EP3650799B1 - Corps d'ailette pour un tube d'échange de chaleur - Google Patents

Corps d'ailette pour un tube d'échange de chaleur Download PDF

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Publication number
EP3650799B1
EP3650799B1 EP18382793.0A EP18382793A EP3650799B1 EP 3650799 B1 EP3650799 B1 EP 3650799B1 EP 18382793 A EP18382793 A EP 18382793A EP 3650799 B1 EP3650799 B1 EP 3650799B1
Authority
EP
European Patent Office
Prior art keywords
heat exchange
exchange tube
fin body
plane
wavy
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP18382793.0A
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German (de)
English (en)
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EP3650799A1 (fr
Inventor
Sonia Civeira Domínguez
Antonio VIDE LINARES
Alejandro VARGAS CURTO
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BorgWarner Emissions Systems Spain SL
Original Assignee
BorgWarner Emissions Systems Spain SL
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by BorgWarner Emissions Systems Spain SL filed Critical BorgWarner Emissions Systems Spain SL
Priority to EP18382793.0A priority Critical patent/EP3650799B1/fr
Priority to US16/675,900 priority patent/US20200217596A1/en
Priority to CN201911082041.9A priority patent/CN111156852A/zh
Publication of EP3650799A1 publication Critical patent/EP3650799A1/fr
Application granted granted Critical
Publication of EP3650799B1 publication Critical patent/EP3650799B1/fr
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Anticipated expiration legal-status Critical

