EP1985957A1 - Échangeur thermique pour véhicule - Google Patents

Échangeur thermique pour véhicule Download PDF

Info

Publication number
EP1985957A1
EP1985957A1 EP07707712A EP07707712A EP1985957A1 EP 1985957 A1 EP1985957 A1 EP 1985957A1 EP 07707712 A EP07707712 A EP 07707712A EP 07707712 A EP07707712 A EP 07707712A EP 1985957 A1 EP1985957 A1 EP 1985957A1
Authority
EP
European Patent Office
Prior art keywords
projecting portion
corrugated fins
portions
core part
radiator
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Withdrawn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
EP07707712A
Other languages
German (de)
English (en)
Inventor
Mitsuru Iwasaki
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.)
Marelli Corp
Original Assignee
Calsonic Kansei 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
Application filed by Calsonic Kansei Corp filed Critical Calsonic Kansei Corp
Publication of EP1985957A1 publication Critical patent/EP1985957A1/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F28D1/0435—Combination of units extending one behind 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • 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
    • 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
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • the present invention relates to a heat exchanger for motor vehicles, and more particularly it relates to a heat exchanger having a core part thereof which is provided with a plurality of corrugated fins formed with louvers thereon.
  • Corrugated fins with louvers used for conventional heat exchangers, are disclosed in Japanese Patent Applications Laid-Open Publication No. 9 - 61081 , No. 11 - 173784 , No. 2000 - 18880 , No. 2002 - 350077 and No. 2003 - 83691 .
  • the corrugated fins and a plurality of tubes are alternately piled up to form a core part of the heat exchanger.
  • Japanese Patent Application Laid-Open No. 2005 - 257104 discloses a conventional integrated heat exchanger, in which corrugated fins are extended into both core parts of a radiator and a condenser.
  • the corrugated fins are provided with a plurality of dimple portions, formed like a cylindrical projection, between the core parts of the condenser and the radiator to improve coolability of the radiator by increasing a heat radiation area.
  • the conventional heat exchangers have a problem in that heat exchange efficiency thereof is poor because cooling air discharged through the core part of the condenser passes through the louvers of the core part of the radiator without sufficient introduction thereto.
  • the projections have no operation or effects of surely introducing the cooling air to the louvers of the core part of the radiator, although they contribute to increase in heat radiation area.
  • Such a problem also occurs in conventional radiators and condensers which are independent from each other and are provided with corrugated fins, respectively.
  • the present invention is made in order to solve the above-described problem, and its object is to provide a heat exchanger for motor vehicles which can improve coolability thereof by surely conducting cooling air to louvers arranged between core parts of the heat exchanger.
  • a heat exchanger for motor vehicles including a pair of tanks located apart from each other and a core part located between the pair of tanks.
  • the core part has a plurality of tubes and a plurality of corrugated fins arranged between the adjacent tubes, where the corrugated fins are formed with a plurality of louvers.
  • the corrugated fins have an upstream projecting portion provided with a projecting portion so that cooling air converges downward to be conducted to the louvers by the projecting portion.
  • the heat exchanger has a radiator with a core part and a condenser with a core part, the core parts being arranged near each other to have a plurality of corrugated fins, piled up alternately with tubes, so that upstream portions and downstream portions of the corrugated fins are shared for the core parts, respectively.
  • the corrugated fins are formed with first louvers at a position corresponding to the core part of the condenser and second louvers at a position corresponding to the core part of the radiator.
  • the projecting portion is provided on the corrugated fins between the core parts.
  • the heat exchanger has a radiator with a core part and a condenser with a core part arranged near the core part of the radiator.
  • the upstream projecting portions and the downstream projecting portions have the projecting portion.
  • the projecting portion projects in a direction where the cooling air flows into the louvers arranged at a downstream side of the projecting portion.
  • the projecting portion includes a first projecting portion and a second projecting portion that are arranged like a V-letter shape.
