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    • 专利摘要:
    A plate heat exchanger (1) comprises a plate package (2) of permanently connected heat exchanger plates that defines a surrounding wall (4). Two mounting plates (7) are permanently connected to an end surface (5) of the plate package (2), in spaced relation to each other. Each mounting plate (7) comprises opposing flat engagement surfaces connected by an edge portion that extends along the perimeter of the mounting plate (7). Each mounting plate (7) is arranged with one of its engagement surfaces permanently connected to the end surface (5), such that the perimeter of the mounting plate (7) partially extends beyond the surrounding wall (4), to define a mounting flange, and partially extends across the end surface (5) in contact with the same within the perimeter of the surrounding wall (4). The perimeter of the mounting plate (7) defines a concave shape comprising two concave portions (15) as seen in a normal direction to the end surface (5), the concave portions (15) being located to intersect the surrounding external wall (4).Elected for publication: Fig. 2
    公开号:SE1650782A1
    申请号:SE1650782
    申请日:2014-12-11
    公开日:2016-06-03
    发明作者:Larsson Håkan；Bader Roger
    申请人:Alfa Laval Corp Ab；
    IPC主号:
    专利说明:

    PLATE HEAT EXCHANGER WITH MOUNTING FLANGE Technical Field The present invention relates to a plate heat exchanger that comprises a pluralityof heat exchanger plates which are stacked and permanently connected to form a platepackage 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.
    Background Heat exchangers are utilized in various technical applications for transferring heatfrom one fluid to another fluid. Heat exchangers in plate configuration are well-known inthe art. ln these heat exchangers, a plurality of stacked plates having overlappingperipheral side walls are put together and permanently connected to define a platepackage with hollow fluid passages between the plates, usually with different fluids inheat exchange relationship in alternating spaces between the plates. Usually a coherentbase plate or mounting plate is directly or indirectly attached to the outermost one of thestacked plates. The mounting plate has an extension that exceeds the stack of plates soas to define a circumferential mounting flange. The mounting flange has holes orfasteners to attach the heat exchanger to a piece of equipment. This type of plate heatexchanger is e.g. known from US2010/O258095 and US8181695.
    When fastened on the piece of equipment, the mounting plate may be subjected toa significant pressure and weight load which tends to deform the mounting plate. Toachieve an adequate strength and rigidity, the mounting plate needs to be comparativelythick. Such a thick mounting plate may add significantly to the weight of the heatexchanger. Furthermore, the use of a thick mounting plate leads to a larger consumptionof material and a higher cost for the heat exchanger.
    The need for a thick mounting plate may be particularly pronounced when the heatexchanger is mounted in an environment which is subjected to vibrations. Suchvibrations may e.g. occur when the plate heat exchanger is mounted in a vehicle such asa car, truck, bus, ship or airplane. ln these environments, the design of the plate heatexchanger 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 unload-ing of the mounting plate by the vibrations. The cyclic stresses in the heat exchangermay cause it to fail due to fatigue, especially in the joints between the plates, even if thenominal 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 willmake it even more difficult to keep down the weight and cost of the plate heat exchanger.
    Summarylt is an objective of the invention to at least partly overcome one or more limitations of the prior art.
    Another objective is to provide a plate heat exchanger with a relatively low weightand a relatively high strength when mounted to an external supporting structure.
    A further objective is to provide a plate heat exchanger that can be manufacturedat low cost.
    Yet another objective is to provide a plate heat exchanger suitable for use inenvironments subjected to vibrations.
    One or more of these objects, as well as further objects that may appear from thedescription below, are at least partly achieved by a plate heat exchanger according to theindependent claim, embodiments thereof being defined by the dependent claims.
    A first aspect of the invention is a plate heat exchanger, comprising: a plurality ofheat exchanger plates which are stacked and permanently connected to form a platepackage that defines first and second fluid paths for a first medium and a secondmedium, respectively, separated by said heat exchanger plates, said plate packagedefining a surrounding external wall that extends in an axial direction between first andsecond axial ends; an end plate permanently connected to one of the first and secondaxial ends so as to provide an end surface that extends between first and secondlongitudinal ends in a lateral plane which is orthogonal to the axial direction; and twomounting plates permanently connected to a respective surface portion of the endsurface at the first longitudinal end and the second longitudinal end, respectively, suchthat the mounting plates are spaced from each other in a longitudinal direction on theend surface, wherein the respective mounting plate comprises opposing flat engagementsurfaces connected by an edge portion that extends along the perimeter of the mountingplate. The respective mounting plate is arranged with one of its engagement surfacespermanently connected to the end surface, such that the perimeter of the mounting platepartially 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 theperimeter of the surrounding external wall. The perimeter of the mounting plate defines aconcave shape comprising two concave portions as seen in a normal direction to the endsurface, the concave portions being located to intersect the surrounding external wall ata respective intersection point.
