JP2009270802A - Internal heat exchanger - Google Patents

Internal heat exchanger Download PDF

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JP2009270802A
JP2009270802A JP2008130245A JP2008130245A JP2009270802A JP 2009270802 A JP2009270802 A JP 2009270802A JP 2008130245 A JP2008130245 A JP 2008130245A JP 2008130245 A JP2008130245 A JP 2008130245A JP 2009270802 A JP2009270802 A JP 2009270802A
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heat exchanger
internal heat
pipe
outer tube
tube
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Hisatoshi Hirota
久寿 広田
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TGK Co Ltd
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TGK Co Ltd
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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
    • F28D7/10—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 being arranged one within the other, e.g. concentrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means

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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 facilitate bending of an internal heat exchanger having a double pipe structure. <P>SOLUTION: The internal heat exchanger 4a with the double pipe structure is provided with an outer pipe 11 and an inner pipe 12 stored in the outer pipe 11. The inner pipe 12 has a shape spirally wound around the axial center of the outer pipe 11, and the outermost peripheral face of the spiral portion is brought into contact with the inner wall of the outer pipe 11. Since the inner pipe 12 is fixed inside the outer pipe 11 due to the contact, the outer pipe 11 and the inner pipe 12 located inside the outer pipe 11 can be easily bent, and even when the pipes 11, 12 receive vibration from outside, noise caused by collision can be prevented. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

本発明は内部熱交換器に関し、特に自動車用空調装置の冷凍サイクル内で膨張装置に導入される高温・高圧の冷媒と、圧縮機へ導入される低温・低圧の冷媒との間で熱交換を行う内部熱交換器に関する。   The present invention relates to an internal heat exchanger, and in particular, performs heat exchange between a high-temperature and high-pressure refrigerant introduced into an expansion device in a refrigeration cycle of an automotive air conditioner and a low-temperature and low-pressure refrigerant introduced into a compressor. It relates to an internal heat exchanger that performs.

自動車用空調装置では、一般に、エンジンルーム内に圧縮機、凝縮器およびレシーバドライヤが設置され、車室内に蒸発器が設置され、圧縮機、凝縮器、レシーバドライヤ、膨張弁および蒸発器がこの順序で冷媒が流れるよう配管され、蒸発器を出た冷媒は圧縮機へ戻るようにして冷凍サイクルが構成されている。膨張弁は、車室とエンジンルームとを区画している隔壁に設置されて車室内側の配管とエンジンルーム内側の配管との継手を兼ねるようにしていたり、蒸発器の中または蒸発器の直近に設置されていたりしている。   In an automotive air conditioner, a compressor, a condenser and a receiver dryer are generally installed in an engine room, an evaporator is installed in a vehicle compartment, and the compressor, condenser, receiver dryer, expansion valve and evaporator are arranged in this order. Then, the refrigerant is piped so that the refrigerant flows out, and the refrigerant exiting the evaporator returns to the compressor to constitute the refrigeration cycle. The expansion valve is installed in the partition that separates the vehicle compartment from the engine room, and serves as a joint between the piping inside the vehicle compartment and the piping inside the engine room, or in or near the evaporator. It is installed in.

このような冷凍サイクルにおいて、その成績係数の向上を目的として内部熱交換器を備えることが知られている。この内部熱交換器は、レシーバドライヤから膨張弁に送られる高温・高圧の冷媒と、蒸発器から圧縮機へ送られる低温・低圧の冷媒との間で熱交換を行って、膨張弁に導入される冷媒の過冷却度および圧縮機に導入される冷媒の過熱度を大きくする機能を有している。この冷凍サイクルで使用される内部熱交換器は、熱交換率を重要視するよりも配管の機能を重要視している。   In such a refrigeration cycle, it is known to include an internal heat exchanger for the purpose of improving the coefficient of performance. This internal heat exchanger exchanges heat between the high-temperature and high-pressure refrigerant sent from the receiver dryer to the expansion valve and the low-temperature and low-pressure refrigerant sent from the evaporator to the compressor, and is introduced into the expansion valve. The refrigerant has a function of increasing the degree of supercooling of the refrigerant and the degree of superheating of the refrigerant introduced into the compressor. The internal heat exchanger used in this refrigeration cycle places importance on the function of the piping rather than on the heat exchange rate.

このため、内部熱交換器としては、熱交換のための大きな表面積は必要ないので、たとえば非常にシンプルな同軸二重管構造のものが用いられている（たとえば、特許文献１参照）。この同軸二重管は、外管と、この外管の中に収容された内管と、これら内管および外管の同心を維持するために内管と外管との間に配置された支持部材とを備え、中空押し出し成形によって一体に形成されている。
特表２００３−５１０５４６号公報（段落〔００１８〕，図８） For this reason, since a large surface area for heat exchange is not required as the internal heat exchanger, for example, a very simple coaxial double tube structure is used (for example, see Patent Document 1). This coaxial double pipe is an outer pipe, an inner pipe housed in the outer pipe, and a support disposed between the inner pipe and the outer pipe to maintain concentricity between the inner pipe and the outer pipe. And is integrally formed by hollow extrusion molding.
Japanese translation of PCT publication No. 2003-510546 (paragraph [0018], FIG. 8)

しかしながら、中空押し出し成形によって形成された同軸二重管は、内管および外管の同心を維持するための支持部材が一体に形成されているので、曲げ難いという問題点があった。   However, the coaxial double tube formed by hollow extrusion molding has a problem that it is difficult to bend because the support member for maintaining the concentricity of the inner tube and the outer tube is integrally formed.

本発明はこのような点に鑑みてなされたものであり、曲げ加工の容易な二重管構造の内部熱交換器を提供することを目的とする。   This invention is made | formed in view of such a point, and it aims at providing the internal heat exchanger of the double pipe structure with easy bending.

本発明では上記問題点を解決するために、冷凍サイクル内で膨張装置に導入される高温・高圧の冷媒と圧縮機へ導入される低温・低圧の冷媒との間で熱交換を行う内部熱交換器において、外管とこの外管の中に収容された内管とを備え、前記内管は、前記外管の軸心を中心にして螺旋状に巻かれた形状を有し、その最外周面の少なくとも一部が前記外管の内壁に接触されていることを特徴とする内部熱交換器が提供される。   In the present invention, in order to solve the above problems, internal heat exchange is performed in which heat exchange is performed between a high-temperature / high-pressure refrigerant introduced into the expansion device and a low-temperature / low-pressure refrigerant introduced into the compressor in the refrigeration cycle. The outer tube includes an outer tube and an inner tube accommodated in the outer tube, and the inner tube has a shape wound spirally around the axis of the outer tube, and has an outermost periphery. An internal heat exchanger is provided in which at least a part of a surface is in contact with an inner wall of the outer tube.

