EP3097378B1 - Entretoise de fil pour échangeur de chaleur à plaques, échangeur de chaleur à plaques comprenant une telle entretoise, et procédé du perfectionnement d'un échangeur de chaleur - Google Patents

Entretoise de fil pour échangeur de chaleur à plaques, échangeur de chaleur à plaques comprenant une telle entretoise, et procédé du perfectionnement d'un échangeur de chaleur Download PDF

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Publication number
EP3097378B1
EP3097378B1 EP15700713.9A EP15700713A EP3097378B1 EP 3097378 B1 EP3097378 B1 EP 3097378B1 EP 15700713 A EP15700713 A EP 15700713A EP 3097378 B1 EP3097378 B1 EP 3097378B1
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EP
European Patent Office
Prior art keywords
wire
support
heat transfer
segments
spacer
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EP15700713.9A
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German (de)
English (en)
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EP3097378A1 (fr
Inventor
Mircea Dinulescu
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Apex International Holding BV
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Apex International Holding BV
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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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/0075—Supports for plates or plate assemblies
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0025—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being formed by zig-zag bend plates
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted 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
    • 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
    • F28F3/022—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being wires or pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means

Definitions

  • the invention relates to a wire spacer for a plate type heat exchanger, and to a heat exchanger provided with a plurality of such wire spacers. Furthermore, the invention relates to a method for upgrading existing plate type heat exchangers.
  • a conventional plate type heat exchanger generally consists of a plurality of heat transfer plates, forming spatially separated but thermally connected fluid channels through which fluid streams with a different temperature are allowed to flow. This enables heat transfer to take place from the hotter fluid to the colder fluid.
  • a yoke portion of a U-shape for abutting the first heat transfer plate along a first support line in the direction of the fluid flow
  • second support segments e.g. a yoke portion of an inverted U-shape
  • spacing segments e.g. legs of the U-shape
  • the periodical wire spacers from US 2,595,457 have to be welded or brazed with their yoke portions to at least one of the heat transfer plates, in order to fix the orientation of the wire spacer with respect to the plates, and to provide sufficient thermal bonding for obtaining the increased effective heat transfer area.
  • the required welding or brazing complicates manufacturing of such a heat exchanger.
  • the wire spacer according to this aspect of the invention is formed by bending a stiff wire into a desired elongate shape.
  • the mechanical stiffness (or rigidity) of the wire material is sufficient to maintain the predefined wire shape during use of the heat exchanger, to properly space (i.e. maintain the desired space between) the heat transfer plates.
  • the minimally required stiffness is determined by the allowed deformations of the wire spacers and the heat transfer plates under the typical thermal gradients and mechanical stresses occurring during heat exchanger operation.
  • the wire portion perpendicular to the plates must be rigid with respect to the stresses imposed on the wire, and the wire thickness must be selected to meet this condition.
  • the heat transfer plates are 1 - 2 millimeter thick, so that the wire cross-section (or diameter, in case of a cylindrical wire) typically needs to be in the range of 2 - 4 millimeter.
  • height of the vertical portion must be 0.1 to 0.2 mm smaller than the spacing distance between the heat transfer plates, both in cold condition and during shop assembly, in order to accommodate the small deformation due to thermal gradients during operation.
  • the material of the wire should be selected based on the expected heat exchanger operating temperature and thermal gradient forces.
  • the possible wire materials are carbon steel wire (uncoated or aluminized or galvanized), various grades of austenitic stainless steel.
  • a circular wire cross-section is preferred, but other wire cross-section shapes (e.g. polygonal) are possible.
  • the wire paths jointly span the support plane parallel to and abutting the first (lower) heat transfer plate.
