JPH09296994A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JPH09296994A JPH09296994A JP13260096A JP13260096A JPH09296994A JP H09296994 A JPH09296994 A JP H09296994A JP 13260096 A JP13260096 A JP 13260096A JP 13260096 A JP13260096 A JP 13260096A JP H09296994 A JPH09296994 A JP H09296994A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- circular pipe
- pipe
- diameter
- small diameter
- 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
- 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
- F28F9/04—Arrangements for sealing elements into header boxes or end plates
- F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
- F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
- F28F9/182—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding the heat-exchange conduits having ends with a particular shape, e.g. deformed; the heat-exchange conduits or end plates having supplementary joining means, e.g. abutments
-
- 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
- F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05341—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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Details Of Heat-Exchange And Heat-Transfer (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、たとえば車両用空
調装置に用いられる多管式の熱交換器に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-tube heat exchanger used in, for example, a vehicle air conditioner.
【０００２】[0002]
【従来の技術】従来から、多管式熱交換器としては、た
とえば図８ないし図１０に示すようなものが知られてい
る。図において、３１は上タンクを示しており、上タン
ク３１と下タンク３２とは細径管からなる複数の円管３
３によって連通されている。円管３３とタンク３１、３
２との接続部構造は、図９、図１０に示すように、たと
えば円管３３の先端に絞り加工が施され、テーパ部４１
と縮径部４２が形成されている。そして、縮径部４２を
上下タンク３１、３２の円管接続側の壁３４、３５に穿
設された穴３９、４０に挿通させ、該穴３４、３５の内
縁と円管３３の縮径部４２の外周面とをろう付けするこ
とにより、上下タンク３１、３２間が円管３３を介して
連通されるようになっている。2. Description of the Related Art Conventionally, as a multitubular heat exchanger, for example, those shown in FIGS. 8 to 10 have been known. In the drawing, 31 indicates an upper tank, and the upper tank 31 and the lower tank 32 are a plurality of circular pipes 3 each having a small diameter pipe.
3 are in communication. Round pipe 33 and tanks 31, 3
As shown in FIGS. 9 and 10, the structure of the connection portion with 2 is such that the tip end of the circular pipe 33 is drawn, and the tapered portion 41 is formed.
And a reduced diameter portion 42 are formed. Then, the reduced diameter portion 42 is inserted into the holes 39 and 40 formed in the walls 34 and 35 of the upper and lower tanks 31 and 32 on the circular pipe connection side, and the inner edges of the holes 34 and 35 and the reduced diameter portion of the circular pipe 33 are inserted. By brazing the outer peripheral surface of 42, the upper and lower tanks 31, 32 are communicated with each other through a circular pipe 33.
【０００３】上記のような熱交換器においては、入口パ
イプ３７から流入された熱媒（たとえば、冷媒）は、熱
交換器内を循環された後出口パイプ３８から流出される
ようになっている。そして、円管３３内を流れる冷媒と
複数の円管３３を通過する空気との間で熱交換が行われ
るようになっている。In the heat exchanger as described above, the heat medium (for example, a refrigerant) introduced from the inlet pipe 37 is circulated in the heat exchanger and then discharged from the outlet pipe 38. . Then, heat exchange is performed between the refrigerant flowing in the circular pipe 33 and the air passing through the plural circular pipes 33.
【０００４】また、上記熱交換器においては、円管３３
の先端に縮径部４２を設けることにより、タンク３１、
３２の穴３９、４０への円管の挿通作業の容易化が図ら
れている。また、テーパ部４１の外径は、縮径部４２に
向かって徐々に小径になっているが、穴３９、４０の内
径よりも大きく形成されているので、円管３３の上下タ
ンク３１、３２内への一定の挿入代が確保されるように
なっている。Further, in the above heat exchanger, the circular pipe 33
By providing the reduced diameter portion 42 at the tip of the tank 31,
The work of inserting the circular pipe into the holes 39 and 40 of 32 is facilitated. Further, the outer diameter of the tapered portion 41 is gradually reduced toward the reduced diameter portion 42, but since it is formed larger than the inner diameters of the holes 39, 40, the upper and lower tanks 31, 32 of the circular pipe 33 are formed. A certain amount of insertion fee is secured inside.
