい、第２平板部３２に対向する面を第２対向面５２という。また、第１対向面５１および第２対向面５２は、互いに平行になっている。 The header tank 12 is formed with a hole portion 5 for inserting a longitudinal end portion of the tube 13 (hereinafter also referred to as an insertion site 130). The hole 5 is formed in a shape corresponding to the tubular member 3 of the tube 13 and is sized so as to allow a predetermined clearance between the hole 5 and the tubular member 3. Here, the surface facing the first flat plate portion 31 of the cylindrical member 3 at the outer edge portion of the hole 5 is referred to as a first facing surface 51, and the surface facing the second flat plate portion 32 is referred to as a second facing surface 52. Moreover, the 1st opposing surface 51 and the 2nd opposing surface 52 are mutually parallel.

穴部５の第１、第２対向面５１、５２には、チューブ１３の挿入部位１３０側、すなわち穴部５の内方側に突出する突起部５０がそれぞれ設けられている。そして、穴部５に挿入部位１３０を挿入した際に、穴部５と挿入部位１３０とが突起部５０を介して接触するようになっている。 The first and second opposing surfaces 51 and 52 of the hole 5 are respectively provided with protrusions 50 that protrude toward the insertion portion 130 side of the tube 13, that is, the inward side of the hole 5. When the insertion part 130 is inserted into the hole 5, the hole 5 and the insertion part 130 come into contact with each other through the protrusion 50.

突起部５０は、第１、第２対向面５１、５２の空気流れ方向両端部近傍、すなわちチューブ１３の第１、第２平板部３１、３２における空気流れ方向の両端部近傍に対応する部位にそれぞれ設けられている。したがって、突起部５０は、第１対向面５１の空気流れ方向両端部近傍に１つずつ設けられているとともに、第２対向面５２の空気流れ方向両端部近傍に１つずつ設けられている。なお、第１、第２平板部３１、３２の空気流れ方向端部とは、板状部材から筒状部材３を形成する際に、曲げ加工が施された部位（以下、加工部ともいう）である。 The protrusions 50 are located in the vicinity of both ends in the air flow direction of the first and second opposing surfaces 51 and 52, that is, in the vicinity of both ends in the air flow direction of the first and second flat plate portions 31 and 32 of the tube 13. Each is provided. Accordingly, one protrusion 50 is provided near both ends of the first facing surface 51 in the air flow direction, and one protrusion 50 is provided near both ends of the second facing surface 52 in the air flow direction. In addition, the air flow direction edge part of the 1st, 2nd flat plate parts 31 and 32 is the site | part (henceforth a process part) to which the bending process was performed when forming the cylindrical member 3 from a plate-shaped member. It is.

本実施形態のように、突起部５０を、穴部５の第１、第２対向面５１、５２における空気流れ方向両端部近傍に設けることで、筒状部材３の加工部、すなわち第１、第２平板部３１、３２の空気流れ方向の端部近傍において、チューブ１３と穴部５とを突起部５０を介して接触させることができる。これにより、チューブ１３とヘッダタンク１２とのろう付け性を向上させることが可能となる。 As in the present embodiment, the protrusion 50 is provided in the vicinity of both end portions in the air flow direction on the first and second opposing surfaces 51 and 52 of the hole 5, so that the processed portion of the cylindrical member 3, that is, the first and second In the vicinity of the ends of the second flat plate portions 31 and 32 in the air flow direction, the tube 13 and the hole portion 5 can be brought into contact with each other through the protruding portion 50. Thereby, the brazing property between the tube 13 and the header tank 12 can be improved.

また、突起部５０により、第１、第２平板部３１、３２の空気流れ方向の端部近傍、すなわち加工硬化している部位をチューブ１３の外側から押さえることができるので、チューブ１３とインナーフィン４との間に発生したクリアランスをなくすことができる。これにより、チューブ１３とインナーフィン４とのろう付け性を向上させることが可能となる。 Further, the projections 50 can press the vicinity of the end portions of the first and second flat plate portions 31 and 32 in the air flow direction, that is, the work-hardened portions from the outside of the tube 13, so that the tube 13 and the inner fin 4 can be eliminated. Thereby, the brazing property between the tube 13 and the inner fin 4 can be improved.

