WO2019050258A1 - DOUBLE TUBE FOR HEAT EXCHANGE - Google Patents

DOUBLE TUBE FOR HEAT EXCHANGE Download PDF

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Publication number
WO2019050258A1
WO2019050258A1 PCT/KR2018/010315 KR2018010315W WO2019050258A1 WO 2019050258 A1 WO2019050258 A1 WO 2019050258A1 KR 2018010315 W KR2018010315 W KR 2018010315W WO 2019050258 A1 WO2019050258 A1 WO 2019050258A1
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WO
WIPO (PCT)
Prior art keywords
pipe
fluid
heat exchange
spiral
double tube
Prior art date
Application number
PCT/KR2018/010315
Other languages
English (en)
French (fr)
Inventor
Kilnam LEE
Dominik Kempf
Original Assignee
Contitech Fluid Korea 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 Contitech Fluid Korea Ltd. filed Critical Contitech Fluid Korea Ltd.
Priority to KR1020207006575A priority Critical patent/KR20200027061A/ko
Priority to JP2020531412A priority patent/JP2020531790A/ja
Priority to EP18854722.8A priority patent/EP3679312A4/en
Publication of WO2019050258A1 publication Critical patent/WO2019050258A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L53/00—Heating of pipes or pipe systems; Cooling of pipes or pipe systems
    • F16L53/30—Heating of pipes or pipe systems
    • F16L53/32—Heating of pipes or pipe systems using hot fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L9/00—Rigid pipes
    • F16L9/18—Double-walled pipes; Multi-channel pipes or pipe assemblies
    • 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
    • F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0248—Arrangements for sealing connectors to header boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/06—Heat exchange conduits having walls comprising obliquely extending corrugations, e.g. in the form of threads

