JPWO2019131569A1 - Header plateless heat exchanger - Google Patents

Header plateless heat exchanger Download PDF

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JPWO2019131569A1
JPWO2019131569A1 JP2019561680A JP2019561680A JPWO2019131569A1 JP WO2019131569 A1 JPWO2019131569 A1 JP WO2019131569A1 JP 2019561680 A JP2019561680 A JP 2019561680A JP 2019561680 A JP2019561680 A JP 2019561680A JP WO2019131569 A1 JPWO2019131569 A1 JP WO2019131569A1
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heat exchanger
bulging portion
plates
fluid
flat tube
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JP7244439B2 (en
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中村　洋一
洋一 中村
弘仁 杉本
弘仁 杉本
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T Rad Co Ltd
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T Rad Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Abstract

ヘッダープレートレス型熱交換器において、高温の排気ガス等が流入するチューブ先端部の温度上昇を抑え、耐久性を向上させること。偏平チューブ７を構成する各プレート５，６の膨出部４の幅を、膨出部４の長手方向両端部で広い幅広部４ｂとし、それ以外の中間部で幅狭部４ａとする。In a header plateless heat exchanger, the temperature rise at the tip of the tube into which high-temperature exhaust gas etc. flows in is suppressed to improve durability. The width of the bulging portion 4 of each of the plates 5 and 6 constituting the flat tube 7 is set to a wide wide portion 4b at both ends in the longitudinal direction of the bulging portion 4, and a narrow portion 4a at the other intermediate portions.

Description

本発明は、主として排気ガスを冷却水で冷却するＥＧＲクーラや、排気ガスの熱を冷却水に回収する排熱回収器に最適な熱交換器であって、ヘッダープレートレス型のコアを有するものに関する。
ヘッダープレートレス型のコアとは、偏平チューブの開口端を厚み方向に膨出したものを使用し、その膨出部において積層することにより、ヘッダープレートを不要としたものである。The present invention is a heat exchanger most suitable for an EGR cooler that mainly cools an exhaust gas with cooling water and an exhaust heat recovery device that recovers the heat of the exhaust gas to the cooling water, and has a header plateless type core. Regarding.
The header plateless type core uses a flat tube whose opening end is bulged in the thickness direction, and is laminated at the bulging portion to eliminate the need for a header plate.

下記特許文献１にヘッダープレートレス型熱交換器が提案されている。
この熱交換器は、図５〜図７に示す如く、そのコアを形成する偏平チューブ１１が、一対の溝型に形成されたプレートを互いに溝底を対向して嵌着したものからなり、その両端開放側の縁に膨出部１１ａが形成され、その膨出部１１ａにおいて各偏平チューブ１１を積層し、各プレート間を一体にろう付固定したものである。そして、図６に示されているように、各プレートの交角θは鋭角に形成されている。A header plateless heat exchanger is proposed in Patent Document 1 below.
As shown in FIGS. 5 to 7, this heat exchanger consists of a flat tube 11 forming a core of a pair of groove-shaped plates fitted to each other with their groove bottoms facing each other. A bulging portion 11a is formed on the edge on the open side at both ends, and each flat tube 11 is laminated on the bulging portion 11a, and the plates are integrally brazed and fixed. Then, as shown in FIG. 6, the intersection angle θ of each plate is formed at an acute angle.

特開２０１６−１８３８３３号公報Japanese Unexamined Patent Publication No. 2016-183833

従来のヘッダープレートレス型熱交換器は、排気ガスの入口部において、各偏平チューブが高温となり、繰り返し生じるヒートサイクルにより熱交換器が劣化するおそれがある。
これは、ヘッダープレートレス型熱交換器は構造が簡単になる利点を有するも、欠点として、ヘッダープレートのある熱交換器に比べて、各偏平チューブの先端部の冷却性が悪くその部分が高温となるからである。
そこで、本発明はヘッダープレートレスの利点を有しつつ、可能な限り偏平チューブの先端部の温度を低下できる熱交換器を提供することを課題とする。In the conventional header plateless heat exchanger, each flat tube becomes hot at the exhaust gas inlet, and the heat exchanger may deteriorate due to repeated heat cycles.
This has the advantage that the header plateless heat exchanger has a simple structure, but the disadvantage is that the cooling performance at the tip of each flat tube is poor and the temperature is high compared to the heat exchanger with the header plate. Because it becomes.
Therefore, it is an object of the present invention to provide a heat exchanger capable of lowering the temperature of the tip of a flat tube as much as possible while having the advantage of no header plate.

