JP2007040605A - Heat exchanger for multistage compression type refrigeration cycle device - Google Patents

Heat exchanger for multistage compression type refrigeration cycle device Download PDF

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JP2007040605A
JP2007040605A JP2005225293A JP2005225293A JP2007040605A JP 2007040605 A JP2007040605 A JP 2007040605A JP 2005225293 A JP2005225293 A JP 2005225293A JP 2005225293 A JP2005225293 A JP 2005225293A JP 2007040605 A JP2007040605 A JP 2007040605A
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radiator
heat exchanger
refrigerant
refrigeration cycle
heat exchange
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Tadashi Ikeda
直史 池田
Junichiro Kasuya
潤一郎 粕谷
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Sanden Corp
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Sanden 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
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0443—Combination of units extending one beside or one above the other
    • 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
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/0287—Other particular headers or end plates having passages for different heat exchange media

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger for multistage compression type refrigeration cycle device, which is miniaturized by incorporating a first radiator and a second radiator to a multiflow heat exchanger in an integrated manner. <P>SOLUTION: In the heat exchanger for multistage compression type refrigeration cycle device comprises the first radiator for cooling primarily compressed refrigerant and the second radiator B for cooling secondarily compressed refrigerant, the first radiator A and the second radiator B are formed as an integrated unit by the multiflow heat exchanger 10 including a pair of headers 11 and 12 for dividing or combining the refrigerant, a plurality of refrigerant distributing heat exchanger tubes erected at intervals between the headers 11 and 12 and a heat exchanger fin 14 interposed each between the heat exchanger tubes 13. According to this structure, the setting space of the first radiator A and the second radiator can be minimized. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、冷媒として二酸化炭素（ＣＯ2）冷媒等を複数回に亘って圧縮する多段圧縮式冷凍サイクル装置に使用される熱交換器に関するものである。 The present invention relates to a heat exchanger used in a multistage compression refrigeration cycle apparatus that compresses a carbon dioxide (CO 2 ) refrigerant or the like as a refrigerant a plurality of times.

従来、この種の多段圧縮式冷凍サイクル装置として図９に示されたものが知られており、この冷凍サイクル装置の冷媒サイクルを図９を参照して説明する。なお、実線矢印はＣＯ2冷媒の流れを示す。 Conventionally, as this type of multistage compression refrigeration cycle apparatus, what is shown in FIG. 9 is known, and the refrigerant cycle of this refrigeration cycle apparatus will be described with reference to FIG. The solid arrow indicates the flow of the CO 2 refrigerant.

まず、ＣＯ2冷媒は多段（２段）圧縮可能な圧縮機１で一次圧縮され、この一次圧縮されたＣＯ2冷媒が第１放熱器２に流される。この第１放熱器２で冷却されたＣＯ2冷媒は再び圧縮機１に戻され、圧縮機１で二次圧縮される。二次圧縮されたＣＯ2冷媒は第２放熱器３に流され、第２放熱器３で冷却される。この低温のＣＯ2冷媒は二重管構造の内部熱交換器４に流され、内部熱交換器４で更に冷却される。しかる後、この低温のＣＯ2冷媒は膨張弁５を通って減圧され、減圧低温冷媒となる。この減圧低温冷媒は蒸発器６に流され、熱交換媒体である水や空気等から吸熱する。この吸熱したＣＯ2冷媒は内部熱交換器４に流され、内部熱交換器４で更に吸熱し、しかる後、低圧高温冷媒となって圧縮機１に戻ることとなる。
特開２００４−３１７０７３号公報 First, the CO 2 refrigerant is primarily compressed by a multistage (two-stage) compressible compressor 1, and this primarily compressed CO 2 refrigerant is passed through the first radiator 2. The CO 2 refrigerant cooled by the first radiator 2 is returned to the compressor 1 and is secondarily compressed by the compressor 1. The second-compressed CO 2 refrigerant flows into the second radiator 3 and is cooled by the second radiator 3. This low-temperature CO 2 refrigerant flows into the internal heat exchanger 4 having a double-pipe structure, and is further cooled by the internal heat exchanger 4. Thereafter, the low-temperature CO 2 refrigerant is depressurized through the expansion valve 5 and becomes a depressurized low-temperature refrigerant. The reduced-pressure low-temperature refrigerant flows into the evaporator 6 and absorbs heat from water, air, or the like that is a heat exchange medium. The absorbed CO 2 refrigerant flows into the internal heat exchanger 4, further absorbs heat in the internal heat exchanger 4, and then returns to the compressor 1 as a low-pressure high-temperature refrigerant.
JP 2004-317073 A

ところで、従来の多段圧縮式冷凍サイクル装置に使用されている熱交換器、即ち、第１放熱器２及び第２放熱器３は、フィンコイル式の熱交換器で構成されている。   By the way, the heat exchangers used in the conventional multistage compression refrigeration cycle apparatus, that is, the first radiator 2 and the second radiator 3 are constituted by fin-coil heat exchangers.

しかしながら、第１放熱器２及び第２放熱器３を一体的にフィンコイル式の熱交換器に組み込むときは、フィンの横幅寸法が大きい分、放熱器全体が大型化するため、設置スペースに余裕のない自動車等では不向きなものとなっていた。   However, when the first radiator 2 and the second radiator 3 are integrally incorporated into a fin coil type heat exchanger, the entire radiator becomes larger due to the large width of the fin, so there is room for installation space. It was unsuitable for automobiles without it.

本発明の目的は前記従来の課題に鑑み、第１放熱器及び第２放熱器をマルチフロー熱交換器に一体的に組み込んで小型化した多段圧縮式冷凍サイクル装置用熱交換器を提供することにある。   An object of the present invention is to provide a heat exchanger for a multistage compression refrigeration cycle apparatus in which the first radiator and the second radiator are integrally incorporated in a multiflow heat exchanger in view of the above-described conventional problems. It is in.

本発明は前記課題を解決するため、請求項１の発明は、一次圧縮された冷媒が冷却される第１放熱器と二次圧縮された冷媒が冷却される第２放熱器とを備えた多段圧縮式冷凍サイクル装置用熱交換器において、第１放熱器及び第２放熱器は、冷媒を分流又は合流させる一対のヘッダと、各ヘッダ間に間隔をおいて複数架設された冷媒流通用の熱交換チューブと、各熱交換チューブの間に介装された熱交換フィンとを有するマルチフロー熱交換器にて一体に形成された構造となっている。   In order to solve the above-mentioned problems, the invention of claim 1 includes a multi-stage including a first radiator that cools a primary compressed refrigerant and a second radiator that cools a secondary compressed refrigerant. In the heat exchanger for the compression refrigeration cycle apparatus, the first radiator and the second radiator include a pair of headers for diverting or merging the refrigerant, and a plurality of refrigerant circulation heats installed at intervals between the headers. It has a structure integrally formed by a multiflow heat exchanger having an exchange tube and heat exchange fins interposed between the heat exchange tubes.

