EP4001821B1 - Wärmeübertragungsrohr und wärmetauscher damit - Google Patents

Wärmeübertragungsrohr und wärmetauscher damit Download PDF

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Publication number
EP4001821B1
EP4001821B1 EP19937853.0A EP19937853A EP4001821B1 EP 4001821 B1 EP4001821 B1 EP 4001821B1 EP 19937853 A EP19937853 A EP 19937853A EP 4001821 B1 EP4001821 B1 EP 4001821B1
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EP
European Patent Office
Prior art keywords
heat transfer
transfer tube
heat
main body
axis
Prior art date
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Active
Application number
EP19937853.0A
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English (en)
French (fr)
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EP4001821A4 (de
EP4001821A1 (de
Inventor
Atsushi Morita
Tsuyoshi Maeda
Shin Nakamura
Akira YATSUYANAGI
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP4001821A4 publication Critical patent/EP4001821A4/de
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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
    • F28F1/02—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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0391—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits a single plate being bent to form one or more conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel 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
    • F28F1/10—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

Definitions

  • the present disclosure relates to a heat transfer tube through which heat exchange fluid flows, and also to a heat exchanger employing the heat transfer tube.
  • Patent Literature 1 discloses an elongated heat transfer tube that is formed by bending a single plate a number of times.
  • the heat transfer tube disclosed in Patent Literature 1 includes a flat plate-like base portion, two bent portions that are bent from both end portions of the base portion toward a central portion of the base portion, and two partition portions that are bent from end portions of the bent portions toward the base portion, the end portions facing the central portion of the base portion.
  • This heat transfer tube further includes layered portions which are bent from end portions of the two partition portions toward the both end portions of the base portion, which overlap the base portion, and is jointed to the base portion with a brazing material.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2018-204919
  • the material cost is increased, and the weight of the heat transfer tube is also increased.
  • the length of the short axis or the length of the long axis of the section of the heat transfer tube is decreased, the heat-transfer area of the outer periphery of the heat transfer tube is decreased, thus deteriorating the heat exchange performance of the heat exchanger.
  • electric power required for the compressor may be increased.
  • KR 100378055 describes a coolant tube of a heat exchanger having the features of the preamble of claim 1 and a processing method thereof.
  • WO 2019/026239 describes a heat exchanger in which each of a plurality of heat exchange members has a flat tube that extends from a first header tank to a second header tank, and a heat transfer plate that is integral with the flat tube along the longitudinal direction of the flat tube.
  • the present disclosure is applied to solve the problem of the above related art, and relates to an elongated heat transfer tube that is formed by bending a plate material, and that can reduce deterioration of a heat exchange performance, and also to a heat exchanger using the heat transfer tube.
  • a heat transfer tube of one embodiment of the present disclosure includes: an elongated main body including a plurality of flow passages formed by bending a single plate material a number of times; and an extension portion corresponding to at least one of the end portions of the single plate material, the extension portion being formed such that the at least one of the end portions of the single plate material extends from the main body in an elongated-section long-axis direction that is a direction along a long axis of a section of the main body.
  • the extension portion is longer than a short axis of the section of the main body.
  • a heat exchanger of another embodiment of the present disclosure includes a plurality of heat transfer tubes each described above.
  • the plurality of heat transfer tubes are arranged in parallel to each other along a direction perpendicular to a flow direction of first heat exchange fluid and a flow direction of second heat exchange fluid, the first heat exchange fluid flowing through the plurality of flow passages, the second heat exchange fluid flowing over an outer surface of the main body.
  • the main body and the extension portion or portions are formed by bending a single plate material, and the extension portion or portions are each formed to be longer than the short axis of the section of the main body.
  • a heat transfer tube according to Embodiment 1 of the present disclosure will be described.
  • the heat transfer tube according to Embodiment 1 is used as, for example, a heat exchanger included in a refrigeration cycle apparatus.
  • Fig. 1 is a perspective view illustrating an example of the configuration of the heat transfer tube according to Embodiment 1.
  • a heat transfer tube 1 includes a main body 1A and an extension portion or extension portions 1B.
  • the main body 1A and the extension portion or portions 1B of the heat transfer tube 1 are formed by bending a single plate material a number of times.
  • the single plate material is made of metal material having a high heat conductivity, such as aluminum, copper, or brass.
  • the main body 1A is formed into an elongated shape having a substantially elliptical section.
  • a plurality of flow passages are formed to extend in a direction along a long axis of the heat transfer tube 1.
  • First heat exchange fluid flows through the flow passages.
