JPH06129734A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JPH06129734A JPH06129734A JP4277491A JP27749192A JPH06129734A JP H06129734 A JPH06129734 A JP H06129734A JP 4277491 A JP4277491 A JP 4277491A JP 27749192 A JP27749192 A JP 27749192A JP H06129734 A JPH06129734 A JP H06129734A
- Authority
- JP
- Japan
- Prior art keywords
- tube
- refrigerant
- heat exchange
- heat exchanger
- flat
- 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
- 239000003507 refrigerant Substances 0.000 claims abstract description 44
- 238000004891 communication Methods 0.000 claims abstract description 16
- 230000003014 reinforcing effect Effects 0.000 claims description 22
- 230000000694 effects Effects 0.000 abstract description 2
- 238000005219 brazing Methods 0.000 description 8
- 229910052782 aluminium Inorganic materials 0.000 description 7
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 7
- 238000000034 method Methods 0.000 description 4
- 238000012937 correction Methods 0.000 description 3
- 238000003780 insertion Methods 0.000 description 2
- 230000037431 insertion Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000000638 solvent extraction Methods 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
Classifications
-
- 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
-
- 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
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
-
- 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
- F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
- F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
(57)【要約】
【構成】 熱交換用偏平チューブ１内に波型インナーフ
ィン２が配置され、チューブ１の対向平面壁１ａ、１ａ
同士ががインナーフィン２にて連結され、該インナーフ
ィン２に、該フィン２にて仕切られた隣り合う冷媒通路
１０、１０同士を連通する複数個の連通孔９…が分散状
態に設けられている。
【効果】 チューブ１内を流通する冷媒を効率良く凝縮
することができると共に、冷媒の圧力損失も低く抑える
ことができる。
(57) [Summary] [Structure] The corrugated inner fins 2 are arranged in the flat tube 1 for heat exchange, and the opposed flat walls 1a, 1a of the tube 1 are arranged.
The inner fins 2 are connected to each other, and the inner fin 2 is provided with a plurality of communication holes 9 ... Which communicate with adjacent refrigerant passages 10 partitioned by the fins 2 in a dispersed state. There is. [Effect] The refrigerant flowing through the tube 1 can be efficiently condensed, and the pressure loss of the refrigerant can be suppressed low.
Description
【０００１】[0001]
【産業上の利用分野】この発明は、カークーラーやルー
ムエアコンの凝縮器等に用いられるアルミニウム等の金
属製熱交換器に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger made of metal such as aluminum used for a car cooler, a condenser of a room air conditioner and the like.
【０００２】[0002]
【従来の技術】近時、例えばカークーラー用凝縮器とし
て、並列状態に配置された複数本の熱交換器用チューブ
の両端に一対の中空ヘッダーが連通状態に接続されると
共に、チューブ間に熱交換用のコルゲートフィンが配置
された構造の、マルチフローないしはパラレルフロータ
イプと称される熱交換器が、高熱交換性能、低圧力損
失、超コンパクト化を実現しうるものとして、好んで使
用される傾向にある。2. Description of the Related Art Recently, for example, as a condenser for a car cooler, a pair of hollow headers are connected to both ends of a plurality of heat exchanger tubes arranged in parallel, and heat exchange is performed between the tubes. A heat exchanger called a multi-flow or parallel-flow type, in which corrugated fins are arranged, is favorably used as a heat exchanger that can achieve high heat exchange performance, low pressure loss, and ultra compactness. It is in.
【０００３】そして、従来、上記熱交換用チューブとし
て、耐圧性能の向上及び伝熱面積の拡大などを目的とし
て、例えば、第６図に示されるように、横断面長円状の
偏平チューブ（51）内に波型のインナーフィン（52）が
配置され、該フィン（52）がチューブ（51）の上下の壁
（51a ）（51a ）にろう付けにより接合一体化された構
造を有するものが用いられることがあった。Conventionally, as the heat exchange tube, for the purpose of improving the pressure resistance performance and expanding the heat transfer area, for example, as shown in FIG. 6, a flat tube (51) having an oval cross section. ) In which a corrugated inner fin (52) is disposed, and the fin (52) is joined to the upper and lower walls (51a) (51a) of the tube (51) by brazing to be integrated. I was sometimes told.
【０００４】あるいはまた、第７図に示されるように、
横断面長円状の偏平チューブ（61）内にマルチエントリ
型のインナーフィン（62）が配置され、該フィン（62）
がチューブ（61）の上下の壁（61a ）（61a ）にろう付
けにより接合一体化された構造を有するものが用いられ
ることもあった。Alternatively, as shown in FIG.
