JPH06317363A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JPH06317363A JPH06317363A JP10698993A JP10698993A JPH06317363A JP H06317363 A JPH06317363 A JP H06317363A JP 10698993 A JP10698993 A JP 10698993A JP 10698993 A JP10698993 A JP 10698993A JP H06317363 A JPH06317363 A JP H06317363A
- Authority
- JP
- Japan
- Prior art keywords
- header
- refrigerant
- flat tube
- split
- pipe
- 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
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
- F28D1/047—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 bent, e.g. in a serpentine or zig-zag
- F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
- F28D1/0478—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
- F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、例えばカー・エアコ
ンの蒸発器として使用される熱交換器に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger used as an evaporator for car air conditioners, for example.
【０００２】[0002]
【従来の技術】従来、この種熱交換器としては、複数の
冷媒通路を有する蛇行状偏平管と、これの各直管部同士
の間に介在されたコルゲートフィンと、偏平管の両端部
にそれぞれ接続された有底筒形の入口および出口ヘッダ
とを備えているものが知られている。2. Description of the Related Art Heretofore, as this kind of heat exchanger, a meandering flat pipe having a plurality of refrigerant passages, corrugated fins interposed between straight pipe portions of the flat pipe, and both end portions of the flat pipe have been used. It is known that each has a bottomed tubular inlet and outlet header connected to it.
【０００３】[0003]
【発明が解決しようとする課題】上記従来の熱交換器で
は、強制送風により冷媒通路と直交状に風が流される
が、風上側の冷媒通路では熱負荷が大きくて冷媒の蒸発
が早くかつ冷媒の蒸発量が多く、これとは逆に風下側の
冷媒通路では熱負荷が小さくて冷媒の蒸発量が少ないた
めに、全体として熱交換効率がよくないという問題があ
った。しかも、蒸発器出口における冷媒が不安定とな
り、冷媒流量の制御を行う膨張弁の開閉が頻繁となる不
安定状態（ハンチング現象）が起こるという問題もあっ
た。In the above conventional heat exchanger, forced air blows air in a direction orthogonal to the refrigerant passage, but in the refrigerant passage on the windward side, the heat load is large and the refrigerant evaporates quickly and the refrigerant However, there is a problem that the heat exchange efficiency is not good as a whole because the heat load is small in the leeward side refrigerant passage and the evaporation amount of the refrigerant is small. Moreover, the refrigerant at the outlet of the evaporator becomes unstable, and an unstable state (hunting phenomenon) occurs in which the expansion valve that controls the refrigerant flow rate is opened and closed frequently.
【０００４】そこで、偏平管の長さの中間部に、風の流
れ方向に長い直方体状箱形の中間ヘッダを設け、中間ヘ
ッダにおいて各冷媒通路を通過してきた温度差のある冷
媒を混合した後、再び冷媒通路に分配することにより、
各通路を流れる冷媒の蒸発器出口での温度差を小さくす
ることも提案されている（特開昭６０−１４００９７号
公報参照）。Therefore, a rectangular parallelepiped box-shaped intermediate header, which is long in the direction of air flow, is provided in the middle of the length of the flat tube, and after mixing the refrigerants having different temperatures which have passed through the respective refrigerant passages in the intermediate header. , By distributing again to the refrigerant passage,
It has also been proposed to reduce the temperature difference at the evaporator outlet of the refrigerant flowing through each passage (see JP-A-60-140097).
【０００５】しかしながら、上記の提案では、中間ヘッ
ダの２つの偏平管端部嵌入用開口とコルゲート・フィン
が介在された状態の２つの偏平管端部とを嵌め合わせた
後、接合する必要があり、この作業が面倒で製造しにく
いという問題があった。However, in the above proposal, it is necessary to fit the two flat tube end fitting openings of the intermediate header and the two flat tube end parts with the corrugated fins interposed therebetween, and then to join them. There was a problem that this work was troublesome and difficult to manufacture.
【０００６】この発明の目的は、各通路を流れる冷媒の
蒸発器出口での温度差を小さくすることにより、熱交換
効率を向上させかつ膨張弁を安定させて制御を容易に
し、しかも製造もしやすい熱交換器を提供することにあ
る。An object of the present invention is to improve the heat exchange efficiency and stabilize the expansion valve by facilitating the control by facilitating the control by reducing the temperature difference of the refrigerant flowing through each passage at the evaporator outlet. It is to provide a heat exchanger.
【０００７】[0007]
【課題を解決するための手段】この発明による熱交換器
は、複数の冷媒通路を有する蛇行状偏平管と、これの各
直管部同士の間に介在されたコルゲートフィンと、偏平
管の両端部にそれぞれ接続された有底筒形の入口および
出口ヘッダとを備えている熱交換器であって、蛇行状偏
平管が長さの中間部において２つに分割されており、入
口ヘッダを有する蛇行状第１分割偏平管の他端部に有底
筒形の第１中間ヘッダが接続されるとともに、出口ヘッ
ダを有する蛇行状第２分割偏平管の他端部に有底筒形の
第２中間ヘッダが接続されて、第１および第２中間ヘッ
ダが略平行状に配置され、第１および第２中間ヘッダ
に、両者を連結する連結管が接続されているものであ
る。A heat exchanger according to the present invention comprises a meandering flat pipe having a plurality of refrigerant passages, corrugated fins interposed between the straight pipe portions of the flat pipe, and both ends of the flat pipe. A heat exchanger having a bottomed tubular inlet and outlet headers each connected to a section, the serpentine flat tube being divided into two in the middle of the length and having an inlet header A bottomed tubular first intermediate header is connected to the other end of the serpentine first split flat tube, and a bottomed tubular second intermediate header is connected to the other end of the serpentine second split flat tube having an outlet header. The intermediate header is connected, the first and second intermediate headers are arranged in a substantially parallel shape, and a connecting pipe that connects them is connected to the first and second intermediate headers.
【０００８】[0008]
【作用】この発明による熱交換器は、蛇行状偏平管が長
さの中間部において２つに分割されており、入口ヘッダ
を有する蛇行状第１分割偏平管の他端部に有底筒形の第
１中間ヘッダが接続されるとともに、出口ヘッダを有す
る蛇行状第２分割偏平管の他端部に有底筒形の第２中間
ヘッダが接続されて、第１および第２中間ヘッダが略平
行状に配置され、第１および第２中間ヘッダに、両者を
連結する連結管が接続されているものであるから、各冷
媒通路を流れてきた温度差のある冷媒は、第１中間ヘッ
ダ、連結管および第２中間ヘッダを通る間に混合された
後、各冷媒通路に分かれて流れていく。In the heat exchanger according to the present invention, the meandering flat tube is divided into two in the middle portion of the length, and the other end of the meandering first split flat tube having the inlet header has a bottomed cylindrical shape. The first intermediate header is connected, and the second intermediate header having a bottomed cylindrical shape is connected to the other end of the meandering second split flat tube having the outlet header, and the first and second intermediate headers are substantially Since the first and second intermediate headers are arranged in parallel and the connecting pipes that connect them are connected to each other, the refrigerant having a temperature difference flowing through each refrigerant passage is After being mixed while passing through the connecting pipe and the second intermediate header, they are divided into respective refrigerant passages and flow.
【０００９】第１および第２中間ヘッダは出入口ヘッダ
と同形状の有底筒形であるため、各中間ヘッダと各分割
偏平管との接合は、出入口ヘッダを偏平管に接合するの
と同様の方法により行え、接合作業を容易に行うことが
できる。Since the first and second intermediate headers have a bottomed cylindrical shape having the same shape as the inlet / outlet header, the joining of the intermediate headers and the divided flat tubes is similar to joining the inlet / outlet headers to the flat tubes. It can be performed by a method and the joining work can be easily performed.
【００１０】[0010]
【実施例】この発明の実施例を、以下図面を参照して説
明する。以下の説明において、左右は図２の左右をい
い、前後については、図２の上を前、下を後というもの
とする。Embodiments of the present invention will be described below with reference to the drawings. In the following description, the left and right refer to the left and right in FIG. 2, and the front and back refer to the top of FIG. 2 as the front and the bottom as the rear.
【００１１】図１および図２は、この発明の熱交換器を
カー・エアコンの蒸発器として使用する場合の第１実施
例を示しており、蒸発器(1) は、横形のもので、複数の
冷媒通路(9) を有するアルミニウム押出形材製蛇行状偏
平管(2) と、偏平管(2) の各水平直管部(2a)の間にろう
接されて介在されたルーバ付アルミニウム薄板製コルゲ
ートフィン(3) と、偏平管(2) の両端部にそれぞれ接続
された有底筒形の入口および出口ヘッダ(4)(5)とを備え
ており、強制送風により前から後に向かって風が流され
るものである。FIGS. 1 and 2 show a first embodiment in which the heat exchanger of the present invention is used as an evaporator of a car air conditioner. The evaporator (1) is a horizontal type, and a plurality of evaporators (1) are provided. Aluminum thin plate with louver interposed by brazing between each flat straight tube (2a) of the flat tube (2) and the meandering flat tube (2) made of extruded aluminum having the refrigerant passage (9) It is equipped with corrugated fins (3) and bottomed cylindrical inlet and outlet headers (4) and (5) connected to both ends of the flat tube (2). The wind is swept away.
