EP3239638A1 - Tuyau double - Google Patents

Tuyau double Download PDF

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Publication number
EP3239638A1
EP3239638A1 EP17168237.0A EP17168237A EP3239638A1 EP 3239638 A1 EP3239638 A1 EP 3239638A1 EP 17168237 A EP17168237 A EP 17168237A EP 3239638 A1 EP3239638 A1 EP 3239638A1
Authority
EP
European Patent Office
Prior art keywords
pipe
inner pipe
cooling medium
extends
double
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP17168237.0A
Other languages
German (de)
English (en)
Inventor
Takeshi Ito
Hirotaka KAJIZUKA
Naoto Hayashi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Japan Co Ltd
Original Assignee
Valeo Japan Co Ltd
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 Valeo Japan Co Ltd filed Critical Valeo Japan Co Ltd
Publication of EP3239638A1 publication Critical patent/EP3239638A1/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • F28D7/14—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 both tubes being bent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • 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
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section

Definitions

  • the present invention relates to a double pipe used as an internal heat exchanger of a refrigeration cycle to be mounted in a vehicle.
  • Patent Literature 1 Japanese Patent Literature 2
  • Patent Literature 2 as an internal heat exchanger for heat exchange between a high pressure medium and a low pressure medium to improve the refrigeration efficiency of a refrigeration cycle.
  • Patent Literature 1 and Patent Literature 2 have an outer pipe and an inner pipe inserted into the outer pipe and perform heat exchange between a high pressure medium flowing through the passage between the outer pipe and the inner pipe and a low pressure medium flowing through the inner pipe.
  • the inner pipe having an outer diameter smaller than an inner diameter of the outer pipe is used.
  • vibrations of the vehicle are transferred to the double pipe, however, the outer pipe and the inner pipe vibrate individually and make contact with each other, possibly generating abnormal sound or damaging the outer pipe or the inner pipe.
  • the double pipe is configured so as to have a straight pipe portion and bent portions disposed on both sides of the straight pipe portion.
  • the outer surface (outer periphery) of the inner pipe does not make contact with the inner surface (inner periphery) of the outer pipe or the outer surface of the inner pipe makes contact with the inner surface of the outer pipe only on one side.
  • the bent portions the cross sections of the outer pipe and the inner pipe are flattened and the inner peripheral surface of the outer pipe makes contact with the outer peripheral surface of the inner pipe in radial directions.
  • the double pipe has such a structure to fix the outer pipe and the inner pipe.
  • the outer pipe and the inner pipe are flattened while being brought into contact with each other, the passage between the outer pipe and the inner pipe through which a high pressure medium passes is also deformed by a bending process.
  • the outer bent sides of the outer pipe and the inner pipe are stretched and brought into substantially close contact with each other, making it difficult to obtain a sufficient passage.
  • Patent Literature 1 has the structure in which the outer surface (outer periphery) of the inner pipe and the inner surface (inner periphery) of the outer pipe are fixed by bringing the outer and inner surfaces into contact with each other at a plurality of points in a radial direction in the straight pipe portion and, in the bent portion, a sufficient space is provided for the outer pipe and the inner pipe so that these pipes do not make contact with each other even when the pipes are bent and flattened or the pipes make contact with each other only at one point in the radial direction.
  • An object of the invention is to provide a double pipe that suppresses an increase in the passage resistance and has high pressure strength in bent portions.
  • a double pipe (10) used as an internal heat exchanger (5) of a refrigeration cycle (1) to be mounted in a vehicle the double pipe including an outer pipe (20) and an inner pipe (30) disposed on an inner side of the outer pipe, in which, in a bent portion (C) in which the outer pipe and the inner pipe are bent, the inner pipe does not make contact with the outer pipe or the inner pipe makes contact with the outer pipe at one point in a radial direction, and in which a convex and/or concave rib (R1, R2, R3) having a predetermined length is formed in an outer bent portion of the inner pipe (first aspect).
  • a high pressure medium passes through the passage between the outer pipe and the inner pipe and a low pressure medium passes through the inner pipe for heat exchange.
  • the rib preferably extends in a direction substantially orthogonal to a direction in which the inner pipe extends (second aspect).
  • the rib can receive a pressure in a direction in which the inner pipe is crushed and transfer the pressure to the inner pipe, thereby improving the proof strength.
  • the rib preferably extends obliquely with respect to a direction in which the inner pipe extends (third aspect).
  • the rib can receive a pressure in a direction in which the inner pipe is crushed, transfer the pressure to the inner pipe, and distribute the pressure in the direction in which the inner pipe extends, thereby improving the proof strength.
