JPH02154986A - Finned heat exchanger - Google Patents
Finned heat exchangerInfo
- Publication number
- JPH02154986A JPH02154986A JP30804188A JP30804188A JPH02154986A JP H02154986 A JPH02154986 A JP H02154986A JP 30804188 A JP30804188 A JP 30804188A JP 30804188 A JP30804188 A JP 30804188A JP H02154986 A JPH02154986 A JP H02154986A
- Authority
- JP
- Japan
- Prior art keywords
- fins
- flat
- flat tube
- pitch
- tube
- 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
- 238000000034 method Methods 0.000 abstract 2
- 238000001125 extrusion Methods 0.000 abstract 1
- 238000009423 ventilation Methods 0.000 description 11
- 239000003507 refrigerant Substances 0.000 description 8
- 230000000694 effects Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000005057 refrigeration 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
- F28D1/04—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 tubular conduits
- F28D1/053—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 tubular conduits the conduits being straight
- F28D1/0535—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 tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel 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
- F28F1/10—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
- 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
Description
【発明の詳細な説明】
産業上の利用分野
本発明は空調機器や冷凍機器、自動車機器等に使用され
、冷媒と空気等の流体間で熱の授受を行なうフィン付熱
交換器に関するものである。[Detailed Description of the Invention] Industrial Application Field The present invention relates to a finned heat exchanger that is used in air conditioning equipment, refrigeration equipment, automobile equipment, etc., and exchanges heat between fluids such as refrigerant and air. .
従来の技術
近年、フィン付熱交換器は機器設計の面からコンパクト
化が要求されており、フィン形状及び管内面形状の改善
による高効率化が取り組まれている。BACKGROUND OF THE INVENTION In recent years, finned heat exchangers have been required to be more compact in terms of equipment design, and efforts have been made to improve efficiency by improving the fin shape and tube inner surface shape.
以下、図面を参照しながら一ト述した従来のフィン付熱
交換器について説明を行う。Hereinafter, the conventional finned heat exchanger mentioned above will be explained with reference to the drawings.
第８図と第９図は従来のフィン付熱交換器の形状を示し
、第１０図は従来のフィン付熱交換器を構成するフィン
形状、第１１図は円管形状を示す。8 and 9 show the shape of a conventional finned heat exchanger, FIG. 10 shows a fin shape constituting a conventional finned heat exchanger, and FIG. 11 shows a circular tube shape.
第８図から第１１図において、１は一定間隔で平行に並
べられた複数の平板フィンで、一定の段方向ピッチＰｉ
で配列された円穴２と気ｔＭへ方向に分割されたルーパ
３が設けられている。４は前記平板フィンの円穴２に挿
入密着された円管で、両端のベンド５により円管４相互
が接続され管内冷媒Ｒ流路を構成すると共に、管内には
複数の螺旋溝６が設けられている。また従来、性能及び
加工性の面から円管４の外径Ｄｏは７〜１０ｍｍ、円管
４の段方向ピッチＰｄは２１〜２５ｍｍの範囲が主に用
いられていた。8 to 11, reference numeral 1 denotes a plurality of flat plate fins arranged in parallel at regular intervals, with a constant pitch in the step direction Pi.
A looper 3 is provided which is divided in the direction of the circular holes 2 arranged in the direction tM. Reference numeral 4 denotes a circular tube that is inserted into the circular hole 2 of the flat fin and is tightly fitted.The circular tubes 4 are connected to each other by bends 5 at both ends to form a refrigerant R flow path in the tube, and a plurality of spiral grooves 6 are provided in the tube. It is being Conventionally, in terms of performance and workability, the outer diameter Do of the circular tube 4 has been mainly used in the range of 7 to 10 mm, and the pitch Pd in the step direction of the circular tube 4 has been mainly used in the range of 21 to 25 mm.
以−Ｌのように構成されたフィン付熱交換器について、
以下第１２図と第１３図を用いてその動作を説明する。Regarding the finned heat exchanger configured as shown below,
The operation will be explained below using FIG. 12 and FIG. 13.