Definitions

  • the present invention generally relates to a double tube for heat exchange. More particularly, the present invention relates to a double tube for heat exchange, which can improve heat exchange efficiency between a first fluid flowing through a spiral pipe axially inserted into an outer pipe and a second fluid flowing between the outer pipe and the spiral pipe by increasing a contact area between an outer surface of the spiral pipe and the second fluid; can improve flow directionality of the second fluid through formation of grooves in valleys of the spiral pipe along a spiral track thereof; can reduce flow-induced noise through expansion of a space between an end joint of the outer pipe and an inner pipe for reducing pressure of the second fluid; and can further improve heat exchange efficiency through resistance members protruding from valleys to increase residence time of the second fluid.
  • a double tube includes an inner pipe and an outer pipe surrounding an outer circumferential surface of the inner pipe to form a flow path between the outer pipe and the inner pipe.
  • Such a double tube allows heat exchange between a first fluid flowing through the inner pipe and a second fluid owing through the flow path between the inner pipe and the outer pipe.
  • the double tube may be used in a liquid supercooling system, which allows a low-temperature and low-pressure refrigerant at an outlet of an evaporator of an automotive air conditioner to exchange heat with a high-temperature and high-pressure refrigerant at an outlet of a condenser of the air conditioner to increase a supercooling degree of a refrigerant entering the evaporator, thereby improving cooling performance of the air conditioner.
  • a refrigerant circulates in order of a compressor ⁇ a condenser ⁇ an expansion valve ⁇ an evaporator ⁇ a compressor, and a double tube is employed to allow a refrigerant at an outlet of the evaporator to exchange heat with a refrigerant at an outlet of the condenser (or at an inlet of the evaporator).
  • a double tube connection structure is disclosed in Korean Patent Publication No. l0-2012-0007799 A.
  • a typical double tube for heat exchange has a problem in that the double tube cannot secure a sufficient heat transfer area during flow of the second fluid and thus exhibits poor heat exchange efficiency.
  • a method in which an inner pipe is formed in a spiral shape to increase a heat transfer area to improve heat exchange efficiency has been proposed.
  • an inner pipe is formed in a spiral shape to increase a heat transfer area to improve heat exchange efficiency.
  • Embodiments of the present invention have been conceived to solve such a problem in the art and it is one aspect of the present invention to provide a double tube for heat exchange which includes a spiral pipe axially inserted into an outer pipe to increase residence time of a second fluid inside the outer pipe by virtue of a spiral shape of the spiral pipe, thereby improving heat exchange efficiency.
  • a double tube for heat exchange may include: a spiral pipe having ridges and valleys alternately formed on a circumferential surface thereof along a spiral track thereof and guiding a first fluid to flow therethrough; and an outer pipe receiving the spiral pipe axially inserted thereinto and guiding a second fluid to flow along the circumferential surface of the spiral pipe such that the second fluid exchanges heat with the first fluid, wherein the ridges contact with an inner surface of the outer pipe such that no gap is formed between the ridges and the inner surface of the outer pipe.
  • the ridges may still be in contact with the inner surface of the outer pipe even after the double tube for heat exchange is bent.
  • outer pipe may be pressed inward such that a final inner diameter of the outer pipe after pressing may become less than an initial outer diameter of the spiral pipe before pressing.
  • the spiral pipe may be pressed inward as the outer pipe is pressed such that a final outer diameter of the spiral pipe after pressing may become less than the initial outer diameter of the spiral pipe before pressing and equal to the final inner diameter of the outer pipe after pressing.
  • a double tube for heat exchange may include: a spiral pipe having ridges and valleys alternately formed on a circumferential surface thereof along a spiral track thereof and guiding a first fluid to flow therethrough; and an outer pipe receiving the spiral pipe axially inserted thereinto and guiding a second fluid to flow along the circumferential surface of the spiral pipe such that the second fluid exchanges heat with the first fluid, wherein the second fluid flows only through the valleys.
  • a double tube for heat exchange may include: a spiral pipe having ridges and valleys alternately formed on a circumferential surface thereof along a spiral track thereof and guiding a first fluid to flow therethrough; an outer pipe receiving the spiral pipe axially inserted thereinto and guiding a second fluid to flow along the circumferential surface of the spiral pipe such that the second fluid exchanges heat with the first fluid; inner pipes connected to opposite sides of the spiral pipe to allow the first fluid to flow therethrough; and pipe expansion joints provided at opposite sides of the outer pipe to have a greater diameter than the outer pipe, the pipe expansion joints being placed at junctions of the spiral pipe and the inner pipes, wherein a first part of an end portion of each of the pipe expansion joints is crimped upon the inner pipes, respectively.
  • each of the inner pipes corresponding to the first part may be deformed inward such that a diameter of the inner pipe decreases in said portion.
  • first part may be bent inward while being in contact with a circumferential surface of each of the inner pipes as the first part is crimped such that the pipe expansion joints and the inner pipes may be fixed to each other.
  • a second part of the end portion of each of the pipe expansion joints which is positioned farther from the spiral pipe than the first part, may be bent outward as the first part is crimped such that a gap may be formed between the second part and each of the inner pipes.
  • the gap may be filled with a coupling material configured to couple the second part to each of the inner pipes.
  • each of the pipe expansion joints may have a uniform thickness in the axial direction of the double tube for heat exchange even after being crimped.
  • FIG. l is a perspective view of a double tube for heat exchange according to one embodiment of the present invention.