  • the first heat exchange fluid is, for example, water, brine, an HFC-based refrigerant, or a hydrocarbon (HC)-based refrigerant.
  • a first direction is a direction along the long-axis direction of a section of the main body 1A that is taken along a plane perpendicular to the flow passages of the main body 1A, and will be also referred to as an elongated-section long-axis direction
  • a second direction is a direction perpendicular to the first direction and a direction along a short axis of the section of the main body 1A that is taken along the plane perpendicular to the flow passages of the main body 1A, the direction along the short axis of the section of the main body 1A being to be also referred to as an elongated-section short-axis direction
  • a third direction is a direction perpendicular to the first and second directions and a flow direction of the first heat exchange fluid.
  • Second heat exchange fluid flows over an outer surface of the main body 1A in a direction parallel to the first direction or the third direction.
  • the second heat exchange fluid is, for example, air.
  • flow directions of the first heat exchange fluid and the second heat exchange fluid are indicated by respective outlined arrows.
  • the extension portion or portions 1B are each formed to extend from the main body 1A in the first direction.
  • the extension portion or portions 1B are formed at one end portion or respective end portions of the single plate material that forms the main body 1A and the extension portion or portions 1B.
  • Fig. 2 is a schematic sectional view illustrating an example of the heat transfer tube according to Embodiment 1 as the heat transfer tube is viewed in the third direction.
  • the main body 1A includes an outer tube wall 10 and an inner tube wall 11.
  • the outer tube wall 10 corresponds to an outer periphery of the heat transfer tube 1 formed by bending the single plate material a number of times.
  • the inner tube wall 11 is a wall portion of the main body 1A that is other than the outer tube wall 10.
  • the outer tube wall 10 includes contact portions of the main body 1A with which the second heat exchange fluid comes into contact and other portions of the main body 1A that are adjacent to the contact portions.
  • the inner tube wall 11 is a portion of the main body 1A that is other than the outer tube wall 10.
  • the inner tube wall 11 has two or more layered portions 11a and at least one partition portion 11b.
  • the layered portions 11a of the inner tube wall 11 are portions which are in contact with the outer tube wall 10, and are joined to the outer tube wall 10 by, for example, brazing.
  • the at least one partition portion 11b is formed by bending the plate material in such a manner as to partition the interior of the main body 1A.
  • inner spaces of the main body 1A are surrounded by the outer tube wall 10 and the layered portions 11a and the at least one partition portion 11b of the inner tube wall 11, and serve as flow passages through which the first heat exchange fluid flows.
  • the length of the main body 1A in the elongated-section long-axis direction (the first direction) is defined as an elongated-section long-axis length DA and the length of the main body 1A in the elongated-section short axis direction (the second direction) is defined as an elongated-section short-axis length DB.
  • the extension portion or portions 1B that is, at least one extension portion 1B, is formed such that at least one of the end portions of the plate material extends from the main body 1A in the elongated-section long-axis direction that is the first direction. Furthermore, the extension portion or portions 1B are each formed to have a greater length than the elongated-section short-axis length DB of the main body 1A in order to improve the heat transfer performance of a heat exchanger in the case where the heat transfer tube 1 is used in the heat exchanger. The heat transfer performance of the heat exchanger will be described later.
  • two extension portions 1B are provided at respective ends of the plate material, and extend in the opposite directions along the elongated-section long-axis direction, that is, the two extension portions 1B corresponds to the respective ends of the plate material.
  • the number of extension portions 1B to be formed is not limited to that of the above example.
  • the heat transfer tube 1 may be formed to have only a single extension portion 1B.
  • Fig. 3 is a side view illustrating modification 1 of the heat transfer tube according to Embodiment 1 as the heat transfer tube is viewed in the third direction.
  • one of extension portions 1B is bent and then stacked on the other extension portion 1B to form a single extension portion 1B.
  • the heat transfer tube 1 according to Embodiment 1 may be formed to have a single extension portion 1B.
  • the extension portion 1B and part of the outer tube wall 10 of the main body 1A each have a double-layered structure, and thus each have a greater thickness.
  • the pressure resistance and durability of the heat transfer tube 1 can be improved.
  • Fig. 4 is a side view illustrating modification 2 of the heat transfer tube according to Embodiment 1 as the heat transfer tube is viewed in the third direction.
  • the heat transfer tube 1 as illustrated in Fig. 4 is formed such that one of the end portions of the plate material is provided as the inner tube wall 11.
