EP0058628A2 - Heat exchanger with capillary structure for refrigerating machines and/or heat pumps - Google Patents
Heat exchanger with capillary structure for refrigerating machines and/or heat pumps Download PDFInfo
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- EP0058628A2 EP0058628A2 EP82450003A EP82450003A EP0058628A2 EP 0058628 A2 EP0058628 A2 EP 0058628A2 EP 82450003 A EP82450003 A EP 82450003A EP 82450003 A EP82450003 A EP 82450003A EP 0058628 A2 EP0058628 A2 EP 0058628A2
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- Prior art keywords
- fibers
- capillary
- capillary structure
- internal wall
- tube
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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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
- F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
- F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
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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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
- F28D7/12—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically the surrounding tube being closed at one end, e.g. return type
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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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/04—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by preventing the formation of continuous films of condensate on heat-exchange surfaces, e.g. by promoting droplet formation
Definitions
- the present invention relates to heat exchangers using the energy supplied during the change of liquid / vapor or vapor / liquid phase of certain fluids and, more particularly, those used in refrigeration machines and / or heat pumps.
- the heat exchangers are either constructed and dimensioned with a view to playing a specific predetermined role, either as an evaporator or as a condenser, or else produced so as to serve both as an evaporator and as a condenser.
- the heat exchanger In the case where the heat exchanger is designed to be used exclusively as an evaporator, it is underused because it is only half filled with liquid in general and at most 2/3 full, in order to 'avoid "liquid blows" to the compressor.
- the object of the present invention is to overcome these two major drawbacks simultaneously by proposing a new capillary structure for heat exchangers allowing heat exchanges over the entire useful surface of the exchangers with a significantly increased efficiency, while not impeding the circulation of lubricating oil.
- the subject of the invention is a heat exchanger for refrigeration machines and / or heat pumps, of the type in which an annular capillary structure is applied against the internal wall of the tubular heat exchange network, characterized in that that said capillary structure is constituted by a set of free and smooth fibers of suitable material, substantially rectilinear and parallel to the axis of the tubular elements concerned, regularly distributed in a ring and pressed by any appropriate means against the internal wall of said tubular elements, preferably over the entire length of the latter.
- Such an arrangement allows, thanks to the wicking effect provided by the free fibers over the entire internal surface, an excellent distribution of the liquid phase without any hindrance to the circulation of oil because the fibers are smooth, straight and parallel to the 'axis of the tubes.
- the exchanger of FIG. 1 comprises two collectors 1 and 2 connected by a network of heat exchange tubes 3, parallel and identical rectilinear, made of a material which is a good thermal conductor such as copper for example.
- all of the tubes 3 have a capillary annular structure 4 over their entire length, as does the collector of the liquid phase (collector 1 in FIG.) Of the heat transfer fluid (or refrigerant).
- Figs. 2 and 3 illustrate an embodiment of said capillary annular structure 4 according to which this structure consists of a number of identical individual fibers 5, smooth, straight and of constant diameter. These fibers are free from each other while being in contact with each other and with the internal wall of the tube (1 or 3) and confined in an annular space by any suitable means.
- the distribution of the fibers 5 is uniform, the thickness of the annular layer being in a proportion determined relative to the diameter of the tube in order to have an appropriate circulation and flow of the fluid in the liquid phase in the conduits 1 and 3.
- the fibers 5 line the internal wall of the latter over their entire useful length and are applied against the wall of the tubes, for example in the known manner by a helical element 6 (Fig. 3) forming a spring, engaged in the central part of the tubes ( 3.1).
- This helical element 6 could of course be replaced by any other member capable of pressing the fibers against the wall such as rings for example.
- the fibers 5 and the holding members 6 are made of metallic or plastic material, or the like, compatible with the nature of the fluid circulating in the exchanger.
- the diameter of the fibers 5 can vary insofar as the interstitial spaces between fibers make it possible to obtain the capillary effect sought for the coolant or refrigerant considered.
- the fibers 5 arranged in the collector 1 ensure a uniform distribution of the liquid towards the exchanger tubes 3, while the fibers 5 of the latter allow the liquid to "wet" absolutely the entire useful surface of the tubes 3 and therefore ensure maximum heat exchange between the liquid phase fluid in contact with the internal wall of the tubes 3 and the external fluid.
- the exchanger works as an evaporator and cools the fluid (for example air) circulating in 7 between the tubes 3.
- the fluid circulating in the tubes 3 is then called refrigerant.
- the working fluid arrives in the gaseous phase at 2 and leaves by 1 in the liquid phase, the fluid is heat-transferable and transfers part of its calories to the fluid circulating in 7.
- the latter is air
- the liquid phase is distributed over the tubes 3 as it is formed and is evacuated and the capillary structure 4 thus ensures a good distribution of the temperature and therefore improves the heat exchanges.
- an exchanger such as that of FIG. 1 working in an evaporator has a much higher efficiency than that of traditional evaporators
- the filling of the exchange tubes in liquid phase is usually of the order of half and at most 2/3 while, thanks to the capillary structure 4 according to the invention in the evaporator arranged according to FIG. 1, the entire internal surface of the exchange tubes 3 is in contact with the liquid phase, uniformly, thanks to the effect of capillary wick.
- the exchanger shown in FIG. 1 operating either as an evaporator or as a condenser, improves the coefficient of performance of reversible machines in substantial proportions (of the order of 30 to 40%).
- Fig. 4 illustrates an exchanger according to the invention designed essentially to operate as an evaporator.
- the refrigerant arrives in the liquid phase in the collector 8 having internally a capillary structure 4 like the collector 1 of FIG. 1.