    The inventive plate heat exchanger is based on the insight that the coherentmounting plate of the prior art may be replaced by tvvo smaller mounting plates that arelocated at a respective longitudinal end on the end surface on the plate package toprovide 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 itsmanufacturing cost, since material is eliminated in the space between the mountingplates, beneath the end surface of the plate package. The inventive heat exchanger isfurthermore based on the insight that the use of two separated mounting plates may leadto local stress concentration in the heat exchanger, which may act to reduce the heatexchanger's ability to sustain loads, and in particular cyclic loads. The concentration ofstress has been found to originate in the region where the edge portion of the mountingplate intersects the surrounding wall of the plate package. To counteract stressconcentration in a simple and efficient way, the perimeter of the mounting plate is shapedwith two concave portions which are located to intersect the surrounding wall at arespective intersection point. An improved distribution of stress is enabled since theconcave portions increase the extent of the perimeter of the mounting plate in a region atand around the intersection points and since the concave portions may orient theperimeter of the mounting plate to the surrounding wall so as to distribute stress.
    The distribution of stress may be controlled further by optimizing the designparameters of the heat exchanger in general, and the mounting plates in particular, forexample according to the following embodiments. ln one embodiment, a subset of the respective concave portion is located at orwithin the surrounding external wall and is non-perpendicular to the perimeter of thesurrounding external wall at the respective intersection point, as seen in the normaldirection to the end surface. The subset of the respective concave portion may extendfrom a starting point to an end point on the concave portion, such that the localinclination of the concave portion, given by a tangential line, along said subset is lessthan a maximum design angle, and the end point may be located where the localinclination exceeds the maximum design angle. ln one embodiment, the maximum design angle is defined between the tangentialline and the longitudinal direction and has a value of approximately 65 °. ln one embodiment, the subset comprises an essentially linear portion within atleast 30% of the subset, said linear portion having a predefined angle, to the longitudinaldirection, which is less that the maximum design angle. ln one embodiment, the subset of the respective concave portion has a first extentin 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 theratio of the second extent to the first extent is equal to or less than approximately 2, andpreferably equal to or less than approximately 1 or approximately 0.5. ln one embodiment, the predefined starting point of the subset is located within amaximum design distance, in the transverse direction, from the respective intersectionpoint, wherein the maximum design distance is 20% of the first extent. ln one embodiment, the starting point essentially coincides with the respectiveintersection point. ln one embodiment, the end point is located on an outward corner of the mountingplate, the outward corner being defined by a second radius. ln one embodiment, the perimeter of the mounting plate is non-perpendicular to theperimeter of the surrounding external wall at the respective intersection point, as seen inthe normal direction to the end surface. ln one embodiment, the mounting plate abuts on and is permanently connected tothe end surface along said subset of the concave portion. ln one embodiment, the respective concave portion comprises an inward cornerdefined by a first radius, said inward corner intersecting the surrounding external wall atthe intersection point, as seen in the direction normal to the end surface. ln one embodiment, the respective concave portion extends between two limitpoints on the perimeter of the mounting plate, said limit points being defined by amathematical line which intersects the perimeter of the mounting plate only at the limitpoints and which extends beyond the perimeter of the mounting plate intermediate thelimit points, as seen in the direction normal to the end surface. ln one embodiment, the end plate is a sealing plate which is permanently andsealingly connected to one of the heat exchanger plates at one of said first and secondaxial ends. ln an alternative embodiment, the end plate is a reinforcement plate which ispermanently connected to a sealing plate on the plate package, wherein the end platehas at least two supporting flanges that extend beyond the perimeter of the surroundingexternal wall so as to abut on the mounting flange defined by the respective mountingplate. Further, the end plate may comprise, along its perimeter and as seen in the normaldirection of the end surface, concave or beveled surfaces adjacent to the supportingflanges, wherein the concave or beveled surfaces may be located to overlap theperimeter of the respective mounting plate at the intersection points, and the respectiveconcave 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 directionto the end surface. ln one embodiment, at least one of the mounting plates defines at least onethrough hole that extends between the engagement surfaces and is aligned with acorresponding through hole defined in the end plate and an internal channel defined inthe plate package, so as to form an inlet or an outlet for the first or the second medium. ln one embodiment, the mounting flange comprises a plurality of mounting holesadapted to receive bolts or pins for fastening the plate heat exchanger. ln one embodiment, the heat exchanger plates are permanently joined to eachother through melting of metallic material.
    Still other objectives, features, aspects and advantages of the present invention willappear from the following detailed description, from the attached claims as well as fromthe drawings.
    Brief Description of Drawinds Embodiments of the invention will now be described in more detail with referenceto the accompanying schematic drawings.
    Fig. 1 is a perspective view of a plate heat exchanger according to an embodimentof the invention.
    Fig. 2 is a bottom plan view of the plate heat exchanger in Fig. 1.
    Figs 3A-3B are perspective views from two directions of a mounting plate includedin the plate heat exchanger in Fig. 1.
    Fig. 4 is a bottom plan view of the mounting plate in Figs 3A-3B.