【００１２】蛇行状偏平管(2) は、蒸発器(1) の高さの
中央よりも若干下において偏平管(2) の左の屈曲部が取
り除かれ、入口ヘッダ(4) を有する上部の蛇行状第１分
割偏平管(10)と、出口ヘッダ(5) を有する下部の蛇行状
第２分割偏平管(11)とに分割されている。The meandering flat tube (2) is slightly below the center of the height of the evaporator (1), the left bend of the flat tube (2) is removed and the upper header with the inlet header (4) is removed. It is divided into a serpentine first split flat tube (10) and a lower serpentine second split flat tube (11) having an outlet header (5).
【００１３】第１分割偏平管(10)の分割側の端部に有底
筒形の第１中間ヘッダ(12)が接続され、第２分割偏平管
(11)の分割側の端部に有底筒形の第２中間ヘッダ(13)が
接続されている。第１中間ヘッダ(12)と第２中間ヘッダ
(13)とは、略平行状であり、後側（風下側）においてＵ
字形の連結管(14)により連結されている。A first intermediate header (12) having a bottomed cylindrical shape is connected to an end portion of the first split flat tube (10) on the split side, and a second split flat tube (10) is connected.
A bottomed cylindrical second intermediate header (13) is connected to the end of the split side of (11). First intermediate header (12) and second intermediate header
(13) is almost parallel and U on the rear side (leeward side)
They are connected by a character-shaped connecting pipe (14).
【００１４】蛇行状第２分割偏平管(11)は下方に蛇行し
た後、蒸発器(1) の右下において折り曲げられ、蒸発器
(1) の右上に位置させられている出口ヘッダ(5) までの
びている。入口ヘッダ(4) は、出口ヘッダ(5) のすぐ内
側に出口ヘッダ(5) と平行となるように位置させられて
いる。入口ヘッダ(4) の後端の開口に入口管(7) が、出
口ヘッダ(5) の前端の開口に出口管(8) がそれぞれ接続
されている。入口管(7) は折り返されており、出口管
(8) と同じ方向にのびている。After the meandering second split flat tube (11) meanders downward, it is bent at the lower right of the evaporator (1) to form an evaporator.
It extends to the exit header (5) located in the upper right corner of (1). The inlet header (4) is positioned just inside the outlet header (5) and parallel to the outlet header (5). The inlet pipe (7) is connected to the opening at the rear end of the inlet header (4), and the outlet pipe (8) is connected to the opening at the front end of the outlet header (5). The inlet pipe (7) is folded back and the outlet pipe
It extends in the same direction as (8).
【００１５】第２分割偏平管(11)の左縁部は、第１分割
偏平管(10)の左縁部より内側に、第１中間ヘッダ(12)は
蒸発器(1) の左縁よりも内側に、第２中間ヘッダ(13)は
第１中間ヘッダ(12)よりもさらに内側にあり、蒸発器
(1) の左下の部分が若干凹まされている。この凹まされ
ている位置を種々変更することにより、蒸発器(1) を自
動車のエンジンルーム内に配置するさい、他の部品と干
渉することを防止することができる。The left edge of the second split flat tube (11) is inside the left edge of the first split flat tube (10), and the first intermediate header (12) is from the left edge of the evaporator (1). Inside, the second intermediate header (13) is further inside than the first intermediate header (12),
The lower left part of (1) is slightly recessed. By changing the recessed position variously, it is possible to prevent the evaporator (1) from interfering with other parts when the evaporator (1) is arranged in the engine room of the automobile.
【００１６】第１分割偏平管(10)と第１中間ヘッダ(12)
との接合および第２分割偏平管(11)と第２中間ヘッダ(1
3)との接合は、ろう付けにより行われている。このろう
付けは、入口および出口ヘッダ(4)(5)を偏平管(2) に接
合するのと同様であり、非常に容易に行うことができ、
かつ冷媒の漏れに対する信頼性も高い。第１中間ヘッダ
(12)および第２中間ヘッダ(13)と連結管(14)との接合
は、アーク溶接により行われている。この溶接は、入口
ヘッダ(4) と入口管(7) との接合と同様であり、非常に
容易に行うことができ、かつ冷媒の漏れに対する信頼性
も高い。The first split flat tube (10) and the first intermediate header (12)
And the second split flat tube (11) and the second intermediate header (1
3) is joined by brazing. This brazing is similar to joining the inlet and outlet headers (4) (5) to the flat tubes (2) and can be done very easily,
Moreover, the reliability against leakage of the refrigerant is high. First intermediate header
The joining between the (12) and the second intermediate header (13) and the connecting pipe (14) is performed by arc welding. This welding is similar to the joining of the inlet header (4) and the inlet pipe (7), can be performed very easily, and has high reliability against refrigerant leakage.
【００１７】上記構成の蒸発器(1) では、冷媒は各冷媒
通路(9) を通過する間に蒸発して熱交換が行われる。冷
媒の蒸発作用は熱負荷が大きい風上側ほど活発であるた
め、第１分割偏平管(10)の分割側の端部近くにおいて
は、風上側の冷媒通路(9) を流れる冷媒と風下側の冷媒
通路(9) を流れる冷媒との間に温度差が生じてくる。そ
して、温度差のある冷媒は、第１中間ヘッダ(12)、連結
管(14)および第２中間ヘッダ(13)を通る間に混合され均
一な温度になった後、各冷媒通路(9) に分かれて流れて
いく。In the evaporator (1) having the above structure, the refrigerant evaporates and exchanges heat while passing through the respective refrigerant passages (9). Since the evaporating action of the refrigerant is more active on the windward side where the heat load is larger, the refrigerant flowing in the refrigerant passage (9) on the windward side and on the leeward side near the split end of the first split flat tube (10). A temperature difference occurs between the refrigerant flowing through the refrigerant passage (9) and the refrigerant. Then, the refrigerants having different temperatures are mixed while passing through the first intermediate header (12), the connecting pipe (14) and the second intermediate header (13) to reach a uniform temperature, and then the respective refrigerant passages (9) It divides into and flows.
【００１８】図２は、第１中間ヘッダ(12)、連結管(14)
および第２中間ヘッダ(13)を通る前後における冷媒の混
合状態を概略的に示すものである。入口管(7) から第１
中間ヘッダ(12)に達するまでは、各冷媒通路(9) のうち
風上側に近いものほど蒸発完了部（図２において斜線を
施していない部分）が大きくなっており、風下側に近い
ものでは冷媒は液状のまま（図２において斜線を施した
部分）となっている。液状冷媒は、連結管(14)に沿って
ターンさせられて混合されながら第２直管部(10)に流
れ、さらに各冷媒通路(9) に分かれて流される。ターン
させられるさいには、液状冷媒の慣性により、風上側に
より多くの液状冷媒が流れることになる。したがって出
口管(8) に近いところにおいては、各冷媒通路(9) の蒸
発完了部がほぼ同じ大きさとなる。FIG. 2 shows a first intermediate header 12 and a connecting pipe 14.
3 schematically shows the mixed state of the refrigerant before and after passing through the second intermediate header (13). First to the inlet pipe (7)
Until reaching the intermediate header (12), the closer to the windward side of each refrigerant passage (9), the larger the evaporation completion portion (the portion not shaded in FIG. 2) is, and the closer to the leeward side. The refrigerant remains liquid (the shaded portion in FIG. 2). The liquid refrigerant flows along the connecting pipe (14) while being turned and mixed, and then flows into the second straight pipe portion (10), and further flows into the respective refrigerant passages (9) separately. When it is turned, the inertia of the liquid refrigerant causes more liquid refrigerant to flow to the windward side. Therefore, in the vicinity of the outlet pipe (8), the evaporation completion portions of the refrigerant passages (9) have almost the same size.
【００１９】なお、図示は省略したが、蒸発器(1) の入
口には膨張弁が設けられ、蒸発器(1) に流れ込む冷媒流
量の制御を行っている。この膨張弁の制御基準は、蒸発
器出口における冷媒のスーパーヒートにより行われるも
ので、出口での冷媒の温度が高ければ弁が開き、低けれ
ば弁が閉じる。Although not shown, an expansion valve is provided at the inlet of the evaporator (1) to control the flow rate of the refrigerant flowing into the evaporator (1). This expansion valve is controlled by superheat of the refrigerant at the outlet of the evaporator. If the temperature of the refrigerant at the outlet is high, the valve is opened, and if it is low, the valve is closed.
【００２０】図３および図４は、この発明の熱交換器を
カー・エアコンの蒸発器として使用する場合の第２実施
例を示している。FIGS. 3 and 4 show a second embodiment in which the heat exchanger of the present invention is used as an evaporator of a car air conditioner.
【００２１】この実施例の蒸発器(21)は、横形のもの
で、複数の冷媒通路(29)を有するアルミニウム押出形材
製蛇行状偏平管(22)と、偏平管(22)の各水平直管部(22
a) の間にろう接されて介在されたルーバ付アルミニウ
ム薄板製コルゲートフィン(23)と、偏平管(22)の両端部
にそれぞれ接続された有底筒形の入口および出口ヘッダ
(24)(25)とを備えており、強制送風により前から後に向
かって風が流されるものである。The evaporator (21) of this embodiment is of a horizontal type, and the meandering flat pipe (22) made of aluminum extruded profile having a plurality of refrigerant passages (29) and the horizontal pipe of the flat pipe (22). Straight pipe part (22
Aluminum corrugated fins with louvers (23) brazed between a) and bottomed cylindrical inlet and outlet headers connected to both ends of the flat tube (22).
(24) and (25) are provided, and the wind is blown from the front to the rear by forced air flow.