請求項１に記載の本発明は、それぞれ両側に一対の側壁１，２が立上げられて全体が溝状に形成され且つ、その側壁に直交した溝底３の両開放側の縁に厚み方向外側に細幅の膨出部４が形成された一対のプレート５，６を有し、それらのプレート５，６が互いに逆向きに対向して嵌着されている偏平チューブ７と、
複数の偏平チューブ７が膨出部４で互いに積層され、各プレート５，６が互いにろう付接合されている熱交換器コアと、を有し、
各偏平チューブの前記膨出部４の先端から第一流体１６が内部に流入し、その外側に第二流体２０が流通する熱交換器であって、
前記各プレート５，６の前記膨出部４の細幅が、前記膨出部４の長手方向の両端部で広い幅広部４ｂとなり、それ以外の中間部で狭い幅狭部４ａに形成されていることを特徴とするヘッダープレートレス型熱交換器である。
請求項２に記載の本発明は、前記各プレート５，６の前記膨出部４の細幅が、前記両端部では前記側壁１，２に近づく程広くなる平面三角の、または平面が湾曲したろう付接合部を有することを特徴とする請求項１に記載のヘッダープレートレス型熱交換器である。
請求項３に記載の本発明は、積層された各偏平チューブ７の前記膨出部４の長手方向の中間部の位置で、ろう付接合部からそれを横断して外面側に広がる各プレート５，６の交角θが、鈍角に形成されていることを特徴とする請求項１または請求項２に記載のヘッダープレートレス型熱交換器である。According to the first aspect of the present invention, a pair of side walls 1 and 2 are erected on both sides to form a groove shape as a whole, and the groove bottom 3 orthogonal to the side wall is formed in a thickness direction on both open side edges. A flat tube 7 having a pair of plates 5 and 6 having a narrow bulge 4 formed on the outside, and the plates 5 and 6 are fitted so as to face each other in opposite directions.
It has a heat exchanger core in which a plurality of flat tubes 7 are laminated with each other at a bulge 4 and each plate 5 and 6 are brazed to each other.
A heat exchanger in which the first fluid 16 flows into the inside from the tip of the bulging portion 4 of each flat tube, and the second fluid 20 flows to the outside thereof.
The narrow width of the bulging portion 4 of each of the plates 5 and 6 becomes a wide wide portion 4b at both ends in the longitudinal direction of the bulging portion 4, and is formed in a narrow narrow portion 4a at the other intermediate portions. It is a header plateless heat exchanger characterized by being
According to the second aspect of the present invention, the narrow width of the bulging portion 4 of each of the plates 5 and 6 becomes wider toward the side walls 1 and 2 at both ends, or the plane is curved. The header plateless heat exchanger according to claim 1, further comprising a brazed joint.
According to the third aspect of the present invention, each plate 5 extending from the brazed joint to the outer surface side at the position of the intermediate portion in the longitudinal direction of the bulging portion 4 of each of the laminated flat tubes 7. The header plateless heat exchanger according to claim 1 or 2, wherein the intersection angle θ of, 6 is formed at an obtuse angle.

