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EP3062054B1 - Échangeur thermique, en particulier pour un vehicule automobile - Google Patents

Échangeur thermique, en particulier pour un vehicule automobile Download PDF

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Publication number
EP3062054B1
EP3062054B1 EP16153327.8A EP16153327A EP3062054B1 EP 3062054 B1 EP3062054 B1 EP 3062054B1 EP 16153327 A EP16153327 A EP 16153327A EP 3062054 B1 EP3062054 B1 EP 3062054B1
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EP
European Patent Office
Prior art keywords
fluid
plate
heat exchanger
turbulence generating
generating elements
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16153327.8A
Other languages
German (de)
English (en)
Other versions
EP3062054A1 (fr
Inventor
Yavuz Altunkaya
Tobias Fetzer
Wilhelm Grauer
Boris Kerler
Jonas Kühndel
Marco Renz
Volker Velte
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.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
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Filing date
Publication date
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP3062054A1 publication Critical patent/EP3062054A1/fr
Application granted granted Critical
Publication of EP3062054B1 publication Critical patent/EP3062054B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • 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
    • F28D7/16—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 being arranged in parallel spaced relation
    • F28D7/1684—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 being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • 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
    • F28D9/0081—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 a single plate-like element ; the conduits for one heat-exchange medium being integrated in one single plate-like element
    • 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
    • F28F1/38—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 and being staggered to form tortuous fluid passages
    • 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 present invention relates to a heat exchanger, in particular for a motor vehicle.
  • GB 24242645 A discloses a heat exchanger with the features in the preamble of claim 1.
  • a heat exchanger or heat exchanger is commonly referred to a device that transfers heat from one stream to another stream.
  • Heat exchangers are used, for example, in motor vehicles to cool the fresh air charged by means of an exhaust-gas turbocharger in a fresh-air system interacting with the internal combustion engine of the motor vehicle.
  • the fresh air to be cooled is introduced into the heat exchanger, where it interacts thermally with a likewise introduced into the heat exchanger coolant and emits heat in this way to the coolant.
  • Such a heat exchanger may be configured, for example, as a plate heat exchanger and have a plurality of plate assemblies each having a pair of plates stacked in a stacking direction, wherein between the plates of a plate pair, a coolant path is formed through which a coolant is passed.
  • the medium to be cooled for example in a turbocharger charged charge air
  • the medium to be cooled can be fluidically separated from the coolant, so that the coolant through the plates of the plate assembly in thermal interaction can be set with the charge air to be cooled.
  • additional rib structures may be provided between adjacent plate assemblies which increase the interaction area of the plates available for the thermal interaction. Such constructions are known in the art as so-called "rib-tube heat exchanger".
  • the GB 2 424 2645 A discloses a heat exchanger having a plurality of pairs of plates disposed adjacent to each other along a stacking direction and each comprising a first and a second plates defining in the stacking direction a first fluid path through which a first fluid can flow. Between two plate pairs adjacent in the stacking direction, a second fluid path is formed to flow through with a second fluid. In at least one second fluid path, a plurality of turbulence generating elements are arranged, which are connected at one end to a first plate of a pair of plates bounding the second fluid path and are connected at the other end to a second plate of a plate pair adjacent in the stacking direction.
  • a heat exchanger comprises a plurality of plate pairs, which are adjacent and spaced apart along a stacking direction.
  • the plate pairs each comprise a first and a second plates, which define in the stacking direction a fluid path through which a first fluid can flow.
  • This fluid may be fresh air, for example, which has been charged by an exhaust gas turbocharger in a fresh air system of an internal combustion engine and thereby heated and should therefore be cooled in the heat exchanger.
  • a second fluid path for flowing through a second fluid which is fluidically separated and thermally connected to the first fluid path, is formed
  • Coolant may be that causes cooling of the same by thermal interaction with the fresh air flowing through the first fluid path.
  • a plurality of turbulence-generating elements are arranged in at least one second fluid path, which are connected at one end to a first plate of a plate pair bounding the second fluid path.
  • the turbulence generating elements are connected to a second plate of a plate pair adjacent in the stacking direction.