  • the rib is preferably part of a first groove (S1) extending spirally with respect to the direction in which the inner pipe extends (fourth aspect).
  • the rib can receive a pressure in a direction in which the inner pipe is crushed, transfer the pressure to the inner pipe, and distribute the pressure more surely in the direction in which the inner pipe extends, thereby improving the proof strength.
  • the inner pipe preferably has, in a straight pipe portion in which the outer pipe and the inner pipe are not bent, a second groove (S2) extending spirally with respect to the direction in which the inner pipe extends, and in which a direction in which the first groove extends spirally is preferably the same as a direction in which the second groove extends spirally (fifth aspect).
  • the rib preferably extends along the direction in which the inner pipe extends (sixth aspect).
  • the rib can receive a pressure in a direction in which the inner pipe is crushed and distribute the pressure in the direction in which the inner pipe extends, thereby improving the proof strength.
  • a plurality of the ribs or a plurality of the first grooves is preferably formed in the inner pipe (seventh aspect).
  • the proof strength can be further improved against the pressure in which the inner pipe is crushed.
  • Fig. 1 illustrates an example of a refrigeration cycle 1 having a double pipe 10 described below.
  • This refrigeration cycle 1 is a part of an in-vehicle air conditioner (not illustrated) to be mounted in a vehicle.
  • the refrigeration cycle 1 includes a compressor 2 compressing a cooling medium, a condenser 3 cooling the cooling medium compressed by the compressor 2, a gas-liquid separator 4 extracting only a liquid cooling medium by performing the gas-liquid separation of the cooling medium cooled by the condenser 3, an expansion device 6 expanding the liquid cooling medium by decompressing the liquid cooling medium, and an evaporator 7 evaporating the cooling medium decompressed by the expansion device 6.
  • the refrigeration cycle 1 is provided with an internal heat exchanger 5 including a high pressure cooling medium passage 51 through which the cooling medium from the gas-liquid separator 4 to the expansion device 6 passes and a low pressure cooling medium passage 52 through which the cooling medium from the evaporator 7 to the compressor 2 passes.
  • the internal heat exchanger 5 can reduce the enthalpy of the cooling medium flowing through the evaporator 7 and improve the cooling capacity of the refrigeration cycle 1.
  • the refrigeration cycle 1 includes a pipe 61 making direct or indirect connection between the compressor 2 and the condenser 3, a pipe 62 making direct or indirect connection between the condenser 3 and the gas-liquid separator 4, a pipe 63 making direct or indirect connection between the gas-liquid separator 4 and the high pressure cooling medium passage 51 of the internal heat exchanger 5, a pipe 64 making direct or indirect connection between the high pressure cooling medium passage 51 of the internal heat exchanger 5 and the expansion device 6, a pipe 65 making direct or indirect connection between the expansion device 6 and the evaporator 7, a pipe 66 making direct or indirect connection between the evaporator 7 and the low pressure cooling medium passage 52 of the internal heat exchanger 5, and a pipe 67 making direct or indirect connection between the low pressure cooling medium passage 52 of the internal heat exchanger 5 and the compressor 2 to configure a cycle through which cooling medium is capable of circulating.
  • the gas-liquid separator 4 is a component different from the condenser 3 in this example, the gas-liquid separator 4 may be integrated with the condenser 3.
  • the pipe 65 is provided between the expansion device 6 and the evaporator 7, the expansion device 6 may be directly connected to the evaporator 7 by omitting the pipe 65.
  • a high-temperature and high-pressure cooling medium is discharged, flows through the condenser 3, the gas-liquid separator 4, and the high pressure cooling medium passage 51 of the internal heat exchanger 5 as indicated by the hollow arrows in Fig. 1 , and reaches the expansion device 6.
  • the cooling medium expanded by the expansion device 6 becomes a low-temperature and low-pressure cooling medium, flows through the evaporator 7 and the low pressure cooling medium passage 52 of the internal heat exchanger 5 as indicated by the solid arrows in Fig. 1 , and reaches the compressor 2 to circulate.
  • Fig. 2 is a cross sectional view schematically illustrating, as the first embodiment, the double pipe 10 used as the internal heat exchanger 5 in Fig. 1 .
  • the double pipe 10 has an outer pipe 20 made of aluminum alloy and an inner pipe 30, made of aluminum alloy, that is disposed inside the outer pipe 20 and has straight pipe portions B1 and B2 and a bent portion C.
  • the bent portion C is configured so that the inner pipe 30 does not make contact with the outer pipe 20 or the inner pipe 30 makes contact with the outer pipe 20 at one point in a radial direction.
  • the only one bent portion C is present and the bent portion C has substantially a right angle in the first embodiment, the number of the bent portions C and the angle are not particularly limited in the invention.
