WO2003036215A1 - Echangeur d'energie thermique dote de plusieurs noyaux et d'une barriere thermique - Google Patents

Echangeur d'energie thermique dote de plusieurs noyaux et d'une barriere thermique Download PDF

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Publication number
WO2003036215A1
WO2003036215A1 PCT/US2002/031965 US0231965W WO03036215A1 WO 2003036215 A1 WO2003036215 A1 WO 2003036215A1 US 0231965 W US0231965 W US 0231965W WO 03036215 A1 WO03036215 A1 WO 03036215A1
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WO
WIPO (PCT)
Prior art keywords
fin
thermal
exchanger
thermal energy
core
Prior art date
Application number
PCT/US2002/031965
Other languages
English (en)
Inventor
Richard P. Stoynoff
Steven Falko Wayne
Larry P. Prater
Original Assignee
Heatcraft, Inc.
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 Heatcraft, Inc. filed Critical Heatcraft, Inc.
Publication of WO2003036215A1 publication Critical patent/WO2003036215A1/fr

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Classifications

    • 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
    • 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
    • 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
    • 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
    • F28F2270/00—Thermal insulation; Thermal decoupling

Definitions

  • This invention relates to a multiple core exchanger of thermal energy having corrugated fms that are provided with a thermal barrier comprising a longitudinal slit formed without removal of material for impeding the flow of heat thereacross and bridges that locally connect material across the slit for promoting stability during construction of the heat exchanger and in service.
  • louvers In the field of exchangers of thermal energy, and more particularly of heat exchangers, louvers deflect or direct a fluid such as air and channel heat or coldness from a source. In older designs, little turbulation actually occurs, and laminar flow is relatively uninterrupted. Over the years, a louvered serpentine fin in heat exchangers has undergone design changes to optimize its contribution to the process of exchanging heat between, for example, a radiator and a condenser in the automotive field. Louver width has varied, as has its angle. Louver length has increased, bend radii have changed, and louver patterns have been experimented with in continued efforts to improve the efficiency of the heat exchange process.
  • USPN 6,213,196 discloses a double heat exchanger that combines a condenser of a refrigeration cycle for a vehicle air conditioner and a radiator for cooling engine coolant. That patent is incorporated herein by reference. The reference teaches that in double heat exchangers, plural condenser tubes and plural radiator tubes can be arranged in a vertical direction at the same pitch. The height of each of the radiator tubes is larger than that of the condenser tubes in the vertical direction. Accordingly, the height of the condenser fm disposed between adjacent condenser tubes needs to be larger than that of the radiator fin disposed between adjacent radiator tubes in the vertical direction. '196 patent, col. 1, 11. 20-34. That reference teaches also that the heights of the fins associated with the first and second heat exchangers differ. Id. , col. 2, 11. 31-33.
  • each heat exchanger in a double exchanger configuration is brazed before assembly.
  • the thermal break between the condenser and radiator is defined by mechanical brackets so that contact is avoided between the heat exchanger surfaces of the fin and the tube of the condenser and radiator heat exchangers.
  • contemporary automotive radiators and condensers are being combined by mechanical assembly and mounted in vehicles. Fabrication and manufacturing costs are significant.
  • the disclosed invention calls for a fin that includes a radiator fin and a condenser fin (in the case of a condenser/radiator assembly) that are separated by a thermal break.
  • a thermal break In order for the thermal break to be effective, it is integrated with other components of the heat exchanger assembly: headers, side supports, and channels or flattened tubes.
  • the cores of the disclosed invention have one or more fins interposed between the channels and the manifolds.
  • the fins are separated from each other by a thermal barrier comprising a slit which is formed without removal of material.
  • the slit inhibits the flow of heat energy across the width of the strip.
  • At least some of the fins include louvers defined within the strip of which the fins are constructed.
  • the louvers extend transversely partially across a given elongated strip.
  • the louvers are configured in a plurality of arrays, the arrays being situated adjacent each other across the elongated strip.
  • FIGURE 1(a) is a perspective view of an exchanger of thermal energy through which a cooling medium (such as ambient air) passes;