  • the first projecting portion and the second projecting portion are arranged symmetrically relative to a central line extending in a longitudinal direction of the corrugated fin at a central height thereof.
  • the first projecting portion and the second projecting portion have linear portions whose extended lines intersect each other on the central line.
  • the projecting portion includes a first projecting portion and a second projecting portion that are arranged like a V-letter shape.
  • the first projecting portion and the second projecting portion are arranged symmetrically relative to a central line extending in a longitudinal direction of the corrugated fin at a central height thereof.
  • the first projecting portion and the second projecting portion have curved portions which are bent to further depart from each other toward the downstream side.
  • the first corrugated fins and the second corrugated fins are different in at least one of fin pitch and fin height.
  • the heat changers include the pair of tanks located apart from each other and the core part located between the pair of tanks.
  • the core part has the plurality of tubes and the plurality of corrugated fins arranged between the adjacent tubes, where the corrugated fins are formed with the plurality of louvers.
  • the corrugated fins have the upstream projecting portion provided with the projecting portion so that the cooling air converges downward to be conducted to the louvers by the projecting portion. Therefore, coolability of the heat exchanger can be improved.
  • the heat exchanger has the radiator with the core part and the condenser with the core part, the core parts being arranged near each other to have the plurality of corrugated fins, piled up alternately with the tubes, so that the upstream portions and the downstream portions of the corrugated fins are shared for the core parts, respectively.
  • the corrugated fins are formed with the first louvers at the position corresponding to the core part of the condenser and the second louvers at the position corresponding to the core part of the radiator.
  • the projecting portion is provided on the corrugated fins between the core parts. This can improve especially the coolability of the radiator.
  • the heat exchanger has the radiator with the core part and the condenser with the core part arranged near the core part of the radiator.
  • the plurality of first corrugated fins of the radiator, piled up alternately with the tubes, have the upstream projecting portions
  • the plurality of second corrugated fins of the condenser, piled up alternately with the tubes have the downstream projecting portions to approach the upstream projecting portions.
  • the upstream projecting portions and the downstream projecting portions have the projecting portion. This can improve the coolability of the radiator, protecting the upstream and downstream projecting portions from buckling due to contact with their peripheral parts.
  • the projecting portion projects in the direction where the cooling air flows into the louvers arranged at the downstream side of the projecting portion. This enables the cooling air to be separated by the projecting portion to be well conducted to the louvers.
  • the projecting portion includes the first projecting portion and the second projecting portion that are arranged like the V-letter shape.
  • the first projecting portion and the second projecting portion are arranged symmetrically relative to the central line extending in the longitudinal direction of the corrugated fin at the central height thereof.
  • the first projecting portion and the second projecting portion have the linear portions whose extended lines intersect each other on the central line.
  • the projecting portion can be manufactured in a simple shape and enables the cooling air to well converge downward.
  • the projecting portion includes the first projecting portion and the second projecting portion that are arranged like the V-letter shape.
  • the first projecting portion and the second projecting portion are arranged symmetrically relative to the central line extending in the longitudinal direction of the corrugated fin at the central height thereof.
  • the first projecting portion and the second projecting portion have the curved portions which are bent to further depart from each other toward the downstream side. This enables the cooling air to well converge downward, enhancing torsion rigidity of the corrugated fins.
  • the first corrugated fins and the second corrugated fins are different in at least one of the fin pitch and the fin height.
  • the fin pitches and the fin heights thereof can be set appropriately in compliance with respective demands from heat radiation of the radiator and the condenser.
  • a longitudinal direction of a motor vehicle is expressed as “a frontward and rearward direction”
