WO2012127925A1 - Heat exchanger and manufacturing method therefor - Google Patents

Heat exchanger and manufacturing method therefor Download PDF

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Publication number
WO2012127925A1
WO2012127925A1 PCT/JP2012/053043 JP2012053043W WO2012127925A1 WO 2012127925 A1 WO2012127925 A1 WO 2012127925A1 JP 2012053043 W JP2012053043 W JP 2012053043W WO 2012127925 A1 WO2012127925 A1 WO 2012127925A1
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WIPO (PCT)
Prior art keywords
refrigerant tube
heat exchanger
slits
refrigerant
long hole
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PCT/JP2012/053043
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French (fr)
Japanese (ja)
Inventor
和士 村田
政成 今井
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サンデン株式会社
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Publication of WO2012127925A1 publication Critical patent/WO2012127925A1/en

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    • 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
    • F28F1/24—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 and extending transversely
    • F28F1/32—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 and extending transversely the means having portions engaging further tubular elements
    • 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
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • 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
    • F28F2275/125—Fastening; Joining by methods involving deformation of the elements by bringing elements together and expanding

Definitions

  • the present invention relates to a heat exchanger used for a heat exchanger (evaporator or condenser) of a refrigeration cycle such as a vending machine or a showcase, and a method for manufacturing the same.
  • Patent Document 1 discloses a heat exchanger that does not have a joint portion in which a refrigerant passage is configured by a single continuous refrigerant tube (seamless tube).
  • a straight tube portion and a curved tube portion are continuously connected to form a meander-like refrigerant tube through a long hole formed in a plurality of plate fins arranged at intervals. It is attached.
  • burring is applied to the peripheral edge of both ends of the long hole, and the burring part is brought into close contact with the outer wall of the refrigerant tube, thereby improving the heat exchange efficiency.
  • the burring process has a high manufacturing cost because it is necessary to use an expensive mold. Further, the burring portion becomes hard and resistance when penetrating the refrigerant tube is increased. As a result, the refrigerant tube is deformed and the yield is deteriorated and the manufacturing cost is further increased.
  • the heat exchanger according to the present invention is A refrigerant tube formed in a meandering shape by connecting a straight pipe portion and a curved pipe portion, and a plurality of plate fins having a plurality of long holes through which the refrigerant tube passes and arranged at intervals from each other.
  • a heat exchanger comprising, comprising: A plurality of slits are arranged radially along the circumferential direction at outer peripheral edge portions of the both ends of the long hole of the plate fin, and a belt-like portion between the slits bent and deformed along the circumferential direction is a refrigerant tube. It has a structure that is fixed in pressure contact with the outer wall surface.
  • the manufacturing method of the heat exchanger according to the present invention includes: A refrigerant tube formed in a meandering shape by connecting a straight pipe portion and a curved pipe portion, and a plurality of plate fins having a plurality of long holes through which the refrigerant tube passes and arranged at intervals from each other.
  • a method of manufacturing a heat exchanger comprising: A plurality of slits are arranged radially along the circumferential direction on the outer peripheral edge of the both ends of the long hole of the plate fin, When penetrating the refrigerant tube through the long hole, the strip-shaped portion between the slits is spread and bent along the circumferential direction by the outer wall of the refrigerant tube, and the bent strip-shaped portion is pressed against the outer wall surface of the refrigerant tube. It is characterized by being configured to be fixed.
  • the band-shaped portion formed between the slits is easily bent by being spread by the outer wall of the refrigerant tube, and the bent band-shaped portion Is fixed in pressure contact with the outer wall surface of the refrigerant tube.
  • heat transfer efficiency improves between a refrigerant
  • burring processing is not required, and an expensive die for burring processing is not required, and the resistance when the refrigerant tube penetrates the long hole is small, so that deterioration in yield due to deformation of the refrigerant tube is suppressed, and manufacturing costs are reduced. Can be lowered.
  • FIG. 1 is a perspective view of a heat exchanger applied to a heat exchanger of a refrigeration cycle such as a vending machine or a showcase.
  • a heat exchanger 1 includes a refrigerant tube 2 in which a straight pipe portion 2A and a curved pipe portion 2B are continuous as shown in FIG.
  • the refrigerant tube 2 includes a plurality of long holes 3 ⁇ / b> A, and a plurality of plate fins 3 arranged at intervals from each other.
  • End plates 4 and 5 that support the bent tube portions 2B of the refrigerant tube 2 in a state of projecting outward through the long holes 4a and 5a are arranged on both side ends with the plurality of plate fins 3 interposed therebetween. (See FIGS. 4 and 5).
  • One end plate 4 (or end plate 5) supports both end portions of the meandering refrigerant tube 2 so as to protrude through the circular holes 4b of the end plate 4, and both end portions of the refrigerant tube 2 are
  • the refrigerant cycle is connected to an external refrigerant tube (not shown).
  • the refrigerant tube 2 for example, copper or aluminum is generally used as a material having a high thermal conductivity, and for the plate fin 3, for example, an aluminum material or the like is used as a light material having a high thermal conductivity.
  • the end plates 4 and 5 for example, steel is used to ensure strength.
  • the long holes 4a and 5a and the circular holes 4b of the end plates 4 and 5 are bent in the refrigerant tube 2 so as to reduce the frictional resistance when penetrating the refrigerant tube 2 as shown in FIGS.
  • the tube portion 2B is formed slightly larger than the projected contour line viewed from the penetration direction.
  • the elongated holes 3A of the plate fins 3 are formed as follows, as shown in an enlarged view in FIG. Before the refrigerant tube 2 is penetrated, the long hole 3A has circular hole portions 3a at both ends and a connecting hole portion 3b that connects the circular hole portions 3a to each other.