請求項１に記載の発明は、各プレート５，６の前記膨出部４の細幅が、前記膨出部４の長手方向の両端部で広く、それ以外の中間部で狭く形成されたものである。
それにより、第二流体２０との温度差が最も大きくなる各偏平チューブ７の膨出部４の中間部において、各偏平チューブ７の先端から第二流体２０までの距離が短くなり、その先端部と第二流体２０との伝熱が向上し、その間の温度差が抑制される。なお、前記両端部においては、前記膨出部４の細幅は広く形成されており、前記両端部における側壁１，２とそれらに被嵌されるケーシング１３とのろう付面積が確保されるので、ろう付の信頼性および強度は維持される。
その結果、ヒートサイクルによる熱交換器の劣化が抑制され、熱交換器の耐久性が向上する。
請求項２に記載の発明は、前記膨出部４の細幅を側壁１，２に近づく程広くなる平面三角または湾曲した形に形成したものである。それにより、側壁近傍の熱応力の集中が緩和されるので、耐久性の高い熱交換器を提供できる。
請求項３に記載の発明は、各偏平チューブ７の膨出部４の外面側における、ろう付接合の交角θが、鈍角に形成されたものである。これにより、膨出部４の近傍の冷却水の流通を促進して、偏平チューブ７の先端部の温度上昇を抑えることができる。According to the first aspect of the present invention, the narrow width of the bulging portion 4 of each of the plates 5 and 6 is formed to be wide at both ends in the longitudinal direction of the bulging portion 4 and narrow at the other intermediate portions. Is.
As a result, in the intermediate portion of the bulging portion 4 of each flat tube 7 having the largest temperature difference with the second fluid 20, the distance from the tip of each flat tube 7 to the second fluid 20 becomes shorter, and the tip portion thereof. The heat transfer between the and the second fluid 20 is improved, and the temperature difference between them is suppressed. At both ends, the narrow width of the bulging portion 4 is formed wide, and the brazed area between the side walls 1 and 2 at both ends and the casing 13 fitted thereto is secured. , Brazing reliability and strength are maintained.
As a result, deterioration of the heat exchanger due to the heat cycle is suppressed, and the durability of the heat exchanger is improved.
The invention according to claim 2 is formed in which the narrow width of the bulging portion 4 is formed into a plane triangular shape or a curved shape that becomes wider as it approaches the side walls 1 and 2. As a result, the concentration of thermal stress in the vicinity of the side wall is relaxed, so that a highly durable heat exchanger can be provided.
According to the third aspect of the present invention, the intersection angle θ of the brazed joint on the outer surface side of the bulging portion 4 of each flat tube 7 is formed at an obtuse angle. As a result, the flow of cooling water in the vicinity of the bulging portion 4 can be promoted, and the temperature rise at the tip portion of the flat tube 7 can be suppressed.

図１は本発明の熱交換器コアの要部平面図。
図２は図１のＩＩ−ＩＩ矢視断面図。
図３は同コアの斜視図。
図４は同コアを有する熱交換器の分解斜視図。
図５は従来型熱交換器コアの要部平面図。
図６は図５のＶＩ−ＶＩ矢視断面図。
図７は同従来型コアの斜視図。FIG. 1 is a plan view of a main part of the heat exchanger core of the present invention.
FIG. 2 is a cross-sectional view taken along the line II-II of FIG.
FIG. 3 is a perspective view of the core.
FIG. 4 is an exploded perspective view of a heat exchanger having the same core.
FIG. 5 is a plan view of a main part of the conventional heat exchanger core.
FIG. 6 is a sectional view taken along line VI-VI of FIG.
FIG. 7 is a perspective view of the conventional core.