  • the inventive measures lead to a comparison with conventional heat exchangers improved thermal interaction of the two fluids together. As a result, therefore, a heat exchanger with improved efficiency is realized. Therefore, all second fluid paths are particularly preferably equipped with turbulence generation elements. At the same time, the turbulence generating elements, when properly designed, can act as a support structure for the first and second plates of the plate pairs, which improves the rigidity of the heat exchanger.
  • the plurality of turbulence-generating elements are arranged in a grid-like manner with at least two raster lines in a plan view of the first or second plate.
  • a line direction is defined by the at least two raster lines.
  • the turbulence generating elements are in the plan view of the first Plate longitudinally formed and each extend along a longitudinal direction.
  • longitudinal direction is meant that a length of the respective turbulence generating element - measured in the longitudinal direction - is at least five times, preferably ten times, most preferably twenty times, a maximum width measured transversely to the longitudinal direction.
  • the longitudinal direction extends substantially transversely to the row direction.
  • a plurality of subchannels in the first and second fluid path can be produced, wherein the first or second fluid can also be exchanged between the individual subchannels via the intermediate spaces present in the longitudinal direction between the individual turbulence generation elements.
  • this leads to a uniform flow through the respective fluid path to form a plurality of vortices, resulting in an improved heat exchange between the two, flowing through the first and second fluid path fluids.
  • the turbulence-generating elements can be formed integrally on the first plate and-alternatively or additionally-on the second plate.
  • the production of the heat exchanger offers the use of an additive manufacturing process, which significantly simplifies the entire production process of the heat exchanger according to the invention and should therefore be explained in more detail below.
  • At least the plate pairs and the turbulence generating elements may be manufactured by means of an additive manufacturing method.
  • additive manufacturing process in the present case includes all manufacturing processes which build up the building component directly from a computer model. Such production processes are also known by the name “rapid forming".
  • rapid forming are in particular production processes For fast and flexible production of components using tool-free production directly from CAD data.
  • the use of an additive manufacturing method allows the production of the heat exchanger according to the invention without component-specific investment means such as tool molds or the like. and almost no geometric restrictions.
  • heat exchangers manufactured using other methods usually have a large number of small parts such as sealing elements or fastening elements such as struts or the like, for example, in a wide variety of shapes and sizes. Therefore, all components of the heat exchanger are preferably produced by means of the additive manufacturing process.
  • the heat exchanger may be integrally formed.
  • Such a one-piece design is formed in particular when using the above-proposed additive manufacturing process, in particular laser melting.
  • a one-piece design of the heat exchanger eliminates the very costly and therefore costly attaching the individual components of the heat exchanger together.
  • the additive manufacturing process may include laser melting.
  • a laser melting process is used for producing the plate pairs and the turbulence generating elements, preferably for producing the entire heat exchanger.
  • the components of the heat exchanger can be made directly from 3D CAD data. Basically, the components of the heat exchanger in the laser melting process without tools and in layers based on the three-dimensional CAD model associated with the heat exchanger.
  • turbulent flow patterns in the fluids flowing through the second fluid paths can be generated by forming the turbulence generation elements as guide vanes projecting from the first and second plates, in particular in the stacking direction.
  • At least one turbulence generating element is curved along the longitudinal direction. This preferably applies to all turbulence generation elements of at least one second fluid channel, particularly preferably to all turbulence generation elements of the heat exchanger. By means of this measure, the formation of eddy currents in the fluid paths is further enhanced.
  • two adjacent first and / or second turbulence generation elements of a raster line are designed such that a distance measured transversely to the longitudinal direction between these two turbulence generation elements decreases at least in sections along the longitudinal direction.
  • all turbulence generation elements of the same raster line are each provided in pairs with such a geometry.
  • the heat exchanger is designed such that the first fluid flows through the first fluid path substantially along a first main flow direction.
  • This first main flow direction extends substantially orthogonal to a second main flow direction, through which the second fluid flows substantially in the second fluid path.
  • the two fluids flow at an angle of substantially 90 ° to each other through the first and second fluid paths, respectively. This measure leads to an increased thermal interaction between the two fluids and thus to an improved efficiency of the heat exchanger.
  • each first fluid path present in the heat exchanger can have a common first fluid inlet for introducing the first fluid into the first fluid path and a fluid outlet for discharging the first fluid from the first fluid path.
