JPWO2019130386A1 - Heat exchanger manufacturing method and heat exchanger - Google Patents

Heat exchanger manufacturing method and heat exchanger Download PDF

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JPWO2019130386A1
JPWO2019130386A1 JP2019561401A JP2019561401A JPWO2019130386A1 JP WO2019130386 A1 JPWO2019130386 A1 JP WO2019130386A1 JP 2019561401 A JP2019561401 A JP 2019561401A JP 2019561401 A JP2019561401 A JP 2019561401A JP WO2019130386 A1 JPWO2019130386 A1 JP WO2019130386A1
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pipe
heat exchanger
inner pipe
bending
tube
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JP6861848B2 (en
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功介 山口
功介 山口
正章 我妻
正章 我妻
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Mitsubishi Electric Corp
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/06—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of metal 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
    • 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
    • F28D7/02—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 helically coiled

Abstract

熱交換器は、流体が流通する内管及び外管を備える。外管は、内管の外周面に螺旋状に巻き付けられた状態で内管に接合されている。内管において、外管が巻き付けられていない両端部の強度は、外管が巻き付けられている部分の強度よりも高くなるよう構成されている。The heat exchanger includes an inner tube and an outer tube through which a fluid flows. The outer pipe is joined to the inner pipe in a state of being spirally wound around the outer peripheral surface of the inner pipe. In the inner pipe, the strength of both ends where the outer pipe is not wound is configured to be higher than the strength of the portion where the outer pipe is wound.

Description

本発明は、流体が流通する内管及び外管を備えた熱交換器の製造方法、及び熱交換器に関するものである。 The present invention relates to a method for manufacturing a heat exchanger provided with an inner tube and an outer tube through which a fluid flows, and a heat exchanger.

熱交換器には、水が流通する内管と、冷媒が流通する外管とを備えるものがある。外管は、内管の外周面に巻き付けられている。このような構造を有する熱交換器において、内管と外管が、ロウ付け若しくははんだ付けにより伝熱接合される場合がある。ロウ付け若しくははんだ付けにより伝熱接合する場合、内管及び外管の他に、ロウ付けに用いるロウ材、又は、はんだ付けに用いるはんだが必要である。また、ロウ付け若しくははんだ付けのための熱源を確保しなければならない。そのため、このような伝熱接合は製造コストが高騰するという問題がある。そこで、例えば、特許文献１には、ロウ付け若しくははんだ付けを使用することなく、内管と外管とを接合する方法として、水等の液体によって内管を拡管させることにより、内管と外管とを密着させる方法が記載されている。 Some heat exchangers include an inner pipe through which water flows and an outer pipe through which refrigerant flows. The outer tube is wound around the outer peripheral surface of the inner tube. In a heat exchanger having such a structure, the inner pipe and the outer pipe may be heat-transfer-bonded by brazing or soldering. When heat transfer bonding is performed by brazing or soldering, in addition to the inner and outer pipes, the brazing material used for brazing or the solder used for soldering is required. In addition, a heat source for brazing or soldering must be secured. Therefore, such a heat transfer junction has a problem that the manufacturing cost rises. Therefore, for example, in Patent Document 1, as a method of joining the inner pipe and the outer pipe without using brazing or soldering, the inner pipe and the outer pipe are expanded by expanding the inner pipe with a liquid such as water. A method for bringing the tube into close contact is described.

特開２００４−９３０５７号公報Japanese Unexamined Patent Publication No. 2004-93057

特許文献１に記載されているように水等の液体によって内管を拡管する方法では、内管と外管とを十分に密着させるために、非常に高い圧力で内管を拡管させる必要がある。しかしながら、高い圧力を内管にかけると、内管において外管が巻き付けられていない部分は、外管が巻き付けられていない部分に比べ強度が弱いため、過剰に変形してしまう。このような内管の変形を回避するため、内管にかける圧力を抑えることが考えられる。しかしながら、内管にかける圧力が不十分だと、内管と外管との密着が弱い状態となり、十分な伝熱接合が得られない。その結果、内管を流通する水と外管を流通する冷媒との間で、高い熱交換率が得られないという問題がある。 In the method of expanding the inner pipe with a liquid such as water as described in Patent Document 1, it is necessary to expand the inner pipe with a very high pressure in order to sufficiently bring the inner pipe and the outer pipe into close contact with each other. .. However, when a high pressure is applied to the inner pipe, the portion of the inner pipe where the outer pipe is not wound is weaker than the portion where the outer pipe is not wound, and therefore is excessively deformed. In order to avoid such deformation of the inner pipe, it is conceivable to suppress the pressure applied to the inner pipe. However, if the pressure applied to the inner pipe is insufficient, the adhesion between the inner pipe and the outer pipe becomes weak, and sufficient heat transfer bonding cannot be obtained. As a result, there is a problem that a high heat exchange rate cannot be obtained between the water flowing through the inner pipe and the refrigerant flowing through the outer pipe.

本発明は、上記のような課題を解決するためになされたものであり、より高い熱交換率を有する熱交換器の製造方法、及び熱交換器を提供することを目的とする。 The present invention has been made to solve the above problems, and an object of the present invention is to provide a method for manufacturing a heat exchanger having a higher heat exchange rate and a heat exchanger.

本発明に係る熱交換器の製造方法は、流体が流通する内管及び外管を備え、前記外管は前記内管の両端部を除く外周面に螺旋状に巻き付けられた状態で前記内管に接合されている熱交換器の製造方法であって、前記内管の前記両端部の強度を、前記外管が巻き付けられる部分の強度よりも高くする補強工程と、前記外管が巻き付けられている前記内管の内部の圧力を上昇させて前記内管を拡管する拡管工程とを含んでいる。 The method for manufacturing a heat exchanger according to the present invention includes an inner pipe and an outer pipe through which fluid flows, and the outer pipe is spirally wound around an outer peripheral surface excluding both ends of the inner pipe. A method of manufacturing a heat exchanger joined to the above, wherein the strength of both ends of the inner pipe is made higher than the strength of the portion around which the outer pipe is wound, and the outer pipe is wound. It includes a tube expansion step of increasing the pressure inside the inner tube to expand the inner tube.

