JPH09310989A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JPH09310989A JPH09310989A JP8128738A JP12873896A JPH09310989A JP H09310989 A JPH09310989 A JP H09310989A JP 8128738 A JP8128738 A JP 8128738A JP 12873896 A JP12873896 A JP 12873896A JP H09310989 A JPH09310989 A JP H09310989A
- Authority
- JP
- Japan
- Prior art keywords
- heat transfer
- flat heat
- transfer tube
- flat
- heat exchanger
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
- F28D1/0391—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits a single plate being bent to form one or more conduits
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明に係る熱交換器は、自動
車用空気調和装置に組み込んで、コンプレッサから吐出
された高温、高圧の冷媒ガスを凝縮液化するコンデンサ
として利用する。BACKGROUND OF THE INVENTION The heat exchanger according to the present invention is incorporated in an air conditioner for an automobile and used as a condenser for condensing and liquefying a high temperature, high pressure refrigerant gas discharged from a compressor.
【０００２】[0002]
【従来の技術】自動車用空気調和装置を構成するコンデ
ンサとして、多数のフィンと伝熱管とによりコア部を構
成した熱交換器が知られている。この熱交換器は、図４
に示す様に、それぞれを水平方向に、且つ、上下方向に
亙り交互に配置した扁平伝熱管１、１とコルゲートフィ
ン２、２とから成るコア部３の左右両端部に、入口管５
を有する入口側ヘッダ６と出口管７を有する出口側ヘッ
ダ８とを設けて成る。又、上記コア部３の上下両端部に
は、このコア部３の補強を図ると共に、熱交換器を車体
に取り付けるのに利用する為のサイドサポート４、４を
設けている。2. Description of the Related Art A heat exchanger having a core portion composed of a large number of fins and heat transfer tubes is known as a condenser constituting an automobile air conditioner. This heat exchanger is shown in FIG.
As shown in FIG. 2, the inlet pipe 5 is provided at both left and right ends of the core portion 3 including the flat heat transfer tubes 1 and 1 and the corrugated fins 2 and 2 which are alternately arranged in the horizontal direction and in the vertical direction.
And an outlet side header 8 having an outlet pipe 7. Further, side supports 4 and 4 are provided at both upper and lower end portions of the core portion 3 so as to reinforce the core portion 3 and to be used for attaching the heat exchanger to the vehicle body.
【０００３】上述の様な熱交換器の使用時、入口管５か
ら入口側ヘッダ６に送り込まれ、扁平伝熱管１、１内を
流れる冷媒等の流体は、コア部３を構成する扁平伝熱管
１、１及びコルゲートフィン２、２の間を図４の表裏方
向に流通する空気との間で熱交換して冷却された後、出
口側ヘッダ８を介して出口管７から送り出される。When the heat exchanger as described above is used, a fluid such as a refrigerant sent from the inlet pipe 5 to the inlet side header 6 and flowing in the flat heat transfer pipes 1, 1 is a flat heat transfer pipe forming the core portion 3. After being cooled by exchanging heat between the air flowing in the front-back direction of FIG. 4 between the 1 and 1 and the corrugated fins 2 and 2, it is sent out from the outlet pipe 7 through the outlet-side header 8.
【０００４】上述の様な熱交換器の性能を向上させる為
には、扁平伝熱管１、１内を流れる冷媒等の流体の流れ
を乱すと共に、この流体と扁平伝熱管１、１との接触面
積を増大させる事が効果的である。又、各扁平伝熱管
１、１の耐圧強度を確保する為には、各扁平伝熱管１、
１を構成する上板部と下板部とを複数個所で互いに結合
する必要がある。この為、上記熱交換器を構成する扁平
伝熱管１、１の内側にインナーフィンを挿入し、このイ
ンナーフィンを上記上板部の下面及び下板部の上面にろ
う付け結合する構造が、従来から用いられている。In order to improve the performance of the heat exchanger as described above, the flow of a fluid such as a refrigerant flowing in the flat heat transfer tubes 1 and 1 is disturbed, and the fluid is brought into contact with the flat heat transfer tubes 1 and 1. It is effective to increase the area. Further, in order to ensure the pressure resistance of each flat heat transfer tube 1, 1, each flat heat transfer tube 1,
It is necessary to connect the upper plate portion and the lower plate portion that form 1 to each other at a plurality of locations. For this reason, the structure in which the inner fins are inserted inside the flat heat transfer tubes 1 and 1 constituting the heat exchanger and the inner fins are brazed to the lower surface of the upper plate portion and the upper surface of the lower plate portion is conventionally used. Used from.
