EP1269100A1 - Plate heat exchanger - Google Patents

Plate heat exchanger

Info

Publication number
EP1269100A1
EP1269100A1 EP01919584A EP01919584A EP1269100A1 EP 1269100 A1 EP1269100 A1 EP 1269100A1 EP 01919584 A EP01919584 A EP 01919584A EP 01919584 A EP01919584 A EP 01919584A EP 1269100 A1 EP1269100 A1 EP 1269100A1
Authority
EP
European Patent Office
Prior art keywords
manifold
outlet
fluid
exchanger according
exchanger
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Withdrawn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
EP01919584A
Other languages
German (de)
French (fr)
Inventor
Marc Altazin
André Bailly
Jean-Michel Croiset
Romuald Jurkowski
Slimane Meziani
Jean-Marie Michaud
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.)
Compagnie Industrielle dApplications Thermiques SA CIAT
Original Assignee
Compagnie Industrielle dApplications Thermiques SA CIAT
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 Compagnie Industrielle dApplications Thermiques SA CIAT filed Critical Compagnie Industrielle dApplications Thermiques SA CIAT
Publication of EP1269100A1 publication Critical patent/EP1269100A1/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Withdrawn legal-status Critical Current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
    • 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
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall

Definitions

  • the present invention relates to a plate heat exchanger.
  • such an exchanger is composed of superimposed plates which, after brazing, welding or clamping, form two series of circulation channels, allowing respectively the flow of first and second fluids, which can be in the single-phase or two-phase state , at their entrance.
  • the first fluid is for example a refrigerating fluid
  • the second fluid can be a fluid to be cooled or to be heated.
  • Mechanical means are also provided for making these two series of channels independent, so that the two aforementioned fluids do not come into mutual contact.
  • a plate exchanger also includes first and second inlet manifolds, placed in communication with respective pipes for supplying each fluid.
  • Each input collector supplies power to a corresponding series of channels. Downstream of the channels are provided outlet collectors, each of which is in communication with an outlet pipe allowing the evacuation of a corresponding fluid.
  • the plate heat exchangers mentioned above have certain drawbacks. In fact, their performance increases in a roughly linear fashion with the number of plates which equip them, up to a threshold value which is between approximately 40 and 100 plates. Beyond this threshold value, which depends in particular on the nature of the fluids and their flow rate, the performance of the exchanger tends to stagnate or even decrease as the total number of plates is increased . Furthermore, the pressure drops occurring at these heat exchangers are relatively high. The phenomena described above are detrimental, in the sense that the exchanger is limited in its performance.
  • the invention proposes to produce a plate heat exchanger whose performance is improved compared to the prior art, and in particular continues to increase beyond the threshold value of plates, which is mentioned above.
  • the invention also proposes to produce such an exchanger, whose design is simple and whose associated pressure drops are reduced compared to the prior art.
  • a plate heat exchanger comprising several plates, housed in the interior volume of the exchanger and defining first and second series of independent circulation channels, respectively for the circulation of first and second fluids.
  • said exchanger further comprising first and second inlet manifolds, extending respectively upstream of the first and second channels, with reference to the flow of each fluid, as well as first and second outlet manifolds, extending downstream of said first and second channels, characterized in that at least one of the first and second outlet manifolds is provided with an attached member arranged in the internal volume of the collector, this added member extending from a bottom of the or each collector, and making it possible to reduce the cross-section substantially continuously passage of or each fluid in the or each outlet manifold, towards the bottom of this manifold.
  • FIG. 1 is a partial sectional view of a plate heat exchanger according to l invention
  • Figures 2 and 3 are views in partial section, illustrating the outlet manifold of the exchanger of Figure 1, provided with two alternative embodiments of an attached member allowing the reduction of the cross section of the fluid in this manifold.
  • the plate heat exchanger illustrated in FIG. 1, which is generally designated by the reference 2, contains several plates 6 extending in parallel, so as to define first 8 and second 10 series of channels, arranged alternately.
  • means are provided for preventing communication between two adjacent channels 8, 10. These means, which can for example be produced by stamping, then brazing or adding a joint, are shown schematically, for the sake of clarity, by dividing lines 12.
  • the exchanger 2 also comprises a connection fitting 14 for a first fluid, which is for example a cooling fluid, intended to flow in the first channels 8.
  • This fitting 14 is provided with a peripheral shoulder 16, against which abuts a tube 18 allowing the supply of this coolant.
  • the inlet connector 14 opens into an inlet collection zone, or inlet manifold 20. The latter, which extends longitudinally in the direction of flow of the coolant, is thus disposed opposite of all the channels 8, 10, upstream of the latter in the direction of flow of the coolant.
  • the channels 8 are placed in communication, opposite the inlet manifold 20, with an outlet collection zone, or outlet manifold 22.
  • the latter which extends longitudinally in the direction of flow of the fluid, is arranged opposite the channels 8, 10, downstream of these, symmetrically with the inlet manifold 20.
  • the outlet manifold 22 is placed in communication with a discharge connection 24, or outlet, of the refrigerant.
  • This connector 24 is provided with a peripheral shoulder 26, against which abuts a tube 28 allowing the evacuation of the refrigerant.
  • the exchanger 2 also comprises, in a known manner, connections for supplying and discharging a second fluid, which is for example a fluid to be cooled, as well as inlet and outlet manifolds for this fluid, arranged on either side of the circulation channels 10.
