JPH01285795A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JPH01285795A JPH01285795A JP11245488A JP11245488A JPH01285795A JP H01285795 A JPH01285795 A JP H01285795A JP 11245488 A JP11245488 A JP 11245488A JP 11245488 A JP11245488 A JP 11245488A JP H01285795 A JPH01285795 A JP H01285795A
- Authority
- JP
- Japan
- Prior art keywords
- sides
- strip
- central part
- fine
- heat transfer
- 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
- 239000002131 composite material Substances 0.000 claims abstract description 14
- 238000009423 ventilation Methods 0.000 claims description 10
- 230000003247 decreasing effect Effects 0.000 abstract 1
- 238000000034 method Methods 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 6
- 229910001369 Brass Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 239000013585 weight reducing agent Substances 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
Landscapes
- Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Geometry (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、車両空調機などに用いられるコルゲートフィ
ンに係り、特に通風抵抗が小さく伝熱性能に優れたフィ
ンの実現に好適な細片形状に関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to corrugated fins used in vehicle air conditioners, etc., and in particular, a strip shape suitable for realizing a fin with low ventilation resistance and excellent heat transfer performance. Regarding.
従来の熱交換器に使用する伝熱フィンは、特開昭５９−
１０７１９０号に記載のように、細片の両側立ち上げ部
を除いて、それらの細片の通風方向断面はどの部分もほ
ぼ一定となるような形状に構成されていた。The heat transfer fins used in conventional heat exchangers are disclosed in Japanese Patent Application Laid-Open No. 59-
As described in No. 107190, the cross sections of the strips in the ventilation direction were configured to have a substantially constant shape at all parts, except for the raised portions on both sides of the strips.
（発明が解決しようとするｌｌ１ｇ）
上記従来技術は、細片長手方向に対して通風抵抗が均一
となるため、基本的には通過風速もほぼ均一になる。実
際には、細片の両端に位置する伝熱管の作用により、空
気とフィンの温度差の小さい細片中央部の風速がむしろ
速くなる傾向にあり伝熱性能上の限界があった。(11g to be Solved by the Invention) In the above-mentioned prior art, since the ventilation resistance is uniform in the longitudinal direction of the strip, basically the passing wind speed is also almost uniform. In reality, due to the action of the heat transfer tubes located at both ends of the strip, the wind speed in the center of the strip, where the temperature difference between the air and the fins is small, tends to be faster, and there is a limit to heat transfer performance.
本発明の目的は、伝熱性能をさらの向上させ。The purpose of the present invention is to further improve heat transfer performance.
熱交換器の軽量化、低コスト化を達成することにある。The aim is to achieve weight reduction and cost reduction of heat exchangers.
上記目的は、細片群より成る伝熱フィンにおいて、細片
中央部の角度を両側部より太き（シ、なおかつ各細片の
中央部付近を除く両側部を更に小さい細片に分割して成
る複合細片にすることにより、達成される。The above purpose is to create a heat transfer fin consisting of a group of strips by making the angle at the center of each strip wider than at both sides, and by dividing each strip into smaller strips at both sides except for the vicinity of the center. This is achieved by making a composite strip consisting of:
空気流とフィンの温度差の大きい複合細片両側部は中央
部付近と比較し１通風抵抗が小さくなる。On both sides of the composite strip where there is a large temperature difference between the airflow and the fins, the ventilation resistance is smaller than near the center.
それによって、通過風速も大きくなり、伝熱性能は向上
する。また、フィン全体の剛性を損うことなく、フィン
のｆＩＩＩＪｌｌｌ化が可能となる。This increases the passing wind speed and improves heat transfer performance. Further, it is possible to make the fin fIIIJllll without impairing the rigidity of the entire fin.
以下、本発明の一実施例を図により説明する。 Hereinafter, one embodiment of the present invention will be described with reference to the drawings.