そこで、本発明者は、上記構成になる本実施形態の蒸発器について、突起部５０の最適仕様の検討を行った。 Therefore, the present inventor examined the optimum specification of the protrusion 50 for the evaporator of the present embodiment having the above-described configuration.

図３は、突起部５０の空気流れ方向の長さ（以下、突起部５０の幅という）Ａが１ｍｍの場合における、突起部位置ｘ／ＴＬとろう付け起点形成率との関係を実験により求めた結果を示す図である。 FIG. 3 shows the relationship between the protrusion position x / TL and the brazing start point formation rate when the length A of the protrusion 50 in the air flow direction (hereinafter referred to as the width of the protrusion 50) A is 1 mm. It is a figure which shows the result.

ここで、突起部位置とは、突起部５０の第１、第２平板部３１、３２に対する空気流れ方向の相対位置をいう。そして、チューブ１３の第１、第２平板部３１、３２の空気流れ方向の長さをＴＬ（単位：ｍｍ）とし、第１、第２平板部３１における空気流れ方向の一方の端部と、当該一方の端部に近い側の突起部５０における空気流れ方向中央部との間の空気流れ方向の距離をｘ（単位：ｍｍ）としたとき、突起部位置は、ｘ／ＴＬとなる。なお、本実施形態では、１つの穴部５に形成される４つの突起部５０の突起部位置ｘ／ＴＬは、全て等しくなっている。 Here, the protrusion position refers to a relative position of the protrusion 50 in the air flow direction with respect to the first and second flat plate portions 31 and 32. The length of the first and second flat plate portions 31 and 32 of the tube 13 in the air flow direction is TL (unit: mm), and one end portion of the first and second flat plate portions 31 in the air flow direction, When the distance in the air flow direction between the protrusion 50 on the side close to the one end and the center in the air flow direction is x (unit: mm), the protrusion position is x / TL. In the present embodiment, the protrusion positions x / TL of the four protrusions 50 formed in one hole 5 are all equal.

また、ろう付け起点形成率（単位：％）とは、コア部１１を構成する全チューブ１３のうち、ヘッダタンク１２との根付部にろう付け起点が形成された、すなわちヘッダタンク１２との根付部がろう付けされたチューブ１３の割合をいう。例えば、コア部１１を構成するチューブ１３が７０本で、ヘッダタンク１２との根付部にろう付け起点が形成されたチューブ１３が５６本である場合、ろう付け起点形成率は８０％となる。 The brazing starting point formation rate (unit:%) means that the brazing starting point is formed at the root part of the header tank 12 among all the tubes 13 constituting the core part 11, that is, the rooting with the header tank 12. The ratio of the tube 13 where the part was brazed is said. For example, when the number of the tubes 13 constituting the core portion 11 is 70 and the number of the tubes 13 in which the brazing start points are formed at the root portion with the header tank 12 is 56, the brazing start point forming rate is 80%.

図３から明らかなように、突起部５０の幅Ａが１ｍｍの場合、突起部位置ｘ／ＴＬを０．０５より大きく０．３２より小さくすることにより、ろう付け起点形成率が８０％以上となり、突起部位置ｘ／ＴＬを０．１５より大きく０．２５より小さくすることにより、ろう付け起点形成率が１００％となる。 As is apparent from FIG. 3, when the width A of the protrusion 50 is 1 mm, the protrusion start position x / TL is made larger than 0.05 and smaller than 0.32, so that the brazing starting point formation rate becomes 80% or more. By making the protrusion position x / TL larger than 0.15 and smaller than 0.25, the brazing starting point formation rate becomes 100%.