【０００５】ところが、別々に造られたインナーフィン
と扁平伝熱管とを後から組み合わせる事は面倒で、熱交
換器のコストを高くする原因となる。この様な事情に鑑
みて実開平２−２８９８６号公報には、図５に示す様な
扁平伝熱管１ａが記載されている。この扁平伝熱管１ａ
は、上板部１８の下面及び下板部１６の上面の複数個所
で互いに整合する位置にそれぞれ突起９ａ、９ｂを形成
した素子１０ａ、１０ｂを、最中状に組み合わせ、両素
子１０ａ、１０ｂの当接面同士を互いにろう付け接合し
て成る。この様な扁平伝熱管１ａ内を流れる冷媒等の流
体は、上記突起９ａ、９ｂの存在によりその流れを乱さ
れる為、この流体と扁平伝熱管１ａとの間の熱交換効率
が向上する。又、上板部１８及び下板部１６に形成した
複数の突起９ａ、９ｂの先端面同士が互いにろう付け接
合される為、上記扁平伝熱管１ａ内の圧力上昇に拘ら
ず、上記上板部１８と下板部１６との間隔が広がる事が
ない。従って、上記扁平伝熱管１ａの耐圧強度を十分に
確保できる。However, it is troublesome to combine the separately prepared inner fins and the flat heat transfer tubes later, which causes the cost of the heat exchanger to be increased. In view of such circumstances, Japanese Utility Model Laid-Open No. 2-28986 discloses a flat heat transfer tube 1a as shown in FIG. This flat heat transfer tube 1a
Is a combination of elements 10a and 10b having protrusions 9a and 9b formed on the lower surface of the upper plate portion 18 and the upper surface of the lower plate portion 16 at positions aligned with each other, respectively, in the middle of the process. The contact surfaces are brazed to each other. The fluid such as the refrigerant flowing in the flat heat transfer tube 1a is disturbed by the presence of the projections 9a and 9b, so that the heat exchange efficiency between the fluid and the flat heat transfer tube 1a is improved. Further, since the tip surfaces of the plurality of projections 9a and 9b formed on the upper plate portion 18 and the lower plate portion 16 are brazed to each other, the upper plate portion is irrespective of the pressure increase in the flat heat transfer tube 1a. The distance between 18 and the lower plate portion 16 does not increase. Therefore, the pressure resistance of the flat heat transfer tube 1a can be sufficiently ensured.
【０００６】[0006]
【発明が解決しようとする課題】上述の様な構成による
扁平伝熱管１ａの場合、両素子１０ａ、１０ｂに複数の
突起９ａ、９ｂを形成している。この為、扁平伝熱管１
ａの上下両面に、それぞれ凹部１１ａ、１１ｂが形成さ
れる。このうち、扁平伝熱管１ａの上板部１８の上面に
形成された凹部１１ａ、１１ａの内側には、塵や水等の
異物が溜まり易い。この為、自動車の走行時に路上から
飛散した泥や融雪塩等の物質が上記凹部１１ａ、１１ａ
の内側に溜まり、上記扁平伝熱管１ａを腐食させて、熱
交換器の耐久性を損なう原因となる。In the case of the flat heat transfer tube 1a having the above-described structure, the plurality of protrusions 9a and 9b are formed on both the elements 10a and 10b. Therefore, the flat heat transfer tube 1
Recesses 11a and 11b are formed on the upper and lower surfaces of a, respectively. Of these, foreign matters such as dust and water easily accumulate inside the recesses 11a and 11a formed in the upper surface of the upper plate portion 18 of the flat heat transfer tube 1a. For this reason, substances such as mud and snow-melting salt scattered from the road when the automobile is running are liable to be recessed in the recesses 11a, 11a.
