EP0859209A1 - Wärmetauscher - Google Patents

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Publication number
EP0859209A1
EP0859209A1 EP97937831A EP97937831A EP0859209A1 EP 0859209 A1 EP0859209 A1 EP 0859209A1 EP 97937831 A EP97937831 A EP 97937831A EP 97937831 A EP97937831 A EP 97937831A EP 0859209 A1 EP0859209 A1 EP 0859209A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
tank
tubes
tube
heat
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Withdrawn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
EP97937831A
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English (en)
French (fr)
Other versions
EP0859209A4 (de
Inventor
Kunihiko Zexel Corp. Kohnan Plant NISHISHITA
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.)
Bosch Corp
Original Assignee
Zexel Corp
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
Priority claimed from JP22913796A external-priority patent/JPH1073388A/ja
Priority claimed from JP26291696A external-priority patent/JPH10111086A/ja
Priority claimed from JP35166596A external-priority patent/JPH10197174A/ja
Application filed by Zexel Corp filed Critical Zexel Corp
Publication of EP0859209A1 publication Critical patent/EP0859209A1/de
Publication of EP0859209A4 publication Critical patent/EP0859209A4/de
Withdrawn legal-status Critical Current

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    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F28D1/0341—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/035—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other with U-flow or serpentine-flow inside the conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0391—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits a single plate being bent to form one or more conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0443—Combination of units extending one beside or one above the other
    • 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
    • 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
    • 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
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • F28F9/0212—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions the partitions being separate elements attached to header boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
    • 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
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • F28F2009/004—Common frame elements for multiple cores
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/0287—Other particular headers or end plates having passages for different heat exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/04—Arrangements of conduits common to different heat exchange sections, the conduits having channels for different circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/02—Arrangements of fins common to different heat exchange sections, the fins being in contact with different heat exchange media

