EP0737296B1 - Plate heat exchanger - Google Patents

Plate heat exchanger Download PDF

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Publication number
EP0737296B1
EP0737296B1 EP95905679A EP95905679A EP0737296B1 EP 0737296 B1 EP0737296 B1 EP 0737296B1 EP 95905679 A EP95905679 A EP 95905679A EP 95905679 A EP95905679 A EP 95905679A EP 0737296 B1 EP0737296 B1 EP 0737296B1
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EP
European Patent Office
Prior art keywords
plates
lines
facets
heat exchanger
bumps
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.)
Expired - Lifetime
Application number
EP95905679A
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German (de)
French (fr)
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EP0737296A1 (en
Inventor
Bernard Thonon
Roland Vidil
Claude Roussel
Jean-Michel Grillot
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.)
Vicarb SA
Commissariat a lEnergie Atomique et aux Energies Alternatives CEA
Original Assignee
Vicarb SA
Commissariat a lEnergie Atomique CEA
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Publication of EP0737296A1 publication Critical patent/EP0737296A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • F28F3/083—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning capable of being taken apart
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the invention relates to a plate heat exchanger, formed by a stack of corrugated plates delimiting channels of variable section.
  • corrugations The general function of the corrugations is to disturb the flow of fluids in order to increase the heat transfers through the plates, but they have the drawback of making the pressure drops much greater than with flat plates.
  • FR-A-2 648 220 a particular form of corrugated plate was described which made it possible to reduce the volume of the dead zones or of recirculation, where the fluid stagnates appreciably, which is one of the main causes of losses of heat exchange efficiency and fouling of the plates if the fluid is loaded with particles, because these then settle much more easily.
  • the plates of this prior invention had facets alternately of two different lengths and were joined together so that the corrugations of the consecutive plates formed angles preferably close to 180 °, that is to say that, in each channel , the long facets were oriented substantially in the same direction, which corresponded to the direction of flow of the fluid in the canal: the short facets therefore faced the fluid and, thanks to their steeper slope, deviated it strongly towards the long facets on the other plate delimiting the channel.
  • the fluid current licked the long facets over a large part of their surface and the recirculation zones, which form behind the undulations which restrict the channel, to know before long facets, were reduced accordingly. We therefore obtained better heat exchange performance and also easier flow.
  • the corrugations composed of a long facet and a short facet have, with identical pitch (the pitch designating the width of the corrugation), a lesser height than the corrugations of a conventional corrugated sheet, composed of two similar facets.
  • the channels have a smaller average section.
  • it is desired not to reduce this section which requires the use of plates of similar shape but with larger undulations and not larger.
  • the corrugation lines are then spaced apart and the number of points of contact of the plates between them smaller, which reduces the mechanical resistance of the stack.
  • the present invention can be viewed as an improvement on the previous invention, since it offers substantially equivalent advantages with regard to the heat exchange performance and the weakness of the fouling of the walls of the plates, but also losses of significantly lower load by reducing movements vortex, while involving the same number of points of contact between plates as ordinary corrugated plates.
  • the invention also lends itself to similar flows of fluids in both directions, which makes it possible to freely choose flows with parallel currents as well as with countercurrents.
  • the invention relates in its most general form to a heat exchanger composed of corrugated plates and joined together to delimit channels, the plates being similar, composed of facets joined by bottom and top lines, the plates being joined together at contact points; the plates are alternately turned over and joined either by their top lines or by their bottom lines; it is characterized in that the facets include bumps near the top lines and hollows near the bottom lines.
  • hollows and bumps be discontinuous along the facets, the bumps being located near the contact points, which allows them to play the role of reduction of volume of the channel only in the places where the dead or stagnant zones are most likely to form.
  • the bumps are much less useful elsewhere.
  • a simple construction is one whose facets include alternating hollows and bumps.
  • FIG. 1 A common type of plate heat exchanger is shown in FIG. 1. It is formed by a superposition of rectangular plates 1, carrying four holes 2 at the corners, a smooth groove 3 peripheral and corrugations 4 on the rest of their surface.
  • the plates can be manufactured by various means, by stamping, machining or molding, and in the real heat exchanger they are supported one on the other by their corrugations 4. Joints not shown are then compressed between the grooves 3 and maintain the seal. The stack is maintained by clamping.
