WO2001014817A1 - Tube a echange thermique - Google Patents

Tube a echange thermique Download PDF

Info

Publication number
WO2001014817A1
WO2001014817A1 PCT/JP2000/001937 JP0001937W WO0114817A1 WO 2001014817 A1 WO2001014817 A1 WO 2001014817A1 JP 0001937 W JP0001937 W JP 0001937W WO 0114817 A1 WO0114817 A1 WO 0114817A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
heat transfer
medium
flow path
heat exchanger
Prior art date
Application number
PCT/JP2000/001937
Other languages
English (en)
Japanese (ja)
Inventor
Akihiko Takano
Original Assignee
Bosch Automotive Systems Corporation
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 Bosch Automotive Systems Corporation filed Critical Bosch Automotive Systems Corporation
Publication of WO2001014817A1 publication Critical patent/WO2001014817A1/fr

Links

Classifications

    • 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
    • F28F1/14—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 longitudinally
    • F28F1/16—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 longitudinally the means being integral with the element, e.g. formed by extrusion
    • 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
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features

Definitions

  • the present invention relates to a tube for a heat exchanger that performs heat exchange by radiating heat by a medium flowing between heat exchange cycles.
  • the medium taken in from one header pipe flows through the medium flow path inside the heat exchange tube, and the medium transfers heat to the fin mounted on the tube surface and between the tubes, and exchanges heat with the outside air. After that, it is discharged from the other header pipe.
  • the heat exchange tube used in this type of heat exchanger is formed by using an aluminum and / or aluminum alloy or the like as a material and using a manufacturing method such as extrusion molding.
  • the heat exchanger includes a fin that is in contact with the heat exchange tube, and the cross section of the heat exchange tube has a flat shape in order to increase the contact area between the heat exchange tube and the fin. And a structure in which a plurality of medium flow paths are formed in the flat tube.
  • CFC-based refrigerants cause destruction of the ozone layer, and there has been an increasing demand for the ban on the use and reduction of these refrigerants.
  • refrigerant of the full B down system for example, heat exchange cycle to the C 0 2 and refrigerant is used.
  • the C ⁇ 2 was used in a refrigeration cycle as a refrigerant, it high-temperature and high-pressure In order to radiate heat from the refrigerant, the state of the refrigerant when flowing through the heat exchanger is in the supercritical region beyond the critical point of the gas-liquid two-phase state, and the refrigerant in the normal gas-liquid two-phase state It is assumed that excessive pressure will be applied to the heat exchanger as compared with the case where the water flows through the heat exchanger.
  • the heat exchanger for emitting volatilizing the heat radiating function of the refrigerant becomes high temperature and high pressure, as compared with the case where refrigerant in a gas-liquid mixed state is flowing, 6 times It is considered that the above pressure resistance is required.
  • the invention described in Japanese Patent Application Laid-Open No. H10-3116997 discloses a radiator for exchanging heat of a medium in a supercritical state, and uses c co 2 as a refrigerant.
  • the members such as heat exchanger tubes and header pipes through which the refrigerant flows are made thicker to ensure the pressure resistance ( however, As shown in FIG. 11, when the thickness of the tube 27 and the thickness of the header pipe 4 are increased, the inner diameter of the medium flow path of the header pipe 4 is reduced, and the medium flow of the header pipe 4 is reduced.
  • the insertion part 27 e of the tube inserted into the header pipe 4 becomes smaller, regardless of the tube insertion part 27 e, the end of the tube 27 abuts and the header pipe It may be possible to communicate with the medium flow path, but a pair is required to prevent medium leakage. It is difficult to regulate the length of the tube to be joined between the header pipes 4.
  • the tube is inserted into the tube insertion hole formed in the header pipe by inserting the tube end. Connected.
  • a heat transfer expansion portion 27a that does not form a medium flow path is provided at both ends of the cross section of the tube.
  • a tube provided with an insertion part 27e that cuts the heat transfer expansion part 27a to fit into the tube insertion hole of the header pipe 4 is considered.
  • the “sparse” part of the extrusion mold has less resistance due to the mold, so the material concentrates on the “sparse” part and the “dense” part.
  • the problem is that the product yield is poor when extruded with the same pressure, because the material does not evenly spread over the part where it is.
  • an object of the present invention is to provide a tube for a heat exchanger, which has a high pressure resistance requirement, has good moldability and is excellent in heat exchange performance.
  • the invention described in claim 1 of the present application is directed to a heat exchanger tube provided with a medium flow path through which a medium flows in the longitudinal direction, wherein the tube has a transmission path in which the medium flow path is not formed at both ends or one end of the tube cross section. It is a tube for a heat exchanger having a heat expansion section, and a heat transfer expansion section having a hole through which a medium does not flow.
  • the mold for dispensing is in a “dense” state in which a mandrel (core material) is provided in the area where the refrigerant flow path is formed, and no member is provided in the area where the heat transfer expansion section is formed. There is no sparse, and the status is “sparse”.