  • the first fluid inlet and the first fluid outlet are in the plan view of the first and second plate of the first and second fluid path limiting plate pair substantially opposite.
  • each second fluid path has a second fluid inlet for introducing the second fluid into the second fluid path and a common fluid outlet for discharging the second fluid from the same second fluid path, the second fluid inlet and the second fluid outlet also being in plan view of the first plate in the second fluid path Essentially opposite.
  • the respective common fluid inlet or joint fluid outlet may be formed integrally on the respective plate pairs and contain a respective passage opening. This may in particular apply to the particularly preferred case that the plate pairs with the first and second plates are part of a flat tube; In this case, the passage openings forming a fluid inlet or fluid outlet can be formed in the flat tubes.
  • first fluid inlet and the second fluid inlet are arranged in the plan view of the first plate substantially orthogonal to each other.
  • the first fluid outlet and the second fluid outlet can also be arranged substantially orthogonal to one another in the plan view of the first plate.
  • Both measures taken alone or in combination result in that - with respect to the plan view of the plate pairs - the first fluid outlet are arranged on a first side of the first and second plate.
  • This page may for example be a longitudinal or transverse side of the plate.
  • the second fluid inlet is then - preferably rotated by 90 ° - arranged on the transverse or longitudinal side.
  • first and second fluid inlets This facilitates the assembly of the first and second fluid inlets, in particular when a multiplicity of plate pairs stacked on one another is present, and consequently a multiplicity of first and second fluid inlets is required for the individual fluid paths.
  • first fluid distributor which distributes the first fluid to all first fluid inlets and, in the process, communicates fluidically with these.
  • a second fluid distributor Twisted on the transverse or longitudinal side, ie preferably by 90 °, a second fluid distributor can be provided in the same way, which communicates fluidically with all second fluid inlets to distribute the second fluid to the second fluid paths.
  • the two fluid distributors can thus be mounted on the outside of different sides of the plate pairs, which significantly reduces the design effort for the realization of the two fluid manifold.
  • a first and a second fluid collector on the remaining longitudinal or transverse side.
  • a first fluid collector may be provided which fluidically communicates with all first fluid outlets for collecting the first fluid after flowing through the first fluid paths.
  • a second fluid collector is provided on the last remaining transverse or longitudinal side, which communicates fluidically with all second fluid outlets for collecting the second fluid after flowing through the second fluid paths.
  • first and second plates of at least one pair of plates are part of a flat tube delimiting the first fluid path.
  • the distance between stack-flat adjacent flat tubes may be in this scenario serve as a space for a respective second fluid path.
  • all plate pairs can each be part of a flat tube delimiting the first fluid path.
  • a first plate of a respective plate pair and the second plate adjacent in the stacking direction, which is consequently assigned to the plate pair adjacent in the stacking direction to be formed as a flat tube which delimits the second fluid path.
  • all second fluid paths can be realized in the form of flat tubes described above.
  • the first and second plates of the plate pairs can be designed to be complementary to one another, a channel structure being formed on the inner sides facing the respective other plate.
  • a channel structure may for example have a meander-like or geometry.
  • other geometries are conceivable that can be generated in the plates in a particularly simple and flexible manner by using the aforementioned additive manufacturing process.
  • FIG. 1 shows an example of a heat exchanger 1 according to the invention in a longitudinal section along a stacking direction S of the plate pairs 2 of the heat exchanger, the FIG. 2 a pair of plates 2 of the heat exchanger 1 in a perspective view.
  • the heat exchanger 1 comprises a plurality of plate pairs 2 which are adjacent and spaced apart along a stacking direction S and each comprising a first and a second plates 3a, 3b.
  • the first and second plates 3a, 3b of the plate pairs 2 each delimit in the stacking direction S a first fluid path 4a, through which a first fluid F 1 can flow.
  • a main flow direction of the first fluid F 1 is in a direction indicated by Z.
  • a second fluid path 4 b for flowing through with a second fluid F 2 formed.
  • a main flow direction of the second fluid F 2 extends in a direction designated L perpendicular to the plane of the drawing, that is orthogonal to the main flow direction of the first fluid F 1 .
