EP3001133B1 - Heat exchanger for a motor vehicle - Google Patents

Heat exchanger for a motor vehicle Download PDF

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Publication number
EP3001133B1
EP3001133B1 EP15186571.4A EP15186571A EP3001133B1 EP 3001133 B1 EP3001133 B1 EP 3001133B1 EP 15186571 A EP15186571 A EP 15186571A EP 3001133 B1 EP3001133 B1 EP 3001133B1
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EP
European Patent Office
Prior art keywords
corrugated tubes
heat exchanger
tubes
fluid
orifices
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EP15186571.4A
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German (de)
French (fr)
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EP3001133A1 (en
Inventor
Isabelle Citti
Jérémy BLANDIN
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Valeo Systemes Thermiques SAS
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Valeo Systemes Thermiques SAS
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Publication of EP3001133A1 publication Critical patent/EP3001133A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • 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
    • F28F9/0229—Double end plates; Single end plates with hollow spaces

Definitions

  • the present invention relates to a heat exchanger, in particular for a vehicle air conditioning fluid circuit, according to the preamble of claim 1.
  • a heat exchanger is known from the document EP 2 384 837 A2 .
  • the heat exchangers for an air conditioning fluid circuit of a vehicle may be traversed by a supercritical refrigerant such as carbon dioxide (CO 2 ).
  • This fluid remains substantially in the gaseous state and under a high operating pressure usually between 100 and 150 bar. It is therefore necessary for such heat exchangers to withstand such pressures, and a bursting pressure generally substantially equivalent to three times the value of the operating pressure is provided for this purpose.
  • such exchangers comprise a plurality of flat tubes stacked on each other forming a heat exchange bundle and having circulation channels of a first fluid, a second fluid circulating between the tubes.
  • Each end of the tubes is connected to a manifold for distributing the first fluid at one end and collect at the other end.
  • Interlayers / disruptors / turbulators are also arranged and fixed between the tubes so as to disturb the circulation of the second fluid and thus increase the heat exchange.
  • the use of disrupters or the like is expensive, both by the realization of complementary elements and by the tricky method of setting up and fixing these elements.
  • their presence limits the minimum height of exchange surface and it does not allow to ensure satisfactory mechanical strength for the heat exchange beam because these disturbers are usually thin and fragile.
  • An object of the present invention is therefore to at least partially solve the disadvantages of the prior art and to provide an improved heat exchanger.
  • the present invention therefore relates to a heat exchanger according to claim 1.
  • the thickness of the corrugated tubes is between 0.9 and 2.8 mm.
  • the undulations of the corrugated tubes have an amplitude of between 0.5 and 3.5 mm.
  • the undulations of the corrugated tubes have a pitch of between 5 and 9 mm.
  • said corrugated tubes comprise at least one corrugation line extending obliquely with respect to the longitudinal axis of the corrugated tube at an angle of between 30 and 60 °.
  • said corrugated tubes have a section adapted so that the section formed by the tube ends of said assembled corrugated tubes is oblong.
  • the distance between the upper faces of two successive assemblies of corrugated tubes is between 2 and 8mm.
  • the invention relates to a heat exchanger 1, in particular exchanger for an air conditioning circuit of a vehicle, allowing a heat exchange between a first fluid F1 and a second fluid F2.
  • Said exchanger 1 comprises a plurality of corrugated tubes 3 for circulating the first fluid F1, stacked on one another and at least one manifold 5 comprising a collecting plate 7.
  • said exchanger 1 comprises, at each of these ends 1a and 1b, first and second collectors 5a and 5b.
  • the first collector 5a is an inlet manifold of the first fluid F1, which is here a gas under high pressure, such as CO 2 and the second collector 5b is an outlet manifold of this fluid F1.
  • Each collector 5a and 5b is connected to the plurality of corrugated tubes 3, also called beam 4, by the collecting plate 7.
  • the first fluid F1 thus passes successively through said inlet manifold 5a, said bundle 4 and said outlet manifold 5b .
  • Said exchanger 1 comprises, here, a housing 9 formed of side walls 9a and 9b.
  • Said walls 9a and 9b comprise an inlet orifice 11a and / or an outlet orifice 11b for the second fluid F2 which is here a heat-transfer liquid, in particular brine, circulating between the corrugated tubes 3 stacked so as to cool the first fluid F1.
  • a heat-transfer liquid in particular brine
  • the inlet orifice 11a of the second fluid F2 is located at the end 1b where the outlet manifold 5b of the first fluid F1 is located and the outlet port 11b is located opposite, ie at the end 1a, to the inlet manifold 5a of the first fluid F1. In this way, counterflow of said fluids is available.
  • the manifold plate 7 comprises orifices 13 for introducing an end 3a of the corrugated tubes 3 so that said ends 3a said corrugated tubes 3 are assembled two by two in one and the same orifices 13 for introducing the collector plate 7. In this way, a collector having a compact and robust configuration is arranged.
  • the distance between the upper faces of two successive assemblies of corrugated tubes 3 may for example be between 2 and 8 mm.
  • Said collector 5 may also comprise a cover 15 and an intermediate plate, called a reinforcing plate 17.
