EP0072797B1 - Plaque d'echangeur de chaleur possedant des plis uniformes et resistant a la deformation - Google Patents

Plaque d'echangeur de chaleur possedant des plis uniformes et resistant a la deformation Download PDF

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Publication number
EP0072797B1
EP0072797B1 EP81901731A EP81901731A EP0072797B1 EP 0072797 B1 EP0072797 B1 EP 0072797B1 EP 81901731 A EP81901731 A EP 81901731A EP 81901731 A EP81901731 A EP 81901731A EP 0072797 B1 EP0072797 B1 EP 0072797B1
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EP
European Patent Office
Prior art keywords
fluid flow
forming
sheet
flow passage
plate
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.)
Expired
Application number
EP81901731A
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German (de)
English (en)
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EP0072797A4 (fr
EP0072797A1 (fr
Inventor
Gonzalo Dario Vidal-Meza
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Caterpillar Inc
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Caterpillar Tractor Co
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Publication date
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Publication of EP0072797A1 publication Critical patent/EP0072797A1/fr
Publication of EP0072797A4 publication Critical patent/EP0072797A4/fr
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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
    • 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
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D13/00—Corrugating sheet metal, rods or profiles; Bending sheet metal, rods or profiles into wave form
    • B21D13/02—Corrugating sheet metal, rods or profiles; Bending sheet metal, rods or profiles into wave form by pressing
    • 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
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/108—Particular pattern of flow of the heat exchange media with combined cross flow and parallel flow

Definitions

  • This invention relates to a low cost, distortion resistant heat transfer plate for use in a heat exchanger such as a gas turbine recuperator or other type of primary surface heat exchanger.
  • the invention also relates to a method for efficiently and easily forming a heat exchanger plate out of ductile metal or other heat conductive sheet material and to apparatus for forming an undulatory pattern of uniform pleats in such sheet material to form a heat exchanger plate.
  • One known kind of heat exchanger plate hereinafter referred to as of the kind described, includes undulatory pleats forming a set of donative fluid flow passages on one side of the plate and a set of recipient fluid flow passages on the other side of the plate interleaved with the donative fluid flow passages, each flow passage being bounded on opposite sides by the side walls of a pleat and having a central axis extending along a continuous curvilinear path between separate points on the plate perimeter.
  • An example of this type of corrugated heat exchanger plate is illustrated in US-A-3,759,323. It is in order to prevent nesting of the plates when stacked, that the pleats are given a wavy (or curvilinear) configuration. When thus constructed the pleat crests of one plate form at least some points of contact with the crests of the adjacent plates.
  • a heat exchanger plate of the kind described is characterised in that the slope of each of the side walls of each of the pleats is constant along the entire length of the flow passage, wherein the slope is measured in a plane perpendicular to the central axis of the corresponding flow passage.
  • This construction provides a low cost, structurally rigid heat exchanger plate which overcomes the deficiencies of the prior art as described above.
  • the new heat exchanger plate is provided with an undulatory pattern of pleats the side wall of each of which has a constant slope throughout the length of each fluid flow passage. This iniformity in slope provides greater structural rigidity and over-all uniformity to the heat exchanger plate.
  • restriction and/or obstruction of fluid flow passages due to mechanical or temperature induced distortions in the walls forming the fluid flow passages can be reduced by this arrangement without sacrificing the efficiency and low cost manufacturing advantages of prior art pleated heat exchanger plates.
  • each side wall may be formed of a plurality of wavelength portions, each wavelength portion including a first section which, as seen perpendicular to the general plane of the plate, forms a first circular arc on one fluid passage side and a second circular arc on the other fluid passage side with the first and second circular arcs having a first coincident centre of curvature on one side of the side wall and wherein each wavelength portion of the side wall includes a remaining section which forms a third circular arc on the other fluid passage side and a fourth circular arc on the one fluid passage side with the third and fourth circular arcs having a second coincident centre of curvature on the side of the side wall which is opposite to the first coincident centre of curvature.