A multi-entry type inner fin (62) is arranged in a flat tube (61) having an oval cross section.
In some cases, a tube having a structure in which the upper and lower walls (61a) (61a) of the tube (61) are joined and integrated by brazing is used.
【０００５】[0005]
【発明が解決しようとする課題】しかしながら、波型の
インナーフィン（52）を使用したチューブ（51）では、
チューブ（51）内がその幅方向に複数の冷媒通路（53）
…に完全に仕切られてしまい、チューブ幅方向の風上側
の冷媒通路を流通される冷媒は活発に凝縮されるもの
の、風下側の冷媒通路を流通する冷媒は凝縮されにく
く、そのため、熱交換が効率良く行われないという問題
があった。However, in the tube (51) using the corrugated inner fin (52),
Inside the tube (51) are a plurality of refrigerant passages (53) in the width direction.
Since the refrigerant is completely partitioned into ... And the refrigerant flowing through the refrigerant passage on the windward side in the tube width direction is actively condensed, the refrigerant flowing through the refrigerant passage on the leeward side is less likely to be condensed, so that heat exchange There was a problem that it was not done efficiently.
【０００６】また、マルチエントリ型のインナーフィン
（62）を内部に配したチューブ（61）では、冷媒の内部
撹拌作用によりチューブ（61）の幅方向にも冷媒の行来
を生じ、そのため、上記のような欠点はないが、反面、
内部を流通する冷媒の流通抵抗が非常に大きなものとな
って、熱交換器の圧力損失が大きなものになってしまう
という問題があった。Further, in the tube (61) having the multi-entry type inner fins (62) arranged therein, the internal stirring action of the refrigerant causes the refrigerant to come and go in the width direction of the tube (61). There is no such drawback, but on the other hand,
There is a problem that the flow resistance of the refrigerant flowing inside becomes very large, and the pressure loss of the heat exchanger becomes large.
【０００７】この発明は、上記のような従来の欠点を解
消し、チューブ内を流通する熱交換媒体の熱交換効率の
向上、及び圧力損失の低減を調和良く実現することが可
能な熱交換器を提供することを目的とする。The present invention eliminates the above-mentioned conventional drawbacks and improves the heat exchange efficiency of the heat exchange medium flowing through the tube and reduces the pressure loss in a harmony manner. The purpose is to provide.
【０００８】[0008]
【課題を解決するための手段】上記目的において、この
発明は、熱交換用偏平チューブの対向平面壁同士が、長
さ方向に延びる補強壁によりチューブ内において連結さ
れた熱交換器において、該補強壁に、補強壁にて仕切ら
れた隣り合う冷媒通路同士を連通する複数個の連通孔が
分散状態に設けられてなることを特徴とする熱交換器を
要旨とする。To achieve the above object, the present invention provides a heat exchanger in which opposed flat walls of a flat tube for heat exchange are connected in a tube by reinforcing walls extending in a longitudinal direction. A gist of a heat exchanger is characterized in that a plurality of communication holes communicating with adjacent refrigerant passages partitioned by a reinforcing wall are provided on a wall in a dispersed state.
【０００９】この熱交換器において、補強壁のチューブ
幅方向における形成ピッチは、熱交換性能を高いものに
しつつつ圧力損失を低く抑える目的、本来の耐圧という
目的等において、１．０〜５．０ｍｍの範囲、特に１．
５〜３．０ｍｍの範囲において設定されるのが好まし
い。In this heat exchanger, the forming pitch of the reinforcing wall in the width direction of the tube is 1.0 to 5 for the purpose of keeping pressure loss low while keeping the heat exchange performance high, and the original pressure resistance. 0 mm range, especially 1.
It is preferably set in the range of 5 to 3.0 mm.
【００１０】また、補強壁の高さは、熱交換性能を高い
ものにしつつつ圧力損失を低く抑える目的等において、
０．５〜２．５ｍｍの範囲、特に１．０〜２．０ｍｍの
範囲において設定されるのが好ましい。The height of the reinforcing wall is such that the heat exchange performance is high and the pressure loss is low.
It is preferably set in the range of 0.5 to 2.5 mm, particularly 1.0 to 2.0 mm.
【００１１】更に、連通孔の断面積は、熱交換性能を高
いものにしつつつ圧力損失を低く抑える目的、各冷媒通
路間の冷媒の有効な行来の実現を図る目的、耐圧という
本来の目的等において、０．１５〜１．５ｍｍ2 の範
囲、特に０．５〜１．２５ｍｍ2 の範囲に設定されるの
が好ましい。Further, the cross-sectional area of the communication hole is to achieve high heat exchange performance while keeping pressure loss low, to achieve effective passage of the refrigerant between the refrigerant passages, and to achieve the original purpose of pressure resistance. in such a range of 0.15～1.5Mm 2, in particular being set in a range of 0.5～1.25Mm 2 preferred.
