EP3394545B1 - Wärmetauscher, insbesondere für ein kraftfahrzeug - Google Patents

Wärmetauscher, insbesondere für ein kraftfahrzeug Download PDF

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Publication number
EP3394545B1
EP3394545B1 EP16826393.7A EP16826393A EP3394545B1 EP 3394545 B1 EP3394545 B1 EP 3394545B1 EP 16826393 A EP16826393 A EP 16826393A EP 3394545 B1 EP3394545 B1 EP 3394545B1
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EP
European Patent Office
Prior art keywords
frame
fluid
frames
heat exchanger
internal
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EP16826393.7A
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English (en)
French (fr)
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EP3394545A1 (de
Inventor
Isabelle Citti
Sébastien JACOPE
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Valeo Systemes Thermiques SAS
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Valeo Systemes Thermiques SAS
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28D7/1692—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 with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
    • F28F9/0253—Massive connectors, e.g. blocks; Plate-like connectors with multiple channels, e.g. with combined inflow and outflow channels

Definitions

  • the invention relates to the field of heat exchangers.
  • US 3,334,399 discloses a heat exchanger comprising the characteristics of the preamble of claim 1.
  • Such heat exchangers find particular application in motor vehicles. They can in particular constitute a gas cooler in which the refrigerant fluid such as CO 2 is cooled by a second fluid, such as liquid. Conversely, the second fluid can be cooled by the first fluid, for example in gaseous form, the heat exchanger is then commonly referred to as “Water chiller” in English.
  • Such heat exchangers can in particular be used in the thermal regulation of one or more batteries of an electric or hybrid vehicle.
  • the thermal regulation of the batteries is an important point because if the batteries are subjected to too cold temperatures, their autonomy can decrease significantly and if they are subjected to too high temperatures, there is a risk of thermal runaway which can go up to to the destruction of the battery, or even the motor vehicle.
  • a heat transfer fluid generally a coolant comprising a mixture of glycol water, which circulates within a heat exchanger in contact with the battery(ies).
  • the coolant can thus provide heat to the battery(ies) to heat them, this heat having been absorbed by the coolant for example during the heat exchange with the CO 2 circulating in the gas cooler.
  • the coolant can also, if necessary, absorb heat emitted by the battery(ies) in order to cool them and evacuate this heat to one or more other heat exchangers.
  • Such heat exchangers can also be used like any other gas cooler in an air conditioning circuit.
  • heat exchangers comprising a stack of plates allowing the circulation of the first fluid, such as the refrigerant fluid or refrigerant gas, and the second fluid such as the cooling liquid.
  • first fluid such as the refrigerant fluid or refrigerant gas
  • second fluid such as the cooling liquid
  • the subject of the invention is a heat exchanger, in particular for a motor vehicle, said exchanger comprising a heat exchange bundle defining circulation channels for at least one fluid.
  • Such frames allow, in a simple manner, circulation in at least two passes of at least one fluid, for example coolant, in the heat exchanger, thus improving the performance of the heat exchanger.
  • the heat exchange bundle which comprises a plurality of heat exchange tubes, is distinct from the frames.
  • the heat exchanger allows heat exchange between at least a first fluid and a second fluid, and comprises an alternating stack of first frames for receiving heat exchange tubes defining first circulation channels for the first fluid, and second frames respectively defining second circulation channels for the second fluid and respectively comprising said at least one internal bar.
  • the superimposed frames make it possible to create the flow path of the first fluid such as a refrigerant fluid, when the frames are assembled, preferably by brazing, and likewise, the superimposed frames make it possible to create the flow path of the second fluid such as coolant in particular on two opposite sides of the heat exchange bundle.
  • Such an architecture allows a simpler production of the heat exchanger as a whole which has a reduced bulk while having interesting properties in order to best resist high local pressures, in particular due to the circulation of CO 2 as refrigerant fluid in the first executives.
  • the heat exchanger is assembled by brazing.
  • Such a coating is commonly referred to as “clad” in the field of brazing metal parts, particularly aluminum.
  • the first fluid is a refrigerant fluid intended to circulate at high pressure such as CO 2 , also designated by R744 according to industrial nomenclature.
  • the heat exchanger 1 comprises a heat exchange bundle 3 allowing the heat exchange between the first fluid and the second fluid.
  • the heat exchange bundle 3 has a shape generally substantially parallelepiped.
  • the introduction of the second fluid into the heat exchange bundle 3 and the evacuation of the second fluid out of the heat exchange bundle 3 is shown schematically by way of example by the arrows F2 I for the introduction and F2 O for evacuation.
  • the heat exchange bundle 3 alternately comprises first circulation channels for the first fluid (not visible in the figures) and second circulation channels 9 for the second fluid (see figure 2 ).