  • a second fluid which is for example a fluid to be cooled
  • inlet and outlet manifolds for this fluid arranged on either side of the circulation channels 10.
  • An attached member which is a conical body 30, is housed in the interior volume of the outlet manifold 22.
  • the main axis of this cone coincides with the median longitudinal axis A of the outlet manifold 22, while its base 32 is fixed, for example by brazing, on the bottom wall 34 of one exchanger 2, opposite the inlet fittings 14 and discharge 24 of the first fluid.
  • the tip 36 of this cone 30 extends to the outlet of the downstream channel 8 ', adjacent to both the fittings 14 and 24.
  • the transverse dimensions of the outlet manifold 22 are substantially constant. They are defined by the side wall 38, as well as by the outlets of all of the channels 8. Furthermore, the transverse dimensions of the cone 30 increase continuously in the direction of the bottom wall 34, namely opposite of the discharge connection 24, which corresponds upstream, with reference to the flow of the coolant in the outlet manifold 22.
  • the cross section of the coolant which corresponds to the difference between the total cross section of the outlet manifold 22 and the cross section of the cone 30, therefore decreases continuously upstream, i.e. the bottom 34 of the collector.
  • the fluid passage section, at the outlet of the upstream channel 8 ", adjacent to the bottom wall 34, is between 1 and 50%, preferably between 5 and 25%, of the total cross section of the outlet manifold 22.
  • FIG. 2 illustrates a variant of the invention, in which the added member is a cone 80 whose longitudinal dimension, or length, is less than that of the cone 30 of the previous figure.
  • This cone 80 extends over a length 1, equal to approximately 50% of the length L, or longitudinal dimension of the outlet manifold 22, corresponding to the distance separating the outlet of the downstream channel 8 'and the bottom wall 34.
  • the cone 80 therefore extends only in the upstream region 40 of the outlet manifold 22, with reference to the flow of the fluid.
  • the tip 86 of the cone is integral with a longitudinal rod 88 terminated by transverse wires 90 interposed between the tube 28 and the shoulder 26.
  • the base 82 of the cone is then pressed against the bottom wall 34 and does not need to be brazed there.
  • the means for reducing the cross section of the fluid are no longer formed by a cone, but by a member 130, the side walls 131 of which do not have a rectilinear profile, in axial section. These walls 131 have a concavity facing the median longitudinal axis A of the outlet manifold 22.
  • the base 132 of this added member 130 is pressed against the bottom 34, while its tip 136 is integral with a rod 138 extended by wires 140, similar to those 88 and 90 in FIG. 2.
  • the invention is not limited to the examples described and shown. Thus, provision can be made to have an insert member similar to those 30, 80 and 130, in the outlet manifold of the second fluid.
  • Such an attached member can therefore equip the outlet manifold of the first fluid and / or the outlet manifold of the second fluid.
  • the insert arranged in the interior volume of the collector, can be offset, in the sense that its main axis is distinct from that of the collector considered. Furthermore, this added member may have a roughly conical shape, in the sense that it is constituted by a deformed cone.
  • the invention makes it possible to achieve the objectives mentioned above.
  • the Applicant has found that the stagnation, or even the decrease in performance of a plate heat exchanger, occurring beyond a threshold value of plates, is in particular linked to a poor distribution of the fluid in the channels of circulation.
  • This poor distribution implies in particular that the flow rate of fluid flowing in the channel adjacent to the supply and discharge connections is significantly higher than that of the fluid flowing in the opposite channel, adjacent to the bottom plate of the exchanger.
  • this unsatisfactory distribution is linked to the fact that, towards the bottom of the exchanger, the difference between the static pressures of the fluid at the inlet and at the outlet of a channel considered is much less than the difference between the pressures static of the fluid at the inlet and outlet of a channel located towards the inlet and outlet fittings.
  • providing an add-on member making it possible to reduce the cross section of the fluid, towards the bottom of the outlet manifold ensures an increase in the flow rate of the fluid, in this region upstream of the manifold. This induces an increase in the dynamic pressure of this fluid, in the aforementioned upstream region, as well as a corresponding decrease in its static pressure.
  • the difference between the static pressures of the fluid at the inlet and at the outlet of the channels opening out in the vicinity of the bottom of the outlet manifold is notably greater than in the prior art. This contributes to homogenizing, along the outlet manifold, the differences in static pressures existing between the inlet and the outlet of the channels, and therefore ensures a satisfactory distribution of the fluid between these channels.
  • the invention guarantees great simplicity in manufacturing the plate heat exchanger. Indeed, it only uses an add-on unit, the cost price of which is low, and which can be fixed easily on the walls of the collector.
  • this added member making it possible to reduce the cross-section of the fluid passage towards the bottom of the manifold, has a satisfactory adaptability to the number of plates of the exchanger. Indeed, in the context of an increase in the length of the collector, linked to a higher number of plates, it is only necessary to modify the angle of revolution, as well as the length of one added member.
  • the invention is particularly advantageous in the case of two-phase flows, formed of a gas loaded with oil. Since the presence of the added member makes it possible to increase the speed of the fluid towards the bottom of the collector, without however creating turbulence, any retention of this oil is substantially avoided, in the vicinity of this bottom.
  • the added member has a main axis coincident with the median longitudinal axis of the outlet manifold.
  • the fluid is able to flow in a regularly distributed manner around this member.

