EP2006631A1 - Collector flange for a heat exchanger - Google Patents

Collector flange for a heat exchanger Download PDF

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Publication number
EP2006631A1
EP2006631A1 EP08155365A EP08155365A EP2006631A1 EP 2006631 A1 EP2006631 A1 EP 2006631A1 EP 08155365 A EP08155365 A EP 08155365A EP 08155365 A EP08155365 A EP 08155365A EP 2006631 A1 EP2006631 A1 EP 2006631A1
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EP
European Patent Office
Prior art keywords
flange
channels
collector
fluid
chambers
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Withdrawn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
EP08155365A
Other languages
German (de)
French (fr)
Inventor
Isabelle Citti
Nicolas Vallée
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
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Filing date
Publication date
Application filed by Valeo Systemes Thermiques SAS filed Critical Valeo Systemes Thermiques SAS
Publication of EP2006631A1 publication Critical patent/EP2006631A1/en
Withdrawn legal-status Critical Current

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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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • 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
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
    • F28F9/0253—Massive connectors, e.g. blocks; Plate-like connectors with multiple channels, e.g. with combined inflow and outflow channels
    • 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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/12—Fastening; Joining by methods involving deformation of the elements
    • F28F2275/122—Fastening; Joining by methods involving deformation of the elements by crimping, caulking or clinching

Definitions

  • the present invention relates to a collector flange for a heat exchanger for the equipment of a motor vehicle.
  • It has more particularly as object, but not exclusively, a flange and a collector, having at least a collection chamber, for an exchanger in which circulates a heat transfer fluid cooled by an external air flow.
  • the heat exchangers intended for the circulation of the "R-744" must be adapted to satisfy the high operating pressure of this fluid. This is why these types of heat exchangers often have collectors with two arches or two chambers to allow a good resistance to pressure.
  • This system has several disadvantages. First, it makes particularly difficult the orientation of the tubing in the different directions required by the general structure under hood. Moreover, the distribution of the fluid between the two ducts does not take place in a balanced ratio, in particular this distribution is a function of the CO 2 pressure / flow rate.
  • the document is also known EP 1462749 in which the fluid supply is carried out using a tubular pierced at its end, this tubing being pierced either in its longitudinal direction or in its transverse direction.
  • the optimization of the distribution of the fluid in the two arches is effected by varying the outlet diameters or by offsetting the position of the tubing relative to the longitudinal center of symmetry of the box.
  • this embodiment lies in a high pressure loss due in particular to the fact that in both cases, the fluid hits a flat surface before distributing in the two chambers. Furthermore, this embodiment has a low mechanical strength, especially to torsion, since the collector / flange contact is made on two cylinders, without return.
  • the present invention intends to overcome the disadvantages of existing heat exchanger flanges.
  • the invention relates to a flange for feeding a collector, comprising at least two chambers, to a heat exchanger, the flange having an inlet for communication with a pipe carrying a coolant towards the collector, characterized in that it comprises at least two fluid circulation channels, respectively to each of the two chambers, extending linearly from the aforesaid inlet orifice, to form between them an angle less than 180 °.
  • ifice means that the flange according to the invention does not include any inlet chamber receiving the fluid from the tubing. Indeed, the inlet orifice of the flange according to the invention is solely constituted by the meeting of the two linear flow channels, without other cut or truncated portion of the flange.
  • the present invention is particularly well suited to heat exchangers in which circulates a gas at very high pressure, such as CO 2 .
  • the collector chambers are often small because of their thick walls necessary for the holding of significant pressures (of the order of 100 to 150 bars).
  • the tubing it is not possible for the tubing to directly feed the two or more chambers of the collector; the diameter of the tubing being classically lower than the thickness of the wall separating the two chambers of the manifold. This is especially visible on the figure 1 .
  • the present invention also relates to a collector for a heat exchanger, comprising at least two chambers for the circulation of at least one fluid, characterized in that a flange, according to the characteristics described herein, is fixed to said collector.
  • this collector is adapted to the circulation of a very high pressure fluid of the CO 2 type.
  • the present invention relates to a heat exchanger for exchanging heat between two fluids, in particular for motor vehicles, comprising at least one collector and / or a flange according to the characteristics described above.
  • the present invention applies to all types of exchanger comprising at least one manifold including at least two inlet / distribution chambers of a heat transfer fluid.
  • the collector chosen to illustrate the invention represented on the figure 5 , a collector plate 1, an intermediate plate 2 and a cover 3 which here comprises two arches 4, 4 'so as to create two fluid circulation chambers 5 and 6.
  • the invention applies to a manifold of different structure, always having a plurality of flow chambers 5, 6, for example a manifold, or manifold, made in one piece.
  • the lid 3 has a flat upper surface 7 located respectively at its two ends, or lateral sides intended to allow optimum crimping of protuberances, or teeth 8, extending from the collector plate 1 in order to bind / fix the elements 1, 2 and 3 together.
  • Each arch 4, 4 ' consists essentially of a semicircle so that their section fits in a circle so as to best withstand the pressure of the supercritical fluid, CO 2 or the like.
  • the tubing 9 conventionally consists of a hollow cylinder with a thick wall, still for holding at high pressures.
  • the flange 10 constitutes, punctually, that is to say only where the flange 10 is attached to the collector, the tops of the arches 4, 4 'and the upper part of the lid 3.
  • the flange 10 comprises in particular the flat surfaces 7 so that the flange is fixed to the lid 3, to the intermediate plate 2 and to the collector plate 1 mainly by crimping the teeth 8 on these parts 7.
  • the flange 10 comprises a housing portion 11 intended to receive and accommodate the end of the tubing 9.
  • This housing portion 11 obviously has a geometry adapted to or equivalent to that of the end of the tubing 9.
  • the pipe 9 extends vertically, that is to say perpendicularly to the longitudinal axis of the collector and extending in the plane defined by the two circulation channels 12, 12 'of the flange 10.
  • the angle between the two channels 5, 6 will ideally be between 60 ° and 120 °.
  • the tubing 9 extends parallel to the manifold so that the tubing 9, and therefore the circulation of the fluid inside, extends perpendicularly to the plane defined by the two circulation channels 12, 12 'of the flange 10. It will be possible to provide that the inner end of the tubing 9 has a curved portion bringing the fluid to the inlet of the tubing 9.
  • tubing 9 extends horizontally, that is to say it has an axis perpendicular to the longitudinal axis of the collector and is in the plane defined by the two circulation channels 12, 12 'of the flange 10.
  • the angle between the two channels 5, 6 will be considerably less than 90 °, preferably between 30 ° and 80 °.
  • the figure 6 illustrates the flow of the fluid in the circulation channels 12, 12 'of the flange 10, the main common flow, at the level of the pipe 9, and that of each of the two channels 12 and 12', and the balanced distribution of the fluid between the two channels 12, 12 '. It is clearly seen in this figure that the fluid flow in each of the two channels 12, 12 'is optimized.
  • the two channels 12, 12 ' may have a linear section, as shown in the accompanying figures.
  • these two channels 12, 12 ' have different end sections, for example sections substantially parallel to each other, while retaining the two aspects of the invention which are the absence of a chamber / part dedicated to receiving the fluid from the tubing 9 and producing a plurality of channels 12, 12 'extending from the inlet port of the flange 10, extending substantially linearly and forming between an angle strictly less than the flat angle (180 °).
  • the invention makes it possible to distribute in a particularly equitable manner the flow rate in the two distribution channels 12, 12 'of the flange 10 so that the fluid occupies substantially equally the different chambers 5, 6 of the collector.
  • the invention thus allows a "self-balancing" flow rates in each chamber 5, 6 without having to resort to variations in diameter.
  • the design, or the "Design”, of Y-distribution of the flange 10 also allows an optimization in terms of size, thus avoiding the counter drilling.

