EP2390612A1 - Wärmetauscher und damit ausgerüstetes wärmepumpen-heisswasserversorgungsgerät - Google Patents

Wärmetauscher und damit ausgerüstetes wärmepumpen-heisswasserversorgungsgerät Download PDF

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Publication number
EP2390612A1
EP2390612A1 EP10733496A EP10733496A EP2390612A1 EP 2390612 A1 EP2390612 A1 EP 2390612A1 EP 10733496 A EP10733496 A EP 10733496A EP 10733496 A EP10733496 A EP 10733496A EP 2390612 A1 EP2390612 A1 EP 2390612A1
Authority
EP
European Patent Office
Prior art keywords
protruding portions
metal tube
fluid flow
heat exchanger
flow channel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP10733496A
Other languages
English (en)
French (fr)
Inventor
Tomonori Kikuno
Satoshi Inoue
Akihiro Fujiwara
Hyunyoung Kim
Yoshikazu Shiraishi
Kaori Yoshida
Takayuki Hyoudou
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries 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 Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP2390612A1 publication Critical patent/EP2390612A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • 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
    • F28D7/0008—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 for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—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 for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • F28D7/0033—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 for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes the conduits for one medium or the conduits for both media being bent
    • 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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • 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
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • 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
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • 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
    • F28D7/04—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 spirally coiled
    • 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
    • F28F2225/04—Reinforcing means for conduits

Definitions

  • the present invention has been created with the foregoing in view and it is an object of the present invention to provide a heat exchanger with excellent heat exchange efficiency and a heat pump type hot water supply apparatus equipped with such a heat exchanger.
  • the heat exchanger in accordance with the present invention includes a metal tube (47) that has a flat shape with a width greater than a thickness, a fluid flow channel (53) formed inside thereof along a longitudinal direction, respective outer surfaces (61, 63) formed on one side and the other side in a thickness direction, and a support portion (55) formed in the fluid flow channel (53) and inhibiting deformation in the thickness direction; and a multiple-hole metal tube (45) stacked on one side of the metal tube (47) in the thickness direction and having a flat shape with a width greater than a thickness, a plurality of fluid flow channels (51) formed inside thereof along the longitudinal direction, and the multiple-hole metal tube (45) having an opposing surface (65) disposed opposite the outer surface (61) on the one side of the metal tube (47) and joined by at least part thereof to the outer surface (61) on the one side.
  • Fig. 1 is a configuration diagram illustrating a heat pump type hot water supply apparatus according to an embodiment of the present invention.
  • Fig. 1 is a configuration diagram illustrating a heat pump type hot water supply apparatus 11 according to an embodiment of the present invention.
  • the heat pump type hot water supply apparatus 11 is provided with a coolant circuit 13 where a coolant is circulated and a hot water storage circuit 17 for boiling low-temperature water by heat exchange with the coolant of the coolant circuit 13 and storing high-temperature water in a tank 15.
  • the coolant circuit 13 has a compressor 19, a heat exchanger (water heat exchanger) 21, an expansion valve (pressure reducing mechanism) 23, an evaporator 25, and pipes connecting these components.
  • a heat exchanger water heat exchanger
  • an expansion valve pressure reducing mechanism
  • evaporator 25 evaporator
  • carbon dioxide can be used as the coolant circulating in the coolant circuit 13.
  • the coolant is compressed to a pressure equal to or higher than a critical pressure by the compressor 19.
  • the hot water storage circuit 17 has the tank 15 for storing water, a water inlet pipe 27 for introducing water from the tank 15 into the heat exchanger 21, a hot water outlet pipe 29 for returning water heated by heat exchange with the heat exchanger 21 into the tank 15, and a pump 31 that causes water to circulate in the hot water storage circuit 17.
  • the hot water supply apparatus 11 is provided with a control unit 33 that controls the coolant circuit 13 and the hot water storage circuit 17.
  • the control unit 33 introduces low-temperature water located in the tank 15 from a water outlet port provided in the bottom portion of the tank 15 into the heat exchanger 21 through the water inlet pipe 27.
  • the low-temperature water introduced into the heat exchanger 21 is heated in the heat exchanger 21 and returned into the tank 15 from the water inlet port provided in the upper portion of the tank 15 via the hot water outlet pipe 29.
  • high-temperature water is stored in the upper portion inside the tank 15, and the water temperature decreases toward the lower portion of the tank.
  • Fig. 2 is a perspective view illustrating the heat exchanger 21 according to the first embodiment of the present invention.
  • the heat exchanger 21 has a structure that is spirally wound so that one end 41 in the longitudinal direction is disposed on the inner side and the other end 43 in the longitudinal direction is disposed on the outer side.
  • the heat exchanger 21 performs heat exchange between the coolant circulating in the coolant circuit 13 and water circulating in the hot water storage circuit 17 in the hot water supply apparatus 11 shown in Fig. 1 .
  • the directions of the coolant and water flowing in the heat exchanger 21 are mutually opposite directions as shown in Fig. 1 . Therefore, where either of the coolant and water flows from the one end 41 to the other end 43 of the heat exchanger 21, the other fluid flows from the other end 43 toward the one end 41.
  • the temperature of water can thus be regulated by performing heat exchange between the water and coolant as the coolant and water pass through inside the heat exchanger 21.
  • Fig. 3 is a cross-sectional view taken along the III-III line in Fig. 2 .
  • the heat exchanger 21 has a structure in which a first multiple-hole metal tube 45, a metal tube 47, and a second multiple-hole metal tube 49 are stacked in the thickness direction in the order of description.
  • These metal tubes 45, 47, 49 are integrated by joining the opposing outer surfaces thereof by joining by the below-described resistance welding.
  • the metal tube 47 has a flat shape with a width greater than a thickness.
  • a fluid flow channel 53 extending in the longitudinal direction is formed inside the metal tube 47. Water circulating in the hot water storage circuit 17 flows in the fluid flow channel 53.
  • the ratio of fusion of the opposing surfaces 65, 67 to the outer surfaces 61, 63 can be increased by setting conditions such as to decrease the welding rate (feed rate) during resistance welding, increase the current value during welding, and increase the pressurizing force in the thickness direction during welding. Therefore, from the standpoint of heat exchange efficiency of the heat exchanger 21, it is preferred that substantially the entire opposing surfaces 65, 67 be fused to the outer surfaces 61, 63.