  • “Spanning of the plane” refers herein to providing at least three points that are non-coinciding and not co-linear, and that together define the support plane.
  • the term "wire path” refers herein to a continuous portion of the bent wire that traces out a curved or bent wire trajectory spanning at least a line but preferably spanning a portion of the support plane (e.g. by forming a semi-circular shape, a U-shape, an S-shape, or a W-shape, within the support plane). In any case, the wire paths are formed to at least jointly span the support plane comprising the first support line.
  • the first support line forms a path along the first heat transfer plate, which path may for example be linear along a first direction corresponding to the main flow direction of the fluid within the channel enclosed by the adjacent heat transfer plates, e.g. in a cross-flow plate type heat exchanger with linear fluid channels.
  • the first support line may be slightly curved, or even substantially curved so as to follow a more sophisticated trajectory, e.g. the trajectory defined by the curved fluid channels in a Z-type concurrent- or counter-flow plate type heat exchanger.
  • Each wire path extends at its path ends into respective spacing segments.
  • the spacing segments interconnect the first support segments and the second support segments in an alternating manner, and have a mechanical stiffness that is sufficiently large for keeping the first and second heat transfer plates at the desired spacing distance, as was described herein above.
  • each wire path in the wire spacer functions as a base for supporting the wire spacer, and for fixing the orientation of the wire spacer with respect to the heat transfer plates.
  • the spacing segments extend at least partially and preferably entirely along a second direction that is locally perpendicular to the first support line.
  • the second direction is perpendicular to the first direction.
  • this second direction will be perpendicular to the heat transfer surfaces of both heat transfer plates.
  • the proposed wire spacer according to this aspect allows for easy placement between two adjacent heat transfer plates, without needing further means for holding the wire spacer in the correction upright orientation.
  • the proposed wire spacers may be configured as relatively thin elongated structures, which do not occupy a significant volume.
  • bar spacers e.g. known from patent document US 5,383,516
  • plate-embossing spacers create large flow obstructions and corresponding pressure drops.
  • the wire paths of the wire spacer jointly extend bi-directionally from the first support line and along a transversal direction, which is perpendicular to the first support line and is within in the support plane.
  • the wire paths may comprise smoothly curved portions and/or connected linear segments, or various other shapes spanning the support plane.
  • any of the wire paths may comprise interconnected linear path segments that are oriented in the support plane and perpendicular to the first support line.
  • any wire path may be formed as a smoothly curved shape with its curvature spanning the support plane, e.g. a semi-circular wire path.
  • each wire path extends to at least one side of the first support line along the transversal direction, which is oriented perpendicular to the first support line.
  • the wire paths may extend toward opposite sides in an alternating manner along the wire spacer. For example, one particular wire path may extend to the positive transversal direction, while the preceding and subsequent wire paths extend to the negative (i.e. opposite) transversal direction. This alternating configuration allows fixing the orientation of the wire spacer between the heat transfer plates, while requiring a minimal amount of wire.
  • each wire path may be individually bent to extend bi-directionally along both the positive and negative transversal directions from the first support line, to span a total base width.
  • a wire path that by itself extends to both directions from the first support line allows stabilization of its orientation with respect to the first heat transfer plate.
  • the wire spacer may be formed as a periodical structure of consecutive identical units that each comprise an interconnected quadruplet formed by a first support segment, a spacing segment, a second support segment, and a further spacing segment. This periodicity greatly simplifies the manufacturing process wherein the wire is bent to form the proposed wire spacer.
  • the total base width equals the spacing distance
  • the total base width equals the spacing distance