請求項１の発明によれば、第１放熱器及び第２放熱器がマルチフロー熱交換器にて一体成形されているため、熱交換器全体が小型化する。なお、第１放熱器及び第２放熱器を並設するようにしてもよいし（請求項２）、また、第２放熱器を間にして複数の第１放熱器を配置するようにしてもよい（請求項３）。   According to invention of Claim 1, since the 1st heat radiator and the 2nd heat radiator are integrally molded by the multiflow heat exchanger, the whole heat exchanger is reduced in size. The first radiator and the second radiator may be arranged side by side (Claim 2), or a plurality of first radiators may be arranged with the second radiator interposed therebetween. (Claim 3)

また、第１放熱器の冷媒圧力と第２放熱器の冷媒圧力を比較すると、第１放熱器側の冷媒圧力が低くなっているため（二次圧縮冷媒より一次圧縮冷媒の方が圧力が低いため）、第１放熱器側の押さえ板及びキャップの強度が小さくて済み（請求項４及び請求項５）、また、第１放熱器側の熱交換チューブの強度が小さくて済み（請求項６）、逆に第１放熱器側の熱交換チューブの強度が小さい分、第１放熱器側の熱交換チューブの冷媒流通断面積を大きくすることができる（請求項７）。また、熱交換チューブの冷媒流通断面を円形状にするときは、二酸化炭素などの高圧冷媒に対しても強度上優れたものとなる。   Further, when the refrigerant pressure of the first radiator and the refrigerant pressure of the second radiator are compared, the refrigerant pressure on the first radiator side is lower (the pressure of the primary compressed refrigerant is lower than that of the secondary compressed refrigerant). Therefore, the strength of the holding plate and the cap on the first radiator side is small (Claims 4 and 5), and the strength of the heat exchanger tube on the first radiator side is small (Claim 6). On the contrary, since the strength of the heat exchanger tube on the first radiator side is small, the refrigerant flow cross-sectional area of the heat exchanger tube on the first radiator side can be increased (Claim 7). Further, when the refrigerant flow cross section of the heat exchange tube is circular, it is excellent in strength against a high-pressure refrigerant such as carbon dioxide.

更に、請求項９の発明は、請求項１乃至請求項８の多段圧縮式冷凍サイクル装置用熱交換器において、マルチフロー熱交換器で形成された第１放熱器及び第２放熱器は、冷媒と熱交換する熱交換媒体の流れ方向に対して下流側に配置された第１マルチフロー熱交換器と上流側に配置された第２マルチフロー熱交換器とを互いに連通させて並設してなり、第１マルチフロー熱交換器には冷媒入口を通じて流入した冷媒が流通し、第２マルチフロー熱交換器には第１マルチフロー熱交換器を通過した冷媒が流通するよう設定した構造となっている。   Further, the invention of claim 9 is the heat exchanger for a multistage compression refrigeration cycle apparatus according to claims 1 to 8, wherein the first radiator and the second radiator formed by the multiflow heat exchanger are refrigerants. A first multi-flow heat exchanger disposed downstream with respect to the flow direction of the heat exchange medium to exchange heat with the second multi-flow heat exchanger disposed upstream is arranged in parallel with each other. Thus, the first multi-flow heat exchanger has a structure in which the refrigerant flowing in through the refrigerant inlet flows and the second multi-flow heat exchanger is set so that the refrigerant that has passed through the first multi-flow heat exchanger flows. ing.

請求項９の発明によれば、圧縮機から吐出した冷媒が、風下側の第１マルチフロー熱交換器３１に流れた後に、風上側の第２マルチフロー熱交換器３２に流れるので、冷媒と熱交換媒体（例えば空気）との熱交換が効率よく行われる。   According to the ninth aspect of the present invention, since the refrigerant discharged from the compressor flows to the first multiflow heat exchanger 31 on the leeward side and then flows to the second multiflow heat exchanger 32 on the leeward side, Heat exchange with a heat exchange medium (for example, air) is efficiently performed.

なお、請求項１乃至請求項９の多段圧縮式冷凍サイクル装置用熱交換器の冷媒として二酸化炭素を使用するようにしても良い。   In addition, you may make it use a carbon dioxide as a refrigerant | coolant of the heat exchanger for multistage compression refrigeration cycle apparatuses of Claims 1 thru | or 9.

本発明によれば、第１放熱器及び第２放熱器がマルチフロー熱交換器にて一体成形されているため、小型化の多段圧縮式冷凍サイクル装置用熱交換器を実現できるという利点を有する。   According to the present invention, since the first radiator and the second radiator are integrally formed by the multiflow heat exchanger, there is an advantage that a heat exchanger for a multistage compression refrigeration cycle apparatus can be realized with a reduced size. .

図１及び図２は本発明に係る多段圧縮式冷凍サイクル装置用熱交換器の第１実施形態を示すもので、図１は第１実施形態に係るマルチフロー熱交換器の正面図、図２は第１実施形態に係るマルチフロー熱交換器の平面図である。なお、多段圧縮式冷凍サイクル装置の冷媒サイクルは図９で説明した従来例と同一であるため、その図示及び説明を省略する。   1 and 2 show a first embodiment of a heat exchanger for a multistage compression refrigeration cycle apparatus according to the present invention. FIG. 1 is a front view of the multiflow heat exchanger according to the first embodiment. These are top views of the multiflow heat exchanger which concerns on 1st Embodiment. The refrigerant cycle of the multistage compression refrigeration cycle apparatus is the same as that of the conventional example described with reference to FIG.

マルチフロー熱交換器１０は、冷媒を分流又は合流させる一対のヘッダ１１，１２と、各ヘッダ１１，１２の間で冷媒を流通させる複数の熱交換チューブ１３と、熱交換媒体例えば空気と熱交換する熱交換フィン１４と、最上位或いは最下位の熱交換フィン１４を保持する押さえ板１５，１６とから構成されたもので、各部材１１〜１６がろう付けにより一体に固着されている。   The multiflow heat exchanger 10 exchanges heat with a pair of headers 11 and 12 for diverting or merging refrigerant, a plurality of heat exchange tubes 13 for circulating the refrigerant between the headers 11 and 12, and a heat exchange medium such as air. The heat exchange fins 14 and the holding plates 15 and 16 for holding the uppermost or lowermost heat exchange fins 14 are formed, and the members 11 to 16 are integrally fixed by brazing.

各ヘッダ１１，１２は密閉した縦長円筒状を呈したもので、互いに間隔をおいて対向配置されている。また、各ヘッダ１１，１２の内部は上下に２つに分離され、上部には第１放熱器用のタンク部１１ａ，１２ａが形成され、下部には第２放熱器用のタンク部１１ｂ、１２ｂが形成されている。   Each of the headers 11 and 12 has a sealed vertically long cylindrical shape, and is opposed to each other with a space therebetween. Further, the interior of each header 11 and 12 is divided into two vertically, the first radiator tank portions 11a and 12a are formed in the upper portion, and the second radiator tank portions 11b and 12b are formed in the lower portion. Has been.