  • the heat transfer tube 1 has a single extension portion 1B. Therefore, in the heat transfer tube 1 of modification 2, the extension portion 1B and part of the outer tube wall 10 of the main body 1A do not have a double-layered structure. Because of provision of the above configuration, it is possible to reduce the amount of material to be used and the amount of brazing material for use in joining portions of the double-layered structure together, and thus reduce manufacturing costs of the heat transfer tube 1, as compared with the heat transfer tube 1 of modification 1.
  • the heat transfer performance of a heat exchanger can be determined using an overall heat transfer coefficient AoK.
  • the overall heat transfer coefficient AoK is calculated on the basis of equation (1) below.
  • Ao is an outer heat transfer area
  • K is a heat transfer coefficient
  • Ap is a heat-transfer-tube surface area
  • ⁇ is a fin efficiency
  • a F is a fin surface area
  • ⁇ o is an outer heat transfer coefficient (including a contact thermal resistance)
  • Ai is an inner heat transfer area
  • ⁇ i is an inner heat transfer coefficient.
  • the heat transfer performance of a heat exchanger can be improved by increasing the heat-transfer-tube surface area Ap and the fin surface area A F .
  • the heat transfer tube 1 according to Embodiment 1 is provided with the extension portion or portions 1B formed integrally with the main body 1A, even when the main body 1A has a tubular shape similar to those of existing heat transfer tubes, the outer heat transfer area Ao can still be increased, as compared with the existing heat transfer tubes.
  • the length of the extension portion or portions 1B is further increased, whereby while the inner tube volume is decreased, the outer heat transfer area Ao can still be kept substantially equal to those of the existing heat transfer tubes.
  • the heat transfer tube 1 includes the main body 1A through which the first heat exchange fluid flows, the main body 1A being formed by bending a single plate material a number of times, and includes the at least one extension portion 1B that corresponds to at least one of end portions of the single plate material in the elongated-section long-axis direction.
  • the heat transfer tube 1 is formed to have the at least one extension portion 1B, even when the main body 1A has a tubular shape similar to those of the existing heat transfer tubes, the outer heat transfer area Ao can be made larger than those of the existing heat transfer tubes. Therefore, in the case where a heat exchanger employs the heat transfer tube 1, the heat transfer performance of the heat exchanger can be improved.
  • the extension portion or portions 1B of the heat transfer tube 1 are each formed to have a length greater than the elongated-section short-axis length DB.
  • the extension portion or portions 1B is used as a grip or grips for a manufacturing device. Because of this configuration, it is possible to improve the manufacturability of the heat transfer tube 1.
  • a clad material may be used as a plate material of which the heat transfer tube 1 is formed.
  • a clad material aluminum or other material is used as a base material, and opposite sides of the base are coated with brazing material.
  • brazing material In the case where such a clad material is used as the plate material, at the time of manufacturing of the heat transfer tube 1, it is not necessary to provide a step of applying brazing material on surfaces of the plate material. It is therefore possible to improve the manufacturability of the heat transfer tube 1.
  • Embodiment 2 of the present disclosure will be described.
  • part of the outer tube wall 10 that extends in the elongated-section short axis direction is formed to have a double-layered structure.
  • Embodiment 2 is different from Embodiment 1.
  • components that are the same as those in Embodiment 1 will be denoted by the same reference signs, and their detailed descriptions will thus be omitted.
  • Fig. 5 is a schematic sectional view illustrating an example of a heat transfer tube according to Embodiment 2 as the heat transfer tube is viewed in the third direction.
  • the outer tube wall 10 of the heat transfer tube 1 according to Embodiment 2 has an outer-wall layered portion or portions 10a each of which extends in the elongated-section short axis direction and has a double-layered structure.
  • the outer-wall layered portion or portions 10a are each formed by bending the plate material at the boundary between the main body 1A and the extension portion 1B in Embodiment 1 along the part of the outer tube wall 10 that extends in the elongated-section short axis direction.
  • the bent portion of the plate material and the above part of the outer tube wall 10 are joined together by, for example, brazing to form the outer-wall layered portion 10a.
  • the part of the outer tube wall 10 that extends in the elongated-section short axis direction has a higher strength, thus improving the pressure resistance and the durability of the heat transfer tube 1.
  • the length of the outer-wall layered portion 10a be, for example, greater than or equal to half of the elongated-section short-axis length DB.
  • the heat transfer tube 1 can improve the heat transfer performance of the heat exchanger as in Embodiment 1.
  • the outer-wall layered portion 10a is provided as the part of the outer tube wall 10 that extends in the elongated-section short axis direction. Furthermore, it is preferable that the length of the outer-wall layered portion 10a is greater than or equal to half of the elongated-section short-axis length DB.
  • the part of the outer tube wall 10 that extends in the elongated-section short axis direction has a higher strength, as a result of which it is possible to improve the pressure resistance and the durability of the heat transfer tube 1.