  • FIG. 2 is an exploded perspective view of the double tube for heat exchange according to one embodiment of the present invention
  • FIG. 3 is a sectional view taken along A-A line of FIG. l;
  • FIG. 4 is an enlarged view of a main section of FIG. 3;
  • FIG. 5 is a sectional view taken along B-B line of FIG. l;
  • FIG. 6 is a plan view of a flattened portion according to one embodiment of the present invention.
  • FIG. 7 is an enlarged view of a main section of FIG. 3 showing the state after crimping.
  • FIG. l is a perspective view of a double tube for heat exchange according to one embodiment of the present invention
  • FIG. 2 is an exploded perspective view of the double tube for heat exchange according to one embodiment of the present invention.
  • FIG. 3 is a sectional view taken along A-A line of FIG. l
  • FIG. 4 is an enlarged view of a main section of FIG. 3
  • FIG. 5 is a sectional view taken along B-B line of FIG. l.
  • FIG. 6 is a plan view of a flattened portion according to one embodiment of the present invention.
  • FIG. 7 is an enlarged view of a main section of FIG. 3 showing the state after crimping.
  • a double tube for heat exchange 100 includes inner pipes 112, 114, a spiral pipe 120, pipe expansion joints 132, 134, and an outer pipe 140.
  • the double tube for heat exchange 100 allows heat exchange between a refrigerant (first fluid) at an outlet of an evaporator of an automotive air conditioner and a refrigerant (second fluid) at an outlet of a condenser of the air conditioner to reduce load of the compressor through increase in temperature of the first fluid introduced into a compressor, while improving vaporization efficiency through decrease in temperature of the second fluid introduced into an expansion valve.
  • first fluid refrigerant
  • second fluid refrigerant
  • the outer pipe 140 has a tubular shape and allows a high-temperature and high-pressure fluid (the second fluid) at the outlet of the condenser to flow therethrough.
  • the inner pipes 112, 114 have a tubular shape, allow a low-temperature and low-pressure fluid (the first fluid) at the outlet of the evaporator to ow therethrough, and are inserted into the outer pipe 140.
  • the second fluid at high temperature and high pressure at the outlet of the condenser flows through a space between the inner pipes 112, 114 and the outer pipe 140.
  • the double tube for heat exchange 100 allows heat exchange between the first fluid at low temperature and low pressure at the outlet of the evaporator and the second fluid at high temperature and high pressure at the outlet of the condenser through the inner pipes 112, 114.
  • spiral pipe 120 connects the inner pipes 112, 114 to each other and is formed on a circumferential surface thereof with ridges 122 and valleys 124 in an alternating manner along a spiral track thereof.
  • the spiral pipe 120 is connected at opposite sides thereof to the inner pipes 112, 114.
  • a first inner pipe 112 is connected to one side of the spiral pipe 120 and the second inner pipe 114 is connected to the other side of the spiral pipe 120.
  • the spiral pipe 120 may be formed at a portion of the first inner pipe 112 or a portion of the second inner pipe 114.
  • the first fluid flows through the first inner pipe 112, the spiral pipe 120, and the second inner pipe 114.
  • the spiral pipe 120 is formed with the ridges 122 and the valleys 124 in an alternating manner. Since the second fluid flows along the valleys 124 of the circumferential surface of the spiral pipe 120, residence time of the second fluid in the outer pipe 140 and the spiral pipe 120 is increased, thereby improving heat exchange efficiency between the second fluid and the first fluid.
  • the ridges 122 of the spiral pipe 120 may consecutively adjoin an inner surface of the outer pipe 140. As a result, the second fluid is allowed to flow along the valleys 124 of the spiral pipe 120.
  • each of the ridges 122 may contact with the inner surface of the outer pipe 140, which results in no gap between the ridges 122 and the inner surface of the outer pipe 140. Accordingly, in this case, the second fluid is allowed to flow only through the valleys 124 of the spiral pipe 120, i.e., the second fluid cannot flow through between the ridges 122 and the inner surface of the outer pipe 140.
  • the contact state of the ridges 122 and the inner surface of the outer pipe 140 can be obtained by using a suitable press machine, e.g. a press molding.
  • a suitable press machine e.g. a press molding.
  • the outer pipe 140 may be pressed inward by the press machine.
  • a circumferential surface of the outer pipe 140 may be pressed onto the circumferential surface of the spiral pipe 120. Due to this pressing, the outer pipe 140 may be deformed, e.g. plastic deformed.
  • the spiral pipe 120 may also be deformed, e.g. plastic deformed, as the outer pipe 140 is pressed.
  • an initial inner diameter of the outer pipe 140 may be greater than an initial outer diameter of the spiral pipe 120 (the vertical distance between portions of the circumferential surface of the spiral pipe 120 corresponding to ridges on a side in a circumferential direction and the other portions of the circumferential surface of the spiral pipe 120 corresponding to the other ridges on the opposite side in the circumferential direction) such that a gap between the ridges 122 and the inner surface of the outer pipe 140 may be present.
  • the inner diameter of the outer pipe 140 and the outer diameter of the spiral pipe 120 may decrease, and then a final inner diameter of the outer pipe 140 and a final outer diameter of the spiral pipe 120 may become equal to each other.
  • the final inner diameter of the outer pipe 140 may be less than the initial outer diameter of the spiral pipe 120.
  • the pipe expansion joints 132, 134 are placed at junctions between the inner pipes 112, 114 and the spiral pipe 120, respectively.
  • the pipe expansion joints 132, 134 are sealed against a circumferential surface of the corresponding pipe of the inner pipes 112, 114 and are provided with ports 133, 135 for inflow/outflow of the second fluid, respectively.
  • a first pipe expansion joint 132 covers a junction between the first inner pipe 112 and the spiral pipe 120
  • a second pipe expansion joint 134 covers a junction between the second inner pipe 114 and the spiral pipe 120.
  • the first pipe expansion joint 132 is sealed along a circumferential surface of the rst inner pipe 112 by brazing, welding and the like.
  • the second pipe expansion joint 134 is sealed along a circumferential surface of the second inner pipe 114 by brazing, welding and the like.
