EP3308096B1 - Heat exchanger for motor vehicle - Google Patents

Heat exchanger for motor vehicle Download PDF

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Publication number
EP3308096B1
EP3308096B1 EP16728027.0A EP16728027A EP3308096B1 EP 3308096 B1 EP3308096 B1 EP 3308096B1 EP 16728027 A EP16728027 A EP 16728027A EP 3308096 B1 EP3308096 B1 EP 3308096B1
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EP
European Patent Office
Prior art keywords
circuit
heat exchanger
channels
channel
multichannel
Prior art date
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Application number
EP16728027.0A
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German (de)
French (fr)
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EP3308096A1 (en
Inventor
Dawid Szostek
Grzegorz Romanski
Andrzej Fudala
Grzegorz ZELEK
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Valeo Systemes Thermiques SAS
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Valeo Systemes Thermiques SAS
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Publication of EP3308096A1 publication Critical patent/EP3308096A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • 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
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/048—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels

Definitions

  • the field of the present invention is that of heat exchangers for motor vehicles, and the present invention applies more particularly, but not exclusively, to heat exchangers used in the air conditioning circuits of these vehicles.
  • WO 2012/132924 A1 describes a heat exchanger according to the preamble of claim 1.
  • the refrigerant currently most used in this type of exchanger is a fluorinated compound known under the name R134a.
  • This coolant is usually kept in a sealed closed circuit of the vehicle. In certain situations, however, this fluid can escape into the atmosphere: this is the case, for example, when the vehicle is involved in an accident, or when the vehicle is at the end of its life, or even when the refrigerant circuit has a leak.
  • this refrigerant is known to contribute negatively to the greenhouse effect on the planet.
  • the aim of the present invention is to provide a simple, effective solution. and reliable to achieve an efficient heat exchange between a heat transfer fluid and a supercritical refrigerant fluid such as carbon dioxide, a solution which is also easy to assemble before the welding / brazing operations of the heat exchanger.
  • the subject of the invention is a heat exchanger according to claim 1.
  • the first circuit comprises several channels and the second circuit comprises several tubes, and the tubes and channels are stacked alternately on top of each other.
  • the multichannel tube is an extruded tube of low height, of the order of a few millimeters at most, in particular between 1 and 3 millimeters.
  • the multichannel tube comprises a plurality of walls, and these walls define a set of channels which extend from one longitudinal end of said multichannel tube to the other.
  • the channels thus delimited are straight and aligned one beside the other.
  • the two plates forming a channel of the first circuit of the heat exchanger are assembled to one another at least by their periphery, in particular by a peripheral edge of these plates.
  • the first circuit comprising several channels of this type, two plates forming a first channel of the first circuit and two plates forming a second channel of said first circuit communicate with each other by collars fitted into one another and assembled in a sealed manner. Internal channel volume adjacent sites is thus placed in a fluid relationship.
  • Each plate entering into the formation of a channel of the first circuit comprises two orifices placed at each of the longitudinal ends of the channel and each delimited by a collar which extends, once said plate is assembled with a similar plate to form said channel, towards outside said channel, that is to say towards the outside of the internal volume delimited by two plates forming a channel.
  • the plates which form, by assembly, the first circuit also comprise one or more reinforcements which delimit circulation passages for the heat transfer fluid, these reinforcements being located in the central portion of the plate called bowl.
  • the contact between the elements forming the first circuit and the elements forming the second circuit is made between at least one flat portion of a plate forming part of a channel of the first circuit and at least a part of an outer face of a multichannel tube forming the second circuit.
  • a direction in which extends at least one channel forming the second circuit of said heat exchanger and a direction passing through orifices formed at each longitudinal end of a plate are substantially perpendicular to each other.
  • the set, or the series, of first orifices and the set, or the series, of second orifices respectively form, once the set of channels are assembled in a sealed manner by said collars, a first tubular passage and a second tubular passage which interconnect all the internal volumes of the channels.
  • each plate entering the formation of a channel of the first circuit comprises at least one rib which defines at least one passage for circulation of the heat transfer fluid.
  • a rib also has a function of mechanical reinforcement of the channel.
  • each rib has substantially the shape of a "V", thus forming a chevron.
  • each end of the multichannel tubes protrudes from edges located at the periphery of the plates constituting the channels.
  • Multichannel tubes can thus be connected to manifolds without interfering with the plates.
  • each plate entering into the formation of a channel of the first circuit comprises at least one planar part in contact with an outer face of a multichannel tube. This guarantees the transfer of calories from the liquid heat transfer fluid to the supercritical coolant, or in the opposite direction.
  • the invention also relates to a heat transfer fluid circuit or a supercritical refrigerant fluid circuit for a motor vehicle, characterized in that one and / or the other of these circuits comprises a heat exchanger as detailed above.
  • the figure 1 shows an external perspective view of two plates 1 entering the formation of a channel A of the first circuit of a heat exchanger 100 according to the invention, capable of being traversed by a heat transfer fluid such as a glycol liquid, for example . It should be understood here that a channel A of this first circuit is formed by the assembly of these two plates 1 as represented by the figure 1 .
  • Each plate 1 is a thin plate, advantageously produced by stamping a metallic material so as to form a cup 10 (visible on the figure 2 ) of shallow depth delimited by a bottom 12 and, in periphery, by an edge 11.
  • the thickness of each plate 1 is advantageously of the order of a few tenths of a millimeter, typically, but in a non-limiting manner, 3/10 th to 7/10 th of a millimeter.
  • the depth of the bowl 10 is advantageously of the order of a few tenths of a millimeter to about 1 millimeter.
  • each plate 1 has substantially the general shape of a hexagon of which two parallel sides 1a and 1b are longer than the other sides, the lengths of said other sides being substantially equal between they.
  • Each plate 1 is also pierced with two orifices, hereinafter referred to as the first orifice 13a and second orifice 13b.
  • the orifices 13a and 13b have an oblong shape and are placed substantially at each end of the plate 1, substantially spaced apart the length of the parallel sides 1a and 1b. They are also placed in such a way that the plate 1 has at least one plane of symmetry P.
  • the plane of symmetry P is substantially perpendicular to the parallel sides of greater length 1a and 1b, and passes through the middle of these.
  • each plate 1 may also have a plurality of ribs 14 each of which forms, within the bowl 10, a projection whose height is slightly less than the depth of the bowl 10.
  • the ribs 14 are arranged symmetrically with respect to the previously mentioned plane of symmetry P, and they each have the shape of a "V". In other words, these ribs 14 each form a chevron. By their shape, these ribs 14 have a role of mechanical reinforcement and stiffening of each plate 1. They also have another role which will be specified later. Between the ribs 14, the bottom 12 of each plate 1 is substantially flat.
  • a channel A of the first circuit of the heat exchanger according to the invention intended to be traversed by the liquid heat transfer fluid two plates 1 as described above are assembled by their edge 11. More precisely, the blanks 110 of the two plates 1 are contiguous and brazed together, so that the two cups 10 of each plate 1 together form an internal volume V in which the liquid heat transfer fluid is required to circulate. Given the depth of each bowl 10, the height of a channel A is typically, but not limited to, of the order of 1 to 3 millimeters. However, it emerges from the description of the plates 1 above that the internal volume V delimited by the assembly of the latter communicates with the outside through the orifices 13a, 13b carried by them.
  • the first circuit of the heat exchanger according to the invention consists of a stack or succession of several channels as described above.
  • the figure 2 shows a detail of the assembly of two immediately adjacent plates constituting two channels forming the first circuit. It appears on the figure 2 that, during the assembly of the two adjacent channels A, the orifices 13a formed on the plates 1 are located opposite one another, and that their collars 13c, which then extend towards one another towards the other, cooperate to form a passage portion making it possible to make the internal volumes V formed within the adjacent channels communicate with each other. When these channels are assembled together, the collars 13c, brazed together, therefore form a sealed passage between the internal volumes V of said channels each delimited by a pair of plates 1.
  • Each plate 1 having a first orifice 13a and a second orifice 13b at each of its ends, a second tubular passage 15b is formed in the same way as the first tubular passage 15a, as shown in FIG. figure 3 , that is to say through the series of second orifices 13b.