【００２２】蛇行状偏平管(22)は、蒸発器(21)の高さの
中央よりも若干下において偏平管(22)の左の屈曲部が取
り除かれ、入口ヘッダ(24)を有する上側の蛇行状第１分
割偏平管(30)と、出口ヘッダ(25)を有する下側の蛇行状
第２分割偏平管(31)とに分割されている。入口ヘッダ(2
4)の後端の開口に入口管(27)が、出口ヘッダ(25)の前端
の開口に出口管(28)がそれぞれ接続されている。The meandering flat tube (22) is slightly below the center of the height of the evaporator (21), the left bent portion of the flat tube (22) is removed, and the upper tube having the inlet header (24) is removed. It is divided into a serpentine first split flat tube (30) and a lower serpentine second split flat tube (31) having an outlet header (25). Inlet header (2
The inlet pipe (27) is connected to the opening at the rear end of 4), and the outlet pipe (28) is connected to the opening at the front end of the outlet header (25).
【００２３】第１分割偏平管(30)の分割側の端部に有底
筒形の第１中間ヘッダ(32)が接続され、第２分割偏平管
(31)の分割側の端部に有底筒形の第２中間ヘッダ(33)が
接続されている。第１中間ヘッダ(32)と第２中間ヘッダ
(33)とは、略平行状であり、後側（風下側）においてＵ
字形の連結管(34)により連結されている。A first intermediate header (32) having a bottomed cylindrical shape is connected to an end portion of the first split flat tube (30) on the split side, and a second split flat tube (30) is connected.
A bottomed cylindrical second intermediate header (33) is connected to the end of the (31) on the split side. First intermediate header (32) and second intermediate header
(33) is almost parallel with U on the rear side (leeward side)
They are connected by a character-shaped connecting pipe (34).
【００２４】さらに、入口管(27)と第２中間ヘッダ(33)
とを連通するバイパス用パイプ(35)が設けられている。
入口管(27)の管壁および第２中間ヘッダ(33)の風上側の
管壁には、それぞれバイパス用パイプ(35)を差し込むた
めの小さい貫通孔があけられ、入口管(27)および第２中
間ヘッダ(33)とバイパス用パイプ(35)とはアーク溶接に
より接合されている。Further, the inlet pipe (27) and the second intermediate header (33)
A bypass pipe (35) is provided for communicating with and.
A small through hole for inserting the bypass pipe (35) is formed in the pipe wall of the inlet pipe (27) and the pipe wall on the windward side of the second intermediate header (33). 2. The intermediate header (33) and the bypass pipe (35) are joined by arc welding.
【００２５】図４は、第１中間ヘッダ(32)、連結管(34)
および第２中間ヘッダ(33)を通る前後における冷媒の混
合状態を概略的に示すものである。入口管(27)から第１
中間ヘッダ(32)に達するまでは、各冷媒通路(29)のうち
風上側に近いものほど蒸発完了部（図４において斜線を
施していない部分）が大きくなっており、風上側に近い
ものでは冷媒は液状（図４において斜線を施した部分）
となっている。液状冷媒は、連結管(34)に沿ってターン
させられて第２直管部(30)に流れ、さらに各冷媒通路
(9) に分かれて流される。ターンさせられるさいには、
液状冷媒の慣性により、風上側により多くの液状冷媒が
流れ、さらに、バイパス用パイプ(35)を通った冷媒が直
接風上側の冷媒通路(9) に流される。このようにして、
第２中間ヘッダ(33)通過以降の時点で液状冷媒を風上側
に多く配分することにより、出口管(8) に近いところに
おいては、各冷媒通路(9) の蒸発完了部がほぼ同じ大き
さとすることができる。FIG. 4 shows the first intermediate header (32) and the connecting pipe (34).
3 schematically shows the mixed state of the refrigerant before and after passing through the second intermediate header (33). First from the inlet pipe (27)
Until reaching the intermediate header (32), the nearer to the windward side of each refrigerant passage (29) is, the larger the evaporation completion portion (the portion not shaded in FIG. 4) is. Refrigerant is liquid (hatched area in Figure 4)
Has become. The liquid refrigerant is turned along the connecting pipe (34) and flows into the second straight pipe portion (30), and further, the respective refrigerant passages.
It is divided into (9) and washed away. When it is turned,
Due to the inertia of the liquid refrigerant, a larger amount of the liquid refrigerant flows to the windward side, and the refrigerant that has passed through the bypass pipe (35) is directly flown to the windward refrigerant passage (9). In this way
By distributing a large amount of liquid refrigerant to the windward side after passing through the second intermediate header (33), the evaporation completion portion of each refrigerant passage (9) has approximately the same size in the vicinity of the outlet pipe (8). can do.
【００２６】図５および図６は、この発明の熱交換器を
カー・エアコンの蒸発器として使用する場合の第３実施
例を示している。FIGS. 5 and 6 show a third embodiment in which the heat exchanger of the present invention is used as an evaporator of a car air conditioner.
【００２７】この実施例の蒸発器(41)は、横形のもの
で、複数の冷媒通路(49)を有するアルミニウム押出形材
製蛇行状偏平管(42)と、偏平管(42)の各水平直管部(42
a) の間にろう接されて介在されたルーバ付アルミニウ
ム薄板製コルゲートフィン(43)と、偏平管(42)の両端部
にそれぞれ接続された有底筒形の入口および出口ヘッダ
(44)(45)とを備えており、強制送風により前から後に向
かって風が流されるものである。The evaporator (41) of this embodiment is a horizontal type, and the meandering flat tube (42) made of aluminum extruded profile having a plurality of refrigerant passages (49) and the horizontal tubes of the flat tube (42) are provided. Straight pipe part (42
Aluminum corrugated fins (43) with louvers interposed by brazing between a) and bottomed cylindrical inlet and outlet headers connected to both ends of the flat tube (42), respectively.
(44) and (45) are provided, and the wind is blown from the front to the rear by the forced air flow.
【００２８】蛇行状偏平管(42)は、偏平管(42)の長さの
中央においてその左の屈曲部が取り除かれ、入口ヘッダ
(44)を有する上側の蛇行状第１分割偏平管(50)と、出口
ヘッダ(45)を有する下側の蛇行状第２分割偏平管(51)と
に分割されている。入口ヘッダ(44)の後端の開口に入口
管(47)が、出口ヘッダ(45)の前端の開口に出口管(48)が
それぞれ接続されている。The meandering flat tube (42) has its left bent portion removed at the center of the length of the flat tube (42), and the inlet header is removed.
It is divided into an upper meandering first split flat tube (50) having (44) and a lower meandering second split flat tube (51) having an outlet header (45). The inlet pipe (47) is connected to the opening at the rear end of the inlet header (44), and the outlet pipe (48) is connected to the opening at the front end of the outlet header (45).
【００２９】第１分割偏平管(50)の分割側の端部に有底
筒形の第１中間ヘッダ(52)が接続され、第２分割偏平管
(51)の分割側の端部に有底筒形の第２中間ヘッダ(53)が
接続されている。第１中間ヘッダ(52)と第２中間ヘッダ
(53)とは、略平行状であり、第１中間ヘッダ(52)の前側
（風上側）端部と第２中間ヘッダ(53)の後側（風下側）
端部とが、Ｓ字形の連結管(54)により連結されている。A first intermediate header (52) having a bottomed cylindrical shape is connected to an end of the first split flat tube (50) on the split side, and a second split flat tube (50) is connected.
A bottomed cylindrical second intermediate header (53) is connected to the end of the split side of (51). First intermediate header (52) and second intermediate header
(53) is substantially parallel to the front (windward) end of the first intermediate header (52) and the rear (downward) of the second intermediate header (53).
The ends are connected by an S-shaped connecting pipe (54).
【００３０】図６は、第１中間ヘッダ(52)、連結管(54)
および第２中間ヘッダ(53)を通る前後における冷媒の混
合状態を概略的に示すものである。入口管(47)から第１
中間ヘッダ(52)に達するまでは、各冷媒通路(49)のうち
風上側に近いものほど蒸発完了部（図６において斜線を
施していない部分）が大きくなっており、風上側に近い
ものでは冷媒は液状（図６において斜線を施した部分）
となっている。液状冷媒は、連結管(54)に沿ってターン
させられて第２直管部(50)に流れ、さらに各冷媒通路(4
9)に分かれて流される。ターンさせられるさいには、液
状冷媒の慣性により、風上側により多くの液状冷媒が流
れることになる。ここで、連結管(54)がＳ字形であり、
第１中間ヘッダ(52)の出口が風上側にあるため、より風
上側に冷媒が流れ、しかも冷媒の混合も助長される。し
たがって、出口管(48)に近いところにおいては、各冷媒
通路(49)の蒸発完了部がほぼ同じ大きさとすることがで
き、しかも、第１実施例よりも蒸発完了部を大きくする
ことができる。FIG. 6 shows the first intermediate header (52) and the connecting pipe (54).
3 schematically shows a mixed state of the refrigerant before and after passing through the second intermediate header (53). First from the inlet pipe (47)
Until reaching the intermediate header (52), the nearer to the windward side of each refrigerant passage (49) is, the larger the evaporation completion portion (the portion not shaded in FIG. 6) is. Refrigerant is liquid (hatched area in Figure 6)
Has become. The liquid refrigerant is turned along the connecting pipe (54) and flows into the second straight pipe portion (50), and further, the respective refrigerant passages (4
It is divided into 9) and washed away. When it is turned, the inertia of the liquid refrigerant causes more liquid refrigerant to flow to the windward side. Here, the connecting pipe (54) is S-shaped,
Since the outlet of the first intermediate header (52) is on the windward side, the refrigerant flows further to the windward side, and the mixing of the refrigerant is also promoted. Therefore, in the vicinity of the outlet pipe (48), the evaporation completion portion of each refrigerant passage (49) can be made substantially the same size, and further, the evaporation completion portion can be made larger than in the first embodiment. .