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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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
    • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • the present invention relates to a fin body intended for being housed inside a heat exchange tube which is one from among heat exchange tubes showing a planar configuration.
  • the fin body is configured in the form of a plate, this plate being the one inserted into the heat exchange tube.
  • the plate is configured from a metal sheet bent into a plurality of consecutive bends. Each of the bends extends along a longitudinal direction which will be identified as Z and is oriented, in the operating position, in the longitudinal direction of the exchange tube.
  • the invention is characterized by the configuration of the plate of the fin body according to a transverse section with respect to direction Z.
  • transverse will be understood to be synonymous to perpendicular.
  • the bends show a profile defining a periodic zigzag wavy path with a characteristic width s and a characteristic height h , both measured on said path.
  • the wavy path follows the midplane of the metal sheet having a thickness e , so the plate height will be h + e since on one of the faces of the plate the thickness contributes an amount of e/2 to the plate height with respect to the position of the path and another amount of e/2 on the opposite face of the plate.
  • the measurement that can be most readily measured is h out and the thickness e , and they both allow determining h .
  • the plate is supported on the inner faces thereof such that the bends form channels.
  • the characteristic width s used for determining s ch is defined throughout this description as half the wavelength of the wavy path and the characteristic height h used for determining h ch is defined as the distance between peaks of maximum amplitude of the wavy path.
  • the properties of the plate expressed, for example, by means of correlations of efficiency or a pressure drop will be established from the channel width s ch and plate height h out unless it is explicitly specified that they are other variables.
  • the invention is characterized by a range of the channel width s ch to plate height h out ratio in the interval of 0.15-0.5, and according to more specific cases, in the lower subranges.
  • the fin gives rise to a heat exchange tube with a higher efficiency than fins known in the state of the art without penalizing the pressure drop.
  • Heat exchangers intended for reducing the temperature of hot exhaust gases by transferring heat to a liquid coolant. Heat exchangers of this type are found in exhaust gas recirculation (EGR) systems.
  • EGR exhaust gas recirculation
  • Another field of application of interest are heat recuperators where heat is transferred to a second fluid which allows making subsequent use of the heat extracted from the hot gas.
  • other applications are exchangers for acclimatizing or controlling the temperature of the vehicle.
  • the technical problem to be solved is that of providing an exchange tube configuration and elements which increase heat exchange in the exchange tube without penalizing the pressure drop or with the pressure drop being minimal.
  • the present invention solves the technical problem being considered by proposing designs that are close to the limits of manufacturability which, although possible, are hard to achieve, and which a designer tends to not use. These designs are characterized by a wavy aspect ratio in a very narrow range of values where it has been experimentally proven that, far from what was expected, efficiency values that are surprisingly higher than those obtained in the state of the art and with low pressure drops have been obtained.
  • the invention relates to a fin body intended to be housed inside a heat exchange tube having a planar configuration. Once the fin body has been housed therein, the heat exchange tube is provided with fins considerably increasing the heat exchange area when hot gas flows through the inside thereof in the operating mode.
  • the configuration of the heat exchange tube is a constraint because by housing the fin body therein, the tube has walls closing the space where said fin body is housed and the attachment between both elements is established in these inner walls. Specifically, the attachment is established on the faces of the exchange tube which are shown as planar inner faces, parallel to and facing one another.
  • the heat exchange tube extends along a longitudinal direction which will be identified throughout the text as X-X'.
  • the exchange tubes have a planar configuration comprising two planar inner faces, parallel to and facing one another.
  • the planar faces will have a pre-established constant width and are connected on the sides through a straight or curved wall.
  • the fin body is configured in the form of a plate and formed from a metal sheet having a thickness e, bent into a plurality of consecutive bends extending according to a direction Z, where the direction Z is intended for being parallel to the longitudinal direction X-X' of the heat exchange tube housing it.
  • the fin body is a planar plate configured from a metal sheet with a specific width configured for enabling the housing thereof in the heat exchange tube and also a length suited to the length of the heat exchange tube.
  • the plate height is achieved by means of folds of the metal sheet.
  • a method for manufacturing this sheet is by stamping between two molds, or according to a second example, the method is a continuous method, by rolling the metal sheet between two rollers with opposite or complementary configurations.
  • the bends of the sheet give rise to the fin plate height.
  • the height is identified as defined in the description above as “h out " and is different from and strictly greater than the value of the thickness of the metal sheet which will be identified with the letter "e”.
  • the bends of the plurality of bends are parallel to one another, both when they are straight bends and when they are curved wavy shapes, and extend along a direction which has been identified as direction Z.
  • This direction is the longitudinal direction of the tube when the fin body is operatively housed inside the tube.
  • the direction Z is the direction in which said generatrix extends.
  • a specific case of a wavy generatrix is a sine wave.
  • the direction Z will be the axis around which the sine wave oscillates.
  • the bends are configured by alternating between a first plane P 1 and a second plane P 2 parallel to the first plane P 1 , and with both planes being spaced from one another, wherein the first plane P 1 and the second plane P 2 are intended to coincide with the planar inner faces of the heat exchange tube, parallel to and facing one another;
