JP2003106793A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JP2003106793A JP2003106793A JP2001302189A JP2001302189A JP2003106793A JP 2003106793 A JP2003106793 A JP 2003106793A JP 2001302189 A JP2001302189 A JP 2001302189A JP 2001302189 A JP2001302189 A JP 2001302189A JP 2003106793 A JP2003106793 A JP 2003106793A
- Authority
- JP
- Japan
- Prior art keywords
- tank
- tube
- heat exchanger
- refrigerant
- sectional area
- 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
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Details Of Heat-Exchange And Heat-Transfer (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、熱交換器に関す
る。TECHNICAL FIELD The present invention relates to a heat exchanger.
【０００２】[0002]
【従来の技術】自動車用冷凍サイクルの熱交換器は、い
わゆるパラレルフロータイプのものが主流である。これ
は、複数の偏平なチューブと、チューブと連通する筒状
のタンクとを備え、冷媒がタンクからチューブへ分配さ
れ、チューブを流通した冷媒がタンクへ集合するように
なっている。2. Description of the Related Art A so-called parallel flow type heat exchanger is mainly used as a heat exchanger for an automobile refrigeration cycle. This includes a plurality of flat tubes and a tubular tank that communicates with the tubes, the refrigerant is distributed from the tank to the tubes, and the refrigerant flowing through the tubes collects in the tank.
【０００３】チューブには、通常、伝熱面積を増やすた
めにフィンが装着されている。また、最外側のフィンを
保護するとともに、熱交換器全体としての構造的な強度
を補強するために、サイドプレートがタンクに支持され
ている。The tubes are usually fitted with fins to increase the heat transfer area. Further, the side plates are supported by the tank in order to protect the outermost fins and to reinforce the structural strength of the heat exchanger as a whole.
【０００４】タンクには、チューブの端部を挿入するチ
ューブ挿入孔が設けられ、タンクの端部開口は閉塞部材
により閉塞されている。The tank is provided with a tube insertion hole into which the end of the tube is inserted, and the end opening of the tank is closed by a closing member.
【０００５】上記の各構成部材は組み立てた後、炉中に
て一括ろう付けすることにより接合される。After the above components are assembled, they are joined together by brazing in a furnace.
【０００６】自動車用冷凍サイクルの熱交換器は、車室
内空間の確保や燃費向上などのため、小型・軽量化が要
求されている。その結果、タンクの外径は年々小さくな
ってきている。A heat exchanger for a refrigerating cycle for automobiles is required to be small and lightweight in order to secure an interior space of a vehicle and improve fuel efficiency. As a result, the outer diameter of the tank is becoming smaller year by year.
【０００７】また、従来のフロンに代わる冷媒として、
自然冷媒である二酸化炭素を冷媒とする冷凍サイクルが
実用化されつつあるが、二酸化炭素を用いる冷凍サイク
ルは、従来のフロンを用いた冷凍サイクルと比較して動
作圧力が高く、熱交換器にも高度な耐圧性能が要求され
ている。その結果、タンクは厚肉となり、外径に比して
内径が小さくなっている。Also, as a refrigerant replacing conventional CFCs,
A refrigeration cycle using carbon dioxide, which is a natural refrigerant, is being put to practical use, but a refrigeration cycle using carbon dioxide has a higher operating pressure than a refrigeration cycle using a conventional CFC and is also used in a heat exchanger. High pressure resistance is required. As a result, the tank becomes thicker and the inner diameter is smaller than the outer diameter.
【０００８】[0008]
【発明が解決しようとする課題】パラレルフロータイプ
の熱交換器においては、タンクに挿入されたチューブの
端部がタンクの内部に突出しているため、このチューブ
の端部が、タンク内を流れる冷媒の通路抵抗を増加させ
る。このような通路抵抗の増加は、冷媒がチューブ内に
流れ込むのを妨げ、各チューブ内に流れ込む冷媒の量が
不均一になることにより、熱交換器の性能が低下すると
いう問題があった。In the parallel flow type heat exchanger, since the end of the tube inserted into the tank projects into the inside of the tank, the end of this tube flows into the refrigerant inside the tank. Increase passage resistance. Such an increase in passage resistance hinders the refrigerant from flowing into the tubes, and the amount of the refrigerant flowing into each tube becomes non-uniform, resulting in a problem that the performance of the heat exchanger is deteriorated.
