EP2886996B1 - Échangeur de chaleur à plaques avec bride de montage - Google Patents

Échangeur de chaleur à plaques avec bride de montage Download PDF

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Publication number
EP2886996B1
EP2886996B1 EP13198883.4A EP13198883A EP2886996B1 EP 2886996 B1 EP2886996 B1 EP 2886996B1 EP 13198883 A EP13198883 A EP 13198883A EP 2886996 B1 EP2886996 B1 EP 2886996B1
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EP
European Patent Office
Prior art keywords
plate
heat exchanger
perimeter
mounting
mounting 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.)
Active
Application number
EP13198883.4A
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German (de)
English (en)
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EP2886996A1 (fr
Inventor
Håkan Larsson
Roger BADER
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.)
Alfa Laval Corporate AB
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Alfa Laval Corporate AB
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Application filed by Alfa Laval Corporate AB filed Critical Alfa Laval Corporate AB
Priority to EP13198883.4A priority Critical patent/EP2886996B1/fr
Priority to SE1650782A priority patent/SE1650782A1/en
Priority to PCT/EP2014/077423 priority patent/WO2015091215A1/fr
Priority to TW103144274A priority patent/TWI539135B/zh
Publication of EP2886996A1 publication Critical patent/EP2886996A1/fr
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Publication of EP2886996B1 publication Critical patent/EP2886996B1/fr
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Classifications

    • 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
    • F28D9/0031—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 paired plates touching each other
    • F28D9/0043—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • F28F9/002—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core with fastening means for other structures
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2280/00—Mounting arrangements; Arrangements for facilitating assembling or disassembling of heat exchanger parts
    • F28F2280/06—Adapter frames, e.g. for mounting heat exchanger cores on other structure and for allowing fluidic connections