Definitions

  • the invention relates to a heat exchanger formed into one body by combining two heat exchangers having different applications and arranging them horizontally or vertically or by disposing them at upstream and downstream of a flowing direction of air.
  • heat exchangers for automobiles and household electrical appliances include a parallel flow type heat exchanger and a single tank type heat exchanger.
  • the parallel flow type heat exchanger has a plurality of tubes and fins stacked alternately, both ends of the stacked tubes being inserted and bonded in insertion holes formed on tanks disposed vertically or horizontally. And, partition plates for dividing the tanks in a longitudinal direction are disposed at required portions of the tanks to divide them in the longitudinal direction, thereby meandering a heat exchange medium a plurality of times to flow between inlet and outlet joints formed on the tanks.
  • this heat exchanger has a structure that the heat exchange medium supplied through the inlet joint is flown while meandering a plurality of times through the tubes between the tanks to make heat exchange with the outside while flowing through the tubes and discharged from the outlet joint.
  • the single tank type heat exchanger has a structure that tubes having a U-shaped passage are connected to a single tank.
  • Japanese Utility Model Publication No. Hei 6-45157 proposes that a third tank having two tank segments is disposed between right and left tanks, and tubes and fins are disposed between the respective tank segments of the third tank and the right and left tanks, thereby having separate heat exchangers on right and let sides practically.
  • Japanese Utility Model Laid-Open Publication No. Hei 2-54076 proposes a heat exchanger having a first heat exchanger and a second heat exchanger formed into one body which is configured by stacking flat plate fins, connecting to communicate a plurality of tubes with the plate fins, connecting ends of the tubes to an end plate configuring a tank, and assembling a tank plate to the end plate, wherein the end plate and the tank plate are separately formed or the tank plate is separately formed.
  • the two heat exchangers having different functions By forming the two heat exchangers having different functions into one body as described above, the number of components is decreased, the working steps is decreased, and the cost can be reduced. And, when the heat exchangers having different functions are formed into one body, there is an advantage that a heat exchange space can be decreased.
  • the conventional heat exchanger formed of a plurality of heat exchangers which has the partition plate at the midpoint of the pair of tanks to have two heat exchange regions which are divided by the partition plate, has disadvantages that heat is conducted readily because the tank has one body and heat is conducted through the partition plate fitted to the tanks.
  • the heat exchanger described in Japanese Utility Model Publication No. Hei 6-45157 has a hollow portion between the two tank segments of the third tank disposed at the center to prevent the heat conduction. But, since the third tank is disposed between the right and left tanks, there is a disadvantage that the heat exchange space for disposing the tubes is decreased, and the heat exchange efficiency is lowered.
  • the heat exchanger which has heat exchangers with different functions formed into one body, has different heat exchange temperatures and different heat radiation rates owing to the functions of the respective heat exchangers.
  • the radiator performs heat exchange at higher temperatures. Therefore, a heat exchanger having a radiator and a condenser formed into one body has a disadvantage that heat is conducted to the condenser because the radiator has a higher heat exchange temperature, thereby preventing the heat radiation of the condenser and lowering the heat exchange rate of the condenser.
  • forming heat exchangers having different functions into one body has drawbacks that the respective heat exchangers have different optimum temperatures, heat is conducted between the respective heat exchangers through the integrally formed fins, tubes and tanks, and the respective heat exchangers formed into one body can not make heat exchange at the optimum temperature.
  • the heat exchanger having two heat exchangers formed into one body has variable required performance such as a pressure applied to the tube itself and corrosion resistance required for the tube, depending on the functions of the respective heat exchangers.
  • a first heat exchanger is a radiator
  • a second heat exchanger is a condenser
  • the radiator requires a high corrosion resistance on the inner and outer surfaces of the tubes.
  • the condenser is required to have a high-pressure resistance because it condenses a high temperature and high pressure heat exchange medium.
  • the inner surface of the tubes of the condenser does not have a corrosion problem because it is in contact with the flowing heat exchange medium, but the outer surface of the tubes is required to have a high corrosion resistance because it is exposed to high temperature and humid surroundings.
  • tubes are known to be formed of, for example, an improved material of JIS (Japanese Industrial Standard) A 1050 or A 1100 (99.0 wt% of Al) with Cu added by extrusion molding.
  • the fins are also known to be formed of a brazing material, an improved material of JIS A 4343 or JIS A 4045 (Al-Si based) with Zn added and clad with it, and A 3003 (Al-Mn based) with Zn added.
  • the tubes have a good pressure resistance in view of the properties of the extruded material, and when the fins and the tubes are combined, the surface of the tubes has a high potential and the fins are determined as sacrificial anode, so that fins are corroded with priority to prevent the tubes from being corroded.
  • the outer face of the tubes has good corrosion resistance, satisfying the required performance of the condenser as the second heat exchanger.
  • the tubes have poor corrosion resistance on the inner surface and cannot satisfy the required performance of the radiator as the first heat exchanger.
  • the tubes and fins are brazed together integrally, it is necessary to use a brazing sheet clad with a brazing material to form the fins, but since a die used for forming the fins is heavily abraded due to a fin material clad with the brazing material, the maintenance cost is increased, the material cost is increased, and the production cost is increased as a result.
  • the tubes of the first heat exchanger are electric-welded tubes which are formed of a three-layered material consisting of JIS A 3003 (Al-Mn based) as a core material, a brazing material of JIS A 4343 or JIS A 4045 (AL-Si based) clad to a layer forming the outer surface of the tubes, and JIS A 7072 (Al-Zn) material clad to a layer forming the inner surface of the tubes, and the tubes of the second heat exchanger are formed of an improved material of JIS A 1050 or A 1100 (99.0 wt% of Al) with Cu added by extrusion molding.
  • the tubes of the first exchanger have the potential of the core material determined high owing to a difference of electric potential between JIS A 3003 material as the core material of the tube and JIS A 7072 (Al-Zn) material, and the corrosion resistance of the inner surface of the tube is improved owing to a sacrificial anode effect of JIS A 7072 material. And the outer face of the tube given an improved corrosion resistance owing to a sacrificial corrosion resistance of the fins, so that the required performance of the first heat exchanger can be satisfied.
  • the fins may be made of a material not clad with a brazing material, while the tubes may be formed of a material clad with a brazing material.
  • the tubes may be formed of a material which is made of JIS A 3003 (Al-Mn based) material as a core material and clad with a brazing material of JIS A 4343 or JIS A 4045 (Al-Si based) material. Since extrusion processing is poor in this case, the tubes cannot be fabricated by extrusion molding, and therefore an electric-welded tube is required to be formed. But, there is a drawback that the electric-welded tube cannot satisfy a pressure resistance that the second heat exchanger (e.g., a condenser) is required to have.
  • the second heat exchanger e.g., a condenser
  • the present invention aims to provide a heat exchanger having first and second heat exchangers formed into one body, which can be produced at a reduced production cost by forming tubes satisfying the required performance of the respective heat exchangers into one body.
  • a first aspect of the invention relates to a heat exchanger which comprises a pair of tanks and a plurality of tubes and fins disposed between the tanks, wherein the tubes have a sealed section at the midpoint to divide a passage into two to form a passage on one side connected to a tank on one side and other passage on the other side connected to a tank on the other side so that each passage has a U-shape, and the tank on one side and the U-shaped passages on one side of the tubes configure a first heat exchanger having a single tank structure, and the tank on the other side and the U-shaped passages on the other side of the tubes configure a second heat exchanger having a single tank structure.
  • the heat exchanger has a pair of tanks and a plurality of tubes and fins disposed between the tanks.
  • This heat exchanger is a combination of the heat exchangers respectively having substantially a single tank structure, nevertheless the plurality of tubes and fins are alternately stacked and disposed between the pair of tanks.
  • the tubes are integrally formed between the pair of tanks and both ends of the tubes and fins are supported by the pair of tanks to enhance the rigidity of the heat exchanger.
  • even the single tank structure can have the features of the parallel flow type.
  • both the first and second heat exchangers have a single tank structure and have an advantage inherent in the single tank structure that the tanks are decreased to half as compared with the parallel flow type heat exchanger, a space to be used for the tanks can be used for the heat exchange. Therefore, there are advantages that the heat exchange efficiency is improved, the number of components is decreased, and the cost can be reduced.
  • first and second heat exchangers are configured in a connected form, and their rigidity is improved as described above.
  • heat is conducted between them and performance may be degraded.
  • a sealed section is formed at the midpoint of the tubes to prevent the heat exchange medium from flowing between the first and second heat exchangers and to lower the heat conduction between them as low as possible, thereby preventing the performance from being degraded.
  • the tubes are formed of two plates which are joined or a single plate which is folded into halves.
  • the invention is applied when the tube is formed by connecting two plates formed by pressing or rolling, by folding a single plate formed by pressing or rolling into halves, or by folding a single plate into halves while rolling.
  • the tubes are stacked to be integrally formed with tank segments forming the tanks.
  • the heat exchanger configured as described above is a so-called laminate type having the tanks configured with the tubes integrally.
  • the invention can also be applied to the laminate type.
  • the sealed section of the tube has heat-insulating holes.
  • the sealed section enables to connect the passages of the first and second heat exchangers to integrally form the tubes and to lower the heat conduction between them as low as possible. And, the heat insulating effect can be improved further by forming holes on the sealed section.
  • the sealed section of the tube has a heat-insulating cavity.
  • the heat insulating effect can be additionally improved by the cavity.
  • the sealed section of the tube has a folded part
  • the first and second heat exchangers are provided with separate fins
  • the ends of the fins are positioned at the folded part of the sealed section.
  • the separate fins are disposed for the first and second heat exchangers, fins having performance suitable to the respective heat exchangers can be prepared separately, thereby satisfying the required performance of the respective heat exchangers. And, since the sealed section has the folded portion, the ends of the fins can be positioned at the folded portion. As a result, the ends of the fins are prevented from extending from the folded part, and the fins are mounted properly.
  • a single fin is disposed along the first heat exchanger and the second heat exchanger respectively, and has a different number of ridges in the first heat exchanger and the second heat exchanger.
  • the single fin is disposed along the first heat exchanger and the second heat exchanger, it is economical because one type of fin is sufficiently used. And, the fin has different number of ridges for the first heat exchanger and the second heat exchanger (a change of fin pitches) so to comply with the required performance of the respective heat exchangers.
  • the tubes and fins are assembled into one body and brazed in an oven.
  • the tubes and the fins are assembled into one body and brazed in the oven.
  • any of the tank, the tank segments configuring the tank, the end plate configuring the tank is brazed at the same time.
  • the tubes, fins and tanks are assembled into one body and brazed in the oven.
  • the tanks are cylindrical or a split type combined into the tank and brazed together with the tubes and the fins, integrally.
  • the tubes, fins and tank segments stacked to form the tank are assembled into one body and brazed in the oven.
  • the tubes, the fins and the end plate are assembled into one body and brazed in the oven, and a tank plate is joined to the end plate.
  • the tank in this case is formed of the end plate and the tank plate. After brazing the tubes, the fins and the end plate, the tank plate is assembled and connected by caulking with a sealing material.
  • a side plate is disposed between the pair of tanks.
  • the side plate improves the strength of the heat exchanger. And, the side plate is preferably brazed at the same time.
  • a second aspect of the invention relates to a heat exchanger having tubes and fins stacked alternately and the ends of the tubes inserted into tanks, wherein a heat exchanger body formed by stacking the tubes and the fins is divided into a first heat exchanger and a second heat exchanger, and a heat insulation region not having a fin is disposed between the divided first and second heat exchangers.
  • the heat insulation region not having a fin when the heat insulation region not having a fin is disposed between the divided first and second heat exchangers, heat conduction between the adjacent heat exchangers can be prevented by the heat insulation region, and this provides the one-body heat exchanger with the performance of the respective heat exchangers prevented from being degraded. And, since the first and second heat exchangers having two different applications are formed into one body, the heat exchange space can be increased to improve the heat exchange rate, and the number of components is decreased, then the cost can be reduced.
  • the first and second heat exchangers are mutually adjacent vertically or horizontally, and a bonding plate is disposed in the heat insulation region to connect the adjacent first and second heat exchangers.
  • the bonding plate when the bonding plate is disposed in the heat insulation region to connect the adjacent first and second heat exchangers, the heat insulation region is reinforced, and, then the entire heat exchanger is reinforced.
