EP2379977B1 - Heat exchanger comprising tubes with grooved fins - Google Patents
Heat exchanger comprising tubes with grooved fins Download PDFInfo
- Publication number
- EP2379977B1 EP2379977B1 EP09716192A EP09716192A EP2379977B1 EP 2379977 B1 EP2379977 B1 EP 2379977B1 EP 09716192 A EP09716192 A EP 09716192A EP 09716192 A EP09716192 A EP 09716192A EP 2379977 B1 EP2379977 B1 EP 2379977B1
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- European Patent Office
- Prior art keywords
- fin
- tube
- tubes
- grooves
- heat exchanger
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
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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
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
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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
- F28F2215/00—Fins
- F28F2215/10—Secondary fins, e.g. projections or recesses on main fins
Definitions
- the invention relates to a tube heat exchanger comprising finned tubes, in which the tubes extend in a certain axial direction and are provided with heat exchange fins, each fin having a heat exchange surface. surrounding a tube which extends in a certain radial direction relative to the tube and which is structured in relief to form grooves spaced relative to each other in the radial direction.
- a tube heat exchanger is known from the document US 2008/0023180 A1 , see in particular the Figures 5 and 6 .
- Such an exchanger corresponds to the preamble of claim 1.
- the invention applies more particularly to a tube heat exchanger using air as a secondary exchange fluid such as aero-refrigerant, aero-condenser, aero-heater or aero-evaporator type equipment, used respectively for cooling, condensing, reheating and evaporation of a fluid, in particular in refining processes, gas treatment and compression plants, gas liquefaction units, coal synthesis units and gas, power generation facilities, regasification units, or any other fluid treatment facility.
- a secondary exchange fluid such as aero-refrigerant, aero-condenser, aero-heater or aero-evaporator type equipment, used respectively for cooling, condensing, reheating and evaporation of a fluid, in particular in refining processes, gas treatment and compression plants, gas liquefaction units, coal synthesis units and gas, power generation facilities, regasification units, or any other fluid treatment facility.
- such equipment comprises a main heat exchanger equipped with a bundle of external finned tubes in which circulates the fluid to be cooled, condensed, heated or evaporated, as well as distribution and distribution manifolds. fluid between the tubes.
- the fluid is cooled in the outer finned tubes by heat exchange with a second fluid circulating around the external tubes and fins, including ambient air.
- a circulation or forced ventilation of ambient air is provided by fans positioned either below (what is called a forced draft) or above (so-called induced draft) tubes exchanger .
- the ambient air is pulsed through the finned tube bundle at a relatively low frontal speed of between 1.5 and 4 meters per second (m / s).
- the flow regime of the ambient air is generally laminar with some local turbulence.
- the areas of the heat exchanger where heat exchange is most important are the leading edges of the fins and tubes in the direction of the flow of air.
- Patent document is known US-2008023180 a fin for aero-refrigerant tube which has on the surface a relief with cavities or grooves formed by mechanical deformation of the fins. Such cavities or grooves make it possible to increase the heat exchange between the air and the fin thanks to creating turbulence while increasing pressure losses.
- concentric grooves 42 of semi-cylindrical section are formed on each fin.
- Patent document is also known WO 2007/147754 a fin for a heat exchanger tube equipped with airflow deflectors in the form of projecting surfaces which modify the structure of the air flow in order to improve heat exchanges between the air and the fin .
- These surfaces are in the form of rectangular or triangular cutouts in the fin.
- the heat exchangers being mostly outside and the ambient air not being filtered, the cuts made in the fin can be sources of fouling due to dust, insects, etc ... that come to obstruct the cuts.
- the object of the invention is to provide a grooved fin structure for a heat exchanger tube which makes it possible to obtain an increase in the heat exchange between the air and the fluid circulating in the tube, without deteriorating the loss of heat. charge.
- the subject of the invention is a tube heat exchanger comprising finned tubes, in which the tubes extend in a certain axial direction and are provided with heat exchange fins, each fin having a heat exchange surface surrounding a tube which extends in a certain radial direction relative to the tube and which is structured in relief to form grooves spaced from each other in the radial direction, and wherein the grooves of a fin have dimensions different that decrease as one moves away from the tube in the radial direction so as to provide a guide for a fluid around the tube.
- the main advantage of such a staggered conformation of the relief of the fins is that it makes it possible to better guide the flow of air at the rear of the tubes in the radial direction of the tubes (according to the direction of the flow which arrives on the tubes ).
- tubes with external fins according to the invention it is thus possible to greatly reduce an air recirculation zone at the rear of the tubes in the direction of the flow of air, which is normally important when uses flat-profiled (flat-profile) finned tubes.
- the stepped relief surface guiding the air at the rear of the tubes reduces the areas of recirculation where the heat exchange is bad and therefore to take better advantage of the surface of the fins. In this way with a fin according to the invention, the gain obtained in terms of thermal performance can be very important.
