EP3850293B1 - Échangeur de chaleur comprenant des éléments de surface ayant des cavités convexes et des épaississements de matériau intégrés - Google Patents

Échangeur de chaleur comprenant des éléments de surface ayant des cavités convexes et des épaississements de matériau intégrés Download PDF

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Publication number
EP3850293B1
EP3850293B1 EP19805232.6A EP19805232A EP3850293B1 EP 3850293 B1 EP3850293 B1 EP 3850293B1 EP 19805232 A EP19805232 A EP 19805232A EP 3850293 B1 EP3850293 B1 EP 3850293B1
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EP
European Patent Office
Prior art keywords
tube
heat exchanger
surface elements
reinforcing beads
partition
Prior art date
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EP19805232.6A
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German (de)
English (en)
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EP3850293A1 (fr
Inventor
Sebastian Unger
Uwe Hampel
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Helmholtz Zentrum Dresden Rossendorf eV
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Helmholtz Zentrum Dresden Rossendorf eV
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/26—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 the means being integral with the element
    • 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
    • F28F1/30—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 the means being attachable to the element
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/06—Reinforcing means for fins

Definitions

  • the invention relates to a heat exchanger with at least one partition, from which protruding surface elements are arranged on at least one side, around which a fluid can flow.
  • heat exchangers are used in various designs to transfer heat from one medium to another medium, with the two media remaining physically separate.
  • heat exchangers can be divided into liquid-gas heat exchangers, liquid-liquid heat exchangers and gas-gas heat exchangers, for example.
  • tube bundle heat exchangers with finned tubes are known, which are also referred to as finned tube heat exchangers.
  • the liquid flows inside the tube and the gas flows around the outside of the tube.
  • the heat transfer coefficients of liquids are one to two orders of magnitude higher than those of gases.
  • the surface of the tube is therefore increased on the outside by ribs, resulting in reduced heat transfer resistance on the gas side of this heat exchanger.
  • the heat transfer resistance for both media is low.
  • the ribs of finned tubes are often designed as voluminous attachments that are connected to the dividing wall of the heat exchanger. Large volumes of the ribs are coupled with high material costs in production and a high weight of the heat exchanger. High weights can be disadvantageous and undesirable, for example when used in vehicles. A high material consumption is disadvantageously associated with correspondingly high costs.
  • rib thickness A large wall thickness of the individual ribs, referred to below as rib thickness, leads to a lower number of ribs per finned tube than with thinner ribs, given the same distance between the ribs. Limited heat transfer surfaces and low overall thermal performance are associated with large fin thickness.
  • the GB 436 656 A discloses a heat exchanger with finned tubes in which three-dimensional fins are arranged on the fins, which extend essentially perpendicularly to the base area of the fins.
  • the fins have a peg-shaped cross-section and not all fins abut the wall of the tube separating the fluids.
  • the disadvantage of these finned tubes is the increase in mass, which is proportional to the volume of the three-dimensional fins, and a limited overall thermal performance of the heat exchanger.
  • Another disadvantage is that the slats are vertical to the flow direction of the Fins aligned fluid flowing around and hardly affect the heat conduction within the rib away from the tube or towards the tube.
  • the CH 435 436 A discloses a lamellar tube consisting of a core tube and a multiplicity of sheet metal laminations arranged on the core tube and having a rectangular outline as ribs.
  • the laminations each have beads - i.e. depressions - which extend from the core tube and increase rigidity.
  • the disadvantage of such ribs is that the heat-conducting cross-sectional area increases with distance from the core tube and thus leads to cooling of the rib, as a result of which the temperature difference between the rib and the medium flowing around decreases and the heat transfer performance decreases.
  • the DE 160 351 A describes a heat exchanger in which further tubes are arranged radially on the surface of a heating or cooling body tube.
  • ribs can be arranged perpendicularly to the heating or cooling element tube axis, with the ribs being arranged as a separate layer between two layers of radial tubes or within a layer of radial tubes connected to them for reasons of reinforcement.