このような内部熱交換器によれば、内管は外管の内壁との接触により外管内に固定されているので、外管およびその中の内管が曲げ易くなっている。   According to such an internal heat exchanger, since the inner tube is fixed in the outer tube by contact with the inner wall of the outer tube, the outer tube and the inner tube therein are easily bent.

上記構成の内部熱交換器は、外管の軸心を中心にして螺旋状に巻かれた内管をその螺旋部分の最外周面が外管の内壁に接触することにより外管の中に固定するようにしたので、曲げ加工時に外管およびその中の内管が互いに接触しながら移動可能となり、非常に曲げ易くなっている。また、内管は、外管に接触された状態で外管の中に保持されているので、外部より振動を受けても外管との衝突による異音を発生することもない。   The internal heat exchanger configured as described above fixes the inner tube wound spirally around the axis of the outer tube, with the outermost peripheral surface of the spiral portion coming into contact with the inner wall of the outer tube. As a result, the outer tube and the inner tube in the outer tube and the inner tube can move while in contact with each other at the time of bending, making it very easy to bend. In addition, since the inner tube is held in the outer tube while being in contact with the outer tube, no abnormal noise is generated due to a collision with the outer tube even when subjected to vibration from the outside.

以下、本発明の実施の形態について、自動車用空調装置の冷凍サイクルに適用した場合を例に図面を参照して詳細に説明する。
図１は自動車用空調装置の冷凍サイクルを示すシステム図である。 DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings, taking as an example a case where the present invention is applied to a refrigeration cycle of an automotive air conditioner.
FIG. 1 is a system diagram showing a refrigeration cycle of an automotive air conditioner.

この自動車用空調装置の冷凍サイクルは、冷媒を圧縮する圧縮機１と、圧縮された冷媒を外気との熱交換により凝縮させる凝縮器２と、凝縮された冷媒を気液に分離するとともに冷凍サイクル内の余剰冷媒を蓄えておくレシーバドライヤ３とをエンジンルーム内に備えている。冷凍サイクルは、エンジンルームと車室との間の配管を行う内部熱交換器４を備え、さらに、内部熱交換器４からの液冷媒を絞り膨張させる温度式の膨張弁５と、膨張された冷媒を車室内の空気との熱交換により蒸発させる蒸発器６とを車室内に備えている。蒸発器６は、これを出た冷媒の温度および圧力を検出するために膨張弁５に接続され、さらに、内部熱交換器４を介して圧縮機１の吸入口に接続される。   The refrigeration cycle of this automotive air conditioner includes a compressor 1 that compresses a refrigerant, a condenser 2 that condenses the compressed refrigerant by heat exchange with outside air, and separates the condensed refrigerant into gas and liquid and a refrigeration cycle. A receiver dryer 3 for storing the excess refrigerant is provided in the engine room. The refrigeration cycle includes an internal heat exchanger 4 that performs piping between the engine room and the vehicle compartment, and is further expanded with a temperature type expansion valve 5 that squeezes and expands the liquid refrigerant from the internal heat exchanger 4. An evaporator 6 that evaporates the refrigerant by heat exchange with the air in the passenger compartment is provided in the passenger compartment. The evaporator 6 is connected to the expansion valve 5 in order to detect the temperature and pressure of the refrigerant that has left the evaporator 6, and is further connected to the suction port of the compressor 1 via the internal heat exchanger 4.

内部熱交換器４は、レシーバドライヤ３からの高温・高圧の液冷媒を膨張弁５へ送り出す高圧通路と蒸発器６からの低温・低圧のガス冷媒を圧縮機１へ送り出す低圧通路とを有し、高圧通路を流れる高温の冷媒と低圧通路を流れる低温の冷媒との間で熱交換を行う。これにより、高圧通路を流れる冷媒は、低圧通路の冷媒によって過冷却され、低圧通路を流れる冷媒は、高圧通路の冷媒によって過熱されることになるため、冷凍サイクルの成績係数を向上させることができる。   The internal heat exchanger 4 has a high-pressure passage for sending high-temperature and high-pressure liquid refrigerant from the receiver dryer 3 to the expansion valve 5 and a low-pressure passage for sending low-temperature and low-pressure gas refrigerant from the evaporator 6 to the compressor 1. Heat exchange is performed between the high-temperature refrigerant flowing through the high-pressure passage and the low-temperature refrigerant flowing through the low-pressure passage. Thereby, the refrigerant flowing through the high-pressure passage is supercooled by the refrigerant in the low-pressure passage, and the refrigerant flowing through the low-pressure passage is overheated by the refrigerant in the high-pressure passage, so that the coefficient of performance of the refrigeration cycle can be improved. .

図２は第１の実施の形態に係る内部熱交換器を示す図であって、（Ａ）は内部熱交換器の内部を示す長軸断面図、（Ｂ）は内管および位置決め部材を示す図、（Ｃ）は内管のａ−ａ矢視拡大端面図、（Ｄ）は内管のｂ−ｂ矢視拡大断面図、（Ｅ）は内管のｃ−ｃ矢視拡大端面図である。   2A and 2B are views showing the internal heat exchanger according to the first embodiment, in which FIG. 2A is a longitudinal sectional view showing the inside of the internal heat exchanger, and FIG. 2B is an inner tube and a positioning member. (C) is an aa arrow enlarged end view of the inner tube, (D) is an enlarged cross sectional view of the inner tube taken along the line bb, and (E) is an enlarged end view of the inner tube taken along the line cc. is there.