  • the heat exchange tubes can be made by extrusion, for example in the form of flat tubes, advantageous in terms of size.
  • turbulators (not illustrated) of the flow of the second fluid can advantageously be arranged in the second circulation channels 9 defined by the second frames 15, thus improving the heat exchange of the two fluids.
  • a plurality of second frames 15 arranged between two successive first frames 13 form the spacers.
  • the stacking is done here approximately vertically.
  • the first frames 13 can be designated as tube frames.
  • Each second frame 15 can receive turbulators and this assembly forms another stage of the heat exchange bundle 3.
  • the first frames 13 and the second frames 15 are described in more detail below.
  • closure plates 17, 18, in particular at least one lower closure plate 17 and at least one upper closure plate 18, can be arranged on either side of the stack of first frames 13 and second frames 15, so as to close the heat exchange bundle 3.
  • the closing plates 17, 18 advantageously have a shape complementary to the shape of the first frames 13 and the second frames 15.
  • the heat exchanger 1 further comprises at least one collector box 19 for the first fluid arranged in fluid communication with the first circulation channels in the first frames 13.
  • the collector box 19 is, according to the example illustrated, arranged on an upper closing plate 18 placed at the top of the heat exchange bundle 3.
  • the collector box 19 can be arranged on the lower closing plate 17 placed at the bottom of the heat exchange bundle 3.
  • the same collector box 19 can be compartmentalized, so as to define on the one hand the introduction of the first fluid schematized by the arrow F1 I on the figure 1 and on the other hand the evacuation of the first fluid schematized by the arrow F1 O on the figure 1 .
  • the two tubes 21 are arranged on the same upper closure plate 18 as the collector box 19 for the first fluid.
  • the collector box 19 can be arranged on one side of the heat exchange bundle 3 and the tubes 21 can be arranged on the other side of the heat exchange bundle 3, thus allowing counter-current circulation of the two fluids.
  • the collector box 19 is arranged on the left while the pipes 21 are arranged on the right.
  • First frames called tube frames
  • first frames 13 they can be at least partially made of aluminum.
  • These first frames 13 can have a thickness of the order of a few millimeters, for example of the order of 1mm.
  • these first frames 13 can have the same thickness as the heat exchange tubes that they receive.
  • the thickness is considered in the direction of the height of the heat exchange bundle 3, we can also speak of the height of the first frames 13. This is the thickness in the stacking direction of the frames 13, 15.
  • the heat exchange tubes can be held in the first respective frames 13 before superposition of the different frames.
  • two adjacent heat exchange tubes arranged in a first frame 13 can communicate with each other at one end.
  • the first frames 13 are for example of generally rectangular shape.
  • frames could be provided having a general shape which is not rectangular, for example elliptical, or diamond-shaped.
  • the first frames 13 comprise means for putting the first fluid into fluid communication (not visible in the figures) of the first circulation channels of the first fluid with the collector box 19.
  • each first frame 13 are advantageously arranged in fluidic communication with the means of fluidic communication of the other first frames 13 of the heat exchange bundle 3 and with the collector box 19.
  • fluidic communication means are for example made in the form of recesses defining through openings for fluidic communication, into which the first circulation channels of the first fluid open, in particular the longitudinal ends, heat exchange tubes received in the first frames 13.
  • the first frames 13 also have guides 134 for the passage of the second fluid.
  • the first receiving frames 13 can be made by stamping cutting.
  • the second frames 15 can be at least partially made of aluminum.
  • the second frames 15 can be made by stamping cutting.
  • the second frames 15 have a thickness Th which is of the order of a few millimeters, for example of the order of 0.5mm to 4mm, preferably of the order of 2mm.
  • the thickness is here considered in the direction of the height of the heat exchange bundle 3, we can also speak of the height of the second frames 15. In this example it is the thickness in the direction of stacking of the frames 13, 15.
  • the thickness or height of the second frames 15 makes it possible to define the pitch between the first frames 13.
  • the second frames 15 When the second frames 15 receive turbulators (not shown), the second frames 15 are called turbulator frames or turbulator-carrying frames.
  • the thickness of the turbulators (not shown) can be substantially equal to the thickness Th of a second frame 15.
  • the second fluid can circulate in two passes, in a so-called “U” circulation, in each second frame 15.
  • the second frames 15 have two opposite edges 15A, 15B extending perpendicular to the general direction of flow of the second fluid and two other opposite edges 15C, 15D extending parallel to the general direction of the second fluid.
  • the general direction of flow of the second fluid here means the direction of the branches of the “U” in the case of two-pass circulation of the second fluid.