  • the present invention also includes a method for forming a heat exchanger plate, the method including the steps of (a) bending a sheet of ductile heat conductive material to form an undulatory pleat containing a donative fluid flow passage bounded on opposed sides by a pair of side walls formed from the sheet and having a central axis, perpendicular to the general plane of the plate, extending along a continuous curvilinear path between separate points on the sheet perimeter, (b) bending a portion of the sheet adjacent the donative fluid flow passage to form a recipient fluid flow passage on an opposite side of the sheet from the donative fluid flow passage with the recipient fluid flow passage being bounded by a pair of side walls one of which is shared by the donative fluid flow passage and having a central axis extending along a continuous curvilinear path between separate points on the sheet perimeter, and (c) repeating steps (a) and (b) to form a set of donative fluid flow passages on one side of the sheet and a set of recipient fluid flow passages on the
  • a method of forming a heat exchanger plate from a deformable sheet into narrowly grooved corrugations across the sheet comprises positioning a first forming blade of undulating serpentine profile having a substantially uniform thickness along its length against one'side of the sheet; and sequentially and repetitively moving second and third forming blades against the other side of the sheet in a straddling manner with respect to the first blade, each of the second and third forming blades having an undulating serpentine profile and a variable thickness along its length sufficient to slope the side walls of the corrugations substantially uniformly across the sheet.
  • the invention also includes apparatus for forming a heat exchanger plate including pleat forming means for forming undulatory pleats in a sheet of ductile heat transfer material, the pleat forming means including first passage forming means for forming donative fluid flow passages on one side of the sheet with each donative fluid flow passage being bounded on opposite sides by the side walls of a pleat and having a central axis extending along a continuous curvilinear path between separate points on the sheet perimeter and second passage forming means for forming recipient fluid flow passages on the opposite side of the sheet with each recipient fluid flow passage being bounded on opposite sides by the side walls of a pleat and having a central axis extending along a continuous curvilinear path between separate points on the sheet perimeter, characterised in that the first and second passage forming means are shaped and positioned to cause the slope of each of the side walls of each of the said pleats to be constant along the entire length of the flow passage, wherein the slope is measured in a plane perpendicular to the central axi
  • the first passage forming means includes a first blade having an operative portion with a configuration corresponding to the desired undulatory configuration of each donative fluid flow passage and the second passage forming means including a second blade having an operative portion with a configuration corresponding to the desired undulatory configuration of each recipient fluid flow passage, one of the blades having a cross-sectional thickness which varies along its length.
  • each heat exchanger plate includes a plurality of undulatory pleats 12 having a wavy pattern in plan view designed to prevent nesting of the respective plates by causing the crowns or crests of each pleat to contact the crowns of the pleats formed in an adjacent heat exchanger plate.
  • the side walls of each pleat subdivide the space between adjacent plates into a plurality of fluid flow passages to increase the total surface area actually contacted by the heat transfer fluids flowing between the heat exchanger plates.
  • edge bars 14 are positioned at selected peripheral positions between successive heat exchanger plates to direct the flow of heat exchange fluids through the heat exchanger and prevent commingling of the fluids while allowing heat transfer therebetween.
  • Inlet sections 15 and outlet sections 16 are attached to opposed sides of each heat exchanger plate to assist in directing the heat exchange fluids into the interplate spaces.
  • the term "donative fluid” will refer to fluids capable of giving up heat energy within a heat exchanger and may include either gas or liquid.
  • the term “recipient fluid” will refer to any fluid, gas or liquid, which, when introduced into a heat exchanger, is capable of receiving heat energy from the donative fluid.
  • heat exchanger plates 2 and 4 are designed to define a recipient fluid flow chamber when the respective plates are positioned adjacent one another. Within this recipient fluid flow chamber, a plurality of recipient fluid flow passages 18 are defined by. adjacent side walls of the pleats 12 projecting into the recipient fluid flow chamber from plates 2 and 4.