第１図は本発明の伝熱フィンを配設した熱交換器の立体
図である。１は黄銅またはアルミニウムの板材をサイン
カーブの波形状に折まげ成形したコルゲートフィン、２
は伝熱管、そして３はコルゲートフィン１と伝熱Ｉｒ！
２より成る車両空調機用熱交換器である。第２図は第１
図のコルゲートフインの平面図である。４．４’は小さ
い細片で構成された複合山形細片６〜１０を具備する細
片両側部、５は大きい細片で構成された基本山形細片６
′〜１０′を具備する細片中央部である。第３図は第２
図のＡ−Ａ方向またはＣ−Ｃ方向から見た細片両側部の
一部の拡大断面図である。細片の各部分は図に示すよう
に断面方向中央部に角度θ１の山形細片、その両側に同
じ角度θｌの山形細片を具備する山形細片６〜１０で構
成されている。一方、第４図は第２図のＢ−Ｂ方向から
見た細片中央部の一部の拡大断面図である。この部分は
図に示すように山角度θ２の基本山形細片６′〜１０′
となっている。また第５図は第２図の複合山形細片−つ
分の長手方向投影図の一部分である０本実施例による伝
熱フィンは上述したように通風方向断面形状が中央部付
近で連続し、両側部で断続した山形細片で構成されてい
る。また細片中央部の山角度θ２が、細片両側部の山角
度θ１より大きいことを特徴とする１次に本実施例の動
作を説明する。まず、従来の伝熱フィンの特性について
説明する。細片の形状がどうであれ、その通風方向断面
形状がどこでもほぼ同様である伝熱フィンの場合は、伝
熱管の影響により、空気流Ｕ、が細片中央部方向に曲げ
られる。従って、細片長手方向の風速分布は細片中央部
付近に高風速部、細片両側部に低風速部が生じることに
なる。FIG. 1 is a three-dimensional view of a heat exchanger provided with heat transfer fins of the present invention. 1 is a corrugated fin made by folding a brass or aluminum plate into a sine curve wave shape; 2
is the heat transfer tube, and 3 is the corrugated fin 1 and the heat transfer Ir!
This is a heat exchanger for a vehicle air conditioner consisting of two parts. Figure 2 is the first
FIG. 3 is a plan view of the corrugated fin shown in FIG. 4.4' is a strip side comprising composite chevron strips 6 to 10 made up of small strips; 5 is a basic chevron strip 6 made up of large strips;
10' to 10'. Figure 3 is the second
It is an enlarged sectional view of a part of both sides of a strip seen from the AA direction or the CC direction of the figure. As shown in the figure, each part of the strip is composed of chevron-shaped strips 6 to 10 having a chevron-shaped strip having an angle θ1 at the center in the cross-sectional direction, and chevron-shaped strips having the same angle θl on both sides thereof. On the other hand, FIG. 4 is an enlarged cross-sectional view of a part of the central part of the strip seen from the direction BB in FIG. This part consists of basic chevron-shaped strips 6' to 10' with a chevron angle θ2 as shown in the figure.
It becomes. FIG. 5 is a partial longitudinal projection of the composite chevron-shaped strip shown in FIG. It is composed of chevron-shaped strips interrupted on both sides. Further, the operation of this embodiment will be described below, in which the peak angle θ2 at the center of the strip is larger than the peak angle θ1 at both sides of the strip. First, the characteristics of conventional heat transfer fins will be explained. Regardless of the shape of the strip, in the case of heat transfer fins whose cross-sectional shape in the ventilation direction is almost the same everywhere, the air flow U is bent toward the center of the strip due to the influence of the heat transfer tube. Therefore, the wind speed distribution in the longitudinal direction of the strip has a high wind speed section near the center of the strip and a low wind speed section on both sides of the strip.
また空気温度Ｔａとフィン温度ＴＩの温度差ΔＴ（Ｔａ
Ｔａ）を考えると、空気温度Ｔａは細片長手方向で
同様の温度分布をもつが、フィン温度は伝熱管周辺で大
、細片中央部付近で小といった分布をもつ、従って、温
度差ΔＴは細片中央部で小。Also, the temperature difference ΔT (Ta
Ta), the air temperature Ta has a similar temperature distribution in the longitudinal direction of the strip, but the fin temperature has a distribution such that it is large around the heat transfer tube and small near the center of the strip. Therefore, the temperature difference ΔT is Small in the center of the strip.
両側部で大といった温度分布をもつことになる。This results in a large temperature distribution on both sides.
さて、フィンと空気の間の熱交換量Ｑは、Ｑ−Ｕａ’・
ΔＴであるので、Ｑを増すためにはΔτ大。Now, the amount of heat exchange Q between the fins and the air is Q-Ua'・
Since ΔT, in order to increase Q, Δτ is large.