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

Abstract

The flange (10) has an inlet opening for communication with an insert (9) carrying a heat transfer fluid towards a manifold. Two fluid circulation channels (12, 12 ') circulates the fluid to two fluid circulation tubes (5, 6) respectively, where a number of channels is equivalent to a number of tubes of the manifold. The tubes linearly extend from the inlet opening to form an angle less than 180 degree between them, and an angle between the two channels is below 90 degree. The channels extend in a parallel plane to a linear axis of the insert.

Description

La présente invention concerne une bride de collecteur pour un échangeur de chaleur destiné à l'équipement d'un véhicule automobile.The present invention relates to a collector flange for a heat exchanger for the equipment of a motor vehicle.

Elle a plus particulièrement comme objet, mais non exclusivement, une bride et un collecteur, présentant au moins de chambre de collecte, pour un échangeur dans lequel circule un fluide caloporteur refroidi par une circulation d'air extérieur.It has more particularly as object, but not exclusively, a flange and a collector, having at least a collection chamber, for an exchanger in which circulates a heat transfer fluid cooled by an external air flow.

Elle s'applique particulièrement bien aux échangeurs utilisés dans l'industrie automobile pour refroidir (en partie haute pression) un fluide utilisé dans une boucle frigorifique. Lorsqu'on refroidit du CO2 gazeux à pression constante (aux pertes de charge près), il y a un échange d'énergie calorifique avec le milieu ambiant. On peut donc utiliser ce phénomène physique (appelé également supercriticité) pour réaliser une machine frigorifique performante par compression/détente. Ce fluide super critique (au dessus de 31°C) est connu sous la dénomination « R-744 ».It is particularly applicable to exchangers used in the automotive industry for cooling (at high pressure part) a fluid used in a refrigerating loop. When CO 2 gas is cooled at constant pressure (at pressure losses), there is an exchange of heat energy with the ambient environment. It is therefore possible to use this physical phenomenon (also called supercriticality) to produce a powerful refrigeration machine by compression / expansion. This super critical fluid (above 31 ° C) is known under the name "R-744".

Les échangeurs de chaleur destinés à la circulation du « R-744 » doivent être adaptés pour satisfaire à la pression de service élevée de ce fluide. C'est pourquoi ces types d'échangeurs de chaleur comportent souvent des collecteurs à deux arches ou deux chambres pour permettre une bonne tenue à la pression.The heat exchangers intended for the circulation of the "R-744" must be adapted to satisfy the high operating pressure of this fluid. This is why these types of heat exchangers often have collectors with two arches or two chambers to allow a good resistance to pressure.