Will be accumulated inside and will corrode the flat heat transfer tube 1a, which will cause the durability of the heat exchanger to be impaired.
【０００７】又、図６に示す様に、上記扁平伝熱管１ａ
の上下両面で、上記各凹部１１ａ、１１ｂが形成された
位置では、この扁平伝熱管１ａの上下両面とコルゲート
フィン２の湾曲部１２、１２とが接触しない。この為、
接触していない分、扁平伝熱管１ａからコルゲートフィ
ン２への伝熱性が悪化し、熱交換器の放熱性能を低下さ
せてしまう。本発明の熱交換器は上述の様な事情に鑑み
て発明したものである。Further, as shown in FIG. 6, the flat heat transfer tube 1a is
The upper and lower surfaces of the flat heat transfer tube 1a and the curved portions 12, 12 of the corrugated fins 2 do not come into contact with each other at the positions where the recesses 11a and 11b are formed on the upper and lower surfaces of the corrugated fin 2. Therefore,
As much as they are not in contact with each other, heat transfer from the flat heat transfer tube 1a to the corrugated fins 2 deteriorates, and the heat dissipation performance of the heat exchanger deteriorates. The heat exchanger of the present invention was invented in view of the above circumstances.
【０００８】[0008]
【課題を解決する為の手段】本発明の熱交換器は、前述
した従来の熱交換器と同様に、水平方向に間隔をあけて
配置された左右１対のヘッダと、上下方向に互いに間隔
をあけてそれぞれ水平方向に配設され、それぞれの両端
開口を上記各ヘッダ内に通じさせた複数本の扁平伝熱管
と、上下に隣り合う扁平伝熱管同士の間に設けられた複
数のコルゲートフィンとを備える。特に、本発明の熱交
換器に於いては、上記各扁平伝熱管を構成する上板部と
下板部とのうち、上板部は全面に亙って平坦であり、下
板部の上面には上記上板部の下面に向けて突出する多数
の突起を形成して、これら各突起の先端面と上記上板部
の下面とを互いにろう付けしている。The heat exchanger of the present invention, like the above-mentioned conventional heat exchanger, has a pair of left and right headers horizontally spaced from each other and vertically spaced from each other. A plurality of flat heat transfer tubes which are respectively arranged in the horizontal direction and have both end openings communicating with the headers, and a plurality of corrugated fins provided between vertically adjacent flat heat transfer tubes. With. In particular, in the heat exchanger of the present invention, among the upper plate portion and the lower plate portion that constitute each of the flat heat transfer tubes, the upper plate portion is flat over the entire surface, and the upper surface of the lower plate portion is Is formed with a large number of protrusions protruding toward the lower surface of the upper plate portion, and the tip surfaces of these protrusions and the lower surface of the upper plate portion are brazed to each other.