  • the space between plates 4 and 6 is designed to form a donative fluid flow chamber with the area between pleats 12 opening into the chamber forming a plurality of donative fluid flow passages 20.
  • the edge bars 14 and inlet and outlet sections 15 and 16 are arranged to cause the donative fluid to flow along the C-shaped flow path illustrated by arrow 22 within alternate spaced formed by the stacked plates while the recipient fluid is caused to flow in a reverse C-pattern illustrated by arrows 24 within the remaining alternate spaces.
  • the blades are designed to move between a first position in which the blades are separated to recieve an unpleated ductile sheet material and a second position in which the ductile sheet material has been deformed so as to form a pleat side wall in the clearance space between the respective passage forming blades.
  • Fig. 2 is a schematic cross-sectional illustration of pleating apparatus in which both the method and apparatus of the prior art as well as that of the present invention may be employed.
  • First forming means 26 and second forming means 28 each carry an identical donative fluid passage forming blade 34 and 36, respectively.
  • Third forming means 30 is positioned to cooperate with blade 34 in order to properly position the incoming ductile sheet material 37 and to form one side wall 38 of each pleat.
  • Fourth forming means 32 supports a recipient fluid passage forming blade 40 adapted to enter the space between blades 34 and 36 as illustrated in Fig. 2, thereby causing a second side wall 42 to be formed in the clearance space between blades 34 and 40 and a third side wall 44 to be formed in the clearance space between blades 40 and 36.
  • Fig. 3 illustrates the apparatus of Fig. 2 wherein first and second forming means 26 and 28 have been displaced upwardly to permit the ductile sheet material 37 to be displaced by a distance equal to the wavelength of the pleat wave in plan view in preparation for forming a successive pleat by forming means 26 through 32, all as described in greater detail in US-A-3 892 119.
  • FIG. 4 a perspective view of prior art fluid passage forming blades of the type used in the apparatus of U.S. Patent No. 3,892,119 is shown including a pair of donative fluid flow passage forming blades 34' and 36' and a recipient fluid flow passage forming blades 40'.
  • the prior art blades of Fig. 4 have uniform thicknesses.
  • the apparatus of Fig. 2 will form pleats in ductile sheet material 37 having side walls of irregular slope, thus creating an unstable structure in which the side walls are easily distorted by outside mechanical force or temperature induced contractions and expansions.
  • Fig. 4 a perspective view of prior art fluid passage forming blades of the type used in the apparatus of U.S. Patent No. 3,892,119 is shown including a pair of donative fluid flow passage forming blades 34' and 36' and a recipient fluid flow passage forming blades 40'.
  • the prior art blades of Fig. 4 have uniform thicknesses.
  • the apparatus of Fig. 2 will form pleats in ductile sheet
  • Fig. 5 wherein a cross-sectional view taken along lines 5-5 of the apparatus of Fig. 2 is illustrated as the apparatus would appear if equipped with the prior art blades of Fig. 4.
  • Fig. 5 illustrates donative fluid passage forming blades 34' and 36' having a constant thickness d, and a pair of curvilinear side walls each of which consists of alternating circular arcs arranged in a path which defines a periodic function.
  • the recipient fluid passage forming blade 40' is also formed with a constant thickness d 2 and is provided with side walls which in cross section are each formed of successive circular arcs which define a periodic function having the said phase and wavelength as the periodic functions defined by the surfaces of blades 34' and 36'.
  • the clearance space between the blades in plan view regardless of the shape or configuration of the curvilinear pattern formed by the blade surfaces, cannot be constant. Even if the surfaces of each blade were formed by identical sine waves displaced laterally, the clearance spacing between the blade surfaces would still vary when the clearance is measured in a direction perpendicular to the central axis of the. clearance space.