【００３１】上記第１から第３までの実施例によると、
蒸発が完了してしまって熱交換作用を行わない冷媒通路
(9)(29)(49) をなくすことができ、熱交換性能を向上さ
せることができる。According to the first to third embodiments,
Refrigerant passage that does not perform heat exchange due to completion of evaporation
(9) (29) (49) can be eliminated and heat exchange performance can be improved.
【００３２】図７には、第１実施例、第３実施例、およ
び中間ヘッダの無い従来例の各蒸発器について、各蒸発
器出口近くの風上側の冷媒通路(49)における冷媒温度の
測定結果を示す。図７より分かるように、第１実施例お
よび第３実施例のものでは、従来のものに比べて、最低
温度は高くかつ最高温度との差が小さくなっており、出
口における冷媒の蒸発が盛んであり、しかも冷媒温度が
安定している。すなわち、第１実施例および第３実施例
の蒸発器は、熱交換効率に優れ、しかも冷媒流量の制御
を行う膨張弁の開閉が頻繁となる不安定状態（ハンチン
グ現象）が起こりにくくなっている。また、第１実施例
と第３実施例との比較では、第３実施例のもののほう
が、さらに最低温度が高くしたがって最高温度との差が
小さくなっており、偏平管(42)の長さのほぼ中央に中間
ヘッダ(52)(53)を設け、かつ連結管(54)をＳ字形とする
ことがより好ましいことが分かる。FIG. 7 shows the measurement of the refrigerant temperature in the refrigerant passage (49) on the windward side near the outlets of the evaporators of the evaporators of the first embodiment, the third embodiment, and the conventional example without the intermediate header. The results are shown. As can be seen from FIG. 7, in the first and third embodiments, the minimum temperature is higher and the difference from the maximum temperature is smaller than that of the conventional one, and the evaporation of the refrigerant at the outlet is active. And the refrigerant temperature is stable. That is, in the evaporators of the first and third embodiments, the heat exchange efficiency is excellent, and an unstable state (hunting phenomenon) in which the expansion valve that controls the refrigerant flow rate is frequently opened and closed is unlikely to occur. . In comparison between the first embodiment and the third embodiment, the third embodiment has a higher minimum temperature and therefore a smaller difference from the maximum temperature, and the flat tube (42) has a different length. It can be seen that it is more preferable to provide the intermediate headers (52) and (53) substantially at the center and to make the connecting pipe (54) S-shaped.
【００３３】[0033]
【発明の効果】この発明の熱交換器によると、各冷媒通
路を流れてきた温度差のある冷媒は、第１中間ヘッダ、
連結管および第２中間ヘッダを通る間に混合されて均一
な温度となり、これ以後の熱交換効率を向上させるとと
もに、膨張弁が安定して作動するので制御を容易に行う
ことができる。According to the heat exchanger of the present invention, the refrigerant having the temperature difference flowing through the respective refrigerant passages is transferred to the first intermediate header,
The temperature is mixed while passing through the connecting pipe and the second intermediate header to have a uniform temperature, which improves the heat exchange efficiency thereafter, and the expansion valve operates stably, so that the control can be easily performed.
【００３４】さらに、第１および第２中間ヘッダは出入
口ヘッダと同様の有底筒形であるため、各中間ヘッダと
各分割偏平管とは、出入口ヘッダを偏平管に接合するの
と同様の方法により接合することができ、接合作業を容
易に行うことができ、したがって、上記の高い熱交換効
率を得るために熱交換器の製造がしにくくなるというこ
とはない。Further, since the first and second intermediate headers have a bottomed cylindrical shape similar to the inlet / outlet header, each intermediate header and each divided flat pipe are formed by the same method as that for joining the inlet / outlet header to the flat pipe. Therefore, the joining work can be easily performed, and therefore, it is not difficult to manufacture the heat exchanger in order to obtain the above-mentioned high heat exchange efficiency.
【図１】この発明による熱交換器の第１実施例を示す斜
視図である。FIG. 1 is a perspective view showing a first embodiment of a heat exchanger according to the present invention.
【図２】第１実施例の熱交換器の中間ヘッダの前後にお
ける冷媒の混合状態を概略的に示す図である。FIG. 2 is a diagram schematically showing a mixed state of refrigerants before and after an intermediate header of the heat exchanger of the first embodiment.
【図３】この発明による熱交換器の第２実施例を示す斜
視図である。FIG. 3 is a perspective view showing a second embodiment of the heat exchanger according to the present invention.
【図４】第２実施例の熱交換器の中間ヘッダの前後にお
ける冷媒の混合状態を概略的に示す図である。FIG. 4 is a diagram schematically showing a mixed state of refrigerant before and after an intermediate header of the heat exchanger of the second embodiment.
【図５】この発明による熱交換器の第３実施例を示す斜
視図である。FIG. 5 is a perspective view showing a third embodiment of the heat exchanger according to the present invention.
【図６】第３実施例の熱交換器の中間ヘッダの前後にお
ける冷媒の混合状態を概略的に示す図である。FIG. 6 is a diagram schematically showing a mixed state of refrigerant before and after an intermediate header of a heat exchanger according to a third embodiment.
【図７】実施例および従来の熱交換器の出口における冷
媒温度の測定結果を示すグラフである。FIG. 7 is a graph showing the measurement results of the refrigerant temperature at the outlet of the heat exchanger of the example and the conventional heat exchanger.
(1)(21)(41) 蒸発器（熱交換器） (2)(22)(42) 蛇行状偏平管 (2a)(22a)(42a) 直管部 (3)(23)(43) コルゲートフィン (4)(24)(44) 入口ヘッダ (5)(25)(45) 出口ヘッダ (9)(29)(49) 冷媒通路 (10)(30)(50) 第１分割偏平管 (11)(31)(51) 第２分割偏平管 (12)(32)(52) 第１中間ヘッダ (13)(33)(53) 第２中間ヘッダ (14)(34)(54) 連結管 (1) (21) (41) Evaporator (heat exchanger) (2) (22) (42) Meandering flat tube (2a) (22a) (42a) Straight tube section (3) (23) (43) Corrugated fins (4) (24) (44) Inlet headers (5) (25) (45) Outlet headers (9) (29) (49) Refrigerant passages (10) (30) (50) 1st split flat pipe ( 11) (31) (51) 2nd split flat pipe (12) (32) (52) 1st intermediate header (13) (33) (53) 2nd intermediate header (14) (34) (54) connecting pipe
─────────────────────────────────────────────────────
─────────────────────────────────────────────────── ───
【手続補正書】[Procedure amendment]
【提出日】平成５年９月６日[Submission date] September 6, 1993
【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】発明の詳細な説明[Name of item to be amended] Detailed explanation of the invention
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【発明の詳細な説明】Detailed Description of the Invention
【０００１】[0001]
【産業上の利用分野】この発明は、例えばカー・エアコ
ンの蒸発器として使用される熱交換器に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger used as an evaporator for car air conditioners, for example.
【０００２】[0002]
【従来の技術】従来、この種熱交換器としては、複数の
冷媒通路を有する蛇行状偏平管と、これの各直管部同士
の間に介在されたコルゲートフィンと、偏平管の両端部
にそれぞれ接続された有底筒形の入口および出口ヘッダ
とを備えているものが知られている。2. Description of the Related Art Heretofore, as this kind of heat exchanger, a meandering flat pipe having a plurality of refrigerant passages, corrugated fins interposed between straight pipe portions of the flat pipe, and both end portions of the flat pipe have been used. It is known that each has a bottomed tubular inlet and outlet header connected to it.
【０００３】[0003]
【発明が解決しようとする課題】上記従来の熱交換器で
は、強制送風により冷媒通路と直交状に風が流される
が、風上側の冷媒通路では熱負荷が大きくて冷媒の蒸発
が早くかつ冷媒の蒸発量が多く、これとは逆に風下側の
冷媒通路では熱負荷が小さくて冷媒の蒸発量が少ないた
めに、全体として熱交換効率がよくないという問題があ
った。しかも、蒸発器出口における冷媒が不安定とな
り、冷媒流量の制御を行う膨張弁の開閉が頻繁となる不
安定状態（ハンチング現象）が起こるという問題もあっ
た。In the above conventional heat exchanger, forced air blows air in a direction orthogonal to the refrigerant passage, but in the refrigerant passage on the windward side, the heat load is large and the refrigerant evaporates quickly and the refrigerant However, there is a problem that the heat exchange efficiency is not good as a whole because the heat load is small in the leeward side refrigerant passage and the evaporation amount of the refrigerant is small. Moreover, the refrigerant at the outlet of the evaporator becomes unstable, and an unstable state (hunting phenomenon) occurs in which the expansion valve that controls the refrigerant flow rate is opened and closed frequently.
【０００４】そこで、偏平管の長さの中間部に、風の流
れ方向に長い直方体状箱形の中間ヘッダを設け、中間ヘ
ッダにおいて各冷媒通路を通過してきた温度差のある冷
媒を混合した後、再び冷媒通路に分配することにより、
各通路を流れる冷媒の蒸発器出口での温度差を小さくす
ることも提案されている（特開昭６０−１４００９７号
公報参照）。Therefore, a rectangular parallelepiped box-shaped intermediate header, which is long in the direction of air flow, is provided in the middle of the length of the flat tube, and after mixing the refrigerants having different temperatures which have passed through the respective refrigerant passages in the intermediate header. , By distributing again to the refrigerant passage,
It has also been proposed to reduce the temperature difference at the evaporator outlet of the refrigerant flowing through each passage (see JP-A-60-140097).