    Fig. 5A is an enlarged view of a portion in Fig. 2 to illustrate a set of design para-meters for the mounting plate included in the plate heat exchanger, Fig. 5B is a viewcorresponding to Fig. 5A to illustrate design parameters in an alternative configuration,and Figs 5C-5D are perspective views from above and below, respectively, of the portionshown in Fig. 5A.
    Fig. 6 is a partial perspective view of a plate heat exchanger with a convexmounting plate.
    Fig. 7 is a perspective view of a sealing plate included in the plate heat exchangerof Fig. 1.
    Fig. 8 is a perspective view of a reinforcement plate included in the plate heatexchanger of Fig. 1.
    Figs 9A-9B are partial plan views of a plate heat exchanger with concave mountingplates of alternative configuration.
    Detailed Description of Example Embodiments Embodiments of the present invention relate to configurations of a mountingstructure on a plate heat exchanger. Corresponding elements are designated by thesame reference numerals.
    Figs 1-2 disclose an embodiment of a plate heat exchanger 1 according to theinvention. The plate heat exchanger 1 comprises a plurality of plates which are stackedone on top of the other to form a plate package 2. The plate package 2 may be of anyconventional design. Generally the plate package 2 comprises a plurality of heatexchanger 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 suchthat heat is transferred through the heat transfer portions from one fluid to the other. Theheat exchanger plates 3 may be single-walled or double-walled. The heat exchangerplates 3 are only schematically indicated in Fig. 1, since they are well-known to theperson 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 roundedcorners. Other shapes are conceivable. Generally, the plate package 2 defines asurrounding external wall 4 which extends in a height or axial direction A between a topaxial end and a bottom axial end. The wall 4 has a given perimeter or contour at itsbottom axial end. ln the illustrated example, the wall 4 has essentially the same contouralong its extent in the axial direction A. The bottom axial end of the plate package 2comprises or is provided with an essentially planar end surface 5 (Fig. 2), which may butneed not conform to the contour of the wall 4 at the bottom axial end. The end surface 5extends in a lateral plane. Generally, the plate package 2, and the end surface 5,extends between two longitudinal ends in a longitudinal direction L and between twotransverse ends in a transverse direction T (Fig. 2).
    Although not shown on the drawings, the heat transfer plates 3 have in their cornerportions through-openings, which form inlet channels and outlet channels in communi-cation with the flow passages for the first fluid and the second fluid. These inlet andoutlet channels open in the end surface 5 of the plate package 2 to define separateportholes for inlet and outlet of the first and second fluids, respectively. ln the illustratedexample, 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 aspace free of material beneath the center portion of the plate package 2. Compared to using a single mounting plate that extends beneath the entire plate package 2, theillustrated configuration saves weight and material of the heat exchanger 1, and therebyalso cost. Each mounting plate 7 has two through-holes 8 which are mated with arespective pair of the portholes 6 of the plate package 2 to define inlet and outlet ports ofthe heat exchanger 1. The mounting plates 7 are configured for attaching the heatexchanger 1 to an external suspension structure (not shown) such that the inlet andoutlet ports mate with corresponding supply ports for the first and second medium on theexternal structure. Optionally, one or more seals (not shown) may be provided in theinterface between the mounting plate 7 and the external structure.
    Each mounting plate 7 defines a mounting flange 9 that projects from the wall 4and extends around the longitudinal end of the plate package 2. Bores 10 are provided inthe mounting flange 9 as a means for fastening the heat exchanger 1 to the externalstructure. Threaded fasteners or bolts, for example, may be introduced into the bores 10for engagement with corresponding bores in the external structure.
    The plate package 2 and the mounting plates 7 are made of metal, such asstainless steel or aluminum. All the plates in the heat exchanger 1 are permanentlyconnected to each other, preferably through melting of a metallic material, such asbrazing, welding or a combination of brazing and welding. The plates in the platepackage 2 may alternatively be permanently connected by gluing.
    The mounting plates 7 are dimensioned, with respect to material, thickness andextent in the longitudinal and transverse directions, so as to have an adequate strengthand stiffness to the static load that is applied to the mounting plates 7 when fastened onthe external structure. The static load, which tends to deform the mounting plates 7, mayoriginate from a combination of the weight of the heat exchanger 1, internal pressureapplied 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-mentionedseals, via the fasteners and the bores 10. This static load tend to deform the mountingplates 7. As seen in Figs 1-3, the mounting plates 7 are generally designed to have asignificant thickness. As a non-limiting example, the thickness may be 15-40 mm. Thebottom of the plate package 2, on the other hand, is normally made of much thinnermaterial. lf the heat exchanger 1 is installed in an environment where vibrations aretransferred to the mounting plate 7 via the external structure, the heat exchanger 1 alsoneeds to be designed to account for the mechanical stresses caused by the cyclicloading of the vibrations, i.e. cyclic stresses. For example, such vibrations occur for heatexchangers that are mounted in vehicles, such as cars, trucks and ships. ln one non- Iimiting example, the heat exchanger 1 is an oil cooler for an engine. When cyclicstresses are applied to a material, even though the stresses do not cause plasticdeformation, the material may fail due to fatigue especially in local regions with highstress concentration. The use of stiff thick mounting plates 7 connected to a platepackage 2 with a relatively thin bottom is likely to lead to high concentrations of cyclicstress at the interface between the mounting plates 7 and the plate package 2, andpossibly also within the plate package 2.