  • the central axis between two curvilinear lines will be defined as the loci of all points located midway between the two curvilinear lines as measured along a line normal to one of the curvilinear lines at each point along such line. Obviously, this definition presupposes the absence of any discontinuities in the two curvilinear lines in order for there to be a continuous central axis.
  • each donative fluid flow passage must be larger in cross-sectional area than is each of the recipient fluid flow passages.
  • each wavelength portion W of blade 40' is constructed in a first section with side walls which sweep out circular arcs having radii r 1 and r 2 with both arcs having a coincident center of curvature C 1 .
  • the remaining portion of the wavelength section of blade 40' is similarly formed to provide blade surfaces having radii of curvature r/ and r 2 ' with a coincident center of curvature C 2 located on the opposite side of the blade.
  • each wavelength portion of donative fluid forming passage blades 34' and 36' similarly includes surfaces which define circular arcs having radii of curvature R 1 and R 2 with a coincident center of curvature C 3 .
  • the clearance between the blades varies from a maximum of M to a minimum of m.
  • the minimum clearance m is normally made only slightly larger than the thickness of the plate material plus a small amount allowed for ease of withdrawing the blades of the pleating apparatus. This arrangement allows the greatest number of pleats per unit length of plate as possible.
  • the slope of the side walls formed in the areas of minimum clearance m between the respective passage forming blades will have a substantially vertical slope.
  • Side walls formed in this manner have very little lateral rigidity which causes shifting of the pleating and uncontrolled obstruction of the fluid flow passages.
  • Some shifting of the side walls forming the donative fluid flow passages may be tolerated since these passages have a substantial larger cross-sectional area.
  • a shift in the side walls forming each of the recipient fluid flow passages can be highly detrimental due to their smaller cross-sectional area.
  • Fig. 6 is a partial cross-sectional view taken along lines 6-6 of Fig. 5 located at a point of minimum clearance between respective pleat forming blades.
  • lines 6-6 indicate a cross-section taken along a plane perpendicular to the central axis of blade 34' and thus lines S1 in Fig. 6 are representative of the slope of both side walls 38 and 42.
  • the slope of these side walls is virtually perpendicular to the plan surface of the heat exchanger plate being pleated.
  • Fig. 6 Contrasting with the configuration of Fig. 6 is the cross-sectional view of Fig. 7 of a portion of a heat exchanger plate being formed by the assembly illustrated in Fig. 5 as taken along line 7-7.
  • the slope of side wall 38 as represented by line s 2 and yet another slope angle represented by line s 3 of side wall 42.
  • this varying slope of the pleat side walls 38 and 42 along the longitudinal extent of each pleat formed by the assembly of Fig. 5 results from variation in the clearance between the blade surfaces.
  • FIG. 8 wherein a perspective view is shown of the heat exchanger plate forming apparatus of the subject invention.
  • donative fluid flow passage forming blades 34" and 36" have been substituted for the corresponding blades of the prior art illustrated in Fig. 4.
  • blades 34" and 36" have a non-uniform cross-sectional configuration.
  • Fig. 9 is a cross-sectional view of the apparatus illustrated in Fig. 8 when positioned by the forming assembly, illustrated in Fig. 2 taken along lines 5-5.
  • the donative fluid passage forming blades 34" and 36" are shown as having a substantial blade thickness variation along the longitudinal extent of each blade from a minimum of P i to a maximum of P 21
  • the recipient fluid passage forming blade 40" is provided with a uniform thickness as measured in the direction of a plane passing perpendicularly through the central axis of the blade in plan view along the entire longitudinal length of the central axis.
  • Variations in the width of the donative fluid flow passages are significanly more acceptable in view of the substantial width of such passages as compared with the narrower cross-sectional width of the recipient fluid flow passages.
  • each of the circular arcs identified by arrows S 1 through S 4 are coincident at point SC.