  • These tubular passages 15a and 15b form, with the succession of the internal volumes V of the channels A assembled to form the first circuit of the heat exchanger 100 according to the invention, the first heat transfer fluid circuit.
  • the figure 3 also illustrates the presence of a plurality of multichannel tubes B interposed between each channels A of the first circuit.
  • the multichannel tubes B are connected in a sealed manner to one or more inlet 7a and outlet 7b sleeves, both connected to a single flange 50.
  • a collector box 51 consisting of a stack of components.
  • One of these components is a first plate 5 on one side of which the sleeves input 7a and output 7b are directly secured.
  • Another component is formed by an intermediate plate 52 sandwiched between the first plate 5 and a collector plate 6. The latter comprises folded longitudinal edges to grip the first plate and thus maintain the stack of components.
  • a multichannel tube B which is advantageously an extruded tube, is in the form of a rigid plate 20 of generally substantially rectangular shape with a large side L , of small side l, and of thickness d.
  • this plate comprises, in its thickness, a set of walls 22, for example parallel, of width h1 which extend, in a direction D1 parallel to that of the large side L of the multichannel tube B, of a longitudinal end to the other of the plate 20.
  • the walls 22 form bridges of material between two large outer faces 33 and 34 defined by the large side L and the small side l.
  • the walls 22 define between them, in the direction D1, a set of channels 21 aligned parallel to each other which extend, also in the direction D1, from one longitudinal end of the plate 20 to the other, so as to open at both ends of it.
  • each of the channels 21 has a substantially oblong shape, the height H of which is greater than the width h and slightly less than the thickness d of the rigid plate 20.
  • the channels 21 are therefore spaced from each other by the width h1 of each wall 22, and each of these walls acts as a mechanical reinforcement for the assembly of the multichannel tube B, the channels 21 being aligned side by side.
  • the figure 6 illustrates more precisely the assembly between two channels A of the first circuit of the heat exchanger 100 according to the invention and a tube multichannel B of the second circuit of this heat exchanger. It appears in this figure that the multichannel tube B is interposed between the two channels A, and that the multichannel tube B protrudes, at each of its ends, from the longitudinal edges 1a, 1b of greater length of each of the channels A. More precisely , and as mentioned above, the outer wall of the bowl 10 formed in each plate 1 entering the formation of a channel A is, between the ribs 14 that this plate carries, substantially flat. According to the invention, at least a portion 35 of these flat parts is in direct contact, in particular by brazing, with an outer face 33 or 34 of the multichannel tube B immediately adjacent.
  • the dimensions of the collars 13c of the adjacent channels A and the thickness d of each multichannel tube B are defined in such a way that the insertion of these tubes between two adjacent channels A is possible while leaving a small space such that it is then possible to make direct contact by simple welding or brazing between multichannel tube B of the second circuit and plates 1 of the channels of the first circuit.
  • the thickness d of each plate 20 is of the order of 1 to 3 millimeters, thus corresponding to the space which separates two channels A immediately adjacent to the first circuit.
  • the first and second circuits of a heat exchanger 100 are formed by a succession of channels A and multichannel tubes B interposed between two adjacent channels, the tubular passages 15a and 15b defining an inlet and an outlet of the heat transfer fluid in the first circuit and thus a general direction of circulation of said fluid in said first circuit.
  • the supercritical refrigerant circulates in the channels 21 of the multichannel tubes B in the second circuit.
  • an inlet cheek 3 is combined with a first plate 1 so as to define an inlet zone for the coolant in the first circuit.
  • the entry cheek 3 has a thickness greater than the thickness of a plate 1 and thus forms a reinforcement mechanical for the heat exchanger.
  • the inlet cheek 3 receives an inlet pipe 31 also delimiting one of the tubular passages 15a or 15b.
  • the heat exchanger 100 also comprises an outlet cheek 4 assembled in a sealed manner to a plate 1.
  • This outlet cheek 4 supports an outlet pipe 41 delimiting the second tubular passage 15b.
  • the heat transfer fluid therefore enters the first circuit through the inlet pipe 31, circulates in the first tubular passage 15, then is distributed in each channels A, to be collected by the second tubular passage 15b, and finally out of the exchanger heat 100 through the outlet pipe 41.
  • the inlet and outlet of the heat transfer fluid circuit are each located at one end of the heat exchanger 100 according to the invention, in the direction of stacking of the assembly.
  • multichannel ducts-tubes are each located at one end of the heat exchanger 100 according to the invention, in the direction of stacking of the assembly.
  • the multichannel tubes B are connected, at each of their ends, to a manifold 51 as described in connection with figure 3 above. Only one of two manifolds is connected to a set of inlet and outlet sleeves 7a and 7b, which ensure the circulation of the supercritical refrigerant fluid within the second circuit of the heat exchanger according to the invention. It will thus be understood that the inlet and outlet sleeves 7a and 7b of the second circuit are located on the same side of the heat exchanger, thus defining a "U" configuration of this second circuit.
  • the collector box devoid of inlet and outlet sleeves 7a and 7b, called the recovery collector box 53 ensures the recovery of the supercritical refrigerant fluid arriving through part of the channels 21 of the multichannel tubes B. This collector box then directs this fluid from so that what enters the other part of the channels 21 to move towards the manifold 51, called the inlet manifold.
  • a general direction D2 of circulation of the heat transfer fluid in the channels A constituting the first circuit is defined by a straight line passing through the first orifice 13a and the second orifice 13b of the same plate 1.
  • This direction D2 is perpendicular, or substantially perpendicular, to the general direction D1 of circulation of the supercritical refrigerant fluid in the multichannel tubes B , defined by the orientation of the channels 21 of the multichannel tubes B.
  • at least one channel A of the first circuit and at least one multichannel tube B of the second circuit are arranged in the heat exchanger 100 so as to that their respective fluid path is perpendicular, or substantially perpendicular.
  • the process for producing a heat exchanger 100 according to the invention can be as follows: stacking the channels A and multichannel tubes B so as to form a heat exchange body, respectively forming the first and the second fluid circuit, pre-assembly of the manifolds 51, pre-assembly of the inlet 31 and outlet 41 pipes on the stack of multichannel tubes B, pre-assembly of the inlet 7a and outlet 7 sleeves on the stack of channels A , then brazing or welding of the assembly in a suitable furnace.
  • the invention therefore makes it possible to produce a simple one-piece exchanger in which the elements in which the supercritical refrigerant circulates are designed to withstand the high pressures necessary for the implementation of the latter, while offering high performance of heat exchange.
  • the manufacturing operations of the various elements of the heat exchanger circuits such as the stamping of the plates forming the channels of the heat transfer fluid circuit, the extrusion of the multichannel tubes, the brazing of the assembled elements, the pre-assembly steps and the final brazing step are, moreover, simple, and cost under control for mass production.
  • Such a heat exchanger 100 therefore remains economically viable for mass production, as is notably the case in the world of mass-produced automobiles.
  • such an exchanger is compact, which facilitates its integration into a vehicle, and allows its installation on a wide variety of vehicles.
  • the invention cannot be reduced to the means and configurations described and illustrated.
  • the inlet and outlet sleeves 7a and 7b of the second circuit of the heat exchanger 100 according to the invention are located on the same side of this exchanger, defining circulation of the refrigerant fluid in a "U", such a configuration is not exclusive, and the inlet and outlet sleeves of the second circuit can be arranged to define an "I" configuration without this harming the invention .
  • an inlet sleeve 7a is secured to a first manifold 51
  • an outlet sleeve 7b is secured to a second manifold 53.
  • any other respective configuration of the inlet and outlet sleeves or pipes of the first or of the second circuit can also be implemented, as long as it contributes to optimizing the circulation of the coolant and supercritical refrigerant fluids and, thus, the efficiency of the heat exchange.
  • any general shape other than hexagonal can be given to the plates 1 entering into the formation of the channels A, insofar as the specificities of these plates described here with regard to the invention are respected.

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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)

Description

Le domaine de la présente invention est celui des échangeurs de chaleur pour véhicules automobiles, et la présente invention s'applique plus particulièrement, mais de manière non exclusive, aux échangeurs de chaleur utilisés dans les circuits de climatisation de ces véhicules.The field of the present invention is that of heat exchangers for motor vehicles, and the present invention applies more particularly, but not exclusively, to heat exchangers used in the air conditioning circuits of these vehicles.

