JPH03117887A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JPH03117887A JPH03117887A JP25621889A JP25621889A JPH03117887A JP H03117887 A JPH03117887 A JP H03117887A JP 25621889 A JP25621889 A JP 25621889A JP 25621889 A JP25621889 A JP 25621889A JP H03117887 A JPH03117887 A JP H03117887A
- Authority
- JP
- Japan
- Prior art keywords
- passage group
- tubes
- passage
- refrigerant
- group
- 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.)
- Granted
Links
- 230000007423 decrease Effects 0.000 claims abstract description 9
- 238000005192 partition Methods 0.000 claims description 10
- 239000003507 refrigerant Substances 0.000 abstract description 17
- 230000003247 decreasing effect Effects 0.000 abstract description 3
- 239000007788 liquid Substances 0.000 abstract description 2
- 230000005494 condensation Effects 0.000 abstract 1
- 238000009833 condensation Methods 0.000 abstract 1
- 238000010438 heat treatment Methods 0.000 abstract 1
- 239000000203 mixture Substances 0.000 abstract 1
- 239000002699 waste material Substances 0.000 abstract 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 4
- 229910052782 aluminium Inorganic materials 0.000 description 4
- 238000004781 supercooling Methods 0.000 description 3
- 239000000463 material Substances 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 238000005219 brazing Methods 0.000 description 1
- 239000003990 capacitor Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000004519 manufacturing process 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
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
-
- 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
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
この発明は、例えばカーエアコンやルームエアコン等に
用いられる凝縮器あるいは蒸発器等の熱交換器に関する
。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application This invention relates to a heat exchanger such as a condenser or evaporator used in, for example, a car air conditioner or a room air conditioner.
従来の技術
従来、この種の熱交換器として複数本の偏平チューブと
コルゲートフィンとを交互配置に積層すると共に、各チ
ューブの両端を筒状中空ヘッダーに連結し、かつヘッダ
ーに仕切を設けて前記チューブによって構成される全熱
交換媒体通路を複数の通路群に区画し、熱交換媒体が各
通路群を蛇行状に流通するように構成されたものが既知
である。BACKGROUND ART Conventionally, this type of heat exchanger has been constructed by stacking a plurality of flat tubes and corrugated fins in an alternating arrangement, connecting both ends of each tube to a cylindrical hollow header, and providing a partition in the header. It is known that the total heat exchange medium passage constituted by tubes is divided into a plurality of passage groups, and the heat exchange medium is configured to flow through each passage group in a meandering manner.
ところで、凝縮器にあってはその冷媒通路は、冷媒が気
体状態となっている入口側に近い冷媒凝縮部と、冷媒が
液化状態となっている出口側に近い過冷却部とに大別さ
れ、熱交換効率を大きくするためには凝縮部での伝熱面
積を大きく確保する必要があり、過冷却部の伝熱面積は
比較的小さくともかまわない。而して、例えば特開昭６
３−３４４６６号に示されるように、ヘッダーの仕切位
置を適宜設定して各通路群を構成するチューブ本数を代
えることにより、通路群の通路断面積を入口側から出口
側に向って減少させたものが提案されている。By the way, the refrigerant passage in a condenser is roughly divided into a refrigerant condensing section near the inlet side where the refrigerant is in a gaseous state, and a supercooling section near the outlet side where the refrigerant is in a liquefied state. In order to increase the heat exchange efficiency, it is necessary to ensure a large heat transfer area in the condensing part, and the heat transfer area in the supercooling part may be relatively small. For example, JP-A No. 6
As shown in No. 3-34466, by appropriately setting the partition position of the header and changing the number of tubes constituting each passage group, the passage cross-sectional area of the passage group is reduced from the inlet side to the outlet side. something is proposed.
発明が解決しようとする課題
しかしながら、上記のような熱交換器にあっては、各通
路群の通路断面積をチューブの本数によって設定するも
のであったため、各通路群の通路断面積を各チューブの
チューブ断面積毎に段階的にしか変更することができず
、各通路群に要求される必要かつ十分な通路断面積を微
妙に調整できないとか、あるいはパス回数を多く設定し
ようとして仕切部の数を増やすと必要最少限の通路断面
積をも確保できなくなり圧力損失が増大し結局バス回数
を制限せざるを得ない等の不都合が生じる。このような
ことより、熱交換効率が最も高い最適状態には必ずしも
設定しうるちのではなかった。Problems to be Solved by the Invention However, in the heat exchanger as described above, the passage cross-sectional area of each passage group is set by the number of tubes. The cross-sectional area of each tube can only be changed in stages, and the necessary and sufficient passage cross-sectional area required for each passage group cannot be finely adjusted, or the number of partitions may be changed in an attempt to increase the number of passes. If the number of buses is increased, it becomes impossible to secure even the minimum required cross-sectional area of the passage, resulting in an increase in pressure loss, resulting in inconveniences such as having to limit the number of baths. For these reasons, it has not always been possible to set the optimum state with the highest heat exchange efficiency.