【００１２】また、連通孔の形成ピッチは、同様に熱交
換性能を高いものにしつつつ圧力損失を低く抑える目
的、各冷媒通路間の冷媒の有効な行来の実現を図る目
的、耐圧という本来の目的等において、２．０〜１０．
０ｍｍに設定されるのが好ましい。Further, the pitch of the communication holes is likewise intended to increase the heat exchange performance while keeping the pressure loss low, to achieve the effective passage of the refrigerant between the refrigerant passages, and to withstand pressure. In the purpose etc. of 2.0-10.
It is preferably set to 0 mm.
【００１３】[0013]
【作用】上記構成では、熱交換中、チューブ内を流通す
る冷媒は、連通孔を通じて、チューブ幅方向に行来され
る。そのため、チューブ内を流通される冷媒と熱交換器
を前後方向に流通される空気等との熱交換が効率良く行
われる。In the above structure, during heat exchange, the refrigerant flowing in the tube comes in the tube width direction through the communication hole. Therefore, the heat exchange between the refrigerant flowing in the tube and the air flowing in the heat exchanger in the front-rear direction is efficiently performed.
【００１４】しかも、補強壁はチューブの長さ方向に延
ばされ、かつ、このような補強壁に連通孔が形成された
ものであることにより、冷媒は、チューブ内において、
大きく撹拌されることなく、スムーズに流通していく。
従って、チューブ内を流通する冷媒の圧力損失が大きく
なることもない。Moreover, since the reinforcing wall is extended in the length direction of the tube, and the communication hole is formed in such a reinforcing wall, the refrigerant is allowed to flow in the tube.
It flows smoothly without being greatly stirred.
Therefore, the pressure loss of the refrigerant flowing through the tube does not increase.
【００１５】[0015]
【実施例】次に、この発明を、マルチフロータイプのカ
ークーラー用アルミニウム製凝縮器に適用した実施例に
ついて説明する。EXAMPLES Next, examples in which the present invention is applied to a multi-flow type aluminum condenser for car coolers will be described.
【００１６】なお、本発明は、ルームエアコン用熱交換
器等の各種用途の熱交換器や、各種タイプの熱交換器に
広く適用されうるものであることはいうまでもない。Needless to say, the present invention can be widely applied to heat exchangers for various uses such as heat exchangers for room air conditioners and various types of heat exchangers.
【００１７】第１図ないし第３図に示される熱交換器に
おいて、（１）…は熱交換用偏平チューブで、所定長さ
のものが複数本用意され、これらが所定の所定間隔おき
に並列状態に配置されている。（２）は補強用インナー
フィンで、各チューブ（１）…内に配置され、該チュー
ブ（１）の上下の平面壁（1a）（1a）を連結する補強壁
を構成している。（３）（３）は中空ヘッダーで、上記
チューブ（１）…の両端部に連通状態に接続されてい
る。（４）は冷媒入口管、（５）は同出口管で、それぞ
れヘッダー（３）（３）に連通接続されている。（６）
…は仕切部材で、ヘッダー（３）（３）内を所定高さ位
置において上下の室に仕切り、冷媒が上記チューブ
（１）…群を蛇行状に流通するようになされている。な
お、（７）は熱交換用フィンで、チューブ（１）…間に
配置されている。In the heat exchangers shown in FIGS. 1 to 3, (1) ... are flat tubes for heat exchange, a plurality of flat tubes having a predetermined length are prepared, and these tubes are arranged in parallel at predetermined predetermined intervals. It is arranged in a state. (2) is a reinforcing inner fin, which is arranged in each tube (1) ... and constitutes a reinforcing wall that connects the upper and lower flat walls (1a) (1a) of the tube (1). (3) (3) is a hollow header, which is connected to both ends of the tubes (1). Reference numeral (4) is a refrigerant inlet pipe, and (5) is the outlet pipe, which are connected to the headers (3) and (3), respectively. (6)
Is a partitioning member that partitions the headers (3) and (3) into upper and lower chambers at predetermined height positions so that the refrigerant circulates in the tube (1) group in a meandering manner. The heat exchange fins (7) are arranged between the tubes (1).
