TWI539135B - Plate heat exchanger with mounting flange - Google Patents

Description

Plate heat exchanger with mounting flange

The present invention relates to a plate heat exchanger comprising a plurality of heat exchanger plates stacked and permanently joined to form a plate package and permanently connected to the plate package for use in the plate heat exchanger to the exterior A releasably attachable mounting structure of the support structure.

Heat exchangers are utilized in various technical applications to transfer heat from one fluid to another. Heat exchangers in a plate configuration are well known in the art. In such heat exchangers, a plurality of stacked panels having overlapping peripheral sidewalls are assembled together and permanently joined to define a panel package having hollow fluid passages between the panels, typically in an alternating space between the panels. Different fluids in a heat exchange relationship. Typically, a coherent bottom plate or mounting plate is attached directly or indirectly to the outermost one of the stacked plates. The mounting plate has an extension that extends beyond the plate stack to define a circumferential mounting flange. The mounting flange has holes or fasteners to attach the heat exchanger to a piece of equipment. A plate heat exchanger of this type is known, for example, from US 2010/0258095 and US Pat. No. 8181695.

When secured to the piece of equipment, the mounting plate can withstand significant pressure and weight loads that tend to deform the mounting plate. To achieve proper strength and rigidity, the mounting plate needs to be relatively thick. This thick mounting plate can significantly increase the weight of the heat exchanger. In addition, the use of thick mounting plates results in greater material consumption and higher cost of the heat exchanger.

The need for thick mounting plates can be particularly significant when the heat exchanger is installed in an environment subject to vibration. Such vibrations may occur, for example, when the plate heat exchanger is installed in a vehicle such as a car, truck, bus, ship or aircraft. In such environments, the design of the plate heat exchangers is generally required and the design and attachment of the mounting plates in particular requires consideration of the risk of fatigue damage caused by the weekly loading and unloading of the mounting plates by vibration. Even if the nominal stress value is well below the tensile stress limit, the weekly stress in the heat exchanger can cause the heat exchanger to fail due to fatigue, especially in the joint between the plates. The risk of fatigue damage is usually handled by further increasing the thickness of the mounting plate, which would make it even more difficult to reduce the weight and cost of the plate heat exchanger.

One of the objectives of the present invention is to at least partially overcome one or more of the limitations of the prior art.

Another object is to provide a plate heat exchanger that has relatively low gravitational and relatively high strength when mounted to an external support structure.

Yet another object is to provide a plate heat exchanger that can be manufactured at low cost.

Another object is to provide a plate heat exchanger that is suitable for use in an environment subject to vibration.

One or more of these objectives, and further goals that may be apparent from the description below, are at least partially achieved by a plate heat exchanger according to an independent claim, the implementation of which is defined by a dependent request.

A first aspect of the invention is a plate heat exchanger comprising: a plurality of heat exchanger plates stacked and permanently joined to form a plate package, the plate The package defines a first fluid path and a second fluid path for the first medium and the second medium, respectively, the first fluid path and the second fluid path are separated by the heat exchanger plates, the plate package defining a surrounding exterior a wall extending in an axial direction between the first axial end and the second axial end; an end plate permanently connected to the first axial end and the second axial end To provide an end surface extending between the first longitudinal end and the second longitudinal end in a side plane, the side plane being orthogonal to the axial direction; and two mounting plates respectively at the first The longitudinal end and the second longitudinal end are permanently joined to the respective surface portions of the end surface such that the mounting plates are spaced apart from one another in the longitudinal direction on the end surface, wherein the individual mounting plates comprise opposing flat engaging surfaces, The opposite flat engagement surfaces are joined by edge portions that extend along the periphery of the mounting plate. The individual mounting plate is arranged such that one of the mating surfaces of the individual mounting plate is permanently connected to the end surface such that the peripheral portion of the mounting plate extends beyond the surrounding outer wall to define a mounting flange and span the mounting The end surface of the peripheral contact of the panel extends partially within the perimeter of the peripheral outer wall. The perimeter of the mounting plate defines a concave shape that includes two concave portions, as seen in the normal direction of the end surface, the concave portions being positioned at and at individual intersections The outer walls intersect.

The inventive plate heat exchanger is based on the prior art homogenous mounting plate that can be replaced by two smaller mounting plates located at individual longitudinal ends on the end surface of the plate package to provide Individual mounting flanges for heat exchangers. The use of two smaller separate mounting plates reduces the weight of the heat exchanger and also reduces the manufacturing cost of the heat exchanger by eliminating material in the space between the mounting plates below the end surface of the plate package. Furthermore, the inventive heat exchanger is based on the use of two separate mounting plates which can result in a heat exchanger An insight into the local stress concentration that can act to reduce the ability of the heat exchanger to maintain load and, in particular, weekly load. Stress concentration has been found to originate in the portion of the mounting plate where the edge portion intersects the surrounding wall of the plate package. To counteract the stress concentration in a simple and effective manner, the perimeter of the mounting plate is shaped to have two concave portions that are positioned to intersect the surrounding wall at individual intersections. Allowing an improved stress distribution because the concave portion increases the extent of the perimeter of the mounting plate at the intersection and in the portion surrounding the intersection, and because the concave portion can orient the perimeter of the mounting plate to The surrounding wall is for distributing stress.