この第１の実施の形態に係る内部熱交換器４ａは、図２の（Ａ）に示したように、外管１１とこの外管１１の中に収容された内管１２とを有し、内管１２および外管１１がそれぞれ冷凍サイクルの高圧配管および低圧配管として使用される配管兼用の二重管熱交換器を構成している。外管１１は、ストレートパイプであり、その中に収容される内管１２は、図２の（Ｂ）に示したように、ストレートパイプの両端近傍を除く部分がその軸心を中心にして螺旋状に巻かれた形状に加工されている。このとき、この内管１２の螺旋部分は、非常に長い螺旋ピッチで巻かれており、かつ、最外周に内接する仮想円筒の径が外管１１の内径より僅かに大きくなるように形成されている。したがって、この内管１２は、外管１１の中に圧入されると、螺旋部分の概略全周が外管１１の内壁に接触した状態で外管１１の中に収容されることになる。これにより、内管１２は、外管１１によってその中にきつく拘束されることになるため、外部より振動が与えられても、外管１１に衝突することによる異音が発生するということはない。   The internal heat exchanger 4a according to the first embodiment has an outer tube 11 and an inner tube 12 accommodated in the outer tube 11, as shown in FIG. The inner pipe 12 and the outer pipe 11 constitute a double-pipe heat exchanger that is also used as a high-pressure pipe and a low-pressure pipe of a refrigeration cycle, respectively. The outer pipe 11 is a straight pipe, and the inner pipe 12 accommodated in the outer pipe 11 is spiraled around its axis center except for the vicinity of both ends of the straight pipe as shown in FIG. It is processed into a shape wound in a shape. At this time, the spiral portion of the inner tube 12 is wound at a very long spiral pitch, and the diameter of the virtual cylinder inscribed in the outermost periphery is formed to be slightly larger than the inner diameter of the outer tube 11. Yes. Therefore, when the inner tube 12 is press-fitted into the outer tube 11, the entire circumference of the spiral portion is accommodated in the outer tube 11 with the inner wall of the outer tube 11 in contact with the inner tube 12. As a result, the inner tube 12 is tightly constrained therein by the outer tube 11, so that even if vibration is applied from the outside, no abnormal noise is generated due to collision with the outer tube 11. .

また、内管１２の螺旋部分は、緩い螺旋ピッチで巻かれているため、全長が長くならないことから、冷媒通路が長くなることによる圧力損失がなく、しかも、外管１１とは、その長手方向に沿って物理的に結合している部分はなく、単なる接触にて外管１１内に固定されているだけなので、外管１１およびその中の内管１２が非常に曲げ易くなっており、内部熱交換器４ａの曲げ加工を容易に行うことを可能にしている。   Further, since the helical portion of the inner tube 12 is wound at a loose helical pitch, the overall length does not become long, so there is no pressure loss due to the long refrigerant passage, and the outer tube 11 is in the longitudinal direction. There is no portion physically coupled along the outer tube 11, and the outer tube 11 and the inner tube 12 therein are very easy to bend. The bending of the heat exchanger 4a can be easily performed.

さらに、内管１２は、その両端に位置決め部材１３，１４が設けられている。位置決め部材１３は、図２の（Ｃ）および（Ｄ）に示したように、内管１２の先端近傍のストレート部分に嵌合される筒状部１５とその外周に突設された３つの支持部材１６とを有し、好ましくは、筒状部１５および３つの支持部材１６が中空押し出し成形によって一体に形成されたものが使用される。もちろん、位置決め部材１３は、その支持部材１６の最外周に内接する仮想円筒の径が外管１１の内径に概略等しくなるよう形成されている。これにより、位置決め部材１３が取り付けられた内管１２を外管１１の中に挿入すると、内管１２は、外管１１の軸心に位置決めされることになり、その開口端を同軸二重管構造にしている。   Furthermore, the inner tube 12 is provided with positioning members 13 and 14 at both ends thereof. As shown in FIGS. 2C and 2D, the positioning member 13 includes a cylindrical portion 15 fitted to a straight portion near the tip of the inner tube 12 and three supports protruding from the outer periphery thereof. It is preferable that the cylindrical portion 15 and the three support members 16 are integrally formed by hollow extrusion molding. Of course, the positioning member 13 is formed such that the diameter of the virtual cylinder inscribed in the outermost periphery of the support member 16 is substantially equal to the inner diameter of the outer tube 11. Thus, when the inner tube 12 to which the positioning member 13 is attached is inserted into the outer tube 11, the inner tube 12 is positioned at the axial center of the outer tube 11, and the open end of the inner tube 12 is connected to the coaxial double tube. It has a structure.

一方、位置決め部材１４は、図２の（Ｅ）に示したように、外管１１の内径に概略等しい外径を有する円筒部１７とそれより大きな外径を有するリング部１８とこれらの間に固定的に配置された３つの支持部材１９とを有し、軸心位置には、貫通孔が形成されている。この貫通孔は、図２の（Ａ）および（Ｂ）に見られるように、円筒部１７の軸方向内側から外側にかけて拡径されている。この拡径された貫通孔に内管１２を挿入後、その内管１２の先端近傍を拡管加工することによって、位置決め部材１４と内管１２とが固定されるとともに、拡管加工の部分は、レシーバドライヤ３からの高圧配管が嵌合される雌型継手を形成している。位置決め部材１４は、図２の（Ａ）に示したように、先端近傍が拡管加工された外管１１に嵌合される。これにより、内管１２は、外管１１の軸心に位置決めされることになり、その開口端は、同軸二重管構造になっている。   On the other hand, as shown in FIG. 2E, the positioning member 14 includes a cylindrical portion 17 having an outer diameter substantially equal to the inner diameter of the outer tube 11, a ring portion 18 having a larger outer diameter, and a gap between them. It has three support members 19 arranged in a fixed manner, and a through hole is formed at the axial center position. As can be seen in FIGS. 2A and 2B, the through hole is enlarged in diameter from the inner side to the outer side of the cylindrical portion 17. After the inner tube 12 is inserted into the expanded through-hole, the positioning member 14 and the inner tube 12 are fixed by expanding the vicinity of the distal end of the inner tube 12, and the expanded portion is used as a receiver. A female joint to which a high-pressure pipe from the dryer 3 is fitted is formed. As shown in FIG. 2A, the positioning member 14 is fitted to the outer tube 11 in which the vicinity of the tip is expanded. As a result, the inner tube 12 is positioned at the axial center of the outer tube 11, and the open end has a coaxial double tube structure.

図３は第２の実施の形態に係る内部熱交換器を示す図であって、（Ａ）は内部熱交換器の内部を示す長軸断面図、（Ｂ）は内管および位置決め部材を示す図、（Ｃ）は内部熱交換器のａ−ａ矢視拡大断面図、（Ｄ）は内部熱交換器のｂ−ｂ矢視拡大断面図、（Ｅ）は内管のｃ−ｃ矢視拡大断面図、（Ｆ）は内管のｄ−ｄ矢視拡大断面図である。なお、この図３において、図２に示した構成要素と同じ構成要素については同じ符号を付してその詳細な説明は省略する。   3A and 3B are views showing an internal heat exchanger according to the second embodiment, in which FIG. 3A is a longitudinal sectional view showing the inside of the internal heat exchanger, and FIG. 3B is an inner tube and a positioning member. (C) is an aa arrow expanded sectional view of an internal heat exchanger, (D) is a bb arrow expanded sectional view of an internal heat exchanger, (E) is a cc arrow view of an inner pipe. An expanded sectional view and (F) are dd arrow expanded sectional views of an inner pipe. 3, the same components as those shown in FIG. 2 are denoted by the same reference numerals, and detailed description thereof is omitted.