【０００９】特に、小型の熱交換器や二酸化炭素を用い
た冷凍サイクルの熱交換器においては、タンクの内径が
小さく、冷媒通路断面積が小さいため、この問題は顕著
になる。Particularly, in a small-sized heat exchanger or a heat exchanger of a refrigeration cycle using carbon dioxide, this problem becomes remarkable because the inner diameter of the tank is small and the refrigerant passage cross-sectional area is small.
【００１０】本発明は以上の点に鑑みてなされたもの
で、パラレルフロータイプの熱交換器において、タンク
内を流れる冷媒の通路抵抗を低減することを目的とす
る。The present invention has been made in view of the above points, and it is an object of the present invention to reduce passage resistance of a refrigerant flowing in a tank in a parallel flow type heat exchanger.
【００１１】[0011]
【課題を解決するための手段】請求項１記載の発明は、
偏平なチューブと、前記チューブの端部を挿入する筒状
のタンクとを備えた熱交換器において、前記タンクの冷
媒入口の面積をＡ、前記チューブの端部が挿入された状
態での前記タンクの通路断面積をＢとすると、Ａ＜Ｂで
あることを特徴とする熱交換器である。The invention according to claim 1 is
In a heat exchanger comprising a flat tube and a tubular tank into which the end of the tube is inserted, the area of the refrigerant inlet of the tank is A, and the tank with the end of the tube inserted The heat exchanger is characterized in that A <B, where B is the cross-sectional area of the passage.
【００１２】本発明によれば、タンクの冷媒入口の面積
よりもタンクの通路断面積を大きくしたので、冷媒がタ
ンクの冷媒入口からタンク内へ流入する際に、通路抵抗
が増加するのを防止することができる。According to the present invention, since the passage sectional area of the tank is made larger than the area of the refrigerant inlet of the tank, the passage resistance is prevented from increasing when the refrigerant flows from the refrigerant inlet of the tank into the tank. can do.
【００１３】請求項２記載の発明は、偏平なチューブ
と、前記チューブの端部を挿入する筒状のタンクとを備
えた熱交換器において、前記チューブの端部が挿入され
た状態での前記タンクの通路断面積は、前記チューブの
端部が挿入されない状態での前記タンクの通路断面積の
６０％以上であることを特徴とする熱交換器である。According to a second aspect of the present invention, in a heat exchanger having a flat tube and a tubular tank into which the end of the tube is inserted, the heat exchanger with the end of the tube inserted is used. In the heat exchanger, the passage cross-sectional area of the tank is 60% or more of the passage cross-sectional area of the tank when the end portion of the tube is not inserted.
【００１４】本発明によれば、チューブの端部がタンク
の内部に突出する量を減らしたので、チューブの端部に
よる通路抵抗の増加がおさえられる。チューブの端部が
挿入された状態でのタンクの通路断面積は、チューブの
端部が挿入されない状態でのタンクの通路断面積の６０
％以上となるようにすることが好ましい。According to the present invention, the amount of protrusion of the end portion of the tube into the inside of the tank is reduced, so that increase in passage resistance due to the end portion of the tube is suppressed. The passage cross-sectional area of the tank when the end of the tube is inserted is 60 times the cross-sectional area of the passage of the tank when the end of the tube is not inserted.
It is preferable to set it to be at least%.
【００１５】請求項３記載の発明は、請求項１又は２記
載の発明において、前記チューブの端部を凹状にカット
したことを特徴とする熱交換器である。A third aspect of the present invention is the heat exchanger according to the first or second aspect of the invention, characterized in that the end portion of the tube is cut into a concave shape.
