WO2012172928A1 - Serpentine heat exchanger - Google Patents

Serpentine heat exchanger Download PDF

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Publication number
WO2012172928A1
WO2012172928A1 PCT/JP2012/062900 JP2012062900W WO2012172928A1 WO 2012172928 A1 WO2012172928 A1 WO 2012172928A1 JP 2012062900 W JP2012062900 W JP 2012062900W WO 2012172928 A1 WO2012172928 A1 WO 2012172928A1
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WO
WIPO (PCT)
Prior art keywords
tube
heat exchanger
serpentine heat
folded
serpentine
Prior art date
Application number
PCT/JP2012/062900
Other languages
French (fr)
Japanese (ja)
Inventor
由和 高松
中村　将之
Original Assignee
カルソニックカンセイ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by カルソニックカンセイ株式会社 filed Critical カルソニックカンセイ株式会社
Priority to EP12800204.5A priority Critical patent/EP2722628A4/en
Priority to US14/124,345 priority patent/US20140116662A1/en
Priority to CN201280029492.6A priority patent/CN103608636A/en
Publication of WO2012172928A1 publication Critical patent/WO2012172928A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F28D1/0478—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0358—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 plate-like or laminated conduits the conduits being formed by bent plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/04—Reinforcing means for 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
    • F28F2275/00—Fastening; Joining
    • F28F2275/12—Fastening; Joining by methods involving deformation of the elements
    • F28F2275/122—Fastening; Joining by methods involving deformation of the elements by crimping, caulking or clinching

Definitions

  • the present invention relates to a serpentine heat exchanger.
  • a serpentine heat exchanger disclosed in JP2001-27484A is known as a heat exchanger used as an evaporator or a condenser of a vehicle air conditioner.
  • the serpentine heat exchanger has a configuration in which a tube in which a medium passage is formed is folded back into a serpentine shape and fins are arranged in a space sandwiched between the folded tubes.
  • the serpentine heat exchanger has an advantage that heat exchangers of various sizes, that is, various capacities can be manufactured by changing the length of the tube and the position / number of times of bending.
  • the tube is thinned to reduce the radius of curvature of the bent portion, the space inside the bent portion where fins cannot be placed is reduced, and as many fins as possible. Need to be placed.
  • the tube used for the serpentine heat exchanger is formed by extrusion, it is difficult to reduce the thickness.
  • the medium passage formed in the tube is a plurality of parallel passages as shown in FIG.
  • a medium flowing in a certain passage is not mixed with a medium flowing in another passage. Therefore, a temperature difference occurs between the passages, and it is difficult to increase the efficiency of the heat exchanger.
  • the present invention has been made in view of such a technical problem, and an object thereof is to realize miniaturization and high efficiency in a serpentine heat exchanger.
  • a serpentine heat exchanger is configured by bonding two press-formed tube sheets, and is sandwiched between a tube folded in a serpentine shape and the folded tube Fins disposed in the space, and a plurality of convex portions protruding from one tube sheet and contacting the other tube sheet are formed in the folded portion of the tube at intervals.
  • An exchanger is provided.
  • a serpentine-like tube is configured by stacking press-formed tube sheets and turning them back. Since the thickness of the tube can be made thinner than that of a tube manufactured by extrusion molding, the radius of curvature of the bent portion can be reduced. Thereby, the space inside the bent portion where fins cannot be installed can be reduced, and more fins can be arranged to achieve downsizing and higher efficiency of the heat exchanger.
  • the efficiency of the heat exchanger can also be improved.
  • FIG. 1 is an overall configuration diagram of a serpentine heat exchanger according to a first embodiment of the present invention.
  • FIG. 2A is a view in which the tube is cut in the short direction at the folded portion.
  • FIG. 2B is a diagram in which the tube is cut in the short direction at the straight portion.
  • FIG. 2C is a view in which the folded portion and the straight portion of the tube are cut in the longitudinal direction.
  • FIG. 3 is a cross-sectional view of the tube.
  • FIG. 4A is a diagram illustrating a manufacturing method.
  • FIG. 4B is a diagram illustrating the manufacturing method.
  • FIG. 4C is a diagram illustrating the manufacturing method.
  • FIG. 4D is a diagram illustrating the manufacturing method.
  • FIG. 4E is a diagram illustrating a manufacturing method.
  • FIG. 4A is a diagram illustrating a manufacturing method.
  • FIG. 4B is a diagram illustrating the manufacturing method.
  • FIG. 4C is a diagram illustrating the manufacturing method.
  • FIG. 4F is a diagram for explaining the manufacturing method.
  • FIG. 4G is a diagram illustrating a manufacturing method.
  • FIG. 4H is a diagram for explaining the manufacturing method.
  • FIG. 5 is a cross-sectional view of a tube according to a second embodiment of the present invention.
  • FIG. 6 is a cross-sectional view of a conventional tube.