  • a lateral direction of the motor vehicle is expressed as “a left and right direction”.
  • a heat exchanger for motor vehicles employs an integrated heat exchanger including a radiator 1 and a condenser 2 that is arranged in front of the radiator 1, being integrally assembled therewith.
  • the radiator 1 is what is called a parallel-flow type radiator in which a pair of tanks 1b and 1c is located at a right side and a left side of a core part 1a, respectively.
  • the core part 1a includes a plurality of tubes 1d and a plurality of corrugated fins 3, where both end portions of the tubes 1d are inserted in and fixed to the first and second tanks 1b and 1c, respectively, and each of the corrugated fins 3 is disposed between the adjacent tubes 1d.
  • the corrugated fins 3 are shared with the core part 1a of the radiator 1 and a core part 2a of the condenser 2.
  • first and second tanks 1b and 1c On top and bottom portions of the first and second tanks 1b and 1c, four mounting pins 1e are vertically provided, respectively, for mounting the integrated heat exchanger on the motor vehicle.
  • An inlet port P1 is provided on a rear surface of the first tank 1b, and an outlet port P2 is provided on a rear surface of the second tank 1c.
  • the condenser 2 is equipped with a pair of tanks 2b and 2c at a right side and a left side of the core part 2a, respectively.
  • the core part 2a includes a plurality of tubes 2d and the corrugated fins 3, where both end portions of the tubes 2d are inserted in and fixed to the first tank 2b and the second tank 2c, respectively, and each of the corrugated fins 3 is disposed between the adjacent tubes 2d.
  • an inner space of the first tank 2b is divided by a partition plate S1 into a first chamber R1 and a fourth chamber R4, and an inner space of the second tank 2c is divided by another partition plate S1 into a second chamber R2 and a third chamber R3.
  • a connector 2e is provided to fluidically communicate with the first chamber R1
  • a connecting pipe 2f is provided to fluidically communicate with the fourth chamber R4
  • a receiver tank 2j is provided to fluidically communicate with the second chamber R2 through a connecting pipe 2g and also with the third chamber R3 through a connecting pipe 2h.
  • a pair of reinforcements 4 and 5 are inserted into and fixed to upper end portions of the first tanks 1b and 2b of the radiator 1 and condenser 2 and lower end portions of the second tanks 1c and 2c thereof, respectively. Accordingly, the radiator 1 and the condenser 2 are integrally connected with each other by the pair of the reinforcements 4 and 5.
  • the corrugated fins 3 are formed with a plurality of first louvers 3a at a position corresponding to the core part 2a of the condenser 2 and a plurality of second louvers 3b at a position corresponding to the core part 1a of the radiator 1, the first and second louvers 3a and 3b being raised in directions opposite to each other.
  • the corrugated fins 3 are formed with a first dimple portion (a first projecting portion) 3c and a second dimple portion (a second projecting portion) 3d, which are arranged along an appropriate V-letter shape, at the radiator core part side so that cooling air converges from a front side (an upstream side of the cooling airflow) toward a rear side (a downstream side of the cooling airflow).
  • the first and second dimple portions 3c and 3d correspond to a projecting portion of the present invention.
  • the first dimple portion 3c is designed to project in a direction where the cooling air passing through the first louvers 3a flows into the second louvers 3b as shown in FIG. 9 .
  • the second dimple portion 3d is designed similarly.
  • the first and second dimple portions 3c and 3d are arranged symmetrically to each other relative to a central line Z1 extending in a longitudinal direction of the corrugated fin 3 at a central height thereof.
  • the first and second dimple portions 3c and 3d are inclined at the same angle relative to the central line Z1 so that extended lines thereof intersect with each other at their downstream side at a predetermined angle of ⁇ .
  • the angle ⁇ is preferably set to be approximately 90°.
  • the first and second dimple portions 3c and 3d are formed to have a cross section having a pair of linear portions 3e and a pair of semicircular portions 3f connected with both end portions of the linear portions 3e. They are press-formed with the first and second louvers 3a and 3b at the same time when the corrugated fin 3 is manufactured, or they are formed by press working in advance of corrugation formation of material to be the corrugated fin 3.
  • the height H, as shown in FIG. 5 , width W, length L and angle ⁇ of the first and second dimple portions 3c and 3d may be set appropriately.