平板フィン１間を流れる気流Ａと円管４内を流れる冷媒
Ｒとの間で平板フィン１及び円管４を介して熱交換が行
なわれる。その際、平板フィン１の表面にはルーバ３が
分割して設けられているため、平板フィン１の表面に生
じる気流Ａの温度境界層の発達が抑えられ、気流Ａと平
板フィン１との熱伝達率の向上が図られている。また、
円管４内では螺旋溝６によって冷媒Ｒが乱流促進される
ため、円管４と冷媒Ｒとの熱伝達率の向上が図られてい
る。Heat exchange is performed between the airflow A flowing between the flat plate fins 1 and the refrigerant R flowing in the circular tube 4 via the flat plate fins 1 and the circular tube 4. At this time, since the louver 3 is provided separately on the surface of the flat fin 1, the development of a temperature boundary layer of the airflow A generated on the surface of the flat fin 1 is suppressed, and the heat between the airflow A and the flat fin 1 is suppressed. Efforts are being made to improve the transmission rate. Also,
In the circular tube 4, the spiral groove 6 promotes turbulent flow of the refrigerant R, so that the heat transfer coefficient between the circular tube 4 and the refrigerant R is improved.
発明が解決しようとする課題
しかしながら上記のような構成では、円管４の外径Ｄｏ
が大きいために円管４を横切る気流Ａの通風抵抗が大き
く、円管４の段方向ピッチＰｄを大きくすることによる
気流Ａの通風抵抗の低下と、段方向ピッチＰｄを小さく
することによるフィン効率の向上及び実通過風速の向上
が相反する作用のため、通風抵抗を考慮すると従来以上
の性能向りが望めないという課題を有していた。Problems to be Solved by the Invention However, in the above configuration, the outer diameter Do of the circular tube 4
is large, so the ventilation resistance of the airflow A crossing the circular tube 4 is large, and the ventilation resistance of the airflow A is reduced by increasing the step direction pitch Pd of the circular tube 4, and the fin efficiency is reduced by decreasing the step direction pitch Pd. Since the improvement of the airflow and the improvement of the actual passing wind speed have contradictory effects, there has been a problem in that it is impossible to expect better performance than the conventional one when ventilation resistance is taken into consideration.
本発明は上記課題に鑑み、気流の通、風抵抗を従来と同
等に抑えながら大幅に熱交換能力を向−トするフィン付
熱交換器を提供するものである。In view of the above-mentioned problems, the present invention provides a finned heat exchanger that significantly increases heat exchange capability while suppressing air flow and wind resistance to the same level as conventional ones.
課題を解決するための手段
を記課題を解決するために本発明のフィン付熱交換器は
、波形状に屈曲成形され一定間隔で平行に並べられたフ
ィンと、長辺と短辺に囲まれ中空状に押し出し成形され
た偏平管とから成り、前記偏平管が長辺方向相互を平行
にして複数段構成され、その相互間に前記フィンが屈曲
部両端を接して密着され、かつ偏平管の短辺方向厚さＬ
を１〜３ｍｍの範囲にし、偏平管の段方向ピッチＰｄを
８〜１２ｍｍの範囲に限定するという構成を備えたもの
である。Means for Solving the Problems In order to solve the problems, the finned heat exchanger of the present invention has fins that are bent into a wave shape and arranged in parallel at regular intervals, and that are surrounded by long sides and short sides. It consists of a flat tube extruded into a hollow shape, and the flat tubes are configured in multiple stages with their long sides parallel to each other, and the fins are closely attached between the two with both ends of the bent portions in contact with each other. Short side thickness L
is in the range of 1 to 3 mm, and the pitch Pd of the flat tubes in the step direction is limited to the range of 8 to 12 mm.