  • Embodiment 3 of the present disclosure will be described.
  • each of end portions of the main body 1A in the elongated-section long-axis direction is rounded, and the extension portion or portions 1B are each located substantially on a central axis of the heat transfer tube that passes through the center of the part of the outer tube wall that extends in the elongated-section short axis direction.
  • Embodiment 3 is different from Embodiments 1 and 2. It should be noted that regarding Embodiment 3, components that are the same as those in Embodiment 1 and/or Embodiment 2 will be denoted by the same reference signs, and their detailed descriptions will thus be omitted.
  • Fig. 6 is a schematic sectional view illustrating an example of a heat transfer tube according to Embodiment 3 as the heat transfer tube is viewed in the third direction.
  • each end portion of the main body 1A in the elongated-section long-axis direction is rounded.
  • the extension portion or portions 1B are each formed substantially on the central axis that extends through the center of part of the heat transfer tube 1 that has the elongated-section short-axis length DB.
  • the outer tube wall 10 of the main body 1A is formed by bending the plate material such that each end portion of the main body 1A in the elongated-section long-axis direction is rounded.
  • the extension portion or portions 1B are each formed in the following manner: the plate material is bent along the rounded portion of the outer tube wall 10 of the main body 1A, and from this bent portion, part of the plate material that is close to the axis extending through the center of the part of the heat transfer tube 1 that has the elongated-section short-axis length DB is bent to form the extension portion 1B.
  • the second heat exchange fluid first flows along the extension portion or portions 1B. Then, while flowing along the rounded shape of the main body 1A, the second heat exchange fluid strikes the main body 1A. At this time, a flow resistance generated when the second heat exchange fluid strikes the main body 1A is reduced, as compared with the case where the main body 1A is formed not to have a rounded shape.
  • the heat transfer tube 1 can improve the heat transfer performance of the heat exchanger as in Embodiments 1 and 2.
  • each of the end portions of the main body 1A in the elongated-section long-axis direction is rounded, and the extension portion or portions 1B are each formed on the axis that passes through the center of the part of the heat transfer tube 1 that has the elongated-section short-axis length DB.
  • This configuration reduces a flow resistance that is caused by the second heat exchange fluid that flows over the surface of the heat transfer tube 1 when the second heat exchange fluid strikes the main body 1A. It is therefore possible to reduce a drive force that is required for a fan or other devices to supply the second heat exchange fluid.
  • Embodiment 4 of the present disclosure will be described.
  • Embodiment 4 after being bent toward the central axis of the heat transfer tube 1 that passes through the center of part of the heat transfer tube 1 that extends in the elongated-section short axis direction, a portion or portions of the outer tube wall 10 of the main body 1A extends along the central axis.
  • components that are the same as any of Embodiments 1 to 3 will be denoted by the same reference signs, and their detailed descriptions will thus be omitted.
  • Fig. 7 is a schematic sectional view illustrating an example of a heat transfer tube according to Embodiment 4 as the heat transfer tube is viewed in the third direction.
  • the abovementioned portion or portions of the outer tube wall 10 of the main body 1A extends along the above axis.
  • the above bent portion or portions of the outer tube wall 10 are brought in contact with the inner tube wall 11.
  • the heat transfer tube 1 can improve the heat transfer performance of the heat exchanger as in Embodiments 1 to 3.
  • the abovementioned portion or portions of the outer tube wall 10 extend along the central axis that passes through the center of the part of the heat transfer tube 1 that has the elongated-section short-axis length DB, after being bent toward the central axis.
  • the inner volume of the heat transfer tube 1, which include flow passages for the first heat exchange fluid is reduced, with compared with the case where the outer tube wall 10 is not bent.
  • the amount of the first heat exchange fluid to be filled can be reduced.
  • the heat transfer tube 1 can improve the heat exchange performance of the heat exchanger.
  • the above portions of the outer tube wall 10 are bent to be in contact with the inner tube wall 11, and as a result the contact area between the outer tube wall 10 and the inner tube wall 11 is increased. Accordingly, the heat transfer tube 1 can improve the pressure resistance and the durability.
  • Embodiment 5 of the present disclosure will be described.
  • the entire outer tube wall 10 of the main body 1A is formed to have a double-layered structure or a multi-layered structure.
  • Embodiment 5 is different from Embodiments 1 to 4. It should be noted that regarding Embodiment 5, components that are the same as those in any of Embodiments 1 to 4 are denoted by the same reference signs, and their detailed descriptions will thus be omitted.
