EP0641980B1 - Device for heat exchange with a fluid which is partially freezing - Google Patents

Device for heat exchange with a fluid which is partially freezing Download PDF

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Publication number
EP0641980B1
EP0641980B1 EP94420241A EP94420241A EP0641980B1 EP 0641980 B1 EP0641980 B1 EP 0641980B1 EP 94420241 A EP94420241 A EP 94420241A EP 94420241 A EP94420241 A EP 94420241A EP 0641980 B1 EP0641980 B1 EP 0641980B1
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EP
European Patent Office
Prior art keywords
fluid
cooled
rotor
heat exchange
circulation
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EP94420241A
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German (de)
French (fr)
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EP0641980A1 (en
Inventor
Adrien Laude-Bousquet
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A. LAUDE-BOUSQUET
Johnson Controls Enterprises SAS
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MC International SA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25C—PRODUCING, WORKING OR HANDLING ICE
    • F25C1/00—Producing ice
    • F25C1/12—Producing ice by freezing water on cooled surfaces, e.g. to form slabs
    • F25C1/14—Producing ice by freezing water on cooled surfaces, e.g. to form slabs to form thin sheets which are removed by scraping or wedging, e.g. in the form of flakes

Definitions

  • the present invention relates generally to any indirect heat exchange between, on the one hand a refrigerant or refrigerant, for example a refrigerant (for example ammonia) during vaporization, and on the other hand a fluid with cool, namely a liquid during cooling and / or partial freezing, excluding any setting or mass of said fluid, such as glycol, alcoholic or salty water, the crystallization point of which is less than 0 ° vs.
  • a refrigerant or refrigerant for example a refrigerant (for example ammonia) during vaporization
  • a fluid with cool namely a liquid during cooling and / or partial freezing, excluding any setting or mass of said fluid, such as glycol, alcoholic or salty water, the crystallization point of which is less than 0 ° vs.
  • scraped surface heat exchangers constitute devices of complicated structure and construction, and therefore of a non-negligible cost, in particular if the scrapers are pivotally mounted on the rotor, each with its own return means. .
  • the subject of the present invention is an alternative to scraped surface heat exchangers, which is much simpler as regards its construction and operation.
  • the present invention in general, to oppose the deposition of any solid layer on the hot face of the heat exchange wall, there is created in the current of the fluid to be cooled, circulating in the aforementioned pressure circulation conduit. , and in contact with the hot face of the heat exchange wall, a turbulent boundary layer, sub-cooled in the liquid phase, and in direct heat exchange with the rest of the current of the fluid to be cooled.
  • the various antagonistic elements of the deposition of any solid layer of the fluid to be cooled, on the hot face of the heat exchange wall comprise a multiplicity of flexible filaments, one end of which is integral with the rotor , and whose other free end is adjacent, that is to say in contact or in the vicinity but at a distance from the hot face of the heat exchange wall.
  • the flexible filaments are arranged essentially to stir in the liquid phase the boundary layer of the current of the fluid to be cooled, in contact with the hot face of the heat exchange wall, and in admixture with the rest of said fluid to cool.
  • sub-cooled is meant the characteristic that the heat exchange fluid is brought into the liquid phase, that is to say without at least partial freezing, at a temperature below its crystallization point.
  • the formation of a turbulent boundary layer in contact with the hot face of the heat exchange wall has the effect that freezing takes place, not on the hot face of said wall, but within of the fluid to be cooled in circulation, immediately in the vicinity of said wall, by direct heat exchange, that is to say by mixing the turbulent and sub-cooled boundary layer, expelled from said hot face, with the rest of the fluid to cool.
  • this turbulent boundary layer is obtained, in a non-exclusive manner, by the vibratile effect, of agitation and / or homogenization of the free end of the flexible filaments, in rotation.
  • the intrinsic characteristics of these filaments including the nature (in terms of flexibility and / or rigidity, resistance to low temperatures, etc.), as well as the arrangement of these different filaments, including density per unit area, are chosen, firstly according to the nature of the fluid to be cooled, and secondly the speed of rotation of the rotor, so as to obtain the turbulent boundary layer in phase liquid, characterizing the present invention.
  • the present invention also provides the following determining advantages.
  • the freezing of the fluid to be cooled takes place by obtaining micro-crystals, that is to say solid phase crystals of dimensions much smaller than those of the crystals obtained with a scraped surface exchanger. Obtaining such micro-crystals promotes the homogeneity of the cooled fluid, that is to say of the mixture of the liquid and solid phases of said fluid.
  • micro-crystals reduce or suppress the inertia when melting the cooled fluid, obtained in two-phase form, which appears extremely favorable when said fluid is then used in heat exchange processes, in particular refrigeration, with exchange of the latent heat of fusion of the solid phase of said fluid.
  • the present invention also makes it possible to reduce or limit the expenditure of energy required, in particular mechanical energy, to prevent or counteract the formation of any solid layer on the hot face of the heat exchange wall.
  • the invention also makes it possible to increase the heat exchange coefficient of the fluid during cooling with respect to the heat exchange wall.
  • the filamentary members 15 are separated from each other, being at the same time, superimposed in groups of two, and offset angularly with respect to the axis of the rotor, for example at an angle of 90 ° or 60 °, from one group to another, and this from one end to the other of the circulation duct 3. And two filamentary members 15 of the same group are arranged opposite in a single and same diametrical plane.
  • the rotor drive means 40 consists of a motor 17 mounted outside of the circulation duct 3, and coupled to the rotor 12 by any suitable means, for example a gear motor.
  • FIG. 2 differs from that previously described, by the mode of driving the rotor 12.
  • the rotor is driven, with a means 18 acting under the driving effect of the fluid 2 to be cooled, passing through the circulation duct 3.
  • conduits 3 for circulation of the fluid to be cooled are arranged in a battery.
  • one and the same motor 17 is coupled by a transmission means 31 to the various rotors 12 of the various circulation conduits 3.
  • the embodiment shown in Figure 7 includes a battery of conduits 3, as previously described with reference to Figures 4 to 6. But in this case, and as already described with reference to Figure 2, the motor 17 has been deleted in favor of motor means 23 integrated in the rotors 12, and acting under the sole effect of the circulation of the fluid 2. To this end, the distributor 29 of the fluid to be cooled communicates only with the different axial inlets 21 of the hollow rotors 12 of the different traffic conduits 3 respectively.
  • filamentary members 15 are superimposed in pairs, possibly being angularly offset from one pair to the other, as shown more particularly in FIGS. 10 to 14.
  • the same arm 46 or 47 of radial extension carries two filamentary members 15 opposite one with respect to the other, in relation to the two hot faces 6a of two exchange partitions 42 and 43 thermal, belonging respectively to the two abovementioned capacities 41, that is to say facing one another.
  • FIG. 9 differs from that described according to FIG. 8, essentially by the presence of vanes 54 for driving the rotor 12, under the driving effect of the fluid 2 to be cooled in circulation, distributed radially in the box 51 of introduction of said fluid.
  • the pairs of radial arms 46 and 47 are angularly offset with respect to each other, at a predetermined angle, for example 60 °, and this according to the same direction of rotation, clockwise or counterclockwise.
  • the fixed tube 55 has two perforations 55a and 55b, axially elongated, and opposite.
  • the angular dimension of each perforation 55a or 55b is identical to the predetermined angle of offset from one pair to the other, for example 60 °.

