EP3411650A1 - Heat exchanger with improved tubes - Google Patents

Heat exchanger with improved tubes

Info

Publication number
EP3411650A1
EP3411650A1 EP17706551.3A EP17706551A EP3411650A1 EP 3411650 A1 EP3411650 A1 EP 3411650A1 EP 17706551 A EP17706551 A EP 17706551A EP 3411650 A1 EP3411650 A1 EP 3411650A1
Authority
EP
European Patent Office
Prior art keywords
tube
heat exchanger
walls
wall
exchanger according
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.)
Withdrawn
Application number
EP17706551.3A
Other languages
German (de)
French (fr)
Inventor
Christian Riondet
Jean-Marc Lesueur
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Systemes Thermiques SAS
Original Assignee
Valeo Systemes Thermiques SAS
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Valeo Systemes Thermiques SAS filed Critical Valeo Systemes Thermiques SAS
Publication of EP3411650A1 publication Critical patent/EP3411650A1/en
Withdrawn legal-status Critical Current

Links

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
    • F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/006—Tubular elements; Assemblies of tubular elements with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • 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
    • F28F2001/027—Tubular elements of cross-section which is non-circular with dimples

Definitions

  • the present invention relates to a heat exchanger, and more particularly to a tube for brazed type heat exchanger.
  • a heat exchanger generally comprises tubes, in which a heat transfer fluid is intended to circulate, and heat exchange elements connected to these tubes.
  • Brazed and mechanical type heat exchangers are usually distinguished by their manufacturing process.
  • the fluid circulation tubes are generally delimited each by first and second opposed planar walls.
  • the fins are interposed between the tubes to which they are connected by brazing.
  • the ends of the tubes are connected to fluid collectors.
  • This type of tube however, has the disadvantage of being expensive to manufacture, because it is usually made by extrusion in corrosion-sensitive materials. In addition, it is difficult to make a tube whose walls have a small thickness while maintaining channels of large width.
  • the object of the invention is to propose a heat exchanger whose tubes make it possible to increase heat exchange with limited pressure losses and whose production cost is reduced.
  • the subject of the invention is a heat exchanger comprising at least one flat fluid circulation tube defined by first and second opposed flat walls,
  • each wall comprises elongated depressions substantially parallel to each other and to a direction of flow of the fluid intended to flow in the tube, the depressions of the first wall being shifted transversely relative to those of the second wall, so that to that Depression of the first wall extends between two depressions of the second wall.
  • the depressions are elongated, there are no discontinuities along the walls of the tube, and the pressure losses are limited. Moreover, the cost of manufacturing such a tube is limited because the depressions can be made by shaping the flat walls of the tube, without extrusion.
  • the depressions of the first wall being shifted transversely relative to those of the second wall, so that a depression of the first wall extends between two depressions of the second wall, the channel effect is accentuated. flat with rounded contours, this being conducive to heat exchange without significant pressure losses.
  • two successive recesses of the same plane wall are separated by a flat portion of the same wall.
  • each wall comprises a central portion extending in the longitudinal direction of the tube in which the depressions extend and longitudinal end portions without depressions extending in the longitudinal direction of the tube.
  • the distance between the inner faces of the planar walls in the central portion having depressions is less than the distance between the inner faces of the planar walls in the longitudinal end portions.
  • the distance between the outer faces of the walls in the longitudinal end portions is between 0.8 mm and 2 mm, preferably between 1 mm and 1 .4 mm.
  • the length of the longitudinal end portions is between 20 mm and 40 mm.
  • the section of the tube being of generally oblong shape, the width of the central part comprising depressions is equal to at least 70% of the width of the tube, preferably at least 80% of the width of the tube. , the width of the tube being defined as the major axis of the section of the tube.
  • each wall includes lateral end portions extending in the lateral direction of the tube without depressions.
  • the distance between the inner faces of the planar walls in the central portion having depressions is less than the distance between the inner faces of the planar walls in the lateral end portions.
  • the distance between the outer faces of the walls in the lateral end portions is between 0.8 mm and 2 mm, preferably between 1 mm and 1.4 mm.
  • the maximum distance between the inner faces of the walls in the central part having recesses is between 0.3 mm and 0.8 mm, preferably between 0.5 mm and 0.6 mm. In a particular embodiment, the thickness of the walls is between 0.2 mm and 0.4 mm.
  • the exchanger comprising at least two consecutive fluid circulation flat tubes each delimited by first and second opposed flat walls, the section of each tube being of generally oblong shape, the distance between the median longitudinal planes of two consecutive tubes is between 5 mm and 10 mm, preferably between 5 mm and 8 mm.
  • the invention also relates to a motor vehicle comprising a heat exchanger according to the invention.
  • FIG. 1 is a cross-sectional view of a heat exchanger according to a particular embodiment of the invention.
  • FIG. 2 is a perspective view of a portion of a tube of a heat exchanger according to a particular embodiment of the invention
  • FIG. 3 is a cross-sectional view along the plane III-III of Figure 2;
  • FIG. 4 is a detailed view of the circled portion IV of FIG. 3.
  • FIG. 1 shows a portion of a brazed heat exchanger 1 according to the invention intended to equip a motor vehicle.
  • the heat exchanger 1 comprises 2 flat tubes of fluid circulation connected by soldering to superposed fins 3. For the sake of clarity, FIG. 1 only shows one of these fins 3.
  • Each tube 2 has a generally flat tubular elongated shape of substantially oblong cross-section, and is delimited by first and second opposed flat walls 2a, 2b.
  • the distance, or not, P, between the median longitudinal planes of two consecutive tubes 2 is between 5 mm and 10 mm, preferably between 5 mm and 8 mm.
  • the thickness T T (see in particular FIG. 3) of the first wall 2a and the second wall 2b is advantageously between 0.2 mm and 0.4 mm.
  • each wall 2a, 2b comprises recesses 4 elongated substantially parallel to one another and to a direction of flow of the fluid intended to flow in the tube 2.
  • the recesses 4 extend over respective central portions 6 of the first wall 2a and the second wall 2b, which extend in the longitudinal direction of the tube 2 so as to leave without recesses 4 longitudinal end portions 8 which extend in the longitudinal direction of the tube 2.
  • the longitudinal term here must be understood as following the longitudinal direction of the tube, which corresponds to the direction of flow of the fluid intended to flow in the tube 2.
  • the length L E of the longitudinal end portions 8 is between 20 mm and 40 mm.
  • the central portion 6 comprising the recesses 4 extends in the lateral direction of the tube 2 so as to leave the end portions without recesses.
  • Lateral extension of the tube should be understood here as in the lateral direction of the tube, which corresponds to the direction of the width of the tube 2, the width of the tube being defined as the large axis of the oblong section of the tube 2.
  • the width W D of the central portion 6 is equal to at least 70% of the width of the tube 2, or 80% of the width of the tube 2.
  • the depressions 4 have a semicircular cross section.
  • the recesses of the first wall 2a are offset transversely relative to those of the second wall 2b (lower wall), so that a depression 4 of the first wall 2a extends between two recesses 4 of the second wall 2b.
  • a depression 4 of the first wall 2a is located opposite a flat portion 12 of the second wall 2b.
  • the distance H between the inner faces 14 of the walls p! AR- ⁇ 2a, 2b in the central part 6, where the depressions 4 extend, is less than the distance H E between the inner faces 14 of the walls 2a, 2b planes in the longitudinal end portions 8, as well as in the lateral end portions 1 0.
  • the variation between, on the one hand, the maximum distance Hi between the inner faces 14 of the walls 2a, 2b in the central part 6 having depressions 4 and, on the other hand, on the other hand, the minimum distance H 2 between the internal faces 14 of the walls 2a, 2b in the central part 6 is less than 20% between the internal faces 14 of the walls 2a, 2b in the central part 6.
  • the maximum distance between the inner faces 14 of the walls 2a, 2b, which corresponds to the distance H in the central portion 6 having the depressions 4, is between 0.3 mm and 0.8 mm, preferably between 0.5 mm and 0.6 mm. .
  • the maximum distance between the outer faces 1 6 of the walls 2a, 2b, also called height of the tube H T is between 0.8 mm and 2 mm, preferably between 1 mm and 1 .4 mm.
  • the height of the tube H T corresponds in this case to, firstly, the distance between the outer faces 16 of the walls 2a, 2b in the longitudinal end portions 8, and, secondly, to the distance between the outer faces of the walls 2a, 2b in the lateral end portions 1 0.
  • the cross section of the depressions may have a general triangular or rectangular shape rather than semi-circular.
  • the tube may also be a bent tube with central legs, or an electro-welded tube.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