【０００５】[0005]
【発明が解決しようとする課題】しかしながら、上記の
ような装置においては、円管３３の先端には、テーパ部
４１、縮径部４２が形成されており、図１０に示すよう
にその内径は他の部位に比べて小さくなっている。この
ため、円管３３内を流入する熱媒（たとえば、冷媒）の
圧力損失がこの部分で増大する。However, in the above-mentioned device, the circular tube 33 has the tapered portion 41 and the reduced diameter portion 42 formed at the tip thereof, and as shown in FIG. It is smaller than other parts. Therefore, the pressure loss of the heat medium (for example, refrigerant) flowing in the circular pipe 33 increases at this portion.
【０００６】一般に、流路長ｌ、相当直径（内径）ｄの
通路抵抗Ｐは、 Ｐ＝λ（ｌ／ｄ）・（ｕ2 ／２ｇ） ・・・（１） で表される。ここで、ｕ：流速、ｇ：重力加速度、λ：
係数である。また、冷媒循環量Ｇと流速ｕの関係は、 Ｇ＝３６００・Ａ・ｕ ・・・（２） で表される。ここで、Ａ：流路断面積である。上記
（１）、（２）式より冷媒循環量Ｇを一定、また流路長
ｌをタンク内挿入代とし、任意の管径仕様（ｎ：任意の
管径）ごとに挿入代を同一とした場合、管径ｄn 、通路
断面積Ａn に対する通路抵抗Ｐn は、 Ｐn ＝λ（ｌ／ｄn ）・（１／２ｇ）・（Ｇ／３６００
Ａn ） と表される。次に、Ａn について説明する。まず本熱交
換器における管の配列を図１２を用いて説明すると、管
の外径をＤ、空気流方向の配列ピッチをＸ、それと直交
する方向をＹとする。ここで、管の外径が異なる場合に
も、配列ピッチＸ／Ｄ、及びＹ／Ｄが一定なる条件で、
円管接続側の壁の単位面積当たりに配列できる管本数Ｎ
n について考えてみる。この場合管外径が小さくなる
と、単位面積当たりに配列できる管本数Ｎn は増加す
る。ここで、通路断面積Ａn は、Ａn ＝（１／４）・π
・ｄn 2 ×Ｎn となる。なお、ｄn に関し、管の外径が
変わっても管の肉厚は一定としてｄn の値を決定する。
（管肉厚は、所望の耐食性を得るため、管外径が変わっ
ても一定の値を選定できる。）そして、管径ｄn と通路
抵抗Ｐn の関係を内径２．５ｍｍの場合との比で求める
と、通路抵抗比は、 Ｐn ／Ｐ2.5 ＝ｄ2.5 ／ｄn （Ａ2.5 ／Ａn ）2 と表される。Ｐ2.5 ＝１とした場合のＰn を図１１に示
す。Generally, a passage resistance P having a flow path length 1 and an equivalent diameter (inner diameter) d is expressed by P = λ (l / d) · (u 2 / 2g) (1) Here, u: flow velocity, g: gravitational acceleration, λ:
It is a coefficient. Further, the relationship between the refrigerant circulation amount G and the flow velocity u is expressed by G = 3600 · A · u (2). Here, A: flow path cross-sectional area. According to the above formulas (1) and (2), the refrigerant circulation amount G is constant, the flow path length 1 is used as the insertion allowance in the tank, and the insertion allowance is the same for each arbitrary pipe diameter specification (n: arbitrary pipe diameter). If, tube diameter d n, the flow resistance P n for passage cross sectional area A n, P n = λ ( l / d n) · (1 / 2g) · (G / 3600
A n ). Next, A n will be described. First, the arrangement of the tubes in the heat exchanger will be described with reference to FIG. 12, where the outer diameter of the tubes is D, the arrangement pitch in the air flow direction is X, and the direction orthogonal thereto is Y. Here, even when the outer diameters of the pipes are different, under the condition that the array pitches X / D and Y / D are constant,
Number of pipes that can be arranged per unit area of the wall on the side of circular pipe connection N
Think about n . In this case, when the outer diameter of the pipe becomes small, the number N n of pipes that can be arranged per unit area increases. Here, the passage cross-sectional area A n is A n = (1/4) · π
・ D n 2 × N n . Note relates d n, a thickness of the tube even if the outer diameter is changed in the tube to determine the value of d n is constant.