Avec ce type de collecteur à deux arches ou deux chambres de distribution, il est recommandé d'alimenter équitablement ces deux arches/chambres afin de limiter au maximum la perte de charge liée, à l'écoulement. En effet, le problème principal de ce genre de structure pour le collecteur réside dans la perte de charge, souvent importante, au niveau de l'entrée du fluide ce qui nécessite d'utiliser pour le circuit thermique une pompe plus puissante, et donc plus coûteuse, et dégrade également sensiblement la résistance à la corrosion de l'échangeur dans la zone située au niveau de ces pertes de charge.With this type of collector with two arches or two distribution chambers, it is recommended to equitably feed these two arches / chambers in order to limit as much as possible the pressure loss associated with the flow. Indeed, the main problem of this kind of structure for the collector lies in the loss of charge, often important, at the fluid inlet which requires the use of a more powerful pump for the thermal circuit, and therefore more expensive, and also degrades substantially the corrosion resistance of the exchanger in the area at the level of these pressure drops.

Pour répondre à cette problématique, on connaît déjà le document JP 2004293876 qui divulgue une bride dont les diamètres des conduits d'alimentation destinés respectivement à chacune des deux chambres présentent des diamètres différents, le premier conduit, c'est-à-dire le conduit pour lequel le fluide circulant rencontre l'entrée en premier, présente un diamètre inférieur au second conduit, afin d'équilibrer la proportion de fluide passant par le premier conduit par rapport à celle passant par le second conduit.To answer this problem, we already know the document JP 2004293876 which discloses a flange whose diameters of the supply ducts intended respectively for each of the two chambers have different diameters, the first duct, that is to say the duct for which the flowing fluid meets the inlet first, presents a diameter smaller than the second duct, in order to balance the proportion of fluid passing through the first duct relative to that passing through the second duct.

Ce système présente plusieurs inconvénients. Tout d'abord, il rend particulièrement difficile l'orientation de la tubulure dans les différentes directions exigées par la structure générale sous capot. Par ailleurs, la distribution du fluide entre les deux conduits ne s'effectue pas selon un rapport équilibré, en particulier cette distribution est fonction de la pression/débit du CO2.This system has several disadvantages. First, it makes particularly difficult the orientation of the tubing in the different directions required by the general structure under hood. Moreover, the distribution of the fluid between the two ducts does not take place in a balanced ratio, in particular this distribution is a function of the CO 2 pressure / flow rate.

On connaît également le document EP 1462749 dans lequel l'alimentation en fluide est réalisée à l'aide d'une tubulure percée en son extrémité, cette tubulure étant percée soit dans son sens longitudinal soit dans son sens transversal. Dans cette réalisation, l'optimisation de la répartition du fluide dans les deux arches s'effectue en faisant varier les diamètres de sortie ou en excentrant la position de la tubulure par rapport au centre de symétrie longitudinal de la boîte.The document is also known EP 1462749 in which the fluid supply is carried out using a tubular pierced at its end, this tubing being pierced either in its longitudinal direction or in its transverse direction. In this embodiment, the optimization of the distribution of the fluid in the two arches is effected by varying the outlet diameters or by offsetting the position of the tubing relative to the longitudinal center of symmetry of the box.

Les inconvénients de cette réalisation résident dans une forte perte de charge due en particulier au fait que dans les deux cas, le fluide vient frapper une surface plane avant de se répartir dans les deux chambres. Par ailleurs, cette réalisation présente une faible tenue mécanique, notamment à la torsion, étant donné que le contact collecteur/bride se fait sur deux cylindres, sans retour.The disadvantages of this embodiment reside in a high pressure loss due in particular to the fact that in both cases, the fluid hits a flat surface before distributing in the two chambers. Furthermore, this embodiment has a low mechanical strength, especially to torsion, since the collector / flange contact is made on two cylinders, without return.

D'autres concepts envisagent de venir alimenter les arches/chambres du collecteur par deux conduits droits, l'alimentation de ces conduits étant réalisée à l'aide d'un contre perçage dans la bride. Cette réalisation présente une forte perte de charge interne au niveau de la bride du fait que le fluide vient frapper une surface plane avant de se répartir dans les conduits. Par ailleurs, cette réalisation augmente globalement l'encombrement du au contre perçage.Other concepts envisage coming to feed the arches / chambers of the collector by two straight conduits, the feeding of these ducts being made using a counterboring in the flange. This embodiment has a high internal pressure loss at the flange that the fluid hits a flat surface before being distributed in the ducts. Moreover, this embodiment generally increases the bulk of the against drilling.

La présente invention entend remédier aux inconvénients des brides pour échangeurs de chaleur existantes.The present invention intends to overcome the disadvantages of existing heat exchanger flanges.