本発明に係る熱交換器は、流体が流通する内管及び外管を備え、前記外管は、前記内管の両端部を除く外周面に螺旋状に巻き付けられた状態で前記内管に接合されており、前記内管において、前記外管が巻き付けられていない前記両端部の強度は、前記外管が巻き付けられている部分の強度よりも高く構成されているものである。 The heat exchanger according to the present invention includes an inner pipe and an outer pipe through which a fluid flows, and the outer pipe is joined to the inner pipe in a state of being spirally wound around an outer peripheral surface excluding both ends of the inner pipe. In the inner pipe, the strength of both ends of the inner pipe from which the outer pipe is not wound is higher than the strength of the portion around which the outer pipe is wound.

本発明に係る熱交換器の製造方法によると、内管の両端部の強度を外管が巻き付けられている部分の強度よりも高くするので、内管を拡管したとき、外管が巻き付けられていない内管の両端部の過剰な変形を抑制することができる。従って、内管の拡管圧力をより高くすることができ、内管において外管が巻き付けられている部分と外管とを密着させることができる。その結果、内管と外管との間の熱交換効率がより高められた熱交換器が得られる。 According to the method for manufacturing a heat exchanger according to the present invention, the strength of both ends of the inner pipe is made higher than the strength of the portion around which the outer pipe is wound. Therefore, when the inner pipe is expanded, the outer pipe is wound. Excessive deformation of both ends of the inner tube can be suppressed. Therefore, the expansion pressure of the inner pipe can be made higher, and the portion of the inner pipe around which the outer pipe is wound can be brought into close contact with the outer pipe. As a result, a heat exchanger with higher heat exchange efficiency between the inner pipe and the outer pipe can be obtained.

本発明の実施の形態１に係る熱交換器を示す図である。It is a figure which shows the heat exchanger which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る熱交換器の内管の一方の端部を拡大して示す図である。It is a figure which shows enlarged one end part of the inner tube of the heat exchanger which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る熱交換器の内管の他方の端部を拡大して示す図である。It is an enlarged view which shows the other end of the inner tube of the heat exchanger which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る熱交換器の製造方法の工程を示すフローチャートである。It is a flowchart which shows the process of the manufacturing method of the heat exchanger which concerns on Embodiment 1 of this invention. 内管において焼きなまし処理を施す箇所を示す図である。It is a figure which shows the part where the annealing treatment is performed in the inner pipe. 拡管工程を実行する際の内管の一方の端部を拡大して示す図である。It is a figure which enlarges and shows one end part of the inner pipe at the time of performing a pipe expansion process. 拡管工程を実行する際の内管の他方の端部を拡大して示す図である。It is a figure which enlarges and shows the other end part of the inner pipe at the time of performing a pipe expansion process. 本発明の実施の形態２に係る熱交換器の内管の一方の端部を拡大して示す図である。It is a figure which shows enlarged one end part of the inner tube of the heat exchanger which concerns on Embodiment 2 of this invention.

以下に、本発明における熱交換器、及びその製造方法の実施の形態を図面に基づいて詳細に説明する。尚、以下に説明する実施の形態によって本発明が限定されるものではない。また、以下の図面においては各構成部材の大きさ及び形状は実際の装置とは異なる場合がある。 Hereinafter, embodiments of the heat exchanger and the method for manufacturing the heat exchanger in the present invention will be described in detail with reference to the drawings. The present invention is not limited to the embodiments described below. Further, in the following drawings, the size and shape of each component may differ from the actual device.

実施の形態１．
図１は、本発明の実施の形態１に係る熱交換器を示す図である。熱交換器１は、内管１０と、外管２０Ａ、外管２０Ｂ、及び外管２０Ｃとを有している。以降の説明において、外管２０Ａ、外管２０Ｂ、及び外管２０Ｃを総称して外管２０と言う場合がある。内管１０には水等の流体が流通する。すなわち、内管１０は例えば水管である。外管２０Ａ、外管２０Ｂ、及び外管２０Ｃには、それぞれ冷媒等の流体が流通する。すなわち、外管２０Ａ、外管２０Ｂ、及び外管２０Ｃは、例えば冷媒管である。内管１０は、一方の端部１１と、他方の端部１２と、螺旋構造部１３とを有している。螺旋構造部１３は、端部１１と端部１２との間に位置している。内管１０は螺旋構造部１３の複数箇所で曲げ加工されており、全体として略長方形の螺旋状に形成されている。内管１０の両端部のうちの一方の端部１１には配管３０が接合され、他方の端部１２には配管４０が接合されている。Embodiment 1.
FIG. 1 is a diagram showing a heat exchanger according to the first embodiment of the present invention. The heat exchanger 1 has an inner tube 10, an outer tube 20A, an outer tube 20B, and an outer tube 20C. In the following description, the outer pipe 20A, the outer pipe 20B, and the outer pipe 20C may be collectively referred to as the outer pipe 20. A fluid such as water flows through the inner pipe 10. That is, the inner pipe 10 is, for example, a water pipe. A fluid such as a refrigerant flows through the outer pipe 20A, the outer pipe 20B, and the outer pipe 20C, respectively. That is, the outer pipe 20A, the outer pipe 20B, and the outer pipe 20C are, for example, refrigerant pipes. The inner pipe 10 has one end portion 11, the other end portion 12, and a spiral structure portion 13. The spiral structure portion 13 is located between the end portion 11 and the end portion 12. The inner pipe 10 is bent at a plurality of points of the spiral structure portion 13, and is formed in a substantially rectangular spiral shape as a whole. A pipe 30 is joined to one end 11 of both ends of the inner pipe 10, and a pipe 40 is joined to the other end 12.

