JPS63201495A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JPS63201495A JPS63201495A JP3249887A JP3249887A JPS63201495A JP S63201495 A JPS63201495 A JP S63201495A JP 3249887 A JP3249887 A JP 3249887A JP 3249887 A JP3249887 A JP 3249887A JP S63201495 A JPS63201495 A JP S63201495A
- Authority
- JP
- Japan
- Prior art keywords
- fin
- air
- louvers
- increased
- louver
- 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
- 239000007788 liquid Substances 0.000 claims 1
- 230000000694 effects Effects 0.000 abstract description 6
- 238000001816 cooling Methods 0.000 abstract description 4
- 238000000926 separation method Methods 0.000 abstract description 2
- 238000000034 method Methods 0.000 abstract 1
- 230000017525 heat dissipation Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 239000003507 refrigerant Substances 0.000 description 3
- 229910000838 Al alloy Inorganic materials 0.000 description 2
- 229910000881 Cu alloy Inorganic materials 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000005219 brazing Methods 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000005476 soldering Methods 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、自動車用ラジェータや自動車用冷暖房装置に
適する熱交換器に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a heat exchanger suitable for automobile radiators and automobile air conditioning systems.
自動車用ラジェータや自動車用冷暖房装置として使用さ
れている熱交換器は、従来、実開昭59−97378号
公報などに示されるように、冷媒や温水が通る例えば偏
平なチューブと、コルゲートフィンまたはプレートフィ
ンを交互に配置した積層構造をなしており、これらフィ
ンは上記偏平チューブにろう付けまたは半田付けされて
いる。Conventionally, heat exchangers used as automobile radiators or automobile air-conditioning systems are made of, for example, a flat tube through which refrigerant or hot water passes, and corrugated fins or plates, as shown in Japanese Utility Model Application Publication No. 59-97378. It has a laminated structure with fins arranged alternately, and these fins are brazed or soldered to the flat tube.
上記従来の熱交換器では、空気との熱交換性を良好にす
るため、フィンに温度境界層の前縁効果を狙ったルーバ
を切り起こし形成しである。すなわち、偏平チューブの
熱がフィンに伝導されると、このフィンにおいては表面
を流れる空気との間で熱交換がなされることになるが、
このフィンにルーバ部を形成すると空気との熱伝達効率
が大きくなって良好な熱交換が行われる。In the conventional heat exchanger described above, in order to improve heat exchange performance with air, louvers are cut and raised on the fins to improve the leading edge effect of the temperature boundary layer. In other words, when the heat of the flat tube is conducted to the fins, heat is exchanged with the air flowing over the surface of the fins.
When a louver portion is formed on the fin, the efficiency of heat transfer with the air increases and good heat exchange is performed.
しかしながら、従来におけるルーバ部は、フィンにおけ
る偏平チューブ間の中央平坦部に形成されており、この
ルーバ部とフィン側端の偏平チューブ接合部の間、つま
りフィンの根元部は平坦な形状をなしていた。However, the conventional louver part is formed in the central flat part between the flat tubes of the fin, and the area between this louver part and the flat tube joint at the fin side end, that is, the root part of the fin, has a flat shape. Ta.
このような構造であると、フィンに流入した空気は抵抗
の大きなルーバ部を避けて、このルーバ部両側に形成さ
れている抵抗の小さな上記平坦部を早い速度で流れてし
まい、熱伝達率の小さな平坦部で熱交換するので効率が
良くないばかりでなく、ルーバを通る風量が相対的に少
なくなり、ルーバの熱交換機能が充分生かし切れていな
い不具合がある。With such a structure, the air flowing into the fins avoids the louver part with high resistance and flows at a high speed through the flat parts with low resistance formed on both sides of the louver part, resulting in a decrease in heat transfer coefficient. Since heat is exchanged in a small flat area, not only is the efficiency not good, but the amount of air passing through the louver is relatively small, and the heat exchange function of the louver is not fully utilized.