Ｕａ大とすることが有効である。しかるに、上記従来技
術はΔＴが大の部分でＵ＆が小、ΔＴが小の部分でＵａ
が大となっているから、熱交＊ｔＱは小さく、伝熱性能
は小さかった。It is effective to make Ua large. However, in the above conventional technology, U& is small in the part where ΔT is large, and Ua is small in the part where ΔT is small.
Since the was large, the heat exchanger *tQ was small and the heat transfer performance was small.
次に５本発明の動作について説明する１本発明は細片中
央部の通風抵抗が大、細片両側部の通風抵抗が小さなる
。このため、細片中央部に低風速部、細片両側部に高風
速部が生じる。一方温度差ΔＴの傾向（細片中央部小、
細片両側部大）は本質的に不変である。この結果、ΔＴ
が大の部分でＵ、を大とすることができ、熱交換量Ｑ
Ｏ’： Ｕ ａ”・ΔＴが飛躍的に増加する。細片中央
部はΔＴ及びＩＪａ共に小であるが、もともと絶対値的
に小さいので、全体に与える影響は小さい。Next, 5 operations of the present invention will be explained. 1. The present invention has a large ventilation resistance at the center of the strip and a small ventilation resistance at both sides of the strip. For this reason, a low wind speed portion is generated in the center of the strip, and a high wind speed portion is generated on both sides of the strip. On the other hand, the tendency of temperature difference ΔT (small in the center of the strip,
The strip sides (large) are essentially unchanged. As a result, ΔT
In the part where is large, U can be made large, and the amount of heat exchange Q
O': U a''·ΔT increases dramatically. Both ΔT and IJa are small at the center of the strip, but since they are originally small in absolute value, their influence on the whole is small.
本実施例によれば、総合伝熱性能が一層向上し。According to this example, the overall heat transfer performance is further improved.
しかも基本山形細片の両側部に更に小さい細片が形成さ
れる複合山形細片の構造により、フィン全体の強度低下
がなく、細片の前縁効果（細片の微細化による）を−層
大きくすることができる。Moreover, due to the structure of the composite chevron-shaped strip in which smaller strips are formed on both sides of the basic chevron-shaped strip, there is no decrease in the strength of the entire fin, and the leading edge effect of the strip (due to the miniaturization of the strip) is reduced. Can be made larger.
第６図〜第９図（第４，５図、第６，７図の組合せ）は
、一部の拡大断面形状であり９本発明の別の実施例を示
すものである。これらの場合も効果は第３，４図のもの
とほぼ同様である。第６図は通風方向に対して傾斜状と
した傾斜状複合山形細片１１．第７図は同じく傾斜状と
した傾斜状基本山形細片１２である。第８図は通風方向
に対して、傾斜状とした傾斜状複合細片１３．第９図は
同じく傾斜状とした傾斜状基本細片１４である。6 to 9 (a combination of FIGS. 4, 5, 6, and 7) are partially enlarged cross-sectional views showing another embodiment of the present invention. In these cases, the effects are almost the same as those shown in FIGS. 3 and 4. Figure 6 shows an inclined composite chevron-shaped strip 11 which is inclined with respect to the ventilation direction. FIG. 7 shows an inclined basic chevron-shaped strip 12 which is also inclined. FIG. 8 shows an inclined composite strip 13. which is inclined with respect to the ventilation direction. FIG. 9 shows a slanted basic strip 14 which is also slanted.
本発明によれば、空気温度とフィン温度の差が大きい部
分の風速を速くするという風速制御ができるので、伝熱
効率の向上に効果がある。According to the present invention, it is possible to control the wind speed to increase the wind speed in a portion where the difference between the air temperature and the fin temperature is large, which is effective in improving heat transfer efficiency.
更に、フィン全体の強度低下がなく細片の微小化ができ
るので前縁効果の増大に伴う伝熱性能の向上と、フィン
の信頼性の確保、伝熱性能の向上が期待できるので、熱
交換器の軽量化、低コスト化の効果がある。Furthermore, since the strength of the entire fin is not reduced and the pieces can be miniaturized, it is expected that the leading edge effect will increase, leading to improved heat transfer performance, ensuring the reliability of the fin, and improving heat transfer performance. This has the effect of reducing the weight and cost of the device.
