EP2573494B1 - Use of a heat exchanger for the supply of hot water - Google Patents

Use of a heat exchanger for the supply of hot water Download PDF

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Publication number
EP2573494B1
EP2573494B1 EP11783340.0A EP11783340A EP2573494B1 EP 2573494 B1 EP2573494 B1 EP 2573494B1 EP 11783340 A EP11783340 A EP 11783340A EP 2573494 B1 EP2573494 B1 EP 2573494B1
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EP
European Patent Office
Prior art keywords
fluid
flat tube
supply
tubular space
grooves
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP11783340.0A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2573494A1 (en
EP2573494A4 (en
Inventor
Masashige Hashimoto
Kenji Murata
Hidenori Yoshioka
Yasuhiko Suzuki
Masayuki Mizuta
Kazuhiro Nishida
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Yjs Co Ltd
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Yjs Co Ltd
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Filing date
Publication date
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Publication of EP2573494A1 publication Critical patent/EP2573494A1/en
Publication of EP2573494A4 publication Critical patent/EP2573494A4/en
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Publication of EP2573494B1 publication Critical patent/EP2573494B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—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
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/02—Casings; Cover lids; Ornamental panels
    • 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
    • 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
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/02—Reinforcing means for casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/14—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes molded
    • F28F2255/143—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes molded injection molded