本発明は、フィンでの熱交換性能を一層高めることがで
きる熱交換器を提供しようとするものである。The present invention aims to provide a heat exchanger that can further improve heat exchange performance with fins.
本発明は、フィンにおけるチューブに近い根元部にルー
バを形成するとともに、上記フィンの中央平坦部に波状
の凹凸面を形成したことを特徴とする。The present invention is characterized in that a louver is formed in the root portion of the fin near the tube, and a wavy uneven surface is formed in the central flat portion of the fin.
本発明によると、チューブに近いことにより温度が高い
フィンの根元部にルーバを形成したから熱伝達効率が増
すとともに、フィンの剛性が増し、しかもフィンの中央
平坦部に波状の凹凸面を形成したので、この部分でも熱
伝達効率が増し、かつこの波状の凹凸面は空気抵抗が増
して上記ルーバ部に流入する空気量を増加させるから、
ルーバの放熱機能を充分に発揮させることができる。According to the present invention, a louver is formed at the base of the fin where the temperature is high due to its proximity to the tube, increasing heat transfer efficiency and increasing the rigidity of the fin.In addition, a wavy uneven surface is formed on the flat central part of the fin. Therefore, the heat transfer efficiency increases in this part as well, and this wavy uneven surface increases air resistance and increases the amount of air flowing into the louver part.
The heat dissipation function of the louver can be fully demonstrated.
以下、本発明について、第1図ないし第6図に示す第1
の実施例にもとづき説明する。Hereinafter, regarding the present invention, the first embodiment shown in FIGS. 1 to 6 will be explained.
This will be explained based on an example.
第4図に熱交換器の全体を示し、1はアルミまたは銅合
金などよりなる偏平チューブであり、蛇行状に配置され
ている。この蛇行状をなす偏平チューブ1の間には、ア
ルミまたは銅合金などよりなるコルゲートフィン2が介
装され、このコルゲートフィン2の屈曲部は偏平チュー
ブ1の側面に半田付けまたはろう付けにより接合されて
いる。FIG. 4 shows the entire heat exchanger, and numeral 1 denotes flat tubes made of aluminum or copper alloy, which are arranged in a meandering pattern. Corrugated fins 2 made of aluminum or copper alloy are interposed between the meandering flat tubes 1, and the bent portions of the corrugated fins 2 are joined to the side surfaces of the flat tubes 1 by soldering or brazing. ing.
偏平チューブ1の一端は流入管3に接続されているとと
もに、他端は流出管4に接続されている。One end of the flat tube 1 is connected to an inflow pipe 3, and the other end is connected to an outflow pipe 4.
コルゲートフィン2は第1図に示すように、偏平チュー
ブ1に近い根元部、すなわち屈曲部にそれぞれルーバ部
5,5を形成しである。これらルーバ部5,5は上記コ
ルゲートフィン2における根元部に、空気の流れ方向に
沿って多数のルーバ片5a・・・、 5b・・・を一体
に形成したものであり、各ルーバ片5a・・・、 5b
・・・は、第2図に断面して示す通り、図示の上下に互
い違いをなして形成されている。As shown in FIG. 1, the corrugated fin 2 has louver portions 5, 5 formed at the root portion close to the flat tube 1, that is, at the bent portion. These louver parts 5, 5 are formed by integrally forming a large number of louver pieces 5a..., 5b... at the root part of the corrugated fin 2 along the air flow direction, and each louver piece 5a... ..., 5b
. . . are formed alternately above and below the figure, as shown in cross section in FIG. 2.
なお、空気は、第1図中矢印F方向に流れる。Note that the air flows in the direction of arrow F in FIG.
本実施例では、これら各ルーバ片5a・・・、 5b・
・・が、偏平チューブ1の側壁に対して、ろう付けまた
は半田付けされているものである。なお、ルーバ片5a
・・・または5b・・・の間隔はフィン2のピッチの1
/4程度が良好である。In this embodiment, each of these louver pieces 5a..., 5b...
... are brazed or soldered to the side wall of the flat tube 1. In addition, the louver piece 5a
... or 5b... the interval is 1 of the pitch of fin 2
/4 is good.