  • the circulation of fluids is against the current, but it could be otherwise.
  • the corrugations 4 are in the form of chevrons but could be rectilinear. Fluids are generally liquids in existing embodiments, but this is not mandatory, and there may also be changes in state. The invention can be applied to all these categories of exchangers as well as to still different kinds of exchangers.
  • the corrugations 4 of the plates 1 can be broken down into top lines 10 alternating with bottom lines 11, the lines 10 and 11 all being parallel to each other and separating facets 12 contiguous.
  • the facets 12 have an uneven surface, that is to say that they are not straight over most of their length as in conventional corrugated sheets, but have bumps 13 and recesses 14.
  • the observation reference is located in the channel 6 above the plate 1, and the top lines 10 are above the bottom lines 11; the bumps 13 are convex reliefs and the hollows 14 are concave reliefs in this channel 6.
  • Holes and bumps 14 and 13 are produced without difficulty with the corrugations 4, for example by stamping with special dies, without any particular operation.
  • the hollows 14 and the bumps 13 do not extend over the entire length of the corrugations 4 but are, on the contrary, discontinuous and that the bumps 13 extend near the apex lines 10, about half the length of the corrugations 4, and at places close to the contact points 15 of the neighboring plate 1; more precisely, the bumps 13 of the adjacent facets 12 extend on either side of the adjoining top line 10 so as to surround the contact points 15 in pairs.
  • the recesses 14 are adjacent to the bottom lines 11 and s '' each extend between two consecutive bumps 13 of the facet 12 to which they belong (hollow 14 and bumps 13 therefore alternate along each of the facets 12), in such a way that they form a more or less uninterrupted series along each bottom lines 11, alternately on the two facets 12 which border it.
  • the average direction of the flow of the fluid in the channel 6 is vertical (according to the representation of this figure 3) and the angle ⁇ of the corrugations 4 with this direction is 60 °.
  • the other plate 1 delimiting the channel 6 will be similar but placed after having been turned over, so that the plates 1 will join by their apex lines 10 (FIGS. 4 and 5), their corrugations 4 being crossed and making angles of 60 °.
  • each pair of plates 1 which will be joined either by their respective top lines 10, or by their bottom lines 11. Whether the direction of flow is ascending or descending, the characteristics of the flow are identical because the shape of the channels 6 is symmetrical.
  • the bumps 13 form areas where the section of the channel 6 is very small around the contact points 15, where the fluid would have tended to stagnate, but that the bumps 13 do not contribute to obstruct the flow to other places in the canals 6.
  • the points of contact 16 with the other adjacent plate 1, located in the center of the diamonds formed by four points of contact 15 neighbors, will be surrounded by two pairs of hollows 14 of the two plates 1 concerned, but which can be seen as bumps 13 in the neighboring channel 6 that these two plates 1 delimit. It can therefore be seen that all of the channels 6 will have the same shape.
  • recesses 17 can be produced on the crown lines 10 at the contact points 15, between the bumps 13. These recesses allow on the one hand to precisely position the plates and on the other hand to better profile the flow around the corrugation.
  • the dimension of these recesses 17 is approximately 0.5 mm deep (between 0.3 mm and 1 mm), and their shape allows the interlocking of the contact points 15 of the upper plate. Their realization is done in the same way as the rest of the plate, without additional cost.
  • the recesses 17 are established on a plate 1 of two; the top lines 10 of the other plates 1 remain straight.
  • Bumps could also be made at the bottom lines 11, at the location of the contact points 16, of some of the plates 1 to also facilitate the interlocking of the plates 1 by these bottom lines 11.
  • One embodiment actually tested included plates with corrugations 4 whose angle ⁇ with respect to the flow was equal to 60 °, plates 1 whose pitch p (FIGS. 2 and 3) was 13 mm and the height e ( figure 2) of 3.9 mm, for heights or maximum depths of 0.8 mm and diameters of 3 to 4 mm for the bumps 13 and the hollows 14.
  • the channels 6 were 0.4 m long and 0.14 m wide.
  • the flow rate was 6 to 40 m 3 per hour in each channel 6.
  • the plates 1 according to the invention produced a pressure (or pressure) loss of 30 to 50% less than a conventional corrugated plate, that is to say devoid of bumps 13 and hollows 14.
  • the heat exchange coefficients were close, with deviations of less than 5%.
  • the plates were formed by stamping stainless steel sheets 0.6 mm thick.
  • the invention can be applied to all fields of activity where this type of exchanger already finds use, and in particular the chemical, para-chemical, petroleum, climatic, agro-food, energy producing and metallurgical industries.

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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)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Abstract

Heat exchanger comprising corrugated plates with faces (12) provided with bosses (13) and cavities (14) so as to reduce load loss. The invention is applicable in the field of chemical industries.