作用
本発明は上記した構成によって、偏平管とフィンの高密
度化が図れ、伝熱面積の増大と熱伝達率の向上及びフィ
ン効率の向上により大幅な熱交換能力の向上ができ、か
つ偏平管とフィンの高密度化によって生じる気流の通風
抵抗の増大を薄型の偏平管の採用によって抑えることが
できる。Effect of the present invention With the above-described configuration, the density of the flat tube and fins can be increased, and the heat exchange capacity can be greatly improved by increasing the heat transfer area, improving the heat transfer coefficient, and improving the fin efficiency. The increase in airflow resistance caused by the high density of the fins can be suppressed by using thin flat tubes.
実施例
以下本発明の実施例のフィン付熱交換器について図面を
参照しながら説明する。EXAMPLE Hereinafter, a finned heat exchanger according to an example of the present invention will be described with reference to the drawings.
第１図と第２図は本発明の実施例におけるフィン付熱交
換器の形状を示すもので、第３図はフィンの形状、第４
図は偏平管の形状を示す。第１図から第４図において、
７は波形状に屈曲成形され一定間隔で平行に並べられた
フィンで、屈曲部８と気流入方向に分割されたルーバ９
とを備えている。１０は長辺１０ａと短辺１０ｂ及び管
内を分割する分割板１０ｃとから構成され、中空状に押
し出し成形された偏平管で、前記偏平管１０は長辺１０
ａ方向相互を平行にして段ピツチＰｄで複数段構成され
、その相互間に前記フィン７が両端の屈曲部８を接して
密着されている。１１は偏平管１０の長手方向両端に接
続したヘッダで、偏平管１０と共に冷媒凡の管内流路を
構成している。Figures 1 and 2 show the shape of a finned heat exchanger in an embodiment of the present invention, and Figure 3 shows the shape of the fins, and Figure 4 shows the shape of the fins.
The figure shows the shape of a flat tube. In Figures 1 to 4,
Reference numeral 7 denotes fins bent into a wave shape and arranged in parallel at regular intervals, with a bent part 8 and a louver 9 divided in the air inflow direction.
It is equipped with Reference numeral 10 denotes a hollow extrusion-molded flat tube that is composed of a long side 10a, a short side 10b, and a dividing plate 10c that divides the inside of the tube.
The fins 7 are formed in a plurality of stages with the step pitch Pd parallel to each other in the a direction, and the fins 7 are closely attached between the stages with the bent portions 8 at both ends in contact with each other. Headers 11 are connected to both ends of the flat tube 10 in the longitudinal direction, and together with the flat tube 10 constitute an internal flow path for the refrigerant.
更に偏平管１０の短辺１０ｂ方向厚さｔは１〜３ｍ Ｉ
Ｔ＋の範囲に、段ピツチＰｄは８〜１２ ｍ ｍの範囲
に規定されている。Furthermore, the thickness t of the flat tube 10 in the direction of the short side 10b is 1 to 3 m I
In the range of T+, the step pitch Pd is specified to be in the range of 8 to 12 mm.
以上のように構成されたフィン付熱交換器ついて、以下
第５図と第６図を用いてその動作について説明する。The operation of the finned heat exchanger constructed as above will be described below with reference to FIGS. 5 and 6.
フィン７間を流れる気流Ａとへラダ１１を経て偏平管１
０内を流れる冷媒Ｒとの間でフィン７及び偏平管１０′
！！：介して熱交換が行なわれる。その際、フィン７の
表面にはルーバ９が設けられているため、フィン７の表
面に生じる気流Ａの温度境界層の発達が抑えられ、気流
Ａとフィン７との熱伝達率の向上が図られている。また
、偏平管１０の管内は分割板１０ｃによって微小流路化
され、偏平管１０と冷媒Ｒとの熱伝達率の向上が図られ
ている。Airflow A flowing between the fins 7 and the flat tube 1 via the ladder 11
The fins 7 and the flat tube 10'
! ! : Heat exchange is carried out through. At this time, since the louvers 9 are provided on the surface of the fins 7, the development of a temperature boundary layer of the airflow A generated on the surface of the fins 7 is suppressed, and the heat transfer coefficient between the airflow A and the fins 7 is improved. It is being Moreover, the inside of the flat tube 10 is made into microchannels by the dividing plate 10c, and the heat transfer coefficient between the flat tube 10 and the refrigerant R is improved.
