JP2007017133A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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JP2007017133A
JP2007017133A JP2005202127A JP2005202127A JP2007017133A JP 2007017133 A JP2007017133 A JP 2007017133A JP 2005202127 A JP2005202127 A JP 2005202127A JP 2005202127 A JP2005202127 A JP 2005202127A JP 2007017133 A JP2007017133 A JP 2007017133A
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fluid
flat tube
heat exchanger
flat
refrigerant
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Hiroyuki Okumura
弘幸 奥村
Masaaki Kawakubo
昌章 川久保
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Denso Corp
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Denso Corp
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    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/0056—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another with U-flow or serpentine-flow inside conduits; with centrally arranged openings on the 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
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

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  • 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)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of combining easily a flow passage for water with a flow passage for a refrigerant. <P>SOLUTION: Header tank parts 23, 24 of the first flat tube 21 are arranged in the same side with respect to a width direction of a plurality of second flat tubes 22. Slots 27a of header tanks 25, 26 are thereby engaged with both end sides of the plurality of second flat tubes 22 to form the flow passage for the refrigerant, and the flow passage for the water is easily combined with the flow passage for the refrigerant, by inserting respective fluid passing parts 21A in the water flow passage layered with the first flat tube 21, between the second flat tubes 22, from a width-directional one side face of the second flat tubes 22. The slots 27a of the header tanks 25, 26 get easy to be engaged with the both end sides of the second flat tubes 22 when engaged, since a positioning jig can be inserted to position the each second flat tube 22 instead of the first flat tube 21, by assembling the flow passage for the water separately from the flow passage for the refrigerant. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、水、ブライン（熱交換媒体）、低圧冷媒などの第1流体と、高圧冷媒などの第２流体とを熱交換させる熱交換器に関するものである。   The present invention relates to a heat exchanger that exchanges heat between a first fluid such as water, brine (heat exchange medium), and a low-pressure refrigerant and a second fluid such as a high-pressure refrigerant.

従来技術として、下記特許文献１の第５実施形態（図７、８）に示されるような熱交換器がある。これは、タンク部と流体流通部とを形成した一対の扁平プレートで形成され、内部に第１流体を流通させる第１扁平チューブを複数本厚み方向に積層し、複数本の第１扁平チューブの一端側に形成され、各第1扁平チューブの流体流通部と連通して第１流体を分配供給する第１ヘッダタンク部と、複数本の第1扁平チューブの他端側に形成され、各第1扁平チューブの流体流通部と連通して流出する第１流体を集合回収する第２ヘッダタンク部とを有している。   As a prior art, there is a heat exchanger as shown in a fifth embodiment (FIGS. 7 and 8) of Patent Document 1 below. This is formed of a pair of flat plates that form a tank part and a fluid circulation part, and a plurality of first flat tubes that circulate a first fluid are laminated in the thickness direction to form a plurality of first flat tubes. A first header tank portion that is formed on one end side, communicates with a fluid circulation portion of each first flat tube and distributes the first fluid, and is formed on the other end side of the plurality of first flat tubes, It has the 2nd header tank part which collects and collects the 1st fluid which communicates with the fluid circulation part of 1 flat tube, and flows out.

また、内部に第２流体が流通する複数の流路が一体に形成された第２扁平チューブを複数本と、複数本の第２扁平チューブの一端側に設けられ、各第２扁平チューブの複数の流路と連通して第２流体を分配供給する第３ヘッダタンク部と、複数本の第２扁平チューブの他端側に設けられ、各第２扁平チューブの複数の流路と連通して流出する第２流体を集合回収する第４ヘッダタンク部とを有している。そして、第１扁平チューブと第２扁平チューブとを交互に積層して接触させ、第1流体と第２流体とを熱交換させるようにした熱交換器である。
特開２００３−３２９３７８号公報 A plurality of second flat tubes in which a plurality of flow paths through which the second fluid flows are integrally formed, and one end side of the plurality of second flat tubes, and a plurality of second flat tubes are provided. A third header tank portion that communicates with the flow path and distributes the second fluid and is provided on the other end side of the plurality of second flat tubes, and communicates with the plurality of flow paths of the second flat tubes. And a fourth header tank section for collecting and collecting the second fluid flowing out. The first flat tube and the second flat tube are alternately stacked and brought into contact with each other to exchange heat between the first fluid and the second fluid.
JP 2003-329378 A

上記特許文献１の第５実施形態（図７、８）に示されるような熱交換器では、複数の第１扁平チューブと複数の第２扁平チューブとを交互に積層した後、複数本の第２扁平チューブの両端と第３、第４ヘッダータンクの複数の長孔とを両側から嵌め合せる構造となっている。   In the heat exchanger as shown in the fifth embodiment (FIGS. 7 and 8) of Patent Document 1, a plurality of first flat tubes and a plurality of second flat tubes are alternately stacked, and then a plurality of first flat tubes are stacked. 2 Both ends of the flat tube and a plurality of elongated holes of the third and fourth header tanks are fitted from both sides.

よって、片側づつ嵌め合せるとしても、同時に複数箇所のチューブ端と長孔とを同時に嵌め合せなければならない。しかしながら、第１、第２扁平チューブの各厚み寸法の積み重ねで各第２扁平チューブの積層位置が決まるため、第３、第４ヘッダータンクに設けたスリットと各第２扁平チューブのチューブ端とが嵌め合せにくいという問題点がある。   Therefore, even if it fits one side at a time, it is necessary to fit a plurality of tube ends and long holes at the same time. However, since the stacking positions of the second flat tubes are determined by stacking the thicknesses of the first and second flat tubes, the slits provided in the third and fourth header tanks and the tube ends of the second flat tubes There is a problem that it is difficult to fit.

また、別の問題点として、第２流体が第１流体の流路に混入するおそれがある。例えば、本熱交換器を水−冷媒熱交換器に用いて第１流体に水、第２流体に高圧冷媒を流した場合、侵食によって高圧冷媒の第２扁平チューブに孔が開いて貫通した時には高圧冷媒が水の流れる第１扁平チューブに洩れ、第１扁平チューブに高圧が掛かって熱交換器が破壊してしまう。   Another problem is that the second fluid may be mixed into the flow path of the first fluid. For example, when this heat exchanger is used as a water-refrigerant heat exchanger and water flows as the first fluid and high-pressure refrigerant flows through the second fluid, when a hole is opened through the second flat tube of the high-pressure refrigerant due to erosion. The high-pressure refrigerant leaks into the first flat tube through which water flows, and high pressure is applied to the first flat tube and the heat exchanger is destroyed.

これを防ぐには第２扁平チューブの外周部全体に耐食性処理を施す必要があるが、コストアップとなってしまう。そもそも、熱交換器の設計においては安全を考慮したフェールセーフの考え方として、万が一高圧側の流体が洩れたとしても低圧側の流体流路に混入させずに外気へ逃がすなどの設計としておく必要がある。   In order to prevent this, it is necessary to apply corrosion resistance treatment to the entire outer peripheral portion of the second flat tube, but this increases the cost. In the first place, in the design of heat exchangers, as a fail-safe concept that considers safety, even if the high-pressure side fluid leaks, it is necessary to design it to escape to the outside air without mixing it into the low-pressure side fluid flow path. is there.

本発明は、上記従来技術の問題点に鑑みて成されたものであり、その第１の目的は、第１流体の流路と第２流体の流路とを容易に組み合わせることのできる熱交換器を提供することにあり、その第２の目的は、万が一高圧側の流体が洩れたとしても低圧側の流体流路に混入させずに外気へ逃がすことのできる熱交換器を提供することにある。   The present invention has been made in view of the above-described problems of the prior art, and a first object of the present invention is heat exchange that can easily combine the flow path of the first fluid and the flow path of the second fluid. The second object of the present invention is to provide a heat exchanger that can escape to the outside air without being mixed into the low-pressure fluid flow path even if the high-pressure fluid leaks. is there.