  • the DE 42 07 597 A1 discloses a heat exchange element for fixing to a pipe through which medium flows, with a multiplicity of radially protruding heat exchanger ribs.
  • the heat exchanger fins extend along the longitudinal axis of the tube in the direction of flow of the fluid flowing through the tube and do not form a surface perpendicular to the direction of flow of the fluid in the tube.
  • a heat exchanger such as is designed, for example, as the rear wall of a refrigerator.
  • Such single-wall heat exchangers consist of a pipe coil to hold the heating or cooling medium and a metal wall with pressed rows of gills and grooves or beads to hold the pipe sections. Tabs punched out of the sheet metal wall overlap the pipe sections for attachment like a clamp. The tabs may have beads for greater stability. The metal sheet and the punched tabs are aligned along the flow direction of the heating or cooling medium through the tube.
  • the WO 02/048595 A1 describes a sewer pipe for transporting media made of plastic, which enables the transport of media in the pipe without loss of pressure, even when the sewer pipe is laid in a curved manner.
  • the sewer pipe has a wavy shape in the flow direction of the pipe wall up.
  • the U.S. 3,311,163 discloses a heat exchanger composed of a metal tube and a plurality of rectangular metal fins fixed to the outside of the metal tube.
  • the fins have parallel vertical embossments to compensate for lateral thermal expansion of the tube and fins. These embossings are aligned vertically to the flow direction of the fluid through the tube
  • the object of the invention is to provide a low-mass heat exchanger with high thermal output and a homogeneous temperature profile along the ribs.
  • the heat exchanger contains a partition and surface elements that protrude from at least one side of the partition and increase the surface of the partition, around which a fluid can flow.
  • the surface elements have reinforcing beads and surface areas located between the reinforcing beads, the reinforcing beads extending from the partition wall and having a circular or oval cross-sectional shape.
  • the reinforcing beads extend from the partition over at least part of the height of the surface element.
  • the surface elements have a plurality of convex recesses, each of the convex recesses being located in one of the areas between two reinforcing beads and extending from an outer edge of the surface element.
  • the apex of each recess is at a height greater than or equal to 30% and less than or equal to 70% of the height of the surfel. The height is measured from the partition wall.
  • Protruding from at least one side of the partition means that the surface elements extend at an angle greater than zero and less than or equal to 90° from the partition.
  • the thickness of the surfels also referred to as wall thickness, is small compared to the area of the surfels, the thickness being measured parallel to the partition wall and perpendicular to the face of the surfels.
  • the surface elements extend perpendicularly from the partition.
  • the surface elements are rigidly connected to the partition wall and are also rigid in themselves.
  • the surface elements serving as ribs of the heat exchanger are divided into thin-walled surface areas with a correspondingly small volume and low mass.
  • the thickness of the surface areas corresponds to the wall thickness of the surface elements.
  • the subdivision is made by reinforcement beads with larger cross-sections for increased heat conduction. This means that the reinforcing beads have a greater thickness than the wall thickness of the surface elements.
  • the reinforcement beads thus form material thickenings that are solid and therefore not hollow.
  • the surface element in the area of a reinforcing bead in cross section consists entirely of the material of the surface element, which completely fills the cross section.
  • the reinforcement beads are aligned in such a way that they conduct the heat towards or away from the partition between the two fluids, depending on the temperature gradient.
  • the height of the surfers is the extension of the surfers from the partition along the face of the surfers to the outer edge of the surfers in an area that is not a convex recess.
  • the height of the surfers is the radius of the surfers from the partition.
  • the outer edge of the surfel is the side of the surfel that is not adjacent to the partition.
  • Convex recess means that the recess has a convex shape that has its greatest width at the outer edge of the surface element and that decreases in width along the surface element towards the partition. The width is measured along the surface of the surfel.
  • a recess is the complete absence of the material of the surface element, ie the recess extends over the entire thickness of the surface element and does not only represent a thinning of the surface element in a certain area.