  • the extruded material is concentrated on the “sparse” portion, and is “sparse”. Since the part has less resistance due to the mold, the fluidity of the material is improved, and the material is not evenly distributed, which may result in poor molding of the tube.
  • the core material is also provided and extruded at the expanded heat transfer portion of the tube, so that the material is evenly distributed over the expanded heat transfer portion of the tube, and the moldability of the tube is improved. I do.
  • the tube can be formed without causing molding failure or failure of the mandrel.
  • the molded tube expands its heat transfer. Since the hole is formed in the part, the required pressure resistance is secured and the heat transfer area is expanded, so that the heat exchange performance is improved, the members are lighter, and the manufacturing cost is reduced. It can be reduced.
  • the thickness of the tube from the outer surface of the tube to the inner surface of the hole through which the medium does not flow is equal to the thickness of the tube. It is formed larger than the wall thickness of the tube extending from the outer surface of the tube to the inner surface of the refrigerant channel.
  • the thickness of the tube from the outer surface of the tube to the inner surface of the hole through which the medium does not flow is from the outer surface of the tube. If the tube is configured to be thicker than the tube reaching the hole of the tube, the heat resistance will not increase due to the thickness of the tube, so that heat transfer can be secured and heat exchange performance can be improved. Becomes possible.
  • the invention described in claim 3 of the present application is directed to a heat exchanger tube provided with a medium flow path through which a medium flows in the longitudinal direction, wherein the tube has a medium flow path not formed at both ends or one end of the tube cross section. An open portion that is open toward the outside of the tube is provided in the heat transfer expanding portion that includes the heat expanding portion and in which the medium flow path is not formed.
  • the tube has an open portion that opens toward the outer surface of the tube in the heat transfer expansion portion provided to increase the heat transfer area. Since only the portion constituting the flow path does not become dense, the core material is also installed and extruded at the portion constituting the open portion, so that the load due to the material becomes uniform and the formability is improved.
  • the heat exchange performance is improved by securing a heat transfer area, and the formation of the open portion can reduce the weight of the tube and reduce the product cost.
  • the cross-sectional shape of the medium flow path is circular.
  • the cross-sectional shape of the portion is configured so as to conform to the outer peripheral shape of the heat transfer expansion portion.
  • the circular shape means a true circle having the same radius, an elliptical shape having a major axis and a minor axis, and other similar circular shapes.
  • the shape of the hole formed in the heat transfer expansion portion is not limited because the hole does not need the pressure resistance as described above.
  • the cross-sectional shape of the hole is along the flat surface of the tube. A rectangular shape may be considered.
  • the invention described in claim 5 of the present application is the invention according to any one of claims 1 to 5, wherein the heat transfer expansion portion of the tube is a medium flow path. It is formed so as to be on the same plane as the part where the is formed.
  • a fin can also be attached to the heat transfer expansion portion of the tube, and the heat transfer area can be increased and the heat exchange performance can be improved.
  • FIG. 2 is a diagram showing a schematic configuration of a heat exchanger according to a specific example of the present invention.
  • FIG. 2 is a cross-sectional view of a tube according to a specific example of the present invention.
  • FIG. 3 is a perspective view of a tube shown in FIG. 2 according to a specific example of the present invention.
  • FIG. 4 is a sectional view showing a tube and a fin according to a second specific example of the present invention.
  • FIG. 9 is a sectional view of a tube according to a third specific example of the present invention.
  • FIG. 9 is a cross-sectional view of a tube according to a fourth example of the present invention.
  • FIG. 14 is a cross-sectional view of a tube according to a fifth specific example of the present invention.
  • FIG. 6 is a plan view showing a state where the tube shown in FIG. 5 is connected to a header pipe.
  • FIG. 14 is a partial cross-sectional view of a tube according to a sixth example of the present invention.
  • FIG. 14 is a partial cross-sectional view of a tube according to a seventh embodiment of the present invention. [Fig. 11]
  • FIG. 13 is a plan view showing a state where a header pipe and a tube are connected according to a conventional example.
  • FIG. 9 is a perspective view showing a tube according to a conventional example.
  • FIG. 1 is a plan view showing a schematic configuration of the heat exchanger of this example.
  • a heat exchanger 1 is configured such that a plurality of heat exchange tubes 2 and fins 3 are alternately stacked, and both ends of the stacked tubes 2 and 2 are respectively connected to each other.
  • the pair of header pipes 4, 4 are inserted and connected to the tube insertion holes.
  • the header pipe 4 is provided with a refrigerant channel through which the refrigerant flows.
  • Side plates 5 and 5 are arranged above and below the heat exchanger 1.
  • One header pipe 4 is provided with a feed pipe 7 for feeding the refrigerant to the header pipe 4, and the other header pipe 4 is provided with a discharge pipe 8 for discharging the refrigerant from the header pipe 4.