  • a plurality of turbulence generating elements 6 are arranged, which are connected at one end to a first plate 3a of the respective second fluid path 4b limiting plate pair 2 and the other end connected to a second plate 3b of a plate pair 2 adjacent in the stacking direction S ,
  • This second plate 3b also defines the fluid passage 4b with the turbulence generating elements 6.
  • the turbulence generating elements 6 are integrally formed on both the first plate 3a and the second plate 3b to which they are connected endwise.
  • the plate pairs 2 with the first and second plates 3a, 3b and the turbulence generating elements 6 are manufactured by an additive manufacturing method.
  • all other components of the heat exchanger 1 can be produced by means of such an additive manufacturing process.
  • the use of an additive manufacturing method allows the production of the heat exchanger 1 with almost no geometric restrictions.
  • the additive manufacturing process it is possible to construct the design of the heat exchanger 1 functionally bound - and no longer tool-bound.
  • the individual components of the heat exchanger 1, such as the pairs of plates 2 and the adjacent pairs of plates 2 connecting turbulence generating elements 6 can be integrally formed directly in the course of the manufacturing process to each other.
  • turbulence generating elements 6 can be made with almost any geometry.
  • the additive manufacturing process may also include the so-called laser melting process.
  • a laser melting process is used for producing the plate pairs 2 and the Turbulence generating elements 6, in an extreme case for producing the entire heat exchanger 1.
  • the above-mentioned components of the heat exchanger can be produced directly from 3D CAD data.
  • the said components of the heat exchanger 1 during the laser melting process are manufactured without tools and in layers on the basis of a three-dimensional CAD model assigned to the heat exchanger 1.
  • the turbulence generating elements 6 may be formed in each case as from the first plate 3a and second plate 3b projecting vanes 8.
  • the formation of the turbulence-generating elements 6 in the form of guide vanes 8 assists in the formation of particularly turbulent flow patterns in the second fluid F 2 flowing through the second fluid paths 4 b. This leads to an improved efficiency of the heat exchanger 1.
  • FIG. 3 can be seen, the plurality of turbulence generating elements 6 in the plan view of the first plate 3a grid-like with multiple raster lines 9 - in FIG. 3
  • three such raster lines 9 are shown - arranged on this.
  • a row direction Z is defined.
  • the turbulence generating elements 6 are formed longitudinally in the stacking direction S on the first plate 3a and each extending along a longitudinal direction L which is substantially transverse to the row direction Z.
  • a length l of the turbulence generating elements 6 is at least five times a maximum width b of the same turbulence generating element 6.
  • the length is preferably at least ten times, more preferably at least twenty times the maximum width b.
  • the length I in the longitudinal direction L and the width b in the row direction Z are measured.
  • the width b measured in the row direction Z can be determined according to FIG. 3 vary along the longitudinal direction L.
  • At least one turbulence generating element 6 is formed curved in the top direction in the stacking direction S on the first plate 3a in the longitudinal direction L. This is especially preferred as in FIG. 3 shown for all turbulence generating elements 6 of the heat exchanger 1.
  • the turbulence elements 6 with a curved geometry can be produced in a particularly simple manner by using the aforementioned additive manufacturing method, in particular laser melting. This proves to be particularly advantageous if, as shown in the example, a large number of turbulence generating elements 6 to be used, which can then be used as a support structure for the plates 3a, 3b of the plate pairs 2.
  • Two adjacent turbulence generation elements 6 of a raster line 9 are preferably designed such that a distance a measured transversely to the longitudinal direction L between these two turbulence generation elements 6 decreases along the longitudinal direction L at least in sections.
  • all turbulence generating elements 6 of the same raster line 9 can be provided in pairs with such a geometry.
  • the turbulence generation elements 6 of a respective raster line 9 which are adjacent in a specific line direction Z can form element pairs 12.
  • the two turbulence generating elements 6 of a respective pair of elements 12 can with respect to an axis of symmetry A, in the plan view of the first or second plate 3a, 3b runs along the longitudinal direction L, be arranged axisymmetric to each other.
  • a particularly advantageous arrangement geometry of the turbulence generating elements 6 is realized, which causes a particularly pronounced turbulence in the first and second fluid F 2 and thus to an improved heat exchange between the two fluids F1, F 2 when flowing through the fluid paths 4a, 4b in the heat exchanger 1 leads.