The invention relates to a heat exchanger comprising at least one flat fluid-circulation tube (2) delimited by first (2a) and second (2b) facing planar walls. Each wall (2a, 2b) comprises elongate recesses (4) substantially parallel to one another and to a flow direction of the fluid intended for circulating in the tube (2). The recesses of the first wall (2a) are transversely offset relative to those of the second wall (2b), so that one recess of the first wall (2a) extends between two recesses (4) of the second wall (2b).

Description

Echangeur de chaleur à tubes améliorés  Improved tube heat exchanger
La présente invention concerne un échangeur de chaleur, et plus particulièrement un tube pour échangeur de chaleur de type brasé. The present invention relates to a heat exchanger, and more particularly to a tube for brazed type heat exchanger.
Un échangeur de chaleur comprend généralement des tubes, dans lesquels un fluide caloporteur est destiné à circuler, et des éléments d'échange de chaleur reliés à ces tubes.  A heat exchanger generally comprises tubes, in which a heat transfer fluid is intended to circulate, and heat exchange elements connected to these tubes.
On distingue habituellement des échangeurs de chaleur de type brasé et de type mécanique selon leur procédé de fabrication.  Brazed and mechanical type heat exchangers are usually distinguished by their manufacturing process.
Dans un échangeur de type brasé, les tubes de circulation de fluide sont généralement délimités chacun par des première et seconde parois planes opposées. Des ailettes sont intercalées entre les tubes auxquels elles sont reliées par brasage. Les extrémités des tubes sont reliées à des collecteurs de fluide.  In a brazed type exchanger, the fluid circulation tubes are generally delimited each by first and second opposed planar walls. The fins are interposed between the tubes to which they are connected by brazing. The ends of the tubes are connected to fluid collectors.
Afin d'augmenter les échanges thermiques dans l'échangeur, il est connu de l'art antérieur de prévoir, entre les première et seconde parois planes de chaque tube, des cloisons internes définissant une ou plusieurs rangées de canaux parallèles.  In order to increase heat exchange in the exchanger, it is known from the prior art to provide, between the first and second planar walls of each tube, internal partitions defining one or more rows of parallel channels.
Ce type de tube présente toutefois l'inconvénient d'être cher à fabriquer, car il est généralement réalisé par extrusion dans des matériaux sensibles à la corrosion. En outre, il est difficile de réaliser un tube dont les parois ont une faible épaisseur tout en conservant des canaux de largeur importante.  This type of tube, however, has the disadvantage of being expensive to manufacture, because it is usually made by extrusion in corrosion-sensitive materials. In addition, it is difficult to make a tube whose walls have a small thickness while maintaining channels of large width.
On connaît du document US 8'267'163 un échangeur de chaleur comprenant des tubes plats de circulation de fluide caloporteur délimités chacun par des première et seconde parois planes opposées comprenant plusieurs rangées de petits enfoncements localisés.  Document US Pat. No. 8,267,163 discloses a heat exchanger comprising heat transfer fluid circulation flat tubes each delimited by first and second opposed flat walls comprising several rows of small localized depressions.
Cependant, la présence de ces enfoncements en grand nombre, et en particulier les discontinuités qu'ils engendrent le long des parois, a pour conséquence une perte de charge importante du fluide circulant dans les tubes.  However, the presence of these depressions in large numbers, and in particular the discontinuities they generate along the walls, results in a significant pressure drop of the fluid flowing in the tubes.
L'invention a pour but de proposer un échangeur de chaleur dont les tubes permettent d'augmenter l'échange thermique avec des pertes de charge limitées et dont le coût de fabrication est réduit.  The object of the invention is to propose a heat exchanger whose tubes make it possible to increase heat exchange with limited pressure losses and whose production cost is reduced.
A cet effet, l'invention a pour objet un échangeur de chaleur comprenant au moins un tube plat de circulation de fluide délimité par des première et seconde parois planes opposées,  For this purpose, the subject of the invention is a heat exchanger comprising at least one flat fluid circulation tube defined by first and second opposed flat walls,
caractérisé en ce que chaque paroi comprend des enfoncements allongés sensiblement parallèles entre eux et à une direction d'écoulement du fluide destiné à circuler dans le tube, les enfoncements de la première paroi étant décalés transversalement par rapport à ceux de la seconde paroi, de façon à ce qu'un enfoncement de la première paroi s'étende entre deux enfoncements de la seconde paroi. characterized in that each wall comprises elongated depressions substantially parallel to each other and to a direction of flow of the fluid intended to flow in the tube, the depressions of the first wall being shifted transversely relative to those of the second wall, so that to that Depression of the first wall extends between two depressions of the second wall.
Du fait que les enfoncements sont allongés, il n'y a pas de discontinuités le long des parois du tube, et les pertes de charge sont limitées. Par ailleurs, le coût de fabrication d'un tel tube est limité car les enfoncements peuvent être réalisés par mise en forme des parois planes du tube, sans extrusion.  Because the depressions are elongated, there are no discontinuities along the walls of the tube, and the pressure losses are limited. Moreover, the cost of manufacturing such a tube is limited because the depressions can be made by shaping the flat walls of the tube, without extrusion.