本発明は上記目的を達成するために、請求項１ないし請求項９に記載の技術的手段を採用する。すなわち、請求項１に記載の発明では、タンク部（２３、２４）と流体流通部（２１Ａ）とを形成した一対の扁平プレート（２１ａ、２１ｂ）で形成され、内部に第１流体を流通させる第１扁平チューブ（２１）を複数本厚み方向に積層し、
複数本の第１扁平チューブ（２１）の一端側に形成され、各第1扁平チューブ（２１）の流体流通部（２１Ａ）と連通して第１流体を分配供給する第１ヘッダタンク部（２３）と、
複数本の第1扁平チューブ（２１）の他端側に形成され、各第1扁平チューブ（２１）の流体流通部（２１Ａ）と連通して流出する第１流体を集合回収する第２ヘッダタンク部（２４）と、
内部に第２流体が流通する複数の流路が一体に形成された第２扁平チューブ（２２）を複数本と、
複数本の第２扁平チューブ（２２）の一端側に設けられ、各第２扁平チューブ（２２）の複数の流路と連通して第２流体を分配供給する第３ヘッダタンク部（２５）と、
複数本の第２扁平チューブ（２２）の他端側に設けられ、各第２扁平チューブ（２２）の複数の流路と連通して流出する第２流体を集合回収する第４ヘッダタンク部（２６）とを有し、
第１扁平チューブ（２１）と第２扁平チューブ（２２）とを交互に積層して接触させ、第1流体と第２流体とを熱交換させる熱交換器において、
複数本の第２扁平チューブ（２２）の幅方向に対し、第１扁平チューブ（２１）の第１、第２ヘッダタンク部（２３、２４）を同じ側に配設したことを特徴としている。 In order to achieve the above object, the present invention employs technical means described in claims 1 to 9. That is, in the first aspect of the present invention, it is formed by a pair of flat plates (21a, 21b) in which the tank portions (23, 24) and the fluid circulation portions (21A) are formed, and the first fluid is circulated therein. Laminating a plurality of first flat tubes (21) in the thickness direction,
A first header tank portion (23) formed on one end side of the plurality of first flat tubes (21), and communicates with a fluid circulation portion (21A) of each first flat tube (21) to distribute and supply the first fluid. )When,
A second header tank that is formed on the other end of the plurality of first flat tubes (21) and collects and collects the first fluid that flows out and communicates with the fluid circulation portion (21A) of each first flat tube (21). Part (24);
A plurality of second flat tubes (22) integrally formed with a plurality of flow paths through which the second fluid flows;
A third header tank portion (25) provided on one end side of the plurality of second flat tubes (22) and communicating with the plurality of flow paths of the respective second flat tubes (22) to distribute the second fluid; ,
A fourth header tank section (collected) for collecting and recovering the second fluid that is provided on the other end side of the plurality of second flat tubes (22) and flows out in communication with the plurality of flow paths of the respective second flat tubes (22). 26)
In the heat exchanger in which the first flat tube (21) and the second flat tube (22) are alternately stacked and brought into contact with each other to exchange heat between the first fluid and the second fluid.
The first and second header tank portions (23, 24) of the first flat tube (21) are arranged on the same side with respect to the width direction of the plurality of second flat tubes (22).

この請求項１に記載の発明によれば、複数本の第２扁平チューブ（２２）の両端側に、第３、第４ヘッダータンク（２５、２６）の長孔（２７ａ）を嵌め合せて第２流体の流路を作っておき、これに第1扁平チューブ（２１）を積層した第１流体の流路の各流体流通部（２１Ａ）を、第２扁平チューブ（２２）の幅方向片側面から各第２扁平チューブ（２２）の間に差し込むことにより、第１流体の流路と第２流体の流路とを容易に組み合わせることができるようになる。   According to the first aspect of the present invention, the elongated holes (27a) of the third and fourth header tanks (25, 26) are fitted to both end sides of the plurality of second flat tubes (22). A two-fluid flow path is formed, and each fluid flow portion (21A) of the first fluid flow path in which the first flat tube (21) is laminated thereon is connected to one side surface of the second flat tube (22) in the width direction. By inserting between the second flat tubes (22), the flow path of the first fluid and the flow path of the second fluid can be easily combined.

また、このように第１流体の流路と第２流体の流路とを分けて組み立てることは、第２扁平チューブ（２２）の両端側に、第３、第４ヘッダータンク（２５、２６）の長孔（２７ａ）を嵌め合せる際も、第1扁平チューブ（２１）の代わりに各第２扁平チューブ（２２）を位置決めする位置決め治具を挿入できることことから嵌め合せ易くすることができる。   In addition, assembling the first fluid flow path and the second fluid flow path separately in this way, the third and fourth header tanks (25, 26) are arranged on both ends of the second flat tube (22). When the long holes (27a) are fitted, a positioning jig for positioning the second flat tubes (22) can be inserted instead of the first flat tubes (21), so that the fitting can be facilitated.

これらは、第１扁平チューブ（２１）を一対の扁平プレート（２１ａ、２１ｂ）で形成しているため、タンク位置などはプレス形状次第で形状の自由度が大きいことにもよる。また、一対の扁平プレート（２１ａ、２１ｂ）で形成していることによりチューブ内部に犠牲腐食層を設けることも可能である。   In these, since the first flat tube (21) is formed of a pair of flat plates (21a, 21b), the tank position and the like depend on the press shape and the degree of freedom of the shape is large. Moreover, it is also possible to provide a sacrificial corrosion layer inside a tube by forming with a pair of flat plates (21a, 21b).

また、請求項２に記載の発明では、請求項１に記載の熱交換器において、第１扁平チューブ（２１）と第２扁平チューブ（２２）とをロウ付けにより接合したことを特徴としている。これは、第１扁平チューブ（２１）と第２扁平チューブ（２２）とが接触しているだけでも熱交換器としての機能は果たすが、この請求項２に記載の発明によれば、ロウ付けで接合することにより熱伝達効率を良くすることができる。また、熱交換器としての剛性が高くなり、形状・寸法が安定するうえ、各チューブ間が密閉されることから耐食性も向上させることができる。   Moreover, in invention of Claim 2, in the heat exchanger of Claim 1, the 1st flat tube (21) and the 2nd flat tube (22) were joined by brazing. This functions as a heat exchanger only by the first flat tube (21) and the second flat tube (22) being in contact with each other. It is possible to improve the heat transfer efficiency by joining with. In addition, the rigidity as a heat exchanger is increased, the shape and dimensions are stabilized, and the corrosion resistance can be improved because each tube is hermetically sealed.

また、請求項３に記載の発明では、請求項２に記載の熱交換器において、第２扁平チューブ（２２）と接合する第１扁平チューブ（２１）のロウ付け面を波型形状に形成したことを特徴としている。この請求項３に記載の発明によれば、平面同士のロウ付け性を向上させることができる。   Moreover, in invention of Claim 3, in the heat exchanger of Claim 2, the brazing surface of the 1st flat tube (21) joined to a 2nd flat tube (22) was formed in the waveform shape. It is characterized by that. According to the third aspect of the invention, it is possible to improve the brazing property between the flat surfaces.

また、請求項４に記載の発明では、請求項３に記載の熱交換器において、第２扁平チューブ（２２）のロウ付け面に、優先的に腐食する犠牲腐食層（Ｇ）を設けるとともに、第１扁平チューブ（２１）に形成した波型形状の端部が大気開放されるようにしたことを特徴としている。この請求項４に記載の発明によれば、波加工の端部を大気開放することにより、万が一第１流路もしくは第２流路が腐食して孔が開いたとしても、フェールセーフとして両流体が混合する前に外気に漏洩させることができる。   Moreover, in invention of Claim 4, in the heat exchanger of Claim 3, while providing the sacrificial corrosion layer (G) which corrodes preferentially in the brazing surface of a 2nd flat tube (22), The wave-shaped end portion formed on the first flat tube (21) is open to the atmosphere. According to the fourth aspect of the present invention, even if the first flow path or the second flow path is corroded and a hole is opened by opening the end of wave processing to the atmosphere, both fluids can be used as fail safe. Can be leaked to the outside before mixing.

また、請求項５に記載の発明では、請求項１ないし請求項４のいずれか１項に記載の熱交換器において、第１扁平チューブ（２１）を流通する第１流体の流れ方向と、第２扁平チューブ（２２）を流通する第２流体の流れ方向とが互いに対向することを特徴としている。この請求項５に記載の発明によれば、両流体間での熱交換効率を向上させることができる。   Moreover, in invention of Claim 5, in the heat exchanger of any one of Claim 1 thru | or 4, in the flow direction of the 1st fluid which distribute | circulates a 1st flat tube (21), The flow direction of the 2nd fluid which distribute | circulates 2 flat tubes (22) opposes each other. According to the fifth aspect of the present invention, the efficiency of heat exchange between the two fluids can be improved.