L'état de la technique le plus proche est formé par les échangeurs de chaleur à deux circuits, dans lesquels un premier circuit contient un fluide caloporteur du type eau glycolée, et dans lesquels un second circuit contient un fluide réfrigérant, les calories étant transférées du fluide caloporteur au fluide réfrigérant. WO 2012/132924 A1 décrit un échangeur de chaleur selon le préambule de la revendication 1.The closest prior art is formed by heat exchangers with two circuits, in which a first circuit contains a heat transfer fluid of the glycol water type, and in which a second circuit contains a refrigerant fluid, the calories being transferred from the coolant to refrigerant. WO 2012/132924 A1 describes a heat exchanger according to the preamble of claim 1.

Le fluide réfrigérant actuellement le plus utilisé dans ce type d'échangeur est un composé fluoré connu sous la dénomination R134a. Ce fluide réfrigérant est habituellement maintenu dans un circuit fermé étanche du véhicule. Dans certaines situations, toutefois, ce fluide peut s'échapper dans l'atmosphère : c'est le cas, par exemple, lorsque le véhicule est accidenté, ou lorsque le véhicule est en fin de vie, ou encore lorsque le circuit réfrigérant présente une fuite. Or, ce fluide réfrigérant est connu pour contribuer de manière négative à l'effet de serre sur la planète.The refrigerant currently most used in this type of exchanger is a fluorinated compound known under the name R134a. This coolant is usually kept in a sealed closed circuit of the vehicle. In certain situations, however, this fluid can escape into the atmosphere: this is the case, for example, when the vehicle is involved in an accident, or when the vehicle is at the end of its life, or even when the refrigerant circuit has a leak. However, this refrigerant is known to contribute negatively to the greenhouse effect on the planet.

Pour pallier cet inconvénient, il a été proposé de remplacer le composé fluoré R134a par du dioxyde de carbone connu sous la dénomination R744 qui a un impact nettement moins négatif sur l'effet de serre de la planète que celui des composés fluorés évoqués plus haut. La mise en œuvre de ce fluide aux caractéristiques supercritique impose toutefois un certain nombre de contraintes techniques. En effet, le cycle thermodynamique du CO2 impose, pour l'obtention d'un effet réfrigérant correspondant aux exigences de l'application, la mise en œuvre de hautes pressions, typiquement de l'ordre de 160 bars. Les technologies d'échangeur à plaques utilisées pour des fluides réfrigérants fluorés ne résistent pas à ces pressions.To overcome this drawback, it has been proposed to replace the fluorinated compound R134a with carbon dioxide known under the name R744 which has a markedly less negative impact on the greenhouse effect on the planet than that of the fluorinated compounds mentioned above. However, the use of this fluid with supercritical characteristics imposes a certain number of technical constraints. In fact, the thermodynamic cycle of CO2 requires, in order to obtain a cooling effect corresponding to the requirements of the application, the use of high pressures, typically of the order of 160 bars. Plate heat exchanger technologies used for fluorinated refrigerants do not withstand these pressures.

Le but de la présente invention est de proposer une solution simple, efficace et fiable pour réaliser un échange thermique performant entre un fluide caloporteur et un fluide réfrigérant supercritique tel qu'un dioxyde de carbone, solution qui soit en outre facile à assembler avant les opérations de soudage/brasage de l'échangeur de chaleur.The aim of the present invention is to provide a simple, effective solution. and reliable to achieve an efficient heat exchange between a heat transfer fluid and a supercritical refrigerant fluid such as carbon dioxide, a solution which is also easy to assemble before the welding / brazing operations of the heat exchanger.

Dans ce but, l'invention a pour objet un échangeur de chaleur selon la revendication 1.For this purpose, the subject of the invention is a heat exchanger according to claim 1.

Selon un mode de réalisation privilégié de l'invention, le premier circuit comprend plusieurs canaux et le deuxième circuit comprend plusieurs tubes, et les tubes et canaux sont empilés alternativement les uns sur les autres.According to a preferred embodiment of the invention, the first circuit comprises several channels and the second circuit comprises several tubes, and the tubes and channels are stacked alternately on top of each other.

Avantageusement, le tube multicanaux est un tube extrudé de faible hauteur, de l'ordre de quelques millimètres au maximum, notamment compris entre 1 et 3 millimètres. Selon un mode de réalisation de l'invention, le tube multicanaux comprend une pluralité de parois, et ces parois délimitent un ensemble de canaux qui s'étendent d'une extrémité longitudinale dudit tube multicanaux à l'autre. Avantageusement, les canaux ainsi délimités sont droits et alignés les uns à côté des autres.Advantageously, the multichannel tube is an extruded tube of low height, of the order of a few millimeters at most, in particular between 1 and 3 millimeters. According to one embodiment of the invention, the multichannel tube comprises a plurality of walls, and these walls define a set of channels which extend from one longitudinal end of said multichannel tube to the other. Advantageously, the channels thus delimited are straight and aligned one beside the other.

Selon une autre caractéristique de l'invention, les deux plaques formant un canal du premier circuit de l'échangeur de chaleur sont assemblées l'une à l'autre au moins par leur périphérie, notamment par un bord périphérique de ces plaques. Le premier circuit comprenant plusieurs canaux de ce type, deux plaques formant un premier canal du premier circuit et deux plaques formant un deuxième canal dudit premier circuit communiquent entre eux par des collets emmanchés l'un dans l'autre et assemblés de manière étanche. Le volume interne de canaux adjacents est ainsi mis en relation fluidique.According to another characteristic of the invention, the two plates forming a channel of the first circuit of the heat exchanger are assembled to one another at least by their periphery, in particular by a peripheral edge of these plates. The first circuit comprising several channels of this type, two plates forming a first channel of the first circuit and two plates forming a second channel of said first circuit communicate with each other by collars fitted into one another and assembled in a sealed manner. Internal channel volume adjacent sites is thus placed in a fluid relationship.

Chaque plaque entrant dans la formation d'un canal du premier circuit comporte deux orifices placés à chacune des extrémités longitudinales du canal et délimité chacun par un collet qui s'étend, une fois ladite plaque assemblée avec une plaque similaire pour former ledit canal, vers l'extérieur dudit canal, c'est-à-dire vers l'extérieur du volume interne délimité par deux plaques formant un canal.Each plate entering into the formation of a channel of the first circuit comprises two orifices placed at each of the longitudinal ends of the channel and each delimited by a collar which extends, once said plate is assembled with a similar plate to form said channel, towards outside said channel, that is to say towards the outside of the internal volume delimited by two plates forming a channel.

Selon un mode de réalisation de l'invention, les plaques qui forment, par assemblage, le premier circuit, comprennent également un ou des renforts qui délimitent des passages de circulation du fluide caloporteur, ces renforts étant situés dans la portion centrale de la plaque appelée cuvette.According to one embodiment of the invention, the plates which form, by assembly, the first circuit, also comprise one or more reinforcements which delimit circulation passages for the heat transfer fluid, these reinforcements being located in the central portion of the plate called bowl.

Selon une autre caractéristique de l'invention, le contact entre les éléments formant le premier circuit et les éléments formant le deuxième circuit est réalisé entre au moins une portion plane d'une plaque formant une partie d'un canal du premier circuit et au moins une partie d'une face extérieure d'un tube multicanaux formant le deuxième circuit.According to another characteristic of the invention, the contact between the elements forming the first circuit and the elements forming the second circuit is made between at least one flat portion of a plate forming part of a channel of the first circuit and at least a part of an outer face of a multichannel tube forming the second circuit.

Selon un aspect de l'invention, une direction selon laquelle s'étend au moins un canal formant le deuxième circuit dudit échangeur de chaleur et une direction passant par orifices ménagés à chaque extrémité longitudinale d'une plaque sont sensiblement perpendiculaires entre elles.According to one aspect of the invention, a direction in which extends at least one channel forming the second circuit of said heat exchanger and a direction passing through orifices formed at each longitudinal end of a plate are substantially perpendicular to each other.

L'ensemble, ou la série, de premiers orifices et l'ensemble, ou la série, de deuxièmes orifices forment respectivement, une fois l'ensemble des canaux assemblés de manière étanche par lesdits collets, un premier passage tubulaire et second un passage tubulaire qui relient entre eux l'ensemble des volumes interne des canaux.The set, or the series, of first orifices and the set, or the series, of second orifices respectively form, once the set of channels are assembled in a sealed manner by said collars, a first tubular passage and a second tubular passage which interconnect all the internal volumes of the channels.