  • an incidental occurrence of local twisting of the wire spacer about an axis parallel to the support line i.e. a rotation of wire paths in the plane spanned by the spacing direction and transversal direction
  • the rotated wire paths with a total base width matching the desired spacing distance will still locally provide a spacing function.
  • the wire path may be formed by multiple interconnected linear path segments that are arranged with their long axes directed along the transversal direction. These linear path segments may be abutting as viewed along the support line, and interconnected by short curved portions at the respective segment end points.
  • a length of the wire path viewed along the support line i.e. the first or fluid flow direction
  • the support width in the transversal direction will be maximized.
  • the wire path may be formed as one of a contracted U-shape, a contracted S-shape, or a contracted W-shape. Any one of these shapes is easily formed in a manufacturing process involving wire bending actions in the positive and negative transversal directions only. Hence, wire bending actions in the direction along the support line, which complicate the manufacturing process, are avoided.
  • the wire path is smoothly curved in the support plane.
  • the wire path forms one of a U-shape, an S-shape, or a curved W-shape.
  • a smoothly curved wire path is easily formed by bending the wire into the desired shape, without creating sharp turns or folds. Smooth curves minimize the risk of breaking the wire during construction.
  • the smoothly curved wire path provides a considerable structural support area in the support plane, while minimizing the thermal contact area between the wire spacer and the first heat transfer plate. Any one of a smoothly curved U-shape, an S-shape, or a curved W-shape, is easily formed in a manufacturing process involving wire bending actions in the transversal directions only. Hence, wire bending actions in the direction along the first support line, which would complicate the manufacturing process, are avoided.
  • the second support segments are formed by linear support segments with support lengths along the first support line.
  • the first support segments are effectively spaced along the first support line by the linear support segments.
  • the preferred lengths of these linear support segments are determined by the expected differential pressures between the adjacent channels and the operating temperatures occurring in the heat exchanger.
  • the wire spacer possesses a linear symmetry that will provide a nearly uniform linear supporting capability along the first support line.
  • the wire spacer manufacturing process is greatly simplified.
  • the support lengths are equal support lengths in the range of 100 mm - 200 mm.
  • Support lengths in the range of 100 mm - 200 millimeter allow robust spacing in a heat exchanger having heat transfer plates of 1 - 2 millimeter thickness, and operating at a differential pressure of 500 - 1000 Pa in a temperature range of 100-300 C.
  • the spacing segments are formed by perpendicular linear segments with spacing heights equal to the spacing distance.
  • the wire could extend transversely at the end of the perpendicular linear segments in addition to or in alternative to support segments along the first support line.
  • Spacing segments formed from linear segments that are oriented along the spacing direction provide maximal structural integrity and support.
  • a cross-section of the bent wire is circular.
  • a circular wire is easy and cheap to construct. Due to its cylindrical symmetry, the circular wire is easily bent into any desired elongated wire spacer shape.
  • the isotropic bending resistance of the circular wire allows bending in the transversal and spacing directions required for forming the inherently three-dimensional configuration of the proposed wire spacer according to the first aspect.
  • the circular cross section also minimizes the contact area between the wire spacer and the heat transfer plates, thereby avoiding excessive thermal gradients and resulting stresses occurring during operation of the heat exchanger (as is the case with pins or stud spacers welded to heat transfer plates, e.g. known from patent document WO96/19708 ).
  • any thermal insulation coating can be applied to the smooth surface of the circular wire spacer in an easy and durable manner.
  • a wire diameter of the bent wire is in a diameter range of 2 - 4 mm.
  • this preferred diameter range yields a wire spacer that is sufficiently rigid to prevent deformation, while still allowing the wire to be manufactured without difficulty. A thicker wire would be difficult to process, while a thinner wire would not be able to prevent deformation.
