US20090133860A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US20090133860A1
US20090133860A1 US12/313,165 US31316508A US2009133860A1 US 20090133860 A1 US20090133860 A1 US 20090133860A1 US 31316508 A US31316508 A US 31316508A US 2009133860 A1 US2009133860 A1 US 2009133860A1
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United States
Prior art keywords
fin
fluid
portions
flow direction
tube
Prior art date
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Abandoned
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US12/313,165
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English (en)
Inventor
Masaki Harada
Sumio Susa
Haruhiko Watanabe
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Denso Corp
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Denso Corp
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Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HARADA, MASAKI, SUSA, SUMIO, WATANABE, HARUHIKO
Publication of US20090133860A1 publication Critical patent/US20090133860A1/en
Abandoned legal-status Critical Current

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    • 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
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0082—Charged air coolers

Definitions

  • the present invention relates to a heat exchanger.
  • the heat exchanger can be suitably used as an intercooler for cooling intake air to be supplied to an internal combustion engine, for example.
  • a heat exchanger such as an intercooler performs heat exchange between cooling air and intake air to be drawn into an internal combustion engine so as to cool the intake air (for example, JP-A-2006-90305).
  • the intercooler includes inner fins inserted into tubes in which the intake air flows, thereby promoting heat exchange between the intake air and the cooling air.
  • the inner fins have generally the same shape, that is, the same specification from an intake air inlet side of the tubes to an intake air outlet side thereof in the intercooler.
  • FIG. 8 shows a relationship between an intake air temperature Tg in the tube and a distance H from an intake air inlet of the tube in the intercooler, according to experiments by the inventors of the present application.
  • FIG. 8 shows a relationship between an intake air temperature Tg in the tube and a distance H from an intake air inlet of the tube in the intercooler, according to experiments by the inventors of the present application.
  • high-temperature intake air flowing from the intake air inlet of the tube into the tube is drastically cooled in the tube, resulting in a large difference in temperature of the intake air between the intake air inlet side and the intake air outlet side of the tube. That is, the temperature Tg of the intake air is rapidly reduced from the intake air inlet of the tube as the distance H from the intake air inlet of the tube increases.
  • FIG. 9 shows a relationship between a flow velocity Vg of intake air and the distance H from the intake air inlet of the tube in the intercooler, according to experiments by the inventors of the present application.
  • the flow velocity Vg of intake air flowing from the intake air inlet of the tube into the tube has a large difference between the intake air inlet side and the intake air outlet side of the tube. That is, the flow velocity Vg of the intake air is rapidly reduced from the intake air inlet of the tube as the distance H from the intake air inlet of the tube increases.
  • the use of the inner fins with the same specification from the intake air inlet side to the outlet side as described above may drastically increase the loss in pressure at the intake air inlet side, resulting in reduction in heat exchange performance of the whole intercooler.
  • the temperature Tg of intake air becomes very low on the intake air outlet side of the tube, as compared to the intake air inlet side of the tube.
  • the difference in temperature between the intake air and the cooling air becomes small on the intake-air outlet side, and thereby it may be difficult to exchange heat between the intake air and the cooling air.
  • the use of the inner fins having the same specification from the intake air inlet side to the intake air outlet side described above may be difficult to effectively perform heat exchange at the intake air outlet side of the tube.
  • a heat exchanger includes a tube having therein a flow passage through which a first fluid flows, and an inner fin provided in the tube.
  • the tube is adapted to exchange heat between the first fluid and a second fluid flowing through an outer periphery of the tube, and the inner fin is located in the tube to promote the heat exchange between the first fluid and the second fluid.
  • the inner fin is configured to divide the flow passage in the tube into a plurality of flow paths.
  • the inner fin includes a plurality of fin portions with different specifications, and the fin portions are arranged in series with respect to a flow direction of the first fluid.
  • the fin portion with the smallest flowing resistance of the first fluid among the plurality of fin portions is arranged on an upstream side of the flow direction of the first fluid with respect to at least an another fin portion. Accordingly, the heat exchange performance in the heat exchanger can be effectively increased.
  • the fin portion with the smallest flowing resistance of the first fluid is arranged on the upstream side of the flow direction of the first flow with respect to at least an another fin portion