Abstract

The present invention relates to a device for heat exchange between a coolant fluid (1) undergoing vaporisation and a fluid (2) to be cooled which is undergoing freezing. According to the invention, the device comprises a duct (3) for the fluid to be cooled, a casing (7) which forms, around the duct (3), an enclosure (8) for passage of the coolant fluid, and a mechanical means (11) for separating the wall (6) of the duct (3) from any solid phase in the fluid to be cooled, which mechanical means (11) consists of a rotor (12) provided with flexible radial filaments (14). The invention applies in particular to obtaining homogeneous mixtures of water and of ice. <IMAGE>

Description

La présente invention concerne de manière générale tout échange de chaleur indirect entre, d'une part un fluide frigorigène ou réfrigérant, par exemple un liquide frigorigène (par exemple de l'ammoniac) en cours de vaporisation, et d'autre part un fluide à refroidir, à savoir un liquide en cours de refroidissement et/ou congélation partielle, à l'exclusion de toute prise ou masse dudit fluide, tel que de l'eau glycolée, alcoolisée ou salée, dont le point de cristallisation est inférieur à 0°C.The present invention relates generally to any indirect heat exchange between, on the one hand a refrigerant or refrigerant, for example a refrigerant (for example ammonia) during vaporization, and on the other hand a fluid with cool, namely a liquid during cooling and / or partial freezing, excluding any setting or mass of said fluid, such as glycol, alcoholic or salty water, the crystallization point of which is less than 0 ° vs.

S'agissant du refroidissement avec congélation partielle d'un liquide ou fluide, de manière à éviter la prise en masse de ce dernier sous l'effet de sa solidification, et obtenir un fluide consistant en un mélange homogène des phases liquide et solide du fluide, on connaît déjà (voir le document EP-A-0 257 936) et utilise des dispositifs d'échange de chaleur dits "à surface raclée", comprenant :

  • au moins un conduit de circulation sous pression du fluide à refroidir, d'une entrée à une sortie opposée pour ledit fluide, et dont la paroi constitue une surface d'échange thermique, avec une face dite chaude au contact du fluide à refroidir, et une face opposée, dite froide, au contact du fluide frigorigène ;
  • une enveloppe ménageant avec et autour dudit conduit de circulation une enceinte ou moyen de réception ou passage du fluide frigorigène, préférentiellement à contre-courant du fluide à refroidir, d'une entrée à une sortie pour ledit fluide frigorigène ;
  • et un moyen mécanique antagoniste du dépôt sur la face chaude de la paroi du conduit, de toute couche solide du fluide en cours de refroidissement, ce moyen comportant un rotor monté au sein dudit conduit, et différents éléments antagonistes dudit dépôt, consistant chacun en un racleur au contact ou au voisinage de la face chaude de la paroi du conduit ; ces différents éléments dits antagonistes sont distribués selon l'axe et autour du rotor, et entraînés par un moyen moteur, monté à l'extérieur du conduit de circulation.
With regard to cooling with partial freezing of a liquid or fluid, so as to avoid solidification of the latter under the effect of its solidification, and to obtain a fluid consisting of a homogeneous mixture of the liquid and solid phases of the fluid , we already know (see document EP-A-0 257 936) and use so-called "scraped surface" heat exchange devices, comprising:
  • at least one pressurized circulation pipe for the fluid to be cooled, from an inlet to an opposite outlet for said fluid, and the wall of which constitutes a heat exchange surface, with a so-called hot face in contact with the fluid to be cooled, and an opposite face, called cold, in contact with the refrigerant;
  • an envelope providing with and around said circulation duct an enclosure or means for receiving or passing the refrigerant, preferably against the current of the fluid to be cooled, from an inlet to an outlet for said refrigerant;
  • and a mechanical means antagonistic to the deposition on the hot face of the wall of the conduit, of any solid layer of the fluid being cooled, this means comprising a rotor mounted within said conduit, and different antagonistic elements of said deposit, each consisting of a scraper in contact with or near the hot face of the wall of the duct; these different so-called antagonistic elements are distributed along the axis and around the rotor, and driven by a motor means, mounted outside the circulation duct.

Un tel dispositif d'échange de chaleur, à surface raclée, permet d'échanger de la chaleur entre, d'une part le fluide frigorigène, par exemple en cours de vaporisation, et d'autre part le fluide à refroidir, en cours de congélation partielle, et ceci :

  • en faisant circuler un courant du fluide à refroidir, sous pression dans le conduit de circulation, en échange de chaleur indirect avec le fluide frigorigène, de part et d'autre de la paroi d'échange thermique, c'est-à-dire de la paroi dudit conduit, dont l'une des faces, dite chaude est au contact du fluide à refroidir, et dont l'autre face, dite froide est au contact du fluide frigorigène
  • et en s'opposant, au moyen du rotor avec ses racleurs, au dépôt sur la face chaude de la paroi d'échange thermique, de toute couche solide du fluide à refroidir.
Such a heat exchange device, with a scraped surface, makes it possible to exchange heat between, on the one hand the refrigerant, for example during vaporization, and on the other hand the fluid to be cooled, during partial freezing, and this:
  • by circulating a current of the fluid to be cooled, under pressure in the circulation duct, in exchange for indirect heat with the refrigerant, on either side of the heat exchange wall, that is to say of the wall of said duct, one of the so-called hot faces being in contact with the fluid to be cooled, and the other so-called cold face of which is in contact with the refrigerant
  • and by opposing, by means of the rotor with its scrapers, the deposition on the hot face of the heat exchange wall, of any solid layer of the fluid to be cooled.

Aujourd'hui, les échangeurs de chaleur à surface raclée constituent des dispositifs de structure et construction compliquées, et donc d'un coût non négligeable, en particulier si les racleurs sont montés sur le rotor de manière pivotante, chacun avec son propre moyen de rappel.Today, scraped surface heat exchangers constitute devices of complicated structure and construction, and therefore of a non-negligible cost, in particular if the scrapers are pivotally mounted on the rotor, each with its own return means. .

La présente invention a pour objet une alternative aux échangeurs de chaleur à surface raclée, beaucoup plus simple quant à sa construction et son fonctionnement.The subject of the present invention is an alternative to scraped surface heat exchangers, which is much simpler as regards its construction and operation.

Selon la présente invention, de manière générale, pour s'opposer au dépôt de toute couche solide sur la face chaude de la paroi d'échange thermique, on crée dans le courant du fluide à refroidir, circulant dans le conduit précité de circulation sous pression, et au contact de la face chaude de la paroi d'échange thermique, une couche limite turbulente, sous-refroidie en phase liquide, et en échange de chaleur direct avec le reste du courant du fluide à refroidir.According to the present invention, in general, to oppose the deposition of any solid layer on the hot face of the heat exchange wall, there is created in the current of the fluid to be cooled, circulating in the aforementioned pressure circulation conduit. , and in contact with the hot face of the heat exchange wall, a turbulent boundary layer, sub-cooled in the liquid phase, and in direct heat exchange with the rest of the current of the fluid to be cooled.

A cette fin, selon la revendication 1, les différents éléments antagonistes du dépôt de toute couche solide du fluide à refroidir, sur la face chaude de la paroi d'échange thermique, comprennent une multiplicité de filaments souples, dont une extrémité est solidaire du rotor, et dont l'autre extrémité libre est adjacente, c'est-à-dire au contact ou au voisinage mais à distance de la face chaude de la paroi d'échange thermique. En relation avec la rotation du rotor, les filaments souples sont agencés essentiellement pour agiter en phase liquide la couche limite du courant du fluide à refroidir, au contact de la face chaude de la paroi d'échange thermique, et en mélange avec le reste dudit fluide à refroidir.To this end, according to claim 1, the various antagonistic elements of the deposition of any solid layer of the fluid to be cooled, on the hot face of the heat exchange wall, comprise a multiplicity of flexible filaments, one end of which is integral with the rotor , and whose other free end is adjacent, that is to say in contact or in the vicinity but at a distance from the hot face of the heat exchange wall. In relation to the rotation of the rotor, the flexible filaments are arranged essentially to stir in the liquid phase the boundary layer of the current of the fluid to be cooled, in contact with the hot face of the heat exchange wall, and in admixture with the rest of said fluid to cool.