Description

L'invention se rapporte à un échangeur de chaleur à plaques, formé d'un empilement de plaques ondulées délimitant des canaux à section variable.The invention relates to a plate heat exchanger, formed by a stack of corrugated plates delimiting channels of variable section.

Les ondulations ont pour fonction générale de perturber l'écoulement des fluides pour accroître les transferts de chaleur à travers les plaques, mais elles présentent l'inconvénient de rendre les pertes de charge beaucoup plus importantes qu'avec des plaques planes. Dans un brevet français antérieur (FR-A-2 648 220), on décrivait une forme particulière de plaque ondulée qui permettait de réduire le volume des zones mortes ou de recirculation, où le fluide stagne sensiblement, ce qui est une des causes principales des pertes d'efficacité d'échange de chaleur et des encrassements des plaques si le fluide est chargé de particules, car celles-ci se déposent alors beaucoup plus facilement. Les plaques de cette invention antérieure présentaient des facettes alternativement de deux longueurs différentes et étaient assemblées entre elles de telle façon que les ondulations des plaques consécutives formaient des angles de préférence proches de 180°, c'est-à-dire que, dans chaque canal, les facettes longues étaient orientées sensiblement vers une même direction, qui correspondait à la direction d'écoulement du fluide dans le canal : les facettes courtes faisaient donc face au fluide et, grâce à leur pente plus forte, le déviaient fortement vers les facettes longues de l'autre plaque délimitant le canal. Il en résultait que le courant de fluide léchait les facettes longues sur une grande partie de leur surface et que les zones de recirculation, qui se forment derrière les ondulations qui restreignent le canal, à savoir devant les facettes longues, étaient réduites en conséquence. On obtenait donc de meilleures performances d'échange de chaleur et aussi un écoulement plus facile.The general function of the corrugations is to disturb the flow of fluids in order to increase the heat transfers through the plates, but they have the drawback of making the pressure drops much greater than with flat plates. In a prior French patent (FR-A-2 648 220), a particular form of corrugated plate was described which made it possible to reduce the volume of the dead zones or of recirculation, where the fluid stagnates appreciably, which is one of the main causes of losses of heat exchange efficiency and fouling of the plates if the fluid is loaded with particles, because these then settle much more easily. The plates of this prior invention had facets alternately of two different lengths and were joined together so that the corrugations of the consecutive plates formed angles preferably close to 180 °, that is to say that, in each channel , the long facets were oriented substantially in the same direction, which corresponded to the direction of flow of the fluid in the canal: the short facets therefore faced the fluid and, thanks to their steeper slope, deviated it strongly towards the long facets on the other plate delimiting the channel. As a result, the fluid current licked the long facets over a large part of their surface and the recirculation zones, which form behind the undulations which restrict the channel, to know before long facets, were reduced accordingly. We therefore obtained better heat exchange performance and also easier flow.

Les objectifs assignés à cette invention étaient ainsi remplis, mais on peut trouver certains inconvénients à une telle configuration de plaques. Tout d'abord, les ondulations composées d'une facette longue et d'une facette courte ont, à pas identique (le pas désignant la largeur de l'ondulation), une hauteur moindre que les ondulations d'une plaque ondulée classique, composée de deux facettes semblables. En d'autres termes, les canaux ont une section moyenne plus réduite. En pratique, on souhaite cependant ne pas diminuer cette section, ce qui oblige à utiliser des plaques de forme semblable mais aux ondulations plus grandes et à pas plus grand. Les lignes d'ondulations sont alors plus espacées et le nombre de points de contact des plaques entre elles plus petit, ce qui amoindrit la résistance mécanique de l'empilement.The objectives assigned to this invention were thus fulfilled, but one can find certain drawbacks with such a configuration of plates. First of all, the corrugations composed of a long facet and a short facet have, with identical pitch (the pitch designating the width of the corrugation), a lesser height than the corrugations of a conventional corrugated sheet, composed of two similar facets. In other words, the channels have a smaller average section. In practice, however, it is desired not to reduce this section, which requires the use of plates of similar shape but with larger undulations and not larger. The corrugation lines are then spaced apart and the number of points of contact of the plates between them smaller, which reduces the mechanical resistance of the stack.