  • the convex recesses reduce the area of the surface element as the distance from the partition wall increases, so that the heat-conducting cross-sectional area of the surface element is reduced.
  • the reduced surface area of the surface elements advantageously offers a low frictional pressure loss of the fluid flowing around.
  • the mass of the surface element is further reduced due to the reduced material consumption or it is possible to carry out the surface element without increasing the mass of the surface element by means of the reinforcing beads or by increasing the thickness of the surface element.
  • the reinforcing beads Due to their increased material thickness, the reinforcing beads contribute locally to improving heat conduction. As a result, the combination of the plurality of convex recesses and intermediate reinforcing beads improves the temperature profile along the surface element and contributes to homogenizing the temperature of the surface element and increasing the heat transfer performance.
  • the heat exchanger can be a liquid-gas heat exchanger, for example a water-air heat exchanger.
  • the heat exchanger can be designed as a finned tube heat exchanger as described above, with the dividing wall between the first fluid (eg water) and the second fluid (eg air) being formed by the tube wall of the tube or tubes.
  • the fluids water and air are to be understood as pure examples that can also stand for other liquid and gaseous fluids.
  • the inner sides of the tube can be in contact with a liquid, first fluid. The heat transfer resistance is low at this interface due to the liquid state of aggregation of the first fluid. Accordingly, there is no need to increase the surface area on the inside of the pipes.
  • a gas flow is conducted in a cross-flow, the main flow direction of which runs perpendicularly to the pipe axis.
  • the interfaces on the outside of the tubes that are in contact with the gaseous second fluid have a higher heat transfer resistance per unit area of the partition surface.
  • the surface of the partition of the heat exchanger according to the invention is enlarged on at least this side by ribs in the form of the surface elements described.
  • Such surface-enlarging surface elements can be used in others according to the invention
  • Heat exchangers can also be arranged on both sides of the partition wall, for example in a gas-gas heat exchanger.
  • the surface elements can have any shape. For example, square, round or oval shapes of the surface elements are usual. Furthermore, the shape of the surface element can be adapted to the cross section of the pipe, so pipes with a circular cross section can have surface elements with a round circular shape.
  • the reinforcing beads extend over the entire height of the surface element, i.e. up to the outer edge of the surface element.
  • the reinforcing beads taper along the height of the surface elements from the partition. “Tapering” means that the cross-sectional area of the reinforcing beads decreases from the partition along the height of the surface element to the outer edge of the surface element. The cross-sectional shape of the reinforcing beads is retained.
  • the apex of the convex recesses is at 40% of the total height of the surface element.
  • the convex recesses are formed in the shape of a parabola.
  • the heat-conducting cross-section of the surface element increases quadratically with the radius of the surface element, so that the area of the surface elements is effectively reduced by parabolic recesses.
  • the heat exchanger is a finned tube heat exchanger with at least one tube for a first fluid to flow through inside the tube and with surface elements that increase the surface of the tube on the outside, around which a second fluid can flow in cross flow to the first fluid.
  • the tube forms the partition of the heat exchanger.
  • the UI elements are at Finned tube heat exchangers referred to as fins.
  • the surface elements or ribs are formed protruding from the tube and have reinforcing beads, the reinforcing beads extending away from the tube.
  • the thermal conductivity of the fins of finned tubes is a material property of the material used to manufacture the fins. For a large heat flow, a large cross-sectional area transverse to the direction of heat conduction is required.
  • the heat exchanger according to the invention uses surface elements as ribs, which have reinforcing ridges spaced apart from one another and surface areas of smaller thickness between the reinforcing ridges. Because of their small thickness, these surface areas have a high thermal resistance.
  • the reinforcement beads on the other hand, have a larger cross-section and a low thermal resistance, which is also sufficiently small for heat transport over greater lengths.
  • the reinforcing beads are in cross-section in contact with the tube or the tube wall or other partition and extend away from the tube. In other words, the reinforcing beads are orthogonal or at an angle to the tube wall, but not parallel or otherwise spaced from the tube wall.