  • FIGURE 1(b) is a sectional view in the plane lb-lb of FIGURE 1(a), illustrating a multiple core heat exchanger made according to the present invention;
  • FIGURE 1(c) is a top plan view of a flattened fin which illustrates a thermal break between adjacent fins and bridges of material continuity (thermal fuses) extending between adjacent edges of the fins;
  • FIGURE 1(d) is a quartering perspective view of a serpentine form of fin made according to the present invention.
  • FIGURES 2(a)-(f) are more detailed sections of a fin of the subject invention.
  • FIGURE 3 illustrates the locations of thermal fuses in the fin of the subject invention
  • FIGURE 4 is an assembly drawing of a fin roll which, in one alternative method, is used to manufacture the fin of the present invention
  • FIGURE 5 is a sectional view taken along the line 5-5 in FIGURE 4;
  • FIGURES 6(a)-(e) are side elevational views of cutting blades that are assembled into a fin-forming roll that illustrate the geometry which forms the louvered and non-louvered surfaces of the serpentine fin;
  • FIGURES 7(a)-(c) depict blade tooth forms which when rolled in the locations shown in FIGURE 5, create slits along the length of the fin, which form the thermal break in section 2e-2e (FIGURE 2(a));
  • FIGURE 8 illustrates alternative embodiments of the thermal fuses of the subject invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
  • FIGURE 1(a) illustrates one embodiment of the disclosed exchanger of thermal energy: a heat exchanger 10 for a vehicle.
  • the exchanger of thermal energy has a core providing fluid passages through which, for example, a coolant (such as water) flows through a radiator while in cooling a water-cooled engine.
  • a core portion of a condenser 12 is illustrated in FIGURE 1(b). It provides fluid passages through which a refrigerant circulates in a refrigeration cycle.
  • the temperature of the refrigerant is lower than that of the coolant.
  • the core portion of the condenser is typically oriented on the air upstream side of the core portion of the radiator.
  • FIGURE 1(a) depicts a exchanger of thermal energy 10 (such as, but not limited to a condenser) through which a cooling medium such as air passes.
  • the heat exchanger 10 includes such features as channels or flattened tubes 14 that extend transversely between spatially separated manifolds or headers. Fins 16 (preferably, but not necessarily in convoluted or serpentine form) are inserted between and fused to the fluid-carrying transverse channels 14 to facilitate the heat exchange between a fluid flowing in the channels and the cooling medium, such as ambient air. Once assembled, the manifolds, the channels, and fins are fused to each other to form an integral, fluid-tight assembly.
  • the exchanger of thermal energy 10 may be used as a radiator, oil cooler, transmission cooler, charge air cooler, condenser, evaporator, heater or any other type of heat exchange assembly.
  • FIGURE 1(b) is a cross-sectional view taken along the line lb- lb of FIGURE 1(a).
  • a first core 12 is, for example, a condenser that is placed on the upwind side of the multiple core exchanger of thermal energy 10.
  • a second exchanger of thermal energy 30 (such as, but not limited to a radiator) is juxtaposed therewith. Both cores 12, 30 are disposed between the side manifolds shown in FIGURE 1(a).
  • the first core 12 has a plurality of first channels 14 through which a first fluid flows and a first fin 16 that is disposed, preferably in a convoluted manner, between adjacent first channels 14 to facilitate heat exchange between the first fluid and the cooling medium.
  • a second core 30 (such as a radiator) is disposed downstream of the first core 12.
  • the second core 30 has a plurality of second channels 32 through which a second fluid flows.
  • a second fin 34 is disposed between adjacent second channels 32 to facilitate heat exchange between the second fluid and the cooling medium.
  • the second channels 32 extend substantially parallel with the first channels 14.
  • FIGURES 1(c) - (d) there are depicted top and quartering views of a flattened strip of pre-corrugated material that has been flattened for visualization (FIGURE 1 (c)) and after it is corrugated into a serpentine fin configuration (FIGURE 1(d)).
  • the first fin 16 has first upper folds 18, first lower folds 20 and first walls 22 extending between one of the first upper folds and one of the first lower folds.
  • a first array of louvers 24 extends from the first wall 22.
  • the second fin 34 (FIGURE 1(d)) is integrally formed with the first fin 16.
  • the second fin 34 also has a corrugated shape defined by second upper folds 36, second lower folds 38 and second walls 40 that connect one of the second upper folds 36 and one of the second lower folds 38.
  • a second array of louvers 42 extends from the second wall 40.