  • the bends give rise to a constant height h out in the entire plate and are limited between two parallel planes identified as P 1 and P 2 .
  • This condition allows the plate to be housed inside the heat exchange tube having a planar configuration, such that the plate is in contact with its parallel inner faces.
  • Transverse section P T is understood to be the section according to a plane perpendicular to direction Z.
  • the transverse section P T of the fin body formed by bends results in a wavy path.
  • the two different wavy shapes that appear throughout the description must be differentiated:
  • the term "longitudinal wavy shape” will be used in the description for the first wavy shape, or it will be associated with direction Z.
  • the term “longitudinal” is excluded or the wavy shape is associated with transverse section P T .
  • the present invention relates to a fin body suitable for being inserted in a heat exchange tube having a planar configuration.
  • the heat exchange tube with the fin body is particularly suitable for heat exchangers which transfer heat energy between a hot gas and a liquid coolant. It is indicated as suitable because the use of the fin body is not limited to this application, such that the fluids transferring heat energy may be other fluids.
  • the heat exchange tube In the operating mode, the heat exchange tube is housed in a chamber through which the liquid coolant flows.
  • the hot gas flows through the inside of the heat exchange tube and transfers part of the heat energy to the tube, and the heat exchange tube in turn transfers the same heat energy to the liquid coolant. Heat transfer from the hot gas to the tube is considerably increased due to the increase of the exchange surface due to the presence of the fin body.
  • the fin body once inserted in the exchange tube and attached thereto, gives rise to a set of channels (CH) extending along the longitudinal direction X-X' of the tube, guiding the hot gas flow, generating turbulence and offering a larger exchange area.
  • CH channels
  • CH The configuration of the channels (CH) increases the area of exchange with the hot gas but also increases the pressure drop, so the configuration that these channels must have in order to increase efficiency without a significant pressure drop is not obvious.
  • Figure 1 shows a first embodiment of the invention, where the fin body (1) is configured from a metal sheet having a thickness e , which metal sheet has been stamped between two molds having a complementary shape.
  • the fin body (1) is in the form of a plate having a height h out , this height being obtained by means of a plurality of bends of the metal sheet.
  • the front part corresponds to any transverse section PT with respect to the plate along coordinate Z, and shows a profile according to a first wavy shape which, in this drawing, is shown with a thick line, with the thickness e of the sheet giving rise to the fin body.
  • Figure 5 shows a significantly enlarged first wavy shape according to an embodiment which allows viewing in greater detail the geometric aspects of a transverse section PT of an embodiment.
  • This fist wavy shape according to the transverse section PT defines a path (T) having a zigzag configuration.
  • the path (T) follows the midplane of the metal sheet, and it is shown in Figure 5 with a discontinuous line.
  • the bends of the metal sheet are demarcated between a first plane P 1 and a second plane P 2 limiting the main faces of the fin body (1) in the form of a plate.
  • the fist wavy shape shows vertices (1.2) at the ends corresponding to the contact points of the sheet with the planes P 1 and P 2 .
  • the vertices (1.2) are connected by means of segments (1.1). These segments (1.1) have a straight central part perpendicular to planes P 1 and P 2 , and the ends (1.3) of these segments (1.1) directly connecting with the vertices (1.2) are curved ends.
  • a way of expressing that the straight central part is perpendicular to planes P 1 and P 2 is by asserting that such central parts are parallel to the normal to any of the planes P 1 and P 2 .
  • the path (T) of the fist wavy shape is periodic and allows defining a characteristic distance which, in this description, is referred to as characteristic width (s), and corresponds to half the period of the path (T) of the fist wavy shape.
  • the characteristic width (s) of any path (T) of the fist wavy shape can be measured as the distance between two consecutive points of the intersection between the path (T) of the fist wavy shape and a midplane P M located at a distance h /2 from plane P 1 or P 2 .
  • the thickness reduces the characteristic width by an amount of e /2 on each of the sides of the channel (CH), giving rise to a smaller channel width s ch .
  • the configuration of the wavy path (T) of Figure 5 is different from the wavy path (T) of the first example, the definitions and ratios between distances defined by the wavy path (T) and the dimensions of the channels reduced by the thickness of the metal sheet are likewise valid.
  • the present invention is characterized by a first mode of configuring this first embodiment, where the channel width ( s ch ) to plate height ( h out ) ratio is in the interval of [0.15-0.5] . It has been found that in this interval, efficiency exceeds the value by 3.7% with respect to the best designs of the state of the art.
  • a second wavy shape extending along direction Z is seen.
  • the second wavy shape can be represented, for example, by the curve defining any of the vertices (1.2) when they extend along direction Z.
  • This curve can be considered a generatrix of the surface defined by the metal sheet of the fin body (1).
  • Two wavy paths (T) corresponding to two different transverse planes PT therefore give rise to two directrices which, together with the generatrix defined above, allow generating the surface established by the bent sheet of the fin body (1).
  • the fin body (1) only shows the first wavy shape given that the bends are straight according to direction Z.
  • a straight segment parallel to any of the planes (P 1 , P 2 ) is placed in the position of the vertices (1.2) for increasing the welding area with the tube intended for housing the fin body (1).
  • FIG 2 shows a heat exchange tube (2) housing a fin body (1) like the embodiment described and shown in Figure 1 .
  • the heat exchange tube (2) has a planar configuration and shows a planar lower wall and a planar upper wall connected on both sides through a curved wall, in this embodiment in the form of a circular half-arc according to the transverse section.