- the fluid is distributed in identical flow for each exchange tube 9 also provided internally with a capillary annular structure 4 over its entire length.
- tubes 9 are dead-end. the liquid is distributed along each tube 9 uniformly and evaporates completely and uniformly under the effect of the heat provided by the fluid circulating at 10.
- the vapor produced is collected by conduits 11 pitted on the exhaust manifold 12 of the gas phase and engaged in the end of the tubes 9 coaxially with the latter.
- Fig. 5 schematically shows an exchanger according to the invention designed to work essentially as a condenser.
- the heat transfer fluid arrives in the gas phase in the collector 13, condenses in the liquid phase on contact with the internal wall, provided with a capillary annular structure 4, exchange tubes 14 and leaves in the liquid phase through the collector 15 also provided of a capillary annular structure 4. in accordance with the invention.
- the invention is not limited to the embodiment shown and described above, but on the contrary covers all variants, in particular those concerning the nature of the material constituting the fibers 5, their sizing, their distribution along the internal wall of the tubular exchange members and collectors of the liquid phase of the working fluid as well as the means for pressing or containing said fibers against the internal wall of said tubular members.
- the sheet of fibers 5 may comprise only a single layer of fibers more or less parallel to the axis of the tube and contiguous or not.
- FIG. 6 shows a particularly interesting embodiment by its simplicity and its efficiency.
- a sheet of fibers 5 is shown, consisting of a single layer of parallel and non-contiguous fibers, said sheet being pressed against the internal wall of the tube 3 by an elastic system constituted by a sheet of wires 17 of spring steel (or material likely to have the same elasticity characteristics).
- the wires 17 are parallel, non-contiguous and wound in a helix.
- the fibers 5 have an axis substantially parallel to the axis of the tube 3, while the wires 17 form a more or less significant acute angle with the fibers 5.
- the propeller produced by the wires 17 does not comprise a single wire but several in parallel, the bundle of wires being wound in a helix. It is therefore possible to easily vary the inclination between the fibers 5 and the wires 17 while having a tight network of wires 17 in contact at numerous points with the sheet of fibers 5.
- Fig. 7 illustrates a variant according to which the internal wall of the tube 3 is no longer smooth but striated, grooved or grooved.
- streaks 18 or the like are produced by any suitable means, parallel to the axis of the tube 3 and preferably with a generally flared V-shaped cross section. These recesses 18 are responsible for facilitating the correct positioning of the fibers 5, it being understood that the depth of these streaks or the like is less than the radius of the fibers 5 which are held in place by an elastic system identical to that of FIG. 6 or different.
- the capillary structure may consist of two layers of fibers 5 with identical or nonparallel dimensional characteristics and not contiguous, the fibers of one of the layers being inclined with respect wearing the fibers of the other layer and the whole of this structure being pressed against the tube by an elastic system identical or not to that of FIG. 6.
- one of the layers may comprise fibers parallel to the axis of the tube, this layer being either in contact with the internal wall of the tube, or in contact with said elastic system (vapor side).
- Fig. 8 illustrates a process for producing a capillary structure according to Fi g. 6 and its insertion into an aluminum or light alloy tube produced by extrusion.
- a cylindrical mandrel 19 On a cylindrical mandrel 19 is helically wound a sheet 20 of spring wires or the like, made of steel for example.
- the wires 21 of this nanope form contiguous turns on the mandrel 19.
- the ply 20 is wrapped in a ply 22 of free smooth fibers 5 parallel to the axis of the mandrel 19.
- the fibers 5 are regularly distributed in a single layer around the helical ply 20.
- the plies 20 and 22 at the outlet of the mandrel 19 are guided and held in shape by a cylindrical sleeve 23 in the extension of the mandrel 19 and integrated in an extrusion head 24 coaxially with the annular orifice 25 for extruding a tube 3 for example made of aluminum, said orifice 25 being delimited between the sleeve 23 and the die 26.
- the tube 3 As the tube 3 is formed, it is automatically provided internally with the capillary ply 22 and the elastic retaining ply 20, the plies 20 and 22 being formed continuously and introduced into the tube 3 at the same speed. scrolling.
- the plies 20 and 22 expand radially under the elastic action of the spring wires 21 and are pressed against the internal wall of the tube 3.
- the tube thus equipped conforms to what is shown in Fi g . 6.
- the tube 3 may internally have grooves such as 18 (Fig. 7) made during the extrusion.
- the tube 3 can, of course, be obtained in another way, for example by rolling a flat plate and then welding or from a strip wound helically on a mandrel, these two techniques being perfectly known.
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Abstract
Echangeur de chaleur pour machines frigorifiques et/ou pompes à chaleur, du type dans lequel une structure capillaire annulaire est appliquée contre la paroi interne du réseau tubulaire d'échange de chaleur, caractérisé en ce que ladite structure capillaire (4) est constituée par un jeu de fibres libres et lisses (5) en matériau approprié sensiblement rectilignes et parallèles à l'axe des éléments tubulaires rectilignes et parallèles à l'axe des éléments tubulaires concernée (3), réparties régulièrement en anneau et plaquées par tous moyens appropriés (6) contre la paroi interne desdits éléments tubulaires, de préférence sur toute la longueur de ces derniers. Application aux machines frigorifiques et/ou pompes à chaleur.Heat exchanger for refrigeration machines and / or heat pumps, of the type in which an annular capillary structure is applied against the internal wall of the tubular heat exchange network, characterized in that said capillary structure (4) consists of a set of free and smooth fibers (5) of suitable material substantially rectilinear and parallel to the axis of the tubular elements rectilinear and parallel to the axis of the tubular elements concerned (3), regularly distributed in a ring and plated by any appropriate means (6 ) against the internal wall of said tubular elements, preferably over the entire length of the latter. Application to refrigeration machines and / or heat pumps.