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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 invention concerns a heat exchanger (2) comprising several plates (6) defining first (8) and second (10) series of independent flow channels, for circulating first and second fluids, first and second intake manifolds emerging respectively upstream of the first (8) and second (10) channels, and first (22) and second outlet manifolds extending downstream of said first (8) and second (10) channels. At least one of the first (22) and second outlet manifolds is provided with a directly mounted member (30) arranged in the internal volume of the manifold, said directly mounted member extending from a base of the or of each manifold, and enabling to reduce substantially continuously the cross-section of the passage of the or of each fluid in the or each outlet manifold (22), towards the base (34) of said manifold.

Description

ECHANGEUR DE CHALEUR A PLAQUES PLATE HEAT EXCHANGER
La présente invention concerne un échangeur de chaleur à plaques.The present invention relates to a plate heat exchanger.
De manière habituelle, un tel échangeur est composé de plaques superposées qui, après brasage, soudage ou serrage, forment deux séries de canaux de circulation, permettant respectivement l'écoulement de premier et second fluides, qui peuvent être à l'état monophasique ou diphasique, à leur entrée. Le premier fluide est par exemple un fluide réfrigérant, alors que le second fluide peut être un fluide à refroidir ou à réchauffer. Il est par ailleurs prévu des moyens mécaniques permettant de rendre indépendantes ces deux séries de canaux, de sorte que les deux fluides précités n'entrent pas en contact mutuel.Usually, such an exchanger is composed of superimposed plates which, after brazing, welding or clamping, form two series of circulation channels, allowing respectively the flow of first and second fluids, which can be in the single-phase or two-phase state , at their entrance. The first fluid is for example a refrigerating fluid, while the second fluid can be a fluid to be cooled or to be heated. Mechanical means are also provided for making these two series of channels independent, so that the two aforementioned fluids do not come into mutual contact.
Un échangeur à plaques comprend également des premier et second collecteurs d'entrée, mis en communication avec des canalisations respectives d'amenée de chaque fluide. Chaque collecteur d'entrée assure l'alimentation d'une série correspondante de canaux. En aval des canaux sont prévus des collecteurs de sortie, dont chacun se trouve en communication avec une canalisation de sortie permettant l'évacuation d'un fluide correspondant . Les echangeurs de chaleur à plaques évoqués ci-dessus présentent certains inconvénients. En effet, leurs performances augmentent de façon à peu près linéaire avec le nombre de plaques qui les équipent, jusqu'à une valeur seuil qui est comprise entre environ 40 et 100 plaques. Au-delà de cette valeur seuil, qui dépend notamment de la nature des fluides et de leur débit, les performances de 1 ' échangeur ont tendance à stagner, voire à décroître au fur et à mesure que l'on augmente le nombre total de plaques. Par ailleurs, les pertes de charge intervenant au niveau de ces echangeurs de chaleur sont relativement élevées. Les phénomènes décrits ci- dessus sont préjudiciables, en sens que 1 ' échangeur se voit limité dans ses performances.A plate exchanger also includes first and second inlet manifolds, placed in communication with respective pipes for supplying each fluid. Each input collector supplies power to a corresponding series of channels. Downstream of the channels are provided outlet collectors, each of which is in communication with an outlet pipe allowing the evacuation of a corresponding fluid. The plate heat exchangers mentioned above have certain drawbacks. In fact, their performance increases in a roughly linear fashion with the number of plates which equip them, up to a threshold value which is between approximately 40 and 100 plates. Beyond this threshold value, which depends in particular on the nature of the fluids and their flow rate, the performance of the exchanger tends to stagnate or even decrease as the total number of plates is increased . Furthermore, the pressure drops occurring at these heat exchangers are relatively high. The phenomena described above are detrimental, in the sense that the exchanger is limited in its performance.
Afin de pallier ces inconvénients, l'invention se propose de réaliser un échangeur de chaleur à plaques dont les performances sont améliorées par rapport à l'art antérieur, et continuent en particulier à augmenter au-delà de la valeur seuil de plaques, dont il est fait mention précédemment. L'invention se propose également de réaliser un tel échangeur, dont la conception est simple et dont les pertes de charge associées sont réduites par rapport à l'art antérieur.In order to overcome these drawbacks, the invention proposes to produce a plate heat exchanger whose performance is improved compared to the prior art, and in particular continues to increase beyond the threshold value of plates, which is mentioned above. The invention also proposes to produce such an exchanger, whose design is simple and whose associated pressure drops are reduced compared to the prior art.