また、請求項６に記載の発明では、請求項１ないし請求項５のいずれか１項に記載の熱交換器において、第１扁平チューブ（２１）による第１流路、もしくは第２扁平チューブ（２２）による第２流路、もしくは第１流路と第２流路との両方に、少なくとも１回以上のＵターンを設けたことを特徴としている。この請求項６に記載の発明によれば、流路長さが長く取れ、両流体間での熱交換効率を向上させることができる。   Moreover, in invention of Claim 6, in the heat exchanger of any one of Claim 1 thru | or 5, the 1st flow path by a 1st flat tube (21), or a 2nd flat tube ( 22), the second flow path or both the first flow path and the second flow path are provided with at least one U-turn. According to the sixth aspect of the present invention, the flow path length can be increased, and the heat exchange efficiency between the two fluids can be improved.

また、請求項７に記載の発明では、請求項１ないし請求項６のいずれか１項に記載の熱交換器において、第１流体として水、第２流体として冷媒を流通させることを特徴としている。この請求項７に記載の発明によれば、本熱交換器を車両用や家庭用の水−冷媒熱交換器に適用することができる。   The invention according to claim 7 is characterized in that, in the heat exchanger according to any one of claims 1 to 6, water is circulated as the first fluid and refrigerant is circulated as the second fluid. . According to the seventh aspect of the present invention, the present heat exchanger can be applied to a water-refrigerant heat exchanger for vehicles or households.

例えば車両用ならば、空調用冷凍サイクルにおいて、放熱器にて大気中に放熱している熱を本熱交換器を用いてエンジン冷却水側に排出させることにより、エンジン起動直後で水温が充分に暖まっていない状況化で水温を上昇させ、エンジンの暖機を促進させてエミッション対応するとともに、冬季では暖房性能向上にも利用することができる。また家庭用ならば、給湯装置に利用することができる。   For example, in the case of a vehicle, in a refrigeration cycle for air conditioning, the heat that is radiated into the atmosphere by a radiator is discharged to the engine cooling water side using this heat exchanger, so that the water temperature is sufficiently high immediately after the engine is started. It can be used to improve the heating performance in winter as well as to increase the water temperature in an unwarmed situation and promote engine warm-up to cope with emissions. Moreover, if it is for home use, it can be used for a hot water supply device.

また、請求項８に記載の発明では、請求項７に記載の熱交換器において、第１扁平チューブ（２１）の厚さを、第２扁平チューブ（２２）の厚さより大きくしたことを特徴としている。この請求項８に記載の発明によれば、水と冷媒との粘性の違いに対応して水の流れる第１扁平チューブ（２１）の厚さを大きくすることにより、流通抵抗を低減して圧力損失を小さくすることができる。   The invention according to claim 8 is characterized in that, in the heat exchanger according to claim 7, the thickness of the first flat tube (21) is made larger than the thickness of the second flat tube (22). Yes. According to the eighth aspect of the invention, the flow resistance is reduced by increasing the thickness of the first flat tube (21) through which water flows corresponding to the difference in viscosity between water and the refrigerant. Loss can be reduced.

また、請求項９に記載の発明では、請求項１ないし請求項６のいずれか１項に記載の熱交換器において、第１流体として低圧冷媒、前記第２流体として高圧冷媒を流通させることを特徴としている。この請求項９に記載の発明によれば、本熱交換器を蒸気圧縮式冷凍サイクルの内部熱交換器（４）に適用することができる。例えば、二酸化炭素冷媒はＲ１３４ａなどのフロン系冷媒と比べて定圧比熱が大きいため、低圧側熱交換器の入口側の乾き度が大きくなる。   In the invention according to claim 9, in the heat exchanger according to any one of claims 1 to 6, the low-pressure refrigerant is circulated as the first fluid and the high-pressure refrigerant is circulated as the second fluid. It is a feature. According to the invention of the ninth aspect, the present heat exchanger can be applied to the internal heat exchanger (4) of the vapor compression refrigeration cycle. For example, since the carbon dioxide refrigerant has a large constant-pressure specific heat as compared with a fluorocarbon refrigerant such as R134a, the dryness on the inlet side of the low-pressure side heat exchanger is increased.

そのため、低圧側熱交換器の入口側と出口側でのエンタルピ差が小さくなり、低圧側熱交換器（６）の空気冷却能力が低下する。そこで、本発明の熱交換器を利用して高圧側熱交換器（３）で冷却された冷媒と低圧側熱交換器（６）で熱交換を終えた冷媒との間で熱交換をし、低圧側熱交換器（６）の入口側と出口側でのエンタルピ差を大きくして冷却能力を向上させるのに利用することができる。ちなみに、上記各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示す一例である。   Therefore, the enthalpy difference between the inlet side and the outlet side of the low-pressure side heat exchanger is reduced, and the air cooling capacity of the low-pressure side heat exchanger (6) is reduced. Therefore, heat exchange is performed between the refrigerant cooled in the high-pressure side heat exchanger (3) and the refrigerant whose heat exchange has been completed in the low-pressure side heat exchanger (6) using the heat exchanger of the present invention, This can be used to increase the enthalpy difference between the inlet side and the outlet side of the low pressure side heat exchanger (6) to improve the cooling capacity. Incidentally, the reference numerals in parentheses of the above means are examples showing the correspondence with the specific means described in the embodiments described later.

（第１実施形態）
以下、本発明の第１実施形態（請求項１〜５、７、８に対応）について、添付した図１〜７を用いて詳細に説明する。図１は、本発明の実施形態に係わる水−冷媒熱交換器２と内部熱交換器４とを用いた冷凍サイクルの模式図である。まず、冷媒回路Ｒを説明する。 (First embodiment)
Hereinafter, a first embodiment of the present invention (corresponding to claims 1 to 5, 7, and 8) will be described in detail with reference to FIGS. FIG. 1 is a schematic diagram of a refrigeration cycle using a water-refrigerant heat exchanger 2 and an internal heat exchanger 4 according to an embodiment of the present invention. First, the refrigerant circuit R will be described.

本冷凍サイクルは二酸化炭素（ＣＯ２）を冷媒として用いており、圧縮機１で圧縮（本実施形態では、約１５ＭＰａ）された高温高圧のガス冷媒は、水−冷媒熱交換器２にて温水回路Ｗを流通するエンジン冷却水に放熱して冷却される。そして、冷媒回路Ｒを構成するガスクーラ３と内部熱交換器４とを通過して更に冷却される。ガスクーラ３は、冷媒回路Ｒの放熱器を構成するものである。 The refrigeration cycle uses carbon dioxide (CO 2 ) as a refrigerant, and the high-temperature and high-pressure gas refrigerant compressed by the compressor 1 (about 15 MPa in the present embodiment) is heated by the water-refrigerant heat exchanger 2. Heat is dissipated to the engine coolant flowing through the circuit W to be cooled. And it passes through the gas cooler 3 and the internal heat exchanger 4 which comprise the refrigerant circuit R, and is further cooled. The gas cooler 3 constitutes a radiator of the refrigerant circuit R.

また、内部熱交換器４は、ガスクーラ３で冷却された冷媒と、エバポレータ６で熱交換を終えた低温の冷媒との間で熱交換をするものである。これは、ＣＯ２冷媒が従来のＲ１３４ａ冷媒などと比べて定圧比熱が大きいため、エバポレータ６の入口側の乾き度が大きくなる。そのため、エバポレータ６の入口側と出口側でのエンタルピ差が小さくなり、エバポレータ６の空気冷却能力が低下する。 The internal heat exchanger 4 exchanges heat between the refrigerant cooled by the gas cooler 3 and the low-temperature refrigerant whose heat exchange has been completed by the evaporator 6. This is because the CO 2 refrigerant has a large constant pressure specific heat as compared with the conventional R134a refrigerant and the like, and the dryness on the inlet side of the evaporator 6 increases. Therefore, the enthalpy difference between the inlet side and the outlet side of the evaporator 6 is reduced, and the air cooling capacity of the evaporator 6 is reduced.