図４は、突起部位置ｘ／ＴＬが０．２の場合における、干渉寸法ΣＡ／ＴＬとろう付け起点形成率との関係、および干渉寸法ΣＡ／ＴＬとチューブ挿入圧力比との関係を実験により求めた結果を示す図である。なお、図４中の破線は、従来例、すなわち第１、第２対向面５１、５２におけるチューブ１３の空気流れ方向略中央部に対向する部位にのみ、突起部５０を設けた蒸発器の場合を示している。 FIG. 4 shows the relationship between the interference dimension ΣA / TL and the brazing start point formation rate and the relationship between the interference dimension ΣA / TL and the tube insertion pressure ratio when the protrusion position x / TL is 0.2. It is a figure which shows the calculated | required result. Note that the broken line in FIG. 4 indicates the conventional example, that is, in the case of the evaporator in which the protrusion 50 is provided only in the portion of the first and second opposing surfaces 51 and 52 facing the substantially central portion in the air flow direction of the tube 13. Is shown.

ここで、干渉寸法とは、第１、第２平板部３１、３２の空気流れ方向の長さに対する突起部５０の空気流れ方向の長さの割合をいう。そして、１つの突起部５０の幅をＡ（単位：ｍｍ）とし、１つの対向面５１に形成される２つの突起部５０の幅の合計をΣＡ（単位：ｍｍ）としたとき、干渉寸法は、ΣＡ／ＴＬとなる。なお、本実施形態では、１つの穴部５に形成される４つの突起部５０の幅Ａは、全て等しくなっている。 Here, the interference dimension refers to the ratio of the length of the projection 50 in the air flow direction to the length of the first and second flat plate portions 31 and 32 in the air flow direction. When the width of one protrusion 50 is A (unit: mm) and the total width of two protrusions 50 formed on one opposing surface 51 is ΣA (unit: mm), the interference dimension is , ΣA / TL. In the present embodiment, the widths A of the four protrusions 50 formed in one hole 5 are all equal.

また、挿入圧力とは、穴部５にチューブ１３の挿入部位１３０を挿入する際に加える圧力であり、挿入圧力比とは、従来例の挿入圧力を１００％としたものである。 The insertion pressure is a pressure applied when the insertion portion 130 of the tube 13 is inserted into the hole 5, and the insertion pressure ratio is a value obtained by setting the conventional insertion pressure to 100%.

図４から明らかなように、従来例では、ろう付け起点形成率を８０％以上にするためには、干渉寸法ΣＡ／ＴＬを０．４以上にする必要があった。これに対し、本実施形態では、突起部位置ｘ／ＴＬが０．２の場合、干渉寸法ΣＡ／ＴＬを０．０５より大きくすることにより、ろう付け起点形成率が８０％以上となる。そして、干渉寸法ΣＡ／ＴＬを０．１より大きくすることにより、ろう付け起点形成率が１００％となる。したがって、従来例と比較して、干渉寸法ΣＡ／ＴＬを著しく大きくすることなく、ろう付け性を向上させることができる。このとき、干渉寸法ΣＡ／ＴＬを０．３より小さくすることにより、挿入圧力を従来例と比較して２割程度の増加に抑えることができる。 As apparent from FIG. 4, in the conventional example, in order to make the brazing start point formation rate 80% or more, the interference dimension ΣA / TL needs to be 0.4 or more. On the other hand, in this embodiment, when the protrusion position x / TL is 0.2, the brazing start point formation rate is 80% or more by increasing the interference dimension ΣA / TL to more than 0.05. And by making the interference dimension ΣA / TL larger than 0.1, the brazing starting point formation rate becomes 100%. Therefore, brazing performance can be improved without significantly increasing the interference dimension ΣA / TL as compared with the conventional example. At this time, by making the interference dimension ΣA / TL smaller than 0.3, the insertion pressure can be suppressed to an increase of about 20% compared to the conventional example.