コルゲートフィン2における上記ルーバ部5゜5の間の
中央平坦部には凹凸面6が形成されている。この凹凸面
6は中央平坦部をプレス加工して一体成型したものであ
り、例えば第3図に示すように、10〜20度の傾斜角
をなして三角形状の山6a・・・および谷6b・・・を
、空気の流れ方向に沿って交互に形成することにより波
形をなしている。An uneven surface 6 is formed in the central flat portion of the corrugated fin 2 between the louver portions 5°5. This uneven surface 6 is integrally formed by pressing a central flat part, and has triangular peaks 6a and valleys 6b with an inclination angle of 10 to 20 degrees, for example, as shown in FIG. ... are formed alternately along the air flow direction to form a waveform.
なお、上記ルーバ部5,6および中央平坦部の凹凸面6
は、同時に一体成形することができる。Note that the louver portions 5 and 6 and the uneven surface 6 of the central flat portion
can be integrally molded at the same time.
すなわち、従来においてコルゲートフィンは、第5図に
示されるように一対の歯車状成形具20゜21の間にフ
ィン構成板材22を通過させることにより波形の成形加
工を施して得られるようになっており、フィン構成板材
22を歯車状成形具20.21間を通過させて蛇行形の
癖を付与するものであった。That is, in the past, corrugated fins were obtained by forming a corrugated fin by passing a fin-constituting plate 22 between a pair of gear-shaped forming tools 20 and 21, as shown in FIG. In this case, the fin-constituting plate material 22 was passed between gear-shaped forming tools 20 and 21 to give it a meandering shape.
本実施例のようなルーバ部5,6および凹凸面6を形成
するには、上記歯車状成形具20.21の歯面に、第6
図に示すような切り起こし歯28.23および凹凸成型
面24を形成しておく。切り起こし歯23、28は歯面
の端部に設けられるとともに、凹凸成型面24が該歯面
の上記切り起こし歯28.23間に形成される。このよ
うにすれば、一対の歯車状成形具20.21の間にフィ
ン構成板材22を通過させることにより波形の成形加工
を施して波形の癖を与えると同時に、ルーバ5および凹
凸面6を同時に成型加工することができる。In order to form the louver portions 5, 6 and the uneven surface 6 as in this embodiment, a sixth
Cut and raised teeth 28, 23 and an uneven molded surface 24 as shown in the figure are formed in advance. The cut and raised teeth 23 and 28 are provided at the end of the tooth surface, and a concave and convex molded surface 24 is formed between the cut and raised teeth 28 and 23 on the tooth surface. In this way, by passing the fin-constituting plate material 22 between the pair of gear-shaped forming tools 20 and 21, the fin forming plate material 22 is formed into a wave shape to give a wave shape, and at the same time, the louver 5 and the uneven surface 6 are formed. Can be molded.
このような構成の実施例によれば、偏平チューブl内の
冷媒通路7内を通る冷媒や温水が偏平チューブ1の壁を
通じてフィン2と熱交換する。According to the embodiment having such a configuration, the refrigerant and hot water passing through the refrigerant passage 7 in the flat tube 1 exchange heat with the fins 2 through the wall of the flat tube 1.
フィン2にあっては表面を流れる空気と熱交換する。こ
の場合、フィン2に形成したルーバ部5゜5は空気との
熱伝達率を増し、かつ通風抵抗を増すので空気との熱交
換効率を高める。特に、ルーバ部5,5は、フィン2に
おける偏平チューブ1に近い根元部に形成したので、こ
の根元部は偏平チューブlからの熱伝導により温度が高
い部分であり、したがって温度の高い部分に設置したル
ーバ部5.5は空気との熱交換作用を充分に発揮し、熱
交換性能が増す。The fins 2 exchange heat with the air flowing over their surfaces. In this case, the louver portions 5.5 formed on the fins 2 increase the heat transfer coefficient with the air and the ventilation resistance, thereby increasing the efficiency of heat exchange with the air. In particular, since the louver parts 5, 5 are formed at the root part of the fin 2 close to the flat tube 1, this root part is a part where the temperature is high due to heat conduction from the flat tube 1, and therefore it is installed in a high temperature part. The louvered portion 5.5 exhibits a sufficient heat exchange effect with the air, increasing heat exchange performance.