    Embodiments of the present invention are designed to counteract stressconcentration that may lead to fatigue failure. To this end, the mounting plates 7 have aperimeter with concave portions 15, which are located so as to intersect the perimeter ofthe surrounding wall 4 of the plate package 2, as seen in the normal direction to the endsurface 5. As used herein, the "perimeter" designates the outer contour as seen in planview. ln the plan view of Fig. 2, intersection points 11 between the perimeters of themounting plates 7 and the wall 4 are indicated by black dots. By providing the concaveportions 15 at the intersection points 11, the perimeter of the mounting plate 7 is given anincreased extent in a region at and around the intersection points 11. The increasedextent favors distribution of stress. Furthermore, the concave portions 15 generallydefine more favorable angles between the perimeter of the mounting plate 7 and thesurrounding wall 4 for counteracting stress concentration.
    Figs 3A-3B illustrate a mounting plate 7 in more detail. The mounting plate 7 hasessentially planar top and bottom surfaces 12, 13, where the top surface 12 forms anengagement surface to be permanently connected to the end surface 5 on the platepackage 2, and the bottom surface 13 forms an engagement surface to be applied andfixed to the external supporting structure. The through-holes 8 and bores 10 are formedto extend between the top and bottom surfaces 12, 13. At the perimeter of the mountingplate 7, the top and bottom surfaces are connected by a peripheral edge surface 14. Theedge 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 inplan view. The term "concave shape" is used in its ordinary meaning to denote a shapethat contains at least one portion that bends inwards, i.e. a concave portion. A concaveshape is also known as a "non-convex shape". ln a geometric sense, as shown in Fig. 4,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 MLtouches 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 7between these two locations. As seen in Fig. 4, the respective concave portion 15extends to an inward corner between a distal outward corner, containing the limit pointC1, and a proximate outward corner, containing the limit point G2. ln plan view, the concave portions 15 of the mounting plate 7 are connected by anessentially straight contour line that extends across the end surface 5. This design isselected 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. 2and illustrates a region of overlap between the perimeter of the mounting plate 7 and theplate package 2 near the surrounding wall 4. The wall 4 is hidden from view byintermediate structures (see below), but its location is indicated by a dashed line. ln theillustrated example, the inward corner follows an arc of a circle with radius R1. Similarly,the proximate outward corner, which is located on and attached to the end surface 5,follows an arc of a circle with radius P2. ln the illustrated example, the inward corner andthe proximate outward corner are connected by an essentially straight (linear) lineportion.
    Simulations indicate that a more uniform distribution of stress is favored byconstraining the angles between the concave portion 15 and the surrounding wall 4where the concave portion 15 overlaps the plate package, i.e. at and within the perimeterof the surrounding wall 4. The present Applicant has identified a constraint that may beapplied to a subset of the concave portion 15 that overlaps the plate package. Thissubset is denoted "constrained perimeter" in the following. ln the example of Fig. 5A, theconstrained perimeter extends from a starting point P1, which coincides with theintersection point 11, to a well-defined end point P2. Along the extent of the constrainedperimeter, the local inclination of the perimeter is constrained to be within a predefinedangular range. The local inclination is given by the tangent to the perimeter at eachindividual 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 dmax, which is defined withrespect to the longitudinal direction L (i.e. the direction of the nearby wall 4). The angularrange thus extends from -dmax to dmax. The end point P2 is given by the location along theperimeter where the local inclination exceeds the maximum design angle om, as indica-ted in Fig. 5A. The constrained perimeter has an overall extent AL in the longitudinaldirection L and an overall extent AT in the transverse direction T. The present Applicanthas found that a favorable distribution of stress is achieved by designing the concaveportion 15 with a constrained perimeter such that AT/AL s 2. For example, it may be desirable to configure the concave portion 15 with AT/AL s 1.5, AT/AL s 1 or AT/AL s0.5.