  • Said reinforcing plate 17 is configured to form a spacer between a wall 15a of the lid 15 and the header plate 7. It comprises orifices 19 for the passage of the fluid F1 facing the orifices 13 for introducing the header plate 7 so that the fluid F1 can flow between the corrugated tubes 3 and the collector 5 through the orifices 13, 19.
  • said orifices 19 of said reinforcing plate 17 are larger than the dimension orifices 13 of said collector plate 7.
  • said reinforcing plate 17 comprises shoulder straps 21 configured to bear on collars 23 bordering said orifices 13 of said collector plate 7. In this way, each of said straps 21 is in contact with a lower part 23a. and an upper portion 23b of the same collar 23 bordering two adjacent orifices 13. Said reinforcing plate 17 thus limits the risk of buckling of the manifold plate 7 at the level of the flanges 23 bordering the introduction orifices 13, and between said introduction orifices 13, in particular when the heat exchanger 1 is intended for a gas under high pressure.
  • Said cover 15 can define several chambers 25 in said manifold 5, as shown in FIG. figure 5 .
  • the lid 15 then comprises legs 27 delimiting on each side a chamber 25. Here, three parallel chambers 25 formed by two legs 27 are shown.
  • the supply of said first fluid collector F1 and the outlet thereof can be done, as shown here, by means of a supply flange 29.
  • Said supply flanges 29 may comprise a plurality of ducts 31.
  • said flange 29 comprises a number of ducts 31 equivalent to the number of chambers 25 of the collector 5, each duct 31 feeding a 25.
  • the flange 29 shown in FIGS. figures 1 , 3 to 5 comprises a fluid inlet duct 31a which divides into three regularly distributed ducts 31b, possibly of lower section to the inlet duct 31a, each of the three ducts 31b supplying one of the three chambers 25.
  • This type of flange 29 associated with a The plurality of chambers 25 allows a uniform distribution of the fluid F1 in the different chambers 25 and an optimized supply, which can be advantageous in a heat exchanger for gas under high pressure.
  • Said flange 29 may be carried by said lid 15.
  • the latter here has an opening allowing the passage of the first fluid F1 in the manifold 5.
  • said heat exchanger 1 further comprises an additional plate 33 placed between the cover 15 and the reinforcing plate 17.
  • Said additional plate 33 allows the brazing of said cover 15 and said reinforcing plate 17 between them.
  • it is coated for example with a brazing alloy.
  • the additional plate 33 has a contour surface substantially identical to that of the reinforcing plate 17.
  • Said additional plate 33 also comprises orifices 35 for the passage of the first fluid F1 facing the orifices 13 of the plate manifold 7 and 19 holes of the reinforcing plate 17 in which the end 3a of a pair of corrugated tubes 3 is inserted.
  • the additional plate 33 has jambs 37 complementary to the jambs 27 of the lid 15 delimiting each of the chambers 25.
  • the lid 15 and the reinforcing plate 17 are thus brazed together over a large contact surface.
  • Said additional plate 33 further comprises, here, shoulder straps 38, located opposite straps 21 of the reinforcing plate 17.
  • Said straps 38 of the additional plate 33 and its legs 37 are orthogonal and define between them the holes 35 of said additional plate 33. In the example illustrated, there are therefore three orifices 35 of the additional plate 33 opposite one and the same orifice 19 of the reinforcing plate 17.
  • said collecting plate 7 comprises two parallel outer side portions 39a and 39b bordering longitudinally the cover 15 and said reinforcing plate 17 and ending with a return 41 over its entire height in contact with said flange 29 so as to form with the cover 15 and said reinforcing plate 17 a unitary assembly.
  • the corrugated tubes 3 are extruded flat tubes comprising a plurality of channels 43 for the circulation of the first fluid F1, here a gas under high pressure.
  • Said extruded tubes have a thickness Te generally between 0.9 and 2.8 mm in order to ensure a good heat exchange and they are deformed so as to form a plurality of corrugation lines 45.
  • the lines 45 are, here, parallel to each other and are substantially identical
  • the corrugation lines 45 extend obliquely with respect to the longitudinal axis of the corrugated tube 3 at an angle preferably between 30 and 60 °.
  • the corrugated tubes 3 are assembled so as to cross the corrugation lines 45 of adjacent tubes 3. Said stacked corrugated tubes 3 are thus in contact with one another, in particular at parts of the vertices 47 of the ripples, called points of contact.
  • said corrugated tubes 3 are brazed together at their points of contact.
  • the corrugated tubes 3 may have, at their end 3a, a particular section so that the section formed by two ends 3a of assembled corrugated tubes 3 is oblong, advantageously formed of straight and / or convex portion
  • the ends 3a of the corrugated tubes 3 are substantially planar, ie devoid of corrugation lines 45, in ways that can be assembled in pairs and inserted into the orifices 13 for introducing the collector plates 7 of each of the two collectors 5a. and 5b, as just described.
  • Said corrugated tubes 3 may be configured so as to be longitudinally held so that their end remains in the thickness of the reinforcing plate 17 set back from one face of said reinforcing plate 17 turned towards the inside of the collector 5, even remains set back from a free edge of said collars 23 of the collector plate 7.
  • all the elements of the exchanger 1 are brazed together in one step, according to one or more preassembly steps.
  • the corrugations of said corrugated tubes 3 have an amplitude Oa and a pitch Op so that the ratio Op / Oh is between 1.5 and 3.5.
  • This ratio allows an optimal heat exchange between the two fluids F1 and F2.
  • the corrugations can thus have an amplitude Oa of between 0.5 and 3.5 mm and a pitch Op between 5 and 9 mm.
  • each insertion orifice is sized to receive at least two tubes.