  • the first columnar body 55a and the second columnar body 55b may be also joined by the distal end portions thereof. Whether the distal end portions are joined to each other can be regulated by changing welding conditions during resistance welding. More specifically, the ratio of the distal end portions joined together can be increased, for example, by decreasing the welding rate (feed rate) during resistance welding, increasing the current value during welding, and increasing the pressurizing force in the thickness direction during welding.
  • Metals having thermal conductivity, corrosion resistance, rigidity, and machinability can be used as materials of the metal tube 47, first multiple-hole metal tube 45, and second multiple-hole metal tube 49.
  • suitable metals include aluminum and aluminum alloys.
  • the support members 55 may be from a material identical to that of the outer peripheral portion of the metal tube 47.
  • the support members 55 which inhibit deformation of the metal tube 47 in the thickness direction, are located in the fluid flow channel 53. Therefore, the metal tube 47 and multiple-hole metal tubes 45, 49 that are stacked in the thickness direction can be joined by resistance welding, while pressurizing the tubes in the thickness direction by a pair of roller electrodes 71, 73. Since the heat exchanger can be manufactured by resistance welding that excels in productivity, the cost can be reduced. Further, in the present embodiment, the metal tube 47 has support members 55 in the fluid flow channel 53. Therefore, deformation of the metal tube 47 can be inhibited even in long-term use of the heat exchanger.
  • the plurality of first columnar bodies 55a and second columnar bodies 55b that have distal end portions abutted on each other or disposed close to each other are arranged along the longitudinal direction of the fluid flow channel 53. Therefore, deformation of the metal tube 47 along the longitudinal direction can be inhibited over a long period. Moreover, since a configuration is used in which these columnar bodies 55a, 55b are arranged in a spot-like pattern in the longitudinal direction, the increase in resistance to flow of fluid in the fluid flow channel 53 caused by the arrangement of support members 55 can be inhibited and smooth fluid flow can be ensured.
  • the rigidity of the metal tube 47 can be increased. As a result, deformation of the metal tube 47 can be inhibited over a long period.
  • the multiple-hole metal tubes 45, 49 are stacked on both sides in the thickness direction of the metal tube 47, the efficiency of heat exchange between the coolant and water can be further increased.
  • the heat exchanger 21 of the present embodiment is sometimes used in a bent form for example such as shown in Fig. 2 .
  • some portions of the entire heat exchanger 21. in the longitudinal direction are curved, whereas other portions remain straight.
  • the support members 55 of the metal tube 47 have a function of inhibiting deformation of the metal tube 47 in the thickness direction during bending.
  • the resistance welding apparatus 100 is provided with a pair of roller electrodes 71, 73, a pressurizing device 75 that applies pressure to the roller electrode 71, a power supply device 79 that supplies electric power to the pressurizing device 75 and the roller electrodes 71, 73, and a control unit (not shown in the figure) that controls the operation of each unit.
  • the roller electrode 71 and the roller electrode 73 have a substantially round columnar shape and respectively have rotating shafts 72, 74 in the center thereof.
  • the rotating shaft 72 and the rotating shaft 74 are disposed substantially parallel to each other.
  • the width of the roller electrodes 71, 73 in the axial direction is designed to be greater than the width of the metal tube 47 and multiple-hole metal tubes 45, 49 that are the welding objects.
  • a motor (not shown in the figure) is connected to the rotating shaft 72, 74, and the shafts are supported on a support table (not shown in the figure) in a state in which each shaft can rotate about the axis thereof.
  • the motor is connected to the power supply device 79.
  • the roller electrode 71 and the roller electrode 73 rotate in the mutually opposite direction. For example, in the configuration shown in Fig. 5 , the roller electrode 71 rotates counterclockwise and the roller electrode 73 rotates clockwise. Further, the roller electrode 71 is supported on the support table so as to enable the movement thereof in the direction of approaching the roller electrode 73 and in the opposite direction (up-down direction in Fig. 5 ).
  • roller electrodes 71, 73 are connected to the power supply device 79, and electric power is supplied thereto from the power supply device 79 during resistance welding. It is possible to use a configuration in which only the roller electrode 71 moves in the up-down direction, as in the present embodiment, or a configuration in which the two roller electrodes 71, 73 move in the up-down direction.
  • the pressurizing device 75 is provided with a cylindrical cylinder 78, a piston 77 disposed inside the cylinder 78, and a pump (not shown in the figure) that generates energy such as air pressure or oil pressure.
  • a pump (not shown in the figure) that generates energy such as air pressure or oil pressure.
  • the pump is driven and the piston 77 is slidingly moved in a predetermined direction inside the cylinder 78.
  • the roller electrode 71 is pressurized.
  • the pressurized roller electrode 71 moves toward the roller electrode 73, and the metal tube 47 and the multiple-hole metal tubes 45, 49 disposed between the roller electrodes 71, 73 are pressurized in the thickness direction.
  • the metal tube 47, first multiple-hole metal tube 45, and second multiple-hole metal tube 49 are fabricated.
  • the metal tube 47 is obtained by bending a long thin metal sheet (not shown in the figure) so that the end portions thereof in the width direction face each other and an internal space is formed along the longitudinal direction and then joining together the opposing end sides.
  • the internal space extending in the longitudinal direction serves as the fluid flow channel 53.
  • the first multiple-hole metal tube 45 and the second multiple-hole metal tube 49 are obtained, for example, by extruding a metal material by using a die provided with an extrusion outlet port having a cross-sectional shape such as shown in Fig. 3 .
  • the metal tube 47, first multiple-hole metal tube 45, and second multiple-hole metal tube 49 obtained in the metal tube forming step are then stacked.
  • the first multiple-hole metal tube 45, metal tube 47, and second multiple-hole metal tube 49 are arranged so that longitudinal directions and thickness directions thereof are oriented in the same respective directions and the metal tubes are stacked in the thickness direction in the order of description.