この第２の実施の形態に係る内部熱交換器４ｂは、図３の（Ａ）に示したように、外管１１とこの外管１１の中に収容された内管１２とを有し、その内管１２および外管１１のそれぞれについて、第１の実施の形態に係る内部熱交換器４ａと基本的には同じ構成を有している。ただし、内管１２の螺旋部分は、その最外周に内接する仮想円筒の径が外管１１の内径より僅かに小さくなるように形成されている。これにより、内管１２が外管１１の中に挿入されたときには、図３の（Ａ）および（Ｃ）に示したように、内管１２の螺旋部分のほとんどは、外管１１に内接していない。また、螺旋部分の内管１２は、図３の（Ｆ）に示したように、部分的に潰されている。すなわち、内管１２は、所定のピッチにて、たとえば１ターン当たり２〜３箇所となる間隔を以て、半径方向に長径を有する断面楕円となる形状に部分的に変形されている。このとき、螺旋中心から長径の外方端までの距離は、外管１１の内壁面の半径より大きくなるようにしている。これにより、内管１２は、外管１１に挿入されたときに、図３の（Ｄ）に示したように、変形部分の長径方向の外壁だけが外管１１の内壁に部分的に接触した状態で外管１１の中に収容されるようになる。   The internal heat exchanger 4b according to the second embodiment has an outer tube 11 and an inner tube 12 accommodated in the outer tube 11, as shown in FIG. Each of the inner pipe 12 and the outer pipe 11 has basically the same configuration as the internal heat exchanger 4a according to the first embodiment. However, the spiral portion of the inner tube 12 is formed such that the diameter of the virtual cylinder inscribed in the outermost periphery thereof is slightly smaller than the inner diameter of the outer tube 11. As a result, when the inner tube 12 is inserted into the outer tube 11, most of the spiral portion of the inner tube 12 is inscribed in the outer tube 11, as shown in FIGS. Not. Moreover, as shown to (F) of FIG. 3, the inner tube | pipe 12 of the spiral part is crushed partially. That is, the inner tube 12 is partially deformed at a predetermined pitch, for example, into a shape of a cross-sectional ellipse having a major axis in the radial direction at intervals of two to three per turn. At this time, the distance from the spiral center to the outer end of the long diameter is made larger than the radius of the inner wall surface of the outer tube 11. As a result, when the inner tube 12 is inserted into the outer tube 11, only the outer wall in the major axis direction of the deformed portion partially contacts the inner wall of the outer tube 11 as shown in FIG. It will be accommodated in the outer tube 11 in a state.

ここで、以上のような内部熱交換器４ａ，４ｂを採用した冷凍サイクルでは、レシーバドライヤ３から膨張弁５に送り込まれる液冷媒は、内部熱交換器４ａ，４ｂにて過冷却される。このため、膨張弁５の入口における冷媒は、十分大きな過冷却度を確保することができるので、内部熱交換器４ａ，４ｂで大きな圧力降下があっても、モリエル線図上で、液相域から飽和液線を超えて液とガスが共存する飽和蒸気域に進入してしまうことはない。逆に言えば、内部熱交換器４ａ，４ｂで大きな圧力降下があってもよいので、高圧の液冷媒が流れる内管１２は、その通路断面積を小さくすることが可能になる。つまり、内管１２は、その内径の小さな配管によって作ることができる。   Here, in the refrigeration cycle employing the internal heat exchangers 4a and 4b as described above, the liquid refrigerant sent from the receiver dryer 3 to the expansion valve 5 is supercooled by the internal heat exchangers 4a and 4b. For this reason, since the refrigerant at the inlet of the expansion valve 5 can ensure a sufficiently large degree of supercooling, even if there is a large pressure drop in the internal heat exchangers 4a and 4b, the liquid phase region on the Mollier diagram Therefore, the liquid does not enter the saturated vapor region where the liquid and the gas coexist beyond the saturated liquid line. In other words, since there may be a large pressure drop in the internal heat exchangers 4a and 4b, the inner pipe 12 through which the high-pressure liquid refrigerant flows can have a smaller passage cross-sectional area. That is, the inner tube 12 can be made of a pipe having a small inner diameter.

具体的には、現状の冷凍サイクルでは、高圧配管として、その内径が６ミリメートルまたは８ミリメートルの配管が用いられており、低圧配管としては、その内径が１４ミリメートルないし１７ミリメートルの配管が用いられている。これに対し、内部熱交換器４ａ，４ｂで大きな圧力降下を許容できる高圧配管として使用している内管１２は、その内径が３ミリメートルないし５ミリメートルの配管を用いることができる。３ミリメートル、４ミリメートルおよび５ミリメートルの配管を低圧配管として用いられている内径が１４ミリメートルまたは１７ミリメートルの配管と組み合わせた場合の内管１２と外管１１との配管断面積比を計算すると、０．０４５９２〜０．１２７５５となる。いずれの組み合わせでも、内管１２の通路断面積が外管１１の通路断面積の１５％以下になる。なお、配管断面積比の最も大きな組み合わせを除けば、内管１２の通路断面積は、外管１１の通路断面積の１０％以下になっている。このように、内管１２に通路断面積の小さな細い配管を使うことで、冷凍サイクル内を循環する冷媒の総量を抑えることができ、事故などにより冷媒が大気に漏れた場合においても、その総量を減らすことができるというメリットがある。   Specifically, in the current refrigeration cycle, a pipe having an inner diameter of 6 millimeters or 8 millimeters is used as the high pressure pipe, and a pipe having an inner diameter of 14 millimeters to 17 millimeters is used as the low pressure pipe. Yes. On the other hand, the inner pipe 12 used as a high-pressure pipe capable of allowing a large pressure drop in the internal heat exchangers 4a and 4b can be a pipe having an inner diameter of 3 millimeters to 5 millimeters. When the pipe cross-sectional area ratio between the inner pipe 12 and the outer pipe 11 when a pipe of 3 mm, 4 mm and 5 mm is combined with a pipe having an inner diameter of 14 mm or 17 mm used as a low pressure pipe is calculated as 0 .04592 to 0.12755. In any combination, the passage sectional area of the inner tube 12 is 15% or less of the passage sectional area of the outer tube 11. Except for the largest combination of pipe cross-sectional area ratios, the cross-sectional area of the inner pipe 12 is 10% or less of the cross-sectional area of the outer pipe 11. Thus, by using a thin pipe having a small passage cross-sectional area for the inner pipe 12, the total amount of refrigerant circulating in the refrigeration cycle can be suppressed, and even when the refrigerant leaks to the atmosphere due to an accident or the like, the total amount There is an advantage that can be reduced.