  • a portion of the corrugated fin 3 at the condenser core part side is provided with a first slit portion 3g and a second slit portion 3h, where the first slit portion 3g extends downward from a top portion of a folded portion of the corrugated fin 3 and the second slit portion 3h extends upward from a bottom portion of the folded portion so that they exceed the central line X1 to be overlapped with each other. They form a heat insulating portion 3i that vertically and zigzag connects an upstream portion and a downstream portion of the corrugated fin 3.
  • the heat insulating portion 3i may have a shape different from that of the first embodiment, and it may be removed according to the level of need.
  • Aluminum is used for all parts of the integrated heat exchanger, and one side portions of connecting portions of the parts are provided thereon with clad layers (brazing sheets) of brazing material.
  • the parts are temporally assembled, and then they are heat-treated in a not-shown heat furnace, so that the connecting portions of the parts are brazed and fixed with each other.
  • a cooling medium which enters the first tank 1b at a temperature of approximately 110°C from a not-shown engine side through the inlet port P1 of the radiator 1, is cooled down to approximately 60°C, while it flows through the tubes 1d, due to heat exchange between the cooling medium and the cooling air (ram airflow generated when the motor vehicle is running and/or airflow generated by the motor fan) passing through the core part 1a.
  • the cooled cooling medium enters the second tank 1c, and then it is discharged toward the engine side through the outlet port P2.
  • a cooling medium which enters the first chamber R1 of the first tank 2b of the condenser 2 at a temperature of approximately 70°C from a not-shown compressor side through the connector 2e, is heat-exchanged between the cooling medium and the cooling air passing through the core part 2a of the condenser 2 while it flows through the tubes 2d fluidically connecting the first chamber R1 and the second chamber R2.
  • the cooling medium entering the second chamber R2 is conducted to the receiver tank 2j through the connecting pipe 2g, being gas-liquid separated therein. Only the liquid cooling medium enters the third chamber R3 through the connecting pipe 2h, and then it is supercooled down to approximately 45°C due to heat exchange between the cooling medium and the cooling air while it flows through the tubes 2d fluidically connecting the third chamber R3 and the fourth chamber R4.
  • the supercooled cooling medium in the fourth chamber R4 is discharged to a not-shown evaporator side through the connecting pipe 2f and the connector 2e.
  • the cooling air CA enters from a front side of the integrated heat exchanger and passes the first louvers 3a that correspond to the core part 2a of the condenser 2. Then it flows, being separated by the first and second dimple portions 3c and 3d; along a first flow path X1 where it flows along insides of the first and second dimple portions 3c and 3d to run through the second louvers 3b that correspond to the core part 1a of the radiator 1, and also along a second flow pat X2 where it passes over the corrugated fin 3 in a lateral direction of the corrugated fin 3 to flow along outsides of the fist and second dimple portions 3c and 3d and return, then running through the second louvers 3b.
  • This enables the cooling air to be avoided from flowing away from the first louvers 3a in the lateral direction, thus surely flowing through the second louvers 3b to improve a heat radiation performance of the corrugated fin 3.
  • the heat insulating portion 3i suppresses heat transfer from a radiator side toward a condenser side in the corrugated fin 3. This can suppress harmful effects due to heat transfer between the core parts 1a and 2a.
  • the heat insulating portion 3i is preferably provided between the core parts 1a and 2a, at the condenser side where the condenser 2 is arranged at the upstream side of the cooling air CA and a temperature of the cooling medium thereof is low.
  • the first and second dimple portions 3c are preferably provided at the radiator side, where a temperature of the cooling medium of the radiator 1 is high.
  • FIG. 17 shows the test results in the heat radiation test which measured and compared the corrugated fin 3 of the first embodiment and corrugated fins A1 - A7 with various shapes shown in FIG. 10 to FIG. 16 .
  • the corrugated fin A2 has a conventional normal shape.
  • the cooling air CA is simulated as that generated when a motor vehicle runs at vehicle speeds of 40 to 120 km/h at an outside air temperature of 20°C, and, as shown in FIG. 6 , pressures and temperatures of the cooling air CA were measured at an inlet Y1 of the corrugated fin 3 and its temperatures were measured at an outlet Y2 thereof.
  • each measured temperature is indicated by "TEMP (°C)"
  • each measured pressure is indicated by "PRES (Pa)”.