Ainsi, l'invention concerne une bride pour l'alimentation d'un collecteur, comportant au moins deux chambres, d'un échangeur de chaleur, la bride présentant un orifice d'entrée pour la communication avec une tubulure transportant un fluide caloporteur vers le collecteur, caractérisée en ce qu'elle comprend au moins deux canaux de circulation du fluide, respectivement à destination de chacune des deux chambres, s'étendant linéairement, à partir du susdit orifice d'entrée, pour former entre eux un angle inférieur à 180°.Thus, the invention relates to a flange for feeding a collector, comprising at least two chambers, to a heat exchanger, the flange having an inlet for communication with a pipe carrying a coolant towards the collector, characterized in that it comprises at least two fluid circulation channels, respectively to each of the two chambers, extending linearly from the aforesaid inlet orifice, to form between them an angle less than 180 °.

On entend par l'expression « orifice » le fait que la bride selon l'invention ne comprend aucune chambre d'entrée recevant le fluide provenant de la tubulure. En effet, l'orifice d'entrée de la bride selon l'invention est uniquement constitué par la réunion des deux canaux de circulation linéaire, sans autre découpe ou partie tronquée de la bride.The term "orifice" means that the flange according to the invention does not include any inlet chamber receiving the fluid from the tubing. Indeed, the inlet orifice of the flange according to the invention is solely constituted by the meeting of the two linear flow channels, without other cut or truncated portion of the flange.

Grâce à l'invention, il est dorénavant possible de pouvoir alimenter les deux, ou plus, chambres de distribution du collecteur tout en limitant au maximum les pertes de charge liées à l'écoulement du fluide grâce à ce système de bride à canaux de circulation inclinés formant un Y, plus précisément un Y inversé.Thanks to the invention, it is now possible to be able to feed the two or more distribution chambers of the manifold while minimizing the pressure losses associated with the flow of the fluid through the flange system with flow channels inclined forming a Y, more precisely an inverted Y.

Par ailleurs, la présente invention est particulièrement bien adaptée aux échangeurs de chaleur dans lesquels circule un gaz à très haute pression, tel le CO2. En effet, dans ce type d'échangeurs de chaleur, les chambres du collecteur sont souvent petites du fait de leurs parois épaisses nécessaires à la tenue des pressions importantes (de l'ordre de 100 à 150 bars). Ainsi, dans ces structures particulières d'échangeurs de chaleur, il n'est pas possible que la tubulure alimente directement les deux, ou plus, chambres du collecteur ; le diamètre de la tubulure étant classiquement inférieur à l'épaisseur de la paroi séparant les deux chambres du collecteur. Ceci est notamment visible sur la figure 1.Furthermore, the present invention is particularly well suited to heat exchangers in which circulates a gas at very high pressure, such as CO 2 . Indeed, in this type of heat exchanger, the collector chambers are often small because of their thick walls necessary for the holding of significant pressures (of the order of 100 to 150 bars). Thus, in these particular heat exchanger structures, it is not possible for the tubing to directly feed the two or more chambers of the collector; the diameter of the tubing being classically lower than the thickness of the wall separating the two chambers of the manifold. This is especially visible on the figure 1 .

D'autres particularités ou caractéristiques sont présentées dans la suite :

  • la bride comprend un nombre de canaux équivalent au nombre de chambres du collecteur ;
  • l'angle entre les deux susdits canaux est inférieur à 90° ;
  • le susdit angle est compris entre 30° et 80° ;
  • les susdits canaux s'étendent dans un plan perpendiculaire à l'axe linéaire de la tubulure ;
  • l'angle entre les deux susdits canaux est compris entre 60° et 120° ;
  • les susdits canaux s'étendent dans un plan parallèle à l'axe linéaire de la tubulure. Ainsi, la tubulure pourra être disposée, c'est-à-dire son axe longitudinal, parallèle et contigu au collecteur ou bien la tubulure pourra être disposée horizontalement et perpendiculairement au collecteur.
  • la bride comprend un orifice destiné à recevoir l'extrémité de la tubulure.
Other particularities or characteristics are presented in the following:
  • the flange comprises a number of channels equivalent to the number of chambers of the collector;
  • the angle between the two aforesaid channels is less than 90 °;
  • the aforesaid angle is between 30 ° and 80 °;
  • the aforesaid channels extend in a plane perpendicular to the linear axis of the tubing;
  • the angle between the two aforesaid channels is between 60 ° and 120 °;
  • the aforesaid channels extend in a plane parallel to the linear axis of the tubing. Thus, the tubing may be disposed, that is to say, its longitudinal axis, parallel and contiguous to the collector or the tubing may be disposed horizontally and perpendicular to the collector.
  • the flange includes an orifice for receiving the end of the tubing.

La présente invention concerne également un collecteur pour un échangeur de chaleur, comportant au moins deux chambres pour la circulation d'au moins un fluide, caractérisé en ce qu'une bride, selon les caractéristiques décrites ici, est fixée audit collecteur.The present invention also relates to a collector for a heat exchanger, comprising at least two chambers for the circulation of at least one fluid, characterized in that a flange, according to the characteristics described herein, is fixed to said collector.

Avantageusement, ce collecteur est adapté à la circulation d'un fluide à très haute pression, du type CO2.Advantageously, this collector is adapted to the circulation of a very high pressure fluid of the CO 2 type.