  • the reinforcing beads extend orthogonally to the surface of the tube.
  • the reinforcing beads can extend radially and in the case of flat partitions orthogonally to the partition, so that the heat is conducted away from or towards the partition in a short distance.
  • the reinforcement beads can also run differently towards the tube for geometric or flow-related reasons.
  • the diameter of the circular cross-section of the reinforcing beads on the partition wall is at least twice the thickness of the surface element.
  • the reinforcing beads and the convex recesses of adjacent surface elements are offset from one another, forming an offset in a direction of flow of the second fluid between the surface elements.
  • the tube of the finned tube heat exchanger is designed as an oval tube, the cross section of which is formed from two semicircles and two straight lines connecting the semicircles.
  • the surface elements are oval in shape and are arranged in a plane orthogonal to a longitudinal axis of the tube. Adjacent surface elements are arranged parallel to one another along the longitudinal axis of the tube
  • the reinforcement beads can be positioned almost perpendicularly to the flow, parallel and at a constant distance from one another. In this way, a maximized convective heat transfer between adjacent surface elements can be achieved. Due to the offset reinforcement beads in surface elements that are opposite one another, i.e. adjacent to one another, a wavy flow can be formed, which further improves the heat transfer.
  • the length of the straight line of the cross section of the oval tube is at least once as large as the diameter of the semicircle of the cross section of the oval tube, in particular 2.5 times as large.
  • high heat transfer can be achieved at the large, straight areas of the oval tube and the areas of the surface element adjoining them.
  • the heat exchanger 1 shows an embodiment of the heat exchanger 1 according to the invention, specifically a finned tube heat exchanger, in a perspective view in part.
  • the oval tube 2 can be seen in the center of the object shown.
  • the walls of the tube 2 are partitions between a first fluid inside the tube 2 and a second fluid outside the tube 2. Heat is exchanged between the first and the second fluid through the partition or the tube wall without the first and the second Fluid come into physical contact with each other.
  • the tube On the outside, the tube has 2 surface-enlarging ribs, which give the finned-tube heat exchanger its name.
  • the ribs connected to the tube are designed as low-volume and essentially two-dimensional surface elements 3 .
  • the surface elements 3 have pin-shaped reinforcing beads 4 with a round cross section. These reinforcing beads 4 extend from the pipe 2 to the outer edge 31 of the surface elements 3. Between the reinforcing beads 4, the surface element 3 has surface areas 5 which are less thick than the reinforcing beads 4.
  • the reinforcement beads 4 are massive material thickenings of the material of the surface element 3, which in the illustrated embodiment extends over the entire height of the surface element 3 up to the outer edge 31 extend and taper outwards.
  • the reinforcement beads 4 thus have a large cross-sectional diameter directly at the interface with the pipe 2, while the diameter of the reinforcement beads 4 on the outer edge 31 of the surface element 3 is equal to or only slightly larger than the thickness of the surface areas 5.
  • the reinforcement beads 4 improve the heat transport within the surface element 3 from the pipe 2 to the outer edge 31 or vice versa, as is exemplified by the arrows in three reinforcing beads 4.
  • the direction of the heat transport depends in a known manner on which of the two fluids inside the tube 2 and outside the tube 2 is warmer.
  • the surface element 3 has convex recesses 6 in the area of some of the surface areas 5, which extend from the outer edge 31 of the surface element 3 in the direction of the tube 2 and thereby reduce in width.
  • the width of one of the recesses 6 is measured along the areal extent of the surface element 2 and thus perpendicular to the thickness of the surface element 3 .
  • the recesses 6 represent the complete absence of the material of the surface element 3 in the area of the recesses.
  • the recesses 6 do not extend to the tube 2, but only up to a defined height within the surface element 3, the height starting from the outer surface of the Tube 2 is measured.
  • the apex of the recess 6 is thus at this defined height, which is greater than or equal to 30% and less than or equal to 70% of the height of the surface element 3 .
  • the height of the surface element 3 is the maximum height of the outer edge 31 of the surface element 3.
  • the recesses 6 are parabolic and extend up to a height of about 40% of the height of the surface element 3.