図４は車室内側の内部熱交換器の設置例を示す断面図である。
配管を兼ねる内部熱交換器４は、車室内の配管とエンジンルーム内の配管の一部を構成することができる。図示の例では、膨張弁５は、蒸発器６に直結されていて、内部熱交換器４ｃの一端が接続されている。なお、この内部熱交換器４ｃは、図示の関係で短くしてあり、途中で直角に折り曲げている場合を示している。内部熱交換器４の他端は、エンジンルームと車室とを隔てている隔壁２０を介してエンジンルーム内に伸びているが、自動車への組み付けの都合上、隔壁２０のところで、エンジンルーム内に配管されるもう一つの内部熱交換器４ｄの一端と接続され、パイプクランプ２１によって締結されている。内部熱交換器４ｄの他端は、図示しない分岐部に結合され、その分岐部には、レシーバドライヤ３からの高圧配管と、圧縮機１への低圧配管とがそれぞれ接続されている。 FIG. 4 is a cross-sectional view showing an installation example of the internal heat exchanger on the vehicle interior side.
The internal heat exchanger 4 that also serves as a pipe can constitute a part of the pipe in the vehicle compartment and the pipe in the engine room. In the illustrated example, the expansion valve 5 is directly connected to the evaporator 6, and one end of the internal heat exchanger 4c is connected thereto. In addition, this internal heat exchanger 4c is shortened by the relationship of illustration, and has shown the case where it is bent at right angles in the middle. The other end of the internal heat exchanger 4 extends into the engine room via a partition wall 20 that separates the engine room and the vehicle compartment. For convenience of assembly to the automobile, the other end of the internal heat exchanger 4 is located in the engine room. It is connected to one end of another internal heat exchanger 4d that is connected to the pipe, and is fastened by a pipe clamp 21. The other end of the internal heat exchanger 4d is coupled to a branch portion (not shown), and a high pressure pipe from the receiver dryer 3 and a low pressure pipe to the compressor 1 are connected to the branch portion.

蒸発器６は、その冷媒入口と冷媒出口とがタンクの同一側面に並設されており、その冷媒入口には入口配管が結合されている。冷媒出口に連通する出口配管は、入口配管を取り囲むようにしてその入口配管とは同軸二重管を成すように蒸発器６のタンクに結合されている。   The evaporator 6 has a refrigerant inlet and a refrigerant outlet arranged on the same side surface of the tank, and an inlet pipe is coupled to the refrigerant inlet. The outlet pipe communicating with the refrigerant outlet is connected to the tank of the evaporator 6 so as to surround the inlet pipe and form a coaxial double pipe with the inlet pipe.

膨張弁５は、蒸発器６の入口配管および出口配管に接続される同軸二重管構造のボディを有し、このボディの蒸発器６との接続側とは反対側に、蒸発器６を出た冷媒の温度および圧力を感知するパワーエレメントが装着されている。膨張弁５のボディの側面（図では、下方の面）には、同軸二重管構造の開口部を有し、その内側の開口部は高圧冷媒入口を構成し、その外側の開口部は低圧冷媒出口を構成している。その高圧冷媒入口には、内部熱交換器４ｃの内管１２が接続され、低圧冷媒出口の開口部には、外管１１が接続されている。   The expansion valve 5 has a body having a coaxial double pipe structure connected to the inlet pipe and the outlet pipe of the evaporator 6, and the evaporator 6 is provided on the opposite side of the body from the side connected to the evaporator 6. A power element that senses the temperature and pressure of the refrigerant is installed. The side surface (lower surface in the figure) of the expansion valve 5 has an opening portion of a coaxial double pipe structure, the inner opening portion forms a high-pressure refrigerant inlet, and the outer opening portion has a low pressure. It constitutes the refrigerant outlet. The inner pipe 12 of the internal heat exchanger 4c is connected to the high-pressure refrigerant inlet, and the outer pipe 11 is connected to the opening of the low-pressure refrigerant outlet.

これにより、レシーバドライヤ３を出た高温・高圧の液冷媒は、エンジンルーム内に配置された内部熱交換器４ｄの内管、内部熱交換器４ｃの内管１２を介して膨張弁５に供給される。その液冷媒は、膨張弁５で膨張されて低温・低圧の蒸気となる。その蒸気冷媒は、蒸発器６に供給され、車室内の空気と熱交換されることにより蒸発される。蒸発された冷媒は、膨張弁５のボディに形成された低圧冷媒通路を通って内部熱交換器４ｃの外管１１に送られる。膨張弁５は、蒸発された冷媒が低圧冷媒通路を通過するとき、パワーエレメントがその冷媒の温度および圧力を検出してその冷媒が所定の過熱度を維持するように蒸発器６に供給する冷媒の流量を制御する。内部熱交換器４ｃの外管１１に送り込まれた冷媒は、内部熱交換器４ｄの外管および分岐部を介して圧縮機１の吸入口に送られることになる。   As a result, the high-temperature and high-pressure liquid refrigerant exiting the receiver dryer 3 is supplied to the expansion valve 5 via the inner pipe of the internal heat exchanger 4d and the inner pipe 12 of the internal heat exchanger 4c arranged in the engine room. Is done. The liquid refrigerant is expanded by the expansion valve 5 and becomes low temperature / low pressure steam. The vapor refrigerant is supplied to the evaporator 6 and is evaporated by exchanging heat with the air in the passenger compartment. The evaporated refrigerant passes through the low-pressure refrigerant passage formed in the body of the expansion valve 5 and is sent to the outer tube 11 of the internal heat exchanger 4c. When the evaporated refrigerant passes through the low-pressure refrigerant passage, the expansion valve 5 detects the temperature and pressure of the refrigerant and supplies the refrigerant to the evaporator 6 so that the refrigerant maintains a predetermined degree of superheat. To control the flow rate. The refrigerant sent into the outer pipe 11 of the internal heat exchanger 4c is sent to the suction port of the compressor 1 through the outer pipe and the branch portion of the internal heat exchanger 4d.