- the grooves of a fin may have different depths and widths which decrease as one moves away from the tube in said radial direction.
- Each fin may have a thickness which decreases as one moves away from the tube in said radial direction.
- the grooves of a fin may be spaced from each other in a concentric shape pattern or in an elliptical shape pattern.
- the grooves of a fin may be very close to one another, that is to say joined.
- the grooves may be disposed on both sides of the fin.
- Each fin can be rolled up helically around the tube or where the fins may be in the form of disc.
- a heat exchanger 1 comprising a tube bundle 2 with finned circular section disposed in several substantially parallel superimposed rows extending in an axial direction A in which circulates a fluid to be cooled between an inlet B and an outlet C fluid, and around which circulates a flow of pulsed ambient air from the bottom upwards in the direction indicated by the arrows D, transversely to the tubes 2, by fans 3 positioned above the heat exchanger 1.
- the flow of fluid is here divided into three passage sections or passes 2a, 2b, 2c successive schematically represented on the figure 1 to improve the cooling of the fluid.
- a heat exchanger 1 thus generally comprises between three and eight rows of superposed tubes 2 arranged staggered or aligned with respect to the fluid flow direction in the tubes 2 as indicated by the arrows F.
- the tubes 2 are provided with outer radial annular fins 4 substantially perpendicular to the tube 2 and substantially parallel to each other, favoring the heat exchange between the ambient air and the fluid, as well as guiding the flow of air towards the rear of the tubes. tubes 2 in the axial direction, as this will be described below.
- the outer fins 4 make it possible to increase the external heat exchange area by a factor of between 15 and 25 with respect to the surface of a similar tube 2 without fins. Such a surface increase makes it possible to increase the heat exchange, but also generates losses which are in particular compensated by the use of efficient fans.
- fins 4 are preferably arranged all along all the tubes 2 of the exchanger 1.
- shape and size of the outer fins 4 may vary from one tube to another of the bundle of tubes 2.
- the configurations of tubes 2 outer fins 4 are not necessarily homogeneous within a bundle of tubes 2, in particular the diameters of the tubes 2 may vary.
- a fin 4 according to the invention with a radial surface structured in relief 5 to form grooves 5a, 5b, 5c spaced from each other in a certain radial direction E by a fin portion 8 substantially flat annular.
- the grooves 5a, 5b, 5c of the fin 4 have different dimensions which decrease as one moves away from the tube 2 in such a way as to guide the flow of ambient air around the tube 2 in the axial direction A. More precisely, the grooves 5a, 5b, 5c of a fin 4 have respective respective depths p1, p2, p3 in the axial direction A and respective widths 11, 12, 13 in the radial direction E, respectively.
- the innermost groove 5a is the uppermost and widest of the grooves
- the outermost groove 5c is the lowest and the smallest
- the middle groove 5b is of intermediate height and width.
- the number of grooves 5a, 5b, 5c on a fin 4 is between two and four, but other grooves may be added depending on the application.
- the raised surface 5 consists of three circular grooves 5a, 5b, 5c arranged in a concentric pattern and centered around the tube 2.
- Adjacent fins 4 may have concentric grooves 5a, 5b, 5c which are respectively in alignment axial (the fins 4 have the same raised surface 5 and thus a groove 5a, 5b, 5c of a fin 4 is in axial alignment with the corresponding groove of the other fins 4 on the tube 2).
- the concentric adjacent grooves 5a, 5b, 5c of a fin 4 are separated (disjoint) radially from each other by annular planar flat portions 8.
- These annular portions 8 may have in the radial direction E the same width d1, d2 or different widths d1, d2 according to a variable diagram, d1, d2 being for example between 1 and 5 mm.
- the portion widths decreases going from the tube 2 to the outer peripheral edge 4A or vice versa. It is also possible to provide adjacent grooves which are contiguous and in this case the width of the separation portions 8 is very small (less than 1 mm).
- a tube 2 has fins 4 of the same configuration over its entire length.
- tubes 2 with different configurations of fins 4.
- the grooves 5a, 5b, 5c are formed on the same face 4c of the fin 4, that is to say oriented in the same direction relative to the fin 4.
- the figure 4 shows another embodiment of a fin 4 according to the invention in which grooves 5d, 5e, 5f are oriented on either side of the fin 4, that is to say they are arranged alternately on two faces 4c, 4d of the blade 4 opposite, which can confer a better mechanical strength with respect to the grooves 5a, 5b, 5c.
- FIG. 5 another embodiment of a fin 4 according to the invention in which the concentric grooves 5a, 5b, 5c have been replaced by grooves 6a, 6b, 6c arranged according to an elliptical shape diagram 4.