  • the temperature of the corrugated fin 3 of the first embodiment is the highest at the outlet Y2 compared to those of the corrugated fins A1 to A7.
  • the corrugated fin 3 of the first embodiment is superior to the corrugated fins A1 to A7 in the heat radiation performance.
  • the pressure at the inlet Y1 is low, thus a flow resistance being low.
  • the first embodiment can provide smooth flow of the cooling air CA.
  • the similar test was conducted by using a corrugated fin having first and second dimple portions shaped like a V-letter where the first and second dimple portions so that cooling air CA diffuses from the front side toward the rear side thereof, this test cannot produce favorable result.
  • the integrated heat exchanger of the first embodiment is constructed so that the core part 1a of the radiator 1 and the core part 2a of the condenser 2 are arranged near each other and that the corrugated fins 3 are piled up alternately with the tubes 1d and 2d of the core part 1a and the core part 2a to be shared therewith.
  • the first and second louvers 3a and 3b are formed, rising in the opposite directions, at the position of the corrugated fin 3 corresponding to the core part 2a of the condenser 2 and at the position thereof corresponding to the core part 1 of the radiator 1, respectively, and the first and second dimple portions 3c and 3d are provided between the core part 1a and the core part 2a. Therefore, the cooling air CA can be surely conducted to the second louvers 3b at the core part 1a side, which especially improves coolability of the radiator 1.
  • the first and second dimple portions 3c and 3d are projected in the directions where the cooling air CA passing through the first louvers 3a flows into the second louvers 3b at the downstream side. This enables the cooling air CA to hit the first and second dimple portions 3c and 3d to separate therefrom, then being well conducted to the second louvers 3b.
  • the projecting portion consists of the first and second dimple portions 3c and 3d that are arranged like the V-letter shape so that the cooling air CA converges from the upstream side of the cooling air CA toward downstream side.
  • they are arranged symmetrically relative to the central line Z1 extending in the longitudinal direction of the corrugated fin 3 at the central height thereof, and they have the linear portions 3e whose extended lines intersect with each other on the central line Z1. Therefore, they can be manufactured in a simple shape to converge the cooling air CA toward the downstream side.
  • the heat insulating portion 3i is press-formed to vertically zigzag connect portions of the corrugated fin 3, consisting of the first and second opening portions 3g and 3h provided so that they respectively extend from the top portion and the bottom portion of the folded portion of the corrugated fin 3 toward the central line Z1 to overlap with each other.
  • This improves the coolability of the radiator 1, suppressing the heat transfer from the radiator 1 to the condenser 2 to decrease deterioration in the coolability of the condenser 2.
  • a radiator 1 is independently used, where a core part 1a of the radiator 1 is equipped with a plurality of corrugated fins 20 only for the radiator 1.
  • the corrugated fin 20 for the core part 1a of the radiator 1 is projected toward an upstream side from the core part 1a, and this upstream projecting portion is formed with a first projecting portion 21 and a second projecting portion 22 that are arranged like a V-letter shape so that an interval between the first and second projecting portions 21 and 22 becomes narrower toward a downstream side.
  • each of the first and second projecting portions 21 and 22 consists of two dimple portions 23 and 24, formed in a quadrangular pyramid shape, which project in a direction where cooling air CA flows into louvers 3b of the corrugated fin 20 as shown in FIG. 19 .
  • An angle ⁇ between the first and second projecting portions 21 and 22 is set to be 90°.
  • the first and second projecting portions 21 and 22 may consist of more than two dimple portions, or they may employ the first and second dimple portions 3c and 3d of the first embodiment.
  • the sizes, shapes and angle ⁇ of the dimple portions 23 and 24, and a length of the upstream projecting portion of the corrugated fin 20 may be set appropriately.
  • corrugated fin 20 of the second embodiment is similar to that of the first embodiment, and its explanation is omitted.
  • the cooling air CA converges by the first and second projecting portions 21 and 22 to converge and flow downward, thus being surely conducted to the louvers 3b. This increases a heat exchange efficiency to improve coolability of the radiator 1.
  • the upstream projecting portion increases a heat radiation area and can conduct the cooling air CA to the louvers 3b.