【００１８】偏平チューブ（１）は、第１図に示される
ように、横断面長円状をしたアルミニウムブレージング
シート製の電縫管によるもので、その一側縁が電縫溶接
されたものである。As shown in FIG. 1, the flat tube (1) is made of an electric braided tube made of an aluminum brazing sheet having an oval cross section, and one side edge of which is electric welded. is there.
【００１９】補強用インナーフィン（２）は、偏平チュ
ーブ（１）の耐圧強度を増すと共に、冷媒側の伝熱面積
を増加して熱交換性能を向上するものである。即ち、こ
のインナーフィン（２）は、アルミニウムシートを波形
に成形した波型フィンによるもので、これが、波の山の
長さ方向をチューブ（１）の長さ方向に向けた状態に、
上記偏平チューブ（１）内に配置され、その表裏各山部
の先端がチューブ（１）の上下の平面壁（1a）（1a）に
ろう付けにより接合一体化されて、両平面壁（1a）（1
a）同士がインナーフィン（２）にて連結されたものと
なされている。The reinforcing inner fins (2) increase the pressure resistance of the flat tube (1) and increase the heat transfer area on the refrigerant side to improve the heat exchange performance. That is, the inner fin (2) is a corrugated fin formed by corrugating an aluminum sheet, and when the length direction of the wave crest is oriented in the length direction of the tube (1),
The flat tubes (1) are arranged in the flat tube (1), and the tips of the front and back crests are brazed to the upper and lower flat walls (1a) (1a) of the tube (1) so that both flat walls (1a). (1
a) The inner fins (2) are connected to each other.
【００２０】そして、チューブ（１）内において、イン
ナーフィン（２）の各立ち上がり壁（2a）…には、その
長さ方向に沿って所定間隔おきに分散状態に多数の連通
孔（９）…が設けられ、この連通孔（９）…を通じて、
インナーフィン（２）にて仕切られたチューブ（１）内
の長さ方向に延びる互いに独立した複数の冷媒通路（1
0）…同士が、冷媒の流通を許容するように、互いに連
通されたものとなされている。In the tube (1), each rising wall (2a) of the inner fin (2) has a large number of communicating holes (9) in a dispersed state at predetermined intervals along the lengthwise direction thereof. Is provided, and through this communication hole (9) ...
A plurality of independent refrigerant passages (1) extending in the length direction in the tube (1) partitioned by the inner fins (2)
0) ... are communicated with each other so as to allow the circulation of the refrigerant.
【００２１】インナーフィン（２）の波のピッチＰは
１．０〜５．０ｍｍの範囲、特に１．５〜３．０ｍｍの
範囲、高さＨは０．５〜２．５ｍｍの範囲、特に１．０
〜２．０ｍｍの範囲において設定されるのが好ましく、
また、各連通孔（９）の横断面積ａは、０．１５〜１．
５ｍｍ2 の範囲、特に０．５〜１．２５ｍｍ2 の範囲の
範囲、穿孔ピッチｐは２．０〜１０．０ｍｍの範囲にお
いて設定されるのが好ましい。The wave pitch P of the inner fin (2) is in the range of 1.0 to 5.0 mm, especially in the range of 1.5 to 3.0 mm, and the height H is in the range of 0.5 to 2.5 mm, especially 1.0
Is preferably set in the range of ~ 2.0 mm,
The cross-sectional area a of each communication hole (9) is 0.15 to 1.
Range of 5 mm 2, in particular the scope of 0.5~1.25mm 2, perforation pitch p is preferably set in a range of 2.0～10.0Mm.
【００２２】因みに、第４図（イ）には、インナーフィ
ン（２）の波のピッチＰと、熱交換性能Ｑ及び圧力損失
ΔＰｒとの関係を、また、同図（ロ）には、同インナー
フィン（２）の波の高さＨと、熱交換性能Ｑ及び圧力損
失ΔＰｒとの関係を、更に、同図（ハ）には、連通孔の
横断面積ａと、熱交換性能Ｑ及び圧力損失ΔＰｒとの関
係を、同図（ニ）には、穿孔ピッチｐと、熱交換性能Ｑ
及び圧力損失ΔＰｒとの関係を示している。これらのグ
ラフより、上記の数値範囲に設定することにより、熱交
換性能を高いものにしつつつ圧力損失を低く抑え得るこ
とが判る。Incidentally, FIG. 4 (a) shows the relationship between the wave pitch P of the inner fins (2), the heat exchange performance Q and the pressure loss ΔPr, and FIG. 4 (b) shows the same. The relationship between the wave height H of the inner fin (2) and the heat exchange performance Q and the pressure loss ΔPr is further shown in FIG. The relationship between the loss ΔPr and the loss ΔPr is shown in FIG.