Un autre inconvénient provient de ce que l'effet bénéfique n'est obtenu que pour un seul sens d'écoulement du fluide dans chaque canal, alterné dans des canaux adjacents, ce qui impose des circulations à contre-courant des fluides qui ne sont pas toujours souhaitées. Enfin, si les pertes de charge sont plus faibles qu'avec des plaques ondulées classiques, elles restent importantes.Another drawback stems from the fact that the beneficial effect is obtained only for a single direction of flow of the fluid in each channel, alternating in adjacent channels, which imposes counter-current circulations of the fluids which are not always wanted. Finally, if the pressure drops are lower than with conventional corrugated sheets, they remain significant.

La présente invention peut être regardée comme un perfectionnement de l'invention antérieure, puisqu'elle offre des avantages sensiblement équivalents en ce qui concerne la performance d'échange thermique et la faiblesse de l'encrassement des parois des plaques, mais aussi des pertes de charge sensiblement plus faibles en diminuant les mouvements tourbillonnaires, tout en impliquant le même nombre de points de contact entre plaques que les plaques ondulées ordinaires. Dans ses meilleures réalisations, l'invention se prête aussi à des écoulements semblables des fluides dans les deux sens, ce qui permet de choisir librement des écoulements à courants parallèles aussi bien qu'à contre-courant.The present invention can be viewed as an improvement on the previous invention, since it offers substantially equivalent advantages with regard to the heat exchange performance and the weakness of the fouling of the walls of the plates, but also losses of significantly lower load by reducing movements vortex, while involving the same number of points of contact between plates as ordinary corrugated plates. In its best embodiments, the invention also lends itself to similar flows of fluids in both directions, which makes it possible to freely choose flows with parallel currents as well as with countercurrents.

L'invention est relative sous sa forme la plus générale à un échangeur de chaleur composé de plaques ondulées et accolées entre elles pour délimiter des canaux, les plaques étant semblables, composées de facettes jointes par des lignes de fond et de sommet, les plaques étant jointes entre elles à des points de contact; les plaques sont alternativement retournées et jointes soit par leurs lignes de sommet, soit par leurs lignes de fond; elle est caractérisée en ce que les facettes comprennent des bosses près des lignes de sommet et des creux près des lignes de fond.The invention relates in its most general form to a heat exchanger composed of corrugated plates and joined together to delimit channels, the plates being similar, composed of facets joined by bottom and top lines, the plates being joined together at contact points; the plates are alternately turned over and joined either by their top lines or by their bottom lines; it is characterized in that the facets include bumps near the top lines and hollows near the bottom lines.

On arrive ainsi à une disposition où les ondulations sont aplaties et resserrent la section des canaux près des points de contact des ondulations, grâce à cette combinaison de creux et de bosses telle qu'elle est décrite et au retournement alternatif des plaques. Le brevet US-A-4 014 385, qui est le document le plus proche, décrit un agencement où les facettes comprennent au contraire des creux au sommet et des bosses au fond, si bien qu'elles sont raccordées entre elles en formant des angles droits, ce qui permet de raidir les plaques mais a un effet opposé à celui de l'invention sur l'écoulement du fluide. Une autre conception est présentée dans le brevet US-A-3 661 203: les lignes de sommet d'une plaque sur deux sont cassées par des enfoncements dans lesquels pénètrent les lignes de fond des autres plaques. Cette imbrication donne une bonne cohésion entre les plaques et une grande régularité de largeur des canaux.We thus arrive at an arrangement where the corrugations are flattened and tighten the section of the channels near the contact points of the corrugations, thanks to this combination of hollows and bumps as described and the alternating inversion of the plates. US-A-4,014,385, which is the closest document, describes an arrangement in which the facets, on the contrary, include hollows at the top and bumps at the bottom, so that they are connected together by forming angles straight, which makes it possible to stiffen the plates but has an opposite effect to that of the invention on the flow of the fluid. Another design is presented in US-A-3,661,203: the top lines of every second plate are broken by indentations into which the bottom lines of the other plates penetrate. This nesting gives good cohesion between the plates and a great regularity of width of the channels.

On préconise que creux et bosses soient discontinus le long des facettes, les bosses étant situées près des points de contact, ce qui permet qu'elles ne jouent le rôle de réduction de volume du canal qu'aux endroits où les zones mortes ou stagnantes sont le plus susceptibles de se former. Les bosses sont beaucoup moins utiles ailleurs. Une construction simple est celle dont les facettes comprennent des creux et des bosses qui alternent. Enfin, si chaque point de contact est situé entre deux bosses appartenant à des facettes adjacentes d'une même plaque, la réversibilité de l'écoulement dans les canaux est assurée.It is recommended that hollows and bumps be discontinuous along the facets, the bumps being located near the contact points, which allows them to play the role of reduction of volume of the channel only in the places where the dead or stagnant zones are most likely to form. The bumps are much less useful elsewhere. A simple construction is one whose facets include alternating hollows and bumps. Finally, if each contact point is located between two bumps belonging to adjacent facets of the same plate, the reversibility of the flow in the channels is ensured.