  • a thermal break comprising a slit 50 (FIGURES l(c)-(d) is roll formed without removal of material between the first and second upper and lower folds, and the first and second walls.
  • the slit 50 insulates heat conductivity between the first and second fins, and may be of uniform or non-uniform length.
  • one or more thermal fuses or bridges 52 locally connect the first and second fins.
  • the thermal fuses 52 may or may not be broken after brazing.
  • Such a selective activation function permits the designer to promote structural integrity during pre-braze assembly and enable a localized transfer of heat. It will be appreciated that such fusing can be fabricated from heavy-gauge or light-gauge material so that they may respectively retain mechanical integrity and positioning, or be readily degradable.
  • the first and second fins 16, 34 comprise an elongated strip 60 having a pair of opposing edges 62, 64, an upper 66 and a lower face 68 (FIGURE 1(d)) and (optionally) at least one louver 70 defined within the strip so that no material of which the strip is formed is removed during formation of the at least one louver.
  • the at least one louver extends transversely at least partially across the elongated strip, either inclined or orthogonally to its edges.
  • the thermal fuse 52 is formed between adjacent edges 64 of the first and second fins 16, 34.
  • Each thermal fuse 52 comprises a portion of material continuity extending between the first and second fins 16, 34 for promoting stability during construction of the exchanger of thermal energy.
  • the thermal fuse can be eliminated following mechanical assembly by subsequent degradation during the brazing process or by other means, such as chemical dissolution by an active flux during controlled atmosphere brazing.
  • the consequent reduction in the number of thermal fuses serves to further isolate the radiator and condenser forms of exchangers of thermal energy.
  • the thermal fuse 52 fulfills the dual role of adding strength during assembly while degrading fin junctions during operation.
  • the first fin has a width (L,), and the second fin has a width (L 2 ).
  • Lj is less than or equal to L 2 where the first and second heat exchangers are respectively a condenser and a radiator
  • FIGURES 2(a)-(f) there are depicted other views of the thermal break comprising a slit 50 and a thermal fuse 52 (FIGURE 2(e)) between condenser and radiator fins.
  • the slit 50 is shown with displaced opposing edges, thereby creating one form of the thermal break.
  • the thermal fuse appears once every 6.5 convolutions.
  • FIGURES 2(c)-(f) are sectional views taken along the respective sectional lines illustrated in FIGURE 2(a).
  • FIGURE 2(c) illustrates a configuration wherein the first fin 16 has one array of louvers extending between the edges thereof.
  • FIGURE 2 (d) illustrates a configuration wherein the louver (in the example shown, of the second core 34) are split.
  • FIGURE 2(e) illustrates a thermal break roll formed by fin separation and the slit 50 formed between the first and second upper and lower folds, and the first and second walls.
  • FIGURE 2(f) illustrates a neutral surface of either fin.
  • FIGURE 3 there is depicted a side elevational view of a fin which is illustrative of that which may be associated with either the first or the second cores 12,30.
  • the thermal fuse 52 can be located on the upper folds 18, 36 respectively of the first or second fins 16, 34, or the lower folds 20, 38.
  • the thermal fuses 52 are located once every 6 and one-half convolutions. As illustrated, the thermal fuse 52 is located alternatively from top to bottom, but need not be so located.
  • the slits 50 and thermal fuses 52 can be manufactured by such techniques as laser cutting, plasma cutting, water jet cutting, or other similar processes.
  • a fin forming roll produces 4 such thermal fuses during each revolution of the fin roll.
  • the minimum number possible is one thermal fuse per revolution of the fin roll, which could exist either on the top of the fin or the bottom of the fin.
  • the number of thermal fuses cannot exceed the number of teeth on the fin roll.
  • Equal spacing between the thermal fuses is not a requirement. Irregular spacing is enabled by using such techniques as laser cutting, plasma cutting, or water jet cutting.
  • FIGURE 4 there is depicted an assembly drawing of a fin roll which creates a fin with a plurality of thermal fuses.
  • the reference numerals 12, 30, and 50 respectively indicate the locations on the fin roll that form the first and second fins 16, 34 and the thermal break 50.
  • FIGURE 5 is a sectional view taken along the line 5-5 of FIGURE
  • FIG. 4 illustrates the locations of each blade in the fin roll which create a specific part feature, e.g. louvered and non-louvered areas.
  • the thermal break is created at fin blade locations) locations 80, 82.
  • the blades on the left hand side of FIGURE 5 form the first core (e.g. condenser).