Definitions

  • the present invention relates to a plate heat exchanger that comprises a plurality of heat exchanger plates which are stacked and permanently connected to form a plate package and a mounting structure which is permanently connected to the plate package for releasable attachment of the plate heat exchanger to an external supporting structure.
  • Heat exchangers are utilized in various technical applications for transferring heat from one fluid to another fluid.
  • Heat exchangers in plate configuration are well-known in the art.
  • a plurality of stacked plates having overlapping peripheral side walls are put together and permanently connected to define a plate package with hollow fluid passages between the plates, usually with different fluids in heat exchange relationship in alternating spaces between the plates.
  • a coherent base plate or mounting plate is directly or indirectly attached to the outermost one of the stacked plates.
  • the mounting plate has an extension that exceeds the stack of plates so as to define a circumferential mounting flange.
  • the mounting flange has holes or fasteners to attach the heat exchanger to a piece of equipment.
  • This type of plate heat exchanger is e.g. known from US2010/0258095 and US8181695 .
  • the mounting plate When fastened on the piece of equipment, the mounting plate may be subjected to a significant pressure and weight load which tends to deform the mounting plate. To achieve an adequate strength and rigidity, the mounting plate needs to be comparatively thick. Such a thick mounting plate may add significantly to the weight of the heat exchanger. Furthermore, the use of a thick mounting plate leads to a larger consumption of material and a higher cost for the heat exchanger.
  • the need for a thick mounting plate may be particularly pronounced when the heat exchanger is mounted in an environment which is subjected to vibrations. Such vibrations may e.g. occur when the plate heat exchanger is mounted in a vehicle such as a car, truck, bus, ship or airplane.
  • the design of the plate heat exchanger in general, and the design and attachment of the mounting plate in particular need to take into account the risk for fatigue failure caused by cyclic loading and unloading of the mounting plate by the vibrations.
  • the cyclic stresses in the heat exchanger may cause it to fail due to fatigue, especially in the joints between the plates, even if the nominal stress values are well below the tensile stress limit.
  • the risk for fatigue failure is typically handled by further increasing the thickness of the mounting plate, which will make it even more difficult to keep down the weight and cost of the plate heat exchanger.
  • the prior art comprises DE102007008459 , which proposes a unitary tray-shaped mounting plate for a plate heat exchanger.
  • the mounting plate has a planar bottom surface and an edge surface which is inclined upwards from the bottom surface to define a tray for receiving the stack of plates. Tongues for fastening the heat exchanger are integrated with the edge surface and arranged to extend parallel to the bottom surface.
  • WO2011/009412 discloses a plate heat exchanger with two spaced apart mounting plates attached to the end of the stack of plates.
  • the shape of the mounting plates conform to the contour of the stack of plates, so that the plate heat exchanger lacks any mounting flanges. Instead, the heat exchanger is fastened by connecting members that extend out of the respective mounting plate and are received in cavities defined between the respective mounting plate and the end of the stack of plates.
  • Another objective is to provide a plate heat exchanger with a relatively low weight and a relatively high strength when mounted to an external supporting structure.
  • a further objective is to provide a plate heat exchanger that can be manufactured at low cost.
  • Yet another objective is to provide a plate heat exchanger suitable for use in environments subjected to vibrations.
  • a first aspect of the invention is a plate heat exchanger, comprising: a plurality of heat exchanger plates which are stacked and permanently connected to form a plate package that defines first and second fluid paths for a first medium and a second medium, respectively, separated by said heat exchanger plates, said plate package defining a surrounding external wall that extends in an axial direction between first and second axial ends; an end plate permanently connected to one of the first and second axial ends so as to provide an end surface that extends between first and second longitudinal ends in a lateral plane which is orthogonal to the axial direction; and two mounting plates permanently connected to a respective surface portion of the end surface at the first longitudinal end and the second longitudinal end, respectively, such that the mounting plates are spaced from each other in a longitudinal direction on the end surface, wherein the respective mounting plate comprises opposing flat engagement surfaces connected by an edge portion that extends along the perimeter of the mounting plate.
  • the respective mounting plate is arranged with one of its engagement surfaces permanently connected to the end surface, such that the perimeter of the mounting plate partially extends beyond the surrounding external wall, so as to define a mounting flange, and partially extends across the end surface in contact with the same within the perimeter of the surrounding external wall.
  • the perimeter of the mounting plate comprises two concave portions as seen in a normal direction to the end surface, the concave portions being located to intersect the surrounding external wall at a respective intersection point.
  • the inventive plate heat exchanger is based on the insight that the coherent-mounting plate of the prior art may be replaced by two smaller mounting plates that are located at a respective longitudinal end on the end surface on the plate package to provide a respective mounting flange for the heat exchanger.
  • the use of two smaller, separated mounting plates may reduce the weight of the heat exchanger, and also its manufacturing cost, since material is eliminated in the space between the mounting plates, beneath the end surface of the plate package.
  • the inventive heat exchanger is furthermore based on the insight that the use of two separated mounting plates may lead to local stress concentration in the heat exchanger, which may act to reduce the heat exchanger's ability to sustain loads, and in particular cyclic loads.
  • the concentration of stress has been found to originate in the region where the edge portion of the mounting plate intersects the surrounding wall of the plate package.