(For the wall thickness of the pipe, a constant value can be selected even if the outer diameter of the pipe changes in order to obtain desired corrosion resistance.) Then, the relationship between the pipe diameter d n and the passage resistance P n is the same as when the inner diameter is 2.5 mm. When determining the ratio, the passage resistance ratio is expressed as P n / P 2.5 = d 2.5 / d n (a 2.5 / a n) 2. FIG. 11 shows P n when P 2.5 = 1.
【０００７】図１１に示すように、円管３３の内径が減
少していくと、挿入代部分の通路抵抗比が急激に増大す
る。したがって、管肉厚を一定とした場合に管外径の細
径化を行うと熱交換器に対して、上記のような縮径部４
２を形成した場合には、回路圧損が急激に増大するとと
もに性能低下を招くおそれがある。これはとくに、内径
２．０ｍｍ程度以下から顕著となる。As shown in FIG. 11, as the inner diameter of the circular pipe 33 decreases, the passage resistance ratio at the insertion allowance portion rapidly increases. Therefore, if the outer diameter of the pipe is reduced when the pipe wall thickness is constant, the reduced diameter portion 4 as described above is provided to the heat exchanger.
When 2 is formed, the circuit pressure loss may rapidly increase and the performance may be deteriorated. This becomes remarkable especially when the inner diameter is about 2.0 mm or less.
【０００８】本発明の課題は、細径管を用いた多管式熱
交換器において、圧損の増大を防止し、優れた熱交換性
能を発揮する熱交換器を提供することにある。An object of the present invention is to provide a multi-tube heat exchanger using a small-diameter tube, which can prevent an increase in pressure loss and exhibit excellent heat exchange performance.
【０００９】[0009]
【課題を解決するための手段】上記課題を解決するため
に、本発明の熱交換器は、一対のタンクと、該一対のタ
ンク間に延設され該一対のタンク間を連通するように該
一対のタンクに接続された複数の細径管を備えた多管式
熱交換器であって、前記細径管の端部に、該細径管が接
続されるタンクの細径管接続側の壁に係止または係合可
能な拡径部を形成したことを特徴とするものからなる。In order to solve the above-mentioned problems, the heat exchanger of the present invention comprises a pair of tanks, and a heat exchanger extending between the pair of tanks so as to communicate between the pair of tanks. A multi-tubular heat exchanger comprising a plurality of small diameter pipes connected to a pair of tanks, wherein an end of the small diameter pipe is connected to a small diameter pipe connection side of a tank to which the small diameter pipe is connected. It is characterized in that an expanded diameter portion that can be locked or engaged is formed on the wall.
【００１０】上記拡径部は、細径管の端部外周面に形成
された環状膨出部から構成することができる。また、上
記拡径部は、細径管の先端に形成された拡開部として構
成することも可能である。The expanded diameter portion may be composed of an annular bulge portion formed on the outer peripheral surface of the end portion of the small diameter tube. The expanded diameter portion can also be configured as an expanded portion formed at the tip of the small diameter tube.
【００１１】なお、拡径部を、細径管の先端に形成され
た拡開部とした場合には、上記タンクの細径管接続側の
壁を、細径管の拡開部の内面に沿う形状に突出加工し
て、該突出加工部に拡開部を嵌合することが望ましい。When the enlarged diameter portion is an enlarged portion formed at the tip of the small diameter pipe, the wall of the tank on the side of the small diameter pipe is attached to the inner surface of the enlarged portion of the small diameter pipe. It is desirable to perform a protruding process in a shape that conforms to the shape, and to fit the expanding portion into the protruding process part.
【００１２】本発明は細径管の内径が２．０ｍｍ以下の
熱交換器に対して適用できる。The present invention can be applied to a heat exchanger having an inner diameter of a thin tube of 2.0 mm or less.