  • a first part of an end portion of the first pipe expansion joint 132 may be crimped upon the first inner pipe 112 by a suitable press machine such that a portion of the first inner pipe 112 corresponding to the first part may be deformed (e.g. plastic deformed) inward, and therefore a diameter of the first inner pipe 112 may decrease in said portion.
  • the first part may be bent inward while being in contact with the circumferential surface of the first inner pipe 112 as the first part is crimped, thus the first pipe expansion joint 132 and the first inner pipe 112 may be fixed to each other.
  • the aforementioned first part may refer to a specific region of a circumferential surface of the end portion of the first pipe expansion joint 132 that extends in the circumferential direction.
  • a second part of the end portion of the first pipe expansion joint 132 which is positioned farther from the spiral pipe 120 than the first part, may be bent outward as the first part is crimped such that a gap 170 may be formed between the second part and the first inner pipe 112.
  • the gap 170 may be filled with a coupling material configured to couple the second part to the first inner pipe 112.
  • the coupling material could be a brazing material, a welding material, a soldering material and the like.
  • a first part of an end portion of the second pipe expansion joint 134 may be crimped upon the second inner pipe 114 by a suitable press machine such that a portion of the second inner pipe 114 corresponding to the first part may be deformed (e.g. plastic deformed) inward, and therefore a diameter of the second inner pipe 114 may decrease in said portion.
  • the first part may be bent inward while being in contact with the circumferential surface of the second inner pipe 114 as the first part is crimped, thus the second pipe expansion joint 134 and the second inner pipe 114 may be fixed to each other.
  • the aforementioned first part may refer to a specific region of a circumferential surface of the end portion of the second pipe expansion joint 134 that extends in the circumferential direction.
  • a second part of the end portion of the second pipe expansion joint 134 which is positioned farther from the spiral pipe 120 than the first part, may be bent outward as the first part is crimped such that a gap 170 may be formed between the second part and the second inner pipe 114.
  • the gap 170 may be filled with a coupling material configured to couple the second part to the second inner pipe 114.
  • the coupling material could be a brazing material, a welding material, a soldering material and the like.
  • each of the inner pipes 112, 114 corresponding to the first part may be deformed inward and the first part may be bent inward while being in contact with the circumferential surface of each of the inner pipes 112, 114 as the first part is crimped, as described above, fixation between the pipe expansion joints 132, 134 and the inner pipes 112, 114 could be improved.
  • the second part may be automatically bent outward as the first part is crimped and the gap 170 may be formed accordingly, coupling of the pipe expansion joints 132, 134 and the inner pipes 112, 114 could easily be performed by filling the gap 170 with the coupling material.
  • each of the end portions of the pipe expansion joints 132, 134 may be cut off straight and may have a uniform thickness in the axial direction.
  • the first pipe expansion joint 132 and the second pipe expansion joint 134 are connected to the outer pipe 140.
  • the outer pipe 140 may be integrally formed with the first pipe expansion joint 132 at one side thereof and be integrally formed with the second pipe expansion joint 134 at the other side thereof.
  • first pipe expansion joint 132 and the second pipe expansion joint 134 may also be connected to the outer pipe 140 by welding and the like.
  • the outer pipe 140 is configured to surround the entire spiral pipe 120.
  • first pipe expansion joint 132 has a first port 133 for receiving the second fluid at high temperature and high pressure from the outlet of the condenser
  • second pipe expansion joint 134 has a second port 135 for discharging the heat exchanged second fluid to the expansion valve.
  • the second fluid introduced through the first port 133 flows along the valleys 124 in a space between the outer pipe 140 and the spiral pipe 120 and is then discharged through the second port 135.
  • the second fluid exchanges heat with the first fluid that flows along the first inner pipe 112, the spiral pipe 120, and the second inner pipe 114. That is, the first fluid is heated through heat exchange with the second fluid, and the second fluid is cooled through heat exchange with the first fluid.
  • the inner pipes 112, 114, the spiral pipe 120, and the outer pipe 140 may be formed of a material having high thermal conductivity.
  • the first pipe expansion joint 132 and the second pipe expansion joint 134 have the same shape to be interchangeable with each other.
  • each of the first pipe expansion joint 132 and the second pipe expansion joint 134 includes a pipe expansion portion 137, a packing member 138, and a connection member 139.
  • the packing member 138 may correspond to the end portions of the pipe expansion joints 132, 134 discussed above.
  • the pipe expansion portion 137 has a greater diameter than the outer pipe 140 so as to reduce flow noise of the second fluid.
  • the pipe expansion portions 137 are configured to surround a junction between the first inner pipe 112 and the spiral pipe 120 and a junction between the second inner pipe 114 and the spiral pipe 120, respectively. It should be understood that the pipe expansion portions 137 may also be placed at both sides in an axial direction of the spiral pipe 120.
  • the pipe expansion portion 137 has a greater diameter than the outer pipe 140.
  • the packing member 138 may be connected to the circumferential surface of the corresponding pipe of the first inner pipe 112 and the second inner pipe 114 to be packed.
  • the packing member 138 may have a first part 138a and a second part 138b as shown in Fig. 4.
  • the second part 138b may be positioned farther from the spiral pipe 120 than the first part 138a.
  • the first part 138a of the packing member 138 of each of the pipe expansion joints 132, 134 may be crimped upon the inner pipes 112, 114, in the direction of the illustrated arrows, by a suitable press machine such that a portion 112a, 114a of each of the inner pipes 112, 114 corresponding to the first part 138a may be deformed (e.g. plastic deformed) inward, and therefore a diameter of each of the inner pipes 112, 114 may decrease in said portion 112a, 114a.