図２は、本発明の実施の形態１に係る熱交換器の内管の一方の端部を拡大して示す図である。図３は、本発明の実施の形態１に係る熱交換器の内管の他方の端部を拡大して示す図である。尚、図２及び図３は、熱交換器１を内管１０の管軸に沿って切断した断面を模式的に示している。図２には、内管１０の端部１１が拡大して示されており、図３には内管１０の端部１２が拡大されて示されている。図２及び図３に示すように、螺旋構造部１３の外周面に３条の螺旋溝１３Ａ、螺旋溝１３Ｂ、及び螺旋溝１３Ｃが形成されている。螺旋溝１３Ａ、螺旋溝１３Ｂ、及び螺旋溝１３Ｃの間の山部１３Ｄと、谷部である螺旋溝１３Ａ、螺旋溝１３Ｂ、及び螺旋溝１３Ｃとで、螺旋構造部１３の螺旋構造が形成されている。螺旋構造部１３の螺旋構造は、直管形状の伝熱管を加工することで得られる。端部１１の外周面及び端部１２の外周面には螺旋溝が形成されておらず、端部１１及び端部１２は直管形状を呈している。すなわち、端部１１及び端部１２はそれぞれ直管部を構成している。 FIG. 2 is an enlarged view of one end of an inner tube of the heat exchanger according to the first embodiment of the present invention. FIG. 3 is an enlarged view of the other end of the inner tube of the heat exchanger according to the first embodiment of the present invention. Note that FIGS. 2 and 3 schematically show a cross section of the heat exchanger 1 cut along the pipe axis of the inner pipe 10. FIG. 2 shows an enlarged end 11 of the inner pipe 10, and FIG. 3 shows an enlarged end 12 of the inner pipe 10. As shown in FIGS. 2 and 3, three spiral grooves 13A, a spiral groove 13B, and a spiral groove 13C are formed on the outer peripheral surface of the spiral structure portion 13. The spiral structure of the spiral structure portion 13 is formed by the mountain portion 13D between the spiral groove 13A, the spiral groove 13B, and the spiral groove 13C, and the spiral groove 13A, the spiral groove 13B, and the spiral groove 13C which are valley portions. There is. The spiral structure of the spiral structure portion 13 is obtained by processing a straight tube-shaped heat transfer tube. No spiral groove is formed on the outer peripheral surface of the end portion 11 and the outer peripheral surface of the end portion 12, and the end portion 11 and the end portion 12 have a straight pipe shape. That is, each of the end portion 11 and the end portion 12 constitutes a straight pipe portion.

螺旋溝１３Ａには外管２０Ａが巻き付けられ、螺旋溝１３Ｂには外管２０Ｂが巻き付けられ、螺旋溝１３Ｃには外管２０Ｃが巻き付けられている。外管２０を内管１０の外周面に螺旋状に巻き付けた状態で、すなわち、螺旋構造部１３に外管２０が巻き付けられ、端部１１及び端部１２には外管２０が巻き付けられていない状態で、後述するように内管１０の内部から液圧を加える。これにより、内管１０が液圧拡管されて、外管２０は内管１０に接合された状態となっている。 The outer tube 20A is wound around the spiral groove 13A, the outer tube 20B is wound around the spiral groove 13B, and the outer tube 20C is wound around the spiral groove 13C. In a state where the outer tube 20 is spirally wound around the outer peripheral surface of the inner tube 10, that is, the outer tube 20 is wound around the spiral structure portion 13, and the outer tube 20 is not wound around the end 11 and the end 12. In this state, hydraulic pressure is applied from the inside of the inner tube 10 as described later. As a result, the inner pipe 10 is hydraulically expanded, and the outer pipe 20 is in a state of being joined to the inner pipe 10.

図２に示すように、端部１１には、伝熱管である配管３０が接続されている。配管３０の内径は、端部１１の外径よりも大きい。配管３０の一方の端部に、内径が外側に向けて徐々に大きくなっているフレア部３１が形成されている。配管３０の肉厚は、端部１１の肉厚よりも厚い。配管３０は、フレア部３１が外側を向くよう配置されている。配管３０においてフレア部３１が形成されていない側である他方の端部が内管１０の端部１１とロウ付けにより接合されている。配管３０は、その内周面が端部１１の外周面に接触した状態で接合されている。これにより直管部である端部１１と配管３０とにより二重構造が形成されている。 As shown in FIG. 2, a pipe 30 which is a heat transfer tube is connected to the end portion 11. The inner diameter of the pipe 30 is larger than the outer diameter of the end portion 11. A flare portion 31 having an inner diameter gradually increasing toward the outside is formed at one end of the pipe 30. The wall thickness of the pipe 30 is thicker than the wall thickness of the end portion 11. The pipe 30 is arranged so that the flare portion 31 faces outward. The other end of the pipe 30, which is the side on which the flare portion 31 is not formed, is joined to the end 11 of the inner pipe 10 by brazing. The pipe 30 is joined in a state where its inner peripheral surface is in contact with the outer peripheral surface of the end portion 11. As a result, a double structure is formed by the end portion 11 which is a straight pipe portion and the pipe 30.

図３に示すように、端部１２には、伝熱管である配管４０が接続されている。配管４０の内径は、端部１２の外径よりも大きい。配管４０の肉厚は、端部１２の肉厚よりも厚い。端部１２と配管４０は、ロウ付けにより接合されている。配管４０は、その内周面が端部１２の外周面に接触した状態で接合されている。これにより直管部である端部１２と配管４０とにより二重構造が形成されている。 As shown in FIG. 3, a pipe 40, which is a heat transfer tube, is connected to the end portion 12. The inner diameter of the pipe 40 is larger than the outer diameter of the end portion 12. The wall thickness of the pipe 40 is thicker than the wall thickness of the end portion 12. The end portion 12 and the pipe 40 are joined by brazing. The pipe 40 is joined in a state where its inner peripheral surface is in contact with the outer peripheral surface of the end portion 12. As a result, a double structure is formed by the end portion 12 which is a straight pipe portion and the pipe 40.