そこで、内部熱交換器４を用いてガスクーラ３で冷却された冷媒とエバポレータ６で熱交換を終えた冷媒との間で熱交換をし、エバポレータ６の入口側と出口側でのエンタルピ差を大きくして冷却能力の向上を図るものである。内部熱交換器４を流出した冷媒は、減圧器５で減圧（本実施形態では、約５ＭＰａ）された後エバポレータ６に流入する。   Therefore, heat exchange is performed between the refrigerant cooled by the gas cooler 3 using the internal heat exchanger 4 and the refrigerant whose heat exchange has been completed by the evaporator 6, and the enthalpy difference between the inlet side and the outlet side of the evaporator 6 is increased. Thus, the cooling capacity is improved. The refrigerant that has flowed out of the internal heat exchanger 4 is decompressed by the decompressor 5 (about 5 MPa in the present embodiment) and then flows into the evaporator 6.

エバポレータ６は、冷媒回路Ｒの蒸発器を構成するものであり、空気と熱交換を行い、液冷媒が蒸発して低温のガス冷媒となる。エバポレータ６から流出した低温のガス冷媒は、一端アキュームレータ７に流入して気液分離し、ガス冷媒のみが内部熱交換器４にてガスクーラ３から流出された高温の冷媒から受熱して圧縮機１に送られる。   The evaporator 6 constitutes the evaporator of the refrigerant circuit R, exchanges heat with air, and the liquid refrigerant evaporates to become a low-temperature gas refrigerant. The low-temperature gas refrigerant that has flowed out of the evaporator 6 flows into the accumulator 7 to be separated into gas and liquid, and only the gas refrigerant receives heat from the high-temperature refrigerant that has flowed out of the gas cooler 3 in the internal heat exchanger 4 to receive the compressor 1. Sent to.

次に、温水回路Ｗを説明する。温水回路Ｗには、図示しないエンジンの発熱によって温められたエンジン冷却水と車室内の空気とを熱交換して暖房用熱交換器を構成するヒータコア８が設けられており、そのヒータコア８の手前に水−冷媒熱交換器２が接続されている。   Next, the hot water circuit W will be described. The warm water circuit W is provided with a heater core 8 that constitutes a heat exchanger for heating by exchanging heat between engine cooling water heated by heat generated by an engine (not shown) and air in the passenger compartment. A water-refrigerant heat exchanger 2 is connected to the main body.

水−冷媒熱交換器２は、エンジン側から供給されるエンジン冷却水と、圧縮機１で圧縮された高温高圧のガス冷媒との間で熱交換するものである。そして、エンジン冷却水が水−冷媒熱交換器２にて熱交換した後、ヒータコア８を通り、エンジン側に戻るように構成されている。   The water-refrigerant heat exchanger 2 exchanges heat between the engine coolant supplied from the engine side and the high-temperature and high-pressure gas refrigerant compressed by the compressor 1. The engine coolant is configured to return to the engine side through the heater core 8 after exchanging heat in the water-refrigerant heat exchanger 2.

次に、熱交換器２について説明する。図２は、本発明の第１実施形態における熱交換器２の斜視図である。また、図３は図２中のＡ−Ａ断面図であり、熱交換器２の縦断面を示し、図４は図３中のＢ−Ｂ断面図であり、熱交換器２の横断面を示す。   Next, the heat exchanger 2 will be described. FIG. 2 is a perspective view of the heat exchanger 2 in the first embodiment of the present invention. 3 is a cross-sectional view taken along the line AA in FIG. 2, showing a vertical cross section of the heat exchanger 2, and FIG. 4 is a cross-sectional view taken along the line BB in FIG. Show.

図３に示すように、第１流体としてのエンジン冷却水を流通させる流路は、タンク部２３、２４と流体流通部２１Ａとをアルミニウム板をプレス成形にて形成した一対の扁平プレート２１ａ、２１ｂを対向させて重ね合わせて第１扁平チューブ２１を形成し、この第１扁平チューブ２１を複数本厚み方向に積層して形成されている。   As shown in FIG. 3, the flow path through which the engine coolant as the first fluid circulates is a pair of flat plates 21a, 21b in which the tank portions 23, 24 and the fluid circulation portion 21A are formed by press forming an aluminum plate. The first flat tube 21 is formed by superimposing them in a stacked manner, and a plurality of the first flat tubes 21 are stacked in the thickness direction.

そして、各第1扁平チューブ２１の流体流通部２１Ａと連通して水を分配供給する第１ヘッダタンク部２３と、各第1扁平チューブ２１の流体流通部２１Ａと連通して流出する水を集合回収する第２ヘッダタンク部２４とは、同じく扁平プレート２１ａ、２１ｂにプレス成形で形成されたタンク部２３、２４を重ね合わせることで複数本の第１扁平チューブ２１の両端部に形成される。なお、この第１扁平チューブ２１の第１、第２ヘッダタンク部２３、２４は、後述する複数本の第２扁平チューブ２２の幅方向に対して同じ側に配設している。   Then, the first header tank portion 23 that communicates with the fluid circulation portion 21A of each first flat tube 21 and distributes water, and the water that flows out through the fluid circulation portion 21A of each first flat tube 21 gathers. The second header tank parts 24 to be collected are formed at both ends of the plurality of first flat tubes 21 by superimposing tank parts 23 and 24 formed by press molding on the flat plates 21a and 21b. In addition, the 1st, 2nd header tank parts 23 and 24 of this 1st flat tube 21 are arrange | positioned on the same side with respect to the width direction of the several 2nd flat tube 22 mentioned later.

また、第２流体としての高圧冷媒を流通させる流路は、内部に高圧冷媒が流通する複数の流路を押し出し成形にて一体に形成した複数本の第２扁平チューブ２２と、各第２扁平チューブ２２の複数の流路と連通して高圧冷媒を分配供給する第３ヘッダタンク部２５と、各第２扁平チューブ２２の複数の流路と連通して流出する高圧冷媒を集合回収する第４ヘッダタンク部２６とが複数本の第２扁平チューブ２２の両端部に設けられている。   Further, the flow path for circulating the high-pressure refrigerant as the second fluid includes a plurality of second flat tubes 22 integrally formed by extrusion forming a plurality of flow paths through which the high-pressure refrigerant flows, and each of the second flat tubes. A third header tank unit 25 that distributes and supplies the high-pressure refrigerant in communication with the plurality of flow paths of the tubes 22, and a fourth that collects and recovers the high-pressure refrigerant that flows out in communication with the plurality of flow paths of the second flat tubes 22. Header tank portions 26 are provided at both ends of the plurality of second flat tubes 22.

図５は、図３、図４の熱交換器２における第４ヘッダタンク部２６の構成を示す分解斜視図である。ヘッダータンク部２５、２６は図３、図５に示すように、ロウ材を被覆したアルミニウムの圧延材に複数本の第２扁平チューブ２２を差し込んで接合するための長孔２７ａを複数個開け、コの字状に成形した接合プレート２７と、その接合プレート２７の長孔２７ａに対応した連通孔２８ａを開けたアルミニウム材の連通プレート２８と、半円筒形状の冷媒通路２５Ａ、２６Ａを形成したアルミニウム材のタンクプレート２９とから構成されている。   FIG. 5 is an exploded perspective view showing the configuration of the fourth header tank portion 26 in the heat exchanger 2 of FIGS. 3 and 4. As shown in FIGS. 3 and 5, the header tank portions 25 and 26 have a plurality of elongated holes 27a for inserting and joining a plurality of second flat tubes 22 to a rolled aluminum material covered with a brazing material, A joining plate 27 formed in a U-shape, an aluminum communicating plate 28 having a communicating hole 28a corresponding to the elongated hole 27a of the joining plate 27, and aluminum formed with semi-cylindrical refrigerant passages 25A and 26A. And a tank plate 29 of material.