  • FIG. 1 is an overall configuration diagram of a serpentine heat exchanger (hereinafter referred to as “heat exchanger”) 100 according to a first embodiment of the present invention.
  • the heat exchanger 100 includes a tube 1, a corrugated fin 2, an inlet adapter 3, an outlet adapter 4, an inlet pipe 5, and an outlet pipe 6.
  • the tube 1 includes a tube sheet 11 (see FIG. 4A) in which a concave groove 7 and a plurality of frustoconical convex portions 8 (see FIGS. 2A to 2C and 3) projecting into the concave groove 7 are formed by press molding. Are overlapped and folded back into a serpentine shape.
  • the folded portion of the tube 1 is expressed as a “folded portion”, and the unfolded portion is expressed as a “straight line portion”.
  • FIG. 2A to 2C are diagrams in which the tube 1 is cut in the short direction at the folded portion, the tube 1 is cut in the short direction at the straight portion, and the folded portion and the straight portion of the tube 1 are cut in the longitudinal direction.
  • FIG. FIG. 3 is a cross-sectional view of the tube 1.
  • the convex portion 8 of one tube sheet 11 is brought into contact with the convex portion 8 of the other tube sheet 11 to form a column extending in the thickness direction of the tube 1 inside the tube 1. .
  • the convex portions 8 are formed at intervals in the surface direction of the tube sheet 11 (the flow direction of the medium and the direction perpendicular thereto), reinforce the linear portion, and the tube 1 is crushed at the folded portion to reduce the passage cross-sectional area. To prevent becoming.
  • the convex portions 8 are arranged in a staggered manner and do not block the passage of the medium.
  • the tab 12 of the tube sheet 11 is folded in the folded direction of the tube 1, and the tube sheets 11 are caulked.
  • the corrugated fin 2 is a fin configured by bending a metal plate into a wave shape.
  • the corrugated fins 2 are respectively arranged in a plurality of U-shaped spaces formed by the folded tube 1, and the upper end and the lower end are in contact with the tube 1.
  • the inlet adapter 3 and the inlet pipe 5 are connected to one end of the tube 1.
  • the outlet adapter 4 and the outlet pipe 6 are connected to the other end of the tube 1.
  • the heat exchanger 100 according to the first embodiment is configured as described above, and the medium flowing into the inlet adapter 3 from the inlet pipe 5 flows through the meandering tube 1 from the lower side to the upper side in the figure. Thus, heat exchange with the air passing through the corrugated fins 2 is performed. The medium after the heat exchange is sent to the outlet adapter 4 and discharged from the outlet pipe 6.
  • the tube sheet 11 is manufactured by press working (FIG. 4A).
  • the tube sheet 11 has a concave groove 7 extending in the longitudinal direction at the center, and a plurality of convex portions 8 project from the bottom of the concave groove 7 at intervals in the surface direction of the tube sheet 11.
  • the height of the convex portion 8 is equal to the depth of the concave groove 7.
  • tabs 12 are formed on both sides of the portion to be the folded portion.
  • the tube sheet 11 is crimped by bending the tab 12 (FIG. 4C).
  • the direction in which the tab 12 is bent is the same as the direction in which the tube 1 is folded.
  • the tube 1 is folded at a plurality of locations to form a serpentine shape (FIG. 4D).
  • the folding is performed by applying a force to both sides of the part while bringing the jig into contact with the part to be folded back. Since the tube sheets 11 are caulked by the tabs 12 in the portion, the two tube sheets 11 are kept in close contact even after being folded back, and no gap is formed on the side surface of the tube 1.
  • the inlet adapter 3 is connected to one end of the tube 1, and the outlet adapter 4 is connected to the other end (FIG. 4E).
  • Each of the inlet adapter 3 and the outlet adapter 4 has a cylindrical shape, and has an opening to which the inlet pipe 5 or the outlet pipe 6 is connected at the end face, and a slit-like opening to which the end of the tube 1 is connected to the side face. .
  • the corrugated fins 2 are inserted and arranged in the space between the folded tubes 1 (FIG. 4F).
  • the inlet pipe 5 is connected to the inlet adapter 3, and the outlet pipe 6 is connected to the outlet adapter 4 (FIG. 4G).
  • the serpentine-like tube 1 is configured by stacking the press-formed tube sheets 11 and folding them back at a plurality of locations. Since the wall thickness of the tube 1 can be made thinner than that of a tube manufactured by extrusion, the radius of curvature of the bent portion can be reduced. Thereby, the space inside a bending part which cannot install corrugated fin 2 can be made small, and more corrugated fins 2 can be arranged and size reduction and high efficiency of heat exchanger 100 can be realized.
  • the tube 1 when the thickness of the tube 1 is reduced, the tube 1 may be crushed at the bent portion.