  • the heat insulation region may lower the pressure resistance therefor, and there may be a drawback that the heat exchanger is deformed during production. Therefore, the bonding plate is disposed in the heat insulation region formed between the respective heat exchangers to reinforce the heat exchanger, thereby the above-described drawback can be eliminated.
  • the bonding plate may be disposed by integrally brazing in the oven in addition to the brazing of the tubes and the fins.
  • a partition is disposed in the tanks to divide the first and second heat exchangers.
  • the partition is disposed between the first and second heat exchangers having the common tank to prevent the heat conduction between the respective heat exchangers, and this provides the one-body heat exchanger with the performance of the respective heat exchangers prevented from being lowered.
  • the partition is formed of at least two partition plates, which form a cavity in the tanks.
  • the heat conduction between the first heat exchanger and the second heat exchanger can be prevented by the heat insulation action of the cavity formed in the tank.
  • the cavity has a communication hole to communicate with the outside.
  • the atmosphere air flows through the cavity to improve the heat insulation action of the cavity.
  • the presence of the cavity makes it easy to find the leak by an airtight test, enabling early finding of a defective product.
  • the communication hole may allow the atmosphere air to permeate into the cavity and to accumulate water in the cavity due to environmental changes such as changes of atmospheric pressure and temperatures. Therefore, the communication hole is preferably formed at a lower part of the tank. Thus, water can be discharged from the cavity with ease, and the tank can be prevented from being corroded by water.
  • the first and second heat exchangers are disposed between a pair of tanks, the respective tubes have a sealed section at the midpoint to divide each passage, passages on one side connected to the tank on one side and passages on the other side connected to the tank on the other side are formed to have a U-shape.
  • a first heat exchanger having a single tank structure is formed of the tank on one side and the U-shaped passages on one side of the tubes
  • a second heat exchanger having a single tank structure is formed of the tank on the other side and the U-shaped passages on the other side of the tubes
  • the heat insulation region is formed on the sealed section for dividing the respective tubes.
  • the heat conduction between the heat exchangers each having the single tank structure and formed into the one-body heat exchanger can be decreased as low as possible by the sealed section and can be prevented by the heat insulation region, so that the performance of the respective heat exchangers can be prevented from being degraded.
  • the first and second heat exchangers each having a single tank structure into one body, the heat exchange space is enlarged to improve the heat exchange rate. And, the number of components is decreased, and the cost can be reduced.
  • the first and second heat exchangers each have a single tank structure and are disposed adjacent to each other horizontally or vertically, and the tubes are integrally formed with the tank segments configuring the tank.
  • the heat exchanger configured as described above is a so-called laminate type having the tank segments integrally formed with the tubes. And, the invention can also be applied to the laminate type heat exchanger.
  • the heat exchanger has the plurality of heat exchangers having substantially different applications formed into one body, wherein the heat insulation region not having a fin is formed between the respective heat exchangers to prevent the heat conduction between the heat exchangers.
  • the heat exchanger having an improved heat exchange rate can be obtained.
  • a third aspect of the invention relates to a heat exchanger which comprises tubes configuring a first heat exchanger and tubes configuring a second heat exchanger which are disposed downstream and upstream of a flowing direction of air, fins disposed between the tubes, ends of the tubes inserted into respective tanks to form the first and second heat exchangers, and the first and second heat exchangers brazed into one body, wherein the tubes are formed by folding a single plate or joining two plates made of an aluminum material or aluminum alloy with both sides clad, each tube has a sealed section to divide its passage into two in a longitudinal direction of the tube so to form the first heat exchanger by the passages on one side and the second heat exchanger by the passages on the other side, and the fins disposed between the tubes are made of an aluminum material or aluminum alloy not clad.
  • the core material has a high electric potential owing to a difference of electric potential between the core material and the brazing material having both sides clad, and the outer and inner surfaces of the tubes can have an improved corrosion resistance owing to a sacrificial anode effect of the brazing material.
  • the first heat exchanger when the first heat exchanger is required to have a corrosion resistance on the inner and outer surfaces of the tubes, and the second heat exchanger is not highly required to have a corrosion resistance on the inner surface of the tubes, but, it is required to have a corrosion resistance and a pressure resistance on the outer surface of the tubes, these heat exchangers having substantially different applications are formed into one body.
  • the tubes satisfying the required performance for the respective heat exchangers can be formed integrally.
  • the sealed section is formed in the tubes, the heat conduction between the respective heat exchangers can be decreased as low as possible by the sealed section, the heat conduction between the respective heat exchangers can be prevented, and the heat exchange rate can be improved.
  • the fins can be made of an aluminum material or aluminum alloy not clad with a brazing material, so that the abrasion of the die caused when the fins are made of a material clad with the brazing material can be decreased, the maintenance cost can be reduced, and the material cost can also be reduced, so that the production cost can be reduced.
  • a tube material for the tubes is a three-layered material formed of an aluminum material or aluminum alloy as a core material, and a layer forming the inner face of the tube and a layer forming the outer face of the tube clad with an Al-Si based brazing material, or a four-layered material formed of an aluminum material or aluminum alloy as a core material, an intermediate layer clad with an aluminum material or aluminum alloy having a potential lower than that of the core material, and a layer forming the inner face of the tube and a layer forming the outer face of the tube clad with an Al-Si based brazing material.
  • the corrosion resistance of the inner surface of the tubes is improved by a sacrificial corrosion resistance uniform on the surface of the intermediate layer.
  • the tubes are formed of an aluminum material or aluminum alloy of the three- or four-layered material with both surfaces clad, the pressure resistance of the tubes is improved.
  • the tubes have a plurality of projections formed in the passage on one side or the passages on both sides to protrude inwardly, tips of the projections are mutually contacted or contacted with the flat face.
  • the tips of the projections are mutually contacted or the tips of the projections are contacted with the flat surface of the plate to divide the passage into a multiple number, and the heat exchange medium flowing through the passages is made turbulent to improve the heat exchange rate.
  • the pressure resistance of the tubes can be improved, so that the projections are formed on either or both of the passages as required to make it possible to satisfy the required performance of the respective heat exchangers.
  • the projections are easily contacted and can be formed as required.
  • the tubes are formed of a single plate which is folded into halves, ends of the plate forming the tubes are overlaid and brazed on a bead portion, a flat portion, the end portion or the passage portion of the tubes.
  • the tube when the tube is formed by bonding ends of a single plate to have the plate ends protruded outwardly of the tube ends, the tube may have different shapes of cross sections at both sides, and, therefore, it is necessary to form the tube insertion holes of header tanks to match the shapes of the cross sections of the tube, requiring a dedicated jig or the like. Therefore, there are disadvantages that the production cost becomes high, and the production process becomes complicated.
  • the tube can have the same shape of cross section at both sides, its assemblability can be improved, the manufacturing fixtures and equipment can be decreased and the manufacturing process can be simplified.
  • the respective tubes have passages on one side connected to the tank on one side and passages on the other side connected to the tank on the other side formed to have a U-shape
  • the first heat exchanger having the single tank structure is formed of the tank on one side and the U-shaped passages on one side of the tubes
  • the second heat exchanger having the single tank structure is formed of the tank on the other side and the U-shaped passages on the other side of the tubes.
  • the invention is also used for a heat exchanger having the tubes in which U-shaped passages are formed.
  • the heat exchanger having this configuration is a single tank type which is formed by connecting the U-shaped passages and the tube ends on the other side to the tank. And the invention can also be applied to this tank single type heat exchanger.
  • Such a single tank type heat exchanger has advantages that the tank is half of the parallel flow type heat exchanger, an area to contact with air is increased to improve the heat exchange rate, the number of components is decreased, and the cost can be reduced.
  • the tubes have heat insulation holes formed on the sealed section for dividing the passage.
  • the heat conduction between the first and second heat exchangers can be decreased as low as possible by virtue of the sealed section, and by forming the heat insulation holes on the sealed section, the heat conduction can be further prevented. Therefore, there is an advantage that the respective heat exchangers have an improved heat exchange rate.
  • the tubes and the fins are assembled into one body and brazed in the oven.
  • the invention can be applied to a heat exchanger configured by assembling tubes and fins into one body and brazing them in the oven.
  • the tubes and fins are assembled into one body and brazed in the oven.
  • any of the tank, the tank segments configuring the tank and the end plate configuring the tank is brazed at the same time.
  • the tubes, the fins and the tanks are assembled into one body and brazed in the oven.
  • the invention can also be applied to the heat exchanger configured by assembling the tubes, the fins and the tank into one body and brazing them in the oven.
  • the tank is cylindrical or a combination of two pieces formed into a tank body, and brazed with the tubes and the fins into one body.
  • the tubes, the fins and the tank segments stacked to form the tanks are assembled into one body and brazed in the oven.
  • the invention can also be applied to the heat exchanger configured by assembling the tubes, the fins and the tank segments stacked to form the tanks into one body and brazed in the oven.
  • the above-described laminate type heat exchanger having the tank segments integrally formed with the tubes is brazed into one body.
  • the tubes, the fins and an end plate are brazed in the oven and connected to the tanks.
  • the invention can also be applied to the heat exchanger configured by brazing the tubes, the fins and the end plate in the oven and connecting to the tanks.
  • the tubes, the fins and the end plate are brazed in the oven, and connected to the tanks by caulking or the like using a sealing material. This is employed when a pressure resistance required for the heat exchanger is not so high.
  • the heat exchanger has the heat exchangers having substantially different applications formed into one body, wherein the tubes satisfying the required performance different for the respective heat exchangers can be formed into one body.
  • the invention provides the heat exchanger, which has the heat exchangers with different applications configured into one body, with an improved durability, and, at the same time, the maintenance cost of the production equipment is reduced, and the material cost is reduced, thereby the production cost can be reduced.
  • Fig. 1 is a front view of the heat exchanger according to an embodiment of a first aspect of the invention.
  • Fig. 2 is a transverse sectional view of a tube and tanks for the heat exchanger according to an embodiment of the first aspect of the invention.
  • Fig. 3 is a front view of a sealed section of the tube shown in Fig. 2.
  • Fig. 4 is a transverse sectional view of a tube and tanks for the heat exchanger according to another embodiment of the first aspect of the invention.
  • Fig. 5 is a front view of a sealed section of the tube shown in Fig. 4.
  • Fig. 6 is a sectional view of passages of a first heat exchanger.
  • Fig. 7 is a sectional view of passages of a second heat exchanger.
  • Fig. 8 is a transverse sectional view of a tube and tanks for the heat exchanger according to another embodiment of the first aspect of the invention.
  • Fig. 9 is a front view of a sealed section of the tube shown in Fig. 8.
  • Fig. 10 is a transverse sectional view of a tube and tanks for the heat exchanger according to another embodiment of the first aspect of the invention.
  • Fig. 11 is a front view of a sealed section of tubes shown in Fig. 10.
  • Fig. 12 is a diagram showing a plate for forming a tube used for a heat exchanger according to another embodiment of the first aspect of the invention.
  • Fig. 13 is a sectional view of passages of the first heat exchanger where the tube is formed by folding the plate shown in Fig. 12 into halves.
  • Fig. 14 is a sectional view of passages of the second heat exchanger where the tube is formed by folding the plate shown in Fig. 12 into halves.
  • Fig. 15 is a front view of a heat exchanger according to another embodiment of the first aspect of the invention.
  • Fig. 16 is a plan view of the heat exchanger shown in Fig. 15.
  • Fig. 17 is a plan view of a tube of the heat exchanger shown in Fig. 15.
  • Fig. 18 is a front view of a heat exchanger having the first and second heat exchangers arranged in a vertical direction according to another embodiment of the first aspect of the invention.
  • Fig. 19 is a vertical sectional view of a tube and tanks of the heat exchanger shown in Fig. 18.
  • Fig. 20 is a perspective view of a heat exchanger having the first and second heat exchangers arranged in a vertical direction according to another embodiment of the first aspect of the invention.
  • Fig. 21 is a perspective view showing a tank section of a heat exchanger having the first and second heat exchangers arranged in a vertical direction according to another embodiment of the first aspect of the invention.
  • Fig. 22 is a vertical sectional view of a tube of the heat exchanger shown in Fig. 21.
  • Fig. 23 is a front view of the heat exchanger according to an embodiment of a second aspect of the invention.
  • Fig. 24 is a perspective view of a joining plate.
  • Fig. 25 is a perspective view of a joining plate.
  • Fig. 26 is a perspective view of a joining plate.
  • Fig. 27 is a perspective view of a joining plate.
  • Fig. 28 is a perspective view of a joining plate.
  • Fig. 29 is a perspective view of a joining plate.
  • Fig. 30 is a perspective view of a joining plate.