  • the phrase means not only that the fin portion with the smallest flowing resistance of the first fluid is arranged only on the upstream side of the first fluid flow with respect to the other fin portions, but also the following case. That is, the phrase also means that the fin portion with the smallest flowing resistance of the first fluid is arranged on the upstream side of the first fluid flow, and the fin portion with the smallest flowing resistance of the first fluid may be also arranged on the downstream side of the first fluid flow with respect to the other fin portion.
  • the fin portion with the smallest flowing resistance of the first fluid is arranged on the upstream side of the flow direction of the first fluid with respect to at least an another fin portion with a flowing resistance of the first fluid larger than the smallest flowing resistance, the shape or the like of the other fin portion(s) can be suitably changed.
  • the fin portion with the largest flowing resistance of the first fluid among the plurality of fin portions may be arranged on a downstream side of the flow direction of the first fluid with respect to the other fin portion.
  • the fin portions may be arranged symmetrically with respect to a center line of the inner fin in the flow direction of the first fluid.
  • the fin portions may be constructed of at least first and second different kinds of fin portions.
  • the plurality of fin portions may include a straight fin portion and a louver fin portion, and the straight fin portion may be arranged on an upstream side of the flow direction of the first fluid with respect to the louver fin portion.
  • the straight fin portion may have a plurality of wall surfaces extending linearly in the flow direction of the first fluid, and the wall surfaces may be configured to divide the flow passage of the tube into the plurality of flow paths.
  • the louver fin portion may include a plurality of flat portions substantially in parallel to the flow direction of the first fluid, and a plurality of louvers may be provided at the flat portions along the flow direction of the first fluid.
  • the louvers may be formed by cutting and raising a part of the flat portion.
  • the plurality of fin portions may include a straight fin portion and an offset fin portion, and the straight fin portion may be arranged on an upstream side of the flow direction of the first fluid with respect to the offset fin portion.
  • straight fin portion has a plurality of wall surfaces extending linearly in the flow direction of the first fluid, and the wall surfaces are configured to divide the flow passage of the tube into the plurality of flow paths.
  • the offset fin portion including wall portions are arranged in a zigzag shape along the flow direction of the first fluid, and the wall portions are configured to divide the flow passage of the tube into the plurality of flow paths.
  • the inner fin may be a louver fin that includes a plurality of flat portions substantially in parallel to the flow direction of the first fluid, and a plurality of louvers provided at the flat portions along the flow direction of the first fluid.
  • the fin portions are configured to have different louver pitches in the louvers, and the fin portion with the largest louver pitch among the plurality of fin portions is arranged on an upstream side of the flow direction of the first fluid with respect to at least an another fin portion.
  • the fin portions may have different fin pitches.
  • the fin portion with the largest fin pitch among the fin portions is arranged on an upstream side of the flow direction of the first fluid, with respect to at least an another fin portion.
  • the fin portions may be continuously arranged in the flow direction of the first fluid such that flow resistances of the first fluid in the fin portions are increased as toward downstream in the flow direction of the first fluid.
  • the first fluid flowing in the tube generally may have a temperature higher than that of the second fluid.
  • the heat exchanger may include a plurality of the tubes stacked in a stacking direction, and a plurality of outer fins each of which is located between adjacent tubes.
  • the first fluid is an intake air to be supplied to an internal combustion engine
  • the second fluid is a cooling air.
  • FIG. 1 is a front view of an intercooler according to a first embodiment of the present invention
  • FIG. 2 is a cross sectional view taken along the line I-I in FIG. 1 ;
  • FIG. 3 is a cross sectional view taken along the line II-II in FIG. 2 ;
  • FIG. 4 is an enlarged perspective view showing an inner fin in the first embodiment
  • FIG. 5 is a sectional view showing an inner fin when being viewed in a stacking direction of tubes according to a second embodiment of the present invention
  • FIG. 6 is an enlarged perspective view showing a third fin portion of the inner fin in the second embodiment
  • FIG. 7 is a sectional view showing an inner fin when being viewed in a stacking direction of tubes according to a third embodiment of the present invention.
  • FIG. 8 is a graph showing a relationship between an intake air temperature Tg in a tube and a distance H from an intake air inlet of the tube in an intercooler;
  • FIG. 9 is a graph showing a relationship between a flow velocity Vg of intake air in a tube and a distance H from an intake air inlet of the tube in an intercooler.