Description

La présente invention a pour objet un échangeur de chaleur, notamment pour circuit de fluide de climatisation d'un véhicule, conforme au préambule de la revendication 1. Un tel échangeur est connu du document EP 2 384 837 A2 .The present invention relates to a heat exchanger, in particular for a vehicle air conditioning fluid circuit, according to the preamble of claim 1. Such an exchanger is known from the document EP 2 384 837 A2 .

Les échangeurs de chaleur pour circuit de fluide de climatisation d'un véhicule sont susceptibles d'être parcourus par un fluide réfrigérant à l'état supercritique tel que du dioxyde de carbone (CO2). Ce fluide reste essentiellement à l'état gazeux et sous une pression de fonctionnement élevée habituellement comprise entre 100 et 150 bars. Il est donc nécessaire que de tels échangeurs de chaleur résistent à de telles pressions et on prévoit à cette fin une pression d'éclatement généralement sensiblement équivalente à trois fois la valeur de la pression de fonctionnement.The heat exchangers for an air conditioning fluid circuit of a vehicle may be traversed by a supercritical refrigerant such as carbon dioxide (CO 2 ). This fluid remains substantially in the gaseous state and under a high operating pressure usually between 100 and 150 bar. It is therefore necessary for such heat exchangers to withstand such pressures, and a bursting pressure generally substantially equivalent to three times the value of the operating pressure is provided for this purpose.

De façon générale, de tels échangeurs comprennent une pluralité de tubes plats empilés les uns sur les autres formant un faisceau d'échange de chaleur et présentant des canaux de circulation d'un premier fluide, un second fluide circulant entre les tubes. Chaque extrémité des tubes est reliée à un collecteur permettant de distribuer le premier fluide à une extrémité et de le collecter à l'autre extrémité. Cela permet d'obtenir des échangeurs de chaleur peu encombrants tout en conservant des caractéristiques intéressantes.In general, such exchangers comprise a plurality of flat tubes stacked on each other forming a heat exchange bundle and having circulation channels of a first fluid, a second fluid circulating between the tubes. Each end of the tubes is connected to a manifold for distributing the first fluid at one end and collect at the other end. This makes it possible to obtain space-saving heat exchangers while maintaining interesting characteristics.

Des intercalaires/perturbateurs/turbulateurs sont également disposés et fixés entre les tubes de manière à perturber la circulation du second fluide et ainsi augmenter les échanges thermiques. L'utilisation de perturbateurs ou analogues est coûteuse, tant par la réalisation d'éléments complémentaires que par le délicat procédé de mise en place et de fixation des ces éléments. De plus, leur présence limite la hauteur minimum de surface d'échange et elle ne permet pas d'assurer une résistance mécanique satisfaisante pour le faisceau d'échange de chaleur car ces perturbateurs sont généralement fins et fragiles.Interlayers / disruptors / turbulators are also arranged and fixed between the tubes so as to disturb the circulation of the second fluid and thus increase the heat exchange. The use of disrupters or the like is expensive, both by the realization of complementary elements and by the tricky method of setting up and fixing these elements. In addition, their presence limits the minimum height of exchange surface and it does not allow to ensure satisfactory mechanical strength for the heat exchange beam because these disturbers are usually thin and fragile.

Un des buts de la présente invention est donc de résoudre au moins partiellement les inconvénients de l'art antérieur et de proposer un échangeur de chaleur amélioré.An object of the present invention is therefore to at least partially solve the disadvantages of the prior art and to provide an improved heat exchanger.

La présente invention concerne donc un échangeur de chaleur conforme à la revendication 1.The present invention therefore relates to a heat exchanger according to claim 1.

Selon un aspect de l'invention, l'épaisseur des tubes ondulés est comprise entre 0.9 et 2.8 mm.According to one aspect of the invention, the thickness of the corrugated tubes is between 0.9 and 2.8 mm.

Selon un autre aspect de l'invention, les ondulations des tubes ondulés ont une amplitude comprise entre 0.5 et 3.5 mm.According to another aspect of the invention, the undulations of the corrugated tubes have an amplitude of between 0.5 and 3.5 mm.

Selon un autre aspect de l'invention, les ondulations des tubes ondulés ont un pas compris entre 5 et 9 mm.According to another aspect of the invention, the undulations of the corrugated tubes have a pitch of between 5 and 9 mm.

Selon un autre aspect de l'invention, lesdits tubes ondulés comprennent au moins une ligne d'ondulation s'étendant obliquement par rapport à l'axe longitudinal du tube ondulés selon un angle compris entre 30 et 60°.According to another aspect of the invention, said corrugated tubes comprise at least one corrugation line extending obliquely with respect to the longitudinal axis of the corrugated tube at an angle of between 30 and 60 °.

