WO1996020383A1 - Circulating fluid heat exchanger - Google Patents

Circulating fluid heat exchanger Download PDF

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Publication number
WO1996020383A1
WO1996020383A1 PCT/FR1995/001678 FR9501678W WO9620383A1 WO 1996020383 A1 WO1996020383 A1 WO 1996020383A1 FR 9501678 W FR9501678 W FR 9501678W WO 9620383 A1 WO9620383 A1 WO 9620383A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
fluid
exchanger according
fins
walls
Prior art date
Application number
PCT/FR1995/001678
Other languages
French (fr)
Inventor
Guy Clerc
Olivier Friquet
Original Assignee
Thomson Tubes Electroniques
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 Thomson Tubes Electroniques filed Critical Thomson Tubes Electroniques
Publication of WO1996020383A1 publication Critical patent/WO1996020383A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01J—ELECTRIC DISCHARGE TUBES OR DISCHARGE LAMPS
    • H01J23/00—Details of transit-time tubes of the types covered by group H01J25/00
    • H01J23/005—Cooling methods or arrangements

Definitions

  • the present invention relates to a heat exchanger with fluid circulation, in particular for an electronic tube.
  • the heat exchanger functions as a cooler.
  • the collector requires cooling.
  • the anode In grid electron tubes, the anode must be cooled.
  • the anode or the collector are generally solid parts, in the form of a hollow cylinder, made of a material which is a good conductor of heat. Their inner surface is bombarded by the electrons emitted by the cathode and the thermal power is discharged radially towards their outer surface by conduction.
  • the fins are mounted radially around the part to be cooled.
  • FIG. 1 illustrates such a heat exchanger.
  • the fins bear the reference 1, the part to be cooled, which is for example an anode, the reference 2.
  • the fins 1 are generally made of a material which is a good thermal conductor such as copper, for example and are brazed to the part 2 to cool.
  • the fins 1 are arranged along generatrices of the cylinder forming the part 2.
  • the space 3 between the end of two contiguous fins 1 is closed so as to define channels 4 of substantially trapezoidal section.
  • the channels 4 force the fluid to travel a path directed along the generatrices of the cylinder of the part 2 to be cooled.
  • the passage section is smaller near the part to be cooled 2 than at the end of the fins 1, consequently less fluid circulates near the part to be cooled than at the end of the fins.
  • the temperature is highest at the level of the part to be cooled 2, while at the end of the fins, the temperature is lowest. The efficiency of this heat exchanger is far from the best.
  • FIGS. 2a, 2b, 2c Improvements have been made by limiting the cross section of the fluid far from the part to be cooled as illustrated in FIGS. 2a, 2b, 2c.
  • the fins 1 have deformations 5 and openings 6. These modifications to the surface of the fins 1 cause significant pressure drops.
  • the fluid is air, high-power turbines are then necessary to inject it into the exchanger thermal. The noise level increases considerably. It becomes well above acceptable levels. In addition, the high cost of the high power turbine must be taken into account.
  • the diameter of the part to be cooled is imposed by the characteristics of the tube. We often have to increase its outside diameter by thickening its wall to be able to braze enough radial fins. The whole becomes heavy and bulky.
  • the present invention aims to improve the efficiency of a heat exchanger with fluid circulation while retaining a low noise device, simple to manufacture, relatively small and economical.
  • the present invention therefore relates to a heat exchanger with circulation of fluid intended to ensure a heat exchange with a part, comprising several channels intended to convey the fluid.
  • the purpose of a first portion of these channels is to convey the fluid to a second portion in which the fluid is in contact with the external surface of the part.
  • a third portion of these channels has the purpose of discharging the fluid from the second portion. In the first and third portions, the fluid is conveyed in directions transverse to the external surface of the part.
  • the invention optimizes the circulation of the fluid in the channels which will preferably be delimited by fins.
  • the heat exchanger may include, in contact with the part, several substantially parallel fins and in the interval between two fins, several walls to divide this interval into independent spaces.
  • At least one partial partition is provided to divide the independent spaces, it provides a passage close to the exterior surface of the room.
  • An independent space contributes to delimiting a channel, its second portion being at the level of the passage, its first and its third portions on either side of the partial partition.
  • the use of both partitions and walls improves heat transfer.
  • the fins and / or the walls are substantially normal to the external surface of the part.
  • a particularly simple construction consists in placing the fins substantially normally to the axis of the cylinder and the walls radially. It is also preferable that the partitions are radial.
  • the fluid which leaves the third portion of a channel can be collected in a conduit.
  • the same conduit can collect the fluid coming from several channels.
  • the duct will preferably be directed along the axis of the cylinder.
  • the fixing is rounded to facilitate the passage of the fluid in the second portion of the channel. Indeed, this second portion forms an elbow relative to the other two and rounded angles allow better flow of the fluid. As in conventional exchangers, it is preferable to improve the heat transfer that the fins and / or the walls are brazed to the piece.
  • FIG. 3a, 3b respectively a cross section and a longitudinal section of a heat exchanger according to the invention.