【００１６】本発明によれば、チューブの端部を凹状に
カットすることにより、チューブの端部がタンクの内部
に突出する量を減らしたので、チューブの端部による通
路抵抗の増加がおさえられる。According to the present invention, by cutting the end portion of the tube into a concave shape, the amount of the end portion of the tube protruding into the tank is reduced, so that the increase in passage resistance due to the end portion of the tube is suppressed. .
【００１７】請求項４記載の発明は、請求項１乃至３の
いずれか記載の発明において、当該熱交換器の内部の圧
力は、前記冷媒の臨界圧力を上まわることを特徴とする
熱交換器である。The invention according to claim 4 is the heat exchanger according to any one of claims 1 to 3, characterized in that the internal pressure of the heat exchanger exceeds the critical pressure of the refrigerant. Is.
【００１８】例えば二酸化炭素を冷媒とする冷凍サイク
ルのように、高圧側の圧力が冷媒の臨界圧力を越える冷
凍サイクルの熱交換器（放熱器）は、高度な耐圧性能が
要求されるためにタンクが厚肉となり、冷媒通路断面積
が小さいため、タンク内に突出したチューブによる通路
抵抗の増加が顕著であるところ、本発明によれば、通路
抵抗を効果的に低減することができる。A heat exchanger (radiator) of a refrigeration cycle in which the pressure on the high pressure side exceeds the critical pressure of the refrigerant, such as a refrigeration cycle using carbon dioxide as a refrigerant, requires a high pressure resistance performance, and therefore a tank. Since the refrigerant has a large thickness and the cross-sectional area of the refrigerant passage is small, the passage resistance is significantly increased by the tube protruding into the tank. According to the present invention, however, the passage resistance can be effectively reduced.
【００１９】[0019]
【発明の実施の形態】以下に、本発明の具体例を図面に
基いて詳細に説明する。BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, specific examples of the present invention will be described in detail with reference to the drawings.
【００２０】図１及び図２に示す本例の熱交換器１は、
自動車の車内冷房用の冷凍サイクルに用いられる放熱器
である。冷媒としては二酸化炭素を採用しており、熱交
換器１内部の圧力は、気温等の使用条件により、冷媒の
臨界圧力を上まわる。The heat exchanger 1 of this embodiment shown in FIGS. 1 and 2 is
This is a radiator used in a refrigeration cycle for cooling the interior of an automobile. Carbon dioxide is used as the refrigerant, and the pressure inside the heat exchanger 1 exceeds the critical pressure of the refrigerant depending on the operating conditions such as the temperature.
【００２１】本例の熱交換器１は、偏平状のチューブ２
１と波型のフィン２２とを交互に積層してなるコア２
と、チューブ２１の端部を挿入するタンク３とを備え、
チューブ２１を流通する冷媒がコア２に伝わる熱にて熱
交換を行う構成となっている。The heat exchanger 1 of this example is composed of a flat tube 2
A core 2 formed by alternately laminating 1 and corrugated fins 22.
And a tank 3 into which the end of the tube 21 is inserted,
The refrigerant flowing through the tube 21 is configured to exchange heat with the heat transmitted to the core 2.
【００２２】コア２の上下側部には、補強部材たるサイ
ドプレート４を設けており、各サイドプレート４の両端
部は、それぞれタンク３に支持されている。Side plates 4 serving as reinforcing members are provided on the upper and lower sides of the core 2, and both ends of each side plate 4 are supported by the tank 3.
【００２３】また、一方のタンク３には冷媒を導入する
入口パイプ５が連通接続されており、他方のタンク３に
は冷媒を排出する出口パイプ６が連通接続されている。An inlet pipe 5 for introducing a refrigerant is connected to one tank 3 and an outlet pipe 6 for discharging a refrigerant is connected to the other tank 3.