  • the blades on the right hand side of FIGURE 5 form the second core (e.g. radiator).
  • FIGURES 6(a)-(e) illustrate the shapes of teeth in a fin roll that form the louvered and non-louvered surfaces of the fin. An appreciation of the surfaces and shapes is helpful in visualizing the different louver patterns formed by the blades depicted in FIGURES 4-5.
  • FIGURE 6(a) depicts a blade which is used to form a border 90 (FIGURE 5).
  • FIGURE 6(b) shows the blade form used in sections 94, 96 of the fin roll (FIGURE 5).
  • FIGURE 6(c) illustrates the form of blade which is used at 98, 100 of the fm roll illustrated in FIGURE 5.
  • FIGURE 6(d) illustrates a cutting blade on which the shapes of the teeth create different louver patterns.
  • FIGURE 6(e) illustrates the blade form that occupies positions 102, 104 of the fin roll in FIGURE 5.
  • FIGURE 7(a)-(c) respectively illustrate the crotch areas of blades used in the fin forming roll.
  • the normal crotch areas are depicted by the reference numeral 110 in FIGURE 7(a).
  • the altered crotch 112 creates two locations at which there is a thermal fuse 52 at location 80.
  • FIGURE 7(b) illustrates a blade configuration at locations 82 (FIGURE 5).
  • the exaggerated tooth form 114 is at location 82 (FIGURE 5).
  • FIGURE 7(c) the special crotches 112 (FIGURE 7(a) are shown in relation to the overall circumference of the fin roll at locations 116.
  • FIGURES 7(a)-(b) illustrate the blade forms which when rolled in the proper locations defined in FIGURE 5 create a continuous slit 50 along the length of the blade edge form.
  • the slit continues to be formed until a specially designed area of the form is encountered in the shape of an altered crotch 112 (FIGURE 7(a)).
  • This area is designed to allow the radiator side of the fin, for example, to be joined with the condenser side of the fin. It should be realized that the altered area to create a thermal fuse need not reside at the crest of a convolution or bend radius. It can exist anywhere on the flank of a tooth.
  • the thermal fuse 52 is located on a wall of a fin, approximately midway between two adjacent bend radii. Such a configuration orients the thermal break in the midair wall of the core.
  • the location of the thermal fuse is predicted, as opposed to being randomly placed by an additional operation.
  • the thermal fuse 52 eliminates or reduces the number of thermal junctions, so that heat transfer characteristics in the combined exchanger of thermal energy are improved.
  • the thermal fuse 52 provides mechanical support during assembly and may optionally subsequently be degraded or eliminated during the brazing process.
  • the thermal fuse contemplates that the morphology of the junctions may be small and can be removed by chemical dissolution using an effective flux during controlled atmosphere brazing and/or thermal degradation. This results in a reduction in the number of thermal junctions and serves to further isolate the cores in the exchanger of thermal energy.
  • FIGURE 8 illustrates an enlargement of the area in FIGURE 1(c) depicted by the reference numeral 52 and shows alternative thermal fuse morphology.
  • the thermal fuse is generally rectangular or square with sides depicted as X and Y.
  • the length of segment X (where X ⁇ zero at the thermal break) is less than or equal to that of segment Y.
  • the thermal fuse is formed by two curvilinear arcuate sections.
  • the thermal fuse is made of a homogeneous material.
  • the thermal fuse includes cavities or areas of material discontinuity. It will be appreciated that any combination of these configurations may be effective in use.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention se rapporte à un échangeur thermique (10) doté de plusieurs noyaux et d'une barrière thermique. Le premier noyau (par exemple un condensateur) (12) présente une première ailette (16). Un second noyau (par exemple un radiateur) (30) est juxtaposé au premier noyau (12) et placé en aval de ce dernier en relation avec un flux d'air ambiant. Les noyaux (12, 30) sont respectivement dotés de premières et de secondes ailettes (16, 34) qui sont reliées par une mèche thermique (52) qui apporte une certaine stabilité au cours de l'assemblage, mais qui est susceptible de se dégrader. La séparation entre la première et la seconde ailette (16, 34) consiste en une fente (50) à rupture thermique qui est formée sans qu'il ne soit nécessaire d'ôter le matériau, ce qui permet de bloquer le flux d'énergie thermique à travers les ailettes (16, 34) entre les premiers et seconds noyaux (12, 30) de l'échangeur thermique.
PCT/US2002/031965 2001-10-22 2002-10-07 Echangeur d'energie thermique dote de plusieurs noyaux et d'une barriere thermique WO2003036215A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US10/004,376 US20030075307A1 (en) 2001-10-22 2001-10-22 Exchanger of thermal energy with multiple cores and a thermal barrier
US10/004,376 2001-10-22

