EP2208955B1 - Intercalaire d'échange de chaleur pour un dispositif d'échange de chaleur. - Google Patents

Intercalaire d'échange de chaleur pour un dispositif d'échange de chaleur. Download PDF

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Publication number
EP2208955B1
EP2208955B1 EP10150574.1A EP10150574A EP2208955B1 EP 2208955 B1 EP2208955 B1 EP 2208955B1 EP 10150574 A EP10150574 A EP 10150574A EP 2208955 B1 EP2208955 B1 EP 2208955B1
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EP
European Patent Office
Prior art keywords
thickness
heat exchange
innerfin
exchange device
localized
Prior art date
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Active
Application number
EP10150574.1A
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German (de)
English (en)
French (fr)
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EP2208955A1 (fr
Inventor
Christophe Denoual
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.)
Valeo Systemes Thermiques SAS
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Valeo Systemes Thermiques SAS
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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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • F28F2215/00—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
    • F28F2225/00—Reinforcing means
    • F28F2225/06—Reinforcing means for fins

Definitions

  • the invention relates to a heat exchange pad for a heat exchange device according to the preamble of claim 1 to heat exchange devices comprising such spacers.
  • JP 2002 147982 discloses such a heat exchange interlayer. It relates more particularly to a heat exchange device, particularly for motor vehicles, comprising a bundle of spaced apart tubes and a plurality of corrugated heat exchange tabs in the form of folded metal strips. so as to form a succession of substantially planar portions each disposed between two tubes and connected in pairs by an angled junction portion of size adapted to the intervals.
  • a heat exchange device has the function of allowing the exchange of heat between a fluid circulating inside tubes and an external fluid passing through the heat exchange device. To increase the performance of the heat exchange between the fluid circulating inside the tubes and the external fluid, it is common to provide the heat exchange device with means for increasing the exchange surface between the external fluid and the circulating fluid inside the tubes.
  • such a heat exchanger commonly comprises one or more rows of aligned tubes in which circulates a heat transfer fluid. All of these tubes are generally referred to as the beam term.
  • Such a heat exchanger serves to allow a heat exchange between the fluid coolant circulating in the tubes, and a fluid traversing externally the heat exchange device.
  • the heat exchange device of a plurality of corrugated general heat exchange tabs formed by the succession of substantially flat portions connected two by two by an angled junction portion.
  • a corrugated spacer is disposed between two tubes so that a portion of the bent portion is in contact with a tube.
  • Such a heat exchange device may for example be integrated with a motor vehicle air conditioning system.
  • the external fluid passing through the device is generally air intended to be blown into the passenger compartment of the vehicle, and the coolant a cooling fluid.
  • the purpose of heat exchange is to cool the air supply.
  • the heat exchange device is then an evaporator.
  • the circulation of the fluid, inside the air conditioning circuit, is provided by a compressor, generally driven directly by the engine of the motor vehicle.
  • the heat exchange device is made from metals, in particular aluminum.
  • metals in particular aluminum.
  • the thickness of the metal foils used tends to be less than 70 micrometers for the spacers and less than 270 micrometers for the tubes. Such reductions in thickness have the disadvantageous consequences that the mechanical strength of the heat exchange device is reduced resulting in an increased risk of failure and accelerated deterioration.
  • the risk of deterioration is even greater when, in the production phase of the heat exchange device, the bundle of tubes and spacers is put under holding stress in order to ensure good cohesion during the final phase. manufacturing process of brazing the various elements together.
  • the bundle of tubes and spacers may be deformed and / or staggered and thus be defective, for example by the creation of leaks, or be of lesser performance, for example by an increase in pressure losses. .
  • the object of the invention is therefore to provide a new type of heat exchange device of the type mentioned in the introduction overcoming the aforementioned drawbacks.
  • the invention therefore provides a spacer for a heat exchange device according to claim 1.
  • the first thickness and the second thickness are such that the second thickness is less than twice the first thickness and the second thickness is greater than or equal to one and a half times the first thickness.
  • the second zone defines a localized excess thickness arranged at the ends of the spacer.
  • the first zone is obtained by local thinning of the metal strip, produced by machining, rolling, stamping or forming.
  • the localized extra thickness of the spacer defines at least one transverse excrescence of a given height, for example equal to the difference between the second thickness and the first thickness.