図５は、突起部高さ（ＴＨ−Ｈ２）とろう付け起点形成率との関係を実験により求めた結果を示す図である。 FIG. 5 is a diagram showing a result of an experiment for determining the relationship between the protrusion height (TH-H2) and the brazing starting point formation rate.

ここで、突起部高さとは、第１対向面５１に設けられた１つの突起部５０（以下、第１突起部５０１という）のチューブ積層方向の長さと、第２対向面５２に設けられた１つの突起部（以下、第２突起部５０２）のチューブ積層方向の長さとの合計をいう。そして、チューブ１３のチューブ積層方向（すなわち第１、第２平板部３１、３２の配置方向）の長さをＴＨ（単位：ｍｍ）とし、穴部５の第１、第２対向面５１、５２間の距離をＨ１（単位：ｍｍ）とし、第１突起部５０１から第２対向面５２におろした垂線の長さ、すなわち第１突起部５０１と第２突起部５０２との間のチューブ積層方向の距離をＨ２（単位：ｍｍ）としたとき、突起部高さは、ＴＨ−Ｈ２（単位：μｍ）となる。なお、ＴＨ、Ｈ１、Ｈ２は、Ｈ２≦ＴＨ＜Ｈ１の関係を満たしている。 Here, the protrusion height refers to the length in the tube stacking direction of one protrusion 50 (hereinafter referred to as the first protrusion 501) provided on the first facing surface 51 and the second facing surface 52. The sum of the length of one protrusion (hereinafter referred to as the second protrusion 502) in the tube stacking direction. The length of the tube 13 in the tube stacking direction (that is, the arrangement direction of the first and second flat plate portions 31 and 32) is TH (unit: mm), and the first and second opposing surfaces 51 and 52 of the hole portion 5 are used. The distance between them is H1 (unit: mm), the length of the perpendicular line from the first protrusion 501 to the second facing surface 52, that is, the tube stacking direction between the first protrusion 501 and the second protrusion 502 When the distance is H2 (unit: mm), the height of the protrusion is TH-H2 (unit: μm). Note that TH, H1, and H2 satisfy the relationship of H2 ≦ TH <H1.

図５から明らかなように、突起部高さ（ＴＨ−Ｈ２）を０より大きくすることにより、ろう付け起点形成率が８０％以上となり、突起部高さ（ＴＨ−Ｈ２）を２０μｍより大きくすることにより、ろう付け起点形成率が１００％となる。 As is apparent from FIG. 5, by setting the protrusion height (TH-H2) to be greater than 0, the brazing starting point formation rate is 80% or more, and the protrusion height (TH-H2) is greater than 20 μm. As a result, the brazing starting point formation rate becomes 100%.

（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実施形態におけるヘッダタンク１２とチューブ１３との接合部を示す拡大断面図である。なお、図６は、チューブ１３をヘッダタンク１２に挿入後で、かつろう付け前の状態を示している。 (Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 6 is an enlarged cross-sectional view showing a joint portion between the header tank 12 and the tube 13 in the second embodiment. FIG. 6 shows a state after the tube 13 is inserted into the header tank 12 and before brazing.

図６に示すように、穴部５の第１、第２対向面５１、５２におけるチューブ１３の空気流れ方向の略中央部に対向する部位には、チューブ１３側に突出する中央突起部５０ａがそれぞれ設けられている。したがって、穴部５の第１、第２対向面５１、５２には、それぞれ、２つの突起部５０と中央突起部５０ａの合計３つの突起部が設けられている。本実施形態では、中央突起部５０ａの高さ、すなわちチューブ積層方向の長さは、突起部５０の高さと略同等になっている。また、中央突起部５０ａの幅は、突起部５０の幅と略同等になっている。 As shown in FIG. 6, a central protrusion 50 a that protrudes toward the tube 13 is formed at a portion of the first and second opposing surfaces 51 and 52 of the hole 5 that faces the substantially central portion in the air flow direction of the tube 13. Each is provided. Accordingly, the first and second opposing surfaces 51 and 52 of the hole 5 are each provided with a total of three protrusions, that is, two protrusions 50 and a central protrusion 50a. In the present embodiment, the height of the central protrusion 50 a, that is, the length in the tube stacking direction is substantially equal to the height of the protrusion 50. Further, the width of the central protrusion 50 a is substantially equal to the width of the protrusion 50.