  • the convex recesses 6 serve to reduce the heat-transferring surface of the surface element 3 with the height, starting from the tube 2. This avoids an increase in the heat-conducting cross-sectional area of the surface element with increasing height. Since such an increase in the thermally conductive cross-sectional area occurs primarily in areas of the surface element 3 which adjoin round areas of the tube 2, the recesses 6 are mainly formed in these areas in the exemplary embodiment shown. On the other hand, the increase in cross-sectional area does not occur or occurs only to a small extent in surface areas 5 adjoining the straight areas of the oval tube 2 used here, so that these surface areas 5 cannot have any recesses 6 . In the exemplary embodiment shown, this is the case at least for some of the surface areas 5 .
  • figure 2 shows a section of the heat exchanger from figure 1 schematically in a side view of the tube 2. To avoid repetition, reference is made to the description of FIG figure 1 referred.
  • FIG figure 1 shows two surface elements 3 arranged parallel to one another, with the reinforcing beads 4 and in the straight area 21 also the surface areas 5 being clearly visible, while the recesses are not visible.
  • the flow of the second fluid outside of the tube 2 is shown schematically using streamlines 7 .
  • the reinforcing beads 4 and the recesses disturb laminar flow between adjacent surface elements 3 by causing turbulence. The turbulence improves the heat transfer between the second fluid and the surface element 3.
  • FIG. 3 and 4 is a very concrete design example of the finned tube heat exchanger from the figures 1 and 2 shown in two different views along the tube 2 and transverse to it.
  • the tube 2 is designed here as an oval tube, which is the figure 2 shown flow with the streamlines 7 with the same cross-section opposes a lower resistance than a round tube of the same cross-sectional size.
  • the concrete oval tube has an outside diameter 9 of 16 mm of its semi-circular portions and a length 10 of the straight side portions 21 of 18 mm.
  • the ratio of the straight length 10 to the diameter 9 is greater than 1, in the present case 1.125.
  • the exact size of this ratio can be used as an optimization parameter when designing the heat exchanger based on given framework conditions.
  • the surface element 3 has a height 11 of 44.5 mm, which is measured from the outer surface of the tube 2 in the straight area 21 to the outer edge 31 of the surface element 3 .
  • the recesses 6 have a width 12 of 21 mm on the outer edge 31 of the surface element 3 and extend from the outer edge 31 over a length 13 of 26.5 mm in the direction of the tube 2. The apex of the recesses 6 is therefore at approx. 40% of height 11.
  • the reinforcing beads 4 have a diameter 14 of 4 mm at the boundary surface with the tube 2 , which diameter decreases continuously towards the outer edge 31 of the surface element 3 .
  • the surface areas 5 have a small thickness 15 of only 1 mm and the reinforcing beads 4 with a maximum diameter of 4 mm have an enlarged cross-section compared to the surface areas 5 or a thickness four times greater. That The ratio of the maximum diameter of a reinforcing bead to the thickness of a surface area can also be different, but it should be greater than or equal to 2.
  • Two adjacent surface elements 3 are arranged parallel to one another along the tube 2, ie along the direction of flow of the fluid inside the tube 2, at a distance 16 of 12 mm.
  • the left-hand surface element 3 has three reinforcing beads 4 in the flat surface area, the straight area 21, of the oval tube 2.
  • the right-hand surface element 3, has only two reinforcing beads 4 in the same detail, with the reinforcing beads 4 being offset from one another on the adjacent surface elements. This misalignment of the reinforcement beads 4 and also of the recesses in 4 are not recognizable, continues over the entire extent of the two surface elements 3.
  • figure 5 shows the heat flux density achieved using a finned tube with 18 surface elements for a given face velocity of the fluid flowing around the finned tube and surface elements.
  • the curve with the solid boxes shows the measured heat flux for a fabricated finned tube with conventional surface elements, ie with surface elements without reinforcing beads and without recesses, while the curve with the empty boxes shows the measured heat flux for a prototype finned tube with surface elements according to the present invention shows, the external dimensions of the tube and the surface elements and the material used were the same in each case.
  • the heat flow density is up to 90% higher than when using conventional surface elements.
  • the adjacent surface elements 3 are mounted on a tube 2 . In other examples, not shown, adjacent surface elements 3 are mounted on adjacent tubes 2 and the ribs of adjacent tubes engage in a comb-like manner. A person skilled in the art can derive further exemplary embodiments on the basis of the above examples in adaptation to a given task