  • a column is formed inside the tube 1 by the convex portion 8 protruding from the tube sheet 11. The tube 1 is not crushed at the bent portion and the passage cross-sectional area is not reduced.
  • the efficiency of the heat exchanger 100 can also be improved.
  • the tube sheets 11 are crimped by the tabs 12 in the folded portion, the tube sheet 11 and the tube sheet 11 are not separated when the tube 1 is folded, and the side surface of the tube 1 It is possible to prevent a gap from being generated.
  • the shape of the convex portion 8 formed on the tube sheet 11 is a truncated cone shape, it is possible to ensure the ease of bending at the bent portion while ensuring the strength of the tube 1 at the straight portion.
  • the second embodiment is different from the first embodiment in the method of forming columns formed inside the tube 1.
  • the convex part 8 was formed in both the two tube sheets 11 which comprise the tube 1, and the pillar was formed by attaching these together, in 2nd Embodiment, the convex part 8 is formed. Only one tube sheet 11 is formed, and the other tube sheet 11 is not formed. In 2nd Embodiment, a pillar is formed in the inside of the tube 1 by attaching the convex part 8 formed in one tube sheet 11 to the flat surface of the other tube sheet 11.
  • FIG. 5 is a cross-sectional view of the tube 1 of the second embodiment.
  • the convex portion 8 is formed only on one tube sheet 11 and is not formed on the other tube sheet 11. With such a configuration, a column may be formed inside the tube 1. According to this configuration, the alignment of the convex portion 8 is unnecessary, and the manufacturing process can be simplified.
  • the convex portion 8 is formed on the entire tube 2, but the convex portion 8 may be provided at least in the bent portion. If the strength of the straight portion can be ensured without the convex portion 8, the convex portion 8 of the straight portion is not necessary.
  • the shape of the convex portion 8 is not a truncated cone shape, but may be a cylindrical shape or a prism shape (triangular prism shape, quadrangular prism shape, etc.).

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

Abstract

This serpentine heat exchanger comprises a tube folded into a serpentine shape and configured by bonding together two press-molded tube sheets, and corrugated fins arranged in spaces enclosed by the folded tube. A plurality of convex parts that protrude from one of the tube sheets to make contact with the other tube sheet are formed with intervals therebetween on the inside of the folded part of the tube.

Description

サーペンタイン熱交換器Serpentine heat exchanger
　本発明は、サーペンタイン熱交換器に関する。 The present invention relates to a serpentine heat exchanger.
　車両用空調装置のエバポレータ又はコンデンサとして利用される熱交換器として、ＪＰ２００１－２７４８４Ａに開示されるサーペンタイン熱交換器が知られている。 A serpentine heat exchanger disclosed in JP2001-27484A is known as a heat exchanger used as an evaporator or a condenser of a vehicle air conditioner.
　サーペンタイン熱交換器は、内部に媒体の通路が形成されたチューブをサーペンタイン（蛇行）状に折り返し、折り返されたチューブで挟まれた空間にフィンを配置した構成である。 The serpentine heat exchanger has a configuration in which a tube in which a medium passage is formed is folded back into a serpentine shape and fins are arranged in a space sandwiched between the folded tubes.
　サーペンタイン熱交換器は、チューブの長さ、折り曲げる位置・回数を変更することで、様々な大きさ、すなわち、様々な容量の熱交換器を製造することができるという利点がある。 The serpentine heat exchanger has an advantage that heat exchangers of various sizes, that is, various capacities can be manufactured by changing the length of the tube and the position / number of times of bending.
　サーペンタイン熱交換器において小型化及び高効率化を実現するためには、チューブを薄肉化して折り曲げ部の曲率半径を小さくし、フィンを配置できない折り曲げ部内側の空間を小さくして、なるべく多くのフィンを配置する必要がある。 In order to achieve miniaturization and high efficiency in the serpentine heat exchanger, the tube is thinned to reduce the radius of curvature of the bent portion, the space inside the bent portion where fins cannot be placed is reduced, and as many fins as possible. Need to be placed.
　しかしながら、サーペンタイン熱交換器に用いられるチューブは、押し出し成形によって成形されるので、薄肉化が難しかった。 However, since the tube used for the serpentine heat exchanger is formed by extrusion, it is difficult to reduce the thickness.
　また、チューブに形成される媒体の通路は、図６に示すように、平行な複数の通路となる。このような流路構成では、ある通路を流れる媒体が他の通路を流れる媒体と混じることがないので、通路間で温度差が生じ、熱交換器の高効率化が難しかった。 Further, the medium passage formed in the tube is a plurality of parallel passages as shown in FIG. In such a flow path configuration, a medium flowing in a certain passage is not mixed with a medium flowing in another passage. Therefore, a temperature difference occurs between the passages, and it is difficult to increase the efficiency of the heat exchanger.