The stress distribution can be further controlled by, for example, generally optimizing the design parameters of the heat exchanger according to the following embodiments and specifically optimizing the design parameters of the mounting plate.

In one embodiment, the subset of the individual concave portions are located at or within the peripheral outer wall and are not perpendicular to the perimeter of the peripheral outer wall at the individual intersections, such as the normal direction at the end surface See you above. The subset of the individual concave portions may extend from the starting point to the end point on the concave portion such that the local inclination of the concave portion along the subset given by the tangent is less than the maximum design, and the end The point can be located where the local tilt exceeds the maximum design angle.

In an embodiment, the maximum design angle is defined between the tangent and the longitudinal direction and has approximately 65. The value.

In an embodiment, the subset comprises a substantially linear portion within at least 30% of the subset, the linear portion having a predetermined angle relative to the longitudinal direction, the predetermined angle being less than the maximum design angle.

In one embodiment, the subset of the individual concave portions has a first extension in the longitudinal direction and a second extension in the lateral direction, the lateral direction being flat on the mounting plate The face is orthogonal to the longitudinal direction, wherein the ratio of the second extension to the first extension is equal to or less than approximately 2, and is preferably equal to or less than approximately 1 or approximately 0.5.

In one embodiment, the predetermined starting point of the subset is located in the lateral direction within a maximum design distance from the individual intersection, wherein the maximum design distance is 20% of the first extension.

In an embodiment, the starting point substantially coincides with the individual intersection.

In an embodiment, the end point is located on an outward corner of the mounting plate, the outward corner being defined by a second radius.

In one embodiment, the perimeter of the mounting plate is not perpendicular to the perimeter of the peripheral outer wall at the individual intersections, as seen in the normal direction of the end surface.

In an embodiment, the mounting plate abuts the end surface along the subset of the concave portion and is permanently connected to the end surface.

In one embodiment, the individual concave portion includes an inward corner defined by a first radius, the inward corner intersecting the peripheral outer wall at the intersection, as seen in a direction orthogonal to the end surface .

In an embodiment, the individual concave portion extends between the two restriction points on the periphery of the mounting plate, the restriction points being defined by a mathematical line, and the mathematical line is only at the restriction points The perimeter of the mounting plate intersects and the mathematical line extends beyond the perimeter of the mounting plate intermediate the restriction points as seen in a direction normal to the end surface.

In one embodiment, the end plate is a sealing plate that is permanently and sealingly connected to one of the heat exchanger plates at one of the first axial end and the second axial end.

In an alternative embodiment, the end plate is a stiffener that is permanently attached to the seal plate on the plate package, wherein the end plate has at least two support flanges, the at least two support flanges extending The perimeter of the surrounding outer wall is exceeded to abut against the mounting flange defined by the individual mounting plate. Furthermore, the end plate may comprise a concave or beveled surface along its periphery and as seen in the normal direction of the end surface, the concave or beveled surfaces being adjacent to the support flanges, wherein the concave or oblique The surface may be positioned to overlap the perimeter of the individual mounting plate at the intersections, and the individual concave or beveled surface may be such that the overlap is not perpendicular to the perimeter of the mounting plate and the mounting plate The perimeters coextend as seen in the normal direction of the end surface.

In one embodiment, at least one of the mounting plates defines at least one through hole extending between the mating surfaces and a corresponding through hole defined in the end plate and defined in the plate package The inner channel is aligned to form an inlet or outlet for the first medium or the second medium.

In an embodiment, the mounting flange includes a plurality of mounting holes adapted to receive screws or pins for fastening the plate heat exchanger.

In one embodiment, the heat exchanger plates are permanently joined to one another via melting of the metallic material.

The other objects, features, aspects and advantages of the present invention will be apparent from the description and appended claims.

A‧‧‧ Height or axial direction

C1‧‧‧ restriction point

C2‧‧‧Restriction point

L‧‧‧ longitudinal direction

L1‧‧‧ arrow

L2‧‧‧ arrow

L3‧‧‧ District Department

ML‧‧‧Mathematical line

P1‧‧‧ starting point

P2‧‧‧ end point

Radius of R1‧‧

Radius of R2‧‧

T‧‧‧ transverse direction

W‧‧‧Width

△L‧‧‧Extension

△T‧‧‧Extension

δ T‧‧‧lateral spacing

‧‧‧‧ main main angle

Max max‧‧‧Maximum design angle

1‧‧‧ Plate heat exchanger / heat exchanger

2‧‧‧ plate package

3‧‧‧heat exchanger plates

4‧‧‧ surrounding outer wall/wall/surrounding wall

5‧‧‧End surface

5A‧‧‧dotted rectangle

5C‧‧‧dredded rectangle

6‧‧‧ Holes

7‧‧‧Installation board

8‧‧‧through hole

9‧‧‧Flange

10‧‧‧镗孔

11‧‧‧ intersection

12‧‧‧ top surface

13‧‧‧ bottom surface

14‧‧‧ peripheral edge surface/edge surface

15‧‧‧ concave part

21‧‧‧ Sealing plate

22‧‧‧through hole

23‧‧‧around flange

24‧‧‧Extra plate/strength plate

25‧‧‧through hole

26‧‧‧Cuts

27‧‧‧ concave or inclined surface

28‧‧‧Protruding tab part/tab/tab part/support flange

Embodiments of the present invention will now be described in more detail with reference to the accompanying schematic drawings.