  • Such an axisymmetric arrangement of a multiplicity of element pairs 12 can also be realized in a particularly simple and precise manner by using an additive manufacturing method.
  • the heat exchanger 1 can be formed such that the first fluid F 1 flows through the first fluid path 4a substantially along a first main flow direction R 1 .
  • the first main flow direction R 1 extends substantially orthogonal to a second main flow direction R 2 , through which the second fluid F 2 flows in the second fluid path 4 b.
  • Each first fluid path 4a may have a common first fluid inlet 13 for introducing the first fluid F 1 into the first fluid paths 4a and a common first fluid outlet 14 for discharging the first fluid F 1 from the first fluid paths 4a.
  • the first fluid inlet 13 and the first fluid outlet 14 - whose position is in FIG.
  • each second fluid path may have 4b 4b a common second fluid inlet 15 for introducing the second fluid F2 into the second fluid path 4b and a common second fluid outlet 16 for discharging the second fluid F2 from the second fluid paths.
  • the common second fluid inlet 15 and the common second fluid outlet 16 are likewise opposite one another in the plan view of the first plate 3a.
  • the first fluid inlet 13 and the second fluid inlet 15 with respect to the plan view of the first plate 3a in the stacking direction S are arranged substantially rotated by 90 ° to each other.
  • first fluid outlet 14 and the second fluid outlet 16 are arranged substantially orthogonal to each other with respect to the plan view of the first plate 2 along the stacking direction S.
  • first plate 3a with two longitudinal sides 17a, 17b and two transverse sides 17c, 17d
  • the common first fluid inlet 13 and the common first fluid outlet 14 in the region of opposite longitudinal sides 17a, 17b may be arranged
  • the common second fluid inlet 15 and the common second fluid outlet 16 can be arranged in the region of the opposite transverse sides 17c, 17d.
  • the first and second plates 3a, 3b of the plate pairs 2 may each be part of a flat tube defining the first and / or second fluid path 4a, 4b (not shown). This allows a production of the heat exchanger 1 in flat construction.
  • the two plates 3a, 3b of a respective plate pair 2 may be formed complementary to each other.
  • a channel structure may be formed on the inner side 11 facing the respective other plate.
  • Such a channel structure may for example have a meander-like or geometry.
  • other geometries are conceivable, which can be produced in the plates 3a, 3b in a particularly simple and flexible manner by using the aforementioned additive manufacturing process.
  • the heat exchanger 1 may be formed in one piece. Such a one-piece design is formed in particular when using the above-proposed additive manufacturing process, in particular laser melting. In a one-piece design of the heat exchanger eliminates the very costly and therefore costly attaching the individual components of the heat exchanger together. It is understood that in the case of a one-piece construction of the heat exchanger 1, the terms used herein such as e.g. "first plate 3a" remain valid.

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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)

Claims (12)

  1. Echangeur de chaleur (1), en particulier pour un véhicule automobile,
    - avec une pluralité de paires de plaques (2) qui sont agencées de manière contiguë les unes aux autres le long d'un sens d'empilage (S) et comportent respectivement une première et une seconde plaque (3a, 3b) qui délimitent, dans le sens d'empilage (S), une première voie de fluide (4a) pouvant être traversée par un premier fluide (F1),
    - dans lequel, entre deux paires de plaques (2) contiguës dans le sens d'empilage (S), une seconde voie de fluide (4b) est réalisée pour la traversée avec un second fluide,
    - dans lequel une pluralité d'éléments de génération de turbulence (6) sont agencés dans au moins une seconde voie de fluide (4b), de préférence dans toutes les secondes voies de fluide (4b), lesquels sont reliés, à une extrémité, à une première plaque (3a) d'une paire de plaques (2) délimitant la seconde voie de fluide (4b) et sont reliés, à l'autre extrémité, à une seconde plaque (3b) d'une paire de plaques (2) contiguë dans le sens d'empilage (S),