  • the space between the outer pipe 20 and the inner pipe 30 is the high pressure cooling medium passage 51 through which a high pressure cooling medium passes and the inside of the inner pipe 30 is the low pressure cooling medium passage 52 through which a low pressure cooling medium passes.
  • the outer pipe 20 includes an input hole 22 through which the high pressure cooling medium flows in and a high pressure cooling medium lead-in pipe 21, connected to the pipe 63, that guides the high pressure cooling medium to the input hole 22.
  • the outer pipe 20 further includes an output hole 23 through which the high pressure cooling medium flows out and a high pressure cooling medium lead-out pipe 24 guiding the high pressure cooling medium led out of the output hole 23 to the pipe 64.
  • the outer peripheries of the inner pipe 30 are sealed by sealing portions 25 and 26.
  • a spiral groove S2 is formed in each of the straight pipe portions B1 and B2. This causes the high pressure cooling medium flowing through the high pressure cooling medium passage 51 to flow while spirally rotating and part of the low pressure cooling medium flowing through the low pressure cooling medium passage 52 to flow while spirally rotating, thereby achieving efficient heat exchange.
  • the high pressure cooling medium travels while rotating counterclockwise with respect to the travel direction.
  • the spiral groove S2 preferably makes contact with the inner peripheral surface of the outer pipe 20 as illustrated in Fig. 2 or substantially makes contact with the inner peripheral surface. This prevents the high pressure cooling medium from being short-circuited in the direction in which the double pipe 10 extends, thereby obtaining high heat exchange efficiency.
  • the high pressure cooling medium and the low pressure cooling medium as the cooling medium flow in mutually opposite directions.
  • Fig. 3 illustrates the bent portion in the first embodiment
  • Fig. 3A is a diagram seen from arrow A in Fig. 2
  • Fig. 3B is a cross sectional view of range C in Fig. 2
  • Fig. 3C is a cross sectional view taken along line X-X in Fig. 2 .
  • the outer pipe 20 and the inner pipe 30 are flattened in the bent portion and the flatness is high (further flattened) particularly on the outer bent side (upper side in the drawing).
  • Figs. 3 illustrates the bent portion in the first embodiment
  • Fig. 3A is a diagram seen from arrow A in Fig. 2
  • Fig. 3B is a cross sectional view of range C in Fig. 2
  • Fig. 3C is a cross sectional view taken along line X-X in Fig. 2 .
  • the outer pipe 20 and the inner pipe 30 are flattened in the bent portion and the flatness is high (further flattened) particularly on the outer
  • ribs R1 are concave on the outside of the bent portion and extend in a direction substantially orthogonal to the direction in which the inner pipe 30 extends.
  • a rib length LR1 of the ribs R1 is preferably smaller than, but substantially equal to a width LIN of the inner pipe 30. Even when the pressure of the high pressure cooling medium flowing through the high pressure cooling medium passage 51 is applied to the flattened portion, the pressure is received by the ribs R1. The pressure is transferred to the left and right sides of the inner pipe 30 in Fig. 3C to prevent the inner pipe 30 from being broken by the pressure of the high pressure cooling medium.
  • the ribs R1 may be convex on the outside of the bent portion and may extend in a direction substantially orthogonal to the direction in which the inner pipe 30 extends. The direction in which the ribs R1 are formed is selected as appropriate.
  • the plurality of ribs R1 are preferably formed to improve the proof strength against the pressure.
  • Fig. 4A is a diagram seen from arrow A in Fig. 2
  • Fig. 4B is a cross sectional view illustrating range C in Fig. 2
  • Fig. 4C is a cross sectional view taken along line X-X in Fig. 2 .
  • the outer pipe 20 and the inner pipe 30 are flattened in the bent portion and the flatness is high (further flattened) particularly in the outer bent side (upper side in the drawing).
  • ribs R2 are concave on the outside of the bent portion and extend obliquely with respect to the direction in which the inner pipe 30 extends.
  • a rib length LR2 of the ribs R2 is preferably smaller than, but substantially equal to the width LIN of the inner pipe 30. After receiving the pressure, the ribs R2 transfer the pressure to the left and right sides of the inner pipe 30 in Fig. 4C . In addition, since the plurality of ribs R2 are formed, the received pressure can be distributed along the direction in which the inner pipe 30 extends. As a result, it is possible to prevent the inner pipe 30 from being broken by the pressure of the high pressure cooling medium.
  • the ribs R2 may be concave on the outside of the bent portion and may extend in a direction substantially orthogonal to the direction in which the inner pipe 30 extends. The direction in which the ribs R2 are formed is selected as appropriate.
  • Fig. 5A is a diagram seen from arrow A in Fig. 2
  • Fig. 5B is a cross sectional view illustrating range C in Fig. 2
  • Fig. 5C is a cross sectional view taken along line X-X in Fig. 2 .
  • the outer pipe 20 and the inner pipe 30 are flattened in the bent portion and the flatness is high (further flattened) particularly on the outer bent side (upper side in the drawing).
  • Figs. 5A is a diagram seen from arrow A in Fig. 2
  • Fig. 5B is a cross sectional view illustrating range C in Fig. 2
  • Fig. 5C is a cross sectional view taken along line X-X in Fig. 2 .