Description
La présente invention concerne les échangeurs de chaleur utilisant l'énergie fournie lors du changement de phase liquide/vapeur ou vapeur/liquide de certains fluides et, plus particulièrement, ceux utilisés dans les machines frigorifiques et/ou pompes à chaleur.The present invention relates to heat exchangers using the energy supplied during the change of liquid / vapor or vapor / liquid phase of certain fluids and, more particularly, those used in refrigeration machines and / or heat pumps.
Dans les machines de ce type, les échangeurs de chaleur sont ou bien construits et dimensionnés en vue de jouer un rôle spécifique prédéterminé, soit comme évaporateur, soit comme condenseur, ou bien réalisés de façon à servir aussi bien d'évaporateur que de condenseur.In machines of this type, the heat exchangers are either constructed and dimensioned with a view to playing a specific predetermined role, either as an evaporator or as a condenser, or else produced so as to serve both as an evaporator and as a condenser.
Dans le cas où l'échangeur de chaleur est conçu pour être employé exclusivement comme évaporateur, il est sous-utilisé du fait qu'il n'est rempli qu'à moitié de liquide en général et aux 2/3 au maximum, afin d'éviter des "coups de liquide" au compresseur.In the case where the heat exchanger is designed to be used exclusively as an evaporator, it is underused because it is only half filled with liquid in general and at most 2/3 full, in order to 'avoid "liquid blows" to the compressor.
Les 2/3 seulement, voire la moitié, de la surface d'échange de l'évaporateur lorsque le débit de fluide diminue, sont donc utilisés. En outre, du fait que l'échange se fait au niveau de surfaces froides réduites, la formation de givre est favorisée dans le cas des évaporateurs à air ce qui nuit bien entendu au rendement.Only 2/3, or even half, of the evaporator exchange surface when the fluid flow decreases, are therefore used. In addition, since the exchange takes place at reduced cold surfaces, the formation of frost is favored in the case of air evaporators, which obviously affects performance.
Dans le cas des condenseurs conçus essentiellement comme tels, il faut, pour des raisons technologiques, que les vapeurs arrivant au condenseur soient complètement condensées à la sortie. Il en résulte un sur-dimensionnement augmentant les coûts de revient de ces échangeurs.In the case of condensers designed essentially as such, it is necessary, for technological reasons, that the vapors arriving at the condenser are completely condensed at the outlet. This results in an over-sizing increasing the production costs of these exchangers.
Enfin, actuellement, l'utilisation de machines frigorifiques réversibles oblige à réaliser des échangeurs qui soient un compromis entre évaporateur et condenseur, puisque devant fonctionner aussi bien en évaporateur qu'en condenseur, et qui, de ce fait, outre les inconvénients des échangeurs spécifiques rappelés ci-dessus, ont un mauvais rendement.Finally, currently, the use of reversible refrigeration machines requires the production of exchangers which are a compromise between evaporator and condenser, since they must operate as well in evaporator as in condenser, and which, therefore, in addition to the disadvantages of specific exchangers recalled above, have poor performance.
Afin d'améliorer les réndements d'échange thermique on a déjà imaginé de tapisser la paroi interne des tubes échangeurs d'une structure capillaire en vue d'avoir une meilleure répartition de la phase liquide sur la paroi interne de ces tubes.In order to improve the heat exchange efficiency, it has already been imagined to line the internal wall of the exchanger tubes with a capillary structure in order to have a better distribution of the liquid phase on the internal wall of these tubes.
Cependant les diverses solutions de ce type conçues jusqu'à présent ne donnent pas satisfaction sur deux points importants.However, the various solutions of this type designed so far are not satisfactory on two important points.
Toutes les structures capillaires proposées, soit ne permettent pas d'avoir une capillarité sur toute la surface interne des tubes, soit (c'est le cas notamment des structures à base de toiles métalliques tissées ou maillées) constituent des chicanes et des obstacles freinant et retenant-l'huile de lubrification du compresseur du système, certaines structures cumulant les deux inconvénients.All the capillary structures proposed, either do not make it possible to have capillarity over the entire internal surface of the tubes, or (this is particularly the case with structures based on woven or meshed metallic fabrics) constitute baffles and obstacles braking and retaining the lubricating oil from the compressor of the system, certain structures combining the two disadvantages.
Le but de la présente invention est de pallier simultanément ces deux inconvénients majeure en proposant une nouvelle structure capillaire pour échangeurs de chaleur permettant les échanges thermiques sur toute la surface utile des échangeurs avec un rendement sensiblement accru, tout en n'entravant pas la circulation d'huile de lubrification.The object of the present invention is to overcome these two major drawbacks simultaneously by proposing a new capillary structure for heat exchangers allowing heat exchanges over the entire useful surface of the exchangers with a significantly increased efficiency, while not impeding the circulation of lubricating oil.
A cet effet, l'invention a pour objet un échangeur de chaleur pour machines frigorifiques et/ou pompes à chaleur, du type dans lequel une structure capillaire annulaire est appliquée contre la paroi interne du réseau tubulaire d'échange de chaleur, caractérisé en ce que ladite structure capillaire est constituée par un jeu de fibres libres et lisses en matériau approprié, sensiblement rectilignes et parallèles à l'axe des éléments tubulaires concernés, réparties régulièrement en anneau et plaquées par tous moyens appropriés contre la paroi interne desdits éléments tubulaires, de préférence sur toute la longueur de ces derniers.To this end, the subject of the invention is a heat exchanger for refrigeration machines and / or heat pumps, of the type in which an annular capillary structure is applied against the internal wall of the tubular heat exchange network, characterized in that that said capillary structure is constituted by a set of free and smooth fibers of suitable material, substantially rectilinear and parallel to the axis of the tubular elements concerned, regularly distributed in a ring and pressed by any appropriate means against the internal wall of said tubular elements, preferably over the entire length of the latter.