    - dans lequel la pluralité d'éléments de génération de turbulence (6) sont agencés, dans une vue de dessus, sur la première ou seconde plaque (3a, 3b) comme une trame avec au moins deux lignes de trame (9) sur la première et/ou seconde plaque (3a, 3b),
    - dans lequel un sens de ligne (Z) est défini par les au moins deux lignes de trame (9),
    - dans lequel les éléments de génération de turbulence (6) sont réalisés de manière longitudinale, dans la vue de dessus, le long du sens d'empilage (S) sur la première plaque (3a, 3b) et s'étendent respectivement le long d'un sens longitudinal (L) qui s'étend transversalement au sens de ligne (Z),
    - dans lequel une longueur (I) d'au moins un élément de génération de turbulence (6), de préférence de tous les éléments de génération de turbulence (6), s'élève au moins au quintuple, de préférence au moins au décuple, au maximum de préférence au moins au vingtuple, d'une largeur (b) maximale de l'élément de génération de turbulence (6) respectif,
    - dans lequel la longueur (I) est mesurée dans le sens longitudinal (L) et la largeur (b), dans le sens de ligne (Z),
    caractérisé en ce que
    les éléments de génération de turbulence (6) contigus dans le sens de ligne (Z) réalisent des paires d'éléments (12), dans lequel les deux éléments de génération de turbulence (6) d'une paire d'éléments (12) respective sont agencés de manière symétrique à l'axe l'une à l'autre par rapport à un axe de symétrie (A) qui s'étend, dans la vue de dessus, sur la première ou seconde plaque le long du sens longitudinal (L).
  2. Echangeur de chaleur selon la revendication 1,
    caractérisé en ce que
    les éléments de génération de turbulence (6) sont façonnés d'un seul tenant au niveau de la première et/ou seconde plaque (3a, 3b).
  3. Echangeur de chaleur selon la revendication 1 ou 2,
    caractérisé en ce que
    - au moins les paires de plaques (2) et les éléments de génération de turbulence (6) sont fabriqués au moyen d'un procédé de fabrication additif, et/ou que
    - l'échangeur de chaleur (1) est réalisé d'un seul tenant.
  4. Echangeur de chaleur selon la revendication 3,
    caractérisé en ce que
    le procédé de fabrication additif comporte des procédés de fusion laser.
  5. Echangeur de chaleur selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce que
    les éléments de génération de turbulence (6) sont réalisés respectivement en tant qu'aubes de guidage dépassant de la première et seconde plaque (3a, 3b).
  6. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que
    au moins un élément de génération de turbulence (6), de préférence tous les éléments de génération de turbulence (6), sont réalisés de manière courbée dans le sens longitudinal (L).
  7. Echangeur de chaleur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    deux éléments de génération de turbulence (6) contigus d'une ligne de trame (9) sont réalisés de telle manière qu'une distance (a) mesurée transversalement au sens longitudinal (L) diminue au moins par sections entre ces deux éléments de génération de turbulence (6) le long du sens longitudinal (L).
  8. Echangeur de chaleur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    l'échangeur de chaleur est réalisé de telle manière que le premier fluide (F1) traverse la première voie de fluide (4a) sensiblement le long d'un premier sens d'écoulement principal (R1) qui s'étend sensiblement orthogonalement à un second sens d'écoulement principal (R2) par lequel le second fluide (F2) s'écoule dans la seconde voie de fluide (4b).
  9. Echangeur de chaleur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    - chaque première voie de fluide (4a) présente une première entrée de fluide (13) commune pour l'introduction du premier fluide (F1) les premières voies de fluide (4a) et une première sortie de fluide (14) commune pour l'évacuation du premier fluide (F1) hors des premières voies de fluide (4a), dans lequel la première entrée de fluide (13) commune et la première sortie de fluide (14) commune sont opposées, dans la vue de dessus, sur la première plaque (3a),
    - chaque seconde voie de fluide (4b) présente une seconde entrée de fluide (15) commune pour l'introduction du second fluide (F2) dans les secondes voies de fluide (4b) et une seconde sortie de fluide (16) commune pour l'évacuation du second fluide (F2) hors des secondes voies de fluide (4b), dans lequel la seconde entrée de fluide (15) commune et la seconde sortie de fluide (16) commune sont opposées, dans la vue de dessus, sur la première plaque (3a).