また薄型の偏平管１０の採用により気流への通風抵抗を
下げることができ、従来例と同等通風抵抗基準では偏平
管１０とフィン７の高密度化が可能となり、伝熱面積の
増大と熱伝達率の向上及びフィン効率の向上により大幅
な熱交換能力の向上ができる。In addition, by adopting the thin flat tube 10, the ventilation resistance to the airflow can be lowered, and with the same ventilation resistance standard as the conventional example, it is possible to increase the density of the flat tube 10 and the fins 7, increasing the heat transfer area and improving heat transfer. The heat exchange capacity can be significantly improved by improving the heat exchange rate and fin efficiency.
また、第７図に本発明の実施例におけるフィン付熱交換
器の偏平管１０の段ピツチＰｄと温度効率及び通風抵抗
との関係について解析した結果を示している。この結果
によれば、偏平管１０の短径１０ｂ方向厚さｔが１〜３
ｍｍで段ピツチＰｄが８〜１２ｍｍのときに気流Ａの通
風抵抗を増大させずに温度効率の最大範囲を得ることが
できる。Further, FIG. 7 shows the results of an analysis of the relationship between the stage pitch Pd of the flat tubes 10 of the finned heat exchanger according to the embodiment of the present invention, the temperature efficiency, and the ventilation resistance. According to this result, the thickness t in the short axis 10b direction of the flat tube 10 is 1 to 3
When the step pitch Pd is 8 to 12 mm in mm, the maximum range of temperature efficiency can be obtained without increasing the ventilation resistance of the air flow A.
以上のように本実施例によれば、波形状に屈曲成形され
一定間隔で平行に並べられたフィン７と、長辺１０ａと
短辺１０ｂに囲まれ中空状に押し出し成形された偏平管
１０とから成り、前記偏平管１０は長辺１０ａ方向相互
を平行にして複数段構成され、その相互間に前記フィン
７が両端の屈曲部８を接して密着され、かつ偏平管１０
の短辺１ｏｂ方向１￥ざｔを１〜３ｍｍの範囲にし、偏
平管の段方向ピッチＰｄを８〜１２ｍｒｎの範囲に限定
することにより、偏平管１０とフィン７の高密度化が図
れ、伝熱面積の増大と熱伝達率の向上及びフィン効率の
向上により大幅な熱交換能力の向上とそのピーク点を得
ることができ、かつ偏平管１０とフィン７の高密度化に
よって生じる気流Ａの通風抵抗の増大を薄型の偏平管１
０の採用によって抑えることができ、従来例と同等通風
抵抗レベルに抑えることができる。また、この効果をフ
ィン付熱交換器の小型化に適用した場合には従来のフィ
ン付熱交換器（円管外径７ ｍ ｍ−段ピッチ２１ｍｒ
ｎ）に比べて容積を約２分の１化できる。As described above, according to this embodiment, the fins 7 are bent into a wave shape and arranged in parallel at regular intervals, and the flat tube 10 is extruded into a hollow shape surrounded by the long side 10a and the short side 10b. The flat tube 10 is composed of a plurality of stages with the long sides 10a parallel to each other, and the fins 7 are closely attached between the stages with the bent portions 8 at both ends in contact with each other, and the flat tube 10
By setting the short side 1ob direction 1\t in the range of 1 to 3 mm and limiting the pitch Pd of the flat tube in the step direction to the range of 8 to 12 mrn, the density of the flat tube 10 and the fins 7 can be increased, and the transmission By increasing the heat area, improving the heat transfer coefficient, and improving the fin efficiency, it is possible to significantly improve the heat exchange ability and obtain its peak point, and the ventilation of the airflow A generated by the high density of the flat tube 10 and the fins 7. Thin flat tube 1 to increase resistance
By adopting 0, the ventilation resistance can be suppressed to the same level as the conventional example. In addition, when this effect is applied to the miniaturization of finned heat exchangers, it is possible to reduce the size of conventional finned heat exchangers (circular tube outer diameter 7 mm, stage pitch 21 mr).