Selon un autre aspect de l'invention, lesdits tubes ondulés ont une section adaptée pour que la section formée par les extrémités de tubes desdits tubes ondulés assemblées soit oblongue.According to another aspect of the invention, said corrugated tubes have a section adapted so that the section formed by the tube ends of said assembled corrugated tubes is oblong.

Selon un autre aspect de l'invention, la distance entre les faces supérieures de deux assemblages successifs de tubes ondulés est comprise entre 2 et 8mm.According to another aspect of the invention, the distance between the upper faces of two successive assemblies of corrugated tubes is between 2 and 8mm.

L'invention sera mieux comprise, et d'autres buts, détails, caractéristiques et avantages de celle-ci apparaîtront plus clairement au cours de la description explicative détaillée qui va suivre, d'au moins un mode de réalisation de l'invention donné à titre d'exemple purement illustratif et non limitatif, en référence aux dessins schématiques annexés.The invention will be better understood, and other objects, details, features and advantages thereof will become more clearly apparent in the following detailed explanatory description of at least one embodiment of the invention given to As a purely illustrative and non-limiting example, with reference to the accompanying schematic drawings.

Sur ces dessins :

  • la figure 1 est une vue en perspective en coupe longitudinale d'un échangeur de chaleur selon l'invention, selon une orientation du dessus,
  • la figure 2 est une vue en perspective de l'intérieur de l'échangeur représenté en figure 1,
  • la figure 3 est une vue en perspective en coupe longitudinale d'une extrémité de l'échangeur représenté en figure 1, selon une orientation de côté,
  • la figure 4 est une vue de détail de la figure 1, montrant un collecteur,
  • la figure 5 est une vue semblable à la figure 4 montrant un autre mode de réalisation d'un collecteur, conforme à l'invention,
  • la figure 6 est une vue éclatée de plusieurs tubes utilisés dans l'échangeur de la figure 1,
  • la figure 7 est une vue en perspective d'une extrémité de tube utilisé dans l'échangeur de la figure 1, coupé transversalement,
  • la figure 8 est une vue en perspective de deux tubes utilisés dans l'échangeur de la figure 1 dont les extrémités sont assemblées.
On these drawings:
  • the figure 1 is a perspective view in longitudinal section of a heat exchanger according to the invention, in a top orientation,
  • the figure 2 is a perspective view of the inside of the exchanger represented in figure 1 ,
  • the figure 3 is a perspective view in longitudinal section of one end of the exchanger shown in FIG. figure 1 , in a side orientation,
  • the figure 4 is a detail view of the figure 1 , showing a collector,
  • the figure 5 is a view similar to the figure 4 showing another embodiment of a collector according to the invention,
  • the figure 6 is an exploded view of several tubes used in the exchanger of the figure 1 ,
  • the figure 7 is a perspective view of a tube end used in the heat exchanger of the figure 1 , cut transversely,
  • the figure 8 is a perspective view of two tubes used in the heat exchanger figure 1 whose ends are assembled.

Comme illustré aux différentes figures, l'invention concerne un échangeur de chaleur 1, en particulier échangeur pour circuit de climatisation d'un véhicule, permettant un échange de chaleur entre un premier fluide F1 et un second fluide F2. Ledit échangeur 1 comprend une pluralité de tubes ondulés 3 de circulation du premier fluide F1, empilés les uns sur les autres et au moins un collecteur 5 comprenant une plaque collectrice 7.As illustrated in the various figures, the invention relates to a heat exchanger 1, in particular exchanger for an air conditioning circuit of a vehicle, allowing a heat exchange between a first fluid F1 and a second fluid F2. Said exchanger 1 comprises a plurality of corrugated tubes 3 for circulating the first fluid F1, stacked on one another and at least one manifold 5 comprising a collecting plate 7.

Dans les différents modes de réalisation représentés, ledit échangeur 1 comprend, à chacune de ces extrémités 1a et 1b, un premier et un second collecteurs 5a et 5b. Le premier collecteur 5a est un collecteur d'entrée du premier fluide F1, qui est ici un gaz sous haute pression, tel que du CO2 et le second collecteur 5b est un collecteur de sortie de ce fluide F1. Chaque collecteur 5a et 5b est relié à la pluralité de tubes ondulés 3, appelée aussi faisceau 4, par la plaque collectrice 7. Le premier fluide F1 traverse ainsi successivement ledit collecteur d'entrée 5a, le dit faisceau 4 et ledit collecteur de sortie 5b.In the various embodiments shown, said exchanger 1 comprises, at each of these ends 1a and 1b, first and second collectors 5a and 5b. The first collector 5a is an inlet manifold of the first fluid F1, which is here a gas under high pressure, such as CO 2 and the second collector 5b is an outlet manifold of this fluid F1. Each collector 5a and 5b is connected to the plurality of corrugated tubes 3, also called beam 4, by the collecting plate 7. The first fluid F1 thus passes successively through said inlet manifold 5a, said bundle 4 and said outlet manifold 5b .