Selon un mode de réalisation de l'invention, chaque plaque entrant dans la formation d'un canal du premier circuit comprend au moins une nervure qui délimite au moins un passage de circulation du fluide caloporteur. Une telle nervure présente également une fonction de renfort mécanique du canal. Selon un exemple, chaque nervure a sensiblement la forme d'un "V", formant ainsi un chevron.According to one embodiment of the invention, each plate entering the formation of a channel of the first circuit comprises at least one rib which defines at least one passage for circulation of the heat transfer fluid. Such a rib also has a function of mechanical reinforcement of the channel. According to one example, each rib has substantially the shape of a "V", thus forming a chevron.

Dans l'empilement intercalé des canaux et tubes multicanaux, chaque extrémité des tubes multicanaux dépasse de bords situés à la périphérie des plaques constitutives des canaux. On peut ainsi raccorder les tubes multicanaux à des boîtes collectrices sans entrer en interférence avec les plaques.In the interposed stack of multichannel channels and tubes, each end of the multichannel tubes protrudes from edges located at the periphery of the plates constituting the channels. Multichannel tubes can thus be connected to manifolds without interfering with the plates.

Selon l'invention, chaque plaque entrant dans la formation d'un canal du premier circuit comprend au moins une partie plane en contact avec une face extérieure d'un tube multicanaux. On garantit ainsi le transfert des calories du fluide caloporteur liquide vers le fluide réfrigérant supercritique, ou en sens contraire.According to the invention, each plate entering into the formation of a channel of the first circuit comprises at least one planar part in contact with an outer face of a multichannel tube. This guarantees the transfer of calories from the liquid heat transfer fluid to the supercritical coolant, or in the opposite direction.

L'invention vise également un circuit de fluide caloporteur ou un circuit de fluide réfrigérant supercritique pour un véhicule automobile, caractérisée en ce que l'un et/ou l'autre de ces circuits comprend un échangeur de chaleur tel que détaillé ci-dessus.The invention also relates to a heat transfer fluid circuit or a supercritical refrigerant fluid circuit for a motor vehicle, characterized in that one and / or the other of these circuits comprises a heat exchanger as detailed above.

D'autres caractéristiques, détails et avantages de l'invention ressortiront plus clairement à la lecture de la description donnée ci-après à titre indicatif, en relation avec des dessins dans lesquels :

  • la figure 1 est une vue en perspective extérieure de deux plaques entrant dans la formation d'un canal du premier circuit d'un échangeur de chaleur selon l'invention,
  • la figure 2 est une vue en perspective rapprochée d'un détail de l'assemblage de deux canaux du premier circuit d'un échangeur de chaleur selon l'invention,
  • la figure 3 est une vue en perspective de l'assemblage des canaux formant le premier circuit et des tubes formant le deuxième circuit d'un échangeur de chaleur selon l'invention,
  • la figure 4 est une vue schématique en perspective d'un tube multicanaux entrant dans la formation du deuxième circuit d'un échangeur de chaleur selon l'invention,
  • la figure 5 est une vue rapprochée d'un détail du tube multicanaux représenté à la figure 4,
  • la figure 6 est une vue en perspective de l'assemblage de deux éléments du premier circuit et d'un élément du deuxième circuit d'un échangeur de chaleur selon l'invention,
  • la figure 7 est une vue schématique en perspective des deux circuits d'un échangeur selon l'invention, assemblés,
  • et la figure 8 est une vue schématique de côté d'un échangeur de chaleur complet selon l'invention.
Other characteristics, details and advantages of the invention will emerge more clearly on reading the description given below by way of indication, in relation to the drawings in which:
  • the figure 1 is an external perspective view of two plates forming part of a channel of the first circuit of a heat exchanger according to the invention,
  • the figure 2 is a close-up perspective view of a detail of the assembly of two channels of the first circuit of a heat exchanger according to the invention,
  • the figure 3 is a perspective view of the assembly of the channels forming the first circuit and the tubes forming the second circuit of a heat exchanger according to the invention,
  • the figure 4 is a schematic perspective view of a multichannel tube forming part of the second circuit of a heat exchanger according to the invention,
  • the figure 5 is a close-up view of a detail of the multichannel tube shown in figure 4 ,
  • the figure 6 is a perspective view of the assembly of two elements of the first circuit and one element of the second circuit of a heat exchanger according to the invention,
  • the figure 7 is a schematic perspective view of the two circuits of an exchanger according to the invention, assembled,
  • and the figure 8 is a schematic side view of a complete heat exchanger according to the invention.

Il faut tout d'abord noter que les figures exposent l'invention de manière détaillée pour la mettre en œuvre, lesdites figures pouvant bien entendu servir à mieux définir l'invention le cas échéant.It should first of all be noted that the figures set out the invention in detail in order to implement it, said figures being of course able to serve to better define the invention if necessary.

Dans la suite de la description, la dénomination "intérieur" se réfère aux volumes dans lesquels circulent soit le fluide caloporteur soit le fluide réfrigérant.In the remainder of the description, the name “interior” refers to the volumes in which either the coolant or the coolant circulates.

La figure 1 montre une vue en perspective extérieure deux plaques 1 entrant dans la formation d'un canal A du premier circuit d'un échangeur de chaleur 100 selon l'invention, apte à être parcouru par un fluide caloporteur tel qu'un liquide glycolé, par exemple. Il faut comprendre ici qu'un canal A de ce premier circuit est formé de l'assemblage de ces deux plaques 1 tel que représenté par la figure 1.The figure 1 shows an external perspective view of two plates 1 entering the formation of a channel A of the first circuit of a heat exchanger 100 according to the invention, capable of being traversed by a heat transfer fluid such as a glycol liquid, for example . It should be understood here that a channel A of this first circuit is formed by the assembly of these two plates 1 as represented by the figure 1 .

Chaque plaque 1 est une plaque mince, avantageusement réalisée par emboutissage d'un matériau métallique de manière à former une cuvette 10 (visible sur la figure 2) de faible profondeur délimitée par un fond 12 et, en périphérie, par un bord 11. A titre indicatif, l'épaisseur de chaque plaque 1 est avantageusement de l'ordre de quelques dixièmes de millimètre, typiquement, mais de manière non limitative, 3/10e à 7/10e de millimètre. La profondeur de la cuvette 10 est avantageusement de l'ordre de quelques dixièmes de millimètre à environ 1 millimètre. Le bord 11, surélevé par rapport au fond 12 de la cuvette 10 lorsque l'on regarde la partie intérieure de la plaque 1, forme un flan 110 de faible largeur, sensiblement parallèle au fond 12, et s'étendant vers l'extérieur de la cuvette 10. Une fois les deux plaques 1 assemblées pour délimiter un canal A, l'épaisseur de celui-ci mesurée au droit des cuvettes 10 est comprise entre 1 et 3 millimètres.Each plate 1 is a thin plate, advantageously produced by stamping a metallic material so as to form a cup 10 (visible on the figure 2 ) of shallow depth delimited by a bottom 12 and, in periphery, by an edge 11. As an indication, the thickness of each plate 1 is advantageously of the order of a few tenths of a millimeter, typically, but in a non-limiting manner, 3/10 th to 7/10 th of a millimeter. The depth of the bowl 10 is advantageously of the order of a few tenths of a millimeter to about 1 millimeter. The edge 11, raised relative to the bottom 12 of the bowl 10 when looking at the inner part of the plate 1, forms a blank 110 of small width, substantially parallel to the bottom 12, and extending outwards from the bowl 10. Once the two plates 1 assembled to delimit a channel A, the thickness of the latter measured in line with the bowls 10 is between 1 and 3 millimeters.

Selon le mode de réalisation, non exclusif, présenté par les figures, chaque plaque 1 a sensiblement la forme générale d'un hexagone dont deux côtés parallèles 1a et 1b sont plus longs que les autres côtés, les longueurs desdits autres côtés étant sensiblement égales entre elles.According to the non-exclusive embodiment shown in the figures, each plate 1 has substantially the general shape of a hexagon of which two parallel sides 1a and 1b are longer than the other sides, the lengths of said other sides being substantially equal between they.