  • Fig. 8 is a schematic sectional view illustrating an example of a heat transfer tube according to Embodiment 5 as the heat transfer tube is viewed in the third direction.
  • the outer tube wall 10 of the main body 1A is formed by bending the plate material such that two or more layers of the plate material are stacked together.
  • the stacked two or more layers of the plate material are joined together by, for example, brazing.
  • the entire outer tube wall 10 has a double-layered structure or a multi-layered structure.
  • the heat transfer tube 1 can improve the heat transfer performance of the heat exchanger as in Embodiments 1 to 4.
  • the entire outer tube wall 10 has a double-layered structure or a multi-layered structure. Therefore, the heat transfer tube 1 according to Embodiment 5 can further improve the pressure resistance and the durability, as compared with Embodiments 1 to 4.
  • Embodiment 6 of the present disclosure will be described.
  • the outer tube wall 10 and the inner tube wall 11 of the main body 1A are formed symmetrically with respect to the intersection of an axis that passes through the center of part of the heat transfer tube 1 that has the elongated-section long-axis length DA and the central axis that passes through the center of the part of the heat transfer tube 1 that has the elongated-section short-axis length DB.
  • Fig. 9 is a schematic sectional view illustrating an example of a heat transfer tube according to Embodiment 6 as the heat transfer tube is viewed in the third direction.
  • the outer tube wall 10 and the inner tube wall 11 of the main body 1A according to Embodiment 6 are formed by bending the plate material such that the outer tube wall 10 and the inner tube wall 11 are symmetrical with respect to the intersection of the axis that passes through the center of the part of the heat transfer tube 1 that has the elongated-section long-axis length DA and the central axis that passes through the center of the part of the heat transfer tube 1 that has the elongated-section short-axis length DB.
  • the heat transfer tube 1 can improve the heat transfer performance of the heat exchanger as in Embodiments 1 to 5. Furthermore, in the heat transfer tube 1 according to Embodiment 6, the outer tube wall 10 and the inner tube wall 11 are formed symmetrical with respect to the intersection of the axis that passes through the center of the part of the heat transfer tube 1 that has the elongated-section long-axis length DA and the central axis that passes through the center of the part of the heat transfer tube 1 that has the elongated-section short-axis length DB.
  • the shape of the heat transfer tube 1 is the same as that before the heat transfer tube 1 is rotated. Therefore, when a heat exchanger is manufactured such that a plurality of heat transfer tubes 1 are arranged, the heat transfer tubes 1 can be arranged without the need to consider the orientation of the heat transfer tubes 1. It is therefore possible to improve the manufacturability of the heat exchanger.
  • Embodiment 7 of the present disclosure will be described.
  • the extension portion or portions 1B are subjected to heat transfer promotion processing.
  • Embodiment 7 is different from Embodiments 1 to 6. It should be noted that regarding Embodiment 7, components that are the same as those in any of Embodiments 1 to 6 will be denoted by the same reference signs, and their detailed descriptions will thus be omitted.
  • Fig. 10 is a perspective view illustrating an example of the configuration of a heat transfer tube according to Embodiment 7.
  • the heat transfer tube 1 includes the main body 1A and the extension portion or portions 1B as in Embodiments 1 to 6.
  • the extension portion or portions 1B each have a heat-transfer promotion portion 12 that promotes heat transfer from the second heat exchange fluid, such as cut-and-raised portions or irregularities.
  • the heat-transfer promotion portion 12 is formed by performing press working on part of the plate material that corresponds to the extension portion 1B in the plate material. It should be noted that in this example, the heat-transfer promotion portion 12 is provided at least at outer part of the extension portion 1B, however, location of the heat-transfer promotion portion 12 is not limited to that of the above example. For example, the heat-transfer promotion portion 12 may also be provided, for example, at inner part of the extension portion 1B.
  • the extension portion 1B has the heat-transfer promotion portion 12.
  • the second heat exchange fluid strikes the heat-transfer promotion portion 12, thereby forming a swirl flow of the fluid.
  • the outer heat transfer coefficient of the heat transfer tube 1 is improved, and the heat transfer tube 1 for use in the heat exchanger can further improve the heat exchange performance of the heat exchanger.
  • Embodiment 8 of the present disclosure will be described.
  • the description concerning Embodiment 8 refers to the case where the heat transfer tube 1 described regarding each of Embodiments 1 to 7 is provided in a heat exchanger. It should be noted that regarding Embodiment 8, components that are the same as those of any of Embodiments 1 to 7 will be denoted by the same reference signs, and their detailed descriptions will thus be omitted.