On va maintenant décrire l'invention plus en détail à l'aide des figures suivantes annexées à titre illustratif et non limitatif :

  • la figure 1 est une vue générale d'un échangeur de chaleur à plaques, où les plaques sont représentées en éclaté par souci de clarté,
  • la figure 2 est une vue partielle, en coupe, d'une plaque conforme à l'invention,
  • la figure 3 est une vue de dessus d'une plaque de l'invention, destinée à montrer la répartition des bosses et des creux,
  • la figure 4 illustre la façon dont les plaques sont superposées et en particulier l'angle de leurs ondulations,
  • et la figure 5 illustre les positions respectives des creux et des bosses sur les deux plaques superposées, selon une coupe plane indiquée par la trace V-V sur une plaque sur la figure 3.
The invention will now be described in more detail with the aid of the following figures which are given by way of illustration and not limitation:
  • FIG. 1 is a general view of a plate heat exchanger, where the plates are shown in exploded form for the sake of clarity,
  • FIG. 2 is a partial view, in section, of a plate according to the invention,
  • FIG. 3 is a top view of a plate of the invention, intended to show the distribution of the bumps and the hollows,
  • FIG. 4 illustrates the way in which the plates are superimposed and in particular the angle of their undulations,
  • and FIG. 5 illustrates the respective positions of the recesses and the bumps on the two superimposed plates, according to a plane section indicated by the trace VV on a plate in FIG. 3.

Une échangeur de chaleur à plaques d'un genre courant est représenté à la figure 1. Il est formé d'une superposition de plaques 1 rectangulaires, porteuses de quatre perçages 2 aux coins, d'une gorge lisse 3 périphérique et d'ondulations 4 sur le reste de leur surface. Les plaques peuvent être fabriquées par divers moyens, par emboutissage, usinage ou moulage, et dans l'échangeur de chaleur réel elles sont appuyées les unes sur les autres par leurs ondulations 4. Des joints non représentés sont alors comprimés entre les gorges 3 et maintiennent l'étanchéité. L'empilement est maintenu par serrage.A common type of plate heat exchanger is shown in FIG. 1. It is formed by a superposition of rectangular plates 1, carrying four holes 2 at the corners, a smooth groove 3 peripheral and corrugations 4 on the rest of their surface. The plates can be manufactured by various means, by stamping, machining or molding, and in the real heat exchanger they are supported one on the other by their corrugations 4. Joints not shown are then compressed between the grooves 3 and maintain the seal. The stack is maintained by clamping.

Dans la réalisation représentée, la circulation des fluides est à contre-courant, mais il pourrait en être autrement. Les ondulations 4 sont en forme de chevrons mais pourraient être rectilignes. Les fluides sont généralement des liquides dans les réalisations existantes, mais ce n'est pas obligatoire, et il peut aussi y avoir des changements d'état. L'invention peut s'appliquer à toutes ces catégories d'échangeurs ainsi qu'à des genres d'échangeurs encore différents.In the illustrated embodiment, the circulation of fluids is against the current, but it could be otherwise. The corrugations 4 are in the form of chevrons but could be rectilinear. Fluids are generally liquids in existing embodiments, but this is not mandatory, and there may also be changes in state. The invention can be applied to all these categories of exchangers as well as to still different kinds of exchangers.

Selon l'invention (figures 2 à 5), les ondulations 4 des plaques 1 peuvent être décomposées en lignes de sommet 10 alternant avec des lignes de fond 11, les lignes 10 et 11 étant toutes parallèles entre elles et séparant des facettes 12 jointives. Les facettes 12 ont une surface accidentée, c'est-à-dire qu'elles ne sont pas droites sur l'essentiel de leur longueur comme dans les plaques ondulées classiques, mais présentent des bosses 13 et des creux 14. Pour les besoins de la description, la référence d'observation est située dans le canal 6 au-dessus de la plaque 1, et les lignes de sommet 10 sont au-dessus de lignes de fond 11; les bosses 13 sont des reliefs convexes et les creux 14 des reliefs concaves dans ce canal 6.According to the invention (Figures 2 to 5), the corrugations 4 of the plates 1 can be broken down into top lines 10 alternating with bottom lines 11, the lines 10 and 11 all being parallel to each other and separating facets 12 contiguous. The facets 12 have an uneven surface, that is to say that they are not straight over most of their length as in conventional corrugated sheets, but have bumps 13 and recesses 14. For the purposes of the description, the observation reference is located in the channel 6 above the plate 1, and the top lines 10 are above the bottom lines 11; the bumps 13 are convex reliefs and the hollows 14 are concave reliefs in this channel 6.