  • the heat exchange tube (2) has straight side walls of the tube, resulting in it having a section with a rectangular configuration.
  • the heat exchange tube (2) extends according to a longitudinal direction which is identified as X-X'. Once the fin body (1) has been housed, the direction Z along which the plurality of bends extends is parallel to direction X-X' of the heat exchange tube (2).
  • the heat exchange tube (2) shows a first planar inner face (2.1) which is shown in the lower part according to the orientation of Figure 2 , and a second planar inner face (2.2) located opposite the first planar inner face (2.1). These two faces (2.1, 2.2) are in contact with the fin body (1) and they are also the contact sites where they are attached to one another by brazing.
  • the heat exchange tube (2) shows a plurality of punched spots (2.3) which assure the position of the fin body (1) with respect to the heat exchange tube (2) before carrying out the welding step.
  • the punched spots (2.3) generate inner projections or protrusions which coincide with some channels (CH) of the bends of the fin body (1).
  • the channels (CH) formed by the bends of the fin body (1) are identified.
  • the fist wavy shape identified on the transverse section generates, in an alternating manner, a channel (CH) closed by the lower inner face (2.1) and a channel (CH) closed by the upper inner face (2.2) .
  • Figure 3 shows a plan view of the same fin body (1), where the second wavy shape identified, for example, by the path of the vertices (1.2) of the bends of the metal sheet according to a projection on the horizontal plane, is shown along direction Z.
  • the longitudinal wavy path has an r/p ratio between the minimum characteristic radius (r) of the wavy shape, defined as the minimum radius of curvature measured in a projection according to a plane parallel to plane P 1 or P 2 , and the pitch (p) that is smaller than 2, defined as the entire length of a wave of the wavy shape also measured on the same plane, more preferably in the interval of [0.2-1], and more preferably in the interval of [0.4 and 0.5].
  • Both measurements are depicted in Figure 3 .
  • This Figure 3 shows the longitudinal wavy path where the wavy shape has an area of tangency between the concave curve segment and the convex curve segment. In this area of tangency, the radius becomes infinite (it is an inflection point), hence the curvature becomes maximum when the radius is minimum, and it is in this region where the radius is minimum, where the figure shows the limitation of said minimum characteristic radius (r).
  • the longitudinal wavy path is configured by the concatenation of curved segments with a constant radius, alternating the curvature on both sides according to the projection on the horizontal plane of the fin body (1).
  • Figure 4 shows a perspective view of a fin body (1) according to a second embodiment, where the bends of the metal sheet are configured such that the path (T) of the fist wavy shape defined through the transverse section PT is different from that of the first embodiment.
  • the wavy path (T) shows a periodic wave configuration formed by segments (1.1) connected by alternately located vertices (1.2) .
  • the bends of the plate of the fin body (1) are limited between an upper plane (P 1 ) and a lower plane (P 2 ), and where the wavy path (T) has in its intermediate part straight and oblique segments.
  • a rectangle has been depicted with a thick dotted line on the perspective view of the fin body (1), said rectangle identifying a portion of the drawing that has been enlarged in the top right part.
  • the thickness e of the metal sheet and the manner in which the path (T) of the fist wavy shape is configured according to the transverse section according to the plane P T can be seen in this enlarged area. Given that the thickness e is small, Figure 5 shows in greater detail the path (T) of the fist wavy shape with a discontinuous line.
  • the path (T) is mainly formed by the straight and oblique intermediate parts of the segments (1.1) connected by vertices (1.2). These straight intermediate parts are connected at the vertex (1.2) by means of a curved portion (1.3).
  • two consecutive straight intermediate parts have been prolonged by means of respective dotted lines so as to identify the angle of inclination of these oblique surfaces of the bend which, once inserted in the heat exchange tube (2), give rise to channels (CH) having an essentially triangular configuration.
  • the trace of the midplane (PM) where the characteristic width (s) can be determined is identified with a discontinuous line both in the fin body (1) and in the enlarged area.
  • the attachment between the fin body (1) and the inner face (2.1, 2.2) of the heat exchange tube (2) is performed through the generatrix that goes through the vertex of the bend (V) coinciding with the vertex (1.2) of the wavy path (T).
  • the vertex of the bend (V) is distinguished from the vertex (1.2) of the path (T) as graphically shown in Figure 5 . If the attachment is performed by means of brazing, there will be a meniscus (M) on each side of the vertex (1.2) as schematically shown on the right side of the enlarged area.
  • the position of the upper inner face (2.2) of the heat exchange tube (2) is schematically shown by means of a discontinuous line and the meniscus (M) of molten metal giving rise to the fin body (1) being welded by brazing to the heat exchange tube (2) is shown by means of a blackened region.
  • the configuration of the channels (CH) formed by a fin body (1) such as the one of this embodiment has a triangular shape with the vertices of the triangle rounded according to a curved portion (1.3).
  • meniscus (M) gives rise to an increase of the contact area for improving attachment between the fin body (1) and the heat exchange tube (2), and also a higher heat transfer by conduction through said meniscus (M).
  • the tube (2) is formed by the consecutive stacking of stamped and stacked sheets (this configuration of heat exchangers is identified as stacked coolers).
  • a tube configuration formed by the stacking of sheets gives rise to an inner space with planar faces parallel to and spaced apart from one another which is also occupied by the fin body (1) according to any of the described embodiments.
  • a specific way to perform attachment by brazing for any of the described examples of heat exchange tubes (2) and fin body (1) is by means of a nickel brazing sheet which is interposed between the fin body (1) and the inner face (2.1, 2.2) of the heat exchange tube (2) before being passed through the oven.