  • the circular hole portion 3 a is formed in a circular shape having a diameter smaller than the diameter of the straight pipe portion 2 ⁇ / b> A of the refrigerant tube 2.
  • the connecting hole portion 3b is formed by curving the contour line so that the width is narrower than the diameter of the circular hole portion 3a and the width is narrowest at the center portion.
  • a plurality of slits 3c are formed radially along the circumferential direction at the outer peripheral edge of the circular hole 3a at both ends.
  • the diameter of the circle connecting the deepest portions of the plurality of slits 3c is formed to be slightly larger than the diameter of the refrigerant tube 2 portion (straight tube portion 2A) penetrating the circular hole portion 3a.
  • the refrigerant tube 2 is formed by bending a straight pipe in a meandering manner so as to form a plurality of rows vertically and horizontally. Further, as shown in FIG. 6, before the heat exchanger 1 is assembled, the curved pipe portion 2B is formed in the connecting hole portion 2c so as to easily penetrate the connecting hole portion 2c of the long hole 3A, as will be described later. It is processed to be slightly flat parallel to the longitudinal direction to form a narrow width.
  • a plurality of plate fins 3 are installed at predetermined intervals with a jig interposed therebetween, and the meandering refrigerant tube 2 is connected to the curved pipe portion of the plurality of plate fins 3 installed. 2B is inserted into the slot 3A of the plate fin 3.
  • the distal end portion of the bent tube portion 2B passes through the connecting hole portion 3b of the long hole 3A.
  • the curved pipe portion 2B is deformed by expanding the connecting hole portion 3b outward, and as described above, the curved pipe portion 2B is processed to be flat and narrow in parallel with the longitudinal direction of the connecting hole portion 3b. Therefore, the amount of deformation can be reduced.
  • the surface area of the plate fin 3 can be increased by reducing the opening area of the connecting hole portion 3b as much as possible while reducing the resistance caused by deformation of the connecting hole portion 3b when the bent tube portion 2B passes through the connecting hole portion 3b. , Heat exchange efficiency can be improved.
  • both side edges of the connecting hole portion are elongated when the bent tube portion is penetrated.
  • the airflow that flows between the plate fins is likely to generate turbulence due to the corner portions that are raised in a rectangular shape and formed at both ends thereof.
  • the heat dissipation performance (in the case of a condenser) or the heat absorption performance (in the case of an evaporator) of the plate fin is likely to fluctuate, and it is difficult to obtain a stable heat exchange performance.
  • the connecting hole 3b since the connecting hole 3b has a convex arcuate contour at the center, the arcuate convex is raised when the bent pipe penetrates the connecting hole, Does not have a part. For this reason, it becomes difficult to produce a turbulent flow in the airflow flowing between the plate fins, the heat dissipation performance or heat absorption performance of the plate fins can be kept constant, and stable heat exchange performance can be secured.
  • the shape of the connecting hole portion may be a rectangular shape having a width that is the same as or slightly larger than the flat width of the curved pipe portion 2B, so that the frictional resistance when penetrating the curved pipe portion 2B can be eliminated or made as small as possible.
  • the diameter of the straight pipe part 2A is larger than the diameter of the circular hole part 3a. Since the diameters of the circles connecting the deepest portions of the plurality of slits 3c are smaller than each other, the strips between the slits 3c of the plate fin 3 are formed as shown in FIGS. 8 (A) to (C) and FIG. 3 d is pressed and fixed to the outer wall surface of the refrigerant tube 2 while being bent toward the insertion destination side of the refrigerant tube 2.
  • the meandering refrigerant tube 2 is attached in a state in which the long holes 3A of all the plate fins 3 are penetrated and the curved pipe portions 2B protrude from the plate fins 3 at both ends.
  • end plates 4 and 5 are attached to the outer sides of the plate fins 3 at both ends, respectively, through the refrigerant tubes 2 through the long holes 4a and 5a and the circular holes 4b formed therein.
  • a predetermined gap may be provided between the end plates 4 and 5 and the plate fins 3 on both sides with a jig interposed therebetween, but the end plates 4 and 5 and the plate fins 3 may be joined and attached. Good.
  • both ends of the meandering refrigerant tube 2 pass through a pair of circular holes 4 b formed in one end plate 4.
  • a liquid such as water or oil pressurized to a high pressure is injected into the refrigerant tube 2 after being attached to the plate fin 3.
  • the refrigerant tube 2 is expanded by the hydraulic pressure, and each band-like portion 3d of the plate fin 3 is further deformed to increase the contact area with the outer wall surface of the refrigerant tube 2 and press with a stronger force. .
  • the heat transfer coefficient between the refrigerant tube 2 and the plate fin 3 is increased.
  • the part processed into the flat part of the curved pipe part 2B is returned to the original circular cross section or the shape close
  • the refrigerant tube 2 is expanded by the hydraulic pressure, so that the refrigerant tube 2 is firmly attached to the long holes 4a and 5a and the circular holes 4b of the end plates 4 and 5 by being more strongly pressed. Finally, the jig for setting the gap between the plate fins and between the plate fins and the end plates is removed, and the manufacture of the heat exchanger 1 is completed.
  • the belt-like portion 3d formed and bent at the outer peripheral edge of the long hole 3A of the plate fin 3 is brought into pressure contact with the outer wall of the refrigerant tube 2, so that the heat between the refrigerant tube 2 and the plate fin 3 is The transfer rate is increased, and the heat exchange efficiency, and thus the heat efficiency of the refrigeration cycle using this heat exchanger can be maintained well.