  • the perimeter of the mounting plate is shaped with two concave portions which are located to intersect the surrounding wall at a respective intersection point.
  • An improved distribution of stress is enabled since the concave portions increase the extent of the perimeter of the mounting plate in a region at and around the intersection points and since the concave portions may orient the perimeter of the mounting plate to the surrounding wall so as to distribute stress.
  • the distribution of stress may be controlled further by optimizing the design parameters of the heat exchanger in general, and the mounting plates in particular, for example according to the following embodiments.
  • a subset of the respective concave portion is located at or within the surrounding external wall and is non-perpendicular to the perimeter of the surrounding external wall at the respective intersection point, as seen in the normal direction to the end surface.
  • the subset of the respective concave portion may extend from a starting point to an end point on the concave portion, such that the local inclination of the concave portion, given by a tangential line, along said subset is less than a maximum design angle, and the end point may be located where the local inclination exceeds the maximum design angle.
  • the maximum design angle is defined between the tangential line and the longitudinal direction and has a value of approximately 65°.
  • the subset comprises an essentially linear portion within at least 30% of the subset, said linear portion having a predefined angle, to the longitudinal direction, which is less that the maximum design angle.
  • the subset of the respective concave portion has a first extent in the longitudinal direction and a second extent in a transverse direction, which is orthogonal to the longitudinal direction in the plane of the mounting plate, wherein the ratio of the second extent to the first extent is equal to or less than approximately 2, and preferably equal to or less than approximately 1 or approximately 0.5.
  • the predefined starting point of the subset is located within a maximum design distance, in the transverse direction, from the respective intersection point, wherein the maximum design distance is 20% of the first extent.
  • the starting point essentially coincides with the respective intersection point.
  • the end point is located on an outward corner of the mounting plate, the outward corner being defined by a second radius.
  • the perimeter of the mounting plate is non-perpendicular to the perimeter of the surrounding external wall at the respective intersection point, as seen in the normal direction to the end surface.
  • the mounting plate abuts on and is permanently connected to the end surface along said subset of the concave portion.
  • the respective concave portion comprises an inward corner defined by a first radius, said inward corner intersecting the surrounding external wall at the intersection point, as seen in the direction normal to the end surface.
  • the respective concave portion extends between two limit points on the perimeter of the mounting plate, said limit points being defined by a mathematical line which intersects the perimeter of the mounting plate only at the limit points and which extends beyond the perimeter of the mounting plate intermediate the limit points, as seen in the direction normal to the end surface.
  • the end plate is a sealing plate which is permanently and sealingly connected to one of the heat exchanger plates at one of said first and second axial ends.
  • the end plate is a reinforcement plate which is permanently connected to a sealing plate on the plate package, wherein the end plate has at least two supporting flanges that extend beyond the perimeter of the surrounding external wall so as to abut on the mounting flange defined by the respective mounting plate.
  • the end plate may comprise, along its perimeter and as seen in the normal direction of the end surface, concave or beveled surfaces adjacent to the supporting flanges, wherein the concave or beveled surfaces may be located to overlap the perimeter of the respective mounting plate at the intersection points, and the respective concave or beveled surface may be non-perpendicular to, and preferably co-extending with, the perimeter of the mounting plate at the overlap, as seen in the normal direction to the end surface.
  • At least one of the mounting plates defines at least one through hole that extends between the engagement surfaces and is aligned with a corresponding through hole defined in the end plate and an internal channel defined in the plate package, so as to form an inlet or an outlet for the first or the second medium.
  • the mounting flange comprises a plurality of mounting holes adapted to receive bolts or pins for fastening the plate heat exchanger.
  • the heat exchanger plates are permanently joined to each other through melting of metallic material.
  • Embodiments of the present invention relate to configurations of a mounting structure on a plate heat exchanger. Corresponding elements are designated by the same reference numerals.
  • Figs 1-2 disclose an embodiment of a plate heat exchanger 1 according to the invention.
  • the plate heat exchanger 1 comprises a plurality of plates which are stacked one on top of the other to form a plate package 2.
  • the plate package 2 may be of any conventional design.
  • the plate package 2 comprises a plurality of heat exchanger plates 3 with corrugated heat transfer portions that define flow passages (Internal channels) for a first and second fluid between the heat exchanger plates 3 such that heat is transferred through the heat transfer portions from one fluid to the other.
  • the heat exchanger plates 3 may be single-walled or double-walled.
  • the heat exchanger plates 3 are only schematically indicated in Fig. 1 , since they are well-known to the person skilled in the art and their configuration is not essential for the present invention.
  • the plate package 2 has the general shape of a rectangular cuboid, albeit with rounded corners. Other shapes are conceivable.
  • the plate package 2 defines a surrounding external wall 4 which extends in a height or axial direction A between a top axial end and a bottom axial end.
  • the wall 4 has a given perimeter or contour at its bottom axial end. In the illustrated example, the wall 4 has essentially the same contour along its extent in the axial direction A.
  • the bottom axial end of the plate package 2 comprises or is provided with an essentially planar end surface 5 ( Fig. 2 ), which may but need not conform to the contour of the wall 4 at the bottom axial end.
  • the end surface 5 extends in a lateral plane.
  • the plate package 2, and the end surface 5 extends between two longitudinal ends in a longitudinal direction L and between two transverse ends in a transverse direction T ( Fig. 2 ).