  • FIGS. 3a and 3b show in transverse and longitudinal section, a heat exchanger 31 according to the invention intended to provide a heat exchange with a part referenced 30.
  • the heat exchanger is arranged around the part 30 which can, for example, be the anode to be cooled by an electronic grid tube. In this case, it is a hollow cylinder. Of course in other applications, it could have another shape, a parallelepiped or a prism for example.
  • the heat exchanger 31 comprises several channels 33 intended to convey the fluid, this fluid coming into contact with the exterior surface of the part to be cooled 30.
  • These channels 33 comprise a first portion 34 intended to convey the fluid to a second portion 32 in which the fluid is in contact with the external surface of the part to be cooled 30, and a third portion 35 intended to evacuate the fluid coming from the second portion 32.
  • the fluid is conveyed in directions transverse to the exterior surface of the part to be cooled 30.
  • the heat exchanger 31 comprises, in contact with the external surface of the part to be cooled 30, fins 36 substantially parallel to one another.
  • the fins 36 are substantially normal to the outer surface of the part to be cooled 30.
  • the gap between two fins 36 is partitioned by walls 37 in contact with the outer surface of the part to be cooled 30.
  • the walls 37 have a height substantially equal to that of the fins 36. These walls 37 divide the interval between two fins 36 into spaces independent of each other. An independent space contributes to delimiting a channel 33. These independent spaces are divided by at least one partial partition 38. Passages 39 are arranged between the partial partitions 38 and the external surface of the part to be cooled 30.
  • the second portion 32 of a channel is located at a passage 39.
  • the first 34 and the third 35 portions are located on either side of a partial partition 38.
  • the part to be cooled 30 shown in FIGS. 3a and 3b is cylindrical with an axis XX '.
  • the fins 36 are substantially normal to the axis XX 'and the walls 37 are radial.
  • the partial partitions 38 have also been shown to be radial. It would have been possible for them to be parallel to the fins 36. Other configurations would still be possible. It is preferable that an independent space is divided by a partial partition 38 into two equal parts and that the passage 39 is such that the section for passage of the fluid in the three portions of the channel is substantially the same.
  • the cooling fluid enters the heat exchanger through the first portion 34 of the channels 33 at a temperature lower than that of the part to be cooled, comes into contact with the part to be cooled 30 in the second portion 32 and is then evacuated by the third portion 35.
  • the fluid heats up when it comes into contact with the part to be cooled 30.
  • the part to be cooled 30 and the heat exchanger 31 are generally placed in an enclosure 40 supplied with cooling fluid.
  • the fluid is a gas, for example air
  • a turbine (not shown) can be used to circulate the gas in the enclosure 40.
  • the enclosure 40 can be supplied with liquid under pressure.
  • the heated fluid is collected after passing through the third portion 35 of the channels 33.
  • the channels 33 open into a conduit 41.
  • the same conduit 41 can be used to collect the fluid coming from several channels 33.
  • the conduit 41 is directed along the axis XX '. It collects the fluid coming from channels 33 which have walls 37 placed on the same radius. This conduit 41 evacuates the heated fluid from the enclosure 40.
  • the fins 36, the walls 37 and the partial partitions 38 will preferably be made of a material which is a good thermal conductor such as copper. They can be assembled together and fixed to the part to be cooled by brazing, for example, to improve heat transfer. To facilitate the passage of the fluid in the second portion 32 of the channels 33, it is possible that the fastenings between the fins 36 and the outer surface of the part to be cooled 30 are rounded. It is the same for the fastenings between the walls 37 and the outer surface of the part to be cooled 30. Unlike heat exchangers of the type shown in FIG. 1, the temperature of the fluid is substantially constant over the entire surface of the part 30 The heat exchanger according to the invention leads to a more uniform heat transfer. To optimize the efficiency of the heat exchanger according to the invention, it is possible to modify the number of channels, their cross-section and their length.
  • a heat exchanger according to the invention can be associated with a part whose wall thickness is smaller than that of the parts used so far.
  • the number of fins that can be used no longer depends on the outside diameter of the part. As the wall thickness is smaller, the volume of the part will be less and that of the heat exchanger also. A gain in volume is always appreciable.
  • the channels of the heat exchanger according to the invention have been delimited with fins, walls and partial partitions. Other channel configurations can be envisaged without departing from the scope of the invention.
  • the heat exchanger according to the invention has been described previously only in a cooler application, but it can of course be used in a heater application, it is sufficient that the fluid has in the first portion of the channels a temperature higher than that of the room to be heated.

Abstract

The invention concerns a circulating fluid heat exchanger for conducting heat exchange with a part (30) and comprising a plurality of channels (33) for transporting the fluid. The channels (33) include a first portion (34) in which the fluid is transported towards a second portion (32) where the fluid contacts the outer surface of said part (30), and a third portion (35) which receives the fluid discharged from the second portion (32). The fluid is transported in a direction transversal to the outer surface of the part (30) in the first and third portions (34, 35). The invention is useful as a cooler for an electron tube.