The volume can be reduced to about half compared to (n).
発明の効果
以上のように本発明は、波形状に屈曲成形され一定間隔
で平行に並べられたフィンと、長辺と短辺に囲まれ中空
状に押し出し成形された偏平管とから成り、前記偏平管
は長辺方向相互を平行にして複数段構成され、その相互
間に前記フィンが両端の屈曲部を接して密着され、かつ
偏平管の短辺方向厚さ【を１〜３ｍｍの範囲にし、偏平
管の段方向ピッチＰｄを８〜１２ｍｍの範囲に限定する
ことにより、偏平管と平板フィンの高密度化が図れ、伝
熱面積の増大と熱伝達率の向上及びフィン効率の向上に
より大幅な熱交換能力の向上とそのピーク点を得ること
ができ、かつ偏平管と平板フィンの高密度化によって生
じる気流の通風抵抗の増大を薄型の偏平管の採用によっ
て抑えることができ、従来例と同等通風抵抗レベルに抑
えることができる。また、この効果をフィン付熱交換器
の小型化に適用した場合には従来のフィン付熱交換器に
比べて容積を約２分の１化できる。Effects of the Invention As described above, the present invention consists of fins bent into a wave shape and arranged in parallel at regular intervals, and a flat tube surrounded by a long side and a short side and extruded into a hollow shape. The flat tube has a plurality of stages with the long sides parallel to each other, the fins are closely attached between the stages with the bent portions of both ends in contact, and the thickness of the flat tube in the short side direction is in the range of 1 to 3 mm. By limiting the step pitch Pd of the flat tubes to a range of 8 to 12 mm, the density of the flat tubes and flat fins can be increased, and the heat transfer area, heat transfer coefficient, and fin efficiency are greatly improved. It is possible to improve the heat exchange capacity and its peak point, and by using thin flat tubes, it is possible to suppress the increase in airflow resistance caused by the high density of flat tubes and flat plate fins. It is possible to suppress the ventilation resistance to the same level. Furthermore, when this effect is applied to downsizing a finned heat exchanger, the volume can be reduced to about half that of a conventional finned heat exchanger.
【図面の簡単な説明】
第１図は本発明の実施例におけるフィン付熱交換器の形
状を示す斜視図、第２図は第１図の要部斜視図、第３図
は第１図のフィンの形状を示す平面図、第４図は第１図
の偏平管の形状を示す断面図、第５図は第１図の使用状
態における気流の流動状態を示す断面図、第６図は第１
図の冷媒回路を示す斜視図、第７図は第１図の偏平管の
段ピツチと温度効率及び通風抵抗との関係を示すグラフ
、第８図は従来のフィン付熱交換器の形状を示す斜視図
、第９図は第８図の要部斜視図、第１０図は第８図の平
板フィンの形状を示す平面図、第１１図は第８図の円管
の形状を示す断面図、第１２図は第８図の使用状態にお
ける気流の流動状態を示す断面図、第１３図は第８図の
使用状態における冷媒の流動状態を示す断面図である。
７・・・フィン、８・・・屈曲部、１ｏ・・・偏平管。
代理人の氏名 弁理士 粟野重孝 他１名第
図
第
図
−−−フィン
第
図
第
図
ノｏ−ａｉｎｓｒ−ｖ
０Ｃ
ｑ−ｍ−ルー、ぐ
第
図
１０−−一偏干管
ｊ９ご−ｙｆＰ〆（ｍに）
富
図
第１０図[Brief Description of the Drawings] Fig. 1 is a perspective view showing the shape of a finned heat exchanger in an embodiment of the present invention, Fig. 2 is a perspective view of the main part of Fig. 1, and Fig. 3 is a perspective view of the main part of Fig. 1. FIG. 4 is a plan view showing the shape of the fin, FIG. 4 is a sectional view showing the shape of the flat tube in FIG. 1, FIG. 1