  • the heat transfer plates 3 have in their corner portions through-openings, which form inlet channels and outlet channels in communication with the flow passages for the first fluid and the second fluid. These inlet and outlet channels open in the end surface 5 of the plate package 2 to define separate portholes for inlet and outlet of the first and second fluids, respectively.
  • the end surface 5 has four portholes 6 ( Fig. 2 ).
  • the plate package 2 is permanently connected to two identical (in this example) mounting plates 7, which are arranged on a respective end portion of the end surface 5.
  • the mounting plates 7 are thereby separated in the longitudinal direction L, leaving a space free of material beneath the center portion of the plate package 2.
  • Each mounting plate 7 has two through-holes 8 which are mated with a respective pair of the portholes 6 of the plate package 2 to define inlet and outlet ports of the heat exchanger 1.
  • the mounting plates 7 are configured for attaching the heat exchanger 1 to an external suspension structure (not shown) such that the inlet and outlet ports mate with corresponding supply ports for the first and second medium on the external structure.
  • one or more seals may be provided in the interface between the mounting plate 7 and the external structure.
  • Each mounting plate 7 defines a mounting flange 9 that projects from the wall 4 and extends around the longitudinal end of the plate package 2. Bores 10 are provided in the mounting flange 9 as a means for fastening the heat exchanger 1 to the external structure. Threaded fasteners or bolts, for example, may be introduced into the bores 10 for engagement with corresponding bores in the external structure.
  • the plate package 2 and the mounting plates 7 are made of metal, such as stainless steel or aluminum. All the plates in the heat exchanger 1 are permanently connected to each other, preferably through melting of a metallic material, such as brazing, welding or a combination of brazing and welding. The plates in the plate package 2 may alternatively be permanently connected by gluing.
  • the mounting plates 7 are dimensioned, with respect to material, thickness and extent in the longitudinal and transverse directions, so as to have an adequate strength and stiffness to the static load that is applied to the mounting plates 7 when fastened on the external structure.
  • the static load which tends to deform the mounting plates 7, may originate from a combination of the weight of the heat exchanger 1, internal pressure applied by the media in the heat exchanger 1 and transferred to the mounting plates 7, and compression forces applied to the mounting plates 7, e.g. at the above-mentioned seals, via the fasteners and the bores 10. This static load tend to deform the mounting plates 7.
  • the mounting plates 7 are generally designed to have a significant thickness. As a non-limiting example, the thickness may be 15-40 mm.
  • the bottom of the plate package 2, on the other hand, is normally made of much thinner material.
  • the heat exchanger 1 is installed in an environment where vibrations are transferred to the mounting plate 7 via the external structure, the heat exchanger 1 also needs to be designed to account for the mechanical stresses caused by the cyclic loading of the vibrations, i.e. cyclic stresses.
  • cyclic stresses occur for heat exchangers that are mounted in vehicles, such as cars, trucks and ships.
  • the heat exchanger 1 is an oil cooler for an engine.
  • cyclic stresses are applied to a material, even though the stresses do not cause plastic deformation, the material may fail due to fatigue especially in local regions with high stress concentration.
  • the use of stiff thick mounting plates 7 connected to a plate package 2 with a relatively thin bottom is likely to lead to high concentrations of cyclic stress at the interface between the mounting plates 7 and the plate package 2, and possibly also within the plate package 2.
  • Embodiments of the present invention are designed to counteract stress concentration that may lead to fatigue failure.
  • the mounting plates 7 have a perimeter with concave portions 15, which are located so as to intersect the perimeter of the surrounding wall 4 of the plate package 2, as seen in the normal direction to the end surface 5.
  • the "perimeter” designates the outer contour as seen in plan view. In the plan view of Fig. 2 , intersection points 11 between the perimeters of the mounting plates 7 and the wall 4 are indicated by black dots.
  • the concave portions 15 By providing the concave portions 15 at the intersection points 11, the perimeter of the mounting plate 7 is given an increased extent in a region at and around the intersection points 11. The increased extent favors distribution of stress.
  • the concave portions 15 generally define more favorable angles between the perimeter of the mounting plate 7 and the surrounding wall 4 for counteracting stress concentration.
  • Figs 3A-3B illustrate a mounting plate 7 in more detail.
  • the mounting plate 7 has essentially planar top and bottom surfaces 12, 13, where the top surface 12 forms an engagement surface to be permanently connected to the end surface 5 on the plate package 2, and the bottom surface 13 forms an engagement surface to be applied and fixed to the external supporting structure.
  • the through-holes 8 and bores 10 are formed to extend between the top and bottom surfaces 12, 13.
  • the top and bottom surfaces are connected by a peripheral edge surface 14.
  • the edge surface 14 is essentially planar and right-angled to the top and bottom surfaces 12, 13 and defines the perimeter of the mounting plate 7.
  • the mounting plate 7 is generally elongated and has a concave shape, as seen in plan view.
  • the term "concave shape” is used in its ordinary meaning to denote a shape that contains at least one portion that bends inwards, i.e. a concave portion.
  • a concave shape is also known as a "non-convex shape".
  • each of the concave portions 15 extends between two well-defined limit points C1, C2.
  • the limit points C1, C2 are located where a straight mathematical (fictitious) line ML touches the perimeter of the mounting plate 7 so as to bridge the concave portion 15.
  • the respective line ML thus intersects the perimeter of the mounting plate 7 at only two locations (at C1 and C2) and is spaced from the perimeter of the mounting plate 7 between these two locations.
  • the respective concave portion 15 extends to an inward corner between a distal outward corner, containing the limit point C1, and a proximate outward corner, containing the limit point C2.