第１図はコルゲートフィンを配設した熱交換器の立体図
、第２図は第１図のコルゲートフインの平面図、第３図
は第２図のＡ−Ａ方向またはＣ−Ｃ方向から見た一部の
拡大断面図、第４図は第２図のＢ−Ｂ方向から見た一部
の拡大断面図、第５図は第２図の複合山形細片１つ分の
長手方向投影図、第６〜９図はその他の実施例で第２図
の一部の拡大断面図である。
１・・・コルゲートフィン、２・・・伝熱管、３−・・
車両空調機用熱交換器、４．４’・・・細片片側部、５
・・・細片中央部、６〜１０・・・複合山形細片、６′
〜１０′・・・基本山形側片、１１・・・傾斜状複合山
形細片、１２・・・傾斜状基本山形細片、１３・・・傾
斜状複合細第 ｊ 図
第 Ｚ 図Figure 1 is a three-dimensional view of a heat exchanger equipped with corrugated fins, Figure 2 is a plan view of the corrugated fins in Figure 1, and Figure 3 is viewed from the A-A direction or C-C direction in Figure 2. Fig. 4 is an enlarged sectional view of a part seen from the direction B-B in Fig. 2, and Fig. 5 is a longitudinal projection of one composite chevron strip in Fig. 2. , and FIGS. 6 to 9 are enlarged sectional views of a part of FIG. 2 in other embodiments. 1...corrugate fin, 2...heat exchanger tube, 3-...
Heat exchanger for vehicle air conditioner, 4.4'...One side of strip, 5
...Central part of strip, 6 to 10...Composite chevron strip, 6'
~10'...Basic chevron-shaped side piece, 11...Slanted composite chevron-shaped strip, 12...Slanted basic chevron-shaped strip, 13...Slanted composite thin Fig. J Fig. Z
Claims (1)
インにおいて、各細片の中央部付近の通風方向投影面積
がその両側部と比べ大きく、また中央部付近を除く両側
部を更に小さい細片に分割している複合細片で構成した
伝熱フインを用いることを特徴とする熱交換器。1. In corrugated fins used in heat exchangers for vehicle air conditioners, the projected area in the ventilation direction near the center of each strip is larger than that on both sides, and both sides except for the center are divided into smaller strips. A heat exchanger characterized by using heat transfer fins made of composite strips.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11245488A JPH01285795A (en) | 1988-05-11 | 1988-05-11 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11245488A JPH01285795A (en) | 1988-05-11 | 1988-05-11 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH01285795A true JPH01285795A (en) | 1989-11-16 |
Family
ID=14587040
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11245488A Pending JPH01285795A (en) | 1988-05-11 | 1988-05-11 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH01285795A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2016133248A (en) * | 2015-01-19 | 2016-07-25 | 株式会社デンソー | Heat exchanger |
-
1988
- 1988-05-11 JP JP11245488A patent/JPH01285795A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2016133248A (en) * | 2015-01-19 | 2016-07-25 | 株式会社デンソー | Heat exchanger |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5099914A (en) | Louvered heat exchanger fin stock | |
| US6889757B2 (en) | Core structure of integral heat-exchanger | |
| JPS5926237B2 (en) | Heat exchanger | |
| JPS6157556B2 (en) | ||
| US4791984A (en) | Heat transfer fin | |
| JPS5845495A (en) | Heat transmitting fin | |
| JPH01305296A (en) | Corrugate fin for heat exchanger | |
| JPH01285795A (en) | Heat exchanger | |
| JPS6159195A (en) | Heat exchanger core | |
| JP2009139085A (en) | Louver type corrugated insert for heat exchanger | |
| JPS5932792A (en) | Heat exchanger | |
| JP2003083690A (en) | Corrugated fin heat-exchanger | |
| JPS5866793A (en) | Fin for air heat exchanger | |
| JPH0275897A (en) | Heat transfer fan | |
| JPH0160759B2 (en) | ||
| JP2730649B2 (en) | Heat exchanger | |
| JPS62172192A (en) | Heat exchanger | |
| JPS60216188A (en) | Fin of heat exchanger | |
| JPH071156B2 (en) | Heat transfer fins and heat exchangers | |
| JP3099714B2 (en) | Cross fin heat exchanger | |
| JPS6133432Y2 (en) | ||
| JPS6155595A (en) | Heat exchanger with fin | |
| JPS6324389Y2 (en) | ||
| JP2692917B2 (en) | Heat exchanger | |
| JPH07103677A (en) | Corrugated fin for heat exchanger |