  • the remaining side surfaces of each of the blades 34", 36" and 40" form in plan view circular arcs touched by arrows Y 1 , Y 2 , Y 3 and Y 4 having a coincident center of curvature YC located on a side of blade 40" opposite to center of curvature SC.
  • the circular arcs touched by arrows Y 1 and S 1 complete a full wavelength of one side of blade 40".
  • arrows Y 2 and S 2 complete a wavelength of the opposite side of blade 40".
  • a full wavelength of the surface of blade 34" adjacent blade 40" is formed by circular arcs touched by arrows Y 4 and S 4 .
  • a full wave length of the side of blade 36" adjacent blade 40" is formed by the circular arcs touched by arrows Y 3 and S 3 .
  • the cross-sectional area of the recipient fluid flow passages formed by blade 40" will remain constant throughout their longitudinal length.
  • the slope of all of the side walls forming the pleats within the heat exchanger plate will remain uniformly constant and equal throughout the full longitudinal extent of each pleat.
  • the side walls 42 and 44 similarly include wavelength sections W having concentric circular arc sections having radii of curvature corresponding to the radii S 1 through S 4 and Y 1 through Y 4 . Each such radius is less or greater than the corresponding radius by an amount equal to the spacing of the blade surface from the corresponding side wall surface.
  • Fig. 10 a partial cross-sectional view of blades 34", 36" and 40" is illustrated as taken along lines 10-10 of Fig. 9 wherein the slopes of side walls 38, 42 and 44 are illustrated by lines 46, 48 and 50. As can be seen in Fig. 10, lines 46, 48 and 50 form an equal angle relative to a plane formed by the outer plane surfaces of the pleated heat exchanger plate.
  • Fig. 11 similarly discloses a partial cross-sectional view of blades 34", 36" and 40" taken along lines 11-11 of Fig. 9. Note that the cross-sectional view of Fig. 11 has been taken at a point of maximum width of blade 34" as compared with the position of the cross-sectional view illustrated in Fig. 10 wherein the thickness of blade 34" is at a minimum. Despite this variation in the cross section width of blade 34", the slopes of side walls 38, 42 and 44 as represented by lines 52, 54 and 56 are identical to the slopes of the corresponding lines 46, 48 and 50 of Fig. 9.
  • the method and apparatus of forming a pleated heat exchanger plate as illustrated in Figs. 8-11 is capable of providing a heat exchanger plate wherein the recipient fluid flow passages include uniform and constant cross-sectional areas while the slope of the side walls of the pleats forming the respective fluid flow passages is constant throughout the entire longitudinal extent of each fluid flow passage.
  • a highly efficient, compact and rigid heat exchanger can be formed by stacking plural pleated heat exchanger plates of the type formed by the apparatus and method illustrated in Figs. 2, 8 and 9.
  • Heat exchangers formed by the method and apparatus disclosed herein, as well as the heat exchanger plates designed in accordance with this invention, can be employed in a vast number of applications wherein the transfer of heat from one fluid to a second fluid is desired.
  • the exhaust gases from a gas turbine may form the donative fluid for heating the compressed intake air leading to the combustor and then to the turbine whereby the intake air becomes the recipient fluid referred to above.
  • a heat exchanger formed in accordance with the subject invention and including the pleated plates described above can be used in the boiler of a steam generation device wherein hot gases from fuel combustion forms the donative fluid while the recipient fluid is the return water or make-up water from which steam is to be generated in the heat exchanger.
  • Still other applications include the use of a heat exchanger formed in accordance with the subject invention wherein the recipient fluid is the cooling water of an internal combustion engine and the donative fluid is the hot oil. Additional applications include the use of heat exchangers of the subject type employed in heat treatment furnaces and other industrial applications wherein it is desired to transfer heat from one fluid to another.