  • the first multiple-hole metal tube 45, metal tube 47, and second multiple-hole metal tube 49 that have thus been stacked in the stacking step are supplied between the roller electrodes 71, 73, fed along the longitudinal direction, while being pressurized in the thickness direction by the roller electrodes 71, 73.
  • an electric current is supplied through the roller electrodes 71, 73 and the opposing outer surfaces of the metal tubes are resistance welded (seam welded) together.
  • the linear heat exchanger 21 is obtained in which the metal tubes are integrated as shown in Fig. 6 .
  • the outer surfaces 61, 63 of the metal tube 47 and the opposing surfaces 65, 67 of the multiple-hole metal tubes 45, 49 arte fused and a nugget 76 is continuously formed along the longitudinal direction in the side portion.
  • the resistance welding conditions include the pressurizing force created by the roller electrodes 71, 73, conduction time, standby time, current value during welding, welding rate (feed rate), electrode shape, and the like. These conditions are set as appropriate according to the welding object, application, etc.
  • the abovementioned resistance welding may be intermittent welding in which conduction periods and standby periods are repeated or continuous welding in which the conduction is continuous.
  • the metal tube 47 is slightly deformed in the thickness direction and the distal end portions of some or all of the plurality of first columnar bodies 55a and the plurality of second columnar bodies 55b abut on each other. Where the distal end portions thus abut on each other, deformation of the metal tube 47 in the thickness direction can be inhibited.
  • the heat exchanger 21 can be used as is, that is, in the linear form such as shown in Fig. 6 , or may be used upon bending spirally as shown in Fig. 2 . In the case of the form shown in Fig. 2 , the bending is performed so that the thickness direction of the metal tubes 45, 47, 49 is in the radial direction of the spiral.
  • the metal tube 47 having the support members 55 in the fluid flow channel 53 and the multiple-hole metal tubes 45, 49 are stacked and disposed between the roller electrodes 71, 73, and the metal tube 47 and the multiple-hole, metal tubes 45, 49 are moved along the longitudinal direction and resistance welded, while being pressurized in the thickness direction. Therefore, deformation of the metal tube 47 by pressure during resistance welding can be inhibited.
  • the welding can be performed in a state in which a sufficient pressure is applied by the roller electrodes 71, 73 in the thickness direction so that the outer surfaces 61, 63 of the metal tube 47 and the opposing surfaces 65, 67 of the multiple-hole metal tubes that are disposed opposite the outer surfaces are brought into intimate contact with each other.
  • the joining surface area of the outer surfaces 61, 63 and the opposing surfaces 65, 67 can be increased, deformation of the fluid flow channel 53 is inhibited and a flow channel necessary for the fluid to flow smoothly is ensured. Therefore, the efficiency of heat exchange between the coolant and fluid can be increased.
  • productivity can be increased.
  • Fig. 7 is a cross-sectional view illustrating the heat exchanger according to the second embodiment of the present invention. As shown in Fig. 7 , in the heat exchanger 21, the structure of the support members 55 is different from that of the first embodiment. Other components are assigned with same reference numerals as in the first embodiment and the explanation thereof is herein omitted.
  • the support members (support portions) 55 according to the second embodiment are constituted by a plurality of columnar bodies arranged along the longitudinal direction of the fluid flow channel 53. One end in an axial direction of each columnar body is joined to an inner surface (inner surface 57 or inner surface 59) on either side in the thickness direction of the fluid flow channel 53, and the other end in the axial direction of each columnar body is disposed on the inner surface side on the other side in the thickness direction of the fluid flow channel 53. All of the plurality of columnar bodies may be joined by one end thereof to the inner surface on the same side, or some of them may be joined to the inner surface on the other side.
  • Both ends in the axial direction of some or all of the plurality of columnar bodies are respectively joined to the inner surface 57 on one side and the inner surface 59 on the other side of the fluid flow channel 53.
  • the rigidity of the metal tube 47 can be increased.
  • the flexibility of the metal tube 47 can be maintained at a certain level.
  • the metal tube 47 according to the second embodiment may be fabricated in the same manner as the metal tube 47 according to the first embodiment.
  • the metal tube 47 is obtained by bending a flat metal sheet (not shown in the figure) so as to form a hollow portion along the longitudinal direction and joining by welding the side end portions thereof.
  • the hollow portion along the longitudinal direction serves as the fluid flow channel 53.
  • each columnar body Prior to bending the metal sheet, one end of each columnar body is joined by welding or the like in the region that will be the inner surface 57 or the inner surface 59 after the bending is completed. Then, the metal sheet is bent and the side end portions of the metal sheet are joined together. As a result, the metal tube 47 is obtained in which the support members 55 constituted by a plurality of columnar bodies are provided in the internal fluid flow channel 53.
  • each columnar body is joined to the inner surface 57 or the inner surface 59 in the thickness direction of the fluid flow channel 53. Therefore, the columnar bodies can be prevented from displacing when pressurized in the thickness direction by the roller electrodes 71, 73 during resistance welding. As a result, a sufficient pressure can be applied in the thickness direction by the roller electrodes 71, 73 to the metal tube 47 and the multiple-hole metal tubes 45, 49 during resistance welding.
  • a plurality of columnar bodies are provided in the fluid flow channel 53 of the metal tube 47. Therefore, where pressurization is performed in the thickness direction by the roller electrodes 71, 73, the metal tube 47 is slightly deformed in the thickness direction and other ends of some or all of the plurality of columnar bodies abut on the inner surface 57 or the inner surface 59 of the metal tube 47. Such an abutment of other ends of the columnar bodies inhibits deformation of the metal tube 47 in the thickness direction.
  • the columnar bodies can be joined to the inner surface 57 or the inner surface 59 under certain conditions of resistance welding.
  • Fig. 8 is a cross-sectional view illustrating the heat exchanger according to the third embodiment of the present invention. As shown in Fig. 8 , the structure of the support member 55 of the heat exchanger 21 is different from that of the first embodiment. Other components are assigned with same reference numerals as in the first embodiment and the explanation thereof is herein omitted.