【００２４】冷媒は、入口パイプ５から一方のタンク３
の内部に導入されて、チューブ２１に分配され、コア２
に伝わる熱によって熱交換をしつつチューブ２１を流通
した後に、他方のタンク３に集合し、出口パイプ６から
外部に排出される。図１中の白矢印は、冷媒の流れを示
している。The refrigerant flows from the inlet pipe 5 to one tank 3
It is introduced into the inside of the tube and distributed to the tube 21,
After passing through the tube 21 while exchanging heat with the heat transmitted to the other side, they are collected in the other tank 3 and discharged from the outlet pipe 6 to the outside. The white arrow in FIG. 1 indicates the flow of the refrigerant.
【００２５】各タンク３は、両端を閉鎖した管状の部材
であり、各チューブ２１は、複数の小さな流路を有する
偏平状のものである。Each tank 3 is a tubular member whose both ends are closed, and each tube 21 has a flat shape having a plurality of small flow paths.
【００２６】また、各チューブ２１は、一方の端部を一
方のタンク３に挿入され、かつ、他方の端部を他方のタ
ンク３に挿入されている。各タンク３には、長手方向に
わたり、所定のピッチでチューブ２１の端部を挿入する
チューブ挿入孔３１が設けられている。Each tube 21 has one end inserted in one tank 3 and the other end inserted in the other tank 3. Each tank 3 is provided with a tube insertion hole 31 for inserting the end portion of the tube 21 at a predetermined pitch over the longitudinal direction.
【００２７】そして、チューブ２１、フィン２２、タン
ク３、サイドプレート４、入口パイプ５及び出口パイプ
６は、それぞれアルミニウム又はアルミニウム合金から
なる部材であり、治具を用いて一体に組み立てるととも
に、この組み立て体を炉中で一括ろう付けしている。ま
た、このようなろう付けに関し、各部材の要所には、予
めろう材及びフラックスが設けられる。The tube 21, the fins 22, the tank 3, the side plate 4, the inlet pipe 5 and the outlet pipe 6 are members made of aluminum or aluminum alloy, and they are assembled together by using a jig and the assembly is performed. The body is brazed all at once in the furnace. In addition, regarding such brazing, a brazing material and a flux are provided in advance at important points of each member.
【００２８】図３は、本例の熱交換器１におけるチュー
ブ２１及びタンク３を示す断面図である。本例では、タ
ンク３の冷媒入口の面積すなわち入口パイプ５の通路断
面積Ａ（図示省略）と、チューブ２１の端部が挿入され
た状態でのタンク３の通路断面積Ｂとの間にＡ＜Ｂの関
係が成立する。FIG. 3 is a sectional view showing the tube 21 and the tank 3 in the heat exchanger 1 of this example. In this example, the area A of the refrigerant inlet of the tank 3, that is, the passage cross-sectional area A (not shown) of the inlet pipe 5 and the passage cross-sectional area B of the tank 3 with the end portion of the tube 21 inserted is A. <B relationship is established.
【００２９】これにより冷媒がタンクの冷媒入口からタ
ンク内へ流入する際に、通路抵抗が増加するのを防止す
ることができる。This makes it possible to prevent the passage resistance from increasing when the refrigerant flows into the tank from the refrigerant inlet of the tank.
【００３０】また、本例の場合、チューブ２１の端部が
挿入された状態でのタンク３の通路断面積Ｂは、チュー
ブ２１の端部が挿入されない状態でのタンク３の通路断
面積（Ｃとする）の６０％以上となるように、チューブ
２１の挿入量が規制されている。Further, in this example, the passage sectional area B of the tank 3 with the end portion of the tube 21 inserted is the passage sectional area (C) of the tank 3 with the end portion of the tube 21 not inserted. The insertion amount of the tube 21 is regulated to be 60% or more.
【００３１】本例のようにチューブ２１の先端が直線状
にカットされている場合、タンク３の形状にもよるが、
チューブ２１の挿入量を、タンク３の内部のチューブ挿
入方向の寸法ｈのおおよそ１／３以下となるようにすれ
ば、ＢがＣの６０％以上となる。When the tip of the tube 21 is cut straight as in this example, it depends on the shape of the tank 3.
If the insertion amount of the tube 21 is set to be approximately 1/3 or less of the dimension h in the tube insertion direction inside the tank 3, B becomes 60% or more of C.