A cet effet, elle a pour objet un échangeur de chaleur à plaques, comprenant plusieurs plaques, logées dans le volume intérieur de l' échangeur et définissant des première et seconde séries de canaux de circulation indépendants, respectivement pour la circulation de premier et second fluides, notamment d'un fluide réfrigérant et d'un fluide à réfrigérer, ledit échangeur comprenant en outre des premier et second collecteurs d'entrée, s'étendant respectivement en amont des premier et second canaux, en faisant référence à l'écoulement de chaque fluide, ainsi que des premier et second collecteurs de sortie, s'étendant en aval desdits premier et second canaux, caractérisé en ce qu'au moins l'un des premier et second collecteurs de sortie est pourvu d'un organe rapporté disposé dans le volume intérieur du collecteur, cet organe rapporté s'étendant à partir d'un fond du ou de chaque collecteur, et permettant de diminuer de façon sensiblement continue la section de passage du ou de chaque fluide dans le ou chaque collecteur de sortie, vers le fond de ce collecteur.To this end, it relates to a plate heat exchanger, comprising several plates, housed in the interior volume of the exchanger and defining first and second series of independent circulation channels, respectively for the circulation of first and second fluids. , in particular a coolant and a coolant, said exchanger further comprising first and second inlet manifolds, extending respectively upstream of the first and second channels, with reference to the flow of each fluid, as well as first and second outlet manifolds, extending downstream of said first and second channels, characterized in that at least one of the first and second outlet manifolds is provided with an attached member arranged in the internal volume of the collector, this added member extending from a bottom of the or each collector, and making it possible to reduce the cross-section substantially continuously passage of or each fluid in the or each outlet manifold, towards the bottom of this manifold.
L'invention va être décrite ci-dessous, en référence aux dessins annexés, donnée uniquement à titre d'exemple non limitatif et dans lesquels : - la figure 1 est une vue en coupe partielle d'un échangeur de chaleur à plaques conforme à l'invention ; et les figures 2 et 3 sont des vues en coupe partielle, illustrant le collecteur de sortie de l' échangeur de la figure 1, muni de deux variantes de réalisation d'un organe rapporté permettant la diminution de la section de passage du fluide dans ce collecteur.The invention will be described below, with reference to the accompanying drawings, given only by way of nonlimiting example and in which: - Figure 1 is a partial sectional view of a plate heat exchanger according to l invention; and Figures 2 and 3 are views in partial section, illustrating the outlet manifold of the exchanger of Figure 1, provided with two alternative embodiments of an attached member allowing the reduction of the cross section of the fluid in this manifold.
L' échangeur de chaleur à plaques illustré sur la figure 1, qui est désigné dans son ensemble par la référence 2, renferme plusieurs plaques 6 s'étendant parallèlement, de manière à définir des première 8 et seconde 10 séries de canaux, disposés de façon alternée. De façon connue, il est prévu des moyens permettant d'empêcher la communication entre deux canaux 8, 10 adjacents. Ces moyens, qui peuvent par exemple être réalisés par emboutissage, puis brasage ou adjonction d'un joint, sont représentés de façon schématique, dans un but de clarté, par des lignes de séparation 12.The plate heat exchanger illustrated in FIG. 1, which is generally designated by the reference 2, contains several plates 6 extending in parallel, so as to define first 8 and second 10 series of channels, arranged alternately. In known manner, means are provided for preventing communication between two adjacent channels 8, 10. These means, which can for example be produced by stamping, then brazing or adding a joint, are shown schematically, for the sake of clarity, by dividing lines 12.
L' échangeur 2 comprend également un raccord d'amenée 14 d'un premier fluide, qui est par exemple un fluide réfrigérant, destiné à s'écouler dans les premiers canaux 8. Ce raccord 14 est muni d'un épaulement périphérique 16, contre lequel vient en butée une tubulure 18 permettant l'alimentation de ce fluide réfrigérant. De façon classique, le raccord d'amenée 14 débouche dans une zone de collecte d'entrée, ou collecteur d'entrée 20. Ce dernier, qui s'étend longitudinalement selon la direction d'écoulement du fluide réfrigérant, est ainsi disposé en regard de l'ensemble des canaux 8, 10, en amont de ces derniers selon la direction d'écoulement du fluide réfrigérant .The exchanger 2 also comprises a connection fitting 14 for a first fluid, which is for example a cooling fluid, intended to flow in the first channels 8. This fitting 14 is provided with a peripheral shoulder 16, against which abuts a tube 18 allowing the supply of this coolant. Conventionally, the inlet connector 14 opens into an inlet collection zone, or inlet manifold 20. The latter, which extends longitudinally in the direction of flow of the coolant, is thus disposed opposite of all the channels 8, 10, upstream of the latter in the direction of flow of the coolant.