1 is a perspective view of a plate heat exchanger according to an embodiment of the present invention.

Figure 2 is a bottom plan view of the plate heat exchanger of Figure 1.

3A to 3B are perspective views of two directions from a mounting plate included in the plate type heat exchanger of Fig. 1.

Figure 4 is a bottom plan view of the mounting plate of Figures 3A-3B.

5A is an enlarged view of a portion of FIG. 2 to illustrate a set of design parameters for a mounting plate included in a plate heat exchanger, and FIG. 5B is a view corresponding to FIG. 5A to illustrate design parameters in an alternative configuration. 5C to 5D are perspective views from the top and the bottom, respectively, of the portion shown in FIG. 5A.

Figure 6 is a partial perspective view of a plate heat exchanger having a convex mounting plate.

Figure 7 is a perspective view of a sealing plate included in the plate heat exchanger of Figure 1.

Figure 8 is a perspective view of a reinforcing plate included in the plate heat exchanger of Figure 1.

9A-9B are partial plan views of a plate heat exchanger having an alternately configured female mounting plate.

Embodiments of the invention relate to the configuration of the mounting structure on a plate heat exchanger. Corresponding components are designated by the same component symbols.

1 to 2 disclose an embodiment of a plate heat exchanger 1 according to the present invention. The plate heat exchanger 1 comprises a plurality of plates stacked on top of each other to form a plate package 2. The plate package 2 can have any conventional design. Typically, the slab package 2 includes a plurality of heat exchanger plates 3 having a wavy heat transfer portion that defines a flow path for the first fluid and the second fluid between the heat exchanger plates 3 (internal grooves) (Channel), causing heat to transfer from one fluid to another via the heat transfer portion. Heat exchanger plate 3 can be single wall or double wall formula. The heat exchanger plates 3 are only schematically indicated in Figure 1, as such heat exchanger plates are well known to those skilled in the art, and the configuration of such heat exchanger plates is not essential to the invention. . Although the plate package 2 has a rounded corner, it has a general shape of a rectangular rectangular parallelepiped. Other shapes are conceivable. Typically, the plate package 2 defines a peripheral outer wall 4 that extends between a top axial end and a bottom axial end in a height or axial direction A. The wall 4 has a given perimeter or profile at its bottom axial end. In the illustrated example, the walls 4 have substantially the same profile along their extension in the axial direction A. The bottom axial end of the plate package 2 contains or has a substantially planar end surface 5 (Fig. 2) that 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. Typically, the plate package 2 and the end surface 5 extend between the two longitudinal ends in the longitudinal direction L and between the two lateral ends in the transverse direction T (Fig. 2).

Although not shown in the drawings, the heat transfer plate 3 has through-openings in its corner portions that form inlet and outlet channels in communication with the flow passages for the first fluid and the second fluid. The inlet and outlet channels are open in the end surface 5 of the slab package 2 to define separate channels for the inlet and outlet of the first fluid and the second fluid, respectively. In the illustrated example, the end surface 5 has four cells 6 (Fig. 2).

The plate package 2 is permanently connected to two identical (in this example) mounting plates 7, which are arranged on individual end portions of the end surfaces 5. The mounting plates 7 are thereby separated in the longitudinal direction L such that the space below the central portion of the plate package 2 is free of material. The illustrated configuration saves the weight and material of the heat exchanger 1 compared to the use of a single mounting plate that extends below the entire panel package 2, and thereby also saves cost. Each mounting plate 7 has two through holes 8 that cooperate with an individual pair of holes 6 of the plate package 2 to define the inlet of the heat exchanger 1 Speaking and exporting. The mounting plate 7 is configured for attaching the heat exchanger 1 to an external suspension structure (not shown) such that the inlet and outlet ports cooperate with corresponding supply ports for the first and second media on the outer structure . Optionally, one or more seals (not shown) may be provided in the interface between the mounting plate 7 and the outer structure.

Each mounting plate 7 defines a mounting flange 9 that projects from the wall 4 and extends around the longitudinal ends of the panel package 2. A bore 10 is provided in the mounting flange 9 as a member for reinforcing the heat exchanger 1 to an external structure. A threaded fastener or screw can be introduced into the bore 10, for example, for engagement with a corresponding bore in the outer structure.

The plate package 2 and the mounting plate 7 are made of metal such as stainless steel or aluminum. All of the plates in heat exchanger 1 are preferably permanently joined to one another by melting of a metallic material such as brazing, welding or a combination of brazing and welding. The plates in the plate package 2 can alternatively be permanently joined by adhesive.