この発明は、上述のような問題点に鑑みてなされたもの
で、より一層熱交換効率の向上された熱交換器を提供す
ることを目的とするものである。This invention was made in view of the above-mentioned problems, and an object thereof is to provide a heat exchanger with further improved heat exchange efficiency.
課題を解決するための手段
而して、この発明は、各通路群の通路断面積の設定をチ
ューブ本数によって決定するのではなく、各通路群を構
成するチューブとして通路断面積が異なるものを採用す
ることにより上記問題点を解消したものである。As a means to solve the problem, the present invention does not determine the setting of the passage cross-sectional area of each passage group by the number of tubes, but employs tubes having different passage cross-sectional areas as the tubes constituting each passage group. This solves the above problem.
即ち、この発明は、複数本の偏平チューブとコルゲート
フィンとが交互配置に積層されると共に、前記チューブ
の両端に中空ヘッダーが連通接続され、かつ該ヘッダー
に仕切部が設けられることにより、前記チューブによっ
て構成される熱交換媒体通路が複数の通路群に区画され
、熱交換媒体を少なくとも１回以上蛇行させて流通する
ように構成されると共に、少なくとも入口側通路群と出
口側通路群とでチューブ断面積が異なるチューブが用い
られることにより、各通路群の通路断面積が入口側から
出口側に向って熱交換媒体の体積減少または体積増加に
応じて減少または増加されてなることを特徴とする熱交
換器を要旨とするものである。That is, in the present invention, a plurality of flat tubes and corrugated fins are stacked in an alternating arrangement, hollow headers are connected to both ends of the tubes, and partitions are provided in the headers, so that the tubes The heat exchange medium passage constituted by the tube is divided into a plurality of passage groups, and the heat exchange medium is configured to meander at least once and circulate, and at least the inlet side passage group and the outlet side passage group By using tubes with different cross-sectional areas, the passage cross-sectional area of each passage group decreases or increases from the inlet side to the outlet side in accordance with the decrease or increase in volume of the heat exchange medium. This article focuses on heat exchangers.
前記チューブとして、少なくとも入口側通路群と出口側
通路群とでチューブ幅が異なるものを用いても良いし、
またチューブ高さが異なるものを用いても良い。The tube may have a different width between at least the inlet side passage group and the outlet side passage group, or
Also, tubes with different heights may be used.
作用
各通路群の通路断面積が入口側から出口側に向って熱交
換媒体の体積減少または体積増加に応じて減少または増
加されているから、圧力損失が低減されると共に、熱交
換効率が向上する。Function: Since the passage cross-sectional area of each passage group decreases or increases from the inlet side to the outlet side in accordance with the decrease or increase in volume of the heat exchange medium, pressure loss is reduced and heat exchange efficiency is improved. do.
しかも、通路群の通路断面積の減少、増大を断面積の異
なるチューブを採用することにより達成していることよ
り、通路群の通路断面積の調整をチューブ本数を変更す
ることにより行う場合と較べて容易かつ微妙に行うこと
ができ、また仕切部の位置、各通路群の数あるいは幅を
最適な状態に設定する°ことができる。Moreover, since the passage cross-sectional area of the passage group can be reduced or increased by using tubes with different cross-sectional areas, it is easier to adjust the passage cross-sectional area of the passage group by changing the number of tubes. This can be done easily and delicately, and the position of the partition, the number or width of each passage group can be set to the optimum state.
実施例
以下、この発明を、カーエアコン用のコンデンサに適用
した実施例に基づいて説明する。EXAMPLE The present invention will be described below based on an example in which the present invention is applied to a capacitor for a car air conditioner.
なお、この明細書において、アルミニウムの語はアルミ
ニウム合金を含む意味において使用する。In this specification, the term aluminum is used to include aluminum alloys.