  • the concave portions 15 of the mounting plate 7 are connected by an essentially straight contour line that extends across the end surface 5. This design is selected to minimize the width of the mounting plates 7 in the longitudinal direction L ( Fig. 2 ). Other designs are conceivable.
  • Fig. 5A is taken within the dashed rectangle 5A in the bottom plan view of Fig. 2 and illustrates a region of overlap between the perimeter of the mounting plate 7 and the plate package 2 near the surrounding wall 4.
  • the wall 4 is hidden from view by intermediate structures (see below), but its location is indicated by a dashed line.
  • the inward corner follows an arc of a circle with radius R1.
  • the proximate outward corner which is located on and attached to the end surface 5, follows an arc of a circle with radius R2.
  • the inward corner and the proximate outward corner are connected by an essentially straight (linear) line portion.
  • Simulations indicate that a more uniform distribution of stress is favored by constraining the angles between the concave portion 15 and the surrounding wall 4 where the concave portion 15 overlaps the plate package, i.e. at and within the perimeter of the surrounding wall 4.
  • the present Applicant has identified a constraint that may be applied to a subset of the concave portion 15 that overlaps the plate package. This subset is denoted "constrained perimeter" in the following.
  • the constrained perimeter extends from a starting point P1, which coincides with the intersection point 11, to a well-defined end point P2.
  • the local inclination of the perimeter is constrained to be within a predefined angular range.
  • the local inclination is given by the tangent to the perimeter at each individual location on the perimeter, as seen in a normal direction to the end surface 5.
  • the angular range is given by a maximum design angle ⁇ max , which is defined with respect to the longitudinal direction L (i.e. the direction of the nearby wall 4). The angular range thus extends from - ⁇ max to ⁇ max .
  • the end point P2 is given by the location along the perimeter where the local inclination exceeds the maximum design angle ⁇ max , as indicated in Fig. 5A .
  • the constrained perimeter has an overall extent ⁇ L in the longitudinal direction L and an overall extent ⁇ T in the transverse direction T.
  • the present Applicant has found that a favorable distribution of stress is achieved by designing the concave portion 15 with a constrained perimeter such that ⁇ T/ ⁇ L ⁇ 2. For example, it may be desirable to configure the concave portion 15 with ⁇ T/ ⁇ L ⁇ 1.5, ⁇ T/ ⁇ L ⁇ 1 or ⁇ T/ ⁇ L ⁇ 0.5.
  • the mounting plate 7 abuts on and is attached to the end surface 5 along the entire extent of the constrained perimeter. This configuration may improve the stability and durability of the heat exchanger.
  • the maximum design angle ⁇ max set to a value of about 65°, although other values are conceivable.
  • the maximum design angle ⁇ max generally defines the end point P2, and that the local inclination may be significantly smaller than ⁇ max along a significant portion of the constrained perimeter.
  • a further design criterion may be applied to restrict the local inclination to a main angle ⁇ main for at least 30%, and typically at least 50%, of the constrained perimeter.
  • the main angle ⁇ main may set the inclination of the linear portion that connects circular arcs (defined by R1, R2 in Fig. 5A ).
  • the main angle ⁇ main is smaller than the maximum design angle ⁇ max and may e.g. be set to approximately 55°, 45°, 35°, 25°, 15° or 5°.
  • the main angle ⁇ main may even be 0, which means that the constrained perimeter would partially extend in alignment with the wall 4, i.e. along the dashed line 4 in Fig. 5A .
  • the radii R1, R2 of the circular arcs, as well as the extent of the line portion (if present) that connects the circular arcs, may be set so as to fulfill the above-described design criteria. It should also be noted that even if an implementation with circular arcs and an essentially linear portion that connects the circular arcs (as in Figs 5A-5B ) may simplify manufacture of the mounting plates 7, other configurations of the inward and outward corners are conceivable.
  • the transverse spacing ⁇ T between the starting point P1 and the intersection point 11 fulfills ⁇ T/ ⁇ L ⁇ 0.2, and preferably ⁇ T/ ⁇ L ⁇ 0.1. In a practical implementation, this may correspond to a transverse spacing ⁇ T of less than about 5 mm.
  • Figs 5C-5D are perspective views from above and below, respectively, of the juncture between the mounting plate 7 and the plate package 2 for the embodiment in Fig. 5A , where Fig. 5C is taken within the dashed rectangle 5C in Fig. 1 .
  • further structures are located in the interface between the plate package and the mounting plate 7, for the purpose of improving the stability and durability of the heat exchanger 1.
  • These structures include a sealing plate 21 which is connected to the stack of heat exchanger plates 3 to define a bottom surface of the plate package 2.
  • the sealing plate 21, as shown in Fig. 7 is generally planar and has through-holes 22 at its corners to be mated with corresponding through-holes in the heat exchanger plates 3.
  • the perimeter of the sealing plate 21 is bent upwards to form a surrounding flange 23 which adapted to abut on and be fixed to a corresponding flange of an overlying heat exchanger plate, as is known in the art.
  • the material thickness of the sealing plate 21 typically exceeds the material thickness of the heat exchanger plates, and thus the surrounding flange 23 may project slightly beyond the perimeter of the surrounding wall 4 (by 1-2 mm). This is illustrated in the bottom plan views of Figs 5A-5B .
  • the mounting plates 7 may be directly attached to the sealing plate 21.
  • the sealing plate 21 is an end plate that defines the end surface 5.
  • an additional plate 24 is attached intermediate the sealing plate 21 and the mounting plate 7 for the purpose of reinforcing the bottom surface of the plate package 2.
  • the end surface 5 is defined by this additional reinforcement or supporting plate 24.
  • the use of such a reinforcement plate 24 may be advantageous when the working pressure of one or both of the media conveyed through the heat exchanger 1 is high or when the working pressure for one or both of the media varies over time.
  • the reinforcement plate 24, which is shown in greater detail in Fig. 8 has a uniform thickness and defines through-holes 25 which are matched to the portholes in the plate package 2.
  • the perimeter of the reinforcement plate 24 may be essentially level with the perimeter of the sealing plate 21 or the perimeter of the wall 4 of the plate package 2.
  • the reinforcement plate 24 is adapted to locally project from the perimeter of the wall 4.