Enfin, les enfoncements de la première paroi étant décalés transversalement par rapport à ceux de la seconde paroi, de façon à ce qu'un enfoncement de la première paroi s'étende entre deux enfoncements de la seconde paroi, on accentue l'effet de canal plat avec des contours arrondis, ceci étant propice à l'échange thermique sans pertes de charge importantes.  Finally, the depressions of the first wall being shifted transversely relative to those of the second wall, so that a depression of the first wall extends between two depressions of the second wall, the channel effect is accentuated. flat with rounded contours, this being conducive to heat exchange without significant pressure losses.
Dans un mode de réalisation particulier, deux enfoncements successifs d'une même paroi plane sont séparés par une portion plane de cette même paroi.  In a particular embodiment, two successive recesses of the same plane wall are separated by a flat portion of the same wall.
Dans un mode de réalisation particulier, chaque paroi comprend une partie centrale s'étendant dans le sens longitudinal du tube dans laquelle s'étendent les enfoncements et des parties d'extrémité longitudinale sans enfoncements s'étendant dans le sens longitudinal du tube.  In a particular embodiment, each wall comprises a central portion extending in the longitudinal direction of the tube in which the depressions extend and longitudinal end portions without depressions extending in the longitudinal direction of the tube.
Conserver une partie d'extrémité longitudinale du tube sans enfoncements permet de conserver une surface pour le brasage des tubes au collecteur.  Keeping a longitudinal end portion of the tube without depressions keeps a surface for soldering the tubes to the collector.
Dans un mode de réalisation particulier, la distance entre les faces internes des parois planes dans la partie centrale comportant des enfoncements est inférieure à la distance entre les faces internes des parois planes dans les parties d'extrémité longitudinale.  In a particular embodiment, the distance between the inner faces of the planar walls in the central portion having depressions is less than the distance between the inner faces of the planar walls in the longitudinal end portions.
Dans un mode de réalisation particulier, la distance entre les faces externes des parois dans les parties d'extrémité longitudinale est comprise entre 0.8 mm et 2 mm, de préférence entre 1 mm et 1 .4 mm.  In a particular embodiment, the distance between the outer faces of the walls in the longitudinal end portions is between 0.8 mm and 2 mm, preferably between 1 mm and 1 .4 mm.
Dans un mode de réalisation particulier, la longueur des parties d'extrémité longitudinale est comprise entre 20 mm et 40 mm.  In a particular embodiment, the length of the longitudinal end portions is between 20 mm and 40 mm.
Dans un mode de réalisation particulier, la section du tube étant de forme générale oblongue, la largeur de la partie centrale comportant des enfoncements est égale au moins à 70% de la largeur du tube, de préférence au moins 80% de la largeur du tube, la largeur du tube étant définie comme le grand axe de la section du tube.  In a particular embodiment, the section of the tube being of generally oblong shape, the width of the central part comprising depressions is equal to at least 70% of the width of the tube, preferably at least 80% of the width of the tube. , the width of the tube being defined as the major axis of the section of the tube.
Dans un mode de réalisation particulier, la variation entre, d'une part, la distance maximale entre les faces internes des parois planes dans la partie centrale comportant des enfoncements et, d'autre part, la distance minimale entre les faces internes des parois dans la partie centrale est inférieure à 20% la distance minimale entre les faces internes des parois dans la partie centrale. De préférence, chaque paroi comprend des parties d'extrémité latérale s'étendant dans le sens latéral du tube sans enfoncements. In a particular embodiment, the variation between, on the one hand, the maximum distance between the inner faces of the flat walls in the central part comprising depressions and, on the other hand, the minimum distance between the internal faces of the walls in the central part is less than 20% the minimum distance between the internal faces of the walls in the central part. Preferably, each wall includes lateral end portions extending in the lateral direction of the tube without depressions.
Dans un mode de réalisation particulier, la distance entre les faces internes des parois planes dans la partie centrale comportant des enfoncements est inférieure à la distance entre les faces internes des parois planes dans les parties d'extrémité latérale.  In a particular embodiment, the distance between the inner faces of the planar walls in the central portion having depressions is less than the distance between the inner faces of the planar walls in the lateral end portions.
Dans un mode de réalisation particulier, la distance entre les faces externes des parois dans les parties d'extrémité latérale est comprise entre 0.8 mm et 2 mm, de préférence entre 1 mm et 1 .4 mm.  In a particular embodiment, the distance between the outer faces of the walls in the lateral end portions is between 0.8 mm and 2 mm, preferably between 1 mm and 1.4 mm.
Dans un mode de réalisation particulier, la distance maximale entre les faces internes des parois dans la partie centrale comportant des enfoncements est comprise entre 0.3 mm et 0.8 mm, de préférence entre 0.5 mm et 0.6 mm. Dans un mode de réalisation particulier, l'épaisseur des parois est comprise entre 0.2 mm et 0.4 mm.  In a particular embodiment, the maximum distance between the inner faces of the walls in the central part having recesses is between 0.3 mm and 0.8 mm, preferably between 0.5 mm and 0.6 mm. In a particular embodiment, the thickness of the walls is between 0.2 mm and 0.4 mm.