Les canaux 8 sont mis en communication, à l'opposé du collecteur d'entrée 20, avec une zone de collecte de sortie, ou collecteur de sortie 22. Ce dernier, qui s'étend longitudinalement selon la direction d'écoulement du fluide, est disposé en regard des canaux 8, 10, en aval de ceux-ci, de façon symétrique au collecteur d'entrée 20.The channels 8 are placed in communication, opposite the inlet manifold 20, with an outlet collection zone, or outlet manifold 22. The latter, which extends longitudinally in the direction of flow of the fluid, is arranged opposite the channels 8, 10, downstream of these, symmetrically with the inlet manifold 20.
Le collecteur de sortie 22 est mis en communication avec un raccord d'évacuation 24, ou de sortie, du fluide réfrigérant. Ce raccord 24 est muni d'un épaulement périphérique 26, contre lequel vient en butée une tubulure 28 permettant l'évacuation du fluide réfrigérant.The outlet manifold 22 is placed in communication with a discharge connection 24, or outlet, of the refrigerant. This connector 24 is provided with a peripheral shoulder 26, against which abuts a tube 28 allowing the evacuation of the refrigerant.
L' échangeur 2 comprend également, de façon connue, des raccords d'amenée et d'évacuation d'un second fluide, qui est par exemple un fluide à refroidir, ainsi que des collecteurs d'entrée et de sortie de ce fluide, disposés de part et d'autre des canaux de circulation 10. Les éléments mécaniques évoqués ci-dessus ne sont pas représentés sur les figures. Un organe rapporté, qui est un corps conique 30, est logé dans le volume intérieur du collecteur de sortie 22. L'axe principal de ce cône est confondu avec l'axe longitudinal médian A du collecteur de sortie 22, alors que sa base 32 est fixée, par exemple par brasage, sur la paroi de fond 34 de 1' échangeur 2, opposée aux raccords d'amenée 14 et d'évacuation 24 du premier fluide. La pointe 36 de ce cône 30 s'étend jusqu'au débouché du canal aval 8' , adjacent à la fois aux raccords 14 et 24. Les dimensions transversales du collecteur de sortie 22 sont sensiblement constantes. Elles sont définies par la paroi latérale 38, ainsi que par les débouchés de l'ensemble des canaux 8. Par ailleurs, les dimensions transversales du cône 30 augmentent de façon continue en direction de la paroi de fond 34, à savoir à l'opposé du raccord d'évacuation 24, ce qui correspond à l'amont, en référence à l'écoulement du fluide réfrigérant dans le collecteur de sortie 22.The exchanger 2 also comprises, in a known manner, connections for supplying and discharging a second fluid, which is for example a fluid to be cooled, as well as inlet and outlet manifolds for this fluid, arranged on either side of the circulation channels 10. The mechanical elements mentioned above are not shown in the figures. An attached member, which is a conical body 30, is housed in the interior volume of the outlet manifold 22. The main axis of this cone coincides with the median longitudinal axis A of the outlet manifold 22, while its base 32 is fixed, for example by brazing, on the bottom wall 34 of one exchanger 2, opposite the inlet fittings 14 and discharge 24 of the first fluid. The tip 36 of this cone 30 extends to the outlet of the downstream channel 8 ', adjacent to both the fittings 14 and 24. The transverse dimensions of the outlet manifold 22 are substantially constant. They are defined by the side wall 38, as well as by the outlets of all of the channels 8. Furthermore, the transverse dimensions of the cone 30 increase continuously in the direction of the bottom wall 34, namely opposite of the discharge connection 24, which corresponds upstream, with reference to the flow of the coolant in the outlet manifold 22.
La section de passage du fluide réfrigérant, qui correspond à la différence entre la section transversale totale du collecteur de sortie 22 et la section transversale du cône 30, diminue donc de façon continue vers l'amont, c'est-à-dire le fond 34 du collecteur. A titre indicatif, la section de passage du fluide, au niveau du débouché du canal amont 8", adjacent à la paroi de fond 34, est comprise entre 1 et 50 %, de préférence entre 5 et 25 %, de la section transversale totale du collecteur de sortie 22.The cross section of the coolant, which corresponds to the difference between the total cross section of the outlet manifold 22 and the cross section of the cone 30, therefore decreases continuously upstream, i.e. the bottom 34 of the collector. As an indication, the fluid passage section, at the outlet of the upstream channel 8 ", adjacent to the bottom wall 34, is between 1 and 50%, preferably between 5 and 25%, of the total cross section of the outlet manifold 22.
La figure 2 illustre une variante de l'invention, dans laquelle l'organe rapporté est un cône 80 dont la dimension longitudinale, ou longueur, est inférieure à celle du cône 30 de la figure précédente. Ce cône 80 s'étend sur une longueur 1, égale à environ 50 % de la longueur L, ou dimension longitudinale du collecteur de sortie 22, correspondant à la distance séparant le débouché du canal aval 8' et la paroi de fond 34. Le cône 80 s'étend donc uniquement dans la région amont 40 du collecteur de sortie 22, en faisant référence à l'écoulement du fluide. La pointe 86 du cône est solidaire d'une tige longitudinale 88 terminée par des fils transversaux 90 interposés entre la tubulure 28 et l' épaulement 26. La base 82 du cône est alors plaquée contre la paroi de fond 34 et n'a pas besoin d'y être brasée. En cas de fixation par brasage, l'emploi de la tige 88 et des fils 90 n'est pas nécessaire. A la figure 3, les moyens de diminution de la section de passage du fluide ne sont plus formés par un cône, mais