  10. Echangeur de chaleur selon la revendication 9,
    caractérisé en ce que
    - la première entrée de fluide (13) commune et la seconde entrée de fluide (15) commune sont agencées, dans la vue de dessus, sur la première plaque (3a) sensiblement orthogonalement l'une à l'autre, et/ou que
    - la première sortie de fluide (14) et la seconde sortie de fluide (16) sont agencées, dans la vue de dessus, sur la première plaque (3a) sensiblement orthogonalement l'une à l'autre.
  11. Echangeur de chaleur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    les première et seconde plaques (3a, 3b) d'au moins une paire de plaques (2) font partie d'un tube plat délimitant la première et/ou seconde voie de fluide (4a, 4b).
  12. Echangeur de chaleur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    les première et seconde plaques (3a, 3b) d'une paire de plaques (2) sont réalisées de manière complémentaire l'une à l'autre, dans lequel une structure de canal est réalisée sur le côté intérieur (11), tourné vers l'autre plaque (3a, 3b) respective, des deux plaques (3a, 3b).
EP16153327.8A 2015-02-26 2016-01-29 Échangeur thermique, en particulier pour un vehicule automobile Active EP3062054B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015203472.0A DE102015203472A1 (de) 2015-02-26 2015-02-26 Wärmetauscher, insbesondere für ein Kraftfahrzeug

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EP3062054A1 EP3062054A1 (fr) 2016-08-31
EP3062054B1 true EP3062054B1 (fr) 2018-10-24

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1024621B1 (fr) * 2016-10-03 2018-05-24 Safran Aero Boosters S.A. Matrice d'echangeur de chaleur air huile de turboreacteur
FR3057057B1 (fr) * 2016-10-05 2019-08-09 Valeo Systemes Thermiques Procede de fabrication par impression en trois dimensions d'un echangeur thermique a plaques
US20180292146A1 (en) * 2017-04-10 2018-10-11 United Technologies Corporation Partially additively manufactured heat exchanger
WO2019073277A1 (fr) 2017-10-13 2019-04-18 Volvo Truck Corporation Échangeur de chaleur et procédé de fabrication additive d'échangeur de chaleur
JP6663899B2 (ja) * 2017-11-29 2020-03-13 本田技研工業株式会社 冷却装置
DE102018219626A1 (de) * 2018-11-16 2020-05-20 Mahle International Gmbh Wärmeübertrager
JP7208053B2 (ja) * 2019-02-19 2023-01-18 株式会社Subaru 冷却装置
DE202019102083U1 (de) 2019-04-11 2019-04-18 Mahle International Gmbh Kühlfluiddurchströmte Wellrippenanordnung und Kraftfahrzeugbauteil
DE102019110262A1 (de) * 2019-04-18 2020-10-22 Hans Quack Platten-Rippen-Wärmeübertrager
CN113834368B (zh) * 2021-10-22 2023-07-25 河北工业大学 一种三维变截面扰流柱结构、换热板及换热器芯体

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GB892534A (en) * 1957-10-24 1962-03-28 Richard Kablitz Improvements in and relating to heat exchangers
JPS55152397A (en) * 1979-05-18 1980-11-27 Hitachi Ltd Plate type heat exchanger
DE3521914A1 (de) * 1984-06-20 1986-01-02 Showa Aluminum Corp., Sakai, Osaka Waermetauscher in fluegelplattenbauweise
FR2795166B1 (fr) * 1999-06-21 2001-09-07 Valeo Thermique Moteur Sa Echangeur de chaleur a plaques, en particulier pour le refroidissement d'une huile de vehicule automobile
GB0427362D0 (en) * 2004-12-14 2005-01-19 Sustainable Engine Systems Ltd Heat exchanger
GB2424265A (en) * 2005-02-16 2006-09-20 Timothy Frank Brise Heat Exchanger including Heat Exchange Tubes with Integral Fins
ITPN20080042A1 (it) * 2008-05-20 2009-11-21 Parker Hiross Spa Essicatore di gas compresso a refrigerazione con scambiatori di calore perfezionati
US9404691B2 (en) * 2013-07-24 2016-08-02 Cale Patrick Collins Kaupp Condensing heat recovery unit for a portable fluid heater

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DE102015203472A1 (de) 2016-09-01

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