内部熱交換器４では、その内管１２を流れる高温・高圧の冷媒と、外管１１と内管１２との間の空間を流れる低温・低圧の冷媒との間で熱交換が行われ、これによって、膨張弁５に導入される冷媒はさらに過冷却され、圧縮機１に導入される冷媒はさらに過熱されることになるので、この冷凍サイクルの成績係数を向上させることができる。成績係数が向上されることにより、冷凍サイクルが所要の冷力を得るのにより少ない動力で済むことになり、圧縮機１の駆動源であるエンジンの負荷をより小さくできることから、省エネルギの自動車運転が可能になる。   In the internal heat exchanger 4, heat exchange is performed between the high-temperature and high-pressure refrigerant flowing through the inner pipe 12 and the low-temperature and low-pressure refrigerant flowing through the space between the outer pipe 11 and the inner pipe 12. Thus, the refrigerant introduced into the expansion valve 5 is further subcooled, and the refrigerant introduced into the compressor 1 is further overheated, so that the coefficient of performance of the refrigeration cycle can be improved. By improving the coefficient of performance, the refrigeration cycle requires less power to obtain the required cooling power, and the load on the engine that is the driving source of the compressor 1 can be further reduced. Is possible.

図５は第３の実施の形態に係る内部熱交換器を示す長軸断面図である。なお、この図５において、図２に示した構成要素と同じ構成要素については同じ符号を付してその詳細な説明は省略する。   FIG. 5 is a long-axis cross-sectional view showing an internal heat exchanger according to the third embodiment. In FIG. 5, the same components as those shown in FIG. 2 are denoted by the same reference numerals, and detailed description thereof is omitted.

この第３の実施の形態に係る内部熱交換器４ｅは、エンジンルーム内に設置される配管として使用されるもので、外管１１の一部がフレキシブルホース２２によって構成されている。すなわち、この内部熱交換器４ｅの外管１１は、圧縮機１に接続される側の第１外管１１ａと、フレキシブルホース２２と、隔壁２０にて車室内側の内部熱交換器４ｄの外管１１に接続される第２外管１１ｂとを有している。この内部熱交換器４ｅの両端における末端処理および外管１１の中に配置される内管１２は、第１の実施の形態に係る内部熱交換器４ａと同じ構成にしてある。内部熱交換器４ｅの内管１２は、第１の実施の形態に係る内部熱交換器４ａで使用しているものよりも細い金属パイプを使用している。これにより、内管１２は、フレキシブルホース２２に近いしなやかさを持たせ、冷凍サイクル内を循環する冷媒の総量をさらに減らすことを可能にしている。   The internal heat exchanger 4e according to the third embodiment is used as a pipe installed in the engine room, and a part of the outer tube 11 is constituted by a flexible hose 22. That is, the outer pipe 11 of the internal heat exchanger 4e is connected to the first outer pipe 11a on the side connected to the compressor 1, the flexible hose 22, and the partition wall 20 outside the internal heat exchanger 4d on the vehicle interior side. And a second outer tube 11 b connected to the tube 11. The end treatment at both ends of the internal heat exchanger 4e and the inner tube 12 disposed in the outer tube 11 have the same configuration as the internal heat exchanger 4a according to the first embodiment. The inner pipe 12 of the internal heat exchanger 4e uses a metal pipe that is thinner than that used in the internal heat exchanger 4a according to the first embodiment. As a result, the inner tube 12 has flexibility close to that of the flexible hose 22 and can further reduce the total amount of refrigerant circulating in the refrigeration cycle.

フレキシブルホース２２は、外管１１の外径に概略等しい内径を有し、両側の開口端から第１および第２外管１１ａ，１１ｂの先端部が圧入され、この先端部とその圧入領域にわたってフレキシブルホース２２に外嵌された金属スリーブ２３とで挟持することによって第１および第２外管１１ａ，１１ｂと固定されている。第１および第２外管１１ａ，１１ｂは、その先端近傍に複数の溝２４が円周方向に設けられており、金属スリーブ２３を溝２４に向かって内側に変形させて、フレキシブルホース２２を溝２４に食い込ませることにより、第１および第２外管１１ａ，１１ｂとフレキシブルホース２２とを気密に接続するとともに軸方向のずれが生じないようにしている。   The flexible hose 22 has an inner diameter substantially equal to the outer diameter of the outer tube 11, and the distal ends of the first and second outer tubes 11a and 11b are press-fitted from the open ends on both sides, and the flexible hose 22 is flexible over the distal end and the press-fitted region. It is fixed to the first and second outer pipes 11a and 11b by being sandwiched by a metal sleeve 23 fitted on the hose 22. The first and second outer pipes 11a and 11b are provided with a plurality of grooves 24 in the circumferential direction in the vicinity of the tips thereof, and the metal sleeve 23 is deformed inward toward the grooves 24 so that the flexible hose 22 is grooved. By biting into 24, the first and second outer tubes 11a, 11b and the flexible hose 22 are connected in an airtight manner, and an axial displacement is prevented from occurring.

フレキシブルホース２２は、第１および第２外管１１ａ，１１ｂの厚さの分だけ内径が大きくなっているため、内管１２がフレキシブルホース２２の内壁に接触できなくなる。そのため、この内部熱交換器４ｅでは、フレキシブルホース２２の内壁に第１および第２外管１１ａ，１１ｂの厚さに概略等しい太さを有するひも状の緩衝材２５を螺旋状に巻かれた状態で配置している。この緩衝材２５は、たとえば樹脂製のひもであり、内管１２が巻かれている螺旋方向とは逆方向に螺旋状に巻かれていることで、適当なピッチで内管１２と接触されることになり、外部より与えられる振動によって内管１２が外管１１に衝突してしまうこともない。   Since the inner diameter of the flexible hose 22 is increased by the thickness of the first and second outer tubes 11 a and 11 b, the inner tube 12 cannot contact the inner wall of the flexible hose 22. Therefore, in this internal heat exchanger 4e, a string-like cushioning material 25 having a thickness substantially equal to the thickness of the first and second outer tubes 11a and 11b is spirally wound on the inner wall of the flexible hose 22 It is arranged with. The buffer material 25 is a string made of resin, for example, and is wound in a spiral shape in a direction opposite to the spiral direction in which the inner tube 12 is wound, so that the buffer material 25 comes into contact with the inner tube 12 at an appropriate pitch. In other words, the inner tube 12 does not collide with the outer tube 11 due to vibration applied from the outside.

なお、フレキシブルホース２２は、たとえば耐候性のゴムホースとすることができ、その内壁には冷媒の浸透を防止する樹脂チューブが内張りされ、中には編組繊維による補強層が埋設されたものを使用している。また、緩衝材２５は、断面円形のひもではなく、外管１１の厚さに概略等しい厚さを有する樹脂製のテープであっても良い。   The flexible hose 22 can be, for example, a weather-resistant rubber hose, and a resin tube for preventing the penetration of the refrigerant is lined on the inner wall, and a reinforcing layer made of braided fibers is embedded inside. ing. The buffer material 25 may be a resin tape having a thickness substantially equal to the thickness of the outer tube 11 instead of a string having a circular cross section.