The mounting plate 7 is dimensioned with respect to material, thickness and extension in the longitudinal and transverse directions to provide suitable strength and rigidity to the static load applied to the mounting plate 7 when secured to the outer structure. The static load that tends to deform the mounting plate 7 may originate from a combination of forces: the weight of the heat exchanger 1, the internal pressure applied by the medium in the heat exchanger 1 and transferred to the mounting plate 7, and via fasteners and The bore 10 is applied to the compressive force of the mounting plate 7, for example at the seal mentioned above. This static load tends to deform the mounting plate 7. As seen in Figures 1-3, the mounting plate 7 is typically designed to have a significant thickness. As a non-limiting example, the thickness can be from 15 mm to 40 mm. On the other hand, the bottom of the plate package 2 is normally made of a much thinner material.

If the heat exchanger 1 is placed in a ring in which vibration is transferred to the mounting plate 7 via the external structure In the meantime, the heat exchanger 1 also needs to be designed to be responsible for the mechanical stress (i.e., the weekly stress) caused by the weekly load of the vibration. For example, such vibrations occur with heat exchangers installed in vehicles such as automobiles, trucks, and ships. In a non-limiting example, heat exchanger 1 is an oil cooler for an engine. When the stress is applied to the material once a week, even if the stress does not cause deformation of the plastic, the material may fail due to fatigue particularly in a localized portion having a high stress concentration. The use of a rigid thick mounting plate 7 connected to a plate package 2 having a relatively thin bottom may result in a high concentration of the weekly stresses at the interface between the mounting plate 7 and the plate package 2 and possibly also within the plate package 2.

Embodiments of the invention are designed to counteract stress concentrations that can cause fatigue damage. To this end, the mounting plate 7 has a perimeter containing a concave portion 15 that is positioned to intersect the perimeter of the surrounding wall 4 of the panel package 2, as seen in the normal direction of the end surface 5. As used herein, "perimeter" specifies the outer contour as seen in plan view. In the plan view of Fig. 2, the intersection 11 between the periphery of the mounting plate 7 and the wall 4 is indicated by a black dot. By providing the concave portion 15 at the intersection 11, an increased extension of the periphery of the mounting plate 7 in the region surrounding the intersection 11 is given. The increased extension facilitates the stress distribution. Furthermore, the concave portion 15 generally defines a more favorable angle between the periphery of the mounting plate 7 and the surrounding wall 4 for counteracting stress concentrations.

3A to 3B illustrate the mounting plate 7 in more detail. The mounting plate 7 has a substantially planar top surface 12 and a bottom surface 13, wherein the top surface 12 forms an engagement surface for permanent attachment to the end surface 5 on the panel package 2, and the bottom surface 13 forms an engagement surface for application and fixation to the exterior supporting structure. The through hole 8 and the bore 10 are formed to extend between the top surface 12 and the bottom surface 13. At the periphery of the mounting plate 7, the top and bottom surfaces are joined by a peripheral edge surface 14. The edge surface 14 is substantially planar and opposite the top surface 12 and The bottom surface 13 is at right angles 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 sense to mean the shape of at least a portion (i.e., a concave portion) that contains inward deflection. The concave shape is also referred to as a "non-convex shape". In a geometric sense, as shown in Figure 4, each of the concave portions 15 extends between two well defined limit points C1, C2. The restriction points C1, C2 are positioned at the periphery of the mounting plate 7 to the straight math (imaginary) line ML so as to straddle the concave portion 15. The individual lines ML thus intersect the periphery of the mounting plate 7 only at two locations (at C1 and C2) and are spaced apart from the periphery of the mounting plate 7 between the two positions. As seen in Figure 4, the individual concave portions 15 extend to an inward corner between the far outward corner containing the restriction point C1 and the near outward corner containing the restriction point C2.

In plan view, the concave portion 15 of the mounting plate 7 is joined by a substantially straight contour extending across the end surface 5. This design is chosen to minimize the width of the mounting plate 7 in the longitudinal direction L (Fig. 2). Other designs are imaginable.

5A is taken in the dashed rectangle 5A in the bottom plan view of FIG. 2, and illustrates the overlapping portion between the periphery of the mounting board 7 and the panel package 2 in the vicinity of the surrounding wall 4. The wall 4 is hidden from the field of view by the intermediate structure (see below), but the position of the wall is indicated by a dashed line. In the example shown, the inward corner follows an arc of a circle having a radius R1. Similarly, the nearest outward corner on the end surface 5 and attached to the end surface follows an arc of a circle having a radius R2. In the illustrated example, the inward corners and the most recent outward corners are connected by substantially straight (linear) line portions.