【０００５】しかしながら、上記の提案では、中間ヘッ
ダの２つの偏平管端部嵌入用開口とコルゲート・フィン
が介在された状態の２つの偏平管端部とを嵌め合わせた
後、接合する必要があり、この作業が面倒で製造しにく
いという問題があった。However, in the above proposal, it is necessary to fit the two flat tube end fitting openings of the intermediate header and the two flat tube end parts with the corrugated fins interposed therebetween, and then to join them. There was a problem that this work was troublesome and difficult to manufacture.
【０００６】この発明の目的は、各通路を流れる冷媒の
蒸発器出口での温度差を小さくすることにより、熱交換
効率を向上させかつ膨張弁を安定させて制御を容易に
し、しかも製造もしやすい熱交換器を提供することにあ
る。An object of the present invention is to improve the heat exchange efficiency and stabilize the expansion valve by facilitating the control by facilitating the control by reducing the temperature difference of the refrigerant flowing through each passage at the evaporator outlet. It is to provide a heat exchanger.
【０００７】[0007]
【課題を解決するための手段】この発明による熱交換器
は、複数の冷媒通路を有する蛇行状偏平管と、これの各
直管部同士の間に介在されたコルゲートフィンと、偏平
管の両端部にそれぞれ接続された有底筒形の入口および
出口ヘッダとを備えている熱交換器であって、蛇行状偏
平管が長さの中間部において２つに分割されており、入
口ヘッダを有する蛇行状第１分割偏平管の他端部に有底
筒形の第１中間ヘッダが接続されるとともに、出口ヘッ
ダを有する蛇行状第２分割偏平管の他端部に有底筒形の
第２中間ヘッダが接続されて、第１および第２中間ヘッ
ダが略平行状に配置され、第１および第２中間ヘッダ
に、両者を連結する連結管が接続されているものであ
る。A heat exchanger according to the present invention comprises a meandering flat pipe having a plurality of refrigerant passages, corrugated fins interposed between the straight pipe portions of the flat pipe, and both ends of the flat pipe. A heat exchanger having a bottomed tubular inlet and outlet headers each connected to a section, the serpentine flat tube being divided into two in the middle of the length and having an inlet header A bottomed tubular first intermediate header is connected to the other end of the serpentine first split flat tube, and a bottomed tubular second intermediate header is connected to the other end of the serpentine second split flat tube having an outlet header. The intermediate header is connected, the first and second intermediate headers are arranged in a substantially parallel shape, and a connecting pipe that connects them is connected to the first and second intermediate headers.
【０００８】[0008]
【作用】この発明による熱交換器は、蛇行状偏平管が長
さの中間部において２つに分割されており、入口ヘッダ
を有する蛇行状第１分割偏平管の他端部に有底筒形の第
１中間ヘッダが接続されるとともに、出口ヘッダを有す
る蛇行状第２分割偏平管の他端部に有底筒形の第２中間
ヘッダが接続されて、第１および第２中間ヘッダが略平
行状に配置され、第１および第２中間ヘッダに、両者を
連結する連結管が接続されているものであるから、各冷
媒通路を流れてきた温度差のある冷媒は、第１中間ヘッ
ダ、連結管および第２中間ヘッダを通る間に混合された
後、各冷媒通路に分かれて流れていく。In the heat exchanger according to the present invention, the meandering flat tube is divided into two in the middle portion of the length, and the other end of the meandering first split flat tube having the inlet header has a bottomed cylindrical shape. The first intermediate header is connected, and the second intermediate header having a bottomed cylindrical shape is connected to the other end of the meandering second split flat tube having the outlet header, and the first and second intermediate headers are substantially Since the first and second intermediate headers are arranged in parallel and the connecting pipes that connect them are connected to each other, the refrigerant having a temperature difference flowing through each refrigerant passage is After being mixed while passing through the connecting pipe and the second intermediate header, they are divided into respective refrigerant passages and flow.
【０００９】第１および第２中間ヘッダは出入口ヘッダ
と同形状の有底筒形であるため、各中間ヘッダと各分割
偏平管との接合は、出入口ヘッダを偏平管に接合するの
と同様の方法により行え、接合作業を容易に行うことが
できる。Since the first and second intermediate headers have a bottomed cylindrical shape having the same shape as the inlet / outlet header, the joining of the intermediate headers and the divided flat tubes is similar to joining the inlet / outlet headers to the flat tubes. It can be performed by a method and the joining work can be easily performed.
【００１０】[0010]
【実施例】この発明の実施例を、以下図面を参照して説
明する。以下の説明において、左右は図２の左右をい
い、前後については、図２の上を前、下を後というもの
とする。Embodiments of the present invention will be described below with reference to the drawings. In the following description, the left and right refer to the left and right in FIG. 2, and the front and back refer to the top of FIG. 2 as the front and the bottom as the rear.
【００１１】図１および図２は、この発明の熱交換器を
カー・エアコンの蒸発器として使用する場合の第１実施
例を示しており、蒸発器(1) は、横形のもので、複数の
冷媒通路(9) を有するアルミニウム押出形材製蛇行状偏
平管(2) と、偏平管(2) の各水平直管部(2a)の間にろう
接されて介在されたルーバ付アルミニウム薄板製コルゲ
ートフィン(3) と、偏平管(2) の両端部にそれぞれ接続
された有底筒形の入口および出口ヘッダ(4)(5)とを備え
ており、強制送風により前から後に向かって風が流され
るものである。FIGS. 1 and 2 show a first embodiment in which the heat exchanger of the present invention is used as an evaporator of a car air conditioner. The evaporator (1) is a horizontal type, and a plurality of evaporators (1) are provided. Aluminum thin plate with louver interposed by brazing between each flat straight tube (2a) of the flat tube (2) and the meandering flat tube (2) made of extruded aluminum having the refrigerant passage (9) It is equipped with corrugated fins (3) and bottomed cylindrical inlet and outlet headers (4) and (5) connected to both ends of the flat tube (2). The wind is swept away.
【００１２】蛇行状偏平管(2) は、蒸発器(1) の高さの
中央よりも若干下において偏平管(2) の左の屈曲部が取
り除かれ、入口ヘッダ(4) を有する上部の蛇行状第１分
割偏平管(10)と、出口ヘッダ(5) を有する下部の蛇行状
第２分割偏平管(11)とに分割されている。The meandering flat tube (2) is slightly below the center of the height of the evaporator (1), the left bend of the flat tube (2) is removed and the upper header with the inlet header (4) is removed. It is divided into a serpentine first split flat tube (10) and a lower serpentine second split flat tube (11) having an outlet header (5).
【００１３】第１分割偏平管(10)の分割側の端部に有底
筒形の第１中間ヘッダ(12)が接続され、第２分割偏平管
(11)の分割側の端部に有底筒形の第２中間ヘッダ(13)が
接続されている。第１中間ヘッダ(12)と第２中間ヘッダ
(13)とは、略平行状であり、後側（風下側）においてＵ
字形の連結管(14)により連結されている。A first intermediate header (12) having a bottomed cylindrical shape is connected to an end portion of the first split flat tube (10) on the split side, and a second split flat tube (10) is connected.
A bottomed cylindrical second intermediate header (13) is connected to the end of the split side of (11). First intermediate header (12) and second intermediate header
(13) is almost parallel and U on the rear side (leeward side)
They are connected by a character-shaped connecting pipe (14).
【００１４】蛇行状第２分割偏平管(11)は下方に蛇行し
た後、蒸発器(1) の右下において折り曲げられ、蒸発器
(1) の右上に位置させられている出口ヘッダ(5) までの
びている。入口ヘッダ(4) は、出口ヘッダ(5) のすぐ内
側に出口ヘッダ(5) と平行となるように位置させられて
いる。入口ヘッダ(4) の後端の開口に入口管(7) が、出
口ヘッダ(5) の前端の開口に出口管(8) がそれぞれ接続
されている。入口管(7) は折り返されており、出口管
(8) と同じ方向にのびている。After the meandering second split flat tube (11) meanders downward, it is bent at the lower right of the evaporator (1) to form an evaporator.
It extends to the exit header (5) located in the upper right corner of (1). The inlet header (4) is positioned just inside the outlet header (5) and parallel to the outlet header (5). The inlet pipe (7) is connected to the opening at the rear end of the inlet header (4), and the outlet pipe (8) is connected to the opening at the front end of the outlet header (5). The inlet pipe (7) is folded back and the outlet pipe
It extends in the same direction as (8).
【００１５】第２分割偏平管(11)の左縁部は、第１分割
偏平管(10)の左縁部より内側に、第１中間ヘッダ(12)は
蒸発器(1) の左縁よりも内側に、第２中間ヘッダ(13)は
第１中間ヘッダ(12)よりもさらに内側にあり、蒸発器
(1) の左下の部分が若干凹まされている。この凹まされ
ている位置を種々変更することにより、蒸発器(1) を自
動車のエンジンルーム内に配置するさい、他の部品と干
渉することを防止することができる。The left edge of the second split flat tube (11) is inside the left edge of the first split flat tube (10), and the first intermediate header (12) is from the left edge of the evaporator (1). Inside, the second intermediate header (13) is further inside than the first intermediate header (12),
The lower left part of (1) is slightly recessed. By changing the recessed position variously, it is possible to prevent the evaporator (1) from interfering with other parts when the evaporator (1) is arranged in the engine room of the automobile.