ここで、第１放熱器用のタンク部１１ａの側壁には一次圧縮冷媒流入口１１ｃが形成され、圧縮機で一次圧縮された冷媒が一次圧縮冷媒流入口１１ｃを通じてタンク部１１ａに流入されるようになっている。第１放熱器用のタンク部１２ａの側壁には一次圧縮冷媒流出口１２ｃが形成され、タンク１２ａに流入した冷媒が一次圧縮冷媒流出口１２ｃを通じて圧縮機に戻されるようになっている。他方、第２放熱器用のタンク部１１ｂの側壁には二次圧縮冷媒流入口１１ｄが形成され、圧縮機で二次圧縮された冷媒が二次圧縮冷媒流入口１１ｄを通じてタンク部１１ｂに流入されるようになっている。第２放熱器用のタンク部１２ｂの側壁には二次圧縮冷媒流出口１２ｄが形成され、タンク１２ｄに流入した冷媒が二次圧縮冷媒流出口１２ｄを通じて内部熱交換器に向かって流出されるようになっている。   Here, a primary compressed refrigerant inlet 11c is formed on the side wall of the tank portion 11a for the first radiator so that the refrigerant primarily compressed by the compressor flows into the tank portion 11a through the primary compressed refrigerant inlet 11c. It has become. A primary compressed refrigerant outlet 12c is formed on the side wall of the tank portion 12a for the first radiator, and the refrigerant flowing into the tank 12a is returned to the compressor through the primary compressed refrigerant outlet 12c. On the other hand, a secondary compressed refrigerant inlet 11d is formed on the side wall of the tank portion 11b for the second radiator, and the refrigerant secondarily compressed by the compressor flows into the tank portion 11b through the secondary compressed refrigerant inlet 11d. It is like that. A secondary compressed refrigerant outlet 12d is formed on the side wall of the tank portion 12b for the second radiator so that the refrigerant flowing into the tank 12d flows out toward the internal heat exchanger through the secondary compressed refrigerant outlet 12d. It has become.

熱交換チューブ１３は偏平状に形成されたもので、各ヘッダ１１，１２間に上下に間隔をおいて多数架設されている。また、各熱交換チューブ１３の両端はヘッダー１１のタンク部１１ａ，１１ｂとヘッダ１２のタンク部１２ａ，１２ｂに連通し、タンク部１１ａからタンク部１２ａに冷媒が流れ、また、タンク部１１ｂからタンク部１２ｂに冷媒が流れるようになっている。   The heat exchanging tube 13 is formed in a flat shape, and a large number of the heat exchanging tubes 13 are installed between the headers 11 and 12 at intervals in the vertical direction. Further, both ends of each heat exchange tube 13 communicate with the tank portions 11a and 11b of the header 11 and the tank portions 12a and 12b of the header 12, and the refrigerant flows from the tank portion 11a to the tank portion 12a. The refrigerant flows through the portion 12b.

熱交換フィン１４は各熱交換チューブ１３の間に介装されたもので、各熱交換チューブ１３に流れる冷媒と各熱交換フィン１４との間に流れる熱交換媒体が各熱交換フィン１４を介して熱交換するようになっている。   The heat exchange fins 14 are interposed between the heat exchange tubes 13, and a heat exchange medium flowing between the refrigerant flowing in the heat exchange tubes 13 and the heat exchange fins 14 passes through the heat exchange fins 14. Heat exchange.

押さえ板１５は最上位の熱交換フィン１４ａの上面を覆うよう延在するとともに、両端側を熱交換フィン１４ａの両端に沿って下方に屈曲させて熱交換フィン１４ａの全体を覆い、これにより、熱交換フィン１４ａを最上位の熱交換チューブ１３に保持するようになっている。他方、押さえ板１６は最下位の熱交換フィン１４ｂの下面を覆うよう延在するとともに、両端側を熱交換フィン１４ｂの両端に沿って上方に屈曲させて熱交換フィン１４ｂの全体を覆い、これにより、熱交換フィン１４ｂを最下位の熱交換チューブ１３に保持するようになっている。   The holding plate 15 extends so as to cover the upper surface of the uppermost heat exchange fin 14a, and both ends are bent downward along both ends of the heat exchange fin 14a to cover the entire heat exchange fin 14a. The heat exchange fins 14a are held in the uppermost heat exchange tube 13. On the other hand, the pressing plate 16 extends so as to cover the lower surface of the lowest heat exchange fin 14b, and both end sides are bent upward along both ends of the heat exchange fin 14b to cover the entire heat exchange fin 14b. Thus, the heat exchange fins 14b are held in the lowest heat exchange tube 13.

以上のように多段圧縮式冷凍サイクル装置用熱交換器をマルチフロー熱交換器１０で構成することにより、第１放熱器Ａ及び第２放熱器Ｂが一体に組み込まれている。   As described above, the heat exchanger for the multistage compression refrigeration cycle apparatus is configured by the multiflow heat exchanger 10, whereby the first radiator A and the second radiator B are integrally incorporated.

即ち、第１放熱器Ａは、タンク部１１ａ，１２ａ、各タンク部１１ａ，１２ａに連通する熱交換チューブ１３、一次圧縮冷媒流入口１１ｃ、一次圧縮冷媒流出口１２ｃ及び押さえ板１５により構成されている。また、第２放熱器Ｂは、タンク部１１ｂ，１２ｂ、各タンク部１１ｂ，１２ｂに連通する熱交換チューブ１３、二次圧縮冷媒流入口１１ｄ、二次圧縮冷媒流出口１２ｄ及び押さえ板１６により構成されている。   That is, the first radiator A includes tank portions 11a and 12a, a heat exchange tube 13 communicating with each of the tank portions 11a and 12a, a primary compressed refrigerant inlet port 11c, a primary compressed refrigerant outlet port 12c, and a holding plate 15. Yes. The second radiator B includes tank portions 11b and 12b, a heat exchange tube 13 communicating with each of the tank portions 11b and 12b, a secondary compressed refrigerant inlet port 11d, a secondary compressed refrigerant outlet port 12d, and a pressing plate 16. Has been.

本実施形態は、前述の如く、第１放熱器Ａ及び第２放熱器Ｂが上下並列でマルチフロー熱交換器１０に一体に組み込まれ、また、マルチフロー熱交換器１０はフィンコイル式熱交換器と比較して設置スペースが狭くて済むため、自動車等の狭い設置スペースにも容易に設置することができる。   In the present embodiment, as described above, the first radiator A and the second radiator B are integrated in the multiflow heat exchanger 10 in a vertical parallel manner, and the multiflow heat exchanger 10 is a fin coil heat exchanger. Since the installation space is narrower than that of the container, it can be easily installed in a narrow installation space such as an automobile.