  • a first embodiment of the present invention will be described below with reference to FIGS. 1 to 4 .
  • a heat exchanger according to the first embodiment of the present invention is typically used for an intercooler.
  • the intercooler is configured to perform heat exchange between outside air (cooling air) and intake air for combustion to be supplied into an internal combustion engine, thereby to cool the intake air.
  • the intake air is an example of a first fluid of the present invention
  • the cooling air is an example of a second fluid of the present invention.
  • a core portion 1 of the intercooler includes a plurality of stacked flat tubes 2 each having a flow passage formed therein for allowing intake air to flow therethrough, inner fins 3 disposed within the flat tubes 2 , and outer fins 4 each of which is disposed between the stacked flat tubes 2 .
  • the flat tubes 2 are stacked in a tube stacking direction that is perpendicular to the tube longitudinal direction and a flow direction of the cooling air, as shown in FIGS. 1 and 2 .
  • the tube 2 is made of copper or stainless material, and both the inner fin 3 and the outer fin 4 are made of copper, for example.
  • the outer fin 4 is formed in a wave-like shape (corrugated shape) to be bonded to the outer wall surface of the tube 2 , and adapted to promote heat exchange between cooling air flowing through between the tubes 2 and intake air flowing in the tubes 2 .
  • the outer fin 4 is provided with louvers 4 a formed by cutting and raising a part of the fin to have a louver window shape in order to prevent disturbance of air flow and growing of a temperature interface layer.
  • the inner fin 3 is formed into a wave-like shape (corrugated shape) to be bonded to the inner wall surface of the tube 2 , and adapted to promote heat exchange between the cooling air and intake air.
  • the inner fin 3 includes a plurality of wall surfaces 3 a each of which extends to connect opposite wall surfaces of the tubes 2 .
  • a flow passage in the tube 2 is divided into a plurality of thin wall flow paths 20 by the wall surfaces 3 a of the inner fin 3 , as shown in FIGS. 2 and 4 .
  • the detailed structure of the inner fin 3 will be described later.
  • Header tanks 5 and 6 are provided on both end sides of the tubes 2 in the tube longitudinal direction, to extend in the stacking direction of the tubes 2 . Each of the header tanks 5 and 6 is located to communicate with the respective tubes 2 .
  • One header tank 5 has an inlet 50 connected to a supercharger, from which intake air pressure-fed is introduced. The intake air flowing into the header tank 5 from the inlet 50 is distributed among and flows into the respective tubes 2 .
  • the other header tank 6 has an outlet 60 connected to an intake port of the internal combustion engine.
  • the other header tank 6 is adapted to collect and recover intake air flowing from the tubes 2 , so as to feed the air to an intake port of the internal combustion engine.
  • Both header tanks 5 and 6 can be made of a metal such as copper.
  • FIG. 2 is a cross sectional view taken along the line I-I in FIG. 1
  • FIG. 3 is a cross sectional view taken along the line II-II in FIG. 2
  • FIG. 4 is an enlarged perspective view showing the inner fin 3 in the first embodiment.
  • the inner fin 3 of the present embodiment shown in FIGS. 3 and 4 is formed by applying a roller forming method to a thin metallic material.
  • the inner fin 3 includes the wall surfaces 3 a extending substantially in parallel to the flow direction of the intake air in the tube 2 , and top parts 3 b connecting the adjacent wall surfaces 3 a .
  • the inner fin 3 is formed in a corrugated shape when being viewed from the flow direction of the intake air.
  • a plurality of the wall surfaces 3 a are arranged in the flow direction of cooling air (e.g., in the width direction of the tube 2 ), as shown in FIG. 2 .
  • the wall surface 3 a may be a flat surface as shown in FIG. 4 .
  • the inner fin 3 of the present embodiment includes two different kinds of fin portions 31 and 32 . These two fin portions 31 and 32 are arranged continuously in series in the flow direction of the intake air. One of the two fin portions 31 and 32 which is arranged on the upstream side in the intake-air flow direction is hereinafter referred to as the first fin portion 31 , whereas the other arranged on the downstream side in the intake-air flow direction is hereinafter referred to as the second fin portion 32 . In the present embodiment, the first fin portion 31 and the second fin portion 32 are continuously formed to be integrated as one inner fin.
  • the second fin portion 32 is a louver fin having a plurality of louvers 321 .
  • the wall surface 3 a of the second fin portion 32 is integrally formed with the louvers 321 each of which has a louver window shape by cutting and raising a part of the wall surface 3 a .
  • Each louver 321 is formed by being bent and twisted at a predetermined twist angle with respect to the wall surface 3 a as being viewed in the stacking direction of the tubes 2 .
  • a plurality of louvers 321 are provided in the wall surface 3 a along the flow direction of the intake air.
  • a louver-to-louver passage 322 is formed between the adjacent louvers 321 .
  • the second fin portion 32 of the present embodiment includes turning portions 323 each reversing the twisting direction of the louver 321 , as shown in FIG. 3 .