Fig. 7 is a graph showing the relationship between the step pitch of the flat tubes shown in Fig. 1, temperature efficiency, and ventilation resistance; Fig. 8 shows the shape of a conventional finned heat exchanger. 9 is a perspective view of the main part of FIG. 8, FIG. 10 is a plan view showing the shape of the flat fin in FIG. 8, FIG. 11 is a sectional view showing the shape of the circular tube in FIG. 8, FIG. 12 is a cross-sectional view showing the flow state of airflow in the use state shown in FIG. 8, and FIG. 13 is a cross-sectional view showing the flow state of the refrigerant in the use state shown in FIG. 7... Fin, 8... Bent part, 1o... Flat tube. Name of agent: Patent attorney Shigetaka Awano and 1 other person --- Fin diagram diagram o-ainsr-v 0C q-m-ru, gu diagram 10--one-sided pipe j9go-yfP 〆 (to m) Tomizu Figure 10
Claims (1)
ィンと、長辺と短辺に囲まれ中空状に押し出し成形され
た偏平管とから成り、前記偏平管は長辺方向相互を平行
にして複数段構成され、その相互間に前記フィンが両端
の屈曲部を接して密着され、かつ偏平管の短辺方向厚さ
ｔを１〜３ｍｍの範囲にし、偏平管の段方向ピッチＰｄ
を８〜１２ｍｍの範囲にしたことを特徴とするフィン付
熱交換器It consists of fins bent into a wave shape and arranged in parallel at regular intervals, and a flat tube surrounded by long and short sides and extruded into a hollow shape, the flat tubes having their long sides parallel to each other. The fins are in close contact with each other with the bent portions of both ends in contact with each other, and the thickness t of the flat tube in the short side direction is in the range of 1 to 3 mm, and the pitch of the flat tube in the step direction Pd.
A heat exchanger with fins, characterized in that the diameter is in the range of 8 to 12 mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30804188A JPH02154986A (en) | 1988-12-06 | 1988-12-06 | Finned heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30804188A JPH02154986A (en) | 1988-12-06 | 1988-12-06 | Finned heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH02154986A true JPH02154986A (en) | 1990-06-14 |
Family
ID=17976173
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP30804188A Pending JPH02154986A (en) | 1988-12-06 | 1988-12-06 | Finned heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH02154986A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5654764A (en) * | 1993-07-23 | 1997-08-05 | Samsung Electronics Co., Ltd. | Data separating circuit |
| FR2764647A1 (en) * | 1997-06-17 | 1998-12-18 | Valeo Thermique Moteur Sa | ECONOMICAL CONSTRUCTION BOOST AIR COOLER |
| JP2017172956A (en) * | 2016-03-25 | 2017-09-28 | ユニゾン・インダストリーズ，エルエルシー | Heat exchanger |
-
1988
- 1988-12-06 JP JP30804188A patent/JPH02154986A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5654764A (en) * | 1993-07-23 | 1997-08-05 | Samsung Electronics Co., Ltd. | Data separating circuit |
| FR2764647A1 (en) * | 1997-06-17 | 1998-12-18 | Valeo Thermique Moteur Sa | ECONOMICAL CONSTRUCTION BOOST AIR COOLER |
| JP2017172956A (en) * | 2016-03-25 | 2017-09-28 | ユニゾン・インダストリーズ，エルエルシー | Heat exchanger |
| US11215405B2 (en) | 2016-03-25 | 2022-01-04 | Unison Industries, Llc | Heat exchanger with non-orthogonal perforations |
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