- Such grooves 6a, 6b 6c elliptical make it possible to take advantage of the phenomenon of guiding the air through the grooves while limiting the increase in the associated pressure drop.
- the advantage of this solution is an increase in performance gain for similar conditions of use, ie iso speed and even pressure drop.
- the outer fins 4 can be made from an aluminum strip 7, or even another heat-conducting material, helically wound in the axial direction A around each tube 2, as shown schematically in FIG. figure 6 .
- the fins 4 are here very slightly inclined relative to the tube 2 and the direction A, as indicated by the arrow 4e, this inclination being small because the fins 4 are very close to each other, so that we can consider that the fins 4 are almost perpendicular to the tube 2. It is also possible to make a tube 2 with fins 4 more inclined relative to the axial direction A of the tube 2.
- Another embodiment of an outer fin 4 is formed by means of a series of rotating disks.
- the attachment between the fin 4 and the tube 2 may be made by embedding the fin 4, for example in a groove previously made on the periphery of the tube 2 (not shown), or by winding the fin 4 to the base of which a folding is achieved and crimping on the tube 2 for example knurled.
- the fin 4 can also be obtained by forming or deformation of an aluminum tube attached to the tube 2.
- the fin 4 can also be made using stacked disks.
- the fin 4 has a thickness which decreases as one moves away from the tube from the inner edge 4b the fin 4 towards its outer edge 4a.
- the thickness e1 of the fin 4 at its outer edge 4a may be between about 0.15 and 0.4 millimeters (mm) and the thickness e2 of the fin 4 at its inner edge 4b can be between about 0.4 and 1 mm.
- the grooves 5a, 5b, 5c have respective depths p1, p2, p3 of between approximately 0.4 and 1.5 mm, as well as respective widths 11, 12, 13 at the base of the groove of between approximately 1 and 4. mm, the grooves 5a, 5b, 5c having different heights and widths so as to obtain the stepped relief decreasing away from the tube 2 such that p1> p2> p3 and 11> 12> 13.
- the fin 4 according to the invention has a length H of between approximately 10 and 20 mm and preferably between approximately 12 and 18 mm.
- the pitch P between two consecutive fins along the tube 2 is between about 2.2 and 3.5 mm and preferably between about 2.5 and 3.2 mm, or generally less than the conventional spacing between two blades profiled consecutive dish.
- a heat exchanger 1 comprises a bundle of tubes 2 resting on a steel structure (not shown) and formed of about 50 to 300 tubes 2 of diameter between about 15 millimeters and 55 millimeters, the width of the exchanger heat 1 being between 0.3 meters and 5 meters, and its length between 8 meters and 18 meters.
- the tubes 2 may be composed of steel, for example stainless steel or carbon steel or a high-alloy steel, such as incoloy, the choice of the material of the tubes 2 being a function of the transported fluid which may be aggressive. , and operating conditions.
- the outer fins 4 are generally made of aluminum, but may also be stainless steel, or any other heat conducting material.
- the Figures 7 and 8 present current lines (obtained by numerical simulation) of the ambient air flowing in the direction D around several tubes 2 of the heat exchanger 1 in a plane M substantially perpendicular to the tubes 2 and located centrally between two fins 4 consecutive as indicated on the figure 1 and on the figure 3 . More specifically, the figure 7 presents the case of a flat-profile fin and the figure 8 presents the case of a fin 4 according to the invention having concentric grooves 5a, 5b, 5c. As can be seen on the figure 7 , a fluid recirculation zone Z1 is located at the rear of the tubes 2 in the direction of the flow D of the air in which the heat exchange is bad.
- the pressure drop is represented as a function of the frontal air speed on the tubes 2 for flat-profile tubes 2 (curve 9A) and for tubes 2 with fins 4 according to the invention with grooves 5a , 5b, 5c concentric (curve 9B).
- curve 9A flat-profile tubes 2
- curve 9B tubes 2 with fins 4 according to the invention with grooves 5a , 5b, 5c concentric
- This increase in the pressure drop can be compensated by spacing the fins 4 each other along the tube 2.
- the pitch P between two consecutive fins is different according to whether the surface of the fins is raised or not: 2.54 mm in the case of the flat profile vane and 3 mm for the fin 4 according to the invention with grooves 5a, 5b, 5c concentric. In this way, as can be seen on the figure 9 the increase in pressure drop caused by the raised surface 5 remains very low.