次に、図面に基づいて本発明の実施の形態につき説明する。
この熱交換器は、ＥＧＲクーラや排熱回収器として最適なものである。これは、図４に示す如く、多数の偏平チューブ７を積層してコア１８を形成し、そのコア１８の外周をケーシング１３で被嵌する。そして、各偏平チューブ７の内面側に第一流体（この例では、排気ガス）１６を流通させ、その外面側に第二流体（この例では、冷却水）２０を流通させるものである。
各偏平チューブ７は、図１〜図３に示す如く、両側に一対の側壁１，２が立ち上げられ、全体が溝状に形成された一対のプレート５，６を互いに逆向きに対向して嵌着したものである。各プレート５，６の両開放側（偏平チューブ７の両開口端側に相当）の縁には、厚み方向外側に幅の狭い細幅の膨出部４が形成されている。
各偏平チューブ７の内部にはインナーフィン１９を挿入し、また、互いに接合される部品の少なくとも一方側にはろう材を被覆または塗布しておくことが好ましい。
一例として図４に示す如く、ケーシング１３内に積層されたコア１８が挿入される。この例では、ケーシング１３は箱状のケーシング本体１３ａと端蓋１３ｂにより形成されている。そして、コア１８の内部側に第一流体（排気ガス）１６が流通するようにケーシング１３の両端に一対の排気ガス用のパイプ１７を配し、コア１８の外面側に第二流体（冷却水）２０が流通するように冷却水用のパイプ１５を配する。そして、高温の炉内で各部品間を一体的にろう付して熱交換器を形成する。
そして、その偏平チューブ７に図２において矢印方向に第一流体（排気ガス）１６が供給される。
また、図４において、一方の水パイプ１５から第二流体（冷却水）２０が供給され、各偏平チューブ７の外面側にそれが導かれて、他方の水パイプ１５からそれが排出される。そして、その間に第一流体（排気ガス）１６と第二流体（冷却水）２０との間に熱交換が行われるものである。
（発明の特徴）
ここにおいて、本発明の特徴とするところは、図１及び図２に示す膨出部４の形状である。この膨出部４は、各プレート５，６の開放側において、厚み方向にプレス成形により膨出させたものである。この膨出部４は、その幅が図１において両端部で広く、それ以外で狭く形成されている。
即ち、中間部ではその幅狭部４ａが幅Ｌ１となり、両端部ではその幅広部４ｂが幅Ｌ２となる。ここに、Ｌ２＞Ｌ１である。図１に示すように、幅広部４ｂにおける幅は、その側壁１，２の両側に近づくほど広くなる平面三角、または平面が湾曲した形状とすることが好ましい。
（作用）
このような特徴により、第二流体（冷却水）２０との温度差が最も大きくなる各偏平チューブ７の膨出部４の中間部において、各偏平チューブ７の先端から第二流体（冷却水）２０までの距離が短くなり、その先端部と第二流体（冷却水）２０との伝熱が向上し、その間の温度差が抑制される。なお、前記両端部においては、前記膨出部４の細幅は広く形成されており、前記両端部における側壁１，２とそれらに被嵌されるケーシング１３とのろう付け面積は確保されるので、ろう付けの信頼性および強度は維持される。
さらに、この例では、幅広部４ｂにおける幅は、その側壁１，２の両側に近づくほど広くなる平面三角、または平面が湾曲した形状となっており、その形状変化がなだらかになっているので、側壁近傍の熱応力の集中が緩和される。
その結果、ヒートサイクルによる熱交換器の劣化が抑制され、熱交換器の耐久性が向上する。
また、図２に示されているように、積層された各偏平チューブ７の前記膨出部４の長手方向の中間部の位置で、ろう付接合部からそれを横断して外面側に広がる各プレート５，６の交角θを鈍角に形成することが好ましく、この形状にすることで、膨出部４の近傍の冷却水の流通を促進して、偏平チューブ７の先端部の温度上昇を抑えることができる。
本発明の効果を確認するために一例について数値解析を実施したところ、図５〜図７に示す従来型のコアの偏平チューブの先端部温度の最大値が３５８℃であったのに対し、本発明のコアの偏平チューブの先端部温度の最大値は２７５℃であり、大幅な温度低下効果が確認された。Next, an embodiment of the present invention will be described with reference to the drawings.
This heat exchanger is most suitable as an EGR cooler or an exhaust heat recovery device. As shown in FIG. 4, a large number of flat tubes 7 are laminated to form a core 18, and the outer periphery of the core 18 is fitted with a casing 13. Then, the first fluid (exhaust gas in this example) 16 is circulated on the inner surface side of each flat tube 7, and the second fluid (cooling water in this example) 20 is circulated on the outer surface side thereof.
As shown in FIGS. 1 to 3, each flat tube 7 has a pair of side walls 1 and 2 raised on both sides, and a pair of plates 5 and 6 formed in a groove shape as a whole facing each other in opposite directions. It is a fitted one. A narrow bulging portion 4 having a narrow width is formed on the edges of the plates 5 and 6 on both open sides (corresponding to both open end sides of the flat tube 7) on the outside in the thickness direction.
It is preferable that the inner fins 19 are inserted inside each flat tube 7, and that at least one side of the parts to be joined to each other is coated or coated with a brazing material.
As an example, as shown in FIG. 4, the laminated core 18 is inserted into the casing 13. In this example, the casing 13 is formed by a box-shaped casing main body 13a and an end lid 13b. Then, a pair of exhaust gas pipes 17 are arranged at both ends of the casing 13 so that the first fluid (exhaust gas) 16 flows on the inner side of the core 18, and the second fluid (cooling water) is arranged on the outer surface side of the core 18. ) Arrange the cooling water pipe 15 so that 20 can flow. Then, each component is brazed integrally in a high-temperature furnace to form a heat exchanger.