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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)

Claims (11)

  1. Un corps d'ailette (1) destiné à être logé à l'intérieur d'un tube (2) d'échange de chaleur ayant une configuration plane, lequel tube d'échange de chaleur fait partie des tubes d'échange s'étendant selon une direction longitudinale X-X' et comprenant deux faces intérieures planes (2.1, 2.2) parallèles et se faisant face l'une l'autre;
    le corps d'ailette (1) est configuré selon une forme de plaque et formé d'une tôle ayant une épaisseur e, pliée en une pluralité de coudes consécutifs s'étendant selon une direction Z; la direction Z est destinée à être parallèle à la direction longitudinale X-X' du tube (2) d'échange de chaleur le logeant, et
    les coudes sont configurés en alternant entre un premier plan (P1) et un deuxième plan (P2) parallèles au premier plan (P1), et les deux plans étant espacés l'un de l'autre, le premier plan (P1) et le deuxième plan (P2) étant destinés à coïncider avec les faces intérieures planes du tube (2) d'échange de chaleur parallèles et se faisant face l'une l'autre;
    les coudes, selon une coupe transversale (PT) par rapport à la direction z, présentent une trajectoire ondulée périodique en zigzag (T),
    - ladite trajectoire ondulée (T) comprend des segments (1.1), les segments (1.1) étant reliés par des sommets (1.2) situés dans les pics d'amplitude maximale;
    - la largeur caractéristique (s) est la moitié de la longueur d'onde de la trajectoire ondulée (T) et la hauteur caractéristique (h) est la distance entre les pics d'amplitude maximale de la trajectoire ondulée (T),
    la trajectoire ondulée (T), selon la section transversale (PT), ayant un rapport largeur de canal (Sch) à hauteur de plaque (hout ) situé dans l'intervalle [0,15-0,5], avec Sch = s-e et hout = h+e,
    la section transversale en zigzag (PT) s'étendant selon la direction Z en suivant une trajectoire longitudinale ondulée, et
    ladite trajectoire longitudinale ondulée ayant un rapport caractéristique minimal rayon (r) sur pas (p), en abrégé r/p, situé dans l'intervalle [0,2, 2].
  2. Le corps (1) selon la revendication 1, dans lequel le rapport largeur de canal (Sch) sur hauteur de plaque (hout ) est situé dans l'intervalle [0,3-0,4].
  3. Le corps (1) selon l'une quelconque des revendications précédentes, dans lequel le rapport largeur de canal (Sch) sur hauteur de plaque (hout ) est situé dans l'intervalle [0,35-0,36].
  4. Le corps (1) selon l'une quelconque des revendications, dans lequel les segments (1.1) reliés par des sommets (1.2) sont droits.
  5. Le corps (1) selon l'une quelconque des revendications précédentes, dans lequel les segments (1.1) reliés par des sommets (1.2) sont obliques par rapport à la normale à l'un quelconque des plans (P1, P2).
  6. Le corps (1) selon l'une quelconque des revendications précédentes, dans lequel les segments (1.1) sont reliés aux sommets (1.2) au moyen de portions courbes (1.3) .
  7. Le corps (1) selon la revendication 1, dans lequel le rapport caractéristique minimal rayon (r) sur pas (p), en abrégé r/p, est situé dans l'intervalle [0,2-1], et de façon encore préférée dans l'intervalle [0,4, 0,5].
  8. Le corps (1) selon la revendication 1, dans lequel la trajectoire longitudinale ondulée est configurée par l'enchaînement de segments courbes à rayon constant, alternant la courbure de part et d'autre selon la projection sur le plan horizontal du corps d'ailette (1).
  9. Un tube d'échange de chaleur (2) ayant une configuration plane et s'étendant selon une direction longitudinale X-X' et avec au moins deux faces intérieures planes (2.1, 2.2), parallèles et se faisant face l'une l'autre, ledit tube comprenant un corps d'ailette (1) selon l'une quelconque des revendications précédentes logé à l'intérieur de lui, le corps d'ailette (1) étant orienté de telle sorte que:
    - le premier plan (P1) coïncide avec une première face interne (2.1) du tube d'échange de chaleur (2),
    - le deuxième plan (P2) coïncide avec une deuxième face interne (2.2) tournée vers la première face interne (2.1) du tube d'échange de chaleur (2), et
    - la direction Z du corps d'ailette (1) s'étend parallèlement à la direction longitudinale X-X' du tube d'échange de chaleur (2); et
    le corps d'ailette (1) étant fixé par soudage aux faces intérieures planes (2.1, 2.2) du tube d'échange de chaleur (2) formant des canaux (CH).
  10. Le tube d'échange de chaleur (2) selon la revendication 9, dans lequel au moins une fixation entre le corps d'ailette (1) et le tube d'échange de chaleur (10) est faite par brasage et elle est établie entre un sommet (1.2) du corps d'ailette (1) et une face interne (2.1, 2.2) du tube d'échange de chaleur (2) avec un ménisque de soudage concave (M) se courbant vers l'un quelconque des espaces adjacents.
  11. Un échangeur de chaleur comprenant au moins un tube d'échange de chaleur (2) selon la revendication 9 ou la revendication 10.
EP18382793.0A 2018-11-07 2018-11-07 Corps d'ailette pour un tube d'échange de chaleur Active EP3650799B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP18382793.0A EP3650799B1 (fr) 2018-11-07 2018-11-07 Corps d'ailette pour un tube d'échange de chaleur
US16/675,900 US20200217596A1 (en) 2018-11-07 2019-11-06 Fin Body For A Heat Exchange Tube
CN201911082041.9A CN111156852A (zh) 2018-11-07 2019-11-07 用于热交换管的翅片本体