Ledit échangeur 1 comprend, ici, un boitier 9 formé de parois latérales 9a et 9b. Lesdites parois 9a et 9b comprennent un orifice d'entrée 11a et/ou un orifice de sortie 11b pour le second fluide F2 qui est ici un liquide caloporteur, notamment de l'eau glycolée, circulant entre les tubes ondulés 3 empilés de manière à refroidir le premier fluide F1.Said exchanger 1 comprises, here, a housing 9 formed of side walls 9a and 9b. Said walls 9a and 9b comprise an inlet orifice 11a and / or an outlet orifice 11b for the second fluid F2 which is here a heat-transfer liquid, in particular brine, circulating between the corrugated tubes 3 stacked so as to cool the first fluid F1.

Pour permettre un refroidissement maximal, dans le mode de réalisation représenté dans les différentes figures, l'orifice d'entrée 11a du second fluide F2 est situé à l'extrémité 1b où se situe le collecteur de sortie 5b du premier fluide F1 et l'orifice de sortie 11b est situé à l'opposé, i.e. à l'extrémité 1a, vers le collecteur d'entrée 5a du premier fluide F1. On dispose de la sorte d'une circulation à contre-courant desdits fluides.To allow maximum cooling, in the embodiment shown in the various figures, the inlet orifice 11a of the second fluid F2 is located at the end 1b where the outlet manifold 5b of the first fluid F1 is located and the outlet port 11b is located opposite, ie at the end 1a, to the inlet manifold 5a of the first fluid F1. In this way, counterflow of said fluids is available.

La plaque collectrice 7 comprend des orifices 13 d'introduction d'une extrémité 3a des tubes ondulés 3 de manière à ce que lesdites extrémités 3a desdits tubes ondulés 3 soient assemblées deux par deux dans un même desdits orifices 13 d'introduction de la plaque collectrice 7. On dispose de la sorte d'un collecteur présentant une configuration compacte et robuste.The manifold plate 7 comprises orifices 13 for introducing an end 3a of the corrugated tubes 3 so that said ends 3a said corrugated tubes 3 are assembled two by two in one and the same orifices 13 for introducing the collector plate 7. In this way, a collector having a compact and robust configuration is arranged.

La distance entre les faces supérieures de deux assemblages successifs de tubes ondulés 3 peut par exemple être comprise entre 2 et 8mm.The distance between the upper faces of two successive assemblies of corrugated tubes 3 may for example be between 2 and 8 mm.

Ledit collecteur 5 pourra également comprendre un couvercle 15 et une plaque intermédiaire, dite plaque de renfort 17.Said collector 5 may also comprise a cover 15 and an intermediate plate, called a reinforcing plate 17.

Ladite plaque de renfort 17 est configurée pour former une entretoise entre une paroi 15a du couvercle 15 et la plaque collectrice 7. Elle comprend des orifices 19 de passage du fluide F1 en vis-à-vis des orifices 13 d'introduction de la plaque collectrice 7 de manière à ce que le fluide F1 puisse circuler entre les tubes ondulés 3 et le collecteur 5 à travers les orifices 13, 19. De façon avantageuse, lesdits orifices 19 de ladite plaque de renfort 17 sont d'une dimension supérieure à la dimension des orifices 13 de ladite plaque collectrice 7.Said reinforcing plate 17 is configured to form a spacer between a wall 15a of the lid 15 and the header plate 7. It comprises orifices 19 for the passage of the fluid F1 facing the orifices 13 for introducing the header plate 7 so that the fluid F1 can flow between the corrugated tubes 3 and the collector 5 through the orifices 13, 19. Advantageously, said orifices 19 of said reinforcing plate 17 are larger than the dimension orifices 13 of said collector plate 7.

Entre chacun de ses orifices 19, ladite plaque de renfort 17 comprend des bretelles 21 configurées pour prendre appuis sur des collets 23 bordant lesdits orifices 13 de ladite plaque collectrice 7. De cette façon, chacune desdites bretelles 21 est en contact avec une partie inférieure 23a et une partie supérieure 23b d'un même collet 23 bordant deux orifices 13 voisins. Ladite plaque de renfort 17 limite ainsi le risque de flambage de la plaque collectrice 7 au niveau des collets 23 bordant les orifices 13 d'introduction, et entre lesdits orifices 13 d'introduction, notamment lorsque l'échangeur de chaleur 1 est destiné à un gaz sous haute pression.Between each of its orifices 19, said reinforcing plate 17 comprises shoulder straps 21 configured to bear on collars 23 bordering said orifices 13 of said collector plate 7. In this way, each of said straps 21 is in contact with a lower part 23a. and an upper portion 23b of the same collar 23 bordering two adjacent orifices 13. Said reinforcing plate 17 thus limits the risk of buckling of the manifold plate 7 at the level of the flanges 23 bordering the introduction orifices 13, and between said introduction orifices 13, in particular when the heat exchanger 1 is intended for a gas under high pressure.

Ledit couvercle 15 peut définir plusieurs chambres 25 dans ledit collecteur 5, comme représenté en figure 5. Le couvercle 15 comprend alors des jambages 27 délimitant de part et d'autre une chambre 25. Ici, trois chambres 25 parallèles formées par deux jambages 27 sont représentées.Said cover 15 can define several chambers 25 in said manifold 5, as shown in FIG. figure 5 . The lid 15 then comprises legs 27 delimiting on each side a chamber 25. Here, three parallel chambers 25 formed by two legs 27 are shown.