  • Fig. 31 is a perspective view of a joining plate.
  • Fig. 32 is a sectional view taken along line X-X of section C of the heat exchanger of Fig. 23.
  • Fig. 33 is an enlarged perspective view of section C of the heat exchanger shown in Fig. 23.
  • Fig. 34 is a front view of the heat exchanger according to another embodiment of the second aspect of the invention.
  • Fig. 35 is a front view of the heat exchanger according to another embodiment of the second aspect of the invention.
  • Fig. 36 is a transverse sectional view of a tube and tanks shown in Fig. 35.
  • Fig. 37 is a perspective view of the heat exchanger according to another embodiment of the second aspect of the invention.
  • Fig. 38 is a sectional view taken along line Y-Y of Fig. 37 to show a part of the heat exchanger.
  • Fig. 39 is a perspective view of the heat exchanger according to an embodiment of a third aspect of the invention.
  • Fig. 40 is a transverse sectional view of the heat exchanger according to an embodiment of the third aspect of the invention.
  • Fig. 41 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 42 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 43 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 44 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 45 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 46 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 47 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 48 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 49 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 50 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 51 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 52 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 53 is a perspective view of an end face portion of a tube according to an embodiment of the third aspect of the invention.
  • Fig. 54 is a perspective view of the heat exchanger according to another embodiment of the third aspect of the invention.
  • Fig. 55 is a transverse sectional view of a tube and tanks of the heat exchanger shown in Fig. 54.
  • Fig. 56 is a perspective view of the heat exchanger according to another embodiment of the third aspect of the invention.
  • Fig. 57 is a perspective view of the heat exchanger according to another embodiment of the third aspect of the invention.
  • Fig. 1 is a front view of the heat exchanger of this embodiment and Fig. 2 is a transverse sectional view of a tube and tanks for this heat exchanger.
  • This heat exchanger designated by numeral 1 is a heat exchanger having a plurality of tubes 4, 4 and fins 3a, 3a disposed between a pair of tanks 2, 2, the respective tubes 4, 4 have a sealed section 5 to divide a passage into two, and one passage 6 connected to the tank 2 on one side and the other passage 7 connected to the tank 2 on the other side, and each formed to have a U-shape.
  • numerals 60 and 70 denote a ridge, and these ridges 60, 70 are bonded to the plate face, or the ridges 60, 60 or the ridges 70, 70 are mutually bonded, and the passages 6, 7 are respectively formed into the U-shape.
  • Reference numeral 7a denotes beads, and these beads 7a are bonded to the plate face, or the beads 7a, 7a are mutually bonded to improve a pressure resistance and to cause turbulence in the flow of a heat exchange medium, thereby to improve a heat exchange rate.
  • Fig. 3 is a front view of the sealed section 5.
  • a first heat exchanger A having a single tank structure is formed of the tank 2 on one side and the passage 6 having the U-shape on one side
  • a second heat exchanger B having a single tank structure is formed of the tank 2 on the other side and the passage 7 having the U-shape on the other side of the tube.
  • the first heat exchanger A is a radiator
  • the second heat exchanger B is a condenser
  • the first and second heat exchangers A, B are horizontally arranged to form the heat exchanger 1.
  • Both ends of the respective tubes 4, 4 are inserted into connected with tube insertion holes (not shown) of the tanks 2, 2, on both sides.
  • side plate connection holes (not shown) are formed at upper and lower ends of the tanks 2, 2, and both ends of side plates 3b having a square C-shaped cross section are inserted into these side plate connection holes.
  • the respective tanks 2, 2 have partition plates 2a, 2a integrally formed in a longitudinal direction to divide the interior into inlet sides 20A, 20B and outlet sides 21A, 21B.
  • Inlet joints 8A, 8B for the heat exchange medium are connected to the inlet sides 20A, 20B, and outlet joints 9A, 9B are connected to the outlet sides 21A, 21B, respectively.
  • the tube 4 is formed by joining two plates which are formed by pressing or rolling, or by folding a single plate formed by pressing or rolling into halves, or by folding a single plate into halves while forming it by rolling. And, the tube is made of a three-layered material of a two-sided clad or a four-layered material having an intermediate layer in a two-sided clad.
  • the heat exchange medium flows through the passages 6, 6 having the U-shape in the respective tubes 4 to undergo heat exchange between the inlet joint 8A and the outlet joint 9A of the first heat exchanger A.
  • the heat exchange medium flows through the passages 7, 7 having the U-shape in the respective tubes 4 to undergo heat exchange between the inlet joint 8B and the outlet joint 9B of the second heat exchanger B.
  • the heat exchanger 1 configured as described above, even though it is substantially formed by assembling heat exchangers each having a single tank structure (the first and second heat exchangers A, B), alternately stacked multiple tubes 4, 4 and fins 3a, 3a are mounted between the pair of tanks 2, 2, the tubes 4 are integrally formed between the pair of tanks 2, 2, and both ends of the tubes 4, 4 and the fins 3a, 3a are supported by the pair of tanks 2, 2, so that rigidity of the heat exchanger can be increased.
  • the heat exchanger 1 has an advantage of a parallel flow type heat exchanger even if it has a single tank structure. And, since this embodiment uses the side plates 3b, strength of the heat exchanger 1 is further enhanced.
  • the first and second heat exchangers A, B respectively have the single tank structure (the heat exchanger A has the tank 2 and the heat exchanger B has the tank 2), there is an advantage inherent to the single tank structure, namely the tank is halved as compared with a parallel flow type heat exchanger, and the saved space can be used for the heat exchange.
  • the heat exchange efficiency can be improved, the number of parts can be decreased and the cost can be reduced.
  • first and second heat exchangers A, B are connected to form the heat exchanger 1, rigidity is improved as described above, and since the sealed section 5 is formed at the midpoint of the tube 4, the flow of heat exchange medium is stopped there, and heat conduction between the two heat exchangers A, B can be minimized by virtue of the sealed section 5, and lowering of the performance can be prevented.
  • the sealed section 5 also connects passages of both the first and second heat exchangers A, B to enable the integral formation of the tubes 4.
  • the sealed section 5 of the tube 4 has pores 5a, 5a for heat insulation.
  • a heat insulation effect can be improved further by the pores 5a, 5a of the sealed section 5.
  • two plates 4a, 4b are joined to form the tube 4, and pores 5a are formed larger than those of the above described embodiment. And, the plates 4a, 4b are formed by pressing or rolling.
  • Fig. 6 is a sectional view of a passage 6 of the first heat exchanger A
  • Fig. 7 is a sectional view of a passage 7 of the second heat exchanger B, in which ridges 60, 70 are bonded to the plate face to form each passage 6, 7 in a U-shape.
  • the passage 7 has an improved pressure resistance by bonding beads 7a to the plate face and an improved heat exchange efficiency by causing turbulence in the flow of the heat exchange medium.
  • Fig. 8 and Fig. 9 show another embodiment of the tube 4, in which the sealed section 5 of the tube 4 has a cavity 5b for heat insulation. Accordingly, the heat insulation effect can be improved by the cavity 5b in the same way as in the above-described embodiment.
  • Fig. 10 and Fig. 11 show another embodiment of the tube 4, which has folded portions 5c, 5c on the sealed section 5 of the tube 4. Further, the first heat exchanger A and the second heat exchanger B are provided with separate fins 3a with their ends positioned at the folded portions 5c, 5c on the sealed section 5.
  • the respective heat exchangers A, B can be provided with the fins having performance suitable for each of them.
  • the performance required for the respective heat exchangers A, B can be satisfied.
  • the sealed section 5 is provided with the folded portions 5c, 5c, the ends of the respective fins 3a are positioned at the folded parts 5c, 5c. As a result, the fin ends are prevented from extending from the folded portions 5c, 5c, and the fins are held appropriately.
  • the first and second heat exchangers A, B may be provided with a single fin, though not illustrated. And, the fin may have a different number of ridges in the first and second heat exchangers A, B. Thus, when only one fin is disposed in the first and second heat exchangers A, B, it is economical because only one type of fin is used. And, the number of peaks of the fin can be changed for the first and second heat exchangers thereby the fin pitches can be varied so to suit the required performance of each heat exchanger.
  • Fig. 12 through Fig. 14 show an embodiment that a single plate 4c is folded into halves to form the tube 4.
  • the tube 4 is formed by further folding the single plate 4c formed by pressing or rolling into halves or by folding the single plate 4c into halves while rolling.
  • Fig. 15 through Fig. 17 show an embodiment that tank segments 2b, 2b stacked to form tanks 2, 2 are of a laminate type integrally formed with the tubes 4.
  • the heat exchanger 1 is a heat exchanger having a plurality of tubes 4, 4 and fins 3a, 3a between a pair of tanks 2, 2.
  • the respective tubes 4, 4 have a sealed section 5 at their midpoints to divide passages into two.
  • a passage 6 on one side connected to one tank 2 and a passage 7 on the other side connected to the other tank 2 are pressed to have a U-shape, respectively.
  • the tank 2 on one side and the passage 6 having the U-shape on one side of the tube 4 form the first heat exchanger A having a single tank structure.
  • the tank 2 on the other side and the passage 7 having the U-shape on the other side of the tube 4 form the second heat exchanger B having a single tank structure.
  • the fins 3a are separately disposed in the first and second heat exchangers A, B. Accordingly, the fins having performance suitable for the respective heat exchangers can be provided, thereby satisfying the required performance of the respective heat exchangers.
  • a single fin may be formed for the first and second heat exchangers A, B. And, the fin may have a different number of ridges for the first and second heat exchangers A, B so as to meet the required performance of the respective heat exchangers.
  • Fig. 18 and Fig. 19 show an embodiment that the first and second heat exchangers A, B are vertically assembled to form the heat exchanger 1.
  • This heat exchanger 1 is a heat exchanger having a plurality of tubes 4, 4 and fins 3a, 3a disposed between the vertically disposed pair of tanks 2, 2.
  • the respective tubes 4, 4 have the sealed section 5 at their midpoints to divide passages into two, and a passage 6 on one side connected to one tank 2 and a passage 7 on the other side connected to the other tank 2 are formed to have a U-shape, respectively.
  • the heat exchanger 1 is configured by integrally assembling the tubes 4, 4, and the fins 3a, 3a and brazing them in an oven.
  • the heat exchanger 1 shown in each of Fig. 1, Fig. 15 and Fig. 18 is basically produced by integrally assembling the tubes 4, 4 and the fins 3a, 3a and brazing them in the oven, and in addition to the brazing of the tubes and the fins, the tanks 2, 2 (the heat exchangers shown in Fig. 1 and Fig. 18) and the tank segments 2b, 2b configuring the tanks 2, 2 (the heat exchanger shown in Fig. 15) are brazed at the same time to form the heat exchanger.
  • the heat exchanger shown in each of Fig. 20 through Fig. 22 is of a so-called post-attaching tank and caulking type and a separate tank type.
  • the heat exchanger 1 is produced by assembling the first and second heat exchangers A, B vertically, and having a plurality of tubes 4, 4 and fins 3a, 3a disposed between a pair of tanks disposed vertically.
  • the respective tubes 4, 4 have the sealed section at the midpoint to divide the passage into two in the same way as in the above-described embodiment, the passage on one side connected to the tank on one side and the passage on the other side connected to the tank on the other side are formed into a U-shape, respectively.
  • This heat exchanger 1 has the tubes 4, 4, the fins 3a, 3a and an end plate 2c integrally assembled and brazed in the oven, then a tank plate 2d is fixed to the end plate 2c to form the first heat exchanger A.
  • the tank 2 is formed of the end plate 2c and the tank plate 2d by brazing the tubes 4, 4, the fins 3a, 3a and the end plate 2c, assembling the tank plate 2d, and caulking them by a sealing material (not shown).
  • the heat exchanger may be configured to bond components by caulking with a sealing material in the same way as the tank 2 of Fig. 20.
  • Fig. 21 and Fig. 22 show an embodiment of the heat exchanger 1, which is formed by assembling the first and second heat exchangers, A, B vertically.
  • This heat exchanger 1 has a plurality of tubes 4, 4 and fins 3a, 3a disposed between a pair of tanks disposed vertically.
  • the respective tubes 4, 4 have the sealed section 5 at the midpoint to divide the passage into two in the same way as in the above-described embodiment, the passage on one side connected to the tank on one side and the passage on the other side connected to the tank on the other side are formed to have a U-shape, respectively.
  • This heat exchanger 1 has the tank 2 formed of the end plate 2c and the tank plate 2d in the first heat exchanger A, and the tubes 4, 4, the fins 3a, 3a, the end plate 2c and the tank plate 2d are integrally brazed in the oven.
  • the heat exchanger of this embodiment is basically formed by integrally assembling the tubes and the fins and brazing them in the oven.
  • any of the tank, the tank segments forming the tank and the end plates configuring the tank can be brazed at the same time.
  • the tank is cylindrical or made by integrally assembling two parts and can be brazed integrally with the tubes and the fins.
  • the tubes, the fins and the tank segments which are stacked to form the tank are integrally assembled, namely a laminate type having the tank segments integrally formed with the tubes can be brazed in the oven.
  • it can be configured by a procedure that the tubes, the fins and the end plate are integrally assembled and brazed in the oven, then the tank plate is fixed to the end plate.
  • heat exchanger In the above-described embodiments, two heat exchangers were assembled horizontally or vertically, but a third heat exchanger can be fitted to either or both of the top and bottom sides of the heat exchanger formed by assembling two heat exchangers horizontally, or a third heat exchanger can be fitted to either or both of the right and left sides of the heat exchanger formed by assembling two heat exchangers vertically.
  • the heat exchanger may be formed by assembling as required.
  • Fig. 23 is a front view of the heat exchanger of an embodiment of the second aspect of this invention.