And the pressure loss ΔPr. From these graphs, it is understood that by setting the above numerical range, the heat exchange performance can be improved and the pressure loss can be suppressed to be low.
【００２３】なお、インナーフィン（２）の隣り合う立
ち上がり壁部（2a）（2a）の連通孔（９）…（９）…同
士は、第１図（ハ）に示されるように、互いに位相を異
ならせて例えばちどり状に配列されたものとなされてい
てもよいし、同一位相によって長さ方向に配列されたも
のとなされていても、また、不規則状に配列されていて
もよい。The communicating holes (9) ... (9) of the adjacent rising wall portions (2a) (2a) of the inner fins (2) are in phase with each other as shown in FIG. 1 (C). May be arranged differently, for example, in a staggered arrangement, may be arranged in the lengthwise direction according to the same phase, or may be arranged irregularly.
【００２４】ヘッダー（３）（３）は、アルミニウムブ
レージングシートの両側縁部をろう材の介在した突き合
わせ状態に曲成することによりパイプ状となした円筒状
のヘッダーパイプ（3a）の上下端部開口をアルミニウム
製ヘッダーキャップ（3b）にて外嵌め状態に塞いだもの
である。このヘッダー（３）には、チューブ（１）の端
部を挿入するチューブ挿入孔（3c）…が列設され、各チ
ューブ挿入孔（3c）…にチューブ（１）…の端部が挿入
され、その状態で、ろう付けにより、チューブ（１）…
とヘッダー（３）とが連通状態に接合一体化され、併せ
て両側突き合わせ部、及びパイプ（3a）とキャップ（3
b）とが気密状態に接合一体化されている。The headers (3) and (3) are upper and lower end portions of a cylindrical header pipe (3a) formed into a pipe shape by bending both side edges of an aluminum brazing sheet into a butt state in which a brazing material is interposed. The opening is closed with an aluminum header cap (3b). The header (3) is provided with a row of tube insertion holes (3c) into which the ends of the tubes (1) are inserted, and the ends of the tubes (1) are inserted into the respective tube insertion holes (3c). , Then, by brazing, the tube (1) ...
And the header (3) are connected and integrated so as to communicate with each other, and at the same time, the butted portions on both sides, the pipe (3a) and the cap (3
b) and are joined and integrated in an airtight state.
【００２５】なお、熱交換用フィン（７）は、チューブ
（１）の幅と略同じ幅のアルミニウムシート材をコルゲ
ート状に成形してルーバーを切り起こしたもので、その
上下に位置するチューブ（１）…とろう付けにより接合
一体化されている。The heat exchanging fins (7) are formed by forming a corrugated aluminum sheet material having a width substantially the same as that of the tube (1) and cutting and raising the louver. 1) ... and are joined and integrated by brazing.
【００２６】上記構成の凝縮器では、図示しない凝縮器
ファンを駆動すると共に圧縮機の駆動すると、空気が凝
縮器を前後方向に流通すると共に、冷媒が凝縮器内を流
通する。この冷媒は、チューブ（１）…内において、イ
ンナーフィン（２）によって仕切られた幅方向に複数本
の冷媒通路（10）…を分流してチューブ長さ方向に流通
されていくと共に、その流通過程において、連通孔
（９）…を通じて各冷媒通路（10）…間で行来を行うこ
とによってチューブ幅方向にも流通される。これによ
り、冷媒は、チューブ（１）内をその長さ方向に通路抵
抗をあまり大きくすることなく流通されていく。同時
に、冷媒は、熱交換が最も活発に行われるチューブ幅方
向の風上側とそうでない風下側との間で行来を行い、風
上側で凝縮された冷媒が風下側に移行されると共に、風
下側の冷媒が熱交換が活発に行われる風上側に移行さ
れ、これにより、チューブ（１）内を流通される冷媒は
効率良く凝縮熱交換される。もとより、チューブ（１）
の上下の壁（1a）（1a）はインナーフィン（７）にて連
結されていることにより、熱交換中、十分な耐圧性能を
発揮する。In the condenser having the above construction, when a condenser fan (not shown) is driven and a compressor is driven, air flows through the condenser in the front-rear direction and refrigerant flows through the inside of the condenser. In the tubes (1), the refrigerant is divided into a plurality of refrigerant passages (10) in the width direction partitioned by the inner fins (2) so as to be distributed in the tube length direction and the distribution thereof. In the process, the refrigerant flows through the communication holes (9) between the respective refrigerant passages (10) so that the refrigerant flows in the tube width direction. Thereby, the refrigerant is circulated in the tube (1) in the length direction thereof without increasing the passage resistance so much. At the same time, the refrigerant travels between the windward side in the tube width direction where heat exchange is most actively performed and the leeward side in the tube width direction, where the refrigerant condensed on the upwind side is transferred to the leeward side, The refrigerant on the side is moved to the windward side where heat exchange is actively performed, and thereby, the refrigerant circulating in the tube (1) is efficiently condensed and heat-exchanged. Of course, the tube (1)
Since the upper and lower walls (1a) (1a) are connected by the inner fin (7), sufficient pressure resistance performance is exhibited during heat exchange.