    Although not clearly shown in Fig. 5A, the mounting plate 7 abuts on and isattached to the end surface 5 along the entire extent of the constrained perimeter. Thisconfiguration may improve the stability and durability of the heat exchanger. lt is currently believed that a favorable distribution of stress is achieved with themaximum design angle om set to a value of about 65°, although other values areconceivable. lt should also be noted that the maximum design angle om generallydefines the end point P2, and that the local inclination may be significantly smaller thanomax along a significant portion of the constrained perimeter. Such an example is seen inFig. 5A. Thus, a further design criterion may be applied to restrict the local inclination to amain angle orm", for at least 30%, and typically at least 50%, of the constrainedperimeter. For example, the main angle orm", may set the inclination of the linear portionthat connects circular arcs (defined by R1, P2 in Fig. 5A). The main angle omain is smallerthan the maximum design angle omax and may e.g. be set to approximately 55°, 45°, 35°,25 °, 15° or 5°. The main angle omain may even be 0, which means that the constrainedperimeter would partially extend in alignment with the wall 4, i.e. along the dashed line 4in Fig. 5A. lt is realized that the radii R1, P2 of the circular arcs, as well as the extent of theline portion (if present) that connects the circular arcs, may be set so as to fulfill theabove-described design criteria. lt should also be noted that even if an implementationwith circular arcs and an essentially linear portion that connects the circular arcs (as inFigs 5A-5B) may simplify manufacture of the mounting plates 7, other configurations ofthe inward and outward corners are conceivable. lt is currently believed that the stress distribution is favored by locating the startingpoint P1 of the constrained perimeter at the intersection point 11, as shown in Fig. 5A.However, this means that the local inclination of the perimeter at the intersection point 11should not exceed the maximum design angle omax. However, it is conceivable that otherdesign considerations call for a greater freedom to locate the constrained perimeter.Simulations indicate that a comparable stress distribution is achieved even if the startingpoint P1 is shifted from the intersection point 11. Fig. 5B illustrates an example of a con-cave portion 15 that extends across the wall 4 at right angles, whereby the starting pointP1 is set to the location where the local inclination equals the maximum design angleomax. This means that the starting point P1 is shifted from the intersection point 11 in boththe transverse direction T and the longitudinal direction L. According to one designcriterion, the transverse spacing öT between the starting point P1 and the intersection 11 point 11 fulfills öT/AL s 0.2, and preferably öT/AL s 0.1. ln a practical implementation,this may correspond to a transverse spacing öT of less than about 5 mm. lt should be noted, though, that even if it is possible for the concave portion 15 tointersect the wall 4 at right angles, the distribution of stress is generally favored by a non-perpendicular intersection, e.g. as shown in Fig. 5A.
    For reference, it may be noted that the configuration in Fig. 5A is designed withdmain =15°,AT/AL = 4.75/12.21 = 0.39, öT = 0, R1 = 10 mm, R2 = 4 mm. Theconfiguration in Fig. 5B is designed with dmain = 15°, AT/AL = 8.6/18 = 0.48,öT/AL= 2/18 = 0.11, R1 =1 mm, R2 = 10 mm.
    Figs 5C-5D are perspective views from above and below, respectively, of thejuncture between the mounting plate 7 and the plate package 2 for the embodiment inFig. 5A, where Fig. 5C is taken within the dashed rectangle 5C in Fig. 1. ln this particularexample, further structures are located in the interface between the plate package andthe mounting plate 7, for the purpose of improving the stability and durability of the heatexchanger 1. These structures include a sealing plate 21 which is connected to the stackof heat exchanger plates 3 to define a bottom surface of the plate package 2. Thesealing plate 21, as shown in Fig. 7, is generally planar and has through-holes 22 at itscorners 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 23which adapted to abut on and be fixed to a corresponding flange of an overlying heatexchanger plate, as is known in the art. The material thickness of the sealing plate 21typically exceeds the material thickness of the heat exchanger plates, and thus thesurrounding 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. ln certainembodiments, the mounting plates 7 may be directly attached to the sealing plate 21. lnsuch embodiments, the sealing plate 21 is an end plate that defines the end surface 5.
    However, in the illustrated embodiment, an additional plate 24 is attachedintermediate the sealing plate 21 and the mounting plate 7 for the purpose of reinforcingthe bottom surface of the plate package 2. Thus, the end surface 5 is defined by thisadditional reinforcement or supporting plate 24. The use of such a reinforcement plate 24may be advantageous when the working pressure of one or both of the media conveyedthrough the heat exchanger 1 is high or when the working pressure for one or both of themedia varies over time. The reinforcement plate 24, which is shown in greater detail inFig. 8, has a uniform thickness and defines through-holes 25 which are matched to theportholes in the plate package 2. The perimeter of the reinforcement plate 24 may beessentially level with the perimeter of the sealing plate 21 or the perimeter of the wall 4 of 12 the plate package 2. However, in the illustrated example, the reinforcement plate 24 isadapted to locally project from the perimeter of the wall 4. Specifically, the reinforcementplate 24 is provided with cutouts 26 that are located to extend in the longitudinal directionbetween the intersection points 11 on a respective transverse side of the plate package 2so as to be essentially level with the axial wall 4. ln Figs 5A-5B, however, the cutouts 26are slightly displaced inwardly from the axial wall 4. The longitudinal end points of thecutouts 26 define a respective transition 27 to a projecting tab portion 28. ln the exampleof Figs 5C-5D, the transitions 27 are located to overlap the perimeter of the mountingplate 7 in proximity to the intersection points 11 and are shaped to be non-perpendicularto the perimeter of the mounting plate 7 at the overlap, as seen in a direction towards thebottom of the heat exchanger 1. This configuration of the reinforcement plate 24 willlocally 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. lnFigs 5C-5D, the transitions 27 are further configured to essentially co-extend withperimeter of the mounting plate 7 at the overlap. Further, as seen in Figs 5C-5D, the tabportions 28 protrude from the plate package 2 to essentially co-extend with and abutagainst a respective mounting plate 7. This has been found to result in a favorabledistribution of stress between the mounting plate 7, the reinforcement plate 24 and thesealing plate 21 especially at the corners of the plate package 2. lt will also increase thestrength of the joint between the reinforcement plate 24 and the mounting plate 7 due tothe increased contact area between them. ln an alternative implementation, not shown,the reinforcement plate 24 projects from the plate package 2 around its entire perimeterexcept for small notches that are located in the proximity of the intersection points 11 toprovide transitions 27 that are appropriately shaped to be non-perpendicular to, andpreferably co-extending with, the perimeter of the mounting plate 7.