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

Claims (10)

1. Plaque d'échangeur de chaleur (2, 4, 6, 8) pour former une barrière entre un fluide donneur et un fluide récepteur s'écoulant l'un et l'autre dans un échangeur de chaleur et pour former des conduits d'écoulement du fluide (18, 20) disposés pour provoquer un transfert de chaleur au travers de la plaque depuis le fluide donneur au fluide récepteur, la plaque (2, 4, 6, 8) comportant des plis ondulés (12) formant un ensemble de conduits d'écoulement (20) du fluide donneur sur l'une des faces de la plaque, et un ensemble de conduits d'écoulement (18) du fluide récepteur sur l'autre face de la plaque, alternant avec les conduits d'écoulement (20) du fluide donneur, chacun des conduits (18,20) étant limité sur ses extrémités opposées par les parois latérales (38, 42, 44) d'un pli (12) et comportant un axe central s'étendant le long d'un trajet curviligne continu entre des points séparés du périmètre de la plaque, caractérisée en ce que la pente de chacune des parois latérales (38, 42, 44) de chacun des plis (12) est constante sur toute la longueur du conduit d'écoulement (18, 20), la pente étant mesurée dans un plan perpendiculaire à l'axe central du conduit d'écoulement (18, 20) corespondant.
2. Plaque d'échangeur de chaleur (2, 4, 6, 8) selon la revendication 1, dans lequelle la pente de chacune des parois latérales (38, 42, 44) est égale à la pente de toutes les autres parois latérales (38, 42, 44).
3. Plaque d'échangeur de chaleur (2, 4, 6, 8) selon la revendication 1 ou la revendication 2, dans laquelle l'axe central définit un trajet curviligne ayant une fonction périodique constante d'amplitude constante.
4. Plaque d'échangeur de chaleur (2, 4, 6, 8) selon la revendication 3, dans laquelle chacune des parois latérales (38, 42, 44) est formée de plusieurs parties égales chacune à une longueur d'onde (W), chaque partie égale à une longueur d'onde (W) comprenant une première partie qui, vue perpendiculairement au plan général de la plaque, forme un premier arc de cercle (Y1) sur l'une des faces de conduit d'écoulement du fluide, et un second arc de cercle (Y2) sur l'autre face de conduit d'écoulement du fluide, le premier et le second arcs de cercle ayant un premier centre de courbure coïncident (YC) sur l'une des faces de la paroi latérale (38, 42, 44), et dans laquelle chacune des parties égale à une longueur d'onde (W) de la paroi latérale (38, 42, 44) comporte une partie restante qui forme un troisième arc de cercle (S2) sur l'autre face de conduit d'écoulement du fluide et un quatrième arc de cercle (S1) sur la première face de conduit d'écoulement du fluide, le troisième et le quatrième arcs de cercle ayant un second centre de courbure coïncident (SC) sur la face de la paroi latérale qui est opposée au premier centre de courbure coïncident.
5. Procédé pour former une plaque d'échangeur de chaleur (2, 4, 6, 8) destinée à être utilisée comme barrière entre un fluide donneur et un fluide récepteur s'écoulant l'un et l'autre dans un échangeur de chaleur, et pour former des conduits d'écoulement (18, 20) d'un fluide dans la plaque (2, 4, 6, 8) disposés pour provoquer un transfert de chaleur au travers de la plaque (2, 4, 6, 8) depuis le fluide donneur au fluide récepteur, ce procédé comportant les étapes consistant à:
(a) courber une feuille (37) d'un matériau ductile conducteur de la chaleur pour former un pli ondulé (12) contenant un conduit d'écoulement (20) d'un fluide donneur limité à ses extrémités opposées par deux parois latérales (38, 42, 44) formées par la feuille (37) et comportant un axe central perpendiculaire au plan général de la plaque, et s'étendant le long d'un trajet curviligne continu entre des points séparés sur le périmètre de la feuille;