Creux et bosses 14 et 13 sont produits sans difficulté avec les ondulations 4, par exemple par emboutissage avec des matrices spéciales, sans opération particulière. On voit sur la représentation générale de la figure 3 que les creux 14 et les bosses 13 ne s'étendent pas sur toute la longueur des ondulations 4 mais sont au contraire discontinus et que les bosses 13 s'étendent près des lignes de sommet 10, environ sur la moitié de la longueur des ondulations 4, et aux endroits proches des points de contact 15 de la plaque 1 voisine ; plus précisément, les bosses 13 des facettes 12 adjacentes s'étendent de part et d'autre de la ligne de sommet 10 mitoyenne de façon à entourer par paires les points de contact 15. Les creux 14 sont adjacents aux lignes de fond 11 et s'étendent chacun entre deux bosses 13 consécutives de la facette 12 à laquelle ils appartiennent (creux 14 et bosses 13 alternent donc le long de chacune des facettes 12), de telle façon qu'ils forment une suite à peu près ininterrompue le long de chacune des lignes de fond 11, alternativement sur les deux facettes 12 qui la bordent. Dans cette réalisation, la direction moyenne de l'écoulement du fluide dans le canal 6 est verticale (selon la représentation de cette figure 3) et l'angle α des ondulations 4 avec cette direction est de 60°. L'autre plaque 1 délimitant le canal 6 sera semblable mais posée après avoir été retournée, si bien que les plaques 1 se joindront par leurs lignes de sommet 10 (figures 4 et 5), leurs ondulations 4 étant croisées et faisant des angles de 60°. Il en sera de même pour chaque couple de plaques 1, qui seront jointes soit par leurs lignes de sommet 10 respectives, soit par leurs lignes de fond 11. Que le sens d'écoulement soit ascendant ou descendant, les caractéristiques de l'écoulement sont identiques car la forme des canaux 6 est symétrique. On remarque en particulier que les bosses 13 forment des zones où la section du canal 6 est très réduite autour des points de contact 15, où le fluide aurait eu tendance à stagner, mais que les bosses 13 ne contribuent pas à gêner l'écoulement aux autres endroits des canaux 6.Holes and bumps 14 and 13 are produced without difficulty with the corrugations 4, for example by stamping with special dies, without any particular operation. We see in the general representation of FIG. 3 that the hollows 14 and the bumps 13 do not extend over the entire length of the corrugations 4 but are, on the contrary, discontinuous and that the bumps 13 extend near the apex lines 10, about half the length of the corrugations 4, and at places close to the contact points 15 of the neighboring plate 1; more precisely, the bumps 13 of the adjacent facets 12 extend on either side of the adjoining top line 10 so as to surround the contact points 15 in pairs. The recesses 14 are adjacent to the bottom lines 11 and s '' each extend between two consecutive bumps 13 of the facet 12 to which they belong (hollow 14 and bumps 13 therefore alternate along each of the facets 12), in such a way that they form a more or less uninterrupted series along each bottom lines 11, alternately on the two facets 12 which border it. In this embodiment, the average direction of the flow of the fluid in the channel 6 is vertical (according to the representation of this figure 3) and the angle α of the corrugations 4 with this direction is 60 °. The other plate 1 delimiting the channel 6 will be similar but placed after having been turned over, so that the plates 1 will join by their apex lines 10 (FIGS. 4 and 5), their corrugations 4 being crossed and making angles of 60 °. It will be the same for each pair of plates 1, which will be joined either by their respective top lines 10, or by their bottom lines 11. Whether the direction of flow is ascending or descending, the characteristics of the flow are identical because the shape of the channels 6 is symmetrical. We note in particular that the bumps 13 form areas where the section of the channel 6 is very small around the contact points 15, where the fluid would have tended to stagnate, but that the bumps 13 do not contribute to obstruct the flow to other places in the canals 6.