  • the support member 55 is a corrugated plate-like body, deformation of the metal tube 47 in the longitudinal direction can be inhibited over a long period. Further, since the rigidity of the support member 55 itself can be increased over that attained when the support member 55 is in the form of the above-described columnar bodies, such a configuration is particularly advantageous when a larger pressurization force is desired to be obtained with the pair of roller electrodes 71, 73. Furthermore, since the corrugated plate-like body acts to disperse the fluid flow, it is possible to regulate the fluid flow and produce a flow with low turbulence.
  • Fig. 9 is a cross-sectional view illustrating the heat exchanger 21 according to the fourth embodiment of the present invention.
  • Figs. 10 to 13 illustrate the metal tube 47 used in the heat exchanger 21.
  • the structure of the support portion of the metal tube 47 of the heat exchanger 21 is different from that of the first embodiment.
  • Other components are assigned with same reference numerals as in the first embodiment and the explanation thereof is herein omitted.
  • the metal tube 47 has, in the fluid flow channel 53 thereof, the support portions 55 that inhibit deformation in the thickness direction.
  • the support portions 55 are constituted by a plurality of first protruding portions 55a arranged along the longitudinal direction of the fluid flow channel 53 at the inner surface 57 on one side in the thickness direction of the fluid flow channel 53 and a plurality of second protruding portions 55b arranged along the longitudinal direction of the fluid flow channel 53 at the inner surface 59 on the other side in the thickness direction of the fluid flow channel 53.
  • Each first protruding portion 55a extends from the inner surface 57 on one side toward the inner surface 59 on the other side
  • each second protruding portion 55b extends from the inner surface 59 on the other side toward the inner surface 57 on one side.
  • first protruding portions 55a and second protruding portions 55b are formed by press forming a metal sheet as described hereinbelow. Therefore, the outer surface 61 on the one side in the thickness direction recedes on the inner surface 59 side, thereby causing the first protruding portions 55a to protrude to the inner surface 59 side in the fluid flow channel 53. The outer surface 63 on the other side in the thickness direction recedes on the inner surface 57 side, thereby causing the second protruding portions 55b to protrude to the inner surface 57 side in the fluid flow channel 53.
  • a first receding portion 55c is formed on the rear surface (outer surface 61) of the first protruding portion 55a, and a second receding portion 55d is formed on the rear surface (outer surface 63) of the second protruding portion 55b.
  • the support portions 55 have the following specific features because the first protruding portions 55a and second protruding portions 55b are arranged in a regular manner.
  • the support portions 55 are arranged regularly so as to form five rows (row A1 to row A5), each row extending in the longitudinal direction.
  • the first protruding portions 55a and second protruding portions 55b are arranged together in the row A1 to row A5.
  • the second protruding portions 55b are disposed at positions facing the first protruding portions 55a in the thickness direction.
  • the second protruding portions 55b are provided at all of the respective positions facing the first protruding portions 55a of the row A3 shown in Fig. 11 .
  • This row A3, from among the five rows, is positioned in the central portion in the width direction of the metal tube 47.
  • the distal end portions of the first protruding portions 55a are disposed at the predetermined distance from the distal end portions of the second protruding portions 55b opposite thereto in the thickness direction, but the protruding portions may be also disposed without the distance t therebetween and the distal end portions thereof may abut on each other.
  • the first protruding portions 55a and second protruding portions 55b are disposed opposite each other in the central portion in the width direction, as mentioned hereinabove, but in the rows positioned at both sides, the first protruding portions 55a are provided at positions displaced in the longitudinal direction with respect to the second protruding portions 55b. Therefore, deformation in the thickness direction of the metal tube 47 in the central portion in the width direction can be effectively inhibited, and narrowing of the fluid flow channel can be inhibited and a smooth fluid flow can be realized at both sides in the width direction.
  • Each first protruding portion 55a protrude from the inner surface on the one side toward the inner surface on the other side, and each second protruding portion 55b protrude from the inner surface on the other side toward the inner surface on the one side.
  • Each first protruding portion 55a and each second protruding portion 55b can be formed, for example, by press forming a metal sheet in the same manner as in the fourth embodiment.
  • each of the first protruding portions 55a and second protruding portions 55b has an elongated shape in the plan view thereof.
  • the longitudinal direction of the first protruding portions 55a and second protruding portions 55b is substantially parallel to the longitudinal direction L of the metal tube 47.
  • all of the plurality of first protruding portions 55a are provided, as shown in Figs. 17C and 17D , at positions that are opposite the second protruding portions 55b in the thickness direction. It is also possible to provided some of the plurality of first protruding portions 55a at positions that are opposite the second protruding portions 55b in the thickness direction and provide the remaining first protruding portions 55a at positions that are not opposite the second protruding portions 55b. In such a configuration, the first protruding portions 55a provided at positions that are not opposite the second protruding portions 55b function as obstacles that create appropriate turbulence in the fluid in the fluid flow channel 53. Where the fluid becomes appropriately turbulent, heat transfer between the fluid and the metal tube 47 is enhanced. Therefore, heat exchange efficiency of the heat exchanger can be increased.
  • the opposing first protruding portions 55a and second protruding portions 55b are disposed along the longitudinal direction. Therefore, such a configuration is particularly advantageous in terms of the effect of ensuring contact surface area of the first protruding portions 55a and second protruding portions 55b when the heat exchanger 21 is bent, for example, spirally as shown in Fig. 2 .
  • the elongation of material in the portion of the metal tube 47 on the radially outer side is large and the elongation of material in the portion on the radially inner side is small, as shown in Fig. 18A . Therefore, relative positions of the first protruding portions 55a and second protruding portions 55b can be easily displaced.
  • the longitudinal direction of the first protruding portions 55a and the longitudinal direction of the second protruding portions 55b are arranged along the longitudinal direction of the metal tube 47.
  • the contact state of the first protruding portions 55a and second protruding portions 55b can be maintained even when the relative positions of the first protruding portions and second protruding portions are somewhat displaced. As a result, bending with a small curvature radius can be performed.
  • Fig. 19 is a plan view illustrating a variation example of the metal tube 47 in the heat exchanger 21 according to the fifth embodiment.
  • the first protruding portions 55a and the second protruding portions 55b have a wedge-like shape.