- the spacing of the fins 4 along the tube 2 reduces the amount of material used to make the fins, which compensates for the increase in material caused by the realization of the raised surface 5 on the fin 4 by modifying the surface of the fin, and decreases the amount of material used to achieve a saving of the order of 3 to 6% per meter.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
L'invention concerne un échangeur de chaleur à tubes comprenant des tubes à ailettes, dans lequel les tubes s'étendent selon une certaine direction axiale et sont munis d'ailettes d'échange de chaleur, chaque ailette ayant une surface d'échange de chaleur entourant un tube qui s'étend selon une certaine direction radiale par rapport au tube et qui est structurée en relief pour former des rainures espacées l'une par rapport à l'autre selon la direction radiale. Un tel échangeur est connu du document
L'invention s'applique plus particulièrement à un échangeur de chaleur à tubes utilisant l'air comme fluide d'échange secondaire tel qu'un équipement de type aéro-réfrigérant, aéro-condenseur, aéro-réchauffeur ou aéro-évaporateur, utilisé respectivement pour le refroidissement, la condensation, le réchauffage et l'évaporation d'un fluide, notamment dans des procédés de raffinage, des stations de traitement et de compression du gaz, des unités de liquéfaction de gaz, des unités de synthèse du charbon et du gaz, des installations de production d'électricité, des unités de regazéification, ou tout autre installation de traitement de fluide.The invention applies more particularly to a tube heat exchanger using air as a secondary exchange fluid such as aero-refrigerant, aero-condenser, aero-heater or aero-evaporator type equipment, used respectively for cooling, condensing, reheating and evaporation of a fluid, in particular in refining processes, gas treatment and compression plants, gas liquefaction units, coal synthesis units and gas, power generation facilities, regasification units, or any other fluid treatment facility.
De manière générale, un tel équipement comprend un échangeur de chaleur principal muni d'un faisceau de tubes à ailettes externes dans lesquels circule le fluide à refroidir, à condenser, à réchauffer ou à évaporer, ainsi que des collecteurs de distribution et de répartition du fluide entre les tubes. En particulier, le refroidissement du fluide s'effectue dans les tubes à ailettes externes par échange de chaleur avec un deuxième fluide circulant autour des tubes et des ailettes externes, notamment de l'air ambiant. Pour cela, une circulation ou ventilation forcée d'air ambiant est assurée par des ventilateurs positionnés soit en dessous (ce qu'on appelle un tirage forcé) ou en dessus (ce qu'on appelle un tirage induit) des tubes de l'échangeur.In general, such equipment comprises a main heat exchanger equipped with a bundle of external finned tubes in which circulates the fluid to be cooled, condensed, heated or evaporated, as well as distribution and distribution manifolds. fluid between the tubes. In particular, the fluid is cooled in the outer finned tubes by heat exchange with a second fluid circulating around the external tubes and fins, including ambient air. For this, a circulation or forced ventilation of ambient air is provided by fans positioned either below (what is called a forced draft) or above (so-called induced draft) tubes exchanger .
En général, l'air ambiant est pulsé au travers du faisceau de tubes à ailettes à une vitesse frontale relativement faible comprise entre 1,5 et 4 mètres par seconde (m/s). A de telles vitesses et pour les configurations géométriques considérées (notamment de sections de passage de l'air, d'espace entre deux ailettes ou deux tubes consécutifs), le régime d'écoulement de l'air ambiant est globalement laminaire avec quelques turbulences locales, ce qui se caractérise par des échanges thermiques avec les ailettes externes relativement faibles. Les zones de l'échangeur où les échanges thermiques sont les plus importants sont les bords d'attaque des ailettes et des tubes dans le sens de l'écoulement de l'air. Ainsi, du fait de la structure de l'écoulement et de l'échangeur, les zones des tubes situées à l'arrière des tubes dans le sens de l'écoulement de l'air sont quasiment inexploitées pour l'échange thermique. Ces zones dites de recirculation de l'échangeur se caractérisent par une recirculation de l'air qui engendre des pertes de charges et qui ne permettent pas un bon refroidissement de l'ailette.In general, the ambient air is pulsed through the finned tube bundle at a relatively low frontal speed of between 1.5 and 4 meters per second (m / s). At such speeds and for the geometric configurations considered (in particular air passage sections, space between two fins or two consecutive tubes), the flow regime of the ambient air is generally laminar with some local turbulence. , which is characterized by heat exchanges with the relatively small external fins. The areas of the heat exchanger where heat exchange is most important are the leading edges of the fins and tubes in the direction of the flow of air. Thus, because of the structure of the flow and the exchanger, the zones of the tubes located at the rear of the tubes in the direction of the flow of air are almost unexploited for heat exchange. These so-called recirculation zones of the exchanger are characterized by recirculation of the air which generates losses of charge and which do not allow good cooling of the fin.
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Le but de l'invention est de proposer une structure d'ailette rainurée pour tube d'échangeur de chaleur qui permet d'obtenir une augmentation des échanges thermiques entre l'air et le fluide circulant dans le tube, sans dégradation de la perte de charge.The object of the invention is to provide a grooved fin structure for a heat exchanger tube which makes it possible to obtain an increase in the heat exchange between the air and the fluid circulating in the tube, without deteriorating the loss of heat. charge.