【００１６】第１分割偏平管(10)と第１中間ヘッダ(12)
との接合および第２分割偏平管(11)と第２中間ヘッダ(1
3)との接合は、ろう付けにより行われている。このろう
付けは、入口および出口ヘッダ(4)(5)を偏平管(2) に接
合するのと同様であり、非常に容易に行うことができ、
かつ冷媒の漏れに対する信頼性も高い。第１中間ヘッダ
(12)および第２中間ヘッダ(13)と連結管(14)との接合
は、アーク溶接により行われている。この溶接は、入口
ヘッダ(4) と入口管(7) との接合と同様であり、非常に
容易に行うことができ、かつ冷媒の漏れに対する信頼性
も高い。なお、第１中間ヘッダ(12)および第２中間ヘッ
ダ(13)と連結管(14)との接合も入口ヘッダ (4) と入口管
(7) との接合も共にろう付けとし、すべての熱交換器構
成部材を一括ろう付けにより、接合してもよい。 The first split flat tube (10) and the first intermediate header (12)
And the second split flat tube (11) and the second intermediate header (1
3) is joined by brazing. This brazing is similar to joining the inlet and outlet headers (4) (5) to the flat tubes (2) and can be done very easily,
Moreover, the reliability against leakage of the refrigerant is high. First intermediate header
The joining between the (12) and the second intermediate header (13) and the connecting pipe (14) is performed by arc welding. This welding is similar to the joining of the inlet header (4) and the inlet pipe (7), can be performed very easily, and has high reliability against refrigerant leakage. The first intermediate header (12) and the second intermediate header
The connection between the duct (13) and the connecting pipe (14) is also performed by the inlet header (4)
The joint with (7) was also brazed together so that all heat exchanger structures
The formed members may be joined by collective brazing.
【００１７】上記構成の蒸発器(1) では、冷媒は各冷媒
通路(9) を通過する間に蒸発して熱交換が行われる。冷
媒の蒸発作用は熱負荷が大きい風上側ほど活発であるた
め、第１分割偏平管(10)の分割側の端部近くにおいて
は、風上側の冷媒通路(9) を流れる冷媒と風下側の冷媒
通路(9) を流れる冷媒との間に温度差が生じてくる。そ
して、温度差のある冷媒は、第１中間ヘッダ(12)、連結
管(14)および第２中間ヘッダ(13)を通る間に混合され均
一な温度になった後、各冷媒通路(9) に分かれて流れて
いく。In the evaporator (1) having the above structure, the refrigerant evaporates and exchanges heat while passing through the respective refrigerant passages (9). Since the evaporating action of the refrigerant is more active on the windward side where the heat load is larger, the refrigerant flowing in the refrigerant passage (9) on the windward side and on the leeward side near the split end of the first split flat tube (10). A temperature difference occurs between the refrigerant flowing through the refrigerant passage (9) and the refrigerant. Then, the refrigerants having different temperatures are mixed while passing through the first intermediate header (12), the connecting pipe (14) and the second intermediate header (13) to reach a uniform temperature, and then the respective refrigerant passages (9) It divides into and flows.
【００１８】図２は、第１中間ヘッダ(12)、連結管(14)
および第２中間ヘッダ(13)を通る前後における冷媒の混
合状態を概略的に示すものである。入口管(7) から第１
中間ヘッダ(12)に達するまでは、各冷媒通路(9) のうち
風上側に近いものほど蒸発完了部（図２において斜線を
施していない部分）が大きくなっており、風下側に近い
ものでは冷媒は液状のまま（図２において斜線を施した
部分）となっている。液状冷媒は、連結管(14)に沿って
ターンさせられて混合されながら第２直管部(10)に流
れ、さらに各冷媒通路(9) に分かれて流される。ターン
させられるさいには、液状冷媒の慣性により、風上側に
より多くの液状冷媒が流れることになる。したがって出
口管(8) に近いところにおいては、各冷媒通路(9) の蒸
発完了部がほぼ同じ大きさとなる。FIG. 2 shows a first intermediate header 12 and a connecting pipe 14.
3 schematically shows the mixed state of the refrigerant before and after passing through the second intermediate header (13). First to the inlet pipe (7)
Until reaching the intermediate header (12), the closer to the windward side of each refrigerant passage (9), the larger the evaporation completion portion (the portion not shaded in FIG. 2) is, and the closer to the leeward side. The refrigerant remains liquid (the shaded portion in FIG. 2). The liquid refrigerant flows through the second straight pipe portion (10) while being turned along the connecting pipe (14) and mixed, and further divided into the respective refrigerant passages (9). When it is turned, the inertia of the liquid refrigerant causes more liquid refrigerant to flow to the windward side. Therefore, in the vicinity of the outlet pipe (8), the evaporation completion portions of the refrigerant passages (9) have almost the same size.
【００１９】なお、図示は省略したが、蒸発器(1) の入
口には膨張弁が設けられ、蒸発器(1) に流れ込む冷媒流
量の制御を行っている。この膨張弁の制御基準は、蒸発
器出口における冷媒のスーパーヒートにより行われるも
ので、出口での冷媒の温度が高ければ弁が開き、低けれ
ば弁が閉じる。Although not shown, an expansion valve is provided at the inlet of the evaporator (1) to control the flow rate of the refrigerant flowing into the evaporator (1). This expansion valve is controlled by superheat of the refrigerant at the outlet of the evaporator. If the temperature of the refrigerant at the outlet is high, the valve is opened, and if it is low, the valve is closed.
【００２０】図３および図４は、この発明の熱交換器を
カー・エアコンの蒸発器として使用する場合の第２実施
例を示している。FIGS. 3 and 4 show a second embodiment in which the heat exchanger of the present invention is used as an evaporator of a car air conditioner.
【００２１】この実施例の蒸発器(21)は、横形のもの
で、複数の冷媒通路(29)を有するアルミニウム押出形材
製蛇行状偏平管(22)と、偏平管(22)の各水平直管部(22
a) の間にろう接されて介在されたルーバ付アルミニウ
ム薄板製コルゲートフィン(23)と、偏平管(22)の両端部
にそれぞれ接続された有底筒形の入口および出口ヘッダ
(24)(25)とを備えており、強制送風により前から後に向
かって風が流されるものである。The evaporator (21) of this embodiment is of a horizontal type, and the meandering flat pipe (22) made of aluminum extruded profile having a plurality of refrigerant passages (29) and the horizontal pipe of the flat pipe (22). Straight pipe part (22
Aluminum corrugated fins with louvers (23) brazed between a) and bottomed cylindrical inlet and outlet headers connected to both ends of the flat tube (22).
(24) and (25) are provided, and the wind is blown from the front to the rear by forced air flow.
【００２２】蛇行状偏平管(22)は、蒸発器(21)の高さの
中央よりも若干下において偏平管(22)の左の屈曲部が取
り除かれ、入口ヘッダ(24)を有する上側の蛇行状第１分
割偏平管(30)と、出口ヘッダ(25)を有する下側の蛇行状
第２分割偏平管(31)とに分割されている。入口ヘッダ(2
4)の後端の開口に入口管(27)が、出口ヘッダ(25)の前端
の開口に出口管(28)がそれぞれ接続されている。The meandering flat tube (22) is slightly below the center of the height of the evaporator (21), the left bent portion of the flat tube (22) is removed, and the upper tube having the inlet header (24) is removed. It is divided into a serpentine first split flat tube (30) and a lower serpentine second split flat tube (31) having an outlet header (25). Inlet header (2
The inlet pipe (27) is connected to the opening at the rear end of 4), and the outlet pipe (28) is connected to the opening at the front end of the outlet header (25).
【００２３】第１分割偏平管(30)の分割側の端部に有底
筒形の第１中間ヘッダ(32)が接続され、第２分割偏平管
(31)の分割側の端部に有底筒形の第２中間ヘッダ(33)が
接続されている。第１中間ヘッダ(32)と第２中間ヘッダ
(33)とは、略平行状であり、後側（風下側）においてＵ
字形の連結管(34)により連結されている。A first intermediate header (32) having a bottomed cylindrical shape is connected to an end portion of the first split flat tube (30) on the split side, and a second split flat tube (30) is connected.
A bottomed cylindrical second intermediate header (33) is connected to the end of the (31) on the split side. First intermediate header (32) and second intermediate header
(33) is almost parallel with U on the rear side (leeward side)
They are connected by a character-shaped connecting pipe (34).
【００２４】さらに、入口管(27)と第２中間ヘッダ(33)
とを連通するバイパス用パイプ(35)が設けられている。
入口管(27)の管壁および第２中間ヘッダ(33)の風上側の
管壁には、それぞれバイパス用パイプ(35)を差し込むた
めの小さい貫通孔があけられ、入口管(27)および第２中
間ヘッダ(33)とバイパス用パイプ(35)とはアーク溶接に
より接合されている。Further, the inlet pipe (27) and the second intermediate header (33)
A bypass pipe (35) is provided for communicating with and.
A small through hole for inserting the bypass pipe (35) is formed in the pipe wall of the inlet pipe (27) and the pipe wall on the windward side of the second intermediate header (33). 2. The intermediate header (33) and the bypass pipe (35) are joined by arc welding.