一般にマルチフロー熱交換器１０では、各熱交換チューブ１３内を流通する高圧冷媒により各熱交換チューブ１３の上下方向に圧力が付加され、この結果、各熱交換チューブ１３の長手方向中央を中心として外側に向かって湾曲する傾向がある。ここで、第１放熱器側熱交換チューブ１３の冷媒圧力と第２放熱器側熱交換チューブ１３の冷媒圧力を比較するとき、第２放熱器Ｂ側が第１放熱器Ａ側よりも高くなっているため、第２放熱器Ｂ側の湾曲が顕著となり、これにより、第２放熱器側熱交換チューブ１３とタンク部１１ｂ，１２ｂとの連結部分に隙間ができ、この連結部分で冷媒漏れを起こすおそれがある。   In general, in the multi-flow heat exchanger 10, pressure is applied in the vertical direction of each heat exchange tube 13 by the high-pressure refrigerant flowing through each heat exchange tube 13, and as a result, the longitudinal center of each heat exchange tube 13 is centered. There is a tendency to bend outward. Here, when comparing the refrigerant pressure of the first radiator-side heat exchange tube 13 and the refrigerant pressure of the second radiator-side heat exchange tube 13, the second radiator B side is higher than the first radiator A side. Therefore, the curvature on the second radiator B side becomes prominent, and as a result, a gap is formed in the connecting portion between the second radiator-side heat exchange tube 13 and the tank portions 11b and 12b, and refrigerant leakage occurs at this connecting portion. There is a fear.

本実施形態に係るマルチフロー熱交換器１０は、前述の如く、第１放熱器Ａ及び第２放熱器Ｂが並列に一体成形されているため、第２放熱器Ｂ側の湾曲が第１放熱器Ａによって抑制され、第２放熱器Ｂにおける冷媒漏れを抑制することができる。   In the multiflow heat exchanger 10 according to the present embodiment, as described above, since the first radiator A and the second radiator B are integrally formed in parallel, the curvature on the second radiator B side is the first heat dissipation. It can be suppressed by the radiator A, and refrigerant leakage in the second radiator B can be suppressed.

図３(a)(b)はマルチフロー熱交換器１０の各押さえ板１５，１６の変形例を示すものである。前記実施形態では各押さえ板１５，１６は、同一素材、同一形状のものを用いており、同一の強度となっているが、本変形例では各押さえ板１５０，１６０として強度の異なるものを用いている。即ち、図３(a)(b)に示すように、第１放熱器Ａの構成部材である押さえ板１５０の厚さ寸法Ｔ１を第２放熱器Ｂの構成部材である押さえ板１６０の厚さ寸法Ｔ２よりも小さくしている。   FIGS. 3A and 3B show a modification of the holding plates 15 and 16 of the multi-flow heat exchanger 10. In the embodiment, the pressing plates 15 and 16 are made of the same material and the same shape and have the same strength. However, in the present modification, the pressing plates 150 and 160 having different strengths are used. ing. That is, as shown in FIGS. 3A and 3B, the thickness dimension T1 of the pressing plate 150 which is a constituent member of the first radiator A is set to the thickness of the pressing plate 160 which is a constituent member of the second radiator B. It is smaller than the dimension T2.

前述の如く、第２放熱器側熱交換チューブ１３よりも第１放熱器側熱交換チューブ１３の冷媒圧力が小さくなっているため、押さえ板１６０の強度よりも押さえ板１５０の強度が小さくてよく、これに伴い、押さえ板１５０の板厚を薄くした分、押さえ板１５０の材料費が割安になる。なお、各押さえ板１５，１６の強度変更を板厚ではなく、材質強度の異なる材料を用いて実現するようにしてもよい。   As described above, since the refrigerant pressure in the first radiator-side heat exchange tube 13 is smaller than that in the second radiator-side heat exchange tube 13, the strength of the holding plate 150 may be lower than the strength of the holding plate 160. Accordingly, the material cost of the pressing plate 150 is reduced by the thickness of the pressing plate 150 being reduced. In addition, you may make it implement | achieve the intensity | strength change of each holding | suppressing board 15 and 16 not using board thickness but using the material from which material strength differs.

図４はマルチフロー熱交換器１０のヘッダ１１，１２のキャップの変形例を示すものである。以下、ヘッダ１１０のみを図４に示して説明するが、他方のヘッダについても同様であるので、図示及び説明は省略する。   FIG. 4 shows a modification of the caps of the headers 11 and 12 of the multiflow heat exchanger 10. Hereinafter, only the header 110 will be described with reference to FIG. 4, but the same applies to the other header, and thus illustration and description thereof will be omitted.

図４に示すように、ヘッダ１１０は密閉した縦長円筒状を呈している。このヘッダ１１０は上下端を開口したヘッダ本体１１０ａと該各開口を閉塞するキャップ１１０ｂ，１１０ｃとを有し、また、各キャップ１１０ｂ，１１０ｃは強度の異なるものを用いている。即ち、図４に示すように、第１放熱器Ａの構成部材であるキャップ１１０ｂの厚さ寸法Ｔ３を第２放熱器Ｂの構成部材であるキャップ１１０ｃの厚さ寸法Ｔ４よりも小さくしている。   As shown in FIG. 4, the header 110 has a sealed vertically long cylindrical shape. The header 110 has a header body 110a having upper and lower ends opened and caps 110b and 110c that close the openings, and the caps 110b and 110c have different strengths. That is, as shown in FIG. 4, the thickness dimension T3 of the cap 110b that is a constituent member of the first radiator A is made smaller than the thickness dimension T4 of the cap 110c that is a constituent member of the second radiator B. .

前述の如く、第２放熱器Ｂの冷媒圧力よりも第１放熱器Ａの冷媒圧力が小さくなっているため、キャップ１１０ｃの強度よりもキャップ１１０ｂの強度が小さくてよく、これに伴い、キャップ１１０ｂの厚さ寸法Ｔ３が薄くなった分、キャップ１１０ｂの材料費が割安になる。なお、各キャップ１１０ｂ，１１０ｃの強度変更を板厚ではなく、材質強度の異なる材料を用いて実現するようにしてもよい。   As described above, since the refrigerant pressure of the first radiator A is smaller than the refrigerant pressure of the second radiator B, the strength of the cap 110b may be smaller than the strength of the cap 110c. The material cost of the cap 110b is cheaper because the thickness dimension T3 is reduced. In addition, you may make it implement | achieve the intensity | strength change of each cap 110b and 110c using the material from which material strength differs instead of board thickness.