また、ルーバ部5,5は、偏平チューブ1に接合される
フィン2の根元部に形成しであるから、フィン2の剛性
が増す。Further, since the louver portions 5, 5 are formed at the root portions of the fins 2 joined to the flat tube 1, the rigidity of the fins 2 is increased.
しかも、左右のルーバ部5,5間の平坦部には凹凸面6
を形成したので、この平坦部の熱伝達率が、凹凸面6を
設けない場合よりも増すから、フィン2全体の熱伝達効
率を増加させ、よって熱交換効率を高める。しかも、平
坦部に沿って流れる冷却風は凹凸面6によって剥離や乱
流が促されるから、流れの抵抗が大きくなり、このため
凹凸面6は冷却風をルーバ部5,5に向かわせる。よっ
て、放熱性能の高いルーバ部5,5を流れる風量が多く
なり、熱交換効率が一層向上することになる。Moreover, an uneven surface 6 is formed on the flat part between the left and right louver parts 5, 5.
Since the heat transfer coefficient of the flat portion is increased compared to the case where the uneven surface 6 is not provided, the heat transfer efficiency of the entire fin 2 is increased, thereby increasing the heat exchange efficiency. In addition, the uneven surface 6 promotes separation and turbulence of the cooling air flowing along the flat portion, so the resistance to the flow increases, and therefore the uneven surface 6 directs the cooling air toward the louver portions 5, 5. Therefore, the amount of air flowing through the louver parts 5, 5 having high heat dissipation performance increases, and the heat exchange efficiency is further improved.
また、平坦部に形成した凹凸面6は該平坦部の機械的強
度を増す。Further, the uneven surface 6 formed on the flat portion increases the mechanical strength of the flat portion.
なお、上記第1の実施例では、ルーバ部5が多数のルー
バ片5a・・・、 5b・・・を図示の上下に互い違い
をなして形成されている場合を説明したが、ルーバ部5
は第7図に示す第2の実施例のように、多数のルーバ片
30・・・を傾斜して切り起こした様な形状であっても
よい。In the first embodiment, the louver portion 5 is formed of a large number of louver pieces 5a, 5b, etc., which are alternately arranged vertically in the figure.
As in the second embodiment shown in FIG. 7, the shape may be such that a large number of louver pieces 30 are cut and raised at an angle.
また、上記第1の実施例では、平坦部の凹凸面6が、三
角形状の山6a・・・および谷6b・・・により形成さ
れた例を示したが、本発明は第8図に示す第3の実施例
のように、凹凸面を丸形状の山40a・・・および谷4
0b・・・によって波形に形成してもよい。Further, in the first embodiment, the uneven surface 6 of the flat portion is formed of triangular peaks 6a and valleys 6b, but the present invention is as shown in FIG. As in the third embodiment, the uneven surface has round peaks 40a... and valleys 4.
0b... may be formed into a waveform.
そしてまた、ルーバ部5,5間の平坦部に形成した凹凸
面6は一列に限らず、複数列設けるようにしてもよい。Further, the uneven surface 6 formed on the flat part between the louver parts 5, 5 is not limited to one row, but may be provided in a plurality of rows.
さらに、フィン2はコルゲートフィンに限らず、プレー
トフィンであっても実施可能であり、チューブlは偏平
に限らず、楕円、丸型などのチューブであっても実施可
能である。Furthermore, the fins 2 are not limited to corrugated fins, but may also be plate fins, and the tube 1 is not limited to being flat, but may also be an elliptical or round tube.