そして、接合プレート２７のコの字状内に連通プレート２８とタンクプレート２９とを入れ、接合プレート２７の両端２７ｂを内側に折り込むことで一体としている。長孔２７ａに差し込まれた第２扁平チューブ２２の端面とタンクプレート２９との間に連通孔２８ａを介することにより、冷媒通路２５Ａ、２６Ａ両脇の平面部においても冷媒通路２５Ａ、２６Ａと第２扁平チューブ２２の全冷媒通路孔が連通するようになっている。   Then, the connecting plate 27 and the tank plate 29 are placed in a U-shape of the joining plate 27, and both ends 27b of the joining plate 27 are folded inward to be integrated. By connecting the communication hole 28a between the end face of the second flat tube 22 inserted into the long hole 27a and the tank plate 29, the refrigerant passages 25A, 26A and the second passages are also formed in the flat portions on both sides of the refrigerant passages 25A, 26A. All the refrigerant passage holes of the flat tube 22 communicate with each other.

なお、冷媒通路２５Ａ、２６Ａの上下端はキャッププレート３０が差し入れられて閉じられるようになっている。そして、プレス成形した一対の扁平プレート２１ａ、２１ｂで形成する、いわゆるドロンカップチューブの第１扁平チューブ２１と、高圧冷媒が通る押し出しの第２扁平チューブ２２とを交互に複数枚積層し接触するように組み合わせてコア部を形成するとともに、全体を炉中でロウ付けすることによって一体に接合している。   The upper and lower ends of the refrigerant passages 25A and 26A are closed by inserting the cap plate 30 therein. Then, a plurality of first flat tubes 21 of so-called drone cup tubes, which are formed by a pair of press-formed flat plates 21a and 21b, and a plurality of extruded second flat tubes 22 through which high-pressure refrigerant passes are alternately stacked and brought into contact with each other. Are combined together to form a core portion, and the whole is joined together by brazing in a furnace.

次に、本実施形態の特徴部を説明する。図６は図３中のＣ部拡大詳細図である。また、図７は図４中のＤ−Ｄ断面図であり、熱交換器２の幅方向断面図である。図６に示すように、第２扁平チューブ２２と接合する第１扁平チューブ２１のロウ付け面、より具体的には一対の扁平プレート２１ａ、２１ｂの外方ロウ付け面を波型形状に形成している。   Next, the characteristic part of this embodiment is demonstrated. FIG. 6 is an enlarged detail view of a portion C in FIG. FIG. 7 is a cross-sectional view taken along the line DD in FIG. 4, and is a cross-sectional view in the width direction of the heat exchanger 2. As shown in FIG. 6, the brazing surface of the first flat tube 21 to be joined to the second flat tube 22, more specifically, the outer brazing surfaces of the pair of flat plates 21a and 21b are formed in a corrugated shape. ing.

更には、第２扁平チューブ２２のロウ付け面に、優先的に腐食する犠牲腐食層Ｇを設けるとともに、図７に示すように、第１扁平チューブ２１に形成した先の波型形状の端部が大気開放されるようにしている。なお、第１扁平チューブ２１は図７に示すように、中間プレート２１ｃやインナーフィン２１ｄを設けて流路を微細化し、伝熱面積を増やすことによって熱伝達効率を向上させたり、一体ロウ付けして耐圧強度を向上させたりしても良い。   Further, a sacrificial corrosion layer G that preferentially corrodes is provided on the brazing surface of the second flat tube 22 and, as shown in FIG. 7, the end portion of the previous corrugated shape formed on the first flat tube 21. Is open to the atmosphere. As shown in FIG. 7, the first flat tube 21 is provided with an intermediate plate 21c and an inner fin 21d to refine the flow path and increase the heat transfer area, thereby improving the heat transfer efficiency or integrally brazing. The pressure strength may be improved.

最後に全体での流体の流れ方を説明すると、水は第１ヘッダタンク部２３に設けられた流入口２３ａから第１ヘッダタンク部２３内に流入し、各第１扁平チューブ２１に分配供給され、各流体流通部２１Ａを並行して流れ、第２ヘッダタンク部２４で集合回収され、第２ヘッダタンク部２４に設けられた流出口２４ａから流出する流れとなる。   Finally, the flow of the fluid as a whole will be described. Water flows into the first header tank portion 23 from the inlet 23a provided in the first header tank portion 23, and is distributed and supplied to each first flat tube 21. The fluid flows through each fluid circulation part 21A in parallel, is collected and collected by the second header tank part 24, and flows out from the outlet 24a provided in the second header tank part 24.

一方高圧冷媒は、第３ヘッダタンク部２５に設けられた流入口２５１から第３ヘッダタンク部２５内に流入し、各第２扁平チューブ２２に分配供給され、各複数の流路内を先の水とは対向する向きに並行して流れ、第４ヘッダタンク部２６で集合回収され、第４ヘッダタンク部２６に設けられた流出口２２６１から流出する流れとなる。   On the other hand, the high-pressure refrigerant flows into the third header tank section 25 from the inlet 251 provided in the third header tank section 25, is distributed and supplied to each second flat tube 22, and the above-mentioned plurality of flow passages are previously supplied. The water flows in parallel in the opposite direction, is collected and collected by the fourth header tank section 26, and flows out from the outlet 2261 provided in the fourth header tank section 26.

次に、本実施形態での特徴と、その効果について述べる。まず、タンク部２３、２４と流体流通部２１Ａとを形成した一対の扁平プレート２１ａ、２１ｂで形成され、内部に水を流通させる第１扁平チューブ２１を複数本厚み方向に積層し、複数本の第１扁平チューブ２１の一端側に形成され、各第1扁平チューブ２１の流体流通部２１Ａと連通して水を分配供給する第１ヘッダタンク部２３と、複数本の第1扁平チューブ２１の他端側に形成され、各第1扁平チューブ２１の流体流通部２１Ａと連通して流出する水を集合回収する第２ヘッダタンク部２４と、内部に高圧冷媒が流通する複数の流路が一体に形成された第２扁平チューブ２２を複数本と、複数本の第２扁平チューブ２２の一端側に設けられ、各第２扁平チューブ２２の複数の流路と連通して高圧冷媒を分配供給する第３ヘッダタンク部２５と、複数本の第２扁平チューブ２２の他端側に設けられ、各第２扁平チューブ２２の複数の流路と連通して流出する高圧冷媒を集合回収する第４ヘッダタンク部２６とを有し、第１扁平チューブ２１と第２扁平チューブ２２とを交互に積層して接触させ、第1流体と第２流体とを熱交換させる熱交換器において、
複数本の第２扁平チューブ２２の幅方向に対し、第１扁平チューブ２１の第１、第２ヘッダタンク部２３、２４を同じ側に配設している。 Next, features and effects of this embodiment will be described. First, a plurality of first flat tubes 21 that are formed of a pair of flat plates 21a and 21b that form tank portions 23 and 24 and a fluid circulation portion 21A and that circulate water therein are laminated in the thickness direction. A first header tank portion 23 that is formed on one end side of the first flat tube 21, communicates with the fluid circulation portion 21 </ b> A of each first flat tube 21 and distributes water, and other than the first flat tubes 21. A second header tank portion 24 that is formed on the end side and collects and collects water flowing out in communication with the fluid circulation portion 21A of each first flat tube 21, and a plurality of flow paths through which high-pressure refrigerant circulates are integrated. A plurality of formed second flat tubes 22 are provided on one end side of the plurality of second flat tubes 22 and communicated with a plurality of flow paths of the respective second flat tubes 22 to supply and supply high-pressure refrigerant. 3 Header tank 2 And a fourth header tank portion 26 provided on the other end side of the plurality of second flat tubes 22 and collecting and recovering the high-pressure refrigerant flowing out in communication with the plurality of flow paths of the second flat tubes 22. In the heat exchanger in which the first flat tube 21 and the second flat tube 22 are alternately stacked and brought into contact with each other, and heat exchange is performed between the first fluid and the second fluid.
The first and second header tank portions 23 and 24 of the first flat tube 21 are disposed on the same side with respect to the width direction of the plurality of second flat tubes 22.