  • burring processing for bringing the peripheral edge portion of the plate fin into contact with the outer wall of the refrigerant tube, and an expensive die for burring processing is not necessary.
  • the yield decreases due to deformation when penetrating the hardened burring portion, but in this embodiment, when the refrigerant tube is inserted into the long hole, the band-shaped portion formed by the slit is easy. Therefore, a high yield can be maintained.
  • both of the two end plates have a shape in which long holes are arranged as shown in FIG.
  • the end plate when the strength of the heat exchanger is ensured with only the refrigerant tube and the plate fin, the end plate can be omitted. Furthermore, as shown in FIG. 10, slits 3e may also be provided at the outer edge of the connecting hole 3b of the long hole 3A, and the band-like part 3f between the slits 3e is easily deformed when penetrating the curved pipe part 2B. Thus, the resistance during deformation can be further reduced.

Abstract

In a method for manufacturing a heat exchanger whereby cooling medium tubes (2) formed by connecting straight tube parts and curved tube parts in a serpentine shape are attached by inserting them through elongated holes (3A) formed in multiple plate fins arranged at intervals, the heat exchanger is constructed such that multiple slits (3c) are arranged radially along the circumference at the outer peripheral edge of circular holes (3a) at both ends of the elongated holes (3A), and when the curved parts of the cooling medium tubes (2) are inserted through the elongated holes (3A), strip-shaped parts (3d) between the slits (3c) are pressed and spread outward by the outer walls of the cooling medium tubes (2), and are bent at the base parts of the slits (3c), with the bent strip-shaped parts (3d) being pressed against and affixed to the outer wall surfaces of the cooling medium tubes (2). Thus, the manufacturing cost for the heat exchanger can be reduced while maintaining excellent heat exchange capability.

Description

熱交換器及びその製造方法Heat exchanger and manufacturing method thereof
　本発明は、自動販売機、ショーケースなどの冷凍サイクルの熱交換器（蒸発器や凝縮器）に使用される熱交換器及びその製造方法に関する。 The present invention relates to a heat exchanger used for a heat exchanger (evaporator or condenser) of a refrigeration cycle such as a vending machine or a showcase, and a method for manufacturing the same.
　冷媒漏れ防止用として、特許文献１には、冷媒通路を１本の連続した冷媒チューブ（シームレスチューブ）で構成した接合部を有しない熱交換器が開示されている。
　この種の熱交換器では、直管部及び曲管部を連続させて蛇行状に形成された冷媒チューブを、相互に間隔を置いて配置された複数のプレートフィンに形成された長孔に貫通させて取り付けている。 As a refrigerant leakage prevention, Patent Document 1 discloses a heat exchanger that does not have a joint portion in which a refrigerant passage is configured by a single continuous refrigerant tube (seamless tube).
In this type of heat exchanger, a straight tube portion and a curved tube portion are continuously connected to form a meander-like refrigerant tube through a long hole formed in a plurality of plate fins arranged at intervals. It is attached.
　また、長孔両端部の周縁部にバーリング加工を施し、バーリング部を冷媒チューブ外壁に密着させることにより、熱交換効率の向上を図っている。 Also, burring is applied to the peripheral edge of both ends of the long hole, and the burring part is brought into close contact with the outer wall of the refrigerant tube, thereby improving the heat exchange efficiency.
日本国特許公報：特開２００９－１３８９９２号公報Japanese Patent Gazette: JP 2009-138992 A
　しかしながら、上記のバーリング加工は、高価な型を用いる必要があるため製造コストが高くなる。
　また、バーリング部が硬くなって、冷媒チューブを貫通させる際の抵抗が大きくなり、その結果、冷媒チューブが変形する等、歩留まりが悪化してさらに製造コストが高くなる等の問題を生じていた。 However, the burring process has a high manufacturing cost because it is necessary to use an expensive mold.
Further, the burring portion becomes hard and resistance when penetrating the refrigerant tube is increased. As a result, the refrigerant tube is deformed and the yield is deteriorated and the manufacturing cost is further increased.
　このため、本発明に係る熱交換器は、
　直管部及び曲管部を連続させて蛇行状に形成された冷媒チューブと、該冷媒チューブが貫通する長孔を複数有し、相互に間隔を置いて配置された複数のプレートフィンと、を含んで構成される熱交換器であって、
　前記プレートフィンの前記長孔両端部の外周縁部に、周方向に沿って放射状に複数のスリットが列設され、前記周方向に沿って屈曲変形された該スリット間の帯状部が、冷媒チューブ外壁面に圧接して固定された構造を有していることを特徴とする。 For this reason, the heat exchanger according to the present invention is
A refrigerant tube formed in a meandering shape by connecting a straight pipe portion and a curved pipe portion, and a plurality of plate fins having a plurality of long holes through which the refrigerant tube passes and arranged at intervals from each other. A heat exchanger comprising, comprising:
A plurality of slits are arranged radially along the circumferential direction at outer peripheral edge portions of the both ends of the long hole of the plate fin, and a belt-like portion between the slits bent and deformed along the circumferential direction is a refrigerant tube. It has a structure that is fixed in pressure contact with the outer wall surface.