【００１３】上記熱交換器においては、細径管、すなわ
ち円管の端部に、該円管が接続されるタンクの円管接続
側の壁に係止または係合可能な拡径部が形成されてい
る。つまり、円管の端部には従来のような縮径部は形成
されていないので、とくに細径の円管において、それ自
身の本来の内径以上に小さい内径部は形成されず、円管
接続部内における圧損の増大を防止することができる。
また、上記タンク壁に係止または係合可能な拡径部を形
成することにより、円管端部のタンク内への挿入代を目
標とする範囲内に精度よく納めること、あるいはタンク
内に円管を挿入しないような構造を採用することができ
るので、所望の熱交換器を寸法精度よく構成できるとと
もに、回路内における圧損を一層低減することが可能と
なる。したがって、優れた熱交換性能を有する熱交換器
を得ることができる。In the above heat exchanger, a small-diameter pipe, that is, a circular pipe has an enlarged diameter portion formed at an end thereof which can be locked or engaged with a wall of the tank to which the circular pipe is connected, on the circular pipe connection side. Has been done. In other words, since there is no reduced diameter part formed at the end of the circular pipe as in the conventional case, an inner diameter part smaller than the original inner diameter of itself is not formed especially in a small diameter circular pipe, and the circular pipe connection It is possible to prevent an increase in pressure loss inside the section.
In addition, by forming an expanded diameter portion that can be locked or engaged with the tank wall, it is possible to accurately fit the insertion end of the circular pipe end into the tank within a target range, or to provide a circle inside the tank. Since it is possible to adopt a structure in which no pipe is inserted, it is possible to configure a desired heat exchanger with dimensional accuracy and further reduce pressure loss in the circuit. Therefore, a heat exchanger having excellent heat exchange performance can be obtained.
【００１４】上記拡径部は、円管の外周面に形成された
環状膨出部とすることができる。つまり、円管の外周面
に環状膨出部を形成するのであるから、円管の内径は縮
径されず、圧損の増大を効果的に防止することができ
る。また、環状膨出部は、タンクの円管接続側の壁に係
止されるので、各円管のタンク内への挿入代を均一化す
ることができる。The enlarged diameter portion may be an annular bulge portion formed on the outer peripheral surface of the circular pipe. That is, since the annular bulging portion is formed on the outer peripheral surface of the circular pipe, the inner diameter of the circular pipe is not reduced, and it is possible to effectively prevent an increase in pressure loss. Further, since the annular bulging portion is locked to the wall of the tank on the side where the circular pipe is connected, the insertion allowance of each circular pipe into the tank can be made uniform.
【００１５】また、拡径部は、円管の先端に形成された
拡開部とすることができる。そして、タンクの円管接続
側の壁を拡開部の内面に沿う形状に突出加工し、該突出
加工部に拡開部を嵌合すれば、円管の先端をタンク内部
に突出させずに、また、管の内径を減少させずに両者を
接続することができるので、タンク内での圧損を抑える
とともにタンク内の流れを円滑化でき、熱交換器全体と
しての圧損を一層効果的に抑制することができる。Further, the expanded diameter portion may be an expanded portion formed at the tip of the circular pipe. Then, by projecting the wall of the tank on the side of the circular pipe connection into a shape along the inner surface of the expanding portion, and fitting the expanding portion into the projecting portion, the tip of the circular pipe does not project into the tank. Also, since both can be connected without reducing the inner diameter of the pipe, pressure loss in the tank can be suppressed and flow in the tank can be smoothed, and pressure loss in the heat exchanger as a whole can be suppressed more effectively. can do.
【００１６】[0016]
【発明の実施の形態】以下に、本発明の望ましい実施の
形態について、図面を参照して説明する。図１ないし図
３は、本発明の一実施態様に係る熱交換器を示してい
る。図１において、１は上タンクを示しており、２は下
タンクを示している。一対の上下タンク１、２間には細
径管である複数の円管３が延設され、上下タンク１、２
は、後述するように、接続される円管３を介して互いに
連通されている。DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the drawings. 1 to 3 show a heat exchanger according to one embodiment of the present invention. In FIG. 1, 1 indicates an upper tank and 2 indicates a lower tank. A plurality of circular pipes 3 which are small-diameter pipes are extended between the pair of upper and lower tanks 1 and 2,
Are communicated with each other through the connected circular tubes 3, as will be described later.