  • the heat exchanger 1 when used in the C 0 2 and the refrigerant of the refrigeration cycle, the refrigerant becomes high temperature and high pressure exceeds the critical point of the gas-liquid two-phase ultrasonic Since heat is radiated in the critical region, the heat exchanger is required to have a pressure resistance that is at least six times that of a normal gas-liquid two-phase refrigerant flowing between heat exchangers. Therefore, the header pipe 4 and the tube 2 of the heat exchanger 1 are formed with a sufficient thickness to ensure the required pressure resistance.
  • FIG. 2 is a sectional view showing the tube 2 of the present example
  • FIG. 3 is a perspective view of the tube 2 shown in FIG.
  • the tube 2 is provided with a refrigerant flow passage 9 communicating in the longitudinal direction, and is provided with a heat transfer expanding portion 2 a at both ends of the cross section of the tube to increase the heat transfer area. ing.
  • the medium flow path 9 is formed so that the cross section of the medium flow path is circular in order to ensure high pressure resistance.
  • the cross-sectional shape of the medium flow path is formed in a shape close to a perfect circle, but is not limited to this example, and may be formed in an elliptical shape having a long axis and a short axis.
  • the heat transfer expansion portion 2 a forms a rectangular cross-section hole 10 that matches the flat shape of the tube 2.
  • the tube 2 is formed by using an extrusion forming method in which a metal material is extruded into a mold and molded.
  • a portion of the tube 2 where the medium flow path 9 is formed is provided with a mandrel (core material). "Dense”.
  • the portion composing the heat transfer expansion section 2a has no core material, so that portion is “sparse”.
  • the material is concentrated on the “sparse” part during extrusion forming, and the “dense” part is formed. Since the material is not sufficiently distributed, the moldability is poor, and a load is applied to the mandrel provided in the “dense” part by the material, resulting in dimensional defects and damage to the mold.
  • the core material forming the hole 10 was installed in the portion forming the heat transfer expansion portion 2a, the "sparse" portion and the “dense” portion could not be formed in the extrusion mold.
  • the material is distributed on average, the thickness of the tube is made uniform, the extrudability is improved, and dimensional defects and mold breakage can be avoided.
  • the hole 10 formed in the large portion 2 a is formed in a shape communicating with the tube 2 in the longitudinal direction.
  • hole 10 is formed in the heat transfer expansion portion of the tube 2 as in this example, it is possible to reduce the weight of the tube 2 and reduce the material cost.
  • the cross-sectional shape of the hole 10 is not limited to a circular shape, but may be a tube 2 shape. Anything that matches may be used.
  • the thickness 2c from the outer surface 2b of the tube 2 to the inner surface of the hole 10 is larger than the thickness 2d from the outer surface 2b of the tube 2 to the inner surface of the medium flow path 9. Should also be large o
  • FIG. 4 is a cross-sectional view showing a tube 20 and a fin 3 in which a hole 11 having another cross-sectional shape is formed in a heat transfer enlarged portion 20a of the tube 20.
  • the hole 11 formed in the heat transfer enlarged portion 20a of the tube 20 is different from the hole 10 described above. 11 has a circular cross section.
  • the hole 12 formed in the heat transfer expansion part 21a of the tube 21 shown in FIG. 5 has a rectangular cross section.
  • the shape of the holes 11 and 12 depends on the shape of the core material. It can be easily deformed.
  • the tube 22 shown in Fig. 6 has a hole 14 with a circular cross section in the heat transfer enlarged portion 22a of the tube 22, and the hole 14a gradually extends toward both ends of the cross section of the tube 2.
  • the diameter of the hole 14 formed in the expanded heat transfer section 22a of the tube 22 is gradually increased.
  • the tube 24 has a heat transfer enlarged portion 24a formed on one side of the cross section of the tube 24, and a hole 15 formed in the heat transfer enlarged portion 24a.
  • the heat transfer expansion portion 24 is formed on one side of the cross section of the tube 24 and the hole 15 is formed in the heat transfer expansion portion 24a, the side on which the hole 15 is formed is formed.
  • the heat of the medium transferred to the heat transfer expansion section 24 is sufficiently cooled by the outside air, and the outside air having a cooling effect is removed. Since the heat of the high-temperature medium also reaches the surface of the tube 24 having the medium flow path 16 through which the heat of the medium flows, the cooling efficiency of the tube 24 can be improved.
  • Fig. 8 is a diagram showing the state in which the tube 24 shown in Fig. 7 is joined to the header pipe 4.
  • the heat transfer expansion portions 25a and 26a formed at the cross-sectional ends of the tubes 25 and 26 are provided with a rectangular or wedge-shaped tube 25. It is also conceivable to form open portions 17 and 18 that open to the outer surfaces 25b and 26b of the, 26. As described above, when the wedge-shaped or rectangular core material is placed in the extrusion mold, the tubes 25, 26 formed by extrusion molding face the outer surfaces of the tubes 25, 26. Opening portions 17 and 18 are formed.
  • the tubes 25 and 26 are provided with the open portions 17 and 18, the heat transfer area can be secured, the members can be reduced in weight, and the manufacturing cost can be reduced.
  • the open portion 17 has a wedge-shaped cross-sectional shape, the thickness of the heat transfer expansion portion 25a gradually decreases, and it is possible to efficiently cool the heat of the medium. Become. Industrial applicability
  • the heat exchanger tube according to the present invention has improved moldability, and the formed tube has a hole formed in the heat transfer enlarged portion, thereby ensuring the required pressure resistance.
  • the heat transfer area is enlarged while improving the heat exchange performance. DOO Ri reason, pressure resistance and heat exchange performance is required, Ru suitable der the refrigeration cycle of the C 0 2 and the refrigerant