Un tel agencement permet grâce à l'effet de mèche procuré par les fibres libres sur toute la surface interne une excellente répartition de la phase liquide sans aucune entrave à la circulation d'huile du fait que les fibres sont lisses, rectilignes et parallèles à l'axe des tubes.Such an arrangement allows, thanks to the wicking effect provided by the free fibers over the entire internal surface, an excellent distribution of the liquid phase without any hindrance to the circulation of oil because the fibers are smooth, straight and parallel to the 'axis of the tubes.
De plus, une telle structure est particulièrement simple et peu coûteuse à réaliser.In addition, such a structure is particularly simple and inexpensive to produce.
D'autres caractéristiques et avantages ressortiront de la description qui va suivre de divers modes de réalisation d'une telle structure capillaire suivant l'invention, ainsi que d'un procédé de réalisation et de mise en place d'un mode préféré de ladite structure capillaire, description donnée à titre d'exemple uniquement et en regard des dessins annexés sur lesquels :
- - Fig. 1 représente une coupe schématique d'un échangeur conforme à l'invention et pouvant fonctionner en évaporateur ou en condenseur :
- - Fig. 2 représente une vue en section transversale d'un élément tubulaire de l'échangeur de la Fig. 1 ;
- - Fig. 3 représente une coupe longitudinale partielle d'un élément tubulaire de l'échangeur de la Fig. 1 ;
- - Fig. 4 représente une coupe schématique d'un évaporateur conforme à l'invention;
- - Fig. 5 représente une coupe schématique d'un condenseur également conforme à l'invention;
- - Fig. 6 est une coupe partielle d'un mode de réalisation préféré d'une structure capillaire selon l'invention ;
- - Fig. 7 est une variante de réalisation du dispositif de la Fig. 6 , et
- - Fig. 8 est une coupe axiale d'un dispositif permettant la réalisation et la mise en place d'une structure capillaire suivant la Fig. 6 ou 7 associé à une tête d'extrusion de tubes dans laquelle est intégré ledit dispositif.
- - Fig. 1 represents a schematic section of an exchanger according to the invention and capable of operating as an evaporator or a condenser:
- - Fig. 2 shows a cross-sectional view of a tubular element of the exchanger of FIG. 1;
- - Fig. 3 shows a partial longitudinal section of a tubular element of the exchanger of FIG. 1;
- - Fig. 4 shows a schematic section of an evaporator according to the invention;
- - Fig. 5 shows a schematic section of a condenser also according to the invention;
- - Fig. 6 is a partial section of a preferred embodiment of a capillary structure according to the invention;
- - Fig. 7 is an alternative embodiment of the device of FIG. 6, and
- - Fig. 8 is an axial section of a device allowing the production and installation of a capillary structure according to FIG. 6 or 7 associated with a tube extrusion head in which said device is integrated.
L'échangeur de la Fig. 1 comporte deux collecteurs 1 et 2 reliés par un réseau de tubes 3 d'échange de chaleur, rectilignes parallèles et identiques, en matériau bon conducteur thermique tel que le cuivre par exemple.The exchanger of FIG. 1 comprises two
Conformément à l'invention, tous les tubes 3 comportent une structure annulaire capillaire 4 sur toute leur longueur, de même que le collecteur de la phase liquide (collecteur 1 sur la Fig.) du fluide caloporteur (ou frigorigène).According to the invention, all of the
Les Fig. 2 et 3 illustrent un mode de réalisation de ladite structure annulaire capillaire 4 suivant lequel cette structure est constituée par un certain nombre de fibres individuelles 5 identiques, lisses, rectilignes et de diamètre constant. Ces fibres sont libres entre elles tout en étant en contact les unes les autres et avec la paroi interne du tube (1 ou 3) et confinées dans un espace annulaire par tous moyens appropriés. La répartition des fibres 5 est uniforme, l'épaisseur de la couche annulaire étant dans une proportion déterminée par rapport au diamètre du tube afin d'avoir une circulation et un débit appropriés du fluide en phase liquide dans les conduits 1 et 3.Figs. 2 and 3 illustrate an embodiment of said capillary
Les fibres 5 tapissent la paroi interne de ces derniers sur toute leur longueur utile et sont appliquées contre la paroi des tubes,par exemple à la manière connuepar un élément hélicoidal 6 (Fig. 3) formant ressort, engagé dans la partie centrale des tubes (3,1).The
Cet élément hélicoïdal 6 pourrait bien entendu être remplacé par tous autres organes susceptibles de plaquer les fibres.5 contre la paroi tels que des anneaux par exemple.This
Les fibres 5 et les organes de maintien 6 sont en matériau métallique ou plastique, ou autre, compatible avec la nature du fluide circulant dans l'échangeur.The
Le diamètre des fibres 5 peut varier dans la mesure où les espaces interstitiels entre fibres permettent d'obtenir l'effet de capillarité recherché pour le fluide caloporteur pu frigorigène considéré.The diameter of the
Les fibres 5 disposées dans le collecteur 1 assurent une répartition uniforme du liquide vers les tubes échangeurs 3 cependant que les fibres 5 de ces derniers permettent au liquide de "mouiller" absolument toute la surface utile des tubes 3 et assurent donc un échange thermique maximal entre le fluide en phase liquide en contact avec la paroi interne des tubes 3 et le fluide extérieur.The
D'autre part, du fait de la géométrie des espaces interstitiels aussi bien entre fibres 5 qu'entre celles-ci et la paroi interne des tubes 3 et de l'absence d'obstacle transversal à l'écoulement axial de l'huile de lubrification celle-ci n'est pas retenue et peut s'écouler librement.On the other hand, due to the geometry of the spaces interstitial both between
Le compresseur du système ne risque donc pas de manquer d'huile.There is therefore no risk of the system compressor running out of oil.