図４は、本発明の実施の形態１に係る熱交換器の製造方法の工程を示すフローチャートである。ステップＳ１において、内管１０の焼なまし工程が実行される。上述のように、外管２０Ａ、外管２０Ｂ、及び外管２０Ｃが内管１０の螺旋構造部１３に巻き付けられた状態で、螺旋構造部１３の複数箇所に曲げ加工をすることにより、図１に示すように、内管１０が略長方形の螺旋状に成形された熱交換器１が得られる。このように内管１０を成形するために、螺旋構造部１３では、９０度の角度に曲げられる箇所が存在する。螺旋構造部１３は、螺旋溝１３Ａ、螺旋溝１３Ｂ、及び螺旋溝１３Ｃが形成されたことで、加工硬化している。従って、螺旋構造部１３は、９０度の角度に曲げる曲げ加工の加工性が悪い。そこで、この曲げ加工の加工性の悪さを解消するため、螺旋構造部１３の一部に焼なましが行われる。 FIG. 4 is a flowchart showing a process of a method for manufacturing a heat exchanger according to the first embodiment of the present invention. In step S1, the annealing step of the inner pipe 10 is executed. As described above, in a state where the outer pipe 20A, the outer pipe 20B, and the outer pipe 20C are wound around the spiral structure portion 13 of the inner pipe 10, the spiral structure portion 13 is bent at a plurality of locations, whereby FIG. As shown in the above, a heat exchanger 1 in which the inner tube 10 is formed into a substantially rectangular spiral shape is obtained. In order to form the inner tube 10 in this way, the spiral structure portion 13 has a portion that can be bent at an angle of 90 degrees. The spiral structure portion 13 is work-hardened due to the formation of the spiral groove 13A, the spiral groove 13B, and the spiral groove 13C. Therefore, the spiral structure portion 13 has poor workability in the bending process of bending at an angle of 90 degrees. Therefore, in order to eliminate the poor workability of the bending process, annealing is performed on a part of the spiral structure portion 13.

図５は、内管１０において焼きなまし処理を施す箇所を示す図である。太矢印で示す第１曲げ加工部Ｘ１は、曲げ加工される複数の曲げ加工部のうち端部１１に最も近い加工部である。太矢印で示す第２曲げ加工部Ｘ２は、曲げ加工される複数の曲げ加工部のうち、端部１２に最も近い曲げ加工部である。ステップＳ１の焼なまし工程では、端部１１から第１曲げ加工部Ｘ１の手前までの領域Ｙ１に、焼なまし処理は施されず、また端部１２から第２曲げ加工部Ｘ２の手前までの領域Ｙ２に、焼なまし処理は施されない。そして、第１曲げ加工部Ｘ１から第２曲げ加工部Ｘ２までの領域Ｙ３に焼なまし処理が施される。 FIG. 5 is a diagram showing a portion of the inner pipe 10 to be annealed. The first bending portion X1 indicated by the thick arrow is the processing portion closest to the end portion 11 among the plurality of bending processing portions to be bent. The second bending portion X2 indicated by the thick arrow is the bending portion closest to the end portion 12 among the plurality of bending portions to be bent. In the annealing step of step S1, the region Y1 from the end 11 to the front of the first bending portion X1 is not annealed, and from the end 12 to the front of the second bending portion X2. No annealing treatment is applied to the region Y2 of. Then, the region Y3 from the first bending portion X1 to the second bending portion X2 is annealed.

再び図４を参照すると、焼なまし工程の実行後、ステップＳ２において、内管１０の両端部、すなわち端部１１及び端部１２の強度を、外管２０が巻き付けられている螺旋構造部１３の強度よりも高くする補強工程が実行される。換言すると、補強工程の実行前に、上述の焼なまし処理が施される。ステップＳ２の補強工程では、図２に示すように、端部１１に配管３０が嵌め合わされ、ロウ付けにより接合され、図３に示すように、端部１２に配管４０が嵌め合わされ、ロウ付けにより接合される。ここで、強度とは、内管１０の内部から液圧がかけられた場合における耐圧強度を言う。その後、螺旋構造部１３に外管２０Ａ、外管２０Ｂ、及び外管２０Ｃが巻き付けられる。 Referring to FIG. 4 again, after the annealing step is executed, in step S2, the strength of both ends of the inner pipe 10, that is, the ends 11 and 12, is adjusted to the strength of the spiral structure portion 13 around which the outer pipe 20 is wound. A reinforcement step is performed that is greater than the strength of. In other words, the above-mentioned annealing treatment is performed before the reinforcement step is executed. In the reinforcement step of step S2, as shown in FIG. 2, the pipe 30 is fitted to the end portion 11 and joined by brazing, and as shown in FIG. 3, the pipe 40 is fitted to the end portion 12 by brazing. Be joined. Here, the strength refers to the pressure resistance strength when hydraulic pressure is applied from the inside of the inner pipe 10. After that, the outer tube 20A, the outer tube 20B, and the outer tube 20C are wound around the spiral structure portion 13.

次いで、ステップＳ３において、外管２０が巻き付けられた内管１０を拡管する拡管工程が実行される。図６は、拡管工程を実行する際の内管の一方の端部を拡大して示す図である。図７は、拡管工程を実行する際の内管の他方の端部を拡大して示す図である。図６及び図７は、図２及び図３と同様、熱交換器１を内管１０の管軸に沿って切断した断面を模式的に示している。図６に示すように、一方の端部１１にポンプ５０を接続し、図７に示すように、他方の端部１２に蓋部材６０を取り付ける。ポンプ５０は例えば液体ポンプである。この状態でポンプ５０を作動させて、内管１０の内部の圧力を上昇させて内管１０を拡管する拡管工程を実行することにより、内管１０は液圧拡管される。 Next, in step S3, a pipe expansion step of expanding the inner pipe 10 around which the outer pipe 20 is wound is executed. FIG. 6 is an enlarged view showing one end of the inner pipe when the pipe expanding step is executed. FIG. 7 is an enlarged view showing the other end of the inner pipe when the pipe expanding step is executed. 6 and 7 schematically show a cross section of the heat exchanger 1 cut along the tube axis of the inner tube 10, as in FIGS. 2 and 3. As shown in FIG. 6, the pump 50 is connected to one end 11, and the lid member 60 is attached to the other end 12 as shown in FIG. The pump 50 is, for example, a liquid pump. By operating the pump 50 in this state to increase the pressure inside the inner pipe 10 and execute the pipe expanding step of expanding the inner pipe 10, the inner pipe 10 is hydraulically expanded.