  • a radiator 1 and a condenser 2 have a plurality of first corrugated fins 20 and a plurality of second corrugated fins 30, respectively.
  • the second corrugated fins 30 of a core part 2a of the condenser 2 project downward from the core part 2a to have downstream projecting portions so that their downstream end portions 30a are arranged near upstream end portions 20a of the second corrugated fins 20.
  • Each of the downstream projecting portions of the first corrugated fins 30 is formed with a first projecting portion 31 and a second projecting portion 32.
  • the first and second projecting portions 31 and 32 have shapes similar to those of the first projecting portion 21 and the second projecting portion 22 of the corrugated fin 20, and each of the first and second projecting portions 31 and 32 consists of two dimple portions 33 and 34.
  • each of the first and second projecting portions 21 and 22 formed on the second corrugated fins 20 consists of two dimple portions 23 and 24 similarly to those of the second embodiment.
  • the dimple portions 22, 23, 33 and 34 have the same shapes in this embodiment, they may have different shapes.
  • a distance between the downstream end portion 30a and the upstream end portion 20a may be set appropriately.
  • the radiator 1 has a pair of tanks 1b and 1c, on their upper portions and lower portions, which are respectively provided with four receiving brackets B1 that are shaped like an L-letter opening upward and project forward, while the condenser 2 has a pair of tanks 2b and 2c, on their upper portions and lower portions, which are respectively provided with four inserting brackets B2 that are shaped like a plate and project laterally outwardly.
  • the inserting brackets B2 of the condenser 2 are inserted from above into the brackets B1 of the radiator 1 to engage with each other, thereby integrally fixing the radiator 1 and the condenser 2 with each other.
  • downstream projecting portions of the corrugated fins 30 and the upstream projecting portions of the corrugated fins 20 increase heat radiation areas thereof, thus improving coolability of the radiator 1 and that of the condenser 2 and suppressing harmful effects due to heat transfer the radiator 1 and the condenser 2.
  • the cooling air surely converges toward the downstream side and is conducted to the louvers 3b by using the first and second projecting portions 31 and 32 of corrugated fins 30 of the condenser 2 and the first and second projecting portions 21 and 22 of the corrugated fins 20 of the radiator 1.
  • buckling of the upstream projecting portions of the corrugated fins 20 may occur due to contact with their peripheral parts, while, in the third embodiment, the upstream projecting portions of the corrugated fins 20 and the downstream projecting portions of the corrugated fms 30 are arranged so that the downward end portions 30a and the upstream end portions 20a are arranged near each other. Therefore, they are protected from the bucking.
  • the fin pitches and heights of the corrugate fins 20 and the corrugated fins 30 may be set to be different from each other, and accordingly they may be set appropriately in compliance with respective demands from heat radiation of the radiator 1 and the condenser 2.
  • a corrugated fin 3 has a first projecting portion 41 and a second projecting portion 42 formed to have curved portions instead of the liner portions 3e of the first embodiment so that the curved portions are bent to further depart from each other toward a downstream side
  • the first and second projecting portions 41 and 42 enable the cooling air to effectively converge toward the downstream side, and they enhance torsional rigidity of the corrugated fins 3.
  • louvers and tubes may be appropriately set in the number, length, thickness, angles, arrangement and so forth.
  • the heat insulating portion is not indispensable, and, as shown in FIG. 25 of a modification, they may be replaced by two louvers 50 and 51 connected at both end portions thereof that form openings therebetween. These louvers 50 and 51 can provide the similar effects.
  • a return louver 52 and third louvers 53 may be provided at the downstream side of the second louvers 3b so that the cooling air CA, passing through the second louvers 3b and changed its flow direction, changes again the flow direction by the third louvers 53.
  • the integrated heat exchanger of the present invention is available to those used for motor vehicles and others as long as it cools cooling medium flowing through a core part by cooling air through corrugated fins.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP07707712A 2006-02-01 2007-01-30 Échangeur thermique pour véhicule Withdrawn EP1985957A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006025035 2006-02-01
PCT/JP2007/051494 WO2007088850A1 (fr) 2006-02-01 2007-01-30 Échangeur thermique pour véhicule