これによれば、チューブ１３の空気流れ方向の略中央部にもろう付け起点を形成することができるので、ろう付け性をより向上させることが可能となる。 According to this, since the brazing start point can be formed at the substantially central portion of the tube 13 in the air flow direction, the brazing performance can be further improved.

（他の実施形態）
なお、上記各実施形態では、筒状部材３とインナーフィン４は、それぞれ異なる板状部材で構成した例について説明したが、これに限らず、例えば図７に示すように、筒状部材３とインナーフィン４を、一枚の板状部材から形成してもよい。 (Other embodiments)
In each of the above embodiments, the cylindrical member 3 and the inner fin 4 have been described as examples configured by different plate-like members. However, the present invention is not limited to this, and for example, as shown in FIG. The inner fin 4 may be formed from a single plate-like member.

また、上記各実施形態では、突起部５０を、第１対向面５１および第２対向面５２の両方に設けた例について説明したが、これに限らず、第１、第２対向面５１、５２のうちいずれか一方にのみ設けてもよい。 In the above embodiments, the example in which the protrusions 50 are provided on both the first facing surface 51 and the second facing surface 52 has been described. However, the present invention is not limited thereto, and the first and second facing surfaces 51 and 52 are not limited thereto. You may provide only in either.

また、上記第２実施形態では、中央突起部５０ａを、第１、第２対向面におけるチューブ１３の空気流れ方向の略中央部に対向する部位に設けた例について説明したが、これに限らず、第１、第２平板部３１、３２の空気流れ方向の略中央部に対向する部位に設けてもよい。 Moreover, although the said 2nd Embodiment demonstrated the example which provided the center protrusion part 50a in the site | part facing the substantially center part of the air flow direction of the tube 13 in a 1st, 2nd opposing surface, it does not restrict to this. The first flat plate portion 31 and the second flat plate portion 32 may be provided at a portion facing the substantially central portion in the air flow direction.

第１実施形態に係る蒸発器を示す斜視図である。It is a perspective view which shows the evaporator which concerns on 1st Embodiment. 第１実施形態におけるヘッダタンク１２とチューブ１３との接合部を示す拡大断面図である。It is an expanded sectional view showing the joined part of header tank 12 and tube 13 in a 1st embodiment. 突起部位置ｘ／ＴＬとろう付け起点形成率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 protrusion part position x / TL and the brazing origin formation rate by experiment. 干渉寸法ΣＡ／ＴＬとろう付け起点形成率との関係、および干渉寸法ΣＡ／ＴＬとチューブ挿入圧力比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 interference dimension (SIGMA) A / TL and brazing origin formation rate, and the relationship between interference dimension (SIGMA) A / TL and tube insertion pressure ratio by experiment. 突起部高さ（ＴＨ−Ｈ２）とろう付け起点形成率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 protrusion part height (TH-H2) and the brazing origin formation rate by experiment. 第２実施形態におけるヘッダタンク１２とチューブ１３との接合部を示す拡大断面図である。It is an expanded sectional view which shows the junction part of the header tank 12 and the tube 13 in 2nd Embodiment. 他の実施形態におけるチューブ１３を示す拡大断面図である。It is an expanded sectional view showing tube 13 in other embodiments.