再び図４を参照すると、拡管工程の実行後、ステップＳ４に進み、螺旋構造部１３において、図５の第１曲げ加工部Ｘ１及び第２曲げ加工部Ｘ２を含む複数の曲げ加工部で、内管１０を９０度に曲げる曲げ工程が実行される。その結果、図１に示す熱交換器１が得られる。 Referring to FIG. 4 again, after the pipe expansion step is executed, the process proceeds to step S4, and in the spiral structure portion 13, a plurality of bending portions including the first bending portion X1 and the second bending portion X2 of FIG. A bending step of bending the tube 10 at 90 degrees is performed. As a result, the heat exchanger 1 shown in FIG. 1 is obtained.

そして、上述の工程で得られた熱交換器１において、内管１０を流通する水と、外管２０Ａ、外管２０Ｂ、及び外管２０Ｃを流れる冷媒とが熱交換することにより、内管１０を流通する水は、その温度が上昇し、湯となる。 Then, in the heat exchanger 1 obtained in the above step, the water flowing through the inner pipe 10 and the refrigerant flowing through the outer pipe 20A, the outer pipe 20B, and the outer pipe 20C exchange heat with each other to exchange heat with the inner pipe 10. The temperature of the water circulating in the water rises and becomes hot water.

上述のように、螺旋構造部１３の螺旋構造は、直管形状の伝熱管を加工することにより形成されており、螺旋構造部１３は加工硬化している。さらに、螺旋構造部１３の外周面には、外管２０Ａ、外管２０Ｂ、及び外管２０Ｃが巻き付けられている。一方、図２に示すように、端部１１の外周面には外管２０は巻き付けられておらず、端部１１は直管のままである。同様に、図３に示すように、端部１２の直管部の外周面には外管２０は巻き付けられておらず、端部１２は直管のままである。従って、内管１０を液圧拡管する際の拡管圧力に対する強度は、端部１１及び端部１２よりも螺旋構造部１３の方が高い。従って、螺旋構造部１３における内管１０と外管２０の接合を十分なものとすべく、内管１０の内部から液圧をかけると、直管部である端部１１及び端部１２は過剰に変形する可能性がある。これに対して、本実施の形態１の内管１０は、先述したように端部１１及び端部１２の強度が補強された構成を有している。 As described above, the spiral structure of the spiral structure portion 13 is formed by processing a straight tube-shaped heat transfer tube, and the spiral structure portion 13 is work-hardened. Further, the outer tube 20A, the outer tube 20B, and the outer tube 20C are wound around the outer peripheral surface of the spiral structure portion 13. On the other hand, as shown in FIG. 2, the outer pipe 20 is not wound around the outer peripheral surface of the end portion 11, and the end portion 11 remains a straight pipe. Similarly, as shown in FIG. 3, the outer pipe 20 is not wound around the outer peripheral surface of the straight pipe portion of the end portion 12, and the end portion 12 remains a straight pipe. Therefore, the strength against the expansion pressure when the inner tube 10 is hydraulically expanded is higher in the spiral structure portion 13 than in the end portion 11 and the end portion 12. Therefore, when hydraulic pressure is applied from the inside of the inner pipe 10 in order to sufficiently join the inner pipe 10 and the outer pipe 20 in the spiral structure portion 13, the end portion 11 and the end portion 12 which are straight pipe portions are excessive. May be transformed into. On the other hand, the inner pipe 10 of the first embodiment has a structure in which the strength of the end portion 11 and the end portion 12 is reinforced as described above.

以上の構成により、外管２０が巻き付けられていない部分である端部１１及び端部１２の強度は、外管２０が巻き付けられている部分である螺旋構造部１３の強度よりも、高くなっている。 With the above configuration, the strength of the end portion 11 and the end portion 12 which is the portion where the outer pipe 20 is not wound becomes higher than the strength of the spiral structure portion 13 which is the portion where the outer pipe 20 is wound. There is.

本実施の形態１によれば、端部１１には端部１１より肉厚の配管３０が接合され、端部１２には端部１２より肉厚の配管４０が接合されており、端部１１及び端部１２は強度が補強されている。従って、内管１０の内部から液圧がかけられた場合でも、液圧により過剰な変形を起こすことを抑制することができる。そのため、内管１０を液圧拡管する際、拡管圧力をより高くすることができ、内管１０の螺旋構造部１３における内管１０と外管２０の密着をより高めることができる。その結果、内管１０と外管２０との熱交換効率がより高められた熱交換器１が得られる。 According to the first embodiment, a pipe 30 thicker than the end 11 is joined to the end 11, and a pipe 40 thicker than the end 12 is joined to the end 12. And the end 12 is reinforced in strength. Therefore, even when the hydraulic pressure is applied from the inside of the inner pipe 10, it is possible to suppress excessive deformation due to the hydraulic pressure. Therefore, when the inner pipe 10 is hydraulically expanded, the expansion pressure can be further increased, and the adhesion between the inner pipe 10 and the outer pipe 20 in the spiral structure portion 13 of the inner pipe 10 can be further enhanced. As a result, the heat exchanger 1 in which the heat exchange efficiency between the inner pipe 10 and the outer pipe 20 is further improved can be obtained.