  • the present invention is also specific to a heat exchange device comprising at least one interlayer as defined above.
  • the interlayer comprises two localized thicknesses arranged on the same side or on two opposite sides of the insert.
  • the exchanger comprises at least one heat exchange tube arranged between at least two localized thicknesses.
  • the heat exchange tube comprises at least one localized deformation adapted to cooperate with the localized thickness of the interlayer.
  • the figure 1 represents, viewed from the front, a heat exchange device 2.
  • the heat exchange device 2 comprises a bundle of tubes 8 spaced apart by a gap 12 in which a corrugated spacer 10 is arranged.
  • the corrugated inserts 10 are in the form of a sheet or metal strip 20 folded so as to form a succession of planar portions 22 or substantially planar disposed each between two tubes 8 and connected in pairs by a junction portion 24 bent of dimension adapted to the gaps 12 arranged between two successive tubes 10.
  • the heat exchange device 2 also comprises a first collector 4 and a second collector 6 respectively receiving one and the other of the ends of fluid circulation tubes 8, in particular a coolant or heat transfer fluid.
  • the tubes 8 are arranged aligned, regularly spaced from each other, and thus form the bundle of tubes 8.
  • the first collector 4 is connected to an inlet pipe 14 and the second collector 6 is connected to an outlet pipe 16 respectively connected to an air conditioning circuit in which a fluid circulates, in particular a coolant or heat transfer fluid.
  • the fluid coming from an upstream portion of the air conditioning circuit, enters via the inlet pipe 14 into the first tubular collector 4, circulates in the tubes 8 and reaches the second collector 6. From there, the fluid flows through the second collector 6 before exiting via the outlet pipe 16, which is connected to a downstream part of the air conditioning circuit.
  • the heat exchange device 2 comprises a single collector having two internal parts separated by an internal partition or made by two chambers. collectors arranged side-by-side so that the inlet pipe 14 and the outlet pipe 16 are respectively disposed in the single collector.
  • the bundle of tubes 8 and inserts 10 comprises two end plates 18 contributing to the general maintenance and overall resistance of the heat exchange device 2.
  • the present invention also covers heat exchange devices not comprising end plates 18.
  • the heat exchange device 2 makes it possible to exchange heat between an external fluid, for example air, passing through the heat exchange device 2 and the fluid circulating inside the tubes 8, for example a refrigerant or heat transfer fluid.
  • an external fluid for example air
  • the fluid flowing inside the tubes 8 may be a supercritical fluid, in particular carbon dioxide, also known under the name R744, or a subcritical fluid, in particular a fluorinated compound, especially the refrigerant referenced R134a.
  • the present invention may be used with other alternative fluids.
  • the fluid flowing inside the tubes 8 may also be a heat transfer fluid, in particular a cooling fluid of a thermal engine of the vehicle.
  • the figure 2 is a view a perspective view of part of the beam of the heat exchange device of the figure 1 .
  • the figure 2 specifies the shape of the tubes 8 and tabs 10 and their arrangement relative to each other.
  • a heat exchange interlayer 10 of corrugated appearance As shown in figure 1 between two tubes 8 is arranged a heat exchange interlayer 10 of corrugated appearance.
  • Each interlayer 10 is made in the form of a sheet or strip of folded metal metal, for example aluminum alloy.
  • Each interlayer 10 is provided with louvers 26 made by cutting in the metal strip 20.
  • the corrugated insert 10 is made, for example by successive bends of the metal strip sometimes called "strip".
  • the insert 10 has a succession of planar portions 20 arranged such that two adjacent planar portions 20 are interconnected by a connecting portion 24.
  • the heat exchange device 2 is traversed by a flow of air F. It follows that the bundle of tubes 8 and spacers 10 is traversed by the air flow F.
  • the heat exchange device 2 thus has an upstream face constituting the inlet face of the air flow F in the heat exchange device 2 and a downstream face constituting the outlet face of the air flow. F of heat exchange device 2.
  • the interlayer 10 also includes a localized allowance 30.
  • This localized allowance 30 makes it possible to increase the rigidity of the insert 10 and thus to contribute to increasing the holding of the heat exchange device 2.
  • two localized thicknesses 30 are arranged at the two ends of the spacer 10 in the flow direction of the air flow F.
  • the first localized allowance 30 is disposed at the upstream face of the device.
  • heat exchange 2 and the second localized excess thickness 30 is disposed at the downstream face of the heat exchange device 2.
  • the localized excess thickness 30 is achieved by localized turning, in particular by folding, on a first length A of the metal strip 20 constituting the insert 10.
  • the metal strip is at a first thickness Th1
  • the extra thickness located at a second thickness Th2, such that the second thickness Th2 is equal to twice the first thickness Th1.
  • the interlayer 10 is such that it comprises a first zone having the first thickness Th1 and at least a second zone having the second thickness Th2.