The simulation indicates that a more uniform stress distribution is facilitated by limiting the angle between the concave portion 15 and the peripheral portion 4 where the concave portion 15 overlaps the plate package (i.e., at and around the periphery of the surrounding wall 4). The Applicant has identified constraints that can be applied to a subset of the concave portions 15 of the overlapping plate package. This subset is indicated below as a "restricted" perimeter. In the example of FIG. 5A, the restricted perimeter extends from a starting point P1 that coincides with the intersection 11 to a well defined end point P2. The extension of the perimeter is limited to a predetermined angular extent along the extension of the restricted perimeter. The local tilt is given by the tangent to the perimeter at each individual location on the perimeter, as seen in the normal direction of the end surface 5. The angular extent is given by the maximum design angle α _max , which is defined with respect to the longitudinal direction L (ie the direction near the wall 4). The angular range therefore extends from -α _max to α _max . The end point P2 is given by the position along the periphery where the local tilt exceeds the maximum design angle α _max , as indicated in Figure 5A. The restricted perimeter has an entire extension ΔL in the longitudinal direction L and an entire extension ΔT in the lateral direction T. The Applicant has found that a favorable stress distribution is achieved by designing a concave portion 15 having a restricted perimeter such that ΔT/ΔL 2. For example, it may be desirable to construct the concave portion 15 as ΔT/ΔL 1.5, △ T / △ L 1 or △T/△L 0.5.

Although not clearly shown in Figure 5A, the mounting plate 7 abuts the end surface 5 along the entire extension of the restricted perimeter and is attached to the end surface. This configuration improves the stability and durability of the heat exchanger.

It is currently known that a favorable stress distribution is achieved with the maximum design angle α _max set to a value of about 65°, but other values are conceivable. It should also be noted that the maximum design angle α _max generally defines the end point P2 and the local tilt may be significantly less than α _max along the significant portion of the restricted perimeter. This example is seen in Figure 5A. Accordingly, further design criteria may be applied for at least 30% of the perimeter is limited and typically at least 50% of the local angle of inclination α to the main _primary limit. For example, the primary angle α can be set to connect _{the main} arc (by R1, R2 defined in FIG. 5A) in the inclined linear portion. The main angle α _is less than the maximum design angle α _max and can be set, for example, to approximately 55°, 45°, 35°, 25°, 15° or 5°. Main _primary angle α may even be 0, i.e., this means that the limited periphery extending portion 4 are aligned along the wall 4 in the broken line in FIG. 5A.

It will be appreciated that the extension of the radius R1, R2 of the arc and the portion of the line connecting the arc, if any, may be set to achieve the design criteria described above. It should also be noted that even embodiments having a substantially linear portion of arcs and connecting arcs (as in Figures 5A-5B) may simplify the manufacture of the mounting plate 7, as are other configurations of inward and outward corners. Imagine.

It is currently believed that the stress distribution is facilitated by positioning the starting point P1 of the restricted perimeter at the intersection 11, as shown in Figure 5A. However, this means that the local inclination of the perimeter at the intersection 11 should not exceed the maximum design angle α _max . However, it is conceivable that other design considerations require greater freedom to locate a restricted perimeter. The simulation indicates that a comparable stress distribution is achieved even if the starting point P1 is displaced from the intersection 11. Figure 5B illustrates an example of a concave portion 15 that extends across the wall 4 at a right angle, thereby setting the starting point P1 to a position where the local tilt is equal to the maximum design angle α _max . This means that the starting point P1 is displaced from the intersection 11 in both the lateral direction T and the longitudinal direction L. According to a design criterion, the lateral spacing δ T between the starting point P1 and the intersection 11 is δ T / ΔL 0.2, and preferably δ T/ΔL 0.1. In a practical embodiment, this may correspond to a lateral spacing δ T of less than about 5 mm.

It should be noted that although it is possible for the concave portion 15 to intersect the wall 4 at a right angle, the stress distribution is generally facilitated by non-vertical crossings, such as shown in Figure 5A.

For reference, it can be noted that the configuration in Fig. 5A is designed to be α _main = 15°, ΔT / ΔL = 4.75 / 12.21 = 0.39, δ T = 0, R1 = 10 mm, R2 = 4 mm. The configuration in Fig. 5B is designed to be α _main = 15°, ΔT / ΔL = 8.6 / 18 = 0.48, δ T / ΔL = 2 / 18 = 0.11, R1 = 1 mm, R2 = 10 mm.