  • the reinforcement plate 24 is provided with cutouts 26 that are located to extend in the longitudinal direction between the intersection points 11 on a respective transverse side of the plate package 2 so as to be essentially level with the axial wall 4.
  • the cutouts 26 are slightly displaced inwardly from the axial wall 4.
  • the longitudinal end points of the cutouts 26 define a respective transition 27 to a projecting tab portion 28.
  • the transitions 27 are located to overlap the perimeter of the mounting plate 7 in proximity to the intersection points 11 and are shaped to be non-perpendicular to the perimeter of the mounting plate 7 at the overlap, as seen in a direction towards the bottom of the heat exchanger 1. This configuration of the reinforcement plate 24 will locally decrease the stress in the reinforcement plate 24 at the intersection points 11.
  • the transitions 27 may e.g. form a bevel or a curve from the cutout 26 to the tab 28.
  • the transitions 27 are further configured to essentially co-extend with perimeter of the mounting plate 7 at the overlap.
  • the tab portions 28 protrude from the plate package 2 to essentially co-extend with and abut against a respective mounting plate 7. This has been found to result in a favorable distribution of stress between the mounting plate 7, the reinforcement plate 24 and the sealing plate 21 especially at the corners of the plate package 2. It will also increase the strength of the joint between the reinforcement plate 24 and the mounting plate 7 due to the increased contact area between them.
  • the reinforcement plate 24 projects from the plate package 2 around its entire perimeter except for small notches that are located in the proximity of the intersection points 11 to provide transitions 27 that are appropriately shaped to be non-perpendicular to, and preferably co-extending with, the perimeter of the mounting plate 7.
  • the design of the mounting plate 7, and the reinforcement plate 24 if present, may be optimized based on the general principles outlined above, by simulating the distribution of stress in the heat exchanger structure. Such simulations may serve to adapt one or more of the thickness of the mounting plates 7, the width of the mounting plate 7 in the longitudinal direction L, the shape and location of the concave portions 15, as well as further design parameters for the concave portions 15, such as the extents ⁇ L, ⁇ T (for a given ⁇ max ), the transverse spacing ⁇ T, the radii R1, R2, and the main angle ⁇ main .
  • the simulations may be based on any known technique for numerical approximation of stress, such as the finite element method, the finite difference method, and the boundary element method.
  • FIGs 9A-9B A few non-limiting examples of alternative configurations of the concave portion 15 is shown in Figs 9A-9B .
  • a simulation of the stress distribution within the structure in Figs 5C-5D indicates that stresses are well-distributed without any significant peaks in the interface between the reinforcement plate 24 and the sealing plate 21.
  • the maximum stress levels are distributed along arrow L1, which is co-located with the starting point P1 ( Fig. 5A ).
  • the stress values are approximately 80 N/mm 2 (MPa).
  • the simulation also indicates that stresses are equally well-distributed in the interface between the mounting plate 7 and the reinforcement plate 24, where maximum stress levels of approximately 50 N/mm 2 are distributed along arrow L2 in Fig. 5D .
  • the arrow L2 is co-located with the end point P2.
  • FIG. 9A indicates corresponding maximum stress levels with a similar distribution.
  • Simulations for the structure in Fig. 9B indicate maximum stress levels of approximately 110 N/mm 2 around the starting point P1 and approximately 60 N/mm 2 around the end point P2.
  • the stress distribution has also been simulated, for the same vibration load condition, within a heat exchanger provided with a convex mounting plate 7, i.e. a mounting plate 7 without concave portions, as shown in Fig. 6 .
  • the reinforcement plate 24 has the same extension as the sealing plate 21.
  • the width of the mounting plates 7 in the longitudinal direction L may be set to minimize weight and/or cost of the heat exchanger. Such a constraint may also limit the available width W of the concave portion 15 in the longitudinal direction L.
  • the width W is generally indicated in Figs 9A-9B .
  • the width W should be as long as possible so as to distribute stress over a longer perimeter.
  • the width W is typically limited in practice.
  • the above-described design criteria stipulate that ⁇ T/ ⁇ L ⁇ 2 for effective suppression of stress concentration. This does not necessarily mean that it is optimal to minimize ⁇ T/ ⁇ L.
  • the design parameters, and thus ⁇ T/ ⁇ L may be optimized to minimize the maximum stress values for any given width W.
  • the structures in Figs 9A-9B have been optimized in this way.
  • at ⁇ T/ ⁇ L 1.7 for the structure in Fig. 9B .
  • the optimum ⁇ T/ ⁇ L increases with decreasing width W. This can be understood by considering that although the stresses at the starting point P1 will decrease with increasing width W and with decreasing ⁇ T (i.e.
  • edge surface 14 may have any shape and angle to the top and bottom surfaces 12, 13 of the mounting plate 7.
  • the reinforcement plate 24, as described and exemplified herein, may also be installed in a plate heat exchanger 1 with convex mounting plates 7, e.g. as shown in Fig. 6 , to increase the stability and durability of the plate heat exchanger 1 and, to a certain degree, counteract stress concentration at the intersection points 11.
  • a reinforcement plate 24 may provide supporting flanges 28 that extend beyond the perimeter of the surrounding wall 4 and are permanently connected to the top surface 12 of the mounting plates 7.
  • the reinforcement plate 24 may also define the above-described transitions 27, which are located to overlap the perimeter of the respective mounting plate 7 at the intersection points 11 and are shaped to be non-perpendicular to, and preferably co-extending with, the perimeter of the respective mounting plate 7 at the overlap.
  • top, bottom, vertical, vertical, etc merely refer to directions in the drawings and does not imply any particular positioning of the heat exchanger 1. Nor does this terminology imply that the mounting plates 7 need to be arranged on any particular end of the plate package 2.
  • the mounting plates may alternatively be arranged on the top axial end of the plate package 2 and may be permanently connected either to a sealing plate or to a reinforcement plate overlying the sealing plate.
  • the mounting plates 7 may be arranged on an end of the plate package 2 that lacks portholes or on which each or at least one porthole 6 is located intermediate the mounting plates 7.