  • Fig. 11 is a schematic sectional view illustrating an example of the configuration of a heat exchanger according to Embodiment 8.
  • Fig. 11 illustrates a section of a heat exchanger 20A that is taken along a plane that extends in the first and second directions as the heat exchanger 20A is viewed in the third direction.
  • the heat exchanger 20A is a fin-and-tube heat exchanger.
  • the heat exchanger 20A is made up of a plurality of fins 21 and a plurality of heat transfer tubes 1 each of which is described regarding Embodiments 1 to 7 and which are arranged in parallel.
  • Each of fins 21 is provided between associated adjacent two of the heat transfer tubes 1, and is joined to both the associated adjacent heat transfer tubes 1.
  • the following description is made concerning the heat exchanger 20A including the heat transfer tubes 1 each of which corresponds to the heat transfer tube 1 according to Embodiment 3.
  • the heat transfer tubes 1 are provided to extend in the third direction.
  • the heat transfer tubes 1 are arranged in parallel in the second direction. That is, the heat transfer tubes 1 are arranged in parallel in a direction perpendicular to both the flow direction of the first heat exchange fluid and the flow direction of the second heat exchange fluid.
  • headers (not illustrated) are connected to opposite ends of each of the heat transfer tubes 1 in the third direction.
  • the fins 21 are, for example, corrugated fins, and each provided between associated adjacent two of the heat transfer tubes 1.
  • Each of the fins 21 is a plate-like member made of metal material having a high heat conductivity, such as aluminum.
  • each fin 21 the plate-like member is bent and shaped such that flat portions and curved portions (both not illustrated) of the plate-like member are alternately arranged.
  • the flat portions are arranged substantially in parallel and at regular intervals.
  • the curved portions of the fins 21 are connected to the outer tube walls 10 of the heat transfer tubes 1 by brazing, welding, or other methods.
  • the flat portions of the fins 21 are subjected to processing to form slits, cut-and-raised portions, or irregularities in order to promote heat transfer.
  • Fig. 12 is a schematic sectional view illustrating another example of the configuration of the heat exchanger according to Embodiment 8.
  • Fig. 12 illustrates a section of a heat exchanger 20B that is taken along a plane that extends in the first and second directions, as the heat exchanger 20B is viewed in the third direction, as well as Fig. 11 .
  • This example is an example of the heat exchanger 20B including the heat transfer tubes 1 each of which corresponds to the heat transfer tube 1 according to Embodiment 4.
  • the abovementioned portion or portions of the outer tube wall 10 extend along the central axis.
  • the heat exchanger 20B spaces 22 are provided between the heat transfer tube 1 and the fin 21.
  • the space 22 serves as a water passage through which dew condensation water is discharged.
  • each of the heat exchangers 20A and 20B according to Embodiment 8 includes the heat transfer tubes 1 each of which is described regarding Embodiments 1 to 7.
  • Each of the fins 21 is provided between associated adjacent two of the heat transfer tubes 1.
  • the heat transfer tubes 1 each have the extension portion or portions 1B as described regarding Embodiments 1 to 7, and thus has a larger outer heat transfer area Ao than existing fin-and-tube heat exchangers. Therefore, the heat exchangers 20A and 20B according to Embodiment 8 can improve the heat exchange performance, as compared with the existing heat exchangers.
  • the heat exchanger 20B including the heat transfer tubes 1 each of which corresponds to the heat transfer tube 1 according to Embodiment 4 is provided with water passages through which dew condensation water is discharged, and thus can improve a drainage performance. Since the drainage performance is improved, it is possible to improve a latent-heat exchange performance or reduce a defrosting operation time that is time in which the heat exchanger 20B is defrosted.
  • Embodiment 9 of the present disclosure will be described.
  • a plurality of heat transfer tubes 1 each of which is described regarding Embodiments 1 to 7 are provided in a heat exchanger.
  • Embodiment 9 is the same as Embodiment 8.
  • a fin is not provided.
  • components that are the same as those in any of Embodiments 1 to 8 will be denoted by the same reference signs, and their detailed descriptions will thus be omitted.
  • Fig. 13 is a schematic view illustrating an example of the configuration of a heat exchanger according to Embodiment 9.
  • Fig. 13 illustrates a side of a heat exchanger 30 as viewed in the first direction.
  • the heat exchanger 30 according to Embodiment 9 is configured such that only a plurality of heat transfer tubes 1 each of which is described above regarding Embodiments 1 to 7 are arranged in parallel, as well as the heat exchangers 20A and 20B according to Embodiment 8.
  • the heat transfer tubes 1 are provided to extend in the third direction.