【００１７】図２、図３に示すように、円管３の端部に
は、円管３が接続されるタンク１、２の円管接続側の壁
４、５に係止可能な拡径部として環状膨出部６が形成さ
れている。環状膨出部６は、円管３の端部外周面に形成
されている。また、壁４、５には、円管３挿入用の穴
７、８が設けられている。円管３の端部は穴７、８を貫
通し、タンク１、２の内部へ突出されている。円管３の
端部外周面と穴７、８の内縁とはろう付けされている。
そして、環状膨出部６が壁４、５に係止され、円管３の
タンク１、２内への挿入代が所望の一定値に保たれるよ
うになっている。As shown in FIGS. 2 and 3, the end portion of the circular pipe 3 is expanded in diameter so that it can be locked to the walls 4 and 5 on the circular pipe connection side of the tanks 1 and 2 to which the circular pipe 3 is connected. An annular bulging portion 6 is formed as a portion. The annular bulging portion 6 is formed on the outer peripheral surface of the end portion of the circular pipe 3. Further, the walls 4 and 5 are provided with holes 7 and 8 for inserting the circular tube 3. The end of the circular pipe 3 penetrates through the holes 7 and 8 and projects into the tanks 1 and 2. The outer peripheral surface of the end of the circular pipe 3 and the inner edges of the holes 7 and 8 are brazed.
The annular bulging portion 6 is locked to the walls 4 and 5 so that the insertion allowance of the circular pipe 3 into the tanks 1 and 2 is maintained at a desired constant value.
【００１８】なお、円管３の端部外周面に環状膨出部６
を形成する方法はとくに限定されるものではないが、た
とえば図４に示すように、円管３を上型９と下型１０と
で狭持した状態にて治具１１で矢印方向に押圧すること
により形成することができる。An annular bulge 6 is formed on the outer peripheral surface of the end of the circular pipe 3.
There is no particular limitation on the method for forming the circular tube 3, but as shown in FIG. 4, for example, the circular tube 3 is held by the upper die 9 and the lower die 10 and pressed by the jig 11 in the direction of the arrow. Can be formed.
【００１９】本実施態様に係る熱交換器においては、入
口パイプ１２から熱交換器内に導入された冷媒が円管３
内を流通し、該円管３部分を流れる空気との間で熱交換
が行われるようになっている。また、熱交換器内を循環
された冷媒は出口パイプ１３から流出される。In the heat exchanger according to this embodiment, the refrigerant introduced from the inlet pipe 12 into the heat exchanger is the circular pipe 3
Heat is exchanged with the air flowing through the inside and flowing through the circular pipe 3 portion. The refrigerant circulated in the heat exchanger is discharged from the outlet pipe 13.
【００２０】また、本実施態様に係る熱交換器において
は、円管３の端部外周面にタンク１、２の円管接続側の
壁４、５に係止可能な拡径部として環状膨出部６が形成
されている。したがって、円管３には従来のような縮径
部が形成されていないので、管端部挿入部における圧損
の増大を効果的に防止できる。Further, in the heat exchanger according to this embodiment, an annular expansion is formed on the outer peripheral surface of the end portion of the circular pipe 3 as an enlarged diameter portion which can be locked to the walls 4 and 5 on the circular pipe connection side of the tanks 1 and 2. The projecting portion 6 is formed. Therefore, since the circular tube 3 is not formed with a reduced diameter portion as in the conventional case, it is possible to effectively prevent an increase in pressure loss at the tube end portion insertion portion.
【００２１】次に、本実施態様に係る熱交換器と従来の
熱交換器（図８〜図１０）との回路圧損の比較を図５に
基づいて説明する。図５は図１ないし図３に基づく熱交
換器の回路圧損５１と、図８ないし図１０に基づく熱交
換の回路圧損５２を示している。図１ないし図３の熱交
換器に使用した円管の挿入部内径は２．４ｍｍである。
一方、図８ないし図１０に基づく熱交換器の円管の挿入
部内径は１．８ｍｍである。これらの熱交換器は、管挿
入部内径を除き同一の仕様であることは言うまでもな
い。図５より、本実施態様による熱交換器の回路圧損は
効果的に低減されていることが分かる。Next, comparison of circuit pressure loss between the heat exchanger according to this embodiment and the conventional heat exchanger (FIGS. 8 to 10) will be described with reference to FIG. FIG. 5 shows the circuit pressure loss 51 of the heat exchanger according to FIGS. 1 to 3 and the circuit pressure loss 52 of the heat exchange according to FIGS. 8 to 10. The inner diameter of the insertion portion of the circular pipe used in the heat exchanger of FIGS. 1 to 3 is 2.4 mm.