　本発明は、このような技術的課題に鑑みてなされたもので、サーペンタイン熱交換器において、小型化及び高効率化を実現することを目的とする。 The present invention has been made in view of such a technical problem, and an object thereof is to realize miniaturization and high efficiency in a serpentine heat exchanger.
　本発明のある態様によれば、サーペンタイン熱交換器であって、プレス成形された二枚のチューブシートを貼り合わせて構成され、サーペンタイン状に折り返されるチューブと、前記折り返されたチューブによって挟まれた空間に配置されるフィンと、を備え、前記チューブの折り返し部の内部には、一方のチューブシートから突出し、他方のチューブシートに当接する複数の凸部が間隔をおいて形成される、サーペンタイン熱交換器が提供される。 According to an aspect of the present invention, a serpentine heat exchanger is configured by bonding two press-formed tube sheets, and is sandwiched between a tube folded in a serpentine shape and the folded tube Fins disposed in the space, and a plurality of convex portions protruding from one tube sheet and contacting the other tube sheet are formed in the folded portion of the tube at intervals. An exchanger is provided.
　上記態様によれば、プレス成形されたチューブシートを重ね合わせ、これを折り返すことでサーペンタイン状のチューブが構成される。チューブの肉厚を押し出し成形によって製造されるチューブに比べて薄くできるので、折り曲げ部の曲率半径を小さくすることができる。これにより、フィンを設置できない折り曲げ部内側の空間を小さくすることができ、より多くのフィンを配置して熱交換器の小型化及び高効率化を実現することができる。 According to the above aspect, a serpentine-like tube is configured by stacking press-formed tube sheets and turning them back. Since the thickness of the tube can be made thinner than that of a tube manufactured by extrusion molding, the radius of curvature of the bent portion can be reduced. Thereby, the space inside the bent portion where fins cannot be installed can be reduced, and more fins can be arranged to achieve downsizing and higher efficiency of the heat exchanger.
　また、チューブ内を流れる媒体は、凸部間の隙間を介して絶えず混合されながら流れるので、これによっても熱交換器の高効率化が実現される。 Also, since the medium flowing in the tube flows while being constantly mixed through the gaps between the convex portions, the efficiency of the heat exchanger can also be improved.
図１は、本発明の第１実施形態に係るサーペンタイン熱交換器の全体構成図である。FIG. 1 is an overall configuration diagram of a serpentine heat exchanger according to a first embodiment of the present invention. 図２Ａは、チューブを折り返し部で短手方向にカットした図である。FIG. 2A is a view in which the tube is cut in the short direction at the folded portion. 図２Ｂは、チューブを直線部で短手方向にカットした図である。FIG. 2B is a diagram in which the tube is cut in the short direction at the straight portion. 図２Ｃは、チューブの折り返し部及び直線部を長手方向にカットした図である。FIG. 2C is a view in which the folded portion and the straight portion of the tube are cut in the longitudinal direction. 図３は、チューブの断面図である。FIG. 3 is a cross-sectional view of the tube. 図４Ａは、製造方法を説明する図である。FIG. 4A is a diagram illustrating a manufacturing method. 図４Ｂは、製造方法を説明する図である。FIG. 4B is a diagram illustrating the manufacturing method. 図４Ｃは、製造方法を説明する図である。FIG. 4C is a diagram illustrating the manufacturing method. 図４Ｄは、製造方法を説明する図である。FIG. 4D is a diagram illustrating the manufacturing method. 図４Ｅは、製造方法を説明する図である。FIG. 4E is a diagram illustrating a manufacturing method. 図４Ｆは、製造方法を説明する図である。FIG. 4F is a diagram for explaining the manufacturing method. 図４Ｇは、製造方法を説明する図である。FIG. 4G is a diagram illustrating a manufacturing method. 図４Ｈは、製造方法を説明する図である。FIG. 4H is a diagram for explaining the manufacturing method. 図５は、本発明の第２実施形態のチューブの断面図である。FIG. 5 is a cross-sectional view of a tube according to a second embodiment of the present invention. 図６は、従来のチューブの断面図である。FIG. 6 is a cross-sectional view of a conventional tube.
　以下、添付図面を参照しながら本発明の実施形態について説明する。 Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
　＜第１実施形態＞
　図１は、本発明の第１実施形態に係るサーペンタイン熱交換器（以下、「熱交換器」という。）１００の全体構成図である。 <First Embodiment>
FIG. 1 is an overall configuration diagram of a serpentine heat exchanger (hereinafter referred to as “heat exchanger”) 100 according to a first embodiment of the present invention.
　熱交換器１００は、チューブ１と、コルゲートフィン２と、入口アダプタ３と、出口アダプタ４と、入口パイプ５と、出口パイプ６と、を備える。 The heat exchanger 100 includes a tube 1, a corrugated fin 2, an inlet adapter 3, an outlet adapter 4, an inlet pipe 5, and an outlet pipe 6.