5C to 5D are mounting plates 7 and plates for the embodiment of FIG. 5A A perspective view of the joint between the packages 2 from above and below, wherein FIG. 5C is taken within the dashed rectangle 5C of FIG. In this particular example, a further structure is positioned 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 that is connected to the stack of heat exchanger plates 3 to define the bottom surface of the plate package 2. The sealing plate 21 is substantially planar as shown in Figure 7, and has a through hole 22 at the corner of the sealing plate for mating with a corresponding through hole in the heat exchanger plate 3. The periphery of the sealing plate 21 is deflected upwardly to form a peripheral flange 23 that is adapted to abut against a corresponding flange of the overlying heat exchanger plate and to the corresponding flange, as is known in the art. The material thickness of the sealing plate 21 generally exceeds the material thickness of the heat exchanger plate, and thus the peripheral flange 23 can protrude slightly beyond the periphery of the surrounding wall 4 (1 mm to 2 mm). This example is shown in the bottom plan view of Figures 5A-5B. In certain embodiments, the mounting plate 7 can be attached directly to the sealing plate 21. In such 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 attached between the sealing plate 21 and the mounting plate 7 for the purpose of reinforcing the bottom surface of the plate package 2. Thus, the end surface 5 is thus defined by an additional reinforcement or support plate 24. The use of the stiffener 24 can be advantageous when the operating pressure of one or both of the media transported via the heat exchanger 1 is high, or when the operating pressure of one or both of the media changes over time. The stiffeners 24, shown in more detail in FIG. 8, have a uniform thickness and define through holes 25 that fit into the holes in the slab package 2. The periphery of the reinforcing plate 24 may be substantially flush with the periphery of the sealing plate 21 or the periphery of the wall 4 of the panel package 2. However, in the illustrated example, the stiffener 24 is adapted to protrude partially from the periphery of the wall 4. In particular, the stiffener 24 has a current interrupter 26 that is positioned to extend in a longitudinal direction between intersections 11 on individual lateral sides of the plate package 2 so as to substantially intersect the axial wall 4 Qi Ping. However, in Figures 5A-5B, the current interrupter 26 is slightly displaced inwardly from the axial wall 4. The longitudinal end points of the current interrupter 26 define an individual transition 27 to the protruding tab portion 28. In the example of Figures 5C to 5D, the transition 27 is positioned to overlap the perimeter of the mounting plate 7 near the intersection 11, and is shaped such that it is not perpendicular to the perimeter of the mounting plate 7 at the overlap, as in the heat exchanger 1 Seen in the direction of the bottom. This configuration of the stiffener 24 will locally reduce the stress in the stiffener 24 at the intersection 11. The transition 27 can, for example, form a bevel or bend from the current interrupter 26 to the tab 28. In Figures 5C-5D, the transition 27 is further configured to extend substantially coextensive with the perimeter of the mounting plate 7 at the overlap. Furthermore, as seen in Figures 5C-5D, the tab portions 28 protrude from the plate package 2 to substantially coextend with the individual mounting plates 7 and abut the individual mounting plates 7. This has been found to result in a favorable stress distribution between the mounting plate 7, the reinforcing plate 24 and the sealing plate 21, especially at the corners of the plate package 2. This will also increase the joint strength between the reinforcing plate and the mounting plate due to the increased contact area between the reinforcing plate 24 and the mounting plate 7. In an alternative embodiment, not shown, in addition to the small recesses, the stiffeners 24 project from the panel package 2 around the entire perimeter of the panel package 2, the small recesses being located near the intersection 11 to provide suitable A transition 27 is formed that is not perpendicular to the perimeter of the mounting plate 7 and preferably coextends with the perimeter.

The design of the mounting plate 7 (and the reinforcing plate if the reinforcing plate 24 is present) can be optimized based on the general principles outlined above by simulating the distribution of stresses in the heat exchanger structure. Such a simulation can be used to adapt the thickness of the mounting plate 7, the width of the mounting plate 7 in the longitudinal direction L, the shape and position of the concave portion 15 and such as the extension ΔL, ΔT (for a given α _max ), the lateral spacing δ T, radius R1, R2 and one or more of the further design parameters of the _main portion α _main for the concave portion 15. The simulation can be based on any known technique for numerical approximation of stress, such as finite element method, finite difference method, and boundary element method.

Several non-limiting examples of alternative configurations of the concave portion 15 are shown in Figures 9A-9B. The configuration in Fig. 9A is designed to be α _main = 6°, ΔT / ΔL = 10.4/29.6 = 0.35, δ T = 0, R1 = 10 mm, R2 = 15 mm. The configuration in Fig. 9B is designed to be α _main = 60°, ΔT / ΔL = 1.7, δ T = 0, R1 = 10 mm, and R2 = 15 mm.

The simulation of the stress distribution within the structure of Figures 5C-5D indicates that the stress is uniformly distributed for a particular vibration load condition without any significant spikes in the interface between the stiffener 24 and the seal plate 21. For this particular simulation, the maximum stress level is distributed along arrow L1, which is co-located with the starting point P1 (Fig. 5A). Here, the stress value is approximately 80 N/mm ² (MPa). The simulation also indicates that the stress is equally evenly distributed in the interface between the mounting plate 7 and the reinforcing plate 24, wherein a maximum stress level of approximately 50 N/mm ² is distributed along the arrow L2 in Fig. 5D. Incidentally, the arrow L2 is co-located with the end point P2. The corresponding simulation for the structure in Figure 9A indicates a corresponding maximum stress level with a similar distribution. The simulation for the structure in Figure 9B indicates approximately 110 N/mm ² around the starting point P1 and a maximum stress level of approximately 60 N/mm ² around the end point P2. For comparison, the stress distribution in the heat exchanger having the male mounting plate 7 (i.e., the mounting plate 7 without the concave portion) has also been simulated for the same vibration load condition, as shown in FIG. In this example, the reinforcing plate 24 has the same extension as the sealing plate 21. The simulation indicates a significant stress concentration at the junction of the mounting plate 7 and the reinforcing plate 24, with a maximum stress value of about 310 N/mm ² in the portion L3.