図５(a)(b)はマルチフロー熱交換器１０の熱交換チューブ１３の一変形例を示すものである。前記実施形態では第１放熱器Ａ及び第２放熱器Ｂの各熱交換チューブ１３は同一強度のものを用いているが、本変形例では第１放熱器Ａ側の熱交換チューブ１３０の強度を第２放熱器Ｂ側の熱交換チューブ１３１の強度よりも小さなものを用いている。即ち、図５(a)(b)に示すように、各熱交換チューブ１３０，１３１の内部には断面円形状の複数の冷媒流通路１３０ａ，１３１ａが形成されている。また、各冷媒流通路１３０ａの合計冷媒流通量と各冷媒流通路１３１ａの合計冷媒流通量がほぼ同一となっているが、各冷媒流通路１３０ａの隔壁１３０ｂの厚さ寸法Ｔ５を各冷媒流通路１３１ａの隔壁１３１ｂの厚さ寸法Ｔ６よりも小さくしている。   FIGS. 5A and 5B show a modification of the heat exchange tube 13 of the multiflow heat exchanger 10. In the embodiment, the heat exchanger tubes 13 of the first radiator A and the second radiator B have the same strength, but in this modification, the strength of the heat exchanger tube 130 on the first radiator A side is increased. The thing smaller than the intensity | strength of the heat exchange tube 131 by the side of the 2nd heat radiator B is used. That is, as shown in FIGS. 5A and 5B, a plurality of refrigerant flow passages 130a and 131a having a circular cross section are formed inside the heat exchange tubes 130 and 131, respectively. Further, although the total refrigerant flow amount in each refrigerant flow passage 130a and the total refrigerant flow amount in each refrigerant flow passage 131a are substantially the same, the thickness T5 of the partition wall 130b of each refrigerant flow passage 130a is set to each refrigerant flow passage. It is smaller than the thickness dimension T6 of the partition wall 131b of 131a.

既に説明したように、第２放熱器Ｂ側の熱交換チューブ１３１よりも第１放熱器Ａ側の熱交換チューブ１３０の冷媒圧力が小さくなっているため、熱交換チューブ１３１の強度よりも熱交換チューブ１３０の強度が小さくてよく、これに伴い、各冷媒流通路１３０ａの隔壁１３０ｂが薄くなった分、熱交換チューブ１３０が小型化されるし、また、材料費が割安になる。なお、各熱交換チューブ１３０，１３１の強度変更を板厚ではなく、材質強度の異なる材料を用いて実現するようにしてもよい。   As already described, since the refrigerant pressure in the heat exchanger tube 130 on the first radiator A side is smaller than the heat exchanger tube 131 on the second radiator B side, the heat exchange is higher than the strength of the heat exchanger tube 131. The strength of the tube 130 may be small, and as a result, the heat exchange tube 130 is reduced in size and the material cost is reduced by the amount that the partition wall 130b of each refrigerant flow passage 130a is thinned. In addition, you may make it implement | achieve the intensity | strength change of each heat exchange tube 130 and 131 using the material from which material strength differs instead of plate | board thickness.

図６(a)(b)はマルチフロー熱交換器１０の熱交換チューブ１３の他の変形例を示すものである。前記実施形態では第１放熱器Ａ及び第２放熱器Ｂの各熱交換チューブ１３はほぼ同一冷媒流通量のものを用いているが、本変形例では第１放熱器Ａ側の熱交換チューブ１３２の冷媒流通量を第２放熱器Ｂ側の熱交換チューブ１３３の冷媒流通量よりも小さなものを用いている。即ち、図６(a)(b)に示すように、各熱交換チューブ１３２，１３３の内部には複数の冷媒流通路１３２ａ，１３３ａが形成されている。また、各冷媒流通路１３２ａ，１３３ａの冷媒流通断面積が異なるよう、各冷媒流通路１３２ａの隔壁１３２ｂの厚さ寸法Ｔ７を各冷媒流通路１３３ａの隔壁１３３ｂの厚さ寸法Ｔ８よりも小さくしている。   FIGS. 6A and 6B show another modification of the heat exchange tube 13 of the multiflow heat exchanger 10. In the above-described embodiment, the heat exchanger tubes 13 of the first radiator A and the second radiator B use substantially the same refrigerant circulation amount, but in this modification, the heat exchanger tube 132 on the first radiator A side. The refrigerant circulation amount is smaller than the refrigerant circulation amount of the heat exchanger tube 133 on the second radiator B side. That is, as shown in FIGS. 6A and 6B, a plurality of refrigerant flow passages 132a and 133a are formed inside the heat exchange tubes 132 and 133, respectively. Further, the thickness dimension T7 of the partition wall 132b of each refrigerant flow path 132a is made smaller than the thickness dimension T8 of the partition wall 133b of each refrigerant flow path 133a so that the refrigerant flow cross sections of the refrigerant flow paths 132a and 133a are different. Yes.

既に説明したように、第２放熱器Ｂ側の熱交換チューブ１３３よりも第１放熱器Ａ側の熱交換チューブ１３２の冷媒圧力が小さくなっているため、その分、各熱交換チューブ１３２の冷媒流通量を多くすることができる。これにより、各熱交換チューブ１３２の本数を減らすことができため、マルチフロー熱交換器１０を小型化でき、かつ、製造コストの低減化を実現することができる。   As already described, the refrigerant pressure in the heat exchanger tube 132 on the first radiator A side is smaller than the heat exchanger tube 133 on the second radiator B side. The amount of distribution can be increased. Thereby, since the number of each heat exchange tube 132 can be reduced, the multiflow heat exchanger 10 can be reduced in size and the reduction of manufacturing cost can be implement | achieved.

図７は本発明に係る多段圧縮式冷凍サイクル装置用熱交換器の第２実施形態に係るマルチフロー熱交換器を示すものである。なお、多段圧縮式冷凍サイクル装置用熱交換器の冷媒サイクルは図９で説明した従来例と同一であるため、その図示及び説明を省略する。   FIG. 7 shows a multiflow heat exchanger according to a second embodiment of the heat exchanger for a multistage compression refrigeration cycle apparatus according to the present invention. The refrigerant cycle of the heat exchanger for the multistage compression refrigeration cycle apparatus is the same as that of the conventional example described with reference to FIG.

前記実施形態に係るマルチフロー熱交換器１０は第１放熱器Ａと第２放熱器Ｂとを一台ずつ上下に並設した構成となっているが、本実施形態に係るマルチフロー熱交換器２０は第１放熱器Ａ１，Ａ２が２台で、且つ、第２放熱器Ｂ１が１台で構成され、第２放熱器Ｂ１を間にして第１放熱器Ａ１，Ａ２を上下に並設している。   The multiflow heat exchanger 10 according to the embodiment has a configuration in which the first radiator A and the second radiator B are arranged one above the other vertically, but the multiflow heat exchanger according to the present embodiment is arranged. 20 includes two first radiators A1 and A2 and one second radiator B1, and the first radiators A1 and A2 are arranged in parallel up and down with the second radiator B1 in between. ing.