  • Such an embodiment makes it possible to have a first thickness Th1 that is less than or equal to twice the second thickness Th2.
  • Th1 is less than the second thickness Th2.
  • the localized excess thickness 30 is thinned, for example by rolling, in order to reduce the size of the localized allowance and obtain the second thickness Th2.
  • the second thickness Th2 it is desirable for the second thickness Th2 to be between one and a half times and twice the first thickness Th1.
  • the present invention allows the localized thicknesses 30 define extremal stops having a height h2 at least equal to the difference between the second thickness Th2 and the first thickness Th1.
  • Such end stops also contribute to maintaining the position of the spacers 10 between the tubes 8. Indeed, as presented especially in figure 2 , the spacers 10 are maintained in a transverse direction, that is to say in the direction of flow of the air flow F which is perpendicular to the median plane.
  • the localized thickening 30 by thinning a first portion of the insert 10, in particular by machining operations.
  • the first portion of the spacer 10 which is thinned is located symmetrically with respect to the median plane of the bundle of tubes 8 and spacers 10.
  • the median plane is a plane equidistant from the upstream and downstream faces of the device heat exchange 2 and parallel thereto.
  • FIG. 3 represents a sectional view according to the line III-III of the beam portion of the heat exchange device 2 of the figure 2 .
  • the end stops come into contact with a peripheral wall 40 of the tube 8.
  • the contact is made at the two small sides of the tube 8 which connect two long sides of the tubes 8 which are in contact with the insert 10 .
  • the spacers 10 are placed in position and held so that they can not move between the tubes 8 during the stressing for the mounting of the heat exchange device 2.
  • the two localized thicknesses 30 are arranged on the same side of the insert 10.
  • This embodiment makes it possible to have two end stops on either side of the same tube 8 at the same section along a plane perpendicular to the median plane and to the upstream and downstream faces of the heat exchange device 2.
  • the tabs 10 is held in position on the tube 8.
  • the two localized thicknesses 30 are arranged on either side of the insert 10. This is more particularly detailed in FIG. figure 4 which is a sectional view along line IV-IV of the figure 3 .
  • the end of the spacer 10 disposed on the downstream face has a localized extra thickness 30 disposed of a first next to the tab 10.
  • the end of the insert 10 disposed on the upstream face has a localized extra thickness 30 disposed on a second side of the insert 10, opposite the first side.
  • the figure 5 illustrates a perspective view of the embodiment of the interlayer according to the figure 4 .
  • the present invention finds particular application in heat exchange devices for a heating, ventilation and / or air conditioning system for motor vehicles, such as an evaporator, a condenser or a gas cooler or a radiator. heater.
  • the examples described above are based on heat exchange devices comprising tubes of folded types.
  • the present invention also covers embodiments of plate tubes or extruded tubes.
  • fluid circulation tubes 8 are of the 'single channel' type.
  • the tubes 8 described here are only exemplary.
  • Other types of tubes can be used here as fluid circulation tubes.
  • the present invention also covers the embodiments in which the tubes 8 are provided with internal partitions delimiting several internal channels.
  • Such tubes are generally referred to as “multichannel tubes”.
  • the tubes 8 are known as "multichannel flat tubes”.
  • the figure 6 illustrates an alternative embodiment of the present invention.
  • the tube 8 comprises a localized deformation 32.
  • the localized deformation 32 makes it possible to create a space adapted to receive the localized thickening 30 of the interlayer 10.
  • the localized deformation 32 is arranged at the end portions 36 of the tube 8.
  • the localized deformation 32 is such that it cooperates by complementarity of form with the localized extra thickness 30 of the insert 10.
  • the tube 8 has a central portion 34 having a thickness e1 and two end portions 36 disposed on either side of the central portion 34.
  • Each end portion 36 has a thickness e2.
  • the thickness e1 is equal to the thickness e2 plus two times the height h2 of the end stops of the insert 10.
  • the embodiment of the figure 6 also shows a particular embodiment of the corrugated interlayer 10.
  • the insert 10 has two localized thickenings 30 on each side of the insert 10, a total of four localized thicknesses 30.
  • Such an interlayer 10 results, in particular, from an inverted double folding, that is to say in two opposite directions, of the metal strip over a first length (A) of the ends of the insert 10. Consequently, this double folding can be reduced in thickness by a thinning operation, preferably by rolling as described above.
  • Such an embodiment also has the same advantages of maintaining the spacers 10 in the bundle of tubes 8 during the stressing for the mounting of the heat exchange device 2.
  • the present invention is not limited to evaporators. It is of interest for all types of heat exchange devices such as condensers, gas coolers, heating radiators, ...