【０００９】[0009]
【作用】上述の様に構成される本発明の熱交換器の場
合、扁平伝熱管の下板部上面に形成された多数の突起
が、この扁平伝熱管の内側面に沿って流れる流体を撹乱
すると共に、この流体を扁平伝熱管の内側面との接触面
積を増大させる。従って、上記流体と扁平伝熱管との間
の熱交換性能を高める事ができる。又、上記多数の突起
が、上記扁平伝熱管を構成する上板部と下板部とが離れ
る事を防止して、この扁平伝熱管の耐圧性を向上させ
る。又、本発明の熱交換器の場合、上記扁平伝熱管の上
板部は全面に亙り平坦である為、自動車の走行時に路上
から飛散した泥や融雪塩等の扁平伝熱管を腐食させる物
質が、上記上板部上面に溜まりにくい。更に、扁平伝熱
管の上板部が全面に亙り平坦である為、この上板部の上
面とコルゲートフィンの湾曲部との接触面積を十分に確
保できる。この結果、上記扁平伝熱管とコルゲートフィ
ンとの間の伝熱性が向上し、熱交換器全体としての放熱
性能を向上させる事ができる。In the heat exchanger of the present invention configured as described above, a large number of protrusions formed on the upper surface of the lower plate of the flat heat transfer tube disturb the fluid flowing along the inner surface of the flat heat transfer tube. In addition, the contact area of this fluid with the inner surface of the flat heat transfer tube is increased. Therefore, the heat exchange performance between the fluid and the flat heat transfer tube can be enhanced. Further, the large number of protrusions prevent the upper plate portion and the lower plate portion of the flat heat transfer tube from separating from each other, thereby improving the pressure resistance of the flat heat transfer tube. Further, in the case of the heat exchanger of the present invention, since the upper plate portion of the flat heat transfer tube is flat over the entire surface, there is a substance that corrodes the flat heat transfer tube such as mud or snow melting salt scattered from the road when the vehicle is running. , It is hard to collect on the upper surface of the upper plate portion. Further, since the upper plate of the flat heat transfer tube is flat over the entire surface, a sufficient contact area between the upper surface of the upper plate and the curved portion of the corrugated fin can be secured. As a result, the heat transfer between the flat heat transfer tube and the corrugated fin is improved, and the heat dissipation performance of the heat exchanger as a whole can be improved.
【００１０】[0010]
【実施例】図１〜３は本発明の実施の形態の１例を示し
ている。尚、本発明の特徴は、コルゲートフィン２と共
にコア部３（図４参照）を構成する扁平伝熱管１５の構
造及び作用にある。その他の部分の構造及び作用は、前
述した従来構造と同様であるから、重複する説明を省略
若しくは簡略にし、以下、本発明の特徴部分を中心に説
明する。1 to 3 show an example of an embodiment of the present invention. The feature of the present invention lies in the structure and operation of the flat heat transfer tube 15 that constitutes the core portion 3 (see FIG. 4) together with the corrugated fins 2. Since the structure and operation of the other parts are the same as those of the conventional structure described above, redundant description will be omitted or simplified, and the characteristic part of the present invention will be mainly described below.
【００１１】本発明の熱交換器に組み込まれる扁平伝熱
管１５は、アルミニウム合金製で帯状の板材１３をロー
ル成形して成る。即ち、ロール成形に伴って上記板材１
３の幅方向両端縁に接合部１４ａ、１４ｂを、この板材
１３の全長に亙って形成した後、これら両接合部１４
ａ、１４ｂ同士を互いに突き合わせてろう付けする事に
より、扁平伝熱管１５としている。The flat heat transfer tube 15 incorporated in the heat exchanger of the present invention is formed by roll-forming a strip-shaped plate material 13 made of an aluminum alloy. That is, the above-mentioned plate material 1 is accompanied by roll forming.
After the joint portions 14a and 14b are formed on both end edges in the width direction of 3 over the entire length of the plate member 13, both joint portions 14 are formed.
The flat heat transfer tube 15 is formed by abutting and brazing the a and 14b against each other.