【００２５】図４は、第１中間ヘッダ(32)、連結管(34)
および第２中間ヘッダ(33)を通る前後における冷媒の混
合状態を概略的に示すものである。入口管(27)から第１
中間ヘッダ(32)に達するまでは、各冷媒通路(29)のうち
風上側に近いものほど蒸発完了部（図４において斜線を
施していない部分）が大きくなっており、風下側に近い
ものでは冷媒は液状（図４において斜線を施した部分）
となっている。液状冷媒は、連結管(34)に沿ってターン
させられて第２直管部(31)に流れ、さらに各冷媒通路
(9) に分かれて流される。ターンさせられるさいには、
液状冷媒の慣性により、風上側により多くの液状冷媒が
流れ、さらに、バイパス用パイプ(35)を通った冷媒が直
接風上側の冷媒通路(9) に流される。このようにして、
第２中間ヘッダ(33)通過以降の時点で液状冷媒を風上側
に多く配分することにより、出口管(8) に近いところに
おいては、各冷媒通路(9) の蒸発完了部がほぼ同じ大き
さとすることができる。FIG. 4 shows the first intermediate header (32) and the connecting pipe (34).
3 schematically shows the mixed state of the refrigerant before and after passing through the second intermediate header (33). First from the inlet pipe (27)
Until it reaches the intermediate header (32), and the more increased the evaporation completion portion (portion not hatched in FIG. 4) is close to the inner air above each coolant passage (29), close to leeward side Then, the refrigerant is liquid (the shaded area in Figure 4)
Has become. The liquid refrigerant is turned along the connecting pipe (34 ) to flow into the second straight pipe portion (31) , and further, in each refrigerant passage.
It is divided into (9) and washed away. When it is turned,
Due to the inertia of the liquid refrigerant, a larger amount of the liquid refrigerant flows to the windward side, and the refrigerant that has passed through the bypass pipe (35) is directly flown to the windward refrigerant passage (9). In this way
By distributing a large amount of liquid refrigerant to the windward side after passing through the second intermediate header (33), the evaporation completion portion of each refrigerant passage (9) has approximately the same size in the vicinity of the outlet pipe (8). can do.
【００２６】図５および図６は、この発明の熱交換器を
カー・エアコンの蒸発器として使用する場合の第３実施
例を示している。FIGS. 5 and 6 show a third embodiment in which the heat exchanger of the present invention is used as an evaporator of a car air conditioner.
【００２７】この実施例の蒸発器(41)は、横形のもの
で、複数の冷媒通路(49)を有するアルミニウム押出形材
製蛇行状偏平管(42)と、偏平管(42)の各水平直管部(42
a) の間にろう接されて介在されたルーバ付アルミニウ
ム薄板製コルゲートフィン(43)と、偏平管(42)の両端部
にそれぞれ接続された有底筒形の入口および出口ヘッダ
(44)(45)とを備えており、強制送風により前から後に向
かって風が流されるものである。The evaporator (41) of this embodiment is a horizontal type, and the meandering flat tube (42) made of aluminum extruded profile having a plurality of refrigerant passages (49) and the horizontal tubes of the flat tube (42) are provided. Straight pipe part (42
Aluminum corrugated fins (43) with louvers interposed by brazing between a) and bottomed cylindrical inlet and outlet headers connected to both ends of the flat tube (42), respectively.
(44) and (45) are provided, and the wind is blown from the front to the rear by the forced air flow.
【００２８】蛇行状偏平管(42)は、偏平管(42)の長さの
中央においてその左の屈曲部が取り除かれ、入口ヘッダ
(44)を有する上側の蛇行状第１分割偏平管(50)と、出口
ヘッダ(45)を有する下側の蛇行状第２分割偏平管(51)と
に分割されている。入口ヘッダ(44)の後端の開口に入口
管(47)が、出口ヘッダ(45)の前端の開口に出口管(48)が
それぞれ接続されている。The meandering flat tube (42) has its left bent portion removed at the center of the length of the flat tube (42), and the inlet header is removed.
It is divided into an upper meandering first split flat tube (50) having (44) and a lower meandering second split flat tube (51) having an outlet header (45). The inlet pipe (47) is connected to the opening at the rear end of the inlet header (44), and the outlet pipe (48) is connected to the opening at the front end of the outlet header (45).
【００２９】第１分割偏平管(50)の分割側の端部に有底
筒形の第１中間ヘッダ(52)が接続され、第２分割偏平管
(51)の分割側の端部に有底筒形の第２中間ヘッダ(53)が
接続されている。第１中間ヘッダ(52)と第２中間ヘッダ
(53)とは、略平行状であり、第１中間ヘッダ(52)の前側
（風上側）端部と第２中間ヘッダ(53)の後側（風下側）
端部とが、Ｓ字形の連結管(54)により連結されている。A first intermediate header (52) having a bottomed cylindrical shape is connected to an end of the first split flat tube (50) on the split side, and a second split flat tube (50) is connected.
A bottomed cylindrical second intermediate header (53) is connected to the end of the split side of (51). First intermediate header (52) and second intermediate header
(53) is substantially parallel to the front (windward) end of the first intermediate header (52) and the rear (downward) of the second intermediate header (53).
The ends are connected by an S-shaped connecting pipe (54).
【００３０】図６は、第１中間ヘッダ(52)、連結管(54)
および第２中間ヘッダ(53)を通る前後における冷媒の混
合状態を概略的に示すものである。入口管(47)から第１
中間ヘッダ(52)に達するまでは、各冷媒通路(49)のうち
風上側に近いものほど蒸発完了部（図６において斜線を
施していない部分）が大きくなっており、風上側に近い
ものでは冷媒は液状（図６において斜線を施した部分）
となっている。液状冷媒は、連結管(54)に沿ってターン
させられて第２直管部(50)に流れ、さらに各冷媒通路(4
9)に分かれて流される。ターンさせられるさいには、液
状冷媒の慣性により、風上側により多くの液状冷媒が流
れることになる。ここで、連結管(54)がＳ字形であり、
第１中間ヘッダ(52)の出口が風上側にあるため、より風
上側に冷媒が流れ、しかも冷媒の混合も助長される。し
たがって、出口管(48)に近いところにおいては、各冷媒
通路(49)の蒸発完了部がほぼ同じ大きさとすることがで
き、しかも、第１実施例よりも蒸発完了部を大きくする
ことができる。FIG. 6 shows the first intermediate header (52) and the connecting pipe (54).
3 schematically shows a mixed state of the refrigerant before and after passing through the second intermediate header (53). First from the inlet pipe (47)
Until reaching the intermediate header (52), the nearer to the windward side of each refrigerant passage (49) is, the larger the evaporation completion portion (the portion not shaded in FIG. 6) is. Refrigerant is liquid (hatched area in Figure 6)
Has become. The liquid refrigerant is turned along the connecting pipe (54) and flows into the second straight pipe portion (50), and further, the respective refrigerant passages (4
It is divided into 9) and washed away. When it is turned, the inertia of the liquid refrigerant causes more liquid refrigerant to flow to the windward side. Here, the connecting pipe (54) is S-shaped,
Since the outlet of the first intermediate header (52) is on the windward side, the refrigerant flows further to the windward side, and the mixing of the refrigerant is also promoted. Therefore, in the vicinity of the outlet pipe (48), the evaporation completion portion of each refrigerant passage (49) can be made substantially the same size, and further, the evaporation completion portion can be made larger than in the first embodiment. .
【００３１】上記第１から第３までの実施例によると、
蒸発が完了してしまって熱交換作用を行わない冷媒通路
(9)(29)(49) をなくすことができ、熱交換性能を向上さ
せることができる。According to the first to third embodiments,
Refrigerant passage that does not perform heat exchange due to completion of evaporation
(9) (29) (49) can be eliminated and heat exchange performance can be improved.
【００３２】図７には、第１実施例、第３実施例、およ
び中間ヘッダの無い従来例の各蒸発器について、各蒸発
器出口近くの風上側の冷媒通路(49)における冷媒温度の
測定結果を示す。図７より分かるように、第１実施例お
よび第３実施例のものでは、従来のものに比べて、最低
温度は高くかつ最高温度との差が小さくなっており、、
かつその周期が長くなっている。このことは、出口にお
ける冷媒の蒸発が盛んであり、しかも冷媒温度が安定し
ていることを示している。すなわち、第１実施例および
第３実施例の蒸発器は、熱交換効率に優れ、しかも冷媒
流量の制御を行う膨張弁の開閉が頻繁となる不安定状態
（ハンチング現象）が起こりにくくなっている。また、
第１実施例と第３実施例との比較では、第３実施例のも
ののほうが、さらに最低温度が高くしたがって最高温度
との差が小さくなっており、偏平管(42)の長さのほぼ中
央に中間ヘッダ(52)(53)を設け、かつ連結管(54)をＳ字
形とすることがより好ましいことが分かる。FIG. 7 shows the measurement of the refrigerant temperature in the refrigerant passage (49) on the windward side near the outlets of the evaporators of the evaporators of the first embodiment, the third embodiment, and the conventional example without the intermediate header. The results are shown. As can be seen from FIG. 7, in the first and third embodiments, the minimum temperature is higher and the difference from the maximum temperature is smaller than that of the conventional one,
And the cycle is getting longer. This means that the evaporation of the refrigerant at the outlet is high and the refrigerant temperature is stable. That is, in the evaporators of the first and third embodiments, the heat exchange efficiency is excellent, and an unstable state (hunting phenomenon) in which the expansion valve that controls the refrigerant flow rate is frequently opened and closed is unlikely to occur. . Also,
A comparison between the first embodiment and the third embodiment shows that the third embodiment has a higher minimum temperature and therefore a smaller difference from the maximum temperature, and the flat tube (42) has a substantially central length. It can be seen that it is more preferable to provide the intermediate headers (52) and (53) in the and the connecting pipe (54) is S-shaped.