A cet effet, l'invention a pour objet un échangeur de chaleur à tubes comprenant des tubes à ailettes, dans lequel les tubes s'étendent selon une certaine direction axiale et sont munis d'ailettes d'échange de chaleur, chaque ailette ayant une surface d'échange de chaleur entourant un tube qui s'étend selon une certaine direction radiale par rapport au tube et qui est structurée en relief pour former des rainures espacées l'une par rapport à l'autre selon la direction radiale, et dans lequel les rainures d'une ailette ont des dimensions différentes qui diminuent à mesure qu'on s'éloigne du tube selon la direction radiale de telle façon à réaliser un guidage pour un fluide autour du tube.For this purpose, the subject of the invention is a tube heat exchanger comprising finned tubes, in which the tubes extend in a certain axial direction and are provided with heat exchange fins, each fin having a heat exchange surface surrounding a tube which extends in a certain radial direction relative to the tube and which is structured in relief to form grooves spaced from each other in the radial direction, and wherein the grooves of a fin have dimensions different that decrease as one moves away from the tube in the radial direction so as to provide a guide for a fluid around the tube.
L'avantage principal d'une telle conformation étagée du relief des ailettes est qu'elle permet de mieux guider le flux d'air à l'arrière des tubes selon la direction radiale des tubes (selon la direction du flux qui arrive sur les tubes). En utilisant des tubes avec des ailettes externes selon l'invention, on peut ainsi fortement diminuer une zone de recirculation de l'air à l'arrière des tubes dans le sens de l'écoulement de l'air, normalement importante lorsque l'on utilise des tubes à ailettes sans relief (à profil plat). Ainsi, la surface en relief étagé guidant l'air à l'arrière des tubes permet de réduire les zones de recirculation où l'échange thermique est mauvais et donc de tirer un meilleur profit de la surface des ailettes. De cette manière avec une ailette selon l'invention, le gain obtenu en termes de performance thermique peut être très important.The main advantage of such a staggered conformation of the relief of the fins is that it makes it possible to better guide the flow of air at the rear of the tubes in the radial direction of the tubes (according to the direction of the flow which arrives on the tubes ). By using tubes with external fins according to the invention, it is thus possible to greatly reduce an air recirculation zone at the rear of the tubes in the direction of the flow of air, which is normally important when uses flat-profiled (flat-profile) finned tubes. Thus, the stepped relief surface guiding the air at the rear of the tubes reduces the areas of recirculation where the heat exchange is bad and therefore to take better advantage of the surface of the fins. In this way with a fin according to the invention, the gain obtained in terms of thermal performance can be very important.
Selon certaines particularités de l'échangeur selon l'invention, les rainures d'une ailette peuvent avoir des profondeurs et des largeurs différentes qui diminuent à mesure qu'on s'éloigne du tube selon ladite direction radiale. Chaque ailette peut avoir une épaisseur qui diminue à mesure qu'on s'éloigne du tube selon ladite direction radiale. Les rainures d'une ailette peuvent être espacées l'une de l'autre selon un schéma de forme concentrique ou encore selon un schéma de forme elliptique. Les rainures d'une ailette peuvent être très rapprochées l'une de l'autre, c'est-à-dire jointives. Les rainures peuvent être disposées sur les deux faces de l'ailette. Chaque ailette peut être enroulée de façon hélicoïdale autour du tube ou encore ou les ailettes peuvent être sous la forme de disque.According to certain features of the exchanger according to the invention, the grooves of a fin may have different depths and widths which decrease as one moves away from the tube in said radial direction. Each fin may have a thickness which decreases as one moves away from the tube in said radial direction. The grooves of a fin may be spaced from each other in a concentric shape pattern or in an elliptical shape pattern. The grooves of a fin may be very close to one another, that is to say joined. The grooves may be disposed on both sides of the fin. Each fin can be rolled up helically around the tube or where the fins may be in the form of disc.