以上説明したように本発明によれば、チューブに近くて
温度が高いフィンの根元部にルーバを形成したから熱伝
達効率が増すとともに、フィンの剛性が増し、しかもフ
ィンの中央平坦部に波状の凹凸面を形成したので、この
部分でも熱伝達効率が増し、かつこの波状の凹凸面は空
気抵抗が増して上記ルーバ部に流入する空気量を増加さ
せるから、ルーバの放熱機能を充分に発揮させることが
でき、従来に比べて熱交換能力が向上する等の効果があ
る。As explained above, according to the present invention, since the louver is formed at the base of the fin, which is close to the tube and has a high temperature, the heat transfer efficiency is increased and the rigidity of the fin is increased. Since the uneven surface is formed, heat transfer efficiency is increased in this area as well, and this wavy uneven surface increases air resistance and increases the amount of air flowing into the louver, so the heat dissipation function of the louver can be fully demonstrated. This has the effect of improving heat exchange capacity compared to conventional methods.
第1図ないし第6図は本発明の第1の実施例を示し、第
1図は第4図の1部を拡大して示す斜視図、第2図およ
び第3図はそれぞれ第1図中■−■線および■−■線の
断面図、第4図は熱交換器全体の正面図、第5図および
第6図はそれぞれコルゲートフィンの製造装置を説明す
る図、第7図は本発明の第2実施例を示す第2図に相当
する部分の断面図、第8図は本発明の第3実施例を示す
第3図に相当する部分の断面図である。
■・・・偏平チューブ、2・・・コルゲートフィン、5
゜5・・−ルーバ部、6・・・凹凸面。
出願人代理人 弁理士 鈴江武彦
b。
第3図
第4図
第5図
第6図
第7図
第8図1 to 6 show a first embodiment of the present invention, FIG. 1 is an enlarged perspective view of a part of FIG. 4, and FIGS. 2 and 3 are parts of FIG. 1, respectively. 4 is a front view of the entire heat exchanger, 5 and 6 are diagrams each illustrating a corrugated fin manufacturing apparatus, and 7 is a cross-sectional view taken along lines ■-■ and ■-■. 8 is a sectional view of a portion corresponding to FIG. 2 showing a second embodiment of the present invention, and FIG. 8 is a sectional view of a portion corresponding to FIG. 3 showing a third embodiment of the present invention. ■...Flat tube, 2...Corrugated fin, 5
゜5...-louver part, 6... uneven surface. Applicant's agent Patent attorney Takehiko Suzue b. Figure 3 Figure 4 Figure 5 Figure 6 Figure 7 Figure 8
Claims (1)
プレートフィンを接合してコア部を構成した熱交換器に
おいて、上記フィンにおけるチューブに近い根元部にル
ーバを形成するとともに、上記フィンの中央平坦部に波
状の凹凸面を形成したことを特徴とする熱交換器。In a heat exchanger in which a core portion is formed by joining corrugated fins or plate fins to a tube through which liquid flows, a louver is formed at the root portion of the fin near the tube, and a wavy shape is formed in the central flat portion of the fin. A heat exchanger characterized by forming an uneven surface.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3249887A JPS63201495A (en) | 1987-02-17 | 1987-02-17 | Heat exchanger |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3249887A JPS63201495A (en) | 1987-02-17 | 1987-02-17 | Heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS63201495A true JPS63201495A (en) | 1988-08-19 |
Family
ID=12360659
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP3249887A Pending JPS63201495A (en) | 1987-02-17 | 1987-02-17 | Heat exchanger |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS63201495A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE202008016603U1 (en) * | 2008-12-15 | 2010-04-29 | Autokühler GmbH & Co. KG | Corrugated rib for heat exchanger |
KR20170063543A (en) * | 2014-09-19 | 2017-06-08 | 가부시키가이샤 티라도 | Corrugated fins for heat exchanger |
-
1987
- 1987-02-17 JP JP3249887A patent/JPS63201495A/en active Pending
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE202008016603U1 (en) * | 2008-12-15 | 2010-04-29 | Autokühler GmbH & Co. KG | Corrugated rib for heat exchanger |
KR20170063543A (en) * | 2014-09-19 | 2017-06-08 | 가부시키가이샤 티라도 | Corrugated fins for heat exchanger |
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