On the other hand, the inner diameter of the insertion portion of the circular pipe of the heat exchanger according to FIGS. 8 to 10 is 1.8 mm. It goes without saying that these heat exchangers have the same specifications except for the inner diameter of the tube insertion portion. From FIG. 5, it can be seen that the circuit pressure loss of the heat exchanger according to this embodiment is effectively reduced.
【００２２】また、環状膨出部６がタンク壁４、５に係
止することにより、円管３のタンク１、２内への挿入代
を一定範囲に精度よく納めることができるので、一層良
好に回路内の圧損増大を防止することができる。Further, since the annular bulging portion 6 is locked to the tank walls 4 and 5, the insertion allowance of the circular pipe 3 into the tanks 1 and 2 can be accurately set within a certain range, which is even better. Moreover, it is possible to prevent an increase in pressure loss in the circuit.
【００２３】図６、図７は、本発明の別の実施態様に係
る熱交換器を示している。本実施態様においては、円管
３の先端に拡径部として拡開部１２が形成されている。
また、タンク１、２の円管接続側の壁４、５には拡開部
１２の内面１３に沿う形状に加工された突出加工部１４
が設けられている。該突出加工部１４には拡開部１２が
嵌合されており、突出加工部１４の外面１５と拡開部１
２の内面１３とはろう付けされている。つまり、本実施
態様においては、円管３の端部に形成された拡径部とし
ての拡開部１２がタンク１、２の壁４、５に係合するよ
うになっている。6 and 7 show a heat exchanger according to another embodiment of the present invention. In the present embodiment, an expanded portion 12 is formed at the tip of the circular pipe 3 as an expanded diameter portion.
Further, on the walls 4 and 5 of the tanks 1 and 2 on the side of the circular pipe connection, a protrusion processing portion 14 processed into a shape along the inner surface 13 of the expansion portion 12.
Is provided. The expanding portion 12 is fitted into the protruding portion 14, and the outer surface 15 of the protruding portion 14 and the expanding portion 1 are fitted together.
The inner surface 13 of 2 is brazed. That is, in this embodiment, the expanded portion 12 as the expanded diameter portion formed at the end of the circular pipe 3 engages with the walls 4 and 5 of the tanks 1 and 2.
【００２４】本実施態様においても、円管３及び突出加
工部１４には縮径部は形成されていないので、流通する
冷媒の圧損を効果的に小さく抑えることができる。ま
た、本実施態様においては、円管３の端部に形成された
拡開部１２がタンク壁４、５に係合するようになってい
るので、タンク１、２内に円管３は挿通されていない。
したがって、回路内の圧損をより効果的に抑制すること
ができる。In this embodiment as well, since the circular tube 3 and the protruding portion 14 are not formed with a reduced diameter portion, the pressure loss of the circulating refrigerant can be effectively suppressed. Further, in the present embodiment, since the expanding portion 12 formed at the end of the circular pipe 3 is adapted to engage with the tank walls 4 and 5, the circular pipe 3 is inserted into the tanks 1 and 2. It has not been.
Therefore, the pressure loss in the circuit can be suppressed more effectively.
【００２５】[0025]
【発明の効果】以上説明したように、本発明によるとき
は、細径管を用いた多管式熱交換器、とくに内径２．０
ｍｍ以下の多管式熱交換器の圧損を効果的に小さく抑え
ることができるとともに、優れた熱交換性能を発揮させ
ることができる。As described above, according to the present invention, a multi-tube heat exchanger using a small diameter tube, especially an inner diameter of 2.0
The pressure loss of the multi-tube heat exchanger having a diameter of mm or less can be effectively suppressed, and excellent heat exchange performance can be exhibited.
【図１】本発明の一実施態様に係る熱交換器の斜視図で
ある。FIG. 1 is a perspective view of a heat exchanger according to an embodiment of the present invention.
【図２】図１の装置の円管とタンクの円管接続側の壁と
の接続状態を示す部分断面図である。FIG. 2 is a partial cross-sectional view showing a connection state between a circular pipe of the apparatus of FIG. 1 and a wall of the tank on the circular pipe connection side.