Explanation of symbols

４インナーフィン
５穴部
１２ヘッダタンク
１３チューブ
３１、３２平板部
５０突起部
５１、５２対向面
１３０挿入部位 4 Inner fin 5 Hole 12 Header tank 13 Tube 31, 32 Flat plate 50 Projection 51, 52 Opposing surface 130 Insertion site

Claims

The two flat plate portions (31, 32) are arranged to face each other so that the first fluid flows through the inside and the cross section perpendicular to the longitudinal direction has a flat shape along the flow direction of the second fluid flowing through the outside. A tube (13),
A header tank (12) disposed at both longitudinal ends of the tube (13), joined to the tube (13), and in communication with the tube (13);
An inner fin (4) provided inside the tube (13) and increasing a heat transfer area with the first fluid;
After inserting the insertion site (130) at both ends in the longitudinal direction of the tube (13) into the hole (5) of the header tank (12), the hole (5) and the site of the insertion site (130) A heat exchanger for brazing and joining the header tank (12) and the tube (13),
The opposing surface (51, 52) that faces at least one flat plate portion (31) of the two flat plate portions (31, 32) in the hole portion (5) protrudes toward the insertion site (130). A protrusion (50) is provided,
After forming the protrusion (50), the insertion part (130) is inserted into the hole (5), and the hole (5) and the insertion part (130) are connected to the protrusion (50). Through the contact,
The protrusion (50) is provided in the vicinity of both ends in the flow direction of the second fluid on the facing surface (51, 52).

The length of the flow direction of the second fluid of the at least one flat plate portion (31) is TL (unit: mm),
One end portion in the flow direction of the second fluid in the at least one flat plate portion (31), and a central portion in the flow direction of the second fluid in the projection portion (50) on the side close to the one end portion. When the distance in the flow direction of the second fluid between x is x (unit: mm),
The heat exchanger according to claim 1, wherein x / TL is larger than 0.05 and smaller than 0.32.

The length of the flow direction of the second fluid of the at least one flat plate portion (31) is TL (unit: mm),
One end portion in the flow direction of the second fluid in the at least one flat plate portion (31), and a central portion in the flow direction of the second fluid in the projection portion (50) on the side close to the one end portion. When the distance in the flow direction of the second fluid between x is x (unit: mm),
The heat exchanger according to claim 1, wherein x / TL is greater than 0.15 and less than 0.25.

The length of the flow direction of the second fluid of the at least one flat plate portion (31) is TL (unit: mm), and the second of the protrusion portion (50) provided on one of the opposed surfaces (51). When the total length in the fluid flow direction is ΣA (unit: mm),
The heat exchanger according to any one of claims 1 to 3, wherein ΣA / TL is larger than 0.05 and smaller than 0.3.

The length of the flow direction of the second fluid of the at least one flat plate portion (31) is TL (unit: mm), and the second of the protrusion portion (50) provided on one of the opposed surfaces (51). When the total length in the fluid flow direction is ΣA (unit: mm),
The heat exchanger according to any one of claims 1 to 3, wherein ΣA / TL is larger than 0.1 and smaller than 0.3.

The length in the arrangement direction of the two flat plate portions (31, 32) in the tube (13) is TH (unit: mm),
From the protrusion (50) provided on the facing surface (51) facing one flat plate portion (31) of the two flat plate portions (31, 32) in the hole portion (5), the hole portion ( When the length of the perpendicular drawn on the facing surface (52) facing the other flat plate portion (32) in 5) is H2 (unit: mm),
The heat exchanger according to any one of claims 1 to 5, wherein TH-H2 (unit: µm) is 0 or more.

The length in the arrangement direction of the two flat plate portions (31, 32) in the tube (13) is TH (unit: mm),
From the protrusion (50) provided on the facing surface (51) facing one flat plate portion (31) of the two flat plate portions (31, 32) in the hole portion (5), the hole portion ( When the length of the perpendicular drawn on the facing surface (52) facing the other flat plate portion (32) in 5) is H2 (unit: mm),
The heat exchanger according to any one of claims 1 to 5, wherein TH-H2 (unit: µm) is larger than 20.