Dans un mode de réalisation particulier, l'échangeur comprenant au moins deux tubes plats de circulation de fluide consécutifs délimités chacun par des première et seconde parois planes opposées, la section de chaque tube étant de forme générale oblongue, la distance entre les plans longitudinaux médians de deux tubes consécutifs est comprise entre 5 mm et 10 mm, de préférence entre 5 mm et 8 mm.  In a particular embodiment, the exchanger comprising at least two consecutive fluid circulation flat tubes each delimited by first and second opposed flat walls, the section of each tube being of generally oblong shape, the distance between the median longitudinal planes of two consecutive tubes is between 5 mm and 10 mm, preferably between 5 mm and 8 mm.
L'invention concerne également un véhicule automobile comprenant un échangeur de chaleur selon l'invention.  The invention also relates to a motor vehicle comprising a heat exchanger according to the invention.
L'invention sera mieux comprise à la lecture de la description qui va suivre donnée uniquement à titre d'exemple et faite en se référant aux dessins dans lesquels :  The invention will be better understood on reading the description which follows, given solely by way of example and with reference to the drawings in which:
- la figure 1 est une vue en coupe transversale d'un échangeur de chaleur selon un mode de réalisation particulier de l'invention ;  - Figure 1 is a cross-sectional view of a heat exchanger according to a particular embodiment of the invention;
- la figure 2 est une vue en perspective d'une partie d'un tube d'un échangeur de chaleur selon un mode de réalisation particulier de l'invention ;  FIG. 2 is a perspective view of a portion of a tube of a heat exchanger according to a particular embodiment of the invention;
- la figure 3 est une vue en coupe transversale suivant le plan lll-lll de la figure 2 ;  - Figure 3 is a cross-sectional view along the plane III-III of Figure 2;
- la figure 4 est une vue de détail de la partie cerclée IV de la figure 3.  FIG. 4 is a detailed view of the circled portion IV of FIG. 3.
On a représenté à la figure 1 une partie d'un échangeur de chaleur 1 brasé, selon l'invention, destiné à équiper un véhicule automobile.  FIG. 1 shows a portion of a brazed heat exchanger 1 according to the invention intended to equip a motor vehicle.
L'échangeur de chaleur 1 comprend des tubes 2 plats de circulation de fluide reliés par brasage à des ailettes 3 superposées. Pour des raisons de clarté, on n'a représenté à la figure 1 qu'une seule de ces ailettes 3.  The heat exchanger 1 comprises 2 flat tubes of fluid circulation connected by soldering to superposed fins 3. For the sake of clarity, FIG. 1 only shows one of these fins 3.
Chaque tube 2 a une forme générale allongée plane tubulaire de section sensiblement oblongue, et est délimité par des première et seconde parois planes opposées 2a, 2b.  Each tube 2 has a generally flat tubular elongated shape of substantially oblong cross-section, and is delimited by first and second opposed flat walls 2a, 2b.
De préférence, la distance, ou pas P, entre les plans longitudinaux médians de deux tubes 2 consécutifs est comprise entre 5 mm et 10 mm, de préférence entre 5 mm et 8 mm. Preferably, the distance, or not, P, between the median longitudinal planes of two consecutive tubes 2 is between 5 mm and 10 mm, preferably between 5 mm and 8 mm.
Par ailleurs, l'épaisseur TT (voir notamment la figure 3) de la première paroi 2a et de la seconde paroi 2b, est avantageusement comprise entre 0.2 mm et 0.4 mm. Moreover, the thickness T T (see in particular FIG. 3) of the first wall 2a and the second wall 2b is advantageously between 0.2 mm and 0.4 mm.
Comme on peut le voir sur la figure 2 notamment, chaque paroi 2a, 2b comprend des enfoncements 4 allongés sensiblement parallèles entre eux et à une direction d'écoulement du fluide destiné à circuler dans le tube 2.  As can be seen in FIG. 2 in particular, each wall 2a, 2b comprises recesses 4 elongated substantially parallel to one another and to a direction of flow of the fluid intended to flow in the tube 2.
Les enfoncements 4 s'étendent sur des parties centrales 6 respectives de la première paroi 2a et de la seconde paroi 2b, qui s'étendent dans le sens longitudinal du tube 2 de manière à laisser sans enfoncements 4 des parties d'extrémité longitudinale 8 qui s'étendent dans le sens longitudinal du tube 2. Le terme longitudinal doit ici être compris comme suivant la direction longitudinale du tube, qui correspond à la direction de l'écoulement du fluide destiné à circuler dans le tube 2.  The recesses 4 extend over respective central portions 6 of the first wall 2a and the second wall 2b, which extend in the longitudinal direction of the tube 2 so as to leave without recesses 4 longitudinal end portions 8 which extend in the longitudinal direction of the tube 2. The longitudinal term here must be understood as following the longitudinal direction of the tube, which corresponds to the direction of flow of the fluid intended to flow in the tube 2.
Dans un mode de réalisation préféré, la longueur LE des parties d'extrémité longitudinale 8 est comprise entre 20 mm et 40 mm. In a preferred embodiment, the length L E of the longitudinal end portions 8 is between 20 mm and 40 mm.