Description

ECHANGEUR THERMIQUE A CIRCULATION DE FLUIDE FLUID CIRCULATION HEAT EXCHANGER
La présente invention est relative à un échangeur thermique à circulation de fluide notamment pour tube électronique. Dans cette application, l'échangeur thermique fonctionne en refroidisseur. Dans les tubes électroniques tels que les klystrons, c'est le collecteur qui nécessite un refroidissement. Dans les tubes électroniques à grille, c'est l'anode qui doit être refroidie. L'anode ou le collecteur sont généralement des pièces massives, en forme de cylindre creux, en matériau bon conducteur de la chaleur. Leur surface intérieure est bombardée par les électrons émis par la cathode et la puissance thermique est évacuée radialement vers leur surface extérieure par conduction. Dans les échangeurs thermiques à circulation de fluide connus, pour améliorer le transfert thermique entre la surface extérieure et la masse de fluide (généralement de l'air) des ailettes sont montées radialement autour de la pièce à refroidir. La figure 1 illustre un tel échangeur thermique. Les ailettes portent la référence 1 , la pièce à refroidir, qui est par exemple une anode, la référence 2. Les ailettes 1 sont généralement réalisées dans un matériau bon conducteur thermique tel que le cuivre, par exemple et sont brasées à la pièce 2 à refroidir. Les ailettes 1 sont disposées selon des génératrices du cylindre formant la pièce 2. L'espace 3 entre l'extrémité de deux ailettes 1 contiguëes est obturé de manière à définir des canaux 4 de section sensiblement trapézoïdale. Les canaux 4 obligent le fluide à parcourir un chemin dirigé selon les génératrices du cylindre de la pièce 2 à refroidir. La section de passage est plus petite à proximité de la pièce à refroidir 2 qu'à l'extrémité des ailettes 1 , en conséquence moins de fluide circule à proximité de la pièce à refroidir qu'à l'extrémité des ailettes. C'est au niveau de la pièce à refroidir 2 que la température est la plus élevée, tandis qu'au niveau de l'extrémité des ailettes la température est moindre. Le rendement de cet échangeur thermique est loin d'être des meilleurs.The present invention relates to a heat exchanger with fluid circulation, in particular for an electronic tube. In this application, the heat exchanger functions as a cooler. In electronic tubes such as klystrons, the collector requires cooling. In grid electron tubes, the anode must be cooled. The anode or the collector are generally solid parts, in the form of a hollow cylinder, made of a material which is a good conductor of heat. Their inner surface is bombarded by the electrons emitted by the cathode and the thermal power is discharged radially towards their outer surface by conduction. In heat exchangers with known fluid circulation, to improve the heat transfer between the external surface and the mass of fluid (generally air), the fins are mounted radially around the part to be cooled. Figure 1 illustrates such a heat exchanger. The fins bear the reference 1, the part to be cooled, which is for example an anode, the reference 2. The fins 1 are generally made of a material which is a good thermal conductor such as copper, for example and are brazed to the part 2 to cool. The fins 1 are arranged along generatrices of the cylinder forming the part 2. The space 3 between the end of two contiguous fins 1 is closed so as to define channels 4 of substantially trapezoidal section. The channels 4 force the fluid to travel a path directed along the generatrices of the cylinder of the part 2 to be cooled. The passage section is smaller near the part to be cooled 2 than at the end of the fins 1, consequently less fluid circulates near the part to be cooled than at the end of the fins. The temperature is highest at the level of the part to be cooled 2, while at the end of the fins, the temperature is lowest. The efficiency of this heat exchanger is far from the best.
Des améliorations ont été apportées en limitant la section de passage du fluide loin de la pièce à refroidir comme l'illustrent les figures 2a, 2b, 2c. Les ailettes 1 comportent des déformations 5 et des ouvertures 6. Ces modifications de la surface des ailettes 1 provoquent des pertes de charge importantes. Lorsque le fluide est de l'air, des turbines de forte puissance sont alors nécessaires pour l'injecter dans l'échangeur thermique. Le niveau sonore augmente considérablement. Il devient bien supérieur aux niveaux acceptables. De plus, le coût élevé de la turbine de forte puissance doit être pris en considération.Improvements have been made by limiting the cross section of the fluid far from the part to be cooled as illustrated in FIGS. 2a, 2b, 2c. The fins 1 have deformations 5 and openings 6. These modifications to the surface of the fins 1 cause significant pressure drops. When the fluid is air, high-power turbines are then necessary to inject it into the exchanger thermal. The noise level increases considerably. It becomes well above acceptable levels. In addition, the high cost of the high power turbine must be taken into account.
Dans les tubes électroniques, le diamètre de la pièce à refroidir est imposé par les caractéristiques du tube. On est souvent obligé d'augmenter son diamètre extérieur en épaississant sa paroi pour pouvoir y braser suffisamment d'ailettes radiales. L'ensemble devient alors lourd et volumineux.In electronic tubes, the diameter of the part to be cooled is imposed by the characteristics of the tube. We often have to increase its outside diameter by thickening its wall to be able to braze enough radial fins. The whole becomes heavy and bulky.
La présente invention vise à améliorer le rendement d'un échangeur thermique à circulation de fluide tout en conservant un dispositif peu bruyant, simple à fabriquer, relativement peu volumineux et économique.The present invention aims to improve the efficiency of a heat exchanger with fluid circulation while retaining a low noise device, simple to manufacture, relatively small and economical.