Then, the first fluid (exhaust gas) 16 is supplied to the flat tube 7 in the direction of the arrow in FIG.
Further, in FIG. 4, a second fluid (cooling water) 20 is supplied from one water pipe 15, is guided to the outer surface side of each flat tube 7, and is discharged from the other water pipe 15. In the meantime, heat exchange is performed between the first fluid (exhaust gas) 16 and the second fluid (cooling water) 20.
(Characteristics of Invention)
Here, the feature of the present invention is the shape of the bulging portion 4 shown in FIGS. 1 and 2. The bulging portion 4 is formed by press molding in the thickness direction on the open side of each of the plates 5 and 6. The width of the bulging portion 4 is wide at both ends in FIG. 1 and narrow at other ends.
That is, in the intermediate portion, the narrow portion 4a has a width L1, and at both ends, the wide portion 4b has a width L2. Here, L2> L1. As shown in FIG. 1, the width of the wide portion 4b is preferably a plane triangle that becomes wider toward both sides of the side walls 1 and 2, or a shape in which the plane is curved.
(Action)
Due to these characteristics, in the middle portion of the bulging portion 4 of each flat tube 7 where the temperature difference from the second fluid (cooling water) 20 is the largest, the second fluid (cooling water) is formed from the tip of each flat tube 7. The distance to 20 is shortened, the heat transfer between the tip end portion and the second fluid (cooling water) 20 is improved, and the temperature difference between them is suppressed. At both ends, the narrow width of the bulging portion 4 is formed to be wide, and the brazing area between the side walls 1 and 2 at both ends and the casing 13 fitted thereto is secured. , Brazing reliability and strength are maintained.
Further, in this example, the width of the wide portion 4b is a plane triangle that becomes wider toward both sides of the side walls 1 and 2, or a shape in which the plane is curved, and the shape change is gentle. The concentration of thermal stress near the side wall is relaxed.
As a result, deterioration of the heat exchanger due to the heat cycle is suppressed, and the durability of the heat exchanger is improved.
Further, as shown in FIG. 2, at the position of the intermediate portion in the longitudinal direction of the bulging portion 4 of each of the laminated flat tubes 7, each extending from the brazed joint portion across the brazing joint portion to the outer surface side. It is preferable to form the intersection angles θ of the plates 5 and 6 at an obtuse angle, and this shape promotes the flow of cooling water in the vicinity of the bulging portion 4 and suppresses the temperature rise at the tip portion of the flat tube 7. be able to.
When a numerical analysis was performed on an example to confirm the effect of the present invention, the maximum value of the tip temperature of the flat tube of the conventional core shown in FIGS. 5 to 7 was 358 ° C. The maximum value of the temperature at the tip of the flat tube of the core of the present invention was 275 ° C., and a significant temperature lowering effect was confirmed.