【００３３】[0033]
【発明の効果】この発明の熱交換器によると、各冷媒通
路を流れてきた温度差のある冷媒は、第１中間ヘッダ、
連結管および第２中間ヘッダを通る間に混合されて均一
な温度となり、これ以後の熱交換効率を向上させるとと
もに、膨張弁が安定して作動するので制御を容易に行う
ことができる。According to the heat exchanger of the present invention, the refrigerant having the temperature difference flowing through the respective refrigerant passages is transferred to the first intermediate header,
The temperature is mixed while passing through the connecting pipe and the second intermediate header to have a uniform temperature, which improves the heat exchange efficiency thereafter, and the expansion valve operates stably, so that the control can be easily performed.
【００３４】さらに、第１および第２中間ヘッダは出入
口ヘッダと同様の有底筒形であるため、各中間ヘッダと
各分割偏平管とは、出入口ヘッダを偏平管に接合するの
と同様の方法により接合することができ、接合作業を容
易に行うことができ、したがって、上記の高い熱交換効
率を得るために熱交換器の製造がしにくくなるというこ
とはない。Further, since the first and second intermediate headers have a bottomed cylindrical shape similar to the inlet / outlet header, each intermediate header and each divided flat pipe are formed by the same method as that for joining the inlet / outlet header to the flat pipe. Therefore, the joining work can be easily performed, and therefore, it is not difficult to manufacture the heat exchanger in order to obtain the above-mentioned high heat exchange efficiency.
【手続補正２】[Procedure Amendment 2]
【補正対象書類名】図面[Document name to be corrected] Drawing
【補正対象項目名】図７[Name of item to be corrected] Figure 7
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【図７】 [Figure 7]
───────────────────────────────────────────────────── フロントページの続き (72)発明者 大橋 日出雄 堺市海山町６丁224番地 昭和アルミニウ ム株式会社内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hideo Ohashi 6-224, Kaiyamacho, Sakai City, Showa Aluminum Co., Ltd.
Claims (1)
行状偏平管(2)(22)(42) と、これの各直管部(2a)(22a)
(42a)同士の間に介在されたコルゲートフィン(3)(23)(4
3) と、偏平管(2)(22)(42) の両端部にそれぞれ接続さ
れた有底筒形の入口ヘッダ(4)(24)(44) および出口ヘッ
ダ(5)(25)(45) とを備えている熱交換器であって、蛇行
状偏平管(2)(22)(42) が長さの中間部において２つに分
割されており、入口ヘッダ(4)(24)(44) を有する蛇行状
第１分割偏平管(10)(30)(50)の他端部に有底筒形の第１
中間ヘッダ(12)(32)(52)が接続されるとともに、出口ヘ
ッダ(5)(25)(45) を有する蛇行状第２分割偏平管(11)(3
1)(51)の他端部に有底筒形の第２中間ヘッダ(13)(33)(5
3)が接続されて、第１および第２中間ヘッダ(12)(13)(3
2)(33)(52)(53)が略平行状に配置され、第１および第２
中間ヘッダ(12)(13)(32)(33)(52)(53)に、両者を連結す
る連結管(14)(34)(54)が接続されている熱交換器。1. A meandering flat pipe (2) (22) (42) having a plurality of refrigerant passages (9) (29) (49) and respective straight pipe portions (2a) (22a) thereof.
(42a) Corrugated fins interposed between each other (3) (23) (4
3) and the bottomed cylindrical inlet headers (4) (24) (44) and outlet headers (5) (25) (45) connected to both ends of the flat tubes (2) (22) (42) respectively. ) And a meandering flat tube (2) (22) (42) is divided into two in the middle of the length, the inlet header (4) (24) ( 44) The meandering first split flat tube (10) (30) (50) has a bottomed cylindrical first end at the other end.
The meandering second split flat tubes (11) (3) having the outlet headers (5) (25) (45) while the intermediate headers (12) (32) (52) are connected.
1) The other end of (51) has a bottomed cylindrical second intermediate header (13) (33) (5
3) are connected to connect the first and second intermediate headers (12) (13) (3
2) (33) (52) (53) are arranged substantially parallel to each other, and the first and second
A heat exchanger in which intermediate pipes (12) (13) (32) (33) (52) (53) are connected to connecting pipes (14) (34) (54) for connecting the two.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10698993A JPH06317363A (en) | 1993-05-07 | 1993-05-07 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10698993A JPH06317363A (en) | 1993-05-07 | 1993-05-07 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH06317363A true JPH06317363A (en) | 1994-11-15 |
Family
ID=14447657
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10698993A Pending JPH06317363A (en) | 1993-05-07 | 1993-05-07 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06317363A (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19641029A1 (en) * | 1996-10-04 | 1998-04-23 | Audi Ag | Vehicle air conditioner evaporator |
| US7069980B2 (en) | 2002-10-18 | 2006-07-04 | Modine Manufacturing Company | Serpentine, multiple paths heat exchanger |
| DE102007023672A1 (en) * | 2007-05-22 | 2008-11-27 | Institut für Luft- und Kältetechnik gGmbH | Compact condenser for e.g. house-hold refrigerator, has band-like extruded section pipe having breadth that is double thickness of pipe, and two channels that are separated from each other and run parallel to each other |
| DE102007023696A1 (en) * | 2007-05-22 | 2008-11-27 | Institut für Luft- und Kältetechnik gGmbH | Condenser for refrigerator, particularly for household refrigerators, is provided with lines for refrigerants, where lines are formed in band form |
| US20100139891A1 (en) * | 2008-12-04 | 2010-06-10 | Fujitsu Limited | Radiator and cooling unit |
| JP2014501381A (en) * | 2010-12-30 | 2014-01-20 | ピーディーエックス テクノロジーズ エルエルシー | Cooling system controlled by refrigerant quality in the evaporator |
| GB2521113A (en) * | 2013-10-11 | 2015-06-17 | Reaction Engines Ltd | Heat exchangers |
| CN106546112A (en) * | 2016-11-04 | 2017-03-29 | 杭州三花家电热管理系统有限公司 | Coil heat exchanger |
| CN106705018A (en) * | 2016-11-22 | 2017-05-24 | 无锡锡东能源科技有限公司 | Boiler water header structure |
| JP2018048799A (en) * | 2016-09-16 | 2018-03-29 | 東芝ライフスタイル株式会社 | refrigerator |
| CN112923443A (en) * | 2021-03-03 | 2021-06-08 | 青岛海信日立空调系统有限公司 | Air conditioner |
| US11162424B2 (en) | 2013-10-11 | 2021-11-02 | Reaction Engines Ltd | Heat exchangers |
-
1993
- 1993-05-07 JP JP10698993A patent/JPH06317363A/en active Pending
Cited By (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19641029A1 (en) * | 1996-10-04 | 1998-04-23 | Audi Ag | Vehicle air conditioner evaporator |
| DE19641029C2 (en) * | 1996-10-04 | 1999-10-21 | Audi Ag | Evaporator |
| US7069980B2 (en) | 2002-10-18 | 2006-07-04 | Modine Manufacturing Company | Serpentine, multiple paths heat exchanger |
| DE102007023672A1 (en) * | 2007-05-22 | 2008-11-27 | Institut für Luft- und Kältetechnik gGmbH | Compact condenser for e.g. house-hold refrigerator, has band-like extruded section pipe having breadth that is double thickness of pipe, and two channels that are separated from each other and run parallel to each other |
| DE102007023696A1 (en) * | 2007-05-22 | 2008-11-27 | Institut für Luft- und Kältetechnik gGmbH | Condenser for refrigerator, particularly for household refrigerators, is provided with lines for refrigerants, where lines are formed in band form |
| DE102007023696B4 (en) * | 2007-05-22 | 2011-06-22 | Institut für Luft- und Kältetechnik gGmbH, 01309 | Condenser for household refrigerators |
| US20100139891A1 (en) * | 2008-12-04 | 2010-06-10 | Fujitsu Limited | Radiator and cooling unit |
| JP2010133642A (en) * | 2008-12-04 | 2010-06-17 | Fujitsu Ltd | Radiator, cooling unit, cooling system and electronic device |
| JP2014501381A (en) * | 2010-12-30 | 2014-01-20 | ピーディーエックス テクノロジーズ エルエルシー | Cooling system controlled by refrigerant quality in the evaporator |
| GB2521113A (en) * | 2013-10-11 | 2015-06-17 | Reaction Engines Ltd | Heat exchangers |
| GB2521113B (en) * | 2013-10-11 | 2017-05-24 | Reaction Engines Ltd | Heat exchangers |
| US11162424B2 (en) | 2013-10-11 | 2021-11-02 | Reaction Engines Ltd | Heat exchangers |
| US11203975B2 (en) | 2013-10-11 | 2021-12-21 | Reaction Engines Ltd | Heat exchangers |
| US11661888B2 (en) | 2013-10-11 | 2023-05-30 | Reaction Engines Ltd. | Heat exchangers |
| JP2018048799A (en) * | 2016-09-16 | 2018-03-29 | 東芝ライフスタイル株式会社 | refrigerator |
| CN106546112A (en) * | 2016-11-04 | 2017-03-29 | 杭州三花家电热管理系统有限公司 | Coil heat exchanger |
| CN106705018A (en) * | 2016-11-22 | 2017-05-24 | 无锡锡东能源科技有限公司 | Boiler water header structure |
| CN112923443A (en) * | 2021-03-03 | 2021-06-08 | 青岛海信日立空调系统有限公司 | Air conditioner |
| CN112923443B (en) * | 2021-03-03 | 2022-04-01 | 青岛海信日立空调系统有限公司 | Air conditioner |
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