　また、本発明に係る熱交換器の製造方法は、
　直管部及び曲管部を連続させて蛇行状に形成された冷媒チューブと、該冷媒チューブが貫通する長孔を複数有し、相互に間隔を置いて配置された複数のプレートフィンと、を含んで構成される熱交換器の製造方法であって、
　前記プレートフィンの前記長孔両端部の外周縁部に、周方向に沿って放射状に複数のスリットを列設し、
　前記冷媒チューブを前記長孔に貫通させる際に、前記冷媒チューブの外壁によって前記スリット間の帯状部を押し広げて前記周方向に沿って屈曲させ、該屈曲した帯状部を冷媒チューブ外壁面に圧接させて固定する構成としたことを特徴とする。 Moreover, the manufacturing method of the heat exchanger according to the present invention includes:
A refrigerant tube formed in a meandering shape by connecting a straight pipe portion and a curved pipe portion, and a plurality of plate fins having a plurality of long holes through which the refrigerant tube passes and arranged at intervals from each other. A method of manufacturing a heat exchanger comprising:
A plurality of slits are arranged radially along the circumferential direction on the outer peripheral edge of the both ends of the long hole of the plate fin,
When penetrating the refrigerant tube through the long hole, the strip-shaped portion between the slits is spread and bent along the circumferential direction by the outer wall of the refrigerant tube, and the bent strip-shaped portion is pressed against the outer wall surface of the refrigerant tube. It is characterized by being configured to be fixed.
　このようにすれば、冷媒チューブをプレートフィンの長孔に貫通させる際に、スリット間に形成される帯状部が、冷媒チューブの外壁によって押し広げられることにより容易に屈曲し、該屈曲した帯状部が冷媒チューブ外壁面に圧接して固定される。 In this way, when the refrigerant tube is passed through the long hole of the plate fin, the band-shaped portion formed between the slits is easily bent by being spread by the outer wall of the refrigerant tube, and the bent band-shaped portion Is fixed in pressure contact with the outer wall surface of the refrigerant tube.
　これにより、冷媒チューブとプレートフィンとの間で熱伝達効率が向上し、熱交換効率を良好に維持できる。
　また、バーリング加工が不要となりバーリング加工用の高価な型が不要となると共に、冷媒チューブが長孔を貫通する時の抵抗が小さいため、冷媒チューブの変形等による歩留まりの悪化が抑制され、製造コストを引き下げることができる。 Thereby, heat transfer efficiency improves between a refrigerant | coolant tube and a plate fin, and heat exchange efficiency can be maintained favorable.
In addition, burring processing is not required, and an expensive die for burring processing is not required, and the resistance when the refrigerant tube penetrates the long hole is small, so that deterioration in yield due to deformation of the refrigerant tube is suppressed, and manufacturing costs are reduced. Can be lowered.
自動販売機、ショーケースなどの冷凍サイクルの熱交換器に適用される熱交換器を示す斜視図である。It is a perspective view which shows the heat exchanger applied to the heat exchanger of refrigeration cycles, such as a vending machine and a showcase. 同上熱交換器の冷媒チューブを示す正面図である。It is a front view which shows the refrigerant | coolant tube of a heat exchanger same as the above. 同上熱交換器のプレートフィンを示す図である。It is a figure which shows the plate fin of a heat exchanger same as the above. 同上熱交換器の一方の端板を示す図である。It is a figure which shows one end plate of a heat exchanger same as the above. 同上熱交換器の他方の端板を示す図である。It is a figure which shows the other end plate of a heat exchanger same as the above. 同上冷媒チューブの曲管部を図２のＡ方向から視た図である。It is the figure which looked at the curved pipe part of the refrigerant tube same as the above from the A direction of FIG. 同上プレートフィンに形成される長孔の拡大図である。It is an enlarged view of the long hole formed in a plate fin same as the above. 同上の冷媒チューブをプレートフィンの長孔に挿入するときの工程を示す図である。It is a figure which shows a process when inserting a refrigerant | coolant tube same as the above into the long hole of a plate fin. 図８（Ｃ）のＸ部をＢ方向から見た状態を拡大して示した図である。It is the figure which expanded and showed the state which looked at the X section of FIG.8 (C) from the B direction. プレートフィンに形成される長孔の別の形態を示す図である。It is a figure which shows another form of the long hole formed in a plate fin.
　図１は、自動販売機、ショーケースなどの冷凍サイクルの熱交換器に適用される熱交換器の斜視図を示す。
　図１において、熱交換器１は、図２に示すように直管部２Ａ及び曲管部２Ｂが連続し、かつ縦横に複数ずつ列をなして蛇行状に屈曲加工された冷媒チューブ２と、図３に示すように該冷媒チューブ２が貫通する長孔３Ａを複数有し、相互に間隔を置いて配置された複数のプレートフィン３と、を含んで構成される。 FIG. 1 is a perspective view of a heat exchanger applied to a heat exchanger of a refrigeration cycle such as a vending machine or a showcase.
In FIG. 1, a heat exchanger 1 includes a refrigerant tube 2 in which a straight pipe portion 2A and a curved pipe portion 2B are continuous as shown in FIG. As shown in FIG. 3, the refrigerant tube 2 includes a plurality of long holes 3 </ b> A, and a plurality of plate fins 3 arranged at intervals from each other.
　前記複数のプレートフィン３を挟んで、両側端には、冷媒チューブ２の曲管部２Ｂを、長孔４ａ，５ａを貫通させて外側に突出させた状態で支持する端板４，５が配設されている（図４，図５参照）。なお、一方の端板４（または端板５）には、蛇行状の冷媒チューブ２の両端部が端板４の円孔４ｂを貫通して突出して支持され、該冷媒チューブ２の両端部は、冷媒サイクルを構成する外部の冷媒チューブ（図示せず）に接続される。 End plates 4 and 5 that support the bent tube portions 2B of the refrigerant tube 2 in a state of projecting outward through the long holes 4a and 5a are arranged on both side ends with the plurality of plate fins 3 interposed therebetween. (See FIGS. 4 and 5). One end plate 4 (or end plate 5) supports both end portions of the meandering refrigerant tube 2 so as to protrude through the circular holes 4b of the end plate 4, and both end portions of the refrigerant tube 2 are The refrigerant cycle is connected to an external refrigerant tube (not shown).