  • Each turning portion 323 is positioned at a center portion of the second louver portion 32 in the flow direction of the intake air.
  • the first fin portion 31 does not have any louver 321 , and is a straight fin including a wall surface 30 linearly extending in the flow direction of the intake air.
  • a flowing resistance of intake air in the first fin portion 31 (hereinafter referred to as an “air flowing resistance”) is smaller than that in the second fin portion 32 with the louvers 321 .
  • the intake air inlet side that is, the most upstream side of the intake air flow in the tube 2 has an intake air temperature higher than that of other parts thereof, thereby making a flow velocity of intake air on the inlet side higher than that of the other parts. For this reason, providing the inner fin 3 in the tube 2 may lead to the largest loss of pressure on the intake air inlet side.
  • the first fin portion 31 which is the straight fin having the small air flowing resistance is disposed on the intake air inlet side in the tube 2 , and thereby it can reduce the loss in pressure on the intake air inlet side of the tube 2 .
  • the heat exchange performance on the intake air inlet side of the tube 2 may be relatively reduced in the intercooler 1 .
  • the intake air inlet side of the tube 2 can sufficiently have a difference in temperature between the intake air and cooling air, and thereby it can suppress the reduction in heat exchange performance on the intake air inlet side of the tube 2 to a very small level. That is, the reduction in heat exchange performance of the intake air inlet side of the tube 2 due to reduction in heat exchange performance of the first fin portion 31 is very small, as compared to the increase of the heat exchange performance of the entire intercooler due to reduction in loss of pressure on the intake air inlet side of the tube 2 .
  • the shape of the first fin portion 31 is not limited to the straight line shape shown in FIG. 1 , but may be suitably changed.
  • a first fin portion 31 having an air flowing resistance smaller than that of the second fin portion 32 can be arranged on the intake air inlet side within the tube 2 . Even in this case, the heat exchange performance of the entire heat exchanger can be effectively improved.
  • the intake air outlet side that is, the most downstream side of the intake air flow, in the tube 2 has an intake air temperature lower than that of the other parts thereof, resulting in a small difference in temperature between the intake air and the cooling air, making it difficult to perform heat exchange.
  • the second fin portion 32 which is a louver fin having a large air flowing resistance (or having high heat exchange performance) is disposed on the intake air outlet side of the tube 2 , and thereby it can improve the heat exchange performance on the intake air outlet side of the tube 2 .
  • the air flowing resistance is increased on the intake air outlet side of the tube 2 .
  • the intake air temperature on the intake air output side of the tube 2 is low and thus the flow velocity of the intake air is low, so that it can suppress the amount of increase in loss of pressure on the intake air output side of the tube 2 to a very small level. That is, the reduction in heat exchange performance of the entire intercooler due to an increase in loss of pressure on the intake air outlet side of the tube 2 is very small, as compared to improvement of the heat exchange performance by disposing the second fin portion 32 having the large air flowing resistance on the intake air output side of the tube 2 .
  • the second fin portion 32 having the air flowing resistance larger than that of the first fin portion 31 is disposed on the intake air outlet side of the tube 2 , it can further effectively improve the heat exchange performance in the entire heat exchanger. That is, the second fin portion 32 is configured to have the higher heat exchange performance between the intake air and the cooling air in the intercooler 1 , than that of the first fin portion 31 , the shapes of the first fin portion 31 and the second fin portion 32 can be suitably changed.
  • FIG. 5 is a sectional view of the inner fin 3 of the second embodiment when being viewed in the stacking direction of the tubes 2 .
  • FIG. 5 of the second embodiment is a drawing corresponding to FIG. 3 .
  • an inter fin 3 of the present embodiment includes three different kinds of fin portions 31 to 33 .
  • the three fin portions 31 to 33 namely, the first fin portion 31 , the third fin portion 33 , and the second fin portion 32 are arranged continuously in that order from the upstream side of the intake air flow.
  • the first fin portion 31 is a straight fin similar to that in the first embodiment.
  • the second fin portion 32 is a louver fin similar to that in the first embodiment.
  • FIG. 6 is an enlarged perspective view showing the third fin portion 33 in the second embodiment.
  • the third fin portion 33 of the present embodiment has a corrugated sectional shape in cross section substantially perpendicular to the flow direction of the intake air, or when being viewed in the flow direction of the intake air.
  • the sectional shape is formed by alternately positioning and bending convex portions 331 on one side and on the other side.
  • the third fin portion 33 includes cut-up portions 332 formed by partially cutting and raising the fin 33 in the flow direction of the intake air.