  • the outer pipe 20 and the inner pipe 30 are flattened in the bent portion and the flatness is high (further flattened) particularly on the outer bent side (upper side in the drawing).
  • the ribs R2 are concave on the outside of the bent portion and extend obliquely with respect to the direction in which the inner pipe 30 extends.
  • the ribs R2 are formed as part of a spiral groove S1 (first spiral groove) in the third embodiment.
  • the ribs R2 transfer the pressure to the left and right sides of the inner pipe 30 in Fig. 5C .
  • the pressure received by the ribs R2 can be distributed in the direction in which the inner pipe 30 extends via the spiral groove S1. As a result, it is possible to prevent the inner pipe 30 from being broken by the pressure of the high pressure cooling medium.
  • the high pressure cooling medium travels while rotating counterclockwise with respect to the travel direction.
  • This rotation direction is the same as that of the high pressure cooling medium flowing through the spiral grooves S2 formed in the straight pipe portions B1 and B2 illustrated in Fig. 2 .
  • the rotation direction (rotation direction of the spiral groove S1 with respect to the direction in which the inner pipe 30 extends) of the spiral groove S1 illustrated in the third embodiment is preferably the same as the rotation direction of the spiral grooves S2 (second spiral grooves) of the straight pipe portions B1 and B2.
  • An increase in the passage resistance can be suppressed by making the flow direction (that is, the rotation direction of the spiral) of the high pressure cooling medium in the straight pipe portions identical to the flow direction (that is, the rotation direction of the spiral) of the high pressure cooling medium in the bent portion.
  • Fig. 6A is a diagram seen from arrow A in Fig. 2
  • Fig. 6B is a cross sectional view illustrating range C in Fig. 2
  • Fig. 6C is a cross sectional view taken along line X-X in Fig. 2 .
  • the outer pipe 20 and the inner pipe 30 are flattened in the bent portion and the flatness is high (further flattened) particularly in the outer bent side (upper side in the drawing).
  • Figs. 6A is a diagram seen from arrow A in Fig. 2
  • Fig. 6B is a cross sectional view illustrating range C in Fig. 2
  • Fig. 6C is a cross sectional view taken along line X-X in Fig. 2 .
  • the outer pipe 20 and the inner pipe 30 are flattened in the bent portion and the flatness is high (further flattened) particularly in the outer bent side (upper side in the drawing).
  • a rib R3 is concave on the outside of the bent portion and extends along the direction in which the inner pipe 30 extends. After receiving the pressure of the high pressure cooling medium, the rib R3 can distribute the pressure across a length LR3 of the rib R3 in the direction in which the inner pipe 30 extends. As a result, it is possible to prevent the inner pipe 30 from being broken by the pressure of the high pressure cooling medium.
  • the rib R3 may be convex on the outside of the bent portion and may extend in a direction substantially orthogonal to the direction in which the inner pipe 30 extends. The direction in which the rib R3 is formed is selected as appropriate.
  • Fig. 7 is a cross sectional view schematically illustrating a double pipe 100 used to describe the related art.
  • the double pipe 100 has an outer pipe 200 made of aluminum alloy and an inner pipe 300, made of aluminum alloy, that is disposed inside the outer pipe 200 and has straight pipe portions B1' and B2' and a bent portion C'.
  • the bent portion C' is configured so that the inner pipe 300 does not make contact with the outer pipe 200 or the inner pipe 300 makes contact with the outer pipe 200 at one point in the radial direction.
  • the space between the outer pipe 200 and the inner pipe 300 is the high pressure cooling medium passage 51 through which a high pressure cooling medium passes and the inside of the inner pipe 300 is the low pressure cooling medium passage 52 through which a low pressure cooling medium passes.
  • Fig. 8A is a cross sectional view taken along line Y-Y in Fig. 7 and Fig. 8B is a cross sectional view illustrating the state of the double pipe broken by the high pressure cooling medium.
  • the outer pipe 200 and the inner pipe 300 are flattened in the bent portion and the flatness is high (further flattened) particularly on the outer bent side (upper side in the drawing) .
  • pressure Ph of the high pressure cooling medium is applied to the flattened part of the inner pipe 300.
  • the inner pipe 300 receives a force so as to be crashed since there is a difference between the pressures. Since the inner pipe 300 does not have ribs unlike the invention, a portion having the higher flatness is first crashed inside as illustrated in Fig. 8B , possibly generating a damaged portion D. A breakage such as the damaged portion D causes a short circuit between the high pressure cooling medium passage 51 and the low pressure cooling medium passage 52, which should be separated from each other, so the cooling medium discharged from the compressor 2 returns to the compressor 2 without passing through the expansion device 6 and the evaporator 7 and the refrigeration cycle 1 cannot provide the normal cooling capability.
  • the in-vehicle air conditioner according to the invention can be manufactured industrially and treated as the target of business transaction, the in-vehicle air conditioner has economic value and can be utilized industrially.