  • This heat exchanger 1 has a plurality of tubes 4A, 4A and fins 3a, 3a configuring a first heat exchanger A and a plurality of tubes 4B, 4B and fins 3a, 3a configuring a second heat exchanger B stacked alternately in parallel to each other between a pair of tanks 2, 2, and both ends of the stacked tubes are inserted into and connect with tube insertion holes formed in the tanks 2.
  • the heat exchanger 1 has the pair of tanks 2, 2 erected on both sides of the tubes, both ends of the tubes 4A, 4A configuring the first heat exchanger A are connected to the upper half of the tanks 2, and both ends of the tubes 4B, 4B configuring the second heat exchanger B are connected to the lower half of the tanks 2 so as to connect the first and second heat exchangers A, B in parallel in a vertical direction.
  • the first heat exchanger A is a radiator
  • the second heat exchanger B is a condenser, which are integrally formed into a heat exchanger.
  • top and bottom openings of the tanks 2 are sealed by caps 3c.
  • the tanks 2 of this embodiment are formed of a flat sheet material, which is formed into a circular pipe.
  • a heat exchange medium is meandered a plurality of times to flow between the inlet joints 8A, 8B and the outlet joints 9A, 9B. More specifically, the heat exchange medium supplied through the inlet joints 8A, 8B of the heat exchanger 1 is flown to meander a plurality of times from both tanks 2, 2 through the tubes 4A, 4B, which configure the first heat exchanger A and the second heat exchanger B, to perform heat exchange with outside while passing through the tubes 4A, 4B, and discharged from the outlet joints 9A, 9B.
  • the tubes 4A, 4B are formed by extrusion molding, by combining two plates formed by pressing or rolling, by folding to half a single plate formed by pressing or rolling, or by folding a single plate into halves while being formed by rolling. And, the tube is made of an extruded material, a three-layered material of a two-sided clad with the brazing material, or a four-layered material having an intermediate layer in a two-sided clad with the brazing material.
  • the heat exchanger 1 has an heat insulation region 11 having no fin 3a between the tubes 4A configuring the first heat exchanger A and the tubes 4B configuring the second heat exchanger B.
  • the heat exchange space is enlarged to improve a heat exchange rate, the number of components is decreased, and the cost can be reduced.
  • the heat insulation region 11 formed between the vertically adjacent tubes 4A and tubes 4B has a bonding plate 12 having a length substantially equal to those of the tubes 4A, 4B.
  • the tubes 4A, 4B, the fins 3a, 3a and the bonding plate 12 are integrally brazed in the oven.
  • the heat exchanger 1 includes the heat insulation region 11, the pressure resistance of the heat exchanger may be lowered in the heat insulation region 11 and the heat exchanger 1 may be deformed during production.
  • disposing of the bonding plate 12 in the heat insulation region 11 can eliminate the above-described disadvantages and reinforce the heat exchanger 1.
  • the bonding plate 12 is formed of a flat bonding plate material, which is bent into a rectangular or corrugated shape.
  • the bonding plate is made of a three-layered material of a two-sided clad with the brazing material or a bare material and integrally formed together with the tubes and the fins by brazing in the oven.
  • the bonding plate can have an improved pressure resistance, and an area of heat conduction can be decreased to prevent the heat conduction between the two heat exchangers.
  • Fig. 24 through Fig. 31 show embodiments of the bonding plates each formed by bending the bonding plate into a rectangular or corrugated shape.
  • a direction of long sides of the flat bonding plate material is determined as a longitudinal direction
  • a direction of short sides is determined as a perpendicular direction
  • the long sides are expressed as long ends
  • the short sides are simply expressed as ends.
  • both ends of the bonding plate are bent two times in a vertical direction to form end joints 12a having a square side shape with its part opened, and the middle flat portion is bent in a vertical direction to form projections and depressions at an equal interval, thereby forming a bonding plate 12 (1) having a plurality of projections 12b and a plurality of depressions 12c.
  • the bonding plate 12 (1) has its pressure resistance at both ends improved by the end joints 12a and also the pressure resistance in the middle improved by the plurality of projections 12b and depressions 12c.
  • the bonding plate 12 (1) is formed to have the projections and depressions, the flat faces of the end joints 12a and the flat faces of the projections 12b are in contact with the tube 4A, and the flat faces on the other side of the end joints 12a and the flat faces of the depressions 12c of the bonding plate 12 (1) are in contact with the tube 4B, so that a heat conducting area between the bonding plate 12 (1) and the tubes 4A, 4B is decreased, and the heat conduction between the first heat exchanger and the second heat exchanger can be decreased.
  • Fig. 25 shows an embodiment which uses a bonding plate having a length substantially a half, upon bending, of the length of the tube 4 in a longitudinal direction, its both ends are bent in a vertical direction two times to form a bonding plate 12 (2) having a rectangular joint 12d at both ends.
  • Two bonding plates 12 (2) are disposed in the heat insulation region 11 to reinforce the heat insulation region 11.
  • a bonding plate 12 (3) shown in Fig. 26 is formed by bending both ends of the bonding plate in a vertical direction into a rectangular shape to form a bonding joint 12e having an L-shape inward of the bonding plate 12 (3) at both ends, entering two L-shaped cuts from both long ends at a given interval on the middle flat face, bending four portions formed by cutting in a vertical direction two times to form four L-shaped projections 12f having a height substantially equal to that of the projection 12e.
  • Fig. 27 shows a bonding plate 12 (4) having a corrugated shape formed by sequentially bending the bonding plate in a vertical direction.
  • Fig. 28 shows a bonding plate 12 (5) having bonding joints 12g formed by bending both long ends of the bonding plate in a longitudinal direction into a rectangular shape.
  • Fig. 29 shows a bonding plate 12 (6) configured to have a plurality of holes 12h on the flat face of the bonding plate 12 (5).
  • Fig. 30 shows a bonding plate 12 (7) formed by bending both long ends of the bonding plate in a longitudinal direction into a rectangular shape and bending its flat portion in a longitudinal direction to make a depression 12i.
  • Fig. 31 shows a bonding plate 12 (8) formed by bending the bonding plate in a longitudinal direction into a corrugated shape.
  • the bonding plate 12 shown in each of the above-described embodiments is formed by bending the bonding plate to improve reinforcement of the heat exchanger for the pressure resistance or the like and also serves to decrease the area of heat conduction between the tubes 4A configuring the first heat exchanger A and the tubes 4B configuring the second heat exchanger B to prevent the heat conduction between them.
  • bending is preferably made at a predetermined interval because excessively fine bending provides the same effects as the fins.
  • Fig. 32 is a partially sectional view (part C in Fig. 23) of the heat exchanger 1.
  • Fig. 33 is a perspective view showing a part (part C in Fig. 23) of the tank 2 and the partition plate 10 configuring the heat exchanger 1.
  • An arrow mark in the Figure denotes a direction of gravitation.
  • the heat insulation region 11 is formed between the tube 4A and the tube 4B, and two slits 13, 13 having a predetermined shape are formed in the tank 2 which is on an extension of the heat insulation region 11, namely between the tube 4A and the tube 4B.
  • the partition plate 10 is formed to have a large diameter portion 10a corresponding to the outer periphery of the tank 2, a small diameter portion 10b corresponding to the inner periphery of the tank 2, and shoulders 10c formed between the large diameter portion 10a and the small diameter portion 10b.
  • formation of the cavity 14 in the tank 2 located between the first heat exchanger A and the second heat exchanger B can prevent the heat conduction between the heat exchangers A, B by virtue of the heat sealing region 11, and, the heat exchangers A, B having a different application can be formed into one body to have a common tank without degrading the performance of the first heat exchanger A and the second heat exchanger B.
  • a bypass leak can be checked from the communication hole 15 if a defective product with the interior of the tank 2 not sealed is produced due to a defective bonding or a defective brazing of the partition plates 10, 10, so that early finding of a defective product is possible.
  • Air or the like may permeate into the cavity 14 and be transformed into water depending on temperature and pressure conditions to accumulate in the cavity 14. But, since the communication hole 15 is formed on the lower part in a direction of gravitation of the outer wall of the tank 2 configuring the cavity 14, water accumulated in the cavity 14 can be discharged from there with ease, and the tank 2 can be prevented from being corroded by the accumulated water.
  • Fig. 34 shows an embodiment of a heat exchanger 1 formed by disposing horizontally first and second heat exchangers A, B horizontally and in parallel.
  • the heat exchanger 1 is a heat exchanger formed by vertically connecting a plurality of tubes 4A, 4B and fins 3a, 3a between a pair of tanks 2, 2 disposed vertically.
  • a heat insulation region 11 is formed between the tubes 4A configuring the first heat exchanger A and the tubes 4B configuring the second heat exchanger B which are adjacent horizontally.
  • a bonding plate 12 is provided in the heat insulation region 11.
  • two partition plates 10, 10 are disposed to seal the inside of the tanks 2 to form a cavity (not shown) between the tubes 4A and the tubes 4B of the top and bottom tanks 2 to which connected are the tubes 4A configuring the first heat exchanger A and the tubes 4B configuring the second heat exchanger B which are adjacent horizontally.
  • a communication hole 15 for communicating the cavity with the outside is formed on the lower part in a direction of gravitation of the outer wall of the tank 2 having the cavity.
  • Fig. 35 and Fig. 36 show an embodiment of a laminate type heat exchanger in that tank segments 2b, 2b stacked to form a tank 2 are integrally formed with tubes 4A, 4B.
  • this heat exchanger 1 is a single tank type having the tank segments 2b, 2b and fins 3a, 3a between a plurality of tubes 4, 4.
  • the tubes 4A, 4B are provided with a ridge 22 formed as partition from one end integral with the tank 2 to near the other end. This ridge 22 forms going and return passages in a longitudinal direction for the heat exchange medium, and the passages are in a U-shape at the other end in the tubes 4A, 4B.
  • a heat insulation region 11 without any fin 3a is formed between the tubes 4A configuring the first heat exchanger A and the tubes 4B configuring the second heat exchanger B which are adjacent horizontally, and a bonding plate 12 is provided in the heat insulation region 11. Therefore, the heat conduction between the first heat exchanger A and the second heat exchanger B is prevented by the heat insulation region 11, and the respective heat exchangers A, B can have the respective required performance.
  • Fig. 37 and Fig. 38 show an embodiment that tubes 4A, 4B and fins 3a, 3a configuring first and second heat exchangers A, B are vertically connected to a tank 2 to combine the first and second heat exchangers A, B in parallel to form a single tank type heat exchanger 1. And, a heat insulation region 11 is formed without any fin 3a between the tubes 4A configuring the first heat exchanger and the tubes 4B configuring the second heat exchanger which are adjacent horizontally, and a bonding plate 12 is disposed in the heat insulation region 11.
  • the tubes 4A, 4B are provided with a ridge 22 formed as partition from one end integrally formed with the tank 2 to near the other end.
  • This ridge 22 forms going and return passages for the heat exchange medium in a longitudinal direction within the tubes 4A, 4B, and the passages are formed in a U-shape at the other end.
  • This heat exchanger 1 has the tank 2 formed of an end plate 2c and a tank plate 2d. And, the tubes 4A, 4B, the fins 3a, 3a and the end plate 2c are integrally assembled and brazed in the oven, the tank plate 2d is fixed to the end plate 2c by torch brazing, welding, caulking or the like.
  • the tubes 4A, 4B, the fins 3a, 3a, the end plate 2c and the tank plate 2d may be brazed integrally in the oven.
  • the inside of the tank 2 is sealed by two partition plates 10, 10 which are disposed between the tubes 4A and the tubes 4B of the tank 2 connected with the tubes 4A configuring the first heat exchanger A and the tubes 4B configuring the second heat exchanger B.
  • a cavity 14 is formed in the tank 2
  • a communication hole 15 is formed on the lower part in a direction of gravitation of the outer wall of the tank 2 having the cavity 14.
  • this embodiment has the communication hole 15 formed in the end plate 2c.
  • the heat exchanger of this embodiment is formed by integrally assembling the tubes and the fins and brazing them in the oven.
  • any of the bonding plate, the tank, the tank segments forming the tank and the end plate configuring the tank can be brazed at the same time.
  • the tank is formed of a tank material which is rolled into a circular pipe, a two-split material, or the tubes, the fins and the tank segments forming the tank are integrally assembled, namely a laminate type having the tank segments integrally assembled to the tubes, and brazed in the oven.
  • a third heat exchanger can be fitted to either or both of the upper and lower heat exchangers formed by combining two heat exchangers horizontally, or a third heat exchanger can be fitted to either or both of the right and left sides of the heat exchanger formed by assembling two heat exchangers vertically.
  • the heat exchanger may be formed by assembling as required.
  • Fig. 39 is a perspective view of the heat exchanger of this embodiment
  • Fig. 40 is a transverse sectional view of the heat exchanger.
  • This heat exchanger 1 is a heat exchanger having a plurality of fins 3a, 3a and tubes 4, 4 alternately stacked parallel to each other between a pair of tanks 2, 2.
  • the passages in the tubes 4 are divided into two by a sealing section 5.
  • the tanks 2, 2 have a partition plate 2a integrally formed in a longitudinal direction to divide the interior into the tanks 2A, 2A of the first heat exchanger A and the tanks 2B, 2B of the second heat exchanger B, and inlet joints 8A, 8B are connected to one tank and outlet joints 9A, 9B are connected to the other tank.
  • a side plate connecting hole (not shown) is formed in the tanks 2 on the top and bottom of the stacked tubes 4, 4, and both ends of side plates 3b, 3b having a square C-shaped cross section are inserted into the side plate connecting holes.
  • partition plates (not shown) are disposed on required positions of the tank 2B to divide in a longitudinal direction the interior of the tank 2B of the second heat exchanger B into a plurality of sections.
  • the first heat exchanger A is a radiator and the second heat exchanger B is a condenser.
  • the first and second heat exchangers A, B are disposed downstream and upstream of an air flow direction to form the heat exchanger 1.
  • the tube 4 is formed by bonding both ends 4m, 4n of two plates at both ends of the tube, the tube 4 has its passage divided into two in its longitudinal direction by the sealing section 5 to form a passage 6 on one side connected to the tanks 2A, 2A and a passage 7 on the other side connected to the tanks 2B, 2B.