これによれば、複数本の第２扁平チューブ２２の両端側に、第３、第４ヘッダータンク２５、２６の長孔２７ａを嵌め合せて第２流体の流路を作っておき、これに第1扁平チューブ２１を積層した水の流路の各流体流通部２１Ａを、第２扁平チューブ２２の幅方向片側面から各第２扁平チューブ２２の間に差し込むことにより、水の流路と高圧冷媒の流路とを容易に組み合わせることができるようになる。   According to this, the second fluid flow path is made by fitting the elongated holes 27a of the third and fourth header tanks 25 and 26 to the both end sides of the plurality of second flat tubes 22, By inserting each fluid circulation portion 21A of the water flow path in which the flat tubes 21 are stacked between the second flat tubes 22 from one side in the width direction of the second flat tube 22, the water flow path and the high-pressure refrigerant It becomes possible to easily combine the flow paths.

また、このように水の流路と高圧冷媒の流路とを分けて組み立てることは、第２扁平チューブ２２の両端側に、第３、第４ヘッダータンク２５、２６の長孔２７ａを嵌め合せる際も、第1扁平チューブ２１の代わりに各第２扁平チューブ２２を位置決めする位置決め治具を挿入できることことから嵌め合せ易くすることができる。   In addition, assembling the water flow path and the high-pressure refrigerant flow path in such a manner allows the elongated holes 27a of the third and fourth header tanks 25 and 26 to be fitted to both end sides of the second flat tube 22. In this case, since the positioning jig for positioning each second flat tube 22 can be inserted instead of the first flat tube 21, it can be easily fitted.

これらは、第１扁平チューブ２１を一対の扁平プレート２１ａ、２１ｂで形成しているため、タンク位置などはプレス形状次第で形状の自由度が大きいことにもよる。また、一対の扁平プレート２１ａ、２１ｂで形成していることによりチューブ内部に犠牲腐食層を設けることも可能である。   In these, since the first flat tube 21 is formed by a pair of flat plates 21a and 21b, the tank position and the like depend on the press shape and the degree of freedom of the shape is large. Moreover, it is also possible to provide a sacrificial corrosion layer inside the tube by forming it with a pair of flat plates 21a, 21b.

また、第１扁平チューブ２１と第２扁平チューブ２２とをロウ付けにより接合している。これは、第１扁平チューブ２１と第２扁平チューブ２２とが接触しているだけでも熱交換器としての機能は果たすが、これによれば、ロウ付けで接合することにより熱伝達効率を良くすることができる。また、熱交換器としての剛性が高くなり、形状・寸法が安定するうえ、各チューブ間が密閉されることから耐食性も向上させることができる。   Moreover, the 1st flat tube 21 and the 2nd flat tube 22 are joined by brazing. Although the function as a heat exchanger is achieved even if the first flat tube 21 and the second flat tube 22 are in contact with each other, according to this, heat transfer efficiency is improved by joining by brazing. be able to. In addition, the rigidity as a heat exchanger is increased, the shape and dimensions are stabilized, and the corrosion resistance can be improved because each tube is hermetically sealed.

また、第２扁平チューブ２２と接合する第１扁平チューブ２１のロウ付け面を波型形状に形成している。これによれば、平面同士のロウ付け性を向上させることができる。また、第２扁平チューブ２２のロウ付け面に、優先的に腐食する犠牲腐食層Ｇを設けるとともに、第１扁平チューブ２１に形成した波型形状の端部が大気開放されるようにしている。   Further, the brazing surface of the first flat tube 21 joined to the second flat tube 22 is formed in a corrugated shape. According to this, the brazing property between planes can be improved. A sacrificial corrosion layer G that corrodes preferentially is provided on the brazing surface of the second flat tube 22, and the corrugated end formed on the first flat tube 21 is opened to the atmosphere.

これによれば、波加工の端部を大気開放することにより、万が一水流路もしくは高圧冷媒流路が腐食して孔が開いたとしても、フェールセーフとして両流体が混合する前に外気に漏洩させることができる。また、第１扁平チューブ２１を流通する水の流れ方向と、第２扁平チューブ２２を流通する高圧冷媒の流れ方向とが互いに対向するようにしている。これによれば、両流体間での熱交換効率を向上させることができる。   According to this, by opening the end of wave processing to the atmosphere, even if the water flow path or the high-pressure refrigerant flow path corrodes and opens a hole, it is leaked to the outside air before mixing both fluids as fail-safe be able to. Further, the flow direction of the water flowing through the first flat tube 21 and the flow direction of the high-pressure refrigerant flowing through the second flat tube 22 are opposed to each other. According to this, the heat exchange efficiency between both fluids can be improved.

また、第１流体として水、第２流体として高圧冷媒を流通させている。これによれば、本熱交換器を車両用や家庭用の水−冷媒熱交換器に適用することができる。例えば車両用ならば、空調用冷凍サイクルにおいて、放熱器にて大気中に放熱している熱を本熱交換器を用いてエンジン冷却水側に排出させることにより、エンジン起動直後で水温が充分に暖まっていない状況化で水温を上昇させ、エンジンの暖機を促進させてエミッション対応するとともに、冬季では暖房性能向上にも利用することができる。   Further, water is circulated as the first fluid and high-pressure refrigerant is circulated as the second fluid. According to this, this heat exchanger can be applied to the water-refrigerant heat exchanger for vehicles or households. For example, in the case of a vehicle, in a refrigeration cycle for air conditioning, the heat that is radiated into the atmosphere by a radiator is discharged to the engine cooling water side using this heat exchanger, so that the water temperature is sufficiently high immediately after the engine is started. It can be used to improve the heating performance in winter as well as to increase the water temperature in an unwarmed situation and promote engine warm-up to cope with emissions.

また家庭用ならば、給湯装置に利用することができる。また、第１扁平チューブ２１の厚さを、第２扁平チューブ２２の厚さより大きくしている。これによれば、水と冷媒との粘性の違いに対応して水の流れる第１扁平チューブ２１の厚さを大きくすることにより、流通抵抗を低減して圧力損失を小さくすることができる。   Moreover, if it is for home use, it can be used for a hot water supply apparatus. Further, the thickness of the first flat tube 21 is larger than the thickness of the second flat tube 22. According to this, the flow resistance can be reduced and the pressure loss can be reduced by increasing the thickness of the first flat tube 21 through which water flows corresponding to the difference in viscosity between water and the refrigerant.

（第２実施形態）
図８は、本発明の第２実施形態における熱交換器２の横断面図である。これは、第１扁平チューブ２１による第１流路にＵターンを設けたものである。第１ヘッダタンク部２３から流入した第１流体（水）は第１扁平チューブ２１内をＵターンして第２ヘッダタンク部２４から流出する。これに対し、第３ヘッダタンク部２５の２箇所の流体通路２５Ａから分配供給された第２流体（高圧冷媒）は第２扁平チューブ２２内を直進して第４ヘッダタンク部２６の２箇所の流体通路２６Ａで集合回収されて流出する。 (Second Embodiment)
FIG. 8 is a cross-sectional view of the heat exchanger 2 in the second embodiment of the present invention. This is a U-turn provided in the first flow path by the first flat tube 21. The first fluid (water) flowing in from the first header tank portion 23 makes a U-turn in the first flat tube 21 and flows out from the second header tank portion 24. On the other hand, the second fluid (high-pressure refrigerant) distributed and supplied from the two fluid passages 25A of the third header tank portion 25 travels straight in the second flat tube 22 and reaches the two locations of the fourth header tank portion 26. Collected and recovered by the fluid passage 26A and then flows out.

（第３実施形態）
図９は、本発明の第３実施形態における熱交換器２の横断面図である。これは、第２扁平チューブ２２による第２流路にＵターンを設けたものである。第１ヘッダタンク部２３から流入した第１流体（水）は第１扁平チューブ２１内を直進して第２ヘッダタンク部２４から流出する。 (Third embodiment)
FIG. 9 is a cross-sectional view of the heat exchanger 2 in the third embodiment of the present invention. This is a U-turn provided in the second flow path by the second flat tube 22. The first fluid (water) flowing in from the first header tank portion 23 goes straight through the first flat tube 21 and flows out from the second header tank portion 24.

これに対し、第３ヘッダタンク部２５の２箇所の流体通路のうち、一方の流体通路２５Ａから分配供給された第２流体（高圧冷媒）は、一方の第２扁平チューブ２２Ａ内を直進して第４ヘッダタンク部２６の２箇所の流体通路のうち、一方の流体通路２６Ａで一旦集合回収される。   On the other hand, of the two fluid passages of the third header tank portion 25, the second fluid (high-pressure refrigerant) distributed and supplied from one fluid passage 25A travels straight in the second flat tube 22A. Of the two fluid passages of the fourth header tank section 26, the fluid is once collected and collected by one fluid passage 26A.