La présente invention sera mieux comprise et d'autres avantages apparaîtront à la lecture de la description détaillée de quelques modes de réalisation pris à titre d'exemples nullement limitatifs et illustrés par les dessins annexés dans lesquels :
- la
figure 1 montre schématiquement en coupe un échangeur de chaleur ; - la
figure 2 est une vue en plan d'une ailette selon l'invention ; - la
figure 3 est une vue en coupe partielle radiale selon l'axe III-III de lafigure 2 d'un tube avec deux ailettes selon l'invention; - la
figure 4 est une vue en coupe partielle radiale selon l'axe III-III de lafigure 2 d'un tube avec deux ailettes selon l'invention dans un autre mode de réalisation ; - la
figure 5 est une vue en plan d'une ailette selon l'invention dans encore un autre mode de réalisation ; - la
figure 6 est une vue en coupe radiale selon l'axe III-III de lafigure 2 d'un tube muni de plusieurs ailettes selon l'invention ; - la
figure 7 est une vue en coupe radiale d'un ensemble de tubes avec ailettes à profil plat montrant des lignes de courant dans un plan entre deux ailettes obtenues par simulation numérique ; - la
figure 8 est une vue en coupe radiale d'un ensemble de tubes avec ailettes selon l'invention montrant des lignes de courant obtenus par simulation numérique ; - la
figure 9 représente schématiquement un graphique représentatif de la perte de charge en fonction de la vitesse frontale de l'air arrivant sur une ailette selon l'invention et sur une ailette à profil plat; - la
figure 10 représente schématiquement un graphique représentatif de la puissance échangée en fonction de la vitesse frontale de l'air arrivant sur une ailette selon l'invention et sur une ailette à profil plat.
- the
figure 1 schematically shows in section a heat exchanger; - the
figure 2 is a plan view of a fin according to the invention; - the
figure 3 is a radial partial sectional view along the axis III-III of thefigure 2 a tube with two fins according to the invention; - the
figure 4 is a radial partial sectional view along the axis III-III of thefigure 2 a tube with two fins according to the invention in another embodiment; - the
figure 5 is a plan view of a fin according to the invention in yet another embodiment; - the
figure 6 is a radial sectional view along the axis III-III of thefigure 2 a tube provided with several fins according to the invention; - the
figure 7 is a radial sectional view of a set of tubes with flat profile fins showing current lines in a plane between two fins obtained by numerical simulation; - the
figure 8 is a radial sectional view of a set of tubes with fins according to the invention showing current lines obtained by digital simulation; - the
figure 9 schematically represents a representative graph of the pressure drop as a function of the frontal velocity of the air arriving on a fin according to the invention and on a flat-profile fin; - the
figure 10 schematically represents a representative graph of the power exchanged as a function of the frontal speed of the air arriving on a fin according to the invention and on a flat profile fin.
Sur la
Les tubes 2 sont munis d'ailettes 4 annulaires radiales externes sensiblement perpendiculaires au tube 2 et sensiblement parallèles entre elles favorisant l'échange thermique entre l'air ambiant et le fluide, ainsi que le guidage du flux d'air vers l'arrière des tubes 2 dans la direction axiale, comme cela sera décrit plus bas. De manière générale, les ailettes externes 4 permettent d'augmenter la surface d'échange de chaleur externe d'un facteur compris entre 15 et 25 par rapport à la surface d'un tube 2 similaire sans ailettes. Une telle augmentation de surface permet d'augmenter l'échange de chaleur, mais engendre également des pertes de charges qui sont notamment compensées par l'utilisation de ventilateurs 3 performants.The
Pour une meilleure clarté, on a représenté sur la
On a représenté sur la
De préférence, le nombre de rainures 5a,5b,5c sur une ailette 4 est compris entre deux et quatre, mais on peut ajouter d'autres rainures en fonction de l'application. Sur la
Par simplicité de fabrication, un tube 2 a des ailettes 4 de même configuration sur toute sa longueur. Mais dans un échangeur de chaleur 1, on peut prévoir des tubes 2 avec des configurations d'ailettes 4 différentes. Par exemple, on peut avoir un tube 2 dans lequel les ailettes 4 ont des rainures 5a,5b,5c adjacentes dont les largeurs d1,d2 de portion 8 de séparation vont croissant vers le bord périphérique extérieur 4A, et un tube 2 adjacent dans lequel les ailettes 4 ont des rainures 5a,5b,5c adjacentes dont les largeurs d1,d2 de portion 8 de séparation vont à l'inverse décroissant vers le bord périphérique extérieur 4A.For simplicity of manufacture, a
