WO2012017777A1 - Double tuyauterie pour échangeur thermique - Google Patents

Double tuyauterie pour échangeur thermique Download PDF

Info

Publication number
WO2012017777A1
WO2012017777A1 PCT/JP2011/065650 JP2011065650W WO2012017777A1 WO 2012017777 A1 WO2012017777 A1 WO 2012017777A1 JP 2011065650 W JP2011065650 W JP 2011065650W WO 2012017777 A1 WO2012017777 A1 WO 2012017777A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
pipe
double
inner tube
shape
Prior art date
Application number
PCT/JP2011/065650
Other languages
English (en)
Japanese (ja)
Inventor
松田　眞一
Original Assignee
住友軽金属工業株式会社
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 住友軽金属工業株式会社 filed Critical 住友軽金属工業株式会社
Publication of WO2012017777A1 publication Critical patent/WO2012017777A1/fr

Links

Images

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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • F28F1/34—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 obliquely
    • F28F1/36—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 obliquely the means being helically wound fins or wire spirals
    • 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

Definitions

  • the present invention relates to a double tube for a heat exchanger that can be applied to a heat exchange cycle such as an air conditioner for an automobile.
  • a heat exchange cycle such as an air conditioner for automobiles includes a condenser, an evaporator, a compressor, and an expansion valve, and a refrigerant such as CFC, CO 2 , and ammonia is circulated in a circulation path connecting them. It is a system to let you.
  • a double pipe is disposed in the circulation path, and a high-temperature refrigerant coming out of the condenser and a low-temperature refrigerant coming out of the evaporator are disposed in a two-layer space constituted by the double pipe. It has been proposed that the heat exchange performance is improved by flowing the gas in the opposite direction to exchange heat (see Patent Documents 1 and 2).
  • the problem is that heat cannot be exchanged if the refrigerant flows into the compressor in a state where the refrigerant cannot be sufficiently vaporized (liquid is mixed).
  • the problem can be solved by incorporating the double pipe. That is, in the double pipe, the refrigerant before flowing into the compressor can be heated, and the refrigerant can be sufficiently vaporized.
  • torsion pipes are often used as the inner pipes in order to improve heat exchange performance (see Patent Documents 1 and 2).
  • Patent Document 2 is a combination of an inner tube having a spiral groove and a smooth outer tube, in which the inner diameter of the outer tube is larger than the outer diameter of the inner tube.
  • the inner tube and the outer tube are not in contact with each other at least in a straight portion of the double tube or only in one place, noise is generated due to vibration during operation of the heat exchange system. is there.
  • Patent Document 1 shows that a double tube structure is used for a heat exchange cycle, and that an outer peripheral surface of the inner tube or an inner peripheral surface of the outer tube is formed with a spiral groove. However, there is almost no disclosure regarding the specific structure of the double tube beyond that.
  • the present invention has been made in view of such a background, and is intended to provide a double tube for a heat exchanger having a structure that can be used without generating noise during operation and can exhibit excellent heat exchange performance. It is what.
  • a first aspect of the present invention has a double tube structure in which an inner tube is arranged inside an outer tube, and flows between the inner tube and the outer tube.
  • a heat exchanger double tube for exchanging heat with a fluid The inner tube has a shape having a plurality of convex portions whose cross-sectional shape is deformed so that a part of the circumference of a circle protrudes outward of the circle, and the position of the convex portion is in the longitudinal direction.
  • the outer tube has a smooth tube shape with a circular cross-sectional shape
  • the inner peripheral surface of the outer tube and the apex portion of the convex portion of the inner tube are in contact with each other, and an outer flow path partitioned in a plurality of circumferential directions is formed between the outer tube and the inner tube. It is in the double pipe for heat exchangers characterized by being.
  • the double tube for heat exchanger is composed of an inner tube spirally twisted with a special shape and an outer tube made of a circular smooth tube. And the vertex part of the said some convex part of an inner tube is in contact with the internal peripheral surface of an outer tube
  • an outer flow path is defined in a plurality of circumferential directions by a plurality of convex portions of the inner pipe, and each outer flow path is formed in a spiral shape. It becomes.
  • the inside of the inner tube also becomes an inner flow path having an outer wall that is spirally twisted. Therefore, if a fluid (refrigerant) flows through each of the outer and inner channels of the double pipe, the fluid (refrigerant) flows in both channels while causing moderate turbulence and efficiently exchanges heat. Can do.
  • the double pipe is integrated with the inner pipe and the outer pipe in contact with each other. Therefore, even if vibration occurs when operating the heat exchange cycle in which the double pipe is incorporated, it is possible to reliably prevent noise from being generated due to collision between the inner pipe and the outer pipe in the double pipe.
  • FIG. 3 is a cross-sectional view showing only the outer pipe of the double pipe in the first embodiment.
  • FIG. 3 is a cross-sectional view showing only the inner pipe of the double pipe in the first embodiment.
  • FIG. 2 is a cross-sectional view of a double pipe in Example 1. Explanatory drawing which shows the inner tube
  • FIG. 6 is a cross-sectional view of a double pipe in Example 3.
  • the inner peripheral surface of the outer pipe and the apex portion of the convex part of the inner pipe may be in contact with each other under pressure (pressure contact). In this case, it becomes easy to obtain a noise prevention effect due to the vibration.
  • the number of the convex portions formed in the inner pipe is not particularly limited, and is determined in consideration of fluid (refrigerant) flow rate, heat exchange performance, ease of convex portion formation, and the like. be able to.