  • the heat exchanger 30 is provided such that the third direction is parallel to the direction of gravity.
  • the heat transfer tubes 1 are arranged in parallel to each other in the second direction. That is, the heat transfer tubes 1 are arranged in parallel in a direction perpendicular to both the flow direction of the first heat exchange fluid and the flow direction of the second heat exchange fluid.
  • headers 31A and 31B are connected to opposite ends of the heat transfer tubes 1 in the third direction, respectively.
  • the heat exchanger 30 In the heat exchanger 30, no fins 21 are provided. Needless to say, the heat exchanger 30 is not configured such that fins 21 are each provided between adjacent ones of the heat transfer tubes 1. Therefore, a space or spaces are provided between the adjacent heat transfer tubes 1. Thus, it is possible to improve drainage of dew condensation water that is generated when dew condensation occurs on a surface of the heat exchanger 30.
  • the heat exchanger 30 according to Embodiment 9, as well as the heat exchanger according to Embodiment 8, can improve the heat exchange performance, as compared with the existing heat exchangers.
  • the heat exchanger 30 according to Embodiment 9 is provided such that the third direction that is the flow direction of the first heat exchange fluid is parallel to the direction of gravity, and no fins are provided. Needless to say, the heat exchanger 30 is not configured such that fins are each provided between adjacent ones of the heat transfer tubes 1.
  • the heat exchanger 30 can improve drainage of dew condensation water. Furthermore, because of improvement of drainage of dew condensation water, the latent-heat exchange performance can be improved, or the defrosting operation time in which the heat exchanger 30 is defrosted can be reduced.
  • 1 heat transfer tube
  • 1A main body
  • 1B extension portion
  • 10 outer tube wall
  • 10a outer-wall layered portion
  • 11 inner tube wall
  • 11a layered portion
  • 11b partition portion
  • 12 heat-transfer promotion portion
  • 20A, 20B, 30 heat exchanger
  • 21 fin
  • 22 space
  • 31A, 31B header

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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)

Claims (10)

  1. Wärmeübertragungsleitung (1), aufweisend:
    einen länglichen Hauptkörper (1A), aufweisend eine äußere Leitungswand (10), eine innere Leitungswand (11) und eine Vielzahl von Strömungsdurchlässen, wobei die äußere Leitungswand (10) und die innere Leitungswand (11) durch mehrmaliges Biegen eines einzelnen Plattenmaterials gebildet werden, und die Vielzahl von Strömungsdurchlässen von der äußeren Leitungswand (10) und der inneren Leitungswand (11) umgeben und definiert sind; und gekennzeichnet durch
    einen Verlängerungsabschnitt (1B), der mit mindestens einem der Endabschnitte des einzelnen Plattenmaterials korrespondiert, wobei der Verlängerungsabschnitt (1B) so geformt ist, dass sich der mindestens eine der Endabschnitte des einzelnen Plattenmaterials von dem Hauptkörper (1A) in einer Langachsenrichtung eines länglichen Abschnitts erstreckt, die eine Richtung entlang einer langen Achse eines Abschnitts des Hauptkörpers (1A) ist, der Verlängerungsabschnitt (1B) so ausgebildet ist, dass er sich von der äußeren Leitungswand (10) in einer Richtung parallel zu der Langachsenrichtung des länglichen Abschnitts erstreckt, wobei der Verlängerungsabschnitt (1B) länger als eine kurze Achse des Abschnitts des Hauptkörpers (1A) ausgebildet ist.
  2. Wärmeübertragungsleitung (1) nach Anspruch 1, wobei ein Teil der äu-βeren Leitungswand (10), der sich in einer Kurzachsenrichtung eines verlängerten Abschnitts erstreckt, die eine Richtung entlang der kurzen Achse des Abschnitts des Hauptkörpers (1A) ist, ein Außenwand-Schichtabschnitt (10a) ist, der eine doppelschichtige Struktur aufweist.
  3. Wärmeübertragungsleitung (1) nach Anspruch 2, wobei der Außenwand-Schichtabschnitt (10a) eine Länge hat, die größer oder gleich der Hälfte der Länge der kurzen Achse ist.
  4. Wärmeübertragungsleitung (1) nach einem der Ansprüche 1 bis 3, wobei sich ein Teil der äußeren Leitungswand (10) in einer Richtung entlang einer durch ein Zentrum der kurzen Achse verlaufenden Achse erstreckt, nachdem er in Richtung der durch das Zentrum der kurzen Achse verlaufenden Achse gebogen wurde.