Chaque plaque 1 est également percée de deux orifices, ci-après nommé premier orifice 13a et deuxième orifice 13b. Dans l'exemple illustré par les figures, les orifices 13a et 13b ont une forme oblongue et sont placés sensiblement à chaque extrémité de la plaque 1, sensiblement espacés de la longueur des côtés parallèles 1a et 1b. Ils sont également placés de telle manière que la plaque 1 présente au moins un plan de symétrie P. Dans l'exemple illustré par les figures, le plan de symétrie P est sensiblement perpendiculaire aux côtés parallèles de plus grande longueur 1a et 1b, et passe par le milieu de ces derniers.Each plate 1 is also pierced with two orifices, hereinafter referred to as the first orifice 13a and second orifice 13b. In the example illustrated by the figures, the orifices 13a and 13b have an oblong shape and are placed substantially at each end of the plate 1, substantially spaced apart the length of the parallel sides 1a and 1b. They are also placed in such a way that the plate 1 has at least one plane of symmetry P. In the example illustrated by the figures, the plane of symmetry P is substantially perpendicular to the parallel sides of greater length 1a and 1b, and passes through the middle of these.

Chaque orifice 13a, 13b présente, à sa périphérie, un collet 13c qui s'étend vers l'extérieur de la plaque 1, à l'opposé du sens dans lequel s'étend le bord 11 par rapport au fond 12 de la cuvette 10. Entre le premier orifice 13a et le deuxième orifice 13b, chaque plaque 1 peut présenter également une pluralité de nervures 14 dont chacune forme, au sein de la cuvette 10, une saillie dont la hauteur est légèrement inférieure à la profondeur de la cuvette 10. Selon le mode de réalisation de l'invention illustré par les figures, les nervures 14 sont agencées symétriquement par rapport au plan de symétrie P précédemment évoqué, et elles ont chacune la forme d'un "V". En d'autres termes, ces nervures 14 forment chacune un chevron. Par leur forme, ces nervures 14 ont un rôle de renfort mécanique et de rigidification de chaque plaque 1. Elles ont également un autre rôle qui sera précisé plus loin. Entre les nervures 14, le fond 12 de chaque plaque 1 est sensiblement plan.Each orifice 13a, 13b has, at its periphery, a collar 13c which extends outwardly of the plate 1, opposite the direction in which the edge 11 extends relative to the bottom 12 of the bowl 10 Between the first orifice 13a and the second orifice 13b, each plate 1 may also have a plurality of ribs 14 each of which forms, within the bowl 10, a projection whose height is slightly less than the depth of the bowl 10. According to the embodiment of the invention illustrated by the figures, the ribs 14 are arranged symmetrically with respect to the previously mentioned plane of symmetry P, and they each have the shape of a "V". In other words, these ribs 14 each form a chevron. By their shape, these ribs 14 have a role of mechanical reinforcement and stiffening of each plate 1. They also have another role which will be specified later. Between the ribs 14, the bottom 12 of each plate 1 is substantially flat.

Pour former un canal A du premier circuit de l'échangeur de chaleur selon l'invention destiné à être parcouru par le fluide caloporteur liquide, deux plaques 1 telles que décrites ci-dessus sont assemblées par leur bord 11. Plus précisément, les flans 110 des deux plaques 1 sont accolés et brasés entre eux, de manière à ce que les deux cuvettes 10 de chaque plaque 1 forment, ensemble, un volume interne V dans lequel le fluide caloporteur liquide est appelé à circuler. Etant donnée la profondeur de chaque cuvette 10, la hauteur d'un canal A est typiquement, mais de manière non limitative, de l'ordre de 1 à 3 millimètres. Il ressort toutefois de la description des plaques 1 qui précède que le volume interne V délimité par l'assemblage de ces dernières communique avec l'extérieur par les orifices 13a, 13b portés par celles-ci.To form a channel A of the first circuit of the heat exchanger according to the invention intended to be traversed by the liquid heat transfer fluid, two plates 1 as described above are assembled by their edge 11. More precisely, the blanks 110 of the two plates 1 are contiguous and brazed together, so that the two cups 10 of each plate 1 together form an internal volume V in which the liquid heat transfer fluid is required to circulate. Given the depth of each bowl 10, the height of a channel A is typically, but not limited to, of the order of 1 to 3 millimeters. However, it emerges from the description of the plates 1 above that the internal volume V delimited by the assembly of the latter communicates with the outside through the orifices 13a, 13b carried by them.

Selon une caractéristique, le premier circuit de l'échangeur de chaleur selon l'invention est constitué d'un empilement ou succession de plusieurs canaux tels que décrits ci-dessus. La figure 2 montre un détail de l'assemblage de deux plaques immédiatement adjacentes constitutives de deux canaux formant le premier circuit. Il apparaît sur la figure 2 que, lors de l'assemblage des deux canaux A adjacents, les orifices 13a ménagés sur les plaques 1 se trouvent en regard l'un de l'autre, et que leurs collets 13c, qui s'étendent alors l'un vers l'autre, coopèrent pour former une portion de passage permettant de faire communiquer entre eux les volumes internes V formés au sein des canaux adjacents. Lors de l'assemblage de ces canaux entre eux, les collets 13c, brasés ensemble, forment donc un passage étanche entre les volumes internes V desdits canaux délimités chacun par une paire de plaques 1. On notera que le collet 13c d'un premier canal A est emmanché dans le collet 13c d'un second canal A immédiatement adjacent. Ces passages étanches successifs forment, avec la succession des canaux assemblés pour former le premier circuit de l'échangeur de chaleur selon l'invention, un premier passage tubulaire 15a délimité par la série de premiers orifices 13a visible sur la figure 3 à travers lequel le fluide caloporteur peut circuler en vue d'entrer ou de sortir de chaque canal formant le premier circuit.According to one characteristic, the first circuit of the heat exchanger according to the invention consists of a stack or succession of several channels as described above. The figure 2 shows a detail of the assembly of two immediately adjacent plates constituting two channels forming the first circuit. It appears on the figure 2 that, during the assembly of the two adjacent channels A, the orifices 13a formed on the plates 1 are located opposite one another, and that their collars 13c, which then extend towards one another towards the other, cooperate to form a passage portion making it possible to make the internal volumes V formed within the adjacent channels communicate with each other. When these channels are assembled together, the collars 13c, brazed together, therefore form a sealed passage between the internal volumes V of said channels each delimited by a pair of plates 1. It will be noted that the collar 13c of a first channel A is fitted into the collar 13c of a second immediately adjacent channel A. These successive sealed passages form, with the succession of channels assembled to form the first circuit of the heat exchanger according to the invention, a first tubular passage 15a delimited by the series of first orifices 13a visible on the figure 3 through which the heat transfer fluid can flow in order to enter or leave each channel forming the first circuit.

Chaque plaque 1 présentant un premier orifice 13a et un deuxième orifice 13b à chacune de ses extrémités, un second passage tubulaire 15b est formé de la même manière que le premier passage tubulaire 15a, comme le montre la figure 3, c'est-à-dire par la série de deuxième orifices 13b. Ces passages tubulaires 15a et 15b forment, avec la succession des volumes internes V des canaux A assemblés pour former le premier circuit de l'échangeur de chaleur 100 selon l'invention, le premier circuit de fluide caloporteur. On notera ici l'intérêt qu'il y a à ménager les premier orifices 13a et les deuxième orifices 13b de telle manière qu'ils soient aussi éloignés que possible l'un de l'autre sur chaque plaque 1, de manière à augmenter autant que possible la longueur parcourue par le fluide caloporteur et, ainsi, de manière à améliorer l'efficacité de l'échange thermique.Each plate 1 having a first orifice 13a and a second orifice 13b at each of its ends, a second tubular passage 15b is formed in the same way as the first tubular passage 15a, as shown in FIG. figure 3 , that is to say through the series of second orifices 13b. These tubular passages 15a and 15b form, with the succession of the internal volumes V of the channels A assembled to form the first circuit of the heat exchanger 100 according to the invention, the first heat transfer fluid circuit. It will be noted here the advantage that there is in providing the first orifices 13a and the second orifices 13b so that they are as far apart as possible from each other on each plate 1, so as to increase as much as possible the length traveled by the heat transfer fluid and, thus, so as to improve the efficiency of the heat exchange.