    The design of the mounting plate 7, and the reinforcement plate 24 if present, maybe optimized based on the general principles outlined above, by simulating the distribu-tion of stress in the heat exchanger structure. Such simulations may serve to adapt oneor more of the thickness of the mounting plates 7, the width of the mounting plate 7 in thelongitudinal direction L, the shape and location of the concave portions 15, as well asfurther design parameters for the concave portions 15, such as the extents AL, AT (for agiven dmax), the transverse spacing öT, the radii R1, R2, and the main angle dmain. Thesimulations may be based on any known technique for numerical approximation ofstress, such as the finite element method, the finite difference method, and the boundaryelement method. 13 A few non-limiting examples of alternative configurations of the concave portion 15is shown in Figs 9A-9B. The configuration in Fig. 9A is designed with dmain = 6°, AT/AL =10.4/29.6 = 0.35, öT = 0, F11 = 10 mm, F12 = 15 mm. The configuration in Fig.9B is designed with dmain = 60°, AT/AL = 1.7, öT = 0, F11 = 10 mm, F12 = 15 mm.
    A simulation of the stress distribution within the structure in Figs 5C-5D, for onespecific vibration load condition, indicates that stresses are well-distributed without anysignificant peaks in the interface between the reinforcement plate 24 and the sealingplate 21. For this particular simulation, the maximum stress levels are distributed alongarrow L1, which is co-located with the starting point P1 (Fig. 5A). Here, the stress valuesare approximately 80 N/mm2 (MPa). The simulation also indicates that stresses areequally well-distributed in the interface between the mounting plate 7 and thereinforcement plate 24, where maximum stress levels of approximately 50 N/mm2 aredistributed along arrow L2 in Fig. 5D. lncidentally, the arrow L2 is co-located with the endpoint P2. Corresponding simulations for the structure in Fig. 9A indicates correspondingmaximum stress levels with a similar distribution. Simulations for the structure in Fig. 9Bindicate maximum stress levels of approximately 110 N/mm2 around the starting point P1and approximately 60 N/mm2 around the end point P2. For comparison, the stressdistribution has also been simulated, for the same vibration load condition, within a heatexchanger provided with a convex mounting plate 7, i.e. a mounting plate 7 withoutconcave portions, as shown in Fig. 6. ln this example, the reinforcement plate 24 has thesame extension as the sealing plate 21. The simulation indicated a significant stressconcentration at the juncture of the mounting plate 7 and the reinforcement plate 24, witha maximum stress value of about 310 N/mm2 in region L3. lt should be understood that the design of the mounting plates 7 is subject toseveral design considerations. For example, the width of the mounting plates 7 in thelongitudinal 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 thelongitudinal direction L. The width W is generally indicated in Figs 9A-9B. ln principle, thewidth W should be as long as possible so as to distribute stress over a longer perimeter.As noted, the width W is typically limited in practice. The above-described design criteriastipulate that AT/AL s 2 for effective suppression of stress concentration. This does notnecessarily mean that it is optimal to minimize AT/AL. instead, the design parameters,and thus AT/AL, may be optimized to minimize the maximum stress values for any givenwidth W. The structures in Figs 9A-9B have been optimized in this way. Thus, themaximum stress values are minimized at AT/AL = 0.35 for the structure in Fig. 9A, and atAT/AL = 1.7 for the structure in Fig. 9B. Generally, the optimum AT/AL increases with 14 decreasing width W. This can be understood by considering that although the stresses atthe starting point P1 will decrease with increasing width W and with decreasing AT (i.e.as the constricted perimeter is being more parallel to the longitudinal direction L),significant stresses are formed at and around the end point P2 if located close to thesurrounding wall 4, when the width W is limited. Thus, the possible optimization withrespect to AT/AL is aimed at balancing the stresses formed at the starting point P1 andthe stresses formed at the end point P2. Generally, with decreasing width W, theoptimum is found by moving the end point P2 away from the wall 4, i.e. by increasing AT,e.g. by increasing the main angle dmain and/or the radius F12. The foregoing discussion isonly given to explain the relevance of the ratio AT/AL and does not imply that the designparameters of the concave portion 15 need to be optimized for a specific width W.