  • the first protruding portions 55a and the second protruding portions 55b have a substantially triangular shape in a plan view thereof.
  • the first protruding portions 55a and the second protruding portions 55b are disposed so that the apexes of the triangles face the flow direction F of the fluid in a plan view.
  • the fluid flows smoothly along the side surfaces of the first protruding portions 55a and second protruding portions 55b and therefore the occurrence of pressure loss inside the metal tube 47 can be inhibited.
  • Fig. 20 is a perspective view illustrating the heat exchanger 21 according to the sixth embodiment of the present invention.
  • the structure of the metal tube 47 of the heat exchanger 21 according to the sixth embodiment is different from that of the first embodiment.
  • Other components are identical to those of the heat exchanger 21 according to the first embodiment and therefore assigned with same reference numerals as in the first embodiment and the explanation thereof is herein omitted.
  • the metal tube 47 in this heat exchanger 21. is provided with the fluid flow channel 53 and the support portion 55.
  • the fluid flow channel 53 has a first fluid flow channel 53a and a second fluid flow channel 53b extending in the longitudinal direction L and arranged parallel to each other in the width direction W.
  • the support portion 55 is provided in the fluid flow channel 53 constituted by the first fluid flow channel 53a and the second fluid flow channel 53b arranged parallel to each other in the width direction W.
  • the metal tube 47 is obtained by bending a flat metal sheet M and joining the predetermined portions as shown in Fig. 21A .
  • the first fluid flow channel 53a is formed in the following manner. First, the metal sheet M is bent at a bending position B1 extending along the longitudinal direction L and the metal sheet M is bent into a tube so that the end side E1 on one side in the width direction of the metal sheet M comes into contact with a surface S on one side of the mental sheet M. Then, the end side E1 is joined for example by welding to the surface S along the longitudinal direction L, thereby forming the first fluid flow channel 53a.
  • the support portion 55 is constituted by portions of the metal sheet M, that is, by portions extending upward in the height direction (thickness direction of the metal tube 47) from the end side E1 and end side E2.
  • the support portion 55 zones in the vicinity of the end side E1 and end side E2 abut on each other.
  • the support portion 55 branches to both sides in the width direction W from the vicinity of the central portion in the height direction.
  • the branched portions of the support portion 55 extend obliquely from the height direction to the left and to the right.
  • the metal tube 47 according to the sixth embodiment is formed in the above-described manner by using the metal sheet M, the metal tube has a substantially B-like cross-sectional shape.
  • the support portion 55 thus extending along the longitudinal direction L can be formed by a simple manufacturing method. Further, since the support portion 55 of the metal tube 47 extends continuously along the longitudinal direction L, the configuration demonstrates excellent effect of inhibiting deformation in the thickness direction.
  • the plurality of protruding portions 55c are arranged in a row along the longitudinal direction L at the inner surface 57 on one side in the thickness direction of the fluid flow channels 53a, 53b.
  • the plurality of protruding portions 55d are arranged in a row along the longitudinal direction L at the inner surface 59 on the other side in the thickness direction of the fluid flow channels 53a, 53b.
  • the protruding portions 55c extend from the inner surface 57 on one side toward the inner surface 59 on the other side, and the protruding portions 55d extend from the inner surface 59 on the other side toward the inner surface 57 on one side.
  • the support portion 55 can be formed in the fluid flow channel 53 by using the above-described manufacturing method. Therefore, the protruding portions for increasing the heat transfer performance can be provided in the fluid flow channels 53a, 53b by a free design (design focused on the increase in heat transfer performance), as in the variation example illustrated by Figs. 22A and 22B .
  • Fig. 23A is a perspective view illustrating the heat exchanger 21 according to the seventh embodiment of the present invention.
  • the structure of the metal tube 47 of the heat exchanger 21 according to the seventh embodiment is different from that of the first embodiment.
  • Other components are identical to those of the heat exchanger 21 according to the first embodiment and therefore assigned with same reference numerals as in the first embodiment and the explanation thereof is herein omitted.
  • the metal tube 47 in the heat exchanger 21 according to the seventh embodiment is constituted by a first metal tube 47a and a second metal tube 47b arranged parallel to each other in the width direction W.
  • the first metal tube 47a and the second metal tube 47b are cylindrical flat pipes formed separately from each other by an appropriate method, for example, extrusion forming. Therefore, the fluid flow channel 53 of the metal tube 47 is constituted by the first fluid flow channel 53a inside the first metal tube 47a and the second fluid flow channel 53b inside the second metal tube 47b.
  • These first fluid flow channel 53a and second fluid flow channel 53b are partitioned by the support portion 55.
  • the support portion 55 is provided in the fluid flow channel 53 constituted by the first fluid flow channel 53a and the second fluid flow channel 53b arranged parallel to each other in the width direction W.
  • the support portion 55 is constituted by a side wall 55a of the first metal tube 47a and a side wall 55b of the second metal tube 47b.
  • the side wall 55a and the side wall 55b are in surface contact with each other.
  • Protruding portions 55c and protruding portions 55d such as shown in Figs. 22A and 22B may be provided in the fluid flow channels 53a, 53b.
  • the cylindrical flat pipes can be formed in a simple manner by an appropriate method, for example, extrusion forming. Therefore, the production cost can be reduced.
  • the number of flat tubes arranged parallel to each other in the width direction W is not limited to 2 and may be 3, as shown in Fig. 23B , or 4 or more.
  • the metal tube 47 such as shown in Fig. 24B may be also used.
  • This metal tube 47 is obtained by combining two tubular members 47a, 47b with a substantially P-like cross-sectional shape, as shown in Fig. 24A .
  • the tubular members 47a, 47b are formed by bending a metal sheet.
  • the tubular member 47a is formed by folding the metal sheet at a bending position extending along the longitudinal direction and bending the metal sheet to a substantially P-like shape such that the end side on one side in the width direction of the metal sheet is brought into contact with the surface on one side of the metal sheet.
  • the tubular member 47b is formed in a similar manner.
  • the tubular member 47a has the first fluid flow channel 53a
  • the tubular member 47b has the second fluid flow channel 53b.
  • the tubular member 47a and the tubular member 47b have flat portions 48a, 48b extending in the width direction W from cylindrical portions constituting the fluid flow channels 53a, 53b.