Par "sous-refroidie", on entend la caractéristique selon laquelle le fluide d'échange thermique est amené en phase liquide, c'est-à-dire sans congélation au moins partielle, à une température inférieure à son point de cristallisation.By "sub-cooled" is meant the characteristic that the heat exchange fluid is brought into the liquid phase, that is to say without at least partial freezing, at a temperature below its crystallization point.

Grâce à la présente invention, la formation d'une couche limite turbulente au contact de la face chaude de la paroi d'échange thermique a pour effet que la congélation s'effectue, non pas sur la face chaude de ladite paroi, mais au sein du fluide à refroidir en circulation, immédiatement au voisinage de ladite paroi, par échange de chaleur direct, c'est-à-dire par mélange de la couche limite turbulente et sous-refroidie, chassée de ladite face chaude, avec le reste du fluide à refroidir.Thanks to the present invention, the formation of a turbulent boundary layer in contact with the hot face of the heat exchange wall has the effect that freezing takes place, not on the hot face of said wall, but within of the fluid to be cooled in circulation, immediately in the vicinity of said wall, by direct heat exchange, that is to say by mixing the turbulent and sub-cooled boundary layer, expelled from said hot face, with the rest of the fluid to cool.

Comme indiqué précédemment, cette couche limite turbulente est obtenue, de manière non exclusive, par l'effet vibratile, d'agitation et/ou homogénéisation de l'extrémité libre des filaments souples, en rotation.As indicated above, this turbulent boundary layer is obtained, in a non-exclusive manner, by the vibratile effect, of agitation and / or homogenization of the free end of the flexible filaments, in rotation.

Les caractéristiques intrinsèques de ces filaments, dont la nature (en termes de souplesse et/ou rigidité, résistance à des basses températures, etc.), ainsi que l'agencement de ces différents filaments, dont densité par unité de surface, sont choisis, d'une part en fonction de la nature du fluide à refroidir, et d'autre part de la vitesse de rotation du rotor, de manière à obtenir l'obtention de la couche limite turbulente en phase liquide, caractérisant la présente invention.The intrinsic characteristics of these filaments, including the nature (in terms of flexibility and / or rigidity, resistance to low temperatures, etc.), as well as the arrangement of these different filaments, including density per unit area, are chosen, firstly according to the nature of the fluid to be cooled, and secondly the speed of rotation of the rotor, so as to obtain the turbulent boundary layer in phase liquid, characterizing the present invention.

La présente invention apporte encore les avantages déterminant suivants.The present invention also provides the following determining advantages.

Grâce à l'échange de chaleur direct entre la couche limite turbulente et le reste du fluide à refroidir, et/ou sous l'action de l'extrémité libre de la multiplicité des filaments, la congélation du fluide à refroidir s'effectue en obtenant des micro-cristaux, c'est-à-dire des cristaux de phase solide de dimensions bien inférieures à celles des cristaux obtenus avec un échangeur à surface raclée. L'obtention de tels micro-cristaux favorise l'homogénéité du fluide refroidi, c'est-à-dire du mélange des phases liquide et solide dudit fluide. Et ces micro-cristaux diminuent ou suppriment l'inertie à la fusion du fluide refroidi, obtenu sous forme diphasique, ce qui apparaît extrêmement favorable lorsque ledit fluide est utilisé ensuite dans des processus d'échange thermique, notamment de réfrigération, avec échange de la chaleur latente de fusion de la phase solide dudit fluide.Thanks to the direct heat exchange between the turbulent boundary layer and the rest of the fluid to be cooled, and / or under the action of the free end of the multiplicity of filaments, the freezing of the fluid to be cooled takes place by obtaining micro-crystals, that is to say solid phase crystals of dimensions much smaller than those of the crystals obtained with a scraped surface exchanger. Obtaining such micro-crystals promotes the homogeneity of the cooled fluid, that is to say of the mixture of the liquid and solid phases of said fluid. And these micro-crystals reduce or suppress the inertia when melting the cooled fluid, obtained in two-phase form, which appears extremely favorable when said fluid is then used in heat exchange processes, in particular refrigeration, with exchange of the latent heat of fusion of the solid phase of said fluid.

La présente invention permet également de diminuer ou limiter la dépense d'énergie nécessaire, notamment d'énergie mécanique, pour empêcher ou contrarier la formation de toute couche solide sur la face chaude de la paroi d'échange thermique.The present invention also makes it possible to reduce or limit the expenditure of energy required, in particular mechanical energy, to prevent or counteract the formation of any solid layer on the hot face of the heat exchange wall.

Et l'invention permet aussi d'augmenter le coefficient d'échange thermique du fluide en cours de refroidissement par rapport à la paroi d'échange thermique.And the invention also makes it possible to increase the heat exchange coefficient of the fluid during cooling with respect to the heat exchange wall.

Selon la présente invention, de manière préférée, mais non exclusivement, les modalités d'exécution suivantes peuvent être retenues :

  • lesdits éléments antagonistes sont séparés les uns des autres, en formant une pluralité d'organes filamentaires, notamment disposés axialement, et distribués selon l'axe et autour du rotor ; ou lesdits filaments constituent ensemble une hélice, continue ou discontinue, autour de l'axe du rotor ;
  • le moyen d'entraînement du rotor consiste en un moteur monté à l'extérieur du conduit de circulation, et couplé au rotor de ce dernier ; ou il n'existe pas de moteur extérieur, et les moyens d'entraînement du rotor sont constitués par tout système ou agencement auto-moteur, entraînant ledit rotor sous l'effet moteur du fluide à refroidir passant dans le conduit de circulation ; ce système ou agencement auto-moteur peut d'ailleurs être appliqué à tout dispositif de refroidissement, tel que défini généralement dans le préambule de la présente description, conforme ou non à la présente invention
  • les conduits de circulation peuvent être disposés en batterie, et à cette fin, le dispositif selon l'invention comprend une pluralité de conduits de circulation du fluide à refroidir, disposés en parallèle, et une enveloppe commune ménageant avec lesdits conduits une seule et même enceinte de passage du fluide frigorigène, un distributeur du fluide à refroidir dans les différents conduits de circulation, et un collecteur du fluide refroidi évacué des différents conduits de circulation ; dans ce cas, on fait circuler une pluralité de courants du fluide à refroidir, en échange de chaleur indirect avec le fluide frigorigène.
According to the present invention, preferably, but not exclusively, the following methods of execution can be retained:
  • said opposing elements are separated from each other, forming a plurality of filamentary members, in particular arranged axially, and distributed along the axis and around the rotor; or said filaments together constitute a helix, continuous or discontinuous, around the axis of the rotor;
  • the rotor drive means consists of a motor mounted outside the circulation duct, and coupled to the rotor of the latter; or there is no external motor, and the rotor drive means are constituted by any self-powered system or arrangement, driving said rotor under the motor effect of the fluid to be cooled passing through the circulation duct; this self-driving system or arrangement can moreover be applied to any cooling device, as generally defined in the preamble to this description, whether or not in accordance with the present invention
  • the circulation conduits can be arranged in a battery, and for this purpose, the device according to the invention comprises a plurality of conduits for circulation of the fluid to be cooled, arranged in parallel, and a common envelope providing with said conduits a single and same enclosure for the passage of the refrigerant, a distributor of the fluid to be cooled in the various circulation conduits, and a collector of the cooled fluid discharged from the various circulation conduits; in this case, a plurality of currents of the fluid to be cooled are circulated in exchange for indirect heat with the refrigerant.