本実施の形態１では、端部１１よりも肉厚の配管３０を端部１１にロウ付けし、端部１２よりも肉厚の配管４０を端部１２にロウ付けすることにより、端部１１及び端部１２の液圧に対する強度を高めているがこれに限るものではない。強度の高い材料からなる配管を、端部１１及び端部１２に接合してもよい。この場合、配管の調質は、例えば日本工業規格における「Ｈ」以上の強度が望ましい。この場合も、端部１１及び端部１２の強度が補強されているため、上述の効果が得られる。 In the first embodiment, the end portion 11 is formed by brazing the pipe 30 thicker than the end portion 11 to the end portion 11 and brazing the pipe 40 thicker than the end portion 12 to the end portion 12. And the strength of the end portion 12 against hydraulic pressure is increased, but the strength is not limited to this. Piping made of a high-strength material may be joined to the end 11 and the end 12. In this case, it is desirable that the tempering of the piping is, for example, a strength of "H" or higher in the Japanese Industrial Standards. Also in this case, since the strength of the end portion 11 and the end portion 12 is reinforced, the above-mentioned effect can be obtained.

尚、端部１１及び端部１２において、螺旋構造部１３よりも強度の高い二重管構造が構成できるのであれば、配管３０と配管４０の肉厚及び材料は、上述のものに限定されることはない。 If a double pipe structure having a strength higher than that of the spiral structure portion 13 can be formed at the end portion 11 and the end portion 12, the wall thickness and material of the pipe 30 and the pipe 40 are limited to those described above. There is no such thing.

焼なまし処理は、図５に示す領域Ｙ１及び領域Ｙ２には施されておらず、領域Ｙ３に施されている。従って、端部１１及び端部１２の強度を低下させることなく、内管１０を曲げ加工して図１に示すように成形するときの加工性をより良いものとすることができる。 The annealing treatment is not applied to the regions Y1 and Y2 shown in FIG. 5, but is applied to the region Y3. Therefore, the workability when the inner tube 10 is bent and molded as shown in FIG. 1 can be improved without lowering the strength of the end portion 11 and the end portion 12.

尚、直管部である端部１１及び端部１２に焼なまし処理を施さず、螺旋構造部１３に焼なまし処理を施すようにしてもよい。 It should be noted that the end portion 11 and the end portion 12 which are the straight pipe portions may not be annealed, but the spiral structure portion 13 may be annealed.

また、本実施の形態１では、焼なまし処理を端部１１及び端部１２の補強処理の前に実行しているがこれに限るものではない。例えば、端部１１及び端部１２の補強処理の実行後に焼なまし処理を実行してもよい。 Further, in the first embodiment, the annealing treatment is executed before the reinforcement treatment of the end portion 11 and the end portion 12, but the present invention is not limited to this. For example, the annealing treatment may be executed after the reinforcement treatment of the end portion 11 and the end portion 12 is executed.

本実施の形態１では、螺旋構造部１３の外周面に３条の螺旋溝１３Ａ、螺旋溝１３Ｂ、及び螺旋溝１３Ｃが形成されているが、螺旋溝の数はこれに限るものではない。螺旋構造部１３に複数条の螺旋溝が形成され、各螺旋溝に外管が巻き付けられていればよい。 In the first embodiment, three spiral grooves 13A, a spiral groove 13B, and a spiral groove 13C are formed on the outer peripheral surface of the spiral structure portion 13, but the number of spiral grooves is not limited to this. It suffices that a plurality of spiral grooves are formed in the spiral structure portion 13 and an outer tube is wound around each spiral groove.

実施の形態２．
図８は、本発明の実施の形態２に係る熱交換器の内管の一方の端部を拡大して示す図である。図８には内管１００の端部１０１が示されている。図８において、実施の形態１と同様の部材には同一の符号が付されている。内管１００の螺旋構造部１０３は、実施の形態１の内管１０の螺旋構造部１３と同様の構成を有しており、その外周面には、外管２０Ａ、外管２０Ｂ、及び外管２０Ｃが巻き付けられている。内管１００の両端部のうちの一方の端部１０１は直管部であり、縮管加工が施されている。すなわち、端部１０１の外径Ｄ１は、螺旋構造部１０３の外径Ｄ２よりも小さい。端部１０１は、縮管により加工硬化されている。尚、端部１０１において縮管加工を施す範囲は、内管１０が形成する水回路の圧力損失を起こすことがなく、かつ、端部１０１の強度が最も高くなるよう、定められる。内管１００の他方の端部においても、同様に縮管加工が施されており、加工硬化されている。また、実施の形態１と同様、端部１０１の先端部に、ポンプ５０を取り付けるためのフレア部を形成してもよい。その他の構成は、実施の形態１と同様である。Embodiment 2.
FIG. 8 is an enlarged view of one end of the inner tube of the heat exchanger according to the second embodiment of the present invention. FIG. 8 shows the end 101 of the inner tube 100. In FIG. 8, the same members as those in the first embodiment are designated by the same reference numerals. The spiral structure portion 103 of the inner pipe 100 has the same configuration as the spiral structure portion 13 of the inner pipe 10 of the first embodiment, and the outer pipe 20A, the outer pipe 20B, and the outer pipe are on the outer peripheral surface thereof. 20C is wrapped around. One end 101 of both ends of the inner pipe 100 is a straight pipe portion, and is subjected to a reduced pipe processing. That is, the outer diameter D1 of the end portion 101 is smaller than the outer diameter D2 of the spiral structure portion 103. The end 101 is work-hardened by a shrink tube. The range in which the end portion 101 is subjected to the contraction processing is determined so as not to cause a pressure loss in the water circuit formed by the inner pipe 10 and to have the highest strength of the end portion 101. The other end of the inner tube 100 is also work-hardened in the same manner. Further, as in the first embodiment, a flare portion for attaching the pump 50 may be formed at the tip end portion of the end portion 101. Other configurations are the same as those in the first embodiment.

端部１０１及び他方の端部の縮管加工は、上述の実施の形態１における補強工程で実行される。 The shrinkage tube processing of the end portion 101 and the other end portion is performed in the reinforcing step in the above-described first embodiment.

本実施の形態２によれば、内管１００の端部１０１及び他方の端部は、加工硬化されており、強度が補強されている。従って、実施の形態１と同様の効果が得られる。さらに、縮管加工では、端部１０１及び他方の端部は加熱されない。従って、本実施の形態２によれば、端部１０１及び他方の端部において、加熱による強度の低下を回避することができる。 According to the second embodiment, the end 101 of the inner pipe 100 and the other end are work-hardened to reinforce the strength. Therefore, the same effect as that of the first embodiment can be obtained. Further, in the reduced tube processing, the end 101 and the other end are not heated. Therefore, according to the second embodiment, it is possible to avoid a decrease in strength due to heating at the end portion 101 and the other end portion.