  • the third fin portion 33 is an offset fin in which wave-shaped portions formed by the cut-up portions 332 are offset by adjacent wave-shaped portions in the intake-air flowing direction when being viewed in the intake-air flowing direction.
  • the convex portions 331 of the third fin portion 33 are located in contact with the inner wall surface of the tube 2 .
  • the inside of the tube 2 is divided into a plurality of flow paths by the third fin portion 33 .
  • the flow paths divided in the tube 2 are partially offset in the intake-air flowing direction. That is, wall portions 333 for dividing the inside of the tube 2 into the flow paths are arranged in a zigzag shape along the intake-air flowing direction.
  • the concave portions 331 are adjacent to each other on the same side, that is, on one side and on the other side, in the intake-air flowing direction.
  • the concave portions 31 are positioned so as to be offset from each other.
  • the first fin portion 31 serving as the straight fin has the smaller air flowing resistance than that of each of the second fin portion 32 serving as the louver fin and the third fin portion 33 serving as the offset fin.
  • the first fin portion 31 has the smallest air flowing resistance.
  • the second fin portion 32 has the higher heat exchange performance, but the larger air flowing resistance, as compared to that of the third fin portion 33 . That is, the first fin portion 31 is configured to have an air flowing resistance, the third fin portion 33 is configured to have an air flowing resistance larger than that of the first fin portion 31 , and the second fin portion 32 is configured to have an air flowing resistance larger than that of the third fin portion 33 .
  • FIG. 7 is a sectional view showing an inner fin 3 of the third embodiment when being viewed in the stacking direction of tubes 2 .
  • FIG. 7 is a diagram corresponding to the diagram of FIG. 3 .
  • the inner fin 3 of the present embodiment includes two first fin portions 31 each of which is a straight fin similar to that of the first embodiment, and a second fin portion 32 which is a louver fin similar to that of the first embodiment.
  • the two first fin portions 31 are disposed one by one on the upstream and downstream sides of the second fin portion 32 in the flow direction of intake air.
  • the second fin portion 31 is disposed between the two first fin portions 31 in the flow direction of the intake air.
  • the two first fin portions 31 may be set to have substantially the same length in the flow direction of the intake air.
  • the second fin portion 32 has substantially a symmetric shape with respect to a center line L 1 in the intake-air flowing direction.
  • the inner fin 3 of the present embodiment has substantially a symmetric shape with respect to a center line L 2 of the entire inner fin 3 in the intake-air flowing direction. That is, the first and second fin portions 31 and 32 are disposed so as to be symmetrical to each other with respect to the center line L 2 of the inner fin 3 in the intake-air flowing direction.
  • the center line L 1 of the second fin portion 32 in the intake-air flowing direction is substantially the same as the center line L 2 of the inner fin 3 in the intake-air flowing direction.
  • the intercooler with this arrangement can prevent the wrong assembly of the inner fin 3 to the tube 2 , while obtaining the same effects as those of the first embodiment.
  • the different kinds of fin portions 31 to 33 are employed as fin portions with different specifications, the present invention is not limited thereto.
  • the fin portions with different specifications may be constructed by setting the same kind of fins to have different respective fin pitches.
  • a fin portion with the largest fin pitch among the fin portions is disposed on the upstream side of the intake-air flowing direction with respect to at least the other fin portions, thereby reducing the loss in pressure on the intake air inlet side of the tube 2 .
  • the entire intercooler can have an improved heat exchange performance.
  • Fin portions with different specifications may be constructed by employing the louver fin as the inner fin 3 and by setting the louver fins to have different louver pitches.
  • a fin portion with the largest louver pitch among the fin portions is disposed on the upstream side of the intake-air flowing direction with respect to at least the other fin portions, so as to reduce the loss in pressure on the intake air inlet side of the tube 2 .
  • the entire intercooler can have improved heat exchange performance.
  • louver fin is used as the second fin 32
  • the present invention is not limited thereto.
  • an offset fin may be used as the second fin 32 .
  • the first fin portion 31 , the third fin portion 33 , and the second fin portion 32 are arranged in that order from the upstream side of the intake air flow.
  • the first fin portion 31 , the second fin portion 32 , and the third fin portion 33 may be arranged in that order from the upstream side of the intake air flow.
  • a heat exchanger includes a tube 2 having therein a flow passage through which a first fluid flows, and an inner fin 3 provided in the tube 2 .
  • the tube 2 is adapted to exchange heat between the first fluid and a second fluid flowing through an outer periphery of the tube 2