Enfin, la présente invention concerne un échangeur de chaleur pour l'échange de chaleur entre deux fluides, en particulier pour véhicules automobiles, comportant au moins un collecteur et/ou une bride selon les caractéristiques décrites ci-dessus.Finally, the present invention relates to a heat exchanger for exchanging heat between two fluids, in particular for motor vehicles, comprising at least one collector and / or a flange according to the characteristics described above.

Un mode de réalisation de l'invention sera décrit ci-après, à titre d'exemple non limitatif, en faisant référence aux dessins annexés dans lesquels :

  • La figure 1 représente une bride selon l'invention montée/fixée sur un collecteur à deux chambres, la tubulure étant montée verticalement ;
  • La figure 2 montre également une bride selon l'invention montée/fixée sur un collecteur à deux chambres, la tubulure étant cette fois montée/fixée parallèlement ;
  • La figure 3 est une vue différente du collecteur et de la bride de l'invention représentés sur la figure 2 ;
  • La figure 4 montre, une bride selon l'invention montée/fixée sur un collecteur à deux chambres, la tubulure étant cette fois montée/fixée horizontalement ;
  • La figure 5 illustre en coupe la structure d'un collecteur à deux arches/chambres;
  • la figure 6 illustre l'écoulement de fluide circulant dans la bride de l'invention.
An embodiment of the invention will be described hereinafter, by way of non-limiting example, with reference to the appended drawings in which:
  • The figure 1 represents a flange according to the invention mounted / fixed on a two-chamber manifold, the pipe being mounted vertically;
  • The figure 2 also shows a flange according to the invention mounted / attached to a collector with two chambers, the tubing being this time mounted / fixed parallel;
  • The figure 3 is a different view of the manifold and flange of the invention shown on the figure 2 ;
  • The figure 4 shows, a flange according to the invention mounted / fixed on a collector with two chambers, the tubing being this time mounted / fixed horizontally;
  • The figure 5 illustrates in section the structure of a collector with two arches / chambers;
  • the figure 6 illustrates the flow of fluid flowing in the flange of the invention.

La présente invention s'applique à tous types d'échangeur comportant au moins un collecteur incluant au moins deux chambres d'admission/distribution d'un fluide caloporteur.The present invention applies to all types of exchanger comprising at least one manifold including at least two inlet / distribution chambers of a heat transfer fluid.

Néanmoins, dans un souci de simplification pour la description de la présente invention, cette dernière est ici décrite dans le cadre d'un collecteur à deux chambres 4, 4' de circulation du fluide. Néanmoins, il sera bien compris que l'invention n'est pas limitée à cette réalisation et s'applique dès que le collecteur comprend au moins deux arches/chambres 4, 4' de circulation du fluide.However, for the sake of simplification for the description of the present invention, the latter is here described in the context of a collector with two chambers 4, 4 'of fluid circulation. Nevertheless, it will be understood that the invention is not limited to this embodiment and applies as soon as the collector comprises at least two arches / chambers 4, 4 'of fluid circulation.

Le collecteur choisi pour illustrer l'invention, représenté sur la figure 5, une plaque collectrice 1, une plaque intermédiaire 2 et un couvercle 3 qui ici comprend deux arches 4, 4' de manière à créer deux chambres de circulation du fluide 5 et 6.The collector chosen to illustrate the invention, represented on the figure 5 , a collector plate 1, an intermediate plate 2 and a cover 3 which here comprises two arches 4, 4 'so as to create two fluid circulation chambers 5 and 6.

On pourra prévoir que l'invention s'applique à un collecteur de structure différente, toujours comportant une pluralité de chambres de circulation 5, 6, par exemple un collecteur, ou boîte collectrice, réalisé en une seule pièce.It can be provided that the invention applies to a manifold of different structure, always having a plurality of flow chambers 5, 6, for example a manifold, or manifold, made in one piece.

Le couvercle 3 présente une surface supérieure plane 7 située respectivement à ses deux extrémités, ou côtés, latéraux destinée à permettre un sertissage optimum de protubérances, ou dents 8, s'étendant à partir de la plaque collectrice 1 afin de lier/fixer les éléments 1, 2 et 3 ensemble.The lid 3 has a flat upper surface 7 located respectively at its two ends, or lateral sides intended to allow optimum crimping of protuberances, or teeth 8, extending from the collector plate 1 in order to bind / fix the elements 1, 2 and 3 together.

Chaque arche 4, 4' consiste essentiellement en un demi-cercle de sorte que leur section s'inscrit dans un cercle de manière à résister au mieux à la pression du fluide supercritique, CO2 ou analogue.Each arch 4, 4 'consists essentially of a semicircle so that their section fits in a circle so as to best withstand the pressure of the supercritical fluid, CO 2 or the like.