Lorsque le fluide de travail arrive en phase liquide en 1 et repart en phase gazeuse en 2, l'échangeur travaille en évaporateur et refroidit le fluide (par exemple de l'air) circulant en 7 entre les tubes 3.When the working fluid arrives in the liquid phase at 1 and leaves again in the gas phase at 2, the exchanger works as an evaporator and cools the fluid (for example air) circulating in 7 between the
Le fluide circulant dans les tubes 3 est alors appelé frigorigène.The fluid circulating in the
Si, au contraire, le fluide de travail arrive en phase gazeuse en 2 et repart par 1 en phase liquide, le fluide est caloporteur et cède une partie de ses calories au fluide circulant en 7. Lorsque ce dernier est de l'air, on peut avantageusement munir extérieurement les tubes 3 d'ailettes en aluminium ou autre matériau bon conducteur de la chaleur. L'échangeur travaille alors en condenseur.If, on the contrary, the working fluid arrives in the gaseous phase at 2 and leaves by 1 in the liquid phase, the fluid is heat-transferable and transfers part of its calories to the fluid circulating in 7. When the latter is air, we can advantageously provide the
La phase liquide se répartit sur les tubes 3 au fur et à mesure qu'elle se forme et est évacuée et la structure capillaire 4 assure ainsi une bonne répartition de la température et améliore d'autant les échanges thermiques.The liquid phase is distributed over the
Ainsi, un échangeur tel que celui de la Fig. 1 travaillant en évaporateur a une efficacité bien supérieure à celle des évaporateurs traditionnels dont le remplissage des tubes d'échange en phase liquide est de l'ordre habituellement de la moitié et au maximum des 2/3 alors que, grâce à la structure capillaire 4 selon l'invention dans l'évaporateur agencé suivant la Fig. 1, toute la surface interne des tubes d'échange 3 est en contact avec la phase liquide, de manière uniforme, gràce à l'effet de mèche capillaire.Thus, an exchanger such as that of FIG. 1 working in an evaporator has a much higher efficiency than that of traditional evaporators, the filling of the exchange tubes in liquid phase is usually of the order of half and at most 2/3 while, thanks to the
On supprime donc, en outre, dans le cas où le fluide circulant en 7 est de l'air, l'apparition prématurée de points froids engendrant la formation de givre sur les tubes 3. Il a été ainsi constaté qu'avec un évaporateur selon l'invention, la formation de givre n'apparaissait que pour une température de l'air circulant en 7 inférieure de 4 à 5°C à celle à laquelle apparaît le givre habituellement sur les évaporateurs classiques.It therefore therefore eliminates, in the case where the fluid flowing at 7 is air, the premature appearance of cold spots causing the formation of frost on the
L'échangeur représenté sur la Fig. 1 fonctionnant indifféremment en évaporateur ou en condenseur, améliore le coefficient de performance des machines réversibles dans des proportions substantielles (de l'ordre de 30 à 40%).The exchanger shown in FIG. 1 operating either as an evaporator or as a condenser, improves the coefficient of performance of reversible machines in substantial proportions (of the order of 30 to 40%).
La Fig. 4 illustre un échangeur suivant l'invention conçu essentiellement pour fonctionner en évaporateur.Fig. 4 illustrates an exchanger according to the invention designed essentially to operate as an evaporator.
Le fluide frigorigène arrive en phase liquide dans le collecteur 8 comportant intérieurement une structure capillaire 4 comme le collecteur 1 de la Fig. 1. Le fluide est réparti en débit identique pour chaque tube d'échange 9 également muni intérieurement d'une structure annulaire capillaire 4 sur toute sa longueur.The refrigerant arrives in the liquid phase in the
Ces tubes 9 sont en cul-de-sac. le liquide est réparti le long de chaque tube 9 uniformément et s'évapore totalement et uniformément sous l'effet de la chaleur apportée par le fluide circulant en 10. La vapeur produite est collectée par des conduits 11 piqués sur le collecteur 12 d'évacuation de la phase gazeuse et engagés dans l'extrémité des tubes 9 coaxialement à ces derniers.These tubes 9 are dead-end. the liquid is distributed along each tube 9 uniformly and evaporates completely and uniformly under the effect of the heat provided by the fluid circulating at 10. The vapor produced is collected by
La Fig. 5 représente schématiquement un échangeur conforme à l'invention conçu pourtravailler essentiellement en condenseur.Fig. 5 schematically shows an exchanger according to the invention designed to work essentially as a condenser.
Le fluide caloporteur arrive en phase gazeuse dans le collecteur 13, se condense en phase liquide au contact avec la paroi interne, pourvue d'une structure annulaire capillaire 4, des tubes d'échange 14 et ressort en phase liquide par le collecteur 15 également muni d'une structure annulaire capillaire 4. conforme à l'invention.The heat transfer fluid arrives in the gas phase in the
Des conduits 16 piqués sur le collecteur 13 d'amenée en phase liquide du fluide caloporteur et engagés chacun dans l'extrémité d'un des tubes 14, coaxialement à ceux-ci, permettent de répartir uniformément le fluide caloporteur.