  • the inner pipe may be configured to have 2 to 8 convex portions.
  • the number of the convex portions is one, the support of the inner tube tends to become unstable when forming the convex portions, and the convex portion forming property is deteriorated.
  • the above-mentioned convex part is two or more places, even if the inner tube is bent, it is difficult to be deformed, which can contribute to improvement of deformation resistance.
  • the convex portions when the number of the convex portions is 8 or less, the convex portions can be stably formed even when the pipe diameter is relatively small, for example, in the case of a double tube for heat exchange in an automotive air conditioner. Easy to form. Moreover, the fluid (refrigerant) flow rate does not decrease excessively, and the heat exchange performance is easily maintained.
  • the convex portion may be disposed at any position in the circumferential direction of the cross-sectional shape.
  • the adjacent convex portions may be provided at equal intervals.
  • the convex portion includes two places that are 180 degrees apart in the circumferential direction of the cross-sectional shape, three places that are 120 degrees apart in the circumferential direction of the cross-sectional shape, and the circumferential direction of the cross-sectional shape. It is possible to provide them at four places 90 degrees apart, six places 60 degrees apart in the circumferential direction of the cross-sectional shape, eight places 45 degrees apart in the circumferential direction of the cross-sectional shape, and the like.
  • the fluid (refrigerant) flow rate in the outer flow path is equal in the circumferential direction. Therefore, it becomes easy to suppress heat exchange unevenness with the fluid (refrigerant) in the inner flow path.
  • the convex portions are provided at two positions that are 180 degrees apart in the circumferential direction of the cross-sectional shape.
  • the outer flow path can be divided into two. Thereby, it can divide into a plurality of channels, without reducing the channel cross-sectional area of an outside channel greatly, and can obtain the refrigerant stirring effect moderately.
  • the inner pipe and the outer pipe are preferably made of an aluminum alloy or a copper alloy.
  • the aluminum alloy here refers to all alloys including pure aluminum and mainly composed of aluminum.
  • the copper alloy refers to all alloys including pure copper and mainly copper. These metal materials are relatively excellent in heat transfer characteristics and are effective in improving heat exchange performance. In view of weight reduction, it is most preferable to use an aluminum alloy.
  • an aluminum alloy is selected as the material, pure aluminum (A1050, A1100), aluminum alloy (A3003, A6063), or the like is preferable.
  • copper is selected, there are pure copper phosphorous deoxidized copper, copper alloy with high thermal conductivity, and the like.
  • a material with favorable workability is desirable as a material, when corrosion resistance and intensity
  • the angle of the spiral displacement of the inner tube with respect to the axial direction is in a range of 15 to 60 degrees.
  • the angle is smaller than the above range, the pressure loss in flowing the fluid can be reduced, while the turbulent flow effect is small and the heat exchange performance improving effect may be reduced.
  • the angle is larger than the above range, the effect of improving the heat exchange performance can be enhanced by increasing the turbulent flow effect when flowing the fluid, while the pressure loss may be excessively increased.
  • the lower limit value of the angle is more preferably 20 degrees, still more preferably 25 degrees, and still more preferably 30 degrees.
  • the upper limit value of the angle is more preferably 55 degrees, further preferably 50 degrees, and still more preferably 45 degrees, from the viewpoint of ease of twisting.
  • the inner tube can be produced by linearly drawing a smooth tube having a circular cross section as a material while rotating a die having an inner hole having a shape corresponding to the desired spiral shape.
  • the inner tube processing method other processing methods such as a processing method in which the die is not rotated may be employed.
  • the outer tube is made of a smooth tube having a circular cross section having an inner diameter larger than the outer diameter of the inner tube.
  • the molded inner pipe is inserted into the outer pipe material to form a double pipe structure.
  • the outer tube material is subjected to reduced diameter drawing while maintaining the double tube structure. As a result, the tip of the arcuate apex of the inner tube and the inner surface of the outer tube can be brought into strong contact, and the double tube in which both are integrated can be obtained.
  • pipes will be connected to the inner flow path of the inner pipe and the outer flow path between the inner pipe and the outer pipe, respectively. It is not particularly limited, and various structures and various joining methods can be employed. Examples of the joining method include caulking joining method, brazing joining, adhesive joining, and friction stir welding.
  • the size of the double pipe can be appropriately designed according to the flow rate of the refrigerant in the heat exchange cycle to be applied.
  • the wall thickness for example, when the material of the double tube is an aluminum alloy, when A1050 is used, the wall thickness of the inner tube is 0.8 to 1.8 mm, and the wall thickness of the outer tube is 1. 0.0-2.2mm, when using A3003, the inner tube thickness is 0.6-1.5mm, outer tube thickness is 0.8-1.8mm, when A6063 is used
  • the thickness of the tube is preferably 0.5 to 1.2 mm, and the thickness of the outer tube is preferably about 0.6 to 1.8 mm.
  • the inner tube has a thickness of 0.6 to 1.0 mm and the outer tube has a thickness of 0.8 to 1.5 mm.
  • Example 1 Examples of the double pipe for heat exchanger will be described with reference to FIGS.
  • the double pipe 1 of this example has a double pipe structure in which an inner pipe 2 is disposed inside an outer pipe 10, and a fluid flowing inside the inner pipe 2 and an inner pipe 2. It is a double tube for heat exchangers for performing heat exchange between the fluid flowing between the outer tube 10 and the outer tube 10.