Comme représenté sur la figure 1, la tubulure 9 consiste classiquement en un cylindre creux à paroi épaisse, toujours pour la tenue aux pressions importantes. Dans cet exemple, la bride 10 constitue, ponctuellement, c'est-à-dire uniquement à l'endroit où la bride 10 est fixée au collecteur, les sommets des arches 4, 4' ainsi que la partie supérieure du couvercle 3. Ainsi, la bride 10 comprend en particulier les surfaces planes 7 de sorte que la bride est fixée au couvercle 3, à la plaque intermédiaire 2 et à la plaque collectrice 1 principalement par sertissage des dents 8 sur ces parties 7.As shown on the figure 1 , the tubing 9 conventionally consists of a hollow cylinder with a thick wall, still for holding at high pressures. In this example, the flange 10 constitutes, punctually, that is to say only where the flange 10 is attached to the collector, the tops of the arches 4, 4 'and the upper part of the lid 3. Thus , the flange 10 comprises in particular the flat surfaces 7 so that the flange is fixed to the lid 3, to the intermediate plate 2 and to the collector plate 1 mainly by crimping the teeth 8 on these parts 7.

La bride 10 comprend une partie de logement 11 destinée à recevoir et loger l'extrémité de la tubulure 9. Cette partie de logement 11 présente évidemment une géométrie adaptée ou équivalente à celle de l'extrémité de la tubulure 9.The flange 10 comprises a housing portion 11 intended to receive and accommodate the end of the tubing 9. This housing portion 11 obviously has a geometry adapted to or equivalent to that of the end of the tubing 9.

Dans la réalisation de la figure 1, la tubulure 9 s'étend verticalement, c'est-à-dire perpendiculairement à l'axe longitudinal du collecteur et s'étendant dans le plan défini par les deux canaux de circulation 12, 12' de la bride 10. Dans le cas où la tubulure 9 s'étend verticalement, l'angle entre les deux canaux 5, 6 sera idéalement compris entre 60° et 120°.In the realization of the figure 1 , the pipe 9 extends vertically, that is to say perpendicularly to the longitudinal axis of the collector and extending in the plane defined by the two circulation channels 12, 12 'of the flange 10. In the case where the tubing 9 extends vertically, the angle between the two channels 5, 6 will ideally be between 60 ° and 120 °.

Dans la réalisation représentée sur les figures 2 et 3, la seule différence entre cette réalisation et celle de la figure 1 réside dans l'extension et en conséquence le raccordement de la tubulure 9. Sur ces deux figures, la tubulure 9 s'étend parallèlement au collecteur de sorte que la tubulure 9, et donc la circulation du fluide à l'intérieur, s'étend perpendiculairement au plan défini par les deux canaux de circulation 12, 12' de la bride 10. On pourra prévoir que l'extrémité interne de la tubulure 9 présente une partie courbée amenant le fluide vers l'orifice d'entrée de la tubulure 9.In the embodiment shown on the Figures 2 and 3 , the only difference between this achievement and that of the figure 1 lies in the extension and accordingly the connection of the tubing 9. In these two figures, the tubing 9 extends parallel to the manifold so that the tubing 9, and therefore the circulation of the fluid inside, extends perpendicularly to the plane defined by the two circulation channels 12, 12 'of the flange 10. It will be possible to provide that the inner end of the tubing 9 has a curved portion bringing the fluid to the inlet of the tubing 9.

La réalisation présentée sur la figure 4 est à nouveau différente des deux précédentes uniquement en ce que la tubulure 9 s'étend horizontalement, c'est-à-dire qu'elle présente un axe perpendiculaire à l'axe longitudinal du collecteur et s'inscrit dans le plan défini par les deux canaux de circulation 12, 12' de la bride 10.The realization presented on the figure 4 is again different from the previous two only in that the tubing 9 extends horizontally, that is to say it has an axis perpendicular to the longitudinal axis of the collector and is in the plane defined by the two circulation channels 12, 12 'of the flange 10.

Dans le cas où la tubulure 9 s'étend horizontalement ou parallèlement, l'angle entre les deux canaux 5, 6 sera considérablement inférieur à 90°, de préférence compris entre 30° et 80°.In the case where the pipe 9 extends horizontally or parallel, the angle between the two channels 5, 6 will be considerably less than 90 °, preferably between 30 ° and 80 °.

La figure 6 illustre l'écoulement du fluide dans les canaux de circulation 12, 12' de la bride 10, le flux principal commun, au niveau de la tubulure 9, et celui de chacun des deux canaux 12 et 12', et la répartition équilibrée du fluide entre les deux canaux 12, 12'. On remarque clairement sur cette figure que l'écoulement du fluide dans chacun des deux canaux 12, 12' est optimisé.The figure 6 illustrates the flow of the fluid in the circulation channels 12, 12 'of the flange 10, the main common flow, at the level of the pipe 9, and that of each of the two channels 12 and 12', and the balanced distribution of the fluid between the two channels 12, 12 '. It is clearly seen in this figure that the fluid flow in each of the two channels 12, 12 'is optimized.