  • the first fluid flow channel 53a and the second fluid flow channel 53b are arranged parallel to each other in the width direction W.
  • the flat portion 48a is disposed below the tubular member 47b, and the flat portion 48b is disposed below the tubular member 47a.
  • the side wall of the tubular member 47a functions as the support portion 55a
  • the side wall of the tubular member 47b functions as the support portion 55b.
  • the support portion 55a and the support portion 55b are in surface contact with each other.
  • the entire upper surface and the entire lower surface in the thickness direction are flat. Therefore, the surface area of contact with the multiple-hole metal tubes 45, 47 can be increased. As a result, heat exchange efficiency of the heat exchanger 21 can be increased.
  • the fluid flow channels 53a, 53b of the tubular member 47a and tubular member 47b are less than those shown in Fig. 24B , and the support member 55a and the support member 55b are separated so as to avoid surface contact thereof.
  • a third fluid flow channel 53c is additionally formed between the first fluid flow channel 53a and the second fluid flow channel 53b.
  • the metal tube 47 of this heat exchanger 21 is formed by spirally bending a metal sheet.
  • the metal tube 47 has the support portion 55 and the fluid flow channel 53.
  • the fluid flow channel 53 is constituted by the first fluid flow channel 53a and the second fluid flow channel 53b partitioned in the width direction W by the support portion 55.
  • the support portion 55 is provided in the fluid flow channel 53 constituted by the first fluid flow channel 53a and the second fluid flow channel 53b arranged parallel to each other in the width direction W.
  • the support portion 55 corresponds to a portion obtained by bending the end portion on one side of the metal sheet in the width direction W in a L-like shape with a width substantially of the same order as the thickness of the first fluid flow channel 53a.
  • the metal sheet is bent spirally so that the support portion 55 is positioned close to the center of the metal tube 47 in the width direction W. Because of such spiral bending, a joining surface 50a and a joining surface 50b are in surface contact with each other.
  • the joining surface 50a and the joining surface 50b can be joined by an appropriate method such as the above-described resistance welding, brazing, and soldering.
  • braze layer has been formed on both surfaces (upper and lower surfaces) in the thickness direction of the metal tube 47, not only the joining surfaces 50a, 50b, but also the metal tube 47 and the multiple-hole metal tubes 45, 49 can be joined together at the same time by heating the pre-assembled body in the heating furnace.
  • the entire upper surface and the entire lower surface in the thickness direction of the metal tube 47 can be flat. Therefore, the contact surface area with the multiple-hole metal tubes 45, 47 can be increased. As a result, heat exchange efficiency of the heat exchanger 21 can be improved.
  • the metal tube 47 has a plurality of protruding portions 55c and a plurality of protruding portions 55d in the first fluid flow channel 53a and the second fluid flow channel 53b, respectively.
  • the support portion 55 can be formed, by forming the tube by the above-described manufacturing method. Therefore, the protruding portions for increasing the heat transfer performance can be provided in the fluid flow channels 53a, 53b by a free design (design focused on the increase in heat transfer performance).
  • Figs. 26A and 26B are plan views illustrating the process for manufacturing the metal tube 47 for the heat exchanger 21 according to the ninth embodiment of the present invention.
  • Fig. 26C is a cross-sectional view taken along the XXVIc-XXVIc line in Fig. 26B .
  • the structure of the protruding portion 55 serving as the support portion of the heat exchanger 21 is different from that of the first embodiment.
  • Other components are identical to those of the heat exchanger 21 according to the first embodiment and therefore assigned with same reference numerals as in the first embodiment and the explanation thereof is herein omitted.
  • the metal tube 47 is provided with a plurality of first protruding portions 55a and a plurality of second protruding portions 55b serving as support portions 55.
  • the plurality of first protruding portions 55a are arranged along the longitudinal direction of the fluid flow channel 53 at the inner surface on one side in the thickness direction of the fluid flow channel 53.
  • the plurality of second protruding portions 55b are provided along the longitudinal direction of the fluid flow channel 53 at the inner surface on the other side in the thickness direction of the fluid flow channel 53.
  • Each first protruding portion 55a protrudes from the inner surface on the one side toward the inner surface on the other side, and each second protruding portion 55b protrudes from the inner surface on the other side toward the inner surface on the one side.
  • the first protruding portions 55a and the second protruding portions 55b are formed by press forming a metal sheet in the same manner as in the fourth embodiment.
  • the metal tube 47 according to the ninth embodiment is formed in the following manner.
  • the plurality of protruding portions 55 are formed with a predetermined spacing on almost the entire surface of the metal sheet M.
  • These protruding portions 55 include a plurality of first protruding portions 55a formed in a region on one side (upper side in Fig. 26A ) on a central line B3 positioned as a boundary close to the center of the metal tube M in the width direction W and a plurality of second protruding portions 55b formed in a region on the other side (lower side in Fig. 26A ).
  • the first protruding portions 55a and second protruding portions 55b are formed in the same direction at the same inclination angle.
  • a braze is disposed, for example, between the metal tube 47 and the multiple-hole metal tube 45 and between the metal tube 47 and the multiple-hole metal tube 49, and the components are heated in this state in a heating furnace or the like. As a result, the braze is melted and the metal tube 47 and the multiple-hole metal tubes 45, 49 are joined to each other.
  • the metal tube and multiple-hole metal tubes can be sufficiently pressurized in the thickness direction by the pair of roller electrodes during resistance welding.
  • the joining surface area of the outer surfaces of the metal tube and the opposing surfaces of the multiple-hole metal tubes opposite thereto can be increased and therefore a heat exchanger with excellent heat exchange efficiency can be obtained.
  • the metal tube has a support portion in the fluid flow channel, for example, even when the heat exchanger is bent as shown in the below-described Fig. 2 , the excess deformation of the metal tube can be inhibited. As a result, the fluid flow channel can be prevented from being excessively narrowed or closed.
  • Both ends in the axial direction of at least one of the plurality of columnar bodies may be respectively joined to the inner surface on one side and the inner surface on the other side of the fluid flow channel.