即ち、マルチフロー熱交換器２０は、冷媒を分流又は合流させる一対のヘッダ２１，２２と、各ヘッダ２１，２２の間で冷媒を流通させる複数の熱交換チューブ２３と、熱交換媒体例えば空気と熱交換する熱交換フィン２４と、最上位及び最下位の熱交換フィン２４を保持する押さえ板２５，２６とから構成されたもので、各部２１〜２６がろう付けにより一体に固着されている。なお、熱交換チューブ２３、熱交換フィン２４及び押さえ板２５，２６は、前記実施形態に係る熱交換チューブ１３、熱交換フィン１４及び押さえ板１５，１６と同一の構成となっているので、その詳細は省略する。   That is, the multi-flow heat exchanger 20 includes a pair of headers 21 and 22 that divide or join the refrigerant, a plurality of heat exchange tubes 23 that circulate the refrigerant between the headers 21 and 22, and a heat exchange medium such as air. The heat exchanging fins 24 for exchanging heat and the pressing plates 25 and 26 for holding the uppermost and lowermost heat exchanging fins 24 are provided, and the respective parts 21 to 26 are fixed together by brazing. The heat exchange tube 23, the heat exchange fin 24, and the holding plates 25, 26 have the same configuration as the heat exchange tube 13, the heat exchange fin 14, and the holding plates 15, 16 according to the above embodiment. Details are omitted.

各ヘッダ２１，２２は密閉した縦長円筒状を呈したもので、互いに間隔をおいて対向配置されている。また、各ヘッダ２１，２２の内部は上下に３つに分離され、上部と下部には第１放熱器用のタンク部２１ａ，２１ｂ，２２ａ，２２ｂが形成され、中間には第２放熱器用のタンク部２１ｃ，２２ｃが形成されている。   Each of the headers 21 and 22 has a sealed vertically long cylindrical shape, and is disposed so as to face each other with a space therebetween. Further, the inside of each header 21 and 22 is divided into three in the vertical direction, tank portions 21a, 21b, 22a and 22b for the first radiator are formed in the upper and lower portions, and a tank for the second radiator is formed in the middle. Portions 21c and 22c are formed.

ここで、ヘッダ２１側の第１放熱器用のタンク部２１ａ，２１ｂの側壁には一次圧縮冷媒流入口２１ｄ，２１ｅが形成され、圧縮機で一次圧縮された冷媒が一次圧縮冷媒流入口２１ｄ，２１ｅを通じてタンク部２１ａ，２１ｂに流入されるようになっている。ヘッダ２２側の第１放熱器用のタンク部２２ａ，２２ｂの側壁には一次圧縮冷媒流出口２２ｄ，２２ｅが形成され、各タンク２２ａ，２２ｂに流入した冷媒が一次圧縮冷媒流出口２２ｄ，２２ｅを通じて圧縮機に戻されるようになっている。他方、第２放熱器用のタンク部２１ｃの側壁には二次圧縮冷媒流入口２１ｆが形成され、圧縮機で二次圧縮された冷媒が二次圧縮冷媒流入口２１ｆを通じてタンク部２１ｃに流入されるようになっている。第２放熱器用のタンク部２２ｃの側壁には二次圧縮冷媒流出口２２ｆが形成され、タンク２２ｃに流入した冷媒が二次圧縮冷媒流出口２２ｆを通じて内部熱交換器に向かって流出されるようになっている。   Here, primary compressed refrigerant inlets 21d and 21e are formed on the side walls of the first radiator tank portions 21a and 21b on the header 21 side, and the refrigerant primarily compressed by the compressor is the primary compressed refrigerant inlets 21d and 21e. Through the tank portion 21a and 21b. Primary compressed refrigerant outlets 22d and 22e are formed on the side walls of the first radiator tank portions 22a and 22b on the header 22 side, and the refrigerant flowing into the tanks 22a and 22b is compressed through the primary compressed refrigerant outlets 22d and 22e. It is supposed to be returned to the machine. On the other hand, a secondary compressed refrigerant inlet 21f is formed on the side wall of the tank portion 21c for the second radiator, and the refrigerant secondarily compressed by the compressor flows into the tank portion 21c through the secondary compressed refrigerant inlet 21f. It is like that. A secondary compressed refrigerant outlet 22f is formed on the side wall of the tank portion 22c for the second radiator, so that the refrigerant flowing into the tank 22c flows out toward the internal heat exchanger through the secondary compressed refrigerant outlet 22f. It has become.

以上のようにマルチフロー熱交換器２０を構成することにより、第１放熱器Ａ１，Ａ２及び第２放熱器Ｂ１が一体に形成されている。   By configuring the multiflow heat exchanger 20 as described above, the first radiators A1 and A2 and the second radiator B1 are integrally formed.

即ち、上側の第１放熱器Ａ１は、タンク部２１ａ，２２ａ、各タンク部２１ａ，２２ａに連通する熱交換チューブ２３、一次圧縮冷媒流入口２１ｄ、一次圧縮冷媒流出口２２ｄ及び押さえ板２５により構成されている。下側の第１放熱器Ａ２は、タンク部２１ｂ，２２ｂ、各タンク部２１ｂ，２２ｂに連通する熱交換チューブ２３、一次圧縮冷媒流入口２１ｅ、一次圧縮冷媒流出口２２ｅ及び押さえ板２６により構成されている。第２放熱器Ｂ１は、タンク部２１ｃ，２２ｃ、各タンク部２１ｃ，２２ｃに連通する熱交換チューブ２３、二次圧縮冷媒流入口２１ｆ、二次圧縮冷媒流出口２２ｆにより構成されている。   That is, the upper first radiator A1 includes tank portions 21a and 22a, a heat exchange tube 23 communicating with each of the tank portions 21a and 22a, a primary compressed refrigerant inlet 21d, a primary compressed refrigerant outlet 22d, and a holding plate 25. Has been. The lower first radiator A2 includes tank portions 21b and 22b, a heat exchange tube 23 communicating with each of the tank portions 21b and 22b, a primary compressed refrigerant inlet 21e, a primary compressed refrigerant outlet 22e, and a holding plate 26. ing. The second radiator B1 includes tank portions 21c and 22c, a heat exchange tube 23 communicating with each of the tank portions 21c and 22c, a secondary compressed refrigerant inlet 21f, and a secondary compressed refrigerant outlet 22f.

本実施形態に係るマルチフロー熱交換器２０は、熱交換チューブ２３のうち外側に湾曲しがちな第２放熱器Ｂ１を各第１放熱器Ａ１，Ａ２で挟み込むようにしているので、第２放熱器Ｂ１側の湾曲が各第１放熱器Ａ１，Ａ２によって抑制され、第２放熱器Ｂ１における冷媒漏れを確実に抑制することができる。なお、その他の構成、作用は前記実施形態と同様である。   In the multi-flow heat exchanger 20 according to the present embodiment, the second radiator B1 that tends to be bent outward is sandwiched between the first radiators A1 and A2 in the heat exchange tube 23. The curvature on the side of the radiator B1 is suppressed by the first radiators A1 and A2, and the refrigerant leakage in the second radiator B1 can be reliably suppressed. Other configurations and operations are the same as those in the above embodiment.