Par ailleurs, on notera que les deux canaux 12, 12' pourront présenter une section linéaire, comme cela est représenté sur les figures annexées. Bien entendu, on pourra également envisager que ces deux canaux 12, 12' présentent des sections terminales différentes, par exemple des sections sensiblement parallèles entre elles, tout en conservant les deux aspects de l'invention qui sont l'absence d'une chambre/partie dédiée à la réception du fluide provenant de la tubulure 9 et la réalisation d'une pluralité de canaux 12, 12', s'étendant à partir de l'orifice d'entrée de la bride 10, s'étendant sensiblement linéairement et formant entre un angle strictement inférieur à l'angle plat (180°).Furthermore, it will be noted that the two channels 12, 12 'may have a linear section, as shown in the accompanying figures. Of course, it can also be envisaged that these two channels 12, 12 'have different end sections, for example sections substantially parallel to each other, while retaining the two aspects of the invention which are the absence of a chamber / part dedicated to receiving the fluid from the tubing 9 and producing a plurality of channels 12, 12 'extending from the inlet port of the flange 10, extending substantially linearly and forming between an angle strictly less than the flat angle (180 °).

L'utilisation de canaux inclinés 12, 12' dans la bride 10 permet de centrer l'alimentation des chambres de distribution 5, 6 et permet de diminuer sensiblement la perte de charge, ceci dans toutes les configurations et dispositions de la tubulure 9. Selon les analyses réalisées, grâce aux canaux inclinés 12, 12' de la bride 10 de l'invention, on diminue d'un facteur 3 en perte de charge interne par rapport au concept classique.The use of inclined channels 12, 12 'in the flange 10 makes it possible to center the supply of the distribution chambers 5, 6 and makes it possible to reduce substantially the pressure drop, this in all configurations and arrangements of the pipe 9. According to the analyzes carried out, thanks to the inclined channels 12, 12 'of the flange 10 of the invention, is reduced by a factor 3 in loss of internal load compared to the classic concept.

L'invention permet de répartir de façon particulièrement équitable le débit dans les deux canaux de distribution 12, 12' de la bride 10 afin que le fluide occupe sensiblement de manière égale les différentes chambres 5, 6 du collecteur. L'invention permet ainsi un « auto-équilibrage » des débits dans chaque chambre 5, 6 sans avoir à recourir à des variations de diamètre.The invention makes it possible to distribute in a particularly equitable manner the flow rate in the two distribution channels 12, 12 'of the flange 10 so that the fluid occupies substantially equally the different chambers 5, 6 of the collector. The invention thus allows a "self-balancing" flow rates in each chamber 5, 6 without having to resort to variations in diameter.

La conception, ou le « Design », de distribution en Y de la bride 10 permet également une optimisation en terme d'encombrement, en évitant ainsi le contre perçage.The design, or the "Design", of Y-distribution of the flange 10 also allows an optimization in terms of size, thus avoiding the counter drilling.

Claims (11)

Bride (10) pour l'alimentation d'un collecteur, comportant au moins deux chambres (5, 6), d'un échangeur de chaleur, la bride (10) présentant un orifice d'entrée pour la communication avec une tubulure (9) transportant un fluide caloporteur vers le collecteur, caractérisée en ce qu'elle comprend au moins deux canaux de circulation (12, 12') du fluide, respectivement à destination de chacune des deux chambres (5, 6), s'étendant linéairement, à partir du susdit orifice d'entrée, pour former entre eux un angle inférieur à 180°.Flange (10) for feeding a manifold, having at least two chambers (5, 6), of a heat exchanger, the flange (10) having an inlet for communication with a manifold (9 ) carrying a heat transfer fluid to the collector, characterized in that it comprises at least two circulation channels (12, 12 ') of the fluid, respectively intended for each of the two chambers (5, 6), extending linearly, from the aforesaid inlet orifice, to form between them an angle less than 180 °. Bride (10) selon la revendication 1, caractérisée en ce qu'elle comprend un nombre de canaux équivalent au nombre de chambres (5, 6) du collecteur.Flange (10) according to claim 1, characterized in that it comprises a number of channels equivalent to the number of chambers (5, 6) of the collector. Bride (10) selon la revendication 1 ou 2, caractérisée en ce que l'angle entre les deux susdits canaux est inférieur à 90°.Flange (10) according to claim 1 or 2, characterized in that the angle between the two said channels is less than 90 °. Bride (10) selon la revendication 3, caractérisée en ce que le susdit angle est compris entre 30° et 80°.Flange (10) according to claim 3, characterized in that the aforesaid angle is between 30 ° and 80 °. Bride (10) selon l'une quelconque des revendications précédentes, caractérisée en ce que les susdits canaux (12, 12') s'étendent dans un plan perpendiculaire à l'axe linéaire de la tubulure.Flange (10) according to any one of the preceding claims, characterized in that the aforesaid channels (12, 12 ') extend in a plane perpendicular to the linear axis of the tubing. Bride (10) selon la revendication 1 ou 2, caractérisée en ce que l'angle entre les deux susdits canaux (12, 12') est compris entre 60° et 120°.Flange (10) according to claim 1 or 2, characterized in that the angle between the two said channels (12, 12 ') is between 60 ° and 120 °. Bride (10) selon la revendication 6, caractérisée en ce que les susdits canaux (12, 12') s'étendent dans un plan parallèle à l'axe linéaire de la tubulure (9).Flange (10) according to claim 6, characterized in that the aforesaid channels (12, 12 ') extend in a plane parallel to the linear axis of the tubing (9). Bride (10) selon l'une quelconque des revendication précédentes, caractérisée en ce qu'elle comprend un orifice destinée à recevoir l'extrémité de la tubulure (9).Flange (10) according to any one of the preceding claims, characterized in that it comprises an orifice intended to receive the end of the tubing (9). Collecteur pour un échangeur de chaleur, comportant au moins deux chambres (5, 6) pour la circulation d'au moins un fluide, caractérisé en ce qu'une bride (10), selon l'une quelconque des revendications précédentes, est fixée audit collecteur.Collector for a heat exchanger, comprising at least two chambers (5, 6) for the circulation of at least one fluid, characterized in that a flange (10) according to any one of the preceding claims is attached to said manifold. Collecteur selon la revendication 9, caractérisé en ce qu'il est adapté à la circulation d'un fluide à très haute pression (supérieure à 100 bars), du type CO2.Collector according to Claim 9, characterized in that it is suitable for the circulation of a fluid at a very high pressure (greater than 100 bar), of the CO 2 type. Echangeur de chaleur pour l'échange de chaleur entre deux fluides, en particulier pour véhicules automobiles, comportant au moins un collecteur selon la revendication 9 ou 10.Heat exchanger for exchanging heat between two fluids, in particular for motor vehicles, comprising at least one collector according to claim 9 or 10.
EP08155365A 2007-06-22 2008-04-29 Collector flange for a heat exchanger Withdrawn EP2006631A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0704501A FR2917820B1 (en) 2007-06-22 2007-06-22 COLLECTOR FLANGE FOR A HEAT EXCHANGER