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

Abstract

L'invention concerne un tube à échange thermique (2) comprenant des voies d'écoulement de milieu (9) parcourues par un milieu circulant dans un sens longitudinal. Ce tube comporte une partie extensible de transfert de chaleur (2a) dépourvue de voies d'écoulement de milieu et située aux deux extrémités ou à une seule extrémité de la section transversale du tube, cette partie extensible de transfert de chaleur (2a) comportant toutefois une ouverture (10) que le milieu en question ne traverse pas. L'épaisseur de la paroi du tube entre la surface externe du tube (2) et la surface interne de cette ouverture est plus large que celle du tube entre la surface externe du tube et la surface interne des voies d'écoulement de ce milieu.
PCT/JP2000/001937 1999-08-20 2000-03-29 Tube a echange thermique WO2001014817A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11233484A JP2001059689A (ja) 1999-08-20 1999-08-20 熱交換器用のチューブ
JP11/233484 1999-08-20

Publications (1)

Publication Number Publication Date
WO2001014817A1 true WO2001014817A1 (fr) 2001-03-01

Family

ID=16955741

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2000/001937 WO2001014817A1 (fr) 1999-08-20 2000-03-29 Tube a echange thermique

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JP (1) JP2001059689A (fr)
WO (1) WO2001014817A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170211892A1 (en) * 2016-01-25 2017-07-27 Hanon Systems Tube for heat exchanger

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009068742A (ja) * 2007-09-12 2009-04-02 Sharp Corp 熱交換器
US8776874B2 (en) 2007-12-30 2014-07-15 Valeo, Inc. Heat exchanger tubes and methods for enhancing thermal performance and reducing flow passage plugging
WO2010105170A2 (fr) * 2009-03-13 2010-09-16 Carrier Corporation Ensemble collecteur pour distribuer un fluide à un échangeur de chaleur
US20100263847A1 (en) * 2009-04-21 2010-10-21 Hamilton Sundstrand Corporation Microchannel heat exchanger
WO2020239120A1 (fr) * 2019-05-31 2020-12-03 杭州三花微通道换热器有限公司 Tube plat, échangeur de chaleur à canaux multiples et système de réfrigération de climatisation

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4932247A (fr) * 1972-07-24 1974-03-23
JPS53114647U (fr) * 1977-02-21 1978-09-12
JPS5539411B2 (fr) * 1977-05-18 1980-10-11
JPH027492U (fr) * 1988-06-21 1990-01-18
JPH0596770U (ja) * 1992-05-20 1993-12-27 日産ディーゼル工業株式会社 車両用ラジエータ
JPH10288476A (ja) * 1997-04-10 1998-10-27 Sanden Corp 熱交換器
JP2000028226A (ja) * 1998-07-10 2000-01-28 Calsonic Corp 炭酸ガス冷凍サイクル用熱交換器

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4932247A (fr) * 1972-07-24 1974-03-23
JPS53114647U (fr) * 1977-02-21 1978-09-12
JPS5539411B2 (fr) * 1977-05-18 1980-10-11
JPH027492U (fr) * 1988-06-21 1990-01-18
JPH0596770U (ja) * 1992-05-20 1993-12-27 日産ディーゼル工業株式会社 車両用ラジエータ
JPH10288476A (ja) * 1997-04-10 1998-10-27 Sanden Corp 熱交換器
JP2000028226A (ja) * 1998-07-10 2000-01-28 Calsonic Corp 炭酸ガス冷凍サイクル用熱交換器

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170211892A1 (en) * 2016-01-25 2017-07-27 Hanon Systems Tube for heat exchanger

Also Published As

Publication number Publication date
JP2001059689A (ja) 2001-03-06

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