  • the inner fin 3 is located in the tube 2 to promote the heat exchange between the first fluid and the second fluid.
  • the inner fin 3 is configured to divide the flow passage in the tube 2 into a plurality of flow paths 20 .
  • the inner fin 3 includes a plurality of fin portions ( 31 , 32 , 33 ) with different specifications, and the fin portions ( 31 , 32 , 33 ) are arranged in series with respect to a flow direction of the first fluid.
  • the fin portion ( 31 ) with the smallest flowing resistance of the first fluid among the plurality of fin portions ( 31 , 32 , 33 ) is arranged on an upstream side of the flow direction of the first fluid with respect to at least an another fin portion ( 32 , 33 ). Accordingly, the heat exchange performance in the heat exchanger can be effectively increased.
  • the fin portion ( 31 ) with the smallest flowing resistance of the first fluid is arranged on the upstream side of the flow direction of the first flow with respect to at least an another fin portion ( 32 , 33 )” as used herein means not only that the fin portion ( 31 ) with the smallest flowing resistance of the first fluid is arranged only on the upstream side of the first fluid flow with respect to the other fin portions ( 32 , 33 ), but also the following case.
  • the phrase also means that the fin portion ( 31 ) with the smallest flowing resistance of the first fluid is arranged on the upstream side of the first fluid flow, and the fin portion ( 31 ) with the smallest flowing resistance of the first fluid may be also arranged on the downstream side of the first fluid flow with respect to the other fin portions ( 32 , 33 ).
  • the fin portion ( 31 ) with the smallest flowing resistance of the first fluid is arranged on the upstream side of the flow direction of the first fluid with respect to at least an another fin portion ( 32 , 33 ) with a flowing resistance of the first fluid larger than the smallest flowing resistance
  • the specification such as the shape of the other fin portion(s) ( 32 , 33 ) can be suitably changed.
  • the fin portion ( 31 ) with the largest flowing resistance of the first fluid among the plurality of fin portions ( 31 , 32 , 33 ) may be arranged on a downstream side of the flow direction of the first fluid with respect to the other fin portion ( 32 , 33 ).
  • the fin portions ( 31 , 32 , 33 ) may be arranged symmetrically with respect to a center line L 2 of the inner fin in the flow direction of the first fluid.
  • the fin portions ( 31 , 32 , 33 ) may be constructed of at least first and second different kinds of fin portions.
  • the plurality of fin portions ( 31 , 32 , 33 ) may include a straight fin portion 31 and a louver fin portion 32 , and the straight fin portion 31 is arranged on an upstream side of the flow direction of the first fluid with respect to the louver fin portion 32 .
  • the straight fin portion 31 may have a plurality of wall surfaces 30 extending linearly in the flow direction of the first fluid, and the wall surfaces 30 may be configured to divide the flow passage of the tube into the plurality of flow paths.
  • the louver fin portion may include a plurality of flat portions 3 a substantially in parallel to the flow direction of the first fluid, and a plurality of louvers 321 may be provided at the flat portions 3 a along the flow direction of the first fluid.
  • the louvers 321 may be formed by cutting and raising a part of the flat portion.
  • the plurality of fin portions may include a straight fin portion 31 and an offset fin portion 33 , and the straight fin portion 31 may be arranged on an upstream side of the flow direction of the first fluid with respect to the offset fin portion 33 .
  • the straight fin portion 31 has a plurality of wall surfaces 30 extending linearly in the flow direction of the first fluid, and the wall surfaces 30 are configured to divide the flow passage of the tube 2 into the plurality of flow paths.
  • the offset fin portion 33 including wall portions 333 are arranged in a zigzag shape along the flow direction of the first fluid, and the wall portions 333 are configured to divide the flow passage of the tube 2 into the plurality of flow paths.
  • the inner fin may be a single louver fin including a plurality of flat portions 3 a substantially in parallel to the flow direction of the first fluid, and a plurality of louvers 321 provided at the flat portions 3 a along the flow direction of the first fluid.
  • the fin portions are configured to have different louver pitches in the louvers 321 , and the fin portion with the largest louver pitch among the plurality of fin portions 321 is arranged on an upstream side of the flow direction of the first fluid with respect to at least an another fin portion.
  • the fin portions may have different fin pitches.
  • the fin portion with the largest fin pitch among the fin portions is arranged on an upstream side of the flow direction of the first fluid, with respect to at least an another fin portion.
  • the fin portions ( 31 , 32 , 33 ) may be continuously arranged in the flow direction of the first fluid such that flow resistances of the first fluid in the fin portions ( 31 , 32 , 33 ) are increased as toward downstream in the flow direction of the first fluid.
  • the first fluid flowing in the tube 2 generally may have a temperature higher than that of the second fluid.
  • the first fluid is an intake air to be supplied to an internal combustion engine
  • the second fluid is a cooling air (i.e., outside air).