Publications (1)

Publication Number Publication Date
WO2003036215A1 true WO2003036215A1 (fr) 2003-05-01

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US (1) US20030075307A1 (fr)
WO (1) WO2003036215A1 (fr)

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EP1331463A2 (fr) * 2002-01-25 2003-07-30 Calsonic Kansei Corporation Echangeur de chaleur intégré et sa méthode de fabrication
EP1729078A2 (fr) * 2005-05-26 2006-12-06 LG Electronics Inc. Échangeur de chaleur pour séchoir et séchoir de type à condensation utilisant celui-ci
JP2014126339A (ja) * 2012-12-27 2014-07-07 Denso Corp 熱交換器

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JP2002277180A (ja) * 2001-03-16 2002-09-25 Calsonic Kansei Corp 一体型熱交換器のコア部構造
US20030102113A1 (en) * 2001-11-30 2003-06-05 Stephen Memory Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle
US20030106677A1 (en) * 2001-12-12 2003-06-12 Stephen Memory Split fin for a heat exchanger
DE10218912A1 (de) * 2002-04-27 2003-11-06 Modine Mfg Co Gewellter Wärmetauschkörper
FR2849174B1 (fr) * 2002-12-23 2006-01-06 Valeo Thermique Moteur Sa Ailette d'echange de chaleur, notamment de refroidissement, module d'echange de chaleur comprenant une telle ailette et procede de fabrication d'echangeurs de chaleur utilisant ladite ailette
DE112005000391T5 (de) * 2004-02-17 2007-12-27 Modine Manufacturing Co., Racine Integrierte Brennstoffverarbeitungsanlage für eine dezentrale Wasserstoffproduktion
US20070175094A1 (en) * 2006-01-30 2007-08-02 Reinke Michael J Integrated autothermal reformer recuperator
JP2007232246A (ja) * 2006-02-28 2007-09-13 Denso Corp 熱交換器
US20090052876A1 (en) * 2006-11-15 2009-02-26 Macduffco Manufacturing Inc. Fins For An Electric Cable In An Electric Radiant Heating System
US8408283B2 (en) * 2007-06-28 2013-04-02 Centrum Equities Acquisition, Llc Heat exchanger fin with ribbed hem
US7866042B2 (en) * 2007-01-12 2011-01-11 Centrum Equities Acquisition, Llc Method for producing a split louver heat exchanger fin
DE102007049474B4 (de) * 2007-10-16 2023-02-09 Innerio Heat Exchanger GmbH Verfahren zur Herstellung von gewellten Wärmetauscherelementen
US8471296B2 (en) 2011-01-21 2013-06-25 International Business Machines Corporation FinFET fuse with enhanced current crowding
JP5920175B2 (ja) * 2012-11-13 2016-05-18 株式会社デンソー 熱交換器
CN106102952A (zh) * 2014-03-28 2016-11-09 摩丁制造公司 热交换器及其制造方法
EP3330657B1 (fr) * 2016-12-01 2020-10-28 Modine Manufacturing Company Lamelle d'évacuation de l'air d'un échangeur de chaleur et son procédé de fabrication
EP4127420A4 (fr) * 2020-03-23 2024-01-24 Cummins, Inc. Refroidisseur de charge à récupération de chaleur à noyaux multiples

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WO1999053253A1 (fr) * 1998-04-09 1999-10-21 Zexel Valeo Climate Control Corporation Echangeur de chaleur monobloc monte en parallele
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US6095239A (en) * 1996-08-12 2000-08-01 Calsonic Kansei Corporation Integral-type heat exchanger
JP2000220983A (ja) * 1999-02-01 2000-08-08 Denso Corp 熱交換器用フィン
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US5992514A (en) * 1995-11-13 1999-11-30 Denso Corporation Heat exchanger having several exchanging portions
US6095239A (en) * 1996-08-12 2000-08-01 Calsonic Kansei Corporation Integral-type heat exchanger
US6142220A (en) * 1996-10-02 2000-11-07 Matsushita Electric Industrial Co., Ltd. Finned heat exchanger
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EP1331463A2 (fr) * 2002-01-25 2003-07-30 Calsonic Kansei Corporation Echangeur de chaleur intégré et sa méthode de fabrication
EP1331463A3 (fr) * 2002-01-25 2006-07-12 Calsonic Kansei Corporation Echangeur de chaleur intégré et sa méthode de fabrication
EP1729078A2 (fr) * 2005-05-26 2006-12-06 LG Electronics Inc. Échangeur de chaleur pour séchoir et séchoir de type à condensation utilisant celui-ci
EP1729078A3 (fr) * 2005-05-26 2012-11-07 LG Electronics Inc. Échangeur de chaleur pour séchoir et séchoir de type à condensation utilisant celui-ci
JP2014126339A (ja) * 2012-12-27 2014-07-07 Denso Corp 熱交換器

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