Publications (1)

Publication Number Publication Date
EP2006631A1 true EP2006631A1 (en) 2008-12-24

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Family Applications (1)

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EP08155365A Withdrawn EP2006631A1 (en) 2007-06-22 2008-04-29 Collector flange for a heat exchanger

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EP (1) EP2006631A1 (en)
FR (1) FR2917820B1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3671067A1 (en) * 2018-12-17 2020-06-24 Valeo Autosystemy SP. Z.O.O. A heat exchanger

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Publication number Priority date Publication date Assignee Title
JPH05312492A (en) * 1992-05-14 1993-11-22 Showa Alum Corp Heat exchanger
JPH0829091A (en) * 1994-07-14 1996-02-02 Sharp Corp Heat exchanger
DE19906289A1 (en) * 1998-02-16 1999-08-19 Denso Corp Heat exchanger for carbon dioxide coolant in circuit
JP2001133191A (en) * 1999-11-05 2001-05-18 Calsonic Kansei Corp Heat exchanger for vehicle
JP2004219025A (en) * 2003-01-17 2004-08-05 Denso Corp Temporary fixing method of bracket
EP1462749A2 (en) 2003-03-26 2004-09-29 Calsonic Kansei Corporation Heat exchanger
JP2004293876A (en) 2003-03-26 2004-10-21 Calsonic Kansei Corp Heat exchanger
JP2006064201A (en) * 2004-08-24 2006-03-09 Calsonic Kansei Corp Header tank of heat exchanger and connecting structure of header tank of heat exchanger and refrigerant circulating pipe
DE102006040848A1 (en) * 2005-09-08 2007-03-29 Behr Gmbh & Co. Kg Heat exchanger with a minimum of one collector and/or distributor device made up of two moulded sections and having two flow paths for fluids and a further through-flow device
US20070131405A1 (en) * 2005-12-09 2007-06-14 Denso Corporation Outlet/inlet piping structure for intercooler

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05312492A (en) * 1992-05-14 1993-11-22 Showa Alum Corp Heat exchanger
JPH0829091A (en) * 1994-07-14 1996-02-02 Sharp Corp Heat exchanger
DE19906289A1 (en) * 1998-02-16 1999-08-19 Denso Corp Heat exchanger for carbon dioxide coolant in circuit
JP2001133191A (en) * 1999-11-05 2001-05-18 Calsonic Kansei Corp Heat exchanger for vehicle
JP2004219025A (en) * 2003-01-17 2004-08-05 Denso Corp Temporary fixing method of bracket
EP1462749A2 (en) 2003-03-26 2004-09-29 Calsonic Kansei Corporation Heat exchanger
JP2004293876A (en) 2003-03-26 2004-10-21 Calsonic Kansei Corp Heat exchanger
JP2006064201A (en) * 2004-08-24 2006-03-09 Calsonic Kansei Corp Header tank of heat exchanger and connecting structure of header tank of heat exchanger and refrigerant circulating pipe
DE102006040848A1 (en) * 2005-09-08 2007-03-29 Behr Gmbh & Co. Kg Heat exchanger with a minimum of one collector and/or distributor device made up of two moulded sections and having two flow paths for fluids and a further through-flow device
US20070131405A1 (en) * 2005-12-09 2007-06-14 Denso Corporation Outlet/inlet piping structure for intercooler

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3671067A1 (en) * 2018-12-17 2020-06-24 Valeo Autosystemy SP. Z.O.O. A heat exchanger
WO2020127253A1 (en) * 2018-12-17 2020-06-25 Valeo Autosystemy Sp. Z O.O. A heat exchanger

Also Published As

Publication number Publication date
FR2917820B1 (en) 2009-08-21
FR2917820A1 (en) 2008-12-26

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