  5. Wärmeübertragungsleitung (1) nach einem der Ansprüche 1 bis 4, wobei die Gesamtheit der äußeren Leitungswand (10) so geformt ist, dass sie eine zweischichtige Struktur oder eine mehrschichtige Struktur aufweist.
  6. Wärmeübertragungsleitung (1) nach einem der Ansprüche 1 bis 5, wobei die äußere Leitungswand (10) und die innere Leitungswand (11) symmetrisch sind in Bezug auf einen Schnittpunkt einer Achse, die durch ein Zentrum der langen Achse des Abschnitts des Hauptkörpers (1A) verläuft, und einer Achse, die durch das Zentrum der kurzen Achse verläuft.
  7. Wärmeübertragungsleitung (1) nach einem der Ansprüche 1 bis 6, wobei der Verlängerungsabschnitt (1B) einen Wärmeübertragungsförderungsabschnitt (12) aufweist, der eingerichtet ist, Wärmeübertragung von Fluid, das über eine Außenfläche des Verlängerungsabschnitts (1B) strömt, zu fördern.
  8. Wärmeübertragungsleitung (1) nach einem der Ansprüche 1 bis 7, wobei beide Seiten einer Basis des einzelnen Plattenmaterials mit Hartlötmaterial beschichtet sind.
  9. Wärmetauscher (30), umfassend eine Vielzahl von Wärmeübertragungsleitungen (1), die mit der Wärmeübertragungsleitung (1) nach einem der Ansprüche 1 bis 8 identisch sind, wobei
    die Vielzahl von Wärmeübertragungsleitungen (1) parallel zueinander entlang einer Richtung senkrecht zu einer Strömungsrichtung eines ersten Wärmeaustauschfluids und einer Strömungsrichtung eines zweiten Wärmeaustauschfluids angeordnet sind, wobei das erste Wärmeaustauschfluid durch die Vielzahl von Strömungsdurchlässen strömt und das zweite Wärmeaustauschfluid über eine Außenfläche des Hauptkörpers (1A) strömt, und
    ein Zwischenraum oder Zwischenräume jeweils zwischen zugeordneten benachbarten Leitungen der Vielzahl von Wärmeübertragungsleitungen (1) ohne eine Rippe (21) oder Rippen (21) vorgesehen sind.
  10. Wärmetauscher (30) nach Anspruch 9, wobei der Wärmetauscher so angeordnet ist, dass die Strömungsrichtung des ersten Wärmeaustauschfluids parallel zu einer Schwerkraftrichtung verläuft.
EP19937853.0A 2019-07-18 2019-07-18 Wärmeübertragungsrohr und wärmetauscher damit Active EP4001821B1 (de)

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PCT/JP2019/028190 WO2021009889A1 (ja) 2019-07-18 2019-07-18 伝熱管およびそれを用いた熱交換器

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JPS60185884U (ja) * 1984-05-22 1985-12-09 昭和アルミニウム株式会社 熱交換器
JPS61198884U (de) * 1985-05-27 1986-12-12
JP2517872Y2 (ja) * 1989-12-29 1996-11-20 昭和アルミニウム株式会社 熱交換器
JPH09159386A (ja) * 1995-12-13 1997-06-20 Sanden Corp 多管式熱交換器
JP3536275B2 (ja) * 1997-01-21 2004-06-07 東洋ラジエーター株式会社 熱交換器用チューブ
JP2000227293A (ja) * 1999-02-05 2000-08-15 Zexel Corp 熱交換器及びその製造方法
KR100378055B1 (ko) * 2000-12-21 2003-03-29 만도공조 주식회사 열교환기의 냉매튜브와 그 제조방법
JP2009168361A (ja) * 2008-01-17 2009-07-30 Sanden Corp 熱交換器用チューブ及びその製造方法
US20130206376A1 (en) * 2012-02-14 2013-08-15 The University Of Tokyo Heat exchanger, refrigeration cycle device equipped with heat exchanger, or heat energy recovery device
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JP2018204919A (ja) 2017-06-09 2018-12-27 カルソニックカンセイ株式会社 熱交換チューブ及び熱交換器
WO2019026239A1 (ja) * 2017-08-03 2019-02-07 三菱電機株式会社 熱交換器、及び冷凍サイクル装置
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CN209310597U (zh) * 2018-12-18 2019-08-27 杭州三花微通道换热器有限公司 换热管及具有该换热管的换热器

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CN114072627A (zh) 2022-02-18
EP4001821A4 (de) 2022-07-06
JP7262586B2 (ja) 2023-04-21
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CN114072627B (zh) 2023-12-22
JPWO2021009889A1 (ja) 2021-11-25
WO2021009889A1 (ja) 2021-01-21

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