Par ailleurs, comme on peut le voir sur la figure 3, et plus particulièrement sur la figure 4, la partie centrale 6 comprenant les enfoncements 4 s'étend dans le sens latéral du tube 2 de manière à laisser sans enfoncements des parties d'extrémité latérale 10 qui s'étendent dans le sens latéral du tube 2. Le terme latéral doit ici être compris comme suivant la direction latérale du tube, qui correspond à la direction de la largeur du tube 2, la largeur du tube étant définie comme le grand axe de la section oblongue du tube 2.  Furthermore, as can be seen in FIG. 3, and more particularly in FIG. 4, the central portion 6 comprising the recesses 4 extends in the lateral direction of the tube 2 so as to leave the end portions without recesses. 10 Lateral extension of the tube should be understood here as in the lateral direction of the tube, which corresponds to the direction of the width of the tube 2, the width of the tube being defined as the large axis of the oblong section of the tube 2.
De préférence, la largeur WD de la partie centrale 6 est égale à au moins 70% de la largeur du tube 2, voire 80% de la largeur du tube 2. Preferably, the width W D of the central portion 6 is equal to at least 70% of the width of the tube 2, or 80% of the width of the tube 2.
Comme on peut le voir aux figures 3 et 4, dans le mode de réalisation illustré, les enfoncements 4 ont une section transversale semi-circulaire.  As can be seen in Figures 3 and 4, in the illustrated embodiment, the depressions 4 have a semicircular cross section.
Les enfoncements de la première paroi 2a (paroi supérieure) sont décalés transversalement par rapport à ceux de la deuxième paroi 2b (paroi inférieure), de façon à ce qu'un enfoncement 4 de la première paroi 2a s'étende entre deux enfoncements 4 de la seconde paroi 2b.  The recesses of the first wall 2a (upper wall) are offset transversely relative to those of the second wall 2b (lower wall), so that a depression 4 of the first wall 2a extends between two recesses 4 of the second wall 2b.
Par ailleurs, deux enfoncements 4 successifs d'une même paroi 2a, 2b plane sont séparés par une portion plane 12 de cette même paroi 2a, 2b.  Moreover, two successive recesses 4 of the same wall 2a, 2b plane are separated by a flat portion 12 of the same wall 2a, 2b.
Ainsi, un enfoncement 4 de la première paroi 2a est situé en regard d'une portion plane 12 de la seconde paroi 2b.  Thus, a depression 4 of the first wall 2a is located opposite a flat portion 12 of the second wall 2b.
La distance H entre les faces internes 14 des parois p!a-R-θθ 2a,2b dans la partie centrale 6, où s'étendent les enfoncements 4, est inférieure à la distance HE entre les faces internes 14 des parois 2a, 2b planes dans les parties d'extrémité longitudinale 8, ainsi que dans les parties d'extrémité latérale 1 0. The distance H between the inner faces 14 of the walls p! AR-θθ 2a, 2b in the central part 6, where the depressions 4 extend, is less than the distance H E between the inner faces 14 of the walls 2a, 2b planes in the longitudinal end portions 8, as well as in the lateral end portions 1 0.
En particulier, comme on peut le voir à la figure 4, la variation entre, d'une part, la distance maximale Hi entre les faces internes 14 des parois 2a, 2b dans la partie centrale 6 comportant des enfoncements 4 et, d'autre part, la distance minimale H2 entre les faces internes 14 des parois 2a, 2b dans la partie centrale 6 est inférieure à 20% entre les faces internes 14 des parois 2a, 2b dans la partie centrale 6. In particular, as can be seen in FIG. 4, the variation between, on the one hand, the maximum distance Hi between the inner faces 14 of the walls 2a, 2b in the central part 6 having depressions 4 and, on the other hand, on the other hand, the minimum distance H 2 between the internal faces 14 of the walls 2a, 2b in the central part 6 is less than 20% between the internal faces 14 of the walls 2a, 2b in the central part 6.
De préférence, la distance maximale entre les faces internes 14 des parois 2a, 2b, qui correspond à la distance H dans la partie centrale 6 comportant les enfoncements 4, est comprise entre 0.3 mm et 0.8 mm, de préférence entre 0.5 mm et 0.6 mm.  Preferably, the maximum distance between the inner faces 14 of the walls 2a, 2b, which corresponds to the distance H in the central portion 6 having the depressions 4, is between 0.3 mm and 0.8 mm, preferably between 0.5 mm and 0.6 mm. .
De préférence également, la distance maximale entre les faces externes 1 6 des parois 2a, 2b, également appelée hauteur du tube HT, est comprise entre 0.8 mm et 2 mm, de préférence entre 1 mm et 1 .4 mm. Also preferably, the maximum distance between the outer faces 1 6 of the walls 2a, 2b, also called height of the tube H T , is between 0.8 mm and 2 mm, preferably between 1 mm and 1 .4 mm.
La hauteur du tube HT correspond en l'occurrence à, d'une part, la distance entre les faces externes 16 des parois 2a, 2b dans les parties d'extrémité longitudinale 8, et, d'autre part, à la distance entre les faces externes des parois 2a, 2b dans les parties d'extrémité latérale 1 0. The height of the tube H T corresponds in this case to, firstly, the distance between the outer faces 16 of the walls 2a, 2b in the longitudinal end portions 8, and, secondly, to the distance between the outer faces of the walls 2a, 2b in the lateral end portions 1 0.
L'invention n'est pas limitée au mode de réalisation présenté et d'autres modes de réalisation apparaîtront clairement à l'homme du métier.  The invention is not limited to the embodiment shown and other embodiments will become apparent to those skilled in the art.
Ainsi, la section transversale des enfoncements pourra avoir une forme générale triangulaire ou rectangulaire plutôt que semi-circulaire.  Thus, the cross section of the depressions may have a general triangular or rectangular shape rather than semi-circular.
Le tube pourra également être un tube plié avec des jambes centrales, ou un tube électro-soudé.  The tube may also be a bent tube with central legs, or an electro-welded tube.