  • the heat exchange medium is flown through the passages 6, 7 of the tubes 4 between the inlet joints 8A, 8B and the outlet joints 9A, 9B to perform heat exchange.
  • the passage 7 has beads 7a, 7a having a U-shaped cross section to protrude inward of the tube, and the leading ends of the beads 7a are in contact with the plate.
  • the beads 7a have an ellipse shape.
  • the tube 4 can decrease the heat conduction between the heat exchangers as low as possible by the sealed section 5 formed and prevent the heat conduction between the heat exchangers to improve the heat exchange rate.
  • the sealed section 5 of the tube 4 has holes 5a, 5a for heat insulation.
  • the heat insulating effect can be improved additionally by the holes 5a, 5a formed in the sealed section 5.
  • the tube material is a three-layered material formed of an alloy (Al-Mn based) of JIS A 3003 as a core and both a layer forming the inner face of the tube and a layer forming the outer face of the tube clad with an alloy (Al-Si based) of JIS A 4045 as a brazing material, or a four-layered material formed of an alloy (Al-Mn based) of JIS A 3003 as a core and a layer forming the intermediate of the tube being clad with a 1000-based (99.0 wt% Al) aluminum alloy and both a layer forming the inner face of the tube and a layer forming the outer face of the tube clad with an alloy (Al-Si based) of JIS A 4045 as a brazing material.
  • the layer forming the inner face of the tube and the layer forming the outer face are clad with the brazing material, the potential of the core material is determined high owing to a potential difference between the core material and the brazing material, and the outer and inner faces of the tube can have an improved corrosion resistance owing to a sacrificial anode effect of the brazing material.
  • the inner face of the tube has an improved pitting corrosion resistance owing to sacrificial corrosion prevention uniformly effecting on the surface of the intermediate layer.
  • the tube when the tube is formed of a three-layered material having both sides of a core material clad with a brazing material or a four-layered material having the core material and the intermediate layer clad with a brazing material, the tube itself has an improved pressure resistance.
  • an aluminum material or an aluminum alloy used for a three-layered material or a four-layered material is, for example, an aluminum alloy having Si and Mg added, and used to deposit an intermetallic compound Mg2Si, thereby providing an effect of improving the strength of the material and an effect of improving the structural strength of the heat exchanger or an alloy containing elements for improving a corrosion resistance of the brazing material may be used.
  • the tube has the sealed section, the heat conduction of both heat exchangers can be decreased as low as possible, so that the heat conduction between the respective heat exchangers can be prevented, and the heat exchange rate can be improved.
  • the tube having the improved corrosion resistance and pressure resistance can be produced. Therefore, for example, when both inner and outer faces of the tube are required to have a high corrosion resistance like a radiator is used for the first heat exchanger A, and the inner face of the tube is not required such a high corrosion resistance like a condenser used for the second heat exchanger B, but the outer face of the tube is required to have a corrosion resistance and a pressure resistance, the tubes satisfying the required performance different for the respective heat exchangers can be formed integrally, and the number of components can be decreased when a heat exchanger is formed by having the first and second heat exchangers formed into one body, and the production cost can be reduced.
  • the fins 3 can be made of a bare material of an aluminum alloy not clad with the brazing material as the fin material.
  • an alloy (Al-Mn based) of JIS A 3003 added with 1.5% of Zn can be used, and since the fin is made of a material not clad with the brazing material, abrasion of a die for making the fins can be decreased, and the maintenance cost can be reduced.
  • the fins can be produced using a material not clad with the brazing material, the material cost can be reduced, and the production cost can also be reduced.
  • the fin material is added with 1.5% of Zn, when the tubes 4 and the fins 3a are assembled into one body, the tubes have a high potential. Therefore, the outer face of the tube is prevented from being corroded by virtue of the sacrificial anode effect while the fins 3a are corroded first, and the corrosion resistance of the outer face of the tube is improved.
  • Fig. 42 through Fig. 44 are perspective views showing embodiments of the tubes 4, which are formed of two plates in the same manner as shown in Fig. 41 and viewed, from their end faces.
  • the tube 4 is formed of plates which are bent to protrude beads 7b inward, the beads 7b are formed in a longitudinal direction of the tube 4, and the leading ends of the beads 7b are in contact with the surface of each opposed plate.
  • the tube 4 shown in Fig. 43 has beads 7c which are protruded inward and to have a U-shaped cross section, and the beads 7c are also formed in a longitudinal direction of the tube 4 in this case. And, the leading ends of the beads 7c are in contact with the surface of each opposed plate.
  • the tube 4 shown in Fig. 44 has circular beads 7d having a U-shaped cross section protruded inward. And the leading ends of the beads 7d are in contact with the surface of each opposed plate.
  • the above-described embodiments have two plates to form the tubes, but the beads can also be formed in the same way on the tube formed by folding a single plate formed by pressing or rolling into halves or the tube formed by folding a single plate into halves while rolling.
  • Fig. 45 through Fig. 48 are perspective views showing embodiments of the tubes viewed from the end faces of the tubes. There are shown embodiments of the tubes 4 formed by folding a single plate into halves to join the plate ends 4m, 4n at one end of the tube.
  • the tube 4 is formed to have long beads 7e, 7e having a U-shaped cross section to protrude inward in a passage 7 on one side, and the long beads 7e, 7e have an ellipse plane form. The leading ends of the beads 7e are mutually contacted.
  • the tube 4 is formed to have beads 7f in a longitudinal direction of the tube by bending a plate so as to protrude inward, and the leading ends of the beads 7f, 7f are mutually contacted.
  • Fig. 47 shows that the tube 4 is formed to have beads 7g having a U-shaped cross section so to protrude inward, and the leading ends of the beads 7g, 7g are mutually contacted.
  • Fig. 48 shows that the tube 4 is formed to have circular beads 7h having a U-shaped cross section so to protrude inward, and the leading ends of the beads 7h, 7h are mutually contacted.
  • Fig. 49 shows another embodiment of the tube 4 comprising a plurality of beads 7c, 7c formed in a passage 7 on one side and a bead 6c also formed to protrude inward of a passage 6 on the other side, and the beads 6c, 7c are in contact with the opposed flat faces.
  • the beads 6c, 7c are long beads formed in a longitudinal direction of the tube.
  • the beads are formed in the passage on one side and in the passage on the other side as well to improve the heat exchange rate and also to satisfy the required performance such as a pressure resistance and the like for the respective heat exchangers.
  • Fig. 50 through Fig. 53 are perspective views showing other embodiments of the tube viewed from their end faces.
  • the tube 4 is formed of a single plate, except that the ends of the plate were joined in a different way and the joining points are changed.
  • Fig. 50 shows that the tube 4 is formed to have long beads 7c in a passage 7 on one side to protrude inward along a longitudinal direction of the tube, and the leading ends of the beads 7c are in contact with the opposed flat faces of the plate. Both ends 4m, 4n of the plate are bent to protrude inward of the tube, and the bent ends 4m, 4n are mutually joined by their flat faces.
  • Fig. 51 shows that the tube 4 is formed to have a plurality of long beads 7c in a passage 7 on one side in a longitudinal direction of the tube. And, one end 4m of the plate is bent to have an L-shape on the passage 7 so to be in contact with the opposed face of the plate, and the other end 4n of the plate is also bent to have the L-shape on the same position so to be overlaid on the end 4m of the plate. In other words, the ends 4m, 4n of the plate form a long bead having a U-shaped cross section.
  • Fig. 52 shows that the tube 4 is formed to have long beads 7c in a passage 7 on one side, and the plate ends 4m, 4n are mutually overlaid and bonded on the flat faces where a bead 7c is not formed.
  • a bead 7c' which is in contact with a flat face where the plate ends 4m, 4n are bonded, is formed to have a U-shaped cross section with a height lower than those of other beads, and the plate end 4m and the plate end 4n are overlaid and bonded on the flat face of the tube where the bead 7c' is contacted.
  • Fig. 53 shows that the tube 4 is formed to have a plurality of beads 7c in a passage 7 on one side, the ends 4m, 4n of the plate are bent to protrude inward at the center of a passage 6 on the other side so that the surfaces of the bent ends 4m, 4n are mutually contacted and also in contact with the flat face of the tube.
  • the plate ends 4m, 4n are bonded to form the tube and also serve as a bead to divide the passage 6.
  • the tube when the tube is made of a single plate, the plate ends are joined not to protrude outward at the formed tube ends, but the joining style and joining portions are changed so to join the plate material at the tube end, bead position, flat face or passage. Therefore, the tube has an appearance with substantially the same shape on both sides thereof.
  • the tube insertion holes having different shapes on the tanks on both sides, unlike the conventional one, so that the production facilities can be decreased, the assembling property of the tubes can be improved, and the production process can be simplified.
  • the plate ends are joined on a layer which becomes the outer face of the tube, when a tube not required to have a corrosion resistance on its inner face is formed or when an intermediate layer having electric potential different from the core material is coated on a layer which becomes the inner face of the tube, the layer becoming the inner face of the tube is not required to be clad with the brazing material, and the production cost can be reduced.
  • Fig. 54 and Fig. 55 show an embodiment that first and second heat exchangers A, B, each is a single tank type, are combined parallel to form a heat exchanger 1.
  • the heat exchanger 1 shown in Fig. 54 is a heat exchanger having a plurality of tubes 4, 4 and fins 3a, 3a which are connected to tanks 2A, 2B.
  • the respective tubes 4, 4 are formed of a single or two plates of an aluminum material or aluminum alloy of a three-layered or four-layered material of a two-sided clad with the brazing material in the same way as the previously described embodiments.
  • the tube 4 has its passage divided in a longitudinal direction of the tube by a sealed section 5 to form a passage 6 on one side connected to one tank 2A and another passage 7 on the other side connected to the other tank 2B.
  • Ridges 60, 70 are formed at the middle of the respective passages 6, 7 to be in contact with the surface of the plate, or the ridges 60, 60 or the ridges 70, 70 are mutually contacted to form the respective passages 6, 7 each having a U-shape.
  • Reference numerals 7a, 7a denote ellipse beads, and these long beads 7a, 7a are in contact with the surface of the plate, or the long beads 7a, 7a are mutually contacted.
  • This configuration is sufficient with a tank which is a half as compared with a parallel flow-type heat exchanger, an area in contact with air is increased accordingly, and a heat exchange rate is improved. And, there are also advantages that the number of components is decreased, and the cost is reduced.
  • Fig. 56 shows an embodiment that first and second heat exchangers A, B, each is a single tank type, are disposed in parallel to position the tanks alternately, a tank 2A being on the left and a tank 2B on the right side.
  • a plurality of tubes 4, 4 and fins 3a, 3a are disposed between the tank 2A and the tank 2B, the tubes 4, 4 are provided with the sealed section 5 to divide the passage in the same way as the previously described embodiments, a passage 6 on one side connected to one tank 2A and other passage 7 on the other side connected to the other tank 2B are each formed to have a U-shape.
  • the tubes 4, 4 are formed of a single or two plates of an aluminum material or aluminum alloy of a three-layered or four-layered material of a two-sided clad with the brazing material, and the fins are formed of an aluminum material or aluminum alloy containing 1.5% of Zn.
  • the heat exchanger formed by assembling the first and second heat exchangers A, B described above can be mounted on a vehicle body with brackets fitted to its both sides, and assemblability can be improved.
  • Fig. 57 shows an embodiment that stacked tank segments 2b, 2b forming tanks 2A, 2B are of a laminate type and integrally formed with tubes 4, 4.
  • the heat exchanger 1 is also a heat exchanger having a plurality of tubes 4, 4 disposed between two pairs of tanks 2A, 2A and 2B, 2B disposed in parallel, the respective tubes 4, 4 have a sealed section 5 to divide the passage in a longitudinal direction to form a passage 6 on one side connected to the tanks 2A, 2A on one side and a passage 7 on the other side connected to the tanks 2B, 2B on the other side.
  • the tubes 4, 4 are formed of a single or two plates of an aluminum material or aluminum alloy of a three-layered or four-layered material of a two-sided clad with the brazing material, and the tubes satisfying the required performance of the respective heat exchangers are formed into one body.
  • the heat exchanger of this embodiment is basically formed by integrally assembling tubes and fins and brazing them in the oven, and in addition to the brazing of the tubes and fins, any of a bonding plate, a tank and tank segments configuring the tank can be brazed at the same time.
  • the tank is formed of a tank material which is rolled into a circular pipe or a two-split material, and the tubes, the fins and the tank segments to be stacked to form the tank are integrally assembled, namely a laminate type having the tank segments integrally assembled to the tubes, and brazed in the oven.
  • the above-described embodiment has two heat exchangers assembled in parallel and horizontally to form the heat exchanger. But, two heat exchangers may be assembled in parallel and vertically, or a third heat exchanger can be fitted to either or both of the upper and lower heat exchangers formed by two heat exchangers. Thus, the heat exchanger may be formed by assembling and combining the heat exchangers as required.
  • the invention is applied to heat exchangers for automobiles and home uses, and more particularly to a heat exchanger combining a radiator and a condenser for automobiles.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP97937831A 1996-08-29 1997-08-28 Wärmetauscher Withdrawn EP0859209A4 (de)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
JP22913796A JPH1073388A (ja) 1996-08-29 1996-08-29 熱交換器
JP229137/96 1996-08-29
JP26291696A JPH10111086A (ja) 1996-10-03 1996-10-03 熱交換器
JP262916/96 1996-10-03
JP35166596A JPH10197174A (ja) 1996-12-27 1996-12-27 熱交換器
JP351665/96 1996-12-27
PCT/JP1997/003010 WO1998009124A1 (fr) 1996-08-29 1997-08-28 Echangeur thermique