  • the second frames 15 advantageously have a shape similar to and complementary to the shape of the first frames 13.
  • the external contours of the first frames 13 and second frames 15 are practically identical so that the alternating stacking of the first frames 13 and second frames 15 forms a block.
  • the second frames 15 extend over the same length and over the same width as the first frames 13.
  • the heat exchanger 1 is preferably assembled by brazing.
  • the second frames 15 are intended to be assembled by brazing to the first frames 13.
  • the longitudinal edges 15C, 15D of the second frames 15 are intended to be assembled by brazing to the longitudinal edges of the first frames 13 and the lateral edges of the second frames 15 are intended to be assembled by brazing to the lateral edges of the first frames 13.
  • each second frame 15 defines an internal width and an internal length L (see figure 2 ).
  • internal length is meant the length L defined between the internal walls, facing the inside of the second frame 15, of the opposite side edges 15A and 15B.
  • the side edges of the second frames 15 can be slightly larger than the side edges of the first frames 13, so that when heat exchange tubes are received in the first frames 13, the ends of these exchange tubes thermal (not shown), rest on the peripheral edge of the side edges of the second frames 15.
  • the second frames 15 define in this case an internal length L less than the internal length defined by the internal space of the first frames 13.
  • the internal length L of a second frame 15 is defined relative to the surface of the second frame 15 which is actually crossed by the second fluid.
  • the second frames 15 each comprise at least one bar 150, arranged inside the respective second frame 15 so as to separate two circulation passes for the second fluid. It is therefore an internal strip 150.
  • the bar 150 makes it possible to shape the second circulation channel 9 defined by a second frame 15 substantially "U".
  • a second frame 15 comprises a single bar 150.
  • the turbulators are then advantageously arranged on either side of the or each internal bar 150.
  • the internal bar 150 therefore extends longitudinally from a side edge 15A of a second frame 15 towards the opposite side edge 15B but without reaching this opposite side edge 15B.
  • the internal bar 150 therefore extends longitudinally from a lateral edge 15A of a second frame 15 over a length l less than the internal length L of a second frame 15.
  • the width W of the internal bar 150 can be greater than or equal to, preferably strictly greater than the thickness Th of the second frame 15.
  • the strip 150 can also be described as a tab.
  • the bar 150 is substantially of the same thickness as the second frame 15.
  • the second frames 15, in particular the second intermediate frames 15 arranged between two first frames 13, present guides for the passage of the first fluid allowing its flow in the stack of the first frames 13 and second frames 15.
  • the second frames 15 respectively present means 152 for placing the second circulation channels 9 in fluid communication with each other on the one hand and with the pipes 21 for the second fluid on the other hand.
  • the fluid communication means 152 provided on the second frames 15 allow, in a simple manner, to collect the second fluid and distribute it in the second frames 15.
  • the through openings 152 are arranged on the same side of a second frame 15 in the longitudinal direction, that is to say here on the right or on the left, in a manner complementary to the arrangement of the tubes 21 on the same side of the heat exchange bundle 3.
  • the handles 153 of the second frames 15 are made in a similar manner to the handles 134 of the first frames 13 and are aligned with these handles 134 which allow the passage of the second fluid through the heat exchange bundle 3.
  • the figures show an example of producing the handles 153 of substantially rounded shape.
  • the fluid inlet 152 extends over a maximum fluid inlet length L1.
  • This maximum fluid inlet length L1 is, according to the particular embodiment illustrated, defined by the maximum length of the loop 153, at the level of the start of its formation on the second frame 15.
  • the internal bar 150 is arranged inside a second frame 15 so that the bar 150 is spaced by a lateral distance L2, here in the width direction, from the longitudinal edge 15C of the second frame 15 presenting the fluid inlet 152.
  • the central bar 150 is spaced by the same lateral distance L2 from each longitudinal edge 15C, 15D of the second frame 15.
  • This lateral distance L2 is considered in relation to the part of the edge, here the longitudinal edge 15C or 15D, which extends parallel to the bar 150, and not in relation to the loop 153 formed on the side of the longitudinal edge 15C or 15D.
  • the fluid inlet length L1 is strictly greater than the lateral distance L2 according to the relation (b'): L 1 > L 2
  • the lateral distance L2 is included in a range of the order of 15mm to 60mm.
  • each through opening 152 defines a fluidic communication area S1.
  • each through opening 152 is shaped so that the fluidic communication area S1 verifies a strict relationship: 0.1 ⁇ L 1 ⁇ L 3 ⁇ S 1 ⁇ 3 ⁇ L 1 ⁇ L 3 .
  • the internal bar 150 as described above, defining several circulation passes for the second fluid, for example the cooling liquid, in a second frame 15 has dimensions advantageously chosen to optimize the thermal efficiency of the heat exchanger 1 while limiting coolant pressure losses.