　冷媒チューブ２には、一般に熱伝導率の大きい材料として例えば、銅、アルミ材等が用いられ、プレートフィン３には軽量で熱伝導率の大きい材料として例えば、アルミ材等が用いられる。端板４、５には、強度確保のため、例えば鋼材等が用いられる。 For the refrigerant tube 2, for example, copper or aluminum is generally used as a material having a high thermal conductivity, and for the plate fin 3, for example, an aluminum material or the like is used as a light material having a high thermal conductivity. For the end plates 4 and 5, for example, steel is used to ensure strength.
　ここで、端板４，５の長孔４ａ，５ａ及び円孔４ｂは、図４、図５に示すように、冷媒チューブ２の貫通時の摩擦抵抗を低減できるように、冷媒チューブ２の曲管部２Ｂを貫通方向からみた投影外郭線より若干大きめに形成させてある。 Here, the long holes 4a and 5a and the circular holes 4b of the end plates 4 and 5 are bent in the refrigerant tube 2 so as to reduce the frictional resistance when penetrating the refrigerant tube 2 as shown in FIGS. The tube portion 2B is formed slightly larger than the projected contour line viewed from the penetration direction.
　一方、プレートフィン３の長孔３Ａは、図７に拡大して示すように、以下のように形成されている。冷媒チューブ２貫通前の状態で、長孔３Ａは、両端の円孔部３ａと、これら円孔部３ａ相互を連繋する連繋孔部３ｂと、を有している。 On the other hand, the elongated holes 3A of the plate fins 3 are formed as follows, as shown in an enlarged view in FIG. Before the refrigerant tube 2 is penetrated, the long hole 3A has circular hole portions 3a at both ends and a connecting hole portion 3b that connects the circular hole portions 3a to each other.
　円孔部３ａは、冷媒チューブ２の直管部２Ａの直径より小さい直径を有した円形状に形成されている。
　連繋孔部３ｂは、円孔部３ａの直径より幅が狭く、かつ、中央部で最も幅が狭くなるように輪郭線を湾曲させて形成されている。 The circular hole portion 3 a is formed in a circular shape having a diameter smaller than the diameter of the straight pipe portion 2 </ b> A of the refrigerant tube 2.
The connecting hole portion 3b is formed by curving the contour line so that the width is narrower than the diameter of the circular hole portion 3a and the width is narrowest at the center portion.
　両端の円孔部３ａの外側周縁部には、周方向に沿って放射状に複数のスリット３ｃが形成されている。これら複数のスリット３ｃの最深部を結ぶ円の直径は、円孔部３ａを貫通する冷媒チューブ２部分（直管部２Ａ）の直径より少し大きく形成されている。 A plurality of slits 3c are formed radially along the circumferential direction at the outer peripheral edge of the circular hole 3a at both ends. The diameter of the circle connecting the deepest portions of the plurality of slits 3c is formed to be slightly larger than the diameter of the refrigerant tube 2 portion (straight tube portion 2A) penetrating the circular hole portion 3a.
　次に、上記熱交換器１の製造方法について説明する。
　冷媒チューブ２は、ストレートなパイプを縦横に複数列をなすように蛇行状に曲げ加工して形成される。また、図６に示すように、曲管部２Ｂは、熱交換器１の組立前において、後述するように、長孔３Ａの連繋孔部２ｃを貫通しやすくするため、該連繋孔部２ｃの長手方向と平行に若干偏平に加工されて幅が狭く形成される。 Next, a method for manufacturing the heat exchanger 1 will be described.
The refrigerant tube 2 is formed by bending a straight pipe in a meandering manner so as to form a plurality of rows vertically and horizontally. Further, as shown in FIG. 6, before the heat exchanger 1 is assembled, the curved pipe portion 2B is formed in the connecting hole portion 2c so as to easily penetrate the connecting hole portion 2c of the long hole 3A, as will be described later. It is processed to be slightly flat parallel to the longitudinal direction to form a narrow width.
　複数枚のプレートフィン３を、治具を挟んで相互に所定の間隔をあけて設置し、該設置された複数枚のプレートフィン３に対し、上記蛇行状の冷媒チューブ２を、その曲管部２Ｂからプレートフィン３の長孔３Ａに挿入する。 A plurality of plate fins 3 are installed at predetermined intervals with a jig interposed therebetween, and the meandering refrigerant tube 2 is connected to the curved pipe portion of the plurality of plate fins 3 installed. 2B is inserted into the slot 3A of the plate fin 3.
　ここで、まず、曲管部２Ｂの先端部が長孔３Ａの連繋孔部３ｂを貫通する。この際、曲管部２Ｂは、連繋孔部３ｂを外側に押し拡げて変形させるが、上記のように曲管部２Ｂは連繋孔部３ｂの長手方向と平行に偏平な幅狭に加工されているので、変形量を少なくすることができる。 Here, first, the distal end portion of the bent tube portion 2B passes through the connecting hole portion 3b of the long hole 3A. At this time, the curved pipe portion 2B is deformed by expanding the connecting hole portion 3b outward, and as described above, the curved pipe portion 2B is processed to be flat and narrow in parallel with the longitudinal direction of the connecting hole portion 3b. Therefore, the amount of deformation can be reduced.