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (11)

  1. Échangeur de chaleur (1) comportant au moins une cloison et des éléments de surface (3) faisant saillie au moins depuis un côté de la cloison et agrandissant la surface de la cloison, lesquels peuvent être parcourus par un fluide,
    dans lequel
    - les éléments de surface (3) comportent des renflements de renforcement (4) et des zones de surface (5) situées entre les renflements de renforcement (4), dans lequel les renflements de renforcement (4) s'étendent à partir de la cloison et présentent une forme de section transversale circulaire ou ovale,
    - les renflements de renforcement (4) s'étendent, à partir de la cloison, sur au moins une partie de la hauteur de l'élément de surface (3), et
    - les éléments de surface (3) comportent une pluralité d'évidements (6) convexes, dans lequel chacun des évidements (6) convexes est disposé dans l'une des zones de surface (5) entre deux renflements de renforcement (4) et s'étend depuis un bord extérieur (31) de l'élément de surface (3), dans lequel leur sommet sont à une hauteur supérieure ou égale à 30 % et inférieure ou égale à 70 % de la hauteur totale de l'élément de surface (3), dans lequel la hauteur est mesurée à partir de la cloison.
  2. Échangeur de chaleur (1) selon la revendication 1, caractérisé en ce que les renflements de renforcement (4) s'étendent sur toute la hauteur de l'élément de surface (3).
  3. Échangeur de chaleur (1) selon la revendication 1 ou 2, caractérisé en ce que les renflements de renforcement (4) se rétrécissent le long de la hauteur des éléments de surface (3) à partir de la cloison.
  4. Échangeur de chaleur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le sommet des évidements (6) convexes se trouve à 40 % de la hauteur totale de l'élément de surface (3).
  5. Échangeur de chaleur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que les évidements (6) convexes sont réalisés en forme de parabole.
  6. Échangeur de chaleur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que l'échangeur de chaleur (1) est un échangeur de chaleur à tubes à ailettes, comportant au moins un tube (2) permettant l'écoulement d'un premier fluide à l'intérieur du tube (2) et comportant les éléments de surface (3) agrandissant la surface du tube (2) vers l'extérieur et pouvant être parcourus par un second fluide dans un flux croisé par rapport au premier fluide, dans lequel le tube (2) forme la cloison de l'échangeur de chaleur (1).
  7. Échangeur de chaleur (1) selon la revendication 6, caractérisé en ce que les renflements de renforcement (4) s'étendent orthogonalement à la surface du tube (2).
  8. Échangeur de chaleur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le diamètre (14) de la section transversale circulaire des renflements de renforcement (4) sur la cloison est au moins le double de l'épaisseur (15) des éléments de surface (3).
  9. Échangeur de chaleur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que les renflements de renforcement (4) et les évidements (6) convexes des éléments de surface (3) adjacents sont disposés décalés les uns par rapport aux autres en formant un décalage (8) dans une direction d'écoulement du second fluide entre les éléments de surface (3).
  10. Échangeur de chaleur (1) selon les revendications 6 et 9, caractérisé en ce que le tube (2) de l'échangeur de chaleur à tubes à ailettes est conçu sous la forme d'un tube ovale, dont la section transversale est formée par deux demi-cercles et deux lignes droites reliant les demi-cercles, les éléments de surface (3) présentent respectivement une forme ovale et sont disposés dans un plan orthogonal à un axe longitudinal du tube et des éléments de surface (3) adjacents sont disposés parallèlement les uns aux autres.
  11. Échangeur de chaleur (1) selon la revendication 10, caractérisé en ce que la longueur (10) de la ligne droite de la section transversale du tube ovale est au moins une fois supérieure au diamètre (9) du demi-cercle de la section transversale du tube ovale.
EP19805232.6A 2018-11-26 2019-11-14 Échangeur de chaleur comprenant des éléments de surface ayant des cavités convexes et des épaississements de matériau intégrés Active EP3850293B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018129788.2A DE102018129788B3 (de) 2018-11-26 2018-11-26 Wärmeübertrager mit konvexen Aussparungen der Rippenflächen und integrierten Materialaufdickungen
PCT/EP2019/081270 WO2020109013A1 (fr) 2018-11-26 2019-11-14 Échangeur de chaleur comprenant des éléments de surface ayant des cavités convexes et des épaississements de matériau intégrés