【００２７】第５図に示される他の実施例にかかる偏平
チューブ（21）は、その上下平面壁（21a ）（21a ）
に、該壁（21a ）（21a ）と一体の折返し屈曲状の、チ
ューブ長さ方向に延びる補強壁（22）…が内方立ち上が
り状態に設けられ、該補強壁（22）…の先端部が対向す
る平面壁（21a ）（21a ）の内面にろう付けされて、チ
ューブ（１）の耐圧性能が高められたものとなされてい
る。そして、各補強壁（22）…には、該補強壁（22）…
にて仕切られた隣り合う冷媒通路（23）…同士を連通す
る連通孔（24）…が、上記実施例の場合と同様に隣り合
う冷媒通路（23）（23）を流通する冷媒の行来を許容す
る態様において、設けられている。このようなチューブ
（21）を用いた熱交換器においても、上記実施例熱交換
器の場合と同様の効果が発揮される。A flat tube (21) according to another embodiment shown in FIG. 5 has upper and lower flat walls (21a) (21a).
In addition, reinforcing walls (22) ... Integral with the walls (21a) (21a) and extending in the tube length direction are provided in a bent back shape, and the tips of the reinforcing walls (22). It is supposed that the pressure resistance of the tube (1) is enhanced by being brazed to the inner surfaces of the opposing flat walls (21a) (21a). Then, the reinforcing walls (22) ...
The communication holes (24) for communicating between the adjacent refrigerant passages (23), which are partitioned by, are connected to each other by the passage of the refrigerant flowing through the adjacent refrigerant passages (23) (23) as in the case of the above embodiment. Is provided in a mode that allows Also in the heat exchanger using such a tube (21), the same effects as in the case of the above-mentioned heat exchanger of the embodiment are exhibited.
【００２８】[0028]
【発明の効果】上述の次第で、この発明の熱交換器は、
熱交換用偏平チューブの対向平面壁同士が、長さ方向に
延びる補強壁によりチューブ内において連結され、該補
強壁に、補強壁にて仕切られた隣り合う冷媒通路同士を
連通する複数個の連通孔が分散状態に設けられたもので
あるから、チューブの耐圧性能を高いものにすることが
できるのはもとより、熱交換中、チューブ内の各冷媒通
路を流通する熱交換媒体は連通孔を通じてチューブの幅
方向への行来を行い、そのため、熱交換媒体が、熱交換
器を前後方向に流通する空気等と効率良く熱交換を行う
ことができて、熱交換効率の向上を図ることができる。According to the above, the heat exchanger of the present invention is
The opposing flat walls of the flat tube for heat exchange are connected in the tube by a reinforcing wall extending in the longitudinal direction, and a plurality of communication for communicating adjacent refrigerant passages partitioned by the reinforcing wall to the reinforcing wall. Since the holes are provided in a dispersed state, not only can the pressure resistance of the tube be enhanced, but during heat exchange, the heat exchange medium flowing through each refrigerant passage in the tube can be passed through the communication hole to the tube. In the width direction, and therefore, the heat exchange medium can efficiently exchange heat with air or the like flowing through the heat exchanger in the front-rear direction, and the heat exchange efficiency can be improved. .
【００２９】しかも、補強壁は、上記のように、チュー
ブの長さ方向の延ばされ、このような補強壁に連通孔が
形成された構成であることにより、熱交換媒体は、チュ
ーブ内を、大きく撹拌されることなくスムーズに流通さ
れ、その圧力損失を低く抑えることができる。In addition, the reinforcing wall is extended in the lengthwise direction of the tube as described above, and the communication hole is formed in such a reinforcing wall, so that the heat exchange medium flows inside the tube. Therefore, it can be smoothly distributed without being greatly stirred, and its pressure loss can be suppressed to a low level.
【図１】一実施例にかかる熱交換器のチューブ構成を示
すもので、図（イ）は横断面図、図（ロ）はインナーフ
ィンを途中まで引き出した状態の斜視図、図（ハ）は図
（イ）のＩ−Ｉ線断面図である。FIG. 1 shows a tube configuration of a heat exchanger according to one embodiment, FIG. 1 (a) is a cross-sectional view, FIG. 1 (b) is a perspective view in which an inner fin is partially pulled out, and FIG. FIG. 4B is a sectional view taken along line I-I of FIG.