La présente invention est maintenant décrite par référence au dessin annexé, dans lequel :

  • la figure 1 représente, en coupe verticale, un dispositif d'échange de chaleur selon un mode d'exécution de l'invention ;
  • la figure 2 représente, toujours en coupe transversale et verticale, un dispositif d'échange de chaleur selon un deuxième mode d'exécution de l'invention ;
  • la figure 3 représente, en coupe longitudinale et verticale, un dispositif d'échange de chaleur selon un troisième mode d'exécution de l'invention ;
  • la figure 4 représente, en coupe verticale, un dispositif d'échange de chaleur selon un quatrième mode d'exécution de l'invention ;
  • la figure 5 représente le dispositif selon figure 4, en coupe selon la ligne V.V de cette dernière ;
  • la figure 6 représente une vue en coupe d'un conduit de circulation appartenant au dispositif selon figures 4 et 5, selon la ligne de coupe VI.VI de la figure 4 ;
  • la figure 7 représente un dispositif d'échange de chaleur selon un cinquième mode d'exécution de l'invention ;
  • la figure 8 représente, en coupe axiale, un dispositif d'échange de chaleur selon un sixième mode d'exécution de l'invention ;
  • la figure 9 représente, un dispositif d'échange de chaleur selon un septième mode d'exécution de l'invention, toujours en coupe axiale ;
  • la figure 10 représente, en coupe axiale, un dispositif selon un huitième mode d'exécution de l'invention ;
  • la figure 11 représente une vue de dessus du rotor appartenant au dispositif selon figure 10 ;
  • les figures 12 à 14 explicitent, dans des plans transversaux respectivement superposés, la relation angulaire existant entre le tube fixe du rotor d'un dispositif selon figure 10, et respectivement trois paires de bras radiaux superposés, mais décalés angulairement les uns par rapport aux autres.
The present invention is now described with reference to the accompanying drawing, in which:
  • Figure 1 shows, in vertical section, a heat exchange device according to an embodiment of the invention;
  • Figure 2 shows, still in transverse and vertical section, a heat exchange device according to a second embodiment of the invention;
  • Figure 3 shows, in longitudinal and vertical section, a heat exchange device according to a third embodiment of the invention;
  • Figure 4 shows, in vertical section, a heat exchange device according to a fourth embodiment of the invention;
  • Figure 5 shows the device according to Figure 4, in section along the line VV of the latter;
  • 6 shows a sectional view of a circulation duct belonging to the device according to Figures 4 and 5, along the section line VI.VI of Figure 4;
  • FIG. 7 represents a heat exchange device according to a fifth embodiment of the invention;
  • FIG. 8 represents, in axial section, a heat exchange device according to a sixth embodiment of the invention;
  • FIG. 9 represents a heat exchange device according to a seventh embodiment of the invention, still in axial section;
  • FIG. 10 represents, in axial section, a device according to an eighth embodiment of the invention;
  • Figure 11 shows a top view of the rotor belonging to the device according to Figure 10;
  • FIGS. 12 to 14 explain, in respectively superimposed transverse planes, the angular relationship existing between the fixed tube of the rotor of a device according to FIG. 10, and respectively three pairs of radial arms superimposed, but angularly offset with respect to each other .

Conformément à la figure 1, le dispositif selon l'invention permet d'échanger indirectement de la chaleur entre, d'une part, un fluide frigorigène 1, par exemple de l'ammoniac en cours de vaporisation, et d'autre part, un fluide 2 à refroidir, par exemple de l'eau dont on a abaissé le point de congélation (par exemple eau glycolée, alcoolisée ou salée), en cours de congélation ou cristallisation partielle. Ce dispositif comprend :

  • un conduit 3 droit, disposé verticalement, pour la circulation sous pression du fluide 2 à refroidir, d'une entrée 4 située au bas du conduit 3, à deux sorties 5 opposées, situées au haut du conduit 3 ; c'est la paroi métallique 6 du conduit 3 qui constitue la surface d'échange thermique entre le fluide frigorigène 1, du côté de sa face dite froide 6b, et le fluide à refroidir 2, du côté de sa face dite chaude 6a ;
  • une enveloppe 7, rapportée sur le conduit 3, ménageant avec et autour de ce dernier, une enceinte ou moyen de passage du fluide frigorigène 1, à contre-courant du fluide 2 à refroidir, d'une entrée haute 9 à une sortie basse 10 ;
  • un moyen mécanique 11 antagoniste du dépôt, sur la face chaude 6a de la paroi 6 d'échange thermique, de toute couche solide du fluide à refroidir.
In accordance with FIG. 1, the device according to the invention makes it possible to exchange heat indirectly between, on the one hand, a refrigerant 1, for example of ammonia in the course of vaporization, and on the other hand, a fluid 2 to be cooled, for example water whose freezing point has been lowered (for example glycol, alcoholic or salty water), in the course of freezing or partial crystallization. This device includes:
  • a straight duct 3, arranged vertically, for the pressurized circulation of the fluid 2 to be cooled, from an inlet 4 located at the bottom of the duct 3, with two opposite outlets 5, located at the top of the duct 3; it is the metal wall 6 of the conduit 3 which constitutes the heat exchange surface between the refrigerant 1, on the side of its so-called cold face 6b, and the fluid to be cooled 2, on the side of its so-called hot face 6a;
  • a casing 7, attached to the duct 3, providing with and around the latter, an enclosure or means for the passage of the refrigerant 1, counter-current to the fluid 2 to be cooled, from a high inlet 9 to a low outlet 10 ;
  • a mechanical means 11 antagonistic of the deposition, on the hot face 6a of the wall 6 of heat exchange, of any solid layer of the fluid to be cooled.

Conformément à l'invention, ce moyen mécanique 11 comprend :

  • un rotor 12 monté au sein du conduit 3 ;
  • une pluralité d'organes filamentaires 15, disposés axialement, en étant distribués selon l'axe et autour du rotor 12, et comportant chacune une multiplicité de filaments 14 radiaux et souples, formant des éléments antagonistes 13 du dépôt de toute couche solide sur la face chaude 6a de la paroi du conduit 3 ; ces filaments 14 peuvent être obtenus par exemple en toute matière synthétique, relativement souple et rigide à la fois, par exemple à partir de fils de polyamide ; chaque filament 14 a une extrémité solidaire du rotor, et l'autre extrémité libre adjacente à la paroi du conduit de circulation, c'est-à-dire au contact ou au voisinage immédiat de la face chaude 6a du conduit 6 ;
  • et un moyen 40 d'entraînement du rotor 12 équipé des organes filamentaires 15.
According to the invention, this mechanical means 11 comprises:
  • a rotor 12 mounted within the conduit 3;
  • a plurality of filamentary members 15, arranged axially, being distributed along the axis and around the rotor 12, and each comprising a multiplicity of radial and flexible filaments 14, forming antagonistic elements 13 from the deposition of any solid layer on the face hot 6a of the wall of the conduit 3; these filaments 14 can be obtained for example from any synthetic material, relatively flexible and rigid at the same time, for example from polyamide yarns; each filament 14 has one end integral with the rotor, and the other free end adjacent to the wall of the duct circulation, that is to say in contact with or in the immediate vicinity of the hot face 6a of the duct 6;
  • and a means 40 for driving the rotor 12 equipped with the filamentary members 15.