par un organe 130, dont les parois latérales 131 ne possèdent pas un profil rectiligne, en coupe axiale. Ces parois 131 présentent une concavité tournée vers l'axe longitudinal médian A du collecteur de sortie 22. La base 132 de cet organe rapporté 130 est plaquée contre le fond 34, alors que sa pointe 136 est solidaire d'une tige 138 prolongée par des fils 140, analogues à ceux 88 et 90 de la figure 2.FIG. 2 illustrates a variant of the invention, in which the added member is a cone 80 whose longitudinal dimension, or length, is less than that of the cone 30 of the previous figure. This cone 80 extends over a length 1, equal to approximately 50% of the length L, or longitudinal dimension of the outlet manifold 22, corresponding to the distance separating the outlet of the downstream channel 8 'and the bottom wall 34. The cone 80 therefore extends only in the upstream region 40 of the outlet manifold 22, with reference to the flow of the fluid. The tip 86 of the cone is integral with a longitudinal rod 88 terminated by transverse wires 90 interposed between the tube 28 and the shoulder 26. The base 82 of the cone is then pressed against the bottom wall 34 and does not need to be brazed there. In the case of fixing by brazing, the use of rod 88 and wires 90 is not necessary. In FIG. 3, the means for reducing the cross section of the fluid are no longer formed by a cone, but by a member 130, the side walls 131 of which do not have a rectilinear profile, in axial section. These walls 131 have a concavity facing the median longitudinal axis A of the outlet manifold 22. The base 132 of this added member 130 is pressed against the bottom 34, while its tip 136 is integral with a rod 138 extended by wires 140, similar to those 88 and 90 in FIG. 2.
L'invention n'est pas limitée aux exemples décrits et représentés. Ainsi, on peut prévoir de disposer un organe rapporté analogue à ceux 30, 80 et 130, dans le collecteur de sortie du second fluide.The invention is not limited to the examples described and shown. Thus, provision can be made to have an insert member similar to those 30, 80 and 130, in the outlet manifold of the second fluid.
Un tel organe rapporté peut donc équiper le collecteur de sortie du premier fluide et/ou le collecteur de sortie du second fluide.Such an attached member can therefore equip the outlet manifold of the first fluid and / or the outlet manifold of the second fluid.
Il est également possible de munir au moins un collecteur d'entrée de l' échangeur, au moyen d'un organe rapporté tel que décrit ci-dessus. Ceci permet de réduire le volume de réfrigérant utilisé dans l' échangeur. L'invention trouve son application à tous types de fluides, que ce soit monophasique ou diphasique.It is also possible to provide at least one inlet manifold of the exchanger, by means of an attached member as described above. This makes it possible to reduce the volume of refrigerant used in the exchanger. The invention finds its application to all types of fluids, whether single-phase or two-phase.
L'organe rapporté, disposé dans le volume intérieur du collecteur, peut être désaxé, en ce sens que son axe principal est distinct de celui du collecteur considéré. Par ailleurs, cet organe rapporté peut présenter une forme à peu près conique, en ce sens qu'il est constitué par un cône déformé.The insert, arranged in the interior volume of the collector, can be offset, in the sense that its main axis is distinct from that of the collector considered. Furthermore, this added member may have a roughly conical shape, in the sense that it is constituted by a deformed cone.
L'invention permet de réaliser les objectifs précédemment mentionnés .The invention makes it possible to achieve the objectives mentioned above.
En effet, la Demanderesse a constaté que la stagnation, voire la diminution des performances d'un échangeur de chaleur à plaques, intervenant au-delà d'une valeur seuil de plaques, est notamment liée à une mauvaise répartition du fluide dans les canaux de circulation. Cette mauvaise répartition implique en particulier que le débit de fluide circulant dans le canal adjacent aux raccords d'amenée et d'évacuation est nettement supérieur à celui du fluide circulant dans le canal opposé, adjacent à la plaque de fond de l' échangeur. Par ailleurs, cette répartition insatisfaisante est liée au fait que, vers le fond de l' échangeur, la différence entre les pressions statiques du fluide à l'entrée et à la sortie d'un canal considéré est nettement inférieure à la différence entre les pressions statiques du fluide a l'entrée et à la sortie d'un canal situé vers les raccords d'amenée et d' évacuation.Indeed, the Applicant has found that the stagnation, or even the decrease in performance of a plate heat exchanger, occurring beyond a threshold value of plates, is in particular linked to a poor distribution of the fluid in the channels of circulation. This poor distribution implies in particular that the flow rate of fluid flowing in the channel adjacent to the supply and discharge connections is significantly higher than that of the fluid flowing in the opposite channel, adjacent to the bottom plate of the exchanger. Furthermore, this unsatisfactory distribution is linked to the fact that, towards the bottom of the exchanger, the difference between the static pressures of the fluid at the inlet and at the outlet of a channel considered is much less than the difference between the pressures static of the fluid at the inlet and outlet of a channel located towards the inlet and outlet fittings.