【００１２】尚、上記接合部１４ａ、１４ｂ同士のろう
付けは、この扁平伝熱管１５と共に熱交換器を構成する
部材同士のろう付けと同時に行なう。この為に、上記板
材１３は、芯材の両面にろう材を積層した、所謂両面ク
ラッド材を使用する。又、この扁平伝熱管１５を構成す
る下板部１６の上面には、上記板材１３に上述したロー
ル成形を施す事により、多数の突起１７、１７を形成し
ている。これら各突起１７、１７は、図２に示す様に、
この扁平伝熱管１５の軸方向に亙る平行流路を形成しな
い様に、上記下板部１６に千鳥配置している。そして、
これら各突起１７、１７の上端面は、上記扁平伝熱管１
５の上板部１８の下面に突き当てて、突き当て部をろう
付け接合している。勿論、このろう付けも、熱交換器の
構成各部品同士のろう付けと同時に行なう。The brazing of the joints 14a and 14b is performed at the same time as the brazing of the members constituting the heat exchanger with the flat heat transfer tube 15. Therefore, the plate material 13 is a so-called double-sided clad material in which a brazing material is laminated on both surfaces of a core material. Further, a large number of protrusions 17 and 17 are formed on the upper surface of the lower plate portion 16 constituting the flat heat transfer tube 15 by performing the above-described roll forming on the plate material 13. As shown in FIG. 2, each of these protrusions 17, 17 is
The flat heat transfer tubes 15 are arranged in a staggered manner on the lower plate portion 16 so as not to form parallel flow paths extending in the axial direction. And
The upper end surface of each of these protrusions 17 and 17 has the flat heat transfer tube 1 described above.
5 is abutted against the lower surface of the upper plate portion 18, and the abutted portion is brazed and joined. Of course, this brazing is also performed at the same time as brazing the constituent parts of the heat exchanger.
【００１３】上述の様な扁平伝熱管１５を組み込んだ本
発明の熱交換器の使用時、この扁平伝熱管１５内に冷媒
等の流体を流通させると、この流体が上記各突起１７、
１７により流れを乱されると共に、この流体と上記扁平
伝熱管１５の内側面との接触面積が増大する。この為、
上記流体と上記扁平伝熱管１５との間の伝熱効率が向上
して、この扁平伝熱管１５を組み込んだ熱交換器の放熱
性能を高める事ができる。又、上記各突起１７、１７
が、前記下板部１６と上板部１８とが離れる事を防止し
て、上記扁平伝熱管１５の耐圧強度を確保する。When a heat exchanger of the present invention incorporating the flat heat transfer tube 15 as described above is used, when a fluid such as a refrigerant is circulated in the flat heat transfer tube 15, this fluid causes the projections 17,
The flow is disturbed by 17, and the contact area between this fluid and the inner surface of the flat heat transfer tube 15 increases. Therefore,
The heat transfer efficiency between the fluid and the flat heat transfer tube 15 is improved, and the heat dissipation performance of the heat exchanger incorporating the flat heat transfer tube 15 can be improved. In addition, each of the above-mentioned protrusions 17, 17
However, the lower plate portion 16 and the upper plate portion 18 are prevented from separating from each other, and the pressure resistance of the flat heat transfer tube 15 is secured.
【００１４】又、上記扁平伝熱管１５の下板部１６の下
面には、この下板部１６の上面に上記各突起１７、１７
を形成するのに伴って凹部１９、１９が形成されるが、
上記扁平伝熱管１５の上板部１８の上面は平坦面のまま
である。従って、自動車の走行時に路上から飛散した泥
や融雪塩等の上記扁平伝熱管１５を腐食させる物質が、
上記上板部１８の上面に溜まりにくい。この結果、上記
扁平伝熱管１５の耐食性を十分に確保できる。On the lower surface of the lower plate portion 16 of the flat heat transfer tube 15, the projections 17 and 17 are formed on the upper surface of the lower plate portion 16.
The concave portions 19 and 19 are formed along with the formation of
The upper surface of the upper plate portion 18 of the flat heat transfer tube 15 remains a flat surface. Therefore, a substance that corrodes the flat heat transfer tube 15 such as mud or snow melting salt scattered from the road when the vehicle is running is
It is hard to collect on the upper surface of the upper plate portion 18. As a result, the corrosion resistance of the flat heat transfer tube 15 can be sufficiently ensured.
【００１５】更に、図３に示す様に、上記扁平伝熱管１
５の上下両面と前記コルゲートフィン（図４参照）の湾
曲部１２、１２との接触部分に就いては、上記扁平伝熱
管１５の上板部１８の上面部分で、十分な接触面積が確
保できる。この為、これら扁平伝熱管１５とコルゲート
フィン２との間の伝熱性を確保して、これら両部材１
５、２を組み込んだ熱交換器の性能を向上させる事がで
きる。Further, as shown in FIG. 3, the flat heat transfer tube 1 is used.