De même, les points de contact 16 avec l'autre plaque 1 adjacente, situés au centre des losanges formés par quatre points de contact 15 voisins, seront entourés par deux paires de creux 14 des deux plaques 1 concernées, mais qu'on voit comme des bosses 13 dans le canal 6 voisin que ces deux plaques 1 délimitent. On s'aperçoit donc que tous les canaux 6 auront la même forme.Similarly, the points of contact 16 with the other adjacent plate 1, located in the center of the diamonds formed by four points of contact 15 neighbors, will be surrounded by two pairs of hollows 14 of the two plates 1 concerned, but which can be seen as bumps 13 in the neighboring channel 6 that these two plates 1 delimit. It can therefore be seen that all of the channels 6 will have the same shape.

L'influence des creux 14 n'est guère sensible sur l'écoulement dans les canaux 6.The influence of the recesses 14 is hardly noticeable on the flow in the channels 6.

Pour permettre le bon positionnement des plaques les unes par rapport aux autres, des creux 17 peuvent être réalisés sur les lignes de sommet 10 aux points de contact 15, entre les bosses 13. Ces creux permettent d'une part de positionner de façon précise les plaques et d'autre part de mieux profiler l'écoulement autour de l'ondulation. La dimension de ces creux 17 est de 0,5 mm de profondeur environ (entre 0,3 mm et 1 mm), et leur forme permet l'emboîtement des points de contact 15 de la plaque supérieure. Leur réalisation se fait de la même façon que le reste de la plaque, sans coût supplémentaire. Les creux 17 sont établis sur une plaque 1 sur deux ; les lignes de sommet 10 des autres plaques 1 restent droites.To allow the correct positioning of the plates with respect to each other, recesses 17 can be produced on the crown lines 10 at the contact points 15, between the bumps 13. These recesses allow on the one hand to precisely position the plates and on the other hand to better profile the flow around the corrugation. The dimension of these recesses 17 is approximately 0.5 mm deep (between 0.3 mm and 1 mm), and their shape allows the interlocking of the contact points 15 of the upper plate. Their realization is done in the same way as the rest of the plate, without additional cost. The recesses 17 are established on a plate 1 of two; the top lines 10 of the other plates 1 remain straight.

Des bosses pourraient aussi être réalisées aux lignes de fond 11, à l'endroit des points de contact 16, de certaines des plaques 1 pour faciliter aussi l'emboîtement des plaques 1 par ces lignes de fond 11.Bumps could also be made at the bottom lines 11, at the location of the contact points 16, of some of the plates 1 to also facilitate the interlocking of the plates 1 by these bottom lines 11.

D'autres réalisations sont envisageables en fonction en particulier des angles que font les ondulations par rapport à la direction moyenne de l'écoulement.Other embodiments are possible depending in particular on the angles made by the undulations with respect to the mean direction of the flow.

Une réalisation effectivement essayée comprenait des plaques avec des ondulations 4 dont l'angle α par rapport à l'écoulement était égal à 60°, des plaques 1 dont le pas p (figures 2 et 3) était de 13 mm et la hauteur e (figure 2) de 3,9 mm, pour des hauteurs ou des profondeurs maximales de 0,8 mm et des diamètres de 3 à 4 mm pour les bosses 13 et les creux 14. Les canaux 6 avaient 0,4 m de longueur et 0,14 m de largeur. Le débit était de 6 à 40 m3 à l'heure dans chaque canal 6. Les plaques 1 conformes à l'invention ont produit une perte de charge (ou de pression) de 30 à 50% moindre qu'une plaque ondulée classique, c'est-à-dire dépourvue de bosses 13 et de creux 14. Les coefficients d'échange de chaleur ont été proches, avec des écarts inférieurs à 5%. Les plaques étaient formées par un emboutissage de tôles d'acier inoxydable de 0,6 mm d'épaisseur.One embodiment actually tested included plates with corrugations 4 whose angle α with respect to the flow was equal to 60 °, plates 1 whose pitch p (FIGS. 2 and 3) was 13 mm and the height e ( figure 2) of 3.9 mm, for heights or maximum depths of 0.8 mm and diameters of 3 to 4 mm for the bumps 13 and the hollows 14. The channels 6 were 0.4 m long and 0.14 m wide. The flow rate was 6 to 40 m 3 per hour in each channel 6. The plates 1 according to the invention produced a pressure (or pressure) loss of 30 to 50% less than a conventional corrugated plate, that is to say devoid of bumps 13 and hollows 14. The heat exchange coefficients were close, with deviations of less than 5%. The plates were formed by stamping stainless steel sheets 0.6 mm thick.