Un autre rôle des nervures 14 ménagées sur les plaques 1 apparaît également ici. La présence de ces nervures, en saillie au sein des différents volumes internes V des canaux A empilés, permet de perturber la circulation laminaire du fluide caloporteur en créant des turbulences de ce fluide au sein du volume interne V. Il s'ensuit une optimisation de la surface de contact entre le fluide caloporteur circulant et la surface interne des canaux A et, ainsi, une amélioration de l'efficacité de l'échange thermique par la génération de turbulences favorisant l'échange thermique entre le fluide liquide et les plaques 1 délimitant le canal A.Another role of the ribs 14 formed on the plates 1 also appears here. The presence of these ribs, projecting within the various internal volumes V of the stacked channels A, makes it possible to disrupt the laminar circulation of the heat transfer fluid by creating turbulence of this fluid within the internal volume V. This results in an optimization of the heat transfer fluid. the contact surface between the circulating heat transfer fluid and the internal surface of the channels A and, thus, an improvement in the efficiency of the heat exchange by the generation of turbulence promoting the heat exchange between the liquid fluid and the plates 1 delimiting channel A.

La figure 3 illustre également la présence d'une pluralité de tubes multicanaux B intercalés entre chaque canaux A du premier circuit. Les tubes multicanaux B sont raccordés de manière étanche à un ou des manchons d'entrée 7a et de sortie 7b tous deux raccordés à une unique bride 50. Entre ces manchons d'entrée 7a et de sortie 7b et les tubes multicanaux B se trouve une boîte collectrice 51 constituée d'un empilement de composants. L'un de ces composants est une première plaque 5 sur une face de laquelle les manchons d'entrée 7a et de sortie 7b sont directement solidarisés. Un autre composant est formé par une plaque intermédiaire 52 prise en sandwich entre la première plaque 5 et une plaque collectrice 6. Cette dernière comprend des bords longitudinaux repliés pour enserrer la première plaque et la maintenir ainsi l'empilement de composants.The figure 3 also illustrates the presence of a plurality of multichannel tubes B interposed between each channels A of the first circuit. The multichannel tubes B are connected in a sealed manner to one or more inlet 7a and outlet 7b sleeves, both connected to a single flange 50. Between these inlet 7a and outlet 7b sleeves and the multichannel tubes B is a collector box 51 consisting of a stack of components. One of these components is a first plate 5 on one side of which the sleeves input 7a and output 7b are directly secured. Another component is formed by an intermediate plate 52 sandwiched between the first plate 5 and a collector plate 6. The latter comprises folded longitudinal edges to grip the first plate and thus maintain the stack of components.

Les figures 4 et 5 montrent des vues schématiques d'un tube multicanaux B entrant dans la formation du deuxième circuit de l'échangeur de chaleur 100 selon l'invention. Selon le mode de réalisation de l'invention, non exclusif, illustré par les figures, un tube multicanaux B, qui est avantageusement un tube extrudé, se présente sous la forme d'une plaque rigide 20 de forme générale sensiblement rectangulaire de grand côté L, de petit côté l, et d'épaisseur d. Selon l'invention, cette plaque comprend, en son épaisseur, un ensemble de parois 22, par exemple parallèle, de largeur h1 qui s'étendent, selon une direction D1 parallèle à celle du grand côté L du tube multicanaux B, d'une extrémité longitudinale à l'autre de la plaque 20.The figures 4 and 5 show schematic views of a multichannel tube B entering the formation of the second circuit of the heat exchanger 100 according to the invention. According to the embodiment of the invention, which is non-exclusive, illustrated by the figures, a multichannel tube B, which is advantageously an extruded tube, is in the form of a rigid plate 20 of generally substantially rectangular shape with a large side L , of small side l, and of thickness d. According to the invention, this plate comprises, in its thickness, a set of walls 22, for example parallel, of width h1 which extend, in a direction D1 parallel to that of the large side L of the multichannel tube B, of a longitudinal end to the other of the plate 20.

Les parois 22 forment des ponts de matière entre deux grandes faces extérieures 33 et 34 définies par le grand côté L et le petit côté l. Les parois 22 délimitent entre elles, selon la direction D1, un ensemble de canaux 21 alignés parallèles entre eux qui s'étendent, également selon la direction D1, d'une extrémité longitudinale de la plaque 20 à l'autre, de manière à déboucher aux deux extrémités de celle-ci. En section selon un plan perpendiculaire au grand côté L du tube multicanaux B, et comme le montre plus précisément la figure 5, chacun des canaux 21 a une forme sensiblement oblongue dont la hauteur H est supérieure à la largeur h et légèrement inférieure à l'épaisseur d de la plaque rigide 20. Selon une direction D3 sensiblement parallèle à celle du petit côté l de la plaque rigide 20, les canaux 21 sont donc espacés entre eux de la largeur h1 de chaque paroi 22, et chacune de ces parois joue un rôle de renfort mécanique de l'ensemble du tube multicanaux B, les canaux 21 étant alignés côte à côte.The walls 22 form bridges of material between two large outer faces 33 and 34 defined by the large side L and the small side l. The walls 22 define between them, in the direction D1, a set of channels 21 aligned parallel to each other which extend, also in the direction D1, from one longitudinal end of the plate 20 to the other, so as to open at both ends of it. In section along a plane perpendicular to the long side L of the multichannel tube B, and as more precisely shown in figure 5 , each of the channels 21 has a substantially oblong shape, the height H of which is greater than the width h and slightly less than the thickness d of the rigid plate 20. In a direction D3 substantially parallel to that of the short side l of the rigid plate. 20, the channels 21 are therefore spaced from each other by the width h1 of each wall 22, and each of these walls acts as a mechanical reinforcement for the assembly of the multichannel tube B, the channels 21 being aligned side by side.

La figure 6 illustre plus précisément l'assemblage entre deux canaux A du premier circuit de l'échangeur de chaleur 100 selon l'invention et un tube multicanaux B du deuxième circuit de cet échangeur de chaleur. Il apparaît sur cette figure que le tube multicanaux B est intercalé entre les deux canaux A, et que le tube multicanaux B dépasse, en chacune de ses extrémités, des bords longitudinaux 1a, 1b de plus grande longueur de chacun des canaux A. Plus précisément, et comme il a été évoqué plus haut, la paroi extérieure de la cuvette 10 ménagée dans chaque plaque 1 entrant dans la formation d'un canal A est, entre les nervures 14 que cette plaque porte, sensiblement plan. Selon l'invention, au moins une portion 35 de ces parties planes est en contact direct, notamment par brasage, avec une face extérieure 33 ou 34 du tube multicanaux B immédiatement adjacent.The figure 6 illustrates more precisely the assembly between two channels A of the first circuit of the heat exchanger 100 according to the invention and a tube multichannel B of the second circuit of this heat exchanger. It appears in this figure that the multichannel tube B is interposed between the two channels A, and that the multichannel tube B protrudes, at each of its ends, from the longitudinal edges 1a, 1b of greater length of each of the channels A. More precisely , and as mentioned above, the outer wall of the bowl 10 formed in each plate 1 entering the formation of a channel A is, between the ribs 14 that this plate carries, substantially flat. According to the invention, at least a portion 35 of these flat parts is in direct contact, in particular by brazing, with an outer face 33 or 34 of the multichannel tube B immediately adjacent.

Avantageusement, les dimensions des collets 13c des canaux A adjacents et l'épaisseur d de chaque tube multicanaux B sont définies de telle manière que l'insertion de ces tubes entre deux canaux A adjacents soit possible en laissant un espace de faible dimensions tel qu'il soit possible de réaliser alors un contact direct par simple soudage ou brasage entre tube multicanaux B du deuxième circuit et plaques 1 des canaux du premier circuit. Selon un mode de réalisation préféré de l'invention, non limitatif, l'épaisseur d de chaque plaque 20 est de l'ordre de 1 à 3 millimètres, correspondant ainsi à l'espace qui sépare deux canaux A immédiatement adjacent du premier circuit.Advantageously, the dimensions of the collars 13c of the adjacent channels A and the thickness d of each multichannel tube B are defined in such a way that the insertion of these tubes between two adjacent channels A is possible while leaving a small space such that it is then possible to make direct contact by simple welding or brazing between multichannel tube B of the second circuit and plates 1 of the channels of the first circuit. According to a preferred embodiment of the invention, which is not limiting, the thickness d of each plate 20 is of the order of 1 to 3 millimeters, thus corresponding to the space which separates two channels A immediately adjacent to the first circuit.