La présente invention concerne donc un échangeur thermique à circulation de fluide destiné à assurer un échange thermique avec une pièce, comportant plusieurs canaux destinés à véhiculer le fluide. Une première portion de ces canaux a pour finalité de véhiculer le fluide vers une deuxième portion dans laquelle le fluide est en contact avec la surface extérieure de la pièce. Une troisième portion de ces canaux a pour finalité d'évacuer le fluide de la deuxième portion. Dans la première et la troisième portions, le fluide est véhiculé selon des directions transversales à la surface extérieure de la pièce.The present invention therefore relates to a heat exchanger with circulation of fluid intended to ensure a heat exchange with a part, comprising several channels intended to convey the fluid. The purpose of a first portion of these channels is to convey the fluid to a second portion in which the fluid is in contact with the external surface of the part. A third portion of these channels has the purpose of discharging the fluid from the second portion. In the first and third portions, the fluid is conveyed in directions transverse to the external surface of the part.
Tout le fluide est obligé de venir en contact avec la pièce puis est évacué.All the fluid is forced to come into contact with the part then is evacuated.
L'invention optimise la circulation du fluide dans les canaux qui seront de préférence délimités par des ailettes. L'échangeur thermique peut comporter en contact avec la pièce, plusieurs ailettes sensiblement parallèles et dans l'intervalle entre deux ailettes, plusieurs parois pour diviser cet intervalle en espaces indépendants.The invention optimizes the circulation of the fluid in the channels which will preferably be delimited by fins. The heat exchanger may include, in contact with the part, several substantially parallel fins and in the interval between two fins, several walls to divide this interval into independent spaces.
Au moins une cloison partielle est prévue pour diviser les espaces indépendants, elle aménage un passage à proximité de la surface extérieure de la pièce. Un espace indépendant contribue à délimiter un canal, sa deuxième portion se trouvant au niveau du passage, sa première et sa troisième portions de part et d'autre de la cloison partielle. Par rapport aux échangeurs thermiques classiques, l'utilisation à la fois de cloisons et de parois améliore le transfert thermique. De préférence, les ailettes et/ou les parois sont sensiblement normales à la surface extérieure de la pièce.At least one partial partition is provided to divide the independent spaces, it provides a passage close to the exterior surface of the room. An independent space contributes to delimiting a channel, its second portion being at the level of the passage, its first and its third portions on either side of the partial partition. Compared to conventional heat exchangers, the use of both partitions and walls improves heat transfer. Preferably, the fins and / or the walls are substantially normal to the external surface of the part.
Lorsque la pièce est cylindrique, une construction particulièrement simple consiste à placer les ailettes sensiblement normalement à l'axe du cylindre et les parois radialement. Il est aussi préférable que les cloisons soient radiales.When the part is cylindrical, a particularly simple construction consists in placing the fins substantially normally to the axis of the cylinder and the walls radially. It is also preferable that the partitions are radial.
Le fluide qui sort de la troisième portion d'un canal peut être collecté dans un conduit. Pour simplifier la construction, un même conduit peut collecter le fluide provenant de plusieurs canaux. Dans la configuration d'une pièce cylindrique, le conduit sera de préférence dirigé selon l'axe du cylindre.The fluid which leaves the third portion of a channel can be collected in a conduit. To simplify construction, the same conduit can collect the fluid coming from several channels. In the configuration of a cylindrical part, the duct will preferably be directed along the axis of the cylinder.
Lorsque les ailettes et/ou les parois sont fixées à la pièce, il est préférable que la fixation soit arrondie pour faciliter le passage du fluide dans la deuxième portion de canal. En effet, cette deuxième portion forme un coude par rapport aux deux autres et des angles arrondis permettent un meilleur écoulement du fluide. Comme dans les échangeurs classiques, il est préférable pour améliorer le transfert thermique que les ailettes et/ou les parois soient brasées à la pièce.When the fins and / or the walls are fixed to the part, it is preferable that the fixing is rounded to facilitate the passage of the fluid in the second portion of the channel. Indeed, this second portion forms an elbow relative to the other two and rounded angles allow better flow of the fluid. As in conventional exchangers, it is preferable to improve the heat transfer that the fins and / or the walls are brazed to the piece.
La présente invention sera mieux comprise à l'aide de la description qui suit, faite à titre d'exemple non limitatif et illustrée par les figures jointes qui représentent :The present invention will be better understood with the aid of the description which follows, given by way of nonlimiting example and illustrated by the attached figures which represent:
- la figure 1 , déjà décrite, une coupe transversale d'un échangeur thermique de type connu;- Figure 1, already described, a cross section of a heat exchanger of known type;
- les figures 2a, 2b, 2c, déjà décrites, respectivement une coupe transversale d'un échangeur thermique de type connu, une vue de face et une vue de profil d'une ailette du même échangeur thermique;- Figures 2a, 2b, 2c, already described, respectively a cross section of a known type heat exchanger, a front view and a side view of a fin of the same heat exchanger;
- les figures 3a, 3b respectivement une coupe transversale et une coupe longitudinale d'un échangeur thermique conforme à l'invention.- Figures 3a, 3b respectively a cross section and a longitudinal section of a heat exchanger according to the invention.