以上の構成の内部熱交換器４ｅによれば、外管１１の一部がフレキシブルホース２２によって構成されているので、第１外管１１ａの側に接続される圧縮機１の振動は、フレキシブルホース２２によって吸収される。したがって、圧縮機１およびレシーバドライヤ３を介して第１外管１１ａに伝達されるエンジンの振動は、フレキシブルホース２２で遮断され、第２外管１１ｂの側へ伝達されることはない。フレキシブルホース２２内に配置された内管１２は、細く、螺旋状に形成されていてよりしなやかな構成になっているので、第１外管１１ａの振動を第２外管１１ｂの側へ伝達するには至らない。   According to the internal heat exchanger 4e having the above configuration, since a part of the outer tube 11 is constituted by the flexible hose 22, the vibration of the compressor 1 connected to the first outer tube 11a side is caused by the flexible hose. 22 is absorbed. Therefore, the engine vibration transmitted to the first outer tube 11a via the compressor 1 and the receiver dryer 3 is blocked by the flexible hose 22 and is not transmitted to the second outer tube 11b. Since the inner tube 12 disposed in the flexible hose 22 is thin and formed in a spiral shape and has a more supple structure, the vibration of the first outer tube 11a is transmitted to the second outer tube 11b side. It does not lead to.

自動車用空調装置の冷凍サイクルを示すシステム図である。It is a system diagram which shows the refrigerating cycle of the air conditioner for motor vehicles. 第１の実施の形態に係る内部熱交換器を示す図であって、（Ａ）は内部熱交換器の内部を示す長軸断面図、（Ｂ）は内管および位置決め部材を示す図、（Ｃ）は内管のａ−ａ矢視拡大端面図、（Ｄ）は内管のｂ−ｂ矢視拡大断面図、（Ｅ）は内管のｃ−ｃ矢視拡大端面図である。It is a figure which shows the internal heat exchanger which concerns on 1st Embodiment, Comprising: (A) is a longitudinal cross-sectional view which shows the inside of an internal heat exchanger, (B) is a figure which shows an inner tube and a positioning member, (C) is an aa arrow enlarged end view of the inner pipe, (D) is an enlarged cross sectional view of the inner pipe taken along the line bb, and (E) is an enlarged end view of the inner pipe taken along the line cc. 第２の実施の形態に係る内部熱交換器を示す図であって、（Ａ）は内部熱交換器の内部を示す長軸断面図、（Ｂ）は内管および位置決め部材を示す図、（Ｃ）は内部熱交換器のａ−ａ矢視拡大断面図、（Ｄ）は内部熱交換器のｂ−ｂ矢視拡大断面図、（Ｅ）は内管のｃ−ｃ矢視拡大断面図、（Ｆ）は内管のｄ−ｄ矢視拡大断面図である。It is a figure which shows the internal heat exchanger which concerns on 2nd Embodiment, Comprising: (A) is a longitudinal cross-sectional view which shows the inside of an internal heat exchanger, (B) is a figure which shows an inner tube and a positioning member, C) is an enlarged cross-sectional view of the internal heat exchanger taken along the aa arrow, (D) is an enlarged cross-sectional view of the internal heat exchanger taken along the bb arrow, and (E) is an enlarged cross-sectional view of the inner tube taken along the cc arrow. , (F) is an enlarged cross-sectional view of the inner tube taken along line dd. 車室内側の内部熱交換器の設置例を示す断面図である。It is sectional drawing which shows the example of installation of the internal heat exchanger of the vehicle interior side. 第３の実施の形態に係る内部熱交換器を示す長軸断面図である。It is a long axis sectional view showing an internal heat exchanger concerning a 3rd embodiment.

符号の説明Explanation of symbols

１ 圧縮機
２ 凝縮器
３ レシーバドライヤ
４，４ａ，４ｂ，４ｃ，４ｄ，４ｅ 内部熱交換器
５ 膨張弁
６ 蒸発器
１１ 外管
１１ａ 第１外管
１１ｂ 第２外管
１２ 内管
１３，１４ 位置決め部材
１５ 筒状部
１６ 支持部材
１７ 円筒部
１８ リング部
１９ 支持部材
２０ 隔壁
２１ パイプクランプ
２２ フレキシブルホース
２３ 金属スリーブ
２４ 溝
２５ 緩衝材 DESCRIPTION OF SYMBOLS 1 Compressor 2 Condenser 3 Receiver dryer 4,4a, 4b, 4c, 4d, 4e Internal heat exchanger 5 Expansion valve 6 Evaporator 11 Outer tube 11a First outer tube 11b Second outer tube 12 Inner tube 13,14 Positioning Member 15 Cylindrical portion 16 Support member 17 Cylindrical portion 18 Ring portion 19 Support member 20 Bulkhead 21 Pipe clamp 22 Flexible hose 23 Metal sleeve 24 Groove 25 Buffer material

Claims (9)