Definitions

  • This invention relates to the use of a heat exchanger for the supply of hot water, and more specifically to a heat exchanger capable of exchanging heat with significantly high efficiency according to the preamble of claim 1.
  • a heat exchanger is already known from JP H05 10694A .
  • EP 0 840 081 A2 refers to a heat exchanger and a method of manufacturing same.
  • a first tube is constructed by connecting a plate material into a tubular shape.
  • the first tube is disposed around the second tube, and the first tube and the second tube are fixed by connecting the plate material in such a manner that the inner fin is in contact with the both tubes.
  • US 2009/183861 A1 refers to the use of a heat exchanger for the cooling of exhaust gases.
  • a typical flat type heat exchanger used to supply hot water includes a flat elongated outer case in which at least one flat tube is mounted in the outer case with a gap left between the outer surface of the flat tube and the inner wall of the outer case as a fluid passage. Heated fluid is fed through the fluid passage from one to the other end, while fluid to be heated is fed through a flow passage defined in the flat tube from the other end thereof to the one end. Thus, heat is exchanged between the heated fluid and the fluid to be heated, which flow outside and inside of the flat tube, thus heating the fluid fed through the flow passage defined in the tube.
  • the flat tube of a conventional such heat exchanger is made of a material having high heat conductivity in an attempt to improve heat exchange efficiency between fluid fed through the fluid passage outside the flat tube and fluid fed through the flow passage defined in the flat tube.
  • Patent document 1 JP Utility Model Registration 3133996
  • An object of the present invention is to provide a use of a heat exchanger for the supply of hot water of which the heat exchange efficiency is significantly improved.
  • the outer case comprises a lower half member and an upper half member disposed over and joined to the lower half member, the lower and upper half members having opposed recessed grooves opposed to each other and defining the tubular space, and the fluid flow rectifying grooves are formed in bottom surfaces of the opposed recessed grooves.
  • the outer case comprises a lower half member carrying mounting frames at two ends thereof to which fluid supply and discharge heads are mounted, respectively, and an upper half member having a length such that it is received between the mounting frames.
  • the lower half member is formed with three longitudinal recessed grooves on its top surface
  • the upper half member is formed with three longitudinal recessed grooves on its bottom surface.
  • the upper and lower half members are joined together with an annular packing disposed between the abutting outer edges of the upper and lower half members. With the upper and lower half members joined together, tubular spaces are defined between the respective longitudinal recessed grooves of the lower half member and the corresponding longitudinal recessed grooves of the upper half members. Flat tubes are inserted in the respective tubular spaces.
  • a large number of longitudinally extending narrow fluid flow rectifying grooves are formed on the bottom surface of each of the longitudinal recessed grooves so as to be arranged parallel to each other in the width direction.
  • the fluid flow rectifying grooves define fluid passages for fluid that flows outside the respective flat tubes.
  • the outer case comprises a case body in the shape of a pipe, and two fluid passage forming members in the form of split members that are joined together into a tubular member and received in the case body, the fluid passage forming members being formed with opposed recessed grooves on opposed surfaces of the respective fluid passage forming members, the opposed recessed grooves defining the tubular space, in which the flat tube is received.
  • the fluid flow rectifying grooves are formed in bottom surfaces of the opposed recessed grooves.
  • the surface area increasing shape of the peripheral wall of the flat tube may be one kind selected from the group consisting of a longitudinally continuous helical corrugation or corrugations, longitudinally continuous corrugations, corrugations continuous in section in a width direction, longitudinally extending fins formed on an outer surface of the peripheral wall of the flat tube so as to be spaced apart from each other in the width direction.
  • the heat exchanger further comprises fluid supply and discharge heads watertightly fixed to the respective ends of the outer case, respectively, each of the fluid supply and discharge heads comprising a supply and discharge pipe for a first fluid communicating with a flow passage defined in the flat tube, and a supply and discharge pipe for a second fluid communicating with the fluid passage of the outer case.
  • the flat tube is made of a material having high heat conductivity, and has a flat elliptical section that snugly fits in the tubular space. Its length is determined such that its ends protrude from the respective mounting frames of the lower half member, and its interior serves as the fluid flow passage.
  • the peripheral wall of the flat tube has the surface area increasing shape at its portion located inside of the tubular space.
  • the helical corrugation or corrugations may be thread or threads having an arcuate section. If the surface area increasing shape comprises double helical corrugations, such double helical corrugations may comprise two threads which are inclined in opposite directions to each other.
  • the flat tube has a structure similar to an ordinary corrugated pipe. If the surface area increasing shape comprises corrugations continuous in section in the width direction, the corrugations may comprise alternating arcuate recesses and protrusions, or may consist only of continuous recesses, or continuous chevron-shaped corrugations.