It should be understood that the design of the mounting plate 7 is affected by several design considerations. For example, the width of the mounting plate 7 in the longitudinal direction L can be set to minimize the weight and/or cost of the heat exchanger. This constraint can also limit the available width W of the concave portion 15 in the longitudinal direction L. The width W is generally indicated in Figures 9A-9B. In principle, the width W should be as long as possible in order to distribute the stress over the longer circumference. As stated, the width W is actually generally limited. The above design criteria specify △T/△L 2 for effective suppression of stress concentration. This does not necessarily mean that ΔT/ΔL is minimized. Instead, the design parameters and thus ΔT/ΔL can be optimized to minimize the maximum stress value for any given width W. The structure in Figures 9A through 9B has been optimized in this manner. Therefore, the maximum stress value is minimized for the structure in Fig. 9A at ΔT / ΔL = 0.35, and the maximum stress value is minimized at ΔT / ΔL = 1.7 for the structure in Fig. 9B. In general, the optimum ΔT/ΔL increases as the width W decreases. This can be understood by considering the following situation: although the stress at the starting point P1 will increase with the width W and decrease as ΔT decreases (ie, as the restricted perimeter is more parallel to the longitudinal direction L), However, when the width W is limited, significant stress is formed at and around the end point P2 if it is located near the surrounding wall 4. Therefore, the possible optimization for ΔT/ΔL aims to balance the stress formed at the starting point P1 with the stress formed at the end point P2. Generally, as the width W decreases, the end point P2 is moved away from the wall 4, i.e., by increasing ΔT, for example by increasing the main angle α _main and/or radius R2. The previous discussion is given to explain only the correlation of the ratio ΔT/ΔL, and does not imply that the design parameters of the concave portion 15 need to be optimized for a particular width W.

Although the present invention has been described in connection with what is presently regarded as the most practical and preferred embodiment, it is understood that the invention is not limited to the disclosed embodiments, but the invention is intended to cover the scope of the accompanying claims Various modifications and equivalent arrangements within the spirit and scope.

For example, the edge surface 14 can have any shape and angle relative to the top surface 12 and the bottom surface 13 of the mounting plate 7.

The reinforcing plate 24 may also be disposed in a plate heat exchanger 1 having a convex mounting plate 7 as shown in FIG. 6 as described and exemplified herein to increase the stability and durability of the plate heat exchanger 1, and The stress concentration at the intersection 11 is offset to some extent. This reinforcing plate 24 Support flanges 28 may be provided that extend beyond the perimeter of the surrounding wall 4 and are permanently connected to the top surface 12 of the mounting plate 7. The stiffener 24 can also define the transition 27 described above, which is positioned to overlap the perimeter of the individual mounting panels 7 at the intersection 11, and is shaped such that the overlap is not perpendicular to the perimeter of the individual mounting panels 7, and preferably The ground extends together with the perimeter.

As used herein, "top", "bottom", "vertical", "horizontal", and the like refer only to the orientation in the drawings and does not imply any particular orientation of heat exchanger 1. This terminology does not imply that the mounting board 7 needs to be disposed on any particular end of the panel package 2. Returning to Figure 1, the mounting plate can alternatively be disposed on the top axial end of the plate package 2 and can be permanently attached to the sealing plate or to the reinforcing plate of the overlying sealing plate. Furthermore, the mounting plate 7 can be arranged on the end of the plate package 2, which end is free of holes or at least one of the holes 6 is located in the middle of the mounting plate 7 at the end.

4‧‧‧ surrounding outer wall/wall/surrounding wall

5‧‧‧End surface

5A‧‧‧dotted rectangle

6‧‧‧ Holes

7‧‧‧Installation board

8‧‧‧through hole

10‧‧‧镗孔

11‧‧‧ intersection

13‧‧‧ bottom surface

15‧‧‧ concave part

Claims (19)