Bien entendu, l'invention n'est pas limitée au mode de réalisation représenté et décrit ci-dessus mais en couvre au contraire toutes les variantes, notamment celles concernant la nature du matériau constitutif des fibres 5, leur dimensionnement, leur distribution le long de la paroi interne des organes tubulaires d'échange et collecteurs de la phase liquide du fluide de travail ainsi que les moyens pour plaquer ou contenir lesdites fibres contre la paroi interne desdits organes tubulaires.Of course, the invention is not limited to the embodiment shown and described above, but on the contrary covers all variants, in particular those concerning the nature of the material constituting the
La nappe de fibres 5 peut ne comporter qu'une seule couche de fibres plus ou moins parallèles à l'axe du tube et jointives ou non.The sheet of
La Fig. 6 représente un mode de réalisation particulièrement intéressant par sa simplicité et son efficacité. Sur cette Fig., on a représenté une nappe de fibres 5 constituée d'une seule couche de fibres parallèles et non jointives, ladite nappe étant plaquée contre la paroi interne du tube 3 par un système élastique constitué par une nappe de fils 17 d'acier à ressort (ou matériau susceptible de présenter les mêmes caractéristiques d'élasticité). Les fils 17 sont parallèles, non jointifs et enroulés en hélice.Fig. 6 shows a particularly interesting embodiment by its simplicity and its efficiency. In this FIG., A sheet of
Les fibres 5 sont d'axe sensiblement parallèle à l'axe du tube 3 cependant que les fils 17 forment avec les fibres 5 un angle aigu plus ou moins important.The
L'hélice réalisée par les fils 17 ne comporte pas un fil unique mais plusieurs en parallèle, le faisceau de fils étant enroulé en hélice. On peut donc faire varier facilement l'inclinaison entre les fibres 5 et les fils 17 tout en ayant un réseau serré de fils 17 en contact en de nombreux points avec la nappe de fibres 5.The propeller produced by the
Il est à noter que par un dimensionnement et une distribution appropriés des fils 17, la nappe élastique constituée de ces fils augmente les effets de capillarité procurés par la structure capillaire 5.It should be noted that by appropriate dimensioning and distribution of the
La Fig. 7 illustre une variante suivant laquelle la paroi interne du tube 3 n'est plus lisse mais striée, rainurée ou cannelée. A cet effet, on réalise par tous moyens appropriés des stries 18 ou analogues, parallèles à l'axe du tube 3 et de préférence à section en forme générale de V largement évasé. Ces creux 18 sont chargés de faciliter le positionnement correct des fibres 5 étant entendu que la profondeur de ces stries ou analogues est inférieure au rayon des fibres 5 lesquelles sont maintenues en place par un système élastique identique à celui de la Fig. 6 ou différent.Fig. 7 illustrates a variant according to which the internal wall of the
Par ailleurs, la structure capillaire peut être constituée de deux couches de fibres 5 de caractéristiques dimensionnelles identiques ou nonparallèles et non jointives, les fibres de l'une des couches étant inclinées par rapport aux fibres de l'autre couche et l'ensemble de cette structure étant plaqué contre le tube par un système élastique identique ou non à celui de la Fig. 6.Furthermore, the capillary structure may consist of two layers of
Il est à noter que l'une des couches peut comporter des fibres parallèles à l'axe du tube, cette couche étant, soit en contact avec la paroi interne du tube, soit en contact avec ledit système élastique (côté vapeur). ,It should be noted that one of the layers may comprise fibers parallel to the axis of the tube, this layer being either in contact with the internal wall of the tube, or in contact with said elastic system (vapor side). ,
La Fig. 8 illustre un procédé pour la réalisation d'une structure capillaire suivant la Fig. 6 et son insertion dans un tube en aluminium ou alliage léger réalisé par extrusion. Sur un mandrin cylindrique 19 est enroulé en hélice une nappe 20 de fils à ressort ou analogue, en acier par exemple. Les fils 21 de cette nanpe forment des spires jointives sur le mandrin 19.Fig. 8 illustrates a process for producing a capillary structure according to
La nappe 20 est enveloppée d'une nappe 22 de fibres lisses libres 5 parallèles à l'axe du mandrin 19. Les fibres 5 sont régulièrement réparties en une seule couche autour de la nappe en hélice 20.The
Les nappes 20 et 22 au débouché du mandrin 19 sont guidées et maintenues en forme par un manchon cylindrique 23 dans le prolongement du mandrin 19 et intégré dans une tête d'extrusion 24 coaxialement à l'orifice annulaire 25 d'extrusion d'un tube 3 par exemple en aluminium, ledit orifice 25 étant délimité entre le manchon 23 et la filière 26.The
Au fur et à mesure que se forme le tube 3 il est muni intérieurement automatiquement de la nappe capillaire 22 et de la nappe élastique de maintien 20, les nappes 20 et 22 étant formées en continu et introduites dans le tube 3 à la même vitesse de défilement.As the
A la sortie du manchon 23, les nappes 20 et 22 se dilatent radialement sous l'action élastique des fils à ressort 21 et se plaquent contre la paroi interne du tube 3.At the outlet of the
Le tube ainsi équipé est conforme à ce qui est représenté à la Fig. 6.The tube thus equipped conforms to what is shown in Fi g . 6.