第１図ないし第４図において、（１）は水平状態で上下
方向に配置された複数のチューブ、（２）はその隣接す
るチューブ（１）（１）間に介在されたコルゲートフィ
ンである。In FIGS. 1 to 4, (1) is a plurality of tubes arranged vertically in a horizontal state, and (2) is a corrugated fin interposed between adjacent tubes (1).
チューブ（１）はアルミニウム材による押出型材からな
るもので、いわゆるハーモニカチューブと称されるよう
な多孔型のものを用いても良い。また押出型材によらず
電縫管を用いても良い。The tube (1) is made of an extruded aluminum material, and a porous type such as a so-called harmonica tube may be used. Furthermore, an electric resistance welded tube may be used instead of the extruded material.
コルゲートフィン（２）は、同じくアルミニウム製のも
ので、ろう付によりチューブ（１）に接合されている。The corrugated fin (2) is also made of aluminum and is joined to the tube (1) by brazing.
コルゲートフィン（２）は、望ましくはルーバー（２ａ
）を切り起こしたものを用いるのが良い。The corrugated fin (2) preferably has a louver (2a
) is better to use.
（３）（４）は断面円形の左右のアルミニウム製中空ヘ
ッダーであり、前記各チューブ（１）の両端に連通接続
されたものである。かつ左右ヘッダー（３）（４）の上
端は上部蓋体（５）（５）により、また下端は下部蓋体
（６）（６）によりそれぞれ閉塞されている。(3) and (4) are left and right aluminum hollow headers with a circular cross section, which are connected to both ends of each tube (1). The upper ends of the left and right headers (3) (4) are closed by upper lid bodies (5) (5), and the lower ends are closed by lower lid bodies (6) (6), respectively.
更に、左ヘッダー（３）の外側上部には熱交換媒体入口
管（７）が連結される一方、同ヘッダー（３）の外側下
部には同出口管（８）が連結されている。上記出入口管
（７）（８）は、差し込み端部側のヘッダー当接面がヘ
ッダー（３）（４）に沿接する対応形状に形成されてお
り、仮組状態において容易に位置決めができると共に、
ヘッダー（３）（４）との接触面積が増大されることに
よって、より一層強固に接合しうるようになされている
。また、第１図に示すように、左ヘッダー（３）の長手
方向中間部に該ヘッダー（３）を上下２室に分割する仕
切板（９）が設けられ前記チューブによって構成される
全熱交換媒体通路が上下２段の通路群（Ａ）（Ｂ）に区
画され、熱交換媒体が各通路群（Ａ）（Ｂ）をＵターン
状に流通して熱交換媒体出口管（８）から流出し、この
間に、チューブ（１）間に形成されたコルゲートフィン
（２）を含む空気流通間隙を流通する空気と熱交換を行
い、凝縮するものとなされている。Further, a heat exchange medium inlet pipe (7) is connected to the upper outer side of the left header (3), while an outlet pipe (8) is connected to the lower outer side of the left header (3). The inlet/outlet pipes (7) and (8) are formed in a corresponding shape so that the header abutment surface on the insertion end side is in contact with the headers (3) and (4), and can be easily positioned in the temporarily assembled state.
By increasing the contact area with the headers (3) and (4), it is possible to bond even more firmly. Further, as shown in Fig. 1, a partition plate (9) is provided at the longitudinally intermediate portion of the left header (3) to divide the header (3) into two upper and lower chambers, and a total heat exchanger configured by the tubes is provided. The medium passage is divided into two upper and lower passage groups (A) and (B), and the heat exchange medium flows through each passage group (A) and (B) in a U-turn shape and flows out from the heat exchange medium outlet pipe (8). However, during this time, heat is exchanged with the air flowing through the air circulation gap including the corrugated fins (2) formed between the tubes (1), and the air is condensed.
なお、第１図に示す（１０） （１１）は最外側のコ
ルゲートフィン（２）の外側に配置された上下のサイド
プレートである。Note that (10) and (11) shown in FIG. 1 are upper and lower side plates arranged on the outside of the outermost corrugated fin (2).
上述の構成は従来の凝縮器と同様であるが、この実施例
にかかる凝縮器にあっては、冷媒入口側（上段）の通路
群（Ａ）を構成する前記チューブ（１）の幅（Ｗ）が、
冷媒出口側（下段）の通路群（Ｂ）を構成する前記チュ
ーブ（１）の幅（Ｗ）より大に設定されている。The above-mentioned configuration is similar to the conventional condenser, but in the condenser according to this embodiment, the width (W) of the tube (1) constituting the passage group (A) on the refrigerant inlet side (upper stage) )but,
The width (W) is set larger than the width (W) of the tube (1) constituting the passage group (B) on the refrigerant outlet side (lower stage).