  • the bent wire has a first end and a second end, wherein each end is provided with attachment means for connecting the wire spacer to the first heat transfer plate and/or the second heat transfer plate.
  • this connection could be through electrical resistance welding or through a pin welded to the first and/or second heat transfer plates.
  • the wire spacer may be easily fixed with respect to the heat exchanger by attachment to externally accessible regions of the heat exchanger, for example to the plate edges near fluid channel apertures, or to flow guiding elements (ferrules) located at the plate edges.
  • a plate type heat exchanger as defined by claim 10.
  • the first direction corresponding to the main flow direction of the fluid within the channel enclosed by the adjacent heat transfer plates may define a straight first support line along the first heat transfer plate (like in a cross-flow plate type heat exchanger with linear fluid channels).
  • this first direction may also be construed as a local direction, which may change along the first support line. This allows the first support line to be curved along the fluid channel of the heat transfer plate (like in curved fluid channels in a Z-type concurrent- or counter-flow plate type heat exchanger).
  • the at least one wire spacer of the plate type heat exchanger is releasably positioned between the adjacent heat transfer plates, and wherein the first end and second end of the wire spacer are fixed to respective outer edges of the heat transfer plates.
  • this attachment can be made by electrical resistance welding or by welding a pin to the heat transfer plates.
  • the method according to this aspect may also represent the reassembly phase after cleaning or repairing any heat exchanger provided with the wire spacers according to the first aspect of the invention.
  • the initial phase comprises removing the wire spacers from the fluid channels of the plate type heat exchanger.
  • the heat transfer plates having the wire spacers removed are easily cleaned or repaired by suitable methods without obstruction from the wire spacers.
  • the original wire spacers or repaired substitutes are re-inserted into the fluid channels, as defined by this third aspect of the invention.
  • Fig.1 shows a perspective view of a plate type heat exchanger 1 for exchanging thermal energy between a first fluid 14 and a second fluid 16 having a different temperature.
  • the shown heat exchanger 1 comprises a number of stacked heat transfer plates 2, 4. Between each two adjacent heat transfer plates 2, 4 first fluid channels 6 and second fluid channels 8 are formed, for transporting the first fluid 14 and second fluid 16 respectively.
  • the first and second fluid channels 6, 8 are oriented mutually perpendicular, along a first direction X and a transversal direction Z respectively.
  • the first and second fluid channels 6, 8 are alternatingly provided in the heat exchanger 1 in a second (vertical) direction Y, which is perpendicular to the first direction X and the transversal direction Z.
  • This plate configuration forms a so-called cross flow plate type heat exchanger.
  • the adjacent heat transfer plates 2, 4 are spaced apart at a spacing height ⁇ y in the second direction Y.
  • Several of the first fluid channels 6 are provided with a plurality of wire spacers 20.
  • the shown wire spacers 20 comprise first support segments 24, second support segments 26, and spacing segments 28 that interconnect the first support segments 24 and the second support segments 26.
  • the first support segments 24 are formed so as to abut the first heat transfer plate 2 along a first support line C1
  • the second support segments 26 are formed so as to abut the second heat transfer plate 4 along a second support line C2.
  • the first support segments 24 are curved into wire paths 32, which jointly define a first support plane S1 that comprises the first support line C1.
  • each wire path 32 comprises three linear path segments 34a-c that are interconnected via sharply curved segments, jointly forming a contracted S-shape.
  • the linear path segments 34a-c of each wire path 32 jointly extend bidirectionally from the first support line C1, and span the first support plane S1 along both the first support line C1 and a transversal direction Z. Consequently, each wire path 32 forms a support portion that spans a total base width ⁇ z and effectively holds the wire spacer 20 steady between the heat transfer plates 2, 4, with the spacing wire segments 28 in an upright orientation.
  • the total base widths ⁇ z of the wire paths 32 equal the spacing distance ⁇ y between the second support segments 26 and the first support line C 1.
  • the second support segments 26 are formed as linear wire segments with second support lengths ⁇ x2 along the second support line C2.