L'alimentation dudit collecteur 5 en premier fluide F1 et la sortie de celui-ci peuvent se faire, comme représenté ici, par l'intermédiaire d'une bride 29 d'alimentation. Lesdites brides 29 d'alimentation peuvent comprendre plusieurs conduits 31. Notamment dans le cas d'un collecteur 5 comprenant plusieurs chambres 25, ladite bride 29 comprend un nombre de conduits 31 équivalent aux nombre de chambres 25 du collecteur 5, chaque conduit 31 alimentant une chambre 25. Ici, la bride 29 représentée aux figures 1, 3 à 5 comprend un conduit 31a d'entrée du fluide qui se divise en trois conduits 31b régulièrement répartis, éventuellement de section inférieure au conduit 31a d'entrée, chacun des trois conduits 31b alimentant une des trois chambres 25. Ce type de bride 29 associé à une pluralité de chambres 25 permet une répartition uniforme du fluide F1 dans les différentes chambres 25 et une alimentation optimisée, ce qui peut être avantageux dans un échangeur de chaleur pour gaz sous haute pression.The supply of said first fluid collector F1 and the outlet thereof can be done, as shown here, by means of a supply flange 29. Said supply flanges 29 may comprise a plurality of ducts 31. In particular, in the case of a manifold 5 comprising a plurality of chambers 25, said flange 29 comprises a number of ducts 31 equivalent to the number of chambers 25 of the collector 5, each duct 31 feeding a 25. Here, the flange 29 shown in FIGS. figures 1 , 3 to 5 comprises a fluid inlet duct 31a which divides into three regularly distributed ducts 31b, possibly of lower section to the inlet duct 31a, each of the three ducts 31b supplying one of the three chambers 25. This type of flange 29 associated with a The plurality of chambers 25 allows a uniform distribution of the fluid F1 in the different chambers 25 and an optimized supply, which can be advantageous in a heat exchanger for gas under high pressure.

Ladite bride 29 pourra être portée par ledit couvercle 15. Ce dernier présente ici une ouverture permettant le passage du premier fluide F1 dans le collecteur 5.Said flange 29 may be carried by said lid 15. The latter here has an opening allowing the passage of the first fluid F1 in the manifold 5.

Dans un autre mode de réalisation représenté en figure 5, ledit échangeur de chaleur 1 comprend en outre une plaque supplémentaire 33 placée entre le couvercle 15 et la plaque de renfort 17. Ladite plaque supplémentaire 33 permet le brasage dudit couvercle 15 et de ladite plaque de renfort 17 entre eux. De façon avantageuse, elle est revêtue par exemple d'un alliage de brasage. La plaque supplémentaire 33 présente une surface de contour sensiblement identique à celui de la plaque de renfort 17. Ladite plaque supplémentaire 33 comprend, elle aussi, des orifices 35 de passage du premier fluide F1 en vis-à-vis des orifices 13 de la plaque collectrice 7 et des orifices 19 de la plaque de renfort 17 dans lesquels l'extrémité 3a d'une paire de tubes ondulés 3 vient s'insérer.In another embodiment shown in figure 5 , said heat exchanger 1 further comprises an additional plate 33 placed between the cover 15 and the reinforcing plate 17. Said additional plate 33 allows the brazing of said cover 15 and said reinforcing plate 17 between them. Advantageously, it is coated for example with a brazing alloy. The additional plate 33 has a contour surface substantially identical to that of the reinforcing plate 17. Said additional plate 33 also comprises orifices 35 for the passage of the first fluid F1 facing the orifices 13 of the plate manifold 7 and 19 holes of the reinforcing plate 17 in which the end 3a of a pair of corrugated tubes 3 is inserted.

Dans le cas d'un collecteur 5 comprenant plusieurs chambres 25, la plaque supplémentaire 33 présente des jambages 37 complémentaires aux jambages 27 du couvercle 15 délimitant chacune des chambres 25. Le couvercle 15 et la plaque de renfort 17 sont ainsi brasés ensemble sur une large surface de contact.In the case of a manifold 5 comprising several chambers 25, the additional plate 33 has jambs 37 complementary to the jambs 27 of the lid 15 delimiting each of the chambers 25. The lid 15 and the reinforcing plate 17 are thus brazed together over a large contact surface.

Ladite plaque supplémentaire 33 comprend en outre, ici, des bretelles 38, situées en vis-à-vis des bretelles 21 de la plaque de renfort 17. Lesdites bretelles 38 de la plaque supplémentaire 33 et ses jambages 37 sont orthogonaux et définissent entre eux les orifices 35 de ladite plaque supplémentaire 33. Dans l'exemple illustré, on trouve donc trois orifices 35 de la plaque supplémentaire 33 en regard d'un seul et même orifice 19 de la plaque de renfort 17.Said additional plate 33 further comprises, here, shoulder straps 38, located opposite straps 21 of the reinforcing plate 17. Said straps 38 of the additional plate 33 and its legs 37 are orthogonal and define between them the holes 35 of said additional plate 33. In the example illustrated, there are therefore three orifices 35 of the additional plate 33 opposite one and the same orifice 19 of the reinforcing plate 17.