(b) courber une partie de la feuille (37) adjacente au conduit d'écoulement (20) du fluide donneur pour former un conduit d'écoulement (18) du fluide récepteur sur une face de la feuille (37) opposée au conduit d'écoulement (20) du fluide donneur, le conduit d'écoulement (18) du fluide récepteur étant limité par deux parois latérales (38, 42, 44) dont l'une est partagée par le conduit d'écoulement du fluide donneur et ayant un axe central s'étendant le long d'un trajet curviligne continu entre des points séparés sur le périmètre de la feuille; et
(c) répéter les étapes (a) et (b) pour former un ensemble de conduits d'écoulement (20) du fluide donneur sur l'une des faces de la feuille (37) et un ensemble de conduits d'écoulement (18) du fluide récepteur sur la face opposée de la feuille (37), chacun des conduits d'écoulement (18, 20) partageant une paroi latérale commune (38, 42, 44) avec les conduits d'écoulement (18, 20) qui lui sont adjacents, caractérisé par un contrôle des étapes de courbage (a) et (b) de manière à faire que la pente de chacune des parois latérales (38, 42, 44) de chacun des conduits d'écoulement (18, 20) soit constante sur toute la longueur des conduits d'écoulement ( 18,20), la pente étant mesurée dans un plan perpendiculaire à l'axe central du conduit d'écoulement (18, 20) correspondant.
6. Procédé pour former une plaque d'échangeur de chaleur (2, 4, 6, 8) selon la revendication 5, dans lequel les étapes (a) et (b) comportent l'étape consistant à courber la feuille (37) de manière à ce que la pente de chacune des parois latérales (38, 42, 44) soit égale à la pente de toutes les autres parois latérales (38, 42, 44).
7. Procédé pour former une plaque d'échangeur de chaleur (2, 4, 6, 8) à partir d'une feuille déformable (37) en ondulations étroitement creusées en travers de la feuille, selon la revendication 5 ou 6, ce procédé comportant les étapes consistant à:
- disposer contre l'une des faces de la feuille (37) une première lame de formage (40") de profil ondulant ayant une épaisseur sensiblement uniforme le long de sa longueur; et
-déplacer successivement et répétitivement une seconde et une troisième lames de formage (34", 36") contre l'autre face de la feuille (37) d'une manière chevauchante par rapport à la première lame (40"), chacune des seconde et troisième lames de formage (34", 36") ayant un profil ondulant et une épaisseur variable le long de sa longueur et suffisante pour incliner les parois latérales (38, 42, 44) des ondulations de façon sensiblement uniforme en travers de la feuille (37).
8. Appareil pour former une plaque d'échangeur de chaleur (2, 4, 6, 8) comportant des moyens de formage (26, 28, 30, 32, 34", 36", 40"), des plis pour former des plis ondulés (12) dans une feuille (37) d'un matériau ductile conducteur de la chaleur, les moyens de formage (26, 28, 30, 32, 34", 36", 40") des plis comportant un premier moyen de formage (26, 28, 34", 36") des conduits pour former des conduits d'écoulement (20) du fluide donneur sur l'une des faces de la feuille (37), chacun des conduits d'écoulement (20) du fluide donneur étant limité à ses extrémités opposées par les parois latérales (38, 42, 44) d'un pli (12) et comportant un axe central s'étendant le long d'un trajet curviligne continu entre des points séparés sur le périmètre de la feuille, et un second moyen de formage (30, 32, 40") des conduits, pour former les conduits d'écoulement (18) du fluide récepteur sur la face opposée de la feuille (37), chacun des conduits d'écoulement (18) du fluide récepteur étant limité à ses extrémités par les parois latérales (38, 42, 44) d'un pli (12) et ayant un axe central s'étendant le long d'un trajet curviligne continu entre des points séparés sur le périmètre de la feuille, caractérisé en ce que les premiers et seconds moyens de formage (26, 28, 30, 32, 34", 36", 40") des conduits ont une forme et une disposition propres à faire que la pente de chacune des parois latérales (38, 42, 44) de chacun desdits plis (12) soit constante sur toute la longueur du conduit d'écoulement (18, 20), cette pente étant mesurée dans un plan perpendiculaire à l'axe central du conduit d'écoulement (18, 20) correspondant.