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US12/313,165 2007-11-22 2008-11-18 Heat exchanger Abandoned US20090133860A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007-303289 2007-11-22
JP2007303289A JP4674602B2 (ja) 2007-11-22 2007-11-22 熱交換器

Publications (1)

Publication Number Publication Date
US20090133860A1 true US20090133860A1 (en) 2009-05-28

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US12/313,165 Abandoned US20090133860A1 (en) 2007-11-22 2008-11-18 Heat exchanger

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Country Link
US (1) US20090133860A1 (zh)
JP (1) JP4674602B2 (zh)
CN (1) CN101441041B (zh)
DE (1) DE102008057334A1 (zh)

Cited By (18)

* Cited by examiner, † Cited by third party
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US20100300647A1 (en) * 2009-05-28 2010-12-02 Hans-Ulrich Steurer Heat exchanger
US20120024511A1 (en) * 2010-07-27 2012-02-02 Denso Corporation Intercooler
CN103061867A (zh) * 2012-12-20 2013-04-24 华南理工大学 一种气液式中冷器
CN103061866A (zh) * 2012-12-20 2013-04-24 华南理工大学 一种风冷式中冷器
GB2500871A (en) * 2012-04-05 2013-10-09 Ford Global Tech Llc An air to liquid heat exchanger having a tapered fin and tube block
US9038607B2 (en) 2013-02-06 2015-05-26 Ford Global Technologies, Llc Air cooler and method for operation of an air cooler
WO2015168234A1 (en) * 2014-04-29 2015-11-05 Carrier Corporation Improved heat exchanger
EP3015808A4 (en) * 2013-06-28 2016-07-27 Mitsubishi Heavy Ind Ltd HEAT EXCHANGERS, HEAT EXCHANGE STRUCTURE AND HEAT EXCHANGER RUBBER
US20160313070A1 (en) * 2014-02-10 2016-10-27 Mitsubishi Heavy Industries Automotive Thermal Systems Co., Ltd. Heat-exchanger offset fin and refrigerant heat-exchanger utilizing same
WO2017111750A1 (en) * 2015-12-25 2017-06-29 Kale Oto Radyator Sanayi Ve Ticaret Anonim Sirketi Turbulator with triangular airfoils increasing the performance of engine intercoolers
US10094624B2 (en) 2016-01-08 2018-10-09 Hanon Systems Fin for heat exchanger
US20180306101A1 (en) * 2017-04-25 2018-10-25 GM Global Technology Operations LLC Transitional Turbulator
US10352599B2 (en) * 2012-04-02 2019-07-16 Denso Corporation Evaporator
US10655530B2 (en) 2016-02-12 2020-05-19 Denso Corporation Intercooler
US11009300B2 (en) 2017-02-21 2021-05-18 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
EP4023988A1 (en) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Heat exchanger
EP4023995A1 (en) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Heat exchanger
US20230042424A1 (en) * 2020-01-03 2023-02-09 Valeo Systemes Thermiques Tube heat exchanger having spacers

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JP2010096449A (ja) * 2008-10-17 2010-04-30 Denso Corp 熱交換器
JP5387436B2 (ja) * 2010-02-17 2014-01-15 株式会社デンソー 熱交換器
JP2012067955A (ja) * 2010-09-22 2012-04-05 Hino Motors Ltd 熱交換器及びそれを用いたエンジンの吸気冷却装置
JP6531357B2 (ja) * 2014-07-16 2019-06-19 いすゞ自動車株式会社 コルゲートフィン式熱交換器
JP6409793B2 (ja) * 2016-02-11 2018-10-24 株式会社デンソー インタークーラ
JP2018169073A (ja) * 2017-03-29 2018-11-01 株式会社デンソー 熱交換器
CN109026350B (zh) * 2018-09-29 2023-09-08 吉林大学 一种带有展向涡生成器的车用管片式风冷中冷器
CN112013695A (zh) * 2020-06-10 2020-12-01 湖北雷迪特冷却系统股份有限公司 一种非均匀波距结构芯体组件