Conformément à l'invention, prévoir un organe rapporté permettant de diminuer la section de passage du fluide, vers le fond du collecteur de sortie, assure une augmentation de la vitesse d'écoulement du fluide, dans cette région amont du collecteur. Ceci induit une augmentation de la pression dynamique de ce fluide, dans la région amont précitée, ainsi qu'une diminution correspondante de sa pression statique.According to the invention, providing an add-on member making it possible to reduce the cross section of the fluid, towards the bottom of the outlet manifold, ensures an increase in the flow rate of the fluid, in this region upstream of the manifold. This induces an increase in the dynamic pressure of this fluid, in the aforementioned upstream region, as well as a corresponding decrease in its static pressure.
On conçoit donc que, grâce à l'invention, la différence entre les pressions statiques du fluide à l'entrée et à la sortie des canaux débouchant au voisinage du fond du collecteur de sortie, est notablement plus importante que dans l'art antérieur. Ceci contribue à homogénéiser, le long du collecteur de sortie, les différences de pressions statiques existant entre l'entrée et la sortie des canaux, et assure donc une répartition satisfaisante du fluide entre ces canaux.It is therefore understandable that, thanks to the invention, the difference between the static pressures of the fluid at the inlet and at the outlet of the channels opening out in the vicinity of the bottom of the outlet manifold, is notably greater than in the prior art. This contributes to homogenizing, along the outlet manifold, the differences in static pressures existing between the inlet and the outlet of the channels, and therefore ensures a satisfactory distribution of the fluid between these channels.
Les débits de fluide s'écoulant dans ces différents canaux étant, de ce fait, sensiblement identiques, les performances de l' échangeur à plaques conforme à l'invention sont substantiellement supérieures à celles de l'art antérieur. Par ailleurs, les pertes de charges inhérentes à l'emploi de cet échangeur sont notablement réduites, par rapport à celles intervenant dans l'art antérieur.The fluid flow rates flowing in these different channels being, therefore, substantially identical, the performance of the plate heat exchanger according to the invention is substantially higher than that of the prior art. Furthermore, the pressure drops inherent in the use of this exchanger are significantly reduced, compared with those occurring in the prior art.
L'invention garantit une grande simplicité de fabrication de l' échangeur à plaques. En effet, ele fait uniquement appel à un organe rapporté, dont le prix de revient est faible, et qui peut être fixé de manière aisée sur les parois du collecteur. En outre, cet organe rapporté, permettant de diminuer la section de passage du fluide vers le fond du collecteur, possède une faculté d'adaptation satisfaisante au nombre de plaques de l' échangeur. En effet, dans le cadre d'une augmentation de la longueur du collecteur, liée à un nombre de plaques plus élevé, il est uniquement nécessaire de modifier l'angle de révolution, ainsi que la longueur de 1 ' organe rapporté .The invention guarantees great simplicity in manufacturing the plate heat exchanger. Indeed, it only uses an add-on unit, the cost price of which is low, and which can be fixed easily on the walls of the collector. In addition, this added member, making it possible to reduce the cross-section of the fluid passage towards the bottom of the manifold, has a satisfactory adaptability to the number of plates of the exchanger. Indeed, in the context of an increase in the length of the collector, linked to a higher number of plates, it is only necessary to modify the angle of revolution, as well as the length of one added member.
Par ailleurs, étant donné que l'organe rapporté induit une diminution continue de la section de passage du fluide, ceci permet de ne créer pratiquement aucune turbulence, dans le collecteur de sortie.Furthermore, since the added member induces a continuous decrease in the cross-section of the fluid, this makes it possible to create practically no turbulence in the outlet manifold.
L' invention est tout particulièrement avantageuse dans le cas d'écoulements diphasiques, formés d'un gaz chargé en huile. Etant donné que la présence de l'organe rapporté permet d'augmenter la vitesse du fluide vers le fond du collecteur, sans pour autant créer de turbulences, toute rétention de cette huile est sensiblement évitée, au voisinage de ce fond.The invention is particularly advantageous in the case of two-phase flows, formed of a gas loaded with oil. Since the presence of the added member makes it possible to increase the speed of the fluid towards the bottom of the collector, without however creating turbulence, any retention of this oil is substantially avoided, in the vicinity of this bottom.
Il est avantageux que l'organe rapporté possède un axe principal confondu avec l'axe longitudinal médian du collecteur de sortie. Ainsi, le fluide est à même de s'écouler de façon régulièrement répartie autour de cet organe. It is advantageous that the added member has a main axis coincident with the median longitudinal axis of the outlet manifold. Thus, the fluid is able to flow in a regularly distributed manner around this member.