  • the second support lengths ⁇ x2 of subsequent second support segments 26 are shown to be equal.
  • a typical value for the second support lengths ⁇ x2 may be in the range of 100 mm - 200 mm.
  • the spacing segments 28 interconnect the first support segments 24 and the second support segments 26 in an alternating manner.
  • the spacing segments 28 in the shown embodiments are formed as linear wire segments that are perpendicular to the first support plane S1, and which hold the second support segments 26 at a spacing distance ⁇ y from the first support line C1.
  • the spacing distance ⁇ y is preferably 0.1 to 0.2 mm smaller than a plate distance between the heat transfer plates 2, 4 of a fluid channel 6, 8 in cold condition.
  • the wire spacer 20 is manufactured from bending a wire having a circular cross-section, into a periodical structure having a multiplicity of the described segments.
  • a typical wire diameter ⁇ of the bent wire (see Fig.2a ) is in a diameter range of 2 - 4 mm.
  • each bent wire has a first wire end 6 located at one side of the first fluid channel 6.
  • the bent wire is provided with attachment means 44 for connecting the wire spacer 20 to the first heat transfer plate 2.
  • the wire spacer 20 terminates in a second end (not shown), wherein also the second end is provided with similar plate attachment means 44.
  • the wire spacers 20 are releasably positioned between the adjacent heat transfer plates 2, 4, by temporarily fixing each wire spacer 20 with its first and second ends via the attachment means 44 to respective outer edges of the first heat transfer plate 2.
  • the attachment means 44 may also be provided on an upwardly bent portion of the wire spacer 20, so as to attach the wire spacer 20 to the second heat transfer plate (4).
  • the attachment means 44 can include ends of wire being attached through electrical resistance welding or through a pin welded to the heat transfer plate 2 and/or 4.
  • each wire path 32 comprises only two linear path segments 34a, 34b that is interconnected via one sharply curved segment, and which jointly form a contracted U-shape.
  • each wire path 32 only extends in a single transversal direction Z within the first support plane S1 from the first support line C 1.
  • Consecutive wire paths 32, 32' transversally extend in opposite transversal directions, so that the wire paths 32 jointly extend bidirectionally from the first support line C 1.
  • wire spacers 20 provided with wire paths 32 formed from linear path segments and sharply curved connection segments may be conceived.
  • the wire path 32 may be formed from a contracted W-shape with four linear path segments joined by three sharply curved interconnection segments.
  • Fig.2c shows an alternative embodiment of the wire spacer 20, wherein the wire paths 32 are smoothly curved within the support plane S1, so as to form a smooth S-shape. Also in this embodiment, each wire path 32 extends bi-directionally from the first support line C1, and spans a total base width ⁇ z.
  • the wire spacer 20 in Fig.2c has a smoothly curved first support segment 24 with a first support length ⁇ x1 that is considerably larger than in the previous embodiments.
  • the wire path 32 may be formed as a U-shape, or a curved W-shape.
  • Fig. 2d shows a further alternative embodiment of wire spacer 20, wherein each wire path 32 comprises three linear path segments 34a-c that are interconnected via sharply curved segments, jointly forming a contracted S-shape, similar to the embodiment shown in Fig. 2A .
  • wire path 32 alternatingly forms first support segments 24 along line C1 and C2, with second support segments 26 and spacing segments 28 between.
  • wire spacer 20 is formed by bending the wire using only bending operations in directions transversal to a main direction along the wire spacer 20, e.g. along the first direction X (or any of the support lines C1, C2).
  • the wire path 32 may also be formed from backward or forward wire bending operations along this main direction along the wire spacer 20, although this will complicate the manufacturing process.
  • a wire spacer 20 having a more complex wire path 32 configuration may be obtained.
  • An example of such a complex wire path 32 is a (nearly) circular wire path (not shown) that starts at an end of a spacing wire 28, extends perpendicular along the transversal direction Z, curves backward along the negative first direction -X, toward the negative transversal direction -Z, toward the positive first direction X, and back along the transversal direction Z to extend into a subsequent spacing wire.
  • any combination of the wire paths 32 described above may be provided within a single wire spacer 20.