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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)
EP17168237.0A 2016-04-27 2017-04-26 Tuyau double Withdrawn EP3239638A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2016089790A JP2017198392A (ja) 2016-04-27 2016-04-27 二重管

Publications (1)

Publication Number Publication Date
EP3239638A1 true EP3239638A1 (fr) 2017-11-01

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP17168237.0A Withdrawn EP3239638A1 (fr) 2016-04-27 2017-04-26 Tuyau double

Country Status (3)

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EP (1) EP3239638A1 (fr)
JP (1) JP2017198392A (fr)
CN (1) CN107421164A (fr)

Cited By (2)

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EP3722723A1 (fr) * 2019-04-08 2020-10-14 Hamilton Sundstrand Corporation Échangeur de chaleur courbe
US20220290925A1 (en) * 2019-10-23 2022-09-15 Uacj Corporation Heat-transferring double pipe, inner pipe for heat-transferring double pipe, and manufacturing method thereof

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KR102403434B1 (ko) * 2017-08-18 2022-05-27 조한용 이중 파이프
JP2020012619A (ja) * 2018-07-20 2020-01-23 株式会社ヴァレオジャパン 二重管式熱交換器
CN109282675B (zh) * 2018-08-23 2020-02-14 常州市盛士达汽车空调有限公司 套管式热交换器及其制造方法和模具
CN110285600B (zh) * 2019-05-15 2021-12-17 中国电子科技集团公司第十一研究所 采用双层肋片式热交换器的j-t制冷器
CN114791234B (zh) * 2022-04-21 2024-06-21 桂林电子科技大学 一种管壳程变体积同轴套管热交换器

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Publication number Priority date Publication date Assignee Title
EP1096131A1 (fr) * 1999-10-26 2001-05-02 Senior Flexonics Automotive Limited Refroidisseur de recirculation de gaz d'échappement
EP1136780A2 (fr) * 2000-03-23 2001-09-26 Senior Investments AG Echangeur de chaleur à tubes doubles
JP2005055064A (ja) * 2003-08-04 2005-03-03 Toyo Radiator Co Ltd 二重管型熱交換器およびその製造方法
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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
GB2451862A (en) * 2007-08-15 2009-02-18 Senior Uk Ltd High gas inlet temperature EGR system
WO2009034833A1 (fr) * 2007-09-10 2009-03-19 Usui Kokusai Sangyo Kaisha Limited Structure de tubulure d'urée-eau pour un dispositif de purification d'échappement pour un moteur à combustion interne
JP2013113525A (ja) 2011-11-30 2013-06-10 Watanabe Seisakusho:Kk 二重管

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3722723A1 (fr) * 2019-04-08 2020-10-14 Hamilton Sundstrand Corporation Échangeur de chaleur courbe
US20220290925A1 (en) * 2019-10-23 2022-09-15 Uacj Corporation Heat-transferring double pipe, inner pipe for heat-transferring double pipe, and manufacturing method thereof

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JP2017198392A (ja) 2017-11-02

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