Comme représenté à la figure 1, les organes filamentaires 15 sont séparés les uns des autres, en étant à la fois, superposés par groupes de deux, et décalés angulairement par rapport à l'axe du rotor, par exemple selon un angle de 90° ou 60°, d'un groupe à l'autre, et ceci d'une extrémité à l'autre du conduit 3 de circulation. Et deux organes filamentaires 15 d'un même groupe sont disposés de manière opposée dans un seul et même plan diamétral.As shown in Figure 1, the filamentary members 15 are separated from each other, being at the same time, superimposed in groups of two, and offset angularly with respect to the axis of the rotor, for example at an angle of 90 ° or 60 °, from one group to another, and this from one end to the other of the circulation duct 3. And two filamentary members 15 of the same group are arranged opposite in a single and same diametrical plane.

Le moyen d'entraînement 40 du rotor consiste en un moteur 17 monté à l'extérieur du conduit de circulation 3, et couplé au rotor 12 par tout moyen approprié, par exemple un moto-réducteur.The rotor drive means 40 consists of a motor 17 mounted outside of the circulation duct 3, and coupled to the rotor 12 by any suitable means, for example a gear motor.

Avec l'échangeur précédemment décrit par référence à la figure 1, on échange de la chaleur entre, d'une part le fluide frigorigène 1 en cours de vaporisation, dans l'enceinte ménagée entre l'enveloppe 7 et le conduit 3, et d'autre part le fluide à refroidir, circulant sous pression dans le conduit 3, en cours de congélation partielle, à l'exclusion de toute prise en masse dudit fluide, notamment par dépôt d'une couche solide sur la face chaude 6a de la paroi métallique 6. A cette fin :

  • on fait circuler, sous pression, un courant du fluide 2 à refroidir, dans le conduit 3, en échange de chaleur indirect avec le fluide frigorigène 1, lesdits fluides étant respectivement de part et d'autre de la paroi 6 d'échange thermique. La face chaude 6a de la paroi 6 est au contact du fluide à refroidir, tandis que l'autre face froide 6b de la même paroi 6 est au contact du fluide frigorigène 1 ;
  • grâce au moyen mécanique 11, constitué comme décrit précédemment par le rotor 12 et sa pluralité d'organes filamentaires 15, et au moyen 40 d'entraînement, on crée dans le courant du fluide 2 à refroidir, et au contact de la face chaude 6a de la paroi 6 du conduit 3, une couche limite turbulente, sous-refroidie en phase liquide, et en échange de chaleur direct avec le reste du courant du fluide à refroidir.
With the exchanger previously described with reference to FIG. 1, heat is exchanged between, on the one hand the refrigerant 1 during vaporization, in the enclosure formed between the casing 7 and the conduit 3, and d on the other hand the fluid to be cooled, circulating under pressure in the conduit 3, during partial freezing, to the exclusion of any solidification of said fluid, in particular by depositing a solid layer on the hot face 6a of the wall metallic 6. To this end:
  • a current of the fluid 2 to be cooled is circulated under pressure, in the conduit 3, in exchange for indirect heat with the refrigerant 1, said fluids being respectively on either side of the wall 6 of heat exchange. The hot face 6a of the wall 6 is in contact with the fluid to be cooled, while the other cold face 6b of the same wall 6 is in contact with the refrigerant 1;
  • by mechanical means 11, constituted as described above by the rotor 12 and its plurality of members filamentary 15, and by means of drive 40, a turbulent boundary layer, sub-cooled in liquid phase, is created in the stream of fluid 2 to be cooled, and in contact with the hot face 6a of the wall 6 of the conduit 3 and in exchange for direct heat with the rest of the stream of fluid to be cooled.

Ainsi, non seulement on s'oppose au dépôt sur la face chaude 6a de la paroi 6, de toute couche solide du fluide à refroidir, mais aussi on favorise le mélange direct et homogène de ladite couche avec le reste du courant du fluide à refroidir, en formant des micro-cristaux de phase solide, qui sont entraînés et évacués dans le courant, sans possibilité d'adhésion ou dépôt sur la face chaude 6a de la paroi 6 précitée.Thus, not only is it opposed to the deposition on the hot face 6a of the wall 6, of any solid layer of the fluid to be cooled, but also it promotes direct and homogeneous mixing of said layer with the rest of the current of the fluid to be cooled , by forming micro-crystals of solid phase, which are entrained and discharged in the current, without possibility of adhesion or deposit on the hot face 6a of the above-mentioned wall 6.

Le mode d'exécution représenté à la figure 2 diffère de celui précédemment décrit, par le mode d'entraînement du rotor 12.The embodiment shown in FIG. 2 differs from that previously described, by the mode of driving the rotor 12.

Selon la figure 2, on entraîne le rotor, avec un moyen 18 agissant sous l'effet moteur du fluide 2 à refroidir, passant dans le conduit de circulation 3.According to FIG. 2, the rotor is driven, with a means 18 acting under the driving effect of the fluid 2 to be cooled, passing through the circulation duct 3.

Conformément à la figure 2, ce moyen 18 est obtenu par la combinaison des dispositions suivantes :

  • le rotor 12 est creux, et aménagé pour une circulation axiale du fluide 2 à refroidir, préalable à sa circulation dans le conduit 3, d'une entrée axiale 21, du côté de l'entrée 4 dans le conduit de circulation, à une sortie opposée 22 d'introduction du fluide, par retour dans le conduit 3 proprement dit, entre ce dernier et le rotor 12 ;
  • un moyen moteur 23, sous l'effet du fluide 2 circulant à l'intérieur du rotor 12, est monté dans ce dernier et calé en rotation sur ledit rotor ; selon ce mode d'exécution, ce moyen moteur 23 consiste en une hélice 24 coaxiale au rotor 12, comportant un noyau axial 25 et une aile 26 hélicoïdale reliant ce dernier et la paroi 27 du rotor, en ménageant un canal 28 hélicoïdal de circulation du fluide 2 à refroidir.
In accordance with FIG. 2, this means 18 is obtained by the combination of the following arrangements:
  • the rotor 12 is hollow, and arranged for an axial circulation of the fluid 2 to be cooled, prior to its circulation in the duct 3, from an axial inlet 21, on the side of the inlet 4 in the circulation duct, to an outlet opposite 22 for introducing the fluid, by return to the conduit 3 proper, between the latter and the rotor 12;
  • a motor means 23, under the effect of the fluid 2 circulating inside the rotor 12, is mounted in the latter and locked in rotation on said rotor; according to this embodiment, this drive means 23 consists of a propeller 24 coaxial with the rotor 12, comprising an axial core 25 and a helical wing 26 connecting the latter and the wall 27 of the rotor, providing a helical channel 28 for circulation of the fluid 2 to be cooled.

Le mode d'exécution de la figure 3 diffère de ceux décrits par référence aux figures 1 et 2, par les caractéristiques techniques suivantes :

  • les éléments antagonistes 13, ou multiplicité de filaments 14 radiaux et souples, constituent ensemble une hélice 16 continue, autour de l'axe 12, ce qui permet au surplus de transporter le fluide 2 à refroidir, à la manière d'une vis d'Archimède ;
  • l'entraînement du rotor 12, sous l'effet moteur du fluide 2 à refroidir passant dans le conduit de circulation 3, est obtenu d'une autre manière ; plus précisément, une pluralité de pales 19 sont montées sur le rotor 12, chacune s'étendant avec au moins une direction radiale, et présentant par rapport au fluide 2 en circulation, une surface antérieure opposant localement une résistance audit fluide ; comme le montre la figure 3, les pales sont distribuées et disposées dans l'interstice 20, délimité par l'hélice radiale 16.
The embodiment of FIG. 3 differs from those described with reference to FIGS. 1 and 2, by the following technical characteristics:
  • the opposing elements 13, or multiplicity of radial and flexible filaments 14, together constitute a continuous helix 16, around the axis 12, which allows the surplus to transport the fluid 2 to be cooled, in the manner of a screw Archimedes;
  • the drive of the rotor 12, under the driving effect of the fluid 2 to be cooled passing through the circulation duct 3, is obtained in another way; more specifically, a plurality of blades 19 are mounted on the rotor 12, each extending with at least one radial direction, and having, with respect to the fluid 2 in circulation, a front surface locally opposing a resistance to said fluid; as shown in FIG. 3, the blades are distributed and arranged in the gap 20, delimited by the radial propeller 16.