Claims (13)

  1. Séparateur filaire (20) pour séparer une première plaque de transfert thermique (2) et une deuxième plaque de transfert thermique (4) dans un échangeur de chaleur à plaques (1), dans lequel le séparateur filaire comprend un fil courbé comprenant
    - des premiers segments de support (24) en appui contre la première plaque de transfert thermique (2) le long d'une première ligne de support (C1) ;
    - des deuxièmes segments de support (26) en appui contre la deuxième plaque de transfert thermique (4) le long d'une deuxième ligne de support (C2) ;
    - des segments de séparation (28) reliant les premiers segments de support et les deuxièmes segments de support de manière alternée, et séparant les deuxièmes segments de support d'une distance de séparation (Δy) par rapport à la première ligne de support ;
    caractérisé en ce que
    les premiers segments de support (24) sont courbés selon des trajectoires de fil (32) qui définissent conjointement un plan de support (S1) comprenant la première ligne de support (C1).
  2. Séparateur filaire (20) selon la revendication 1, dans lequel les trajectoires de fil (32) s'étendent conjointement de façon bidirectionnelle à partir de la première ligne de support (C1) et le long d'une direction transversale (Z) perpendiculaire à la première ligne de support (C1) et contenue dans le plan de support (S1).
  3. Séparateur filaire (20) selon la revendication 2, dans lequel chaque trajectoire de fil (32) s'étend de façon bidirectionnelle et couvre une largeur de base totale (Δz) de préférence égale à la distance de séparation (Δy).
  4. Séparateur filaire (20) selon l'une quelconque des revendications 1 à 3, dans lequel la trajectoire de fil (32) comprend des segments de trajectoire linéaires (34) reliés couvrant la direction transversale (Z), et présente de préférence une forme parmi celles d'un U contracté, d'un S contracté ou d'un W contracté.
  5. Séparateur filaire (20) selon l'une quelconque des revendications 1 à 3, dans lequel la trajectoire de fil (32) est incurvée en douceur dans le plan de support (S1) et présente de préférence une forme parmi celles d'un U, d'un S ou d'un W incurvé.
  6. Séparateur filaire (20) selon l'une quelconque des revendications 1 à 5, dans lequel les deuxièmes segments de support sont formés par des segments de support linéaires (26) avec des longueurs de support (Δxi) le long de la deuxième ligne de support (C2), de préférence dans lequel les longueurs de support sont des longueurs de support égales (Δx) comprises entre 100 mm et 200 mm.
  7. Séparateur filaire (20) selon l'une quelconque des revendications 1 à 6, dans lequel les segments de séparation sont formés par des segments linéaires perpendiculaires (28) avec des hauteurs de séparation égales à la distance de séparation (Δy).
  8. Séparateur filaire (20) selon l'une quelconque des revendications 1 à 7, dans lequel la trajectoire de fil (32) s'étend de façon bidirectionnelle à partir de la deuxième ligne de support (C2) et le long d'une direction transversale (Z) perpendiculaire à la deuxième ligne de support (C2).
  9. Séparateur filaire (20) selon l'une quelconque des revendications 1 à 8, dans lequel une section transversale du fil courbé est circulaire, et en particulier dans lequel le diamètre de fil (Ø) du fil courbé est compris dans une gamme de diamètre de 2 à 4 mm.
  10. Séparateur filaire (20) selon l'une quelconque des revendications 1 à 9, dans lequel le fil courbé présente une première extrémité (40) et une deuxième extrémité (42), dans lequel chaque extrémité est pourvue de moyens de fixation (44) pour relier le séparateur filaire à la première plaque de transfert thermique (2) et/ou à la deuxième plaque de transfert thermique (4).
  11. Echangeur de chaleur à plaques (1) destiné à échanger de l'énergie thermique entre deux fluides (14, 16) et comprenant deux plaques de transfert thermique adjacentes (2, 4) formant un canal de fluide (6) le long d'une première direction (X) et séparées par une hauteur de séparation (Δy) dans une deuxième direction (Y), dans lequel l'échangeur de chaleur à plaques comprend au moins un séparateur filaire (20) selon l'une quelconque des revendications 1 à 10 disposé entre les deux plaques de transfert thermique adjacentes.
  12. Echangeur de chaleur à plaques (1) selon la revendication 11, dans lequel ledit au moins un séparateur filaire (20) est positionné de manière amovible entre les deux plaques de transfert thermique (2, 4), et dans lequel la première extrémité (40) et la deuxième extrémité (42) du séparateur filaire sont fixées aux bords extérieurs respectifs (18) des plaques de transfert thermique.
  13. Procédé d'amélioration d'un échangeur de chaleur à plaques existant (1) destiné à échanger de l'énergie thermique entre deux fluides (14, 16) et comprenant deux plaques de transfert thermique adjacentes (2, 4) formant un canal de fluide (6) le long d'une première direction (X) et séparées par une hauteur de séparation (Δy) dans une deuxième direction (Y), le procédé consistant à :
    - insérer au moins un séparateur filaire (20) selon l'une quelconque des revendications 1 à 10 entre les deux plaques de transfert thermique adjacentes (2, 4) ;
    - positionner les trajectoires de fil (20) des premiers segments de support (24) en appui contre la première plaque de transfert thermique (2) le long d'une première ligne de support (C1) dans la première direction (X), et
    - positionner les deuxièmes segments de support (26) en appui contre la deuxième plaque de transfert thermique le long d'une deuxième ligne de support (C2) à une distance de séparation (Δy) à partir de la première ligne de support, séparant ainsi les plaques de transfert thermique adjacentes.
EP15700713.9A 2014-01-20 2015-01-20 Entretoise de fil pour échangeur de chaleur à plaques, échangeur de chaleur à plaques comprenant une telle entretoise, et procédé du perfectionnement d'un échangeur de chaleur Active EP3097378B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL2012111A NL2012111C2 (en) 2014-01-20 2014-01-20 Wire spacer for a plate type heat exchanger, plate type heat exchanger provided with such a wire spacer, and method of upgrading a heat exchanger.
PCT/EP2015/050954 WO2015107209A1 (fr) 2014-01-20 2015-01-20 Espaceur de câbles pour échangeur de chaleur de type plaque, échangeur de chaleur de type plaque pourvu de cet espaceur de câbles, et procédé d'amélioration d'un échangeur de chaleur