【図３】図１の装置の円管とタンクの円管接続側の壁と
の接続状態を示す拡大部分断面図である。FIG. 3 is an enlarged partial cross-sectional view showing a connection state between the circular pipe of the apparatus of FIG. 1 and a wall of the tank on the side where the circular pipe is connected.
【図４】図１の装置の円管に拡径部を形成する上下型と
治具の側面図である。FIG. 4 is a side view of an upper die and a jig for forming an enlarged diameter portion on a circular pipe of the apparatus of FIG.
【図５】図１の装置と図８の装置との冷媒循環重量と回
路圧損との関係図である。5 is a relationship diagram between the refrigerant circulating weight and the circuit pressure loss between the device of FIG. 1 and the device of FIG.
【図６】本発明の別の実施態様に係る熱交換器の円管と
タンクの円管接続側の壁との接続状態を示す部分断面図
である。FIG. 6 is a partial cross-sectional view showing a connection state between a circular pipe of a heat exchanger according to another embodiment of the present invention and a wall of the tank on the circular pipe connection side.
【図７】図６の装置の円管とタンクの円管接続側の壁と
の接続状態を示す拡大部分断面図である。7 is an enlarged partial cross-sectional view showing a connection state between the circular pipe of the apparatus of FIG. 6 and a wall of the tank on the circular pipe connection side.
【図８】従来の熱交換器の正面図である。FIG. 8 is a front view of a conventional heat exchanger.
【図９】図８の熱交換器の円管とタンクの円管接続側の
壁との接続状態を示す部分断面図である。9 is a partial cross-sectional view showing a connected state of the circular pipe of the heat exchanger of FIG. 8 and a wall of the tank on the circular pipe connection side.
【図１０】図９の装置の円管の拡大部分断面図である。10 is an enlarged partial sectional view of a circular tube of the apparatus of FIG.
【図１１】円管の内径と通路抵抗比との関係図である。FIG. 11 is a relationship diagram between an inner diameter of a circular pipe and a passage resistance ratio.
【図１２】熱交換器の円管の配列を示す状態図である。FIG. 12 is a state diagram showing an arrangement of circular tubes of a heat exchanger.
１ 上タンク ２ 下タンク ３ 円管 ４ 円管接続側の壁 ５ 円管接続側の壁 ６ 拡径部としての環状膨出部 ７、８ 穴 ９ 上型 １０ 下型 １１ 治具 １２ 拡径部としての拡開部 １３ 内面 １４ 突出加工部 １５ 外面 1 Upper tank 2 Lower tank 3 Circular pipe 4 Circular pipe connection side wall 5 Circular pipe connection side wall 6 Annular swelling part as expanded part 7, 8 holes 9 Upper mold 10 Lower mold 11 Jig 12 Expanded part Expansion part 13 as inner surface 14 Projection processing part 15 External surface
Claims (5)
設され該一対のタンク間を連通するように該一対のタン
クに接続された複数の細径管を備えた多管式熱交換器で
あって、前記細径管の端部に、該細径管が接続されるタ
ンクの細径管接続側の壁に係止または係合可能な拡径部
を形成したことを特徴とする熱交換器。1. A multi-tubular heat exchange comprising a pair of tanks, and a plurality of small-diameter tubes extending between the pair of tanks and connected to the pair of tanks so as to communicate between the pair of tanks. And an enlarged diameter portion formed at an end portion of the small diameter pipe that can be locked or engaged with a wall of the tank to which the small diameter pipe is connected on the small diameter pipe connection side. Heat exchanger.
成された環状膨出部からなる、請求項１の熱交換器。2. The heat exchanger according to claim 1, wherein the enlarged diameter portion comprises an annular bulge portion formed on the outer peripheral surface of the end portion of the small diameter tube.
拡開部からなる、請求項１の熱交換器。3. The heat exchanger according to claim 1, wherein the enlarged diameter portion comprises an enlarged portion formed at the tip of the small diameter tube.
細径管の拡開部の内面に沿う形状に突出加工され、該突
出加工部に前記拡開部が嵌合されている、請求項３の熱
交換器。4. A wall of the tank on the side of the small-diameter pipe connection is projecting processed into a shape along the inner surface of the expanding part of the small-diameter pipe, and the expanding part is fitted to the projecting processed part. The heat exchanger according to claim 3.