Le mode d'exécution décrit par référence aux figures 4 à 6 diffère de ceux décrits précédemment, par le fait que les conduits 3 de circulation du fluide à refroidir sont disposés en batterie. A cette fin, il existe donc une pluralité de conduits 3, disposés en parallèle, et une seule et même enveloppe 7 commune, cylindrique par exemple, ménageant avec les conduits 3, une seule et même enceinte 8 de passage du fluide frigorigène. En haut et en bas du dispositif, se situent respectivement un distributeur 29 du fluide 2 dans les différents conduits 3, et un collecteur 30 du fluide 2 refroidi évacué des différents conduits 3, ce distributeur et ce collecteur étant séparés et étanches par rapport à l'enceinte 8 de passage du fluide frigorigène.The embodiment described with reference to FIGS. 4 to 6 differs from those described above, in that the conduits 3 for circulation of the fluid to be cooled are arranged in a battery. To this end, there is therefore a plurality of conduits 3, arranged in parallel, and one and the same common envelope 7, cylindrical for example, providing with the conduits 3, one and the same enclosure 8 for the passage of the refrigerant. At the top and at the bottom of the device, there is respectively a distributor 29 of the fluid 2 in the various conduits 3, and a collector 30 of the cooled fluid 2 discharged from the various conduits 3, this distributor and this collector being separated and sealed with respect to the 'enclosure 8 for the passage of the refrigerant.

Par ailleurs, un seul et même moteur 17 est couplé par un moyen de transmission 31 aux différents rotors 12 des différents conduits 3 de circulation.Furthermore, one and the same motor 17 is coupled by a transmission means 31 to the various rotors 12 of the various circulation conduits 3.

Le mode d'exécution représenté à la figure 7 comporte une batterie de conduits 3, comme précédemment décrit par référence aux figures 4 à 6. Mais dans ce cas, et comme déjà décrit par référence à la figure 2, le moteur 17 a été supprimé au profit de moyens moteur 23 intégrés dans les rotors 12, et agissant sous le seul effet de la circulation du fluide 2. A cette fin, le distributeur 29 du fluide à refroidir communique uniquement avec les différentes entrées 21 axiales des rotors creux 12 des différents conduits 3 de circulation respectivement.The embodiment shown in Figure 7 includes a battery of conduits 3, as previously described with reference to Figures 4 to 6. But in this case, and as already described with reference to Figure 2, the motor 17 has been deleted in favor of motor means 23 integrated in the rotors 12, and acting under the sole effect of the circulation of the fluid 2. To this end, the distributor 29 of the fluid to be cooled communicates only with the different axial inlets 21 of the hollow rotors 12 of the different traffic conduits 3 respectively.

Le dispositif d'échange représenté selon figure 8 diffère de ceux décrits précédemment, par les caractéristiques techniques suivantes :

  • 1) Une pluralité de capacités 41 de passage du fluide frigorigène sont disposées en parallèle, coaxialement à l'axe du rotor 12 et de manière étagée dans le conduit 3 de circulation du fluide à refroidir ; chaque capacité 41 comprend deux cloisons 42 et 43 d'extension radiale, formant chacune un élément de la paroi 6 d'échange thermique entre le fluide à refroidir et le fluide frigorigène ; en pratique, et comme représenté à la figure 8, chaque capacité 41 consiste en un élément circulaire, creux et aplati, évidé en son centre, ayant généralement la forme d'un disque, et dont les deux faces planes 42 et 43 constituent respectivement les deux cloisons d'échange thermique précitées.
  • 2) Un distributeur 44 du fluide frigorigène, en relation avec l'entrée 9 pour ledit fluide, et un collecteur 45 du même fluide, en relation avec la sortie 10 pour ce dernier, sont disposés à l'extérieur du conduit 3 de circulation, et communiquent avec la pluralité des capacités 41 de passage identifiées précédemment.
  • 3) Une pluralité de bras 46 et 47, chacun d'extension radiale, sont solidaires du rotor 12, et disposés chacun entre deux capacités 41 de passage du fluide frigorigène, ou entre une dite capacité et une extrémité du conduit 3 de circulation.
  • 4) Une pluralité d'organes filamentaires 15, tels que définis précédemment, sont montés sur la pluralité des bras 46 et 47, en étant orientés chacun radialement ; en conséquence, les différents filaments souples 14 des organes 15 sont dirigés individuellement selon une direction axiale, avec leurs extrémités libres adjacentes à la face chaude 6a des différentes cloisons radiales 42 et 43 d'échange thermique, identifiées précédemment.
The exchange device represented according to FIG. 8 differs from those described above, by the following technical characteristics:
  • 1) A plurality of capacities 41 for the passage of the refrigerant are arranged in parallel, coaxial with the axis of the rotor 12 and in a stepped manner in the conduit 3 for circulation of the fluid to be cooled; each capacity 41 comprises two partitions 42 and 43 of radial extension, each forming an element of the wall 6 of heat exchange between the fluid to be cooled and the refrigerant; in practice, and as shown in FIG. 8, each capacity 41 consists of a circular, hollow and flattened element, hollowed out at its center, generally having the shape of a disc, and the two flat faces 42 and 43 of which constitute respectively two aforementioned heat exchange partitions.
  • 2) A distributor 44 of the refrigerant, in relation to the inlet 9 for said fluid, and a manifold 45 of the same fluid, in relation to the outlet 10 for the latter, are arranged outside the conduit 3 of circulation, and communicate with the plurality of passage capacities 41 identified previously.
  • 3) A plurality of arms 46 and 47, each of radial extension, are integral with the rotor 12, and each disposed between two capacities 41 for the passage of the refrigerant, or between a said capacity and one end of the circulation conduit 3.
  • 4) A plurality of filamentary members 15, as defined above, are mounted on the plurality of arms 46 and 47, each being oriented radially; consequently, the various flexible filaments 14 of the members 15 are directed individually in an axial direction, with their free ends adjacent to the hot face 6a of the various radial partitions 42 and 43 of heat exchange, identified previously.

S'agissant des organes filamentaires 15, ceux-ci sont superposés par paires, en étant éventuellement décalés angulairement d'une paire à l'autre, comme représenté plus particulièrement aux figures 10 à 14.As regards the filamentary members 15, these are superimposed in pairs, possibly being angularly offset from one pair to the other, as shown more particularly in FIGS. 10 to 14.

S'agissant des deux organes filamentaires 15 appartenant à une même paire, ceux-ci sont disposés dans un même plan diamétral. Et, entre deux capacités 41, un même bras 46 ou 47 d'extension radiale porte deux organes filamentaires 15 opposés l'un par rapport à l'autre, en relation avec les deux faces chaudes 6a de deux cloisons 42 et 43 d'échange thermique, appartenant respectivement aux deux capacités 41 précitées, c'est-à-dire en vis-à-vis.As regards the two filamentary members 15 belonging to the same pair, these are arranged in the same diametral plane. And, between two capacities 41, the same arm 46 or 47 of radial extension carries two filamentary members 15 opposite one with respect to the other, in relation to the two hot faces 6a of two exchange partitions 42 and 43 thermal, belonging respectively to the two abovementioned capacities 41, that is to say facing one another.