Les figures 3a et 3b montrent en coupe transversale et longitudinale, un échangeur thermique 31 selon l'invention destiné à assurer un échange thermique avec une pièce référencée 30. L'échangeur thermique est disposé autour de la pièce 30 qui peut, par exemple, être l'anode à refroidir d'un tube électronique à grille. Dans ce cas, c'est un cylindre creux. Bien entendu dans d'autres applications, elle pourrait avoir une autre forme, un parallélipipède ou un prisme par exemple. L'échangeur thermique 31 comporte plusieurs canaux 33 destinés à véhiculer le fluide, ce fluide venant en contact avec la surface extérieure de la pièce à refroidir 30.FIGS. 3a and 3b show in transverse and longitudinal section, a heat exchanger 31 according to the invention intended to provide a heat exchange with a part referenced 30. The heat exchanger is arranged around the part 30 which can, for example, be the anode to be cooled by an electronic grid tube. In this case, it is a hollow cylinder. Of course in other applications, it could have another shape, a parallelepiped or a prism for example. The heat exchanger 31 comprises several channels 33 intended to convey the fluid, this fluid coming into contact with the exterior surface of the part to be cooled 30.
Ces canaux 33 comportent une première portion 34 destinée à véhiculer le fluide vers une deuxième portion 32 dans laquelle le fluide est en contact avec la surface extérieure de la pièce à refroidir 30, et une troisième portion 35 destinée à évacuer le fluide provenant de la deuxième portion 32. Dans la première et la troisième portions, le fluide est véhiculé selon des directions transversales à la surface extérieure de la pièce à refroidir 30.These channels 33 comprise a first portion 34 intended to convey the fluid to a second portion 32 in which the fluid is in contact with the external surface of the part to be cooled 30, and a third portion 35 intended to evacuate the fluid coming from the second portion 32. In the first and third portions, the fluid is conveyed in directions transverse to the exterior surface of the part to be cooled 30.
Selon un mode de réalisation préféré, l'échangeur thermique 31 comporte en contact avec la surface extérieure de la pièce à refroidir 30, des ailettes 36 sensiblement parallèles entre elles. De préférence, les ailettes 36 sont sensiblement normales à la surface extérieure de la pièce à refroidir 30. L'intervalle entre deux ailettes 36 est cloisonné par des parois 37 en contact avec la surface extérieure de la pièce à refroidir 30.According to a preferred embodiment, the heat exchanger 31 comprises, in contact with the external surface of the part to be cooled 30, fins 36 substantially parallel to one another. Preferably, the fins 36 are substantially normal to the outer surface of the part to be cooled 30. The gap between two fins 36 is partitioned by walls 37 in contact with the outer surface of the part to be cooled 30.
De préférence, les parois 37 ont une hauteur sensiblement égale à celle des ailettes 36. Ces parois 37 divisent l'intervalle entre deux ailettes 36 en espaces indépendants les uns des autres . Un espace indépendant contribue à délimiter un canal 33. Ces espaces indépendants sont divisés par au moins une cloison partielle 38. Des passages 39 sont aménagés entre les cloisons partielles 38 et la surface extérieure de la pièce à refroidir 30.Preferably, the walls 37 have a height substantially equal to that of the fins 36. These walls 37 divide the interval between two fins 36 into spaces independent of each other. An independent space contributes to delimiting a channel 33. These independent spaces are divided by at least one partial partition 38. Passages 39 are arranged between the partial partitions 38 and the external surface of the part to be cooled 30.
La deuxième portion 32 d'un canal est située au niveau d'un passage 39. La première 34 et la troisième 35 portions sont situées de part et d'autre d'une cloison partielle 38.The second portion 32 of a channel is located at a passage 39. The first 34 and the third 35 portions are located on either side of a partial partition 38.
La pièce à refroidir 30 représentée sur les figures 3a et 3b est cylindrique d'axe XX'. Les ailettes 36 sont sensiblement normales à l'axe XX' et les parois 37 sont radiales. Les cloisons partielles 38 ont été représentées également radiales. Il aurait été possible qu'elles soient parallèles aux ailettes 36. D'autres configurations seraient encore possibles. Il est préférable qu'un espace indépendant soit divisé par une cloison partielle 38 en deux parties égales et que le passage 39 soit tel que la section de passage du fluide dans les trois portions du canal soit sensiblement la même. Le fluide de refroidissement pénètre dans l'échangeur thermique par la première portion 34 des canaux 33 à une température inférieure à celle de la pièce à refroidir, arrive en contact avec la pièce à refroidir 30 dans la deuxième portion 32 et est ensuite évacué par la troisième portion 35. Le fluide se réchauffe lorsqu'il vient en contact avec la pièce à refroidir 30.The part to be cooled 30 shown in FIGS. 3a and 3b is cylindrical with an axis XX '. The fins 36 are substantially normal to the axis XX 'and the walls 37 are radial. The partial partitions 38 have also been shown to be radial. It would have been possible for them to be parallel to the fins 36. Other configurations would still be possible. It is preferable that an independent space is divided by a partial partition 38 into two equal parts and that the passage 39 is such that the section for passage of the fluid in the three portions of the channel is substantially the same. The cooling fluid enters the heat exchanger through the first portion 34 of the channels 33 at a temperature lower than that of the part to be cooled, comes into contact with the part to be cooled 30 in the second portion 32 and is then evacuated by the third portion 35. The fluid heats up when it comes into contact with the part to be cooled 30.