  • the surface area increasing shape of the peripheral wall of the flat tube significantly increases the surface areas of both inner and outer surfaces of the flat tube, which in turn markedly improve the efficiency of heat exchange between fluids that flow inside and outside of the flat tube.
  • the fluid passages formed in the inner surface of the tubular space of the outer case are defined by the large number of fluid flow rectifying grooves extending parallel to each other, the fluid flow rectifying grooves rectify, and thus increase the speed of, the flow of fluid that flows outside the flat tube.
  • the fluid flow rectifying grooves rectify, and thus increase the speed of, the flow of fluid that flows outside the flat tube.
  • the heat exchange efficiency further dramatically increases due to the synergetic effect between the surface area increasing shape of the flat tube and the fluid flow rectifying grooves, which define the fluid passages.
  • FIGs. 1 to 6 show the heat exchanger according to the first embodiment of the invention.
  • This heat exchanger 1 includes a longitudinally elongated flat outer case 2 formed with three tubular spaces 3 extending through the entire length of the outer case 2 in parallel to each other.
  • Flat tubes 4 are received in the respective tubular spaces 3.
  • the tubular spaces 3 are each formed with fluid passages 5 in its inner periphery through which a first fluid can flow in the longitudinal direction, and the interiors of the flat tubes 4 each define a flow passage 6 through which a second fluid can flow such that heat can be exchanged between the first and second fluids.
  • Fluid supply and discharge heads 7 and 8 are watertightly fixed to the respective ends of the outer case 2.
  • the fluid supply and discharge heads 7 and 8 have fluid supply and discharge passages 9 for the first fluid, respectively, which communicate with the respective first and second longitudinal ends of the fluid passages 5.
  • the fluid supply and discharge heads 7 and 8 further include fluid supply and discharge passages 10 for the second fluid, which communicates with the respective first and second longitudinal ends of the flow passages 6, which are defined in the respective flat tubes 4.
  • the heat exchanger 1 has a flat shape.
  • the outer case 2 is formed by assembling together lower half and upper half members 2a and 2b which are made of a synthetic resin or a metal.
  • the lower half member 2a is a longitudinally elongated flat strip having mounting frames 11 at the respective longitudinal ends thereof to which the respective fluid supply and discharge heads 7 and 8 are mounted.
  • the lower half member 2a has in its top surface three recessed grooves 12 extending longitudinally parallel to each other.
  • the upper half member 2b is a flat strip substantially equal in width to the lower half member 2a and having a length such that it is received between the mounting frames 11 at the respective longitudinal ends.
  • the upper half member 2b has a bottom surface located over the lower half member 2a and formed with recessed grooves 13 facing the respective recessed grooves 12 of the lower half member 2a so as to extend the entire length of the upper half member 2b.
  • the upper half member 2b is placed on top of the lower half member 2a with an annular packing 14 disposed therebetween along their outer edges, and the two members 2a and 2b are assembled into the outer case 2 by tightening screws at a plurality of locations.
  • the upper half member 2b With the upper half member 2b disposed over the lower half member 2a as shown in Fig. 4(a) , the upper half member 2b is placed on top of the lower half member 2a and the screws are tightened at the plurality of locations.
  • the recessed grooves 12 of the lower half member 2a are located under and communicate with the respective recessed grooves 13 of the upper half member 2b, defining the respective three flat tubular spaces 3, which are arranged parallel to each other, while being spaced from each other.
  • the tubular spaces 3 are surrounded, and watertightly sealed from outside, by the annular packing 14, which are disposed between the lower half member 2a and the upper half member 2b along their outer edges placed one over the other.
  • the recessed grooves 12 and 13 have such cross-sectional shapes that the recessed grooves 12 and 13 can be located right under and right over the respective flat tubes 4.
  • the fluid passages 5 are defined in the inner peripheral surface of each tubular space 3.
  • the fluid passages 5 are defined by fluid flow rectifying grooves 5a formed in the bottom surfaces of the recessed grooves 12 of the lower half member 2a and in the top surfaces of the recessed grooves 13 of the upper half member 2b so as to extend the entire length of the lower half member 2a and the upper half member 2b.
  • the fluid flow rectifying grooves 5a are narrow grooves each having a relatively small cross-sectional area, and a large number of them are arranged in the width direction of each of the recessed grooves 12 and 13 at regular intervals.
  • Narrow ribs 5b provided between the adjacent grooves 5a and defining the grooves 5a form, in cooperation with the grooves 5a, a rugged terrain on the surface of each recessed groove 12, 13.
  • the first fluid When the first fluid is fed through the fluid passages 5, which are defined by the fluid flow rectifying grooves 5b outside the respective flat tubes 4, the first fluid flows in the longitudinal direction while kept in contact with the flat tubes 4, so that the flow of the first fluid is rectified along the longitudinal shape of the fluid flow rectifying grooves 5. This speeds up the flow of the first fluid.
  • the depth, width and intervals of the fluid flow rectifying grooves 5a formed on the surface of each recessed groove 12, 13 are not particularly limited.