　チューブ１は、プレス成形によって凹溝７及び凹溝７内に突出する円錐台形状の複数の凸部８（図２Ａ～図２Ｃ及び図３参照）が形成されたチューブシート１１（図４Ａ参照）を重ね合わせ、サーペンタイン（蛇行）状に折り返すことで構成される。以下の説明では、チューブ１の折り返された部分を「折り返し部」と表現し、折り返されていない部分を「直線部」と表現する。 The tube 1 includes a tube sheet 11 (see FIG. 4A) in which a concave groove 7 and a plurality of frustoconical convex portions 8 (see FIGS. 2A to 2C and 3) projecting into the concave groove 7 are formed by press molding. Are overlapped and folded back into a serpentine shape. In the following description, the folded portion of the tube 1 is expressed as a “folded portion”, and the unfolded portion is expressed as a “straight line portion”.
　図２Ａから図２Ｃは、それぞれ、チューブ１を折り返し部で短手方向にカットした図、チューブ１を直線部で短手方向にカットした図、チューブ１の折り返し部及び直線部を長手方向にカットした図である。図３はチューブ１の断面図である。 2A to 2C are diagrams in which the tube 1 is cut in the short direction at the folded portion, the tube 1 is cut in the short direction at the straight portion, and the folded portion and the straight portion of the tube 1 are cut in the longitudinal direction. FIG. FIG. 3 is a cross-sectional view of the tube 1.
　これらの図に示されるように、一方のチューブシート１１の凸部８は、他方のチューブシート１１の凸部８と付き合わされ、チューブ１の内部にチューブ１の厚さ方向に延びる柱を形成する。凸部８は、チューブシート１１の面方向（媒体の流れ方向及びそれに直交する方向）に間隔をおいて形成され、直線部を補強するとともに、チューブ１が折り返し部において潰れて通路断面積が小さくなるのを防止する。凸部８は千鳥に配置され、媒体の通路を閉塞することはない。 As shown in these drawings, the convex portion 8 of one tube sheet 11 is brought into contact with the convex portion 8 of the other tube sheet 11 to form a column extending in the thickness direction of the tube 1 inside the tube 1. . The convex portions 8 are formed at intervals in the surface direction of the tube sheet 11 (the flow direction of the medium and the direction perpendicular thereto), reinforce the linear portion, and the tube 1 is crushed at the folded portion to reduce the passage cross-sectional area. To prevent becoming. The convex portions 8 are arranged in a staggered manner and do not block the passage of the medium.
　チューブ１の折り返し部においては、チューブシート１１のタブ１２がチューブ１の折り返し方向に折り曲げられて、チューブシート１１同士がかしめ加工されている。 In the folded part of the tube 1, the tab 12 of the tube sheet 11 is folded in the folded direction of the tube 1, and the tube sheets 11 are caulked.
　コルゲートフィン２は、金属板を波状に折り曲げて構成されるフィンである。コルゲートフィン２は、折り返されたチューブ１によって形成される複数のＵ字状の空間にそれぞれ配置され、上端及び下端がチューブ１に接触する。 The corrugated fin 2 is a fin configured by bending a metal plate into a wave shape. The corrugated fins 2 are respectively arranged in a plurality of U-shaped spaces formed by the folded tube 1, and the upper end and the lower end are in contact with the tube 1.
　入口アダプタ３及び入口パイプ５はチューブ１の一方の端部に接続される。出口アダプタ４及び出口パイプ６はチューブ１の他方の端部に接続される。 The inlet adapter 3 and the inlet pipe 5 are connected to one end of the tube 1. The outlet adapter 4 and the outlet pipe 6 are connected to the other end of the tube 1.
　第１実施形態に係る熱交換器１００は以上のように構成され、入口パイプ５から入口アダプタ３に流入する媒体は、蛇行するチューブ１内を通って図中下側から上側に流れ、その過程で、コルゲートフィン２を通過する空気と熱交換を行う。熱交換後の媒体は出口アダプタ４へと送られ、出口パイプ６から排出される。 The heat exchanger 100 according to the first embodiment is configured as described above, and the medium flowing into the inlet adapter 3 from the inlet pipe 5 flows through the meandering tube 1 from the lower side to the upper side in the figure. Thus, heat exchange with the air passing through the corrugated fins 2 is performed. The medium after the heat exchange is sent to the outlet adapter 4 and discharged from the outlet pipe 6.
　続いて、図４Ａ～図４Ｈを参照しながら、第１実施形態に係る熱交換器１００の製造方法について説明する。 Subsequently, a method of manufacturing the heat exchanger 100 according to the first embodiment will be described with reference to FIGS. 4A to 4H.