第４ヘッダタンク部２６の２箇所の流体通路２６Ａ、２６Ｂは連通しており、第４ヘッダタンク部２６の２箇所の流体通路のうち、他方の流体通路２６Ｂから再度分配供給された第２流体（高圧冷媒）は、他方の第２扁平チューブ２２Ｂ内を直進して第３ヘッダタンク部２５の２箇所の流体通路のうち、他方の流体通路２５Ｂで集合回収されて流出する。   The two fluid passages 26A and 26B of the fourth header tank portion 26 communicate with each other, and the second fluid redistributed and supplied from the other fluid passage 26B among the two fluid passages of the fourth header tank portion 26. The (high-pressure refrigerant) goes straight in the other second flat tube 22B, and is collected and discharged in the other fluid passage 25B out of the two fluid passages of the third header tank portion 25, and flows out.

（第４実施形態）
図１０は、本発明の第４実施形態における熱交換器２の横断面図である。これは、第１扁平チューブ２１による第１流路、および第２扁平チューブ２２による第２流路のそれぞれにＵターンを設けたものである。第１ヘッダタンク部２３から流入した第１流体（水）は第１扁平チューブ２１内をＵターンして第２ヘッダタンク部２４から流出する。 (Fourth embodiment)
FIG. 10 is a cross-sectional view of the heat exchanger 2 in the fourth embodiment of the present invention. This is a U-turn provided in each of the first flow path by the first flat tube 21 and the second flow path by the second flat tube 22. The first fluid (water) flowing in from the first header tank portion 23 makes a U-turn in the first flat tube 21 and flows out from the second header tank portion 24.

これに対し、第３ヘッダタンク部２５の２箇所の流体通路のうち、一方の流体通路２５Ａから分配供給された第２流体（高圧冷媒）は、一方の第２扁平チューブ２２Ａ内を直進して第４ヘッダタンク部２６の２箇所の流体通路のうち、一方の流体通路２６Ａで一旦集合回収される。   On the other hand, of the two fluid passages of the third header tank portion 25, the second fluid (high-pressure refrigerant) distributed and supplied from one fluid passage 25A travels straight in the second flat tube 22A. Of the two fluid passages of the fourth header tank section 26, the fluid is once collected and collected by one fluid passage 26A.

第４ヘッダタンク部２６の２箇所の流体通路２６Ａ、２６Ｂは連通しており、第４ヘッダタンク部２６の２箇所の流体通路のうち、他方の流体通路２６Ｂから再度分配供給された第２流体（高圧冷媒）は、他方の第２扁平チューブ２２Ｂ内を直進して第３ヘッダタンク部２５の２箇所の流体通路のうち、他方の流体通路２５Ｂで集合回収されて流出する。   The two fluid passages 26A and 26B of the fourth header tank portion 26 communicate with each other, and the second fluid redistributed and supplied from the other fluid passage 26B among the two fluid passages of the fourth header tank portion 26. The (high-pressure refrigerant) goes straight in the other second flat tube 22B, and is collected and discharged in the other fluid passage 25B out of the two fluid passages of the third header tank portion 25, and flows out.

前述した第１実施形態と上述した第２〜第４実施形態との異なる特徴部分を説明する。第２〜第４実施形態（請求項６に対応）では、第１扁平チューブ２１による第１流路、もしくは第２扁平チューブ２２による第２流路、もしくは第１流路と第２流路との両方に、少なくとも１回以上のＵターンを設けている。これによれば、流路長さが長く取れ、両流体間での熱交換効率を向上させることができる。   Different features of the first embodiment described above and the second to fourth embodiments described above will be described. In the second to fourth embodiments (corresponding to claim 6), the first flow path by the first flat tube 21, or the second flow path by the second flat tube 22, or the first flow path and the second flow path, Both are provided with at least one U-turn. According to this, the flow path length can be made long and the heat exchange efficiency between both fluids can be improved.

（その他の実施形態）
上述の実施形態では、水と冷媒とを熱交換する熱交換器に適用したが、本発明に係わる熱交換器はこれに限定されるものではなく、第1流体としては水以外に空気や不凍液・エチレングリコールなどのブライン（熱交換媒体）などと熱交換する熱交換器に適用することができる。また、第２流体として低圧冷媒を流通させても良い（請求項９に対応）。これによれば、本熱交換器を図１の蒸気圧縮式冷凍サイクルの内部熱交換器４に適用することができる。 (Other embodiments)
In the above-described embodiment, the present invention is applied to a heat exchanger that exchanges heat between water and a refrigerant. However, the heat exchanger according to the present invention is not limited to this, and the first fluid may be air or antifreeze liquid other than water. -It can be applied to a heat exchanger that exchanges heat with brine (heat exchange medium) such as ethylene glycol. Further, a low-pressure refrigerant may be circulated as the second fluid (corresponding to claim 9). According to this, this heat exchanger can be applied to the internal heat exchanger 4 of the vapor compression refrigeration cycle of FIG.

例えば、二酸化炭素冷媒はＲ１３４ａなどのフロン系冷媒と比べて定圧比熱が大きいため、エバポレータ６の入口側の乾き度が大きくなる。そのため、エバポレータ６の入口側と出口側でのエンタルピ差が小さくなり、エバポレータ６の空気冷却能力が低下する。そこで、本発明の熱交換器を利用してガスクーラ３で冷却された冷媒とエバポレータ６で熱交換を終えた冷媒との間で熱交換をし、エバポレータ６の入口側と出口側でのエンタルピ差を大きくして冷却能力を向上させるのに利用することができる。   For example, since the carbon dioxide refrigerant has a large constant-pressure specific heat as compared with a fluorocarbon refrigerant such as R134a, the degree of dryness on the inlet side of the evaporator 6 is increased. Therefore, the enthalpy difference between the inlet side and the outlet side of the evaporator 6 is reduced, and the air cooling capacity of the evaporator 6 is reduced. Therefore, heat exchange is performed between the refrigerant cooled by the gas cooler 3 using the heat exchanger of the present invention and the refrigerant after the heat exchange by the evaporator 6, and the enthalpy difference between the inlet side and the outlet side of the evaporator 6 is achieved. Can be used to increase the cooling capacity.

また図１１は、本発明の他の実施形態における熱交換器２の横断面図である。上述した各実施形態と異なる特徴点は、第２流体の流路である第２扁平チューブ２２にも曲げを施したものであり、このように構成しても良い。また図１２は、本発明の他の実施形態における熱交換器２の幅方向断面図である。このように第１流体の流路である第１扁平チューブ２１に丸パイプを用い、その丸パイプをつぶして第２扁平チューブ２２との接合面が平面になるように構成しても良い。   FIG. 11 is a cross-sectional view of the heat exchanger 2 according to another embodiment of the present invention. A different feature from the above-described embodiments is that the second flat tube 22 that is the flow path of the second fluid is also bent, and may be configured in this way. FIG. 12 is a cross-sectional view in the width direction of the heat exchanger 2 in another embodiment of the present invention. In this manner, a round pipe may be used for the first flat tube 21 that is the flow path of the first fluid, and the round pipe may be crushed so that the joint surface with the second flat tube 22 is flat.