冷凍サイクル内で膨張装置に導入される高温・高圧の冷媒と圧縮機へ導入される低温・低圧の冷媒との間で熱交換を行う内部熱交換器において、
外管とこの外管の中に収容された内管とを備え、前記内管は、前記外管の軸心を中心にして螺旋状に巻かれた形状を有し、その最外周面の少なくとも一部が前記外管の内壁に接触されていることを特徴とする内部熱交換器。 In the internal heat exchanger that performs heat exchange between the high-temperature and high-pressure refrigerant introduced into the expansion device in the refrigeration cycle and the low-temperature and low-pressure refrigerant introduced into the compressor,
An outer tube and an inner tube accommodated in the outer tube, the inner tube having a shape wound spirally around the axis of the outer tube, and having at least an outermost peripheral surface thereof An internal heat exchanger characterized in that a part thereof is in contact with the inner wall of the outer tube. 前記内管は、その最外周に内接する仮想円筒の径が前記外管の内径より大きくなるよう螺旋状に巻かれた形状に形成され、前記外管に圧入することによって螺旋部分の概略全周が前記外管の内壁に接触した状態で前記外管の中に収容されている請求項１記載の内部熱交換器。   The inner tube is formed in a spirally wound shape so that the diameter of a virtual cylinder inscribed at the outermost periphery thereof is larger than the inner diameter of the outer tube, and the entire circumference of the spiral portion is formed by press-fitting into the outer tube. The internal heat exchanger according to claim 1, wherein the internal heat exchanger is accommodated in the outer pipe in a state of being in contact with the inner wall of the outer pipe. 前記内管は、その最外周に内接する仮想円筒の径が前記外管の内径より小さくなるよう螺旋状に巻かれた形状に形成され、所定のピッチにて半径方向に長径を有する断面楕円となる形状に部分的に変形されて螺旋中心から前記長径の外方端までの距離が前記外管の内壁面の半径より大きくし、前記外管に圧入することによって変形部分の外壁が前記外管の内壁に部分的に接触した状態で前記外管の中に収容されている請求項１記載の内部熱交換器。   The inner tube is formed in a spirally wound shape so that the diameter of a virtual cylinder inscribed in the outermost periphery thereof is smaller than the inner diameter of the outer tube, and a cross-sectional ellipse having a major axis in the radial direction at a predetermined pitch The distance from the spiral center to the outer end of the major axis is made larger than the radius of the inner wall surface of the outer tube, and the outer wall of the deformed portion is press-fitted into the outer tube. The internal heat exchanger according to claim 1, wherein the internal heat exchanger is housed in the outer pipe in a state of being in partial contact with the inner wall of the outer pipe. 前記内管は、その両端に位置決め部材を有し、両側の開口端が同軸二重管構造になっている請求項１記載の内部熱交換器。   The internal heat exchanger according to claim 1, wherein the inner pipe has positioning members at both ends thereof, and the open ends on both sides have a coaxial double pipe structure. 前記内管は、その通路断面積が前記外管の通路断面積の１５％以下である請求項１記載の内部熱交換器。   The internal heat exchanger according to claim 1, wherein the inner pipe has a passage cross-sectional area of 15% or less of a passage cross-sectional area of the outer pipe. 前記外管は、その一部がフレキシブルホースによって構成されている請求項１記載の内部熱交換器。   The internal heat exchanger according to claim 1, wherein a part of the outer pipe is configured by a flexible hose. 前記フレキシブルホースは、前記外管の外径に概略等しい内径を有し、両端より先端近傍に少なくとも一条の溝が円周方向に設けられた前記外管の先端部が圧入され、かつ、その圧入領域にわたって前記フレキシブルホースに外嵌された金属スリーブを前記溝に向かって内側に変形させることにより、前記外管と気密に接続されている請求項６記載の内部熱交換器。   The flexible hose has an inner diameter that is substantially equal to the outer diameter of the outer tube, and the distal end portion of the outer tube in which at least one groove is provided in the circumferential direction in the vicinity of the distal end from both ends, and the press-fitting thereof The internal heat exchanger according to claim 6, wherein a metal sleeve externally fitted to the flexible hose is deformed inward toward the groove over an area, thereby being hermetically connected to the outer tube. 前記フレキシブルホースの内壁に前記外管の厚さに概略等しい太さまたは厚さを有するひも状またはテープ状の緩衝材が前記内管の巻かれている螺旋方向とは逆向きに螺旋状に巻かれた状態で配置されている請求項６記載の内部熱交換器。   A string-like or tape-like cushioning material having a thickness or thickness substantially equal to the thickness of the outer tube is wound spirally on the inner wall of the flexible hose in a direction opposite to the spiral direction in which the inner tube is wound. The internal heat exchanger according to claim 6, wherein the internal heat exchanger is arranged in an open state. 前記フレキシブルホースは、補強層を有するゴムホースである請求項６記載の内部熱交換器。   The internal heat exchanger according to claim 6, wherein the flexible hose is a rubber hose having a reinforcing layer.
JP2008130245A 2008-04-08 2008-05-19 Internal heat exchanger Pending JP2009270802A (en)

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2333472A1 (en) * 2009-12-10 2011-06-15 Hutchinson Internal heat exchanger for a vehicule air conditioning circuit and such circuit
CN102121800A (en) * 2010-01-11 2011-07-13 Lg电子株式会社 Heat exchanger
JP2013052862A (en) * 2011-09-05 2013-03-21 Dr Ing Hcf Porsche Ag Refrigeration circuit for use in automobile
CN103292620A (en) * 2013-05-30 2013-09-11 西安交通大学 Novel telescopic heat exchange tube
JP2017198392A (en) * 2016-04-27 2017-11-02 株式会社ヴァレオジャパン Double tube
JP2019527805A (en) * 2016-07-01 2019-10-03 テクニップ フランス ソシエテ パ アクシオンス シンプリフィエ Cracking furnace
KR102152001B1 (en) * 2019-07-26 2020-09-04 동명대학교산학협력단 Agricultural Heating and Cooling System Using Renewable Energy
KR102152002B1 (en) * 2019-07-26 2020-09-07 동명대학교산학협력단 Agricultural Heating and Cooling System Using Renewable Energy and Hydrogen

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2333472A1 (en) * 2009-12-10 2011-06-15 Hutchinson Internal heat exchanger for a vehicule air conditioning circuit and such circuit
FR2953917A1 (en) * 2009-12-10 2011-06-17 Hutchinson INTERNAL THERMAL EXCHANGER FOR AIR CONDITIONING CIRCUIT OF MOTOR VEHICLE AND SUCH CIRCUIT
CN102121800A (en) * 2010-01-11 2011-07-13 Lg电子株式会社 Heat exchanger
KR101608996B1 (en) * 2010-01-11 2016-04-05 엘지전자 주식회사 Heat exchanger
JP2013052862A (en) * 2011-09-05 2013-03-21 Dr Ing Hcf Porsche Ag Refrigeration circuit for use in automobile
CN103292620A (en) * 2013-05-30 2013-09-11 西安交通大学 Novel telescopic heat exchange tube
JP2017198392A (en) * 2016-04-27 2017-11-02 株式会社ヴァレオジャパン Double tube
JP2019527805A (en) * 2016-07-01 2019-10-03 テクニップ フランス ソシエテ パ アクシオンス シンプリフィエ Cracking furnace
US11162034B2 (en) 2016-07-01 2021-11-02 Technip France S.A.S. Cracking furnace
JP7005538B2 (en) 2016-07-01 2022-01-21 テクニップ フランス ソシエテ パ アクシオンス シンプリフィエ Decomposition furnace
KR102152001B1 (en) * 2019-07-26 2020-09-04 동명대학교산학협력단 Agricultural Heating and Cooling System Using Renewable Energy
KR102152002B1 (en) * 2019-07-26 2020-09-07 동명대학교산학협력단 Agricultural Heating and Cooling System Using Renewable Energy and Hydrogen

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