    While the invention has been described in connection with what is presentlyconsidered to be the most practical and preferred embodiments, it is to be understoodthat the invention is not to be limited to the disclosed embodiments, but on the contrary,is intended to cover various modifications and equivalent arrangements included withinthe spirit and the scope of the appended claims.
    For example, the edge surface 14 may have any shape and angle to the top andbottom surfaces 12, 13 of the mounting plate 7.
    The reinforcement plate 24, as described and exemplified herein, may also beinstalled 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 certaindegree, counteract stress concentration at the intersection points 11. Such a reinforce-ment plate 24 may provide supporting flanges 28 that extend beyond the perimeter of thesurrounding wall 4 and are permanently connected to the top surface 12 of the mountingplates 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 theintersection 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.
    As used herein, "top", "bottom", "vertical", "horizontal", etc merely refer todirections in the drawings and does not imply any particular positioning of the heatexchanger 1. Nor does this terminology imply that the mounting plates 7 need to bearranged on any particular end of the plate package 2. Reverting to Fig. 1, the mountingplates may alternatively be arranged on the top axial end of the plate package 2 and maybe permanently connected either to a sealing plate or to a reinforcement plate overlyingthe sealing plate. Furthermore, 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 islocated intermediate the mounting plates 7.
    权利要求:
    Claims (19)
    [1] 1. A plate heat exchanger, comprising: a plurality of heat exchanger plates (3) which are stacked and permanentlyconnected to form a plate package (2) that defines first and second fluid paths for a firstmedium and a second medium, respectively, separated by said heat exchanger plates(3), said plate package (2) defining a surrounding external wall (4) that extends in anaxial direction (A) between first and second axial ends, an end plate (21; 24) permanently connected to one of the first and second axialends so as to provide an end surface (5) that extends between first and secondlongitudinal ends in a lateral plane which is orthogonal to the axial direction (A), and two mounting plates (7) permanently connected to a respective surface portion ofthe end surface (5) at the first longitudinal end and the second longitudinal end,respectively, such that the mounting plates (7) are spaced from each other in alongitudinal direction (L) on the end surface (5), wherein the respective mounting plate(7) comprises opposing flat engagement surfaces (12, 13) connected by an edge portionthat extends along the perimeter of the mounting plate (7), wherein the respective mounting plate (7) is arranged with one of its engagementsurfaces (12, 13) permanently connected to the end surface (5), such that the perimeterof the mounting plate (7) partially extends beyond the surrounding external wall (4), so asto define a mounting flange (9), and partially extends across the end surface (5) incontact with the same within the perimeter of the surrounding external wall (4), and wherein the perimeter of the mounting plate (7) defines a concave shapecomprising two concave portions (15) as seen in a normal direction to the end surface(5), the concave portions (15) being located to intersect the surrounding external wall (4)at a respective intersection point (11).
    [2] 2. The plate heat exchanger of claim 1, wherein a subset of the respective concaveportion (15) is located at or within the surrounding external wall (4) and is non-perpendicular to the perimeter of the surrounding external wall (4) at the respectiveintersection point (11), as seen in the normal direction to the end surface (5).
    [3] 3. The plate heat exchanger of claim 2, wherein said subset of the respectiveconcave portion (15) extends from a starting point (P1) to an end point (P2) on theconcave portion (15), such that the local inclination of the concave portion, given by atangential line, along said subset is less than a maximum design angle (dmax), andwherein the end point (P2) is located where the local inclination exceeds the maximumdesign angle (om). 17
    [4] 4. The plate heat exchanger of claim 3, wherein the maximum design angle isdefined between the tangential line and the longitudinal direction (L) and has a value ofapproximately 65 °.
    [5] 5. The plate heat exchanger of claim 3 or 4, wherein said subset comprises anessentially linear portion within at least 30% of said subset, said linear portion having apredefined angle (dmain), to the longitudinal direction (L), which is less that the maximumdesign angle (om).
    [6] 6. The plate heat exchanger of any one of claims 3-5, wherein said subset of therespective concave portion (15) has a first extent (AL) in the longitudinal direction (L) anda second extent (AT) in a transverse direction (T), which is orthogonal to the longitudinaldirection (L) in the plane of the mounting plate (7), wherein the ratio of the second extent(AT) to the first extent (AL) is equal to or less than approximately 2, and preferably equalto or less than approximately 1 or approximately 0.5.
    [7] 7. The plate heat exchanger of any one of claims 3-6, wherein the predefinedstarting point (P1) of said subset is located within a maximum design distance (öT), inthe transverse direction (T), from the respective intersection point (11), wherein themaximum design distance (öT) is 20% of the first extent (AL).