Publications (2)

Publication Number Publication Date
EP0859209A1 true EP0859209A1 (de) 1998-08-19
EP0859209A4 EP0859209A4 (de) 1999-06-09

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EP97937831A Withdrawn EP0859209A4 (de) 1996-08-29 1997-08-28 Wärmetauscher

Country Status (3)

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EP (1) EP0859209A4 (de)
CN (1) CN1199458A (de)
WO (1) WO1998009124A1 (de)

Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2785376A1 (fr) * 1998-10-29 2000-05-05 Valeo Thermique Moteur Sa Echangeur de chaleur multifonction, notamment pour vehicule automobile
US6267177B1 (en) 1999-01-19 2001-07-31 Calsonic Kansei Corporation Flat tubes for use with heat exchanger and manufacturing method thereof
FR2832789A1 (fr) * 2001-11-27 2003-05-30 Valeo Thermique Moteur Sa Ailette de module d'echange de chaleur, en particulier pour vehicule automobile
FR2853052A1 (fr) * 2003-03-31 2004-10-01 Valeo Thermique Moteur Sa Module d'echange de chaleur a fonctionnement optimise, notamment pour vehicule automobile
EP1477758A2 (de) * 2003-05-14 2004-11-17 Calsonic Kansei Corporation Mehrzweckwärmetauscher
WO2005001365A1 (en) * 2003-05-30 2005-01-06 Valeo Inc Heat exchanger having an improved baffle
EP1568960A2 (de) * 2004-02-24 2005-08-31 Behr GmbH & Co. KG Wärmeübertrager mit Seitenteilen
US6938675B2 (en) 2000-10-11 2005-09-06 Denso Corporation Heat exchanger
WO2005087523A1 (en) * 2004-03-12 2005-09-22 Nissan Motor Co., Ltd Heat exchanger
WO2006014956A1 (en) * 2004-07-31 2006-02-09 Valeo, Inc. Heat exchano'er having a double baffle
US7036571B2 (en) * 2003-05-15 2006-05-02 Calsonic Kansei Corporation Compound type heat exchanger
US7077193B2 (en) * 2003-05-14 2006-07-18 Calsonic Kansei Corporation Compound type heat exchanger
US7096932B2 (en) * 2003-12-22 2006-08-29 Modine Manufacturing Company Multi-fluid heat exchanger and method of making same
US7131488B2 (en) 2003-10-01 2006-11-07 Denso Corporation Heat exchanger module
WO2007014560A2 (de) * 2005-08-04 2007-02-08 Visteon Global Technologies, Inc. Mehrflutiger wärmeübertrager
DE102006037302A1 (de) * 2006-08-08 2008-02-14 Behr Gmbh & Co. Kg Wärmetauscher, insbesondere für eine Kraftfahrzeug-Klimaanlage
WO2008131001A1 (en) * 2007-04-16 2008-10-30 Luvata Franklin, Inc. Method of producing a corrosion resistant aluminum heat exchanger
FR2925665A1 (fr) * 2007-12-24 2009-06-26 Valeo Systemes Thermiques Tube plie pour echangeur de chaleur brase,procede de fabrication et echangeur de chaleur
DE102008050611A1 (de) * 2008-10-09 2010-04-15 Behr Gmbh & Co. Kg Wärmeübertrager
US7921559B2 (en) 2006-01-19 2011-04-12 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8091621B2 (en) 2006-01-19 2012-01-10 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8191258B2 (en) 2006-01-19 2012-06-05 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
EP2481899A1 (de) * 2011-01-27 2012-08-01 Bayerische Motoren Werke Aktiengesellschaft Wärmetauscher
US8281489B2 (en) 2006-01-19 2012-10-09 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8438728B2 (en) 2006-01-19 2013-05-14 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
EP2151650A3 (de) * 2008-08-06 2013-09-18 Delphi Technologies, Inc. Kreuzgegenstrom-Wärmeaustauschereinheit
US8683690B2 (en) 2006-01-19 2014-04-01 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8726508B2 (en) 2006-01-19 2014-05-20 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US9038267B2 (en) 2010-06-10 2015-05-26 Modine Manufacturing Company Method of separating heat exchanger tubes and an apparatus for same
US11441841B2 (en) 2018-12-28 2022-09-13 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Heat exchanger assembly and method for assembling same
WO2024088811A1 (fr) * 2022-10-26 2024-05-02 Valeo Systemes Thermiques Echangeur de chaleur, notamment pour un véhicule

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2001278689A1 (en) * 2000-08-04 2002-02-18 Showa Denko K K Integrated heat exchanger
DE112005001009T5 (de) * 2004-05-11 2007-03-08 Showa Denko Kk Wärmetauscher
US8434227B2 (en) 2006-01-19 2013-05-07 Modine Manufacturing Company Method of forming heat exchanger tubes
DE102007004993A1 (de) 2007-02-01 2008-08-07 Modine Manufacturing Co., Racine Herstellungsverfahren für Flachrohre und Walzenstraße
JP5408017B2 (ja) * 2009-06-05 2014-02-05 株式会社デンソー 蓄冷熱交換器
JP2016153718A (ja) * 2015-02-12 2016-08-25 カルソニックカンセイ株式会社 熱交換器、熱交換器の組み立て装置、及び熱交換器の組み立て方法
JP6767621B2 (ja) * 2016-10-21 2020-10-14 パナソニックＩｐマネジメント株式会社 熱交換器およびそれを用いた冷凍システム