Regarding the contact portions between the upper and lower surfaces of 5 and the curved portions 12, 12 of the corrugated fins (see FIG. 4), a sufficient contact area can be secured at the upper surface portion of the upper plate portion 18 of the flat heat transfer tube 15. . Therefore, heat transfer between the flat heat transfer tubes 15 and the corrugated fins 2 is ensured, and both members 1
It is possible to improve the performance of the heat exchanger incorporating the elements 5 and 2.
【００１６】[0016]
【発明の効果】本発明の熱交換器は以上に述べた様に構
成され作用する為、扁平伝熱管の耐食性を低下させる事
なく、扁平伝熱管内を流れる流体と扁平伝熱管との間の
伝熱効率の向上と、扁平伝熱管の耐圧性確保とを図れる
だけでなく、扁平伝熱管とコルゲートフィンとの間の伝
熱性能を向上させる事もできる。この為、優れた耐久性
及び熱交換性能を有する熱交換器を実現できる。Since the heat exchanger of the present invention is constructed and operates as described above, the heat exchange between the fluid flowing in the flat heat transfer tube and the flat heat transfer tube can be performed without lowering the corrosion resistance of the flat heat transfer tube. Not only can the heat transfer efficiency be improved and the pressure resistance of the flat heat transfer tube can be secured, but also the heat transfer performance between the flat heat transfer tube and the corrugated fins can be improved. Therefore, a heat exchanger having excellent durability and heat exchange performance can be realized.
【図１】本発明の実施の形態の１例を示す、扁平伝熱管
の一部を上方から見た斜視図。FIG. 1 is a perspective view showing a part of a flat heat transfer tube as seen from above, showing an example of an embodiment of the present invention.
【図２】同じく下方から見た斜視図。FIG. 2 is a perspective view of the same seen from below.
【図３】本発明の熱交換器に於けるコア部の略部分縦断
面図。FIG. 3 is a schematic partial vertical cross-sectional view of a core portion in the heat exchanger of the present invention.
【図４】従来から知られている熱交換器の１例を示す略
斜視図。FIG. 4 is a schematic perspective view showing an example of a conventionally known heat exchanger.
【図５】従来から知られている扁平伝熱管の１例を示す
部分斜視図。FIG. 5 is a partial perspective view showing an example of a conventionally known flat heat transfer tube.
【図６】従来品に於ける、図３と同様の図。FIG. 6 is a view similar to FIG. 3 in the conventional product.
１、１ａ 扁平伝熱管 ２ コルゲートフィン ３ コア部 ４ サイドサポート ５ 入口管 ６ 入口側ヘッダ ７ 出口管 ８ 出口側ヘッダ ９ａ、９ｂ 突起 １０ａ、１０ｂ 素子 １１ａ、１１ｂ 凹部 １２ 湾曲部 １３ 板材 １４ａ、１４ｂ 接合部 １５ 扁平伝熱管 １６ 下板部 １７ 突起 １８ 上板部 １９ 凹部 1, 1a Flat heat transfer tube 2 Corrugated fins 3 Core part 4 Side support 5 Inlet tube 6 Inlet side header 7 Outlet tube 8 Outlet side header 9a, 9b Protrusion 10a, 10b Element 11a, 11b Recess 12 Curved portion 13 Plate material 14a, 14b Joint part 15 Flat Heat Transfer Tube 16 Lower Plate 17 Protrusion 18 Upper Plate 19 Recess
Claims (1)
１対のヘッダと、上下方向に互いに間隔をあけてそれぞ
れ水平方向に配設され、それぞれの両端開口を上記各ヘ
ッダ内に通じさせた複数本の扁平伝熱管と、上下に隣り
合う扁平伝熱管同士の間に設けられた複数のコルゲート
フィンとを備えた熱交換器に於いて、上記各扁平伝熱管
を構成する上板部と下板部とのうち、上板部は全面に亙
って平坦であり、下板部の上面には上記上板部の下面に
向けて突出する多数の突起が形成されて、これら各突起
の先端面と上記上板部の下面とが互いにろう付けされて