Claims

REVENDICATIONS
1 . Echangeur de chaleur comprenant au moins un tube (2) plat de circulation de fluide délimité par des première (2a) et seconde (2b) parois planes opposées, 1. Heat exchanger comprising at least one flat fluid circulation tube (2) delimited by first (2a) and second (2b) opposed flat walls,
caractérisé en ce que chaque paroi (2a, 2b) comprend des enfoncements (4) allongés sensiblement parallèles entre eux et à une direction d'écoulement du fluide destiné à circuler dans le tube (2), les enfoncements de la première paroi (2a) étant décalés transversalement par rapport à ceux de la seconde paroi (2b), de façon à ce qu'un enfoncement de la première paroi (2a) s'étende entre deux enfoncements (4) de la seconde paroi (2b).  characterized in that each wall (2a, 2b) comprises recesses (4) elongate substantially parallel to each other and at a flow direction of the fluid for circulation in the tube (2), the depressions of the first wall (2a). being offset transversely relative to those of the second wall (2b), so that a depression of the first wall (2a) extends between two recesses (4) of the second wall (2b).
2. Echangeur de chaleur selon la revendication 1 , dans lequel deux enfoncements (4) successifs d'une même paroi plane (2a, 2b) sont séparés par une partie plane (12) de cette même paroi.  2. heat exchanger according to claim 1, wherein two successive recesses (4) of the same plane wall (2a, 2b) are separated by a flat portion (12) of the same wall.
3. Echangeur de chaleur selon la revendication 1 ou 2, dans lequel chaque paroi 3. Heat exchanger according to claim 1 or 2, wherein each wall
(2a, 2b) comprend une partie centrale (6) s'étendant dans le sens longitudinal du tube (2) dans laquelle s'étendent les enfoncements (4) et des parties d'extrémité longitudinale (8) sans enfoncements (4) s'étendant dans le sens longitudinal du tube (2). (2a, 2b) comprises a central portion (6) extending in the longitudinal direction of the tube (2) in which the depressions (4) extend and longitudinal end portions (8) without depressions (4). extending in the longitudinal direction of the tube (2).
4. Echangeur de chaleur selon la revendication 3, dans lequel la distance (H) entre les faces internes (14) des parois planes (2a, 2b) dans la partie centrale (6) comportant des enfoncements (4) est inférieure à la distance (HE) entre les faces internes (14) des parois planes (2a, 2b) dans les parties d'extrémité longitudinale (8). 4. Heat exchanger according to claim 3, wherein the distance (H) between the inner faces (14) of the planar walls (2a, 2b) in the central portion (6) having depressions (4) is less than the distance. (H E ) between the inner faces (14) of the planar walls (2a, 2b) in the longitudinal end portions (8).
5. Echangeur de chaleur selon la revendications 3 ou 4, dans lequel la distance (HT) entre les faces externes (16) des parois (2a, 2b) dans les parties d'extrémité longitudinale (8) est comprise entre 0.8 mm et 2 mm, de préférence entre 1 mm et 1 .4 mm. 5. Heat exchanger according to claim 3 or 4, wherein the distance (H T ) between the outer faces (16) of the walls (2a, 2b) in the longitudinal end portions (8) is between 0.8 mm and 2 mm, preferably between 1 mm and 1 .4 mm.
6. Echangeur de chaleur selon l'une quelconque des revendications 3 à 5, dans lequel la longueur (LE) des parties d'extrémité longitudinale (8) est comprise entre 20 mm et 40 mm. 6. Heat exchanger according to any one of claims 3 to 5, wherein the length (L E ) of the longitudinal end portions (8) is between 20 mm and 40 mm.
7. Echangeur de chaleur selon l'une quelconque des revendications 3 à 6, dans lequel, la section du tube (2) étant de forme générale oblongue, la largeur (WD) de la partie centrale (6) comportant des enfoncements (4) est égale au moins à 70% de la largeur du tube (2), de préférence au moins à 80% de la largeur du tube (2), la largeur du tube (2) étant définie comme le grand axe de la section du tube (2), 7. Heat exchanger according to any one of claims 3 to 6, wherein, the section of the tube (2) being generally oblong shape, the width (W D ) of the central portion (6) having depressions (4). ) is at least 70% of the width of the tube (2), preferably at least 80% of the width of the tube (2), the width of the tube (2) being defined as the major axis of the section of the tube (2) tube (2),