【図２】チューブ、ヘッダー等を分離状態にして示す一
部切欠き斜視図である。FIG. 2 is a partially cutaway perspective view showing a tube, a header and the like in a separated state.
【図３】熱交換器の全体構成を示すもので、図（イ）は
正面図、図（ロ）は平面図である。3A and 3B show the entire configuration of a heat exchanger, FIG. 3A is a front view and FIG. 3B is a plan view.
【図４】図（イ）〜図（ロ）は各種寸法を変更した場合
の熱交換性能と圧力損失の変化を示すグラフ図である。4A to 4B are graphs showing changes in heat exchange performance and pressure loss when various dimensions are changed.
【図５】変更例にかかるチューブの横断面図である。FIG. 5 is a cross-sectional view of a tube according to a modification.
【図６】従来の熱交換器用チューブを示すもので、図
（イ）は横断面図、図（ロ）はインナーフィンを途中ま
で引き出した状態の斜視図、図（ハ）は図（イ）のＶＩ
−ＶＩ線断面図である。6A and 6B are views showing a conventional heat exchanger tube, in which FIG. 6A is a cross-sectional view, FIG. 6B is a perspective view with an inner fin partially pulled out, and FIG. VI
It is a VI line sectional view.
【図７】従来の他の熱交換器用チューブを示すもので、
図（イ）は横断面図、図（ロ）はインナーフィンを途中
まで引き出した状態の斜視図、図（ハ）は図（イ）のＶ
ＩＩ−ＶＩＩ線断面図である。FIG. 7 shows another conventional heat exchanger tube,
Figure (a) is a cross-sectional view, Figure (b) is a perspective view with the inner fin pulled out part way, and Figure (c) is V in Figure (a).
FIG. 11 is a sectional view taken along line II-VII.
１、２１…偏平チューブ １ａ、２１ａ…上下の平面壁 ２…波型インナーフィン（補強壁） ９…連通孔 １０…冷媒通路 ２２…補強壁 ２４…連通孔 1, 21 ... Flat tubes 1a, 21a ... Upper and lower flat walls 2 ... Corrugated inner fins (reinforcing wall) 9 ... Communication hole 10 ... Refrigerant passage 22 ... Reinforcing wall 24 ... Communication hole
─────────────────────────────────────────────────────
─────────────────────────────────────────────────── ───
【手続補正書】[Procedure amendment]
【提出日】平成４年１０月３０日[Submission date] October 30, 1992
【手続補正１】[Procedure Amendment 1]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】０００４[Correction target item name] 0004
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【０００４】あるいはまた、第７図に示されるように、
横断面長円状の偏平チューブ（61）内にマルチエントリ
型のインナーフィン（62）が配置され、該フィン（62）
がチューブ（61）の上下の壁（61a ）（61a ）にろう付
けにより接合一体化された構造を有するものが用いられ
ることもあった（実開平２−２８９８０号公報参照）。Alternatively, as shown in FIG.
A multi-entry type inner fin (62) is arranged in a flat tube (61) having an oval cross section.
In some cases, the tube (61) has a structure in which it is joined and integrated with the upper and lower walls (61a) (61a) of the tube (61) by brazing (see Japanese Utility Model Laid-Open No. 2-28980) .