  • the grooves 5a may extend longitudinally in straight lines as viewed from top, or as shown in Figs. 2(b) and 3(b) , the grooves 5a may extend longitudinally in a zigzag manner, as viewed from top.
  • the grooves 5b extending in a zigzag manner increases the length of contact of the first fluid with the outer surface of the flat tubes 4, thus improving the efficiency of heat exchange.
  • the flat tubes 4 are made of e.g. a metal having high heat conductivity, and have a flat elliptical cross-section such that they can be snugly fitted in the respective tubular spaces 3, which are defined by the recessed grooves 12 and 13.
  • the flat tubes 4 each have their respective ends protruding by a predetermined length from the respective mounting frames 11, which are provided at both ends of the lower half member 2a.
  • the flat tubes 4 each have a peripheral wall having a surface-area-increasing shape 15 at its longitudinal portion located inside the tubular space 3.
  • Figs. 5(a) to 5(e) and Figs. 6(a) to 6(d) show different surface area increasing shapes 15.
  • the shape 15 shown in Fig. 5(a) and 5(b) comprises a single or multiple longitudinally continuous helical corrugations or threads having an arcuate section and formed on the peripheral wall of each flat tube 4.
  • the shape 15 shown in Fig. 5(c) comprises two helical threads formed on the peripheral wall of each flat tube 4 so as to be inclined in the opposite directions to each other and overlap with each other.
  • the shape 15 shown in Figs. 5(d) and 5(e) comprises longitudinally continuous corrugations, i.e. alternating circular recesses and protrusions formed on the peripheral wall of each flat tube 4.
  • This flat tube of this embodiment is therefore similar to a well-known corrugated pipe.
  • the surface area increasing shapes 15 of Figs. 6(a) to 6(d) each comprise bent shapes formed on the top and bottom surfaces of the peripheral wall of each flat tube 4 so as to be continuous in the width direction, the peripheral wall having a flat rectangular widthwise section.
  • the shape 15 of Fig. 6(a) has a corrugated section comprising alternating arcuate recesses and protrusions that are continuous with each other.
  • the shape 15 of Fig. 6(b) comprises, in section, a plurality of continuous U-shaped recesses.
  • the shape 15 of Fig. 6(c) comprises, in section, a plurality of continuous chevron-shaped corrugations.
  • the surface area increasing shape 15 of Fig. 6(d) comprises a large number of fins 15a protruding from the top and bottom outer surfaces of the peripheral wall of each flat tube 4 so as to be arranged at regular intervals in the width direction, the peripheral wall having a flat rectangular cross-section.
  • any one of the shapes shown in Figs. 5(a) to 5(e) and Figs. 6(a) to 6(d) may be selected as the surface area increasing shape 15 formed on the peripheral wall of each flat tube 4.
  • the depth of each of the fluid passages 5, which surround the flat tubes 4 varies in the longitudinal direction. But since its depth never decreases below the depth of the fluid flow rectifying groove 5a, the first fluid can reliably flow through the respective fluid passages 5.
  • the fluid supply and discharge heads 7 and 8 each include a U-shaped mounting portion 17 watertightly fitted around the mounting frame 11 through a packing 16 fitted around the mounting frame 11.
  • the fluid supply and discharge passage 9 for the first fluid and the fluid supply and discharge passage 10 for the second fluid are provided outside the mounting portion 17.
  • the fluid supply and discharge passages 9 for the first fluid watertightly communicate with the respective ends of the fluid passages 5 of the outer case 2
  • the fluid supply and discharge passages 10 for the second fluid watertightly communicate with the respective ends of the flow passages 6 defined in the respective flat tubes 4, which are received in the respective tubular spaces 3 of the outer case 2.
  • Figs. 7(a) and 7(b) show a heat exchanger according to the second embodiment of this invention. Elements identical to those of the first embodiment are denoted by identical numerals and their description is omitted.
  • the heat exchanger 1 of the second embodiment does not include the annular packing 14 and the screws, which are used in the outer case 2 of the first embodiment.
  • the heat exchanger of this embodiment includes a case body 21 in the form of a monolithic pipe having a flat rectangular cross-section, and a plurality of pairs of fluid passage forming members 22 mounted in the case body 21.
  • the mounting frames 11 are mounted on the outer surface of the case body 21 at the respective end portions thereof.
  • the interior of the case body 21 is partitioned into four tubular chambers 24 arranged in parallel to each other and each having a slightly larger sectional area than that of the flat tubes 4, by partitioning walls 23.
  • Each pair of fluid passage forming members 22 are longitudinally split thin strips having a length equal to the length of the case body 21 and forming a square tube which can be snugly received in one of the tubular chambers 24.
  • a tubular space 3 is defined by opposed recessed grooves of the respective fluid passage forming members 22 in which a flat tube 4 can be snugly received.
  • a large number of longitudinally continuous thin fluid flow rectifying grooves 5a similar to those of the first embodiment are formed on the bottom surface of the recessed groove of each fluid passage forming member 22 so as to be arranged in parallel to each other in the width direction of the fluid passage forming member 22.
  • the flat tubular heat exchanger 1 of the second embodiment is assembled as follows: The respective pairs of fluid passage forming members are combined together and inserted into the respective tubular chambers 24; the flat tubes 4 are inserted through the tubular spaces 3 defined between the respective pairs of fluid passage forming members 22; and the fluid supply and discharge heads 7 and 8 are fixed to the respective mounting frames 11 at the respective ends of the case body 21 such that the fluid supply and discharge passages 9 for the first fluid of the respective heads 7 and 8 watertightly communicate with the respective ends of the fluid passages 5 of the outer case 2, and the fluid supply and discharge passages 10 for the second fluid of the respective heads 7 and 8 watertightly communicate with the respective ends of the flow passages 6 defined in the respective flat tubes 4.