  • the support portion has a plurality of first columnar bodies arranged along the longitudinal direction of the fluid flow channel on an inner surface on one side in the thickness direction of the fluid flow channel and a plurality of second columnar bodies arranged along the longitudinal direction of the fluid flow channel on an inner surface on the other side in the thickness direction of the fluid flow channel; the first columnar bodies extend from the inner surface on the one side toward the inner surface on the other side; and the second columnar bodies extend from the inner surface on the other side toward the inner surface on the one side, and distal end portions thereof abut on or are disposed close to respective distal end portions of the plurality of first columnar bodies.
  • a plurality of first columnar bodies and a plurality of second columnar bodies that have distal portions abutted on each other or disposed close to each other are arranged in the longitudinal direction of the fluid flow channel. Therefore, deformation of the metal tubes in the longitudinal direction can be inhibited over along period. Furthermore, since the columnar bodies are arranged in a spot-like pattern in the longitudinal direction, the increase in resistance to the flow of fluid in the fluid flow channel that is caused by the support portion can be inhibited and the fluid can smoothly flow in the fluid flow channel.
  • At least one of the plurality of first columnar bodies and at least one of the plurality of second columnar bodies may be joined together at the distal end portions thereof.
  • the support portion may be a corrugated plate-like body disposed along the longitudinal direction of the fluid flow channel.
  • the corrugated plate-like body is disposed along the longitudinal direction, deformation of the metal tubes in the longitudinal direction can be inhibited over a long period. Further, the corrugated plate-like body acts to disperse the fluid flow. Therefore, it is possible to regulate the fluid flow and produce a flow with low turbulence. Since the rigidity of the support body itself can be increased over that in the case of the above-described columnar bodies, such a configuration is particularly advantageous when a larger pressurization force is desired to be obtained with the pair of roller electrodes.
  • the support portion may have a plurality of protruding portions arranged along the longitudinal direction of the fluid flow channel, and each of the protruding portions may protrude from an inner surface on either side in the thickness direction of the fluid flow channel toward an inner surface on the other side in the thickness direction.
  • a size of each of the protruding portions in a width direction may be set less than the size thereof in the longitudinal direction.
  • the protruding portions are not limited to the abovementioned columnar bodies and can be formed, for example, by causing the outer surface on one side in the thickness direction to recede toward the other side or the outer surface on the other side in the thickness direction to recede toward the one side.
  • the protruding portions can be formed, for example, by pressing a metal sheet. Therefore, the production is simple and cost can be reduced.
  • the support portion may have a plurality of first protruding portions arranged along the longitudinal direction of the fluid flow channel on an inner surface on one side in the thickness direction of the fluid flow channel, and a plurality of second protruding portions arranged along the longitudinal direction of the fluid flow channel on an inner surface on the other side in the thickness direction of the fluid flow channel, the first protruding portions may protrude from the inner surface on the one side toward the inner surface on the other side, and the second protruding portions may protrude from the inner surface on the other side toward the inner surface on the one side.
  • the plurality of the first protruding portions and the plurality of the second protruding portions are arranged along the longitudinal direction of the fluid flow channel. Therefore, deformation of the metal tube in the longitudinal direction can be inhibited over a long period.
  • the protruding portions can be formed, for example, by pressing a metal sheet. Therefore, the production is simple and cost can be reduced.
  • Some or all of the plurality of first protruding portions are preferably provided at positions opposite the second protruding portions in the thickness direction.
  • first protruding portions and second protruding portions are disposed to cross each other, and there are portions in which the first protruding portions and second protruding portions are in contact with each other and portions adjacent thereto in which the first protruding portions and second protruding portions are not in contact with each other.
  • These contact-free portions function as obstacles that create appropriate turbulence in the fluid in the fluid flow channel. Where the fluid becomes appropriately turbulent, heat transfer between the fluid and the metal tube is enhanced. Therefore, heat exchange efficiency of the heat exchanger can be increased.
  • this configuration is effective when the metal tube is formed by bending a metal sheet (flat sheet) and joining together the end sides of the metal sheet.
  • the first protruding portions and second protruding portions are formed at the metal sheet in advance, before the metal sheet is bent. Even when the opposing positions of the opposing first protruding portions and second protruding portions somewhat shift during bending, where the displacement in various directions takes place within the range in which the crossing state of the first protruding portions and second protruding portions is maintained, the mutual contact surface area assumes an almost same value. As a result, decrease in the deformation inhibition effect in the thickness direction of the metal tube can be suppressed even if the displacement occurs when the metal tube is formed.
  • a longitudinal direction of the first protruding portions be inclined to one side in a width direction of the metal tube with respect to the longitudinal direction of the metal tube; a longitudinal direction of the second protruding portions be inclined to the other side in the width direction with respect to the longitudinal direction of the metal tube; and an inclination angle of the first protruding portions with respect to the longitudinal direction be equal to an inclination angle of the second protruding portions with respect to the longitudinal direction.
  • the first protruding portions and the second protruding portions provided at the metal tube may be formed in the same direction and at the same inclination angle. Therefore, the design and processing are simple. Furthermore, in this configuration, the size component of the first protruding portions 55a or the second protruding portions 55b in the width direction of the metal tube can be reduced by comparison with that in the case in which either of the first protruding portions and second protruding portions are disposed parallel to the width direction of the metal tube. As a result, an excess increase in the resistance encountered by the fluid flowing in the metal tube can be inhibited.
  • the first protruding portions and the second protruding portions may respectively have elongated shapes in a plan view thereof, and a longitudinal direction of the first protruding portions and the second protruding portions, which are facing each other in the thickness direction, may be parallel to the longitudinal direction of the metal tube.
  • the longitudinal direction of the first protruding portions and the second protruding portions is along the longitudinal direction of the metal tube and therefore excellent effect of maintaining the mutual contact state is demonstrated even when the relative positions are displaced in the longitudinal direction by the abovementioned bending. As a result, bending with a small curvature radius is possible.
  • the plurality of first protruding portions be arranged so that three or more rows thereof extending in the longitudinal direction are formed, and in a row positioned in a central portion in the width direction from among these rows, the first protruding portions be provided at positions opposite the second protruding portions in the thickness direction.