  • first part 138a may be bent inward while being in contact with the circumferential surface of each of the inner pipes 112, 114 as the first part 138a is crimped, thus the pipe expansion joints 132, 134 and the inner pipes 112, 114 may be fixed to each other.
  • the aforementioned first part 138a may refer to a specific region of a circumferential surface of the packing member 138 of the pipe expansion joints 132, 134 that extends in the circumferential direction.
  • the second part 138b of the packing member 138 of each of the pipe expansion joints 132, 134 may be bent outward as the first part 138a is crimped such that a gap 170 may be formed between the second part 138b and each of the inner pipes 112, 114.
  • the gap 170 may be filled with a coupling material configured to couple the second part 138b to the inner pipes 112, 114.
  • the coupling material could be a brazing material, a welding material, a soldering material and the like.
  • the packing member 138 may be cut off straight at the one end, the left-end when referring to Fig. 4, and may have a uniform thickness in the axial direction even after crimping of the first part 138a.
  • the packing member 138 may also have a third part 138c which is positioned closer to the spiral pipe 120 than the first part 138a and is tapered, i.e. inclined towards the inner pipes 112, 114 from one side of the pipe expansion portion 137 as shown in Fig. 4. Particularly, since the packing member 138 has the tapered third part 138c inclined towards the inner pipes 112, 114 from the pipe expansion portion 137, flow resistance of the second fluid can be reduced, thereby reducing flow-induced noise.
  • connection member 139 may have a tapered part inclined towards the spiral pipe 120 from the other side of the pipe expansion portion 137 as shown in Fig. 4.
  • connection member 139 is connected to the outer pipe 140.
  • the connection member 139 is sealed at an edge thereof against a corresponding edge of the outer pipe 140 by welding and the like. Since the connection member 139 has the tapered part inclined towards the spiral pipe 120 from the pipe expansion portion 137, flow resistance of the second fluid can be reduced, thereby reducing flow-induced noise.
  • each of the valleys 124 is provided with at least one groove 126 along a spiral track of the valley 124.
  • a plurality of grooves 126 is formed to be parallel to one another in order to improve flow directionality of the second fluid while increasing a contact area between the second fluid and the spiral pipe 120.
  • the groove 126 is not particularly limited in terms of shape, number, and height.
  • each of the pipe expansion joints 132, 134 may be formed with a attened portion 150 at a portion of the curved circumferential surface thereof at which the corresponding pipe of the first port 133 and the second port 135 is formed.
  • the flattened portion 150 is formed by flattening the circumferential surfaces of the pipe expansion joints 132, 134 along the peripheries of the first port 133 and the second port 135 such that the first port 133 and the second port 135 can be easily coupled to the pipe expansion joints 132, 134, respectively, by welding and the like.
  • first port 133 and the second port 135 may be partially inserted into the corresponding pipe of the pipe expansion joints 132, 134 and then welded by two-dimensionally moving a welding jig (not shown) on the flattened portion 150, thereby allowing easy welding while preventing welding defects.
  • a space expansion portion 152 can be naturally created inside the pipe expansion portion 137. It should be understood that the space expansion portion 152 may also be separately formed in an inner surface of each of the pipe expansion joints 132, 134.
  • the space expansion portion 152 can further reduce flow resistance of the second fluid, thus reducing flow-induced noise. It should be understood that the flattened portion 150 may be machined using various jigs.
  • Heat exchange performance can be controlled by increasing/reducing the pitch between adjacent valleys 124 or between adjacent ridges 122 of the spiral pipe 120.
  • the distance between adjacent ridges 122 in the axial direction of the outer pipe 140 increases, thereby reducing flow-induced noise.
  • a resistance member 160 may protrude from the valley 124.
  • the resistance member 160 protrudes between adjacent ridges 122 and is not limited in terms of shape and number.
  • the resistance member 160 serves to increase the residence time of the second fluid in the valleys 124 while supporting the ridges 122 adjacent thereto.
  • adjacent resistance members 160 is not particularly limited.
  • the spiral pipe 120 is formed with the grooves 126 along the spiral track thereof in a discontinuous manner such that the resistance members 160 can be naturally formed.
  • the resistance member 160 needs to have a smaller height than the ridge portion 122 to allow flow of the second fluid.
  • the resistance member 160 may be partially chamfered at an upper portion thereof. It should be understood that the resistance member 160 may be formed in various shapes.
  • the double tube for heat exchange includes the spiral pipe axially inserted into the outer pipe to increase residence time of the second fluid inside the outer pipe, thereby improving heat exchange efficiency between the first fluid flowing through the spiral pipe and the second fluid flowing between the outer pipe and the spiral pipe.
  • the double tube for heat exchange includes at least one groove formed on the circumferential surface of the spiral pipe along the spiral track of the valleys to improve flow directionality of the second fluid so as to allow the second fluid to flow more stably, thereby further improving heat exchange efficiency.
  • the double tube for heat exchange has pipe expansion joints, which are having increased diameters and connected to the ends of the outer pipe, to expand a space between the outer pipe and the inner pipe so as to reduce pressure of a fluid during inflow and outflow of the fluid, thereby reducing flow-induced noise.
  • the double tube for heat exchange can prevent excessive warpage of the ridges of the spiral pipe through the resistance member adjacent to the ridges, thus durability of the spiral pipe can be improved.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/KR2018/010315 2017-09-06 2018-09-04 DOUBLE TUBE FOR HEAT EXCHANGE WO2019050258A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
KR1020207006575A KR20200027061A (ko) 2017-09-06 2018-09-04 열 교환용 이중관
JP2020531412A JP2020531790A (ja) 2017-09-06 2018-09-04 熱交換用二重管
EP18854722.8A EP3679312A4 (en) 2017-09-06 2018-09-04 DOUBLE PIPE FOR A HEAT EXCHANGER