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

Claims (19)

  1. Échangeur de chaleur à plaques, comprenant :
    une pluralité de plaques d'échangeur de chaleur (3) qui sont empilées et raccordées de manière permanente pour former un ensemble de plaques (2) qui définit des premier et deuxième chemins de fluide, pour respectivement un premier milieu et un deuxième milieu, séparés par lesdites plaques d'échangeur de chaleur (3), ledit ensemble de plaques (2) définissant une paroi externe (4) environnante qui s'étend dans une direction axiale (A) entre des première et deuxième extrémités axiales,
    une plaque d'extrémité (21 ; 24) raccordée de manière permanente à une parmi les première et deuxième extrémités axiales de manière à fournir une surface d'extrémité (5) qui s'étend entre des première et deuxième extrémités longitudinales dans un plan latéral qui est orthogonal par rapport à la direction axiale (A), et
    deux plaques de montage (7) raccordées de manière permanente à une partie surface respective de la surface d'extrémité (5) au niveau de la première extrémité longitudinale et de la deuxième extrémité longitudinale, respectivement, de telle manière que les plaques de montage (7) sont espacées les unes par rapport aux autres dans une direction longitudinale (L) sur la surface d'extrémité (5), dans lequel la plaque de montage (7) respective comprend des surfaces de mise en prise (12, 13) plates se faisant face raccordées grâce à une partie bord qui s'étend le long du périmètre de la plaque de montage (7), dans lequel
    la plaque de montage (7) respective est agencée avec une de ses surfaces de mise en prise (12, 13) raccordée de manière permanente à la surface d'extrémité (5), de telle manière que le périmètre de la plaque de montage (7) s'étend partiellement au-delà de la paroi externe (4) environnante, de manière à définir une bride de montage (9), et caractérisé en ce que la plaque de montage (7) respective s'étend partiellement sur la surface d'extrémité (5) en étant en contact avec celle-ci au sein du périmètre de la paroi externe (4) environnante, et
    le périmètre de la plaque de montage (7) comprend deux parties concaves (15), vu dans une direction normale par rapport à la surface d'extrémité (5), les parties concaves (15) étant situées de manière à croiser la paroi externe (4) environnante au niveau d'un point d'intersection respectif (11).
  2. Échangeur de chaleur à plaques selon la revendication 1, dans lequel un sous-ensemble de la partie concave (15) respective est située au niveau ou au sein de la paroi externe (4) environnante et n'est pas perpendiculaire au périmètre de la paroi externe (4) environnante au niveau du point d'intersection respectif (11), vu dans la direction normale par rapport à la surface d'extrémité (5).
  3. Échangeur de chaleur à plaques selon la revendication 2, dans lequel ledit sous-ensemble de la partie concave (15) respective s'étend à partir d'un point de départ (P1) jusqu'à un point terminal (P2) sur la partie concave (15), de telle manière que l'inclinaison locale de la partie concave, fournie par une ligne tangente, le long dudit sous-ensemble est inférieure à un angle de consigne maximal (αmax), et dans lequel le point terminal (P2) est situé là où l'inclinaison locale dépasse l'angle de consigne maximal (αmax).
  4. Échangeur de chaleur à plaques selon la revendication 3, dans lequel l'angle de consigne maximal est défini entre la ligne tangente et la direction longitudinale (L) et présente une valeur d'approximativement 65°.
  5. Échangeur de chaleur à plaques selon la revendication 3 ou 4, dans lequel ledit sous-ensemble comprend une partie essentiellement linéaire au sein d'au moins 30% dudit sous-ensemble, ladite partie linéaire présentant un angle (αmain) prédéfini, par rapport à la direction longitudinale (L), qui est inférieur à l'angle maximal (αmax).
  6. Échangeur de chaleur à plaques selon l'une quelconque des revendications 3 à 5, dans lequel ledit sous-ensemble de la partie concave (15) respective présente une première étendue (ΔL) dans la direction longitudinale (L) et une deuxième étendue (ΔT) dans une direction transversale (T), qui est orthogonale par rapport à la direction longitudinale (L) dans le plan de la plaque de montage (7), dans lequel le rapport de la deuxième étendue (ΔT) sur la première étendue (ΔL) est inférieur ou égal à approximativement 2, et est de manière préférée inférieur ou égal à approximativement 1 ou approximativement 0,5.
  7. Échangeur de chaleur à plaques selon l'une quelconque des revendications 3 à 6, dans lequel le point de départ (P1) prédéfini dudit sous-ensemble est situé à l'intérieur d'une distance de consigne maximale (δT), dans la direction transversale (T), à partir du point d'intersection respectif (11), dans lequel la distance de consigne maximale (δT) représente 20% de la première étendue (ΔL).
  8. Échangeur de chaleur à plaques selon l'une quelconque des revendications 3 à 7, dans lequel le point de départ (P1) coïncide essentiellement avec le point d'intersection respectif (11).
  9. Échangeur de chaleur à plaques selon l'une quelconque des revendications 3 à 8, dans lequel ledit point terminal (P2) est situé sur un coin extérieur de la plaque de montage (7), ledit coin extérieur étant défini grâce à un deuxième rayon (R2).
  10. Échangeur de chaleur à plaques selon l'une quelconque des revendications précédentes, dans lequel le périmètre de la plaque de montage (7) n'est pas perpendiculaire au périmètre de la paroi externe (4) environnante au niveau du point d'intersection respectif (11), vu dans la direction normale par rapport à la surface d'extrémité (5).
  11. Échangeur de chaleur à plaques selon l'une quelconque des revendications 2 à 9, dans lequel la plaque de montage (7) est contiguë sur la surface d'extrémité (5) et raccordée de manière permanente à celle-ci le long dudit sous-ensemble de la partie concave (15).
  12. Échangeur de chaleur à plaques selon l'une quelconque des revendications précédentes, dans lequel la partie concave (15) respective comprend un coin intérieur défini par un premier rayon (R1), ledit coin intérieur croisant la paroi externe (4) environnante au niveau du point d'intersection (11), vu dans la direction normale par rapport à la surface d'extrémité (5).
  13. Échangeur de chaleur à plaques selon l'une quelconque des revendications précédentes, dans lequel la partie concave (15) respective s'étend entre deux points limites (C1, C2) sur le périmètre de la plaque de montage (7), lesdits points limites (C1, C2) étant définis par une droite mathématique (ML) qui croise le périmètre de la plaque de montage (7) seulement au niveau des points limites (C1, C2) et qui s'étend au-delà du périmètre de la plaque de montage (7) entre les points limites (C1, C2), vu dans la direction normale par rapport à la surface d'extrémité (5).
  14. Échangeur de chaleur à plaques selon l'une quelconque des revendications précédentes, dans lequel la plaque d'extrémité (21) est une plaque de fermeture étanche qui est raccordée de manière permanente et étanche à l'une des plaques d'échangeur de chaleur (3) au niveau d'une parmi lesdites première et deuxième extrémités axiales.
  15. Échangeur de chaleur à plaques selon l'une quelconque des revendications 1 à 13, dans lequel la plaque d'extrémité (24) est une plaque de renforcement (24) qui est raccordée de manière permanente à une plaque d'étanchéité (21) sur l'ensemble de plaques (2), dans lequel la plaque d'extrémité (24) présente au moins deux brides d'appui (28) qui s'étendent au-delà du périmètre de la paroi externe (4) environnante de manière à être contiguës sur la bride de montage (9) définie par la plaque de montage (7) respective.
  16. Échangeur de chaleur à plaques selon la revendication 15, dans lequel la plaque d'extrémité (24) comprend, le long de son périmètre et vu dans la direction normale par rapport à la surface d'extrémité (5), des surfaces concaves ou biseautées (27) adjacentes aux brides d'appui (28), dans lequel les surfaces concaves ou biseautées (27) sont situées de manière à chevaucher le périmètre de la plaque de montage (7) respective au niveau des points d'intersection (11), et dans lequel la surface concave ou biseautée (27) respective n'est pas perpendiculaire au périmètre de la plaque de montage (7) au niveau du chevauchement, vu dans la direction normale par rapport à la surface d'extrémité (5), et s'étend de manière préférée conjointement audit périmètre.
  17. Échangeur de chaleur à plaques selon l'une quelconque des revendications précédentes, dans lequel au moins une des plaques de montage (7) définit au moins un trou traversant (8) qui s'étend entre les surfaces de mise en prise (12, 13) et est alignée avec un trou traversant (22 ; 25) correspondant défini dans la plaque d'extrémité (21 ; 24) et un canal interne défini dans l'ensemble de plaques (2), de manière à former une entrée ou une sortie pour le premier ou le deuxième milieu.
  18. Échangeur de chaleur à plaques selon l'une quelconque des revendications précédentes, dans lequel la bride de montage (9) comprend une pluralité de trous de montage (10) conçus pour recevoir des boulons ou des goupilles permettant de fixer l'échangeur de chaleur à plaques.
  19. Échangeur de chaleur à plaques selon l'une quelconque des revendications précédentes, dans lequel les plaques d'échangeur de chaleur (3) sont réunies de manière permanente les unes aux autres par fusion d'un matériau métallique.
EP13198883.4A 2013-12-20 2013-12-20 Échangeur de chaleur à plaques avec bride de montage Active EP2886996B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP13198883.4A EP2886996B1 (fr) 2013-12-20 2013-12-20 Échangeur de chaleur à plaques avec bride de montage
SE1650782A SE1650782A1 (en) 2013-12-20 2014-12-11 Plate heat exchanger with mounting flange
PCT/EP2014/077423 WO2015091215A1 (fr) 2013-12-20 2014-12-11 Échangeur thermique à plaques avec bride de montage
TW103144274A TWI539135B (zh) 2013-12-20 2014-12-18 具有安裝凸緣的板式熱交換器