Le tube 3 peut comporter intérieurement des stries telles que 18 (Fig. 7) réalisées au cours de l'extrusion.The
Le tube 3 peut, bien entendu, être obtenu d'une autre manière, par exemple par roulage d'une plaque plane puis soudage ou à partir d'une bande enroulée en hélice sur un mandrin, ces deux techniques étant parfaitement connues.The
Dans ce cas, c'est l'ensemble des deux nappes 2p - 22 qui est introduit dans le tube 3 préalablement formé.In this case, it is the assembly of the two plies 2p - 22 which is introduced into the
Dans le cas où le fluide à vaporiser ou à condenser circule à l'extérieur des tubes, une telle structure capillaire est appliquée à l'extérieur du tube comme dans le cas des condenseurs à eau où cette dernière circule à l'intérieur des tubes, le fluide frigorigène s'évaporant ou se condensant à l'extérieur des tubes.In the case where the fluid to be vaporized or to be condensed circulates outside the tubes, such a capillary structure is applied to the outside of the tube as in the case of water condensers where the latter circulates inside the tubes, the refrigerant evaporating or condensing outside the tubes.
Claims (12)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR8103033 | 1981-02-13 | ||
FR8103033A FR2500143A1 (en) | 1981-02-13 | 1981-02-13 | HEAT EXCHANGERS WITH CAPILLARY STRUCTURE FOR REFRIGERATING MACHINES AND / OR HEAT PUMPS |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0058628A2 true EP0058628A2 (en) | 1982-08-25 |
EP0058628A3 EP0058628A3 (en) | 1983-04-13 |
EP0058628B1 EP0058628B1 (en) | 1989-12-20 |
Family
ID=9255262
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP82450003A Expired EP0058628B1 (en) | 1981-02-13 | 1982-02-12 | Heat exchanger with capillary structure for refrigerating machines and/or heat pumps |
Country Status (5)
Country | Link |
---|---|
US (1) | US4448043A (en) |
EP (1) | EP0058628B1 (en) |
DE (1) | DE3280070D1 (en) |
ES (1) | ES510203A0 (en) |
FR (1) | FR2500143A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0119777A2 (en) * | 1983-03-22 | 1984-09-26 | Imperial Chemical Industries Plc | Centrifugal heat pump |
FR2591504A1 (en) * | 1985-12-13 | 1987-06-19 | Centre Nat Rech Scient | Process for evaporation-condensation of trickling films, components for its implementation and its applications |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5184675A (en) * | 1991-10-15 | 1993-02-09 | Gardner Ernest A | Thermal energy transfer apparatus and method of making same |
US20060191355A1 (en) * | 2003-12-04 | 2006-08-31 | Mts Systems Corporation | Platform balance |
US20100270002A1 (en) * | 2008-08-05 | 2010-10-28 | Parrella Michael J | System and method of maximizing performance of a solid-state closed loop well heat exchanger |
US8616000B2 (en) | 2008-06-13 | 2013-12-31 | Michael J. Parrella | System and method of capturing geothermal heat from within a drilled well to generate electricity |
US20100270001A1 (en) * | 2008-08-05 | 2010-10-28 | Parrella Michael J | System and method of maximizing grout heat conductibility and increasing caustic resistance |
US8534069B2 (en) * | 2008-08-05 | 2013-09-17 | Michael J. Parrella | Control system to manage and optimize a geothermal electric generation system from one or more wells that individually produce heat |
US9423158B2 (en) * | 2008-08-05 | 2016-08-23 | Michael J. Parrella | System and method of maximizing heat transfer at the bottom of a well using heat conductive components and a predictive model |
US20100313589A1 (en) * | 2009-06-13 | 2010-12-16 | Brent Alden Junge | Tubular element |
CN102278904B (en) * | 2011-07-29 | 2013-03-06 | 华北电力大学 | Internal liquid-dividing hood-type condensed heat-exchanging pipe |
JP2013178052A (en) * | 2012-02-29 | 2013-09-09 | Daikin Industries Ltd | Heat exchanger |
Citations (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB308966A (en) * | 1928-04-02 | 1930-04-10 | Superheater Co Ltd | Improvements in or relating to heat exchange apparatus |
US2517654A (en) * | 1946-05-17 | 1950-08-08 | Gen Motors Corp | Refrigerating apparatus |
US2565221A (en) * | 1946-04-06 | 1951-08-21 | Gen Motors Corp | Refrigerating apparatus |
FR990531A (en) * | 1949-07-12 | 1951-09-24 | Devices and apparatus for improving the efficiency of absorption and compression refrigerating machines | |
US2702460A (en) * | 1951-06-23 | 1955-02-22 | Gen Motors Corp | Refrigerant evaporating means |
US3498369A (en) * | 1968-06-21 | 1970-03-03 | Martin Marietta Corp | Heat pipes with prefabricated grooved capillaries and method of making |
US3521708A (en) * | 1968-10-30 | 1970-07-28 | Trane Co | Heat transfer surface which promotes nucleate ebullition |
US3554183A (en) * | 1968-10-04 | 1971-01-12 | Acf Ind Inc | Heat pipe heating system for a railway tank car or the like |
US3576210A (en) * | 1969-12-15 | 1971-04-27 | Donald S Trent | Heat pipe |
US3786861A (en) * | 1971-04-12 | 1974-01-22 | Battelle Memorial Institute | Heat pipes |
US3921710A (en) * | 1972-08-23 | 1975-11-25 | Tokico Ltd | Heat pipe and manufacturing method thereof |