Comme il est visible aux figures 1 à 5, ladite plaque collectrice 7 comprend deux parties latérales 39a et 39b extérieures parallèles bordant longitudinalement le couvercle 15 et ladite plaque de renfort 17 et se terminant par un retour 41 sur toute sa hauteur au contact de ladite bride 29 de manière à former avec le couvercle 15 et ladite plaque de renfort 17 un ensemble solidaire.As it is visible to Figures 1 to 5 said collecting plate 7 comprises two parallel outer side portions 39a and 39b bordering longitudinally the cover 15 and said reinforcing plate 17 and ending with a return 41 over its entire height in contact with said flange 29 so as to form with the cover 15 and said reinforcing plate 17 a unitary assembly.

Dans les différents modes de réalisations représentés ici, les tubes ondulés 3 sont des tubes plats extrudés comprenant une pluralité de canaux 43 pour la circulation du premier fluide F1, ici un gaz sous haute pression. Lesdits tubes extrudés ont une épaisseur Te généralement comprise entre 0.9 et 2.8mm afin d'assurer un bon échange thermique et ils sont déformés de manière à former une pluralité de lignes d'ondulation 45. Les lignes 45 sont, ici, parallèles entre elles et sont sensiblement identiquesIn the various embodiments represented here, the corrugated tubes 3 are extruded flat tubes comprising a plurality of channels 43 for the circulation of the first fluid F1, here a gas under high pressure. Said extruded tubes have a thickness Te generally between 0.9 and 2.8 mm in order to ensure a good heat exchange and they are deformed so as to form a plurality of corrugation lines 45. The lines 45 are, here, parallel to each other and are substantially identical

D'autre part, comme il est visible sur les figures 6 et 8, les lignes d'ondulation 45 s'étendent obliquement par rapport à l'axe longitudinal du tube ondulés 3 selon un angle de préférence compris entre 30 et 60°. Les tubes ondulés 3 sont assemblés de manières à croiser les lignes d'ondulation 45 de tubes 3 contigus. Lesdits tubes ondulés 3 empilés sont ainsi au contact les uns des autres, notamment au niveau de parties des sommets 47 des ondulations, appelés points de contact. Avantageusement lesdits tubes ondulés 3 sont brasés entre eux au niveau de leurs points de contact. Une telle structure permet de créer un réseau sinueux entre les tubes ondulés 3 pour perturber la circulation du deuxième fluide F2 et assurer un échange thermique performant entre les deux fluides F1 et F2. Cela améliore en outre la robustesse du produit.On the other hand, as it is visible on Figures 6 and 8 , the corrugation lines 45 extend obliquely with respect to the longitudinal axis of the corrugated tube 3 at an angle preferably between 30 and 60 °. The corrugated tubes 3 are assembled so as to cross the corrugation lines 45 of adjacent tubes 3. Said stacked corrugated tubes 3 are thus in contact with one another, in particular at parts of the vertices 47 of the ripples, called points of contact. Advantageously, said corrugated tubes 3 are brazed together at their points of contact. Such a structure makes it possible to create a sinuous network between the corrugated tubes 3 in order to disturb the circulation of the second fluid F 2 and to ensure efficient heat exchange between the two fluids F1 and F2. This further enhances the robustness of the product.

De façon avantageuse, les tubes ondulés 3 peuvent avoir, à leur extrémité 3a, une section particulière de façon à ce que la section formée par deux extrémités 3a de tubes ondulés 3 assemblées soit oblongue, avantageusement formée de portion droite et/ou convexeAdvantageously, the corrugated tubes 3 may have, at their end 3a, a particular section so that the section formed by two ends 3a of assembled corrugated tubes 3 is oblong, advantageously formed of straight and / or convex portion

Comme illustré aux différentes figures 3 et 6 à 8, les extrémités 3a des tubes ondulés 3 sont sensiblement planes, i.e. dépourvues de lignes d'ondulation 45, de manières à pouvoir être assemblées deux par deux et être insérées dans les orifices 13 d'introduction des plaques collectrices 7 de chacun des deux collecteurs 5a et 5b, comme il vient d'être décrit.As illustrated in different figures 3 and 6 to 8 , the ends 3a of the corrugated tubes 3 are substantially planar, ie devoid of corrugation lines 45, in ways that can be assembled in pairs and inserted into the orifices 13 for introducing the collector plates 7 of each of the two collectors 5a. and 5b, as just described.

Lesdits tubes ondulés 3 pourront être configurés de façon à être longitudinalement maintenus de manière à ce que leur extrémité reste dans l'épaisseur de la plaque de renfort 17 en retrait d'une face de ladite plaque de renfort 17 tourné vers l'intérieur du collecteur 5, voire reste en retrait d'un bord libre desdits collets 23 de la plaque collectrice 7.Said corrugated tubes 3 may be configured so as to be longitudinally held so that their end remains in the thickness of the reinforcing plate 17 set back from one face of said reinforcing plate 17 turned towards the inside of the collector 5, even remains set back from a free edge of said collars 23 of the collector plate 7.

De façon avantageuse, l'ensemble des éléments de l'échangeur 1 sont brasés entre eux, en une seule étape, suivant une ou des étapes de préassemblage.Advantageously, all the elements of the exchanger 1 are brazed together in one step, according to one or more preassembly steps.