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13198883.4A EP2886996B1 (fr) 2013-12-20 2013-12-20 Échangeur de chaleur à plaques avec bride de montage

Publications (2)

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EP2886996A1 EP2886996A1 (fr) 2015-06-24
EP2886996B1 true EP2886996B1 (fr) 2016-07-13

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EP (1) EP2886996B1 (fr)
SE (1) SE1650782A1 (fr)
TW (1) TWI539135B (fr)
WO (1) WO2015091215A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10347181A1 (de) 2003-10-10 2005-05-19 Modine Manufacturing Co., Racine Wärmetauscher, insbesondere Ölkühler
DE102007008459A1 (de) 2006-02-22 2007-12-13 Behr Gmbh & Co. Kg Stapelscheibenwärmeübertrager
CN201285244Y (zh) 2008-10-21 2009-08-05 宁波路润冷却器制造有限公司 板翅式机油冷却器
US20100258095A1 (en) 2009-03-13 2010-10-14 Christian Saumweber Heat exchanger
WO2011009412A1 (fr) 2009-07-23 2011-01-27 Caterpillar Inc. Ensemble échangeur de chaleur, et machine utilisant cet ensemble
US8181695B2 (en) 2005-10-05 2012-05-22 Dana Canada Corporation Reinforcement for dish plate heat exchangers
DE202012007775U1 (de) 2012-04-26 2012-10-15 Dana Canada Corporation Wärmetauscher mit Adaptermodul
DE102011080824A1 (de) 2011-08-11 2013-02-14 Mahle International Gmbh Plattenwärmetauscher

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10347181A1 (de) 2003-10-10 2005-05-19 Modine Manufacturing Co., Racine Wärmetauscher, insbesondere Ölkühler
US20050121182A1 (en) 2003-10-10 2005-06-09 Jurgen Hummel Heat exchanger, especially oil cooler
US8181695B2 (en) 2005-10-05 2012-05-22 Dana Canada Corporation Reinforcement for dish plate heat exchangers
DE102007008459A1 (de) 2006-02-22 2007-12-13 Behr Gmbh & Co. Kg Stapelscheibenwärmeübertrager
CN201285244Y (zh) 2008-10-21 2009-08-05 宁波路润冷却器制造有限公司 板翅式机油冷却器
US20100258095A1 (en) 2009-03-13 2010-10-14 Christian Saumweber Heat exchanger
WO2011009412A1 (fr) 2009-07-23 2011-01-27 Caterpillar Inc. Ensemble échangeur de chaleur, et machine utilisant cet ensemble
DE102011080824A1 (de) 2011-08-11 2013-02-14 Mahle International Gmbh Plattenwärmetauscher
DE202012007775U1 (de) 2012-04-26 2012-10-15 Dana Canada Corporation Wärmetauscher mit Adaptermodul

Also Published As

Publication number Publication date
EP2886996A1 (fr) 2015-06-24
SE1650782A1 (en) 2016-06-03
WO2015091215A1 (fr) 2015-06-25
TW201525408A (zh) 2015-07-01
TWI539135B (zh) 2016-06-21

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