而して上段の通路群（Ａ）を通過する冷媒は未だ体積の
大きいガス化状態にあるが、該通路群（Ａ）を構成する
チューブ（１）として幅広状のものを用いているので、
伝熱面積が大きいものとなされており効率良く冷媒の凝
縮が行われる。下段の通路群（Ｂ）を通過する冷媒は一
部が液化された気液混合状態ないしは液化状態を呈し体
積も小さくなっているから通路断面積も小さくて良いが
、これに応じて下段の通路断面積は上段のそれよりも小
に設定されているので、冷媒を通過させるのにスペース
の無駄がなくなる。このように凝縮部に相当する入口側
通路群（Ａ）から過冷却部に相当する出口側通路群（Ｂ
）へと至るに従って、各通路群の通路断面積を小さくす
ることによって、効率の良い熱交換が行われることにな
る。The refrigerant passing through the upper passage group (A) is still in a gasified state with a large volume, but since the tubes (1) constituting the passage group (A) are wide-shaped,
The heat transfer area is large, and the refrigerant is efficiently condensed. The refrigerant passing through the lower passage group (B) is partially liquefied in a gas-liquid mixed state or in a liquefied state, and the volume is small, so the cross-sectional area of the passage may be small. Since the cross-sectional area is set smaller than that of the upper stage, no space is wasted in passing the refrigerant. In this way, from the inlet side passage group (A) corresponding to the condensing section to the outlet side passage group (B) corresponding to the supercooling section.
), efficient heat exchange is performed by reducing the passage cross-sectional area of each passage group.
第５図は他の実施例を示すもので、上記実施例と略同様
であるが、左右のヘッダーがそれぞれ上下に２分割され
、左側の上下両ヘッダー（３）（３）が連結仕切部材（
１２）を介して接続される一方、右側の上下両ヘッダー
（４）（４）が連通状態に接続されている。このような
構造を採用することにより、製造能率の向上を図ること
ができるのである。他の構成は上記実施例と同様である
ので対応箇所に同一符号を付して説明を省略する。FIG. 5 shows another embodiment, which is almost the same as the above embodiment, but the left and right headers are divided into two vertically, and both the upper and lower left headers (3) (3) are connected to the connecting partition member (3).
12), while both the upper and lower headers (4) on the right side (4) are connected in communication. By adopting such a structure, manufacturing efficiency can be improved. Since the other configurations are the same as those of the above embodiment, corresponding parts are given the same reference numerals and explanations will be omitted.
第６図は更に他の実施例を示すものであり、前記両実施
例と同様に入口側通路群（Ａ）の通路断面積の方が出口
側通路群（Ｂ）のそれより大きく設定されているが、こ
の実施例においては上段の通路群（Ａ）のチューブ（１
）のチューブ高さ（Ｈ）が下段のそれよりも高く設定さ
れている。他の構成は第１の実施例と同様であるので対
応箇所に同一符号を付して説明を省略する。FIG. 6 shows still another embodiment, in which the passage cross-sectional area of the inlet side passage group (A) is set larger than that of the outlet side passage group (B), as in both of the above embodiments. However, in this embodiment, the tube (1) of the upper passage group (A)
) is set higher than that of the lower tube. Since the other configurations are the same as those of the first embodiment, corresponding parts are given the same reference numerals and explanations will be omitted.
なお、以上の実施例においては、入口側（上段）の通路
群の通路断面積の方が出口側（下段）の通路群のそれよ
り大に設定したものを示したが、蒸発器の場合にあって
は逆に出口側通路群の通路断面積の方を入口側のそれよ
り大に設定することはいうまでもない。In the above embodiments, the passage cross-sectional area of the passage group on the inlet side (upper stage) was set larger than that of the passage group on the outlet side (lower stage), but in the case of an evaporator, On the contrary, it goes without saying that the passage cross-sectional area of the exit-side passage group is set larger than that of the entrance-side passage group.