１ 熱交換器、１０ 内管、１１ 端部、１２ 端部、１３ 螺旋構造部、１３Ａ 螺旋溝、１３Ｂ 螺旋溝、１３Ｃ 螺旋溝、１３Ｄ 山部、２０ 外管、２０Ａ 外管、２０Ｂ 外管、２０Ｃ 外管、３０ 配管、３１ フレア部、４０ 配管、５０ ポンプ、６０ 蓋部材、１００ 内管、１０１ 端部、１０３ 螺旋構造部、Ｘ１ 第１曲げ加工部、Ｘ２ 第２曲げ加工部、Ｙ１ 領域、Ｙ２ 領域、Ｙ３ 領域。 1 heat exchanger, 10 inner pipe, 11 end, 12 end, 13 spiral structure, 13A spiral groove, 13B spiral groove, 13C spiral groove, 13D mountain part, 20 outer pipe, 20A outer pipe, 20B outer pipe, 20C outer pipe, 30 pipes, 31 flare part, 40 pipes, 50 pumps, 60 lid members, 100 inner pipes, 101 ends, 103 spiral structure parts, X1 first bending part, X2 second bending part, Y1 area , Y2 area, Y3 area.

本発明に係る熱交換器の製造方法は、流体が流通する内管及び外管を備え、前記外管は前記内管の両端部を除く外周面に螺旋状に巻き付けられた状態で前記内管に接合されている熱交換器の製造方法であって、前記内管の一部を焼なましする焼なまし工程と、前記焼なまし工程の実行後に、前記内管の前記両端部の強度を、前記外管が巻き付けられる部分の強度よりも高くする補強工程と、前記外管が巻き付けられている前記内管の内部の圧力を上昇させて前記内管を拡管する拡管工程と、前記拡管工程の実行後に前記内管の複数箇所を曲げ加工し、螺旋状に形成する曲げ工程とを含み、前記焼なまし工程において、前記両端部のうちの一方の端部から、前記曲げ工程で曲げ加工される複数の曲げ加工部のうち前記一方の端部に最も近い第１曲げ加工部の手前までの領域に、焼なまし処理は施されず、前記両端部のうちの他方の端部から、前記曲げ工程で曲げ加工される複数の曲げ加工部のうち前記他方の端部に最も近い第２曲げ加工部の手前までの領域に、焼なまし処理は施されず、前記第１曲げ加工部から前記第２曲げ加工部までの領域に焼なまし処理が施されるものである。 The method for manufacturing a heat exchanger according to the present invention includes an inner pipe and an outer pipe through which fluid flows, and the outer pipe is spirally wound around an outer peripheral surface excluding both ends of the inner pipe. A method for manufacturing a heat exchanger joined to the inner tube , wherein a part of the inner tube is annealed, and after the annealing step is executed, the strength of both ends of the inner tube is increased. and a reinforcing step higher than the strength of the portion where the outer tube is wound, the tube expansion step of pipe expanding the inner pipe by increasing the pressure inside of the inner tube wherein the outer tube is wound, the tube expansion the inner tube is bent a plurality of locations in the after step, seen including a bending process to form spirally in the annealing step, from one end of said end portions, in the bending step The region up to the front of the first bending portion closest to the one end of the plurality of bending portions to be bent is not annealed, and the other end of the both ends is not subjected to the annealing treatment. Therefore, the area up to the front of the second bending portion closest to the other end of the plurality of bending portions to be bent in the bending step is not subjected to the annealing treatment, and the first bending is performed. The region from the processed portion to the second bending portion is annealed .

本発明に係る熱交換器は、流体が流通する内管及び外管を備え、前記外管は、前記内管の両端部を除く外周面に螺旋状に巻き付けられた状態で前記内管に接合されており、前記内管の一部が焼なましされ、前記内管の前記両端部の強度が、前記外管が巻き付けられる部分の強度よりも高くされ、前記外管が巻き付けられている前記内管が拡管され、前記内管の複数箇所が曲げ加工され、螺旋状に形成されている熱交換器において、前記両端部のうちの一方の端部から、曲げ加工されている複数の曲げ加工部のうち前記一方の端部に最も近い第１曲げ加工部の手前までの領域に、焼なまし処理は施されておらず、前記両端部のうちの他方の端部から、曲げ加工されている複数の曲げ加工部のうち前記他方の端部に最も近い第２曲げ加工部の手前までの領域に、焼なまし処理は施されておらず、前記第１曲げ加工部から前記第２曲げ加工部までの領域に焼なまし処理が施されているものである。 The heat exchanger according to the present invention includes an inner pipe and an outer pipe through which fluid flows, and the outer pipe is joined to the inner pipe in a state of being spirally wound around an outer peripheral surface excluding both ends of the inner pipe. The inner tube is partially annealed, the strength of both ends of the inner tube is made higher than the strength of the portion around which the outer tube is wound, and the outer tube is wound. In a heat exchanger in which an inner pipe is expanded and a plurality of parts of the inner pipe are bent to form a spiral shape, a plurality of bending processes are performed from one end of both ends. The region of the portion up to the front of the first bending portion closest to the one end is not annealed, and is bent from the other end of the both ends. The region of the plurality of bending portions up to the front of the second bending portion closest to the other end portion is not annealed, and the first bending portion to the second bending portion are not subjected to the annealing treatment. The area up to the processed part is annealed .