図９は本発明に係る多段圧縮式冷凍サイクル装置用熱交換器の第３実施形態に係るマルチフロー熱交換器を示すものである。なお、多段圧縮式冷凍サイクル装置の冷媒サイクルは図９で説明した従来例と同一であるため、その図示及び説明を省略する。   FIG. 9 shows a multiflow heat exchanger according to a third embodiment of the heat exchanger for a multistage compression refrigeration cycle apparatus according to the present invention. The refrigerant cycle of the multistage compression refrigeration cycle apparatus is the same as that of the conventional example described with reference to FIG.

本実施形態に係るマルチフロー熱交換器３０は、熱交換媒体（空気）の流れ方向に対向して並設された、風下側の第１マルチフロー熱交換部３１と風上側のマルチフロー熱交換部３２とから構成されている。   The multiflow heat exchanger 30 according to the present embodiment includes a first multiflow heat exchange section 31 on the leeward side and a multiflow heat exchange on the leeward side that are arranged in parallel in the flow direction of the heat exchange medium (air). Part 32.

第１，２マルチフロー熱交換器３１，３２は前記第１実施形態と同様に上下に第１放熱器Ａと第２放熱器（図示しない）を有するもので、第１マルチフロー熱交換器３１はタンク部３１ｄ，３１ｅ同士を熱交換チューブ３１ｃを介して連結した一対のヘッダ３１ａ，３１ｂを有し、同じく、第２マルチフロー熱交換器３２はタンク部３２ｄ，３２ｅ同士を熱交換チューブ３２ｃを介して連結した一対のヘッダ３２ａ，３２ｂを有している。   The first and second multi-flow heat exchangers 31 and 32 have a first heat radiator A and a second heat radiator (not shown) in the upper and lower sides as in the first embodiment. Has a pair of headers 31a and 31b in which the tank parts 31d and 31e are connected to each other via a heat exchange tube 31c. Similarly, the second multi-flow heat exchanger 32 connects the tank parts 32d and 32e to the heat exchange tube 32c. It has a pair of headers 32a and 32b connected via each other.

また、図示しないが、熱交換フィン及び押さえ板についても前記第１実施形態と同様になっている。   Although not shown, the heat exchange fins and the pressing plate are the same as in the first embodiment.

更に、第１マルチフロー熱交換器３１のヘッダ３１ａには一次圧縮冷媒流入口３１ｆが連結し、第２マルチフロー熱交換器３２のヘッダ３２ａには同じく一次圧縮冷媒流出口３１ｆが連結している。   Furthermore, a primary compressed refrigerant inlet 31f is connected to the header 31a of the first multiflow heat exchanger 31, and a primary compressed refrigerant outlet 31f is also connected to the header 32a of the second multiflow heat exchanger 32. .

更にまた、第１マルチフロー熱交換器３１のヘッダ３１ｂと第２マルチフロー熱交換器３２のヘッダ３２ｂは連結パイプ３３にて連結し、第１マルチフロー熱交換器３１を流れた冷媒が連結パイプ３３を介して第２マルチフロー熱交換器３２に流れるようになっている。   Furthermore, the header 31b of the first multiflow heat exchanger 31 and the header 32b of the second multiflow heat exchanger 32 are connected by a connecting pipe 33, and the refrigerant flowing through the first multiflow heat exchanger 31 is connected to the connecting pipe. It flows through the second multi-flow heat exchanger 32 through 33.

この冷媒の流れを図９の一点矢印で説明すれば、圧縮機から吐出した冷媒は一次圧縮冷媒流入口３１ｆ→タンク部３１ｄ→熱交換チューブ３１ｃ→タンク部３１ｅ→連結パイプ３３→タンク部３２ｅ→熱交換チューブ３２ｃ→タンク部３２ｄ→一次圧縮冷媒流出口３２ｆ→圧縮機と順次流れることとなる。   If the flow of this refrigerant is described with a single-pointed arrow in FIG. 9, the refrigerant discharged from the compressor is the primary compressed refrigerant inlet 31f → tank part 31d → heat exchange tube 31c → tank part 31e → connection pipe 33 → tank part 32e → The heat exchange tube 32c, the tank portion 32d, the primary compressed refrigerant outlet 32f, and the compressor sequentially flow.

本実施形態によれば、圧縮機から吐出した冷媒を一旦風下側の第１マルチフロー熱交換器３１に流した後に、風上側の第２マルチフロー熱交換器３２に流すようにしたので、冷媒と熱交換媒体である空気と効率よく熱交換される。   According to the present embodiment, the refrigerant discharged from the compressor is once allowed to flow to the first multiflow heat exchanger 31 on the leeward side and then to the second multiflow heat exchanger 32 on the leeward side. And efficiently exchanges heat with air, which is a heat exchange medium.

なお、図９では第１放熱器Ａ側の構造を図示しているが、図示しない第２放熱器側の構造についても同様に冷媒を風下側から風上側に冷媒を流すようになっている。その他の構成、作用は前記第１実施形態と同様である。   In FIG. 9, the structure on the first radiator A side is illustrated, but the refrigerant is similarly caused to flow from the leeward side to the leeward side also on the second radiator side structure (not shown). Other configurations and operations are the same as those in the first embodiment.

第１実施形態に係るマルチフロー熱交換器の正面図Front view of the multiflow heat exchanger according to the first embodiment 第１実施形態に係るマルチフロー熱交換器の平面図The top view of the multiflow heat exchanger concerning a 1st embodiment 押さえ板の変形例を示す正面図Front view showing a modification of the holding plate キャップの変形例を示す一部断面正面図Partially sectional front view showing a modified example of the cap 熱交換チューブの一変形例を示す断面図Sectional drawing which shows one modification of heat exchange tube 熱交換チューブの他の変形例を示す断面図Sectional drawing which shows the other modification of a heat exchange tube 第２実施形態に係るマルチフロー熱交換器の正面図Front view of the multi-flow heat exchanger according to the second embodiment 第３実施形態に係るマルチフロー熱交換器の平面断面図Plan sectional drawing of the multiflow heat exchanger which concerns on 3rd Embodiment 多段圧縮式冷凍サイクル装置を示す冷媒管路図Refrigerant pipeline diagram showing multistage compression refrigeration cycle equipment

符号の説明Explanation of symbols

１…圧縮機、２，Ａ，Ａ１，Ａ２…第１放熱器、３，Ｂ，Ｂ１…第２放熱器、１０，２０，３０…マルチフロー熱交換器、１１，１２，２１，２２，３１ａ，３１ｂ，３２ａ，３２ｂ…ヘッダ、１１ｆ，１１ｇ…キャップ、１３，２３，３１ｃ，３２ｃ…熱交換チューブ、１４，２４…熱交換フィン、１５，１６，２５，２６…押さえ板、３１…第１マルチフロー熱交換器、３２…第２マルチフロー熱交換器。   DESCRIPTION OF SYMBOLS 1 ... Compressor, 2, A, A1, A2 ... 1st heat radiator, 3, B, B1 ... 2nd heat radiator, 10, 20, 30 ... Multiflow heat exchanger, 11, 12, 21, 22, 31a , 31b, 32a, 32b ... header, 11f, 11g ... cap, 13, 23, 31c, 32c ... heat exchange tube, 14, 24 ... heat exchange fins, 15, 16, 25, 26 ... pressure plate, 31 ... first Multi-flow heat exchanger, 32 ... second multi-flow heat exchanger.