La pièce à refroidir 30 et l'échangeur thermique 31 sont généralement placés dans une enceinte 40 alimentée en fluide de refroidissement. Dans le cas où le fluide est un gaz, de l'air par exemple, une turbine (non représentée) peut être utilisée pour mettre en circulation le gaz dans l'enceinte 40. Dans le cas où le fluide est un liquide, de l'eau par exemple, l'enceinte 40 peut être alimentée en liquide sous pression.The part to be cooled 30 and the heat exchanger 31 are generally placed in an enclosure 40 supplied with cooling fluid. In the case where the fluid is a gas, for example air, a turbine (not shown) can be used to circulate the gas in the enclosure 40. In the case where the fluid is a liquid, l for example, the enclosure 40 can be supplied with liquid under pressure.
Le fluide réchauffé est collecté après avoir être passé dans la troisième portion 35 des canaux 33. Les canaux 33 débouchent dans un conduit 41. Un même conduit 41 peut servir pour collecter le fluide provenant de plusieurs canaux 33. Dans l'exemple des figures 3a, 3b, le conduit 41 est dirigé selon l'axe XX'. Il collecte le fluide provenant de canaux 33 qui ont des parois 37 placées sur un même rayon. Ce conduit 41 évacue le fluide réchauffé hors de l'enceinte 40.The heated fluid is collected after passing through the third portion 35 of the channels 33. The channels 33 open into a conduit 41. The same conduit 41 can be used to collect the fluid coming from several channels 33. In the example of FIGS. 3a , 3b, the conduit 41 is directed along the axis XX '. It collects the fluid coming from channels 33 which have walls 37 placed on the same radius. This conduit 41 evacuates the heated fluid from the enclosure 40.
Les ailettes 36, les parois 37 et les cloisons partielles 38 seront de préférence réalisées dans un matériau bon conducteur thermique tel que le cuivre. Elles pourront être assemblées entre elles et fixées à la pièce à refroidir 30 par brasure par exemple pour améliorer le transfert thermique. Pour faciliter le passage du fluide dans la deuxième portion 32 des canaux 33, il est possible que les fixations entre les ailettes 36 et la surface extérieure de la pièce à refroidir 30 soient arrondies. Il en est de même pour les fixations entre les parois 37 et la surface extérieure de la pièce à refroidir 30. Contrairement aux échangeurs thermiques du type représenté sur la figure 1 , la température du fluide est sensiblement constante sur toute la surface de la pièce 30. L'échangeur thermique selon l'invention conduit à un transfert thermique plus uniforme. Pour optimiser le rendement de l'échangeur thermique selon l'invention, il est possible de jouer sur le nombre de canaux, sur leur section et sur leur longueur .The fins 36, the walls 37 and the partial partitions 38 will preferably be made of a material which is a good thermal conductor such as copper. They can be assembled together and fixed to the part to be cooled by brazing, for example, to improve heat transfer. To facilitate the passage of the fluid in the second portion 32 of the channels 33, it is possible that the fastenings between the fins 36 and the outer surface of the part to be cooled 30 are rounded. It is the same for the fastenings between the walls 37 and the outer surface of the part to be cooled 30. Unlike heat exchangers of the type shown in FIG. 1, the temperature of the fluid is substantially constant over the entire surface of the part 30 The heat exchanger according to the invention leads to a more uniform heat transfer. To optimize the efficiency of the heat exchanger according to the invention, it is possible to modify the number of channels, their cross-section and their length.
Il est alors possible de choisir de manière appropriée l'épaisseur des ailettes 36, des parois 37, et des cloisons partielles 38, leur espacement, leur hauteur ainsi que la section des conduits d'évacuation 41.It is then possible to appropriately choose the thickness of the fins 36, the walls 37, and the partial partitions 38, their spacing, their height as well as the section of the evacuation conduits 41.
Entre quatre et huit canaux 33, par exemple peuvent ceinturer l'anode d'un tube de type tétrode et une quinzaine de canaux peuvent déboucher dans un même conduit 41. Un échangeur thermique selon l'invention peut être associé à une pièce dont l'épaisseur de la paroi est plus faible que celle des pièces utilisées jusqu'à présent. En effet, le nombre d'ailettes que l'on peut utiliser ne dépend plus du diamètre extérieur de la pièce. L'épaisseur de paroi étant plus faible, le volume de la pièce sera moindre et celui de l'échangeur thermique également. Un gain en volume est toujours appréciable.Between four and eight channels 33, for example can surround the anode of a tetrode-type tube and fifteen channels can lead into the same conduit 41. A heat exchanger according to the invention can be associated with a part whose wall thickness is smaller than that of the parts used so far. The number of fins that can be used no longer depends on the outside diameter of the part. As the wall thickness is smaller, the volume of the part will be less and that of the heat exchanger also. A gain in volume is always appreciable.
Les canaux de l'échangeur thermique selon l'invention ont été délimités aves les ailettes, les parois et les cloisons partielles. D'autres configurations de canaux sont envisageables sans sortir du cadre de l'invention. L'échangeur thermique selon l'invention n'a été décrit précédemment que dans une application de refroidisseur, mais il peut bien sûr être utilisé dans une application de réchauffeur, il suffit que le fluide ait dans la première portion des canaux une température supérieure à celle de la pièce à réchauffer. The channels of the heat exchanger according to the invention have been delimited with fins, walls and partial partitions. Other channel configurations can be envisaged without departing from the scope of the invention. The heat exchanger according to the invention has been described previously only in a cooler application, but it can of course be used in a heater application, it is sufficient that the fluid has in the first portion of the channels a temperature higher than that of the room to be heated.