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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. Wärmetauscher (1), insbesondere für ein Kraftfahrzeug, wobei der Wärmetauscher (1) ein Wärmetauschbündel (3) umfasst, das Zirkulationskanäle (9) für mindestens ein Fluid umfasst, wobei:
    - der Wärmetauscher (1) eine vordefinierte Anzahl von Rahmen (15) umfasst, die jeweils einen Zirkulationskanal für das Fluid definieren, wobei jeder Rahmen (15) eine innere Breite und eine innere Länge (L) definiert, und wobei
    - jeder Rahmen (15) mindestens einen inneren Steg (150) aufweist, der eine geringere Breite (W) als die innere Breite des Rahmens (15) aufweist und sich in Längsrichtung innerhalb des Rahmens (15) über eine Länge (1) erstreckt, die geringer als die innere Länge (L) des Rahmens (15) ist, um so eine Bahn mit mindestens zwei Durchgängen für das Fluid im Rahmen (15) zu definieren, und
    dadurch gekennzeichnet, dass
    - die Breite (W) des inneren Stegs (150) in der Stapelrichtung der Rahmen (15) größer als oder so groß wie, vorzugsweise strikt größer als die Dicke (Th) des Rahmens (15) ist.
  2. Wärmetauscher (1) nach dem vorangehenden Anspruch, wobei sich der innere Steg (150) über eine Länge (1) erstreckt, die mindestens der Hälfte der inneren Länge (L) des Rahmens (15) entspricht.
  3. Wärmetauscher (1) nach dem vorangehenden Anspruch, wobei der Rahmen (15) und der innere Steg (150) so geformt sind, dass die folgende Beziehung erfüllt ist: 0,49 < l L ≤ 0,95 .
    Figure imgb0016
  4. Wärmetauscher (1) nach einem der Ansprüche, wobei die innere Länge (L) des Rahmens (15) in einem Bereich von 30 mm bis 500 mm liegt.
  5. Wärmetauscher (1) nach einem der vorangehenden Ansprüche, wobei:
    - der Rahmen (15) einen Rand umfasst, der im Wesentlichen parallel zum inneren Steg (150) verläuft und mindestens einen Fluideinlass (152) aufweist, der sich über eine Fluideinlasslänge (L1) erstreckt, und wobei
    - der innere Steg (150) innerhalb des Rahmens (15) angeordnet ist, wobei er vom Rand mit dem Fluideinlass (152) um einen seitlichen Abstand (L2) entfernt ist, so dass die Fluideinlasslänge (L1) gemäß folgender Beziehung größer als der seitliche Abstand (L2) oder so groß wie dieser ist: L1 ≥ L2.
  6. Wärmetauscher (1) nach dem vorangehenden Anspruch, wobei:
    - der Rahmen (15) über eine verbleibende Länge (L3) zwischen dem freien Längsende des inneren Stegs (150) und dem Rand des Rahmens (15) gegenüber dem freien Längsende des inneren Stegs (150), der sich im Wesentlichen senkrecht zum inneren Steg (150) erstreckt, keinen Steg (150) aufweist, und wobei
    - die Erstreckungslänge (1) des inneren Stegs (150) so gewählt ist, dass der seitliche Abstand (L2) gemäß der folgenden Beziehung größer als die verbleibende Länge (L3) oder so groß wie diese ist: L2 ≥ L3 = L - 1.
  7. Wärmetauscher (1) nach einem der Ansprüche 5 oder 6, wobei der seitliche Abstand (L2) in einem Bereich von 15 mm bis 60 mm liegt.
  8. Wärmetauscher (1) nach einem der Ansprüche 5 bis 7, umfassend mindestens einen Einlassstutzen und einen Auslassstutzen (21) für das Fluid, und wobei die Rahmen (15) jeweils Durchgangsöffnungen (152) zur fluidischen Verbindung mit dem Einlass- und dem Auslassstutzen (21) aufweisen und jeweils in das Innere des Rahmens (15) münden, wobei mindestens eine Durchgangsöffnung (152) einen Fluideinlass definiert.
  9. Wärmetauscher (1) nach dem vorangehenden Anspruch, wobei die Rahmen (15) jeweils mindestens zwei Buchten (153) aufweisen, die die Fluidverbindungsöffnungen (152) begrenzen und an zwei gegenüberliegenden Rändern (15C, 15D) des Rahmens (15) ausgebildet sind, die sich im Wesentlichen parallel zum inneren Steg (150) erstrecken.
  10. Wärmetauscher (1) nach den Ansprüchen 5 und 6 in Kombination mit einem der vorangehenden Ansprüche, wobei der Rahmen (15) und jede Fluidverbindungsöffnung (152) so geformt sind, dass sie einen Fluidverbindungsraum (S1) definieren, der in einem Bereich liegt:
    - dessen oberer Grenzwert dem Dreifachen des Produkts der Fluideinlasslänge (L1) mit der verbleibenden Länge (L3) entspricht und
    - dessen unterer Grenzwert einem Zehntel des Produkts der Fluideinlasslänge (L1) mit der verbleibenden Länge (L3) entspricht, so dass die folgende Beziehung erfüllt ist: 0,1 × L 1 × L 3 ≤ S 1 ≤ 3 × L 1 × L 3 .
    Figure imgb0017
  11. Wärmetauscher (1) nach einem der vorangehenden Ansprüche, wobei die Dicke (Th) des Rahmens (15) in der Stapelrichtung der Rahmen (15) im Bereich von 0,5 mm bis 4 mm, vorzugsweise im Bereich von 2 mm, liegt.
  12. Wärmetauscher (1) für einen Wärmetausch zwischen mindestens einem ersten Fluid und einem zweiten Fluid nach einem der vorangehenden Ansprüche, umfassend eine abwechselnde Stapelung von:
    - ersten Rahmen (13) zur Aufnahme von Wärmetauschrohren, die erste Zirkulationskanäle für das erste Fluid definieren, und von
    - zweiten Rahmen (15), die jeweils zweite Zirkulationskanäle für das zweite Fluid definieren und jeweils den mindestens einen inneren Steg (150) umfassen.
EP16826393.7A 2015-12-21 2016-12-16 Wärmetauscher, insbesondere für ein kraftfahrzeug Active EP3394545B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1562887A FR3045804B1 (fr) 2015-12-21 2015-12-21 Echangeur thermique, notamment pour vehicule automobile
PCT/FR2016/053505 WO2017109356A1 (fr) 2015-12-21 2016-12-16 Échangeur thermique, notamment pour vehicule automobile