De préférence, les ondulations desdits tubes ondulés 3 ont une amplitude Oa et un pas Op de sorte que le rapport Op/Oh est compris entre 1.5 et 3.5. Ce rapport permet un échange thermique optimal entre les deux fluides F1 et F2. Par pas, on entend la distance entre deux sommets successifs.Preferably, the corrugations of said corrugated tubes 3 have an amplitude Oa and a pitch Op so that the ratio Op / Oh is between 1.5 and 3.5. This ratio allows an optimal heat exchange between the two fluids F1 and F2. By step, we mean the distance between two successive vertices.

Les ondulations peuvent ainsi avoir une amplitude Oa comprise entre 0.5 et 3.5mm ainsi qu'un pas Op compris entre 5 et 9mm.The corrugations can thus have an amplitude Oa of between 0.5 and 3.5 mm and a pitch Op between 5 and 9 mm.

Il est à noter que des variantes de réalisation sont bien sûr possibles et que la présente invention ne se limite pas aux modes de réalisations décrits ci-dessus.It should be noted that alternative embodiments are of course possible and that the present invention is not limited to the embodiments described above.

A titre d'exemple, dans un mode de réalisation non représenté, chaque orifice d'introduction est dimensionné afin de recevoir au moins deux tubes.For example, in an embodiment not shown, each insertion orifice is sized to receive at least two tubes.

Claims (7)

  1. Heat exchanger (1), in particular a heat exchanger for a vehicle air conditioning circuit, allowing an exchange of heat between first (F1) and second (F2) fluids, the said exchanger (1) comprising a plurality of corrugated tubes (3) for the circulation of the first fluid (F1), these being stacked on one another, and at least one header (5) comprising a header plate (7), the said header plate (7) comprising orifices (13) into which the ends (3a) of corrugated tubes (3) are inserted, characterized in that the corrugations of the said corrugated tubes (3) have an amplitude (Oa) and a pitch (Op) such that the ratio of pitch (Op)/amplitude (Oa) is comprised between 1.5 and 3.5, the said ends (3a) of the said corrugated tubes (3) being assembled at least in pairs in one same one of the said insertion orifices (13) in the header plate (7).
  2. Heat exchanger (1) according to the preceding claim, characterized in that the thickness (Te) of the corrugated tubes (3) is comprises between 0.9 and 2.8 mm.
  3. Heat exchanger (1) according either one of the preceding claims, characterized in that the corrugations of the corrugated tubes (3) have an amplitude (Oa) comprised between 0.5 and 3.5 mm.
  4. Heat exchanger (1) according to any of the preceding claims, characterized in that the corrugations of the corrugated tubes (3) have a pitch (Op) comprised between 5 and 9 mm.
  5. Heat exchanger (1) according to any one of the preceding claims, characterized in that the said corrugated tubes (3) comprise at least one line of corrugation (45) extending obliquely with respect to the longitudinal axis of the corrugated tubes (3) at an angle comprised between 30 and 60°.
  6. Heat exchanger (1) according to any one of the preceding claims, characterized in that the said corrugated tubes (3) have a cross section adapted to ensure that the cross section formed by the tube ends (3a) of the said corrugated tubes (3) assembled is oblong.
  7. Heat exchanger (1) according to any one of the preceding claims, characterized in that the distance between the upper faces of two successive assemblies of corrugated tubes (3) is comprised between 2 and 8 mm.
EP15186571.4A 2014-09-24 2015-09-23 Heat exchanger for a motor vehicle Active EP3001133B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1458986A FR3026164B1 (en) 2014-09-24 2014-09-24 HEAT EXCHANGER FOR MOTOR VEHICLE

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EP3001133A1 EP3001133A1 (en) 2016-03-30
EP3001133B1 true EP3001133B1 (en) 2018-09-19

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Publication number Priority date Publication date Assignee Title
IT201600111604A1 (en) * 2016-11-07 2018-05-07 Carmelo Vitale RADIATOR, PRESS AND METHOD
US11454451B2 (en) * 2020-10-23 2022-09-27 Raytheon Technologies Corporation Tube bank heat exchanger

Family Cites Families (6)

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Publication number Priority date Publication date Assignee Title
US3702632A (en) * 1970-08-14 1972-11-14 Frederick W Grimshaw Heat exchanger core
DE102007054913A1 (en) * 2006-11-15 2008-08-28 Behr Gmbh & Co. Kg Heat exchanger
FR2923589B1 (en) * 2007-11-08 2015-12-11 Valeo Systemes Thermiques Branche Thermique Moteur HEAT EXCHANGER FLUID / FLUID TYPE HEAT EXCHANGER
DE102010019241A1 (en) * 2010-05-03 2011-11-03 Benteler Automobiltechnik Gmbh Process for the preparation of a heat exchanger tube and heat exchanger
FR2992713A1 (en) * 2012-06-29 2014-01-03 Valeo Systemes Thermiques Beam for heat exchanger of car, has tubes stacked in stacking direction, where tubes include raised portions that are in contact with each other by stack of tubes, so as to form partition wall of fluids for manifold of heat exchanger
US20140041840A1 (en) * 2012-08-09 2014-02-13 Cooper-Standard Automotive, Inc. Oil cooler

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EP3001133A1 (en) 2016-03-30
FR3026164A1 (en) 2016-03-25

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