　まず、チューブシート１１をプレス加工によって製造する（図４Ａ）。チューブシート１１は、長手方向に延びる凹溝７を中央に有し、凹溝７の底部からは複数の凸部８がチューブシート１１の面方向に間隔をおいて突出する。凸部８の高さは凹溝７の深さに等しい。また、折り返し部となる部位の両側にはタブ１２が形成される。 First, the tube sheet 11 is manufactured by press working (FIG. 4A). The tube sheet 11 has a concave groove 7 extending in the longitudinal direction at the center, and a plurality of convex portions 8 project from the bottom of the concave groove 7 at intervals in the surface direction of the tube sheet 11. The height of the convex portion 8 is equal to the depth of the concave groove 7. Further, tabs 12 are formed on both sides of the portion to be the folded portion.
　次に、チューブシート１１を二枚用意し、凹溝７が内側になるようにこれらを重ね合わせ、チューブ１に構成する（図４Ｂ）。このとき、一方のチューブシート１１の凸部８及びタブ１２の位置が他方のチューブシート１１の凸部８及びタブ１２の位置と一致するように、二枚のチューブシート１１の位置が合わされる。凹溝７が重ね合わされることによって、チューブ１の内部に媒体の通路が形成され、また、凸部８が付き合わされることによって、チューブ１の内部に厚さ方向に延びる柱が形成される。 Next, two tube sheets 11 are prepared, and they are overlapped so that the concave groove 7 is on the inner side to form the tube 1 (FIG. 4B). At this time, the positions of the two tube sheets 11 are aligned so that the positions of the convex portions 8 and tabs 12 of one tube sheet 11 coincide with the positions of the convex portions 8 and tabs 12 of the other tube sheet 11. When the concave grooves 7 are overlapped, a medium passage is formed inside the tube 1, and a protrusion extending in the thickness direction is formed inside the tube 1 by attaching the convex portions 8 together.
　次に、タブ１２を折り曲げてチューブシート１１同士をかしめ加工する（図４Ｃ）。タブ１２を折り曲げる方向は、チューブ１が折り返される方向と同一である。 Next, the tube sheet 11 is crimped by bending the tab 12 (FIG. 4C). The direction in which the tab 12 is bent is the same as the direction in which the tube 1 is folded.
　次に、チューブ１を複数箇所で折り返し、サーペンタイン形状にする（図４Ｄ）。折り返しは、治具を折り返す部位に当接させながら、当該部位の両側に力を掛けることによって行われる。当該部位においては、タブ１２によってチューブシート１１同士がかしめ加工されているので、折り返された後でも二枚のチューブシート１１は密着状態を維持し、チューブ１の側面に隙間が生じることはない。 Next, the tube 1 is folded at a plurality of locations to form a serpentine shape (FIG. 4D). The folding is performed by applying a force to both sides of the part while bringing the jig into contact with the part to be folded back. Since the tube sheets 11 are caulked by the tabs 12 in the portion, the two tube sheets 11 are kept in close contact even after being folded back, and no gap is formed on the side surface of the tube 1.
　次に、チューブ１の一方の端部に入口アダプタ３を接続し、他方の端部に出口アダプタ４を接続する（図４Ｅ）。入口アダプタ３及び出口アダプタ４は、いずれも円筒形状であり、端面に入口パイプ５又は出口パイプ６が接続される開口を有し、側面にチューブ１の端部が接続されるスリット状開口を有する。 Next, the inlet adapter 3 is connected to one end of the tube 1, and the outlet adapter 4 is connected to the other end (FIG. 4E). Each of the inlet adapter 3 and the outlet adapter 4 has a cylindrical shape, and has an opening to which the inlet pipe 5 or the outlet pipe 6 is connected at the end face, and a slit-like opening to which the end of the tube 1 is connected to the side face. .
　次に、折り返されたチューブ１の間の空間に、コルゲートフィン２を挿入し、配置する（図４Ｆ）。 Next, the corrugated fins 2 are inserted and arranged in the space between the folded tubes 1 (FIG. 4F).
　次に、入口アダプタ３に入口パイプ５を接続し、出口アダプタ４に出口パイプ６を接続する（図４Ｇ）。 Next, the inlet pipe 5 is connected to the inlet adapter 3, and the outlet pipe 6 is connected to the outlet adapter 4 (FIG. 4G).
　最後に、全体が炉の中に配置され、各部品をロウ付けによって結合する（図４Ｈ）。 Finally, the whole is placed in the furnace and the parts are joined by brazing (FIG. 4H).
　続いて、第１実施形態の作用効果について説明する。 Subsequently, the function and effect of the first embodiment will be described.