Toujours selon la figure 8, le fluide à refroidir 2 est introduit dans le dispositif d'échange, grâce aux dispositions suivantes :

  • le rotor 12 est creux, avec des passages 48 vers l'intérieur du conduit 3, ménagés au travers de sa paroi, et étagés entre les différentes capacités 41 de passage du fluide frigorigène, ceci pour permettre la circulation du fluide à refroidir, d'une extrémité ouverte 49 à une extrémité fermée 50 du rotor 12 ;
  • et une boîte 51 d'introduction du fluide à refroidir est seulement en relation avec l'extrémité ouverte 49 du rotor creux 12, et l'entrée 4 pour le fluide à refroidir 2.
Still according to FIG. 8, the fluid to be cooled 2 is introduced into the exchange device, thanks to the following arrangements:
  • the rotor 12 is hollow, with passages 48 towards the inside of the duct 3, formed through its wall, and stepped between the various capacities 41 for the passage of the refrigerant, this to allow the circulation of the fluid to be cooled, from an open end 49 to a closed end 50 of the rotor 12;
  • and a box 51 for introducing the fluid to be cooled is only in relation to the open end 49 of the hollow rotor 12, and the inlet 4 for the fluid to be cooled 2.

Par ailleurs, l'évacuation du fluide refroidi est obtenue par les dispositions suivantes :

  • une pluralité d'orifices 52 sont ménagés dans la paroi 3, en étant étagés respectivement en relation avec les différents interstices entre les capacités 41 de passage du fluide frigorigène ;
  • et un carter 53 d'évacuation du fluide refroidi est en relation, d'une part avec tous les orifices 52 du conduit 3, et d'autre part avec la sortie 5 du fluide refroidi.
Furthermore, the evacuation of the cooled fluid is obtained by the following arrangements:
  • a plurality of orifices 52 are formed in the wall 3, being staged respectively in relation to the different interstices between the capacities 41 for the passage of the refrigerant;
  • and a casing 53 for evacuating the cooled fluid is in relation, on the one hand with all the orifices 52 of the conduit 3, and on the other hand with the outlet 5 of the cooled fluid.

Le mode d'exécution selon figure 9 diffère de celui décrit selon figure 8, essentiellement par la présence d'aubes 54 d'entraînement du rotor 12, sous l'effet moteur du fluide 2 à refroidir en circulation, distribuées radialement dans la boîte 51 d'introduction dudit fluide.The embodiment according to FIG. 9 differs from that described according to FIG. 8, essentially by the presence of vanes 54 for driving the rotor 12, under the driving effect of the fluid 2 to be cooled in circulation, distributed radially in the box 51 of introduction of said fluid.

Pour terminer, le dernier mode d'exécution de l'invention, selon figures 10 à 14 diffère de ceux décrits par référence aux figures 8 et 9, par les différentes caractéristiques suivantes.Finally, the last embodiment of the invention, according to Figures 10 to 14 differs from those described with reference to Figures 8 and 9, by the following different characteristics.

Tout d'abord, des moyens auto-moteur d'entraînement du rotor 12 sont obtenus par la combinaison des dispositions suivantes :

  • la disposition sur le conduit 3 d'un tube fixe 55, coaxial au rotor creux 12, comportant une extrémité 56 ouverte pour l'entrée 4 du fluide à refroidir, des passages 55a et 55b (cf figures 12 à 14) d'évacuation du fluide à refroidir vers le rotor 12, et une autre extrémité fermée 57 ; par construction, le rotor 12 est susceptible de tourner de manière relativement étanche par rapport au tube fixe 55 ;
  • les différents bras 46 et 47 radiaux creux, communiquent avec l'intérieur du rotor 12 et les passages précités 55a et 55b d'évacuation du tube fixe 55, et comportent à leur extrémité libre un moyen 58, tel qu'une buse d'éjection du fluide à refroidir dans le conduit 3. Ensuite, les bras 46 et 47 radiaux, sont alignés diamétralement par paires disposées de manière étagée selon l'axe du conduit 3 (cf les paires A, B, C représentées aux figures 11 à 14). Pour les deux bras 46 et 47 d'une même paire, par exemple A, les moyens 58 d'éjection sont opposés, de manière à permettre une rotation du rotor 12, sous l'effet des jets éjectés par les moyens 58 d'une même paire de bras.
First of all, self-motor means for driving the rotor 12 are obtained by the combination of the following arrangements:
  • the provision on the conduit 3 of a fixed tube 55, coaxial with the hollow rotor 12, comprising an open end 56 for the inlet 4 of the fluid to be cooled, passages 55a and 55b (cf. FIGS. 12 to 14) for discharging the fluid to be cooled towards the rotor 12, and another closed end 57; by construction, the rotor 12 is capable of rotating relatively tightly relative to the fixed tube 55;
  • the various hollow radial arms 46 and 47 communicate with the interior of the rotor 12 and the aforementioned passages 55a and 55b for evacuating the fixed tube 55, and comprise at their free end a means 58, such as an ejection nozzle of the fluid to be cooled in the duct 3. Next, the radial arms 46 and 47 are aligned diametrically in pairs arranged in a staggered fashion along the axis of the duct 3 (cf. the pairs A, B, C shown in FIGS. 11 to 14) . For the two arms 46 and 47 of the same pair, for example A, the ejection means 58 are opposite, so as to allow rotation of the rotor 12, under the effect of the jets ejected by the means 58 of a same pair of arms.

Finalement, comme mieux représenté aux figures 12 à 14, les paires de bras radiaux 46 et 47, par exemple A à C, sont décalées angulairement les unes par rapport aux autres, selon un angle prédéterminé, par exemple 60°, et ceci selon le même sens de rotation, horaire ou anti-horaire. En correspondance, le tube fixe 55 présente deux perforations 55a et 55b, allongées axialement, et opposées. La dimension angulaire de chaque perforation 55a ou 55b est identique à l'angle prédéterminé de décalage d'une paire à l'autre, par exemple 60°. Une telle disposition permet de ne pas éjecter le fluide à refroidir par tous les bras radiaux 46 et 47 du rotor 12, mais successivement par groupes de paires A, B et C respectivement. Autrement dit, les paires A, B et C éjectent successivement à leur tour le fluide à refroidir ; et pendant l'éjection dudit fluide par une paire B par exemple, les paires C et A sont inactives.Finally, as best shown in FIGS. 12 to 14, the pairs of radial arms 46 and 47, for example A to C, are angularly offset with respect to each other, at a predetermined angle, for example 60 °, and this according to the same direction of rotation, clockwise or counterclockwise. In correspondence, the fixed tube 55 has two perforations 55a and 55b, axially elongated, and opposite. The angular dimension of each perforation 55a or 55b is identical to the predetermined angle of offset from one pair to the other, for example 60 °. Such an arrangement makes it possible not to eject the fluid to be cooled by all the radial arms 46 and 47 of the rotor 12, but successively in groups of pairs A, B and C respectively. In other words, the pairs A, B and C successively eject in turn the fluid to be cooled; and during the ejection of said fluid by a pair B for example, the pairs C and A are inactive.