Claims (13)

流体が流通する内管及び外管を備え、前記外管は前記内管の両端部を除く外周面に螺旋状に巻き付けられた状態で前記内管に接合されている熱交換器の製造方法であって、
前記内管の前記両端部の強度を、前記外管が巻き付けられる部分の強度よりも高くする補強工程と、
前記外管が巻き付けられている前記内管の内部の圧力を上昇させて前記内管を拡管する拡管工程とを含む熱交換器の製造方法。A method for manufacturing a heat exchanger, which comprises an inner pipe and an outer pipe through which a fluid flows, and the outer pipe is spirally wound around an outer peripheral surface excluding both ends of the inner pipe and joined to the inner pipe. There,
A reinforcing step of increasing the strength of both ends of the inner pipe to be higher than the strength of the portion around which the outer pipe is wound.
A method for manufacturing a heat exchanger, which comprises a tube expanding step of increasing the pressure inside the inner tube around which the outer tube is wound to expand the inner tube. 前記補強工程は、前記両端部の外径よりも内径が大きい配管を、前記両端部に嵌め合わせて接合する工程を含む請求項１に記載の熱交換器の製造方法。 The method for manufacturing a heat exchanger according to claim 1, wherein the reinforcing step includes a step of fitting and joining a pipe having an inner diameter larger than the outer diameter of both ends to the both ends. 前記配管は、前記両端部よりも肉厚に構成された請求項２に記載の熱交換器の製造方法。 The method for manufacturing a heat exchanger according to claim 2, wherein the pipe is thicker than both ends. 前記配管は、前記両端部よりも強度が高く構成された請求項２に記載の熱交換器の製造方法。 The method for manufacturing a heat exchanger according to claim 2, wherein the piping is configured to have higher strength than both ends. 前記補強工程は、前記内管において、前記両端部の外径が、前記外管が巻き付けられている部分の外径よりも小さくなるよう、前記両端部を縮管加工する工程を含む請求項１に記載の熱交換器の製造方法。 The reinforcing step includes a step of shrinking both ends of the inner pipe so that the outer diameters of both ends thereof are smaller than the outer diameter of the portion around which the outer pipe is wound. The method for manufacturing a heat exchanger described in 1. 前記補強工程の実行前に、前記内管の一部を焼なましする焼なまし工程をさらに含み、
前記焼なまし工程は、前記外管が巻き付けられる部分に焼なまし処理を施す工程を含む請求項１〜５のいずれか一項に記載の熱交換器の製造方法。Further including an annealing step of annealing a part of the inner pipe before executing the reinforcement step.
The method for manufacturing a heat exchanger according to any one of claims 1 to 5, wherein the annealing step includes a step of performing an annealing treatment on a portion around which the outer pipe is wound. 前記補強工程の実行前に、前記内管の一部を焼なましする焼なまし工程をさらに含み、
前記拡管工程の実行後に前記内管の複数箇所を曲げ加工し、螺旋状に形成する曲げ工程をさらに含み、
前記焼なまし工程において、
前記両端部のうちの一方の端部から、前記曲げ工程で曲げ加工される複数の曲げ加工部のうち前記一方の端部に最も近い第１曲げ加工部の手前までの領域に、焼なまし処理は施されず、
前記両端部のうちの他方の端部から、前記曲げ工程で曲げ加工される複数の曲げ加工部のうち前記他方の端部に最も近い第２曲げ加工部の手前までの領域に、焼なまし処理は施されず、
前記第１曲げ加工部から前記第２曲げ加工部までの領域に焼なまし処理が施される請求項１〜５のいずれか一項に記載の熱交換器の製造方法。Further including an annealing step of annealing a part of the inner pipe before executing the reinforcement step.
Further including a bending step of bending a plurality of parts of the inner pipe to form a spiral shape after executing the pipe expanding step.
In the annealing step,
Annealing is performed in the region from one end of both ends to the front of the first bending portion closest to the one end of the plurality of bending portions to be bent in the bending step. No treatment,
Annealing is performed in the region from the other end of both ends to the front of the second bending portion closest to the other end of the plurality of bending portions to be bent in the bending step. No treatment,
The method for manufacturing a heat exchanger according to any one of claims 1 to 5, wherein the region from the first bending portion to the second bending portion is annealed. 流体が流通する内管及び外管を備え、
前記外管は、前記内管の両端部を除く外周面に螺旋状に巻き付けられた状態で前記内管に接合されており、
前記内管において、前記外管が巻き付けられていない前記両端部の強度は、前記外管が巻き付けられている部分の強度よりも高く構成されている熱交換器。Equipped with an inner pipe and an outer pipe through which fluid flows
The outer pipe is joined to the inner pipe in a state of being spirally wound around the outer peripheral surface excluding both ends of the inner pipe.
A heat exchanger in which the strength of both ends of the inner pipe to which the outer pipe is not wound is higher than the strength of the portion to which the outer pipe is wound. 前記両端部に、前記両端部の外径よりも内径が大きい配管が、前記配管の内周面が前記両端部の外周面に接触した状態で接合されている請求項８に記載の熱交換器。 The heat exchanger according to claim 8, wherein a pipe having an inner diameter larger than the outer diameter of both ends is joined to both ends of the pipe in a state where the inner peripheral surface of the pipe is in contact with the outer peripheral surfaces of both ends. .. 前記配管は、前記両端部よりも肉厚に構成されている請求項９に記載の熱交換器。 The heat exchanger according to claim 9, wherein the pipe is thicker than both ends. 前記配管は、前記両端部よりも強度が高く構成されている請求項９に記載の熱交換器。 The heat exchanger according to claim 9, wherein the piping is configured to have higher strength than both ends. 前記両端部の外径は、前記外管が巻き付けられている部分の外径よりも小さい請求項８に記載の熱交換器。 The heat exchanger according to claim 8, wherein the outer diameters of both ends are smaller than the outer diameter of the portion around which the outer tube is wound. 前記内管は、前記両端部の間に位置し外周面に複数条の螺旋溝が形成されている螺旋構造部を有し、
前記外管は、前記螺旋溝に巻き付けられている請求項８〜１２のいずれか一項に記載の熱交換器。The inner pipe has a spiral structure portion located between both end portions and having a plurality of spiral grooves formed on the outer peripheral surface.
The heat exchanger according to any one of claims 8 to 12, wherein the outer tube is wound around the spiral groove.
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