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Publication Number Publication Date
EP3097378A1 EP3097378A1 (fr) 2016-11-30
EP3097378B1 true EP3097378B1 (fr) 2017-11-08

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EP15700713.9A Active EP3097378B1 (fr) 2014-01-20 2015-01-20 Entretoise de fil pour échangeur de chaleur à plaques, échangeur de chaleur à plaques comprenant une telle entretoise, et procédé du perfectionnement d'un échangeur de chaleur

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US (1) US20160341493A1 (fr)
EP (1) EP3097378B1 (fr)
KR (1) KR20160111979A (fr)
CA (1) CA2937382A1 (fr)
NL (1) NL2012111C2 (fr)
RU (1) RU2710457C2 (fr)
WO (1) WO2015107209A1 (fr)

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JP6728781B2 (ja) * 2016-03-03 2020-07-22 株式会社Ihi 反応装置

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US721855A (en) * 1902-03-29 1903-03-03 Exear Belenger Wheeled toy.
DE721855C (de) * 1938-06-09 1942-06-20 Robert V Linde Dipl Ing Waermeaustauscher mit aus Draht fortlaufend geformten Waermeleitgittern
GB559107A (en) * 1942-10-29 1944-02-03 Edwin James Bowman Improvements in radiators for cooling liquids and for heating rooms
US2595457A (en) * 1947-06-03 1952-05-06 Air Preheater Pin fin heat exchanger
US2505619A (en) * 1948-08-10 1950-04-25 Air Preheater Method of creating pin fin surfaces for heat exchangers
US2814470A (en) * 1952-02-12 1957-11-26 Air Preheater Heat exchanger
DE1162318B (de) * 1954-05-07 1964-02-06 John Randolph Gier Jun Verfahren zum Herstellen eines maeanderfoermigen Drahtelements
US3079994A (en) * 1956-01-30 1963-03-05 Daimler Benz Ag Heat transfer plate construction
RU2028572C1 (ru) * 1990-02-07 1995-02-09 Одесский институт низкотемпературной техники и энергетики Теплообменник
JP2004356114A (ja) * 2003-05-26 2004-12-16 Tadahiro Omi Ｐチャネルパワーｍｉｓ電界効果トランジスタおよびスイッチング回路
JP2006138538A (ja) * 2004-11-11 2006-06-01 Usui Kokusai Sangyo Kaisha Ltd 偏平伝熱管および該伝熱管を組込んでなる多管式熱交換器並びに多管式熱交換型ｅｇｒガス冷却装置
RU2008133998A (ru) * 2006-01-19 2010-02-27 Модайн Мэньюфэкчеринг Компани (Us) Плоская трубка, теплообменник из плоских трубок и способ их изготовления

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Also Published As

Publication number Publication date
EP3097378A1 (fr) 2016-11-30
KR20160111979A (ko) 2016-09-27
US20160341493A1 (en) 2016-11-24
WO2015107209A1 (fr) 2015-07-23
RU2710457C2 (ru) 2019-12-26
CA2937382A1 (fr) 2015-07-23
RU2016133969A (ru) 2018-02-28
NL2012111C2 (en) 2015-07-21
RU2016133969A3 (fr) 2018-08-03

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