Claims

REVENDICATIONS
1 - Echangeur thermique (31 ) à circulation de fluide, destiné à assurer un échange thermique avec une pièce (30), équipé de plusieurs canaux (33) destinés à véhiculer le fluide, ces canaux (33) comportant une première portion (34) dans laquelle le fluide est véhiculé vers une deuxième portion (32) dans laquelle le fluide est en contact avec la surface extérieure de la pièce (30) et une troisième portion (35) dans laquelle le fluide est évacué de la deuxième portion (32), le fluide étant véhiculé selon des directions transversales à la surface extérieure de la pièce (30) dans la première et la troisième portions (34, 35),1 - Heat exchanger (31) with circulation of fluid, intended to ensure a heat exchange with a part (30), equipped with several channels (33) intended to convey the fluid, these channels (33) comprising a first portion (34) in which the fluid is conveyed to a second portion (32) in which the fluid is in contact with the external surface of the part (30) and a third portion (35) in which the fluid is discharged from the second portion (32) , the fluid being conveyed in directions transverse to the external surface of the part (30) in the first and third portions (34, 35),
- l'échangeur thermique (31 ) comportant en contact avec la pièce (30) plusieurs ailettes (36) sensiblement parallèles les unes aux autres, caractérisé en ce qu'il comporte en outre, plusieurs parois (37) pour cloisonner l'intervalle entre deux ailettes (36) en espaces indépendants, ces espaces indépendants comportant au moins une cloison (38) partielle pour les diviser, un passage (39) étant aménagé entre la cloison (38) et la surface extérieure de la pièce (30), un espace indépendant contribuant à délimiter un canal (33), sa deuxième portion (32) se trouvant au niveau du passage (39), ses première et troisième portions (34,35) de part et d'autre de la cloison partielle (38).- The heat exchanger (31) comprising in contact with the part (30) several fins (36) substantially parallel to each other, characterized in that it further comprises, several walls (37) for partitioning the interval between two fins (36) in independent spaces, these independent spaces comprising at least one partition (38) partial to divide them, a passage (39) being arranged between the partition (38) and the external surface of the room (30), a independent space contributing to delimit a channel (33), its second portion (32) being at the level of the passage (39), its first and third portions (34,35) on either side of the partial partition (38) .
2 - Echangeur thermique selon la revendication 1 , caractérisé en ce que les ailettes (36) sont sensiblement normales à la surface extérieure de la pièce (30).2 - Heat exchanger according to claim 1, characterized in that the fins (36) are substantially normal to the outer surface of the part (30).
3 - Echangeur thermique selon l'une des revendications 1 ou 2, caractérisé en ce que les parois (37) sont sensiblement normales à la surface extérieure de la pièce (30).3 - Heat exchanger according to one of claims 1 or 2, characterized in that the walls (37) are substantially normal to the outer surface of the part (30).
4 - Echangeur thermique selon l'une des revendications 1 à 3, caractérisé en ce que, lorsque la pièce (30) est circulaire d'axe (XX'), les ailettes (36) sont normales à l'axe (XX1), les parois (37) radiales.4 - Heat exchanger according to one of claims 1 to 3, characterized in that, when the part (30) is circular with an axis (XX '), the fins (36) are normal to the axis (XX 1 ) , the radial walls (37).
• 5 - Echangeur thermique selon la revendication 4, caractérisé en ce que les cloisons partielles (38) sont radiales. 6 - Echangeur thermique selon l'une des revendications 1 à 5, caractérisé en ce que la troisième portion (35) d'un canal (33) débouche dans un conduit (41 ) d'évacuation du fluide. • 5 - Heat exchanger according to claim 4, characterized in that the partial partitions (38) are radial. 6 - Heat exchanger according to one of claims 1 to 5, characterized in that the third portion (35) of a channel (33) opens into a conduit (41) for discharging the fluid.