    [8] 8. The plate heat exchanger of any one of claims 3-7, wherein the starting point(P1) essentially coincides with the respective intersection point (11).
    [9] 9. The plate heat exchanger of any preceding claim, wherein said end point (P2) islocated on an outward corner of the mounting plate (7), said outward corner beingdefined by a second radius (Fl2).
    [10] 10. The plate heat exchanger of any preceding claim, wherein the perimeter of themounting plate (7) is non-perpendicular to the perimeter of the surrounding external wall(4) at the respective intersection point (11), as seen in the normal direction to the endsurface (5).
    [11] 11. The plate heat exchanger of any preceding claim, wherein the mounting plate(7) abuts on and is permanently connected to the end surface (5) along said subset ofthe concave portion (15).
    [12] 12. The plate heat exchanger of any preceding claim, wherein the respectiveconcave portion (15) comprises an inward corner defined by a first radius (Fl1), saidinward corner intersecting the surrounding external wall (4) at the intersection point (11),as seen in the direction normal to the end surface (5).
    [13] 13. The plate heat exchanger of any preceding claim, wherein the respectiveconcave portion (15) extends between two limit points (C1, C2) on the perimeter of themounting plate (7), said limit points (C1, C2) being defined by a mathematical line (ML)which intersects the perimeter of the mounting plate (7) only at the limit points (C1, C2) 18 and which extends beyond the perimeter of the mounting plate (7) intermediate the limitpoints (C1, C2), as seen in the direction normal to the end surface (5).
    [14] 14. The plate heat exchanger of any preceding claim, wherein the end plate (21) isa sealing plate which is permanently and sealingly connected to one of the heatexchanger plates (3) at one of said first and second axial ends.
    [15] 15. The plate heat exchanger of any one of claims 1-13, wherein the end plate (24)is a reinforcement plate (24) which is permanently connected to a sealing plate (21) onthe plate package (2), wherein the end plate (24) has at least two supporting flanges (28)that extend beyond the perimeter of the surrounding external wall (4) so as to abut on themounting flange (9) defined by the respective mounting plate (7).
    [16] 16. The plate heat exchanger of claim 15, wherein the end plate (24) comprises,along its perimeter and as seen in the normal direction of the end surface (5), concave orbeveled surfaces (27) adjacent to the supporting flanges (28), wherein the concave orbeveled surfaces (27) are located to overlap the perimeter of the respective mountingplate (7) at the intersection points (11), and wherein the respective concave or beveledsurface (27) is non-perpendicular to, and preferably co-extending with, the perimeter ofthe mounting plate (7) at the overlap, as seen in the normal direction to the end surface(5).
    [17] 17. The plate heat exchanger of any preceding claim, wherein at least one of themounting plates (7) defines at least one through hole (8) that extends between theengagement surfaces (12, 13) and is aligned with a corresponding through hole (22; 25)defined in the end plate (21; 24) and an internal channel defined in the plate package (2),so as to form an inlet or an outlet for the first or the second medium.
    [18] 18. The plate heat exchanger of any preceding claim, wherein the mounting flange(9) comprises a plurality of mounting holes (10) adapted to receive bolts or pins forfastening the plate heat exchanger.
    [19] 19. The plate heat exchanger of any preceding claim, wherein the heat exchangerplates (3) are permanently joined to each other through melting of metallic material.
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    同族专利:
    公开号 | 公开日
    EP2886996B1|2016-07-13|
    TWI539135B|2016-06-21|
    WO2015091215A1|2015-06-25|
    EP2886996A1|2015-06-24|
    TW201525408A|2015-07-01|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE10347181B4|2003-10-10|2005-12-22|Modine Manufacturing Co., Racine|Heat exchangers, in particular oil coolers|
    CN101317069B|2005-10-05|2010-06-16|达纳加拿大公司|Reinforcement for dish plate heat exchangers|
    DE102007008459A1|2006-02-22|2007-12-13|Behr Gmbh & Co. Kg|Stacked plate heat-exchanger, has reinforcement disk connected with base plate, where baseplate formed as single piece with reinforcement disk is connected at base disk with defined reinforcement structure|
    CN201285244Y|2008-10-21|2009-08-05|宁波路润冷却器制造有限公司|Plate type finned oil cooler|
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    CN201440047U|2009-07-23|2010-04-21|卡特彼勒公司|Heat exchanger device and machine using same|
    DE102011080824A1|2011-08-11|2013-02-14|Mahle International Gmbh|Plate heat exchanger|
    WO2013159172A1|2012-04-26|2013-10-31|Dana Canada Corporation|Heat exchanger with adapter module|
    法律状态:
    2019-09-17| NAV| Patent application has lapsed|
    优先权:
    申请号 | 申请日 | 专利标题
    EP13198883.4A|EP2886996B1|2013-12-20|2013-12-20|Plate heat exchanger with mounting flange|
    PCT/EP2014/077423|WO2015091215A1|2013-12-20|2014-12-11|Plate heat exchanger with mounting flange|
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