Claims

REVENDICATIONS
1. Echangeur de chaleur (2) à plaques, comprenant plusieurs plaques (6) , logées dans le volume intérieur de1. Plate heat exchanger (2), comprising several plates (6), housed in the interior volume of
1' échangeur et définissant des première (8) et seconde (10) séries de canaux de circulation indépendants, respectivement pour la circulation de premier et second fluides, notamment d'un fluide réfrigérant et d'un fluide à réfrigérer, ledit échangeur (2) comprenant en outre des premier (20) et second collecteurs d'entrée, s'étendant respectivement en amont des premier (8) et second (10) canaux, en faisant référence à l'écoulement de chaque fluide, ainsi que des premier (22) et second collecteurs de sortie, s'étendant en aval desdits premier (8) et second (10) canaux, caractérisé en ce qu'au moins l'un des premier (22) et second collecteurs de sortie est pourvu d'un organe rapporté (30 ; 80 ; 130) disposé dans le volume intérieur du collecteur, cet organe rapporté s'étendant à partir d'un fond (34) du ou de chaque collecteur, et permettant de diminuer de façon sensiblement continue la section de passage du ou de chaque fluide dans le ou chaque collecteur de sortie (22) , vers le fond (34) de ce collecteur.1 exchanger and defining first (8) and second (10) series of independent circulation channels, respectively for the circulation of first and second fluids, in particular a coolant and a coolant, said exchanger (2 ) further comprising first (20) and second inlet manifolds, extending respectively upstream of the first (8) and second (10) channels, with reference to the flow of each fluid, as well as first ( 22) and second outlet manifolds, extending downstream of said first (8) and second (10) channels, characterized in that at least one of the first (22) and second outlet manifolds is provided with a add-on member (30; 80; 130) disposed in the interior volume of the manifold, this add-on member extending from a bottom (34) of the or each manifold, and making it possible to decrease the passage cross-section substantially continuously or each fluid in the or each so collector rtie (22), towards the bottom (34) of this manifold.
2. Echangeur selon la revendication 1, caractérisé en que la section de passage du ou de chaque fluide, au voisinage du débouché du canal amont (8") dans le collecteur de sortie (22) , est comprise entre 1 et 50 %, de préférence entre 5 et 25 %, de la section transversale du collecteur de sortie (22) .2. Exchanger according to claim 1, characterized in that the passage section of the or each fluid, in the vicinity of the outlet of the upstream channel (8 ") in the outlet manifold (22), is between 1 and 50%, preferably between 5 and 25%, of the cross section of the outlet manifold (22).
3. Echangeur selon la revendication 1 ou 2 , caractérisé en ce que les dimensions transversales de l'organe rapporté (30 ; 80 ; 130) augmentent de façon sensiblement continue vers le fond (34) du collecteur de sortie (22) .3. Exchanger according to claim 1 or 2, characterized in that the transverse dimensions of the insert (30; 80; 130) increase substantially continuously towards the bottom (34) of the outlet manifold (22).
4. Echangeur selon l'une des revendications précédentes, caractérisé en ce que ledit organe rapporté possède des dimensions longitudinales (!) supérieures à 30%, de préférence à 50%, de la dimension longitudinale (L) du collecteur de sortie (22) .4. Exchanger according to one of the preceding claims, characterized in that said added member has longitudinal dimensions (!) Greater than 30%, preferably 50%, of the longitudinal dimension (L) of the outlet manifold (22) .
5. Echangeur selon l'une des revendications précédentes, caractérisé en ce que ledit organe rapporté (30 ; 80 ; 130) est fixé, notamment par brasage, sur le fond (34) dudit collecteur de sortie (22) .5. Exchanger according to one of the preceding claims, characterized in that said added member (30; 80; 130) is fixed, in particular by brazing, to the bottom (34) of said outlet manifold (22).
6. Echangeur selon l'une des revendications précédentes, caractérisé en ce que l'organe rapporté (30 ; 80 ; 130) possède un axe principal confondu avec un axe longitudinal médian (A) du collecteur de sortie (22) .6. Exchanger according to one of the preceding claims, characterized in that the added member (30; 80; 130) has a main axis coincident with a median longitudinal axis (A) of the outlet manifold (22).
7. Echangeur selon la revendication 6, caractérisé en ce que l'organe rapporté est un cône (30 ; 80) .7. Exchanger according to claim 6, characterized in that the added member is a cone (30; 80).
8. Echangeur selon la revendication 6, caractérisé en ce que les parois latérales (131) de l'organe rapporté (130) possèdent une concavité tournée vers ledit axe longitudinal médian (A) .8. Exchanger according to claim 6, characterized in that the side walls (131) of the insert (130) have a concavity facing towards said median longitudinal axis (A).
9. Echangeur selon l'une quelconque des revendications précédentes, caractérisé en ce que les dimensions transversales du collecteur de sortie (22) sont sensiblement constante .9. Exchanger according to any one of the preceding claims, characterized in that the transverse dimensions of the outlet manifold (22) are substantially constant.
10. Echangeur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins l'un des premier10. Exchanger according to any one of the preceding claims, characterized in that at least one of the first
(20) et second collecteurs d'entrée est également pourvu dudit organe rapporté. (20) and second inlet manifolds is also provided with said insert.
EP01919584A 2000-03-28 2001-03-27 Plate heat exchanger Withdrawn EP1269100A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0003917 2000-03-28
FR0003917A FR2807152B1 (en) 2000-03-28 2000-03-28 PLATE HEAT EXCHANGER
PCT/FR2001/000931 WO2001073366A1 (en) 2000-03-28 2001-03-27 Plate heat exchanger

Publications (1)

Publication Number Publication Date
EP1269100A1 true EP1269100A1 (en) 2003-01-02

Family

ID=8848577

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EP01919584A Withdrawn EP1269100A1 (en) 2000-03-28 2001-03-27 Plate heat exchanger

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EP (1) EP1269100A1 (en)
AU (1) AU2001246655A1 (en)
FR (1) FR2807152B1 (en)
WO (1) WO2001073366A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2855600B1 (en) * 2003-05-27 2005-07-08 Air Liquide CRYOGENOUS / WATER HEAT EXCHANGER AND APPLICATION TO GAS SUPPLY TO A POWER UNIT IN A VEHICLE
US8240367B2 (en) 2007-06-28 2012-08-14 Exxonmobil Research And Engineering Company Plate heat exchanger port insert and method for alleviating vibrations in a heat exchanger
CA2947321A1 (en) 2014-05-02 2015-11-05 Dana Canada Corporation Manifold structure for re-directing a fluid stream
CN108398039B (en) * 2018-04-17 2024-03-08 睿能太宇（沈阳）能源技术有限公司 Plate heat exchanger

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DE1901475A1 (en) * 1969-01-14 1970-08-27 Messer Griesheim Gmbh Distributing a two-phase flow to plate heat - exchangers
GB2054124B (en) * 1979-07-03 1983-03-30 Apv Co Ltd Plate heat exchanger
DE3311579C2 (en) * 1983-03-30 1985-10-03 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co. KG, 7000 Stuttgart Heat exchanger
JP2574488B2 (en) * 1989-12-05 1997-01-22 松下冷機株式会社 Heat exchanger
JP2644900B2 (en) * 1989-12-26 1997-08-25 松下冷機株式会社 Heat exchanger
JPH07301472A (en) * 1994-05-09 1995-11-14 Matsushita Refrig Co Ltd Header
JPH094995A (en) * 1995-06-19 1997-01-10 Matsushita Refrig Co Ltd Header
JP3007839B2 (en) * 1996-03-13 2000-02-07 松下冷機株式会社 Shunt

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Title
See references of WO0173366A1 *

Also Published As

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AU2001246655A1 (en) 2001-10-08
FR2807152B1 (en) 2002-12-06
FR2807152A1 (en) 2001-10-05
WO2001073366A1 (en) 2001-10-04

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