本発明の実施形態に係わる水−冷媒熱交換器２と内部熱交換器４とを用いた冷凍サイクルの模式図である。It is a schematic diagram of the refrigerating cycle using the water-refrigerant heat exchanger 2 and the internal heat exchanger 4 concerning embodiment of this invention. 本発明の第１実施形態における熱交換器２の斜視図である。It is a perspective view of the heat exchanger 2 in 1st Embodiment of this invention. 図２中のＡ−Ａ断面図であり、熱交換器２の縦断面を示す。It is AA sectional drawing in FIG. 2, and shows the longitudinal cross-section of the heat exchanger 2. FIG. 図３中のＢ−Ｂ断面図であり、熱交換器２の横断面を示す。FIG. 4 is a cross-sectional view taken along line BB in FIG. 図３、図４の熱交換器２における第４ヘッダタンク部２６の構成を示す分解斜視図である。FIG. 5 is an exploded perspective view showing a configuration of a fourth header tank section 26 in the heat exchanger 2 of FIGS. 3 and 4. 図３中のＣ部拡大詳細図である。FIG. 4 is an enlarged detail view of a portion C in FIG. 3. 図４中のＤ−Ｄ断面図であり、熱交換器２の幅方向断面図である。FIG. 5 is a cross-sectional view taken along the line DD in FIG. 4, and is a cross-sectional view in the width direction of the heat exchanger 2. 本発明の第２実施形態における熱交換器２の横断面図である。It is a cross-sectional view of the heat exchanger 2 in the second embodiment of the present invention. 本発明の第３実施形態における熱交換器２の横断面図である。It is a cross-sectional view of the heat exchanger 2 in the third embodiment of the present invention. 本発明の第４実施形態における熱交換器２の横断面図である。It is a cross-sectional view of the heat exchanger 2 in the fourth embodiment of the present invention. 本発明の他の実施形態における熱交換器２の横断面図である。It is a cross-sectional view of the heat exchanger 2 in other embodiment of this invention. 本発明の他の実施形態における熱交換器２の幅方向断面図である。It is sectional drawing of the width direction of the heat exchanger 2 in other embodiment of this invention.

符号の説明Explanation of symbols

２１…第１扁平チューブ
２１ａ…扁平プレート
２１ｂ…扁平プレート
２１Ａ…流体流通部
２２…第２扁平チューブ
２３…タンク部、第１ヘッダタンク部
２４…タンク部、第２ヘッダタンク部
２５…第３ヘッダタンク部
２６…第４ヘッダタンク部
Ｇ…犠牲腐食層 DESCRIPTION OF SYMBOLS 21 ... 1st flat tube 21a ... Flat plate 21b ... Flat plate 21A ... Fluid distribution part 22 ... 2nd flat tube 23 ... Tank part, 1st header tank part 24 ... Tank part, 2nd header tank part 25 ... 3rd header Tank part 26 ... 4th header tank part G ... Sacrificial corrosion layer

Claims (9)

タンク部（２３、２４）と流体流通部（２１Ａ）とを形成した一対の扁平プレート（２１ａ、２１ｂ）で形成され、内部に第１流体を流通させる第１扁平チューブ（２１）を複数本厚み方向に積層し、
前記複数本の第１扁平チューブ（２１）の一端側に形成され、各第1扁平チューブ（２１）の前記流体流通部（２１Ａ）と連通して前記第１流体を分配供給する第１ヘッダタンク部（２３）と、
前記複数本の第1扁平チューブ（２１）の他端側に形成され、各第1扁平チューブ（２１）の前記流体流通部（２１Ａ）と連通して流出する前記第１流体を集合回収する第２ヘッダタンク部（２４）と、
内部に第２流体が流通する複数の流路が一体に形成された第２扁平チューブ（２２）を複数本と、
前記複数本の第２扁平チューブ（２２）の一端側に設けられ、各第２扁平チューブ（２２）の前記複数の流路と連通して前記第２流体を分配供給する第３ヘッダタンク部（２５）と、
前記複数本の第２扁平チューブ（２２）の他端側に設けられ、各第２扁平チューブ（２２）の前記複数の流路と連通して流出する前記第２流体を集合回収する第４ヘッダタンク部（２６）とを有し、
前記第１扁平チューブ（２１）と前記第２扁平チューブ（２２）とを交互に積層して接触させ、前記第1流体と前記第２流体とを熱交換させる熱交換器において、
前記複数本の第２扁平チューブ（２２）の幅方向に対し、前記第１扁平チューブ（２１）の前記第１、第２ヘッダタンク部（２３、２４）を同じ側に配設したことを特徴とする熱交換器。 A plurality of first flat tubes (21) that are formed by a pair of flat plates (21a, 21b) that form tank portions (23, 24) and fluid circulation portions (21A) and that allow the first fluid to flow therethrough. Laminated in the direction,
A first header tank that is formed on one end side of the plurality of first flat tubes (21) and communicates with the fluid circulation part (21A) of each first flat tube (21) to distribute the first fluid. Part (23);
The first fluid is formed on the other end side of the plurality of first flat tubes (21) and collects and recovers the first fluid flowing out in communication with the fluid circulation portion (21A) of each first flat tube (21). 2 header tank section (24),
A plurality of second flat tubes (22) integrally formed with a plurality of flow paths through which the second fluid flows;
A third header tank portion (provided on one end side of the plurality of second flat tubes (22)), which communicates with the plurality of flow paths of each second flat tube (22) and distributes the second fluid ( 25)
A fourth header that is provided on the other end side of the plurality of second flat tubes (22) and collects and recovers the second fluid that flows out and communicates with the plurality of flow paths of the second flat tubes (22). A tank part (26),
In the heat exchanger for alternately laminating and contacting the first flat tube (21) and the second flat tube (22), and exchanging heat between the first fluid and the second fluid,
The first and second header tank portions (23, 24) of the first flat tube (21) are arranged on the same side with respect to the width direction of the plurality of second flat tubes (22). Heat exchanger. 前記第１扁平チューブ（２１）と前記第２扁平チューブ（２２）とをロウ付けにより接合したことを特徴とする請求項１に記載の熱交換器。   The heat exchanger according to claim 1, wherein the first flat tube (21) and the second flat tube (22) are joined by brazing. 前記第２扁平チューブ（２２）と接合する前記第１扁平チューブ（２１）のロウ付け面を波型形状に形成したことを特徴とする請求項２に記載の熱交換器。   The heat exchanger according to claim 2, wherein a brazing surface of the first flat tube (21) joined to the second flat tube (22) is formed in a corrugated shape. 前記第２扁平チューブ（２２）のロウ付け面に、優先的に腐食する犠牲腐食層（Ｇ）を設けるとともに、前記第１扁平チューブ（２１）に形成した前記波型形状の端部が大気開放されるようにしたことを特徴とする請求項３に記載の熱交換器。   A sacrificial corrosion layer (G) that preferentially corrodes is provided on the brazing surface of the second flat tube (22), and the corrugated end formed on the first flat tube (21) is open to the atmosphere. The heat exchanger according to claim 3, wherein the heat exchanger is configured as described above. 前記第１扁平チューブ（２１）を流通する前記第１流体の流れ方向と、前記第２扁平チューブ（２２）を流通する前記第２流体の流れ方向とが互いに対向することを特徴とする請求項１ないし請求項４のいずれか１項に記載の熱交換器。   The flow direction of the first fluid flowing through the first flat tube (21) and the flow direction of the second fluid flowing through the second flat tube (22) are opposed to each other. The heat exchanger according to any one of claims 1 to 4. 前記第１扁平チューブ（２１）による第１流路、もしくは前記第２扁平チューブ（２２）による第２流路、もしくは前記第１流路と前記第２流路との両方に、少なくとも１回以上のＵターンを設けたことを特徴とする請求項１ないし請求項５のいずれか１項に記載の熱交換器。   At least once in the first flow path by the first flat tube (21), the second flow path by the second flat tube (22), or both the first flow path and the second flow path. The heat exchanger according to any one of claims 1 to 5, wherein a U-turn is provided. 前記第１流体として水、前記第２流体として冷媒を流通させることを特徴とする請求項１ないし請求項６のいずれか１項に記載の熱交換器。   The heat exchanger according to any one of claims 1 to 6, wherein water is circulated as the first fluid and refrigerant is circulated as the second fluid. 前記第１扁平チューブ（２１）の厚さを、前記第２扁平チューブ（２２）の厚さより大きくしたことを特徴とする請求項７に記載の熱交換器。   The heat exchanger according to claim 7, wherein the thickness of the first flat tube (21) is larger than the thickness of the second flat tube (22). 前記第１流体として低圧冷媒、前記第２流体として高圧冷媒を流通させることを特徴とする請求項１ないし請求項６のいずれか１項に記載の熱交換器。   The heat exchanger according to any one of claims 1 to 6, wherein a low-pressure refrigerant is circulated as the first fluid, and a high-pressure refrigerant is circulated as the second fluid.
JP2005202127A 2005-07-11 2005-07-11 Heat exchanger Pending JP2007017133A (en)

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