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB583814A (en) * 1944-01-17 1946-12-31 James Frank Belaieff Improvements in or relating to secondary surface heat exchange apparatus
US2505790A (en) * 1946-07-24 1950-05-02 Perfex Corp Combination radiator and oil cooler
US4651816A (en) * 1986-03-19 1987-03-24 Modine Manufacturing Company Heat exchanger module for a vehicle or the like
US5180004A (en) * 1992-06-19 1993-01-19 General Motors Corporation Integral heater-evaporator core
US5197538A (en) * 1991-04-22 1993-03-30 Zexel Corporation Heat exchanger apparatus having fluid coupled primary heat exchanger unit and auxiliary heat exchanger unit
EP0677716A1 (de) * 1994-04-12 1995-10-18 Showa Aluminum Corporation Doppelwärmetauscher in Stapelbauweise
EP0694747A2 (de) * 1994-07-25 1996-01-31 Sanden Corporation Wärmetauscher
US5509199A (en) * 1995-01-17 1996-04-23 General Motors Corporation Method of making a dual radiator and condenser assembly
EP0719997A1 (de) * 1994-12-26 1996-07-03 Valeo Climatisation Raumsparender Wärmeaustauscher für drei Media
DE19536116A1 (de) * 1995-09-28 1997-04-03 Behr Gmbh & Co Wärmeübertrager für ein Kraftfahrzeug

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5916692U (ja) 1982-07-26 1984-02-01 株式会社ユニバ−サル スロツトマシンのハンドルロツク装置
JPS61115862U (de) 1985-01-05 1986-07-22
JPS6458991A (en) * 1987-08-31 1989-03-06 Hisaka Works Ltd Composite heat exchanger
JPH0236772U (de) 1988-09-02 1990-03-09
JPH0254076U (de) 1988-10-11 1990-04-19
JPH0645157Y2 (ja) * 1988-10-25 1994-11-16 昭和アルミニウム株式会社 一体連設型熱交換器
JPH02122966U (de) * 1989-03-15 1990-10-09
JP2586753Y2 (ja) * 1990-09-28 1998-12-09 サンデン株式会社 熱交換器
JPH05272889A (ja) * 1992-03-26 1993-10-22 Nippondenso Co Ltd 熱交換器
JPH0645157U (ja) 1992-11-30 1994-06-14 デルタ工業株式会社 自動車用オートチェンジレバー
JP3683001B2 (ja) * 1994-04-12 2005-08-17 昭和電工株式会社 複式積層型熱交換器
JP3674058B2 (ja) * 1994-10-11 2005-07-20 株式会社デンソー 積層型熱交換器の製造方法

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB583814A (en) * 1944-01-17 1946-12-31 James Frank Belaieff Improvements in or relating to secondary surface heat exchange apparatus
US2505790A (en) * 1946-07-24 1950-05-02 Perfex Corp Combination radiator and oil cooler
US4651816A (en) * 1986-03-19 1987-03-24 Modine Manufacturing Company Heat exchanger module for a vehicle or the like
US5197538A (en) * 1991-04-22 1993-03-30 Zexel Corporation Heat exchanger apparatus having fluid coupled primary heat exchanger unit and auxiliary heat exchanger unit
US5180004A (en) * 1992-06-19 1993-01-19 General Motors Corporation Integral heater-evaporator core
EP0677716A1 (de) * 1994-04-12 1995-10-18 Showa Aluminum Corporation Doppelwärmetauscher in Stapelbauweise
EP0694747A2 (de) * 1994-07-25 1996-01-31 Sanden Corporation Wärmetauscher
EP0719997A1 (de) * 1994-12-26 1996-07-03 Valeo Climatisation Raumsparender Wärmeaustauscher für drei Media
US5509199A (en) * 1995-01-17 1996-04-23 General Motors Corporation Method of making a dual radiator and condenser assembly
DE19536116A1 (de) * 1995-09-28 1997-04-03 Behr Gmbh & Co Wärmeübertrager für ein Kraftfahrzeug

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO9809124A1 *

Cited By (45)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2785376A1 (fr) * 1998-10-29 2000-05-05 Valeo Thermique Moteur Sa Echangeur de chaleur multifonction, notamment pour vehicule automobile
US6267177B1 (en) 1999-01-19 2001-07-31 Calsonic Kansei Corporation Flat tubes for use with heat exchanger and manufacturing method thereof
EP1022532A3 (de) * 1999-01-19 2001-08-01 Calsonic Kansei Corporation Flachröhren für Wärmetauscher und Verfahren zu deren Herstellung
US6431265B2 (en) 1999-01-19 2002-08-13 Calsonic Kansei Corporation Flat tubes for use with heat exchanger and manufacturing method thereof
US6938675B2 (en) 2000-10-11 2005-09-06 Denso Corporation Heat exchanger
FR2832789A1 (fr) * 2001-11-27 2003-05-30 Valeo Thermique Moteur Sa Ailette de module d'echange de chaleur, en particulier pour vehicule automobile
WO2003046458A1 (fr) * 2001-11-27 2003-06-05 Valeo Thermique Moteur Ailette de module d'echange de chaleur
WO2004090448A2 (fr) * 2003-03-31 2004-10-21 Valeo Thermique Moteur Module d’echange de chaleur, notamment pour vehicule automobile
FR2853052A1 (fr) * 2003-03-31 2004-10-01 Valeo Thermique Moteur Sa Module d'echange de chaleur a fonctionnement optimise, notamment pour vehicule automobile
WO2004090448A3 (fr) * 2003-03-31 2005-02-10 Valeo Thermique Moteur Sa Module d’echange de chaleur, notamment pour vehicule automobile
EP1477758A3 (de) * 2003-05-14 2008-02-06 Calsonic Kansei Corporation Mehrzweckwärmetauscher
EP1477758A2 (de) * 2003-05-14 2004-11-17 Calsonic Kansei Corporation Mehrzweckwärmetauscher
US7077193B2 (en) * 2003-05-14 2006-07-18 Calsonic Kansei Corporation Compound type heat exchanger
US7036571B2 (en) * 2003-05-15 2006-05-02 Calsonic Kansei Corporation Compound type heat exchanger
EP1477760A3 (de) * 2003-05-15 2008-03-12 Calsonic Kansei Corporation Verbundwärmetauscher
WO2005001365A1 (en) * 2003-05-30 2005-01-06 Valeo Inc Heat exchanger having an improved baffle
US6942014B2 (en) 2003-05-30 2005-09-13 Valeo, Inc. Heat exchanger having an improved baffle
US7131488B2 (en) 2003-10-01 2006-11-07 Denso Corporation Heat exchanger module
US7096932B2 (en) * 2003-12-22 2006-08-29 Modine Manufacturing Company Multi-fluid heat exchanger and method of making same
EP1568960A2 (de) * 2004-02-24 2005-08-31 Behr GmbH & Co. KG Wärmeübertrager mit Seitenteilen
EP1568960A3 (de) * 2004-02-24 2010-09-15 Behr GmbH & Co. KG Wärmeübertrager mit Seitenteilen
WO2005087523A1 (en) * 2004-03-12 2005-09-22 Nissan Motor Co., Ltd Heat exchanger
US7845392B2 (en) 2004-03-12 2010-12-07 Nissan Motor Co., Ltd. Heat exchanger assembly
WO2006014956A1 (en) * 2004-07-31 2006-02-09 Valeo, Inc. Heat exchano'er having a double baffle
US8561681B2 (en) 2005-08-04 2013-10-22 Visteon Global Technologies, Inc. Multiple flow heat exchanger
WO2007014560A3 (de) * 2005-08-04 2007-03-22 Visteon Global Tech Inc Mehrflutiger wärmeübertrager
WO2007014560A2 (de) * 2005-08-04 2007-02-08 Visteon Global Technologies, Inc. Mehrflutiger wärmeübertrager
US8683690B2 (en) 2006-01-19 2014-04-01 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8281489B2 (en) 2006-01-19 2012-10-09 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8726508B2 (en) 2006-01-19 2014-05-20 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US7921559B2 (en) 2006-01-19 2011-04-12 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8091621B2 (en) 2006-01-19 2012-01-10 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8191258B2 (en) 2006-01-19 2012-06-05 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
US8438728B2 (en) 2006-01-19 2013-05-14 Modine Manufacturing Company Flat tube, flat tube heat exchanger, and method of manufacturing same
DE102006037302A1 (de) * 2006-08-08 2008-02-14 Behr Gmbh & Co. Kg Wärmetauscher, insbesondere für eine Kraftfahrzeug-Klimaanlage
US8152047B2 (en) 2007-04-16 2012-04-10 Luvata Franklin, Inc. Method of producing a corrosion resistant aluminum heat exchanger
WO2008131001A1 (en) * 2007-04-16 2008-10-30 Luvata Franklin, Inc. Method of producing a corrosion resistant aluminum heat exchanger
FR2925665A1 (fr) * 2007-12-24 2009-06-26 Valeo Systemes Thermiques Tube plie pour echangeur de chaleur brase,procede de fabrication et echangeur de chaleur
EP2151650A3 (de) * 2008-08-06 2013-09-18 Delphi Technologies, Inc. Kreuzgegenstrom-Wärmeaustauschereinheit
DE102008050611A1 (de) * 2008-10-09 2010-04-15 Behr Gmbh & Co. Kg Wärmeübertrager
US9038267B2 (en) 2010-06-10 2015-05-26 Modine Manufacturing Company Method of separating heat exchanger tubes and an apparatus for same
EP2481899A1 (de) * 2011-01-27 2012-08-01 Bayerische Motoren Werke Aktiengesellschaft Wärmetauscher
US11441841B2 (en) 2018-12-28 2022-09-13 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Heat exchanger assembly and method for assembling same
WO2024088811A1 (fr) * 2022-10-26 2024-05-02 Valeo Systemes Thermiques Echangeur de chaleur, notamment pour un véhicule
FR3141515A1 (fr) * 2022-10-26 2024-05-03 Valeo Systemes Thermiques Sas Echangeur de chaleur, notamment pour un véhicule

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CN1199458A (zh) 1998-11-18
WO1998009124A1 (fr) 1998-03-05
EP0859209A4 (de) 1999-06-09

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