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR20170114094 2017-09-06
KR10-2017-0114094 2017-09-06

Publications (1)

Publication Number Publication Date
WO2019050258A1 true WO2019050258A1 (en) 2019-03-14

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PCT/KR2018/010315 WO2019050258A1 (en) 2017-09-06 2018-09-04 DOUBLE TUBE FOR HEAT EXCHANGE

Country Status (4)

Country Link
EP (1) EP3679312A4 (ja)
JP (1) JP2020531790A (ja)
KR (1) KR20200027061A (ja)
WO (1) WO2019050258A1 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3848660A1 (fr) * 2020-01-09 2021-07-14 Hutchinson Raccordement étanche d'un connecteur a un échangeur thermique tubulaire coaxial

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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EP3848660A1 (fr) * 2020-01-09 2021-07-14 Hutchinson Raccordement étanche d'un connecteur a un échangeur thermique tubulaire coaxial
FR3106201A1 (fr) * 2020-01-09 2021-07-16 Hutchinson Raccordement etanche d’un connecteur a un echangeur thermique tubulaire coaxial
US11365939B2 (en) 2020-01-09 2022-06-21 Hutchinson Sealed connection of a connector to a coaxial tubular heat exchanger

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EP3679312A1 (en) 2020-07-15
KR20200027061A (ko) 2020-03-11
JP2020531790A (ja) 2020-11-05

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