  • the row positioned in the central portion in the width direction means the row closest to the center of the metal tube in the width direction. Therefore, when the number of the plurality of rows (the aforementioned three or more rows) extending in the longitudinal direction is an even number, "the row positioned in the central portion in the width direction" can mean two rows.
  • the first protruding portions be provided at positions displaced in the longitudinal direction with respect to the second protruding portions.
  • the first protruding portions and the second protruding portions are disposed opposite each other, whereas in the rows positioned at both sides, the first protruding portions are provided at positions displaced in the longitudinal direction with respect to the second protruding portions. Therefore, deformation of the metal tube in the thickness direction in the central portion in the width direction can be inhibited with good balance, narrowing of the fluid flow channel at both sides in the width direction is inhibited, and a smooth flow of the fluid can be realized.
  • first protruding portions and the second first protruding portions are provided at both sides in the width direction, when an unexpectedly high pressure is applied in the thickness direction, the distal end portions of the first protruding portions or the distal end portions of the second protruding portions abut on an inner surface or an inner surface of the metal tube, thereby making it possible to inhibit subsequent deformation of the metal tube.
  • the plurality of first protruding portions be arranged, as described hereinabove, so that three or more rows thereof extending in the longitudinal direction are formed, and also that the first protruding portions be arranged so that a plurality of rows thereof extending in a inclination direction inclined with respect to the longitudinal direction are formed; the second protruding portions be also arranged so that a plurality of rows thereof extending in the inclination direction are formed; and the rows of the first protruding portions in the inclination direction and the rows of the second protruding portions in the inclination direction be disposed alternately along the longitudinal direction.
  • steps (protruding portions) in the thickness direction can be disposed continuously with an inclination against the longitudinal direction and the steps (first protruding portions) on one side and the steps (second protruding portions) on the other side in the thickness direction can be disposed alternately. Therefore pulsations can be effectively generated in the flow of fluid in the fluid flow channel. As a result, the drift in the fluid flow channel can be inhibited and the development of turbulent flow of the fluid in the fluid flow channel can be enhanced, thereby increasing the efficiency of heat exchange.
  • the fluid flow channel includes a first fluid flow channel and a second fluid flow channel provided parallel to each other in the width direction and extending in the longitudinal direction;
  • the first fluid flow channel is formed by folding a metal sheet at a position along the longitudinal direction and bending the metal sheet into a tubular shape so that one end side in the width direction of the metal sheet abuts on a surface on one side of the metal sheet, and the one end side is joined to the one surface along the longitudinal direction;
  • the second fluid flow channel is formed by folding the metal sheet at another position along the longitudinal direction and bending the metal sheet into a tubular shape so that another end side in the width direction of the metal sheet abuts on the one surface at a position adjacent to the one end side, and the other end side is joined to the one surface along the longitudinal direction;
  • the support portion is constituted by parts of the metal sheet, each part extending from the one end side and the other end side in the thickness direction or a direction inclined from the thickness direction.
  • a metal with a substantially B-like cross section can be obtained by forming a metal sheet in the above-described manner.
  • the support portion extending along the longitudinal direction can be formed and a pair of fluid flow channel can be formed by forming the metal sheet in the above-described manner. Therefore, the metal tube is manufactured in a simple manner. Further, since the support portion of the metal tube extends continuously along the longitudinal direction, an excellent effect of inhibiting deformation in the thickness direction is demonstrated.
  • the multiple-hole metal tube may be a first multiple-hole metal tube and the heat exchanger may further include a second multiple-hole metal tube stacked on the other side of the metal tube in the thickness direction, the second multiple-hole metal tube that has a flat shape with a width greater than a thickness, a plurality of fluid flow channels formed inside thereof along the longitudinal direction, and an opposing surface that is disposed opposite an outer surface on the other side of the metal tube and joined by at least part thereof to the outer surface on the other side.
  • the heat exchanger may be configured by spirally winding so that one end in the longitudinal direction is disposed inside and another end in the longitudinal direction is disposed outside.
  • the heat exchanger is spirally wound, dead space can be reduced and the heat exchanged can be reduced in size. Further, since the support portion is provided in the fluid flow channel of the metal tube, the fluid flow channel can be prevented from decreasing is size or closing due to deformation of the metal tube occurring during bending from a linear shape to the spiral shape and the decrease in heat exchange efficiency can be inhibited.
  • the first protruding portions 55a protrude from one inner surface 57
  • the second protruding portions protrude from the other inner surface 59
  • these first protruding portions 55a and second protruding portions 55b are disposed alternately in the longitudinal direction and thickness direction, instead of being disposed at the mutually opposing positions.
  • the distal end portions of the first protruding portions 55a extend close to the other inner surface 59
  • the distal end portions of the second protruding portions 55b extend close to the one inner surface 57.
  • the heat exchanger in accordance with the present invention may be used for heat exchange between coolants or for heat exchange between the coolant and another fluid.
  • the support member in addition to the case in which the support member is a corrugated plate-like body in the form of an S-like curve, as in the abovementioned embodiments, the support member can be in the form of a corrugated plate-like body composed by angular protrusions and depressions.
  • a three-layer configuration is explained that is obtained by stacking the first multiple-hole metal tube, metal tube, and second multiple-hole metal tube in the order of description, but a two-layer configuration including only one multiple-hole metal tube and the metal tube or a configuration including four or more layers may be also used.
  • each metal tube has a flat shape having a substantially quadrangular cross section
  • another flat shape for example, such that has a cross section with a curved side portion in the width direction, may be also used.

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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)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Details Of Fluid Heaters (AREA)
EP10733496A 2009-01-22 2010-01-20 Wärmetauscher und damit ausgerüstetes wärmepumpen-heisswasserversorgungsgerät Withdrawn EP2390612A1 (de)

Applications Claiming Priority (3)

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JP2009011561 2009-01-22
JP2009074136 2009-03-25
PCT/JP2010/050648 WO2010084889A1 (ja) 2009-01-22 2010-01-20 熱交換器およびこれを備えたヒートポンプ式給湯機

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JP4770989B2 (ja) 2011-09-14
CN102292611A (zh) 2011-12-21

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