Publications (2)

Publication Number Publication Date
EP3850293A1 EP3850293A1 (fr) 2021-07-21
EP3850293B1 true EP3850293B1 (fr) 2022-05-25

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EP19805232.6A Active EP3850293B1 (fr) 2018-11-26 2019-11-14 Échangeur de chaleur comprenant des éléments de surface ayant des cavités convexes et des épaississements de matériau intégrés

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EP (1) EP3850293B1 (fr)
DE (1) DE102018129788B3 (fr)
WO (1) WO2020109013A1 (fr)

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Publication number Priority date Publication date Assignee Title
CN112312752B (zh) * 2020-11-27 2024-04-16 浙江工业大学 一种可用于大功率机车的管片式散热器的优化结构

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE160351C (de) 1904-04-07 1905-05-10 Heiz- oder kuhlkörper
GB436656A (en) 1934-04-16 1935-10-16 Francis William Green Improvements in heat-exchange tubes
US2402262A (en) * 1943-08-30 1946-06-18 American Coils Co Heat exchange fin
DE1910549U (de) * 1964-12-11 1965-02-25 Chester H Kirk Lamellenrohr fuer heiz- und kuehlzwecke.
CH435346A (de) 1964-12-11 1967-05-15 Howard Kirk Chester Lamellenrohr für Heiz- oder Kühlzwecke
US3311163A (en) 1965-06-25 1967-03-28 Twin Temp Inc Heat exchanger
CH435436A (it) 1966-04-22 1967-05-15 Thomson Italiana Societa Per A Dispositivo elettronico per la frenatura mista di motori elettrici trifasi per mezzo di condensatori e di corrente continua
DE7020851U (de) 1970-06-04 1970-09-03 Benteler Werke Ag Waermeaustauscher fuer heiz- und kuehlgeraete.
DD283299A7 (de) * 1988-07-25 1990-10-10 Veb Schwermaschinenbau "Karl Liebknecht" Magdeburg,Dd Rippenrohr mit profil
DE4207597A1 (de) 1992-03-10 1993-09-23 Zl Cryo Technik Gmbh Industrie Waermeaustauschelement und waermetauschereinheit
JPH0979357A (ja) * 1995-09-19 1997-03-25 Daihatsu Motor Co Ltd 車両のフィン付冷却パイプ構造
DE20021348U1 (de) * 2000-12-16 2001-05-10 Pluggit International N.V., Curaçao, Niederländische Antillen Kanalrohr
US20100282456A1 (en) * 2009-05-06 2010-11-11 General Electric Company Finned tube heat exchanger

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DE102018129788B3 (de) 2019-10-24
EP3850293A1 (fr) 2021-07-21
WO2020109013A1 (fr) 2020-06-04

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