　これにより、曲管部２Ｂの連繋孔部３ｂ貫通時に、連繋孔部３ｂ変形による抵抗を小さくしつつ、連繋孔部３ｂの開口面積をできるだけ小さくしてプレートフィン３の表面積を大きくすることができ、熱交換効率を向上できる。 As a result, the surface area of the plate fin 3 can be increased by reducing the opening area of the connecting hole portion 3b as much as possible while reducing the resistance caused by deformation of the connecting hole portion 3b when the bent tube portion 2B passes through the connecting hole portion 3b. , Heat exchange efficiency can be improved.
　また、特許文献１の図８のように、連繋孔部を両端の円孔より幅狭の矩形状とした場合は、曲管部の連繋孔部貫通時に、連繋孔部の両側縁部が細長い矩形状に起こされ、それらの両端部に形成される角部によって、プレートフィン間を流通する空気流が乱流を生じやすくなる。これにより、プレートフィンの放熱性能（凝縮器の場合）または吸熱性能（蒸発器の場合）が変動しやすく、安定した熱交換性能が得られにくい。 In addition, as shown in FIG. 8 of Patent Document 1, when the connecting hole portion has a rectangular shape narrower than the circular holes at both ends, both side edges of the connecting hole portion are elongated when the bent tube portion is penetrated. The airflow that flows between the plate fins is likely to generate turbulence due to the corner portions that are raised in a rectangular shape and formed at both ends thereof. Thereby, the heat dissipation performance (in the case of a condenser) or the heat absorption performance (in the case of an evaporator) of the plate fin is likely to fluctuate, and it is difficult to obtain a stable heat exchange performance.
　これに対し、本実施形態では、連繋孔部３ｂが中央部で凸の円弧状の輪郭を有しているため、曲管部の連繋孔部貫通時に該円弧状の凸部が起こされ、角部を有しない。このため、プレートフィン間を流通する空気流に乱流が生じにくくなり、プレートフィンの放熱性能または吸熱性能を一定に保つことができ、安定した熱交換性能を確保できる。 On the other hand, in this embodiment, since the connecting hole 3b has a convex arcuate contour at the center, the arcuate convex is raised when the bent pipe penetrates the connecting hole, Does not have a part. For this reason, it becomes difficult to produce a turbulent flow in the airflow flowing between the plate fins, the heat dissipation performance or heat absorption performance of the plate fins can be kept constant, and stable heat exchange performance can be secured.
　なお、連繋孔部の形状を、曲管部２Ｂの偏平な幅と同一、若しくはやや大きい幅を有する矩形状として、曲管部２Ｂ貫通時の摩擦抵抗を無くすか、できるだけ小さくすることもできる。 It should be noted that the shape of the connecting hole portion may be a rectangular shape having a width that is the same as or slightly larger than the flat width of the curved pipe portion 2B, so that the frictional resistance when penetrating the curved pipe portion 2B can be eliminated or made as small as possible.
　曲管部２Ｂの両端部から直管部２Ａに移行する部分が長孔３Ａの円孔部３ａを貫通する際には、直管部２Ａの直径は、円孔部３ａの直径より大きく、また、多数のスリット３ｃの最深部相互を結ぶ円の直径より小さく形成されているので、図８（Ａ）～（Ｃ）及び図９に示すように、プレートフィン３のスリット３ｃ間の各帯状部３ｄが冷媒チューブ２の挿入先側に押し曲げられつつ、冷媒チューブ２の外壁面に圧接して固定される。 When the portion that transitions from both ends of the curved pipe part 2B to the straight pipe part 2A passes through the circular hole part 3a of the long hole 3A, the diameter of the straight pipe part 2A is larger than the diameter of the circular hole part 3a. Since the diameters of the circles connecting the deepest portions of the plurality of slits 3c are smaller than each other, the strips between the slits 3c of the plate fin 3 are formed as shown in FIGS. 8 (A) to (C) and FIG. 3 d is pressed and fixed to the outer wall surface of the refrigerant tube 2 while being bent toward the insertion destination side of the refrigerant tube 2.
　このようにして、蛇行状の冷媒チューブ２を、全てのプレートフィン３の長孔３Ａを貫通させて、曲管部２Ｂが両端のプレートフィン３から突出させた状態で取り付ける。
　次いで、両端のプレートフィン３の外側に、それぞれ端板４，５を、これらに形成された長孔４ａ，５ａ及び円孔４ｂに冷媒チューブ２を貫通させて、取り付ける。なお、両側の端板４，５とプレートフィン３との間に、治具を挟んで、所定の間隔を設けてよいが、端板４，５とプレートフィン３とを接合して取り付けてもよい。 In this manner, the meandering refrigerant tube 2 is attached in a state in which the long holes 3A of all the plate fins 3 are penetrated and the curved pipe portions 2B protrude from the plate fins 3 at both ends.
Next, end plates 4 and 5 are attached to the outer sides of the plate fins 3 at both ends, respectively, through the refrigerant tubes 2 through the long holes 4a and 5a and the circular holes 4b formed therein. It should be noted that a predetermined gap may be provided between the end plates 4 and 5 and the plate fins 3 on both sides with a jig interposed therebetween, but the end plates 4 and 5 and the plate fins 3 may be joined and attached. Good.
　また、一方の端板４に形成された一対の円孔４ｂには、蛇行状の冷媒チューブ２の両端部が貫通する。
　次いで、上記プレートフィン３への取付後の冷媒チューブ２内に、高圧に加圧された水または油等の液体を注入する。これにより、液圧によって冷媒チューブ２が拡開され、プレートフィン３の各帯状部３ｄが、より大きく変形して冷媒チューブ２の外壁面との接触面積を増大させつつ、より強い力で圧接する。 Further, both ends of the meandering refrigerant tube 2 pass through a pair of circular holes 4 b formed in one end plate 4.