【００３２】これにより、チューブ２１の端部がタンク
３の内部に突出する量が減少し、チューブの端部による
通路抵抗の増加がおさえられる。As a result, the amount by which the end portion of the tube 21 projects inside the tank 3 is reduced, and the passage resistance due to the end portion of the tube is suppressed.
【００３３】また、図４に示すように、チューブ２１の
端部を凹状にカットすることにより、Ｃに対するＢの割
合を大きくしてもよい。Further, as shown in FIG. 4, the ratio of B to C may be increased by cutting the end of the tube 21 into a concave shape.
【００３４】この場合も、チューブ２１の端部がタンク
３の内部に突出する量が減少し、チューブ２１の端部に
よる通路抵抗の増加がおさえられる。In this case as well, the amount by which the end portion of the tube 21 projects into the tank 3 is reduced, and the passage resistance due to the end portion of the tube 21 is suppressed.
【００３５】以上、二酸化炭素を冷媒とする冷凍サイク
ルの放熱器を例に説明したが、これに限定されず、本発
明は従来のフロンを冷媒とする冷凍サイクルの熱交換器
の小型のものに適用しても有効である。Although the heat radiator of the refrigeration cycle using carbon dioxide as the refrigerant has been described above as an example, the present invention is not limited to this, and the present invention provides a small heat exchanger for the refrigeration cycle using freon as the refrigerant. It is effective even if applied.
【００３６】[0036]
【発明の効果】以上説明したように、請求項１記載の発
明は、偏平なチューブと、前記チューブの端部を挿入す
る筒状のタンクとを備えた熱交換器において、前記タン
クの冷媒入口の面積をＡ、前記チューブの端部が挿入さ
れた状態での前記タンクの通路断面積をＢとすると、Ａ
＜Ｂであることを特徴とする熱交換器である。As described above, the invention according to claim 1 is a heat exchanger provided with a flat tube and a cylindrical tank into which an end of the tube is inserted. Where A is the area and B is the passage cross-sectional area of the tank with the end of the tube inserted.
<B is a heat exchanger characterized by the following.
【００３７】本発明によれば、タンクの冷媒入口の面積
よりもタンクの通路断面積を大きくしたので、冷媒がタ
ンクの冷媒入口からタンク内へ流入する際に、通路抵抗
が増加するのを防止することができる。According to the present invention, the passage sectional area of the tank is made larger than the area of the refrigerant inlet of the tank, so that the passage resistance is prevented from increasing when the refrigerant flows from the refrigerant inlet of the tank into the tank. can do.
【００３８】請求項２記載の発明は、偏平なチューブ
と、前記チューブの端部を挿入する筒状のタンクとを備
えた熱交換器において、前記チューブの端部が挿入され
た状態での前記タンクの通路断面積は、前記チューブの
端部が挿入されない状態での前記タンクの通路断面積の
６０％以上であることを特徴とする熱交換器である。According to a second aspect of the present invention, in a heat exchanger including a flat tube and a tubular tank into which the end of the tube is inserted, the heat exchanger with the end of the tube inserted is used. In the heat exchanger, the passage cross-sectional area of the tank is 60% or more of the passage cross-sectional area of the tank when the end portion of the tube is not inserted.
【００３９】本発明によれば、チューブの端部がタンク
の内部に突出する量を減らしたので、チューブの端部に
よる通路抵抗の増加がおさえられる。チューブの端部が
挿入された状態でのタンクの通路断面積は、チューブの
端部が挿入されない状態でのタンクの通路断面積の６０
％以上となるようにすることが好ましい。According to the present invention, the amount of protrusion of the end portion of the tube into the inside of the tank is reduced, so that increase in passage resistance due to the end portion of the tube is suppressed. The passage cross-sectional area of the tank when the end of the tube is inserted is 60 times the cross-sectional area of the passage of the tank when the end of the tube is not inserted.
It is preferable to set it to be at least%.