また、上記実施例においては、余熱交換媒体通路が上下
２段に区画されたものを示したが、３段以上に区画され
たものであってもこの発明は適用され得る。３段以上に
区画されたものにあっては、通路群の通路断面積を入口
側から出口側に向って熱交換媒体の体積減少または体積
増加に応じて減少または増加せしめれば良いが、必ずし
も全ての通路群の通路断面積を段階的に減少または増加
させなくても良く、任意の１または２以上の通路群毎に
通路断面積を減少させあるいは増加させるようにしても
良い。Further, in the above embodiment, the residual heat exchange medium passage is divided into two stages, upper and lower, but the present invention can be applied even if the residual heat exchange medium passage is divided into three or more stages. For those partitioned into three or more stages, the cross-sectional area of the passage group may be reduced or increased from the inlet side to the outlet side in accordance with the decrease or increase in volume of the heat exchange medium, but it is not necessary. It is not necessary to reduce or increase the passage cross-sectional area of all the passage groups in a stepwise manner, and the passage cross-sectional area may be decreased or increased for each arbitrary one or more passage groups.
発明の効果
この発明にかかる熱交換器は、上述のとおり、各通路群
の通路断面積が入口側から出口側に向って熱交換媒体の
体積減少または体積増加に応じて減少または増加されて
いるから、圧力損失が低減されると共に、熱交換効率が
向上する。Effects of the Invention As described above, in the heat exchanger according to the present invention, the passage cross-sectional area of each passage group is decreased or increased from the inlet side to the outlet side in accordance with the decrease or increase in volume of the heat exchange medium. Therefore, pressure loss is reduced and heat exchange efficiency is improved.
しかも、通路群の通路断面積の減少、増加を断面積の異
なるチューブを採用することにより達成していることよ
り、各通路群の通路断面積の調整をチューブ本数を変更
することにより行う場合と較べて各通路群毎に要求され
る必要かつ十分な通路断面積の設定を容易かつ微妙に行
うことができ、また仕切部の位置、通路群の数（ターン
回数）あるいは通路群の幅にかかわらず、各通路群の通
路断面積を任意に設定することができるので熱交換効率
の最も高い最適状態に設定することができる。従って、
小型でありながら、極めて効率の高い熱交換器を提供す
ることができる。Furthermore, since the passage cross-sectional area of each passage group can be reduced or increased by using tubes with different cross-sectional areas, it is possible to adjust the passage cross-sectional area of each passage group by changing the number of tubes. In comparison, it is possible to easily and delicately set the necessary and sufficient passage cross-sectional area required for each passage group, and regardless of the position of the partition, the number of passage groups (number of turns), or the width of the passage group. First, since the passage cross-sectional area of each passage group can be set arbitrarily, it can be set to the optimum state with the highest heat exchange efficiency. Therefore,
Although the heat exchanger is small, it is possible to provide an extremely efficient heat exchanger.
図面はこの発明の実施例を示すもので、第１図は熱交換
器の全体正面図、第２図は同平面図、第３図は第１図■
−■線の拡大断面図、第４図は分解状態を示す部分斜視
図、第５図は他の実施例を示すもので分解状態を示す全
体斜視図、第６図は更に他の実施例を示すもので第３図
に対応する断面図である。
（１）・・・チューブ、（２）・・・コルゲートフィン
、（３）（４）・・・ヘッダー （９）・・・仕ｔｌ、
（Ａ）（Ｂ）・・・熱交換媒体通路群、（Ｈ）・・・チ
ューブ高さ、（Ｗ）・・・チューブ幅。
以上
］］
第３図
第６図The drawings show an embodiment of the present invention, and FIG. 1 is an overall front view of the heat exchanger, FIG. 2 is a plan view of the same, and FIG. 3 is similar to FIG.