Comme le montrent les figures 3, 7 et 8, les premier et deuxième circuits d'un échangeur de chaleur 100 selon l'invention sont formés d'une succession de canaux A et de tubes multicanaux B intercalés entre deux canaux adjacents, les passages tubulaires 15a et 15b définissant une entrée et une sortie du fluide caloporteur dans le premier circuit et, ainsi une direction générale de circulation dudit fluide dans ledit premier circuit.As the figures 3 , 7 and 8 , the first and second circuits of a heat exchanger 100 according to the invention are formed by a succession of channels A and multichannel tubes B interposed between two adjacent channels, the tubular passages 15a and 15b defining an inlet and an outlet of the heat transfer fluid in the first circuit and thus a general direction of circulation of said fluid in said first circuit.

Le fluide réfrigérant supercritique circule dans les canaux 21 des tubes multicanaux B dans le deuxième circuit. En référence aux figures 7 et 8, une joue d'entrée 3 est combinée à une première plaque 1 de manière à définir une zone d'entrée du fluide caloporteur dans le premier circuit. La joue d'entrée 3 présente une épaisseur supérieure à l'épaisseur d'une plaque 1 et forme ainsi un renfort mécanique pour l'échangeur de chaleur. La joue d'entrée 3 reçoit une tubulure d'entrée 31 délimitant également l'un des passages tubulaires 15a ou 15b.The supercritical refrigerant circulates in the channels 21 of the multichannel tubes B in the second circuit. With reference to figures 7 and 8 , an inlet cheek 3 is combined with a first plate 1 so as to define an inlet zone for the coolant in the first circuit. The entry cheek 3 has a thickness greater than the thickness of a plate 1 and thus forms a reinforcement mechanical for the heat exchanger. The inlet cheek 3 receives an inlet pipe 31 also delimiting one of the tubular passages 15a or 15b.

L'échangeur de chaleur 100 selon l'invention comprend encore une joue de sortie 4 assemblée de manière étanche à une plaque 1. Cette joue de sortie 4 supporte une tubulure de sortie 41 délimitant le second passage tubulaire 15b. Le fluide caloporteur entre donc dans le premier circuit par la tubulure d'entrée 31, circule dans le premier passage tubulaire 15, puis se réparti dans chaque canaux A, pour être collecté par le second passage tubulaire 15b, et finalement sortir de l'échangeur de chaleur 100 par la tubulure de sortie 41.The heat exchanger 100 according to the invention also comprises an outlet cheek 4 assembled in a sealed manner to a plate 1. This outlet cheek 4 supports an outlet pipe 41 delimiting the second tubular passage 15b. The heat transfer fluid therefore enters the first circuit through the inlet pipe 31, circulates in the first tubular passage 15, then is distributed in each channels A, to be collected by the second tubular passage 15b, and finally out of the exchanger heat 100 through the outlet pipe 41.

Selon le mode de réalisation avantageux illustré par les figures, l'entrée et la sortie du circuit du fluide caloporteur sont situées chacune à une extrémité de l'échangeur de chaleur 100 selon l'invention, selon la direction d'empilement de l'ensemble canaux-tubes multicanaux.According to the advantageous embodiment illustrated by the figures, the inlet and outlet of the heat transfer fluid circuit are each located at one end of the heat exchanger 100 according to the invention, in the direction of stacking of the assembly. multichannel ducts-tubes.

De même, les tubes multicanaux B sont raccordés, en chacune de leurs extrémités, à une boîte collectrice 51 telle que décrite en rapport avec la figure 3 ci-dessus. Une seule de deux boîtes collectrice est relié à un ensemble de manchons d'entrée et de sortie 7a et 7b, qui assurent la circulation du fluide réfrigérant supercritique au sein du deuxième circuit de l'échangeur de chaleur selon l'invention. On comprend ainsi que les manchons d'entrée et de sortie 7a et 7b du deuxième circuit sont situés d'un même côté de l'échangeur de chaleur, définissant ainsi une configuration "en U" de ce deuxième circuit. La boîte collectrice dépourvue de manchons d'entrée et de sortie 7a et 7b, dite boîte collectrice de récupération 53, assure la récupération du fluide réfrigérant supercritique arrivant par une partie des canaux 21 du tubes multicanaux B. Cette boîte collectrice dirige alors ce fluide de manière à ce qui pénètre dans l'autre partie des canaux 21 pour se diriger vers la boîte collectrice 51, dite boîte collectrice d'entrée.Likewise, the multichannel tubes B are connected, at each of their ends, to a manifold 51 as described in connection with figure 3 above. Only one of two manifolds is connected to a set of inlet and outlet sleeves 7a and 7b, which ensure the circulation of the supercritical refrigerant fluid within the second circuit of the heat exchanger according to the invention. It will thus be understood that the inlet and outlet sleeves 7a and 7b of the second circuit are located on the same side of the heat exchanger, thus defining a "U" configuration of this second circuit. The collector box devoid of inlet and outlet sleeves 7a and 7b, called the recovery collector box 53, ensures the recovery of the supercritical refrigerant fluid arriving through part of the channels 21 of the multichannel tubes B. This collector box then directs this fluid from so that what enters the other part of the channels 21 to move towards the manifold 51, called the inlet manifold.

Selon l'invention, et comme le montre la figures 6, une direction générale D2 de circulation du fluide caloporteur dans les canaux A constitutifs du premier circuit est définie par une droite passant par le premier orifice 13a et le deuxième orifice 13b d'une même plaque 1. Cette direction D2 est perpendiculaire, ou sensiblement perpendiculaire, à la direction générale D1 de circulation du fluide réfrigérant supercritique dans les tubes multicanaux B, définie par l'orientation des canaux 21 des tubes multicanaux B. En d'autres termes, au moins un canal A du premier circuit et au moins un tube multicanaux B du deuxième circuit sont agencés dans l'échangeur de chaleur 100 de manière à ce que leur parcours de fluide respectif soit perpendiculaire, ou sensiblement perpendiculaire.According to the invention, and as shown in figures 6 , a general direction D2 of circulation of the heat transfer fluid in the channels A constituting the first circuit is defined by a straight line passing through the first orifice 13a and the second orifice 13b of the same plate 1. This direction D2 is perpendicular, or substantially perpendicular, to the general direction D1 of circulation of the supercritical refrigerant fluid in the multichannel tubes B , defined by the orientation of the channels 21 of the multichannel tubes B. In other words, at least one channel A of the first circuit and at least one multichannel tube B of the second circuit are arranged in the heat exchanger 100 so as to that their respective fluid path is perpendicular, or substantially perpendicular.

Le processus de réalisation d'un échangeur de chaleur 100 selon l'invention peut être le suivant : empilement des canaux A et tubes multicanaux B de manière à former un corps d'échange thermique, formant respectivement le premier et le deuxième circuit de fluides, pré-assemblage des boîtes collectrices 51, pré-assemblage des tubulures d'entrée 31 et de sortie 41 sur l'empilement de tubes multicanaux B, pré-assemblage des manchons d'entrée 7a et de sortie 7 sur l'empilement des canaux A, puis brasage ou soudage de l'ensemble dans un four approprié.The process for producing a heat exchanger 100 according to the invention can be as follows: stacking the channels A and multichannel tubes B so as to form a heat exchange body, respectively forming the first and the second fluid circuit, pre-assembly of the manifolds 51, pre-assembly of the inlet 31 and outlet 41 pipes on the stack of multichannel tubes B, pre-assembly of the inlet 7a and outlet 7 sleeves on the stack of channels A , then brazing or welding of the assembly in a suitable furnace.