　第１実施形態によれば、プレス成形されたチューブシート１１を重ね合わせ、これを複数箇所で折り返すことでサーペンタイン状のチューブ１が構成される。チューブ１の肉厚を押し出し成形によって製造されるチューブに比べて薄くできるので、折り曲げ部の曲率半径を小さくすることができる。これにより、コルゲートフィン２を設置できない折り曲げ部内側の空間を小さくすることができ、より多くのコルゲートフィン２を配置して熱交換器１００の小型化及び高効率化を実現することができる。 According to the first embodiment, the serpentine-like tube 1 is configured by stacking the press-formed tube sheets 11 and folding them back at a plurality of locations. Since the wall thickness of the tube 1 can be made thinner than that of a tube manufactured by extrusion, the radius of curvature of the bent portion can be reduced. Thereby, the space inside a bending part which cannot install corrugated fin 2 can be made small, and more corrugated fins 2 can be arranged and size reduction and high efficiency of heat exchanger 100 can be realized.
　また、チューブ１の肉厚が薄くなると、折り曲げ部においてチューブ１が潰れる可能性があるが、第１実施形態ではチューブシート１１から突出する凸部８によってチューブ１の内部に柱が形成されるので、チューブ１が折り曲げ部において潰れて通路断面積が小さくなることもない。 Moreover, when the thickness of the tube 1 is reduced, the tube 1 may be crushed at the bent portion. However, in the first embodiment, a column is formed inside the tube 1 by the convex portion 8 protruding from the tube sheet 11. The tube 1 is not crushed at the bent portion and the passage cross-sectional area is not reduced.
　また、チューブ１内を流れる媒体は、凸部８（柱）間の隙間を介して絶えず混合されながら流れるので、これによっても熱交換器１００の高効率化が実現される。 Further, since the medium flowing in the tube 1 flows while being constantly mixed through the gaps between the convex portions 8 (columns), the efficiency of the heat exchanger 100 can also be improved.
　また、折り返し部においては、タブ１２によってチューブシート１１同士をかしめ加工するようにしたので、チューブ１を折り返す際に、チューブシート１１とチューブシート１１とが離れてしまうことはなく、チューブ１の側面に隙間が生じるのを防止することができる。 Further, since the tube sheets 11 are crimped by the tabs 12 in the folded portion, the tube sheet 11 and the tube sheet 11 are not separated when the tube 1 is folded, and the side surface of the tube 1 It is possible to prevent a gap from being generated.
　また、チューブシート１１に形成した凸部８の形状を円錐台形状にしたので、直線部におけるチューブ１の強度を確保しつつ、折り曲げ部における折り曲げやすさを確保することができる。 Moreover, since the shape of the convex portion 8 formed on the tube sheet 11 is a truncated cone shape, it is possible to ensure the ease of bending at the bent portion while ensuring the strength of the tube 1 at the straight portion.
　＜第２実施形態＞
　第２実施形態は、チューブ１の内部に形成される柱の形成方法が第１実施形態と異なる。 Second Embodiment
The second embodiment is different from the first embodiment in the method of forming columns formed inside the tube 1.
　第１実施形態では、チューブ１を構成する二枚のチューブシート１１の両方に凸部８を形成し、これらを付き合わせることで柱を形成したが、第２実施形態では、凸部８が形成されるのは一方のチューブシート１１のみで、他方のチューブシート１１には形成されない。第２実施形態では、一方のチューブシート１１に形成される凸部８を他方のチューブシート１１の平坦面に付き合わせることで、チューブ１の内部に柱が形成される。 In 1st Embodiment, although the convex part 8 was formed in both the two tube sheets 11 which comprise the tube 1, and the pillar was formed by attaching these together, in 2nd Embodiment, the convex part 8 is formed. Only one tube sheet 11 is formed, and the other tube sheet 11 is not formed. In 2nd Embodiment, a pillar is formed in the inside of the tube 1 by attaching the convex part 8 formed in one tube sheet 11 to the flat surface of the other tube sheet 11.
　図５は、第２実施形態のチューブ１の断面図である。凸部８が形成されるのは一方のチューブシート１１のみであり、他方のチューブシート１１には形成されない。このような構成で、チューブ１の内部に柱を形成するようにしてもよい。この構成によれば、凸部８の位置合わせが不要であり、製造工程を簡略化することが可能である。 FIG. 5 is a cross-sectional view of the tube 1 of the second embodiment. The convex portion 8 is formed only on one tube sheet 11 and is not formed on the other tube sheet 11. With such a configuration, a column may be formed inside the tube 1. According to this configuration, the alignment of the convex portion 8 is unnecessary, and the manufacturing process can be simplified.
　その他の構成は第１実施形態と同じであるので、説明を省略する。 Other configurations are the same as those in the first embodiment, and thus description thereof is omitted.
　以上、本発明の実施形態について説明したが、上記実施形態は本発明の適用例を示したものであり、本発明の技術的範囲を上記実施形態の具体的構成に限定する趣旨ではない。 The embodiment of the present invention has been described above, but the above embodiment shows an application example of the present invention, and is not intended to limit the technical scope of the present invention to the specific configuration of the above embodiment.