  • the inner tube 2 has a shape in which the cross-sectional shape has two convex portions 21 that are deformed so that a part of the circumference of the circle protrudes outward of the circle. . Furthermore, it has a shape in which the position of the convex portion 21 is displaced spirally in the longitudinal direction.
  • the outer tube 10 has a smooth tube shape with a circular cross section. As shown in FIG. 3, the inner peripheral surface of the outer tube 10 is in contact with the apex portion 210 of the convex portion 21 of the inner tube 2, and there are two circumferential directions between the outer tube 10 and the inner tube 2. A partitioned outer flow path 31 is formed.
  • the double tube 1 was produced as follows. First, two extruded smooth tubes having an outer diameter of 10 mm ⁇ , a thickness of 1.0 mm, and a length of 500 mm made of material A3003 were prepared as materials. One of them was used as a material for an inner tube, 100 mm from both ends was passed through a die having an inner diameter of 8 mm ⁇ , diameter reduction processing was performed, and pretreatment for drawing processing was performed.
  • the inner tube 2 was formed.
  • the obtained inner tube 2 has a cross-sectional shape orthogonal to the axial direction deformed so that a part of the circumference of the circle protrudes outward of the circle at any position.
  • the shape which has two convex parts 21 is exhibited.
  • each part is connected by a smooth curved surface, and the vertex part 210 of the convex part 21 is an arcuate curved surface.
  • a circular boundary line 26 inscribed in the cross-sectional shape can be seen on the inner side of the cross-sectional shape, and on the outer side of the cross-sectional shape, A circular boundary line 27 circumscribing can be seen.
  • These boundary lines 26 and 27 are generated because the minimum diameter portion and the maximum diameter portion of each portion are displaced in the circumferential direction due to the spiral twist of the inner tube 2.
  • the diameter d1 of the boundary line 26 is 5 mm
  • the diameter d2 of the boundary line 27 is 8 mm.
  • the angle ⁇ of the direction b of the helical displacement of the inner tube 2 obtained with respect to the axial direction a is approximately 30 °.
  • the remaining one extruded smooth tube is used as a material for an outer tube (hereinafter simply referred to as an outer tube 10), and the inner tube 2 is inserted therein to form a double tube structure. .
  • an outer tube 10 there is a difference between the inner diameter of the outer tube 10 and the outer diameter of the inner tube 2. Therefore, the outer tube 10 and the inner tube 2 are joined and integrated by passing the outer tube 10 through a die having a circular inner hole having an inner diameter of 9 mm and reducing the diameter of the outer tube 10. Thereby, the double pipe 1 of this example is obtained.
  • the double pipe 1 is composed of the spirally twisted inner pipe 2 having a special shape and the outer pipe 10 made of a circular smooth pipe.
  • the apex portions 210 of the two convex portions 21 of the inner tube are in contact with the inner peripheral surface of the outer tube 10.
  • the inside of the inner tube 2 also becomes an inner flow path 32 having an outer wall that is twisted in a spiral shape. Therefore, if a fluid (refrigerant) is caused to flow in each of the outer flow path 31 and the inner flow path 32 of the double pipe 1, the fluid flows in both flow paths while causing moderate turbulence, and heat can be exchanged efficiently. it can.
  • a fluid refrigerant
  • the double pipe 1 is integrated with the inner pipe 2 and the outer pipe 10 in contact with each other. Therefore, even if vibration occurs when the heat exchange cycle incorporating the double pipe 1 is operated, the inner pipe 2 and the outer pipe 20 collide with each other in the double pipe 1 to reliably prevent noise. it can.
  • the double pipe 1 for a heat exchanger that can be used without generating noise during operation and has a structure that can exhibit excellent heat exchange performance.
  • the double pipe 1 of the present example has an inner pipe 2 having equally spaced convex portions 21 that are deformed so that a part of the circumference of a circle has a circular shape projecting outward of the circle. The shape which has four places is exhibited. Therefore, as shown in FIG. 5, outer flow paths 31 are formed between the outer tube 10 and the inner tube 2 at equal intervals in four circumferential directions.
  • the double pipe 1 of this example uses an outer tube material made of material A3003 with an outer diameter of 21 mm ⁇ and a wall thickness of 1.2 mm, and an inner tube material made of material A3003 with an outer diameter of 19 mm ⁇ and a wall thickness of 1.2 mm.
  • Example 1 The specific shape of the double tube 1 of this example is that the outer diameter of the outer tube 10 is 20.4 mm and the wall thickness is 1.2 mm. Further, the inner diameter d1 of the inner tube 2 without the convex portion 21 is 12.7 mm, the outer diameter d2 of the inner tube 2 with the convex portion 21 is 18 mm, and the outer diameter of the inner tube 2 without the convex portion 21. d3 is 15.1 mm and the wall thickness is 1.2 mm. Also with the double pipe 1 of this example, the same effect as Example 1 can be show
  • the double pipe 1 of the present example has inner pipes 2 having convex portions 21 that are deformed so that a part of the circumference of a circle having a cross-sectional shape protrudes outward from the circle. The shape which has eight places is exhibited. Therefore, as shown in FIG. 6, outer flow paths 31 are formed between the outer tube 10 and the inner tube 2 at equal intervals in eight circumferential directions.
  • the double pipe 1 of this example uses an outer tube material made of material A3003 with an outer diameter of 23 mm ⁇ and a wall thickness of 1.3 mm, and an inner tube material made of material A3003 with an outer diameter of 21 mm ⁇ and a wall thickness of 1.2 mm.
  • the specific shape of the double tube 1 of this example is that the outer diameter of the outer tube 10 is 22 mm and the wall thickness is 1.3 mm. Further, the inner diameter d1 of the portion without the convex portion 21 in the inner tube 2 is 13.6 mm, the outer diameter d2 of the portion with the convex portion 21 in the inner tube 2 is 19.4 mm, and the portion of the inner tube 2 where the convex portion 21 is absent. The outer diameter d3 is 16 mm and the wall thickness is 1.2 mm. Also with the double pipe 1 of this example, the same effect as Example 1 can be show