L'invention peut être appliquée à tous les domaines d'activité où ce genre d'échangeurs trouve déjà emploi, et notamment les industries chimiques, para-chimiques, pétrolières, climatiques, agro-alimentaires, productrices d'énergie et métallurgiques.The invention can be applied to all fields of activity where this type of exchanger already finds use, and in particular the chemical, para-chemical, petroleum, climatic, agro-food, energy producing and metallurgical industries.

Claims (5)

  1. Heat exchanger composed of corrugated plates (1) placed side by side to delimit channels (6), the plates (1) being similar, composed of facets (12) joined by bottom lines (11) and top lines (10), the plates being joined together at contact points (15, 16), characterized in that the plates being alternately turned over and joined either through their top lines (10, 10) or their bottom lines (11, 11), characterized in that the facets (12) include bosses (13) near the top lines (10) and hollows (14) near the bottom lines (11).
  2. Heat exchanger according to claim 1, characterized in that hollows and bosses are discontinuous along the facets, the bosses (13) being located near the contact points (15).
  3. Heat exchanger according to claim 2, characterized in that each facet (12) includes hollows (14) and bosses (13) which alternate.
  4. Heat exchanger according to claim 2, characterized in that each contact point (15) is located between two bosses (13) belonging to adjacent facets (12) of the same plate (1).
  5. Heat exchanger according to claim 1, characterized in that the top lines (10) of certain plates (1) have hollows (17) at the contact points (15), in which the top lines (10) of other plates (1) fit.
EP95905679A 1993-12-29 1994-12-28 Plate heat exchanger Expired - Lifetime EP0737296B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9315816A FR2714456B1 (en) 1993-12-29 1993-12-29 Improved plate heat exchanger.
FR9315816 1993-12-29
PCT/FR1994/001545 WO1995018348A1 (en) 1993-12-29 1994-12-28 Heat exchanger with improved plates

Publications (2)

Publication Number Publication Date
EP0737296A1 EP0737296A1 (en) 1996-10-16
EP0737296B1 true EP0737296B1 (en) 1997-08-06

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Application Number Title Priority Date Filing Date
EP95905679A Expired - Lifetime EP0737296B1 (en) 1993-12-29 1994-12-28 Plate heat exchanger

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US (1) US5806584A (en)
EP (1) EP0737296B1 (en)
JP (1) JP3618350B2 (en)
DE (1) DE69404868T2 (en)
DK (1) DK0737296T3 (en)
ES (1) ES2107911T3 (en)
FR (1) FR2714456B1 (en)
GR (1) GR3025251T3 (en)
NO (1) NO305920B1 (en)
WO (1) WO1995018348A1 (en)

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DE19963373A1 (en) * 1999-12-28 2001-07-12 Abb Alstom Power Ch Ag Device for cooling a flow channel wall surrounding a flow channel with at least one rib train
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US7011904B2 (en) * 2002-07-30 2006-03-14 General Electric Company Fluid passages for power generation equipment
DE10249724B4 (en) * 2002-10-25 2005-03-17 Bayer Industry Services Gmbh & Co. Ohg High-tempering
DE10333177A1 (en) * 2003-07-22 2005-02-24 Modine Manufacturing Co., Racine Flow channel for a heat exchanger
US6976531B2 (en) * 2003-10-22 2005-12-20 Dana Canada Corporation Heat exchanger, method of forming a sleeve which may be used in the heat exchanger, and a sleeve formed by the method
FR2876179B1 (en) * 2004-10-04 2007-02-16 Alfa Laval Vicarb Sa HEAT EXCHANGER WITH SPECIFIC PLATES
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JP2016114300A (en) * 2014-12-15 2016-06-23 フタバ産業株式会社 Heat exchanger
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Also Published As

Publication number Publication date
NO962758L (en) 1996-06-28
US5806584A (en) 1998-09-15
DE69404868T2 (en) 1998-02-12
ES2107911T3 (en) 1997-12-01
NO962758D0 (en) 1996-06-28
NO305920B1 (en) 1999-08-16
WO1995018348A1 (en) 1995-07-06
DK0737296T3 (en) 1998-02-23
DE69404868D1 (en) 1997-09-11
FR2714456B1 (en) 1996-01-12
GR3025251T3 (en) 1998-02-27
JP3618350B2 (en) 2005-02-09
EP0737296A1 (en) 1996-10-16
JPH09511565A (en) 1997-11-18
FR2714456A1 (en) 1995-06-30

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