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Publication Number Publication Date
EP3394545A1 EP3394545A1 (de) 2018-10-31
EP3394545B1 true EP3394545B1 (de) 2023-12-13

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FR (1) FR3045804B1 (de)
WO (1) WO2017109356A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3819580B1 (de) * 2019-11-06 2022-08-31 Valeo Autosystemy SP. Z.O.O. Wärmetauscher

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3334399A (en) * 1962-12-31 1967-08-08 Stewart Warner Corp Brazed laminated construction and method of fabrication thereof
DE19719256B4 (de) * 1997-05-07 2005-08-18 Valeo Klimatechnik Gmbh & Co. Kg Mehr als zweiflutiger Flachrohrwärmetauscher für Kraftfahrzeuge mit Umlenkboden sowie Herstelungsverfahren
EP2474803A2 (de) * 2011-01-05 2012-07-11 HS Marston Aerospace Limited Laminierter Wärmetauscher

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2382666A1 (fr) * 1977-03-04 1978-09-29 Gir Pi Echangeurs de chaleur elementaires et bloc d'echange de chaleur forme de tels echangeurs de chaleur elementaires
FR2912811B1 (fr) * 2007-02-16 2013-02-08 Valeo Systemes Thermiques Echangeur de chaleur pour fluides a circulation en u
FR2986315B1 (fr) * 2012-01-30 2014-01-10 Valeo Systemes Thermiques Echangeur de chaleur

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3334399A (en) * 1962-12-31 1967-08-08 Stewart Warner Corp Brazed laminated construction and method of fabrication thereof
DE19719256B4 (de) * 1997-05-07 2005-08-18 Valeo Klimatechnik Gmbh & Co. Kg Mehr als zweiflutiger Flachrohrwärmetauscher für Kraftfahrzeuge mit Umlenkboden sowie Herstelungsverfahren
EP2474803A2 (de) * 2011-01-05 2012-07-11 HS Marston Aerospace Limited Laminierter Wärmetauscher

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EP3394545A1 (de) 2018-10-31
FR3045804A1 (fr) 2017-06-23
WO2017109356A1 (fr) 2017-06-29
FR3045804B1 (fr) 2017-12-29

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