9. Appareil selon la revendication 8, dans lequel le premier moyen de formage (26, 28, 34", 36") des conduits comprend une première lame (34", 36") ayant une partie active dont la configuration correspond à la configuration ondulée désirée pour chacun des conduits d'écoulement (20) du fluide donneur et dans lequel le second moyen de formage (30, 32, 40") des conduits comporte une seconde lame (40") ayant une partie active dont la configuration correspond à la configuration ondulée désirée pour chacun des conduits d'écoulement (18) du fluide récepteur, l'une des lames (34", 36", 40") ayant une épaisseur en coupe transversale qui varie le long de son longueur.
10. Appareil selon la revendication 9, dans lequel ladite seconde lame (40") possède une épaisseur uniforme en coupe transversale.
EP81901731A 1981-02-18 1981-02-18 Plaque d'echangeur de chaleur possedant des plis uniformes et resistant a la deformation Expired EP0072797B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1981/000208 WO1982002940A1 (fr) 1981-02-18 1981-02-18 Plaque d'echangeur de chaleur possedant des plis uniformes et resistant a la deformation

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Publication Number Publication Date
EP0072797A1 EP0072797A1 (fr) 1983-03-02
EP0072797A4 EP0072797A4 (fr) 1983-07-04
EP0072797B1 true EP0072797B1 (fr) 1984-09-26

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EP81901731A Expired EP0072797B1 (fr) 1981-02-18 1981-02-18 Plaque d'echangeur de chaleur possedant des plis uniformes et resistant a la deformation

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EP (1) EP0072797B1 (fr)
JP (1) JPS58500080A (fr)
CA (1) CA1152977A (fr)
DE (1) DE3166239D1 (fr)
WO (1) WO1982002940A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5081834A (en) * 1990-05-29 1992-01-21 Solar Turbines Incorporated Circular heat exchanger having uniform cross-sectional area throughout the passages therein
FR2836077B1 (fr) * 2002-02-21 2004-07-09 Const Aero Navales Outillage de formage de surfaces d'echange thermique ondulees pour echangeur thermique, par pliage a froid d'un feuillard et procede de realisation des profils de formage d'un tel outillage
US7065873B2 (en) 2003-10-28 2006-06-27 Capstone Turbine Corporation Recuperator assembly and procedures
US7147050B2 (en) 2003-10-28 2006-12-12 Capstone Turbine Corporation Recuperator construction for a gas turbine engine

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB189702543A (en) * 1897-01-30 1897-12-18 Isaac Braithwaite Improvements in Drying Rooms or Closets for Drying Linen or other Textile Goods or Clothing.
FR695346A (fr) * 1929-05-18 1930-12-13 Procédé de fabrication de tôles ondulées à ondulations concordant exactement
DE528487C (de) * 1929-05-19 1931-06-29 Hans Syrowy Verfahren zur Herstellung von Wellblech mit genau uebereinstimmenden Wellen
DE543337C (de) * 1929-07-23 1932-02-04 Hans Syrowy Verfahren zur Herstellung von Wellblechen und Formplatten
GB351984A (en) * 1930-03-25 1931-06-25 Calvert & Co Ab Improvements in air preheaters and like surface apparatus for the exchange of heat between two fluids
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US4022050A (en) * 1975-12-04 1977-05-10 Caterpillar Tractor Co. Method of manufacturing a heat exchanger steel

Also Published As

Publication number Publication date
JPS58500080A (ja) 1983-01-13
EP0072797A4 (fr) 1983-07-04
DE3166239D1 (en) 1984-10-31
WO1982002940A1 (fr) 1982-09-02
EP0072797A1 (fr) 1983-03-02
CA1152977A (fr) 1983-08-30

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