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18382793.0A EP3650799B1 (fr) 2018-11-07 2018-11-07 Corps d'ailette pour un tube d'échange de chaleur

Publications (2)

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EP3650799A1 EP3650799A1 (fr) 2020-05-13
EP3650799B1 true EP3650799B1 (fr) 2021-12-15

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EP (1) EP3650799B1 (fr)
CN (1) CN111156852A (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6893003B2 (ja) * 2018-08-09 2021-06-23 富士電機株式会社 冷却器、半導体モジュール
JP1653096S (fr) * 2018-11-26 2020-02-17
JP1653095S (fr) * 2018-11-26 2020-02-17
JP1653094S (fr) * 2018-11-26 2020-02-17
FR3105387B1 (fr) * 2019-12-20 2021-11-26 Liebherr Aerospace Toulouse Sas Échangeur de chaleur à passages de fluide optimisés
US20210254904A1 (en) * 2020-02-19 2021-08-19 The Boeing Company Additively manufactured heat exchanger
US20220170706A1 (en) * 2020-11-30 2022-06-02 Dana Canada Corporation Compact heat exchanger with wavy fin turbulizer
CN114353391A (zh) * 2021-12-28 2022-04-15 江西鑫田车业有限公司 一种具有双波浪形翅片的冷凝器
JP2024051571A (ja) * 2022-09-30 2024-04-11 東京ラヂエーター製造株式会社 インナーフィン

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1069883A (fr) * 1975-07-14 1980-01-15 Caterpillar Tractor Co. Echangeur de chaleur a surface primaire compacte
US5372187A (en) * 1993-05-24 1994-12-13 Robinson Fin Machines, Inc. Dual corrugated fin material
DE202005009948U1 (de) * 2005-06-23 2006-11-16 Autokühler GmbH & Co. KG Wärmeaustauschelement und damit hergestellter Wärmeaustauscher
JP4756585B2 (ja) * 2005-09-09 2011-08-24 臼井国際産業株式会社 熱交換器用伝熱管
FR2962204B1 (fr) * 2010-06-30 2014-11-21 Valeo Systemes Thermiques Tube d'echangeur de chaleur, echangeur de chaleur comportant de tels tubes et procede d'obtention d'un tel tube.
JP5655676B2 (ja) * 2010-08-03 2015-01-21 株式会社デンソー 凝縮器
CN102997741B (zh) * 2012-11-30 2014-12-03 艾普尔换热器(苏州)有限公司 一种换热器翅片及其制造方法
KR101569829B1 (ko) * 2014-06-13 2015-11-19 주식회사 코렌스 Egr 가스 차압 저감용 웨이브 핀 플레이트를 갖는 열교환기

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EP3650799A1 (fr) 2020-05-13
CN111156852A (zh) 2020-05-15

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