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US140914A (en) * 1873-07-15 Improvement in rotary steam-engines
US4049051A (en) * 1974-07-22 1977-09-20 The Garrett Corporation Heat exchanger with variable thermal response core
US4676304A (en) * 1985-01-15 1987-06-30 Sanden Corporation Serpentine-type heat exchanger having fin plates with louvers
US20030079868A1 (en) * 1996-12-18 2003-05-01 Samy Bouzida Metallic cooling fin for a heat exchanger, especially for a motor vehicle
US6209628B1 (en) * 1997-03-17 2001-04-03 Denso Corporation Heat exchanger having several heat exchanging portions
US6253840B1 (en) * 1998-02-10 2001-07-03 Denso Corporation Refrigerant evaporator including refrigerant passage with inner fin
US20060131006A1 (en) * 2004-12-17 2006-06-22 Viktor Brost Heat exchanger and ribs
US7468693B1 (en) * 2005-05-26 2008-12-23 Trimble Navigation Limited GPS rover station providing a high integrity position with a selected error
US7336225B1 (en) * 2005-06-07 2008-02-26 Trimble Navigation Limited Synthetic phase processor for controlling accuracy of high integrity GPS positions

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100300647A1 (en) * 2009-05-28 2010-12-02 Hans-Ulrich Steurer Heat exchanger
US10254056B2 (en) * 2009-05-28 2019-04-09 Mahle International Gmbh Heat exchanger
US20120024511A1 (en) * 2010-07-27 2012-02-02 Denso Corporation Intercooler
US10352599B2 (en) * 2012-04-02 2019-07-16 Denso Corporation Evaporator
GB2500871A (en) * 2012-04-05 2013-10-09 Ford Global Tech Llc An air to liquid heat exchanger having a tapered fin and tube block
RU2633280C2 (ru) * 2012-04-05 2017-10-11 Форд Глобал Технолоджис, ЛЛК Воздушно-жидкостный теплообменник и система двигателя
GB2500871B (en) * 2012-04-05 2017-03-01 Ford Global Tech Llc An Air to Liquid Heat Exchanger
US9593647B2 (en) 2012-04-05 2017-03-14 Ford Global Technologies, Llc Gas-to-liquid heat exchanger
CN103061866A (zh) * 2012-12-20 2013-04-24 华南理工大学 一种风冷式中冷器
CN103061867A (zh) * 2012-12-20 2013-04-24 华南理工大学 一种气液式中冷器
US9038607B2 (en) 2013-02-06 2015-05-26 Ford Global Technologies, Llc Air cooler and method for operation of an air cooler
EP3015808A4 (en) * 2013-06-28 2016-07-27 Mitsubishi Heavy Ind Ltd HEAT EXCHANGERS, HEAT EXCHANGE STRUCTURE AND HEAT EXCHANGER RUBBER
US20160313070A1 (en) * 2014-02-10 2016-10-27 Mitsubishi Heavy Industries Automotive Thermal Systems Co., Ltd. Heat-exchanger offset fin and refrigerant heat-exchanger utilizing same
WO2015168234A1 (en) * 2014-04-29 2015-11-05 Carrier Corporation Improved heat exchanger
US20170045299A1 (en) * 2014-04-29 2017-02-16 Carrier Corporation Improved heat exchanger
WO2017111750A1 (en) * 2015-12-25 2017-06-29 Kale Oto Radyator Sanayi Ve Ticaret Anonim Sirketi Turbulator with triangular airfoils increasing the performance of engine intercoolers
US10094624B2 (en) 2016-01-08 2018-10-09 Hanon Systems Fin for heat exchanger
US10655530B2 (en) 2016-02-12 2020-05-19 Denso Corporation Intercooler
US11009300B2 (en) 2017-02-21 2021-05-18 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
US20180306101A1 (en) * 2017-04-25 2018-10-25 GM Global Technology Operations LLC Transitional Turbulator
US10294855B2 (en) * 2017-04-25 2019-05-21 GM Global Technology Operations LLC Transitional turbulator
US20230042424A1 (en) * 2020-01-03 2023-02-09 Valeo Systemes Thermiques Tube heat exchanger having spacers
EP4023988A1 (en) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Heat exchanger
EP4023995A1 (en) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Heat exchanger

Also Published As

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JP4674602B2 (ja) 2011-04-20
CN101441041B (zh) 2011-07-27
CN101441041A (zh) 2009-05-27
DE102008057334A1 (de) 2009-07-09
JP2009127937A (ja) 2009-06-11

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