L'invention permet donc de réaliser un échangeur monobloc simple et dont les éléments dans lesquels circule le fluide réfrigérant supercritique sont conçus pour supporter les hautes pressions nécessaires à la mise en œuvre de ce dernier, tout en offrant des performances élevés d'échange thermique. Selon le mode de réalisation décrit, les opérations de fabrication des différents éléments des circuits de l'échangeur de chaleur comme l'emboutissage des plaques formant les canaux du circuit du fluide caloporteur, l'extrusion des tubes multicanaux, le brasage des éléments assemblés, les étapes de pré-assemblage et l'étape finale de brasage sont, en outre, simples, et d'un coût maîtrisé pour une réalisation en grande série. Un tel échangeur de chaleur 100 reste donc économiquement viable pour une production en grande série, comme c'est notamment le cas dans le monde de l'automobile de série. De plus, un tel échangeur est d'un encombrement restreint, ce qui facilite son intégration dans un véhicule, et permet son installation sur une large variété de véhicules.The invention therefore makes it possible to produce a simple one-piece exchanger in which the elements in which the supercritical refrigerant circulates are designed to withstand the high pressures necessary for the implementation of the latter, while offering high performance of heat exchange. According to the embodiment described, the manufacturing operations of the various elements of the heat exchanger circuits such as the stamping of the plates forming the channels of the heat transfer fluid circuit, the extrusion of the multichannel tubes, the brazing of the assembled elements, the pre-assembly steps and the final brazing step are, moreover, simple, and cost under control for mass production. Such a heat exchanger 100 therefore remains economically viable for mass production, as is notably the case in the world of mass-produced automobiles. In addition, such an exchanger is compact, which facilitates its integration into a vehicle, and allows its installation on a wide variety of vehicles.

Il est bien sûr à noter que l'invention ne saurait se réduire aux moyens et configurations décrits et illustrés. En particulier, si, dans l'exemple décrit par le présent document, les manchons d'entrée et de sortie 7a et 7b du deuxième circuit de l'échangeur de chaleur 100 selon l'invention sont situés du même côté de cet échangeur, définissant une circulation du fluide réfrigérant en "U", une telle configuration n'est pas exclusive, et les manchons d'entrée et de sortie du deuxième circuit peuvent être agencés pour définir une configuration en "I" sans que cela nuise à l'invention. Dans ce cas de figure, un manchon d'entrée 7a est solidarisé à une première boîte collectrice 51, et un manchon de sortie 7b est solidarisé à une seconde boîte collectrice 53. Toute autre configuration respective des manchons ou tubulures d'entrée et de sortie du premier ou du deuxième circuit peut également être mise en œuvre, tant qu'elle contribue à optimiser la circulation des fluides caloporteur et réfrigérant supercritique et, ainsi, l'efficacité de l'échange thermique. De même, toute forme générale autre qu'hexagonal peut être donnée aux plaques 1 entrant dans la formation des canaux A, dans la mesure où les spécificités de ces plaques décrites ici au regard de l'invention sont respectées.It should of course be noted that the invention cannot be reduced to the means and configurations described and illustrated. In particular, if, in the example described by this document, the inlet and outlet sleeves 7a and 7b of the second circuit of the heat exchanger 100 according to the invention are located on the same side of this exchanger, defining circulation of the refrigerant fluid in a "U", such a configuration is not exclusive, and the inlet and outlet sleeves of the second circuit can be arranged to define an "I" configuration without this harming the invention . In this case, an inlet sleeve 7a is secured to a first manifold 51, and an outlet sleeve 7b is secured to a second manifold 53. Any other respective configuration of the inlet and outlet sleeves or pipes of the first or of the second circuit can also be implemented, as long as it contributes to optimizing the circulation of the coolant and supercritical refrigerant fluids and, thus, the efficiency of the heat exchange. Likewise, any general shape other than hexagonal can be given to the plates 1 entering into the formation of the channels A, insofar as the specificities of these plates described here with regard to the invention are respected.

Claims (14)

  1. Heat exchanger (100) comprising a first circuit intended to be passed through by a liquid heat-transfer fluid and a second circuit intended to be passed through by a supercritical coolant, characterized in that the first circuit is formed by at least one channel (A) delimited by at least two plates (1), and in that the second circuit is formed by at least one multichannel tube (B), said at least one channel (A) being in contact with said at least one multichannel tube (B), wherein each plate (1) involved in the formation of a channel (A) of the first circuit comprises two orifices (13a, 13b) placed at each of its longitudinal ends; characterized in that each of the orifices is delimited by a neck (13c) which extends, once said plate is assembled with a similar plate to form said channel (A), outward from said channel (A), wherein the channels (A) of the first circuit communicate with one another by the necks (13c) fitted together by press-fitting.
  2. Heat exchanger according to Claim 1, characterized in that the first circuit comprises several channels (A), in that the second circuit comprises several multichannel tubes (B), and in that the multichannel tubes (B) and channels (A) are stacked alternately one on top of the other.
  3. Heat exchanger according to one or the other of Claims 1 and 2, characterized in that each multichannel tube (B) is an extruded tube whose thickness (d) is between 1 and 3 millimetres.
  4. Heat exchanger according to any one of Claims 1 to 3, characterized in that each multichannel tube (B) comprises a plurality of walls (22) which delimit between them a set of channels (21) which extend from one end of said multichannel tube (B) to the other.
  5. Heat exchanger according to Claim 4, characterized in that the walls (22) and channels (21) of each multichannel tube (B) extend, in a general direction (D1), straight and aligned parallel alongside one another.
  6. Heat exchanger according to Claim 5, characterized in that the directions (D1) in which at least one channel (21) forming the second circuit of said exchanger and a direction (D2) passing through orifices (13a, 13b) formed at each longitudinal end of a plate (1) extend are substantially at right angles to one another.
  7. Heat exchanger according to any one of Claims 1 to 6, characterized in that two plates (1) forming a channel (A) of the first circuit are assembled tightly with one another at least by their edge (11).
  8. Heat exchanger according to Claim 1, characterized in that a plurality of first orifices (13a) and a plurality of second orifices (13b) form, respectively, once all of the channels (A) are assembled tightly by said necks (13c), a first tubular passage (15a) and a second tubular passage (15b) which link all the internal volumes (V) of the channels (A) to one another.
  9. Heat exchanger according to any one of Claims 1 to 8, characterized in that each plate (1) involved in the formation of a channel (A) of the first circuit comprises at least one rib (14) which delimits at least one heat-transfer fluid circulation passage.
  10. Heat exchanger according to Claim 9, characterized in that each rib (14) is substantially "V" shaped.
  11. Heat exchanger according to any one of Claims 1 to 13, characterized in that, in the interleaved stack of the channels (A) and multichannel tubes (B), each end of the multichannel tubes (B) extends beyond edges (11) situated at the periphery of the plates (1) constituting the channels (A).
  12. Heat exchanger according to any one of Claims 1 to 11, characterized in that each plate (1) involved in the formation of a channel (A) of the first circuit of said exchanger comprises at least one flat part (35) in contact with an outer face (33) of a multichannel tube (B).
  13. Heat-transfer fluid circuit for a motor vehicle, characterized in that it comprises a heat exchanger (100) according to any one of Claims 1 to 12.
  14. Supercritical coolant circuit for a motor vehicle, characterized in that it comprises a heat exchanger (100) according to any one of Claims 1 to 12.
EP16728027.0A 2015-06-12 2016-06-09 Heat exchanger for motor vehicle Active EP3308096B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1555347A FR3037387B1 (en) 2015-06-12 2015-06-12 HEAT EXCHANGER FOR MOTOR VEHICLE
PCT/EP2016/063188 WO2016198536A1 (en) 2015-06-12 2016-06-09 Heat exchanger for motor vehicle

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EP3308096A1 EP3308096A1 (en) 2018-04-18
EP3308096B1 true EP3308096B1 (en) 2020-12-16

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FR3084698B1 (en) * 2018-07-31 2020-07-24 Safran Aircraft Engines TURBOMACHINE HEAT EXCHANGER

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JP2007017133A (en) * 2005-07-11 2007-01-25 Denso Corp Heat exchanger
ES2349909B1 (en) * 2008-10-21 2011-09-28 Valeo Termico, S.A. HEAT EXCHANGER OF STACKED PLATES.
JP5206830B2 (en) * 2011-03-25 2013-06-12 ダイキン工業株式会社 Heat exchanger
DE102012224353A1 (en) * 2012-12-21 2014-06-26 Behr Gmbh & Co. Kg Heat exchanger

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EP3308096A1 (en) 2018-04-18
WO2016198536A1 (en) 2016-12-15
FR3037387B1 (en) 2019-07-19

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