8. Echangeur de chaleur selon l'une quelconque des revendications 3 à 7, dans lequel la variation entre, d'une part la distance maximale (Hi) entre les faces internes (14) des parois (2a,2b) dans la partie centrale (6) comportant des enfoncements (4) et, d'autre part, la distance minimale (H2) entre les faces internes (14) des parois (2a, 2b) dans la partie centrale (6) est inférieure à 20% de la distance minimale (H2) entre les faces internes (14) des parois (2a, 2b) dans la partie centrale (6). 8. Heat exchanger according to any one of claims 3 to 7, wherein the variation between, on the one hand the maximum distance (Hi) between the inner faces. (14) walls (2a, 2b) in the central portion (6) having recesses (4) and, on the other hand, the minimum distance (H 2 ) between the inner faces (14) of the walls (2a, 2b ) in the central part (6) is less than 20% of the minimum distance (H 2 ) between the inner faces (14) of the walls (2a, 2b) in the central part (6).
9. Echangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel chaque paroi (2a, 2b) comprend des parties d'extrémité latérale (10) s'étendant dans le sens latéral du tube (2) sans enfoncements (4).  9. Heat exchanger according to any one of the preceding claims, wherein each wall (2a, 2b) comprises lateral end portions (10) extending in the lateral direction of the tube (2) without depressions (4). .
10. Echangeur de chaleur selon la revendication 9 , dans lequel la distance (H) entre les faces internes (14) des parois planes (2a, 2b) dans la partie centrale (6) comportant des enfoncements (4) est inférieure à la distance (HE) entre les faces internes (14) des parois planes (2a, 2b) dans les parties d'extrémité latérale (10). 10. Heat exchanger according to claim 9, wherein the distance (H) between the inner faces (14) of the plane walls (2a, 2b) in the central portion (6) having depressions (4) is less than the distance. (H E ) between the inner faces (14) of the planar walls (2a, 2b) in the lateral end portions (10).
11 . Echangeur de chaleur selon la revendications 9 ou 10, dans lequel la distance (HT) entre les faces externes (16) des parois (2a,2b) dans les parties d'extrémité latérale (10) est comprise entre 0.8 mm et 2 mm, de préférence entre 1 mm et 1 .4 mm. 11. Heat exchanger according to claim 9 or 10, wherein the distance (H T ) between the outer faces (16) of the walls (2a, 2b) in the lateral end portions (10) is between 0.8 mm and 2 mm preferably between 1 mm and 1 .4 mm.
12. Echangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel la distance maximale (H) entre les faces internes (14) des parois (2a, 2b) dans la partie centrale (6) comportant des enfoncements (4) est comprise entre 0.3 mm et 0.8 mm, de préférence entre 0.5 mm et 0.6 mm.  12. Heat exchanger according to any one of the preceding claims, wherein the maximum distance (H) between the inner faces (14) of the walls (2a, 2b) in the central portion (6) having depressions (4) is between 0.3 mm and 0.8 mm, preferably between 0.5 mm and 0.6 mm.
13. Echangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel l'épaisseur (TT) des parois (2a, 2b) est comprise entre 0.2 mm et 0.4 mm. 13. Heat exchanger according to any one of the preceding claims, wherein the thickness (T T ) of the walls (2a, 2b) is between 0.2 mm and 0.4 mm.
14. Echangeur de chaleur selon l'une quelconque des revendications précédentes, comprenant au moins deux tubes (2) plats de circulation de fluide consécutifs délimités chacun par des première (2a) et seconde (2b) parois planes opposées, la section de chaque tube (2) étant de forme générale oblongue, dans lequel la distance (P) entre les plans longitudinaux médians de deux tubes (2) consécutifs est comprise entre 5 mm et 10 mm, de préférence entre 5 mm et 8 mm.  14. Heat exchanger according to any one of the preceding claims, comprising at least two tubes (2) consecutive fluid circulation each delimited by first (2a) and second (2b) opposite flat walls, the section of each tube. (2) being of generally oblong shape, wherein the distance (P) between the median longitudinal planes of two consecutive tubes (2) is between 5 mm and 10 mm, preferably between 5 mm and 8 mm.
15. Véhicule automobile comprenant un échangeur de chaleur (1 ) selon l'une quelconque des revendications précédentes.  15. Motor vehicle comprising a heat exchanger (1) according to any one of the preceding claims.
EP17706551.3A 2016-02-05 2017-01-20 Heat exchanger with improved tubes Withdrawn EP3411650A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1650927A FR3047554B1 (en) 2016-02-05 2016-02-05 HEAT EXCHANGER WITH IMPROVED TUBES
PCT/FR2017/050119 WO2017134359A1 (en) 2016-02-05 2017-01-20 Heat exchanger with improved tubes