る、請求項１ないし４のいずれかに記載の熱交換器。5. The heat exchanger according to claim 1, wherein the inner diameter of the thin tube is 2.0 mm or less.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13260096A JPH09296994A (en) | 1996-04-30 | 1996-04-30 | Heat exchanger |
| EP97302896A EP0805331A3 (en) | 1996-04-30 | 1997-04-28 | Multi-tube heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13260096A JPH09296994A (en) | 1996-04-30 | 1996-04-30 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09296994A true JPH09296994A (en) | 1997-11-18 |
Family
ID=15085133
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13260096A Pending JPH09296994A (en) | 1996-04-30 | 1996-04-30 | Heat exchanger |
Country Status (2)
| Country | Link |
|---|---|
| EP (1) | EP0805331A3 (en) |
| JP (1) | JPH09296994A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105423777A (en) * | 2015-12-29 | 2016-03-23 | 张伟 | Header body shell tube communication pressure-bearing heat exchanger |
| CN105627627A (en) * | 2016-01-21 | 2016-06-01 | 徐明海 | Self-locking fixing device and method for PE pipe and steel bars of pile foundation buried pipe heat exchanger |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2799826B1 (en) * | 1999-09-28 | 2002-03-29 | Valeo Thermique Moteur Sa | HEAT EXCHANGER WITH COMPACT STRUCTURE, PARTICULARLY FOR A MOTOR VEHICLE |
| US6997248B2 (en) | 2004-05-19 | 2006-02-14 | Outokumpu Oyj | High pressure high temperature charge air cooler |
| DE102006003317B4 (en) | 2006-01-23 | 2008-10-02 | Alstom Technology Ltd. | Tube bundle heat exchanger |
| US8177932B2 (en) | 2009-02-27 | 2012-05-15 | International Mezzo Technologies, Inc. | Method for manufacturing a micro tube heat exchanger |
| US9557119B2 (en) | 2009-05-08 | 2017-01-31 | Arvos Inc. | Heat transfer sheet for rotary regenerative heat exchanger |
| US9200853B2 (en) | 2012-08-23 | 2015-12-01 | Arvos Technology Limited | Heat transfer assembly for rotary regenerative preheater |
| US10175006B2 (en) | 2013-11-25 | 2019-01-08 | Arvos Ljungstrom Llc | Heat transfer elements for a closed channel rotary regenerative air preheater |
| US10094626B2 (en) | 2015-10-07 | 2018-10-09 | Arvos Ljungstrom Llc | Alternating notch configuration for spacing heat transfer sheets |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2031668A5 (en) * | 1969-02-03 | 1970-11-20 | Chausson Usines Sa | |
| FR2690515A1 (en) * | 1992-04-24 | 1993-10-29 | Valeo Thermique Moteur Sa | Heat exchanger with oblong section tubes, in particular for motor vehicles. |
| DE4325427A1 (en) * | 1993-07-29 | 1995-02-02 | Behr Gmbh & Co | Heat exchanger, in particular a motor vehicle radiator |
| ES2152111T3 (en) * | 1994-07-22 | 2001-01-16 | Mitsubishi Electric Corp | HEAT EXCHANGER. |
| JPH09280781A (en) * | 1996-04-17 | 1997-10-31 | Sanden Corp | Multitubular heat exchanger |
-
1996
- 1996-04-30 JP JP13260096A patent/JPH09296994A/en active Pending
-
1997
- 1997-04-28 EP EP97302896A patent/EP0805331A3/en not_active Withdrawn
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105423777A (en) * | 2015-12-29 | 2016-03-23 | 张伟 | Header body shell tube communication pressure-bearing heat exchanger |
| CN105627627A (en) * | 2016-01-21 | 2016-06-01 | 徐明海 | Self-locking fixing device and method for PE pipe and steel bars of pile foundation buried pipe heat exchanger |
| CN105627627B (en) * | 2016-01-21 | 2017-10-31 | 徐明海 | Self-locking fixer and method between a kind of pile foundation buried tube heat exchanger PE pipes and reinforcing bar |
Also Published As
| Publication number | Publication date |
|---|---|
| EP0805331A2 (en) | 1997-11-05 |
| EP0805331A3 (en) | 1998-07-08 |
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