　例えば、上記実施形態では、チューブ２の全体に凸部８を形成しているが、凸部８は少なくとも折り曲げ部に設けられていればよい。凸部８がなくても直線部の強度を確保できる場合は、直線部の凸部８は不要である。 For example, in the above embodiment, the convex portion 8 is formed on the entire tube 2, but the convex portion 8 may be provided at least in the bent portion. If the strength of the straight portion can be ensured without the convex portion 8, the convex portion 8 of the straight portion is not necessary.
　また、凸部８の形状は円錐台形状ではなく、円柱形状、角柱形状（三角柱形状、四角柱形状等）であってもよい。 Further, the shape of the convex portion 8 is not a truncated cone shape, but may be a cylindrical shape or a prism shape (triangular prism shape, quadrangular prism shape, etc.).
　本願は2011年6月17日に日本国特許庁に出願された特願2011-135178に基づく優先権を主張し、この出願の全ての内容は参照により本明細書に組み込まれる。 This application claims priority based on Japanese Patent Application No. 2011-135178 filed with the Japan Patent Office on June 17, 2011, the entire contents of which are incorporated herein by reference.

Claims (7)

  1. 　サーペンタイン熱交換器であって、
    　プレス成形された二枚のチューブシートを貼り合わせて構成され、サーペンタイン状に折り返されるチューブと、
    　前記折り返されたチューブによって挟まれた空間に配置されるフィンと、
    を備え、
    　前記チューブの折り返し部の内部には、一方のチューブシートから突出し、他方のチューブシートに当接する複数の凸部が間隔をおいて形成される、
    サーペンタイン熱交換器。     A serpentine heat exchanger,
    A tube that is composed of two press-formed tube sheets bonded together and folded back into a serpentine shape,
    A fin disposed in a space sandwiched between the folded tubes;
    With
    Inside the folded portion of the tube, a plurality of convex portions that protrude from one tube sheet and come into contact with the other tube sheet are formed at intervals.
    Serpentine heat exchanger.
  2. 　請求項１に記載のサーペンタイン熱交換器であって、
    　前記チューブの直線部の内部にも前記凸部が形成される、
    サーペンタイン熱交換器。     The serpentine heat exchanger according to claim 1,
    The convex portion is also formed inside the straight portion of the tube.
    Serpentine heat exchanger.
  3. 　請求項１に記載のサーペンタイン熱交換器であって、
    　前記凸部は、前記他方のチューブシートから突出する別の凸部と付き合わされる、
    サーペンタイン熱交換器。     The serpentine heat exchanger according to claim 1,
    The convex portion is associated with another convex portion protruding from the other tube sheet.
    Serpentine heat exchanger.
  4. 　請求項１に記載のサーペンタイン熱交換器であって、
    　前記凸部は、前記一方のチューブシートにのみ形成される、
    サーペンタイン熱交換器。     The serpentine heat exchanger according to claim 1,
    The convex portion is formed only on the one tube sheet.
    Serpentine heat exchanger.
  5. 　請求項１に記載のサーペンタイン熱交換器であって、
    　前記凸部は、千鳥に配置される、
    サーペンタイン熱交換器。     The serpentine heat exchanger according to claim 1,
    The convex portions are arranged in a staggered manner,
    Serpentine heat exchanger.
  6. 　請求項１に記載のサーペンタイン熱交換器であって、
    　前記凸部は、円錐台形状、円柱形状又は角柱形状である、
    サーペンタイン熱交換器。     The serpentine heat exchanger according to claim 1,
    The convex portion has a truncated cone shape, a cylindrical shape or a prismatic shape,
    Serpentine heat exchanger.
  7. 　請求項１に記載のサーペンタイン熱交換器であって、
    　前記チューブの前記折り返し部において、前記一方のチューブシートと前記他方のチューブシートとが両側においてかしめ加工される、
    サーペンタイン熱交換器。
          The serpentine heat exchanger according to claim 1,
    In the folded portion of the tube, the one tube sheet and the other tube sheet are caulked on both sides,
    Serpentine heat exchanger.
PCT/JP2012/062900 2011-06-17 2012-05-21 Serpentine heat exchanger WO2012172928A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP12800204.5A EP2722628A4 (en) 2011-06-17 2012-05-21 Serpentine heat exchanger
US14/124,345 US20140116662A1 (en) 2011-06-17 2012-05-21 Serpentine heat exchanger
CN201280029492.6A CN103608636A (en) 2011-06-17 2012-05-21 Serpentine heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011-135178 2011-06-17
JP2011135178A JP5663413B2 (en) 2011-06-17 2011-06-17 Serpentine heat exchanger

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EP2722628A1 (en) 2014-04-23
JP5663413B2 (en) 2015-02-04
JP2013002753A (en) 2013-01-07
CN103608636A (en) 2014-02-26
EP2722628A4 (en) 2015-06-03
US20140116662A1 (en) 2014-05-01

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