Claims (1)
が、長さ方向に延びる補強壁によりチューブ内において
連結された熱交換器において、該補強壁に、補強壁にて
仕切られた隣り合う冷媒通路同士を連通する複数個の連
通孔が分散状態に設けられてなることを特徴とする熱交
換器。1. A heat exchanger in which opposed flat walls of a flat tube for heat exchange are connected to each other in a tube by a reinforcing wall extending in a longitudinal direction, and adjacent to each other, the reinforcing wall is partitioned by the reinforcing wall. A heat exchanger characterized in that a plurality of communication holes communicating the refrigerant passages are provided in a dispersed state.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4277491A JPH06129734A (en) | 1992-10-15 | 1992-10-15 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4277491A JPH06129734A (en) | 1992-10-15 | 1992-10-15 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH06129734A true JPH06129734A (en) | 1994-05-13 |
Family
ID=17584343
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4277491A Pending JPH06129734A (en) | 1992-10-15 | 1992-10-15 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06129734A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1253391A1 (en) * | 2001-04-28 | 2002-10-30 | Behr GmbH & Co. | Folded flat tube with multiple cavities |
| WO2004085948A1 (en) * | 2003-03-26 | 2004-10-07 | Calsonic Kansei Corp. | Inner fin withi cutout window for heat exchanger |
| EP2064509A4 (en) * | 2006-08-28 | 2013-06-05 | Dana Canada Corp | Heat transfer surfaces with flanged apertures |
| CN104185769A (en) * | 2012-04-02 | 2014-12-03 | 株式会社电装 | Evaporator |
| US10048020B2 (en) | 2006-08-28 | 2018-08-14 | Dana Canada Corporation | Heat transfer surfaces with flanged apertures |
| CN110439990A (en) * | 2019-08-20 | 2019-11-12 | 南宁市安和机械设备有限公司 | A kind of high intensity oil cooler hose |
| CN111546021A (en) * | 2020-05-14 | 2020-08-18 | 安徽法雷特热交换科技有限公司 | Manufacturing method of automobile heat exchanger radiating fin |
| CN113566453A (en) * | 2020-04-29 | 2021-10-29 | 南宁市安和机械设备有限公司 | Novel multi-effect evaporator |
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| JPS59129392A (en) * | 1983-01-10 | 1984-07-25 | Nippon Denso Co Ltd | Heat exchanger |
| JPS6055885U (en) * | 1983-09-21 | 1985-04-19 | カルソニックカンセイ株式会社 | automotive heat exchanger |
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| JPH0379081U (en) * | 1989-11-21 | 1991-08-12 | ||
| JPH0525175U (en) * | 1991-08-23 | 1993-04-02 | 東洋ラジエーター株式会社 | Tube of heat exchanger for evaporator |
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1992
- 1992-10-15 JP JP4277491A patent/JPH06129734A/en active Pending
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57105690A (en) * | 1980-12-24 | 1982-07-01 | Nippon Denso Co Ltd | Heat exchanger |
| JPS59129392A (en) * | 1983-01-10 | 1984-07-25 | Nippon Denso Co Ltd | Heat exchanger |
| JPS6055885U (en) * | 1983-09-21 | 1985-04-19 | カルソニックカンセイ株式会社 | automotive heat exchanger |
| JPH0198896A (en) * | 1987-10-12 | 1989-04-17 | Nippon Denso Co Ltd | Heat exchanger |
| JPH0228981U (en) * | 1988-08-12 | 1990-02-23 | ||
| JPH0363497A (en) * | 1989-07-28 | 1991-03-19 | Matsushita Refrig Co Ltd | Heat transmitting pipe |
| JPH0379081U (en) * | 1989-11-21 | 1991-08-12 | ||
| JPH0525175U (en) * | 1991-08-23 | 1993-04-02 | 東洋ラジエーター株式会社 | Tube of heat exchanger for evaporator |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1253391A1 (en) * | 2001-04-28 | 2002-10-30 | Behr GmbH & Co. | Folded flat tube with multiple cavities |
| WO2004085948A1 (en) * | 2003-03-26 | 2004-10-07 | Calsonic Kansei Corp. | Inner fin withi cutout window for heat exchanger |
| KR100764263B1 (en) * | 2003-03-26 | 2007-10-05 | 칼소닉 칸세이 가부시끼가이샤 | Inner fin with cutout window for heat exchanger |
| US7290595B2 (en) | 2003-03-26 | 2007-11-06 | Calsonic Kansei Corporation | Inner fin with cutout window for heat exchanger |
| EP2064509A4 (en) * | 2006-08-28 | 2013-06-05 | Dana Canada Corp | Heat transfer surfaces with flanged apertures |
| US10048020B2 (en) | 2006-08-28 | 2018-08-14 | Dana Canada Corporation | Heat transfer surfaces with flanged apertures |
| CN104185769A (en) * | 2012-04-02 | 2014-12-03 | 株式会社电装 | Evaporator |
| CN104185769B (en) * | 2012-04-02 | 2017-02-22 | 株式会社电装 | Evaporator |
| US10352599B2 (en) | 2012-04-02 | 2019-07-16 | Denso Corporation | Evaporator |
| CN110439990A (en) * | 2019-08-20 | 2019-11-12 | 南宁市安和机械设备有限公司 | A kind of high intensity oil cooler hose |
| CN113566453A (en) * | 2020-04-29 | 2021-10-29 | 南宁市安和机械设备有限公司 | Novel multi-effect evaporator |
| CN111546021A (en) * | 2020-05-14 | 2020-08-18 | 安徽法雷特热交换科技有限公司 | Manufacturing method of automobile heat exchanger radiating fin |
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