本発明は、ＥＧＲクーラとして最適であると共に、その他の熱交換器、例えば排熱回収器等に用いることができる。 The present invention is optimal as an EGR cooler and can be used in other heat exchangers such as an exhaust heat recovery device.

１，２ 側壁
３ 溝底
４ 膨出部
４ａ 幅狭部
４ｂ 幅広部
５，６ プレート
７ 偏平チューブ
８ 端部境界線
９ ディンプル
９ａ ディンプル
１０ 偏平チューブ
１１ 偏平チューブ
１１ａ 膨出部
１２ コア
１３ ケーシング
１３ａ ケーシング本体
１３ｂ 端蓋
１５ パイプ
１６ 第一流体（排気ガス）
１７ パイプ
１８ コア
１９ インナーフィン
２０ 第二流体（冷却水）
θ 交角
Ｌ１ 幅
Ｌ２ 幅1, 2 Side wall 3 Groove bottom 4 Protruding part 4a Narrow part 4b Wide part 5, 6 Plate 7 Flat tube 8 End boundary line 9 Dimple 9a Dimple 10 Flat tube 11 Flat tube 11a Protruding part 12 Core 13 Casing 13a Casing Main body 13b End lid 15 Pipe 16 First fluid (exhaust gas)
17 Pipe 18 Core 19 Inner Fin 20 Second fluid (cooling water)
θ cross angle L1 width L2 width

Claims (3)

それぞれ両側に一対の側壁（１）（２）が立上げられて全体が溝状に形成され且つ、その側壁に直交した溝底（３）の両開放側の縁に厚み方向外側に細幅の膨出部（４）が形成された一対のプレート（５）（６）を有し、それらのプレート（５）（６）が互いに逆向きに対向して嵌着されている偏平チューブ（７）と、
複数の偏平チューブ（７）が膨出部（４）で互いに積層され、各プレート（５）（６）が互いにろう付接合されている熱交換器コアと、を有し、
各偏平チューブの前記膨出部（４）の先端から第一流体（１６）が内部に流入し、その外側に第二流体（２０）が流通する熱交換器であって、
前記各プレート（５）（６）の前記膨出部（４）の細幅が、前記膨出部（４）の長手方向の両端部で広い幅広部（４ｂ）となり、それ以外の中間部で狭い幅狭部（４ａ）に形成されていることを特徴とするヘッダープレートレス型熱交換器。A pair of side walls (1) and (2) are erected on both sides to form a groove as a whole, and the edge of the groove bottom (3) orthogonal to the side wall is narrowed outward in the thickness direction. A flat tube (7) having a pair of plates (5) and (6) on which a bulge (4) is formed, and the plates (5) and (6) are fitted so as to face each other in opposite directions. When,
It has a heat exchanger core in which a plurality of flat tubes (7) are laminated together at a bulge (4) and each plate (5) (6) is brazed to each other.
A heat exchanger in which the first fluid (16) flows inward from the tip of the bulging portion (4) of each flat tube, and the second fluid (20) flows outside the first fluid (16).
The narrow width of the bulging portion (4) of each of the plates (5) and (6) becomes a wide wide portion (4b) at both ends in the longitudinal direction of the bulging portion (4), and in the other intermediate portions. A header plateless heat exchanger characterized in that it is formed in a narrow narrow portion (4a). 前記各プレート（５）（６）の前記膨出部（４）の細幅が、前記両端部では前記側壁（１）（２）に近づく程広くなる平面三角の、または平面が湾曲したろう付接合部を有することを特徴とする請求項１に記載のヘッダープレートレス型熱交換器。 The narrow width of the bulging portion (4) of each of the plates (5) and (6) becomes wider as it approaches the side walls (1) and (2) at both ends, and the flat triangular or curved brazing The header plateless heat exchanger according to claim 1, further comprising a joint. 積層された各偏平チューブ（７）の前記膨出部（４）の長手方向の中間部の位置で、ろう付接合部からそれを横断して外面側に広がる各プレート（５）（６）の交角θが、鈍角に形成されていることを特徴とする請求項１または請求項２に記載のヘッダープレートレス型熱交換器。 At the position of the intermediate portion in the longitudinal direction of the bulging portion (4) of each of the laminated flat tubes (7), of each plate (5) (6) extending from the brazed joint to the outer surface side across the brazing joint. The header plateless heat exchanger according to claim 1 or 2, wherein the intersection angle θ is formed at an obtuse angle.
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