Landscapes

  • 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

La présente invention concerne une double tuyauterie (1) qui est destinée à un échangeur thermique, qui comporte une structure de double tuyauterie formée en disposant une tuyauterie interne (2) dans une tuyauterie externe (10), et permet l'échange de chaleur entre un fluide qui s'écoule à l'intérieur de la tuyauterie interne (2) et un fluide qui s'écoule entre la tuyauterie interne (2) et la tuyauterie externe (10). La forme en coupe de la tuyauterie interne (2) présente une forme comportant deux sections convexes (21) au niveau desquelles une partie du périmètre d'un cercle est déformée de façon à faire saillie vers l'extérieur du cercle, et les positions des sections convexes (21) dans la direction de la longueur ont une forme hélicoïdalement déplacée. La forme en coupe de la tuyauterie externe (10) présente une forme de tuyauterie lisse circulaire. La surface périphérique interne de la tuyauterie externe (10) est en contact avec les parties apicales (210) des sections saillantes (21) de la tuyauterie interne (2), et un tuyau externe (31) qui est compartimentalisé dans la direction périphérique est formé entre la tuyauterie externe (10) et la tuyauterie interne (2).
PCT/JP2011/065650 2010-08-02 2011-07-08 Double tuyauterie pour échangeur thermique WO2012017777A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2010173249 2010-08-02
JP2010-173249 2010-08-02
JP2011-137917 2011-06-22
JP2011137917A JP2012052784A (ja) 2010-08-02 2011-06-22 熱交換器用二重管