Next, a liquid such as water or oil pressurized to a high pressure is injected into the refrigerant tube 2 after being attached to the plate fin 3. As a result, the refrigerant tube 2 is expanded by the hydraulic pressure, and each band-like portion 3d of the plate fin 3 is further deformed to increase the contact area with the outer wall surface of the refrigerant tube 2 and press with a stronger force. .
　これにより、冷媒チューブ２－プレートフィン３間の熱伝達率が高められる。
　また、曲管部２Ｂの偏平に加工された部分が、液圧によって、元の円形断面、またはこれに近い形状に戻され、冷媒の流通抵抗を良好に維持できる。 Thereby, the heat transfer coefficient between the refrigerant tube 2 and the plate fin 3 is increased.
Moreover, the part processed into the flat part of the curved pipe part 2B is returned to the original circular cross section or the shape close | similar to this by hydraulic pressure, and can maintain the distribution | circulation resistance of a refrigerant | coolant favorably.
　さらに、前記液圧による冷媒チューブ２の拡開により、冷媒チューブ２が端板４，５の長孔４ａ，５ａ及び円孔４ｂに、より強く圧接して強固に取り付けられる。
　最後に、プレートフィン相互間、プレートフィンと端板間との間隔設定用の治具を取り除き、熱交換器１の製造を完了する。 Further, the refrigerant tube 2 is expanded by the hydraulic pressure, so that the refrigerant tube 2 is firmly attached to the long holes 4a and 5a and the circular holes 4b of the end plates 4 and 5 by being more strongly pressed.
Finally, the jig for setting the gap between the plate fins and between the plate fins and the end plates is removed, and the manufacture of the heat exchanger 1 is completed.
　かかる構成とすれば、プレートフィン３の長孔３Ａ外周縁部に形成されて屈曲される帯状部３ｄが、冷媒チューブ２外壁に圧接して密着するので、冷媒チューブ２－プレートフィン３間の熱伝達率が高められ、熱交換効率、ひいては、本熱交換器を用いた冷凍サイクルの熱効率を良好に維持できる。 With such a configuration, the belt-like portion 3d formed and bent at the outer peripheral edge of the long hole 3A of the plate fin 3 is brought into pressure contact with the outer wall of the refrigerant tube 2, so that the heat between the refrigerant tube 2 and the plate fin 3 is The transfer rate is increased, and the heat exchange efficiency, and thus the heat efficiency of the refrigeration cycle using this heat exchanger can be maintained well.
　また、プレートフィンの長孔周縁部に冷媒チューブ外壁と接触させるためのバーリング加工を施すことが不要となり、バーリング加工用の高価な型が不要となる。
　また、バーリング加工したときには、硬くなったバーリング部を貫通する際の変形による歩留まりの低下を生じるが、本実施形態では、冷媒チューブの長孔への挿入時に、スリットにより形成される帯状部が容易に変形するため、高い歩留まりを維持できる。 Further, it is not necessary to perform burring processing for bringing the peripheral edge portion of the plate fin into contact with the outer wall of the refrigerant tube, and an expensive die for burring processing is not necessary.
In addition, when burring is performed, the yield decreases due to deformation when penetrating the hardened burring portion, but in this embodiment, when the refrigerant tube is inserted into the long hole, the band-shaped portion formed by the slit is easy. Therefore, a high yield can be maintained.
　このように、熱交換器の高い性能を確保しつつ、製造コストを大幅に引き下げることができる。
　なお、本実施形態では、冷媒チューブ２を複数枚のプレートフィン３に貫通させた後で、端板４，５を両側から冷媒チューブ２に貫通して取り付ける構成のものを示したが、複数枚のプレートフィン３と端板４，５とに同時に冷媒チューブ２に貫通して取り付ける構成としてもよい。この場合、２つの端板は、共に、図５に示したように長孔を配設した形状となる。 Thus, the manufacturing cost can be greatly reduced while ensuring the high performance of the heat exchanger.
In the present embodiment, a configuration in which the end plates 4 and 5 are attached through the refrigerant tubes 2 from both sides after the refrigerant tubes 2 have passed through the plurality of plate fins 3 is shown. It is good also as a structure which penetrates the refrigerant | coolant tube 2 and is attached to the plate fin 3 and the end plates 4 and 5 simultaneously. In this case, both of the two end plates have a shape in which long holes are arranged as shown in FIG.
　また、冷媒チューブとプレートフィンのみで熱交換器の強度が確保される場合には、端板を省略することもできる。
　さらに、図１０に示すように、長孔３Ａの連繋孔部３ｂの外縁部にもスリット３ｅを設けてもよく、曲管部２Ｂの貫通時に、スリット３ｅ間の帯状部３ｆが容易に変形して、変形時の抵抗をより小さくすることができる。 Moreover, when the strength of the heat exchanger is ensured with only the refrigerant tube and the plate fin, the end plate can be omitted.
Furthermore, as shown in FIG. 10, slits 3e may also be provided at the outer edge of the connecting hole 3b of the long hole 3A, and the band-like part 3f between the slits 3e is easily deformed when penetrating the curved pipe part 2B. Thus, the resistance during deformation can be further reduced.