A plate heat exchanger comprising: a plurality of heat exchanger plates (3) stacked and permanently connected to form a plate package (2) defining a first medium and a second a first fluid path and a second fluid path of the medium, the first fluid path and the second fluid path being separated by the heat exchanger plates (3), the plate package (2) defining a surrounding outer wall (4), The peripheral outer wall extends in an axial direction (A) between the first axial end and the second axial end, an end plate (21; 24) permanently connected to the first axial end and One of the second axial ends to provide an end surface (5) extending between the first longitudinal end and the second longitudinal end in a lateral plane, the lateral plane being orthogonal to the axis Directional direction (A), and two mounting plates (7) permanently connected to respective surface portions of the end surface (5) at the first longitudinal end and the second longitudinal end, respectively, such that the mounting The plates (7) are spaced apart from one another in the longitudinal direction (L) on the end surface (5), wherein the mounting plates (7) The ground includes opposing flat engaging surfaces (12, 13) joined by an edge portion extending along the periphery of the mounting plate (7), wherein the mounting plates (7) are each One of the engagement surfaces (12, 13) arranged to be such a mounting plate is permanently connected to the end surface (5) such that the periphery of the mounting plate (7) extends partially beyond the peripheral outer wall (4) so that Defining a mounting flange (9) and extending across the periphery of the peripheral outer wall (4) across the end surface (5) in contact with the perimeter of the mounting plate, and wherein the mounting plate (7) The perimeter defines a concave shape comprising two concave portions (15) as seen in a normal direction of one of the end surfaces (5), the concave portions (15) being positioned Each of the surrounding outer walls (4) intersects at the intersection (11). A plate heat exchanger according to claim 1, wherein a subset of the concave portions (15) is located at or within the peripheral outer wall (4), respectively, and at the intersection (11) It is not perpendicular to the perimeter of the peripheral outer wall (4) as seen in the normal direction of the end surface (5). The plate heat exchanger of claim 2, wherein the subset of the concave portion (15) extends from the starting point (P1) to an end point (P2) on the concave portion (15), The local inclination of the concave portion given by the line along the subset is less than a maximum design angle (α _max ), and wherein the end point (P2) is located at the local inclination exceeding the maximum design angle (α _max ) Where. A plate heat exchanger according to claim 3, wherein the maximum design angle is defined between the tangent line and the longitudinal direction (L) and has a value of approximately 65°. A plate heat exchanger according to claim 3, wherein the subset comprises a substantially linear portion within at least 30% of the subset, the linear portion having a relative to the longitudinal direction (L) A predetermined angle (α _main ) that is less than the maximum design angle (α _max ). A plate heat exchanger according to claim 3, wherein the subset of the concave portions (15) has a first extension (ΔL) in the longitudinal direction (L) and a lateral direction a second extension (ΔT) on (T), the transverse direction (T) being orthogonal to the longitudinal direction (L) in the plane of the mounting plate (7), wherein the second extension (ΔT) is The ratio of the first extension (ΔL) is equal to or less than approximately 2, and is preferably equal to or less than approximately 1 or approximately 0.5. A plate heat exchanger according to claim 3, wherein the predetermined starting point (P1) of the subset is located at a maximum design distance from the individual intersection (11) in the lateral direction (T) Within (δ T), wherein the maximum design distance (δ T) is 20% of the first extension (ΔL). A plate heat exchanger according to claim 7, wherein the starting point (P1) substantially coincides with the intersection (11). A plate heat exchanger according to claim 3, wherein the end point (P2) is located in an outward corner of one of the mounting plates (7), the outward corner being defined by a second radius (R2). A plate heat exchanger according to any one of claims 1 to 4, wherein the periphery of the mounting plate (7) is not perpendicular to the periphery of the peripheral outer wall (4) at the intersection (11) As seen in the normal direction of the end surface (5). A plate heat exchanger according to claim 10, wherein the mounting plate (7) abuts the end surface (5) along the subset of the concave portion (15) and is permanently connected to the end surface . A plate heat exchanger according to claim 11, wherein the concave portion (15) comprises an inward corner defined by a first radius (R1) at which the inward corner is The surrounding outer walls (4) intersect as seen in a direction perpendicular to the end surface (5). The plate heat exchanger of claim 12, wherein the concave portion (15) extends between the two restriction points (C1, C2) on the periphery of the mounting plate (7), the restriction points (C1, C2) is defined by a mathematical line (ML) that intersects only the periphery of the mounting plate (7) at the limit points (C1, C2) and the mathematical line extends beyond the The periphery of the mounting plate (7) in the middle of the restriction point (C1, C2) is as seen in this direction perpendicular to the end surface (5). The plate heat exchanger according to any one of claims 1 to 4, wherein the end plate (21) is a sealing plate at one of the first axial end and the second axial end Permanently and sealingly connected to one of the heat exchanger plates (3). The plate heat exchanger according to any one of claims 1 to 4, wherein the end plate (24) is a reinforcing plate (24) permanently connected to one of the plate packages (2) a sealing plate (21), wherein the end plate (24) has at least two support flanges (28) extending beyond the periphery of the peripheral outer wall (4) so as to abut The installation defined by the mounting plate (7) On the flange (9). A plate heat exchanger according to claim 15 wherein the end plate (24) comprises a concave or inclined surface (27) along its periphery and as seen in the normal direction of the end surface (5). a concave or beveled surface adjacent the support flanges (28), wherein the concave or beveled surfaces (27) are positioned to overlap the perimeter of the mounting plate (7) at the intersections (11), respectively And wherein the concave or inclined surface (27) is not perpendicular to the periphery of the mounting plate (7) at the overlap and preferably coextends with the perimeter, such as the normal direction of the end surface (5) See you above. A plate heat exchanger according to any one of claims 1 to 4, wherein at least one of the mounting plates (7) defines at least one through hole (8) at the engaging surface (12) And extending between 13) and 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) to form An inlet or an outlet for the first medium or the second medium. The plate heat exchanger according to any one of claims 1 to 4, wherein the mounting flange (9) comprises a plurality of mounting holes (10), the plurality of mounting holes being adapted to receive for fastening Screws or pins for plate heat exchangers. The plate heat exchanger according to any one of claims 1 to 4, wherein the heat exchanger plates (3) are permanently joined to each other via melting of the metal material.