  • Fig. 8 shows the heat exchanger of the third embodiment, of which the outer case 2 includes, as in the second embodiment, a case body 21 and fluid passage forming members 22.
  • the third embodiment is characterized in that the case body 21 can be easily formed by molding of synthetic resin and can be made long.
  • the fluid passage forming members 22 of this embodiment are similar to those of the second embodiment in that each pair are longitudinally split strips. With the respective pairs combined into square tubes, the fluid passage forming members 22 are set in a mold for forming the case body 21, which is in the shape of a square tube, and a resin is injected into the mold to form the case body 21 with the pairs of fluid passage forming members 22 embedded in the resin. The case body 21 is thus formed by insert molding.
  • the case body 21 can be formed by insert molding using a mold including upper and lower split mold members. Since no draft is necessary as in the case with a monolithic pipe, a long case body 21 can be formed from synthetic resin. Since the fluid passage forming members 22 are longitudinally split members, they can also be formed using split molds. By using such molds, a large number of thin fluid flow rectifying grooves 5a can be easily formed on the fluid passage forming members 22, even if they are non-straight complex-shaped grooves such as zigzag grooves.
  • the fluid passage forming members 22 can also be formed easily by cutting or pressing a metal.
  • the case body 21 is formed by insert molding with two pairs of the fluid passage forming members 22 set in the case body 21 in parallel to each other.
  • the mounting frames 11 are integrally formed at the respective ends of the case body 21, and a large number of reinforcing ribs 27 are formed on the outer periphery of the case body 21 at predetermined intervals.
  • Two or more of such case bodies 21 are connected together at their abutting ends through the mounting frames 11 and a connecting member 28 to form a long heat exchanger.
  • the outer case 2 is formed by combining the lower half member 2a and the upper half member 2b.
  • the flat tubes 4 are inserted into the respective tubular spaces 3 defined in the outer case 2.
  • a supply pipe 29 for heating fluid is connected to the fluid supply and discharge passage 9 for the first fluid of the fluid supply and discharge head 7, which is mounted at one end of the outer case 2.
  • a discharge pipe 30 for heating fluid is connected to the fluid supply and discharge passage 9 for the first fluid of the fluid supply and discharge head 8, which is mounted at the other end of the outer case 2.
  • a discharge pipe 31 for fluid to be heated is connected to the fluid supply and discharge passage 10 for the second fluid of the fluid supply and discharge head 7.
  • a supply pipe 32 for fluid to be heated is connected to the fluid supply and discharge passage 10 for the second fluid of the fluid supply and discharge head 8.
  • heating fluid is fed into the fluid passages 5, which are formed in the inner peripheries of the tubular spaces 3 of the outer case 2, from the supply pipe for heating fluid.
  • fluid to be heated is fed into the flow passages 6 defined in the respective flat tubes 4 from the supply pipe 32 for fluid to be heated.
  • the heating fluid and the fluid to be heated flow in the opposite longitudinal directions, outside and inside of the respective flat tubes 4.
  • heat is exchanged between the two fluids through the peripheral walls of the flat tubes 4.
  • the fluid to be heated is heated, while flowing through the flow passages 6 of the flat tubes 4, by the heat of the heating fluid, which is flowing through the outer fluid passages 5, and the thus heated hot water is discharged from the discharge pipe 31.
  • the surface area increasing shape 15 on the inner and outer surfaces of peripheral wall of each flat tube 4 provides a larger surface area and thus a larger contact area for both the heating fluid and the fluid to be heated.
  • the heat exchange efficiency thus improves corresponding to an increase in surface area due to the provision of the surface area increasing shape 15, which makes it possible to efficiently heat the fluid to be heated.
  • the flow of heating fluid through the fluid passages 5, which are located outside the flat tubes 4, is rectified by the thin fluid flow rectifying grooves 5a formed on the inner peripheries of the tubular spaces 3 in the longitudinal direction of the flat tubes in straight lines or in a zigzag pattern. Since the flow of the heating fluid is rectified and guided in the desired direction by the fluid flow rectifying grooves 5a, the heating fluid flows at an increased speed, which quickens displacement of the heating fluid in the fluid passages 5, thus improving the heat exchange efficiency.
  • the operation of the heat exchanger 1 of the second or third embodiment is the same as the above-described operation of the heat exchanger of the first embodiment.
  • the number of the flat tubes 4 used which is equal to the number of the tubular spaces 3 defined in the outer case 2, is not limited to two to four, as shown, and may be one or larger than four.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP11783340.0A 2010-05-18 2011-04-06 Use of a heat exchanger for the supply of hot water Active EP2573494B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2010114356 2010-05-18
JP2011065860A JP5559088B2 (ja) 2010-05-18 2011-03-24 熱交換器
PCT/JP2011/058709 WO2011145403A1 (ja) 2010-05-18 2011-04-06 熱交換器