Claims (12)

  1. Device for heat exchange between, on the one hand, a refrigerant (1), for example in the course of vaporization, and, on the other hand, a fluid (2) to be cooled, in the course of partial freezing, the said device comprising:
    - at least one conduit (3) for pressurized circulation of the fluid (2) to be cooled, from an inlet (4, 22) to an opposed outlet (5) for the said fluid, comprising a heat exchange wall (6), one of the faces of which, called the warm face (6a), is in contact with the fluid (2) to be cooled;
    - a means (8) for passing the refrigerant, in contact with the other face, called the cold face (6b), of the heat exchange wall (6),
    - a mechanical means (11) resisting deposition, on the warm face (6a) of the heat exchange wall (6), of any solid layer of the fluid to be cooled, which includes a rotor (12) mounted within the conduit (3), elements resisting the said deposition, each in contact with or in the vicinity of the warm face (6a) of the heat exchange wall (6), these being distributed along the axis of and around the rotor (12), as well as a means (40) for driving the latter,
    characterized in that the said resisting elements (13) comprise a multiplicity of flexible filaments (14), one end of which is fastened to the rotor (12), the other, free end of which is adjacent to the warm face (6a) of the heat exchange wall (6), and arranged in connection with the rotation of the rotor, essentially in order to agitate, in liquid phase, the boundary layer of the stream of the fluid (2) to be cooled, in contact with the warm face (6a) of the heat exchange wall (6).
  2. Device according to Claim 1, characterized in that the circulation conduit (3) constitutes the heat exchange wall (6), a shell (7) makes, with and around the conduit (3), a chamber (8) for passage of the refrigerant, especially with counterflow of the fluid to be cooled, and the flexible filaments (14) exhibit individually at least one radial extension.
  3. Device according to Claim 1, characterized in that the filaments (14) are separated from each other, forming a plurality of filamentary members (15).
  4. Device according to Claim 1, characterized in that, from one end of the circulation conduit (3) to the other, the filamentary members (15) are superimposed in groups of two, being angularly offset with respect to the axis of the rotor, from one group to the other.
  5. Device according to Claim 4, characterized in that, for each group, the two filamentary members (15) are arranged in the same diametral plane.
  6. Device according to Claim 4, characterized in that a group of filamentary members (15) is angularly offset by 90° or 60° with respect to the next one.
  7. Device according to Claim 2, characterized in that the filaments (14) together constitute a continuous or discontinuous helix (16) about the axis of the rotor (12).
  8. Device according to Claim 1, characterized in that it includes means (18) for driving the rotor (12), acting under the motory effect of the fluid (2) to be cooled passing through the circulation conduit (3).
  9. Device according to Claim 2, characterized in that it comprises a plurality of conduits (3) for circulation of the fluid to be cooled, these being arranged in parallel, and a common shell (7) making, with the said conduits, one and the same chamber (8) for passage of the refrigerant, a distributor (29) for distributing the fluid to be cooled into the various circulation conduits (3), and a manifold (30) for the cooled fluid discharged from the various circulation conduits.
  10. Device according to Claim 1, characterized in that, firstly, a plurality of volumes (41) for passage of the refrigerant are arranged in parallel, coaxial with the axis of the rotor (12) and in a staged manner in the conduit (3) for circulation of the fluid to be cooled, each volume comprising at least one radially extending partition (42, 43) forming an element of the heat exchange wall (6), secondly, a distributor (44) for the refrigerant, in connection with the inlet (9) for the said fluid, and a manifold (45) for the said refrigerant, in connection with the outlet (10) for the said fluid, these being arranged especially on the outside of the circulation conduit (3), communicate with the plurality of the volumes (41) for passage of the refrigerant, and, thirdly, the flexible filaments (14) exhibit individually at least one axial extension, with their free end adjacent to the warm face (6a) of a radial partition of a volume (41).
  11. Device according to Claim 10, characterized in that each volume (41) for passage of the refrigerant consists of a circular, hollow and flattened element, hollowed at its centre, generally having the shape of a disc, the two plane faces (42, 43) of which respectively constitute two heat exchange partitions.
  12. Device according to Claim 10, characterized in that it includes a means for introducing the fluid to be cooled, comprising the following arrangements:
    - a hollow rotor (12), with passages (48) towards the inside of the conduit (3), these being made through its wall and staged between the volumes (41) for passage of the refrigerant, for the circulation of the fluid to be cooled, from an open end (49) to a closed end (50) of the said rotor;
    - a box (51) for introducing the fluid to be cooled, in connection with the open end (49) of the hollow rotor (12).
EP94420241A 1993-09-08 1994-09-08 Device for heat exchange with a fluid which is partially freezing Expired - Lifetime EP0641980B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9310887 1993-09-08
FR9310887A FR2709817B1 (en) 1993-09-08 1993-09-08 Heat exchange device incorporating means for removing a solid phase.

Publications (2)

Publication Number Publication Date
EP0641980A1 EP0641980A1 (en) 1995-03-08
EP0641980B1 true EP0641980B1 (en) 1996-07-17

Family

ID=9450814

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94420241A Expired - Lifetime EP0641980B1 (en) 1993-09-08 1994-09-08 Device for heat exchange with a fluid which is partially freezing

Country Status (8)

Country Link
US (1) US5488836A (en)
EP (1) EP0641980B1 (en)
AT (1) ATE140528T1 (en)
DE (1) DE69400307T2 (en)
DK (1) DK0641980T3 (en)
ES (1) ES2091111T3 (en)
FR (1) FR2709817B1 (en)
GR (1) GR3021128T3 (en)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
CN113503755A (en) * 2021-09-09 2021-10-15 北京福典工程技术有限责任公司 Method for enhancing mass transfer heat exchange and heat exchange member using same

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US5884501A (en) * 1996-04-19 1999-03-23 Goldstein; Vladimir Ice-making machine and heat exchanger therefor
DE19938044C1 (en) * 1999-08-12 2000-10-05 Fraunhofer Ges Forschung Ice generator for providing ice slurry uses stripping devices for removing ice from inside walls of parallel pipes for aqueous medium within heat exchanger
FR2827037B1 (en) * 2001-07-03 2003-09-12 Bousquet Adrien Laude DEVICE AND METHOD FOR STORING AND REGENERATING A REFRIGERANT FLUID COMPRISING A MIXED SOLID PHASE AND LIQUID PHASE
JP4330830B2 (en) * 2001-09-28 2009-09-16 高砂熱学工業株式会社 Ice making equipment
FR2833340B1 (en) 2001-12-07 2004-07-02 Lgl France HEAT EXCHANGE DEVICE
FR2881820B1 (en) * 2005-02-10 2008-05-30 Saint Gobain Vetrotex DEVICE FOR THE EXTRACTION OF HEAT FROM GAS AND FOR THE RECOVERY OF CONDENSATES
CN100401001C (en) * 2006-02-24 2008-07-09 哈尔滨工业大学 Solidification heat utilization and pollution preventing device for surface water source heat pump
US8132424B2 (en) * 2008-09-17 2012-03-13 Integrated Marine Systems, Inc. Ice machines with extruded heat exchanger
ES2751390T3 (en) * 2010-07-12 2020-03-31 Evert Frederik Potgieter Industrial shell and tube heat exchanger
US9599404B2 (en) * 2013-08-27 2017-03-21 Black Night Enterprises, Inc. Fluid direct contact heat exchange apparatus and method
CN103697726B (en) * 2013-12-23 2016-05-25 南京迪泽尔空调设备有限公司 A kind of case tube heat exchanger
KR102201142B1 (en) * 2019-01-28 2021-01-08 엘지전자 주식회사 Heat transfer pipe and Heat exchanger for chiller

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Publication number Priority date Publication date Assignee Title
CN113503755A (en) * 2021-09-09 2021-10-15 北京福典工程技术有限责任公司 Method for enhancing mass transfer heat exchange and heat exchange member using same

Also Published As

Publication number Publication date
FR2709817A1 (en) 1995-03-17
EP0641980A1 (en) 1995-03-08
GR3021128T3 (en) 1996-12-31
ES2091111T3 (en) 1996-10-16
US5488836A (en) 1996-02-06
DE69400307D1 (en) 1996-08-22
FR2709817B1 (en) 1995-10-20
DK0641980T3 (en) 1996-12-02
ATE140528T1 (en) 1996-08-15
DE69400307T2 (en) 1996-11-21

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