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cell Separators (AREA)
EP10150574.1A 2009-01-15 2010-01-12 Intercalaire d'échange de chaleur pour un dispositif d'échange de chaleur. Active EP2208955B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0900160A FR2941040B1 (fr) 2009-01-15 2009-01-15 Intercalaire d'echange de chaleur pour un dispositif d'echange de chaleur

Publications (2)

Publication Number Publication Date
EP2208955A1 EP2208955A1 (fr) 2010-07-21
EP2208955B1 true EP2208955B1 (fr) 2017-09-13

Family

ID=40568321

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10150574.1A Active EP2208955B1 (fr) 2009-01-15 2010-01-12 Intercalaire d'échange de chaleur pour un dispositif d'échange de chaleur.

Country Status (6)

Country Link
US (1) US20100175863A1 (es)
EP (1) EP2208955B1 (es)
JP (1) JP5539742B2 (es)
CN (1) CN101793477A (es)
ES (1) ES2649039T3 (es)
FR (1) FR2941040B1 (es)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012027098A2 (en) * 2010-08-24 2012-03-01 Carrier Corporation Microchannel heat exchanger fin
CN102879483A (zh) * 2011-07-13 2013-01-16 江苏汉邦科技有限公司 超临界流体色谱仪(sfc)以及用于其中的液态co2恒温装置
US10113812B2 (en) * 2013-02-18 2018-10-30 Denso Corporation Heat exchanger and manufacturing method thereof
EP2984433A1 (en) * 2013-04-10 2016-02-17 Carrier Corporation Folded tube multiple bank heat exchange unit
DE102014200680A1 (de) * 2014-01-16 2015-07-16 Mahle International Gmbh Wärmeübertrager
FR3037388B1 (fr) * 2015-06-12 2019-07-26 Valeo Systemes Thermiques Ailette d'un echangeur thermique notamment pour vehicule automobile, et echangeur thermique correspondant
EP3255368A1 (en) * 2016-06-09 2017-12-13 Valeo Systemes Thermiques Heat exchanger, especially a gas radiator or a condenser for a car
JP2018009731A (ja) * 2016-07-13 2018-01-18 株式会社ティラド 熱交換器のコア部構造
US10451360B2 (en) 2016-10-24 2019-10-22 Hamilton Sundstrand Corporation Heat exchanger with integral anti-icing
CN110073167B (zh) * 2016-12-21 2021-01-01 三菱电机株式会社 热交换器及其制造方法以及制冷循环装置
FR3066014A1 (fr) * 2017-05-02 2018-11-09 Valeo Systemes Thermiques Echangeur de chaleur avec dispositif de protection et procede de fabrication associe
JPWO2022180823A1 (es) * 2021-02-26 2022-09-01
WO2023199400A1 (ja) * 2022-04-12 2023-10-19 三菱電機株式会社 熱交換器および冷凍サイクル装置

Citations (1)

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Publication number Priority date Publication date Assignee Title
JPS53126070U (es) * 1977-03-16 1978-10-06

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US1878511A (en) * 1929-04-27 1932-09-20 Harrison Radiator Corp Radiator core for automobile cooling systems
GB1027366A (en) * 1962-11-24 1966-04-27 Svenska Metallverken Ab An improved radiator and method of making it
JPS6082787A (ja) * 1983-10-13 1985-05-10 Matsushita Electric Ind Co Ltd フイン付熱交換器
JPH11148795A (ja) * 1997-11-14 1999-06-02 Toyo Radiator Co Ltd 複合型熱交換器
JP4456750B2 (ja) * 2000-11-10 2010-04-28 株式会社ティラド コルゲートフィン型熱交換器およびその製造方法
JP2003083691A (ja) * 2001-09-06 2003-03-19 Toyo Radiator Co Ltd 熱交換器用コルゲートフィンおよびその製造方法
JP2003322486A (ja) * 2002-05-07 2003-11-14 Japan Climate Systems Corp 熱交換器
US8408283B2 (en) * 2007-06-28 2013-04-02 Centrum Equities Acquisition, Llc Heat exchanger fin with ribbed hem
EP2106520B1 (en) * 2007-01-12 2014-11-19 Vista-Pro Automotive, LLC Heat exchanger fin

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JPS53126070U (es) * 1977-03-16 1978-10-06

Also Published As

Publication number Publication date
US20100175863A1 (en) 2010-07-15
JP5539742B2 (ja) 2014-07-02
FR2941040A1 (fr) 2010-07-16
FR2941040B1 (fr) 2012-08-31
ES2649039T3 (es) 2018-01-09
CN101793477A (zh) 2010-08-04
JP2010181140A (ja) 2010-08-19
EP2208955A1 (fr) 2010-07-21

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