Publications (3)

Publication Number Publication Date
EP2573494A1 EP2573494A1 (en) 2013-03-27
EP2573494A4 EP2573494A4 (en) 2014-10-15
EP2573494B1 true EP2573494B1 (en) 2022-03-30

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EP11783340.0A Active EP2573494B1 (en) 2010-05-18 2011-04-06 Use of a heat exchanger for the supply of hot water

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EP (1) EP2573494B1 (ja)
JP (1) JP5559088B2 (ja)
KR (1) KR101827401B1 (ja)
CN (1) CN102297614B (ja)
DE (1) DE112011101673T5 (ja)
MY (1) MY160271A (ja)
TW (1) TWI453367B (ja)
WO (1) WO2011145403A1 (ja)

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WO2013113362A1 (de) * 2012-01-30 2013-08-08 A-Heat Allied Heat Exchange Technology Ag Wärmetauscher
JP6057154B2 (ja) * 2012-09-28 2017-01-11 パナソニックＩｐマネジメント株式会社 熱交換器
KR101418089B1 (ko) * 2013-11-28 2014-07-09 주식회사 플로우포스 열교환 장치 및 그 제조방법
JP6321442B2 (ja) * 2014-05-08 2018-05-09 株式会社ワイ・ジェー・エス． 熱交換管及びこれを用いた熱交換器並びに熱交換装置
CN105043158A (zh) * 2015-09-07 2015-11-11 南宁八菱科技股份有限公司 一种单管加强套
EP3173710B1 (en) * 2015-11-25 2018-06-06 Daikin Industries, Limited Heat exchanger
IL248304B (en) 2016-10-10 2021-07-29 Magen Eco Energy A C S Ltd Heat exchanger and its module
KR20180078367A (ko) * 2016-12-29 2018-07-10 주식회사 효성 파이어 히터
DE102017101142A1 (de) 2017-01-20 2018-07-26 Otto Altmann Wärmetauscher bzw. Wärmetauscheranordnung für eine Kühleinrichtung und eine Kühleinrichtung mit einem solchen Wärmetauscher
US10401055B2 (en) * 2017-03-03 2019-09-03 Trane International Inc. Reduced drag combustion pass in a tubular heat exchanger
EP3389088A1 (en) * 2017-04-12 2018-10-17 ABB Schweiz AG Heat exchanging arrangement and subsea electronic system
CN111256495B (zh) * 2018-11-30 2021-12-07 比亚迪股份有限公司 换热器、车辆的热管理系统和车辆
KR102256025B1 (ko) 2020-11-06 2021-05-24 김필수 열교환기
CN113340129A (zh) * 2021-06-10 2021-09-03 祥博传热科技股份有限公司 一种高效换热器及其加工工艺

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Also Published As

Publication number Publication date
JP5559088B2 (ja) 2014-07-23
EP2573494A1 (en) 2013-03-27
MY160271A (en) 2017-02-28
EP2573494A4 (en) 2014-10-15
CN102297614B (zh) 2014-12-10
KR101827401B1 (ko) 2018-02-08
JP2012002495A (ja) 2012-01-05
WO2011145403A1 (ja) 2011-11-24
KR20130124150A (ko) 2013-11-13
DE112011101673T5 (de) 2013-05-08
TW201207349A (en) 2012-02-16
TWI453367B (zh) 2014-09-21
CN102297614A (zh) 2011-12-28

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