Claims (10)

一次圧縮された冷媒が冷却される第１放熱器と二次圧縮された冷媒が冷却される第２放熱器とを備えた多段圧縮式冷凍サイクル装置用熱交換器において、
前記第１放熱器及び前記第２放熱器は、冷媒を分流又は合流させる一対のヘッダと、該各ヘッダ間に間隔をおいて複数架設された冷媒流通用の熱交換チューブと、該各熱交換チューブの間に介装された熱交換フィンとを有するマルチフロー熱交換器にて一体に形成された
ことを特徴とする多段圧縮式冷凍サイクル装置用熱交換器。 In a heat exchanger for a multistage compression refrigeration cycle apparatus comprising a first radiator that cools a primary compressed refrigerant and a second radiator that cools a secondary compressed refrigerant,
The first radiator and the second radiator include a pair of headers for diverting or merging the refrigerant, a plurality of refrigerant circulation heat exchange tubes provided at intervals between the headers, and the heat exchanges. A heat exchanger for a multistage compression refrigeration cycle apparatus, which is integrally formed by a multiflow heat exchanger having heat exchange fins interposed between tubes. 前記第１放熱器及び前記第２放熱器を並設してなる
ことを特徴とする請求項１記載の多段圧縮式冷凍サイクル装置用熱交換器。 The heat exchanger for a multistage compression refrigeration cycle apparatus according to claim 1, wherein the first radiator and the second radiator are arranged in parallel. 前記第２放熱器を間にして複数の前記第１放熱器を配置した
ことを特徴とする請求項２記載の多段圧縮式冷凍サイクル装置用熱交換器。 The heat exchanger for a multistage compression refrigeration cycle apparatus according to claim 2, wherein a plurality of the first radiators are arranged with the second radiator interposed therebetween. 前記第１放熱器及び前記第２放熱器は一番外側の前記熱交換フィンを押さえる押さえ板を有し、該第１放熱器の押さえ板の強度は該第２放熱器の押さえ板の強度より小さくした
ことを特徴とする請求項２記載の多段圧縮式冷凍サイクル装置用熱交換器。 The first radiator and the second radiator have a pressing plate for pressing the outermost heat exchange fin, and the strength of the pressing plate of the first radiator is higher than the strength of the pressing plate of the second radiator. The heat exchanger for a multistage compression refrigeration cycle apparatus according to claim 2, wherein the heat exchanger is small. 前記第１放熱器及び前記第２放熱器は前記ヘッダの端部を閉塞するキャップを有し、該第１放熱器のキャップの強度は該第２放熱器のキャップの強度より小さくした
ことを特徴とする請求項１乃至請求項４の何れか一項記載の多段圧縮式冷凍サイクル装置用熱交換器。 The first radiator and the second radiator have a cap that closes an end of the header, and the strength of the cap of the first radiator is smaller than the strength of the cap of the second radiator. The heat exchanger for a multistage compression refrigeration cycle apparatus according to any one of claims 1 to 4. 前記第１放熱器の前記熱交換チューブの強度を前記第２放熱器の前記熱交換チューブの強度より小さくした
ことを特徴とする請求項１乃至請求項５の何れか一項記載の多段圧縮式冷凍サイクル装置用熱交換器。 The multistage compression type according to any one of claims 1 to 5, wherein the strength of the heat exchange tube of the first radiator is smaller than the strength of the heat exchange tube of the second radiator. Heat exchanger for refrigeration cycle equipment. 前記第１放熱器の前記熱交換チューブの冷媒流通断面積を前記第２放熱器の前記熱交換チューブの冷媒流通断面積より大きくした
ことを特徴とする請求項１乃至請求項５の何れか一項記載の多段圧縮式冷凍サイクル装置用熱交換器。 The refrigerant flow cross-sectional area of the heat exchange tube of the first radiator is made larger than the refrigerant flow cross-sectional area of the heat exchange tube of the second radiator. A heat exchanger for a multistage compression refrigeration cycle apparatus as described in the paragraph 前記熱交換チューブの冷媒流通断面を円形状に形成した
ことを特徴とする請求項１乃至請求項５の何れか一項記載の多段圧縮式冷凍サイクル装置用熱交換器。 The refrigerant flow section of the heat exchange tube is formed in a circular shape. The heat exchanger for a multistage compression refrigeration cycle apparatus according to any one of claims 1 to 5. 前記マルチフロー熱交換器で形成された前記第１放熱器及び前記第２放熱器は、冷媒と熱交換する熱交換媒体の流れ方向に対して下流側に配置された第１マルチフロー熱交換器と上流側に配置された第２マルチフロー熱交換器とを互いに連通させて並設してなり、該第１マルチフロー熱交換器には冷媒入口を通じて流入した冷媒が流通し、該第２マルチフロー熱交換器には第１マルチフロー熱交換器を通過した冷媒が流通するよう設定した
ことを特徴とする請求項１乃至請求項８の何れか一項記載の多段圧縮式冷凍サイクル装置用熱交換器。 The first radiator and the second radiator formed by the multiflow heat exchanger are disposed on the downstream side with respect to the flow direction of the heat exchange medium that exchanges heat with the refrigerant. And a second multi-flow heat exchanger arranged on the upstream side are connected in parallel with each other, and the refrigerant flowing in through the refrigerant inlet flows through the first multi-flow heat exchanger, The heat for a multistage compression refrigeration cycle apparatus according to any one of claims 1 to 8, wherein the refrigerant that has passed through the first multiflow heat exchanger flows in the flow heat exchanger. Exchanger. 前記冷媒として二酸化炭素を使用した
ことを特徴とする請求項１乃至請求項９の何れか一項記載の多段圧縮式冷凍サイクル装置用熱交換器。 The carbon exchanger is used as the refrigerant. The heat exchanger for a multistage compression refrigeration cycle apparatus according to any one of claims 1 to 9, wherein carbon dioxide is used as the refrigerant.
JP2005225293A 2005-08-03 2005-08-03 Heat exchanger for multistage compression type refrigeration cycle device Pending JP2007040605A (en)

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