【００４０】請求項３記載の発明は、請求項１又は２記
載の発明において、前記チューブの端部を凹状にカット
したことを特徴とする熱交換器である。The invention according to claim 3 is the heat exchanger according to the invention according to claim 1 or 2, characterized in that the end portion of the tube is cut into a concave shape.
【００４１】本発明によれば、チューブの端部を凹状に
カットすることにより、チューブの端部がタンクの内部
に突出する量を減らしたので、チューブの端部による通
路抵抗の増加がおさえられる。According to the present invention, by cutting the end portion of the tube into a concave shape, the amount of the end portion of the tube protruding into the inside of the tank is reduced, so that an increase in passage resistance due to the end portion of the tube can be suppressed. .
【００４２】請求項４記載の発明は、請求項１乃至３の
いずれか記載の発明において、当該熱交換器の内部の圧
力は、前記冷媒の臨界圧力を上まわることを特徴とする
熱交換器である。The invention according to claim 4 is the heat exchanger according to any one of claims 1 to 3, characterized in that the internal pressure of the heat exchanger exceeds the critical pressure of the refrigerant. Is.
【００４３】例えば二酸化炭素を冷媒とする冷凍サイク
ルのように、高圧側の圧力が冷媒の臨界圧力を越える冷
凍サイクルの熱交換器（放熱器）は、高度な耐圧性能が
要求されるためにタンクが厚肉となり、冷媒通路断面積
が小さいため、タンク内に突出したチューブによる通路
抵抗の増加が顕著であるところ、本発明によれば、通路
抵抗を効果的に低減することができる。A heat exchanger (radiator) of a refrigeration cycle in which the pressure on the high pressure side exceeds the critical pressure of the refrigerant, such as a refrigeration cycle using carbon dioxide as a refrigerant, requires a high pressure resistance performance, and therefore a tank. Since the refrigerant has a large thickness and the cross-sectional area of the refrigerant passage is small, the passage resistance is significantly increased by the tube protruding into the tank. According to the present invention, however, the passage resistance can be effectively reduced.
【図１】 本発明の具体例に係り、熱交換器を示す正面
図である。FIG. 1 is a front view showing a heat exchanger according to a specific example of the present invention.
【図２】 本発明の具体例に係り、コア及びタンクを示
す分解斜視図である。FIG. 2 is an exploded perspective view showing a core and a tank according to a specific example of the present invention.
【図３】 本発明の具体例に係り、チューブ及びタンク
を示す断面図である。FIG. 3 is a cross-sectional view showing a tube and a tank according to a specific example of the present invention.
【図４】 本発明の具体例に係り、チューブ及びタンク
を示す断面図である。FIG. 4 is a cross-sectional view showing a tube and a tank according to an embodiment of the present invention.
１ 熱交換器 ２ コア ２１ チューブ ２２ フィン ３ タンク ４ サイドプレート ５ 入口パイプ ６ 出口パイプ 1 heat exchanger 2 cores 21 tubes 22 fins 3 tanks 4 side plates 5 inlet pipe 6 outlet pipe
Claims (4)
を挿入する筒状のタンクとを備えた熱交換器において、 前記タンクの冷媒入口の面積をＡ、 前記チューブの端部が挿入された状態での前記タンクの
通路断面積をＢとすると、 Ａ＜Ｂであることを特徴とする熱交換器。1. A heat exchanger comprising a flat tube and a cylindrical tank into which an end of the tube is inserted, wherein a refrigerant inlet area of the tank is A, and an end of the tube is inserted. A heat exchanger characterized in that when the passage cross-sectional area of the tank in the state is B, A <B.
を挿入する筒状のタンクとを備えた熱交換器において、 前記チューブの端部が挿入された状態での前記タンクの
通路断面積は、前記チューブの端部が挿入されない状態
での前記タンクの通路断面積の６０％以上であることを
特徴とする熱交換器。2. A heat exchanger comprising a flat tube and a tubular tank into which the end of the tube is inserted, wherein the passage cross-sectional area of the tank with the end of the tube inserted is The heat exchanger characterized in that it is 60% or more of the passage cross-sectional area of the tank when the end of the tube is not inserted.