Sur l'ailette 4 de la
On a représenté sur la
Les ailettes externes 4 peuvent être fabriquées à partir d'un feuillard 7 en aluminium, voire d'un autre matériau conducteur de chaleur, enroulé de manière hélicoïdale dans la direction axiale A autour de chaque tube 2, comme représenté schématiquement sur la
Comme visible sur la
Les rainures 5a,5b,5c ont des profondeurs respectives p1,p2,p3 comprises entre environ 0,4 et 1,5 mm, ainsi que des largeurs respectives 11,12,13 à la base de la rainure comprise entre environ 1 et 4 mm, les rainures 5a,5b,5c ayant des hauteurs et largeurs différentes de façon à obtenir le relief étagé diminuant en s'éloignant du tube 2 tel que p1 >p2>p3 et 11 >12>13.The
L'ailette 4 selon l'invention a une longueur H comprise entre environ 10 et 20 mm et préférentiellement entre environ 12 et 18 mm. Le pas P entre deux ailettes consécutives le long du tube 2 est compris entre environ 2,2 et 3,5 mm et préférentiellement entre environ 2,5 et 3,2 mm, ou généralement inférieur à l'espacement classique entre deux ailettes à profil plat consécutives.The
Généralement, un échangeur de chaleur 1 comprend un faisceau de tubes 2 reposant sur une structure en acier (non montrée) et formé d'environ 50 à 300 tubes 2 de diamètre compris entre environ 15 millimètres et 55 millimètres, la largeur de l'échangeur de chaleur 1 étant comprise entre 0,3 mètres et 5 mètres, et sa longueur comprise entre 8 mètres et 18 mètres.Generally, a
Les tubes 2 peuvent être composés d'acier, par exemple de l'acier inoxydable ou de l'acier carbone ou un acier fortement allié, comme l'incoloy, le choix du matériau des tubes 2 étant fonction du fluide transporté qui peut être agressif, et des conditions de fonctionnement. Les ailettes externes 4 sont généralement réalisées en aluminium, mais peuvent également être en inox, ou tout autre matériau conducteur de chaleur.The
Les
Sur la
On a représenté sur la
En outre, l'espacement des ailettes 4 le long du tube 2 permet de diminuer la quantité de matière utilisée pour réaliser les ailettes, ce qui compense l'augmentation de matière provoquée par la réalisation de la surface en relief 5 sur l'ailette 4 par modification de la surface de l'ailette, et diminue la quantité de matière utilisée pour réaliser une économie de l'ordre de 3 à 6% par mètre.In addition, the spacing of the
Claims (9)
- Heat exchanger (1) with tube (2) comprising finned tubes, wherein the tubes extend according to a certain axial direction and are provided with heat exchange fins (4), each fin having a heat exchange surface surrounding a tube that extends according to a certain radial direction (E) relative to the tube and which is relief structured to form grooves (8a, 5b, 5c, 6a, 6b, 6c) spaced apart from one another following said radial direction, characterized in that the grooves of a fin have different dimensions that decrease on moving away from the tube following said radial direction so as to form a guide for a fluid around the tube.
- Heat exchanger according to claim 1, wherein the grooves of a fin have different depths and widths that decrease on moving away from the tube according to said radial direction.
- Heat exchanger according to claims 1 or 2, wherein each fin has a thickness that decreases on moving away from the tube according to said radial direction.
- Heat exchanger according to one of the claims 1 to 3, wherein the grooves of a fin are spaced apart from each other according to a concentric shaped pattern.
- Heat exchanger according to one of the claims 1 to 3, wherein the grooves of a fin are spaced apart from each other according to an elliptical shaped pattern.
- Heat exchanger according to one of the claims 1 to 5, wherein the grooves of a fin are spaced apart from each other in a joined manner.
- Heat exchanger according to one of the claims 1 to 6, wherein each fin has two opposite faces (4c, 4d) acting as heat exchange surface, said grooves being arranged on the two faces of the fin.
- Tube heat exchanger according to one of the claims 1 to 7 wherein the tubes are each fitted with a heat exchange fin helicoidally wound around the tube.
- Heat exchanger according to one of the claims 1 to 7, wherein the tubes are each fitted with a disc shape fin.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PL09716192T PL2379977T3 (en) | 2008-12-19 | 2009-05-05 | Heat exchanger comprising tubes with grooved fins |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0858864A FR2940422B1 (en) | 2008-12-19 | 2008-12-19 | HEAT EXCHANGER COMPRISING GROOVED FINNED TUBES |