Publications (1)

Publication Number Publication Date
WO2012017777A1 true WO2012017777A1 (fr) 2012-02-09

Family

ID=45559287

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2011/065650 WO2012017777A1 (fr) 2010-08-02 2011-07-08 Double tuyauterie pour échangeur thermique

Country Status (2)

Country Link
JP (1) JP2012052784A (fr)
WO (1) WO2012017777A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021117725A1 (fr) * 2019-12-13 2021-06-17 株式会社Uacj Tuyau double pour échangeur de chaleur

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6172950B2 (ja) * 2012-02-01 2017-08-02 株式会社Uacj 熱交換器用二重管
JP5945824B2 (ja) * 2012-07-23 2016-07-05 株式会社日本自動車部品総合研究所 内燃機関の燃料供給装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002318015A (ja) * 2001-04-17 2002-10-31 Orion Mach Co Ltd 冷凍装置
JP2006162241A (ja) * 2004-11-09 2006-06-22 Denso Corp 二重管、その製造方法、およびそれを備える冷凍サイクル装置
JP2008232449A (ja) * 2007-03-16 2008-10-02 Sumitomo Light Metal Ind Ltd 二重管式熱交換器及びその製造方法

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3239833B2 (ja) * 1998-02-25 2001-12-17 三菱マテリアル株式会社 異形管の製造方法
JP2008267791A (ja) * 2007-03-27 2008-11-06 Kobelco & Materials Copper Tube Inc 漏洩検知管およびそれを用いた熱交換器

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002318015A (ja) * 2001-04-17 2002-10-31 Orion Mach Co Ltd 冷凍装置
JP2006162241A (ja) * 2004-11-09 2006-06-22 Denso Corp 二重管、その製造方法、およびそれを備える冷凍サイクル装置
JP2008232449A (ja) * 2007-03-16 2008-10-02 Sumitomo Light Metal Ind Ltd 二重管式熱交換器及びその製造方法

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021117725A1 (fr) * 2019-12-13 2021-06-17 株式会社Uacj Tuyau double pour échangeur de chaleur
JP2021096011A (ja) * 2019-12-13 2021-06-24 株式会社Uacj 熱交換器用二重管

Also Published As

Publication number Publication date
JP2012052784A (ja) 2012-03-15

Similar Documents

Publication Publication Date Title
JP6172950B2 (ja) 熱交換器用二重管
JP2007032949A (ja) 熱交換器
JP2008164245A (ja) 熱交換器
JP2011027285A (ja) 熱交換器およびその製造方法と熱交換器を具備する物品貯蔵装置
WO2011162170A1 (fr) Tube double pour échangeur thermique
JP2009243715A (ja) 漏洩検知管および熱交換器
JP2009103393A (ja) 熱交換器
JP5911597B2 (ja) 扁平形状伝熱管、それを備えたクロスフィンチューブ型熱交換器の製造方法、その方法で製造されたクロスフィンチューブ型熱交換器
WO2012017777A1 (fr) Double tuyauterie pour échangeur thermique
JP2009041798A (ja) 熱交換器
JP5709733B2 (ja) 二重管
JP2005030619A (ja) 二重管およびこれを用いた二重管式熱交換器
JP2012102928A (ja) 熱交換器およびこれを備えた車両用空調装置
JP4947162B2 (ja) 熱交換器
WO2013118762A1 (fr) Échangeur de chaleur du type à tubes à ailettes
JP2010203726A (ja) 熱交換器、空気調和機
JP2012007771A (ja) 熱交換器
JP2006234355A (ja) 熱交換器
JP2012007773A (ja) 熱交換器
JP2009250600A (ja) 銅製扁平伝熱管
JP2011099620A (ja) 熱交換器
JP5533328B2 (ja) 熱交換器
JP5540683B2 (ja) 熱交換器及びそれを備えた給湯機
JP2007032943A (ja) 複合伝熱管
JP2005321122A (ja) 管型熱交換器

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11814407

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 11814407

Country of ref document: EP

Kind code of ref document: A1