ことを特徴とする請求項１又は２記載の熱交換器。3. The heat exchanger according to claim 1, wherein an end of the tube is cut into a concave shape.
の臨界圧力を上まわることを特徴とする請求項１乃至３
のいずれか記載の熱交換器。4. The pressure inside the heat exchanger exceeds the critical pressure of the refrigerant.
The heat exchanger according to any one of 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001302189A JP2003106793A (en) | 2001-09-28 | 2001-09-28 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001302189A JP2003106793A (en) | 2001-09-28 | 2001-09-28 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003106793A true JP2003106793A (en) | 2003-04-09 |
Family
ID=19122480
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001302189A Pending JP2003106793A (en) | 2001-09-28 | 2001-09-28 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003106793A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007003080A (en) * | 2005-06-23 | 2007-01-11 | Calsonic Kansei Corp | Evaporator |
| JP2010112695A (en) * | 2008-10-07 | 2010-05-20 | Showa Denko Kk | Evaporator |
| JP2013152032A (en) * | 2012-01-24 | 2013-08-08 | Nikkei Nekko Kk | Internal heat exchanger |
| WO2013145965A1 (en) * | 2012-03-27 | 2013-10-03 | サンデン株式会社 | Vehicle interior heat exchanger and member for connecting headers of vehicle interior heat exchanger |
-
2001
- 2001-09-28 JP JP2001302189A patent/JP2003106793A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007003080A (en) * | 2005-06-23 | 2007-01-11 | Calsonic Kansei Corp | Evaporator |
| JP2010112695A (en) * | 2008-10-07 | 2010-05-20 | Showa Denko Kk | Evaporator |
| JP2013152032A (en) * | 2012-01-24 | 2013-08-08 | Nikkei Nekko Kk | Internal heat exchanger |
| WO2013145965A1 (en) * | 2012-03-27 | 2013-10-03 | サンデン株式会社 | Vehicle interior heat exchanger and member for connecting headers of vehicle interior heat exchanger |
| JP2013204825A (en) * | 2012-03-27 | 2013-10-07 | Sanden Corp | In-cabin heat exchanger and between-header connection member of in-cabin heat exchanger |
| US9797656B2 (en) | 2012-03-27 | 2017-10-24 | Sanden Holdings Corporation | Vehicle interior heat exchanger and inter-header connecting member of vehicle interior heat exchanger |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6523603B2 (en) | Double heat exchanger with condenser and radiator | |
| US20070193732A1 (en) | Heat exchanger | |
| JP4767408B2 (en) | Heat exchanger | |
| JP2003314987A (en) | Heat exchanger | |
| JPH11316093A (en) | Liquid-cooled tow-phase heat exchanger | |
| JP2004225961A (en) | Multi-flow type heat exchanger | |
| JP2006322636A (en) | Heat exchanger | |
| JP2008170140A (en) | Heat exchanger for vehicle | |
| JP4542552B2 (en) | Heat exchanger | |
| US20060048930A1 (en) | Heat exchanger | |
| US20080105419A1 (en) | Heat exchanger | |
| JP2003106793A (en) | Heat exchanger | |
| JP3805628B2 (en) | Heat exchanger | |
| JP4430482B2 (en) | Heat exchanger | |
| JP3840736B2 (en) | Laminate heat exchanger | |
| KR100668445B1 (en) | Heat exchanger of header type | |
| JP2002206889A (en) | Heat exchanger | |
| JPWO2006073135A1 (en) | Heat exchange tube, heat exchanger, and refrigeration cycle | |
| JP4679734B2 (en) | Heat exchanger | |
| JP2002318092A (en) | Heat exchanger | |
| JP2000220982A (en) | Heat exchanger | |
| JP2007303734A (en) | Heat exchanger | |
| KR101081962B1 (en) | Heat exchanger | |
| JP2000220979A (en) | Heat exchanger | |
| JP2001336886A (en) | Heat exchanger |