7 - Echangeur thermique selon la revendication 6, caractérisé en ce que le conduit (41 ) est dirigé selon l'axe (XX') de la pièce (30)7 - Heat exchanger according to claim 6, characterized in that the duct (41) is directed along the axis (XX ') of the part (30)
8 - Echangeur thermique selon l'une des revendications 6 ou 7, caractérisé en ce qu'un même conduit (41 ) recueille le fluide de plusieurs canaux (33)8 - Heat exchanger according to one of claims 6 or 7, characterized in that the same conduit (41) collects the fluid from several channels (33)
9 - Echangeur thermique selon l'une des revendications 1 à 8, caractérisé en ce qu'il est contenu avec la pièce (30) dans une enceinte (40) alimentée en fluide9 - Heat exchanger according to one of claims 1 to 8, characterized in that it is contained with the part (30) in an enclosure (40) supplied with fluid
10 - Echangeur thermique selon la revendication 9, caractérisé en ce que le conduit (41 ) évacue le fluide à l'extérieur de l'enceinte (40)10 - Heat exchanger according to claim 9, characterized in that the conduit (41) evacuates the fluid outside the enclosure (40)
11 - Echangeur thermique selon l'une des revendications 1 à 10, caractérisé en ce que les ailettes (36) sont fixées à la surface extérieure de la pièce (30), cette fixation étant arrondie11 - Heat exchanger according to one of claims 1 to 10, characterized in that the fins (36) are fixed to the external surface of the part (30), this fixing being rounded
12 - Echangeur thermique selon l'une des revendications 1 à 1 1 , caractérisé en ce que les parois (37) sont fixées à la surface extérieure de la pièce (30), cette fixation étant arrondie12 - Heat exchanger according to one of claims 1 to 1 1, characterized in that the walls (37) are fixed to the external surface of the part (30), this fixing being rounded
13 - Echangeur thermique selon l'une des revendications 2 à 12, caractérisé en ce que la hauteur des parois (37) est sensiblement égale à celle des ailettes (36)13 - Heat exchanger according to one of claims 2 to 12, characterized in that the height of the walls (37) is substantially equal to that of the fins (36)
14 - Echangeur thermique selon l'une des revendications 2 à 13, caractérisé en ce que les ailettes (36) et/ou les parois sont brasées à la surface extérieure de la pièce (30) 15 - Echangeur thermique selon l'une des revendications 1 à 14, caractérisé en ce que les portions d'un même canal (33) ont une section de passage sensiblement égale. 14 - Heat exchanger according to one of claims 2 to 13, characterized in that the fins (36) and / or the walls are brazed to the external surface of the part (30) 15 - Heat exchanger according to one of claims 1 to 14, characterized in that the portions of the same channel (33) have a substantially equal passage section.
PCT/FR1995/001678 1994-12-28 1995-12-15 Circulating fluid heat exchanger WO1996020383A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9415779A FR2728961B1 (en) 1994-12-28 1994-12-28 FLUID CIRCULATION HEAT EXCHANGER
FR94/15779 1994-12-28

Publications (1)

Publication Number Publication Date
WO1996020383A1 true WO1996020383A1 (en) 1996-07-04

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PCT/FR1995/001678 WO1996020383A1 (en) 1994-12-28 1995-12-15 Circulating fluid heat exchanger

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FR (1) FR2728961B1 (en)
WO (1) WO1996020383A1 (en)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1356114A (en) * 1970-09-03 1974-06-12 Lage J R Method of and apparatus for heat transfer
FR2277295A1 (en) * 1974-07-05 1976-01-30 Acec Oil cooling heat exchanger - muff shaped duct around oil pipe includes baffle plates
US4684844A (en) * 1984-07-30 1987-08-04 Iversen Arthur H Liquid cooled stationary anode tubes

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1356114A (en) * 1970-09-03 1974-06-12 Lage J R Method of and apparatus for heat transfer
FR2277295A1 (en) * 1974-07-05 1976-01-30 Acec Oil cooling heat exchanger - muff shaped duct around oil pipe includes baffle plates
US4684844A (en) * 1984-07-30 1987-08-04 Iversen Arthur H Liquid cooled stationary anode tubes

Also Published As

Publication number Publication date
FR2728961A1 (en) 1996-07-05
FR2728961B1 (en) 1997-01-31

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