Publications (1)

Publication Number Publication Date
EP3411650A1 true EP3411650A1 (en) 2018-12-12

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ID=55752529

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Application Number Title Priority Date Filing Date
EP17706551.3A Withdrawn EP3411650A1 (en) 2016-02-05 2017-01-20 Heat exchanger with improved tubes

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EP (1) EP3411650A1 (en)
CN (1) CN109073335A (en)
FR (1) FR3047554B1 (en)
WO (1) WO2017134359A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114184059A (en) * 2020-09-15 2022-03-15 洛阳明远石化技术有限公司 Heat exchange tube and heat exchanger comprising same

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5186250A (en) * 1990-05-11 1993-02-16 Showa Aluminum Kabushiki Kaisha Tube for heat exchangers and a method for manufacturing the tube
KR100261006B1 (en) * 1996-07-03 2000-07-01 오타 유다카 Flat tube for radiator
JPH10137877A (en) * 1996-11-05 1998-05-26 Zexel Corp Manufacture of tube heat exchanger
US6151949A (en) * 1999-08-25 2000-11-28 Visteon Global Technologies, Inc. Method of manufacturing a flat corrugated tube
CN202145023U (en) * 2011-07-01 2012-02-15 北京桑普电器有限公司 Oil-filled type sheet electric heater with diamond-shaped channels
CN204202469U (en) * 2014-10-29 2015-03-11 张博然 Wing type flat heat exchange pipe

Also Published As

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FR3047554B1 (en) 2019-05-17
FR3047554A1 (en) 2017-08-11
CN109073335A (en) 2018-12-21
WO2017134359A1 (en) 2017-08-10

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