PCT/FR2009/050832 WO2010070216A1 (en) | 2008-12-19 | 2009-05-05 | Heat exchanger comprising tubes with grooved fins |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2379977A1 EP2379977A1 (en) | 2011-10-26 |
EP2379977B1 true EP2379977B1 (en) | 2012-10-17 |
Family
ID=40627684
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09716192A Active EP2379977B1 (en) | 2008-12-19 | 2009-05-05 | Heat exchanger comprising tubes with grooved fins |
Country Status (12)
Country | Link |
---|---|
US (1) | US8376033B2 (en) |
EP (1) | EP2379977B1 (en) |
KR (1) | KR101177726B1 (en) |
CN (1) | CN101861506B (en) |
BR (1) | BRPI0906068B1 (en) |
CA (1) | CA2747353C (en) |
ES (1) | ES2399504T3 (en) |
FR (1) | FR2940422B1 (en) |
HK (1) | HK1149073A1 (en) |
PL (1) | PL2379977T3 (en) |
RU (1) | RU2494330C2 (en) |
WO (1) | WO2010070216A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015188812A1 (en) | 2014-06-11 | 2015-12-17 | GEA Luftkühler GmbH | Heat exchanger |
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CN102322765A (en) * | 2011-09-19 | 2012-01-18 | 无锡市冠云换热器有限公司 | Rectangular waveform fin with spherical concave-convex |
CN102322761A (en) * | 2011-09-19 | 2012-01-18 | 无锡市冠云换热器有限公司 | A kind of have a spherical concavo-convex sawtooth corrugated fin |
US9938935B2 (en) | 2012-07-12 | 2018-04-10 | General Electric Company | Exhaust gas recirculation system and method |
US10508621B2 (en) | 2012-07-12 | 2019-12-17 | Ge Global Sourcing Llc | Exhaust gas recirculation system and method |
US9360258B2 (en) | 2013-03-15 | 2016-06-07 | Ormat Technologies, Inc. | Fin configuration for air cooled heat exchanger tubes |
EP2784426A1 (en) | 2013-03-27 | 2014-10-01 | GEA Batignolles Technologies Thermiques | Tube heat exchanger with optimized thermo-hydraulic characteristics |
KR101321708B1 (en) * | 2013-09-12 | 2013-10-28 | 주식회사 두발 | Heat exchanger |
CN103884220B (en) * | 2014-04-15 | 2016-03-23 | 重庆大学 | Be applicable to the oval fin with circular hole of fin tube type refrigerated heat exchanger under frozen condition |
NO20141176A1 (en) | 2014-09-30 | 2016-03-31 | Global Lng Services As | Process and plant for the production of LNG |
CA2930827A1 (en) | 2016-05-25 | 2017-11-25 | Nova Chemicals Corporation | Furnace coil modified fins |
US20180372413A1 (en) | 2017-06-22 | 2018-12-27 | Rheem Manufacturing Company | Heat Exchanger Tubes And Tube Assembly Configurations |
GB2575015B (en) * | 2018-05-23 | 2023-02-22 | Veragon Srl | Atmospheric water generator using a finned heat exchanger |
RU188272U1 (en) * | 2018-11-14 | 2019-04-04 | Наиль Закуанович Галиванов | HEAT EXCHANGE PIPE WITH PROFILED RIBS |
CN117980687A (en) * | 2021-09-30 | 2024-05-03 | 三菱电机株式会社 | Heat exchanger and refrigeration cycle device |
KR102599087B1 (en) | 2021-12-08 | 2023-11-07 | 전주대학교 산학협력단 | Fin tube heat exchanger |
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-
2008
- 2008-12-19 FR FR0858864A patent/FR2940422B1/en active Active
-
2009
- 2009-05-05 EP EP09716192A patent/EP2379977B1/en active Active
- 2009-05-05 WO PCT/FR2009/050832 patent/WO2010070216A1/en active Application Filing
- 2009-05-05 RU RU2011129831/06A patent/RU2494330C2/en active
- 2009-05-05 KR KR1020097020333A patent/KR101177726B1/en active IP Right Grant
- 2009-05-05 PL PL09716192T patent/PL2379977T3/en unknown
- 2009-05-05 BR BRPI0906068-5 patent/BRPI0906068B1/en active IP Right Grant
- 2009-05-05 CA CA2747353A patent/CA2747353C/en active Active
- 2009-05-05 ES ES09716192T patent/ES2399504T3/en active Active
- 2009-05-05 CN CN2009800002273A patent/CN101861506B/en active Active
- 2009-05-11 US US12/463,861 patent/US8376033B2/en active Active
-
2011
- 2011-03-29 HK HK11103193.6A patent/HK1149073A1/en unknown
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015188812A1 (en) | 2014-06-11 | 2015-12-17 | GEA Luftkühler GmbH | Heat exchanger |
DE102014108209A1 (en) | 2014-06-11 | 2015-12-17 | GEA Luftkühler GmbH | heat exchangers |
Also Published As
Publication number | Publication date |
---|---|
FR2940422B1 (en) | 2010-12-03 |
RU2494330C2 (en) | 2013-09-27 |
CA2747353C (en) | 2015-08-11 |
BRPI0906068B1 (en) | 2019-12-03 |
KR20100103777A (en) | 2010-09-28 |
HK1149073A1 (en) | 2011-09-23 |
US20100155041A1 (en) | 2010-06-24 |
WO2010070216A1 (en) | 2010-06-24 |
US8376033B2 (en) | 2013-02-19 |
KR101177726B1 (en) | 2012-08-28 |
ES2399504T3 (en) | 2013-04-01 |
BRPI0906068A2 (en) | 2015-06-30 |
FR2940422A1 (en) | 2010-06-25 |
PL2379977T3 (en) | 2013-03-29 |
CN101861506B (en) | 2012-01-11 |
EP2379977A1 (en) | 2011-10-26 |
RU2011129831A (en) | 2013-01-27 |
CN101861506A (en) | 2010-10-13 |
CA2747353A1 (en) | 2010-06-24 |
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