Publications (1)

Publication Number Publication Date
EP1985957A1 true EP1985957A1 (fr) 2008-10-29

Family

ID=38327422

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07707712A Withdrawn EP1985957A1 (fr) 2006-02-01 2007-01-30 Échangeur thermique pour véhicule

Country Status (4)

Country Link
US (1) US20090301696A1 (fr)
EP (1) EP1985957A1 (fr)
CN (1) CN101379360A (fr)
WO (1) WO2007088850A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3279598A4 (fr) * 2015-03-30 2019-01-02 Mitsubishi Electric Corporation Échangeur de chaleur et climatiseur
EP3483544A4 (fr) * 2016-07-07 2019-10-09 Mitsubishi Electric Corporation Échangeur de chaleur
EP3435000B1 (fr) * 2016-03-21 2021-03-31 Danfoss Micro Channel Heat Exchanger (Jiaxing) Co. Ltd. Échangeur de chaleur et système de climatisation

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2897078B1 (fr) 2006-02-09 2011-08-19 Arjowiggins Materiau en feuille comportant au moins un filigrane avec une nuance coloree.
JP4970022B2 (ja) * 2006-08-02 2012-07-04 カルソニックカンセイ株式会社 複合型熱交換器及び複合型熱交換器システム
JP5712777B2 (ja) * 2011-05-10 2015-05-07 日本軽金属株式会社 アルミニウム又はアルミニウム合金からなる熱交換器
US9109841B2 (en) * 2011-10-06 2015-08-18 Halla Visteon Climate Control Corporation Air to refrigerant heat exchanger with phase change material
US20150377561A1 (en) * 2013-02-13 2015-12-31 Carrier Corporation Multiple Bank Flattened Tube Heat Exchanger
CN205352165U (zh) * 2015-12-16 2016-06-29 杭州三花微通道换热器有限公司 换热器芯体和具有它的换热器
CN110300879B (zh) * 2017-02-21 2020-11-03 三菱电机株式会社 热交换器及空气调节机
CN109209610A (zh) * 2017-07-07 2019-01-15 天津市金博阳热传电子技术有限公司 高效节能汽车散热器
KR102518597B1 (ko) * 2018-10-30 2023-04-05 현대자동차 주식회사 차량용 쿨링모듈
JP2022534740A (ja) * 2019-05-31 2022-08-03 杭州三花▲微▼通道▲換▼▲熱▼▲器▼有限公司 扁平管、マルチチャネル熱交換器及び空調冷却システム

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0645182Y2 (ja) * 1988-12-15 1994-11-16 カルソニック株式会社 コルゲートフィン
JP4482991B2 (ja) * 1999-12-14 2010-06-16 株式会社デンソー 複式熱交換器
JP4173959B2 (ja) * 2001-05-21 2008-10-29 カルソニックカンセイ株式会社 一体型熱交換器のコア部構造
JP2005257104A (ja) * 2004-03-09 2005-09-22 Calsonic Kansei Corp 一体型熱交換器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007088850A1 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3279598A4 (fr) * 2015-03-30 2019-01-02 Mitsubishi Electric Corporation Échangeur de chaleur et climatiseur
EP3435000B1 (fr) * 2016-03-21 2021-03-31 Danfoss Micro Channel Heat Exchanger (Jiaxing) Co. Ltd. Échangeur de chaleur et système de climatisation
EP3483544A4 (fr) * 2016-07-07 2019-10-09 Mitsubishi Electric Corporation Échangeur de chaleur

Also Published As

Publication number Publication date
CN101379360A (zh) 2009-03-04
US20090301696A1 (en) 2009-12-10
WO2007088850A1 (fr) 2007-08-09

Similar Documents

Publication Publication Date Title
EP1985957A1 (fr) Échangeur thermique pour véhicule
US6213196B1 (en) Double heat exchanger for vehicle air conditioner
US7182128B2 (en) Heat exchanger tube having strengthening deformations
JP4117429B2 (ja) 熱交換器用フィン
JP4379967B2 (ja) 複式熱交換器
US7303003B2 (en) Heat exchanger
US7938172B2 (en) Heat exchanger
EP1696195B1 (fr) Refroidisseur d'huile refroidi par air
EP2645041A2 (fr) Tube pour échangeur de chaleur et échangeur de chaleur
JP4946348B2 (ja) 空気熱交換器
US6209628B1 (en) Heat exchanger having several heat exchanging portions
US6889757B2 (en) Core structure of integral heat-exchanger
US8069911B2 (en) Radiator with built-in oil cooler
EP1195566B1 (fr) Echangeur de chaleur comportant plusieurs portions d'échange de chaleur
JP2007232356A (ja) 車両用熱交換器
US6942024B2 (en) Corrugated heat exchange element
US20070068662A1 (en) Heat exchanger
EP3623738A1 (fr) Tube d'échangeur de chaleur
US20070289728A1 (en) Heat exchanger and mounting structure of the same
JP5187047B2 (ja) 熱交換器用チューブ
JPH0976734A (ja) 車載用凝縮器
JP4513207B2 (ja) 空気熱交換器
JP2006112731A (ja) 細径多管式熱交換器の細径伝熱管ユニット
JP2005090946A (ja) 熱交換器およびエバポレータ
JP5525805B2 (ja) 熱交換器

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20080829

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR GB

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20100211