いる事を特徴とする熱交換器。1. A pair of left and right headers horizontally spaced apart from each other, and a pair of headers horizontally spaced apart vertically from each other, and opening both ends of each header into the respective headers. In a heat exchanger comprising a plurality of flat heat transfer tubes and a plurality of corrugated fins provided between vertically adjacent flat heat transfer tubes, an upper plate portion constituting each of the flat heat transfer tubes, Of the lower plate part, the upper plate part is flat over the entire surface, and a large number of projections projecting toward the lower surface of the upper plate part are formed on the upper surface of the lower plate part. A heat exchanger characterized in that a tip surface and a lower surface of the upper plate portion are brazed to each other.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8128738A JPH09310989A (en) | 1996-05-23 | 1996-05-23 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8128738A JPH09310989A (en) | 1996-05-23 | 1996-05-23 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09310989A true JPH09310989A (en) | 1997-12-02 |
Family
ID=14992243
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8128738A Pending JPH09310989A (en) | 1996-05-23 | 1996-05-23 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09310989A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010107147A (en) * | 2008-10-31 | 2010-05-13 | Showa Denko Kk | Heat exchanger and method of manufacturing the same |
| DE102019106012A1 (en) * | 2019-03-08 | 2020-09-10 | Mahle International Gmbh | Heat exchanger arrangement and heat exchanger |
| EP3677865A4 (en) * | 2017-09-22 | 2021-06-02 | Zhejiang Dunan Artificial Environment Co., Ltd. | Flat tube for microchannel heat exchanger, and microchannel heat exchanger |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5997377U (en) * | 1982-12-15 | 1984-07-02 | 日産自動車株式会社 | Heat exchanger liquid pipe structure |
| JPH0228986U (en) * | 1988-08-12 | 1990-02-23 | ||
| JPH0321683U (en) * | 1989-07-03 | 1991-03-05 | ||
| JPH03155422A (en) * | 1989-11-14 | 1991-07-03 | Calsonic Corp | Heat transfer tube for heat exchanger and its manufacturing method |
| JPH049593A (en) * | 1990-04-26 | 1992-01-14 | Showa Alum Corp | Heat exchanger |
| JPH0719774A (en) * | 1993-06-30 | 1995-01-20 | Zexel Corp | Flat tube of heat exchanger |
-
1996
- 1996-05-23 JP JP8128738A patent/JPH09310989A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5997377U (en) * | 1982-12-15 | 1984-07-02 | 日産自動車株式会社 | Heat exchanger liquid pipe structure |
| JPH0228986U (en) * | 1988-08-12 | 1990-02-23 | ||
| JPH0321683U (en) * | 1989-07-03 | 1991-03-05 | ||
| JPH03155422A (en) * | 1989-11-14 | 1991-07-03 | Calsonic Corp | Heat transfer tube for heat exchanger and its manufacturing method |
| JPH049593A (en) * | 1990-04-26 | 1992-01-14 | Showa Alum Corp | Heat exchanger |
| JPH0719774A (en) * | 1993-06-30 | 1995-01-20 | Zexel Corp | Flat tube of heat exchanger |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010107147A (en) * | 2008-10-31 | 2010-05-13 | Showa Denko Kk | Heat exchanger and method of manufacturing the same |
| EP3677865A4 (en) * | 2017-09-22 | 2021-06-02 | Zhejiang Dunan Artificial Environment Co., Ltd. | Flat tube for microchannel heat exchanger, and microchannel heat exchanger |
| DE102019106012A1 (en) * | 2019-03-08 | 2020-09-10 | Mahle International Gmbh | Heat exchanger arrangement and heat exchanger |
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