4 is a partial perspective view showing an exploded state, FIG. 5 is an overall perspective view showing another embodiment and is an exploded state, and FIG. 6 is an enlarged sectional view of another embodiment. FIG. 4 is a sectional view corresponding to FIG. 3; (1)...tube, (2)...corrugate fin, (3)(4)...header (9)...partition tl,
(A) (B)... Heat exchange medium passage group, (H)... Tube height, (W)... Tube width. Above] Figure 3 Figure 6
Claims (3)
互配置に積層されると共に、前記チューブの両端に中空
ヘッダーが連通接続され、かつ該ヘッダーに仕切部が設
けられることにより、前記チューブによって構成される
熱交換媒体通路が複数の通路群に区画され、熱交換媒体
を少なくとも１回以上蛇行させて流通するように構成さ
れると共に、少なくとも入口側通路群と出口側通路群と
でチューブ断面積が異なるチューブが用いられることに
より、各通路群の通路断面積が入口側から出口側に向っ
て熱交換媒体の体積減少または体積増加に応じて減少ま
たは増加されてなることを特徴とする熱交換器。(1) A plurality of flat tubes and corrugated fins are laminated in an alternating arrangement, hollow headers are connected to both ends of the tubes, and partitions are provided in the headers, so that the structure is made up of the tubes. The heat exchange medium passages are divided into a plurality of passage groups, and the heat exchange medium is configured to meander at least once and circulate, and the tube cross-sectional area is equal to at least the inlet side passage group and the outlet side passage group. A heat exchanger characterized in that, by using different tubes, the passage cross-sectional area of each passage group decreases or increases from the inlet side to the outlet side in accordance with the decrease or increase in volume of the heat exchange medium. .
側通路群とでチューブ幅が異なるものであることを特徴
とする請求項（１）記載の熱交換器。(2) The heat exchanger according to claim 1, wherein the tubes have different tube widths at least between the inlet side passage group and the outlet side passage group.
側通路群とでチューブ高さが異なるものであることを特
徴とする請求項（１）記載の熱交換器。(3) The heat exchanger according to claim 1, wherein the tubes have different heights at least between the inlet side passage group and the outlet side passage group.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1256218A JP2891486B2 (en) | 1989-09-29 | 1989-09-29 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1256218A JP2891486B2 (en) | 1989-09-29 | 1989-09-29 | Heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03117887A true JPH03117887A (en) | 1991-05-20 |
| JP2891486B2 JP2891486B2 (en) | 1999-05-17 |
Family
ID=17289575
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1256218A Expired - Fee Related JP2891486B2 (en) | 1989-09-29 | 1989-09-29 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2891486B2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100825709B1 (en) * | 2001-09-29 | 2008-04-29 | 한라공조주식회사 | Heat exchanger |
| JP2010112580A (en) * | 2008-11-04 | 2010-05-20 | Daikin Ind Ltd | Heat exchanger |
| US7751197B2 (en) | 2008-11-20 | 2010-07-06 | Kabushiki Kaisha Toshiba | Fastening device, module mounting mechanism and information processing apparatus |
| JP2010151426A (en) * | 2008-12-26 | 2010-07-08 | Calsonic Kansei Corp | Heat exchanger |
| JP2012077976A (en) * | 2010-09-30 | 2012-04-19 | Daikin Industries Ltd | Solar heat collector and hot water supply system |
| JP2017099611A (en) * | 2015-12-01 | 2017-06-08 | 東芝ライフスタイル株式会社 | Clothes dryer |
| JP2021025748A (en) * | 2019-08-08 | 2021-02-22 | 株式会社Uacj | Heat exchanger and air conditioner |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6334466A (en) * | 1986-07-29 | 1988-02-15 | 昭和アルミニウム株式会社 | Condenser |
| JPS63179476U (en) * | 1987-05-07 | 1988-11-21 |
-
1989
- 1989-09-29 JP JP1256218A patent/JP2891486B2/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6334466A (en) * | 1986-07-29 | 1988-02-15 | 昭和アルミニウム株式会社 | Condenser |
| JPS63179476U (en) * | 1987-05-07 | 1988-11-21 |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100825709B1 (en) * | 2001-09-29 | 2008-04-29 | 한라공조주식회사 | Heat exchanger |
| JP2010112580A (en) * | 2008-11-04 | 2010-05-20 | Daikin Ind Ltd | Heat exchanger |
| US7751197B2 (en) | 2008-11-20 | 2010-07-06 | Kabushiki Kaisha Toshiba | Fastening device, module mounting mechanism and information processing apparatus |
| JP2010151426A (en) * | 2008-12-26 | 2010-07-08 | Calsonic Kansei Corp | Heat exchanger |
| JP2012077976A (en) * | 2010-09-30 | 2012-04-19 | Daikin Industries Ltd | Solar heat collector and hot water supply system |
| JP2017099611A (en) * | 2015-12-01 | 2017-06-08 | 東芝ライフスタイル株式会社 | Clothes dryer |
| JP2021025748A (en) * | 2019-08-08 | 2021-02-22 | 株式会社Uacj | Heat exchanger and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2891486B2 (en) | 1999-05-17 |
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| LAPS | Cancellation because of no payment of annual fees |