FR2280872A1 (en) * | 1974-08-02 | 1976-02-27 | Agency Ind Science Techn | Differential pressure heat transfer unit - has wick with resistance to liq. flow diminishing progressively from inlet to outlet |
DE2552459A1 (en) * | 1974-11-28 | 1976-06-10 | Schramel Dieter | All year heat pump installation - operates with freezing water by extracting latent of fusion |
US4018269A (en) * | 1973-09-12 | 1977-04-19 | Suzuki Metal Industrial Co., Ltd. | Heat pipes, process and apparatus for manufacturing same |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE552459C (en) * | 1932-06-13 | Aeg | Railway drive by electric motors with cardan shafts | |
FR327078A (en) * | 1902-12-06 | 1903-06-13 | Dubois Henri | Air cooler for air or gas and for vapor condensation |
FR341536A (en) * | 1904-03-22 | 1904-08-10 | Colomann Von Rimanoczy Senior | Arrangement intended to protect the performance hall when the stage is engulfed in flames |
FR433166A (en) * | 1911-08-11 | 1911-12-27 | Mills Equipment C Ltd | Improvements to woven fabric bands |
US1602890A (en) * | 1922-07-25 | 1926-10-12 | James E Keith | Refrigerator |
US2448261A (en) * | 1945-04-30 | 1948-08-31 | Gen Motors Corp | Capillary heat transfer device for refrigerating apparatus |
US2691281A (en) * | 1951-01-16 | 1954-10-12 | Servel Inc | Heat and material transfer apparatus |
AT294148B (en) * | 1967-09-06 | 1971-11-10 | Danfoss As | Forced through evaporator for a compression refrigeration system |
US3598177A (en) * | 1968-10-29 | 1971-08-10 | Gen Electric | Conduit having a zero contact angle with an alkali working fluid and method of forming |
US3789920A (en) * | 1970-05-21 | 1974-02-05 | Nasa | Heat transfer device |
GB1398780A (en) * | 1971-07-23 | 1975-06-25 | Thermo Electron Corp | Food cooking apparatus |
NL7206063A (en) * | 1972-05-04 | 1973-11-06 | N.V. Philips Gloeilampenfabrieken | HEATING DEVICE |
NL7209936A (en) * | 1972-07-19 | 1974-01-22 | ||
US4044797A (en) * | 1974-11-25 | 1977-08-30 | Hitachi, Ltd. | Heat transfer pipe |
US4074753A (en) * | 1975-01-02 | 1978-02-21 | Borg-Warner Corporation | Heat transfer in pool boiling |
-
1981
- 1981-02-13 FR FR8103033A patent/FR2500143A1/en active Granted
-
1982
- 1982-02-11 US US06/347,970 patent/US4448043A/en not_active Expired - Lifetime
- 1982-02-12 EP EP82450003A patent/EP0058628B1/en not_active Expired
- 1982-02-12 ES ES510203A patent/ES510203A0/en active Granted
- 1982-02-12 DE DE8282450003T patent/DE3280070D1/en not_active Expired - Lifetime
Patent Citations (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB308966A (en) * | 1928-04-02 | 1930-04-10 | Superheater Co Ltd | Improvements in or relating to heat exchange apparatus |
US2565221A (en) * | 1946-04-06 | 1951-08-21 | Gen Motors Corp | Refrigerating apparatus |
US2517654A (en) * | 1946-05-17 | 1950-08-08 | Gen Motors Corp | Refrigerating apparatus |
FR990531A (en) * | 1949-07-12 | 1951-09-24 | Devices and apparatus for improving the efficiency of absorption and compression refrigerating machines | |
US2702460A (en) * | 1951-06-23 | 1955-02-22 | Gen Motors Corp | Refrigerant evaporating means |
US3498369A (en) * | 1968-06-21 | 1970-03-03 | Martin Marietta Corp | Heat pipes with prefabricated grooved capillaries and method of making |
US3554183A (en) * | 1968-10-04 | 1971-01-12 | Acf Ind Inc | Heat pipe heating system for a railway tank car or the like |
US3521708A (en) * | 1968-10-30 | 1970-07-28 | Trane Co | Heat transfer surface which promotes nucleate ebullition |
US3576210A (en) * | 1969-12-15 | 1971-04-27 | Donald S Trent | Heat pipe |
US3786861A (en) * | 1971-04-12 | 1974-01-22 | Battelle Memorial Institute | Heat pipes |
US3921710A (en) * | 1972-08-23 | 1975-11-25 | Tokico Ltd | Heat pipe and manufacturing method thereof |
US4018269A (en) * | 1973-09-12 | 1977-04-19 | Suzuki Metal Industrial Co., Ltd. | Heat pipes, process and apparatus for manufacturing same |
FR2280872A1 (en) * | 1974-08-02 | 1976-02-27 | Agency Ind Science Techn | Differential pressure heat transfer unit - has wick with resistance to liq. flow diminishing progressively from inlet to outlet |
DE2552459A1 (en) * | 1974-11-28 | 1976-06-10 | Schramel Dieter | All year heat pump installation - operates with freezing water by extracting latent of fusion |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0119777A2 (en) * | 1983-03-22 | 1984-09-26 | Imperial Chemical Industries Plc | Centrifugal heat pump |
US4793154A (en) * | 1983-03-22 | 1988-12-27 | Imperial Chemical Industries Plc | Centrifugal heat pump |
EP0119777A3 (en) * | 1983-03-24 | 1985-08-07 | Imperial Chemical Industries Plc | Centrifugal heat pump |
FR2591504A1 (en) * | 1985-12-13 | 1987-06-19 | Centre Nat Rech Scient | Process for evaporation-condensation of trickling films, components for its implementation and its applications |
Also Published As
Publication number | Publication date |
---|---|
FR2500143B1 (en) | 1984-03-09 |
ES8306864A1 (en) | 1983-06-01 |
EP0058628B1 (en) | 1989-12-20 |
DE3280070D1 (en) | 1990-01-25 |
ES510203A0 (en) | 1983-06-01 |
FR2500143A1 (en) | 1982-08-20 |
EP0058628A3 (en) | 1983-04-13 |
US4448043A (en) | 1984-05-15 |
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