　１…熱交換器
　２…冷媒チューブ
　３…プレートフィン
　３Ａ…長孔
　３ａ…円孔部
　３ｂ…連繋孔部
　３ｃ…スリット
　３ｄ…帯状部
　４…端板
　４ａ…長孔
　４ｂ…円孔
　５…端板
　５ａ…長孔 DESCRIPTION OF SYMBOLS 1 ... Heat exchanger 2 ... Refrigerant tube 3 ... Plate fin 3A ... Long hole 3a ... Circular hole part 3b ... Connection hole part 3c ... Slit 3d ... Strip | belt-shaped part 4 ... End plate 4a ... Long hole 4b ... Circular hole 5 ... End plate 5a ... Long hole

Claims (5)

  1. 　直管部及び曲管部を連続させて蛇行状に形成された冷媒チューブと、該冷媒チューブが貫通する長孔を複数有し、相互に間隔を置いて配置された複数のプレートフィンと、を含んで構成される熱交換器であって、
    　前記プレートフィンの前記長孔両端部の外周縁部に、周方向に沿って放射状に複数のスリットが列設され、前記周方向に沿って屈曲変形された該スリット間の帯状部が、冷媒チューブ外壁面に圧接して固定された構造を有していることを特徴とする熱交換器。     A refrigerant tube formed in a meandering shape by connecting a straight pipe portion and a curved pipe portion, and a plurality of plate fins having a plurality of long holes through which the refrigerant tube passes and arranged at intervals from each other. A heat exchanger comprising, comprising:
    A plurality of slits are arranged radially along the circumferential direction at outer peripheral edge portions of the both ends of the long hole of the plate fin, and a belt-like portion between the slits bent and deformed along the circumferential direction is a refrigerant tube. A heat exchanger characterized by having a structure fixed in pressure contact with an outer wall surface.
  2. 　前記プレートフィンの長孔は、両端が円形状の円孔部と、これら円孔部相互を連繋する連繋部とを備え、前記円孔部の外周縁部に前記スリットが形成されている請求項１に記載の熱交換器。 The long hole of the plate fin includes a circular hole part having both ends circular and a connecting part that connects the circular hole parts, and the slit is formed in an outer peripheral edge part of the circular hole part. The heat exchanger according to 1.
  3. 　前記長孔の連繋部は、前記円孔部の直径より狭い幅を有して形成されている請求項２に記載の熱交換器。 The heat exchanger according to claim 2, wherein the long hole connecting portion is formed to have a width narrower than the diameter of the circular hole portion.
  4. 　直管部及び曲管部を連続させて蛇行状に形成された冷媒チューブと、該冷媒チューブが貫通する長孔を複数有し、相互に間隔を置いて配置された複数のプレートフィンと、を含んで構成される熱交換器の製造方法であって、
    　前記プレートフィンの前記長孔両端部の外周縁部に、周方向に沿って放射状に複数のスリットを列設し、
    　前記冷媒チューブを前記長孔に貫通させる際に、前記冷媒チューブの外壁によって前記スリット間の帯状部を押し広げて前記周方向に沿って屈曲させ、該屈曲した帯状部を冷媒チューブ外壁面に圧接させて固定する構成としたことを特徴とする熱交換器の製造方法。     A refrigerant tube formed in a meandering shape by connecting a straight pipe portion and a curved pipe portion, and a plurality of plate fins having a plurality of long holes through which the refrigerant tube passes and arranged at intervals from each other. A method of manufacturing a heat exchanger comprising:
    A plurality of slits are arranged radially along the circumferential direction on the outer peripheral edge of the both ends of the long hole of the plate fin,
    When penetrating the refrigerant tube through the long hole, the strip-shaped portion between the slits is spread and bent along the circumferential direction by the outer wall of the refrigerant tube, and the bent strip-shaped portion is pressed against the outer wall surface of the refrigerant tube. A method of manufacturing a heat exchanger, characterized by being configured to be fixed.
  5. 　前記冷媒チューブを前記複数枚のプレートフィンを貫通して取り付けた後、前記冷媒チューブ内に、高圧に加圧された液体を注入し、液圧によって冷媒チューブを拡開して前記プレートフィンの帯状部をさらに変形させつつ冷媒チューブ外壁との接触面積を増大させる請求項４に記載の熱交換器の製造方法。 After the refrigerant tube is attached through the plurality of plate fins, a liquid pressurized to a high pressure is injected into the refrigerant tube, and the refrigerant tube is widened by the liquid pressure to form a band shape of the plate fin. The manufacturing method of the heat exchanger of Claim 4 which increases a contact area with a refrigerant | coolant tube outer wall, deform | transforming a part further.
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WO2023219133A1 (en) * 2022-05-13 2023-11-16 株式会社Afrex Finless heat exchanger, and cooling system employing same

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02217158A (en) * 1988-10-28 1990-08-29 Showa Alum Corp Heat exchanger
JPH06201285A (en) * 1992-12-28 1994-07-19 Showa Alum Corp Cross-fin heat exchanger
JPH0719778A (en) * 1993-06-30 1995-01-20 Showa Alum Corp Manufacture of tube with radial fin
JP2007518962A (en) * 2004-01-20 2007-07-12 オートクンプ ヒートクラフト ユーエスエー リミテッド ライアビリティー カンパニー Brazed plate fin heat exchanger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02217158A (en) * 1988-10-28 1990-08-29 Showa Alum Corp Heat exchanger
JPH06201285A (en) * 1992-12-28 1994-07-19 Showa Alum Corp Cross-fin heat exchanger
JPH0719778A (en) * 1993-06-30 1995-01-20 Showa Alum Corp Manufacture of tube with radial fin
JP2007518962A (en) * 2004-01-20 2007-07-12 オートクンプ ヒートクラフト ユーエスエー リミテッド ライアビリティー カンパニー Brazed plate fin heat exchanger

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